JP7706738B2 - Flow Control Unit, Fluid Control Valve - Google Patents

Description

The present invention relates to a flow rate adjustment unit that is used in connection with a fluid supply source, such as an oxygen cylinder, to adjust the flow rate of the fluid.

Conventionally, for example, oxygen cylinders used in home oxygen therapy are connected to a fluid adjustment valve that adjusts the flow rate and pressure of oxygen gas. This fluid adjustment valve has a built-in pressure adjustment unit and flow rate adjustment unit, making it possible to adjust the pressure and flow rate of oxygen gas. Fluid adjustment valves include continuous supply valves that continuously supply gas such as oxygen, and respiration-synchronized valves that supply gas in synchronization with the user's breathing.

As shown in Patent Document 1, the flow rate adjustment unit built into the fluid adjustment valve includes a flow rate adjustment plate that adjusts the flow rate. This flow rate adjustment plate has a number of through holes (orifice holes) with different inner diameters (pressure loss) aligned in the circumferential direction. This flow rate adjustment plate is pressed against the flow path forming surface that forms the flow path by the biasing force of a spring. A fixed side flow path hole is formed in the flow path forming surface. When the flow rate adjustment plate is rotated with a knob, the fixed side flow path hole and a specific orifice hole are opposed and communicated, so the flow rate can be selectively determined.

The flow passage forming surface has an annular groove (ring groove) that surrounds the flow passage hole on the fixed side, and an O-ring is held in this annular groove. The O-ring is crushed by the force of the spring described above, and the gap between the flow passage on the fixed side and the orifice hole becomes a highly airtight space.

JP2003-247695

In the flow rate adjustment unit, the O-ring slides against the flow rate adjustment plate each time the flow rate is adjusted. At this time, because the flow rate adjustment plate has an orifice hole formed therein, the elastically deforming O-ring is likely to get caught in the orifice hole. When the O-ring elastically deforms due to the sliding between the O-ring and the flow rate adjustment plate, the O-ring pops out of the annular groove and gets caught between the flow rate adjustment plate and the flow path formation surface. When scratches are formed on the surface of the O-ring, the airtightness provided by the O-ring decreases, and the accuracy of flow rate adjustment deteriorates.

Furthermore, once the O-ring completely comes out of the annular groove, it cannot return to its original position (ring groove). As a result, the flow rate control function will no longer function properly. Therefore, the O-ring must be replaced.

On the other hand, if the pressing force (spring force) on the O-ring is weakened in order to prevent this problem, the airtightness provided by the O-ring is likely to decrease. In particular, the accuracy of adjusting the flow rate of high-pressure fluid is likely to deteriorate.

The present invention was made in consideration of the above-mentioned circumstances, and aims to provide a flow control unit etc. that can adjust the flow rate stably and with high accuracy over a long period of time.

The present invention, which achieves the above object, is a flow rate adjustment unit for adjusting the flow rate of a fluid, comprising: a first main flow path forming section in which a first main flow path is formed; a first branch flow path forming section in which a plurality of first branch flow paths branched from the first main flow path and having different pressure losses are formed; a second flow path forming section in which a second flow path communicating with at least one of the plurality of first branch flow paths is formed; a first opposing surface provided in the first branch flow path forming section and having a first branch opening which is an open end of the plurality of first branch flow paths; a second opposing surface provided in the second flow path forming section and having a second opening which is an open end of the second flow path and which faces the first opposing surface at a distance; A flow rate adjustment unit comprising: a relative movement mechanism for selecting a first branch flow path; a ring groove portion recessed into the first or second opposing surface so as to surround the periphery of the first branch opening or the periphery of the second opening; and a ring member disposed in the ring groove portion and partially protruding from the ring groove to abut against the first or second opposing surface (hereinafter, the opposing opposing surface), which is the opposing side. The ring groove portion satisfies Wm>Fm when the maximum groove depth in the axial direction is Wm and the maximum groove thickness obtained by dividing the difference between the maximum outer diameter and the minimum inner diameter is Fm; and the ring member before receiving an axial external force in the ring groove portion satisfies Wr>Fr when the maximum ring width in the axial direction is Wr and the maximum ring thickness obtained by dividing the difference between the maximum outer diameter and the minimum inner diameter is Fr.

In relation to the above-mentioned flow rate adjustment unit, a gap (hereinafter, outer circumferential gap) may be formed between the outer circumferential edge of the opening in the ring groove portion and the ring member before it is subjected to an axial external force in the ring groove portion.

In relation to the above-mentioned flow rate adjustment unit, a gap (hereinafter, inner circumferential gap) may be formed between the inner circumferential edge of the opening in the ring groove portion and the ring member before it is subjected to an axial external force in the ring groove portion.

In relation to the above flow rate adjustment unit, when the axial opening side of the ring groove portion is defined as the axial front side and the bottom side as the axial rear side, the outer peripheral side gap and/or the inner peripheral side gap may be characterized in that they extend from the outer peripheral edge or the inner peripheral edge toward the axial rear side by 10% or more of the maximum groove depth Wm.

In relation to the above flow rate adjustment unit, the outer peripheral gap or the inner peripheral gap may be characterized as being 5% or more of the maximum groove thickness Fm.

In relation to the above flow rate adjustment unit, when the open end side in the axial direction of the ring groove portion is defined as the axial front side, and the bottom side in the axial direction is defined as the axial rear side, and a cross section along the central axis of the ring member is defined as a ring cross section, the ring cross section may have a front-side convex region that is convex toward the axial front side, and the front-side convex region may include a curved portion with a radius of curvature of less than Fm/2.

In relation to the above-mentioned flow rate adjustment unit, when a cross section along the radial and axial directions of the ring member is defined as a ring cross section, the ring cross section may be characterized in that it has an outer recessed area that is concave in the range facing the outer wall of the ring groove portion.

The flow rate adjustment unit may be characterized in that it has an outer convex region that is convex in the area of the ring cross section that faces the outer wall of the ring groove portion, and the outer concave region is formed on both sides of the outer convex region.

The flow rate adjustment unit may be characterized in that it has a plurality of outer convex regions that are convex in the area of the ring cross section that faces the outer wall of the ring groove portion, and the outer concave region is formed between the plurality of outer convex regions.

In relation to the above-mentioned flow rate adjustment unit, when a cross section along the radial and axial directions of the ring member is defined as a ring cross section, the ring cross section may be characterized in that it has an inner recessed area that is concave in the range facing the inner wall of the ring groove portion.

The flow rate adjustment unit may be characterized in that it has an inner convex region that is convex in the area of the ring cross section that faces the inner wall of the ring groove portion, and the outer concave region is formed on both sides of the inner convex region.

The flow rate adjustment unit may be characterized in that it has a plurality of inner convex regions that are convex in the area of the ring cross section that faces the inner wall of the ring groove portion, and the inner concave region is formed between the plurality of inner convex regions.

In relation to the above flow rate adjustment unit, the inner convex area may be characterized in that it includes a curved portion having a radius of curvature of Wr/2 or less.

In relation to the above flow rate adjustment unit, the inner convex region may be characterized in that it includes a curved portion having a radius of curvature equal to or less than Fr.

The present invention, which achieves the above object, is a fluid regulation valve that regulates the flow of a fluid, characterized in that it comprises a pressure regulation unit that regulates the pressure of the fluid, and a flow rate regulation unit described above, into which the fluid whose pressure is regulated by the pressure regulation unit is guided.

The present invention makes it possible to obtain a flow rate adjustment unit that can adjust the flow rate stably and with high precision over a long period of time.

FIG. 1A is a cross-sectional view showing the overall configuration of a flow control unit according to a first embodiment of the present invention, and FIG. 1B is a diagram showing the flow guide display mode shown on a handle end cover of the same flow control unit. 4 is a perspective view showing the flow rate adjusting unit with some components disassembled. FIG. 3 is an enlarged cross-sectional view showing a portion of the flow rate adjusting unit. FIG. 3 is an enlarged cross-sectional view showing a portion of the flow rate adjusting unit. FIG. 1A is a plan view of the ring member of the flow rate adjustment unit, and FIG. 1B and FIG. 1C are cross-sectional views taken along the line II-II of FIG. 4 is an enlarged cross-sectional view of the vicinity of a ring groove and a ring member of the flow rate regulating unit as viewed from a ring radial direction. FIG. 4A is an enlarged plan view of the vicinity of a ring member of the flow rate adjusting unit as viewed from the axial direction, and FIG. 4B is an enlarged cross-sectional view of the ring member as viewed from the radial direction. 10A to 10C are enlarged cross-sectional views of the vicinity of a ring member of a conventional flow rate adjusting unit as viewed from a radial direction. 1A is a plan view of a ring member alone relating to a first modified example of the same flow control unit, FIG. 1B is a cross-sectional view taken along the line II-II of FIG. 1A, and FIG. 1C is an enlarged cross-sectional view of a flow control unit using the same ring member, viewed from the ring radial direction. 1A is a plan view of a ring member alone for a second modified example of the same flow control unit, FIG. 1B is a cross-sectional view taken along the line II-II of FIG. 1A, and FIG. 1C is an enlarged cross-sectional view of a flow control unit using the same ring member as viewed from the radial direction of the ring. FIG. 11 is an overall cross-sectional view of a flow rate adjusting unit according to a third modified example. 11A is a diagram showing a cylinder residual pressure display mode for a fluid regulating valve according to a second embodiment of the present invention, and FIG. 11B is a side view of the same fluid regulating valve. 4A is a partial cross-sectional plan view of the fluid regulating valve, and FIG. 4B is a front view of the fluid regulating valve. 11 is a partially enlarged cross-sectional view showing a modified example of the flow rate adjusting unit of the present embodiment. FIG.

The following describes an embodiment of the present invention with reference to the attached drawings.

First embodiment (flow rate adjusting unit)
1 shows an overall configuration of a flow rate adjusting unit 1 according to a first embodiment of the present invention. Note that, although a case where the flow rate adjusting unit 1 adjusts the flow rate of a gas (e.g., oxygen gas) as a fluid is illustrated here, the flow rate adjusting unit 1 may adjust the flow rate of a liquid.

The flow rate adjustment unit 1 comprises a main body 10, a main shaft 60 rotatably supported by the main body 10, a flow rate adjustment plate 30 integrally formed near one end of the main shaft 60, a handle 40 connected to the other end of the main shaft 60 so as not to rotate relative to the main shaft 60, and a flow path forming body 50 fixed to the main body 10 so as to surround the flow rate adjustment plate 30. For ease of explanation, the handle 40 side in the figure (left side in the figure) may be referred to as the axial rear side and the flow path forming body 50 side in the figure (right side in the figure) as the axial front side, based on the axial direction E of the main shaft 60.

<Main body>
The main body 10 is a cylindrical member, and a main shaft hole 11 that accommodates the main shaft 60 is formed therein. Furthermore, a second flow passage 12 through which gas flows is formed in the main body 10. With the axial direction E of the main shaft 60 as a reference, a second opposing surface 14 that faces the first opposing surface 32 of the flow rate adjustment plate 30 is formed at the front end of the main body 10 in the axial direction E. A second opening 12A, which is one end of the second flow passage 12, is formed in the second opposing surface 14. The other open end 12B of the second flow passage 12 reaches the side surface of the main body 10. A joint 70 is connected to this open end 12B.

As shown in an enlarged view in FIG. 2, the second opposing surface 14 is recessed with a ring groove portion 16 that is an annular groove surrounding the second opening 12A. A ring member 100 is accommodated in the ring groove portion 16. In addition, a plurality of (here, two) auxiliary ring groove portions 26 are recessed into the second opposing surface 14. A first auxiliary ring member 27 and a second auxiliary ring member 28 are accommodated in each of the auxiliary ring groove portions 26. The axial direction J of the ring groove portion 16 and the auxiliary ring groove portion 26 is parallel to the axial direction E of the main body portion 10. The ring groove portion 16 and the auxiliary ring groove portion 26 are arranged at equal intervals in the circumferential direction. In this embodiment, one ring groove portion 16 and two auxiliary ring groove portions 26 are formed, so that a total of three ring grooves are arranged at 120 degree intervals in the circumferential direction. The ring member 100 plays a role of increasing the airtightness of the flow path by being pressed against the second opposing surface 14. The first auxiliary ring member 27 and the second auxiliary ring member 28 arranged in the auxiliary ring groove 26 serve to homogenize the external force that the second opposing surface 14 receives from the ring member 100 in the circumferential direction. Therefore, the second auxiliary ring member 28 is not required to have a fluid sealing function, so it has a cross-sectional shape (e.g., rectangular) that makes it difficult to remove from the auxiliary ring groove 26. In addition, in order to suppress sliding resistance, it is preferable to select a material with low friction for the second auxiliary ring member 28, or to select a material that has been surface-treated to reduce surface friction, such as Teflon (registered trademark). In order to generate the desired repulsive force, at least one of the first auxiliary ring member 27 and the second auxiliary ring member 28 is selected from an elastic material such as rubber.

Returning to FIG. 1, a seal groove 11A extending in the circumferential direction is formed on the inner circumferential surface of the main shaft hole 11 of the main body 10. A seal ring 24 is housed in this seal groove 11A, and when this seal ring 24 is pressed against the main shaft 60, the first main flow passage 54 described below becomes a highly airtight space. Similarly, a seal groove 13 extending in the circumferential direction is formed on the outer circumferential surface of the main body 10. A seal ring 25 is housed in this seal groove 13, and when this seal ring 25 is pressed against the inner circumferential surface of the flow passage forming body 50, the first main flow passage 54 becomes a highly airtight space.

<Main shaft, flow rate adjustment plate, handle>
The main shaft 60 is a rod-shaped member extending in the axial direction E. A flow rate adjustment plate 30 is integrally formed near one end of the main shaft 60. The other side of the main shaft 60 protrudes from the main body 10, and a male threaded portion 64 is formed near the other end. The handle 40 is inserted into the male threaded portion 64. A female threaded body 66 that screws into the male threaded portion 64 prevents the handle 40 from slipping out. A ring-shaped spacer 49 is interposed between the handle 40 and the main body 10, allowing them to rotate relative to each other.

A through hole 42 extending in the axial direction is formed in the center of the handle 40, and the main shaft 60 is inserted into this through hole 42. An engagement portion 62 having an irregular cross section, such as a key groove or D-cut, is formed at the back side of the main shaft 60 in the axial direction E. The through hole 42 of the handle 40 has an engagement region 43 and a pressure-receiving region 44. The engagement region 43 is a hole with a non-circular cross section, and engages with the engagement portion 62 of the main shaft 60 in the circumferential direction. The pressure-receiving region 44 is adjacent to the back side of the engagement region 43 in the axial direction E, and the inner diameter of the pressure-receiving region 44 is larger than that of the engagement region 43, forming a step 44A at the boundary between them. A gap is formed between the pressure-receiving region 44 and the main shaft 60, and the spring 46 is accommodated in this gap. The female threaded body 66 presses the spring 46 through the spacer 48 to contract the spring 46. One of the restoring forces of the spring 46 is transmitted to the step 44A (handle 40), and then to the main body 10 via the spacer 49. The other of the restoring forces of the spring 46 is transmitted to the female threaded body 66 via the spacer 48, and then to the flow rate adjustment plate 30 via the main shaft 60. In other words, the restoring force of the spring 46 becomes an external force that brings the first opposing surface 32 and the second opposing surface 14 closer together. A handle end face cover 68 is fixed to the other end of the main shaft 60, and as shown in FIG. 1(B), a guide is displayed to the effect that the flow rate increases or decreases depending on the rotation angle of the handle 40.

2, the flow rate adjustment plate 30 is disk-shaped. A recess extending in a circumferential direction is formed on the back surface 36 of the flow rate adjustment plate 30 opposite the first opposing surface 32. This recess becomes the annular flow passage 36A through which gas flows. The annular flow passage 36A also becomes part of the first main flow passage 54. A plurality of flow rate adjustment holes 34 are formed in the circumferential direction on the bottom surface of the recess of the annular flow passage 36A, penetrating to the first opposing surface 32. The inner diameters of the plurality of flow rate adjustment holes 34 are different from each other, and the inner diameter increases stepwise in the circumferential order. In other words, the plurality of flow rate adjustment holes 34 are set so that the pressure loss levels are different from each other. Each flow rate adjustment hole 34 constitutes a first branch flow passage 56 branched off from the first main flow passage 54.

As shown enlarged in FIG. 4, the flow rate adjustment hole 34 (first branch flow path 56) has a first branch opening 34A in the first opposing surface 32. By facing any one of the first branch openings 34A among the multiple flow rate adjustment holes 34 to the second opening 12A of the second flow path 12, the first branch flow path 56 and the second flow path 12 are communicated. The first opposing surface 32 of the flow rate adjustment plate 30 and the second opposing surface 14 of the main body 10 try to approach each other due to the restoring force of the spring 46, but as a result of a part of the ring member 100 housed in the ring groove portion 16 protruding, a gap is formed between the first opposing surface 32 and the second opposing surface 14. The ring member 100 in the ring groove portion 16 is contracted in the axial direction by the first opposing surface 32 and the bottom surface of the ring groove portion 16. The ring member 100 surrounds the gap between the first opposing surface 32 and the second opposing surface 14 facing each other with high airtightness. As a result, a communication space 190 is formed that connects the flow rate adjustment hole 34 (first branch flow path 56) and the second flow path 12.

As shown in FIG. 3, a portion of the second auxiliary ring member 28 disposed in each of the auxiliary ring grooves 26 also protrudes from the auxiliary ring groove 26. As a result, the first auxiliary ring member 27 and the second auxiliary ring member 28 in the auxiliary ring groove 26 are also crushed in the axial direction by the first opposing surface 32 and the bottom surface of the auxiliary ring groove 26 due to the restoring force of the spring 46.

<Flow Channel Forming Body>
Returning to FIG. 1, the flow path forming body 50 is a bottomed cylindrical member surrounding the flow rate adjusting plate 30, and its internal space forms the first main flow path 54. Specifically, a part of the main body 10 on the front side in the axial direction E is inserted into the cylindrical flow path forming body 50. A flange-shaped stopper 15A that is partially enlarged in diameter is formed on the outer circumferential surface of the main body 10, and a relative position is determined by the end face of the flow path forming body 50 abutting against it. A ring-shaped cap nut 15B is arranged on the main body 10 so as to engage with the axial rear side surface of the stopper 15A. The female thread portion of the cap nut 15B is screwed into the male thread portion formed on the outer periphery of the flow path forming body 50, thereby fixing the flow path forming body 50 to the front side in the axial direction E of the main body 10. The seal ring 25 held on the outer circumferential surface of the main body 10 is pressed against the inner circumferential surface of the flow path forming body 50. As a result, the space surrounded by the inside of the flow path forming body 50 and the second opposing surface 14 of the main body portion 10 becomes a highly airtight first main flow path 54.

<Conceptual explanation of components forming flow path>
Next, the concept of the members forming the flow paths will be described with reference to Fig. 1. The first main flow path 54 is formed by an airtight space surrounded by the flow path forming body 50, the main body 10, the flow rate adjustment plate 30, etc. In other words, these members become the first flow path forming portion. The multiple first branch flow paths 56 branched from the first main flow path 54 are formed by the multiple flow rate adjustment holes 34 of the flow rate adjustment plate 30. In other words, the multiple flow rate adjustment holes 34 of the flow rate adjustment plate 30 become the first branch flow path forming portion. The second flow path 12 is formed inside the main body 10. In other words, the main body 10 becomes the second flow path forming portion.

The first opposing surface 32 of the flow rate adjustment plate 30 and the second opposing surface 14 of the main body 10 move relative to each other by rotating the main shaft 60 held in the main body 10 with the handle 40. This selects the first branch flow path 56 (flow rate adjustment hole 34) that is connected to the second flow path 12. In other words, the main shaft 60 and the handle 40 held in the main body 10 function as a relative movement mechanism for the first opposing surface 32 and the second opposing surface 14. Note that, although a structure for relative movement by rotational motion is exemplified here, the first opposing surface 32 and the second opposing surface 14 can also be moved relative to each other by linear reciprocating motion.

<Details of the ring groove>
6C, when the maximum groove depth of the ring groove portion 16 in the axial direction J is Wm and the maximum groove thickness obtained by dividing the difference between the maximum outer diameter Kmax and the minimum inner diameter Kmin of the ring groove portion 16 in half is Fm, the ring groove portion 16 satisfies Wm>Fm. In other words, the cross-sectional shape of the ring groove portion 16 cut along the central axis (groove cross section) is a rectangle whose long side is the axial direction J and whose short side is the radial direction.

<Details of the shape of the ring component>
As shown in the enlarged view of Fig. 5 (A) and (B), the ring member 100 satisfies Wr>Fr, where Wr is the maximum ring width in the axial direction J, and Fr is the maximum ring thickness obtained by dividing the difference between the maximum outer diameter Rmax and the minimum inner diameter Rmin in half. In other words, as shown in Fig. 5 (B), the cross-sectional shape of the cut surface (ring cross section) along the central axis is a non-circular shape with the axial direction J being the long side and the radial direction being the short side. Note that the description of the shape in Fig. 5 (A) and (B) is based on the ring member 100 alone before being stored in the ring groove portion 16. In other words, the shape of the ring member 100 is based on an open state in which it is not subjected to external forces in the axial or radial directions.

Incidentally, the minimum inner diameter Rmin of the ring member 100 is smaller than the minimum inner diameter Kmin of the ring groove portion 16. This is the so-called tightening margin, and by storing the ring member 100 in the ring groove portion 16 while expanding its diameter, the airtightness on the inner circumference side is increased. This tightening margin (Kmin-Rmin) is preferably 3% or more of Kmin, and desirably 5% or more.

When considering the orientation of the ring member 100 that can be accommodated in the ring groove portion 16 shown in Figure 6 as a reference, the ring member 100 in the open state of Figure 5 (B) has a front-side convex region 110 that is convex on the front side in the axial direction J in the ring cross section. This front-side convex region 110 is designed to include a curved portion with a radius of curvature less than Fm/2 near the convex end (apex).

The ring member 100 in the open state shown in FIG. 5(B) has a rear convex region 140 that is convex toward the rear in the axial direction J in the cross section of the ring. This rear convex region 140 includes a curved portion with a radius of curvature less than Fm/2 near the convex end (apex).

The ring member 100 in the open state of FIG. 5(B) has an outer convex region 120 that is convex radially outward in the ring cross section within the outer peripheral range (see FIG. 6) facing the outer wall 16C of the ring groove portion 16. The minimum radius of curvature of this outer convex region 120 is set to be larger than the minimum radius of curvature of the front convex region 110 and/or larger than the minimum radius of curvature of the inner convex region 130 (described below).

Furthermore, the ring member 100 in the open state of FIG. 5(B) has an inner convex region 130 that is convex radially inward in the ring cross section within the inner circumferential range (see FIG. 6) facing the inner wall 16D of the ring groove portion 16. The inner convex region 130 includes a curved portion with a radius of curvature of Wr/2 or less near the convex end (apex), preferably includes a curved portion with a radius of curvature of Fr or less near the convex end (apex), and more preferably includes a curved portion with a radius of curvature of Fr/2 or less near the convex end (apex). The minimum radius of curvature of this inner convex region 130 is set to be smaller than the minimum radius of curvature of the front convex region 110 and/or smaller than the minimum radius of curvature of the outer convex region 120.

Furthermore, the ring member 100 in the open state of FIG. 5(B) has an outer concave region 125 that is concave in the ring cross section in the outer peripheral range (see FIG. 6) facing the outer wall 16C of the ring groove portion 16. This outer concave region 125 can be expressed as a region that forms a valley on the real part side of the cross section when the contour of the ring cross section is taken as a waveform. In the right cross section of the two ring cross sections in FIG. 5(B), when the ring cross section is matched to the XY coordinate plane and the range in which the inclination angle of the contour line decreases clockwise is defined as convex, the outer concave region 125 includes the range in which the inclination angle of the contour line increases in the same clockwise direction. In this embodiment, the range is the inflection point where the contour bends in a V-shape in the direction of increasing the inclination angle, but it may also be a concave curved range in which the inclination angle gradually increases. In this case, the place where the change in the inclination angle becomes zero is the boundary between the convex region and the concave region. Also, for example, when the outer convex region 120 and the front convex region 110 are considered as corrugated peaks, the outer concave region 125 includes a region that is concave toward the solid part side of the tangent line 120P connecting the peaks. In this embodiment, a pair of outer concave regions 125 are formed adjacent to both sides of the outer convex region 120 in the axial direction J.

Furthermore, the ring member 100 in the open state of FIG. 5(B) has an inner concave region 135 that is concave in the ring cross section in the inner circumferential range (see FIG. 6) facing the inner wall 16D of the ring groove portion 16. This inner concave region 135 can be expressed as a region that forms a valley on the real part side of the cross section when the contour of the ring cross section is taken as a waveform. In the right cross section of the two ring cross sections in FIG. 5(B), when the ring cross section is matched to the XY coordinate plane and the range in which the inclination angle of the contour line increases clockwise is defined as convex, the inner concave region 135 includes a range in which the inclination angle of the contour line decreases in the same clockwise direction. In this embodiment, the range is the inflection point where the contour bends in a V-shape in the direction of decreasing the inclination angle, but it may also be a concave curved range in which the inclination angle gradually decreases. In this case, the place where the change in the inclination angle becomes zero is the boundary between the convex region and the concave region. Also, for example, when the inner convex region 130 and the front convex region 110 are considered as corrugated peaks, the inner concave region 135 includes a region that is concave toward the solid part side of the tangent line 130P connecting the peaks. In this embodiment, a pair of inner concave regions 135 are formed adjacent to both sides of the inner convex region 130 in the axial direction J.

In addition, in the ring member 100 in the open state of FIG. 5(B), the maximum thickness F2r in the radial direction (X-axis direction in the figure) of the front convex region 110 in the ring cross section is smaller than the maximum groove thickness Fm of the ring groove portion 16. More specifically, the maximum thickness F2r in the radial direction (X-axis direction in the figure) from the front convex region 110 as the starting point to the outer convex region 120 and the inner convex region 130 is smaller than the maximum groove thickness Fm of the ring groove portion 16. The maximum thickness F2r is preferably 80% or less of Fm, and more preferably 70% or less. In this embodiment, it is set to 67%.

In FIG. 5(B), if the maximum ring width of the ring member 100 is considered based on a center line M that passes through the center of Wr and is perpendicular to the axial direction J, the ring cross section will have an axisymmetric shape with the center line M as the base line. In other words, when the ring member 100 is inverted, the front convex region 110 becomes the rear convex region 140, and the rear convex region 140 becomes the front convex region 110. Since there are no restrictions on the insertion direction of the ring member 100 into the ring groove portion 16, assembly errors can be reduced.

Referring to FIG. 5(C), the relationship between the ring groove portion 16 and the ring member 100 will be described when the ring member 100 is housed in the ring groove portion 16. Note that even in this state, the reference is a state in which the ring member 100 is not subjected to an external force in the axial direction (a crushing external force).

A gap (hereinafter, outer circumferential gap) 150A is formed between the outer circumferential edge 16A of the opening in the ring groove portion 16 and the ring member 100. The radial distance Sa of the outer circumferential gap 150A is set to 5% or more of the maximum groove width Fm, and preferably 10% or more of Fm. This outer circumferential gap 150A starts from the outer circumferential edge 16A and spreads toward the rear side in the axial direction J, and its maximum distance La is set to 20% or more of the maximum groove depth Wm, and preferably 30% or more.

Furthermore, a gap (hereinafter, inner gap) 150B is formed between the inner periphery 16B of the opening in the ring groove portion 16 and the ring member 100. The radial distance Sb of the inner gap 150B is set to 5% or more of the maximum groove width Fm, and preferably 10% or more of Fm. This inner gap 150B starts from the inner periphery 16B and spreads toward the back side in the axial direction J, and its maximum distance Lb is set to 20% or more of the maximum groove depth Wm, and preferably 30% or more.

<Explanation of the action of the ring groove portion and the ring member>
6 shows a state in which the ring member 100 is accommodated in the ring groove portion 16 and the flow rate adjusting plate 30 is pressed against the front side convex region 110 of the ring member 100. In this state, the ring member 100 is crushed and contracted in the axial direction.

As shown in FIG. 6A, the front convex region 110 of the ring member 100 is pressed against the flow rate adjustment plate 30. Since the front convex region 110 is included in the vicinity of the convex end where the radius of curvature is less than Fm/2, the ring-shaped contact area between the flow rate adjustment plate 30 and the front convex region 110 is small, and the surface pressure is large. As a result, the sealing characteristics of the fluid are improved.

The inner convex region 130 of the ring member 100 is pressed against the inner wall 16D of the ring groove portion 16 by the interference (Kmin-Rmin). Because the minimum radius of curvature of the inner convex region 130 is set small, the contact area between the inner wall 16D and the inner convex region 130 is small, and the surface pressure is increased. As a result, the fluid sealing characteristics are improved.

The front convex region 110 and the inner convex region 130 tightly surround the gap between the first opposing surface 32 of the flow rate adjustment plate 30 and the second opposing surface 14 of the main body 10, forming a communication space 190 that connects the first branch flow path 56 and the second flow path 12.

As shown by arrow A, the high-pressure gas on the first main flow path 54 side passes around the flow rate adjustment plate 30, enters the outer wall 16C and bottom surface 16E of the ring groove portion 16, and reaches the inner wall 16D from the bottom surface 16E side. On the other hand, as shown by arrow B, the high-pressure gas on the first main flow path 54 side is reduced in pressure due to pressure loss caused by the orifice of the flow rate adjustment hole 34 (first branch flow path 56), and flows into the communication space 190 and the second flow path 12. A pressure difference occurs between the front convex area 110 and the inner convex area 130, which are the boundary between the communication space 190 and the first main flow path 54, but the mutual movement of gas is suppressed because the sealing characteristics of the fluid are good. As a result, the flow rate adjustment hole 34 can exert a high-precision flow rate adjustment function. Note that here, a case is illustrated in which the first main flow path 54 side is high pressure and the second flow path 12 side is low pressure, but the opposite is also possible. In other words, the fluid may be flowed from the second flow path 12 to the first main flow path 54 side.

As shown in Figures 7(A) and (B), when the flow adjustment plate 30 is moved in the direction of arrow C to select another flow adjustment hole 34, the flow adjustment plate 30 slides against the front convex region 110. As shown by dotted line D, the front convex region 110 is deformed by the frictional force generated on the contact surface, and is displaced in the movement direction of the flow adjustment plate 30 (arrow C).

The cross-sectional shape of the ring groove portion 16 and the ring member 100 is long in the axial direction J, so even if the front convex region 110 is deformed, the ring member 100 is unlikely to jump out of the ring groove portion 16. In other words, the ring member 100 is held over a long distance in the axial direction J by the ring groove portion 16, so the amount of deformation of the front convex region 110 is naturally limited.

Furthermore, at this time, an outer peripheral gap 150A and/or an inner peripheral gap 150B are secured around the front convex region 110. As long as the front convex region 110 is displaced within the range of the outer peripheral gap 150A and/or the inner peripheral gap 150B, the front convex region 110 is unlikely to enter the gap between the flow rate adjustment plate 30 and the main body 10. As a result, damage to the front convex region 110 is suppressed, so that high sealing characteristics can be maintained for a long period of time. Furthermore, since the inner convex region 130 is sufficiently separated in the axial direction J from the inner peripheral edge 16B of the ring groove portion 16, even if the front convex region 110 is deformed or displaced, the influence is unlikely to be transmitted to the inner convex region 130, so that the sealing characteristics of the inner convex region 130 can be maintained in a good state.

<Function of conventional ring groove and ring member>
For reference, Fig. 8 shows the operation of a conventional ring groove portion 1600 and ring member 1100. The maximum groove depth Wm of the ring groove portion 1600 is smaller than the maximum groove thickness Fm. In other words, the cross-sectional shape of a cut surface (groove cross section) along the central axis is a rectangle with the axial direction J as the short side and the radial direction as the long side. The ring member 1100 housed in this ring groove portion 1600 is a so-called O-ring whose cross section is a perfect circle in the open state.

As shown in FIG. 8A, the ring member 1100 is sandwiched between the ring groove portion 1600 and the flow rate adjustment plate, and is deformed into an elliptical cross-sectional shape with the major axis in the radial direction and the minor axis in the axial direction. As a result, the contact area between the front convex region 11000 of the ring member 1100 and the flow rate adjustment plate increases, reducing the surface pressure, which tends to reduce the sealing characteristics of the fluid.

As shown in Figures 8B and 8C, when the flow rate adjustment plate is moved in the direction of the arrow C, the front convex region 11000 slides and is deformed and displaced as shown by the dotted line D. At this time, the front convex region 11000 approaches the outer peripheral edge 1600A and the inner peripheral edge 1600B of the opening of the ring groove portion 1600, so that the front convex region 11000 enters the gap between the flow rate adjustment plate and the main body portion as shown in Figure 8C, and the front convex region 11000 is likely to be damaged. Furthermore, since the inner convex region 13000 is close to the inner peripheral edge 1600B, when the front convex region 11000 is deformed and displaced, the inner convex region 13000 is likely to be exposed to the outside from the inner peripheral edge 1600B of the ring groove portion 1600, and the sealing properties of the fluid are likely to deteriorate.

<First Modification of First Embodiment>
Next, a first modified example of the flow rate adjusting unit 1 according to the first embodiment will be described with reference to Fig. 9. Since the modified example differs only in the shape of the ring member 300, differences between the ring member 100 and the ring member 300 will be described and other descriptions will be omitted. Note that the same reference numerals as those used in the flow rate adjusting unit 1 according to the first embodiment will be used for parts and members other than the ring member 300.

The ring member 300 satisfies the relationship Wr>Fr for the maximum ring width Wr and maximum ring thickness Fr. In other words, the cross-sectional shape of the cut surface (ring cross section) along the central axis is a non-circular shape with the axial direction J as the long side and the radial direction as the short side.

The ring member 300 in the open state has a proximal convex region 310 that is convex on the proximal side in the axial direction J in the ring cross section. This proximal convex region 310 includes a curved portion with a radius of curvature less than Fm/2 near the protruding end (apex).

In addition, the ring member 300 in the open state has a rear convex region 340 that is convex toward the rear side in the axial direction J in the ring cross section. The radius of curvature of this rear convex region 340 is set to be approximately the same as the outer convex region 320 and the inner convex region 330 described below.

The ring member 300 in the open state has an outer convex region 320 that is convex radially outward in the ring cross section within the outer peripheral range facing the outer wall 16C of the ring groove portion 16. The radius of curvature of this outer convex region 320 is set to be greater than the minimum radius of curvature of the front convex region 310 and approximately the same as the radius of curvature of the inner convex region 330.

The ring member 300 in the open state has an inner convex region 330 that is convex radially inward in the ring cross section within the inner circumferential range facing the inner wall 16D of the ring groove portion 16. The radius of curvature of this inner convex region 330 is set to be smaller than the minimum radius of curvature of the front convex region 310 and approximately the same as the radius of curvature of the outer convex region 320.

In this modified example, the rear convex region 340, the outer convex region 320, and the inner convex region 330 form a region whose cross section is a perfect circular arc.

Furthermore, the ring member 300 in the open state has an outer recessed region 325 that has a recessed shape in the ring cross section in the outer peripheral range facing the outer wall 16C of the ring groove portion 16. This outer recessed region 325 can be expressed as a region that forms a valley that is recessed toward the solid part of the cross section when the outline of the ring cross section is viewed as a waveform. For example, when the outer convex region 320 and the front convex region 310 are viewed as corrugated peaks, the outer recessed region 325 includes a region that is recessed toward the solid part from the tangent line 320P connecting the peaks. In this embodiment, the outer recessed region 325 is formed adjacent to the front side of the outer convex region 320 in the axial direction J.

Furthermore, the ring member 300 in the open state has an inner recessed region 335 that has a recessed shape in the ring cross section in the inner circumferential range facing the inner wall 16D of the ring groove portion 16. This inner recessed region 335 can be expressed as a region that forms a valley that is recessed toward the solid part of the cross section when the outline of the ring cross section is viewed as a waveform. For example, when the inner convex region 330 and the front convex region 310 are viewed as the peaks of a waveform, the inner recessed region 335 includes a region that is recessed toward the solid part from the tangent line 330P connecting the peaks. In this embodiment, the inner recessed region 335 is formed adjacent to the front side of the inner convex region 330 in the axial direction J.

In addition, in the ring member 300 in the open state, the maximum thickness F2r in the radial direction (X-axis direction in the figure) of the front convex region 310 in the ring cross section is smaller than the maximum groove thickness Fm of the ring groove portion 16. More specifically, the maximum thickness F2r in the radial direction (X-axis direction in the figure) from the front convex region 310 as the starting point to the outer convex region 320 and the inner convex region 330 is smaller than the maximum groove thickness Fm of the ring groove portion 16. The maximum thickness F2r is preferably 80% or less of Fm, and more preferably 70% or less.

Referring to FIG. 9(C), the relationship between the ring groove portion 16 and the ring member 300 will be described when the ring member 300 is housed in the ring groove portion 16. Note that even in this state, the reference is a state in which the ring member 100 is not subjected to an external force in the axial direction (a crushing external force).

A gap (hereinafter, outer gap) 350A is formed between the outer peripheral edge 16A of the opening in the ring groove portion 16 and the ring member 300. The radial distance Sa of the outer peripheral gap 350A is set to 5% or more of the maximum groove width Fm, and preferably 10% or more of Fm. This outer peripheral gap 350A starts from the outer peripheral edge 16A and spreads toward the back side in the axial direction J, and its maximum distance La is set to 20% or more of the maximum groove depth Wm, and preferably 30% or more, and more preferably 40% or more.

Furthermore, a gap (hereinafter, inner gap) 350B is formed between the inner periphery 16B of the opening in the ring groove portion 16 and the ring member 300. The radial distance Sb of the inner gap 350B is set to 5% or more of the maximum groove width Fm, and preferably 10% or more of Fm. This inner gap 350B starts from the inner periphery 16B and spreads toward the back side in the axial direction J, and its maximum distance Lb is set to 20% or more of the maximum groove depth Wm, and preferably 30% or more, and more preferably 40% or more.

In this modified ring member 300, the ring-shaped contact area between the front convex region 310 and the flow rate adjustment plate 30 is smaller, and the surface pressure is increased. As a result, the fluid sealing characteristics are improved.

The radius of curvature of the inner convex region 330 of the ring member 300 is larger than that of the ring member 100 already shown. By doing so, the contact margin (Kmin-Rmin) can be increased, allowing for a larger surface pressure. As a result, the fluid sealing characteristics can be improved.

When the flow rate adjustment plate 30 is moved in the direction of the arrow C, the flow rate adjustment plate 30 and the front side convex region 310 slide against each other, and as shown by the dotted line D, the front side convex region 310 is deformed and displaced by frictional force. At this time, since the outer peripheral gap 350A and/or the inner peripheral gap 350B are secured around the front side convex region 310, as long as the front side convex region 310 is displaced within the range of the outer peripheral gap 350A and/or the inner peripheral gap 350B, the front side convex region 310 is unlikely to enter the gap between the flow rate adjustment plate 30 and the main body 10. As a result, damage to the front side convex region 310 is suppressed, and high airtightness can be maintained for a long period of time. Furthermore, the inner convex region 330 is sufficiently separated in the axial direction J from the inner peripheral edge 16B of the ring groove portion 16, so even if the front convex region 310 is deformed or displaced, the effect is not easily transmitted to the inner convex region 330, and the good sealing characteristics of the inner convex region 330 can be maintained.

<Second Modification of First Embodiment>
Next, a second modified example of the flow rate adjusting unit 1 according to the first embodiment will be described with reference to Fig. 10. Since the second modified example differs only in the shape of the ring member 400, differences between the ring member 100 and the ring member 400 will be described and other descriptions will be omitted. Note that the same reference numerals as those used in the flow rate adjusting unit 1 according to the first embodiment will be used for parts and members other than the ring member 400.

The ring member 400 satisfies the relationship Wr>Fr with respect to the maximum ring width Wr and maximum ring thickness Fr. In other words, the cross-sectional shape of the cut surface (ring cross section) along the central axis is a non-circular shape with the axial direction J as the long side and the radial direction as the short side.

The ring member 400 in the open state has a proximal convex region 410 that is convex on the proximal side in the axial direction J in the ring cross section. The radius of curvature of this proximal convex region 410 is set to be approximately the same as the outer convex region 420 and the inner convex region 430 described below.

The ring member 400 in the open state has a rear convex region 440 that is convex toward the rear in the axial direction J in the ring cross section. The radius of curvature of this rear convex region 440 is set to be approximately the same as the outer convex region 420 and the inner convex region 430 described below.

The ring member 400 in the open state has multiple (three in this example) outer convex regions 420 that are convex radially outward in the ring cross section within the outer peripheral range facing the outer wall 16C of the ring groove portion 16. The radius of curvature of the outer convex regions 420 is set to be approximately the same as the radius of curvature of the front convex region 410 and the inner convex region 430.

The ring member 400 in the open state has multiple (three in this example) inner convex regions 430 that are convex radially inward in the ring cross section within the inner circumferential range facing the inner wall 16D of the ring groove portion 16. The radius of curvature of the inner convex regions 430 is set to be approximately the same as the radius of curvature of the front convex region 410 and the outer convex region 420.

In this modified example, the front convex region 410, the frontmost outer convex region 420, and the frontmost inner convex region 430 form a region whose cross section is a perfect circle. The back convex region 440, the backmost outer convex region 420, and the backmost inner convex region 430 form a region whose cross section is a perfect arc.

Furthermore, the ring member 400 in the open state has an outer recessed region 425 that has a recessed shape in the ring cross section in the outer peripheral range facing the outer wall 16C of the ring groove portion 16. This outer recessed region 425 can be expressed as a region that forms a valley that is recessed toward the solid part of the cross section when the outline of the ring cross section is viewed as a waveform. For example, when the multiple outer convex regions 420 are viewed as the peaks of a waveform, the outer recessed region 425 includes a region that is recessed toward the solid part from the tangent line 420P connecting the peaks. In this embodiment, a total of two outer recessed regions 425 are formed between the multiple outer convex regions 420.

Furthermore, the ring member 400 in the open state has an inner recessed region 435 that has a recessed shape in the ring cross section in the inner circumferential range facing the inner wall 16D of the ring groove portion 16. This inner recessed region 435 can be expressed as a region that forms a valley that is recessed toward the solid part of the cross section when the outline of the ring cross section is viewed as a waveform. For example, when the multiple inner convex regions 430 are viewed as the peaks of a waveform, the inner recessed region 435 includes a region that is recessed toward the solid part from the tangent line 430P connecting the peaks. In this embodiment, a total of two inner recessed regions 435 are formed between the multiple inner convex regions 430.

Referring to FIG. 10(C), the relationship between the ring groove portion 16 and the ring member 400 will be described when the ring member 400 is housed in the ring groove portion 16.

In the ring member 400 of this modified example, the radius of curvature of the front convex region 410 is larger than that of the ring member 100 already shown, and the contact area with the flow rate adjustment plate 30 is larger. By increasing the restoring force of the spring 46 accordingly, the surface pressure can be set to be large. As a result, the sealing characteristics of the fluid can be improved.

The ring member 400 has multiple inner convex regions 430, so the sealing characteristics can be improved by a multi-stage sealing function. In addition, since the inner convex regions 430 are distributed in multiple areas, the radius of curvature of each inner convex region 430 can be set to be smaller, so the surface pressure can be increased.

When the flow rate adjustment plate 30 is moved in the direction of arrow C, the flow rate adjustment plate 30 and the front convex region 410 slide against each other, and as shown by the dotted line D, the frictional force causes the front convex region 410 to deform and displace. At this time, since there are multiple inner convex regions 430, the frictional force with the inner peripheral wall 16D acts as a resistance, suppressing the displacement of the front convex region 410.

Furthermore, the middle or innermost convex region 430 is sufficiently separated in the axial direction J from the inner peripheral edge 16B of the ring groove portion 16, so that even if the front convex region 410 is deformed or displaced, the effect is not easily transmitted to the inner convex region 430 at the rear, and the sealing property of the inner convex region 430 can be maintained in a good state.

In FIG. 10(B), if the maximum ring width of ring member 400 is based on center line M, which passes through the center of Wr and is perpendicular to axial direction J, the ring cross section will have an axisymmetric shape with center line M as the base line. In other words, when ring member 400 is inverted, front side convex region 410 becomes rear side convex region 440, and rear side convex region 440 becomes front side convex region 410. Since there are no restrictions on the insertion direction of ring member 400 into ring groove portion 16, assembly errors can also be reduced.

In the second modified example of the ring member 400, three outer convex regions 420 and three inner convex regions 430 are formed, but the present invention is not limited to this and includes cases where two of each are formed, or four or more of each are formed. It also includes cases where the numbers of outer convex regions 420 and inner convex regions 430 are not the same, for example, including a case where there is one outer convex region 420 and two or more inner convex regions 430, and a case where there are two outer convex regions 420 and three or more inner convex regions 430.

<Third Modification of First Embodiment>
Next, a third modified example of the flow control unit 1 according to the first embodiment will be described with reference to Fig. 11. In the flow control unit 2 of the third modified example, differences from the flow control unit 1 will be mainly described, and descriptions of the same or similar parts and members will be omitted. For ease of description, the parts and members of the flow control unit 2 will use the same names and symbols as those used in the flow control unit 1 of the first embodiment.

The first opposing surface 32 of the flow rate adjustment plate 30 faces the flow path forming body 50. The back surface 36 of the flow rate adjustment plate 30 faces the main body 10. An annular flow path 36A is formed on this back surface 36 side. A plurality of flow rate adjustment holes 34 that penetrate to the first opposing surface 32 are formed in the circumferential direction in the bottom surface of the recess of this annular flow path 36A.

A gap N1 is formed between the flow rate adjustment plate 30 and the main body 10, which serves as a flow path through which gas flows. Furthermore, a flow path N2 that communicates with this gap N1 is formed on the flow path forming body 50 side. This gap N1 and flow path N2 correspond to the first main flow path 54.

The flow path forming body 50 is formed with a second opposing surface 14 that faces the first opposing surface 32. The flow path forming body 50 is formed with a second flow path 12, and its second opening 12A is formed in the second opposing surface 14. A ring groove portion 16 is recessed around the second opening 12A in the second opposing surface 14. A ring member 100 is housed in the ring groove portion 16. An auxiliary ring groove portion 26 is recessed in the second opposing surface 14, and a first auxiliary ring member 27 and a second auxiliary ring member 28 are housed in this auxiliary ring groove portion 26.

A spring 46 is disposed between the flow rate adjustment plate 30 and the main body 10. This spring 46 biases the first opposing surface 32 of the flow rate adjustment plate 30 toward the second opposing surface 14 of the flow path forming body 50 by its own restoring force. As a result, the ring member 100 surrounds the gap between the first opposing surface 32 of the flow rate adjustment plate 30 and the second opposing surface 14 of the flow path forming body 50 in a highly airtight manner, and a communication space 190 is formed that connects the first branch flow path 56 (flow rate adjustment hole 34) and the second flow path 12.

The flow rate control unit 2 of this third modified example has a different arrangement of the first main flow path 54, the first branch flow path 56, and the second flow path 12, but the functions of the ring groove portion 16 and the ring member 100 are all the same as those of the flow rate control unit 1.

<Second embodiment (flow rate adjustment valve)>
Next, a fluid regulating valve 600 according to a second embodiment will be described with reference to Fig. 12 and Fig. 13. The fluid regulating valve 600 is connected to, for example, a gas cylinder B to regulate the flow rate and pressure of gas released from the gas cylinder B.

The fluid adjustment valve 600 has a valve housing 610, a filling port 620 formed in the valve housing 610 for filling a gas cylinder B with gas, a check valve unit 630 provided inside the filling port 620, an upstream pressure reduction unit 640A installed in the valve housing 610, a flow rate adjustment unit 1 of the first embodiment installed in the valve housing 610, and a pressure measurement unit 650 installed in the valve housing 610. Note that a downstream pressure reduction unit 640B is provided inside the flow path forming body 50 in the flow rate adjustment unit 1.

The valve housing 610 is formed with a male threaded portion (connection portion) 612 that screws into the female threaded portion of the gas cylinder B. A first flow path 710 that can be connected to the gas cylinder B is formed within the male threaded portion 612. This first flow path 710 guides gas to the pressure measurement unit 650. The filling port 620 is connected to the first flow path 710 via a check valve unit 630, and the gas cylinder B can be filled with the desired gas from the outside. A filling port cap 622 is provided on this filling port 620.

The check valve unit 630 is a known valve mechanism that blocks the flow of gas from the first flow path 710 to the filling port 620 and allows the flow of gas from the filling port 620 to the first flow path 710.

The upstream pressure reducing unit 640A is a known pressure reducing valve that reduces the pressure of the gas guided from the first flow path 710 and then guides it to the second flow path 720. The downstream pressure reducing unit 640B is a known pressure reducing valve that further reduces the pressure of the gas that has passed from the upstream pressure reducing unit 640A through the second flow path 720 and provides it to the flow rate adjustment unit 1.

The first flow path 710 is connected to a pressure measurement unit 650 via a measurement path 715, which detects the residual pressure in gas cylinder B and displays it on a display 652 (see FIG. 12 (A)).

The fluid adjustment valve 600 of this second embodiment is preferably used as an oxygen supply device in home oxygen therapy by connecting it to a gas cylinder B filled with oxygen. As described in the first embodiment, the flow rate adjustment unit 1 can provide a highly accurate flow rate adjustment function over a long period of time, reducing the frequency of replacement maintenance of the ring member 100.

In the above-mentioned fluid adjustment valve 600, a continuous supply method in which the fluid flows at a set flow rate and pressure at all times has been exemplified, but the present invention is not limited to this. Furthermore, by adding a tuning unit, the supply and stop of the fluid may be performed in response to pressure changes downstream.

Furthermore, in the flow rate adjustment unit 1 of the first embodiment described above, the ring groove portion 16 is formed on the second opposing surface 14 side, but the present invention is not limited to this. For example, as shown in FIG. 14, the ring groove portion 16 may be formed around each of the flow rate adjustment holes 34 on the first opposing surface 32 side, and a ring member 100 may be disposed inside the ring groove portion 16.

The present invention is not limited to the above-described embodiment, and various modifications can be made without departing from the spirit of the present invention.

1 Flow rate adjustment unit 10 Main body 11 Main shaft hole 12 Second flow path 12A Second opening 12B Open end 14 Second opposing surface 16 Ring groove 30 Flow rate adjustment plate 32 First opposing surface 34 Flow rate adjustment hole 50 Flow path forming body 54 First main flow path 56 First branch flow path 60 Main shaft 100 Ring member 110 Front convex area 120 Outer convex area 125 Outer concave area 130 Inner convex area 135 Inner concave area 140 Back convex area 150A Outer gap 150B Inner gap 300 Ring member 310 Front convex area 320 Outer convex area 325 Outer concave area 330 Inner convex area 335 Inner concave area 340 Convex area on the back side 350A Gap on the outer circumference side 350B Inner peripheral gap 400 Ring member 410 Front convex area 420 Outer convex area 425 Outer concave area 430 Inner convex area 435 Inner concave area 440 Back convex area 600 Fluid adjustment valve

Claims (12)

A flow rate adjusting unit for adjusting a flow rate of a fluid,
a first main flow path forming portion in which a first main flow path is formed;
a first branch flow passage forming portion in which a plurality of first branch flow passages branched from the first main flow passage and having different pressure losses are formed;
a second flow path forming portion formed therein, the second flow path being connected to at least one of the first branch flow paths;
a first opposing surface provided in the first branch flow passage forming portion and having first branch openings which become open ends of the first branch flow passages;
a second opposing surface provided in the second flow path forming portion, the second opposing surface having a second opening that serves as an open end of the second flow path and opposing the first opposing surface with a gap therebetween;
a relative movement mechanism that moves the first opposing surface and the second opposing surface relatively in a planar direction to select the first branch flow path that is connected to the second flow path;
a ring groove portion recessed into the first opposing surface or the second opposing surface so as to surround a periphery of the first branch opening or a periphery of the second opening;
a ring member that is disposed in the ring groove portion and has one end in an axial direction protruding from the ring groove to come into contact with the first opposing surface or the second opposing surface (hereinafter, the opposing surface),
The ring groove portion is
If the maximum groove depth in the axial direction is Wm and the maximum groove thickness obtained by dividing the difference between the maximum outer diameter and the minimum inner diameter in half is Fm, Wm>Fm is satisfied.
The ring member before receiving an axial external force in the ring groove portion is
If the maximum ring width in the axial direction is Wr and the maximum ring thickness obtained by dividing the difference between the maximum outer diameter and the minimum inner diameter in half is Fr, Wr>Fr is satisfied.
A gap (hereinafter, an outer circumferential gap) is formed between an outer circumferential edge of the doughnut-shaped opening in the ring groove portion and the ring member before it receives an axial external force in the ring groove portion,
When defining the opening side of the ring groove as the axial front side and the bottom side as the axial rear side,
The outer circumferential gap extends from the outer circumferential edge toward the inner side in the axial direction by 10% or more of a maximum groove depth Wm,
The ring member has an outer convex region that is convex radially outward on the axially inner side of the outer peripheral gap, thereby eliminating the outer peripheral gap, and that contacts an outer wall of the ring groove portion.
Characterized in that
Flow regulation unit. A flow rate adjusting unit for adjusting a flow rate of a fluid,
a first main flow path forming portion in which a first main flow path is formed;
a first branch flow passage forming portion in which a plurality of first branch flow passages branched from the first main flow passage and having different pressure losses are formed;
a second flow path forming portion formed therein, the second flow path being connected to at least one of the first branch flow paths;
a first opposing surface provided in the first branch flow passage forming portion and having first branch openings which become open ends of the first branch flow passages;
a second opposing surface provided in the second flow path forming portion, the second opposing surface having a second opening that serves as an open end of the second flow path and opposing the first opposing surface with a gap therebetween;
a relative movement mechanism that moves the first opposing surface and the second opposing surface relatively in a planar direction to select the first branch flow path that is connected to the second flow path;
a ring groove portion recessed into the first opposing surface or the second opposing surface so as to surround a periphery of the first branch opening or a periphery of the second opening;
a ring member that is disposed in the ring groove portion and has one end in an axial direction protruding from the ring groove to come into contact with the first opposing surface or the second opposing surface (hereinafter, the opposing surface),
The ring groove portion is
If the maximum groove depth in the axial direction is Wm and the maximum groove thickness obtained by dividing the difference between the maximum outer diameter and the minimum inner diameter in half is Fm, Wm>Fm is satisfied.
The ring member before receiving an axial external force in the ring groove portion is
If the maximum ring width in the axial direction is Wr and the maximum ring thickness obtained by dividing the difference between the maximum outer diameter and the minimum inner diameter in half is Fr, Wr>Fr is satisfied.
a gap (hereinafter, an inner peripheral gap) is formed between an inner peripheral edge of a doughnut-shaped opening in the ring groove portion and the ring member before the ring member receives an axial external force in the ring groove portion,
When defining the opening side of the ring groove as the axial front side and the bottom side as the axial rear side,
The inner peripheral gap extends from the inner peripheral edge toward the inner side in the axial direction by 10% or more of a maximum groove depth Wm,
The ring member has a convex shape on the radially inward side at the axial rear side of the inner peripheral gap, thereby eliminating the inner peripheral gap, and has an inner convex area that contacts the inner wall of the ring groove portion .
Flow regulation unit. The outer peripheral side gap or the inner peripheral side gap is 5% or more of a maximum groove thickness Fm.
The flow rate adjusting unit according to claim 1 or 2 . When defining the axial open end side of the ring groove portion as the axial front side, the axial bottom side as the axial back side, and the cross section along the central axis of the ring member as the ring cross section,
The ring cross section has a front convex region that is convex toward the axial front side,
The front side convex region includes a curved portion having a radius of curvature less than Fm/2.
The flow rate adjusting unit according to any one of claims 1 to 3 . When a cross section along the radial direction and the axial direction of the ring member is defined as a ring cross section,
The ring groove portion has an outer recessed region having a recessed shape in an axial direction deeper than the outer convex region and facing an outer wall of the ring groove portion of the ring cross section.
The flow rate adjusting unit according to claim 1 . The outer convex region has a plurality of outer convex regions,
The outer concave region is formed between a plurality of the outer convex regions.
The flow rate adjusting unit according to claim 5 . When a cross section along the radial direction and the axial direction of the ring member is defined as a ring cross section,
The ring groove portion has an inner recessed area having a recessed shape in a range facing the inner wall of the ring groove portion of the ring cross section.
The flow rate adjusting unit according to any one of claims 1 to 6 . When a cross section along the radial direction and the axial direction of the ring member is defined as a ring cross section,
The ring has an inner recessed area having a recessed shape in a range facing an inner wall of the ring groove portion of the ring cross section,
The inner concave region is formed on both sides of the inner convex region,
The flow rate adjusting unit according to claim 2 . The inner convex region has a plurality of inner convex regions,
The inner concave region is formed between a plurality of the inner convex regions.
The flow rate adjusting unit according to claim 8 . The inner convex region includes a curved portion having a radius of curvature of Wr/2 or less.
The flow rate adjusting unit according to claim 2 . The inner convex region includes a curved portion having a radius of curvature Fr or less.
The flow rate adjusting unit according to claim 2 or 10 . A fluid regulating valve for regulating a flow of a fluid, comprising:
a pressure adjusting unit for adjusting the pressure of the fluid;
A flow rate adjusting unit according to any one of claims 1 to 11 , to which the fluid whose pressure is adjusted by the pressure adjusting unit is guided;
A fluid regulating valve comprising:

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