WO2007124873A1 - Pompe de dosage - Google Patents

Pompe de dosage Download PDF

Info

Publication number
WO2007124873A1
WO2007124873A1 PCT/EP2007/003458 EP2007003458W WO2007124873A1 WO 2007124873 A1 WO2007124873 A1 WO 2007124873A1 EP 2007003458 W EP2007003458 W EP 2007003458W WO 2007124873 A1 WO2007124873 A1 WO 2007124873A1
Authority
WO
WIPO (PCT)
Prior art keywords
piston
inlet
valve
pump
pump according
Prior art date
Application number
PCT/EP2007/003458
Other languages
German (de)
English (en)
Inventor
Olaf OHLIGSCHLÄGER
Original Assignee
Thomas Magnete Gmbh
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 Thomas Magnete Gmbh filed Critical Thomas Magnete Gmbh
Priority to EP07724395A priority Critical patent/EP2010785A1/fr
Publication of WO2007124873A1 publication Critical patent/WO2007124873A1/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
    • 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
    • F04B17/046—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids the fluid flowing through the moving part of the motor

Definitions

  • the invention relates to a metering pump according to the features of the generic part of claim 1.
  • Dosierpumpem of the type mentioned operate on the principle of an electromagnetically or otherwise actuated axial reciprocating pump, which promotes well-defined amounts of hydraulic fluid from an inlet region in the outlet of the pump.
  • Piston pumps have a higher efficiency than other pumps. This makes it easier to realize a higher dosing accuracy.
  • a typical but not exclusive field of application is the metering of fuel for a combustion process, e.g. B in an internal combustion engine in the vehicle.
  • Dosing pumps usually have an outlet valve and an inlet valve.
  • the inlet valve is used to allow the hydraulic fluid from the inlet region of the pump in metered quantities to flow into the reciprocating region of the pump piston.
  • the fluid collected in the working chamber of the piston is conveyed and discharged by means of the outlet valve into the outlet region of the pump.
  • At the beginning of a delivery stroke closes the intake valve, so that the inflow to the displacement is closed by the stroke.
  • the inlet valve In the subsequent reverse suction stroke opens the inlet valve, the inlet is opened again and it flows through the resulting negative pressure a defined flow in the displacement.
  • DE 10 2004 028 889 A1 shows a metering pump in the function of a piston pump for conveying a hydraulic fluid, which is used in particular in brake systems of vehicles.
  • the inlet of the hydraulic fluid takes place in the form of a slot-controlled inlet valve, which is arranged in the direction of movement of the pump piston.
  • the fluid collected in the displacement of the pump is conveyed through an outlet valve in the form of a ball seat valve in the outlet of the pump.
  • the control bores for the inlet valve are arranged exclusively in the housing. The holes are however determined by the construction. A positive control that compensates or degrades occurring pressure peaks of the inlet area is not provided in the known arrangement.
  • Hubkolbenraum be prevented by damping measures in the form of a transverse and arranged longitudinal bore in the piston, which, however, relate exclusively to the inlet region of the pump and are permanently connected thereto.
  • the two holes on the inlet side is only a pressure pad, which smoothes the pressure profile of the pending between the inlet port and the inlet opening in the pumped medium. They contain air and are not suitable as feed.
  • the longitudinal bore is closed at its end facing the displacement with a seal. The inlet to the displacement takes place exclusively through a suction hole in the housing, which is closed when the piston is passed over and reopened in a subsequent rearward suction stroke.
  • a "positive control” is realized by the positioning of the inlet, which is positioned such that it establishes a connection between the inlet area and the lifting area in each exposed position of the piston and is only closed when the delivery end position is reached.
  • the supply bore remains open until the piston reaches its final delivery position, and only when this position is reached is a further inflow of the hydraulic medium into the displacement prevented
  • control bores a balance between the pressure peak and the required metering accuracy is achieved and realized in the displacement compensation for the pressure occurring during the delivery stroke. This is achieved only by modifying the bore, "slot geometry,” or other combinations of different sizes or different positioned holes, and eliminating the need for stronger return springs and higher drive forces.
  • the inflow comprises an additional inflow in the housing with a further inlet valve.
  • Both intake valves have different functions.
  • the inlet valve arranged in the housing serves in the delivery stroke for controlling and exact filling of the displacement.
  • the intake valve in the piston reduces the negative pressure in the displacement during the return / or suction stroke of the piston.
  • the valve inlet in the housing may comprise a simple inlet bore, with which the conveying fluid is conveyed into the displacement of the piston during a suction stroke, and which opens and / or closes when passing over the piston.
  • such an inlet valve can also be configured slit-controlled, wherein a plurality of control slots can also be provided, which are arranged concentrically to one another.
  • the control bores for such a valve are advantageous in the space between the Innident the cylindrical housing and a guide sleeve for the piston arranged.
  • the guide sleeve has an opening to the displacement of the pump.
  • the inlet valve in the pump piston advantageously comprises a blind bore in the direction of the inlet region with a subsequent transverse bore which opens in the inlet region of the pump.
  • a seat valve is provided on the front side of the piston.
  • the longitudinal bore is closed by the seat body in the form of a ball.
  • the mouth of the transverse bore to the inlet area remains open until the piston has reached its final delivery position.
  • the overpressure present in the inlet area is also applied to the seat valve at the mouth to the displacement of the piston.
  • the transverse bore closes the inlet to the ball seat valve in the end position of the piston, the pressure peak in the inlet area of the pump can not open the ball seat valve. There is no over-promotion. On the return or suction stroke, however, the transverse bore releases the conveying path again. Now, the overpressure in the suction part of the pump compared to the negative pressure in the capacity slightly open the ball seat valve, thus allowing a smooth piston stroke.
  • the guide and / or bearing sleeve arranged between the housing and the piston is advantageously used.
  • This type of storage of the piston is state of the art today.
  • the axial length of the slide bearing sleeve extending in the direction of the transverse bore is dimensioned as a function of the piston stroke.
  • the position of the transverse bore and the Ausragin the guide sleeve is arranged so that upon reaching the winningendhubes the transverse bore is covered by the Ausragmother of the sleeve in this direction and is closed.
  • the sliding bearing of the piston in the guide sleeve prevents fluid material between piston and sleeve can penetrate into the displacement in the closed position.
  • the dosing pump according to the invention is advantageously magnet-actuated.
  • the stroke of the piston is generated with an integrated electromagnetic system, in which the piston is firmly connected to an armature of a solenoid, which is centrally surrounded by a coil.
  • the pump piston forms an anchor rod arranged in the stroke direction of the armature, which passes through the cone of the magnet.
  • all cavities in the inlet region and in the displacement of the piston are filled with hydraulic fluid.
  • the armature displaces the piston against the force of a compression spring, which is arranged between the armature and the bearing sleeve of the piston. Due to the pumped medium collected in the displacement, the outlet valve is opened and the fluid is ejected.
  • FIG. 1 shows a cross-sectional view of the invention in a first position of the pump piston.
  • FIG. 2 shows a section of FIG. 1.
  • Fig. 3 shows the detail of Fig. 1 in a different position of the pump piston.
  • Fig. 1 shows in a cross-sectional view of a solenoid-operated fuel metering pump 1, which is used for example for diesel injection or for use in motor vehicle heating systems.
  • the cylindrical pump piston 12 is fixed to the likewise cylindrical Magnet armature 13 is connected, which is surrounded centrally by a coil body 21 embedded in a magnetic coil 14.
  • the flow direction of the fuel is from right to left in the direction of arrow X.
  • the pump 1 essentially comprises three areas, an inlet area 2, a pump area 3 and an outlet area 4.
  • the inlet and pump area 2, 3 are shown enlarged in FIGS. 2 and 3.
  • the inlet portion 2 has, as shown in Fig. 1 rightmost, an intake 5 with an axial bore 7 for sucking the fuel.
  • the entrance of the bore 7 is closed with a protective cap 6 against contamination in the delivery and transport state.
  • the fuel flows through a filter 8 and enters a region designated as the zero closure 9. This region prevents the fuel flow into the pump region 3 when the pump piston 12 is not actuated.
  • the zero seal 9 comprises a plastic sleeve 10, in the opening region of which the filter 8 is arranged. Its sleeve bottom has an axial passage opening 11 in the direction of the pump region 2 which, when the magnet armature 13 is not actuated, as is apparent in particular from FIG.
  • the magnet armature 13 has a continuous stepped anchor bore 18 whose diameter is slightly increased in the direction of its cone 17 and in the other direction is designed as a chamber 19 in which the fuel can flow when the through-opening 11 is open.
  • the pump piston 12 is firmly inserted as a rod. stressed.
  • the armature 13, the zero closure 9 and the filter 8 are surrounded by an existing of ferromagnetic material anchor housing 20 and sealed against the plastic sleeve 10 of the zero degree 9 and the intake manifold 5 by two O-ring seals 54, 55.
  • the armature 13 and thus the pump piston 12 is axially displaceable in the armature housing 20 movable.
  • the outer wall of the armature 13 and the inner wall of the armature housing 20 are arranged at a distance from one another and form an inlet channel 42, which establishes a connection from the chamber 19 in the zero end 9 to the pump region 3.
  • the bobbin 21 On the armature housing 20, the bobbin 21 is pushed in its left end portion, which is suitably connected by brazing or welding to the armature housing 20, and surrounded by a magnetic housing 22, at its in the direction of the inlet portion 2 extending end with the armature housing 20 is firmly connected.
  • a likewise made of ferromagnetic material sleeve 23 is inserted, whose end cone 24 facing conical opening is effective as a magnetic pole, and, as the armature housing 20, in the Clamp seat within the bobbin 21 holds.
  • a bearing sleeve 26 is fitted with a suction port 25, which secures as sliding bearing 27 the pressed-in the armature 13 pump piston 12 an axial guidance.
  • a further inlet channel 43 is arranged, which connects the Hubankerraum 29 with the suction port 25.
  • the bobbin 21 is delimited in the direction of the outlet region 4 by a conical disk 33, which forms the radial extending region of the magnetic pole.
  • the bobbin 21 has at this end a radial cover 35 which is axially penetrated by the sleeve 23 and with this is firmly connected.
  • the energization of the coil 14 via a protruding from the cover coupling plug 34.
  • the cover 35 is sealed relative to the sleeve 23 by a further O-ring seal 56.
  • Another O-ring seal 57 seals it from the magnet housing 22.
  • the end faces of the sleeve 23 and the armature 13 are arranged in the middle of the bobbin 21 at an axial distance from one another and form a Hubankerraum 29, which is filled in the armature region with fuel in the de-energized state through the inlet channel 42.
  • a compression spring 28 is arranged, which is supported with its one end against the end cone 24 of the armature 13 and supported with its other end against the protruding end of the bearing sleeve 26.
  • the inlet channel 43 discharges via the suction opening 25 into a displacement 30, which determines the Nutzhub Silver the pump 1 in the axial direction and two inlet valves 31, 32, of which the valve 31 in the housing and the valve 32 are arranged in the piston 12. In the radial direction of the displacement 30 is determined by the inner diameter of the sleeve 23.
  • the inlet valve 31 in the housing is formed by the suction opening 25 and the stroke movement of the pump piston 12.
  • the associated inlet channel 43 is opened or closed by the position of the piston 12.
  • the other inlet valve 32 is arranged on the end face of the piston 12. It forms a series-connected valve arrangement with a transverse bore 37 and subsequent axial blind bore 36, which is positively controlled closed as soon as the piston 12 has reached the end of the delivery stroke.
  • the transverse bore 37 which is connected to the lifting armature space 29 of the Lass region 2 is in communication, is positioned so that it is closed by reaching the winningendhubes of the piston 12 of the bearing sleeve 26. However, if this inlet is opened by the position of the piston 12, the transverse bore 37 and the axial blind bore 36 form a further inlet for the displacement 30 of the pump 1.
  • the mouth region of the blind bore 36 has a seat valve 38.
  • the inlet via the transverse and blind bore 36, 37 is closed in the displacement 30.
  • the closure is effected by a seat body 41 and a further compression spring 39, which is supported in the valve seat 40.
  • the outlet region 4 essentially comprises an outlet valve 46 and an outlet nozzle 47 bounding the pump, the bore 40 of which is closed by a further protective cap 48 in the transport and storage state.
  • the exhaust valve 46 is also designed like the second inlet valve 31 in the piston as a seat valve.
  • the associated valve seat 50 is inserted with a central opening 51 for the passage 45 of the fuel.
  • the associated seat body is designed as a ball 52 which closes the opening 51 by a further compression spring 53. During the delivery stroke of the fuel, the ball 52 is raised from its sitting position against the force of the compression spring 53 and conveys the fuel into the outlet connection 47.
  • FIGS. 1 and 2 show the de-energized state in which all interspaces in the pump 1 are flooded with fuel. This concerns the Hubankerraum 29 im Inlet area 2 and in particular the displacement 30 in the pumping area 3.
  • the first inlet valve 31, which is formed by the inlet channel 43 and the suction opening 25, is open.
  • the second inlet valve 32 is closed, although the inlet in the piston 12 is still free, since the transverse bore 37 functioning as a control bore is not yet covered by the bearing sleeve 26 in this position. The delivery pressure of the fuel occurring in the inlet region 2 is thus directly applied to the seat valve 38.
  • the coil 14 is energized and connected to the armature 13 pump piston 12 is moved in the direction against the stop 44 in its bainendposition.
  • the suction opening 25 in the Lagerh ⁇ lse 26 is positioned so that it is already closed at the beginning of the delivery stroke by driving over the piston 12, so that no fuel can flow through the inlet channel 43.
  • the present invention has been explained using the example of two inflows, each with two inlet valves. However, it is understandable without further explanation to those skilled in the art that the invention can also be used in metering pumps in which the inflow takes place exclusively via the second inlet valve 32 in the piston and the inflow via the first inlet valve 31 is dispensed with, so that the valve 32 in addition to control functions at the same time the filling of the displacement 30 takes over. For this purpose, only the seat valve 38 provided there is to be interpreted accordingly.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details Of Reciprocating Pumps (AREA)

Abstract

Pompe de dosage comprenant un corps en forme de cylindre avec un piston de pompe (12) exécutant des mouvements d'aller et retour dans le corps pour refouler (course de refoulement) et aspirer (course d'aspiration) un fluide hydraulique d'une zone d'entrée (2) dans une zone de sortie (4) de la pompe (1), un espace de levée (30) dans lequel le fluide est alimenté en pression au moyen du piston de la pompe (12), une vanne de sortie (46) pour l'évacuation orientée du fluide hydraulique se trouvant dans l'espace de levée (30) et une vanne d'entrée (32) disposée dans le piston de la pompe (12) pour l'alimentation définie du fluide hydraulique de la zone d'entrée (2) de la pompe dans l'espace de levée (30). Au moins une vanne d'entrée (32) présente des forages de commande (36, 37), avec lesquels l'alimentation est ouverte jusqu'à ce que la course de fin de refoulement du piston (12) est atteinte et que l'alimentation vers l'espace de levée (30) est interrompue grâce à cette position.
PCT/EP2007/003458 2006-04-27 2007-04-20 Pompe de dosage WO2007124873A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP07724395A EP2010785A1 (fr) 2006-04-27 2007-04-20 Pompe de dosage

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006019584.1 2006-04-27
DE200610019584 DE102006019584B4 (de) 2006-04-27 2006-04-27 Dosierpumpe

Publications (1)

Publication Number Publication Date
WO2007124873A1 true WO2007124873A1 (fr) 2007-11-08

Family

ID=38261668

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2007/003458 WO2007124873A1 (fr) 2006-04-27 2007-04-20 Pompe de dosage

Country Status (3)

Country Link
EP (1) EP2010785A1 (fr)
DE (1) DE102006019584B4 (fr)
WO (1) WO2007124873A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100111728A1 (en) * 2008-11-03 2010-05-06 Thomas Magnete Gmbh Reciprocating Piston Pump
US8225602B2 (en) 2009-06-11 2012-07-24 Stanadyne Corporation Integrated pump and injector for exhaust after treatment
US9359999B2 (en) 2011-02-25 2016-06-07 Thomas Magnete Gmbh Pressure-regulating reciprocating-piston pump having a magnet drive
US10047736B2 (en) 2011-07-15 2018-08-14 Thomas Magnete Gmbh Metering pump

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008013441B4 (de) * 2008-03-10 2010-10-14 Thomas Magnete Gmbh Dosierpumpe
DE102008055611B4 (de) * 2008-11-03 2010-09-16 Thomas Magnete Gmbh Hubkolbenpumpe
DE102008057365B4 (de) * 2008-11-14 2015-12-17 Eberspächer Climate Control Systems GmbH & Co. KG Verfahren zum Betreiben einer elektromagnetisch betriebenen Dosierpumpe mit Anschlagdämpfung
DE102010013106A1 (de) 2010-03-26 2011-09-29 Thomas Magnete Gmbh Pumpe
DE102012001963B4 (de) * 2012-02-02 2013-12-19 Thomas Magnete Gmbh Dosierpumpe und Verfahren zum Betrieb einer Dosierpumpe mit verschieblichem Auslassventil
DE102012010146B4 (de) * 2012-05-24 2016-07-07 Thomas Magnete Gmbh Elektromagnetische Pumpe
DE102014001126A1 (de) 2014-01-28 2015-07-30 Thomas Magnete Gmbh Dosierpumpe und Verfahren zum Betrieb einer Dosierpumpe mit einem verschieblichen Auslassventil
DE102015007464A1 (de) * 2015-06-09 2016-12-15 Thomas Magnete Gmbh Hubkolbenpumpe mit eingangsseitiger Förderstrombegrenzung
DE102015007465A1 (de) * 2015-06-09 2016-12-15 Thomas Magnete Gmbh Hubkolbenpumpe mit eingangsseitiger Förderstrombegrenzung und Verfahren zum Betrieb der Hubkolbenpumpe
DE102017004949B4 (de) 2017-05-23 2021-12-09 Thomas Magnete Gmbh Hubkolbenpumpe
DE102020111328A1 (de) 2020-04-27 2021-10-28 Thomas Magnete Gmbh Verdrängerbaugruppe

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1653538A1 (de) * 1968-02-03 1972-02-17 Langen & Co Kolbenpumpe
DE4242420A1 (de) * 1992-12-16 1994-06-23 Bosch Gmbh Robert Pumpe für ein hydraulisches System
DE4328621A1 (de) * 1993-08-26 1995-03-02 Thomas Magnete Gmbh Elektromagnetisch betreibbare Pumpe, insbesondere Dosierpumpe
WO2004040135A1 (fr) * 2002-11-01 2004-05-13 Danfoss A/S Pompe a liquide alternative servant a alimenter un bruleur domestique en combustible liquide
DE102004028889A1 (de) * 2004-06-15 2006-01-05 Robert Bosch Gmbh Kolbenpumpe mit schlitzgesteuertem Einlassventil
EP1624188A2 (fr) * 2004-08-04 2006-02-08 Mikuni Corporation Pompe à piston et procédé pour contrôler le débit de la pompe

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004037146A1 (de) * 2004-07-30 2006-03-23 Robert Bosch Gmbh Kolbenpumpe mit optimiertem Schadraum

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1653538A1 (de) * 1968-02-03 1972-02-17 Langen & Co Kolbenpumpe
DE4242420A1 (de) * 1992-12-16 1994-06-23 Bosch Gmbh Robert Pumpe für ein hydraulisches System
DE4328621A1 (de) * 1993-08-26 1995-03-02 Thomas Magnete Gmbh Elektromagnetisch betreibbare Pumpe, insbesondere Dosierpumpe
WO2004040135A1 (fr) * 2002-11-01 2004-05-13 Danfoss A/S Pompe a liquide alternative servant a alimenter un bruleur domestique en combustible liquide
DE102004028889A1 (de) * 2004-06-15 2006-01-05 Robert Bosch Gmbh Kolbenpumpe mit schlitzgesteuertem Einlassventil
EP1624188A2 (fr) * 2004-08-04 2006-02-08 Mikuni Corporation Pompe à piston et procédé pour contrôler le débit de la pompe

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100111728A1 (en) * 2008-11-03 2010-05-06 Thomas Magnete Gmbh Reciprocating Piston Pump
US8696330B2 (en) 2008-11-03 2014-04-15 Thomas Magnete Gmbh Reciprocating piston pump
US8225602B2 (en) 2009-06-11 2012-07-24 Stanadyne Corporation Integrated pump and injector for exhaust after treatment
US9359999B2 (en) 2011-02-25 2016-06-07 Thomas Magnete Gmbh Pressure-regulating reciprocating-piston pump having a magnet drive
US10047736B2 (en) 2011-07-15 2018-08-14 Thomas Magnete Gmbh Metering pump

Also Published As

Publication number Publication date
DE102006019584A1 (de) 2007-11-08
DE102006019584B4 (de) 2008-06-05
EP2010785A1 (fr) 2009-01-07

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