EP2743493A2 - Fuel injector - Google Patents
Fuel injector Download PDFInfo
- Publication number
- EP2743493A2 EP2743493A2 EP13189766.2A EP13189766A EP2743493A2 EP 2743493 A2 EP2743493 A2 EP 2743493A2 EP 13189766 A EP13189766 A EP 13189766A EP 2743493 A2 EP2743493 A2 EP 2743493A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- pressure
- valve
- valve element
- fuel injector
- control
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 239000000446 fuel Substances 0.000 title claims abstract description 77
- 238000002347 injection Methods 0.000 claims abstract description 22
- 239000007924 injection Substances 0.000 claims abstract description 22
- 238000011144 upstream manufacturing Methods 0.000 claims abstract description 17
- 238000007789 sealing Methods 0.000 claims description 28
- 238000002485 combustion reaction Methods 0.000 description 4
- 230000015572 biosynthetic process Effects 0.000 description 3
- 238000010586 diagram Methods 0.000 description 3
- 238000011161 development Methods 0.000 description 2
- 230000018109 developmental process Effects 0.000 description 2
- 240000001439 Opuntia Species 0.000 description 1
- 235000004727 Opuntia ficus indica Nutrition 0.000 description 1
- 230000004913 activation Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000003111 delayed effect Effects 0.000 description 1
- 230000004941 influx Effects 0.000 description 1
- 230000000977 initiatory effect Effects 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
Images
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
- 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
- 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
- F02M63/0003—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure
- F02M63/0005—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure using valves actuated by fluid 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
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/0012—Valves
- F02M63/0014—Valves characterised by the valve actuating means
- F02M63/0028—Valves characterised by the valve actuating means 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
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/0012—Valves
- F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
- F02M63/0078—Valve member details, e.g. special shape, hollow or fuel passages in the valve member
- F02M63/008—Hollow valve members, e.g. members internally guided
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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
- F02M2200/28—Details of throttles in fuel-injection apparatus
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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
- F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
- F02M2547/001—Control chambers formed by movable sleeves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
- F02M2547/003—Valve inserts containing control chamber and valve piston
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
- F02M2547/008—Means for influencing the flow rate out of or into a control chamber, e.g. depending on the position of the needle
Definitions
- the connection to the fuel return is closed again.
- fuel flows from at least one throttle element from a high-pressure fuel volume in the control chamber, with the result that the nozzle needle is displaced again in the direction of its rest position and closes.
- the proposed fuel injector comprises a control valve for controlling the lifting movement of a liftable nozzle needle for releasing and closing at least one injection opening, wherein the end of the nozzle needle facing away from the injection opening delimits a control space.
- the control chamber can be filled to influence a control chamber pressure acting on the nozzle needle via an inlet throttle with high-pressure fuel and can be relieved in the open position of the control valve via an outlet throttle.
- upstream of the inlet throttle is a pressure-actuated further valve with a displaceable valve element for releasing and closing a hydraulic connection of the inlet throttle formed with a high-pressure region. Due to the further valve formed upstream of the inlet throttle, the inflow from a high-pressure fuel volume into the control chamber can be interrupted.
- the control valve is opened and the control chamber is relieved via the outlet throttle.
- the control chamber is relieved faster because no additional amount of fuel flows into the control chamber, on the other hand, the return flow reduces and thus increases the efficiency of the fuel injection system.
- the outlet throttle can be designed with a considerably reduced throttle cross-section.
- the valve element of the pressure-actuable further valve has a first control surface, which abuts the pressure prevailing in the control chamber, and at least one further control surface, at which the downstream of the outlet throttle between the outlet throttle and a valve seat of the control valve and / or the upstream of the inlet throttle between the other valve and the inlet throttle ruling pressure prevails.
- the first control surface therefore preferably limits - together with the nozzle needle - the control chamber in the axial direction.
- the at least one further control surface preferably defines a further pressure chamber, which is formed downstream of the outlet throttle in front of the valve seat of the control valve and / or upstream, preferably immediately upstream, of the inlet throttle.
- the control chamber pressure preferably causes a force acting on the valve element in the closing direction, while the pressure in at least one further pressure chamber causes a force acting on the valve element in the opening direction. If, for example, the control valve is opened, the pressure drops sharply in at least one further pressure space, preferably between the outlet throttle and the valve seat of the control valve. The pressure difference causes the other valve closes and there is no connection of the control chamber via the inlet throttle with the high-pressure region of the fuel injector. This means that no fuel can flow into the control chamber via the inlet throttle. As a result, the amount of fuel flowing out via the outlet throttle is significantly reduced. Only the amount of fuel displaced from the control chamber by the nozzle needle in the course of its opening movement must still escape via the outlet throttle from the control chamber.
- the outlet throttle can be designed in the episode with a much smaller throttle cross-section, without thereby reducing the opening speed of the nozzle needle or delayed the beginning of the injection.
- valve element of the pressure-actuatable further valve is acted upon in the closing direction by the spring force of a spring.
- the spring serves to return the valve element of the further valve after the end of an injection.
- the spring is supported either directly or indirectly on the one hand on the valve element and on the other hand on the nozzle needle. In this way, the spring can be used in addition to the loading of the nozzle needle with a force independent of the high pressure closing force.
- the valve element limits the control chamber in the axial and / or radial direction. This simplifies the formation of a first control surface to which control chamber pressure is applied.
- the valve element may be designed to be piston-shaped and / or have a section designed as a hollow piston.
- the valve element has a preferably axially extending bore in which the outlet throttle is formed.
- the bore preferably opens on the one hand into the control chamber and on the other hand into a further pressure chamber, which is delimited by a further control surface of the valve element.
- the bore thus connects the control room with the further pressure chamber.
- This further pressure chamber is preferably formed between the outlet throttle and the valve seat of the control valve.
- the valve element has an inlet bore extending preferably radially or obliquely to a longitudinal axis A of the valve element, which connects the control chamber to a pressure chamber.
- the inlet throttle is preferably formed in the inlet bore or upstream thereof outside of the valve element.
- the radially or obliquely extending inlet bore opens on the one hand into the control chamber upstream of the outlet throttle, on the other hand into a pressure chamber, which is connectable in dependence on the switching position of the other valve with the high-pressure region of the fuel injector.
- the valve element is at least partially axially slidably received in a guide bore of a valve member, wherein the guide bore is designed to form at least one pressure chamber and / or cooperating with the valve element annular sealing edge stepped.
- the annular sealing edge seals the at least one further pressure chamber with respect to the high-pressure region of the fuel injector when the valve element bears against the sealing edge.
- the annular sealing edge can also be arranged on the valve element and interact with a sealing surface on the valve piece.
- valve element delimit the at least one pressure chamber formed in the guide bore in the radial and / or axial direction.
- the surfaces defining a pressure chamber in the axial direction preferably also serve as control surfaces, via which the valve element of the further valve can be acted upon by a pressure force.
- the valve element defines at least two pressure chambers, which are arranged at an axial distance from one another and are hydraulically connected via the inlet throttle.
- the inlet throttle is preferably formed in the valve piece and not in the valve element.
- the valve element is acted upon in the opening direction of the spring force of a spring - alternatively or in addition to acting in the closing direction spring force of the aforementioned spring.
- the spring force of the further, acting in the opening direction spring is preferably selected to be greater than the spring force of the spring acting in the closing direction. This applies in particular when the spring acting in the closing direction also serves to return the nozzle needle.
- the spring force of the other spring causes the other valve in the idle state assumes an open position.
- the valve element has a cooperating with a stroke stop radially extending stop surface.
- the opening stroke of the valve element is limited in this way.
- the stroke stop can be formed by a body of the fuel injector, in particular a nozzle body or a holding body, or by a separate, preferably disk-shaped component.
- the disk-shaped component is used in the high-pressure region of the fuel injector and preferably has at least one through-flow opening in order to ensure a connection of the pressure chambers located on either side of and beyond the disk-shaped component.
- the Indian FIG. 1 schematically illustrated fuel injector according to the invention comprises a liftable nozzle needle 2 for releasing and closing a plurality of injection openings 3.
- the movement of the nozzle needle 2 is controlled by a control valve 1, which in the present case designed as a ball valve and a solenoid actuator 27 can be actuated.
- the pressure drop in the control chamber 4 has the consequence that the nozzle needle 2, which limits the control chamber 4 with one end, opens and the injection openings 3 releases. High-pressure fuel from a high-pressure region 11 is then injected into the combustion chamber of an internal combustion engine (not shown) via the injection openings 3. To close the nozzle needle 2, the activation of the solenoid actuator 27 is terminated, so that the spring force of the spring 29 causes the return of the anchor member 31, wherein the spherical control valve member 28 is placed back in the valve seat 30 and the control valve 1 closes.
- the fuel flowing through an inlet throttle 8 from a volume of fuel under high pressure into the control chamber 4 causes a reversal of direction of the nozzle needle movement and, consequently, a continuous closing movement of the nozzle needle 2.
- the nozzle needle 2 returns to its starting position spent and the injection ends.
- a pressure-actuatable further valve 9 is arranged upstream of the inlet throttle 8, which interrupts the supply of high-pressure fuel to the inlet throttle 8 and then into the control chamber 4 in the closed position.
- the pressure-actuable further valve 9 has a displaceable valve element 10 with a first control surface 12 and a second control surface 13.
- the first control surface 12 limits the control chamber 4, so that here control chamber pressure is applied.
- the pressure prevails downstream of the outlet throttle 7 between the outlet throttle 7 and the valve seat 30 of the control valve 1. With the opening of the control valve 1, the pressure drops downstream of the outlet throttle 7 more than in the control chamber 4.
- the high-pressure fuel from a high-pressure volume 11 of the injector in front of the sealing seat of the other valve 9 may act on a part of the second control surface 13, which favors the immediate initiation of the opening operation of the further valve 9 after closing the control valve 1.
- the first still present opening movement of the nozzle needle 2 now leads to a compression of the fuel in the control chamber 4 and thus to a brief Increase in the control room pressure.
- the control chamber pressure may exceed the high pressure in the high-pressure region 11 of the injector. Due to the increase in the control chamber pressure, the nozzle needle 2 is braked and reverses its direction of movement, so that the fuel in the control chamber 4 relaxes again and the control chamber pressure decreases again. If the sealing diameter 20 selected larger than the control chamber diameter, so the short-term exceeding the pressure level in the high pressure chamber 11 by the pressure in the control chamber 4 and in the pressure chambers 17, 18 and 19 results in a resulting opening force on the valve element 10 and thus to open at the Sealing edge 20 formed sealing seat.
- the opening operation of the valve element 10 causes a further increase in the force in the opening direction on the valve element 10 and thus a positive feedback on the opening movement, which stabilizes the opening operation of the other valve 9.
- a received between the valve member 16 and a body 24 disc-shaped member 25 forms a stroke stop 22, which cooperates with a radially extending stop surface 23 on the valve element 10 to limit limiting.
- the spring 14 which at the same time serves as a nozzle needle closing spring in the present case, is not supported on the valve element 10 but, for example, on the body 24, it is not necessary for the spring force of the spring 21 to be greater than that of the spring 14.
- An additional spring 21, whose spring force acts on the valve element 10 in the opening direction, can also in the in the FIGS. 3 to 5 used embodiment shown.
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
Description
Die Erfindung betrifft einen Kraftstoffinjektor für ein Kraftstoffeinspritzsystem, insbesondere ein Common-Rail-Einspritzsystem, mit den Merkmalen des Oberbegriffs des Anspruchs 1.The invention relates to a fuel injector for a fuel injection system, in particular a common rail injection system, having the features of the preamble of claim 1.
Aus der Offenlegungsschrift
Da über das mindestens eine Drosselelement konstant eine Verbindung zwischen einem unter Hochdruck stehenden Kraftstoffvolumen und dem Steuerraum besteht, unabhängig davon, ob die Verbindung zum Kraftstoffrücklauf geöffnet oder geschlossen ist, fließt eine nicht unwesentliche Menge an Kraftstoff bei geöffnetem Steuerventil durch den Steuerraum hindurch vom Hochdruckbereich des Injektors zum Kraftstoffrücklauf. Diese durchströmende Kraftstoffmenge trägt nicht direkt zur Injektorfunktion bei, muss aber zusätzlich durch eine Hochdruckpumpe bereitgestellt werden. Die funktional nutzlose, durchströmende Kraftstoffmenge erhöht also die Anforderungen an die Fördermengenkapazität der Hochdruckpumpe und es erhöhen sich deren Antriebsmoment sowie Antriebsleistung. Zugleich verschlechtern sich der Wirkungsgrad des Kraftstoffeinspritzsystems und die CO2-Bilanz des zugehörigen Fahrzeugs.Since there is a constant connection between a high-pressure fuel volume and the control chamber via the at least one throttle element, irrespective of whether the connection to the fuel return is open or closed, a not insignificant amount of fuel flows when the fuel is open Control valve through the control chamber from the high pressure area of the injector to the fuel return. This amount of fuel flowing through does not contribute directly to the injector function, but must additionally be provided by a high-pressure pump. The functionally useless, flowing fuel quantity thus increases the requirements of the delivery capacity of the high pressure pump and it increases their drive torque and drive power. At the same time, the efficiency of the fuel injection system and the CO 2 balance of the associated vehicle deteriorate.
Aufgabe der vorliegenden Erfindung ist es daher, einen Kraftstoffinjektor der vorstehend genannten Art anzugeben, bei welchem zur Verringerung der dem Kraftstoffrücklauf zugeführten Kraftstoffmenge der Zustrom aus dem unter Hochdruck stehenden Kraftstoffvolumen in den Steuerraum unterbrechbar ist.Object of the present invention is therefore to provide a fuel injector of the aforementioned type, in which to reduce the fuel return supplied amount of fuel, the influx from the high pressure fuel volume is interrupted in the control room.
Zur Lösung der Aufgabe wird der Kraftstoffinjektor mit den Merkmalen des Anspruchs 1 vorgeschlagen. Vorteilhafte Weiterbildungen der Erfindung sind in den Unteransprüchen angegeben.To solve the problem, the fuel injector with the features of claim 1 is proposed. Advantageous developments of the invention are specified in the subclaims.
Der vorgeschlagene Kraftstoffinjektor umfasst ein Steuerventil zur Steuerung der Hubbewegung einer hubbeweglichen Düsennadel zum Freigeben und Verschließen wenigstens einer Einspritzöffnung, wobei das der Einspritzöffnung abgewandte Ende der Düsennadel einen Steuerraum begrenzt. Der Steuerraum ist zur Beeinflussung eines auf die Düsennadel einwirkenden Steuerraumdrucks über eine Zulaufdrossel mit unter Hochdruck stehendem Kraftstoff befüllbar und in Offenstellung des Steuerventils über eine Ablaufdrossel entlastbar. Erfindungsgemäß ist stromaufwärts der Zulaufdrossel ein druckbetätigbares weiteres Ventil mit einem verschiebbaren Ventilelement zum Freigeben und Verschließen einer hydraulischen Verbindung der Zulaufdrossel mit einem Hochdruckbereich ausgebildet. Durch das weitere stromaufwärts der Zulaufdrossel ausgebildete Ventil kann der Zustrom aus einem unter Hochdruck stehenden Kraftstoffvolumen in den Steuerraum unterbrochen werden. Dies ist dann von Vorteil, wenn das Steuerventil geöffnet und der Steuerraum über die Ablaufdrossel entlastet wird. Denn einerseits wird der Steuerraum schneller entlastet, da keine zusätzliche Menge Kraftstoff in den Steuerraum nachströmt, andererseits wird die Rücklaufmenge reduziert und damit der Wirkungsgrad des Kraftstoffeinspritzsystems erhöht. Da sich der bei geöffnetem Steuerventil durch die Ablaufdrossel fließende Volumenstrom erheblich reduziert, kann die Ablaufdrossel mit einem erheblich verringerten Drosselquerschnitt ausgeführt werden. Indem das weitere Ventil druckbetätigbar ist, kann dieses als einfaches passives Ventil ausgelegt sein, welches unabhängig von einer Aktorik, insbesondere unabhängig von einem zur Betätigung des Steuerventils vorgesehenen Aktor betätigbar ist.The proposed fuel injector comprises a control valve for controlling the lifting movement of a liftable nozzle needle for releasing and closing at least one injection opening, wherein the end of the nozzle needle facing away from the injection opening delimits a control space. The control chamber can be filled to influence a control chamber pressure acting on the nozzle needle via an inlet throttle with high-pressure fuel and can be relieved in the open position of the control valve via an outlet throttle. According to the invention upstream of the inlet throttle is a pressure-actuated further valve with a displaceable valve element for releasing and closing a hydraulic connection of the inlet throttle formed with a high-pressure region. Due to the further valve formed upstream of the inlet throttle, the inflow from a high-pressure fuel volume into the control chamber can be interrupted. This is advantageous when the control valve is opened and the control chamber is relieved via the outlet throttle. On the one hand, the control chamber is relieved faster because no additional amount of fuel flows into the control chamber, on the other hand, the return flow reduces and thus increases the efficiency of the fuel injection system. Since the volume flow flowing through the outlet throttle when the control valve is open is considerably reduced, the outlet throttle can be designed with a considerably reduced throttle cross-section. By the further valve is pressure-actuated, this can be designed as a simple passive valve, which is independent of an actuator, in particular independently of a provided for actuating the control valve actuator operable.
Gemäß einer bevorzugten Ausführungsform der Erfindung besitzt das Ventilelement des druckbetätigbaren weiteren Ventils eine erste Steuerfläche, an welcher der im Steuerraum herrschende Druck anliegt, und wenigstens eine weitere Steuerfläche, an welcher der stromabwärts der Ablaufdrossel zwischen der Ablaufdrossel und einem Ventilsitz des Steuerventils und/oder der stromaufwärts der Zulaufdrossel zwischen dem weiteren Ventil und der Zulaufdrossel herrschende Druck anliegt. Die erste Steuerfläche begrenzt demnach bevorzugt - gemeinsam mit der Düsennadel - den Steuerraum in axialer Richtung. Die wenigstens eine weitere Steuerfläche begrenzt vorzugsweise einen weiteren Druckraum, der stromabwärts der Ablaufdrossel vor dem Ventilsitz des Steuerventils und/oder stromaufwärts, vorzugsweise unmittelbar stromaufwärts, der Zulaufdrossel ausgebildet ist. Da im Ablaufkanal stromabwärts der Ablaufdrossel und/oder unmittelbar stromaufwärts der Zulaufdrossel ein zumindest zeitweise vom Steuerraumdruck abweichender Druck herrscht bzw. herrschen, kann über die Druckdifferenz bzw. die Druckdifferenzen zwischen dem Steuerraumdruck und dem Druck bzw. den Drücken im wenigstens einen weiteren Druckraum das weitere Ventil betätigt werden.According to a preferred embodiment of the invention, the valve element of the pressure-actuable further valve has a first control surface, which abuts the pressure prevailing in the control chamber, and at least one further control surface, at which the downstream of the outlet throttle between the outlet throttle and a valve seat of the control valve and / or the upstream of the inlet throttle between the other valve and the inlet throttle ruling pressure prevails. The first control surface therefore preferably limits - together with the nozzle needle - the control chamber in the axial direction. The at least one further control surface preferably defines a further pressure chamber, which is formed downstream of the outlet throttle in front of the valve seat of the control valve and / or upstream, preferably immediately upstream, of the inlet throttle. Since in the outlet channel downstream of the outlet throttle and / or immediately upstream of the inlet throttle prevails at least temporarily diverging from the control chamber pressure or prevail over the pressure difference or the pressure differences between the control chamber pressure and the pressure or pressures in at least one further pressure chamber the other Valve operated.
Vorzugsweise bewirkt der Steuerraumdruck eine auf das Ventilelement in Schließrichtung wirkende Kraft, während der Druck im wenigstens einen weiteren Druckraum eine auf das Ventilelement in Öffnungsrichtung wirkende Kraft bewirkt. Wird beispielsweise das Steuerventil geöffnet, fällt der Druck im wenigstens einen weiteren Druckraum, vorzugsweise zwischen der Ablaufdrossel und dem Ventilsitz des Steuerventils, stark ab. Die Druckdifferenz bewirkt, dass das weitere Ventil schließt und keine Verbindung des Steuerraums über die Zulaufdrossel mit dem Hochdruckbereich des Kraftstoffinjektors besteht. Das heißt, dass kein Kraftstoff über die Zulaufdrossel in den Steuerraum nachströmen kann. In der Folge wird die über die Ablaufdrossel abströmende Kraftstoffmenge deutlich reduziert. Lediglich die von der Düsennadel im Zuge ihrer Öffnungsbewegung aus dem Steuerraum verdrängte Kraftstoffmenge muss noch über die Ablaufdrossel aus dem Steuerraum entweichen. Eine vom Hochdruckbereich über Zulauf- und Ablaufdrossel zum Injektorrücklauf fließende Kraftstoffmenge existiert nicht mehr. Die Ablaufdrossel kann in der Folge mit einem erheblich kleineren Drosselquerschnitt ausgelegt werden, ohne dass sich dadurch die Öffnungsgeschwindigkeit der Düsennadel verringert oder der Beginn der Einspritzung verzögert. Schließt das Steuerventil, dann steigt der Druck im wenigstens einen Druckraum zwischen der Ablaufdrossel und dem Steuerventilsitz auf den Steuerraumdruck an. Des weiteren kann die Druckdifferenz zwischen dem Hochdruck und dem Steuerraumdruck eine zusätzliche Öffnungskraft auf das Ventilelement des weiteren Ventils bewirken, so dass dieses nach dem Schließen des Steuerventils sicher zu öffnen beginnt. Über den dadurch entstehenden Druckabfall an der Zulaufdrossel kann dann eine weitere Steigerung der Öffnungskraft auf das Ventilelement bewirkt werden, so dass dieses schnell vollständig öffnet und unmittelbar stromaufwärts der Zulaufdrossel sehr schnell wieder der Hochdruck ungedrosselt ansteht.The control chamber pressure preferably causes a force acting on the valve element in the closing direction, while the pressure in at least one further pressure chamber causes a force acting on the valve element in the opening direction. If, for example, the control valve is opened, the pressure drops sharply in at least one further pressure space, preferably between the outlet throttle and the valve seat of the control valve. The pressure difference causes the other valve closes and there is no connection of the control chamber via the inlet throttle with the high-pressure region of the fuel injector. This means that no fuel can flow into the control chamber via the inlet throttle. As a result, the amount of fuel flowing out via the outlet throttle is significantly reduced. Only the amount of fuel displaced from the control chamber by the nozzle needle in the course of its opening movement must still escape via the outlet throttle from the control chamber. A fuel quantity flowing from the high-pressure region via inlet and outlet throttle to the injector return no longer exists. The outlet throttle can be designed in the episode with a much smaller throttle cross-section, without thereby reducing the opening speed of the nozzle needle or delayed the beginning of the injection. When the control valve closes, the pressure in the at least one pressure chamber between the outlet throttle and the control valve seat increases to the control chamber pressure. Furthermore, the pressure difference between the high pressure and the control chamber pressure can cause an additional opening force on the valve element of the further valve, so that it begins to open safely after closing the control valve. On the resulting pressure drop at the inlet throttle then a further increase in the opening force can be effected on the valve element, so that this quickly opens completely and immediately upstream of the inlet throttle again very high pressure unthrottled pending.
Weiterhin bevorzugt ist das Ventilelement des druckbetätigbaren weiteren Ventils in Schließrichtung von der Federkraft einer Feder beaufschlagt. Die Feder dient der Rückstellung des Ventilelements des weiteren Ventils nach dem Ende einer Einspritzung. Vorzugsweise ist die Feder einerseits am Ventilelement und andererseits an der Düsennadel jeweils unmittelbar oder mittelbar abgestützt. Auf diese Weise kann die Feder zusätzlich zur Beaufschlagung der Düsennadel mit einer vom Hochdruck unabhängigen Schließkraft eingesetzt werden.Further preferably, the valve element of the pressure-actuatable further valve is acted upon in the closing direction by the spring force of a spring. The spring serves to return the valve element of the further valve after the end of an injection. Preferably, the spring is supported either directly or indirectly on the one hand on the valve element and on the other hand on the nozzle needle. In this way, the spring can be used in addition to the loading of the nozzle needle with a force independent of the high pressure closing force.
Vorteilhafterweise begrenzt das Ventilelement den Steuerraum in axialer und/oder radialer Richtung. Dies vereinfacht die Ausbildung einer ersten Steuerfläche, an welcher Steuerraumdruck anliegt. Das Ventilelement kann hierzu kolbenförmig ausgebildet sein und/oder einen als Hohlkolben ausgebildeten Abschnitt besitzen. Des Weiteren wird vorgeschlagen, dass das Ventilelement eine vorzugsweise axial verlaufende Bohrung besitzt, in der die Ablaufdrossel ausgebildet ist. Die Bohrung mündet bevorzugt einerseits in den Steuerraum und andererseits in einen weiteren Druckraum, der von einer weiteren Steuerfläche des Ventilelements begrenzt wird. Die Bohrung verbindet demnach den Steuerraum mit dem weiteren Druckraum. Dieser weitere Druckraum ist vorzugsweise zwischen der Ablaufdrossel und dem Ventilsitz des Steuerventils ausgebildet.Advantageously, the valve element limits the control chamber in the axial and / or radial direction. This simplifies the formation of a first control surface to which control chamber pressure is applied. The valve element may be designed to be piston-shaped and / or have a section designed as a hollow piston. Furthermore, it is proposed that the valve element has a preferably axially extending bore in which the outlet throttle is formed. The bore preferably opens on the one hand into the control chamber and on the other hand into a further pressure chamber, which is delimited by a further control surface of the valve element. The bore thus connects the control room with the further pressure chamber. This further pressure chamber is preferably formed between the outlet throttle and the valve seat of the control valve.
Als weiterbildende Maßnahme wird vorgeschlagen, dass das Ventilelement eine vorzugsweise radial oder schräg zu einer Längsachse A des Ventilelements verlaufende Zulaufbohrung besitzt, welche den Steuerraum mit einem Druckraum verbindet. Die Zulaufdrossel ist vorzugsweise in der Zulaufbohrung oder stromaufwärts davon außerhalb des Ventilelements ausgebildet. Bevorzugt mündet die radial oder schräg verlaufende Zulaufbohrung einerseits in den Steuerraum stromaufwärts der Ablaufdrossel, andererseits in einen Druckraum, der in Abhängigkeit von der Schaltstellung des weiteren Ventils mit dem Hochdruckbereich des Kraftstoffinjektors verbindbar ist. Unabhängig davon, ob die Zulaufdrossel im Ventilelement in der Zulaufbohrung ausgeführt ist oder stromaufwärts davon außerhalb des Ventilelements, liegt der Dichtsitz des weiteren Ventils, über den die Verbindung zum Hochdruckbereich des Injektors geschaltet wird, stromaufwärts der Zulaufdrossel.As a further development measure, it is proposed that the valve element has an inlet bore extending preferably radially or obliquely to a longitudinal axis A of the valve element, which connects the control chamber to a pressure chamber. The inlet throttle is preferably formed in the inlet bore or upstream thereof outside of the valve element. Preferably, the radially or obliquely extending inlet bore opens on the one hand into the control chamber upstream of the outlet throttle, on the other hand into a pressure chamber, which is connectable in dependence on the switching position of the other valve with the high-pressure region of the fuel injector. Regardless of whether the inlet throttle is carried out in the valve element in the inlet bore or upstream thereof outside the valve element, the sealing seat of the further valve, via which the connection is switched to the high-pressure region of the injector, upstream of the inlet throttle.
Gemäß einer weiteren bevorzugten Ausführungsform der Erfindung ist das Ventilelement zumindest teilweise in einer Führungsbohrung eines Ventilstücks axial verschiebbar aufgenommen, wobei die Führungsbohrung zur Ausbildung wenigstens eines Druckraums und/oder einer mit dem Ventilelement zusammenwirkenden ringförmigen Dichtkante gestuft ausgeführt ist. Die ringförmige Dichtkante dichtet den wenigstens einen weiteren Druckraum gegenüber dem Hochdruckbereich des Kraftstoffinjektors ab, wenn das Ventilelement an der Dichtkante anliegt. Alternativ kann die ringförmige Dichtkante auch am Ventilelement angeordnet sein und mit einer Dichtfläche am Ventilstück zusammenwirken.According to a further preferred embodiment of the invention, the valve element is at least partially axially slidably received in a guide bore of a valve member, wherein the guide bore is designed to form at least one pressure chamber and / or cooperating with the valve element annular sealing edge stepped. The annular sealing edge seals the at least one further pressure chamber with respect to the high-pressure region of the fuel injector when the valve element bears against the sealing edge. Alternatively, the annular sealing edge can also be arranged on the valve element and interact with a sealing surface on the valve piece.
Des Weiteren wird vorgeschlagen, dass das Ventilelement den wenigstens einen innerhalb der Führungsbohrung ausgebildeten Druckraum in radialer und/oder axialer Richtung begrenzt. Die einen Druckraum in axialer Richtung begrenzenden Flächen dienen bevorzugt zugleich als Steuerflächen, über welche das Ventilelement des weiteren Ventils mit einer Druckkraft beaufschlagbar ist. Vorzugsweise begrenzt das Ventilelement wenigstens zwei Druckräume, die in einem axialen Abstand zueinander angeordnet und über die Zulaufdrossel hydraulisch verbunden sind. Die Zulaufdrossel ist in diesem Fall bevorzugt in dem Ventilstück und nicht in dem Ventilelement ausgebildet.Furthermore, it is proposed that the valve element delimit the at least one pressure chamber formed in the guide bore in the radial and / or axial direction. The surfaces defining a pressure chamber in the axial direction preferably also serve as control surfaces, via which the valve element of the further valve can be acted upon by a pressure force. Preferably, the valve element defines at least two pressure chambers, which are arranged at an axial distance from one another and are hydraulically connected via the inlet throttle. In this case, the inlet throttle is preferably formed in the valve piece and not in the valve element.
Gemäß einer weiteren bevorzugten Ausführungsform der Erfindung ist das Ventilelement - alternativ oder ergänzend zur in Schließrichtung wirkenden Federkraft der bereits genannten Feder - in Öffnungsrichtung von der Federkraft einer Feder beaufschlagt. Sofern zwei Federn vorgesehen sind, deren Federkräfte einander entgegen gesetzt sind, ist vorzugsweise die Federkraft der weiteren, in Öffnungsrichtung wirkenden Feder größer als die Federkraft der in Schließrichtung wirkenden Feder gewählt. Dies gilt insbesondere dann, wenn die in Schließrichtung wirkende Feder zugleich der Rückstellung der Düsennadel dient. Die Federkraft der weiteren Feder bewirkt, dass das weitere Ventil im Ruhezustand eine geöffnete Position einnimmt.According to a further preferred embodiment of the invention, the valve element is acted upon in the opening direction of the spring force of a spring - alternatively or in addition to acting in the closing direction spring force of the aforementioned spring. If two springs are provided whose spring forces are set against each other, the spring force of the further, acting in the opening direction spring is preferably selected to be greater than the spring force of the spring acting in the closing direction. This applies in particular when the spring acting in the closing direction also serves to return the nozzle needle. The spring force of the other spring causes the other valve in the idle state assumes an open position.
Vorteilhafterweise besitzt das Ventilelement eine mit einem Hubanschlag zusammenwirkende radial verlaufende Anschlagfläche. Der Öffnungshub des Ventilelementes wird auf diese Weise begrenzt. Dabei kann der Hubanschlag von einem Körper des Kraftstoffinjektors, insbesondere einem Düsenkörper oder einem Haltekörper, oder von einem separaten, vorzugsweise scheibenförmigen Bauteil ausgebildet werden. Das scheibenförmige Bauteil ist im Hochdruckbereich des Kraftstoffinjektors eingesetzt und besitzt bevorzugt wenigstens eine Durchströmöffnung, um eine Verbindung der diesseits und jenseits des scheibenförmigen Bauteils gelegenen Druckräume zu gewährleisten.Advantageously, the valve element has a cooperating with a stroke stop radially extending stop surface. The opening stroke of the valve element is limited in this way. In this case, the stroke stop can be formed by a body of the fuel injector, in particular a nozzle body or a holding body, or by a separate, preferably disk-shaped component. The disk-shaped component is used in the high-pressure region of the fuel injector and preferably has at least one through-flow opening in order to ensure a connection of the pressure chambers located on either side of and beyond the disk-shaped component.
In einer Weiterbildung der Erfindung ist das der Einspritzöffnung abgewandte Ende der Düsennadel von einer Dichthülse umgeben. Die Dichthülse begrenzt den zwischen der Düsennadel und dem Ventilelement des weiteren Ventil ausgebildeten Steuerraum in radialer Richtung. Die Dichthülse ist hierzu bevorzugt an dem Ventilelement abgestützt und/oder zur Abdichtung des Steuerraums gegenüber dem Hochdruckbereich über die Federkraft der Feder in Richtung des Ventilelementes axial vorgespannt. Die Dichthülse ermöglicht den Ausgleich eines etwaigen Achsversatzes zwischen der Düsennadel und dem Ventilelement. Zugleich wird die Ausbildung des Ventilelements vereinfacht.In one embodiment of the invention, the injection opening facing away from the end of the nozzle needle is surrounded by a sealing sleeve. The sealing sleeve defines the control space formed between the nozzle needle and the valve element of the further valve in the radial direction. For this purpose, the sealing sleeve is preferably supported on the valve element and / or axially preloaded in the direction of the valve element for sealing the control chamber with respect to the high-pressure region via the spring force of the spring. The sealing sleeve allows the compensation of any axial offset between the nozzle needle and the valve element. At the same time, the formation of the valve element is simplified.
Bevorzugte Ausführungsformen der Erfindung werden nachfolgend anhand der beigefügten Zeichnungen näher beschrieben. Diese zeigen:
-
Figur 1 ein hydraulisches Schaltbild einer ersten bevorzugten Ausführungsform eines erfindungsgemäßen Kraftstoffinjektors, -
ein hydraulisches Schaltbild einer zweiten bevorzugten Ausführungsform eines erfindungsgemäßen Kraftstoffinjektors,Figur 2 -
einen Längsschnitt durch eine erste bevorzugte Ausführungsform eines erfindungsgemäßen Kraftstoffinjektors bei geschlossenem Steuerventil,Figur 3 -
denFigur 4Injektor der Figur 3 bei geöffnetem Steuerventil, -
denFigur 5Injektor der Figur 3 bei geschlossenem Steuerventil und geöffnetem weiteren Ventil, -
Figur 6 einen Längsschnitt durch eine zweite bevorzugte Ausführungsform eines erfindungsgemäßen Kraftstoffinjektors bei geschlossenem Steuerventil, -
den Injektor derFigur 7Figur 6 bei geöffnetem Steuerventil, -
den Injektor derFigur 8Figur 6 bei geschlossenem Steuerventil und geöffnetem weiteren Ventil, -
einen Längsschnitt durch eine dritte bevorzugte Ausführungsform eines erfindungsgemäßen Kraftstoffinjektors bei geschlossenem Steuerventil undFigur 9 -
einen Längsschnitt durch eine vierte bevorzugte Ausführungsform eines erfindungsgemäßen Kraftstoffinjektors bei geschlossenem Steuerventil.Figur 10
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FIG. 1 a hydraulic circuit diagram of a first preferred embodiment of a fuel injector according to the invention, -
FIG. 2 a hydraulic circuit diagram of a second preferred embodiment of a fuel injector according to the invention, -
FIG. 3 a longitudinal section through a first preferred embodiment of a fuel injector according to the invention with a closed control valve, -
FIG. 4 the injector ofFIG. 3 with open control valve, -
FIG. 5 the injector ofFIG. 3 with closed control valve and opened further valve, -
FIG. 6 a longitudinal section through a second preferred embodiment of a fuel injector according to the invention with a closed control valve, -
FIG. 7 the injector ofFIG. 6 with open control valve, -
FIG. 8 the injector ofFIG. 6 with closed control valve and opened further valve, -
FIG. 9 a longitudinal section through a third preferred embodiment of a fuel injector according to the invention with a closed control valve and -
FIG. 10 a longitudinal section through a fourth preferred embodiment of a fuel injector according to the invention with a closed control valve.
Der in der
Bei deaktiviertem Magnetaktor 27 wird ein kugelförmiges Steuerventilelement 28 des Steuerventils 1 von der Druckkraft einer Feder 29 gegen einen Ventilsitz 30 gedrückt. Als Druckübertragungsglied dient ein Ankerelement 31, das zwischen der Feder 29 und dem Steuerventilelement 28 angeordnet ist. Bei aktiviertem Magnetaktor 27 wird das Ankerelement 31 entgegen der Federkraft der Feder 29 in Richtung des Magnetaktors 27 gezogen, wobei das Steuerventil 1 öffnet. Bei geöffnetem Steuerventil 1 besteht eine Verbindung eines Steuerraums 4 über eine Ablaufdrossel 7 mit einem Rücklauf 32, so dass eine Entlastung des Steuerraums 4 bewirkt wird. Der Druckabfall im Steuerraum 4 hat zur Folge, dass die Düsennadel 2, die mit einem Ende den Steuerraum 4 begrenzt, öffnet und die Einspritzöffnungen 3 freigibt. Über die Einspritzöffnungen 3 wird dann unter Hochdruck stehender Kraftstoff aus einem Hochdruckbereich 11 in den Brennraum einer Brennkraftmaschine (nicht dargestellt) eingespritzt. Zum Schließen der Düsennadel 2 wird die Aktivierung des Magnetaktors 27 beendet, so dass die Federkraft der Feder 29 die Rückstellung des Ankerelements 31 bewirkt, wobei das kugelförmige Steuerventilelement 28 zurück in den Ventilsitz 30 gestellt wird und das Steuerventil 1 schließt. In Schließstellung des Steuerventils 1 bewirkt der über eine Zulaufdrossel 8 aus einem Volumen mit unter Hochdruck stehendem Kraftstoff in den Steuerraum 4 nachströmende Kraftstoff eine Richtungsumkehr der Düsennadelbewegung und in der Folge eine kontinuierliche Schließbewegung der Düsennadel 2. Dadurch wird die Düsennadel 2 schließlich in ihre Ausgangsposition zurück verbracht und die Einspritzung endet.When the
Zur Reduzierung der bei geöffnetem Steuerventil 1 über die Ablaufdrossel 7 abströmenden Kraftstoffmenge, ist stromaufwärts der Zulaufdrossel 8 ein druckbetätigbares weiteres Ventil 9 angeordnet, das in Schließstellung den Zulauf von unter Hochdruck stehendem Kraftstoff zur Zulaufdrossel 8 und danach in den Steuerraum 4 unterbricht. Das druckbetätigbare weitere Ventil 9 weist hierzu ein verschiebbares Ventilelement 10 mit einer ersten Steuerfläche 12 und einer zweiten Steuerfläche 13 auf. Die erste Steuerfläche 12 begrenzt den Steuerraum 4, so dass hier Steuerraumdruck anliegt. An der zweiten Steuerfläche 13 liegt der Druck an, der stromabwärts der Ablaufdrossel 7 zwischen der Ablaufdrossel 7 und dem Ventilsitz 30 des Steuerventils 1 herrscht. Mit Öffnen des Steuerventils 1 fällt der Druck stromabwärts der Ablaufdrossel 7 stärker ab als im Steuerraum 4. Die Druckdifferenz bewirkt, dass das Ventilelement 10 des weiteren Ventils 9 von einer auf die erste Steuerfläche 12 wirkenden Schließkraft beaufschlagt wird, welche größer als eine auf die zweite Steuerfläche 13 wirkende Öffnungskraft ist, die aus dem hieran anliegenden hydraulischen Druck sowie der Federkraft einer Feder 14 resultiert. Dies hat zur Folge, dass das weitere Ventil 9 schließt und mangels Verbindung zu einem Hochdruckspeicher 33 kein Kraftstoff über die Zulaufdrossel 8 in den Steuerraum 4 nachströmt. Mit Schließen des Steuerventils 1 gleichen sich die Druckverhältnisse am Ventilelement 10 des weiteren Ventils 9 an, was ein Öffnen des weiteren Ventils 9 und damit eine schnelle Wiederbefüllung des Steuerraums 4 über die Zulaufdrossel 8 zur Folge hat.In order to reduce the amount of fuel flowing out through the
In der
Den
Ist das Verhältnis der beiden Durchmesser umgekehrt gewählt, ist also der Dichtdurchmesser 20 kleiner als der Steuerraumdurchmesser, so bewirkt die Überschreitung des Druckniveaus im Hochdruckraum 11 durch den Druck im Steuerraum 4 sowie in den Druckräumen 17, 18 und 19 eine zusätzliche Schließkraft auf das Ventilelement 10 und das weitere Ventil 9 bleibt zunächst geschlossen. Nach dem Umkehrvorgang der Düsennadel 2 nehmen aber die Drücke im Steuerraum 4 sowie in den Druckräumen 17 bis 19 wieder unter den im Hochdruckraum 11 herrschenden Druck ab, was eine resultierende Kraft in Öffnungsrichtung auf das Ventilelement 10 und folglich ein Öffnen des weiteren Ventils 9 zur Folge hat. In diesem Fall ist der Öffnungszeitpunkt des weiteren Ventils 9 unabhängig von der Höhe des kurzen Druckimpulses im Steuerraum 4 während der Düsennadelumkehr. Daher ist diese Ausführungsform besonders vorteilhaft.If the ratio of the two diameters is chosen vice versa, that is, the sealing
Sobald der durch die Dichtkante 20 und das Ventilelement 10 gebildete Dichtsitz des weiteren Ventils 9 öffnet, nimmt der Druck im Druckraum 19 den Wert des Hochdrucks im Hochdruckraum 11 an und damit einen Wert, der höher ist als bei geöffnetem Steuerventil. Somit bewirkt der Öffnungsvorgang des Ventilelements 10 einen weiteren Anstieg der Kraft in Öffnungsrichtung auf das Ventilelement 10 und damit eine Mitkopplung auf die Öffnungsbewegung, welche den Öffnungsvorgang des weiteren Ventils 9 stabilisiert. Ein zwischen dem Ventilstück 16 und einem Körper 24 aufgenommenes scheibenförmiges Bauteil 25 bildet einen Hubanschlag 22 aus, welcher mit einer radial verlaufenden Anschlagfläche 23 am Ventilelement 10 hubbegrenzend zusammenwirkt.As soon as the sealing seat formed by the sealing
Eine alternative konkrete Ausgestaltung eines erfindungsgemäßen Kraftstoffinjektors ist in den
Eine Abwandlung der in den
Eine weitere bevorzugte konkrete Ausgestaltung eines erfindungsgemäßen Kraftstoffinjektors geht aus der
Claims (12)
dadurch gekennzeichnet, dass stromaufwärts der Zulaufdrossel (8) ein druckbetätigbares weiteres Ventil (9) mit einem verschiebbaren Ventilelement (10) zum Freigeben und Verschließen einer hydraulischen Verbindung der Zulaufdrossel (8) mit einem Hochdruckbereich (11) ausgebildet ist.Fuel injector for a fuel injection system, in particular a common rail injection system, comprising a control valve (1) for controlling the lifting movement of a liftable nozzle needle (2) for releasing and closing at least one injection opening (3), wherein the injection opening (3) facing away from the end Nozzle needle (2) delimits a control chamber (4) which can be filled with high-pressure fuel via an inlet throttle (8) to influence a control chamber pressure acting on the nozzle needle (2) and can be relieved in the open position of the control valve (1) via an outlet throttle (7) is
characterized in that upstream of the inlet throttle (8) is a druckbetätigbares further valve (9) with a displaceable valve element (10) for releasing and closing a hydraulic connection of the inlet throttle (8) with a high-pressure region (11) is formed.
dadurch gekennzeichnet, dass das Ventilelement (10) des druckbetätigbaren weiteren Ventils (9) eine erste Steuerfläche (12), an welcher der im Steuerraum (4) herrschende Druck anliegt, und wenigstens eine weitere Steuerfläche (13) besitzt, an welcher der stromabwärts der Ablaufdrossel (7) zwischen der Ablaufdrossel (7) und einem Ventilsitz (30) des Steuerventils (1) und/oder der stromaufwärts der Zulaufdrossel (8) zwischen dem weiteren Ventil (9) und der Zulaufdrossel (8) herrschende Druck anliegt.Fuel injector according to claim 1,
characterized in that the valve element (10) of the pressure-actuated further valve (9) has a first control surface (12) against which the pressure prevailing in the control chamber (4) and at least one further control surface (13) at which the downstream of the Outflow throttle (7) between the outlet throttle (7) and a valve seat (30) of the control valve (1) and / or the upstream of the inlet throttle (8) between the further valve (9) and the inlet throttle (8) prevails pressure.
dadurch gekennzeichnet, dass das Ventilelement (10) des druckbetätigbaren weiteren Ventils (9) in Schließrichtung von der Federkraft einer Feder (14) beaufschlagt ist, die vorzugsweise einerseits am Ventilelement (10) und andererseits an der Düsennadel (2) jeweils unmittelbar oder mittelbar abgestützt ist.Fuel injector according to claim 1 or 2,
characterized in that the valve element (10) of the pressure-actuated further valve (9) is acted upon in the closing direction by the spring force of a spring (14), preferably on the one hand on the valve element (10) and on the other hand on the nozzle needle (2) respectively directly or indirectly supported is.
dadurch gekennzeichnet, dass das Ventilelement (10) den Steuerraum (4) in axialer und/oder radialer Richtung begrenzt und eine vorzugsweise axial verlaufende Bohrung besitzt, in der die Ablaufdrossel (7) ausgebildet ist.Fuel injector according to one of the preceding claims,
characterized in that the valve element (10) delimits the control chamber (4) in the axial and / or radial direction and has a preferably axially extending bore in which the outlet throttle (7) is formed.
dadurch gekennzeichnet, dass das Ventilelement (10) eine vorzugsweise radial oder schräg zu einer Längsachse (A) des Ventilelements (10) verlaufende Zulaufbohrung (5) besitzt, welche den Steuerraum (4) mit einem Druckraum (18, 19) verbindet.Fuel injector according to one of the preceding claims,
characterized in that the valve element (10) has a preferably radially or obliquely to a longitudinal axis (A) of the valve element (10) extending inlet bore (5) which connects the control chamber (4) with a pressure chamber (18, 19).
dadurch gekennzeichnet, dass die Zulaufdrossel (8) in der Zulaufbohrung (5) ausgebildet ist.Fuel injector according to claim 5,
characterized in that the inlet throttle (8) is formed in the inlet bore (5).
dadurch gekennzeichnet, dass das Ventilelement (10) zumindest teilweise in einer Führungsbohrung (15) eines Ventilstücks (16) axial verschiebbar aufgenommen ist, wobei die Führungsbohrung (15) zur Ausbildung wenigstens eines Druckraums (17, 18, 19) und/oder einer mit dem Ventilelement (10) zusammenwirkenden ringförmigen Dichtkante (20) gestuft ausgeführt ist.Fuel injector according to one of the preceding claims,
characterized in that the valve element (10) is at least partially axially slidably received in a guide bore (15) of a valve piece (16), wherein the guide bore (15) for forming at least one pressure chamber (17, 18, 19) and / or one with the valve element (10) cooperating annular sealing edge (20) is executed stepped.
dadurch gekennzeichnet, dass das Ventilelement (10) den wenigstens einen innerhalb der Führungsbohrung (15) ausgebildeten Druckraum (17, 18, 19) in radialer und/oder axialer Richtung begrenzt, wobei vorzugsweise wenigstens zwei Druckräume (18, 19) in einem axialen Abstand zueinander angeordnet und über die Zulaufdrossel (8) hydraulisch verbunden sind.Fuel injector according to claim 7,
characterized in that the valve element (10) defines the at least one within the guide bore (15) formed pressure chamber (17, 18, 19) in the radial and / or axial direction, preferably at least two pressure chambers (18, 19) at an axial distance arranged to each other and are hydraulically connected via the inlet throttle (8).
dadurch gekennzeichnet, dass die Zulaufdrossel (8) den Steuerraum (4) mit dem Druckraum (19) verbindet.Fuel injector according to claim 6 or 7,
characterized in that the inlet throttle (8) connects the control chamber (4) with the pressure chamber (19).
dadurch gekennzeichnet, dass das Ventilelement (10) in Öffnungsrichtung von der Federkraft einer Feder (21) beaufschlagt ist, wobei die Federkraft der Feder (21) vorzugsweise größer als die Federkraft der Feder (14) ist.Fuel injector according to one of the preceding claims,
characterized in that the valve element (10) is acted upon in the opening direction by the spring force of a spring (21), wherein the spring force of the spring (21) is preferably greater than the spring force of the spring (14).
dadurch gekennzeichnet, dass das Ventilelement (10) eine mit einem Hubanschlag (22) zusammenwirkende radial verlaufende Anschlagfläche (23) besitzt, wobei der Hubanschlag (22) von einem Körper (24) des Kraftstoffinjektors oder einem separaten, vorzugsweise scheibenförmigen Bauteil (25) ausgebildet wird.Fuel injector according to one of the preceding claims,
characterized in that the valve element (10) has a stroke stop (22) cooperating radially extending stop surface (23), wherein the stroke stop (22) of a body (24) of the fuel injector or a separate, preferably disc-shaped member (25) becomes.
dadurch gekennzeichnet, dass das der Einspritzöffnung (3) abgewandte Ende der Düsennadel (2) von einer Dichthülse (26) umgeben ist, welche vorzugsweise an dem Ventilelement (10) abgestützt und/oder zur Abdichtung des Steuerraums (4) gegenüber dem Hochdruckbereich (11) über die Federkraft der Feder (14) in Richtung des Ventilelementes (10) axial vorgespannt ist.Fuel injector according to one of the preceding claims,
characterized in that the injection orifice (3) facing away from the end of the nozzle needle (2) by a sealing sleeve (26) is preferably supported on the valve element (10) and / or for sealing the control chamber (4) relative to the high pressure region (11 ) is axially biased by the spring force of the spring (14) in the direction of the valve element (10).
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102012223166.8A DE102012223166A1 (en) | 2012-12-14 | 2012-12-14 | fuel injector |
Publications (3)
Publication Number | Publication Date |
---|---|
EP2743493A2 true EP2743493A2 (en) | 2014-06-18 |
EP2743493A3 EP2743493A3 (en) | 2015-07-29 |
EP2743493B1 EP2743493B1 (en) | 2017-02-08 |
Family
ID=49447474
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP13189766.2A Active EP2743493B1 (en) | 2012-12-14 | 2013-10-22 | Fuel injector |
Country Status (2)
Country | Link |
---|---|
EP (1) | EP2743493B1 (en) |
DE (1) | DE102012223166A1 (en) |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102015205582A1 (en) * | 2015-03-27 | 2016-09-29 | Robert Bosch Gmbh | Fuel injector for a fuel injection system |
DE102015226070A1 (en) * | 2015-12-18 | 2017-06-22 | Robert Bosch Gmbh | fuel injector |
DE102017205772A1 (en) | 2017-04-05 | 2018-10-11 | Robert Bosch Gmbh | ball valve |
EP3990770A1 (en) * | 2019-06-25 | 2022-05-04 | Ganser-Hydromag AG | Fuel injection valve for combustion engines |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102006049050A1 (en) | 2006-10-18 | 2008-04-30 | Robert Bosch Gmbh | Injector for injecting fuel |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP4428357B2 (en) * | 2006-04-03 | 2010-03-10 | 株式会社デンソー | Fuel injection valve |
CH700396A1 (en) * | 2009-02-09 | 2010-08-13 | Ganser Hydromag | Fuel injection valve for internal combustion engines. |
JP5531713B2 (en) * | 2010-03-29 | 2014-06-25 | 株式会社デンソー | Fuel injection device |
-
2012
- 2012-12-14 DE DE102012223166.8A patent/DE102012223166A1/en not_active Withdrawn
-
2013
- 2013-10-22 EP EP13189766.2A patent/EP2743493B1/en active Active
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102006049050A1 (en) | 2006-10-18 | 2008-04-30 | Robert Bosch Gmbh | Injector for injecting fuel |
Also Published As
Publication number | Publication date |
---|---|
EP2743493B1 (en) | 2017-02-08 |
DE102012223166A1 (en) | 2014-06-18 |
EP2743493A3 (en) | 2015-07-29 |
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