JP4343322B2 - Pressure gas supply device - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to an apparatus for supplying a gas at a stable pressure. More particularly, the present invention relates to an apparatus for stabilizing the pressure when the gas flow rate changes.
[0002]
[Prior art]
In a hydraulic / pneumatic circuit system, various types of control valves are used to control the pressure, flow rate, direction, and the like of fluid flowing through the circuit. In general, the hydraulic / pneumatic control valves are roughly classified into pressure control valves, flow control valves, and directional control valves. The pressure control valve adjusts the supply pressure to generate a predetermined output. The flow control valve controls the flow rate of the pressure fluid from a pump or the like. The direction control valve is a control valve that changes the direction of movement by controlling the direction of flow. These control valves are subdivided as having various functions, structures, and operational characteristics depending on the purpose and method of use. For example, the pressure control valve includes a relief valve, an unloader valve, a sequence valve, and a pressure reducing valve. Since the control valve has a common function in terms of fluid control, it basically has many structural features regardless of whether the medium flowing through the circuit is oil (liquid phase fluid) or air (gas phase fluid pressure). Have something in common. However, since the present invention relates to an apparatus for adjusting air pressure, hereinafter, the prior art will be described for a control valve for adjusting air pressure.
[0003]
There is a pressure control valve that performs pressure control in a pneumatic circuit. The pressure reducing valve reduces the pressure of the primary compressed air sent from the air pressure source, adjusts the secondary pressure to a predetermined set value, changes the primary pressure, or changes the secondary air flow rate. It has the function of suppressing the fluctuation of the set pressure to the minimum and supplying a stable air pressure. In order to keep the secondary side pressure below a predetermined pressure, the relief valve and the safety valve function to relieve the pressure increase on the secondary side and keep it below the predetermined pressure when the pressure exceeds the predetermined pressure. Of these, the relief valve functions to release part or all of the compressed air in order to maintain the pressure of the pneumatic circuit at a set value. On the other hand, the safety valve limits the maximum pressure of the pneumatic circuit in order to prevent damage to pneumatic equipment and pipes, and when the pressure in the circuit exceeds the set value, it works to release the rising pressure from the circuit . Both the relief valve and the safety valve are the same as the pressure reducing valve in terms of reducing the pressure. The difference is in its intended use. In any case, the pressure control valve has many aspects common to functions and applications, and is often used in a structure that takes each function into consideration.
[0004]
FIG. 1 is an example of a direct acting relief valve. The direct acting relief valve includes a valve portion 101 and an adjustment portion 102. By rotating the handle 103 of the adjustment unit, the adjustment screw 104 is moved up and down to adjust the strength of the adjustment spring 105. The valve body 106 and the adjustment spring 105 are interlocked. Normally, the valve body 106 is pushed down by the force of the adjustment spring 105 and is in close contact with the valve seat 107 to prevent fluid flow. The relief pressure is constantly applied to the diaphragm 108 from the A side in the figure. When the relief pressure applied to the diaphragm 108 increases and becomes higher than the elastic force of the adjustment spring 105, the diaphragm 108 is pushed up, the valve body interlocked with it rises, the valve body 106 and the valve seat 107 are separated, and the fluid flows from the port A side to the port B. It flows out to the side and is discharged. As a result, when the relief pressure on the A side is lowered again, the valve body 106 is pushed down by the force of the adjustment spring 105, the valve body 106 and the valve seat 107 are brought into close contact with each other, and relief (discharge) is stopped.
[0005]
FIG. 2 is an example of a conventional pilot type 2-port pressure reducing valve. The pilot chamber 153 is connected to the pilot port 151 through the pilot passage 152. The breathing chamber 163 is connected through the breathing passage 162. A pressure equalizing chamber 112 having substantially the same area as the opening area of the valve seat 107 is connected to the port A through the pressure equalizing hole 113.
[0006]
When pilot air is supplied from the pilot port 151, the pressure in the pilot chamber 153 increases, the rod 114 is pushed up by overcoming the force of the return spring 110, the valve body 106 is separated from the valve seat 107, and air flows from the port A to the port B. On the other hand, when the air in the pilot chamber 153 is removed, the valve body 106 is pushed down by the elastic force of the return spring 110, the valve seat 107 is brought into close contact, and the ports A and B are shut off. In the case of a pressure reducing valve, the port A is also called the primary side (suction) and the boat B is also called the secondary side (discharge).
[0007]
In the above two-port valve, when the pilot fluid pressure is increased, the opening speed of the valve seat 107 can be increased, but the closing speed of the valve seat 107 due to the urging force of the return spring 110 is decreased. In order to increase the closing speed of the valve seat, it is necessary to lower the pilot fluid pressure or increase the biasing force of the return spring 110. In this case, however, the opening speed of the valve seat 107 becomes slow. Arise. In Japanese Patent Laid-Open No. 4-38951, in order to solve this problem, a relief valve with a relief is provided in the drive unit (adjusting unit) 102, and the relief valve with a relief is pressed when the piston 111 reaches the end of the drive stroke. Then, the fluid in the pilot chamber 153 is discharged, and the pressure of the fluid is reduced to a pressure that outputs an acting force substantially equal to the biasing force of the return spring 110, and the pressure is maintained. Thereby, the valve body 106 and the valve seat 107 can be opened and closed at a high speed.
[0008]
FIG. 3 is an example of a pressure reducing valve with an external pilot type relief. Pilot pressure is applied to the diaphragm 108a on the pilot chamber 153 side, and air pressure on the secondary side (port B side) is applied to the diaphragm 108b. The pressure that determines the opening and closing of the valve body 106, that is, the set pressure is determined by the pilot pressure. When pilot air is supplied from the pilot port 151 to the pilot chamber 153 and the pressure applied to the diaphragm 108a is higher than the pressure applied to the secondary diaphragm 108b, that is, when the secondary air pressure is lower than the set pressure, the stem The valve body 106 that is linked through 117 is pushed down to open the valve passage, and air flows from the port A (primary side) to the port B (secondary side). When the pressure on the secondary side is balanced with the set pressure, the diaphragm 108 (108a and 108b operate in conjunction with each other, so here, simply described as “diaphragm 108”) is pushed up, the valve body 106 is closed, and the primary side and the secondary side are closed. The secondary passage is closed and the air flow is blocked. At this time, when the pressure on the secondary side is higher than the set pressure, the diaphragm 108 is pushed up, the relief valve body 118 is opened, and the excess pressure passes through the relief nozzle 120 and is discharged to the relief hole 121. When the compressed air on the secondary side is consumed and the pressure on the secondary side decreases, the valve body 106 opens again, and the compressed air flows from the primary side to the secondary side. In this way, the compressed air always flows from the primary side to the secondary side while the pressure on the secondary side is kept below a certain value (set pressure).
[0009]
The above example is an example of a mechanical pressure adjustment mechanism using an adjustment spring or a pilot pressure, but there is also a system in which this is controlled by an electronic circuit. In the case of an electronic circuit, since the adjustment pressure can be set digitally, the setting is easy. FIG. 4 shows the principle of a simple air pressure solenoid valve. When a current is passed through the solenoid 122, the plunger 123 is attracted by the solenoid (electromagnet), the poppet 124 interlocked therewith is lifted, the valve is opened, and the compressed air from the port A flows to the port B. When the current is cut off, the plunger 123 is pushed down by the plunger spring 121, the poppet 124 interlocked therewith is pushed down, the valve is closed, and the air flow from the port A to the port B is blocked.
[0010]
When determining whether or not to pass current through the solenoid 122 based on the air pressure in the circuit, a pressure sensor is provided in the circuit, and the pressure control value of the pressure sensor is preset in the electronic control circuit. Whether to energize the solenoid is determined by comparing with the pressure value. Since it is an electronic control circuit, the set value can be set by upper and lower limits. In this case, since the solenoid 122 can be energized only when the pressure measured by the pressure sensor is within the upper and lower limits of the set value, air is circulated within a specific range of pressure in the circuit. You can also.
[0011]
FIG. 5 shows an example of a double-acting pneumatic cylinder (air cylinder) having two ports A and B for supplying and exhausting air. In this type of pneumatic cylinder, the piston 111 is driven left and right by switching a port for supplying air pressure and a port for exhausting by a switching valve (electromagnetic valve). That is, when air is supplied to the port A, the piston 111 moves to the left and the air in the cylinder is exhausted from the port B. On the other hand, when port B becomes the air supply side by the switching valve, the piston moves to the right and air is exhausted from port A.
[0012]
FIG. 6 shows an example of a weight type relief damper type control valve that constantly sends a large amount of air supplied from port A stably to port B while adjusting the pressure. The relief valve 301 opens and closes by rotating around a fulcrum 303. A weight 302 is attached to the valve 301. By changing the weight of the weight, the pressure of the chamber 304 can be changed. However, this pressure control method has a problem that the position of the weight 302 is shifted from the center as the valve 301 is opened, and the adjustment pressure changes.
[0013]
[Problems to be solved by the invention]
Several control valves have been seen in the prior art as devices for controlling air pressure. Many control valves are used to control the circulation of high-pressure gas in a closed circuit. The purpose of the present invention is to provide a large amount of air at all times with a stable amount of air pressure fluctuation and a small amount of air pressure. Valves have problems such as poor controllability and expensive equipment. In particular, when the consumption condition on the load side changes suddenly, a delay occurs due to the resistance of the relief system and the like, resulting in a failure that increases the pressure control width.
[0014]
A pressure control device using a relief damper is suitable as a pressure control device that constantly supplies a large amount of air as an object of the present invention. In addition, the structure is simple, there is no resistance in the exhaust path for releasing the pressure, and there is an advantage that a large opening area can be secured as compared with the apparatus shown in FIG. However, in this apparatus, since the pressure change changes depending on the opening degree of the relief valve, a mechanism for adjusting the pressure by adjusting the position of the weight is necessary to make this constant. However, when such a mechanism is used, there is a new problem that pulsation is intense and stability is poor. This is because if the opening of the valve at the moment when the pressure rises is larger than the required amount, a sudden change in pressure occurs, and the valve is repeatedly operated in the closing direction, which may cause pulsation. .
[0015]
Although a method of controlling a motor-operated valve (solenoid valve) with an adjustment needle based on a signal from a pressure sensor is also conceivable, it is difficult to control instantaneous and random flow rate changes and pressure changes on the load side. There is a method using PID control, but in this case, there is a problem that a delicate setting corresponding to a change in the set pressure is required. In addition, since an electric circuit is used, the circuit becomes expensive and complicated.
[0016]
The problem to be solved by the present invention is that, in an apparatus that supplies a large amount of air at a high pressure, it reacts instantaneously to a sudden change in the air amount or pressure on the load side, does not cause pulsation, and the pressure fluctuation range Is to propose a small air pressure control device.
[0017]
[Means for Solving the Problems]
In order to solve the above problems, the present invention provides an apparatus for supplying gas at a constant pressure with a pressure chamber. An opening area adjusting plate for changing the opening area of the pressure adjusting opening, The apparatus includes a pressure adjusting movable valve facing the opening surface of the pressure adjusting opening, and a pressure adjusting mechanism that moves the pressure adjusting movable valve while maintaining a substantially parallel state with the opening surface.
[0018]
The pressure adjusting movable valve is urged and supported in a direction to close the valve by an air cylinder or a weighted mechanism using gravity. In addition, the movable valve for pressure adjustment can be supported by a pantograph so that the opening surface and the surface of the valve can move in parallel.
[0019]
The device of the present invention is a device that supplies a large amount of gas at a constant pressure, and is a pressure control device controlled by a pressurized air blower, an air passage, a pressure chamber suction port, a pressure control chamber (pressure chamber), and a pressure mechanism. And a pressure chamber exhaust port.
[0020]
DETAILED DESCRIPTION OF THE INVENTION
An embodiment of the apparatus of the present invention will be described with reference to the block diagram of FIG. The gas taken in from the suction port 401 by the pressurized blower 402 such as a blower fan passes through the blower passage 403 and is guided from the pressure chamber suction port A to the pressure chamber 404. In the pressure chamber 404, the sucked gas is once stored, but this air pressure is detected by the pressure adjusting plug 411 of the pressurizing mechanism 410 in contact with the control port 406, and the pressure in the pressure chamber 404 is set to the set pressure of the pressurizing mechanism 410. When the pressure is higher than that, the pressure adjusting valve of the pressurizing mechanism 410 is separated from the control port 406, and the excess gas is discharged from the pressure chamber 404 to maintain a constant air pressure.
[0021]
In addition, when the air blown from the suction port A directly hits the pressure adjusting plug 411 of the pressurizing mechanism 410, the pressurizing mechanism 410 does not correctly detect the pressure in the pressure chamber 404. Therefore, in the present invention, as shown in FIG. It is installed in the position away from. When the high-pressure gas is sucked from the suction port A, the pressure is propagated into the chamber almost instantaneously, so that the response performance of the pressurizing mechanism is not deteriorated.
[0022]
In the present invention, an air cylinder is used for the pressure adjusting mechanism. FIG. 8 simply shows the structure of the air cylinder. The air cylinder 410 is basically the same as the air cylinder (pneumatic cylinder) in FIG. 5, but in the present invention, the cylinder chamber 415 is a mechanism that is always maintained at the set pressure P. That is, the pressure in the cylinder chamber 415 always maintains the set pressure P regardless of the position of the piston 413. The description of the mechanism for holding the set pressure P has been given in the embodiment. When the pressure applied to the pressure control valve 411 (relief valve) (more precisely, the force applied to the pressure control valve 411) is smaller than the set air pressure P (specifically, the force applied to the piston) of the cylinder chamber 415, the piston 413 is Moving to the left, the control port 406 of the pressure chamber 404 is closed. When a pressure higher than the set pressure is applied to the pressure control plug 411, the pressure control plug 411 also moves to the right, the pressure control plug 411 opens, and excess compressed gas in the pressure chamber is discharged from the control port 406. Is done.
[0023]
The set pressure of the air cylinder 410 that determines the pressure in the pressure chamber 404 may be changed by changing the pressurizing pressure P as necessary. The present invention Proposes a method in which a control port opening area adjusting plate is provided at the contact point between the control port 406 and the pressure adjusting plug 411 to adjust the pressure applied to the pressure adjusting plug 411. FIG. 9 shows an example of a method for adjusting the opening area of the control port. In the front view of the figure, the area of the control port 406 can be changed by sliding the control port opening area adjusting plate 407 in the direction of the arrow. The figure which looked at the place of the circle | round | yen shown in the front view from the downward direction is sectional drawing. By opening and closing the adjusting plate 407 along the grooved guide plate 408, the area of the control port 406 is changed as shown in the right side view (viewed from the direction of the pressure adjusting plug 411). The pressure applied to 411 changes. Thereby, even if the pressure in the cylinder chamber 415 is constant, the pressure adjustment in the pressure chamber 404 can be changed. For example, when the cross-sectional area Sp of the piston 413, the pressure Pp of the cylinder chamber, the area Sc of the control port, and the pressure Pc of the chamber, the conditions for opening the pressure regulating plug 411 are as follows:
Pc / Sc> Pp / Sp
Therefore, if Sc is decreased, the pressure of the pressure chamber 404 can be increased, and conversely, Sc can be increased and the pressure of the pressure chamber 404 can be decreased. Therefore, it is possible to change the conditions for opening the pressure adjusting plug without changing the pressure in the air cylinder.
[0024]
In the relief damper using the weight mentioned in the prior art, the set pressure is determined by using the gravity applied to the weight, so that the relief direction of the gas from the pressure chamber is fixed in a fixed direction. On the other hand, since the air cylinder system of the present invention is controlled by the air pressure in the cylinder, the mounting direction of the cylinder is free. For example, the example of FIG. 10 shows the mounting direction of the air cylinder and the direction in which surplus gas in the pressure chamber is exhausted. Thereby, there is no restriction | limiting in the attachment place of an air cylinder, and a freedom degree can be given to the design of a pressure chamber.
[0025]
The mechanism for changing the control port area shown in FIG. 9 can take various forms. For example, it is also possible to change the opening area of the control port 406 by moving the control port opening area adjusting plates 407a and 407b of the same type cut in a “<” shape in the direction of the arrow in the figure. 11A shows the maximum opening area, and FIG. 11B shows an example in which the opening area is reduced by bringing the adjusting plates 407a and 407b closer to each other.
[0026]
FIG. 12 shows the relationship between the pressure applied to the relief valve (adjustment plug) and the area. If the pressure P in the pressure chamber, the opening area adjusted by the adjusting plate 407 is Sc, and the area of the relief valve 411 is Sr, the force applied to the relief valve in the closed state ((a) in the figure) is P · Sc. It is. In a state where the pressure P is increased and the relief valve is slightly opened ((b) in the figure), the pressure applied to the relief valve is P · Sr. Since Sr> Sc, when the valve is slightly opened, the force for pushing up the valve is increased at once, and the relief valve is quickly opened. That is, this change in the opening area improves the response performance. If the relief valve is opened too much, the gas quickly diffuses in all directions again, so that the pressure applied to the valve decreases and the valve moves in the closing direction. Although this operation continues for a while, this vertical motion (linear motion) appears as a pressure pulsation. In the case of the apparatus using the air cylinder of the present invention, this pulsation can be prevented.
[0027]
FIG. 13 is a diagram conceptually showing an example of a mechanism for keeping the pressure of the air cylinder 410 constant. High-pressure compressed air compressed by the compressor 600 is sent from the primary suction port 501 of the regulator 500, and the gas reduced to the set pressure P by the regulator 500 is sent from the secondary discharge port 502 to the air cylinder 410. The regulator 500 has a relief function, and when the pressure in the air cylinder 410 becomes higher than the set pressure P, the regulator relief valve opens and the pressure in the air cylinder chamber is always kept at P. Specifically, the pressure reducing valve with a relief valve mentioned in the prior art can be used as the regulator. As a pressure reducing valve with a relief valve suitable for the object of the present invention, a pilot type that can quickly bring the secondary side pressure close to the set pressure is preferable to a direct acting type that adjusts the pressure with an adjusting screw.
[0028]
In terms of applying a constant pressure to the pressure chamber, the spline type weight type pressure control device of FIG. 14 and the pantograph type weight type control device as shown in FIG. 15 are also conceivable. The adjustment spring 307 in FIGS. 14 and 15 has a function of canceling the load of the weight 302, and a wide range of control from low pressure to high pressure is possible by adjusting the adjustment screw. In the spline type, the shaft 308 moves up and down while keeping the relief valve 301 horizontal, and in the pantograph type, the pantograph 306 moves up and down while keeping the relief valve 301 horizontal. Since the air to be relieved has a structure that is released in all directions, the pressure control accuracy can be improved.
[0029]
FIG. 14 and FIG. 15 are different from the conventional relief damper shown in FIG. 6 in that the weight moves up and down while maintaining the level, so that it is constant regardless of the opening degree of the relief valve 301. The pressure is applied to the control port 406 of the chamber. However, the weight type pressure control device has a drawback that the pressure fluctuation range due to the pulsation phenomenon becomes larger with respect to the set pressure at a high pressure. In order to suppress this pressure fluctuation, a new cushioning material that suppresses vibration is required, which is complicated in structure. In addition, there is a restriction on the installation location due to the structure that pressure adjustment is performed with a weight. In this respect, in the pressure adjusting mechanism of the present invention, the pressure fluctuation can be suppressed to less than half that of the relief damper type pressure control device, and the mounting direction is not affected as shown in FIG. There is also an advantage that the degree of freedom of the installation location is large.
[0030]
【Example】
Since the apparatus of the present invention can blow a large amount of gas stably from low pressure to high pressure, it can be used for a load test in a bench test apparatus for wind pressure applied to an engine such as a racing car that runs at a maximum speed of 350 km / h. For example, in the case of the F1 car 700 shown in FIG. 16, the air is taken in from the intake port 701 directed in the traveling direction, supplied to the engine 703, and then exhausted from the exhaust port 702 at the rear of the automobile. At this time, the engine 703 repeatedly starts and stops, but when testing a load of wind pressure applied to the engine in accordance with actual traveling, a device capable of supplying the wind pressure corresponding to the traveling speed in a stable state with little pressure fluctuation. Is required. In such an engine test, there is an immediate response to a pressure change, and stable air blowing with little pressure fluctuation is required. Since the pressure control device of the present invention has good responsiveness to pressure changes and has a small pressure fluctuation range, stable air blowing is possible. .
[0031]
【The invention's effect】
As an effect of the apparatus of the present invention,
(1) Quick response of pressure control
(2) Since the pressure adjustment valve facing the opening surface of the pressure adjusting opening moves while maintaining a state substantially parallel to the opening surface, fine weight position control that is absolutely necessary in the relief damper system It has a simple structure that does not require any
(3) Excess gas released from the pressure adjustment opening is quickly diffused after passing through the pressure adjustment movable valve, and the resistance due to gas release is small.
(4) Instantaneous detection of flow rate and pressure fluctuations due to changes in usage conditions on the load side, and control to a constant pressure.
(5) The stability of pressure is greatly improved,
(6) The pressure fluctuation range can be suppressed to less than half compared to the conventional method using a relief damper.
(7) Compared to a solenoid valve using a pressure sensor, it has a simple and inexpensive structure.
(8) An opening area adjustment plate can be provided in the pressure adjustment opening to change the pressure area applied to the pressure adjustment movable valve. Can also be adjusted,
(9) When an air cylinder is used for the pressurization mechanism, the air cylinder itself has a pulsation prevention effect, and the installation direction is free compared to the weight system.
(10) If an air cylinder is used for the pressurization mechanism, the pressure chamber design can be given freedom.
(11) When an air cylinder is used for the pressurization mechanism, the regulator can adjust the pressure in the air cylinder or the pressure using the opening area adjustment plate, and it can be controlled over a wide range from low pressure to high pressure.
The point is mentioned.
[Brief description of the drawings]
FIG. 1 is a valve structure diagram for explaining the structure of a direct acting relief valve in the prior art.
FIG. 2 is a valve structure diagram for explaining the structure of a pilot type two-port pressure reducing valve in the prior art.
FIG. 3 is a valve structure diagram for explaining the structure of a pilot-type relief-equipped pressure reducing valve in the prior art.
FIG. 4 is a valve structure diagram for explaining the structure of a direct acting solenoid valve in the prior art.
FIG. 5 is a structural diagram of an air cylinder for explaining the structure of a double-acting air cylinder in the prior art.
FIG. 6 is a structural diagram of a gas pressure control device for explaining the structure of the gas pressure control device using a weight type relief valve in the prior art.
FIG. 7 is an overall configuration diagram of a gas pressure control device in means for solving the problems.
FIG. 8 is a structural diagram of an air cylinder in a means for solving the problems.
FIG. 9 is a conceptual diagram of an area adjusting mechanism for explaining a control port opening area in means for solving the problems.
FIG. 10 is an example of an installation direction of the air cylinder in the embodiment of the invention.
FIG. 11 is an example of a control port opening area adjustment and an adjustment plate in the embodiment of the invention.
12 is a diagram for explaining a pressure area applied to a control port opening area adjusting plate and a pressure regulating plug of FIG. 11 in the embodiment of the invention;
FIG. 13 is a conceptual diagram of a pressurizing mechanism that adjusts the in-cylinder set pressure of the air cylinder in the embodiment of the invention.
FIG. 14 is an example of a weight-type spline relief valve for adjusting the pressure in the pressure chamber in the embodiment of the invention.
FIG. 15 is an example of a weight type pantograph relief valve for adjusting the pressure in the pressure chamber in the embodiment of the invention.
FIG. 16 is a diagram showing the appearance of the F1 racing car and the racing car showing the wind pressure applied to the engine of the racing car and the air blowing mechanism in the embodiment.
[Explanation of symbols]
101 Valve
102 Adjustment unit (drive unit)
103 Handle
104 Adjustment screw
105 Adjustment spring
106 Valve body (valve)
107 Valve seat
108, 108a, 108b Diaphragm
109 relief hole
110 Return spring (spring)
111 piston
112 Pressure equalizing chamber
113 Pressure equalizing hole
114 Rod (piston rod, shaft)
115 Travel spring (valve spring)
116 plates
117 stem
118 Relief valve (valve)
119 Valve seat
120 relief nozzle
121 Plunger spring
122 Solenoid (electromagnet)
123 Plunger
124 Poppet (main valve)
125 cylinder tube
126 Bumper
127 piston packing
151 Pilot port
151 Pilot passage
153 Pilot room
161 breathing port
162 Breathing passage
163 Breathing room
200 Air cylinder (pneumatic cylinder)
201 cases
202 ring
203 pins
204 Handle
205 Valve shaft
206 Valve
210 Special rack
211 gears
212 Piston shaft
213 piston
214 Pipe joint
301 Relief valve (Relief bumper)
302 weight
303 fulcrum
304 Pressure chamber
306 Pantograph
307 Adjustment spring
308 shaft
400 Gas pressure control device
401 Gas inlet
402 Pressurized blower (such as blower fan)
403 Air passage
404 Pressure control chamber (pressure chamber)
405 Compressed gas outlet
406 Control port
407 Control port opening area adjustment plate (adjustment plate)
408 Guide plate
410 Air cylinder (Pressure mechanism)
411 Pressure regulator (Relief valve)
413 piston
414 Compressed gas inlet
415 Cylinder chamber
416 piston stop
500 regulator (pressure regulator)
501 Suction port (primary side)
502 Exhaust port (secondary side)
600 compressor
700 racing car
701 inlet
702 Exhaust port
703 engine

Claims (3)

In an apparatus for supplying gas at a constant pressure with a pressure chamber, the pressure chamber includes:
(1) an opening area adjusting plate for changing the opening area of the pressure adjusting opening;
(2) a pressure adjusting movable valve facing the opening surface of the pressure adjusting opening;
(3) A pressure adjustment mechanism in which the movable valve for pressure adjustment moves while maintaining a substantially parallel state with the opening surface.
A pressure gas supply device comprising: The pressure gas supply device according to claim 1, wherein the movable valve for pressure adjustment is urged and supported in a direction to close the valve by an air cylinder mechanism. The pressure gas supply device according to claim 1, wherein the pressure adjusting movable valve is urged and supported in a direction to close the valve by a gravity-use pressurizing mechanism.

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