JPH10141499A - Four position actuator and automatic transmission with same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce the number of solenoid valves, reduce cost, improve the reliability of a four position actuator and an automatic transmission which uses it, and facilitate the layout of them. SOLUTION: In a four position actuator 4, a piston 45 receives travel force F1 , F2 , or F3 due to the supply of fluid pressure, and a first free piston 56, a second free piston 57, and a third free piston 58 generate piston travel force F4 (=F2 +F3 -F1 ), F5 , and F6 . The travel of the first to third free pistons is regulated by a first regulation part 74, a second regulation part 75, and a third regulation part 76. The above-mentioned travel force is generated selectively and the four position actuator is positioned to four positions by an air pressure supply control in which four solenoid valves M/V1, M/V2, M/V3, and M/V4 are used. Moreover, since the four position actuator can generate travel force F1 if one of the solenoid valves M/V1 and M/V2 is ON, these solenoid valves are also used to control a three position actuator 1, thereby realizing an automatic transmission which is operated by four solenoid valves.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a four-position actuator applied to a vehicle automatic transmission (remotely operated transmission) and the like, and an automatic transmission using the same.

[0002]

2. Description of the Related Art Recently, there has been an increasing demand for automatic shifting of large vehicles such as buses and trucks. Will be performed automatically.

[0003] In an automatic transmission, instead of manually operating the transmission, an actual shift operation of the transmission is performed by using an actuator that uses fluid pressure such as pneumatic pressure or hydraulic pressure. ing. However, the driver operates the shift lever when selecting a gear, but this only substantially switches the electric switch. By operating the shift lever, a signal of the selected stage is transmitted from the shift lever to an electronic control device as a control unit, and the electronic control device sends a control signal to the automatic clutch device to perform an automatic on / off operation of the friction clutch. At the same time, a control signal is sent to the above-described actuator to execute a shift operation of the transmission. In particular, when such an automatic transmission is used, it is not necessary to link the shift lever and the transmission in the vehicle interior with a link, and the distance is relatively long, which is very advantageous in layout.

Incidentally, as a fluid pressure actuator applied to an automatic transmission, a three-position actuator for performing a shift operation of an H-shaped gate in a vertical direction (vehicle longitudinal direction),
There is known a four-position actuator that performs a select operation in a lateral direction (vehicle left-right direction). These actuators are mainly composed of a cylinder and a piston, and operate a transmission-side operation lever in conjunction with the movement of the piston to execute a shift operation. Conventionally, three solenoid valves are used for each actuator to position the piston at three or four positions, and these are turned ON / OFF as appropriate.
By controlling this, the positioning of the piston was controlled. (Related technology: JP-A-5-60227)

[0005]

By the way, in such a conventional automatic transmission, at least six solenoid valves are required.
Including 12 for backup, 12 are required, and many solenoid valves are required, which is disadvantageous in cost and layout. In addition, when the number of solenoid valves is large, the probability of failure increases, reliability is deteriorated, and the running cost increases because the solenoid valves need to be periodically replaced. Further, the number of output ports of the electronic control device is increased, which is disadvantageous for miniaturization and integration of the electronic control device. Thus, it is desirable that the required number of solenoid valves be as small as possible.

[0006]

4-position actuator according to the present invention In order to achieve the above object, according to a piston reciprocating between one side and the other side in the cylinder by the action of the fluid pressure, whereas the moving force F ₁ to the side first pressure receiving surface that occurs, first generates a moving force F ₃ to the moving force F ₁ second pressure receiving surface that generates a moving force F ₂ to a larger second side, and the moving force F ₂ is greater than the other side Due to the piston having three pressure receiving surfaces and the fluid pressure acting on the second pressure receiving surface, a moving force F ₄ = F ₂ to one side is obtained.
+ F ₃ -F ₁ is generated on the fourth pressure receiving surface, and the moving force F to one side is generated by the first free piston transmitting the moving force F ₄ to the piston and the fluid pressure acting on the second pressure receiving surface.
₅ is generated on the fifth pressure receiving surface, and the second free piston transmitting the moving force F ₅ to the piston and the fluid pressure acting on the third pressure receiving surface generate the moving force F ₆ to the other side by the sixth free piston. A third free piston generated on the pressure receiving surface and transmitting the moving force F ₆ to the piston, a first regulating portion for regulating movement of the first free piston to one side,
The second to restrict the movement of the free piston to one side
It is provided with a regulating portion and a third regulating portion for regulating the movement of the third free piston to the other side.

The area ratio of the first to sixth pressure receiving surfaces is preferably 2: 3: 4: 5: 1: 1.

The automatic transmission according to the present invention further includes a fourth free piston on the other side of the piston, the four-position actuator for executing a select side operation of the transmission, and one end in a cylinder; Fluid pressure is supplied to the other end or both ends, and the piston is positioned at three positions.
A three-position actuator for performing a shift-side operation of the transmission, and four pipes for supplying fluid pressure to the four-position actuator, the first pipe being connected to the other side of the fourth free piston; A second pipe communicating between the fourth free piston and the piston, a third pipe communicating with the second pressure receiving face, a fourth pipe communicating with the third pressure receiving face, And a first and a second branch branched from a downstream side of the electromagnetic valves of the first and second pipes and connected to both ends of the three-position actuator, respectively. It is provided with piping.

Here, the three-position actuator includes a piston housed in the cylinder with a radial gap,
A pair of annular free pistons fitted into the gaps at both ends in the longitudinal direction of the piston, connecting portions of the first and second pipes provided at both ends in the longitudinal direction of the cylinder, and the free piston A protrusion provided on an end portion of the cylinder in the longitudinal direction of the cylinder and protruding radially inward so as to abut against an end surface of the piston; and a center portion of the free piston provided on an inner wall of the cylinder in the cylinder longitudinal direction. It is preferable to include a restricting portion for restricting the movement to the side.

[0010]

Preferred embodiments of the present invention will be described below in detail with reference to the accompanying drawings.

FIG. 5 shows the configuration of an automatic transmission according to the present invention. The automatic transmission is a combination of a transmission 2 shown in the drawings and a transmission (gear box) not shown. The transmission 2 has a three-position actuator 1 and a four-position actuator 4, and these actuators 1 and 4 are driven by pneumatic pressure supplied from an air tank 3. That is, here, air is used as the working fluid.
The air tank 3 and the four-position actuator 4 are connected to each other by four pneumatic pipes joined on the side of the air tank 3, that is, a first pipe 5, a second pipe 6, a third pipe 7, and a fourth pipe 8. The first, second, third and fourth solenoid valves M / V1, M / V2, M /
V3 and M / V4 are interposed. The solenoid valves M / V1 are ON / OFF controlled by an electronic control unit (controller) 9 such as an ECU. When ON, the solenoid valves M / V1 are opened to allow pneumatic supply to the four-position actuator 4 side (downstream side) and OFF. In this case, the air pressure supply is stopped by shutting off the air tank 3 side (upstream side), while releasing the air pressure by opening the 4-position actuator 4 side to the atmosphere.

Further, among these pipes 5, 6, 7, and 8,
In particular, in the first and second pipes 5 and 6, the solenoid valves M / V1,
The first and second branch pipes 10 and 11 are branched from the downstream side of the M / V 2 and connected to the three-position actuator 1.

FIG. 9 shows an H-shaped operation pattern of the transmission. In this operation pattern, a shift operation (for example, (R) to (N1) to (1)) along the vehicle longitudinal direction is a three-position actuator. The four-position actuator 4 is in charge of the select operation ((N1) to (N2) to (N3) to (N4)) along the left and right direction of the vehicle. Here, the transmission is a seven-speed gearbox with a reverse gear, and the actual shift position of the transmission or the shift lever is shown in parentheses. The numbers without parentheses indicate the position numbers by serial numbers corresponding to the respective shift positions. In this operation pattern, there are a total of twelve positions, three in the shift direction and four in the select direction.

Although not shown, a shift lever device manually operated by a driver is provided in the vehicle interior.
The shift lever device is an electric switch using a hall element or the like, and outputs a predetermined shift signal to the electronic control unit 9 by operating the driver's shift lever. The shift lever can be operated according to the operation pattern shown in FIG.

FIG. 6 is a sectional view showing the three-position actuator 1. The three-position actuator 1 is arranged along the front-rear direction of the vehicle. The upper part in the figure indicates the front of the vehicle.

As shown, a three-position actuator 1
Has a cylinder body 12, and a cylinder 13 is defined inside the cylinder body 12. The cylinder body 12 has a central portion in the longitudinal direction swelled in the orthogonal direction, and a housing chamber 14a of the shifter lever 14 is defined inside the swelled portion. The shifter lever 14 is a member that forms a part of the transmission.
The shift operation of the transmission is performed by rotating the transmission back and forth about the center 4b. The illustrated shifter lever 14 is at a center position corresponding to the neutral positions (N1) to (N4) in the operation pattern of FIG. 9 and can rotate forward or backward by a predetermined angle from this position.

The tip of the shifter lever 14 is the piston 1
5, the piston 15 moves in the cylinder 13 along the axial direction, and rotates the shifter lever 14. Here, a reduced diameter portion 16 is formed at the center in the longitudinal direction of the piston 15, and a hole 16a of the reduced diameter portion 16 is formed.
And the tip of the shifter lever 14 is engaged.

The piston 15 and the cylinder 13 extend in the longitudinal direction of the vehicle. Cylinder 13 is rear cylinder 1
7 and a front cylinder 18.
Both ends of the piston 15 are accommodated in 7, 18 respectively. Here, the two cylinders 17 and 18 are formed to have the same diameter, and the piston 15 is formed to have a smaller diameter than the cylinders 17 and 18, whereby a radial gap is formed between the piston 15 and the cylinder wall. A pair of annular free pistons, that is, a rear free piston 21 and a front free piston 22 are fitted in the gaps.

These free pistons 21 and 22 are
Protrusions 23 and 24 are formed at the ends on both ends in the longitudinal direction of the cylinder to be in contact with both end surfaces of the piston 15 respectively. Here, the projections 23 and 24 are ring-shaped, and the pistons 15 and
Are made to face inside the cylinders 17 and 18.

At both ends in the longitudinal direction of the cylinder 13, connecting portions 27 and 28 for connecting the first and second branch pipes 10 and 11 (FIG. 5) are provided.
The branch pipe 10 is provided in the rear cylinder 17 with the second branch pipe 1.
1 are communicated with each other in the front cylinder 18.

Further, the rear cylinder 17 and the front cylinder 18 have a rear end regulating portion 29 for regulating movement of the free pistons 21 and 22 toward the center in the cylinder longitudinal direction. A section regulation section 30 is provided. These restricting portions 29, 30 are cylinder 1
The thick wall portion 31 is formed on the cylinder body 12 so as to protrude to the vicinity of the outer peripheral surface of the piston 15.
It comprises a housing chamber 14a and a pair of partition walls 32 protrudingly formed to partition the inside of each of the cylinders 17 and 18. The partition 32 and the thick wall 31 define a hole 33 through which the piston 15 is inserted.

The free pistons 21 and 22 are slidable along the inner walls of the cylinders 17 and 18, respectively.
5 is slidable along the inner peripheral surfaces of the free pistons 21 and 22. In order to seal these sliding contact portions, seal members 34 and 35 are provided on the free pistons 21 and 22 and the piston 15, respectively. Rear cylinder 1
7, a rear pneumatic chamber 36 partitioned by the rear free piston 21 and the piston 15 is defined, and the front free piston 22 and the piston 15 are formed in the front cylinder 18.
And a front pneumatic chamber 37 is defined.
Then, air pressure is appropriately supplied to the air pressure chambers 36 and 37 as described later, and the piston 15 is moved to perform a shift operation. Note that the thick wall portion 31 is provided with an air vent hole 38 for opening the accommodation room 14a to the atmosphere.

In particular, in the illustrated example, the front and rear symmetrical configuration is made, and the outer diameter D of the free pistons 21 and 22 and the outer diameter d of the piston 15 are formed equal at the rear side and the front side, respectively. I have. Accordingly, the end surfaces of the piston 15 and the free pistons 21 and 22 have the same area on the rear side and the front side, and thus the total pressure receiving area of the piston 15 and the free pistons 21 and 22 is equal to the value A. Become.

FIG. 6 shows a state where the piston 15 is at the centering position, the shifter lever 14 is located at the center, and the transmission is in the neutral position (N1) to (N4). In this state, when the driver operates the shift lever to the neutral position (N1) to (N4), both the solenoid valves M / V1 and M / V2 are turned on, and both the pneumatic chambers 36 and 37 are turned on. This is achieved by supplying pneumatic pressure. In this case, the piston 15 is pushed with equal force from the front and rear and is positioned at the centering position.

Next, when the driver operates the shift lever forward to select a forward shift stage ((R), (2), (4) or (6)), the rear solenoid valve M / V1 is selected. Is ON, front solenoid valve M / V2 is
Set to OFF. As a result, as shown in FIG. 7, pneumatic pressure is supplied to the rear pneumatic chamber 36, and pneumatic pressure is discharged from the front pneumatic chamber 37. When this occurs, the piston 15 is positioned forward, the shifter lever 14 is rotated forward, and the transmission is put into the forward shift stage ((R), (2), (4) or (6)).

In particular, at this time, the movement of the rear free piston 21 is regulated by the rear regulating portion 29, and only the piston 15 moves while pushing away from the projection 23 and pressing the front free piston 22.

When the driver operates the shift lever rearward to select the rear shift stage ((1), (3), (5) or (7)), the electromagnetic wave on the front side is reversed. The valve M / V2 is turned on, and the rear solenoid valve M / V1 is turned off. As a result, as shown in FIG. 8, pneumatic pressure is supplied to the front pneumatic chamber 37 and the rear pneumatic chamber 3
Air pressure is discharged from 6. When this happens, the piston 15 is positioned rearward, the shifter lever 14 is rotated rearward, and the transmission shifts to the rear shift stage ((1), (3), (5) or (7)).
). Also at this time, similarly, the movement of the front free piston 22 is regulated by the front regulation part 30, and only the piston 15 moves while pressing away from the projection 24 and pushing the rear free piston 21.

FIG. 11 shows the relationship between the ON / OFF of the solenoid valve and the position of the piston 15. As can be seen, the pneumatic pressure is always supplied to one or both of the two pneumatic chambers 36 and 37 here. That is, the cylinder 13
Pneumatic pressure is supplied to one end, the other end, or both ends of the inside, whereby the piston 15 is positioned at three positions.

Now, in the three-position actuator 1, the free piston 2 is particularly provided at both ends of the piston 15.
By providing the first and second parts, the pressure receiving areas can be made equal at both ends, and the shifting force can be made uniform when moving in either direction. As a result, the shift operation can be performed in either the front or rear direction with the maximum shift force that the transmission synchronization can withstand, and the shift speed can be increased. And it can respond suitably also to the automatic transmission of a large vehicle.

That is, even in the conventional three-position actuator, there is an actuator which supplies air pressure to one end, the other end or both ends in the cylinder 13 to position the piston at the three positions. The piston is located only on one end side, and the pressure receiving area is different between the side with the free piston and the side without the free piston, resulting in a difference in the shift force and the shift speed. For this reason, even if the maximum shift force and the shift speed are obtained on one side of the free piston, the maximum shift speed cannot be obtained on the other side because the shift force is weak. Such a three-position actuator 1 can solve this point brilliantly. However, it is possible to use such a conventional product in the present invention.

In the configuration of the three-position actuator 1, the protrusions 2 of the free pistons 21 and 22 are used.
3 and 24 serve to transmit the pressure applied to the free pistons 21 and 22 to the piston 15, and
A value of 0 helps to position the free pistons 21 and 22 toward the center of the cylinder and to accurately position the piston 15 at the centering position when air pressure is applied from both front and rear directions. Further, the regulating portions 29 and 30 are useful for leaving the free pistons 21 and 22 as they are at the end of the piston 15 when air pressure is applied from any one of the front and rear directions. Note that the projection and the regulating portion may be provided separately instead of being provided integrally.

In this configuration, since air pressure supply / discharge control is performed through the two connecting portions 27 and 28, only two solenoid valves are required, and the cost can be reduced by reducing the number of solenoid valves.
Layout property or reliability can be improved. Moreover,
There is also an advantage that the cost can be prevented since the number of parts is almost the same as that of the conventional product.

Next, the four-position actuator 4 will be described.

FIG. 1 is a half sectional view showing the four-position actuator 4, and the upper part of the figure shows the front of the vehicle. The four-position actuator 4 is arranged along the left-right direction of the vehicle.

As shown, the four-position actuator 4
Also has a cylinder body 42 and the cylinder body 4
2, a cylinder 43 is defined and formed in the cylinder 43.
A piston 45 is inserted therein. A substantially central portion in the longitudinal direction of the cylinder body 42 is swelled in the orthogonal direction, and a housing chamber 44a of the selector lever 44 is defined and formed inside the swelling portion. The selector lever 44 is also a member forming part of the transmission, and the selector operation of the transmission is executed by rotating the selector lever 44 right and left about the rotation shaft 44b. The tip of the selector lever 44 is engaged with a piston 45, and the piston 45 is
3 moves along its axial direction and the selector lever 4
4 is rotated. Hole 4 in piston 45
6 is formed and fitted into the hole 46 so that the distal end of the selector lever 44 is engaged.

The movement of the piston 45 and the selector lever 44 is as shown in FIGS. FIG.
The state at the leftmost first position is shown, which is the leftmost column ((R), (N1),
(1)) is supported. Similarly, FIG. 2 shows the second position from the left (corresponding to (2), (N2), (3)), and FIG. 3 shows the third position from the left ((4), (N3 ), (5)), and FIG. 4 shows a state at the fourth position from the left, that is, at the fourth position on the rightmost side (corresponding to (6), (N4), (7)). Hereinafter, description will be made with reference to FIG.

The piston 45 has a first sliding portion 4 at its left end.
7 and the left end surface of the first sliding portion 47 is a first pressure receiving surface 48 for receiving pneumatic pressure. The right side of the first sliding portion 47 is a first shaft portion 49 reduced in diameter from the first sliding portion 47, and a reduced diameter portion 46 is formed in an intermediate portion thereof, and a right end portion thereof is formed. Is formed with a plate-shaped or flange-shaped second sliding portion 50 protruding outward in the radial direction. The right side of the first shaft portion 49 is a second shaft portion 52 having a further reduced diameter.
The right end surface of the first shaft portion 49 and the right side surface of the second sliding portion 50 thus formed have a second pressure receiving surface 51 for receiving air pressure.
To form The right side of the second shaft portion 52 is a third shaft portion 53 whose diameter is enlarged from the first sliding portion 47. At the right end of the third shaft portion 53, a plate-shaped or flange-shaped third sliding portion 54 protruding outward in the radial direction is formed, and the right end surface of the third sliding portion 54, that is, the right end surface of the piston 45 is formed. Is the third to receive air pressure
It is a pressure receiving surface 55.

An annular first ring is provided radially outside the second shaft portion 52.
A free piston 56 is slidably fitted. First
The left end face of the free piston 56 has a fourth
It is a pressure receiving surface 82. And the first free piston 5
An annular second free piston 57 is slidably fitted to the radially outer side of 6. Further, an annular third free piston 58 is slidably fitted radially outside the third sliding portion 54. On the left side of the piston 45, a fourth free piston 59 having the same diameter as the first sliding portion 47 is provided.

The cylinder 43 includes a first sliding portion 47 and a fourth sliding portion 47.
First cylinder portion 60 on which free piston 59 slides
And the second cylinder portion 61 on which the second sliding portion 50 is slid.
, A third cylinder portion 62 on which the second free piston 57 slides, and a fourth cylinder portion 63 on which the third free piston 58 slides. The inner radii R ₁ , R ₂ , R ₃ ,
R ₄ has a relationship of R ₃ > R ₄ > R ₂ > R ₁ .

On the other hand, in the first cylinder section 60, the fourth
The left side of the free piston 59 and the fourth free piston 59
And between the first sliding portion 47 and the first pneumatic chamber 6.
The fourth and second pneumatic chambers 65 are defined. Also the second
The cylinder part 61 and the third cylinder part 62 communicate with each other, and the left end is partitioned by the second sliding part 50 and the right end is the first slide part.
And a third pneumatic chamber 66 partitioned by the second free pistons 56 and 57. Further, the fourth cylinder portion 6
3, the third sliding portion 54 and the third free piston 5
On the right side of 8, a fourth pneumatic chamber 67 is defined. Each of the pneumatic chambers 64, 65, 66, and 67 has a first supply / discharge port 68, a second supply / discharge port 69, a third supply / discharge port 70, and a fourth supply / discharge port 71 serving as pneumatic supply / discharge ports, respectively. Is open. The above-mentioned first to fourth pipes 5, 6, 7, 8 are connected to these supply / discharge ports 68, 69, 70, 71, and communicate therewith.

Here, the second free piston 57 has, at the left end thereof, a projecting portion 57a projecting radially inward to push the left end surface of the first free piston 56. The third free piston 58 also has, at its right end, a protruding portion 58a protruding radially inward to press the right end surface of the third sliding portion 54.

The cylinder body 42 has first and second restricting portions 74 and 75 for restricting the first and second free pistons 56 and 57 from moving to the right, and a left side of the third free piston 58. And a third restricting portion 76 for restricting the movement to the side. Specifically, the first restricting portion 74 and the third restricting portion 76 are formed by both side surfaces of a partition wall 77 that partitions the third cylinder portion 62 and the fourth cylinder portion 63, and the second restricting portion 75 It is formed by the left side surface of the step portion 78 formed on the inner peripheral surface of the three cylinder portion 62. These restricting portions 74, 75, 76 are arranged in this order from the left side to a second restricting portion 75, a first restricting portion 74, and a third restricting portion 76. In particular, the first free piston 56 includes a second restricting portion 75.
Can be moved further to the right (see FIGS. 3 and 4).

It is to be noted that 79 and 80 are accommodation rooms 44 respectively.
a and an air vent hole opened at the right end of the third cylinder portion 62. Reference numeral 81 denotes the first to third sliding portions 47, 5
0, 54 and the first to fourth free pistons 56, 57,
Reference numerals 58 and 59 respectively denote seal members.

When pneumatic pressure is supplied to the third pneumatic chamber 66, the projection 57a of the second free piston 57 overlaps the first free piston 56 from the left side. Pneumatic pressure is applied to the left end face of the. At this time, the force substantially applied to the first free piston 56 is due to the pneumatic pressure applied to a portion of the left end surface of the second free piston 57 other than the protrusion 57a. Therefore, the second free piston 57
A portion of the left end surface excluding the portion of the protruding portion 57a, that is, a portion located radially outward from the first free piston 56 forms a fifth pressure receiving surface 72. Similarly, in the third free piston 58, a portion of the right end surface excluding the protruding portion 58a, that is, a portion located radially outside the third sliding portion 54 forms the sixth pressure receiving surface 73. .

Here, in particular, the radius of the first sliding portion 47 and the fourth free piston 59 is r ₁ (= R ₁ ), and the second sliding portion 5
The radius of 0 is r ₂ (= R ₂ ), and the radius of the third sliding portion 54 is r
₃ , the radius of the first free piston 56 is r ₄ , the radius of the second free piston 57 is r ₅ (= R ₃ ), the radius of the third free piston 58 is r ₆ (= R ₄ ), and the second shaft 52 Is r ₇ , and the ratio of these radii is r ₁ : r ₂ : r ₃ :
r ₄ : r ₅ : r ₆ : r ₇ = {2: {4:} 4: { ₆ :}
7: $ 5: $ 1. Therefore, the area ratio of the first to sixth pressure receiving surfaces 48, 51, 55, 82, 72, 73 is A
_{1: A 2: A 3:} A 4: A 5: A 6 = 2: 3: 4: 5:
1: 1.

When the pressure receiving surfaces 48 receive the air pressure P, a moving force F ₁ = 2P for pushing the piston 45 to the right on the first pressure receiving surface 48 is generated using the pressure P as a parameter.
On the second pressure receiving surface 51, a moving force F for pushing the piston 45 to the left.
₂ = 3P is generated, and a moving force F ₃ = 4P for pushing the piston 45 to the left is generated on the third pressure receiving surface 55, and the fourth pressure receiving surface 82 is generated.
, A moving force F ₄ = 5P for pushing the piston 45 to the right is generated, a moving force F ₅ = 1P for pushing the piston 45 to the right is generated on the fifth pressure receiving surface 72, and the piston 4 is pressed on the sixth pressure receiving surface 73.
A moving force F ₆ = 1P for pushing 5 to the left is generated. In this case, the relationship of F ₄ = F ₂ + F ₃ −F ₁ is established.

Next, the four-position actuator 4
Will be described.

First, as shown in FIG. 1, when it is desired to position the four-position actuator 4 or the piston 45 at the leftmost first position, the solenoid valves M / V1, M / V2 and M / V4 are turned on, and the solenoid valve M is turned on. Turn off / V3. In this case, the first pneumatic chamber 64 and the second
Pneumatic pressure is supplied to the pneumatic chamber 65 and the fourth pneumatic chamber 67, and the third
The pneumatic chamber 66 is opened to the atmosphere. In this case, since the fourth free piston 59 receives equal moving forces F ₇ and F ₈ (= 2P) in opposite directions on the left end face and the right end face, the fourth free piston 59 balances.
Eventually, the resultant force applied to the piston 45 is F
= F ₁ −F ₃ = 2P−4P = −2P, and the piston 4
5 will move to the left. The movement of the piston 45 is caused by the third sliding portion 54 abutting on the third regulating portion 76 and the piston 45 is moved by the fourth free piston 5.
The stop is achieved by abutting the left end wall of the cylinder 43 via 9. Thus, the four-position actuator 4 is positioned at the first position. At this time, the movement of the third free piston 58 is restricted by the third restricting portion 76 and is left behind, and the piston 45 moves leftward away from the third free piston 58. Therefore, the third free piston 58 exerts no force on the piston 45.

Here, the first pneumatic chamber 64 and the second pneumatic chamber 65
The air pressure was supplied to both of them, but the same operation can be achieved by only performing either one. That is, if only the first pneumatic chamber 64 is operated, the piston 45 can be pushed to the right with the moving force F ₇ = 2P via the fourth free piston 59, and if only the second pneumatic chamber 65 is operated, the pneumatic pressure is reduced. By itself, the piston 45 can be pushed to the right with a moving force F ₁ = 2P, and the fourth free piston 59 can be pushed to the left with a moving force F ₈ . Thus, the first pneumatic chamber 64 and the second pneumatic chamber 65
The same situation would occur if only one or both were supplied with air pressure. In the above case, there is also a method in which the pneumatic pressure is not supplied to both the pneumatic chambers 64 and 65.

Next, as shown in FIG. 2, when it is desired to position the four-position actuator 4 at the second second position from the left, one or both of the solenoid valves M / V1 and M / V2 are turned ON (see FIG. 2). In both cases, the solenoid valves M / V3 and M / V4 are turned ON. In this case, pneumatic pressure is supplied to all the pneumatic chambers 64, 65, 66, 67. In this case, the fourth free piston 59
Only gives a moving force F ₁ = 2P to the right of the piston 45, so that the resultant force applied to the piston 45 is F =
F ₁ −F ₂ + F ₄ + F ₅ −F ₃ −F ₆ = 2P−3P + 5
P + 1P-4P-1P = 0, and the piston 45 is placed in a balanced state. On the other hand, the second free piston 57 hits the second restricting portion 75 and stops, and the piston 45 is positioned from the left side via the first free piston 56, and the third free piston 58 stops hitting the third restricting portion 76. Since the piston 45 is positioned from the right side, the piston 45 is accurately positioned at the second position where the left side surface of the third shaft portion 53 contacts the first free piston 56.

[0051] Incidentally, if the piston 45 is to have moved from the position shown to the right, gone force F ₅ according to the second free piston 57 F = -1P next, the piston 4
5 is pushed back to the left. If the piston 45 moves to the left from the position shown in the figure,
Lost force F ₆ by the free piston 58 is F = 1P
, And the piston 45 is pushed back to the right. As a result, accurate positioning of the piston 45 to the second position is achieved. In the figure, the fourth free piston 59
Moves to the right and pushes the piston 45 at F ₇ = 2P, because the supply of pneumatic pressure from the second pneumatic chamber 65 to the first pneumatic chamber 64 was slightly faster, and vice versa. The fourth free piston 59 is pressed to the left and the piston 45
Will be pushed directly by air pressure. In any case, there is no change in giving F ₁ = 2P to the piston 45.

Next, as shown in FIG. 3, when it is desired to position the four-position actuator 4 at the third third position from the left, one or both of the solenoid valves M / V1 and M / V2 are turned ON (FIG. In both cases, the solenoid valve M / V3 is turned on and the solenoid valve M / V4 is turned off. In this case, the first to third pneumatic chambers 64, 65, 66
And the fourth pneumatic chamber 67 is opened to the atmosphere.
In this case, since the second free piston 57 hits the second restricting portion 75 and stops, the resultant force applied to the piston 45 is F = F ₁ −F ₂ + F ₄ = 2P−3P + 5P.
= 4P, and the piston 45 moves rightward. This movement is caused by the first free piston 56 being moved by the first regulating portion 7.
4 until it hits. At this time, the first free piston 56 is connected to the projection 57a of the second free piston 57.
Move to the right side away from. Thus, the positioning of the four-position actuator 4 to the third position is achieved.

[0053] Note that if the piston 45 is to have moved from the position shown to the right, the force F ₄ according to the first free piston 56 is lost F = -1P next, the piston 4
5 is pushed back to the left. Even if the piston 45 moves to the left from the position shown in the figure, if the first free piston 56 does not hit the projection 57a of the second free piston 57, the F = 4P remains unchanged, and the piston 45
Is pushed back to the right. This achieves accurate positioning of the piston 45 at the third position.

Next, as shown in FIG. 4, when it is desired to position the four-position actuator 4 at the fourth fourth position from the left, one or both of the solenoid valves M / V1 and M / V2 are turned on (see FIG. 4). In both cases, the solenoid valves M / V3 and M / V4 are both turned off. Thus, air pressure is supplied only to the first and second pneumatic chambers 64 and 65, the third and fourth pneumatic chambers 66 and 67 are opened to the atmosphere, and the moving force received by the piston 45 is F = F ₁ = With only 2P, the piston 45 moves to the right. This movement is caused by the movement of the piston 45 to the third free piston 5.
8 until it hits the right end wall of the cylinder 43. Thus, the positioning of the four-position actuator 4 to the fourth position is achieved.

In the four-position actuator 4 operated as described above, the same operation is achieved no matter how the pneumatic pressure is supplied to the first pneumatic chamber 64 and the second pneumatic chamber 65. Therefore, by combining with the above-described three-position actuator 1 and performing ON / OFF control of the solenoid valve in the combination shown in FIG. 10, the transmission can be operated at all positions 1 to 12 in the operation pattern of FIG. At the end of control such as when the vehicle is stopped, all the solenoid valves are turned off.

In particular, in the four-position actuator 4, since the pneumatic supply to the first pneumatic chamber 64 and the second pneumatic chamber 65 does not interfere with each other, the pneumatic supply to these pneumatic chambers 64, 65 is not performed. The solenoid valves M / V1 and M / V2 for executing control can be used for controlling the three-position actuator 1. Since the operation control of the four-position actuator 4 can be completely executed in combination with the remaining two solenoid valves M / V3 and M / V4, at least four solenoid valves and eight including the backup valve are required. This greatly reduces the number of solenoid valves, reduces costs (including running costs), improves reliability, simplifies layout,
The output port of the electronic control unit can be omitted, the weight can be reduced, and the assembling work can be simplified.

Although the preferred embodiment of the present invention has been described above, the present invention can adopt various other embodiments. For example, as the working fluid, other fluids such as working oil can be used in addition to air. Further, the values of the radius ratio and the moving force of each part can be changed to other values. Further, the four-position actuator of the present invention can be used as a positioning actuator not only in an automatic transmission of a vehicle but also in various other fields.

[0058]

In summary, the present invention significantly reduces the number of solenoid valves, reduces costs (including running costs),
Excellent effects such as improvement of reliability, simplification of layout, elimination of output ports of the electronic control device, reduction of weight, simplification of assembly work, and the like are exhibited.

[Brief description of the drawings]

FIG. 1 is a half-sectional view of a four-position actuator according to the present invention, showing a state at a first position.

FIG. 2 is a half sectional view of a four-position actuator according to the present invention, showing a state when the actuator is at a second position.

FIG. 3 is a half sectional view of the four-position actuator according to the present invention, showing a state when the actuator is at a third position.

FIG. 4 is a half sectional view of a four-position actuator according to the present invention, showing a state when the actuator is at a fourth position.

FIG. 5 is a configuration diagram showing an automatic transmission according to the present invention.

FIG. 6 is a sectional view showing a three-position actuator.

FIG. 7 shows a state when the three-position actuator is at a front position.

FIG. 8 shows a state when the three-position actuator is at the rear position.

FIG. 9 is a diagram showing an operation pattern of a shift lever and a transmission.

FIG. 10 is a table showing combinations of ON / OFF of solenoid valves in the automatic transmission.

FIG. 11 is a table showing combinations of ON / OFF of solenoid valves when the three-position actuator operates.

[Explanation of symbols]

1 3 position actuator 4 4 position actuator 5 1st piping 6 2nd piping 7 3rd piping 8 4th piping 10 1st branch piping 11 2nd branch piping 13 cylinder 15 piston 21 rear free piston 22 front free piston 23, 24 Projecting portions 27, 28 Connecting portion 29 Rear regulating portion 30 Front regulating portion 43 Cylinder 45 Piston 48 First pressure receiving surface 51 Second pressure receiving surface 55 Third pressure receiving surface 56 First free piston 57 Second free piston 58 Third free piston 59 Fourth free piston 72 Fifth pressure receiving surface 73 Sixth pressure receiving surface 74 First restricting portion 75 Second restricting portion 76 Second restricting portion 82 Fourth pressure receiving surface F ₁ , F ₂ , F ₃ , F ₄ , F ₅ , F ₆ Moving force M / V1, M / V2, M / V3, M / V4 Solenoid valve

Claims (4)

[Claims] 1. A piston for reciprocating the one side and the other side in the cylinder by the action of the fluid pressure, while the first pressure receiving surface that generates a moving force F ₁ to the side, than the moving force F ₁ second pressure receiving surface that generates a moving force F ₂ to the large other side, and a piston having a third pressure receiving surface which generates a moving force F ₃ to the moving force F ₂ is greater than the other side, the second pressure receiving Due to the fluid pressure acting on the surface, the moving force F ₄ = F ₂ to one side
+ F ₃ -F ₁ on the fourth pressure receiving surface, and the first free piston for transmitting the moving force F ₄ to the piston;
Due to the fluid pressure acting on the pressure receiving surface, a moving force F ₅ to one side is obtained.
Was generated in the fifth pressure receiving surface, and a second free piston for transmitting該移power F ₅ to the piston by the fluid pressure acting on the third pressure receiving surface, the sixth receiving a moving force F ₆ to the other side And a third force generated on the surface and transmitting the moving force F ₆ to the piston.
A free piston, a first regulating portion for regulating movement of the first free piston to one side, a second regulating portion for regulating movement of the second free piston to one side, A three-position actuator, comprising: a third regulating part for regulating movement of the three free pistons to the other side. 2. An area ratio of the first to sixth pressure receiving surfaces is 2:
The four position actuator of claim 1 wherein the ratio is 3: 4: 5: 1: 1. 3. The four-position actuator according to claim 1, further comprising a fourth free piston on the other side of the piston to perform a select side operation of the transmission, and one end side and the other end side in the cylinder. Alternatively, a fluid pressure is supplied to both ends, and the piston is positioned at the three positions, and a three-position actuator for executing a shift-side operation of the transmission and four pipes for supplying the fluid pressure to the four-position actuator are provided. A first pipe connected to the other side of the fourth free piston, a second pipe connected between the fourth free piston and the piston, a third pipe connected to the second pressure receiving surface, A fourth pipe communicated with the third pressure receiving surface, a solenoid valve interposed in each of the first to fourth pipes, and a branch from a downstream side of the solenoid valve of the first and second pipes, 3rd above An automatic transmission comprising: first and second branch pipes respectively connected to both ends of a stationary actuator. 4. The piston, wherein the three-position actuator is accommodated in the cylinder with a radial gap, and a pair of annular free pistons respectively fitted into the gap at both longitudinal ends of the piston. A connecting portion of the first and second pipes provided at both ends in the longitudinal direction of the cylinder, and a radially inner portion provided at an end of the free piston in the longitudinal direction of the cylinder and abutting against an end surface of the piston. 4. The automatic apparatus according to claim 3, further comprising: a projection formed so as to protrude in a direction, and a regulating portion provided on an inner wall of the cylinder, for regulating movement of the free piston toward the center in the longitudinal direction of the cylinder. transmission.