EP3423717A1 - 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

Info

Publication number
EP3423717A1
EP3423717A1 EP17700485.0A EP17700485A EP3423717A1 EP 3423717 A1 EP3423717 A1 EP 3423717A1 EP 17700485 A EP17700485 A EP 17700485A EP 3423717 A1 EP3423717 A1 EP 3423717A1
Authority
EP
European Patent Office
Prior art keywords
inlet valve
armature
magnetic core
intermediate element
sleeve
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.)
Granted
Application number
EP17700485.0A
Other languages
German (de)
French (fr)
Other versions
EP3423717B1 (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
Original Assignee
Robert Bosch 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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP3423717A1 publication Critical patent/EP3423717A1/en
Application granted granted Critical
Publication of EP3423717B1 publication Critical patent/EP3423717B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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 operable 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 operable inlet valve for a high-pressure pump of a fuel injection system is known from DE 10 2014 200 339 A1.
  • the high-pressure pump has at least one pump element with one in one
  • the pump working space can be connected to an inlet for the fuel via the inlet valve.
  • the inlet valve comprises a valve member which cooperates 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 against the valve seat.
  • the inlet valve comprises an electromagnetic actuator, through which the valve member is movable.
  • the electromagnetic actuator has a magnet armature acting at least indirectly on the valve member, a magnet coil surrounding the magnet armature and a magnet core.
  • the magnet armature is displaceably guided in a carrier element, wherein the carrier element and the magnetic core are connected to each other via a sleeve-shaped component.
  • the armature When the solenoid is energized, the armature is movable against the force of a return spring and comes at least indirectly on the magnetic core to the plant. If the magnet armature comes to bear directly on the magnet core, this can lead to so-called magnetic sticking and a movement of the magnet armature away from the magnet core is thereby achieved. sword. This can lead to delays in the movement of the armature and thus to functional impairments of the intake valve. In addition, it can lead to high loads of these two components and the connection between the support member and the magnetic core when hitting the magnet armature on the magnetic core, which over a longer period of operation may cause damage to the connection between the magnetic core and the support element, whereby the operability of the inlet valve impaired can be. If necessary, the magnetic core has to be elaborately machined in order to achieve sufficient wear resistance.
  • the inlet valve according to the invention with the features of claim 1 has the advantage that a direct contact with the magnetic core is avoided by the intermediate element, so that its load is reduced.
  • By connecting the intermediate element with the sleeve-shaped component no additional assembly step is required for this and this is positioned directly during the assembly of the sleeve-shaped component between the armature and the magnetic core.
  • FIG. 1 shows a schematic 2 longitudinal section through a high-pressure pump
  • Figure 2 shows an enlarged view of a designated II in Figure 1 section with an inlet valve of the high-pressure pump
  • Figure 3 a in Figure 2 with III designated section in a further enlarged view according to a first embodiment
  • Figure 4 the section III according to a second embodiment.
  • a high pressure pump is shown in fragmentary form, which is provided for the production of fuel 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 in the cylinder bore 14 a pump working space 18 limited.
  • a drive for the pump piston 12 a
  • Drive shaft 20 may be provided with a cam 22 or eccentric on which the pump piston 12 is supported directly or via a plunger, for example a roller tappet.
  • the pump working chamber 18 can be connected to a fuel inlet 26 via an inlet valve 24 and via an outlet valve 28 to a reservoir 30.
  • the pump working chamber 18 can be filled with fuel when the inlet valve 24 is open.
  • the delivery stroke of the pump piston 12 is displaced by this fuel from the pump working chamber 18 and conveyed into the memory 30.
  • the housing part 16 of the high-pressure pump as shown in FIG.
  • the inlet valve 24 has a piston-shaped valve member 34 which has a shaft 36 slidably guided in the through-bore 32 and a diameter in relation to the
  • Shaft 36 has larger head 38 which is arranged in the pump working chamber 18.
  • a valve seat 40 is formed on the housing part 16, with which the valve member 34 cooperates with a formed on its head 38 sealing surface 42.
  • the through hole 32 has a larger diameter than in the shaft 36 of the valve member 34 leading section, so that the shaft 36 of the valve member 34 surrounding annular space 44 is formed.
  • in the annular space 44 open one or more inlet bores 46, on the other hand open on the outside of the housing part 16.
  • valve member 34 protrudes on the pump working chamber 18 side facing away from the housing part 16 out of the through hole 32 and on this a support member 48 is attached.
  • a valve spring 50 is supported, on the other hand supported on a shaft 36 of the valve member 34 surrounding region of the housing part 16.
  • the inlet valve 24 can be actuated by an electromagnetic actuator 60, which is shown in particular in FIG.
  • the actuator 60 is controlled by an electronic control device 62 as a function of operating parameters of the internal combustion engine to be supplied.
  • the electromagnetic actuator 60 has a magnetic coil 64, a magnetic core 66 and a magnet armature 68.
  • the electromagnetic actuator 60 is arranged on the pump working chamber 18 side facing away from the inlet valve 24.
  • the magnetic core 66 and the magnetic coil 64 are arranged in a housing 70, which can be designed in several parts and which can be fastened to the housing part 16 of the high-pressure pump.
  • the housing 70 can be fastened, for example, to the housing part 16 by means of a fastening element in the form of a screw ring 72, which is screwed onto a cylindrical section 74 of the housing part 16 provided with an external thread.
  • the magnet armature 68 is formed at least substantially cylindrical and slidably guided over 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 points in FIG his the housing part 16 remote from the end portion 77 on a cylindrical outer shape.
  • the magnetic core 66 is arranged in the housing 70 on the side facing away from the housing part 16 of the support member 78 and has a cylindrical outer shape.
  • the armature 68 has an at least approximately coaxial with the longitudinal axis 69 of the magnet armature 68 disposed central bore 80 into which a on the valve member 34 remote from the armature 68 disposed return spring 82 projects, which is supported on the armature 68.
  • the return spring 82 is supported at its other end at least indirectly on the magnetic core 66 having a central bore 84 into which the return spring 82 protrudes.
  • a support member 85 may be inserted for the return spring 82, for example, be pressed.
  • an intermediate element 86 is inserted, which may be formed as an anchor bolt.
  • the anchor bolt 86 is preferably pressed into the bore 80 of the magnet armature 68.
  • the return spring 80 may also be supported in the bore 80 on the anchor bolt 86.
  • the magnet armature 68 may have one or more passage openings 67.
  • an annular shoulder 88 is formed by a reduction in diameter between the armature 68 and the inlet valve 24, by which the movement of the armature 68 is limited to the inlet valve 24 out. If the housing 70 is not yet attached to the housing part 16 of the high pressure pump, the armature 68 is secured by the annular shoulder 88 against falling out of the bore 76. Between the annular shoulder 88 and the magnet armature
  • a disc 89 may be arranged.
  • 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 portion on the cylindrical portion 77 of the support member 78 and connected thereto and arranged with its other axial end portion on the cylindrical magnetic core 66 and connected thereto.
  • the sleeve-shaped component 90 is, for example, materially connected to the carrier element 78 and the magnetic core 66, in particular welded.
  • the welded joints are marked in FIG. 3 by triangles labeled A.
  • the disc-shaped intermediate member 92 is disposed within the sleeve-shaped member 90 and connected to the inner shell or integrally formed therewith.
  • the intermediate member 92 has a central opening 93 through which the return spring 82 passes.
  • the component 90 and the intermediate element 92 may be made of steel and the intermediate element 92 may be integrally formed with the component 90 or is connected at its radially outer edge region with the component 90, for example welded.
  • the intermediate element 92 and also the component 90 are made of non-magnetic steel.
  • the intermediate member 92 may be made of a material having high wear resistance.
  • the intermediate element 92 is positioned such that it bears against the end face of the magnetic core 66 facing the magnet armature 68.
  • the sleeve-shaped member 90 is welded to the magnetic core 66 and the support member 78.
  • the magnet coil 64 When the magnet coil 64 is energized, the magnet armature 68 is moved toward the magnet core 66 and comes to rest on the magnet core 66 via the intermediate element 92.
  • the stop of the magnet armature 68 takes place on the intermediate element 92, which is connected to the sleeve-shaped component 90, whereby the load of the magnetic core 66 is kept low.
  • the armature 68 is shown in its position when energized solenoid 64 and this is in contact with the intermediate element 92nd
  • FIG. 4 shows a second exemplary embodiment, in which again the disc-shaped intermediate element 92 is provided which is arranged between magnet armature 68 and magnetic core 66.
  • the intermediate element 92 has at 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 rule 92 with the collar 94 may be integrally formed or the collar 94 may be connected to the intermediate element 92, for example, be welded.
  • the collar 94 extends between the mutually facing end faces of the support member 78 and the magnetic core 66 and is connected to these in each case, preferably welded.
  • the welded connections of the collar 94 are marked in FIG. 4 by triangles labeled A.
  • the collar 94 is tightly connected to the support member 78 and the magnetic core 66, so that the internal space in which the armature 68 is disposed opposite to the collar 94 surrounding outer space is sealed.
  • the armature 68 is shown in its position when energized solenoid 64 and this is in contact with the intermediate element 92nd
  • the formation of the intermediate element 92 with the collar 94 according to the second embodiment can also be provided when using a separate sleeve-shaped component 90 as in the first embodiment, in which case the intermediate element 92 is connected via the collar 94 to the component 90, for example, welded ,
  • the inlet valve 24 is opened by the valve member 34 is in its open position, in which this is arranged with its sealing surface 42 away from the valve seat 40.
  • the movement of the valve member 34 in its open position is effected by the prevailing between the fuel inlet 26 and the pump working chamber 18 pressure difference against the force of the valve spring 50.
  • the magnetic coil 64 of the actuator 60 may be energized or de-energized. When the solenoid 64 is energized, the armature 68 is pulled by the resulting magnetic field against the force of the return spring 80 to the magnetic core 66 out.
  • the actuator 60 determines whether the valve member 34 of the inlet valve 24 is in its open position or closed position.
  • the armature 68 is pressed by the return spring 82 in the direction of arrow B in Figure 2, wherein the valve member 34 is pressed by the armature 68 against the valve spring 50 in the direction of adjustment B in its open position.
  • the force of the force acting on the armature 68 return spring 82 is greater than the force of the valve member 34 acting on the valve spring 50.
  • the armature 68 acts on the valve member 34 and the armature 68 and the valve member 34 are together in the direction of adjustment B emotional.
  • the solenoid coil 64 is not energized can thus be promoted by the pump piston 12 no fuel in the memory 30 but displaced by the pump piston 12 fuel is fed back into the fuel inlet 26. If during the delivery stroke of the pump piston 12 fuel is to be conveyed into the reservoir 30, the magnetic coil 64 is energized, so that the magnet armature 68 is pulled toward the magnetic core 66 in a direction opposite to the direction of adjustment B as indicated by arrow A in FIG.
  • the armature 68 thus no longer exerts force on the valve member 34, wherein the magnet armature 68 is moved by the magnetic field in the direction A and the valve member 34 independent of the armature 68 due to the valve spring 50 and between the pump working chamber 18 and the fuel inlet 26 prevailing pressure difference in the direction of adjustment A is moved to its closed position.
  • the delivery rate of the high-pressure pump can be set variably in the memory 30.
  • the intake 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 fuel delivery amount is required, the intake valve 34 becomes only for a small part or not at all during the delivery stroke the pump piston 12 is kept open.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

The invention proposes an electromagnetically actuatable inlet valve (24) for a high-pressure pump, in particular of a fuel-injection system. The inlet valve (24) has a valve member (34) which can be moved between an open position and a closed position. Provided is an electromagnetic actuator (60), by means of which the valve member (34) can be moved, wherein the electromagnetic actuator (60) has an armature (68) which acts at least indirectly on the valve member (34), a solenoid coil (64) which surrounds the armature (68), and a magnetic core (66), against which the armature (68) comes to rest, at least indirectly, when current is applied to the solenoid coil (64). The armature (68) is displaceably guided in a carrier element (78) and the carrier element (78) and the magnetic core (66) are connected to one another by means of a sleeve-type component (90). A discoid intermediate element (92), which is connected to the sleeve-type element (90), is located between the armature (68) and the end of the magnetic core (66) facing said armature. The intermediate element (92) allows the stress on the magnetic core (66) upon impact of the armature (68) to be reduced. The intermediate element (92) is produced from a non-magnetic material, such that said element also causes magnetic separation between the armature (68) and the magnetic core (66).

Description

Beschreibung  description
Titel: Title:
Elektromagnetisch betätigbares Einlassventil und Hochdruckpumpe mit Einlassventil  Electromagnetically actuated inlet valve and high-pressure pump with inlet valve
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 operable 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 Technik State of the art
Ein elektromagnetisch betätigbares Einlassventil für eine Hochdruckpumpe eines Kraftstoffeinspritzsystems, ist durch die DE 10 2014 200 339 A1 bekannt. Die Hochdruckpumpe weist wenigstens ein Pumpenelement auf mit einem in einerAn electromagnetically operable inlet valve for a high-pressure pump of a fuel injection system is known from DE 10 2014 200 339 A1. The high-pressure pump has at least one pump element with one in one
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 Öffnungs- Stellung 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 Mag- netkern 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 zumindest mittelbar am Magnetkern zur Anlage. Wenn der Magnetanker direkt am Magnetkern zur Anlage kommt, so kann dies zu sogenanntem magnetischem Kleben führen und eine Bewegung des Magnetankers weg vom Magnetkern wird hierdurch er- schwert. Dies kann zu Verzögerungen bei der Bewegung des Magnetankers und somit zu Funktionsbeeinträchtigungen des Einlassventils führen. Außerdem kann es beim Anschlagen des Magnetankers am Magnetkern zu hohen Belastungen dieser beiden Bauteile sowie der Verbindung zwischen dem Trägerelement und dem Magnetkern kommen, was über eine längere Betriebsdauer zu Beschädigungen der Verbindung zwischen dem Magnetkern und dem Trägerelement führen kann, wodurch die Funktionsfähigkeit des Einlassventils beeinträchtigt werden kann. Der Magnetkern muss dabei gegebenenfalls aufwendig bearbeitet werden um eine ausreichende Verschleißbeständigkeit zu erreichen. Stroke driven pump piston limiting a pump working space. The pump working space can be connected to an inlet for the fuel via the inlet valve. The inlet valve comprises a valve member which cooperates 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 against the valve seat. Furthermore, the inlet valve comprises an electromagnetic actuator, through which the valve member is movable. The electromagnetic actuator has a magnet armature acting at least indirectly on the valve member, a magnet coil surrounding the magnet armature and a magnet core. The magnet armature is displaceably guided in a carrier element, wherein the carrier element and the magnetic core are connected to each other via a sleeve-shaped component. When the solenoid is energized, the armature is movable against the force of a return spring and comes at least indirectly on the magnetic core to the plant. If the magnet armature comes to bear directly on the magnet core, this can lead to so-called magnetic sticking and a movement of the magnet armature away from the magnet core is thereby achieved. sword. This can lead to delays in the movement of the armature and thus to functional impairments of the intake valve. In addition, it can lead to high loads of these two components and the connection between the support member and the magnetic core when hitting the magnet armature on the magnetic core, which over a longer period of operation may cause damage to the connection between the magnetic core and the support element, whereby the operability of the inlet valve impaired can be. If necessary, the magnetic core has to be elaborately machined in order to achieve sufficient wear resistance.
Offenbarung der Erfindung Vorteile der Erfindung Das erfindungsgemäße Einlassventil mit den Merkmalen des Anspruchs 1 hat demgegenüber den Vorteil, dass durch das Zwischenelement eine direkte Anlage am Magnetkern vermieden ist, so dass dessen Belastung verringert ist. Durch die Verbindung des Zwischenelements mit dem hülsenförmigen Bauteil ist für dieses kein zusätzlicher Montageschritt erforderlich und dieses wird direkt bei der Mon- tage des hülsenförmigen Bauteils zwischen dem Magnetanker und dem Magnetkern positioniert. The inlet valve according to the invention with the features of claim 1 has the advantage that a direct contact with the magnetic core is avoided by the intermediate element, so that its load is reduced. By connecting the intermediate element with the sleeve-shaped component, no additional assembly step is required for this and this is positioned directly during the assembly of the sleeve-shaped component between the armature and the magnetic core.
In den abhängigen Ansprüchen sind vorteilhafte Ausgestaltungen und Weiterbildungen des erfindungsgemäßen Einlassventils angegeben. Durch die Ausbil- dung gemäß Anspruch 2 ist eine magnetische Trennung erreicht, so dass einIn the dependent claims advantageous refinements and developments of the inlet valve according to the invention are given. By the embodiment according to claim 2, a magnetic separation is achieved, so that a
Kleben des Magnetankers am Magnetkern vermieden und die Funktion des Einlassventils verbessert ist. Durch die Ausbildung gemäß Anspruch 3 oder 4 ist eine einfache Verbindung des Zwischenelements mit dem hülsenförmigen Bauteil ermöglicht. Die Ausbildung gemäß Anspruch 6 hat den Vorteil, dass der Aufwand zur Erzeugung des hülsenförmigen Bauteils vereinfacht ist, da dieses nicht als separates Bauteil ausgeführt ist. Sticking of the armature on the magnetic core avoided and the function of the inlet valve is improved. Due to the design according to claim 3 or 4, a simple connection of the intermediate element with the sleeve-shaped component is made possible. The embodiment according to claim 6 has the advantage that the effort for producing the sleeve-shaped component is simplified, since this is not designed as a separate component.
Zeichnung Mehrere Ausführungsbeispiele der Erfindung werden nachfolgend anhand der beigefügten Zeichnung näher beschrieben. Es zeigen Figur 1 einen schemati- sehen 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. DRAWING Several exemplary embodiments of the invention will be described in more detail below with reference to the attached drawing. FIG. 1 shows a schematic 2 longitudinal section through a high-pressure pump, Figure 2 shows an enlarged view of a designated II in Figure 1 section with an inlet valve of the high-pressure pump, Figure 3 a in Figure 2 with III designated section in a further enlarged view according to a first embodiment and Figure 4 the section III according to a second embodiment.
Beschreibung der Ausführungsbeispiele Description of the embodiments
In Figur 1 ist ausschnittsweise eine Hochdruckpumpe dargestellt, die zur Kraft- Stoffförderung 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 Pum- penarbeitsraum 18 begrenzt. Als Antrieb für den Pumpenkolben 12 kann eineIn Figure 1, a high pressure pump is shown in fragmentary form, which is provided for the production of fuel 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 in the cylinder bore 14 a pump working space 18 limited. As a drive for the pump piston 12, a
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. 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 demDrive shaft 20 may be provided with a cam 22 or eccentric on which the pump piston 12 is supported directly or via a plunger, for example a roller tappet. The pump working chamber 18 can be connected to a fuel inlet 26 via an inlet valve 24 and via an outlet valve 28 to a reservoir 30. During the suction stroke of the pump piston 12, the pump working chamber 18 can be filled with fuel when the inlet valve 24 is open. During the delivery stroke of the pump piston 12 is displaced by this fuel from the pump working chamber 18 and conveyed into the memory 30. In the housing part 16 of the high-pressure pump, as shown in FIG. 2, a through-bore 32 with a smaller diameter than the cylinder bore 14, which opens on the outside of the housing part 16, adjoins the cylinder bore 14 on its side facing away from the pump piston 12. The inlet valve 24 has a piston-shaped valve member 34 which has a shaft 36 slidably guided in the through-bore 32 and a diameter in relation to the
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 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. Shaft 36 has larger head 38 which is arranged in the pump working chamber 18. At the transition from the cylinder bore 14 to the through hole 32, a valve seat 40 is formed on the housing part 16, with which the valve member 34 cooperates with a formed on its head 38 sealing surface 42. In a subsequent to the valve seat 40 portion, the through hole 32 has a larger diameter than in the shaft 36 of the valve member 34 leading section, so that the shaft 36 of the valve member 34 surrounding annular space 44 is formed. In the annular space 44 open one or more inlet bores 46, on the other hand open on the outside of the housing part 16.
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 Dicht- fläche 42 am Ventilsitz 40 anliegt. Die Ventilfeder 50 ist beispielsweise alsThe shaft 36 of the valve member 34 protrudes on the pump working chamber 18 side facing away from the housing part 16 out of the through hole 32 and on this a support member 48 is attached. On the support member 48, a valve spring 50 is supported, on the other hand supported on a shaft 36 of the valve member 34 surrounding region of the housing part 16. By the valve spring 50, the valve member 34 is acted upon in a direction A in its closing direction, the valve member 34 in its closed position with its sealing surface 42 abuts the valve seat 40. The valve spring 50 is for example as
Schraubendruckfeder ausgebildet. Formed 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 Magnet- spule 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 Ge- häuseteils 16 aufgeschraubt ist. The inlet valve 24 can be actuated by an electromagnetic actuator 60, which is shown in particular in FIG. The actuator 60 is controlled by an electronic control device 62 as a function of operating parameters of the internal combustion engine to be supplied. The electromagnetic actuator 60 has a magnetic coil 64, a magnetic core 66 and a magnet armature 68. The electromagnetic actuator 60 is arranged on the pump working chamber 18 side facing away from the inlet valve 24. The magnetic core 66 and the magnetic coil 64 are arranged in a housing 70, which can be designed in several parts and which can be fastened to the housing part 16 of the high-pressure pump. The housing 70 can be fastened, for example, to the housing part 16 by means of a fastening element in the form of a screw ring 72, 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 Trä- gerelement 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 formed at least substantially cylindrical and slidably guided over 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 points in FIG his the housing part 16 remote from the end portion 77 on a cylindrical outer shape. The magnetic core 66 is arranged in the housing 70 on the side facing away from the housing part 16 of the support member 78 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 Anker- bolzen 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. 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 MagnetankerThe armature 68 has an at least approximately coaxial with the longitudinal axis 69 of the magnet armature 68 disposed central bore 80 into which a on the valve member 34 remote from the armature 68 disposed return spring 82 projects, which is supported on the armature 68. The return spring 82 is supported at its other end at least indirectly on the magnetic core 66 having a central bore 84 into which the return spring 82 protrudes. In the bore 84 of the armature 66, a support member 85 may be inserted for the return spring 82, for example, be pressed. In the central bore 80 of the armature 68, an intermediate element 86 is inserted, which may be formed as an anchor bolt. The anchor bolt 86 is preferably pressed into the bore 80 of the magnet armature 68. The return spring 80 may also be supported in the bore 80 on the anchor bolt 86. The magnet armature 68 may have one or more passage openings 67. In the bore 76, an annular shoulder 88 is formed by a reduction in diameter between the armature 68 and the inlet valve 24, by which the movement of the armature 68 is limited to the inlet valve 24 out. If the housing 70 is not yet attached to the housing part 16 of the high pressure pump, the armature 68 is secured by the annular shoulder 88 against falling out of the bore 76. Between the annular shoulder 88 and the magnet armature
68 kann eine Scheibe 89 angeordnet sein. 68, a disc 89 may be arranged.
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 portion on the cylindrical portion 77 of the support member 78 and connected thereto and arranged with its other axial end portion on the cylindrical magnetic core 66 and connected thereto. The sleeve-shaped component 90 is, for example, materially connected to the carrier element 78 and the magnetic core 66, in particular welded. The welded joints are marked in FIG. 3 by triangles labeled A. When energizing the solenoid 64, the armature 68 is against the Force of the return spring 82 is pulled toward the magnetic core 66 out and comes via a disk-shaped intermediate element 92 on the magnetic core 66 to the system, which will be explained in more detail with reference to Figures 3 and 4.
Bei einem in Figur 3 dargestellten ersten Ausführungsbeispiel ist das scheibenförmige Zwischenelement 92 innerhalb des hülsenförmigen Bauteils 90 angeordnet und mit dessen Innenmantel verbunden oder mit diesem einstückig ausgebildet. 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 kann einstückig mit dem Bauteil 90 ausgebildet sein oder ist an seinem radial äußeren Randbereich mit dem Bauteil 90 verbunden, beispielsweise 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. In a first embodiment shown in Figure 3, the disc-shaped intermediate member 92 is disposed within the sleeve-shaped member 90 and connected to the inner shell or integrally formed therewith. The intermediate member 92 has a central opening 93 through which the return spring 82 passes. The component 90 and the intermediate element 92 may be made of steel and the intermediate element 92 may be integrally formed with the component 90 or is connected at its radially outer edge region with the component 90, for example welded. Preferably, the intermediate element 92 and also the component 90 are made of non-magnetic steel. The intermediate member 92 may be made of a material having high wear resistance. During assembly of the sleeve-shaped component 90, which forms a structural unit with the disc-shaped intermediate element 92 arranged in the latter, the intermediate element 92 is positioned such that it bears against the end face of the magnetic core 66 facing the magnet armature 68. In this arrangement, the sleeve-shaped member 90 is welded to the magnetic core 66 and the support member 78. When the magnet coil 64 is energized, the magnet armature 68 is moved toward the magnet core 66 and comes to rest on the magnet core 66 via the intermediate element 92. The stop of the magnet armature 68 takes place on the intermediate element 92, which is connected to the sleeve-shaped component 90, whereby the load of the magnetic core 66 is kept low. In Figure 3, the armature 68 is shown in its position when energized solenoid 64 and this is in contact with the intermediate element 92nd
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 Zwi- schenelement 92 mit dem Kragen 94 kann einstückig ausgebildet sein oder der Kragen 94 kann mit dem Zwischenelement 92 verbunden sein, beispielsweise verschweißt sein. 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. FIG. 4 shows a second exemplary embodiment, in which again the disc-shaped intermediate element 92 is provided which is arranged between magnet armature 68 and magnetic core 66. In the second exemplary embodiment, the intermediate element 92 has at 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 rule 92 with the collar 94 may be integrally formed or the collar 94 may be connected to the intermediate element 92, for example, be welded. The collar 94 extends between the mutually facing end faces of the support member 78 and the magnetic core 66 and is connected to these in each case, preferably welded. The welded connections of the collar 94 are marked in FIG. 4 by triangles labeled A. Preferably, the collar 94 is tightly connected to the support member 78 and the magnetic core 66, so that the internal space in which the armature 68 is disposed opposite to the collar 94 surrounding outer space is sealed. In Figure 4, the armature 68 is shown in its position when energized solenoid 64 and this is in contact with the intermediate element 92nd
Die Ausbildung des Zwischenelements 92 mit dem Kragen 94 gemäß dem zweiten Ausführungsbeispiel kann auch bei Verwendung eines separaten hülsenför- migen 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 provided when using a separate sleeve-shaped component 90 as in the first embodiment, in which case the intermediate element 92 is connected via the collar 94 to the component 90, for example, 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. 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. Hereinafter, the function of the solenoid-operated intake valve 24 will be explained. During the intake stroke of the pump piston 12, the inlet valve 24 is opened by the valve member 34 is in its open position, in which this is arranged with its sealing surface 42 away from the valve seat 40. The movement of the valve member 34 in its open position is effected by the prevailing between the fuel inlet 26 and the pump working chamber 18 pressure difference against the force of the valve spring 50. The magnetic coil 64 of the actuator 60 may be energized or de-energized. When the solenoid 64 is energized, the armature 68 is pulled by the resulting magnetic field against the force of the return spring 80 to the magnetic core 66 out. When the solenoid 64 is deenergized, the armature 68 is urged toward the inlet valve 24 by the force of the return spring 82. The magnet armature 68 abuts on the end face of the shaft 36 of the valve member 34 via the anchor bolt 86. 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 energized solenoid 64, the armature 68 is pressed by the return spring 82 in the direction of arrow B in Figure 2, wherein the valve member 34 is pressed by the armature 68 against the valve spring 50 in the direction of adjustment B in its open position. The force of the force acting on the armature 68 return spring 82 is greater than the force of the valve member 34 acting on the valve spring 50. In the direction of adjustment B, the armature 68 acts on the valve member 34 and the armature 68 and the valve member 34 are together in the direction of adjustment B emotional. As long as the solenoid coil 64 is not energized can thus be promoted by the pump piston 12 no fuel in the memory 30 but displaced by the pump piston 12 fuel is fed back into the fuel inlet 26. If during the delivery stroke of the pump piston 12 fuel is to be conveyed into the reservoir 30, the magnetic coil 64 is energized, so that the magnet armature 68 is pulled toward the magnetic core 66 in a direction opposite to the direction of adjustment B as indicated by arrow A in FIG. The armature 68 thus no longer exerts force on the valve member 34, wherein the magnet armature 68 is moved by the magnetic field in the direction A and the valve member 34 independent of the armature 68 due to the valve spring 50 and between the pump working chamber 18 and the fuel inlet 26 prevailing pressure difference in the direction of adjustment 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 can be set variably in the memory 30. When a small fuel delivery amount is required, the intake 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 fuel delivery amount is required, the intake valve 34 becomes only for a small part or not at all during the delivery stroke the pump piston 12 is kept open.

Claims

Elektromagnetisch betätigbares Einlassventil (24) für eine Hochdruckpumpe, insbesondere eines Kraftstoffeinspritzsystems, mit einem Ventilglied (34), das zwischen einer Öffnungsstellung und einer Schließstellung bewegbar ist, mit einem elektromagnetischen Aktor (60), durch den das Ventilglied (34) bewegbar ist, wobei der elektromagnetische Aktor (60) einen zumindest mittelbar auf das Ventilglied (34) wirkenden Magnetanker (68), eine den Magnetanker (68) umgebende Magnetspule (64) und einen Magnetkern (66) aufweist, an dem der Magnetanker (68) bei Bestromung der Magnetspule (64) zumindest mittelbar zur Anlage kommt, wobei der Magnetanker (68) in einem Trägerelement (78) verschiebbar geführt ist, wobei das Trägerelement (78) und der Magnetkern (66) über ein hülsenförmiges Bauteil (90; 94) miteinander verbunden sind, Electromagnetically actuated inlet valve (24) for a high-pressure pump, in particular of a fuel injection system, with a valve member (34) that can be moved between an open position and a closed position, with an electromagnetic actuator (60) through which the valve member (34) can be moved, wherein the electromagnetic actuator (60) has a magnet armature (68) which acts at least indirectly on the valve member (34), a magnetic coil (64) surrounding the magnet armature (68) and a magnetic core (66) on which the magnet armature (68) is energized Magnetic coil (64) comes into contact at least indirectly, the magnet armature (68) being slidably guided in a carrier element (78), the carrier element (78) and the magnetic core (66) being connected to one another via a sleeve-shaped component (90; 94). ,
dadurch gekennzeichnet, dass zwischen dem Magnetanker (68) und dem diesem zugewandten Ende des Magnetkerns (66) ein scheibenförmiges Zwischenelement (92) angeordnet ist, das mit dem hülsenförmigen Bauteil (90; 94) verbunden ist. characterized in that a disk-shaped intermediate element (92) is arranged between the magnet armature (68) and the end of the magnetic core (66) facing it, which is connected to the sleeve-shaped component (90; 94).
Einlassventil nach Anspruch 1 , Inlet valve according to claim 1,
dadurch gekennzeichnet, dass das Zwischenelement (92) aus nichtmagnetischem Material besteht, so dass durch dieses eine magnetische Trennung zwischen dem Magnetanker (68) und dem Magnetkern (66) bewirkt wird. characterized in that the intermediate element (92) consists of non-magnetic material, so that this causes a magnetic separation between the magnetic armature (68) and the magnetic core (66).
Einlassventil nach Anspruch 1 oder 2, Inlet valve according to claim 1 or 2,
dadurch gekennzeichnet, dass das Zwischenelement (92) mit dem Innenmantel des hülsenförmigen Bauteils (90; 94) verbunden ist. characterized in that the intermediate element (92) is connected to the inner jacket of the sleeve-shaped component (90; 94).
Einlassventil nach Anspruch 3, Inlet valve according to claim 3,
dadurch gekennzeichnet, dass das Zwischenelement (92) mit dem hülsenförmigen Bauteil (90; 94) verschweißt ist. characterized in that the intermediate element (92) is welded to the sleeve-shaped component (90; 94).
5. Einlassventil nach einem der vorstehenden Ansprüche, 5. Inlet valve according to one of the preceding claims,
dadurch gekennzeichnet, dass das Zwischenelement (92) an seinem radial äußeren Randbereich einen sich in Richtung der Längsachse (69) des Magnetankers (68) erstreckenden Kragen (94) aufweist, der mit dem hülsenför- migen Bauteil (90) verbunden ist. characterized in that 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 connected to the sleeve-shaped component (90).
6. Einlassventil nach einem der Ansprüche 1 bis 4, 6. Inlet valve according to one of claims 1 to 4,
dadurch gekennzeichnet, dass das Zwischenelement (92) an seinem radial äußeren Randbereich einen sich in Richtung der Längsachse (69) des Magnetankers (68) erstreckenden Kragen (94) aufweist, der das hülsenförmige Bauteil bildet. characterized in that 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 forms the sleeve-shaped component.
7. Einlassventil nach Anspruch 5 oder 6, 7. Inlet valve according to claim 5 or 6,
dadurch gekennzeichnet, dass das Zwischenelement (92) und der Kragen (94) einstückig ausgebildet sind. characterized in that the intermediate element (92) and the collar (94) are formed in one piece.
8. Hochdruckpumpe, insbesondere Kraftstoffhochdruckpumpe, mit wenigstens einem Pumpenelement (10), das einen einen Pumpenarbeitsraum (18) begrenzenden Pumpenkolben (12) aufweist, wobei der Pumpenarbeitsraum (18) über ein Einlassventil (24) mit einem Zulauf (26) verbindbar ist, 8. High-pressure pump, in particular high-pressure fuel pump, with at least one pump element (10), which has a pump piston (12) delimiting a pump working space (18), the pump working space (18) being connectable to an inlet (26) via an inlet valve (24),
dadurch gekennzeichnet, dass das Einlassventil (24) gemäß einem der vorstehenden Ansprüche ausgebildet ist. characterized in that the inlet valve (24) is designed 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

Publications (2)

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

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DE (1) DE102016203516A1 (en)
WO (1) WO2017148600A1 (en)

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

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EP3423717B1 (en) 2020-07-15
WO2017148600A1 (en) 2017-09-08

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