JPH01250657A - Toroidal type continuously variable transmission - Google Patents

Abstract

PURPOSE:To prevent slippage by providing input and output discs, attaching a hydraulic operating chamber to one of the discs for urging the disk to be pressed to a power roller, and introducing line pressure controlled by a control valve to the operating chamber. CONSTITUTION:Input and output discs 11, 13 are pressed to a power roller 12 rotatably mounted on a support capable of moving in the axial direction. An oil path 66 diverged from an oil path 61 of a regulator valve 3 is connected to a hydraulic operating chamber 7 for urging the disc, which is formed at the rear portion of the input disc 11. The oil path 61 is kept at line pressure by the regulator valve 3 to operate the hydraulic operating chamber 71 through the oil path 66. When input torque from the input disc 11 is increased, the oil pressure on drive side is increased and passed through an oil path 63 in the direction of closing a port, so that the line pressure in the oil path 66 is increased to increase the P pressing force of the input disk 11. Accordingly, slippage between the input and output discs 11, 13 and the power roller 12 can be prevented.

Description

Detailed Description of the Invention (Industrial Application Field) The present invention provides a power roller that is interposed between discs on the input side and output side in a press-contact state, and by changing the inclination of the power roller using hydraulic pressure, the power roller can be used in a stepless manner. This invention relates to a toroidal continuously variable transmission that changes speed.

(Prior art) As a conventional toroidal continuously variable transmission,
There was one described in JP-119864.

As shown in FIG. 4, this conventional toroidal continuously variable transmission has a toroidal transmission section 1, a control valve 2. It was equipped with a regulator valve 3 and a pump 5.

In this conventional toroidal continuously variable transmission, when the engine is started, the oil pump 5 is driven, and the oil pressure generated by the oil pump 5 is transferred to the central port 3 of the regulator valve 3.
Sent to 5. Then, this oil pressure acts on the port 37 at the right end of the spool 32 via the oil passage 62, and the spool 32
is moved to the left against the spring 34. As a result, the ports 35 and 38 are communicated with each other, and the suction side of the oil pump 5 is drained. Therefore, the central port 35
The oil pressure in the oil passage 61 connected to the line is maintained in a state where this oil pressure and the spring force of the spring 34 are balanced (line pressure).

When changing the gear ratio of the toroidal transmission section 1, the actuator 24 operates the sleeve 22 of the control valve 2, for example, to the right in the figure. As a result, the ports 27 and 28 communicate with each other, and the line pressure acts on the drive-side hydraulic chamber 17a through the oil passages 61 and 64, and the port communicates with the non-drive-side hydraulic chamber 17b through the oil passage 65. 29 is drained through a hole 23a provided in the spool 23. Therefore, the hydraulic pressure in the drive-side hydraulic chamber 17a increases, and the left support 14 moves upward.
The right supports 14 each move downward. As a result, the direction of the tangential force applied to the power roller 12 changes, so the left power roller 12 and the support 14 rotate counterclockwise around the axis of the input disk 11.
The right power roller 12 and support body 14 rotate clockwise. That is, the toroidal transmission section l shifts to the deceleration side. The precise cam 25, which rotates together with the left support 14, rotates counterclockwise, and the spool 2
3 to the right until port 28 is closed. As described above, the toroidal transmission section 1 is controlled to a desired gear ratio and maintained at the gear ratio shown in parentheses.

Note that 63 is an oil passage for transmitting the oil pressure in the drive-side hydraulic chamber 17a to the back pressure chamber 33 of the regulator valve 3 to regulate the line pressure.

In a toroidal continuously variable transmission with two or more, the input disk 11 and the output disk are moved in a direction in which the input disk 11 and the output disk approach each other so that the power roller 12 does not slip between one input disk member and the opposing output disk. Needs to be energized.

A conventional device for preventing the power roller from slipping between the input disk and the output disk is disclosed in Japanese Patent Publication No. 1242/1983. As shown in FIG. 5, this toroidal type continuously variable transmission has a race 114 arranged behind an input disk 111, and this race 114 is connected to a disk member 114a having a cylinder 114a' formed inside, It consists of a piston 114b that is slidably fitted into 114a', and a bearing eye 5 is interposed between the piston 114b and the input disk III. and cylinder 114
Hydraulic pressure generated by a pump 117 driven by a cam l17a as the input shaft 118 rotates is introduced into a' via an oil passage 118, and the piston 1I4b presses the input disk III via the bearing 115. , to prevent the power roller 112 from slipping.

(Problem to be solved by the invention) However, in the above-mentioned conventional toroidal continuously variable transmission, 9
In order to prevent slippage between the disks 111, 113 and the power roller 112 even when the input torque from the input disk 111 is at its maximum, the line pressure generated by the pump 117 must be adjusted to the maximum when the input torque is at its maximum. It was necessary to configure them accordingly.

In this case, even when the input torque from the 1-input disk 111 is low, a high line pressure is always introduced into the cylinder 114a, so the discharge loss of the pump 117 becomes large, and the disk 11.1.113 Since the pressing force between the disk and the power roller 112 is always at the maximum, there has been a problem in that the efficiency of transmitting the driving force between the disk and the power roller is also reduced.

This invention has been made in order to solve the problems of conventional toroidal continuously variable transmissions as described in 2. In other words, the contact force between the disc and the power roller is always optimally controlled by hydraulic pressure.

An object of the present invention is to provide a toroidal continuously variable transmission capable of preventing discharge loss of an oil pump and reduction in transmission efficiency between a disk and a power roller.

(Means for Achieving the Object) In order to achieve the second object, a power roller is interposed in pressure contact between an input disk and an output disk facing each other, and this power roller is connected to the input disk. and is rotatably supported by a support that is movable in a direction perpendicular to the axial direction of the output disk, and has a drive side and a non-drive side on both sides of the support body in the direction of movement for urging the support body toward the other side by hydraulic pressure. A drive-side hydraulic chamber is formed, and a control valve for controlling the hydraulic pressure in these hydraulic chambers is connected between the control valve and a hydraulic pressure supply source to regulate line pressure and adjust the line pressure to the spool. In the toroidal continuously variable transmission, the toroidal continuously variable transmission is further provided with a regulator valve on one end side, through which the hydraulic pressure in the drive side working hydraulic chamber acts on the other end side of the spool in opposite directions, respectively, at least one of the input disk or the output disk. A hydraulic pressure chamber for biasing the disk is provided for introducing hydraulic pressure into the disk and urging the disk in a direction to press the disk against the power roller, and the control valve is connected to this hydraulic pressure chamber for pressure regulation. It is characterized by the fact that the line pressure is introduced.

In addition to the configuration of the invention described in item 2, a second aspect of the present invention provides a torque converter connected between the engine and the input disk, and a forward shift position and a position between the disk biasing hydraulic chamber and the regulator valve. It is characterized in that a shift valve is connected that supplies line pressure from the regulator valve to the hydraulic pressure chamber for disc bias only when in the reverse shift position.

(Function) In the toroidal continuously variable transmission with the above configuration, the control valve controls the hydraulic pressure in the driving side and non-driving side working hydraulic chambers to move the support body and bring the power roller into contact with the input disk and the output disk. By displacing the position, the speed can be changed steplessly between the input disk and the output disk.

When the torque input from the input disk increases, the support body is urged in the direction of compressing the drive-side working hydraulic chamber, and the pressure inside the drive-side working hydraulic chamber increases. The line pressure acting on the spool of the regulator valve is opposed to the line pressure acting on one end of the spool, thereby displacing the spool and regulating the line pressure. The line pressure regulated by this regulator valve is increased or decreased in conjunction with the oil pressure in the drive-side working hydraulic chamber, and therefore the line pressure is regulated in response to fluctuations in the input torque at the input disk.

The line pressure regulated in response to fluctuations in the input torque is introduced into a disk biasing hydraulic chamber attached to at least one of the input disk and the output disk. This disc biasing hydraulic chamber is designed to press the disc and power roller into hydraulic pressure contact in order to prevent slippage between the input disc, power roller, and output disc in the toroidal transmission section. be.

Line pressure regulated in response to increases and decreases in the input torque of the input disk is introduced from the regulator valve into this disk biasing hydraulic chamber. Therefore, when the input torque from the input disk increases, the hydraulic pressure in the disk biasing hydraulic chamber increases due to the increase in line pressure.
Since the contact force between the input disk, power roller and output disk is increased, there is no risk of slippage occurring.

Also, when the input torque from the input disk decreases,
The line pressure is reduced and the contact force in the toroidal transmission section is also reduced.

Furthermore, in the second aspect of the toroidal continuously variable transmission, when a torque converter is used as the 0-start clutch, this torque converter cannot completely cut off the driving force, so the shift valve is only in the forward or reverse shift position. Hydraulic pressure is introduced into the urging hydraulic chamber, thereby making the toroidal transmission part double as a clutch.

(Example) This invention will be described in more detail below based on an example shown in two drawings. Note that the same reference numerals will be used to describe the same configurations as in the prior art.

In FIGS. 1 and 2, the toroidal transmission section 1 has two power rollers 12 disposed in pressure contact between an input disk it and an output disk 13 facing each other, and each power roller 12 has a shaft. via support 14
It is rotatably supported by. At both ends of the support body 14 are provided pistons 15a that are slidable within the cylinder.
, 15b are arranged in series, and the support body 14 is the piston 15a,
15b in the axial direction (in the figure).

It is movable in the vertical direction) and rotatable around the axis of the power roller. Moreover, hydraulic working chambers 17a and 17b are formed inside the cylinder, and one of these hydraulic working chambers 17a and 17b is connected to an input disk 1.
The side opposite to the illustrated rotation direction A of 1 is the drive side hydraulic operating chamber 1
7a, and the opposite side thereof is a non-drive side hydraulic chamber 17b.

The control valve 2 includes a sleeve 22 slidably inserted into the valve body and a spool 23 slidably inserted into the sleeve 22. sleeve 2
2 is actuated in the axial direction by an actuator 24 of the gear ratio control device, and the left end of the spool 23 is connected to the presis cam 2.
5 and the biasing force of spring 2B.

This brisis cam 25 is connected to the upper end of one of the supports 9, for example, the left support 14, and rotates together with the support 14 to move the spool 23 forward and backward.

The regulator valve 3 has a spool 32 inserted into the valve body so as to be freely retractable.
is urged rightward by a spring 34 provided in the first back pressure chamber 33. A central port 35 of the regulator valve 3 is connected to the discharge side of the oil pump 5, and a port 3B adjacent to this port 35 is connected to the suction side of the oil pump 5. The port 35 is connected to the central port 27 of the control valve 2 via the oil passage 61 and the oil passage 61A, and is also connected to the oil passage 6! An oil passage 62 branched from is connected to the port 37 at the right end of the regulator valve 3. The first back pressure chamber 33 of the regulator valve 3 is connected to the drive side hydraulic chamber 17a of the toroidal transmission section 1 via an oil passage 63, and further connected to the left side of the control valve 2 via an oil passage 64 branched from the oil passage 63. port 28 of
It is connected to the. On the other hand, the non-drive side hydraulic chamber 17b is connected to the right port 29 of the control valve 2 through an oil passage 65.

The above configuration is the same as that of the conventional toroidal continuously variable transmission.9For example, when this transmission is mounted on a car and the car runs on flat ground, torque is transmitted from the input disk 11 of the toroidal transmission section 1. is input, and when this input torque increases, the increase in hydraulic pressure in the drive-side hydraulic chamber 17a is transmitted to the first back pressure chamber 33 of the regulator valve 3 via the oil passage 63, and as a result, the spool 3
2 to the right in the drawing to increase the line pressure in the oil passage 61.

The toroidal continuously variable transmission according to the present invention further includes an oil passage 6.
As shown in FIG. 2, an oil passage 6B branched from the input disk 1 is connected to a hydraulic chamber 71 (disk biasing hydraulic chamber) formed at the rear of the input disk U of the toroidal transmission section 1.

FIG. 2 shows the configuration of the toroidal transmission section 1 of the toroidal continuously variable transmission shown in FIG. 1 viewed from the radial direction of the disk. The input disk 11 is fitted into a cylinder 72 that is immovably attached to the cylinder 72 so as to be slidable in the axial direction. A hydraulic chamber 71 is formed between the cylinder 72 and the input disk 11, and an oil passage 6B branched from the oil passage 61 is connected to this hydraulic chamber 71.

The input disk 11 is attached to an input shaft 81 connected to an engine 82 so as to be able to slide freely in the axial direction and rotate integrally therewith, and power is transmitted from the input disk 11 to the output disk 13 via the power roller 12. will be done. Further, a starting clutch 83 is provided at the rear of the output disk 13, and engagement of the starting clutch 83 drives the output shaft 84, thereby rotating the forward gear 85 and the reverse gear 8B.

Next, the operation of the ``-2 toroidal continuously variable transmission will be explained.

When the engine 82 is started, the oil pump 5 is driven, and the hydraulic pressure generated by the oil pump 5 is introduced into the boat 35 at the center of the regulator valve 3. Then, this oil pressure acts on the right end of the spool 32 through the oil passage ei, 82, and moves the spool 32 to the left against the spring 34. As a result, the boat 35 and the boat 36 are communicated with each other and connected to the suction side of the oil pump 5. Therefore, the oil pressure in the oil passage 61 connected to the central boat 35 is maintained in a state where this oil pressure and the spring force of the spring 34 are balanced (line pressure PL).

This line pressure PL acts on the hydraulic chamber 71 of the input disk 11 of the toroidal transmission section 1 through the oil path 6B, urges the input disk 11 to the right in the drawing, and forces the input disk 11
．． A pressure contact force is generated between the power roller 12 and the output disk 13 to enable transmission of driving force.

Here, when the input torque from the input disk 11 increases, the input disk It moves to the support 14 on the right side in FIG.
In order to urge the support body 14 on the left side upward and downward, the hydraulic pressure in the drive-side hydraulic chamber 17a increases. This increase in the hydraulic pressure in the drive-side hydraulic chamber 17a is transmitted to the back pressure chamber 33 of the regulator valve 3 via the oil passage 63, and urges the spool 32 to the right, that is, in the direction of closing the boat 36. As a result, the line pressure PL in the oil passage 6B rises, and the contact force between the two-input disk 11, the power roller 12, and the output disk 13 increases.

Conversely, when the input torque from the 1-input disk 11 decreases, the right support 14 moves downward due to rotational resistance from the output disk 13 side.

The left support body ■4 is forced upward and the drive side hydraulic operation chamber 1
The oil pressure in 7a is reduced. This decrease in the hydraulic pressure in the drive-side hydraulic chamber 17a is transmitted to the back pressure chamber 33 of the regulator valve 3 through the oil passage 63, and the spool 32 of the regulator valve 3 is biased by the line pressure of the boat 37 to the left side. By sliding in the opposite direction, the line pressure PL in the oil passage 6G is lowered. As a result, the hydraulic pressure in the hydraulic chamber 71 decreases, causing the input disc If in the toroidal transmission section 1 to decrease.

The contact force between the power roller 12 and the output disk 13 is reduced as the input torque is reduced.

FIG. 3 shows another embodiment of the present invention, and while the embodiments shown in FIGS. 1 and 2 are equipped with a starting clutch 83 at the rear of the toroidal transmission section 1, this starting clutch 83 is An example is shown in which a torque converter 100 is used instead. A shift valve 200 that can be switched manually is connected in the middle of the oil path from the regulator valve 3 to the hydraulic chamber 71 of the toroidal transmission section 1. When in this position, the oil passage 86A and the oil passage 813B are connected to introduce pressure oil into the hydraulic working chamber 71.

In this embodiment, the operation of the toroidal transmission section 1' in response to fluctuations in input torque is similar to the embodiments shown in FIGS. 1 and 2. Here, the torque converter 100 cannot completely cut off the driving force when in neutral,
By operating the shift valve 200, pressure oil is introduced from the regulator valve 3 into the hydraulic chamber 71 only during forward and reverse shifts, so that drive force transmission can be completely cut off in the toroidal transmission section 1. Therefore, when using the torque converter 100.

There is no need for a separate clutch to completely disconnect the driving force transmission, and the torque converter 10 can also be used as a starting clutch.
By using 0, complicated control such as an electromagnetic clutch or a wet multi-disc clutch is not required.

In each of the above embodiments, only the case where the hydraulic chamber for disc biasing is attached to the input disk side is shown, but this hydraulic chamber may be attached to the output disk, or the input disk It may be attached to both the output disk and the output disk.

(Effects of the Invention) As described above, according to the present invention, the pressure contact force between the input disk, power roller, and output disk in the toroidal transmission section is increased or decreased in accordance with the increase or decrease in input torque, so that the oil pump discharge loss is reduced. There is no risk of slippage occurring in the toroidal transmission section even if the input torque increases, and there is no risk of the driving force transmission efficiency decreasing even if the input torque decreases. Furthermore, it is less expensive than electronically controlling the pressure contact force in the toroidal transmission section.

Furthermore, if a shift valve is added that supplies pressure pressure to the toroidal transmission section only in the forward and reverse shift positions, it becomes possible to provide the toroidal transmission section with a clutch function.

[Brief explanation of the drawing]

1 and 2 are hydraulic circuit diagrams showing one embodiment of the present invention;
FIG. 3 is a hydraulic circuit diagram showing another embodiment of the present invention, FIG. 4 is a hydraulic circuit diagram showing a conventional example, and FIG. 5 is a side sectional view showing another conventional example. 1.1°...Toroidal transmission section. 2...Control valve. 3...Regulator valve. 5...Oil pump. 11...Input disk. 12...Power roller. 13...Output disk. 14...Support. 17a... Drive side hydraulic operation chamber. 63...Oil road. 6B...Oil road. 71... Hydraulic operating chamber. 100...torque converter. 200...Shift valve. Figure 1 Figure 4

Claims (1)

[Claims] 1. A power roller is interposed in pressure contact between an input disk and an output disk that face each other, and this power roller is movable in a direction perpendicular to the axial direction of the input disk and output disk. The support body is rotatably supported, and drive-side and non-drive-side hydraulic chambers are formed on both sides of the support body in the moving direction for urging the support body toward the other side using hydraulic pressure. A control valve is connected between the control valve and a hydraulic pressure supply source to regulate line pressure, and the line pressure is applied to one end of the spool, and the hydraulic pressure in the driving side hydraulic chamber is connected to the spool. In a toroidal continuously variable transmission equipped with regulator valves acting in opposite directions on the other end side, hydraulic pressure is introduced into at least one of the input disk and the output disk to cause the disk to act as a power roller. A toroidal device characterized in that a hydraulic chamber for biasing the disc is attached to bias the disc in a direction of pressure contact, and the control valve is connected to the hydraulic chamber for biasing the disc, and a regulated line pressure is introduced therein. Continuously variable transmission. 2. Connect a torque converter between the engine and the input disk, and connect a line from the regulator valve to the hydraulic chamber for disc bias only in the forward shift position and reverse shift position between the hydraulic pressure chamber for disc bias and the regulator valve. The toroidal continuously variable transmission according to claim 1, further comprising a shift valve for supplying pressure.