KR930008517B1 - Control device for governor proportion valve - Google Patents

Abstract

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Description

Control device of constant pressure proportional valve

1 to 5 relate to the first embodiment,

1 is a control block diagram.

2 is a schematic diagram of a gas fan heater.

3 is a cross-sectional view of the solenoid valve and the positive pressure proportional valve.

4 is a graph showing the relationship between the frequency and the raising of the regulator.

5 is a graph showing the relationship between frequency and hysteresis.

6 and 7 relate to the second embodiment,

6 is a control block diagram.

7 is a graph showing the relationship between the amount of current and frequency.

8 and 9 relate to the third embodiment,

8 is a control block diagram.

9 is a graph showing the relationship between the amount of current and frequency.

10 is a control block diagram according to the fourth embodiment.

11 is a cross-sectional view of a conventional hydrostatic proportional valve.

* Explanation of symbols for main parts of the drawings

10: positive pressure proportional valve 21: primary pressure chamber

23: valve body 25: secondary pressure chamber

26: electronic actuator 33: control unit

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a control device for supplying current to an electromagnetic actuator of a voltage proportional valve, and more particularly, to a technique for suppressing a constant proportional valve and a constant pressure gradient.

In the voltage proportional valve in which the constant pressure valve and the electromagnetic proportional valve are integrated, the valve body vibrates in accordance with the gas passing through. The vibrating valve element and the valve seat come into contact with each other to form a sound source.

In general, the frequency of this sound source closely matches the natural frequency of the secondary pressure chamber of the hydrostatic valve. For this reason, static pressure skew arises by resonance. In order to suppress this static pressure slope, the partition wall provided with the communication hole was provided in the secondary pressure chamber conventionally.

That is, the positive pressure proportional valve (also known as a pressure regulator), which has been provisionally filed by the present applicant (Japanese Patent Publication No. 56-24282), is a primary pressure chamber connected to the inlet port 2 as shown in FIG. (3), the valve | bulb 6 in the middle which communicated with the outlet 4, the secondary pressure chamber 5 connected, etc., and the spring 8 of the back side according to the pressure increase in this primary pressure chamber 3, and the like. In which the side 7 connected to the diaphragm 9, which is retracted, is operated on the secondary pressure chamber 5 side, the small hole 11 is formed on the rear surface of the diaphragm 9. The air chamber 12 is formed by connecting with the atmosphere through the air chamber, and at the same time, the air chamber 15 is formed by dividing it into a partition 14 having a communication hole 13 and a communication hole 13 on the rear surface of the secondary pressure chamber 5. It was.

In this way, when a partition wall having communication holes is provided in the secondary pressure chamber, the natural frequency of the secondary pressure chamber is released at a high frequency. For this reason, the frequency of the sound source does not coincide with the natural frequency of the secondary pressure chamber, and the static pressure gradient is suppressed.

Therefore, in the conventional positive pressure proportionality valve, a separate partition wall having communication holes must be installed in the secondary pressure chamber in order to suppress the static pressure gradient, and thus, the structure of the positive pressure proportionality valve is complicated and the number of parts increases.

SUMMARY OF THE INVENTION The present invention has been made to solve the above problems, and an object thereof is to control a constant pressure proportional valve capable of eliminating partitions in a secondary pressure chamber, suppressing static pressure skew, and further suppressing hysteresis of a proportional valve. To provide.

In order to achieve the above object, the control device of the hydrostatic proportional valve of the present invention employs the following technical means.

[Means corresponding to claim 1]

The control device of the positive pressure proportional valve displaces the valve body in accordance with the gas pressure flowing into the primary pressure chamber, and corresponds to the amount of current applied to the constant pressure mechanism for maintaining a constant flow rate of the gas flowing out of the secondary pressure chamber. A positive pressure proportional valve having an electromagnetic actuator for imparting a displacement force to the sieve, and a pulse wave current at a frequency excluding the natural frequency of the secondary pressure chamber is applied to the electromagnetic actuator to control the displacement force applied to the valve body. It is provided with a control unit. Control of the amount of current by the pulse waveform can be achieved by changing the time ratio of ON and OFF of the pulse signal or by changing the amount of ON pulse current.

[Means corresponding specifically to claim 1]

When the current amount of the actuator is less than a predetermined amount of current, the control unit applies a pulse type current of a frequency to avoid the natural frequency of the secondary pressure chamber to the electronic actuator, and when the current amount of the actuator is greater than or equal to the predetermined amount of current, A low frequency pulse waveform current is applied to the electronic actuator.

[Means corresponding to claim 2]

The frequency applied to the electronic actuator by the control unit is 10 Hz or less than the natural frequency of the secondary pressure chamber, or 10 Hz or more of the natural frequency and 1000 Hz or less.

[Means corresponding to claim 4]

The control unit applies a pulse waveform current of 150 to 1000 Hz to the electric actuator when the current amount of the electronic actuator is less than the predetermined current amount, and a pulse waveform current of less than 150 Hz when the current amount of the actuator is greater than or equal to the predetermined current amount. It is provided with a switching means for applying to the electronic actuator.

[Means corresponding to claim 5]

The controller is provided with inverse proportion means for decreasing the frequency of the pulse waveform in inverse proportion from 150 to 1000 Hz as the amount of current in the electronic actuator increases.

[Means corresponding to claim 6]

The control section is provided with gas type switching means for switching the frequency of the pulse waveform according to the gas type.

[Operation and Effect of the Invention Corresponding to Claim 1]

The frequency of the pulse waveform applied to the electromagnetic actuator becomes a frequency which avoided the natural frequency of the secondary pressure chamber. At this time, since the sound source of the proportional valve is a contact sound between the valve body and the valve seat, the frequency of the sound source generated in the proportional valve does not match the natural frequency of the secondary pressure chamber.

As a result, the static pressure skew caused by the coincidence of the frequency of the sound source and the natural frequency of the secondary pressure chamber can be suppressed even if it does not occur or occurs. That is, by removing the partition wall in the secondary pressure chamber, it is possible to suppress the static pressure skew.

In addition, by eliminating the partition wall in the secondary pressure chamber, it is possible to simplify the structure of the hydrostatic proportional valve, and the use parts thereof are reduced.

As a result, it is possible to increase the proportionality of the positive pressure proportionality valve, thereby reducing the cost of the constant pressure proportionality valve.

[Effects and Effects of the Invention Corresponding to the Specific Means of Claim 1]

When the current amount of the electromagnetic actuator is less than the predetermined current amount, that is, when the lift amount of the valve body is small, the degree of contact between the valve body and the valve seat increases. As a result, the sound source of the static pressure gradient is large.

At this time, the frequency of the pulse waveform applied to the electromagnetic actuator is a frequency that avoids the natural frequency of the secondary pressure chamber, so that the frequency of the sound source generated in the proportional valve and the natural frequency of the secondary pressure chamber do not coincide. It is possible to suppress static pressure skew.

On the contrary, when the current amount of the electromagnetic actuator is equal to or greater than the predetermined current amount, that is, when the leaf amount of the valve body is large, the degree of contact between the valve body and the valve seat becomes small. As a result, the sound source of constant pressure ringing becomes small. At this time, by setting the frequency of the pulse waveform applied to the pulse waveform low, the static pressure gradient is suppressed because there is no sound source (or small) even if the frequency of the sound source and the frequency in the secondary pressure chamber coincide. Since a low frequency pulse waveform is applied to the electromagnetic actuator, the vibration width of the valve body is increased, thereby increasing the effect of suppressing the hysteresis of the proportional valve.

That is, by adopting this method, it is possible to suppress the static pressure skew and to suppress the hysteresis when the degree of opening of the valve body is large.

[Operation and Effect of the Invention Corresponding to Claim 2]

Controlling the displacement force applied to the valve body by applying a wave shaped current to the electromagnetic actuator can suppress the hysteresis of the proportional valve.

However, when the frequency of the pulse waveform is higher than 1000 Hz, the vibration width of the valve body becomes very small, possibly exceeding the numerical value that can allow hysteresis.

Therefore, the hysteresis of the proportional valve can be suppressed by setting the frequency of the pulse waveform applied to the electromagnetic actuator to 1000 Hz or less.

In addition, the natural vibration means has a peak within 10 Hz before and after, and has no influence other than 10 Hz before and after. Therefore, by making the frequency of the pulse waveform applied to the electromagnetic actuator out of 10 Hz before and after the natural frequency, the frequency of the sound source can be made to be inconsistent with the natural frequency of the secondary pressure chamber.

[Operation and Effect of the Invention Corresponding to Claim 4]

If the current amount of the electronic actuator is less than the predetermined current amount, the sound source is large. At this time, the switching means sets the frequency of the pulse waveform to 150 to 1000 Hz. The natural frequency of a typical secondary pressure chamber is around 100 Hz.

For this reason, the frequency of a sound source (contact sound which a valve body and a valve seat contact | abut) does not correspond with the natural frequency in a secondary pressure chamber, and even if a sound source is large, it is possible to suppress static pressure gradient.

On the contrary, when the current amount of the electronic actuator is more than the predetermined current, the sound source is small. At this time, the power supply means sets the frequency of the pulse waveform to less than 150 Hz. As a result, even if the frequency of the sound source coincides with the natural frequency of the secondary pressure chamber, since there is no sound source (or because it is small), the static pressure gradient is suppressed. By setting the frequency of the pulse waveform to less than 150 Hz, the vibration width of the valve body can be increased and the hysteresis of the proportional valve can be suppressed.

[Operation and Effect of the Invention Corresponding to Claim 5]

As the current amount of the electromagnetic actuator increases, the lift amount of the valve body increases and the degree of contact between the valve body and the valve seat gradually decreases. In other words, as the amount of current in the electronic actuator increases, the sound source becomes smaller. Therefore, as the amount of current of the forward actuator increases by inverse proportion, the frequency of the pulse waveform decreases in inverse proportion from 150 to 1000 Hz. When the frequency of the pulse waveform is reduced in Braille, the effect of suppressing the static pressure gradient due to the frequency of the pulse waveform is reduced, but the sound source is smaller as the frequency is lowered. As a result, it is possible to suppress static pressure skew.

On the other hand, when the frequency of the pulse waveform is lowered, the vibration width of the valve body increases. In other words, as the amount of current in the electromagnetic actuator increases, the vibration width of the valve body increases and the hysteresis of the proportional valve decreases.

[Operation and Effect of the Invention Corresponding to Claim 6]

The constant pressure proportional valve is sometimes used as an adjusting means for adjusting the combustion amount of gas (gas fuel). The amount of heat per body is different depending on the type of gas. For this reason, the lift amount of the valve body for obtaining the predetermined combustion amount varies depending on the type of gas.

That is, the generation level of static pressure slope differs according to the type of gas. Thus, the frequency of the pulse waveform is switched to the gas type switching means to set the frequency of the pulse waveform corresponding to the type of gas.

That is, the frequency of the pulse waveform is set high in the gas having a large constant pressure slope, and the frequency of the pulse waveform is set low in the gas having a small constant pressure slope.

As a result, it is possible to suppress the hysteresis of the proportional valve in the gas with small constant pressure gradient.

EXAMPLE

Next, the control apparatus of the constant pressure proportionality valve of this invention is demonstrated based on drawing.

[First embodiment corresponding to claims 1 and 2]

2 is a schematic configuration diagram of a gas fan heater to which the present invention is applied.

The gas fan heater 1 is a heating apparatus which burns gas (gas fuel) internally, mixes the combustion gas with the air sucked into the intake port 3 of the combustion passage 2, and blows it out to the exhaust port 4.

Air suction into the combustion passage 2 and combustion gas discharge from the exhaust port 4 are made by the blower 5 provided in the combustion passage 2. The combustion in the combustion passage 2 is performed by the combustion section 6 provided in the combustion passage 2. This combustion part 6 is equipped with the burner 6a which forms a flame by burning the gas supplied to the gas path 7 with the air guide | induced to the combustion path 2, and is formed. The gas passage 7 is provided with two solenoid valves 8 and 9 and a constant pressure proportionality valve 10 from upstream.

In this embodiment, the two solenoid valves 8, 9 and the constant pressure proportionality valve 10 are integrated, and the structure thereof is briefly described in FIG.

The upstream solenoid valve 8 always supports the armature 13 integrated with the valve body 12 by the spring 14, as the valve body 12 blocks the valve seat 11 formed in the gas passage. It is becoming. Then, when the electromagnetic coil 15 around the armature 13 is energized, the armature 13 is sucked in response to the spring force of the spring 14, and the valve body 12 is separated from the valve seat 11, so that the gas It is supposed to open the passage. In the downstream solenoid valve 9, as the valve body 17 blocks the valve seat 16 formed in the gas passage, the armature 18 integral with the valve body 17 is always forced by the spring 19. Is getting. Then, when the electromagnetic coil 20 around the armature 18 is energized, the armature 18 is attracted against the spring force of the spring 19, and the valve body 17 drops from the valve seat 16, thereby allowing the gas passage. It is supposed to open.

The constant pressure proportionality valve 10 is equipped with the valve body 23 provided in the diaphragm 22 (3 cm diameter around) which displaces according to the pressure of the primary pressure chamber 21. This valve body 23 changes with the pressure of a primary pressure chamber, and displaces the opening degree (gas flow path) of the proportional valve formed between the valve body 23 and the valve seat 24. Specifically, the valve body 23 is located below the valve seat 24 and the valve body 23 is displaced downward, so that the gap between the valve body 23 and the valve seat 24 (gas passage). ) Becomes large. And when the pressure of the primary pressure chamber 21 becomes large, the force which displaces the valve body 23 to upper part of a figure acts and acts to block the valve seat 24. As shown in FIG.

On the contrary, when the pressure of the primary pressure chamber 21 decreases, it acts to open the valve seat 24 on which the force to displace the valve body 23 acts downward of the figure. As a result, even if the pressure of the gas flowing into the primary pressure chamber 21 fluctuates, it is possible to maintain the flow rate of the gas which flows out of the secondary pressure chamber 25 (around 14 cm <2>) constant (static pressure mechanism mechanism). ).

The static pressure proportional valve 10 is provided with an electromagnetic actuator 26 for imparting a displacement force to the valve body 23. The electromagnetic actuator 26 is composed of an electromagnetic coil 27 provided above the valve body 23 and an armature 28 to which a displacement force is applied in correspondence with the current amount of the electromagnetic coil 27. When the current amount of the electromagnetic coil 27 is changed, the displacement force is applied to the valve body 23 via the armature 28. Specifically, when the amount of current in the electromagnetic coil 27 increases, the force for applying the valve body 23 downward in the figure increases, and the proportional valve formed between the valve body 23 and the valve seat 24. The opening degree of becomes large.

In addition, in the figure, 29-32 represents a spring, and the spring 32 which applies the force to one end of the armature is provided so that the force applied to the adjustment screw 32a can be finely adjusted.

The electromagnetic coils 15 and 20 of the two solenoid valves 8 and 9 and the electromagnetic coils 27 of the constant pressure proportionality valve 10 are energized and controlled by the control part 33.

Next, the control part 33 is demonstrated.

1 is a block diagram of the controller 33. The control unit 33 performs the energization control of the speaker 34, the blower 5, the two solenoid valves 8, 9 and the constant pressure proportionality valve 10 in accordance with the pressure from various sensors. A computer 35, a relay circuit 36, and a drive circuit 37 are provided.

In addition, as a specific example of various sensors, the temperature of the air sucked into the controller 38 and the combustion passage 2, which is manually operated according to the user and gives the on-off instruction of the whole apparatus, sets the load and the room temperature. The thermistor 39 and the thermocouple 40 which detect a flame are illustrated.

The opening degree (the amount of current of the electromagnetic coil 27) of the constant pressure proportional valve 10 of the present embodiment is determined by the microcomputer 35.

The microcomputer 35 sets the opening degree of the constant pressure proportionality valve 10 according to the difference between the temperature detected by the thermistor 39 and the temperature set in the controller 38. Then, the microcomputer 35 outputs a signal in which the ratio of the ON-OFF time is changed in accordance with the set temperature (main duty ratio control). The frequency of the pulse symbol output by the microcomputer 35 is controlled at 500 Hz.

The pulse signal of 500 Hz, in which the ratio of ON-OFF output from the microcomputer 35 changes, is current-converted in the drive circuit 37 and applied to the electromagnetic coil 27 of the constant pressure proportional valve 10.

Next, the operation of the above embodiment will be briefly described.

The controller 38 is operated by the user, and when the operation is started, after the prepurge, the two solenoid valves 8 and 9 and the positive pressure proportionality valve 10 are opened, and the speaker 34 is driven to operate the gas at the burner 6a. Ignition takes place. After ignition, the microcomputer 35 determines the opening degree of the positive pressure proportionality valve 10 according to the set temperature of the controller 38 and the detection temperature of the thermistor 39, and burns the gas in the combustion section 6. .

The microcomputer 35 outputs a duty uncontrolled pulse signal in accordance with the set opening degree of the constant pressure proportionality valve 10. The pulse signal output by the microcomputer 35 is converted into current in the driving circuit 37 and applied to the electromagnetic coil 27 of the constant pressure proportional valve 10.

That is, a pulse waveform current is applied to the electromagnetic coil 27.

Since the current applied to the electromagnetic coil 27 is a 500 Hz pulse symbol, the armature 28 and the valve body 23 vibrate at 500 Hz.

4 shows the relationship between the frequency of the pulse symbol and the sound pressure of the static pressure gradient. As can be seen from the graph, static pressure skew occurs when the frequency of the pulse signal is between 100Hz and 10Hz.

5 shows the relationship between the hysteresis of the proportional valve and the frequency of the pulse signal. As shown in this graph, when the frequency of the pulse signal exceeds 1000 Hz, the vibration width of the armature 28 and the valve body 23 becomes very small, and exceeds the numerical value that can allow hysteresis in function.

As shown in the present embodiment, by setting the frequency of the pulse signal to 500 Hz, it is possible to eliminate the partition wall having the communication hole conventionally used in the secondary pressure chamber, to suppress the static pressure skew, and at the same time, the positive pressure proportional valve 10 The hysteresis of can be suppressed small.

In addition, since the partition wall is removed from the secondary pressure chamber 25, the positive pressure proportionality valve 10 can be reduced in weight, and the manufacturing cost of the constant pressure proportionality valve 20 can be reduced.

[Modifications in First Embodiment]

In this embodiment, the frequency of the pulse signal is set to 500 Hz, but if it is between 50 to 90 Hz or 110 to 1000 Hz, another frequency may be set.

The reason why the frequency of the pulse signal is 50 Hz or more is because if the frequency is lower than 50 Hz, the valve body follows the change in the applied current, and the stroke of the valve body 23 becomes large, and the contact sound becomes loud.

[Second embodiment corresponding to claims 1 and 4]

6 is a block diagram of the control unit 33 including the embodiment corresponding to claims 1 and 4. FIG.

The microcomputer 35 of this embodiment is provided with switching means 41 for switching the frequency of the pulse symbol output to the drive circuit 37 to 100Hz and 500Hz. As shown in FIG. 7, the switching means 41 sets 500 Hz when the current amount of the constant pressure proportionality valve 10 is less than the predetermined current amount X. The current amount of the constant pressure proportionality valve 10 is a predetermined amount of current X. As shown in FIG. ) Is set to 100 Hz. In addition, in the figure, the hatched area indicates the range in which the static pressure slope occurs.

When the current amount of the constant pressure proportionality valve 10 is small, the lift amount of the valve body 23 is also small, and the contact sound (sound source) between the valve body 23 and the valve seat 24 also becomes large.

At this time, by setting the frequency of the pulse symbol to 500 Hz, the static pressure skew can be suppressed.

On the contrary, when the current amount of the constant pressure proportional valve 10 is large, the lift of the valve body 23 is large, and the contact sound (sound source) between the valve body 23 and the valve seat 24 is small. For this reason, when the amount of current of the constant pressure proportionality valve 10 is large, even if the frequency of a pulse symbol is set to 100 Hz, static pressure skew can be suppressed. By setting the frequency of this pulse signal to 100 Hz, the hysteresis of the constant pressure proportionality valve 10 can be reduced compared with the hysteresis of 500 Hz state.

[Modifications in Second Embodiment]

In addition, although the switching means of this embodiment set and switched 100 Hz and 500 Hz, you may switch by setting another frequency.

The switching means switches two frequencies, but may switch three or more frequencies.

[Third embodiment corresponding to claims 1 and 5]

8 is a block diagram of the control unit 33 including the embodiment corresponding to the first and fifth claims.

As shown in FIG. 9, the microcomputer 35 of the present embodiment has an inverse proportional frequency of the pulse signal output to the drive circuit 37 from 500 Hz as the amount of current in the constant pressure proportionality valve 10 increases. It is provided with the inverse proportion 42 which reduces.

When the current amount of the constant pressure proportionality valve 10 is less than the predetermined current amount X, the frequency of the pulse signal becomes 150 Hz or more.

In the figure, the hatched area indicates the range in which the static pressure slope occurs.

When the amount of current in the constant pressure proportionality valve 10 is minimum, the amount of lift of the valve body 23 is also minimum. For this reason, the contact sound (sound source) of the valve body 23 and the valve seat 24 also becomes maximum. At this time, by setting the frequency of the pulse signal to 500 Hz, the static pressure skew is suppressed.

As the current amount of the constant pressure proportionality valve 10 increases, the degree of contact between the valve body 23 and the valve seat 24 gradually decreases. That is, the sound source becomes small.

Therefore, if the frequency of the pulse waveform gradually decreases as the current amount of the constant pressure proportional valve 10 increases, the effect of suppressing the static pressure slope is reduced, but the sound source also decreases as the frequency decreases, and consequently, the constant pressure slope is suppressed. The effect of suppressing gradually increases.

[Modifications in Third Embodiment]

The inverse proportional means of this embodiment sets the frequency of the pulse signal when the current value of the constant pressure proportionality valve 10 is 500 Hz, but may be set to the next frequency as long as it is 150 Hz or more at the current value at which the constant pressure slope occurs.

[Fourth embodiment corresponding to claim 6]

10 is a block diagram of the control unit 33 including the embodiment according to claim 6.

The microcomputer 35 of this embodiment has gas type switching means 43 for switching the frequency of the pulse waveform according to the gas type.

The gas used for a gas fan heater (refer to 1st Example) differs in the quantity of heat per volume. That is, the gas amount for obtaining a predetermined combustion amount is different, and as a result, the lift amount of the valve body 23 varies depending on the type of gas.

In this embodiment, the frequency of the pulse symbol output by the microcomputer 35 is switched to the gas type switching means 43, and the frequency of the pulse waveform corresponding to the gas type is set.

Specifically, in the case of using gas having a large amount of heat per volume (for example, LP gas and 13A gas), the lift amount (proportional valve opening degree) of the valve body 23 is small and the valve of the valve body 23 is small. Since the contact with the seat 24 is large, the frequency of the pulse waveform is set to 500 Hz.

On the contrary, when the gas (for example, 6 C gas) with a small amount of heat per volume is used, since the lift amount of the valve body 23 is large and the contact degree of the valve body 23 and the valve seat 24 is the same, a pulse is generated. Set the frequency of the waveform to 150 Hz.

As a result, it is possible to suppress hysteresis when using a gas having a small amount of heat per volume (a kind of gas having a small constant pressure gradient).

[Modifications in the fourth embodiment]

In addition, the gas type switching means of the present embodiment is switched by setting 100 Hz and 500 Hz, but may be switched by setting another frequency.

The gas type switching means switches two frequencies, but may switch three or more frequencies according to the gas type.

[Common Modifications of First to Fourth Embodiments]

Although the example which applied this invention to the positive pressure proportional valve of a gas fan heater was shown, you may apply this invention to the constant pressure proportional valve used for a gas water heater as well as an FF type gas heating apparatus.

Although the example which used the microcomputer for the control part was shown, what is called the discrete circuit which does not use the microcomputer may also be comprised.

Although the example in which the amount of current of the positive pressure proportionality valve was changed by duty ratio control was shown, you may change the amount of current of a positive pressure proportionality valve by making the time ratio between ON and OFF of a pulse signal constant, and changing the electric current value of a pulse waveform.

Claims (5)

The secondary pressure chamber 25 is disposed by displacing the valve body 23 according to the gas pressure flowing into the primary pressure chamber 21 into the positive pressure proportional valve 10 integrally formed with the two solenoid valves 8 and 9. ) Is provided with an electronic actuator 26 for imparting the displacement force of the valve body 23 in accordance with the amount of current applied to the constant pressure mechanism that maintains a constant flow rate of the gas flowing out from In the controlling unit 33, when the current amount of the actuator 26 is less than a predetermined amount of current, a pulse wave current of a frequency avoiding the natural frequency of the secondary pressure chamber 25 is output and the current amount of the actuator 26 is output. In the case of more than a predetermined amount of current, the microcomputer 35 outputs a pulse frequency current of a low frequency and the pulse waveform current of a predetermined frequency is input to the electronic actuator 26 by receiving a predetermined signal output from the microcomputer 35. Directly And a driving circuit (37) for applying and controlling the displacement force applied to the valve body (23). 2. The control device of a constant pressure proportional valve according to claim 1, wherein said frequency is 10 Hz or less than said natural frequency of said secondary pressure chamber (25) or more than 10 Hz of said natural frequency and 1000 Hz or less. The electronic device of claim 1, wherein in the microcomputer 35, when the current amount of the electronic actuator 26 is less than a predetermined current amount, a pulse wave current of 150 to 1000 Hz is applied to the electronic actuator 26. And a switching means (41) for applying a pulse wave current of less than 150 Hz to the electromagnetic actuator (26) when the current amount of the actuator is greater than or equal to a predetermined current amount. The microcomputer 35 is provided with inverse proportional means (42) for decreasing the frequency of the pulse waveform in inverse proportion from 150 to 1000 Hz as the amount of current in the electronic actuator (26) increases. Control device of the hydrostatic proportional valve, characterized in that. 2. The control device for a constant pressure proportional valve according to claim 1, wherein said microcomputer (35) is provided with gas type switching means (43) for switching the frequency of pulse waveforms according to the gas type.

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