WO2017108343A1 - Electromagnetically actuatable inlet valve and high-pressure pump having an inlet valve - Google Patents

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

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Publication number
WO2017108343A1
WO2017108343A1 PCT/EP2016/079034 EP2016079034W WO2017108343A1 WO 2017108343 A1 WO2017108343 A1 WO 2017108343A1 EP 2016079034 W EP2016079034 W EP 2016079034W WO 2017108343 A1 WO2017108343 A1 WO 2017108343A1
Authority
WO
WIPO (PCT)
Prior art keywords
inlet valve
magnetic core
connecting element
armature
pump
Prior art date
Application number
PCT/EP2016/079034
Other languages
German (de)
French (fr)
Inventor
Tobias Landenberger
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 WO2017108343A1 publication Critical patent/WO2017108343A1/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
    • F02M59/368—Pump inlet valves being closed when actuated
    • 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0452—Distribution members, e.g. valves
    • F04B1/0461—Conical
    • 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/053—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of valves
    • 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
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F04B9/04—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms
    • F04B9/042—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms the means being cams
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
    • F16K31/0686—Braking, pressure equilibration, shock absorbing
    • F16K31/0696—Shock absorbing, e.g. using a dash-pot
    • 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
    • F02M2200/26—Fuel-injection apparatus with elastically deformable elements other than coil springs
    • 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
    • F02M2200/30—Fuel-injection apparatus having mechanical parts, the movement of which is damped
    • F02M2200/306—Fuel-injection apparatus having mechanical parts, the movement of which is damped using mechanical 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
    • F02M2200/80—Fuel injection apparatus manufacture, repair or assembly
    • F02M2200/8084—Fuel injection apparatus manufacture, repair or assembly involving welding or soldering

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 2013 220 593 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 one another.
  • 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. Between the armature and the magnetic core, a spacer made of non-magnetic material may be arranged to ensure a residual air gap and to magnetically bond the armature to the magnetic core avoid. When the magnet armature is impacted on the magnet core, high loads of these two components can occur, which over a longer period of operation can lead to damage of the two components, as a result of which the functionality of the inlet valve can be impaired.
  • the inlet valve according to the invention with the features of claim 1 has the advantage that is damped by the elastic deformability of the connec tion elements of the stop of the armature at least indirectly on the magnetic core, so that the load on these two components is reduced and their possible operating time is extended.
  • FIG. 1 shows a schematic longitudinal section through a high-pressure pump
  • Figure 2 shows an enlarged view of a designated II in Figure 1 section with the inlet valve of the high pressure pump
  • Figure 3 is a connecting element of an electromagnetic actuator of the inlet valve in a longitudinal section according to a first embodiment
  • Figure 4 the Connecting element in a longitudinal section according to a second embodiment.
  • FIG. 1 shows a detail of a high-pressure pump 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 limits a pump working chamber 18 in the cylinder bore 14.
  • 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 inlet valve 24 has a piston-shaped valve member 34 which has a shaft 36 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 working space 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.
  • the annular space 44 open one or more inlet holes 46, the other part open on the outside of the housing part 16.
  • the 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.
  • a valve spring 50 is supported, which on the other hand is supported on a region 52 of the housing part 16 surrounding the shaft 36 of the valve member 34.
  • Valve spring 50 the valve member 34 is acted upon in a direction of adjustment A in the closing direction, wherein the valve member 34 rests in its closed position with its sealing surface 42 on the valve seat 40.
  • the valve spring 50 is formed for example as a helical compression spring.
  • 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 an actuator housing 70 which can be fastened to the housing part 16 of the high-pressure pump.
  • the actuator housing 70 can be fastened to the housing part 16, for example, by means of a screw ring 72 which overlaps it and which is screwed onto a collar 74 of the housing part 16 provided with an external thread.
  • the magnet armature 68 is at least substantially cylindrical in shape and is displaceably guided via its outer jacket in a bore 76 in a carrier element 78 arranged in the actuator housing 70.
  • the bore 76 in the support member 78 extends at least approximately coaxially to the through hole 32 in the housing part 16 and thus to the valve member 34.
  • the support member 78 has in its the housing part 16 opposite end portion 79 has a cylindrical outer hform.
  • the magnetic core 66 is arranged in the actuator housing 70 on the side facing away from the housing part 16 of the support member 78 and has a cylindrical outer shape.
  • the magnet armature 68 has an at least approximately coaxial to the longitudinal axis 69 of the magnet armature 68 arranged central bore 80 into which a on the valve member 34 opposite side of the magnet armature 68 arranged return Stellfeder 82 protrudes, 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 element 85 can be inserted for the restoring 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 78 on the anchor bolt 86.
  • the magnet armature 68 may have one or more passage openings 67.
  • 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 actuator 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, 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 connecting element 90.
  • the connecting element 90 is arranged with its one axial end portion 90a on the cylindrical portion 79 of the support member 78 and connected thereto and arranged with its other axial end portion 90b on the cylindrical magnetic core 66 and connected thereto.
  • the connecting element 90 is, for example, materially connected to the carrier element 78 and the magnetic core 66, in particular welded.
  • the connecting element 90 is connected neither to the carrier element 78 nor to the magnetic core 66 and bridges an axial distance between the carrier element 78 and the magnetic core 66.
  • the connecting element 90 in its central region 90c at least in sections in the direction of its longitudinal axis 91 is formed elastically deformable. This elastic deformability of the connecting element 90, the impact of the armature 68 is attenuated at the magnetic core 66, whereby the load on these components is reduced and their durability is improved.
  • the connecting element 90 has in its middle region 90c at least one peripheral bead 92, through which the elastic deformability is achieved. It is also possible for a plurality of beads 92 to follow one another in the axial direction.
  • 92 can be introduced, for example, by a rolling process in the connecting element 90.
  • the connecting element 90 has at least one annular insert 94 in its central region 90c, which consists of a material with higher elasticity than the material from which the remaining connecting element 90 consists.
  • at least one bead 92 may be provided in the middle region 90c of the connecting element 90, as in the first exemplary embodiment.
  • 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 solenoid 64 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 is determined by the actuator 60, whether the valve member 34 of the inlet valve 24 is in its open position or closed position.
  • the solenoid 64 is de-energized, the magnet armature 68 is pressed by the return spring 82 in the direction of adjustment according to arrow B in FIG. 2, wherein the valve member 34 is pressed by the magnet armature 68 against the armature 68
  • Valve spring 50 is pressed 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.
  • Solenoid 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 fuel is to be conveyed into the reservoir 30 during the delivery stroke of the pump piston 12, the magnetic coil 64 is energized, so that the magnet armature
  • 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.

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. An electromagnetic actuator (60) is provided, it being possible for the valve member (34) to be moved by said electromagnetic actuator, wherein the electromagnetic actuator (60) has a magnet armature (68) which acts at least indirectly on the valve member (34), a magnet coil (64) which surrounds the magnet armature (68), and a magnetic core (66), against which the magnet armature (68) comes to rest at least indirectly when current is applied to the magnet coil (64), wherein the magnet armature (68) is displaceably guided in a carrier element (78), and wherein the carrier element (78) and the magnetic core (66) are connected to one another. The carrier element (78) and the magnetic core (66) connected to each other by means of a sleeve-shaped connecting element (90) which is elastically deformable at least in sections in the direction of its longitudinal axis (91).

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 2013 220 593 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 2013 220 593 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 miteinander verbunden sind. Bei Bestromung der Magnetspule ist der Magnetanker gegen die Kraft einer Rückstellfeder bewegbar und kommt zumindest mittelbar am Magnetkern zur Anlage. Zwischen dem Magnetanker und dem Magnetkern kann ein Abstandselement aus nichtmagnetischem Material angeordnet sein, um einen Restluftspalt sicherzustellen und ein magnetisches Kleben des Magnetankers am Magnetkern zu vermeiden. Beim Anschlagen des Magnetankers am Magnetkern kann es zu hohen Belastungen dieser beiden Bauteile kommen, was über eine längere Betriebsdauer zu Beschädigungen der beiden Bauteile führen kann, wodurch die Funktionsfähigkeit des Einlassventils beeinträchtigt werden kann. 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 one another. 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. Between the armature and the magnetic core, a spacer made of non-magnetic material may be arranged to ensure a residual air gap and to magnetically bond the armature to the magnetic core avoid. When the magnet armature is impacted on the magnet core, high loads of these two components can occur, which over a longer period of operation can lead to damage of the two components, as a result of which the functionality of the inlet valve can be impaired.
Offenbarung der Erfindung Disclosure of the invention
Vorteile der Erfindung Advantages of the invention
Das erfindungsgemäße Einlassventil mit den Merkmalen des Anspruchs 1 hat demgegenüber den Vorteil, dass durch die elastische Verformbarkeit des Verbin dungselements der Anschlag des Magnetankers zumindest mittelbar am Magnetkern gedämpft wird, so dass die Belastung dieser beiden Bauteile verringert ist und entsprechend deren mögliche Betriebsdauer verlängert ist. The inlet valve according to the invention with the features of claim 1 has the advantage that is damped by the elastic deformability of the connec tion elements of the stop of the armature at least indirectly on the magnetic core, so that the load on these two components is reduced and their possible operating time is extended.
In den abhängigen Ansprüchen sind vorteilhafte Ausgestaltungen und Weiterbildungen des erfindungsgemäßen Einlassventils angegeben. Durch die Ausbildung des Verbindungselements gemäß Anspruch 2 ist auf einfache Weise die elastische Verformbarkeit des Verbindungselements erreicht. Durch die Ausbildung gemäß Anspruch 3 ist alternativ oder in Kombination mit der Ausbildung gemäß Anspruch 2 auf einfache Weise die elastische Verformbarkeit des Verbin dungselements erreicht. In the dependent claims advantageous refinements and developments of the inlet valve according to the invention are given. Due to the design of the connecting element according to claim 2, the elastic deformability of the connecting element is achieved in a simple manner. Due to the design according to claim 3, the elastic deformability of the connec tion elements is achieved alternatively or in combination with the embodiment according to claim 2 in a simple manner.
Zeichnung drawing
Zwei 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 dem Einlassventil der Hochdruckpumpe, Figur 3 ein Verbindungselement eines elektromagnetischen Aktors des Einlassventils in einem Längsschnitt gemäß einem ersten Ausführungsbeispiel und Figur 4 das Verbindungselement in einem Längsschnitt gemäß einem zweiten Ausführungsbeispiel. Beschreibung der Ausführungsbeispiele Two embodiments of the invention are described below with reference to the accompanying drawings. 1 shows a schematic longitudinal section through a high-pressure pump, Figure 2 shows an enlarged view of a designated II in Figure 1 section with the inlet valve of the high pressure pump, Figure 3 is a connecting element of an electromagnetic actuator of the inlet valve in a longitudinal section according to a first embodiment and Figure 4 the Connecting element in a longitudinal section according to a second embodiment. Description of the embodiments
In Figur 1 ist ausschnittsweise eine Hochdruckpumpe dargestellt, die zur Kraftstoffförderung in einem Kraftstoffeinspritzsystem einer Brennkraftmaschine vor- gesehen 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 Pumpenarbeits- räum 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. FIG. 1 shows a detail of a high-pressure pump 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 limits a pump working chamber 18 in the cylinder bore 14. As 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. 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.
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 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 Gehäuse- teils 16 münden. 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 Ven- tilglieds 34 umgebenden Bereich 52 des Gehäuseteils 16 abstützt. Durch dieIn 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 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 working space 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 holes 46, the other part open on the outside of the housing part 16. The 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 element 48, a valve spring 50 is supported, which on the other hand is supported on a region 52 of the housing part 16 surrounding the shaft 36 of the valve member 34. By the
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. Valve spring 50, the valve member 34 is acted upon in a direction of adjustment A in the closing direction, wherein the valve member 34 rests in its closed position with its sealing surface 42 on the valve seat 40. The valve spring 50 is formed 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 ei- ne 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 Aktorgehäuse 70 angeordnet, das am Gehäuseteil 16 der Hochdruckpumpe befestigbar ist. Das Aktorgehäuse 70 ist beispielsweise mittels eines dieses übergreifenden Schraubrings 72 am Gehäuseteil 16 befestigbar, der auf einem mit einem Außengewinde versehenen Kragen 74 des Gehäuseteils 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 an actuator housing 70 which can be fastened to the housing part 16 of the high-pressure pump. The actuator housing 70 can be fastened to the housing part 16, for example, by means of a screw ring 72 which overlaps it and which is screwed onto a collar 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 Aktorgehäuse 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 79 eine zylindrische Au- ßenform auf. Der Magnetkern 66 ist im Aktorgehäuse 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 substantially cylindrical in shape and is displaceably guided via its outer jacket in a bore 76 in a carrier element 78 arranged in the actuator housing 70. The bore 76 in the support member 78 extends at least approximately coaxially to the through hole 32 in the housing part 16 and thus to the valve member 34. The support member 78 has in its the housing part 16 opposite end portion 79 has a cylindrical outer ßenform. The magnetic core 66 is arranged in the actuator 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 Rück- stellfeder 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 Rück- stellfeder 82 eingefügt, beispielsweise eingepresst sein. In die zentrale BohrungThe magnet armature 68 has an at least approximately coaxial to the longitudinal axis 69 of the magnet armature 68 arranged central bore 80 into which a on the valve member 34 opposite side of the magnet armature 68 arranged return Stellfeder 82 protrudes, 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 magnet armature 66, a support element 85 can be inserted for the restoring spring 82, for example, be pressed. In the central hole
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 78 auch am Ankerbolzen 86 abstützen. Der Magnetanker 68 kann eine oder mehrere Durchgangsöffnungen 67 aufweisen. 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 78 on the anchor bolt 86. The magnet armature 68 may have one or more passage 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 Aktorgehäuse 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. 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 actuator 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, a disc 89 may be arranged.
Das Trägerelement 78 und der Magnetkern 66 sind mittels eines hülsenförmigen Verbindungselements 90 miteinander verbunden. Das Verbindungselement 90 ist dabei mit seinem einen axialen Endbereich 90a auf dem zylindrischen Abschnitt 79 des Trägerelements 78 angeordnet und mit diesem verbunden und mit seinem anderen axialen Endbereich 90b auf dem zylindrischen Magnetkern 66 angeordnet und mit diesem verbunden. Das Verbindungselement 90 ist beispielsweise mit dem Trägerelement 78 und dem Magnetkern 66 stoffschlüssig verbunden, insbesondere verschweißt. In einem zwischen dessen axialen Endbereichen 90a, 90b angeordneten mittleren Bereich 90c ist das Verbindungselement 90 weder mit dem Trägerelement 78 noch mit dem Magnetkern 66 verbunden und überbrückt einen axialen Abstand zwischen Trägerelement 78 und Magnetkern 66. Bei Bestromung der Magnetspule 64 wird der Magnetanker 68 gegen die Kraft der Rückstellfeder 82 zum Magnetkern 66 hin gezogen und kommt zumindest mittelbar am Magnetkern 66 zur Anlage. Erfindungsgemäß ist vorgesehen, dass das Verbindungselement 90 in seinem mittleren Bereich 90c zumindest abschnittsweise in Richtung seiner Längsachse 91 elastisch verformbar ausgebildet ist. Durch diese elastische Verformbarkeit des Verbindungselements 90 wird der Aufprall des Magnetankers 68 am Magnetkern 66 gedämpft, wodurch die Belastung dieser Bauteile verringert und deren Haltbarkeit verbessert wird. The carrier element 78 and the magnetic core 66 are connected to one another by means of a sleeve-shaped connecting element 90. The connecting element 90 is arranged with its one axial end portion 90a on the cylindrical portion 79 of the support member 78 and connected thereto and arranged with its other axial end portion 90b on the cylindrical magnetic core 66 and connected thereto. The connecting element 90 is, for example, materially connected to the carrier element 78 and the magnetic core 66, in particular welded. In a middle region 90c arranged between its axial end regions 90a, 90b, the connecting element 90 is connected neither to the carrier element 78 nor to the magnetic core 66 and bridges an axial distance between the carrier element 78 and the magnetic core 66. When the magnet coil 64 is energized, the magnet armature 68 is counteracted the force of the return spring 82 is pulled towards the magnetic core 66 and comes at least indirectly on the magnetic core 66 to the plant. According to the invention it is provided that the connecting element 90 in its central region 90c at least in sections in the direction of its longitudinal axis 91 is formed elastically deformable. This elastic deformability of the connecting element 90, the impact of the armature 68 is attenuated at the magnetic core 66, whereby the load on these components is reduced and their durability is improved.
Bei einem in Figur 3 dargestellten ersten Ausführungsbeispiel des Verbindungselements 90 ist vorgesehen, dass das Verbindungselement 90 in seinem mittleren Bereich 90c wenigstens eine umlaufende Sicke 92 aufweist, durch die die die elastische Verformbarkeit erreicht wird. Es können auch mehrere in axialer Rich- tung aufeinanderfolgende Sicken 92 vorgesehen sein. Die wenigstens eine SickeIn a first exemplary embodiment of the connecting element 90 shown in FIG. 3, it is provided that the connecting element 90 has in its middle region 90c at least one peripheral bead 92, through which the elastic deformability is achieved. It is also possible for a plurality of beads 92 to follow one another in the axial direction. The at least one bead
92 kann beispielsweise durch ein Rollverfahren in das Verbindungselement 90 eingebracht werden. 92 can be introduced, for example, by a rolling process in the connecting element 90.
Bei einem in Figur 4 dargestellten zweiten Ausführungsbeispiel des Verbin- dungselements 90 ist vorgesehen, dass das Verbindungselement 90 in seinem mittleren Bereich 90c wenigstens einen ringförmigen Einsatz 94 aufweist, der aus einem Werkstoff mit höherer Elastizität besteht als der Werkstoff, aus dem das übrige Verbindungselement 90 besteht. Zusätzlich kann auch wenigstens eine Sicke 92 wie beim ersten Ausführungsbeispiel im mittleren Bereich 90c des Ver- bindungselements 90 vorgesehen sein. In a second exemplary embodiment of the connecting element 90 shown in FIG. 4, it is provided that the connecting element 90 has at least one annular insert 94 in its central region 90c, which consists of a material with higher elasticity than the material from which the remaining connecting element 90 consists. In addition, at least one bead 92 may be provided in the middle region 90c of the connecting element 90, as in the first exemplary embodiment.
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 befin- det, 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 Fi- gur 2 gedrückt, wobei das Ventilglied 34 durch den Magnetanker 68 gegen dieHereinafter, the function of the solenoid-operated intake valve 24 will be explained. During the suction 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 is determined by the actuator 60, whether the valve member 34 of the inlet valve 24 is in its open position or closed position. When the solenoid 64 is de-energized, the magnet armature 68 is pressed by the return spring 82 in the direction of adjustment according to arrow B in FIG. 2, wherein the valve member 34 is pressed by the magnet armature 68 against the armature 68
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 dieValve spring 50 is pressed 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
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 geför- dert werden soll so wird die Magnetspule 64 bestromt, so dass der MagnetankerSolenoid 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 fuel is to be conveyed into the reservoir 30 during the delivery stroke of the pump piston 12, the magnetic coil 64 is energized, so that the magnet armature
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. 68 is pulled toward the magnetic core 66 in a direction opposite to the direction of adjustment B direction of adjustment according to arrow A in Figure 2. 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

Ansprüche claims
1 . 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 und wobei das Trägerelement (78) und der Magnetkern (66) miteinander verbunden sind, dadurch gekennzeichnet, dass das Trägerelement (78) und der Magnetkern (66) über ein hülsenförmiges Verbindungselement (90) miteinander verbunden sind, das zumindest abschnittsweise in Richtung seiner Längsachse (91 ) elastisch verformbar ist. 1 . Electromagnetically actuated inlet valve (24) for a high-pressure pump, in particular a fuel injection system, having a valve member (34) movable between an open position and a closed position, with an electromagnetic actuator (60) through which the valve member (34) is movable the electromagnetic actuator (60) has a magnet armature (68) acting at least indirectly on the valve member (34), a magnet coil (64) surrounding the magnet armature (68) and a magnetic core (66) on which the magnet armature (68) energizes the magnet armature (68) Magnetic coil (64) at least indirectly comes to rest, wherein the armature (68) in a support member (78) is displaceably guided and wherein the carrier element (78) and the magnetic core (66) are interconnected, characterized in that the carrier element (78 ) and the magnetic core (66) via a sleeve-shaped connecting element (90) are interconnected, at least partially in the direction of his Longitudinal axis (91) is elastically deformable.
2. Einlassventil nach Anspruch 1 , 2. inlet valve according to claim 1,
dadurch gekennzeichnet, dass das Verbindungselement (90) zur Ermöglichung der elastischen Verformbarkeit wenigstens eine über dessen Umfang verlaufende Sicke (92) aufweist.  characterized in that the connecting element (90) for enabling the elastic deformability has at least one extending over the circumference bead (92).
3. Einlassventil nach Anspruch 1 oder 2, 3. inlet valve according to claim 1 or 2,
dadurch gekennzeichnet, dass das Verbindungselement (90) zur Ermöglichung der elastischen Verformbarkeit wenigstens einen ringförmigen Einsatz (94) aus einem Werkstoff mit gegenüber dem Werkstoff des übrigen Verbindungselements (90) höherer Elastizität aufweist.  characterized in that the connecting element (90) for enabling the elastic deformability at least one annular insert (94) made of a material with respect to the material of the remaining connecting element (90) has higher elasticity.
4. Einlassventil nach einem der Ansprüche 1 bis 3, 4. Inlet valve according to one of claims 1 to 3,
dadurch gekennzeichnet, dass das Verbindungselement (90) an einem axialen Endbereich (90a) mit dem Trägerelement (78) verbunden ist und mit seinem anderen axialen Endbereich (90b) mit dem Magnetkern (66) verbunden ist und dass das Verbindungselement (90) in einem zwischen dessen axialen Endbereichen (90a, 90b) angeordneten mittleren Bereich (90c) elastisch verformbar ist. characterized in that the connecting element (90) is connected to the carrier element (78) at an axial end region (90a) and with its other axial end portion (90b) is connected to the magnetic core (66) and that the connecting element (90) in a between the axial end portions (90a, 90b) arranged central region (90c) is elastically deformable.
Einlassventil nach Anspruch 4, Inlet valve according to claim 4,
dadurch gekennzeichnet, dass das Trägerelement (78) zumindest abschnittsweise eine zylindrische Außenform aufweist und/oder dass der Magnetkern (66) zumindest abschnittsweise eine zylindrische Außenform aufweist und dass das Verbindungselement (90) mit dem zylindrischen Abschnitt (79) des Trägerelements (78) und/oder mit dem zylindrischen Abschnitt des Magnetkerns (66) verbunden ist. characterized in that the carrier element (78) at least partially has a cylindrical outer shape and / or that the magnetic core (66) at least partially has a cylindrical outer shape and that the connecting element (90) with the cylindrical portion (79) of the carrier element (78) and / or with the cylindrical portion of the magnetic core (66) is connected.
Einlassventil nach einem der vorstehenden Ansprüche, Inlet valve according to one of the preceding claims,
dadurch gekennzeichnet, dass das Verbindungselement (90) mit dem Trägerelement (78) und/oder dem Magnetkern (66) stoffschlüssig verbunden, insbesondere verschweißt ist. characterized in that the connecting element (90) with the support member (78) and / or the magnetic core (66) integrally connected, in particular welded.
Hochdruckpumpe, insbesondere Kraftstoffh och d ruckpumpe, 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, dadurch gekennzeichnet, dass das Einlassventil (24) gemäß einem der vorstehenden Ansprüche ausgebildet ist. High-pressure pump, in particular fuel high-pressure pump, with at least one pump element (10) having a pump piston (12) defining a pump working space (18), wherein the pump working space (18) via an inlet valve (24) with an inlet (26) is connectable , characterized in that the inlet valve (24) is designed according to one of the preceding claims.
PCT/EP2016/079034 2015-12-21 2016-11-28 Electromagnetically actuatable inlet valve and high-pressure pump having an inlet valve WO2017108343A1 (en)

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JP6708238B2 (en) * 2017-09-29 2020-06-10 株式会社デンソー High pressure pump

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1909361A1 (en) * 1969-02-25 1970-08-06 Herion Werke Kg Solenoid valve for alternating current operation
DE10212138A1 (en) * 2001-10-02 2003-04-17 Mitsubishi Electric Corp Fuel supply apparatus
JP2003314738A (en) * 2002-04-23 2003-11-06 Bosch Automotive Systems Corp Flow control valve
US20050073194A1 (en) * 2003-10-06 2005-04-07 Advics Co., Ltd. Brake fluid control device
DE102005061410A1 (en) * 2005-12-22 2007-06-28 Robert Bosch Gmbh Electromagnetically operated valve comprises axle together with core and plastic coil body in which coil is wound
DE102011076784A1 (en) * 2011-05-31 2012-12-06 Continental Automotive Gmbh Inlet valve for a fluid pump and method of mounting an inlet valve for a fluid pump
DE102013220593A1 (en) 2013-10-11 2015-04-16 Robert Bosch Gmbh Electromagnetically controllable suction valve

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1909361A1 (en) * 1969-02-25 1970-08-06 Herion Werke Kg Solenoid valve for alternating current operation
DE10212138A1 (en) * 2001-10-02 2003-04-17 Mitsubishi Electric Corp Fuel supply apparatus
JP2003314738A (en) * 2002-04-23 2003-11-06 Bosch Automotive Systems Corp Flow control valve
US20050073194A1 (en) * 2003-10-06 2005-04-07 Advics Co., Ltd. Brake fluid control device
DE102005061410A1 (en) * 2005-12-22 2007-06-28 Robert Bosch Gmbh Electromagnetically operated valve comprises axle together with core and plastic coil body in which coil is wound
DE102011076784A1 (en) * 2011-05-31 2012-12-06 Continental Automotive Gmbh Inlet valve for a fluid pump and method of mounting an inlet valve for a fluid pump
DE102013220593A1 (en) 2013-10-11 2015-04-16 Robert Bosch Gmbh Electromagnetically controllable suction valve

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