EP2195522A1 - Injector having a sleeve-shaped control valve element - Google Patents

Injector having a sleeve-shaped control valve element

Info

Publication number
EP2195522A1
EP2195522A1 EP08804280A EP08804280A EP2195522A1 EP 2195522 A1 EP2195522 A1 EP 2195522A1 EP 08804280 A EP08804280 A EP 08804280A EP 08804280 A EP08804280 A EP 08804280A EP 2195522 A1 EP2195522 A1 EP 2195522A1
Authority
EP
European Patent Office
Prior art keywords
injector
valve sleeve
valve
channel
fuel
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.)
Granted
Application number
EP08804280A
Other languages
German (de)
French (fr)
Other versions
EP2195522B1 (en
Inventor
Nadja Eisenmenger
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
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 EP2195522A1 publication Critical patent/EP2195522A1/en
Application granted granted Critical
Publication of EP2195522B1 publication Critical patent/EP2195522B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • 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 for injecting fuel into a combustion chamber of an internal combustion engine, in particular a common rail injector, according to the preamble of claim 1.
  • a common rail injector with a pressure-balanced control valve in the axial direction is known.
  • the control valve which has a sleeve-shaped control valve element
  • the fuel pressure can be influenced within a control chamber bounded on the end side by an injection valve element.
  • the injection valve element is adjusted between an open position and a closed position, wherein the injection valve element releases the fuel flow into the combustion chamber of an internal combustion engine in its open position.
  • the sleeve-shaped control valve element is connected to an anchor plate, which cooperates with an electromagnetic actuator for adjusting the sleeve-shaped control valve element.
  • the invention is therefore based on the object to propose an improved injector in which the of the open with the control valve in the direction of
  • the invention is based on the idea of acting on the anchor plate flow forces of when open Control valve (servo-valve) in the direction of the Inj ektor Weglaufan gleiches flowing fuel to minimize or preferably completely avoid that the fuel, at least one partial flow of fuel, with open control valve through a channel within the valve sleeve in the axial direction in the direction of ej ektorschreiblaufan gleiches flows.
  • the fuel thus flows within the valve sleeve, possibly additionally inside the armature plate on the armature plate in the axial direction radially inward past without flow forces that could affect the switching behavior of the injector, act on the armature plate.
  • the fuel flowing out of the control chamber when the control valve is open (control quantity) does not have to be in the axial direction by providing the channel within the valve sleeve or along the large, the control valve seat facing (lower) surfaces of the anchor plate
  • Control valve element of the control valve arranged channel has an optimized switching behavior, as avoided by the flowing out of the control chamber in the direction of the ej ektor Weglaufan gleiches fuel in known injectors valve sleeve vibrations.
  • the optimized switching behavior is characterized in particular by minimized injection tolerances.
  • the valve sleeve of the control valve is operatively connected to a formed according to the concept of the invention injector with the valve sleeve, that is, either integrally formed with this or, in particular form-fitting, connected thereto.
  • the control valve when this rests against its control valve seat, is pressure balanced in the axial direction.
  • sealing edge is arranged on the inner circumference of the valve sleeve, so that a pressure step on the valve sleeve, which would cause an opening force on the valve sleeve, is avoided.
  • the provision of a centric, extending within the valve sleeve in the axial direction channel for discharging at least a subset, preferably the total amount of fuel flowing in the direction of the injector return port with open control valve fuel allows the realization of a particularly preferred embodiment of the injector, wherein the Inj ektor Weglaufan gleich to Connecting the injector to a return line for a fuel control amount is arranged centrally on a side facing away from the combustion chamber end face (cover) of the injector.
  • Such an arrangement of the injector return connection (low-pressure connection) can be produced cost-effectively and, above all, permits a simple assembly of the injector connections on the internal combustion engine.
  • asymmetrical deformations are avoided by the injector internal pressure due to a substantially coaxial injector configuration with an injector return port arranged centrally on one end side.
  • Valve sleeve is sufficient, so the fuel from the front side of the
  • Anchor plate flows out. It is according to a first
  • the channel is extended in such a way that it does not open directly into the armature space but into a central duct arranged above the armature space in an electromagnet arrangement of the actuator.
  • a pressure pin is arranged, which is designed as a separate component from the control valve seat having the component.
  • This pressure pin is either supported on an injector component which is at a distance from the control valve seat, preferably in a spring-assisted manner, or is formed integrally with an injector component which is at a distance from the control valve seat.
  • the task of the separate pressure pin is to absorb the compressive forces acting in the axial direction, support and thereby seal the inner cross-section of the valve sleeve high-pressure tight in the axial direction, so that when the control valve is closed, ie at the control valve seat fitting valve sleeve, no fuel from the control chamber Injector return can flow.
  • the pressure pin integral with the Injector component is formed, on which also the control valve seat is located.
  • the channel is formed within the valve sleeve as an annular channel which is radially outwardly of the inner circumference of the valve sleeve and radially inwardly of the, preferably centrally disposed within the valve sleeve, pressure pin is limited.
  • the pressure pin has a thickened (lower) end portion which serves as a high pressure seal for sealing the inner cross section of the valve sleeve in the axial direction (up).
  • a thickened end portion of the channel does not extend, but begins in an axial direction seen adjacent to the thickened end portion adjacent, thin portion of the pressure pin, which preferably extends in the axial direction to a spaced from the control valve member member and at this is supported in the axial direction or formed integrally therewith.
  • the diameter of the thickened end portion is at least approximately the inner diameter of the valve sleeve.
  • the thinned portion has a smaller diameter than the thickened end portion, which is dimensioned such that on the one hand results in a channel of sufficient cross-section for the derivation of the fuel tax and on the other strength problems are avoided.
  • the pressure pin can be formed both one-piece and multi-part. In a development of the invention, it is advantageously provided that at least one axial passage leading to the injector return is provided in the component on which the pressure pin is supported in the axial direction.
  • the component on which the pressure pin is supported is preferably located within a central channel arranged in an electromagnet arrangement, which leads directly to the injector return.
  • the control valve seat is surrounded by an annular space in the fuel with open control valve can flow from within the valve sleeve in the radial direction, said annular space is hydraulically connected to the disposed within the valve sleeve channel.
  • the hydraulic connection between the annular space and the channel disposed within the valve sleeve is designed as at least one bore, preferably as at least one radial bore, which leads from the annular space in the disposed within the valve sleeve channel for discharging the fuel.
  • annular space is limited in the axial direction and possibly also in the radial direction of a component which is designed as a guide member for guiding the valve sleeve on its outer periphery.
  • This guide component is preferably designed as a separate component from the component having the control valve seat, so that the guide for the axially adjustable valve sleeve and the control valve seat can be made separately from each other and are easily accessible.
  • an embodiment is advantageous in which to ensure a low flow through the armature space fuel (partial flow of fuel control amount) via a throttle from the annulus in the armature space and from there to the injector return flow.
  • the injector can be dispensed with such a throttle, especially if the unavoidable leakage between the valve sleeve and the outer guide is sufficiently large to ensure a venting of the armature space.
  • FIG. 1 shows in the only Fig. 1 designed as a common rail injector injector with a disposed within a valve sleeve of a control valve channel (annular channel).
  • Fig. 1 designed as a common rail injector injector 1 for injecting fuel into a combustion chamber of an internal combustion engine of a motor vehicle is shown.
  • a high-pressure pump 2 delivers fuel from a reservoir 3 in a high-pressure fuel storage 4 (Rail).
  • fuel especially diesel or gasoline, under high pressure, of about 2000 bar in this embodiment.
  • 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 (high pressure area) of the injector 1 and flows from there in an injection process directly into the combustion chamber of the internal combustion engine.
  • the injector 1 is connected via an injector return port 7 to a return line 8 to the reservoir 3. Via the return line 8, a later to be explained control amount of fuel from the injector 1 to flow to the reservoir 3 and are fed back from there from the high pressure circuit.
  • an injector body 9 Within an injector body 9 is a one-piece injection valve element 10 in this embodiment, which may also be designed in several parts, if necessary, adjustable in the axial direction.
  • the injection valve element 10 is guided within a nozzle body 11 at its outer periphery. This nozzle body 11 is clamped by means of a union nut, not shown, with the injector 9.
  • the injection valve element 10 has at its tip 12 a closing surface 13, with which the injection valve element 10 can be brought into a tight contact with an injection valve element seat 14 formed inside the nozzle body 11.
  • a control chamber 22 is limited, via a radially extending in the sleeve-shaped portion 20 of the plate member 21 inlet throttle 23 with high-pressure fuel from the pressure chamber 6 is supplied.
  • the sleeve-shaped portion 20 with enclosed therein control chamber 22 is radially outwardly surrounded by fuel under high pressure, so that an annular guide gap 24 radially between the sleeve-shaped portion 20 and the injection valve member 10 is comparatively fuel-tight.
  • the control chamber 22 is connected via a arranged in the plate member 21 drain passage 25 with outlet throttle 26 with a valve chamber 27, the radially outward of a, adjustable in the axial direction, valve sleeve 28 of a pressure-balanced in the axial direction of the control valve 29 (servo valve ) is limited. From this, fuel can flow into a low-pressure region 30 of the injector 1 and from there to the Inj ektor Weglaufan gleich 7 when the valve sleeve 28 which is fixedly connected to an anchor plate 31, lifted from its formed on the plate member 21 control valve seat 35, that is, the control valve 29 is open.
  • an electromagnetic actuator 32 For adjusting the valve sleeve 28 in the drawing plane up an electromagnetic actuator 32 is provided with electromagnets 33, which cooperates with the armature plate 31 which is arranged in an armature space 34 and in the sequence with the valve sleeve 28.
  • the actuator 32nd When energized the actuator 32nd lifts the valve sleeve 28 from its arranged on the plate member 21, formed in this embodiment as a flat seat control valve seat 35 from.
  • the flow cross-sections of the inlet throttle 23 and the outlet throttle 26 are matched to one another such that when the control valve 29 is open, a net outflow of fuel (fuel control quantity) from the control chamber 22 via the valve chamber 27 into the low-pressure region 30 of the injector 1 and from there via the injector return port 7 and the return line 8 flows into the reservoir 3.
  • the pressure in the control chamber 22 drops rapidly, whereby the injection valve element 10 lifts off from its injection valve element seat 14, so that fuel can flow out of the pressure chamber 6 through the nozzle hole arrangement 15.
  • the energization of the electromagnetic actuator 32 is interrupted, whereby the valve sleeve 28 is adjusted by means of a control spring 36 which is supported on the armature plate 31 in the drawing plane down to its control valve seat 35.
  • a control spring 36 which is supported on the armature plate 31 in the drawing plane down to its control valve seat 35.
  • Fuel flowing in through the inlet throttle 23 into the control chamber 22 ensures rapid pressure increase in the control chamber 22 and thus a closing force acting on the injection valve element 10.
  • the resulting closing movement of the injection valve element 10 is assisted by a closing spring 37, which is supported at one end on a peripheral collar 38 of the injection valve element 10 and at the other end on the lower side in the drawing plane end face 39 of the sleeve-shaped portion 20 of the plate member 21.
  • Valve sleeve 28 designed as an annular channel channel 40 which passes through the armature plate 34 radially inside and opens in an upper plane in the drawing plane above the anchor plate 31 in the armature space 34 and from there directly through a central channel 41 within an electromagnet assembly 42 of the electromagnetic actuator 32 in the axial direction to the centrically arranged on the end face 43 of the injector 1 Injektor Wegnnenan gleich 7 can flow without having to flow along the large anchor surfaces of the armature plate 31.
  • the control spring 36 is arranged, which is supported in the axial direction of a plate member 44 with axial channels 45 through which fuel to the return line 8 can flow.
  • a pressure pin 46 which seals the valve chamber 27 in the axial direction with an upper in the plane of the lower thickened end portion 47.
  • the pressure forces acting on the thickened end section 47 are thereby supported by the pressure pin 46 on the plate element 44 and thus on a front-side cover 54 of the injector 1.
  • the pressure pin 46 is formed thickened only in its lower end portion 47. In the axial direction of this is followed by a thin portion 48, which extends up to the plate member 44. This thin portion 48 of the pressure pin 46 defines radially inside the channel 40, which is bounded radially outwardly by the valve sleeve 28 and the anchor plate 31.
  • the fuel When the control valve 29 is open, the fuel initially flows into an annular space 49, which surrounds a lower portion of the valve sleeve 28 radially on the outside.
  • This annular space 49 in turn is bounded radially outwardly and in the axial direction upward by a component 50 which guides the valve sleeve 28 on its outer circumference below the anchor plate 31.
  • the fuel flows through a bore 51, which is designed as a radial bore in the valve sleeve 28 in the channel 40 in the plane above the thickened end portion 47 of the pressure pin 46 and flows from there in the axial direction further into the central channel 41st via the Injektor Weglaufan gleich 7 in the return line 8.
  • the component 50 which defines the annular space 49 is braced in the axial direction between the plate member 21 and a screw plate 52 which is held within the injector body 9 by screwing.
  • a throttle 53 is provided, via which a minimum fuel flow, that is to say a minimal subset of the control quantity, can flow from the annular space 49 into the armature space 34 into a region below the armature plate 31.
  • the throttle 53 is dimensioned (small cross-section), that the switching behavior of the control valve 29 is not or only minimally adversely affected by this Kraftstoffström.

Abstract

The invention relates to an injector (1) for injecting fuel into the combustion chamber of an internal combustion engine, particularly a common rail injector, having an injection valve element (10) that can be adjusted between a closed position and an open position in the axial direction as a function of the pressure in a control chamber (22), wherein the control chamber (22) can be connected to an injector return connection (7) by means of a control valve (29) having an adjustable valve sleeve (28), and wherein the valve sleeve (28) is operatively connected to an armature plate (31), which interacts with an electromagnetic actuator (31) for adjusting the valve sleeve (28). The invention provides that a channel (40) extending in the axial direction is disposed within the valve sleeve (28), by means of which fuel may flow from the control chamber (22) past the armature plate (31) to the injector return connection (7) while the control valve (29) is open.

Description

Beschreibung description
Titeltitle
Injektor mit hülsenförmigem SteuerventilelementInjector with sleeve-shaped control valve element
Stand der TechnikState of the art
Die Erfindung betrifft einen Injektor zum Einspritzen von Kraftstoff in einen Brennraum einer Brennkraftmaschine, insbesondere einen Common-Rail-Injektor, gemäß dem Oberbegriff des Anspruchs 1.The invention relates to an injector for injecting fuel into a combustion chamber of an internal combustion engine, in particular a common rail injector, according to the preamble of claim 1.
Aus der EP 1 612 403 Al ist ein Common-Rail-Injektor mit einem in axialer Richtung druckausgeglichenen Steuerventil bekannt. Mittels des Steuerventils, das ein hülsenförmiges Steuerventilelement aufweist, kann der Kraftstoffdruck innerhalb einer von einem Einspritzventilelement stirnseitig begrenzten Steuerkammer beeinflusst werden. Durch die Variation des Kraftstoffdruckes innerhalb der Steuerkammer wird das Einspritzventilelement zwischen einer Öffnungsstellung und einer Schließstellung verstellt, wobei das Einspritzventilelement in seiner Öffnungsstellung den Kraftstofffluss in den Brennraum einer Brennkraftmaschine freigibt. Das hülsenförmige Steuerventilelement ist mit einer Ankerplatte verbunden, die mit einem elektromagnetischen Aktuator zum Verstellen des hülsenförmigen Steuerventilelementes zusammenwirkt. Bei geöffnetem Steuerventil strömt der Kraftstoff aus der Steuerkammer durch einen die Ankerplatte aufnehmenden Ankerraum in Richtung eines Injektorrücklaufanschlusses . Dabei trifft der ausströmende Kraftstoff auf die radialen, unteren, dem Steuerventilsitz zugewandten Flächen der Ankerplatte, wodurch Strömungskräfte auf die Ankerplatte wirken, die zu einer ungewollten Beeinflussung der Einspritzung führen. Diese Strömungskräfte wirken sich bei dem bekannten Injektor besonders stark aus, da das Steuerventil als in axialer Richtung druckausgeglichenes Ventil ausgebildet ist und in der Folge mit dem elektromagnetischen Aktuator nur kleine Magnetkräfte realisiert werden, wodurch wiederum die Ankerplatte durch die bei geöffnetem Steuerventil auftretenden Strömungskräfte vergleichsweise leicht verstellt werden kann .From EP 1 612 403 A1, a common rail injector with a pressure-balanced control valve in the axial direction is known. By means of the control valve, which has a sleeve-shaped control valve element, the fuel pressure can be influenced within a control chamber bounded on the end side by an injection valve element. By varying the fuel pressure within the control chamber, the injection valve element is adjusted between an open position and a closed position, wherein the injection valve element releases the fuel flow into the combustion chamber of an internal combustion engine in its open position. The sleeve-shaped control valve element is connected to an anchor plate, which cooperates with an electromagnetic actuator for adjusting the sleeve-shaped control valve element. When the control valve is open, the fuel flows out of the control chamber through an armature space receiving the armature plate in the direction of an injector return port. In this case, the outflowing fuel strikes the radial, lower, the control valve seat facing surfaces of the armature plate, whereby flow forces on the armature plate act, which lead to an unwanted influence on the injection. These flow forces have a particularly strong effect in the known injector, since the control valve is designed as a valve pressure-balanced in the axial direction and only small magnetic forces are realized with the electromagnetic actuator, which in turn makes the armature plate comparatively easy by the flow forces occurring when the control valve is open can be adjusted.
Offenbarung der Erfindung Technische AufgabeDISCLOSURE OF THE INVENTION Technical Problem
Der Erfindung liegt daher die Aufgabe zugrunde, einen verbesserten Injektor vorzuschlagen, bei dem die von dem bei geöffnetem Steuerventil in Richtung desThe invention is therefore based on the object to propose an improved injector in which the of the open with the control valve in the direction of
Injektorrücklaufanschlusses strömenden Kraftstoff verursachten, auf die Ankerplatte wirkenden und damit dasInjector return port caused flowing fuel, acting on the anchor plate and thus the
Schaltverhalten des Injektors negativ beeinflussenden Strömungskräfte zumindest reduziert sind.Switching behavior of the injector negatively influencing flow forces are at least reduced.
Technische LösungTechnical solution
Diese Aufgabe wird mit einem Injektor mit den Merkmalen des Anspruchs 1 gelöst. Vorteilhafte Weiterbildungen der Erfindung sind in den Unteransprüchen angegeben. In den Rahmen der Erfindung fallen auch sämtliche Kombinationen aus zumindest zwei von in der Beschreibung, den Ansprüchen und/oder den Figuren offenbarten Merkmalen.This object is achieved with an injector having the features of claim 1. Advantageous developments of the invention are specified in the subclaims. All combinations of at least two features disclosed in the description, the claims and / or the figures also fall within the scope of the invention.
Der Erfindung liegt der Gedanke zugrunde, die auf die Ankerplatte wirkenden Strömungskräfte von bei geöffnetem Steuerventil (Servo-Ventil) in Richtung des Inj ektorrücklaufanschlusses strömendem Kraftstoff dadurch zu minimieren oder bevorzugt vollständig zu vermeiden, dass der Kraftstoff, zumindest ein Kraftstoffteilstrom, bei geöffnetem Steuerventil durch einen Kanal innerhalb der Ventilhülse in axialer Richtung in Richtung des Inj ektorrücklaufanschlusses strömt. Der Kraftstoff strömt also innerhalb der Ventilhülse, ggf. zusätzlich innerhalb der Ankerplatte an der Ankerplatte in axialer Richtung radial innen vorbei, ohne dass Strömungskräfte, die das Schaltverhalten des Injektors beeinflussen könnten, auf die Ankerplatte wirken. Der aus der Steuerkammer bei geöffnetem Steuerventil abfließende Kraftstoff (Steuermenge) muss durch das Vorsehen des Kanals innerhalb der Ventilhülse nicht durch oder entlang der großen, dem Steuerventilsitz zugewandten (unteren) Flächen der Ankerplatte in axialerThe invention is based on the idea of acting on the anchor plate flow forces of when open Control valve (servo-valve) in the direction of the Inj ektorrücklaufanschlusses flowing fuel to minimize or preferably completely avoid that the fuel, at least one partial flow of fuel, with open control valve through a channel within the valve sleeve in the axial direction in the direction of ej ektorrücklaufanschlusses flows. The fuel thus flows within the valve sleeve, possibly additionally inside the armature plate on the armature plate in the axial direction radially inward past without flow forces that could affect the switching behavior of the injector, act on the armature plate. The fuel flowing out of the control chamber when the control valve is open (control quantity) does not have to be in the axial direction by providing the channel within the valve sleeve or along the large, the control valve seat facing (lower) surfaces of the anchor plate
Richtung strömen, sondern fließt zentral in Richtung desFlow towards it, but flows centrally in the direction of
Injektorrücklaufs. Ein nach dem Konzept der Erfindung ausgebildeter Injektor mit einem innerhalb der VentilhülseInjektorrücklaufs. A designed according to the concept of the invention injector with a within the valve sleeve
(Steuerventilelement) des Steuerventils angeordneten Kanal weist ein optimiertes Schaltverhalten auf, da von dem aus der Steuerkammer in Richtung des Inj ektorrücklaufanschlusses strömenden Kraftstoff bei bekannten Injektoren verursachte Ventilhülsenschwingungen vermieden werden. Das optimierte Schaltverhalten zeichnet sich insbesonders durch minimierte Einspritztoleranzen aus. Die Ventilhülse des Steuerventils ist bei einem nach dem Konzept der Erfindung ausgebildeten Injektor mit der Ventilhülse wirkverbunden, das heißt, entweder einstückig mit dieser ausgebildet oder, insbesondere formschlüssig, mit dieser verbunden. In Weiterbildung der Erfindung ist mit Vorteil vorgesehen, dass das Steuerventil, wenn dieses an seinem Steuerventilsitz anliegt, in axialer Richtung druckausgeglichen ist. Dies kann bevorzugt dadurch realisiert werden, dass die Dichtkante (Sitzkante) am Innenumfang der Ventilhülse angeordnet ist, so dass eine Druckstufe an der Ventilhülse, die eine Öffnungskraft auf die Ventilhülse verursachen würde, vermieden wird.(Control valve element) of the control valve arranged channel has an optimized switching behavior, as avoided by the flowing out of the control chamber in the direction of the ej ektorrücklaufanschlusses fuel in known injectors valve sleeve vibrations. The optimized switching behavior is characterized in particular by minimized injection tolerances. The valve sleeve of the control valve is operatively connected to a formed according to the concept of the invention injector with the valve sleeve, that is, either integrally formed with this or, in particular form-fitting, connected thereto. In a further development of the invention is advantageously provided that the control valve, when this rests against its control valve seat, is pressure balanced in the axial direction. This can preferably be realized in that the sealing edge (seat edge) is arranged on the inner circumference of the valve sleeve, so that a pressure step on the valve sleeve, which would cause an opening force on the valve sleeve, is avoided.
Insbesondere das Vorsehen eines zentrischen, innerhalb der Ventilhülse in axialer Richtung verlaufenden Kanals zur Ableitung zumindest einer Teilmenge, vorzugsweise der Gesamtmenge, von bei geöffnetem Steuerventil in Richtung des Injektorrücklaufanschlusses strömendem Kraftstoff ermöglicht die Realisierung einer besonders bevorzugten Ausführungsform des Injektors, bei der der Inj ektorrücklaufanschluss zum Anschließen des Injektors an eine Rücklaufleitung für eine Kraftstoffsteuermenge zentrisch an einer von dem Brennraum abgewandten Stirnseite (Deckel) des Injektors angeordnet ist. Eine derartige Anordnung des Injektorrücklaufanschlusses (Niederdruck- Anschluss) ist kostengünstig herstellbar und erlaubt vor allem eine einfache Montage der Injektoranschlüsse am Verbrennungsmotor. Ferner werden asymmetrische Verformungen durch den Injektorinnendruck aufgrund einer im Wesentlichen koaxialen Injektorbauform mit einem zentrisch auf einer Stirnseite angeordneten Injektorrücklaufanschluss vermieden .In particular, the provision of a centric, extending within the valve sleeve in the axial direction channel for discharging at least a subset, preferably the total amount of fuel flowing in the direction of the injector return port with open control valve fuel allows the realization of a particularly preferred embodiment of the injector, wherein the Inj ektorrücklaufanschluss to Connecting the injector to a return line for a fuel control amount is arranged centrally on a side facing away from the combustion chamber end face (cover) of the injector. Such an arrangement of the injector return connection (low-pressure connection) can be produced cost-effectively and, above all, permits a simple assembly of the injector connections on the internal combustion engine. Furthermore, asymmetrical deformations are avoided by the injector internal pressure due to a substantially coaxial injector configuration with an injector return port arranged centrally on one end side.
Bevorzugt ist eine Ausführungsform, bei der der Kanal bis zu dem von dem Steuerventilsitz abgewandten Ende derPreferred is an embodiment in which the channel is up to the remote from the control valve seat end of
Ventilhülse reicht, der Kraftstoff also stirnseitig aus derValve sleeve is sufficient, so the fuel from the front side of the
Ventilhülse oder ggf. stirnseitig aus der die Ventilhülse umgebenden oder axial benachbart zu dieser angeordnetenValve sleeve or possibly the front side of the valve sleeve surrounding or axially adjacent to this
Ankerplatte ausströmt. Dabei ist es gemäß einer erstenAnchor plate flows out. It is according to a first
Alternative denkbar, dass der Kanal in den AnkerraumAlternative conceivable that the channel in the anchor space
(bevorzugt oberhalb der Ankerplatte) ausmündet und von dort aus weiter in axialer Richtung zum Injektorrücklauf strömt. Gemäß einer zweiten Alternative ist es denkbar, dass der Kanal derart verlängert ist, dass dieser nicht unmittelbar in den Ankerraum, sondern in einen oberhalb des Ankerraums in einer Elektromagnetanordnung des Aktuators angeordneten Zentralkanal ausmündet.(Preferably, above the anchor plate) opens and flows from there further in the axial direction to the injector return. According to a second alternative, it is conceivable that the channel is extended in such a way that it does not open directly into the armature space but into a central duct arranged above the armature space in an electromagnet arrangement of the actuator.
Von besonderem Vorteil ist eine Ausführungsform des Injektors, bei der innerhalb der Ventilhülse ein Druckstift angeordnet ist, der als ein von dem den Steuerventilsitz aufweisenden Bauteil separates Bauteil ausgebildet ist. Dieser Druckstift stützt sich entweder an einem von dem Steuerventilsitz beabstandeten Injektorbauteil, bevorzugt federkraftunterstützt, ab oder ist einstückig mit einem von dem Steuerventilsitz beabstandeten Injektorbauteil ausgebildet. Eine derartige Ausführungsform hat den Vorteil, dass der Steuerventilsitz bei seiner Herstellung gut zugänglich ist und die Führung für die Ventilhülse und der Steuerventilsitz an separaten, getrennt voneinander zu bearbeitenden Bauteilen ausgebildet sind. Die Aufgabe des separaten Druckstiftes besteht darin, die in axialer Richtung wirkenden Druckkräfte aufzunehmen, abzustützen und dabei den inneren Querschnitt der Ventilhülse hochdruckdicht in axialer Richtung abzudichten, so dass bei geschlossenem Steuerventil, also bei an dem Steuerventilsitz anliegender Ventilhülse, kein Kraftstoff aus der Steuerkammer zum Injektorrücklauf strömen kann. Selbstverständlich ist auch eine Ausführungsform realisierbar, bei der der Druckstift einstückig mit dem Injektorbauteil ausgebildet ist, an dem sich auch der Steuerventilsitz befindet.Of particular advantage is an embodiment of the injector, wherein within the valve sleeve, a pressure pin is arranged, which is designed as a separate component from the control valve seat having the component. This pressure pin is either supported on an injector component which is at a distance from the control valve seat, preferably in a spring-assisted manner, or is formed integrally with an injector component which is at a distance from the control valve seat. Such an embodiment has the advantage that the control valve seat is easily accessible during its manufacture and the guide for the valve sleeve and the control valve seat are formed on separate, separate from each other to be machined components. The task of the separate pressure pin is to absorb the compressive forces acting in the axial direction, support and thereby seal the inner cross-section of the valve sleeve high-pressure tight in the axial direction, so that when the control valve is closed, ie at the control valve seat fitting valve sleeve, no fuel from the control chamber Injector return can flow. Of course, an embodiment can be realized in which the pressure pin integral with the Injector component is formed, on which also the control valve seat is located.
Von besonderem Vorteil ist eine Ausführungsform bei der der Kanal innerhalb der Ventilhülse als Ringkanal ausgebildet ist, der radial außen vom Innenumfang der Ventilhülse und radial innen von dem, vorzugsweise zentrisch innerhalb der Ventilhülse angeordneten, Druckstift begrenzt ist.Of particular advantage is an embodiment in which the channel is formed within the valve sleeve as an annular channel which is radially outwardly of the inner circumference of the valve sleeve and radially inwardly of the, preferably centrally disposed within the valve sleeve, pressure pin is limited.
Zur Realisierung eines axial innerhalb der Ventilhülse verlaufenden Ringkanals ist eine Ausführungsform von Vorteil, bei der der Druckstift einen verdickten (unteren) Endabschnitt aufweist, der als Hochdruckdichtung zur Abdichtung des Innenquerschnitts der Ventilhülse in axialer Richtung (nach oben) dient. Durch diesen verdickten Endabschnitt hindurch verläuft der Kanal nicht, sondern beginnt in axialer Richtung gesehen erst an einem zu dem verdickten Endabschnitt benachbart angeordneten, dünnen Abschnitt des Druckstiftes, der sich bevorzugt in axialer Richtung bis an ein von dem Steuerventilsitz beabstandetes Bauteil erstreckt und sich an diesem in axialer Richtung abstützt oder einstückig mit diesem ausgebildet ist. Bevorzugt beträgt der Durchmesser des verdickten Endabschnittes zumindest näherungsweise dem Innendurchmesser der Ventilhülse. Der verdünnte Abschnitt weist dabei einen geringeren Durchmesser als der verdickte Endabschnitt auf, der so bemessen ist, dass zum einen ein Kanal mit ausreichendem Querschnitt zur Ableitung der Kraftstoffsteuermenge resultiert und zum anderen Festigkeitsprobleme vermieden werden. Der Druckstift kann sowohl einteilig als auch mehrteilig ausgebildet werden. In Weiterbildung der Erfindung ist mit Vorteil vorgesehen, dass in dem Bauteil, an dem sich der Druckstift in axialer Richtung abstützt, mindestens ein zum Injektorrücklauf führender Axialkanal vorgesehen ist. Bevorzugt befindet sich das Bauteil, an dem sich der Druckstift abstützt, innerhalb eines, in einer Elektromagnetanordnung angeordneten, Zentralkanals, der unmittelbar zum Injektorrücklauf führt.To realize an axially extending inside the valve sleeve annular channel is an embodiment of advantage in which the pressure pin has a thickened (lower) end portion which serves as a high pressure seal for sealing the inner cross section of the valve sleeve in the axial direction (up). Through this thickened end portion of the channel does not extend, but begins in an axial direction seen adjacent to the thickened end portion adjacent, thin portion of the pressure pin, which preferably extends in the axial direction to a spaced from the control valve member member and at this is supported in the axial direction or formed integrally therewith. Preferably, the diameter of the thickened end portion is at least approximately the inner diameter of the valve sleeve. The thinned portion has a smaller diameter than the thickened end portion, which is dimensioned such that on the one hand results in a channel of sufficient cross-section for the derivation of the fuel tax and on the other strength problems are avoided. The pressure pin can be formed both one-piece and multi-part. In a development of the invention, it is advantageously provided that at least one axial passage leading to the injector return is provided in the component on which the pressure pin is supported in the axial direction. The component on which the pressure pin is supported is preferably located within a central channel arranged in an electromagnet arrangement, which leads directly to the injector return.
Da der Kraftstoff aufgrund der Dichtwirkung des verdickten Endabschnittes des Druckstiftes nicht unmittelbar, nachdem er eine der Steuerkammer nachgeordnete Ablaufdrossel durchströmt hat, in den Kanal innerhalb der Ventilhülse strömen kann, ist gemäß einer bevorzugten Ausführungsform vorgesehen, dass der Steuerventilsitz von einem Ringraum umgeben ist, in den der Kraftstoff bei geöffnetem Steuerventil von innerhalb der Ventilhülse in radialer Richtung aufströmen kann, wobei dieser Ringraum hydraulisch mit dem innerhalb der Ventilhülse angeordneten Kanal verbunden ist. Bevorzugt ist die hydraulische Verbindung zwischen dem Ringraum und dem innerhalb der Ventilhülse angeordneten Kanal als mindestens eine Bohrung, vorzugsweise als mindestens eine Radialbohrung, ausgeführt, die von dem Ringraum in den innerhalb der Ventilhülse angeordneten Kanal zum Abführen des Kraftstoffes führt.Since the fuel due to the sealing effect of the thickened end portion of the pressure pin not immediately after it has flowed through a control chamber downstream outlet throttle, can flow into the channel within the valve sleeve, is provided according to a preferred embodiment that the control valve seat is surrounded by an annular space in the fuel with open control valve can flow from within the valve sleeve in the radial direction, said annular space is hydraulically connected to the disposed within the valve sleeve channel. Preferably, the hydraulic connection between the annular space and the channel disposed within the valve sleeve is designed as at least one bore, preferably as at least one radial bore, which leads from the annular space in the disposed within the valve sleeve channel for discharging the fuel.
Besonders bevorzugt ist eine Ausführungsform, bei der der Ringraum in axialer Richtung und ggf. auch in radialer Richtung von einem Bauteil begrenzt ist, das als Führungsbauteil zur Führung der Ventilhülse an ihrem Außenumfang ausgebildet ist. Dieses Führungsbauteil ist bevorzugt als ein von dem den Steuerventilsitz aufweisenden Bauteil separates Bauteil ausgeführt, so dass die Führung für die axial verstellbare Ventilhülse und der Steuerventilsitz separat voneinander hergestellt werden können und gut zugänglich sind. Zur Optimierung des Strömungsverhaltens, insbesondere zur Entlüftung des Ankerraums, ist eine Ausführungsform von Vorteil, bei der zur Gewährleistung einer geringen Durchströmung des Ankerraums Kraftstoff (Teilstrom der Kraftstoffsteuermenge) über eine Drossel von dem Ringraum in den Ankerraum und von dort aus zum Injektorrücklauf strömen kann. Je nach Auslegung des Injektors kann auf eine derartige Drossel verzichtet werden, insbesondere dann, wenn die nicht zu vermeidende Leckage zwischen der Ventilhülse und der äußeren Führung ausreichend groß ist, um eine Entlüftung des Ankerraums sicherzustellen.Particularly preferred is an embodiment in which the annular space is limited in the axial direction and possibly also in the radial direction of a component which is designed as a guide member for guiding the valve sleeve on its outer periphery. This guide component is preferably designed as a separate component from the component having the control valve seat, so that the guide for the axially adjustable valve sleeve and the control valve seat can be made separately from each other and are easily accessible. To optimize the flow behavior, in particular for venting the armature space, an embodiment is advantageous in which to ensure a low flow through the armature space fuel (partial flow of fuel control amount) via a throttle from the annulus in the armature space and from there to the injector return flow. Depending on the design of the injector can be dispensed with such a throttle, especially if the unavoidable leakage between the valve sleeve and the outer guide is sufficiently large to ensure a venting of the armature space.
Kurze Beschreibung der ZeichnungenBrief description of the drawings
Weitere Vorteile, Merkmale und Einzelheiten der Erfindung ergeben sich aus der nachfolgenden Beschreibung eines bevorzugten Ausführungsbeispiels sowie anhand der Zeichnung. Diese zeigt in der einzigen Fig. 1 einen als Common-Rail-Injektor ausgebildeten Injektor mit einem innerhalb einer Ventilhülse eines Steuerventils angeordneten Kanal (Ringkanal) .Further advantages, features and details of the invention will become apparent from the following description of a preferred embodiment and from the drawing. This shows in the only Fig. 1 designed as a common rail injector injector with a disposed within a valve sleeve of a control valve channel (annular channel).
Ausführungsformen der ErfindungEmbodiments of the invention
In Fig. 1 ist ein als Common-Rail-Injektor ausgebildeter Injektor 1 zum Einspritzen von Kraftstoff in einen Brennraum einer Brennkraftmaschine eines Kraftfahrzeugs dargestellt. Eine Hochdruckpumpe 2 fördert Kraftstoff aus einem Vorratsbehälter 3 in einen Kraftstoff- Hochdruckspeicher 4 (Rail) . In diesen ist Kraftstoff, insbesondere Diesel oder Benzin, unter hohem Druck, von in diesem Ausführungsbeispiel 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 einen Druckraum 6 (Hochdruckbereich) des Injektors 1 und strömt von dort aus bei einem Einspritzvorgang unmittelbar in den Brennraum der Brennkraftmaschine. Der Injektor 1 ist über einen Injektorrücklaufanschluss 7 an eine Rücklaufleitung 8 an den Vorratsbehälter 3 angeschlossen. Über die Rücklaufleitung 8 kann eine später noch zu erläuternde Steuermenge an Kraftstoff von dem Injektor 1 zu dem Vorratsbehälter 3 abfließen und von dort aus dem Hochdruckkreislauf wieder zugeführt werden.In Fig. 1, designed as a common rail injector injector 1 for injecting fuel into a combustion chamber of an internal combustion engine of a motor vehicle is shown. A high-pressure pump 2 delivers fuel from a reservoir 3 in a high-pressure fuel storage 4 (Rail). In these is fuel, especially diesel or gasoline, under high pressure, of about 2000 bar in this embodiment. 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 (high pressure area) of the injector 1 and flows from there in an injection process directly into the combustion chamber of the internal combustion engine. The injector 1 is connected via an injector return port 7 to a return line 8 to the reservoir 3. Via the return line 8, a later to be explained control amount of fuel from the injector 1 to flow to the reservoir 3 and are fed back from there from the high pressure circuit.
Innerhalb eines Injektorkörpers 9 ist ein in diesem Ausführungsbeispiel einstückiges Einspritzventilelement 10, das bei Bedarf auch mehrteilig ausgeführt sein kann, in axialer Richtung verstellbar. Dabei ist das Einspritzventilelement 10 innerhalb eines Düsenkörpers 11 an seinem Außenumfang geführt. Dieser Düsenkörper 11 ist mittels einer nicht dargestellten Überwurfmutter mit dem Injektorkörper 9 verspannt.Within an injector body 9 is a one-piece injection valve element 10 in this embodiment, which may also be designed in several parts, if necessary, adjustable in the axial direction. In this case, the injection valve element 10 is guided within a nozzle body 11 at its outer periphery. This nozzle body 11 is clamped by means of a union nut, not shown, with the injector 9.
Das Einspritzventilelement 10 weist an seiner Spitze 12 eine Schließfläche 13 auf, mit welcher das Einspritzventilelement 10 in eine dichte Anlage an einen innerhalb des Düsenkörpers 11 ausgebildeten Einspritzventilelementsitz 14 bringbar ist.The injection valve element 10 has at its tip 12 a closing surface 13, with which the injection valve element 10 can be brought into a tight contact with an injection valve element seat 14 formed inside the nozzle body 11.
Wenn das Einspritzventilelement 10 an seinem Einspritzventilelementsitz 14 anliegt, das heißt, sich in einer Schließstellung befindet, ist der Kraftstoffaustritt aus einer Düsenlochanordnung 15 gesperrt. Ist es dagegen von seinem Einspritzventilelementsitz 14 abgehoben, kann Kraftstoff aus dem Düsenraum 6 durch in einem Führungsabschnitt 16 am Außenumfang des Einspritzventilelementes 10 gebildete Axialkanäle 17 in einen in der Zeichnungsebene unteren, radial zwischen dem Einspritzventilelement 10 und dem Düsenkörper 11 ausgebildeten Ringraum 18 an dem Einspritzventilelementsitz 14 vorbei zur Düsenlochanordnung 15 strömen und dort im Wesentlichen unter dem Hochdruck (Raildruck) stehend in den Brennraum gespritzt werden.When the injection valve element 10 abuts against its injection valve element seat 14, that is, in is a closed position, the fuel outlet from a nozzle hole assembly 15 is locked. If, on the other hand, it is lifted off its injection valve element seat 14, fuel can flow from the nozzle chamber 6 through axial channels 17 formed in a guide section 16 on the outer circumference of the injection valve element 10 into an annular space 18 at the injection valve element seat which is lower in the plane of the drawing and formed between the injection valve element 10 and the nozzle body 11 14 flow past the nozzle hole assembly 15 and there are injected substantially under the high pressure (rail pressure) standing in the combustion chamber.
Von einer oberen Stirnseite 19 des Einspritzventilelementes 10 und einem in der Zeichnungsebene unteren, hülsenförmigen Abschnitt 20 eines Plattenelementes 21 wird eine Steuerkammer 22 begrenzt, die über eine radial in dem hülsenförmigen Abschnitt 20 des Plattenelementes 21 verlaufende Zulaufdrossel 23 mit unter Hochdruck stehendem Kraftstoff aus dem Druckraum 6 versorgt wird. Der hülsenförmige Abschnitt 20 mit darin eingeschlossener Steuerkammer 22 ist radial außen von unter Hochdruck stehendem Kraftstoff umschlossen, so dass ein ringförmiger Führungsspalt 24 radial zwischen dem hülsenförmigen Abschnitt 20 und dem Einspritzventilelement 10 vergleichsweise kraftstoffdicht ist.From an upper end face 19 of the injection valve element 10 and a lower in the plane of the sleeve-shaped portion 20 of a plate member 21, a control chamber 22 is limited, via a radially extending in the sleeve-shaped portion 20 of the plate member 21 inlet throttle 23 with high-pressure fuel from the pressure chamber 6 is supplied. The sleeve-shaped portion 20 with enclosed therein control chamber 22 is radially outwardly surrounded by fuel under high pressure, so that an annular guide gap 24 radially between the sleeve-shaped portion 20 and the injection valve member 10 is comparatively fuel-tight.
Die Steuerkammer 22 ist über einen, in dem Plattenelement 21 angeordneten Ablaufkanal 25 mit Ablaufdrossel 26 mit einer Ventilkammer 27 verbunden, die radial außen von einer, in axialer Richtung verstellbaren, Ventilhülse 28 eines im geschlossenen Zustand in axialer Richtung druckausgeglichenen Steuerventils 29 (Servo-Ventil) begrenzt ist. Aus dieser kann Kraftstoff in einen Niederdruckbereich 30 des Injektors 1 und von dort aus zum Inj ektorrücklaufanschluss 7 strömen, wenn die Ventilhülse 28, die mit einer Ankerplatte 31 fest verbunden ist, von ihrem am Plattenelement 21 ausgebildeten Steuerventilsitz 35 abgehoben, das heißt, das Steuerventil 29 geöffnet ist. Zum Verstellen der Ventilhülse 28 in der Zeichnungsebene nach oben ist ein elektromagnetischer Aktuator 32 mit Elektromagneten 33 vorgesehen, der mit der Ankerplatte 31, die in einem Ankerraum 34 angeordnet ist, zusammenwirkt und in der Folge auch mit der Ventilhülse 28. Bei Bestromung des Aktuators 32 hebt die Ventilhülse 28 von ihrem am Plattenelement 21 angeordneten, in diesem Ausführungsbeispiel als Flachsitz ausgebildeten Steuerventilsitz 35 ab. Die Durchflussquerschnitte der Zulaufdrossel 23 und der Ablaufdrossel 26 sind dabei derart aufeinander abgestimmt, dass bei geöffnetem Steuerventil 29 ein Nettoabfluss von Kraftstoff (Kraftstoffsteuermenge) aus der Steuerkammer 22 über die Ventilkammer 27 in den Niederdruckbereich 30 des Injektors 1 und von dort aus über den Injektorrücklaufanschluss 7 und die Rücklaufleitung 8 in den Vorratsbehälter 3 strömt. Hierdurch sinkt der Druck in der Steuerkammer 22 rapide ab, wodurch das Einspritzventilelement 10 von seinem Einspritzventilelementsitz 14 abhebt, so dass Kraftstoff aus dem Druckraum 6 durch die Düsenlochanordnung 15 ausströmen kann.The control chamber 22 is connected via a arranged in the plate member 21 drain passage 25 with outlet throttle 26 with a valve chamber 27, the radially outward of a, adjustable in the axial direction, valve sleeve 28 of a pressure-balanced in the axial direction of the control valve 29 (servo valve ) is limited. From this, fuel can flow into a low-pressure region 30 of the injector 1 and from there to the Inj ektorrücklaufanschluss 7 when the valve sleeve 28 which is fixedly connected to an anchor plate 31, lifted from its formed on the plate member 21 control valve seat 35, that is, the control valve 29 is open. For adjusting the valve sleeve 28 in the drawing plane up an electromagnetic actuator 32 is provided with electromagnets 33, which cooperates with the armature plate 31 which is arranged in an armature space 34 and in the sequence with the valve sleeve 28. When energized the actuator 32nd lifts the valve sleeve 28 from its arranged on the plate member 21, formed in this embodiment as a flat seat control valve seat 35 from. The flow cross-sections of the inlet throttle 23 and the outlet throttle 26 are matched to one another such that when the control valve 29 is open, a net outflow of fuel (fuel control quantity) from the control chamber 22 via the valve chamber 27 into the low-pressure region 30 of the injector 1 and from there via the injector return port 7 and the return line 8 flows into the reservoir 3. As a result, the pressure in the control chamber 22 drops rapidly, whereby the injection valve element 10 lifts off from its injection valve element seat 14, so that fuel can flow out of the pressure chamber 6 through the nozzle hole arrangement 15.
Zum Beenden des Einspritzvorgangs wird die Bestromung des elektromagnetischen Aktuators 32 unterbrochen, wodurch die Ventilhülse 28 mittels einer Steuerfeder 36, die sich auf der Ankerplatte 31 abstützt, in der Zeichnungsebene nach unten auf ihren Steuerventilsitz 35 verstellt wird. Der durch die Zulaufdrossel 23 in die Steuerkammer 22 nachströmende Kraftstoff sorgt für eine schnelle Druckerhöhung in der Steuerkammer 22 und damit für eine auf das Einspritzventilelement 10 wirkende Schließkraft. Die daraus resultierende Schließbewegung des Einspritzventilelementes 10 wird von einer Schließfeder 37 unterstützt, die sich einenends an einem Umfangsbund 38 des Einspritzventilelementes 10 und anderenends an der in der Zeichnungsebene unteren Stirnseite 39 des hülsenförmigen Abschnittes 20 des Plattenelementes 21 abstützt.To end the injection process, the energization of the electromagnetic actuator 32 is interrupted, whereby the valve sleeve 28 is adjusted by means of a control spring 36 which is supported on the armature plate 31 in the drawing plane down to its control valve seat 35. Of the Fuel flowing in through the inlet throttle 23 into the control chamber 22 ensures rapid pressure increase in the control chamber 22 and thus a closing force acting on the injection valve element 10. The resulting closing movement of the injection valve element 10 is assisted by a closing spring 37, which is supported at one end on a peripheral collar 38 of the injection valve element 10 and at the other end on the lower side in the drawing plane end face 39 of the sleeve-shaped portion 20 of the plate member 21.
Um zu verhindern, dass der bei geöffnetem Steuerventil 29 aus der Ventilkammer 27 ausströmende Kraftstoff bzw. der größte Teil dieses Kraftstoffes, durch den Ankerraum 34 an der in der Zeichnungsebene unteren Seite der sich radial in den Ankerraum 34 erstreckenden Ankerplatte 31 vorbeiströmt, ist innerhalb der Ventilhülse 28 ein als Ringkanal ausgebildeter Kanal 40 vorgesehen, der die Ankerplatte 34 radial innen durchsetzt und in einem in der Zeichnungsebene oberen Abschnitt oberhalb der Ankerplatte 31 in den Ankerraum 34 mündet und von dort aus unmittelbar durch einen Zentralkanal 41 innerhalb einer Elektromagnetanordnung 42 des elektromagnetischen Aktuators 32 in axialer Richtung zu dem zentrisch auf der Stirnseite 43 des Injektors 1 angeordneten Injektorrücklaufanschluss 7 strömen kann, ohne dabei entlang der großen Ankerflächen der Ankerplatte 31 strömen zu müssen. Innerhalb des Zentralkanals 41, der radial außen von der Elektromagnetanordnung 42 begrenzt ist, ist auch die Steuerfeder 36 angeordnet, die sich in axialer Richtung an einem Plattenelement 44 mit Axialkanälen 45 abstützt, durch die Kraftstoff zur Rücklaufleitung 8 strömen kann. An dem Plattenelement 44 stützt sich in axialer Richtung auch ein Druckstift 46 ab, der mit einem in der Zeichnungsebene unteren verdickten Endabschnitt 47 die Ventilkammer 27 in axialer Richtung nach oben abdichtet. Die auf den verdickten Endabschnitt 47 wirkenden Druckkräfte werden dabei von dem Druckstift 46 an dem Plattenelement 44 und damit an einem stirnseitigen Deckel 54 des Injektors 1 abgestützt. Der Druckstift 46 ist nur in seinem unteren Endabschnitt 47 verdickt ausgebildet. In axialer Richtung daran schließt ein dünner Abschnitt 48 an, der bis an das Plattenelement 44 heranreicht. Dieser dünne Abschnitt 48 des Druckstiftes 46 begrenzt radial innen den Kanal 40, der radial außen von der Ventilhülse 28 und der Ankerplatte 31 begrenzt wird.In order to prevent the fuel flowing out of the valve chamber 27 when the control valve 29 is open, or the major part of this fuel, passing through the armature space 34 at the lower side of the drawing plane in the armature space 34 extending armature plate 31 is within the Valve sleeve 28 designed as an annular channel channel 40 which passes through the armature plate 34 radially inside and opens in an upper plane in the drawing plane above the anchor plate 31 in the armature space 34 and from there directly through a central channel 41 within an electromagnet assembly 42 of the electromagnetic actuator 32 in the axial direction to the centrically arranged on the end face 43 of the injector 1 Injektorrücklaufanschluss 7 can flow without having to flow along the large anchor surfaces of the armature plate 31. Within the central channel 41, which is bounded radially on the outside of the solenoid assembly 42, and the control spring 36 is arranged, which is supported in the axial direction of a plate member 44 with axial channels 45 through which fuel to the return line 8 can flow. On the plate member 44 is supported in the axial direction and a pressure pin 46 which seals the valve chamber 27 in the axial direction with an upper in the plane of the lower thickened end portion 47. The pressure forces acting on the thickened end section 47 are thereby supported by the pressure pin 46 on the plate element 44 and thus on a front-side cover 54 of the injector 1. The pressure pin 46 is formed thickened only in its lower end portion 47. In the axial direction of this is followed by a thin portion 48, which extends up to the plate member 44. This thin portion 48 of the pressure pin 46 defines radially inside the channel 40, which is bounded radially outwardly by the valve sleeve 28 and the anchor plate 31.
Bei geöffnetem Steuerventil 29 strömt der Kraftstoff zunächst in einen Ringraum 49, der einen unteren Abschnitt der Ventilhülse 28 radial außen umgibt. Dieser Ringraum 49 wiederum ist radial außen und in axialer Richtung nach oben begrenzt von einem Bauteil 50, das die Ventilhülse 28 an ihrem Außenumfang unterhalb der Ankerplatte 31 führt. Von dem Ringraum 49 strömt der Kraftstoff über eine Bohrung 51, die als Radialbohrung in der Ventilhülse 28 ausgeführt ist, in den Kanal 40 in der Zeichnungsebene oberhalb des verdickten Endabschnitts 47 des Druckstiftes 46 und strömt von dort aus in axialer Richtung weiter in den Zentralkanal 41, über den Injektorrücklaufanschluss 7 in die Rücklaufleitung 8. Das Bauteil 50, welches den Ringraum 49 begrenzt, ist in axialer Richtung verspannt zwischen dem Plattenelement 21 und einer Schraubplatte 52, die innerhalb des Injektorkörpers 9 durch Verschrauben gehalten ist. Um eine vollständige Entlüftung des Ankerraums 34 zu gewährleisten, ist eine Drossel 53 vorgesehen, über die ein minimaler Kraftstoffström, also eine minimale Teilmenge der Steuermenge, aus dem Ringraum 49 in den Ankerraum 34 in einen Bereich unterhalb der Ankerplatte 31 strömen kann. Dabei ist die Drossel 53 so bemessen (geringer Querschnitt) , dass durch diesen Kraftstoffström das Schaltverhalten des Steuerventils 29 nicht oder nur minimal negativ beeinflusst wird. When the control valve 29 is open, the fuel initially flows into an annular space 49, which surrounds a lower portion of the valve sleeve 28 radially on the outside. This annular space 49 in turn is bounded radially outwardly and in the axial direction upward by a component 50 which guides the valve sleeve 28 on its outer circumference below the anchor plate 31. From the annular space 49, the fuel flows through a bore 51, which is designed as a radial bore in the valve sleeve 28 in the channel 40 in the plane above the thickened end portion 47 of the pressure pin 46 and flows from there in the axial direction further into the central channel 41st via the Injektorrücklaufanschluss 7 in the return line 8. The component 50, which defines the annular space 49 is braced in the axial direction between the plate member 21 and a screw plate 52 which is held within the injector body 9 by screwing. In order to ensure a complete venting of the armature space 34, a throttle 53 is provided, via which a minimum fuel flow, that is to say a minimal subset of the control quantity, can flow from the annular space 49 into the armature space 34 into a region below the armature plate 31. In this case, the throttle 53 is dimensioned (small cross-section), that the switching behavior of the control valve 29 is not or only minimally adversely affected by this Kraftstoffström.

Claims

Ansprüche claims
1. Injektor zum Einspritzen von Kraftstoff in den Brennraum einer Brennkraftmaschine, insbesondere Common-Rail-Inj ektor, mit einem Einspritzventilelement (10), das in Abhängigkeit des Druckes in einer Steuerkammer (22) zwischen einer Schließstellung und einer Öffnungsstellung in axialer Richtung verstellbar ist, wobei die Steuerkammer (22) mittels eines eine verstellbare Ventilhülse (28) aufweisenden Steuerventils (29) mit einem Injektorrücklaufanschluss1. injector for injecting fuel into the combustion chamber of an internal combustion engine, in particular common rail Inj ector, with an injection valve element (10) which is adjustable in dependence on the pressure in a control chamber (22) between a closed position and an open position in the axial direction wherein the control chamber (22) by means of an adjustable valve sleeve (28) having control valve (29) with an injector return port
(7) verbindbar ist, und wobei die Ventilhülse (28) mit einer Ankerplatte (31) wirkverbunden ist, die zum(7) is connectable, and wherein the valve sleeve (28) with an anchor plate (31) is operatively connected to the
Verstellen der Ventilhülse (28) mit einem elektromagnetischen Aktuator (31) zusammenwirkt,Adjusting the valve sleeve (28) with an electromagnetic actuator (31) cooperates,
dadurch gekennzeichnet,characterized,
dass innerhalb der Ventilhülse (28) ein in axialer Richtung verlaufender Kanal (40) angeordnet ist, durch den Kraftstoff bei geöffnetem Steuerventil (29) aus der Steuerkammer (22) innen an der Ankerplatte (31) vorbei zum Injektorrücklaufanschluss (7) strömen kann.in that an axially extending channel (40) is arranged within the valve sleeve (28) through which fuel can flow from the control chamber (22) inside the anchor plate (31) to the injector return port (7) when the control valve (29) is open.
2. Injektor nach Anspruch 1, dadurch gekennzeichnet, dass das Steuerventil (29) im geschlossenen Zustand als in axialer Richtung druckausgeglichenes Ventil ausgebildet ist.2. An injector according to claim 1, characterized in that the control valve (29) is formed in the closed state as a pressure-balanced valve in the axial direction.
3. Injektor nach einem der Ansprüche 1 oder 2, dadurch gekennzeichnet, dass der Injektorrücklaufanschluss (7) zentrisch an einer Stirnseite (43) des Injektors (1) angeordnet ist.3. Injector according to one of claims 1 or 2, characterized in that the Injektorrücklaufanschluss (7) centrally to an end face (43) of the injector (1) is arranged.
4. Injektor nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Kanal (40) in einen die Ankerplatte (31) aufnehmenden Ankerraum (34) oder in einen benachbart zum Ankerraum (34) angeordneten Zentralkanal (41) in einer Elektromagnetanordnung (42) des Aktuators (32) mündet .4. Injector according to one of the preceding claims, characterized in that the channel (40) in an armature plate (31) receiving the armature space (34) or in an adjacent to the armature space (34) arranged in the central channel (41) in an electromagnet assembly (42). of the actuator (32) opens.
5. Injektor nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass radial innerhalb der Ventilhülse (28) ein Druckstift (46) angeordnet ist, der als ein von einem einen Steuerventilsitz (35) aufweisenden Plattenelement (21) separates Bauteil ausgebildet ist.5. Injector according to one of the preceding claims, characterized in that radially within the valve sleeve (28) a pressure pin (46) is arranged, which is formed as a one of a control valve seat (35) having a plate member (21) separate component.
6. Injektor nach Anspruch 5, dadurch gekennzeichnet, dass der Kanal (40) als radial zwischen der Ventilhülse (28) und dem Druckstift (46) angeordneter Ringkanal ausgebildet ist.6. An injector according to claim 5, characterized in that the channel (40) is designed as a radially between the valve sleeve (28) and the pressure pin (46) arranged annular channel.
7. Injektor nach einem der Ansprüche 5 oder 6, dadurch gekennzeichnet, dass der Druckstift (46) einen verdickten Endabschnitt7. Injector according to one of claims 5 or 6, characterized in that the pressure pin (46) has a thickened end portion
(47) aufweist, der die Ventilhülse (28) innen in axialer Richtung hochdruckdicht verschließt, und dass an den verdickten Endabschnitt (47) in axialer Richtung ein dünner Abschnitt (48) anschließt, der den(47), which closes the valve sleeve (28) inside high pressure-tight manner in the axial direction, and that the thickened end portion (47) in the axial direction, a thin portion (48) connects, which
Kanal (40) radial innen begrenzt. Channel (40) bounded radially inside.
8. Injektor nach einem der Ansprüche 5 bis 7, dadurch gekennzeichnet, dass sich der Druckstift (46) in axialer Richtung an einem mit mindestens einem Axialkanal (45) ausgestatteten, in Kraftstofffließrichtung vor dem Injektorrücklaufanschluss (7) angeordneten Plattenelement (44) abstützt.8. Injector according to one of claims 5 to 7, characterized in that the pressure pin (46) in the axial direction on a with at least one axial channel (45) equipped, in fuel flow before the injector return port (7) arranged plate member (44) is supported.
9. Injektor nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Ventilhülse (28) in einem dem Steuerventilsitz (35) zugewandten unteren Abschnitt radial außen von einem Ringraum (49) umgeben ist, in den der Kraftstoff bei geöffnetem Steuerventil (29) aus einem Bereich innerhalb der Ventilhülse (28) ausströmen kann, und dass der Ringraum (49) mit dem Kanal (40) hydraulisch verbunden ist.9. Injector according to one of the preceding claims, characterized in that the valve sleeve (28) in a control valve seat (35) facing the lower portion radially outwardly of an annular space (49) is surrounded, in which the fuel with open control valve (29) an area within the valve sleeve (28) can flow out, and that the annular space (49) with the channel (40) is hydraulically connected.
10. Injektor nach Anspruch 9, dadurch gekennzeichnet, dass der Ringraum (49) über eine, insbesondere als Radialbohrung ausgeführte, Bohrung (51) in der Ventilhülse (28) mit dem Kanal (40) verbunden ist.10. An injector according to claim 9, characterized in that the annular space (49) via a, in particular designed as a radial bore, bore (51) in the valve sleeve (28) is connected to the channel (40).
11. Injektor nach einem der Ansprüche 9 oder 10, dadurch gekennzeichnet, dass der Ringraum (49) von einem die Ventilhülse (28) an ihrem Außenumfang führenden Bauteil (50) begrenzt ist.11. Injector according to one of claims 9 or 10, characterized in that the annular space (49) of a valve sleeve (28) on its outer periphery leading component (50) is limited.
12. Injektor nach einem der Ansprüche 9 bis 11, dadurch gekennzeichnet, dass der Ringraum (49) über eine Drossel (53) unmittelbar mit einem Ankerraum (34) hydraulisch verbunden ist, in dem die mit der Ventilhülse (28) wirkverbundene Ankerplatte (31) angeordnet ist. 12. Injector according to one of claims 9 to 11, characterized in that the annular space (49) via a throttle (53) is directly hydraulically connected to an armature space (34), in which with the valve sleeve (28) operatively connected armature plate (31) is arranged.
EP08804280.9A 2007-10-02 2008-09-16 Injector having a sleeve-shaped control valve element Not-in-force EP2195522B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200710047129 DE102007047129A1 (en) 2007-10-02 2007-10-02 Injector with sleeve-shaped control valve element
PCT/EP2008/062323 WO2009047091A1 (en) 2007-10-02 2008-09-16 Injector having a sleeve-shaped control valve element

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EP2195522A1 true EP2195522A1 (en) 2010-06-16
EP2195522B1 EP2195522B1 (en) 2015-11-11

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EP (1) EP2195522B1 (en)
DE (1) DE102007047129A1 (en)
WO (1) WO2009047091A1 (en)

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Publication number Priority date Publication date Assignee Title
DE102009027841A1 (en) * 2009-07-20 2011-01-27 Robert Bosch Gmbh Fuel injection valve
DE102015202726A1 (en) * 2015-02-16 2016-08-18 Robert Bosch Gmbh Control valve assembly

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Publication number Priority date Publication date Assignee Title
JP2005090422A (en) * 2003-09-19 2005-04-07 Bosch Automotive Systems Corp Fuel injection valve
ES2277229T3 (en) 2004-06-30 2007-07-01 C.R.F. Societa Consortile Per Azioni SERVOVALVULA TO CONTROL THE FUEL INJECTOR OF AN INTERNAL COMBUSTION ENGINE.
EP1731752B1 (en) * 2005-05-27 2010-01-20 C.R.F. Società Consortile per Azioni Fuel-control servo valve, and fuel injector provided with such servo valve
DE102006015745A1 (en) * 2006-04-04 2007-10-11 Robert Bosch Gmbh Fuel injector especially for diesel engine has a solenoid operated valve with a bypass for enhanced switching speed
DE102006055548A1 (en) * 2006-11-24 2008-05-29 Robert Bosch Gmbh fuel injector
DE102006055487A1 (en) * 2006-11-24 2008-05-29 Robert Bosch Gmbh fuel injector
DE102007001554A1 (en) * 2007-01-10 2008-07-17 Robert Bosch Gmbh fuel injector

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* Cited by examiner, † Cited by third party
Title
See references of WO2009047091A1 *

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WO2009047091A1 (en) 2009-04-16
DE102007047129A1 (en) 2009-04-09

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