EP2362100B2 - Agrégat de pompes de dosage et procédé de commande d'un agrégat de pompes de dosage - Google Patents

Agrégat de pompes de dosage et procédé de commande d'un agrégat de pompes de dosage Download PDF

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Publication number
EP2362100B2
EP2362100B2 EP10001643.5A EP10001643A EP2362100B2 EP 2362100 B2 EP2362100 B2 EP 2362100B2 EP 10001643 A EP10001643 A EP 10001643A EP 2362100 B2 EP2362100 B2 EP 2362100B2
Authority
EP
European Patent Office
Prior art keywords
stroke
speed
increased
metering pump
stroke speed
Prior art date
Legal status (The legal status 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 status listed.)
Active
Application number
EP10001643.5A
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German (de)
English (en)
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EP2362100A1 (fr
EP2362100B1 (fr
Inventor
Serge Gerz
Valeri Kechler
Markus Simon
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Grundfos Management AS
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Grundfos Management AS
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.)
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Application filed by Grundfos Management AS filed Critical Grundfos Management AS
Priority to EP10001643.5A priority Critical patent/EP2362100B2/fr
Priority to CN201180009714.3A priority patent/CN102762860B/zh
Priority to JP2012553215A priority patent/JP5902101B2/ja
Priority to PCT/EP2011/000722 priority patent/WO2011101119A1/fr
Priority to US13/579,719 priority patent/US10054117B2/en
Publication of EP2362100A1 publication Critical patent/EP2362100A1/fr
Publication of EP2362100B1 publication Critical patent/EP2362100B1/fr
Application granted granted Critical
Publication of EP2362100B2 publication Critical patent/EP2362100B2/fr
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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
    • 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
    • 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
    • F04B43/0009—Special features
    • F04B43/0081—Special features systems, control, safety measures
    • 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

Definitions

  • the invention relates to a metering pump unit according to the preamble of claim 1.
  • Known metering pump units have a metering space which is delimited on one side by a displacement body, for example in the form of a membrane.
  • the displacer body can change the volume of the dosing chamber, whereby a pumping effect is achieved.
  • a suitable linear drive is provided for driving the displacement body.
  • this is a rotationally driving drive motor in the form of a stepper motor, which sets a connecting rod in linearly oscillating motion via an eccentric.
  • Check valves are arranged on the inlet and outlet sides of the metering chamber, which prevent the medium to be pumped from flowing back into the metering chamber in the suction stroke and prevent the medium from being pressed into the suction line instead of the pressure line.
  • WO 03 / 054392A1 discloses a metering pump which has an electric motor drive which can be variably controlled in its speed and direction of rotation. This control enables the suction stroke to be carried out faster than the pressure stroke.
  • EP 1 278 961 B1 discloses a pump for conveying liquid, which is designed as a piston pump, wherein the piston can be moved so that the speed increases during the pressure stroke towards the center of the pressure stroke and then reduced again at the end of the pressure stroke.
  • US 4,131,393 discloses a fluid pump system in which the suction stroke is started at a slower speed to avoid cavitation.
  • the metering pump unit has, in a known manner, a metering space, on which a displacement body is arranged adjacent.
  • the displacement body thus forms a wall of the metering chamber and can change the volume of the metering chamber by its movement.
  • a displacer drive is provided for moving the displacer body and can be controlled or regulated via a control device.
  • the control device can be used in particular to specify the speed, operating time and direction of movement of the displacement drive in order to set or regulate the volume to be metered by actuating the displacement drive.
  • the displacer drive is preferably an electric drive motor, in particular a stepper motor, which can be controlled very precisely in order to selectively adjust the stroke length and / or stroke speed of the displacer body in order to maintain the quantity to be metered and the metering speed in accordance with predetermined values.
  • the drive motor can be a linear motor or a rotating electric motor, the rotary movement then being converted into a linear movement of the displacement body by means of suitable gear means, for example a crank drive, a cam drive, an eccentric or a spindle.
  • suitable gear means for example a crank drive, a cam drive, an eccentric or a spindle.
  • an EC motor, a servo motor or another suitable electrical drive motor can also be used as the drive motor.
  • control device and the displacement drive are designed such that the travel speed of the displacement body can be changed even during a pressure stroke. This is done by changing the speed of the displacement drive, e.g. B. the speed or speed of rotation of the drive motor.
  • the control device is also designed such that it selects a special driving or driving characteristic of the displacement drive for certain desired flow rates to be generated by the metering pump and controls the displacement drive accordingly.
  • a special drive characteristic is designed in such a way that the pressure stroke of the displacement body is started with a first increased stroke speed and then continued with a second, lower stroke speed.
  • the control device is designed such that it, at least for certain flow rates to be generated by the metering pump, the displacement drive, for. B. controls a drive motor such that a pressure stroke of the displacer begins at a first increased stroke speed and then continues at the second lower stroke speed. It is thereby achieved that the check valve to the suction channel is closed quickly and reliably in the case of a pressure stroke for, in particular, low flow rates, so that there are no or only slight leakage losses and thus a high metering accuracy is achieved even with low flow rates.
  • the control device determines the stroke speed by reducing the speed of the displacement drive, i.e. H. e.g. B. the speed of the drive motor is reduced, so that overall only a lower flow rate is achieved in the pressure stroke.
  • control device is designed in such a way that it executes the special drive characteristic described above and below in the pressure stroke
  • control device can also be designed such that it additionally has the special drive strategy described above or below in the suction stroke.
  • the control device is thus preferably designed such that it controls the displacement drive for flow rates below a predetermined limit value in such a way that a pressure stroke of the displacement body begins with a first increased stroke speed and then continues with a second lower stroke speed.
  • the exact limit value can depend on the design of the dosing chamber and in particular on the check valves used.
  • the described special driving characteristics of the displacement body are to be used, according to which the lifting stroke begins and the pressure stroke is then continued with a stroke speed that is reduced compared to this increased stroke speed .
  • the corresponding specific limit values are specified for the control device or are stored in a memory of the control device.
  • the stroke speed of the displacement drive is changed by appropriate control by means of the control device, so that the displacement drive can be operated at different speeds or speeds according to the control device.
  • the motor can carry out a predetermined number of individual steps in a specific time interval. The number of individual steps per time interval can be predetermined by the control device in order to change the speed of the drive motor.
  • the control device is designed in such a way that the first increased lifting speed is set faster than is required for a desired delivery flow. This ensures that, compared to the initial rapid pressure increase which would occur at the stroke speed otherwise required for the desired delivery flow, a rapid initial pressure increase is exerted on the medium to be pumped, which leads to a reliable closing of the valves, in particular the valve in the suction channel leads.
  • the stroke speed for an actually higher flow rate must be selected at the beginning of the pressure stroke. This is then compensated for by the later reduction in the stroke speed in order to achieve a lower delivery volume flow overall over the total stroke than is achieved at the start of the pressure stroke with the higher stroke speed.
  • the control device is designed in such a way that the second, lower stroke speed is set slower than is required for a desired delivery flow.
  • the target flow rate can be achieved on average over the entire pressure stroke.
  • the control device is designed in such a way that it selects or calculates the first increased lifting speed and the second reduced lifting speed and the duration of the partial stroke with the first lifting speed as a function of a predetermined desired flow rate so that an average flow rate is achieved over the entire pressure stroke , which corresponds to the desired flow rate.
  • the duration with which the pressure stroke is operated at an increased stroke speed and the absolute values for the higher and, in contrast, the reduced stroke speed can be stored in the control device for certain desired delivery volume flows or can currently be stored for a selected desired delivery volume flow according to predetermined algorithms be calculated.
  • the volume flow can also be monitored by suitable sensors during the pressure stroke, so that the stroke speed could also be adjusted to a specific desired value by the control device during the pressure stroke.
  • 2% or more of the total pressure stroke becomes with the first increased lifting speed. More preferably, less than 20% of the total pressure stroke is carried out with the first increased stroke speed.
  • the stroke does not have to be the maximum possible stroke, rather it can only be a shortened stroke. This is only a small part of the total stroke, so that the constant metering of the medium to be metered is only slightly impaired by the increased stroke speed at the beginning of the pressure stroke.
  • the higher stroke speed at the beginning of the pressure stroke results in a higher dosing accuracy overall.
  • the change in the lifting speed from the first increased lifting speed to the second lower lifting speed can be carried out in leaps and bounds or else in the form of a ramp. A change in several steps or stages or via a ramp with changing incline is also possible.
  • the first increased stroke speed is more preferably greater than or equal to six strokes per minute, while the second lower stroke speed is preferably less than six strokes per minute.
  • the first increased lifting speed can further preferably essentially correspond to the lifting speed in the suction stroke.
  • the first increased lifting speed is expediently many times greater than the second lower lifting speed, preferably the first increased lifting speed is three times, according to a further preferred embodiment five times or seven times or more the second lower lifting speed.
  • the metering pump unit has a drive housing 2 with a pump head 4 arranged thereon on the end face.
  • the drive motor 6 drives an eccentric 10 via a gear 8.
  • the eccentric 10 converts the rotating drive movement of the drive motor 6 into a linear movement of a connecting rod 12.
  • the connecting rod 12 causes a stroke movement of the diaphragm 14 in the pump head 4 in the direction of the stroke axis X.
  • the diaphragm 14 delimits one side of the metering chamber 16 and forms a displacement body in it, by means of which the volume of the metering chamber 16 can be changed for pumping or metering.
  • the metering chamber 16 is connected to a suction port 18 and a pressure port 20.
  • two non-return valves 22 are arranged in series in the suction channel.
  • two check valves 24 are arranged in the flow path from the metering chamber 16 to the pressure connection 20 in the pressure channel. Two check valves 22 and 24 are provided here. It should be understood, however, that only one check valve 22 and one check valve 24 could be used.
  • control electronics 26 which is connected to an operating and display device 28, by means of which parameters, such as the flow rate, can be set and information which the control electronics 26 outputs can be read.
  • a certain delivery flow which is set, for example, via the operating and display device 28, is converted by the control electronics 26 into a corresponding control or regulation of the drive motor 6, so that it is operated at a corresponding speed, so that the membrane 14 with a corresponding lifting speed is moved in the direction of the lifting axis X.
  • the stroke length can also be controlled by the control electronics 26 via the angle of rotation of the drive motor 6, which is preferably designed as a stepper motor.
  • control electronics 26 are designed or programmed such that they use a special drive characteristic in the case of flow rates which are below a certain limit value stored in the control electronics 26 in order to cause the valves 22, 24 to close.
  • the corresponding limit value can depend on the characteristic, size and special design of the pump head 4 and in particular the check valves 22 and 24. Even if it is it is preferred that this special drive characteristic, described below, can be used for low flow rates below a certain limit value, it should be understood that this drive characteristic could also be used for other flow rates.
  • FIG. 2 shows a diagram in which the engine speed n of the drive motor 6 is shown over the stroke length H of the pressure stroke.
  • the point 30 in the diagram indicates the start of a pressure stroke, while the point 32 in the diagram indicates the end of the pressure stroke at which the full stroke length H of the membrane 14 in the direction of the stroke axis X is reached.
  • the pressure stroke is started with an increased speed n 1 of the drive motor 6.
  • the control electronics 26 controls the drive motor 6 accordingly, so that it runs at this speed. Due to the gear 8 and the eccentric 10, this causes a corresponding, proportional first increased stroke speed of the membrane 14 in the pressure stroke.
  • the increased stroke speed due to the increased speed n 1 causes an impulse or rapid pressure increase on the fluid in the metering chamber 16 at the beginning of the stroke, ie an increased pressure, which causes a tight, reliable closing of the suction-side check valve 22.
  • the increased speed n 1 is maintained for a predetermined time, which corresponds to a corresponding stroke length up to point 34 of the pressure stroke.
  • the pressure stroke is then continued at a reduced speed n 2 of the drive motor 6.
  • This reduced speed n 2 thus corresponds to a reduced stroke speed of the diaphragm 14 caused by the gear 8 and the eccentric 10.
  • This reduced speed n 2 or reduced stroke speed is maintained until the end of the pressure stroke 32.
  • This reduced speed n 2 which is proportional to a reduced stroke speed of the diaphragm 14, is also predetermined by the control electronics 26 by appropriate control of the drive motor 6.
  • the control electronics 26 selects the speeds n 1 and n 2 as a function of a predetermined target speed n s .
  • This target speed n s is proportional to a target lifting speed, which in turn is proportional to a target flow, which is specified, for example, by input on the operating and display device 28.
  • the proportional target speeds at which the drive motor 6 has to be driven can be stored in a memory for corresponding target delivery flows or can be currently calculated by the control electronics 26.
  • the correspondingly increased rotational speed n 1 which is proportional to an increased first stroke speed
  • the correspondingly reduced drive speed n 2 which is proportional to a second, lower stroke speed of the diaphragm 14
  • these speeds n 1 and n 2 can also be currently calculated on the basis of algorithms stored in the control electronics 26.
  • the first increased stroke speed and a second, lower stroke speed of the diaphragm 14 are set by the control electronics 26 so that the desired desired flow rate, which corresponds to the desired speed n s of the motor 6, is achieved on average over the entire stroke length 32.
  • the quantity remains constant compared to a metering with a constant lifting speed proportional to the target speed n s .
  • the stroke length 34 which takes place with the increased stroke speed, ie with the increased speed n 1, is preferably chosen to be short or short in comparison with the length of the overall stroke 32, so that an increased delivery flow occurs only very briefly at the start of the stroke, which, however, is negligible in terms of the total delivery flow over the total stroke length and nevertheless leads to increased metering accuracy due to the improved closing quality of the check valves 22 and 24.
  • the point 34 preferably corresponds to between 2 and 20% of the total pressure stroke 32.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Control Of Positive-Displacement Pumps (AREA)

Claims (6)

  1. Groupe pompe doseuse comprenant une chambre de dosage (16), un corps de déplacement (14) disposé adjacent à cette chambre, qui peut être mis en mouvement par un entraînement de déplacement (6), ainsi qu'un dispositif de commande (26) pour le pilotage de l'entraînement de déplacement (6),
    caractérisé en ce que
    le dispositif de commande (26) est conçu de telle sorte qu'au moins pour certains débits de consigne qui doivent être générés par la pompe doseuse, il pilote l'entraînement de déplacement (6) de façon telle qu'une course de pression du corps de déplacement (14) soit commencée à une première vitesse de course plus élevée (n1) et poursuivie ensuite à une seconde vitesse de course plus faible (n2),
    la première vitesse de course plus élevée (n1) étant réglée plus rapide que celle nécessaire pour un débit de consigne,
    la seconde vitesse de course plus faible (n2) étant réglée plus lente que celle nécessaire pour un débit de consigne, et
    la première vitesse de course (n1) et la seconde vitesse de course (n2) ainsi que la durée (34) de la course partielle exécutée à la première vitesse de course (n1) étant réglées par le dispositif de commande (26) de façon à atteindre, sur la course de pression complète (32), un débit moyen qui correspond à un débit de consigne.
  2. Groupe pompe doseuse selon la revendication 1, caractérisé en ce que le dispositif de commande (26) est conçu de façon telle que, pour des débits inférieurs à une limite prédéterminée, il pilote l'entraînement de déplacement (6) de façon à ce qu'une course de pression du corps de déplacement (14) soit commencée à une première vitesse de course plus élevée (n1) et poursuivie ensuite à une seconde vitesse de course plus faible (n2).
  3. Groupe pompe doseuse selon l'une des revendications précédentes, caractérisé en ce que, pour faire varier la vitesse de course, l'entraînement de déplacement (6) peut être mis en action à différents régimes (n) ou à différentes vitesses par un pilotage correspondant du dispositif de commande (26).
  4. Groupe pompe doseuse selon l'une des revendications précédentes, caractérisé en ce que l'entraînement de déplacement (6) est un moteur pas-à-pas.
  5. Groupe pompe doseuse selon l'une des revendications précédentes, caractérisé en ce que 2 % ou plus de la course complète sont effectués à la première vitesse de course plus élevée (n1).
  6. Groupe pompe doseuse selon l'une des revendications précédentes, caractérisé en ce que moins de 20 % de la course de pression complète sont effectués à la première vitesse de course plus élevée (n1).
EP10001643.5A 2010-02-18 2010-02-18 Agrégat de pompes de dosage et procédé de commande d'un agrégat de pompes de dosage Active EP2362100B2 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP10001643.5A EP2362100B2 (fr) 2010-02-18 2010-02-18 Agrégat de pompes de dosage et procédé de commande d'un agrégat de pompes de dosage
US13/579,719 US10054117B2 (en) 2010-02-18 2011-02-16 Dosing pump unit and method for controlling a dosing pump unit
JP2012553215A JP5902101B2 (ja) 2010-02-18 2011-02-16 定量ポンプ装置及び定量ポンプ装置の制御方法
PCT/EP2011/000722 WO2011101119A1 (fr) 2010-02-18 2011-02-16 Groupe motopompe de dosage et procédé pour commander un groupe motopompe de dosage
CN201180009714.3A CN102762860B (zh) 2010-02-18 2011-02-16 计量泵机组以及控制计量泵机组的方法

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP10001643.5A EP2362100B2 (fr) 2010-02-18 2010-02-18 Agrégat de pompes de dosage et procédé de commande d'un agrégat de pompes de dosage

Publications (3)

Publication Number Publication Date
EP2362100A1 EP2362100A1 (fr) 2011-08-31
EP2362100B1 EP2362100B1 (fr) 2013-10-09
EP2362100B2 true EP2362100B2 (fr) 2020-07-08

Family

ID=42167593

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10001643.5A Active EP2362100B2 (fr) 2010-02-18 2010-02-18 Agrégat de pompes de dosage et procédé de commande d'un agrégat de pompes de dosage

Country Status (5)

Country Link
US (1) US10054117B2 (fr)
EP (1) EP2362100B2 (fr)
JP (1) JP5902101B2 (fr)
CN (1) CN102762860B (fr)
WO (1) WO2011101119A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11480163B2 (en) 2018-08-27 2022-10-25 Saudi Arabian Oil Company Pumping system with control features for controlling stroke duration and injection volume

Family Cites Families (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4131393A (en) 1977-01-21 1978-12-26 Altex Scientific, Inc. Fluid pump mechanism
US4359312A (en) * 1978-08-15 1982-11-16 Zumtobel Kg Reciprocating pump for the pulsation-free delivery of a liquid
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US4474309A (en) * 1981-10-22 1984-10-02 Oximetrix, Inc. Stepping motor control procedure for achieving variable rate, quasi-continuous fluid infusion
US4470758A (en) * 1981-11-12 1984-09-11 Oximetrix, Inc. Intravenous fluid pump monitor
CA1186166A (fr) * 1982-02-27 1985-04-30 Katsuhiko Saito Chromatographe a liquide
GB8312069D0 (en) * 1983-05-03 1983-06-08 Peritronic Medical Ind Plc Peristaltic pumps
US4681513A (en) * 1985-02-01 1987-07-21 Jeol Ltd. Two-stage pump assembly
DE3546189A1 (de) * 1985-12-27 1987-07-02 Ott Kg Lewa Verfahren und vorrichtung zur durchflussmessung bei oszillierenden verdraengerpumpen
DE3801157A1 (de) * 1988-01-16 1989-08-03 Hagen W Dieter Elektronisch gesteuerte kolbendosierpumpe bzw. maschine
US5056036A (en) * 1989-10-20 1991-10-08 Pulsafeeder, Inc. Computer controlled metering pump
US5249932A (en) * 1991-10-07 1993-10-05 Erik Van Bork Apparatus for controlling diaphragm extension in a diaphragm metering pump
JPH0868379A (ja) * 1994-08-29 1996-03-12 Oriental Motor Co Ltd リニアパルスモータを備えた往復形ポンプ
DE19525557A1 (de) * 1995-07-13 1997-01-16 Knf Flodos Ag Dosierpumpe
JP3822362B2 (ja) * 1998-07-10 2006-09-20 株式会社スギノマシン 液体加圧装置
SE519091C2 (sv) 2000-05-03 2003-01-14 Aga Ab Anordning och förfarande för pumpning av flytande gas, pumpsystem för pumpning av flytande gas samt system och förfarande för cyklisk framställning av polymerprodukter
DE10162773A1 (de) 2001-12-20 2003-07-10 Knf Flodos Ag Sursee Dosierpumpe
DE202005013090U1 (de) 2005-08-19 2007-01-04 Prominent Dosiertechnik Gmbh Motordosierpumpe
DE102005039772A1 (de) * 2005-08-22 2007-03-08 Prominent Dosiertechnik Gmbh Magnetdosierpumpe

Also Published As

Publication number Publication date
WO2011101119A1 (fr) 2011-08-25
EP2362100A1 (fr) 2011-08-31
CN102762860B (zh) 2015-12-16
JP5902101B2 (ja) 2016-04-13
US20130202454A1 (en) 2013-08-08
JP2013519830A (ja) 2013-05-30
EP2362100B1 (fr) 2013-10-09
CN102762860A (zh) 2012-10-31
US10054117B2 (en) 2018-08-21

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