EP3423717B1 - Electromagnetically actuatable inlet valve and high-pressure pump comprising an inlet valve - Google Patents

Electromagnetically actuatable inlet valve and high-pressure pump comprising an inlet valve Download PDF

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Publication number
EP3423717B1
EP3423717B1 EP17700485.0A EP17700485A EP3423717B1 EP 3423717 B1 EP3423717 B1 EP 3423717B1 EP 17700485 A EP17700485 A EP 17700485A EP 3423717 B1 EP3423717 B1 EP 3423717B1
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EP
European Patent Office
Prior art keywords
magnet
inlet valve
magnet armature
intermediate element
pump
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
EP17700485.0A
Other languages
German (de)
French (fr)
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EP3423717A1 (en
Inventor
Gabriel CICHON
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.)
Robert Bosch GmbH
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Robert Bosch GmbH
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Publication date
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Publication of EP3423717A1 publication Critical patent/EP3423717A1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F02M59/366—Valves being actuated electrically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0075—Stop members in valves, e.g. plates or disks limiting the movement of armature, valve or spring
    • 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
    • F04B49/22—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 by means of valves
    • F04B49/24—Bypassing
    • F04B49/243—Bypassing by keeping open the inlet valve
    • 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
    • F04B7/0076—Piston machines or pumps characterised by having positively-driven valving the members being actuated by electro-magnetic means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/02—Fuel-injection apparatus having means for reducing wear
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/80—Fuel injection apparatus manufacture, repair or assembly
    • F02M2200/8084—Fuel injection apparatus manufacture, repair or assembly involving welding or soldering
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/90—Selection of particular materials
    • F02M2200/9053—Metals
    • F02M2200/9069—Non-magnetic metals
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01F—MAGNETS; INDUCTANCES; TRANSFORMERS; SELECTION OF MATERIALS FOR THEIR MAGNETIC PROPERTIES
    • H01F7/00—Magnets
    • H01F7/06—Electromagnets; Actuators including electromagnets
    • H01F7/08—Electromagnets; Actuators including electromagnets with armatures
    • H01F7/16—Rectilinearly-movable armatures
    • H01F2007/1661—Electromagnets or actuators with anti-stick disc

Definitions

  • the invention relates to an electromagnetically actuated inlet valve for a high-pressure pump, in particular a fuel injection system, according to the preamble of claim 1. Furthermore, the invention relates to a high-pressure pump with such an inlet valve.
  • An electromagnetically actuated inlet valve for a high-pressure pump of a fuel injection system is by JP 2004 014700 A known.
  • the high-pressure pump has at least one pump element with a pump piston which is driven in a lifting movement and delimits a pump working space.
  • the pump work space can be connected to an inlet for the fuel via the inlet valve.
  • the inlet valve comprises a valve member which interacts with a valve seat for control and which is movable between an open position and a closed position. In its closed position, the valve member comes to rest on the valve seat.
  • the inlet valve comprises an electromagnetic actuator, through which the valve member can be moved.
  • the electromagnetic actuator has a magnet armature which acts at least indirectly on the valve member, a magnet coil surrounding the magnet armature and a magnet core.
  • the magnet armature is guided displaceably in a carrier element, the carrier element and the magnetic core being connected to one another via a sleeve-shaped component.
  • the solenoid When the solenoid is energized, the magnet armature can be moved against the force of a return spring and comes into contact with the magnet core via a disc-shaped intermediate element.
  • the intermediate element also serves to seal a space in which the magnetic coil is arranged. The intermediate element prevents so-called magnetic sticking, which would make it difficult to move the armature away from the magnetic core.
  • the assembly of the intermediate element is complex because it is designed as a separate component and can be welded to the magnetic core.
  • the inlet valve according to the invention with the features of claim 1 has the advantage that the assembly of the intermediate element is simplified in that it is welded to the sleeve-shaped component or is formed in one piece or forms the sleeve-shaped component via a collar arranged on its radially outer edge region.
  • the intermediate element therefore does not have to be installed as a separate component.
  • Figure 1 2 shows a schematic longitudinal section through a high pressure pump
  • Figure 2 in an enlarged view Figure 1 II marked section with an inlet valve of the high pressure pump
  • Figure 3 one in Figure 2 with III designated section in a further enlarged representation according to a first embodiment
  • Figure 4 the section III according to a second embodiment.
  • a high-pressure pump is shown in sections, which is provided for fuel delivery in a fuel injection system of an internal combustion engine.
  • the high pressure pump has at least one pump element 10, which in turn has a pump piston 12, which is driven by a drive in a lifting movement, is guided in a cylinder bore 14 of a housing part 16 of the high-pressure pump and delimits a pump working chamber 18 in the cylinder bore 14.
  • a drive shaft 20 with a cam 22 or eccentric can be provided as the drive for the pump piston 12, on which the pump piston 12 is supported directly or via a tappet, for example a roller tappet.
  • the pump work chamber 18 can be connected to a fuel inlet 26 via an inlet valve 24 and to a reservoir 30 via an outlet valve 28.
  • the pump work chamber 18 can be filled with fuel with the inlet valve 24 open.
  • fuel is displaced from the pump work chamber 18 by this and delivered into the accumulator 30.
  • valve member 34 protrudes from the through bore 32 on the side of the housing part 16 facing away from the pump working space 18 and a support element 48 is fastened thereon.
  • a valve spring 50 is supported on the support element 48, which on the other hand is supported on a region of the housing part 16 surrounding the stem 36 of the valve member 34. Through the valve spring 50, the valve member 34 is acted upon in an adjusting direction A in its closing direction, the valve member 34 with its sealing surface 42 abutting the valve seat 40 in its closed position.
  • the valve spring 50 is designed, for example, as a helical compression spring.
  • the inlet valve 24 can be actuated by an electromagnetic actuator 60, which is particularly shown in FIG Figure 2 is shown.
  • the actuator 60 is controlled by an electronic control device 62 depending on the operating parameters of the internal combustion engine to be supplied.
  • the electromagnetic actuator 60 has a magnet coil 64, a magnet core 66 and a magnet armature 68.
  • the electromagnetic actuator 60 is arranged on the side of the inlet valve 24 facing away from the pump working space 18.
  • the magnetic core 66 and the magnetic coil 64 are arranged in a housing 70 which can be constructed in several parts and which can be fastened to the housing part 16 of the high-pressure pump.
  • the housing 70 can, for example, be fastened to the housing part 16 by means of a fastening element which overlaps this and which is screwed onto a cylindrical section 74 of the housing part 16 provided with an external thread.
  • the magnet armature 68 is at least essentially cylindrical and is displaceably guided via its outer jacket in a bore 76 in a carrier element 78 arranged in the housing 70.
  • the bore 76 in the carrier element 78 extends at least approximately coaxially to the through bore 32 in the housing part 16 and thus to the valve member 34.
  • the carrier element 78 has a cylindrical outer shape in its end region 77 facing away from the housing part 16.
  • the magnetic core 66 is arranged in the housing 70 on the side of the carrier element 78 facing away from the housing part 16 and has a cylindrical outer shape.
  • the disc-shaped intermediate element 92 is arranged within the sleeve-shaped component 90.
  • the intermediate element 92 has a central opening 93 through which the return spring 82 passes.
  • the component 90 and the intermediate element 92 can be made of steel and the intermediate element 92 is formed in one piece with the component 90 or is welded to the component 90 at its radially outer edge region.
  • the intermediate element 92 and also the component 90 are preferably made of non-magnetic steel.
  • the intermediate element 92 can be made from a material with high wear resistance.
  • the actuator 60 determines whether the valve member 34 of the inlet valve 24 is in its open position or closed position.
  • the solenoid 64 is deenergized, the magnet armature 68 is pressed by the return spring 82 in the actuating direction according to arrow B in FIG. 2, the valve member 34 being pressed by the magnet armature 68 against the valve spring 50 in the actuating direction B into its open position.
  • the force of the return spring 82 acting on the armature 68 is greater than the force of the valve spring 50 acting on the valve member 34.
  • the magnet armature 68 acts on the valve member 34 and the magnet armature 68 and the valve member 34 together in the setting direction B. emotional.
  • the delivery rate of the high-pressure pump into the accumulator 30 can be set variably. If a small amount of fuel is required, the inlet valve 34 is kept open by the actuator 60 during a large part of the delivery stroke of the pump piston 12 and if a large amount of fuel delivery is required, the inlet valve 34 is only during a small part or not at all during the delivery stroke of the pump piston 12 kept open.

Description

Die Erfindung betrifft ein elektromagnetisch betätigbares Einlassventil für eine Hochdruckpumpe, insbesondere eines Kraftstoffeinspritzsystems, gemäß dem Oberbegriff des Anspruchs 1. Ferner betrifft die Erfindung eine Hochdruckpumpe mit einem solchen Einlassventil.The invention relates to an electromagnetically actuated inlet valve for a high-pressure pump, in particular a fuel injection system, according to the preamble of claim 1. Furthermore, the invention relates to a high-pressure pump with such an inlet valve.

Stand der TechnikState of the art

Ein elektromagnetisch betätigbares Einlassventil für eine Hochdruckpumpe eines Kraftstoffeinspritzsystems, ist durch die JP 2004 014700 A bekannt. Die Hochdruckpumpe weist wenigstens ein Pumpenelement auf mit einem in einer Hubbewegung angetriebenen Pumpenkolben, der einen Pumpenarbeitsraum begrenzt. Der Pumpenarbeitsraum ist über das Einlassventil mit einem Zulauf für den Kraftstoff verbindbar. Das Einlassventil umfasst ein Ventilglied, das mit einem Ventilsitz zur Steuerung zusammenwirkt und das zwischen einer Öffnungsstellung und einer Schließstellung bewegbar ist. In seiner Schließstellung kommt das Ventilglied am Ventilsitz zur Anlage. Ferner umfasst das Einlassventil einen elektromagnetischen Aktor, durch den das Ventilglied bewegbar ist. Der elektromagnetische Aktor weist einen zumindest mittelbar auf das Ventilglied wirkenden Magnetanker, eine den Magnetanker umgebende Magnetspule und einen Magnetkern auf. Der Magnetanker ist in einem Trägerelement verschiebbar geführt, wobei das Trägerelement und der Magnetkern über ein hülsenförmiges Bauteil miteinander verbunden sind. Bei Bestromung der Magnetspule ist der Magnetanker gegen die Kraft einer Rückstellfeder bewegbar und kommt über ein scheibenförmiges Zwischenelement am Magnetkern zur Anlage. Das Zwischenelement dient auch zur Abdichtung eines Raums, in dem die Magnetspule angeordnet ist. Durch das Zwischenelement wird sogenanntes magnetisches Kleben verhindert, durch das eine Bewegung des Magnetankers weg vom Magnetkern erschwert würde. Die Montage des Zwischenelements ist dabei aufwendig da dieses als separates Bauteil ausgeführt ist und mit dem Magnetkern verschweißt sein kann.An electromagnetically actuated inlet valve for a high-pressure pump of a fuel injection system is by JP 2004 014700 A known. The high-pressure pump has at least one pump element with a pump piston which is driven in a lifting movement and delimits a pump working space. The pump work space can be connected to an inlet for the fuel via the inlet valve. The inlet valve comprises a valve member which interacts with a valve seat for control and which is movable between an open position and a closed position. In its closed position, the valve member comes to rest on the valve seat. Furthermore, the inlet valve comprises an electromagnetic actuator, through which the valve member can be moved. The electromagnetic actuator has a magnet armature which acts at least indirectly on the valve member, a magnet coil surrounding the magnet armature and a magnet core. The magnet armature is guided displaceably in a carrier element, the carrier element and the magnetic core being connected to one another via a sleeve-shaped component. When the solenoid is energized, the magnet armature can be moved against the force of a return spring and comes into contact with the magnet core via a disc-shaped intermediate element. The intermediate element also serves to seal a space in which the magnetic coil is arranged. The intermediate element prevents so-called magnetic sticking, which would make it difficult to move the armature away from the magnetic core. The assembly of the intermediate element is complex because it is designed as a separate component and can be welded to the magnetic core.

Offenbarung der ErfindungDisclosure of the invention Vorteile der ErfindungAdvantages of the invention

Das erfindungsgemäße Einlassventil mit den Merkmalen des Anspruchs 1 hat demgegenüber den Vorteil, dass die Montage des Zwischenelements vereinfacht ist, indem dieses mit dem hülsenförmigen Bauteil verschweißt oder einstückig ausgebildet ist oder über einen an dessen radial äußerem Randbereich angeordnetem Kragen das hülsenförmige Bauteil bildet. Das Zwischenelement muss somit nicht als separates Bauteil montiert werden.The inlet valve according to the invention with the features of claim 1 has the advantage that the assembly of the intermediate element is simplified in that it is welded to the sleeve-shaped component or is formed in one piece or forms the sleeve-shaped component via a collar arranged on its radially outer edge region. The intermediate element therefore does not have to be installed as a separate component.

In den abhängigen Ansprüchen sind vorteilhafte Ausgestaltungen und Weiterbildungen des erfindungsgemäßen Einlassventils angegeben. Durch die Ausbildung gemäß Anspruch 2 ist eine magnetische Trennung erreicht, so dass ein Kleben des Magnetankers am Magnetkern vermieden und die Funktion des Einlassventils verbessert ist.Advantageous refinements and developments of the inlet valve according to the invention are specified in the dependent claims. A magnetic separation is achieved by the configuration according to claim 2, so that sticking of the magnet armature to the magnet core is avoided and the function of the inlet valve is improved.

Zeichnungdrawing

Mehrere Ausführungsbeispiele der Erfindung werden nachfolgend anhand der beigefügten Zeichnung näher beschrieben. Es zeigen Figur 1 einen schematischen Längsschnitt durch eine Hochdruckpumpe, Figur 2 in vergrößerter Darstellung einen in Figur 1 mit II bezeichneten Ausschnitt mit einem Einlassventil der Hochdruckpumpe, Figur 3 einen in Figur 2 mit III bezeichneten Ausschnitt in weiter vergrößerter Darstellung gemäß einem ersten Ausführungsbeispiel und Figur 4 den Ausschnitt III gemäß einem zweiten Ausführungsbeispiel.Several embodiments of the invention are described below with reference to the accompanying drawings. Show it Figure 1 2 shows a schematic longitudinal section through a high pressure pump, Figure 2 in an enlarged view Figure 1 II marked section with an inlet valve of the high pressure pump, Figure 3 one in Figure 2 with III designated section in a further enlarged representation according to a first embodiment and Figure 4 the section III according to a second embodiment.

Beschreibung der AusführungsbeispieleDescription of the embodiments

In Figur 1 ist ausschnittsweise eine Hochdruckpumpe dargestellt, die zur Kraftstoffförderung in einem Kraftstoffeinspritzsystem einer Brennkraftmaschine vorgesehen ist. Die Hochdruckpumpe weist wenigstens ein Pumpenelement 10 auf, das wiederum einen Pumpenkolben 12 aufweist, der durch einen Antrieb in einer Hubbewegung angetrieben wird, in einer Zylinderbohrung 14 eines Gehäuseteils 16 der Hochdruckpumpe geführt ist und in der Zylinderbohrung 14 einen Pumpenarbeitsraum 18 begrenzt. Als Antrieb für den Pumpenkolben 12 kann eine Antriebswelle 20 mit einem Nocken 22 oder Exzenter vorgesehen sein, an dem sich der Pumpenkolben 12 direkt oder über einen Stößel, beispielsweise einen Rollenstößel, abstützt. Der Pumpenarbeitsraum 18 ist über ein Einlassventil 24 mit einem Kraftstoffzulauf 26 verbindbar und über ein Auslassventil 28 mit einem Speicher 30. Beim Saughub des Pumpenkolbens 12 kann der Pumpenarbeitsraum 18 bei geöffnetem Einlassventil 24 mit Kraftstoff befüllt werden. Beim Förderhub des Pumpenkolbens 12 wird durch diesen Kraftstoff aus dem Pumpenarbeitsraum 18 verdrängt und in den Speicher 30 gefördert.In Figure 1 a high-pressure pump is shown in sections, which is provided for fuel delivery in a fuel injection system of an internal combustion engine. The high pressure pump has at least one pump element 10, which in turn has a pump piston 12, which is driven by a drive in a lifting movement, is guided in a cylinder bore 14 of a housing part 16 of the high-pressure pump and delimits a pump working chamber 18 in the cylinder bore 14. A drive shaft 20 with a cam 22 or eccentric can be provided as the drive for the pump piston 12, on which the pump piston 12 is supported directly or via a tappet, for example a roller tappet. The pump work chamber 18 can be connected to a fuel inlet 26 via an inlet valve 24 and to a reservoir 30 via an outlet valve 28. During the suction stroke of the pump piston 12, the pump work chamber 18 can be filled with fuel with the inlet valve 24 open. During the delivery stroke of the pump piston 12, fuel is displaced from the pump work chamber 18 by this and delivered into the accumulator 30.

Im Gehäuseteil 16 der Hochdruckpumpe schließt sich wie in Figur 2 dargestellt an die Zylinderbohrung 14 auf deren dem Pumpenkolben 12 abgewandter Seite eine Durchgangsbohrung 32 mit kleinerem Durchmesser als die Zylinderbohrung 14 an, die auf der Außenseite der Gehäuseteils 16 mündet. Das Einlassventil 24 weist ein kolbenförmiges Ventilglied 34 auf, das einen in der Durchgangsbohrung 32 verschiebbar geführten Schaft 36 und einen im Durchmesser gegenüber dem Schaft 36 größeren Kopf 38 aufweist, der im Pumpenarbeitsraum 18 angeordnet ist. Am Übergang von der Zylinderbohrung 14 zur Durchgangsbohrung 32 ist am Gehäuseteil 16 ein Ventilsitz 40 gebildet, mit dem das Ventilglied 34 mit einer an seinem Kopf 38 ausgebildeten Dichtfläche 42 zusammenwirkt.In the housing part 16 of the high pressure pump closes as in Figure 2 shown on the cylinder bore 14 on the side facing away from the pump piston 12, a through bore 32 with a smaller diameter than the cylinder bore 14, which opens on the outside of the housing part 16. The inlet valve 24 has a piston-shaped valve member 34 which has a shaft 36 which is displaceably guided in the through bore 32 and a head 38 which is larger in diameter than the shaft 36 and which is arranged in the pump work chamber 18. At the transition from the cylinder bore 14 to the through bore 32, a valve seat 40 is formed on the housing part 16, with which the valve member 34 cooperates with a sealing surface 42 formed on its head 38.

In einem an den Ventilsitz 40 anschließenden Abschnitt weist die Durchgangsbohrung 32 einen größeren Durchmesser auf als in deren den Schaft 36 des Ventilglieds 34 führendem Abschnitt, so dass ein den Schaft 36 des Ventilglieds 34 umgebender Ringraum 44 gebildet ist. In den Ringraum 44 münden eine oder mehrere Zulaufbohrungen 46, die andererseits auf der Außenseite des Gehäuseteils 16 münden.In a section adjoining the valve seat 40, the through bore 32 has a larger diameter than in its section guiding the stem 36 of the valve member 34, so that an annular space 44 is formed surrounding the stem 36 of the valve member 34. One or more inlet bores 46, which on the other hand open on the outside of the housing part 16, open into the annular space 44.

Der Schaft 36 des Ventilglieds 34 ragt auf der dem Pumpenarbeitsraum 18 abgewandten Seite des Gehäuseteils 16 aus der Durchgangsbohrung 32 heraus und auf diesem ist ein Stützelement 48 befestigt. Am Stützelement 48 stützt sich eine Ventilfeder 50 ab, die sich andererseits an einem den Schaft 36 des Ventilglieds 34 umgebenden Bereich des Gehäuseteils 16 abstützt. Durch die Ventilfeder 50 wird das Ventilglied 34 in einer Stellrichtung A in dessen Schließrichtung beaufschlagt, wobei das Ventilglied 34 in seiner Schließstellung mit seiner Dichtfläche 42 am Ventilsitz 40 anliegt. Die Ventilfeder 50 ist beispielsweise als Schraubendruckfeder ausgebildet.The stem 36 of the valve member 34 protrudes from the through bore 32 on the side of the housing part 16 facing away from the pump working space 18 and a support element 48 is fastened thereon. A valve spring 50 is supported on the support element 48, which on the other hand is supported on a region of the housing part 16 surrounding the stem 36 of the valve member 34. Through the valve spring 50, the valve member 34 is acted upon in an adjusting direction A in its closing direction, the valve member 34 with its sealing surface 42 abutting the valve seat 40 in its closed position. The valve spring 50 is designed, for example, as a helical compression spring.

Das Einlassventil 24 ist durch einen elektromagnetischen Aktor 60 betätigbar, der insbesondere in Figur 2 dargestellt ist. Der Aktor 60 wird durch eine elektronische Steuereinrichtung 62 in Abhängigkeit von Betriebsparametern der zu versorgenden Brennkraftmaschine angesteuert. Der elektromagnetische Aktor 60 weist eine Magnetspule 64, einen Magnetkern 66 und einen Magnetanker 68 auf. Der elektromagnetische Aktor 60 ist auf der dem Pumpenarbeitsraum 18 abgewandten Seite des Einlassventils 24 angeordnet. Der Magnetkern 66 und die Magnetspule 64 sind in einem Gehäuse 70 angeordnet, das mehrteilig ausgebildet sein kann und das am Gehäuseteil 16 der Hochdruckpumpe befestigbar ist. Das Gehäuse 70 ist beispielsweise mittels eines dieses übergreifenden Befestigungselements in Form eines Schraubrings 72 am Gehäuseteil 16 befestigbar, der auf einem mit einem Außengewinde versehenen zylindrischen Abschnitt 74 des Gehäuseteils 16 aufgeschraubt ist.The inlet valve 24 can be actuated by an electromagnetic actuator 60, which is particularly shown in FIG Figure 2 is shown. The actuator 60 is controlled by an electronic control device 62 depending on the operating parameters of the internal combustion engine to be supplied. The electromagnetic actuator 60 has a magnet coil 64, a magnet core 66 and a magnet armature 68. The electromagnetic actuator 60 is arranged on the side of the inlet valve 24 facing away from the pump working space 18. The magnetic core 66 and the magnetic coil 64 are arranged in a housing 70 which can be constructed in several parts and which can be fastened to the housing part 16 of the high-pressure pump. The housing 70 can, for example, be fastened to the housing part 16 by means of a fastening element which overlaps this and which is screwed onto a cylindrical section 74 of the housing part 16 provided with an external thread.

Der Magnetanker 68 ist zumindest im wesentlichen zylinderförmig ausgebildet und über seinen Außenmantel in einer Bohrung 76 in einem im Gehäuse 70 angeordneten Trägerelement 78 verschiebbar geführt. Die Bohrung 76 im Trägerelement 78 verläuft zumindest annähernd koaxial zur Durchgangsbohrung 32 im Gehäuseteil 16 und somit zum Ventilglied 34. Das Trägerelement 78 weist in seinem dem Gehäuseteil 16 abgewandten Endbereich 77 eine zylindrische Außenform auf. Der Magnetkern 66 ist im Gehäuse 70 auf der dem Gehäuseteil 16 abgewandten Seite des Trägerelements 78 angeordnet und weist eine zylindrische Außenform auf.The magnet armature 68 is at least essentially cylindrical and is displaceably guided via its outer jacket in a bore 76 in a carrier element 78 arranged in the housing 70. The bore 76 in the carrier element 78 extends at least approximately coaxially to the through bore 32 in the housing part 16 and thus to the valve member 34. The carrier element 78 has a cylindrical outer shape in its end region 77 facing away from the housing part 16. The magnetic core 66 is arranged in the housing 70 on the side of the carrier element 78 facing away from the housing part 16 and has a cylindrical outer shape.

Der Magnetanker 68 weist eine zumindest annähernd koaxial zur Längsachse 69 des Magnetankers 68 angeordnete zentrale Bohrung 80 auf, in die eine auf der dem Ventilglied 34 abgewandten Seite des Magnetankers 68 angeordnete Rückstellfeder 82 hineinragt, die sich am Magnetanker 68 abstützt. Die Rückstellfeder 82 ist an ihrem anderen Ende zumindest mittelbar am Magnetkern 66 abgestützt, der eine zentrale Bohrung 84 aufweist, in die die Rückstellfeder 82 hineinragt. In der Bohrung 84 des Magnetankers 66 kann ein Abstützelement 85 für die Rückstellfeder 82 eingefügt, beispielsweise eingepresst sein. In die zentrale Bohrung 80 des Magnetankers 68 ist ein Zwischenelement 86 eingesetzt, das als Ankerbolzen ausgebildet sein kann. Der Ankerbolzen 86 ist vorzugsweise in die Bohrung 80 des Magnetankers 68 eingepresst. Die Rückstellfeder 80 kann sich in der Bohrung 80 auch am Ankerbolzen 86 abstützen. Der Magnetanker 68 kann eine oder mehrere Durchgangsöffnungen 67 aufweisen.The magnet armature 68 has a central bore 80, which is arranged at least approximately coaxially to the longitudinal axis 69 of the magnet armature 68 and into which a return spring 82, which is arranged on the side of the magnet armature 68 facing away from the valve member 34, projects and is supported on the magnet armature 68. The return spring 82 is supported at its other end at least indirectly on the magnetic core 66, which has a central bore 84 into which the return spring 82 projects. A support element 85 for the return spring can be located in the bore 84 of the magnet armature 66 82 inserted, for example pressed. An intermediate element 86, which can be designed as an anchor bolt, is inserted into the central bore 80 of the magnet armature 68. The anchor bolt 86 is preferably pressed into the bore 80 of the magnet armature 68. The return spring 80 can also be supported in the bore 80 on the anchor bolt 86. The magnet armature 68 can have one or more through openings 67.

In der Bohrung 76 ist durch eine Durchmesserverringerung zwischen dem Magnetanker 68 und dem Einlassventil 24 eine Ringschulter 88 gebildet, durch die die Bewegung des Magnetankers 68 zum Einlassventil 24 hin begrenzt ist. Wenn das Gehäuse 70 noch nicht am Gehäuseteil 16 der Hochdruckpumpe befestigt ist, so ist der Magnetanker 68 durch die Ringschulter 88 gegen Herausfallen aus der Bohrung 76 gesichert. Zwischen der Ringschulter 88 und dem Magnetanker 68 kann eine Scheibe 89 angeordnet sein.An annular shoulder 88 is formed in the bore 76 by a reduction in diameter between the magnet armature 68 and the inlet valve 24, by means of which the movement of the magnet armature 68 towards the inlet valve 24 is limited. If the housing 70 is not yet attached to the housing part 16 of the high-pressure pump, the magnet armature 68 is secured against falling out of the bore 76 by the annular shoulder 88. A disk 89 can be arranged between the annular shoulder 88 and the magnet armature 68.

Das Trägerelement 78 und der Magnetkern 66 sind mittels eines hülsenförmigen Bauteils 90 miteinander verbunden. Das Bauteil 90 ist dabei mit seinem einen axialen Endbereich auf dem zylindrischen Abschnitt 77 des Trägerelements 78 angeordnet und mit diesem verbunden und mit seinem anderen axialen Endbereich auf dem zylindrischen Magnetkern 66 angeordnet und mit diesem verbunden. Das hülsenförmige Bauteil 90 ist beispielsweise mit dem Trägerelement 78 und dem Magnetkern 66 stoffschlüssig verbunden, insbesondere verschweißt. Die Schweißverbindungen sind in Figur 3 durch mit A bezeichnete Dreiecke markiert. Bei Bestromung der Magnetspule 64 wird der Magnetanker 68 gegen die Kraft der Rückstellfeder 82 zum Magnetkern 66 hin gezogen und kommt über ein scheibenförmiges Zwischenelement 92 am Magnetkern 66 zur Anlage, das nachfolgend anhand der Figuren 3 und 4 näher erläutert wird.The carrier element 78 and the magnetic core 66 are connected to one another by means of a sleeve-shaped component 90. The component 90 is arranged with its one axial end region on the cylindrical section 77 of the carrier element 78 and connected to it, and with its other axial end region is arranged on the cylindrical magnetic core 66 and connected to it. The sleeve-shaped component 90 is integrally connected, in particular welded, to the carrier element 78 and the magnetic core 66, for example. The welded connections are in Figure 3 marked by triangles marked A. When the magnet coil 64 is energized, the magnet armature 68 is pulled towards the magnet core 66 against the force of the return spring 82 and comes into contact with the magnet core 66 via a disk-shaped intermediate element 92, which is subsequently described with reference to FIG Figures 3 and 4th is explained in more detail.

Bei einem in Figur 3 dargestellten ersten Ausführungsbeispiel ist das scheibenförmige Zwischenelement 92 innerhalb des hülsenförmigen Bauteils 90 angeordnet. Das Zwischenelement 92 weist eine zentrale Öffnung 93 auf, durch die die Rückstellfeder 82 hindurchtritt. Das Bauteil 90 und das Zwischenelement 92 können aus Stahl hergestellt sein und das Zwischenelement 92 ist einstückig mit dem Bauteil 90 ausgebildet oder ist an seinem radial äußeren Randbereich mit dem Bauteil 90 verschweißt. Vorzugsweise sind das Zwischenelement 92 und auch das Bauteil 90 aus nichtmagnetischem Stahl hergestellt. Das Zwischenelement 92 kann aus einem Werkstoff mit hoher Verschleißfestigkeit hergestellt sein. Bei der Montage des hülsenförmigen Bauteils 90, das mit dem in diesem angeordneten scheibenförmigen Zwischenelement 92 eine Baueinheit bildet, wird das Zwischenelement 92 so positioniert, dass dieses sich in Anlage an der dem Magnetanker 68 zugewandten Stirnseite des Magnetkerns 66 befindet. In dieser Anordnung wird das hülsenförmige Bauteil 90 mit dem Magnetkern 66 und dem Trägerelement 78 verschweißt. Bei Bestromung der Magnetspule 64 wird der Magnetanker 68 zum Magnetkern 66 hin bewegt und kommt über das Zwischenelement 92 am Magnetkern 66 zur Anlage. Der Anschlag des Magnetankers 68 erfolgt am Zwischenelement 92, das mit dem hülsenförmigen Bauteil 90 verbunden ist, wodurch die Belastung des Magnetkerns 66 gering gehalten wird. In Figur 3 ist der Magnetanker 68 in seiner Position bei bestromter Magnetspule 64 dargestellt und dieser befindet sich in Anlage am Zwischenelement 92.At one in Figure 3 First exemplary embodiment shown, the disc-shaped intermediate element 92 is arranged within the sleeve-shaped component 90. The intermediate element 92 has a central opening 93 through which the return spring 82 passes. The component 90 and the intermediate element 92 can be made of steel and the intermediate element 92 is formed in one piece with the component 90 or is welded to the component 90 at its radially outer edge region. The intermediate element 92 and also the component 90 are preferably made of non-magnetic steel. The intermediate element 92 can be made from a material with high wear resistance. When the sleeve-shaped component 90, which forms a structural unit with the disk-shaped intermediate element 92 arranged therein, the intermediate element 92 is positioned such that it is in contact with the end face of the magnetic core 66 facing the magnet armature 68. In this arrangement, the sleeve-shaped component 90 is welded to the magnetic core 66 and the carrier element 78. When the magnet coil 64 is energized, the magnet armature 68 is moved towards the magnet core 66 and comes into contact with the magnet core 66 via the intermediate element 92. The magnet armature 68 stops on the intermediate element 92, which is connected to the sleeve-shaped component 90, as a result of which the load on the magnetic core 66 is kept low. In FIG. 3, the magnet armature 68 is shown in its position when the magnet coil 64 is energized and it is in contact with the intermediate element 92.

In Figur 4 ist ein zweites Ausführungsbeispiel dargestellt, bei dem wiederum das scheibenförmige Zwischenelement 92 vorgesehen ist, das zwischen Magnetanker 68 und Magnetkern 66 angeordnet ist. Das Zwischenelement 92 weist beim zweiten Ausführungsbeispiel an seinem radial äußeren Randbereich einen sich in Richtung der Längsachse 69 des Magnetankers 68 erstreckenden Kragen 94 auf, der zwischen dem Trägerelement 78 und dem Magnetkern 66 angeordnet ist. Der Kragen 94 bildet dabei ein hülsenförmiges Bauteil, über das das Trägerelement 78 und der Magnetkern 66 miteinander verbunden sind. Das Zwischenelement 92 mit dem Kragen 94 ist einstückig ausgebildet oder der Kragen 94 ist mit dem Zwischenelement 92 verschweißt. Der Kragen 94 erstreckt sich zwischen den einander zugewandten Stirnseiten des Trägerelements 78 und des Magnetkerns 66 und ist mit diesen jeweils verbunden, vorzugsweise verschweißt. Die Schweißverbindungen des Kragens 94 sind in Figur 4 durch mit A bezeichnete Dreiecke markiert. Vorzugsweise ist der Kragen 94 dicht mit dem Trägerelement 78 und dem Magnetkern 66 verbunden, so dass der innenliegende Raum, in dem der Magnetanker 68 angeordnet ist, gegenüber dem den Kragen 94 umgebenden außenliegenden Raum abgedichtet ist. In Figur 4 ist der Magnetanker 68 in seiner Position bei bestromter Magnetspule 64 dargestellt und dieser befindet sich in Anlage am Zwischenelement 92.In Figure 4 A second exemplary embodiment is shown, in which the disk-shaped intermediate element 92 is again provided, which is arranged between the magnet armature 68 and the magnet core 66. In the second exemplary embodiment, the intermediate element 92 has on its radially outer edge region a collar 94 which extends in the direction of the longitudinal axis 69 of the magnet armature 68 and which is arranged between the carrier element 78 and the magnetic core 66. The collar 94 forms a sleeve-shaped component, via which the carrier element 78 and the magnetic core 66 are connected to one another. The intermediate element 92 with the collar 94 is formed in one piece or the collar 94 is welded to the intermediate element 92. The collar 94 extends between the mutually facing end faces of the carrier element 78 and the magnetic core 66 and is in each case connected to them, preferably welded. The collar 94 welds are shown in FIG Figure 4 marked by triangles marked A. The collar 94 is preferably tightly connected to the carrier element 78 and the magnetic core 66, so that the interior space in which the magnet armature 68 is arranged is sealed off from the exterior space surrounding the collar 94. In Figure 4 the magnet armature 68 is shown in its position when the magnet coil 64 is energized and this is in contact with the intermediate element 92.

Die Ausbildung des Zwischenelements 92 mit dem Kragen 94 gemäß dem zweiten Ausführungsbeispiel kann auch bei Verwendung eines separaten hülsenförmigen Bauteils 90 wie beim ersten Ausführungsbeispiel vorgesehen sein, wobei dann das Zwischenelement 92 über dessen Kragen 94 mit dem Bauteil 90 verbunden ist, beispielsweise verschweißt ist.The formation of the intermediate element 92 with the collar 94 according to the second embodiment can also be used when using a separate sleeve-shaped Component 90 can be provided as in the first embodiment, in which case the intermediate element 92 is connected to the component 90 via its collar 94, for example is welded.

Nachfolgend wird die Funktion des elektromagnetisch betätigten Einlassventils 24 erläutert. Während des Saughubs des Pumpenkolbens 12 ist das Einlassventil 24 geöffnet, indem sich dessen Ventilglied 34 in seiner Öffnungsstellung befindet, in der dieses mit seiner Dichtfläche 42 vom Ventilsitz 40 entfernt angeordnet ist. Die Bewegung des Ventilglieds 34 in seine Öffnungsstellung wird durch die zwischen dem Kraftstoffzulauf 26 und dem Pumpenarbeitsraum 18 herrschende Druckdifferenz gegen die Kraft der Ventilfeder 50 bewirkt. Die Magnetspule 64 des Aktors 60 kann dabei bestromt oder unbestromt sein. Wenn die Magnetspule 64 bestromt ist so wird der Magnetanker 68 durch das entstehende Magnetfeld gegen die Kraft der Rückstellfeder 80 zum Magnetkern 66 hin gezogen. Wenn die Magnetspule 64 nicht bestromt ist so wird der Magnetanker 68 durch die Kraft der Rückstellfeder 82 zum Einlassventil 24 hin gedrückt. Der Magnetanker 68 liegt über den Ankerbolzen 86 an der Stirnseite des Schafts 36 des Ventilglieds 34 an.The function of the electromagnetically actuated inlet valve 24 is explained below. During the suction stroke of the pump piston 12, the inlet valve 24 is opened in that the valve member 34 is in its open position, in which it is arranged with its sealing surface 42 away from the valve seat 40. The movement of the valve member 34 into its open position is brought about by the pressure difference between the fuel inlet 26 and the pump working chamber 18 against the force of the valve spring 50. The solenoid 64 of the actuator 60 can be energized or de-energized. When the magnet coil 64 is energized, the magnet armature 68 is pulled towards the magnet core 66 against the force of the return spring 80 by the resulting magnetic field. If the magnet coil 64 is not energized, the magnet armature 68 is pressed toward the inlet valve 24 by the force of the return spring 82. The magnet armature 68 bears against the end face of the shaft 36 of the valve member 34 via the armature bolt 86.

Während des Förderhubs des Pumpenkolbens 12 wird durch den Aktor 60 bestimmt ob sich das Ventilglied 34 des Einlassventils 24 in seiner Öffnungsstellung oder Schließstellung befindet. Bei unbestromter Magnetspule 64 wird der Magnetanker 68 durch die Rückstellfeder 82 in der Stellrichtung gemäß Pfeil B in Figur 2 gedrückt, wobei das Ventilglied 34 durch den Magnetanker 68 gegen die Ventilfeder 50 in der Stellrichtung B in seine Öffnungsstellung gedrückt wird. Die Kraft der auf den Magnetanker 68 wirkenden Rückstellfeder 82 ist größer als die Kraft der auf das Ventilglied 34 wirkenden Ventilfeder 50. In die Stellrichtung B wirkt der Magnetanker 68 auf das Ventilglied 34 und der Magnetanker 68 und das Ventilglied 34 werden gemeinsam in die Stellrichtung B bewegt. Solange die Magnetspule 64 nicht bestromt ist kann somit durch den Pumpenkolben 12 kein Kraftstoff in den Speicher 30 gefördert werden sondern vom Pumpenkolben 12 verdrängter Kraftstoff wird in den Kraftstoffzulauf 26 zurückgefördert. Wenn während des Förderhubs des Pumpenkolbens 12 Kraftstoff in den Speicher 30 gefördert werden soll so wird die Magnetspule 64 bestromt, so dass der Magnetanker 68 zum Magnetkern 66 hin in einer zur Stellrichtung B entgegengesetzten Stellrichtung gemäß Pfeil A in Figur 2 gezogen wird. Durch den Magnetanker 68 wird somit keine Kraft mehr auf das Ventilglied 34 ausgeübt, wobei der Magnetanker 68 durch das Magnetfeld in die Stellrichtung A bewegt wird und das Ventilglied 34 unabhängig vom Magnetanker 68 bedingt durch die Ventilfeder 50 und die zwischen dem Pumpenarbeitsraum 18 und dem Kraftstoffzulauf 26 herrschende Druckdifferenz in der Stellrichtung A in seine Schließstellung bewegt wird.During the delivery stroke of the pump piston 12, the actuator 60 determines whether the valve member 34 of the inlet valve 24 is in its open position or closed position. When the solenoid 64 is deenergized, the magnet armature 68 is pressed by the return spring 82 in the actuating direction according to arrow B in FIG. 2, the valve member 34 being pressed by the magnet armature 68 against the valve spring 50 in the actuating direction B into its open position. The force of the return spring 82 acting on the armature 68 is greater than the force of the valve spring 50 acting on the valve member 34. In the setting direction B, the magnet armature 68 acts on the valve member 34 and the magnet armature 68 and the valve member 34 together in the setting direction B. emotional. As long as the solenoid coil 64 is not energized, no fuel can be conveyed into the accumulator 30 by the pump piston 12, but fuel displaced by the pump piston 12 is conveyed back into the fuel inlet 26. If fuel is to be conveyed into the accumulator 30 during the delivery stroke of the pump piston 12, the magnet coil 64 is energized, so that the magnet armature 68 toward the magnet core 66 in an actuation direction opposite the actuation direction B according to arrow A in Figure 2 is pulled. Through the magnet armature 68 thus no more force is exerted on the valve member 34, the magnetic armature 68 being moved in the actuating direction A by the magnetic field and the valve member 34 being independent of the magnetic armature 68 due to the valve spring 50 and the pressure difference between the pump working chamber 18 and the fuel inlet 26 Actuating direction A is moved to its closed position.

Durch das Öffnen des Einlassventils 34 beim Förderhub des Pumpenkolbens 12 mittels des elektromagnetischen Aktors 60 kann die Fördermenge der Hochdruckpumpe in den Speicher 30 variabel eingestellt werden. Wenn eine geringe Kraftstofffördermenge erforderlich ist so wird das Einlassventil 34 durch den Aktor 60 während eines großen Teils des Förderhubs des Pumpenkolbens 12 offen gehalten und wenn eine große Kraftstofffördermenge erforderlich ist, so wird das Einlassventil 34 nur während eines kleinen Teils oder gar nicht während des Förderhubs des Pumpenkolbens 12 offen gehalten.By opening the inlet valve 34 during the delivery stroke of the pump piston 12 by means of the electromagnetic actuator 60, the delivery rate of the high-pressure pump into the accumulator 30 can be set variably. If a small amount of fuel is required, the inlet valve 34 is kept open by the actuator 60 during a large part of the delivery stroke of the pump piston 12 and if a large amount of fuel delivery is required, the inlet valve 34 is only during a small part or not at all during the delivery stroke of the pump piston 12 kept open.

Claims (4)

  1. Electromagnetically actuable inlet valve (24) for a high-pressure pump, in particular of a fuel injection system, having a valve member (34) which is able to be moved between an open position and a closed position, and having an electromagnetic actuator (60) by way of which the valve member (34) is able to be moved, wherein the electromagnetic actuator (60) has a magnet armature (68) which acts at least indirectly on the valve member (34), has a magnet coil (64) which surrounds the magnet armature (68), and has a magnet core (66) against which the magnet armature (68) comes to bear at least indirectly when the magnet coil (64) is electrically energized, wherein the magnet armature (68) is guided in a displaceable manner in a carrier element (78), wherein the carrier element (78) and the magnet core (66) are connected to one another via a sleeve-shaped component (90; 94), wherein a disc-shaped intermediate element (92) is arranged between the magnet armature (68) and that end of the magnet core (66) facing said magnet armature and is connected to the sleeve-shaped component (90; 94),
    characterized in that the intermediate element (92) is welded to the inner shell of the sleeve-shaped component (90; 94) or is formed in one piece with the sleeve-shaped component (90; 94), or in that the intermediate element (92) has on its radially outer boundary region a collar (94) which extends in the direction of the longitudinal axis (69) of the magnet armature (68) and which forms the sleeve-shaped component.
  2. Inlet valve according to Claim 1,
    characterized in that the intermediate element (92) consists of non-magnetic material, with the result that said intermediate element effects a magnetic separation between the magnet armature (68) and the magnet core (66) .
  3. Inlet valve according to Claim 1 or 2,
    characterized in that the intermediate element (92) and the collar (94) are formed in one piece.
  4. High-pressure pump, in particular high-pressure fuel pump, having at least one pump element (10) which has a pump piston (12) which delimits a pump working chamber (18), wherein the pump working chamber (18) is able to be connected to an inflow (26) via an inlet valve (24),
    characterized in that the inlet valve (24) is formed according to one of the preceding claims.
EP17700485.0A 2016-03-03 2017-01-03 Electromagnetically actuatable inlet valve and high-pressure pump comprising an inlet valve Active EP3423717B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016203516.9A DE102016203516A1 (en) 2016-03-03 2016-03-03 Electromagnetically actuated inlet valve and high-pressure pump with inlet valve
PCT/EP2017/050072 WO2017148600A1 (en) 2016-03-03 2017-01-03 Electromagnetically actuatable inlet valve and high-pressure pump comprising an inlet valve

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EP3423717A1 EP3423717A1 (en) 2019-01-09
EP3423717B1 true EP3423717B1 (en) 2020-07-15

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DE (1) DE102016203516A1 (en)
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Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19639117A1 (en) * 1996-09-24 1998-03-26 Bosch Gmbh Robert Fuel injector
US6655611B2 (en) * 2001-02-12 2003-12-02 Delphi Technologies, Inc. Electromagnetic fuel injector comprising flexible element for positioning armature
JP3874698B2 (en) * 2002-06-05 2007-01-31 株式会社デンソー Solenoid for solenoid valve
DE102009003213A1 (en) * 2009-05-19 2010-11-25 Robert Bosch Gmbh Residual air gap disc
DE102014200339A1 (en) 2014-01-10 2015-07-16 Robert Bosch Gmbh Electromagnetically controllable suction valve
DE102014215589A1 (en) * 2014-02-10 2015-08-13 Robert Bosch Gmbh Residual air gap disk for a magnetic assembly of a solenoid valve and method for producing a residual air gap disk
DE102014214231A1 (en) * 2014-07-22 2016-01-28 Robert Bosch Gmbh Electromagnetic actuator for a suction valve and suction valve

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

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DE102016203516A1 (en) 2017-09-07
EP3423717A1 (en) 2019-01-09
WO2017148600A1 (en) 2017-09-08

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