JP2003254201A - Pressure controller - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To improve an anti-burst property of a pressure controller without causing cost up. <P>SOLUTION: A housing 12 is formed by joining a case 2 and a cover 3 with caulking. In the housing 12, a support body 16 with an opening 18 communicating with a fuel outlet 7 is disposed, and an armature 5 swingably supported by a diaphragm 4 and capable of contacting with and separating from the support body 16 is arranged. A compression coil spring 10 for biasing the armature 5 in a direction of contacting with the support body is arranged between the armature 5 and the cover 3. The compression coil spring 10 closely contacts with the diaphragm 4 and restricts an upward displacement of the armature 5 before the diaphragm receives fuel pressure, expands and tenses. A load acting on the diaphragm 5 is limited after the restriction of displacement, and a burst pressure is improved only by changing specifications of existing parts. <P>COPYRIGHT: (C)2003,JPO

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a pressure control device for adjusting a fluid pressure in a fluid supply system, and more particularly to a pressure control device used in a fuel supply system of an engine.

[0002]

2. Description of the Related Art In a fluid supply system such as a hydraulic circuit, various pressure control devices are used to adjust the pressure of fluid. As such a pressure control device, a fuel damper or a pressure device using a diaphragm is used. A regulator (pressure control valve) and the like are known. Such a pressure control device is also used in a system for supplying fuel to an automobile engine by a fuel injection device. In this case, the fuel damper is used when the fuel is discharged from the fuel pump or when the fuel is injected by the injector. The pulsation (change in pressure) of the fuel that occurs in 1) is absorbed by the upper and lower parts of the diaphragm to reduce the noise generated from the piping and the like. On the other hand, the pressure regulator functions to keep the fuel pressure applied to the injector constant, and adjusts the fuel pressure so that it is always constant by using the negative pressure in the intake manifold. The pressure regulator is the engine O
It also has a residual pressure holding function for holding the fuel pressure in the fuel pipe at the time of FF, and maintains a good restartability of the engine.

FIG. 5 is a sectional view showing an example of a conventional pressure control device (fuel damper) used in a fuel supply system of such an engine. As shown in FIG. 5, the fuel damper 51 has a structure in which an armature 55 supported by a diaphragm 54 is arranged in a housing in which a case 52 and a cover 53 are caulked. In this case, the case 52 is provided with a fuel inlet 56 and a fuel outlet 57, and FIG. 5 shows a state in which the armature 55 is pushed up by the fuel flowing from the fuel inlet 56.

A spring guide 59 is attached to the amateur 55.
The inner peripheral portion of the diaphragm 54 is sandwiched between the armature 55 and the spring guide 59. The outer peripheral portion of the diaphragm 54 is caulked to the upper end of the case 52 together with the diaphragm holder 61. Thereby, the armature 55 is supported by the diaphragm 54 so as to be vertically movable in the housing. On the other hand, the spring guide 59 and the cover 53
A spring 60 for urging the armature 55 downward in the drawing is disposed between the inner periphery of the upper end of the armature.

In such a fuel damper 51, the diaphragm 54 is driven by the fuel flowing from the fuel inlet 56.
When pressure is applied to the armature 55, the armature 55 moves upward against the biasing force of the spring 60. And amateur 5
5 moves and the diaphragm 54 moves up and down,
Fuel pressure fluctuations are absorbed and fuel pulsation is suppressed.

[0006]

By the way, in the above-mentioned fuel damper 51, when the fuel pressure rises abnormally, fuel leakage does not occur except from the fuel outlet 57.
Burst resistance is required for the device. In this case, the burst at the abnormal pressure is generated solely by the damage of the diaphragm 54, and is mostly generated by the outer peripheral portion of the diaphragm 54 coming out of the caulking fixing portion. That is, when the fuel pressure rises, the amateur 55 rises under the pressure,
At some point, the diaphragm 54 is in a fully stretched state. When the fuel pressure further rises in this state, the armature 55 tries to continue to rise further, and finally the diaphragm 54 is pulled out from the crimping fixing portion and comes out to be in a burst state.

As described above, the burst resistance depends on the holding force of the diaphragm 54, and it is necessary to increase the holding force of the diaphragm 54 in order to prevent the burst. Therefore, in the conventional pressure control device, in order to improve the burst resistance, the structure in which the diaphragm 54 is sandwiched between the chevron projection and the V groove, and the plate thickness of the case 52 is increased to improve the diaphragm holding force of the caulking fixing portion. The measures are taken. In addition, the caulking part itself must be managed to secure the holding power.

However, if the V-grooves are formed or the plate thickness is increased, the structure of the device becomes complicated and the material cost increases, and the cost increases accordingly. In addition, man-hours for managing the state of the crimp portion are further required, which causes a problem of cost reduction.

An object of the present invention is to improve the burst resistance of the pressure control device without increasing the cost.

[0010]

A pressure control device according to the present invention includes a housing having first and second flow ports through which a fluid flows in and out, and a housing fixed in the housing and communicating with the first flow port. A support body having an opening portion, an armature swingably provided in the housing and capable of approaching and separating from the support body, an inner peripheral portion of which is fixed to the armature, and an outer peripheral portion of which is fixed to the housing. And a resilient member disposed between the armature and the housing for biasing the armature toward the support body, wherein the diaphragm is the fluid It is characterized in that it has an amateur restricting means for restricting the movement of the amateur before being stretched and tensioned under the pressure of.

According to the present invention, since the movement of the amateur is regulated before the diaphragm is fully stretched by the amateur regulating means and the movement of the amateur is regulated, after the movement of the amateur is regulated, the amateur restraining means receives the pressure received from the fluid by the amateur. Can be taken by. Therefore,
After that, the diaphragm will not be pulled by both the pressure applied to itself and the pressure applied to the amateur, only the pressure applied to itself will act on the diaphragm, and the pressure receiving area of the diaphragm and the amateur will be reduced by the amount of the amateur Becomes Therefore, the load applied to the diaphragm is suppressed, and the limit pressure at which burst occurs is increased.

Further, in the pressure control device, a compression coil spring is used as the elastic member, and the close contact length of the compression coil spring is set so as to make close contact before the diaphragm is stretched and tensioned by the pressure of the fluid. Therefore, the compression coil spring may be used as the amateur restricting means. In this case, the compression coil spring is a component normally used in the pressure control device, and according to the present invention, it is possible to increase the burst pressure by using one of such existing components.
Therefore, without additional parts or major design changes,
The burst resistance can be improved only by changing the specifications of the existing parts, and it is possible to provide a pressure control device having a high burst pressure without increasing the cost.

Further, in the pressure control device, as the amateur restricting means, an amateur restricting portion for contacting the amateur and restricting movement of the amateur before the diaphragm is stretched and tensioned by the pressure of the fluid is provided. It may be provided in the housing. This makes it possible to reliably regulate the movement of the amateur by a relatively simple shape change.

In addition, in the pressure control device, the armature restricting means is provided between the housing and the armature, and contacts the armature before the diaphragm is stretched and tensioned by the pressure of the fluid. You may use the amateur regulation member which contacts and regulates the movement. This makes it possible to reliably regulate the movement of the amateur by a relatively simple shape change. At this time, a screw member may be attached to the housing as an amateur restricting member, and the restricting position of the amateur can be easily changed by using the screw member.

On the other hand, in the pressure control device, the fluid may be a fuel such as gasoline or light oil which is supplied to the engine, whereby the pressure used in the engine fuel supply system does not increase the cost. It is possible to improve the burst pressure of the control device.

[0016]

BEST MODE FOR CARRYING OUT THE INVENTION (Embodiment 1) Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. Figure 1
It is a sectional view showing composition of a pressure control device (fuel damper) which is Embodiment 1 of the present invention. The fuel damper 1 is attached to a fuel supply system in a fuel tank or in an engine room, and is used as a so-called fuel damper in a fuel supply system for a direct injection engine.

The basic structure of the fuel damper 1 is almost the same as that of the conventional fuel damper 51 shown in FIG. 5. As shown in FIG. 1, the housing 12 is formed by caulking the case 2 and the cover 3 together. Here, the case 2 and the cover 3 are made of aluminum or the like, and a flange 2a is formed at the upper end of the case 2. Then, the flange portion 2a is caulked and fixed so as to cover the lower end portion of the cover 3 to form the housing 12.

Inside the housing 12, an armature 5 supported by a diaphragm 4 is arranged. The inside of the housing 12 is divided into two chambers with the diaphragm 4 and the armature 5 as a boundary, and the case 2 side has a fuel chamber 13,
An air chamber 14 is provided on the cover 3 side. Further, the amateur 5 is a compression coil spring 10 (elastic member, hereinafter,
It is urged downward in FIG. 1 by a spring 10). Then, the fuel flows into the fuel chamber 13, the armature 5 is pushed upward against the urging force of the spring 10, and the diaphragm 4 moves up and down, so that the pressure change (pulsation) of the fuel is absorbed. There is.

The case 2 is provided with a fuel inlet 6 and a fuel outlet 7. The fuel inlet 6 is formed below a support 16 fixed to the lower part of the case 2, and a fuel pipe 17 connected to a fuel pump is attached. An opening 18 communicating with the fuel outlet 7 is provided at the upper end of the support 16, and the opening 18 is always open. On the other hand, the fuel outlet 7 is formed in the base 15 attached to the side portion of the case 2, and is connected to the injector via a fuel pipe (not shown). Then, as indicated by an arrow F in FIG. 1, the fuel pressurized by the pump flows into the case 2 from the fuel inlet 6 and flows out from the fuel outlet 7.

The armature 5 is a metal member arranged so as to face the opening 18, and a spring guide 9 is caulked and fixed to the upper part thereof. The armature 5 is swingably mounted in the housing 12 by a rubber diaphragm 4 so that the armature 5 can be moved toward and away from the support 16 between the states shown by the solid line and the broken line in FIG. Has been done. The inner peripheral portion of the diaphragm 4 is sandwiched between the armature 5 and the spring guide 9.

The inner peripheral side of the diaphragm 4 is fixed to the armature 5, while the outer peripheral portion of the diaphragm 4 has a diaphragm holder 11.
At the same time, it is fixed by caulking to the upper end of the case 2. The diaphragm holder 11 has a disk shape with a central portion protruding in a cylindrical shape, and is fixed so that the outer peripheral portion of the diaphragm 4 is sandwiched between the flange portion 11a and the flange portion 2a of the case 2. Then, the flange portion 2a to which the diaphragm 4 and the diaphragm holder 11 are fixed is
It is caulked and fixed to the lower end of the cover 3 together with the packing 19.

Between the spring guide 9 and the inner peripheral portion of the upper end of the cover 3, the armature 5 is arranged in the downward direction of the drawing, that is,
A spring 10 for urging the armature 5 toward the support 16 is provided. As shown in Figure 1,
A spring holding portion 3a is provided at the center of the upper surface of the cover 3, and fits with the inner diameter of the spring 10 to prevent the spring 10 from being displaced.

In the fuel damper 1 as described above, the diaphragm 4 is pressured by the fuel flowing in from the fuel inlet 6, and the armature 5 moves up and down with respect to the support 16. At this time, the diaphragm 4 and the armature 5 move up and down according to the change in fuel pressure, and this change absorbs the change in fuel pressure. Therefore, the fuel whose pressure change is small is discharged from the fuel outlet 7, and the pulsation of the fuel is suppressed.

On the other hand, when the pressure of the fuel rises, the armature 5 is pushed upward, and the diaphragm 4 is stretched accordingly, eventually becoming a fully tensioned tension state.
Then, when the fuel pressure rises due to clogging of the latter stage of the pipe in this state, the diaphragm 4 is pulled out from the caulking fixing portion and becomes a burst state as described above.

On the other hand, in the fuel damper 1, the contact length L ₀ of the spring 10 arranged above the armature 5 is set so as to be in the contact state before the diaphragm 4 becomes in the tension state. That is, the spring 10 is compressed when the armature 5 rises and the diaphragm 4 expands, but before the diaphragm 4 reaches a fully stretched tension state, the spring 10 is brought into a close contact state as shown in FIG. Regulate the movement of.

When the amateur 5 is fixed in this way,
The pressure Pa received from the fuel by the armature 5 is received by the spring 10 and the cover 3 which are in close contact with each other. Therefore, the pressure P applied to the diaphragm 4 is applied to itself.
It is not pulled by both d and the pressure Pa applied to the armature 5, and only the pressure Pd applied to the diaphragm 4 thereafter acts on the diaphragm 4. That is,
After the contact of the spring 10, the pressure receiving areas of the diaphragm 4 and the armature 5 are reduced by the amount of the armature 5. Therefore, the load applied to the diaphragm 4 is suppressed, and the limit pressure (burst pressure) at which burst occurs is increased. According to the experiments by the inventors, when the average value of the burst pressure in the conventional fuel damper 51 as shown in FIG. 5 is 3340 kPa, the average value of the burst pressure is 3340 kPa in the fuel damper 1 of the same size as shown in FIG. 1 according to the present invention. It rose to 6000kPa.

In this way, in the fuel damper 1, the spring 10 which is one of the existing parts is used as a means (amateur restriction means) for restricting the lift amount of the amateur 5, and the amateur is utilized by utilizing the close contact length thereof. The movement of 5 is regulated. For this reason, the burst resistance can be improved by only changing the specifications of the existing parts without adding additional parts or making major design changes. Therefore, it is possible to provide a pressure control device having a high burst pressure without increasing the cost, and it is possible to improve the reliability of the product without burdening the cost.

(Second Embodiment) Next, as a second embodiment of the present invention, a pressure control device (fuel damper) in which movement of the armature 5 is restricted by a cover 3 to improve burst resistance will be described. . FIG. 2 is a cross-sectional view showing the structure of the fuel damper 21 according to the second embodiment of the present invention. In the following embodiments, the same members and parts as those of the fuel damper 1 of the first embodiment are designated by the same reference numerals, and the description thereof will be omitted.

In the fuel damper 21, the lower portion of the cover 3 is formed in a stepped shape, and the inner surface side of the fuel damper 21 is an amateur restricting portion (amateur restricting portion) 22. In this case, the inner diameter of the cylindrical portion 3b of the cover 3 is larger than the outer diameter of the spring 10 and smaller than the outer diameter of the spring guide 9. Further, at the lower part of the cylindrical portion 3b, a step portion 3c having an inner diameter larger than the outer diameter of the spring guide 9 is provided.
Are formed. The inner surface of the upper end of the stepped portion 3c serves as an armature restricting portion 22, and when the armature 5 rises due to the fuel pressure, the upper end 9a of the outer peripheral portion of the spring guide 9 contacts.

Here, when the armature 5 rises under the fuel pressure, the diaphragm 4 expands accordingly. In the fuel damper 21, the spring guide 9 abuts against the amateur restricting portion 22 before the diaphragm 4 is tensioned. As a result, the upward movement of the amateur 5 is restricted, and the amateur 5 is fixed there. Then, the pressure Pa received from the fuel by the armature 5 is received by the spring guide 9 and the cover 3, and as before, the pressure receiving area is reduced by the amount of the armature 5, and the burst pressure can be increased. Becomes

In this way, in the fuel damper 21,
Since the movement of the amateur 5 is regulated by the amateur regulation portion 22 provided on the cover 3, the burst resistance can be improved by only partially changing the form of the cover 3. Since the cover 3 is formed by drawing with a press, it is relatively easy to form the stepped portion 3c in the lower portion thereof.

(Third Embodiment) Further, as a third embodiment of the present invention, a pressure control device (fuel damper) in which movement of the armature 5 is restricted by a screw member attached to the cover 3 will be described. FIG. 3 shows a third embodiment of the present invention.
It is sectional drawing which shows the structure of the fuel damper 31 which is.

In the fuel damper 31, a screw (amateur regulating member) 32 for regulating the movement of the armature 5 is attached to the upper end portion of the cover 3. In this case, a screw mounting portion 33 is formed at the center of the upper surface of the cover 3, and the screw 32 is screwed therein. The screw mounting portion 33 has a structure such that the spring holding portion 3a of FIG. 1 is provided with a screw hole, and includes a recessed portion 33a in which the head portion of the screw 32 is accommodated and a female screw portion 33b. The spring 10 is mounted on the inner peripheral side of the recess 33a to prevent the spring 10 from being displaced, like the spring holding portion 3a.

Then, when the amateur 5 rises due to the fuel pressure, the fuel damper 31 causes the diaphragm 4 to move.
The upper end of the armature 5 comes into contact with the lower end of the screw 32 before the tension of the armature 5 increases. As a result, the upward movement of the amateur 5 is restricted, and the pressure P that the amateur 5 receives from the fuel is reduced.
a is received by the armature 5 and the cover 3, and thereafter, the pressure receiving area is reduced by the amount of the armature 5 as described above, and the burst pressure can be increased.

In this way, in the fuel damper 31,
Since the cover 3 is provided with the screw mounting portion 33 and the movement of the armature 5 is restricted by the screw 32 screwed into the cover 3, it is possible to improve the burst resistance without significantly changing the product specifications. Also, the fuel damper 31
Then, the movement restriction position of the amateur 5 can be appropriately changed by adjusting the screw 32. Therefore, the regulation position can be adjusted without disassembling the device, and the flexibility of product specifications can be enhanced.

(Fourth Embodiment) Further, as a fourth embodiment of the present invention, a pressure regulator (pressure control device) to which the present invention is applied will be described. Figure 4
FIG. 8 is a sectional view showing a configuration of a pressure regulator 41 that is Embodiment 3 of the present invention.

In the pressure regulator 41, the armature 5 has a valve structure. A ball 42 and a ball holder plate 43 are attached to the lower portion of the armature 5. The ball 42 is urged downward in the drawing by a valve spring 44 housed inside the amateur 5. A valve plate 45 is attached to the lower end of the ball 42, and the ball 42 is stored in the ball holder plate 43.
It is fixed by brazing to. On the other hand, a valve seat 46 is fixed to the upper part of the support body 16, and a valve plate 45 is arranged so as to be able to come into contact with and separate from it, and forms a sealing surface.

On the other hand, the cover 3 is provided with a communication port 47 communicating with the air chamber 14. The communication port 47 is connected to the intake manifold, and the inside of the cover 3 partitioned by the armature 5 and the diaphragm 4 is adjusted to have a negative pressure as in the intake manifold.

In such a pressure regulator 41, when the pressure of the diaphragm 4 is affected by the fuel flowing from the fuel inlet 6, and the fuel pressure exceeds a predetermined adjusting pressure P,
The armature 5 separates from the support 16, and the valve plate 45 separates from the valve seat 46 to open the valve. In this case, the adjusting pressure P is determined by the pressure difference ΔP between the fuel chamber 13 and the air chamber 14 and the pressing force Ps of the spring 10 (P = ΔP + Ps), and the pressure Pd that the diaphragm 4 receives from the fuel is equal to the adjusting pressure P. When exceeding (Pd> P), the armature 5 moves and the valve is opened to a position where the adjustment pressure P is reached, and the fuel pressure is maintained at the adjustment pressure P. As a result, the fuel pressure Pf becomes equal to the adjustment pressure P.
When exceeding, the excess fuel is returned from the fuel outlet 7 to the fuel tank, and the regulated fuel is supplied to the fuel injection device of the engine. The pressure Pd received by the diaphragm 4 is obtained by multiplying the fuel pressure Pf by the pressure receiving area of the diaphragm 4.

On the other hand, when the valve is opened, the lower surface of the armature 5 in addition to the diaphragm 4 receives pressure from the fuel, and the armature 5 moves upward with a lift amount corresponding to this pressure. That is, when the valve 5 is closed, the armature 5 is operated by the pressure Pd received by the diaphragm 4, but after the valve is opened, the armature 5 is operated by both pressures (Pd + Pa) received by the diaphragm 4 and the armature 5. Therefore, once the valve is opened, the armature 5 is pushed upwards at a stretch, and the diaphragm 4 is stretched accordingly, and eventually the tension state where the armature 5 is fully stretched is reached. When the fuel pressure Pf rises due to clogging of the latter stage of the pipe in this state, the diaphragm 4 is pulled out from the caulking fixing portion and becomes in a burst state as described above.

On the other hand, the pressure regulator 4
1, the contact length L ₀ of the spring 10 arranged on the upper part of the armature 5 is set so as to be in the contact state before the diaphragm 4 becomes in the tension state, as in the first embodiment. Therefore, before the diaphragm 4 is in a tensioned state in which the diaphragm 4 is fully stretched, the spring 10 is in a close contact state, and the upward movement of the armature 5 is restricted. Therefore, after the spring 10 is in close contact, the load applied to the diaphragm 4 is suppressed, and the limit pressure (burst pressure) at which burst occurs is increased.

It is needless to say that the present invention is not limited to the above-mentioned embodiment, and can be variously modified without departing from the scope of the invention. For example, in the above-described embodiment, the pressure control device used in the fuel supply system of the direct injection engine has been described as an example, but its application is not limited to the engine and can be applied to various hydraulic circuits. Also,
The fluid whose pressure is to be adjusted is not limited to engine fuel such as gasoline and light oil, but can be applied to water, air, hydraulic oil of a hydraulic circuit, and the like. Furthermore, in the second and third embodiments, the compression coil spring is used as the elastic member that biases the armature 5, but other elastic members such as rubber, synthetic resin, and disc springs can be used. In the fourth embodiment, the pressure regulator using the same configuration as in the first embodiment is shown, but it is of course possible to apply the configurations of the second and third embodiments to the pressure regulator.

[0043]

According to the pressure control apparatus of the present invention, the movement of the amateur is regulated before the diaphragm is stretched to the fully tensioned state by the amateur regulation means.
After the movement of the amateur is restricted, the pressure that the amateur receives from the fluid can be received by the amateur restriction means. Therefore, the load applied to the diaphragm thereafter can be suppressed, and the burst resistance can be improved.

Further, since the contact length of the compression coil spring is set so as to be in contact before the diaphragm is tensioned, it is possible to increase the burst pressure by using the parts that are normally used. Therefore, the burst resistance can be improved by only changing the specifications of the existing parts without adding additional parts or major design changes, and it is possible to provide a pressure control device having a high burst pressure without increasing the cost.

[Brief description of drawings]

FIG. 1 is a sectional view showing a structure of a fuel damper according to a first embodiment of the present invention.

FIG. 2 is a sectional view showing a structure of a fuel damper according to a second embodiment of the present invention.

FIG. 3 is a sectional view showing a structure of a fuel damper according to a third embodiment of the present invention.

FIG. 4 is a sectional view showing a configuration of a pressure regulator that is Embodiment 4 of the present invention.

FIG. 5 is a sectional view showing an example of a conventional fuel damper.

[Explanation of symbols]

1 Fuel Damper (Pressure Control Device) 2 Case 2a Flange 3 Cover 3a Spring Holding 3b Cylindrical 3c Step 4 Diaphragm 5 Armature 6 Fuel Inlet 7 Fuel Outlet 9 Spring Guide 9a Outer Edge 10 Compression Coil Spring (Amateur) Regulation means) 11 Diaphragm holder 11a Flange portion 12 Housing 13 Fuel chamber 14 Air chamber 15 Base 16 Support 17 Fuel pipe 18 Opening 19 Packing 21 Fuel damper (pressure control device) 22 Amateur regulation unit (amateur regulation unit, amateur regulation unit) ) 31 fuel damper (pressure control device) 32 screw (amateur restricting means, amateur restricting member, screw member) 33 screw mounting part 33a recessed part 33b female screw part 41 pressure regulator (pressure control device) 42 ball 43 baud Holder plate 44 valve spring 45 valve plate 46 a valve seat 47 communication port 51 fuel damper 52 Case 53 Cover 54 diaphragm 55 amateur 56 fuel inlet 57 fuel outlet opening 59 spring guide 60 spring 61 diaphragm holder L ₀ solid length P adjusting pressure Pd diaphragm Pressure received by Pf Fuel pressure Ps Pressure of compression spring Pa Pressure received by amateur

─────────────────────────────────────────────────── ─── Continuation of front page (51) Int.Cl. ⁷ Identification code FI theme code (reference) G05D 16/06 G05D 16/06 C F term (reference) 3H059 AA05 BB12 CD05 CF06 EE13 FF13 3H066 AA01 BA32 BA33 BA34 EA05 EA36 5H316 AA09 BB09 CC08 DD17 EE10 EE12 GG20

Claims (6)

[Claims] 1. A housing having first and second circulation ports through which a fluid flows in and out, a support body having an opening fixed in the housing and communicating with the first circulation port, and the inside of the housing An armature swingably provided to the support and capable of approaching and separating from the support; a diaphragm having an inner peripheral portion fixed to the armature and an outer peripheral portion fixed to the housing; and the armature and the housing. A pressure control device, comprising: an elastic member arranged between the elastic member and urging the armature toward the support, wherein the diaphragm is stretched and tensioned by receiving the pressure of the fluid. A pressure control device comprising an amateur restriction means for restricting movement of an amateur. 2. The pressure control device according to claim 1, wherein
The amateur control means is a compression coil spring that is used as the elastic member and is in close contact with the diaphragm before the diaphragm is stretched and tensioned by the pressure of the fluid and restricts the movement of the amateur. . 3. The pressure control device according to claim 1,
The amateur restricting means is an amateur restricting portion which is provided in the housing and restricts the movement of the amateur by contacting the amateur before the diaphragm is stretched and tensioned by the pressure of the fluid. Control device. 4. The pressure control device according to claim 1, wherein
The amateur restricting means is an amateur restricting member that is provided between the housing and the armature, contacts the amateur before the diaphragm is stretched and tensioned by the pressure of the fluid, and restricts the movement of the diaphragm. A pressure control device characterized in that 5. The pressure control device according to claim 4,
The pressure control device, wherein the amateur regulating member is a screw member attached to the housing. 6. The pressure control device according to claim 1, wherein the fluid is fuel supplied to an engine.