EP2388467B1 - Fuel injector with hydraulic coupling unit - Google Patents
Fuel injector with hydraulic coupling unit Download PDFInfo
- Publication number
- EP2388467B1 EP2388467B1 EP20110162204 EP11162204A EP2388467B1 EP 2388467 B1 EP2388467 B1 EP 2388467B1 EP 20110162204 EP20110162204 EP 20110162204 EP 11162204 A EP11162204 A EP 11162204A EP 2388467 B1 EP2388467 B1 EP 2388467B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- fuel injector
- piston
- coupling
- compressible reservoir
- injector according
- 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
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/0012—Valves
- F02M63/0057—Means for avoiding fuel contact with valve actuator, e.g. isolating actuators by using bellows or diaphragms
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- 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
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- 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
- F02M2200/31—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements
- F02M2200/315—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements for damping fuel pressure fluctuations
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- 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
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- 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
- F02M2200/80—Fuel injection apparatus manufacture, repair or assembly
- F02M2200/8038—Fuel injection apparatus manufacture, repair or assembly the assembly involving use of adhesives, glue or the like
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- 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
- F02M2200/80—Fuel injection apparatus manufacture, repair or assembly
- F02M2200/8084—Fuel injection apparatus manufacture, repair or assembly involving welding or soldering
Definitions
- the invention relates to a fuel injector with a hydraulic coupler unit according to the preamble of claim 1.
- a hydraulic coupler unit for a fuel injector with a coupler piston and a guided inside the coupler piston valve piston wherein both components define between them filled with a hydraulic medium pressure chamber, which forms a so-called Kopplerspaltvolumen.
- the coupler piston is in communication with an actuator element whose actuation causes a translational movement of the coupler piston in the direction of the pressure chamber against a biasing spring.
- the coupler gap volume is associated with an additional, compressible Reservoir in communication, which is limited to a surrounding pressure chamber by means of a flexible membrane.
- Another hydraulic coupler unit for a fuel injector is off DE 102007028490 A1 in which a coupler gap filled with a liquid is sealed between a first coupler element and a second coupler element by means of a membrane towards a low-pressure space.
- Object of the present invention is to lower the pressure increase after opening the switching valve during the entire life of the fuel injector.
- the fuel injector with the characterizing features of claim 1 has the advantage that is limited by the compressible reservoir, the pressure increase after opening of the switching valve within the low-pressure space, whereby the voltage for driving the piezo-actuator element can be sized smaller.
- the compressible reservoir thereby causes the Ab Kunststoffstoss resulting when opening the switching valve, which leads to a sudden inflow of fuel into the low-pressure chamber is attenuated by the compressible reservoir defining flexible wall yields and provides an additional volume in the low pressure space, creating a sudden Pressure increase in the low pressure space is prevented.
- the lowering of the pressure oscillation amplitude in the low-pressure space also causes a reduced risk of cavitation erosion occurring at the closed ends of the low pressure space, z. B. may occur at the sealing seat of the switching valve or on the support of the actuator element in the injector body. In addition, this reduces the amplitude of pressure oscillations in the entire return system of the fuel injector, resulting in a discharge of the return plug and the return lines.
- the coupler piston has an axially extended solid portion.
- the compressible reservoir is arranged on an outer peripheral surface in the region of the solid portion.
- At least one circumferential annular groove which is sealed by means of a flexible wall, is introduced into the outer peripheral surface in the region of the solid portion.
- the flexible wall may be formed by a cylindrical, sleeve-shaped membrane or a corrugated, sleeve-shaped membrane, wherein the membranes are sealed to the outer peripheral surface of the coupler piston by means of joints.
- a further embodiment provides that the compressible reservoir is delimited by at least one curved, sleeve-shaped membrane, which is attached to the outer peripheral surface in the region of the solid portion and encloses the compressible reservoir.
- a further embodiment is characterized in that the compressible reservoir is formed by at least one introduced into the solid section radially continuous bore, which is closed at the puncture points in each case to the low-pressure space with a cover-shaped membrane as a flexible wall.
- the compressible reservoir is formed by at least one introduced into the solid portion of the coupler piston blind hole, wherein the blind hole is limited with a lid-shaped membrane as a flexible wall to the low pressure space.
- FIG. 1 shown section of a fuel injector shows a coupler unit 20 which is disposed within a formed in an injector 11 low-pressure chamber 12.
- an actuator 13 is further arranged with, for example, a piezo-actuator element 14.
- the low-pressure chamber 12 is further delimited by a valve plate 15, in which a valve element 16 with a valve pin 17 is located.
- the valve plate 15 is hydraulically sealed to the injector body 11 by means of a screw, not shown.
- the valve pin 17 forms a valve seat 19 with a sealing edge on the valve plate 15.
- an unillustrated control chamber to which a nozzle needle, not shown, is exposed to a control surface is connected via a likewise not shown drain throttle via the low pressure chamber 12 with a low pressure / return system , As a result, the nozzle needle is lifted off a nozzle needle seat and fuel is injected into the combustion chamber of an internal combustion engine.
- the coupler unit 20 comprises a sleeve-shaped coupler body 21, a cup-shaped coupler piston 22 and a cylindrical valve piston 23. Between the coupler piston 22 and the valve piston 23, a pressure chamber 25 is arranged, which forms a Kopplerspaltvolumen.
- the coupler body 21 has a frontally open recess 26 in which a trained as a helical compression spring spring 27 is arranged, which is supported with its axial lower end to an annular shoulder of a valve piston 23 fixed to the sleeve 28.
- a trained as a helical compression spring spring 27 is arranged, which is supported with its axial lower end to an annular shoulder of a valve piston 23 fixed to the sleeve 28.
- the cup-shaped coupler piston 22 is formed with a cylindrical peripheral wall 31 and a bottom-shaped, solid portion 33 having an inner end wall 34, wherein the cylindrical peripheral wall 31 forms an outer peripheral surface 32 and an inner circumferential surface 35.
- the bottom-shaped, solid portion 33 is formed by an axial extension of the coupler piston 22.
- the sleeve-shaped coupler body 21 has an outer circumferential surface 36 with a diameter d1, an inner peripheral surface 37 with a diameter d2 and an inner annular end 38.
- the coupler piston 22 is axially guided with the inner peripheral surface 35 on the outer peripheral surface 36 of the coupler body 21.
- the valve piston 23 is guided with a cylindrical piston surface 39.
- the pressure space 25 forming the coupler gap volume is delimited by the inner end wall 34 of the solid portion 33 of the coupler piston 22, the annular end face 38 of the coupler body 21 and by an upper end face 41 of the valve piston 23.
- a radially outwardly directed collar 43 is formed in the region of the cylindrical, solid portion 33.
- Another radially outwardly facing collar 44 is located on the coupler body 21.
- the coupler unit 20 further has a biasing spring 40 which is supported with the lower end in the drawing plane at the collar 44 of the coupler body 21 and with the opposite, in the drawing surface upper end via a dial 45 on the coupler piston 22 formed collar 43.
- the biasing spring 40 presses the coupler piston 22 via the dial 45 and the collar 43 against an adjusting piece 46, to which a transmission element 47 of the actuator unit 13 acts.
- the biasing spring 40 thereby provides on the one hand for a bias of the coupler piston 22 against the actuator unit 13 and causes the other indirectly via the dial 45 and the setting piece 46 necessary for a functioning of the system bias of the actuator 13th
- the coupler unit 20 further has a compressible reservoir 50, which is bounded with a flexible wall 51 to the low pressure chamber 12 out.
- the compressible reservoir 50 forms a volume which is filled with a gas, for example with air, oxygen or a noble gas.
- a gas for example with air, oxygen or a noble gas.
- the flexible wall 51 is designed as a membrane which seals the compressible reservoir 50 by means of joints to the low-pressure chamber 12 in a gastight manner.
- the compressible reservoir 50 is formed on the outer peripheral surface 32 of the coupler piston 22, preferably in the region of the solid portion 33.
- FIG. 1 is to form the compressible reservoir 50 in the outer peripheral surface 32 of the coupler piston 22 in the region of the solid portion 33, a circumferential annular groove 54 is introduced, which is sealed with a cylindrical, sleeve-shaped membrane 55 as a flexible wall 51 to the low-pressure chamber 12.
- the flexible wall 51 is formed by a corrugated, sleeve-shaped membrane 56.
- FIG. 3 shows a third embodiment for forming the compressible reservoir 50, in which through the solid portion 33 of the coupler piston 22, a radially continuous bore 57 is introduced, which at the piercing points on the outer peripheral surface 32 each having a cap-shaped membrane 58 for forming the flexible wall 51st is closed.
- FIG. 4 shows a fourth embodiment for forming the compressible reservoir 50, in which the compressible reservoir 50 is located on the outer peripheral surface 32 on the outside of the coupler piston 22 by a flexible, sleeve-shaped membrane 59 is attached to the outer peripheral surface 32 with two tight joints as a flexible wall 51 wherein the domed sleeve-shaped membrane 59 encloses the gas volume as a compressible reservoir 50.
- Another exemplary embodiment consists in introducing at least one blind bore in the region of the solid section 33, which can assume an arbitrary position with respect to the symmetry axis of the coupler piston 22.
- the blind hole is sealed to the low-pressure chamber 12 by means of a cover-shaped membrane as a flexible wall 51 gas-tight.
- the stiffness of the compressible reservoir 50 may be affected by the geometric configuration of the membrane as well as the size of the trapped volume. However, the formation of the compressible reservoir 50 may be carried out in addition to the already mentioned rotationally symmetrical circumferential groove 54 and by an over the circumference of the coupler piston 22 asymmetric or interrupted form. Suitable for this purpose are, for example, individual polished sections on the circumference of the coupler piston.
- the membrane is preferably made of a metallic material which is welded gas-tight at the contact points with the coupler piston 22. In this case, the gas atmosphere in which the welding process takes place automatically determines the gaseous medium with which the compressible reservoir 50 is filled.
Description
Die Erfindung betrifft einen Kraftstoffinjektor mit einer hydraulischen Kopplereinheit nach dem Oberbegriff des Anspruchs 1.The invention relates to a fuel injector with a hydraulic coupler unit according to the preamble of claim 1.
Insbesondere bei Kraftstoffinjektoren mit einem piezoelektrischen Aktorelement entsteht beim Öffnen des Schaltventils ein Druckstoß in einem das Aktorelement umgebenden Niederdruckraum, der hauptsächlich vom schlagartigen Einströmen der durch das Schaltventil abgesteuerten Menge in den Niederdruckraum und die daran angeschlossene Rücklaufbohrung herrührt. Herrscht im Ruhezustand im Aktorraum ein Druck von ca. 10 bar, so steigt dieser Druck während der Ansteuerung des Schaltventils auf Werte zwischen 40 und 60 bar an. Dieser Druck bewirkt wiederum eine axiale Kraft auf eine Membran am Kopfende des Aktorelements, die sich wieder teilweise auf das Aktorelement stützt und zwar entgegen seiner Wirkrichtung, so dass zur Überwindung dieser Kraft ein zusätzlicher Spannungsanteil zum Ansteuern des piezoelektrischen Aktorelements benötigt wird.Particularly in the case of fuel injectors with a piezoelectric actuator element, when the switching valve opens, a pressure surge occurs in a low-pressure space surrounding the actuator element, which mainly results from the sudden inflow of the quantity diverted by the switching valve into the low-pressure chamber and the return bore connected thereto. If a pressure of approx. 10 bar prevails in the actuator room at rest, this pressure rises to values between 40 and 60 bar during actuation of the switching valve. This pressure in turn causes an axial force on a membrane at the head end of the actuator element, which again partially supported on the actuator element and against its direction of action, so that an additional voltage component for driving the piezoelectric actuator element is required to overcome this force.
Aus
Ein weitere hydraulischen Kopplereinheit für einen Kraftstoffinjektor ist aus
Aufgabe der vorliegenden Erfindung ist es, den Druckanstieg nach dem Öffnen des Schaltventils während der gesamten Lebensdauer des Kraftstoffinjektors abzusenken.Object of the present invention is to lower the pressure increase after opening the switching valve during the entire life of the fuel injector.
Der Kraftstoffinjektor mit den kennzeichnenden Merkmalen des Anspruchs 1 hat den Vorteil, dass durch das kompressible Reservoir der Druckanstieg nach dem Öffnen des Schaltventils innerhalb des Niederdruckraums begrenzt wird, wodurch die Spannung zum Ansteuern des Piezo-Aktorelements geringer bemessen werden kann. Das kompressible Reservoir bewirkt dabei, dass der beim Öffnen des Schaltventils entstehende Absteuerstoß, der zu einem plötzlichen Einströmen von Kraftstoff in den Niederdruckraum führt, gedämpft wird, indem die das kompressible Reservoir begrenzende flexible Wand nachgibt und ein zusätzliches Volumen im Niederdruckraum bereitstellt, wodurch ein plötzlicher Druckanstieg im Niederdruckraum verhindert wird.The fuel injector with the characterizing features of claim 1 has the advantage that is limited by the compressible reservoir, the pressure increase after opening of the switching valve within the low-pressure space, whereby the voltage for driving the piezo-actuator element can be sized smaller. The compressible reservoir thereby causes the Absteuerstoss resulting when opening the switching valve, which leads to a sudden inflow of fuel into the low-pressure chamber is attenuated by the compressible reservoir defining flexible wall yields and provides an additional volume in the low pressure space, creating a sudden Pressure increase in the low pressure space is prevented.
Durch die geringere Druckamplitude im Niederdruckraum sinkt außerdem die Belastung der Membran, mit der das Piezo-Aktorelement gegenüber dem Niederdruckraum abgegrenzt ist, wodurch geringe Anforderungen an die Ausführung der Membran gestellt werden müssen. Dadurch wird die Robustheit des Kraftstoffinjektors erhöht. Darüber hinaus bewirkt die Absenkung der Druckschwingungsamplitude im Niederdruckraum auch eine verringerte Gefahr von Kavitationserosion, die an den geschlossenen Enden des Niederduckraums, z. B. am Dichtsitz des Schaltventils oder an der Auflage des Aktorelements im Injektorkörper auftreten kann. Zusätzlich nimmt dadurch die Amplitude von Druckschwingungen im gesamten Rücklaufsystem des Kraftstoffinjektors ab, was zu einer Entlastung der Rücklaufstecker und der Rücklaufleitungen führt.Due to the lower pressure amplitude in the low-pressure chamber also decreases the load on the membrane with which the piezo-actuator element is delimited from the low-pressure space, whereby low demands on the execution of the membrane must be made. This increases the robustness of the fuel injector. In addition, the lowering of the pressure oscillation amplitude in the low-pressure space also causes a reduced risk of cavitation erosion occurring at the closed ends of the low pressure space, z. B. may occur at the sealing seat of the switching valve or on the support of the actuator element in the injector body. In addition, this reduces the amplitude of pressure oscillations in the entire return system of the fuel injector, resulting in a discharge of the return plug and the return lines.
Weiterbildungen der Erfindung sind durch die Maßnahmen der Unteransprüche möglich.Further developments of the invention are possible by the measures of the subclaims.
Zur Ausbildung des kompressiblen Reservoirs weist der Kopplerkolben einen axial verlängerten massiven Abschnitt auf. Das kompressible Reservoir ist dabei an einer äußere Umfangsfläche im Bereich des massiven Abschnitts angeordnet.To form the compressible reservoir, the coupler piston has an axially extended solid portion. The compressible reservoir is arranged on an outer peripheral surface in the region of the solid portion.
Gemäß einer ersten Ausführungsform ist in die äußere Umfangsfläche im Bereich des massiven Abschnitts mindestens eine umlaufende ringförmigen Nut eingebracht, welche mittels einer flexiblen Wand abgedichtet ist. Die flexible Wand kann durch eine zylindrische, hülsenförmigen Membran oder eine gewellte, hülsenförmigen Membran ausgeführt sein, wobei die Membranen mit der äußeren Umfangsfläche des Kopplerkolbens mittels Fügestellen dicht verbunden sind.According to a first embodiment, at least one circumferential annular groove, which is sealed by means of a flexible wall, is introduced into the outer peripheral surface in the region of the solid portion. The flexible wall may be formed by a cylindrical, sleeve-shaped membrane or a corrugated, sleeve-shaped membrane, wherein the membranes are sealed to the outer peripheral surface of the coupler piston by means of joints.
Eine weitere Ausführungsform sieht vor, dass das kompressible Reservoir mindestens von einer gewölbten, hülsenförmigen Membran begrenzt wird, welche an der äußeren Umfangsfläche im Bereich des massiven Abschnitts angebracht ist und das kompressible Reservoir einschließt.A further embodiment provides that the compressible reservoir is delimited by at least one curved, sleeve-shaped membrane, which is attached to the outer peripheral surface in the region of the solid portion and encloses the compressible reservoir.
Eine weitere Ausführungsform ist dadurch gekennzeichnet, dass das kompressible Reservoir durch mindestens eine in den massiven Abschnitt eingebrachte radial durchgehenden Bohrung ausgebildet ist, welche an den Durchstoßstellen jeweils zum Niederdruckraum hin mit einer deckelförmigen Membran als flexible Wand verschlossen ist. Es ist aber auch denkbar, das kompressible Reservoir durch mindestens eine in den massiven Abschnitt des Kopplerkolbens eingebrachte Sacklochbohrung auszubilden, wobei die Sacklochbohrung mit einer deckelförmigen Membran als flexible Wand zum Niederdruckraum hin begrenzt wird.A further embodiment is characterized in that the compressible reservoir is formed by at least one introduced into the solid section radially continuous bore, which is closed at the puncture points in each case to the low-pressure space with a cover-shaped membrane as a flexible wall. But it is also conceivable to form the compressible reservoir by at least one introduced into the solid portion of the coupler piston blind hole, wherein the blind hole is limited with a lid-shaped membrane as a flexible wall to the low pressure space.
Ausführungsbeispiele der Erfindung sind in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert.Embodiments of the invention are illustrated in the drawings and explained in more detail in the following description.
Es zeigen:
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Figur 1 eine Schnittdarstellung durch eine erfindungsgemäße Kopplereinheit eines Kraftstoffinjektors gemäß einem ersten Ausführungsbeispiel, -
Figur 2 eine Schnittdarstellung durch einen Kopplerkolben ausFigur 1 gemäß einem zweiten Ausführungsbeispiel, -
Figur 3 eine Schnittdarstellung durch einen Kopplerkolben ausFigur 1 gemäß einem dritten Ausführungsbeispiel und -
Figur 4 eine Schnittdarstellung durch einen Kopplerkolben ausFigur 1 gemäß einem vierten Ausführungsbeispiel
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FIG. 1 a sectional view through a coupler unit according to the invention of a fuel injector according to a first embodiment, -
FIG. 2 a sectional view through a coupler pistonFIG. 1 according to a second embodiment, -
FIG. 3 a sectional view through a coupler pistonFIG. 1 according to a third embodiment and -
FIG. 4 a sectional view through a coupler pistonFIG. 1 according to a fourth embodiment
Der in
Der Niederdruckraum 12 ist weiterhin von einer Ventilplatte 15 begrenzt, in welcher sich ein Ventilelement 16 mit einem Ventilbolzen 17 befindet. Die Ventilplatte 15 ist mit dem Injektorkörper 11 mittels einer nicht dargestellten Verschraubung hydraulisch dicht verbunden. Der Ventilbolzen 17 bildet mit einer Dichtkante an der Ventilplatte 15 einen Ventilsitz 19 aus. Durch eine translatorischen Bewegung des Ventilbolzens 17 wird die Dichtkante vom Ventilsitz 19 weggedrückt, wodurch ein nicht dargestellter Steuerraum, dem eine nicht dargestellte Düsennadel mit einer Steuerfläche ausgesetzt ist, über eine ebenfalls nicht dargestellte Ablaufdrossel über den Niederdruckraum 12 mit einem Niederdruck-/Rücklaufsystem verbunden wird. Dadurch wird die Düsennadel von einem Düsennadelsitz abgehoben und Kraftstoff in den Brennraum einer Brennkraftmaschine eingespritzt.The low-
Die Kopplereinheit 20 umfasst einen hülsenförmigen Kopplerkörper 21, einen topfförmigen Kopplerkolben 22 und einen zylindrischen Ventilkolben 23. Zwischen dem Kopplerkolben 22 und dem Ventilkolben 23 ist ein Druckraum 25 angeordnet, welcher ein Kopplerspaltvolumen bildet.The
An seinem unteren Abschnitt weist der Kopplerkörper 21 eine stirnseitig offene Aussparung 26 auf, in der eine als Schraubendruckfeder ausgebildete Feder 27 angeordnet ist, die sich mit ihrem axialen unteren Ende an einer Ringschulter einer am Ventilkolben 23 befestigten Hülse 28 abstützt. Durch die Feder 27 wird der Ventilkolben 23 auf den Ventilbolzen 17 des Ventilelements 16 gedrückt.At its lower portion, the
Der topfförmige Kopplerkolben 22 ist mit einer zylindrischen Umfangswand 31 und einem bodenförmigen, massiven Abschnitt 33 mit einer inneren Stirnwand 34 ausgeführt, wobei die zylindrische Umfangswand 31 eine äußere Umfangsfläche 32 und eine innere Umfangsfläche 35 ausbildet. Der bodenförmige, massive Abschnitt 33 wird dabei von einer axialen Verlängerung des Kopplerkolbens 22 gebildet.The cup-
Der hülsenförmige Kopplerkörper 21 weist eine äußere Umfangsfläche 36 mit einem Durchmesser d1, eine innere Umfangsfläche 37 mit einem Durchmesser d2 und eine innere ringförmige Stirnseite 38 auf. Der Kopplerkolben 22 ist mit der inneren Umfangsfläche 35 an der äußeren Umfangsfläche 36 des Kopplerkörpers 21 axial geführt. An der inneren Umfangsfläche 37 des Kopplerkörpers 21 ist der Ventilkolben 23 mit einer zylindrischen Kolbenfläche 39 geführt.The sleeve-
Der das Kopplerspaltvolumen ausbildende Druckraum 25 wird von der inneren Stirnwand 34 des massiven Abschnitts 33 des Kopplerkolbens 22, der ringförmigen Stirnseite 38 des Kopplerkörpers 21 und von einer oberen Stirnfläche 41 des Ventilkolbens 23 begrenzt.The
Am topfförmigen Kopplerkolben 22 ist im Bereich des zylinderförmigen, massiven Abschnitts 33 ein radial nach außen gerichteter Bund 43 ausgebildet. Ein weiterer radial nach außen weisender Bund 44 befindet sich am Kopplerkörper 21.At cup-
Die Kopplereinheit 20 weist weiterhin eine Vorspannfeder 40 auf, welche sich mit dem in der Zeichnungsebene unteren Ende am Bund 44 des Kopplerkörpers 21 und mit dem gegenüberliegenden, in der Zeichnungsfläche oberen Ende über eine Einstellscheibe 45 an dem am Kopplerkolben 22 ausgebildeten Bund 43 abstützt. Die Vorspannfeder 40 drückt den Kopplerkolben 22 über die Einstellscheibe 45 und den Bund 43 gegen ein Einstellstück 46, an welchem ein Übertragungselement 47 der Aktoreinheit 13 angreift. Die Vorspannfeder 40 sorgt dadurch zum Einen für eine Vorspannung des Kopplerkolbens 22 gegen die Aktoreinheit 13 und bewirkt zum Anderen mittelbar über die Einstellscheibe 45 und das Einstellstück 46 die für eine Funktionsfähigkeit des Systems notwendige Vorspannung der Aktoreinheit 13.The
Die Kopplereinheit 20 weist ferner ein kompressibles Reservoir 50 auf, welches mit einer flexiblen Wand 51 zum Niederduckraum 12 hin begrenzt ist. Das kompressible Reservoir 50 bildet ein Volumen, das mit einem Gas, beispielsweise mit Luft, Sauerstoff oder einem Edelgas gefüllt ist. Zur Ausbildung des kompressiblen Reservoirs 50 weist der Kopplerkolben 22 außerhalb des Kopplergehäuses 21 eine Verlängerung auf, die den massiven Abschnitt 33 bildet, in oder an dem das kompressible Reservoir 50 eingebracht oder angebracht wird. Die flexibel Wand 51 ist als Membran ausgeführt, welche das kompressible Reservoir 50 mittels Fügestellen zum Niederdruckraum 12 hin gasdicht abdichtet. Das kompressible Reservoir 50 ist an der äußeren Umfangsfläche 32 des Kopplerkolbens 22, vorzugsweise im Bereich des massiven Abschnitts 33 ausgebildet.The
Gemäß einem ersten Ausführungsbeispiel in
Eine weiteres Ausführungsbeispiel besteht darin, mindestens eine Sackbohrung im Bereich des massiven Abschnitts 33 einzubringen, die dabei eine beliebige Position bezüglich der Symmetrieachse des Kopplerkolbens 22 einnehmen kann. Die Sacklochbohrung ist zum Niederdruckraum 12 hin mittels einer deckelförmigen Membran als flexible Wand 51 gasdicht verschlossen.Another exemplary embodiment consists in introducing at least one blind bore in the region of the
Die Steifigkeit des kompressiblen Reservoirs 50 kann durch die geometrische Gestaltung der Membran sowie durch die Größe des eingeschlossenen Volumens beeinflusst werden. Die Ausbildung des kompressiblen Reservoirs 50 kann jedoch neben der bereits erwähnten rotationssymmetrisch ausgeführten umlaufenen Nut 54 auch durch eine über den Umfang des Kopplerkolbens 22 asymmetrisch oder unterbrochenen Form ausgeführt sein. Geeignet sind dazu beispielsweise einzelne Anschliffe am Umfang des Kopplerkolbens.The stiffness of the
Die Membran besteht vorzugsweise aus einem metallischen Werkstoff, der an den Kontaktstellen mit dem Kopplerkolben 22 gasdicht verschweißt ist. In diesem Fall bestimmt die Gasatmosphäre, in der der Schweißprozess stattfindet automatisch das gasförmige Medium, mit dem das kompressible Reservoir 50 gefüllt ist.The membrane is preferably made of a metallic material which is welded gas-tight at the contact points with the
Es ist aber auch die Ausführung von Membranen aus nicht metallischen oder aus Verbundwerkstoffen oder einer anderen Art der Verbindung zwischen Membran und Kopplerkolben 22, wie z. B. Kleben denkbar.But it is also the execution of membranes made of non-metallic or composite materials or another type of connection between the membrane and
Bei Betätigung des Aktorelements 14 wird der Kopplerkolben 22 über das Einstellstück 45 und entgegen der Vorspannkraft der Vorspannfeder 40 translatorisch in Richtung des Ventilbolzens 17 bewegt. Diese Bewegung wird durch den im Druckraum 25 befindlichen Kraftstoff auf das kopplereinheitseitige Ende des Ventilkolbens 17 hydraulisch übertragen, wobei die axiale Bewegung des Kopplerkolbens 21 entsprechend eines Durchmesserverhältnisses d1/d2 von Ventilkolben 23 und Kopplerkolben 22 in eine axiale Bewegung des Ventilkolbens 23 übersetzt wird. Die durch die Aktoreinheit 13 zur Verfügung gestellte Kraft wird dementsprechend durch die Kopplereinheit 20 hydraulisch übersetzt und auf den Ventilbolzen 17 des Ventilelements 16 übertragen.Upon actuation of the
Claims (10)
- Fuel injector with a switching valve and with a hydraulic coupling unit (20) which comprises a coupling piston (22), a valve piston and a pressure space (25) as a coupling gap volume which is filled with fuel in order to convert an axial movement of the coupling piston (22) into an axial movement of the valve piston (23) in accordance with a diameter ratio of the valve piston (23) to the coupling piston (22), wherein the coupling piston (22) is prestressed against an actuator element (14) in a manner pointing outwards from the coupling gap volume by means of a prestressing spring (40), and wherein the coupling unit (20) is arranged in a low-pressure space (12) and has a compressible reservoir (50), characterized in that the coupling piston (22) and the valve piston (23) are guided together in an axially displaceable manner on a coupling body (21) and between themselves and the coupling body (21) delimit the pressure space (25) as the coupling gap volume, and in that the compressible reservoir (50) is formed on the coupling piston (22) and is delimited towards the low-pressure space (12) by a flexible wall (51) by means of which a closing surge which arises during the opening of the switching valve is damped.
- Fuel injector according to Claim 1, characterized in that the coupling piston (22) has a solid section (33) on or in which the compressible reservoir (50) is formed.
- Fuel injector according to Claim 2, characterized in that the solid section (33) has an outer circumferential surface (32), and in that the compressible reservoir (50) on the outer circumferential surface (32) of the solid section (33) is delimited by the flexible wall (51).
- Fuel injector according to Claim 3, characterized in that at least one encircling annular groove (54) is introduced into the outer circumferential surface (32) in the region of the solid section (33), said groove being delimited towards the low-pressure space (12) by means of the flexible wall (51).
- Fuel injector according to Claim 4, characterized in that the flexible wall (51) is formed by a cylindrical sleeve-shaped diaphragm (55) or by a corrugated sleeve-shaped diaphragm (56).
- Fuel injector according to Claim 3, characterized in that the compressible reservoir (50) is bounded by at least one curved sleeve-shaped diaphragm (59) which is fitted on the outer circumferential surface (32) in the region of the solid section (33) and delimits the compressible reservoir (50) towards the low-pressure space (12).
- Fuel injector according to Claim 2 or 3, characterized in that the compressible reservoir (50) is formed by at least one radially continuous bore (57) introduced into the solid section (33).
- Fuel injector according to Claim 2 or 3, characterized in that the compressible reservoir (50) is formed by at least one blind bore introduced into the solid section (33).
- Fuel injector according to Claim 7 or 8, characterized in that the continuous bore (57) or the blind bore is delimited towards the low-pressure space (12) at the outlet points on the circumferential surface (32) by in each case a cover-shaped diaphragm (58) as a flexible wall (21).
- Fuel injector according to one of the preceding claims, characterized in that the compressible reservoir (50) is filled with a gas.
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE201010029123 DE102010029123A1 (en) | 2010-05-19 | 2010-05-19 | Fuel injector with hydraulic coupler unit |
Publications (3)
Publication Number | Publication Date |
---|---|
EP2388467A2 EP2388467A2 (en) | 2011-11-23 |
EP2388467A3 EP2388467A3 (en) | 2012-01-04 |
EP2388467B1 true EP2388467B1 (en) | 2013-02-13 |
Family
ID=44484858
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP20110162204 Not-in-force EP2388467B1 (en) | 2010-05-19 | 2011-04-13 | Fuel injector with hydraulic coupling unit |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP2388467B1 (en) |
CN (1) | CN102251894B (en) |
DE (1) | DE102010029123A1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP3035520A1 (en) | 2014-12-19 | 2016-06-22 | Robert Bosch Gmbh | Hydraulic coupler unit for controlling a valve |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102012219867A1 (en) * | 2012-10-30 | 2014-04-30 | Robert Bosch Gmbh | Fuel injector with piezo actuator |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19946831C1 (en) * | 1999-09-30 | 2001-07-12 | Bosch Gmbh Robert | Valve for controlling liquids |
DE10157886B4 (en) * | 2000-11-27 | 2009-12-17 | DENSO CORPORATION, Kariya-shi | Fuel injection unit of an internal combustion engine |
DE10322672A1 (en) * | 2003-05-20 | 2004-12-09 | Robert Bosch Gmbh | Valve for controlling liquids |
DE10332874A1 (en) | 2003-07-19 | 2005-02-10 | Robert Bosch Gmbh | Hydraulic coupler and fuel injector |
DE102006027780A1 (en) * | 2006-06-16 | 2007-12-20 | Robert Bosch Gmbh | fuel injector |
JP4650395B2 (en) * | 2006-11-02 | 2011-03-16 | 株式会社デンソー | Fuel injection valve |
DE102007028490A1 (en) * | 2007-06-21 | 2008-12-24 | Robert Bosch Gmbh | Hydraulic coupler for injector, has coupler element which is connected with stationary component, where another coupler element is provided |
-
2010
- 2010-05-19 DE DE201010029123 patent/DE102010029123A1/en not_active Withdrawn
-
2011
- 2011-04-13 EP EP20110162204 patent/EP2388467B1/en not_active Not-in-force
- 2011-05-19 CN CN201110139228.5A patent/CN102251894B/en not_active Expired - Fee Related
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP3035520A1 (en) | 2014-12-19 | 2016-06-22 | Robert Bosch Gmbh | Hydraulic coupler unit for controlling a valve |
DE102014226673A1 (en) | 2014-12-19 | 2016-06-23 | Robert Bosch Gmbh | Hydraulic coupler unit for controlling a valve |
Also Published As
Publication number | Publication date |
---|---|
EP2388467A2 (en) | 2011-11-23 |
CN102251894A (en) | 2011-11-23 |
EP2388467A3 (en) | 2012-01-04 |
DE102010029123A1 (en) | 2011-11-24 |
CN102251894B (en) | 2015-07-08 |
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