WO1993015316A1 - Pompe de dosage sans vanne et a piston possedant un mouvement de va-et-vient rotatif - Google Patents

Pompe de dosage sans vanne et a piston possedant un mouvement de va-et-vient rotatif Download PDF

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Publication number
WO1993015316A1
WO1993015316A1 PCT/US1992/000821 US9200821W WO9315316A1 WO 1993015316 A1 WO1993015316 A1 WO 1993015316A1 US 9200821 W US9200821 W US 9200821W WO 9315316 A1 WO9315316 A1 WO 9315316A1
Authority
WO
WIPO (PCT)
Prior art keywords
piston
pump
metering pump
adjusting
valveless
Prior art date
Application number
PCT/US1992/000821
Other languages
English (en)
Inventor
Guillermo Pedro Pardinas
Original Assignee
Abbott Laboratories
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Abbott Laboratories filed Critical Abbott Laboratories
Priority to PCT/US1992/000821 priority Critical patent/WO1993015316A1/fr
Priority to AU14252/92A priority patent/AU1425292A/en
Publication of WO1993015316A1 publication Critical patent/WO1993015316A1/fr

Links

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
    • F04B7/00—Piston machines or pumps characterised by having positively-driven valving
    • F04B7/04—Piston machines or pumps characterised by having positively-driven valving in which the valving is performed by pistons and cylinders coacting to open and close intake or outlet ports
    • F04B7/06—Piston machines or pumps characterised by having positively-driven valving in which the valving is performed by pistons and cylinders coacting to open and close intake or outlet ports the pistons and cylinders being relatively reciprocated and rotated

Definitions

  • the invention is generally related to valveless metering pumps for delivering precise volumes of fluid and 5 is specifically related to a microfluid pump for precisely dispensing reagents in assay tests.
  • each pump may deliver a specific reagent to each of one or more test sample locations and, in the prior art, a valve mechanism is used to control the flow of the reagent from first one 25 station and then to the other.
  • valveless, positive displacement metering pumps have been successfully employed in appli ⁇ cations where safe and accurate handling of fluids is required.
  • the valveless pumping function is accomplished by the simultaneous rotation and reciprocation of a piston in a work chamber.
  • the pump head containing the work chamber and piston is mounted such that is may be swiveled with respect to the rotating drive. The degree of angle controls the stroke and length and in turn, the flow rate.
  • This type of pump has been found to be useful in performing accurate transfers of both gaseous and liquid fluids.
  • valveless positive displacement pump An example of a valveless positive displacement pump is disclosed in U.S. Pat. No. 4,008,003.
  • the pump includes a cylinder divided into a pair of working cham- bers, each of the chambers communicating with an inlet and an outlet port.
  • the pump disclosed in the 4,008,003 patent does not lend itself to accurate calibration for metering and dispensing fluids in the precise volumes called for in assay type tests.
  • the piston stroke is not easily adjusted and the angular displacement of the ports cannot be readily calibrated.
  • Another example of a valveless metering pump using a tiltable housing to control the piston stroke disclosed in my co-pending application entitled Pump with Multi-Port Discharge, Serial No. 07/463,260, filed January 10, 1990, with the co-inventors R.W.
  • the valveless metering pump of the subject inven ⁇ tion provides a fluid delivery system particularly suited for precision delivery of fluid reagents to a test sample in an assay test in a dependable and reliable manner.
  • the pump design of the subject invention includes a minimum number of moving parts, is valveless, flexible in config ⁇ uration, and is easy to assemble with minimum risk of tolerance stacking.
  • the pump is of low manufacturing cost and requires minimum field maintenance.
  • the pump is de ⁇ signed to have a broad reagent compatibility and is capable of dispensing fluid volumes in the range of 1-100 micro- liters per port within plus or minus 0.5 microliters and with a precision of less than one percent coefficient of variance.
  • the valveless metering pump of the subject inven ⁇ tion includes a head having a working chamber made of an inert material for receiving a reciprocating and rotating piston for drawing and dispensing fluids in precise quanti- ties to a plurality of ports in sequential manner.
  • the head and piston is mounted on a pump body which may be tilted angularly relative to the drive spindle for cali ⁇ brating and adjusting the reciprocating stroke of the piston to precisely meter the fluids dispensed by the pump.
  • the inlet and outlet ports of the head are in coplanar relationship and are angularly spaced, extending radially outward from the pump working chamber.
  • the angu ⁇ lar orientation of the ports may be calibrated relative to the piston to balance the pump action.
  • the reciprocating drive is provided by a sleeve enveloping the piston and secured to it by a radial drive pin mounted in a spherical bearing which is free to swivel in any direction as the sleeve and piston are rotated by the spindle of a typical
  • the sleeve and piston are carried by a pump housing having one section which is secured in axial align ⁇ ment with the piston and sleeve and a second section hinged to the first section and in axial alignment with the pump chamber, with means for adjusting and controlling the axial angular displacement between the pump housing and the drive axis for controlling the stroke of the piston as it is rotated by the spindle.
  • the angle of the piston axis is controlled by adjustment of a single calibration screw.
  • an object and feature of the subject invention to provide a valveless, positive dis ⁇ placement metering pump for accurately and precisely dis ⁇ pensing minute volumes of fluid. It is another object and feature of the invention to provide for a valveless, positive displacement metering pump with single adjustment screw calibration of the piston stroke.
  • FIG. 1 is a side elevational view of a valveless, positive displacement metering pump in accordance with the present invention.
  • Fig. 2 is an exploded perspective view of the pump of Fig. 1.
  • Fig. 3 is a partial side sectional view looking in the same direction as Fig. 1 and illustrating the inte ⁇ rior chambers of the assembled pump with the piston at the maximum compression point of its stroke.
  • Fig. 4 is a partial side sectional view similar to Fig. 3 and illustrating the piston in the fully retract ⁇ ed point of its stroke.
  • Fig. 5 is a sectional view taken along line 5-5 of Fig. 3, illustrating the relationship between ports, the pump working chamber and the piston.
  • Fig. 6 is a sectional view taken along line 6-6 of Fig. 4, illustrating the relationship between the pis ⁇ ton, the drive pin and sleeve.
  • Fig. 7 is a diagrammatic sectional view looking generally along line 7-7 of Fig. 5, illustrating the .rela- tionship between the piston and the inlet port as fluid is being drawn into the pump chamber.
  • Fig. 8 is a diagrammatic sectional view looking generally along line 8-8 of Fig. 5, illustrating the rela ⁇ tionship between the piston and one outlet port as fluid is being dispensed therethrough.
  • Fig. 9 is a diagrammatic sectional view looking generally along line 9-9 of Fig. 5, illustrating the rela- tionship between the piston and the other outlet port as fluid is being dispensed therethrough.
  • the valveless metering pump of the subject invention includes a head 10, a body 12 including an upper section 14 and a lower section 16 hingedly secured to one another at 18, a motor 20 and a support plate 22.
  • the head 10 is mounted on the upper section 14 of the body via mounting screws 24 which pass through clearance slots 26. provided in the head and are received by tapped holes 28 in the upper body section 14.
  • the motor 20 is mounted on the support plate 22 by mounting screws 30 which pass through the clearance holes 32 provided in the support plate and through spacers 34 to be received by tapped holes (not shown) in the lower housing wall 35 of motor 20.
  • Mounts 36 are located on the support plate 22 outside the perimeter of the motor 20 and include nested mounting screws 37 for mounting the assembled pump in an operating station (not shown) .
  • the motor includes an elongate cylindrical drive shaft 38 which defines the drive axis of the pump.
  • a locating ring 40 is secured to the front wall 42 of the motor housing and is positioned in axial alignment with the drive shaft 38 by the centering boss 41.
  • the ring 40 includes an outer wall 43 which is adapted for receiving and centering the lower body section 16, as best seen in Fig. 3.
  • the hollow spindle 44 is secured on the end of shaft 38 by set screw 45 as best seen in Fig. 3.
  • the spindle rotates in one-to-one relationship with the shaft for driving the piston 46.
  • the lower end of the piston 46 includes a drive pin 48.
  • the drive pin 48 extends through the drive aperture 50 provided in the spindle, as best shown in Fig. 3.
  • a spherical bearing 51 is placed in the aperture 50 for receiving the pin 48 and is movable in any direction rela- tive to spindle 44 to permit free movement of the pin.
  • the head 52 of the piston 46 is received by the pump head 10 and closely conforms to the cylindrical inner ' side wall 55 of the working chamber 54, as best seen in Fig. 4.
  • a series of seals 56, 58 and 60 are disposed between the lower bearing wall 62 (Fig. 3) of the pump head and the upper bearing surface 64 of the upper body section 14 of the pump body for sealing the pump head and piston against leakage.
  • the lower body section 16 is secured to the motor 20 via a plurality of mounting screws 66 which pass through clearance holes 68 provided in the lower body section and are received by tapped holes 70 in the upper wall 42 of the motor housing.
  • the sleeve 44 is surrounded by and is coaxial and centered with the lower body section.
  • the upper body section 14 of the pump body is hingedly mounted on the lower body section at 18 via hinge pins 19.
  • the head 52 of the piston extends through the clearance opening 72 in the upper body section and into the working chamber 54 of the pump head 10, as shown in Fig. 3.
  • a slotted tab seat 74 is provided in the upper body section 14 and is located radially outward and diametrically oppo ⁇ site the center of the hinge axis.
  • a complementary slotted tab seat 76 is provided on the .lower body section 16.
  • a compression spring 78 (Fig. 1) is disposed between seats 74 and 76 and a threaded adjust ⁇ ment screw 80 is passed through the slot 82 in seat 74., through the center of spring 78 and through the clearance slot 84 in seat 76.
  • a slotted retainer 85 may be placed between the screw head 81 and the slotted seat 74 for properly maintaining the screw 80 in seat 74.
  • a nut 86 is threadably received by the adjustment screw 80, whereby the angle of tilt between the upper body portion 14 and the head 10 relative to the lower body section 16 and the shaft 38 may be adjusted by turning screw 80 in nut 86.
  • the lower body section 16 includes a clearance slot 88 providing access to the set screw 45 for adjusting the position of spindle 44 relative to shaft 38.
  • the elongate slots 26 in head 10 (Fig. 5) permit the rotational calibration of the angular relationship between the ports and the piston.
  • the pump head 10 may be made of any suitable material and includes an inert insert 90 made of ceramics or the like which defines the accurately dimensioned inner cylindrical side wall 55 of the pump working chamber 54, as best illustrated in Figs. 3 and 4.
  • the insert 90 includes three precisely metered, coplanar orifices 92, 94 and 96.
  • the head 10 includes three corresponding cylindrical channels 98, 100 and 102.
  • the channels 98, 100 and 102 may be tapped for receiving threaded couplings such as the cou ⁇ pling 104 (Fig. 2) for attaching the assembled pump to fluid control lines in the manner well known.
  • the tilt angle between the upper section 14 and the lower section 16 of the pump body controls the length of the reciprocating stroke of the piston 46.
  • the piston 46 reaches its maximum height when the drive pin is diametrically opposite the adjusting screw 80 and, conversely as shown in Fig. 4, the piston reaches the low point of its stroke when the drive pin 48 is adjacent adjusting screw 80.
  • the maximum height of the piston travel within the working chamber 54 is controlled by adjusting the position of the spindle 44 on the shaft 38 using set screw 45.
  • the fully assembled pump may be calibrated to adjust the length of stroke of the piston by adjusting the tilt angle between the upper body section 14 and the lower body section 16 using adjust ⁇ ment screw 80.
  • the working volume of the pump chamber 54 may be adjusted by positioning the spindle 44 on shaft 38 through use of set screw 45.
  • the inlet and outlet ports in the head 10 may be angularly calibrated for balancing the input and output of the pump by adjusting the angular position of the head relative to the piston via mounting screws 24 and calibration slots 26, as best seen in Fig. 5.
  • the piston includes a flat or duct 106 in the cylindrical outer wall of the head 52. As is shown in Fig.
  • the piston continues its upstroke as it moves into contact with the second sequential outlet port 96, further contracting the working chamber 54 and forcing additional fluid out through port 96 and the associated channel 102, as indicated by arrow 114.
  • the piston moves past port 96, it enters the peak of its upstroke and begins the next downstroke as it moves into contact with port 92 for again drawing fluid into the working chamber of the pump.
  • the fluid flow through the outlet ports 94 and 96 can be accurately balanced by adjusting the angular position of the ports relative to the stroke of the piston by rotating the head within the range permitted by the slots 26.
  • the outlet ports may be adjusted to within less than a one percent coefficient of variance for reagent fluids dispensed in the range of 1-100 microliters. Further, the reagents have been consistently dispensed within a plus or minus 0.5 microliter accuracy and precision.
  • a flag 116 may be mounted on shaft 38.
  • the flag 116 includes a radially projecting indicator tab 118 which permits accurate contin- uous reading of the angular position of the piston 46.
  • An optical or other type of sensor (not shown) can be disposed in communication with the indicator tab 118 of the flag.
  • the flag and indicator can be used to control the speed of motor 20 as it rotates through its cycle, altering the speed of rotation and reciprocation of the piston to increase and/or decrease pressure, as desired, to further control the flow of fluid through the ports 92, 94 and 96.
  • valveless, positive displacement metering pump of the invention is particularly useful for dispensing reagent fluids in minute, accurate volumes into a test sample for- assay testing. It will readily understood that the features of the pump make it readily adaptable to a variety of other applications. While certain features and embodiments of the invention have been described in detail herein, it will be understood that the invention includes all enhancements and modifica ⁇ tions thereof as more distinctly pointed out in the claims which follow.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)

Abstract

Pompe de dosage sans vanne comprenant un piston à mouvement de va-et-vient et de rotation simultané (46). La tête de pompe (10) comprend des orifices (92, 94, 96) coplanaires espacés radialement destinés à prélever et à fournir des fluides au fur et à mesure que le piston (46) tourne séquentiellement devant les orifices. Le mouvement de va-et-vient du piston (46) est commandé par réglage de l'axe du piston par rapport à l'axe d'entraînement. La pompe est conçue de telle sorte que le rapport angulaire des orifices puisse être réglé également par rapport au piston, de manière à équilibrer la sortie des orifices séquentiels. La pluralité de réglages permet d'obtenir une pompe de dosage sans vanne à déplacement positif qui est fiable et destinée à fournir des volumes précis de fluide à travers une pluraité d'orifices de sortie.
PCT/US1992/000821 1991-01-31 1992-01-31 Pompe de dosage sans vanne et a piston possedant un mouvement de va-et-vient rotatif WO1993015316A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
PCT/US1992/000821 WO1993015316A1 (fr) 1992-01-31 1992-01-31 Pompe de dosage sans vanne et a piston possedant un mouvement de va-et-vient rotatif
AU14252/92A AU1425292A (en) 1991-01-31 1992-01-31 Valveless metering pump with reciprocating, rotating piston

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/US1992/000821 WO1993015316A1 (fr) 1992-01-31 1992-01-31 Pompe de dosage sans vanne et a piston possedant un mouvement de va-et-vient rotatif

Publications (1)

Publication Number Publication Date
WO1993015316A1 true WO1993015316A1 (fr) 1993-08-05

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US1992/000821 WO1993015316A1 (fr) 1991-01-31 1992-01-31 Pompe de dosage sans vanne et a piston possedant un mouvement de va-et-vient rotatif

Country Status (2)

Country Link
AU (1) AU1425292A (fr)
WO (1) WO1993015316A1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011113469A2 (fr) 2010-03-15 2011-09-22 Diener Ag Precision Machining Pompe doseuse
CN106640612A (zh) * 2016-12-02 2017-05-10 深圳市恒永达科技有限公司 一种可手动调节冲程的无阀微泵
CN108799035A (zh) * 2018-07-05 2018-11-13 武汉华喜特种液压设备有限公司 一种同步旋转配流微型柱塞泵
CN109555661A (zh) * 2019-01-16 2019-04-02 深圳市利华美科技有限公司 一种流量调节精密注液泵
CN111836959A (zh) * 2018-02-19 2020-10-27 I·M·A·工业机械自动装置股份公司 正排量泵
US10935021B2 (en) 2013-12-13 2021-03-02 Fluid Metering, Inc. Mechanism for coarse and fine adjustment of flows in fixed displacement pump

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3168872A (en) * 1963-01-23 1965-02-09 Harry E Pinkerton Positive displacement piston pump
US4008003A (en) * 1975-06-27 1977-02-15 Pinkerton Harry E Valveless positive displacement pump
US4941809A (en) * 1986-02-13 1990-07-17 Pinkerton Harry E Valveless positive displacement metering pump
US5015157A (en) * 1990-01-10 1991-05-14 Dennis Pinkerton Pump with multi-port discharge
US5044889A (en) * 1990-05-16 1991-09-03 Dennis Pinkerton Phase adjustable metering pump, and method of adjusting the flow rate thereof
US5070980A (en) * 1990-02-06 1991-12-10 Aisin Seiki Kabushiki Kaisha Viscous fluid coupling
US5092037A (en) * 1990-01-05 1992-03-03 Dennis Pinkerton Method of making a valveless positive displacement pump including a living hinge for angular adjustment

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3168872A (en) * 1963-01-23 1965-02-09 Harry E Pinkerton Positive displacement piston pump
US4008003A (en) * 1975-06-27 1977-02-15 Pinkerton Harry E Valveless positive displacement pump
US4941809A (en) * 1986-02-13 1990-07-17 Pinkerton Harry E Valveless positive displacement metering pump
US5092037A (en) * 1990-01-05 1992-03-03 Dennis Pinkerton Method of making a valveless positive displacement pump including a living hinge for angular adjustment
US5015157A (en) * 1990-01-10 1991-05-14 Dennis Pinkerton Pump with multi-port discharge
US5070980A (en) * 1990-02-06 1991-12-10 Aisin Seiki Kabushiki Kaisha Viscous fluid coupling
US5044889A (en) * 1990-05-16 1991-09-03 Dennis Pinkerton Phase adjustable metering pump, and method of adjusting the flow rate thereof

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011113469A2 (fr) 2010-03-15 2011-09-22 Diener Ag Precision Machining Pompe doseuse
WO2011113469A3 (fr) * 2010-03-15 2012-03-01 Diener Ag Precision Machining Pompe doseuse
US10935021B2 (en) 2013-12-13 2021-03-02 Fluid Metering, Inc. Mechanism for coarse and fine adjustment of flows in fixed displacement pump
CN106640612A (zh) * 2016-12-02 2017-05-10 深圳市恒永达科技有限公司 一种可手动调节冲程的无阀微泵
CN111836959A (zh) * 2018-02-19 2020-10-27 I·M·A·工业机械自动装置股份公司 正排量泵
JP2021514445A (ja) * 2018-02-19 2021-06-10 イ．エンメ．ア．インドゥストリア マッキーネ アウトマティケ ソチエタ ペル アツィオニ 容積式ポンプ
CN108799035A (zh) * 2018-07-05 2018-11-13 武汉华喜特种液压设备有限公司 一种同步旋转配流微型柱塞泵
CN108799035B (zh) * 2018-07-05 2024-01-09 武汉华喜特种液压设备有限公司 一种同步旋转配流微型柱塞泵
CN109555661A (zh) * 2019-01-16 2019-04-02 深圳市利华美科技有限公司 一种流量调节精密注液泵

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