Eddy current type fluid mixer

Abstract

To prevent formation of regions where a fluid may stagnate inside an inline fluid mixer that mixes different types of fluids.SOLUTION: A vortex fluid mixer 11 comprises: a vortex chamber 25 which is defined by a cylindrical peripheral side wall 13 and by a first end wall 15 and a second end wall 17 that are provided at both ends of the peripheral side wall and that face each other; an inlet flow path 19 which opens to the peripheral side wall 13; an outlet flow path 21 which opens to the first end wall 15; and at least one additive flow path 23 which is connected to an intermediate portion of the outlet flow path 21 and which adds an additive fluid to the fluid flowing through the outlet flow path 21. The outlet flow path 21 is provided to pass through an approximate center of the first end wall 15, and the vortex chamber 25 is configured such that the fluid flowing in through the inlet flow path 19 generates a swirling flow in the vortex chamber 25 and flows out through the outlet flow path 21 while generating the swirling flow.SELECTED DRAWING: Figure 1

Description

Technical Field

[0001] The present invention relates to a vortex-type fluid mixer that is used in fluid transport pipes in various industries such as chemical factories, semiconductor manufacturing fields, food fields, medical fields, and bio fields, and mixes two or more fluids using vortices.

Background Art

[0002] In various industrial fields such as chemical factories, semiconductor manufacturing fields, food fields, medical fields, and bio fields, as a method of mixing fluids flowing in a pipe, for example, a static mixer using a twisted blade-shaped static mixer element as disclosed in Patent Document 1 is generally used. Usually, the static mixer element has a structure in which a plurality of minimum unit members are connected in series with a rectangle plate twisted 180 degrees around the longitudinal axis as the minimum unit member. In a typical static mixer, the end of the right element (the end in the twisting axis direction) with a shape in which the rectangular plate is twisted 180 degrees in the right rotation direction and the end of the left element (the end in the twisting axis direction) with a shape in which the rectangular plate is twisted 180 degrees in the left rotation direction are joined so as to be orthogonal to each other at a plurality of locations in the fluid flow direction and installed in the pipe. With such a configuration, the fluid flowing in the pipe is divided into two each time it passes through one element, and as the fluid flows along the twisted surface of the element, the action of conversion from the center of the pipe to the pipe wall and the action of reversing the twisting direction of the flow are given, and the fluid is stirred and uniformly mixed in the radial direction of the pipe.

Prior Art Documents

Patent Documents

[0003]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0004] In a static mixer as described in Patent Document 1, a static mixer element is only detachably inserted and arranged inside a pipe, and there is a gap between the pipe wall and the outer peripheral portion of the element. In such a gap, fluid is likely to stagnate. Further, if the shape of the static mixer element is made complex for stirring, a stagnant portion is likely to occur. Such fluid stagnation causes deterioration of the fluid and solidification of the slurry. In particular, when used in semiconductor manufacturing or when a static mixer is used for mixing chemical solutions, stagnation of the chemical solution causes deterioration of the chemical solution, and application of the deteriorated chemical solution to a semiconductor wafer causes defective products. Further, when a static mixer is used for mixing slurry, solidification of the slurry increases the frequency of maintenance.

[0005] Therefore, an object of the present invention is to solve the problems existing in the prior art and to prevent a portion where fluid stagnates from occurring in an in-line type fluid mixer for mixing different types of fluids.

Means for Solving the Problems

[0006] In view of the above object, the present invention provides a vortex chamber defined by a substantially cylindrical peripheral side wall and a first end wall and a second end wall provided at both ends of the peripheral side wall and facing each other, an inlet flow path extending along the central axis of the inlet flow path and opening in the peripheral side wall, an outlet flow path extending along the central axis of the outlet flow path and opening in the first end wall, and at least one addition flow path connected to an intermediate portion of the outlet flow path for adding an addition fluid to the fluid flowing through the outlet flow path. The second end wall is constituted by a diaphragm, The outlet flow path is provided such that the central axis of the outlet flow path passes through the approximate center of the first end wall. The vortex chamber is configured such that the fluid flowing in through the inlet flow path generates a vortex swirling flow in the vortex chamber and flows out from the outlet flow path while generating the swirling flow. A vortex type fluid mixer is provided in which the addition fluid added from the addition flow path is stirred and mixed with the fluid in the outlet flow path by the action of the swirling flow.

[0007] In the above-described vortex-type fluid mixer, a vortex chamber is defined by a cylindrical peripheral side wall and first and second end walls provided at both ends thereof and facing each other. An inlet flow path opens to the peripheral side wall of the vortex chamber, and an outlet flow path opens to the first end wall. Further, the outlet flow path is provided such that the central axis of the outlet flow path passes through the approximate center of the first end wall. When fluid flows into the vortex chamber from the inlet flow path, a vortex-like swirling flow is generated in the vortex chamber. Furthermore, since the vortex chamber has a cylindrical peripheral side wall and the central axis of the outlet flow path is provided so as to pass through the approximate center of the first end wall, the fluid in the vortex chamber flows out from the outlet flow path while generating a swirling flow. Therefore, a swirling flow is also generated in the outlet flow path. Since the additive fluid is added from the additive flow path to the swirling flow in the outlet flow path, the additive fluid is agitated and mixed with the fluid in the outlet flow path by the action of the swirling flow.

[0008] In the above-described vortex-type fluid mixer, it is preferable that the additive flow path is connected to the outlet flow path in a region where a swirling flow is generated in the outlet flow path.

[0009] It is preferable that the inlet flow path is provided such that the central axis of the inlet flow path passes through a position away from the vortex chamber central axis connecting the centers of the first end wall and the second end wall, and it is more preferable that the fluid is provided to flow into the peripheral side wall in a tangential direction from the inlet flow path.

[0010] Also, it is preferable that the length of the outlet flow path is 7.5 times or more the diameter of the outlet flow path.

[0011] In addition, it is preferable that the additive flow path is provided such that the central axis of the additive flow path is arranged at a distance within 8 times the diameter of the outlet flow path in the direction of the central axis of the outlet flow path from the upstream end of the outlet flow path, and it is more preferable that the central axis of the additive flow path is arranged at a distance within 4 times the diameter of the outlet flow path in the direction of the central axis of the outlet flow path from the upstream end of the outlet flow path.

[0012] In one embodiment , the The recording diaphragm can be moved by a driving unit so as to approach and separate from the first end wall.

[0013] Also, The present invention includes a volute chamber defined by a generally cylindrical peripheral side wall and first and second end walls provided at both ends of the peripheral side wall and facing each other, an inlet flow path extending along the center axis of the inlet flow path and opening to the peripheral side wall, an outlet flow path extending along the center axis of the outlet flow path and opening to the first end wall, and at least one addition flow path connected to an intermediate portion of the outlet flow path for adding an additive fluid to the fluid flowing through the outlet flow path, A flow rate adjustment valve for adjusting the flow rate of the additive fluid added from the additive flow path to the outlet flow path and is provided such that the center axis of the outlet flow path passes through the approximate center of the first end wall. The volute chamber is configured such that the fluid flowing in through the inlet flow path generates a swirling flow in the volute chamber and flows out from the outlet flow path while generating the swirling flow. An additive fluid added from the addition flow path is stirred and mixed with the fluid in the outlet flow path by the action of the swirling flow, thereby providing a vortex type fluid mixer.

Advantages of the Invention

[0014] According to the present invention, the fluid flowing into the vortex chamber from the inlet flow path generates a swirling flow in the vortex chamber, and the fluid in the vortex chamber flows out from the outlet flow path while generating a swirling flow. As a result, a swirling flow is also generated in the outlet flow path. When the additive fluid is added from the additive flow path to the swirling flow of this outlet flow path, the additive fluid is stirred and mixed with the fluid in the outlet flow path by the action of the swirling flow. Therefore, mixing can be achieved without providing a static mixer element in the flow path, and since the fluid also flows along the cylindrical circumferential side wall in the vortex chamber, it is possible to suppress the generation of a stagnant portion.

Brief Description of the Drawings

[0015]

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Figure 11

[0016] Hereinafter, embodiments of the vortex-type fluid mixer according to the present invention will be described with reference to the drawings. First, with reference to FIG. 1, the overall configuration of the vortex-type fluid mixer 11 of the first embodiment will be described.

[0017] The vortex fluid mixer 11 includes a generally cylindrical peripheral side wall 13 extending along a central axis, a first end wall 15 and a second end wall 17 provided at both ends in the central axis direction of the peripheral side wall 13 so as to face each other, an inlet flow path 19, an outlet flow path 21, and an additive flow path 23 connected to an intermediate portion of the outlet flow path 21. The first end wall 15 and the second end wall 17 have the same generally circular shape and are provided so as to close both ends in the central axis direction of the peripheral side wall 13, and the space surrounded by the peripheral side wall 13, the first end wall 15, and the second end wall 17 constitutes a vortex chamber 25. A vortex chamber central axis O extending so as to connect the center of the first end wall 15 and the center of the second end wall 17 coincides with the central axis of the peripheral side wall 13 and extends perpendicular to the first end wall 15 and the second end wall 17.

[0018] The inlet flow path 19 extends along an inlet flow path central axis P1 in a direction perpendicular to the vortex chamber central axis O and opens to the peripheral side wall 13. The inlet flow path central axis P1 extends so as to pass through the center of the cross section of the inlet flow path 19. Further, the outlet flow path 21 extends from the vortex chamber 25 to the outside along an outlet flow path central axis P2 parallel to the vortex chamber central axis O and perpendicular to the first end wall 15, and opens to the first end wall 15 of the vortex chamber 25. The outlet flow path central axis P2 extends so as to pass through the center of the cross section of the outlet flow path 21. In the illustrated embodiment, both the inlet flow path 19 and the outlet flow path 21 are constituted by circular pipes having a circular cross-sectional shape. However, the cross sections of the inlet flow path 19 and the outlet flow path 21 are not limited to circular shapes, and may be polygonal shapes such as elliptical shapes or square shapes. Also, in the illustrated embodiment, the inlet flow path 19 is constituted by a straight circular pipe, but may have other shapes such as a nozzle shape as long as fluid can flow into the vortex chamber 25.

[0019] The inlet flow path 19 is provided such that the central axis P1 of the inlet flow path passes through an eccentric position away from the central axis O of the volute chamber. Therefore, the fluid flowing in from the inlet flow path 19 hits the circumferential side wall 13 in the volute chamber 25 and flows along the circumferential side wall 13 to generate a swirling flow, which becomes a vortex flow and heads towards the outlet flow path 21 and flows out from the outlet flow path 21. In order to facilitate the generation of a swirling flow, the inlet flow path 19 is preferably provided such that the fluid flowing into the volute chamber 25 from the inlet flow path 19 flows along the circumferential side wall 13. In the illustrated embodiment, the inlet flow path 19 extends in the tangential direction of the circumferential side wall 13 having a substantially cylindrical shape and is connected to the circumferential side wall 13 such that the central axis P1 of the inlet flow path is parallel to the tangent line, and the fluid flows into the volute chamber 25 from the inlet flow path 19 in a substantially tangential direction with respect to the circumferential side wall 13.

[0020] The outlet flow path 21 is provided such that the central axis P2 of the outlet flow path extends perpendicular to the first end wall 15 and passes through the approximate center of the first end wall 15, that is, the central axis P2 of the outlet flow path extends substantially in line with the central axis O of the volute chamber. With such a configuration, as shown in FIG. 2, the fluid flowing in from the inlet flow path 19 flows along the circumferential side wall 13 in the volute chamber 25 to generate a swirling vortex flow and heads towards the outlet flow path 21, and is discharged from the volute chamber 25 to the outlet flow path 21 while maintaining the swirling flow. Therefore, at least in the vicinity of the inlet of the volute chamber 25 to the outlet flow path 21 (the connection end between the volute chamber 25 and the outlet flow path 21, that is, the upstream end of the outlet flow path 21) in the outlet flow path 21, the swirling flow is maintained and it flows downstream in a vortex state.

[0021] The additive flow path 23 extends along the additive flow path central axis P3 and is connected near the inlet of the vortex chamber 25 to the outlet flow path 21 (i.e., the upstream end of the outlet flow path 21) within the range where the above-described swirling flow occurs in the outlet flow path 21, forming a confluence portion. That is, the confluence portion is configured to add the additive fluid from the additive flow path 23 to the main fluid while the main fluid discharged from the vortex chamber 25 to the outlet flow path 21 maintains the swirling flow. The confluence portion (confluence position) of the outlet flow path 21 and the additive flow path 23 is preferably provided such that the additive flow path central axis P3 of the additive flow path 23 is located within a range of a distance within 8 times the diameter of the outlet flow path 21 from the inlet of the outlet flow path 21 (i.e., the upstream end of the outlet flow path 21), and more preferably provided such that the additive flow path central axis P3 is located within a range of a distance within 4 times the diameter of the outlet flow path 21.

[0022] In the illustrated first embodiment, one end of a single linear additive flow path 23 is connected near the upstream end of a linear outlet flow path 21 such that the outlet flow path 21 and the additive flow path 23 extend perpendicularly, forming a T-shaped flow path. Fluid A, which is the main fluid supplied to the inlet flow path 19, flows into the upstream end of the outlet flow path 21 via the vortex chamber 25, and fluid B, which is the additive fluid, is supplied from the other end of the additive flow path 23 so that fluid A and fluid B merge at the confluence. The shape of the confluence is not limited to a T shape. For example, it may be a Y shape where the additive flow path 23 merges obliquely into the outlet flow path 21. Also, in the illustrated first embodiment, the central axis P3 of the additive flow path 23 extends parallel to the central axis P1 of the inlet flow path 19 for the purpose of reducing the installation space, and the inlet flow path 19 and the additive flow path 23 are arranged on the same side with respect to the vortex chamber 25. However, it is not necessary for the additive flow path central axis P3 to extend parallel to the inlet flow path central axis P1, nor is it necessary for the inlet flow path 19 and the additive flow path 23 to be arranged on the same side with respect to the vortex chamber 25, and the additive flow path 23 can extend in any direction. Furthermore, two or more additive flow paths 23 may be connected to the outlet flow path 21, or three or more types of fluids may be merged. The additive flow path 23 is preferably a linear circular pipe with a circular cross-section, similar to the outlet flow path 21, but is not limited to a circular pipe and can be a pipe with a cross-section of any shape.

[0023] In the vortex fluid mixer 11, the central axis P1 of the inlet flow path passes through an eccentric position away from the central axis O of the vortex chamber, and the central axis P2 of the outlet flow path extends through a position away from the central axis P1 of the inlet flow path. Therefore, in the vortex chamber 25, the main fluid supplied to the inlet flow path 19 and flowing into the vortex chamber 25 hits the circumferential side wall 13 and flows along the circumferential side wall 13 to generate a swirling flow, which becomes a vortex flow and heads toward the outlet flow path 21 and is discharged into the outlet flow path 21. Further, as shown in FIG. 2, the main fluid in the vortex chamber 25 is discharged from the outlet flow path 21 while generating a swirling flow, and the additive fluid is added to and merged with the main fluid from the additive flow path 23 within the range where the main fluid generates a swirling flow in the outlet flow path 21. Therefore, the additive fluid added from the additive flow path 23 to the main fluid of the swirling flow in the outlet flow path 21 is diffused into the main fluid by the stirring action of the swirling flow, and the variation in the concentration of different types of fluids (non-uniformity of the concentration distribution) can be reduced. From this, as long as the swirling flow is maintained in the outlet flow path 21, the longer the outlet flow path 21 is and the higher the flow velocity of the main fluid is, the more the effect of reducing the variation in concentration can be enhanced, and it is preferable that the length of the outlet flow path 21 is 7.5 times or more the diameter of the outlet flow path 21.

[0024] Note that the vortex fluid mixer according to the present invention can achieve the effect of reducing the variation in the concentration of different types of fluids (non-uniformity of the concentration distribution) as long as it generates a swirling vortex flow in the vortex chamber 25, discharges the main fluid into the outlet flow path 21 while maintaining the swirling flow, and adds the additive fluid from the additive flow path 23 to the main fluid that generates a swirling flow in the outlet flow path 21. Therefore, the vortex fluid mixer is not limited to the configuration of the embodiment illustrated in FIG. 1.

[0025] For example, like the eddy current type fluid mixer 51 according to the second embodiment shown in FIG. 3, the second end wall may be constituted by a diaphragm 17'. In the second embodiment, the diaphragm 17' is driven by a driving part (not shown) to approach and separate from the first end wall 15, so that the volume of the vortex chamber 25 can be increased or decreased to adjust the flow velocity of the fluid (main fluid) in the vortex chamber 25. The driving part can adopt various driving methods such as manual type, air-driven type, and electric type. By adjusting the flow velocity of the fluid (main fluid) in the vortex chamber 25, the swirling speed of the main fluid in the vortex chamber 25 and the outlet flow path 21 can be changed, and appropriate mixing with less concentration unevenness can be performed according to the type of the fluid to be mixed.

[0026] FIG. 4 shows an eddy current type fluid mixer 61 according to a third embodiment in which a flow rate adjustment valve 63 is provided on the additive flow path 23. In the eddy current type fluid mixer 61 according to the third embodiment, the flow rate adjustment valve 63 can change the flow rate of the additive fluid added from the additive flow path 23 to the outlet flow path 21, so that the mixing ratio of the main fluid and the additive fluid can be adjusted. However, as long as the flow rate of the additive fluid added from the additive flow path 23 to the outlet flow path 21 can be adjusted, the position where the flow rate adjustment valve 63 is provided is not limited to the additive flow path 23. For example, a flow rate adjustment valve 63 may be provided between the supply source of the additive fluid and the additive flow path 23. Also, instead of changing the flow rate of the additive fluid, the flow rate of the main fluid may be changed. For example, a flow rate adjustment valve (not shown) may be provided to adjust the flow rate of the main fluid supplied from the inlet flow path 19 into the vortex chamber 25. Similarly in this case, a flow rate adjustment valve may be provided on the inlet flow path 19, or a flow rate adjustment valve may be provided between the supply source of the main fluid and the inlet flow path 19.

[0027] In the case of the vortex-type fluid mixer 51 according to the second embodiment and the vortex-type fluid mixer 61 according to the third embodiment shown in FIGS. 3 and 4, the same reference numerals are given to the components common to the vortex-type fluid mixer 11 of the first embodiment shown in FIG. 1. Further, the components to which the same reference numerals are given have the same configuration. Therefore, the description of the components common to the vortex-type fluid mixer 11 of the first embodiment is omitted here.

Example

[0028] The analysis results by numerical simulation using a vortex-type fluid mixer having the same configuration as the vortex-type fluid mixer 11 of the first embodiment shown in FIG. 1 will be described below. In the following description, for the sake of easy understanding, the same reference numerals as those of the vortex-type fluid mixer 11 are given to each component of the vortex-type fluid mixer used in the numerical simulation.

[0029] The numerical simulation was performed using the vortex-type fluid mixer 11 having the configuration and dimensions as shown in FIGS. 5 and 6, unless otherwise specified. Specifically, the vortex chamber 25 has a cylindrical shape with a diameter of 20 mm and a height of 4 mm, and the inlet flow path 19 having a circular tube shape with a diameter of 4 mm is connected to the circumferential side wall 13 so that the central axis P1 of the inlet flow path passes through a position 8 mm away from the center of the vortex chamber 25. Further, the outlet flow path 21 having a circular tube shape with a diameter D and a length L1 is connected to the first end wall 15 so as to extend along the outlet flow path central axis P2 aligned on the same straight line as the vortex chamber central axis O. That is, the outlet flow path 21 extends from the first end wall 15 along the outlet flow path central axis P2 passing through the center of the first end wall 15 and perpendicular to the first end wall 15. Furthermore, the additive flow path 23 having a circular tube shape with a diameter of 4 mm extends along the additive flow path central axis P3 passing through the center of the outlet flow path 21 and perpendicular to the outlet flow path central axis P2 to a position 15 mm away from the outlet flow path central axis P2, and is connected to the outlet flow path 21 so that the distance from the upstream end of the outlet flow path 21 where the outlet flow path 21 and the first end wall 15 are connected to the additive flow path central axis P3 of the additive flow path 23 is L2. In the vortex-type fluid mixer 11 having such a configuration, clear water is supplied as the main fluid to the inlet flow path 19, and red water is supplied as the additive fluid to the additive flow path 23. The additive fluid is added from the additive flow path to the main fluid discharged from the inlet flow path 19, passing through the vortex chamber 25 and discharged from the outlet flow path 21 in a swirling flow state, to merge the two fluids. The passive scalar of the mixed fluid generated by the merging and mixing of the main fluid and the additive fluid is obtained at the downstream end of the outlet flow path 21. The passive scalar is a substitute index for the concentration regarding the color of the mixed fluid, assuming red as 1 (concentration of red water is 100%) and blue as 0 (concentration of red water is 0%).

[0030] First, the variation in the concentration of the mixed fluid (non-uniformity of the concentration distribution) due to the radial position at the downstream end of the outlet flow path 21 (the end located on the most downstream side opposite to the end connected to the volute chamber 25) was confirmed by numerical simulation. In the numerical simulation, a vortex-type fluid mixer 11 having the configuration and dimensions shown in FIGS. 5 and 6 was used, with the diameter D of the outlet flow path 21 being Φ4 mm, the length L1 of the outlet flow path 21 being 80 mm, and the distance L2 from the upstream end of the outlet flow path 21 to the central axis P3 of the addition flow path being 5 mm. Fresh water was supplied as the main fluid to the inlet flow path 19 at 800 mL / min, and red water was supplied as the addition fluid to the addition flow path 23 at 200 mL / min. The passive scalar of the mixed fluid obtained by adding and mixing the addition fluid to the main fluid was determined at the downstream end of the outlet flow path 21, and the mixing state of the fresh water and the red water was evaluated using the passive scalar as an index.

[0031] FIG. 7 is a graph showing the change over time of the passive scalar of the mixed fluid at the downstream end of the outlet flow path 21. In FIG. 7, the cross-section at the downstream end of the outlet flow path 21 is divided into a plurality of regions, and the passive scalar of the mixed fluid in each region is determined. The solid line shows the change over time of the maximum value of the passive scalar in each region thus determined, and the broken line shows the change over time of the minimum value. As shown in FIG. 7, at the downstream end of the outlet flow path 21, the maximum value and the minimum value of the passive scalar of the mixed fluid are almost the same, there is almost no difference in the passive scalar of the mixed fluid between regions at the downstream end of the outlet flow path 21, and there is almost no change over time. That is, it can be seen from FIG. 7 that there is almost no non-uniformity in the concentration distribution of the mixed fluid in the radial and flow directions at the downstream end of the outlet flow path 21, and the fluid is sufficiently mixed. Therefore, it was confirmed that by using the vortex-type fluid mixer 11, the variation in concentration (non-uniformity of the concentration distribution) due to the radial position and flow direction of different types of fluids is reduced, and the effect of concentration uniformity is obtained.

[0032] Next, the influence of the length L1 of the outlet flow path 21 on the variation in the concentration of the mixed fluid (non-uniformity of the concentration distribution) was confirmed by numerical simulation. In the numerical simulation, although having the configuration and dimensions shown in FIGS. 5 and 6, the distance L2 from the upstream end of the outlet flow path 21 to the central axis P3 of the addition flow path was set to 5 mm, the diameter D of the outlet flow path 21 was fixed at Φ4 mm, and the ratio of the length L1 of the outlet flow path 21 to the diameter D was changed in the range of 5 to 25. A vortex-type fluid mixer 11 was used, and the passive scalar of the mixed fluid was obtained at the downstream end of the outlet flow path 21. Further, for each vortex-type fluid mixer 11 having an outlet flow path 21 with a changed ratio of the length L1 to the diameter D, while maintaining the same mixing ratio to enable comparison, the above numerical simulation was performed under different combinations of the flow rates of the main fluid and the addition fluid, and the passive scalar of the mixed fluid was obtained at the downstream end of the outlet flow path 21.

[0033] FIG. 8 is a line graph showing the correlation between the ratio of the length L1 of the outlet channel 21 to the diameter D of the outlet channel 21 and the difference between the maximum value and the minimum value of the passive scalar of the mixed fluid at the downstream end of the outlet channel 21 for each combination of the flow rates of the main fluid and the additive fluid changed while maintaining the same mixing ratio. In FIG. 8, the ratio of the length L1 of the outlet channel 21 to the diameter D of the outlet channel 21 is taken as the horizontal axis, and the difference between the maximum value and the minimum value of the passive scalar of the mixed fluid obtained in each of a plurality of regions obtained by dividing the cross section at the downstream end of the outlet channel 21 is taken as the vertical axis, and the results of the numerical simulation are shown. In FIG. 8, the symbol "◆" indicates the case where the flow rate of the main fluid supplied to the inlet channel 19 is 0.2 L / min and the flow rate of the additive fluid supplied to the additive channel 23 is 0.05 L / min, the symbol "▲" indicates the case where the flow rate of the main fluid supplied to the inlet channel 19 is 0.4 L / min and the flow rate of the additive fluid supplied to the additive channel 23 is 0.1 L / min, the symbol "■" indicates the case where the flow rate of the main fluid supplied to the inlet channel 19 is 0.8 L / min and the flow rate of the additive fluid supplied to the additive channel 23 is 0.2 L / min, and the symbol "●" indicates the case where the flow rate of the main fluid supplied to the inlet channel 19 is 1.6 L / min and the flow rate of the additive fluid supplied to the additive channel 23 is 0.4 L / min, and shows the relationship between the ratio of the length L1 of the outlet channel 21 to the diameter D of the outlet channel 21 and the difference between the maximum value and the minimum value of the passive scalar of the mixed fluid at the downstream end of the outlet channel 21.

[0034] As can be seen from FIG. 8, the larger the ratio of the length L1 of the outlet flow path 21 to the diameter D of the outlet flow path 21, the smaller the difference between the maximum value and the minimum value of the passive scalar of the mixed fluid at the downstream end of the outlet flow path 21. The small difference between the maximum value and the minimum value of the passive scalar of the mixed fluid in each region of the cross section at the downstream end of the outlet flow path 21 means that the mixed fluid is uniformly mixed at the downstream end of the outlet flow path 21. Therefore, the larger the ratio of the length L1 of the outlet flow path 21 to the diameter D of the outlet flow path 21, the higher the effect of more uniformly mixing the mixed fluid. This is presumably because the longer the length L1 of the outlet flow path 21 and the higher the flow velocity of the main fluid flowing through the outlet flow path 21, the more the added fluid is dispersed into the main fluid by the action of the swirling flow. Considering the conditions and results of the numerical simulation shown in FIG. 7 and the conditions and results of the numerical simulation shown in FIG. 8, it can be said that the length L1 of the outlet flow path 21 is preferably 7.5 times or more the diameter D of the outlet flow path 21.

[0035] Furthermore, the influence of the position (confluence position) of the confluence part (connection part) between the outlet flow path 21 and the addition flow path 23 on the variation in the concentration of the mixed fluid (non-uniformity of the concentration distribution) was confirmed by numerical simulation. In the numerical simulation, for the case where the diameter D of the outlet flow path 21 is Φ4 mm, Φ6 mm, Φ8 mm, and Φ10 mm, having the configurations and dimensions shown in FIGS. 5 and 6, the length L1 of the outlet flow path 21 is set to 25 times the diameter D of the outlet flow path 21, that is, 25D, and the distance L2 from the upstream end of the outlet flow path 21 to the central axis P3 of the addition flow path is changed to 1 time, 2 times, 4 times, 8 times, and 12 times the diameter D of the outlet flow path 21, that is, D, 2D, 4D, 8D, and 12D. A vortex type fluid mixer 11 was used, and the passive scalar of the mixed fluid was obtained at the downstream end of the outlet flow path 21.

[0036] Figures 9 and 10 are line graphs showing the correlation between the difference between the maximum and minimum values of the passive scalar of the mixed fluid at the confluence position of the outlet channel 21 and the addition channel and at the downstream end of the outlet channel 21, obtained when the flow rate of the main fluid supplied to the inlet channel 19 is 0.2 L / min and the flow rate of the additive fluid supplied to the addition channel 23 is 0.05 L / min, and when the flow rate of the main fluid supplied to the inlet channel 19 is 1.6 L / min and the flow rate of the additive fluid supplied to the addition channel 23 is 0.4 L / min in numerical simulations, respectively. In order to enable comparison, in the numerical simulations for obtaining Figures 9 and 10, the ratio of the flow rates of the main fluid and the additive fluid is set to be the same so that the same mixing ratio is maintained. In Figures 9 and 10, the horizontal axis represents the confluence position by the ratio of "the distance L2 from the upstream end of the outlet channel 21 in the direction of the central axis P2 of the outlet channel 21 to the central axis P3 of the addition channel" to "the diameter D of the outlet channel 21", and the vertical axis represents the difference between the maximum and minimum values of the passive scalar of the mixed fluid obtained in each of a plurality of regions obtained by dividing the cross section at the downstream end of the outlet channel 21, showing the results of the numerical simulations. In Figures 9 and 10, the symbol "◆" indicates the case where the diameter D of the outlet channel 21 is Φ10 mm, the symbol "▲" indicates the case where the diameter D of the outlet channel 21 is Φ8 mm, the symbol "■" indicates the case where the diameter D of the outlet channel 21 is Φ6 mm, and the symbol "●" indicates the case where the diameter D of the outlet channel 21 is Φ4 mm, showing the correlation between the confluence position (the ratio of "the distance L2 from the upstream end of the outlet channel 21 in the direction of the central axis P2 of the outlet channel 21 to the central axis P3 of the addition channel" to "the diameter D of the outlet channel 21") and the difference between the maximum and minimum values of the passive scalar of the mixed fluid at the downstream end of the outlet channel 21.

[0037] From FIGS. 9 and 10, regardless of the flow rates of the main fluid and the additive fluid, it can be seen that the closer the confluence position of the outlet channel 21 and the additive channel 23 is to the upstream end of the outlet channel 21, that is, the closer it is to the vortex chamber 25, the smaller the difference between the maximum value and the minimum value of the passive scalar of the mixed fluid at the downstream end of the outlet channel 21 becomes. As described above, the small difference between the maximum value and the minimum value of the passive scalar of the mixed fluid in each region of the cross-section at the downstream end of the outlet channel 21 means that the mixed fluid is uniformly mixed at the downstream end of the outlet channel 21. Therefore, the closer the confluence position of the outlet channel 21 and the additive channel 23 is to the upstream end of the outlet channel 21, that is, the closer it is to the vortex chamber 25, the higher the effect of mixing the mixed fluid more uniformly is enhanced. This is presumably because the closer the confluence position of the outlet channel 21 and the additive channel 23 is to the upstream end of the outlet channel 21, the stronger the swirling flow generated in the vortex chamber 25 is maintained in the outlet channel 21, and a higher stirring effect can be obtained due to the swirling flow. Also, from the results shown in FIGS. 9 and 10, the confluence position of the outlet channel 21 and the additive channel 23 (the distance L2 from the upstream end of the outlet channel 21 to the center axis P3 of the additive channel in the direction of the center axis P2 of the outlet channel) is preferably close to the upstream end of the outlet channel 21. In particular, it can be said that it is preferably provided within a range of a distance within 8 times the diameter D of the outlet channel 21, and more preferably within a range of a distance within 4 times the diameter D of the outlet channel 21.

[0038] Furthermore, from the comparison between FIGS. 9 and 10, it can be seen that under the condition that the volume of the vortex chamber 25 is constant, the larger the flow rate of the main fluid is, the smaller the difference between the maximum value and the minimum value of the passive scalar of the mixed fluid at the downstream end of the outlet channel 21 can be suppressed even if the confluence position of the outlet channel 21 and the additive channel 23 is away from the upstream end of the outlet channel 21. Therefore, under the condition that the volume of the vortex chamber 25 is constant, the larger the flow rate of the main fluid is, the higher the effect of mixing the mixed fluid more uniformly is enhanced.

[0039] The above-described embodiments of the vortex fluid mixer 11, 51, 61 according to the present invention have been described with reference to the illustrated embodiments. However, the present invention is not limited to the illustrated embodiments. For example, in the illustrated embodiments, one additive channel 23 is connected to the outlet channel 21 so that two types of fluids merge. However, two or more additive channels 23 may be connected to the outlet channel 21 so that three or more types of fluids merge.

[0040] Also, as shown in FIG. 11, another vortex fluid mixer 71 may be provided downstream of the outlet channel 21. In this case, the vortex fluid mixer 71 includes a cylindrical peripheral side wall 73 extending along the central axis, a first end wall 75 and a second end wall 77 provided to face each other at both ends in the central axis direction of the peripheral side wall 73, and an outlet channel 79 opening in the first end wall 75. A space surrounded by the peripheral side wall 73, the first end wall 75, and the second end wall 77 constitutes a vortex chamber. The outlet channel 21 of the vortex fluid mixer 11 is connected to the peripheral side wall 73 so as to open into the vortex chamber of the vortex fluid mixer 71. Further, the outlet channel 21 is connected to the peripheral side wall 73 so that the outlet channel central axis P2 of the outlet channel 21 passes through an eccentric position away from the central axis of the vortex chamber of the vortex fluid mixer 71, and the outlet channel 79 is provided so that its central axis extends through a position away from the outlet channel central axis P2 of the outlet channel 21. When the outlet channel 21 of the vortex fluid mixer 11 is connected to the vortex fluid mixer 71 having such a configuration, the fluid flowing from the outlet channel 21 into the vortex chamber of the vortex fluid mixer 71 becomes a swirling flow in the vortex chamber of the vortex fluid mixer 71 to generate a vortex and is then discharged from the outlet channel 79. Therefore, the fluid flowing from the outlet channel 21 into the vortex chamber of the vortex fluid mixer 71 is stirred by the action of the vortex in the vortex chamber and is more uniformly mixed.

Description of Reference Numerals

[0041] 11 Vortex fluid mixer 13 Peripheral side wall 15 First end wall 17 Second end wall 17’ Diaphragm 19 Inlet channel 21 Outlet flow path 23 Added flow path 25 Vortex chamber 51 Vortex type fluid mixer 61 Vortex type fluid mixer 71 Vortex type fluid mixer 73 Peripheral side wall 75 First end wall 77 Second end wall 79 Outlet flow path

Claims

1. a vortex chamber defined by a generally cylindrical peripheral wall and a first end wall and a second end wall provided at both ends of the peripheral wall and opposed to each other; an inlet passage extending along a central axis of the inlet passage and opening at the peripheral side wall; an outlet passage extending along an outlet passage central axis and opening at the first end wall; At least one additive flow passage connected to a middle portion of the outlet flow passage for adding an additive fluid to the fluid flowing through the outlet flow passage; Equipped with a vortex type fluid mixer, characterized in that the second end wall is formed by a diaphragm, the outlet flow passage is provided such that a central axis of the outlet flow passage passes approximately through a center of the first end wall, the vortex chamber is configured such that a fluid flowing in via the inlet flow passage generates a vortex-like swirling flow within the vortex chamber and flows out of the outlet flow passage while generating a swirling flow, and an additive fluid added from the additive flow passage is agitated and mixed with the fluid in the outlet flow passage by the action of the swirling flow.

2. The vortex type fluid mixer according to claim 1 , wherein the addition passage is connected to the outlet passage in a region where a swirling flow is generated in the outlet passage.

3. 3. The vortex type fluid mixer according to claim 2, wherein the inlet flow passage is provided such that a central axis of the inlet flow passage passes through a position away from a central axis of a vortex chamber connecting a center of the first end wall and a center of the second end wall.

4. 4. The vortex type fluid mixer according to claim 3, wherein the inlet passage is provided such that fluid flows from the inlet passage in a tangential direction relative to the peripheral side wall.

5. 2. The vortex type fluid mixer according to claim 1, wherein the length of the outlet passage is 7.5 times or more the diameter of the outlet passage.

6. The vortex type fluid mixer according to claim 1, wherein the additive flow passage is provided such that a central axis of the additive flow passage is disposed at a distance within 8 times a diameter of the outlet flow passage from the upstream end of the outlet flow passage in a direction toward the central axis of the outlet flow passage.

7. The vortex type fluid mixer according to claim 6, wherein the additive flow passage is provided such that a central axis of the additive flow passage is disposed at a distance within four times a diameter of the outlet flow passage from the upstream end of the outlet flow passage in a direction toward the central axis of the outlet flow passage.

8. The vortex fluid mixer of claim 1 , wherein the diaphragm is moved toward and away from the first end wall by a driver.

9. A vortex chamber defined by a generally cylindrical peripheral wall and a first end wall and a second end wall provided at both ends of the peripheral wall and facing each other; an inlet passage extending along a central axis of the inlet passage and opening at the peripheral side wall; an outlet passage extending along an outlet passage central axis and opening at the first end wall; At least one additive flow passage connected to a middle portion of the outlet flow passage for adding an additive fluid to the fluid flowing through the outlet flow passage; a flow rate regulating valve for regulating a flow rate of an additive fluid added from the additive flow path to the outlet flow path; Equipped with the outlet flow passage is provided such that a central axis of the outlet flow passage passes approximately through a center of the first end wall, and the vortex chamber is configured such that a fluid flowing in through the inlet flow passage generates a vortex-like swirling flow within the vortex chamber and flows out of the outlet flow passage while generating a swirling flow, and an additive fluid added from the additive flow passage is agitated and mixed with the fluid in the outlet flow passage by the action of the swirling flow.

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