阅读说明：本技术 施力构件保持器及具备该施力构件保持器的减压阀 (Biasing member holder and pressure reducing valve provided with same ) 是由 井上和久 于 2020-03-18 设计创作，主要内容包括：本发明提供一种具有对在内部流动的流体进行整流的功能的阀芯施力构件保持器及具备该阀芯施力构件保持器的减压阀。具备阀芯施力构件的保持部(41)、具备在该保持部的周围形成的多个贯通孔(44)的流路形成部(43)、以及将流体导向所述多个贯通孔(44)的流体引导部(45)的施力构件保持器(40)及具备该施力构件保持器的减压阀(1)。(The invention provides a valve element biasing member holder having a function of rectifying fluid flowing inside and a pressure reducing valve having the same. A valve body biasing member includes a holding portion (41) having a valve body biasing member, a flow path forming portion (43) having a plurality of through holes (44) formed around the holding portion, and a biasing member holder (40) having a fluid guide portion (45) for guiding a fluid to the plurality of through holes (44), and a pressure reducing valve (1) having the biasing member holder.)

1. An urging member holder which defines a first space into which a fluid flows from outside and a second space in which a valve body for switching a flow path of the fluid and an urging member for urging the valve body in a predetermined direction are housed, and which holds the urging member, the urging member holder being characterized in that,

the disclosed device is provided with: a holding portion formed facing the second space; and a flow path forming part formed around the holding part,

the flow path forming portion has an outer peripheral edge that engages with an opening provided in a partition wall that partitions the first space and the second space,

a plurality of through holes communicating the first space and the second space are provided in the flow path forming portion,

a fluid guide portion that guides the fluid that has flowed into the first space to the plurality of through holes is formed facing the first space.

2. The apply member holder of claim 1,

the fluid guide portion includes a truncated cone-shaped protrusion portion that protrudes from a region that is provided inside the flow passage forming portion and faces the first space,

the plurality of through holes are open along a boundary portion between the protruding portion and the flow path forming portion.

3. The apply member holder of claim 2,

the top periphery of the protrusion is formed of a curved surface.

4. A force applying member holder according to any one of claims 1 to 3,

the holding portion is formed of a bottomed recess having a depth corresponding to the entire length of the biasing member when the biasing member is contracted, and the biasing member is fitted into the holding portion so as to be guided by the inner wall surface of the bottomed recess.

5. The biasing member holder according to any one of claims 1 to 4,

the plurality of through holes are circular holes having the same diameter, and are arranged at equal intervals in the circumferential direction of the surface of the flow path forming portion.

6. The biasing member holder according to any one of claims 1 to 4,

the plurality of through holes are circular holes having the same diameter, and are arranged at unequal intervals in the circumferential direction of the surface of the flow path forming portion.

7. The biasing member holder according to any one of claims 1 to 4,

the plurality of through holes are formed by at least two round holes with different apertures.

8. A pressure reducing valve is characterized by comprising:

the apply member holder of any of claims 1-7;

a container having an input chamber, an output chamber, and an exhaust chamber formed by the first space and the second space, an input flow path communicating with the input chamber, an output flow path communicating with the output chamber, and an exhaust hole communicating with the exhaust chamber, and a partition wall defining the input chamber and the output chamber and having a first communication hole communicating with the input chamber and the output chamber;

a diaphragm delimiting the output chamber and the exhaust chamber;

an exhaust port coupled to the diaphragm and having a valve hole communicating the output chamber and the exhaust chamber;

a second biasing member that biases the exhaust port toward the output chamber;

a guide member disposed at the output chamber side opening of the first communication hole, and including a second communication hole communicating the input chamber and the output chamber;

a poppet valve as the valve body includes: a shaft portion inserted and supported in the second communication hole; a first valve portion formed at one end of the shaft portion for closing a valve seat formed on the input chamber side of the second communication hole; and a second valve portion formed at the other end of the shaft portion and disposed opposite to the valve hole; and

the biasing member biases the poppet valve toward the output chamber.

9. A pressure reducing valve, characterized in that,

the biasing member retainer of claim 6 or 7;

a container having an input chamber, an output chamber, and an exhaust chamber formed by the first space and the second space, an input flow path communicating with the input chamber, an output flow path communicating with the output chamber, and an exhaust hole communicating with the exhaust chamber, and a partition wall defining the input chamber and the output chamber and having a first communication hole communicating with the input chamber and the output chamber;

a diaphragm delimiting the output chamber and the exhaust chamber;

an exhaust port coupled to the diaphragm and having a valve hole communicating the output chamber and the exhaust chamber;

a second biasing member that biases the exhaust port toward the output chamber;

a guide member disposed at the output chamber side opening of the first communication hole, and including a second communication hole communicating the input chamber and the output chamber;

a poppet valve as the valve body includes: a shaft portion inserted and supported in the second communication hole; a first valve portion formed at one end of the shaft portion for closing a valve seat formed on the input chamber side of the second communication hole; and a second valve portion formed at the other end of the shaft portion and disposed opposite to the valve hole; and

the urging member urging the poppet valve toward the output chamber,

the distance between the through holes adjacent to each other decreases as the distance from the opening of the input channel decreases.

10. A pressure reducing valve is characterized by comprising:

the apply member retainer of claim 7;

a container having an input chamber, an output chamber, and an exhaust chamber formed by the first space and the second space, an input flow path communicating with the input chamber, an output flow path communicating with the output chamber, and an exhaust hole communicating with the exhaust chamber, and a partition wall defining the input chamber and the output chamber and having a first communication hole communicating with the input chamber and the output chamber;

a diaphragm delimiting the output chamber and the exhaust chamber;

an exhaust port coupled to the diaphragm and having a valve hole communicating the output chamber and the exhaust chamber;

a second biasing member that biases the exhaust port toward the output chamber;

a guide member disposed at the output chamber side opening of the first communication hole, and including a second communication hole communicating the input chamber and the output chamber;

a poppet valve as the valve body includes: a shaft portion inserted and supported in the second communication hole; a first valve portion formed at one end of the shaft portion for closing a valve seat formed on the input chamber side of the second communication hole; and a second valve portion formed at the other end of the shaft portion and disposed opposite to the valve hole; and

the urging member urging the poppet valve toward the output chamber,

the diameters of the through holes increase as the distance from the opening of the input channel decreases.

Technical Field

The present invention relates to a fluid flow rate control device using a valve element and a holder of a valve element biasing member as a component thereof, and more particularly to a pressure reducing valve and a holder of a valve element biasing member as a component thereof.

Background

Conventionally, as one of fluid flow rate control devices, a pressure reducing valve is known which reduces the pressure of a fluid flowing through a flow path to a predetermined pressure and outputs the pressure. As one of the pressure reducing valves, there is a diaphragm type pressure reducing valve disclosed in patent document 1, which includes a diaphragm formed of a flexible material such as rubber as a movable pressure partition wall.

Fig. 25 is a sectional view showing an example of the diaphragm type pressure reducing valve. The diaphragm type pressure reducing valve 100 shown in the figure is configured such that: the first on-off valve that communicates and blocks the input chamber 106 and the output chamber 107, and the second on-off valve that communicates and blocks the output chamber 107 and the exhaust chamber 108 connected to the outside of the pressure reducing valve 100 alternately perform opposite operations.

The first opening/closing valve includes an opening portion on the input chamber 106 side of a through hole 191 provided in a guide member 109, and an umbrella-shaped first valve portion 115b provided at the input chamber 106 side end portion of the poppet valve 115, and the guide member 109 is disposed in a substantially cylindrical through hole 132 that opens in a partition wall 131 that partitions the input chamber 106 and the output chamber 107, more specifically, the guide member 109 is disposed in an opening portion on the output chamber 107 side of the through hole 132. The poppet valve 115 (first valve portion 115b) is biased toward the input chamber 106 side opening of the through hole 191 by the poppet spring 117.

Here, the lift spring 117 is disposed in a space region (hereinafter referred to as "space region 132 a") near the opening of the input chamber 106 of the through hole 132 and is supported on the spring holder 140 so as to be restricted from moving downward in fig. 25. As shown in fig. 26, the spring holder 140 is formed of a rectangular plate material, and an annular convex portion is provided to protrude from substantially the center thereof. The outer peripheral side surface of the convex portion is fitted to and connected to the lower inner peripheral side surface of the lift spring 117, whereby the movement of the lift spring 117 in the horizontal plane of fig. 25 is regulated. The spring holder 140 is held in a stationary state by placing the short side 140a thereof on a support portion provided vertically around the opening of the input chamber 106 of the through hole 132.

In fig. 25, although the input chamber 106 and the space region 132a are isolated by the spring holder 140 and the partition wall 131, a gap, not shown in the figure, is formed between the short side 140a of the spring holder 140 and the partition wall 131, and the input chamber 106 and the space region 132a communicate with each other via the gap. The space region 132a communicates with the output chamber 107 via the through hole 191.

The second opening/closing valve is constituted by the valve seat 110c and the end portion of the poppet valve 115 on the output chamber 107 side, more specifically, the top portion of the stem 115a of the poppet valve 115 (hereinafter referred to as "second valve portion 115 c"). The valve seat 110c is formed in a through hole 110a opened in an exhaust port 110 connected to the diaphragm 104 that separates the output chamber 107 and the exhaust chamber 108, and more specifically, is formed in an opening of the through hole 110a on the output chamber 107 side. The stem 115a of the poppet valve 115 is inserted and extended through the through hole 191 so as to face the through hole 110 a.

Here, the degree of the urging force of the pressure adjusting spring 123 against the diaphragm 104 can be adjusted by the pressure adjusting knob 121, whereby the pressure of the pressurized fluid output from the output chamber 107 (hereinafter referred to as "set pressure") can be set. The axial center of the second valve portion 115c (i.e., the axial center of the poppet valve 115) coincides with the axial center of the through hole 110a, so that the through hole 110a of the exhaust port 110 is blocked by the second valve portion 115c when the diaphragm 104 is pressed toward the output chamber 107.

The pressure reducing valve 100 configured as described above operates as follows. That is, when the diaphragm 104 moves toward the output chamber 107 by the biasing force of the pressure regulating spring 123, the exhaust port 110 coupled to the diaphragm 104 also moves in this direction. When the exhaust port 110 moves to a position of abutting against the second valve portion 115c of the poppet valve 115, the second opening and closing valve is closed. Further, when the movement of the exhaust port 110 in the above-described direction is continued, the poppet valve 115 also moves in the direction, the first valve portion 115b is separated from the input chamber 106 side opening portion of the through hole 191, and the first opening/closing valve is opened. When the pressurized fluid flows into the input chamber 106 through the input-side pipe or the like in a state where the first opening/closing valve is open and the second opening/closing valve is closed, the pressurized fluid enters the output chamber 107 from the input chamber 106 through the through hole 191 of the guide member 109, and is then output from the output chamber 107 through the pipe or the like.

In the above state, when a pressurized fluid of a set pressure or higher is input, the diaphragm 104 moves to the exhaust chamber 108, and the through hole 110a of the exhaust port 110 connected to the diaphragm 104 also moves in conjunction therewith. Then, the poppet valve 115 biased by the through hole 110a moves toward the exhaust chamber 108, in other words, toward the output chamber 107 by the biasing force of the poppet spring 117 in the process of releasing the biasing force. When the first valve portion 115b of the poppet valve 115 moves to and abuts the input chamber 106 side opening portion of the through hole 191a that opens in the guide member 109, the first opening/closing valve is closed. At this time, the poppet valve 115, which is biased by the poppet spring 117, is stationary at this position. In this state, when the diaphragm 104 moves further toward the exhaust chamber 108, the through hole 110a of the exhaust port 110 is separated from the second valve portion 115 c. In a state where the first opening/closing valve is closed and the second opening/closing valve is open, the pressurized fluid in the output chamber 107 flows into the exhaust chamber 108 through the through hole 110a of the exhaust port 110, and is discharged to the outside of the pressure reducing valve 100 through the exhaust hole 105 b. Through the above-described process, the pressure of the pressurized fluid in the output chamber 107 is reduced to the set pressure, and the reduced pressure fluid is output from the output chamber 107 to a device provided downstream through a pipe on the output side or the like.

[ Prior art documents ]

[ patent document 1]

Patent document 1: japanese patent laid-open No. 2015-210746

Disclosure of Invention

Problems to be solved by the invention

In the pressure reducing valve 100 configured as described above, the spring receiver 140 formed of a rectangular plate-like member is disposed in the through hole 132 (the space region 132a) formed in the flow path from the input chamber 106 to the output chamber 107. Therefore, the high-pressure high-flow-rate fluid directly collides with the spring holder 140, that is, the spring holder 140 exists in the flow path as a large flow path resistance. In the pressure reducing valve 100, a gap is formed between the short side 140a of the spring holder 140 and the partition wall 131, and a gap is not formed between the long side 140b of the spring holder 140 and the partition wall 131. Therefore, the flow path cross-sectional area from the input chamber 106 to the space region 132a becomes extremely small, causing pressure loss and a rapid change in flow velocity. Further, by offsetting the fluid flow path, the flow of the pressurized air from the input chamber 106 toward the space region 132a tends to be biased. As a result, a swirling flow or the like is generated in the flow of the pressurized air flowing from the input chamber 106 into the space region 132a, and variations in flow velocity, flux density, or the like are generated.

The flow of the pressurized air described above, that is, the flow of the pressurized fluid containing many unsteady flows such as drift flow, swirl flow, and turbulence and having variations in flow velocity, flux density, and the like adversely affects the flow rate characteristics of the pressure reducing valve 100, and causes a problem such as a decrease in the responsiveness of the pressure reducing valve 1. Further, the distribution of the pressure (pressing force) acting on the diaphragm 104 becomes uneven due to the disturbance of the flow of the pressurized air, and an undesirable situation such as the poppet valve 115 extending from the valve stem 115a swings in the through hole 191 constituting a part of the flow path is caused.

The present invention has been made in view of the above-described problems, and an object thereof is to provide a spring bearing (biasing member holder) that rectifies a flow of pressurized air from an input chamber to an output chamber, and a pressure reducing valve provided with the biasing member holder.

Means for solving the problems

In order to solve the above problem, the present invention provides an urging member holder (40) for holding an urging member while defining a first space (6, 32a) into which a fluid flows from the outside and a second space (32c) in which a valve body (15) for switching a flow path of the fluid and an urging member (17) for urging the valve body in a predetermined direction are housed, the urging member holder (40) comprising: a holding portion (41) formed facing the second space; and a flow path forming portion (43) formed around the holding portion, the flow path forming portion having an outer peripheral edge that engages with an opening portion (32a) provided in a partition wall (31) that separates the first space and the second space, a plurality of through holes (44) that communicate the first space and the second space being provided in the flow path forming portion, and a fluid guide portion (45) that guides the fluid that has flowed into the first space to the plurality of through holes being formed facing the first space.

In the biasing member holder, the fluid guide portion may include a truncated cone-shaped protrusion (45), the truncated cone-shaped protrusion (45) may be provided to protrude from an inner side of the flow passage forming portion and face a region of the first space, and the plurality of through holes may be opened along a boundary portion (46) between the protrusion and the flow passage forming portion.

Further, in the biasing member holder, a peripheral edge of a top portion of the bottomed protruding portion may be chamfered into a curved surface shape.

In the biasing member holder, the holding portion may be formed of a bottomed recess having a depth corresponding to the entire length of the biasing member when the biasing member is contracted, and the biasing member may be fitted into the holding portion so as to be guided by an inner wall surface of the bottomed recess.

Further, in the biasing member holder, the plurality of through holes may be circular holes having the same diameter and may be arranged at equal intervals in the circumferential direction of the surface of the flow passage forming portion.

In the biasing member holder, the plurality of through holes may be circular holes having the same diameter and may be arranged at unequal intervals in the circumferential direction on the surface of the flow path forming portion.

Further, in the biasing member holder, the plurality of through holes may be formed by at least two circular holes having different diameters.

In order to solve the above problem, the present invention provides a pressure reducing valve including: the force application member holder; a container (2, 3, 5) having an inlet chamber (6), an outlet chamber (7), and an exhaust chamber (8) formed by the first space and the second space, an inlet flow path (34) communicating with the inlet chamber, an outlet flow path (35) communicating with the outlet chamber, and an exhaust hole (5b) communicating with the exhaust chamber, and having a partition wall (31) defining the inlet chamber and the outlet chamber and having a first communication hole (32) communicating with the inlet chamber and the outlet chamber; a diaphragm (4) delimiting the output chamber and the exhaust chamber; an exhaust port (10) coupled to the diaphragm (4) and having a valve hole (10a) communicating the output chamber and the exhaust chamber; a second biasing member that biases the exhaust port toward the output chamber; a guide member (9) disposed at the output chamber side opening of the first communication hole (32), and having a second communication hole (91) for communicating the input chamber and the output chamber; a poppet valve (15) as the valve body, comprising: a shaft portion inserted and supported in the second communication hole; a first valve portion (15b) formed at one end of the shaft portion for closing a valve seat (91b) formed on the input chamber side of the second communication hole; and a second valve part (15c) formed at the other end of the shaft part and disposed opposite to the valve hole; and the said forcing member (17), it forces the said poppet valve to the said output chamber.

Further, the present invention for solving the above problems provides a pressure reducing valve including: the force application member holder; a container (2, 3, 5) having an inlet chamber (6), an outlet chamber (7), and an exhaust chamber (8) formed by the first space and the second space, an inlet flow path (34) communicating with the inlet chamber, an outlet flow path (35) communicating with the outlet chamber, and an exhaust hole (5b) communicating with the exhaust chamber, and having a partition wall (31) defining the inlet chamber and the outlet chamber and having a first communication hole (32) communicating with the inlet chamber and the outlet chamber; a diaphragm (4) delimiting the output chamber and the exhaust chamber; an exhaust port (10) coupled to the diaphragm (4) and having a valve hole (10a) communicating the output chamber and the exhaust chamber; a second biasing member that biases the exhaust port toward the output chamber; a guide member (9) disposed at the output chamber side opening of the first communication hole (32), and having a second communication hole (91) for communicating the input chamber and the output chamber; a poppet valve (15) as the valve body, comprising: a shaft portion inserted and supported in the second communication hole; a first valve portion (15b) formed at one end of the shaft portion for closing a valve seat (91b) formed on the input chamber side of the second communication hole; and a second valve part (15c) formed at the other end of the shaft part and disposed opposite to the valve hole; and the said forcing member (17), it forces the said poppet valve to the said output chamber, the interval of adjacent of the said multiple through holes diminishes as the distance from opening of the said input flow path shortens.

In order to solve the above problem, the present invention provides a pressure reducing valve including: the force application member holder; a container (2, 3, 5) having an inlet chamber (6), an outlet chamber (7), and an exhaust chamber (8) formed by the first space and the second space, an inlet flow path (34) communicating with the inlet chamber, an outlet flow path (35) communicating with the outlet chamber, and an exhaust hole (5b) communicating with the exhaust chamber, and having a partition wall (31) defining the inlet chamber and the outlet chamber and having a first communication hole (32) communicating with the inlet chamber and the outlet chamber; a diaphragm (4) delimiting the output chamber and the exhaust chamber; an exhaust port (10) coupled to the diaphragm (4) and having a valve hole (10a) communicating the output chamber and the exhaust chamber; a second biasing member that biases the exhaust port toward the output chamber; a guide member (9) disposed at the output chamber side opening of the first communication hole (32), and having a second communication hole (91) for communicating the input chamber and the output chamber; a poppet valve (15) as the valve body, comprising: a shaft portion inserted and supported in the second communication hole; a first valve portion (15b) formed at one end of the shaft portion for closing a valve seat (91b) formed on the input chamber side of the second communication hole; a second valve part (15c) formed at the other end of the shaft part and disposed opposite to the valve hole; and the said forcing member (17), it forces the said poppet valve to the said output chamber, the aperture of the said multiple through holes increases as the distance from opening of the said input flow path shortens.

ADVANTAGEOUS EFFECTS OF INVENTION

According to the present invention, since the bias of the fluid flow path due to the presence of the spring bearing in the fluid flow path is not generated, the flow of the pressurized air becomes uniform. Further, according to the present invention, since a large flow path cross-sectional area can be ensured, flow path resistance is suppressed, and pressure loss is reduced. Further, according to the present invention, the biasing member holder (spring seat) functions as a rectifying plate, and thus unstable flow (drift, swirl, and turbulence) is suppressed in the flow of the pressurized air passing through the biasing member holder, and the flow rate characteristic of the pressure reducing valve is improved. Further, according to the present invention, the above-described effects can be achieved by merely changing the low-cost specifications of the biasing member holder (spring holder) without changing the shapes of peripheral components such as products, bodies, filters, and filter covers.

Drawings

Fig. 1 is a sectional view showing a structure of a pressure reducing valve according to an embodiment of the present invention.

Fig. 2 is an enlarged view of a main portion of fig. 1.

Fig. 3 is an enlarged view of a main portion of fig. 1.

Fig. 4 is a diagram showing an urging member holder (spring seat), a poppet valve, and a poppet spring used in the pressure reducing valve according to the embodiment of the present invention.

Fig. 5 is a diagram showing an urging member holder (spring seat), a poppet valve, and a poppet spring used in the pressure reducing valve according to the embodiment of the present invention.

Fig. 6 is a plan view of an urging member holder (spring bearing) used in the pressure reducing valve according to the embodiment of the present invention.

Fig. 7 is a bottom view of an urging member holder (spring bearing) used in the pressure reducing valve according to the embodiment of the present invention.

Fig. 8 is a cross-sectional view taken along line P-P of an urging member holder (spring support) used in the pressure reducing valve according to the embodiment of the present invention.

Fig. 9 is a diagram showing a simulation result relating to a fluid trajectory of the pressure reducing valve according to the embodiment of the present invention.

Fig. 10 is a diagram showing a simulation result relating to a fluid trajectory of the pressure reducing valve according to the embodiment of the present invention.

Fig. 11 is a simplified diagram showing a simulation result relating to a fluid trajectory of the pressure reducing valve according to the embodiment of the present invention.

Fig. 12 is a simplified diagram showing the simulation results regarding the fluid trajectory of the pressure reducing valve according to the embodiment of the present invention.

Fig. 13 is a diagram showing a simulation result relating to a fluid trajectory of a conventional pressure reducing valve.

Fig. 14 is a diagram showing a simulation result relating to a fluid trajectory of a conventional pressure reducing valve.

Fig. 15 is a simplified diagram showing a simulation result relating to a fluid trajectory of a conventional pressure reducing valve.

Fig. 16 is a simplified diagram showing a simulation result relating to a fluid trajectory of a conventional pressure reducing valve.

Fig. 17 is a cross-sectional view taken along line P-P of a modification of the biasing member holder (spring support) used in the pressure reducing valve according to the embodiment of the present invention.

Fig. 18 is a cross-sectional view taken along line P-P of a modification of the biasing member holder (spring support) used in the pressure reducing valve according to the embodiment of the present invention.

Fig. 19 is a cross-sectional view taken along line P-P of a modification of the biasing member holder (spring support) used in the pressure reducing valve according to the embodiment of the present invention.

Fig. 20 is an enlarged view of a main part of a sectional view showing a structure of a pressure reducing valve according to another embodiment of the present invention.

Fig. 21 is a plan view of an urging member holder (spring bearing) used in a pressure reducing valve according to another embodiment of the present invention.

Fig. 22 is an enlarged view of a main part of a sectional view showing a structure of a pressure reducing valve according to another embodiment of the present invention.

Fig. 23 is a plan view of an urging member holder (spring bearing) used in a pressure reducing valve according to another embodiment of the present invention.

Fig. 24 is a cross-sectional view taken along line P '-P' of an urging member holder (spring support) used in a pressure reducing valve according to another embodiment of the present invention.

Fig. 25 is a sectional view showing a structure of a conventional pressure reducing valve.

Fig. 26 is a diagram showing an urging member holder (spring seat), a poppet valve, and a poppet spring used in a conventional pressure reducing valve.

Detailed Description

Embodiments of an urging member holder (spring bearing 40) and a pressure reducing valve 1 including the same according to the present invention will be described with reference to fig. 1 to 24. In the specification, the vertical direction, the horizontal direction, and the front-rear direction are defined as the vertical direction, the horizontal direction, and the direction perpendicular to the paper surface of the pressure reducing valve 1 shown in fig. 1, respectively.

[ constitution of urging member holder and pressure reducing valve ]

First, the structure of the biasing member holder (spring receiver 40) and the pressure reducing valve 1 including the biasing member holder will be described with reference to fig. 1 to 8. Although a part of the configuration overlaps with the configuration of the pressure reducing valve 100, the overlapping portion will be described again.

Fig. 1 is a sectional view of a spring bearing 40 and a pressure reducing valve 1 including the spring bearing 40 according to the present embodiment, and fig. 2 is an enlarged sectional view of a main portion of the present invention, that is, the periphery of a biasing member holder (spring bearing 40) according to the present embodiment.

The pressure reducing valve 1 includes a filter cover 2 having a cylindrical shape with a bottom, a cylindrical center body 3, a diaphragm 4, and a valve cover 5 having a cylindrical shape with a top, and these components are stacked in this order to constitute a container of the pressure reducing valve 1. An inlet chamber 6, an outlet chamber 7, and an exhaust chamber 8 are formed in the container.

The filter cover 2 is a bottomed cylindrical member, and is formed of, for example, a casting made of an aluminum alloy, and a drain bolt 11 is screwed to the bottom thereof. The flange 2a formed at the upper end of the filter cover 2 abuts against the outer edge of the center body 3 on the inlet chamber 6 side via a gasket 12, and is joined to the center body 3 via bolts 13. An opening portion communicating between the central body 3 and the filter cover 2 is formed in a part of the joint portion, and a filter 14 made of sponge, stainless steel mesh, or the like for removing dust is provided in the opening portion. In addition, the other part of the opening communicates with an input flow path 34 described later, and thereby the internal space of the filter cover 2 functions as a part of an input chamber 6 (corresponding to the "first space" described in the claims) into which the pressurized fluid flows from the outside.

The central body 3 is a cylindrical member, and is formed of a casting made of an aluminum alloy, for example, as in the filter cover 2. The center body 3 is provided with a partition wall 31 extending substantially perpendicularly to the central axis CL of the pressure reducing valve 1 as a part of the inner wall, and forms a space serving as a part of the input chamber 6 and a space serving as the output chamber 7 with the partition wall 31 interposed therebetween.

The space forming a part of the input chamber 6 is a space formed below the partition wall 31, and forms the input chamber 6 together with the internal space of the filter cover 2. Thus, the inlet chamber 6 is formed as a space defined by the inner wall of the center body 3 including the lower surface of the partition wall 31 and the inner wall of the filter cover 2.

The outlet chamber 7 is a space formed between the diaphragm 4 and the partition wall 31, and is defined by the inner wall of the center body 3 including the upper surface of the partition wall 31 and the diaphragm 4. Between the output chamber 7 and the input chamber 6, a second communication hole 91 described later is opened, and the input chamber 6 side opening portion of the second communication hole 91 is similarly closed or opened by a first valve portion 15b provided in a poppet valve 15 described later, whereby these two chambers are communicated or not communicated. When the output chamber 7 communicates with the input chamber 6, pressurized air flows from the input chamber 6, and the pressurized air is output to a device disposed downstream of the pressure reducing valve 1 through the output flow path 35.

Further, the details of the switching manner of communication/non-communication between the input chamber 6 and the output chamber 7 will be described later.

A first communication hole 32 having openings on the input chamber 6 side and the output chamber 7 side is provided at substantially the center of the partition wall 31 in a plan view. On the input chamber 6 side of the first communication hole 32, a cylindrical opening 32a is formed (the space inside the opening 32a is included in the input chamber 6 and forms a part of the "first space" described in the claims), specifically, an outer peripheral edge portion of a spring holder 40 (corresponding to an "urging member holder" described in the claims) described later, more specifically, a flow path forming portion 43 is embedded by, for example, press-fitting so as to be accommodated in the opening 32 a. Further, a cylindrical opening 32b having a smaller diameter than the input chamber 6 is formed in the first communication hole 32 on the output chamber 7 side, and a guide member 9 described later is fixed to the opening 32b by, for example, press fitting.

Further, the intermediate portion of the first communication hole 32 has a truncated cone shape, and a space region 32c (a space corresponding to a part of the "second space" described in the claims) for accommodating the lift spring 17 described later is formed.

Further, an input flow path 34 and an output flow path 35 are formed in the center body 3, one end of the input flow path 34 opens to the outer surface of the center body 3, the other end opens to the opening portion formed at the joint portion of the center body 3 and the filter cover 2, one end of the output flow path 35 opens to the inside of the output chamber 7, and the other end opens to the outer surface of the center body 3. The input flow path 34 is connected to a pipe (not shown) for introducing a pressurized fluid from the outside, and the output flow path 35 is connected to a pipe (not shown) for sending the pressurized fluid to a control device or the like.

Inside the central body 3 configured as described above, the guide member 9, the poppet valve 15, the poppet spring 17, and the spring holder 40, which will be described below, are disposed at predetermined positions.

As described above, the guide member 9 is a member fixedly provided to the opening 32b on the output chamber 7 side of the first communication hole 32 by press fitting, for example. The guide member 9 is a columnar member, and a second communication hole 91 is formed in the center portion thereof so as to communicate the input chamber 6 and the output chamber 7, and the second communication hole 91 extends along the center axis CL of the pressure reducing valve 1. The second communication hole 91 supports a stem 15a of a poppet valve 15, which will be described later, by being inserted therein. An end 91a is formed on the output chamber 7 side of the second communication hole 91, and a valve seat 91b is formed on the input chamber 6 side of the second communication hole 91. The first valve part 15b of the poppet valve 15 described later abuts on the valve seat 91 b.

As shown in fig. 4 and 5, the poppet valve 15 is composed of a valve rod 15a and a first valve portion 15b that engages with a lower end portion (end portion on the input chamber 6 side) of the valve rod 15a, and is formed of, for example, brass or stainless steel.

The stem 15a is a rod-shaped portion extending along the central axis CL of the pressure reducing valve 1, and is inserted and supported in the second communication hole 91 of the guide member 9. The upper end portion (end portion on the output chamber 7 side) of the valve rod 15a is dome-shaped, and functions as a second opening/closing valve by coming into contact with or separating from a through hole 10a provided in an exhaust port 10 described later, more specifically, a valve seat 10c formed at the output chamber 7 side end portion of the through hole 10a (hereinafter, the upper end portion of the valve rod 15a is referred to as a "second valve portion 15 c"). Here, the through hole 10a of the exhaust port 10, more specifically, the valve seat 10c and the second valve portion 15c of the poppet valve 15 are disposed to face each other along the center axis CL. In addition, the outer diameter of the stem 15a is formed smaller than the inner diameter of the second communication hole 91 so as to form a fluid flow path between the stem 15a and the second communication hole 91 opened in the guide member 9.

The first valve portion 15b is a portion housed in a substantially truncated cone-shaped space region 32c formed in the middle of the first communication hole 32, and has a substantially truncated cone-shaped upper portion joined to the valve rod 15a and a cylindrical lower portion. Further, a part of the upper substantially conical table portion of the first valve portion 15b is disposed along the center axis CL so as to face the valve seat 91b formed at the input chamber 6 side end portion of the second communication hole 91, and the two portions are in contact with or separated from each other, thereby constituting a first opening/closing valve for opening/closing the second communication hole 91. Therefore, the outer diameter of the first valve portion 15b is formed larger than the inner diameter of the second communication hole 91.

A cylindrical projecting portion projects from the bottom surface of the first valve portion 15b facing the input chamber 6. The outer peripheral side surface of the convex portion is engaged with an inner peripheral side surface of a lift spring 17 (corresponding to an "urging member" described in the claims) described later, whereby the poppet valve 15 is placed on the lift spring 17 so as to be restricted from moving in a plane having the center axis CL as a normal line.

The poppet spring 17 is a member that biases the poppet valve 15 toward the output chamber 7, and is formed of, for example, a coil spring made of stainless steel wire as shown in fig. 5. The second valve portion 15c formed at the end portion of the poppet valve 15 on the output chamber 7 side protrudes from the end portion 91a of the second communication hole 91 on the output chamber 7 side due to the biasing force of the poppet spring 17. The lift spring 17 is positioned with a predetermined accuracy by a spring support 40 described later, and the lift spring 17 is supported while suppressing bending of the main body.

As described above, the spring holder 40 is embedded in the input chamber 6 side opening 32a of the first communication hole 32 by press-fitting, for example. As shown in fig. 2 to 8, the spring support 40 has a disk shape bulging downward toward the center of the bottom of the input chamber 6. The spring holder 40 has a space area 32c between itself and the guide member 9, in which the lift spring 17 (and the first valve portion 15b of the lift valve 15) is housed, and a cylindrical recess 41 (corresponding to the "holding portion" described in the claims) into which the lift spring 17 is fitted is provided at a central portion of a surface facing the space area 32c by, for example, cutting with predetermined accuracy. The depth of the recess 41 is substantially the same as the length of the lift spring 17 at the maximum contraction time, for example. An annular groove 42 is cut in the bottom of the recess 41. The lift spring 17 is fitted with its lower portion fitted in the groove portion 42, and its outer peripheral side surface is fitted in contact with the inner peripheral side wall surface of the recess 41. Thus, the lift spring 17 is positioned by the groove portion 42 with a predetermined accuracy, and is guided and supported by the inner peripheral wall surface of the recess 41 so as to be extendable and retractable.

In addition, the diameter of the concave portion 41 needs to be larger than the diameter of the lift spring 17 in consideration of the assembling property, the sliding resistance, and the like, but in order to suppress the bending of the main body of the lift spring 17, it is preferable to set the difference to a predetermined value or less.

A flow path forming portion 43 is formed on the outer periphery of the recessed portion 41, the flow path forming portion 43 is formed in an annular shape (plate-like flange shape) defining the outer peripheral edge of the spring holder 40, and further, for example, 10 cylindrical through holes 44 extending along the center axis CL of the communication opening portion 32a and the space region 32c are arranged at substantially equal intervals in a plan view on the flow path forming portion 43. The pressurized fluid that has flowed into the input chamber 6 through the input flow path 34 (more specifically, a part of the space of the input chamber 6 located below the spring bearing 40) flows into the space region 32c through the through hole 44, and is then introduced into the output chamber 7 through the second communication hole 91.

Further, the upper surface of the spring support 40 facing the space area 32c is a substantially flat surface, and the space area 32c side opening edge of the through hole 44 and the opening edge of the recess 41 are formed in the same horizontal plane in fig. 1.

The opening diameter, the overall length, and the shape of the introduction portion (the shape of the opening on the opening 32a side) of the through hole 44 are appropriately set in consideration of the flow regulation effect of the fluid, the pressure loss, and the like. For example, the opening diameter (flow path cross-sectional area) of the through hole 44 may be set as large as possible from the viewpoint of suppressing the pressure loss and the flow velocity change. In addition, the opening diameter (flow path cross-sectional area) of the through hole 44 may be changed in consideration of the streamline of the pressurized fluid from the input flow path 34 to the through hole 44 so that the pressurized fluid smoothly flows into the through hole 44. In addition, the entire length of the through-hole 44 may be set to a length equal to or greater than a predetermined value, for example, in consideration of the rectifying effect.

The length of the through hole 44 is defined by the thickness of the flow path forming portion 43, but in the present embodiment, the thickness of the flow path forming portion 43 is determined by the depth of the concave portion 41 into which the lift spring 17 is fitted, from the viewpoint of space efficiency (downsizing). Therefore, in the present embodiment, the length of the through hole 44 is substantially equal to the depth of the recess 41.

As described above, the spring holder 40 is fixed to the partition wall 31 by being press-fitted into the inlet chamber 6 side opening 32a of the first communication hole 32 that opens in the partition wall 31. Therefore, the outer diameter of the flow path forming portion 43 is slightly larger than the opening diameter of the first communication hole 32 provided in the partition wall 31 on the input chamber 6 side. The method of fixing the spring holder 40 is not limited to press fitting, and may be a fixing method using a snap ring or the like. In either fixing method, it is preferable that the outer peripheral side wall surface of the spring bearing 40 and the inner peripheral side wall surface of the opening 32a abut against each other over the entire peripheral edge in order not to form a gap between the outer peripheral side wall surface and the inner peripheral side wall surface, from the viewpoint of avoiding an offset of the fluid flow path and a rapid change in the cross-sectional area of the fluid flow path. Therefore, the outer peripheral edge shape of the spring holder 40 and the opening shape of the opening 32a are preferably complementary shapes that engage with each other.

As described above, the spring holder 40, more specifically, the flow path forming portion 43 of the spring holder 40 is embedded and housed in the inner space of the opening portion 32 a. That is, the opening of the inlet chamber 6 of the through hole 44 disposed in the flow path forming portion 43 is positioned in the space inside the opening 32a and is positioned closer to the outlet chamber 7 than the opening edge of the opening 32 a. Thus, the opening portion 32a having a relatively large opening diameter and the through hole 44 having a relatively small opening diameter are connected to each other in the fluid flow path, and the cross-sectional area of the fluid flow path in the vicinity of the spring bearing 40 changes from large to small. Further, by providing the protrusion 45 described later, the fluid flow path cross-sectional area in the vicinity of the spring bearing 40 can be configured to be continuously changed. Such a configuration is useful for reducing the pressure loss associated with the change in the cross-sectional area of the fluid flow path.

The bulge formed at the bottom center facing the input chamber 6 (hereinafter referred to as "protrusion 45". the "protrusion 45" corresponds to the "fluid guide" described in the claims), for example, has a height substantially equal to the thickness of the flow path forming portion 43, and has a truncated conical shape formed such that the outer diameter gradually increases toward the boundary portion 46 with the flow path forming portion 43. The periphery of the top (bottom) of the protrusion 45 is formed of, for example, a curved surface having a radius of curvature equal to the height.

The height of the protruding portion 45 may be set so as to be accommodated in, for example, the space inside the input chamber 6 side opening portion 32a of the first communication hole 32. At this time, the top (bottom) of the projection 45 is disposed above the opening edge of the opening 32a (on the output chamber 7 side) in fig. 1 and 2.

Further, the 10 through holes 44 disposed in the flow path forming portion 43 may be disposed along, for example, the boundary portion 46 with the protruding portion 45. Further, a part of the opening edge of the through hole 44 may overlap the boundary portion 46, and the overlapping portion and the side surface 45a of the protruding portion 45 may be formed of a continuous curved surface.

The projection 45 having the above-described configuration functions as a "fluid guide" for guiding the fluid flowing into the input chamber 6 to the through hole 44. This point will be described in detail in [ effect of the present embodiment ].

The diaphragm 4 is a film-like member having a substantially circular shape in plan view, and is formed of a flexible material such as nitrile rubber, for example, and has an outer diameter substantially equal to that of the upper surface of the center body 3. The diaphragm 4 is disposed between the center body 3 and the bonnet 5 with its outer edge sandwiched between the end surface of the center body 3 on the side of the output chamber 7 and the end surface of the bonnet 5 on the side of the output chamber 7.

An exhaust port 10 is provided on the output chamber side surface of the diaphragm 4 so as to be connected to the diaphragm 4. The exhaust port 10 is a disk-shaped member, for example, formed of brass. The outer diameter of the exhaust port 10 is formed smaller than the outer diameter of the diaphragm 4 and the opening of the center body 3 on the side of the output chamber 7. A columnar protruding portion 10b is formed in the center of the surface of the exhaust port 10 on the side abutting against the diaphragm 4. The protruding portion 10b is inserted through a through hole formed in the center portion of the diaphragm 4, and protrudes from the surface of the diaphragm 4 on the exhaust chamber 8 side. Further, a through hole 10a (corresponding to a "valve hole" in the claims) extending along the center axis CL is opened in the center of the exhaust port 10, and thereby the output chamber 7 and the exhaust chamber 8 partitioned by the diaphragm 4 communicate with each other. A valve seat 10c that abuts against the second valve portion 15c of the poppet valve 15 is formed at the end of the through hole 10a on the output chamber 7 side. The valve seat 10c is disposed to face the second valve portion 15c, and abuts against the second valve portion 15c when the diaphragm 4 moves toward the output chamber 7.

Further, an area plate 18 is disposed on the surface of the diaphragm 4 on the exhaust chamber 8 side. The area plate 18 is a disk-shaped member, for example, formed of brass. The outer diameter of the area plate 18 is smaller than the outer diameter of the diaphragm 4 and a bottom opening of the bonnet 5 described later. The area plate 18 is fixed to the upper surface of the diaphragm 4 in a state where the protruding portion 10b of the exhaust port 10 is inserted into a through hole formed in the center portion of the area plate 18. Further, a pressure regulating spring 23 (corresponding to "second biasing member" described in the claims) described later abuts on the surface of the area plate 18 on the exhaust chamber 8 side.

The bonnet 5 is a cylindrical member having a top formed of, for example, an aluminum alloy, and has a flange 5a formed at a lower end thereof so as to face an outer peripheral edge portion of an upper surface of the center body 3 on the exhaust chamber 8 side. Further, bolt through holes are opened in the flange 5a, and the bolt through holes are engaged with bolt holes formed in the outer peripheral edge portion of the center body 3.

After the bonnet 5 is placed on the outer peripheral edge of the central body 3 on which the diaphragm 4 is placed, the bolt 19 inserted into the bolt through hole is screwed into the bolt hole, whereby the bonnet 5 and the central body 3 are coupled to each other. At this time, the diaphragm 4 is fixed at its outer periphery in such a manner as to be sandwiched by the center body 3 and the bonnet 5.

The space defined by the diaphragm 4 and the inner wall of the bonnet 5 functions as an exhaust chamber 8. In the exhaust chamber 8, the pressurized fluid flows from the output chamber 7 through a through hole 10a (corresponding to a "valve hole" in the claims) opened in an exhaust port 10 connected to the diaphragm 4, and the inflowing pressurized fluid is discharged to the outside of the pressure reducing valve 1 through an exhaust hole 5b opened in a side surface of the bonnet 5.

A pressure adjustment knob 21 is screwed to the top of the bonnet 5. The pressure adjustment knob 21 is composed of a knob 21a and a shaft 21b, one end of the shaft 21b is fixed to the knob 21a, the other end is positioned in the bonnet 5, and the shaft 21b is screwed to the top of the bonnet 5 so as to be movable along the center axis CL of the bonnet 5.

A pressure adjusting spring holder 22 made of, for example, a steel material is disposed in the bonnet 5 near the other end of the shaft 21b of the pressure adjusting knob 21, and a pressure adjusting spring 23 made of, for example, a coil spring made of a spring steel material is disposed between the pressure adjusting spring holder 22 and the surface plate 18 fixed to the diaphragm 4.

[ operating mode of pressure reducing valve ]

Next, an operation mode of the pressure reducing valve 1 of the present embodiment will be described.

In the pressure reducing valve 1, the pressure of the fluid to be output, in other words, the pressure of the fluid at the time of starting pressure reduction is set by operating the pressure regulating knob 21. For example, when the pressure adjustment knob 21 is screwed into the bonnet 5, the lower end portion of the shaft 21b presses the pressure adjustment spring 23 downward (toward the diaphragm 4) along the center axis CL via the pressure adjustment spring holder 22, and the diaphragm 4 moves downward along the center axis CL toward the output chamber 7 by the urging force of the pressure adjustment spring 23. Here, as described above, the valve seat 10c of the exhaust port 10 and the second valve portion 15c of the poppet valve 15 are disposed to face each other along the center axis CL. Therefore, when the diaphragm 4 moves downward along the center axis CL, the valve seat 10c of the exhaust port 10 connected thereto moves toward the second valve portion 15c and abuts against it (i.e., the second opening/closing valve is closed). When the pressure regulating knob 21 is further screwed in, the poppet valve 15 moves toward the input chamber 6, and the first valve portion 15b separates from the valve seat 91b formed at the end of the second communication hole 91 on the input chamber 6 side (i.e., the first opening/closing valve is opened). Thereby, the input chamber 6 and the output chamber 7 are communicated via the second communication hole 91.

In a state where the first opening/closing valve is open and the second opening/closing valve is closed, the input chamber 6 and the output chamber 7 communicate with each other, and the exhaust chamber 8 is isolated from these two chambers, so that the pressurized fluid supplied into the input chamber 6 through a pipe or the like connected to the input flow path 34 flows between the first valve portion 15b and the valve seat 91b, flows into the second communication hole 91, reaches the output chamber 7, and is output to the pipe or the like through the output flow path 35 communicating with the output chamber 7.

Here, the urging force F1 of the pressure adjusting spring 23 generated in proportion to the amount of screwing of the pressure adjusting knob 21 acts on the upper surfaces of the diaphragm 4 and the exhaust port 10, and the pressing force F2 from the pressurized fluid in the output chamber 7 acts on the bottom surface thereof. When the pressing force F2 becomes greater than the pressing force F1, as described below, the first valve portion 15b provided in the poppet valve 15 abuts against the valve seat 91b formed at the end portion of the second communication hole 91 on the input chamber 6 side, the first opening/closing valve is closed, the valve seat 10c provided in the exhaust port 10 is separated from the second valve portion 15c provided in the poppet valve 15, and the second opening/closing valve is opened. At this time, the output chamber 7 and the exhaust chamber 8 communicate with each other, whereby the pressurized air in the output chamber 7 is discharged, and as a result, the pressure is reduced.

Thus, the fluid pressure in the output chamber 7 at the time of starting the pressure reduction depends on the magnitude of the force F1. Therefore, the magnitude of the biasing force F1 can be adjusted by the amount of screwing of the pressure adjustment knob 21, thereby setting the fluid pressure in the output chamber 7 (hereinafter, the fluid pressure thus set is referred to as "set pressure").

In a case where the pressure within the output chamber 7 (hereinafter referred to as "output pressure") does not exceed the set pressure, that is, in a case where the pressing force F2 is equal to or less than the acting force F1, a downward force toward the output chamber 7 of the forces acting on the diaphragm 4 is dominant. Therefore, the diaphragm 4 does not move upward toward the exhaust chamber 8, and the second opening/closing valve is maintained in a closed state (a state in which the valve seat 10c of the exhaust port 10 is in contact with the second valve portion 15c of the poppet valve 15). On the other hand, the first opening/closing valve is also maintained in an open state (a state in which the first valve portion 15b provided in the poppet valve 15 is separated from the valve seat 91b formed at the end of the second communication hole 91 on the input chamber 6 side). Therefore, the pressurized fluid flowing from the input chamber 6 into the output chamber 7 is directly output from the output flow path 35.

On the other hand, when the output pressure exceeds the set pressure, that is, when the pressing force F2 is greater than the acting force F1, the upward force toward the exhaust chamber 8 is dominant among the forces acting on the diaphragm 4, and therefore, the diaphragm 4 moves upward toward the exhaust chamber 8. At this time, the poppet valve 15 is urged by the poppet spring 17 to move upward toward the output chamber 7. As a result, the first valve portion 15b provided in the poppet valve 15 abuts on the valve seat 91b formed at the end of the second communication hole 91 on the input chamber 6 side, and closes the second communication hole 91, that is, closes the first opening/closing valve. Thereby, the input chamber 6 and the output chamber 7 are brought into a non-communicating state, and the supply of the pressurized fluid from the input chamber 6 to the output chamber 7 is stopped, thereby suppressing the increase in the output pressure.

When the output pressure is higher than the set pressure, the diaphragm 4 moves upward toward the exhaust chamber 8, the valve seat 10c of the exhaust port 10 is separated from the second valve portion 15c of the poppet valve 15, and the second opening/closing valve is opened. At this time, since the output chamber 7 and the exhaust chamber 8 are in a state of communication, the pressurized air in the output chamber 7 flows into the exhaust chamber 8 through the through hole 10a and is then discharged to the outside through the exhaust hole 5b opened in the bonnet 5. As a result, the output pressure decreases, and the pressurized air in the output chamber 7 is depressurized.

When the pressurized fluid is discharged from the exhaust port 5b and the output pressure is lower than the set pressure, the diaphragm 4 is moved downward again toward the output chamber 7 by the pressure-regulating spring 23, and the valve seat 10c of the exhaust port 10 abuts against the second valve portion 15c of the poppet valve 15, thereby closing the through hole 10a of the exhaust port 10 (i.e., closing the second opening/closing valve). Thereby, the discharge of the pressurized fluid from the exhaust hole 5b is stopped. Further, if the output pressure is lower than the set pressure, the poppet valve 15 is pressed against the input chamber 6 via the valve seat 10c of the exhaust port 10, and as a result, the first valve portion 15b is separated from the valve seat 91b formed at the end of the second communication hole 91 on the input chamber 6 side (i.e., the first opening/closing valve is opened.). Thereby, the input chamber 6 and the output chamber 7 (output flow path 35) communicate again via the second communication hole 91, and the pressurized air in the input chamber 6 flows into the output chamber 7. Then, the pressure reducing valve 1 repeats the above operation to adjust the pressure of the fluid flowing into the device disposed downstream so as not to exceed the set pressure (the pressure of the fluid is maintained at the set pressure).

[ Effect of the present embodiment ]

In a conventional pressure reducing valve, for example, the pressure reducing valve 100 of the invention described in patent document 1, as described above, the rectangular spring holder 140 is supported and fixed on the support portion provided in a hanging manner around the opening portion on the input chamber 106 side of the through hole 132 provided in the partition wall 131, and the flow path from the input chamber 106 to the through hole 132 is formed only along the short side 140a of the rectangle. Therefore, the rectangular spring seat 140 obstructs the flow of the pressurized fluid flowing into the input chamber 106, and the pressurized fluid flowing into the input chamber 106 is unevenly distributed through the offset flow path, passes through the through-holes 132 with the flow of the swirling flow, and is then guided to the output chamber 107. This phenomenon is a phenomenon confirmed by a simulation relating to the flow of the pressurized fluid, which will be described later. The above-described problem is conspicuously caused in the conventional pressure reducing valve 100 in which the pressurized fluid that is not uniform and flows along with the swirling flow flows into the output chamber 107.

In contrast, in the present embodiment, 10 through holes 44 are opened at substantially equal intervals in a plan view in order to secure as large an opening area as possible in consideration of the strength and rigidity of the flow path forming portion 43. Therefore, in the present embodiment, the flow path cross-sectional area around the spring bearing 40 can be ensured to be larger than that of the conventional pressure reducing valve 100, and the offset of the flow path is not seen. Therefore, according to the present embodiment, it is possible to favorably suppress a change in the flow velocity and a pressure loss (pressure drop) of the pressurized fluid due to the presence of the spring bearing 40 in the flow path, and to realize a uniform flow in which a drift is suppressed. Further, by providing the relatively long through holes 44, a high rectifying effect can be obtained, and unstable flow (drift, swirl, turbulence) in the flow of the pressurized fluid can be suppressed well. These effects are useful in solving the above-described problems.

In addition, according to the present embodiment in which the protrusion 45 is provided on the bottom surface of the spring bearing 40 facing the input chamber 6, the pressurized fluid in the input chamber 6 is smoothly guided to the through hole 44, and an effect of suppressing an unsteady flow (a drift flow, a swirl flow, or a turbulent flow) is exerted.

More specifically, when the flow rate of the pressurized fluid flowing into the input chamber 6 from the input flow path 34 is large, a part of the pressurized fluid is directly sucked into the through hole 44 by the pressure difference, and the rest of the pressurized fluid is guided to the through hole 44 while colliding with the bottom surface portions of the filter cover 2, the partition wall 31, and the spring seat 40 defining the input chamber 6. Here, in the protruding portion 45 provided in the present embodiment, as described above, the surface thereof is formed of a curved surface having a predetermined radius of curvature, and further, 10 through holes 44 are arranged uniformly along the periphery (boundary portion 46). Therefore, the pressurized fluid colliding with the protrusion 45 is smoothly guided to any one of the through holes 44. In addition, the flow of the pressurized fluid colliding with the protrusion 45 is not excessively disturbed by being formed by the curved surface.

In this way, the protrusion 45 functions as a "fluid guide" for guiding the pressurized fluid to the through hole 44, and has an effect of suppressing an unsteady flow (a drift flow, a swirl flow, or a turbulent flow). This function and effect are more remarkably exhibited when a part of the opening periphery of the through hole 44 overlaps the boundary portion 46, and the overlapped portion and the side surface 45a (see fig. 7 and 8) of the protruding portion 45 are formed of a continuous curved surface. The pressurized fluid passing through the through hole 44 is guided to the output chamber 7 through the second communication hole 91 while being rectified to be uniform and in a predetermined direction (for example, a direction along the axial center of the through hole 44, that is, along the central axis CL of the pressure reducing valve 1). As a result, the above-described problem caused by the disturbance of the flow of the pressurized fluid can be solved satisfactorily.

In the spring holder 40, more specifically, in the spring holder 40 of the present embodiment embedded so that the flow path forming portion 43 of the spring holder 40 is accommodated in the space inside the opening portion 32a, the opening portion 32a having a relatively large opening diameter and the through hole 44 having a relatively small opening diameter are connected in the fluid flow path as described above. Further, in the present embodiment in which the substantially truncated cone-shaped protrusion 45 is disposed in the space inside the opening 32a, the cross-sectional area of the fluid flow path in the vicinity of the spring bearing 40 changes continuously from large to small. With this configuration, the pressure loss associated with the change in the cross-sectional area of the fluid flow path can be reduced.

In addition, according to the present embodiment, the above-described rectifying effect can be achieved only by changing the configuration of the spring holder 40. Therefore, the influence on the product shape, the component shape, and the cost can be suppressed to the minimum.

Further, according to the present embodiment in which the lift spring 17 is held by the concave portion 41 having a depth substantially equal to the maximum contracted length of the lift spring 17, the inner peripheral side wall of the concave portion 41 serves as a guide surface, and the main body of the lift spring 17 can be prevented from being bent. Therefore, fluctuation of the movement axis of the poppet valve 15 can be suppressed well. This can avoid the valve seat 10c of the exhaust port 10 from coming into contact with one end of the second valve part 15c of the poppet valve 15, and can prevent the deterioration of the sealing property due to the uneven wear of the second valve part 15c of the poppet valve 15.

Further, in the spring bearing 40 of the present embodiment, a plurality of through holes 44 are opened around the recess 41 formed to house the lift spring 17, and the length of the plurality of through holes 44 is substantially the same as the depth of the recess 41, and the opening edge of the recess 41 and the opening edge of the space area 32c side of the through hole 44 are formed on the same horizontal plane. In this way, the above-described effects and space efficiency (particularly, reduction in thickness) can be achieved at the same time by the spring bearing 40 in which the recess 41 having a predetermined depth and the plurality of through holes 44 having a predetermined length are formed in substantially the same horizontal plane.

[ validation simulation relating to rectification effect ]

In the pressure reducing valve 1 of the present embodiment and the conventional pressure reducing valve 100, a simulation regarding the trajectory of the pressurized fluid was performed under a predetermined boundary condition, and the rectifying effect of the present embodiment was verified.

Fig. 9 and 10 are diagrams showing the results of simulations on the fluid trajectory performed on the pressure reducing valve 1 of the present embodiment, and fig. 11 and 12 are diagrams showing only the main streamlines S1 and S2 based on the results of the simulations. Fig. 9 and 11 show the fluid trajectory of the pressure reducing valve 1 in a front view, and fig. 10 and 12 show the fluid trajectory of the pressure reducing valve 1 in a side view.

The boundary conditions are, for example, air as the fluid, an ambient pressure of 400kPs and a volume flow of 0.0033m³The temperature was 293K. The dimensions of the spring holder 40 are set such that, when the input chamber 6-side opening diameter of the first communication hole 32 and the outer diameter D of the spring holder 40 are set to 10, the length L of the through hole 44 is substantially 2.5, the height t2 of the visible protrusion is substantially 2.5, and the diameter Φ D2 of the through hole 44 is substantially 1.

Fig. 13 and 14 are diagrams showing the results of simulations on the fluid trajectory performed on the conventional pressure reducing valve 100, and fig. 15 and 16 are diagrams showing only main flow lines S '1 and S'2 based on the results of the simulations. Fig. 13 and 15 show the fluid trajectory of the pressure reducing valve 100 in a front view, and fig. 14 and 16 show the fluid trajectory of the pressure reducing valve 100 in a side view. In addition, the boundary conditions are similar to the above conditions except for the conditions relating to the size of the spring bearing 140, and the conditions relating to the size of the spring bearing 140 are such that when the input chamber 106 side opening diameter of the through hole 132 is 10, the short side 140a of the spring bearing 140 included in the pressure reducing valve 100 is substantially 5, the long side 140b is substantially 10, and the plate thickness (height) is substantially 2.

In the conventional pressure reducing valve 100, since the flow path around the spring seat 140 is biased, a region 106a (see fig. 13) where no fluid locus is visible exists in the vicinity of a portion where the flow path is not formed in the input chamber 106. In addition, in the pressurized fluid guided to the upper side of the spring bearing 140 through the limited flow path having a small flow path cross-sectional area, a swirling flow R is generated due to a rapid change in flow velocity, fluid resistance, or the like, and the distribution of the flow line (flow velocity density) is not uniform (see fig. 13 and 14).

In contrast, in the pressure reducing valve 1 of the present embodiment, since no offset is observed in the flow path around the spring seat 40, the fluid locus is observed in substantially the entire region in the input chamber 6 (see fig. 9 and 10). Further, by arranging 10 through holes 44 substantially uniformly and providing the protrusions 45 for guiding the fluid in the through holes 44, the pressurized fluid is guided to the through holes 44 smoothly and substantially uniformly, and the flow of the pressurized fluid passing through the spring bearing 40 is also substantially uniform, and disturbance such as a swirling flow is not observed.

As is clear from the above simulation results, according to the spring bearing 40 and the pressure reducing valve 1 including the spring bearing 40 of the present embodiment, the flow of the pressurized fluid passing through the spring bearing is significantly stabilized as compared with the conventional spring bearing 140 and the pressure reducing valve 100 including the spring bearing 140. Therefore, according to the spring bearing 40 and the pressure reducing valve 1 including the spring bearing 40 of the present embodiment, since the flow of the pressurized fluid flowing into the output chamber 7 is also stable, the pressure applied to the diaphragm 4 becomes uniform, and the movement axis center of the poppet valve 15 can be suppressed from being disturbed by the flow of the pressurized fluid, so that the above-described problem can be satisfactorily solved.

[ modified example of the present embodiment ]

As another modification of the present embodiment, for example, there is a spring holder 40-2 shown in fig. 17. The lower surface of the spring holder 40-2 facing the opening 32a of the flow path forming portion 43-2 forms a substantially truncated conical surface (a substantially truncated conical side surface), and the boundary portion 46-2 between the lower surface and the side surface 45a-2 of the protrusion 45-2 is formed by a continuous curved surface. Here, the protrusion 45-2 forms a substantially truncated conical surface (a side surface of a substantially truncated cone) having a larger inclination angle than the lower surface of the flow path forming portion 43-2, and is connected to the peripheral edge of the substantially flat top portion (bottom portion) by a continuous curved surface (in other words, the peripheral edge of the top portion (bottom portion) is formed by a curved surface).

In the spring support 40-2 of this configuration, the lower surface thereof has a nearly streamlined shape. Accordingly, the pressurized fluid flowing in from the input path 34 is guided toward the through hole 44-2 along the lower surface of the spring support 40-2. Therefore, according to the pressure reducing valve 1-2 including the spring seat 40-2, unstable flow (drift, swirl, and turbulence) in the flow of the pressurized fluid can be suppressed well.

As another modification related to the basic shape of the spring holder 40, for example, a spring holder having a cross-sectional shape as shown in fig. 18 and 19 is used. These modifications are characterized by the shape of the introduction portion of the through hole 44 (the shape of the opening portion on the opening portion 32a side), and for example, in the spring holder 40-3 shown in fig. 18, the introduction portion opening peripheral edge 44 α -3 of the through hole 44-3 is formed by a curved surface, and in the spring holder 40-4 shown in fig. 19, the introduction portion opening peripheral edge 44 α -4 of the through hole 44-4 is formed by a substantially frustoconical surface (a side surface of a substantially truncated cone). This reduces the change in the cross-sectional area of the flow path in the through-hole, thereby reducing the pressure loss.

As another modification of the present embodiment, for example, there is a spring holder 40-5 shown in fig. 20 and 21. Here, fig. 20 is a partially enlarged view of the pressure reducing valve 1-5 having the spring receiver 40-5, and fig. 21 is a plan view of the spring receiver 40-5.

The spring holder 40 is different from the spring holder 40-5 in the adjacent interval of the through holes provided in the flow path forming portion 43-5. That is, of the through holes 44 of the spring bearing 40, the adjacent intervals of the plurality of through holes 44 are all substantially the same, whereas, of the through holes 44-5a to 44-5j of the spring bearing 40-5, as shown in fig. 21, the adjacent intervals of the through holes 44-5a, 44-5b, and 44-5c disposed on the side close to the opening of the input flow path 34 communicating with the input chamber 6 are set smaller than the adjacent intervals of the farthest through holes 44-5h, 44-5i, and 44-5 j.

According to the spring bearing 40-5 and the pressure reducing valve 1-5 including the spring bearing configured as described above, the flow passage opening area per unit area of the region close to the input flow passage 34 is larger than the flow passage opening area per unit area of the region apart from the input flow passage 34. According to this configuration, most of the pressurized fluid flowing from the input channel 34 into the input chamber 6 is efficiently sucked through the through holes 44-5a, 44-5b, and 44-5c located in front. Therefore, even if a large amount of the pressurized fluid exists, most of the pressurized fluid is directly sucked into the through holes 44-5a to 44-5j, whereby the pressure loss and the like of the pressurized fluid can be suppressed to be small.

Further, as another modification of the present embodiment, for example, there is a spring holder 40-6 shown in fig. 22 to 24. Here, fig. 22 is a partially enlarged view of the pressure reducing valve 1-3 having the spring holder 40-6, fig. 23 is a plan view of the spring holder 40-6, and fig. 24 is a cross-sectional view of the spring holder 40-6 taken along line P '-P'.

The spring holder 40 of the present embodiment is different from the spring holder 40-6 as a modification thereof in the hole diameter of the through hole provided in the flow path forming portion 43-6. That is, the through holes 44 of the spring bearing 40 are all the same in diameter, whereas the through holes 44-6a to 44-6j of the spring bearing 40-6 are set so that the diameter gradually decreases from the through hole 44-6a having the shortest distance from the opening of the input channel 34 communicating with the input chamber 6 to the through hole 44-6j having the longest distance as shown in fig. 22 and 23 (in other words, the diameter of the through holes 44-6a to 44-6j is set so that the diameter increases as the distance from the opening of the input channel 34 facing the input chamber 6 decreases).

According to the spring seat 40-6 and the pressure reducing valve 1-6 including the spring seat 40-6 having the above-described configuration, the pressurized fluid flowing from the input flow path 34 into the input chamber 6 is guided more smoothly to the through holes 44-6a to 44-6 j.

Specifically, in the present embodiment in which the opening of the input flow path 34 facing the input chamber 6 is directed downward, the pressurized fluid flowing into the input chamber 6 from the input flow path 34 once flows downward and then flows toward the through holes 44-6a to 44-6j communicating with the output chamber 7 having a low pressure. Here, when a large amount of pressurized fluid is present, a part of the pressurized fluid is directly sucked into the through holes 44-6a to 44-6j, and the remaining part is guided to the through holes 44-6a to 44-6j while colliding with the inner wall of the filter cover 2 defining the input chamber 6, the partition wall 31, the bottom surface portion of the spring holder, and the like. Here, in order to suppress pressure loss or the like without disturbing the flow of the pressurized air, it is preferable that the flows (flow lines) from the opening of the input flow path 34 to the through holes 44-6a to 44-6j do not interfere with each other and that more pressurized fluid is directly sucked to the through holes 44-6a to 44-6 j. As a method for realizing such a flow, for example, in order to cause the pressurized fluid flowing into the input chamber 6 from the opening of the input flow path 34 to reach the through holes 44-6a to 44-6j substantially simultaneously and be sucked, it is useful to design so that the flow velocity is increased in proportion to the distance from the opening of the input flow path 34 to each of the through holes 44-6a to 44-6j (in other words, the flow velocity is decreased in inverse proportion to the distance). In the spring bearing 40-6 according to the modification of the present embodiment, focusing on the phenomenon that the flow velocity is decreased as the hole diameter is larger, the hole diameter is configured to be larger as the distance is shorter, thereby realizing the desired flow of the pressurized fluid.

As another modification, a spring holder having a groove in a bottom surface thereof on the side of the input chamber 6 may be used. The groove may extend from, for example, the substantial center of the bottom surface to each through hole 44, and the pressurized fluid may be guided to each through hole 44 along the groove. The groove may be provided on the surface of the projection 45, or may be provided on the flat bottom surface without providing the projection 45.

Further, as another modification, the opening shape of the through hole 44 may be a shape other than a circle, for example, an ellipse, depending on the flow pattern of the pressurized fluid that varies depending on the opening position of the input flow path 34, the shape of the input chamber 6, and the like.

In the spring bearing 40 of the present embodiment, the height of the projecting portion 45 is set so as to be accommodated in the space inside the opening 32a on the input chamber 6 side of the first communication hole 32, but the top portion may be set to exceed the set range, that is, the top portion may be set so as to project further toward the filter cover 2 side (lower side in fig. 1) than the opening edge of the opening 32a, within a range not interfering with the filter 14 existing between the filter cover 2 and the center body 3. The shape of the protruding portion 45 may be other than a substantially truncated cone, for example, a substantially conical shape.

In the present embodiment, any of a liquid and a gas can be used as the pressurized fluid to be input to and output from the pressure reducing valve 1.

While the embodiments of the present invention have been described above, the present invention is not limited to the embodiments, and various modifications can be made without departing from the scope of the invention. Even a configuration that is not directly described in the specification and the drawings is within the scope of the technical idea of the present invention as long as the operation and effect of the present invention are achieved. In the embodiments described above and shown in the drawings, the contents of the descriptions may be combined as long as the objects, the structures, and the like are not contradictory.

Description of the symbols

1 … pressure reducing valve, 2 … filter cover, 3 … central body, 4 … diaphragm, 5 … valve cover, 5a … flange, 5b … exhaust hole, 6 … input chamber, 7 … output chamber, 8 … exhaust chamber, 9 … guide member, 10 … exhaust port, 10a … through hole, 10b … projection, 11 … discharge bolt, 12 … washer, 13 … bolt, 14 … filter, 15 … poppet valve, 15a … stem, 15b … first valve part, 15c … second valve part, 17 … lifting spring, 18 … area plate, 19 … bolt, 21 … knob, 21a … knob, 21b … shaft, 22 … pressure regulating spring, 23 … pressure regulating spring, 31 … partition, 32 … first connecting hole, 32a … opening part, 32b … opening part, 34 … input flow path 35, … output flow path 40, … seat, … flow path seat, … concave part, … forming flow path, 44 … through hole, 45 … bottom protrusion, 46 … boundary, 91 … second through hole, 91a … end, 91b … valve seat.