EP2511514A2 - Fuel injector valve - Google Patents

Fuel injector valve Download PDF

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Publication number
EP2511514A2
EP2511514A2 EP12158513A EP12158513A EP2511514A2 EP 2511514 A2 EP2511514 A2 EP 2511514A2 EP 12158513 A EP12158513 A EP 12158513A EP 12158513 A EP12158513 A EP 12158513A EP 2511514 A2 EP2511514 A2 EP 2511514A2
Authority
EP
European Patent Office
Prior art keywords
sleeve
valve
bore
fuel injection
annular gap
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
EP12158513A
Other languages
German (de)
French (fr)
Other versions
EP2511514B1 (en
EP2511514A3 (en
Inventor
Karsten-Sepp Ramsauer
Holger Rapp
Daniel Schrader
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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Filing date
Publication date
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Publication of EP2511514A2 publication Critical patent/EP2511514A2/en
Publication of EP2511514A3 publication Critical patent/EP2511514A3/en
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Publication of EP2511514B1 publication Critical patent/EP2511514B1/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
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0045—Three-way valves
    • 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
    • F02M63/0071—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059 characterised by guiding or centering means in valves including the absence of any guiding means, e.g. "flying arrangements"
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/28—Details of throttles in fuel-injection apparatus
    • 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

Definitions

  • the invention relates to a fuel injection valve, in particular an injector for fuel injection systems of internal combustion engines. Specifically, the invention relates to the field of injectors for fuel injection systems of air compressing, self-igniting internal combustion engines.
  • a double-switching control valve in which a valve body is guided in the housing of the control valve, so that the wear on a valve cone of the valve body and a first valve seat in the housing of the control valve is reduced.
  • the control valve has a spring chamber into which a bypass and an outlet throttle lead.
  • the bypass establishes a hydraulic connection between an inlet channel and an inlet of the control valve.
  • the fuel injection valve according to the invention with the features of claim 1 has the advantage that an improved design of the control valve is made possible. In particular, an efficiency as well as the performance requirements of a high-pressure pump can be reduced.
  • the switching valve comprises the sleeve (guide sleeve) for the valve pin, which can seal the space under the valve pin of high-pressure fuel and can provide a connection there to standing under a return pressure fuel.
  • a stroke stop for the valve pin can still be performed and it can still be provided a valve spring, which acts on the valve pin in the pressureless state of the system with a closing force.
  • valve pin in its rest position seals a valve space at a sealing seat against a low-pressure space.
  • sealing seat between the valve pin and the sleeve of the valve chamber is connected to high-pressure fuel.
  • the valve pin is moved downwards so that the sealing seat opens with respect to the low-pressure space and the sealing seat closes with respect to the high-pressure space.
  • the sealing seat between the valve pin and the sleeve at the same time represents a stroke stop.
  • the valve chamber is now connected to the low-pressure volume of the fuel injection valve and thus to the return port.
  • the switching valve is switched back to its idle state, then takes place in an advantageous manner on the then re-opened sealing seat between the valve and the sleeve an inflow from the high pressure passage in the valve chamber and from there also against their actual flow direction via an outlet throttle in a control room ,
  • the control chamber can be filled not only via an inlet throttle, but also via the seat between the sleeve and the valve pin and the outlet throttle, which in this case flows backwards. This makes it possible to achieve an increased closing speed of the nozzle needle.
  • the diaphragm of an actuator module can be loaded. This results in a directed against the actuator force disturbance force on the actuator and there is a risk of unduly high stress on the membrane.
  • the throttle which is designed in the region of the guide between the valve pin and the sleeve, namely the connection to the high pressure passage is provided with a flow resistance.
  • the volume between the throttle point and the sealing seat is reduced.
  • the throttle point which is now provided by the throttle in the region of the guide between the valve pin and the sleeve, be arranged closer to the sealing seat between the sleeve and the valve pin, in contrast to a throttled high-pressure channel.
  • the switching valve would either not completely closed or slightly opened again due to oscillations of the actuator due to the remaining residual charge stationary position, which corresponds to a closing bounce. In either case, there could be a slowed or delayed closing of the nozzle needle, so that the actual injection quantity increases compared to the desired one.
  • both the operation of the switching valve can be favorably influenced by the inventive design of the fuel injection valve, since defined switching positions can be taken at desired times.
  • this also the injection behavior, in particular an injection curve, the fuel injection valve is favorably influenced.
  • the predetermined injection times can be guaranteed.
  • the embodiment of the invention thus also allows greater degrees of freedom in the structural design of the fuel injection valve. Specifically, the supply of fuel does not necessarily have to be through the throttle plate.
  • the high pressure channel can thus be configured in other housing parts.
  • Another disadvantage of a throttled high-pressure channel is that at each switching operation of the switching valve, the pressure in the annular space surrounding the sleeve drops significantly below the rail pressure as a result of the now existing throttling in front of this annulus. As a result, in turn, an increased slip between the sleeve and the throttle plate and thus increased wear on this contact point arises. In this case, the sealing effect of the contact point between the sleeve and the throttle plate can be lost.
  • the high-pressure passage is designed in an advantageous manner as an unthrottled high-pressure passage in comparison to a throttling effect of the throttle, the pressure in the annular space surrounding the sleeve can be maintained at a sufficiently high pressure level. An undesirably high wear at the contact point between the sleeve and the throttle plate is thereby prevented. In addition, the desired sealing effect is reliably ensured at the contact point between the sleeve and throttle plate.
  • a significant advantage of the invention is thus that a strong Abgresstoss is avoided when switching the switching valve, without additional pressure pulsations are generated in the surrounding space of the sleeve.
  • the sleeve has at least one bore, which leads from an outer side of a sleeve to an annular gap between an inner side of the sleeve and the valve pin, and that the valve space via the annular gap and the bore in the sleeve with the high-pressure channel is connectable.
  • the bore is designed as a throttle bore. The bore thereby forms a throttled passage for the fuel.
  • at least one throttle bore is provided. However, it can also be provided several throttle bores.
  • the bore is designed as unthrottled bore.
  • an unthrottled bore is in this case a bore to understand that has at most a comparatively small throttle effect compared to other throttle points.
  • the valve pin and / or the sleeve are configured so that the annular gap between the inside of the sleeve and the valve pin along an axis of the valve pin at least substantially from the sealing seat between the sleeve and the valve pin to the Mouth opening extends and that the annular gap, at least in the region of the mouth opening has a certain radial annular gap height.
  • a throttle point can be formed at the deflection point at the mouth opening.
  • the throttle may advantageously be formed at the deflection of the mouth of the bore, wherein the cross-sectional area of the throttle at least approximately by a product having a multiplier which is equal to the outlet circumference of the mouth of the bore, and a multiplicand equal to the radial annular gap height of the annular gap in the region of the mouth opening is given.
  • the throttle effect can be adjusted specifically.
  • the bore can be designed as a continuous bore with a uniform diameter or as a stepped bore with variable over the length diameter.
  • the bore in the sleeve is designed as a radially oriented bore. As a result, the production costs can be optimized.
  • the bore in the sleeve is configured obliquely in the sleeve. As a result, a flow optimization is possible.
  • the sleeve has a plurality of bores, which lead from an outer side of the sleeve to an annular gap between the inside of the sleeve and the valve pin and that the valve chamber via the annular gap and the holes in the sleeve with the high-pressure channel is connectable.
  • the connection is made according to the switching position of the switching valve.
  • the bores are configured circumferentially distributed in the sleeve with respect to an axis of the valve pin. In this way it can be achieved that the forces resulting from the flow, which act on the sleeve, at least partially compensate.
  • the holes can be distributed not only over the height, that is axially, but also over the circumference of the sleeve, that is, azimuthally. In the case of several holes, these can have a uniform exit diameter or else different exit diameters. For a force compensation, it is advantageous in this case that the mouth openings of the bores, at which the holes open into the annular gap between the inside of the sleeve and the valve pin, at least approximately the same outlet cross-section, in particular outlet diameter.
  • Fig. 1 shows a first embodiment of a fuel injection valve 1 of the invention in a schematic, partial sectional view.
  • the fuel injection valve 1 can be used in particular as an injector for fuel injection systems of air-compressing, self-igniting internal combustion engines.
  • a preferred use of the fuel injection valve 1 is for a fuel injection system with a common rail that stores diesel fuel under high pressure and divides it into several fuel injection valves 1.
  • the fuel injection valve 1 according to the invention is also suitable for other applications.
  • the fuel injection valve 1 has a seat plate 2, a valve plate 3 and a throttle plate 4.
  • a switching valve 5 is configured in the region of the valve plate 3.
  • the switching valve 5 has a space 6 which is configured in the valve plate 3.
  • the space 6 may in this case be configured by a bore in the valve plate 3.
  • a sleeve 7 and a valve pin 8 are arranged in the space 6, .
  • the valve pin 8 is guided in this case in the sleeve 7.
  • valve chamber 9 which is designed as an annular valve chamber 9.
  • valve pin 8 On the valve pin 8 a double-acting valve closing body 10 is formed, so to speak, around which the valve chamber 9 extends circumferentially.
  • a sealing seat 11 is formed, which separates the valve chamber 9 from a low pressure region 12.
  • a low-pressure space 13 may be provided, in which an actuator 14 is arranged for actuating the valve pin 8.
  • the low-pressure region 12 is ensured here by the low-pressure space 13.
  • the low-pressure region 12 may be connected to a tank, for example.
  • valve closing body 10 of the valve closing bolt 8 with the sleeve 7 forms a sealing seat 15.
  • the sealing seat 11 is opened and at the same time the sealing seat 15 is closed.
  • a high pressure passage 16 is formed in the throttle plate 4.
  • the high-pressure passage 16 is designed here as an unthrottled high-pressure passage 16.
  • the high-pressure passage 16 leads fuel under high pressure into an annular space 17, between an outer side 20 of the sleeve 7 and an inner wall 21 of the valve plate 3, which delimits the space 6.
  • a low pressure chamber 22 which is connected, for example, with the low-pressure chamber 13.
  • the sleeve 7 is pressed into the valve plate 3, whereby the annular space 17 and the valve chamber 9 are hydraulically separated from each other.
  • a throttle 23 is provided, which is formed in this embodiment by a throttle bore 23.
  • the throttle bore 23 extends in this case with respect to an axis 24 of the valve pin 8 radially through the sleeve 7.
  • the throttle bore 23 leads from the outer side 20 of the sleeve 7 to an annular gap 25 between an inner side 26 of the sleeve 7 and the valve pin 8.
  • the valve chamber 9 is connected via the annular gap 25 and the throttle bore 23 and the annular space 17 with the high pressure passage 16.
  • the high-pressure passage 16 does not necessarily have to extend through the throttle plate 4.
  • the high-pressure passage 16 can also be configured in the valve plate 3.
  • the sealing seat 11 Upon actuation of the switching valve 5 by means of the actuator 14, the sealing seat 11 is opened and at the same time the sealing seat 15 is closed. Thus flows in the valve chamber 9 under high pressure fuel. Since the throttle 23 is arranged relative to the fluidic distance between the sealing seat 15 and the high-pressure passage 16 relatively close to the sealing seat 15, when switching back the switching valve 5 in the in the Fig. 1 illustrated starting position, the control amount largely limited to the necessary extent and the occurrence of a strong Ab Kunststoffcies avoided during the switching process.
  • the fuel injection valve 1 has a nozzle needle 27, which is enclosed at its end by a sealing sleeve 28.
  • the sealing sleeve 28 is supported here on the throttle plate 4, so that a control chamber 29 between the nozzle needle 27, the sealing sleeve 28 and the throttle plate 4 is formed.
  • the control chamber 29 is connected to the valve space 9 via an outlet throttle 30, which is configured in the throttle plate 4, and a connecting channel 31, which is configured in the valve plate 3, and a recess 32, which is configured in the seat plate 2.
  • the recess 32 in the seat plate 2 can, as in Fig.
  • the recess 32 in the seat plate 2 may alternatively not be configured circumferentially around the valve seat, so that the sleeve 7 between the seat plate 2 and the throttle plate 4 mechanically clamped and so axially is fixed.
  • the pressure in the control chamber 29 is thus influenced by the pressure in the valve chamber 9. If the sealing seat 11 is opened, then the pressure in the control chamber 29 also drops.
  • the sealing seat 11 is closed and thus the sealing seat 15 is opened, then the pressure in the control chamber 29 rises due to the subsequent flow of fuel through an inlet throttle 33.
  • the inlet throttle 33 is shown schematically as a bore in the sealing sleeve 38 for ease of illustration.
  • the closing speed of the nozzle needle 27 is here, however, further increased because under high pressure fuel also flows backwards through the outlet throttle 30, since at the same time high-pressure fuel from the high-pressure passage 16 enters the valve chamber 9.
  • At least one passage bore 23 is provided through the sleeve 7, which is designed as a throttle 23.
  • the fuel volume between the throttle point 23 and the sealing seat 15 can be kept very small, so that the control amount is largely limited to the necessary extent.
  • the high-pressure passage 16 can be configured by a simple bore, through which the fuel is conducted without significant throttle effect. That is, the throttle effect of the high-pressure passage 16 is small in comparison with the throttling action of the throttle bore 23.
  • the throttling takes place only downstream seen from the annular space 17, so that in the annular space 17 always the high pressure, in particular the rail pressure, or the pressure prevails at the inlet to a nozzle of the fuel injection valve 1.
  • a throttle bore 23 and a plurality of throttle bores 23 may be provided in the sleeve 7, which produce a plurality of connections between the annular space 17 and the sealing seat 15 of the switching valve 5.
  • the throttle bores 23, which are designed in particular as transverse bores, can be distributed over the height, that is to say along the axis 24, as well as with respect to the axis 24 over the circumference of the sleeve 7, that is to say azimuthally.
  • the throttle bore 23 is designed to extend radially in this embodiment. But the throttle bore 23 and the plurality of throttle bores 23 may also run as desired obliquely in the sleeve 7.
  • the high-pressure passage 16 can also open further upstream of the throttle plate 4 from open into the annular space 17.
  • Fig. 2 shows a fuel injection valve 1 in a partial, schematic sectional view according to a second embodiment of the invention.
  • a bore 23 ' is provided in the sleeve 7, as unthrottled bore 23 'is configured.
  • the bore 23 ' has an orifice 40, on which the bore 23' has a defined outlet cross-section.
  • the bore 23 ' opens into an annular gap 25, which has defined predetermined dimensions.
  • valve pin 8 and / or the sleeve 7 are designed so that the annular gap 25 between the inner side 26 of the sleeve 7 and the valve pin 8 along the axis 24 of the valve pin 8 of the sealing seat 15 between the sleeve 7 and the valve pin 8 to extends to the orifice 40 and preferably slightly further with a certain, radial annular gap height h B.
  • the radial annular gap height h B is in this case measured or determined radially with respect to the axis 24 of the valve pin 8.
  • At the mouth opening 40 results in a fluidic deflection point 41 of the bore 23 'in the annular gap 25.
  • the cross-sectional area of the throttle 42 formed thereby which is composed of the bore 23' with the orifice 40 and the annular gap 25, at least approximately by a product having a multiplier equal to the exit circumference of the orifice 40 of the bore 23 'and a multiplicand equal to the radial annular gap height h B of the annular gap 25. If the orifice 40 has a diameter d, then the outlet cross-section results according to the exit circumference given by the diameter d and the gap height h B.
  • the bore 23 ' can be designed as a continuous bore with a uniform diameter or as a stepped bore with variable over the length diameter.
  • these transverse bores are distributed uniformly over the circumference, mutual compensation can be achieved with respect to the resulting transverse force acting on the sleeve 7. Also a distribution over the height is possible.
  • Both the outer contour of the valve pin 8 in the region of the mouth opening 40 and the inner side 26 of the sleeve 7 in the region of the mouth opening 40 can be designed exactly or at least approximately cylindrically. But there are also any other, preferably rotationally symmetric contours possible.
  • annular gap 25 is configured by reducing a diameter 45 of the valve pin 8 in sections.
  • an inner diameter 45 of the sleeve 7 can also be made larger in sections in order to form the annular gap 25 in sections.

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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 valve (1) has a communicating passage (31) extending from a control space (29) into an annular valve space (9) of a switching valve (5), where the switching valve comprises a case (7) i.e. guide sleeve, with valve bolts (8). A sealing seat (15) is formed between the case and the valve bolt, where a connection of the valve space with a high pressure channel (16) e.g. unthrottled high pressure channel, is controlled over the sealing seat. A throttle hole (23) is provided in a region of a guide between the valve bolt and the case for connecting the valve space with the high pressure channel.

Description

Stand der TechnikState of the art

Die Erfindung betrifft ein Brennstoffeinspritzventil, insbesondere einen Injektor für Brennstoffeinspritzanlagen von Brennkraftmaschinen. Speziell betrifft die Erfindung das Gebiet der Injektoren für Brennstoffeinspritzanlagen von luftverdichtenden, selbstzündenden Brennkraftmaschinen.The invention relates to a fuel injection valve, in particular an injector for fuel injection systems of internal combustion engines. Specifically, the invention relates to the field of injectors for fuel injection systems of air compressing, self-igniting internal combustion engines.

Aus der DE 10 2004 061 800 A1 ist ein Injektor eines Kraftstoffeinspritzsystems einer Brennkraftmaschine bekannt. Hierbei ist ein doppelt schaltendes Steuerventil vorgesehen, bei dem ein Ventilkörper in dem Gehäuse des Steuerventils geführt wird, so dass der Verschleiß an einem Ventilkegel des Ventilkörpers und einem ersten Ventilsitz im Gehäuse des Steuerventils verringert wird. Das Steuerventil weist einen Federraum auf, in den ein Bypass und eine Ablaufdrossel führen. Der Bypass stellt eine hydraulische Verbindung zwischen einem Zulaufkanal und einem Eingang des Steuerventils her. Durch eine geeignete Ansteuerung des Steuerventils kann eine hydraulische Verbindung zwischen der Ablaufdrossel und einem Kraftstoffrücklauf hergestellt werden, so dass der Druck in einem Steuerraum sinkt, wodurch ein Öffnen einer Düsennadel bewirkt wird.From the DE 10 2004 061 800 A1 An injector of a fuel injection system of an internal combustion engine is known. Here, a double-switching control valve is provided in which a valve body is guided in the housing of the control valve, so that the wear on a valve cone of the valve body and a first valve seat in the housing of the control valve is reduced. The control valve has a spring chamber into which a bypass and an outlet throttle lead. The bypass establishes a hydraulic connection between an inlet channel and an inlet of the control valve. By a suitable control of the control valve, a hydraulic connection between the outlet throttle and a fuel return can be made, so that the pressure in a control chamber decreases, whereby opening of a nozzle needle is effected.

Der aus der DE 10 2004 061 800 A1 bekannte Injektor hat den Nachteil, dass der Federraum ein großes Volumen aufweist, so dass die bei der Steuerung verursachten Absteuermengen groß sind. Dies wirkt sich ungünstig auf den Wirkungsgrad des Injektors und somit des gesamten Brennstoffeinspritzsystems aus.The from the DE 10 2004 061 800 A1 known injector has the disadvantage that the spring chamber has a large volume, so that the Absteuermengen caused in the control are large. This has an unfavorable effect on the efficiency of the injector and thus of the entire fuel injection system.

Offenbarung der ErfindungDisclosure of the invention

Das erfindungsgemäße Brennstoffeinspritzventil mit den Merkmalen des Anspruchs 1 hat den Vorteil, dass eine verbesserte Ausgestaltung des Steuerventils ermöglicht ist. Insbesondere können ein Wirkungsgrad sowie die Leistungsanforderungen an eine Hochdruckpumpe verringert werden.The fuel injection valve according to the invention with the features of claim 1 has the advantage that an improved design of the control valve is made possible. In particular, an efficiency as well as the performance requirements of a high-pressure pump can be reduced.

Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen des im Anspruch 1 angegebenen Brennstoffeinspritzventils möglich.The measures listed in the dependent claims advantageous developments of the fuel injection valve specified in claim 1 are possible.

In vorteilhafter Weise umfasst das Schaltventil die Hülse (Führungshülse) für den Ventilbolzen, die den Raum unter dem Ventilbolzen von unter einem hohen Druck stehenden Brennstoff abdichten kann und dort eine Verbindung zu unter einem Rücklaufdruck stehenden Brennstoff bereitstellen kann. In dem unter Rücklaufdruck stehenden Raum unter dem Ventilbolzen können noch ein Hubanschlag für den Ventilbolzen ausgeführt sein und es kann noch eine Ventilbolzenfeder vorgesehen sein, die den Ventilbolzen auch im drucklosen Zustand des Systems mit einer Schließkraft beaufschlagt.Advantageously, the switching valve comprises the sleeve (guide sleeve) for the valve pin, which can seal the space under the valve pin of high-pressure fuel and can provide a connection there to standing under a return pressure fuel. In the space under the back pressure under the valve pin, a stroke stop for the valve pin can still be performed and it can still be provided a valve spring, which acts on the valve pin in the pressureless state of the system with a closing force.

In vorteilhafter Weise dichtet der Ventilbolzen in seinem Ruhezustand einen Ventilraum an einem Dichtsitz gegen einen Niederdruckraum ab. Durch den dann geöffneten Dichtsitz zwischen dem Ventilbolzen und der Hülse ist der Ventilraum mit unter Hochdruck stehendem Brennstoff verbunden. Wird das Ventil in den aktiven Zustand geschaltet, so wird der Ventilbolzen nach unten bewegt, so dass sich der Dichtsitz bezüglich des Niederdruckraums öffnet und der Dichtsitz bezüglich des Hochdruckraums schließt. Dabei stellt der Dichtsitz zwischen dem Ventilbolzen und der Hülse zugleich einen Hubanschlag dar. Der Ventilraum ist nun mit dem Niederdruckvolumen des Brennstoffeinspritzventils und damit mit dem Rücklaufanschluss verbunden. Wird das Schaltventil wieder in seinen Ruhezustand geschaltet, so erfolgt in vorteilhafter Weise über den dann wieder geöffneten Dichtsitz zwischen dem Ventil bolzen und der Hülse eine Zuströmung aus dem Hochdruckkanal in den Ventilraum und von dort ebenfalls auch entgegen deren eigentlicher Strömungsrichtung über eine Ablaufdrossel in einen Steuerraum. Hierdurch kann der Steuerraum nicht nur über eine Zulaufdrossel, sondern auch über den Sitz zwischen der Hülse und dem Ventilbolzen und die Ablaufdrossel, die hierbei rückwärts durchströmt wird, befüllt werden. Hierdurch lässt sich eine erhöhte Schließgeschwindigkeit der Düsennadel erreichen.In an advantageous manner, the valve pin in its rest position seals a valve space at a sealing seat against a low-pressure space. Through the then opened sealing seat between the valve pin and the sleeve of the valve chamber is connected to high-pressure fuel. When the valve is switched to the active state, the valve pin is moved downwards so that the sealing seat opens with respect to the low-pressure space and the sealing seat closes with respect to the high-pressure space. In this case, the sealing seat between the valve pin and the sleeve at the same time represents a stroke stop. The valve chamber is now connected to the low-pressure volume of the fuel injection valve and thus to the return port. If the switching valve is switched back to its idle state, then takes place in an advantageous manner on the then re-opened sealing seat between the valve and the sleeve an inflow from the high pressure passage in the valve chamber and from there also against their actual flow direction via an outlet throttle in a control room , As a result, the control chamber can be filled not only via an inlet throttle, but also via the seat between the sleeve and the valve pin and the outlet throttle, which in this case flows backwards. This makes it possible to achieve an increased closing speed of the nozzle needle.

Bei der Ausgestaltung eines herkömmlichen Schaltventils ist es denkbar, dass sich ein Sitz unter dem Ventilbolzen an einer Drosselplatte befindet, wo eine Bypassbohrung unter dem Ventilbolzen in den Ventilraum mündet. Bei geöffnetem Schaltventil wird diese Bypassbohrung durch den Ventilbolzen verschlossen. Der Kraftaufwand zum Öffnen dieses Schaltventils ist nun allerdings hoch, da der Ventilbolzen an seiner Unterseite mit Hochdruck beaufschlagt ist. Ferner ergibt sich bei herkömmlichen Schaltventilen gegebenenfalls das Problem, dass es kurzzeitig zu einem Zustand kommt, in dem beide Dichtsitze gewissermaßen teilweise geöffnet sind. Hierdurch besteht kurzzeitig eine direkte Verbindung zwischen einem Hoch- und einem Niederdruckvolumen, was kurzzeitig zu einem erhöhten Abströmen von Brennstoff in den Niederdruckraum führt. Dies kann sich in einem hydraulischen Schaltstoß auswirken, der im Niederdruckraum wiederum zu einer dynamischen Drucküberhöhung führt. Hierdurch kommt es zu einer erhöhten Beanspruchung von Bauteilen. Speziell kann die Membran eines Aktormoduls belastet werden. Hieraus resultiert eine gegen die Aktorkraft gerichtete Störkraft auf den Aktor und es besteht die Gefahr einer unzulässig hohen Belastung der Membran.In the embodiment of a conventional switching valve, it is conceivable that a seat under the valve pin is located on a throttle plate, where a bypass bore opens under the valve pin in the valve chamber. When the switching valve is open, this bypass bore is closed by the valve pin. However, the force required to open this switching valve is now high because the valve pin is acted upon at its bottom with high pressure. Furthermore, in the case of conventional switching valves, there may be the problem that there is a short-term condition in which both occur Seal seats are partially open, so to speak. As a result, there is a short-term direct connection between a high and a low pressure volume, which leads briefly to an increased outflow of fuel into the low-pressure space. This can result in a hydraulic shift shock, which in turn leads to a dynamic pressure increase in the low-pressure space. This leads to an increased stress on components. Specifically, the diaphragm of an actuator module can be loaded. This results in a directed against the actuator force disturbance force on the actuator and there is a risk of unduly high stress on the membrane.

Solch ein hydraulischer Schaltstoß sowie das Abströmen eines erhöhten Volumenstroms können durch die erfindungsgemäße Ausgestaltung vermieden werden. Durch die Drossel, die im Bereich der Führung zwischen dem Ventilbolzen und der Hülse ausgestaltet ist, wird nämlich die Verbindung zu dem Hochdruckkanal mit einem Strömungswiderstand versehen. Außerdem wird im Unterschied zu einem gedrosselten Hochdruckkanal das Volumen zwischen der Drosselstelle und dem Dichtsitz reduziert. Denn bei der erfindungsgemäßen Ausgestaltung kann die Drosselstelle, die nun durch die Drossel im Bereich der Führung zwischen dem Ventilbolzen und der Hülse vorgesehen ist, im Unterschied zu einem gedrosselten Hochdruckkanal näher an dem Dichtsitz zwischen der Hülse und dem Ventilbolzen angeordnet sein.Such a hydraulic switching shock and the outflow of an increased volume flow can be avoided by the inventive design. By the throttle, which is designed in the region of the guide between the valve pin and the sleeve, namely the connection to the high pressure passage is provided with a flow resistance. In addition, in contrast to a throttled high-pressure channel, the volume between the throttle point and the sealing seat is reduced. For in the embodiment according to the invention, the throttle point, which is now provided by the throttle in the region of the guide between the valve pin and the sleeve, be arranged closer to the sealing seat between the sleeve and the valve pin, in contrast to a throttled high-pressure channel.

Somit können insbesondere starke hydraulische Schaltstöße sowohl beim Öffnen als auch beim Schließen des Schaltventils vermieden werden, so dass folglich kurze hohe Druckspitzen im Niederdruckraum unterbleiben. Somit werden auch Störkräfte auf den Aktor, der im Niederdruckraum angeordnet sein kann, vermieden, die durch solche Druckspitzen hervorgerufen werden können. Dies ist besonders beim Schließen relevant, da beim Schließen durch einen hohen in Schließrichtung wirkenden Kraftstoß der Zusammenhang zwischen der Aktorladung und der Aktorspannung derart gestört werden kann, dass die Spannung auf einen Nullwert gelangt, bei dessen Erreichen der Entladevorgang beendet wird, bevor die beim Entladen aufgebrachte elektrische Ladung wieder vollständig abgeflossen ist. Dies würde zu einem zunächst noch leicht vorgespannten Aktor führen. In der Folge wäre dann nach dem gesteuerten Entladevorgang des Aktors durch das Steuergerät das Schaltventil entweder nicht vollständig geschlossen oder durch Schwingungen des Aktors um seine auf Grund der verbleibenden Restladung noch leicht erhöhte stationäre Lage erneut leicht geöffnet, was einem Schließprellen entspricht. In beiden Fällen könnte es zu einem verlangsamten oder verspäteten Schließen der Düsennadel kommen, so dass sich die tatsächliche Einspritzmenge gegenüber der gewünschten erhöht.Thus, in particular strong hydraulic shift shocks can be avoided both when opening and when closing the switching valve, so that consequently avoid short high pressure peaks in the low pressure space. Thus, disturbing forces on the actuator, which can be arranged in the low-pressure space, avoided, which can be caused by such pressure peaks. This is particularly relevant when closing, since when closing by a high force acting in the closing direction impulse the relationship between the actuator charge and the actuator voltage can be disturbed such that the voltage reaches a zero value, when it reaches the unloading is terminated before the unloading applied electric charge has completely drained again. This would lead to an initially slightly biased actuator. As a result, then, after the controlled discharge of the actuator by the control unit, the switching valve would either not completely closed or slightly opened again due to oscillations of the actuator due to the remaining residual charge stationary position, which corresponds to a closing bounce. In either case, there could be a slowed or delayed closing of the nozzle needle, so that the actual injection quantity increases compared to the desired one.

Somit kann durch die erfindungsgemäße Ausgestaltung des Brennstoffeinspritzventils sowohl die Funktionsweise des Schaltventils günstig beeinflusst werden, da definierte Schaltstellungen zu gewünschten Zeitpunkten eingenommen werden können. Außerdem wird hierdurch auch das Einspritzverhalten, insbesondere ein Einspritzverlauf, des Brennstoffeinspritzventils günstig beeinflusst. Speziell können die vorgegebenen Einspritzzeiten gewährleistet werden.Thus, both the operation of the switching valve can be favorably influenced by the inventive design of the fuel injection valve, since defined switching positions can be taken at desired times. In addition, this also the injection behavior, in particular an injection curve, the fuel injection valve is favorably influenced. Specifically, the predetermined injection times can be guaranteed.

Außerdem ergibt sich bei der herkömmlichen Ausgestaltung der Nachteil, dass mit dem starken Absteuerstoß während der Schaltvorgänge des Ventils jeweils eine nennenswerte Menge Brennstoff direkt vom Hochdruckbereich in den Niederdruckbereich entweicht, ohne dass dieses Brennstoffvolumen zur Funktion des Brennstoffeinspritzventils beiträgt. Die Steuermenge würde dann stets das für die Funktionsweise notwendige Maß übersteigen. Dem kann zwar durch einen gedrosselten Hochdruckkanal begegnet werden. Ein gedrosselter Hochdruckkanal hat aber wiederum einige Nachteile. Denn die Versorgung des die Hülse umgebenden, unter Hochdruck stehenden Ringraums mit Brennstoff müsste dann zwingend durch eine Drosselplatte hindurch und damit vom Düsenmodul her erfolgen. Eine konstruktive Variante, bei der dieser Ringraum direkt, beispielsweise durch einen Kanal an der Unterseite der Ventilplatte versorgt wird, scheidet dann aus.In addition, results in the conventional embodiment of the disadvantage that escapes with the strong Absteuerstoß during the switching operations of the valve in each case a significant amount of fuel directly from the high pressure area in the low pressure area, without this volume of fuel contributes to the function of the fuel injection valve. The amount of tax would then always exceed the amount necessary for the operation. This can be countered by a throttled high-pressure channel. A throttled high pressure channel, however, has some disadvantages. Because the supply of the sleeve surrounding, high-pressure annular space with fuel would then necessarily be carried out through a throttle plate and thus from the nozzle module forth. A constructive variant, in which this annulus is supplied directly, for example, by a channel at the bottom of the valve plate, then exudes.

Die erfindungsgemäße Ausgestaltung ermöglicht somit auch größere Freiheitsgrade bei der konstruktiven Ausgestaltung des Brennstoffeinspritzventils. Speziell muss die Zufuhr des Brennstoffs nicht notwendigerweise durch die Drosselplatte hindurch erfolgen. Der Hochdruckkanal kann somit auch in anderen Gehäuseteilen ausgestaltet werden.The embodiment of the invention thus also allows greater degrees of freedom in the structural design of the fuel injection valve. Specifically, the supply of fuel does not necessarily have to be through the throttle plate. The high pressure channel can thus be configured in other housing parts.

Ein weiterer Nachteil eines gedrosselten Hochdruckkanals besteht darin, dass bei jedem Schaltvorgang des Schaltventils der Druck in dem die Hülse umgebenden Ringraum infolge der nun vorhandenen Drosselung vor diesem Ringraum deutlich unter den Raildruck absinkt. In der Folge entsteht wiederum ein erhöhter Schlupf zwischen der Hülse und der Drosselplatte und damit ein erhöhter Verschleiß an dieser Kontaktstelle. Hierbei kann auch die Dichtwirkung der Kontaktstelle zwischen der Hülse und der Drosselplatte verloren gehen.Another disadvantage of a throttled high-pressure channel is that at each switching operation of the switching valve, the pressure in the annular space surrounding the sleeve drops significantly below the rail pressure as a result of the now existing throttling in front of this annulus. As a result, in turn, an increased slip between the sleeve and the throttle plate and thus increased wear on this contact point arises. In this case, the sealing effect of the contact point between the sleeve and the throttle plate can be lost.

Durch die erfindungsgemäße Ausgestaltung, bei der der Hochdruckkanal in vorteilhafter Weise im Vergleich zu einer Drosselwirkung der Drossel als ungedrosselter Hochdruckkanal ausgestaltet ist, kann der Druck in dem die Hülse umgebenden Ringraum auf einem ausreichend hohen Druckniveau gehalten werden. Ein unerwünscht hoher Verschleiß an der Kontaktstelle zwischen Hülse und Drosselplatte wird hierdurch verhindert. Außerdem wird die gewünschte Dichtwirkung an der Kontaktstelle zwischen Hülse und Drosselplatte zuverlässig gewährleistet.Due to the configuration according to the invention, in which the high-pressure passage is designed in an advantageous manner as an unthrottled high-pressure passage in comparison to a throttling effect of the throttle, the pressure in the annular space surrounding the sleeve can be maintained at a sufficiently high pressure level. An undesirably high wear at the contact point between the sleeve and the throttle plate is thereby prevented. In addition, the desired sealing effect is reliably ensured at the contact point between the sleeve and throttle plate.

Ein wesentlicher Vorteil der Erfindung besteht somit darin, dass ein starker Absteuerstoß beim Schalten des Schaltventils vermieden wird, ohne dass zusätzliche Druckpulsationen in dem die Hülse umgebenden Raum erzeugt werden.A significant advantage of the invention is thus that a strong Absteuerstoss is avoided when switching the switching valve, without additional pressure pulsations are generated in the surrounding space of the sleeve.

Vorteilhaft ist es, dass die Hülse zumindest eine Bohrung aufweist, die von einer Außenseite einer Hülse zu einem Ringspalt zwischen einer Innenseite der Hülse und dem Ventilbolzen führt, und dass der Ventilraum über den Ringspalt und die Bohrung in der Hülse mit dem Hochdruckkanal verbindbar ist. Hierbei ist es ferner vorteilhaft, dass die Bohrung als Drosselbohrung ausgestaltet ist. Die Bohrung bildet hierdurch eine gedrosselte Durchtrittsbohrung für den Brennstoff. Hierbei ist zumindest eine Drosselbohrung vorgesehen. Es können allerdings auch mehrere Drosselbohrungen vorgesehen sein.It is advantageous that the sleeve has at least one bore, which leads from an outer side of a sleeve to an annular gap between an inner side of the sleeve and the valve pin, and that the valve space via the annular gap and the bore in the sleeve with the high-pressure channel is connectable. Here, it is also advantageous that the bore is designed as a throttle bore. The bore thereby forms a throttled passage for the fuel. Here, at least one throttle bore is provided. However, it can also be provided several throttle bores.

Möglich ist es allerdings auch, dass die Bohrung als ungedrosselte Bohrung ausgestaltet ist. Unter einer ungedrosselten Bohrung ist hierbei eine Bohrung zu verstehen, die im Vergleich zu anderen Drosselstellen höchstens eine vergleichsweise geringe Drosselwirkung hat. Hierbei ist es ferner vorteilhaft, dass der Ventilbolzen und/oder die Hülse so ausgestaltet sind, dass sich der Ringspalt zwischen der Innenseite der Hülse und dem Ventilbolzen entlang einer Achse des Ventilbolzen zumindest im Wesentlichen von dem Dichtsitz zwischen der Hülse und dem Ventilbolzen bis zu der Mündungsöffnung erstreckt und dass der Ringspalt zumindest im Bereich der Mündungsöffnung eine gewisse, radiale Ringspalthöhe aufweist. Hierdurch kann an der Umlenkstelle an der Mündungsöffnung eine Drosselstelle gebildet werden. Somit kann die Drossel in vorteilhafter Weise an der Umlenkstelle der Mündungsöffnung der Bohrung gebildet sein, wobei die Querschnittsfläche der Drossel zumindest näherungsweise durch ein Produkt mit einem Multiplikator, der gleich dem Austrittsumfang der Mündungsöffnung der Bohrung ist, und einem Multiplikand, der gleich der radialen Ringspalthöhe des Ringspalts im Bereich der Mündungsöffnung ist, gegeben ist. Somit kann die Drosselwirkung gezielt eingestellt werden. Dabei kann die Bohrung als durchgängige Bohrung mit einheitlichem Durchmesser oder auch als Stufenbohrung mit über die Länge veränderlichem Durchmesser ausgeführt sein.It is also possible, however, that the bore is designed as unthrottled bore. Under an unthrottled bore is in this case a bore to understand that has at most a comparatively small throttle effect compared to other throttle points. In this case, it is further advantageous that the valve pin and / or the sleeve are configured so that the annular gap between the inside of the sleeve and the valve pin along an axis of the valve pin at least substantially from the sealing seat between the sleeve and the valve pin to the Mouth opening extends and that the annular gap, at least in the region of the mouth opening has a certain radial annular gap height. As a result, a throttle point can be formed at the deflection point at the mouth opening. Thus, the throttle may advantageously be formed at the deflection of the mouth of the bore, wherein the cross-sectional area of the throttle at least approximately by a product having a multiplier which is equal to the outlet circumference of the mouth of the bore, and a multiplicand equal to the radial annular gap height of the annular gap in the region of the mouth opening is given. Thus, the throttle effect can be adjusted specifically. In this case, the bore can be designed as a continuous bore with a uniform diameter or as a stepped bore with variable over the length diameter.

Vorteilhaft ist es auch, dass die Bohrung in der Hülse als radial orientierte Bohrung ausgestaltet ist. Hierdurch können die Herstellungskosten optimiert werden.It is also advantageous that the bore in the sleeve is designed as a radially oriented bore. As a result, the production costs can be optimized.

Andererseits ist es auch vorteilhaft, dass die Bohrung in der Hülse schräg in der Hülse ausgestaltet ist. Hierdurch ist eine strömungstechnische Optimierung möglich.On the other hand, it is also advantageous that the bore in the sleeve is configured obliquely in the sleeve. As a result, a flow optimization is possible.

Vorteilhaft ist es auch, dass die Hülse mehrere Bohrungen aufweist, die von einer Außenseite der Hülse zu einem Ringspalt zwischen der Innenseite der Hülse und dem Ventilbolzen führen und dass der Ventilraum über den Ringspalt und die Bohrungen in der Hülse mit dem Hochdruckkanal verbindbar ist. Die Verbindung kommt hierbei entsprechend der Schaltstellung des Schaltventils zustande. Hierbei ist es speziell von Vorteil, dass die Bohrungen bezüglich einer Achse des Ventilbolzens umfänglich verteilt in der Hülse ausgestaltet sind. Hierdurch kann erreicht werden, dass sich die auf Grund der Strömung ergebenden Kräfte, die auf die Hülse einwirken, zumindest teilweise kompensieren. Dadurch kann das Entstehen von Querkräften auf die Hülse infolge der Drosselung beim Umlenken des Brennstoffs am jeweiligen Bohrungsaustritt reduziert oder ganz vermieden werden. Die Bohrungen können hierbei nicht nur über die Höhe, das heißt axial, sondern auch über den Umfang der Hülse, das heißt azimutal, verteilt sein. Im Fall mehrerer Bohrungen können diese einen einheitlichen Austrittsdurchmesser oder aber auch unterschiedliche Austrittsdurchmesser aufweisen. Für eine Kraftkompensation ist es hierbei vorteilhaft, dass die Mündungsöffnungen der Bohrungen, an denen die Bohrungen in den Ringspalt zwischen der Innenseite der Hülse und den Ventilbolzen münden, zumindest näherungsweise den gleichen Austrittsquerschnitt, insbesondere Austrittsdurchmesser, aufweisen.It is also advantageous that the sleeve has a plurality of bores, which lead from an outer side of the sleeve to an annular gap between the inside of the sleeve and the valve pin and that the valve chamber via the annular gap and the holes in the sleeve with the high-pressure channel is connectable. The connection is made according to the switching position of the switching valve. In this case, it is particularly advantageous that the bores are configured circumferentially distributed in the sleeve with respect to an axis of the valve pin. In this way it can be achieved that the forces resulting from the flow, which act on the sleeve, at least partially compensate. As a result, the development of lateral forces on the sleeve as a result of throttling during deflection of the fuel at the respective bore outlet can be reduced or avoided altogether. The holes can be distributed not only over the height, that is axially, but also over the circumference of the sleeve, that is, azimuthally. In the case of several holes, these can have a uniform exit diameter or else different exit diameters. For a force compensation, it is advantageous in this case that the mouth openings of the bores, at which the holes open into the annular gap between the inside of the sleeve and the valve pin, at least approximately the same outlet cross-section, in particular outlet diameter.

Kurze Beschreibung der ZeichnungenBrief description of the drawings

Bevorzugte Ausführungsbeispiele der Erfindung sind in der nachfolgenden Beschreibung unter Bezugnahme auf die beigefügten Zeichnungen, in denen sich entsprechende Elemente mit übereinstimmenden Bezugszeichen versehen sind, näher erläutert. Es zeigt:

  • Fig. 1 ein Brennstoffeinspritzventil in einer auszugsweisen, schematischen Schnittdarstellung entsprechend einem ersten Ausführungsbeispiel der Erfindung und
  • Fig. 2 ein Brennstoffeinspritzventil in einer auszugsweisen, schematischen Schnittdarstellung entsprechend einem zweiten Ausführungsbeispiel der Erfindung.
Preferred embodiments of the invention are explained in more detail in the following description with reference to the accompanying drawings, in which corresponding elements are provided with identical reference numerals. It shows:
  • Fig. 1 a fuel injection valve in a partial, schematic sectional view according to a first embodiment of the invention and
  • Fig. 2 a fuel injection valve in a partial, schematic sectional view according to a second embodiment of the invention.

Ausführungsformen der ErfindungEmbodiments of the invention

Fig. 1 zeigt ein erstes Ausführungsbeispiel eines Brennstoffeinspritzventils 1 der Erfindung in einer schematischen, auszugsweisen Schnittdarstellung. Das Brennstoffeinspritzventil 1 kann insbesondere als Injektor für Brennstoffeinspritzanlagen von luftverdichtenden, selbstzündenden Brennkraftmaschinen dienen. Ein bevorzugter Einsatz des Brennstoffeinspritzventils 1 besteht für eine Brennstoffeinspritzanlage mit einem Common-Rail, das Dieselbrennstoff unter hohem Druck speichert und auf mehrere Brennstoffeinspritzventile 1 aufteilt. Das erfindungsgemäße Brennstoffeinspritzventil 1 eignet sich jedoch auch für andere Anwendungsfälle. Fig. 1 shows a first embodiment of a fuel injection valve 1 of the invention in a schematic, partial sectional view. The fuel injection valve 1 can be used in particular as an injector for fuel injection systems of air-compressing, self-igniting internal combustion engines. A preferred use of the fuel injection valve 1 is for a fuel injection system with a common rail that stores diesel fuel under high pressure and divides it into several fuel injection valves 1. However, the fuel injection valve 1 according to the invention is also suitable for other applications.

Das Brennstoffeinspritzventil 1 weist eine Sitzplatte 2, eine Ventilplatte 3 und eine Drosselplatte 4 auf. Hierbei ist im Bereich der Ventilplatte 3 ein Schaltventil 5 ausgestaltet. Das Schaltventil 5 weist einen Raum 6 auf, der in der Ventilplatte 3 ausgestaltet ist. Der Raum 6 kann hierbei durch eine Bohrung in der Ventilplatte 3 ausgestaltet sein. In dem Raum 6 sind eine Hülse 7 und ein Ventilbolzen 8 angeordnet. Der Ventilbolzen 8 ist hierbei in der Hülse 7 geführt.The fuel injection valve 1 has a seat plate 2, a valve plate 3 and a throttle plate 4. Here, in the region of the valve plate 3, a switching valve 5 is configured. The switching valve 5 has a space 6 which is configured in the valve plate 3. The space 6 may in this case be configured by a bore in the valve plate 3. In the space 6, a sleeve 7 and a valve pin 8 are arranged. The valve pin 8 is guided in this case in the sleeve 7.

In dem Raum 6, in dem die Hülse 7 und der Ventilbolzen 8 angeordnet sind, verbleibt unter anderem ein Ventilraum 9, der als ringförmiger Ventilraum 9 ausgestaltet ist. An dem Ventilbolzen 8 ist gewissermaßen ein beidseitig wirkender Ventilschließkörper 10 ausgebildet, um den sich umfänglich der Ventilraum 9 erstreckt.In the space 6, in which the sleeve 7 and the valve pin 8 are arranged, remains, inter alia, a valve chamber 9, which is designed as an annular valve chamber 9. On the valve pin 8 a double-acting valve closing body 10 is formed, so to speak, around which the valve chamber 9 extends circumferentially.

Hierbei ist einerseits zwischen dem Ventilschließkörper 10 des Ventilbolzens 8 und der Sitzplatte 2 ein Dichtsitz 11 gebildet, der den Ventilraum 9 von einem Niederdruckbereich 12 trennt. Beispielsweise kann ein Niederdruckraum 13 vorgesehen sein, in dem ein Aktor 14 zum Betätigen des Ventilbolzens 8 angeordnet ist. Der Niederdruckbereich 12 ist hierbei durch den Niederdruckraum 13 gewährleistet. Der Niederdruckbereich 12 kann beispielsweise mit einem Tank verbunden sein.Here, on the one hand between the valve closure member 10 of the valve pin 8 and the seat plate 2, a sealing seat 11 is formed, which separates the valve chamber 9 from a low pressure region 12. For example, a low-pressure space 13 may be provided, in which an actuator 14 is arranged for actuating the valve pin 8. The low-pressure region 12 is ensured here by the low-pressure space 13. The low-pressure region 12 may be connected to a tank, for example.

Außerdem bildet der Ventilschließkörper 10 des Ventilschließbolzens 8 mit der Hülse 7 einen Dichtsitz 15. Hierbei wird bei einer Betätigung des Ventilbolzens 8 mittels des Aktors 14 der Dichtsitz 11 geöffnet und zugleich der Dichtsitz 15 geschlossen. Somit kommt es je nach Schaltstellung des Schaltventils 5 zum wechselweisen Öffnen und Schließen der Dichtsitze 11, 15.In addition, the valve closing body 10 of the valve closing bolt 8 with the sleeve 7 forms a sealing seat 15. In this case, upon actuation of the valve pin 8 by means of the actuator 14, the sealing seat 11 is opened and at the same time the sealing seat 15 is closed. Thus, depending on the switching position of the switching valve 5 for the alternate opening and closing of the sealing seats 11, 15th

In der Drosselplatte 4 ist ein Hochdruckkanal 16 ausgebildet. Der Hochdruckkanal 16 ist hierbei als ungedrosselter Hochdruckkanal 16 ausgestaltet. Der Hochdruckkanal 16 führt unter hohem Druck stehenden Brennstoff in einen Ringraum 17, zwischen einer Außenseite 20 der Hülse 7 und einer Innenwand 21 der Ventilplatte 3, die den Raum 6 begrenzt. Somit befindet sich im Betrieb unter hohem Druck stehender Brennstoff im Ringraum 17 zwischen der Hülse 7 und der Innenwand 21 der Ventilplatte 3. Unter dem Ventilbolzen 8 befindet sich in der Drosselplatte 4 ein Niederdruckraum 22, der beispielsweise mit dem Niederdruckraum 13 verbunden ist. Im oberen Bereich ihres Außendurchmessers ist die Hülse 7 in die Ventilplatte 3 eingepresst, wodurch der Ringraum 17 und der Ventilraum 9 hydraulisch voneinander getrennt werden.In the throttle plate 4, a high pressure passage 16 is formed. The high-pressure passage 16 is designed here as an unthrottled high-pressure passage 16. The high-pressure passage 16 leads fuel under high pressure into an annular space 17, between an outer side 20 of the sleeve 7 and an inner wall 21 of the valve plate 3, which delimits the space 6. Thus, in operation under high pressure fuel in the annular space 17 between the sleeve 7 and the inner wall 21 of the valve plate 3. Under the valve pin 8 is located in the throttle plate 4, a low pressure chamber 22 which is connected, for example, with the low-pressure chamber 13. In the upper region of its outer diameter, the sleeve 7 is pressed into the valve plate 3, whereby the annular space 17 and the valve chamber 9 are hydraulically separated from each other.

Im Bereich der Führung zwischen dem Ventilbolzen 8 und der Hülse 7 ist eine Drossel 23 vorgesehen, die in diesem Ausführungsbeispiel durch eine Drosselbohrung 23 gebildet ist. Die Drosselbohrung 23 erstreckt sich hierbei bezüglich einer Achse 24 des Ventilbolzens 8 radial durch die Hülse 7. Die Drosselbohrung 23 führt von der Außenseite 20 der Hülse 7 zu einem Ringspalt 25 zwischen einer Innenseite 26 der Hülse 7 und dem Ventilbolzen 8. Bei geöffnetem Dichtsitz 15 ist somit der Ventilraum 9 über den Ringspalt 25 und die Drosselbohrung 23 sowie den Ringraum 17 mit dem Hochdruckkanal 16 verbunden. Der Hochdruckkanal 16 muss sich hierbei nicht notwendigerweise durch die Drosselplatte 4 erstrecken. Beispielsweise kann der Hochdruckkanal 16 auch in der Ventilplatte 3 ausgestaltet sein.In the region of the guide between the valve pin 8 and the sleeve 7, a throttle 23 is provided, which is formed in this embodiment by a throttle bore 23. The throttle bore 23 extends in this case with respect to an axis 24 of the valve pin 8 radially through the sleeve 7. The throttle bore 23 leads from the outer side 20 of the sleeve 7 to an annular gap 25 between an inner side 26 of the sleeve 7 and the valve pin 8. When the sealing seat 15 is open Thus, the valve chamber 9 is connected via the annular gap 25 and the throttle bore 23 and the annular space 17 with the high pressure passage 16. The high-pressure passage 16 does not necessarily have to extend through the throttle plate 4. For example, the high-pressure passage 16 can also be configured in the valve plate 3.

Beim Betätigen des Schaltventils 5 mittels des Aktors 14 wird der Dichtsitz 11 geöffnet und gleichzeitig der Dichtsitz 15 geschlossen. Somit strömt in den Ventilraum 9 unter hohem Druck stehender Brennstoff. Da die Drossel 23 in Bezug auf den strömungstechnischen Abstand zwischen dem Dichtsitz 15 und dem Hochdruckkanal 16 relativ nahe an dem Dichtsitz 15 angeordnet ist, wird beim Zurückschalten des Schaltventils 5 in die in der Fig. 1 dargestellte Ausgangsstellung die Steuermenge weitestgehend auf das notwendige Maß begrenzt und das Auftreten eines starken Absteuerstoßes während des Schaltvorgangs vermieden.Upon actuation of the switching valve 5 by means of the actuator 14, the sealing seat 11 is opened and at the same time the sealing seat 15 is closed. Thus flows in the valve chamber 9 under high pressure fuel. Since the throttle 23 is arranged relative to the fluidic distance between the sealing seat 15 and the high-pressure passage 16 relatively close to the sealing seat 15, when switching back the switching valve 5 in the in the Fig. 1 illustrated starting position, the control amount largely limited to the necessary extent and the occurrence of a strong Absteuerstoßes avoided during the switching process.

Das Brennstoffeinspritzventil 1 weist eine Düsennadel 27 auf, die an ihrem Ende von einer Dichthülse 28 umschlossen ist. Die Dichthülse 28 stützt sich hierbei an der Drosselplatte 4 ab, so dass ein Steuerraum 29 zwischen der Düsennadel 27, der Dichthülse 28 und der Drosselplatte 4 ausgebildet ist. Über den Druck des Brennstoffs im Steuerraum 29 kann die Düsennadel 27 betätigt werden. Der Steuerraum 29 ist über eine Ablaufdrossel 30, die in der Drosselplatte 4 ausgestaltet ist, und einen Verbindungskanal 31, der in der Ventilplatte 3 ausgestaltet ist, sowie eine Vertiefung 32, die in der Sitzplatte 2 ausgestaltet ist, mit dem Ventilraum 9 verbunden. Die Vertiefung 32 in der Sitzplatte 2 kann dabei, wie in Fig. 1 dargestellt, umlaufend um den Ventilsitz gestaltet sein, so dass die Hülse durch den im Ventilraum 9 anstehenden Druck stets mit einer in Richtung der Drosselplatte 4 gerichteten Axialkraft beaufschlagt ist und so niedergehalten wird. Die Vertiefung 32 in der Sitzplatte 2 kann alternativ auch nicht umlaufend um den Ventilsitz ausgestaltet sein, so dass die Hülse 7 zwischen der Sitzplatte 2 und der Drosselplatte 4 mechanisch geklemmt und so axial fixiert wird. Über den Druck im Ventilraum 9 wird somit der Druck im Steuerraum 29 beeinflusst. Wird der Dichtsitz 11 geöffnet, dann fällt somit auch der Druck im Steuerraum 29 ab. Wird andererseits der Dichtsitz 11 geschlossen und somit der Dichtsitz 15 geöffnet, dann steigt der Druck im Steuerraum 29 durch Nachfließen von Brennstoff über eine Zulaufdrossel 33 an. Die Zulaufdrossel 33 ist zur Vereinfachung der Darstellung hierbei schematisch als Bohrung in der Dichthülse 38 dargestellt. Die Schließgeschwindigkeit der Düsennadel 27 wird hierbei allerdings weiter erhöht, da unter hohem Druck stehender Brennstoff auch rückwärts durch die Ablaufdrossel 30 fließt, da zugleich unter hohem Druck stehender Brennstoff aus dem Hochdruckkanal 16 in den Ventilraum 9 gelangt.The fuel injection valve 1 has a nozzle needle 27, which is enclosed at its end by a sealing sleeve 28. The sealing sleeve 28 is supported here on the throttle plate 4, so that a control chamber 29 between the nozzle needle 27, the sealing sleeve 28 and the throttle plate 4 is formed. About the pressure of the fuel in the control chamber 29, the nozzle needle 27 can be actuated. The control chamber 29 is connected to the valve space 9 via an outlet throttle 30, which is configured in the throttle plate 4, and a connecting channel 31, which is configured in the valve plate 3, and a recess 32, which is configured in the seat plate 2. The recess 32 in the seat plate 2 can, as in Fig. 1 shown, circumferentially designed around the valve seat, so that the sleeve is always acted upon by the pending in the valve chamber 9 pressure with a directed in the direction of the throttle plate 4 axial force and is held down. The recess 32 in the seat plate 2 may alternatively not be configured circumferentially around the valve seat, so that the sleeve 7 between the seat plate 2 and the throttle plate 4 mechanically clamped and so axially is fixed. The pressure in the control chamber 29 is thus influenced by the pressure in the valve chamber 9. If the sealing seat 11 is opened, then the pressure in the control chamber 29 also drops. If, on the other hand, the sealing seat 11 is closed and thus the sealing seat 15 is opened, then the pressure in the control chamber 29 rises due to the subsequent flow of fuel through an inlet throttle 33. The inlet throttle 33 is shown schematically as a bore in the sealing sleeve 38 for ease of illustration. The closing speed of the nozzle needle 27 is here, however, further increased because under high pressure fuel also flows backwards through the outlet throttle 30, since at the same time high-pressure fuel from the high-pressure passage 16 enters the valve chamber 9.

Somit ist in diesem Ausführungsbeispiel mindestens eine Durchtrittsbohrung 23 durch die Hülse 7 vorgesehen, die als Drossel 23 ausgeführt ist. Das Brennstoffvolumen zwischen der Drosselstelle 23 und dem Dichtsitz 15 kann hierbei sehr klein gehalten werden, so dass die Steuermenge weitestgehend auf das notwendige Maß begrenzt ist. Der Hochdruckkanal 16 kann durch eine einfache Bohrung ausgestaltet werden, durch die der Brennstoff ohne wesentliche Drosselwirkung geführt wird. Das heißt, die Drosselwirkung des Hochdruckkanals 16 ist im Vergleich zur Drosselwirkung der Drosselbohrung 23 gering. Somit erfolgt die Drosselung erst stromabwärts gesehen vom Ringraum 17, so dass im Ringraum 17 stets der Hochdruck, insbesondere der Raildruck, beziehungsweise der Druck am Zulauf zu einer Düse des Brennstoffeinspritzventils 1 herrscht.Thus, in this embodiment, at least one passage bore 23 is provided through the sleeve 7, which is designed as a throttle 23. The fuel volume between the throttle point 23 and the sealing seat 15 can be kept very small, so that the control amount is largely limited to the necessary extent. The high-pressure passage 16 can be configured by a simple bore, through which the fuel is conducted without significant throttle effect. That is, the throttle effect of the high-pressure passage 16 is small in comparison with the throttling action of the throttle bore 23. Thus, the throttling takes place only downstream seen from the annular space 17, so that in the annular space 17 always the high pressure, in particular the rail pressure, or the pressure prevails at the inlet to a nozzle of the fuel injection valve 1.

Statt einer Drosselbohrung 23 können auch mehrere Drosselbohrungen 23 in der Hülse 7 vorgesehen sein, welche mehrere Verbindungen zwischen dem Ringraum 17 und dem Dichtsitz 15 des Schaltventils 5 herstellen. Dadurch kann das Entstehen von Querkräften auf die Hülse 7 in Folge der Drosselung bei Durchtritt des Brennstoffs durch die einzelnen Drosselbohrungen 23 der Hülse 7 reduziert oder ganz vermieden werden. Die Drosselbohrungen 23, die insbesondere als Querbohrungen ausgestaltet sind, können hierbei über die Höhe, das heißt entlang der Achse 24, als auch bezüglich der Achse 24 über den Umfang der Hülse 7, das heißt azimutal, verteilt sein.Instead of a throttle bore 23 and a plurality of throttle bores 23 may be provided in the sleeve 7, which produce a plurality of connections between the annular space 17 and the sealing seat 15 of the switching valve 5. As a result, the emergence of lateral forces on the sleeve 7 as a result of the throttling upon passage of the fuel through the individual throttle bores 23 of the sleeve 7 can be reduced or avoided altogether. The throttle bores 23, which are designed in particular as transverse bores, can be distributed over the height, that is to say along the axis 24, as well as with respect to the axis 24 over the circumference of the sleeve 7, that is to say azimuthally.

Die Drosselbohrung 23 ist in diesem Ausführungsbeispiel radial verlaufend ausgestaltet. Die Drosselbohrung 23 beziehungsweise die mehreren Drosselbohrungen 23 können aber auch beliebig schräg in der Hülse 7 verlaufen. Der Hochdruckkanal 16 kann auch weiter stromaufwärts von der Drosselplatte 4 aus betrachtet in den Ringraum 17 münden.The throttle bore 23 is designed to extend radially in this embodiment. But the throttle bore 23 and the plurality of throttle bores 23 may also run as desired obliquely in the sleeve 7. The high-pressure passage 16 can also open further upstream of the throttle plate 4 from open into the annular space 17.

Fig. 2 zeigt ein Brennstoffeinspritzventil 1 in einer auszugsweisen, schematischen Schnittdarstellung entsprechend einem zweiten Ausführungsbeispiel der Erfindung. In diesem Ausführungsbeispiel ist eine Bohrung 23' in der Hülse 7 vorgesehen, die als ungedrosselte Bohrung 23' ausgestaltet ist. Allerdings weist die Bohrung 23' eine Mündungsöffnung 40 auf, an der die Bohrung 23' einen definierten Austrittsquerschnitt aufweist. Die Bohrung 23' mündet hierbei in einen Ringspalt 25, der definiert vorgegebene Abmessungen hat. Hierbei sind der Ventilbolzen 8 und/oder die Hülse 7 so ausgestaltet, dass sich der Ringspalt 25 zwischen der Innenseite 26 der Hülse 7 und dem Ventilbolzen 8 entlang der Achse 24 des Ventilbolzens 8 von dem Dichtsitz 15 zwischen der Hülse 7 und dem Ventilbolzen 8 bis zu der Mündungsöffnung 40 und vorzugsweise etwas weiter mit einer gewissen, radialen Ringspalthöhe hB erstreckt. Die radiale Ringspalthöhe hB wird hierbei radial bezüglich der Achse 24 des Ventilbolzens 8 gemessen beziehungsweise bestimmt. An der Mündungsöffnung 40 ergibt sich eine strömungstechnische Umlenkstelle 41 von der Bohrung 23' in den Ringspalt 25. Die Querschnittsfläche der hierdurch gebildeten Drossel 42, die sich aus der Bohrung 23' mit der Mündungsöffnung 40 und dem Ringspalt 25 zusammensetzt, ergibt sich zumindest näherungsweise durch ein Produkt mit einem Multiplikator, der gleich dem Austrittsumfang der Mündungsöffnung 40 der Bohrung 23' ist, und einem Multiplikand, der gleich der radialen Ringspalthöhe hB des Ringspalts 25 ist. Wenn die Mündungsöffnung 40 einen Durchmesser d hat, dann ergibt sich der Austrittquerschnitt entsprechend dem durch den Durchmesser d gegebenen Austrittsumfang und der Spalthöhe hB. Die Bohrung 23' kann dabei als durchgängige Bohrung mit einheitlichem Durchmesser oder auch als Stufenbohrung mit über die Länge veränderlichem Durchmesser ausgeführt sein. Fig. 2 shows a fuel injection valve 1 in a partial, schematic sectional view according to a second embodiment of the invention. In this embodiment, a bore 23 'is provided in the sleeve 7, as unthrottled bore 23 'is configured. However, the bore 23 'has an orifice 40, on which the bore 23' has a defined outlet cross-section. The bore 23 'opens into an annular gap 25, which has defined predetermined dimensions. Here, the valve pin 8 and / or the sleeve 7 are designed so that the annular gap 25 between the inner side 26 of the sleeve 7 and the valve pin 8 along the axis 24 of the valve pin 8 of the sealing seat 15 between the sleeve 7 and the valve pin 8 to extends to the orifice 40 and preferably slightly further with a certain, radial annular gap height h B. The radial annular gap height h B is in this case measured or determined radially with respect to the axis 24 of the valve pin 8. At the mouth opening 40 results in a fluidic deflection point 41 of the bore 23 'in the annular gap 25. The cross-sectional area of the throttle 42 formed thereby, which is composed of the bore 23' with the orifice 40 and the annular gap 25, at least approximately by a product having a multiplier equal to the exit circumference of the orifice 40 of the bore 23 'and a multiplicand equal to the radial annular gap height h B of the annular gap 25. If the orifice 40 has a diameter d, then the outlet cross-section results according to the exit circumference given by the diameter d and the gap height h B. The bore 23 'can be designed as a continuous bore with a uniform diameter or as a stepped bore with variable over the length diameter.

Wenn mehrere Bohrungen 23' vorgesehen sind, dann weisen diese vorzugsweise sich entsprechende Mündungsöffnungen 40 mit gleichen Austrittsdurchmessern auf. Werden diese Querbohrungen gleichmäßig über den Umfang verteilt, dann kann eine gegenseitige Kompensation bezüglich der resultierenden, auf die Hülse 7 wirkenden Querkraft erzielt werden. Auch eine Verteilung über die Höhe ist möglich.If a plurality of holes 23 'are provided, then these preferably have corresponding orifices 40 with the same outlet diameters. If these transverse bores are distributed uniformly over the circumference, mutual compensation can be achieved with respect to the resulting transverse force acting on the sleeve 7. Also a distribution over the height is possible.

Sowohl die Außenkontur des Ventilbolzens 8 im Bereich der Mündungsöffnung 40 als auch die Innenseite 26 der Hülse 7 im Bereich der Mündungsöffnung 40 können exakt oder zumindest näherungsweise zylindrisch ausgeführt sein. Es sind aber auch beliebige andere, vorzugsweise rotationssymmetrische Konturen möglich.Both the outer contour of the valve pin 8 in the region of the mouth opening 40 and the inner side 26 of the sleeve 7 in the region of the mouth opening 40 can be designed exactly or at least approximately cylindrically. But there are also any other, preferably rotationally symmetric contours possible.

In den beschriebenen Ausführungsbeispielen der Fig. 1 und 2 ist der Ringspalt 25 durch abschnittsweises Verringern eines Durchmessers 45 des Ventilbolzens 8 ausgestaltet. Zusätzlich oder alternativ kann jedoch auch ein Innendurchmesser 45 der Hülse 7 abschnittsweise größer ausgestaltet sein, um den Ringspalt 25 abschnittsweise auszugestalten.In the described embodiments of the Fig. 1 and 2 the annular gap 25 is configured by reducing a diameter 45 of the valve pin 8 in sections. In addition or as an alternative, however, an inner diameter 45 of the sleeve 7 can also be made larger in sections in order to form the annular gap 25 in sections.

Die Erfindung ist nicht auf die beschriebenen Ausführungsbeispiele beschränkt.The invention is not limited to the described embodiments.

Claims (13)

Brennstoffeinspritzventil (1), insbesondere Injektor für Brennstoffeinspritzanlagen von luftverdichtenden, selbstzündenden Brennkraftmaschinen, mit einem Schaltventil (5), einem Verbindungskanal (31), der aus einem Steuerraum (29) in einen Ventilraum (9) des Schaltventils (5) führt, und einem Hochdruckkanal (16), wobei je nach Schaltstellung des Schaltventils (5) der Ventilraum (9) mit einem Niederdruckbereich (12) oder zumindest mittelbar mit dem Hochdruckkanal (16) verbindbar ist,
dadurch gekennzeichnet,
dass das Schaltventil (5) eine Hülse (7) und einen in der Hülse (7) geführten Ventilbolzen (8) aufweist, dass zwischen der Hülse (7) und dem Ventilbolzen (8) ein Dichtsitz (15) gebildet ist, über den die Verbindung des Ventilraums (9) mit dem Hochdruckkanal (16) steuerbar ist, und dass im Bereich der Führung zwischen dem Ventilbolzen (8) und der Hülse (7) zumindest eine Drossel (23, 42) ausgestaltet ist, über die der Ventilraum (9) mit dem Hochdruckkanal (16) verbindbar ist.Fuel injection valve (1), in particular injector for fuel injection systems of air-compressing, self-igniting internal combustion engines, with a switching valve (5), a connecting channel (31) leading from a control chamber (29) in a valve chamber (9) of the switching valve (5), and a High-pressure passage (16), wherein depending on the switching position of the switching valve (5), the valve chamber (9) with a low-pressure region (12) or at least indirectly connectable to the high pressure passage (16),
characterized,
in that the switching valve (5) has a sleeve (7) and a valve pin (8) guided in the sleeve (7), that a sealing seat (15) is formed between the sleeve (7) and the valve pin (8), over which the Connection of the valve chamber (9) with the high pressure passage (16) is controllable, and that in the region of the guide between the valve pin (8) and the sleeve (7) at least one throttle (23, 42) is configured, via which the valve space (9 ) is connectable to the high pressure passage (16). Brennstoffeinspritzventil nach Anspruch 1,
dadurch gekennzeichnet,
dass der Hochdruckkanal (16) im Vergleich zu einer Drosselwirkung der Drossel (23, 42) als ungedrosselter Hochdruckkanal (16) ausgestaltet ist.Fuel injection valve according to claim 1,
characterized,
that the high-pressure channel (16) in comparison to a throttling effect of the throttle (23, 42) as unthrottled high pressure passage (16) is arranged. Brennstoffeinspritzventil nach Anspruch 1 oder 2,
dadurch gekennzeichnet,
dass die Hülse (7) zumindest eine Bohrung (23, 23') aufweist, die von einer Außenseite (20) der Hülse (7) zu einem Ringspalt (25) zwischen einer Innenseite (26) der Hülse (7) und dem Ventilbolzen (8) führt, und dass der Ventilraum (9) über den Ringspalt (25) und die Bohrung (23, 23') in der Hülse (7) mit dem Hochdruckkanal (16) verbindbar ist.Fuel injection valve according to claim 1 or 2,
characterized,
in that the sleeve (7) has at least one bore (23, 23 ') which extends from an outer side (20) of the sleeve (7) to an annular gap (25) between an inner side (26) of the sleeve (7) and the valve pin (7). 8) leads, and that the valve chamber (9) via the annular gap (25) and the bore (23, 23 ') in the sleeve (7) with the high pressure passage (16) is connectable. Brennstoffeinspritzventil nach Anspruch 3,
dadurch gekennzeichnet,
dass die Bohrung (23) als Drosselbohrung (23) ausgestaltet ist.Fuel injection valve according to claim 3,
characterized,
that the bore (23) is designed as a throttle bore (23). Brennstoffeinspritzventil nach Anspruch 3,
dadurch gekennzeichnet,
dass eine Mündungsöffnung (40) der Bohrung (23'), an der die Bohrung (23') in den Ringspalt (25) zwischen der Innenseite (26) der Hülse (7) und dem Ventilbolzen (8) mündet, einen definierten Austrittsdurchmesser (d) aufweist.Fuel injection valve according to claim 3,
characterized,
that an opening (40) of the bore (23 ') to which the bore (23') in the annular gap (25) between the inside (26) of the sleeve (7) and the valve pin (8) opens, (a defined outlet diameter d). Brennstoffeinspritzventil nach Anspruch 5,
dadurch gekennzeichnet,
dass der Ventilbolzen (8) und/oder die Hülse (7) so ausgestaltet sind, dass sich der Ringspalt (25) zwischen der Innenseite (26) der Hülse (7) und dem Ventilbolzen (8) entlang einer Achse (24) des Ventilbolzens (8) zumindest im Wesentlichen von dem Dichtsitz (15) zwischen der Hülse (7) und dem Ventilbolzen (8) bis zu der Mündungsöffnung (40) erstreckt und dass der Ringspalt (25) zumindest im Bereich der Mündungsöffnung (40) eine gewisse, radiale Ringspalthöhe (hB) aufweist.Fuel injection valve according to claim 5,
characterized,
in that the valve pin (8) and / or the sleeve (7) are designed so that the annular gap (25) between the inside (26) of the sleeve (7) and the valve pin (8) along an axis (24) of the valve pin (8) extends at least substantially from the sealing seat (15) between the sleeve (7) and the valve pin (8) to the mouth opening (40) and that the annular gap (25) at least in the region of the mouth opening (40) has a certain radial annular gap height (h B ) has. Brennstoffeinspritzventil nach Anspruch 6,
dadurch gekennzeichnet,
dass die Drossel (42) an einer Umlenkstelle (41) der Mündungsöffnung (40) der Bohrung (23') gebildet ist, wobei die Querschnittsfläche der Drossel (42) zumindest näherungsweise durch ein Produkt mit einem Multiplikator, der gleich dem Austrittsumfang der Mündungsöffnung (40) der Bohrung (23') ist, und einem Multiplikand, der gleich der radialen Ringspalthöhe (hB) des Ringspalts (25) im Bereich der Mündungsöffnung (40) ist, gegeben ist.Fuel injection valve according to claim 6,
characterized,
that the throttle (42) at a deflection point (41) of the mouth opening (40) is formed of the bore (23 '), wherein the cross-sectional area of the throttle (42) at least approximately by a product with a multiplier that is equal to (the exit periphery of the mouth opening 40) of the bore (23 '), and a multiplicand equal to the radial annular gap height (h B ) of the annular gap (25) in the region of the mouth opening (40) is given. Brennstoffeinspritzventil nach einem der Ansprüche 3 bis 7,
dadurch gekennzeichnet,
dass die Bohrung (23, 23') in der Hülse (7) als radial orientierte Bohrung (23, 23') ausgestaltet ist.Fuel injection valve according to one of claims 3 to 7,
characterized,
that the bore (23, 23 ') in the sleeve (7) as a radially oriented bore (23, 23') is arranged. Brennstoffeinspritzventil nach einem der Ansprüche 3 bis 7,
dadurch gekennzeichnet,
dass die Bohrung (23, 23') in der Hülse (7) schräg in der Hülse (7) ausgestaltet ist.Fuel injection valve according to one of claims 3 to 7,
characterized,
that the bore (23, 23 ') in the sleeve (7) obliquely in the sleeve (7) is designed. Brennstoffeinspritzventil nach einem der Ansprüche 1 bis 9,
dadurch gekennzeichnet,
dass die Hülse (7) mehrere Bohrungen (23, 23') aufweist, die von einer Außenseite (20) der Hülse (7) zu einem Ringspalt (25) zwischen der Innenseite (26) der Hülse (7) und dem Ventilbolzen (8) führen, und dass der Ventilraum (9) über den Ringspalt (25) und die Bohrungen (23, 23') in der Hülse (7) mit dem Hochdruckkanal (16) verbindbar ist.Fuel injection valve according to one of claims 1 to 9,
characterized,
that the sleeve (7) has several bores (23, 23 ') projecting from an outer side (20) of the sleeve (7) to an annular gap (25) between the inside (26) of the sleeve (7) and the valve pin (8 ), and that the valve space (9) via the annular gap (25) and the bores (23, 23 ') in the sleeve (7) with the high pressure passage (16) is connectable. Brennstoffeinspritzventil nach Anspruch 10,
dadurch gekennzeichnet,
dass zumindest ein Teil der Bohrungen (23, 23') bezüglich einer Achse (24) des Ventilbolzens (8) umfänglich verteilt in der Hülse (7) ausgestaltet ist.Fuel injection valve according to claim 10,
characterized,
in that at least a part of the bores (23, 23 ') is designed to be circumferentially distributed in the sleeve (7) with respect to an axis (24) of the valve pin (8). Brennstoffeinspritzventil nach Anspruch 10 oder 11,
dadurch gekennzeichnet,
dass zumindest ein Teil der Bohrungen (23, 23') bezüglich einer Achse (24) des Ventilbolzens (8) axial verteilt in der Hülse (7) ausgestaltet ist.Fuel injection valve according to claim 10 or 11,
characterized,
in that at least a part of the bores (23, 23 ') is configured axially distributed in the sleeve (7) with respect to an axis (24) of the valve pin (8). Brennstoffeinspritzventil nach einem der Ansprüche 10 bis 12,
dadurch gekennzeichnet,
dass Mündungsöffnungen (40) der Bohrungen (23'), an denen die Bohrungen (23') in einen Ringspalt (25) zwischen der Innenseite (26) der Hülse (7) und dem Ventil bolzen (8) münden, zumindest näherungsweise den gleichen Austrittsdurchmesser (d) aufweisen.Fuel injection valve according to one of claims 10 to 12,
characterized,
that orifices (40) of the bores (23 '), at which the bores (23') in an annular gap (25) between the inside (26) of the sleeve (7) and the valve plug (8) open, at least approximately the same Have outlet diameter (d).
EP20120158513 2011-04-11 2012-03-08 Fuel injector valve Not-in-force EP2511514B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE201110007106 DE102011007106A1 (en) 2011-04-11 2011-04-11 Fuel injector

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EP2511514A2 true EP2511514A2 (en) 2012-10-17
EP2511514A3 EP2511514A3 (en) 2013-11-13
EP2511514B1 EP2511514B1 (en) 2014-11-19

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DE (1) DE102011007106A1 (en)

Cited By (3)

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Publication number Priority date Publication date Assignee Title
WO2014086933A1 (en) * 2012-12-07 2014-06-12 Continental Automotive Gmbh Piezo injector
US9689359B2 (en) 2012-12-20 2017-06-27 Continental Automotive Gmbh Piezo injector
US10024285B2 (en) 2012-07-18 2018-07-17 Continental Automotive Gmbh Piezo injector with hydraulically coupled nozzle needle movement

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Publication number Priority date Publication date Assignee Title
DE102004061800A1 (en) 2004-12-22 2006-07-06 Robert Bosch Gmbh Injector of a fuel injection system of an internal combustion engine

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Publication number Priority date Publication date Assignee Title
DE102007042466B3 (en) * 2007-09-06 2009-04-09 Continental Automotive Gmbh Injection system with reduced switching leakage and method of manufacturing an injection system
DE102009026564A1 (en) * 2009-05-29 2010-12-02 Robert Bosch Gmbh Fuel injector for injecting fuel into combustion chamber of internal-combustion engine, has control valve element that is formed and arranged such that small resulting hydraulic force is applied on control valve element
DE102009027494A1 (en) * 2009-07-07 2011-01-13 Robert Bosch Gmbh Fuel injector with pressure compensated control valve
DE102009055267A1 (en) * 2009-12-23 2011-06-30 Robert Bosch GmbH, 70469 Pressure compensated fuel injector with bypass and minimized valve volume

Patent Citations (1)

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Publication number Priority date Publication date Assignee Title
DE102004061800A1 (en) 2004-12-22 2006-07-06 Robert Bosch Gmbh Injector of a fuel injection system of an internal combustion engine

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10024285B2 (en) 2012-07-18 2018-07-17 Continental Automotive Gmbh Piezo injector with hydraulically coupled nozzle needle movement
WO2014086933A1 (en) * 2012-12-07 2014-06-12 Continental Automotive Gmbh Piezo injector
CN104838130A (en) * 2012-12-07 2015-08-12 大陆汽车有限公司 Piezo injector
CN104838130B (en) * 2012-12-07 2018-09-21 大陆汽车有限公司 Piezoelectric injector
US10508635B2 (en) 2012-12-07 2019-12-17 Continental Automotive Gmbh Piezo injector
US9689359B2 (en) 2012-12-20 2017-06-27 Continental Automotive Gmbh Piezo injector

Also Published As

Publication number Publication date
EP2511514B1 (en) 2014-11-19
DE102011007106A1 (en) 2012-10-11
EP2511514A3 (en) 2013-11-13

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