JP5514176B2 - Liquid mixing device - Google Patents

Description

  The present invention relates to a liquid mixing apparatus. More specifically, for example, the present invention relates to a liquid mixing apparatus that supplies a desired amount of different liquids to a flow path through which liquid flows.

  As a device similar to the liquid mixing device, a fertilizer applying device disclosed in Japanese Utility Model Publication No. 04-36582 is known. This fertilizer application supplies granular fertilizer from the opening formed in the pipe with respect to the paste fertilizer pumped in the pipe. A hopper for supplying granular fertilizer is attached to the opening. A gear-like rotor is attached to the lower end of the hopper. Due to the rotation of the rotor, the granular fertilizer that has entered the groove of the rotor is introduced into the pipe. In this way, a predetermined amount of granular fertilizer according to the rotational speed of the rotor is mixed with the paste fertilizer. The rotor is rotationally driven by a motor, and electric power is consumed for this rotational driving.

  Japanese Patent Application Laid-Open No. 09-266731 discloses a gardening sprinkler using a so-called jet pump (ejector). This sprinkler sprays water after mixing liquid fertilizer with water. This sprinkler sucks in liquid fertilizer using the negative pressure generated in the gap between the water supply nozzle and the diffuser, and mixes this liquid fertilizer into the water ejected from the nozzle.

  In the fertilizer application disclosed in the above Japanese Utility Model Publication No. 04-36582, it is conceivable that the paste fertilizer in the pipe flows back to the granular fertilizer side through the opening. That is, there is a possibility that the groove portion that has discharged the granular fertilizer into the pipe line due to the rotation of the rotor draws up the paste fertilizer in the pipe line and feeds it into the hopper.

  In the watering device disclosed in Japanese Patent Application Laid-Open No. 09-266731, the amount of liquid fertilizer suction varies due to a change in water supply pressure. Therefore, when the liquid fertilizer concentration is reduced, it is difficult to adjust to a constant concentration. Moreover, even if the cross-sectional area of the liquid fertilizer supply channel is adjusted, water may flow back to the liquid fertilizer supply side depending on the water pressure condition.

  Utility Model Registration No. 2540072 discloses a liquid agent mixing device using a so-called jet pump, as in the case of the sprinkler disclosed in Japanese Patent Application Laid-Open No. 09-266731. In this mixing apparatus, a flow rate adjusting valve is provided in the liquid supply path. Japanese Patent Application Laid-Open No. 08-156751 discloses a chemical solution diluting apparatus using an ejector. In this dilution apparatus, the chemical liquid sucked up by the chemical liquid suction ejector is mixed into the water pipe by the chemical liquid mixing ejector. The supply amount of the chemical solution is adjusted by adjusting the amount of air sent to the chemical solution suction ejector with a regulator. Regardless of the apparatus disclosed in any of the above publications, it is not easy to accurately adjust the liquid supply amount. This is because, depending on the ejector, it is difficult to accurately control the suction amount of the liquid agent.

No. 04-36582 Japanese Patent Application Laid-Open No. 09-266731 Utility Model Registration No.2540072 Japanese Patent Laid-Open No. 08-156751

  An object of the present invention is to provide a liquid mixing apparatus that can mix a liquid agent at a highly accurate mixing rate and can achieve energy saving.

  A liquid mixing apparatus according to the present invention includes a conduit portion through which a fluid flows, a liquid agent supply passage for supplying a liquid agent to the conduit portion, and a liquid agent supply mechanism disposed in the liquid agent supply passage. . The liquid supply mechanism is driven by a driving device that uses the flow of the fluid in the conduit.

  Preferably, the pipe section has a branch pipe section. Preferably, the liquid supply mechanism is driven by a driving device that uses the fluid flow in the branch pipe section.

  Preferably, the liquid agent supply mechanism has a measuring function for receiving a liquid agent from the liquid agent supply path and measuring a predetermined amount of the liquid agent, and a function of supplying the measured liquid agent to the pipe line portion.

  Preferably, the liquid supply mechanism includes a liquid supply member. Preferably, the liquid agent supply member is configured to be displaceable between a liquid agent receiving position for receiving the liquid agent from the liquid agent supply path and a liquid agent discharge position for discharging the liquid agent to the pipe line portion. Preferably, the liquid supply member has a measuring unit capable of storing a predetermined amount of liquid. Preferably, the metering unit communicates with the liquid agent supply path when the liquid agent supply member is at the liquid agent receiving position and does not communicate with the pipe line portion, and when the liquid agent supply member is at the liquid agent discharge position, It is configured not to communicate with the liquid supply path.

  Preferably, the drive device includes a rotational force generating unit capable of converting the fluid flow into a rotational force. Preferably, the liquid supply mechanism includes a rotating member that rotates coaxially with the rotational force generating unit. Preferably, the rotating member is provided with the measuring unit. Preferably, the rotation member is rotationally driven to be displaced to the liquid agent receiving position and the liquid agent discharge position.

  With the liquid mixing apparatus according to the present invention, a highly accurate mixing ratio and energy saving can be achieved.

FIG. 1 is a block diagram showing a first embodiment of a mixed liquid supply system according to the present invention. FIG. 2 is a perspective view showing an embodiment of a liquid mixing apparatus according to the present invention. 3 is a perspective view of a main body block used in the liquid mixing apparatus of FIG. FIG. 4 is a perspective view showing the internal structure of the main body h1 of the liquid mixing apparatus of FIG. FIG. 5 is a cross-sectional view taken along line F5-F5 of FIG. 6 is a cross-sectional view taken along line F6-F6 of FIG. FIG. 7 is an exploded perspective view of the liquid supply member. FIG. 8A is a cross-sectional view in which the main part of FIG. 6 is enlarged. FIG. 8A is a cross-sectional view at the liquid agent discharge position. FIG. 8B is a cross-sectional view taken along line F8B-F8B in FIG. FIG. 9A is an enlarged cross-sectional view of the main part of FIG. FIG. 9A is a cross-sectional view at the liquid agent receiving position. FIG. 9B is a cross-sectional view taken along line F9B-F9B in FIG. FIG. 10 is a diagram illustrating a relationship between the presser valve and the rotating member. FIG. 11 is a perspective view of the liquid mixing apparatus shown in FIG. In FIG. 11, the inside of the drive body housing portion is shown. 12 is a cross-sectional view taken along line F12-F12 of FIG. 13 is a cross-sectional view taken along line F13-F13 in FIG. FIG. 14 is a perspective view of the flow rate adjusting valve. FIG. 15A is a block diagram showing a second embodiment of the mixed liquid supply system according to the present invention, and FIG. 15B is a block showing a third embodiment of the mixed liquid supply system according to the present invention. FIG. 15 (c) is a block diagram showing a fourth embodiment of the mixed liquid supply system according to the present invention. FIG. 16A is a schematic diagram illustrating a liquid mixing apparatus according to another embodiment, and FIG. 16B is a schematic diagram illustrating a liquid mixing apparatus according to still another embodiment. FIG. 17 is a cross-sectional view showing a liquid mixing apparatus according to another embodiment.

  Hereinafter, the present invention will be described in detail based on preferred embodiments with appropriate reference to the drawings.

  FIG. 1 schematically shows a mixed liquid supply system 100 according to an embodiment of the present invention. This system 100 mixes liquids such as fertilizers, chemicals, detergents, sugar and other food additives, hydroponic liquids such as hydroponics, inks, nutrients, and the like with water. Supply to the field. The “water” may be water alone such as tap water, or may be mixed water in which various liquid agents are mixed in advance. The system 100 includes a water supply source 101, a water supply pipe 102 connected to the water supply source 101 for supplying a mixed liquid to a user 110, a liquid mixing apparatus 1 installed in the water supply pipe 102, and a liquid mixing apparatus for the water supply pipe 102. 1, a liquid agent concentration sensor 103 installed downstream in the water flow direction (hereinafter abbreviated), and a reflux pipe 104 connected to the upstream side of the liquid mixing apparatus 1 from the downstream side of the concentration sensor 103 of the water supply pipe 102. ing. A pump 105 is installed on the downstream side of the downstream connection point B of the return pipe 104 in the water supply pipe 102. A first on-off valve 106 is installed on the downstream side of the upstream connection point A of the reflux pipe 104 in the water supply pipe 102, and a second on-off valve 107 is installed on the circulating pipe 104.

  The liquid mixing device 1 is a device that mixes a desired amount of liquid agent with water flowing through the water supply pipe 102. The liquid mixing apparatus 1 is connected to a control device 108 that controls the operation of a flow rate adjustment valve VL1 (described later). The concentration sensor 103 includes a detection unit 103a that detects a liquid agent concentration of the liquid flowing in the water supply pipe 102, and a calculation display unit that displays a detection result by the detection unit 103a and transmits the concentration information to the control device 108. 103b. The concentration sensor 103 and the control device 108 are each connected to an AC power source 109. Although not shown, an AC or DC power supply is also connected to the on-off valves 105 and 106 as necessary. In FIG. 1, the power supply system is indicated by a solid line, and the signal system is indicated by a broken line. The on-off valves 106 and 107 may be electromagnetic on-off valves, motor-driven on-off valves, or hydraulic or pneumatic on-off valves.

  In this system 100, an optical refractometer is used as the concentration sensor 103. The photorefractometer calculates the liquid agent concentration of the liquid to be measured based on the degree of refraction of light generated at the interface between the equipped prism and the liquid to be measured. In the present invention, the concentration sensor 103 is not limited to a photorefractometer, and for example, a specific gravity meter, a conductivity meter, a pH meter, a viscometer, or other known measuring devices may be employed. An optical refractometer is preferable because highly accurate measurement is possible even when there are fluctuation factors such as a change in the liquid amount, the application target is wide, and the handling is easy. Since the refractive index varies depending on the temperature of the target liquid, it is preferable that the temperature is measured together with the refractive index of the target liquid, and the refractive index is corrected based on the measured temperature. For this reason, a sensor capable of measuring both refractive index and temperature is preferred. For example, PRM-100α and CM-780N manufactured by Atago Co., Ltd. can be employed. When the liquid to be applied is liquid fertilizer, a conductivity meter that can achieve both high accuracy and low cost is preferable. Since the conductivity increases as the temperature of the target liquid increases, it is preferable that the temperature is measured together with the conductivity of the target liquid, and the conductivity is corrected based on the measured temperature. Alternatively, the correction may be performed by setting a predetermined temperature correction rate, for example, a correction rate of 2% / 1 ° C. or the like in advance.

  The control device 108 transmits a command to increase / decrease the amount of liquid agent supplied per hour to the liquid mixing device 1 based on a comparison between a preset desired liquid agent concentration and concentration information from the concentration sensor 103. In the liquid mixing apparatus 1, the operation of a motor 6 that drives a flow rate adjusting valve VL1 described later is controlled by this command signal. As will be described later, it is not essential to connect the control device 108 to the liquid mixing device 1.

  In this system 100, when the concentration value detected by the concentration sensor 103 is lower than a preset concentration value, the control device 108 sends a valve closing instruction to the first opening / closing valve 106, and the second opening / closing valve 107. May send a valve opening instruction. As a result, while the detected concentration value does not reach the specified value, the supply of the mixed liquid to the user 110 is stopped, and the mixed liquid circulates through the water supply pipe 102 and the reflux pipe 104. When the detected concentration value reaches the specified value, the control device 108 sends a valve opening instruction to the first on-off valve 106, sends a valve closing instruction to the second on-off valve 107, and the mixed liquid is sent to the user 110. Supplied. The operation of the system 100 is an example. The control device 108 sends a valve opening instruction to both the first on-off valve 106 and the second on-off valve 107 and supplies it to the user 110 while circulating the liquid mixture in the reflux pipe 104, so that the detected concentration value is a specified value. It is also possible to send a valve closing instruction from the control device 108 to the second on-off valve 107 when the pressure reaches the value, and supply the mixed water to the user 110. Further, the flow rate can be adjusted by the control device 108 by using one or both of the first on-off valve 106 and the second on-off valve 107 as a valve capable of adjusting the flow rate.

  Note that incorporating the liquid mixing apparatus 1 into the system 100 is merely an example of the use of the liquid mixing apparatus 1. The liquid mixing device 1 may be used alone, for example. A system according to another embodiment will be described later.

  FIG. 2 is a perspective view of the liquid mixing apparatus 1. The liquid mixing device 1 includes a main body h1 and a drive body housing part g1. FIG. 3 is a perspective view of the main body block 2 constituting a part of the main body h1. FIG. 4 is a perspective view showing the internal structure of the main body h1. 5 is a cross-sectional view taken along line F5-F5 in FIG. 4, and FIG. 6 is a cross-sectional view taken along line F6-F6 in FIG.

  The main body h1 includes a main body block 2, a columnar liquid agent supply member 3 incorporated in the main body block 2, a liquid agent container 4 attached to the main body block 2, and a cylindrical pressure valve incorporated in the main body block 2. 5 and a motor 6 for driving a flow rate adjusting valve VL1 (described later). In FIG. 4, the motor 6 and the adjustment valve hole 10 are not shown. The main body h1 has a liquid supply mechanism h2.

  The drive body accommodating part g1 has the branch pipe part 7b (after-mentioned), case ks1, and the rotational force generation part g2. A packing Pk is provided on the boundary surface between the case ks1 and the main body h1 (see FIG. 6). This packing Pk improves water tightness.

  As shown in FIG. 3, the main body block 2 has one adjustment valve hole 10, two first holes 11, and two second holes 12. The main body block 2 has two openings 7h. These openings 7h are located in the middle of the branch pipe portion 7b (described later). Furthermore, the main body block 2 has a protruding pipe P1 on the inlet side and a protruding pipe P2 on the outlet side. The main body block 2 is the body of the main body h1. A flow rate adjusting valve VL1 (described later) is inserted into one adjusting valve hole 10.

  The liquid agent container 4 is attached to the opening of the first hole 11. The drive motor 6 is attached to the outside of the adjustment valve hole 10. As the drive motor 6, a stepping motor, a servo motor, a DC motor or the like can be employed. However, a stepping motor that can control the rotation angle, is inexpensive, has relatively high accuracy, and can obtain a necessary torque is preferable.

  Note that the drive motor 6 may not be provided. Embodiments that do not have the drive motor 6 will be described later.

  The concentration sensor 103 and the control device 108 are preferably attached in order to accurately set the liquid agent concentration and to be able to easily change the liquid agent concentration.

  The main body block 2 and the case ks1 are formed with a duct portion 7 through which a liquid such as water flows. The pipeline part 7 has the main pipeline part 7a and the branch pipeline part 7b. The main pipeline portion 7 a is formed in the main body block 2. The main pipeline 7a is a single pipe that extends straight. The branch pipeline part 7b branches off from the main pipeline part 7a and returns to the main pipeline part 7a. The branch line portion 7b will be described later.

  In FIG. 5, the left end of the main pipeline 7 a is the inlet 8 and the right end is the outlet 9. In the present invention, either the left or right end may be the inlet 8 or the outlet 9. The main body block 2 is formed with two cylindrical first holes 11 that communicate perpendicularly to the main pipeline 7a. The first hole 11 extends vertically downward from the upper surface of the main body block 2 and reaches the main pipeline portion 7a. The central axis of the first hole 11 substantially coincides with the central axis of the main pipe line portion 7a. Each first hole 11 accommodates the presser valve 5.

  The main body block 2 is formed with a cylindrical second hole 12 that communicates perpendicularly to each first hole 11. The central axis of the second hole 12 intersects the central axis of the first hole 11. The second hole 12 extends horizontally from the side surface of the main body block 2 and reaches the first hole 11. The second hole 12 extends in a direction perpendicular to the main pipeline portion 7a and slightly above the main pipeline portion 7a. Further, the second hole 12 communicates with the main pipeline portion 7a. Both the second hole 12 and the first hole 11 are bottomed. The liquid supply member 3 is accommodated in each second hole 12 so as to be rotatable about its own axis. An output shaft z <b> 1 of a water turbine WT installed at the opening end of the second hole 12 is connected to the end of the liquid supply member 3. The liquid supply member 3 is rotationally driven around its own axis by the water wheel WT. The rotating member 21 of the liquid supply member 3 rotates coaxially with the water wheel WT. The water turbine WT is disposed in the case ks1 of the drive body housing part g1 (see FIG. 6). This water wheel WT is a rotational force generation part g2. The water wheel WT is a drive device that uses a fluid flow. Details of the water turbine WT will be described later.

  In this liquid mixing apparatus 1, one liquid agent supply member 3, one liquid agent container 4, and one press valve 5 constitute one liquid agent mixing unit for the main pipe section 7 a. In the main body block 2, two liquid agent mixing units are constructed in series along one main pipe line portion 7a. In the present invention, only one liquid agent mixing unit may be constructed for one main body block 2, or three or more liquid agent mixing units may be constructed. By constructing a plurality of liquid agent mixing units in one main pipe line portion 7a, it is possible to supply while adjusting the mixing amounts of a plurality of types of liquid agents. Further, a plurality of main conduit portions 7a may be formed in one main body block, and a liquid agent mixing unit may be constructed in each main conduit portion 7a. Such a member (liquid supply member 3) that is rotationally driven by the drive device can precisely adjust the liquid supply amount according to the number of rotations, and is more durable than a device that supplies the liquid agent by repeated back and forth movement, etc. And excellent low-vibration properties, and can further reduce the cost of the apparatus. Therefore, it is preferable to employ such a rotating member as the liquid supply function.

  As shown in FIGS. 5 and 6, the presser valve 5 includes a large-diameter portion 14 and a small-diameter portion 15 via a step portion 13. A through hole 16 is formed along the central axis of the presser valve 5. The through hole 16 constitutes a liquid agent supply path 17 through which the liquid agent passes. A cylindrical liquid container stopper 18 having a flange portion 18 f is attached to the opening of the first hole 11. The flange portion 18f of the liquid agent container stopper 18 is detachably attached to the outer surface of the main body block 2 via a gasket (not shown) and a bolt (not shown). On the inner diameter side of the upper end of the liquid container stopper 18, the mouth portion of the liquid container 4 is attached in a watertight and detachable manner. A small diameter portion 15 of the presser valve 5 is fitted via an O-ring 19 on the inner diameter side of the lower end of the liquid agent container stopper 18. The holding valve 5 can move up and down with respect to the liquid container stopper 18. The liquid container stopper 18 is preferably attached to improve the detachability of the liquid container 4 or to ensure the mounting.

  A first coil spring 20 is mounted in a compressed state in a space between the lower surface of the liquid container stopper 18 and the stepped portion 13 of the pressing valve 5 in the first hole 11. The first coil spring 20 is attached to the outer periphery of the small diameter portion 15 of the presser valve 5. By the first coil spring 20, the lower end surface 5 a of the presser valve 5 is elastically pressed against the outer peripheral surface of a rotating member 21 (described later). Therefore, the liquid supply path 17 extends from the mouth portion of the liquid container 4 to the outer peripheral surface of the rotating member 21 through the through hole 16. The liquid agent fills the outer peripheral surface of the rotating member 21.

  The lower end surface 5 a of the presser valve 5 is formed in a partially cylindrical concave shape that is complementary to the outer peripheral surface of the rotating member 21. The outer peripheral surface of the rotating member 21 and the concave portion of the lower end surface 5a of the pressing valve 5 have a cylindrical surface shape having the same curvature. With this shape, the lower end surface 5a of the presser valve 5 is in sliding contact with the outer peripheral surface of the rotating member 21 that rotates about its own axis. The lower end surface 5 a of the presser valve 5 constitutes the sliding contact support surface of the rotating member 21. The presser valve 5 can be closed by sliding contact with the outer peripheral surface of the rotating member 21. The outer diameter of the large-diameter portion 14 of the presser valve 5 is larger than the outer diameter of the rotating member 21. Details of the opening / closing operation of the pressure valve 5 will be described later.

  FIG. 7 is an exploded perspective view of the liquid supply member 3. FIG. 8A is an enlarged cross-sectional view showing the main part of FIG. 6, and FIG. 8B is a cross-sectional view taken along line F8B-F8B in FIG. 8A. FIGS. 8A and 8B are cross-sectional views when the liquid supply member 3 is in the liquid discharge position. FIG. 9A is an enlarged cross-sectional view showing the main part of FIG. 6, and FIG. 9B is a cross-sectional view taken along line F9B-F9B in FIG. 9A. 9A and 9B are cross-sectional views when the liquid supply member 3 is in the liquid receiving position.

  In the present embodiment, the liquid supply member 3 constitutes a liquid supply mechanism h2. The liquid supply member 3 includes the rotating member 21 and the metering portion forming member 22. The rotating member 21 is accommodated in the second hole 12 so as to be rotatable about its own axis. The rotating member 21 has a large-diameter supported portion 33 at a connection side end portion (referred to as a base end portion) with the output shaft z1. The rotating member 21 has a small-diameter supported portion 34 at the tip. The vicinity 35 of the opening of the second hole 12 has an inner diameter that is substantially the same as the outer diameter of the large-diameter supported portion 33. The rear end vicinity 36 of the second hole 12 has an inner diameter substantially the same as the outer diameter of the small-diameter supported portion 34. The rotation member 21 is rotatably supported by the vicinity of the opening 35 and the vicinity of the back end 36 of the second hole 12 and the lower end surface (sliding contact support surface) 10 of the pressing valve 5. O-rings 37 are mounted in the vicinity of both ends in the longitudinal direction (axial direction) of the rotating member 21. Therefore, the liquid is prevented from advancing to the drive body housing part g1 side.

  A housing recess 23 is formed in the rotating member 21. The housing recess 23 extends in the axial direction of the rotating member 21. The measuring portion forming member 22 is accommodated in the accommodating recess 23. The measuring portion forming member 22 and the receiving recess 23 and small and large diameter through holes 30 and 31 described later constitute a measuring portion. The opening portion of the accommodation recess 23 is closed by the lid member 24. The lid member 24 is attached to the opening portion, and may be fixed to the opening portion with an adhesive, a screw, or the like. The measuring portion forming member 22 is provided between the substrate 25, a pair of protrusions 26 protruding from the upper surface of the substrate 25, and a pair of protrusions 26 on the substrate 25. And a convex portion 27. The interval between the protrusions 26 is made smaller than the outer diameter of the large diameter portion 14 of the presser valve 5 in order to ensure the function of the protrusions 26 (pressed by the lower end surface 5a of the presser valve 5). The pair of protrusions 26 and the measurement convex portions 27 are aligned in a straight line. This detail will be described later in the description of the operation of the liquid mixing apparatus 1. A second coil spring 28 is mounted in a compressed state between the back surface of the substrate 25 and the lid member 24. A circular recess 29 serving as a spring seat to which the end of the second coil spring 28 is fitted is formed on the opposing surfaces of the lid member 24 and the substrate 25.

  As shown in FIG. 7, the height of the measurement convex portion 27 is slightly lower than the height of the protrusion 26. Three through holes 30 and 31 are formed at the bottom of the housing recess 23. The measuring convex portion 27 is inserted through the middle large-diameter through hole 31. The pair of protrusions 26 are inserted into a pair of small diameter through holes 30 formed on the left and right sides of the large diameter through hole 31. The three through holes 30, 31 are aligned in a straight line.

[Advance position: Liquid discharge position]
As shown in FIGS. 8A and 8B, the measuring portion forming member 22 is accommodated in the accommodating recess 23, and the upper surface of the substrate 25 is accommodated in the accommodating recess by the restoring force of the second coil spring 28. When coming into contact with the bottom surface of the place 23, the ends of the pair of protrusions 26 protrude outward from the opening 30 a of the small diameter through hole 30. In other words, the tips of the pair of protrusions 26 are elastically protruded outward by the second coil spring 28. That is, the measuring part forming member 22 is in the advanced position. At this time, the tip of the measurement convex portion 27 reaches the opening 31a (also referred to as a liquid agent receiving opening) of the large-diameter through hole 31. However, the tip of the measuring convex portion 27 does not protrude outward from the opening 31 a and coincides with the outer peripheral surface of the rotating member 21. The protrusion 26 and the measurement convex part 27 are formed at such a height (see also FIG. 7). The shape of the tip surface of the measuring convex portion 27 is a partial cylindrical surface having the same curvature as the outer peripheral surface of the rotating member 21. Therefore, when the measuring portion forming member 22 is in the advanced position, the portion of the large-diameter through hole 31 on the outer peripheral surface of the rotating member 21 is a cylindrical outer surface without unevenness. In the present application, this position is referred to as a liquid agent discharge position of the liquid agent supply member 3.

[Backward position: Liquid receiving position]
On the other hand, as shown in FIGS. 9 (a) and 9 (b), the distal ends of the pair of protrusions 26 projecting outwardly penetrate the small diameter against the restoring force of the second coil spring 28 by an external force. When pushed back inward of the hole 30 and coincides with the outer peripheral surface of the rotating member 21, the tip of the metering convex portion 27 passes through the outer peripheral surface of the rotating member 21, that is, the large-diameter through hole 31 from the liquid agent receiving opening 31a. Move backwards. That is, the measuring part forming member 22 is in the retracted position. Accordingly, a space 32 is formed on the outer side in the large-diameter through hole 31 (see FIG. 9A). This space 32 is a liquid agent accommodation space described later. The liquid agent accommodation space 32 is defined by the large-diameter through hole 31 and the distal end surface of the measurement convex portion 27. The liquid agent that has passed through the liquid agent supply path 17 from the liquid agent container 4 is received in the liquid agent storage space 32 through the liquid agent receiving opening 31a. This position is a liquid agent receiving position of the liquid agent supply member 3.

  9A and 9B are the retracted positions of the measuring portion forming member 22 as described above. The backward position of k is the medicine receiving position of the liquid supply member 3. On the other hand, the liquid agent accommodation space 32 has disappeared at the advancement position (FIGS. 8A and 8B) of the metering portion forming member 22 described above. This advance position is the liquid agent discharge position of the liquid supply member 3.

  A cross-sectional area perpendicular to the central axis of the through-hole 16 of the presser valve 5 is S1, and a cross-sectional area perpendicular to the central axis of the large-diameter through-hole 31 is S2 (see FIG. 9B). If the value of S2 / S1 is too large, there is a possibility that the introduction of the liquid agent into the liquid agent storage space 32 may be incomplete when the viscosity of the liquid agent is high or when the amount of liquid agent mixed per hour is large. If the value of S2 / S1 is too small, the liquid agent pool in the through-hole 16 becomes large, which may lead to an increase in size and cost of the device. Moreover, the volume V of the liquid agent accommodation space 32 becomes small, and there is a possibility that the upper limit of the liquid agent introduction amount per time is excessively limited. Therefore, the value of S2 / S1 is preferably 0.3 or more and 3.0 or less. The lower limit is more preferably 0.5 or more, and more preferably 0.7 or more. The upper limit is more preferably 2.0 or less, further preferably 1.5 or less, and particularly preferably 0.95 or less. In the present embodiment, the value of S2 / S1 is 0.9.

  If the volume V of the liquid agent containing space 32 is too small, the upper limit of the liquid agent introduction amount per hour may be excessively limited. Moreover, when too small, when the viscosity of a liquid agent is high etc., there exists a possibility that the introduction of the liquid agent to the liquid agent accommodation space 32 may become incomplete. If this volume V is too large, the concentration change per time of the mixed solution becomes large, and fine concentration setting may be difficult. Therefore, the volume V is preferably 0.05 cc or more and 1.00 cc or less. The lower limit is more preferably 0.10 cc or more, and further preferably 0.15 cc or more. Further, the upper limit is more preferably 0.50 cc or less, further preferably 0.30 cc or less, and particularly preferably 0.20 cc or less. In this embodiment, the volume V is 0.15 cc.

  If the depth T of the liquid agent accommodation space 32 shown in FIG. 9B is too small, the member may be caught in the liquid agent accommodation space 32 when the apparatus 1 is assembled or operated. Conversely, if the depth T is too large, the introduction of the liquid agent into the liquid agent storage space 32 may be incomplete when the viscosity of the liquid agent is high. Therefore, the value of the depth T is preferably 0.2 mm or greater and 4.0 mm or less. The lower limit is more preferably 0.5 mm or more, and particularly preferably 0.8 mm or more. The upper limit is more preferably 3.0 mm or less, and particularly preferably 2.0 mm or less. In this embodiment, the depth T is 1.5 mm.

  The liquid mixing apparatus 1 can be expected to perform highly accurate mixing even at a low mixing rate. Particularly accurate mixing control can be expected when the volume ratio of the mixed liquid to the unit volume of the mixed liquid after mixing is in the range of 0.0001 to 0.05.

  The operation of the liquid mixing apparatus 1 configured as described above will be described below with reference to FIGS. 8 (a), 8 (b), 9 (a), and 9 (b). Water flows through the main pipe portion 7a. The liquid agent in the liquid agent container 4 is filled in the liquid agent supply path 17 and reaches the outer peripheral surface of the rotating member 21 of the liquid agent supply member 3. The liquid supply member 3 is rotated around its own axis by the water wheel WT (rotational force generator g2). The lower end surface 5 a of the pressing valve 5 is in sliding contact with the outer peripheral surface of the rotating member 21. By this sliding contact, a liquid seal between the main pipe line portion 7a and the liquid supply path 17 is realized.

  As shown in FIG. 8A and FIG. 8B, when the liquid supply member 3 rotates to reach the liquid discharge position, the small diameter and large diameter through holes 30 and 31 of the rotating member 21 are opened. It faces the space formed by the main pipe line portion 7a and the first hole 11. Therefore, the tip of the protrusion 26 is not pushed. The protrusion 26 protrudes toward the spaces 7 and 11. The tip of the measurement convex portion 27 coincides with the outer peripheral surface of the rotating member 21, and the liquid agent accommodation space 32 disappears.

  When the liquid supply member 3 rotates and moves to the liquid reception position (FIGS. 9A and 9B), the tip of the protrusion 26 protruding from the opening of the small diameter through hole 30 is below the press valve 5. It is pushed inward of the small diameter through hole 30 by the end face 5a. As a result, the measuring portion forming member 22 is retracted inward of the housing recess 23. The measuring convex portion 27 also moves backward in the large diameter through hole 31. As a result, a liquid agent receiving opening 31a and a liquid agent storage space 32 are formed. While the measuring portion forming member 22 is in this state, the liquid supply member 3 further rotates to reach the liquid reception position shown in FIGS. 9A and 9B. At this liquid agent receiving position, the liquid agent storage space 32 faces the through hole 16 of the presser valve 5 that is the liquid agent supply path 17. The liquid agent flows into the liquid agent storage space 32 through the liquid agent supply path 17 and the liquid agent receiving opening 31a.

  When the liquid supply member 3 rotates and moves toward the liquid discharge position (FIGS. 8A and 8B), the opening of the small-diameter through hole 30 closed by the lower end surface 5a of the presser valve 5 is opened. . Thereby, the tip of the protrusion 26 protrudes toward the spaces 7 and 11. At the same time, the tip of the measurement convex portion 27 advances to the outer peripheral surface of the rotating member 21. Thereby, the liquid agent storage space 32 disappears, and the liquid agent in the liquid agent storage space 32 is discharged into the main conduit portion 7a (FIGS. 8A and 8B). When the liquid supply member 3 rotates once, the liquid agent having the same volume as the volume of the liquid agent storage space 32 is mixed with the water flowing in the main conduit portion 7a. By adjusting the rotation speed of the water wheel WT, the rotation speed of the liquid supply member 3 can be adjusted, and the liquid supply amount per time can be controlled.

  When the liquid supply member 3 rotates and moves from the liquid discharge position (FIGS. 8A and 8B) to the liquid reception position (FIGS. 9A and 9B), the inside of the main pipe section 7a The water does not flow back to the liquid supply path 17. That is, the water in the main pipe line portion 7a is prevented from entering the liquid agent storage space 32 when moving from the liquid agent discharge position to the liquid agent receiving position. This is due to, for example, the following configuration.

  FIG. 10 is a front view showing the positional relationship between the lower end of the presser valve 5 and the rotating member 21. The outer peripheral shape of the lower end surface of the presser valve 5 that is in sliding contact with the outer peripheral surface of the rotating member 21 can be determined as shown in FIG. Consider a situation in which the rotating member 21 rotates in the direction of the arrow in FIG. 10 and the liquid supply member 3 is moving from the liquid discharge position to the liquid reception position. In this situation, the liquid agent receiving opening 31 a of the large-diameter through hole 31 is first closed by the lower end surface of the presser valve 5, and then the opening of the small-diameter through hole 30 can sink under the lower end surface of the presser valve 5. It is. By making the lower end surface of the presser valve 5 into such a shape, after the liquid agent receiving opening 31a is closed, the measuring convex portion 27 is retracted to form the liquid agent containing space 32. As a result, when the liquid supply member 3 moves from the liquid discharge position to the liquid reception position, water in the main pipe line portion 7a is prevented from entering the liquid storage space 32. It is possible to prevent the water in the main pipe part 7 a from flowing back to the liquid supply path 17.

  In the present embodiment, the protrusions 26 and the measurement convex portions 27 are aligned in a straight line, and the small diameter through hole 30 and the large diameter through hole 31 are aligned in a straight line. However, the arrangement of the pair of protrusions 26 and the metering protrusions 27 and the arrangement of the small diameter through holes 30 and the large diameter through holes 31 have been slightly changed in order to more reliably prevent the water from flowing back. Also good. In FIG. 10, only the large-diameter through hole 31 may be changed to a position preceding the rotation direction (a slightly upper position in FIG. 10). The formation position of the measurement convex portion 27 is slightly changed in the vertical direction (upward in the figure) from the position on the virtual straight line connecting the pair of protrusions 26 so as to coincide with the changed position of the large-diameter through hole 31. Is done.

  Since the holding valve 5, the rotating member 21, and the measuring portion forming member 22 are in contact with each other and slidably contacted with each other, a material having wear resistance suitable for such use conditions is selected. From the viewpoint of wear resistance, it is particularly desirable that the presser valve 5 and the rotating member 21 are made of materials having different hardnesses. These members 5, 21, and 22 can be formed from polypropylene (PP), ABS resin, polyacetal (POM), polyphenylene sulfide (PPS), or the like by injection molding, injection compression molding, or the like. In particular, the rotating member 21 is preferably made of ABS resin because dimensional accuracy is required. The presser valve 5 is preferably made of polyacetal because lubricity is required. As the main body block 2, a synthetic resin having a strength that can sufficiently withstand the water pressure used can be selected.

  FIG. 11 is a perspective view of the liquid mixing apparatus 1. In FIG. 11, a driving body accommodating portion g <b> 1 arranged inside the liquid mixing apparatus 1 is shown. 12 is a cross-sectional view taken along line F12-F12 of FIG. 13 is a partial cross-sectional perspective view including a cross section taken along line F13-F13 in FIG. In FIG. 11 to FIG. 13, the motor 6 is not shown.

  The drive body accommodating part g1 has the branch pipe part 7b, the two water turbines WT, and the space Vx for arrange | positioning these water turbines WT. The pipe line part 7 has the 1st branch D1 and the 2nd branch D2. The branch pipeline part 7b is a pipeline from the first branch D1 to the second branch D2. The inlet of the branch pipe part 7b is the first branch D1. The outlet of the branch pipe part 7b is the second branch D2.

  The branch pipe part 7b has an upstream part R1, an intermediate part R2, and a downstream part R3. The upstream portion R1 is a portion from the first branch D1 to the first opening 7h (7h1). The intermediate portion R2 is a portion from the first 7h (7h1) to the second opening 7h (7h2). The downstream portion R3 is a portion from the second opening 7h (7h2) to the second branch D2.

  The upstream portion R1 is provided in the main body block 2 of the main body portion h1. The intermediate portion R2 is provided in the drive body housing portion g1. The downstream portion R3 is provided in the main body block 2 of the main body portion h1. The upstream portion R1 is a cylindrical (straight) hole, and the downstream portion R3 is also a cylindrical (straight) hole. The upstream portion R1 and the downstream portion R3 that are not bent can facilitate the formation of the main body block 2.

  The water turbine WT has an axis z1, a center part c1, and a plurality of wing parts b1. The plurality of wing parts b1 are arranged at equal intervals in the circumferential direction of the water turbine WT. One wing part b1 may be used.

  The shaft z1 is supported by two shaft support portions As. In the present embodiment, one end of the axis z1 is fitted in a hole provided in the case ks1. From the viewpoint of reducing the rotational resistance of the water turbine WT, a bearing member or a bearing may be provided on these shaft support portions As. As this bearing member, a member having low sliding resistance is preferable. Examples of the material of the bearing member include resins such as Teflon (registered trademark) and POM (polyacetal), metal bushes, and oil-impregnated porous bodies. Examples of the bearing include a rolling bearing, a sliding bearing, and a fluid bearing.

  As shown in FIG. 6, the case ks <b> 1 and the axis z <b> 1 can be in contact with each other and slidable. Therefore, a material having wear resistance suitable for such use conditions is selected. The axis z1 and the case ks1 are preferably made of materials having different hardnesses. These members z1 and ks1 can be formed from polypropylene (PP), ABS resin, polyacetal (POM), polyphenylene sulfide (PPS), or the like by injection molding, injection compression molding, or the like. The water turbine WT can also be formed from polypropylene (PP), ABS resin, polyacetal (POM), polyphenylene sulfide (PPS) or the like by injection molding, injection compression molding, or the like. The water wheel WT and the shaft z1 are preferably formed of ABS resin because dimensional accuracy is required.

  The water turbine WT is rotated by the liquid flowing through the branch pipe portion 7b. The axis z1 is rotated by the rotation of the water wheel WT. The rotation member 21 of the liquid supply member 3 is rotated by the rotation of the axis z1. The water turbine WT converts the liquid flow into a rotational force. The water wheel WT is a drive device that uses the flow of liquid.

  The intermediate part R2 of the branch pipe part 7b and the main pipe part 7a extend in parallel. In the main pipe line portion 7a, the liquid agent supply member 3 (liquid agent supply mechanism) described above is provided between the first branch D1 and the second branch D2. The rotation axis of the rotation member 21 and the rotation axis of the axis z1 are common. In the present embodiment, the axis z1 of the water wheel WT directly drives the rotating member 21. Therefore, a member for transmitting the rotation of the water wheel WT to the rotating member 21 may be unnecessary. This configuration can reduce the number of parts and cost. This configuration can contribute to downsizing of the liquid mixing apparatus 1. The rotation of the water wheel WT may be transmitted to the rotation member 21 by a rotation transmission mechanism. Examples of the rotation transmission mechanism include gears and chains.

  Due to the presence of the space formed by the branch pipe portion 7b and the space Vx, the water turbine WT can rotate smoothly. During the rotation of the water wheel WT, only the liquid touches the wing part b1.

  The downstream portion R3 has a bottom surface bf1 (see FIGS. 6 and 12). The cross-sectional view in FIG. 6 is a cross-section cs1 including the wing part b1 and the central axis of the axis z1. The wing part b1 in the cross section cs1 is along the vertical direction. In the cross section cs1, the distance between the tip of the wing part b1 and the bottom surface bf1 is the closest distance G1 (see FIG. 6). This closest approach distance G1 is greater than zero. That is, during rotation of the water wheel WT, the wing b1 does not contact the bottom surface bf1.

  The bottom surface bf1 is a flat surface. In the cross section cs1, the contour line L1 at the tip of the wing part b1 is parallel to the cross sectional line of the bottom surface bf1 (see FIG. 6). This configuration can efficiently rotate the water wheel WT with a small flow rate.

  From the viewpoint of avoiding contact between the wing b1 and the bottom surface bf1 and relaxing the dimensional accuracy, the closest approach distance G1 is preferably 0.1 mm or more, more preferably 0.3 mm or more, and further preferably 0.4 mm or more. From the viewpoint of rotating the water turbine WT even when the flow rate in the branch pipe portion 7b is small, the closest approach distance G1 is preferably 3.0 mm or less, more preferably 2.0 mm or less, and even more preferably 1.0 mm or less.

  In FIG. 6, what is indicated by a double arrow G2 is a gap distance between the side surface of the water turbine WT and the branch pipe portion 7b (intermediate portion R2). From the viewpoint of avoiding contact between the inner surface of the branch pipe portion 7b and the wing portion b1 and relaxing the dimensional accuracy, the gap distance G2 is preferably 0.1 mm or more, more preferably 0.3 mm or more, and 0.4 mm or more. Is more preferable. From the viewpoint of rotating the water turbine WT even when the flow rate in the branch pipe portion 7b is small, the gap distance G2 is preferably 3.0 mm or less, more preferably 2.0 mm or less, and further preferably 1.0 mm or less.

  The liquid mixing device 1 has a flow rate adjustment valve VL1. The flow rate adjusting valve VL1 is provided in the branch pipe portion 7b. The flow rate adjustment valve VL1 is provided in the upstream portion R1 of the branch pipe portion 7b. The flow rate adjustment valve VL1 is located upstream of all the water turbines WT.

  FIG. 14 is a perspective view of the flow rate adjustment valve VL1. The flow rate adjustment valve VL1 has a head portion HE1 and a shaft portion AX1. The head portion HE1 has a flange 40 and a rotation engagement portion 42. The shaft portion AX1 has a flow path hole 44. The flow path hole 44 penetrates the shaft portion AX1. The shaft portion AX1 has a cylindrical shape.

  The adjusting valve hole 10 has an intersecting portion 10a that intersects the branch conduit portion 7b (upstream portion R1) (see FIG. 13). The inner diameter of the intersecting portion 10a is substantially equal to the outer shape of the shaft portion AX1. A shaft portion AX1 is fitted to the intersecting portion 10a. The adjustment valve hole 10 is rotatably supported by the contact between the intersecting portion 10a and the shaft portion AX1. The center of this rotation is the central axis of the adjustment valve hole 10.

  As shown in FIG. 13, an O-ring 46 is provided between the flange 40 and the main body block 2. The O-ring 46 prevents liquid leakage from the adjustment valve hole 10.

  The rotation engaging part 42 is supported by the holding body 48 (see FIG. 13). The holding body 48 is a plate having a through hole. The inner diameter of the through hole of the holding body 48 is substantially the same as the outer diameter of the rotation engaging portion 42. The rotation engaging part 42 is supported rotatably by the contact with the through hole. Moreover, the holding body 48 can suppress liquid leakage from the gap between the adjustment valve hole 10 and the flow rate adjustment valve VL1.

  The rotation engaging part 42 has a groove 42a. The groove 42a can be an engaging portion for rotating the flow rate adjustment valve VL1. For example, the flow rate adjusting valve VL1 can be rotated by engaging a minus driver with the groove 42a.

  The form of the rotation engaging part 42 in the present embodiment is suitable when the flow rate adjustment valve VL1 is manually rotated. In this case, the motor 6 described above may be unnecessary. On the other hand, when the flow control valve VL1 is rotated by the motor 6, the tip of the shaft of the motor 6 can be shaped to engage with the groove 42a. Further, as another mechanism for transmitting the rotation of the motor 6 to the flow rate adjustment valve VL1, for example, a gear mechanism can be cited.

  FIG. 13 shows a state in which the center axis of the flow path hole 44 is parallel to the center line of the upstream portion R1. In this state, the flow rate in the flow rate adjustment valve VL1 is maximum. When the flow regulating valve VL1 is rotated, the center axis of the flow path hole 44 is inclined with respect to the center line of the upstream portion R1. The flow rate passing through the flow path hole 44 can be adjusted by the inclination angle.

  In the present embodiment, the mixing amount in the liquid supply member 3 can be adjusted by the rotational speed of the water wheel WT. The rotation speed of the water turbine WT can be adjusted by the specification of the water turbine WT in addition to the flow rate of the second flow f2.

  The form of the water wheel WT and the wing part b1 is not limited. An angle adjustment mechanism that can adjust the angle of the wing b1 with respect to the water flow direction may be provided. In addition, an adjustment mechanism may be provided that adjusts the area of the portion of the wing portion b1 where the water flow hits. These adjustment mechanisms increase the degree of freedom for adjusting the rotational speed of the water turbine WT.

[Liquid flow]
The liquid flows from the inlet 8 into the pipe line portion 7 and reaches the first branch D1. The first branch D1 is divided into a first flow f1 flowing through the main pipeline 7a and a second flow f2 flowing through the branch pipeline 7b (see FIGS. 12 and 13). The first flow f1 and the second flow f2 merge at the second branch D2. A third flow f3 is obtained by this merging (see FIG. 13). This third flow f3 is discharged from the outlet 9. The second flow f2 hits the wing part b1. The rotation of the water wheel WT is obtained by the second flow f2.

  In the liquid mixing device 1, no electric power is required to rotate the rotating member 21. The rotating member 21 is rotated by the flow of the liquid. In the liquid mixing apparatus 1, power consumption is suppressed. The liquid mixing apparatus 1 can contribute to energy saving. Further, since the rotational force is generated using the liquid itself to be mixed, it is not necessary to separately introduce a liquid flow for hydraulic power. Therefore, energy saving and simplification of the structure and water saving can be realized.

  The flow rate ratio between the first flow f1 and the second flow f2 can be adjusted by the flow rate adjustment valve VL1. The rotation speed of the water turbine WT can be adjusted by adjusting the flow rate of the second flow f2. The amount of mixing in the liquid supply member 3 can be adjusted by adjusting the rotational speed.

  An example of a system 100 having a liquid mixing device of the present invention is shown in FIG. In the following, another example of a system using the liquid mixing apparatus of the present invention will be described.

  FIG. 15A is a block diagram showing a schematic configuration of a mixed liquid supply system 200 using the liquid mixing apparatus 1. FIG. 15B is a block diagram showing a schematic configuration of a mixed liquid supply system 300 using the liquid mixing apparatus 50. FIG. 15C is a block diagram showing a schematic configuration of a mixed liquid supply system 400 using the liquid mixing device 60. As will be described later, these liquid mixing devices 50 and 60 are different from the liquid mixing device 1.

  A system 200 shown in FIG. 15A includes the liquid mixing device 1 and the liquid agent concentration sensor 103 (shown by an ellipse) described above. From the inlet 8 to the outlet 9 is the liquid mixing device 1. In FIG. 15A, the liquid supply mechanism h2 of the liquid mixing apparatus 1 is shown as a square, and the rotational force generating part g2 of the liquid mixing apparatus 1 is shown as a circle. The configuration of the sensor 103 is as described above. The sensor 103 controls the flow rate adjustment valve VL1 via the control device 108 (not shown in FIG. 15A). The sensor 103 is located on the downstream side of the second branch D2. The water wheel WT of the rotational force generating part g2 directly drives the rotating member 21 of the liquid supply mechanism h2. In the liquid mixing apparatus 1, a liquid supply mechanism is provided in the main pipe section 7a, and a driving device using a liquid flow is provided in the branch pipe section 7b. The liquid supply mechanism is driven by a driving device (rotational force generator g2) that uses the flow of fluid in the branch pipe section 7b.

  In the system 200, the liquid flowing from the inlet 8 is divided into the first flow f1 and the second flow f2 in the first branch D1. The liquid supply mechanism h2 mixes the liquid with the first flow f1. The second flow f2 drives the rotational force generating part g2 by hydraulic power. The first flow f1 and the second flow f2 merge at the second branch D2. Due to this merging, a third flow f3 is generated. This third flow f3 is discharged from the outlet 9. The concentration of the third flow f3 is measured by the sensor 103.

  The sensor 103 may be built in the liquid mixing apparatus 1. In this case, from the viewpoint of accurately managing the concentration of the mixed liquid, the built-in sensor 103 is preferably provided on the downstream side of the third second branch D2.

  A system 300 shown in FIG. 15B includes a liquid mixing device 50 and a liquid agent concentration sensor 103. In the liquid mixing device 50, the water wheel WT of the rotational force generating part g2 directly drives the rotating member 21 of the liquid supply mechanism h2. This is the same as the liquid mixing apparatus 1.

  The liquid mixing device 50 has two outlets 9a and 9b. The liquid mixing apparatus 50 has the first branch D1, but does not have the second branch D2. That is, in this liquid mixing apparatus 50, the flow path is branched at only one location. In the liquid mixing apparatus 50, the first flow f1 and the second flow f2 are separated at the first branch D1, but the first flow f1 and the second flow f2 do not merge. The first flow f1 is discharged from the outlet 9a. The second flow f2 is discharged from the outlet 9b. The sensor 103 is located downstream of the outlet 9a. In this system 300, as in the system 200, the sensor 103 controls the flow rate adjustment valve VL1. The sensor 103 may be incorporated in the liquid mixing device 50.

  A system 400 shown in FIG. 15C includes a liquid mixing device 60 and a liquid agent concentration sensor 103. The liquid mixing device 60 is from the inlet 8 to the outlet 9. In FIG. 15C, the liquid supply mechanism h2 of the liquid mixing device 60 is shown as a square, and the rotational force generating part g2 of the liquid mixing device 60 is shown as a circle. Similar to the system 200, the sensor 103 controls the flow rate adjustment valve VL1. The sensor 103 is located on the downstream side of the second branch D2.

  In the liquid mixing device 60, the rotational force generating part g2 is provided in the branch pipe part 7b between the first branch D1 and the second branch D2. This is the same as the liquid mixing apparatus 1. However, in the liquid mixing apparatus 60, the liquid supply mechanism h2 is provided on the downstream side of the second branch D2.

  The liquid mixing device 60 has a rotation transmission mechanism t1. In FIG. 15C, the rotation transmission mechanism t1 is shown by a double circle. The rotation of the water wheel WT in the rotational force generator g2 is transmitted to the liquid supply mechanism h2 via the rotation transmission mechanism t1. Examples of the rotation transmission mechanism t1 include known rotation transmission mechanisms such as a gear mechanism, a chain mechanism, and a belt mechanism.

  In the system 400, the liquid flowing from the inlet 8 is divided into the first flow f1 and the second flow f2 in the first branch D1. The second flow f2 drives the rotational force generating part g2 by hydraulic power. The first flow f1 and the second flow f2 merge at the second branch D2. Due to this merging, a third flow f3 is generated. In the third flow f3, the liquid supply mechanism h2 mixes the liquid. The third flow f3 mixed with the liquid is discharged from the outlet 9.

  The sensor 103 may be built in the liquid mixing device 60. In this case, the built-in sensor 103 is provided on the downstream side of the liquid supply mechanism h2.

  Comparing the above three systems 200, 300 and 400, the following can be said.

  The system 200 is excellent in water saving because there is no water to be discarded. Further, in the system 200, the concentration after the merge of the first flow f1 and the second flow f2 (the concentration of the third flow f3) is measured by the sensor 103. Therefore, compared with the case where the concentration before confluence (the concentration of the first flow f1) is measured, the concentration is accurately managed. That is, in the system 200, the concentration of the finally obtained mixed liquid is accurately managed even though the liquid path is branched to extract hydraulic power and the liquid is mixed in one of the branches. sell. Further, since the rotation transmission mechanism t1 is unnecessary, a low-cost system can be realized.

  In the system 300, waste water is generated, so water saving is inferior. In the system 300, the concentration of the finally obtained mixed liquid (first flow f1) is measured by the sensor 103. Therefore, the concentration is accurately managed. Since the rotation transmission mechanism t1 is unnecessary, low cost can be achieved. Further, since the branching of the liquid path can be reduced, the structure of the liquid path can be simplified. Therefore, the low-cost liquid mixing device 50 can be realized.

  The system 400 is excellent in water saving because there is no water to be discarded. In the system 400, the concentration after the merging of the first flow f1 and the second flow f2 (the concentration of the third flow f3) is measured by the sensor 103. Therefore, compared with the case where the concentration before confluence (the concentration of the first flow f1) is measured, the concentration is accurately managed. On the other hand, since the rotation transmission mechanism t1 is necessary, the cost of the system can be increased. However, by using the rotation transmission mechanism t1, the rotational force generating part g2 and the liquid supply mechanism h2 can be separated. Therefore, the freedom degree of the installation position of the rotational force generation part g2 and the liquid supply mechanism h2 is improved. That is, the degree of freedom in system design can be improved.

  FIG. 16A and FIG. 16B are schematic configuration diagrams of a liquid mixing apparatus according to another embodiment.

  FIG. 16A is a schematic configuration diagram of the liquid mixing apparatus 70. The liquid mixing device 70 has a pipe portion 7 that is not branched, an inlet 8, and an outlet 9. There is one pipe line section 7. A liquid supply mechanism h <b> 2 and a rotational force generating part g <b> 2 are attached to the pipe line part 7. The liquid supply mechanism h2 and the rotational force generator g2 are attached in series. The liquid supply mechanism h2 and the rotational force generator g2 are the same as those of the liquid mixing apparatus 1 described above.

  The liquid mixing device 70 has a rotation transmission mechanism t1. The rotational driving mechanism t1 transmits the rotational driving force generated in the rotational force generator g2 to the rotating member 21 of the liquid supply mechanism h2. This rotation transmission mechanism t1 enables the pipe section 7 without branching.

  In the liquid mixing device 70, the rotational force generating part g2 is disposed on the downstream side of the liquid agent supply mechanism h2. Therefore, the liquid (mixed liquid) after the liquid agent is mixed rotates the rotational force generating part g2. The mass of the fluid increases due to the supply of the liquid agent by the liquid agent supply mechanism h2. This increase in mass can increase the rotational force in the rotational force generation part g2.

  FIG. 16B is a schematic configuration diagram of the liquid mixing apparatus 80. The liquid mixing apparatus 80 includes a pipe portion 7 that is not branched, an inlet 8, and an outlet 9. There is one pipe line section 7. A rotational force generating part g2 and a liquid supply mechanism h2 are attached to the pipe line part 7. The rotational force generating part g2 and the liquid supply mechanism h2 are attached in series. The liquid supply mechanism h2 and the rotational force generator g2 are the same as those of the liquid mixing apparatus 1 described above.

  The liquid mixing device 80 has a rotation transmission mechanism t1. The rotational driving mechanism t1 transmits the rotational driving force generated in the rotational force generator g2 to the rotating member 21 of the liquid supply mechanism h2. This rotation transmission mechanism t1 enables the pipe section 7 without branching.

  In the liquid mixing device 80, the rotational force generating part g2 is disposed on the upstream side of the liquid supply mechanism h2. Therefore, the liquid (medicine or the like) supplied by the liquid agent supply mechanism h2 does not adhere to the rotational force generating part g2 (such as the wing part b1 of the water turbine WT).

  In the liquid mixing device 70 and the liquid mixing device 80, the structure of the pipe line portion can be simplified. This can contribute to cost reduction and miniaturization.

  FIG. 17 is a cross-sectional view showing a liquid mixing apparatus 90 according to another embodiment. Similarly to the liquid mixing device 70 and the liquid mixing device 80, the liquid mixing device 90 is an example in which the pipe line section 7 does not have a branch. Hereinafter, differences from the liquid mixing apparatus 1 will be described.

  The liquid mixing device 90 has a pipe line portion 7 having no branch, an inlet (not shown), and an outlet (not shown). There is one pipe line section 7. The pipe line portion 7 extends along a straight line from the inlet to the outlet. The pipe line part 7 is provided in the case ks1 (driving body accommodating part g1). The inlet and the outlet communicating with the pipe line portion 7 are also provided in the case ks1. The central portion of the conduit portion 7 is the same as the intermediate portion R2 of the branch conduit portion 7b in the liquid mixing apparatus 1. The main body part h1 is not provided with a pipe line part.

  The liquid mixing apparatus 90 includes a supply pipe portion 92 that allows the liquid agent supplied from the liquid agent supply member 3 to flow into the pipe line portion 7. The inlet 94 of the supply pipe part 92 is located below the measurement part forming member 22 (liquid agent containing space 32) described above. The liquid agent supplied from the liquid agent supply member 3 flows into the supply pipe portion 92 from the inlet 94. The opening of the inlet 94 is widened so that all of the liquid agent supplied from the liquid agent supply member 3 can be received. An outlet 96 of the supply pipe part 92 communicates with the pipe line part 7. The supply pipe part 92 has an inclination, and the liquid agent flowing into the supply pipe part 92 flows into the pipe line part 7. In this liquid mixing apparatus 90, the pipe line part 7 does not have a branch. Further, in the liquid mixing apparatus 90, the rotation transmission mechanism t1 may be unnecessary. This structure can contribute to cost reduction and miniaturization.

  The liquid mixing apparatus of the present invention is used by providing a liquid agent supply mechanism having a measuring function for receiving a liquid agent from the liquid agent supply path and measuring a predetermined amount of the liquid agent and a function for supplying the measured liquid agent to the pipe line part. A highly accurate mixing rate is realized regardless of the conditions, and the present invention is not limited to the embodiment described above. In addition, energy saving is achieved because the flow of liquid is used as rotational energy. As the liquid supply mechanism, in addition to the above-described embodiment, a liquid supply mechanism such as one that performs a metering function and a supply function by moving the pump member back and forth, or one that uses an injection device may be employed. However, in order to achieve high accuracy mixing ratio and ease of changing mixing ratio, and high durability and overall performance of suppressing cost rise, as a liquid supply mechanism, it is rotationally driven by a drive device, The measuring unit is provided, and each configuration of the embodiment described above is employed alone or in combination, such as a rotating member that is displaced to a liquid agent receiving position and a liquid agent discharging position by being rotationally driven. Is preferred.

In the liquid mixing apparatus 1 described above, the first rotational force generation part g2 drives the first liquid agent supply mechanism h2, and the second rotational force generation part g2 drives the second liquid agent supply mechanism h2. The number of revolutions obtained by the first torque generation part g2 is Rp1, and the number of revolutions obtained by the second torque generation part g2 is Rp2. In the liquid mixing apparatus 1 described above, the rotational speed Rp1 and the rotational speed Rp2 are substantially the same. On the other hand, the rotational speed Rp1 may be different from the rotational speed Rp2. For example, the following configuration X is exemplified as a configuration when it is desired to make the supply amounts different between the first liquid supply mechanism h2 and the second liquid supply mechanism h2.
(Configuration X) The specifications of the two rotational force generators g2 are made different so that the rotational speed Rp1 and the rotational speed Rp2 are different.

  In this configuration X, the first liquid agent supply mechanism h2 and the second liquid agent supply mechanism h2 are preferably the same. In this case, common parts and reduction in production costs can be achieved. In this configuration X, the specifications of the water wheel WT that can be made different include the number of blade parts b1, the area of the blade parts b1, the angle of the blade parts b1 with respect to the liquid flow direction, and the like.

The following configuration Y is exemplified as another configuration when it is desired to make the supply amounts different between the first liquid supply mechanism h2 and the second liquid supply mechanism h2.
(Configuration Y) The supply amount supplied per rotation of the rotating member 21 is different between the first liquid agent supply mechanism h2 and the second liquid agent supply mechanism h2.

  In the configuration Y, preferably, the first rotational force generation part g2 and the second rotational force generation part g2 are the same. In this case, common parts and reduction in production costs can be achieved. In the configuration Y, as a specification that can be different, the volume V of the liquid agent containing space 32 is exemplified.

  The configuration X and the configuration Y may be combined. With the configuration X and / or the configuration Y, a plurality of types of liquid agents can be mixed at a desired ratio. Further, when there are three or more rotational force generators g2 and liquid supply mechanisms h2, more various liquid supply can be achieved by applying the configuration X and / or the configuration Y.

  In the case of the embodiment in which the motor 6 is not provided, electric power may be unnecessary. Even when the motor 6 is provided, less power is required to control the flow rate adjustment valve VL1. Thus, for example, the motor 6 can be driven by a battery. Further, the flow rate adjusting valve VL1 can be driven even with a small electric power generated by the solar battery. From such a viewpoint, the liquid mixing apparatus 1 may have a storage battery or a solar battery as a power source for driving the flow rate adjustment valve VL1.

  The liquid mixing apparatus according to the present invention is suitable for fields such as hydroponics, food production, and drug production.

DESCRIPTION OF SYMBOLS 1 ... Liquid mixing apparatus 2 ... Main body block 3 ... Liquid agent supply member 4 ... Liquid agent container 5 ... Holding valve 6 ... Drive motor 7 ... Pipe line part 7a ... Main pipe Road part 7b ... Branch pipe part
8 ... (Pipe part) inlet 9 ... (Pipe part) outlet 10 ... Adjustment valve hole 11 ... First hole 12 ... Second hole 13 ... Step part DESCRIPTION OF SYMBOLS 14 ... Large diameter part 15 ... Small diameter part 16 ... Through-hole of (pressing valve) 17 ... Liquid agent supply path 18 ... Liquid agent container stopper 19 ... O-ring 20 ... No. One coil spring 21 ... Rotating member 22 ... Measuring part forming member 23 ... Accommodating recess 24 ... Lid member 25 ... Substrate 26 ... Protrusion 27 ... Measuring convex part 28 ... -Second coil spring 29 ... Circular recess 30 ... Small diameter through hole 31 ... Large diameter through hole 32 ... Liquid agent accommodation space 33 ... Large diameter supported portion 34 ... Small diameter supported Part 35 ... near the opening part (of the second hole) 36 ... near the back end part (of the second hole) 37 ... O-rings 50, 60, 70, 80, 90 ..Liquid mixing device 100 ... mixed liquid supply system 101 ... water supply source 102 ... water supply pipe 103 ... concentration sensor 104 ... reflux pipe 105 ... pump 106 ... first on-off valve 107 ... second on-off valve 108 ... control device 109 ... AC power supply 110 ... uses 200, 300, 400 ... mixed liquid supply system A ... upstream connection point (of reflux pipe) B: Downstream connection point (of the reflux pipe) h1 ... Main body g1 ... Drive body housing part h2 ... Liquid supply mechanism g2 ... Rotational force generating part D1 ... First branch D2 ..Second branch WT ... turbine b1 ... wing part z1 ... shaft of turbine wheel (output shaft)
R1 ... Upstream part of the branch pipe part R2 ... Intermediate part of the branch pipe part R3 ... Downstream part VL1 of the branch pipe part ... Flow control valve

Claims (5)

A conduit section through which fluid flows;
A liquid agent supply path for supplying the liquid agent to the pipe line part;
And a liquid supply mechanism that is disposed in the liquid supply passage,
The liquid supply mechanism is driven by a drive device that uses the flow of the fluid in the conduit section ,
The pipe section has a branch pipe section,
The pipe section has a first branch and a second branch, the inlet of the branch pipe section is the first branch, and the outlet of the branch pipe section is the second branch,
A liquid mixing device in which the liquid supply mechanism is driven by a driving device that uses the flow of the fluid in the branch pipe section. The liquid supply mechanism, the metering function of metering a predetermined amount of the liquid agent accepts liquid from the liquid supply passage, the liquid mixture according to the metered liquid to claim 1, further comprising a function to supply to the pipeline section apparatus. The liquid supply mechanism includes a liquid supply member,
The liquid supply member is configured to be displaceable between a liquid reception position for receiving the liquid from the liquid supply path and a liquid discharge position for discharging the liquid to the pipe section.
The liquid supply member has a measuring section that can store a predetermined amount of liquid,
The weighing unit is, when the liquid supply member is in the liquid receiving position, the and the pipe portion communicates with the liquid supply path not communicating, when the liquid supply member is in the liquid discharge position, the conduit portion and communicating and liquid mixing apparatus according to claim 1 or 2 is configured so as not to communicate with the aforementioned liquid supply path. A conduit section through which fluid flows;
A liquid agent supply path for supplying the liquid agent to the pipe line part;
And a liquid supply mechanism that is disposed in the liquid supply passage,
The liquid supply mechanism is driven by a drive device that uses the flow of the fluid in the conduit section ,
The liquid supply mechanism includes a liquid supply member,
The liquid supply member is configured to be displaceable between a liquid reception position for receiving the liquid from the liquid supply path and a liquid discharge position for discharging the liquid to the pipe section.
The liquid supply member has a measuring section that can store a predetermined amount of liquid,
When the liquid supply member is in the liquid reception position, the metering unit communicates with the liquid supply passage and does not communicate with the pipe portion, and when the liquid supply member is in the liquid discharge position, A liquid mixing apparatus configured to communicate with a pipe section and not to communicate with the liquid supply path. The drive device has a rotational force generator that can convert the flow of fluid into rotational force,
The liquid supply mechanism has a rotating member that rotates coaxially with the rotational force generating unit,
The rotating member is provided with the measuring unit,
Said by the rotating member is rotated, the liquid mixing device according to claim 3 or 4, displaced and the liquid receiving position and the liquid ejection position.

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