EP2630361B1 - Fuel injector - Google Patents

Fuel injector Download PDF

Info

Publication number
EP2630361B1
EP2630361B1 EP11764555.6A EP11764555A EP2630361B1 EP 2630361 B1 EP2630361 B1 EP 2630361B1 EP 11764555 A EP11764555 A EP 11764555A EP 2630361 B1 EP2630361 B1 EP 2630361B1
Authority
EP
European Patent Office
Prior art keywords
pressure
fuel
guide bore
pressure chamber
fuel injector
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.)
Not-in-force
Application number
EP11764555.6A
Other languages
German (de)
French (fr)
Other versions
EP2630361A1 (en
Inventor
Peter Wannenwetsch
Luiz-Alexandre Colodel
Martin Bechle
Heinz-Bernd Haiser
Bernd Berghaenel
Michael Domhan
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 EP2630361A1 publication Critical patent/EP2630361A1/en
Application granted granted Critical
Publication of EP2630361B1 publication Critical patent/EP2630361B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
    • F02M61/12—Other injectors with elongated valve bodies, i.e. of needle-valve type characterised by the provision of guiding or centring means for 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/06—Fuel-injection apparatus having means for preventing coking, e.g. of fuel injector discharge orifices or valve needles
    • 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
    • F02M2200/16—Sealing of fuel injection apparatus not otherwise provided for

Definitions

  • the invention relates to a fuel injector according to the preamble of the independent claims.
  • Such a fuel injector is already well known from the prior art and is used for example for injecting fuel into a combustion chamber of a self-igniting internal combustion engine.
  • fuel injection systems which are also referred to as “common rail systems", each have a separate fuel injector for each cylinder or combustion chamber.
  • the fuel injector in this case has, for example, a valve needle arranged in an injector housing, which is coupled to a magnet armature which moves the valve needle up and down in the longitudinal direction of the injector housing in order to open or close passage openings for the fuel formed on the combustion chamber side of the injector housing , It is essential here that the valve needle is arranged in a guide bore of the injector housing which separates a first pressure chamber facing the passage openings with a relatively high pressure, for example a pressure of more than 1500 bar, from a second pressure chamber in which the magnet armature is arranged the second pressure chamber, a relatively low pressure prevails.
  • a relatively high pressure for example a pressure of more than 1500 bar
  • a fuel injection valve is known, the guide bore for guiding a valve needle a high-pressure chamber, is arranged in the fuel, separated from a second pressure chamber, which is supplied by means of a lubricant pump with pressurized lubricant.
  • the valve needle has an annular groove, which is pressure-relieved via a return channel. Both leakage fluid from the high-pressure chamber of the injector housing, as well as lubricant in a lubricant return container passes through the return channel.
  • the present invention seeks to further develop a fuel injector according to the preamble of the independent claims such that the tendency to deposits of fuel in the guide gap is reduced in particular between the valve needle and its associated guide bore. This object is achieved with a fuel injector having the features of the independent claims.
  • the invention is based on the idea of arranging or forming at least one outflow channel in the region of the guide bore in which a lower pressure prevails than in the pressure chamber with the higher pressure.
  • the outflow channel opens on the side remote from the guide bore in a fuel return of the injector.
  • the leakage losses or the flow through the guide bore between the discharge channel and the pressure chamber at low pressure can be further reduced if the element, in particular the valve needle, in the region of the outflow channel has a radially encircling annular groove. As a result, fuel flowing over the entire circumference of the guide gap can be removed via the outflow channel.
  • the at least one outflow channel is arranged on the side of the guide bore facing the pressure chamber with the higher pressure.
  • a plurality of outflow channels are provided, which are arranged axially spaced from each other on the side facing the pressure chamber with the higher pressure side of the guide bore.
  • the guide bore in the guide region has a conical shape, such that the guide gap increases in the hydraulic pressure-free state of the two pressure chambers in the direction of the pressure chamber with lower pressure.
  • a preferred use of the fuel injector are those fuel injectors designed as solenoid valves, i. that the valve needle is connected to a magnet armature. This is because the magnet armatures of such fuel injectors are usually arranged in a pressure chamber with a relatively low pressure in order to construct the magnet armature structurally relatively easily.
  • the diameter of the element (valve needle) or the diameter of the guide bore results in an arithmetical guide gap when the element is not yet mounted in the injector housing, which is less than a desired guide gap, and that when mounted in the injector housing due to components of the fuel injector, a force is generated on the guide bore, which increases the diameter of the guide bore such that adjusts the desired guide gap.
  • Fig. 1 is a portion of a fuel injector 1 according to the prior art shown.
  • the fuel injector 1 is in particular part of a so-called common-rail system of a self-igniting internal combustion engine, wherein the injection system may have an operating pressure of more than 1500bar.
  • the fuel injector 1 has an injector housing 11 or an insert arranged in an injector housing 11, which is of substantially elongated or sleeve-shaped design.
  • an injector housing 11 In the injector 11, a plurality of areas having recess 12 is formed, in which a corresponding to the double arrow 13 in a longitudinal axis 14 up and down movable valve needle 15 is arranged.
  • the valve needle 15 shown serves for metering fuel via passage openings, not shown in the figure, in the injector housing 11 below the valve needle 15 Fig. 1 illustrated, closed state of the fuel injector 1, in which no fuel is discharged, while sitting the lower end of the valve needle 15th on a conically encircling seat edge 16 of the injector 11 and forms a sealing seat 17 from.
  • the recess 12 forms above the seat edge 16 of an annular high-pressure chamber 20, which is supplied via an inflow channel 21 with under high pressure, in particular the mentioned operating pressure fuel.
  • the high-pressure chamber 20 merges on the side facing away from the seat edge 16 into a guide bore 22, in which the valve needle 15 is guided over a radially formed guide gap 23.
  • the recess 12 forms a magnet armature space 25, which is connected via a return flow channel 26, for example with a fuel return on the injector housing 11.
  • the seat edge 16 opposite end of the valve needle 15 is connected to a magnet armature 28 which is arranged in the armature space 25.
  • the magnet armature 28 is acted upon by the spring force of a compression spring 29 in the direction of the sealing seat 17.
  • the armature 28 cooperates with a magnetic coil 30 and a magnetic core 31, so that when energizing the solenoid 30, the armature 28 and thus the valve needle 15 is pulled in the direction of the magnetic core 31, and consequently the valve needle 15 from its sealing seat 17th takes off.
  • the pressure-relieved via the return passage 26 magnet armature space 25 forms a second pressure chamber, which has a lower pressure compared to the first pressure chamber formed as a high-pressure chamber 20.
  • the pressure in the guide bore 22 decreases in the direction of the magnet armature space 25.
  • the pressure drop in the Fig. 1 represented symbolically by the arrows 32. The pressure drop has the consequence that the guide gap 23 between the valve needle 15 and the guide bore 22 continuously reduced by the high-pressure chamber 20 in the direction of the armature space 23.
  • a fuel injector 10 according to the invention is shown, in which this in a modification of the fuel injector 1 according to the prior art according to the Fig. 1 an additional outflow channel 35 which is preferably connected to the fuel return in the injector 11.
  • the outflow channel 35 is arranged or formed in the region of the guide bore 22 just above the high-pressure chamber 20.
  • the valve needle 15 has a radially encircling annular groove 36 in the region of the outflow channel 35.
  • a further outflow channel 38 is provided or formed, which then preferably cooperates with an additional annular groove 39 on the valve needle 15.
  • the additional outflow channel 38 is preferably arranged or formed relatively close above the outflow channel 35, as can be seen from the dash-dotted representation of FIG Fig. 2 is shown for expression.
  • a further embodiment of a non-inventive fuel injector 10a is shown. It is essential here that the guide bore 22a formed in the injector housing 11a is conical when the guide bore 22a is finished.
  • the diameter of the guide bore 22a on the high-pressure chamber 20 side facing lower than on the magnet armature 25 side facing. Due to the reducing from the high-pressure chamber 20 in the direction of the armature space 25 hydraulic pressure on the guide bore 22a is corresponding to the Fig. 4
  • the guide gap 23a or the guide bore 22a is deformed in such a way that a virtually constant, annular guide gap 23a adjusts over almost the entire guide length of the valve needle 15a in the guide bore 22a.
  • FIGS. 5 and 6 a further non-inventive embodiment is shown. It has been found (depending on the constructive design of a fuel injector 10b) that during assembly of the individual parts of the fuel injector 10b, in particular the injector housing 11b in the region of the guide bore 22b by acting on both sides of the injector 11b by components 42, 43 axial forces, by the arrows 41 in the Fig. 6 are shown in the diameter D is increased. This also increases a guide gap 23b between the valve needle 15b and the guide bore 22b. According to the invention, it is now according to the Fig.
  • the diameter d of the valve needle 15b and the diameter D of the guide bore 22b is selected such that when inserting the valve needle 15b in the guide bore 22b during installation a minimum guide gap 23b sets.
  • This guide gap 23b which is formed in the extreme case as a zero clearance, is designed to be too small for the movement of the valve needle 15b.
  • only symbolically represented components 42, 43 on the injector 11 b this deformed so that the diameter D of the guide bore 22b increases such that the now adjusting guide gap 23b corresponds to a desired guide gap 23b in a desired manner.
  • a further non-inventive embodiment is shown. It is provided here that the injector housing 11c is already subjected to such an axial force A during the machining or forming of the guide bore 22c by one or more additional elements 44, 45, that of the mechanical load when the fuel injector 10c is mounted by its components 42, 43 equivalent. This means that the guide bore 22c is manufactured or formed with a nominal diameter D in a preloaded state of the injector housing 11c, so that after assembly of the components 42, 43 corresponding to the Fig. 8 set the desired target guide gap 23c.
  • the fuel injectors 10, 10a to 10c described so far can be modified or modified in many ways without departing from the spirit of the invention.
  • the invention is not limited to fuel injectors 10, 10a to 10c, which are designed as solenoid valves. Rather, can be provided as an actuator for the valve needle 15 and a piezo drive or the like. Also, it is not necessary that, as shown, the armature 28 is directly connected or coupled to the valve needle 15. Rather, instead of the valve needle 15, another element can be provided, which is arranged or guided in a guide bore 22, wherein on the two sides of the guide bore 23 strongly different pressures prevail.

Description

Stand der TechnikState of the art

Die Erfindung betrifft einen Kraftstoffinjektor nach dem Oberbegriff der unabhängigen Ansprüche.The invention relates to a fuel injector according to the preamble of the independent claims.

Ein derartiger Kraftstoffinjektor ist aus dem Stand der Technik bereits allgemein bekannt und dient beispielsweise zum Einspritzen von Kraftstoff in einen Brennraum einer selbstzündenden Brennkraftmaschine. Hierbei besitzen derartige Kraftstoffeinspritzsysteme, die auch als "Common-Rail-Systeme" bezeichnet werden, für jeden Zylinder bzw. Brennraum jeweils einen separaten Kraftstoffinjektor. Der Kraftstoffinjektor weist hierbei beispielsweise eine in einem Injektorgehäuse angeordnete Ventilnadel auf, die mit einem Magnetanker gekoppelt ist, der die Ventilnadel in Längsrichtung des Injektorgehäuses auf- und abbewegt, um damit auf der Brennraumseite des Injektorgehäuses ausgebildete Durchlassöffnungen für den Kraftstoff zu öffnen bzw. zu verschließen. Wesentlich hierbei ist, dass die Ventilnadel in einer Führungsbohrung des Injektorgehäuses angeordnet ist, die einen den Durchlassöffnungen zugewandten ersten Druckraum mit relativ hohem Druck, beispielsweise einem Druck von mehr als 1500bar, von einem zweiten Druckraum trennt, in dem der Magnetanker angeordnet ist, wobei in dem zweiten Druckraum ein relativ geringer Druck herrscht. Aufgrund der großen Druckunterschiede während des Betriebs des Kraftstoffinjektors strömt dabei Kraftstoff von dem ersten Druckraum mit relativ hohem Druck über die Führungsbohrung in den zweiten Druckraum mit relativ geringem Druck, von wo der Kraftstoff in der Regel einem Kraftstoffrücklauf zugeführt wird. Nachteilig dabei ist, dass die durch das Abströmen des Kraftstoffs aus dem Druckraum mit hohem Druck auftretenden Leckageverluste zum einen in den Gesamtwirkungsgrad des Kraftstoffinjektors eingehen und somit diesen negativ beeinflussen, und zum anderen, dass es bei der Durchströmung des Führungsspaltes zwischen der Ventilnadel und der Führungsbohrung zu Ablagerungen des Kraftstoffes in dem Führungsspalt kommen kann, die die Beweglichkeit der Ventilnadel einschränken, und im Extremfall zum Blockieren der Ventilnadel führen können. Dabei hat es sich herausgestellt, dass die Tendenz zu Ablagerungen von Kraftstoffbestandteilen desto geringer wird, desto geringer der Führungsspalt zwischen der Ventilnadel und der Führungsbohrung ausgebildet ist bzw. desto geringer die Durchflussmenge von Kraftstoff durch den Führungsspalt ist.Such a fuel injector is already well known from the prior art and is used for example for injecting fuel into a combustion chamber of a self-igniting internal combustion engine. In this case, such fuel injection systems, which are also referred to as "common rail systems", each have a separate fuel injector for each cylinder or combustion chamber. The fuel injector in this case has, for example, a valve needle arranged in an injector housing, which is coupled to a magnet armature which moves the valve needle up and down in the longitudinal direction of the injector housing in order to open or close passage openings for the fuel formed on the combustion chamber side of the injector housing , It is essential here that the valve needle is arranged in a guide bore of the injector housing which separates a first pressure chamber facing the passage openings with a relatively high pressure, for example a pressure of more than 1500 bar, from a second pressure chamber in which the magnet armature is arranged the second pressure chamber, a relatively low pressure prevails. Due to the large pressure differences during operation of the fuel injector while flowing fuel from the first pressure chamber at a relatively high pressure via the guide bore in the second pressure chamber at a relatively low pressure, from where the fuel is usually supplied to a fuel return. The disadvantage here is that the leakage losses occurring due to the outflow of fuel from the pressure chamber at high pressure on the one hand in the overall efficiency of the fuel injector and thus adversely affect this, and on the other hand, that during the flow through the guide gap between the valve needle and the guide bore deposits of the fuel can occur in the guide gap, which limit the mobility of the valve needle, and can lead in extreme cases to block the valve needle. It has been found that the tendency for deposits of fuel components, the lower the less the guide gap between the valve needle and the guide bore is formed or the lower the flow rate of fuel through the guide gap.

Aus der US 4,412,657 ist ein Kraftstoffeinspritzventil bekannt, dessen Führungsbohrung zur Führung einer Ventilnadel einen Hochdruckraum, in dem Kraftstoff angeordnet ist, von einem zweiten Druckraum getrennt, der mittels einer Schmiermittelpumpe mit unter Druck stehendem Schmiermittel versorgt wird. Die Ventilnadel weist eine Ringnut auf, die über einen Rücklaufkanal druckentlastet ist. Über den Rücklaufkanal gelangt sowohl Leckagekraftstoff aus dem Hochdruckraum des Injektorgehäuses, als auch Schmiermittel in einen Schmiermittelrücklaufbehälter.From the US 4,412,657 a fuel injection valve is known, the guide bore for guiding a valve needle a high-pressure chamber, is arranged in the fuel, separated from a second pressure chamber, which is supplied by means of a lubricant pump with pressurized lubricant. The valve needle has an annular groove, which is pressure-relieved via a return channel. Both leakage fluid from the high-pressure chamber of the injector housing, as well as lubricant in a lubricant return container passes through the return channel.

Offenbarung der ErfindungDisclosure of the invention

Ausgehend von dem dargestellten Stand der Technik liegt der Erfindung die Aufgabe zugrunde, einen Kraftstoffinjektor nach dem Oberbegriff der unabhängigen Ansprüche derart weiterzubilden, dass die Tendenz zu Ablagerungen von Kraftstoff im Führungsspalt insbesondere zwischen der Ventilnadel und dessen zugeordneter Führungsbohrung reduziert wird. Diese Aufgabe wird bei einem Kraftstoffinjektor mit den Merkmalen der unabhängigen Ansprüche gelöst.Based on the illustrated prior art, the present invention seeks to further develop a fuel injector according to the preamble of the independent claims such that the tendency to deposits of fuel in the guide gap is reduced in particular between the valve needle and its associated guide bore. This object is achieved with a fuel injector having the features of the independent claims.

Der Erfindung liegt dabei bei einer ersten Ausgestaltung der Erfindung die Idee zugrunde, im Bereich der Führungsbohrung wenigstens einen Abströmkanal anzuordnen bzw. auszubilden, in dem ein geringerer Druck herrscht als in dem Druckraum mit dem höheren Druck. Dadurch gelangt Kraftstoff beim Durchströmen des Führungsspaltes von dem Druckraum mit höherem Druck direkt in den Abströmkanal und nicht bis in den Druckraum mit relativ gesehen geringerem Druck. Das bedeutet, dass zwischen dem Abströmkanal und dem Bereich des Druckraums mit geringerem Druck der Führungsspalt gar nicht mehr bzw. nur noch mit einer sehr geringen Durchflussmenge an Kraftstoff durchströmt wird. Dadurch können sich eventuelle Ablagerungen nur noch in dem Bereich zwischen dem Druckraum mit relativ hohem Druck und dem Abströmkanal ausbilden, d.h. über eine relativ geringe Führungslänge der Ventilnadel.In a first embodiment of the invention, the invention is based on the idea of arranging or forming at least one outflow channel in the region of the guide bore in which a lower pressure prevails than in the pressure chamber with the higher pressure. As a result, fuel flows through the guide gap from the pressure chamber with higher pressure directly into the discharge channel and not into the pressure chamber with relatively lower pressure. This means that between the outflow channel and the region of the pressure chamber with lower pressure of the guide gap is no longer flowed through or only with a very small flow rate of fuel. As a result, any deposits can form only in the area between the pressure chamber with a relatively high pressure and the discharge channel, i. over a relatively small guide length of the valve needle.

In einer vorteilhaften Ausgestaltung der ersten Ausführungsform der Erfindung ist es vorgesehen, dass der Abströmkanal auf der der Führungsbohrung abgewandten Seite in einen Kraftstoffrücklauf des Injektorgehäuses mündet. Dadurch wird eine relativ hohe Druckdifferenz zwischen dem Druckraum mit hohem Druck und dem Abströmkanal sichergestellt, so dass der Kraftstoff in der Regel nahezu vollständig über den Abströmkanal abströmt.In an advantageous embodiment of the first embodiment of the invention, it is provided that the outflow channel opens on the side remote from the guide bore in a fuel return of the injector. As a result, a relatively high pressure difference between the pressure chamber with high pressure and Ensured the outflow, so that the fuel usually flows almost completely through the outflow channel.

Die Leckageverluste bzw. die Durchströmung der Führungsbohrung zwischen dem Abströmkanal und dem Druckraum mit geringem Druck lässt sich darüber hinaus verringern, wenn das Element, insbesondere die Ventilnadel, im Bereich des Abströmkanals eine radial umlaufende Ringnut aufweist. Dadurch kann über den gesamten Umfang des Führungsspaltes strömender Kraftstoff über den Abströmkanal abgeführt werden.The leakage losses or the flow through the guide bore between the discharge channel and the pressure chamber at low pressure can be further reduced if the element, in particular the valve needle, in the region of the outflow channel has a radially encircling annular groove. As a result, fuel flowing over the entire circumference of the guide gap can be removed via the outflow channel.

Besonders vorteilhaft ist es weiterhin, wenn der wenigstens eine Abströmkanal auf der dem Druckraum mit dem höheren Druck zugewandten Seite der Führungsbohrung angeordnet ist. Dadurch wird die von Kraftstoff durchströmte Länge der Führungsbohrung reduziert, was eine Verringerung der Tendenz zu Ablagerungen und somit gleichzeitig relativ geringe Bewegungskräfte des Elements bzw. Öffnungs- und Schließkräfte bei einer Ventilnadel, auch beim Vorhandensein von Ablagerungen, zur Folge hat.It is furthermore particularly advantageous if the at least one outflow channel is arranged on the side of the guide bore facing the pressure chamber with the higher pressure. As a result, the fuel-traversed length of the guide bore is reduced, which has a reduction in the tendency to deposits and thus at the same time relatively low movement forces of the element or opening and closing forces in a valve needle, even in the presence of deposits result.

Darüber hinaus kann es vorgesehen sein, dass mehrere Abströmkanäle vorgesehen sind, die axial zueinander beabstandet auf der dem Druckraum mit dem höheren Druck zugewandten Seite der Führungsbohrung angeordnet sind. Dadurch lässt sich die Durchströmmenge des Kraftstoffes in den Druckraum mit dem geringeren Druck weiter reduzieren bzw. minimieren.In addition, it can be provided that a plurality of outflow channels are provided, which are arranged axially spaced from each other on the side facing the pressure chamber with the higher pressure side of the guide bore. As a result, the flow rate of the fuel into the pressure chamber with the lower pressure can be further reduced or minimized.

Bei einer alternativen Ausgestaltung der Erfindung ist es vorgesehen, dass die Führungsbohrung im Führungsbereich eine konische Form aufweist, derart, dass der Führungsspalt im hydraulisch drucklosen Zustand der beiden Druckräume in Richtung des Druckraumes mit geringerem Druck zunimmt. Dies hat während des Betriebs des Kraftstoffinjektors zur Folge, dass infolge des sich in der Führungsbohrung einstellenden hydraulischen Drucks der Führungsspalt in Richtung des Druckraumes mit höherem Druck stärker aufgeweitet wird als im Bereich des Druckraumes mit geringem Druck, so dass sich, im Idealfall, ein möglichst gleichmäßiger, minimierter Führungsspalt über die gesamte Führungslänge des Elementes bzw. der Ventilnadel in der Führungsbohrung einstellt.In an alternative embodiment of the invention, it is provided that the guide bore in the guide region has a conical shape, such that the guide gap increases in the hydraulic pressure-free state of the two pressure chambers in the direction of the pressure chamber with lower pressure. This has the consequence during operation of the fuel injector that due to the adjusting in the guide bore hydraulic pressure of the guide gap in the direction of the pressure chamber with higher pressure is more expanded than in the pressure chamber at low pressure, so that, ideally, as possible uniform, minimized guide gap over the entire guide length of the element or the valve needle in the guide hole sets.

Ein bevorzugter Einsatz des Kraftstoffinjektors sind solche Kraftstoffinjektoren, die als Magnetventile ausgebildet sind, d.h. dass deren Ventilnadel mit einem Magnetanker verbunden ist. Dies deshalb, da die Magnetanker derartiger Kraftstoffinjektoren üblicherweise in einem Druckraum mit relativ geringem Druck angeordnet sind, um den Magnetanker konstruktiv relativ einfach ausbilden zu können.A preferred use of the fuel injector are those fuel injectors designed as solenoid valves, i. that the valve needle is connected to a magnet armature. This is because the magnet armatures of such fuel injectors are usually arranged in a pressure chamber with a relatively low pressure in order to construct the magnet armature structurally relatively easily.

In einer weiteren, alternativen Ausgestaltung der Erfindung, bei der Herstellkosten gegenüber konventioneller Fertigung nicht erhöht werden, ist es vorgesehen, dass der Durchmesser des Elements (Ventilnadel) bzw. der Durchmesser der Führungsbohrung bei noch nicht montiertem Element in dem Injektorgehäuse einen rechnerischen Führungsspalt ergibt, der geringer ist als ein Soll-Führungsspalt, und dass bei in dem Injektorgehäuse montiertem Element aufgrund von Bauteilen des Kraftstoffinjektors eine Kraft auf die Führungsbohrung erzeugt wird, die den Durchmesser der Führungsbohrung derart vergrößert, dass sich der Soll-Führungsspalt einstellt.In a further, alternative embodiment of the invention, in which manufacturing costs are not increased compared to conventional production, it is provided that the diameter of the element (valve needle) or the diameter of the guide bore results in an arithmetical guide gap when the element is not yet mounted in the injector housing, which is less than a desired guide gap, and that when mounted in the injector housing due to components of the fuel injector, a force is generated on the guide bore, which increases the diameter of the guide bore such that adjusts the desired guide gap.

Ergänzend wird erwähnt, dass die Erfindung sämtliche Kombinationen von zumindest zwei von den Ansprüchen, der Beschreibung und/oder den Figuren offenbarten Merkmalen umfasst. Weitere Merkmale und Einzelheiten der Erfindung ergeben sich aus der nachfolgenden Beschreibung bevorzugter Ausführungsbeispiele sowie anhand der Zeichnungen.In addition, it is mentioned that the invention encompasses all combinations of at least two features disclosed by the claims, the description and / or the figures. Further features and details of the invention will become apparent from the following description of preferred embodiments and from the drawings.

Diese zeigt in:

Fig. 1
einen Ausschnitt aus einem Kraftstoffinjektor nach dem Stand der Technik im Längsschnitt,
Fig. 2
einen Ausschnitt bei einer erfindungsgemäßen Ausführungsform des Kraftstoffinjektors mit wenigstens einem Abströmkanal im Längsschnitt,
Fig. 3
einen Teil eines Ventilgehäuses für einen nicht erfindungsgemäßen Kraftstoffinjektor im Längsschnitt,
Fig. 4
den Bereich des Kraftstoffinjektors gemäß Fig. 3 während des Betriebs des Kraftstoffinjektors im Längsschnitt,
Fig. 5 und 6
einen weiteren, nicht erfindungsgemäßen Kraftstoffinjektor vor sowie nach dessen Montage jeweils in vereinfachtem Längsschnitt,
Fig. 7
eine abgewandelte Konfiguration, bei der ein Injektorgehäuse während der Bearbeitung der Führungsbohrung mit Axialkräften beaufschlagt wird im Längsschnitt und
Fig. 8
den Bereich des Injektorgehäuses bei einem Kraftstoffinjektor gemäß Fig. 7 während dessen Betrieb im Längsschnitt.
This shows in:
Fig. 1
a section of a fuel injector according to the prior art in longitudinal section,
Fig. 2
a detail in an embodiment of the fuel injector according to the invention with at least one outflow channel in longitudinal section,
Fig. 3
a part of a valve housing for a non-inventive fuel injector in longitudinal section,
Fig. 4
the area of the fuel injector according to Fig. 3 during operation of the fuel injector in longitudinal section,
FIGS. 5 and 6
a further, not according to the invention fuel injector before and after its assembly in a simplified longitudinal section,
Fig. 7
a modified configuration in which an injector is applied during the machining of the guide bore with axial forces in longitudinal section and
Fig. 8
the area of the injector housing in a fuel injector according to Fig. 7 during its operation in longitudinal section.

Gleiche Bauteile bzw. Bauteile gleicher Funktion sind in den Figuren mit den gleichen Bezugsziffern versehen.The same components or components of the same function are provided in the figures with the same reference numerals.

In der Fig. 1 ist ein Teilbereich eines Kraftstoffinjektors 1 nach dem Stand der Technik dargestellt. Der Kraftstoffinjektor 1 ist hierbei insbesondere Bestandteil eines sogenannten Common-Rail-Systems einer selbstzündenden Brennkraftmaschine, wobei dessen Einspritzsystem einen Betriebsdruck von mehr als 1500bar aufweisen kann.In the Fig. 1 is a portion of a fuel injector 1 according to the prior art shown. The fuel injector 1 is in particular part of a so-called common-rail system of a self-igniting internal combustion engine, wherein the injection system may have an operating pressure of more than 1500bar.

Der Kraftstoffinjektor 1 weist in dem dargestellten Teilbereich ein Injektorgehäuse 11 bzw. ein in einem Injektorgehäuse 11 angeordneten Einsatz auf, das im Wesentlichen länglich bzw. hülsenförmig ausgebildet ist. Im Injektorgehäuse 11 ist eine mehrere Bereiche aufweisende Ausnehmung 12 ausgebildet, in der eine entsprechend des Doppelpfeils 13 in einer Längsachse 14 auf- und abbewegliche Ventilnadel 15 angeordnet ist. Die dargestellte Ventilnadel 15 dient dabei zum Dosieren von Kraftstoff über in der Figur nicht dargestellten Durchlassöffnungen im Injektorgehäuse 11 unterhalb der Ventilnadel 15. In dem in der Fig. 1 dargestellten, geschlossenen Zustand des Kraftstoffinjektors 1, bei dem kein Kraftstoff abgegeben wird, sitzt dabei das untere Ende der Ventilnadel 15 auf einer kegelförmig umlaufenden Sitzkante 16 des Injektorgehäuses 11 auf und bildet dabei einen Dichtsitz 17 aus.In the illustrated partial region, the fuel injector 1 has an injector housing 11 or an insert arranged in an injector housing 11, which is of substantially elongated or sleeve-shaped design. In the injector 11, a plurality of areas having recess 12 is formed, in which a corresponding to the double arrow 13 in a longitudinal axis 14 up and down movable valve needle 15 is arranged. The valve needle 15 shown serves for metering fuel via passage openings, not shown in the figure, in the injector housing 11 below the valve needle 15 Fig. 1 illustrated, closed state of the fuel injector 1, in which no fuel is discharged, while sitting the lower end of the valve needle 15th on a conically encircling seat edge 16 of the injector 11 and forms a sealing seat 17 from.

Die Ausnehmung 12 bildet oberhalb der Sitzkante 16 einen ringförmig ausgebildeten Hochdruckraum 20 aus, der über einen Zuströmkanal 21 mit unter Hochdruck, insbesondere dem angesprochenen Betriebsdruck stehenden Kraftstoff versorgt wird.The recess 12 forms above the seat edge 16 of an annular high-pressure chamber 20, which is supplied via an inflow channel 21 with under high pressure, in particular the mentioned operating pressure fuel.

Der Hochdruckraum 20 geht auf der der Sitzkante 16 abgewandten Seite in eine Führungsbohrung 22 über, in der die Ventilnadel 15 über einen radial ausgebildeten Führungsspalt 23 geführt ist. Oberhalb der Führungsbohrung 22 bildet die Ausnehmung 12 einen Magnetankerraum 25 aus, der über einen Rückströmkanal 26 beispielsweise mit einem Kraftstoffrücklauf am Injektorgehäuse 11 verbunden ist.The high-pressure chamber 20 merges on the side facing away from the seat edge 16 into a guide bore 22, in which the valve needle 15 is guided over a radially formed guide gap 23. Above the guide bore 22, the recess 12 forms a magnet armature space 25, which is connected via a return flow channel 26, for example with a fuel return on the injector housing 11.

Das der Sitzkante 16 gegenüberliegende Ende der Ventilnadel 15 ist mit einem Magnetanker 28 verbunden, der im Magnetankerraum 25 angeordnet ist. Der Magnetanker 28 ist von der Federkraft einer Druckfeder 29 in Richtung des Dichtsitzes 17 kraftbeaufschlagt. Der Magnetanker 28 wirkt mit einer Magnetspule 30 und einem Magnetkern 31 zusammen, so dass bei einer Bestromung der Magnetspule 30 der Magnetanker 28 und somit auch die Ventilnadel 15 in Richtung des Magnetkerns 31 gezogen wird, und in Folge dessen die Ventilnadel 15 von ihrem Dichtsitz 17 abhebt.The seat edge 16 opposite end of the valve needle 15 is connected to a magnet armature 28 which is arranged in the armature space 25. The magnet armature 28 is acted upon by the spring force of a compression spring 29 in the direction of the sealing seat 17. The armature 28 cooperates with a magnetic coil 30 and a magnetic core 31, so that when energizing the solenoid 30, the armature 28 and thus the valve needle 15 is pulled in the direction of the magnetic core 31, and consequently the valve needle 15 from its sealing seat 17th takes off.

Der über den Rückströmkanal 26 druckentlastete Magnetankerraum 25 bildet einen zweiten Druckraum aus, der gegenüber dem als ersten Druckraum ausgebildeten Hochdruckraum 20 einen geringeren Druck aufweist. Infolge der unterschiedlichen Druckverhältnisse im Hochdruckraum 20 und im Magnetankerraum 25 kommt es zu einer Durchströmung des Führungsspaltes 23 vom Hochdruckraum 20 in Richtung des Magnetankerraumes 25. Hierbei nimmt der Druck in der Führungsbohrung 22 in Richtung des Magnetankerraumes 25 ab. Infolge des relativ hohen Druckes in Richtung des Hochdruckraumes 20 wird dabei die Führungsbohrung 22 im Durchmesser stärker elastisch deformiert bzw. aufgeweitet als im Bereich des Magnetankerraumes 25. Hierbei ist der Druckabfall in der Fig. 1 durch die Pfeile 32 symbolisch dargestellt. Der Druckabfall hat zur Folge, dass sich der Führungsspalt 23 zwischen der Ventilnadel 15 und der Führungsbohrung 22 vom Hochdruckraum 20 in Richtung des Magnetankerraumes 23 stetig verkleinert.The pressure-relieved via the return passage 26 magnet armature space 25 forms a second pressure chamber, which has a lower pressure compared to the first pressure chamber formed as a high-pressure chamber 20. As a result of the different pressure conditions in the high-pressure chamber 20 and in the magnet armature space 25, there is a flow through the guide gap 23 from the high-pressure chamber 20 in the direction of the magnet armature space 25. In this case, the pressure in the guide bore 22 decreases in the direction of the magnet armature space 25. As a result of the relatively high pressure in the direction of the high-pressure chamber 20 while the guide bore 22 is deformed more elastically in diameter or expanded than in the region of the magnet armature space 25. In this case, the pressure drop in the Fig. 1 represented symbolically by the arrows 32. The pressure drop has the consequence that the guide gap 23 between the valve needle 15 and the guide bore 22 continuously reduced by the high-pressure chamber 20 in the direction of the armature space 23.

In der Fig. 2 ist eine erfindungsgemäße Ausführungsform eines Kraftstoffinjektors 10 dargestellt, bei der dieser in Abwandlung des Kraftstoffinjektors 1 nach dem Stand der Technik gemäß der Fig. 1 einen zusätzlichen Abströmkanal 35 aufweist, der vorzugsweise mit dem Kraftstoffrücklauf im Injektorgehäuse 11 verbunden ist. Hierbei ist es bevorzugt vorgesehen, dass der Abströmkanal 35 im Bereich der Führungsbohrung 22 knapp oberhalb des Hochdruckraums 20 angeordnet bzw. ausgebildet ist. Ferner ist es vorgesehen, dass die Ventilnadel 15 im Bereich des Abströmkanals 35 eine radial umlaufende Ringnut 36 aufweist.In the Fig. 2 an embodiment of a fuel injector 10 according to the invention is shown, in which this in a modification of the fuel injector 1 according to the prior art according to the Fig. 1 an additional outflow channel 35 which is preferably connected to the fuel return in the injector 11. Here, it is preferably provided that the outflow channel 35 is arranged or formed in the region of the guide bore 22 just above the high-pressure chamber 20. Furthermore, it is provided that the valve needle 15 has a radially encircling annular groove 36 in the region of the outflow channel 35.

Über den Führungsspalt 23 vom Hochdruckraum 20 in Richtung des Magnetankerraums 25 strömender Kraftstoff gelangt somit über die Ringnut 36 in den Abströmkanal 35, und von dort zum Kraftstoffrücklauf. Der über den Abströmkanal 35 abströmende Kraftstoff hat zur Folge, dass die hydraulische Druckbelastung in Folge des Kraftstoffes auf die Wand der Führungsbohrung 22 in dem Bereich zwischen dem Abströmkanal 35 und dem Magnetankerraum 25 deutlich reduziert wird, was durch die Pfeile 37 symbolisch dargestellt ist. Dadurch kommt es zu einer Minimierung des Führungsspaltes 23 in dem Bereich zwischen dem Abströmkanal 35 und dem Magnetankerraum 25.Via the guide gap 23 from the high-pressure chamber 20 in the direction of the armature chamber 25 flowing fuel thus passes through the annular groove 36 in the discharge channel 35, and from there to the fuel return. The fuel flowing out via the outflow channel 35 has the consequence that the hydraulic pressure load due to the fuel on the wall of the guide bore 22 in the region between the outflow channel 35 and the armature space 25 is significantly reduced, which is symbolically represented by the arrows 37. This results in a minimization of the guide gap 23 in the region between the outflow channel 35 and the magnet armature space 25.

Optional kann es vorgesehen sein, dass ein weiterer Abströmkanal 38 vorgesehen bzw. ausgebildet ist, der dann vorzugsweise mit einer zusätzlichen Ringnut 39 an der Ventilnadel 15 zusammenwirkt. Hierbei ist der zusätzliche Abströmkanal 38 vorzugsweise relativ nah oberhalb des Abströmkanals 35 angeordnet bzw. ausgebildet, wie dies anhand der strichpunktierten Darstellung der Fig. 2 zum Ausdruck dargestellt ist.Optionally, it can be provided that a further outflow channel 38 is provided or formed, which then preferably cooperates with an additional annular groove 39 on the valve needle 15. In this case, the additional outflow channel 38 is preferably arranged or formed relatively close above the outflow channel 35, as can be seen from the dash-dotted representation of FIG Fig. 2 is shown for expression.

In den Fig. 3 und 4 ist eine weitere Ausführungsform eines nicht erfindungsgemäßen Kraftstoffinjektors 10a dargestellt. Wesentlich hierbei ist, dass die im Injektorgehäuse 11a ausgebildete Führungsbohrung 22a beim Fertigen der Führungsbohrung 22a konisch ausgebildet ist. Hierbei ist der Durchmesser der Führungsbohrung 22a auf der dem Hochdruckraum 20 zugewandten Seite geringer als auf der dem Magnetankerraum 25 zugewandten Seite. Aufgrund des sich von dem Hochdruckraum 20 in Richtung des Magnetankerraums 25 reduzierenden hydraulischen Drucks auf die Führungsbohrung 22a wird entsprechend der Fig. 4 beim Betrieb des Kraftstoffinjektors 10a der Führungsspalt 23a bzw. die Führungsbohrung 22a derart verformt, dass sich über nahezu die gesamte Führungslänge der Ventilnadel 15a in der Führungsbohrung 22a ein nahezu konstanter, ringförmiger Führungsspalt 23a einstellt.In the 3 and 4 a further embodiment of a non-inventive fuel injector 10a is shown. It is essential here that the guide bore 22a formed in the injector housing 11a is conical when the guide bore 22a is finished. Here, the diameter of the guide bore 22a on the high-pressure chamber 20 side facing lower than on the magnet armature 25 side facing. Due to the reducing from the high-pressure chamber 20 in the direction of the armature space 25 hydraulic pressure on the guide bore 22a is corresponding to the Fig. 4 During operation of the fuel injector 10a, the guide gap 23a or the guide bore 22a is deformed in such a way that a virtually constant, annular guide gap 23a adjusts over almost the entire guide length of the valve needle 15a in the guide bore 22a.

In den Fig. 5 und 6 ist eine weitere nicht erfindungsgemäße Ausführungsform dargestellt. Es hat sich (je nach konstruktiver Gestaltung eines Kraftstoffinjektors 10b) herausgestellt, dass bei der Montage der Einzelteile des Kraftstoffinjektors 10b sich insbesondere das Injektorgehäuse 11b im Bereich der Führungsbohrung 22b durch von auf beiden Stirnseiten auf das Injektorgehäuse 11b durch Bauteile 42, 43 wirkende Axialkräfte, die durch die Pfeile 41 in der Fig. 6 dargestellt sind, im Durchmesser D vergrößert wird. Dadurch vergrößert sich auch ein Führungsspalt 23b zwischen der Ventilnadel 15b und der Führungsbohrung 22b. Erfindungsgemäß ist es nunmehr gemäß der Fig. 5 vorgesehen, dass der Durchmesser d der Ventilnadel 15b bzw. der Durchmesser D der Führungsbohrung 22b derart gewählt wird, dass sich beim Einführen der Ventilnadel 15b in der Führungsbohrung 22b während der Montage ein minimaler Führungsspalt 23b einstellt. Dieser Führungsspalt 23b, welcher im Extremfall als Nullspiel ausgebildet ist, ist konstruktiv gesehen für die Bewegung der Ventilnadel 15b zu gering ausgelegt. Jedoch wird entsprechend der Fig. 6 durch die Axialkräfte anderer, lediglich symbolisch dargestellter Bauteile 42, 43 auf das Injektorgehäuse 11 b dieses derart verformt, dass sich der Durchmesser D der Führungsbohrung 22b derart vergrößert, dass sich der nun einstellende Führungsspalt 23b in gewünschter Weise einem Soll-Führungsspalt 23b entspricht.In the FIGS. 5 and 6 a further non-inventive embodiment is shown. It has been found (depending on the constructive design of a fuel injector 10b) that during assembly of the individual parts of the fuel injector 10b, in particular the injector housing 11b in the region of the guide bore 22b by acting on both sides of the injector 11b by components 42, 43 axial forces, by the arrows 41 in the Fig. 6 are shown in the diameter D is increased. This also increases a guide gap 23b between the valve needle 15b and the guide bore 22b. According to the invention, it is now according to the Fig. 5 provided that the diameter d of the valve needle 15b and the diameter D of the guide bore 22b is selected such that when inserting the valve needle 15b in the guide bore 22b during installation a minimum guide gap 23b sets. This guide gap 23b, which is formed in the extreme case as a zero clearance, is designed to be too small for the movement of the valve needle 15b. However, according to the Fig. 6 by the axial forces of other, only symbolically represented components 42, 43 on the injector 11 b this deformed so that the diameter D of the guide bore 22b increases such that the now adjusting guide gap 23b corresponds to a desired guide gap 23b in a desired manner.

In den Fig. 7 und 8 ist eine weitere nicht erfindungsgemäße Ausführungsform dargestellt. Hierbei ist vorgesehen, dass das Injektorgehäuse 11 c bereits während der Bearbeitung bzw. Ausbildung der Führungsbohrung 22c durch eines oder mehrere zusätzlicher Elemente 44, 45 mit einer derartigen Axialkraft A beaufschlagt wird, die der mechanischen Belastung bei montiertem Kraftstoffinjektor 10c durch dessen Bauteile 42, 43 entspricht. Das bedeutet, dass die Führungsbohrung 22c mit einem Solldurchmesser D in einem vorbelastetem Zustand des Injektorgehäuses 11c gefertigt bzw. ausgebildet wird, so dass sich nach der Montage der Bauteile 42, 43 entsprechend der Fig. 8 der gewünschte Soll-Führungspalt 23c einstellt.In the Fig. 7 and 8th a further non-inventive embodiment is shown. It is provided here that the injector housing 11c is already subjected to such an axial force A during the machining or forming of the guide bore 22c by one or more additional elements 44, 45, that of the mechanical load when the fuel injector 10c is mounted by its components 42, 43 equivalent. This means that the guide bore 22c is manufactured or formed with a nominal diameter D in a preloaded state of the injector housing 11c, so that after assembly of the components 42, 43 corresponding to the Fig. 8 set the desired target guide gap 23c.

Die soweit beschriebenen Kraftstoffinjektoren 10, 10a bis 10c können in vielfältiger Art und Weise abgewandelt bzw. modifiziert werden, ohne vom Erfindungsgedanken abzuweichen. So ist die Erfindung nicht auf Kraftstoffinjektoren 10, 10a bis 10c beschränkt, die als Magnetventile ausgebildet sind. Vielmehr kann als Stellglied für die Ventilnadel 15 auch ein Piezoantrieb oder ähnliches vorgesehen sein. Auch ist es nicht erforderlich, dass, wie dargestellt, der Magnetanker 28 direkt mit der Ventilnadel 15 verbunden bzw. gekoppelt ist. Anstelle der Ventilnadel 15 kann vielmehr auch ein anderes Element vorgesehen sein, das in einer Führungsbohrung 22 angeordnet bzw. geführt ist, wobei auf den beiden Seiten der Führungsbohrung 23 stark unterschiedliche Drücke herrschen.The fuel injectors 10, 10a to 10c described so far can be modified or modified in many ways without departing from the spirit of the invention. Thus, the invention is not limited to fuel injectors 10, 10a to 10c, which are designed as solenoid valves. Rather, can be provided as an actuator for the valve needle 15 and a piezo drive or the like. Also, it is not necessary that, as shown, the armature 28 is directly connected or coupled to the valve needle 15. Rather, instead of the valve needle 15, another element can be provided, which is arranged or guided in a guide bore 22, wherein on the two sides of the guide bore 23 strongly different pressures prevail.

Claims (6)

  1. Fuel injector (10), having an injector housing (11) in which, in a guide bore (22), there is arranged an element (15), in particular a valve needle, which is movable up and down and which serves for at least indirectly opening up and closing off injection openings in the injector housing (11), wherein the guide bore (22) separates two pressure chambers (20, 25), which are at different pressures, from one another, wherein fuel situated in the pressure chambers (20, 25) flows from the pressure chamber (20) at the relatively high pressure in the direction of the pressure chamber (25) at relatively low pressure via the guide gap (23) formed between the element (15) and the guide bore (22), and wherein the pressure chamber (25) at relatively low pressure is connected to a fuel return line on the injector housing (11) via a return flow duct (26), characterized
    in that the guide bore (22) is connected to at least one outflow duct (35, 38) in which a pressure prevails which is lower than that in the pressure chamber (20) at the relatively high pressure.
  2. Fuel injector according to Claim 1,
    characterized
    in that the outflow duct (35, 38) opens, at the side averted from the guide bore (22), into a fuel return line of the injector housing (11).
  3. Fuel injector according to Claim 1 or 2, characterized
    in that the element (15) has, in the region of the outflow duct (35, 38), a radially encircling ringshaped groove (36).
  4. Fuel injector according to one of Claims 1 to 3, characterized
    in that the at least one outflow duct (35, 38) is arranged on that side of the guide bore (22) which faces toward the pressure chamber (20) at the relatively high pressure.
  5. Fuel injector according to Claim 4,
    characterized
    in that multiple outflow ducts (35, 38) are provided, which are arranged axially spaced apart from one another on that side of the guide bore (22) which faces toward the pressure chamber (20) at the relatively high pressure.
  6. Fuel injector according to one of Claims 1 to 5, characterized
    in that the element is a valve needle (15) which is connected to a magnet armature (28).
EP11764555.6A 2010-10-20 2011-10-05 Fuel injector Not-in-force EP2630361B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201010042688 DE102010042688A1 (en) 2010-10-20 2010-10-20 fuel injector
PCT/EP2011/067353 WO2012052293A1 (en) 2010-10-20 2011-10-05 Fuel injector

Publications (2)

Publication Number Publication Date
EP2630361A1 EP2630361A1 (en) 2013-08-28
EP2630361B1 true EP2630361B1 (en) 2016-03-23

Family

ID=44741328

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11764555.6A Not-in-force EP2630361B1 (en) 2010-10-20 2011-10-05 Fuel injector

Country Status (4)

Country Link
EP (1) EP2630361B1 (en)
CN (1) CN103201500B (en)
DE (1) DE102010042688A1 (en)
WO (1) WO2012052293A1 (en)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013220547B4 (en) * 2013-10-11 2017-05-04 Continental Automotive Gmbh Piston fluid line arrangement, in particular control piston control bore arrangement
DE102015211705A1 (en) * 2015-06-24 2016-12-29 Robert Bosch Gmbh Fuel injector with control valve

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ZA813854B (en) * 1980-07-18 1982-07-28 Lucas Industries Ltd Fuel injection nozzles
DE29504608U1 (en) * 1995-03-17 1996-07-11 Bosch Gmbh Robert Fuel injection valve for internal combustion engines
DE10019153A1 (en) * 2000-04-18 2001-10-25 Bosch Gmbh Robert Fuel injection valve for IC engines has valve bore with valve member and valve piston loaded by hydraulic closing force to engage on valve member
DE10147792C2 (en) * 2001-09-27 2003-10-16 Siemens Ag Fuel injection valve
JP4119812B2 (en) * 2003-09-19 2008-07-16 ボッシュ株式会社 Fuel injection valve
DE102004013239B4 (en) * 2004-03-18 2015-10-01 Robert Bosch Gmbh Solenoid valve with adjustable armature stroke and method for setting the same
DE102007002758A1 (en) * 2006-04-04 2007-10-11 Robert Bosch Gmbh fuel injector

Also Published As

Publication number Publication date
EP2630361A1 (en) 2013-08-28
CN103201500B (en) 2016-09-21
WO2012052293A1 (en) 2012-04-26
CN103201500A (en) 2013-07-10
DE102010042688A1 (en) 2012-04-26

Similar Documents

Publication Publication Date Title
DE102011013702B4 (en) Electromagnetic actuator
DE102007001363A1 (en) Injector for injecting fuel into combustion chambers of internal combustion engines
DE102010028835A1 (en) fuel injector
EP2670970B1 (en) Fuel injector
EP2235355B1 (en) Fuel injector
DE102008032133A1 (en) Fuel injector
DE102016221547A1 (en) Fuel injection valve for injecting a gaseous and / or liquid fuel
WO2008061844A1 (en) Fuel injector
EP1952011B1 (en) Fuel injection apparatus for an internal combustion engine having direct fuel injection
EP2310662B1 (en) Fuel injector
DE102014217441A1 (en) Electromagnetically actuated proportional valve
EP2630361B1 (en) Fuel injector
DE102014225392A1 (en) Nozzle assembly for a fuel injector and fuel injector
DE102013212140A1 (en) control valve
WO2017089011A1 (en) Fuel injector
EP2481910B2 (en) Fuel injector component
DE102018201279B4 (en) High-pressure connection for a high-pressure fuel pump of a fuel injection system and high-pressure fuel pump
EP3387247B1 (en) Electromagnetically actuatable inlet valve and high-pressure pump having an inlet valve
DE102009026564A1 (en) Fuel injector for injecting fuel into combustion chamber of internal-combustion engine, has control valve element that is formed and arranged such that small resulting hydraulic force is applied on control valve element
EP2957760B1 (en) Nozzle assembly for a fuel injector and fuel injector
DE102018206659A1 (en) Fuel injector for injecting a gaseous and / or liquid fuel
DE102008000596A1 (en) Common rail injector for injecting fuel into combustion chamber of internal combustion engine, has nozzle needle comprising nozzle-sided part with extension, which is axially, displaceably guided into recess or hole on nozzle body
DE102009045556A1 (en) Injector, particularly common-rail-injector for injecting fuel to combustion chamber of internal combustion engine, comprises valve element which is adjusted between closing position and opening position
DE102013224960A1 (en) fuel injector
DE102007013248A1 (en) Fuel injector, has pressure-balanced switching valve actuated by solenoid valve and seat surface formed in area of valve seat, where seat surface increases outwards in radial direction

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: 20130521

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

DAX Request for extension of the european patent (deleted)
17Q First examination report despatched

Effective date: 20141029

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20151120

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): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 783425

Country of ref document: AT

Kind code of ref document: T

Effective date: 20160415

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502011009186

Country of ref document: DE

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20160323

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

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160624

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160323

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160323

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160623

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

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160323

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160323

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160323

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160323

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160323

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 6

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

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160323

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160723

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160323

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

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160323

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160323

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160323

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160323

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160725

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160323

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

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160323

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502011009186

Country of ref document: DE

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

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

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160323

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

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160623

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161031

26N No opposition filed

Effective date: 20170102

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

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160323

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20161005

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

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

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161031

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161031

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161005

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

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161005

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 7

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

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161005

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20161031

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 783425

Country of ref document: AT

Kind code of ref document: T

Effective date: 20161005

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

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161005

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

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160323

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20111005

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

Ref country code: MK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160323

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160323

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160323

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 8

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

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160323

Ref country code: AL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160323

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

Ref country code: FR

Payment date: 20181023

Year of fee payment: 8

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

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20191031

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

Ref country code: DE

Payment date: 20211214

Year of fee payment: 11

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502011009186

Country of ref document: DE

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

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20230503