JPH07317705A - Fluid pressure actuator - Google Patents

Abstract

PURPOSE:To improve responsiveness by directly connecting the other chamber formed by being sectioned by a movable member to a drain port by a discharge passage, and parallely providing a plurality of control valves having the passage diameters different from each other on a communication passage. CONSTITUTION:The other chamber out of respective chambers sectioned and formed by a movable member (a piston) 5 to reciprocate in a fluid chamber 4 and a drain port 24 are directly connected to each other by a discharge passage 26, and a plurality of control valves 31, 32 having the passage diameters different from each other are provided on a communication passage 27. Thereby, fluid pressure in the chamber is quickly discharged, and responsiveness in the rising part to the full-stroke position of the movable member 5 is improved, and the passage diameter is extended, and fluid pressure can be quickly discharged from one side chamber to the drain port 24, and responsiveness of the movable member 5 in the returning part from the full-stroke position to the original position is improved. Since the DUTY times are increased and the flow rate is decreased, delicate control can be performed, and smooth control is made possible.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a fluid pressure actuator for connecting a clutch, for example.

[0002]

2. Description of the Related Art As a conventional fluid pressure actuator of this type, for example, there is a hydraulic actuator for electrically controlling engagement / disengagement of a clutch, which is implemented in a manual transmission of an automobile as shown in FIG. Figure 7
FIG. 3 is a schematic view of a system in which a hydraulic actuator is used. That is, the hydraulic actuator 100 is composed of a hydraulic cylinder section 101 and a control section 102 for controlling the hydraulic cylinder section 101. The control section 102 controls the hydraulic cylinder section 101 to control the hydraulic cylinder section. A clutch 103, which is operatively connected to 101 via a rod 109, is connected.

The hydraulic cylinder portion 101 includes a hollow body 104 as an actuator body and a body 104.
Of the fluid chamber 105 formed inside the hollow of the
5, a piston 106 as a movable member that is reciprocally inserted, an oil chamber A107 and an oil chamber B108 divided into two chambers by the piston 106, and operatively connected to the oil chamber A107 side of the piston 106. And a rod 109.

On the side wall 104A of the body 104, a supply port 110 for supplying hydraulic pressure to the fluid chamber 105 and a drain port 1 for discharging hydraulic pressure in the fluid chamber 105.
11 is provided.

The control unit 102 is integrally provided on the side wall 104A of the body 104. This control unit 1
Reference numeral 02 denotes a flow passage C112 as a supply flow passage that connects the supply port 110 and the oil chamber B108, a normally closed solenoid valve C113 as a control valve that controls the opening and closing of the flow passage C112, the drain port 111 and the oil. Flow path B11 as a discharge flow path communicating with the chamber A107
4 and a normally closed type solenoid valve B115 as a control valve for controlling opening / closing of the flow passage B114.
And the oil chamber A107 via the flow passage B114 and the flow passage C112.
Flow path A1 as a communication flow path that connects the oil chamber B108 with the oil chamber B108.
16 and a normally open type solenoid valve A117 as a control valve for controlling opening / closing of the flow path A116.
It consists of and.

The hydraulic actuator 100 configured as described above is applied to a system as shown in FIG. In this system 50, a piston 10 of a hydraulic actuator 100 is provided at one end of an oscillating body 53 that oscillates around a fulcrum P.
6, the tip of a rod 109 that is operatively connected is connected, and the driven body 54 that is connected to the clutch 103 is connected to the other end of the oscillating body 53.
Is connected to the engine side E, at the 0 point of the piston 5, the piston 5 moves against the spring force of the clutch spring 52, so that the clutch 103 is released. The arrow D in FIG. 7 indicates the mission drive side.

FIG. 6 shows a fluid circuit diagram of the hydraulic actuator 100.

8 (a) and 8 (b) show the operating characteristics at the time of shifting, and FIG. 8 (a) shows the solenoid valve A.
FIG. 8 is a control timing chart of 117, B115, and C113, and FIG. 8B is a piston stroke diagram according to the control timing shown in FIG. The vertical axis of the piston stroke diagram is the stroke of the piston 106 (m
m), the horizontal axis represents time (sec).

Here, the piston stroke diagram shown in FIG. 8B is shown by a solid line with reference to the solenoid valve control timing diagram shown in FIG. 8A and the system schematic diagram of FIG. 7. After the piston 106 is stroked to the clutch 103 to make a full stroke (6 mm position) against the spring force of the clutch spring 52,
During the return process, the clutch will be 3mm and the clutch will be engaged.

[0010]

However, in the case of the above-mentioned prior art, the response of the piston stroke to the solenoid valve control timing of FIG. 8 (a) is slow from the piston stroke diagram of FIG. 8 (b). I understand. As a result, there is a drawback that the control is difficult.
Therefore, in order to improve the responsiveness (piston speed) as shown by the dotted line in the piston stroke diagram of FIG. 8 (b), it has been considered to increase the oil passage diameter of the solenoid valves A117, B115, C113. Due to the relationship between the supply pressure to 105 and the suction force of the solenoid valves A117, B115, and C113, the current level (solid line) was impossible.

However, in the piston stroke diagram of FIG. 8 (b), the solenoid valve B115 is eliminated and only the portion A of the rising portion to the full stroke position is abolished, and the abolished portion is blindly plugged into the oil chamber. A10
By connecting 7 and the drain port 111 directly, it was possible to obtain the response shown by the dotted line. However,
It was not possible to improve the responsiveness at the portion B of the return portion from the full stroke position to the original connection position via the half clutch position.

9 (a), 9 (b) and 9 (c) show the operating characteristics when the vehicle starts, and FIG. 9 (a) is a control timing chart of the solenoid valves A117, B115 and C113. FIG. 9 (b) is a piston stroke diagram according to the control timing shown in FIG. 9 (a). The vertical axis of the piston stroke diagram is the stroke (mm) of the piston 106, and the horizontal axis is time (sec).

In the control at the time of starting, when the stroke of the piston 106, which is a half clutch, is used, the solenoid valve A117 is set to the duty (DU) as shown in FIG. 9A.
Since the speed of the piston 105 is DUTY controlled by controlling the TY), it actually has a stepped shape as shown by the dotted line, and it is also possible to make it smooth (fine) by the same supply pressure and solenoid valves A117 and B1 as described above.
It was impossible due to the suction force of C13 and C113.

The present invention has been made to solve the above-mentioned problems of the prior art, and an object of the present invention is to provide a fluid pressure actuator capable of improving responsiveness.

[0015]

In order to achieve the above object, the present invention has a movable member that is reciprocally moved in a fluid chamber formed inside a hollow actuator body. A fluid pressure is supplied from a pressure source to one of the compartments formed by controlling the fluid pressure of each compartment. A supply port, a drain port for discharging fluid pressure from the other chamber via a discharge channel, a communication channel for communicating one chamber with the other chamber, and a control valve for controlling opening / closing of the communication channel. In the fluid pressure actuator having, the other chamber and the drain port are directly connected to each other through the discharge flow path, and a plurality of control valves having different flow path diameters are provided in parallel in the communication flow path. And

[0016]

In the hydraulic actuator having the above-mentioned structure, the other of the chambers in which the fluid chamber is partitioned by the movable member and the drain port are directly connected to each other through the discharge passage, so that Since the fluid pressure is discharged quickly, the response at the rising portion of the movable member up to the full stroke position is improved, and a plurality of flow path diameters are connected in parallel between the communication flow paths that connect one chamber and the dray port. By providing different control valves, the flow path diameter is expanded, the discharge of fluid pressure from one chamber to the drain port can be speeded up, and the movable member of the return part from the full stroke position to the original position can be Response is improved.

Further, by providing a plurality of control valves having different flow passage diameters provided in parallel between the communication flow passages, if the control valve having a small flow passage diameter is used for DUTY control, the DUTY cycle is shortened and the DUTY ratio is reduced. Since it also becomes smaller, the number of DUTY increases and the flow rate becomes smaller, so that fine control can be performed and smooth control can be performed.

[0018]

DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention will be described below with reference to illustrated embodiments. 1 and 2 show a hydraulic actuator as a fluid pressure actuator according to an embodiment of the present invention. This hydraulic actuator 1 is for electrically controlling the engagement and disengagement of a clutch, which is carried out in a manual transmission of an automobile, as in the prior art. 1 and 2, reference numeral 1 denotes a hydraulic actuator. The schematic structure of the hydraulic actuator 1 includes a hydraulic cylinder section 2 and a control section 3 for controlling the hydraulic cylinder section 2.
The control unit 3 controls the hydraulic cylinder unit 2 to connect the clutch 51 operatively connected to the hydraulic cylinder unit 2.

The hydraulic cylinder portion 2 includes a hollow body 8 as an actuator body, a fluid chamber 4 formed inside the hollow, and a piston 5 as a movable member which is reciprocally inserted in the fluid chamber 4. An oil chamber A6 and an oil chamber B7 defined by the piston 5, and an oil chamber A of the piston 5.
The rod 9 is operatively connected to the 6 side.

The body 8 has a hollow portion whose one end is open and whose inner diameter is coaxially formed of a large diameter portion 81 and a small diameter portion 18, and a through hole which is coaxially communicated with the small diameter portion 18 of the hollow portion and is open at the other end. And holes 17. A sleeve 10 having a substantially U-shaped cross section is inserted and fixed in the hollow portion at the open end of the large diameter portion 81, and the fluid chamber 4 is formed from the sleeve 10, the large diameter portion 81 and the small diameter portion 18 of the hollow portion. Has been formed.

The piston 5 is reciprocally inserted into the large diameter portion 81 of the fluid chamber 4, and the fluid chamber 4 is partitioned by the piston 5 into an oil chamber A6 and an oil chamber B7. The oil chamber A6 is on the through hole 17 side, and the oil chamber B7 is on the sleeve 10 side. The inside of the small-diameter portion 18 of the oil chamber A has a nut 19 for fixing the rod 9 to the piston 5, which will be described later.
However, it is designed to enter when the piston 5 strokes.

On the oil chamber A6 side of the piston 5, one end of a rod 9 is screwed and fixed coaxially with the piston 5 via a nut 19, and on the oil chamber B7 side, the inside of the sleeve 10 is a bearing A12 and a bearing A12. A protruding portion 5A that is slidably inserted through a packing A14 that is a seal member is integrally provided.

The sleeve 10 has a hole 10A at the bottom, and the stroke sensor 11 of the piston 5 is fixed to the end surface of the body 8 through the hole 10A.
The stroke sensor 11 has a protrusion 5 of the piston 5.
It is provided facing the end face of A.

The rod 9 has a bearing B in the through hole 17.
It is reciprocally movable via 16.

Incidentally, packings B, C15, 13 as seal members are mounted on the outer periphery of the piston 5 and the inner peripheral edge of the outer end surface of the through hole 17 of the body 8, respectively.

On the other hand, on the side wall 8A of the body 8, the fluid chamber 4
A supply port 23 for supplying hydraulic pressure to the valve and a drain port 24 for discharging the hydraulic pressure in the fluid chamber 4 are provided.

The control section 3 is integrally provided on the side wall 8A of the body 8. The control unit 3 includes a flow path C as a supply flow path that connects the supply port 23 and the oil chamber B7.
25, a flow path D26 as a discharge flow path that directly connects the drain port 24 and the oil chamber A6 to each other, and a communication flow that connects the oil chamber A6 and the oil chamber B7 via the flow paths C25 and D26. A channel E27 as a channel, and a channel E27
Is divided into a flow path A28 and a flow path B29 in parallel.

The flow passage C25 is provided with a normally closed type solenoid valve C30 as a control valve for controlling the opening and closing of the flow passage C25.

Further, the flow passage E27 is provided with a normally open type solenoid valve A31 and a normally open type solenoid valve B32 as control valves for controlling opening / closing of the flow passage E27. That is, the solenoid valve A31 controls the opening / closing of the flow path A28, and the solenoid valve B32 controls the opening / closing of the flow path B29. The oil passage diameter of the solenoid valve A31 is almost the same as that of the solenoid valve A117 of the related art, and the oil passage diameter of the solenoid valve B32 is set smaller than that of the solenoid valve A31.

A fluid circuit diagram of the hydraulic actuator 1 having the above-described structure is shown in the right block of the fluid circuit diagram shown in FIG. On the other hand, the block on the left side of the fluid circuit in FIG.
FIG. 6 is a circuit diagram for supplying hydraulic pressure to a supply port 23 via an introduction flow path 33, which shows a tank 34 and a hydraulic oil in the tank 34 through a flow path 33 and a supply port 23. It consists of an electric pump 35 for introducing into the chamber 4, a check valve 36 for preventing backflow, a relief valve 37 for controlling the hydraulic pressure in the fluid circuit, and an accumulator 38 connected between the electric pump 35 and the supply port 23. ing.

The hydraulic actuator 1 having the above structure
Is applied to the system 50 shown in the related art (see FIG. 7), and when the clutch 51 is connected to the engine side E, the stroke of the piston 5 is 0 point (see FIG. 1).
Then, the stroke of the piston 5 (moving to the right in the drawing) causes the clutch 51 to separate from the spring force of the clutch spring 52.

Reference numeral 60 in the drawing denotes a steel ball, which is a side wall 8 of the body 8.
This is for closing the open end when each flow path is formed in A. The steel ball 60 is caulked and deformed after being press-fitted into the open end so as not to come off.

Next, the hydraulic actuator 1 having the above structure.
The operation characteristic of the above-described shift operation will be described when the control is performed by the control timing chart of the solenoid valves A31, B32, C30 shown in FIG.

The initial state is solenoid valves A31 and B3.
Since both 2 and C30 are OFF, the solenoid valves A31 and B32 are opened and the solenoid valve C30 is closed, so that the hydraulic pressure is not supplied and the clutch spring 52
The piston 5 is moved to the left side in the figure by the spring force of, and stops at the stroke 0 point determined by the connection position on the clutch 51 side.

Next, the solenoid valves A31, B32,
When both C30 are turned ON, the solenoid valve C30 is opened and the solenoid valves A31 and B32 are closed, the hydraulic pressure from the pressure source is supplied to the oil chamber B7 through the supply port 24 and the flow path C25, and the oil chamber A6 is also supplied. Is directly connected to the drain port 24 through the flow path D26 and the hydraulic pressure is 0 kgf / cm ² , so the piston 5 makes a stroke and after a full stroke (6 mm position), the solenoid valve C30 is turned off.
Set to F. As a result, the full stroke position is maintained.

When the solenoid valves A31 and B32 are turned off after a predetermined time elapses and both are opened, the hydraulic pressure in the oil chamber B7 is changed to the flow passage C25, the flow passage A28 and the flow passage B2.
Since it is almost discharged from the drain port 24 via 9 (there is a little, it is supplied to the oil chamber A via the flow path D26). Therefore, the piston 5 is returned to the original stroke 0 by the spring force of the clutch spring 52. It returns to the point position, and the clutch 51 is engaged. During this return (3 mm position), solenoid valves A31, B32
Is turned on and off for a half clutch and then connected.

Thus, the stroke of the piston 5 is as shown in FIG.
The operating characteristic is indicated by the dotted line in the piston stroke diagram of (b). The solid line in the figure is the operating characteristic of the above-mentioned conventional technique.

In the hydraulic actuator of the above construction, the oil chamber A6 and the drain port 24 are directly connected by the flow passage D26, so that the oil pressure in the oil chamber A6 is discharged faster than in the prior art. As a result, the response of the piston 5 at the portion A (refer to FIG. 3B) at the rising portion to the full stroke position of the prior art is improved, and at the same time, between the oil passage B7 and the flow passage E27 that communicates the drain port 24. Since the two solenoid valves A31 and B32 are provided in parallel, when the solenoid valves A31 and B32 are opened, the diameter of the oil passage is enlarged, and the oil pressure from the oil chamber B7 to the drain port 24 is discharged quickly, resulting in a full pressure. The response of the piston 5 at the B portion (see FIG. 3B) of the return portion from the stroke position to the connection position of the clutch 51 is improved. This allows
The responsiveness (piston speed) is improved in both parts A and B as compared with the operating characteristics of the prior art.

Next, the operation characteristics at the time of starting will be described when the control is performed by the control timing chart of the solenoid valves A31, B32, C30 as shown in FIG. 4 (a).

In the initial state, solenoid valves A31 and B3
Since both 2 and C30 are OFF, the solenoid valves A31 and B32 are opened and the solenoid valve C30 is closed, so that the hydraulic pressure is not supplied and the clutch spring 52
The piston 5 is moved to the left side in the figure by the spring force of, and stops at the stroke 0 point determined by the connection position on the clutch 51 side.

Next, the solenoid valves A31, B32,
When both C30 are turned ON, the solenoid valve C30 is opened and the solenoid valves A31 and B32 are closed, the hydraulic pressure from the pressure source is supplied to the oil chamber B7 through the supply port 24 and the flow path C25, and the oil chamber A6 is also supplied. Is directly connected to the drain port 24 through the flow path D26 and the hydraulic pressure is 0 kgf / cm ² , so the piston 5 makes a stroke and after a full stroke (6 mm position), the solenoid valve C30 is turned off.
Set to F. As a result, the full stroke position is maintained.

Then, after a lapse of a predetermined time, only the solenoid valve B32 is set to DUTY control, and opening and closing are repeated,
When opened, the hydraulic pressure in the oil chamber B7 is discharged from the drain port 24 through the flow passage C25 and the flow passage B29, so that the piston 5 gradually strokes to the half clutch position (3 mm) by the spring force of the clutch spring 52. . Solenoid valve B3 at this half-clutch position
2 is turned on once, and after a predetermined time of turning on the solenoid valve A31, both are turned off, and when both are opened, the oil pressure in the oil chamber B7 is drained through the flow passage C25, the flow passage A28, and the flow passage B29. 24, the piston 5 strokes at a speed faster than the speed up to the half-clutch, and returns to the original stroke 0 point position.
Are connected.

Thus, the stroke of the piston 5 is as shown in FIG.
The operating characteristics are shown in the piston stroke diagram of (b).

As described above, the clutch 51 is used when starting the vehicle.
When the speed of the stroke of the piston 5 is slowed down in order to connect the valve slowly, in the case of the prior art shown in FIG. 5, the normally open type solenoid valve A117 is set to the DUT.
Y control is performed, but depending on the size of the oil passage diameter of the solenoid valve A117, the solenoid valve A117
Of the stroke of the piston 106 and the duty cycle P2 and
Since the Y ratio R2 was determined, it was impossible to increase the number of DUTY times and smoothly connect.

Therefore, in the hydraulic actuator having the above-described structure, two solenoid valves A31, which are provided in parallel between the passage E27 which connects the oil chamber B7 and the drain port 24,
Of B32, one of the solenoid valves B32 has a smaller oil passage diameter, and the one solenoid valve B32 having a smaller oil passage diameter performs DUTY control.
The DUTY cycle P1 is shorter than the DUTY cycle P2 of the prior art, and the DUTY ratio R1 is the DUT ratio of the prior art.
It becomes smaller than the Y ratio R2 (see FIGS. 4A and 4C and FIGS. 9A and 9C). As a result, the number of DUTY times increases and the flow rate decreases compared to the prior art, so fine control is possible, the clutch 51 can be smoothly engaged, and the connection of the clutch 51 at the time of starting can be performed. The ring improves.

In the above embodiment, the hydraulic pressure is used as an example of the fluid pressure. However, the fluid pressure is not limited to the hydraulic pressure, and other fluid pressures such as air pressure can be similarly applied.

[0047]

According to the present invention having the above-described structure and operation, since the fluid chamber is directly connected to the drain passage of the other chamber of the chambers formed by the movable member. The fluid pressure in the chamber is discharged quickly, and the response at the rising portion of the movable member up to the full stroke position is improved, and a plurality of communication passages that connect one chamber and the dray port are arranged in parallel. Since the control valves with different flow passage diameters are provided, the flow passage diameter will be expanded, the discharge of fluid pressure from one chamber to the drain port can be accelerated, and the return portion from the full stroke position to the original position can be moved. The response of the member is improved. In this way, the response of both the rising portion and the returning portion is improved, so that the responsiveness is improved.

Further, since a plurality of control valves having different flow passage diameters are provided in parallel between the communication flow passages, if the control valve having a small flow passage diameter is used for DUTY control, the DUTY cycle becomes short,
Further, since the DUTY ratio also decreases, the number of DUTY increases and the flow rate decreases, so that fine control is possible and smooth control is possible.

[Brief description of drawings]

FIG. 1 is a sectional view of a hydraulic actuator as a fluid pressure actuator according to an embodiment of the present invention.

FIG. 2 is a fluid circuit diagram of a hydraulic actuator as a fluid pressure actuator according to an embodiment of the present invention.

FIG. 3 shows the operating characteristics of the hydraulic actuators of FIGS. 1 and 2 during a gear shift. FIG. 3 (a) is a solenoid valve control timing diagram, and FIG. 3 (b) is a piston stroke diagram. is there.

FIG. 4 shows the operating characteristics of the hydraulic actuator of FIGS. 1 and 2 at the time of starting. FIG. 4 (a) is a solenoid valve control timing diagram, and FIG. 4 (b) is a piston stroke diagram. The same figure (c) is an enlarged view of the DUTY control section of the same figure (a).

FIG. 5 is a sectional view of a hydraulic actuator as a conventional fluid pressure actuator.

FIG. 6 is a fluid circuit diagram of a hydraulic actuator as a conventional fluid pressure actuator.

FIG. 7 is a system schematic diagram.

8 is a diagram showing the operating characteristics of the hydraulic actuator of FIGS. 5 and 6 during a gear shift, in which FIG. 8 (a) is a solenoid valve control timing diagram, and FIG. 8 (b) is a piston stroke diagram. is there.

9 is a diagram showing the operating characteristics of the hydraulic actuator of FIGS. 5 and 6 at the time of starting; FIG. 9 (a) is a solenoid valve control timing diagram, and FIG. 9 (b) is a piston stroke diagram. The same figure (c) is an enlarged view of the DUTY control section of the same figure (a).

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Hydraulic actuator (fluid pressure actuator) 2 Hydraulic cylinder part 3 Control part 4 Fluid chamber 5 Piston (movable member) 5A Projection part 6 Oil chamber A 7 Oil chamber B 8 Body (actuator main body) 8A Side wall 81 Large diameter part 9 Rod 10 Sleeve 10A Hole 11 Stroke sensor 12 Bearing A 13 Packing C 14 Packing A 15 Packing B 16 Bearing B 17 Through hole 18 Small diameter part 19 Nut 23 Supply port 24 Drain port 25 Flow path C (supply flow path) 26 Flow path D (Discharge) Flow path) 27 Flow path E (communication flow path) 28 Flow path A 29 Flow path B 30 Solenoid valve C 31 Solenoid valve A (control valve) 32 Solenoid valve B (control valve) 33 Introduction flow path 34 Tank 35 Electric pump 36 Check valve 37 Relief valve 38 Accumulator 50 System 51 Clutch 52 Clutch spring 53 Oscillator 54 Follower 60 Steel ball

Claims (1)

[Claims] 1. A hollow actuator body has a movable member that reciprocates in a fluid chamber formed inside, and controls the fluid pressure of each chamber defined by the movable member to operate the movable member. A supply port for supplying fluid pressure from a pressure source to one of the compartments formed through the supply passage and the other chamber to discharge fluid pressure through the discharge passage. In a fluid pressure actuator having a drain port, a communication channel that communicates one chamber and the other chamber, and a control valve that controls opening and closing of the communication channel, wherein the other chamber and the drain port are A fluid pressure actuator characterized in that a plurality of control valves having different flow passage diameters are directly connected to an exhaust flow passage and are provided in parallel in the communication flow passage.