JPS58160663A - Speed shifting device for toroidal stepless trasmission - Google Patents

Abstract

PURPOSE:To smooth the rotation of a trunnion, by applying a transmission ratio instruction signal to a fluid pressure rotary valve extending to the end of the pivot of the trunnion and secured on a housing, to enhance the sensitivity of the valve. CONSTITUTION:A transmission ratio instruction signal generator 21 determines the optimal transmission ratio at every point in time to produce an instruction signal for the ratio to turn a step motor 20 by a required angle. Consequently, a rotor shaft 15 and a rotor 14 are turned by a desired angle to make a phase difference between a sleeve 11 and the shaft and the rotor to connect cylinder ports A, B to a feed port P and a drain port T or connect the cylinder ports A, B to the drain port and the feed port, respectively. As a result, pistons 71, 81 are moved in the same direction so that a trunnion 4 is moved up or down. At that time, a power roller 3 or the trunnion 4 is turned about the axis Z-Z of a pivot to change the radius of circle of engagement of the power roller on an input and an output discs to alter the transmission ratio.

Description

DETAILED DESCRIPTION OF THE INVENTION According to the present invention, the paired inner surfaces of an input disk and an output disk provided on input and output shafts disposed on the same axis cooperate with each other to form a toroidal cavity. Place the KA roller in the toroidal cavity,
The invention relates to a 5K toroidal continuously variable transmission in which the power roller is engaged with the input/output disk and a large torque is transmitted by the traction disturbance generated in the retaining portion, and in particular, the power roller is engaged with the input/output disk. The present invention relates to a transmission device which performs a speed change by rotatably moving the device by a small amount by a hydraulic piston in the direction of the pivot axis.

Generally, in a toroidal continuously variable transmission, when the trunnion device that rotatably supports the power roller is moved a small amount in the direction of its pivot axis, the rotational axis of the power roller is displaced from the rotational axis of the input/output disk. It is known that rotation around the axis occurs and the radius of the engagement circle between the power roller and the input/output disk changes, that is, the gear ratio changes.

However, a transmission device that moves a trunnion device by a small amount in the direction of its pivot axis as described above is conventionally disclosed in U.S. Pat. No. 314
The one disclosed in Japanese Patent No. 2189 is known. This includes, at the pivot shaft end of the trunnion device, a fluid pressure cylinder that moves the trunnion device in the direction of the pivot axis, and a thrust cam that converts the rotation angle of the trunnion device into axial displacement, and further includes these fluid pressure cylinders. A piston-type S-a operated by the interaction of the thrust cam and the thrust cam.
The rotation angle of the trunnion is converted into an axial displacement by a thrust cam, but since the lift amount of the cam cannot be increased, there is a risk that the sensitivity of the servo valve will be limited.

b The gear ratio is limited by the actual rotation angle of the cam and its lift amount, but it is difficult to attach the cam concentrically to the shaft end of the trunnion device, and it is difficult to engage the power roller with the input/output disk. When the trunnion device is bent due to the large pressing force required to achieve this, the cam also moves in the axial direction, changing the apparent lift amount, which has the disadvantage of requiring a large device for accurate control. .

Since the C-cam and valves are connected by links and stacked in the axial direction of the trunnion, it is difficult to make the whole structure compact. Therefore, the pulp piping needs to be made flexible. Therefore, it is disadvantageous in terms of space, life, cost, etc. □ e It was difficult to create a sealed structure for the thrust cam and piston-type servo valve, resulting in insufficient lubrication and measures against foreign objects, which caused problems in terms of precision maintenance and longevity.

The present invention solves all of the above conventional problems, and includes:
In particular, it provides a small, compact and inexpensive transmission with excellent speed ratio selection and durability, and is also suitable for use in continuously variable transmissions for internal combustion engines with good fuel efficiency. , a fluid pressure cylinder device provided at the end of the pivot shaft of the trunnion device, a fluid pressure rotary valve extending to the end of the pivot shaft and fixed to the cylinder, and inputting a speed ratio command signal to the rotary nozzle. It is equipped with a device for

The present invention will be explained below with reference to the illustrated embodiments.

FIG. 1 shows a toroidal continuously variable transmission according to the present invention which is engaged in a well-known manner by a retaining member (not shown) so as to rotate together.

Although not shown, an output shaft and an output disk are similarly provided on the front side.

A plurality of roller rollers 3 are disposed within a toroidal cavity formed between the input disk 2 and the output tie plate and are rotatably supported by bearings on a trunnion 4, and are engaged with the input and output disks by pressing against each other. are doing. Reference numeral 31 is a thrust ball bearing, and 32 is a roller bearing.

Now, the trunnion 4 is held by the tension member 5.5 via a spherical outer surface bearing 6, and is rotatable around the pivot axis Z-2 and can be moved by a small amount in the Z-Z axis direction. ing. Furthermore, a fluid pressure cylinder 7 is installed at the shaft end of the trunnion 4.
．． 8 are provided, each piston 71.81 being in contact with the trunnion 4 via a thrust bearing 41.42. The cylinder shaft z-2 is fixed to the cylinder 9 as a rotary shaft. That is, the sleeve shaft 12
is connected to the shaft end of trunnion 4, and a sleeve
The sleeve nib 11 is rotatably fitted into the valve casing 13, and the rotor 14 is fitted inside the sleeve 11.
It is fitted inside so that it can rotate freely twice. It passes through the sleeve shaft 12 & the piston 71, and is connected to the shaft end of the trunnion 4 via a rotation stopper 16 (see Fig. 2), which rotates as the trunnion 4 rotates, and rotates in the axial direction. Don't follow the movement of... It's like...

The shaft 14 is connected to the rotor shaft 1 through a rotation stopper 17.
The rotor shaft 15 is connected to a stepping motor via a wheel train 19. The stepping motor 20 is connected to a gear ratio command signal generator 21, which receives gear ratio information n such as engine rotational speed and vehicle speed, and determines the gear ratio. The gear ratio command signal output is from the stepping motor 20.
is input.

A cross section of the rotary valve 10 is shown in FIG. In the illustrated embodiment, there are eight grooves 111 and four supply boats P. Cylinder boats A and B are alternately arranged and bored in the land portion between the grooves 111 as shown in the figure. A groove 141 is provided on the outer diameter of the cylinder boat A facing the land of the sleeve 11.
, B, the discharge hole T is bored from the land of the rotor 14 toward the inner hole. Therefore, when the sleeve 11 and the rotor 14 rotate relative to each other, either the cylinder bow A or B communicates with the supply boat P, and the other side communicates with the discharge hole ↑. At this time, in order to prevent relative rotation between the sleeve 11 and the rotor 14 beyond the maximum valve distance f (angle θ), the stopper 18 is placed on the rotor shaft 1 as shown in FIG.
5 to prevent the valve from moving when the present transmission is stationary and causing the positional relationship between the sleeve 11 and the rotor 14 to collapse and the valve to malfunction.

Based on the feeding speed ratio information 22, the optimum speed ratio is calculated and determined every moment in the speed ratio command signal generating device 21, and the speed ratio command signal is issued, and the stepping motor 20 is rotated by the required angle by this output.

Along with this rotation, the rotor shaft 15 and the rotor 14 rotate through the gear train 19 by a required angle, and which phase of the sleeve 11 is shifted so that the cylinders A and B communicate with either the supply point P or the discharge hole T, respectively. and piston 71.81
moves in the same direction, and the trunnion 4 moves either up or down.As mentioned above, the rotational axis of the power roller 3 intersects with the rotational axis of the input/output disk of the transmission, so the power roller 3 and the trunnion 4 pivot. Axis line z-2
The power roller rotates around the input/output disk, and the radius of the engagement circle between the power roller and the input/output disk changes, that is, the gear ratio changes (speeding up or decelerating). At this time, the direction of rotation of the trunnion 40 around the z-2 axis is the same direction as the rotor 14, and therefore the sleeve 11 follows the rotor 14, so that the output signal of the speed ratio command signal generator 21 eventually changes. This means that a gear ratio commensurate with that can be obtained.

Based on wear, link play, etc. (there is no problem, rotary valves have a longer travel distance of the valve surface than the cam lift amount, so the valve sensitivity is improved, and as a result, the trunnion rotation becomes smoother. , transient vibrations during gear shifting are prevented.

Also, since the rotary pulp casing 13 can be directly attached to the housing 9 of the transmission, the fluid piping does not need to be flexible (it can be a metal tube or a hole can be made in the casing 13, and the overall structure is It is simple and advantageous in terms of space and cost, and it is easy to form a sealed structure, which is advantageous in terms of moisture and dirt.

In addition, only the rotation related to gear shifting is transmitted to the rotary valve.
There is no possibility that other deformation or axial movement of the trunnion will directly affect valve operation. As shown in Figure 5, the conventional cam and direct-acting pulp are connected by a link.
A rotor shaft 15 may be connected to the shaft end of the runner 4 via a rotation stopper pin 16 as described above, and a sleeve @12 may be connected to the wheel train 19 which is the final stage of the gear ratio command signal generating device.

In this case, the respective configurations are approximately the same as those in Figure 1, and those with the same functions are also numbered 1,
- Detailed explanation will be omitted since the reference numerals are attached, but it is easy to see that the functions and effects are roughly the same as described above.
W will be understood.

Furthermore, regarding the uninvented components, their shapes, dimensions, etc. are not intended to be limited to those of the embodiments shown in FIGS. 1 to 5 above.

[Brief explanation of the drawing]

FIG. 1 is a partial cross-sectional view of a toroidal continuously variable transmission including a vertical cross-sectional view of the transmission device of the present invention, particularly a rotary pulp, and FIG. 2 is a cross-sectional view taken along the line ■-■ in FIG. l...Input shaft, 2...Input disk, 3...Power roller, 4...Trunion, 7.8...Fluid pressure cylinder, 10...Rotary valve, 11...Sleeve, 12... Sleeve shaft, 14... Rotor, 15
... Rotor shaft, 18... Stopper, adding... Stepping motor, 21... Speed ratio command signal generator,
n...Transmission ratio information Applicant Nippon Shuko Co., Ltd. 弗2 diagram! 75 Figure

Claims (1)

[Scope of Claims] (1) A housing, an input shaft and an output shaft rotatably and coaxially supported by the housing; A disk and an output disk, and opposing surfaces of both disks cooperate with each other to form a toroidal cavity, and a plurality of power rollers are arranged in the toroidal cavity symmetrically with respect to the axis of the input/output shaft, and the power rollers are arranged in the toroidal cavity. A trunnion device rotatably supported by the housing and rotatably supported by the housing around a pivot axis perpendicular to the rotation axis thereof, the input/output disk and the power roller are compressed and engaged with each other to create a trunnion supporter. a support device for attaching the trunnion device to the housing so that the trunnion device can be moved by a small amount in the direction of the pivot axis; A fluid pressure cylinder device provided at the end of the pivot shaft for movement, and a fluid pressure cylinder device provided at the end of the pivot shaft K so that the pulp opens and closes in accordance with the rotation of the trunnion device.
g and a fluid pressure rotary pulp fixedly installed in the I/Using, and a device for inputting a speed ratio command signal to the rotary pulp, and a device for inputting a speed ratio command signal to the rotary pulp. opens, fluid pressure is applied to the cylinder device, and the trunnion device begins to move in the direction of the pivot axis.At the same time, the trunnion device rotates around the pivot axis, and the radius of the engagement circle of the power roller with respect to the input/output disk changes. A transmission device for a toroidal continuously variable transmission, characterized in that the pulp of the rotary valve is returned to a neutral position following this change, and the gear ratio is changed to the commanded gear ratio. □ Body) The rotary pulp sleeve is installed electrically at the end of the pivot shaft of the trunnion device, and is connected via a rotation stopper so that it rotates as the trunnion device rotates but does not follow the movement in the axial direction. The rotor is coaxially fitted into the sleeve and is connected to a gear ratio command signal generator,
2. The transmission device for a toroidal continuously variable transmission according to claim 1, wherein the rotor is rotated relative to the sleeve by input of the command signal to open and close a valve. (3) A transmission device for a toroidal continuously variable transmission according to claim 1, wherein a sleeve of rotary pulp is connected to a gear ratio command signal generating device and connected to a rotor ridge trunnion device. (4) The invention according to any one of claims 1, 2, and 3, wherein means for preventing the sleeve and rotor from mutually rotating beyond the maximum opening of the valve is provided. Toroidal continuously variable transmission gearbox.