EP2473728B1 - Injector for injecting fuel - Google Patents

Injector for injecting fuel Download PDF

Info

Publication number
EP2473728B1
EP2473728B1 EP10736678.3A EP10736678A EP2473728B1 EP 2473728 B1 EP2473728 B1 EP 2473728B1 EP 10736678 A EP10736678 A EP 10736678A EP 2473728 B1 EP2473728 B1 EP 2473728B1
Authority
EP
European Patent Office
Prior art keywords
closing member
pin
section
compression spring
diameter
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP10736678.3A
Other languages
German (de)
French (fr)
Other versions
EP2473728A1 (en
Inventor
Lorenz Zerle
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 EP2473728A1 publication Critical patent/EP2473728A1/en
Application granted granted Critical
Publication of EP2473728B1 publication Critical patent/EP2473728B1/en
Active 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
    • 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
    • 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
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • 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
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/004—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0078—Valve member details, e.g. special shape, hollow or fuel passages in the valve member
    • F02M63/008—Hollow valve members, e.g. members internally guided

Definitions

  • the invention relates to an injector for injecting fuel according to the preamble of claim 1.
  • Such an injector is from the DE 10 2006 021 741 A1 and DE 102 007 059 265 A1 known.
  • an anchor bolt is axially displaceably arranged in an armature, the diameter of which is significantly greater than the diameter of a drain hole connected to a control chamber.
  • the seat for sealing the drain hole is formed by the underside of the valve sleeve connected to the armature, which has a specially shaped annular seat edge, which is arranged at a certain distance from the drain hole.
  • the anchor bolt is surrounded by a compression spring, the magnet armature in Presses the direction of the seat and supported on an upper housing part, it may happen that the anchor bolt, which is also supported on the same area as the compression spring, comes into contact with the compression spring and thus limits or limits the mobility of the anchor bolt by the compression spring is. This can result in a leaking valve seat between the drain hole and the return hole.
  • the present invention seeks to further develop an injector for injecting fuel according to the preamble of claim 1 such that it is relatively inexpensive to produce, at the same time good sealing properties to be achieved at the valve seat.
  • the invention is based on the idea to increase the radial mobility of the anchor bolt at the support point in that the anchor bolt has an enlarged radial distance to the compression spring at this location to the compression spring. As a result, contacts of the anchor bolt are avoided with the compression spring in a critical area, so that the anchor bolt can be moved by the armature with relatively little effort, caused by the self-centering on the seat, radially or transversely.
  • the bolt-like element in the contact area on the support element has a section with a reduced diameter in relation to a pointing in the direction of the closing member section.
  • the section has a length of 30 to 80 percent, preferably 40 to 60 percent, of the region of the bolt-like element protruding from the closing element.
  • the diameter of the reduced-diameter portion is 60 to 90 percent, preferably 70 to 85 percent, of the diameter-unreduced portion.
  • a certain radial distance between the bolt-like element and the compression spring should be present.
  • the radial distance of the reduced diameter portion to the compression spring in the contact area is 5 to 20 percent, in particular 7.5 to 15 percent, of the diameter of the section.
  • the bolt-shaped element can be formed particularly cost-effectively if it is designed as a one-piece component.
  • a defined support surface of the compression spring can be achieved on the closing member, because the compression spring is supported on the closing member facing side on a support ring.
  • the required spring and magnetic forces for the closing member can be reduced if the bolt-like element on the side facing the valve seat and its adapted guide in the armature have a diameter corresponding to the diameter of the seat edge at the lower end of the armature.
  • the centering of the closing member at its seat is ensured when the closing member and the seat for centering are each cone-shaped.
  • an injector 1 for injecting fuel is shown in a combustion chamber, not shown, of an internal combustion engine of a motor vehicle.
  • a designed especially as a radial piston pump high-pressure pump 2 delivers fuel from a fuel reservoir 3 in a high-pressure fuel storage 4 (Rail).
  • the injector 1 is connected via other, not shown, injectors via a supply line 5.
  • the supply line 5 opens into a pressure chamber 6 which is bounded radially on the outside by an injector body 7.
  • a return line 8 a low-pressure region 9 of the injector 1 is connected to the fuel reservoir 3. Via the return line 8, a later to be explained control amount of fuel from the injector 1 to the fuel tank 3 flow.
  • valve element 10 is arranged, which extends in the axial direction into a formed as a blind hole receiving bore 11 of a nozzle body 12, which is clamped with a clamping nut 13 against the injector 7.
  • the valve element 10 is formed in two parts in the embodiment shown and consists of a control rod 14 and coupled thereto a nozzle needle 15.
  • the longitudinally displaceable both in a valve member 16 and in the nozzle body 12 guided valve member 10 has a closing surface 18 at a tip 18, with which the valve element 10 can be brought into close contact with a valve element seat 19 formed inside the nozzle body 12.
  • valve member 10 When the valve member 10 abuts the valve member seat 19, i. is in a closed position, the fuel outlet from a nozzle hole assembly 20 is locked within the nozzle body 12. If, on the other hand, it is lifted from the valve element seat 19, fuel can flow from the pressure chamber 6 through lateral flow connections 21 formed as transverse bores inside the nozzle body 12 on and past the valve element 10 to the nozzle hole arrangement 20 and standing there substantially under high pressure (rail pressure) into a combustion chamber be sprayed.
  • a control chamber 24 is limited, which is arranged radially within the pressure chamber 6, so that a guide gap 25 between the valve element 10 (control rod 14 ) and the sleeve-shaped portion 23 of the valve piece 16 can not expand.
  • the control chamber 24 is supplied from the pressure chamber 6 via an inlet throttle 26 running in the radial direction with the valve piece 16 with fuel under high pressure.
  • the control chamber 24 is connected via an opening in the valve member 16 extending in the axial direction flow restrictor 27 with a valve chamber 28 of a pressure-balanced in this embodiment in the axial direction control valve 29 (servo valve).
  • the control valve 29 has an axially adjustable valve sleeve 30, which is designed in one piece with an anchor plate 31.
  • the armature plate 31 is part of an electromagnetic actuator 32 and is disposed in the valve piece 16 with radial play. If electromagnets 33 of the electromagnetic actuator 32 energized, raises the armature plate 31 together with the valve sleeve 30 of hers formed on the valve piece 16, conical valve seat 34 and are so, as already mentioned, the fuel flow in the direction of the low pressure region 9 free.
  • a matched guide 38 is on the one hand provided, on the other hand, the valve seat 34 facing side of the valve sleeve 30 is conical.
  • an anchor bolt 35 is arranged axially displaceable, which seals the valve chamber 28 in the axial direction upwards.
  • a compression spring 36 formed as a closing spring, the valve sleeve 30 is acted upon in the direction of its valve seat 34 with spring force, so that a rapid closing of the control valve 29 is ensured after an interruption of the energization of the electromagnets 33.
  • the compression spring 36 is supported between an upper housing part 37 of the injector 1 serving as a support element and a support ring 39 surrounding the anchor bolt 35 in the region of the valve sleeve 30.
  • the integrally formed anchor bolt 35 has two sections 40, 41 with different diameters.
  • the one, the valve chamber 28 facing portion 40 in this case has a diameter which corresponds at least approximately to the diameter of the valve seat edge at the lower end of the valve sleeve 30 and has a larger diameter than the other portion 41.
  • the length of the reduced diameter portion 41 is 30% to 80%, preferably 40% to 60% of the length of the armature plate 31 and the valve sleeve 30 projecting portion of the anchor bolt 35th
  • the diameter of the section 41 is 60% to 80%, preferably 70% to 85% of the diameter of the section 40.
  • the radial distance R between the portion 41 and the compression spring 36, in particular in the contact region of the anchor bolt 35 and the compression spring 36 on the upper housing part 37 7.5% to 20%, in particular 10% to 15% of the diameter of section 41.
  • a closing spring 45 is arranged, which is supported on the one hand on the arranged inside the pressure chamber 6, sleeve-shaped portion 23 of the valve member 16 and on the other hand on a peripheral collar 46 of the valve element 10.
  • a compression spring 47 is supported, on the other hand rests on an upper end side of a coupler sleeve 48, and thus compresses the coupler sleeve 48 in the axial direction on an upper end face 49 of a guide portion 50.
  • a hydraulic coupler volume 51 is accommodated, in which the end faces 52, 53 of the control rod 14 and the nozzle needle 15 are opposite. The coupler volume 51 causes the nozzle needle 15 to follow an axial movement of the control rod 14.
  • the formed as part of the nozzle body 12 guide portion 50 is arranged at a radial distance from a peripheral wall 54 of the injector body 7, so that a circumferential gap 55 is formed directly radially between the guide portion 50 and the peripheral wall 54 of the injector body 7.
  • this circumferential gap 55 can be substantially narrower than in the drawing and serve as a centering for the nozzle body 12 relative to the injector body 7.
  • valve element 10 here: the nozzle needle 15
  • the valve element 10 is received axially displaceable.
  • the circumferential gap 55 is radially outside the guide portion 50 under high pressure (rail pressure) standing fuel, so that a widening of the guide gap 56 is prevented radially between the guide portion 50 and the valve member 10.
  • the flow connections 21 are provided within the nozzle body 12 in an axial portion of the nozzle body 12 directly adjacent to the guide portion 50 in the axial direction and also is arranged radially within the injector body 7, so that fuel from the ambient gap 55 can flow in the radial direction through the flow connections 21 and then in the axial direction to the nozzle hole assembly 20.
  • valve sleeve 30 and the anchor plate 31 are formed as separate components.
  • the increased radial distance to the compression spring 36 can be made in the region of the housing part 37 by a specially shaped compression spring, in which this has an enlarged coil diameter in the region of the housing part 37, which decreases in the direction of the valve sleeve 30.

Landscapes

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

Description

Stand der TechnikState of the art

Die Erfindung betrifft einen Injektor zum Einspritzen von Kraftstoff nach dem Oberbegriff des Anspruchs 1.The invention relates to an injector for injecting fuel according to the preamble of claim 1.

Ein derartiger Injektor ist aus der DE 10 2006 021 741 A1 und DE 102 007 059 265 A1 bekannt. Bei dem bekannten Injektor ist in einem Anker ein Ankerbolzen axialverschiebbar angeordnet, dessen Durchmesser deutlich größer ist als der Durchmesser einer mit einer Steuerkammer verbundenen Ablaufbohrung. Der Sitz zum Abdichten der Ablaufbohrung wird von der Unterseite der mit dem Anker verbundenen Ventilhülse gebildet, welche eine speziell geformte ringförmige Sitzkante aufweist, die in gewissem Abstand zur Ablaufbohrung angeordnet ist.Such an injector is from the DE 10 2006 021 741 A1 and DE 102 007 059 265 A1 known. In the known injector, an anchor bolt is axially displaceably arranged in an armature, the diameter of which is significantly greater than the diameter of a drain hole connected to a control chamber. The seat for sealing the drain hole is formed by the underside of the valve sleeve connected to the armature, which has a specially shaped annular seat edge, which is arranged at a certain distance from the drain hole.

Um bei den steigenden Betriebsdrücken von Common-Rail-Einspritzsystemen (gemeint sind hier Betriebsdrücke größer als 1600 bar) die erforderlichen Feder-und Magnetkräfte in Grenzen zu halten, ist es weiterhin bekannt, den Durchmesser des Ankerbolzens zu verringern, und insbesondere den Durchmesser des Ankerbolzens dem Ventilsitzdurchmesser des Ankers anzupassen. Daraus ergibt sich die Problematik, dass der Magnetanker in radialer Richtung eine relativ genaue Führung benötigt, damit dieser den Dichtsitz gewährleisten kann. Derartige genaue radiale Führungen haben einen relativ hohen Aufwand zur Folge, da die benötigten Einzelteile mit hoher Genauigkeit und somit mit hohen Herstellkosten gefertigt werden müssen. Wesentlich ist zudem, dass beim Aufsetzen des Magnetankers auf seinem Sitz Querkräfte erzeugt werden, die der Selbstzentrierung des Ankers auf dem Sitz, unter Mitnahme des Ankerbolzens dienen. Da der Ankerbolzen jedoch von einer Druckfeder umgeben ist, die den Magnetanker in Richtung des Sitzes drückt und an einem oberen Gehäuseteil abstützt, kann es dazu kommen, dass der Ankerbolzen, der sich ebenfalls am selben Bereich wie die Druckfeder abstützt, in Berührung mit der Druckfeder gelangt und somit die Beweglichkeit des Ankerbolzens durch die Druckfeder begrenzt bzw. eingeschränkt ist. Dies kann in Folge zu einem undichten Ventilsitz zwischen der Ablaufbohrung und der Rücklaufbohrung führen.In order to keep the required spring and magnetic forces within the increasing operating pressures of common rail injection systems (meant here operating pressures greater than 1600 bar), it is also known to reduce the diameter of the anchor bolt, and in particular the diameter of the anchor bolt Adjust the valve seat diameter of the armature. This results in the problem that the magnet armature in the radial direction requires a relatively accurate guide so that it can ensure the sealing seat. Such precise radial guides have a relatively high cost result, since the required items must be made with high accuracy and thus with high production costs. It is also essential that transverse forces are generated when placing the armature on his seat, which serve the self-centering of the armature on the seat, with entrainment of the anchor bolt. However, since the anchor bolt is surrounded by a compression spring, the magnet armature in Presses the direction of the seat and supported on an upper housing part, it may happen that the anchor bolt, which is also supported on the same area as the compression spring, comes into contact with the compression spring and thus limits or limits the mobility of the anchor bolt by the compression spring is. This can result in a leaking valve seat between the drain hole and the return hole.

Offenbarung der ErfindungDisclosure of the invention

Ausgehend von dem dargestellten Stand der Technik liegt der Erfindung die Aufgabe zugrunde, einen Injektor zum Einspritzen von Kraftstoff nach dem Oberbegriff des Anspruchs 1 derart weiterzubilden, dass dieser relativ preiswert herstellbar ist, wobei gleichzeitig gute Dichtungseigenschaften an dem Ventilsitz erreicht werden sollen.Based on the illustrated prior art, the present invention seeks to further develop an injector for injecting fuel according to the preamble of claim 1 such that it is relatively inexpensive to produce, at the same time good sealing properties to be achieved at the valve seat.

Diese Aufgabe wird bei einem Injektor zum Einspritzen von Kraftstoff mit den Merkmalen des Anspruchs 1 gelöst. Der Erfindung liegt dabei die Idee zugrunde, die radiale Bewegbarkeit des Ankerbolzens an der Abstützstelle dadurch zu erhöhen, dass der Ankerbolzen an diesem Ort zu der Druckfeder einen vergrößerten radialen Abstand zur Druckfeder aufweist. Dadurch werden Berührungen des Ankerbolzens mit der Druckfeder in einem kritischen Bereich vermieden, sodass sich der Ankerbolzen durch den Anker mit relativ geringem Kraftaufwand, verursacht durch die Selbstzentrierung am Sitz, radial bzw. quer verschieben lässt.This object is achieved in an injector for injecting fuel with the features of claim 1. The invention is based on the idea to increase the radial mobility of the anchor bolt at the support point in that the anchor bolt has an enlarged radial distance to the compression spring at this location to the compression spring. As a result, contacts of the anchor bolt are avoided with the compression spring in a critical area, so that the anchor bolt can be moved by the armature with relatively little effort, caused by the self-centering on the seat, radially or transversely.

Vorteilhafte Weiterbildungen des erfindungsgemäßen Injektors zum Einspritzen von Kraftstoff sind in den Unteransprüchen angegeben. In den Rahmen der Erfindung fallen sämtliche Kombinationen aus zumindest zwei von in der Beschreibung, den Ansprüchen und/oder den Figuren offenbarten Merkmalen.Advantageous developments of the injector according to the invention for the injection of fuel are given in the dependent claims. All combinations of at least two features disclosed in the description, the claims and / or the figures fall within the scope of the invention.

Gemäss der Erfindung, die sich kostengünstig herstellen lässt ist es vorgesehen, dass das bolzenartige Element im Anlagebereich an dem Stützelement einen Abschnitt mit einem reduzierten Durchmesser im Verhältnis zu einem in Richtung des Schließgliedes weisenden Abschnitt aufweist.According to the invention, which can be produced inexpensively, it is provided that the bolt-like element in the contact area on the support element has a section with a reduced diameter in relation to a pointing in the direction of the closing member section.

Hierbei ist es besonders bevorzugt vorgesehen, dass der Abschnitt eine Länge von 30 bis 80 Prozent, bevorzugt 40 bis 60 Prozent, des aus dem Schließglied herausragenden Bereichs des bolzenartigen Elements umfasst. Mittels dieser Ausbildung lässt sich eine radiale Flexibilität bzw. Bewegbarkeit der Druckfeder über einen großen Teil der Länge des bolzenartigen Elements bewirken.In this case, it is particularly preferably provided that the section has a length of 30 to 80 percent, preferably 40 to 60 percent, of the region of the bolt-like element protruding from the closing element. By means of this design can be a radial flexibility or mobility of the compression spring over a large part of the length of the bolt-like element cause.

Außerdem hat sich herausgestellt, dass einerseits die Stabilität des bolzenartigen Elements und somit der Durchmesser nicht zu gering gewählt werden darf, und andererseits die radiale Bewegbarkeit ebenfalls möglichst groß sein soll. Daher hat sich als besonders bevorzugt herausgestellt, wenn der Durchmesser des im Durchmesser reduzierten Abschnitts 60 bis 90 Prozent, vorzugsweise 70 bis 85 Prozent, des im Durchmesser nicht reduzierten Abschnitts beträgt.In addition, it has been found that on the one hand the stability of the bolt-like element and thus the diameter must not be too low, and on the other hand, the radial mobility should also be as large as possible. Therefore, it has been found to be particularly preferable that the diameter of the reduced-diameter portion is 60 to 90 percent, preferably 70 to 85 percent, of the diameter-unreduced portion.

Auch sollte ein bestimmter radialer Abstand zwischen dem bolzenartigen Element und der Druckfeder vorhanden sein. So ist es bevorzugt vorgesehen, dass der radiale Abstand des im Durchmesser reduzierten Abschnitts zur Druckfeder im Anlagebereich 5 bis 20 Prozent, insbesondere 7,5 bis 15 Prozent, des Durchmessers des Abschnitts beträgt.Also, a certain radial distance between the bolt-like element and the compression spring should be present. Thus, it is preferably provided that the radial distance of the reduced diameter portion to the compression spring in the contact area is 5 to 20 percent, in particular 7.5 to 15 percent, of the diameter of the section.

Besonders kostengünstig lässt sich das bolzenärtige Element ausbilden, wenn dieses als einstückiges Bauteil ausgebildet ist.The bolt-shaped element can be formed particularly cost-effectively if it is designed as a one-piece component.

Weiterhin lässt sich eine definierte Abstützfläche der Druckfeder an dem Schließglied erzielen, weil sich die Druckfeder auf der dem Schließglied zugewandten Seite an einem Stützring abstützt.Furthermore, a defined support surface of the compression spring can be achieved on the closing member, because the compression spring is supported on the closing member facing side on a support ring.

Die erforderlichen Feder- und Magnetkräfte für das Schließglied lassen sich reduzieren, wenn das bolzenartige Element an der dem Ventilsitz zugewandten Seite und dessen angepasste Führung im Anker einen Durchmesser aufweisen, der dem Durchmesser der Sitzkante am unteren Ende des Ankers entspricht.The required spring and magnetic forces for the closing member can be reduced if the bolt-like element on the side facing the valve seat and its adapted guide in the armature have a diameter corresponding to the diameter of the seat edge at the lower end of the armature.

Die Zentrierung des Schließgliedes an seinem Sitz wird dadurch gewährleistet, wenn das Schließglied und der Sitz zur Zentrierung jeweils kegelförmig ausgebildet sind.The centering of the closing member at its seat is ensured when the closing member and the seat for centering are each cone-shaped.

Weitere Vorteile, Merkmale und Einzelheiten der Erfindung ergeben sich aus der nachfolgenden Beschreibung bevorzugter Ausführungsbeispiele sowie anhand der Zeichnungen.Further advantages, features and details of the invention will become apparent from the following description of preferred embodiments and from the drawings.

Diese zeigen in:

Fig. 1
einen erfindungsgemäßen Injektor in einem Längsschnitt und
Fig. 2
einen Ausschnitt des Injektors gemäß der Fig. 1 in vergrößerter Darstellung im Bereich des Niederdruckbereichs zur Verdeutlichtung der erfindungsgemäßen Ausbildung des Ankerbolzens.
These show in:
Fig. 1
an injector according to the invention in a longitudinal section and
Fig. 2
a section of the injector according to the Fig. 1 in an enlarged view in the region of the low pressure region to illustrate the inventive design of the anchor bolt.

In der Fig. 1 ist ein Injektor 1 zum Einspritzen von Kraftstoff in einen nicht gezeigten Brennraum einer Brennkraftmaschine eines Kraftfahrzeugs dargestellt. Eine insbesondere als Radialkolbenpumpe ausgebildete Hochdruckpumpe 2 fördert Kraftstoff aus einem Kraftstoff-Vorratsbehälter 3 in einen Kraftstoff-Hochdruckspeicher 4 (Rail). In diesem ist Kraftstoff, insbesondere Dieselkraftstoff, unter hohem Druck, von im Ausführungsbeispiel bis etwa 2000 bar, gespeichert. An den Kraftstoff-Hochdruckspeicher 4 ist der Injektor 1 neben anderen, nicht gezeigten Injektoren über eine Versorgungsleitung 5 angeschlossen. Die Versorgungsleitung 5 mündet in einem Druckraum 6, der von einem Injektorkörper 7 radial außen begrenzt ist. Mittels einer Rücklaufleitung 8 ist ein Niederdruckbereich 9 des Injektors 1 an den Kraftstoff-Vorratsbehälter 3 angeschlossen. Über die Rücklaufleitung 8 kann eine später noch zu erläuternde Steuermenge an Kraftstoff von dem Injektor 1 zu dem Kraftstoff-Vorratsbehälter 3 abfließen.In the Fig. 1 an injector 1 for injecting fuel is shown in a combustion chamber, not shown, of an internal combustion engine of a motor vehicle. A designed especially as a radial piston pump high-pressure pump 2 delivers fuel from a fuel reservoir 3 in a high-pressure fuel storage 4 (Rail). In this fuel, especially diesel fuel, under high pressure, stored in the embodiment to about 2000 bar. To the high-pressure fuel accumulator 4, the injector 1 is connected via other, not shown, injectors via a supply line 5. The supply line 5 opens into a pressure chamber 6 which is bounded radially on the outside by an injector body 7. By means of a return line 8, a low-pressure region 9 of the injector 1 is connected to the fuel reservoir 3. Via the return line 8, a later to be explained control amount of fuel from the injector 1 to the fuel tank 3 flow.

Innerhalb des Druckraums 6 ist ein Ventilelement 10 angeordnet, das sich in axialer Richtung bis in eine als Sacklochbohrung ausgebildete Aufnahmebohrung 11 eines Düsenkörpers 12 erstreckt, welcher mit einer Spannmutter 13 gegen den Injektorkörper 7 verspannt ist. Das Ventilelement 10 ist in dem gezeigten Ausführungsbeispiel zweiteilig ausgebildet und besteht aus einer Steuerstange 14 und einer mit dieser gekoppelten Düsennadel 15. Das längsverschieblich sowohl in einem Ventilstück 16 als auch im Düsenkörper 12 geführte Ventilelement 10 weist an einer Spitze 17 eine Schließfläche 18 auf, mit welcher das Ventilelement 10 in dichter Anlage an einem innerhalb des Düsenkörpers 12 ausgebildeten Ventilelementsitz 19 bringbar ist.Within the pressure chamber 6, a valve element 10 is arranged, which extends in the axial direction into a formed as a blind hole receiving bore 11 of a nozzle body 12, which is clamped with a clamping nut 13 against the injector 7. The valve element 10 is formed in two parts in the embodiment shown and consists of a control rod 14 and coupled thereto a nozzle needle 15. The longitudinally displaceable both in a valve member 16 and in the nozzle body 12 guided valve member 10 has a closing surface 18 at a tip 18, with which the valve element 10 can be brought into close contact with a valve element seat 19 formed inside the nozzle body 12.

Wenn das Ventilelement 10 am Ventilelementsitz 19 anliegt, d.h. sich in einer Schließstellung befindet, ist der Kraftstoffaustritt aus einer Düsenlochanordnung 20 innerhalb des Düsenkörpers 12 gesperrt. Ist es dagegen vom Ventilelementsitz 19 angehoben, kann Kraftstoff aus dem Druckraum 6 durch seitliche, als Querbohrungen ausgebildete Strömungsverbindungen 21 innerhalb des Düsenkörpers 12 an und an dem Ventilelement 10 vorbei zur Düsenlochanordnung 20 strömen und dort im Wesentlichen unter Hochdruck (Raildruck) stehend in einen Brennraum gespritzt werden.When the valve member 10 abuts the valve member seat 19, i. is in a closed position, the fuel outlet from a nozzle hole assembly 20 is locked within the nozzle body 12. If, on the other hand, it is lifted from the valve element seat 19, fuel can flow from the pressure chamber 6 through lateral flow connections 21 formed as transverse bores inside the nozzle body 12 on and past the valve element 10 to the nozzle hole arrangement 20 and standing there substantially under high pressure (rail pressure) into a combustion chamber be sprayed.

Von einer oberen Stirnseite 22 des Ventilelementes 10 (hier: der Steuerstange 14) und einem hülsenförmigen Abschnitt 23 des Ventilstücks 16 wird eine Steuerkammer 24 begrenzt, die radial innerhalb des Druckraums 6 angeordnet ist, sodass sich ein Führungsspalt 25 zwischen dem Ventilelement 10 (Steuerstange 14) und dem hülsenförmigen Abschnitt 23 des Ventilstücks 16 nicht aufweiten kann. Die Steuerkammer 24 wird über eine in radialer Richtung mit dem Ventilstück 16 verlaufende Zulaufdrossel 26 mit unter Hochdruck stehendem Kraftstoff aus dem Druckraum 6 versorgt. Die Steuerkammer 24 ist über eine in dem Ventilstück 16 in axialer Richtung verlaufende Ablaufdrossel 27 mit einer Ventilkammer 28 eines in diesem Ausführungsbeispiel in axialer Richtung druckausgeglichenen Steuerventils 29 (Servoventil) verbunden. Bei geöffnetem Steuerventil 29 kann Kraftstoff aus der Steuerkammer 24 durch den Ablaufkanal 27 und die Ventilkammer 28 in den Niederdruckbereich 9 und von dort aus zur Rücklaufleitung 8 strömen. Dabei sind die Durchflussquerschnitte der Zulaufdrossel 26 und der Ablaufdrossel 27 derart aufeinander abgestimmt, dass bei geöffnetem Steuerventil 29 ein Nettoabfluss von Kraftstoff (Steuermenge) aus der Steuerkammer 24 in den Niederdruckbereich 9 des Injektors 1 resultiert.From an upper end face 22 of the valve element 10 (here: the control rod 14) and a sleeve-shaped portion 23 of the valve piece 16 a control chamber 24 is limited, which is arranged radially within the pressure chamber 6, so that a guide gap 25 between the valve element 10 (control rod 14 ) and the sleeve-shaped portion 23 of the valve piece 16 can not expand. The control chamber 24 is supplied from the pressure chamber 6 via an inlet throttle 26 running in the radial direction with the valve piece 16 with fuel under high pressure. The control chamber 24 is connected via an opening in the valve member 16 extending in the axial direction flow restrictor 27 with a valve chamber 28 of a pressure-balanced in this embodiment in the axial direction control valve 29 (servo valve). When the control valve 29 is open, fuel can flow from the control chamber 24 through the drainage channel 27 and the valve chamber 28 into the low-pressure region 9 and from there to the return line 8. In this case, the flow cross sections of the inlet throttle 26 and the outlet throttle 27 are matched to one another such that when the control valve 29 is open, a net outflow of fuel (control quantity) from the control chamber 24 into the low pressure region 9 of the injector 1 results.

Das Steuerventil 29 weist eine in axialer Richtung verstellbare Ventilhülse 30 auf, die einstückig mit einer Ankerplatte 31 ausgeführt ist. Die Ankerplatte 31 ist Teil eines elektromagnetischen Aktuators 32 und ist mit radialem Spiel in dem Ventilstück 16 angeordnet. Werden Elektromagnete 33 des elektromagnetischen Aktuators 32 bestromt, hebt die Ankerplatte 31 mitsamt der Ventilhülse 30 von ihrem an dem Ventilstück 16 ausgebildeten, kegelförmigen Ventilsitz 34 ab und gibt so, wie bereits erwähnt, den Kraftstofffluss in Richtung des Niederdruckbereichs 9 frei. Zur Bildung einer Zentrierung beim Aufsetzen der Ventilhülse 30 auf dem Ventilsitz 34 ist einerseits eine angepasste Führung 38 vorgesehen, andererseits ist die dem Ventilsitz 34 zugewandte Seite der Ventilhülse 30 kegelförmig ausgebildet.The control valve 29 has an axially adjustable valve sleeve 30, which is designed in one piece with an anchor plate 31. The armature plate 31 is part of an electromagnetic actuator 32 and is disposed in the valve piece 16 with radial play. If electromagnets 33 of the electromagnetic actuator 32 energized, raises the armature plate 31 together with the valve sleeve 30 of hers formed on the valve piece 16, conical valve seat 34 and are so, as already mentioned, the fuel flow in the direction of the low pressure region 9 free. To form a centering when placing the valve sleeve 30 on the valve seat 34, a matched guide 38 is on the one hand provided, on the other hand, the valve seat 34 facing side of the valve sleeve 30 is conical.

Innerhalb der Ventilhülse 30 ist ein Ankerbolzen 35 axial verschiebbar angeordnet, der die Ventilkammer 28 in axialer Richtung nach oben abdichtet. Mittels einer als Druckfeder 36 ausgebildeten Schließfeder wird die Ventilhülse 30 in Richtung ihres Ventilsitzes 34 mit Federkraft beaufschlagt, sodass ein schnelles Schließen des Steuerventils 29 nach einer Unterbrechung der Bestromung der Elektromagnete 33 sichergestellt ist. Hierbei stützt sich die Druckfeder 36 zwischen einem als Stützelement dienenden oberen Gehäuseteil 37 des Injektors 1 und einem den Ankerbolzen 35 im Bereich der Ventilhülse 30 umgebenden Stützring 39 ab.Within the valve sleeve 30, an anchor bolt 35 is arranged axially displaceable, which seals the valve chamber 28 in the axial direction upwards. By means of a compression spring 36 formed as a closing spring, the valve sleeve 30 is acted upon in the direction of its valve seat 34 with spring force, so that a rapid closing of the control valve 29 is ensured after an interruption of the energization of the electromagnets 33. In this case, the compression spring 36 is supported between an upper housing part 37 of the injector 1 serving as a support element and a support ring 39 surrounding the anchor bolt 35 in the region of the valve sleeve 30.

Erfindungsgemäß ist es vorgesehen, dass der einstückig ausgebildete Ankerbolzen 35 zwei Abschnitte 40, 41 mit unterschiedlichem Durchmesser aufweist. Der eine, der Ventilkammer 28 zugewandte Abschnitt 40 weist dabei einen Durchmesser auf, der zumindest annähernd dem Durchmesser der Ventilsitzkante am unteren Ende der Ventilhülse 30 entspricht und hat einen größeren Durchmesser als der andere Abschnitt 41. Die Länge des im Durchmesser reduzierten Abschnitts 41 beträgt dabei 30% bis 80%, bevorzugt 40% bis 60% der Länge des aus der Ankerplatte 31 bzw. der Ventilhülse 30 herausragenden Abschnitts des Ankerbolzens 35.According to the invention, it is provided that the integrally formed anchor bolt 35 has two sections 40, 41 with different diameters. The one, the valve chamber 28 facing portion 40 in this case has a diameter which corresponds at least approximately to the diameter of the valve seat edge at the lower end of the valve sleeve 30 and has a larger diameter than the other portion 41. The length of the reduced diameter portion 41 is 30% to 80%, preferably 40% to 60% of the length of the armature plate 31 and the valve sleeve 30 projecting portion of the anchor bolt 35th

Weiterhin ist es erfindungsgemäß vorgesehen, dass der Durchmesser des Abschnitts 41 60% bis 80%, vorzugsweise 70% bis 85% des Durchmessers des Abschnitts 40 beträgt.Furthermore, it is provided according to the invention that the diameter of the section 41 is 60% to 80%, preferably 70% to 85% of the diameter of the section 40.

Zuletzt ist es vorgesehen, dass der radiale Abstand R zwischen dem Abschnitt 41 und der Druckfeder 36, insbesondere im Anlagebereich des Ankerbolzens 35 und der Druckfeder 36 an dem oberen Gehäuseteil 37 7,5% bis 20%, insbesondere 10% bis 15% des Durchmessers des Abschnitts 41 beträgt.Finally, it is provided that the radial distance R between the portion 41 and the compression spring 36, in particular in the contact region of the anchor bolt 35 and the compression spring 36 on the upper housing part 37 7.5% to 20%, in particular 10% to 15% of the diameter of section 41.

Bei geschlossenem Steuerventil 29 steigt der Druck innerhalb der Steuerkammer 24 rapide an, wodurch die auf die Stirnseite 22 des Ventilelements 10 wirkenden Schließkräfte ansteigen und somit das Ventilelement 10 auf seinem Ventilelementsitz 19 bewegt wird, wodurch der Einspritzvorgang unterbrochen wird.When the control valve 29 is closed, the pressure inside the control chamber 24 increases rapidly, whereby the closing forces acting on the end face 22 of the valve element 10 increase and thus the valve element 10 is moved on its valve element seat 19, whereby the injection process is interrupted.

Innerhalb des Druckraums 6 ist eine Schließfeder 45 angeordnet, die sich einerseits an dem innerhalb des Druckraums 6 angeordneten, hülsenförmigen Abschnitt 23 des Ventilstücks 16 und andererseits an einem Umfangsbund 46 des Ventilelements 10 abstützt.Within the pressure chamber 6, a closing spring 45 is arranged, which is supported on the one hand on the arranged inside the pressure chamber 6, sleeve-shaped portion 23 of the valve member 16 and on the other hand on a peripheral collar 46 of the valve element 10.

Auf der der Schließfeder 45 abgewandten Seite des Umfangsbundes 46 stützt sich eine Druckfeder 47 ab, die andererseits an einer oberen Stirnseite einer Kopplerhülse 48 aufliegt, und somit die Kopplerhülse 48 in axialer Richtung auf eine obere Stirnseite 49 eines Führungsabschnittes 50 presst. Radial innerhalb der Kopplerhülse 48, die die Steuerstange 14 dicht umschließt, ist ein hydraulisches Kopplervolumen 51 aufgenommen, in dem sich die Stirnseiten 52, 53 der Steuerstange 14 und der Düsennadel 15 gegenüberliegen. Das Kopplervolumen 51 bewirkt, dass die Düsennadel 15 einer Axialbewegung der Steuerstange 14 folgt.On the side facing away from the closing spring 45 of the peripheral collar 46, a compression spring 47 is supported, on the other hand rests on an upper end side of a coupler sleeve 48, and thus compresses the coupler sleeve 48 in the axial direction on an upper end face 49 of a guide portion 50. Radially within the coupler sleeve 48, which tightly surrounds the control rod 14, a hydraulic coupler volume 51 is accommodated, in which the end faces 52, 53 of the control rod 14 and the nozzle needle 15 are opposite. The coupler volume 51 causes the nozzle needle 15 to follow an axial movement of the control rod 14.

Der als Teil des Düsenkörpers 12 ausgebildete Führungsabschnitt 50 ist mit Radialabstand zu einer Umfangswand 54 des Injektorkörpers 7 angeordnet, sodass ein Umfangsspalt 55 unmittelbar radial zwischen dem Führungsabschnitt 50 und der Umfangswand 54 des Injektorkörpers 7 gebildet ist. In der Realität kann dieser Umfangsspalt 55 wesentlich schmaler als in der Zeichnung ausgebildet werden und als Zentrierung für den Düsenkörper 12 relativ zum Injektorkörper 7 dienen.The formed as part of the nozzle body 12 guide portion 50 is arranged at a radial distance from a peripheral wall 54 of the injector body 7, so that a circumferential gap 55 is formed directly radially between the guide portion 50 and the peripheral wall 54 of the injector body 7. In reality, this circumferential gap 55 can be substantially narrower than in the drawing and serve as a centering for the nozzle body 12 relative to the injector body 7.

Innerhalb des Führungsabschnittes 50 ist das Ventilelement 10 (hier: die Düsennadel 15) axial verschieblich aufgenommen. Durch das Vorsehen des Umfangsspaltes 55 befindet sich radial außerhalb des Führungsabschnittes 50 unter Hochdruck (Raildruck) stehender Kraftstoff, sodass eine Aufweitung des Führungsspaltes 56 radial zwischen dem Führungsabschnitt 50 und dem Ventilelement 10 verhindert wird.Within the guide portion 50, the valve element 10 (here: the nozzle needle 15) is received axially displaceable. By providing the circumferential gap 55 is radially outside the guide portion 50 under high pressure (rail pressure) standing fuel, so that a widening of the guide gap 56 is prevented radially between the guide portion 50 and the valve member 10.

Damit Kraftstoff bei von dem Ventilelementsitz 19 angehobenem Ventilelement 10 durch die Düsenlochanordnung 20 strömen kann, sind die Strömungsverbindungen 21 innerhalb des Düsenkörpers 12 vorgesehen, und zwar in einem Axialabschnitt des Düsenkörpers 12, der in axialer Richtung unmittelbar an den Führungsabschnitt 50 angrenzt, und der ebenfalls radial innerhalb des Injektorkörpers 7 angeordnet ist, sodass Kraftstoff aus dem Umgebungsspalt 55 in radialer Richtung durch die Strömungsverbindungen 21 und dann in axialer Richtung zu der Düsenlochanordnung 20 strömen kann.In order for fuel to flow through the nozzle hole assembly 20 when the valve member 10 is raised from the valve member seat 19, the flow connections 21 are provided within the nozzle body 12 in an axial portion of the nozzle body 12 directly adjacent to the guide portion 50 in the axial direction and also is arranged radially within the injector body 7, so that fuel from the ambient gap 55 can flow in the radial direction through the flow connections 21 and then in the axial direction to the nozzle hole assembly 20.

Der beschriebene Injektor 1 kann in vielfältiger Weise modifiziert werden, ohne vom Erfindungsgedanken abzuweichen. So ist es beispielsweise denkbar, dass die Ventilhülse 30 und die Ankerplatte 31 als separate Bauteile ausgebildet sind. Auch kann der vergrößerte radiale Abstand zur Druckfeder 36 im Bereich des Gehäuseteils 37 durch eine speziell geformte Druckfeder hergestellt werden, bei der diese im Bereich des Gehäuseteils 37 einen vergrößerten Windungsdurchmesser aufweist, der sich in Richtung der Ventilhülse 30 verringert.The described injector 1 can be modified in many ways without departing from the spirit of the invention. For example, it is conceivable that the valve sleeve 30 and the anchor plate 31 are formed as separate components. Also, the increased radial distance to the compression spring 36 can be made in the region of the housing part 37 by a specially shaped compression spring, in which this has an enlarged coil diameter in the region of the housing part 37, which decreases in the direction of the valve sleeve 30.

Claims (8)

  1. Injector (1) for the injection of fuel into a combustion chamber of an internal combustion engine, in which injector (1) an injection member (10) which opens or closes at least one injection opening (20) is actuated by way of a control valve (29), the control valve (29) opening or closing a connection (43) from a control space (24) to a fuel return line (8), by a closing member (30) which is arranged in an operative connection with a compression spring (36) being placed into a seat (34) or opening the latter, and a pin-like element (35) being arranged axially displaceably in the closing member (30), which pin-like element (35) is surrounded radially by the compression spring (36) in the region which protrudes out of the closing member (30), and which pin-like element (35) is supported together with the compression spring (36) against a stationary supporting element (37) on the side which lies opposite the seat (34), characterized in that the closing member (30) is arranged with radial play opposite a valve element (16), and in that the pin-like element (35) is at an increased radial spacing (R) from the compression spring (36) in the bearing region on the supporting element (37), in that, in the bearing region on the supporting element (37), the pin-like element (35) has a section (41) with a reduced diameter in relation to a section (40) which points in the direction of the closing member (30), and in that, on the side which faces the closing member (30), the compression spring (36) is supported on a supporting ring (39) which surrounds that section (40) of the pin-like element (35) which points in the direction of the closing member (30).
  2. Injector according to Claim 1, characterized in that the section (41) of reduced diameter comprises a length of from 30% to 80%, preferably of from 40% to 60% of that region of the pin-like element (35) which protrudes out of the closing member (30).
  3. Injector according to Claim 1 or 2, characterized in that the diameter of the section (41) of reduced diameter is from 60% to 90%, preferably from 70% to 85% of the section (40) of non-reduced diameter.
  4. Injector according to either of Claims 2 and 3, characterized in that the radial spacing (R) of the section (41) of reduced diameter from the compression spring (36) in the bearing region on the supporting element (37) is from 5% to 20%, in particular from 7.5% to 15% of the diameter of the section (41) of reduced diameter.
  5. Injector according to one of Claims 1 to 4, characterized in that the pin-like element (35) is of single-piece configuration.
  6. Injector according to one of Claims 1 to 5, characterized in that, in the region of the seat (34), the pin-like element (35) has a diameter which corresponds to the diameter of the seat edge on the lower region of the closing member (30).
  7. Injector according to one of Claims 1 to 6, characterized in that the closing member (30) and the seat (34) are in each case of conical configuration for centring purposes.
  8. Injector according to one of Claims 1 to 7, characterized in that the closing member (30) is part of an armature (31) which interacts with a coil arrangement (33).
EP10736678.3A 2009-08-31 2010-07-21 Injector for injecting fuel Active EP2473728B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200910029009 DE102009029009A1 (en) 2009-08-31 2009-08-31 Injector for injecting fuel
PCT/EP2010/060542 WO2011023473A1 (en) 2009-08-31 2010-07-21 Injector for injecting fuel

Publications (2)

Publication Number Publication Date
EP2473728A1 EP2473728A1 (en) 2012-07-11
EP2473728B1 true EP2473728B1 (en) 2014-11-26

Family

ID=42668207

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10736678.3A Active EP2473728B1 (en) 2009-08-31 2010-07-21 Injector for injecting fuel

Country Status (3)

Country Link
EP (1) EP2473728B1 (en)
DE (1) DE102009029009A1 (en)
WO (1) WO2011023473A1 (en)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011078564A1 (en) * 2011-07-04 2013-01-10 Robert Bosch Gmbh Control valve for a fuel injector and fuel injector
DE102013211855A1 (en) * 2013-06-21 2014-12-24 Robert Bosch Gmbh Control valve for a fuel injector
GB201513309D0 (en) 2015-07-29 2015-09-09 Delphi Int Operations Lux Srl Fuel injector

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006021741A1 (en) 2006-05-10 2007-11-15 Robert Bosch Gmbh Fuel injector with pressure compensated control valve
DE102007047152A1 (en) * 2007-10-02 2009-04-09 Robert Bosch Gmbh Injector with an annulus separate anchor space
DE102007059265A1 (en) * 2007-12-10 2009-06-18 Robert Bosch Gmbh Switching valve for injectors
DE102008003348A1 (en) * 2008-01-07 2009-07-09 Robert Bosch Gmbh fuel injector
DE102008041531A1 (en) * 2008-08-25 2010-03-04 Robert Bosch Gmbh Fuel injection device operating method for internal-combustion engine, involves operating valve element by electromagnet, which is strongly active during closing movement of shift valve than during impact of valve element on valve seat

Also Published As

Publication number Publication date
EP2473728A1 (en) 2012-07-11
DE102009029009A1 (en) 2011-03-03
WO2011023473A1 (en) 2011-03-03

Similar Documents

Publication Publication Date Title
EP2201240B1 (en) Injector
EP2116717A2 (en) Fuel injector
EP3529486A1 (en) Electromagnetically actuatable inlet valve and high-pressure pump comprising an inlet valve
EP2235356B1 (en) Fuel injector
WO2011095367A1 (en) Control valve assembly of a fuel injector
EP1865192B1 (en) Fuel injector with servo assistance
EP2294309B1 (en) Fuel injector
EP2310662B1 (en) Fuel injector
EP2473728B1 (en) Injector for injecting fuel
WO2009141182A1 (en) Fuel injector
EP2011995A2 (en) Injector with a valve element which opens to the outside
DE10032517A1 (en) Injector for injecting fuel into combustion chambers of internal combustion engines comprises a control part loaded by spring elements in the injector housing and guided in a guide sleeve surrounding a control space
EP2022975B1 (en) Injector
WO2003074865A1 (en) Installation for the pressure-modulated formation of the injection behavior
DE10132249A1 (en) Fuel injector with force-balanced control valve
DE102006047935A1 (en) Fuel injector for an internal combustion engine
EP2019198B1 (en) Injector
DE102012224247A1 (en) Fuel injector i.e. common-rail injector, for use with self-ignition engine, has magnet armature indirectly connected with coupler, which delimits adjusting element over coupling element by spring element
DE102011076956A1 (en) Fuel injector for internal combustion engine, has valve needle arranged in housing in longitudinally displaceable manner, where valve needle closes scum hole arranged in high-pressure space of housing
EP2136067A1 (en) Fuel injector
DE102007001365A1 (en) Common rail injector, for injecting e.g. petrol, into combustion chamber of internal combustion engine, has switching chamber connected with low pressure area by connecting channel that is closed and opened by control valve
EP3365551A1 (en) Electromagnetically operable inlet valve and high-pressure pump having an inlet valve
DE102008001601A1 (en) Fuel injector and manufacturing process
WO2000017511A1 (en) Fuel injection device for internal combustion engines
WO2008148632A1 (en) Injector comprising a control valve

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: 20120331

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 SE SI SK SM TR

DAX Request for extension of the european patent (deleted)
GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20140829

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 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: 698370

Country of ref document: AT

Kind code of ref document: T

Effective date: 20141215

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: 502010008354

Country of ref document: DE

Effective date: 20150108

REG Reference to a national code

Ref country code: NL

Ref legal event code: VDEP

Effective date: 20141126

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

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

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: 20141126

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: 20141126

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: 20150226

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: 20141126

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: 20141126

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: 20150326

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: 20150326

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: 20150227

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: 20141126

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: 20141126

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: 20141126

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: 20141126

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: 20141126

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: 20141126

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: 20141126

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: 20141126

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: 20141126

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502010008354

Country of ref document: DE

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

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: 20141126

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: 20150827

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

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: 20141126

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: 20141126

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: 20150721

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 FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150721

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: CH

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

Effective date: 20150731

Ref country code: LI

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

Effective date: 20150731

Ref country code: GB

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

Effective date: 20150721

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: 20150721

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 698370

Country of ref document: AT

Kind code of ref document: T

Effective date: 20150721

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: 20150721

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

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: 20141126

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

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: 20100721

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: 20141126

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: 20141126

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: BE

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

Effective date: 20150731

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: 20141126

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: 20141126

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 9

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

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: 20141126

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

Ref country code: IT

Payment date: 20230731

Year of fee payment: 14

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

Ref country code: FR

Payment date: 20230724

Year of fee payment: 14

Ref country code: DE

Payment date: 20230922

Year of fee payment: 14