EP2108080B1 - Injector for injecting fuel into combustion chambers of internal combustion engines - Google Patents

Injector for injecting fuel into combustion chambers of internal combustion engines Download PDF

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Publication number
EP2108080B1
EP2108080B1 EP07847880A EP07847880A EP2108080B1 EP 2108080 B1 EP2108080 B1 EP 2108080B1 EP 07847880 A EP07847880 A EP 07847880A EP 07847880 A EP07847880 A EP 07847880A EP 2108080 B1 EP2108080 B1 EP 2108080B1
Authority
EP
European Patent Office
Prior art keywords
injector
sleeve
part element
spring
coupler space
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
EP07847880A
Other languages
German (de)
French (fr)
Other versions
EP2108080A1 (en
Inventor
Hans-Christoph Magel
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
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2108080A1 publication Critical patent/EP2108080A1/en
Application granted granted Critical
Publication of EP2108080B1 publication Critical patent/EP2108080B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • 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
    • 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/167—Means for compensating clearance or thermal expansion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/30—Fuel-injection apparatus having mechanical parts, the movement of which is damped
    • F02M2200/304—Fuel-injection apparatus having mechanical parts, the movement of which is damped using hydraulic means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
    • 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
    • F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
    • F02M2547/001—Control chambers formed by movable sleeves
    • 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
    • F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
    • F02M2547/003—Valve inserts containing control chamber and valve piston

Definitions

  • the invention relates to an injector, in particular a common rail injector, according to the preamble of claim 1.
  • Such an injector is from the WO 20051068820 A1 the applicant known.
  • a multi-part valve element is provided, the two parts of which are hydraulically coupled to each other via a coupler space.
  • the coupler space is bounded radially by a sleeve which is axially supported on the end face of an additional, separate housing part.
  • a common rail injector known, can be injected with the fuel directly into this associated combustion chamber of an internal combustion engine.
  • a one-piece valve element is arranged in a housing, which has a total acting in the opening direction of the valve element pressure surface.
  • control surface is provided, which limits a control chamber.
  • the control surface acting in the closing direction is larger than the pressure surface acting in the opening direction when the valve element is open.
  • valve element is designed in two parts, wherein the two components (control rod and nozzle needle) abut each other in a permanently connected to a low pressure region of the injector low pressure space.
  • a diameter step of the valve element is realized to increase the hydraulic closing force.
  • a disadvantage of the known injector are the high leakage losses, the inevitably occur, since the low-pressure chamber is connected in two axial directions via a guide gap with the high pressure region of the injector and thus fuel in the low-pressure chamber (part of Injektomieder Kunststoffs) and can flow from there to a return line.
  • an injector in which the valve element is formed in two parts, wherein the two components (control rod and nozzle needle) are hydraulically connected to each other via a coupler space. Since the coupler space is not connected to a low-pressure region of the injector, there is also a high fuel pressure within the coupler space. The hydraulic coupling causes the nozzle needle to follow a controlled movement of the control rod.
  • the invention has the object of developing an injector according to the preamble of claim 1 such that it is structurally particularly simple in construction and inexpensive to produce.
  • the sleeve is guided on one of the two coupled by means of the coupler space sub-elements and spring-loaded in the direction of the respective other sub-element.
  • the only axial sealing or guide gap is formed in the axial direction, via which the coupler chamber is hydraulically connected to the pressure region of the injector.
  • the sleeve With its front side, the sleeve is located on the respective other sub-element or on a contact surface of this sub-element, so that between sleeve and contact surface a sealing area is formed.
  • the force acting on the sleeve in the axial direction spring is arranged such that it acts in the opening direction on the further away from the combustion chamber sub-element, in particular the control rod.
  • the spring counteracts a closing spring, wherein the spring force of the closing spring is greater than the spring force of the sleeve spring, so that only the differential spring force acts in the closed position, which has a positive effect on the control of the injector.
  • the sleeve is not formed as a separate component, but is integrally formed with the first or the second sub-element.
  • the coupler space is within the first and / or the second sub-element.
  • the two sub-elements are slidably guided in the axial direction, wherein the single axial gap is formed in this embodiment between the two sub-elements.
  • This construction makes it possible to arrange a further axially between the two sub-elements, which is supported in each case on the opposite end faces.
  • the spring force is to be dimensioned so that it is less than the spring force a closing spring acting on one of the sub-elements.
  • an axial stop is provided for the subelement further away from the combustion chamber, in particular the control rod, so that a gap is established between the two subelements when the nozzle needle rests on the needle seat when at rest.
  • the stop mass is reduced in the needle seat, since not the entire valve element, but only the nozzle needle is pressed onto the needle seat.
  • a common rail injector 1 for injecting fuel into combustion chambers of internal combustion engines is shown.
  • the injector 1 is supplied via a high-pressure supply line 2 from a high-pressure fuel accumulator 3 (rail) with fuel at high pressure (about 1800 to 2000 bar), in particular diesel oil or gasoline.
  • the high-pressure fuel accumulator 3 is supplied with fuel from a low-pressure reservoir 5 by a high-pressure pump 4 designed in particular as a radial piston pump.
  • a low-pressure region 6 of the injector is hydraulically connected via a return line 7 to the reservoir 5. Depending on the operating condition, the pressure in the low-pressure region of the injector is between approximately 0 and 10 bar.
  • a fuel control amount is discharged from a control chamber 8 and fed via the high-pressure pump 4 the high-pressure circuit again.
  • the injector body 1 has an injector body 9 and a nozzle body 10, the injector body 9 and the nozzle body 10 via a nozzle retaining nut, not shown, which is screwed to the injector body 9, are braced against each other, wherein the nozzle retaining nut, not shown, is penetrated by the nozzle body 10 in the axial direction.
  • a stepped bore 11 is introduced, which continues in the axial direction in a bore 12 in the injector 9.
  • a valve member 14 is guided longitudinally displaceable.
  • the valve element 14 has a control rod 8 with an end face 15 limiting control rod 16 and an axially adjacent to the combustion chamber nozzle needle 17.
  • the nozzle needle 17 has a closing surface 19 with which it can be brought into tight contact with a needle seat 20 formed within the nozzle body 10.
  • the nozzle needle 17 is polygonal contoured in an axial section 22 and guided on the circular contoured stepped bore wall of the nozzle body 10 so that evenly distributed over the circumference Axialkanäle 23 are formed by the fuel within the pressure chamber 13 in the axial direction of the mouth region of the high-pressure supply line 2 can flow to the nozzle hole assembly 21 with the valve element 16 open.
  • a substantially conically shaped pressure application surface 24 is formed, on which a compressive force acts in the opening direction.
  • This opening force temporarily counteracts a closing force on the end face 15 within the control chamber 8.
  • the control chamber 8 is hydraulically connected via an inlet throttle 25 within a sleeve-shaped component 26 with the pressure chamber 13. Via an outlet throttle 27, the radially limited by the sleeve-shaped member 26 control chamber 8 with the low pressure region 6 is connected.
  • the outlet throttle 27 having flow channel 28, can flow through the fuel temporarily in the low-pressure chamber 6, is passed through a cylinder plate 29.
  • the sleeve-shaped component 26 in turn is biased by a closing spring 30 in the axial direction of the tightly clamped inside the injector 1 cylinder plate 29.
  • the closing spring 30 is supported for this purpose in the axial direction on a peripheral collar 31 of the control rod 16, whereby a closing force on the control rod 16 acts permanently.
  • a control valve 32 In order for fuel to flow out of the control chamber 8 into the low-pressure region 6, whereby the pressure force acting on the end face 15 of the control rod 16 is reduced, a control valve 32 is provided which has an electromagnetic actuator 33 which cooperates with an armature plate 34.
  • the anchor plate 34 is fixedly connected to a valve body 35, which in turn acts in the axial direction kraftbeauf provided on a valve ball 36.
  • the valve body 35 and thus the valve ball 36 lifts off from a valve seat 36 formed on the cylinder plate 29, so that fuel can flow via the outlet throttle from the control chamber 8 in the low pressure region 6 and from there via the return line 7.
  • the flow cross-sections of the inlet throttle 25 and the outlet throttle 27 are coordinated so that the inflow into the control chamber 8 from the pressure chamber 13 is weaker than the outflow from the control chamber 8 in the low pressure region and thus with open control valve 32, a net outflow of fuel the control chamber 8 results.
  • the resulting pressure drop in the control chamber 8 causes the amount of the closing force falls below the amount of the opening force and the valve element 14 lifts from the needle seat 20.
  • the control rod 16 and the nozzle needle 17 are hydraulically coupled to each other via a hydraulic coupler 38 only.
  • the nozzle needle 17 follows an opening movement and a closing movement of the control rod 16.
  • the diameter D1 of the nozzle needle 17 within the sleeve 39 delimiting the coupler space 38 is less than the diameter D2 of the control rod 16 guided in the sleeve-shaped component 26.
  • the coupler space 38 which has no Connection to the low pressure region of the injector 1 is filled with fuel and disposed radially within the pressure chamber 13, so that there is approximately rail pressure within the coupler space 38.
  • the coupler space 38 is bounded radially by a sleeve 39 within which the nozzle needle 17 is guided in an axially displaceable manner. Between nozzle needle 17 and sleeve 39, a circular contoured axial gap 40 (guide or sealing gap) is formed. This is the only guide gap, via which the coupler space 38 is connected to the high pressure area, in particular the pressure space 13.
  • the sleeve 39 is spring-loaded by means of a helical spring 41, which is supported axially on an annular shoulder 42 of the stepped bore 11 within the nozzle body 10 in the axial direction on a contact surface 43 on the front face 15 opposite end face 44 of the control rod.
  • the contact surface 43 is formed on a widened in the radial direction paragraph 45 of the control rod 16. Due to the spring force of the spring 41, the sleeve 39 is sealingly against the contact surface 43.
  • the spring 41 acts on the control rod 16 via the sleeve 39 in the opening direction with a spring force which counteracts the spring force of the closing spring 30.
  • the spring 41 is designed to be weaker than the closing spring 30, so that a total of permanently acting in the closing direction, a small resultant spring force on the valve element 14. Since the closing spring 30 is designed to be stronger than the spring 41, the return of the control rod 16 after the injection process via the large spring force of the closing spring 30, whereby a reset of the control rod without opening the sleeve 39, so lifting the sleeve 39 of the contact surface 23 is guaranteed.
  • a slight fuel throttle may be provided in the region of the axial section 22.
  • the fuel circuit is only partially shown.
  • the coupler space 38 is also bounded by a sleeve 39.
  • the spring 41 is not supported an annular shoulder of the stepped bore 11, but at a radially widened portion 46 of the control rod 16, whereby the sleeve 39 in the axial direction on a combustion chamber facing away from abutment surface 47 of the nozzle needle 17 is spring-loaded.
  • the contact surface 47 is formed on a widened in the radial direction portion 48 of the valve needle 17.
  • the section 46 of the control rod 16 forms an axial stop for the control rod 16 on the nozzle body 10, so that in the idle state shown (the nozzle needle 17 rests on the needle seat 20 and the control chamber 8 is pressurized with the control valve 32 closed) a gap 49th between the nozzle needle 17 and the control rod 16 is formed.
  • axial openings 50 are provided within the section 46.
  • the only axial gap which connects the coupler chamber 38 hydraulically to the pressure chamber 13 is formed between the control rod 16 and the sleeve 39 guided thereon.
  • no separate sleeve for limiting the coupler space 38 is provided.
  • the coupler space 38 is formed within the control rod 16.
  • the nozzle needle 17 is guided in a sleeve-shaped extension 51 of the control rod 16.
  • the spring 41 is supported in the axial direction on the one hand on the annular shoulder 42 of the nozzle body 10 and on the other hand frontally on the sleeve-shaped extension 51, whereby the control rod 16 in the opening direction is subjected to spring force.
  • the spring 41 is designed to be weaker than the also acting on the control rod 16 closing spring 30.
  • the coupler chamber 38 with the high-pressure region connecting axial gap 40 is formed in the embodiment shown between the outer surface of the nozzle needle 17 and inner peripheral surface of the sleeve-shaped extension 51.
  • Fig. 4 is the coupler space 38, similar to in Fig. 3 formed within a sleeve-shaped extension 51 of the control rod 16.
  • the control rod 16 is guided with a polygonal contoured portion 21 within the nozzle body 10 in the axial direction to avoid lateral forces on the nozzle needle 17.
  • the nozzle needle is designed substantially smaller than the control rod 16, resulting in a small mass in the needle seat.
  • the spring 41 is supported on the one hand on the control rod 16 and on the other hand on the nozzle needle 17. In the rest state shown, a gap 49 is provided between the control rod 16 and the nozzle needle 17.

Abstract

The invention relates to an injector (1) for injecting fuel into combustion chambers of internal combustion engines, in particular a common rail injector (1), having a high-pressure region and having a valve element (14) which is axially adjustable between a closed position and an open position in which the flow of fuel is enabled. According to the invention, it is provided that the valve element (14) comprises a first partial element (16) and at least one separate second partial element (17), which partial elements are hydraulically coupled to one another by means of a coupler space (38), and that the coupler space (38) is hydraulically connected only in one axial direction to the high-pressure region of the injector (1).

Description

Stand der TechnikState of the art

Die Erfindung betrifft einen Injektor, insbesondere einen Common-Rail-Injektor, gemäß dem Oberbegriff des Anspruchs 1.The invention relates to an injector, in particular a common rail injector, according to the preamble of claim 1.

Ein derartiger Injektor ist aus der WO 20051068820 A1 der Anmelderin bekannt. Bei dem bekannten Injektor ist ein mehrteiliges Ventilelement vorgesehen, dessen beide Teile über einen Kopplerraum hydraulisch miteinander gekoppelt sind. Dabei wird der Kopplerraum radial von einer Hülse begrenzt, die sich axial an die Stirnfläche eines zusätzlichen, separaten Gehäuseteils abstützt. Es sind daher relativ hohe Genauigkeiten an der Hülse sowie der stirnseitigen Anlagefläche an dem Gehäuseteil erforderlich, um die benötigte Dichtheit des Kopplerraums zu gewährleisten.Such an injector is from the WO 20051068820 A1 the applicant known. In the known injector, a multi-part valve element is provided, the two parts of which are hydraulically coupled to each other via a coupler space. In this case, the coupler space is bounded radially by a sleeve which is axially supported on the end face of an additional, separate housing part. There are therefore relatively high accuracies on the sleeve and the end-side contact surface on the housing part required to ensure the required tightness of the coupler space.

Aus der DE 100 24 703 A1 ist ein Common-Rail-Injektor bekannt, mit dem Kraftstoff direkt in einen diesem zugeordneten Brennraum einer Brennkraftmaschine eingespritzt werden kann. Hierzu ist in einem Gehäuse ein einteiliges Ventilelement angeordnet, welches eine insgesamt in Öffnungsrichtung des Ventilelements wirkende Druckfläche aufweist. Am entgegengesetzten Ende des Ventilelements ist eine in Schließrichtung wirkende Steuerfläche vorgesehen, welche einen Steuerraum begrenzt. Die in Schließrichtung wirkende Steuerfläche ist insgesamt größer als die bei geöffnetem Ventilelement in Öffnungsrichtung wirkende Druckfläche. Nachteilig bei dem bekannten Injektor ist, dass aufgrund der einteiligen Ausbildung des Ventilelementes enge Fertigungstoleranzen eingehalten werden müssen und unterschiedliche Durchmesserabschnitte an einem Bauteil realisiert werden müssen.From the DE 100 24 703 A1 is a common rail injector known, can be injected with the fuel directly into this associated combustion chamber of an internal combustion engine. For this purpose, a one-piece valve element is arranged in a housing, which has a total acting in the opening direction of the valve element pressure surface. At the opposite end of the valve element acting in the closing direction control surface is provided, which limits a control chamber. Overall, the control surface acting in the closing direction is larger than the pressure surface acting in the opening direction when the valve element is open. A disadvantage of the known injector that due to the one-piece design of the valve element tight manufacturing tolerances must be met and different diameter sections must be realized on a component.

Aus der DE 102 07 227 A1 ist ein Common-Rail-Injektor bekannt, dessen Ventilelement zweiteilig ausgeführt ist, wobei die beiden Bauteile (Steuerstange und Düsennadel) in einem dauerhaft mit einem Niederdruckbereich des Injektors verbundenen Niederdruckraum aneinander anliegen. Innerhalb des Niederdruckraums ist eine Durchmesserstufe des Ventilelementes realisiert, um die hydraulische Schließkraft zu erhöhen. Nachteilig bei dem bekannten Injektor sind die hohen Leckageverluste, die unweigerlich auftreten, da der Niederdruckraum in zwei Axialrichtungen über einen Führungsspalt mit dem Hochdruckbereich des Injektors verbunden ist und somit Kraftstoff in den Niederdruckraum (Teil des Injektomiederdruckbereichs) und von dort aus zu einer Rücklaufleitung strömen kann.From the DE 102 07 227 A1 a common rail injector is known, the valve element is designed in two parts, wherein the two components (control rod and nozzle needle) abut each other in a permanently connected to a low pressure region of the injector low pressure space. Within the low-pressure space, a diameter step of the valve element is realized to increase the hydraulic closing force. A disadvantage of the known injector are the high leakage losses, the inevitably occur, since the low-pressure chamber is connected in two axial directions via a guide gap with the high pressure region of the injector and thus fuel in the low-pressure chamber (part of Injektomiederdruckbereichs) and can flow from there to a return line.

Aus der nachveröffentlichten DE 10 205 034 599 ist ein Injektor bekannt, bei dem das Ventilelement zweiteilig ausgebildet ist, wobei die beiden Bauteile (Steuerstange und Düsennadel) über einen Kopplerraum hydraulisch miteinander verbunden sind. Da der Kopplerraum nicht mit einem Niederdruckbereich des Injektors verbunden ist, herrscht innerhalb des Kopplerraums ebenfalls ein hoher Kraftstoffdruck. Die hydraulische Kopplung bewirkt, dass die Düsennadel einer gesteuerten Bewegung der Steuerstange folgt.From the post-published DE 10 205 034 599 an injector is known in which the valve element is formed in two parts, wherein the two components (control rod and nozzle needle) are hydraulically connected to each other via a coupler space. Since the coupler space is not connected to a low-pressure region of the injector, there is also a high fuel pressure within the coupler space. The hydraulic coupling causes the nozzle needle to follow a controlled movement of the control rod.

Offenbarung der ErfindungDisclosure of the invention Technische AufgabeTechnical task

Der Erfindung liegt die Aufgabe zugrunde, einen Injektor nach dem Oberbegriff des Anspruchs 1 derart weiterzubilden, dass er konstruktiv besonders einfach aufgebaut und kostengünstig herstellbar ist.The invention has the object of developing an injector according to the preamble of claim 1 such that it is structurally particularly simple in construction and inexpensive to produce.

Technische LösungTechnical solution

Diese Aufgabe wird mit einem Injektor mit den Merkmalen des Anspruchs 1 gelöst. Die Unteransprüche geben günstige Weiterbildungen an.This object is achieved with an injector having the features of claim 1. The dependent claims indicate favorable developments.

Bevorzugt ist die Hülse an einem der beiden mittels des Kopplerraumes miteinander gekoppelten Teilelemente geführt und in Richtung des jeweils anderen Teilelementes federkraftbeaufschlagt. Zwischen dem Teilelement und der Hülse, an dem diese geführt ist, ist in axialer Richtung der einzige axiale Dicht- bzw. Führungsspalt ausgebildet, über den der Kopplerraum hydraulisch mit dem Druckbereich des Injektors verbunden ist. Mit ihrer Stirnseite liegt die Hülse an dem jeweils anderen Teilelement bzw. an einer Anlagefläche dieses Teilelementes an, so dass zwischen Hülse und Anlagefläche ein Dichtbereich gebildet wird. Dadurch, dass nur ein einziger Axialspalt vorgesehen ist, wodurch die während der Ansteuerung in den Kopplerraum fließende Kraftstoffmenge also reduziert ist, kann auf ein Öffnen der Dichthülse, also auf ein Abheben ihrer Stirnseite von der Anlagefläche eines der Teilelemente verzichtet werden, wodurch die Funktionssicherheit des Injektors erhöht wird.Preferably, the sleeve is guided on one of the two coupled by means of the coupler space sub-elements and spring-loaded in the direction of the respective other sub-element. Between the sub-element and the sleeve, on which it is guided, the only axial sealing or guide gap is formed in the axial direction, via which the coupler chamber is hydraulically connected to the pressure region of the injector. With its front side, the sleeve is located on the respective other sub-element or on a contact surface of this sub-element, so that between sleeve and contact surface a sealing area is formed. The fact that only a single axial gap is provided, so that the amount of fuel flowing during the control in the coupler space is thus reduced, can be dispensed with opening of the sealing sleeve, ie on lifting their front side of the contact surface of the sub-elements, whereby the reliability of Injector is increased.

Bevorzugt ist die auf die Hülse in axialer Richtung wirkende Feder derart angeordnet, dass diese in Öffnungsrichtung auf das von dem Brennraum weiter entfernte Teilelement, insbesondere die Steuerstange, wirkt. Der Feder wirkt eine Schließfeder entgegen, wobei die Federkraft der Schließfeder größer ist als die Federkraft der Hülsenfeder, so dass nur die Differenzfederkraft in Schließstellung wirkt, was sich positiv auf die Ansteuerung des Injektors auswirkt.Preferably, the force acting on the sleeve in the axial direction spring is arranged such that it acts in the opening direction on the further away from the combustion chamber sub-element, in particular the control rod. The spring counteracts a closing spring, wherein the spring force of the closing spring is greater than the spring force of the sleeve spring, so that only the differential spring force acts in the closed position, which has a positive effect on the control of the injector.

In Weiterbildung der Erfindung ist mit Vorteil vorgesehen, dass die Hülse nicht als separates Bauteil ausgebildet ist, sondern einstückig mit dem ersten oder dem zweiten Teilelement ausgebildet ist. Somit entfällt eine stirnseitige Dichtfläche sowie ein separates Bauteil, was sich wiederum positiv auf die Montierbarkeit und die Herstellungskosten auswirkt. Dadurch, dass die Hülse einstückig mit dem ersten oder dem zweiten Teilelement ausgebildet ist, befindet sich der Kopplerraum innerhalb des ersten und/oder des zweiten Teilelementes. Anders ausgedrückt, sind die beiden Teilelemente in axialer Richtung ineinander verschieblich geführt, wobei der einzige Axialspalt bei dieser Ausführungsform zwischen den beiden Teilelementen ausgebildet ist. Diese Bauweise ermöglicht es, eine Ferner axial zwischen den beiden Teilelementen anzuordnen, die sich jeweils an den gegenüberliegenden Stirnseiten abstützt. Die Federkraft ist dabei so zu bemessen, dass diese geringer ist, als die Federkraft einer auf eines der Teilelemente wirkenden Schließfeder.In a further development of the invention is advantageously provided that the sleeve is not formed as a separate component, but is integrally formed with the first or the second sub-element. Thus eliminates a frontal sealing surface and a separate component, which in turn has a positive effect on the mountability and the manufacturing cost. Characterized in that the sleeve is formed integrally with the first or the second sub-element, the coupler space is within the first and / or the second sub-element. In other words, the two sub-elements are slidably guided in the axial direction, wherein the single axial gap is formed in this embodiment between the two sub-elements. This construction makes it possible to arrange a further axially between the two sub-elements, which is supported in each case on the opposite end faces. The spring force is to be dimensioned so that it is less than the spring force a closing spring acting on one of the sub-elements.

Bevorzugt ist ein Axialanschlag für das weiter von dem Brennraum entfernte Teilelement, insbesondere die Steuerstange, vorgesehen, so dass sich im Ruhezustand bei auf dem Nadelsitz aufliegender Düsennadel ein Spalt zwischen den beiden Teilelementen einstellt. Hierdurch wird die Anschlagmasse im Nadelsitz verringert, da nicht das gesamte Ventilelement, sondern lediglich die Düsennadel auf den Nadelsitz gepresst wird.Preferably, an axial stop is provided for the subelement further away from the combustion chamber, in particular the control rod, so that a gap is established between the two subelements when the nozzle needle rests on the needle seat when at rest. As a result, the stop mass is reduced in the needle seat, since not the entire valve element, but only the nozzle needle is pressed onto the needle seat.

Kurze Beschreibung der ZeichnungenBrief description of the drawings

Weitere Vorteile, Merkmale und Einzelheiten der Erfindung ergeben sich aus der nachfolgenden Beschreibung bevorzugter Ausführungsbeispiele sowie anhand der Zeichnung; diese zeigt in

  • Fig. 1: einen Injektor mit einem Ventilelement, umfassend eine Steuerstange und eine Düsennadel, die über einen von einer Hülse begrenzten Kopplerraum hydraulisch miteinander gekoppelt sind, wobei die Hülse sich in axialer Richtung an einer Anlagefläche der Steuerstange abstützt,
  • Fig. 2: ein weiteres Ausführungsbeispiel eines Injektors mit einem Ventilelement mit einer Steuerstange und einer mit dieser hydraulisch gekoppelten Düsennadel, wobei eine einen Kopplerraum begrenzende Hülse in axialer Richtung auf eine Anlagefläche der Düsennadel federkraftbeaufschlagt ist,
  • Fig. 3: einen Injektor, mit einem Ventilelement mit einer Steuerstange und einer Düsennadel, wobei ein hydraulischer Kopplerraum innerhalb der Steuerstange ausgebildet ist und die Düsennadel in axialer Richtung innerhalb der Steuerstange geführt ist und
  • Fig. 4: einen Injektor mit einem Ventilelement mit einer Steuerstange und einer Düsennadel, wobei die Düsennadel innerhalb der Steuerstange geführt ist und im Vergleich zur Steuerstange eine wesentlich geringere Masse aufweist.
Further advantages, features and details of the invention will become apparent from the following description of preferred embodiments and from the drawing; this shows in
  • Fig. 1 an injector having a valve element, comprising a control rod and a nozzle needle, which are hydraulically coupled to one another via a coupling space delimited by a sleeve, the sleeve being supported in the axial direction on a contact surface of the control rod,
  • Fig. 2 A further exemplary embodiment of an injector having a valve element with a control rod and a nozzle needle hydraulically coupled thereto, wherein a sleeve delimiting a coupler space is spring-loaded in the axial direction onto a contact surface of the nozzle needle,
  • Fig. 3 an injector having a valve member with a control rod and a nozzle needle, wherein a hydraulic coupler space within the control rod is formed and the nozzle needle is guided in the axial direction within the control rod and
  • Fig. 4 an injector having a valve element with a control rod and a nozzle needle, wherein the nozzle needle is guided within the control rod and compared to the control rod has a much lower mass.

Ausführungsformen der ErfindungEmbodiments of the invention

In den Figuren sind gleiche Bauteile und Bauteile mit der gleichen Funktion mit den gleichen Bezugszeichen gekennzeichnet.In the figures, the same components and components with the same function with the same reference numerals.

In Fig. 1 ist ein Common-Rail-Injektor 1 zum Einspritzen von Kraftstoff in Brennräume von Brennkraftmaschinen dargestellt. Der Injektor 1 wird über eine Hochdruckversorgungsleitung 2 von einem Kraftstoff-Hochdruckspeicher 3 (Rail) mit unter hohem Druck (etwa 1800 bis 2000 bar) stehendem Kraftstoff, insbesondere Dieselöl oder Benzin, versorgt. Der Kraftstoff-Hochdruckspeicher 3 wird von einer, insbesondere als Radialkolbenpumpe ausgebildeten Hochdruckpumpe 4 mit Kraftstoff aus einem auf Niederdruck liegendem Vorratsbehälter 5 versorgt. Ein Niederdruckbereich 6 des Injektors ist über eine Rücklaufleitung 7 mit dem Vorratsbehälter 5 hydraulisch verbunden. Der Druck im Niederdruckbereich des Injektors beträgt je nach Betriebszustand zwischen etwa 0 und 10 bar. Über die Rücklaufleitung 7 wird eine Kraftstoff-Steuermenge aus einer Steuerkammer 8 abgeführt und über die Hochdruckpumpe 4 dem Hoch druckkreislauf wieder zugeführt.In Fig. 1 a common rail injector 1 for injecting fuel into combustion chambers of internal combustion engines is shown. The injector 1 is supplied via a high-pressure supply line 2 from a high-pressure fuel accumulator 3 (rail) with fuel at high pressure (about 1800 to 2000 bar), in particular diesel oil or gasoline. The high-pressure fuel accumulator 3 is supplied with fuel from a low-pressure reservoir 5 by a high-pressure pump 4 designed in particular as a radial piston pump. A low-pressure region 6 of the injector is hydraulically connected via a return line 7 to the reservoir 5. Depending on the operating condition, the pressure in the low-pressure region of the injector is between approximately 0 and 10 bar. About the return line 7, a fuel control amount is discharged from a control chamber 8 and fed via the high-pressure pump 4 the high-pressure circuit again.

Der Injektorkörper 1 weist einen Injektorkörper 9 und einen Düsenkörper 10 auf, wobei der Injektorkörper 9 und der Düsenkörper 10 über eine nicht dargestellte Düsenspannmutter, welche mit dem Injektorkörper 9 verschraubbar ist, gegeneinander verspannbar sind, wobei die nicht gezeigte Düsenspannmutter von dem Düsenkörper 10 in axialer Richtung durchsetzt ist.The injector body 1 has an injector body 9 and a nozzle body 10, the injector body 9 and the nozzle body 10 via a nozzle retaining nut, not shown, which is screwed to the injector body 9, are braced against each other, wherein the nozzle retaining nut, not shown, is penetrated by the nozzle body 10 in the axial direction.

Innerhalb des Düsenkörpers 10 ist eine Stufenbohrung 11 eingebracht, die sich in axialer Richtung in einer Bohrung 12 in dem Injektorkörper 9 fortsetzt. Innerhalb der Bohrungen 11, 12 ist ein zum Hochdruckbereich des Injektors 1 gehörender Druckraum 13 ausgebildet, in dem in axialer Richtung ein Ventilelement 14 längsverschieblich geführt ist. Das Ventilelement 14 weist eine die Steuerkammer 8 mit einer Stirnfläche 15 begrenzende Steuerstange 16 und eine axial in Richtung Brennraum benachbarte Düsennadel 17 auf. An einer Nadelspitze 18 weist die Düsennadel 17 eine Schließfläche 19 auf, mit welcher sie in dichte Anlage an einen innerhalb des Düsenkörpers 10 ausgebildeten Nadelsitz 20 bringbar ist.Within the nozzle body 10, a stepped bore 11 is introduced, which continues in the axial direction in a bore 12 in the injector 9. Within the bores 11, 12 a belonging to the high-pressure region of the injector 1 pressure chamber 13 is formed, in which in the axial direction, a valve member 14 is guided longitudinally displaceable. The valve element 14 has a control rod 8 with an end face 15 limiting control rod 16 and an axially adjacent to the combustion chamber nozzle needle 17. At a needle tip 18, the nozzle needle 17 has a closing surface 19 with which it can be brought into tight contact with a needle seat 20 formed within the nozzle body 10.

Wenn die Düsennadel 17 am Nadelsitz 20 anliegt, d.h. sich in einer Schließstellung befindet, ist der Kraftstoffaustritt aus einer Düsenlochanordnung 21 gesperrt. Ist sie dagegen vom Nadelsitz 20 angehoben, kann Kraftstoff aus dem als Ringraum ausgebildeten Druckraum 13 an dem Nadelsitz 20 vorbei zur Düsenlochanordnung 21 strömen und dort im Wesentlichen unter dem Hochdruck (Raildruck) stehend in einen nicht gezeigten Brennraum gespritzt werden.When the nozzle needle 17 abuts the needle seat 20, i. is in a closed position, the fuel outlet from a nozzle hole arrangement 21 is locked. If, on the other hand, it is lifted by the needle seat 20, fuel can flow from the pressure space 13 formed as an annular space past the needle seat 20 to the nozzle hole arrangement 21 and be sprayed there substantially under the high pressure (rail pressure) into a combustion chamber (not shown).

Die Düsennadel ist 17 in einem Axialabschnitt 22 mehreckig konturiert und an der kreisförmig konturierten Stufenbohrungswand des Düsenkörpers 10 geführt, so dass gleichmäßig über den Umfang verteilte Axialkanäle 23 gebildet sind, durch die der Kraftstoff innerhalb des Druckraums 13 in axialer Richtung von dem Mündungsbereich der Hochdruckversorgungsleitung 2 bis zur Düsenlochanordnung 21 bei geöffnetem Ventilelement 16 strömen kann.The nozzle needle 17 is polygonal contoured in an axial section 22 and guided on the circular contoured stepped bore wall of the nozzle body 10 so that evenly distributed over the circumference Axialkanäle 23 are formed by the fuel within the pressure chamber 13 in the axial direction of the mouth region of the high-pressure supply line 2 can flow to the nozzle hole assembly 21 with the valve element 16 open.

Am unteren Ende des Axialabschnitts 22 ist eine im Wesentlichen konisch ausgeformte Druckangriffsfläche 24 ausgebildet, auf die eine Druckkraft in Öffnungsrichtung wirkt.At the lower end of the axial section 22, a substantially conically shaped pressure application surface 24 is formed, on which a compressive force acts in the opening direction.

Dieser Öffnungskraft wirkt zeitweise eine Schließkraft auf die Stirnfläche 15 innerhalb der Steuerkammer 8 entgegen. Die Steuerkammer 8 ist über eine Zulaufdrossel 25 innerhalb eines hülsenförmigen Bauteils 26 mit dem Druckraum 13 hydraulisch verbunden. Über eine Ablaufdrossel 27 ist die von dem hülsenförmigen Bauteil 26 radial begrenzte Steuerkammer 8 mit dem Niederdruckbereich 6 verbindbar. Der die Ablaufdrossel 27 aufweisende Ablaufkanal 28, durch den Kraftstoff zeitweise in dem Niederdruckraum 6 abströmen kann, ist dabei durch eine Zylinderplatte 29 hindurchgeführt. Das hülsenförmige Bauteil 26 wiederum ist von einer Schließfeder 30 in axialer Richtung auf die fest innerhalb des Injektors 1 verspannte Zylinderplatte 29 vorgespannt. Die Schließfeder 30 stützt sich hierzu in axialer Richtung an einem Umfangsbund 31 der Steuerstange 16 ab, wodurch dauerhaft eine Schließkraft auf die Steuerstange 16 einwirkt.This opening force temporarily counteracts a closing force on the end face 15 within the control chamber 8. The control chamber 8 is hydraulically connected via an inlet throttle 25 within a sleeve-shaped component 26 with the pressure chamber 13. Via an outlet throttle 27, the radially limited by the sleeve-shaped member 26 control chamber 8 with the low pressure region 6 is connected. The outlet throttle 27 having flow channel 28, can flow through the fuel temporarily in the low-pressure chamber 6, is passed through a cylinder plate 29. The sleeve-shaped component 26 in turn is biased by a closing spring 30 in the axial direction of the tightly clamped inside the injector 1 cylinder plate 29. The closing spring 30 is supported for this purpose in the axial direction on a peripheral collar 31 of the control rod 16, whereby a closing force on the control rod 16 acts permanently.

Damit Kraftstoff aus der Steuerkammer 8 in den Niederdruckbereich 6 abströmen wodurch die auf die Stirnfläche 15 der Steuerstange 16 wirkende Druckkraft reduziert wird, ist ein Steuerventil 32 vorgesehen, welches einen elektromagnetischen Aktuator 33 aufweist, der mit einer Ankerplatte 34 zusammenwirkt. Dabei ist die Ankerplatte 34 fest mit einem Ventilkörper 35 verbunden, welcher wiederum in axialer Richtung kraftbeaufschlagend auf eine Ventilkugel 36 einwirkt. Bei Bestromung des Aktuators 33 hebt der Ventilkörper 35 und damit die Ventilkugel 36 von einem an der Zylinderplatte 29 ausgebildeten Ventilsitz 36 ab, so dass Kraftstoff über die Ablaufdrossel aus der Steuerkammer 8 in den Niederdruckbereich 6 und von dort aus über die Rücklaufleitung 7 abströmen kann. Dabei sind die Durchflussquerschnitte der Zulaufdrossel 25 und der Ablaufdrossel 27 so aufeinander abgestimmt, dass der Zufluss in die Steuerkammer 8 aus dem Druckraum 13 schwächer ist, als der Abfluss aus der Steuerkammer 8 in den Niederdruckbereich und demnach bei geöffnetem Steuerventil 32 ein Nettoabfluss von Kraftstoff aus der Steuerkammer 8 resultiert. Der daraus folgende Druckabfall in der Steuerkammer 8 bewirkt, dass der Betrag der Schließkraft unter den Betrag der Öffnungskraft sinkt und das Ventilelement 14 vom Nadelsitz 20 abhebt.In order for fuel to flow out of the control chamber 8 into the low-pressure region 6, whereby the pressure force acting on the end face 15 of the control rod 16 is reduced, a control valve 32 is provided which has an electromagnetic actuator 33 which cooperates with an armature plate 34. In this case, the anchor plate 34 is fixedly connected to a valve body 35, which in turn acts in the axial direction kraftbeaufschlagend on a valve ball 36. When current flows through the actuator 33, the valve body 35 and thus the valve ball 36 lifts off from a valve seat 36 formed on the cylinder plate 29, so that fuel can flow via the outlet throttle from the control chamber 8 in the low pressure region 6 and from there via the return line 7. The flow cross-sections of the inlet throttle 25 and the outlet throttle 27 are coordinated so that the inflow into the control chamber 8 from the pressure chamber 13 is weaker than the outflow from the control chamber 8 in the low pressure region and thus with open control valve 32, a net outflow of fuel the control chamber 8 results. The resulting pressure drop in the control chamber 8 causes the amount of the closing force falls below the amount of the opening force and the valve element 14 lifts from the needle seat 20.

Die Steuerstange 16 und die Düsennadel 17 sind über einen hydraulischen Kopplerraum 38 ausschließlich hydraulisch miteinander gekoppelt. Hierdurch folgt die Düsennadel 17 einer Öffnungsbewegung und einer Schließbewegung der Steuerstange 16. Der Durchmesser D1 der Düsennadel 17 innerhalb der den Kopplerraum 38 begrenzenden Hülse 39 ist geringer als der in dem hülsenförmigen Bauteil 26 geführte Durchmesser D2 der Steuerstange 16. Der Kopplerraum 38, der keine Verbindung zu dem Niederdruckbereich des Injektors 1 aufweist, ist mit Kraftstoff gefüllt und radial innerhalb des Druckraums 13 angeordnet, so dass auch innerhalb des Kopplerraums 38 näherungsweise Raildruck herrscht. Der Kopplerraum 38 ist radial von einer Hülse 39 begrenzt, innerhalb der axial verschieblich die Düsennadel 17 geführt ist. Zwischen Düsennadel 17 und Hülse 39 ist ein kreisförmig konturierter Axialspalt 40 (Führungs- bzw. Dichtspalt) ausgebildet. Hierbei handelt es sich um den einzigen Führungsspalt, über den der Kopplerraum 38 mit dem Hochdruckbereich, insbesondere dem Druckraum 13 verbunden ist.The control rod 16 and the nozzle needle 17 are hydraulically coupled to each other via a hydraulic coupler 38 only. As a result, the nozzle needle 17 follows an opening movement and a closing movement of the control rod 16. The diameter D1 of the nozzle needle 17 within the sleeve 39 delimiting the coupler space 38 is less than the diameter D2 of the control rod 16 guided in the sleeve-shaped component 26. The coupler space 38, which has no Connection to the low pressure region of the injector 1 is filled with fuel and disposed radially within the pressure chamber 13, so that there is approximately rail pressure within the coupler space 38. The coupler space 38 is bounded radially by a sleeve 39 within which the nozzle needle 17 is guided in an axially displaceable manner. Between nozzle needle 17 and sleeve 39, a circular contoured axial gap 40 (guide or sealing gap) is formed. This is the only guide gap, via which the coupler space 38 is connected to the high pressure area, in particular the pressure space 13.

Die Hülse 39 ist mittels einer Schraubenfeder 41, welche sich axial an einer Ringschulter 42 der Stufenbohrung 11 innerhalb des Düsenkörpers 10 abstützt in axialer Richtung auf eine Anlagefläche 43 an der der Stirnfläche 15 gegenüberliegenden Stirnseite 44 der Steuerstange 16 federkraftbeaufschlagt. Die Anlagefläche 43 ist dabei an einem in radialer Richtung verbreiterten Absatz 45 der Steuerstange 16 ausgebildet. Aufgrund der Federkraft der Feder 41 liegt die Hülse 39 dichtend an der Anlagefläche 43 an. Die Feder 41 beaufschlagt die Steuerstange 16 über die Hülse 39 in Öffnungsrichtung mit einer Federkraft, die der Federkraft der Schließfeder 30 entgegenwirkt. Dabei ist die Feder 41 schwächer ausgelegt, als die Schließfeder 30, so dass insgesamt dauerhaft in Schließrichtung eine geringe resultierende Federkraft auf das Ventilelement 14 wirkt. Da die Schließfeder 30 stärker ausgelegt ist als die Feder 41, erfolgt die Rückstellung der Steuerstange 16 nach dem Einspritzvorgang über die große Federkraft der Schließfeder 30, wodurch ein Rückstellen der Steuerstange ohne ein Öffnen der Hülse 39, also ein Abheben der Hülse 39 von der Anlagefläche 23 gewährleistet ist. Zur Optimierung der Schließgeschwindigkeit der Düsennadel kann beispielsweise im Bereich des Axialabschnitts 22 eine geringfügige Kraftstoffdrossel vorgesehen werden.The sleeve 39 is spring-loaded by means of a helical spring 41, which is supported axially on an annular shoulder 42 of the stepped bore 11 within the nozzle body 10 in the axial direction on a contact surface 43 on the front face 15 opposite end face 44 of the control rod. The contact surface 43 is formed on a widened in the radial direction paragraph 45 of the control rod 16. Due to the spring force of the spring 41, the sleeve 39 is sealingly against the contact surface 43. The spring 41 acts on the control rod 16 via the sleeve 39 in the opening direction with a spring force which counteracts the spring force of the closing spring 30. Here, the spring 41 is designed to be weaker than the closing spring 30, so that a total of permanently acting in the closing direction, a small resultant spring force on the valve element 14. Since the closing spring 30 is designed to be stronger than the spring 41, the return of the control rod 16 after the injection process via the large spring force of the closing spring 30, whereby a reset of the control rod without opening the sleeve 39, so lifting the sleeve 39 of the contact surface 23 is guaranteed. To optimize the closing speed of the nozzle needle, for example, a slight fuel throttle may be provided in the region of the axial section 22.

Im Folgenden wird das Ausführungsbeispiel gemäß Fig. 2 näher erläutert. Dabei wird im Wesentlichen nur auf die Unterschiede zu dem Ausführungsbeispiel gemäß Fig. 1 eingegangen. Zur Vermeidung von Wiederholungen wird bezüglich der Gemeinsamkeiten auf die vorherige Beschreibung verwiesen.In the following, the embodiment according to Fig. 2 explained in more detail. It is essentially only on the differences from the embodiment according to Fig. 1 received. To avoid repetition, reference is made to the previous description for similarities.

In Fig. 2 ist aus Übersichtlichkeitsgründen der Kraftstoffkreislauf nur teilweise dargestellt. Bei dem gezeigten Ausführungsbeispiel ist der Kopplerraum 38 ebenfalls durch eine Hülse 39 begrenzt. Die Feder 41 stützt sich jedoch nicht an einer Ringschulter der Stufenbohrung 11, sondern an einem radial verbreiterten Abschnitt 46 der Steuerstange 16 ab, wodurch die Hülse 39 in axialer Richtung auf eine den Brennraum abgewandte Anlagefläche 47 der Düsennadel 17 federkraftbeaufschlagt wird. Dabei ist die Anlagefläche 47 an einem in radialer Richtung verbreiterten Abschnitt 48 der Ventilnadel 17 ausgebildet.In Fig. 2 For reasons of clarity, the fuel circuit is only partially shown. In the embodiment shown, the coupler space 38 is also bounded by a sleeve 39. However, the spring 41 is not supported an annular shoulder of the stepped bore 11, but at a radially widened portion 46 of the control rod 16, whereby the sleeve 39 in the axial direction on a combustion chamber facing away from abutment surface 47 of the nozzle needle 17 is spring-loaded. In this case, the contact surface 47 is formed on a widened in the radial direction portion 48 of the valve needle 17.

Der Abschnitt 46 der Steuerstange 16 bildet einen Axialanschlag für die Steuerstange 16 an dem Düsenkörper 10, so dass in dem gezeigten Ruhezustand (die Düsennadel 17 liegt auf dem Nadelsitz 20 auf und die Steuerkammer 8 ist bei geschlossenem Steuerventil 32 mit Hochdruck beaufschlagt) ein Spalt 49 zwischen Düsennadel 17 und Steuerstange 16 ausgebildet ist. Um einen Durchfluss von Kraftstoff innerhalb des Druckraumes 13 in axialer Richtung bis zu dem Nadelsitz 20 zu gewährleisten, sind innerhalb des Abschnittes 46 axiale Durchbrüche 50 vorgesehen. Durch das Vorsehen des Anschlages (Abschnitt 46) wird die Anschlagmasse des Ventilelementes im Nadelsitz 20 reduziert, da nicht das gesamte Ventilelement 14 am Ende der Schließbewegung am Nadelsitz 20 anschlägt, woraus wiederum ein reduzierter Verschleiß resultiert.The section 46 of the control rod 16 forms an axial stop for the control rod 16 on the nozzle body 10, so that in the idle state shown (the nozzle needle 17 rests on the needle seat 20 and the control chamber 8 is pressurized with the control valve 32 closed) a gap 49th between the nozzle needle 17 and the control rod 16 is formed. In order to ensure a flow of fuel within the pressure chamber 13 in the axial direction to the needle seat 20, axial openings 50 are provided within the section 46. By providing the stop (section 46), the stop mass of the valve element in the needle seat 20 is reduced because not the entire valve element 14 abuts the needle seat 20 at the end of the closing movement, which in turn results in reduced wear.

Der einzige Axialspalt, der den Kopplerraum 38 hydraulisch mit dem Druckraum 13 verbindet, ist zwischen Steuerstange 16 und der an diesem geführten Hülse 39 ausgebildet.The only axial gap which connects the coupler chamber 38 hydraulically to the pressure chamber 13 is formed between the control rod 16 and the sleeve 39 guided thereon.

Bei dem Ausführungsbeispiel gemäß Fig. 3 ist keine separate Hülse zur Begrenzung des Kopplerraums 38 vorgesehen. Der Kopplerraum 38 ist innerhalb der Steuerstange 16 ausgebildet. Die Düsennadel 17 ist in einem hülsenförmigen Fortsatz 51 der Steuerstange 16 geführt. Die Feder 41 stützt sich in axialer Richtung zum einen an der Ringschulter 42 des Düsenkörpers 10 und andererseits stirnseitig an dem hülsenförmigen Fortsatz 51 ab, wodurch die Steuerstange 16 in Öffnungsrichtung federkraftbeaufschlagt wird. Auch hier ist die Feder 41 schwächer ausgelegt als die ebenfalls auf die Steuerstange 16 wirkende Schließfeder 30. Der einzige, den Kopplerraum 38 mit dem Hochdruckbereich verbindende Axialspalt 40 ist bei dem gezeigten Ausführungsbeispiel zwischen Außenfläche der Düsennadel 17 und Innenumfangsfläche des hülsenförmigen Fortsatzes 51 ausgebildet.In the embodiment according to Fig. 3 no separate sleeve for limiting the coupler space 38 is provided. The coupler space 38 is formed within the control rod 16. The nozzle needle 17 is guided in a sleeve-shaped extension 51 of the control rod 16. The spring 41 is supported in the axial direction on the one hand on the annular shoulder 42 of the nozzle body 10 and on the other hand frontally on the sleeve-shaped extension 51, whereby the control rod 16 in the opening direction is subjected to spring force. Again, the spring 41 is designed to be weaker than the also acting on the control rod 16 closing spring 30. The only, the coupler chamber 38 with the high-pressure region connecting axial gap 40 is formed in the embodiment shown between the outer surface of the nozzle needle 17 and inner peripheral surface of the sleeve-shaped extension 51.

Um Querkräfte auf die Düsennadel 17 zu verringern, ist es, anders als in Fig. 3 dargestellt, denkbar, die Steuerstange 16 innerhalb des Düsenkörpers 10 in axialer Richtung zu führen.To reduce lateral forces on the nozzle needle 17, it is, unlike in Fig. 3 illustrated, conceivable to guide the control rod 16 within the nozzle body 10 in the axial direction.

Bei dem letzten Ausführungsbeispiel gemäß Fig. 4 ist der Kopplerraum 38, ähnlich wie in Fig. 3 innerhalb eines hülsenförmigen Fortsatzes 51 der Steuerstange 16 ausgebildet. Hier ist die Steuerstange 16 mit einem mehreckig konturierten Abschnitt 21 innerhalb des Düsenkörpers 10 in axialer Richtung geführt, um Querkräfte auf die Düsennadel 17 zu vermeiden. Die Düsennadel ist wesentlich kleiner ausgeführt als die Steuerstange 16, wodurch sich eine geringe Masse im Nadelsitz ergibt. Die Feder 41 stützt sich einerseits an der Steuerstange 16 und andererseits an der Düsennadel 17 ab. Im gezeigten Ruhezustand ist zwischen Steuerstange 16 und Düsennadel 17 ein Spalt 49 vorgesehen.In the last embodiment according to Fig. 4 is the coupler space 38, similar to in Fig. 3 formed within a sleeve-shaped extension 51 of the control rod 16. Here, the control rod 16 is guided with a polygonal contoured portion 21 within the nozzle body 10 in the axial direction to avoid lateral forces on the nozzle needle 17. The nozzle needle is designed substantially smaller than the control rod 16, resulting in a small mass in the needle seat. The spring 41 is supported on the one hand on the control rod 16 and on the other hand on the nozzle needle 17. In the rest state shown, a gap 49 is provided between the control rod 16 and the nozzle needle 17.

Claims (7)

  1. Injector for injecting fuel into combustion chambers of internal combustion engines, in particular common-rail injector (1), having a high pressure region and having a valve element (14) which can be adjusted axially between a closed position and an open position which releases the fuel flow, the valve element (14) comprising a first part element (16, 17) and at least one separate second part element (17, 16) which are coupled hydraulically to one another via a coupler space (38), the coupler space (38) being connected hydraulically to the high pressure region of the injector (1) only in one axial direction, the coupler space (38) being connected exclusively to the high pressure region of the injector (1), and the coupler space (38) being delimited radially by a sleeve (39), characterized in that the sleeve (39) rests either on a first bearing face (43), in particular the end side (44) of the first part element (16, 17), or on a second bearing face (47), in particular the end side of the second part element (17, 16).
  2. Injector according to Claim 1, characterized in that the sleeve (39) is guided axially either on the first part element (16, 17) or only on the second part element (16, 17).
  3. Injector according to Claim 1, characterized in that the sleeve (39) is loaded with a spring force by means of a spring (41) in the axial direction onto the first or the second bearing face (43, 47).
  4. Injector according to Claim 1, characterized in that the spring (41) is arranged so as to act on the first or the second part element (16, 17) in the opening direction, counter to the force of a closing spring (30).
  5. Injector according to Claim 1, characterized in that the coupler space (38) is arranged within the first and/or the second part element (16, 17).
  6. Injector according to either of Claims 4 and 5, characterized in that an axial stop (46) is provided for the first and/or the second part element (16, 17), and a gap is preferably provided in the rest state between those end sides of the part elements (16, 17) which face one another.
  7. Injector according to one of the preceding claims, characterized in that the first part element (16, 17) is configured as a control rod (16) which is operatively connected to a control chamber, and the second part element (17, 16) is configured as a nozzle needle (17) which interacts sealingly with a needle seat (20).
EP07847880A 2007-01-09 2007-12-06 Injector for injecting fuel into combustion chambers of internal combustion engines Not-in-force EP2108080B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007001363A DE102007001363A1 (en) 2007-01-09 2007-01-09 Injector for injecting fuel into combustion chambers of internal combustion engines
PCT/EP2007/063393 WO2008083881A1 (en) 2007-01-09 2007-12-06 Injector for injecting fuel into combustion chambers of internal combustion engines

Publications (2)

Publication Number Publication Date
EP2108080A1 EP2108080A1 (en) 2009-10-14
EP2108080B1 true EP2108080B1 (en) 2012-05-30

Family

ID=38965774

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07847880A Not-in-force EP2108080B1 (en) 2007-01-09 2007-12-06 Injector for injecting fuel into combustion chambers of internal combustion engines

Country Status (6)

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US (1) US8069840B2 (en)
EP (1) EP2108080B1 (en)
JP (2) JP5284277B2 (en)
CN (1) CN101578445B (en)
DE (1) DE102007001363A1 (en)
WO (1) WO2008083881A1 (en)

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Also Published As

Publication number Publication date
US8069840B2 (en) 2011-12-06
JP2013007389A (en) 2013-01-10
JP5627656B2 (en) 2014-11-19
CN101578445A (en) 2009-11-11
WO2008083881A1 (en) 2008-07-17
DE102007001363A1 (en) 2008-07-10
CN101578445B (en) 2014-04-09
JP2010515853A (en) 2010-05-13
US20100050990A1 (en) 2010-03-04
EP2108080A1 (en) 2009-10-14
JP5284277B2 (en) 2013-09-11

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