EP2628939B1 - Fuel injector valve - Google Patents

Fuel injector valve Download PDF

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Publication number
EP2628939B1
EP2628939B1 EP20130152177 EP13152177A EP2628939B1 EP 2628939 B1 EP2628939 B1 EP 2628939B1 EP 20130152177 EP20130152177 EP 20130152177 EP 13152177 A EP13152177 A EP 13152177A EP 2628939 B1 EP2628939 B1 EP 2628939B1
Authority
EP
European Patent Office
Prior art keywords
shut
control chamber
throttle
nozzle needle
fuel injection
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP20130152177
Other languages
German (de)
French (fr)
Other versions
EP2628939A1 (en
Inventor
Henning Kreschel
Michael Mennicken
Wolfgang Stoecklein
Lorenz Zerle
Volker Beuche
Lars Reichelt
Hans-Christoph Magel
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2628939A1 publication Critical patent/EP2628939A1/en
Application granted granted Critical
Publication of EP2628939B1 publication Critical patent/EP2628939B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
    • F02M2200/708—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic with hydraulic chambers formed by a movable sleeve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
    • F02M2547/001—Control chambers formed by movable sleeves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
    • F02M2547/008—Means for influencing the flow rate out of or into a control chamber, e.g. depending on the position of the needle

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 nozzle module in which a nozzle needle cooperating with an injection nozzle is guided axially movable, to which a valve control chamber adjoins, which is connected via a inlet throttle having inlet channel with a high-pressure chamber.
  • a valve control module is provided, which is designed like a valve and having a valve closure member which is arranged in a valve chamber which is connected via a flow restrictor having a drain passage with the valve control chamber.
  • a bypass channel is provided in the known injection arrangement.
  • a fuel injection valve wherein a valve lift of the valve closing member in an injection process is 100%, so that the valve closure member rests against a second valve seat.
  • This correlates a so-called control amount, which is discharged via the drainage channel and the valve chamber and which triggers a stroke of the nozzle needle.
  • a stroke of the valve closure member in the case of a pressure control, wherein the stroke of the valve closure member is 80%. This correlates to a control amount that is lower than that in an injection process. This control amount is not sufficient to trigger a stroke of the nozzle needle.
  • the from the DE 101 39 623 A1 known injection assembly has the disadvantage that at each actuation of the nozzle needle fuel is separated from the high pressure region in the low pressure region. For example, the amount of control consumed by each control operation flows into a tank of a low pressure return Motor vehicle and must ultimately be fed back via a high-pressure pump. Specifically, the control amount taken from the control room thus contributes to the energy consumption of the entire fuel injection system. Therefore, it is expedient to reduce this control amount as possible, but without worsening the injection behavior by adversely affecting the control process.
  • the fuel injection valve according to the invention with the features of claim 1 has the advantage that an improved design is made possible, in particular, a control amount for driving the nozzle needle is reduced.
  • the efficiency of the fuel injection valve can be improved and thus the overall efficiency of the relevant fuel injection system can be optimized. This reduces energy consumption.
  • a heating resulting from the control, in particular in the region of the return, can be reduced, so that the thermal load of the fuel injection valve and the other components of the fuel injection system is reduced.
  • the first control room part is connected to the second control room part via a throttled connection.
  • a pressure difference to the second control chamber part which moves the shut-off element within the control chamber part, can thereby be set during the pressure reduction in the first control chamber part.
  • the throttled connection creates a hydraulic connection between the first control chamber part and the second control chamber part, so that the nozzle needle also moves.
  • the throttled connection between the first control chamber part and the second control chamber part can be realized by a throttled connection bore. However, it is also possible that a gap is provided in the region of the guide of the shut-off element, via which the throttled connection is realized.
  • the movable shut-off element blocks a connection between the outlet throttle and the inlet throttle via the first control chamber part. This is given neither a direct first nor an indirect connection of the inlet throttle with the outlet throttle over the control chamber when the shut-off is in the shut-off position. An inflow of high-pressure fuel via the inflow throttle in the control room is thus completely interrupted. As a result, further outflow of fuel flowing in via the inlet throttle is also interrupted.
  • the shut-off element has a throttled filling bore and, in the shut-off position, the shut-off element connects the inlet throttle via the throttled filling bore to the second control chamber part.
  • a direct connection of the inlet throttle with the outlet throttle is interrupted via the first control chamber part.
  • About the throttled filling bore may be an indirect connection via the second control room part. In this case, however, occurs on a further throttling, which may be large, without the control behavior is impaired.
  • the shut-off element has a throttled connection bore which connects the first control chamber part and the second control chamber part.
  • a throttled connection bore may be provided alone or parallel to a throttled filling bore, depending on the configuration.
  • the shut-off element and the nozzle needle are guided in a guide bore along a longitudinal axis and that an adjustment path of the shut-off element in the direction of the nozzle needle is limited.
  • the guide bore may be configured as a stepped bore, wherein the shut-off cooperates to limit the adjustment in the direction of the nozzle needle with a step of the guide bore.
  • the shut-off element can be configured, for example, at least approximately as a cylindrical shut-off piston, which has a larger diameter than the nozzle needle in the region of the guide bore.
  • the shut-off element may also have a shoulder which cooperates with the step of the guide bore.
  • a spring element is provided, which is arranged between the step of the guide bore and the shut-off element. In this way, an initial position of the shut-off element in the guide bore can be specified.
  • the spring element may for example be designed as a leaf spring.
  • a control chamber sleeve is provided, that a throttle plate is provided, in which the outlet throttle and the inlet throttle are configured, that the control chamber sleeve cooperates with the throttle plate, that the shut-off and the nozzle needle guided in the guide bore of the control chamber sleeve along a longitudinal axis are and that the control chamber is configured in the guide bore and is limited on the one hand by one side of the throttle plate and on the other hand by an end face of the nozzle needle.
  • Fig. 1 shows a first non-inventive embodiment of a fuel injection valve 1 in a schematic, partial sectional view.
  • the fuel injection valve 1 can serve 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, the diesel fuel under high pressure leads to a plurality of 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 control valve 2 which can be actuated via an actuator 3, as illustrated by the double arrow 4.
  • the actuator 3 may be configured, for example, as a magnetic actuator 3 or as a piezoelectric actuator 3.
  • the fuel injection valve 1 has a nozzle needle 5, which is arranged in a fuel chamber 6. Via a high pressure line 7 can be performed under high pressure fuel in the fuel chamber 6.
  • the high pressure line 7 may be connected, for example, in operation with a common rail of a fuel injection system.
  • the fuel injection valve 1 also has a throttle plate 8, in which an inlet throttle 9 and an outlet throttle 10 are configured.
  • the throttle plate 8 has a first side 11 and a second side 12 facing away from the first side 11.
  • the first side 11 delimits the fuel chamber 6.
  • a control chamber sleeve 13 rests against the first side 11, wherein the control chamber sleeve 13 can rest against the first side 11, for example via a sealing edge.
  • the control chamber sleeve 13 has a guide bore 14, which in This embodiment is designed cylindrical.
  • the control chamber sleeve 13 is designed in this case as a hollow cylinder. In the guide bore 14, the nozzle needle 5 is guided along a longitudinal axis 15.
  • a control chamber 20 is formed, which is divided into a first control chamber part 21 and a second control chamber part 22.
  • a movable shut-off element 23 is provided, which is guided along the longitudinal axis 15 in the guide bore 14.
  • the shut-off element 23 may be configured, for example, as a shut-off piston 23.
  • the shut-off element 23 is designed substantially cylindrical in this embodiment.
  • the shut-off element 23 has a first end face 24, which faces the first side 11 of the throttle plate 8.
  • the shut-off element 23 has a second end face 25, which faces the end face 16 of the nozzle needle 5.
  • the first control chamber part 21 is formed between the first end face 24 of the shut-off element 23 and the first side 11 of the throttle plate 8.
  • the second control chamber part 22 is formed between the second end face 25 of the shut-off element 23 and the end face 16 of the nozzle needle 5.
  • the first control room part 21 is connected via a throttled connection with the second control room part 22.
  • the restricted connection is formed by a throttled connection bore 26 which extends through the shut-off element 23.
  • the throttled connection between the first control chamber part 21 and the control chamber 22 may also be formed by a suitable recess between the shut-off element 23 and the control chamber sleeve 13.
  • the outlet throttle 10 and the inlet throttle 9 both open into the first control chamber part 21.
  • the actuator 3 actuates the control valve 2 to relieve the control chamber 20 via the outlet throttle 10
  • the pressure in the control chamber 20 drops from.
  • the shut-off element 23 moves in a direction 27.
  • the nozzle needle 5 also moves in the direction 27. This opens the fuel injection valve 1 and fuel from the fuel chamber 6 can, for example, enter the combustion chamber of an internal combustion engine be injected.
  • shut-off element 23 By the movement of the shut-off element 23, this enters a shut-off position.
  • a closing body 28 configured on the shut-off element 23 cooperates with a shut-off seat 29 of the inlet throttle 9.
  • the inlet throttle 9 opens at the Absperrsitz 29 in the first control chamber part 21.
  • the shut-off closes the closing body 28 of the shut-off 23 the Absperrsitz 29 of the inlet throttle 9, so that the shut-off element 23 cooperates with the Absperrsitz 29 to a closed sealing seat.
  • the inlet throttle 9 is then closed at Absperrsitz 29.
  • the nozzle needle 5 Due to the throttled connection bore 26, the nozzle needle 5 can move further upwards. Thus, a complete opening of the nozzle needle 5 can be achieved.
  • the throttled connection bore 26 in this case allows damping.
  • the pressure in the first control chamber part 21 is at least approximately the same as the pressure in the second control chamber part 22, since an equilibrium of forces is established on the shut-off element 23 via the identically sized end faces 24, 25.
  • the shut-off position in which the shut-off seat 29 is closed, the inflow to the control chamber 20 via the inlet throttle 9 is interrupted.
  • the control valve 2 is closed again, the pressure in the second control chamber part 22 increases due to the progressive needle movement of the nozzle needle 5 until the needle comes to a standstill.
  • the pressure below the Absperrsitzes 29, the shut-off element 23 again move against the direction 27, so that the inlet throttle 9 is opened. This starts the closing process of the nozzle needle. 5
  • a return flow of fuel via the outlet throttle 10 into the first control chamber part 21 can also take place with the aid of a bypass throttle in order to accelerate the closing movement of the nozzle needle 5.
  • Fig. 2 shows a diagram for explaining the operation of the fuel injection valve 1 according to an embodiment.
  • the time t is plotted on the abscissa of the diagram.
  • the diagram shows a valve lift 30, a needle lift 31 and a flow 32 through the inlet throttle 9 in the form of exemplary curves.
  • the needle stroke 31 illustrates the opening and closing movement of the nozzle needle 5.
  • the flow 32 through the inlet throttle 9 illustrates that from the high pressure line 7 via the inlet throttle 9 in the first control chamber part 21 of the Control room 20 nachfnocden fuel.
  • the area under the curve 32 is hereby Measure of the flowing, under high pressure fuel quantity.
  • the sequence of an actuation is shown here by way of example.
  • the actuator 3 actuates the control valve 2.
  • the pressure in the control chamber 20 drops.
  • the shut-off element 23 and the nozzle needle 5 move in the direction 27.
  • the control valve 2 can be closed again. Since during the opening movement of the nozzle needle 5, that is, between the time t2 and the time t3, the shut-off 23 is already comparatively early in the shut-off, there is no flow of fuel through the inlet throttle 9 or such a flow is at least negligible, as it especially in the case of the Fig. 3 described embodiment is the case.
  • the nozzle needle 5 closes, with the nozzle needle 5 moving counter to the direction 27.
  • fuel now has to be released via the inlet throttle 9. This takes place from the time t4.
  • the control valve 2 is fully closed again at time t5.
  • the nozzle needle 5 is completely closed, that is to say until the time t6, the volume of the control chamber 20 increases, so that a flow 32 through the inlet throttle 9 results.
  • the nozzle needle 5 reaches its end position (closed position), then the supply of fuel through the inlet throttle 9 ends, which is the case at time t6.
  • Fig. 3 shows a fuel injection valve 1 in a partial, schematic sectional view according to a second non-inventive embodiment.
  • the guide bore 14 of the control chamber sleeve 13 is designed as a stepped bore 14.
  • the guide bore 14 thereby has a step 35.
  • the shut-off element 23 has a collar 36, on which a paragraph 37th is designed.
  • the shut-off element 23 opposite to the direction 27 perform an adjustment (stroke) 38.
  • a limitation of the adjustment path 38 is given by striking the shoulder 37 of the shut-off element 23 at the level 35.
  • the shut-off element 28 thus interacts with its shoulder 37 with the step 35 of the guide bore 14.
  • the shut-off element 23 may in particular have a throttled connection bore 26, as described on the basis of Fig. 1 is described. Other embodiments are possible, for example, based on the Fig. 6 described embodiment.
  • Fig. 4 shows a fuel injection valve 1 in a partial, schematic sectional view according to a third non-inventive embodiment.
  • the shut-off element 23 is shown in the shut-off position, wherein the first control chamber part 21 of the control chamber 20 at least approximately disappears.
  • the guide bore 14 is configured as a stepped bore 14.
  • the shut-off element 23 is configured as a cylindrical shut-off piston 23 which abuts against the direction 27 with its second end face 25 at the stage 35 of the guide bore 14 in an adjustment, when the maximum adjustment path 38 is reached.
  • a limitation of the adjustment path 38 is given.
  • a diameter of the nozzle needle 5 is smaller than a diameter of the shut-off element 23.
  • the shut-off element 23 may, for example, a throttled connection bore 26, as they are based on the Fig. 1 is described, or even another embodiment of throttled connections, as for example with reference to the Fig. 6 is described.
  • a diameter of the shutoff element 23 at least in sections equal to, smaller or larger than a diameter of the nozzle needle 5 can be selected.
  • Fig. 5 shows a fuel injection valve 1 in a partial, schematic sectional view according to a fourth embodiment not according to the invention.
  • a shut-off element 23 with a collar 36 in the designed as a stepped bore 14 Guide bore 14 is arranged.
  • a spring element 40 is provided which is arranged between the step 35 of the guide bore 14 and the shoulder 37 of the shut-off element 23.
  • the spring element 40 acts on the shut-off element 23 in the direction 27 with a spring force when the spring element 40 is biased against the direction 27 by a corresponding movement of the shut-off element 23.
  • a starting position (initial position) of the shut-off element 23 is defined.
  • the spring element 40 is configured in this embodiment as a leaf spring 40.
  • the spring element 40, the shut-off element 23 also act against the direction 27 to define the starting position.
  • Fig. 6 shows a fuel injection valve 1 in a partial, schematic sectional view according to an embodiment of the invention.
  • the shut-off element 23 is designed with a cylindrical basic shape.
  • an annular shoulder is configured in which a spring element 41 is inserted.
  • the nozzle needle 5 has on its end face 16 an annular shoulder, which surrounds the spring element 41.
  • the spring element 41 urges the shut-off element 23 in response to the instantaneous position of the nozzle needle 5 in the direction 27 with a spring force.
  • Fig. 6 shows the shut-off element 23 in this case in the shut-off position.
  • the inlet throttle 9 has an outlet 42, at which the inlet throttle 9 opens into the first control chamber part 21 of the control chamber 20.
  • the output 42 of the inlet throttle 9, a projection 43 is assigned in this embodiment, which encloses the output 42 in the shut-off position.
  • the shut-off element 23 has a throttled filling bore 44, which connects the inlet throttle 9 with the second control chamber part 22. As a result, the inlet throttle 9 no longer leads into the first control chamber part 21 when the shut-off element 23 is in the shut-off position.
  • the shut-off element 23 has the throttled connection bore 26. From the inlet throttle 9 via the throttled filling bore 44, the second control chamber part 22 and the throttled connection bore 26 to the outlet throttle 10 results in a large throttle effect, so that the control amount is reduced.
  • the second control chamber part 22 of the control chamber 20 can be filled relatively quickly, since in this respect only the throttling action of the throttled filling bore 44 acts. Thus, closing of the nozzle needle 5 can be accelerated.
  • the inlet throttle 9 can be closed at least temporarily with the control valve 2 open, or at least a reduction of the supplied high-pressure quantity can be achieved.
  • the control valve 2 is closed, the inlet throttle 9 is released again.
  • the control amount can be significantly reduced.
  • the temperature in the return is significantly reduced.
  • Another advantage is that the throttle effect of the outlet throttle 10 and the throttling action of the inlet throttle 9 can be freely selected within certain limits. As a result, a flexible definition of the opening and closing speed of the nozzle needle 5 is possible.
  • the efficiency of the fuel injection valve 1 can be improved. This results in particular lower carbon dioxide emissions of a motor vehicle or the like.

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

Description

Stand der TechnikState of the art

Die Erfindung betrifft 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 101 39 623 A1 ist eine Einspritzanordnung für ein Kraftstoff-Speichereinspritzsystem bekannt. Hierbei ist ein Düsenmodul vorgesehen, in dem eine mit einer Einspritzdüse zusammenwirkende Düsennadel axial bewegbar geführt ist, an die sich ein Ventilsteuerraum anschließt, welcher über einen eine Zulaufdrossel aufweisenden Zulaufkanal mit einem Hochdruckraum verbunden ist. Ferner ist ein Ventilsteuermodul vorgesehen, das ventilartig ausgebildet ist und ein Ventilschließglied aufweist, das in einem Ventilraum angeordnet ist, der über einen eine Ablaufdrossel aufweisenden Ablaufkanal mit dem Ventilsteuerraum verbunden ist. Ferner ist bei der bekannten Einspritzanordnung ein Bypass-Kanal vorgesehen. Bei der bekannten Einspritzanordnung ist ein Kraftstoffeinspritzventil vorgesehen, wobei ein Ventilhub des Ventilschließglieds bei einem Einspritzvorgang 100 % beträgt, so dass das Ventilschließglied an einem zweiten Ventilsitz anliegt. Damit korreliert eine sogenannte Steuermenge, die über den Ablaufkanal und den Ventilraum abgeführt wird und die einen Hub der Düsennadel auslöst. Möglich ist auch ein Hub des Ventilschließglieds im Falle einer Druckabregelung, wobei der Hub des Ventilschließglieds 80 % beträgt. Damit korreliert eine Steuermenge, die geringer als diejenige bei einem Einspritzvorgang ist. Diese Steuermenge reicht nicht aus, um einen Hub der Düsennadel auszulösen.From the DE 101 39 623 A1 an injection arrangement for a fuel storage injection system is known. In this case, a nozzle module is provided, in which a nozzle needle cooperating with an injection nozzle is guided axially movable, to which a valve control chamber adjoins, which is connected via a inlet throttle having inlet channel with a high-pressure chamber. Further, a valve control module is provided, which is designed like a valve and having a valve closure member which is arranged in a valve chamber which is connected via a flow restrictor having a drain passage with the valve control chamber. Furthermore, a bypass channel is provided in the known injection arrangement. In the known injection arrangement, a fuel injection valve is provided, wherein a valve lift of the valve closing member in an injection process is 100%, so that the valve closure member rests against a second valve seat. This correlates a so-called control amount, which is discharged via the drainage channel and the valve chamber and which triggers a stroke of the nozzle needle. Also possible is a stroke of the valve closure member in the case of a pressure control, wherein the stroke of the valve closure member is 80%. This correlates to a control amount that is lower than that in an injection process. This control amount is not sufficient to trigger a stroke of the nozzle needle.

Die aus der DE 101 39 623 A1 bekannte Einspritzanordnung hat den Nachteil, dass bei jeder Betätigung der Düsennadel Brennstoff aus dem Hochdruckbereich in den Niederdruckbereich abgesondert wird. Die durch jeden Steuervorgang verbrauchte Steuermenge fließt beispielsweise über einen Niederdruckrücklauf in einen Tank eines Kraftfahrzeugs und muss letztlich über eine Hochdruckpumpe wieder zugeführt werden. Speziell die aus dem Steuerraum entnommene Steuermenge trägt somit zum Energieverbrauch der gesamten Brennstoffeinspritzanlage bei. Daher ist es zweckmäßig, diese Steuermenge möglichst zu reduzieren, ohne aber das Einspritzverhalten durch eine ungünstige Beeinflussung des Steuervorgangs zu verschlechtern.The from the DE 101 39 623 A1 known injection assembly has the disadvantage that at each actuation of the nozzle needle fuel is separated from the high pressure region in the low pressure region. For example, the amount of control consumed by each control operation flows into a tank of a low pressure return Motor vehicle and must ultimately be fed back via a high-pressure pump. Specifically, the control amount taken from the control room thus contributes to the energy consumption of the entire fuel injection system. Therefore, it is expedient to reduce this control amount as possible, but without worsening the injection behavior by adversely affecting the control process.

Aus der US 2010/0301143 A1 ist ein Einspritzventil für Brennkraftmaschinen bekannt, bei dem ein bewegliches Element im Steuerraum des Einspritzventils angeordnet ist, das während der Einspritzung die Zulaufdrossel verschließen soll.From the US 2010/0301143 A1 an injection valve for internal combustion engines is known in which a movable element is arranged in the control chamber of the injection valve, which is to close the inlet throttle during injection.

Offenbarung der ErfindungDisclosure of the invention

Das erfindungsgemäße Brennstoffeinspritzventil mit den Merkmalen des Anspruchs 1 hat den Vorteil, dass eine verbesserte Ausgestaltung ermöglicht ist, bei der insbesondere eine Steuermenge zur Ansteuerung der Düsennadel reduziert wird.The fuel injection valve according to the invention with the features of claim 1 has the advantage that an improved design is made possible, in particular, a control amount for driving the nozzle needle is 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.

Durch die Verringerung der Steuermenge während der Ansteuerung der Düsennadel, die zum Niederdruck abgesondert wird, kann der Wirkungsgrad des Brennstoffeinspritzventils verbessert werden und somit der Gesamtwirkungsgrad der betreffenden Brennstoffeinspritzanlage optimiert werden. Dadurch verringert sich der Energieverbrauch. Außerdem kann auch eine durch die Steuerung entstehende Erwärmung, insbesondere im Bereich des Rücklaufs, verringert werden, so dass sich die thermische Belastung des Brennstoffeinspritzventils und der anderen Komponenten der Brennstoffeinspritzanlage verringert.By reducing the amount of control during the control of the nozzle needle, which is discharged to low pressure, the efficiency of the fuel injection valve can be improved and thus the overall efficiency of the relevant fuel injection system can be optimized. This reduces energy consumption. In addition, a heating resulting from the control, in particular in the region of the return, can be reduced, so that the thermal load of the fuel injection valve and the other components of the fuel injection system is reduced.

Der erste Steuerraumteil ist mit dem zweiten Steuerraumteil über eine gedrosselte Verbindung verbunden. Bei der Betätigung der Düsennadel kann sich bei der Druckabsenkung im ersten Steuerraumteil dadurch eine Druckdifferenz zum zweiten Steuerraumteil einstellen, die das Absperrelement innerhalb des Steuerraumteils bewegt. Die gedrosselte Verbindung schafft hierbei eine hydraulische Verbindung zwischen dem ersten Steuerraumteil und dem zweiten Steuerraumteil, so dass sich auch die Düsennadel bewegt. Die gedrosselte Verbindung zwischen dem ersten Steuerraumteil und dem zweiten Steuerraumteil kann durch eine gedrosselte Verbindungsbohrung realisiert werden. Möglich ist es allerdings auch, dass ein Spalt im Bereich der Führung des Absperrelements vorgesehen ist, über den die gedrosselte Verbindung realisiert ist.The first control room part is connected to the second control room part via a throttled connection. When the nozzle needle is actuated, a pressure difference to the second control chamber part, which moves the shut-off element within the control chamber part, can thereby be set during the pressure reduction in the first control chamber part. The throttled connection creates a hydraulic connection between the first control chamber part and the second control chamber part, so that the nozzle needle also moves. The throttled connection between the first control chamber part and the second control chamber part can be realized by a throttled connection bore. However, it is also possible that a gap is provided in the region of the guide of the shut-off element, via which the throttled connection is realized.

Das bewegbare Absperrelement sperrt in der Absperrstellung eine Verbindung zwischen der Ablaufdrossel und der Zulaufdrossel über den ersten Steuerraumteil. Dadurch ist weder eine direkte ersten noch eine indirekte Verbindung der Zulaufdrossel mit der Ablaufdrossel über den Steuerraum gegeben, wenn sich das Absperrelement in der Absperrstellung befindet. Ein Zufluss von unter hohem Druck stehenden Brennstoff über die Zuflussdrossel in den Steuerraum wird damit vollständig unterbrochen. Hierdurch wird auch ein weiteres Abfließen von über die Zulaufdrossel nachfließenden Brennstoff unterbrochen.In the shut-off position, the movable shut-off element blocks a connection between the outlet throttle and the inlet throttle via the first control chamber part. This is given neither a direct first nor an indirect connection of the inlet throttle with the outlet throttle over the control chamber when the shut-off is in the shut-off position. An inflow of high-pressure fuel via the inflow throttle in the control room is thus completely interrupted. As a result, further outflow of fuel flowing in via the inlet throttle is also interrupted.

Erfindungsgemäß weist das Absperrelement eine gedrosselte Füllbohrung auf und das Absperrelement verbindet in der Absperrstellung die Zulaufdrossel über die gedrosselte Füllbohrung mit dem zweiten Steuerraumteil. Dadurch wird eine direkte Verbindung der Zulaufdrossel mit der Ablaufdrossel über den ersten Steuerraumteil unterbrochen. Über die gedrosselte Füllbohrung kann allerdings eine indirekte Verbindung über den zweiten Steuerraumteil bestehen. Hierbei tritt jedoch eine weitere Drosselung auf, die groß vorgegeben sein kann, ohne dass das Steuerverhalten beeinträchtigt wird.According to the invention, the shut-off element has a throttled filling bore and, in the shut-off position, the shut-off element connects the inlet throttle via the throttled filling bore to the second control chamber part. As a result, a direct connection of the inlet throttle with the outlet throttle is interrupted via the first control chamber part. About the throttled filling bore, however, may be an indirect connection via the second control room part. In this case, however, occurs on a further throttling, which may be large, without the control behavior is impaired.

Weiterhin weist das Absperrelement eine gedrosselte Verbindungsbohrung auf, die den ersten Steuerraumteil und den zweiten Steuerraumteil verbindet. Solch eine gedrosselte Verbindungsbohrung kann je nach Ausgestaltung alleine oder auch parallel zu einer gedrosselten Füllbohrung vorgesehen sein. Durch die gedrosselte Verbindungsbohrung wird in vorteilhafter Weise eine Einstellung der Drosselwirkung der gedrosselten Verbindung zwischen dem ersten Steuerraumteil und dem zweiten Steuerraumteil erzielt. Wenn die gedrosselte Verbindungsbohrung bezüglich der Verbindung des ersten Steuerraumteils mit dem zweiten Steuerraumteil parallel zu der gedrosselten Füllbohrung in dem Absperrelement realisiert ist, dann ergibt sich jedoch in der Absperrstellung im Hinblick auf die indirekte Verbindung der Zulaufdrossel mit der Ablaufdrossel eine Reihenschaltung der gedrosselten Füllbohrung und der gedrosselten Verbindungsbohrung. Durch diese hohe Drosselwirkung kann die Steuermenge wesentlich reduziert werden.Furthermore, the shut-off element has a throttled connection bore which connects the first control chamber part and the second control chamber part. Such a throttled connection bore may be provided alone or parallel to a throttled filling bore, depending on the configuration. By the throttled connection bore adjustment of the throttling effect of the throttled connection between the first control chamber part and the second control chamber part is achieved in an advantageous manner. If the throttled connection bore is realized with respect to the connection of the first control chamber part with the second control chamber part parallel to the throttled filling bore in the shut-off element, then, however, results in the shut-off position with regard to the indirect connection of the inlet throttle with the outlet throttle a series connection of the throttled filling bore and the throttled connection hole. Due to this high throttle effect, the control amount can be significantly reduced.

Vorteilhaft ist es, dass das Absperrelement und die Düsennadel in einer Führungsbohrung entlang einer Längsachse geführt sind und dass ein Verstellweg des Absperrelements in Richtung der Düsennadel begrenzt ist. Gemäß einer vorteilhaften Ausgestaltung kann hierbei die Führungsbohrung als Stufenbohrung ausgestaltet sein, wobei das Absperrelement zur Begrenzung des Verstellwegs in Richtung der Düsennadel mit einer Stufe der Führungsbohrung zusammenwirkt. Hierbei kann das Absperrelement beispielsweise zumindest näherungsweise als zylinderförmiger Absperrkolben ausgestaltet sein, der einen größeren Durchmesser als die Düsennadel im Bereich der Führungsbohrung aufweist. Alternativ kann das Absperrelement allerdings auch einen Absatz aufweisen, der mit der Stufe der Führungsbohrung zusammenwirkt. Durch die Hubbegrenzung kann eine Reaktionszeit zum Schließen und Öffnen eines Absperrsitzes oder dergleichen reduziert werden.It is advantageous that the shut-off element and the nozzle needle are guided in a guide bore along a longitudinal axis and that an adjustment path of the shut-off element in the direction of the nozzle needle is limited. According to an advantageous embodiment, in this case, the guide bore may be configured as a stepped bore, wherein the shut-off cooperates to limit the adjustment in the direction of the nozzle needle with a step of the guide bore. In this case, the shut-off element can be configured, for example, at least approximately as a cylindrical shut-off piston, which has a larger diameter than the nozzle needle in the region of the guide bore. Alternatively, however, the shut-off element may also have a shoulder which cooperates with the step of the guide bore. By the stroke limitation, a reaction time for closing and opening a Absperrsitzes or the like can be reduced.

Vorteilhaft ist es auch, dass ein Federelement vorgesehen ist, das zwischen der Stufe der Führungsbohrung und dem Absperrelement angeordnet ist. Hierdurch kann eine Anfangslage des Absperrelements in der Führungsbohrung vorgegeben werden. Das Federelement kann beispielsweise als Blattfeder ausgestaltet sein.It is also advantageous that a spring element is provided, which is arranged between the step of the guide bore and the shut-off element. In this way, an initial position of the shut-off element in the guide bore can be specified. The spring element may for example be designed as a leaf spring.

Außerdem ist es vorteilhaft, dass eine Steuerraumhülse vorgesehen ist, dass eine Drosselplatte vorgesehen ist, in der die Ablaufdrossel und die Zulaufdrossel ausgestaltet sind, dass die Steuerraumhülse mit der Drosselplatte zusammenwirkt, dass das Absperrelement und die Düsennadel in der Führungsbohrung der Steuerraumhülse entlang einer Längsachse geführt sind und dass der Steuerraum in der Führungsbohrung ausgestaltet ist und einerseits durch eine Seite der Drosselplatte und andererseits durch eine Stirnseite der Düsennadel begrenzt ist.Moreover, it is advantageous that a control chamber sleeve is provided, that a throttle plate is provided, in which the outlet throttle and the inlet throttle are configured, that the control chamber sleeve cooperates with the throttle plate, that the shut-off and the nozzle needle guided in the guide bore of the control chamber sleeve along a longitudinal axis are and that the control chamber is configured in the guide bore and is limited on the one hand by one side of the throttle plate and on the other hand by an end face of the nozzle needle.

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 nicht erfindungsgemäßen Ausführungsbeispiel,
  • Fig. 2 ein Diagramm zur Erläuterung der Funktionsweise eines Brennstoffeinspritzventils entsprechend einem Ausführungsbeispiel;
  • Fig. 3 ein Brennstoffeinspritzventil in einer auszugsweisen, schematischen Schnittdarstellung entsprechend einem zweiten nicht erfindungsgemäßen Ausführungsbeispiel
  • Fig. 4 ein Brennstoffeinspritzventil in einer auszugsweisen, schematischen Schnittdarstellung entsprechend einem dritten nicht erfindungsgemäßen Ausführungsbeispiel;
  • Fig.5 ein Brennstoffeinspritzventil in einer auszugsweisen, schematischen Schnittdarstellung entsprechend einem vierten nicht erfindungsgemäßen Ausführungsbeispiel und
  • Fig. 6 ein Brennstoffeinspritzventil in einer auszugsweisen, schematischen Schnittdarstellung entsprechend einem 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 an excerpt, schematic sectional view according to a first embodiment not according to the invention,
  • Fig. 2 a diagram for explaining the operation of a fuel injection valve according to an embodiment;
  • Fig. 3 a fuel injection valve in an excerpt, schematic sectional view according to a second non-inventive embodiment
  • Fig. 4 a fuel injection valve in an excerpt, schematic sectional view according to a third embodiment not according to the invention;
  • Figure 5 a fuel injection valve in a partial, schematic sectional view according to a fourth non-inventive embodiment and
  • Fig. 6 a fuel injection valve in a partial, schematic sectional view according to an embodiment of the invention.

Ausführungsformen der ErfindungEmbodiments of the invention

Fig. 1 zeigt ein erstes nicht erfindungsgemäßes Ausführungsbeispiel eines Brennstoffeinspritzventils 1 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 zu mehreren Brennstoffeinspritzventilen 1 führt. Das erfindungsgemäße Brennstoffeinspritzventil 1 eignet sich jedoch auch für andere Anwendungsfälle. Fig. 1 shows a first non-inventive embodiment of a fuel injection valve 1 in a schematic, partial sectional view. The fuel injection valve 1 can serve 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, the diesel fuel under high pressure leads to a plurality of fuel injection valves 1. However, the fuel injection valve 1 according to the invention is also suitable for other applications.

Das Brennstoffeinspritzventil 1 weist ein Steuerventil 2 auf, das über einen Aktor 3 betätigbar ist, wie es durch den Doppelpfeil 4 veranschaulicht ist. Der Aktor 3 kann beispielsweise als Magnetaktor 3 oder als piezoelektrischer Aktor 3 ausgestaltet sein. Ferner weist das Brennstoffeinspritzventil 1 eine Düsennadel 5 auf, die in einem Brennstoffraum 6 angeordnet ist. Über eine Hochdruckleitung 7 kann unter hohem Druck stehender Brennstoff in den Brennstoffraum 6 geführt werden. Die Hochdruckleitung 7 kann beispielsweise im Betrieb mit einem Common-Rail einer Brennstoffeinspritzanlage verbunden sein.The fuel injection valve 1 has a control valve 2 which can be actuated via an actuator 3, as illustrated by the double arrow 4. The actuator 3 may be configured, for example, as a magnetic actuator 3 or as a piezoelectric actuator 3. Furthermore, the fuel injection valve 1 has a nozzle needle 5, which is arranged in a fuel chamber 6. Via a high pressure line 7 can be performed under high pressure fuel in the fuel chamber 6. The high pressure line 7 may be connected, for example, in operation with a common rail of a fuel injection system.

Das Brennstoffeinspritzventil 1 weist außerdem eine Drosselplatte 8 auf, in der eine Zulaufdrossel 9 und eine Ablaufdrossel 10 ausgestaltet sind. Die Drosselplatte 8 weist eine erste Seite 11 und eine von der ersten Seite 11 abgewandte zweite Seite 12 auf. Die erste Seite 11 begrenzt den Brennstoffraum 6. An der ersten Seite 11 liegt eine Steuerraumhülse 13 an, wobei die Steuerraumhülse 13 beispielsweise über eine Dichtkante an der ersten Seite 11 anliegen kann. Die Steuerraumhülse 13 weist eine Führungsbohrung 14 auf, die in diesem Ausführungsbeispiel zylinderförmig ausgestaltet ist. Die Steuerraumhülse 13 ist hierbei hohlzylinderförmig ausgestaltet. In der Führungsbohrung 14 ist die Düsennadel 5 entlang einer Längsachse 15 geführt.The fuel injection valve 1 also has a throttle plate 8, in which an inlet throttle 9 and an outlet throttle 10 are configured. The throttle plate 8 has a first side 11 and a second side 12 facing away from the first side 11. The first side 11 delimits the fuel chamber 6. A control chamber sleeve 13 rests against the first side 11, wherein the control chamber sleeve 13 can rest against the first side 11, for example via a sealing edge. The control chamber sleeve 13 has a guide bore 14, which in This embodiment is designed cylindrical. The control chamber sleeve 13 is designed in this case as a hollow cylinder. In the guide bore 14, the nozzle needle 5 is guided along a longitudinal axis 15.

Zwischen der ersten Seite 11 der Drosselplatte 8 und einer Stirnseite 16 der Düsennadel 5 ist ein Steuerraum 20 ausgebildet, der in einen ersten Steuerraumteil 21 und einen zweiten Steuerraumteil 22 aufgeteilt ist. Hierbei ist ein bewegbares Absperrelement 23 vorgesehen, das entlang der Längsachse 15 in der Führungsbohrung 14 geführt ist. Das Absperrelement 23 kann beispielsweise als Absperrkolben 23 ausgestaltet sein. Das Absperrelement 23 ist in diesem Ausführungsbeispiel im Wesentlichen zylinderförmig ausgestaltet. Das Absperrelement 23 weist eine erste Stirnseite 24 auf, die der ersten Seite 11 der Drosselplatte 8 zugewandt ist. Ferner weist das Absperrelement 23 eine zweite Stirnseite 25 auf, die der Stirnseite 16 der Düsennadel 5 zugewandt ist. Der erste Steuerraumteil 21 ist zwischen der ersten Stirnseite 24 des Absperrelements 23 und der ersten Seite 11 der Drosselplatte 8 ausgebildet. Der zweite Steuerraumteil 22 ist zwischen der zweiten Stirnseite 25 des Absperrelements 23 und der Stirnseite 16 der Düsennadel 5 ausgebildet.Between the first side 11 of the throttle plate 8 and an end face 16 of the nozzle needle 5, a control chamber 20 is formed, which is divided into a first control chamber part 21 and a second control chamber part 22. Here, a movable shut-off element 23 is provided, which is guided along the longitudinal axis 15 in the guide bore 14. The shut-off element 23 may be configured, for example, as a shut-off piston 23. The shut-off element 23 is designed substantially cylindrical in this embodiment. The shut-off element 23 has a first end face 24, which faces the first side 11 of the throttle plate 8. Furthermore, the shut-off element 23 has a second end face 25, which faces the end face 16 of the nozzle needle 5. The first control chamber part 21 is formed between the first end face 24 of the shut-off element 23 and the first side 11 of the throttle plate 8. The second control chamber part 22 is formed between the second end face 25 of the shut-off element 23 and the end face 16 of the nozzle needle 5.

Der erste Steuerraumteil 21 ist über eine gedrosselte Verbindung mit dem zweiten Steuerraumteil 22 verbunden. In diesem Ausführungsbeispiel ist die gedrosselte Verbindung durch eine gedrosselte Verbindungsbohrung 26, die sich durch das Absperrelement 23 erstreckt, gebildet. Die gedrosselte Verbindung zwischen dem ersten Steuerraumteil 21 und dem Steuerraum 22 kann allerdings auch durch eine geeignete Aussparung zwischen dem Absperrelement 23 und der Steuerraumhülse 13 gebildet sein.The first control room part 21 is connected via a throttled connection with the second control room part 22. In this embodiment, the restricted connection is formed by a throttled connection bore 26 which extends through the shut-off element 23. However, the throttled connection between the first control chamber part 21 and the control chamber 22 may also be formed by a suitable recess between the shut-off element 23 and the control chamber sleeve 13.

Die Ablaufdrossel 10 und die Zulaufdrossel 9 münden beide in den ersten Steuerraumteil 21. In der in der Fig. 1 dargestellten Stellung des Absperrelements 23 besteht somit eine direkte Verbindung der Zulaufdrossel 9 mit der Ablaufdrossel 10 über den ersten Steuerraumteil 21. Wenn der Aktor 3 das Steuerventil 2 betätigt, um den Steuerraum 20 über die Ablaufdrossel 10 zu entlasten, dann fällt der Druck im Steuerraum 20 ab. Hierdurch bewegt sich das Absperrelement 23 in einer Richtung 27. Da gleichzeitig der Druck im zweiten Steuerraumteil 22 abfällt, bewegt sich auch die Düsennadel 5 in der Richtung 27. Dadurch öffnet das Brennstoffeinspritzventil 1 und Brennstoff aus dem Brennstoffraum 6 kann beispielsweise in den Brennraum einer Brennkraftmaschine eingespritzt werden.The outlet throttle 10 and the inlet throttle 9 both open into the first control chamber part 21. In the in the Fig. 1 Thus, when the actuator 3 actuates the control valve 2 to relieve the control chamber 20 via the outlet throttle 10, the pressure in the control chamber 20 drops from. As a result, the shut-off element 23 moves in a direction 27. Since the pressure in the second control chamber part 22 drops at the same time, the nozzle needle 5 also moves in the direction 27. This opens the fuel injection valve 1 and fuel from the fuel chamber 6 can, for example, enter the combustion chamber of an internal combustion engine be injected.

Durch die Bewegung des Absperrelements 23 gelangt dieses in eine Absperrstellung. Hierbei wirkt ein an dem Absperrelement 23 ausgestalteter Schließkörper 28 mit einem Absperrsitz 29 der Zulaufdrossel 9 zusammen. Die Zulaufdrossel 9 mündet an dem Absperrsitz 29 in den ersten Steuerraumteil 21. In der Absperrstellung verschließt der Schließkörper 28 des Absperrelements 23 den Absperrsitz 29 der Zulaufdrossel 9, so dass das Absperrelement 23 mit dem Absperrsitz 29 zu einem geschlossenen Dichtsitz zusammenwirkt. Die Zulaufdrossel 9 ist dann am Absperrsitz 29 verschlossen.By the movement of the shut-off element 23, this enters a shut-off position. In this case, a closing body 28 configured on the shut-off element 23 cooperates with a shut-off seat 29 of the inlet throttle 9. The inlet throttle 9 opens at the Absperrsitz 29 in the first control chamber part 21. In the shut-off closes the closing body 28 of the shut-off 23 the Absperrsitz 29 of the inlet throttle 9, so that the shut-off element 23 cooperates with the Absperrsitz 29 to a closed sealing seat. The inlet throttle 9 is then closed at Absperrsitz 29.

In der Absperrstellung wird somit ein Nachfließen von Brennstoff aus der Hochdruckleitung 7 über die Zulaufdrossel 9 in den ersten Steuerraumteil 21 des Steuerraums 20 vollständig unterbrochen. Hierdurch verringert sich auch die Brennstoffmenge, die bei der Betätigung des Steuerventils 2 über die Ablaufdrossel 10 zum Niederdruck abfließen kann.In the shut-off position, a subsequent flow of fuel from the high-pressure line 7 via the inlet throttle 9 into the first control chamber part 21 of the control chamber 20 is thus completely interrupted. This also reduces the amount of fuel that can flow to the low pressure during the actuation of the control valve 2 via the outlet throttle 10.

Durch die gedrosselte Verbindungsbohrung 26 kann sich die Düsennadel 5 weiter nach oben bewegen. Somit kann ein vollständiges Öffnen der Düsennadel 5 erreicht werden. Die gedrosselte Verbindungsbohrung 26 ermöglicht hierbei eine Dämpfung.Due to the throttled connection bore 26, the nozzle needle 5 can move further upwards. Thus, a complete opening of the nozzle needle 5 can be achieved. The throttled connection bore 26 in this case allows damping.

Bei der Bewegung des Absperrelements 23 in der Richtung 27 ist der Druck im ersten Steuerraumteil 21 zumindest näherungsweise gleich groß wie der Druck im zweiten Steuerraumteil 22, da sich über die gleich großen Stirnseiten 24, 25 ein Kräftegleichgewicht am Absperrelement 23 einstellt. In der Absperrstellung, in der der Absperrsitz 29 geschlossen ist, wird der Zufluss zum Steuerraum 20 über die Zulaufdrossel 9 unterbrochen. Wenn das Steuerventil 2 wieder geschlossen ist, dann erhöht sich der Druck im zweiten Steuerraumteil 22 auf Grund der fortschreitenden Nadelbewegung der Düsennadel 5, bis die Nadel zum Stillstand kommt. Der Druck unterhalb des Absperrsitzes 29 kann das Absperrelement 23 wieder entgegen der Richtung 27 bewegen, so dass die Zulaufdrossel 9 geöffnet wird. Damit beginnt der Schließvorgang der Düsennadel 5.During the movement of the shut-off element 23 in the direction 27, the pressure in the first control chamber part 21 is at least approximately the same as the pressure in the second control chamber part 22, since an equilibrium of forces is established on the shut-off element 23 via the identically sized end faces 24, 25. In the shut-off position, in which the shut-off seat 29 is closed, the inflow to the control chamber 20 via the inlet throttle 9 is interrupted. When the control valve 2 is closed again, the pressure in the second control chamber part 22 increases due to the progressive needle movement of the nozzle needle 5 until the needle comes to a standstill. The pressure below the Absperrsitzes 29, the shut-off element 23 again move against the direction 27, so that the inlet throttle 9 is opened. This starts the closing process of the nozzle needle. 5

Je nach Ausgestaltung des Brennstoffeinspritzventils 1 kann auch mit Hilfe einer Bypass-Drossel ein Rückfluss von Brennstoff über die Ablaufdrossel 10 in den ersten Steuerraumteil 21 erfolgen, um die Schließbewegung der Düsennadel 5 zu beschleunigen.Depending on the configuration of the fuel injection valve 1, a return flow of fuel via the outlet throttle 10 into the first control chamber part 21 can also take place with the aid of a bypass throttle in order to accelerate the closing movement of the nozzle needle 5.

Fig. 2 zeigt ein Diagramm zur Erläuterung der Funktionsweise des Brennstoffeinspritzventils 1 entsprechend einem Ausführungsbeispiel. Hierbei ist an der Abszisse des Diagramms die Zeit t angetragen. In dem Diagramm sind ein Ventilhub 30, ein Nadelhub 31 und ein Durchfluss 32 durch die Zulaufdrossel 9 in Form von exemplarischen Kurven dargestellt. Der Ventilhub 30 veranschaulicht hierbei die Öffnungs- und Schließbewegung des Steuerventils 2. Der Nadelhub 31 veranschaulicht die Öffnungs- und Schließbewegung der Düsennadel 5. Der Durchfluss 32 durch die Zulaufdrossel 9 veranschaulicht den aus der Hochdruckleitung 7 über die Zulaufdrossel 9 in den ersten Steuerraumteil 21 des Steuerraums 20 nachfließenden Brennstoff. Die Fläche unter der Kurve 32 ist hierbei ein Maß für die nachfließende, unter hohem Druck stehende Brennstoffmenge. In dem Diagramm ist hierbei exemplarisch der Ablauf einer Betätigung dargestellt. Fig. 2 shows a diagram for explaining the operation of the fuel injection valve 1 according to an embodiment. Here, the time t is plotted on the abscissa of the diagram. The diagram shows a valve lift 30, a needle lift 31 and a flow 32 through the inlet throttle 9 in the form of exemplary curves. The needle stroke 31 illustrates the opening and closing movement of the nozzle needle 5. The flow 32 through the inlet throttle 9 illustrates that from the high pressure line 7 via the inlet throttle 9 in the first control chamber part 21 of the Control room 20 nachfließenden fuel. The area under the curve 32 is hereby Measure of the flowing, under high pressure fuel quantity. In the diagram, the sequence of an actuation is shown here by way of example.

Zum Zeitpunkt t1 betätigt der Aktor 3 das Steuerventil 2. Hierdurch fällt der Druck im Steuerraum 20 ab. Kurz nach dem Zeitpunkt t1, nämlich zum Zeitpunkt t2, bewegen sich daher das Absperrelement 23 und die Düsennadel 5 in der Richtung 27. Zum Zeitpunkt t3 wird der maximale Hub der Düsennadel 5 erreicht. Bereits vor dem Zeitpunkt t3 kann das Steuerventil 2 wieder geschlossen werden. Da sich während der Öffnungsbewegung der Düsennadel 5, das heißt zwischen dem Zeitpunkt t2 und dem Zeitpunkt t3, das Absperrelement 23 bereits vergleichsweise früh in der Absperrstellung befindet, erfolgt kein Durchfluss von Brennstoff durch die Zulaufdrossel 9 oder solch ein Durchfluss ist zumindest vernachlässigbar, wie es speziell bei dem anhand der Fig. 3 beschriebenen Ausführungsbeispiel der Fall ist.At the time t1, the actuator 3 actuates the control valve 2. As a result, the pressure in the control chamber 20 drops. Shortly after time t1, namely at time t2, therefore, the shut-off element 23 and the nozzle needle 5 move in the direction 27. At time t3, the maximum stroke of the nozzle needle 5 is reached. Even before the time t3, the control valve 2 can be closed again. Since during the opening movement of the nozzle needle 5, that is, between the time t2 and the time t3, the shut-off 23 is already comparatively early in the shut-off, there is no flow of fuel through the inlet throttle 9 or such a flow is at least negligible, as it especially in the case of the Fig. 3 described embodiment is the case.

Nach dem Zeitpunkt t3 schließt die Düsennadel 5, wobei sich die Düsennadel 5 entgegen der Richtung 27 bewegt. Um den Druck im Steuerraum 20 aufzubauen, muss jetzt Brennstoff über die Zulaufdrossel 9 nachließen. Dies erfolgt ab dem Zeitpunkt t4. In diesem Ausführungsbeispiel ist zum Zeitpunkt t5 das Steuerventil 2 wieder vollständig geschlossen. Bis zum vollständigen Schließen der Düsennadel 5, das heißt bis zum Zeitpunkt t6, nimmt das Volumen des Steuerraums 20 zu, so dass sich ein Durchfluss 32 durch die Zulaufdrossel 9 ergibt. Wenn die Düsennadel 5 ihre Endposition (Schließstellung) erreicht, dann endet auch der Nachfluss von Brennstoff durch die Zulaufdrossel 9, was zum Zeitpunkt t6 der Fall ist.After the time t3, the nozzle needle 5 closes, with the nozzle needle 5 moving counter to the direction 27. In order to build up the pressure in the control chamber 20, fuel now has to be released via the inlet throttle 9. This takes place from the time t4. In this embodiment, the control valve 2 is fully closed again at time t5. Until the nozzle needle 5 is completely closed, that is to say until the time t6, the volume of the control chamber 20 increases, so that a flow 32 through the inlet throttle 9 results. When the nozzle needle 5 reaches its end position (closed position), then the supply of fuel through the inlet throttle 9 ends, which is the case at time t6.

Wesentlich ist somit die Sperrung des Durchflusses 32 durch die Zulaufdrossel 9 während der Öffnungsphase der Düsennadel 5, das heißt zwischen dem Zeitpunkt t2 und dem Zeitpunkt t3. Ohne die Sperrfunktion des Absperrelements 23 würde es bereits mit der Öffnung der Düsennadel 5 zu einem Nachfluss von Brennstoff über die Zulaufdrossel 9 kommen. Dies würde die Steuermenge erheblich vergrößern. Die zusätzliche Steuermenge würde dann über die Ablaufdrossel 10 zum Niederdruck abfließen. Bei der Ausgestaltung entsprechend dem Ausführungsbeispiel, wie es in dem Diagramm veranschaulicht ist, ist die Steuermenge erheblich reduziert.It is therefore essential to block the flow 32 through the inlet throttle 9 during the opening phase of the nozzle needle 5, that is between the time t2 and the time t3. Without the blocking function of the shut-off element 23, there would already be a supply of fuel via the inlet throttle 9 with the opening of the nozzle needle 5. This would increase the tax amount considerably. The additional control amount would then flow through the outlet throttle 10 to the low pressure. In the embodiment according to the embodiment, as illustrated in the diagram, the control amount is considerably reduced.

Fig. 3 zeigt ein Brennstoffeinspritzventil 1 in einer auszugsweisen, schematischen Schnittdarstellung entsprechend einem zweiten nicht erfindungsgemäßes Ausführungsbeispiel. In diesem Ausführungsbeispiel ist die Führungsbohrung 14 der Steuerraumhülse 13 als Stufenbohrung 14 ausgestaltet. Die Führungsbohrung 14 weist hierdurch eine Stufe 35 auf. Außerdem weist das Absperrelement 23 einen Bund 36 auf, an dem ein Absatz 37 ausgestaltet ist. Ausgehend von der in der Fig. 3 dargestellten Absperrstellung kann das Absperrelement 23 entgegen der Richtung 27 einen Verstellweg (Hub) 38 ausführen. Somit ist eine Begrenzung des Verstellwegs 38 durch Anschlagen des Absatzes 37 des Absperrelements 23 an der Stufe 35 gegeben. Zur Begrenzung des Verstellwegs 38 wirkt das Absperrelement 28 somit mit seinem Absatz 37 mit der Stufe 35 der Führungsbohrung 14 zusammen. Fig. 3 shows a fuel injection valve 1 in a partial, schematic sectional view according to a second non-inventive embodiment. In this embodiment, the guide bore 14 of the control chamber sleeve 13 is designed as a stepped bore 14. The guide bore 14 thereby has a step 35. In addition, the shut-off element 23 has a collar 36, on which a paragraph 37th is designed. Starting from the in the Fig. 3 Shut-off position shown, the shut-off element 23 opposite to the direction 27 perform an adjustment (stroke) 38. Thus, a limitation of the adjustment path 38 is given by striking the shoulder 37 of the shut-off element 23 at the level 35. To limit the adjustment 38, the shut-off element 28 thus interacts with its shoulder 37 with the step 35 of the guide bore 14.

Das Absperrelement 23 kann insbesondere eine gedrosselte Verbindungsbohrung 26 aufweisen, wie sie anhand der Fig. 1 beschrieben ist. Auch andere Ausgestaltungen sind möglich, beispielsweise die anhand der Fig. 6 beschriebene Ausgestaltung.The shut-off element 23 may in particular have a throttled connection bore 26, as described on the basis of Fig. 1 is described. Other embodiments are possible, for example, based on the Fig. 6 described embodiment.

Fig. 4 zeigt ein Brennstoffeinspritzventil 1 in einer auszugsweisen, schematischen Schnittdarstellung entsprechend einem dritten nicht erfindungsgemäßen Ausführungsbeispiel. In diesem Ausführungsbeispiel ist das Absperrelement 23 in der Absperrstellung dargestellt, wobei der erste Steuerraumteil 21 des Steuerraums 20 zumindest näherungsweise verschwindet. Beim Verstellen des Absperrelements 23 entgegen der Richtung 27 nimmt das Volumen des ersten Steuerraumteils 21 zu. In diesem Ausführungsbeispiel ist die Führungsbohrung 14 als Stufenbohrung 14 ausgestaltet. Hierbei ist das Absperrelement 23 als zylinderförmiger Absperrkolben 23 ausgestaltet, der bei einer Verstellung entgegen der Richtung 27 mit seiner zweiten Stirnseite 25 an der Stufe 35 der Führungsbohrung 14 anschlägt, wenn der maximale Verstellweg 38 erreicht ist. Somit ist eine Begrenzung des Verstellwegs 38 gegeben. In diesem Ausführungsbeispiel ist ein Durchmesser der Düsennadel 5 kleiner als ein Durchmesser des Absperrelements 23. Fig. 4 shows a fuel injection valve 1 in a partial, schematic sectional view according to a third non-inventive embodiment. In this embodiment, the shut-off element 23 is shown in the shut-off position, wherein the first control chamber part 21 of the control chamber 20 at least approximately disappears. When adjusting the shut-off element 23 against the direction 27, the volume of the first control chamber part 21 increases. In this embodiment, the guide bore 14 is configured as a stepped bore 14. Here, the shut-off element 23 is configured as a cylindrical shut-off piston 23 which abuts against the direction 27 with its second end face 25 at the stage 35 of the guide bore 14 in an adjustment, when the maximum adjustment path 38 is reached. Thus, a limitation of the adjustment path 38 is given. In this embodiment, a diameter of the nozzle needle 5 is smaller than a diameter of the shut-off element 23.

Das Absperrelement 23 kann beispielsweise eine gedrosselte Verbindungsbohrung 26, wie sie anhand der Fig. 1 beschrieben ist, oder auch eine andere Ausgestaltung von gedrosselten Verbindungen, wie sie beispielsweise anhand der Fig. 6 beschrieben ist, aufweisen.The shut-off element 23 may, for example, a throttled connection bore 26, as they are based on the Fig. 1 is described, or even another embodiment of throttled connections, as for example with reference to the Fig. 6 is described.

Somit sind unterschiedliche Ausgestaltungen der Düsennadel 5 und des Absperrelements 23 möglich. Speziell kann ein Durchmesser des Absperrelements 23 zumindest abschnittsweise gleich, kleiner oder größer als ein Durchmesser der Düsennadel 5 gewählt werden.Thus, different embodiments of the nozzle needle 5 and the shut-off element 23 are possible. Specifically, a diameter of the shutoff element 23 at least in sections equal to, smaller or larger than a diameter of the nozzle needle 5 can be selected.

Fig. 5 zeigt ein Brennstoffeinspritzventil 1 in einer auszugsweisen, schematischen Schnittdarstellung entsprechend einem vierten nicht erfindungsgemäßen Ausführungsbeispiel. Bei diesem Ausführungsbeispiel ist wie bei dem anhand der Fig. 3 beschriebenen Ausführungsbeispiel ein Absperrelement 23 mit einem Bund 36 in der als Stufenbohrung 14 ausgestalteten Führungsbohrung 14 angeordnet. Zusätzlich ist ein Federelement 40 vorgesehen, das zwischen der Stufe 35 der Führungsbohrung 14 und dem Absatz 37 des Absperrelements 23 angeordnet ist. Das Federelement 40 beaufschlagt das Absperrelement 23 in der Richtung 27 mit einer Federkraft, wenn das Federelement 40 durch eine entsprechende Bewegung des Absperrelements 23 entgegen der Richtung 27 vorgespannt wird. Hierdurch ist eine Ausgangslage (Anfangslage) des Absperrelements 23 definiert. Das Federelement 40 ist in diesem Ausführungsbeispiel als Blattfeder 40 ausgestaltet. Bei einer abgewandelten Ausgestaltung kann das Federelement 40 das Absperrelement 23 auch entgegen der Richtung 27 beaufschlagen, um die Ausgangslage zu definieren. Fig. 5 shows a fuel injection valve 1 in a partial, schematic sectional view according to a fourth embodiment not according to the invention. In this embodiment, as in the case of the Fig. 3 described embodiment, a shut-off element 23 with a collar 36 in the designed as a stepped bore 14 Guide bore 14 is arranged. In addition, a spring element 40 is provided which is arranged between the step 35 of the guide bore 14 and the shoulder 37 of the shut-off element 23. The spring element 40 acts on the shut-off element 23 in the direction 27 with a spring force when the spring element 40 is biased against the direction 27 by a corresponding movement of the shut-off element 23. As a result, a starting position (initial position) of the shut-off element 23 is defined. The spring element 40 is configured in this embodiment as a leaf spring 40. In a modified embodiment, the spring element 40, the shut-off element 23 also act against the direction 27 to define the starting position.

Es ist anzumerken, dass bei den anhand der Fig. 3 bis 5 beschriebenen Ausführungsbeispielen 2 bis 4 eine Begrenzung des Zulaufs über die Zulaufdrossel 9 realisiert ist, wie es beispielsweise anhand der Fig. 1 oder anhand der Fig. 5 beschrieben ist.It should be noted that in the case of the Fig. 3 to 5 2 to 4, a limitation of the inlet via the inlet throttle 9 is realized, as for example with reference to Fig. 1 or on the basis of Fig. 5 is described.

Fig. 6 zeigt ein Brennstoffeinspritzventil 1 in einer auszugsweisen, schematischen Schnittdarstellung entsprechend einem erfindungsgemäßen Ausführungsbeispiel. In diesem Ausführungsbeispiel ist das Absperrelement 23 mit einer zylinderförmigen Grundform ausgestaltet. Allerdings ist an der zweiten Stirnseite 25 des Absperrelements 23 ein ringförmiger Absatz ausgestaltet, in den ein Federelement 41 eingesetzt ist. Ferner weist die Düsennadel 5 an ihrer Stirnseite 16 einen ringförmigen Absatz auf, den das Federelement 41 umschließt. Hierdurch beaufschlagt das Federelement 41 das Absperrelement 23 in Abhängigkeit von der momentanen Stellung der Düsennadel 5 in der Richtung 27 mit einer Federkraft. Fig. 6 zeigt das Absperrelement 23 hierbei in der Absperrstellung. Fig. 6 shows a fuel injection valve 1 in a partial, schematic sectional view according to an embodiment of the invention. In this embodiment, the shut-off element 23 is designed with a cylindrical basic shape. However, on the second end face 25 of the shut-off element 23, an annular shoulder is configured in which a spring element 41 is inserted. Furthermore, the nozzle needle 5 has on its end face 16 an annular shoulder, which surrounds the spring element 41. As a result, the spring element 41 urges the shut-off element 23 in response to the instantaneous position of the nozzle needle 5 in the direction 27 with a spring force. Fig. 6 shows the shut-off element 23 in this case in the shut-off position.

Die Zulaufdrossel 9 weist einen Ausgang 42 auf, an dem die Zulaufdrossel 9 in den ersten Steuerraumteil 21 des Steuerraums 20 mündet. Dem Ausgang 42 der Zulaufdrossel 9 ist in diesem Ausführungsbeispiel ein Vorsprung 43 zugeordnet, der in der Absperrstellung den Ausgang 42 umschließt.The inlet throttle 9 has an outlet 42, at which the inlet throttle 9 opens into the first control chamber part 21 of the control chamber 20. The output 42 of the inlet throttle 9, a projection 43 is assigned in this embodiment, which encloses the output 42 in the shut-off position.

Das Absperrelement 23 weist eine gedrosselte Füllbohrung 44 auf, die die Zulaufdrossel 9 mit dem zweiten Steuerraumteil 22 verbindet. Hierdurch führt die Zulaufdrossel 9 nicht mehr in den ersten Steuerraumteil 21, wenn sich das Absperrelement 23 in der Absperrstellung befindet.The shut-off element 23 has a throttled filling bore 44, which connects the inlet throttle 9 with the second control chamber part 22. As a result, the inlet throttle 9 no longer leads into the first control chamber part 21 when the shut-off element 23 is in the shut-off position.

Ferner weist das Absperrelement 23 die gedrosselte Verbindungsbohrung 26 auf. Von der Zulaufdrossel 9 über die gedrosselte Füllbohrung 44, den zweiten Steuerraumteil 22 und die gedrosselte Verbindungsbohrung 26 zur Ablaufdrossel 10 ergibt sich eine große Drosselwirkung, so dass die Steuermenge reduziert ist. Andererseits kann bei dieser Ausgestaltung der zweite Steuerraumteil 22 des Steuerraums 20 vergleichsweise schnell befüllt werden, da diesbezüglich nur die Drosselwirkung der gedrosselten Füllbohrung 44 wirkt. Somit kann ein Schließen der Düsennadel 5 beschleunigt werden.Furthermore, the shut-off element 23 has the throttled connection bore 26. From the inlet throttle 9 via the throttled filling bore 44, the second control chamber part 22 and the throttled connection bore 26 to the outlet throttle 10 results in a large throttle effect, so that the control amount is reduced. On the other hand, in this embodiment, the second control chamber part 22 of the control chamber 20 can be filled relatively quickly, since in this respect only the throttling action of the throttled filling bore 44 acts. Thus, closing of the nozzle needle 5 can be accelerated.

Bei diesem Ausführungsbeispiel befindet sich eine Drossel 45 der gedrosselten Füllbohrung 44 in der Nähe der zweiten Stirnseite 25 des Absperrelements 23. Ferner befindet sich eine Drossel 46 der gedrosselten Verbindungsbohrung 26 in der Nähe der zweiten Stirnseite 25 des Absperrelements 23.In this embodiment, there is a throttle 45 of the throttled filling bore 44 in the vicinity of the second end face 25 of the shut-off element 23. Further, there is a throttle 46 of the throttled connection bore 26 in the vicinity of the second end face 25 of the shut-off element 23rd

Somit kann die Zulaufdrossel 9 bei geöffnetem Steuerventil 2 zumindest zeitweise verschlossen werden oder es kann zumindest eine Reduzierung der zugeführten Hochdruckmenge erreicht werden. Bei geschlossenem Steuerventil 2 wird die Zulaufdrossel 9 wieder freigegeben. Somit kann eine permanente Verbindung zwischen dem Hochdruckbereich und dem Niederdruckbereich wesentlich gedämpft oder ganz vermieden werden. Somit kann die Steuermenge deutlich reduziert werden. Dadurch wird auch die Temperatur im Rücklauf deutlich reduziert. Ein weiterer Vorteil ist, dass die Drosselwirkung der Ablaufdrossel 10 und die Drosselwirkung der Zulaufdrossel 9 innerhalb gewisser Grenzen frei gewählt werden können. Dadurch ist eine flexible Definition der Öffnungs- und Schließgeschwindigkeit der Düsennadel 5 möglich.Thus, the inlet throttle 9 can be closed at least temporarily with the control valve 2 open, or at least a reduction of the supplied high-pressure quantity can be achieved. When the control valve 2 is closed, the inlet throttle 9 is released again. Thus, a permanent connection between the high-pressure region and the low-pressure region can be substantially damped or completely avoided. Thus, the control amount can be significantly reduced. As a result, the temperature in the return is significantly reduced. Another advantage is that the throttle effect of the outlet throttle 10 and the throttling action of the inlet throttle 9 can be freely selected within certain limits. As a result, a flexible definition of the opening and closing speed of the nozzle needle 5 is possible.

Somit kann der Wirkungsgrad des Brennstoffeinspritzventils 1 verbessert werden. Dadurch ergeben sich insbesondere geringere Kohlendioxidemissionen eines Kraftfahrzeugs oder dergleichen.Thus, the efficiency of the fuel injection valve 1 can be improved. This results in particular lower carbon dioxide emissions of a motor vehicle or the like.

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

Claims (6)

  1. Fuel injection valve (1), in particular injector for fuel injection systems of air-compressing, auto-ignition internal combustion engines, having a control valve (2), a control chamber (20) and a nozzle needle (5), wherein an outflow throttle (10) and an inflow throttle (9) for the control chamber (20) are provided, and wherein the control valve (2) serves for controlling a flow through the outflow throttle (10), and a movable shut-off element (23) is provided which divides the control chamber (20) into a first control chamber part (21) and a second control chamber part (22), wherein the outflow throttle (10) and the inflow throttle (9) issue into the first control chamber part (21), and wherein the nozzle needle (5) can be actuated by means of a control chamber pressure in the second control chamber part (22), and the shut-off element (23), in a shut-off position, blocks at least a direct connection between the outflow throttle (10) and the inflow throttle (9) via the first control chamber part (21), characterized in that the shut-off element (23) has a throttled fill bore (44), and in that the shut-off element (23), in the shut-off position, connects the inflow throttle (9) to the second control chamber part (22) via the throttled fill bore (44), wherein the shut-off element (23) has a throttled connecting bore (26) which connects the first control chamber part (21) and the second control chamber part (22).
  2. Fuel injection valve according to Claim 1, characterized in that the movable shut-off element (23), in the shut-off position, blocks a connection between the outflow throttle (10) and the inflow throttle (9) via the first control chamber part (21).
  3. Fuel injection valve according to Claim 1 or 2, characterized in that the shut-off element (23) and the nozzle needle (5) are guided in a guide bore (14) along a longitudinal axis (15), and in that an adjustment travel (38) of the shut-off element (23) in the direction of the nozzle needle (5) is restricted.
  4. Fuel injection valve according to Claim 3, characterized in that the guide bore (14) is designed as a stepped bore (14), and in that, for the restriction of the adjustment travel (38) in the direction of the nozzle needle (5), the shut-off element (23) interacts with a step (35) of the guide bore (14).
  5. Fuel injection valve according to Claim 4, characterized in that a spring element (40) is provided which is arranged between the step (35) of the guide bore (14) and the shut-off element (23).
  6. Fuel injection valve according to one of Claims 1 to 5, characterized in that a control chamber sleeve (13) is provided, in that a throttle plate (8) is provided, in which the outflow throttle (10) and the inflow throttle (9) are formed, in that the control chamber sleeve (13) interacts with the throttle plate (8), in that the shut-off element (23) and the nozzle needle (5) are guided in a guide bore (14) of the control chamber sleeve (13) along a longitudinal axis (15), and in that the control chamber (20) is formed in the guide bore (14) and is delimited at one side by a side (11) of the throttle plate (8) and at the other side by a face side (16) of the nozzle needle (5).
EP20130152177 2012-02-20 2013-01-22 Fuel injector valve Not-in-force EP2628939B1 (en)

Applications Claiming Priority (1)

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DE201210202546 DE102012202546A1 (en) 2012-02-20 2012-02-20 Fuel injector

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EP2628939B1 true EP2628939B1 (en) 2015-03-18

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GB201517148D0 (en) * 2015-09-29 2015-11-11 Delphi Int Operations Lux Srl Fuel injector

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DE10139623A1 (en) 2001-08-11 2003-02-27 Bosch Gmbh Robert Injection arrangement for fuel storage injection system has bypass channel from high-pressure chamber to valve chamber closed by valve closure element during injection process
WO2005019637A1 (en) * 2003-08-22 2005-03-03 Ganser-Hydromag Ag Fuel injection valve controlled by a pilot valve
RU2438035C2 (en) * 2006-03-03 2011-12-27 Ганзер-Хюдромаг Аг Injection fuel valve for internal combustion engine (versions)
JP5493966B2 (en) * 2009-06-02 2014-05-14 株式会社デンソー Fuel injection device

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