EP1764504A1 - Pompe à dosage activé par force electro-magnétique - Google Patents

Pompe à dosage activé par force electro-magnétique Download PDF

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Publication number
EP1764504A1
EP1764504A1 EP06090168A EP06090168A EP1764504A1 EP 1764504 A1 EP1764504 A1 EP 1764504A1 EP 06090168 A EP06090168 A EP 06090168A EP 06090168 A EP06090168 A EP 06090168A EP 1764504 A1 EP1764504 A1 EP 1764504A1
Authority
EP
European Patent Office
Prior art keywords
piston
valve
suction
pressure
armature
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.)
Withdrawn
Application number
EP06090168A
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German (de)
English (en)
Inventor
Karl-Heinz Hirschmann
Arne Sommerfeld
Stefan Barten
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Individual
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Individual
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Filing date
Publication date
Application filed by Individual filed Critical Individual
Publication of EP1764504A1 publication Critical patent/EP1764504A1/fr
Withdrawn legal-status Critical Current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
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
    • F04B17/04—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids
    • F04B17/042—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids the solenoid motor being separated from the fluid flow
    • F04B17/044—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids the solenoid motor being separated from the fluid flow using solenoids directly actuating the piston

Definitions

  • the invention relates to an electromagnetically operable metering pump according to the preamble of claim 1. Use find these pumps specifically as fuel pumps in fuel firing. For this type of application, a nearly continuous flow is desired in all work areas.
  • the dosing pump from the publication DE 102 27 659 B4 has another disadvantage.
  • the accumulator in the metering pump causes a smoothing of the flow.
  • the accumulator must first be filled and emptied after switching off the piston drive inevitably, resulting in an undefined behavior of the heater.
  • the invention has for its object to provide a simple and inexpensive pump that produces a virtually continuous flow without pressure accumulator and is reliably sealed against the environment.
  • an electromagnetically operable metering pump is provided with a movable piston, which is at the same time partially armature of an electromagnet, whose annular winding around the armature generates a magnetic field in the current-carrying state, which exerts a force on the armature or piston, the latter against the force a spring moves, which moves the piston or armature back to its initial state in the de-energized state, in which it closes the outflow opening of the metering pump, wherein the piston sucks the medium to be delivered via an inlet opening in the housing, on the pressure side of the metering pump by a Outflow opening is pressed in the housing, wherein the piston is a stepped piston, the suction-side displacement is preferably twice as large as the pressure-side displacement, the piston is equipped with at least one preloaded valve which opens during the forward movement of the piston, which ch the volume located in the suction through the stepped piston fills the pressure-side displacement and pushes the rest in the outflow
  • the valves used have different designs, wherein the suction-side valve is a plate valve, which has no mechanical bias, whereby the valve opens or closes at minimum pressure differences and that because of the prestressed valve located in the stepped piston, the pressure difference for opening the valve in the piston is higher than that at the suction-side valve, whereby a minimum pressure in the suction chamber adjusts to the intake during the movement of the piston, which forcibly closes the suction-side valve, and the bias of the valve during the movement of the piston to the pressure opening out causes perfect sealing of the suction chamber during suction, thereby adjusting a required for the suction of the pumped medium and the opening of the suction-side valve vacuum.
  • the suction-side plate valve has a low dead volume, whereby the ratio of Schad- to working space is minimized suction side, whereby even at minimum strokes of the stepped piston suction is achieved and thus even at low strokes of the stepped piston promotion is possible, resulting in conveyor frequencies, due to the different natural frequencies of the valves also does not lead to a dynamic coupling via the liquid column.
  • the flow processes are forcibly controlled via the valves. Behave the stroke volume or cross-sectional areas of the piston suction and pressure side as 2: 1, the flow rate is the same in both directions of movement on average.
  • the inventive use of a plate valve without bias as a suction-side valve additionally generated by the valves flow fluctuations are minimized.
  • the plate valve has flaps with at least one elastic joint and is preferably designed in membrane construction as a parallel-stroke valve with at least one elastic joint.
  • This type of valve has a minimal effective dead volume compared to the common, eg with spring-loaded balls.
  • the moving masses of the piston and the valves are minimized, resulting in a higher delivery frequency compared to the known metering pumps. This causes the same Flow rate a smaller size.
  • the pump can be pressure-tight with fewer components.
  • suction-side valve As a ball valve
  • valve in the stepped piston as a plate valve.
  • valves in front of the outflow opening may also be expedient to provide a further valve in front of the outflow opening, which may be designed as a plate valve in membrane construction or ball valve.
  • Figure 1 shows the pump in the de-energized state, i. the piston is in the rest position.
  • a compression spring 51 presses a stepped piston 52 in the rest position and an abutting O-ring 53 terminates the pump on the pressure side.
  • a filter 67 is integrated in the intake.
  • a plate valve 58 is sealed on the suction side due to the pressure load.
  • the sucked-in conveying medium flows via a ball valve 59 integrated in the stepped piston 52 into a pressure chamber 60 via a transverse bore 71.
  • the pressure chamber 60 fills and in addition the excess sucked-in conveying medium is conveyed into an outflow opening 61.
  • the energization of the coil 54 is interrupted.
  • the prestressed compression spring 51 pushes the stepped piston 52 back.
  • the suction-side pressure-controlled plate valve 58 opens and the stepped piston sucks due to the increase in volume of the working chamber 66 fluid into the working space 66.
  • the ball valve 59 is forcibly closed.
  • the conveying medium located in the pressure chamber 60 is simultaneously conveyed into the outflow opening 61.
  • a volume defined by the stepped piston is conveyed into the outflow opening 61 both during the outward and return strokes.
  • the conveyed partial volumes are each the same size.
  • the pump requires despite its Doppelhub characterizing according to the invention only two valves.
  • the suction takes place only during the movement in the direction of the outflow opening 61.
  • the sucked volume corresponds to the volume delivered during the outward and return stroke.
  • the intake behavior of the pump is improved according to the invention, since the design-related proportionate dead space relative to the working space 66 is less expensive.
  • the suction-side plate valve 58 is designed so that it has no bias. As a result, this already opens at the smallest pressure differences in the movement of the stepped piston 52 in the direction of the pressure opening, so that the suction process begins immediately with the piston movement. During the movement of the stepped piston 52 to the suction side, the plate valve 58 is forcibly closed by the generated pressure in the working space 66.
  • the preferably to be used ball valve 59 in the stepped piston 52 must be biased for a good intake of the pump already in the pressureless state to ensure a good seal of the working chamber 66 during suction.
  • the bias at. the movement of the stepped piston 52 to the intake port set a basic pressure level in the working space 66, which is required for a safe closing of the plate valve 58.
  • this offers a ball valve, but in principle could also be a plate valve of the same type as the suction-side plate valve 58 are used with bias.
  • Decisive for the function even at higher control frequencies is that the two valves have a different characteristic with regard to the natural frequencies, so that a dynamic interaction between the valves on the medium is excluded and thus a secure sealing and opening of the valves is guaranteed.
  • a lying between the working space 66 and the pressure chamber 60 leakage oil space 62 does not contribute to the promotion. Due to the existing leaks of the stepped piston 52 in the piston guide 55, leakage oil flows into this space. In order to ensure the function of the pump, this space must be kept unpressurized, that is, it must be made a fluidic connection to the suction side.
  • This space must be kept unpressurized, that is, it must be made a fluidic connection to the suction side.
  • This space must be kept unpressurized, that is, it must be made a fluidic connection to the suction side.
  • the cable of the coil 54 are pressure-tight out through a bore 69 to the outside.
  • the sealing of the entire pump takes over a housing 68.
  • FIG. 2 shows a preferred variant of the plate valve 58 in membrane construction.
  • a planar sealing body or a flap 80 is suspended on four elastic joints 81, whereby a parallel stroke of the sealing body 80 is made possible.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Reciprocating Pumps (AREA)
EP06090168A 2005-09-14 2006-09-13 Pompe à dosage activé par force electro-magnétique Withdrawn EP1764504A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102005044904A DE102005044904B4 (de) 2005-09-14 2005-09-14 Elektromagnetisch betreibbare Dosierpumpe

Publications (1)

Publication Number Publication Date
EP1764504A1 true EP1764504A1 (fr) 2007-03-21

Family

ID=37487747

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06090168A Withdrawn EP1764504A1 (fr) 2005-09-14 2006-09-13 Pompe à dosage activé par force electro-magnétique

Country Status (2)

Country Link
EP (1) EP1764504A1 (fr)
DE (1) DE102005044904B4 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008055611A1 (de) * 2008-11-03 2010-05-06 Thomas Magnete Gmbh Hubkolbenpumpe
EP2491968A1 (fr) * 2011-02-24 2012-08-29 Erbe Elektromedizin GmbH Dispositif de pompe pour fluide stérile et système de pompe doté d'un tel dispositif de pompe
WO2012113579A1 (fr) * 2011-02-25 2012-08-30 Thomas Magnete Gmbh Pompe à piston alternatif régulatrice de pression à entraînement magnétique
CN102758755A (zh) * 2012-07-27 2012-10-31 徐荣兰 一种电磁式直线活塞泵

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102748165B (zh) * 2012-07-10 2014-06-04 余姚晟祺塑业有限公司 汽油精泵
JP2020041469A (ja) * 2018-09-10 2020-03-19 日本電産トーソク株式会社 電磁ポンプ

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3479959A (en) * 1967-10-23 1969-11-25 William N Christensen Electromagnetic metering pump
DE2017680A1 (de) * 1970-04-14 1971-10-28 Swf Tauchpumpe mit elektromagnetischem Antrieb
DE2410768A1 (de) * 1974-03-07 1975-09-18 Danfoss As Elektromagnetische pumpe
US20050047941A1 (en) * 2003-01-14 2005-03-03 Michael Humburg Metering pump device for a vehicle heater

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT116630B (de) * 1928-07-27 1930-03-10 Gustav Ing Schoengut Flüssigkeitspumpe mit elektrischem Antrieb.
US1822242A (en) * 1928-07-27 1931-09-08 Schongut Gustav Pump for liquids
DE2315842B2 (de) * 1973-03-30 1977-12-29 Fa. J. Eberspächer, 7300 Esslingen Durch einen elektromagneten betaetigte brennstoffkolbenpumpe, insbesondere fuer brennstoffeuerungen
DE7631318U1 (de) * 1976-10-06 1978-02-02 Reinhardt-Technik (Gmbh & Co), 5883 Kierspe Dosier-kolbenpumpe
IT1130947B (it) * 1980-03-10 1986-06-18 De Dionigi Manlio Perfezionamenti alle pompe elettromagnetiche alternative in particolare per fluidi non viscosi
DE4328621C2 (de) * 1993-08-26 2002-11-28 Thomas Magnete Gmbh Elektromagnetisch betreibbare Pumpe, insbesondere Dosierpumpe
DE19917009A1 (de) * 1999-04-15 2000-10-19 Leybold Vakuum Gmbh Kolbenvakuumpumpe mit Gaseinlass und Gasauslass
DE10204708A1 (de) * 2002-02-05 2003-08-14 Webasto Thermosysteme Gmbh Mobiles Heizgerät mit einer Brennstoffpumpe
DE10227659B4 (de) * 2002-06-20 2004-12-23 Webasto Ag Dosierpumpe für ein Heizgerät
DE10233302B4 (de) * 2002-07-22 2006-06-14 Knf Neuberger Gmbh Pumpe

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3479959A (en) * 1967-10-23 1969-11-25 William N Christensen Electromagnetic metering pump
DE2017680A1 (de) * 1970-04-14 1971-10-28 Swf Tauchpumpe mit elektromagnetischem Antrieb
DE2410768A1 (de) * 1974-03-07 1975-09-18 Danfoss As Elektromagnetische pumpe
US20050047941A1 (en) * 2003-01-14 2005-03-03 Michael Humburg Metering pump device for a vehicle heater

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008055611A1 (de) * 2008-11-03 2010-05-06 Thomas Magnete Gmbh Hubkolbenpumpe
EP2491968A1 (fr) * 2011-02-24 2012-08-29 Erbe Elektromedizin GmbH Dispositif de pompe pour fluide stérile et système de pompe doté d'un tel dispositif de pompe
WO2012113579A1 (fr) * 2011-02-25 2012-08-30 Thomas Magnete Gmbh Pompe à piston alternatif régulatrice de pression à entraînement magnétique
RU2553887C2 (ru) * 2011-02-25 2015-06-20 Томас Магнете Гмбх Поршневой насос с регулировкой давления, имеющий магнитный привод
US9359999B2 (en) 2011-02-25 2016-06-07 Thomas Magnete Gmbh Pressure-regulating reciprocating-piston pump having a magnet drive
CN102758755A (zh) * 2012-07-27 2012-10-31 徐荣兰 一种电磁式直线活塞泵
CN102758755B (zh) * 2012-07-27 2015-04-15 徐荣兰 一种电磁式直线活塞泵

Also Published As

Publication number Publication date
DE102005044904B4 (de) 2009-12-03
DE102005044904A1 (de) 2007-03-15

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