JP2021163116A - Pressure reduction valve - Google Patents

Abstract

To provide a pressure reduction valve capable of preventing generation of a turbulent flow on a more downstream side than a valve body.SOLUTION: A pressure reduction valve includes: an actuator 13 for activating a pressure force; a main body 12; a supply air port 19 (a partition wall) partitioning a fluid channel 16 into a primary in-flow passage 17 and a secondary out-flow passage 18; a valve seat 22 provided around a valve opening part 21; and a valve body 25 for opening and closing the valve opening part 21, and further includes: a diaphragm 31 stretched, being sandwiched between the actuator 13 and the main body 12; a pressure chamber 34 making a pressure of the secondary out-flow passage 18 work on the diaphragm 31; and a spring member 26 for biasing the valve body 25 in a valve closing direction. The main body 12 is provided with a suction tube 35 (a suction passage) and a thin plate-like separator 41 for dividing the inside of the secondary out-flow passage 18 into a first passage which the suction tube 35 opens and a second passage on the opposite side.SELECTED DRAWING: Figure 1

Description

The present invention relates to a pressure reducing valve in which the valve body operates so that the pressure of the fluid on the secondary side becomes constant.

Conventionally, as a pressure reducing valve in which the valve body operates so that the pressure of the fluid on the secondary side becomes constant, for example, there is one described in Patent Document 1. As shown in FIG. 12, the pressure reducing valve disclosed in Patent Document 1 includes a valve body 2 that opens and closes the fluid passage 1, and an actuator 3 that drives the valve body 2. The fluid flows in the fluid passage 1 from the right side to the left side in FIG.

The actuator 3 has a spring member 4 that urges the valve body 2 in the valve opening direction, and a pressure chamber 6 in which the diaphragm 5 connected to the valve body 2 is a part of the wall. The pressure chamber 6 is communicated with the communication passage 7 on the downstream side of the valve body 2 of the fluid passage 1, and the pressure of the fluid passage 1a on the downstream side is introduced through the communication passage 7. The valve body 2 stops in a state where the pressure of the pressure chamber 6 and the spring force of the spring member 4 are in equilibrium, and the pressure of the pressure chamber 6 decreases as the pressure of the fluid passage 1a on the downstream side decreases, so that the spring It moves in the valve opening direction by the spring force of the member 4.

In the pressure reducing valve shown in Patent Document 1, the fluid flows as shown by the solid line arrow and the broken line arrow in FIG. The solid line arrow indicates the flow path of the fluid flowing at high flow velocity and high flow rate, and the broken line arrow indicates the flow path of the fluid flowing at low flow velocity and low flow rate. In this pressure reducing valve, a fluid having a high flow velocity and a high flow rate and a fluid having a low flow velocity and a low flow rate interfere with each other on the downstream side of the valve body 2, and turbulence is generated. The range in which turbulence occurs is shown by the alternate long and short dash line A in FIG.

Japanese Unexamined Patent Publication No. 2001-255942

In a pressure reducing valve in which the valve body 2 moves in the valve opening direction when the pressure of the fluid passage 1a on the downstream side decreases as described in Patent Document 1, the valve is valved when the flow rate of the fluid becomes large. There is a problem that the body 2 cannot be moved significantly in the valve opening direction, and the pressure in the fluid passage 1a on the downstream side tends to decrease. It is considered that the reason for this is that turbulence occurs on the downstream side of the valve body 2. That is, when turbulence occurs, the flow velocity of the fluid flowing near the opening of the communication passage 7 decreases, and the fluid is sucked out from the inside of the communication passage 7 toward the fluid passage 1a on the downstream side by the principle of so-called Bernoulli's negative pressure. It is considered that this is because the effect of being squeezed cannot be obtained.

An object of the present invention is to provide a pressure reducing valve capable of preventing turbulence from occurring on the downstream side of the valve body and increasing the flow velocity of the fluid.

In order to achieve this object, the pressure reducing valve according to the present invention includes an actuator that applies a pre-adjusted pressing force, an inflow port into which a fluid supplied from a fluid source flows in, and a fluid flowing in from the inflow port. A main body having an outlet that flows out to the outside and having a fluid passage that communicates between the inlet and the outlet to flow a fluid, and a main body provided in the main body, the fluid passage is 1 Provided around a partition partition that divides the inflow passage on the secondary side and the outflow passage on the secondary side, and a valve opening that penetrates the partition and communicates the inflow passage on the primary side and the outflow passage on the secondary side. A valve seat, a valve body that has a valve portion that is seated or separated from the valve seat and that opens and closes the valve opening, is sandwiched between the actuator and the main body body, and has an operating direction of the valve body. A diaphragm that is stretched in the direction orthogonal to each other and operates the valve body in the direction in which the valve opening opens in response to a pressing force from the actuator, and the pressure of the outflow passage on the secondary side is applied to the diaphragm with respect to the valve. In a pressure reducing valve having a pressure chamber that causes the body to operate in the direction in which the valve opening closes, and a spring that causes the valve body to act in a direction in which the valve opening closes, an outflow passage on the secondary side. Extends in a direction parallel to the extension direction of the diaphragm and extends toward the outlet so as to be orthogonal to the operating direction of the valve body, and the main body body is an outflow passage on the secondary side. A thin plate that is provided with a suction passage that communicates with the pressure chamber and divides the inside of the outflow passage on the secondary side into a first passage through which the suction passage opens and a second passage on the opposite side. It is equipped with a fluid separator.

In the present invention, the pressure reducing valve may be configured such that a fluid having a relatively high flow velocity flows through the first passage and a fluid having a relatively low flow velocity flows through the second passage.

In the present invention, in the pressure reducing valve, the separator is provided inside a ring fitted to the wall surface of the outflow passage on the secondary side, and the ring is provided with a through hole connected to the suction passage. It may have been done.

In the present invention, in the pressure reducing valve, the separator may be formed so that the cross section has an airfoil shape, and the flow velocity of the fluid flowing through the first passage may increase.

In the present invention, the suction passage may be positioned at a position facing the maximum blade thickness position of the separator in the pressure reducing valve.

According to the present invention, it is possible to provide a pressure reducing valve capable of increasing the flow velocity of the fluid in order to prevent the separator from generating turbulent flow on the downstream side of the valve body.

FIG. 1 is a cross-sectional view of a pressure reducing valve according to the present invention. FIG. 2 is an enlarged cross-sectional view showing a main part. FIG. 3 is a perspective view of the separator. FIG. 4 is a cross-sectional view for explaining the flow path of the fluid. FIG. 5 is a cross-sectional view showing a modified example of the separator. FIG. 6 is a perspective view of the separator. FIG. 7 is an enlarged cross-sectional view showing the separator. FIG. 8 is a cross-sectional view for explaining the flow path of the fluid. FIG. 9 is a cross-sectional view showing a modified example of the separator. FIG. 10 is a cross-sectional view showing a modified example of the separator. FIG. 11 is a graph showing the change in the pressure difference between the fluid passage and the pressure chamber with respect to the change in the flow rate of the fluid. FIG. 12 is a cross-sectional view of a conventional pressure reducing valve.

Hereinafter, an embodiment of the pressure reducing valve according to the present invention will be described in detail with reference to FIGS. 1 to 11.
The pressure reducing valve 11 shown in FIG. 1 includes a main body 12 located on the lower side of FIG. 1 and an actuator 13 attached to the main body 12 for applying a pre-adjusted pressing force.
The main body 12 according to this embodiment is composed of a valve accommodating portion 12a to which the actuator 13 is attached and a cup-shaped drain bowl 12b located on the opposite side of the actuator 13.

The main body 12 has an inflow port 14 into which a fluid supplied from a fluid source (not shown) flows in at the right end in FIG. 1, and flows in from the inflow 14 into the left end in FIG. It has an outflow port 15 through which the fluid is discharged to the outside. Further, inside the main body 12, a fluid passage 16 that communicates between the inflow port 14 and the outflow port 15 to flow a fluid is provided, and the fluid passage 16 is provided as a primary side inflow passage 17 and a secondary side. An intake port 19 for partitioning the outflow passage 18 on the side is provided. In this embodiment, the air supply port 19 corresponds to the "bulkhead" in the present invention.

The air supply port 19 is formed in a columnar shape, and as shown in FIG. 2, has a valve opening 21 formed of a through hole communicating the inflow passage 17 on the primary side and the outflow passage 18 on the secondary side. ing. An annular valve seat 22 is provided around the upstream end of the valve opening 21. A plurality of communication holes 23 extending radially in the direction orthogonal to the valve opening 21 are formed in the air supply port 19. Further, an annular groove 24 extending over the entire circumferential direction is formed on the outer peripheral portion of the air supply port 19. A part of the groove 24 is connected to the outflow passage 18 on the secondary side. The communication hole 23 is formed so as to extend from the valve opening 21 to the annular groove 24.

A valve body 25 for opening and closing the valve opening 21 is inserted inside the valve opening 21. The valve body 25 has a columnar shaft portion 25a inserted into the valve opening 21 and a valve portion 25b provided at one end (lower end) of the shaft portion 25a, and penetrates the air supply port 19. It is supported so that it can be moved freely. One end of the valve body 25 (the lower end of the valve portion 25b) is urged toward the other (upward) by the spring member 26, and the other end of the valve body 25 (the upper end of the shaft portion 25a) is from the actuator 13 described later. It is pushed toward one end (downward) by the pushing pressure of. The valve portion 25b of the valve body 25 is seated on the valve seat 22 when the pressing force from the actuator 13 is smaller than the spring force of the spring member 26, and when the pressing force from the actuator 13 is larger than the spring force of the spring member 26. Separate from the valve seat 22.

As shown in FIG. 1, a diaphragm 31 is provided at the lower end of the actuator 13 so as to face the shaft portion 25a of the valve body 25 described above. The diaphragm 31 is stretched between the main body 12 and the bonnet 32 of the actuator 13 in a state of extending in a direction orthogonal to the operating direction of the valve body 25 (left-right direction in FIG. 1). A pressing member 33 is attached to the central portion of the diaphragm 31, and the pressing member 33 has an internal space of the bonnet 32 (actuator inner chamber 40), a pressure chamber surrounded by the diaphragm 31 and the main body 12 inside the pressing member 33. A communication passage 33a communicating with the 34 is formed, and the opening 33b of the communication passage 33a on the pressure chamber 34 side is located directly above the upper end of the shaft portion 25a of the valve body 25.

The pressing member 33 and the shaft portion 25a of the valve body 25 are in contact with each other or separated from each other as described later, and the shaft portion 25a of the valve body 25 is in contact with the pressing member 33. Then, the opening 33b on the pressure chamber 34 side of the communication passage 33a is closed by the upper end of the valve shaft 25a, and the communication passage 33a is blocked. On the other hand, when the pressing member 33 and the shaft portion 25a of the valve body 25 are separated from each other, the communication passage 33a is opened so that the pressure chamber 34 and the actuator inner chamber 40 communicate with each other. An exhaust hole 39 that communicates with the actuator inner chamber 40 and the outside of the actuator 13 is formed in a part of the side wall of the bonnet 32, and when the communication passage 33a of the pressing member 33 is blocked, the inside of the actuator is formed. The pressure inside the chamber 40 becomes equal to the pressure outside the actuator 13 (atmospheric pressure).

On the other hand, when the communication passage 33a of the pressing member 33 is open, the fluid in the pressure chamber 34 having a pressure higher than the atmospheric pressure flows into the actuator inner chamber 40 through the communication passage 33a, and further passes through the exhaust hole 39. Is discharged to the outside of the actuator 13.
Here, the displacement of the diaphragm 31 will be described. The diaphragm 31 presses the diaphragm 31 downward from the surface of the diaphragm 31 on the actuator inner chamber 40 side and the force F1 that presses the diaphragm 31 upward from the surface on the pressure chamber 34 side. In response to the force F2, the direction of displacement of the diaphragm 31 is determined by the magnitude relationship between the force F1 and the force F2. That is, when the force F1 is larger than the force F2, the central portion of the diaphragm 31 is displaced in the direction away from the main body body 12.

Then, in conjunction with this, the valve body 25 moves in the direction in which the valve portion 25b is seated on the valve seat 22 (that is, the direction in which the valve opening 21 is closed). On the contrary, when the force F1 is smaller than the force F2, the central portion of the diaphragm 31 is displaced in the direction close to the main body body 12. Then, in conjunction with this, the valve body 25 is in the direction in which the valve portion 25b is separated from the valve seat 22 (that is, the direction in which the valve opening 21 is opened) while maintaining the state in which the tip of the shaft portion 25a of the valve body 25 is in contact with the pressing member 33. ). In this way, the displacement of the diaphragm 31 causes the valve body 25 to move forward and backward in the operating direction to open and close the valve opening 21.

A part of the pressure chamber 34 is formed so as to be located between the outflow passage 18 on the secondary side and the diaphragm 31. The outflow passage 18 on the secondary side according to this embodiment extends in a direction parallel to the extension direction of the diaphragm 31, and extends toward the outflow port 15 so as to be orthogonal to the operating direction of the valve body 25. There is. A suction tube 35 formed of a through hole is provided between the pressure chamber 34 in the main body 12 and the outflow passage 18 on the secondary side. In this embodiment, the suction tube 35 corresponds to the "suction passage" in the present invention. The suction tube 35 communicates the pressure chamber 34 with the outflow passage 18 on the secondary side. Therefore, the fluid is introduced into the pressure chamber 34 from the outflow passage 18 on the secondary side via the suction tube 35. In this way, the pressure of the fluid introduced from the outflow passage 18 on the secondary side becomes the pressure in the pressure chamber 34, and a force F1 for pressing upward is applied to the diaphragm 31, and as a result, the valve body 25 is opened to the valve opening 21. Operates in the closing direction.

The pressing member 33 provided in the central portion of the diaphragm 31 is urged toward the main body 12 by a pressure adjusting spring 36 composed of a compression coil spring housed and installed in the actuator inner chamber 40. The pressure adjusting spring 36 is installed so that one end (lower end) is held by the pressing member 33 to push the pressing member 33 and the other end (upper end) holds the pressure adjusting spring 36. It is provided between these members in a state where the pressure adjusting spring receiver 37 is pushed. The pressure adjusting spring receiver 37 is in contact with one end (lower end) of the pressure adjusting knob 38 screwed into the bonnet 32, and is sandwiched between the pressure adjusting knob 38 and the pressure adjusting spring 36. The pressure adjusting spring 36 held by the pressing member 33 and the pressure adjusting spring receiver 37 applies a pre-adjusted downward pressing force F2 to the diaphragm 31, and as a result, opens the valve body 25 with the valve opening 21. Operates in the direction that opens.

In this way, the upward pressing force F1 and the downward pressing force F2 act on the diaphragm 31, but the operating directions of the valve body 25 are the pressure in the pressure chamber 34 and the spring force of the pressure adjusting spring 36. It is decided based on the magnitude relationship with. When the pressure in the pressure chamber 34 is larger than the spring force of the pressure adjusting spring 36, the valve body 25 is operated in the direction in which the valve opening 21 closes as described above, and as a result, the outflow passage 18 on the secondary side from the valve opening 21 The flow rate of fluid flowing to is reduced. On the other hand, when the pressure in the pressure chamber 34 is smaller than the spring force of the pressure adjusting spring 36, the valve body 25 is operated in the direction in which the valve opening 21 opens, and as a result, the outflow passage 18 on the secondary side from the valve opening 21 The flow rate of fluid flowing to increases.
The pressure reducing valve 11 according to this embodiment is provided with a separator 41 in the outflow passage 18 on the secondary side in order to reduce the pressure in the pressure chamber 34 at the time of a large flow rate.

The separator 41 is formed in a thin plate shape, and as shown in FIG. 2, a first passage 42 in which the suction tube 35 opens inside the outflow passage 18 on the secondary side and a second passage 43 on the opposite side. It is divided into and. The separator 41 according to this embodiment is formed of a flat plate having a constant thickness, and is provided inside the ring 44 so as to extend parallel to the axis C (see FIG. 2) of the ring 44, as shown in FIG. .. The ring 44 is formed so as to fit on the wall surface of the outflow passage 18 on the secondary side. The inner peripheral surface 44a of the ring 44 is connected so that a step does not occur on the inner wall surface 45 of the outflow passage 18 on the secondary side located on the upstream side of the ring 44.

The ring 44 is provided with a through hole 46 connected to the suction tube 35. Therefore, the substantial opening of the suction tube 35 is extended into the ring 44.
The first passage 42 and the second passage 43 separated by the separator 41 are arranged in the operating direction of the valve body 25.

In the pressure reducing valve 11, the valve portion 25b of the valve body 25 is separated from the valve seat 22 to open the valve, so that the fluid flows as shown by arrows in FIGS. 1 and 4. In FIG. 4, the flow path of the fluid flowing at a high flow velocity and a high flow rate is indicated by a thick line arrow, and the flow path of the fluid flowing at a low flow velocity and a low flow rate is indicated by a thin line. The fluid flowing at a high flow velocity and a high flow rate flows through the path where the distance between the inlet (valve seat 22) of the valve opening 21 and the outflow passage 18 on the secondary side is the shortest. That is, this fluid flows through one communication passage 23a extending from the valve opening 21 toward the outflow passage 18 on the secondary side. The flow direction of this fluid is changed by entering the communication passage 23a from the valve opening 21, and the fluid flows toward the first passage 42 by inertia. On the other hand, the fluid flowing at a low flow velocity and a low flow rate flows from the valve opening 21 through the other communication passage 23b and the annular groove 24 into the outflow passage 18 on the secondary side. This fluid mainly flows into the second passage 43 so as to avoid the fluid flowing at a high flow velocity and a high flow rate.

In this way, in the pressure reducing valve 11, the fluid flowing at a high flow velocity and a high flow rate and the fluid flowing at a low flow velocity and a low flow rate are separated by the separator 41. Therefore, it is possible to prevent turbulence from occurring on the downstream side of the valve body 25 (the upstream end of the outflow passage 18 on the secondary side). If turbulence is unlikely to occur in the outflow passage 18 on the secondary side, the flow velocity of the fluid flowing near the opening of the suction tube 35 (opening of the through hole 46) will be higher than in the case where turbulence occurs. According to the so-called Bernoulli negative pressure principle, the fluid in the pressure chamber 34 is sucked out to the outflow passage 18 on the secondary side through the suction tube 354, and the pressure in the pressure chamber 34 decreases. In the following, the phenomenon in which the pressure in the pressure chamber 34 decreases due to Bernoulli's negative pressure principle is simply referred to as the "suction tube effect". In this embodiment, since the valve opening can be relatively increased at the time of a large flow rate due to the suction tube effect, it is possible to reliably prevent the pressure of the outflow passage 18 on the secondary side from dropping at the time of a large flow rate. can.

The pressure reducing valve 11 according to this embodiment is configured such that a fluid having a relatively high flow velocity flows through the first passage 42 and a fluid having a relatively low flow velocity flows through the second passage 43. Therefore, since the suction tube effect becomes more remarkable, the pressure of the outflow passage 18 on the secondary side at the time of a large flow rate can be relatively increased.

The separator 41 according to this embodiment is provided inside the ring 44 that fits into the wall surface of the outflow passage 18 on the secondary side. The ring 44 is provided with a through hole 46 connected to the suction tube 35. Therefore, since the separator 41 can be formed separately from the main body 12 and assembled to the main body 12, the pressure reducing valve 11 having the separator 41 can be easily manufactured.

(Modification example of separator)
The separator can be configured as shown in FIGS. 5-10. In FIGS. 5 to 10, the same or equivalent members as those described with reference to FIGS. 1 to 4 are designated by the same reference numerals, and detailed description thereof will be omitted as appropriate.
The separator 51 shown in FIG. 5 is formed so that the cross-sectional shape has an airfoil shape, and is provided inside the ring 44 as shown in FIG. The airfoil of the separator 41 is an airfoil called a Zhukovskiy wing. The separator 41 has a constant cross section from one end to the other end in the radial direction of the ring 44 with the leading edge 51a (see FIG. 7) located on the upstream side so that the flow velocity of the fluid flowing through the first passage 42 increases. It extends in shape.

As shown in FIG. 7, the chord wire 52 connecting the leading edge 51a and the trailing edge 51b of the separator 51 is inclined with respect to the axis C of the ring 44. The direction in which the chord line 52 is inclined with respect to the axis C is such that the first passage 42 gradually widens toward the downstream side in the direction in which the fluid flows. Further, the separator 41 is configured such that the maximum blade thickness position 51c faces the through hole 46 of the ring 44. That is, the suction tube 35 is positioned at a position facing the maximum blade thickness position 51c of the separator 41.

In the pressure reducing valve 11 using the airfoil-shaped separator 41, the flow velocity of the fluid increases as the fluid flows along the separator 41 in the first passage 42. That is, as shown by the thick line in FIG. 8, the fluid having a high flow velocity and a high flow rate flowing into the first passage 42 is accelerated in the first passage 42. In FIG. 8, the accelerated fluid is indicated by a white arrow.

When forming the separator so that the cross-sectional shape is an airfoil, the airfoil can be formed into a shape as shown in FIGS. 9 and 10.
The airfoil of the separator 61 shown in FIG. 9 is an airfoil called a flat-bottomed blade, and the second passage 43 side is formed substantially flat. The separator 61 is provided on the ring 44 so that the chord wire 62 connecting the leading edge 61a and the trailing edge 61b is parallel to the axis C of the ring 44. The through hole 46 of the ring 44 is provided at a position facing the maximum blade thickness position 61c of the separator 61.

The airfoil of the separator 63 shown in FIG. 10 is an airfoil called a symmetric wing, and is formed so as to be line-symmetrical about a chord line 64 connecting the leading edge 63a and the trailing edge 63b. Further, the chord wire 64 is parallel to the axis C of the ring 44. The through hole 46 of the ring 44 is provided at a position facing the maximum blade thickness position 63c of the separator 63.

By using the separators 51, 61, 63 having an airfoil-shaped cross section as shown in FIGS. 5 to 10, the separator itself does not cause turbulence and flows through the first passage 42. Combined with the ability to increase the flow velocity of the fluid, a large suction tube effect can be obtained. Therefore, also in this embodiment, the pressure difference between the pressure of the outflow passage 18 on the secondary side and the pressure of the pressure chamber 34 can be increased at the time of a large flow rate, so that the outflow passage 18 on the secondary side can be increased at the time of a large flow rate. It is possible to surely prevent the pressure from dropping.

In the pressure reducing valve 11 having the separators 51, 61, 63 having an airfoil-shaped cross section shown in FIGS. 5 to 10, the suction tube 35 is positioned at a position facing the maximum blade thickness positions 51c, 61c, 63c. Therefore, the suction tube 35 is opened at the position where the pressure is the lowest on the inner wall of the first passage 42, so that the suction tube effect is maximized.

In the pressure reducing valve 11 using the separator 41 shown in FIGS. 1 to 8, the suction tube effect as shown in FIG. 11 was obtained. FIG. 11 is a graph showing the volumetric flow rate of the fluid flowing through the outflow passage 18 on the secondary side and the pressure difference between the upstream side and the downstream side of the suction tube. The pressure difference is the pressure difference between the pressure at the opening of the suction tube 35 opening in the first passage 42 and the pressure inside the pressure chamber 34. In FIG. 11, the solid line shows the case where the cross-section airfoil type separator 51 shown in FIGS. 5 to 8 is used, and the broken line shows the case where the flat plate-shaped separator 41 shown in FIGS. 1 to 4 is used. Further, the alternate long and short dash line shows a case where a separator is not used as a comparative example.

As can be seen from FIG. 11, by using the separators 41 and 51, the pressure difference becomes large due to the suction tube effect at a large flow rate. In particular, when the cross-section airfoil separator 51 is used, the pressure difference becomes significantly large. It can be seen that when the separators 41 and 51 are not used, the pressure in the suction tube 35 rises due to the turbulent flow generated at the time of a large flow rate, which has an adverse effect.

When the cross-sectional shape of the separator is an airfoil, the shape of the airfoil is not limited to the shape shown in FIGS. 5 to 10. The same effect can be obtained regardless of the shape of the airfoil as long as the flow velocity of the fluid increases in the first passage 42.

11 ... Pressure reducing valve, 12 ... Main body, 14 ... Inlet, 15 ... Outlet, 16 ... Fluid passage, 17 ... Primary side inflow passage, 18 ... Secondary side outflow passage, 19 ... Air supply port (bulkhead) ), 21 ... Valve opening, 22 ... Valve seat, 25 ... Valve body, 25b ... Valve part, 31 ... Diaphragm, 34 ... Pressure chamber, 35 ... Suction tube (suction passage), 36 ... Pressure regulating spring, 41, 51, 61, 63 ... Separator, 42 ... First passage, 43 ... Second passage, 44 ... Ring, 46 ... Through hole, 51c, 61c, 63c ... Maximum blade thickness position.

Claims (5)

An actuator that applies a pre-adjusted pressing force and
It has an inflow port into which the fluid supplied from the fluid source flows in, and an outflow port in which the fluid flowing in from the inflow port flows out to the outside, and communicates the fluid between the inflow port and the outflow port. A main body with a fluid passage to flow, and
A partition wall provided in the main body and dividing the fluid passage into an inflow passage on the primary side and an outflow passage on the secondary side.
A valve seat provided around a valve opening that penetrates the partition wall and communicates the inflow passage on the primary side and the outflow passage on the secondary side.
A valve body that has a valve portion that sits on or separates from the valve seat and opens and closes the valve opening.
It is sandwiched between the actuator and the main body and stretched in a direction orthogonal to the operating direction of the valve body, and operates in the direction in which the valve opening opens in response to the pressing force from the actuator. Diaphragm to let
A pressure chamber that causes the pressure of the outflow passage on the secondary side to act on the diaphragm so that the valve body operates in the direction in which the valve opening closes.
In a pressure reducing valve having a spring that applies an urging force to the valve body in a direction in which the valve opening closes.
The outflow passage on the secondary side extends in a direction parallel to the extension direction of the diaphragm and extends toward the outflow port so as to be orthogonal to the operating direction of the valve body.
The main body body includes a suction passage that communicates the outflow passage on the secondary side and the pressure chamber, and a first passage through which the suction passage opens inside the outflow passage on the secondary side. A pressure reducing valve including a thin plate-shaped separator that divides into a second passage on the opposite side. In the pressure reducing valve according to claim 1,
A pressure reducing valve characterized in that a fluid having a relatively high flow velocity flows through the first passage and a fluid having a relatively low flow velocity flows through the second passage. In the pressure reducing valve according to claim 1 or 2.
The separator is provided inside a ring fitted to the wall surface of the outflow passage on the secondary side, and the ring is provided with a through hole connected to the suction passage. valve. In the pressure reducing valve according to any one of claims 1 to 3.
The separator is a pressure reducing valve which is formed so as to have an airfoil-shaped cross section and is configured to increase the flow velocity of a fluid flowing through the first passage. In the pressure reducing valve according to claim 4,
A pressure reducing valve characterized in that the suction passage is positioned at a position facing the maximum blade thickness position of the separator.

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