EP2275666A1 - Fuel injector with pressure-equalised control valve - Google Patents

Fuel injector with pressure-equalised control valve Download PDF

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Publication number
EP2275666A1
EP2275666A1 EP10162230A EP10162230A EP2275666A1 EP 2275666 A1 EP2275666 A1 EP 2275666A1 EP 10162230 A EP10162230 A EP 10162230A EP 10162230 A EP10162230 A EP 10162230A EP 2275666 A1 EP2275666 A1 EP 2275666A1
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EP
European Patent Office
Prior art keywords
control valve
valve element
chamber
fuel injector
hydraulic connection
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
EP10162230A
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German (de)
French (fr)
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EP2275666B1 (en
Inventor
Andreas Rau
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 EP2275666A1 publication Critical patent/EP2275666A1/en
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Publication of EP2275666B1 publication Critical patent/EP2275666B1/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
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0026—Valves characterised by the valve actuating means electrical, e.g. using solenoid using piezoelectric or magnetostrictive actuators
    • 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
    • F02M63/0033—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat
    • F02M63/0035—Poppet valves, i.e. having a mushroom-shaped valve member that moves perpendicularly to the plane of the valve seat
    • 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
    • F02M63/0045—Three-way valves

Definitions

  • the invention relates to a fuel 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 fuel injector which has a control valve (servo valve).
  • the control valve is designed as a so-called 3/2-way valve and controls the connection between a directly from an injection valve element control space and a low pressure area (leakage oil space) of the fuel injector.
  • the control valve has a control valve element, which can be adjusted axially by means of an actuator, for example an electromagnetic or piezoelectric actuator, within a control valve chamber and thus cooperates with a first control valve seat and with a second control valve seat. If the control valve element is in contact with the first (upper) control valve seat, the connection between the control space bounded by the injection valve element and the low-pressure region of the fuel injector is blocked.
  • a bypass throttle is opened, via which the control chamber is refilled.
  • the bypass throttle is closed and the hydraulic connection between the control chamber and the low pressure region of the fuel injector is established, as a result of which the pressure in the control valve chamber drops, which in turn causes the injection valve element to move from its position Injector valve seat lifts and thus releases the flow of fuel through a nozzle hole arrangement in the combustion chamber of the internal combustion engine.
  • a disadvantage of the axially not pressure balanced control valve is that the load of the actuator with increasing rail pressure continues to increase. As a result, given a known actuator with the known principle, there is no potential for a further system pressure increase.
  • the control valve member of the control valve is disposed in a control valve space which is bounded radially outwardly by a single plate member, to the axially below a throttle plate and axially above an actuator space limited component abuts.
  • the new injector seems to be optimized in terms of shortened remindbehellles the control room.
  • the invention has for its object to provide a fuel injector, on the one hand has sufficient potential for system pressure increases and in the other hand, a minimized stuntbehellzeit is realized for refilling the control chamber.
  • the invention is based on the idea, a second, in particular lower control valve seat on which the control valve element of the control valve (servo valve) sealingly abuts in the second switching position to the immediate hydraulic Interrupt connection between the high-pressure region of the fuel injector and the control valve chamber on a guide sleeve for the control valve, which leads, preferably not sleeve-shaped, in particular bolt-shaped, control valve element on its outer circumference.
  • the control valve element bears directly against the guide sleeve in a sealing manner.
  • the fuel injector preferably designed as a throttle connection hydraulic connection between the high-pressure region of the fuel injector and the control valve chamber by the second, preferably lower, control valve seat can be separated.
  • the minimized control valve volume results in a significantly lower characteristic slope, which makes it possible to use nozzles that rapidly decompress, whereby the engine output can be increased without impairing the fuel injector's small-capacity capability.
  • the fuel injector according to the invention has particularly good hydraulic properties by the simultaneous presence of a bypass (hydraulic connection between the high-pressure region and the control valve chamber) and a minimum control valve chamber volume, which in combination to an extreme quick refilling the control valve chamber and thus the control chamber and thus in turn leads to a very quick reversal of the injection valve element with said flat map.
  • the refilling time which is required to refill the control chamber, can be reduced in the invention by a minimum, in which instead of a helical compression spring, a plate spring is used as a valve spring for the control valve.
  • the plate spring is arranged such that the control valve element in the direction of the first switching position, i. Federkraftbeaufschlagt in the direction of the first control valve seat, so that the control valve member against the spring force of the spring plate must be moved from the first switching position to the second switching position. Due to the design of the spring as a plate spring, the control valve volume can be reduced to a minimum, resulting in the first switching position of the control valve, an accelerated pressure increase in the control valve chamber and thus also in the control room.
  • the hydraulic connection between the high-pressure region, for example, a pressure chamber surrounding the control chamber radially outside and the control valve chamber is designed as a throttle connection.
  • a throttle bore is integrated, which is particularly preferably, as will be explained later, is arranged in a throttle plate, which bears axially against the guide sleeve for the control valve element.
  • the spring in particular the plate spring, against the spring force
  • the control valve element must be adjusted on its way from the first switching position to the second switching position one end axially on the control valve element, in particular on a peripheral collar of the control valve element and the other end is supported on the guide sleeve for the control valve element.
  • P refers the spring is arranged such that it is not completely flattened even in the second switching position of the control valve.
  • the hydraulic connection comprises a gap, which is bounded radially outwardly directly from the guide sleeve and radially inwardly directly from the control valve member.
  • the space formed as an annular space is preferably contoured and arranged such that resulting from the fuel under high pressure in the space no resulting axial forces on the control valve element.
  • the aforementioned gap is at least one introduced into the guide sleeve sleeve bore hydraulically permanently connected to an annular space which is bounded radially inwardly of the guide sleeve and preferably radially outwardly from the inner periphery of an end-side recess in a throttle plate is limited.
  • annular space arranged radially outside the guide sleeve is connected via a channel in a throttle plate on which the guide sleeve rests in the axial direction to the high-pressure region, preferably to a pressure chamber surrounding the control chamber radially on the outside.
  • this channel is designed as a throttle bore.
  • control valve element on the outer circumference leading guide sleeve, in particular on a, in particular piezoelectric actuator facing Side has a biting edge for sealing cooperation with the control valve element in the second switching position.
  • the fuel can be actuated with an electromagnetic actuator.
  • an embodiment variant with a piezoelectric actuator is particularly preferred, wherein a coupler is preferably provided between the piezoelectric actuator and the control valve element, with which a force path transmission can be realized and compensated for with the expansion effects due to heat.
  • the hydraulic connection between the control chamber and the control valve chamber so the hydraulic connection through which in the second switching position of the control valve fuel from the limited by the injection valve element control chamber can flow into the low pressure region, at least two, Having in different injector components extending sections.
  • a section extends in a previously explained throttle plate and another section in a control valve space radially outwardly bounding plate.
  • Fig. 1 is a designed as a common rail injector fuel injector 1 for injecting fuel in a combustion chamber, not shown, of a likewise not shown internal combustion engine of a motor vehicle in a schematic Illustration shown.
  • 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, stored in this embodiment about 2000 bar.
  • the fuel injector is connected via other, not shown, injectors via a supply line 5.
  • the supply line 5 opens into a supply channel 6 within the fuel injector 1, which in turn opens into a pressure chamber 7, which, like the supply channel 6, belongs to the high-pressure region 8 of the fuel injector 1.
  • the fuel injector 1, more precisely a low-pressure region 10 of the fuel injector 1, is connected to a return line 11 via an injector return port (not shown). Via the return line 11, a control quantity of fuel, which will be explained later, can flow into the fuel injector 1 to the storage container 3 and be fed back from there to the high-pressure circuit.
  • a one-piece injection valve element 12 designed as a nozzle needle is arranged axially adjustable. This can also be made in several parts instead of the one-piece training and, for example, consist of a control rod and a coupled with this nozzle needle.
  • the preferred one-piece injection valve element 12 protrudes in the drawing plane down to an injection valve element seat 13, with which it cooperates in a sealing manner in a conventional manner.
  • the injection valve member 12 abuts its injection valve member seat 13, i. is in a closed position, the fuel outlet from a plurality of injection openings comprehensive nozzle hole assembly 14 is locked. If, on the other hand, it is lifted from its injection valve element seat 13, fuel can be injected from the pressure chamber 7 into a region below the injection valve element 12 and from there through the nozzle hole arrangement 14, substantially under high pressure (rail pressure) into the combustion chamber.
  • a control chamber 17th limited which is supplied via a in a throttle plate 18, on which the sleeve 16 is supported in the axial direction, introduced inlet throttle 19 with high-pressure fuel from the high-pressure region 8, here the supply channel 6.
  • the inlet throttle 19 may also be provided as a radial bore in the sleeve 16.
  • the sleeve 16 with the control chamber 17 enclosed therein is enclosed radially on the outside by fuel under high pressure, so that an annular guide gap between the sleeve 16 and the injection valve element 12 is comparatively fuel-tight.
  • the sleeve 16 is supported in the axial direction from below on the aforementioned throttle plate 18, in which in addition to the inlet throttle 19, a flow restrictor 20 exhibiting flow channel 21 is introduced.
  • the drainage channel 21 as well as an aligned in the flow direction with this channel 22, which is introduced in an axially adjacent to the throttle plate 18 plates 23 to a hydraulic connection between the control chamber 17 and a radially outwardly of the plate 23 limited control valve chamber 24.
  • the control valve chamber 24 is inserted in a lower portion of a stepped bore 25 in the plate 23.
  • Axially adjustable within the control valve chamber 24 is a bolt-shaped control valve element 26 of a control valve 27 which is connected by means of a piezoelectric actuator 29 via a hydraulic coupler 29 between an upper first switching position, i. between an upper first control valve seat 30 and a lower, i. second switching position, ie a second control valve seat 31 is adjustable.
  • the control valve 27 is a 3/2-way valve.
  • the hydraulic connection between the high pressure region 8 and the control valve chamber 24 includes a throttle bore 35 in the throttle plate 18, wherein the throttle bore 35 hydraulically connects the pressure chamber 7 with an annular space 36, wherein the annular space 36 radially outward from the inner periphery of a frontal bore in the throttle plate 18 and is bounded radially inwardly from the outer periphery of the guide sleeve 32 for the control valve element 26.
  • the annular space 36 is connected via a sleeve bore 37 in permanent hydraulic connection with a gap 38, which is bounded radially outwardly from the inner circumference of a central bore in the guide sleeve 32 and radially inwardly from the outer periphery of the control valve element 26.
  • the intermediate space 38 is separated from the control valve chamber 24 via a bite edge 39 formed on the guide sleeve 32, which sealingly cooperates with the underside of a peripheral collar 40 of the control valve element 26.
  • the biting edge 39 is located on the front side of an axial,
  • the extension 41 creates axial space for accommodating a plate spring 42 (control valve spring), against the spring force, the control valve member 26 must be moved in energizing the piezoelectric actuator 28 in the drawing plane down to the second switching position.
  • a plate spring 42 as a control valve spring, the volume of the control valve chamber 24 can be minimized as shown.
  • the plate spring 42 is supported in the axial direction on an upper end side of the guide sleeve 32 and in the other axial direction from below on the peripheral collar 40 of the control valve element 26.
  • the control valve element 26 is an at least approximately pressure-balanced control valve element 26 in the axial direction; this means that when the control valve element 26 is in the upper (first) switching position, no (or possibly only small) resulting hydraulic forces act in the axial direction. This is achieved in that the control valve element 26 is acted upon at a lower end face 43 with low pressure.
  • the lower end face 43 bounded in the axial direction upwards a compensation chamber 44, which belongs to the low pressure region 10 of the fuel injector 1 and is hydraulically connected via a low pressure passage 45 to the injector return port.
  • the compensation chamber 44 is bounded radially on the outside by the guide sleeve 32, which limits the control valve chamber 24 in the axial direction downwards.
  • the guide sleeve 32 is received over a majority of its axial extent in a frontal bore in the throttle plate 18 and is sealingly connected to an upper portion of its outer periphery to a lower portion of the inner periphery of the stepped bore 25, so that the annular space 36 is sealed relative to the control valve chamber 24.

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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)

Abstract

The injector (1) has a control valve element (26) adjustable between two switching positions. The valve element is formed and arranged such that no or reduced resulting hydraulic force is exerted in an axial direction on the valve element by pressure in a control chamber (17) when a hydraulic connection between the chamber and a low pressure region (10) is disconnected in one of the switching positions. The valve element sealingly lies at a guiding sleeve (32) in the other switching position for sealing a hydraulic connection between a control valve chamber (24) and a high pressure region (8).

Description

Stand der TechnikState of the art

Die Erfindung betrifft einen Kraftstoff-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 a fuel 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 DE 10 2004 030 445 A1 ist ein Kraftstoff-Injektor bekannt, der ein Steuerventil (Servoventil) aufweist. Das Steuerventil ist als sogenanntes 3/2-Wegeventil ausgeführt und steuert die Verbindung zwischen einem von einem Einspritzventilelement unmittelbar begrenzten Steuerraum und einem Niederdruckbereich (Leckölraum) des Kraftstoff-Injektors. Das Steuerventil weist ein Steuerventilelement auf, das mittels eines Aktuators, beispielsweise eines elektromagnetischen oder piezoelektrischen Aktuators, innerhalb eines Steuerventilraums axial verstellt werden kann und somit mit einem ersten Steuerventilsitz und mit einem zweiten Steuerventilsitz zusammenwirkt. Befindet sich das Steuerventilelement in der Anlage am ersten (oberen) Steuerventilsitz, so ist die Verbindung zwischen dem von dem Einspritzventilelement begrenzten Steuerraum und dem Niederdruckbereich des Kraftstoff-Injektors gesperrt. Gleichzeitig ist eine Bypass-Drossel geöffnet, über die der Steuerraum rückbefüllt wird. Liegt das Steuerventilelement am zweiten (unteren) Steuerventilsitz an, ist die Bypass-Drossel geschlossen und die hydraulische Verbindung zwischen dem Steuerraum und dem Niederdruckbereich des Kraftstoff-Injektors hergestellt, wodurch der Druck im Steuerventilraum abfällt, was wiederum dazu führt, dass das Einspritzventilelement von seinem Einspritzventilelementsitz abhebt und so den Kraftstofffluss durch eine Düsenlochanordnung in den Brennraum der Brennkraftmaschine freigibt. Nachteilig bei dem axial nicht druckausgeglichenen Steuerventil ist, dass die Belastung des Aktuators bei steigendem Rail-Druck immer weiter zunimmt. Dies führt dazu, dass bei gegebenem Aktuator mit dem bekannten Prinzip kein Potential für eine weitere Systemdrucksteigerung vorhanden ist.From the DE 10 2004 030 445 A1 a fuel injector is known which has a control valve (servo valve). The control valve is designed as a so-called 3/2-way valve and controls the connection between a directly from an injection valve element control space and a low pressure area (leakage oil space) of the fuel injector. The control valve has a control valve element, which can be adjusted axially by means of an actuator, for example an electromagnetic or piezoelectric actuator, within a control valve chamber and thus cooperates with a first control valve seat and with a second control valve seat. If the control valve element is in contact with the first (upper) control valve seat, the connection between the control space bounded by the injection valve element and the low-pressure region of the fuel injector is blocked. At the same time, a bypass throttle is opened, via which the control chamber is refilled. When the control valve element is in contact with the second (lower) control valve seat, the bypass throttle is closed and the hydraulic connection between the control chamber and the low pressure region of the fuel injector is established, as a result of which the pressure in the control valve chamber drops, which in turn causes the injection valve element to move from its position Injector valve seat lifts and thus releases the flow of fuel through a nozzle hole arrangement in the combustion chamber of the internal combustion engine. A disadvantage of the axially not pressure balanced control valve is that the load of the actuator with increasing rail pressure continues to increase. As a result, given a known actuator with the known principle, there is no potential for a further system pressure increase.

Aus der zum Anmeldezeitpunkt vorliegenden Anmeldung noch nicht offengelegten DE 10 2008 001 330 der Anmelderin ist ein alternatives Injektorkonzept mit einem druckausgeglichenem Steuerventil (Servoventil) bekannt. Dieses neue Servoprinzip schaltet prinzipbedingt nicht gegen Rail-Druck, sondern es ist konstruktiv eine Niederdruckanbindung unter das Steuerventilelement geführt. Dies führt dazu, dass die Öffnungskraft des Steuerventils, je nach Grad des Druckausgleichs, geringer und weniger stark vom Rail-Druck abhängig ist. Damit bietet das neue Injektorkonzept, ohne die Aktuatorbelastung unzulässig zu erhöhen, das Potential einer weiteren Systemdruckanhebung. Das Steuerventilelement des Steuerventils ist in einem Steuerventilraum angeordnet, der radial außen von einem einzigen Plattenbauteil begrenzt ist, an das axial unten eine Drosselplatte und axial oben ein einen Aktuatorraum begrenztes Bauteil angrenzt. Der neue Injektor scheint hinsichtlich einer verkürzten Rückbefüllbarkeit des Steuerraums optimierbar.From the present application at the time of filing not yet disclosed DE 10 2008 001 330 The applicant is aware of an alternative injector concept with a pressure compensated control valve (servo valve). As a matter of principle, this new servo principle does not switch against rail pressure, but it is structurally guided by a low-pressure connection under the control valve element. This means that the opening force of the control valve, depending on the degree of pressure compensation, less and less dependent on the rail pressure. Thus, the new injector concept offers the potential of a further system pressure increase without unduly increasing the actuator load. The control valve member of the control valve is disposed in a control valve space which is bounded radially outwardly by a single plate member, to the axially below a throttle plate and axially above an actuator space limited component abuts. The new injector seems to be optimized in terms of shortened Rückbefüllbarkeit the control room.

Offenbarung der ErfindungDisclosure of the invention

Der Erfindung liegt die Aufgabe zugrunde einen Kraftstoff-Injektor anzugeben, der einerseits ausreichend Potential für Systemdrucksteigerungen aufweist und bei dem andererseits eine minimierte Rückbefüllzeit zum Rückbefüllen des Steuerraums realisiert ist.The invention has for its object to provide a fuel injector, on the one hand has sufficient potential for system pressure increases and in the other hand, a minimized Rückbefüllzeit is realized for refilling the control chamber.

Diese Aufgabe wird mit einem Kraftstoff-Injektor mit den Merkmalen des Anspruchs 1 gelöst. Vorteilhafte Weiterbildungen der Erfindung sind in den Unteransprüchen angegeben. In den Rahmen der Erfindung fallen sämtliche Kombinationen aus zumindest zwei von in der Beschreibung, den Ansprüchen und/oder den Figuren offenbarten Merkmalen.This object is achieved with a fuel 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 fall within the scope of the invention.

Der Erfindung liegt der Gedanke zugrunde, einen zweiten, insbesondere unteren Steuerventilsitz, an dem das Steuerventilelement des Steuerventils (Servoventils) in der zweiten Schaltstellung dichtend anliegt, um die unmittelbare hydraulische Verbindung zwischen dem Hochdruckbereich des Kraftstoff-Injektors und dem Steuerventilraum zu unterbrechen an einer Führungshülse für das Steuerventil auszubilden, die das, vorzugsweise nicht hülsenförmige, insbesondere bolzenförmige, Steuerventilelement an seinem Außenumfang führt. Anders ausgedrückt liegt das Steuerventilelement in der zweiten Schaltstellung des vorzugsweise aus 3/2-Wegeventil ausgebildeten Steuerventils unmittelbar dichtend an der Führungshülse an. Auf diese Weise wird in der ersten Schaltstellung, in der das Steuerventilelement nicht dichtend an der Führungshülse anliegt, eine große Querschnittsfläche freigegeben, durch die der Steuerventilraum und damit vorzugsweise über eine Ablaufdrossel, der Steuerraum rückbefüllt werden kann. Hieraus resultiert wiederum ein deutlich schnelleres Schließen des ein- oder mehrteiligen Einspritzventilelementes mit einer wiederum daraus resultierenden größeren Robustheit des Kraftstoff-Injektors. Aufgrund der Verschließbarkeit der hydraulischen Verbindung zwischen dem Hochdruckbereich des Kraftstoff-Injektors, vorzugsweise zwischen einem Druckraum des Kraftstoff-Injektors und dem Steuerventilelement, kann zudem während der Einspritzung eine deutlich geringere Steuermenge als bei üblichen druckausgeglichenen Kraftstoff-Injektoren mit permanent wirkender Fülldrossel realisiert werden, da bei einem nach dem Konzept der Erfindung ausgebildeten Kraftstoff-Injektor die vorzugsweise als Drosselverbindung ausgebildete hydraulische Verbindung zwischen dem Hochdruckbereich des Kraftstoff-Injektors und dem Steuerventilraum durch den zweiten, vorzugsweise unteren, Steuerventilsitz getrennt werden kann. Dieser Vorteil ist deshalb so bedeutend, da bei druckausgeglichenen Kraftstoff-Injektoren aufgrund der vorhandenen Permanentleckagestellen sowieso sehr große und damit teuere Hochdruckpumpen benötigt werden und aufgrund der Erfindung die Möglichkeit geschaffen wird, kleinere und damit günstigere Hochdruckpumpen einzusetzen, wodurch die Systemkosten insgesamt reduziert werden. Durch das minimierte Steuerventilraumvolumen ergibt sich zudem eine deutlich geringere Kennfeldsteilheit, welche es ermöglicht, schnell entdrosselnde Düsen einzusetzen, wodurch die Motorleistung erhöht werden kann, ohne die Kleinstmengenfähigkeit des Kraftstoff-Injektors zu verschlechtern. Der erfindungsgemäße Kraftstoff-Injektor hat besonders gute hydraulische Eigenschaften durch das gleichzeitige Vorhandensein eines Bypasses (hydraulische Verbindung zwischen dem Hochdruckbereich und dem Steuerventilraum) und eines minimalen Steuerventilraumvolumens, was in der Kombination zu einem extrem schnellen Wiederbefüllen des Steuerventilraums und damit des Steuerraums und damit wiederum zu einem sehr schnellen Umkehren des Einspritzventilelementes mit besagtem flachem Kennfeld führt.The invention is based on the idea, a second, in particular lower control valve seat on which the control valve element of the control valve (servo valve) sealingly abuts in the second switching position to the immediate hydraulic Interrupt connection between the high-pressure region of the fuel injector and the control valve chamber on a guide sleeve for the control valve, which leads, preferably not sleeve-shaped, in particular bolt-shaped, control valve element on its outer circumference. In other words, in the second switching position of the control valve, which is preferably formed of a 3/2-way valve, the control valve element bears directly against the guide sleeve in a sealing manner. In this way, a large cross-sectional area is released in the first switching position in which the control valve element is not sealingly against the guide sleeve, through which the control valve space and thus preferably via an outlet throttle, the control chamber can be refilled. This in turn results in a much faster closing of the one- or multi-part injection valve element with a turn resulting greater robustness of the fuel injector. Due to the closeability of the hydraulic connection between the high-pressure region of the fuel injector, preferably between a pressure chamber of the fuel injector and the control valve element, also during the injection a significantly lower control amount than in conventional pressure-balanced fuel injectors can be realized with permanently acting Fülldrossel in a designed according to the concept of the invention, the fuel injector preferably designed as a throttle connection hydraulic connection between the high-pressure region of the fuel injector and the control valve chamber by the second, preferably lower, control valve seat can be separated. This advantage is so important because with pressure balanced fuel injectors due to the existing permanent leakage anyway very large and therefore expensive high-pressure pumps are needed and due to the invention, the possibility is created to use smaller and thus cheaper high-pressure pumps, whereby the system costs are reduced overall. In addition, the minimized control valve volume results in a significantly lower characteristic slope, which makes it possible to use nozzles that rapidly decompress, whereby the engine output can be increased without impairing the fuel injector's small-capacity capability. The fuel injector according to the invention has particularly good hydraulic properties by the simultaneous presence of a bypass (hydraulic connection between the high-pressure region and the control valve chamber) and a minimum control valve chamber volume, which in combination to an extreme quick refilling the control valve chamber and thus the control chamber and thus in turn leads to a very quick reversal of the injection valve element with said flat map.

Die Rückbefüllzeit, die benötigt wird, um den Steuerraum rückzubefüllen, kann in Weiterbildung der Erfindung dadurch auf ein Minimum reduziert werden, in dem anstelle einer Schraubendruckfeder eine Tellerfeder als Ventilfeder für das Steuerventil eingesetzt wird. Bevorzugt ist die Tellerfeder dabei derart angeordnet, dass das Steuerventilelement in Richtung erster Schaltstellung, d.h. in Richtung erstem Steuerventilsitz federkraftbeaufschlagt wird, so dass das Steuerventilelement entgegen der Federkraft der Federteller von der ersten Schaltstellung in die zweite Schaltstellung bewegt werden muss. Durch die Ausbildung der Feder als Tellerfeder kann das Steuerventilraumvolumen auf ein Minimum reduziert werden, woraus in der ersten Schaltstellung des Steuerventils ein beschleunigter Druckanstieg im Steuerventilraum und damit auch im Steuerraum resultiert. Die Kombination der Ausbildung des zweiten Steuerventilsitzes an der Führungshülse für das Steuerventilelement mit der Ausbildung der Steuerventilfeder als Tellerfeder bringt minimale Rückbefüllzeiten mit sich, was in einem extrem schnellen Umkehren, d.h. Schließen des Einspritzventilelementes resultiert.The refilling time, which is required to refill the control chamber, can be reduced in the invention by a minimum, in which instead of a helical compression spring, a plate spring is used as a valve spring for the control valve. Preferably, the plate spring is arranged such that the control valve element in the direction of the first switching position, i. Federkraftbeaufschlagt in the direction of the first control valve seat, so that the control valve member against the spring force of the spring plate must be moved from the first switching position to the second switching position. Due to the design of the spring as a plate spring, the control valve volume can be reduced to a minimum, resulting in the first switching position of the control valve, an accelerated pressure increase in the control valve chamber and thus also in the control room. The combination of the formation of the second control valve seat on the guide sleeve for the control valve member with the design of the control valve spring as a Belleville spring brings minimal Rückbefüllzeiten, resulting in an extremely fast reversal, i. Closing the injection valve element results.

Besonders zweckmäßig ist eine Ausführungsvariante des Kraftstoff-Injektors, bei der die hydraulische Verbindung zwischen dem Hochdruckbereich, beispielsweise einem den Steuerraum radial außen umgebenden Druckraum und dem Steuerventilraum als Drosselverbindung ausgebildet ist. Dies kann auf einfache Weise dadurch realisiert werden, dass in der hydraulischen Verbindung eine Drosselbohrung integriert ist, die besonders bevorzugt, wie später noch erläutert werden wird, in einer Drosselplatte angeordnet ist, an die axial die Führungshülse für das Steuerventilelement anliegt.Particularly useful is an alternative embodiment of the fuel injector, wherein the hydraulic connection between the high-pressure region, for example, a pressure chamber surrounding the control chamber radially outside and the control valve chamber is designed as a throttle connection. This can be realized in a simple manner in that in the hydraulic connection, a throttle bore is integrated, which is particularly preferably, as will be explained later, is arranged in a throttle plate, which bears axially against the guide sleeve for the control valve element.

Besonders zweckmäßig im Hinblick auf eine Minimierung des Steuerventilraumvolumens ist es, die Feder, insbesondere die Tellerfeder, entgegen deren Federkraft das Steuerventilelement auf seinem Weg von der ersten Schaltstellung zur zweiten Schaltstellung verstellt werden muss sich einenends axial am Steuerventilelement, insbesondere an einem Umfangsbund des Steuerventilelementes und anderenends an der Führungshülse für das Steuerventilelement abstützt. Bevorzugt ist die Feder derart angeordnet, dass sie auch in der zweiten Schaltstellung des Steuerventils nicht vollständig plattgedrückt ist.Particularly expedient with a view to minimizing the control valve volume, it is the spring, in particular the plate spring, against the spring force, the control valve element must be adjusted on its way from the first switching position to the second switching position one end axially on the control valve element, in particular on a peripheral collar of the control valve element and the other end is supported on the guide sleeve for the control valve element. Prefers the spring is arranged such that it is not completely flattened even in the second switching position of the control valve.

Im Hinblick auf die konkrete Ausbildung der hydraulischen Verbindung zwischen dem Hochdruckbereich des Kraftstoff-Injektors und dem Steuerventilraum gibt es unterschiedliche Möglichkeiten. Ganz besonders bevorzugt ist eine Ausführungsvariante, bei der die hydraulische Verbindung einen Zwischenraum umfasst, der radial außen unmittelbar von der Führungshülse und radial innen unmittelbar von dem Steuerventilelement begrenzt ist. Dabei ist der als Ringraum ausgebildete Zwischenraum bevorzugt derart konturiert und angeordnet, dass aus dem unter Hochdruck stehenden Kraftstoff im Zwischenraum keine resultierenden Axialkräfte auf das Steuerventilelement resultieren.With regard to the specific design of the hydraulic connection between the high-pressure region of the fuel injector and the control valve chamber, there are different possibilities. Very particularly preferred is a variant in which the hydraulic connection comprises a gap, which is bounded radially outwardly directly from the guide sleeve and radially inwardly directly from the control valve member. In this case, the space formed as an annular space is preferably contoured and arranged such that resulting from the fuel under high pressure in the space no resulting axial forces on the control valve element.

In Weiterbildung der Erfindung ist mit Vorteil vorgesehen, dass der vorgenannte Zwischenraum über mindestens eine in die Führungshülse eingebrachte Hülsenbohrung hydraulisch dauerhaft mit einem Ringraum verbunden ist, welcher radial innen von der Führungshülse begrenzt ist und der vorzugsweise radial außen vom Innenumfang einer stirnseitigen Ausnehmung in einer Drosselplatte begrenzt ist. Durch die Anordnung eines mit unter Hochdruck stehendem Kraftstoff gefüllten Ringraums radial außerhalb der Führungshülse können vergleichsweise kraftstoffdichte Führungsspalte zwischen dem Steuerventilelement und der Führungshülse sichergestellt werden, wodurch Leckageverluste aus dem zuvor erläuterten Zwischenraum in einen radial außen von der Führungshülse und in axialer Richtung von dem Steuerventilelement begrenzten, auf Niederdruck liegenden Raum minimiert werden.In a further development of the invention is advantageously provided that the aforementioned gap is at least one introduced into the guide sleeve sleeve bore hydraulically permanently connected to an annular space which is bounded radially inwardly of the guide sleeve and preferably radially outwardly from the inner periphery of an end-side recess in a throttle plate is limited. By arranging an annular space filled with high-pressure fuel radially outside the guide sleeve, comparatively fuel-tight guide gaps can be ensured between the control valve element and the guide sleeve, whereby leakage losses from the above-described intermediate space are limited in a radially outward direction by the guide sleeve and in the axial direction by the control valve element minimized to low pressure.

Ganz besonders bevorzugt ist es, wenn der radial außerhalb der Führungshülse angeordnete Ringraum über einen Kanal in einer Drosselplatte, auf der die Führungshülse in axialer Richtung aufliegt mit dem Hochdruckbereich, vorzugsweise einem den Steuerraum radial außen umgebenden Druckraum verbunden ist. Besonders bevorzugt ist dieser Kanal als Drosselbohrung ausgeführt.It is particularly preferred if the annular space arranged radially outside the guide sleeve is connected via a channel in a throttle plate on which the guide sleeve rests in the axial direction to the high-pressure region, preferably to a pressure chamber surrounding the control chamber radially on the outside. Particularly preferably, this channel is designed as a throttle bore.

Besonders zweckmäßig ist eine Ausführungsform des Kraftstoff-Injektors, bei der die das Steuerventilelement am Außenumfang führende Führungshülse, insbesondere an einer dem, insbesondere piezoelektrischen Aktuator zugewandten Seite eine Beißkante zum dichtenden Zusammenwirken mit dem Steuerventilelement in der zweiten Schaltstellung aufweist. Durch das Vorsehen einer Beißkante kann eine gute Kraftstoffdichtheit sichergestellt werden, wodurch ein Kraftstoffaustritt über die hydraulische Verbindung in den Steuerventilraum in der zweiten Schaltstellung des Steuerventils unterbunden wird.Particularly useful is an embodiment of the fuel injector, in which the control valve element on the outer circumference leading guide sleeve, in particular on a, in particular piezoelectric actuator facing Side has a biting edge for sealing cooperation with the control valve element in the second switching position. By providing a biting edge a good fuel-tightness can be ensured, whereby a fuel outlet is prevented via the hydraulic connection in the control valve chamber in the second switching position of the control valve.

Grundsätzlich kann der Kraftstoff mit einem elektromagnetischen Aktuator betätigt werden. Besonders bevorzugt ist jedoch eine Ausführungsvariante mit piezoelektrischem Aktuator, wobei bevorzugt zwischen dem piezoelektrischen Aktuator und dem Steuerventilelement ein Koppler vorgesehen ist, mit dem zum einen eine Kraftwegübersetzung realisierbar ist und mit dem zum anderen wärmebedingte Ausdehnungseffekte ausgeglichen werden können.In principle, the fuel can be actuated with an electromagnetic actuator. However, an embodiment variant with a piezoelectric actuator is particularly preferred, wherein a coupler is preferably provided between the piezoelectric actuator and the control valve element, with which a force path transmission can be realized and compensated for with the expansion effects due to heat.

In Weiterbildung der Erfindung ist mit Vorteil vorgesehen, dass die hydraulische Verbindung zwischen dem Steuerraum und dem Steuerventilraum, also die hydraulische Verbindung, durch die in der zweiten Schaltstellung des Steuerventils Kraftstoff aus dem von dem Einspritzventilelement begrenzten Steuerraum in den Niederdruckbereich strömen kann, mindestens zwei, in unterschiedlichen Injektorbauteilen verlaufende Abschnitte aufweist. Ganz besonders bevorzugt verläuft ein Abschnitt in einer zuvor bereits erläuterten Drosselplatte und ein weiterer Abschnitt in einer den Steuerventilraum radial außen begrenzenden Platte.In a further development of the invention is advantageously provided that the hydraulic connection between the control chamber and the control valve chamber, so the hydraulic connection through which in the second switching position of the control valve fuel from the limited by the injection valve element control chamber can flow into the low pressure region, at least two, Having in different injector components extending sections. Most preferably, a section extends in a previously explained throttle plate and another section in a control valve space radially outwardly bounding plate.

Weitere Vorteile, Merkmale und Einzelheiten der Erfindung ergeben sich aus der nachfolgenden Beschreibung eines bevorzugten Ausführungsbeispiels sowie anhand der Zeichnung.Further advantages, features and details of the invention will become apparent from the following description of a preferred embodiment and from the drawing.

Diese zeigt in der einzigen

Fig. 1
eine schematische Darstellung eines Kraftstoff-Injektors mit in axialer Richtung druckausgeglichenem Steuerventil und mit einem piezoelektri- schen Aktuator zum Betätigen des Steuerventils.
This shows in the only one
Fig. 1
a schematic representation of a fuel injector with pressure compensated in the axial direction control valve and with a piezoelectric actuator for actuating the control valve.

In Fig. 1 ist ein als Common-Rail-Injektor ausgebildeter Kraftstoff-Injektor 1 zum Einspritzen von Kraftstoff in einem nicht gezeigten Brennraum einer ebenfalls nicht gezeigten Brennkraftmaschine eines Kraftfahrzeugs in einer schematischen Darstellung gezeigt. 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 Kraftstoff-Injektor neben anderen, nicht gezeigten Injektoren über eine Versorgungsleitung 5 angeschlossen. Die Versorgungsleitung 5 mündet in einen Versorgungskanal 6 innerhalb des Kraftstoff-Injektors 1, welcher wiederum in einen Druckraum 7, der wie der Versorgungskanal 6 zum Hochdruckbereich 8 des Kraftstoff-Injektors 1 gehört, mündet. Der in den von einem Düsenkörper 9 radial außen begrenzten Druckraum 7 einströmende Kraftstoff strömt bei einem Einspritzvorgang unmittelbar in den Brennraum der Brennkraftmaschine. Der Kraftstoff-Injektor 1, genauer ein Niederdruckbereich 10 des Kraftstoff-Injektors 1, ist über einen nicht dargestellten Injektorrücklaufanschluss an eine Rücklaufleitung 11 angeschlossen. Über die Rücklaufleitung 11 kann eine später noch zu erläuternde Steuermenge an Kraftstoff in den Kraftstoff-Injektor 1 zu dem Vorratsbehälter 3 abfließen und von dort aus dem Hochdruckkreislauf wieder zugeführt werden.In Fig. 1 is a designed as a common rail injector fuel injector 1 for injecting fuel in a combustion chamber, not shown, of a likewise not shown internal combustion engine of a motor vehicle in a schematic Illustration shown. 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, stored in this embodiment about 2000 bar. To the high-pressure fuel accumulator 4, the fuel injector is connected via other, not shown, injectors via a supply line 5. The supply line 5 opens into a supply channel 6 within the fuel injector 1, which in turn opens into a pressure chamber 7, which, like the supply channel 6, belongs to the high-pressure region 8 of the fuel injector 1. The fuel flowing into the pressure chamber 7, which is bounded radially on the outside by a nozzle body 9, flows directly into the combustion chamber of the internal combustion engine during an injection process. The fuel injector 1, more precisely a low-pressure region 10 of the fuel injector 1, is connected to a return line 11 via an injector return port (not shown). Via the return line 11, a control quantity of fuel, which will be explained later, can flow into the fuel injector 1 to the storage container 3 and be fed back from there to the high-pressure circuit.

Innerhalb des Düsenkörpers 9 ist ein hier einteiliges als Düsennadel ausgebildetes Einspritzventilelement 12 axial verstellbar angeordnet. Dieses kann anstelle der hier einteiligen Ausbildung auch mehrteilig ausgebildet sein und beispielsweise aus einer Steuerstange und einer mit dieser gekoppelten Düsennadel bestehen. Jedenfalls ragt das bevorzugt einteilige Einspritzventilelement 12 in der Zeichnungsebene nach unten bis zu einem Einspritzventilelementsitz 13, mit dem es in an sich bekannter Weise dichtend zusammenwirkt. Wenn das Einspritzventilelement 12 an seinem Einspritzventilelementsitz 13 anliegt, d.h. sich in einer Schließstellung befindet, ist der Kraftstoffaustritt aus einer mehrere Einspritzöffnungen umfassenden Düsenlochanordnung 14 gesperrt. Ist es dagegen von seinem Einspritzventilelementsitz 13 abgehoben, kann Kraftstoff aus dem Druckraum 7 in einen Bereich unterhalb des Einspritzventilelementes 12 und von dort aus durch die Düsenlochanordnung 14, im Wesentlichen unter Hochdruck (Raildruck) stehend in den Brennraum gespritzt werden.Within the nozzle body 9, a one-piece injection valve element 12 designed as a nozzle needle is arranged axially adjustable. This can also be made in several parts instead of the one-piece training and, for example, consist of a control rod and a coupled with this nozzle needle. In any case, the preferred one-piece injection valve element 12 protrudes in the drawing plane down to an injection valve element seat 13, with which it cooperates in a sealing manner in a conventional manner. When the injection valve member 12 abuts its injection valve member seat 13, i. is in a closed position, the fuel outlet from a plurality of injection openings comprehensive nozzle hole assembly 14 is locked. If, on the other hand, it is lifted from its injection valve element seat 13, fuel can be injected from the pressure chamber 7 into a region below the injection valve element 12 and from there through the nozzle hole arrangement 14, substantially under high pressure (rail pressure) into the combustion chamber.

Von einer oberen Stirnseite 15 des Einspritzventilelementes 12 und einer in der Zeichnungsebene nach oben federkraftbelasteten Hülse 16 ist ein Steuerraum 17 begrenzt, der über eine in eine Drosselplatte 18, an der sich die Hülse 16 in axialer Richtung abstützt, eingebrachte Zulaufdrossel 19 mit unter Hochdruck stehendem Kraftstoff aus dem Hochdruckbereich 8, hier dem Versorgungskanal 6, versorgt wird. Alternativ kann die Zulaufdrossel 19 auch als Radialbohrung in der Hülse 16 vorgesehen sein. Die Hülse 16 mit darin eingeschlossenem Steuerraum 17 ist radial außen von unter Hochdruck stehendem Kraftstoff umschlossen, so dass ein ringförmiger Führungsspalt zwischen Hülse 16 und Einspritzventilelement 12 vergleichsweise kraftstoffdicht ist.From an upper end face 15 of the injection valve element 12 and a spring-loaded in the drawing plane sleeve 16 is a control chamber 17th limited, which is supplied via a in a throttle plate 18, on which the sleeve 16 is supported in the axial direction, introduced inlet throttle 19 with high-pressure fuel from the high-pressure region 8, here the supply channel 6. Alternatively, the inlet throttle 19 may also be provided as a radial bore in the sleeve 16. The sleeve 16 with the control chamber 17 enclosed therein is enclosed radially on the outside by fuel under high pressure, so that an annular guide gap between the sleeve 16 and the injection valve element 12 is comparatively fuel-tight.

Die Hülse 16 stützt sich in axialer Richtung von unten an der zuvor erwähnten Drosselplatte 18 ab, in der neben der Zulaufdrossel 19 ein eine Ablaufdrossel 20 aufweisender Ablaufkanal 21 eingebracht ist. Der Ablaufkanal 21 gehört ebenso wie ein mit diesem in Strömungsrichtung fluchtender Kanal 22, welcher in einer axial an die Drosselplatte 18 angrenzenden Platten 23 eingebracht ist zu einer hydraulischen Verbindung zwischen dem Steuerraum 17 und einem radial außen von der Platte 23 begrenzten Steuerventilraum 24. Der Steuerventilraum 24 ist in einem unteren Abschnitt einer Stufenbohrung 25 in der Platte 23 eingebracht. Axial verstellbar innerhalb des Steuerventilraums 24 ist ein bolzenförmiges Steuerventilelement 26 eines Steuerventils 27 angeordnet, welches mittels eines piezoelektrischen Aktuators 29 über einen hydraulischen Koppler 29 zwischen einer oberen ersten Schaltstellung, d.h. zwischen einem oberen ersten Steuerventilsitz 30 und einer unteren, d.h. zweiten Schaltstellung, also einem zweiten Steuerventilsitz 31 verstellbar ist. Bei dem Steuerventil 27 handelt es sich um ein 3/2-Wegeventil.The sleeve 16 is supported in the axial direction from below on the aforementioned throttle plate 18, in which in addition to the inlet throttle 19, a flow restrictor 20 exhibiting flow channel 21 is introduced. The drainage channel 21 as well as an aligned in the flow direction with this channel 22, which is introduced in an axially adjacent to the throttle plate 18 plates 23 to a hydraulic connection between the control chamber 17 and a radially outwardly of the plate 23 limited control valve chamber 24. The control valve chamber 24 is inserted in a lower portion of a stepped bore 25 in the plate 23. Axially adjustable within the control valve chamber 24 is a bolt-shaped control valve element 26 of a control valve 27 which is connected by means of a piezoelectric actuator 29 via a hydraulic coupler 29 between an upper first switching position, i. between an upper first control valve seat 30 and a lower, i. second switching position, ie a second control valve seat 31 is adjustable. The control valve 27 is a 3/2-way valve.

Wenn das Steuerventilelement 26 sich in der zweiten (unteren) Schaltstellung befindet, also das Steuerventilelement 26 an dem an einer später noch zu erläuternden Führungshülse 32 für das Steuerventilelement 26 ausgebildeten zweiten Steuerventilsitz 31 anliegt, kann Kraftstoff aus dem mit einem minimalen Volumen versehenen Steuerventilraum 24 am ersten Steuerventilsitz 30 vorbei in den Niederdruckbereich 10 und von dort aus zur Rücklaufleitung 11 strömen. Durch den in dieser Schaltstellung über die aus dem Kanal 22 und dem Ablaufkanal 21 bestehende hydraulische Verbindung aus dem Steuerraum 17 nachfließenden Kraftstoff sinkt der Kraftstoffdruck im Steuerraum 17 rapide ab. Dies ist darauf zurückzuführen, dass der Durchflussquerschnitt der Ablaufdrossel 20 größer ist als der der Zulaufdrossel 19, so dass bei in der zweiten Schaltstellung befindlichem Steuerventil 27 ein Nettoabfluss von Kraftstoff (Kraftstoffsteuermenge) aus dem Steuerraum 17 resultiert. Durch den Druckabfall im Steuerraum 17 hebt das Einspritzventilelement 12 vom Einspritzventilelementsitz 13 ab, so dass Kraftstoff durch die Düsenlochanordnung 14 in den Brennraum der Brennkraftmaschine strömen kann.When the control valve element 26 is in the second (lower) switching position, that is, the control valve element 26 abuts the second control valve seat 31 formed on a later to be explained guide sleeve 32 for the control valve element 26, fuel from the provided with a minimum volume control valve chamber 24 on first control valve seat 30 pass into the low-pressure region 10 and from there to the return line 11. By in this switching position on the existing from the channel 22 and the drain passage 21 hydraulic connection from the control chamber 17 fuel flowing down the fuel pressure in the control chamber 17 decreases rapidly. This is due to the fact that the flow area of the outlet throttle 20 is larger as that of the inlet throttle 19, so that when located in the second switching position control valve 27, a net outflow of fuel (fuel control amount) from the control chamber 17 results. Due to the pressure drop in the control chamber 17, the injection valve element 12 lifts off from the injection valve element seat 13 so that fuel can flow through the nozzle hole arrangement 14 into the combustion chamber of the internal combustion engine.

Wird das Steuerventilelement 26 in der Zeichnungsebene nach oben in die erste Schaltstellung bewegt, so dass das Steuerventilelement 26 am ersten, an der Platte 23 ausgebildeten Steuerventilsitz 30 anliegt, ist die hydraulische Verbindung zwischen dem Steuerraum 17 und dem Niederdruckbereich 10 verschlossen. Gleichzeitig ist eine später noch zu erläuternde hydraulische Verbindung 33 zwischen dem Hochdruckbereich 8, genauer dem Druckraum 7 und dem Steuerventilraum 24 geöffnet, so dass Kraftstoff über diese hydraulische Verbindung 33 und den Kanal 22 sowie den Ablaufkanal 21 in den Steuerraum 17 strömen und dort eine Druckerhöhung verursachen kann. Darüberhinaus strömt weiterhin Kraftstoff über die Zulaufdrossel 19 zu, was insgesamt zu einer rapiden Druckerhöhung im Steuerraum 17 führt, wodurch das Einspritzventilelement 12 der in der Zeichnungsebene nach unten auf den Einspritzventilelementsitz 13 verstellt wird und somit der Einspritzvorgang beendet wird.If the control valve element 26 is moved upward in the plane of the drawing into the first switching position, so that the control valve element 26 bears against the first control valve seat 30 formed on the plate 23, the hydraulic connection between the control chamber 17 and the low-pressure region 10 is closed. At the same time, a hydraulic connection 33 to be explained later between the high-pressure region 8, more precisely the pressure chamber 7 and the control valve chamber 24, so that fuel via this hydraulic connection 33 and the channel 22 and the drain channel 21 flow into the control chamber 17 and there an increase in pressure can cause. In addition, fuel continues to flow via the inlet throttle 19, which leads to a total rapid increase in pressure in the control chamber 17, whereby the injection valve element 12 is moved in the drawing plane down to the injection valve element seat 13 and thus the injection process is terminated.

Die hydraulische Verbindung zwischen dem Hochdruckbereich 8 und dem Steuerventilraum 24 umfasst eine Drosselbohrung 35 in der Drosselplatte 18, wobei die Drosselbohrung 35 den Druckraum 7 mit einem Ringraum 36 hydraulisch verbindet, wobei der Ringraum 36 radial außen vom Innenumfang einer stirnseitigen Bohrung in der Drosselplatte 18 und radial innen vom Außenumfang der Führungshülse 32 für das Steuerventilelement 26 begrenzt ist. Der Ringraum 36 steht über eine Hülsenbohrung 37 in dauerhafter hydraulischer Verbindung mit einem Zwischenraum 38, der radial außen vom Innenumfang einer zentrischen Bohrung in der Führungshülse 32 und radial innen vom Außenumfang des Steuerventilelementes 26 begrenzt ist. In der zweiten (unteren) Schaltstellung des Steuerventils 27 ist der Zwischenraum 38 von dem Steuerventilraum 24 über eine an der Führungshülse 32 ausgebildete Beißkante 39 getrennt, die dichtend mit der Unterseite eines Umfangsbundes 40 des Steuerventilelementes 26 zusammenwirkt. Die Beißkante 39 befindet sich an der Stirnseite eines axialen, ringförmigen Fortsatzes 41 der Führungshülse 32. Der Fortsatz 41 schafft axialen Raum zur Unterbringung einer Tellerfeder 42 (Steuerventilfeder), entgegen deren Federkraft das Steuerventilelement 26 bei einer Bestromung des piezoelektrischen Aktuators 28 in der Zeichnungsebene nach unten in die zweite Schaltstellung bewegt werden muss. Durch das Vorsehen einer Tellerfeder 42 als Steuerventilfeder kann das Volumen des Steuerventilraums 24 wie dargestellt minimiert werden. Die Tellerfeder 42 stützt sich in axialer Richtung an einer oberen Stirnseite der Führungshülse 32 und in der anderen axialen Richtung von unten an dem Umfangsbund 40 des Steuerventilelementes 26 ab.The hydraulic connection between the high pressure region 8 and the control valve chamber 24 includes a throttle bore 35 in the throttle plate 18, wherein the throttle bore 35 hydraulically connects the pressure chamber 7 with an annular space 36, wherein the annular space 36 radially outward from the inner periphery of a frontal bore in the throttle plate 18 and is bounded radially inwardly from the outer periphery of the guide sleeve 32 for the control valve element 26. The annular space 36 is connected via a sleeve bore 37 in permanent hydraulic connection with a gap 38, which is bounded radially outwardly from the inner circumference of a central bore in the guide sleeve 32 and radially inwardly from the outer periphery of the control valve element 26. In the second (lower) switching position of the control valve 27, the intermediate space 38 is separated from the control valve chamber 24 via a bite edge 39 formed on the guide sleeve 32, which sealingly cooperates with the underside of a peripheral collar 40 of the control valve element 26. The biting edge 39 is located on the front side of an axial, The extension 41 creates axial space for accommodating a plate spring 42 (control valve spring), against the spring force, the control valve member 26 must be moved in energizing the piezoelectric actuator 28 in the drawing plane down to the second switching position. By providing a plate spring 42 as a control valve spring, the volume of the control valve chamber 24 can be minimized as shown. The plate spring 42 is supported in the axial direction on an upper end side of the guide sleeve 32 and in the other axial direction from below on the peripheral collar 40 of the control valve element 26.

Bei dem Steuerventilelement 26 handelt es sich um ein in axialer Richtung zumindest näherungsweise druckausgeglichenes Steuerventilelement 26; dies bedeutet, dass wenn sich das Steuerventilelement 26 in der oberen (ersten) Schaltstellung befindet, wirken in axialer Richtung keine (oder ggf. nur geringe) resultierenden hydraulischen Kräfte. Dies wird dadurch erreicht, dass das Steuerventilelement 26 an einer unteren Stirnseite 43 mit Niederdruck beaufschlagt ist. Die untere Stirnseite 43 begrenzt in axialer Richtung nach oben einen Ausgleichsraum 44, der zum Niederdruckbereich 10 des Kraftstoff-Injektors 1 gehört bzw. über einen Niederdruckkanal 45 mit dem Injektorrücklaufanschluss hydraulisch verbunden ist. Der Ausgleichsraum 44 wird radial außen von der Führungshülse 32 begrenzt, die den Steuerventilraum 24 in axialer Richtung nach unten begrenzt. Die Führungshülse 32 ist über einen Großteil ihrer Axialerstreckung in einer stirnseitigen Bohrung in der Drosselplatte 18 aufgenommen und liegt mit einem oberen Abschnitt ihres Außenumfangs dichtend an einem unteren Abschnitt des Innenumfangs der Stufenbohrung 25 an, so dass der Ringraum 36 gegenüber dem Steuerventilraum 24 abgedichtet ist.The control valve element 26 is an at least approximately pressure-balanced control valve element 26 in the axial direction; this means that when the control valve element 26 is in the upper (first) switching position, no (or possibly only small) resulting hydraulic forces act in the axial direction. This is achieved in that the control valve element 26 is acted upon at a lower end face 43 with low pressure. The lower end face 43 bounded in the axial direction upwards a compensation chamber 44, which belongs to the low pressure region 10 of the fuel injector 1 and is hydraulically connected via a low pressure passage 45 to the injector return port. The compensation chamber 44 is bounded radially on the outside by the guide sleeve 32, which limits the control valve chamber 24 in the axial direction downwards. The guide sleeve 32 is received over a majority of its axial extent in a frontal bore in the throttle plate 18 and is sealingly connected to an upper portion of its outer periphery to a lower portion of the inner periphery of the stepped bore 25, so that the annular space 36 is sealed relative to the control valve chamber 24.

Claims (10)

Kraftstoff-Injektor zum Einspritzen von Kraftstoff in einen Brennraum einer Brennkraftmaschine, insbesondere Common-Rail-Injektor, umfassend ein ein- oder mehrteiliges Einspritzventilelement (12) zum Öffnen und Schließen mindestens einer Einspritzöffnung, wobei dem Einspritzventilelement (12) ein Steuerventil (27) zugeordnet ist, welches ein zwischen einer ersten und einer zweiten Schaltstellung verstellbares, in einem Steuerventilraum (24) angeordnetes Steuerventilelement (26) aufweist, wobei in der ersten Schaltstellung eine hydraulische Verbindung zwischen einem mit dem Einspritzventilelement (12) wirkverbundenen Steuerraum (17) und einem Niederdruckbereich (10) des Kraftstoff-Injektors (1) gesperrt und ein hydraulische Verbindung (33) zwischen einem Hochdruckbereich des Kraftstoff-Injektors (1) und dem Steuerventilraum (24) geöffnet ist und wobei in der zweiten Schaltstellung die hydraulische Verbindung zwischen dem Steuerraum (17) und dem Niederdruckbereich (10) geöffnet und die hydraulische Verbindung zwischen dem Hochdruckbereich (8) und dem Steuerventilraum (24) unterbrochen ist,
dadurch gekennzeichnet,
dass das Steuerventilelement (26) derart ausgebildet und angeordnet ist, dass durch den Druck im Steuerraum (17) keine oder nur eine geringe resultierende hydraulische Kraft in axialer Richtung auf das Steuerventilelement (26) ausgeübt wird, wenn die hydraulische Verbindung (33) zwischen dem Steuerraum (17) und dem Niederdruckbereich (10) in der ersten Schaltstellung des Steuerventilelementes (26) unterbrochen ist und, dass das Steuerventilelement (26) in der zweiten Schaltstellung zum Abdichtung der hydraulischen Verbindung (33) zwischen dem Hochdruckbereich (8) und dem Steuerventilraum(24) dichtend an einer das Steuerventilelement (26) an seinem Außenumfang führenden Führungshülse (32) anliegt.Fuel injector for injecting fuel into a combustion chamber of an internal combustion engine, in particular a common rail injector, comprising a one- or multi-part injection valve element (12) for opening and closing at least one injection port, wherein the injection valve element (12) associated with a control valve (27) which has an adjustable between a first and a second switching position, in a control valve chamber (24) arranged control valve element (26), wherein in the first switching position, a hydraulic connection between a with the injection valve element (12) operatively connected control chamber (17) and a low pressure region (10) of the fuel injector (1) is blocked and a hydraulic connection (33) between a high-pressure region of the fuel injector (1) and the control valve chamber (24) is opened and wherein in the second switching position, the hydraulic connection between the control chamber (17 ) and the low-pressure region (10) open and the hydraulic connection between the high-pressure region (8) and the control valve chamber (24) is interrupted,
characterized,
in that the control valve element (26) is designed and arranged in such a way that the pressure in the control chamber (17) exerts no or only a slight resultant hydraulic force in the axial direction on the control valve element (26) when the hydraulic connection (33) is between the two Control chamber (17) and the low-pressure region (10) in the first switching position of the control valve element (26) is interrupted and that the control valve element (26) in the second switching position for sealing the hydraulic connection (33) between the high-pressure region (8) and the control valve chamber (24) bears sealingly against a guide sleeve (32) guiding the control valve element (26) on its outer circumference. Kraftstoff-Injektor nach Anspruch 1,
dadurch gekennzeichnet,
dass die Feder als Tellerfeder ausgebildet ist.Fuel injector according to claim 1,
characterized,
that the spring is designed as a plate spring. Kraftstoff-Injektor nach einem der Ansprüche 1 oder 2,
dadurch gekennzeichnet,
dass die hydraulische Verbindung (33) zwischen dem Hochdruckbereich (8) und dem Steuerventilraum (24) als Drosselverbindung, vorzugsweise durch das Vorsehen einer Drosselbohrung (35), ausgebildet ist.Fuel injector according to one of claims 1 or 2,
characterized,
in that the hydraulic connection (33) between the high-pressure region (8) and the control valve chamber (24) is designed as a throttle connection, preferably by the provision of a throttle bore (35). Kraftstoff-Injektor nach einem der vorhergehenden Ansprüche,
dadurch gekennzeichnet,
dass sich die Feder zum einen axial an einem Umfangsbund (40) des Steuerventilelementes (26) und zum anderen axial an der Führungshülse (32) für das Steuerventilelement (26) abstützend angeordnet ist.Fuel injector according to one of the preceding claims,
characterized,
in that the spring is arranged so as to be supported axially on one circumferential collar (40) of the control valve element (26) and, on the other hand, axially on the guide sleeve (32) for the control valve element (26). Kraftstoff-Injektor nach einem der vorhergehenden Ansprüche,
dadurch gekennzeichnet,
dass die hydraulische Verbindung (33) einen radial außen von der Führungshülse (32) und radial innen von dem Steuerventilelement (26) begrenzten Zwischenraum umfasst.Fuel injector according to one of the preceding claims,
characterized,
in that the hydraulic connection (33) comprises a gap which is radially outwardly of the guide sleeve (32) and radially inward of the control valve element (26). Kraftstoff-Injektor nach Anspruch 5,
dadurch gekennzeichnet,
dass der Zwischenraum über mindestens eine Hülsenbohrung (37) in der Führungshülse (32) mit einem radial innen von der Führungshülse (32) begrenzten Ringraum (36) verbunden ist.Fuel injector according to claim 5,
characterized,
in that the intermediate space is connected via at least one sleeve bore (37) in the guide sleeve (32) to an annular space (36) bounded radially inward by the guide sleeve (32). Kraftstoff-Injektor nach einem der vorhergehenden Ansprüche,
dadurch gekennzeichnet,
dass die Führungshülse (32) axial an eine Drosselplatte (18) angrenzt, in der eine, vorzugsweise als Drosselbohrung (35) ausgeführte, Bohrung als Teilabschnitt der hydraulischen Verbindung (33) zwischen dem Hochdruckbereich (8) und dem Steuerventilraum (24) eingebracht ist.Fuel injector according to one of the preceding claims,
characterized,
in that the guide sleeve (32) axially adjoins a throttle plate (18) in which a bore, preferably as a throttle bore (35), is introduced as a section of the hydraulic connection (33) between the high-pressure region (8) and the control valve chamber (24) , Kraftstoff-Injektor nach Anspruch 7,
dadurch gekennzeichnet,
dass die Führungshülse (32) eine Beißkante zum dichtenden Zusammenwirken mit dem Steuerventilelement (26) in der zweiten Schaltstellung aufweist.Fuel injector according to claim 7,
characterized,
in that the guide sleeve (32) has a biting edge for sealing cooperation with the control valve element (26) in the second switching position. Kraftstoff-Injektor nach einem der vorhergehenden Ansprüche,
dadurch gekennzeichnet,
dass zum Betätigen des Steuerventils (27) ein piezoelektrischer Aktuator (28) vorgesehen ist.Fuel injector according to one of the preceding claims,
characterized,
in that a piezoelectric actuator (28) is provided for actuating the control valve (27). Kraftstoff-Injektor nach einem der vorhergehenden Ansprüche,
dadurch gekennzeichnet,
dass die hydraulische Verbindung (33) zwischen dem Steuerraum (17) und dem Steuerventilraum (24) durch zwei axial aneinander angrenzende Bauteile verläuft.Fuel injector according to one of the preceding claims,
characterized,
in that the hydraulic connection (33) runs between the control chamber (17) and the control valve chamber (24) through two axially adjacent components.
EP10162230A 2009-07-07 2010-05-07 Fuel injector with pressure-equalised control valve Not-in-force EP2275666B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102009027494A DE102009027494A1 (en) 2009-07-07 2009-07-07 Fuel injector with pressure compensated control valve

Publications (2)

Publication Number Publication Date
EP2275666A1 true EP2275666A1 (en) 2011-01-19
EP2275666B1 EP2275666B1 (en) 2012-01-18

Family

ID=42767939

Family Applications (1)

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Country Status (3)

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AT (1) ATE542042T1 (en)
DE (1) DE102009027494A1 (en)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2479418A1 (en) * 2011-01-21 2012-07-25 Robert Bosch GmbH Fuel injector valve
WO2013000618A1 (en) * 2011-06-30 2013-01-03 Robert Bosch Gmbh Fuel injector
EP2511514A3 (en) * 2011-04-11 2013-11-13 Robert Bosch GmbH Fuel injector valve

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004030445A1 (en) 2004-06-24 2006-01-12 Robert Bosch Gmbh Fuel injector
DE102004049702B3 (en) * 2004-10-12 2006-03-09 Siemens Ag Servo valve and injector
EP1640604A1 (en) * 2004-09-23 2006-03-29 Siemens Aktiengesellschaft Servo valve and injection valve
DE102006009070A1 (en) * 2006-02-28 2007-08-30 Robert Bosch Gmbh Fuel-injection valve for air-compressing, auto-igniting internal combustion engines comprises a valve with a corrugated washer partly surrounding the periphery of a bolt section of a valve bolt
EP1876342A2 (en) * 2006-07-04 2008-01-09 Denso Corporation Piezo injector and piezo injector system
DE102007047426A1 (en) * 2007-05-15 2008-11-20 Robert Bosch Gmbh Injector with piezo actuator
US20090165749A1 (en) * 2007-12-27 2009-07-02 Caterpillar Inc. Engine and control valve assembly having reduced variability in operation over time
DE102008001330A1 (en) 2008-04-23 2009-10-29 Robert Bosch Gmbh Fuel injection valve for internal combustion engines

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004030445A1 (en) 2004-06-24 2006-01-12 Robert Bosch Gmbh Fuel injector
EP1640604A1 (en) * 2004-09-23 2006-03-29 Siemens Aktiengesellschaft Servo valve and injection valve
DE102004049702B3 (en) * 2004-10-12 2006-03-09 Siemens Ag Servo valve and injector
DE102006009070A1 (en) * 2006-02-28 2007-08-30 Robert Bosch Gmbh Fuel-injection valve for air-compressing, auto-igniting internal combustion engines comprises a valve with a corrugated washer partly surrounding the periphery of a bolt section of a valve bolt
EP1876342A2 (en) * 2006-07-04 2008-01-09 Denso Corporation Piezo injector and piezo injector system
DE102007047426A1 (en) * 2007-05-15 2008-11-20 Robert Bosch Gmbh Injector with piezo actuator
US20090165749A1 (en) * 2007-12-27 2009-07-02 Caterpillar Inc. Engine and control valve assembly having reduced variability in operation over time
DE102008001330A1 (en) 2008-04-23 2009-10-29 Robert Bosch Gmbh Fuel injection valve for internal combustion engines

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2479418A1 (en) * 2011-01-21 2012-07-25 Robert Bosch GmbH Fuel injector valve
EP2511514A3 (en) * 2011-04-11 2013-11-13 Robert Bosch GmbH Fuel injector valve
WO2013000618A1 (en) * 2011-06-30 2013-01-03 Robert Bosch Gmbh Fuel injector

Also Published As

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ATE542042T1 (en) 2012-02-15
EP2275666B1 (en) 2012-01-18
DE102009027494A1 (en) 2011-01-13

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