JP2022161509A - Flor control unit and flow control valve - Google Patents

Abstract

To provide a flow control unit, etc. capable of stably and highly precisely controlling a flow rate for a long period of time.SOLUTION: A flow control unit 1 comprises a first main flow path 54, a plurality of first branch flow paths 56 branched from the first main flow path 54, and a second flow path 12 communicated with at least any of the plurality of first branch flow paths 56. A first facing surface 32 having a first branch opening 34A of the first branch flow path 56 and a second facing surface 14 having a second opening 12A of the second flow path 12 are relatively moved in a surface direction, so that a first branch flow path 56 is selected. A ring groove 16 is provided on the first facing surface 32 or the second facing surface 14 so as to enclose the circumference of the first branch opening 43A or the circumference of the second opening 12A, and a ring member 100 is stored inside thereof. When a maximum groove depth in the axial direction is Wm and a maximum groove thickness obtained by halving a difference between the maximum outside diameter and the minimum inside diameter is Fm, the ring groove 16 satisfies Wm>Fm, and when a maximum ring width in the axial direction is Wr and a maximum ring thickness obtained by halving a difference between the maximum outside diameter and the minimum inside diameter is Fr, the ring member 100 satisfies Wr>Fr.SELECTED DRAWING: Figure 4

Description

TECHNICAL FIELD The present invention relates to a flow rate adjusting unit that is used by being connected to a fluid supply source such as an oxygen cylinder to adjust the flow rate of fluid.

2. Description of the Related Art Conventionally, for example, oxygen cylinders used in home oxygen therapy or the like are connected to fluid control valves for adjusting the flow rate and pressure of oxygen gas. This fluid adjustment valve incorporates a pressure adjustment unit and a flow rate adjustment unit to adjust the pressure and flow rate of the oxygen gas. Fluid control valves include a continuous supply type valve that continuously supplies gas such as oxygen, and a breathing synchronized type valve that supplies gas in synchronization with the user's breathing.

As shown in Patent Literature 1, a flow rate adjustment unit built into a fluid adjustment valve includes a flow rate adjustment plate that adjusts the flow rate. A plurality of passage holes (orifice holes) having different inner diameters (pressure loss) are formed in the flow rate adjusting plate so as to be arranged in the circumferential direction. The flow rate adjusting plate is pressed against the channel forming surface forming the channel by the biasing force of the spring. Fixed-side channel holes are formed in the channel forming surface. When the flow regulating plate is rotated with a knob, the flow channel hole on the fixed side and the specific orifice hole face each other and communicate with each other, so that the flow rate is selectively determined.

An annular groove (ring groove) is formed in the flow path forming surface so as to surround the flow path hole on the fixed side, and the O-ring is held in this annular groove. As a result of the O-ring being crushed by the force of the spring described above, the gap between the fixed side flow path and the orifice hole becomes a highly airtight space.

JP 2003-247695

In the flow rate adjusting unit, the O-ring and the flow rate adjusting plate slide each time the flow rate is adjusted. At this time, since the orifice hole is formed in the flow rate adjusting plate, the elastically deformable O-ring and the orifice hole are easily caught. When the O-ring is elastically deformed due to sliding between the O-ring and the flow rate adjusting plate, the O-ring protrudes from the annular groove and enters between the flow rate adjusting plate and the flow path forming surface. Scratches formed on the surface of the O-ring deteriorate the airtightness of the O-ring and deteriorate the accuracy of flow rate adjustment.

Furthermore, once the O-ring has completely protruded from the annular groove, it cannot return to its original position (ring groove). As a result, the flow regulation will not work completely. Therefore, the O-ring must be replaced.

On the other hand, if the pressing force (biasing of the spring) against the O-ring is weakened in order to suppress this problem, the airtightness of the O-ring tends to deteriorate. In particular, the accuracy of adjusting the flow rate of the high-pressure fluid tends to deteriorate.

SUMMARY OF THE INVENTION It is an object of the present invention to provide a flow regulating unit or the like capable of stably and highly accurately regulating the flow over a long period of time.

The present invention for achieving the above object is a flow rate adjusting unit for adjusting the flow rate of a fluid, comprising: a first main flow path forming portion in which a first main flow path is formed; a first branch flow path forming portion in which a plurality of first branch flow paths having different pressure losses are formed; and a second flow path communicating with at least one of the plurality of first branch flow paths. a second flow channel forming portion formed; a first opposing surface provided in the first branch flow channel forming portion and having a first branch opening serving as an open end of the plurality of first branch flow channels; A second opposing surface that is provided in the two-channel forming portion and has a second opening that is an open end of the second channel and faces the first opposing surface with a gap, and the first opposing surface A relative movement mechanism that selects the first branch flow path that communicates with the second flow path by relatively moving the second opposing surface in the surface direction, and a surrounding of the first branch opening or the second opening A ring groove portion recessed in the first opposing surface or the second opposing surface so as to surround the periphery of the a ring member that abuts against the first opposing surface or the second opposing surface (hereinafter referred to as the mating opposing surface), wherein the ring groove portion has a maximum axial groove depth of Wm, a When the maximum groove thickness obtained by dividing the difference by two is Fm, Wm>Fm is satisfied. The flow control unit is characterized by satisfying Wr>Fr, where Fr is the maximum ring thickness obtained by dividing the difference between the diameter and the minimum inner diameter.

In relation to the flow rate adjusting unit, a gap (hereinafter referred to as an outer gap) is formed between the outer peripheral edge of the opening in the ring groove and the ring member before receiving an axial external force in the ring groove. may be used as a feature.

In relation to the flow rate adjusting unit, a gap (hereinafter referred to as an inner peripheral side gap) is formed between the inner peripheral edge of the opening in the ring groove and the ring member before receiving an axial external force in the ring groove. It may be characterized as

In relation to the flow rate adjustment unit, when defining the axial opening side of the ring groove portion as the axial front side and the bottom side as the axial back side, the outer peripheral side clearance and/or the inner peripheral side clearance is , extending from the outer peripheral edge or the inner peripheral edge toward the inner side in the axial direction over 10% or more of the maximum groove depth Wm.

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

In relation to the flow rate adjusting unit, the axial open end side of the ring groove portion is defined as the front side in the axial direction, the bottom side in the axial direction is defined as the rear side in the axial direction, and the cross section along the central axis of the ring member is defined as When defined as a ring cross section, the ring cross section has a front side convex region that is convex toward the front side in the axial direction, and the front side convex region is curved with a radius of curvature of less than Fm/2. It may be characterized by including a part.

In relation to the flow rate adjusting unit, when the cross section along the radial direction and the axial direction of the ring member is defined as the ring cross section, the range facing the outer wall of the ring groove portion of the ring cross section has a concave shape. It may be characterized by having an outer concave region.

In relation to the flow rate adjusting unit, the ring section has an outer convex region having a convex shape in a range facing the outer wall of the ring groove portion, and the outer concave region is provided on both sides of the outer convex region. It may be characterized in that regions are formed respectively.

In relation to the flow rate adjusting unit, a plurality of outer convex regions having a convex shape are provided in a range facing the outer wall of the ring groove portion of the ring cross section, and between the plurality of outer convex regions, the It may be characterized in that an outer concave region is formed.

In relation to the flow rate adjusting unit, when the cross section along the radial direction and the axial direction of the ring member is defined as the ring cross section, the range facing the inner wall of the ring groove portion of the ring cross section has a concave shape. It may be characterized by having an inner concave region.

In relation to the flow rate adjusting unit, the ring cross section has an inner convex region having a convex shape in a range facing the inner wall of the ring groove portion, and the outer concave portion is provided on both sides of the inner convex region. It may be characterized in that regions are formed respectively.

In relation to the flow rate adjusting unit, a plurality of inner convex regions having a convex shape are provided in a range facing the inner wall of the ring groove portion of the ring cross section, and between the plurality of inner convex regions, the It may be characterized by the formation of an inner recessed region.

In relation to the flow regulating unit, the inner convex region may include a curved portion having a radius of curvature of Wr/2 or less.

In relation to the flow control unit, the inner convex region may include a curved portion having a curvature radius of Fr or less.

The present invention for achieving the above object is a fluid regulating valve for regulating the flow of fluid, comprising: a pressure regulating unit for regulating the pressure of the fluid; A fluid control valve comprising: a flow control unit according to any one of the above.

Advantageous Effects of Invention According to the present invention, it is possible to obtain a flow rate adjusting unit or the like that is capable of stably and highly accurately adjusting the flow rate over a long period of time.

(A) is a cross-sectional view showing the overall configuration of a flow rate adjustment unit according to a first embodiment of the present invention, and (B) is a view showing a flow rate guide display mode shown on a handle end face cover of the flow rate adjustment unit. be. It is a perspective view which shows the state which disassembled some components of the same flow control unit. It is sectional drawing which expands and shows a part of same flow control unit. It is sectional drawing which expands and shows a part of same flow control unit. (A) is a plan view of a single ring member of the same flow rate adjusting unit, and (B) and (C) are cross-sectional views taken along line II-II in (A). It is the enlarged sectional view which looked the vicinity of the ring groove part of the flow control unit, and the ring member from the ring radial direction. (A) is an enlarged plan view of the vicinity of a ring member of the flow control unit viewed from the axial direction, and (B) is an enlarged cross-sectional view of the ring member viewed from the radial direction. (A) to (C) are enlarged cross-sectional views of the vicinity of a ring member of a conventional flow rate adjusting unit as seen from the radial direction. (A) is a plan view of a single ring member according to a first modification of the same flow rate adjustment unit, (B) is a cross-sectional view taken along line II-II of (A), and (C) is the same ring member. It is the expanded sectional view which looked the adopted flow control unit from the ring radial direction. (A) is a plan view of a single ring member according to a second modification of the flow rate adjustment unit, (B) is a cross-sectional view taken along line II-II in (A), and (C) is the ring member. It is the expanded sectional view which looked the adopted flow control unit from the ring radial direction. It is the whole flow regulating unit sectional view concerning the 3rd modification. FIG. 4A is a diagram showing a residual pressure display mode of a cylinder, and FIG. 4B is a side view of the fluid regulating valve according to the second embodiment of the present invention. (A) is a plan partial cross-sectional view of the same fluid control valve, and (B) is a front view of the same fluid control valve. It is a partial expanded sectional view showing a modification of a flow control unit of this embodiment.

BEST MODE FOR CARRYING OUT THE INVENTION Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.

<First embodiment (flow rate adjustment unit)>
FIG. 1 shows the overall configuration of a flow rate adjusting unit 1 according to the first embodiment of the present invention. Here, the case where the flow rate adjusting unit 1 adjusts the flow rate of gas (for example, oxygen gas) as a fluid is exemplified, but the flow rate of liquid may be adjusted.

The flow rate adjusting unit 1 includes a body portion 10, a main shaft 60 rotatably supported by the main body portion 10, a flow rate adjusting plate 30 integrally formed near one end of the main shaft 60, and the main shaft 60. A handle 40 is connected to the vicinity of the other end of the flow passage so as not to rotate relatively, and a flow passage forming body 50 is fixed to the main body 10 so as to surround the flow rate adjusting plate 30 . For convenience of explanation, with the axial direction E of the main shaft 60 as a reference, the handle 40 side in the drawing (left side in the drawing) is the axial back side, and the flow path forming body 50 side in the drawing (right side in the drawing) is the axial direction. This side may be referred to as the front side.

<Body part>
The body portion 10 is a columnar member, and a main shaft hole 11 for accommodating the main shaft 60 is formed therein. Further, the body portion 10 is formed with a second flow path 12 through which gas flows. 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 12</b>A, which is one end of the second flow path 12 , is formed in the second facing surface 14 . The other open end 12B of the second channel 12 reaches the side surface of the body portion 10 . A joint 70 is connected to the open end 12B.

As shown enlarged in FIG. 2, the second facing 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 . A plurality of (here, two) auxiliary ring grooves 26 are recessed in the second facing 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 regular intervals in the circumferential direction. In this embodiment, one ring groove portion 16 is formed and two auxiliary ring groove portions 26 are formed, so that a total of three ring grooves are arranged at intervals of 120 degrees 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 portion 26 play a role of homogenizing the external force that the second opposing surface 14 receives from the ring member 100 in the circumferential direction. Therefore, since the second auxiliary ring member 28 is not required to have a fluid sealing function, it has a cross-sectional shape (for example, a rectangular shape) that is difficult to separate from the auxiliary ring groove portion 26 . In addition, in order to suppress sliding resistance, the second auxiliary ring member 28 is made of a material with low frictional force, or is surface-treated to reduce surface frictional force, such as Teflon (registered trademark) processing. Material selection is preferred. 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 in order to generate a desired repulsive force.

Returning to FIG. 1, a seal groove 11A extending in the circumferential direction is formed in the inner peripheral surface of the main shaft hole 11 of the body portion 10. As shown in FIG. A seal ring 24 is accommodated in the seal groove 11A, and when the seal ring 24 is pressed against the main shaft 60, a first main flow path 54, which will be described later, becomes a highly airtight space. Similarly, a circumferentially extending seal groove 13 is formed on the outer peripheral surface of the body portion 10 . A seal ring 25 is accommodated in the seal groove 13 , and the seal ring 25 is pressed against the inner peripheral surface of the flow path forming body 50 to form the first main flow path 54 as a highly airtight space.

<Spindle, flow control plate, handle>
The main shaft 60 is a rod-shaped member extending in the axial direction E. As shown in FIG. A flow control 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 end thereof. The handle 40 is inserted into the male screw portion 64 side. The female threaded body 66 that is screwed with the male threaded part 64 prevents the handle 40 inserted therein from coming off. A ring-shaped spacer 49 is interposed between the handle 40 and the main body 10 so that the two can 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 the through hole 42 . An engagement portion 62 having an irregular cross section such as a key groove or a D-cut is formed on the back side of the main shaft 60 in the axial direction E. As shown in FIG. Through bore 42 of handle 40 has an engagement area 43 and a pressure receiving area 44 . The engaging region 43 is a hole having a non-perfect circular cross section, and engages with the engaging portion 62 of the main shaft 60 in the circumferential direction. The pressure receiving area 44 is adjacent to the engagement area 43 on the inner side in the axial direction E, and the inner diameter of the pressure receiving area 44 is larger than that of the engagement area 43, so that a step 44A is formed at the boundary. A gap is formed between the pressure receiving area 44 and the main shaft 60, and the spring 46 is accommodated in this gap. The female threaded body 66 presses the spring 46 via 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 further transmitted to the main body 10 via the spacer 49. As shown in FIG. The other restoring force of the spring 46 is transmitted to the internal thread body 66 via the spacer 48 and further transmitted to the flow rate adjusting plate 30 via the main shaft 60 . That is, 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 cover 68 is fixed to the other end of the main shaft 60, and as shown in FIG.

As shown in FIG. 2, the flow regulating plate 30 has a disk shape. A concave portion extending annularly in the circumferential direction is formed in the back surface 36 of the flow rate adjusting plate 30 opposite to the first opposing surface 32 . This recess forms an annular flow path 36A through which gas flows. Note that this annular flow path 36A also forms part of the first main flow path 54 . A plurality of flow rate adjusting holes 34 penetrating to the first opposing surface 32 are formed in the circumferential direction in the bottom surface of the concave portion of the annular flow path 36A. The inner diameters of the plurality of flow rate adjusting holes 34 are different from each other, and the inner diameters increase stepwise in the order in which they are arranged in the circumferential direction. That is, the plurality of flow rate adjustment holes 34 are set to have different pressure loss levels. Each flow control hole 34 constitutes a first branch channel 56 branched from the first main channel 54 .

As enlarged and shown in FIG. 4 , the flow rate adjusting hole 34 (first branch flow path 56 ) has a first branch opening 34A on the first opposing surface 32 . The first branched flow path 56 and the second flow path 12 are communicated with each other by causing one of the first branched openings 34A of the plurality of flow rate adjustment holes 34 to face the second opening 12A of the second flow path 12. be. The first opposing surface 32 of the flow rate adjusting plate 30 and the second opposing surface 14 of the body portion 10 try to approach each other by the restoring force of the spring 46, but part of the ring member 100 accommodated in the ring groove portion 16 protrudes. As a result, a gap is formed between the first facing surface 32 and the second facing surface 14 . The ring member 100 within the ring groove portion 16 is axially contracted 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 communicating space 190 connecting the flow rate adjusting hole 34 (the first branch channel 56) and the second channel 12 is formed.

Incidentally, as shown in FIG. 3 , a part of the second auxiliary ring member 28 arranged in each auxiliary ring groove portion 26 also protrudes from the auxiliary ring groove portion 26 . As a result, the first auxiliary ring member 27 and the second auxiliary ring member 28 in the auxiliary ring groove portion 26 are also axially crushed by the first opposing surface 32 and the bottom surface of the auxiliary ring groove portion 26 by the restoring force of the spring 46. Become.

<Flow path forming body>
Returning to FIG. 1, the flow path forming body 50 is a cylindrical member with a bottom that surrounds the flow rate adjusting plate 30, and the internal space thereof forms a first main flow path 54. As shown in FIG. Specifically, a portion of the main body 10 on the front side in the axial direction E is inserted into the cylinder of the flow path forming body 50 . A flange-like stopper 15A that is partially enlarged in diameter is formed on the outer peripheral surface of the main body 10, and the relative position is determined by the end surface of the flow path forming body 50 coming into contact therewith. A ring-shaped cap nut 15B is arranged on the main body 10 so as to engage with the axially deep side surface of the stopper 15A. The female threaded portion of the cap nut 15B is screwed with the male threaded portion formed on the outer periphery of the channel forming body 50 , thereby fixing the channel forming body 50 to the front side of the main body 10 in the axial direction E. A seal ring 25 held on the outer peripheral surface of the body portion 10 is pressed against the inner peripheral surface of the flow path forming body 50 . As a result, the space surrounded by the interior of the flow path forming body 50 and the second facing surface 14 of the main body 10 forms a highly airtight first main flow path 54 .

<Explanation of concept of members forming flow path>
Next, with reference to FIG. 1, the concept of the member forming the flow path will be described. The first main flow path 54 is formed by an airtight space surrounded by the flow path forming body 50, the body portion 10, the flow rate adjusting plate 30, and the like. In other words, these members become the first flow path forming portion. A plurality of first branch channels 56 branched from the first main channel 54 are formed by a plurality of flow rate adjusting holes 34 of the flow rate adjusting plate 30 . In other words, the plurality of flow rate adjustment holes 34 of the flow rate adjustment plate 30 serve as the first branched flow channel forming portions. The second flow path 12 is formed inside the body portion 10 . That is, the body portion 10 becomes the second flow path forming portion.

The first opposing surface 32 of the flow rate adjusting plate 30 and the second opposing surface 14 of the body portion 10 are moved relative to each other by rotating the main shaft 60 held by the body portion 10 with the handle 40 . As a result, the first branch channel 56 (flow control hole 34) communicating with the second channel 12 is selected. That is, the main shaft 60 and the handle 40 held by the main body 10 function as a relative movement mechanism for the first opposing surface 32 and the second opposing surface 14 . In addition, although the structure which relatively moves by rotational motion is illustrated here, the 1st opposing surface 32 and the 2nd opposing surface 14 can also be relatively moved by linear reciprocating motion.

<Details of the ring groove>
As shown enlarged in FIG. 6(C), Wm is the maximum groove depth of the ring groove portion 16 in the axial direction J, and Fm is 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 into two. , the ring groove portion 16 satisfies Wm>Fm. That is, the cross-sectional shape of the ring groove portion 16 of the cut surface (groove cross section) along the central axis is a rectangle with the long side in the axial direction J and the short side in the radial direction.

<Details of the shape of the ring member>
As shown enlarged in FIGS. 5A and 5B, the ring member 100 has a maximum ring width in the axial direction J of Wr, and a maximum ring thickness obtained by dividing the difference between the maximum outer diameter Rmax and the minimum inner diameter Rmin into two by Fr. , satisfies Wr>Fr. That is, as shown in FIG. 5B, the cross-sectional shape of the cut surface (ring cross section) along the central axis is a non-perfect circular shape in which the axial direction J is the long side and the radial direction is the short side. 5A and 5B are based on the ring member 100 alone before being housed in the ring groove portion 16. As shown in FIG. That is, the shape of the ring member 100 is based on the open state in which no external force is applied in the axial direction or the radial direction.

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 a so-called tightening margin, and by accommodating the ring member 100 in the ring groove portion 16 while enlarging the diameter, the airtightness on the inner peripheral side is enhanced. This interference (Kmin-Rmin) is preferably 3% or more of Kmin, desirably 5% or more.

Considering the posture of the ring member 100 that can be accommodated in the ring groove portion 16 shown in FIG. 6, the ring member 100 in the open state shown in FIG. It has a front convex region 110 . The near side convex region 110 includes a curved portion having a radius of curvature of less than Fm/2 near the convex end (apex).

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

In addition, the ring member 100 in the open state of FIG. 5(B) has an outer convex region 120 which 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. have The minimum radius of curvature of the outer convex region 120 is set 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 later).

Furthermore, the ring member 100 in the open state of FIG. 5B has an inner convex region that is convex radially inward in the ring cross section within the inner peripheral range (see FIG. 6) facing the inner wall 16D of the ring groove portion 16. 130. The inner convex region 130 includes a curved portion with a radius of curvature of Wr/2 or less near the convex end (vertex), preferably includes a curved portion with a radius of curvature of Fr or less near the convex end (vertex), more preferably. includes a curved portion with a radius of curvature of Fr/2 or less in the vicinity of the convex end (apex). The minimum radius of curvature of the inner convex region 130 is set 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 recessed region 125 having a recessed shape in the ring cross section in the outer peripheral range (see FIG. 6) facing the outer wall 16C of the ring groove portion 16. As shown in FIG. This outer recessed region 125 can be expressed as a region that forms a valley recessed toward the real portion 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. A region 125 includes a range in which the slope angle of the outline increases in the counterclockwise direction. In the present embodiment, the range is the inflection point where the contour is bent in a V-shape in the direction of increasing the tilt angle, but it may be a concave curved range in which the tilt angle gradually increases. At this time, the place where the change in the tilt angle becomes zero becomes the boundary between the convex region and the concave region. Further, for example, when the outer convex region 120 and the front side convex region 110 are regarded as wavy peaks, the outer concave region 125 includes a region that is concave toward the real part side of a 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. As shown in FIG.

Furthermore, the ring member 100 in the open state of FIG. 5B has an inner recessed region 135 having a recessed shape in the ring cross section in the inner peripheral range (see FIG. 6) facing the inner wall 16D of the ring groove portion 16. . This inner recessed region 135 can be expressed as a region that forms a valley recessed toward the real part of the cross section when the contour of the ring cross section is taken as a waveform. In the right side cross section of the two ring cross sections in FIG. 135 includes a range in which the slope angle of the outline decreases in the counterclockwise direction. In the present embodiment, the range is the inflection point where the contour is bent in a V-shape in the direction of decreasing the tilt angle, but it may be a concave curved range in which the tilt angle gradually decreases. At this time, the place where the change in the tilt angle becomes zero becomes the boundary between the convex region and the concave region. Further, for example, when the inner convex region 130 and the front convex region 110 are regarded as wavy crests, the inner concave region 135 includes a region that is concave toward the real part side of a tangent line 130P connecting the crests. . 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. As shown in FIG.

Further, in the ring member 100 in the open state shown in FIG. 5B, the maximum thickness F2r in the radial direction (the X-axis direction in the figure) of the front side convex region 110 in the ring cross section is greater than the maximum groove thickness of the ring groove portion 16 Fm. is also small. More specifically, the maximum thickness F2r in the radial direction (the X-axis direction in the figure) in the range from the front convex region 110 to the outer convex region 120 and the inner convex region 130 is the maximum groove thickness of the ring groove portion 16. Thickness less than Fm. The maximum thickness F2r is desirably 80% or less of Fm, more desirably 70% or less. In this embodiment, it is set to 67%.

In FIG. 5B, when the maximum ring width of the ring member 100 is considered based on the central line M passing through the center of Wr and perpendicular to the axial direction J, the ring cross section is a line with the central line M as a base line. It becomes a symmetrical shape. That is, when the ring member 100 is reversed, the front-side convex region 110 becomes the back-side convex region 140 , and the back-side convex region 140 becomes the front-side convex region 110 . Since there is no restriction on the insertion direction of the ring member 100 into the ring groove portion 16, assembly errors can be reduced.

The relationship between the ring groove portion 16 and the ring member 100 in the mode in which the ring member 100 is accommodated in the ring groove portion 16 will be described with reference to FIG. Note that even in this state, the state in which the ring member 100 is not subjected to an axial external force (a crushing external force) is used as a reference.

Between the outer peripheral edge 16A of the opening of the ring groove portion 16 and the ring member 100, a gap (hereinafter referred to as outer gap) 150A is formed. The radial distance Sa of the outer peripheral gap 150A is set to 5% or more of the maximum groove width Fm, preferably 10% or more of Fm. The outer peripheral gap 150A extends to the inner side in the axial direction J from the outer peripheral edge 16A, and the maximum distance La is set to 20% or more of the maximum groove depth Wm, preferably 30% or more. set.

Further, a gap (hereinafter referred to as an inner peripheral side gap) 150B is formed between the inner peripheral edge 16B of the opening of the ring groove portion 16 and the ring member 100 . The radial distance Sb of the inner clearance 150B is set to 5% or more of the maximum groove width Fm, preferably 10% or more of Fm. The inner peripheral gap 150B extends inward in the axial direction J from the inner peripheral edge 16B, and the maximum distance Lb is set to be 20% or more, preferably 30% or more, of the maximum groove depth Wm. is set to

<Explanation of actions of ring groove and ring member>
FIG. 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 axially crushed and contracted.

As shown in FIG. 6(A), the front convex region 110 of the ring member 100 is pressed against the flow rate adjusting 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 control plate 30 and the front convex region 110 becomes small, and the surface pressure increases. As a result, fluid sealing properties are enhanced.

The inner convex region 130 of the ring member 100 is pressed against the inner wall 16D of the ring groove portion 16 by an interference (Kmin-Rmin). Since 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 becomes small and the surface pressure increases. As a result, fluid sealing properties are enhanced.

The front convex region 110 and the inner convex region 130 enclose the gap between the first facing surface 32 of the flow rate adjustment plate 30 and the second facing surface 14 of the main body 10 in a highly airtight manner. Communicating space 190 is formed to connect 56 and second channel 12 .

The high-pressure gas on the side of the first main flow path 54 enters the outer wall 16C and the bottom surface 16E of the ring groove portion 16 via the periphery of the flow rate adjusting plate 30 as indicated by arrow A, and flows from the bottom surface 16E to the inner wall 16D. reach. On the other hand, the high-pressure gas on the side of the first main channel 54 is decompressed due to pressure loss caused by the orifice of the flow rate adjustment hole 34 (the first branch channel 56), as indicated by arrow B, and the communication space 190 and the second It flows into the channel 12 . Although there is a pressure difference between the front convex region 110 and the inner convex region 130, which form the boundary between the communication space 190 and the first main flow path 54, mutual movement of the gas is suppressed because of the good sealing characteristics of the fluid. . As a result, the highly accurate flow rate adjustment function by the flow rate adjustment hole 34 can be exhibited. Although the case where the pressure on the first main flow path 54 side is high and the pressure on the second flow path 12 side is low is illustrated here, the opposite is also possible. That is, the fluid may flow from the second flow path 12 to the first main flow path 54 side.

As shown in FIGS. 7A and 7B, when the flow rate adjusting plate 30 is moved in the direction of the arrow C to select another flow rate adjusting hole 34, the flow rate adjusting plate 30 and the front convex region 110 slide. . As indicated by the dotted line D, the front convex region 110 is deformed by the frictional force generated on the contact surface and displaced in the moving direction (arrow C) of the flow rate adjusting plate 30 .

Since the ring groove portion 16 and the ring member 100 have long cross-sectional shapes in the axial direction J, the ring member 100 is less likely to protrude from the ring groove portion 16 even if the front side convex region 110 is deformed. In other words, the ring member 100 is held at a long distance in the axial direction J by the ring groove portion 16, so the amount of deformation of the front-side convex region 110 is naturally restricted.

Further, at this time, an outer peripheral gap 150A and/or an inner peripheral gap 150B is 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 less likely to enter the gap between the flow rate adjusting plate 30 and the main body 10. As a result, damage to the front-side convex region 110 is suppressed, so that high sealing performance can be maintained for a long period of time. Furthermore, since the inner convex region 130 is sufficiently separated from the inner peripheral edge 16B of the ring groove portion 16 in the axial direction J, even if the front convex region 110 is deformed or displaced, the influence thereof is less likely to be transmitted to the inner convex region 130. Therefore, the sealing property of the inner convex region 130 can be maintained in a favorable state.

<Action of Conventional Ring Groove and Ring Member>
FIG. 8 shows the action of the conventional ring groove portion 1600 and the ring member 1100 for reference. The maximum groove depth Wm of the ring groove portion 1600 is smaller than the maximum groove thickness Fm. That is, the cross-sectional shape of the cut surface (groove cross section) along the central axis is a rectangle with the short side in the axial direction J and the long side in the radial direction. The ring member 1100 accommodated in the ring groove portion 1600 employs a so-called O-ring having a circular cross section 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 adjusting plate, thereby deforming into an elliptical cross-sectional shape with a major axis in the radial direction and a 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 regulating plate increases, and the surface pressure decreases, so the fluid sealing characteristics tend to deteriorate.

As shown in FIGS. 8B and 8C, when the flow rate adjusting plate is moved in the direction of arrow C, the front convex region 11000 slides and deforms/displaces as indicated by dotted line D. FIG. At this time, the front side 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 side convex region 11000 is formed in the gap between the flow rate adjusting plate and the main body as shown in FIG. 8(C). 11000 enters, and the near side convex region 11000 is easily damaged. Furthermore, since the inner convex region 13000 is close to the inner peripheral edge 1600B, when the front convex region 11000 is deformed or displaced, the inner convex region 13000 is easily exposed to the outside from the inner peripheral edge 1600B of the ring groove portion 1600. Fluid sealing characteristics tend to deteriorate.

<First Modification of First Embodiment>
Next, with reference to FIG. 9, a first modified example of the flow rate adjustment unit 1 according to the first embodiment will be described. Since the modification differs only in the shape of the ring member 300, only the differences between the ring member 100 and the ring member 300 will be described, and other descriptions will be omitted. In addition, about parts and members other than the ring member 300, the same code|symbol as the code|symbol used by the flow control unit 1 of 1st embodiment is used.

The ring member 300 satisfies Wr>Fr with respect to the maximum ring width Wr and the maximum ring thickness Fr. That is, the cross-sectional shape of the cut surface (ring cross section) along the central axis is a non-perfect circular shape with the axial direction J being the long side and the radial direction being the short side.

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

The ring member 300 in the open state has a rear-side convex region 340 that has a convex shape on the rear side in the axial direction J in the ring cross section. The radius of curvature of the inner convex region 340 is set to be substantially the same as that of the outer convex region 320 and the inner convex region 330, which will be described later.

The ring member 300 in the open state has an outer convex region 320 having a radially outward convex shape 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 region 320 is set larger than the minimum radius of curvature of the front convex region 310 and substantially 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 having a radially inwardly convex shape in the ring cross section within the inner peripheral range facing the inner wall 16D of the ring groove portion 16 . The radius of curvature of the inner convex region 330 is set to be smaller than the minimum radius of curvature of the front convex region 310 and substantially the same as the radius of curvature of the outer convex region 320 .

In addition, in this modified example, the inner convex region 340, the outer convex region 320, and the inner convex region 330 form a region whose cross section is a regular arc.

Furthermore, the ring member 300 in the open state has an outer recessed region 325 having 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 recessed toward the real portion side of the cross section when the contour of the ring cross section is captured as a waveform. For example, when the outer convex region 320 and the near side convex region 310 are regarded as wavy peaks, the outer concave region 325 includes a region that is concave toward the real part side of a tangent line 320P connecting the peaks. In the present embodiment, an outer concave region 325 is formed adjacent to the front side of the outer convex region 320 in the axial direction J. As shown in FIG.

Furthermore, the ring member 300 in the open state has an inner recessed region 335 having a recessed shape in the ring cross section in the inner peripheral 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 recessed toward the real part of the cross section when the contour of the ring cross section is captured as a waveform. For example, when the inner convex region 330 and the near side convex region 310 are regarded as wavy peaks, the inner concave region 335 includes a region that is concave on the real side from a tangent line 330P connecting the peaks. In the present embodiment, an inner concave region 335 is formed adjacent to the front side of the inner convex region 330 in the axial direction J. As shown in FIG.

Further, in the ring member 300 in the open state, the maximum thickness F2r in the radial direction (the X-axis direction in the figure) of the front side 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 (the X-axis direction in the figure) in the range from the front convex region 310 to the outer convex region 320 and the inner convex region 330 is the maximum groove thickness of the ring groove portion 16. Thickness less than Fm. The maximum thickness F2r is desirably 80% or less of Fm, more desirably 70% or less.

The relationship between the ring groove portion 16 and the ring member 300 in the mode in which the ring member 300 is housed in the ring groove portion 16 will be described with reference to FIG. Note that even in this state, the state in which the ring member 100 is not subjected to an axial external force (a crushing external force) is used as a reference.

Between the outer peripheral edge 16A of the opening in the ring groove portion 16 and the ring member 300, a gap (hereinafter referred to as outer gap) 350A is formed. The radial distance Sa of the outer peripheral gap 350A is set to 5% or more of the maximum groove width Fm, preferably 10% or more of Fm. This outer peripheral gap 350A extends to the far side in the axial direction J from the outer peripheral edge 16A as a starting point. More preferably, it is set to 40% or more.

Further, a gap (hereinafter referred to as an inner peripheral side gap) 350B is formed between the inner peripheral edge 16B of the opening of the ring groove portion 16 and the ring member 300 . The radial distance Sb of the inner peripheral gap 350B is set to 5% or more of the maximum groove width Fm, preferably 10% or more of Fm. The inner peripheral gap 350B extends from the inner peripheral edge 16B toward the inner side in the axial direction J, and the maximum distance Lb is set to 20% or more, preferably 30% or more, of the maximum groove depth Wm. , and more preferably set to 40% or more.

In the ring member 300 of this modified example, the ring-shaped contact area between the front convex region 310 and the flow rate adjusting plate 30 is reduced, and the surface pressure is increased. As a result, fluid sealing properties are enhanced.

The radius of curvature of the inner convex region 330 of the ring member 300 is greater than that of the ring member 100 already shown. By ensuring a large interference (Kmin-Rmin), the contact pressure can be increased. As a result, fluid sealing properties can be enhanced.

When the flow rate adjusting plate 30 is moved in the direction of arrow C, the flow rate adjusting plate 30 and the front convex region 310 slide, and as indicated by the dotted line D, the front convex region 310 is deformed and displaced by the frictional force. At this time, since the outer peripheral gap 350A and/or the inner peripheral gap 350B are secured around the front convex region 310, the front side gap 350A and/or the inner peripheral gap 350B is secured. As long as the convex region 310 is displaced, the front side convex region 310 is less likely to enter the gap between the flow rate adjusting plate 30 and the body portion 10 . As a result, damage to the front convex region 310 is suppressed, so that high airtightness can be maintained for a long period of time. Furthermore, since the inner convex region 330 is sufficiently separated from the inner peripheral edge 16B of the ring groove portion 16 in the axial direction J, even if the front side convex region 310 is deformed or displaced, the influence thereof is less likely to be transmitted to the inner convex region 330. Therefore, good sealing properties of the inner convex region 330 can be maintained.

<Second Modification of First Embodiment>
Next, with reference to FIG. 10, a second modification of the flow rate adjustment unit 1 according to the first embodiment will be described. Since the second modification differs only in the shape of the ring member 400, only the differences between the ring member 100 and the ring member 400 will be described, and other descriptions will be omitted. In addition, about parts and members other than the ring member 400, the same code|symbol as the code|symbol used by the flow control unit 1 of 1st embodiment is used.

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

The ring member 400 in the open state has a front-side convex region 410 that is convex toward the front side in the axial direction J in the ring cross section. The radius of curvature of the front convex region 410 is set to be substantially the same as that of the outer convex region 420 and the inner convex region 430, which will be described later.

The ring member 400 in the open state has a rear-side convex region 440 that is convex toward the rear side in the axial direction J in the ring cross section. The radius of curvature of the inner convex region 440 is set substantially the same as that of the outer convex region 420 and the inner convex region 430, which will be described later.

The ring member 400 in the open state has a plurality (here, three) of 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 region 420 is set to be substantially the same as the radius of curvature of the front side convex region 410 and the inner convex region 430 .

The ring member 400 in the open state has a plurality of (here, three) inner convex regions 430 that are convex radially inward in the ring cross section within the inner peripheral range facing the inner wall 16D of the ring groove portion 16 . The radius of curvature of the inner convex region 430 is set to be substantially 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 outer convex region 420 on the frontmost side, and the inner convex region 430 on the frontmost side form a region whose cross section is a perfect circle. In addition, an area having a cross section of a regular arc is formed by the inner convex area 440, the innermost outer convex area 420, and the innermost inner convex area 430. FIG.

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 real part of the cross section when the contour of the ring cross section is captured as a waveform. For example, when the plurality of outer convex regions 420 are regarded as wavy crests, the outer concave region 425 includes a region that is concave toward the real part side of a tangent line 420P connecting the crests. In this embodiment, a total of two outer concave regions 425 are formed between the plurality of outer convex regions 420 .

Furthermore, the ring member 400 in the open state has an inner recessed region 435 having a recessed shape in the ring cross section in the inner circumferential range facing the inner wall 16D of the ring groove portion 16. As shown in FIG. This inner recessed region 435 can be expressed as a region that forms a trough recessed toward the real portion side of the cross section when the contour of the ring cross section is captured as a waveform. For example, when the plurality of inner convex regions 430 are regarded as wavy peaks, the inner concave region 435 includes a region that is concave on the real side from a tangent line 430P connecting the peaks. In this embodiment, a total of two inner concave regions 435 are formed between the plurality of inner convex regions 430 .

The relationship between the ring groove portion 16 and the ring member 400 in the mode in which the ring member 400 is accommodated in the ring groove portion 16 will be described with reference to FIG.

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

Since the ring member 400 has a plurality of inner protruding regions 430, it is possible to improve the sealing characteristics by a multi-step sealing function. In addition, since the radius of curvature of each inner convex region 430 can be set smaller by the number of inner convex regions 430 dispersed, the surface pressure can be increased.

When the flow regulating plate 30 is moved in the direction of arrow C, the flow regulating plate 30 and the front convex region 410 slide, and as indicated by the dotted line D, the front convex region 410 tends to deform and displace due to the frictional force. . At this time, since a plurality of inner convex regions 430 are provided, the frictional force with the inner peripheral wall 16</b>D acts as a resistance, and displacement of the front side convex regions 410 is suppressed.

Furthermore, since the middle or innermost inner convex region 430 is sufficiently separated from the inner peripheral edge 16B of the ring groove portion 16 in the axial direction J, even if the front convex region 410 is deformed or displaced, the effect of the inner convex region 430 will not affect the depth. Since it is less likely to be transmitted to the inner convex region 430 on the side, the sealing property of the inner convex region 430 can be maintained in a good state.

In FIG. 10(B), when the maximum ring width of the ring member 400 is considered based on the center line M passing through the center of Wr and perpendicular to the axial direction J, the ring cross section has a line symmetrical shape with the center line M as the base line. becomes. That is, when the ring member 400 is reversed, the front side convex region 410 becomes the back side convex region 440 , and the back side convex region 440 becomes the front side convex region 410 . Since there is no restriction on the insertion direction of the ring member 400 into the ring groove portion 16, assembly errors can be reduced.

In addition, in the ring member 400 of the second modification, the case where each of the three outer convex regions 420 and the three inner convex regions 430 is formed is illustrated, but the present invention is not limited to this, and two of each are formed. and cases in which four or more of each are formed. It also includes the case where the number of the outer convex regions 420 and the number of the inner convex regions 430 do not match. The two include the case where the number of inner convex regions 430 is three or more.

<Third Modification of First Embodiment>
Next, with reference to FIG. 11, a third modification of the flow regulating unit 1 according to the first embodiment will be described. In the flow regulating unit 2 of the third modified example, different points from the flow regulating unit 1 will be mainly described, and descriptions of the same or similar parts and members will be omitted. For convenience of explanation, the same names and symbols as those used in the flow rate adjustment unit 1 of the first embodiment are used for parts and members of the flow rate adjustment unit 2 .

The first facing surface 32 of the flow rate adjusting plate 30 faces the flow path forming body 50 side. A rear surface 36 of the flow rate adjusting plate 30 faces the body portion 10 . An annular flow path 36A is formed on the rear surface 36 side. A plurality of flow rate adjusting holes 34 penetrating to the first opposing surface 32 are formed in the circumferential direction in the bottom surface of the concave portion of the annular flow path 36A.

A gap N1 is formed between the flow rate adjusting plate 30 and the body portion 10, and serves as a flow path through which gas flows. Further, a channel N2 communicating with the gap N1 is formed on the channel forming body 50 side. The gap N<b>1 and the flow path N<b>2 correspond to the first main flow path 54 .

A second opposing surface 14 facing the first opposing surface 32 is formed in the flow path forming body 50 . A second flow path 12 is formed in the flow path forming body 50 , and a second opening 12</b>A thereof 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 accommodated in the ring groove portion 16 . An auxiliary ring groove portion 26 is recessed in the second facing surface 14 , and a first auxiliary ring member 27 and a second auxiliary ring member 28 are accommodated in the auxiliary ring groove portion 26 .

A spring 46 is arranged between the flow rate adjusting plate 30 and the body portion 10 . The spring 46 urges the first opposing surface 32 of the flow rate adjusting 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 highly airtightly surrounds the gap between the first opposing surface 32 of the flow rate adjusting plate 30 and the second opposing surface 14 of the flow path forming body 50, and the first branch flow path 56 (flow rate A communication space 190 is formed that connects the adjustment hole 34) and the second flow path 12 .

In the flow rate adjusting unit 2 of this third modification, the arrangement of the first main flow path 54, the first branch flow path 56, and the second flow path 12 is different. It is common with the adjusting unit 1 in all respects.

<Second embodiment (flow control valve)>
Next, a fluid regulating valve 600 according to a second embodiment will be described with reference to FIGS. 12 and 13. FIG. This fluid adjustment valve 600 is connected to the gas cylinder B, for example, to adjust the flow rate and pressure of the gas released from the gas cylinder B. As shown in FIG.

The fluid adjustment valve 600 includes a valve housing 610, a filling port 620 formed in the valve housing 610 for filling the gas cylinder B with gas, a check valve unit 630 provided inside the filling port 620, and a valve It has an upstream decompression unit 640 A installed in the housing 610 , the 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 . A downstream decompression unit 640B is provided inside the flow path forming body 50 in the flow rate adjusting unit 1 .

The valve housing 610 is formed with a male threaded portion (connection portion) 612 that is screwed with the female threaded portion of the gas cylinder B. As shown in FIG. A first flow path 710 that can communicate with the gas cylinder B is formed in the male threaded portion 612 . This first channel 710 guides the gas to the pressure measuring unit 650 . The filling port 620 is connected to the first flow path 710 via a check valve unit 630 so that the gas cylinder B can be filled with a desired gas from the outside. The filling port 620 is provided with a filling port cap 622 .

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

The upstream decompression unit 640A serves as a known decompression 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 decompression unit 640B serves as a known decompression valve that further decompresses the pressure of the gas that has passed through the second flow path 720 from the upstream decompression unit 640A and provides it to the flow rate adjustment unit 1 .

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

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

Although the above-described fluid control valve 600 has been exemplified as a continuous supply system in which the fluid always flows at the set flow rate and set pressure, the present invention is not limited to this, and furthermore, by adding a tuning unit, Fluid supply/stop may be performed according to the pressure change.

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

It should be noted that the present invention is not limited to the above-described embodiments, and it goes without saying that various modifications can be made without departing from the gist of the present invention.

1 Flow Control Unit 10 Main Body 11 Main Shaft Hole 12 Second Channel 12A Second Opening 12B Open End 14 Second Opposing Surface 16 Ring Groove Portion 30 Flow Control Plate 32 First Opposing Surface 34 Flow Control Hole 50 Flow Channel Forming Body 54 Second One main channel 56 First branch channel 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 peripheral 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 Back convex area 350A Outer circumference gap 350B Inner 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 Inner convex area 600 Fluid adjustment valve

Claims (15)

A flow rate adjustment unit that adjusts the flow rate of a fluid,
a first main flow path forming portion in which the first main flow path is formed;
a first branch flow path forming portion branched from the first main flow path and formed therein with a plurality of first branch flow paths having different pressure losses;
a second flow path forming portion 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 channel forming portion and having a first branch opening serving as an open end of the plurality of first branch channel;
A second opposing surface provided in the second flow path forming portion, having a second opening serving as an open end of the second flow path, and facing the first opposing surface with a gap therebetween;
a relative movement mechanism that selects the first branch channel that communicates with the second channel by relatively moving the first opposing surface and the second opposing surface in a planar direction;
a ring groove recessed in the first opposing surface or the second opposing surface so as to surround the periphery of the first branch opening or the periphery of the second opening;
A ring member that is disposed in the ring groove portion and partially protrudes from the ring groove so as to contact the first opposing surface or the second opposing surface (hereinafter referred to as the mating opposing surface) that is a counterpart. prepared,
The ring groove is
Wm>Fm, where Wm is the maximum groove depth in the axial direction and Fm is the maximum groove thickness obtained by dividing the difference between the maximum outer diameter and the minimum inner diameter, and
The ring member before receiving an axial external force in the ring groove,
Where Wr is the maximum ring width in the axial direction, and Fr is the maximum ring thickness obtained by dividing the difference between the maximum outer diameter and the minimum inner diameter, Wr>Fr is satisfied,
flow control unit. A gap (hereinafter referred to as an outer gap) is formed between the outer peripheral edge of the opening in the ring groove portion and the ring member before receiving an axial external force in the ring groove portion,
The flow control unit according to claim 1. A gap (hereinafter referred to as an inner peripheral side gap) is formed between the inner peripheral edge of the opening in the ring groove portion and the ring member before receiving an axial external force in the ring groove portion,
The flow rate adjustment unit according to claim 1 or 2. When defining the opening side of the ring groove portion in the axial direction as the front side in the axial direction and the bottom side as the rear side in the axial direction,
The outer peripheral side gap and/or the inner peripheral side gap extends from the outer peripheral edge or the inner peripheral edge toward the inner side in the axial direction for 10% or more of the maximum groove depth Wm,
The flow rate adjustment unit according to claim 2 or 3. The outer peripheral side gap or the inner peripheral side gap is 5% or more of the maximum groove thickness Fm,
The flow rate adjustment unit according to claim 2 or 3. When the axial open end side of the ring groove portion is defined as the axial front side, the axial bottom side is defined as the axial rear side, and the cross section along the central axis of the ring member is defined as the ring cross section,
The ring cross-section has a front-side convex region that is convex on the front side in the axial direction,
The front side convex region includes a curved portion with a radius of curvature of less than Fm / 2,
A flow rate adjusting unit according to any one of claims 1 to 5. When defining a cross section along the radial direction and the axial direction of the ring member as a ring cross section,
characterized by having an outer recessed region having a recessed shape in a range facing the outer wall of the ring groove portion of the ring cross section,
A flow regulating unit according to any one of claims 1-7. An outer convex region having a convex shape is provided in a range facing the outer wall of the ring groove portion of the ring cross section,
characterized in that the outer concave regions are formed on both sides of the outer convex region,
The flow control unit according to claim 8. A plurality of outer convex regions having a convex shape are provided in a range facing the outer wall of the ring groove portion of the ring cross section,
characterized in that the outer concave region is formed between a plurality of the outer convex regions,
The flow control unit according to claim 8. When defining a cross section along the radial direction and the axial direction of the ring member as a ring cross section,
characterized by having an inner recessed region having a recessed shape in a range facing the inner wall of the ring groove portion of the ring cross section,
A flow regulating unit according to any one of claims 1-11. An inner convex region having a convex shape is provided in a range facing the inner wall of the ring groove portion of the ring cross section,
The outer concave regions are formed on both sides of the inner convex region, respectively,
The flow regulation unit according to claim 12. A plurality of inner convex regions having a convex shape are provided in a range facing the inner wall of the ring groove portion of the ring cross section,
characterized in that the inner concave region is formed between a plurality of the inner convex regions,
The flow regulation unit according to claim 12. The inner convex region includes a curved portion with a radius of curvature of Wr / 2 or less,
A flow control unit according to claim 13 or 14. The inner convex region includes a curved portion with a radius of curvature of Fr or less,
A flow control unit according to claim 13 or 14. A fluid regulating valve for regulating fluid flow, comprising:
a pressure adjustment unit that adjusts the pressure of the fluid;
a flow regulating unit according to any one of claims 1 to 16, wherein the fluid whose pressure is regulated by the pressure regulating unit is guided;
A fluid regulating valve comprising:

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