EP1592880B1 - Fuel injection device for an internal combustion engine - Google Patents

Fuel injection device for an internal combustion engine Download PDF

Info

Publication number
EP1592880B1
EP1592880B1 EP03773529A EP03773529A EP1592880B1 EP 1592880 B1 EP1592880 B1 EP 1592880B1 EP 03773529 A EP03773529 A EP 03773529A EP 03773529 A EP03773529 A EP 03773529A EP 1592880 B1 EP1592880 B1 EP 1592880B1
Authority
EP
European Patent Office
Prior art keywords
housing part
fuel injection
spring element
injection device
magnet assembly
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.)
Expired - Lifetime
Application number
EP03773529A
Other languages
German (de)
French (fr)
Other versions
EP1592880A1 (en
Inventor
Wolfgang Geiger
Peter Grabandt
Uwe Baerenwaldt
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 EP1592880A1 publication Critical patent/EP1592880A1/en
Application granted granted Critical
Publication of EP1592880B1 publication Critical patent/EP1592880B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • 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
    • F02M63/0059—Arrangements of valve actuators
    • F02M63/0064—Two or more actuators acting on two or more valve bodies
    • 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
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • 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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/005—Arrangement of electrical wires and connections, e.g. wire harness, sockets, plugs; Arrangement of electronic control circuits in or on fuel injection apparatus
    • 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
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/02—Injectors structurally combined with fuel-injection pumps
    • F02M57/022—Injectors structurally combined with fuel-injection pumps characterised by the pump drive
    • F02M57/023—Injectors structurally combined with fuel-injection pumps characterised by the pump drive mechanical
    • 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/168—Assembling; Disassembling; Manufacturing; Adjusting
    • 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/20—Closing valves mechanically, e.g. arrangements of springs or weights or permanent magnets; Damping of valve lift
    • F02M61/205—Means specially adapted for varying the spring tension or assisting the spring force to close the injection-valve, e.g. with damping of valve lift

Definitions

  • the invention relates to a fuel injection device for an internal combustion engine according to the preamble of claim 1.
  • Such a fuel injection device is known from the literature, for example Diesel Engine Management, Verlag Vieweg, 2nd edition 1998, page 246.
  • This fuel injection device has a solenoid valve for controlling the fuel injection.
  • the solenoid valve is inserted into a housing part and has a magnet assembly with a magnetic coil and a magnet armature. With the housing part, a cover part is joined, by which the magnet assembly of the solenoid valve is held in the housing part.
  • the cover part should preferably be brought together with the housing part after a functional test of the magnetic assembly to avoid unnecessary assembly steps, but then in the functional test, the risk of falling out of the magnet assembly is. Moreover, no compensation of different lengths of the magnet assembly is possible in this known fuel injector, so that it may not be securely fixed in the housing part.
  • a fuel injector having a solenoid valve for controlling fuel injection.
  • the solenoid valve is arranged in a cover part and has a magnet assembly with a magnet coil and a magnet armature.
  • the cover part forms with the magnet assembly a structural unit and can be inserted into a recess of a housing part of the fuel injection device, wherein the cover part by means of a spring element in the form of a bow spring on the housing part can be fastened.
  • the magnet assembly can be checked separately for their function, but there is the danger that this is unintentionally solved in the attachment of the cover part by means of bow spring and the cover part with the magnet assembly is no longer held on the housing part and thus the function of the fuel injector is impaired.
  • the fuel injection device according to the invention with the features of claim 1 has the advantage that the magnet assembly is fixed in the housing part before attaching the lid part. In addition, a length compensation of the magnet assembly and thus their secure fixation is made possible by the spring element. By integrally forming the at least one retaining element with the spring element, only one additional component is required.
  • FIG. 2 shows a housing part of the fuel injection device according to Figure 1 in a longitudinal section with a spring element according to a first embodiment
  • Figure 3 shows the spring element according to the first embodiment in a perspective view
  • Figure 4 the Housing part with the spring element according to the first embodiment in a perspective view
  • Figure 5 the spring element according to a second embodiment in a perspective Representation
  • Figure 6 shows a detail of the housing part with the spring element according to the second embodiment.
  • FIG. 1 schematically shows a fuel injection device for an internal combustion engine, for example of a motor vehicle.
  • the internal combustion engine is preferably a self-igniting internal combustion engine and has one or more cylinders.
  • the fuel injection device may be formed, for example, as shown in Figure 1 as a pump-nozzle unit, each having a high-pressure fuel pump 10 and a fuel injection valve 12 for each cylinder of the internal combustion engine, which form a common structural unit.
  • At least one solenoid valve 56, 60 for controlling the fuel injection is arranged at the pump-nozzle unit.
  • the fuel injector may be formed as a pump-line-nozzle unit, in which also for each cylinder of the internal combustion engine each have a high-pressure fuel pump and a fuel injection valve are present, however, are arranged separately from each other and are connected to each other via a hydraulic line.
  • a solenoid valve for controlling the fuel injection is arranged on the high-pressure fuel pump or the fuel injection valve of the pump-line-nozzle unit.
  • the fuel injection device can also be designed as a common rail system, in which fuel is conveyed by a high-pressure fuel pump into a memory, are connected to the arranged on the cylinders of the internal combustion engine injectors, on each of which a solenoid valve for controlling the fuel injection is arranged.
  • the fuel injection device can also as Fuel injection pump may be formed, is conveyed by the fuel under high pressure and connected to the arranged on the cylinders of the internal combustion engine fuel injection valves, wherein on the fuel injection pump, a solenoid valve for controlling the high-pressure generation and thus the fuel injection is arranged.
  • the high-pressure fuel pump 10 has a tightly guided in a cylinder bore 16 of a pump body 18 pump piston 20 which limits a pump working chamber 22 in the cylinder bore 16.
  • the pump piston 20 is driven by a cam 24 of a camshaft of the internal combustion engine at least indirectly, for example via a rocker arm against the force of a return spring 26 in a reciprocating motion.
  • the pump working chamber 22 is supplied with fuel from a fuel reservoir 28, for example by means of a feed pump 29 during the suction stroke of the pump piston 20.
  • the fuel injection valve 12 has a connected to the pump body 18 valve body 30 which may be formed in several parts, and in which in a bore 32, an injection valve member 34 is longitudinally displaceably guided. Between the valve body 30 and the pump body 18, an intermediate body 36 is arranged.
  • the valve body 30 has at its end facing the combustion chamber of the cylinder of the internal combustion engine at least one, preferably a plurality of injection openings 38.
  • the injection valve member 34 has, at its end region facing the combustion chamber, an approximately conical sealing surface 40, for example, which engages with a valve body 30 in the valve body 30 its end face facing the combustion chamber formed valve seat 41 cooperates, from or after the discharge the injection ports 32.
  • annular space 42 is provided between the injection valve member 34 and the bore 32 toward the valve seat 41, which merges in its end region remote from the valve seat 41 by a radial widening of the bore 32 into a pressure chamber 44 surrounding the injection valve member 34.
  • the injection valve member 34 has at the level of the pressure chamber 44 by a change in cross section on a valve seat 41 directed towards the pressure shoulder 46.
  • a prestressed closing spring 48 At the end remote from the combustion chamber of the injection valve member 34 engages a prestressed closing spring 48, through which the injection valve member 34 is pressed to the valve seat 41.
  • the closing spring 48 is arranged in a spring chamber 49 in the valve body 30 or in the intermediate body 36, which adjoins the bore 30.
  • a bore 50 with a smaller diameter connects.
  • a control piston 51 is guided tightly, which limits a control pressure chamber 52 in the bore 50.
  • the control piston 51 is supported on the injection valve member 34 and generates depending on the pressure prevailing in the control pressure chamber 52, a closing spring 48 supporting force in the closing direction of the injection valve member 34.
  • the connection 55 is controlled by a first solenoid valve 56, which is designed as a 2/2-way valve.
  • the solenoid valve 56 is driven by an electronic control device 57 and will be explained in more detail below. From the channel 54, another channel 58 leads into the control pressure chamber 52 and the Control pressure chamber 52 has a connection 59 with a discharge area, for example, a return to the fuel tank 28. The connection 59 of the control pressure chamber 52 with the discharge area is controlled by a second solenoid valve 60, which is also controlled by the control device 57. By the first solenoid valve 56, the pressure buildup in the pump chamber 22 of the high-pressure fuel pump 10 is controlled and by the second solenoid valve 60, the pressure in the control pressure chamber 52 and thereby the opening of the fuel injection valve 12 is controlled.
  • the second solenoid valve 60 and the control pressure chamber 52 may also be omitted, wherein the opening of the fuel injection valve 12 is determined only by the closing spring 48. If the pressure prevailing in the pressure chamber 44 via the pressure shoulder 46 generates a greater force on the injection valve member 34 than the closing spring 48 and the pressure prevailing in the control pressure chamber 52, the injection valve member 34 moves in the opening direction 35 and the injection openings 38 free.
  • the intermediate body 36 is shown enlarged with the arranged in this two solenoid valves 56 and 60.
  • the intermediate body 36 has two recesses 61 emanating from its end face facing the pump body 18, in each of which a magnet assembly 62 of the magnetic valves 56, 60 is inserted.
  • the magnet assembly 62 has in each case a magnetic coil 63 and a magnet armature 64 and optionally further components.
  • the magnet assembly 62 is covered toward the open end of the recesses 61 toward each by a pressure piece 65.
  • the cross-section of the recesses 61 and the magnet assemblies 62 is adapted to each other, for example, circular.
  • the armature 64 is respectively connected to a solenoid valve member 66 through which the connection 55 between the channel 50 and the feed pump 29 is opened or closed or through which the connection 59 of Control pressure chamber 52 is opened or closed with the discharge area.
  • solenoid valve member 66 of the respective solenoid valve 56,60 When not energized solenoid 63, the solenoid valve member 66 of the respective solenoid valve 56,60 is in a first position in which this connection 55,59 is open or closed and when energizing the solenoid 63, the solenoid valve member 66 of the respective solenoid valve 56,60 in a moved second position in which this closes or opens the connection 55,59 accordingly.
  • the magnet assemblies 62 of the two solenoid valves 56,60 held by a respective spring element 70 in the recesses 61.
  • a spring element 70 designed as a round disk spring is provided, which clamps the magnet assembly 62 in the recess 61 in an axial direction, that is, in the direction of the longitudinal axis of the recess 61 and the magnet assembly 62 via the respective pressure piece 65.
  • the two spring elements 70 are integrally formed with each other and connected via a Figure 3 apparent web 71 to each other. The spring elements 70 are bent in the axial direction to produce the required preload.
  • a holding element 72 is formed in the form of a hook.
  • the hook 72 projects from the spring element 70 approximately radially outwards and is bent at its free end in a U-shape inwards.
  • the hook 72 is preferably resilient and engages at least indirectly on the intermediate body 36.
  • a pin 74 is pressed, which extends at least approximately parallel to the longitudinal axes of the recesses 61.
  • the hook 72 of Spring element 70 is hooked on the pin 74 and surrounds this on its protruding from the intermediate body 36 part.
  • the hook 72 may be pressed onto the pin 74 as well.
  • a further holding element is integrally formed, which is formed by two mutually offset in the circumferential direction lugs 75 which engage around at least indirectly the intermediate body 36.
  • the embrace the lugs 75 side In the pump body 18 facing the end face of the intermediate body 36 recesses for the holding elements 72 and 75 and for the two spring elements 70 connecting web 71 are introduced so that they do not protrude beyond the end face of the intermediate body 36.
  • the magnetic assemblies 62 inserted into the intermediate body 36 are secured against falling out by the spring members 70 even during subsequent transport prior to final assembly of the fuel injector.
  • the pump body 18 and the valve body 30 are assembled with the intermediate body 36, the pump body 18 forming a lid portion through which the spring members 70 axially be compressed and clamped over these the magnetic assemblies 62 in the recesses 61 of the intermediate body 36 and thus fixed without play.
  • the spring element 170 is shown according to a second embodiment. In this case, only one spring element 170 is provided for one of the solenoid valves 56, 60. There is the possibility that only the first solenoid valve 56 and a spring element 170 is present for this or that both solenoid valves 56,60 and each have a separate spring element 170 for this is present.
  • the spring element 170 is designed as a disc spring with a circular cross-section and integrally formed thereon is a surrounding retaining element 172 in the form of a securing ring.
  • the securing ring 172 is integrally formed on the spring element 170 via an approximately radially extending web 171.
  • the locking ring 172 is radially elastically deformable.
  • the recess 161 in the intermediate body 136 in which the magnet assembly 62 is inserted, has near its the end face of the intermediate body 136 end facing in its periphery an undercut forming cross-sectional enlargement 174, which may be formed by an annular groove, a depression or a bore, in which the retaining ring 172 can be latched radially outwards.
  • the diameter of the locking ring 172 in the relaxed state is slightly larger than the diameter of the recess 161, wherein the insertion of the spring member 170 into the recess 161 of the locking ring 172 is radially elastically compressed and relaxed in the end position of the spring member 170 to the outside and in the Ring groove 174 engages.
  • the spring element 170 is fixed on the intermediate body 136 and secured by this the magnetic assembly 62 against falling out in the intermediate body 136.
  • the spring element 170 in the axial direction compressed and thereby held the magnet assembly 62 backlash in the intermediate body 136.

Landscapes

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

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine nach der Gattung des Anspruchs 1.The invention relates to a fuel injection device for an internal combustion engine according to the preamble of claim 1.

Eine solche Kraftstoffeinspritzeinrichtung ist aus der Literatur, beispielsweise Dieselmotor-Management, Verlag Vieweg, 2.Auflage 1998, Seite 246, bekannt. Diese Kraftstoffeinspritzeinrichtung weist ein Magnetventil zur Steuerung der Kraftstoffeinspritzung auf. Das Magnetventil ist in ein Gehäuseteil eingesetzt und weist eine Magnetbaugruppe mit einer Magnetspule und einem Magnetanker auf. Mit dem Gehäuseteil ist ein Deckelteil zusammengefügt, durch das die Magnetbaugrupppe des Magnetventils im Gehäuseteil gehalten wird. Beim Einsetzen der Magnetbaugruppe in das Gehäuseteil besteht das Problem, dass die Magnetbaugruppe erst mit dem Zusammenfügen des Deckelteils mit dem Gehäuseteil fixiert wird, so dass die Magnetbaugruppe vor dem Anbringen des Deckelteils wieder aus dem Gehäuseteil herausfallen kann. Das Deckelteil sollte zur Vermeidung unnötiger Montageschritte vorzugsweise erst nach einer Funktionsprüfung der Magnetbaugruppe mit dem Gehäuseteil zusammengeführt werden, wobei dann jedoch bei der Funktionsprüfung die Gefahr des Herausfallens der Magnetbaugruppe besteht. Darüberhinaus ist bei dieser bekannten Kraftstoffeinspritzeinrichtung kein Ausgleich unterschiedlicher Längen der Magnetbaugruppe möglich, so dass diese unter Umständen nicht sicher im Gehäuseteil fixiert wird.Such a fuel injection device is known from the literature, for example Diesel Engine Management, Verlag Vieweg, 2nd edition 1998, page 246. This fuel injection device has a solenoid valve for controlling the fuel injection. The solenoid valve is inserted into a housing part and has a magnet assembly with a magnetic coil and a magnet armature. With the housing part, a cover part is joined, by which the magnet assembly of the solenoid valve is held in the housing part. When inserting the magnet assembly into the housing part there is the problem that the magnet assembly is fixed only with the joining of the cover part with the housing part, so that the magnet assembly can fall out of the housing part again before attaching the cover part. The cover part should preferably be brought together with the housing part after a functional test of the magnetic assembly to avoid unnecessary assembly steps, but then in the functional test, the risk of falling out of the magnet assembly is. Moreover, no compensation of different lengths of the magnet assembly is possible in this known fuel injector, so that it may not be securely fixed in the housing part.

Durch die EP-A-1 219 823 ist eine Kraftstoffeinspritzeinrichtung bekannt, die ein Magnetventil zur Steuerung der Kraftstoffeinspritzung aufweist. Das Magnetventil ist in einem Deckelteil angeordnet und weist eine Magnetbaugruppe mit einer Magnetspule und einem Magnetanker auf. Das Deckelteil bildet mit der Magnetbaugruppe eine Baueinheit und ist in eine Ausnehmung eines Gehäuseteils der Kraftstoffeinspritzeinrichtung einsetzbar, wobei das Deckelteil mittels eines Federelements in Form einer Bügelfeder am Gehäuseteil befestigbar ist. Bei dieser Kraftstoffeinspritzeinrichtung kann zwar die Magnetbaugruppe separat auf ihre Funktion überprüft werden, jedoch besteht bei der Befestigung des Deckelteils mittels der Bügelfeder die Gefahr, dass diese unbeabsichtigt gelöst wird und das Deckelteil mit der Magnetbaugruppe nicht mehr am Gehäuseteil gehalten ist und damit die Funktion der Kraftstoffeinspritzeinrichtung beeinträchtigt wird.From EP-A-1 219 823 there is known a fuel injector having a solenoid valve for controlling fuel injection. The solenoid valve is arranged in a cover part and has a magnet assembly with a magnet coil and a magnet armature. The cover part forms with the magnet assembly a structural unit and can be inserted into a recess of a housing part of the fuel injection device, wherein the cover part by means of a spring element in the form of a bow spring on the housing part can be fastened. Although in this fuel injection device, the magnet assembly can be checked separately for their function, but there is the danger that this is unintentionally solved in the attachment of the cover part by means of bow spring and the cover part with the magnet assembly is no longer held on the housing part and thus the function of the fuel injector is impaired.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Kraftstoffeinspritzeinrichtung mit den Merkmalen gemäß Anspruch 1 hat demgegenüber den Vorteil, dass die Magnetbaugruppe schon vor dem Anbringen des Deckelteils im Gehäuseteil fixiert ist. Darüberhinaus ist durch das Federelement ein Längenausgleich der Magnetbaugruppe und damit deren sichere Fixierung ermöglicht. Durch die einstückige Ausbildung des wenigstens einen Halteelements mit dem Federelement ist lediglich ein zusätzliches Bauteil erforderlich.The fuel injection device according to the invention with the features of claim 1 has the advantage that the magnet assembly is fixed in the housing part before attaching the lid part. In addition, a length compensation of the magnet assembly and thus their secure fixation is made possible by the spring element. By integrally forming the at least one retaining element with the spring element, only one additional component is required.

In den abhängigen Ansprüchen sind vorteilhafte Ausgestaltungen und Weiterbildungen der erfindungsgemäßen Kraftstoffeinspritzeinrichtung angegeben. Bei der Ausbildung des Federelements gemäß Anspruch 2 als Tellerfeder erfordert dieses nur einen geringen Bauraum. Die Ausbildung gemäß Anspruch 3 und 4 ermöglicht eine sichere Fixierung des Federelements und damit auch der Magnetbaugruppe.In the dependent claims advantageous refinements and developments of the fuel injection device according to the invention are given. In the formation of the spring element according to claim 2 as a plate spring this requires only a small space. The training according to claim 3 and 4 allows a secure fixation of the spring element and thus also the magnetic assembly.

Zeichnungdrawing

Mehrere Ausführungsbeispiele der Erfindung sind in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 ausschnittsweise eine Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine mit einem Magnetventil, Figur 2 ein Gehäuseteil der Kraftstoffeinspritzeinrichtung gemäß Figur 1 in einem Längsschnitt mit einem Federelement gemäß einem ersten Ausführungsbeispiel, Figur 3 das Federelement gemäß dem ersten Ausführungsbeispiel in einer perspektivischen Darstellung, Figur 4 das Gehäuseteil mit dem Federelement gemäß dem ersten Ausführungsbeispiel in einer perspektivischen Darstellung, Figur 5 das Federelement gemäß einem zweiten Ausführungsbeispiel in einer perspektivischen Darstellung und Figur 6 ausschnittsweise das Gehäuseteil mit dem Federelement gemäß dem zweiten Ausführungsbeispiel.Several embodiments of the invention are illustrated in the drawings and explained in more detail in the following description. 2 shows a housing part of the fuel injection device according to Figure 1 in a longitudinal section with a spring element according to a first embodiment, Figure 3 shows the spring element according to the first embodiment in a perspective view, Figure 4 the Housing part with the spring element according to the first embodiment in a perspective view, Figure 5, the spring element according to a second embodiment in a perspective Representation and Figure 6 shows a detail of the housing part with the spring element according to the second embodiment.

Beschreibung der AusführungsbeispieleDescription of the embodiments

In Figur 1 ist schematisch eine Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine beispielsweise eines Kraftfahrzeugs dargestellt. Die Brennkraftmaschine ist vorzugsweise eine selbstzündende Brennkraftmaschine und weist einen oder mehrere Zylinder auf. Die Kraftstoffeinspritzeinrichtung kann beispielsweise wie in Figur 1 dargestellt als Pumpe-Düse-Einheit ausgebildet sein, die jeweils eine Kraftstoffhochdruckpumpe 10 und ein Kraftstoffeinspritzventil 12 für jeden Zylinder der Brennkraftmaschine aufweist, die eine gemeinsame Baueinheit bilden. An der Pumpe-Düse-Einheit ist wenigstens ein Magnetventil 56,60 zur Steuerung der Kraftstoffeinspritzung angeordnet. Alternativ kann die Kraftstoffeinspritzeinrichtung auch als Pumpe-Leitung-Düse-Einheit ausgebildet sein, bei der ebenfalls für jeden Zylinder der Brennkraftmaschine jeweils eine Kraftstoffhochdruckpumpe und ein Kraftstoffeinspritzventil vorhanden sind, die jedoch getrennt voneinander angeordnet sind und über eine hydraulische Leitung miteinander verbunden sind. An der Kraftstoffhochdruckpumpe oder am Kraftstoffeinspritzventil der Pumpe-Leitung-Düse-Einheit ist ein Magnetventil zur Steuerung der Kraftstoffeinspritzung angeordnet. Ausserdem kann die Kraftstoffeinspritzeinrichtung auch als Common-Rail-System ausgebildet sein, bei dem durch eine Kraftstoffhochdruckpumpe Kraftstoff in einen Speicher gefördert wird, mit dem an den Zylindern der Brennkraftmaschine angeordnete Injektoren verbunden sind, an denen jeweils ein Magnetventil zur Steuerung der Kraftsoffeinspritzung angeordnet ist. Weiterhin kann die Kraftstoffeinspritzeinrichtung auch als Kraftstoffeinspritzpumpe ausgebildet sein, durch die Kraftstoff unter Hochdruck gefördert wird und mit der an den Zylindern der Brennkraftmaschine angeordnete Kraftstoffeinspritzventile verbunden sind, wobei an der Kraftstoffeinspritzpumpe ein Magnetventil zur Steuerung der Hochdruckerzeugung und damit der Kraftstoffeinspritzung angeordnet ist.FIG. 1 schematically shows a fuel injection device for an internal combustion engine, for example of a motor vehicle. The internal combustion engine is preferably a self-igniting internal combustion engine and has one or more cylinders. The fuel injection device may be formed, for example, as shown in Figure 1 as a pump-nozzle unit, each having a high-pressure fuel pump 10 and a fuel injection valve 12 for each cylinder of the internal combustion engine, which form a common structural unit. At least one solenoid valve 56, 60 for controlling the fuel injection is arranged at the pump-nozzle unit. Alternatively, the fuel injector may be formed as a pump-line-nozzle unit, in which also for each cylinder of the internal combustion engine each have a high-pressure fuel pump and a fuel injection valve are present, however, are arranged separately from each other and are connected to each other via a hydraulic line. On the high-pressure fuel pump or the fuel injection valve of the pump-line-nozzle unit, a solenoid valve for controlling the fuel injection is arranged. In addition, the fuel injection device can also be designed as a common rail system, in which fuel is conveyed by a high-pressure fuel pump into a memory, are connected to the arranged on the cylinders of the internal combustion engine injectors, on each of which a solenoid valve for controlling the fuel injection is arranged. Furthermore, the fuel injection device can also as Fuel injection pump may be formed, is conveyed by the fuel under high pressure and connected to the arranged on the cylinders of the internal combustion engine fuel injection valves, wherein on the fuel injection pump, a solenoid valve for controlling the high-pressure generation and thus the fuel injection is arranged.

Nachfolgend wird die Erfindung für die Anwendung bei einer Pumpe-Düse-Einheit erläutert, wobei diese jedoch auch auf die vorstehend genannten anderen Ausführungen von Kraftstoffeinspritzeinrichtungen übertragbar ist. Die Kraftstoffhochdruckpumpe 10 weist einen in einer Zylinderbohrung 16 eines Pumpenkörpers 18 dicht geführten Pumpenkolben 20 auf, der in der Zylinderbohrung 16 einen Pumpenarbeitsraum 22 begrenzt. Der Pumpenkolben 20 wird durch einen Nocken 24 einer Nockenwelle der Brennkraftmaschine zumindest mittelbar, beispielsweise über einen Kipphebel, gegen die Kraft einer Rückstellfeder 26 in einer Hubbewegung angetrieben. Dem Pumpenarbeitsraum 22 wird beim Saughub des Pumpenkolbens 20 Kraftstoff aus einem Kraftstoffvorratsbehälter 28 beispielsweise mittels einer Förderpumpe 29 zugeführt.In the following, the invention will be explained for use with a pump-nozzle unit, but it is also applicable to the above-mentioned other embodiments of fuel injectors. The high-pressure fuel pump 10 has a tightly guided in a cylinder bore 16 of a pump body 18 pump piston 20 which limits a pump working chamber 22 in the cylinder bore 16. The pump piston 20 is driven by a cam 24 of a camshaft of the internal combustion engine at least indirectly, for example via a rocker arm against the force of a return spring 26 in a reciprocating motion. The pump working chamber 22 is supplied with fuel from a fuel reservoir 28, for example by means of a feed pump 29 during the suction stroke of the pump piston 20.

Das Kraftstoffeinspritzventil 12 weist einen mit dem Pumpenkörper 18 verbundenen Ventilkörper 30 auf, der mehrteilig ausgebildet sein kann, und in dem in einer Bohrung 32 ein Einspritzventilglied 34 längsverschiebbar dicht geführt ist. Zwischen dem Ventilkörper 30 und dem Pumpenkörper 18 ist ein Zwischenkörper 36 angeordnet. Der Ventilkörper 30 weist an seinem dem Brennraum des Zylinders der Brennkraftmaschine zugewandten Endbereich wenigstens eine, vorzugsweise mehrere Einspritzöffnungen 38 auf. Das Einspritzventilglied 34 weist an seinem dem Brennraum zugewandten Endbereich eine beispielsweise etwa kegelförmige Dichtfläche 40 auf, die mit einem im Ventilkörper 30 in dessen dem Brennraum zugewandtem Endbereich ausgebildeten Ventilsitz 41 zusammenwirkt, von dem oder nach dem die Einspritzöffnungen 32 abführen. Im Ventilkörper 30 ist zwischen dem Einspritzventilglied 34 und der Bohrung 32 zum Ventilsitz 41 hin ein Ringraum 42 vorhanden, der in seinem dem Ventilsitz 41 abgewandten Endbereich durch eine radiale Erweiterung der Bohrung 32 in einen das Einspritzventilglied 34 umgebenden Druckraum 44 übergeht. Das Einspritzventilglied 34 weist in Höhe des Druckraums 44 durch eine Querschnittsänderung eine zum Ventilsitz 41 hin gerichtete Druckschulter 46 auf. Am dem Brennraum abgewandten Ende des Einspritzventilglieds 34 greift eine vorgespannte Schließfeder 48 an, durch die das Einspritzventilglied 34 zum Ventilsitz 41 hin gedrückt wird. Die Schließfeder 48 ist in einem Federraum 49 im Ventilkörper 30 oder im Zwischenkörper 36 angeordnet, die sich an die Bohrung 30 anschließt.The fuel injection valve 12 has a connected to the pump body 18 valve body 30 which may be formed in several parts, and in which in a bore 32, an injection valve member 34 is longitudinally displaceably guided. Between the valve body 30 and the pump body 18, an intermediate body 36 is arranged. The valve body 30 has at its end facing the combustion chamber of the cylinder of the internal combustion engine at least one, preferably a plurality of injection openings 38. The injection valve member 34 has, at its end region facing the combustion chamber, an approximately conical sealing surface 40, for example, which engages with a valve body 30 in the valve body 30 its end face facing the combustion chamber formed valve seat 41 cooperates, from or after the discharge the injection ports 32. In the valve body 30, an annular space 42 is provided between the injection valve member 34 and the bore 32 toward the valve seat 41, which merges in its end region remote from the valve seat 41 by a radial widening of the bore 32 into a pressure chamber 44 surrounding the injection valve member 34. The injection valve member 34 has at the level of the pressure chamber 44 by a change in cross section on a valve seat 41 directed towards the pressure shoulder 46. At the end remote from the combustion chamber of the injection valve member 34 engages a prestressed closing spring 48, through which the injection valve member 34 is pressed to the valve seat 41. The closing spring 48 is arranged in a spring chamber 49 in the valve body 30 or in the intermediate body 36, which adjoins the bore 30.

An den Federraum 49 schließt sich an dessen dem Druckraum 44 abgewandtem Ende eine Bohrung 50 mit kleinerem Durchmesser an. In der Bohrung 50 ist ein Steuerkolben 51 dicht geführt, der in der Bohrung 50 einen Steuerdruckraum 52 begrenzt. Der Steuerkolben 51 stützt sich am Einspritzventilglied 34 ab und erzeugt abhängig von dem im Steuerdruckraum 52 herrschenden Druck eine die Schließfeder 48 unterstützende Kraft in Schließrichtung auf das Einspritzventilglied 34. Vom Pumpenarbeitsraum 22 führt durch den Pumpenkörper 18, den Zwischenkörper 36 und den Ventilkörper 30 ein Kanal 54 in den Druckraum 44 des Kraftstoffeinspritzventils 12. Vom Kanal 54 führt eine Verbindung 55 zur Förderpumpe 29 und zum Kraftstoffvorratsbehälter 28 ab. Die Verbindung 55 wird durch ein erstes Magnetventil 56 gesteuert, das als 2/2-Wegeventil ausgebildet ist. Das Magnetventil 56 wird von einer elektronischen Steuereinrichtung 57 angesteuert und wird nachfolgend noch näher erläutert. Vom Kanal 54 führt ein weiterer Kanal 58 in den Steuerdruckraum 52 ab und der Steuerdruckraum 52 weist eine Verbindung 59 mit einem Entlastungsbereich, beispielsweise einem Rücklauf in den Kraftstoffvorratsbehälter 28 auf. Die Verbindung 59 des Steuerdruckraums 52 mit dem Entlastungsbereich wird durch ein zweites Magnetventil 60 gesteuert, das ebenfalls durch die Steuereinrichtung 57 angesteuert wird. Durch das erste Magnetventil 56 wird der Druckaufbau im Pumpenarbeitsraum 22 der Kraftstoffhochdruckpumpe 10 gesteuert und durch das zweite Magnetventil 60 wird der Druck im Steuerdruckraum 52 und dadurch die Öffnung des Kraftstoffeinspritzventils 12 gesteuert. Das zweite Magnetventil 60 und der Steuerdruckraum 52 können auch entfallen, wobei die Öffnung des Kraftstoffeinspritzventils 12 nur durch die Schließfeder 48 bestimmt wird. Wenn der im Druckraum 44 herrschende Druck über die Druckschulter 46 eine größere Kraft auf das Einspritzventilglied 34 erzeugt als die Schließfeder 48 und der im Steuerdruckraum 52 herrschende Druck, so bewegt sich das Einspritzventilglied 34 in Öffnungsrichtung 35 und gibt die Einspritzöffnungen 38 frei.At the spring chamber 49, at the end facing away from the pressure chamber 44, a bore 50 with a smaller diameter connects. In the bore 50, a control piston 51 is guided tightly, which limits a control pressure chamber 52 in the bore 50. The control piston 51 is supported on the injection valve member 34 and generates depending on the pressure prevailing in the control pressure chamber 52, a closing spring 48 supporting force in the closing direction of the injection valve member 34. From the pump working chamber 22 through the pump body 18, the intermediate body 36 and the valve body 30 a channel 54 in the pressure chamber 44 of the fuel injection valve 12. From the channel 54 performs a connection 55 to the feed pump 29 and the fuel tank 28 from. The connection 55 is controlled by a first solenoid valve 56, which is designed as a 2/2-way valve. The solenoid valve 56 is driven by an electronic control device 57 and will be explained in more detail below. From the channel 54, another channel 58 leads into the control pressure chamber 52 and the Control pressure chamber 52 has a connection 59 with a discharge area, for example, a return to the fuel tank 28. The connection 59 of the control pressure chamber 52 with the discharge area is controlled by a second solenoid valve 60, which is also controlled by the control device 57. By the first solenoid valve 56, the pressure buildup in the pump chamber 22 of the high-pressure fuel pump 10 is controlled and by the second solenoid valve 60, the pressure in the control pressure chamber 52 and thereby the opening of the fuel injection valve 12 is controlled. The second solenoid valve 60 and the control pressure chamber 52 may also be omitted, wherein the opening of the fuel injection valve 12 is determined only by the closing spring 48. If the pressure prevailing in the pressure chamber 44 via the pressure shoulder 46 generates a greater force on the injection valve member 34 than the closing spring 48 and the pressure prevailing in the control pressure chamber 52, the injection valve member 34 moves in the opening direction 35 and the injection openings 38 free.

In Figur 2 ist der Zwischenkörper 36 mit den in diesem angeordneten beiden Magnetventilen 56 und 60 vergrößert dargestellt. Der Zwischenkörper 36 weist zwei von seiner dem Pumpenkörper 18 zugewandten Stirnseite ausgehende Ausnehmungen 61 auf, in denen jeweils eine Magnetbaugruppe 62 der Magnetventile 56,60 eingesetzt ist. Die Magnetbaugruppe 62 weist jeweils eine Magnetspule 63 und einen Magnetanker 64 sowie gegebenenfalls noch weitere Bauteile auf. Die Magnetbaugruppe 62 ist zum offenen Ende der Ausnehmungen 61 hin jeweils durch ein Druckstück 65 abgedeckt. Der Querschnitt der Ausnehmungen 61 und der Magnetbaugruppen 62 ist einander angepasst, beispielsweise kreisförmig. Der Magnetanker 64 ist jeweils mit einem Magnetventilglied 66 verbunden, durch das die Verbindung 55 zwischen dem Kanal 50 und der Förderpumpe 29 geöffnet oder geschlossen wird oder durch das die Verbindung 59 des Steuerdruckraums 52 mit dem Entlastungsbereich geöffnet oder geschlossen wird. Bei nichtbestromter Magnetspule 63 befindet sich das Magnetventilglied 66 des jeweiligen Magnetventils 56,60 in einer ersten Stellung, in der dieses die Verbindung 55,59 geöffnet oder geschlossen ist und bei Bestromung der Magnetspule 63 wird das Magnetventilglied 66 des jeweiligen Magnetventils 56,60 in eine zweite Stellung bewegt, in der dieses die Verbindung 55,59 entsprechend schließt oder öffnet.In Figure 2, the intermediate body 36 is shown enlarged with the arranged in this two solenoid valves 56 and 60. The intermediate body 36 has two recesses 61 emanating from its end face facing the pump body 18, in each of which a magnet assembly 62 of the magnetic valves 56, 60 is inserted. The magnet assembly 62 has in each case a magnetic coil 63 and a magnet armature 64 and optionally further components. The magnet assembly 62 is covered toward the open end of the recesses 61 toward each by a pressure piece 65. The cross-section of the recesses 61 and the magnet assemblies 62 is adapted to each other, for example, circular. The armature 64 is respectively connected to a solenoid valve member 66 through which the connection 55 between the channel 50 and the feed pump 29 is opened or closed or through which the connection 59 of Control pressure chamber 52 is opened or closed with the discharge area. When not energized solenoid 63, the solenoid valve member 66 of the respective solenoid valve 56,60 is in a first position in which this connection 55,59 is open or closed and when energizing the solenoid 63, the solenoid valve member 66 of the respective solenoid valve 56,60 in a moved second position in which this closes or opens the connection 55,59 accordingly.

Bei einem in den Figuren 2 bis 4 dargestellten ersten Ausführungsbeispiel werden die Magnetbaugruppen 62 der beiden Magnetventile 56,60 durch jeweils ein Federelement 70 in den Ausnehmungen 61 gehalten. Für jede Magnetbaugruppe 62 ist dabei ein als runde Tellerfeder ausgebildetes Federelement 70 vorgesehen, das über das jeweilige Druckstück 65 die Magnetbaugruppe 62 in der Ausnehmung 61 in einer axialen Richtung, das heisst in Richtung der Längsachse der Ausnehmung 61 und der Magnetbaugruppe 62 verspannt. Die beiden Federelemente 70 sind dabei einstückig miteinander ausgebildet und über einen Figur 3 ersichtlichen Steg 71 miteinander verbunden. Die Federelemente 70 sind in axialer Richtung gebogen, um die erforderliche Vorspannung zu erzeugen. An den Federelementen 70 sind ausserdem Halteelemente einstückig angeformt, die eine Fixierung der Federelemente 70 am Zwischenkörper 36 ermöglichen und die nachfolgend näher erläutert werden. An einem der Federelemente 70 ist ein Halteelement 72 in Form eines Hakens angeformt. Der Haken 72 steht vom Federelement 70 etwa radial nach aussen ab und ist an seinem freien Ende u-förmig nach innen gebogen. Der Haken 72 ist vorzugsweise federnd ausgebildet und greift zumindest mittelbar am Zwischenkörper 36 an. In den Zwischenkörper 36 ist in dessen dem Pumpenkörper 18 zugewandter Stirnseite ein Stift 74 eingepresst, der zumindest annähernd parallel zu den Längsachsen der Ausnehmungen 61 verläuft. Der Haken 72 des Federelements 70 ist am Stift 74 eingehakt und umgreift diesen auf dessen aus dem Zwischenkörper 36 herausragenden Teil. Alternativ kann der Haken 72 auf den Stift 74 auch aufgepresst sein. Am anderen Federelement 70 ist ein weiteres Halteelement einstückig angeformt, das durch zwei in Umfangsrichtung zueinander versetzte Nasen 75 gebildet ist, die zumindest mittelbar den Zwischenkörper 36 umgreifen. In den Zwischenkörper 36 ist dabei ein weiterer Stift 76 eingepresst, den die Nasen 75 seitlich umgreifen. In der dem Pumpenkörper 18 zugewandten Stirnseite des Zwischenkörpers 36 sind Vertiefungen für die Halteelemente 72 und 75 sowie für den die beiden Federelemente 70 verbindenden Steg 71 eingebracht, so dass diese nicht über die Stirnseite des Zwischenkörpers 36 hinausragen.In a first embodiment shown in Figures 2 to 4, the magnet assemblies 62 of the two solenoid valves 56,60 held by a respective spring element 70 in the recesses 61. For each magnet assembly 62, a spring element 70 designed as a round disk spring is provided, which clamps the magnet assembly 62 in the recess 61 in an axial direction, that is, in the direction of the longitudinal axis of the recess 61 and the magnet assembly 62 via the respective pressure piece 65. The two spring elements 70 are integrally formed with each other and connected via a Figure 3 apparent web 71 to each other. The spring elements 70 are bent in the axial direction to produce the required preload. On the spring elements 70 also holding elements are integrally formed, which allow a fixation of the spring elements 70 on the intermediate body 36 and are explained in more detail below. On one of the spring elements 70, a holding element 72 is formed in the form of a hook. The hook 72 projects from the spring element 70 approximately radially outwards and is bent at its free end in a U-shape inwards. The hook 72 is preferably resilient and engages at least indirectly on the intermediate body 36. In the intermediate body 36 is in its pump body 18 facing the end face a pin 74 is pressed, which extends at least approximately parallel to the longitudinal axes of the recesses 61. The hook 72 of Spring element 70 is hooked on the pin 74 and surrounds this on its protruding from the intermediate body 36 part. Alternatively, the hook 72 may be pressed onto the pin 74 as well. On the other spring element 70, a further holding element is integrally formed, which is formed by two mutually offset in the circumferential direction lugs 75 which engage around at least indirectly the intermediate body 36. In the intermediate body 36 while another pin 76 is pressed, the embrace the lugs 75 side. In the pump body 18 facing the end face of the intermediate body 36 recesses for the holding elements 72 and 75 and for the two spring elements 70 connecting web 71 are introduced so that they do not protrude beyond the end face of the intermediate body 36.

Beim Einsetzen der Federelemente 70 in die Ausnehmungen 61 umgreift der Haken 72 den Stift 74 oder wird auf den Stift 74 aufgepresst und die Nasen 75 umgreifen den Stift 76, wodurch sich eine Klemmverbindung der Federelemente 70 mit den Stiften 74,76 ergibt, so dass diese nicht mehr aus dem Zwischenkörper 36 herausfallen können. Durch die Federelemente 70 werden somit die Magnetbaugruppen 62 der Magnetventile 56,60 im Zwischenkörper 36 derart fixiert, dass auch diese nicht herausfallen können. Es ist damit eine Funktionsprüfung der in die Ausnehmungen 61 des Zwischenkörpers 36 eingesetzten Magnetbaugruppen 62 der Magnetventile 56,60 ermöglicht, ohne dass die Gefahr des Herausfallens der Magnetbaugruppen 62 besteht. Die in den Zwischenkörper 36 eingesetzten Magnetbaugruppen 62 sind durch die Federelemente 70 auch bei einem nachfolgenden Transport vor dem endgültigen Zusammenbau der Kraftstoffeinspritzeinrichtung gegen Herausfallen gesichert. Beim weiteren Zusammenbau der Kraftstoffeinspritzeinrichtung werden der Pumpenkörper 18 und der Ventilkörper 30 mit dem Zwischenkörper 36 zusammengefügt, wobei der Pumpenkörper 18 ein Deckelteil bildet, durch das die Federelemente 70 axial zusammengedrückt werden und über diese die Magnetbaugruppen 62 in den Ausnehmungen 61 des Zwischenkörpers 36 verspannt und somit spielfrei fixiert werden.When inserting the spring elements 70 in the recesses 61 of the hook 72 engages around the pin 74 or is pressed onto the pin 74 and the lugs 75 engage around the pin 76, whereby a clamping connection of the spring elements 70 results with the pins 74,76, so that this can no longer fall out of the intermediate body 36. By the spring elements 70 thus the magnetic assemblies 62 of the solenoid valves 56,60 are fixed in the intermediate body 36 such that they can not fall out. It is thus a functional test of the inserted into the recesses 61 of the intermediate body 36 magnetic assemblies 62 of the solenoid valves 56,60 allows without the risk of falling out of the magnetic assemblies 62 is. The magnetic assemblies 62 inserted into the intermediate body 36 are secured against falling out by the spring members 70 even during subsequent transport prior to final assembly of the fuel injector. Upon further assembly of the fuel injector, the pump body 18 and the valve body 30 are assembled with the intermediate body 36, the pump body 18 forming a lid portion through which the spring members 70 axially be compressed and clamped over these the magnetic assemblies 62 in the recesses 61 of the intermediate body 36 and thus fixed without play.

In den Figuren 5 und 6 ist das Federelement 170 gemäß einem zweiten Ausführungsbeispiel dargestellt. Hierbei ist nur ein Federelement 170 für eines der Magnetventile 56,60 vorgesehen. Es besteht hierbei die Möglichkeit, dass nur das erste Magnetventil 56 und ein Federelement 170 für dieses vorhanden ist oder dass beide Magnetventile 56,60 und jeweils ein separates Federelement 170 für dieses vorhanden ist. Das Federelement 170 ist als Tellerfeder mit kreisförmigem Querschnitt ausgebildet und an diesem ist einstückig ein dieses umgebendes Halteelement 172 in Form eines Sicherungsrings angeformt. Der Sicherungsring 172 ist über einen etwa radial verlaufenden Steg 171 am Federelement 170 angeformt. Der Sicherungsring 172 ist radial elastisch verformbar ausgebildet. Die Ausnehmung 161 im Zwischenkörper 136, in die die Magnetbaugruppe 62 eingesetzt ist, weist nahe ihrem der Stirnseite des Zwischenkörpers 136 zugewandten Ende in ihrem Umfang eine eine Hinterschneidung bildende Querschnittserweiterung 174 auf, die durch eine Ringnut, eine Einsenkung oder eine Bohrung gebildet sein kann, in der der Sicherungsring 172 radial nach aussen einrastbar ist. Der Durchmesser des Sicherungsring 172 in entspanntem Zustand ist dabei etwas grösser als der Durchmesser der Ausnehmung 161, wobei beim Einsetzen des Federelements 170 in die Ausnehmung 161 der Sicherungsring 172 radial elastisch zusammengedrückt wird und in der Endposition des Federelements 170 sich nach aussen entspannt und in der Ringnut 174 einrastet. Hierdurch ist das Federelement 170 am Zwischenkörper 136 fixiert und über dieses die Magnetbaugruppe 62 gegen Herausfallen im Zwischenkörper 136 gesichert. Beim Zusammenfügen des Pumpenkörpers 18 als Deckelteil mit dem Zwischenkörper 136 wird das Federelement 170 in axialer Richtung zusammengedrückt und hierdurch die Magnetbaugruppe 62 spielfrei im Zwischenkörper 136 gehalten.In Figures 5 and 6, the spring element 170 is shown according to a second embodiment. In this case, only one spring element 170 is provided for one of the solenoid valves 56, 60. There is the possibility that only the first solenoid valve 56 and a spring element 170 is present for this or that both solenoid valves 56,60 and each have a separate spring element 170 for this is present. The spring element 170 is designed as a disc spring with a circular cross-section and integrally formed thereon is a surrounding retaining element 172 in the form of a securing ring. The securing ring 172 is integrally formed on the spring element 170 via an approximately radially extending web 171. The locking ring 172 is radially elastically deformable. The recess 161 in the intermediate body 136, in which the magnet assembly 62 is inserted, has near its the end face of the intermediate body 136 end facing in its periphery an undercut forming cross-sectional enlargement 174, which may be formed by an annular groove, a depression or a bore, in which the retaining ring 172 can be latched radially outwards. The diameter of the locking ring 172 in the relaxed state is slightly larger than the diameter of the recess 161, wherein the insertion of the spring member 170 into the recess 161 of the locking ring 172 is radially elastically compressed and relaxed in the end position of the spring member 170 to the outside and in the Ring groove 174 engages. As a result, the spring element 170 is fixed on the intermediate body 136 and secured by this the magnetic assembly 62 against falling out in the intermediate body 136. When assembling the pump body 18 as a lid part with the intermediate body 136, the spring element 170 in the axial direction compressed and thereby held the magnet assembly 62 backlash in the intermediate body 136.

Claims (10)

  1. Fuel injection device for an internal combustion engine, having at least one solenoid valve (56, 60) for controlling the injection of fuel, which solenoid valve (56, 60) is arranged in a housing part (36; 136) and has a magnet assembly (62) with a magnet coil (63) and a magnet armature (64), which magnet assembly (62) is inserted into a recess (61) of the housing part (36; 136), having a cover part (18) which can be joined to the housing part (36; 136) and by means of which the magnet assembly (62) is fixed in the housing part (36; 136), characterized in that a spring element (70; 170) is arranged between the cover part (18) and the magnet assembly (62), by means of which spring element (70; 170) the magnet assembly (62) is clamped in the housing part (36; 136), and in that at least one retaining element (72, 74; 172) is integrally formed in a unipartite fashion on the spring element (70; 170), by means of which retaining element (72, 74; 172) the spring element (70; 170) is held on the housing part (36; 136) and holds the magnet assembly (62) in the recess (61) of the housing part (36; 136) before the cover part (18) is joined to the housing part (36; 136).
  2. Fuel injection device according to Claim 1, characterized in that the spring element (70; 170) is embodied as a plate spring.
  3. Fuel injection device according to Claim 1 or 2, characterized in that the at least one retaining element (172) is embodied as a radially elastic securing ring which surrounds the spring element (170) and can be latched onto the housing part (136).
  4. Fuel injection device according to Claim 3, characterized in that an undercut (174), into which the securing ring (172) can be latched, is formed at the periphery of the recess (161) in the housing part (136).
  5. Fuel injection device according to Claim 1 or 2, characterized in that the at least one retaining element (72) is embodied as a hook which projects preferably at least approximately radially outwards from the spring element (70) and can be hooked at least indirectly into the housing part (36).
  6. Fuel injection device according to Claim 5, characterized in that the hook (72) can be hooked into, or can be pressed onto, a pin (74) which is fastened to the housing part (36).
  7. Fuel injection device according to one of Claims 1, 2, 5 or 6, characterized in that the at least one retaining element (75) is formed by two lugs which are arranged at a distance from one another, project preferably at least approximately radially outwards from the periphery of the spring element (70) and preferably engage around, or can be pressed onto, a pin which is fastened to the housing part (36).
  8. Fuel injection device according to Claim 5 or 6 and Claim 7, characterized in that a retaining element formed by the hook (72) and a retaining element formed by the lugs (75) are each integrally formed on the spring element (70), and in that the retaining elements (72, 75) are arranged on the spring element (70) so as to be offset relative to one another in the peripheral direction.
  9. Fuel injection device according to Claim 8, characterized in that two solenoid valves (56, 60) are provided, each of which has a magnet assembly (62) which is inserted into a recess (61) in the housing part (36), in that each magnet assembly (62) is assigned a spring element (70) and in that the two spring elements (70) are formed in one piece with one another.
  10. Fuel injection device according to Claim 9, characterized in that a retaining element formed by the hook (72) is integrally formed on one spring element (70), and a retaining element formed by the lugs (75) is integrally formed on the other spring element (70).
EP03773529A 2003-02-06 2003-10-14 Fuel injection device for an internal combustion engine Expired - Lifetime EP1592880B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10304742 2003-02-06
DE10304742A DE10304742A1 (en) 2003-02-06 2003-02-06 Fuel injection device for an internal combustion engine
PCT/DE2003/003415 WO2004070194A1 (en) 2003-02-06 2003-10-14 Fuel injection device for an internal combustion engine

Publications (2)

Publication Number Publication Date
EP1592880A1 EP1592880A1 (en) 2005-11-09
EP1592880B1 true EP1592880B1 (en) 2007-03-07

Family

ID=32730798

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03773529A Expired - Lifetime EP1592880B1 (en) 2003-02-06 2003-10-14 Fuel injection device for an internal combustion engine

Country Status (5)

Country Link
US (1) US7143955B2 (en)
EP (1) EP1592880B1 (en)
JP (1) JP4555688B2 (en)
DE (2) DE10304742A1 (en)
WO (1) WO2004070194A1 (en)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101048589B (en) * 2004-09-28 2010-05-26 电动内燃机公司 Fuel injector with valve opening pressure loss resisting valve spring for engine with emission reaching standard
ATE494477T1 (en) * 2005-10-25 2011-01-15 Crt Common Rail Technologies Ag INJECTOR FOR A FUEL INJECTION SYSTEM AND FUEL INJECTION SYSTEM WITH SUCH AN INJECTOR
DE102009045262B4 (en) * 2009-10-01 2019-03-28 Seg Automotive Germany Gmbh Relay with pneumatic damping
DE102010034411B4 (en) * 2010-08-14 2018-10-11 Audi Ag Internal combustion engine with injection valve
WO2017102173A1 (en) * 2015-12-14 2017-06-22 Robert Bosch Gmbh A fuel injector comprising magnetic valve mechanism with rotary

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4382242A (en) * 1981-12-21 1983-05-03 General Motors Corporation Solenoid operated electrical switch
DE4023828A1 (en) 1990-07-27 1992-01-30 Bosch Gmbh Robert Adjusting EM valve for fuel injection - adjusting current without requiring access to return spring by changing magnetic characteristics of inner pole
US5339063A (en) * 1993-10-12 1994-08-16 Skf U.S.A., Inc. Solenoid stator assembly for electronically actuated fuel injector
JPH07279793A (en) * 1994-04-01 1995-10-27 Aisan Ind Co Ltd Electromagnetic fuel injection valve
JPH08177679A (en) * 1994-12-21 1996-07-12 Nippondenso Co Ltd Fuel injection valve
IT1276503B1 (en) * 1995-07-14 1997-10-31 Elasis Sistema Ricerca Fiat IMPROVEMENTS TO AN ELECTROMAGNETICALLY OPERATED DOSING VALVE, FOR A FUEL INJECTOR.
JP2811062B2 (en) * 1996-03-18 1998-10-15 株式会社ケーヒン Side feed type fuel injection valve
JP3774976B2 (en) * 1997-03-05 2006-05-17 株式会社日本自動車部品総合研究所 Accumulated fuel injection system
US6073862A (en) * 1998-09-16 2000-06-13 Westport Research Inc. Gaseous and liquid fuel injector
DE19849210A1 (en) * 1998-10-26 2000-04-27 Bosch Gmbh Robert Fuel injection valve for internal combustion engine fuel injection system has armature movable between two stops, damping spring arranged between second stop and armature
DE19950761A1 (en) * 1999-10-21 2001-04-26 Bosch Gmbh Robert Fuel injection valve has supporting ring between elastomeric ring and armature that supports elastomeric ring axially near opening of fuel channel in armature and radially on shoulder
JP3631413B2 (en) 2000-04-27 2005-03-23 株式会社デンソー Solenoid valve and fuel injection device using the same
DE10050238A1 (en) * 2000-10-11 2002-04-25 Bosch Gmbh Robert Control module for fluid control in injection systems has electromagnetically actuated control valves; magnetic coils are accommodated in apertures in valve body or in insert elements
DE10056038A1 (en) * 2000-11-11 2002-05-16 Bosch Gmbh Robert Fuel injection system has seals ring-grooved for movement at seal support endfaces plus upstream safety ring to reinforce operational sealing.
ITTO20001229A1 (en) * 2000-12-29 2002-06-29 Fiat Ricerche ASSEMBLY SYSTEM OF A FUEL INJECTOR FOR AN INTERNAL COMBUSTION ENGINE.
US6611186B2 (en) * 2001-02-26 2003-08-26 Woodward Governor Company Solenoid having an elastomeric retaining device and method of manufacturing same without potting

Also Published As

Publication number Publication date
JP2006514193A (en) 2006-04-27
US7143955B2 (en) 2006-12-05
EP1592880A1 (en) 2005-11-09
US20060219803A1 (en) 2006-10-05
DE50306777D1 (en) 2007-04-19
WO2004070194A1 (en) 2004-08-19
DE10304742A1 (en) 2004-08-19
JP4555688B2 (en) 2010-10-06

Similar Documents

Publication Publication Date Title
DE102013220593A1 (en) Electromagnetically controllable suction valve
DE112006003076T5 (en) Fuel system with multiple sources of variable pressure injection
DE102007001363A1 (en) Injector for injecting fuel into combustion chambers of internal combustion engines
DE10320592A1 (en) Feed pump, in particular high-pressure fuel pump for an internal combustion engine
WO2017144185A1 (en) Electromagnetically actuatable inlet valve and high-pressure pump comprising an inlet valve
DE102009000183A1 (en) Fuel injection valve for fuel injection systems of internal combustion engines, particularly for direct injection of fuel in combustion chamber of internal combustion engine, has actuator and flow choke provided in fuel supply
WO2009043717A1 (en) Control valve for a fuel injector
EP2310662B1 (en) Fuel injector
EP1592880B1 (en) Fuel injection device for an internal combustion engine
DE102016206996B3 (en) Switching valve for a fuel injection system and high-pressure fuel pump
DE102016208956A1 (en) Electromagnetically operated suction valve and high-pressure fuel pump
DE102007001550A1 (en) Injector for injecting fuel
DE102016226135A1 (en) Fuel injector
EP2466108A1 (en) Fuel injector valve
EP3387247B1 (en) Electromagnetically actuatable inlet valve and high-pressure pump having an inlet valve
DE102020208768A1 (en) Fuel distributor strip for an injection system and injection system for mixture-compressing, spark-ignited internal combustion engines
DE102007034319A1 (en) injector
DE102018209399A1 (en) Check valve, high pressure component and high pressure fuel pump
EP1831538B1 (en) Fuel-injection unit for an internal combustion engine
DE102016214884A1 (en) Electromagnetically operated suction valve and high-pressure fuel pump
DE102021213785A1 (en) Fuel injector and method for its manufacture
DE102011076259A1 (en) Fuel metering device for fuel injection system used in internal combustion engine, has inlet opening and outlet separated by sealing element applied circumferentially on outer side of sleeve whose outer side is enclosed by housing
EP4081707A1 (en) High-pressure fuel pump
DE102020215621A1 (en) fuel injector
DE102020215218A1 (en) fuel injector

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20050906

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IT LI LU MC NL PT RO SE SI SK TR

RBV Designated contracting states (corrected)

Designated state(s): DE FR GB

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REF Corresponds to:

Ref document number: 50306777

Country of ref document: DE

Date of ref document: 20070419

Kind code of ref document: P

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 20070523

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20071210

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 13

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 14

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 15

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 16

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20221020

Year of fee payment: 20

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20221024

Year of fee payment: 20

Ref country code: DE

Payment date: 20221215

Year of fee payment: 20

REG Reference to a national code

Ref country code: DE

Ref legal event code: R071

Ref document number: 50306777

Country of ref document: DE

REG Reference to a national code

Ref country code: GB

Ref legal event code: PE20

Expiry date: 20231013

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF EXPIRATION OF PROTECTION

Effective date: 20231013

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF EXPIRATION OF PROTECTION

Effective date: 20231013