JP6688591B2 - Self-powered regulating valve - Google Patents

Description

  The present invention relates to a self-regulating valve, and more particularly to a direct acting pressure reducing valve or back pressure valve having a simple structure, or a pilot operated pressure reducing valve or back pressure valve that operates a main valve using a pilot valve. is there.

Conventionally, the pressure reducing valve or back pressure valve, which is a self-powered adjustment valve, operates by simply installing it between the pipes and does not require external power such as electricity or air pressure, so it is a simple and useful self-powered adjustment valve. It is used as a valve (for example, see Patent Document 1).
However, compared to other force type control valves that operate using external power such as electricity or pneumatic pressure, self-powered type control valves have a drawback that they are significantly inferior in control accuracy, so their control accuracy is not a major problem. It is used only for.

Here, the control accuracy of the pressure reducing valve of the self-regulating valve will be described as an example.
The pressure reducing valve is configured to detect the secondary side pressure of the secondary side flow passage and hold the secondary side pressure constant so as to be a preset pressure.
In the pressure reducing valve, when the flow rate from the primary flow path to the secondary flow path is changed from a small flow rate to a rated high flow rate, as shown in FIG. 9, the secondary pressure of the secondary flow path decreases. Therefore, the degree of opening of the main valve of the pressure reducing valve is automatically increased to prevent the secondary side pressure from decreasing.

  However, it is not possible to completely reduce the secondary side pressure drop to zero, and a certain amount of pressure drop (for example, a pressure drop of about 10% at the rated flow rate) will occur. This pressure drop is called an offset (adjustment error or control deviation). It is ideal that this offset is as close to 0 as possible, because the pressure reducing valve has high control accuracy and high performance.

  Further, when the flow rate of the fluid flowing from the primary side flow passage to the secondary side flow passage in the pressure reducing valve is changed from a small flow rate to a large flow rate, as shown in FIG. 10, the valve opening degree of the main valve changes from small to large. However, when the process is viewed microscopically, the vibration of the main valve is attenuated, and eventually it converges to a fixed valve opening that is stopped.

  Self-powered pressure reducing valves operate purely mechanically without using external power such as electricity or air pressure, and the time required for transient response until the valve opening of the main valve stabilizes depends on various conditions. However, with a small-diameter main valve, it is a very short time of about 0.1 to 1.0 seconds.

Therefore, if the offset can be made as small as possible, the self-operated pressure reducing valve can have high performance. Here, the secondary side pressure offset is the pressure receiving area A of the diaphragm that detects the secondary side pressure, the spring constant K of the adjusting spring that biases the main valve to increase the valve opening, and the valve of the main valve. It is expressed by the following (Equation 1) using the movement amount L that determines the opening degree.
Offset = (K × L) / A ………………………………………………………… (Equation 1)

JP-A-2007-51730.

By the way, in such a pressure reducing valve of a self-powered regulating valve, in order to obtain a high control accuracy by reducing the offset of the secondary side pressure, in the case of the direct acting type, the pressure receiving area A of the diaphragm is large and the spring constant of the adjusting spring is large. It is necessary to reduce K.
If it is a pilot operated type, for example, there is a method of making a pilot valve highly accurate. However, there is a drawback that the main valve becomes large in size either in the direct drive type or the pilot operated type.

  Since the self-powered pressure reducing valve is an automatic control device that performs feedback control, if the control accuracy is made higher than necessary (gain or higher gain), it becomes hypersensitive to changes in the secondary pressure of the detection target. As shown in FIG. 11, the main valve vibrates (oscillates) and the operation becomes unstable, so that there is a problem that the offset cannot be extremely reduced.

  The present invention has been made in view of the above-mentioned conventional problems, and an object thereof is to provide a highly accurate self-regulating valve that does not reduce the pressure on the secondary side without increasing the size.

In order to achieve this object, the present invention is arranged so as to face a valve seat (14) provided between a primary side flow path (12a) and a secondary side flow path (12b) of a valve box (11). The primary side flow passage (12a) by driving the diaphragm (30) in which the valve body (15) integrated through the valve rod (17) is driven by the secondary side pressure of the secondary side flow passage (12b). ) And a diaphragm (30) for urging the valve body (15) to separate from the valve seat (14) with respect to the valve seat (14). ) And an adjusting spring (34, 152) integrated with the spring, and a spring protector provided above the diaphragm (30) and accommodating the adjusting spring (34, 152) in a spring chamber (40) in its internal space. (35, 150) and the spring chamber (4) of the spring protection portion (35, 150). ), An auxiliary pressure fluid is supplied from an upstream fluid passage including the primary side flow path (12a) through a pressure reducing valve (6) to generate an auxiliary pressure according to the secondary side pressure. And an auxiliary pressure supply part (3, 130) to be supplied by the auxiliary pressure supply part (3, 130) , the auxiliary pressure supply part (3, 130) communicating with the secondary side flow path (12b) for detecting the secondary side pressure. The pressure detection path (74), the supply path (65) to which the auxiliary pressure fluid for generating the auxiliary pressure is supplied, and the auxiliary pressure fluid from the supply path (65) to the spring protection part ( 35) The output passage (66) for outputting to the spring chamber (40) communicates with the passage (auxiliary chamber 70) extending from the supply passage (65) to the output passage (66) through the through hole (69). And discharges the auxiliary pressure fluid supplied to the supply path (65). A passage (68), a valve portion (72a) for opening and closing the through hole (69), and a valve portion (72a) for detecting the secondary pressure via the pressure detection passage (74). And a pressure detection diaphragm (76) provided as a unit, which is integrated with the pressure detection diaphragm (76) and urges the valve portion (72a) so as to close the through hole (69). A spring (85), the valve portion (72a) opens the through hole (69) when the secondary side pressure is high, and the secondary side pressure decreases to cause the through hole (69). Is configured to be closed, and the opening degree of the valve portion (72a) with respect to the through hole (69) is changed according to the secondary pressure detected via the pressure detection diaphragm (76), and the change Fluid for auxiliary pressure corresponding to The auxiliary pressure by the above is supplied to the spring chamber (40) of the spring protection portion (35) .

  In the present invention, a throttle (67) for generating the auxiliary pressure is provided between the supply passage (65) and the output passage (66).

In the present invention, a throttle valve (7) for generating the auxiliary pressure is provided on the upstream side of the supply passage (65).

  In the present invention, the auxiliary pressure supply unit (3, 130) is separately installed outside the spring protection unit (35, 150).

  In the present invention, the auxiliary pressure supply part (3, 130) is integrally installed on the spring protection part (35, 150).

  According to the present invention, since the auxiliary pressure according to the secondary pressure can be supplied from the auxiliary pressure supply unit (3) to the spring chamber (40) of the spring protection unit (35, 150), the auxiliary pressure The valve opening (15) can be increased by separating the valve body (15) from the valve seat (14) via the diaphragm (30) by an increment, and thus the primary side flow path (12a) in the valve body (2). Therefore, it is possible to realize a highly accurate self-regulating valve that does not increase in size by eliminating a drop in secondary pressure when a fluid flows to the secondary flow path (12b). Further, in this case, the valve element (15) can be brought close to the valve seat (14) through the diaphragm (30) by the amount of the decrease in the auxiliary pressure.

  According to the present invention, the auxiliary pressure supply unit (3) has the valve portion (72a) for the through hole (69) communicating between the supply passage (65) and the output passage (66) and the discharge passage (68). Since the opening degree is changed according to the secondary side pressure detected via the pressure detecting diaphragm (76), the auxiliary pressure corresponding to the change is applied to the spring chamber (40) of the spring protection portion (35, 150). Can be supplied.

  According to the present invention, since the throttle (67) for generating the auxiliary pressure is provided between the supply passage (65) and the output passage (66), the pressure in the supply passage (65) is reduced (67). ), It can be supplied to the spring chamber (40) of the spring protection portion (35) as a further reduced auxiliary pressure. As a result, the pressure increase in the spring chamber (40) can be gradually changed by the auxiliary pressure over time, so that the valve body (15) can be gradually separated from the valve seat (14).

According to the present invention, since the throttle valve (7) for generating the auxiliary pressure is provided outside the supply passage (65), the pressure to the supply passage (65) is passed through the throttle (67). As a result, the auxiliary pressure further reduced can be supplied to the spring chamber (40) of the spring protection portion (35, 150).
As a result, the pressure increase in the spring chamber (40) can be gradually changed by the auxiliary pressure over time, so that the valve body (15) can be gradually separated from the valve seat (14).

  According to the present invention, since the auxiliary pressure supply part (3, 130) is separately installed outside the spring protection part (35, 150), it can be externally attached to the main body part (2) later. It will be possible.

  According to the present invention, since the auxiliary pressure supply part (3, 130) is integrally installed on the upper part of the spring protection part (35, 150), it is possible to reduce the size as a whole.

It is sectional drawing which shows the whole structure of the direct-acting pilot controller separate installation type pressure reducing valve in 1st Embodiment. It is sectional drawing which shows the structure of the pressure reducing valve main body of the pilot controller separate installation type pressure reducing valve in 1st Embodiment. It is sectional drawing which shows the structure of the pilot controller of the pilot controller separate installation type pressure reducing valve in 1st Embodiment. 4 is a graph showing a change over time in valve opening degree according to the first embodiment. 5 is a graph showing a state in which there is no pressure drop with an increase in flow rate in the first embodiment. It is sectional drawing which shows the whole structure of the direct-acting pilot controller integrated installation type pressure reducing valve in 2nd Embodiment. It is a sectional view showing the whole pilot operation type pilot controller separation installation type pressure reducing valve in a 3rd embodiment. It is sectional drawing which expands and shows a part of pilot controller which has a throttle valve for producing | generating auxiliary pressure. It is a graph which shows the state with a pressure drop with the increase of the conventional flow rate. It is a graph which shows the time change of the conventional valve opening degree. It is a graph which shows the state in which the conventional self-regulating valve oscillates.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings.

<First Embodiment>
<Overall structure of pilot controller separated installation type pressure reducing valve>
As shown in FIG. 1, a pilot controller separate installation type pressure reducing valve 1 (hereinafter, simply referred to as “separating type pressure reducing valve”) as a self-regulating valve in the first embodiment has an upstream pipe H1 and It is arranged between the downstream pipes H2.

  This separable pressure reducing valve 1 includes a pressure reducing valve main body 2 for causing a fluid supplied from an upstream pipe H1 through a primary flow passage 12a to flow out from a secondary flow passage 12b to a downstream pipe H2, and this pressure reducing valve main body. 2 and a pilot controller 3 for supplying auxiliary pressure, which is separately installed on the outer peripheral side surface of the outer peripheral surface 2.

<Structure of pressure reducing valve body>
As shown in FIGS. 1 and 2, the pressure reducing valve main body 2 includes a valve box 11 connected between the upstream pipe H1 and the downstream pipe H2, and a spring fixed to the upper portion of the valve box 11 in the arrow B direction. It has a protective cylinder 35.
In the valve box 11, the upstream pipe H1 is connected to the flange portion 11a provided on the inlet side (upstream side) of the flow passage 12, and the flange portion provided on the outlet side (downstream side) of the flow passage 12 is provided. The downstream pipe H2 is connected to 11b. Therefore, the fluid passage 4 in the upstream pipe H1 is connected to the primary passage 12a of the valve box 11, and the fluid passage 5 in the downstream pipe H2 is connected to the secondary passage 12b of the valve box 11. To be done.

The primary-side flow passage 12a and the secondary-side flow passage 12b of the valve box 11 are separated by a partition wall 13 provided inside the valve box 11, and a cylinder is formed in a through hole formed in the central portion of the partition wall 13. The shaped valve seat 14 is fixed.
An annular valve body 15 is provided at a position facing the valve seat 14, and the valve body 15 is fitted and fixed in a recess in the upper end surface of an annular valve body receiver 16. Therefore, the flow rate of the fluid flowing from the primary side flow passage 12a to the secondary side flow passage 12b is adjusted by narrowing or widening the gap between the valve seat 14 and the valve body 15.

A valve rod 17 penetrating the center of the valve seat 14 and protruding in the vertical direction of the valve seat 14 is integrally fixed to the valve body receiver 16. In this case, the valve rod 17 is fixed in a state where the valve rod 17 penetrates the central through hole of the valve body receiver 16.
A lower end portion 17b of the valve rod 17 protruding below the valve body support 16 is slidably supported in a guide hole 21b of a valve rod guide portion 21a of a lower lid 21 attached to the bottom portion of the valve box 11. .

A hexagon nut 18 is attached to the lower end portion 17b of the valve rod 17 at a position facing the valve rod guide portion 21a, and on the lower surface of the valve body receiver 16 so that The bridge 16 is fixed at a position in the figure in the direction of arrow AB.
An annular recess 21c is formed on the bottom surface around the valve rod guide portion 21a in the lower lid 21, and the lower end of the valve spring 19 is supported by the recess 21c. The upper end of the valve body spring 19 is supported on the lower surface of the valve body receiver 16 so as to surround the hexagon nut 18. The valve body spring 19 biases the valve body receiver 16 in the direction of arrow B, which brings the valve body 15 into contact with the valve seat 14.

A substantially cylindrical liner 22 is attached to the upper opening of the valve box 11. In the through hole 22a below the liner 22, a valve rod 17 protruding above the valve body receiver 16 is slidably supported in the arrow AB direction.
A balance piston 23 is slidably supported in the through hole 22b above the liner 22. An O-ring 31 for sealing between the liner 22 and the balance piston 23 is attached to the inner peripheral portion of the through hole 22b.

The valve rod 17 and an upper end portion 17a thereof are integrally fixed to a through hole provided inside the balance piston 23. An annular step portion is formed on the outer peripheral end surface of the flange portion 23a of the flange portion 23a at the upper end of the balance piston 23, and a donut-shaped diaphragm 30 made of, for example, synthetic rubber is placed on the step portion. There is.
A diaphragm receiver 24 is mounted on the upper end surface of the diaphragm 30. The upper end portion 17a of the valve rod 17 is penetrated through the through hole 24a of the diaphragm receiver 24, and the hexagon nut 26 is screwed onto the upper end portion 17a.

That is, in this case, the diaphragm 30 is tightened by the hexagon nut 26 while being sandwiched between the flange portion 23 a of the balance piston 23 and the diaphragm receiver 24. Thus, the diaphragm 30 is integrated with the valve body 15 via the valve rod 17.
Further, the outer peripheral edge of the diaphragm 30 is placed on the stepped portion provided in the opening of the valve box 11. The outer peripheral edge of the spring protection cylinder 35 is abutted against the outer peripheral edge of the opening of the valve box 11 so as to face each other, and the outer peripheral edge of the valve box 11 and the outer peripheral edge of the spring protection cylinder 35 are integrally attached by a bolt 41. To be

One end and the other end of the adjustment spring 34 are different from the stepped portion 24b formed on the upper end surface of the diaphragm receiver 24 and the stepped portion 39b formed on the lower surface of the spring receiver 39 provided in the inner space of the spring protection cylinder 35. Supported.
A tip portion 36a of an adjusting screw 36 screwed into a female screw portion 35b formed on the top portion 35a of the spring protection cylinder 35 is fitted into a recess 39a provided at the center of the upper end surface of the spring receiver 39.
The adjustment spring 34 urges the diaphragm receiver 24 and the diaphragm 30 in the direction of arrow A that separates the valve body 15 from the valve seat 14.

The adjusting screw 36 can be pushed into the spring protection cylinder 35 by the rotation of its head portion 36b. A hexagon nut 38 is attached to the adjusting screw 36, and is used to fix the adjusting screw 36 in the spring protection cylinder 35 in a pushed state.
Therefore, the adjustment spring 34 can be compressed by moving the spring receiver 39 in the arrow A direction via the tip portion 36a of the adjustment screw 36. Further, the adjustment spring 34 can be extended by moving the spring receiver 39 in the arrow B direction via the tip portion 36a of the adjustment screw 36. Thereby, the valve opening degree by the valve element 15 and the valve seat 14 can be adjusted by the set pressure of the adjusting spring 34.

  A closed spring chamber 40 is formed above the diaphragm 30, which is an internal space of the spring protection cylinder 35. In the valve box 11, a diaphragm chamber 50 is formed below the diaphragm 30. A communication hole 32 that communicates with each other is formed between the diaphragm chamber 50 of the valve box 11 and the secondary flow path 12b.

  The operation of the pressure reducing valve main body 2 having such a configuration as a single unit is such that the faucet (not shown) on the secondary flow passage 12b side is closed, that is, the secondary pressure of the secondary flow passage 12b is When the height is high, the upward force acting on the diaphragm 30 in the arrow B direction via the communication hole 32 and the diaphragm chamber 50 is large. Therefore, the valve body 15 is lifted upward together with the valve rod 17, and the valve body 15 and the valve seat 14 are brought into contact with each other to close the valve.

  After that, in the pressure reducing valve body 2, when the faucet on the secondary side flow passage 12b side is opened and the secondary side pressure of the secondary side flow passage 12b decreases, the diaphragm 30 passes through the communication hole 32 and the diaphragm chamber 50. The upward force acting on is reduced. Therefore, the valve body 15 is pushed downward together with the valve rod 17 by the urging force of the adjusting spring 34, and the valve body 15 is separated from the valve seat 14 to open the valve.

  As described above, the pressure reducing valve main body 2 has a valve opening force of the adjusting spring 34 to the lower side of the valve body 15 via the diaphragm 30 and a valve body 15 via the diaphragm 30 due to the secondary side pressure of the secondary side flow passage 12b. The position of the valve element 15 with respect to the valve seat 14 in the direction of arrow AB changes due to the difference between the two valve closing force and the valve closing force, and the flow rate of the fluid flowing from the primary side flow passage 12a to the secondary side flow passage 12b. Is controlled.

<Structure of pilot controller>
As shown in FIGS. 1 and 3, the pilot controller 3 according to this embodiment includes an upstream sub-pipe H1a branched from the upstream pipe H1 and a downstream downstream sub-pipe H2a branched from the pipe H2. An auxiliary pressure supply pipe H3 for generating and supplying auxiliary pressure from the pilot controller 3 to the spring chamber 40 of the pressure reducing valve body 2 is connected.

The pilot controller 3 includes a main body 60 having a substantially rectangular parallelepiped shape as a whole, and an upper lid 80 that closes an upper opening of the main body 60.
The main body portion 60 is configured by stacking a lower step portion 61, a middle step portion 62, and an upper step portion 63 from below in the direction of arrow A. With the upper lid portion 80 further stacked on the upper portion 63 of the main body portion 60, the upper lid portion 80, the upper step portion 63, the middle step portion 62 and the lower step portion 61 are integrally fixed by the bolt 81. An O-ring 61a is attached between the middle step portion 62 and the lower step portion 61.

  In the middle step portion 62 placed on the lower step portion 61 of the main body portion 60, a supply passage 65 having a diameter W1 is formed from the side surface in the arrow D direction toward the inside in the arrow C direction. The upstream sub-pipe H1a is connected to the supply port 65a of the supply path 65. As shown in FIG. 1, the upstream side sub-pipe H1a is provided with a pressure reducing valve 6 in the middle, and connects the fluid passage in the upstream side pipe H1 and the supply passage 65 via the pressure reducing valve 6. .

  The pressure reducing valve 6 reduces the pressure of the fluid in the upstream pipe H1 to a predetermined pressure. The predetermined pressure is a pressure with which an auxiliary pressure described later can be obtained. Hereinafter, the fluid whose pressure is reduced by the pressure reducing valve 6 and is supplied to the pilot controller 3 is simply referred to as an auxiliary pressure fluid. Therefore, in this embodiment, the auxiliary pressure fluid is supplied from the fluid passage 4 in the upstream pipe H1 to the pilot controller 3 via the pressure reducing valve 6.

Further, in the middle section 62, an output path 66 having a diameter W1 for supplying the auxiliary pressure to the spring chamber 40 of the pressure reducing valve main body 2 via the auxiliary pressure supply pipe H3 extends from the side surface in the arrow C direction to the arrow D direction. It is formed inward. An auxiliary pressure supply pipe H3 is connected to the output port 66a of the output path 66.
A diaphragm 67 having a diameter W2 (W2 <W1) is formed between the supply passage 65 and the output passage 66 of the middle section 62. An auxiliary chamber 70 is formed between the output port 66a and the diaphragm 67.

  Further, above the supply passage 65 in the middle portion 62, a discharge passage 68 is formed from the side surface in the arrow D direction toward the inside in the arrow C direction. In this embodiment, the discharge pipe H4 is connected to the discharge port 68a of the discharge path 68. When the fluid flowing through the upstream pipe H1 is a liquid or a gas that cannot be released into the atmosphere, although not shown, a processing device for processing these fluids, a tank for storing these fluids, etc. Is connected to the discharge pipe H4.

When the fluid flowing through the upstream pipe H1 is a gas that can be released into the atmosphere, the exhaust port 68a or the exhaust pipe H4 is opened into the atmosphere.
A through hole 69 for discharging the auxiliary pressure fluid supplied from the upstream side sub-pipe H1a to the supply passage 65 is formed above the auxiliary chamber 70 in the middle section 62 in the direction of the arrow B. Therefore, the auxiliary chamber 70 and the discharge path 68 are communicated with each other through the through hole 69 of the middle section 62.

Further, a valve seat 64 slightly protruding in the direction of arrow B is formed at the upper opening peripheral edge of the through hole 69 formed in the middle step portion 62.
A lower diaphragm 71 is placed on the upper end surface of the middle step portion 62, and a valve body 72 penetrates through a through hole in the center of the lower diaphragm 71. The valve body 72 has a valve portion 72a arranged to face the valve seat 64, and the valve portion 72a is located below the lower diaphragm 71 in the direction of arrow A and is arranged in the discharge passage 68.

  The shaft portion 72b of the valve body 72 is positioned above the lower diaphragm 71 in the direction of the arrow B, and a substantially cylindrical valve body receiver 73 is integrally fixed to the shaft portion 72b.

  An upper step portion 63 is placed on the upper end surface of the lower diaphragm 71, and a valve body receiver 73 is positioned in a diaphragm chamber 75 formed in the upper step portion 63. In addition, in the upper stage portion 63, a secondary side pressure detection path 74 communicating with the secondary side flow path 12b of the pressure reducing valve main body 2 via the downstream side sub-pipe H2a is inward in the direction of arrow C from the side surface in the direction of arrow D. Formed towards. The downstream side sub-pipe H2a is connected to the pressure detection port 74a of the secondary side pressure detection path 74.

  An upper diaphragm 76 is integrally fixed to the upper end surface of the upper step portion 63. A diaphragm receiver 82 is integrally fixed to the upper diaphragm 76. A rear end of the shaft 72b of the valve body 72 in the direction of arrow B is passed through a through hole in the center of the diaphragm receiver 82, and a hexagon nut 83 is screwed to a male screw portion of the rear end. . Thus, the valve body 72 is integrated with the lower diaphragm 71, the valve body receiver 73, the upper diaphragm 76, and the diaphragm receiver 82.

  The upper lid portion 80 is attached to the upper step portion 63 in a state where the upper diaphragm 76 is sandwiched between the upper lid portion 80 and the upper step portion 63. Therefore, since the upper diaphragm 76 and the lower diaphragm 71 are integrally formed with the valve body 72, the valve body 72 moves up and down in conjunction with the upward and downward movements of the upper diaphragm 76 and the lower diaphragm 71 in the arrow AB direction. Accordingly, the valve opening degree between the valve portion 72a of the valve body 72 and the valve seat 64 changes.

  A diaphragm receiver 82 is arranged in an inner space formed by the upper lid portion 80 and the upper diaphragm 76, and a stepped portion 82b formed around a convex portion 82a on the upper end surface of the diaphragm receiver 82 and the diaphragm receiver 82. One end and the lower end of the adjustment spring 85 are supported by the stepped portion 84b formed on the lower surface of the spring receiver 84 provided in the inner space of the upper lid portion 80 so as to face each other. The adjustment spring 85 biases the diaphragm receiver 82 and the upper diaphragm 76 in the direction of arrow A that presses the valve body 72 against the valve seat 64.

The tip end 86a of the adjusting screw 86 screwed to the female screw portion 80b formed on the top 80a of the upper lid 80 is in contact with the recess 84a provided at the center of the upper end surface of the spring receiver 84.
The adjusting screw 86 can be pushed into the internal space of the upper lid portion 80 by the rotation of the head portion 86b. A hexagon nut 87 is attached to the adjusting screw 86 at the top 80 a of the upper lid 80. The hexagon nut 87 is used to fix the state in which the adjusting screw 86 is pushed inside the upper lid portion 80.

  Therefore, the adjustment spring 85 can be compressed by moving the spring receiver 84 in the arrow A direction via the tip portion 86a of the adjustment screw 86. Further, the adjustment spring 85 can be extended by moving the spring receiver 84 in the direction of the arrow B via the tip portion 86a of the adjustment screw 85. As a result, the valve opening degree of the valve portion 72a of the valve body 72 with respect to the through hole 69 can be adjusted by the set pressure of the adjusting spring 85.

In addition, a through hole 80c is formed on the peripheral side surface of the upper lid portion 80, and when the spring receiver 84 moves in the direction of the arrow A, the inside of the upper lid portion 80 enters from the outside through the through hole 80c of the upper lid portion 80. Take in the air.
On the other hand, when the spring receiver 84 moves in the direction of arrow B, the air in the inner space of the upper lid portion 80 is exhausted from the through hole 80c. As a result, the spring bridge 84 is smoothly moved in the arrow AB direction.

  The operation of the pilot controller 3 having such a configuration as a single unit will be described below on the assumption that the fluid of a predetermined pressure is constantly supplied from the upstream side sub-pipe H1a to the supply passage 65.

  When the faucet (not shown) on the secondary side flow passage 12b side is closed, that is, when the secondary side pressure of the secondary side flow passage 12b is high, the pilot controller 3 determines the downstream side sub-pipe H2a and the secondary side pipe H2a. Since the upward force acting on the upper diaphragm 76 in the direction of the arrow B through the side pressure detection path 74 is large, the valve body 72 is pushed upward together with the upper diaphragm 76 and the lower diaphragm 71, and the valve portion 72a moves toward the valve seat 64. To open the valve.

Here, the fluid of a predetermined pressure is supplied from the upstream side sub-pipe H1a to the supply passage 65, but since the valve portion 72a is opened apart from the valve seat 64, the auxiliary chamber 70 is opened via the throttle 67. Most of the fluid supplied to is discharged through the discharge passage 68.
That is, the fluid supplied to the auxiliary chamber 70 via the throttle 67 is not supplied from the output passage 66 to the spring chamber 40 of the pressure reducing valve body 2 via the auxiliary pressure supply pipe H3.

After that, the pilot controller 3 opens the faucet (not shown) on the secondary side flow passage 12b side, and when the secondary side pressure of the secondary side flow passage 12b gradually decreases, the downstream side sub-pipe H2a and the secondary side pipe H2a. The upward force acting on the upper diaphragm 76 in the direction of the arrow B via the side pressure detection path 74 is reduced.
As a result, the valve body 72 is pushed down in the direction of arrow A together with the upper diaphragm 76 and the lower diaphragm 71 by the urging force of the adjusting spring 85, and the valve portion 72a gradually approaches the valve seat 64.

  That is, the pilot controller 3 balances the force of lifting the upper diaphragm 76 in the direction of arrow B by the secondary pressure of the pressure reducing valve main body 2 and the force of the adjusting spring 85 pushing down the upper diaphragm 76 in the direction of arrow A to balance each other. ing. In this state, when the secondary side pressure of the secondary side flow passage 12b in the pressure reducing valve main body 2 increases or decreases, the opening degree between the valve portion 72a of the valve body 72 and the valve seat 64 changes.

  At this time, the pressure of the fluid supplied from the upstream side sub-pipe H1a to the supply path 65 is higher than the pressure when discharged from the discharge path 68. The pressure of the fluid that has passed through the throttle 67 and has flowed into the auxiliary chamber 70 is lower than the pressure of the fluid that is supplied from the upstream side sub-pipe H1a to the supply passage 65, but when the fluid is discharged from the discharge passage 68. Greater than pressure. Therefore, the fluid in the auxiliary chamber 70 is supplied as an intermediate pressure from the output passage 66 to the spring chamber 40 of the pressure reducing valve body 2 via the auxiliary pressure supply pipe H3.

  After that, when the flow rate of the secondary side flow passage 12b in the pressure reducing valve main body 2 becomes maximum and the secondary side pressure becomes the lowest, the upper diaphragm 76 is passed through the downstream side sub-pipe H2a and the secondary side pressure detection path 74. Since the acting upward force is the smallest, the urging force of the adjusting spring 85 pushes down the valve body 72 together with the upper diaphragm 76 and the lower diaphragm 71, and eventually the valve portion 72a and the valve seat 64 come into contact with each other. Completely close the valve.

At this time, since the fluid supplied from the upstream side sub-pipe H1a to the supply passage 65 is not discharged from the discharge passage 68, the fluid flowing through the throttle 67 into the auxiliary chamber 70 flows from the output passage 66 to the auxiliary pressure supply pipe. It is supplied to the spring chamber 40 of the pressure reducing valve body 2 via H3.
Therefore, the intermediate pressure of the auxiliary chamber 70 supplied to the spring chamber 40 of the pressure reducing valve main body 2 from the output path 66 via the auxiliary pressure supplying pipe H3 is equal to the pressure reducing valve main body 2 with respect to the lower surface of the upper diaphragm 76 in the pilot controller 3. When the secondary pressure of the pressure reducing valve main body 2 with respect to the lower surface of the upper diaphragm 76 decreases, the secondary pressure decreases.

  Thus, the pilot controller 3 reduces the clearance between the valve portion 72a and the valve seat 64 as the secondary pressure in the secondary flow path 12b of the pressure reducing valve main body 2 gradually decreases, and the fluid passing through the throttle 67 is discharged. The intermediate pressure is gradually increased and is supplied as auxiliary pressure to the spring chamber 40 of the pressure reducing valve body 2.

<Operation of pressure reducing valve>
The overall operation of the separation type pressure reducing valve 1 having such a configuration will be described.
In the separable pressure reducing valve 1, when the faucet (not shown) on the secondary flow passage 12b side is closed, that is, when the secondary pressure of the secondary flow passage 12b in the pressure reducing valve main body 2 is high, communication is established. The upward force acting on the diaphragm 30 through the hole 32 and the diaphragm chamber 50 is large, and the valve body 15 is lifted upward together with the valve rod 17, so that the valve body 15 and the valve seat 14 are brought into contact with each other to close the valve. .

At this time, since the upward force acting on the upper diaphragm 76 via the secondary side flow passage 12b of the pressure reducing valve main body 2, the downstream side sub-pipe H2a, and the secondary side pressure detection passage 74 of the pilot controller 3 is large, The valve body 72 is lifted upward together with the upper diaphragm 76 and the lower diaphragm 71, and the valve portion 72a of the valve body 72 is separated from the valve seat 64 and is in a state of being opened.
In this case, most of the fluid supplied from the upstream side sub pipe H1a to the supply passage 65 of the pilot controller 3 is discharged through the discharge passage 68, and the fluid in the auxiliary chamber 70 is output from the output passage 66 and the auxiliary pressure supply pipe. It is not supplied to the spring chamber 40 of the pressure reducing valve body 2 via H3. That is, at this time, there is no difference from the conventional pressure reducing valve body 2 when the pilot controller 3 is not installed.

  After that, when the faucet on the secondary flow passage 12b side of the pressure reducing valve body 2 is opened to increase the flow rate of the fluid in the flow passage and the secondary pressure of the secondary flow passage 12b decreases, the communication hole The upward force acting on the diaphragm 30 via the diaphragm 32 and the diaphragm chamber 50 is reduced. As a result, the valve body 15 is pushed downward together with the valve rod 17 by the urging force of the adjusting spring 34, so that the valve body 15 separates from the valve seat 14 and opens the valve.

As a result, in the pressure reducing valve body 2, the fluid starts to flow from the primary side flow passage 12a to the secondary side flow passage 12b. That is, since the pressure reducing valve main body 2 mechanically operates in this way, when the faucet on the secondary side flow passage 12b side is opened, the valve body 15 instantaneously performs a response operation.
At this time, the upward force acting on the upper diaphragm 76 via the secondary side flow passage 12b of the pressure reducing valve main body 2, the downstream side sub-pipe H2a, and the secondary side pressure detection passage 74 of the pilot controller 3 gradually decreases. Therefore, in the pilot controller 3, the valve body 72 is pushed downward together with the upper diaphragm 76 and the lower diaphragm 71 by the urging force of the adjusting spring 85, and the valve portion 72a of the valve body 72 gradually approaches the valve seat 64. .

Then, the amount of the fluid flowing from the upstream side sub-pipe H1a to the auxiliary chamber 70 via the supply passage 65 and the throttle 67 is gradually reduced from the discharge passage 68, so the output passage 66 is increased while gradually increasing the pressure. Is supplied to the spring chamber 40 of the pressure reducing valve main body 2 via the auxiliary pressure supply pipe H3.
Here, since the valve seat 64 built in the pilot controller 3 has a very small valve diameter, the pressure of the fluid supplied from the output passage 66 to the spring chamber 40 of the pressure reducing valve main body 2 is small from the discharge passage 68. Precisely controlled by exhaust.

That is, it takes a predetermined time to change the pressure in the spring chamber 40 of the pressure reducing valve main body 2 by the fluid having the intermediate pressure from the auxiliary chamber 70 of the pilot controller 3.
Therefore, the intermediate pressure of the fluid supplied from the auxiliary chamber 70 of the pilot controller 3 to the spring chamber 40 of the pressure reducing valve body 2 gradually increases with the passage of time.

In this way, since the intermediate pressure supplied to the spring chamber 40 of the pressure reducing valve main body 2 is gradually increased and is supplied to the spring chamber 40, the diaphragm 30 of the pressure reducing valve main body 2 is gradually pushed downward by this intermediate pressure.
As the diaphragm 30 of the pressure reducing valve body 2 is further pushed downward by the intermediate pressure of the fluid supplied from the pilot controller 3, the valve body 15 is separated from the valve seat 14, and as shown in FIG. The valve opening degree of the valve element 15 with respect to the valve seat 14 is gradually increased as compared with the above.

  As described above, the pilot controller 3 reduces the gap between the valve portion 72a and the valve seat 64 as the secondary pressure of the secondary flow path 12b in the pressure reducing valve main body 2 decreases, so that the throttle 67 is closed. The intermediate pressure of the fluid that has passed is supplied as auxiliary pressure to the spring chamber 40 of the pressure reducing valve body 2 while gradually increasing.

After that, when the flow rate of the secondary side flow passage 12b in the pressure reducing valve main body 2 becomes maximum and the secondary side pressure becomes the lowest, the downstream side sub-pipe H2a and the secondary side pressure detection path 74 of the pilot controller 3 are used. The upward force acting on the upper diaphragm 76 is minimized.
The urging force of the adjusting spring 85 pushes down the valve body 72 together with the upper diaphragm 76 and the lower diaphragm 71, causing the valve portion 72a of the valve body 72 and the valve seat 64 to come into contact with each other to close the pilot controller 3. Speak.

At this time, the fluid supplied from the upstream side sub-pipe H1a to the supply passage 65 of the pilot controller 3 is no longer discharged from the discharge passage 68, and the fluid flowing through the throttle 67 into the auxiliary chamber 70 flows from the output passage 66 to the auxiliary pressure. It is supplied to the spring chamber 40 of the pressure reducing valve body 2 via the supply pipe H3.
When the valve portion 72a of the valve body 72 of the pilot controller 3 abuts the valve seat 64 and closes the valve, the intermediate pressure of the fluid from the auxiliary chamber 70 becomes maximum, and the valve body 15 and the valve of the pressure reducing valve body 2 after that time point The valve opening between the seats 14 is constant (FIG. 4).

Therefore, since the fluid (auxiliary pressure) supplied from the pilot controller 3 to the spring chamber 40 of the pressure reducing valve main body 2 makes the valve opening degree between the valve element 15 and the valve element 14 of the pressure reducing valve main body 2 larger and more constant than before. As shown in FIG. 5, it is possible to prevent a decrease in the secondary pressure of the secondary flow path 12b and eliminate the offset.
After that, when the secondary pressure in the secondary flow path 12b increases, the pilot controller 3 gradually opens, so that the fluid (auxiliary pressure) supplied from the pilot controller 3 to the spring chamber 40 of the pressure reducing valve body 2 is increased. ) Also decreases, the valve opening between the valve body 15 and the valve seat 14 of the pressure reducing valve main body 2 is reduced, and the valve is eventually closed.

<Effect>
As described above, in the separation type pressure reducing valve 1, the valve opening degree between the valve body 15 and the valve seat 14 becomes stable within a few seconds when the secondary side pressure of the secondary side flow passage 12b of the pressure reducing valve body 2 decreases. (Fig. 4).
During this time, even if the fluid from the auxiliary chamber 70 of the pilot controller 3 is supplied to the spring chamber 40 of the pressure reducing valve body 2, the valve opening degree between the valve body 15 and the valve seat 14 is not stable and an offset occurs. Therefore, it is not accurate.

However, as the intermediate pressure of the fluid supplied from the pilot controller 3 to the spring chamber 40 of the pressure reducing valve body 2 increases with time, the valve opening degree between the valve body 15 and the valve seat 14 of the pressure reducing valve body 2 increases. Can be gradually increased (Fig. 4).
As described above, in the separation type pressure reducing valve 1, after the valve opening degree between the valve body 15 and the valve seat 14 is stabilized, it is possible to perform correction control so as to eliminate the offset while further increasing the valve opening degree.

  As a result, the separable pressure reducing valve 1 prevents a decrease in the secondary side pressure of the secondary side flow passage 12b in the pressure reducing valve main body 2 while maintaining the operation stability without causing vibration or the like in the valve body 15 and increasing the pressure. The accuracy can be improved. Thus, the separable type pressure reducing valve 1 can perform highly accurate control that is incomparable to the conventional direct-acting type pressure reducing valve without increasing the size.

  In the separable pressure reducing valve 1, since the pilot controller 3 is separately installed outside the spring protection portion 35, the pilot controller 3 can be externally installed afterwards with respect to the pressure reducing valve main body 2.

<Second Embodiment>
<Overall structure of pressure reducing valve with integrated pilot controller>
As shown in FIG. 6 in which parts corresponding to those in FIG. 1 are assigned the same reference numerals, a pilot controller integrated installation type pressure reducing valve 100 (hereinafter referred to simply as “integral type pressure reducing valve” as a self-powered regulating valve in the second embodiment. Is placed between the upstream pipe H1 and the downstream pipe H2.

  The integrated pressure reducing valve 100 includes a valve box 11, a spring protection cylinder 150 fixed to an upper portion of the valve box 11 in the direction of arrow B, and an auxiliary pressure supply integrally fixed to an upper end surface of the spring protection cylinder 150. And a pilot controller 130 for. Here, since the valve box 11 and its internal structure are the same as those of the pressure reducing valve main body 2 in the first embodiment, the description thereof will be omitted here for convenience.

<Structure of spring protection cylinder>
The spring protection cylinder 150 is integrally attached to the upper end portion of the valve box 11 with a bolt 41. The spring protection cylinder 150 has a through hole 151a formed at the upper end thereof. Further, in the spring protection cylinder 150, one end and the other end of the adjustment spring 152 are supported by the lower surface 151b of the upper end portion thereof and the step portion 24b of the diaphragm receiver 24.

  Since the spring protection cylinder 150 is not provided with the adjusting screw 36 (FIGS. 1 and 2) of the pressure reducing valve main body 2 in the first embodiment, the lower surface 151b of the upper end portion of the spring protection cylinder 150 and the diaphragm support 24. The adjusting spring 152 supported by the stepped portion 24b is adjusted to a predetermined set pressure. The valve rod 17, the diaphragm receiver 24, and the hexagonal nut 26 arranged inside the spring protection cylinder 150 are the same as those of the pressure reducing valve main body 2 in the first embodiment.

<Structure of pilot controller>
The pilot controller 130 is integrally fixed to the upper end surface of the spring protection cylinder 150 in a state in which the lower step portion 61 of the pilot controller 3 of the separation type pressure reducing valve 1 according to the first embodiment is removed. . That is, the pilot controller 130 has the same basic configuration as the pilot controller 3 except that the lower stage portion 61 does not exist. Although not shown, the output path 66a of the pilot controller 3 is closed by a plug or the like.

In this case, since the middle step portion 62 is integrally fixed to the upper end surface of the spring protection cylinder 150 instead of attaching the lower step portion 61 to the middle step portion 62, the auxiliary chamber 70 of the pilot controller 130 and the spring protection cylinder 150 are provided. The spring chamber 40 is communicated with the spring chamber 40 through the through hole 151 a of the spring protection cylinder 150.
The operation of the integrated pressure reducing valve 100 having such a configuration will be described. In the integrated pressure reducing valve 100, when the secondary side pressure of the secondary side flow passage 12b in the pressure reducing valve body 2 is high, the upward force acting on the diaphragm 30 via the communication hole 32 and the diaphragm chamber 50 is large, and Since the valve body 15 is lifted upward together with the rod 17, the valve body 15 and the valve seat 14 are brought into contact with each other to close the valve.

  At this time, the force transmitted from the secondary side flow passage 12b of the pressure reducing valve main body 2 to the pilot controller 130 via the downstream side sub pipe H2a and acting upward from the secondary side pressure detection passage 74 to the upper diaphragm 76 is generated. Since it is large, the valve body 72 is lifted upward together with the upper diaphragm 76 and the lower diaphragm 71, and the valve portion 72a of the valve body 72 separates from the valve seat 64 and opens.

In this case, most of the fluid supplied from the upstream side sub-pipe H1a to the supply passage 65 of the pilot controller 130 is discharged through the discharge passage 68, and passes from the auxiliary chamber 70 through the through hole 151a of the spring protection cylinder 150. No fluid is supplied to the spring chamber 40.
After that, in the integrated pressure reducing valve 100, when the secondary pressure of the secondary flow path 12b decreases, the upward force acting on the diaphragm 30 via the communication hole 32 and the diaphragm chamber 50 decreases.

As a result, the valve body 15 is pushed downward together with the valve rod 17 by the urging force of the adjustment spring 152, so that the valve body 15 separates from the valve seat 14 to open the valve, and the primary side flow passage 12a to the secondary side flow passage 12a. The fluid begins to flow to 12b.
At this time, the upward force that is transmitted from the secondary side flow passage 12b to the pilot controller 130 via the downstream side sub-pipe H2a and acts on the upper diaphragm 76 from the secondary side pressure detection passage 74 is gradually reduced. The valve body 72 is pushed downward together with the upper diaphragm 76 and the lower diaphragm 71 by the urging force of the spring 85, and the valve portion 72a of the valve body 72 gradually approaches the valve seat 64.

As a result, the fluid supplied from the upstream side sub-pipe H1a to the supply path 65 passes through the throttle 67 and flows into the auxiliary chamber 70, and the fluid in the auxiliary chamber 70 has an intermediate pressure (FIG. 3), and the spring protection cylinder 150 is provided. Is supplied to the spring chamber 40 via the through hole 151a.
Therefore, as the intermediate pressure of the fluid from the auxiliary chamber 70 of the pilot controller 130 increases (over time), the pressure of the spring chamber 40 gradually increases.
That is, since the intermediate pressure supplied to the spring chamber 40 is gradually increased, the intermediate pressure becomes an auxiliary pressure, and the diaphragm 30 is further pushed downward.

  As a result, the valve body 15 separates from the valve seat 14 by the amount by which the diaphragm 30 is further pushed downward, and the valve opening becomes larger than in the conventional case. As described above, the pilot controller 130 decreases the distance between the valve portion 72a of the valve body 72 and the valve seat 64 as the secondary pressure of the valve box 11 decreases, and thus the auxiliary chamber that has passed through the throttle 67. The intermediate pressure of 70 gradually increases and is supplied to the spring chamber 40 as an auxiliary pressure.

  After this, when the flow rate in the secondary side flow path 12b becomes maximum and the secondary side pressure becomes the lowest, the upward flow that acts on the upper diaphragm 76 via the downstream side sub-pipe H2a and the secondary side pressure detection path 74 is performed. The force becomes the smallest, and the valve body 72 is pushed down the most together with the upper diaphragm 76 and the lower diaphragm 71 by the urging force of the adjusting spring 85, and the valve portion 72a and the valve seat 64 come into contact with each other to close the valve.

At this time, the fluid supplied from the upstream side sub-pipe H1a to the supply path 65 is not completely discharged from the discharge path 68, and all the fluid that has passed through the throttle 67 and flowed into the auxiliary chamber 70 penetrates the spring protection cylinder 150. It is supplied to the spring chamber 40 via the hole 151a.
When the valve portion 72a of the valve body 72 of the pilot controller 130 comes into contact with the valve seat 64 and closes the valve, the intermediate pressure of the fluid from the auxiliary chamber 70 becomes the maximum, so that the valve body 15 of the pressure reducing valve main body 2 after that point. And the valve opening between the valve seats 14 becomes constant (FIG. 4).

  Therefore, the valve opening between the valve bodies 15 and 14 becomes larger than the conventional one due to the fluid (auxiliary pressure) supplied from the pilot controller 130 to the spring chamber 40, so that as shown in FIG. The offset can be eliminated by preventing the secondary pressure in the passage 12b from decreasing.

<Effect>
Also in the integrated pressure reducing valve 100, the valve body 15 increases with the increase of the fluid (auxiliary pressure) supplied from the pilot controller 130 to the spring chamber 40 when the secondary pressure of the secondary flow path 12b gradually decreases. Also, the valve opening between the valve seats 14 can be gradually increased.
In this way, the integrated pressure reducing valve 100 performs the correction control by gradually increasing the valve opening between the valve body 15 and the valve seat 14, so that the valve body 15 does not vibrate or the like and the operation stability is maintained. Therefore, it is possible to prevent the secondary side pressure of the secondary side flow passage 12b from decreasing and to improve the accuracy. Thus, the integrated pressure reducing valve 100 can perform highly accurate control that is incomparable to the conventional direct acting pressure reducing valve without increasing the size.

  The integrated pressure reducing valve 100 has the pilot controller 130 integrally installed on the upper part of the spring protection portion 150, and therefore the configuration thereof is downsized as compared with the separation type pressure reducing valve 1 according to the first embodiment. be able to.

<Third Embodiment>
<Overall structure of pilot operated pressure reducing valve>
As shown in FIG. 7 in which parts corresponding to those in FIG. 1 are denoted by the same reference numerals, a pilot operated pressure reducing valve 200 as a self-adjusting valve in the third embodiment is provided between the upstream pipe H1 and the downstream pipe H2. It is a conventional general type that is arranged in a main valve 201, an ejector (throttle valve) 220 and a pilot valve 230, but is different from the conventional one in that the pilot controller 3 (see FIG. 3) is installed separately.

This pilot controller 3 has the same configuration as that of the first embodiment, and an upstream side sub-pipe H1a, a downstream side sub-pipe H2a, and an auxiliary pressure supply pipe H3 are connected. The auxiliary pressure supply pipe H3 is connected to the spring chamber 240 of the pilot valve 230.
In this case, the pilot operated pressure reducing valve 200 is transmitted to the pilot controller 3 from the secondary side flow passage 202b through the downstream side sub pipe H2a when the secondary side pressure of the secondary side flow passage 202b decreases, and the pilot controller The valve portion 72a of the third valve body 72 gradually approaches the valve seat 64.

At this time, the fluid supplied from the upstream side sub-pipe H1a to the supply passage 65 passes through the throttle 67 and flows into the auxiliary chamber 70, and the fluid in the auxiliary chamber 70 serves as an intermediate pressure to the spring chamber 240 of the pilot valve 230. The pressure is gradually increased and supplied.
Therefore, as the intermediate pressure of the fluid from the auxiliary chamber 70 of the pilot controller 3 increases (over time), the pressure of the spring chamber 240 of the pilot valve 230 gradually increases, so that the pilot valve 230 opens. The degree increases.

As a result, the degree of opening of the pilot valve 230 becomes larger than in the conventional case, so that a large amount of fluid flows from the diaphragm chamber 216 of the main valve 201 to the ejector 220, the pilot valve 230, and the secondary side flow passage 202b.
Thus, in the pilot-operated pressure reducing valve 200, the valve body 211 of the main valve 201 opens in the direction of the arrow B in the direction larger than that of the conventional valve by the degree of opening of the pilot valve 230 that is larger than that of the conventional valve. It is possible to prevent the pressure in the secondary side flow passage 202b from decreasing with respect to the pressure in the flow passage 202a and eliminate the offset.

<Other Embodiments>
In addition, in the above-described first and second embodiments, the case where the pilot controllers 3 and 130 are installed as a separate type or an integrated type with respect to the direct acting pressure reducing valves 1 and 100 has been described. The present invention is not limited to this, and the pilot controllers 3 and 130 may be installed as a separate type or an integral type with respect to the direct-acting type back pressure valve.

  Further, in the above-described third embodiment, the case where the pilot controller 3 is separately installed with respect to the pilot valve 230 has been described, but the present invention is not limited to this, and the second embodiment is different from the second embodiment. Similarly, the pilot controller 3 may be integrally installed above the pilot valve 230.

Furthermore, in the above-described first to third embodiments, the case where the diaphragm 67 is provided inside the pilot controllers 3 and 130 has been described, but the present invention is not limited to this. When supplying the auxiliary pressure fluid to the auxiliary chamber 70, as shown in FIG. 8 , a throttle valve 7 is provided outside (upstream side) of the supply passage 65 of the pilot controllers 3 and 130. The fluid in the upstream side sub-pipe H1a may be supplied to the auxiliary chamber 70 via 65.

  In addition, in the above-described first to third embodiments, the upstream end of the upstream sub-pipe H1a is connected to the upstream pipe H1, and the fluid in the upstream pipe H1 is used as the auxiliary pressure fluid from the fluid passage 4. An example in which the pressure is supplied to the pilot controllers 3 and 130 via the pressure reducing valve 6 has been shown. However, the self-powered regulating valve according to the present invention may have a configuration in which the auxiliary pressure fluid is supplied from the primary side flow passage 12a of the valve box 11 to the pilot controllers 3 and 130 via the pressure reducing valve 6. When this configuration is adopted, the upstream end of the upstream side sub-pipe H1a is connected to the valve box 11. That is, the fluid serving as the auxiliary pressure fluid can be obtained from any fluid passage on the upstream side including the primary passage 12a, in other words, any fluid passage on the upstream side of the valve body 15. is there.

  1 ... Separation type pressure reducing valve, 2 ... Pressure reducing valve body (valve body), 3,130 ... Pilot controller (auxiliary pressure supply unit), 4 ... Fluid passage, 6 ... Pressure reducing valve, 7 ... Throttle valve, 11 ... ... Valve box, 12 ... Flow path, 12a ... Primary side flow path, 12b ... Secondary side flow path, 13 ... Partition wall, 14 ... Valve seat, 15 ... Valve element, 17 ... Valve rod, 18 ... ... Hexagon nut, 19 ... Valve spring, 21 ... Lower lid, 22 ... Liner, 23 ... Balance piston, 24 ... Diaphragm receiver, 26, 38, 83, 87 ... Hexagon nut, 30 ... Diaphragm, 31 ...... O-ring, 34, 85, 152 …… Adjustment spring, 35 …… Spring protection cylinder (spring protection part), 36,86 …… Adjustment screw, 39,84 …… Spring holder, 40 …… Spring chamber, 41 … Bolts, 50… diaphragm chambers, 60 …… main body, 61 …… lower stage, 62 …… Step portion, 63 ... Upper step portion, 64 ... Valve seat, 65 ... Supply passage, 66 ... Output passage, 67 ... Throttle, 68 ... Exhaust passage, 69 ... Through hole, 70 ... Auxiliary chamber, 71 ... Lower diaphragm, 72 ... Valve body, 72a ... Valve part, 73 ... Valve body receiver, 74 ... Secondary side pressure detection path (pressure detection path), 75 ... Diaphragm chamber, 76 ... Top Diaphragm (diaphragm for pressure detection) 80 ... Top cover, 81 ... Bolt, 82 ... Diaphragm receiver, 100 ... Integrated pressure reducing valve, 150 ... Spring protection cylinder, 151a ... Through hole, 200 ... Pilot operation Type pressure reducing valve, 201 ... main valve, 220 ... ejector (throttle valve), 230 ... pilot valve, 240 ... spring chamber, H1 ... upstream piping, H1a ... upstream sub piping.

Claims (5)

A diaphragm, in which a valve body disposed opposite to a valve seat provided between the primary side flow path and the secondary side flow path is integrated via a valve rod, is used as a secondary side pressure of the secondary side flow path. A valve box that drives the fluid to flow from the primary side flow path to the secondary side flow path,
An adjustment spring integrated with the diaphragm that urges the valve body to move away from the valve seat,
A spring protection portion which is provided above the diaphragm and stores the adjustment spring in a spring chamber of its internal space,
The auxiliary pressure fluid, which is installed outside the spring protection portion and is supplied to the spring chamber of the spring protection portion from a fluid passage on the upstream side including the primary side flow path through a pressure reducing valve, is used. An auxiliary pressure supply unit for generating and supplying an auxiliary pressure according to the secondary pressure ,
The auxiliary pressure supply unit,
A pressure detection path communicating with the secondary side flow path for detecting the secondary side pressure,
A supply path to which the auxiliary pressure fluid for generating the auxiliary pressure is supplied;
An output path for outputting the auxiliary pressure fluid from the supply path to the spring chamber of the spring protection part,
A discharge path communicating with the passage extending from the supply path to the output path through a through hole, and discharging the auxiliary pressure fluid supplied to the supply path;
A valve portion that opens and closes the through hole,
A pressure detection diaphragm provided integrally with the valve portion for detecting the secondary pressure via the pressure detection path;
An adjusting spring that is integrated with the pressure detecting diaphragm and urges the valve portion to close the through hole,
The valve portion is configured to open the through hole when the secondary pressure is high, and to close the through hole by decreasing the secondary pressure,
The opening of the valve portion with respect to the through hole is changed according to the secondary pressure detected through the pressure detecting diaphragm, and the auxiliary pressure by the auxiliary pressure fluid corresponding to the change is protected by the spring. A self-regulating valve that is supplied to the spring chamber of the section . The self-regulating valve according to claim 1 , wherein a throttle for generating the auxiliary pressure is provided between the supply passage and the output passage. The self-regulating valve according to claim 1 , wherein a throttle valve for generating the auxiliary pressure is provided on the upstream side of the supply passage. The self-powered regulating valve according to any one of claims 1 to 3 , wherein the auxiliary pressure supply unit is separately installed outside the spring protection unit. The self-powered regulating valve according to any one of claims 1 to 3 , wherein the auxiliary pressure supply unit is integrally installed on the upper portion of the spring protection unit.

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