JP2011011154A - Gas-liquid mixture force-feed system - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a gas-liquid mixture force-feed system capable of precisely controlling the amount of gas to be mixed with liquid.SOLUTION: The gas-liquid mixture force-feed system includes a force-feed pump 10 for force-feeding gas-liquid mixture fluid and gas mixture means for mixing gas with liquid on the suction side of the force-feed pump 10. The gas mixture means includes a plurality of sonic nozzles 481-484 arranged in parallel, and the circulation of any of the sonic nozzles 481-484 is restricted to control the amount of gas mixture.

Description

  The present invention relates to a gas-liquid mixed pumping system for pumping a gas-liquid mixed fluid.

Conventionally, a gas-liquid mixed fluid in which gas and liquid are mixed is sucked by a pump, and the sucked gas-liquid mixed fluid is pressurized and stirred, then discharged from the pump, and the discharged gas-liquid mixed fluid flows into the resistor. A microbubble generator that generates microbubbles for a gas-liquid mixed fluid with a resistor is known (see, for example, Patent Document 1).
Here, microbubbles, and micronanobubbles and nanobubbles that are finer than microbubbles will be described.

It is considered that there are three types of microbubbles.
One type of microbubble is generated in a shear region where a liquid is agitated in a device such as a turbine, a centrifugal pump, or a hydrodynamic meter where blades and impellers rotate at high speed, and is called so-called cavitation. . Hereinafter, microbubbles generated under such circumstances are classified as “micro negative pressure bubbles”. This “micro negative pressure bubble” basically consists of dissolved gas and liquid vaporized components, so it disappears over time. At this time, the space occupied by the bubble disappears rapidly. As described above, the bubble region may become a high temperature and a high pressure.

That is, in the case of microbubbles derived from cavitation, the volume when the “micro negative pressure bubble” is generated is Vf, the outer peripheral pressure at that time is Pf, the temperature is Tf, and the contracted state quantities are Ve, Pe. , Te, and the process is assumed to be polytropic change (n = polytropic index), the following relationship is established.
Pe = (Vf / Ve) ⁿ · Pf (A)
Te = (Vf / Ve) ⁿ⁻¹ · Tf (B)
In simple terms, “n” in the equation is an adiabatic change of “n = 1.4” if a change of “Vf → Ve” occurs in a very short time, and “Vf → Ve” in a long time. Is an isothermal change of “n = 1”. Among the formulas (A) and (B), the most problematic value is the value of “(Vf / Ve)”, and it is said that this disappears like a bubble {micro negative pressure bubble} generated by cavitation. Regardless of the size of “Vf”, “(Vf / Ve) = (Vf / 0) → ∞” tends to be infinite. As a result, the shrinking “micro (nano) bubble” region may have a very high pressure and a very high temperature.
It is said that such microbubbles, which are fine bubbles, and finer nanobubbles, are charged on the surface and generate a large amount of free radicals when crushed. It is considered a type of “pressure bubble”.

The other type of microbubble is a “microbubble” generated by supplying a gas using an ejector (or an aspirator) or the like under a pressure condition near atmospheric pressure. This microbubble has a positive-pressure gas inside as a nucleus, and is classified as a so-called “micro-positive pressure bubble” and does not easily disappear unless dissolved in the surrounding liquid. On the contrary, the bubbles are thought to expand and diffuse slowly.
Further, the bubbles dispersed in the high-pressure liquid are compressed into the surrounding high-pressure liquid and are classified as “micro high-pressure bubbles”, for example, the fuel injection pressure of the latest automobile diesel engine, 200 Bubbles generated under a high pressure of (MPa) are considered to expand at an acoustic velocity at the same time as jetting due to a pressure difference from the jetting environment, and rapidly disperse surrounding liquid.

Next, the effect of microbubbles will be described.
In the global environment, for example, enteric bacteria of house termites = -10 (μm), bacteria = about 0.5- (μm), mycoplasma = 0.125-0.25 (μm), rickettsia = 0.3-0.5 (μm)) × 0.3 (μm) small cocci, virus = 0.02-0.3 (μm), Salmonella = 0.5-2 (μm), staphylococci = There are fine substances such as 1 (μm), Helicobacter pylori = 4 (μm), Mycobacterium tuberculosis = 2 (μm), and Chlamydia = 0.8 (μm). Based on this, when the microbubble has a size of “1 (μm) to 20 (nm)”, the microbubble is taken into the body without a sense of incongruity in organisms such as fish and plants. Therefore, when the microbubbles are derived from a gas useful for ecology such as oxygen, a beneficial result is obtained for the ecology. On the other hand, in order to remove foreign matters such as sludge in the fuel in engines, the “≦ 50 (μm)” filter is used in marine diesel engines, and the “≦ 0.5 (μm)” filter is used in automobile gasoline engines. Is used as the final filter. In other words, the presence of “air” in the fuel usually promotes the wear of the sliding parts, but “gas” of a size below this level does not affect the engine life, but rather friction. It is predicted that the loss will be reduced (see, for example, Patent Document 2). In these two senses, the “gas size” in the liquid is an important factor. Conventionally, “microbubble” refers to a fine bubble having a diameter of 10 (μm) to several tens (μm) or less when it is generated. It is thought that it may change to “micro-nano bubbles”.

Here, “micro / nano bubbles” refers to fine bubbles having a diameter of several hundreds (nm) to 10 (μm) or less. The difference between “microbubbles” and “micronanobubbles” is said to have a large difference in shrinkage speed. As described above, this cause is due to the manufacturing process of “micro bubbles”. In the case of “micro negative pressure bubbles”, it disappears regardless of the pressure at the time of action, and in the case of “micro bubbles” by gas supply, Basically, as described later, when the pressure difference between the time of generation and the time of action is small, the characteristic is that the basic characteristics are not affected by “time”. Spread.
In addition, when the bubbles in the liquid are converted into “micro (nano) bubbles” with a size of “˜ ≦ 1 (μm)” which is the same level as the size of bacteria or viruses, the substance is taken into the living body without feeling uncomfortable. In the case of a useful gas, it gives a good effect. This effect is presumed to increase as “millibubble” → “microbubble” → “nanobubble”.

Furthermore, other effects of the microbubble will be described.
For example, when there is no difference between the generation pressure Pf (MPa (abs)) and the operation pressure Pe (MPa (abs)), such as when bubbles are generated using the ejector due to the effect of the supply liquid in the bathtub, the effect Is limited.
However, since the “micro (nano) bubble” fluid is usually pumped, the relationship is “the pressure Pf (MPa (abs)) during generation ≧ the pressure Pe (MPa (abs)) during operation. When the temperature is the same, assuming that the volume during generation is Vf (m ³ ) and the volume during operation is Ve (m ³ ), the relationship is “(Ve / Vf) = (Pf / Pe)”. In the case of a type pump (vortex pump, cascade pump, etc.), it is about “Pf ≧ 0.2 (MPa (abs))”, so that “Pe = 0.1 (MPa ( abs)) ”, the degree of expansion is only“ (Ve / Vf) = (Pf / Pe) ≈0.2 / 0.1 = 2 ”. However, if the fuel injection pressure Pf (MPa (abs)) is high as in the case of a diesel engine or a gasoline engine, it is assumed that “Pf = 20 (MPa (abs))” and compression at the time of fuel injection When the pressure is “Pf = 3.5 (MPa (abs))”, the pressure increases to “(Ve / Vf) = (Pf / Pe) ≈20 / 3.5 = 5.7”. Air bubbles expand at the speed of sound and contribute to the refinement of the injected fuel (internal explosion). In addition, in diesel engines, if the fuel internal air (oxidant) is at an arbitrary value because the injection atmosphere is high, Internal ignition in the bubble causes an explosion and further promotes fuel diffusion. At the same time, by the same effect as a fuel containing oxygen in the fuel (= oxygen-containing fuel such as dimethyl ether (common name: Dimethylether)), it contributes to the complete combustion of the fuel and the effect of reducing exhaust smoke. Further, since the supercharging effect is expected with respect to the air from the intake pipe, the phenomenon of unburned components such as exhaust smoke and the reduction of NOx due to the decrease in the combustion temperature are also expected by improving the combustion.

Here, when the pressure difference between the generation pressure Pf (MPa (abs)) and the operation pressure Pe (MPa (abs)) is large, the bubble expands the surrounding liquid due to the inertial effect due to the rapid expansion described above. If so, the bubbles are expected to self-contract. In the case of bubbles generated by cavitation, when shrinking, the volume after shrinkage becomes close to “zero”, so that the region becomes high temperature and generates a shock wave.
However, in the case of irrigation, farms, etc., if a part of the gas that has become `` micro (nano) bubbles '' in the surrounding liquid as it expands is dissolved in the liquid, it will be as much as `` micro bubbles '' derived from cavitation. However, in the case of a gas such as oxygen, the function of the bactericidal action may be increased due to reverse shrinkage.

JP 2003-117365 A JP 2007-009900 A

As in Patent Document 1, after the gas-liquid mixed fluid is sucked by the pump, it is compressed and discharged, and the above-described microbubbles are generated in the gas-liquid mixed fluid discharged from the pump, and then supplied to the supply destination. In the microbubble generator, there is a need to generate a microbubble and supply it to the supplier after adjusting the amount of gas with respect to the amount of liquid easily, appropriately and precisely according to the supplier.
The present invention has been made in view of the above-described circumstances, and an object thereof is to provide a gas-liquid mixed pressure feeding system capable of easily and precisely controlling the amount of gas mixed into a liquid.

  In order to achieve the above object, the present invention comprises a pressure-feed pump that pumps a gas-liquid mixed fluid, and a gas mixing means that mixes a gas with a liquid on the suction side of the pressure-feed pump. These sonic nozzles are provided in parallel, and one of the sonic nozzles is restricted in flow so that the gas mixing amount can be controlled.

  Here, in the gas-liquid mixed pressure feeding system of the above invention, the gas mixing means includes an on-off valve corresponding to each sonic nozzle, shuts off any on-off valve, restricts the flow of the corresponding sonic nozzle, The amount of gas mixture may be controlled.

  Further, in the gas-liquid mixed pressure feeding system of the above invention, the gas mixing may be stopped by shutting off the on-off valves for a predetermined period after the driving of the pressure pump is started.

  In the gas-liquid mixed pressure feeding system of the above invention, a constant pressure applying means for supplying gas to the sonic nozzle at a constant pressure may be provided.

  In the gas-liquid mixed pressure feeding system according to the invention, the constant pressure applying means may be a compressor provided upstream of the sonic nozzle.

  The gas-liquid mixed pressure feeding system according to the invention further includes gas supply means for supplying gas to the pressure pump, and the pressure pump is supplied to the sucked gas-liquid mixed fluid from the gas supply means. After the gas is mixed, the gas-liquid mixed fluid may be compressed and discharged.

  Further, in the gas-liquid mixed pressure feeding system according to the invention, the pressure feeding pump houses a piston shaft in a shaft case so as to be capable of reciprocating, and a piston is fixed to one outer end portion of the piston shaft penetrating the shaft case. The piston is accommodated in a cylinder connected to the shaft case, and a first pump chamber is formed in the cylinder on the surface side facing the outside of the piston. The first pump chamber has a first suction port and a first pump. While providing a discharge port, a second pump chamber is formed on the surface facing the inside of the piston, a second suction port and a second discharge port are provided in the second pump chamber, and according to the reciprocating drive of the piston, The pump may alternately perform the suction operation in the first pump chamber and the discharge operation in the second pump chamber, and the discharge operation in the first pump chamber and the suction operation in the second pump chamber.

  Further, in the gas-liquid mixed pressure feeding system according to the invention, the gas-liquid suction pipe through which the gas-liquid mixed fluid sucked by the pressure feed pump flows is divided into two, and one pipe is connected to the first suction port. The other pipe is connected to the second suction port, the gas-liquid discharge pipe through which the gas-liquid mixed fluid discharged from the pressure pump flows is divided into two, and one pipe is connected to the first discharge port In addition, the other pipe may be connected to the second discharge port.

  Further, in the gas-liquid mixed pressure feeding system according to the invention, the gas-liquid mixed fluid in which the gas-liquid mixed fluid sucked by the pressure feeding pump flows through one of the first suction port and the second suction port. A gas-liquid mixed fluid connected to a suction pipe, connected to the discharge port corresponding to the one suction port, and the other suction port, and discharged from the pressure pump to the discharge port corresponding to the other suction port A gas-liquid discharge pipe through which the gas flows may be connected.

  Further, in the gas-liquid mixed pressure feeding system of the above invention, a bubble generating device may be provided in a pipe connecting the discharge port corresponding to the one suction port and the other suction port.

  Further, in the gas-liquid mixed pressure feeding system according to the above invention, the piston is fixed to an outer end of the piston shaft so that the piston shaft does not protrude outward from the piston, The gas-liquid suction pipe may be connected, the first discharge port and the second suction port may be connected, and the gas-liquid discharge tube may be connected to the second discharge port.

  In the gas-liquid mixed pressure feeding system according to the invention, the gas pump chamber functions as a gas pump chamber that sucks and discharges gas in one of the first pump chamber and the second pump chamber, and the other. The pump chamber is made to function as a gas-liquid pump chamber that sucks and discharges the gas-liquid mixed fluid, and the air discharged from the pump chamber that functions as the gas pump chamber functions as the gas-liquid pump chamber You may make it comprise so that mixing with the gas-liquid mixed fluid suck | inhaled by the chamber was possible.

  Further, in the gas-liquid mixed pressure feeding system according to the invention, the piston is fixed to an outer end of the piston shaft so that the piston shaft does not protrude outward from the piston, and the second pump chamber is configured as a gas pump. The first pump chamber may function as a gas-liquid pump chamber.

  Further, in the gas-liquid mixed pressure feeding system according to the above invention, the pressure feeding pump accommodates a piston shaft in a shaft case so as to be capable of reciprocating, and a piston is disposed at each of the outer end portions of the piston shaft penetrating the shaft case. Each of the pistons is fixed and accommodated in each of the cylinders connected to the shaft case. In each of the cylinders, a first pump chamber is formed on the surface side facing the outside of the piston. The first suction port and the first discharge port are provided in one pump chamber, while the second pump chamber is formed on the surface side facing the inside of the piston, and the second suction port and the second discharge port are provided in the second pump chamber. In accordance with the reciprocating drive of the piston, the suction operation in the first pump chamber and the discharge operation in the second pump chamber in one of the cylinders, and the other cylinder Discharge operation in the first pump chamber and suction operation in the second pump chamber, discharge operation in the first pump chamber and suction operation in the second pump chamber in one of the cylinders, and in the other cylinder The pump may alternately perform the suction operation in the first pump chamber and the discharge operation in the second pump chamber.

  In the gas-liquid mixed pressure feeding system of the above invention, the piston shaft may be driven by a constant speed power transmission mechanism.

  According to the present invention, there is an effect that the amount of gas mixed into the liquid can be precisely controlled.

It is a figure which shows the structure of the gas-liquid mixed pressure feeding system which concerns on 1st Embodiment. It is a figure which shows the flow volume characteristic of a sonic nozzle. It is a figure which shows the flow volume characteristic of a sonic nozzle. It is a figure which shows an example of the combination of the sonic nozzle which distribute | circulates gas in a gas flow volume adjustment part. It is sectional drawing of a bubble generator. It is a side view of a mixing element. (A) is AA sectional drawing of FIG. 3, (B) is BB sectional drawing of FIG. 3, (C) is CC sectional drawing of FIG. It is a figure which shows the structure of the gas-liquid mixed pressure feeding system which concerns on 2nd Embodiment. It is a figure which shows the structure of the gas-liquid mixed pressure feeding system which concerns on 3rd Embodiment. It is a figure which shows the structure of the gas-liquid mixed pressure feeding system which concerns on 4th Embodiment. It is a figure which shows the structure of the gas-liquid mixed pressure feeding system which concerns on 5th Embodiment. It is a figure which shows the structure of the gas-liquid mixed pressure feeding system which concerns on 6th Embodiment. It is a figure which shows the structure of the gas-liquid mixed pressure feeding system which concerns on 7th Embodiment. It is a figure which shows the structure of the gas-liquid mixed pressure feeding system which concerns on 8th Embodiment. It is a figure which shows the structure of the gas-liquid mixed pressure feeding system which concerns on 9th Embodiment.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
<First Embodiment>
FIG. 1 is a diagram illustrating a configuration of a gas-liquid mixed pressure feeding system 1 according to the first embodiment.
As shown in FIG. 1, the gas-liquid mixed pumping system 1 includes a pumping pump 10, a gas-liquid suction system 12 is connected to the suction port 11 of the pumping pump 10, and a gas outlet is connected to the discharge port 13 of the pumping pump 10. A liquid discharge system 14 is connected.

The gas / liquid suction system 12 includes a gas suction pipe 15 and a liquid suction pipe 16.
The gas suction pipe 15 is provided with a filter portion 17. In the present embodiment, the outside air cleaned by the filter unit 17 is introduced into the gas suction pipe 15. When a specific gas such as oxygen, hydrogen, methane, CNG, or LPG is introduced into the gas suction pipe 15, a cylinder or the like for storing the specific gas is provided in the gas suction pipe 15.
In the gas suction pipe 15, a gas flow rate adjustment unit 20 (details will be described later) for adjusting the flow rate of the gas flowing through the gas suction pipe 15 is connected to the downstream side of the filter unit 17. A check valve 21 that prevents the backflow of the gas flowing through the gas suction pipe 15 is connected to the downstream side of the gas flow rate adjusting unit 20.
On the other hand, the liquid suction pipe 16 is connected to a liquid supply source 22 which is a supply source of a predetermined liquid such as water or gasoline.

The gas suction pipe 15 and the liquid suction pipe 16 are connected to each other at a connecting portion 23, and one end of a gas / liquid suction pipe 24 is connected to the connecting portion 23. The other end of the gas-liquid suction pipe 24 is connected to the suction port 11 of the pressure pump 10.
When the pressure pump 10 is driven, the air introduced into the gas suction pipe 15 through the filter unit 17 is adjusted in flow rate in the gas flow rate adjusting unit 20 by the negative pressure of the pressure pump 10, and then through the connecting unit 23. While flowing into the gas-liquid suction pipe 24, the liquid introduced from the liquid supply source 22 into the liquid suction pipe 16 flows into the gas-liquid suction pipe 24 through the connecting portion 23. The gas and liquid are mixed in the gas-liquid suction pipe 24 to generate a gas-liquid mixed fluid, and the generated gas-liquid mixed fluid is sucked into the pressure feed pump 10 through the suction port 11.

  The pressure pump 10 is a vane rotary pump, and compresses the gas-liquid mixed fluid sucked from the suction port 11 and then discharges it from the discharge port 13. In addition, the pumping pump 10 should just be a positive displacement pump, and pumps other than a vane-type rotary pump are applicable. Thus, in this embodiment, since the pressure pump 10 is a positive displacement pump, the gas-liquid mixed fluid can be discharged from the pressure pump 10 with a very strong discharge pressure.

One end of a gas-liquid discharge pipe 26 is connected to the discharge port 13 of the pressure feed pump 10.
In the gas / liquid discharge pipe 26, a check valve 27 for preventing the backflow of the gas / liquid flowing through the gas / liquid discharge pipe 26 is connected downstream of the discharge port 13. In addition, since the rotary positive displacement pump does not have a suction valve and a discharge valve like the pressure feed pump 10 according to the present embodiment, the check valve 27 is used to prevent backflow when the pressure feed pump 10 is stopped. However, in the case of a reciprocating pump equipped with a suction valve and a discharge valve, the check valve 27 is not essential.

In the gas-liquid discharge pipe 26, a bubble generator 28 is connected downstream of the check valve 27. The bubble generator 28 is a device that generates microbubbles or nanobubbles in the gas-liquid mixed fluid. A pressure adjustment valve 29 is provided downstream of the bubble generator 28.
When the pressure pump 10 is driven, the gas-liquid mixed fluid discharged from the discharge port 13 of the pressure pump 10 flows into the bubble generator 28 via the check valve 27. Then, after the bubble generating device 28 generates micro bubbles and nano bubbles in the gas-liquid mixed fluid, the pressure is adjusted by the pressure adjusting valve 29 and supplied to the supply destination.

Next, the gas flow rate adjusting unit 20 will be described.
In the present embodiment, the gas flow rate adjusting unit 20 functions as a gas mixing unit in cooperation with the pressure feed pump 10.
The gas flow rate adjusting unit 20 is a part that adjusts the flow rate of the gas flowing through the gas suction pipe 15, and a plurality of (four in this embodiment) sonic nozzles 48 (sonic nozzles 481-484) with respect to the gas suction pipe 15. Are connected in parallel. Further, an electromagnetic valve 49 (electromagnetic valve 491-electromagnetic valve 494) (open / close valve) is provided downstream of each of the sonic nozzles 481-484. The opening and closing of each solenoid valve 49 is controlled by a control unit (not shown). Instead of the electromagnetic valve 49, a mechanical switching valve that can be manually switched may be used. When the pressure feed pump 10 is driven, when the solenoid valve 49 is open, gas flows through the sonic nozzle 48 corresponding to the solenoid valve 49, while when the solenoid valve 49 is closed, the solenoid valve 49 corresponds to the solenoid valve 49. The gas flow in the sonic nozzle 48 is stopped.

The sonic nozzle 48 includes a nozzle body 50 having a cross-sectional area set so that the flow rate of the gas flowing out of the sonic nozzle 48 is constant, and the flow rate of the gas passing through the sonic nozzle 48 is controlled to the sonic speed. The gas flow rate is controlled to a constant flow rate. As the sonic nozzle 48, for example, those described in JP-A-6-201417 can be used. The sonic nozzle 48 is known as a “secondary calibration prototype of gas flow rate”, and the critical flow rate Qc passing through the sonic nozzle 48 depends on the type of gas and the sonic nozzle 48 as shown in (Equation 1) below. If the conditions on the upstream side are the same, it is uniquely determined by “the square root of the nozzle minimum sectional area A and the nozzle part gas temperature Ts”.
(Formula 1) ... Qc = ψ · A · (ρ _S / ρ ₀ ) · (k · g · R · Ts) ^0.5 (where ψ = flow coefficient, A = minimum cross-sectional area of the nozzle portion, (Ρ _S / ρ ₀ ) = flow rate measurement / calibration test gas density ratio, k = specific heat ratio, g = gravity acceleration, R = general gas constant, Ts = throat fluid temperature (= upstream of sonic nozzle 48 Temperature)).

FIG. 2 is a graph showing the flow rate characteristics of the sonic nozzle 48 that gives a gas flow rate Qg = about 1.7 liters / min, and the horizontal axis shows the pressure ratio between the outlet pressure and the inlet pressure of the sonic nozzle 48 (inlet pressure / outlet). Pressure), and the vertical axis represents the gas flow rate of the sonic nozzle 48. FIG. 3 is a graph showing the flow characteristics of the sonic nozzle 48 that gives a gas flow rate Qg = about 2.7 liters / min.
As shown in FIG. 2 and FIG. 3, even if the sonic nozzle 48 gives a gas flow rate Qg of 1.7 liters / min or 2.7 liters / min, from the vicinity of “inlet pressure / outlet pressure ≧ 2”. The gas flow rate of the sonic nozzle 48 is constant. In the present embodiment, the suction pressure condition of the pumping pump 10 that satisfies “inlet pressure / outlet pressure ≧ 2” is “suction pressure ≦ 50 (kPa)”. Regardless of the driving conditions of the pump 10, the gas flow rate is substantially constant. In particular, in the pressure-feed pump 10 that is a positive displacement pump, unless the liquid flow rate is extremely reduced in the liquid suction pipe 16, the liquid flow rate Qf (from the liquid suction pipe 16 to the pressure feed pump 10 via the gas-liquid suction pipe 24). Liter / min) is constant, so that “gas-liquid mixing ratio = Qg / Qf” when the pump 10 is driven can be controlled to be substantially constant.

Further, if the sonic nozzle 48 is precisely processed so as to give a desired gas flow rate, the gas flow rate of the sonic nozzle 48 can be made constant by using the negative pressure when the pressure feed pump 10 is driven. it can. Therefore, by applying the sonic nozzle 48 as a gas flow rate adjustment member, the gas flow rate can be controlled without using a relatively expensive flow rate sensor or flow rate control device. Improvements can be made.
Further, in response to the suction operation of the pressure feed pump 10, liquid suction and gas suction are performed. For this reason, when the suction speed is slow and the liquid flow rate is small (in the case of a reciprocating pump, near the top and bottom dead centers of the piston, and in the rotary pump, the suction starts and ends), the negative pressure by the pressure pump 10 is also small. The gas flow rate flowing through the sonic nozzle 48 is also reduced. Thereby, the gas flow rate is not excessively supplied compared to the liquid flow rate, and “automatic control of the gas flow rate” proportional to the liquid flow rate is possible.

As described above, the gas flow rate of the sonic nozzle 48 itself cannot be changed although the gas flow rate of the sonic nozzle 48 itself can be made very precisely constant. Therefore, conventionally, for example, a flow rate adjustment valve is provided in the gas suction pipe 15, and the gas flow rate is controlled by the flow rate adjustment valve.
Based on this, in the present embodiment, the four sonic nozzles 481-484 of the gas flow rate adjustment unit 20 can be selectively combined with the sonic nozzles 48 that allow gas to flow from among the four sonic nozzles 481-484. Configured. Thereby, the sonic nozzle 48 which distribute | circulates gas was combined appropriately, and the gas flow rate of the gas flow rate adjustment part 20 was controllable to arbitrary gas flow rates from many gas flow rates.

Specifically, in this embodiment, the gas flow rates of the sonic nozzles 481-484 are different from each other. The “gas flow rate of the sonic nozzle 48” is a gas flow rate when the above-described inlet pressure / outlet pressure exceeds a predetermined value and the gas flow rate is stabilized.
That is, the gas flow rate of the sonic nozzle 481 is a liter / min, the gas flow rate of the sonic nozzle 482 is 2 a liter / min, twice that of the sonic nozzle 481, and the gas flow rate of the sonic nozzle 483 is 4 times that of the sonic nozzle 481. The gas flow rate of the sonic nozzle 484 is 8a liter / min, which is eight times that of the sonic nozzle 481.
Then, by controlling the opening and closing of the electromagnetic valves 491 to 494, the sonic nozzles 48 that allow the gas to flow from the sonic nozzles 481 to 484 are selectively combined, and a desired gas flow rate is realized by the gas flow rate adjustment unit 20.

FIG. 4 is a diagram illustrating an example of a combination of sonic nozzles 48 that allow gas to flow in the gas flow rate adjustment unit 20.
In the present embodiment, by combining the sonic nozzles 481-484 through which the gas is circulated, the gas flow rate adjusting unit 20 performs the following as shown in the “settable nozzle flow rate” field of the record related to “record 4” in FIG. 15 types of gas flow rates can be realized.

1. a liter / min. That is, a gas flow rate of a liter / min can be realized by allowing gas to flow only through the sonic nozzle 481. In order to allow the gas to flow only through the sonic nozzle 481, the electromagnetic valve 491 is opened while the electromagnetic valves 492-494 are closed. The same applies to the following.
2.2 a liter / min. This is realized by allowing gas to flow only for the sonic nozzle 482.
3.4 a liter / min. This is realized by allowing gas to flow only for the sonic nozzle 483.
4.8 a liter / min. This is realized by allowing the gas to flow only for the sonic nozzle 484.
5.3 a liter / min. This is realized by allowing gas to flow through the sonic nozzle 481 and the sonic nozzle 482.
6.5 a liter / min. This is realized by allowing gas to flow through the sonic nozzle 481 and the sonic nozzle 483.
7.9 a liter / min. This is realized by allowing gas to flow through the sonic nozzle 481 and the sonic nozzle 484.
8.6 a liter / min. This is realized by allowing gas to flow through the sonic nozzle 481 and the sonic nozzle 483.
9.10 a liter / min. This is realized by allowing gas to flow through the sonic nozzle 482 and the sonic nozzle 484.
10.12 a liter / min. This is realized by allowing gas to flow through the sonic nozzle 483 and the sonic nozzle 484.
11.7 a liter / min. This is realized by allowing gas to flow through the sonic nozzle 481, the sonic nozzle 482, and the sonic nozzle 483.
12.11 a liter / min. This is realized by allowing gas to flow through the sonic nozzle 481, the sonic nozzle 482, and the sonic nozzle 484.
13.13 a liter / min. This is realized by allowing gas to flow through the sonic nozzle 481, the sonic nozzle 483, and the sonic nozzle 484.
14.14 a liter / min. This is realized by allowing gas to flow through the sonic nozzle 482, the sonic nozzle 483, and the sonic nozzle 484.
15.15 a liter / min. This is realized by allowing gas to flow through the sonic nozzle 481, the sonic nozzle 482, the sonic nozzle 483, and the sonic nozzle 484.

As described above, in this embodiment, the plurality of sonic nozzles 481-484 are connected in parallel to the gas suction pipe 15, and the sonic nozzle 48 through which the gas flows is selectable. Here, since the sonic nozzle 48 alone can realize a constant gas flow rate very precisely, a wide range of sonic nozzles 48 can be obtained by selectively combining the sonic nozzles 48 through which gas is circulated from among a plurality of sonic nozzles 481-484. The gas flow rate can be precisely controlled within the range. Furthermore, since the gas flow rate is adjusted by the gas flow rate adjustment unit 20 using the sonic nozzle 48, the gas flow rate can be easily adjusted.
As shown in FIG. 4, the number of sonic nozzles 48 is not limited to four. For example, in the case of two sonic nozzles 48, three types of gas flow rates can be realized, and in the case of three sonic nozzles 48, seven types of gas flow rates can be realized. However, in the case of one sonic nozzle 48, only the gas flow rate corresponding to the inner diameter is generated, so it is important to select the optimum sonic nozzle 48 according to the capacity of the pressure feed pump 10 to be used. .
Depending on the type of the pressure pump 10, when the gas-liquid mixed fluid is sucked, the gas-liquid mixed fluid may be normally sucked when the amount of gas relative to the liquid in the gas-liquid mixed fluid is within a certain range. is there. Based on this, by providing the gas flow rate adjustment unit 20 on the suction side of the pressure pump 10 as in this embodiment, it is possible to ensure that the amount of gas relative to the liquid in the gas-liquid mixed fluid is within a certain range. Thus, normal suction of the pressure feed pump 10 can be reliably realized. The same applies to other embodiments.

  In the present embodiment, in the initial driving of the pressure pump 10, all the solenoid valves 491 to 494 are closed under the control of the control unit under the condition that the inside of the pressure pump 10 is filled with air. Excessive air is prevented from being sucked into the pressure feed pump 10. Only after a predetermined time has elapsed after the pumping pump 10 is driven and the inside of the pumping pump 10 is filled with the liquid, the appropriate electromagnetic valve 49 is opened under the control of the control unit, so that the liquid, the gas, Mixing is started.

In general, when the gas-liquid mixed pressure feeding system 1 is applied to a combustor such as “burner”, “gas turbine”, “gasoline engine”, “diesel engine”, etc., liquid (fuel) is used. to complete combustion, the gas flow rate Vg to liquid flow rate Vf is the stoichiometric air-fuel ratio 15, when the specific weight of air and ^{1.29 × 10-3 (kg / m 3} ), "(Vg / Vf) = (15 / 1.29 × 10−3) / (1 / 0.9) ≈10465 (specific gravity; gasoline≈0.75, kerosene≈0.79, fuel oil≈0.86 to 0.93) ” Also, from the viewpoint of the effect of fuel dispersion by “micro (nano) bubble” air, the larger the (Vg / Vf), that is, the greater the gas-liquid mixing ratio (Qg / Qf) described above, the better. Therefore, the larger the gas flow rate of the gas to be supplied, the better. As a result, in order to reduce the liquid discharge capability of the pressure pump 10, the (Qg / Qf) during actual operation is at most “(Qg / Qf) ≦ It is desirable to be about 0.5 ".

Next, the bubble generator 28 will be described.
FIG. 5 is a longitudinal sectional view of the bubble generator 28. FIG. 6 is a side view of the mixing element 31 included in the bubble generator 28. 7A is a cross-sectional view taken along line AA in FIG. 6, FIG. 7B is a cross-sectional view taken along line BB in FIG. 6, and FIG. 7C is a cross-sectional view taken along line CC in FIG. FIG.
In FIG. 5, the bubble generating device 28 includes a tube body 32, and female screw portions 33 and 33 are formed at both ends of the tube body 32 for connecting the gas-liquid discharge tube 26. An annular seat 34 is integrally formed on the inner periphery of the tubular body 32, and is positioned on the annular seat 34, and three mixing elements 31 are sequentially accommodated in the flow path 35 of the tubular body 32. ing.

  As shown in FIG. 6, the mixing element 31 is a member integrally including a flange portion 37 and a cylindrical portion 38, and the outer peripheral portion of the flange portion 37 is fitted to the inner peripheral portion of the tube body 32. Yes. A sleeve 39 that restricts the distance between the elements 2 is interposed between the mixing elements 31, and the outer peripheral portion of the sleeve 39 is fitted into the inner peripheral portion of the tube body 32. The mixing element 31 has an inlet chamber 40 communicating with the upstream side on the outer peripheral portion thereof. In this example, an annular inlet chamber 40 is formed between the inner periphery of the tube body 32 or the inner periphery of the sleeve 39 and the outer periphery of the tube portion 38. In addition, the mixing element 31 has an outlet chamber 41 communicating with the downstream side on the inner peripheral portion thereof. In this example, an outlet chamber 41 having a circular cross section is formed inside the cylindrical portion 38.

As shown in FIG. 6, the circumferential wall portion of the cylindrical portion 38 of the mixing element 31 has three rows of first communication holes 43 and second rows communicating with the inlet chamber 40 and the outlet chamber 41 with an interval in the axial direction. A communication hole 44 and a third communication hole 45 are formed.
Of the first communication hole 43, the second communication hole 44, and the third communication hole 45 in each row, the first communication hole 43 on the most upstream side is substantially tangent to the inner circumferential circle 46 as shown in FIG. Perforated along the direction. On the other hand, as shown in FIG. 7C, the third communication hole 45 on the most downstream side is drilled along the tangential direction of the inner circumferential circle 46 and in the direction almost opposite to the first communication hole 43. . Further, the second communication hole 44 located in the middle between the first communication hole 43 and the third communication hole 45 is drilled along substantially the radial direction of the inner circumferential circle 46 as shown in FIG. ing.

Next, the operation of the bubble generator 28 will be described.
The gas-liquid mixed fluid discharged from the pressure feed pump 10 flows into the bubble generator 28. The gas-liquid mixed fluid that has flowed into the bubble generator 28 is discharged into the outlet chamber 41 through the first communication hole 43, the second communication hole 44, and the third communication hole 45 in the mixing element 31 of the bubble generator 28. However, the gas-liquid mixed fluid is stirred, diffused, and mixed in the process. Specifically, the fluid discharged to the outlet chamber 41 through the first communication hole 43 on the most upstream side is within a vertical plane orthogonal to the flow in the flow path 35, as shown in FIG. In the figure, the first direction turning force is received in the clockwise direction, and the mixture is first sufficiently stirred in this process. Next, as shown in FIG. 4 (B), the fluid that has passed through the second communication hole 44 is ejected in the radial direction of the inner circumferential circle 46 and collides with the fluid that is sufficiently stirred on the upstream side and flowing. , Diffusion mixed. As shown in FIG. 7C, the fluid that has passed through the third communication hole 45 on the most downstream side receives the second direction turning force in the counterclockwise direction in the drawing, and is sufficiently stirred in this process. This flow collides with the flow that has received the upstream first direction turning force in the outlet chamber 41 and acts to cancel the first direction turning force. In this way, the gas-liquid mixed fluid is stirred, diffused, and mixed.

Furthermore, the gas-liquid mixed fluid that has flowed into the bubble generator 28 is finely divided into a large number so as to pass through the three rows of the first communication holes 43, the second communication holes 44, and the third communication holes 45. Microbubbles and nanobubbles are generated according to the shearing force that acts when this is divided.
In the present embodiment, the gas-liquid mixed fluid is finely divided into a large number by the first communication hole 43, the second communication hole 44, and the third communication hole 45. Nano bubbles are generated.
Furthermore, in this embodiment, the pressure feed pump 10 is a positive displacement pump, and the gas-liquid mixed fluid is discharged from the pressure feed pump 10 with a very strong discharge pressure. For this reason, it is possible to allow the gas-liquid mixed fluid to flow into the bubble generator 28 with a strong pressure. Therefore, the gas-liquid mixed fluid is allowed to pass through the first communication hole 43, the second communication hole 44, and the third communication hole 45 formed in each mixing element 31 so that microbubbles and nanobubbles are reliably contained in the gas-liquid mixed fluid. Can be generated. That is, in the gas-liquid mixed pressure feeding system 1 according to this embodiment, the combination of the pressure-feed pump 10 and the bubble generator 28 can reliably generate microbubbles and nanobubbles in the gas-liquid mixed fluid. For this reason, it is not necessary to give the pump the function of generating bubbles.

As described above, in this embodiment, the pumping pump 10 that pumps the gas-liquid mixed fluid is provided, and gas is mixed with the liquid on the suction side of the pumping pump 10. In the gas flow rate adjusting unit 20, a plurality of sonic nozzles 48 are provided in parallel to the gas suction pipe 15, and the flow rate of any of the sonic nozzles 48 is restricted to control the amount of gas mixed with the liquid.
According to this configuration, by restricting the flow of any of the sonic nozzles 48, the amount of air flowing through the gas suction pipe 15 can be precisely controlled.

In the present embodiment, an electromagnetic valve 49 is provided corresponding to each sonic nozzle 48. The flow of the sonic nozzle 48 is restricted by controlling the opening and closing of the electromagnetic valve 49.
According to this configuration, it is possible to reliably restrict the flow of the sonic nozzle 48 using the electromagnetic valve 49. In the case of manual control, an on-off valve may be used instead of the solenoid valve (not shown).

  Further, in the present embodiment, in the initial driving of the pressure pump 10, all the solenoid valves 491-494 are closed under the control of the control unit under the condition that the inside of the pressure pump 10 is filled with air. Excessive air is prevented from being sucked into the pressure feed pump 10. Only after a predetermined time has elapsed after the pumping pump 10 is driven and the inside of the pumping pump 10 is filled with the liquid, the appropriate electromagnetic valve 49 is opened under the control of the control unit, so that the liquid, the gas, Mixing is started.

Second Embodiment
Next, a second embodiment will be described.
FIG. 8 is a diagram showing a configuration of the gas-liquid mixed pressure feeding system 1b according to the present embodiment.
In the present embodiment, the same components as those in the above-described embodiment are denoted by the same reference numerals, and the description thereof is omitted.
The gas-liquid mixed pressure feeding system 1b according to this embodiment is different from the gas-liquid mixed pressure feeding system 1 according to the first embodiment in the following points.
That is, in the liquid suction pipe 16, a throttle portion 52 that restricts the flow rate of the liquid flowing through the liquid suction pipe 16 is provided on the downstream side of the liquid supply source 22. Downstream of the throttle unit 52, a liquid pressure sensor 53 that detects the pressure of the liquid after passing through the throttle unit 52, and a liquid pressure display that explicitly displays the pressure of the liquid detected by the liquid pressure sensor 53. A total of 54 is provided.

  Moreover, the pump 10b according to the present embodiment is a pump having self-priming performance (a so-called pump of a type divided into a positive displacement pump), and specifically, a Roots pump. It should be noted that a general “reciprocating motion” such as a vane type rotary pump similar to the pressure pump 10 according to the first embodiment, a rotary type pump other than the roots pump, a diaphragm pump, a plunger pump, etc. A “pump” or a direct-acting pump described later may be used. By using these pumps, the gas-liquid mixed fluid can be discharged from the pressure pump 10b at a very high discharge pressure, and microbubbles and nanobubbles can be generated by combining with the bubble generator 28.

Next, the operation of the gas-liquid mixed pressure feeding system 1b will be described.
First, by controlling the throttle unit 52 based on the detection value of the liquid pressure sensor 53, the internal pressure of the gas-liquid mixed fluid at the end of the suction of the pressure pump 10 is slightly reduced to the atmospheric pressure (= saturated vapor pressure of the liquid). ) The above-mentioned “micro negative pressure bubble” is generated as follows. In this state, the gas-liquid mixed fluid is compressed and discharged by the pressure feed pump 10b, and the discharged gas-liquid mixed fluid is caused to flow into the bubble generator 28. As a result, the “bubbles” contained in the gas-liquid mixed fluid are rapidly contracted and eliminated. By such an operation, in particular, it is possible to increase the bactericidal effect due to the disappearance effect of microbubbles and nanobubbles.
In particular, since the above-described operation can be performed after the gas flow rate adjusting unit 20 precisely adjusts the amount of gas with respect to the amount of liquid, the micro negative pressure bubble is adjusted with the amount and state of the micro negative pressure bubble adjusted. Can be generated.

<Third Embodiment>
Next, a third embodiment will be described.
FIG. 9 is a diagram showing a configuration of a gas-liquid mixed pressure feeding system 1c according to the present embodiment.
In the present embodiment, the same components as those in the above-described embodiment are denoted by the same reference numerals, and the description thereof is omitted.
The gas-liquid mixed pressure feeding system 1c according to this embodiment is different from the gas-liquid mixed pressure feeding system 1 according to the first embodiment in the following points.
That is, a feed pump 56 is provided in the liquid suction pipe 16. The feed pump 56 is a pump provided to compensate for the suction pressure loss of the pressure pump 10c. For example, when the distance between the liquid supply source 22 such as a tank and the pressure pump 10c is long, the feed pump 56 circulates through the liquid suction pipe 16. It is provided when the viscosity of the liquid is high. Downstream of the feed pump 56, a liquid pressure sensor 53c that detects the pressure of the liquid after being discharged by the feed pump 56, and a liquid pressure display that explicitly displays the pressure of the liquid detected by the liquid pressure sensor 53c. A total 54c is provided.
In the gas suction pipe 15, a compressor 57 and a motor 58 for driving the compressor 57 are provided on the upstream side of the filter unit 17. Further, in the gas suction pipe 15, on the downstream side of the filter unit 17, a gas pressure sensor 59 for detecting the gas pressure upstream of the gas flow rate adjustment unit 20, that is, the inlet pressure of the sonic nozzle 48, A gas pressure indicator 69 that explicitly displays the gas pressure detected by the gas pressure sensor 59 is provided.
Moreover, the pumping pump 10c according to the present embodiment is a reciprocating pump.

Next, the operation of the gas-liquid mixed pressure feeding system 1c according to this embodiment will be described.
In the present embodiment, the provided compressor 57 to the upstream side of the sonic nozzle 48, by applying a constant pressure P _S against sonic nozzle 48 by the compressor 57, the inlet pressure of the sonic nozzle 48, a feed pump 56 More than the pressure of the pumping capacity.

Here, “ρ _S / ρ ₀ = (P _S / P ₀ ) · (T ₀ / T _S )” (where P _S = the inlet pressure when the compressor 57 exists, P ₀ = the compressor 57 is This is because the inlet pressure in the absence, T ₀ = the inlet temperature of the sonic nozzle 48 in the absence of the compressor 57, and T _S = the inlet temperature of the sonic nozzle 48 in the presence of the compressor 57). Substituting into (Equation 1), the following (Equation 2) is obtained.
(Formula 1) ... Qc = ψ · A · (ρ _S / ρ ₀ ) · (k · g · R · Ts) ^0.5
(Formula 2) ... Qc = ψ · A · (P _S / P ₀ ) · (T ₀ / T _S ) · (k · g · R · Ts) ^0.5
That is, the flow rate Qc flowing through the sonic nozzle 48 is uniquely proportional to “P _S ” if other conditions such as the inlet temperature T _S are fixed, but if constant pressure control is performed with the “P _S ”, It can be seen that the gas flow rate can be kept constant, although “Qc” increases as “P _S ” increases.
That is, when “P _S = P ₀ = atmospheric pressure” and “P _S ” increases, the suffix “0” is added to “Qc” in the case of “T _S = T ₀ ”, and “Qc ₀ ” Then, the flow rate Qc at “P _S ” is
(Formula 3) ... Qc = Ps · Qc ₀
It is possible to control the gas flow rate by managing the flow rates “Qc ₀ ” and “P _S ” of the basic sonic nozzle 48.

  Based on this, in the present embodiment, by driving the compressor 57, gas is supplied to the sonic nozzle 48 at a constant pressure equal to or higher than the pressure of the feed pump 56, and the gas flow rate of the sonic nozzle 48 is increased. Keep constant. This makes it possible to control the gas flow rate more precisely.

<Fourth embodiment>
Next, a fourth embodiment will be described.
FIG. 10 is a diagram showing a configuration of a gas-liquid mixed pressure feeding system 1d according to the present embodiment.
In the present embodiment, the same components as those in the above-described embodiment are denoted by the same reference numerals, and the description thereof is omitted.
The gas-liquid mixed pressure feeding system 1d according to the present embodiment is different from the gas-liquid mixed pressure feeding system 1 according to the first embodiment in the following points.
That is, in the liquid suction pipe 16, a throttle unit 52 is provided downstream of the liquid supply source 22 as in the second embodiment, and a liquid pressure sensor 53 and a liquid pressure indicator 54 are provided downstream of the throttle unit 52. Is provided.

In the gas-liquid mixed pressure feeding system 1d according to this embodiment, a gas supply system 60 is connected to the pressure feeding pump 10d. The gas supply system 60 includes a gas supply pipe 61, and a compressor 62 is connected to the gas supply pipe 61, and a motor 63 for driving the compressor 62 is connected to the compressor 62. ing. In the gas supply pipe 61, a filter portion 64 is provided on the downstream side of the compressor 62, and a gas pressure sensor 65 is provided on the downstream side of the filter portion 64. The gas pressure sensor 65 is connected to a gas pressure indicator 66 that explicitly displays the gas pressure detected by the gas pressure sensor 65. An electromagnetic valve 67 that controls the flow of the gas flowing through the gas supply pipe 61 is provided downstream of the gas pressure sensor 65.
The gas supply system 60 further mixes gas with the gas-liquid mixed fluid sucked into the pressure feed pump 10d from the gas-liquid suction pipe 24 by supplying gas to the pressure feed pump 10d by driving the compressor 62. . The gas supply system 60 can reliably and significantly increase the amount of gas with respect to the amount of liquid in the gas-liquid mixed fluid discharged from the pressure feed pump 10d.

Next, the operation of the gas-liquid mixed pressure feeding system 1d according to this embodiment will be described.
As the pressure feed pump 10d is driven, the gas-liquid mixed fluid is sucked from the gas-liquid suction pipe 24 into the pressure feed pump 10d. At the same time, the compressor 62 is driven by the motor 63, and gas is supplied from the gas supply pipe 61 to the pressure pump 10d. In the pressure pump 10d, the gas-liquid mixed fluid is compressed and discharged after further gas is mixed with the gas-liquid mixed fluid from the gas supply pipe 61. Since it operates in this way, the amount of gas relative to the amount of liquid in the gas-liquid mixed fluid discharged from the pressure feed pump 10d can be made extremely high. Thereby, the gas-liquid mixed fluid in which bubbles are generated by the bubble generator 28 also becomes a gas-liquid mixed fluid with a large amount of gas mixture.
In the case where the amount of gas with respect to the amount of liquid is required to be very high, the above request can be realized more suitably by using the gas-liquid mixed pressure feeding system 1d according to the present embodiment.

<Fifth Embodiment>
Next, a fifth embodiment will be described.
FIG. 11 is a diagram showing a configuration of a gas-liquid mixed pressure feeding system 1e according to the present embodiment.
In the present embodiment, the same components as those in the above-described embodiment are denoted by the same reference numerals, and the description thereof is omitted.
The pumping pump 10e according to the present embodiment includes a shaft case 71 that houses a piston shaft 70, and the shaft case 71 includes end walls 72 and 73. An airtight chamber 74 is formed in the space surrounded by the end walls 72 and 73 inside the shaft case 71.
Bearings 75 and 76 are disposed on the end walls 72 and 73, respectively, and the piston shaft 70 is supported by the pair of bearings 75 and 76 so as to be rotatable and reciprocally movable in the shaft case 71. A piston 77 is fixed to the outer end portion of the piston shaft 70 penetrating the end wall 72 of the shaft case 71 by a piston fixing screw 98. The piston 77 is connected to the end wall 72 side of the shaft case 71. The cylinder 79 is slidably accommodated. A piston ring 105 is fitted on the outer periphery of the piston 77, and the gap between the outer periphery of the piston 77 and the inner periphery of the cylinder 79 is closed by the piston ring 105.

The cylinder 79 is closed by a cylinder head 80, and a pressure communication hole 87 is formed at the top of the cylinder head 80. An O-ring 93 is provided in a through hole through which the piston shaft 70 penetrates in the cylinder head 80. Similarly, a through hole through which the piston shaft 70 penetrates in an end wall 94 provided on the opposite side of the cylinder head 80 of the cylinder 79. An O-ring 95 is provided in the hole, and the O-rings 93 and 95 ensure airtightness inside the cylinder 79.
A piston shaft cover 86 is provided on the end wall 73 side of the shaft case 71. A pressure communication hole 88 is formed in the top of the piston shaft cover 86.

A first suction port 81 is provided at an end of the outer periphery of the cylinder 79 on the cylinder head 80 side (left side in FIG. 11), and a first discharge port 82 is provided corresponding to the first suction port 81. . Each of the first suction port 81 and the first discharge port 82 is provided with a first suction valve body 83 and a first discharge valve body 84 biased by springs. The first suction valve body 83 fluctuates against the bias of the spring when the first pump chamber 100 is in an expansion / suction process described later and a predetermined negative pressure is applied. On the other hand, the first discharge valve body 84 fluctuates against the bias of the spring when the first pump chamber 100 is in a compression / discharge process to be described later and a predetermined pressure is applied.
On the other hand, a second suction port 90 is provided at the end of the outer periphery of the cylinder 79 on the piston shaft cover 86 side (right side in FIG. 11), and a second discharge port 91 is provided corresponding to the second suction port 90. It has been. The second suction port 90 and the second discharge port 91 are respectively provided with a second suction valve body 96 and a second discharge valve body 97 that are biased by a spring.
Further, in the cylinder 79, a first pump chamber 100 is formed on the surface of the piston 77 on the cylinder head 80 side (surface facing outward), and the surface of the piston 77 on the piston shaft 70 side (surface facing inward). ) Is formed with a second pump chamber 101.

A motor 102 capable of rotating in the forward and reverse directions is disposed outside the shaft case 71, and a drive shaft 107 is coupled to an output shaft 103 of the motor 102 via a coupling 104. The drive shaft 107 extends into the hermetic chamber 74 through the sealing portion 108 and the bearing 109, and a pinion gear 110 is fixed to the tip of the drive shaft 107.
The pinion gear 110 meshes with a rack gear 111 fixed to the piston shaft 70, and when the pinion gear 110 rotates by driving the motor 102, the piston shaft 70 reciprocates in the hermetic chamber 74 via the rack gear 111 meshing with the pinion gear 110. The motor 102, pinion gear 110, rack gear 111 and the like constitute a power transmission mechanism. In particular, the power transmission mechanism according to the present embodiment is a constant speed power transmission mechanism in which the piston shaft 70 can reciprocate at a constant speed.

  A proximity sensor 114 is provided at the end of the outer periphery of the shaft case 71 on the cylinder head 80 side (left side in FIG. 11), and a proximity sensor 115 is provided on the end on the piston shaft cover 86 side (right side in FIG. 11). Is provided. On the other hand, in the piston shaft 70, when the piston 77 reaches the top dead center in the first pump chamber 100 (that is, the bottom dead center in the second pump chamber 101), the top dead center is located at a position detected by the proximity sensor 114. A marker 112 is formed. Similarly, in the piston shaft 70, when the piston 77 reaches the top dead center in the second pump chamber 101 (that is, the bottom dead center in the first pump chamber 100), the top dead center is detected at the position detected by the proximity sensor 115. A point marker 113 is formed.

  As the motor 102, a forward / reverse rotation motor such as a pulse motor or a servo motor is used, and the piston shaft 70 is controlled to reciprocate at a constant speed under the control of a control unit (not shown). For this reason, since the piston shaft 70 is controlled to reciprocate at a constant speed, fluid is discharged at the same intake / discharge flow velocity, and discharge without pulsation is ensured.

The operation of the piston shaft 70 accompanying the drive of the motor 102 will be described in detail. When the piston shaft 70 moves at a constant speed toward the cylinder head 80 side as the motor 102 is driven, the first pump chamber 100 compresses and discharges. The process is executed, and the expansion / suction process is executed in the second pump chamber 101. That is, in the first pump chamber 100, the first suction port 81 is closed by the first suction valve body 83, and the gas-liquid mixed fluid compressed by the piston 77 is compressed and then passed through the first discharge port 82. Are discharged into the first gas-liquid discharge pipe 121. On the other hand, in the second pump chamber 101, the second discharge port 91 is closed by the second discharge valve body 97 and the gas-liquid mixed fluid is sucked from the second suction port 90.
When the piston 77 reaches the top dead center of the first pump chamber 100 (that is, the bottom dead center of the second pump chamber 101), the top dead center marker 112 provided on the piston shaft 70 is attached to the shaft case 71. Detected by the proximity sensor 114, a signal to that effect is output to the control unit. Upon receiving the signal input, the control unit controls the motor 102 to reversely rotate the motor 102, thereby causing the piston shaft 70 to move at a constant speed in the reverse direction (the direction toward the piston shaft cover 86).

When the piston shaft 70 moves toward the piston shaft cover 86 at a constant speed, the first pump chamber 100 executes the expansion / suction process, and the second pump chamber 101 executes the compression / discharge process. When the piston 77 reaches the top dead center of the second pump chamber 101 (that is, the bottom dead center of the first pump chamber 100), the top dead center marker 113 provided on the piston shaft 70 is attached to the shaft case 71. Detected by the proximity sensor 115, a signal to that effect is output to the control unit. Upon receiving the signal input, the control unit controls the motor 102 to reversely rotate the motor 102 and move the piston shaft 70 at a constant speed in the reverse direction (the direction toward the cylinder head 80).
In this way, the piston shaft 70 reciprocates.
In the above description, the rotation motor and rack & pinion rotation-linear motion conversion system is used, but it is directly driven by electricity-shaft motor, electric cylinder, or electric actuator may be used. (Not shown).

In the present embodiment, the gas / liquid suction pipe 24 branches at the branching portion 117 into two pipes, a first gas / liquid suction pipe 118 and a second gas / liquid suction pipe 119. One end of the first gas-liquid suction pipe 118, which is one pipe, is connected to the first suction port 81, and one end of the second gas-liquid suction pipe 119, which is the other pipe, is connected to the second suction port 90. It is connected to the. The gas-liquid mixed fluid branches at the branching portion 117 and is sucked into the pressure feed pump 10e via the first suction port 81 or the second suction port 90.
In the present embodiment, the gas-liquid discharge pipe 26 is branched at the branch portion 120 into a first gas-liquid discharge pipe 121 and a second gas-liquid discharge pipe 122, and one end of the first gas-liquid discharge pipe 121. Is connected to the first discharge port 82, and one end of the second gas-liquid discharge tube 122 is connected to the second discharge port 91. The gas-liquid mixed fluid discharged from the pressure pump 10 e is discharged from the first discharge port 82 or the second discharge port 91 and then flows into the bubble generator 28.

  The pressure feed pump 10e according to the present embodiment includes means for converting the rotation of the motor 102 into linear motion, and the piston shaft 70 connected to the piston 77 is held by the bearings 75 and 76 and moved in the axial direction. By increasing the centering accuracy of the cylinder 79 and the piston 77, the direct sliding between the cylinder 79 and the piston 77 becomes zero, and the conventional problem of wear of the piston 77 and the cylinder 79 is eliminated.

Next, the operation of the gas-liquid mixed pressure feeding system 1e according to this embodiment will be described.
As the motor 102 is driven, when the piston shaft 70 linearly moves at a constant speed toward the cylinder head 80 side (left side in FIG. 11), the compression / discharge process is performed in the first pump chamber 100 as described above. The gas-liquid mixed fluid discharged from the first pump chamber 100 through the first discharge port 82 by this compression / discharge process flows into the bubble generator 28, and microbubbles and nanobubbles are generated by the bubble generator 28. Is supplied to the supplier.
At the same time, in the second pump chamber 101, the expansion / suction process is executed. Through this expansion / suction process, the gas-liquid mixed fluid is sucked into the second pump chamber 101 via the second suction port 90.

On the other hand, when the piston shaft 70 moves linearly at a constant speed toward the piston shaft cover 86 side (right side in FIG. 11), as described above, in the first pump chamber 100, the expansion / suction process is performed. Through this expansion / suction process, the gas-liquid mixed fluid is sucked into the first pump chamber 100 via the first suction port 81.
At the same time, a compression / discharge process is performed in the second pump chamber 101. The gas-liquid mixed fluid discharged from the second pump chamber 101 through the second discharge port 91 by this compression / discharge process flows into the bubble generator 28, and microbubbles and nanobubbles are generated by the bubble generator 28. After that, the “micro high pressure bubble” is supplied to the supplier.

Thus, in the present embodiment, in the cylinder 79, the first pump chamber 100 on the surface side of the piston 77 on the cylinder head 80 side is provided with the first suction port 81 and the first discharge port 82, and the piston A second suction port 90 and a second discharge port 91 are provided on the surface of the 77 on the piston shaft cover 86 side. When one of the first pump chamber 100 and the second pump chamber 101 is in the compression / discharge stroke, the other is in the expansion / intake stroke, so that the pump action is performed twice in one cycle. Done. For this reason, when the moving speed of the piston shaft 70 is constant, the piston shaft 70 is operated with a sufficient stroke, and the reversing time is short, a discharge action with less pulsation is expected.
Further, since the inner diameter φd of the piston shaft 70 is provided at the center of the cylinder inner diameter φD, the stroke volume is “(D ² −d ² ) / D ² = {1− (d ² / D ² )}” for the same stroke. ”Has the disadvantage of becoming smaller. However, “Peak and cylinder parts are reduced” and “Leakage from the piston ring, which is important as a moving part, is currently difficult to completely zero, but with this method, leakage to the next stroke There is also a feature such as “no major problem because it is not leaked to the drive system in terms of function and performance”.

As described above, in the present embodiment, the pumping pump 10e accommodates the piston shaft 70 in the shaft case 71 so as to be capable of reciprocating, and the piston 77 is provided at one outer end of the piston shaft 70 that penetrates the shaft case 71. The piston 77 is accommodated in a cylinder 79 connected to the shaft case 71, and a first pump chamber 100 is formed in the cylinder 79 on the surface side facing the outside of the piston 77. While providing the 1 suction port 81 and the 1st discharge port 82, the 2nd pump chamber 101 is formed in the surface side which goes inside the piston 77, and the 2nd suction port 90 and the 2nd discharge port 91 are formed in this 2nd pump chamber 101. In accordance with the reciprocating drive of the piston 77, the suction operation in the first pump chamber 100 and the discharge operation in the second pump chamber 101, the discharge operation in the first pump chamber 100, and the second pump chamber 101 A pump for the the suction operation alternately.
For this reason, discharge with little pulsation is ensured by the pressure feed pump 10e.

In the present embodiment, the gas-liquid suction pipe 24 through which the gas-liquid mixed fluid sucked by the pressure pump 10 e flows is branched into two, and one first gas-liquid suction pipe 118 is connected to the first suction port 81. In addition, the other second gas-liquid suction pipe 119 is connected to the second suction port 90. Further, the gas-liquid discharge pipe 26 through which the gas-liquid mixed fluid discharged from the pressure feed pump 10e flows is branched into two, and one of the first gas-liquid discharge pipes 121 is connected to the first discharge port 82, and the other The second gas / liquid discharge pipe 122 was connected to the second discharge port 91.
For this reason, the gas-liquid mixed fluid generated by mixing and mixing the gas and the liquid is surely sucked, compressed and discharged by the pressure-feed pump 10e and the gas discharged by the pressure-feed pump 10e using the pressure-feed pump 10e. It is possible to realize generation of bubbles for the liquid mixed fluid. In particular, it is possible to realize these while ensuring discharge with less pulsation from the pressure feed pump 10e.

<Sixth Embodiment>
Next, a sixth embodiment will be described.
FIG. 12 is a diagram showing a configuration of a gas-liquid mixed pressure feeding system 1f according to the present embodiment.
In the present embodiment, the same components as those in the above-described embodiment are denoted by the same reference numerals, and the description thereof is omitted.
In the gas-liquid mixed pressure feeding system 1f according to the present embodiment, the configuration of the pressure feeding pump 10f is different from the configuration of the pressure feeding pump 10e according to the fifth embodiment in the following points.
That is, the piston 77 is attached to the piston shaft 70 with the upper surface 89 at one end of the piston shaft 70 on the cylinder head 80f side coincident with the surface of the piston 77 on the cylinder head 80f side (left side in FIG. 12). . That is, the piston 77 is attached to the piston shaft 70 so that the piston shaft 70 does not protrude toward the cylinder head 80f side (outside).
Therefore, when the inner diameter of the cylinder 79 is φD, the outer diameter of the piston shaft 70 is φd, and the stroke is S, the stroke volume of the first pump chamber 100 is “π (D ² · S) / 4”, the second pump The stroke volume of the chamber 101 is “(D ² −d ² ) · S / 4”, and the stroke volume of the first pump chamber 100 is large.

In the present embodiment, the same gas-liquid suction system 12 as that in the first embodiment is connected to the first suction port 81 of the first pump chamber 100.
Further, the first discharge port 82 of the first pump chamber 100 and the second suction port 90 of the second pump chamber 101 are connected by a pipe 125, and a bubble generator 281 f is provided in the pipe 125. ing.
Further, a gas-liquid discharge system 14 similar to that of the first embodiment is connected to the second discharge port 91 of the second pump chamber 101.

Next, the operation of the gas-liquid mixed pressure feeding system 1f according to this embodiment will be described.
When the pinion gear 110 rotates in one direction as the motor 102 is driven, the piston shaft 70 linearly moves toward the cylinder head 80f side (left side in FIG. 12). At this time, the compression / discharge process is performed in the first pump chamber 100, while the expansion / suction process is performed in the second pump chamber 101. Here, the gas-liquid mixed fluid discharged to the pipe 125 through the first discharge port 82 of the first pump chamber 100 is generated in the second pump chamber 101 after microbubbles and nanobubbles are generated in the bubble generator 281f. The air is sucked into the second pump chamber 101 through the second suction port 90.
On the other hand, when the piston shaft 70 linearly moves toward the piston shaft cover 86 side (right side in FIG. 12), the first pump chamber 100 performs the expansion / suction process, and the second pump chamber 101 compresses / A discharge process is performed. Here, in the second pump chamber 101, the gas-liquid mixed fluid in the state in which microbubbles and nanobubbles have already been generated is compressed by the bubble generator 28, and the bubbles containing the included microbubbles and nanobubbles into the liquid are compressed. Dissolution and miniaturization are promoted. The gas-liquid mixed fluid discharged from the second pump chamber 101 through the second discharge port 91 by the compression / discharge process in the second pump chamber 101 flows into the bubble generator 28, and is further reduced by the bubble generator 28. Bubbles and nanobubbles are generated.

Here, as described above, the stroke volume of the first pump chamber 100 is larger than the stroke volume of the second pump chamber 101. In the present embodiment, the gas-liquid mixed fluid is sucked into the first pump chamber 100 by utilizing this, and when the gas-liquid mixed fluid is compressed and the mixture of the gas and the liquid is promoted, the gas compressibility is increased. Therefore, the disadvantage that the discharge pressure is reduced is characterized in that the pressure is increased by repressurization in the second pump chamber 101.
In addition, a bubble generator 281f is connected to a pipe 125 that connects the first discharge port 82 of the first pump chamber 100 and the second suction port 90 of the second pump chamber 101, thereby forcibly stirring the gas-liquid mixed fluid. By mixing, generation of microbubbles and nanobubbles and homogenization of the gas-liquid mixed fluid can be achieved. The gas-liquid mixed fluid in this state is further compressed and increased in pressure in the second pump chamber 101, so that bubbles contained therein are dissolved and miniaturized in the liquid.

In the present embodiment, the gas-liquid mixed fluid discharged from the second pump chamber 101 flows into the bubble generator 28, and microbubbles and nanobubbles are generated by the bubble generator 28. Due to such a system configuration, the two-stage gas-liquid mixed fluid compression in the first pump chamber 100 and the second pump chamber 101 and the two-stage bubble generation by the bubble generator 281f and the bubble generator 28 are performed. Therefore, microbubbles and nanobubbles can be efficiently generated in the high-pressure gas-liquid mixed fluid. That is, the above-mentioned “micro high pressure bubble” is generated.
In particular, in the bubble generation device 281f, homogeneous mixing of gas and liquid, and generation of microbubbles and nanobubbles in the gas-liquid mixed fluid are performed. Based on this, when the pump 10f according to the present embodiment is applied to the gas-liquid mixed pumping system 1d according to the fourth embodiment and the piston 77 exists at the top dead center in the first pump chamber 100, the cylinder head If gas is supplied from the gas supply system 60 according to the fourth embodiment to the first pump chamber 100 via 80f, the amount of gas mixed into the liquid can be greatly increased, and combustion is performed. As a result of fuel refinement due to rapid expansion at the speed of sound of “micro high-pressure bubbles” after injection (supply), the amount of oxygen involved in burners, gas turbines, gasoline engines, diesel engines, etc. In a combustor, it can greatly contribute to combustion improvement.

<Seventh embodiment>
Next, a seventh embodiment will be described.
FIG. 13 is a diagram showing a configuration of a gas-liquid mixed pressure feeding system 1g according to the present embodiment.
In the present embodiment, the same components as those in the above-described embodiment are denoted by the same reference numerals, and the description thereof is omitted.
In the present embodiment, the configuration of the pumping pump 10g is the same as the configuration of the pumping pump 10f of the sixth embodiment.

A gas suction pipe 130 is connected to the second suction port 90 of the second pump chamber 101 of the pressure pump 10g. A filter portion 171g is connected to the gas suction pipe 130, and when the second pump chamber 101 is in the expansion / suction process, the air purified by the filter portion 171g is supplied to the gas suction pipe 130 and the second suction port. The air is sucked into the second pump chamber 101 through 90.
The second discharge port 91 of the second pump chamber 101 and the gas pressurizing hole 87g formed in the cylinder head 80g are connected via a pipe 131. The pipe 131 is provided with an electromagnetic valve 132. When the second pump chamber 101 is in the compression / discharge process, and when the electromagnetic valve 132 is open, gas is discharged to the pipe 131 through the second discharge port 91, and the gas discharged to the pipe 131 is The gas is supplied to the first pump chamber 100 through the gas pressurizing hole 87g.
Further, the same gas-liquid suction system 12 as in the first embodiment is connected to the first suction port 81 of the first pump chamber 100, and the first discharge port 82 of the first pump chamber 100 is connected to the first discharge port 82. A gas-liquid discharge system 14 similar to that of the embodiment is connected.

Next, the operation of the gas-liquid mixed pressure feeding system 1g according to this embodiment will be described.
When the first pump chamber 100 is in the expansion / suction process and the second pump chamber 101 is in the compression / discharge process, the gas is compressed in the second pump chamber 101 from the second discharge port 91. Discharged. In this case, the second pump chamber 101 functions as a compressor that compresses and discharges gas.
At the same time, in the first pump chamber 100, the gas-liquid mixed fluid is sucked from the gas-liquid suction system 12 through the first suction port 81. The gas-liquid mixed fluid sucked here is a fluid in which the amount of gas is precisely controlled by the sonic nozzle 48.
Then, when the suction end timing is reached, that is, when the piston 77 reaches the bottom dead center in the first pump chamber 100, the electromagnetic valve 132 is opened for an arbitrary period of time, via the pipe 131 and the gas pressurizing hole 87g. Thus, the high-pressure gas compressed by the second pump chamber 101 is jetted and supplied to the first pump chamber 100. Thereby, a large amount of air is mixed with the gas-liquid mixed fluid sucked into the first pump chamber 100.
Next, after the piston 77 reaches the bottom dead center, the electromagnetic valve 132 is closed when the compression / discharge process is started in the first pump chamber 100 by moving in the reverse direction. In the compression / discharge process in the first pump chamber 100, compression / discharge is performed after a large amount of gas is mixed with the liquid. For this reason, the gas-liquid mixed fluid discharged from the first pump chamber 100 contains a large amount of gas. By generating microbubbles and nanobubbles by the bubble generator 28 with respect to the gas-liquid mixed fluid, “Micro (nano) bubble” fluids with high gas content can be supplied.
When the first pump chamber 100 is in the compression / discharge process, the expansion / suction process is performed in the second pump chamber 101, and gas is sucked through the second suction port 90.

Here, in order to mix a large amount of gas (for example, air), it is usually necessary to separately prepare a compressor and a high-pressure gas cylinder in addition to the liquid pump. In this embodiment, the second pump Since the chamber 101 functions as a compressor, it is not necessary to prepare these devices separately, and cost reduction can be realized.
The first pump chamber 100 having a large stroke volume (= capacity) of “π (D ² · S) / 4” is used as a gas-liquid pump, and the stroke volume (= capacity) is “π (D ² -d ^2). ) · S / 4 ”, which is a small second pump chamber 101, is used as a gas pump (= compressor), and at the end of the suction of the first pump chamber 100, the compressed gas is injected to increase the gas content. It has the feature of supplying “micro (nano) bubble” fluid.
Further, as an advantage of utilizing the second pump chamber 101 as a compressor for gas, in addition to the above-described advantages, “a slight leak occurred from the piston ring 105 of the piston 77 to the first pump chamber 100 side. However, it can be mixed with gas and returned to the second pump chamber 101 again. ”“ In the first pump chamber 100, since gas such as air is mainly used, temporarily, via the piston shaft 70, Even if there is a leak in the linear motion part, it is a non-corrosive fluid and does not cause major trouble.

<Eighth Embodiment>
Next, an eighth embodiment will be described.
FIG. 14 is a diagram showing a configuration of a gas-liquid mixed pressure feeding system 1h according to the present embodiment.
In the present embodiment, the same components as those in the above-described embodiment are denoted by the same reference numerals, and the description thereof is omitted.
The pump 10h according to this embodiment includes a shaft case 161 that houses a piston shaft 160, and the shaft case 161 includes end walls 162 and 163. Bearings 164 and 165 are disposed on the end walls 162 and 163, respectively, and the piston shaft 160 is supported by the pair of bearings 164 and 165 so as to be rotatable and reciprocally movable in the shaft case 161. Pistons 166 and 167 are fixed to both outer ends of the piston shaft 160 that penetrates the end walls 162 and 163 of the shaft case 161, respectively. These pistons 166 and 167 are connected to both ends of the shaft case 161. The cylinders 168 and 169 are slidably accommodated. Piston rings 175 are attached to the outer circumferences of the pistons 166 and 167, respectively.

A valve seat 170 is attached to the cylinders 168 and 169. The valve seat 170 is provided with a suction port 171 and a discharge port 172. The suction port 173 and the discharge port 172 are each provided with a suction valve body 173 biased by a spring. And a discharge valve body 174 is provided.
Pump chambers 176 and 177 are formed on the pushing side of the pistons 166 and 167, and back pressure chambers 178 and 179 are formed on the piston shaft side of the pistons 166 and 167, respectively. Each of the back pressure chambers 178 and 179 communicates with the airtight chamber 181 of the shaft case 161 through a communication hole 180 formed in the end walls 162 and 163 of the shaft case 161. A motor 183 that can rotate forward and backward is disposed outside the shaft case 161, and a drive shaft 186 is coupled to an output shaft 184 of the motor 183 via a coupling 185. The drive shaft 186 extends into the hermetic chamber 181 via a sealing portion 187 and a bearing 188, and a pinion gear 190 is fixed to the tip of the drive shaft 186.
The pinion gear 190 meshes with a rack gear 191 fixed to the piston shaft 160, and when the pinion gear 190 rotates by driving the motor 183, the piston shaft 160 reciprocates in the hermetic chamber 181 through the rack gear 191 meshing with the pinion gear 190.

  The motor 183 uses a forward / reverse rotating motor such as a “pulse motor” or a “servo motor”, and is controlled by an arbitrary “constant” “piston speed” by a “control device (not shown)”. . For this reason, as in the previous example, fluid is discharged at the same “intake / discharge flow velocity”, and discharge without pulsation is ensured. These operating strokes are the same as in the above case. When one pump is in the “compression / discharge stroke”, the other pump is in the “expansion / intake stroke”. When the piston 166 reaches the top dead center, the top dead center marker 193 is detected by the proximity sensor 194. When the piston 167 reaches the top dead center, the top dead center marker 195 is detected by the proximity sensor 196. The

The pressure feed pump 10e according to the present embodiment includes means for converting the rotation of the motor 183 into linear motion, and the piston shaft 160 connected to the pistons 166 and 167 is held by the bearings 164 and 165 and moved in the axial direction. Therefore, by increasing the centering accuracy of the cylinders 168, 169 and the pistons 166, 167, the direct sliding between the cylinders 168, 169 and the pistons 166, 167 becomes zero, and the piston and cylinder wear, which has been a problem in the past, has become a problem. Is eliminated.
That is, in the pumping pump 10e according to the present embodiment, the piston shaft 160 is held by the bearings 164 and 165 and the center shaft of the cylinders 168 and 169 moves horizontally. No pressing force is generated when rotating on the cylinder wall. As a result, the pistons 166 and 167 have zero sliding friction with the cylinder wall, and the piston ring 175 only slides. By using the piston ring 175 having excellent sliding performance, the wear is made regardless of the gas-liquid fluid. Less operation is possible.

The gas-liquid suction pipe 24 branches into a first gas-liquid suction pipe 199 and a second gas-liquid suction pipe 200 at a branching portion 198, and the first gas-liquid suction pipe 199 is sucked on the cylinder 168 side. The second gas-liquid suction pipe 200 is connected to the inlet 171 on the cylinder 169 side.
Furthermore, the gas-liquid discharge pipe 26 branches into a first gas-liquid discharge pipe 202 and a second gas-liquid discharge pipe 203 at the branching portion 201, and the first gas-liquid discharge pipe 202 is a discharge port on the cylinder 168 side. 172 and the second gas-liquid discharge pipe 203 is connected to the discharge port 172 on the cylinder 169 side.

Next, the operation of the gas-liquid mixed pressure feeding system 1h according to this embodiment will be described.
As the motor 183 is driven, when the piston shaft 160 moves at a constant speed in the direction toward the cylinder 168 (left direction in FIG. 14), the compression / discharge process is executed in the pump chamber 176 and the expansion / suction is performed in the pump chamber 177. The process is executed. The gas-liquid mixed fluid discharged from the discharge port 172 on the cylinder 168 side by the compression / discharge process in the pump chamber 176 flows into the bubble generator 28, and after nanobubbles and microbubbles are generated in the bubble generator 28, Supplied.
On the other hand, when the piston shaft 160 moves at a constant speed in the direction toward the cylinder 169 (right direction in FIG. 14), the compression / discharge process is executed in the pump chamber 177 and the expansion / suction process is executed in the pump chamber 176. . The gas-liquid mixed fluid discharged from the discharge port 172 of the cylinder 169 by the compression / discharge process in the pump chamber 177 flows into the bubble generating device 28 and is supplied after nano bubbles and micro bubbles are generated in the bubble generating device 28. Is done.
As described above, the compression / discharge process is performed in the pump chamber 176 and the expansion / suction process is performed in the pump chamber 177, and the expansion / suction process is performed in the pump chamber 176, and the pump chamber 177 is performed. Since the state in which the compression / discharge process is executed is alternately displaced, the gas-liquid mixed fluid can be discharged from the pressure feed pump 10h with little pulsation.

<Ninth Embodiment>
Next, a ninth embodiment will be described.
FIG. 15 is a diagram showing a configuration of a gas-liquid mixed pressure feeding system 1 i according to the present embodiment.
In the present embodiment, the same components as those in the above-described embodiment are denoted by the same reference numerals, and the description thereof is omitted.
The pumping pump 10i according to the present embodiment is different from the pumping pump 10f according to the sixth embodiment in the following points. In other words, a cylinder 79 i is provided at an end of the shaft case 71 opposite to the end where the cylinder 79 is provided. The structure of the cylinder 79i and the member related to the cylinder 79i is the same as the structure of the cylinder 79 and the member related to the cylinder 79. Briefly, the cylinder 79i is divided into a first pump chamber 100i and a second pump chamber 101i by a piston 77i. The first pump chamber 100i has a first suction port 81i and a first discharge port 82i. The second pump chamber 101i is provided with a second suction port 90i and a second discharge port 91i.

A gas / liquid suction system 12 is connected to the first suction port 81 of the first pump chamber 100 of the cylinder 79. Further, the first discharge port 82 and the second suction port 90 are connected by a pipe 210, and a bubble generator 281 is provided in the pipe 210. A first gas / liquid discharge pipe 282 is connected to the second discharge port 91 of the second pump chamber 101.
On the other hand, a gas-liquid suction system 12i is connected to the first suction port 81i of the first pump chamber 100i of the cylinder 79i. Since the configuration of the gas-liquid suction system 12i is the same as that of the gas-liquid suction system 12, the description thereof is omitted. The first discharge port 82i and the second suction port 90i are connected by a pipe 210i, and a bubble generating device 281i is provided in the pipe 210i. A second gas / liquid discharge pipe 282i is connected to the second discharge port 91i of the second pump chamber 101i.
The first gas-liquid discharge pipe 282 and the second gas-liquid discharge pipe 282 i are connected at a branch portion 285, and the gas-liquid discharge system 14 is connected to the branch portion 285.

Next, the operation of the gas-liquid mixed pressure feeding system 1i according to this embodiment will be described.
When the piston shaft 70 moves toward the cylinder 79 (left side in FIG. 15), the compression / discharge process is executed in the first pump chamber 100 of the cylinder 79. That is, the gas-liquid mixed fluid is compressed by the piston 77 and discharged from the first discharge port 82. The gas-liquid mixed fluid discharged from the first discharge port 82 generates microbubbles and nanobubbles in the bubble generator 281 and is sucked into the second pump chamber 101 that performs the expansion / suction process.
At the same time, the expansion / suction process is executed in the first pump chamber 100i of the cylinder 79i. That is, the gas-liquid mixed fluid is sucked into the first pump chamber 100i from the gas-liquid suction system 12i. At the same time, the compression / discharge process is executed in the second pump chamber 101i of the cylinder 79i. That is, in the second pump chamber 101i, the compressed gas-liquid mixed fluid is discharged from the second discharge port 91i. Here, the gas-liquid mixed fluid discharged from the second discharge port 91i flows into the bubble generator 28, and microbubbles and nanobubbles are generated in the bubble generator 28.

On the other hand, when the piston shaft 70 moves toward the cylinder 79i (the right side in FIG. 15), the expansion / suction process is executed in the first pump chamber 100 of the cylinder 79. That is, the gas-liquid mixed fluid is sucked into the first pump chamber 100 from the gas-liquid suction system 12. At the same time, the compression / discharge process is executed in the second pump chamber 101 of the cylinder 79. That is, in the second pump chamber 101, the compressed gas / liquid mixed fluid is discharged from the second discharge port 91. Here, the gas-liquid mixed fluid discharged from the second discharge port 91 flows into the bubble generator 28, and microbubbles and nanobubbles are generated in the bubble generator 28.
At the same time, the compression / discharge process is performed in the first pump chamber 100i of the cylinder 79i. That is, the gas-liquid mixed fluid is compressed by the piston 77i and discharged from the first discharge port 82i. The gas-liquid mixed fluid discharged from the first discharge port 82 generates micro bubbles and nano bubbles in the bubble generating device 281i, and is sucked into the second pump chamber 101i that executes the expansion / suction process.

  According to this embodiment, discharge with little pulsation is ensured by the pressure feed pump 10i. Furthermore, when the second pump chambers 101 and 101i perform the compression / discharge process, the gas-liquid mixed fluid in the state in which microbubbles and nanobubbles have already been generated is compressed by the bubble generators 281 and 281i, and the contained micro Dissolution and miniaturization of bubbles including bubbles and nanobubbles are promoted. Further, the gas-liquid mixed fluid discharged from the second pump chambers 101 and 101i through the second discharge ports 91 and 90i by the compression / discharge process in the second pump chambers 101 and 101i is further micronized by the bubble generator 28. Since bubbles and nanobubbles are generated, microbubbles and nanobubbles are generated efficiently and reliably.

The above-described embodiment is merely an aspect of the present invention, and can be arbitrarily modified and applied within the scope of the present invention.
For example, in the embodiment described above, the number of sonic nozzles 48 in the gas flow rate adjustment unit 20 is “4”, but the number of sonic nozzles 48 is not limited to this, and is appropriate according to the expected flow rate realized by the system. A large number can be provided.

1, 1b, 1c, 1d, 1e, 1f, 1g, 1h, 1i Gas-liquid mixed pumping system 10, 10b, 10, 10d, 10e, 10f, 10g, 10h, 10i Pumping pump 11 Suction port 13 Discharge port 20 Gas flow rate Adjustment unit (gas mixing means)
28, 281, 281f, 281i Bubble generator 48, 481, 482, 483, 484 Sonic nozzle 49, 491, 492, 493, 494 Solenoid valve (open / close valve)
57 Compressor 70, 160 Piston shaft 71, 161 Shaft case 77, 77i, 166, 167 Piston 79, 79i, 168, 169 Cylinder 81, 81i First suction port 82, 82i First discharge port 90, 90i Second suction port 91, 92i Second discharge port 100, 100i First pump chamber 101, 101i Second pump chamber 171 Suction port 172 Discharge port 176, 177 Pump chamber

Claims (15)

A pump that pumps the gas-liquid mixed fluid;
Gas mixing means for mixing gas with liquid on the suction side of this pump,
The gas mixing means comprises a plurality of sonic nozzles arranged in parallel, the flow of any of the sonic nozzles is restricted, and the gas mixing amount can be controlled.   The gas mixing means includes an on / off valve corresponding to each sonic nozzle, shuts off any of the on / off valves, restricts the flow of the corresponding sonic nozzle, and controls the gas mixing amount. The gas-liquid mixed pressure feeding system according to 1.   3. The gas-liquid mixed pressure feeding system according to claim 2, wherein each of the on-off valves is shut off to stop gas mixing for a predetermined period after the driving of the pressure feeding pump is started.   The gas-liquid mixed pressure feeding system according to any one of claims 1 to 3, further comprising constant pressure applying means for supplying gas to the sonic nozzle at a constant pressure.   5. The gas-liquid mixed pressure feeding system according to claim 4, wherein the constant pressure applying means is a compressor provided upstream of the sonic nozzle. Gas supply means for supplying gas to the pressure pump is further provided,
6. The pump according to claim 1, wherein the pressure-feed pump compresses and discharges the gas-liquid mixed fluid after mixing the gas supplied from the gas supply unit with the sucked gas-liquid mixed fluid. Gas-liquid mixed pressure feeding system according to the above. The pressure pump is
The piston shaft is housed in the shaft case so that it can be driven back and forth.
A piston is fixed to one outer end of the piston shaft penetrating the shaft case,
The piston is accommodated in a cylinder connected to the shaft case,
A first pump chamber is formed on the surface side of the cylinder that faces the outside of the piston, and a first suction port and a first discharge port are provided in the first pump chamber, while a first pump chamber is formed on the surface side of the piston that faces the inside. 2 pump chambers are formed, and a second suction port and a second discharge port are provided in the second pump chamber,
The suction operation in the first pump chamber and the discharge operation in the second pump chamber, and the discharge operation in the first pump chamber and the suction operation in the second pump chamber are alternately performed according to the reciprocating drive of the piston. 4. The gas-liquid mixed pressure feeding system according to claim 1, wherein the gas-liquid mixed pressure feeding system is a pump. The gas-liquid suction pipe through which the gas-liquid mixed fluid sucked by the pressure pump flows is branched into two, and one pipe is connected to the first suction port and the other pipe is connected to the second suction port. And
The gas-liquid discharge pipe through which the gas-liquid mixed fluid discharged from the pressure pump flows is branched into two, and one pipe is connected to the first discharge port and the other pipe is connected to the second discharge port. 8. The gas-liquid mixed pressure feeding system according to claim 7, wherein   A gas-liquid suction pipe through which a gas-liquid mixed fluid sucked by the pump is circulated is connected to one of the first suction port and the second suction port, and the one suction port A corresponding discharge port and the other suction port are connected by a pipe, and a gas-liquid discharge pipe through which the gas-liquid mixed fluid discharged from the pressure pump is connected is connected to the discharge port corresponding to the other suction port. The gas-liquid mixed pressure feeding system according to claim 7,   The gas-liquid mixed pressure feeding system according to claim 9, wherein a bubble generating device is provided in a pipe connecting the discharge port corresponding to the one suction port and the other suction port. The piston shaft is fixed to the outer tip of the piston shaft so that the piston shaft does not protrude outward from the piston,
The gas / liquid inlet pipe is connected to the first inlet, the first outlet and the second inlet are connected, and the gas / liquid outlet is connected to the second outlet. The gas-liquid mixed pressure feeding system according to claim 9 or 10. Either one of the first pump chamber and the second pump chamber functions as a gas pump chamber that sucks and discharges gas, and the other pump chamber sucks gas-liquid mixed fluid. It functions as a pump chamber for the gas-liquid to be discharged,
The air discharged from the pump chamber functioning as the gas pump chamber is configured to be mixed with the gas-liquid mixed fluid sucked into the pump chamber functioning as the gas-liquid pump chamber. The gas-liquid mixed pressure feeding system described in 1. The piston is fixed to the outer tip of the piston shaft so that the piston shaft does not protrude outward from the piston,
13. The gas-liquid mixed pressure feeding system according to claim 12, wherein the second pump chamber functions as a gas pump chamber, and the first pump chamber functions as a gas-liquid pump chamber. The pressure pump is
The piston shaft is housed in the shaft case so that it can be driven back and forth.
The piston is fixed to each of both outer ends of the piston shaft that penetrates the shaft case,
Each of the pistons is housed in each of the cylinders connected to the shaft case;
In each of the cylinders, a first pump chamber is formed on the surface side facing the outside of the piston, and a first suction port and a first discharge port are provided in the first pump chamber. A second pump chamber is formed on the facing surface side, and a second suction port and a second discharge port are provided in the second pump chamber,
Depending on the reciprocating drive of the piston,
A suction operation in the first pump chamber and a discharge operation in the second pump chamber in one of the cylinders; a discharge operation in the first pump chamber and a suction operation in the second pump chamber in the other cylinder;
A discharge operation in the first pump chamber and a suction operation in the second pump chamber in one of the cylinders; a suction operation in the first pump chamber and a discharge operation in the second pump chamber in the other cylinder;
The gas-liquid mixed pressure feeding system according to any one of claims 1 to 3, wherein the pump performs alternately.   15. The gas-liquid mixed pressure feeding system according to claim 7, wherein the piston shaft is driven by a constant speed power transmission mechanism.

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