JP2007211756A - Method for driving pump device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a method for driving a pump device which eliminates instability in changing over between delivery process and suction process. <P>SOLUTION: A correction process moving a valve element 17 in a direction reducing inner volume of a pump chamber 2 is performed at a time of change over from suction process to delivery process, and a correction process moving the valve element 17 in a direction expanding inner volume of the pump chamber 2 is performed at a time of change over from delivery process to suction process in a mixing pump device 1. Instability caused by backlash is thereby eliminated, and instability caused by pressure difference between both sides of a valve is eliminated. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a method for driving a pump device that discharges fluid sucked from an inflow path into a pump chamber by driving a valve body and opening and closing the valve.

  Among mixing pump devices that mix and discharge a plurality of fluids at a predetermined ratio, one pump mechanism that sucks, mixes, and discharges a plurality of fluids is, for example, a high-performance liquid chromatography device, There has been proposed a mixing apparatus that sucks and mixes a solvent by a plunger pump and discharges the solvent toward a column (see, for example, Patent Document 1).

In the mixing pump device disclosed herein, for example, the rotation of the stepping motor in one direction is transmitted to the plunger via the cam mechanism, thereby expanding and reducing the internal volume of the pump chamber. Then, while expanding the pump chamber, by sequentially opening and closing the valves arranged in each of the two inflow passages, the liquid sucked from each of the two inflow passages is mixed in the pump chamber, while the pump chamber is reduced. The liquid mixed in the pump chamber is discharged.
Japanese Patent No. 3117623

  However, in the pump device described in Patent Document 1, when there is a pressure difference between the pump chamber and the valve when switching from the discharge process to the suction process, when the valve is switched from the closed state to the open state, There is a problem that a reverse flow to the inflow path occurs and the mixing ratio of the two fluids fluctuates. Also, in a pump device using a diaphragm valve or the like, when switching from the discharge process to the suction process, or when switching from the suction process to the discharge process, the diaphragm valve undergoes backlash deformation, and the suction amount and discharge amount There is a problem of variation.

  In view of the above problems, an object of the present invention is to provide a driving method of a pump device that can eliminate instability that occurs when a discharge process and a suction process are switched.

  In order to solve the above problems, in the present invention, a pump chamber, a valve element disposed in the pump chamber, an inflow path communicating with the pump chamber, an outflow path communicating with the pump chamber, and the inflow path And a plurality of valves disposed in each of the outflow passages, and a step of sucking fluid from the inflow passage to the pump chamber by driving the valve body and opening and closing the plurality of valves, and the pump chamber In the pump device driving method for performing a fluid discharge process from the discharge process to the outflow passage, at least one of the switching from the suction process to the discharge process and the switching from the discharge process to the suction process, A correction step of closing all of the plurality of valves and moving the position of the valve body is performed.

  In the pump device, when switching from the discharge process to the suction process, or when switching from the suction process to the discharge process, if there is a pressure difference between the pump chamber and the valve, when the valve is switched from the closed state to the open state, A backflow from the pump chamber to the inflow passage or a backflow from the outflow passage to the pump chamber is likely to cause an unstable state when the discharge process and the suction process are switched. Further, when the valve body is switched from the discharge process to the suction process, or when switching from the suction process to the discharge process, backlash instability occurs, and the suction amount and the discharge amount tend to vary. However, in the present invention, when switching from the suction process to the discharge process and at least one of switching from the discharge process to the suction process, all of the plurality of valves are closed to move the position of the valve body. Therefore, the pressure difference between the pump chamber and the outside of the valve and the backlash-like instability of the valve body can be eliminated, so that the accuracy of the suction amount and the discharge amount can be improved.

  In the present invention, it is preferable that the correction step is performed both when the suction step is switched to the discharge step and when the discharge step is switched to the suction step.

  The present invention is effective when applied to a pump device using a diaphragm valve as the valve body. In a pump device using a diaphragm valve, when switching from the discharge process to the suction process, or when switching from the suction process to the discharge process, the diaphragm valve undergoes backlash-like deformation, and the amount of suction and discharge tends to vary. However, if the present invention is applied, such variations can be eliminated.

  In the present invention, in the correction step when switching from the suction step to the discharge step, for example, the valve body is moved in a direction to reduce the internal volume of the pump chamber, and the discharge step is switched to the suction step. In the correction process at the time of replacement, for example, the valve body is moved in the direction of expanding the internal volume of the pump chamber.

  In the present invention, for example, a configuration in which the valve body is moved in a direction to eliminate a pressure difference between both sides across a valve that is switched from a closed state to an open state immediately after the correction step is adopted in the correction step.

  In this case, a valve that is switched from a closed state to an open state when switching from the suction step to the discharge step, and a valve that is switched from a closed state to an open state when switching from the discharge step to the suction step It is preferable that the pressure difference between both sides sandwiching at least one of the valves is directly or indirectly monitored, and the correction step is performed based on the monitoring result of the pressure difference.

  In the present invention, the correction step may be configured to be performed under preset conditions.

  In the present invention, a plurality of the inflow passages are formed, and the valve is disposed in each of the inflow passages. In the suction step, fluid is sequentially supplied from each of the plurality of inflow passages to the pump chamber. In the discharge step, the fluid mixed in the pump chamber may be discharged from the outflow passage.

  In this case, before the fluid having the lowest mixing ratio flows into the pump chamber among the plurality of fluids flowing in from the plurality of inflow passages, at least a part of the fluid having a higher mixing ratio than the fluid is transferred to the pump chamber. It is preferable to flow in. If comprised in this way, a some fluid can be mixed reliably.

  In the present invention, a plurality of the outflow passages are formed, and the valve is disposed in each of the plurality of outflow passages, and in the discharge step, fluid is sequentially discharged from the plurality of outflow passages. May be.

  In the present invention, the outflow path supplies an aqueous methanol solution toward the electromotive part of the fuel cell, for example.

  In the present invention, when switching from the suction process to the discharge process and at least one of switching from the discharge process to the suction process, the valve body is closed and the position of the valve body is moved to move the outside of the pump chamber and the valve. Since the pressure difference and the backlash-like instability of the valve body can be eliminated, the accuracy of the suction amount and the discharge amount can be improved.

  Embodiments of the present invention will be described below with reference to the drawings.

[Outline of mixing pump device]
(Device configuration)
FIG. 1 is a conceptual diagram showing a basic configuration of a mixing pump device to which the present invention is applied. As shown in FIG. 1, in the mixing pump device 1 of this embodiment, a plurality of inlets 30 and outlets 40 are opened in the pump device body 7, and two inlets 30 a, 30 b, In addition, an example in which two outlets 40a and 40b are opened is shown. The pump device body 7 includes a pump chamber 2, an inflow passage 3 (3a, 3b) connected to the pump chamber 2 and the inlets 30a and 30b, and a plurality of pump chambers 2 and a plurality of outlets 40a and 40b connected to the outlets 40a and 40b. An outflow passage 4 (4a, 4b) is formed. Here, the inflow path 3 (3a, 3b) and the outflow path 4 (4a, 4b) communicate with the pump chamber 2 independently of each other.

  The inflow path 3 (3a, 3b) includes an inflow side active valve 5 (5a, 5b), and the outflow path 4 (4a, 4b) includes an outflow side active valve 6 (6a, 6b). A pump mechanism 13 is configured for the pump chamber 2. Here, the pump mechanism 13 includes a valve body 17 disposed in the pump chamber 2 and a driving device 105 including a stepping motor 12 for driving the valve body 17. Further, for the inflow side active valves 5a and 5b and the outflow side active valves 6a and 6b, a control device (not shown) for controlling opening and closing of these valves is configured.

(Operation)
FIGS. 2A and 2B are a timing chart showing the operation of the mixing pump device shown in FIG. 1 and an explanatory diagram showing the relationship between the position of the valve element and the resolution. 3A to 3D are explanatory diagrams relating to the deformation of the diaphragm valve.

  In the present embodiment, the driving device 105 drives the valve body 17 in the direction in which the internal volume of the pump chamber 2 increases when the stepping motor 12 rotates in one direction, and the pump when the stepping motor 12 rotates in the other direction. The valve body 17 is driven in a direction in which the internal volume of the chamber 2 is reduced. In conjunction with such an operation, the control device controls the opening and closing of the plurality of active valves 5 and 6, thereby sequentially sucking the fluid sucked into the pump chamber 2 from each of the two inflow passages 3 in the pump chamber 2. After mixing, the liquid is discharged from the outflow passage 4.

  With reference to Fig.2 (a), operation | movement of the mixing pump apparatus 1 of this form is demonstrated more concretely. Here, of the two inflow passages 3a and 3b, the first liquid LA is sucked through the inflow passage 3a and the second liquid LB is sucked through the inflow passage 3b. The case where the ratio (mixing ratio) of the inflow amounts of the liquid LA and the second liquid LB is 1: 5 will be described. In FIG. 2A, the uppermost stage shows the suction and discharge of the pump mechanism 13, and the suction by the pump mechanism 13 is performed by, for example, the stepping motor 12 rotating clockwise and the valve element 17 being pumped. The discharge in the pump mechanism 13 is performed by moving the stepping motor 12 counterclockwise, for example, so that the valve body 17 reduces the internal volume of the pump chamber 2. This is done by moving in the direction. The pump mechanism 13 is stopped when the power supply to the stepping motor 12 is stopped. Note that in both the inflow side active valve 5 (5a, 5b) and the outflow side active valve 6 (6a, 6b), after the positive pulse is input, the active valves 5, 6 are in an open state and are negative. When a pulse is input, it switches to the closed state. In addition, after the negative pulse is input, the active valves 5 and 6 are in the closed state, and are switched to the open state when the positive pulse is input.

  In FIG. 2A, first, at time t1, power supply to the stepping motor 2 is stopped, and the pump mechanism 13 is in a stopped state. Moreover, all the active valves 5 and 6 are closed until time t1.

  In this state, at time t1, only the inflow side active valve 5b arranged in the inflow path 3b corresponding to the liquid LB is switched to the open state among the two inflow side active valves 5a and 5b. Next, when power is supplied to the stepping motor 12 at time t2 and the stepping motor 12 rotates clockwise, the valve body 17 moves in the direction of expanding the internal volume of the pump chamber 2, so that liquid flows from the inflow path 3b to the pump chamber 2. LB flows in. Then, after 125 steps of pulses are input to the stepping motor 12 until time t3, when the power supply to the stepping motor 12 stops at time t3, the valve body 17 stops. At the same time, the inflow side active valve 5b is switched from the open state to the closed state. As a result, the inflow of the liquid LB from the inflow path 3b to the pump chamber 2 is stopped. Thereby, about the liquid LB, a half of the total amount flows into the pump chamber 2.

  Next, at time t4, only the inflow side active valve 5a is switched to the open state, and when the stepping motor 12 rotates clockwise at time t5 and the stepping motor 12 rotates clockwise, the valve element 17 increases the internal volume of the pump chamber 2. Since the liquid LA moves in the direction of enlargement, the liquid LA flows into the pump chamber 2 from the inflow path 3a. Then, after 50 steps of pulses are input to the stepping motor 12 until time t6, when the power supply to the stepping motor 12 stops at time t6, the valve body 17 stops. At the same time, the inflow side active valve 5a is switched from the open state to the closed state. As a result, the inflow of the liquid LA from the inflow path 3a to the pump chamber 2 is stopped. Thereby, the entire amount of the liquid LA flows into the pump chamber 2.

  Next, at time t7, only the inflow side active valve 5b is switched to the open state again, and when the stepping motor 12 is rotated clockwise by supplying power to the stepping motor 12 at time t8, the valve body 17 is moved to the inner volume of the pump chamber 2. The liquid LB flows into the pump chamber 2 from the inflow passage 3b. Then, after 125 steps of pulses are input to the stepping motor 12 until time t9, when the power supply to the stepping motor 12 stops at time t9, the valve body 17 stops. At the same time, the inflow side active valve 5b is switched from the open state to the closed state. As a result, the inflow of the liquid LB from the inflow path 3b to the pump chamber 2 is stopped. As a result, the remaining half of the liquid LB flows into the pump chamber 2 and the inflow of the liquid LB is completed.

  Next, at time t11, of the two outflow side active valves 6a and 6b, only the outflow side active valve 6a is switched to the open state, and power is supplied to the stepping motor 12 at time t12 and the stepping motor 12 is rotated counterclockwise. When rotating, the valve body 17 moves in a direction to reduce the internal volume of the pump chamber 2, so that the mixed fluid in the pump chamber 2 is discharged from the outflow passage 4a. Then, after 150 steps of pulses are input to the stepping motor 12 until time t13, when the power supply to the stepping motor 12 is stopped at time t13, the valve body 17 is stopped. At the same time, the outflow side active valve 6a is switched from the open state to the closed state. As a result, an amount of mixed liquid corresponding to ½ of the liquid flowing into the pump chamber is discharged from the outflow passage 4a.

  Next, at time t14, of the two outflow side active valves 6a and 6b, only the outflow side active valve 6b is switched to the open state, and power is supplied to the stepping motor 12 at time t15 so that the stepping motor 12 is rotated counterclockwise. When rotating, the valve body 17 moves in a direction to reduce the internal volume of the pump chamber 2, so that the mixed fluid in the pump chamber 2 is discharged from the outflow passage 4b. Then, after 150 steps of pulses are input to the stepping motor 12 until time t16, when the power supply to the stepping motor 12 stops at time t16, the valve body 17 stops. At the same time, the outflow side active valve 6b is switched from the open state to the closed state. As a result, an amount of mixed liquid corresponding to ½ of the liquid flowing into the pump chamber 2 is discharged from the outflow path 4b.

  Further, in this embodiment, the correction operation is performed in the period from time t10 to time t11 and in the period from time t17 to time t18. That is, as shown in FIG. 2B, the resolution tends to be low at the top dead center where the suction process switches to the discharge process and the bottom dead center where the discharge process switches to the suction process. Such a tendency is likely to occur due to backlash when a gear mechanism is used for the driving device 105, for example. Further, backlash-like misalignment is likely to occur at the top dead center and the bottom dead center of the valve body 17 itself. In particular, when a diaphragm valve is used as the valve body 17, the deformation of the diaphragm valve is likely to occur backlash at the top dead center or the bottom dead center, so that the effect of performing the correction operation is great.

  Further, when a diaphragm valve is used as the valve body 17, the shape of the diaphragm valve is easily subjected to a pressure difference between the internal pressure of the pump chamber 2 and the atmospheric pressure. For example, as shown in FIG. 3A, when the internal pressure of the pump chamber 2 is equal to the atmospheric pressure, unnecessary deformation does not occur in the diaphragm valve 170 due to the pressure difference, but FIG. As shown in FIG. 3, when the internal pressure of the pump chamber 2> atmospheric pressure, the diaphragm valve 170 is inflated by the pressure difference. On the contrary, as shown in FIG. 3C, when the internal pressure of the pump chamber 2 is smaller than the atmospheric pressure, the diaphragm valve 170 is depressed by the pressure difference.

  Therefore, when the pump chamber 2 is at negative pressure at time t9 when the suction is finished, the state shown in FIG. 3C is obtained, and when the pump chamber 2 is at positive pressure at time t16 when the discharge is finished. The state shown in FIG. Therefore, in the state shown in FIG. 3C, when the outflow side active valve 6a is opened at time t11 and the pump chamber 2 communicates with the outflow port 40a side from the valve 6a of the outflow tube 4a, the outflow tube 4a. There is a risk that the liquid mixture present on the outlet 40a side will flow back into the pump chamber 2 due to the head difference. When such a situation occurs, the discharge amount of the mixed liquid becomes smaller than a predetermined amount. 3B, when the inflow side active valve 5b is opened at time t1 and the pump chamber 2 communicates with the inlet 30b side from the valve 5b of the inflow pipe 3b, the pump chamber 2 The mixed liquid flows backward from the inflow pipe 3b, and the inflow amount of the second liquid LB becomes smaller than a predetermined amount.

  On the other hand, even when the pump chamber 2 is equivalent to the atmospheric pressure at the time t9 when the suction is finished or the time t16 when the discharge is finished, as shown in FIG. When the inflow pipes 3a and 3b are positioned below, the following problem occurs. First, since the pressure in the pump chamber 2 is equal to the pressure outside the inflow side active valve 5b after completion of the suction at time t9, the outflow side active valve 6a is opened at time t11, and the pump chamber. 2 and the outlet 40a side of the outflow pipe 4a communicate with each other, there is a possibility that the mixed liquid existing on the outlet 40b side from the valve 6a of the outflow pipe 4a will flow back into the pump chamber 2 due to the head difference. When such a situation occurs, the diaphragm valve 170 swells before the diaphragm valve 170 is driven, and the discharge amount of the mixed liquid becomes smaller than a predetermined amount. Further, even if the pump chamber 2 is equal to the atmospheric pressure at the time t16 when the discharge is finished, the pressure in the pump chamber 2 is equivalent to the pressure outside the outflow side active valve 6b after the discharge is finished at the time t16. Therefore, when the suction is performed again, at time t1, when the inflow side active valve 5b is opened and the pump chamber 2 and the inflow side 30b of the inflow pipe 3b communicate with each other, the mixed liquid flows backward through the inflow pipe 3b. There is a risk. When such a situation occurs, the diaphragm valve 170 is recessed before the diaphragm valve 170 is driven, and the inflow amount of the second liquid LB becomes smaller than a predetermined amount.

  Therefore, in the present embodiment, the position of the valve element 17 is corrected when switching from suction to discharge and when switching from discharge to suction. Specifically, when switching from the suction process to the discharge process, the valve body 17 is slightly moved in the direction of reducing the internal volume of the pump chamber 2, and when switching from the discharge process to the suction process, The valve element 17 is slightly moved in the direction in which the internal volume of the chamber 2 is expanded. More specifically, as shown in FIG. 2A, after the suction is finished and before the discharge is started, the stepping motor 12 is fed counterclockwise by supplying power to the stepping motor 12 from the time t10 to the time t11. The valve body 17 is moved in the direction in which the internal volume of the pump chamber 2 is reduced by rotating. Conversely, from time t17 to time t18 after the end of discharge and before starting the next suction, power is supplied to the stepping motor 12 and the stepping motor 12 is rotated clockwise to increase the internal volume of the pump chamber 2. The valve body 17 is moved in the direction.

  Here, with respect to the correction process, a configuration in which the control device causes the valves 5 and 6 and the valve body 17 to perform the correction process in accordance with preset conditions can be employed.

  Further, of the valves 5 and 6, when switching from suction to discharge and when switching from discharge to suction, the valve 5 b and 6 a that are switched from the closed state to the open state have a pressure difference between both sides sandwiching the valve 5 b and 6 a. Direct or indirect monitoring may be used, and in the correction step, a method may be employed in which the valve body 17 is moved in a direction to eliminate such a pressure difference based on the monitoring result. Here, as a method of directly monitoring the pressure difference between the both sides of the valves 5b and 6a, the pressure sensors at the pump chamber 2, the position outside the valve 5b in the inflow pipe 3b, and the position outside the valve 6a in the outflow pipe 4a, respectively. There is a method of detecting the pressure difference based on the detection results of these pressure sensors. Further, as a method of indirectly monitoring the pressure difference between the both side positions of the valves 5b and 6a, while detecting the height position of the outlet 40a of the outlet pipe 4a, the second method shown in FIG. There is a method of monitoring the liquid surface position of the liquid LB.

(Main effects of this form)
As described above, in the mixing pump device 1 of the present embodiment, the liquid sucked sequentially from each of the plurality of inflow paths 3 to the pump chamber 2 by driving the valve body 17 and opening / closing the plurality of active valves 5 and 6. After mixing, in discharging the mixed liquid from the outflow passage 4, the driving device 105 drives the valve body 17 in a direction in which the internal volume of the pump chamber 2 is expanded when the stepping motor 12 rotates in one direction, and the stepping motor 12 When the motor 12 rotates in the other direction, the valve body 17 is driven in a direction in which the internal volume of the pump chamber 2 decreases. Therefore, regardless of the position of the valve body 17, while the stepping motor 12 rotates in one direction, the active valve 6 disposed in the outflow path 4 is closed and the active valves 5 disposed in the inflow path 3 are sequentially placed. By simply opening and closing, a plurality of fluids can be sucked into the pump chamber 2 at a predetermined ratio, and while the stepping motor 12 is rotating in the other direction, the active valve 5 disposed in the inflow path 3 is closed, The fluid mixture can be discharged from the pump chamber 2 simply by opening the active valve 6 disposed in the outflow passage 4. Therefore, unlike the configuration in which the rotation of the stepping motor 12 in one direction is transmitted to the valve body 17 via the cam mechanism, it is not necessary to monitor the position of the cam or the like with a photo interrupter. Therefore, the configuration of the mixing pump device 1 can be simplified, so that downsizing and cost reduction can be achieved.

  Further, in this embodiment, the stroke of the valve element 17 can be easily changed simply by changing the signal pattern supplied to the stepping motor 12. Therefore, there is an advantage that the stroke of the valve element 17 can be set to an optimum length according to the type of liquid to be used.

  Further, the control device sets the mixing ratio before the first liquid LA having a low mixing ratio out of the first liquid LA and the second liquid LB flowing in from the inflow passages 3a and 3b is sucked into the pump chamber 2. The opening and closing of the active valves 5 and 6 is controlled so that a part of the high second liquid LB flows into the pump chamber 2. Therefore, the first liquid LA can be prevented from being unevenly distributed in the corner of the pump chamber 2, for example, in the vicinity of the active valve 5a, so that the first liquid LA and the second liquid LB can be reliably mixed. . In particular, in this embodiment, after the second liquid LB with a high mixing ratio is sucked into the pump chamber 2 by an amount corresponding to ½ of the total amount, the first liquid LA with a low mixing ratio is sucked into the pump chamber 2. Thereafter, since the remaining half of the second liquid LB is sucked into the pump chamber 2, the first liquid LA and the second liquid LB can be mixed more reliably.

  Furthermore, in this embodiment, since the correction operation is performed during the period from time t10 to time t11 and during the period from time t17 to time t18, even when the valve body 17 reaches the top dead center or the bottom dead center. Then, after returning from the top dead center or bottom dead center, suction and discharge are performed. For this reason, the accuracy of the suction amount and the discharge amount is high. In particular, when the valve body 17 is a diaphragm valve, when switching from the discharge process to the suction process, or when switching from the suction process to the discharge process, the diaphragm valve undergoes backlash deformation, and the suction amount and the discharge amount vary. Although it is easy, if the present invention is applied, such variation can be eliminated.

  Further, when the diaphragm valve 170 is used as the valve body 17, unnecessary deformation may occur in the diaphragm valve 170 due to the pressure difference between the internal pressure of the pump chamber 2 and the atmospheric pressure. The suction amount and the discharge amount are highly accurate because the suction and the discharge are performed while correcting the above.

[Specific configuration of mixing pump device]
FIG. 4 is a conceptual diagram showing a basic configuration of a mixing pump device to which the present invention is applied. 5A and 5B are an exploded perspective view when the mixing pump device according to the embodiment of the present invention is viewed obliquely from above and an exploded perspective view when viewed from obliquely below. FIG. 6 is an explanatory diagram showing a cross-sectional configuration of a mixing pump device to which the present invention is applied. FIG. 7 is an explanatory diagram showing a cross-sectional configuration of the mixing pump device according to the embodiment of the present invention.

  As shown in FIG. 4, in the mixing pump device 1 of this embodiment described below with reference to FIGS. 5 to 13, the pump device body 7 has a pump chamber 2 and two inflows communicating with the pump chamber 2. A path 4 and six outflow paths 5 communicating with the pump chamber 2 are configured. Here, the two inflow passages 3 and the six outflow passages 4 communicate with the pump chamber 2 independently of each other. Each of the two inflow paths 3 is configured with an inflow side active valve 5, and each of the six outflow paths 4 is configured with an outflow side active valve 6. A pump mechanism 13 is configured for the pump chamber 2, and the pump mechanism 13 includes a diaphragm valve 170 disposed in the pump chamber 2 and a driving device 105 including a stepping motor for driving the diaphragm valve 170. And a control device (not shown) for controlling opening and closing of the inflow side active valve 5 and the outflow side active valve 6. Also in the mixing pump device 1 configured as described above, the driving device 105 drives the diaphragm 170 in the direction in which the internal volume of the pump chamber 2 increases when the stepping motor rotates in one direction, and the stepping motor 12 moves in the other direction. The diaphragm valve 170 is driven in such a direction that the internal volume of the pump chamber 2 decreases when the pump chamber 2 is rotated. In conjunction with such an operation, the control device controls the opening and closing of the plurality of active valves 5 and 6, thereby sequentially sucking the fluid sucked into the pump chamber 2 from each of the two inflow passages 3 in the pump chamber 2. After mixing, the liquid is discharged from the outflow passage 4. In such a mixing pump device 1, the inflow side active valves 5a and 5b and the outflow side active valves 6a and 6b are opened and closed by a control device (not shown).

  As shown in FIGS. 5A, 5 </ b> B, 6, and 7, the mixing pump device 1 of the present embodiment is described on one surface 71 of the box-shaped device body 7 with reference to FIG. 1. Pipes constituting the inlet 30 and the outlet 40 are connected. Here, the pump device body 7 includes a wiring board 74, a bottom plate 75, a base plate 76 for the pump mechanism 13 and the active valves 5 and 6 to be described later, a flow path constituting plate 77 in which a flow path to be described later is formed in a groove shape, The sealing sheet 78 which covers the upper surface of the flow path by covering the upper surface of the flow path constituting plate, and the upper plate 79 to which the pipe is connected are laminated in this order.

  The base plate 76 is formed with holes 137 and 67a to 67h for configuring a space for arranging the pump mechanism 13 and the active valves 5 and 6 to be described later. In addition, a round through hole 21 for forming the pump chamber 2 is formed at the center position of the flow path component plate 77, and around the through hole 21 on the lower surface side of the flow channel component plate 77. A recess (not shown) that forms the valve chamber of the active valves 5 and 6 is formed. Further, eight grooves 41 a to 41 h extend radially from the through hole 21. Further, in the vicinity of the grooves 41a to 41h of the flow path constituting plate 77, grooves 42a, 42b,... Are formed.

  In this embodiment, the inflow path 3 and the outflow path 4 are configured by the eight grooves 41a to 41h. That is, when the base plate 76, the flow path component plate 77, and the sealing sheet 78 are overlapped, the inflow path 3 and the outflow path 4 are formed by the grooves 41a to 41f, 42a, 42b,. The inflow side active valve 5 and the outflow side active valve 6 are arranged in each of the paths 4.

  Thus, in this embodiment, since the active valves 5 and 6 are arranged in a plane around the pump chamber 2, the flow path can be shortened in each of the inflow path 3 and the outflow path 4, and the mixing pump device 1. Can be made thinner. Moreover, since variation in the discharge amount from each outflow passage 4 can be suppressed, an appropriate amount of fluid can be discharged with high accuracy. Moreover, in the plurality of outflow passages 4, the lengths of the flow paths from the pump chamber 2 to the outflow side active valve 6 are equal. For this reason, it is possible to control the discharge amount through each outflow passage 4 with high accuracy. Moreover, since the inflow port 30 and the outflow port 40 are opened by the same surface 71 of the pump apparatus main body 7, the connection with the mixing pump apparatus 1 and the exterior is easy. Further, the pump device main body 7 includes a flow path component plate 77 in which the inflow channel 3 and the outflow channel 4 are formed in a groove shape on one surface side, and a seal disposed so as to overlap the one surface side of the path component plate 77. Since the sheet 78 is provided, a large number of flow paths can be formed with respect to the small pump device main body 7, and the mixing pump device 1 can be efficiently produced.

  Furthermore, the configurations of the two inflow passages 3 and the six outflow passages 4 are the same, and the configurations of the inflow side active valve 5 and the outflow side active valve 6 are the same. For this reason, any of the inflow path 3 and the outflow path 4 may be used as the inflow path 3 or the outflow path 4. Therefore, not only two types of liquids but also three or more types of liquids can be mixed and discharged.

(Detailed configuration of pump mechanism)
Hereinafter, an example of the pump mechanism 13 used in the mixing pump device 1 to which the present invention is applied will be described. FIG. 8 is an exploded perspective view of a state in which a mixing pump device to which the present invention is applied is vertically divided. FIGS. 9A and 9B are an explanatory diagram showing a state in which the internal volume of the pump chamber is expanded in the mixing pump device shown in FIG. 8, and an explanatory diagram showing a state in which the internal volume of the pump chamber is contracted. is there. FIGS. 10A, 10B, and 10C are a perspective view, a plan view, and a cross-sectional view, respectively, of a rotor that is used in the rotating body of the pump mechanism shown in FIG. 11A, 11B, and 11C are a perspective view, a plan view, and a cross-sectional view, respectively, of a moving body that is used as a rotating body of the pump mechanism shown in FIG.

  8 and 9A, the pump mechanism 13 according to the present embodiment generally includes a valve body that expands and contracts the internal volume of the pump chamber 2 communicating with the inflow path 3 and the outflow path 4 to suck and discharge liquid. As a diaphragm valve 170 and a driving device 105 for driving the diaphragm valve 170.

  As will be described below, the driving device 105 includes an annular stator 120, a rotating body 103 disposed coaxially inside the stator 120, and a moving body disposed coaxially inside the rotating body 103. 160 and a conversion mechanism 140 that converts the rotation of the rotating body 103 into a force that moves the moving body 160 in the axial direction and transmits the force to the moving body 160. Here, the driving device 105 is mounted between the bottom plate 75 and the base plate 76 in the space formed in the base plate 76.

  In the driving device 105, the stator 120 has a structure in which a unit including a coil 121 wound around a bobbin 123 and two yokes 125 arranged so as to cover the coil 121 is stacked in two stages in the axial direction. ing. In this state, in any of the two upper and lower units, the pole teeth protruding in the axial direction from the inner peripheral edges of the two yokes 125 are alternately arranged in the circumferential direction, and function as a stator of the stepping motor.

  As shown in FIGS. 8, 9, and 10 (a), 10 (b), and 10 (c), the rotating body 103 includes a cup-shaped member 130 that opens upward, and a cylindrical body portion of the cup-shaped member 130. An annular rotor magnet 150 fixed to the outer peripheral surface of 131 is provided. In the center of the bottom wall 133 of the cup-shaped member 130, a concave portion 135 is formed that is recessed upward in the axial direction, and a bearing portion 751 that receives the ball 118 disposed in the concave portion 135 is formed on the bottom plate 75. An annular step 766 is formed on the inner surface on the upper end side of the base plate 76, while the upper end portion of the cup-shaped member 130 is formed by the upper end portion of the body 131 and the annular flange portion 134. An annular stepped portion facing the annular stepped portion 766 on the 76 side is formed, and in the annular space defined by these annular stepped portions, an annular retainer 181 and a position spaced apart in the circumferential direction by the retainer 181 A bearing 180 composed of a bearing ball 182 held on the surface is disposed. In this way, the rotating body 103 is in a state of being supported by the pump device body 7 so as to be rotatable about the axis.

  In the rotating body 103, the outer peripheral surface of the rotor magnet 150 faces the pole teeth arranged in the circumferential direction along the inner peripheral surface of the stator 120. Here, on the outer peripheral surface of the rotor magnet 150, the S pole and the N pole are alternately arranged in the circumferential direction, and the stator 120 and the cup-shaped member 130 constitute a stepping motor.

  As shown in FIGS. 8, 9, and 11 (a), 11 (b), and 11 (c), the moving body 160 includes a bottom wall 161, a cylindrical portion 163 protruding in the axial direction from the center of the bottom wall 161, A cylindrical portion 165 is provided so as to surround the cylindrical portion 163, and a male screw 167 is formed on the outer periphery of the cylindrical portion 165.

  In this embodiment, in configuring the conversion mechanism 140 for reciprocating the moving body 160 in the axial direction by the rotation of the rotating body 103, first, FIG. 8, FIG. 9, FIG. 10 (a), (b), (c ), And FIGS. 11A, 11B, and 11C, on the inner peripheral surface of the body 131 of the cup-shaped member 130, female screws 137 are formed at four locations spaced in the circumferential direction. On the other hand, a male screw 167 that forms a power transmission mechanism 141 by engaging with the female screw 137 of the cup-shaped member 130 is formed on the outer peripheral surface of the body 165 of the moving body 160. Therefore, if the moving body 160 is arranged inside the cup-shaped member 130 so that the male screw 167 and the female screw 137 mesh with each other, the moving body 160 is supported on the inside of the cup-shaped member 130. In addition, six long holes 169 are formed as through holes in the bottom wall 161 of the moving body 160 in the circumferential direction, while six protrusions 769 extend from the base plate 76, and a lower end portion of the protrusion 769. Is fitted in the long hole 169, and the rotation prevention mechanism 149 is configured. That is, when the cup-shaped member 130 is rotated, the moving body 160 is prevented from rotating by the rotation prevention mechanism 149 including the protrusion 769 and the elongated hole 169, and therefore the rotation of the cup-shaped member 130 is caused by the female screw 137. As a result of being transmitted to the moving body 160 via the power transmission mechanism 141 including the male screw 167 of the moving body 160, the moving body 161 is linearly formed on one side and the other side in the axial direction according to the rotation direction of the rotating body 103. Will move.

(Valve structure)
8 and 9A again, in this embodiment, a diaphragm valve 170 is directly connected to the moving body 160. The diaphragm valve 170 has a cup shape including a bottom wall 171, a cylindrical body portion 173 that rises in the axial direction from the outer peripheral edge of the bottom wall 171, and a flange portion 175 that extends from the upper end of the body portion 173 to the outer peripheral side. The center portion of the bottom wall 171 is fixed to the set screw 178 and the cap 179 from above and below in a state where the center portion of the bottom wall 171 covers the cylindrical portion 163 of the moving body 160. Further, the outer peripheral edge of the flange portion 175 of the diaphragm valve 170 is a thick portion that functions as liquid tightness and positioning, and this thick portion is the base around the through hole 21 of the flow path component plate 77. It is fixed between the plate 76 and the flow path constituting plate 77. In this way, the diaphragm 170 defines the lower surface of the pump chamber 2 and ensures liquid tightness between the base plate 76 and the flow path component plate 77 around the pump chamber 2.

  In this state, the body portion 173 of the diaphragm valve 170 is folded back in a U-shaped cross section, and the shape of the folded portion 172 changes depending on the position of the moving body 160. However, in this embodiment, the movable body 160 is configured between the first wall surface 168 formed of the outer peripheral surface of the cylindrical portion 163 and the second wall surface 768 formed of the inner peripheral surface of the protrusion 769 extending from the base plate 76. A folded portion 172 having a U-shaped cross section of the diaphragm valve 170 is disposed in the annular space. Therefore, in any of the state shown in FIGS. 9A and 9B and the state in the middle of the state shown in FIGS. 9A and 9B, the folded portion 172 of the diaphragm valve 170 has an annular space. It is deformed so as to expand or roll up along the first wall surface 168 and the second wall surface 768 while being held inside.

  Further, in this embodiment, as shown in FIGS. 8, 9A, 10A, 10B, and 10C, the bottom wall 133 of the cup-shaped member 130 is 270 ° in the circumferential direction. One groove 136 is formed over the angular range, while a protrusion 166 is formed downward from the bottom surface of the moving body 160. Here, the moving body 160 does not rotate around the axis but moves in the axial direction, whereas the rotating body 103 rotates around the axis but does not move in the axial direction. Accordingly, the protrusion 166 and the groove 136 function as a stopper that defines the stop positions of the rotating body 103 and the moving body 160. That is, the depth of the groove 136 is changed in the circumferential direction, and when the moving body 160 moves downward in the axial direction, the protrusion 166 fits in the groove 136 and the end of the groove 136 is rotated by the rotation of the rotating body 103. Comes into contact with the protrusion 166. As a result, the rotation of the rotating body 103 is blocked, and the stop position of the rotating body 103 and the moving body 160, that is, the maximum expansion position of the inner volume of the diaphragm valve 170 is defined.

(Operation)
In the pump mechanism 13 configured as described above, when the coil 121 of the stator 120 is supplied with power, the cup-shaped member 130 rotates, and the rotation is transmitted to the moving body 160 via the conversion mechanism 140. Therefore, the moving body 160 performs a reciprocating linear motion in the axial direction. As a result, the diaphragm valve 170 is deformed in accordance with the movement of the moving body 160 and expands and contracts the internal volume of the pump chamber 2, so that in the pump chamber 2, the inflow of liquid from the inflow passage 3 and the outflow passage 4 The spill of liquid is directed toward. In the meantime, the folded portion 172 of the diaphragm valve 170 is deformed so as to expand or roll up along the first wall surface 168 and the second wall surface 768 while being held in the annular space, and excessive sliding occurs. do not do. Moreover, even if the diaphragm valve 170 receives pressure from the fluid in the pump chamber 2, the diaphragm valve 170 is not deformed because it is defined both inside and outside in the annular space. Further, the lower position of the moving body 160 is defined by a stopper constituted by the groove 136 of the cup-shaped member 130 and the protrusion 166 of the moving body 160. Therefore, as the cup-shaped member 130 rotates, the diaphragm valve 170 changes its volume with high accuracy. Further, in the driving device 105, when the stepping motor rotates in one direction, the diaphragm valve 170 is driven in a direction in which the internal volume of the pump chamber 2 expands, and when the stepping motor rotates in the other direction, the contents of the pump chamber 2 The diaphragm valve 170 is driven in a direction in which the product is reduced.

  As described above, in the pump mechanism 13 of the present embodiment, the rotating body 103 is rotated by the stepping motor mechanism via the conversion mechanism 140 using the power transmission mechanism 141 including the male screw 167 and the female screw 137. And the movable body 160 to which the diaphragm valve 170 is fixed is reciprocated linearly. For this reason, since the power is transmitted from the driving device 105 to the diaphragm valve 170 with the minimum necessary members, the pump mechanism 13 can be reduced in size, thickness, and cost. Further, the moving body 160 can be finely fed by reducing the lead angle of the male screw 167 and the female screw 137 in the power transmission mechanism 141 or increasing the pole teeth of the driving side stator. Therefore, since the volume of the pump chamber 2 can be strictly controlled, it is possible to perform a quantitative discharge with high accuracy.

  Further, in the present embodiment, the diaphragm valve 170 is used. The folded portion 172 of the diaphragm valve 170 is developed along the first wall surface 168 and the second wall surface 768 while being held in the annular space. Or it deform | transforms so that it may wind up and an excessive sliding does not generate | occur | produce. Therefore, useless load does not occur and the life of the diaphragm valve 170 is long. Further, the diaphragm valve 170 does not deform even when it receives pressure from the fluid in the pump chamber 2. Therefore, according to the pump mechanism 13 of the present embodiment, the quantitative discharge can be performed with high accuracy and the reliability is high.

  Furthermore, since the rotating body 103 is supported by the pump device body 7 so as to be rotatable around the axis via the bearing ball 182, the sliding loss is small and the rotating body 103 is stable in the axial direction. The thrust in the axial direction is stable. Therefore, the drive device 105 can be reduced in size, improved in durability, and improved in discharge performance.

  In the above embodiment, a screw is used as the power transmission mechanism 141 of the conversion mechanism 140, but a cam groove may be used. Furthermore, in the above embodiment, a cup-shaped diaphragm valve is used as the valve body, but a diaphragm valve having another shape or a piston having an O-ring may be used.

  Further, in the above embodiment, an example in which there is one inflow port 80 and eight outflow ports 40 has been described, but a plurality of inflow ports 80 may be provided. Further, each of the inlet 80, the pump mechanism 13, and the outlet 40 may be one or a combination thereof. Moreover, in the said form, although the outflow path 4 was made into equal length, you may arrange | position according to a use without being equal. Further, in the above embodiment, the reflux port 90 is provided, but it may not be necessary. Furthermore, in the above embodiment, the sealing sheet 78 that closes the upper surface and the upper plate 79 to which the pipes are connected are shown separately, but there is no pipe for the upper plate 79 and the sealing sheet 78 has an outflow hole. It is also possible to configure such that only the opening is opened and the connection is made via a seal member.

[Configuration of active valve]
FIG. 12 and FIG. 13 are explanatory views when the main parts of the valves used as the active valves 5 and 6 of the mixing pump device 1 to which the present invention is applied are cut in the axial direction and viewed from obliquely above. It is explanatory drawing which shows magnetic field lines.

  As shown in FIGS. 12 and 13, the active valves 5 and 6 include a linear actuator 201 in the holes 57 and 67 a to 67 h of the base plate 76. The linear actuator 201 includes a cylindrical fixed body 203 and the linear actuator 201. The movable body 205 has a substantially cylindrical shape and is disposed inside the fixed body 203. The fixed body 203 includes a coil 233 that is wound around the bobbin 231 in an annular shape, and wraps around both sides in the axial direction of the coil 233 from the outer peripheral surface of the coil 233 so that one tip portion 236a and the other tip portion 236b of the coil 233 The fixed body side yoke 235 which opposes in an axial direction through the slit 237 on the inner peripheral side is provided. The movable body 205 includes a disk-shaped first movable body side yoke 251 and a pair of magnets 253a and 253b stacked on both sides in the axial direction with respect to the first movable body side yoke 251. As the pair of magnets 253a and 253b, Nd—Fe—B or Sm—Co rare earth magnets or resin magnets can be used. Further, in the movable body 205, the second movable body side yokes 255a and 255b are laminated on the end surface opposite to the first movable body side yoke 251 in each of the pair of magnets 253a and 253b.

  In this embodiment, each of the pair of magnets 253a and 253b is magnetized in the axial direction, and has the same polarity toward the first movable body side yoke 251. Hereinafter, in this embodiment, the pair of magnets 253a and 253b will be described as having the N pole facing the first movable body side yoke 251 and the S pole facing the outside in the axial direction. Vice versa.

  Here, the outer peripheral surface of the first movable body side yoke 251 projects from the outer peripheral surface of the pair of magnets 253a and 253b to the outer peripheral side. Further, the outer peripheral surfaces of the second movable body side yokes 255a and 255b also protrude from the outer peripheral surfaces of the pair of magnets 253a and 253b to the outer peripheral side.

  The first movable body side yoke 251 has recesses on both end surfaces in the axial direction, and a pair of magnets 253a and 253b are fitted into these recesses and fixed with an adhesive or the like. Note that the first movable body side yoke 251, the pair of magnets 253a, 253b, and the second movable body side yokes 255a, 255b can be fixed by bonding, press-fitting, or by combining them together. Good.

  Bearing plates 271a and 271b (bearing members) are fixed to openings on both sides in the axial direction of the fixed body 203, and support shafts 257a projecting from the second movable body side yokes 255a and 255b to both sides in the axial direction. 257b is slidably inserted into the holes of the bearing plates 271a and 271b. In this way, the movable body 205 is supported by the fixed body 203 so as to be capable of reciprocating in the axial direction. In this state, the movable body 205 has an outer peripheral surface facing the inner peripheral surface of the fixed body 203 via a predetermined gap, and the distal end portions 236a and 236b of the fixed body side yoke 235 are the first movable body side yoke. In the gap between the outer peripheral surface of 251 and the inner peripheral surface of the coil 233, it is in a state of facing in the axial direction. A gap is secured between the movable body 205 and the fixed body side yoke 235. For fixing the second movable body side yokes 255a and 255b and the support shafts 257a and 257b, a configuration in which they are integrated by bonding, press-fitting, or a combination thereof may be adopted.

  In the linear actuator 201 configured as described above, a period in which a current flows from the far side to the near side on the right side in the drawing and a current flows in the coil 33 from the near side to the far side on the left side in the drawing. Then, the magnetic field lines are expressed as shown in FIG. Therefore, the movable body 5 first receives a thrust in the axial direction by the Lorentz force and moves as indicated by an arrow A. On the other hand, when the energization direction to the coil 233 is reversed, the movable body 205 descends along the axial direction as indicated by an arrow B.

  In the linear actuator 201 of this embodiment, the movable body 205 is propelled by a magnetic force, and on one side in the axial direction, a truncated cone as a biasing member is provided between the bearing plate 271a and the second movable body side yoke 255a. Therefore, when the movable body 205 descends, it moves while deforming the compression spring, and when the movable body 205 rises, the shape return force of the compression spring assists. And move at high speed.

  In the linear actuator 201 configured as described above, in this embodiment, the central portion of the diaphragm valve 260 disposed in the valve chamber 270 (the recesses 68a to 68h) is connected to the end portion of the one support shaft 257b. An annular thick portion 261 that functions as liquid tightness and positioning is formed on the outer peripheral side of the diaphragm valve 260. In the diaphragm valve 260, the outer peripheral side including the annular thick portion 261 is the base plate 76 and the flow path configuration. Liquid tightness is ensured by being sandwiched between the plates 77.

  In addition, about a valve body, you may use not only the diaphragm valve 260 but a bellows valve and another valve body. Further, the support shafts 257a and 257b and the valve body may be configured as separate members, or the support shafts 257a and 257b and the valve body may be formed integrally.

  As described above, in this embodiment, in the movable body 205, the pair of magnets 253a and 253b are directed to the same pole, and a magnetic repulsive force is acting, but the first between the magnets 253a and 253b. Since the movable body side yoke 251 is disposed, the pair of magnets 253a and 253b can be fixed with the same poles directed.

  Further, in the movable body 205, the pair of magnets 253a and 253b have the same polarity directed to the first movable body side yoke 251, and thus a strong magnetic flux is generated in the radial direction from the first movable body side yoke 251. Therefore, if the peripheral surfaces of the first movable body side yoke 251 and the coil 233 are opposed to each other, a large thrust can be applied to the movable body 205.

  Furthermore, since the magnets 253a and 253b may be magnetized in the axial direction, unlike the case where the magnets 253a and 253b are magnetized in the radial direction, the magnets can be easily magnetized even when downsized, and are suitable for mass production. .

  In addition, in this embodiment, since the outer peripheral surface of the first movable body side yoke 251 protrudes from the outer peripheral surface of the pair of magnets 253a and 253b to the outer peripheral side, even when the fixed body side yoke 235 is provided, On the other hand, the magnetic attractive force acting in the direction perpendicular to the axial direction can be reduced. Similarly, since the outer peripheral surface of the second movable body side yoke 255a, 255b projects outward from the outer peripheral surface of the pair of magnets 253a, 253b, even when the fixed body side yoke 235 is provided, Thus, the magnetic attractive force acting in the direction perpendicular to the axial direction can be reduced. Therefore, there is an advantage that the assembly work is easy to perform and the movable body 205 is not easily tilted.

  Further, in this embodiment, since the magnets 253a and 253b are arranged on the outer peripheral side of the coil 33, the magnets 253a and 253b may be smaller than the case where the magnets 253a and 253b are arranged outside the coil 233. The valves 5 and 6 can be configured at low cost. Moreover, since the coil 233 is disposed outside, the magnetic path can be closed only by the fixed side yoke.

  Furthermore, in the fixed body 203, bearing plates 271a and 271b that support the support shafts 257a and 257b so as to be movable in the axial direction are held in the opening portion that opens in the axial direction. There is no. Further, since the bearing plates 271a and 271b can be fixed on the basis of the fixed body 203, there is an advantage that the support shafts 257a and 257b do not tilt.

[Use of mixing pump device]
The mixing pump device 1 to which the present invention is applied can be used, for example, in a direct methanol fuel cell (hereinafter referred to as DMFC) that generates electricity by directly extracting protons from methanol. Such a DMFC includes an electromotive device having an electromotive unit (cell) and a liquid feed pump that pumps a methanol aqueous solution, and the cell has an anode electrode having an anode current collector and an anode catalyst layer ( Fuel electrode), a cathode electrode (air electrode) having a cathode current collector and a cathode catalyst layer, and an electrolyte membrane disposed between the anode electrode and the cathode electrode. An aqueous methanol solution is supplied to the anode electrode by a liquid feed pump, and air is supplied to the cathode electrode by an air supply pump or a blower. Therefore, if the mixing pump apparatus 1 to which the present invention is applied is used as a liquid feed pump, methanol and water, methanol and methanol aqueous solution, methanol aqueous solution and water, methanol aqueous solution are appropriately mixed, and methanol concentration is adjusted. An aqueous solution can be supplied to the cell. In addition, at the anode electrode of the cell that is the electromotive part of the DMFC, the activity of methanol oxidation is low and a voltage loss occurs. There is also a voltage loss at the cathode electrode. For this reason, the output that can be extracted from one cell is extremely low, and in order to obtain a predetermined output, a plurality of cells are used in the DMFC. Even in such a case, if the mixing pump device 1 to which the present invention is applied is used, a methanol aqueous solution with adjusted methanol concentration can be supplied to each cell.

  Moreover, the use of the mixing pump device 1 to which the present invention is applied is not limited to the fuel cell. For example, the mixing pump device 1 can be used as a pump for preparing a compound medicine by preparing a plurality of chemical solutions. Furthermore, it may be used as an ice making pump for a refrigerator and used to discharge a sherbet liquid having a different taste, color and fragrance from the outflow passage for each ice making block.

[Other embodiments]
In the above embodiment, the example in which the diaphragm valve 170 is used as the valve body 17 has been mainly described. However, the present invention may be applied to a mixing pump apparatus using a plunger as the valve body. In the above embodiment, a plurality of outflow passages 4 are configured. However, the present invention may be applied to a mixing pump apparatus having one outflow passage 4.

  Moreover, in the said form, although this invention was applied to the mixing pump apparatus, you may apply this invention to the metering pump which discharges one type of liquid.

It is a conceptual diagram which shows the basic composition of the mixing pump apparatus to which this invention is applied. (A), (b) is a timing chart figure which shows operation | movement of the mixing pump apparatus shown in FIG. 1, and explanatory drawing which shows the relationship between the position of a valve body, and resolution | decomposability. (A)-(d) is explanatory drawing regarding a deformation | transformation of a diaphragm valve. It is a conceptual diagram which shows the basic composition of the mixing pump apparatus to which this invention is applied. (A), (b) is the perspective view of the mixing pump apparatus to which this invention is applied, and explanatory drawing which shows the flow path etc. planarly. It is a disassembled perspective view when the mixing pump apparatus which concerns on embodiment of this invention is seen from diagonally upward. It is explanatory drawing which shows the cross-sectional structure of the mixing pump apparatus which concerns on embodiment of this invention. It is a disassembled perspective view of the state which divided the mixing pump device to which the present invention is applied vertically. (A), (b) is explanatory drawing which shows the state which expanded the internal volume of the pump chamber in the mixing pump apparatus shown in FIG. 8, and explanatory drawing which shows the state which shrunk the internal volume of the pump chamber. (A), (b), (c) is the perspective view, top view, and sectional drawing of the rotor which were respectively used for the rotary body of the pump mechanism shown in FIG. (A), (b), (c) is respectively the perspective view, top view, and sectional drawing of the moving body used for the rotary body of the pump mechanism shown in FIG. It is explanatory drawing when what cut | disconnected the principal part of the valve | bulb used as the passive valves 5 and 6 of the mixing pump apparatus to which this invention was cut | disconnected in the axial direction from diagonally upward. It is explanatory drawing which shows the magnetic force line of the valve | bulb shown in FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Mixing pump apparatus 2 Pump chamber 3 Inflow path 4 Outflow path 5 Inflow side active valve 6 Outflow side active valve 7 Pump apparatus main body 12 Stepping motor 13 Pump mechanism 17 Valve body 105 Drive apparatus 170 Diaphragm valve (valve body)

Claims (11)

A pump chamber, a valve element disposed in the pump chamber, an inflow path communicating with the pump chamber, an outflow path communicating with the pump chamber, and a plurality of disposed in each of the inflow path and the outflow path A fluid suction step from the inflow passage to the pump chamber and a fluid discharge step from the pump chamber to the outflow passage by driving the valve body and opening and closing the plurality of valves. In the driving method of the pump device to be performed,
When at least one of switching from the suction process to the discharge process and switching from the discharge process to the suction process, a correction process for closing the plurality of valves and moving the position of the valve body is performed. A driving method of a pump device.   2. The method of driving a pump device according to claim 1, wherein the correction step is performed both when the suction step is switched to the discharge step and when the discharge step is switched to the suction step.   3. The driving method of a pump device according to claim 1, wherein the valve body is a diaphragm valve. In any one of Claims 1 thru | or 3, in the said correction process at the time of switching from the said suction process to the said discharge process, the said valve body is moved to the direction which reduces the internal volume of the said pump chamber,
In the correction step when switching from the discharge step to the suction step, the valve body is moved in a direction to increase the internal volume of the pump chamber.   4. The method according to claim 1, wherein in the correction step, immediately after the correction step, the valve body is moved in a direction to eliminate a pressure difference between both sides sandwiching a valve that is switched from a closed state to an open state. A driving method of a pump device.   6. The valve according to claim 5, wherein the valve is switched from a closed state to an open state when switching from the suction step to the discharge step, and the valve is switched from a closed state to an open state when switching from the discharge step to the suction step. A method for driving a pump device, comprising: directly or indirectly monitoring a pressure difference between both sides sandwiching at least one of the valves, and performing the correction step based on a monitoring result of the pressure difference.   6. The driving method for a pump device according to claim 1, wherein the correction step is performed under a preset condition. In any one of Claims 1 thru | or 7, While the said inflow path is formed in multiple numbers, the said valve | bulb is arrange | positioned at each of the said some inflow path,
In the suction step, fluid is sequentially sucked into the pump chamber from each of the plurality of inflow passages, and in the discharge step, the fluid mixed in the pump chamber is discharged from the outflow passage. Driving method.   In Claim 8, Before the fluid with the lowest mixing ratio flows into the pump chamber among the plurality of fluids flowing in from the plurality of inflow paths, at least a part of the fluid with the higher mixing ratio than the fluid is A method for driving a pump device, wherein the pump device is caused to flow into a pump chamber. In any one of Claims 1 thru | or 9, While the said outflow path is formed in multiple numbers, the said valve | bulb is arrange | positioned at each of the said several outflow paths,
In the discharging step, a fluid is sequentially discharged from the plurality of outflow passages.   11. The driving method of a pump device according to claim 1, wherein the outflow passage supplies an aqueous methanol solution toward an electromotive portion of the fuel cell.

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