EP2235354B1 - Fuel injector the control valve element of which comprises a support region - Google Patents

Fuel injector the control valve element of which comprises a support region Download PDF

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Publication number
EP2235354B1
EP2235354B1 EP08871236.9A EP08871236A EP2235354B1 EP 2235354 B1 EP2235354 B1 EP 2235354B1 EP 08871236 A EP08871236 A EP 08871236A EP 2235354 B1 EP2235354 B1 EP 2235354B1
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EP
European Patent Office
Prior art keywords
control valve
pressure
valve element
approximately
valve seat
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP08871236.9A
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German (de)
French (fr)
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EP2235354A1 (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
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Robert Bosch GmbH
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Publication of EP2235354A1 publication Critical patent/EP2235354A1/en
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Publication of EP2235354B1 publication Critical patent/EP2235354B1/en
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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
    • 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
    • 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
    • F02M63/0073—Pressure balanced valves
    • 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
    • F02M63/0077—Valve seat details
    • 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, in particular a common rail injector, for injecting fuel into a combustion chamber of an internal combustion engine according to the preamble of claim 1.
  • the control valve comprises a sleeve-shaped control valve element which can be adjusted in the axial direction by means of an electromagnetic actuator and which is guided on a guide pin formed integrally with a valve piece.
  • the sleeve-shaped control valve element delimits with its inner circumference a valve chamber of the control valve formed on a reduced-diameter section of the guide pin only radially outward so that no opening or closing forces from the high pressure fuel within the valve chamber act on the control valve.
  • a sealing line is arranged, which cooperates sealingly with a control valve seat arranged on the valve piece.
  • the diameter of the sealing line corresponds to the guide diameter of the control valve element, wherein the guide diameter corresponds to the outer diameter of the guide pin plus a minimum clearance. Due to its pressure balance, the control valve is suitable for switching very high pressures.
  • a disadvantage of the known injector is the high load on the line-shaped sealing edge when closing the control valve, which can lead to a significant wear on the sealing line.
  • the invention has for its object to provide an injector with a pressure balanced at least approximately in the axial direction control valve, wherein the sealing line wear of the control valve element is reduced.
  • the invention is based on the idea that stability, i. to increase the wear insensitivity of the control valve element in that the approximately line-shaped sealing edge (sealing line) of the control valve element, which rests in the closed position of the control valve sealingly against a control valve seat to assign a support region, viewed in the radial direction across the sealing line away, in the high pressure area of the injector, which is connected with the control valve open to the low pressure region of the injector, thus causing a rapid pressure drop in the control chamber of the injector, which in turn results in an opening movement of the injection valve element.
  • stability i. to increase the wear insensitivity of the control valve element in that the approximately line-shaped sealing edge (sealing line) of the control valve element, which rests in the closed position of the control valve sealingly against a control valve seat to assign a support region, viewed in the radial direction across the sealing line away, in the high pressure area of the injector, which is connected with the control valve open to the low pressure region of the injector, thus
  • the control valve element is not limited in the radial direction from the sealing edge to the pressure chamber, but rather by a support region adjoining the sealing line.
  • the impact pulse with which the control valve element strikes the control valve seat assigned to it is distributed more uniformly in the control valve, in particular in the control valve element, and consequently leads to lower component tensions. This in turn has an increased stability of the control valve element result, with the positive consequence that wear of the sealing line over the life of the injector are minimized.
  • the support region is designed and / or arranged in such a way that it provides the pressure balance of the control valve element in its closed position not or at least not significantly negatively affected.
  • This can be realized, for example, in that the support region is designed and / or arranged such that the pressure forces acting on it in opposite directions cancel each other, at least approximately completely, preferably completely.
  • This is achieved with a support region in which the effective or projection surfaces for generating pressure forces pointing in opposite directions are equal.
  • the inner or the outer diameter (depending on the design) of the control valve element in the region of the sealing line corresponds to the diameter of the control valve element above the support region.
  • the injector in which the diameter of the sealing line, which widened by unavoidable wear over the life of the injector something, and the guide diameter (inner diameter or outer diameter of the control valve element - depending on the design of the control valve element) corresponds.
  • a fully pressure compensated control valve is obtained when the inner diameter of the sealing line exactly corresponds to the inner guide diameter or the outer diameter of the sealing line exactly the outer guide diameter of the control valve element.
  • the high pressure relief angle greater than the low pressure release angle of the control valve.
  • the high-pressure freewheeling angle is the angle in the high-pressure region between the boundary line of the support region or of the control valve element adjoining the sealing line and the control valve seat surface.
  • the low-pressure release angle is the angle between the (lower) boundary line of the control valve element and the control valve seat surface arranged in the low-pressure region of the injector.
  • the low-pressure release angle is from an angle range between 0.5 ° to 5 °, preferably 0.5 ° to 2 °.
  • the high pressure release angle is selected from an angle range between about 5 ° and about 60 °, preferably from an angle range between about 10 ° and about 50 °, more preferably from an angle range between about 20 ° and about 40 °.
  • the difference between the high-pressure freewheeling angle and the low-pressure freewheeling angle is selected from an angle range up to approximately 10 °.
  • the angular difference is between about 1 ° and about 5 °, more preferably between about 1.5 ° and about 3 °.
  • the control valve element angle which is spanned by both extending in the radial direction, adjacent to the sealing line boundary lines of the control valve element, and the control valve seat angle are not the same size.
  • the angular difference is more than 10 °, particularly preferably more than 20 °.
  • Particularly good results with regard to the production accuracy of the sealing line are to be expected with an angular difference between a range between approximately 30 ° and approximately 60 °.
  • the control valve seat angle is greater than the control valve element angle.
  • an at least approximately trapezoidal design of the support region is preferred, wherein the oblique flanks of the trapezoid are connected to one another with a line running parallel to the longitudinal central axis of the control valve element.
  • the pressure compensated control valve is realized with a sleeve-shaped control valve element (valve sleeve).
  • a pressure pin is received within the control valve element.
  • the pressure pin is preferably designed as a separate component from the valve member having the control valve seat, which component has a radially inside the control valve element trained valve chamber seals in the axial direction.
  • the sleeve-shaped control valve element is guided with its inner circumference on the outer circumference of the pressure pin, which is preferably supported on an injector component in the axial direction, preferably on an injector cover or an electromagnet arrangement.
  • an outer guide for the sleeve-shaped control valve element can be provided.
  • the diameter of the sealing line preferably corresponds at least approximately to the outer diameter of the pressure pin, possibly plus a minimum clearance.
  • the support region preferably protrudes into the valve chamber formed inside the sleeve-shaped control valve element, preferably directly connected to the control chamber, and is located between the sealing line and the pressure pin in the axial direction.
  • control valve seat is particularly advantageous to design the control valve seat as a flat seat or a conical seat.
  • Fig. 1 is designed as a common rail injector injector 1 for injecting fuel into a combustion chamber, not shown, of an internal combustion engine of a motor vehicle.
  • a high pressure pump 2 delivers fuel from a reservoir 3 in a high-pressure fuel storage 4 (Rail). In this fuel, especially diesel or gasoline, under high pressure, of about 2000 bar in this embodiment, stored.
  • 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.
  • a return line 8 a low-pressure region 9 of the injector 1 is connected to the reservoir 3. Via the return line 8, a later to be explained control amount of fuel from the injector 1 to the reservoir 3 to flow.
  • an injection valve element 11 is arranged within a nozzle body 13.
  • the injection valve element 11 is on the one hand guided longitudinally displaceable in a lower, sleeve-shaped portion of a valve member 12 and at an axial distance to it in a bore of a nozzle body 13.
  • 13 axial channels 14 (Ausschliffe) are formed on the outer circumference of the injection valve element 11 in the region of its leadership within the nozzle body, via which the pressure chamber 6 is connected to the nozzle chamber 7.
  • the nozzle body 13 is screwed to the injector body 10 via a union nut, not shown.
  • the injection valve element 11 has at its tip 15 a closing surface 16 with which the injection valve element 11 can be brought into close contact with an injection valve element seat 17 formed inside the nozzle body 13.
  • an injection valve element seat 17 formed inside the nozzle body 13.
  • the injection valve element 11 abuts against its injection valve element seat 17, ie is in a closed position, the fuel outlet from a nozzle hole arrangement 18 is blocked. If, on the other hand, it is lifted off its injection valve element seat 17, fuel can flow out of the pressure chamber 6 via the axial channels 14 into the nozzle chamber 7 past the injection valve element 11 to the nozzle hole arrangement 18 within the nozzle body 13 and there substantially under high pressure (rail pressure) into the combustion chamber (FIG. not shown).
  • a control chamber 20 is limited, via a radially in the sleeve-shaped portion of the valve member 12th running inlet throttle 21 is supplied with high-pressure fuel from the pressure chamber 6.
  • the control chamber 20 is connected via a, arranged in the upper, plate-shaped portion of the valve member 12 drain passage 22 with outlet throttle 23 with a valve chamber 24 which is bounded radially outwardly by a sleeve-shaped control valve element 25 of a control valve 26 (servo valve).
  • valve chamber 24 fuel can flow from the valve chamber 24 (high-pressure region) into the low-pressure region 9 of the injector 1 when the control valve element 25 which can be actuated by an electromagnetic actuator 27 lifts off from its control valve seat 28 which is designed as a flat seat and is arranged on the plate-shaped section of the valve piece 12, ie the control valve 26 is open.
  • the control valve seat angle is 180 ° in the flat seat shown.
  • the flow cross sections of the inlet throttle 21 and the outlet throttle 23 are matched to one another such that when the control valve 26 is open, a net outflow of fuel (control quantity) from the control chamber 20 via the valve chamber 24 into the low-pressure region 9 of the injector 1 and from there via the return line 8 into the reservoir 3 results ,
  • the control valve 26 is designed as a valve pressure-balanced in the axial direction in the closed state.
  • the control valve element 25 is formed integrally with its in the drawing plane upper portion with an anchor plate 29 which cooperates with an electromagnet assembly 30 of the electromagnetic actuator.
  • a pressure pin 31 is arranged, which is designed as a separate component from the valve member 12, and which seals the valve chamber 24 in the axial direction upwards. The pressure forces acting on it are supported by the pressure pin 31 on an injector cover 32 screwed to the injector body 10.
  • the pressure pin 31 passes through a central passage opening 33 within the solenoid assembly 30.
  • An annular, line-shaped sealing line 34 of the control valve element 25, which cooperates sealingly in the closed state of the control valve 26 with the control valve seat 28, located on an inner guide diameter D iF , with the Control valve element 25 is guided on the pressure pin 31.
  • the control valve member 25 is guided at its outer periphery by means of a guide plate 35 which is penetrated by the control valve member 25 and which is located axially between the anchor plate 29 and the valve member 12 with its control valve seat 28.
  • control closing spring 36 which is supported in the axial direction on the one hand on the injector cover 32 and on the other from the unit consisting of control valve element 25 and anchor plate 29.
  • the sleeve-shaped control valve element 25 lifts off from its control valve seat 28 designed as a flat seat, whereby the valve chamber 24, ie the high-pressure region 37 of the injector 1, is connected to the low-pressure region 9, whereby the pressure within the hydraulic via the outlet throttle 23 connected to the valve chamber 24 control chamber 20 drops rapidly and the injection valve element 11 moves in the axial direction of the drawing plane up into the control chamber, whereby fuel in the sequence can flow from the nozzle chamber 7 into the combustion chamber.
  • the energization of the solenoid assembly 30 of the electromagnetic actuator 27 is interrupted.
  • the control closing spring 36 subsequently moves the sleeve-shaped control valve element 25 back onto its control valve seat 28 on the upper side of the valve piece 12 in the drawing plane.
  • the fuel flowing in through the inlet throttle 21 rapidly increases the pressure in the control chamber 20, as a result of which the injection valve element 11, supported by the spring force of a closing spring 38, which is supported on a peripheral collar 39 of the injection valve element 11 and on the sleeve-shaped, lower portion of the valve piece 12, is moved in the direction of the injection valve element seat 17, which in turn the flow of fuel from the nozzle hole arrangement 18 into the combustion chamber is interrupted.
  • the at least approximately line-shaped sealing edge is located on the inner guide diameter D iF .
  • the (inner) diameter D D of the sealing line 34 corresponds to the inner guide diameter D iF of the control valve element 25.
  • the sealing line 34 is surmounted by an annular, trapezoidal support region 40 extending from the sealing line 34, which is completely within the high-pressure region 37 , More specifically, is disposed within the valve chamber 24.
  • Fig. 2 the sleeve-shaped control valve element 25 is shown, into which the pressure pin 31 protrudes.
  • the control valve element 25 (additionally) is guided on its outer circumference, an embodiment of the injector 1 can be realized, is dispensed with in an external guide for the sleeve-shaped control valve element.
  • the sleeve-shaped control valve element 25 is delimited at its lower end face in the plane of the drawing by a delimiting line 41 which, in the exemplary embodiment shown, extends exactly in the radial direction outwards from the sealing line 34. Radially inside adjacent to the sealing line 34 at a lower boundary line 42 of the support portion 40 at.
  • the two boundary lines 41, 42 include a control valve element angle ⁇ . This is about 140 ° in the embodiment shown.
  • the control valve seat angle ⁇ ie the angle between two diametrically opposite surface portions of the control valve seat 28 is in the illustrated embodiment about 160 °. The difference between the angles ⁇ and ⁇ is thus 20 °.
  • a high pressure release angle ⁇ between the (lower) boundary line 42 of the support portion 40 and the conical control valve seat surface 43 in the high pressure region 37 is about 3 ° greater than the low pressure release angle ⁇ between the lower boundary line 41 of the control valve element 25 in the low-pressure region 9 and the control valve seat surface 43.
  • the in connection with Fig. 2 Angular ratios described also apply to the embodiment according to Fig. 1 ., Wherein only the control valve seat 28 is not formed as a conical seat, but as a flat seat, whereby in the sequence compared to the embodiment according to Fig. 1 the boundary line 41 can not extend exactly perpendicular to the longitudinal central axis of the control valve element 25.

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

Description

Stand der TechnikState of the art

Die Erfindung betrifft einen Injektor, insbesondere einen Common-Rail-Injektor, zum Einspritzen von Kraftstoff in einen Brennraum einer Brennkraftmaschine gemäß dem Oberbegriff des Anspruchs 1.The invention relates to an injector, in particular a common rail injector, for injecting fuel into a combustion chamber of an internal combustion engine according to the preamble of claim 1.

Aus der EP 1 612 403 A1 und aus der WO 2009 016003 ist ein als Common-Rail-Injektor ausgebildeter Injektor mit einem in axialer Richtung druckausgeglichenen Steuerventil (Servoventil) zum Sperren und Öffnen eines Kraftstoff-Ablaufkanals aus einer Steuerkammer bekannt. Mittels des Steuerventils kann der Kraftstoffdruck innerhalb der Steuerkammer beeinflusst werden, wobei die Steuerkammer dauerhaft über eine Zulaufdrossel mit unter Hochdruck stehendem Kraftstoff versorgt wird. Durch Variation des Kraftstoffdruckes innerhalb der Steuerkammer wird ein Einspritzventilelement zwischen einer Öffnungsstellung und einer Schließstellung verstellt, wobei das Einspritzventilelement in seiner Öffnungsstellung den Kraftstofffluss in den Brennraum einer Brennkraftmaschine freigibt. Das Steuerventil umfasst ein in axialer Richtung mittels eines elektromagnetischen Aktuators verstellbares, hülsenförmiges Steuerventilelement, das an einem einstückig mit einem Ventilstück ausgebildeten Führungsbolzen geführt ist. Das hülsenförmige Steuerventilelement begrenzt mit seinem Innenumfang eine an einem durchmesserreduzierten Abschnitt des Führungsbolzens ausgebildete Ventilkammer des Steuerventils lediglich radial außen, sodass keine öffnenden oder schließenden Kräfte von dem unter Hochdruck stehenden Kraftstoff innerhalb der Ventilkammer auf das Steuerventil wirken. An der Stirnseite des Steuerventilelementes ist eine Dichtlinie angeordnet, die mit einem am Ventilstück angeordneten Steuerventilsitz dichtend zusammenwirkt. Der Durchmesser der Dichtlinie entspricht dabei dem Führungsdurchmesser des Steuerventilelementes, wobei der Führungsdurchmesser dem Außendurchmesser des Führungsbolzens zuzüglich eines minimalen Spiels entspricht. Aufgrund seiner Druckausgeglichenheit ist das Steuerventil zum Schalten sehr großer Drücke geeignet. Nachteilig bei dem bekannten Injektor ist die hohe Belastung auf die linienförmige Dichtkante beim Schließen des Steuerventils, die zu einem nicht unerheblichen Verschleiß an der Dichtlinie führen kann.From the EP 1 612 403 A1 and from the WO 2009 016003 is a trained as a common rail injector injector with a pressure-balanced in the axial direction control valve (servo valve) for blocking and opening a fuel flow channel from a control chamber known. By means of the control valve, the fuel pressure can be influenced within the control chamber, wherein the control chamber is permanently supplied via an inlet throttle with fuel under high pressure. By varying the fuel pressure within the control chamber, an injection valve element is adjusted between an open position and a closed position, the injection valve element releasing the fuel flow into the combustion chamber of an internal combustion engine in its open position. The control valve comprises a sleeve-shaped control valve element which can be adjusted in the axial direction by means of an electromagnetic actuator and which is guided on a guide pin formed integrally with a valve piece. The sleeve-shaped control valve element delimits with its inner circumference a valve chamber of the control valve formed on a reduced-diameter section of the guide pin only radially outward so that no opening or closing forces from the high pressure fuel within the valve chamber act on the control valve. At the end face of the control valve element, a sealing line is arranged, which cooperates sealingly with a control valve seat arranged on the valve piece. The diameter of the sealing line corresponds to the guide diameter of the control valve element, wherein the guide diameter corresponds to the outer diameter of the guide pin plus a minimum clearance. Due to its pressure balance, the control valve is suitable for switching very high pressures. A disadvantage of the known injector is the high load on the line-shaped sealing edge when closing the control valve, which can lead to a significant wear on the sealing line.

Offenbarung der ErfindungDisclosure of the invention Technische AufgabeTechnical task

Der Erfindung liegt die Aufgabe zugrunde, einen Injektor mit einem zumindest näherungsweise in axialer Richtung druckausgeglichenen Steuerventil vorzuschlagen, bei dem der Dichtlinienverschleiß des Steuerventilelementes reduziert ist.The invention has for its object to provide an injector with a pressure balanced at least approximately in the axial direction control valve, wherein the sealing line wear of the control valve element is 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. In the context of the invention, all combinations of at least fall two features disclosed in the specification, claims and / or figures.

Der Erfindung liegt der Gedanke zugrunde, die Stabilität, d.h. die Verschleißunempfindlichkeit, des Steuerventilelementes dadurch zu erhöhen, dass der näherungsweise linienförmigen Dichtkante (Dichtlinie) des Steuerventilelementes, welche in der Schließstellung des Steuerventils dichtend an einem Steuerventilsitz anliegt, einen Stützbereich zuzuordnen, der sich in radialer Richtung betrachtet über die Dichtlinie hinweg, in den Hochdruckbereich des Injektors erstreckt, welcher bei geöffnetem Steuerventil mit dem Niederdruckbereich des Injektors verbunden ist, um somit einen rapiden Druckabfall in der Steuerkammer des Injektors zu verursachen, woraus wiederum eine Öffnungsbewegung des Einspritzventilelementes resultiert. Anders ausgedrückt wird das Steuerventilelement bei einem nach dem Konzept der Erfindung ausgebildeten Injektor in radialer Richtung nicht von der Dichtkante zum Druckraum hin begrenzt, sondern von einem an die Dichtlinie angrenzenden Stützbereich. Durch das erfindungsgemäße Vorsehen eines Stützbereichs wird der Einschlagimpuls, mit dem das Steuerventilelement auf den ihm zugeordneten Steuerventilsitz einschlägt, gleichmäßiger im Steuerventil, insbesondere im Steuerventilelement, verteilt und führt in der Folge zu geringeren Bauteilspannungen. Dies wiederum hat eine erhöhte Stabilität des Steuerventilelementes zur Folge, mit der positiven Konsequenz, dass Verschleißerscheinungen der Dichtlinie über die Lebensdauer des Injektors minimiert werden.The invention is based on the idea that stability, i. to increase the wear insensitivity of the control valve element in that the approximately line-shaped sealing edge (sealing line) of the control valve element, which rests in the closed position of the control valve sealingly against a control valve seat to assign a support region, viewed in the radial direction across the sealing line away, in the high pressure area of the injector, which is connected with the control valve open to the low pressure region of the injector, thus causing a rapid pressure drop in the control chamber of the injector, which in turn results in an opening movement of the injection valve element. In other words, in the case of an injector designed according to the concept of the invention, the control valve element is not limited in the radial direction from the sealing edge to the pressure chamber, but rather by a support region adjoining the sealing line. By providing a support region according to the invention, the impact pulse with which the control valve element strikes the control valve seat assigned to it is distributed more uniformly in the control valve, in particular in the control valve element, and consequently leads to lower component tensions. This in turn has an increased stability of the control valve element result, with the positive consequence that wear of the sealing line over the life of the injector are minimized.

In Weiterbildung der Erfindung ist mit Vorteil vorgesehen, dass der Stützbereich derart ausgebildet und/oder angeordnet ist, dass dieser die Druckausgeglichenheit des Steuerventilelementes in seiner Schließstellung nicht oder zumindest nicht wesentlich negativ beeinflusst. Dies kann beispielsweise dadurch realisiert werden, dass der Stützbereich derart ausgebildet und/oder angeordnet ist, dass sich die auf ihn in einander entgegengesetzte Richtungen wirkenden Druckkräfte, zumindest näherungsweise vollständig, vorzugsweise vollständig aufheben. Dies wird mit einem Stützbereich erreicht, bei dem die Wirk- bzw. Projektionsflächen zum Erzeugen von in einander entgegengesetzte Richtungen weisenden Druckkräften gleich groß sind. Dies kann beispielsweise dadurch realisiert werden, dass der innere oder der äußere Durchmesser (abhängig von der Bauform) des Steuerventilelementes im Bereich der Dichtlinie dem Durchmesser des Steuerventilelementes oberhalb des Stützbereichs entspricht.In a development of the invention, it is advantageously provided that the support region is designed and / or arranged in such a way that it provides the pressure balance of the control valve element in its closed position not or at least not significantly negatively affected. This can be realized, for example, in that the support region is designed and / or arranged such that the pressure forces acting on it in opposite directions cancel each other, at least approximately completely, preferably completely. This is achieved with a support region in which the effective or projection surfaces for generating pressure forces pointing in opposite directions are equal. This can be realized, for example, in that the inner or the outer diameter (depending on the design) of the control valve element in the region of the sealing line corresponds to the diameter of the control valve element above the support region.

Von besonderem Vorteil ist eine Ausführungsform des Injektors, bei der der Durchmesser der Dichtlinie, die sich durch nicht zu vermeidende Verschleißerscheinungen über die Lebensdauer des Injektors etwas verbreitert, und dem Führungsdurchmesser (Innendurchmesser oder Außendurchmesser des Steuerventilelementes - abhängig von der Bauform des Steuerventilelementes) entspricht. Ein vollkommen druckausgeglichenes Steuerventil wird erhalten, wenn der innere Durchmesser der Dichtlinie exakt dem inneren Führungsdurchmesser bzw. der äußere Durchmesser der Dichtlinie exakt dem äußeren Führungsdurchmesser des Steuerventilelementes entspricht.Of particular advantage is an embodiment of the injector, in which the diameter of the sealing line, which widened by unavoidable wear over the life of the injector something, and the guide diameter (inner diameter or outer diameter of the control valve element - depending on the design of the control valve element) corresponds. A fully pressure compensated control valve is obtained when the inner diameter of the sealing line exactly corresponds to the inner guide diameter or the outer diameter of the sealing line exactly the outer guide diameter of the control valve element.

Um die Auswirkungen eines nicht zu vermeidenden Dichtlinienverschleißes auf die druckausgeglichene Eigenschaft des Steuerventils zu minimieren, ist der Hochdruckfreilassungswinkel größer als der Niederdruckfreilassungswinkel des Steuerventils. Dabei ist der Hochdruckfreilassungswinkel der im Hochdruckbereich gelegene Winkel zwischen der an die Dichtlinie angrenzenden Begrenzungslinie des Stützbereichs bzw. des Steuerventilelementes und der Steuerventilsitzfläche. Bei dem Niederdruckfreilassungswinkel handelt es sich um den im Niederdruckbereich des Injektors angeordneten Winkel zwischen der (unteren) Begrenzungslinie des Steuerventilelementes und der Steuerventilsitzfläche.To minimize the effects of unavoidable seal line wear on the pressure balanced property of the control valve is the high pressure relief angle greater than the low pressure release angle of the control valve. In this case, the high-pressure freewheeling angle is the angle in the high-pressure region between the boundary line of the support region or of the control valve element adjoining the sealing line and the control valve seat surface. The low-pressure release angle is the angle between the (lower) boundary line of the control valve element and the control valve seat surface arranged in the low-pressure region of the injector.

Der Niederdruckfreilassungswinkel aus ist einem Winkelbereich zwischen 0,5° bis 5°, bevorzugt 0,5° bis 2°. Idealerweise ist der Hochdruckfreilassungswinkel aus einem Winkelbereich zwischen etwa 5° und etwa 60°, bevorzugt aus einem Winkelbereich zwischen etwa 10° und etwa 50°, besonders bevorzugt aus einem Winkelbereich zwischen etwa 20° und etwa 40° gewählt. Von besonderem Vorteil ist eine Ausführungsform, bei der die Differenz zwischen dem Hochdruckfreilassungswinkel und dem Niederdruckfreilassungswinkel aus einem Winkelbereich bis etwa 10° gewählt ist. Idealerweise liegt die Winkeldifferenz zwischen etwa 1° und etwa 5°, besonders bevorzugt zwischen etwa 1,5° und etwa 3°.The low-pressure release angle is from an angle range between 0.5 ° to 5 °, preferably 0.5 ° to 2 °. Ideally, the high pressure release angle is selected from an angle range between about 5 ° and about 60 °, preferably from an angle range between about 10 ° and about 50 °, more preferably from an angle range between about 20 ° and about 40 °. Of particular advantage is an embodiment in which the difference between the high-pressure freewheeling angle and the low-pressure freewheeling angle is selected from an angle range up to approximately 10 °. Ideally, the angular difference is between about 1 ° and about 5 °, more preferably between about 1.5 ° and about 3 °.

Um die Fertigungsgenauigkeit der Dichtlinie bei einem nach dem Konzept der Erfindung ausgebildeten Injektor mit vertretbarem Aufwand gewährleisten zu können, ist eine Ausführungsform bevorzugt, bei der der Steuerventilelementwinkel, der von beiden in radialer Richtung verlaufenden, an die Dichtlinie angrenzenden Begrenzungslinien des Steuerventilelementes aufgespannt wird, und der Steuerventilsitzwinkel nicht gleich groß sind. Besonders bevorzugt beträgt die Winkeldifferenz mehr als 10°, besonders bevorzugt mehr als 20°. Besonders gute Ergebnisse im Hinblick auf die Fertigungsgenauigkeit der Dichtlinie sind bei einer Winkeldifferenz aus einem Bereich zwischen etwa 30° und etwa 60° zu erwarten. Idealerweise ist der Steuerventilsitzwinkel dabei größer als der Steuerventilelementwinkel. Durch das Vorsehen einer zuvor beschriebenen Winkeldifferenz zwischen dem Steuerventilelementwinkel und dem Steuerventilsitzwinkel ist zum einen eine ausreichend große Stützwirkung des Stützbereichs gegeben und zum anderen resultiert eine exakte Herstellbarkeit der Dichtlinie (Dichtkante). Um die Stützwirkung (auf Kosten der exakten Herstellbarkeit) zu erhöhen, kann auch eine kleinere Winkeldifferenz gewählt werden.In order to ensure the manufacturing accuracy of the sealing line in an embodied according to the concept of the invention injector with reasonable effort, an embodiment is preferred in which the control valve element angle, which is spanned by both extending in the radial direction, adjacent to the sealing line boundary lines of the control valve element, and the control valve seat angle are not the same size. Particularly preferably, the angular difference is more than 10 °, particularly preferably more than 20 °. Particularly good results with regard to the production accuracy of the sealing line are to be expected with an angular difference between a range between approximately 30 ° and approximately 60 °. Ideally, the control valve seat angle is greater than the control valve element angle. By providing a previously described angular difference between the control valve element angle and the control valve seat angle on the one hand given a sufficiently large support effect of the support region and on the other results in an exact manufacturability of the sealing line (sealing edge). In order to increase the supporting effect (at the expense of exact manufacturability), a smaller angular difference can also be selected.

Im Hinblick auf eine einfache Fertigbarkeit des Stützbereichs ist eine zumindest näherungsweise trapezförmige Ausbildung des Stützbereichs bevorzugt, wobei die schrägen Flanken des Trapezes mit einer parallel zur Längsmittelachse des Steuerventilelementes verlaufenden Linie miteinander verbunden sind.With regard to simple manufacturability of the support region, an at least approximately trapezoidal design of the support region is preferred, wherein the oblique flanks of the trapezoid are connected to one another with a line running parallel to the longitudinal central axis of the control valve element.

Das druckausgeglichene Steuerventil wird mit einem hülsenförmigen Steuerventilelement (Ventilhülse) realisiert. Für den Fall des Vorsehens eines als Ventilhülse ausgebildeten Steuerventilelementes ist eine Ausführungsform bevorzugt, bei der innerhalb des Steuerventilelementes ein Druckstift aufgenommen ist. Dabei ist der Druckstift bevorzugt als von dem den Steuerventilsitz aufweisenden Ventilstück separates Bauteil ausgebildet, welches eine radial innerhalb des Steuerventilelementes ausgebildete Ventilkammer in axialer Richtung abdichtet. Bevorzugt ist das hülsenförmige Steuerventilelement dabei mit seinem Innenumfang am Außenumfang des Druckstiftes geführt, welcher sich bevorzugt an einem Injektorbauteil in axialer Richtung, vorzugsweise an einem Injektordeckel oder einer Elektromagnetanordnung, abstützt. Zusätzlich oder alternativ zu der Ausbildung des Druckstiftes als innere Führung kann eine Außenführung für das hülsenförmige Steuerventilelement vorgesehen werden. Unabhängig davon, ob eine innere und/oder äußere Führung für die Ventilhülse vorgesehen wird, entspricht der Durchmesser der Dichtlinie bevorzugt zumindest näherungsweise dem Außendurchmesser des Druckstiftes, ggf. zuzüglich eines minimalen Spiels. Bei einer Ausführungsform des Steuerventilelementes als Ventilhülse ragt der Stützbereich bevorzugt in die innerhalb des hülsenförmigen Steuerventilelementes ausgebildete, vorzugsweise unmittelbar mit der Steuerkammer verbundene Ventilkammer hinein und befindet sich in axialer Richtung betrachtet zwischen der Dichtlinie und dem Druckstift.The pressure compensated control valve is realized with a sleeve-shaped control valve element (valve sleeve). In the case of providing a valve sleeve designed as a control valve element, an embodiment is preferred in which a pressure pin is received within the control valve element. In this case, the pressure pin is preferably designed as a separate component from the valve member having the control valve seat, which component has a radially inside the control valve element trained valve chamber seals in the axial direction. Preferably, the sleeve-shaped control valve element is guided with its inner circumference on the outer circumference of the pressure pin, which is preferably supported on an injector component in the axial direction, preferably on an injector cover or an electromagnet arrangement. Additionally or alternatively to the formation of the pressure pin as an inner guide, an outer guide for the sleeve-shaped control valve element can be provided. Regardless of whether an inner and / or outer guide is provided for the valve sleeve, the diameter of the sealing line preferably corresponds at least approximately to the outer diameter of the pressure pin, possibly plus a minimum clearance. In one embodiment of the control valve element as a valve sleeve, the support region preferably protrudes into the valve chamber formed inside the sleeve-shaped control valve element, preferably directly connected to the control chamber, and is located between the sealing line and the pressure pin in the axial direction.

Von besonderem Vorteil ist es, den Steuerventilsitz als Flachsitz oder Kegelsitz auszubilden.It is particularly advantageous to design the control valve seat as a flat seat or a conical 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 Zeichnungen. Diese zeigen in:

Fig. 1
eine schematische Darstellung eines als Common-Rail-Injektor ausgebildeten Injektors mit einem hülsenförmigen Steuerventilelement, welches einen nach radial innen weisenden Stützbereich für die Dichtlinie aufweist, und
Fig. 2
eine unvollständige Darstellung eines alternativen Ausführungsbeispiels eines Injektors dessen hülsenförmiges Steuerventilelement einen nach radial innen weisenden Stützbereich aufweist, wobei der Steuerventilsitz im Gegensatz zu dem Ausführungsbeispiel gemäß Fig. 1 als Kegelsitz ausgebildet ist.
Further advantages, features and details of the invention will become apparent from the following description of preferred embodiments and from the drawings. These show in:
Fig. 1
a schematic representation of an injector designed as a common rail injector with a sleeve-shaped control valve element, which has a radially inwardly facing support region for the sealing line, and
Fig. 2
a fragmentary view of an alternative embodiment of an injector whose sleeve-shaped control valve member has a radially inwardly facing support region, wherein the control valve seat in contrast to the embodiment according to Fig. 1 is designed as a conical seat.

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 als Common-Rail-Injektor ausgebildeter Injektor 1 zum Einspritzen von Kraftstoff in einen nicht gezeigten Brennraum einer Brennkraftmaschine eines Kraftfahrzeugs dargestellt. Eine Hochdruckpumpe 2 fördert Kraftstoff aus einem Vorratsbehälter 3 in einen Kraftstoff-Hochdruckspeicher 4 (Rail). In diesem 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. Mittels einer Rücklaufleitung 8 ist ein Niederdruckbereich 9 des Injektors 1 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.In Fig. 1 is designed as a common rail injector injector 1 for injecting fuel into a combustion chamber, not shown, of an internal combustion engine of a motor vehicle. A high pressure pump 2 delivers fuel from a reservoir 3 in a high-pressure fuel storage 4 (Rail). In this fuel, especially diesel or gasoline, under high pressure, of about 2000 bar in this embodiment, stored. 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. By means of a return line 8, a low-pressure region 9 of the injector 1 is connected to the reservoir 3. Via the return line 8, a later to be explained control amount of fuel from the injector 1 to the reservoir 3 to flow.

Innerhalb eines Düsenkörpers 13 ist ein Einspritzventilelement 11 angeordnet. Das Einspritzventilelement 11 ist zum einen längsverschieblich in einem unteren, hülsenförmigen Abschnitt eines Ventilstückes 12 sowie mit Axialabstand dazu in einer Bohrung eines Düsenkörpers 13 geführt. Dabei sind am Außenumfang des Einspritzventilelementes 11 im Bereich seiner Führung innerhalb des Düsenkörpers 13 Axialkanäle 14 (Ausschliffe) ausgebildet, über die der Druckraum 6 mit dem Düsenraum 7 verbunden ist. Der Düsenkörper 13 ist über eine nicht dargestellte Überwurfmutter mit dem Injektorkörper 10 verschraubt.Within a nozzle body 13, an injection valve element 11 is arranged. The injection valve element 11 is on the one hand guided longitudinally displaceable in a lower, sleeve-shaped portion of a valve member 12 and at an axial distance to it in a bore of a nozzle body 13. In this case, 13 axial channels 14 (Ausschliffe) are formed on the outer circumference of the injection valve element 11 in the region of its leadership within the nozzle body, via which the pressure chamber 6 is connected to the nozzle chamber 7. The nozzle body 13 is screwed to the injector body 10 via a union nut, not shown.

Das Einspritzventilelement 11 weißt an seiner Spitze 15 eine Schließfläche 16 auf, mit der das Einspritzventilelement 11 in dichter Anlage an einen innerhalb des Düsenkörpers 13 ausgebildeten Einspritzventilelementsitz 17 bringbar ist. Wenn das Einspritzventilelement 11 an seinem Einspritzventilelementsitz 17 anliegt, d.h. sich in einer Schließstellung befindet, ist der Kraftstoffaustritt aus einer Düsenlochanordnung 18 gesperrt. Ist es dagegen von seinem Einspritzventilelementsitz 17 abgehoben, kann Kraftstoff aus dem Druckraum 6 über die Axialkanäle 14 in den Düsenraum 7 an dem Einspritzventilelement 11 vorbei zur Düsenlochanordnung 18 innerhalb des Düsenkörpers 13 strömen und dort im Wesentlichen unter Hochdruck (Raildruck) stehend in den Brennraum (nicht gezeigt) gespritzt werden.The injection valve element 11 has at its tip 15 a closing surface 16 with which the injection valve element 11 can be brought into close contact with an injection valve element seat 17 formed inside the nozzle body 13. When the injection valve element 11 abuts against its injection valve element seat 17, ie is in a closed position, the fuel outlet from a nozzle hole arrangement 18 is blocked. If, on the other hand, it is lifted off its injection valve element seat 17, fuel can flow out of the pressure chamber 6 via the axial channels 14 into the nozzle chamber 7 past the injection valve element 11 to the nozzle hole arrangement 18 within the nozzle body 13 and there substantially under high pressure (rail pressure) into the combustion chamber (FIG. not shown).

Von einer oberen Stirnseite 19 des Einspritzventilelementes 11, welches anstelle der gezeigten einteiligen Ausbildung auch mehrteilig ausgebildet werden kann, und dem in der Zeichnungsebene unteren, hülsenförmigen Abschnitt des Ventilstückes 12 wird eine Steuerkammer 20 begrenzt, die über eine radial in dem hülsenförmigen Abschnitt des Ventilstücks 12 verlaufende Zulaufdrossel 21 mit unter Hochdruck stehendem Kraftstoff aus dem Druckraum 6 versorgt wird. Die Steuerkammer 20 ist über einen, in dem oberen, plattenförmigen Abschnitt des Ventilstückes 12 angeordneten Ablaufkanal 22 mit Ablaufdrossel 23 mit einer Ventilkammer 24 verbunden, die radial außen von einem hülsenförmigen Steuerventilelement 25 eines Steuerventils 26 (Servoventil) begrenzt ist. Aus der Ventilkammer 24 kann Kraftstoff aus der Ventilkammer 24 (Hochdruckbereich) in den Niederdruckbereich 9 des Injektors 1 strömen, wenn das von einem elektromagnetischen Aktuator 27 betätigbare Steuerventilelement 25 von seinem als Flachsitz ausgebildeten und an dem plattenförmigen Abschnitt des Ventilstücks 12 angeordneten Steuerventilsitz 28 abgehoben, d.h. das Steuerventil 26 geöffnet ist. Der Steuerventilsitzwinkel beträgt bei dem gezeigten Flachsitz 180°. Die Durchflussquerschnitte der Zulaufdrossel 21 und der Ablaufdrossel 23 sind derart aufeinander abgestimmt, dass bei geöffnetem Steuerventil 26 ein Nettoabfluss von Kraftstoff (Steuermenge) aus der Steuerkammer 20 über die Ventilkammer 24 in den Niederdruckbereich 9 des Injektors 1 und von dort aus über die Rücklaufleitung 8 in den Vorratsbehälter 3 resultiert.From an upper end face 19 of the injection valve element 11, which can also be formed in several parts instead of the one-piece design shown, and the lower in the drawing plane, sleeve-shaped portion of the valve piece 12, a control chamber 20 is limited, via a radially in the sleeve-shaped portion of the valve member 12th running inlet throttle 21 is supplied with high-pressure fuel from the pressure chamber 6. The control chamber 20 is connected via a, arranged in the upper, plate-shaped portion of the valve member 12 drain passage 22 with outlet throttle 23 with a valve chamber 24 which is bounded radially outwardly by a sleeve-shaped control valve element 25 of a control valve 26 (servo valve). From the valve chamber 24, fuel can flow from the valve chamber 24 (high-pressure region) into the low-pressure region 9 of the injector 1 when the control valve element 25 which can be actuated by an electromagnetic actuator 27 lifts off from its control valve seat 28 which is designed as a flat seat and is arranged on the plate-shaped section of the valve piece 12, ie the control valve 26 is open. The control valve seat angle is 180 ° in the flat seat shown. The flow cross sections of the inlet throttle 21 and the outlet throttle 23 are matched to one another such that when the control valve 26 is open, a net outflow of fuel (control quantity) from the control chamber 20 via the valve chamber 24 into the low-pressure region 9 of the injector 1 and from there via the return line 8 into the reservoir 3 results ,

Das Steuerventil 26 ist als im geschlossenen Zustand in axialer Richtung druckausgeglichenes Ventil ausgebildet. Dabei ist das Steuerventilelement 25 mit seinem in der Zeichnungsebene oberen Abschnitt einstückig mit einer Ankerplatte 29 ausgebildet, die mit einer Elektromagnetanordnung 30 des elektromagnetischen Aktuators zusammenwirkt. Radial innerhalb des hülsenförmigen Steuerventilelementes 25 ist ein Druckstift 31 angeordnet, der als von dem Ventilstück 12 separates Bauteil ausgebildet ist, und der die Ventilkammer 24 in axialer Richtung nach oben abdichtet. Die auf ihn wirkenden Druckkräfte stützt der Druckstift 31 an einem mit dem Injektorkörper 10 verschraubten Injektordeckel 32 ab. Hierzu durchsetzt der Druckstift 31 eine zentrale Durchgangsöffnung 33 innerhalb der Elektromagnetanordnung 30. Eine kreisringförmige, linienförmige Dichtlinie 34 des Steuerventilelementes 25, die im geschlossenen Zustand des Steuerventils 26 mit dem Steuerventilsitz 28 dichtend zusammenwirkt, befindet sich auf einem inneren Führungsdurchmesser DiF, mit dem das Steuerventilelement 25 am Druckstift 31 geführt ist. Zusätzlich ist das Steuerventilelement 25 an seinem Außenumfang mittels einer Führungsplatte 35 geführt, die von dem Steuerventilelement 25 durchsetzt ist und die sich axial zwischen der Ankerplatte 29 und dem Ventilstück 12 mit seinem Steuerventilsitz 28 befindet. Innerhalb der Durchgangsöffnung 33 befindet sich neben dem in diesem Ausführungsbeispiel einteilig ausgebildeten, jedoch mehrteilig ausbildbaren, Druckstift 31 eine Steuerschließfeder 36, die sich in axialer Richtung zum einen am Injektordeckel 32 und zum anderen aus der Einheit, bestehend aus Steuerventilelement 25 und Ankerplatte 29, abstützt.The control valve 26 is designed as a valve pressure-balanced in the axial direction in the closed state. In this case, the control valve element 25 is formed integrally with its in the drawing plane upper portion with an anchor plate 29 which cooperates with an electromagnet assembly 30 of the electromagnetic actuator. Radially within the sleeve-shaped control valve element 25, a pressure pin 31 is arranged, which is designed as a separate component from the valve member 12, and which seals the valve chamber 24 in the axial direction upwards. The pressure forces acting on it are supported by the pressure pin 31 on an injector cover 32 screwed to the injector body 10. For this purpose, the pressure pin 31 passes through a central passage opening 33 within the solenoid assembly 30. An annular, line-shaped sealing line 34 of the control valve element 25, which cooperates sealingly in the closed state of the control valve 26 with the control valve seat 28, located on an inner guide diameter D iF , with the Control valve element 25 is guided on the pressure pin 31. In addition, the control valve member 25 is guided at its outer periphery by means of a guide plate 35 which is penetrated by the control valve member 25 and which is located axially between the anchor plate 29 and the valve member 12 with its control valve seat 28. Within the passage opening 33 is located next to the one-piece in this embodiment, However, multi-part formable, pressure pin 31, a control closing spring 36, which is supported in the axial direction on the one hand on the injector cover 32 and on the other from the unit consisting of control valve element 25 and anchor plate 29.

Wird die Elektromagnetanordnung 30 des elektromagnetischen Aktuators 27 bestromt, hebt das hülsenförmige Steuerventilelement 25 von seinem als Flachsitz ausgebildeten Steuerventilsitz 28 ab, wodurch die Ventilkammer 24, also der Hochdruckbereich 37 des Injektors 1, mit dem Niederdruckbereich 9 verbunden wird, wodurch der Druck innerhalb der hydraulisch über die Ablaufdrossel 23 mit der Ventilkammer 24 verbundenen Steuerkammer 20 rapide abfällt und sich das Einspritzventilelement 11 in axialer Richtung der Zeichnungsebene nach oben in die Steuerkammer hineinbewegt, wodurch in der Folge Kraftstoff aus dem Düsenraum 7 in den Brennraum strömen kann.When the electromagnet arrangement 30 of the electromagnetic actuator 27 is energized, the sleeve-shaped control valve element 25 lifts off from its control valve seat 28 designed as a flat seat, whereby the valve chamber 24, ie the high-pressure region 37 of the injector 1, is connected to the low-pressure region 9, whereby the pressure within the hydraulic via the outlet throttle 23 connected to the valve chamber 24 control chamber 20 drops rapidly and the injection valve element 11 moves in the axial direction of the drawing plane up into the control chamber, whereby fuel in the sequence can flow from the nozzle chamber 7 into the combustion chamber.

Zur Beendigung des Einspritzvorgangs wird die Bestromung der Elektromagnetanordnung 30 des elektromagnetischen Aktuators 27 unterbrochen. Die Steuerschließfeder 36 bewegt in der Folge das hülsenförmige Steuerventilelement 25 zurück auf seinen Steuerventilsitz 28 an der in der Zeichnungsebene oberen Seite des Ventilstücks 12. Durch den durch die Zulaufsdrossel 21 nachströmenden Kraftstoff steigt der Druck in der Steuerkammer 20 rapide an, wodurch das Einspritzventilelement 11, unterstützt durch die Federkraft einer Schließfeder 38, die sich an einem Umfangsbund 39 des Einspritzventilelementes 11 sowie am hülsenförmigen, unteren Abschnitt des Ventilstücks 12 abstützt, in Richtung des Einspritzventilelementsitzes 17 bewegt wird, wodurch wiederum der Kraftstofffluss aus der Düsenlochanordnung 18 in den Brennraum unterbrochen wird.To end the injection process, the energization of the solenoid assembly 30 of the electromagnetic actuator 27 is interrupted. The control closing spring 36 subsequently moves the sleeve-shaped control valve element 25 back onto its control valve seat 28 on the upper side of the valve piece 12 in the drawing plane. The fuel flowing in through the inlet throttle 21 rapidly increases the pressure in the control chamber 20, as a result of which the injection valve element 11, supported by the spring force of a closing spring 38, which is supported on a peripheral collar 39 of the injection valve element 11 and on the sleeve-shaped, lower portion of the valve piece 12, is moved in the direction of the injection valve element seat 17, which in turn the flow of fuel from the nozzle hole arrangement 18 into the combustion chamber is interrupted.

Wie erwähnt, befindet sich die zumindest näherungsweise linienförmige Dichtkante (Dichtlinie 34) auf dem inneren Führungsdurchmesser DiF. Anders ausgedrückt entspricht der (innere) Durchmesser DD der Dichtlinie 34 dem inneren Führungsdurchmesser DiF des Steuerventilelementes 25. In radialer Richtung wird die Dichtlinie 34 überragt von einem ringförmigen, von der Dichtlinie 34 ausgehenden, trapezförmigen Stützbereich 40, der vollständig innerhalb des Hochdruckbereichs 37, genauer innerhalb der Ventilkammer 24 angeordnet ist. Da die wirksame Druckangriffsfläche des Stützbereichs für Druckkräfte in eine erste Axialrichtung und die Druckangriffsfläche des Stützbereichs für Druckkräfte in eine zweite, der ersten Axialrichtung entgegengesetzte, Axialrichtung gleich groß sind, wird die axiale Druckausgeglichenheit des Steuerventilelementes 25 durch den ringförmigen, in Querschnitt trapezförmigen Stützbereich 40 nicht negativ beeinflusst. Wie aus Fig. 1 unschwer zu erkennen ist, befindet sich der Stützbereich 40 in axialer Richtung betrachtet zwischen der in der Zeichnungsebene unteren, freien Stirnseite des Druckstiftes 31 und dem als Flachsitz ausgebildeten Steuerventilsitz 28. Aufgrund des Vorsehens des Stützbereichs 40, bildet die Dichtlinie nicht die radial innerste Grenze des Steuerventilelementes 25.As mentioned, the at least approximately line-shaped sealing edge (sealing line 34) is located on the inner guide diameter D iF . In other words, the (inner) diameter D D of the sealing line 34 corresponds to the inner guide diameter D iF of the control valve element 25. In the radial direction, the sealing line 34 is surmounted by an annular, trapezoidal support region 40 extending from the sealing line 34, which is completely within the high-pressure region 37 , More specifically, is disposed within the valve chamber 24. Since the effective pressure application area of the pressure force support area in a first axial direction and the pressure application area of the pressure force support area are equal in a second axial direction opposite to the first axial direction, the axial pressure balance of the control valve element 25 will not be affected by the annular trapezoidal support area 40 negatively influenced. How out Fig. 1 It is not difficult to see that the support region 40 is located between the free end face of the pressure pin 31 and the control valve seat 28 formed as a flat seat, viewed in the axial direction. Due to the provision of the support region 40, the sealing line does not form the radially innermost boundary of Control Valve Element 25.

Vorteilhafte Winkelverhältnisse im Bereich der Dichtlinie 34 und im Bereich des Steuerventilsitzes 28 werden im Folgenden anhand der vergrößert dargestellten Ausführungsform gemäß Fig. 2 erläutert, wobei im Gegensatz zu dem Ausführungsbeispiel gemäß Fig. 1 anstelle eines als Flachsitz ausgebildeten Steuerventilsitzes 28 ein kegelförmiger, als Außenkonus ausgebildeter Steuerventilsitz 28 vorgesehen ist. Ansonsten entspricht das Ausführungsbeispiel gemäß Fig. 2 im Wesentlichen dem Ausführungsbeispiel gemäß Fig. 1, sodass zur Vermeidung von Wiederholungen in Bezug auf die Gemeinsamkeiten auf die vorhergehende Figurenbeschreibung sowie auf Fig. 1 verwiesen wird.Advantageous angular relationships in the region of the sealing line 34 and in the region of the control valve seat 28 will be described below with reference to the embodiment shown enlarged Fig. 2 explained, in contrast to the embodiment according to Fig. 1 instead of a formed as a flat seat control valve seat 28 a conical, as Outside cone trained control valve seat 28 is provided. Otherwise, the embodiment corresponds to Fig. 2 essentially in accordance with the exemplary embodiment Fig. 1 , so as to avoid repetition in relation to the similarities to the preceding description of the figures as well as on Fig. 1 is referenced.

In Fig. 2 ist das hülsenförmige Steuerventilelement 25 gezeigt, in das der Druckstift 31 hineinragt. Anstelle des gezeigten Ausführungsbeispiels, bei dem das Steuerventilelement 25 (zusätzlich) an seinem Außenumfang geführt ist, ist auch eine Ausführungsform des Injektors 1 realisierbar, bei der auf eine Außenführung für das hülsenförmige Steuerventilelement verzichtet wird.In Fig. 2 the sleeve-shaped control valve element 25 is shown, into which the pressure pin 31 protrudes. Instead of the embodiment shown, in which the control valve element 25 (additionally) is guided on its outer circumference, an embodiment of the injector 1 can be realized, is dispensed with in an external guide for the sleeve-shaped control valve element.

Aus Fig. 2 ist zu erkennen, dass das hülsenförmige Steuerventilelement 25 an seiner in der Zeichnungsebene unteren Stirnseite von einer Begrenzungslinie 41 begrenzt ist, die sich in dem gezeigten Ausführungsbeispiel ausgehend von der Dichtlinie 34 exakt in radialer Richtung nach außen erstreckt. Radial innen grenzt an die Dichtlinie 34 eine untere Begrenzungslinie 42 des Stützbereichs 40 an. Die beiden Begrenzungslinien 41, 42 schließen einen Steuerventilelementwinkel α ein. Dieser beträgt in dem gezeigten Ausführungsbeispiel etwa 140°. Der Steuerventilsitzwinkel β, also der Winkel zwischen zwei diametral gegenüberliegenden Flächenabschnitten des Steuerventilsitzes 28 beträgt in dem gezeigten Ausführungsbeispiel etwa 160°. Die Differenz zwischen den Winkeln α und β beträgt also 20°.Out Fig. 2 It can be seen that the sleeve-shaped control valve element 25 is delimited at its lower end face in the plane of the drawing by a delimiting line 41 which, in the exemplary embodiment shown, extends exactly in the radial direction outwards from the sealing line 34. Radially inside adjacent to the sealing line 34 at a lower boundary line 42 of the support portion 40 at. The two boundary lines 41, 42 include a control valve element angle α. This is about 140 ° in the embodiment shown. The control valve seat angle β, ie the angle between two diametrically opposite surface portions of the control valve seat 28 is in the illustrated embodiment about 160 °. The difference between the angles α and β is thus 20 °.

Ein Hochdruckfreilassungswinkel γ zwischen der (unteren) Begrenzungslinie 42 des Stützbereichs 40 und der konischen Steuerventilsitzfläche 43 im Hochdruckbereich 37 ist etwa 3° größer als der Niederdruckfreilassungswinkel δ zwischen der unteren Begrenzungslinie 41 des Steuerventilelementes 25 im Niederdruckbereich 9 und der Steuerventilsitzfläche 43. Die im Zusammenhang mit Fig. 2 beschriebenen Winkelverhältnisse gelten auch für das Ausführungsbeispiel gemäß Fig. 1., wobei lediglich der Steuerventilsitz 28 nicht als Kegelsitz, sondern als Flachsitz ausgebildet ist, wodurch in der Folge gegenüber dem Ausführungsbeispiel gemäß Fig. 1 die Begrenzungslinie 41 sich nicht exakt senkrecht zur Längsmittelachse des Steuerventilelementes 25 erstrecken kann.A high pressure release angle γ between the (lower) boundary line 42 of the support portion 40 and the conical control valve seat surface 43 in the high pressure region 37 is about 3 ° greater than the low pressure release angle δ between the lower boundary line 41 of the control valve element 25 in the low-pressure region 9 and the control valve seat surface 43. The in connection with Fig. 2 Angular ratios described also apply to the embodiment according to Fig. 1 ., Wherein only the control valve seat 28 is not formed as a conical seat, but as a flat seat, whereby in the sequence compared to the embodiment according to Fig. 1 the boundary line 41 can not extend exactly perpendicular to the longitudinal central axis of the control valve element 25.

Claims (8)

  1. Injector, in particular common-rail injector, for injecting fuel into a combustion chamber of an internal combustion engine, having an injection valve element (11) which is adjustable between a closed position and an open position and which can be actuated by means of a control valve (26), which control valve has a control valve element (25) which can be adjusted between a closed position and an open position by way of an actuator (27) and which is at least approximately pressure-balanced in the closed position and which has a sealing line (34) which, in the closed position of the control valve element (25), interacts sealingly with a control valve seat (28) and which, in the open position, is lifted from the control valve seat (28) and thus permits the flow of fuel from a high-pressure region (37) into a low-pressure region (9) of the injector (1), wherein the control valve element (25) has a support region (40) which projects beyond the sealing line (34) in the radial direction toward the high-pressure region (37) and which is in the form of a sleeve, wherein a high-pressure relief angle (γ) between a delimiting line (42) of the support region (40), which delimiting line faces toward the control valve seat (28) and, in the high-pressure region (37), adjoins the sealing line (34), and the control valve seat surface (43) is greater than a low-pressure relief angle (δ) between a delimiting line (41) of the control valve element (25), which delimiting line faces toward the control valve seat (28) and, in the low-pressure region (9), adjoins the sealing line (34), and the control valve seat surface (43), characterized in that the low-pressure relief angle (δ) is selected from an angle range between 0.5° in 5°, preferably between 0.5° and 2°.
  2. Injector according to Claim 1, characterized in that the support region (40) is designed and/or arranged such that no resultant axial pressure forces act thereon when the control valve (26) is closed.
  3. Injector according to either of Claims 1 and 2, characterized in that the diameter (Dd) of the sealing line (34) corresponds at least approximately, preferably exactly, to a guide diameter (DiF, DaF) of the control valve element (25).
  4. Injector according to Claim 1, characterized in that the high-pressure relief angle (γ) is selected from a value range between approximately 5° and approximately 60°, preferably between approximately 10° and approximately 50°, particularly preferably between approximately 20° and approximately 40°.
  5. Injector according to one of the preceding claims, characterized in that a difference between the control valve element angle (α), which is spanned between the delimiting lines (41, 42) which adjoin one another at the sealing line (34), and the control valve seat angle (β) is greater than 10 ° , preferably greater than 20°, particularly preferably greater than 30°.
  6. Injector according to one of the preceding claims, characterized in that the support region (40) is of at least approximately trapezoidal form in cross section.
  7. Injector according to Claim 1, characterized in that a single-part or multi-part pressure pin (31), which is separate from the valve piece (12) which has the control valve seat (28), is accommodated in the sleeve, and in that the support region (40) is arranged on the inner circumference of the sleeve axially between the pressure pin (31) and the control valve seat (28).
  8. Injector according to one of the preceding claims, characterized in that the control valve seat (28) is in the form of a flat seat or in the form of a conical seat.
EP08871236.9A 2008-01-22 2008-12-30 Fuel injector the control valve element of which comprises a support region Active EP2235354B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008005532A DE102008005532A1 (en) 2008-01-22 2008-01-22 Fuel injector whose control valve element has a support region
PCT/EP2008/068341 WO2009092507A1 (en) 2008-01-22 2008-12-30 Fuel injector the control valve element of which comprises a support region

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EP2235354A1 EP2235354A1 (en) 2010-10-06
EP2235354B1 true EP2235354B1 (en) 2015-07-08

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US (1) US8671912B2 (en)
EP (1) EP2235354B1 (en)
JP (1) JP5264934B2 (en)
CN (1) CN101925733B (en)
DE (1) DE102008005532A1 (en)
RU (1) RU2505701C9 (en)
WO (1) WO2009092507A1 (en)

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JP5264934B2 (en) 2013-08-14
WO2009092507A1 (en) 2009-07-30
RU2010134798A (en) 2012-02-27
CN101925733A (en) 2010-12-22
RU2505701C9 (en) 2014-05-27
EP2235354A1 (en) 2010-10-06
JP2011510221A (en) 2011-03-31
RU2505701C2 (en) 2014-01-27
US20100294241A1 (en) 2010-11-25
US8671912B2 (en) 2014-03-18
DE102008005532A1 (en) 2009-07-23
CN101925733B (en) 2014-07-02

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