JPH0483904A - fluid control device - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a fluid control device that changes the operating speed of an actuator using meter-in/out control and differential control.

(Prior Art) Generally, a valve body has a pump port, a tank port, and first and second load ports, and the first and second load ports are connected to one side of the pump port and the tank port by actuation of a proportional solenoid. When changing the operating speed of an actuator using a normal proportional switching valve equipped with a spool that selectively switches between In addition, the degree of aperture in this meter-in/out control, that is, the adjustment of the operating speed of the actuator, is determined by the processing of the spool, and in order to adjust the speed in response to the movement of the actuator, it is necessary to
It was necessary to make various changes to the structure of the spool, that is, the opening degree and opening timing. Furthermore, in order to adjust the actuator to a higher speed, it has also been proposed to provide a differential control circuit in the control circuit of the actuator. That is, it is known that pressure fluid from the pump port is supplied to both the front and rear chambers of the piston in the cylinder of the actuator to increase the flow rate and adjust the piston to high speed. In order to configure the dynamic control circuit, two of the proportional switching valves described above are required, resulting in a problem that the overall structure becomes extremely complicated.

Therefore, conventional fluid control devices have been developed that use a single proportional switching valve and a sequence valve to enable deceleration by meter-out control of the actuator, high-speed control without using a throttle, and high-speed control using a differential control circuit. However, the special public official
This is proposed in Japanese Patent No. 402. The device described in this publication uses a sequence valve (V) as shown in Fig. 9, and a proportional switching valve with a spool connected to the first and second proportional solenoid as shown in the symbol diagram of Fig. 9. (S
The first to fifth positions (
It is possible to switch between S1) and S5, and the following speed change operations can be performed. That is, when the first and second proportional solenoids (SOL1) (SOL2) are not energized, they are switched to the first position (S1), that is, the neutral position, the pump port (P) is closed, and the cylinder (C ) in the rod side chamber (R) of the piston (PS)
The first and second load ports (A) and (B) connected to the head side chamber (H) are respectively opened to the tank port (T) via a throttle, and the piston (PS) is brought into a neutral state. Retained. From the above state, the second proportional solenoid (SOL2) is energized, and when the current value is small, the pump port (P) is located at the fourth switching position (S4) and the pump port (P) is connected to the first load port. (A), and the second load port (B) is narrowed and opened to the tank port (T), and the piston (PS
) is gradually decelerated and retreated in the direction of contraction using meter-out control. Furthermore, when the current value applied to the second proportional solenoid (SOL2) is increased, the degree of throttling of the second load port (B) to the tank port (T) increases, and at the maximum current value, the fifth position (S5 ), the pump port (P) is connected to the first load port (A), and the second load port (B) is opened to the tank port (T) without being throttled. Therefore, the piston (PS) is retracted at high speed without meter-out control. Furthermore, the first proportional solenoid (SOL1
) is energized and when the current value is small, it is located at the second position (S2), the pump port (P) is connected to the second load port (B), and the first load port ( A) is opened to the tank port (T) side while being throttled, and the piston (PS) is gradually decelerated and advanced in the extension direction under meter-out control. Further, when the value of the current applied to the second proportional solenoid (SOL2) is increased, the second proportional solenoid (SOL2) is located at the third position (S3), the first load port (A) is closed, and the second load port (B) and the opening degree of the pump port (P) increases. At this time, as the first load port (A) is closed, the fluid pressure in the rod side chamber of the cylinder (C), that is, on the first load port (A) side increases. Rod side chamber (R) of cylinder (C)
control line (CL) formed between the
The interposed sequence valve (V) operates, and the return fluid from the rod side chamber (R) passes through the sequence valve (V) and joins the fluid in the pressure line, and the second load port (B) A differential control circuit is formed which supplies the air to the head side chamber (H) of the cylinder (C), and the piston (PS) is controlled at high speed in the direction of extension by this differential control circuit.

(Problem to be Solved by the Invention) By the way, the actuator (AC
), the operation of the piston (PS) requires various operating speeds depending on its use.
Even if the above proportional switching valve is used, the piston (P
The operation of S) cannot meet that demand. That is, by switching the spool to the first to fifth positions (S1) to (S5), the piston (PS) can be decelerated by meter-out control, high-speed control can be performed without forming a throttle, or differential Although the control circuit is designed to perform high-speed control, it is not possible to perform deceleration control by selecting between meter-in control and meter-out control, and when the piston (PS) moves in the extension direction, deceleration control by meter-out control cannot be performed. It is only possible to perform high-speed control using a differential control circuit, but it is not possible to perform high-speed control without using a differential control circuit, and it is not possible to meet various operating speed requirements.

Moreover, the differential control circuit has a complicated structure because it uses a sequence valve (V), and furthermore, the differential control circuit uses the pump port (P), the tank port (T), and the first and second load ports. The arrangement configurations (A) and (B) are not defined by the ISO standard, and therefore have the problem of poor versatility.

The present invention was made in view of the above-mentioned problems, and its purpose is to
While the load port layout can be configured as specified by the ISO standard, meter-in and meter-out control can be selected as desired, and the degree of aperture can be adjusted, as well as high-speed control using a differential control circuit. The object of the present invention is to provide a fluid control device that can be used for various purposes.

(Means for Solving the Problem) In order to achieve the above object, a first invention provides a fluid control device that changes the speed of the operation of an actuator (AC).
First and second proportional solenoids (SOL1) (SoL2) that operate proportionally according to the current value, and a first load port (A) connected to the pump port (P), tank port (T), and the actuator (AC). and the second load port (B)
a valve body (1) comprising: a valve body (1);
SOL1), the first spool (2) switches the first load port (A) to one of the pump port (P) and the tank port (T), and the second proportional solenoid (SOL2). The second load port (B
) to either the pump port (P) or the tank port (T).

The first and second spools (2) and (3) are connected to the first load port (A) and the second load port (B) when the first and second proportional solenoids (SOL1) (SOL2) are not energized. pump port (P) and tank port (T)
It is desirable to provide a port blocking means for blocking ports.

Further, a second invention provides a fluid control device for changing the operation of the actuator (AC), which includes an electromagnetic proportional pilot valve (PV) and a main valve ( The pilot valve (PV) consists of first and second proportional solenoids (SOL1) (SOL2) that operate proportionally according to the current value, a pressure port (O), a tank port (T), and a 1 and a second control port (X) (Y).
) and the first proportional solenoid (SOL1),
a first pilot spool (5) for switching the first control port (X) to one of the pressure port (O) and the tank port (T); and the second proportional solenoid (SOL2).
The second control port (Y) is connected to the pressure port.
) (O) and a tank port (T), and the main valve (MV) has a first control chamber that communicates with the first control port (X). (7) and a control chamber (8) communicating with the second control port (Y), and a first control chamber (8) communicating with the pump port (P), the tank port (T), and the actuator (AC).
and the second load port (A) (B) and the elastic body (9S)
is actuated by a change in control pressure in the first control chamber (7), and connects the first load port (A) to the pump port (
A first main valve spool (9) that switches between the first main valve spool (9) and the first main valve spool (9), which switches between the first main valve spool (9) and the second control chamber (8), is energized by an elastic body (103) and operates according to the control pressure change in the second control chamber (8). It is characterized by comprising a second main valve spool (10) that switches the second load port (B) to one of the pump port (P) and the tank port (T).

The first and second pilot spools (5) ("6") of the electromagnetic proportional pilot valve (PV) are configured to operate when the first and second proportional solenoids (SOL1) (SOL2) are not energized. The first and second main valve shafts (9) of the main valve (MV) are provided with elastic bodies (5S) (BS) that communicate the control ports (X) (Y) with the tank port (T).
(LO) is the first and second control port (X)
(Y) communicates with the tank port (T), the first
and the second load port (A) (B) to the pump port (P)
It is desirable to provide port blocking means for blocking the tank port (T) and the tank port (T).

(Function) In the fluid control device of the first invention, the fluid control device of the first invention. By cutting off the power to the second proportional solenoids (SoL1) (SOL2), the first and second spools (2) and (3) are respectively located at neutral positions, and the pump port (P) is closed; and the first chamber connected to the front and rear piston chambers of the cylinder in the actuator CAC). Second
The load ports (A) and (B) are respectively connected to the tank port (T
), and the actuator (AC) is held in a neutral state.

Then, from the above neutral state, the second proportional solenoid (SOL2) is de-energized, that is, the second load port (B) is opened to the tank port (T) side, and the By energizing the first proportional solenoid (SOL1) and moving the first spool (2) to connect the first load port (A) to the pump port (P), the actuator (AC) is activated. The piston is moved in the advancing direction, and at this time, the value of the current applied to the first proportional solenoid (SOL1) is adjusted so that the pump port (P) is moved by the movement of the first spool (2).
By controlling the degree of constriction between the first load port (A) and the first load port (A), meter-in control becomes possible, and high-speed control without forming a constriction and deceleration by meter-in control become possible. In addition, when connecting the pump port (P) to the first load port (A) without increasing the current value applied to the first proportional solenoid (SOL1) and reducing the current value applied to the first proportional solenoid (SOL1), the second proportional solenoid (SOL2) By energizing and moving the second spool (3), the space between the second load port (B) and the tank port (T) is narrowed, and the actuator (AC) can be decelerated by meter-out control. be.

Moreover, contrary to the above case, the first proportional solenoid (
SOL1) is de-energized, that is, the first load port (A) is opened to the tank port (T) side, the second proportional solenoid (SOL2) is energized, and the second spool (3) By moving the second load port (B
) to the pump port (P) side, the piston of the actuator (AC) is moved in the backward direction, and at this time, the second proportional solenoid (S
Meter-in control is performed by adjusting the current value of the OL1) 611 and controlling the degree of restriction between the pump port (P) and the second load port (B) due to the movement of the second spool (3). This enables high-speed control without forming a throttle and deceleration by meter-in control.

In this case as well, the second proportional solenoid (SO
When connecting the pump port (P) to the second load port (B) without throttling by increasing the current value applied to the current applied to the first spool (L2), the first proportional solenoid (SOL1) is energized and the first spool ( 2) by moving the first
The space between the load port (A) and the tank port (T) is narrowed, and the actuator (AC) can be decelerated by meter-out control.

Furthermore, the first and second proportional solenoids (S).

1) (SOL2) are both energized, and the first. The second spools (2) and (3) are moved respectively, and the second spools (2) and (3) are moved. Second
Both load ports (A) and (B) are connected to the pump port (P).
differential control of the pistons is achieved by connecting the proportional solenoids (SOL
1) (SOL2) is energized and each of the spools (2) (3) is energized.
), a differential control circuit is formed by connecting each load port (A) and (B) to the pump port (P) by moving the actuator (AC
The working fluid discharged from the rod side chamber in ) is supplied to the head side chamber, allowing the piston to advance at high speed.

Further, in the above first invention, when the first and second proportional solenoids (SOL1) (SOL2) are not energized, the first load port 1- (A) and the second load port (B) from the pump port (P) and the tank port (T), when the respective load ports (A) and (B) are blocked during a power outage, etc. The pump port (
It is possible to prevent the actuator (AC) from communicating with the tank port (T) and the actuator (AC), thereby preventing the actuator (AC) from moving without permission, thus making fail-safe possible.

Furthermore, in the fluid control device of the second invention, the first . Second proportional solenoid (S
When cutting off the power supply to OL1) (SOL2), the first and second pilot spools (5) and (6) are respectively located at neutral positions, the pressure port (O) is closed, and the main No. 1 on the valve (MV) side. 2nd control room (7
) (8). 2nd control port (X) (
Y) are each opened to the tank port (T), so
No control is performed on the main valve (MV) side, and the first . The second load ports (A) and (B) are respectively opened to the tank port (T), and the actuator (AC) is maintained in a neutral state.

Then, from the above neutral state, each proportional solenoid (
SOL1) (SOL2) (7) The -blade side of the first and second pilot spools (5) and (6) was stopped by cutting off the current to the -blade side and energizing the other side. While the other side is moved, each control port is
(X) The -blade side of (Y) is connected to the pressure port (O), the other side is connected to the tank port (T), and the pressure fluid from the pressure port (O) is connected to the main valve (MV). The first valve is supplied to the minus blade side of the control chambers (7) and (8), and the first valve provided in the main valve (MV) is supplied accordingly. 2nd main valve spool (9)
The -blade side of (10) is moved to selectively communicate the first and second load ports (A) and (B) of the main valve (MV) with the pump port (P) and tank port (T). The piston of the actuator (AC) is moved in the advancing or retracting direction, and at this time, the value of the current supplied to each of the proportional solenoids (SOL1) (SOL2) is adjusted, and the first... By controlling the fluid flow rate at the first and second control ports (X) and (Y) by moving the second pilot spools (5) and (6), each of the main valve spools (9) and (10) Meter-in control or meter-out control is performed, and high-speed control by not performing meter-in or meter-out control and deceleration control by meter-in or meter-out control are possible.

Further, the first and second proportional solenoids (S).

L1) (SOL2) are both energized to move the first and second pilot spools (5) and (6), respectively. By connecting both the second control ports (X) and (Y) to the pressure port (o) side, the main valve (MV)
Differential control of the actuator (AC) is performed via the proportional solenoid (SOL1).
(S.

L2) is energized and each of the pilot spools (5) (
A differential control circuit is formed by connecting each of the control ports (X) and (Y) to the pressure port (O) by the movement of 6), and the actuator (AC) is controlled by this differential control circuit. This allows for high-speed control.

Furthermore, in the above-mentioned second invention, the first . 2nd pilot spool (5) (
6), the above-mentioned No. 1. 2nd proportional solenoid (SOL1) (
When SOL2) is not energized, the first. 2nd control port (
Elastic body (X) that connects (Y) to the tank port (T)
5S) (6S), and the first valve of the main valve (MV). Second
The main valve spools (9) and (10) are connected to the first. When the second control port (X) (Y) communicates with the tank port (T), the first control port (X) (Y) communicates with the tank port (T). When a port blocking means for blocking the second load ports (A) and (B) from the pump port (P) and the tank port (T) is provided, the first load port (A) and (B) may be blocked from the pump port (P) and the tank port (T) in the event of a power outage or the like. It is possible to prevent the second load ports (A) and (B) from communicating with the pump port (P) and the tank port (T), and it is possible to prevent the actuator (AC) from moving without permission, making it fail-safe. becomes possible.

(Example) The fluid control device shown in FIGS. 1 and 2 has a valve body (1
), the pump port (P) connected to the pump (IA)
and the first one located on both the left and right sides of the pump port (P).
and a second load port (A) (B), located on the outer side of each load port (A) (B), and a tank (IB).
A pair of tank ports (T) (T) opened to the IS
In addition to forming the arrangement according to the O standard, each of the load ports (A) and (B) is connected to the head side chamber (H) and rod side chamber (R) of the piston (PS) in the cylinder (C) that constitutes the actuator (AC). On the other hand, on both sides of the valve body (1) in the lateral direction, there are first and first proportional solenoids (SOL1) (
SOL2) is installed.

Further, a first spool is provided at both left and right sides inside the valve body (1) for selectively switching the first load port (A) to one side of the pump port (P) and the tank port (T). (2) and a second spool (3) for selectively switching the second load bow 1-(B) to one side of the pump port (P) and the tank port (T) are respectively freely movably arranged. Set up The first spool (2) is provided with a spring (2S) that opposes the suction force of the first proportional solenoid (SOL1), and the spring force of the spring (2S) and the first proportional solenoid (SOL1) are The first spool (
2) by proportionally controlling the movement of the first spool (2).
A restriction is formed between the pump port (P) and the first load port (A) by movement control to enable meter-in control, and the tank port (T) and the first load port (A)
A diaphragm is formed between the two to enable out-of-field control.

Further, the second proportional solenoid (SOL2) is also provided on the second spool (3) side, similar to the first spool (2).
) is provided with a spring (3S) that opposes the suction force of the spring (3S).
S) and the second proportional solenoid (SOL2)
), the movement of the second spool (3) is proportionally controlled by the balance with the suction force based on the change in the current value, and the movement control of the second spool (3) controls the movement of the pump port (P).
A restriction is formed between the tank port (T) and the second load port (B) for meter-in control, and a restriction is formed between the tank port (T) and the second load port (B) for meter-out control. It is.

Further, in the center of the spools (2) and (3), there are spring chambers (20) and (30) in which the springs (2S) and (3S) are housed.
The communication hole (21) (31) that communicates with the pump port (P)
), and the pressure in the spring chambers (20, 30) is controlled by the pump port (P), which the spools (2, 3) face.
), and the pressure is balanced.

FIG. 2 shows a symbol diagram of the fluid control device, in which the first spool (2) installed in the valve body (1) is 3
The position of the second spool (3) is controlled to three first to third positions (S1) to (S3), and the second spool (3) is controlled to three fourth to sixth positions (S4) to (S6). Therefore, when the proportional solenoid (SOL1) is de-energized, the position is controlled to the first position (S1), the pump port (P) is blocked, and the first load port (SOL1) is controlled to the first position (S1).
A) communicates with the tank port (T), and when the first proportional solenoid (SOL1) is energized to move the spool (2) and control the position to the second position (S2), Both the pump port (P) and the tank port (T) are closed, and the third position (S
3), the tank port (T
) is blocked, and the first load port (A) communicates with the pump port (P). Furthermore, when the second proportional solenoid (SOL2) is de-energized, the position is controlled to the fourth position (S4), the pump port (P) is blocked, and the second load port (B) is The second proportional solenoid (SOL2) is energized to connect the spool (3) to the tank port (T).
) and when the position is controlled to the fifth position (S5), the pump port (P) and the tank port (
When both the tank port (T) is closed and the position is controlled to the sixth position (S3), the tank port (T) is blocked and the second load port (B) is closed to the pump port (
It communicates with P).

Next, a control mode of the actuator (AC) by the fluid control device configured as above will be explained.

First, the first valve provided in the valve body (1). When the second proportional solenoid (SOL1) (SoL2) is de-energized, the spring force of each of the springs (2S) (3S) causes the first
and the second spools (2) and (3) are respectively switched to the first position (S1) and the fourth position (S4) in FIG.
The pump port (P) is closed, and the first and second load ports (A) and (B) are respectively opened to the tank port (T), and the actuator (AC)
is held in a neutral state.

Then, the second proportional solenoid (SOL2) is de-energized and the second spool (3) is moved to the fourth position (
When the first proportional solenoid (SOL1) is energized to control the position of the first spool (2) in the direction of the second position (S2) while the pump port (P ) and the tank port (T) are both closed through the second position (S2), and then the position is controlled to the third position 1f (S3), and the second load port (B) is moved to the tank port (T) side. In the open state, the pump port
(P) communicates with the first load port (A), and the piston (PS) of the actuator (AC) is moved in the advancing direction, and at this time, the first proportional solenoid (S).

L1) is adjusted to supply current to the first spool (L1).
By moving 2) to form a restriction between the pump port (P) and the first load port (A), meter-in control becomes possible, and the piston (PS) is advanced without forming a restriction. High-speed control and meter-in control to advance while decelerating can be freely performed, and the degree of aperture in this meter-in control can also be freely adjusted. Moreover, the pump port (P) can be connected to the first load port (
A), the second proportional solenoid (SOL
2) to move the second spool (3), the second load port (B) and the tank port (
T), and the actuator (AC) can be decelerated by meter-out control.

Moreover, contrary to the above case, the first proportional solenoid (
The power to the first spool (SOL1) is cut off, and the first spool (2
) remains in the first position (S1), the second proportional solenoid (SOL2) is energized, and the second proportional solenoid (SOL2) is energized.
When controlling the position of the spool (3) in the direction of the fifth position (S5), the pump port (P) and the tank port (T
) is controlled to the sixth position (S6) via the fifth position (S5) where both are closed, and in this case, the first load port (A) is placed on the tank port (T) side. In the open state, the pump port (P) communicates with the second load port (B), and the piston (PS) of the actuator (AC) is moved in the backward direction. When the second proportional solenoid (SO
L2) is adjusted to supply current to the second spool (L2).
By forming a restriction between the pump port (P) and the second load port (B) by the movement of 3), meter-in control becomes possible, and the piston (PS) is retreated at high speed without forming a restriction. High-speed control and deceleration control that causes the vehicle to move backward while decelerating through meter-in control can be freely performed, and the degree of aperture in this meter-in control can also be freely adjusted. In this case as well, the pump port (P) is connected to the second proportional solenoid (SOL2) without increasing the current value applied to the second proportional solenoid (SOL2).
When connecting to the load port (B), the first proportional solenoid (SOL1) is energized to move the first spool (2), thereby connecting the first load port (A) and the tank port (T). The time is narrowed down, and the actuator (AC) can be decelerated by meter-out control.

Furthermore, the first and second proportional solenoids (S).

L1) (SOL1) are commonly energized, and the 1st and 2nd spools (2) and (3) are connected to the 3rd and 6th positions (SOL1), respectively.
83) When the position is moved to (Sθ), the first.
The second load ports (A) and (B) are both connected to the pump port (
P) side to perform differential control of the piston (PS), that is, the first and second proportional solenoids (SOL1) (SOL1) are energized to control each of the spools (2). (3) A differential control circuit is formed by connecting the first and second load ports (A) and (B) to the pump port (P) by moving the actuator (AC). Piston (PS
) The fluid discharged from the rod side chamber (R) is supplied to the head side chamber (H), allowing the piston (PS) to advance at high speed.

Further, in the above fluid control device, the valve body (1)
The first and second proportional solenoids (SOL1) (SO
L2) is de-energized, the first. 2nd load port (A)
(B), the pump port (P) and the tank port (
It is preferable to provide port blocking means for blocking T). Specifically, as shown in FIG.
Lands (2A) and (3A) are provided at intermediate positions between the load ports (A) and (B) and the tank port (T), and the first. 2nd load port (A) (B) and pump port (P)
Lands (2B) and (3B) are provided at intermediate positions between the
When the power to L1) (SOL2) is cut off, the lands (2A) (3A) are connected to the load ports (A) (B).
) and the tank port (T), and each of the lands (2B) and (3B) is located between each of the load ports (A) and (B) and the pump port (P), that is, As shown in FIG. 4, each load port (A) (
B) is configured to block the pump port (P) and tank port (T), and by configuring it in this manner, a fail-safe that prevents arbitrary movement of the actuator (AC) is possible. It will become.

In the above embodiment, the pump port (P) is provided in the center of the valve body (1), and the tank ports (T) are provided on both outer sides of the valve body (1). As shown in FIG. 5, the configuration is such that the pump port (P) is located in the center of the valve body (1), and the tank port (T) is located on both outer sides of the valve body (1). You can do it like this.

Further, in the above fluid control device, each of the proportional solenoids (SOL1) (SOL2) has a corresponding IIW.
I! A position signal detected by each detector is transmitted to each proportional solenoid (S).

Feed back to the input side of L1) (SOL2),
These feedback signals and each proportional solenoid (S
With the position setting signal input to OL1) (SOL2),
Preferably, the proportional solenoids (SOL1) (SOL2) accurately control the movement of the spools (2) and (3).

Furthermore, the present invention provides an electromagnetic proportional pilot valve (PV) and a pilot valve (P) as shown in FIGS. 6 and 7.
The main valve (M) is operated based on the control pressure controlled by the main valve (M
V) It is also possible to apply it to a fluid control device equipped with.

That is, the electromagnetic proportional pilot valve (PV) has a pressure capo connected to its pilot valve body (4) to a pressure source (IC) of pilot control pressure communicating with the pump CIA).
(O), first and second control ports (X) (Y) located on both the left and right sides of the pressure port (O), and the first and second control ports (X) (Y) located on the outer side of each control port (X) (Y). , tank (ID
) and a pair of tank ports (T) (T) that are open to the valve body (4), and first and first proportional ports that are respectively operated proportionally in accordance with the current value on both sides of the valve body (4) in the lateral direction. Solenoids (SOL1) (SoL2) are provided.

Further, a first pilot spool is provided at both left and right sides inside the valve body (4) for selectively switching the first control port (X) to one of the pressure port (O) and the tank port (T). (5) and the second control port (Y
) is selectively switched to the blade side between the pressure capo (O) and the tank port (T).
6) and are arranged freely so as to be movable. Each of the pilot spools (5) (f3) has the first
．． When the second proportional solenoids (SOL1) (SOL2) are de-energized, an elastic body (5S
) (68), and each elastic body (58) (68) is provided.
S) and each proportional solenoid (SOL1
) (SoL2), the first and second pilot spools (5)
(e) Proportional control of the movement of each pilot spool (5) (θ) enables meter-in/out control of the first and second control ports (X) and (Y). . Note that this electromagnetic proportional pilot valve (PV) is basically the same in configuration as shown in FIG.

Furthermore, the main valve (MV) controlled by the pilot valve (PV) has a tank port (T) that is open to the tank (IB) side, and a tank port (T) that is located on the left and right sides of this tank port (T). forming first and second load ports (A) and (B), and a pump port (P) located on the outer side of each of the load ports (A) and (B) and connected to the pump (IA). At the same time, each of the load ports (A) and (B) is connected to the head side chamber (H) and the rond side chamber (R) of the piston (PS) in the cylinder (C). Further, a first control chamber (7) communicated with the first control port (X) and a first control chamber (7) communicated with the second control port (Y) are located at an outer position between the left and right inside the main valve (MV). A control chamber (8) is formed, and first and second main valves are provided on both inner sides of the main valve (MV) and whose movement is controlled by the control pressure applied to each of the control chambers (7) and (8). The valve spools (9) and (10) are freely movable. And each of the main valve spools (9) (
10) includes elastic bodies (9S) (10S) made of springs, etc.
), and each of these elastic bodies (9S) (108)
and the first and second control chambers (7) (8).
The movement of the first and second main valve spools (9) (10) is controlled by the balance with the control pressure applied to the main valve spools (9) (10), and by controlling the movement of each main valve spool (9) (10),
This enables meter-in/out control and differential control on the first and second control ports (X) and (Y) sides. Next, a control mode of the actuator (AC) by the fluid control device configured as above will be explained.

First, the first and second electromagnetic proportional pilot valves (PV)
When cutting off the electricity to the proportional solenoids (SOL1) (SOL2), the first and second pilot spools (
5) (6) are each located at a neutral position, the pressure port (O) is closed, and connected to the first and second control chambers (7) and (8) on the main valve (MV) side. The first and second control ports (X) and (Y) are the tank ports (
Since the main valve (MV) side is not controlled, the first and second load ports (A) and (B) of the main valve (MV) are opened to the tank port (T). The actuator (AC) is held in a neutral state.

Then, from the above neutral state, the second pilot spool (6) is stopped by cutting off the energization to the second proportional solenoid (SOL2) and energizing the first proportional solenoid (SOL1). In this state, the first pilot spool (5) is moved, that is, the second control port (Y) is connected to the tank port (T), and the first control port (X) is connected to the pressure port (O ), the pressure fluid from this pressure port (O) is supplied to the first MwJ chamber (7) provided in the main valve (MV), and accordingly, the first MwJ chamber (7) provided in the main valve (MV) is connected to Main valve spool (
9) is moved and the first load port (
A) is communicated with the pump port (P), the second load port (B) is communicated with the tank port (T), and the piston (PS) of the actuator (AC) is moved in the advancing direction. When the first proportional solenoid (
By adjusting the value of current applied to SOL1), the pressure capo) (O
) and the first control port (X) to control the fluid flow rate supplied to the first control chamber (7), thereby controlling the pump port in the first main valve spool (9). The throttle between (P) and the first load port (A) is adjusted, and deceleration control by meter-in control and high-speed control for high-speed advancement without forming a throttle are performed.

Further, the current value applied to the first proportional solenoid (SOL1) is increased to eliminate the restriction at the first control port (X), and the pump port (9) is controlled by the first main valve spool (9). When connecting the 11th Rt7 port (A) to the pump port (P) by eliminating the restriction between the 1st load port (A) and the 1st load port (A),
OL2) is energized and the second pyro-/ ) spool (
6), the control fluid is introduced from the second control port (Y) into the second control chamber (8) to operate the second main valve spool (10), and the second load port (B) is moved. By forming a throttle between the tank port (T) and the tank port (T), meter-out control becomes possible, and this meter-out control allows the actuator (AC) to advance at a reduced speed.

Moreover, contrary to the above case, the first proportional solenoid (
By cutting off the energization to SOL1) and energizing the first proportional solenoid (SOL2), the second pilot spool (6) is moved while the first pilot spool (5) is stopped. That is, with the first control port (X) connected to the tank port (T), the second control port (Y) is connected to the pressure port (O), and from this pressure port (○) Pressure fluid is supplied to the second control chamber (8) provided in the main valve (MV), and accordingly, the second main valve spool (10) of the main valve (MV) is moved, and the pressure fluid in the main valve (MV) is moved. The second load port (B) of the MV) is communicated with the pump port (P) side, and the first load port (
A) is communicated with the tank port (T), and the piston (PS) of the actuator (AC) is moved in the backward direction. At this time, the second proportional solenoid (
The pressure port (O) by the movement of the second pilot spool (6) is adjusted by adjusting the current value applied to the SOL2).
The pump port ( P) and the second load port (B) are adjusted to enable deceleration and retreat through meter-in control. That is, back-passing and retracting of the piston (PS) without using this meter-in control and decelerating and retracting while decelerating under meter-in control are performed arbitrarily.

Also in this case, as in the previous example, the first proportional solenoid (SOL1) is also energized, and the first pilot spool (5
), the control fluid is introduced from the first control port (X) into the first control chamber (7) to operate the first main valve spool (9), and the first load port (A) By forming a restriction between the tank port (T) and the tank port (T), meter-out control becomes possible, and the actuator (AC) can be decelerated and retreated by this meter-out control.

Furthermore, the first and second proportional solenoids (SOL)
OL2) to move the first and second pilot spools (5) (f3), respectively.
Both the second control ports (X) and (Y) are connected to the pressure capo) (
By connecting the proportional solenoids (SOL1) (S.

L2) is energized and each of the pilot spools (5) (
8) by connecting each of the control ports (X) and (Y) to the pressure port (O), the first
and the second main valve spools (9) and (10) can move together to connect the first and second load ports (A) and (B) to the pump port (P), respectively,
This connection forms a differential control circuit.

Therefore, this differential control circuit controls the actuator (
The fluid discharged from the rod side chamber (R) in AC) is supplied to the head side chamber (H), making it possible to advance the actuator (AC) at high speed.

Further, in the above fluid control device, the first valve of the electromagnetic proportional pilot valve (PV). 2nd pilot spool (
5) In (8), as described above, when each of the proportional solenoids (SOL1) (SOL2) is not energized, the first and second control ports (X) (Y) are communicated with the tank port (T). An elastic body (5S) (O8) is provided, and the main valve (M
V) side 1. The second main valve spools (9) and (10) are connected to the first. The second control port (X) (Y) is the tank port (
T), when the first. Second load port (A
) (B) to pump port (P) and tank port (T)
It is preferable to provide a port blocking means for blocking the port. Specifically, as shown in FIG.
and the second main valve spools (9) and (10), when the power supply to each of the proportional solenoids (SoL1) (SOL2) is cut off due to a power outage, etc., the first. 2nd load port
Block lands (9A) (10A) are installed to cut off communication between (A) and (B) and the tank port (T), and power to each of the proportional solenoids (SOL1) (SOL2) is cut off in the event of a power outage, etc. When each load port (A) (B
) is blocked from the pump port (P) and the tank port (T), thereby making it possible to provide a fail-safe that prevents the actuator (AC) from moving without permission.

Furthermore, in the embodiments shown in FIGS. 6 to 8, the tank port (T) was provided in the center of the main valve (MV), and the pump ports (P) were provided on both sides. ,
Controllability is good because high pressure does not act on each of the main valve spools (9) and (10), but there is a pump port (P
), and tank ports (T) may be provided on both sides.

In this case, the pushing force of the elastic bodies (9S) (108) is adjusted so as to oppose the pushing force of the high pressure fluid acting on the main valve spools (9) (10).

Moreover, each of the main valve spools (
9) The position of (10) is detected by a differential transformer, and the position information is fed back to determine the position of each pilot spool (5) and (8) by the first and second proportional solenoids (SOL1) (SOL2). Preferably, control is provided.

(Effects of the Invention) As explained above, in the fluid control device of the first invention, the first fluid control device operates proportionally according to the current value. Second proportional solenoid (
A valve body (1) comprising a first load port (A) and a second load port (B) connected to a pump port (P), a tank port (T), and an actuator (AC). ), and the first proportional solenoid (SOL
1), a first spool (2) that switches the first load port (A) to one side of the pump port (P) and the tank port (T), and the second proportional solenoid (SOL2). ), the second load port (B) is connected to the pump port (P) and the tank port (T).
Since the actuator (A) is equipped with a second spool (3) that can be switched to one side of the actuator (A), the actuator (A
By combining the operations of the spools (2) and (3), the operating speed of C) can be controlled by deceleration control using meter-in or meter-out control, and at each load port (A) or (C) without performing meter-in or meter-out control. B) can be communicated with the pump port (P), and high-speed control can also be performed with a differential control circuit that simultaneously communicates the load ports (A) and (B) with the pump port (P). In addition, the degree of restriction in meter-in and meter-out control can be adjusted electrically, allowing the operation of the actuator (AC) to be selected at any speed, expanding the range of application, and furthermore, Since the configuration is compatible with ISO standards, it also has versatility.

Further, in the above fluid control g position, the first and second
When the first and second proportional solenoids (SOL1) (SOL2) are not energized, the first
When provided with a port blocking means for blocking the load port (A) and the second load port (B) from the pump port (P) and the tank port (T), each of the load ports (A) and (B) is It is possible to prevent the actuator (AC) from communicating with the pump port (P) or the tank port (T), and it is possible to reliably prevent the actuator (AC) from moving without permission.
This makes failsafe possible.

Furthermore, the fluid control device of the M2 invention includes an electromagnetic proportional pilot valve (PV) and a main valve (MV) that operates with a control pressure controlled by the pilot valve (PV), and the pilot valve (PV) is The first and second proportional solenoids (SOL1) (SOL2) operate proportionally according to the current value, the pressure port (O), the tank port (T), and the first. A pilot valve body (4) having a second control port (X) (Y), and interlocking with the first proportional solenoid (SOL 1),
a first pilot spool (5) for switching the first control port (X) to the -blade side between the pressure port (O) and the tank port (T); and a second proportional solenoid (SOL).
2), a second pilot spool (6) that switches the second control port (Y) to one of the pressure port (O) and the tank port (T) in conjunction with the main valve (MV ) side includes a first control chamber (7) communicating with the first control port 1-(X) and the second control port (Y).
a control chamber (8) communicating with the pump port (P), a tank port (T), and first and second load ports (A) and (B) connected to the actuator (AC); and an elastic body (9S). a first load port (A) that is energized by the pump and operated by a control pressure change in the first control chamber (7) to switch the first load port (A) to one of the pump port (P) and the tank port (T); energized by the main valve spool (9) and an elastic body (108) and operated by control pressure changes in the second control chamber (8);
Since the actuator (AC
) can be controlled arbitrarily as in the first invention, and the same effects as in the first invention can be expected.

Moreover, in the above fluid control device, the above-mentioned 1! The first and second pilot spools (5) and (6) of the magnetic proportional pilot valve (PV) are provided with the first. Second proportional solenoid (SO
L1) (SOL2) is not energized, the first. The main valve (MV) includes an elastic body (5S) Ce3S) that communicates the second control port (X) (Y) with the tank port (T) side.
The first and second main valve spools (9) and (10) of
゜When the second control port (X) (Y) communicates with the tank port (T), the first control port (X) (Y) communicates with the tank port (T). 2nd load port (A) (B)
When provided with port blocking means for blocking the pump port (P) and the tank port (T),
In the event of a power outage, etc., the first and second load ports (A) (B
) can be prevented from communicating with the pump port (P) and the tank port (T), and the actuator (AC) can be prevented from moving without permission, making fail-safe possible.

[Brief explanation of the drawing]

Fig. 1 is a partially cutaway front view of the fluid control device according to the first invention, Fig. 2 is a symbol diagram thereof, and Fig. 3 is a partially cutaway view of another embodiment in which the same fluid control device is provided with port blocking means. 4 is a symbol diagram thereof, FIG. 5 is a partially cutaway front view showing another embodiment, FIG. 6 is a partially cutaway front view of the fluid control device according to the second invention, and FIG. 7 is a partially cutaway front view of the fluid control device according to the second invention. Same symbol diagram, No. 8
The figure is a partially cutaway front view of another embodiment in which the same fluid control device is provided with port blocking means, and FIG. 9 is a symbol diagram showing a conventional example. (1)... Valve body (2)... 11th spool (3)... Second spool (4) -... Pilot valve body (5) @...・First pilot spool (6)...
...Second pilot spool (5S, 6S)...Elastic body (7)...First control room (8)...Second control room (9)-Φ...No. 1 Main valve spool (10), fist, 2nd main valve spool (9S, 10S), Q, elastic body (A), φ-0, 1st load port (B), 2nd load port (P)...Pump port (T)...Fist...Tank port (O)...Pressure port (X)...φ1st control port (Y)...Hisashi... 2nd control port (SOL1)...1st proportional solenoid (SOL2)...
...Second proportional solenoid (PV) ...Pilot valve (MV) ...Main valve (AC) ...Actuator Fig. 3 Fig. 4 C Fig. 5 Fig. 7 B A

Claims (1)

[Claims] 1) A fluid control device that changes the speed of the operation of an actuator (AC), which includes first and second proportional solenoids (SOL1) (SOL2) that operate proportionally according to the current value, and a pump port ( P), a tank port (T), and a first load port (A) and a second load port (B) connected to the actuator (AC); and the first proportional solenoid (SOL1). ), the first load port (A) is connected to the pump port (P) and the tank port (T
) and the second proportional solenoid (SOL2), the second load port (B) is switched between the pump port (P) and the tank port (T). A fluid control device characterized in that it comprises a second spool (3) that is switched to one side. 2) The first and second spools (2) and (3) close the first load port (A) and the second load port (B) when the first and second proportional solenoids (SOL1) (SOL2) are not energized. The fluid control device according to claim 1, further comprising port blocking means for blocking the pump port (P) and the tank port (T). 3) A fluid control device that changes the speed of the operation of an actuator (AC), which includes an electromagnetic proportional pilot valve (PV) and a main valve that operates with the control pressure controlled by the pilot valve (PV).
The pilot valve (PV) has first and second proportional solenoids (PV) that operate proportionally according to the current value.
SOL1) (SOL2), a pilot valve body (4) comprising a pressure port (O), a tank port (T), first and second control ports (X) (Y), and the first proportional solenoid ( SOL1), the first control port (X
) to one of the pressure port (O) and the tank port (T), and the second proportional solenoid (SOL2) to switch the second control port (Y) to one of the pressure port (O) and the tank port (T). Pressure port (O) and tank port (
Second pilot spool (6) switching to one side with T)
The main valve (MV) includes a first control chamber (7) communicating with the first control port (X) and a control chamber (8) communicating with the second control port (Y); first and second load ports (A) (B) connected to a pump port (P), a tank port (T), and the actuator (AC);
) and an elastic body (9S), the first control chamber (7
), the first main valve spool (9) switches the first load port (A) to one of the pump port (P) and the tank port (T), and an elastic body (10S).
), the second control chamber (8) is energized by the control pressure change in the second control chamber (8), and the second load port (B) is connected to the pump port (
1. A fluid control device comprising: a second main valve spool (10) that switches between a tank port (T) and a tank port (T). 4) The first and second pilot spools (5) and (6) in the electromagnetic proportional pilot valve (PV) are connected to the first and second control ports when the first and second proportional solenoids (SOL1) (SOL2) are not energized. (X) (Y) to the tank port (T
) is provided with elastic bodies (5A) (6S) that communicate with the main valve (
MV) first and second main valve spools (9) (10
), when the first and second control ports (X) and (Y) communicate with the tank port (T), the first and second load ports (A) and (B) are connected to the pump port (P) and the tank port. 4. The fluid control device according to claim 3, further comprising port blocking means for blocking (T).