EP1454053B1 - Fuel injection valve - Google Patents
Fuel injection valve Download PDFInfo
- Publication number
- EP1454053B1 EP1454053B1 EP02774434A EP02774434A EP1454053B1 EP 1454053 B1 EP1454053 B1 EP 1454053B1 EP 02774434 A EP02774434 A EP 02774434A EP 02774434 A EP02774434 A EP 02774434A EP 1454053 B1 EP1454053 B1 EP 1454053B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- fuel injection
- injection valve
- hydraulic fluid
- valve
- actuator
- 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.)
- Expired - Lifetime
Links
- 239000000446 fuel Substances 0.000 title claims abstract description 79
- 238000002347 injection Methods 0.000 title claims abstract description 52
- 239000007924 injection Substances 0.000 title claims abstract description 52
- 239000012530 fluid Substances 0.000 claims abstract description 43
- 238000002485 combustion reaction Methods 0.000 claims abstract description 13
- 238000007789 sealing Methods 0.000 claims description 8
- 230000036316 preload Effects 0.000 claims 1
- 239000007789 gas Substances 0.000 description 6
- 238000011010 flushing procedure Methods 0.000 description 5
- 230000016507 interphase Effects 0.000 description 5
- 230000002349 favourable effect Effects 0.000 description 3
- 230000003797 telogen phase Effects 0.000 description 3
- 230000009471 action Effects 0.000 description 2
- 230000008901 benefit Effects 0.000 description 2
- 230000008859 change Effects 0.000 description 2
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 238000001816 cooling Methods 0.000 description 2
- 238000010438 heat treatment Methods 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 239000002184 metal Substances 0.000 description 2
- 230000004044 response Effects 0.000 description 2
- 230000003068 static effect Effects 0.000 description 2
- 230000003044 adaptive effect Effects 0.000 description 1
- 230000032683 aging Effects 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 230000018109 developmental process Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 239000002918 waste heat Substances 0.000 description 1
Images
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
- F02M51/00—Fuel-injection apparatus characterised by being operated electrically
- F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
- F02M51/0603—Injectors peculiar thereto with means directly operating the valve needle using piezoelectric or magnetostrictive operating means
-
- 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
- F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
- F02M61/08—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series the valves opening in direction of fuel flow
-
- 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
- F02M61/167—Means for compensating clearance or thermal expansion
-
- 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
- F02M2200/21—Fuel-injection apparatus with piezoelectric or magnetostrictive elements
Definitions
- the invention relates to a fuel injection valve according to the preamble of the main claim.
- a hydraulic displacement transformer for a piezoelectric actuator of a fuel injection valve which is arranged between the actuator and a valve needle of the fuel injection valve.
- a master piston and a slave piston are in a common axis of symmetry arranged and a hydraulic chamber is disposed between the two pistons.
- a spring is arranged, which presses apart the master cylinder and the slave piston, wherein the master piston in the direction of the actuator and the slave piston are biased in a working direction to a valve needle.
- this stroke movement is transmitted to the slave piston by the pressure of a hydraulic fluid in the hydraulic chamber, since the hydraulic fluid in the hydraulic chamber can not be compressed and only a small portion of the hydraulic fluid through annular gaps between the master piston and a guide bore and slave piston and a guide bore during the short period of a stroke can escape.
- the path transformer automatically adjusts to length expansions and pressure-related expansions of a fuel injection valve.
- a disadvantage of this prior art is that the path transformer is strongly heated by the waste heat of an internal combustion engine.
- the path transformer is arranged in a region of the fuel injection valve, which lies deep in a mounting hole and thus close to the combustion chamber in the assembled fuel injection valve. It can come in the resting phases of the actuator to an evaporation of the fuel and thus to a failure of the fuel injection valve, since the vaporized fuel can be compressed and thereby the valve needle is not opened.
- the DE 30 30 378 A discloses a controllable piezoelectric injection valve, wherein for temperature compensation and for generating the contact pressure of the nozzle needle provided in its valve seat springs should have no negative impact on the piezoelectric caused opening and closing of the nozzle needle. This is achieved by functionally separating the substantially static force action of the spring from the dynamic force action of the piezoelectric body of the valve. Accordingly, the nozzle needle is permanently under the contact pressure of the springs. The nozzle needle is rigidly connected to the piezoelectric body and the piezoelectric body is elastically connected to the housing of the injection valve. For spring-elastic mounting of the piezoelectric body alone, the pressure spring can be used.
- a described fuel injector has an electromechanical actuator which is encapsulated in a metal bellows, mounted within a pressure-fillable working chamber of the housing.
- the actuator is connected at the downstream end face with the valve needle and at the inlet end side with an axially displaceable hydraulic piston.
- a compensation chamber is annular, which is formed by a first fit downstream with the working chamber, and by a second fit on the inlet side with a gap which is formed between a surrounded with a metal bellows smaller diameter of the hydraulic piston and a first bore portion of the housing throttled hydraulically connected.
- the working chamber and said space are connected to the fuel supply, so that the compensation chamber is pressurized from both sides.
- the fuel injection valve according to the invention with the characterizing features of the main claim has the advantage that the compensation chamber is close to a fuel rail and away from the side of the fuel injection valve, which comes into contact with a combustion chamber of an internal combustion engine.
- the fuel injection valve according to the invention therefore has a lower temperature in the region of the compensation chamber than in the prior art. Furthermore, it is advantageous that a larger volume of construction is available for the formation of the compensation chamber.
- a chamber spring is arranged on the compensation chamber side of the pressure piston and exerts on the pressure piston a biasing force which pushes the pressure piston out of the compensation chamber or a guide bore of the pressure piston communicating with the compensation chamber.
- the chamber spring may be a diaphragm spring, a plate spring or a coil spring.
- the actuator exerts no pressure on the pressure piston.
- the pressed movable and slidably mounted actuator which is advanced so far in the direction of the valve needle until it rests against this. Due to the consequent increase in volume of the compensation chamber creates a negative pressure and the hydraulic fluid inlet hydraulic fluid flows into the compensation chamber until the negative pressure is compensated.
- the loss of hydraulic fluid during the working phase of the actuator and the consequent overpressure is compensated. Changes in length of the housing and the transmission path from the valve needle via the actuator to the support of the actuator are thus compensated, since the support of the actuator takes place on the pressure piston, which always advances to the maximum extent in the direction of the valve needle.
- the compensation chamber is supplied with hydraulic fluid which is at a higher pressure than the pressure of the fuel on the actuator side of the pressure piston.
- a force is thereby exerted on the pressure piston, without the need for a chamber spring, during the resting phases of the actuator, which pushes the pressure piston and with it the floating actuator up to the stop on the valve needle.
- This also compensates the leakage losses during the working phase of the actuator and a compensation of the changes in length of the housing or the changes in length of the actuator and the valve needle due to the heating and the fuel pressure during the rest periods of the actuator.
- the hydraulic fluid inlet may include an inlet throttle that allows only a small portion of the equalization chamber volume of hydraulic fluid to flow back during actuation of the actuator.
- the hydraulic fluid inlet may have a check valve and thereby allow a particularly fast filling during the rest periods. If the check valve is designed as a fast responding check valve, backflow losses can be effectively prevented during the working phase of the actuator.
- the hydraulic fluid inlet is in a favorable embodiment, a controllable inlet valve, which is closed in the non-activated state.
- the compensation chamber can be filled up very quickly by a control pulse during the rest phase, since such an inlet valve can release a large cross-section.
- the compensation chamber has a hydraulic fluid drain with an outlet throttle.
- the loss during the actuation phase of the actuator and the resulting increase in pressure is only slight, but during the idle phase of the actuator a steady flushing of the compensation chamber can take place and, advantageously, a cooling of the compensation chamber.
- the compensation chamber to a hydraulic fluid drain with a controllable drain valve, which is closed in the non-driven state in a preferred embodiment.
- the hydraulic fluid drainage of the compensation chamber may alternatively comprise a pressure relief valve.
- a pressure relief valve By increasing the pressure above the limiting pressure of the pressure relief valve, a flushing can be achieved during the idle phase of the actuator.
- a Design of the pressure limiting valve such that the response inertia of the pressure relief valve is greater than the duration of a working phase of the actuator, hydraulic fluid losses can be minimized during the working phase.
- the hydraulic fluid drain in the compensation chamber is arranged at the highest point in the installation position of the fuel injection valve.
- any existing gas bubbles are removed during flushing.
- a functioning of the fuel injection valve can be ensured. Gas bubbles that can be produced by vaporized fuel and due to their compressibility prevent pressure build-up in the compensation chamber are removed safely and quickly.
- the compensation chamber can be filled with fuel, or alternatively be connected to an oil circuit of the internal combustion engine.
- Fig. 1 shows schematically in section and as a schematic diagram of a fuel injection valve 1. It is a fuel injection valve 1 with an outwardly opening valve needle 2, which is connected to a valve closing body 3.
- a valve seat carrier 5 integrally formed or constructed with a valve body 4 has a valve seat surface 6 which forms a sealing seat 7 with the valve closing body 3.
- the valve needle 2 has a spring stop 8, against which the valve spring 9 is supported. At its second end, the valve spring 9 is in contact with a guide sleeve 10 for the valve needle 2.
- the valve spring 9 exerts on the spring stop 8 on the valve needle 2 a bias, which presses the valve closing body 3 against the sealing seat 6.
- An actuator 11 is connected to a guided in a blade 12 Aktorst Schemeel 13. Via leads 14, the actuator 11, power can be supplied. At its end facing away from the sealing seat 6, the actuator 11 is connected to a pressure piston 15, the chamber 17 seals by an elastic seal 16 relative to the valve body 4 a compensation.
- the interconnected and cooperating unit of actuator ram 13, actuator 11 and pressure piston 15 is movably and floatingly supported by the cutting disc 12 via the Aktorst Jardinel 13 and the elastic seal 16 via the pressure piston 15 in the longitudinal axis of the fuel injection valve 1.
- the compensation chamber 17 is continuously supplied with fuel as hydraulic fluid. About a Abflaufdrossel 21 and a fuel outlet 22 also continuously flows from a small amount of fuel.
- Fuel also flows to the sealing seat 6 via the fuel inlet 19 and inlet bores 23 a, 23 b and 23 c.
- valve spring 9 is acted upon at the other end of the actuator 11 via the Aktorst Jardinel 13 with an opening force and the valve needle 2 is actuated with the valve closing body 3, so that the valve closing body 3 lifts from the sealing seat 6. After switching off the flow, the valve spring 9 moves the valve needle 2 back to its original position.
- the chamber spring 18 exerts a pressure force on the pressure piston 15, which holds the actuator 11 with the actuator ram 13 against the spring stop 8 of the valve needle 2 in abutment.
- the actuator 11 is adjusted by the spring forces backlash between hydraulic pad and valve needle. Fuel flows into the compensation chamber 17 via the inlet throttle 20 until it is again completely filled with fuel. If there is a change in length of the valve body 4 or the actuator 11 due to the heating, so the actuator 11 moves with actuator ram 13 and pressure piston 15 in the longitudinal direction of the fuel injector 1 always until it rests against the spring stop 8 of the valve needle. 2 is applied.
- a check valve may be arranged, which releases a large flow cross-section at negative pressure in the compensation chamber 17.
- a pressure relief valve which does not respond due to its inertia during the short operation phase of the actuator 11, but opens at a certain adjustable pressure in the compensation chamber 17 and releases a large flow area.
- Fig. 2 shows a further favorable embodiment of a fuel injection valve according to the invention 1.
- the valve closing body 3 is in operative connection with the valve needle 2 and forms with the valve seat face 6 on the valve seat portion 5, which is formed on the valve body 4, a sealing seat 6.
- pressure piston 15 is connected to the actuator 11, which can be energized via the leads 14.
- the fuel inlet 19 and the supply bores 23a, 23b and 23c the fuel seat 6 is supplied fuel.
- the chamber spring 18 is arranged.
- oil inlet 25 which has a switching valve 26
- the compensation chamber 17 oil is supplied as hydraulic fluid.
- this oil can flow.
- the switching valves 26, 27 release large flow cross sections. After switching off the energization of the actuator 11 can be replenished by the switching valve 26 of the oil inlet 25 quickly the compensation chamber through a large inlet cross section. Likewise, at the same time and to the extent controllable by a switching valve 27 of the oil drain 28 are released and a flushing and cooling of the compensation chamber 17 can be achieved. Similarly, after starting, as well as during operation, it can be prevented that blistering occurs. This danger is further reduced by the use of the medium oil as hydraulic fluid.
Abstract
Description
Die Erfindung geht aus von einem Brennstoffeinspritzventil nach der Gattung des Hauptanspruchs.The invention relates to a fuel injection valve according to the preamble of the main claim.
Aus der
Aus der
In der Ruhephase, wenn der Aktor keine Druckkraft auf den Geberzylinder ausübt, werden durch die Feder der Geberkolben und der Nehmerkolben auseinander gedrückt und durch den entstehenden Unterdruck dringt über die Ringspalte das Hydraulikfluid in die Hydraulikkammer ein und füllt diese wieder auf. Dadurch stellt der Wegtransformator sich automatisch auf Längenausdehnungen und druckbedingte Dehnungen eines Brennstoffeinspritzventils ein.In the resting phase, when the actuator exerts no pressure force on the master cylinder, the master piston and the slave piston are pressed apart by the spring and the resulting negative pressure penetrates through the annular gaps, the hydraulic fluid in the hydraulic chamber and fills them again. As a result, the path transformer automatically adjusts to length expansions and pressure-related expansions of a fuel injection valve.
Nachteilig an diesem Stand der Technik ist, daß der Wegtransformator durch die Abwärme einer Brennkraftmaschine stark erwärmt wird. Der Wegtransformator ist in einem Bereich des Brennstoffeinspritzventils angeordnet, der bei dem montierten Brennstoffeinspritzventil tief in einer Montagebohrung und somit nahe am Brennraum liegt. Es kann in den Ruhephasen des Aktors zu einem Verdampfen des Brennstoffs kommen und somit zu einem Ausfall des Brennstoffeinspritzventils, da sich der verdampfte Brennstoff komprimieren läßt und dadurch die Ventilnadel nicht geöffnet wird.A disadvantage of this prior art is that the path transformer is strongly heated by the waste heat of an internal combustion engine. The path transformer is arranged in a region of the fuel injection valve, which lies deep in a mounting hole and thus close to the combustion chamber in the assembled fuel injection valve. It can come in the resting phases of the actuator to an evaporation of the fuel and thus to a failure of the fuel injection valve, since the vaporized fuel can be compressed and thereby the valve needle is not opened.
Insbesondere besteht diese Gefahr nach dem Abstellen einer heißen Brennkraftmaschine. Das Brennstoffeinspritzsystem - verliert nun seinen Druck. Es kommt besonders leicht zum Verdampfen des Brennstoffs. Bei einem erneuten Startversuch der Brennkraftmaschine kann dies dazu führen, dass die Hubbewegung des Aktors nicht mehr auf eine Ventilnadel übertragen wird und das Brennstoffeinspritzventil nicht funktioniert.In particular, this danger exists after switching off a hot internal combustion engine. The fuel injection system - loses his pressure now. It is particularly easy to evaporate the fuel. In a renewed start attempt of the internal combustion engine, this may mean that the lifting movement of the actuator is no longer transmitted to a valve needle and the fuel injection valve does not work.
In der
Die
Das in der
Das erfindungsgemäße Brennstoffeinspritzventil mit den kennzeichnenden Merkmalen des Hauptanspruchs hat demgegenüber den Vorteil, dass die Ausgleichskammer nahe an einer Brennstoffverteilerleitung liegt und entfernt von der Seite des Brennstoffeinspritzventils, die mit einem Brennraum einer Brennkraftmaschine in Kontakt kommt.The fuel injection valve according to the invention with the characterizing features of the main claim has the advantage that the compensation chamber is close to a fuel rail and away from the side of the fuel injection valve, which comes into contact with a combustion chamber of an internal combustion engine.
Vorteilhaft weist das erfindungsgemäße Brennstoffeinspritzventil daher im Bereich der Ausgleichskammer gegenüber dem Stand der Technik eine niedrigere Temperatur auf. Weiterhin ist vorteilhaft, dass ein größeres Bauvolumen zur Ausbildung der Ausgleichskammer zur Verfügung steht.Advantageously, the fuel injection valve according to the invention therefore has a lower temperature in the region of the compensation chamber than in the prior art. Furthermore, it is advantageous that a larger volume of construction is available for the formation of the compensation chamber.
Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen des im Hauptanspruch angegebenen Brennstoffeinspritzventils möglich.The measures listed in the dependent claims advantageous refinements and improvements of the main claim fuel injector are possible.
Erfindungsgemäß ist eine Kammerfeder auf der Ausgleichskammerseite des Druckkolbens angeordnet und übt auf den Druckkolben eine Vorspannkraft aus, die den Druckkolben aus der Ausgleichskammer oder einer mit der Ausgleichskammer in Verbindung stehenden Führungsbohrung des Druckkolbens herausdrückt. Die Kammerfeder kann eine Membranfeder, eine Tellerfeder oder eine Schraubenfeder sein.According to the invention, a chamber spring is arranged on the compensation chamber side of the pressure piston and exerts on the pressure piston a biasing force which pushes the pressure piston out of the compensation chamber or a guide bore of the pressure piston communicating with the compensation chamber. The chamber spring may be a diaphragm spring, a plate spring or a coil spring.
Während der Ruhephase, in der an dem magnetostriktiven oder piezoelektrischen Aktor keine Spannung anliegt, übt der Aktor auf den Druckkolben keinen Druck aus. Durch die beweglichen und verschiebbar gelagerten Aktor gedrückt, der soweit in Richtung Ventilnadel vorgeschoben wird, bis er an dieser anliegt. Durch die dabei bedingte Volumenvergrößerung der Ausgleichskammer entsteht ein Unterdruck und über den Hydraulikfluidzulauf strömt Hydraulikfluid in die Ausgleichskammer nach, bis der Unterdruck ausgeglichen wird. Somit wird der Verlust an Hydraulikfluid während der Arbeitsphase des Aktors und den dadurch bedingten Überdruck ausgeglichen. Längenänderungen des Gehäuse und des Übertragungsweges von Ventilnadel über Aktor bis zu der Abstützung des Aktors werden somit ausgeglichen, da die Abstützung des Aktors an dem Druckkolben erfolgt, der sich stets bis zum maximalen Maß in Richtung der Ventilnadel vorschiebt.During the resting phase, in which no voltage is applied to the magnetostrictive or piezoelectric actuator, the actuator exerts no pressure on the pressure piston. By the pressed movable and slidably mounted actuator, which is advanced so far in the direction of the valve needle until it rests against this. Due to the consequent increase in volume of the compensation chamber creates a negative pressure and the hydraulic fluid inlet hydraulic fluid flows into the compensation chamber until the negative pressure is compensated. Thus, the loss of hydraulic fluid during the working phase of the actuator and the consequent overpressure is compensated. Changes in length of the housing and the transmission path from the valve needle via the actuator to the support of the actuator are thus compensated, since the support of the actuator takes place on the pressure piston, which always advances to the maximum extent in the direction of the valve needle.
Erfindungsgemäß wird der Ausgleichskammer ein Hydraulikfluid zugeführt, das unter einem höheren Druck wie der Druck des Brennstoffs auf der Aktorseite des Druckkolbens steht.According to the invention, the compensation chamber is supplied with hydraulic fluid which is at a higher pressure than the pressure of the fuel on the actuator side of the pressure piston.
Vorteilhaft wird dadurch auf den Druckkolben, ohne daß es einer Kammerfeder bedarf, eine Kraft während der Ruhephasen des Aktors ausgeübt, die den Druckkolben und mit ihm den schwimmend gelagerten Aktor bis auf Anschlag an die Ventilnadel schiebt. Dadurch erfolgt ebenfalls ein Ausgleich der Leckageverluste während der Arbeitsphase des Aktors und ein Ausgleich der Längenänderungen des Gehäuses bzw. der Längenänderungen des Aktors und der Ventilnadel aufgrund der Erwärmung und des Brennstoffdruckes während der Ruhephasen des Aktors.Advantageously, a force is thereby exerted on the pressure piston, without the need for a chamber spring, during the resting phases of the actuator, which pushes the pressure piston and with it the floating actuator up to the stop on the valve needle. This also compensates the leakage losses during the working phase of the actuator and a compensation of the changes in length of the housing or the changes in length of the actuator and the valve needle due to the heating and the fuel pressure during the rest periods of the actuator.
Der Hydraulikfluidzulauf kann eine Zulaufdrossel aufweisen, die nur einen geringen Teil des Ausgleichskammervolumens an Hydraulikfluid während der Betätigung des Aktors zurückströmen läßt.The hydraulic fluid inlet may include an inlet throttle that allows only a small portion of the equalization chamber volume of hydraulic fluid to flow back during actuation of the actuator.
Während der kurzen Betätigungsphase des Aktors kann dadurch nur wenig Hydraulikfluid abfließen und zurückströmen, aber während der langen Ruhephase des - Aktors genügend Hydraulikfluid nachströmen, um einen Spielausgleich sicherzustellen und die Ausgleichskammer stets aufzufüllen. Der Hydraulikfluidzulauf kann ein Rückschlagventil aufweisen und dadurch ein besonders schnelles Auffüllen während der Ruhephasen ermöglichen. Wenn das Rückschlagventil als schnell ansprechendes Rückschlagventil ausgelegt ist, können Rückströmverluste während der Arbeitsphase des Aktors wirksam verhindert werden.During the short actuation phase of the actuator, only a small amount of hydraulic fluid can flow away and flow back, but enough during the long idle phase of the actuator Add hydraulic fluid to ensure backlash compensation and always top up the compensation chamber. The hydraulic fluid inlet may have a check valve and thereby allow a particularly fast filling during the rest periods. If the check valve is designed as a fast responding check valve, backflow losses can be effectively prevented during the working phase of the actuator.
Der Hydraulikfluidzulauf ist in günstiger Ausführungsform ein ansteuerbares Zulaufventil, das in nicht angesteuerten Zustand geschlossen ist.The hydraulic fluid inlet is in a favorable embodiment, a controllable inlet valve, which is closed in the non-activated state.
Vorteilhaft kann durch einen Ansteuerungsimpuls während der Ruhephase die Ausgleichskammer sehr schnell aufgefüllt werden, da ein solches Zulaufventil einen großen Querschnitt freigeben kann.Advantageously, the compensation chamber can be filled up very quickly by a control pulse during the rest phase, since such an inlet valve can release a large cross-section.
Vorteilhaft weist die Ausgleichskammer einen Hydraulikfluidablauf mit einer Ablaufdrossel auf. Ebenso wie bei dem Hydraulikfluidzufluß ist der Verlust während der Ansteuerungsphase des Aktors und die dadurch entstehende Druckerhöhung nur gering, jedoch kann während der Ruhephase des Aktors ein stetiges Durchspülen der Ausgleichskammer erfolgen und vorteilhaft eine Kühlung der Ausgleichskammer.Advantageously, the compensation chamber has a hydraulic fluid drain with an outlet throttle. As with the hydraulic fluid inflow, the loss during the actuation phase of the actuator and the resulting increase in pressure is only slight, but during the idle phase of the actuator a steady flushing of the compensation chamber can take place and, advantageously, a cooling of the compensation chamber.
Alternativ weist die Ausgleichskammer einen Hydraulikfluidablauf mit einem ansteuerbaren Ablaufventil auf, das im nicht angesteuerten Zustand in bevorzugter Ausführungsform geschlossen ist. Dadurch kann ein besonders großer Querschnitt und eine erhöhte Durchspülung während der Ruhephase erreicht werden.Alternatively, the compensation chamber to a hydraulic fluid drain with a controllable drain valve, which is closed in the non-driven state in a preferred embodiment. As a result, a particularly large cross-section and increased flushing can be achieved during the rest phase.
Der Hydraulikfluidabfluß der Ausgleichskammer kann alternativ ein Druckbegrenzungsventil aufweisen. Durch eine Druckerhöhung über dem Begrenzungsdruck des Druckbegrenzungsventils kann während der Ruhephase des Aktors eine Durchspülung erreicht werden. Durch eine Auslegung des Druckbegrenzungsventils derart, daß die Ansprechträgheit des Druckbegrenzungsventils größer ist, als die Zeitdauer einer Arbeitsphase des Aktors, können Hydraulikfluidverluste während der Arbeitsphase minimiert werden.The hydraulic fluid drainage of the compensation chamber may alternatively comprise a pressure relief valve. By increasing the pressure above the limiting pressure of the pressure relief valve, a flushing can be achieved during the idle phase of the actuator. By a Design of the pressure limiting valve such that the response inertia of the pressure relief valve is greater than the duration of a working phase of the actuator, hydraulic fluid losses can be minimized during the working phase.
In einer günstigen Weiterbildung des erfindungsgemäßen Brennstoffeinspritzventils ist der Hydraulikfluidablauf in der Ausgleichskammer an der in Einbaulage des Brennstoffeinspritzventils höchstgelegensten Stelle angeordnet. Dadurch werden beim Durchspülen eventuell vorhandene Gasblasen entfernt. Insbesondere beim Start einer zuvor in heißem Betriebszustand abgestellten Brennkraftmaschine kann ein Funktionieren des Brennstoffeinspritzventils sichergestellt werden. Gasblasen die durch verdampften Brennstoff entstehen können und aufgrund ihrer Kompressibilität einen Druckaufbau in der Ausgleichskammer verhindern, werden sicher und schnell entfernt.In a favorable development of the fuel injection valve according to the invention, the hydraulic fluid drain in the compensation chamber is arranged at the highest point in the installation position of the fuel injection valve. As a result, any existing gas bubbles are removed during flushing. In particular, at the start of a previously shut down in hot operating condition internal combustion engine, a functioning of the fuel injection valve can be ensured. Gas bubbles that can be produced by vaporized fuel and due to their compressibility prevent pressure build-up in the compensation chamber are removed safely and quickly.
Die Ausgleichskammer kann mit Brennstoff befüllt werden, oder auch alternativ mit einem Ölkreislauf der Brennkraftmaschine verbunden sein.The compensation chamber can be filled with fuel, or alternatively be connected to an oil circuit of the internal combustion engine.
Ausführungsbeispiele der Erfindung sind in der Zeichnung vereinfacht dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigt:
- Fig. 1
- einen schematischen Schnitt durch ein erstes Ausführungsbeispiel eines erfindungsgemäßen Brennstoffeinspritzventils und
- Fig. 2
- einen schematischen Schnitt durch ein zweites Ausführungsbeispiel eines erfindungsgemäßen Brennstoffeinspritzventils.
- Fig. 1
- a schematic section through a first embodiment of a fuel injection valve according to the invention and
- Fig. 2
- a schematic section through a second embodiment of a fuel injection valve according to the invention.
Ein Aktor 11 ist mit einem in einer Trennscheibe 12 geführten Aktorstößel 13 verbunden. Über Anschlußleitungen 14 kann dem Aktor 11 Strom zugeführt werden. An seinem dem Dichtsitz 6 abgewandten Ende ist der Aktor 11 mit einem Druckkolben 15 verbunden, der durch eine elastische Dichtung 16 gegenüber dem Ventilkörper 4 eine Ausgleichs kammer 17 abdichtet. Die miteinander verbundene und zusammenwirkende Einheit aus Aktorstößel 13, Aktor 11 und Druckkolben 15 ist durch die Trennscheibe 12 über den Aktorstößel 13 sowie die elastische Dichtung 16 über den Druckkolben 15 in der Längsachse des Brennstoffeinspritzventils 1 beweglich und schwimmend gelagert. Über einen Brennstoffzulauf 19 und eine Zulaufdrossel 20 wird der Ausgleichskammer 17 kontinuierlich Brennstoff als Hydraulikfluid zugeführt. Über eine Abflaufdrossel 21 und einen Brennstoffablauf 22 fließt ebenso kontinuierlich eine geringfügige Menge Brennstoff ab.An
Ebenfalls über den Brennstoffzulauf 19 und Zulaufbohrungen 23a, 23b und 23c fließt Brennstoff zu dem Dichtsitz 6.Fuel also flows to the sealing seat 6 via the
Wenn der Aktor 11 über die Anschlußleitungen 14 bestromt wird, dehnt er sich in seiner Länge aus und sucht den Druckkolben 15 in die Ausgleichskammer 17 zu drücken. Da der in der Ausgleichskammer 17 enthaltene Brennstoff als Flüssigkeit nur in geringem Maße kompressibel ist und die Zulaufdrossel 20 sowie die Ablaufdrossel 21 geringe Durchmesser aufweisen, beispielsweise ca. 20 µm, können nur geringe Mengen Brennstoff entweichen und es bildet sich schnell ein hoher Druck in der Ausgleichskammer 17, gegen den der Druckkolben 15 sich abstützt. Dadurch wird die Ventilfeder 9 am anderen Ende des Aktors 11 über den Aktorstößel 13 mit einer Öffnungskraft beaufschlagt und die Ventilnadel 2 mit dem Ventilschließkörper 3 betätigt, so daß der Ventilschließkörper 3 von dem Dichtsitz 6 abhebt. Nach dem Abschalten des Stromes bewegt die Ventilfeder 9 die Ventilnadel 2 zurück in ihre Ausgangslage. Zugleich übt die Kammerfeder 18 auf den Druckkolben 15 eine Druckkraft aus, die den Aktor 11 mit dem Aktorstößel 13 an dem Federanschlag 8 der Ventilnadel 2 in Anlage hält. Der Aktor 11 wird durch die Federkräfte spielfrei zwischen Hydraulikpolster und Ventilnadel eingestellt. Über die Zulaufdrossel 20 fließt dabei Brennstoff in die Ausgleichskammer 17 nach, bis diese wieder vollständig mit Brennstoff gefüllt ist. Wenn es zu Längenänderungen des Ventilkörpers 4 oder des Aktors 11 aufgrund der Erwärmung kommt, so verschiebt sich folglich der Aktor 11 mit Aktorstößel 13 und Druckkolben 15 in der Längsrichtung des Brennstoffeinspritzventils 1 stets so lange, bis er in Anlage an dem Federanschlag 8 der Ventilnadel 2 anliegt.When the
Da auch während der Ruhephase des Aktors 11, in der der Aktor 11 nicht über die Anschlußleitungen 14 bestromt ist, stets Brennstoff durch die Ausgleichskammer 17 hindurchfließt, wird diese Ausgleichskammer 17 gekühlt. Weiterhin ist von Vorteil, daß bei dem erfindungsgemäßen Brennstoffeinspritzventil 1 keine Teile eines Kopplers dynamisch bewegt werden müssen, da nur eine statische Abstützkraft über den Druckkolben 15 auf die Ausgleichskammer 17 ausgeübt wird. Das Ansprechverhalten des Brennstoffeinspritzventils 1 wird somit verbessert. Wenn der Brennstoffablauf 22 so angeordnet wird, daß eine Ausmündung 24 an der höchsten Stelle in der Einbaulage des Brennstoffeinspritzventils 1 an einer hier nicht dargestellten Brennkraftmaschine liegt, so werden eventuell entstehende Gasblasen aus der Ausgleichskammer 17 wirksam entfernt. Insbesondere wird dadurch nach dem Abstellen einer heißen Brennkraftmaschine verhindert, daß beim Wiederstart in der Ausgleichskammer 17 verdampfter Brennstoff eine Gasblase bildet, da bei Einsetzen der Brennstoffzufuhr über die Zulaufdrossel 20 solche Gasblasen entfernt werden und in den Brennstoffablauf 22 gedrückt werden. Es kann nicht dazu kommen, daß der Druckkolben 15 in der Ausgleichskammer 17 aufgrund Kompression von Gasblasen keinen Druck aufbauen kann und somit die Ventilnadel 2 nicht öffnet.Since even during the rest phase of the
Alternativ kann anstelle der Zulaufdrossel 20 auch ein Rückschlagventil angeordnet sein, das bei Unterdruck in der Ausgleichskammer 17 einen großen Strömungsquerschnitt freigibt. Ebenfalls alternativ kann anstelle der Ablauf drossel 21 ein Druckbegrenzungsventil angeordnet sein, das aufgrund seiner Trägheit während der kurzen Betätigungsphase des Aktors 11 nicht anspricht, jedoch bei einem bestimmten einstellbaren Überdruck in der Ausgleichskammer 17 öffnet und einen großen Ablaufquerschnitt freigibt.Alternatively, instead of the
Über einen mit dem Ölkreislauf der hier nicht dargestellten Brennkraftmaschine verbundenen Ölzulauf 25, der ein Schaltventil 26 aufweist, wird der Ausgleichskammer 17 Öl als Hydraulikfluid zugeführt. Über ein weiteres Schaltventil 27 und einen Ölablauf 28 kann dieses Öl abfließen.About a connected to the oil circuit of the internal combustion engine, not shown,
Vorteilhaft können die Schaltventile 26, 27 große Strömungsquerschnitte freigeben. Nach dem Abschalten der Bestromung des Aktors 11 kann durch das Schaltventil 26 des Ölzulaufs 25 rasch die Ausgleichskammer durch einen großen Zulaufquerschnitt wieder aufgefüllt werden. Ebenso kann zugleich und in ihrem Ausmaß steuerbar durch ein Schaltventil 27 der Ölablauf 28 freigegeben werden und ein Durchspülen und Kühlen der Ausgleichskammer 17 erreicht werden. In gleicher Weise kann nach dem Start, wie auch während des Betriebes, verhindert werden, daß eine Blasenbildung auftritt. Diese Gefahr wird zusätzlich durch die Verwendung des Mediums Öl als Hydraulikfluid verringert.Advantageously, the switching
Claims (15)
- Fuel injection valve (1), in particular injection valve for fuel injection systems of internal combustion engines, having a piezoelectric or magnetostrictive actuator (11) which, via a valve needle (2), actuates a valve closing body (3) which is arranged on the valve needle (2) and which interacts with a valve seat surface (6) to form a sealing seat (7), having a hydraulic compensating chamber (17) with which a pressure piston (15) interacts and which is filled with hydraulic fluid via a hydraulic fluid inflow line (19; 25), wherein the actuator (11) is arranged between the pressure piston (15) and valve needle (2) and is displaceable along the axis of the valve needle (2) and of the pressure piston (15), wherein the hydraulic fluid is supplied at a pressure higher than the pressure of the fuel on the side of the actuator (11) of the pressure piston (15),
characterized
in that a chamber spring (18) is arranged on the side of the compensating chamber (17) of the pressure piston (15) and exerts on the pressure piston (15) a preload force which pushes the pressure piston (15) out of the compensating chamber (17). - Fuel injection valve according to Claim 1,
characterized
in that the chamber spring is a diaphragm spring. - Fuel injection valve according to Claim 1,
characterized
in that the chamber spring is a plate spring. - Fuel injection valve according to Claim 1,
characterized
in that the chamber spring (18) is a helical spring. - Fuel injection valve according to one of Claims 1 to 4,
characterized
in that the hydraulic fluid inflow line (19) has an inflow throttle (20) which allows only a small part of the volume of the compensating chamber (17) to flow back during the actuation of the actuator (11). - Fuel injection valve according to one of Claims 1 to 5,
characterized
in that the hydraulic fluid inflow line has a check valve. - Fuel injection valve according to one of Claims 1 to 5,
characterized
in that the hydraulic fluid inflow line (19) has an actuable inflow valve (26). - Fuel injection valve according to Claim 7,
characterized
in that the actuable inflow valve (6) is closed in the non-actuated state. - Fuel injection valve according to one of Claims 1 to 8,
characterized
in that the compensating chamber (17) has a hydraulic fluid outflow line (22) with an outflow throttle (21). - Fuel injection valve according to one of Claims 1 to 8,
characterized
in that the compensating chamber (17) has a hydraulic fluid outflow line (28) with an actuable outflow valve (27). - Fuel injection valve according to Claim 10,
characterized
in that the actuable outflow valve (27) is closed in the non-actuated state. - Fuel injection valve according to one of Claims 1 to 8,
characterized
in that the compensating chamber (17) has a hydraulic fluid outflow line with a pressure-limiting valve. - Fuel injection valve according to one of Claims 10 to 12,
characterized
in that the hydraulic fluid outflow line (22; 28) is arranged in the compensating chamber (17) at that point which is highest when the fuel injection valve (1) is in the installed position. - Fuel injection valve according to one of Claims 1 to 12,
characterized
in that the compensating chamber (17) is filled with fuel. - Fuel injection valve according to one of Claims 1 to 12,
characterized
in that the compensating chamber (17) is connected via the hydraulic fluid inflow line (25) to an oil circuit of the internal combustion engine.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10158789 | 2001-11-30 | ||
DE10158789A DE10158789A1 (en) | 2001-11-30 | 2001-11-30 | Fuel injector |
PCT/DE2002/003714 WO2003048559A1 (en) | 2001-11-30 | 2002-10-01 | Fuel injection valve |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1454053A1 EP1454053A1 (en) | 2004-09-08 |
EP1454053B1 true EP1454053B1 (en) | 2011-12-14 |
Family
ID=7707529
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP02774434A Expired - Lifetime EP1454053B1 (en) | 2001-11-30 | 2002-10-01 | Fuel injection valve |
Country Status (7)
Country | Link |
---|---|
US (1) | US7055765B2 (en) |
EP (1) | EP1454053B1 (en) |
JP (1) | JP4276950B2 (en) |
KR (1) | KR100933626B1 (en) |
CN (1) | CN100567729C (en) |
DE (1) | DE10158789A1 (en) |
WO (1) | WO2003048559A1 (en) |
Families Citing this family (22)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10159750A1 (en) * | 2001-12-05 | 2003-06-12 | Bosch Gmbh Robert | Fuel injection valve for IC engine, has pressure balanced valve needle, whereby force exerted in opening direction by fuel pressure is approximately equal to force exerted by fuel in closing direction |
JP4288182B2 (en) * | 2002-04-22 | 2009-07-01 | シーメンス アクチエンゲゼルシヤフト | Metering device for fluids, especially injection valves for automobiles |
DE10328573A1 (en) * | 2003-06-25 | 2005-01-13 | Robert Bosch Gmbh | Fuel injector |
DE102005037267A1 (en) * | 2005-08-08 | 2007-02-15 | Robert Bosch Gmbh | Fuel injector |
DE102006019308A1 (en) * | 2006-04-26 | 2007-10-31 | Robert Bosch Gmbh | Injector for fuel supply to internal combustion engine, especially in motor vehicle, has piezoactuator with foot on end remote from nozzle needle with sealing profile facing needle that contacts seal seat on injector body |
JP4552922B2 (en) | 2006-10-26 | 2010-09-29 | トヨタ自動車株式会社 | In-cylinder injection spark ignition internal combustion engine |
JP4462296B2 (en) * | 2007-07-03 | 2010-05-12 | 株式会社デンソー | Back pressure regulating valve |
DE102007044877B4 (en) * | 2007-09-20 | 2011-06-01 | Compact Dynamics Gmbh | Fluid injection valve |
US20130199501A1 (en) * | 2010-10-11 | 2013-08-08 | A Fuel Injector With A Variable Orifice | Fuel injector with a variable orifice |
DE102012202909A1 (en) * | 2012-02-27 | 2013-08-29 | Robert Bosch Gmbh | Valve for metering fluid |
US9381447B2 (en) | 2012-03-07 | 2016-07-05 | Waters Technologies Corporation | Force balance needle valve pressure regulator for carbon dioxide based chromatography |
DE102013012444A1 (en) * | 2013-07-29 | 2015-01-29 | Astrium Gmbh | Valve assembly for switching and / or regulating a media flow of a spacecraft and spacecraft |
EP2863048B1 (en) * | 2013-10-21 | 2017-12-06 | C.R.F. Società Consortile Per Azioni | Fuel electro-injector for a fuel injection system for an internal combustion engine |
DE102014207587A1 (en) * | 2014-04-22 | 2015-10-22 | Robert Bosch Gmbh | Fuel injection valve for internal combustion engines and a method for operating the same |
DE102015211749A1 (en) * | 2015-06-24 | 2016-12-29 | Robert Bosch Gmbh | Injection device for a liquid reducing agent |
CN105387487B (en) * | 2015-12-29 | 2018-01-30 | 中国航空工业集团公司沈阳发动机设计研究所 | A kind of fuel balance device |
CN106179823B (en) * | 2016-08-15 | 2018-05-25 | 陈曦 | A kind of servo electricity is straight to drive the quick tube-type jet drawn and spray anticorrosive paint |
JP6586931B2 (en) * | 2016-08-26 | 2019-10-09 | 株式会社デンソー | Relief valve device and high-pressure pump using the same |
DE102017212003A1 (en) * | 2016-09-16 | 2018-03-22 | Robert Bosch Gmbh | Overflow valve, in particular for use in a fuel injection system, high-pressure pump and fuel injection system |
CN107725240B (en) * | 2017-11-21 | 2019-11-08 | 聊城科瑞汽车零部件有限公司 | A kind of fuel injector of internal pressurization |
CN111804506B (en) * | 2020-07-05 | 2022-09-09 | 苏州韩迅机器人系统有限公司 | Continuous glue pouring machine and glue pouring process thereof |
CN111894780B (en) * | 2020-07-30 | 2022-06-21 | 一汽解放汽车有限公司 | Oil inlet valve for oil supply pump and high-pressure common rail system |
Family Cites Families (15)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE1079099B (en) | 1957-08-07 | 1960-04-07 | Peter G S Mero | Device for pen guidance in telautographs |
DE3030378C2 (en) * | 1980-08-11 | 1983-01-20 | Siemens AG, 1000 Berlin und 8000 München | Piezoelectrically operated, controllable injection valve |
EP0477400B1 (en) | 1990-09-25 | 2000-04-26 | Siemens Aktiengesellschaft | Device for compensating the tolerance in the lift direction of the displacement transformer of a piezoelectric actuator |
DE19500706C2 (en) | 1995-01-12 | 2003-09-25 | Bosch Gmbh Robert | Metering valve for dosing liquids or gases |
GB9713791D0 (en) * | 1997-07-01 | 1997-09-03 | Lucas Ind Plc | Fuel injector |
US5979803A (en) * | 1997-05-09 | 1999-11-09 | Cummins Engine Company | Fuel injector with pressure balanced needle valve |
DE19742320A1 (en) * | 1997-09-25 | 1999-04-01 | Bosch Gmbh Robert | Fuel injector |
DE19743640A1 (en) * | 1997-10-02 | 1999-04-08 | Bosch Gmbh Robert | Valve for controlling liquids |
DE19940056A1 (en) * | 1999-08-24 | 2001-03-22 | Siemens Ag | Dosing device and method for dosing |
DE19940054C2 (en) * | 1999-08-24 | 2003-11-27 | Siemens Ag | Dosing valve for a pressurized fluid |
DE19940055C1 (en) * | 1999-08-24 | 2001-04-05 | Siemens Ag | Dosing valve |
GB9922408D0 (en) * | 1999-09-23 | 1999-11-24 | Lucas Ind Plc | Fuel injector |
DE19953562A1 (en) * | 1999-11-08 | 2001-05-23 | Bosch Gmbh Robert | Fuel injector |
DE10007733A1 (en) | 2000-02-19 | 2001-08-23 | Daimler Chrysler Ag | Injection valve has actuator is sealed with respect to fuel under high pressure using metallic corrugated tube between fuel chamber and actuator |
DE10007735A1 (en) * | 2000-02-19 | 2001-09-06 | Daimler Chrysler Ag | Fuel injection valve for IC engines has pressure-reducing throttle between high-pressure fuel in fuel chamber/line and lower pressure fuel in valve needle actuator area |
-
2001
- 2001-11-30 DE DE10158789A patent/DE10158789A1/en not_active Withdrawn
-
2002
- 2002-10-01 WO PCT/DE2002/003714 patent/WO2003048559A1/en active Application Filing
- 2002-10-01 KR KR1020047008004A patent/KR100933626B1/en not_active IP Right Cessation
- 2002-10-01 JP JP2003549721A patent/JP4276950B2/en not_active Expired - Fee Related
- 2002-10-01 EP EP02774434A patent/EP1454053B1/en not_active Expired - Lifetime
- 2002-10-01 US US10/470,292 patent/US7055765B2/en not_active Expired - Fee Related
- 2002-10-01 CN CNB028039661A patent/CN100567729C/en not_active Expired - Fee Related
Also Published As
Publication number | Publication date |
---|---|
CN100567729C (en) | 2009-12-09 |
JP2005511953A (en) | 2005-04-28 |
DE10158789A1 (en) | 2003-07-10 |
CN1488035A (en) | 2004-04-07 |
KR100933626B1 (en) | 2009-12-24 |
EP1454053A1 (en) | 2004-09-08 |
US20040112992A1 (en) | 2004-06-17 |
US7055765B2 (en) | 2006-06-06 |
JP4276950B2 (en) | 2009-06-10 |
KR20040066137A (en) | 2004-07-23 |
WO2003048559A1 (en) | 2003-06-12 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP1454053B1 (en) | Fuel injection valve | |
DE60121352T2 (en) | COMPENSATING DEVICE WITH A FLEXIBLE MEMBRANE FOR A FUEL INJECTION VALVE AND METHOD THEREFOR | |
EP1511932B1 (en) | Injection valve | |
DE60207239T2 (en) | DIRECTLY ACTUATED INJECTION VALVE | |
EP1733139B1 (en) | Common rail injector | |
DE19946833C2 (en) | Valve for controlling liquids | |
DE3742241A1 (en) | Piezocontrol valve for controlling fuel injection via an injection valve in internal combustion engines | |
EP1423600A1 (en) | Fuel injection valve | |
EP1407136B1 (en) | Fuel injection valve | |
EP1472451B1 (en) | Fuel injection valve | |
EP1378657B1 (en) | Fuel injector | |
DE10203655A1 (en) | Fuel injector | |
DE10203657A1 (en) | Fuel injector | |
DE10213858A1 (en) | Fuel injector | |
WO2001079688A1 (en) | Fuel injection valve for internal combustion engines | |
EP2185807B1 (en) | Control valve for a fuel injector | |
EP1664525B1 (en) | Metering device | |
EP1519034B1 (en) | Fuel injection valve | |
EP1144845A1 (en) | Device for transmitting an actuator displacement to a modulator and an injection valve having such a device | |
WO2003012283A1 (en) | Fuel injection valve | |
DE102005003449A1 (en) | Clearance compensation element has device which is arranged at throttle point for generation of electrical or magnetic field whereby fluid has electrical or magneto-rheological properties which is influenced by device | |
DE10333693B3 (en) | Fuel injection device for an internal combustion engine comprises a filling chamber arranged between two pistons and connected to a feed line | |
DE10232194B4 (en) | Fuel injector | |
EP0886064A1 (en) | Method for injection of fuel | |
DE102005015996A1 (en) | Fuel injector for internal combustion engine, has temperature equalization unit to effect temperature equalization with respect to actuator and associated at side of actuator, which is averted to pressure transmission unit |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
17P | Request for examination filed |
Effective date: 20040630 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR IE IT LI LU MC NL PT SE SK TR |
|
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
RBV | Designated contracting states (corrected) |
Designated state(s): CZ DE ES FR GB IT |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): CZ DE ES FR GB IT |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: FG4D Free format text: NOT ENGLISH |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R096 Ref document number: 50215314 Country of ref document: DE Effective date: 20120308 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: CZ Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20111214 |
|
PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
26N | No opposition filed |
Effective date: 20120917 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R097 Ref document number: 50215314 Country of ref document: DE Effective date: 20120917 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: ES Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20120325 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 14 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 15 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 16 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: FR Payment date: 20171023 Year of fee payment: 16 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: GB Payment date: 20171024 Year of fee payment: 16 Ref country code: IT Payment date: 20171020 Year of fee payment: 16 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20181206 Year of fee payment: 17 |
|
GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20181001 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: FR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20181031 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: GB Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20181001 Ref country code: IT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20181001 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R119 Ref document number: 50215314 Country of ref document: DE |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: DE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20200501 |