JP2017035679A - Dispersion system - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a dispersion system which can produce a sol having a high quality with a high efficiency.SOLUTION: In a dispersion system, by movement of a rotary vane in a blade chamber, plural fluid spaces S, which are partitioned by plural rotary vanes, a stator and an outer peripheral wall part, are rotationally moved so as to suck a fluid mixture into the fluid space from an introduction chamber via a through-hole, and when the fluid space S is connected to a discharge port 12b, the fluid mixture is discharged from the fluid space S to the discharge port 12b. A control part for controlling operation of a suction pump mechanism part sets number of rotation of the rotary vane so that a pressure of the fluid mixture in a discharge flow passage 12a when the fluid space S is connected to the discharge flow passage 12a is equal to or less than a saturation vapor pressure of a liquid phase dispersion medium, and rotates the rotary vane at said set number of rotation, and consequently, an area immediately after passing at least the discharge port 12b in the discharge flow passage 12a is formed as a fine bubble area in which many fine bubbles of the liquid phase dispersion medium are generated.SELECTED DRAWING: Figure 9

Description

  The present invention includes a centrifugal suction pump mechanism, a dispersion that generates a sol in which a mixed fluid of a dispersoid and a liquid dispersion medium is passed through the suction pump mechanism and the dispersoid is dispersed in the liquid dispersion medium. About the system.

A slurry (an example of a sol) in which a solid phase dispersoid (an example of a dispersoid) is dispersed in a liquid phase dispersion medium is an electrode or separator such as a lithium ion secondary battery or an electric double layer capacitor, paint, toner, and polishing. It is often used for applications such as chemicals. On the other hand, an emulsion (an example of a sol) in which a liquid phase dispersoid (an example of a dispersoid) is dispersed in a liquid phase dispersion medium is used for foods, sheet materials, emulsion fuels, and the like.
In such a sol, if the dispersion of the dispersoid in the liquid phase dispersion medium is insufficient, the performance may be deteriorated, particularly when used as a secondary battery electrode, the cycle characteristics are deteriorated. Leads to.
Incidentally, examples of the liquid phase dispersion medium include solvents such as water, and examples of the dispersoid include solid phase dispersoids such as powder and liquid phase dispersoids such as oil.
The powder is not particularly excluded as long as it is a powder. Examples thereof include chemical raw materials such as battery electrode materials, food raw materials such as skim milk powder and wheat flour, pharmaceutical raw materials, etc. Examples thereof include powders such as bodies and fine particles (including a mixture of these powders). The powder includes a granular material.

  Conventionally, as a dispersion system for generating a sol (dispersion liquid) in which a dispersoid is dispersed in a liquid phase dispersion medium, an introduction chamber to which a fluid is supplied, and a plurality of throttling through holes arranged around the outer periphery of the introduction chamber. A cylindrical stator arranged in a direction, an annular blade chamber communicating with a discharge portion formed on the outer peripheral side of the stator, and a rotary blade that can be driven to rotate in the blade chamber are arranged in the main body casing, and the rotary blade Is known to have a centrifugal suction pump mechanism that sucks fluid from the introduction chamber into the blade chamber through the throttle hole and discharges the fluid from the blade chamber to the discharge portion (for example, patents) References 1-4).

In this type of dispersion system, a mixed fluid of a liquid phase dispersion medium and a dispersoid is supplied to an introduction chamber, and a rotating blade is driven to rotate. On the other hand, the shear force and impact force of the rotor blade are applied, and the dispersoid aggregates (so-called lumps) contained in the mixed fluid are appropriately crushed, so that the dispersoid is appropriately dispersed in the liquid phase dispersion medium. It is supposed to be possible.
Also, in this type of dispersion system, a sudden pressure drop occurs at the back of the rotor blades that are driven to rotate at high speed in the blade chamber, so that the mixed fluid that exists near the back of the rotor blades passes through the throttle hole. Local boiling (cavitation) occurs, and the impact caused by the disappearance of the bubbles contained in the mixed fluid breaks up the dispersoid aggregates (dama) well, and disperses the dispersoid in the liquid phase dispersion medium. It can be promoted.

  In particular, in the dispersion system of Patent Document 4, a throttle portion is provided at the inlet portion of the introduction chamber, and a stator throttling hole is provided on the downstream side (outer peripheral side) of the introduction chamber, so that the rotational speed of the rotor blade is set appropriately. Thus, fine bubbles are generated by the vaporization of the liquid phase dispersion medium over the entire circumference of the blade chamber. Thereby, it is said that dispersion of the dispersoid can be further promoted.

JP 2007-216172 A JP 2006-281017 A International Publication No. 2010/140516 JP 2012-250145 A

  However, since the dispersion system for producing a sol by dispersing a dispersoid in a liquid phase dispersion medium is used in many applications as described above, it is possible to further improve the quality of the produced sol, and to improve the sol in the dispersion system. There is a continuing need to further increase the production efficiency of.

  This invention is made | formed in view of this situation, The objective is to provide the dispersion system which can produce | generate a high quality sol with high efficiency.

In order to achieve the above object, a distributed system according to the present invention includes:
Dispersion system comprising a centrifugal suction pump mechanism, passing a fluid mixture of a dispersoid and a liquid dispersion medium through the suction pump mechanism, and generating a sol in which the dispersoid is dispersed in the liquid dispersion medium And the characteristic composition is
The suction pump mechanism is
An introduction chamber to which the mixed fluid is supplied;
A cylindrical stator disposed outside the introduction chamber and having a plurality of through holes formed in the circumferential direction;
An annular blade chamber formed outside the stator;
A discharge port formed on an outer peripheral wall of the blade chamber and connected to a discharge flow path through which the mixed fluid is discharged;
A plurality of rotating blades that are driven to rotate and move inside the blade chamber;
A plurality of fluid spaces defined by the plurality of rotor blades, the stator, and the outer peripheral wall portion are rotated and moved by the movement of the rotor blades in the blade chamber, and the fluid is separated from the introduction chamber through the through holes. Aspirating the mixed fluid into a fluid space, and discharging the mixed fluid from the fluid space to the discharge port when the fluid space communicates with the discharge port;
The control unit that controls the operation of the suction pump mechanism unit is configured such that the pressure of the mixed fluid in the discharge channel when the fluid space communicates with the discharge channel is equal to or lower than the saturated vapor pressure of the liquid phase dispersion medium. The rotation speed of the rotary blade is set, and the rotary blade is rotated at the set rotation speed, and at least a region immediately after passing through the discharge port in the discharge flow path is a fine portion of the liquid phase dispersion medium. This is in that it is formed as a fine bubble region in which a large number of bubbles are generated.

  The inventors changed the viewpoint from the prior art and focused on a discharge flow path that was handled only as a mere outlet for the generated sol. Then, the present invention finds that the pressure of the mixed fluid is increased in the rotating fluid space, the flow velocity of the mixed fluid is increased when the fluid space is communicated with the discharge port, and the pressure of the mixed fluid is rapidly decreased. Completed.

  That is, according to the above characteristic configuration, the fluid space is rotated and moved to suck the mixed fluid, and the pressure inside the fluid space is increased by the suction force and the centrifugal force. Since the mixed fluid is discharged when the circulation space communicates with the discharge port, the mixed fluid flows into the discharge port at a high flow rate, and the pressure of the mixed fluid decreases. Here, the control unit sets the rotation speed of the rotor blade so that the pressure of the mixed fluid at that time is equal to or lower than the saturated vapor pressure of the liquid phase dispersion medium, and rotates the rotor blade at the rotation speed. At least a region immediately after passing through the discharge port is formed as a fine bubble region in which many fine bubbles of the liquid phase dispersion medium are generated. As a result, in the discharge flow path, the liquid phase dispersion medium that has permeated into the aggregate of the dispersoid foams, so that the crushing of the aggregate is promoted, and the dispersion of the dispersion medium in the liquid phase dispersion medium is good. A quality sol (dispersion) can be produced.

  This point will be described based on FIGS. 11 and 12. These drawings show a state in which the main casing is made of a transparent resin, water as a fluid is passed through the suction pump mechanism, and the discharge channel (12a) and the discharge port (12b) are observed. The number of rotations of the rotor blades was gradually increased, and the generation state of bubbles due to boiling under reduced pressure in the discharge channel was confirmed. At the rotation speed lower than that in the state of FIG. 11, no bubbles were observed, but at the rotation speed in FIG. 11, fine bubbles are generated in the region immediately after passing through the discharge port, and it looks like white mist. ing. In the state of FIG. 12 in which the number of rotations is further increased, the white wrinkles are dark and wide, more bubbles are generated, and the fine bubble region is enlarged. This is because the pressure of the mixed fluid when the fluid space (S) communicates with the discharge passage (12a) decreases as the rotational speed of the rotor blades increases, and the saturated vapor pressure of water (in the case of 25 ° C) Below 3.169 kPa), indicating that vacuum boiling has occurred. In this way, the inventors pay attention to mixing in the discharge flow path, which has not been considered in the past, and set the rotational speed of the rotor blade so that the pressure of the mixed fluid is equal to or lower than the saturated vapor pressure of the liquid phase dispersion medium. , By rotating the rotor blade at the number of rotations, it was found that the region immediately after passing through the discharge port in the discharge flow path is formed as a fine bubble region in which a large number of fine bubbles of the liquid phase dispersion medium are generated, The present invention has been completed.

  The further characteristic structure of the dispersion | distribution system which concerns on this invention exists in the point which the said discharge flow path extends along the tangential direction of the said outer peripheral wall part which is cylindrical.

  According to the above characteristic configuration, the discharge flow path extends along the tangential direction of the outer peripheral wall portion, which is the moving direction of the fluid space, so that the flow of the mixed fluid from the fluid space to the discharge flow path becomes smoother. Thereby, since the flow velocity of the mixed fluid increases, fine bubbles can be generated more efficiently, and the quality of the generated sol can be further improved.

  A further characteristic configuration of the dispersion system according to the present invention is that, in the circumferential connection portion where the discharge flow path and the blade chamber are connected, at least a downstream portion in the rotational direction of the rotor blade is chamfered. There is in point.

  If the downstream part of the circumferential connection part is not chamfered and is sharp, a sharp part exists in the region from the fluid space to the discharge flow path. If it does so, the streamline of the mixed fluid from fluid space to a discharge channel will be disturbed, and the flow velocity will fall. According to the above characteristic configuration, the chamfering is performed on the downstream portion of the circumferential connection portion, so that the disturbance of the streamline of the mixed fluid is suppressed, and the inflow of the mixed fluid from the fluid space to the discharge channel is further increased. Become smooth. Thereby, since the flow velocity of the mixed fluid increases, fine bubbles can be generated more efficiently, and the quality of the generated sol can be further improved.

  A further characteristic configuration of the distributed system according to the present invention is that the chamfering applied to the circumferential connection part is an R chamfering having a radius of 2 mm or more.

  According to the above characteristic configuration, by using an R chamfer with a radius of 2 mm or more, the flow of the mixed fluid from the fluid space to the discharge flow path becomes smoother, and fine bubbles can be generated more efficiently. The quality of the sol produced can be further improved.

  A further characteristic configuration of the dispersion system according to the present invention is that a chamfer is applied to an end of the rotary blade on the outer peripheral wall side.

  If the end on the outer peripheral wall portion side of the rotor blade is not chamfered and is sharp, a sharp point exists in a region from the fluid space to the discharge flow path. If it does so, the streamline of the mixed fluid from fluid space to a discharge channel will be disturbed, and the flow velocity will fall. According to the above characteristic configuration, the chamfering is applied to the end of the rotor blade on the outer peripheral wall side, so that the disturbance of the streamline of the mixed fluid is suppressed, and the inflow of the mixed fluid from the fluid space to the discharge channel is prevented. Even smoother. Thereby, since the flow velocity of the mixed fluid increases, fine bubbles can be generated more efficiently, and the quality of the generated sol can be further improved.

  A further characteristic configuration of the distributed system according to the present invention is that the chamfering applied to the rotor blade is an R chamfer having a radius of 2 mm or more.

  According to the above characteristic configuration, by using an R chamfer with a radius of 2 mm or more, the flow of the mixed fluid from the fluid space to the discharge flow path becomes smoother, and fine bubbles can be generated more efficiently. The quality of the sol produced can be further improved.

  A further characteristic configuration of the dispersion system according to the present invention is that an angle formed by the rotor blade with respect to a moving direction of the rotor blade is 10 ° or more and 80 ° or less.

  According to the above characteristic configuration, the rotor blades are provided to be inclined with respect to the rotation direction, and the angle formed with the moving direction of the rotor blades is 10 ° or more and 80 ° or less, so that the mixed fluid is sucked into the fluid space. The flow of the mixed fluid from the fluid space to the discharge channel can be smoothly performed while securing the force. Therefore, fine bubbles can be generated more efficiently, and the quality of the generated sol can be further improved.

  A further characteristic configuration of the dispersion system according to the present invention is that an angle formed by the rotor blade with respect to a moving direction of the rotor blade is greater than 0 ° and not greater than 31 °.

  The inventors conducted an experiment to investigate the optimum value of the angle of the rotor blade, and found that the angle formed by the rotor blade with respect to the moving direction of the rotor blade is preferably greater than 0 ° and less than or equal to 31 °. Within this angle range, the pressure of the mixed fluid in the space from the introduction chamber to the fluid space is lowered to facilitate the occurrence of reduced-pressure boiling, and the decrease in the suction / discharge capability of the suction pump mechanism can be suppressed. This is preferable.

  In a further characteristic configuration of the dispersion system according to the present invention, the introduction chamber is formed between a front wall portion fixed to the suction pump mechanism portion and a rotor that is rotationally driven by a motor. And the front wall has a first facing surface that is a smooth flat surface that is orthogonal to the rotation axis of the rotor and faces the rotor. It has the point which has a 2nd opposing surface which is a smooth plane which is orthogonal to the rotating shaft of a rotor, and opposes the said 1st opposing surface.

  According to the above characteristic configuration, the introduction chamber is formed between the front wall portion and the rotor and is sandwiched between the first opposed surface and the second opposed surface which are smooth planes. The flow of the mixed fluid in the chamber becomes smoother. Thereby, since the flow velocity of the mixed fluid increases, fine bubbles can be generated more efficiently, and the quality of the generated sol can be further improved.

Schematic configuration diagram of a dispersion system equipped with a centrifugal suction pump mechanism Longitudinal sectional view showing the main part of the fixed-quantity supply device Sectional view in III-III direction view of FIG. Longitudinal side view of centrifugal suction pump mechanism Sectional view in the VV direction view of FIG. The exploded perspective view which shows the assembly structure of the front wall part of a main body casing, a stator, a partition plate, and a rotor Schematic diagram of partition plate A photograph of the blade chamber in which the rotor blades rotate observed from the front side of the main casing A photograph of the blade chamber in which the rotor blades rotate observed from the front side of the main casing Sectional drawing of the suction pump mechanism part concerning 2nd Embodiment from the same viewpoint as FIG. A photograph of the blade chamber in which the rotor blades rotate observed from the front side of the main casing A photograph of the blade chamber in which the rotor blades rotate observed from the front side of the main casing Simulation results of flow velocity of mixed fluid Simulation results of flow velocity of mixed fluid Longitudinal side view of centrifugal suction pump mechanism Simulation results of mixed fluid pressure

<First Embodiment>
Hereinafter, the distributed system according to the first embodiment will be described with reference to the drawings.
FIG. 1 shows a dispersion system 100 having a centrifugal suction pump mechanism Y according to the present invention.
This dispersion system 100 uses a powder P as a dispersoid, a solvent R as a liquid phase dispersion medium, and dissolves the powder P in the solvent R to generate a slurry F as a sol.
In the present embodiment, for example, CMC (carboxyl methylcellulose) is used as the powder P (solid phase dispersoid), and water is used as the solvent R (liquid phase dispersion medium).

  As shown in FIG. 1, the dispersion system 100 includes a quantitative supply device X that supplies powder P in a fixed amount, a solvent supply unit 50 that supplies solvent R in a fixed amount, and a powder P that is supplied in a fixed amount from the quantitative supply device X. A suction pump mechanism Y that sucks and mixes the solvent R that is quantitatively supplied from the solvent supply unit 50 by negative pressure, and a powder P that is not completely dissolved from the slurry F discharged from the suction pump mechanism Y. And a recirculation mechanism 70 that circulates and supplies the solvent R (hereinafter, undissolved slurry Fr) to the suction pump mechanism Y.

[Quantitative supply device]
As shown in FIG. 1, the quantitative supply device X includes a hopper 31 that discharges the powder P received from the upper opening 31a from the lower opening 31b, an agitation mechanism 32 that agitates the powder P in the hopper 31, With the upper opening 31a of the hopper 31 open to the atmosphere, the lower opening is caused by the negative pressure suction force acting on the lower opening 31b by the suction of the suction pump mechanism Y connected to the downstream side of the lower opening 31b. A positive displacement quantitative supply unit 40 that supplies the powder P discharged from 31b to the suction pump mechanism Y is provided.

  The hopper 31 is formed in an inverted conical shape that is reduced in diameter as it goes from the upper part to the lower part, and its central axis A1 is arranged in a posture along the vertical direction. The cross-sectional shape of each of the upper opening 31a and the lower opening 31b of the hopper 31 is a circular shape centered on the central axis A1 when viewed in the vertical direction in FIG. The inclination angle of the wall surface is approximately 60 degrees with respect to the horizontal plane.

  The stirring mechanism 32 is disposed in the hopper 31 and has a stirring blade 32A that stirs the powder P in the hopper 31, a blade driving motor M1 that rotates the stirring blade 32A around the central axis A1 of the hopper 31, An attachment member 32B that supports the blade drive motor M1 positioned above the upper opening 31a of the hopper 31 and a transmission member 32C that transmits the rotational driving force of the blade drive motor M1 to the stirring blade 32A are configured. .

  The stirring blade 32A is configured by bending a rod-like member into a substantially V-shape, with one side portion thereof being along the inner wall surface of the hopper 31, and the other side portion being at the center axis A1 of the hopper 31. It is coaxially and rotatably supported. Further, the stirring blade 32A has a triangular cross-sectional shape, and is disposed so that a surface forming one side of the triangle is substantially parallel to the inner wall surface of the hopper 31. Accordingly, the stirring blade 32A is disposed so as to be rotatable around the central axis A1 along the inner wall surface of the hopper 31.

As shown in FIGS. 1 to 3, the positive displacement quantitative supply unit 40 is a mechanism for supplying a predetermined amount of powder P supplied from the lower opening 31 b of the hopper 31 to the suction pump mechanism Y on the downstream side. It is.
Specifically, the introduction part 41 connected to the lower opening part 31 b of the hopper 31, the casing 43 provided with the supply port 43 a and the discharge port 43 b, and the measuring rotator 44 rotatably disposed in the casing 43. And a metering rotator drive motor M2 that rotationally drives the metering rotator 44.

  The introduction part 41 is formed in a cylindrical shape that communicates the lower opening 31b of the hopper 31 and the supply port 43a formed in the upper part of the casing 43, and has a slit having the same shape as the supply port 43a of the casing 43 at the lowermost end. A shaped opening is formed. The introduction portion 41 is formed in a tapered shape that becomes thinner toward the supply port 43 a side of the casing 43. The shape of the slit-shaped opening can be appropriately set according to the size of the hopper 31, the supply amount of the powder P, the characteristics of the powder P, and the like. The dimension is set to about 20 to 100 mm, and the dimension in the width direction is set to about 1 to 5 mm.

The casing 43 is formed in a substantially rectangular parallelepiped shape, and is connected to the hopper 31 via the introduction portion 41 in a posture inclined by 45 degrees with respect to the horizontal direction (left-right direction in FIG. 1).
As shown in FIGS. 2 and 3, the upper surface of the casing 43 is provided with a slit-shaped supply port 43 a corresponding to the slit-shaped opening of the introduction portion 41, and the powder P from the lower opening 31 b of the hopper 31 is provided. Can be supplied into the casing 43. At the lower part of the lower side surface (right side surface in FIG. 2) of the casing 43 arranged in an inclined manner, the powder P, which is quantitatively supplied by the metering rotator 44, is supplied to the downstream suction pump via the expansion chamber 47. A discharge port 43b for discharging to the mechanism part Y is provided, and a powder discharge pipe 45 is connected to the discharge port 43b. The expansion chamber 47 is provided at a position in the casing 43 to which the powder P supplied from the supply port 43a to the powder storage chamber 44b of the measuring rotator 44 is supplied in a fixed amount, and is operated by the negative pressure acting from the discharge port 43b. The force is maintained at a lower pressure than the supply port 43a (for example, about −0, 06 MPa). That is, the discharge port 43b is connected to the primary side of the suction pump mechanism Y so that the negative pressure suction force acts on the expansion chamber 47 and is maintained at a lower pressure than the supply port 43b. As the measurement rotating body 44 rotates, the state of each powder storage chamber 44b is changed to a negative pressure state (for example, about −0, 06 MPa) and a higher pressure state than the negative pressure state. .

  The measuring rotator 44 has a disk member 49 disposed on the drive shaft 48 of the measuring rotator driving motor M <b> 2, and a plurality of (e.g., eight) plate-shaped partition walls 44 a radially excluding the central portion of the disk member 49. A plurality of powder storage chambers 44b (for example, eight chambers) are formed at equal intervals in the circumferential direction. The powder storage chamber 44 b is configured to open at the outer peripheral surface and the center portion of the measuring rotary body 44. An opening closing member 42 is unevenly distributed in the central direction of the measuring rotating body 44 and is fixedly arranged. The opening on the center side of each powder storage chamber 44b is closed or opened according to the rotation phase. It is configured to be possible. The supply amount of the powder P can be adjusted by changing the number of rotations of the measuring rotator 44 by the measuring rotator driving motor M2 that rotationally drives the measuring rotator 44.

  With the rotation of the measuring rotator 44, each powder storage chamber 44b is opened to the expansion chamber 47, opened to the expansion chamber 47, the first sealed state not communicating with the expansion chamber 47 and the supply port 43a, and opened to the supply port 43a. The supply port is opened and the supply port 43a and the expansion chamber 47 are communicated with each other in the order of the second sealed state. The casing 43 is formed such that the opening on the outer peripheral surface side of the measuring rotator 44 is closed in the first sealed state and the second sealed state, and the opening on the center side of the measuring rotator 44 is the first sealed. The opening closing member 42 is fixedly disposed on the casing 43 so as to be closed in the state, the supply port open state, and the second sealed state.

  Therefore, in the quantitative supply device X, the powder P stored in the hopper 31 is supplied to the quantitative supply unit 40 while being stirred by the stirring blade 32A, and the powder P is discharged from the discharge port 43b by the quantitative supply unit 40. A fixed amount is supplied to the suction pump mechanism Y through the body discharge pipe 45.

  More specifically, the pressure of the expansion chamber 47 in the casing 43 is in a negative pressure state (for example, for example, due to the negative pressure suction force from the suction pump mechanism Y connected to the downstream side of the discharge port 43b of the constant supply unit 40) −0, about 06 MPa). On the other hand, since the upper opening 31a of the hopper 31 is open to the atmosphere, the inside of the hopper 31 is in a state of about atmospheric pressure. The inside of the introduction part 41 and the vicinity of the lower opening 31b communicating with each other through the gap between the expansion chamber 47 and the metering rotator 44 are in a pressure state between the negative pressure state and the atmospheric pressure state.

  In this state, the powder P in the vicinity of the inner wall surface of the hopper 31 and the lower opening 31b is stirred by the stirring blade 32A of the stirring mechanism 32, whereby the powder P in the hopper 31 is sheared by the stirring blade 32A. On the other hand, the metering rotator 44 is rotated by the metering rotator drive motor M2, so that the empty powder storage chambers 44b are in continuous communication with the supply port 43a. Then, the powder P in the hopper 31 flows down through the introduction portion 41 from the lower opening 31b and is stored in a predetermined amount in the powder storage chamber 44b of the measuring rotary body 44 that is in communication with the supply port 43a one after another. The powder P stored in the powder storage chamber 44b flows down to the expansion chamber 47 and is discharged from the discharge port 43b. Therefore, the fixed amount supply device X can continuously supply the powder P to the supply port 11 of the suction pump mechanism Y continuously by a predetermined amount through the powder discharge pipe 45.

  As shown in FIG. 1, the powder discharge pipe 45 is provided with a shutter valve 46 that can stop the supply of the powder P to the supply port 11 of the suction pump mechanism Y.

(Solvent supply unit)
As shown in FIG. 1, the solvent supply unit 50 is configured to continuously supply the solvent R from the solvent source 51 to the supply port 11 of the suction pump mechanism unit Y at a set flow rate.
Specifically, the solvent supply unit 50 includes a solvent source 51 that sends the solvent R, a solvent supply pipe 52 that sends the solvent R from the solvent source 51, and a solvent that is sent from the solvent source 51 to the solvent supply pipe 52. A flow rate adjustment valve (not shown) that adjusts the flow rate of R to a set flow rate, and the solvent R adjusted to the set flow rate are mixed with powder P that is quantitatively supplied from the quantitative supply unit 40 and supplied to the supply port 11. And a mixing mechanism 60.

As shown in FIG. 4, the mixing mechanism 60 includes a mixing member 61 that connects the powder discharge pipe 45 and the solvent supply pipe 52 to the supply port 11.
The mixing member 61 is configured to have a smaller diameter than the cylindrical supply port 11, and a cylindrical portion 62 disposed in an inserted state in the supply port 11 so as to form an annular slit 63 between the mixing member 61 and the supply port 11. And the annular flow path forming part 65 which forms the annular flow path 64 in the outer peripheral part of the supply port 11 in a state communicating with the annular slit 63 over the entire circumference is provided.
The powder discharge pipe 45 is connected to the mixing member 61 in a state of communicating with the cylindrical portion 62, and the solvent supply pipe 52 is connected to supply the solvent R to the annular flow path 64 in the tangential direction. The
The powder discharge pipe 45, the cylindrical portion 62 of the mixing member 61, and the supply port 11 are inclined such that the supply direction of the axis A2 is downward (the angle with respect to the horizontal plane (left and right direction in FIG. 1) is about 45 degrees). It is arranged so as to be inclined.

That is, the powder P discharged from the discharge port 43b of the fixed amount supply unit 40 to the powder discharge tube 45 is introduced into the supply port 11 along the axis A2 through the cylindrical portion 62 of the mixing member 61. On the other hand, since the solvent R is supplied to the annular flow path 64 from the tangential direction, the solvent R is in a state of a hollow cylindrical vortex without a break through the annular slit 63 formed on the inner peripheral side of the annular flow path 64. It is supplied to the supply port 11.
Accordingly, the powder P and the solvent R are uniformly premixed by the cylindrical supply port 11 and the premixed mixture Fp is sucked into the supply chamber 13 of the suction pump mechanism Y.

[Suction pump mechanism]
The suction pump mechanism Y will be described based on FIGS. 1 and 4 to 7.
As shown in FIG. 4, the suction pump mechanism Y includes a main casing 1 having a cylindrical outer peripheral wall 4 whose both ends are closed by a front wall 2 and a rear wall 3. 1 is a concentric rotor 5 that is concentrically provided within the main body casing 1, a cylindrical stator 7 that is concentrically fixed to the front wall 2 inside the main body casing 1, and the rotor 5. And a pump drive motor M3 and the like.

As shown also in FIG. 5, on the radially outer side of the rotor 5, a plurality of rotary blades 6 protrude to the front side (left side in FIG. 4) that is the front wall portion 2 side and are equally spaced in the circumferential direction. Are provided integrally with the rotor 5.
The cylindrical stator 7 is provided with a plurality of through holes 7a and 7b arranged in the circumferential direction, and the stator 7 is on the front side of the rotor 5 (left side in FIG. 4) and on the inner side in the radial direction of the rotor blades 6. An annular blade chamber 8 around which the rotor blade 6 circulates is formed between the stator 7 and the outer peripheral wall portion 4 of the main body casing 1.

As shown in FIGS. 4 to 6, the supply port 11 for sucking and introducing the premixed mixture Fp, in which the powder P and the solvent R are premixed by the mixing mechanism 60, into the inside of the main casing 1 by the rotation of the rotor blades 6. The center wall of the front wall 2 (the axis A3 of the main body casing 1) is shifted to the outer peripheral side.
As shown in FIGS. 4 and 6, an annular groove 10 is formed on the inner surface of the front wall portion 2 of the casing 1, and a supply port 11 is provided in communication with the annular groove 10.
As shown in FIGS. 4 and 5, the cylindrical discharge portion 12 that discharges the slurry F generated by mixing the powder P and the solvent R is a peripheral portion of the cylindrical outer peripheral wall portion 4 of the main body casing 1. It extends in the tangential direction of the outer peripheral wall 4 at one location in the direction. A discharge flow path 12a that is a flow path of the slurry F inside the discharge section 12 and the blade chamber 8 communicate with each other at the discharge port 12b. The discharge flow path 12 a is provided so as to extend in the tangential direction of the outer peripheral wall portion 4. The discharge port 12 b is an elliptical opening provided in the outer peripheral wall portion 4. A circumferential connection part C, which is a part around the discharge port 12b and is connected to the discharge flow path 12a and the blade chamber 8, has an upstream part C1 and a downstream part C2. The upstream portion C1 is a front portion of the circumferential connection portion C with respect to the rotation direction of the rotor blade 6 described later. The downstream portion C2 is a rear portion of the circumferential connection portion C with respect to the rotation direction of the rotor blade 6 described later. The downstream portion C2 is rounded with a chamfer. The radius of the R chamfer is preferably 2 mm or more.

As shown in FIGS. 1 and 4, in this embodiment, the slurry F discharged from the discharge unit 12 is supplied to the recirculation mechanism unit 70 through the discharge path 18 and is supplied to the separation unit 71 of the recirculation mechanism unit 70. The inlet 17 for supplying the undissolved slurry Fr from which bubbles have been separated into the main body casing 1 through the circulation path 16 circulates at the center of the front wall 2 of the main body casing 1 (concentric with the axis A3). Is provided.
4 to 6, a partition plate 15 that divides the inner peripheral side of the stator 7 into a supply chamber 13 on the front wall 2 side and an introduction chamber 14 on the rotor 5 side is provided on the front side of the rotor 5. And a scraping blade 9 on the front wall 2 side of the partition plate 15.
A plurality of scraping blades 9 are concentrically provided at equal intervals in the circumferential direction (four in FIG. 6), and each of the scraping blades 9 enters the annular groove 10 in the state where each of the scraping blades 9 enters the annular groove 10. And are arranged so as to be able to circulate integrally.

The supply chamber 13 and the introduction chamber 14 are configured to communicate with the blade chamber 8 through a plurality of through holes 7 a and 7 b of the stator 7, the supply port 11 communicates with the supply chamber 13, and the introduction port 17 is introduced. It is configured to communicate with the chamber 14.
Specifically, the supply chamber 13 and the blade chamber 8 are communicated with each other through a plurality of supply chamber side through-holes 7a arranged at equal intervals in the circumferential direction at a portion facing the supply chamber 13 in the stator 7, and the introduction chamber. 14 and the blade chamber 8 are communicated with each other through a plurality of introduction chamber side through-holes 7b disposed at equal intervals in the circumferential direction at a portion facing the introduction chamber 14 in the stator 7.

A description will be given of each part of the suction pump mechanism Y.
As shown in FIG. 4, the rotor 5 is configured to have a shape in which the front surface bulges substantially in a truncated cone shape, and is arranged on the outer peripheral side at equal intervals with a plurality of rotating blades 6 protruding forward. Is provided. In FIG. 5, ten rotating blades 6 are arranged at equal intervals in the circumferential direction. Further, the rotor blade 6 is formed so as to project from the outer peripheral side of the rotor 5 to the inner peripheral side so as to incline backward in the rotation direction from the inner peripheral side toward the outer peripheral side. The angle formed by the rotor blade 6 and the moving direction (rotation direction) of the rotor blade 6 is preferably 10 ° or more and 80 ° or less. In the present embodiment, the angle is 30 ° (see FIG. 5). The inner diameter of the tip of the rotor blade 6 is formed to be slightly larger than the outer diameter of the stator 7. A chamfer is applied to the end 6 b of the rotor blade 6 on the outer peripheral wall 4 side. Specifically, an R chamfer is applied to the rear portion of the end portion 6b in the rotational direction of the rotary blade 6. The radius of the R chamfer is preferably 2 mm or more.
The rotor 5 is connected to a drive shaft 19 of a pump drive motor M3 that passes through the rear wall portion 3 and is inserted into the main body casing 1 in a state of being concentric with the main body casing 1 in the main body casing 1. The pump drive motor M3 is rotationally driven.
The rotor 5 is rotationally driven in a direction in which the tip end portion of the rotor blade 6 becomes the front side when viewed in the axial direction (viewed in the direction VV in FIG. 4 as shown in FIG. 5). A so-called local boiling (cavitation) is generated on the rear surface (back surface) 6a in the rotational direction.

As shown in FIGS. 4, 6, and 7, the partition plate 15 is configured in a generally funnel shape having an outer diameter that is slightly smaller than the inner diameter of the stator 7. Specifically, the funnel-shaped partition plate 15 includes a funnel-shaped portion 15b opened at a central sliding portion of a cylindrical sliding contact portion 15a protruding in a cylindrical shape, and the funnel-shaped portion 15b. The outer peripheral portion of the main body casing 1 is configured to have an annular flat plate portion 15c that is in a state orthogonal to the axis A3 of the main body casing 1.
As shown in FIGS. 4 and 5, the partition plate 15 has a plurality of cylindrical plates 15 which are spaced at equal intervals in the circumferential direction with the top cylindrical sliding contact portion 15 a facing the front wall 2 side of the main casing 1. It is attached to the attachment portion 5a on the front surface of the rotor 5 via the spacing members 20 arranged at the places (four places in this embodiment).

  As shown in FIG. 5 and FIG. 7C, when the partition plate 15 is attached to the rotor 5 via the spacing member 20 at each of a plurality of locations, the stirring blade 21 is provided on the rear wall 3 side of the main casing 1. When the rotor 5 is rotationally driven, the four stirring blades 21 are configured to rotate integrally with the rotor 5.

  As shown in FIGS. 4 and 6, in this embodiment, the cylindrical introduction port 17 is concentric with the main body casing 1 and is provided at the center of the front wall portion 2 of the main body casing 1. The introduction port 17 is formed with a narrowed portion 14a that is smaller in diameter than the inner diameter of the circulation path 16 and smaller in diameter than the cylindrical sliding contact portion 15a of the partition plate 15 and has a small flow path area. By rotating the rotor blade 6 of the rotor 5, the slurry F is discharged through the discharge unit 12, and the undissolved slurry Fr is introduced through the throttle unit 14 a of the introduction port 17. The portion Y is depressurized.

  As shown in FIGS. 4 to 6, the supply port 11 is configured so that the opening (inlet portion) that opens into the main body casing 1 includes a part of the annular groove 10 in the circumferential direction inside. It is provided in the front wall part 2 so that it may be located in the side of the opening part of the inlet 17 with respect to the inside. Further, the supply port 11 is viewed in a horizontal direction in which the axis A2 is parallel to the axis A3 of the main casing 1 and is orthogonal to the axis A3 of the casing 1 in a plan view (viewed in the vertical direction in FIGS. 1 and 4). 1 and 4, the front wall of the main body casing 1 is in a downward inclined posture that approaches the axis A3 of the main body casing 1 as the axial center A2 approaches the front wall portion 2 of the main body casing 1. Part 2 is provided. Incidentally, the downward inclination angle of the supply port 11 with respect to the horizontal direction (left-right direction in FIGS. 1 and 4) is about 45 degrees as described above.

  As shown in FIGS. 4 and 6, the stator 7 is attached to the inner surface (the surface facing the rotor 5) of the front wall portion 2 of the main body casing 1, and the front wall portion 2 of the main body casing 1 and the stator 7 are connected. It is fixed so as to be integrated. In the stator 7, the plurality of supply chamber side through-holes 7 a disposed in the portion facing the supply chamber 13 are formed in a substantially circular shape, and the plurality of supply chamber side through-holes 7 a are larger than the flow passage area of the supply chamber 13. The total flow passage area is set to be small, and the plurality of introduction chamber side through holes 7b disposed in the portion facing the introduction chamber 14 are formed in a substantially elliptical shape, and the flow passage of the introduction chamber 14 is formed. The total flow passage area of the plurality of supply chamber side through holes 7b is set to be smaller than the area. As the rotor blades 6 of the rotor 5 rotate, the slurry F is discharged through the discharge unit 12, the preliminary mixture Fp is supplied through the supply chamber side through hole 7 a of the supply chamber 13, Since the undissolved slurry Fr is introduced through the suction pump mechanism Y, the pressure in the suction pump mechanism Y is reduced.

  As shown in FIGS. 6 and 7, in this embodiment, each scraping blade 9 is formed in a rod shape, and the rod-like scraping blade 9 is viewed in the radial direction of the rotor 5 (viewed from the front and back in FIG. 7B). The tip side of the ejector blade 9 is located closer to the front wall 2 side, and the tip side of the rod-shaped scraping blade 9 is closer to the front side of the rotor 5 as viewed in the axial direction of the rotor 5 (viewed from the front and back in FIG. 7A). The base end portion 9B of the rod-shaped scraping blade 9 is fixed so as to rotate integrally with the rotor 5 in an inclined posture located on the radially inner side of the rotor 5, and the rotor 5 is viewed in the axial direction (see FIG. 7 (a), the tip of the scraping blade 9 is rotationally driven in a direction (the direction indicated by an arrow in FIGS. 4 to 7).

Based on FIGS. 5 to 7, the raking blade 9 will be described.
The scraping blade 9 includes a base end portion 9B fixed to the partition plate 15, an intermediate portion 9M that is exposed to the supply chamber 13, and a tip end portion 9T that is fitted in (that is, enters) the annular groove 10. It is configured in a rod shape provided in a series from the proximal end to the distal end.

As shown in FIGS. 5, 6, and 7 (b), the base end portion 9 </ b> B of the scraping blade 9 is generally formed in a rectangular plate shape.
As shown in FIGS. 5, 6, 7 (a) and 7 (b), the intermediate portion 9 </ b> M of the scraping blade 9 is configured in a substantially triangular prism shape with a substantially triangular cross-sectional shape (particularly, (See FIG. 5). Then, by providing the scraping blade 9 in the inclined posture as described above, one side surface 9m (hereinafter referred to as a radiating surface) facing the front side in the rotational direction of the rotor 5 among the three side surfaces of the triangular columnar intermediate portion 9M. Is downwardly inclined toward the front side in the rotational direction of the rotor 5 and is directed radially outward with respect to the radial direction of the rotor 5 (hereinafter sometimes referred to as diagonally outward). (See FIG. 6 and FIG. 7 in particular).

  That is, by providing the bar-like scraping blade 9 in the inclined posture as described above, the intermediate portion 9M exposed to the supply chamber 13 of the scraping blade 9 is more than the tip portion 9T in which the annular groove 10 is fitted. Further, the radiating surface 9m facing the front side in the rotational direction of the intermediate portion 9M is in a front-falling shape inclined toward the front side in the rotational direction of the rotor 5, and in the radial direction of the rotor 5. It is inclined diagonally outward. Thereby, the preliminary mixture Fp scraped from the annular groove 10 by the tip portion 9T of the scraping blade 9 is radially outside the rotor 5 in the supply chamber 13 by the diffusion surface 9m of the intermediate portion 9M of the scraping blade 9. Guided to flow toward the other side.

As shown in FIGS. 6, 7 (a) and 7 (b), the tip end portion 9 </ b> T of the scraping blade 9 has a substantially quadrangular prism shape with a substantially rectangular cross-sectional shape, and the axial view of the rotor 5 ( 7A, the outward side surface 9o facing the radially outward side of the rotor 5 among the four side surfaces is an inwardly facing inner surface facing the radially inward side of the inner surface of the annular groove 10. The inward side surface 9i is configured in an arc shape along the outward inner surface facing the radially outer side of the inner surface of the annular groove 10 on the radially inner side of the rotor 5 among the four side surfaces. .
Of the four side surfaces of the quadrangular columnar tip portion 9T, the scraped surface 9f facing the front side in the rotational direction of the rotor 5 is in a front-falling shape inclined toward the front side in the rotational direction of the rotor 5, and the diameter of the rotor 5 It is configured to face radially outward with respect to the direction (hereinafter sometimes referred to as diagonally outward).
Thereby, the preliminary mixture Fp scraped from the annular groove 10 by the tip portion 9T of the scraping blade 9 is directed radially outward of the rotor 5 by the scraping surface 9f of the tip portion 9T of the scraping blade 9. It will be discharged into the supply chamber 13.
Furthermore, the tip surface 9t of the tip portion 9T of the scraping blade 9 is configured to be parallel to the bottom surface of the annular groove 10 in a state where the tip portion 9T is fitted in the annular groove 10.

  Further, when the rotor 5 is rotationally driven in a direction in which the tip of the scraping blade 9 is the front side when viewed from the axial direction (viewed from the front and back of the paper in FIG. 7A), the base end portion of the scraping blade 9 A surface (back surface) 9a which is the rear side in the rotation direction is formed on each of 9B, the intermediate portion 9M, and the tip portion 9T. The rear surface 9a is configured such that so-called local boiling (cavitation) occurs when the scraping blade 9 rotates.

  The four scraped wings 9 configured in the above-described shape are arranged in the circumferential direction at intervals of 90 degrees at the central angle in the inclined posture as described above, and the base end portions 9B are respectively arranged. It is fixed to the annular flat plate portion 15 c of the partition plate 15.

As shown in FIG. 4, the partition plate 15 provided with the scraping blades 9 is attached to the attachment portion 5 a on the front surface of the rotor 5 in a state of being separated from the front surface of the rotor 5 by the interval holding member 20. 5 is disposed in the main body casing 1 in a state where the cylindrical sliding contact portion 15a of the partition plate 15 is fitted in the introduction port 17 so as to be slidable and rotatable.
Then, a tapered introduction chamber 14 having a smaller diameter toward the front wall 2 side of the main casing 1 is formed between the bulging front surface of the rotor 5 and the rear surface of the partition plate 15, and the introduction port 17 serves as the partition plate. It is configured to communicate with the introduction chamber 14 via 15 cylindrical sliding contact portions 15a.
An annular supply chamber 13 communicating with the supply port 11 is formed between the front wall portion 2 of the main casing 1 and the front surface of the partition plate 15.

  When the rotor 5 is rotationally driven, the partition plate 15 rotates integrally with the rotor 5 in a state where the cylindrical sliding contact portion 15a is in sliding contact with the introduction port 17, and the rotor 5 and the partition plate 15 are Even in a rotating state, the state where the introduction port 17 communicates with the introduction chamber 14 via the cylindrical sliding contact portion 15a of the partition plate 15 is maintained.

[Recirculation mechanism]
The recirculation mechanism part (an example of a separation part) 70 is configured to separate the lysate by specific gravity in the cylindrical container 71, and as shown in FIG. 1, the discharge path from the discharge part 12 of the suction pump mechanism part Y The undissolved slurry Fr that may contain the powder P that is not completely dissolved is supplied to the circulation path 16 from the slurry F that is supplied through the slurry F. It is comprised so that it may isolate | separate into the discharge path 22, respectively. The discharge path 18 and the circulation path 16 are each connected to the lower part of the cylindrical container 71, and the discharge path 22 is connected to the upper part of the cylindrical container 71 and the supply destination 80 of the slurry F.
Here, although not shown, the recirculation mechanism unit 70 is provided with an introduction pipe to which the discharge path 18 is connected protruding from the bottom surface of the cylindrical container 71, and is connected to the discharge path 22 at the upper part of the cylindrical container 71. A twisting plate for turning the flow of the slurry F discharged from the introduction pipe is provided at the upper discharge end of the introduction pipe with a discharge portion connected to the circulation path 16 at the lower part. It is configured. Thereby, the bubbles of the solvent R can be separated from the slurry F, and the bubbles of the solvent R can be supplied into the introduction chamber 14 in a state of being separated from the undissolved slurry Fr circulated and supplied to the circulation path 16.

(Control part)
Although not shown, the control unit provided in the dispersion system 100 includes a known arithmetic processing device including a CPU, a storage unit, and the like, and includes a quantitative supply device X, a suction pump mechanism unit Y, and a solvent supply unit that constitute the dispersion system 100. The operation of each device such as 50 can be controlled.
In particular, the control unit is configured to be able to control the rotation speed of the rotor 5 (rotary blade 6), and the pressure in the outlet region of the supply chamber side through hole 7a and the introduction chamber side through hole 7b (throttle through hole) of the stator 7 is controlled. The rotation speed of the rotor blade 6 is set so that the saturated vapor pressure of the solvent R (3.169 kPa in the case of water at 25 ° C.) or less is set over the entire circumference of the outlet region, and the rotation speed is set. By rotating the blade 6, at least the region in the blade chamber 8 immediately after passing through the supply chamber side through hole 7 a and the introduction chamber side through hole 7 b of the stator 7 is continued over the entire circumference of the blade chamber 8. Thus, the microbubble region of the solvent R can be formed as a microbubble region where a large number of microbubbles are generated.
In addition, the control unit causes the pressure of the mixed fluid in the discharge channel 12a when the fluid space S communicates with the discharge channel 12a to be equal to or lower than the saturated vapor pressure of the solvent R (3,169 kPa in the case of 25 ° C. water). The rotation speed of the rotary blade 6 is set to the rotation speed of the rotary blade 6 and the rotary blade 6 is rotated at the set rotation speed, so that at least the region immediately after passing through the discharge port 12b in the discharge flow path 12a becomes a fine bubble ( It can be formed as a microbubble region where a large number of microbubbles are generated.

[Distributed system operation]
Next, the operation of the distributed system 100 will be described.
First, the quantitative supply device X is stopped, the shutter valve 46 is closed, and the suction of the powder P through the powder discharge pipe 45 is stopped, and the rotor 5 is moved while supplying only the solvent R from the solvent supply unit 50. Rotate and start the operation of the suction pump mechanism Y. When the predetermined operating time has elapsed and the inside of the suction pump mechanism Y is in a negative pressure state (for example, a vacuum state of about −0.06 MPa), the shutter valve 46 is opened. As a result, the expansion chamber 47 of the quantitative supply device X is brought into a negative pressure state (about −0.06 MPa), and the inside of the introduction part 41 and the vicinity of the lower opening 31b of the hopper 31 are between the negative pressure state and the atmospheric pressure state. To the pressure state.

Then, the quantitative supply device X is operated, and the powder P stored in the hopper 31 is quantified from the lower opening 31b of the hopper 31 by the stirring action of the stirring blade 32A and the negative pressure suction force of the suction pump mechanism Y. Through the expansion chamber 47 of the supply unit 40, a predetermined amount is continuously supplied in a predetermined amount to the mixing member 61 of the mixing mechanism 60. In parallel, the solvent supply unit 50 is operated, and the solvent R is continuously supplied in a predetermined amount to the mixing member 61 of the mixing mechanism 60 by the negative pressure suction force of the suction pump mechanism unit Y.
From the mixing member 61 of the mixing mechanism 60, the powder P is supplied to the supply port 11 through the cylindrical portion 62 of the mixing member 61, and the solvent R has a hollow cylindrical vortex flow without a break through the annular slit 63. The powder P and the solvent R are preliminarily mixed through the supply port 11 in a state, and the preliminary mixture Fp is introduced into the annular groove 10.

When the rotor 5 is driven to rotate and the partition plate 15 rotates integrally with the rotor 5, the scraping blade 9 provided concentrically on the partition plate 15 is inserted into the annular groove 10 with the tip 9 </ b> T. Circulate in a state.
Then, as shown by solid line arrows in FIGS. 4 and 5, the preliminary mixture Fp flowing through the supply port 11 and introduced into the annular groove 10 is fitted into the annular groove 10 and the tip of the scraping blade 9 that circulates. The preliminary mixture Fp that is scraped out by the portion 9T is roughly divided into the rotor 5 while being along the front surface of the funnel-shaped portion 15b and the front surface of the annular flat plate portion 15c in the partition plate 15 in the supply chamber 13. , Further flows through the supply chamber side through hole 7a of the stator 7 and flows into the blade chamber 8, flows in the blade chamber 8 in the rotation direction of the rotor 5, and is discharged from the discharge section 12. Is done.

The preliminary mixture Fp introduced into the annular groove 10 undergoes a shearing action when it is scraped by the tip portion 9T of the scraping blade 9. In this case, between the outward side surface 9o of the tip portion 9T of the scraping blade 9 and the inward inner surface of the inner annular groove 10, and the inward side surface 9i of the tip portion 9T of the scraping blade 9 and the inner annular groove. A shearing action acts between the 10 outward inner surfaces. At the same time, the so-called local boiling (cavitation) occurs on the rear surface 9a on the rear side in the rotational direction of the scraping blade 9 as the scraping blade 9 rotates. Further, when passing through the supply chamber side through hole 7 a of the stator 7, a shearing action works.
That is, since a shear force can be applied to the preliminary mixture Fp in the supply chamber 13 and local boiling can be generated, the preliminary mixture Fp to be scraped is sheared from the scraping blade 9 and the supply chamber side through hole 7a. As a result, the powder P is more favorably dispersed in the solvent R due to local boiling (cavitation) generated on the back surface 9 a of the scraping blade 9. Therefore, such a preliminary mixture Fp can be supplied, and good dispersion of the powder P with respect to the solvent R in the blade chamber 8 can be expected.

  The slurry F discharged from the discharge unit 12 is supplied to the recirculation mechanism unit 70 through the discharge path 18, and in the recirculation mechanism unit 70, the undissolved slurry Fr in a state containing the powder P that is not completely dissolved, The powder P is separated into the slurry F in a substantially completely dissolved state, and the bubbles of the solvent R are separated. The undissolved slurry Fr is supplied again to the inlet 17 of the suction pump mechanism Y through the circulation path 16. Then, the slurry F is supplied to the supply destination 80 through the discharge path 22.

  The undissolved slurry Fr is introduced into the introduction chamber 14 through the throttle portion 14a of the introduction port 17 in a state where the flow rate is limited. In the introduction chamber 14, it is shattered by a plurality of rotating stirring blades 21 to be further finely crushed, and is further shattered by the shearing action when passing through the introduction chamber side through hole 7 b. The At this time, the air is introduced into the blade chamber 8 in a state where the flow rate is limited via the introduction chamber side through hole 7b. Then, it flows in the blade chamber 8 in the rotational direction of the rotor 5 and is discharged from the discharge portion 12.

Here, the pressure in the blade chamber 8 which is the exit region of the supply chamber side through hole 7a and the introduction chamber side through hole 7b of the stator 7 becomes equal to or lower than the saturated vapor pressure of the solvent R over the entire circumference by the control unit. Thus, the rotational speed of the rotary blade 6 is set, and the rotary blade 6 is rotated at the set rotational speed.
Thereby, the pressure in the blade chamber 8 which is the said exit area | region is below the saturated vapor pressure (3.169kPa in the case of 25 degreeC water) of the solvent R over the perimeter by the rotation speed setting of the rotary blade 6 by this. Therefore, at least in the region in the blade chamber 8 immediately after passing through the supply chamber side through-hole 7a and the introduction chamber side through-hole 7b of the stator 7, generation of fine bubbles (microbubbles) due to evaporation of the solvent R is promoted. In this state, the region is formed as a fine bubble region in which a large number of fine bubbles are generated continuously over the entire circumference of the blade chamber 8.
Therefore, the crushing of the aggregate is promoted by foaming of the solvent R permeating the aggregate (so-called lumps) of the powder P over the entire circumference of the blade chamber 8, and the generated fine bubbles are further promoted. The dispersion of the powder P is further promoted by the impact force at the time when the blade chamber 8 is pressurized and disappears, and as a result, over almost the entire slurry F existing in the entire circumference of the blade chamber 8, A high-quality slurry F with good dispersion of the powder P in the solvent R can be produced.

  Regarding the operation of the dispersion system described above, the behavior of the premix Fp and the undissolved slurry Fr in the blade chamber 8 will be further described. As described above, the premix Fp flows into the blade chamber 8 through the supply chamber side through hole 7a of the stator 7 and the undissolved slurry Fr flows through the introduction chamber side through hole 7b.

  As shown in FIG. 5, ten rotating blades 6 are arranged in the blade chamber 8. In the blade chamber 8, ten fluid spaces S defined by two rotating blades 6 arranged at equal intervals, the stator 7, and the outer peripheral wall portion 4 are formed. Due to the movement (rotation) of the rotary blade 6 inside the blade chamber 8, the plurality of fluid spaces S rotate around the axis A <b> 3, and the preliminary mixture is supplied from the supply chamber 13 to the fluid space S through the supply chamber side through holes 7 a. Fp is sucked, and undissolved slurry Fr is sucked into the fluid space S from the introduction chamber 14 through the introduction side through hole 7a. Since the fluid space S is also rotated with the rotation of the rotary blade 6, the pressure inside the fluid space S is increased by the centrifugal force and the above suction force. When the fluid space S communicates with the discharge port 12b, the mixed fluid (the undissolved slurry Fr and the preliminary mixture Fp) is discharged from the fluid space S to the discharge port 12b.

Here, the rotational speed of the rotary blade 6 is set by the control unit so that the pressure of the mixed fluid in the discharge channel 12a when the fluid space S communicates with the discharge channel 12a is equal to or lower than the saturated vapor pressure of the solvent R, The rotor blade 6 is rotated at the set rotation speed.
Thereby, the pressure of the area | region immediately after passing the discharge port 12b at least in the discharge flow path 12a by the rotation speed setting of the rotary blade 6 is below the saturated vapor pressure of the solvent R (in the case of 25 degreeC water, 3.169 kPa). Therefore, in the region immediately after passing through the discharge port 12b in the discharge channel 12a, the generation of fine bubbles (microbubbles) due to the vaporization of the solvent R is promoted, and the region is a fine bubble in which many fine bubbles are generated. A state is formed as a region.
Therefore, in the discharge channel 12a, the foaming of the solvent R that has permeated the aggregate (so-called lumps) of the powder P promotes the crushing of the aggregate, and the dispersion of the powder P in the solvent R is good. High quality slurry F can be produced.

  Next, based on FIG. 8 and FIG. 9, the verification test result of generation of fine bubbles when the configuration of the first embodiment is adopted and the rotation speed of the rotor 5 (rotary blade 6) is appropriately controlled will be described. To do.

  These drawings show a state in which the main casing 1 is made of a transparent resin, and water as a fluid is passed through the suction pump mechanism Y, and the discharge flow path 12a and the discharge port 12b are observed. The number of rotations of the rotor blades 6 was gradually increased, and the generation state of bubbles due to vacuum boiling in the discharge flow path 12a was confirmed. Generation of bubbles was not observed at a rotational speed lower than that in the state of FIG. At the rotation speed (1800 rpm) in FIG. 8, fine bubbles are generated from the region immediately after passing through the discharge port 12b to the discharge flow path 12a, and look like white folds or bubbles. In the state of FIG. 9 (3600 rpm) where the rotational speed is further increased, the white wrinkles are darker and finer, more bubbles are generated, and the fine bubble region is larger. This is because the pressure of the mixed fluid when the fluid space (S) communicates with the discharge passage (12a) decreases as the rotational speed of the rotor blades increases, and the saturated vapor pressure of water (in the case of 25 ° C) Below 3.169 kPa), indicating that vacuum boiling has occurred.

Second Embodiment
In the first embodiment described above, R chamfering is applied to the downstream portion C2 of the circumferential connection portion C. Further, the end portion 6b of the rotary blade 6 on the outer peripheral wall portion 4 side is chamfered. As shown in FIG. 10, in 2nd Embodiment, the above-mentioned R chamfering is not provided, but the downstream part C2 and the edge part 6b of the rotary blade 6 have a pointed shape.

  Next, on the basis of FIG. 11 and FIG. 12, the verification test result of the generation of fine bubbles when the configuration of the second embodiment is adopted and the rotation speed of the rotor 5 (rotary blade 6) is appropriately controlled will be described. To do. Generation of bubbles was not observed at a rotational speed lower than that in the state of FIG. At the rotation speed (2400 rpm) in FIG. 11, a region such as a slightly white wrinkle or bubble is generated in the region immediately after passing through the discharge port 12 b. In the state of FIG. 12 (3600 rpm) where the rotational speed is further increased, a white wrinkle region is generated from the region immediately after passing through the discharge port 12b to the discharge channel 12a (fine bubble region). As the number of rotations increases, the pressure of the mixed fluid when the fluid space (S) communicates with the discharge flow path (12a) decreases, and the saturated vapor pressure of water (3,169 kPa at 25 ° C.) Below, indicating that boiling under reduced pressure has occurred.

  In the first embodiment having R chamfering, a fairly wide fine bubble region was generated at a rotation speed of 1800 rpm (FIG. 8). In the second embodiment having no R chamfering, the fine bubbles must be increased to 2400 rpm. The area did not occur. From the above experimental results, the effects of the R chamfering of the downstream portion C2 of the circumferential connection portion C and the R chamfering of the end portion 6b of the outer peripheral wall 4 side of the rotor blade 6 are shown.

  13 and 14 are simulation results of the flow velocity of the mixed fluid in the fluid space S and the discharge flow path 12a. In the second embodiment having no R chamfer shown in FIG. 13, a black region (region having a low flow velocity) exists near the center of the discharge flow path 12a. The area immediately after passing through the discharge port 12b is also a black area except for the upstream side (right side in the drawing) of the rotating blade 6 in the rotation direction.

  On the other hand, in 1st Embodiment which has R chamfering shown in FIG. 13, compared with FIG. 12, the white area | region (area | region where the flow velocity is high) has increased inside the discharge flow path 12a. Also in the area immediately after passing through the discharge port 12b, the white area is increased as compared with FIG. This is because the R portion chamfering is performed on the downstream portion C2 of the circumferential connection portion C, and the end portion 6b on the outer peripheral wall portion 4 side of the rotor blade 6 is subjected to the R chamfering. It shows that the flow of the mixed fluid to 12a becomes smooth.

<Third Embodiment>
In the above-described embodiment, the partition plate 15 is attached to the rotor 5, and the scraping blade 9 is provided on the partition plate 15. And these were rotated integrally, and the raking blade 15 scraped out the preliminary mixture Fp from the annular groove 10 to promote mixing. In the third embodiment, the rotor 5 is not provided with the partition plate 15, the scraping blade 9, and the spacing member 20, and the annular groove 10 on the inner surface of the front wall portion 2 of the casing 1 is not provided. Instead, in the third embodiment, the introduction chamber 14 is formed between the front wall 2 fixed to the suction pump mechanism Y and the rotor 5 that is rotationally driven by the motor M3. The front wall 2 has a first facing surface D1 that is a smooth flat surface that is orthogonal to the rotation axis of the rotor 5 and faces the rotor 5, and the rotor 5 is the rotor 5. And a second opposing surface D2 that is a smooth flat surface that is orthogonal to the rotation axis A3 and that opposes the first opposing surface D1.

  Specifically, as shown in FIG. 15, a region inside the stator 7 on the inner surface of the front wall portion 2 of the casing 1 is formed as a smooth flat surface (first facing surface D1). The first facing surface D1 is formed in a hollow disk shape except for a portion connected to the supply port 11 when viewed from a direction parallel to the axis A3. The first facing surface D <b> 1 is a plane orthogonal to the axis A <b> 3 and is disposed to face the rotor 5.

  The area | region inside the rotary blade 6 of the surface by the side of the front wall part 2 of the rotor 5 is formed as a smooth plane (2nd opposing surface D2). The second facing surface D2 is formed in a hollow disk shape when viewed from a direction parallel to the axis A3. The second facing surface D2 is a plane orthogonal to the axis A3, and is disposed to face the first facing surface D1.

  An introduction chamber 14 is formed between the front wall 2 configured as described above and the rotor 5. In this embodiment, since the partition plate 15 is not provided, the front wall portion 2 and the rotor 5 are directly opposed to each other, and the space between the front wall portion 2 and the rotor 5 is formed as a continuous space. . As a result, the introduction chamber 14 is formed between the front wall portion 2 and the rotor 5 and is sandwiched between the first facing surface D1 and the second facing surface D2, which are smooth planes. Therefore, the flow of the mixed fluid in the introduction chamber 2 becomes smoother. Thereby, since the flow velocity of the mixed fluid increases, fine bubbles can be generated more efficiently, and the quality of the generated sol can be further improved.

  The term “smooth” between the first facing surface D1 and the second facing surface D2 means that the surface is not provided with structures such as grooves, holes, corrugations, blades, etc. If the surface is formed as “,” this is the case. It is not necessary to have a particularly small surface roughness, for example, a mirror finish or a hairline finish.

<Relationship between rotor blade angle and mixed fluid pressure>
The pressure of the mixed fluid in the introduction chamber 14 and the fluid space S was calculated by simulation using a structural model in which the angles of the rotor blades 6 were variously changed. The structural model was the same as that in the above-described flow velocity simulation except for the angle of the rotor blades 6, and the calculation was performed under the condition that the rotational speed of the rotor 5 was 3600 rpm.

  The results are shown in the graph of FIG. The vertical axis represents the minimum value of the pressure of the mixed fluid in the introduction chamber 14 and the fluid space S. The horizontal axis is the angle of the rotor blade 6, that is, the angle formed by the rotor blade 6 and the moving direction (rotation direction) of the rotor blade 6. When the angle of the rotary blade 6 is 0 °, the rotary blade 6 and the rotation direction are parallel, and when the angle is 90 °, the rotary blade 6 is arranged in a direction that matches the diameter direction of the rotor 5.

  As shown in the graph of FIG. 16, when the angle of the rotary blade 6 changes, the pressure of the mixed fluid fluctuates periodically. When the angle is in the range from 0 ° to around 90 °, the pressure of the mixed fluid becomes low (0.4 Mpa or less) and vacuum boiling tends to occur. However, at an angle of 31 ° to 90 °, the pressure is too low, which may cause a drawback that the suction / discharge capability of the suction pump mechanism Y as a pump is lowered. Therefore, the preferred angle of the rotor blade 6 is greater than 0 ° and not greater than 31 °.

<Another embodiment>
In the above-described embodiment, both the downstream portion C2 of the circumferential connection portion C and the rear portion in the rotational direction of the end portion 6b on the outer peripheral wall portion 4 side of the rotor blade 6 are rounded. Only one side may be chamfered. Even in such a case, it is considered that there is an effect of smoothing the flow of the mixed fluid from the fluid space S to the discharge flow path 12a. Further, C chamfering may be performed instead of R chamfering. Other forms of chamfering are also conceivable. For example, not only the downstream part C2 of the circumferential connection part C but also the upstream part C1 may be chamfered, or the entire circumferential connection part C may be chamfered. Not only the rear portion of the end portion 6b of the rotary blade 6 in the rotation direction but also the front portion thereof may be chamfered.

  Note that the configurations disclosed in the above-described embodiments (including the other embodiments, the same applies hereinafter) can be applied in combination with the configurations disclosed in the other embodiments unless there is a contradiction. The embodiments disclosed in this specification are exemplifications, and the embodiments of the present invention are not limited thereto, and can be appropriately modified without departing from the object of the present invention.

1: Main casing (suction pump mechanism)
4: Outer peripheral wall 6: Rotor blade 6b: End 7: Stator 7a: Through hole (supply chamber side through hole)
7b: Through hole (introduction chamber side through hole)
8: Blade chamber 12a: Discharge channel 12b: Discharge port 14: Inlet chamber 100: Dispersion system C: Circumferential connection portion C2: Downstream portion D1: First facing surface D2: Second facing surface F: Slurry (sol)
Fp: Preliminary mixture Fr: Undissolved slurry (part of sol)
P: Powder (dispersoid)
R: solvent (liquid phase dispersion medium)
S: Fluid space Y: Suction pump mechanism

Claims (9)

Dispersion system comprising a centrifugal suction pump mechanism, passing a fluid mixture of a dispersoid and a liquid dispersion medium through the suction pump mechanism, and generating a sol in which the dispersoid is dispersed in the liquid dispersion medium Because
The suction pump mechanism is
An introduction chamber to which the mixed fluid is supplied;
A cylindrical stator disposed outside the introduction chamber and having a plurality of through holes formed in the circumferential direction;
An annular blade chamber formed outside the stator;
A discharge port formed on an outer peripheral wall of the blade chamber and connected to a discharge flow path through which the mixed fluid is discharged;
A plurality of rotating blades that are driven to rotate and move inside the blade chamber;
A plurality of fluid spaces defined by the plurality of rotor blades, the stator, and the outer peripheral wall portion are rotated and moved by the movement of the rotor blades in the blade chamber, and the fluid is separated from the introduction chamber through the through holes. Aspirating the mixed fluid into a fluid space, and discharging the mixed fluid from the fluid space to the discharge port when the fluid space communicates with the discharge port;
The control unit that controls the operation of the suction pump mechanism unit is configured such that the pressure of the mixed fluid in the discharge channel when the fluid space communicates with the discharge channel is equal to or lower than the saturated vapor pressure of the liquid phase dispersion medium. The rotation speed of the rotary blade is set, and the rotary blade is rotated at the set rotation speed, and at least a region immediately after passing through the discharge port in the discharge flow path is a fine portion of the liquid phase dispersion medium. A dispersion system formed as a fine bubble region where many bubbles are generated.   The dispersion system according to claim 1, wherein the discharge flow path extends along a tangential direction of the outer peripheral wall portion having a cylindrical shape.   3. The dispersion system according to claim 1, wherein, in a circumferential connection portion where the discharge flow path and the blade chamber are connected, at least a downstream portion in the rotational direction of the rotary blade is chamfered.   The distributed system according to claim 3, wherein the chamfering applied to the circumferential connection portion is an R chamfering having a radius of 2 mm or more.   The distribution system according to any one of claims 1 to 4, wherein a chamfer is applied to an end portion of the rotary blade on the outer peripheral wall side.   The dispersion system according to claim 5, wherein the chamfering applied to the rotor blade is an R chamfering having a radius of 2 mm or more.   The dispersion system according to any one of claims 1 to 6, wherein an angle between the rotary blade and a moving direction of the rotary blade is 10 ° or more and 80 ° or less.   The dispersion system according to any one of claims 1 to 6, wherein an angle formed by the rotor blade with respect to a moving direction of the rotor blade is greater than 0 ° and not greater than 31 °. The introduction chamber is formed between a front wall portion fixed to the suction pump mechanism portion and a rotor that is rotationally driven by a motor, and the rotor blades are disposed on an outer peripheral portion of the rotor,
The front wall has a first facing surface that is perpendicular to the rotation axis of the rotor and is a smooth flat surface facing the rotor;
The dispersion system according to any one of claims 1 to 8, wherein the rotor has a second facing surface that is a smooth flat surface that is orthogonal to the rotation axis of the rotor and faces the first facing surface.