JPH0433053B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION <Industrial Application Field> The present invention relates to a pressure control circuit which is particularly effective when used, for example, to control the pressure of an exit cylinder of an injection molding machine.

<Prior Art> Conventionally, there is a pressure control circuit as shown in FIG. (Hydraulic and Pneumatic Design, Volume 17, No. 10,
See page 71, Figure 4. ) This pressure control circuit includes a main line 3 connecting the pressure source 1 and the injection cylinder 2.
While connecting the electromagnetic relief valve 5 to the branch path,
The detected pressure signal Id from the pressure detector 7 that detects the pressure in the main line 3 and the target pressure signal Io are inputted to the operational amplifier 6, and based on the comparison value between the detected pressure signal Id and the target pressure signal Io. In other words, the pressure in the main line 3 is controlled by pressure feedback control via the main line 3. Furthermore, this pressure control circuit is connected to the main line 3 of a safety valve 8 for regulating the maximum pressure.

<Problems to be Solved by the Invention> By the way, in the above-mentioned conventional pressure control circuit, during the transition from the flow rate control state (means not shown) to the pressure control state, a large The problem is that pressure overshoots that last for a long time occur.

The reason why such pressure overshoot occurs is as follows. In FIG. 3, Po is the target pressure to be controlled by the electromagnetic relief valve 5, Pm is the set pressure of the safety valve 8, and E is the time when the injection cylinder 2 reaches the stroke end and shifts from the flow rate control state to the pressure control state. . In the flow rate control state before the above time E, the pressure in the main line 3 detected by the pressure detector 7 is extremely lower than the target pressure Po, so the operational amplifier 6 is outputting the maximum output, and the electromagnetic relief valve 5 is completely closed. It is in a closed state. In this state, the control elements of the feedback system, such as the operational amplifier 6 and the electromagnetic relief valve 5, are in a saturated state with respect to the signal magnitude. Next, after time E, when the fluid pressure in the main line 3 exceeds the target pressure Po, the operational amplifier 6 is reversed from the saturation state with a certain time constant unique to this feedback system. Due to the delay in the output of the electromagnetic relief valve 5 by this time constant, a large pressure overshoot exceeding the target pressure Po continues for a long time, as shown by curve A in FIG. This pressure overshoot is larger than the pressure overshoot determined by the inherent characteristics of the electromagnetic relief valve 5 itself and lasts for a long time.

In order to solve this problem, it is conceivable to shorten the time constant of the feedback system including the operational amplifier 6 to reduce the overshoot and shorten the time, but this causes the problem of oscillation.

In addition, in order to eliminate the drawback of pressure overshoot caused by pressure feedback control, it is possible to control the electromagnetic relief valve 5 in an open loop, but in this case, it is possible to control the electromagnetic relief valve 5 in an open loop. Drift occurs and pressure control accuracy deteriorates.

Therefore, the purpose of this invention is to maintain static pressure control accuracy equivalent to pressure feedback control while suppressing pressure overshoot to a small and short time period similar to conventional open loop control during the transition period when entering the pressure control state. be.

<Means for Solving the Problems> In order to achieve the above object, the pressure control circuit of the present invention, as shown in FIG. The outlet port 22 operates according to the differential pressure of the fluid.
An electromagnetic pilot relief valve 26 is connected to the spring chamber 16 of the normally open type pressure reducing main valve 13, which controls the pressure of the fluid in the spring chamber 16 and the target pilot pressure. A feedback system 27 is provided which controls the fluid pressure in the spring chamber 16 to the target pilot pressure by inputting a control signal corresponding to the comparison value.
It is characterized by being connected.

<Operation> With the above configuration, fluid flows into the upstream side of the electromagnetic pilot relief valve 26 from the pressure source 12 that can generate the target pilot pressure. The electromagnetic pilot relief valve 26 operates constantly to discharge the fluid, and accurately controls the fluid pressure within the spring chamber 16 to a target pilot pressure by a control signal from the feedback system 27. in this way,
The pressure reduction main valve 13 is configured to reduce the pressure in the spring chamber 16 by the operating electromagnetic pilot relief valve 26 regardless of whether the main line 11 is under flow control, pressure control, or in a transition state from flow control to pressure control. The pressure is always controlled to a constant pressure, and the pressure reduction main valve 13 operates according to the differential pressure between the spring chamber 16 and the pilot chamber 18, which is controlled to a constant pressure, and the pressure at the outlet port 22 is controlled.

<Examples> The present invention will be described in detail below with reference to illustrated examples.

In FIG. 1, 11 is a main line connected to a pressure source 12, and 13 is a pressure reducing main valve that connects an inlet port 21 and an outlet port 22 of the main line 12.

The pressure reducing main valve 13 is slidably fitted into a spool 15 having three lands 15a, 15b, and 15c in the valve chamber 14. A spring 17 is compressed in the spring chamber 16 at one end of the spool 15, and the spool 15 is operated according to the differential pressure between the spring chamber 16 and the pilot chamber 18 at the other end.
The outlet port 22 and the return port 23 are opened and closed, and the outlet port 22 and the return port 23 are opened and closed. The width Lp of the outlet port 22 is set to be very slightly larger than the width Ls of the central land 15b. In addition, 19 is spool 15
This is a spacer portion provided at the end of the pilot chamber 18 side.

A throttle 25 is interposed in a passage 24 communicating between the spring chamber 16 of the main pressure reducing valve 13 and an electromagnetic pilot relief valve 25 equipped with a proportional solenoid that generates an electromagnetic force proportional to the current value. This electromagnetic pilot relief valve 26 and the spring chamber 16 are connected by a feedback system 27, and the spring chamber 1
The pressure inside 6 is controlled by feedback. The feedback system 27 is the pressure detector 2
8 and an operational amplifier 29. Above pressure detector 2
8 detects the fluid pressure in the spring chamber 16 of the main pressure reducing valve 13, and sends a signal representing this fluid pressure to the operational amplifier 2.
Enter 9. A target pilot pressure signal Ip corresponding to the specified fluid pressure of the main line 11 to be controlled is further input to the operational amplifier 29. The operational amplifier 29 compares the signal representing the fluid pressure in the spring chamber 16 detected by the pressure detector 28 with the target pilot pressure signal Ip, and outputs a control signal obtained by amplifying this comparison value to the electromagnetic pilot relief valve 26. do. Therefore, the electromagnetic pilot relief valve 26 performs feedback control of the fluid pressure in the spring chamber 16 of the main pressure reducing valve 13 to the target pilot pressure corresponding to the target pilot pressure signal Ip.

On the other hand, the spring chamber 16 of the pressure reducing main valve 13 and the throttle 2
The pressure source 12 is connected to the passage 23 branching from the passage 23 through the flow rate regulating valve 32 with pressure compensation. Therefore, a constant flow of fluid always flows between the spring chamber 16 and the throttle 25, and as a result, the electromagnetic pilot relief valve 26 is always in operation at a certain opening degree.

With the above configuration, the electromagnetic pilot relief valve 2
6 is always in operation at a certain opening degree as described above despite feedback control, and the pressure reducing main valve 13
The fluid pressure in the spring chamber 16 is controlled by the electromagnetic pilot relief valve 26, regardless of the operating state of the main pressure reducing valve 13, that is, the flow rate control state of the main line 11, the pressure control state, and from flow control to pressure control. Accurately controls the target pilot pressure regardless of excessive conditions.

Suppose now that the main line 11 downstream of the outlet port 22 of the main pressure reducing valve 13 shifts from the flow rate control state to the pressure control state, and the pressure of the main line 11 rises rapidly.

Then, the spool 15 of the main pressure reducing valve 13 becomes
Since the fluid pressure in the main line 11, that is, the pilot chamber 18, becomes higher than the sum of the fluid pressure in the spring chamber 16, which is accurately controlled to the target pilot pressure, and the spring force of the spring 17, the main line 11, that is, the fluid pressure in the pilot chamber 18, immediately retreats to the spring chamber 16 side. , controls the pressure in the main line 11. When the spool 15 retreats, the fluid pressure in the spring chamber 16 tends to rise, but since the fluid in the spring chamber 16 is quickly discharged from the electromagnetic pilot relief valve 26, which always operates at a certain opening, the spring The fluid pressure in the chamber 16 does not rise excessively and the spool 15
quickly retreats, and the pressure overshoot in the main line 11 is small and lasts only for a short time, as shown by curve B in FIG. From a different perspective, since fluid is flowing into the electromagnetic pilot relief valve 26 from the pressure source 12 having a pressure higher than the target pilot pressure through the pressure compensated flow rate adjustment valve 32, the operational amplifier 29 and the electromagnetic pilot relief valve 26 are not in a saturated state but in an equilibrium state, so they operate with good response, and as a result, the pressure overshoot in the main line 11 is reduced. In other words, the pressure overshoot inherent in pressure feedback control due to the saturation of the operational amplifier, etc. in conventional pressure feedback control does not occur, but only the pressure overshoot caused by the pressure reducing main valve 13 itself, that is, the open control, causes a pressure overshoot equivalent to the pressure overshoot. be.

In addition, statically, the pressure in the spring chamber 16 of the main pressure reducing valve 13 is accurately controlled to the target pilot pressure by the electromagnetic pilot relief valve 26, so the fluid pressure in the main line 11 leading to the outlet port 22 is The static characteristics of pressure control with high precision equivalent to that of pressure feedback control can be obtained.

In the above embodiment, a pressure-compensated flow regulating valve is used as the flow regulating valve, but a throttle may be used instead. Further, the pressure source may be of any type as long as it has a pressure higher than the target pilot pressure.

<Effects of the Invention> As is clear from the above explanation, according to the pressure control circuit of the present invention, the transition period when entering the pressure control state is maintained while maintaining the same static characteristics (pressure control accuracy) as conventional pressure feedback control. Pressure overshoot can be suppressed to the same level as conventional open control.

[Brief explanation of drawings]

FIG. 1 is a circuit diagram of an embodiment of the present invention, FIG. 2 is a circuit diagram of a conventional example, and FIG. 3 is a graph illustrating pressure overshoot in the above embodiment and the conventional example. DESCRIPTION OF SYMBOLS 11... Main line, 12... Pressure source, 13... Pressure reduction main valve, 26... Electromagnetic pilot relief valve, 27
...Feedback system, 32...Flow control valve with pressure compensation.

Claims (1)

[Claims] 1 Pilot chamber 18 communicating with outlet port 22
An electromagnetic pilot relief valve 26 is connected to the spring chamber 16 of the normally open type pressure reducing main valve 13 that operates according to the differential pressure of the fluid between the valve and the spring chamber 16 to control the pressure of the outlet port 22. At the same time, a control signal corresponding to a comparison value between the fluid pressure in the spring chamber 16 and the target pilot pressure is input to the electromagnetic pilot relief valve 26 to adjust the fluid pressure in the spring chamber 16 to a value corresponding to the target pilot pressure. 1. A pressure control circuit characterized in that a feedback system 27 is provided to control the pressure to a pressure of 0.05 to 1.0, and a pressure source 12 is connected to the spring chamber 16.