US20090123299A1 - Method for Driving a Pump Device - Google Patents

Method for Driving a Pump Device Download PDF

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Publication number
US20090123299A1
US20090123299A1 US12/083,990 US8399007A US2009123299A1 US 20090123299 A1 US20090123299 A1 US 20090123299A1 US 8399007 A US8399007 A US 8399007A US 2009123299 A1 US2009123299 A1 US 2009123299A1
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United States
Prior art keywords
pump chamber
suctioning
discharging
fluid
pump
Prior art date
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Abandoned
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US12/083,990
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English (en)
Inventor
Mitsuo Yokozawa
Kenji Muramatsu
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Panasonic Corp
Nidec Instruments Corp
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Individual
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Filing date
Publication date
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Assigned to MATSUSHITA ELECTRIC INDUSTRIAL CO., LTD., NIDEC SANKYO CORPORATION reassignment MATSUSHITA ELECTRIC INDUSTRIAL CO., LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: YOKOZAWA, MITSUO, MURAMATSU, KENJI
Publication of US20090123299A1 publication Critical patent/US20090123299A1/en
Assigned to PANASONIC CORPORATION reassignment PANASONIC CORPORATION CHANGE OF NAME (SEE DOCUMENT FOR DETAILS). Assignors: MATSUSHITA ELECTRIC INDUSTRIAL CO., LTD.
Abandoned legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B13/00—Pumps specially modified to deliver fixed or variable measured quantities
    • F04B13/02—Pumps specially modified to deliver fixed or variable measured quantities of two or more fluids at the same time
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
    • B01F—MIXING, e.g. DISSOLVING, EMULSIFYING OR DISPERSING
    • B01F25/00—Flow mixers; Mixers for falling materials, e.g. solid particles
    • B01F25/40—Static mixers
    • B01F25/45—Mixers in which the materials to be mixed are pressed together through orifices or interstitial spaces, e.g. between beads
    • B01F25/451—Mixers in which the materials to be mixed are pressed together through orifices or interstitial spaces, e.g. between beads characterised by means for moving the materials to be mixed or the mixture
    • B01F25/4512—Mixers in which the materials to be mixed are pressed together through orifices or interstitial spaces, e.g. between beads characterised by means for moving the materials to be mixed or the mixture with reciprocating pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B43/00—Machines, pumps, or pumping installations having flexible working members
    • F04B43/02—Machines, pumps, or pumping installations having flexible working members having plate-like flexible members, e.g. diaphragms
    • F04B43/04—Pumps having electric drive
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/06—Control using electricity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B2207/00—External parameters
    • F04B2207/04—Settings
    • F04B2207/042—Settings of pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type
    • F05B2210/11—Kind or type liquid, i.e. incompressible
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S417/00—Pumps
    • Y10S417/902—Hermetically sealed motor pump unit

Definitions

  • the present invention relates to a method for driving a pump device such as a diaphragm pump, which suctions fluid form its intake port and discharges fluid from its discharge port by casing displacement of a displacing member defining a part of a pump chamber.
  • One mixing pump device known in the art for mixing a plurality of fluids in prescribed proportions is an apparatus designed to suction a plurality of fluids into a single pump chamber, mix them in the pump chamber to form a mixed fluid, then discharge the mixed fluid from the pump chamber.
  • Patent Citation 1 discloses a mixing pump device in a high-performance liquid chromatography device, for suctioning in and mixing several types of solvents with a plunger pump, and discharging the mixed fluid obtained thereby to the column.
  • the mixing pump device disclosed therein is designed to transmit rotation of a stepping motor to the plunger via a cam mechanism, increasing or decreasing the internal volume of the pump chamber.
  • valves positioned on each of two inflow passages communicating with the pump chamber are opened in sequence, and the fluids are suctioned via the inflow passages into the pump chamber where they are mixed. Subsequently, a discharge process is carried out, constricting the pump chamber and discharging the mixed liquid.
  • a pressure differential may arise between the internal pressure of the pump chamber, and the pressure on the inflow passages currently partitioned off by the valves. Where such a pressure differential exists, if a valve that was closed is then opened, there will be a temporary backflow of fluid, the intake of the two types of fluid drawn into the pump chamber via the inflow passages will change, and their mixture ratio will fluctuate.
  • An object of the present invention is to provide a method for driving a pump device able to eliminate instability of the fluid intake operation and fluid discharge operation during switching between the discharging step and the suctioning step.
  • the method for driving a pump device of the present invention comprises a suctioning step for suctioning a fluid into a pump chamber from an intake port by inducing displacement of a displacing member that defines part of an inside peripheral surface of the pump chamber in the direction of increasing internal volume of the pump chamber, with the discharge port of the pump chamber closed and the intake port open; a discharging step for discharging the fluid from the pump chamber by inducing displacement of the displacing member in the direction of decreasing internal volume of the pump chamber, with the discharge port open and the intake port closed; and a correcting step for inducing displacement of the displacing member with both the intake port and the discharge port of the pump chamber closed.
  • the steps are carried out in the order of suctioning, correcting, and discharging; or in the order of discharging, correcting, and suctioning.
  • a correcting step is executed subsequent to completion of the discharging step, followed thereafter by switchover to the suctioning step.
  • a correcting step is executed subsequent to completion of the suctioning step, followed thereafter by switchover to the discharging step.
  • the correcting step since the displacing member undergoes displacement while the intake port and the discharge port are closed, an increase or decrease in the internal volume of the pump chamber occurs in a hermetic state, and the internal pressure of the pump chamber changes in association therewith. Consequently, through appropriate setting of the direction of displacement and the displacement level of the displacing member, it is possible to eliminate the difference between the internal pressure of the pump chamber and the pressure on the fluid discharge end of the discharge port.
  • the correcting step will preferably be carried out both during switchover from the suctioning step to the discharging step, and during switchover from the discharging step to the suctioning step.
  • the correcting step executed between the suctioning step and the discharging step it is possible for example to induce displacing movement of the displacing member in the direction for reducing the internal volume of the pump chamber; and in the correcting step executed between the discharging step and the suctioning step, conversely, to induce displacement of the displacing member in the direction for increasing the internal volume of the pump chamber.
  • displacement of the displacing member is induced so as to eliminate the difference between the internal pressure of the pump chamber and the pressure on the fluid discharge flow passage communicating with the discharge port.
  • displacement of the displacing member is induced so as to eliminate the difference between the internal pressure of the pump chamber and the pressure on the fluid intake flow passage communicating with the intake port.
  • the difference between the internal pressure of the pump chamber and the pressure on the fluid discharge flow passage communicating with the discharge port can be monitored, and displacement of the displacing member induced on the basis of the results of the monitoring.
  • the difference between the internal pressure of the pump chamber and the pressure on the fluid intake flow passage communicating with the intake port can be monitored, and displacement of the displacing member induced on the basis of the results of the monitoring.
  • a plurality of the intake ports may be formed in the pump chamber; and during the suctioning step, an intake operation involving sequentially opening the closed plurality of intake ports and taking in fluid is performed repeatedly, forming a mixed fluid in which the different types of fluids are mixed in predetermined proportions.
  • a plurality of the discharge ports may be formed in the pump chamber; and during the discharging step, the closed plurality of discharge ports may be opened sequentially and the fluid discharged.
  • the actuating method of the present invention is effective when implemented in a pump device constituted with a diaphragm pump in which the displacing member is a diaphragm.
  • the internal volume of the pump chamber can be increased or decreased with accurate response to displacement of the diaphragm during the suctioning step or the discharging step, whereby the fluid intake operation and the fluid discharge operation can be carried out properly.
  • FIG. 1 is a conceptual diagram showing the basic configuration of a mixing pump device embodying the present invention
  • FIG. 2A and FIG. 2B are respectively a timing chart depicting operation of the mixing pump device shown in FIG. 1 , and a descriptive diagram depicting the relationship of the position of the piston to resolution;
  • FIGS. 3A to 3D are descriptive diagrams relating to deformation of a diaphragm
  • FIG. 4 is a conceptual diagram showing the basic configuration of a mixing pump device embodying the present invention.
  • FIG. 5A and FIG. 5B are respectively a perspective view of a mixing pump device embodying the present invention, and a descriptive diagram showing the flow passages thereof in plan view;
  • FIG. 6 is an exploded perspective view of the mixing pump device of FIG. 5 , viewed from diagonally above;
  • FIG. 7 is a descriptive diagram showing in cross section the configuration of the mixing pump device of FIG. 5A ;
  • FIG. 8 is an exploded perspective view of the mixing pump device of FIG. 5A , shown divided on the vertical;
  • FIG. 9A and FIG. 9B are respectively a descriptive diagram of the pump chamber in a state of expanded internal volume, and the pump chamber in a state of contracted internal volume, in the mixing pump device of FIG. 8 ;
  • FIGS. 10A to 10C are respectively a perspective view, a plan view, and a sectional view of a rotor employing the rotating body of the pump mechanism shown in FIG. 8 ;
  • FIGS. 11A to 11C are respectively a perspective view, a plan view, and a sectional view of a moving body employing the rotating body of the pump mechanism shown in FIG. 8 ;
  • FIG. 12 is a descriptive diagram of the principal parts of a valve used for the active valves 5 , 6 of the mixing pump device embodying the invention, shown cut along the axis and viewed from diagonally above; and
  • FIG. 13 is a descriptive diagram of the lines of magnetic force of the valve shown in FIG. 12 .
  • FIG. 1 is a conceptual diagram showing the basic configuration of a mixing pump device embodying the present invention.
  • the mixing pump device 1 has a pump chamber 2 .
  • the pump chamber 2 there are formed a plurality (two, in this example) of intake ports 30 a , 30 b ; and a plurality (two, in this example) of discharge ports 40 a , 40 b .
  • the intake ports 30 a , 30 b communicate respectively with inflow passages 3 a , 3 b ; and the discharge ports 40 a , 40 b communicate respectively with outflow passages 4 a , 4 b .
  • the pump device main unit 7 is made up of the pump chamber 2 , the intake ports 30 a , 30 b , the discharge ports 40 a , 40 b , the inflow passages 3 a , 3 b , and the outflow passages 4 a , 4 b.
  • Inflow-side active valves 5 a , 5 b for individually opening and closing the intake ports 30 a , 30 b are disposed in these ports.
  • Outflow-side active valves 6 a , 6 b for individually opening and closing the discharge ports 40 a , 40 b are disposed in these ports.
  • These inflow-side active valves 5 a , 5 b and outflow-side active valves 6 a , 6 b are opened and closed by means of a control unit 18 .
  • a portion of the inside peripheral surface of the pump chamber 2 is defined by a displacing member 17 such as a piston or diaphragm.
  • the displacing member 17 is displaceable in the outward and inward direction of the pump chamber; in the present example, the displacing member 17 undergoes displacement by means of a drive unit 105 equipped with a stepping motor 12 .
  • the pump drive mechanism 13 is composed of this displacing member 17 and drive unit 105 .
  • the displacing member 17 When the stepping motor 12 of the drive unit 105 turns in one direction, the displacing member 17 is displaced in the direction A of increasing internal volume of the pump chamber 2 ; and when the stepping motor 12 turns in the opposite direction, the displacing member 17 is displaced in the direction B of decreasing internal volume of the pump chamber 2 .
  • the displacing member 17 undergoes displacement towards direction A by means of the drive unit 105 , thereby suctioning a fluid LB into the pump chamber 2 from the inflow passage 3 b via the intake port 30 b .
  • the displacing member 17 undergoes displacement towards direction B via the drive unit 105 , thereby discharging the mixed fluid from the pump chamber 2 into the outflow passage 4 a via the discharge portion 40 a .
  • the mixed fluid can be discharged to the outflow passage 4 b from the other discharge port 40 b.
  • a correcting step is executed in the interval between the suctioning step and the discharging step.
  • FIGS. 2A and 2B are respectively a timing chart depicting operation of the mixing pump device shown in FIG. 1 , and a descriptive diagram depicting the relationship of the position of the displacing member to resolution.
  • the operation of the mixing pump device 1 will be described in detail with reference to FIG. 2A .
  • the proportion of inflow (mixture proportion) of the first fluid LA and the second fluid LB taken in via the two inflow passages 3 a , 3 b is assumed to be 1:5.
  • the uppermost level shows the intake operation and discharge operation by the pump drive mechanism 13 ;
  • the intake operation by the pump drive mechanism 13 is accomplished, for example, by clockwise rotation of the stepping motor 12 displacing the displacing member 17 in the direction A of increasing the internal volume of the pump chamber 2 (see FIG. 1 ).
  • the discharge operation by the pump drive mechanism 13 is accomplished, for example, by counterclockwise rotation of the stepping motor 12 displacing the displacing member 17 in the direction B of decreasing the internal volume of the pump chamber 2 (see FIG. 1 ).
  • the pump drive mechanism 13 is halted via suspending the power supply to the stepping motor 12 .
  • the inflow-side active valves 5 a , 5 b and the outflow-side active valves 6 a , 6 b all assume the open state once a positive pulse has been input, switching to the closed state at the point in time that a negative pulse is input. Once a negative pulse has been input, the valves assume the closed state once a positive pulse has been input, switching to the open state at the point in time that a negative pulse is input.
  • FIG. 2A first, at time t 1 , power to the stepping motor 12 is suspended, and the pump drive mechanism 13 comes to a stop. At time t 1 , all of the active valves 5 a , 5 b , 6 a , 6 b are in the closed state.
  • the inflow-side active valve 5 a is switched from the open state to the closed state.
  • the flow of the liquid LA into the pump chamber 2 from the inlet passage 3 a halts.
  • the total inflow amount of the liquid LA is drawn into the pump chamber 2 .
  • the inflow-side active valve 5 b only is again switched to the open state, and at time t 8 power is supplied to the stepping motor 12 , whereupon the stepping motor 12 rotates in the same direction (clockwise).
  • the displacing member 17 is thereby displaced further in the same direction (the direction of increasing the internal volume of the pump chamber 2 ), and the fluid LB flows into the pump chamber 2 from the inlet passage 3 b .
  • time t 9 following input of a 125-step pulse to the stepping motor 12 , power to the stepping motor 12 is suspended, and the displacing member 17 comes to a halt as well.
  • the inflow-side active valve 5 b is switched from the open state to the closed state.
  • the flow of the liquid LB into the pump chamber 2 from the inlet passage 3 b halts.
  • the remaining one-half of the total inflow amount of the liquid LB is drawn into the pump chamber 2 .
  • the correcting step is executed, followed by switchover to the discharging step.
  • the correcting step will be discussed later; first, a description of the discharging step starting at time t 11 shall be provided.
  • the outflow-side active valve 6 a is switched from the open state to the closed state.
  • the mixed liquid is discharged from the outflow passage 4 a , in an amount equivalent to one-half the liquid that has flowed into the pump chamber 2 .
  • the correcting step is executed, and the operation concludes.
  • the outflow-side active valve 6 b is switched from the open state to the closed state.
  • the mixed liquid is discharged from the outflow passage 4 b , in an amount equivalent to one-half the liquid that has flowed into the pump chamber 2 .
  • the correcting step is executed, and the operation concludes.
  • a diaphragm is employed as the displacing member 17 , delayed response to displacement tends to occur at top dead center and bottom dead center, where the direction of displacement of the diaphragm changes.
  • the shape of the diaphragm is susceptible to a pressure difference between the internal pressure of the pump chamber 2 and atmospheric pressure. This point shall be discussed with reference to FIGS. 3A to 3D .
  • the diaphragm 170 will not experience any unintended displacement due to a pressure difference.
  • the diaphragm 170 becomes distended due to the pressure difference.
  • the diaphragm 170 becomes constricted by the equivalent of the pressure difference.
  • the outflow-side active valve 6 a is opened at time t 11 and the pump chamber 2 now communicates with the outflow passage 4 a to the outflow port 40 a end thereof with respect to the valve 6 a , there is a risk that the mixed fluid in the outflow passage 4 a on the outflow port 40 a end thereof will backflow into the pump chamber 2 due to the differential head. If such a condition occurs, the discharged amount of the mixed liquid will be less than the intended amount. If in the condition depicted in FIG.
  • the inflow-side active valve 5 b is opened at time t 1 and the pump chamber 2 now communicates with the inflow passage 3 b to the outflow inflow port 30 b end thereof with respect to the valve 5 b , the mixed liquid in the pump chamber 2 will backflow from the inflow passage 3 b , and the inflowing amount of the second liquid LB will be less than the intended amount.
  • a correcting step for the purpose of correcting the position of the displacing member 17 is executed during switchover from the suctioning step to the discharging step, and during switchover from the discharging step to the suctioning step.
  • the displacing member 17 undergoes displacement to a slight extent in the direction for reducing the internal volume of the pump chamber 2
  • the displacing member 17 undergoes displacement to a slight extent in the direction for increasing the internal volume of the pump chamber 2 .
  • valves 5 a , 5 b , 6 a , 6 b and the displacing member 17 can be actuated under control by the control unit 18 , in accordance with preestablished conditions.
  • Direct monitoring of the pressure difference between locations to either side of the valves 5 b , 6 a may be accomplished by positioning pressure sensors in the pump chamber 2 , at a location in the inflow passage 3 b to the outside of the valve 5 b , and at a location in the outflow passage 4 a to the outside of the valve 6 a , and detecting pressure difference on the basis of detection results of these pressure sensors.
  • Indirect monitoring of the pressure difference between locations to either side of the valves 5 b , 6 a may be accomplished by measuring the height location of the outflow port 40 a of the outflow passage 4 a , and monitoring the level of the second liquid LB shown in FIG. 3D .
  • a plurality of fluids can be suctioned into the pump chamber 2 in prescribed proportions simply by closing the active valves 6 a , 6 b positioned on the outflow passages 4 a , 4 b , and sequentially opening and closing the active valves 5 a , 5 b positioned on the inflow passages 3 a , 3 b .
  • the mixed fluid can be discharged from the pump chamber 2 simply by closing the active valves 5 a , 5 b positioned on the inflow passages 3 a , 3 b , and opening one or both of the active valves 6 a , 6 b positioned on the outflow passages 4 a , 4 b .
  • a mechanism which transmits rotation of the stepping motor 12 to the displacing member 17 via a cam mechanism there is no need to monitor cam position with a photointerrupter or the like. It is therefore possible to simplify the design of the mixing pump device 1 , and make it smaller and less expensive.
  • the control unit 18 controls opening and closing of the active valves 5 a , 5 b , 6 a , 6 b in such a way that, of the first liquid LA and the second liquid LB which inflow from the inflow passages 3 a , 3 b , a portion of the second liquid LB having the larger mixture proportion flows into the pump chamber 2 prior to suctioning in the first liquid LA having the smaller mixture proportion. It is therefore possible to prevent the first liquid LA from becoming unevenly distributed in a corner of the pump chamber 2 , e.g. in proximity to the active valve 5 a , so as to achieve thorough mixing of the first liquid LA and the second liquid LB.
  • more thorough mixing of the first liquid LA and the second liquid LB can be achieved because an amount equivalent to one-half of the total amount of the second liquid LB having the larger mixture proportion is suctioned into the pump chamber 2 , then the first liquid LA having the smaller mixture proportion is suctioned into the pump chamber 2 , and finally the remaining one-half of the second liquid LB is suctioned into the pump chamber 2 .
  • the correcting step is executed during the interval from time t 10 to time t 11 , and during the interval from time t 17 to time t 18 . Even where the displacing member 17 has reached top dead center or bottom dead center, it will return from the top dead center or bottom dead center and perform intake or discharge. Accuracy of the intake amount and discharge amount is accordingly high.
  • the displacing member 17 is a diaphragm
  • the displacing member 17 is a diaphragm
  • a pressure differential between the internal pressure of the pump chamber 2 and atmospheric pressure can produce unwanted deformation of the diaphragm. Since intake and discharge are carried out after correcting such deformation by executing the correcting step, accuracy of the intake amount and discharge amount is high.
  • the pump device main unit 7 of the mixing pump device 1 A of the present example has a pump chamber 2 , two inflow passages 3 a , 3 b communicating with the pump chamber 2 , and six outflow passages 4 a through 4 f communicating with the pump chamber 2 .
  • the two inflow passages 3 a , 3 b and the six outflow passages 4 a through 4 f communicate mutually independently with the pump chamber 2 .
  • Inflow-side active valves 5 a , 5 b are positioned respectively on the two inflow passages 3 a , 3 b .
  • Outflow-side active valves 6 a through 6 f are positioned respectively on the six outflow passages 4 a through 4 f.
  • the pump drive mechanism 13 has a diaphragm 170 that defines a portion of the inside peripheral surface of the pump chamber 2 ; a drive unit 105 equipped with a stepping motor 12 for displacing this diaphragm 170 ; and a control unit 18 for controlling opening and closing of the inflow-side active valves 5 a , 5 b and the outflow-side active valves 6 a through 6 f.
  • FIG. 5A and FIG. 5B are respectively a perspective view and a plan view of the mixing pump device 1 A.
  • FIG. 6 is an exploded perspective view thereof;
  • FIG. 7 is a descriptive diagram showing the configuration thereof in cross section.
  • the mixing pump device 1 A has pipes defining intake ports 30 a , 30 b and discharge ports 40 a through 40 f connected to one face 71 of the pump device main unit 7 which is in the shape of a box.
  • the pump device main unit 7 has a stacked structure composed, in order, of a circuit board 74 for the pump drive mechanism 13 and the active valves 5 a , 5 b , 6 a through 6 f ; a bottom plate 75 ; a base plate 76 ; a flow passage formation plate 77 having formed thereon flow passages of channel shape to be described later; a sealing sheet 78 for sealing off the upper sides of the flow passages via covering the upper face of the flow passage formation plate; and an upper plate 79 to which the aforementioned pipes are connected.
  • Holes 137 , 67 a through 67 h providing installation spaces for the pump drive mechanism 13 and for the active valves 5 a , 5 b , and 6 a through 6 f are formed in the base plate 76 .
  • a round through-hole 21 constituting the pump chamber 2 is formed at a central location in the flow passage formation plate 77 ; and around this through-hole 21 , on the lower face of the flow passage formation plate 77 , are formed recesses (not shown) constituting the valve chambers of the active valves 5 a , 5 b , 6 a through 6 f
  • Eight channels 41 a through 41 h extend radially out from the through-hole 21 . Additional channels 42 a , 42 b . . . , etc. are formed in proximity to the channels 41 a through 41 h of the flow passage formation plate 77 .
  • the inflow passages 3 a , 3 b and the outflow passages 4 a through 4 f are formed by the eight channels 41 a through 41 h .
  • the inflow passages 3 a , 3 b and the outflow passages 4 a through 4 f are formed by the channels 41 a through 41 f , 42 a , 42 b . . . ; and the inflow-side active valves 5 a , 5 b and the outflow-side active valves 6 a through 6 f are positioned in the individual inflow passages 3 a , 3 b and outflow passages 4 a through 4 f.
  • the active valves 5 a , 5 b , 6 a through 6 f are positioned in a plane around the pump chamber 2 , the flow passages in the individual inflow passages 3 a , 3 b and the outflow passages 4 a through 4 f are short, and the mixing pump device 1 A can have a thin profile. Additionally, since variation in the amount discharged from the outflow passages 4 a through 4 f can be minimized, fluids can be discharged accurately in the proper amounts. Moreover, the length of the flow passage from the pump chamber 2 to the outflow-side active valves 6 a through 6 f is the same in each of the plurality of outflow passages 4 a through 4 f .
  • outflow amounts via the outflow passages 4 a through 4 f can be controlled with high accuracy. Furthermore, since the inflow ports 30 a , 30 b and the outflow ports 40 a through 40 f open onto the same surface 71 of the pump device main unit 7 , external connection of the mixing pump device 1 A is a simple matter.
  • the pump device main unit 7 is furnished with a flow passage formation plate 77 having inflow passages 3 a , 3 b and outflow passages 4 a through 4 f formed in the shape of a channel on one face thereof, and with a sealing sheet 78 that is positioned juxtaposed against this one face, a multitude of flow passages can be formed in a compact pump device main unit 7 , and the mixing pump device 1 A can be manufactured efficiently as well.
  • the two inflow passages 3 a , 3 b and the six outflow passages 4 a through 4 f have mutually identical design; and the inflow-side active valves 5 a , 5 b and the outflow-side active valves 6 a through 6 f have mutually identical design. Consequently, any of the inflow passages 3 a , 3 b and the outflow passages 4 a through 4 f can be utilized as the inflow passages 3 a , 3 b or the outflow passages 4 a through 4 f . Consequently, [the mixing pump device] is not limited to two types of liquid, but can be used to mix and discharge three or more types of liquid.
  • FIG. 8 is an exploded perspective view of the mixing pump device 1 A, shown divided on the vertical.
  • FIG. 9A and FIG. 9B are [respectively] a descriptive diagram of the pump chamber in the expanded state, and the pump chamber in the contracted state.
  • FIGS. 10A to 10C are respectively a perspective view, a plan view, and a sectional view of a rotor employing the rotating body of the pump mechanism shown in FIG. 8 .
  • FIGS. 11A to 11C are respectively a perspective view, a plan view, and a sectional view of a moving body employing the rotating body of the pump mechanism shown in FIG. 8 .
  • the pump drive mechanism 13 is furnished generally with a diaphragm 170 that functions as the displacing member for taking in and discharging liquid by expanding and contracting the pump chamber 2 communicating with the inflow passages 3 a , 3 b and the outflow passages 4 a through 4 f ; and a drive unit 105 for driving the diaphragm 170 .
  • the drive unit 105 is furnished with an annular stator 120 ; a rotating body 103 disposed coaxially to the inside of this stator 120 ; a moving body 160 disposed coaxially to the inside of this rotating body 103 ; and a conversion mechanism 140 for converting rotation of the rotating body 103 to motion of the moving body 160 in the axial direction.
  • the drive unit 105 is installed between the bottom plate 75 and the base plate 76 , within a space formed in the base plate 76 .
  • the stator 120 has a structure including a two-level stack of units each composed of a coil 121 wound around a bobbin 123 , and a pair of yokes 125 positioned so as to cover the coil.
  • the pole teeth which project in the axial direction from the inside peripheral edges of the pair of yokes 125 are arrayed in alternating fashion in the circumferential direction.
  • the rotating body 103 has a cup-shaped member 130 open at the top, and an annular rotor magnet 150 attached to the outside peripheral face of a cylindrical-shaped rotating body 103 drum portion 131 of the cup-shaped member 130 .
  • a recess 135 recessed upwardly in the axial direction; on the bottom plate 75 there is formed a bearing portion 751 adapted to receive a ball 118 that is positioned within the recess 135 .
  • An annular shoulder portion 766 is formed on the inside rim of the upper edge of the base plate 76 .
  • annular shoulder portion which faces towards the annular shoulder portion 766 on the base plate 76 is formed by the upper edge of the drum portion 131 and an annular flange 134 .
  • the annular space defined by these annular shoulder portions accommodates a bearing 180 which is composed of an annular retainer 181 and ball bearings 182 held at locations spaced apart in the circumferential direction by the retainer 181 .
  • the rotating body 103 is supported rotatably about the axis on the pump device main unit 7 .
  • the outside peripheral face of the rotor magnet 150 faces towards the pole teeth which are lined up in the circumferential direction along the inside peripheral face of the stator 120 .
  • S poles and N poles are lined up in alternating fashion in the circumferential direction, with the stator 120 and the cup-shaped member 130 constituting the stepping motor.
  • the moving body 160 has a floor 161 , a cylindrical portion 163 projecting out in the axial direction from the center of the floor 161 , and a drum portion 165 of cylindrical shape formed so as to surround this cylindrical portion 163 ; a male thread 167 is formed on the outside periphery of the drum portion 165 .
  • a female thread 137 is formed at four locations spaced apart in the circumferential direction, on the inside peripheral face of the drum portion 165 of the cup-shaped member 130 .
  • the male thread 167 which engages with the female thread 137 and constitutes a power transmission mechanism 141 , is formed on the outside peripheral face of the drum portion 165 of the moving body 160 . Consequently, the moving body 160 is supported to the inside of the cup-shaped member 130 , with the moving body 160 positioned to the inside of the cup-shaped member 130 so that the male thread 167 meshes with the female thread 137 .
  • the moving body 160 is prevented from rotating by the co-rotation preventing mechanism 149 composed of the projections 769 and the slots 169 ; therefore, rotation of the cup-shaped member 130 will be transmitted to the moving body 160 via the power transmission mechanism 141 composed of the female thread 137 and the male thread 167 of the moving body 160 , as a result of which the moving body 161 undergoes linear movement to one side or the other in the axial direction, depending on the direction of rotation of the rotating body 103 .
  • the diaphragm 170 is linked directly to the moving body 160 .
  • the diaphragm 170 which is cup-shaped, has a floor 171 ; a drum portion 173 of cylindrical shape rising up in the axial direction from the outside peripheral edge of the floor 171 ; and a flange portion 175 spreading towards the outside periphery from the upper end of this drum portion 173 .
  • the diaphragm, with the center portion of the floor 171 thereof covering the cylindrical portion 163 of the moving body 160 is secured in place from above and below by a fastening screw 178 and a cap 179 .
  • the outside peripheral edge of the flange portion 175 of the diaphragm 170 is constituted by a thick section, which is adapted to ensure liquid-tightness, and also functions as a positioning section.
  • the thick section is secured in place between the base plate 76 and the flow passage formation plate 77 , around the through-hole 21 of the flow passage formation plate 77 .
  • the diaphragm 170 defines the lower face of the pump chamber 2 , and assures liquid-tightness between the base plate 76 and the flow passage formation plate 77 around the pump chamber 2 .
  • the drum portion 173 of the diaphragm 170 doubles back in a U shaped cross section, with the doubled back portion 172 thereof changing shape depending on the position of the moving body 160 .
  • the doubled back portion 172 having a U shaped cross section of the diaphragm 170 is positioned within a space of annular shape defined between a first wall face 168 composed of the outside peripheral face of the cylindrical portion 163 of the moving body, and a second wall face 768 composed of the inside peripheral faces of the projections 769 extended from the base plate 76 . Consequently, with the diaphragm in any of the states shown in FIG.
  • the doubled back portion 172 of diaphragm 170 while remaining retained within the annular space, undergoes deformation so as to expand or roll up along the first wall face 168 and the second wall face 768 .
  • a single groove 136 is formed on the floor 133 of the cup-shaped member 130 over an angular range of 270° in the circumferential direction, while a projection 166 is formed facing downward from the bottom face of the moving body 160 .
  • the moving body 160 does not rotate about the axis but does move in the axial direction
  • the rotating body 103 does rotate about the axis but does not move in the axial direction. Consequently, the projection 166 and the groove 136 function as a stopper for regulating the stop position of the rotating body 103 and the moving body 160 .
  • the groove 136 changes in depth in the circumferential direction; as the moving body 160 moves downward in the axial direction the projection 166 will engage within the groove 136 , and upon rotation of the rotating body 103 , the edge of the groove 136 will come into abutment with the projection 166 . As a result, the rotating body 103 will be prevented from rotating, thus regulating the stop position of the rotating body 103 and the moving body 160 , i.e. the position of maximum expansion of the internal volume of the diaphragm 170 .
  • the pump drive mechanism 13 of such a design when power is supplied to the coil 121 of the stator 120 , the cup-shaped member 130 rotates, and this rotation is transmitted to the moving body 160 via the conversion mechanism 140 . Consequently, the moving body 160 undergoes linear reciprocating motion in the axial direction. As a result, the diaphragm 170 deforms in association with the motion of the moving body 160 , causing the pump chamber 2 to expand or contract, whereby the inflow of liquid from the inflow passages 3 a , 3 b and the discharging of liquid to the outflow passages 4 a through 4 f take place in the pump chamber 2 .
  • the doubled back portion 172 of diaphragm 170 while remaining retained within the annular space, undergoes deformation so as to expand or roll up along the first wall face 168 and the second wall face 768 , so no unnecessary sliding motion occurs.
  • the diaphragm 170 is subjected to pressure from the fluid in the pump chamber 2 , the diaphragm is restricted both inside and out within the annular space, and thus will not deform.
  • the lower position of the moving body 160 is restricted by the stopper composed of the groove 136 of the cup-shaped member 130 and the projection 166 of the moving body 160 .
  • the diaphragm 170 undergoes displacement with high accuracy, in association with the rotation of the cup-shaped member 130 .
  • the diaphragm 170 is displaced the direction of increasing the internal volume of the pump chamber 2 ; and when the stepping motor rotates in the other direction, the diaphragm 170 is displaced the direction of decreasing the internal volume of the pump chamber 2 .
  • the moving body 160 can be advanced in very small increments. Consequently, the volume of the pump chamber 2 can be finely controlled, so metered discharge can be carried out with high accuracy.
  • the doubled back portion 172 of diaphragm 170 while remaining retained within the annular space, undergoes deformation so as to expand or roll up along the first wall face 168 and the second wall face 768 , so no unnecessary sliding motion occurs. Consequently, no unnecessary load is produced, and the diaphragm 170 will have a longer life. Moreover, even if the diaphragm 170 is subjected to pressure from the fluid in the pump chamber 2 , it will not deform. Therefore, the pump drive mechanism 13 can carry out metered discharge with high accuracy, and reliability is high as well.
  • the rotating body 103 is rotatably supported about the axis on the pump device main unit 7 via the ball bearings 182 , sliding loss is minimal, and the rotating body 103 is held stably in the axial direction, stabilizing the thrust in the axial direction. It is therefore possible to make the drive unit 105 smaller, improve durability, and improve discharging ability.
  • the numbers of intake ports and discharge ports may be different from those described hereinabove.
  • the sealing sheet 78 for sealing off the upper face and the upper plate 79 to which the pipes are connected are formed by separate components, an arrangement that dispensed with the pipes of the upper plate 79 and provides only outflow holes to the sealing sheet 78 , for connection via seal members would also be possible.
  • FIGS. 12 and 13 are, respectively, a descriptive diagram of the principal parts of a valve used for the active valves 5 a , 5 b and the active valves 6 a through 6 f of the mixing pump device 1 A, shown cut along the axis and viewed from diagonally above; and a descriptive diagram of the lines of magnetic force thereof.
  • the active valves 5 a , 5 b (hereinafter denoted as active valves 5 ) and the active valves 6 a through 6 f (hereinafter denoted as active valves 6 ) are provided with a linear actuator 201 positioned in the holes 57 , 67 a through 67 h of the base plate 76 ; this linear actuator 201 has a stationary body 203 having a cylindrical shape, and a moveable body 205 having a round rod shape positioned inside the stationary body 203 .
  • the stationary body 203 has a coil 233 wound in annular configuration onto a bobbin 231 ; and a stationary body yoke 235 running around both sides of the coil in the axial direction from the outside peripheral face of the coil 233 , with one distal edge 236 a and the other distal edge 236 b thereof facing in the axial direction across a slit 237 , to the inside peripheral side of the coil 233 .
  • the movable body 205 has a first movable body yoke 251 having a disk shape, and a pair of magnets 253 a , 253 b stacked on either side of the first movable body yoke 251 in the axial direction.
  • a second movable body yoke 255 a , 255 b is stacked on each of the pair of magnets 253 a , 253 b , on the end face thereof on the opposite side from the first movable body yoke 251 .
  • the pair of magnets 253 a , 253 b are each magnetized in the axial direction, and oriented with the same pole facing the direction of the first movable body yoke 251 .
  • the pair of magnets 253 a , 253 b are described as oriented with the N pole of each facing the direction of the first movable body yoke 251 , and the S pole of each facing towards the outside in the axial direction; however, the direction of magnetization could be reversed.
  • the outside peripheral face of the first movable body yoke 251 protrudes out beyond the outside peripheral faces of the pair of magnets 253 a , 253 b .
  • the outside peripheral faces of the second movable body yokes 255 a , 255 b protrude out beyond the outside peripheral faces of the pair of magnets 253 a , 253 b.
  • Recesses are formed in each axial end of the first movable body yoke 251 , and the pair of magnets 253 a , 253 b are fitted respectively into these recesses and secured there with adhesive or the like. It is acceptable to employ any arrangement in which the first movable body yoke 251 , the pair of magnets 253 a , 253 b , and the second movable body yokes 255 a , 255 b are fastened through unification by an adhesive, press-fitting, or a combination of these.
  • Bearing plates 271 a , 271 b (bearing members) are fastened in openings at either axial end of the stationary body 203 , and spindles 257 a , 257 b which project out to either side in the axial direction from the second movable body yokes 255 a , 255 b are each slidably inserted into holes in the bearing plates 271 a , 271 b .
  • the movable body 205 is supported on the stationary body 203 so as to be capable of reciprocating motion in the axial direction.
  • the movable body 205 faces the inside peripheral face of the stationary body 203 across a prescribed gap, with the distal edges 236 a , 236 b of the stationary body yoke 235 facing one another in the axial direction within the gap between the outside peripheral face first movable body yoke 251 and the inside peripheral face of the coil 233 .
  • a gap is maintained between the moveable body 205 and the stationary body yoke 235 as well. It is acceptable to employ any arrangement in which the second movable body yokes 255 a , 255 b and the spindles 257 a , 257 b are fastened through unification by an adhesive, press-fitting, or a combination of these.
  • the lines of magnetic force will be as depicted in FIG. 13 . Accordingly, the moveable body 5 is first subjected to thrust and moves in the axial direction due to Lorentz force, as indicated by arrow A. On the other hand, when the direction of current through the coil 233 reverses, the moveable body 205 will descend along the axial direction as indicated by arrow B.
  • the moveable body 205 is propelled by magnetic force, and a frustoconically shaped coil spring 291 is positioned as an urging member between the bearing plate 271 a and the second movable body yoke 255 a , on one side in the axial direction. Consequently, the moveable body 205 descends while deforming the compression spring; and as the moveable body 205 moves at high speed when ascending, assisted by the shape recovery force of the compression spring.
  • the center portion of a diaphragm valve 260 positioned in the valve chamber 270 (recess 68 a through 68 h ) is connected to the end of one of the spindles 257 b .
  • An annular thick section 261 providing liquid-tightness and a positioning function is formed on the outside periphery of the diaphragm 260 ; the outside peripheral section of the diaphragm 260 including this annular thick section 261 is held between the base plate 76 and the flow passage formation plate 77 , ensuring liquid-tightness.
  • the displacing member is not limited to a diaphragm 260 , it being possible to employ a bellows valve or some other valve instead.
  • the pair of magnets 253 a , 253 b in the moveable body 205 are oriented with identical poles facing one another, producing magnetic repulsive force, but since the first movable body yoke 251 is positioned between the magnets 253 a , 253 b , the pair of magnets 253 a , 253 b can be secured oriented with identical poles facing one another.
  • the moveable body 205 can be imparted with strong thrust.
  • magnets 253 a , 253 b need only be magnetized in the axial direction, in contrast to the case where the magnets 253 a , 253 b are magnetized in the radial direction, magnetization is a simple matter even where the magnets are small, which is suitable for mass production purposes.
  • the magnetic attracting force acting in the axial direction and the perpendicular direction on the moveable body 205 can be minimized, even if the stationary body yoke 235 is provided.
  • the magnetic attracting force acting in the axial direction and the perpendicular direction on the moveable body 205 can be minimized, even when the stationary body yoke 235 is provided.
  • the assembly operation is facilitated and the moveable body resists tilting, which are advantages obtained as a result.
  • the magnets 253 a , 253 b are positioned at the outside periphery side in the coil 33 , the magnets 253 a , 253 b can be smaller, and the active valves 5 , 6 may be designed less expensively, as compared to when the magnets 253 a , 253 b are positioned outwardly from the coil 233 . Also, since the coil 233 is positioned to the outside, the magnetic path can be closed with the stationary yoke only.
  • the bearing plates 271 a , 271 b for supporting the spindles 257 a , 257 b so as to be moveable in the axial direction are held in openings that open in the axial direction, there is no need for separate bearing members.
  • An additional advantage is that since the bearing plates 271 a , 271 b can be secured on the basis of the stationary body 203 , the spindles 257 a , 257 b will not tilt.
  • the mixing pump device embodying the present invention can be used, for example, for a direct methanol fuel cell (hereinafter DMFC) that takes protons directly from methanol in order to generate electricity.
  • DMFC direct methanol fuel cell
  • This kind of DMFC has a generating unit having a electromotive portion (cell), and a liquid feed pump for pumping a methanol aqueous solution.
  • the cell is composed of an anode (fuel electrode) having an anode collector and an anode catalyst layer; a cathode (air electrode) having a cathode collector and a cathode catalyst layer; and an electrolyte membrane positioned between the anode and the cathode.
  • the methanol aqueous solution is delivered to the anode by the liquid feed pump, while air is delivered to the cathode by an air pump or blower.
  • the mixing pump device embodying the present invention as the liquid feed pump, it is possible to appropriately mix methanol with water, methanol with a methanol aqueous solution, a methanol aqueous solution with methanol, or a methanol aqueous solution with another methanol aqueous solution, and to supply the cell with a methanol aqueous solution of adjusted methanol concentration.
  • methanol oxidation activity is low, with associated voltage loss. Voltage loss occurs at the cathode as well.
  • the output drawn from a single cell is very low, so the DMFC employs a plurality of cells in order to generate a prescribed output.
  • the mixing pump device 1 A embodying the present invention can be used to deliver methanol aqueous solution of adjusted methanol concentration to each cell.
  • the mixing pump device can be used as a pump for blending a plurality of chemical solutions in order to blend a compound chemical. It can also be used as a refrigerator icemaker pump, for discharging from outflow paths sherbets of different color and flavor for each icemaker block.
  • the invention can instead be embodied in a mixing pump device of a type using a plunger as the displacing member. Also, while the preceding embodiment was an example designed with a plurality of outflow passages, the invention can instead be embodied in a mixing pump device having a single outflow passage.
  • the invention was embodied in a mixing pump device, but the invention can also be embodiment in a metering pump for discharging a single type of liquid.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Dispersion Chemistry (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Reciprocating Pumps (AREA)
US12/083,990 2006-02-13 2007-02-09 Method for Driving a Pump Device Abandoned US20090123299A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2006035702A JP4832098B2 (ja) 2006-02-13 2006-02-13 ポンプ装置の駆動方法
JP2006-035702 2006-02-13
PCT/JP2007/000075 WO2007094132A1 (ja) 2006-02-13 2007-02-09 ポンプ装置の駆動方法

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US (1) US20090123299A1 (ja)
JP (1) JP4832098B2 (ja)
KR (1) KR20080093407A (ja)
CN (1) CN101356370B (ja)
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US6749403B2 (en) * 1999-07-20 2004-06-15 Deka Products Limited Partnership Methods for controlling a pump's flow rate by pulsed discharge
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Also Published As

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WO2007094132A1 (ja) 2007-08-23
CN101356370A (zh) 2009-01-28
CN101356370B (zh) 2010-09-15
JP2007211756A (ja) 2007-08-23
KR20080093407A (ko) 2008-10-21
JP4832098B2 (ja) 2011-12-07

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