EP2019198A2 - Injector - Google Patents
Injector Download PDFInfo
- Publication number
- EP2019198A2 EP2019198A2 EP08104410A EP08104410A EP2019198A2 EP 2019198 A2 EP2019198 A2 EP 2019198A2 EP 08104410 A EP08104410 A EP 08104410A EP 08104410 A EP08104410 A EP 08104410A EP 2019198 A2 EP2019198 A2 EP 2019198A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- chamber
- control
- channel
- injector
- 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
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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
- 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
- F02M63/0012—Valves
- F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
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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
- F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
- F02M63/0045—Three-way valves
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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
- F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
- F02M63/0047—Four-way valves or valves with more than four ways
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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
- 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
- F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
- F02M55/002—Arrangement of leakage or drain conduits in or from injectors
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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
- F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
- F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
- F02M61/167—Means for compensating clearance or thermal expansion
Definitions
- the invention relates to an injector for injecting fuel into a combustion chamber of an internal combustion engine, in particular a common rail injector, according to the preamble of claim 1.
- a common rail injector for injecting fuel in a combustion chamber of an internal combustion engine with a servo-controlled valve element known.
- the valve element is assigned a control valve which can be actuated by means of a piezo actuator.
- the control valve is in turn assigned to a control chamber which is delimited by an end face of the valve element.
- the control chamber is hydraulically connected to a high-pressure region of the injector via an inlet throttle duct formed as an annular channel. In a first switching position of the control valve, a hydraulic connection between the control chamber and a low-pressure region of the injector is interrupted.
- the flow cross sections of the inlet throttle channel and the outlet throttle channel are matched to one another such that in the second switching position of the control valve, a net outflow of fuel from the control chamber results, whereby the pressure in the control chamber decreases and as a result lifts the valve element from its valve seat.
- the well-known injector has proven itself. However, there are still efforts to improve the switching times of injectors.
- the invention begins, whose task is to propose an injector, with the further shortened switching times can be realized. In particular, faster closing times of the valve element should be realized.
- the invention is based on the idea to provide a the control chamber to the valve chamber of the control valve vomyogllkanal, via the fuel, which flows in the first switching position of the control valve through the inlet channel into the valve chamber, can flow further into the control chamber, whereby a faster refilling of the Control chamber and thus a faster closing of the valve element is ensured.
- the closing speed of the valve element is determined at least largely by the additional backfill channel.
- the flow cross sections of the inlet channel and the backfill channel are preferably larger than the flow cross section of the outlet throttle channel and / or the flow cross section of the inlet throttle channel.
- an embodiment is advantageous in which the at least one inlet channel and the at least one backfilling channel have a smaller throttle effect than the inlet throttle channel and / or the outlet throttle channel.
- the fuel flowing into the valve chamber via the inlet channel - depending on the arrangement of the outlet throttle channel - in the first switching position of the control valve either exclusively via the rinse glycollkanal in the Control chamber flows or additionally via the outlet throttle channel.
- a rinse can be realized by the additional provision of aruthellkanals a much faster refilling of the control chamber and thus an optimized closing behavior and optimized switching times of the injector.
- the opening into the control chamber inlet throttle channel and the outlet throttle channel can be designed freely due to the provision of a separate scanyogllkanals on the Ventilelementö Stamms and therefore very small, whereby tax losses are minimized in the low pressure range.
- an embodiment of the injector is dispensed with an inlet throttle channel from the high pressure area to the control room.
- the construction is substantially simplified and the fuel loss quantity is reduced.
- an inlet throttle channel is branched off for permanent connection of the control chamber to the high-pressure region of the inlet channel.
- the inlet channel can open either from a fuel supply channel in the injector body or from a pressure chamber of the injector.
- the inlet throttle channel as a radial bore in a sleeve bounding the control chamber or to arrange the inlet throttle channel as a defined annular gap between the valve element and such a sleeve.
- a simple and cost-effective manufacturability of the injector can be realized when the control valve has a cooperating with a particular at least approximately flat valve seat surface control valve piston.
- the inlet channel opens into this at least approximately flat valve seat surface on which rests the control valve piston in the second switching position.
- the control valve piston and / or the valve seat surface is provided with a peripheral sealing edge (biting edge).
- control valve as a 3/2-way valve
- the backfill channel permanently connects the valve chamber with the control chamber
- the backfill channel of the control valve must therefore not be switched, although such an embodiment is possible.
- the control chamber is not hydraulically connected to the valve chamber flow restrictor channel provided, but this is the control valve, hydraulically seen, downstream and connects a hydraulically arranged behind the control valve area, in particular an intermediate chamber, with the low pressure area of the injector and thus with the injector return.
- an embodiment is advantageous in which the flow cross-section of the inlet channel and / or the flow cross-section of the backfill channel is / are larger than the flow area of the outlet throttle channel and - when providing an inlet throttle channel - are greater than the flow cross-section of this inlet throttle channel, the Control chamber permanently connected to a high pressure area of the injector.
- a piezoelectric actuator is provided for actuating the control valve.
- the provision of a piezoelectric actuator allows an embodiment of the control valve as in the axial direction not pressure-balanced and thus structurally simple and inexpensive control valve.
- Fig. 1 is shown very schematically the structure of an injector 1 designed as a common rail injector.
- the injector 1 is supplied via a high-pressure supply line 2 from a fuel high-pressure accumulator 3 (rail) with fuel at high pressure (preferably higher than 2000 bar), in particular diesel oil or gasoline.
- the fuel high-pressure accumulator 3 is supplied with fuel from a low-pressure reservoir 5 by a high-pressure pump 4 designed as a radial piston pump.
- a low-pressure region 6 of the injector 1 is hydraulically connected via a return 7 to the reservoir 5.
- the pressure in the low-pressure region 6 of the injector 1 is between about 0 and 100 bar, preferably between about 0 and 10 bar.
- a fuel quantity to be explained later is discharged from a control chamber 8 and fed back to the high-pressure circuit via the high-pressure pump 4.
- valve element 10 is arranged within a belonging to a high-pressure region of the injector 1 pressure chamber 9 a one-piece in this embodiment.
- valve element 10 is arranged.
- a multi-part, in particular two-part design of the valve element 10 with control rod and nozzle needle is conceivable.
- the control chamber 8 Radially outward, the control chamber 8 is bounded by a sleeve 12, which is pressed by a closing spring 13 in the axial direction against a throttle plate 14.
- the closing spring 13 is supported on a Peripheral collar 15 of the valve member 10 from and acts on this in the direction of its valve seat 16th
- valve member 10 When the valve member 10 abuts the valve seat 16, i. is in a closed position, the fuel outlet from a nozzle hole arrangement 17 in the combustion chamber (not shown) of the internal combustion engine is locked. If, on the other hand, it is lifted off the valve seat 16, fuel can flow from the pressure chamber 9 via axial channels 18, which are formed by a polygonal contoured guide section 19 of the valve element 10, past the valve seat 16 to the nozzle hole arrangement 17 and from there into the combustion chamber (not shown).
- a control valve 20 associated with the control chamber 8 (servo valve), more precisely a control piston 21 of the control valve 20, transferred from a first switching position shown in a second switching position in which the control piston 21 with a plane lower in the drawing plane (flat) contact surface 22 a first, flat (flat) valve seat surface 23 is moved.
- the coupler space 25 serves to compensate for variations in the length of the actuator 24 caused by temperature fluctuations.
- the control chamber 8 is hydraulically connected via an outlet throttle 26 with the low pressure region 6 of the injector 1.
- Fuel flows via a first portion 27a of an inlet channel 27, which is branched off from the high-pressure supply line 2 (high-pressure region), via an inlet throttle channel 28, which is branched off from the inlet channel 27, into the control chamber 8. From there, the fuel flows via the outlet throttle channel 26 into a valve chamber 29 of the control valve 20 and from there to a hemispherical portion 30 of the control piston 21 passing into an intermediate chamber 31, in which a rod-shaped portion 32 of the control piston 21 is accommodated.
- the fuel flows further into the reservoir 5.
- the flow cross-sections of the inlet throttle channel 28 and the opening from the control chamber 8 into the valve chamber 29 outlet throttle 26 are coordinated such that a net Flow of Fuel from the control chamber 8 results, the fuel pressure in the control chamber 8 thus decreases and the valve element 10 lifts from its valve seat 16 and releases the fuel flow from the pressure chamber 9 (high pressure area) via the nozzle hole arrangement 17 in the combustion chamber of the internal combustion engine.
- valve element 10 are moved to its valve seat 16, the control valve 20 and the control piston 21 from the second switching position in the in Fig. 1 shown moved first switching position in which the hemispherical portion 30 of the control piston 21 rests with its spherical portion on an annular second valve seat surface 33 which is opposite to the planar first valve seat surface 23.
- the energization of the actuator 24 is interrupted, whereby the control piston 21, supported by a spring 34 in the plane of the drawing up to the second valve seat surface 33 of the control valve 20 is moved.
- the flow cross-section of the grant circallkanals 35 is greater than the flow cross-section of the inlet throttle channel 28 and the flow area of the outlet throttle 26, which connects the control chamber 8 permanently hydraulically with the valve chamber 29.
- the scaffoldyogllkanal 35 opens into the flat first valve seat surface 23 for the control piston 21 and is guided in the axial direction into the control chamber 8.
- the scaffoldyogllkanal 35 is connected simultaneously with the inlet channel 27 by means of the control valve 20 and is open only in the first switching position. In the second switching position in which the hemispherical portion 30 rests with its planar contact surface 22 on the planar first valve seat surface 23, both the second portion 27b of the inlet channel 27 and the remindglallkanal 35 are locked. In this second switching position, only fuel flows via the first section 27a of the inlet channel 27 into the inlet throttle channel 28 and from there into the control chamber 8.
- inlet throttle channel 28 is dispensed with the inlet throttle channel 28.
- inlet throttle channel 28 can be realized, in which the inlet throttle channel 28 is not branched off from the inlet channel 27, but is guided, for example, directly from the pressure chamber 9 into the control chamber 8. It is also conceivable that the inlet channel 27 is not branched off from the high pressure supply line 2 within the injector 1, but from the pressure chamber 9.
- FIG. 2 an alternative embodiment of an injector 1 is shown, which is addressed to avoid repetition only to the differences from the already described embodiment.
- the injector 1 according to Fig. 2 has a designed as a 3/2-way valve control valve 20. It can be seen that the outlet throttle channel 26 in comparison to the embodiment according to Fig. 1 in an area, seen hydraulically, behind the valve seat surfaces 23, 33 of the control valve 20, that is arranged between the intermediate chamber 31 and the reservoir 5. The control chamber 8 is thus hydraulically connected exclusively via the rinse chamber 29.
- the flow cross-section of the rinses 35 which in the embodiment according to Fig. 2 at a distance from the first planar valve seat surface 23 opens into the valve chamber 29 and discharges during the rinses, greater than the flow area of the outlet throttle 26 and the flow area of the inlet throttle channel 28, which can optionally be dispensed with.
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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 Injektor zum Einspritzen von Kraftstoff in einen Brennraum einer Brennkraftmaschine, insbesondere einen Common-Rail-Injektor, gemäß dem Oberbegriff des Anspruchs 1.The invention relates to an injector for injecting fuel into a combustion chamber of an internal combustion engine, in particular a common rail injector, according to the preamble of claim 1.
Aus der
An dieser Stelle setzt die Erfindung an, deren Aufgabe es ist, einen Injektor vorzuschlagen, mit dem weiter verkürzte Schaltzeiten realisierbar sind. Insbesondere sollen schnellere Schließzeiten des Ventilelements realisiert werden.At this point, the invention begins, whose task is to propose an injector, with the further shortened switching times can be realized. In particular, faster closing times of the valve element should be realized.
Diese Aufgabe wird mit den Merkmalen des Anspruchs 1 gelöst. Vorteilhafte Weiterbildungen der Erfindung sind in den Unteransprüchen angeben. In den Rahmen der Erfindung fallen auch sämtliche Kombinationen aus zumindest zwei von in der Beschreibung, den Ansprüchen und/oder den Figuren angegebenen Merkmalen.This object is achieved with the features of claim 1. Advantageous developments of the invention are specified in the subclaims. All combinations of at least two features specified in the description, the claims and / or the figures also fall within the scope of the invention.
Der Erfindung liegt der Gedanke zugrunde, einen die Steuerkammer mit der Ventilkammer des Steuerventils verbindenden Rückfüllkanal vorzusehen, über den Kraftstoff, der in der ersten Schaltstellung des Steuerventils durch den Zulaufkanal in die Ventilkammer strömt, weiter in die Steuerkammer strömen kann, wodurch eine schnellere Rückbefüllung der Steuerkammer und damit ein schnelleres Schließen des Ventilelementes sichergestellt wird. Die Schließgeschwindigkeit des Ventilelementes wird dabei zumindest weitgehend durch den zusätzlichen Rückfüllkanal bestimmt. Bevorzugt sind dazu die Durchflussquerschnitte des Zulaufkanals und des Rückfüllkanals größer als der Durchflussquerschnitt des Ablaufdrosselkanals und/oder der Durchflussquerschnitt des Zulaufdrosselkanals. Anders ausgedrückt ist eine Ausführungsform von Vorteil, bei der der mindestens eine Zulaufkanal und der mindestens eine Rückfüllkanal eine geringere Drosselwirkung aufweisen als der Zulaufdrosselkanal und/oder der Ablaufdrosselkanal.The invention is based on the idea to provide a the control chamber to the valve chamber of the control valve Rückfüllkanal, via the fuel, which flows in the first switching position of the control valve through the inlet channel into the valve chamber, can flow further into the control chamber, whereby a faster refilling of the Control chamber and thus a faster closing of the valve element is ensured. The closing speed of the valve element is determined at least largely by the additional backfill channel. For this purpose, the flow cross sections of the inlet channel and the backfill channel are preferably larger than the flow cross section of the outlet throttle channel and / or the flow cross section of the inlet throttle channel. In other words, an embodiment is advantageous in which the at least one inlet channel and the at least one backfilling channel have a smaller throttle effect than the inlet throttle channel and / or the outlet throttle channel.
Es liegt im Rahmen der Erfindung, dass der über den Zulaufkanal in die Ventilkammer strömende Kraftstoff - je nach Anordnung des Ablaufdrosselkanals - in der ersten Schaltstellung des Steuerventils entweder ausschließlich über den Rückfüllkanal in die Steuerkammer strömt oder zusätzlich über den Ablaufdrosselkanal. Jedenfalls kann durch das zusätzliche Vorsehen eines Rückfüllkanals eine wesentlich schnellere Rückbefüllung der Steuerkammer und damit ein optimiertes Schließverhalten bzw. optimierte Schaltzeiten des Injektors realisiert werden. Der in den Steuerraum mündende Zulaufdrosselkanal und der Ablaufdrosselkanal können aufgrund des Vorsehens eines separaten Rückfüllkanals frei auf das Ventilelementöffnungsverhalten ausgelegt und daher sehr klein ausgebildet werden, wodurch Steuerverluste in den Niederdruckbereich minimiert werden. Aufgrund des Vorsehens eines Rückfüllkanals ist eine Ausführungsform des Injektors realisierbar, bei der auf einen Zulaufdrosselkanal aus dem Hochdruckbereich zum Steuerraum verzichtet wird. Bei einer derartigen, zulaufdrosselfreien Ausbildung des Steuerraums bzw. des Injektors vereinfacht sich die Konstruktion wesentlich und die Kraftstoffverlustmenge wird verringert.It is within the scope of the invention that the fuel flowing into the valve chamber via the inlet channel - depending on the arrangement of the outlet throttle channel - in the first switching position of the control valve either exclusively via the Rückfüllkanal in the Control chamber flows or additionally via the outlet throttle channel. In any case, can be realized by the additional provision of a Rückfüllkanals a much faster refilling of the control chamber and thus an optimized closing behavior and optimized switching times of the injector. The opening into the control chamber inlet throttle channel and the outlet throttle channel can be designed freely due to the provision of a separate Rückfüllkanals on the Ventilelementöffnungsverhalten and therefore very small, whereby tax losses are minimized in the low pressure range. Due to the provision of a Rückfüllkanals an embodiment of the injector can be realized, is dispensed with an inlet throttle channel from the high pressure area to the control room. With such a restrictor-free design of the control chamber or of the injector, the construction is substantially simplified and the fuel loss quantity is reduced.
Für den Fall, dass eine den Hochdruckbereich dauerhaft mit der Steuerkammer verbindende Zulaufdrossel vorgesehen ist, kann eine fertigungstechnisch optimierte Konstruktion realisiert werden, nach der ein Zulaufdrosselkanal zur dauerhaften Anbindung der Steuerkammer an den Hochdruckbereich von dem Zulaufkanal abgezweigt ist. Dabei kann der Zulaufkanal entweder aus einem Kraftstoffversorgungskanal im Injektorkörper oder aus einem Druckraum des Injektors ausmünden. Anstelle der Abzweigung der Zulaufdrossel von dem Zulaufkanal ist es denkbar, einen von dem in die Ventilkammer mündenden Zulaufkanal unabhängigen Zulaufdrosselkanal vorzusehen. Beispielsweise ist es in diesem Fall denkbar, den Zulaufdrosselkanal als Radialbohrung in einer die Steuerkammer begrenzenden Hülse einzubringen oder den Zulaufdrosselkanal als definierten Ringspalt zwischen dem Ventilelement und einer derartigen Hülse anzuordnen.In the event that a high-pressure area permanently connected to the control chamber inlet throttle is provided, a production-optimized design can be realized, after which an inlet throttle channel is branched off for permanent connection of the control chamber to the high-pressure region of the inlet channel. In this case, the inlet channel can open either from a fuel supply channel in the injector body or from a pressure chamber of the injector. Instead of the diversion of the inlet throttle from the inlet channel, it is conceivable to provide an inlet channel which is independent of the inlet channel opening into the valve chamber. For example, it is conceivable in this case to introduce the inlet throttle channel as a radial bore in a sleeve bounding the control chamber or to arrange the inlet throttle channel as a defined annular gap between the valve element and such a sleeve.
Eine einfache und kostengünstige Fertigbarkeit des Injektors kann dadurch realisiert werden, wenn das Steuerventil einen mit einer insbesondere zumindest näherungsweise ebenen Ventilsitzfläche zusammenwirkenden Steuerventilkolben aufweist. Bevorzugt mündet der Zulaufkanal in diese zumindest näherungsweise ebene Ventilsitzfläche, auf der der Steuerventilkolben in der zweiten Schaltstellung aufliegt. Um die Dichtheit in der zweiten Schaltstellung zu verbessern, ist eine Ausgestaltungsform realisierbar, bei der der Steuerventilkolben und/oder die Ventilsitzfläche mit einer umlaufenden Dichtkante (Beißkante) versehen ist.A simple and cost-effective manufacturability of the injector can be realized when the control valve has a cooperating with a particular at least approximately flat valve seat surface control valve piston. Preferably, the inlet channel opens into this at least approximately flat valve seat surface on which rests the control valve piston in the second switching position. In order to improve the tightness in the second switching position, an embodiment is feasible, in which the control valve piston and / or the valve seat surface is provided with a peripheral sealing edge (biting edge).
Gemäß einer vorteilhaften Weiterbildung der Erfindung ist vorgesehen, dass in der zweiten Schaltstellung nicht nur der in die Ventilkammer mündende Zulaufkanal, sondern auch der die Ventilkammer hydraulisch mit der Steuerkammer verbindende Rückfüllkanal gesperrt ist. Dies kann auf einfache Weise dadurch realisiert werden, dass der Rückfüllkanal aus der insbesondere ebenen Ventilsitzfläche des Steuerventils ausmündet, in die der Zulaufkanal einmündet. Diese Ausführungsform ermöglicht eine Ausbildung des Steuerventils als 4/2-Wege-Ventil, bei der der Kraftstoff in der ersten Schaltstellung zusätzlich zum Rückfüllkanal über den Ablaufdrosselkanal in die Steuerkammer mündet, die Steuerkammer mit der Ventilkammer also dauerhaft hydraulisch über den Ablaufdrosselkanal verbunden ist.According to an advantageous development of the invention, it is provided that in the second switching position, not only the inlet channel opening into the valve chamber but also the backfilling channel connecting the valve chamber hydraulically to the control chamber is blocked. This can be realized in a simple manner in that the backfill channel opens out of the particular flat valve seat surface of the control valve into which the inlet channel opens. This embodiment allows a design of the control valve as a 4/2-way valve, in which the fuel in the first switching position in addition to the Rückfüllkanal via the outlet throttle channel opens into the control chamber, the control chamber with the valve chamber is thus permanently connected hydraulically via the outlet throttle channel.
Alternativ ist eine Ausbildung des Steuerventils als 3/2-Wege-Ventil denkbar. Bei einer derartigen Ausführungsform ist es möglich, dass der Rückfüllkanal die Ventilkammer dauerhaft mit der Steuerkammer verbindet, der Rückfüllkanal von dem Steuerventil also nicht geschaltet werden muss, wenngleich auch eine derartige Ausführungsform möglich ist. Bei der Ausbildung des Steuerventils als 3/2-Wege-Ventil ist kein die Steuerkammer hydraulisch mit der Ventilkammer verbindender Ablaufdrosselkanal vorgesehen, sondern dieser ist dem Steuerventil, hydraulisch gesehen, nachgeordnet und verbindet einen hydraulisch hinter dem Steuerventil angeordneten Bereich, insbesondere eine Zwischenkammer, mit dem Niederdruckbereich des Injektors und damit mit dem Injektorrücklauf.Alternatively, a design of the control valve as a 3/2-way valve is conceivable. In such an embodiment, it is possible that the backfill channel permanently connects the valve chamber with the control chamber, the backfill channel of the control valve must therefore not be switched, although such an embodiment is possible. In the formation of the control valve as a 3/2-way valve, the control chamber is not hydraulically connected to the valve chamber flow restrictor channel provided, but this is the control valve, hydraulically seen, downstream and connects a hydraulically arranged behind the control valve area, in particular an intermediate chamber, with the low pressure area of the injector and thus with the injector return.
Wie eingangs erwähnt ist eine Ausführungsform von Vorteil, bei der der Durchflussquerschnitt des Zulaufkanals und/oder der Durchflussquerschnitt des Rückfüllkanals größer ist/sind als der Durchflussquerschnitt des Ablaufdrosselkanals und - bei Vorsehen eines Zulaufdrosselkanals - größer sind/ist als der Durchflussquerschnitt dieses Zulaufdrosselkanals, der die Steuerkammer dauerhaft mit einem Hochdruckbereich des Injektors verbindet.As mentioned above, an embodiment is advantageous in which the flow cross-section of the inlet channel and / or the flow cross-section of the backfill channel is / are larger than the flow area of the outlet throttle channel and - when providing an inlet throttle channel - are greater than the flow cross-section of this inlet throttle channel, the Control chamber permanently connected to a high pressure area of the injector.
In einer bevorzugten Ausführungsform ist zum Betätigen des Steuerventils ein Piezoaktor vorgesehen. Insbesondere das Vorsehen eines Piezoaktors ermöglicht eine Ausführungsform des Steuerventils als in axialer Richtung nicht druckausgeglichenes und damit konstruktiv einfaches und kostengünstiges Steuerventil.In a preferred embodiment, a piezoelectric actuator is provided for actuating the control valve. In particular, the provision of a piezoelectric actuator allows an embodiment of the control valve as in the axial direction not pressure-balanced and thus structurally simple and inexpensive control valve.
Weitere Vorteile, Merkmale und Einzelheiten der Erfindung ergeben sich aus der nachfolgenden Beschreibung bevorzugter Ausführungsbeispiele sowie anhand der Zeichnungen; diese zeigen in:
- Fig. 1:
- einen Common-Rail-Injektor mit einem als 4/2-Wege-Ventil ausgebil- deten Steuerventil und
- Fig. 2:
- einen Common-Rail-Injektor mit einem als 3/2-Wege-Ventil ausgebil- deten Steuerventil.
- Fig. 1:
- a common rail injector with a designed as a 4/2-way valve Deten control valve and
- Fig. 2:
- a common rail injector with a control valve designed as a 3/2-way valve.
In den Figuren sind gleiche Bauteile und Bauteile mit der gleichen Funktion mit den gleichen Bezugszeichen gekennzeichnet.In the figures, the same components and components with the same function with the same reference numerals.
In
Innerhalb eines zu einem Hochdruckbereich des Injektors 1 gehörenden Druckraums 9 ist ein in diesem Ausführungsbeispiel einstückiges Ventilelement 10 angeordnet. Alternativ ist eine mehrteilige, insbesondere zweiteilige Ausbildung des Ventilelementes 10 mit Steuerstange und Düsennadel denkbar. Das Ventilelement 10 ist in axialer Richtung längsverschieblich geführt und begrenzt mit seiner in der Zeichnungsebene oberen Stirnseite 11 die Steuerkammer 8. Radial außen wird die Steuerkammer 8 von einer Hülse 12 begrenzt, die von einer Schließfeder 13 in axialer Richtung gegen eine Drosselplatte 14 gedrückt wird. Anderenends stützt sich die Schließfeder 13 an einem Umfangsbund 15 des Ventilelementes 10 ab und beaufschlagt dieses in Richtung auf seinen Ventilsitz 16.Within a belonging to a high-pressure region of the injector 1 pressure chamber 9 a one-piece in this embodiment,
Wenn das Ventilelement 10 am Ventilsitz 16 anliegt, d.h. sich in einer Schließstellung befindet, ist der Kraftstoffaustritt aus einer Düsenlochanordnung 17 in den Brennraum (nicht dargestellt) der Brennkraftmaschine gesperrt. Ist sie dagegen vom Ventilsitz 16 abgehoben, kann Kraftstoff aus dem Druckraum 9 über Axialkanäle 18, die von einem polygonförmig konturierten Führungsabschnitt 19 des Ventilelementes 10 gebildet sind an dem Ventilsitz 16 vorbei zur Düsenlochanordnung 17 und von dort aus in den nicht gezeigten Brennraum strömen.When the
Damit das Ventilelement 10 von seinem Ventilsitz 16 abhebt und sich in der Zeichnungsebene nach oben bewegt, muss der Kraftstoffdruck innerhalb der Steuerkammer 8 abgesenkt werden. Hierzu wird ein der Steuerkammer 8 zugeordnetes Steuerventil 20 (Servoventil), genauer ein Steuerkolben 21 des Steuerventils 20, von einer gezeigten ersten Schaltstellung in eine zweite Schaltstellung überführt, in dem der Steuerkolben 21 mit einer in der Zeichnungsebene unteren ebenen (flachen) Anlagefläche 22 auf eine erste, ebene (flache) Ventilsitzfläche 23 bewegt wird. Hierzu wird ein als Piezoaktor ausgebildeter Aktuator 24, der über einen Kopplerraum 25 hydraulisch mit dem Steuerkolben 21 gekoppelt ist, bestromt. Der Kopplerraum 25 dient dazu, temperaturschwankungsbedingte Längenänderungen des Aktuators 24 auszugleichen.So that the
In der zweiten Schaltstellung, in der der Steuerkolben 21 mit seiner ebenen Anlagefläche 22 auf der ersten Ventilsitzfläche 23 aufliegt, ist die Steuerkammer 8 über einen Ablaufdrosselkanal 26 hydraulisch mit dem Niederdruckbereich 6 des Injektors 1 verbunden. Kraftstoff strömt über einen ersten Abschnitt 27a eines Zulaufkanals 27, der von der Hochdruckversorgungsleitung 2 (Hochdruckbereich) abgezweigt ist, über einen Zulaufdrosselkanal 28, der von dem Zulaufkanal 27 abgezweigt ist, in die Steuerkammer 8. Von dort aus strömt der Kraftstoff über den Ablaufdrosselkanal 26 in eine Ventilkammer 29 des Steuerventils 20 und von dort aus an einem halbkugelförmigen Abschnitt 30 des Steuerkolbens 21 vorbei in eine Zwischenkammer 31, in der ein stangenförmiger Abschnitt 32 des Steuerkolbens 21 aufgenommen ist. Aus der Zwischenkammer 31, die zum Niederdruckbereich 6 des Injektors 1 gehört, fließt der Kraftstoff weiter in den Vorratsbehälter 5. Dabei sind die Durchflussquerschnitte des Zulaufdrosselkanals 28 und des von der Steuerkammer 8 in die Ventilkammer 29 mündenden Ablaufdrosselkanals 26 derart aufeinander abgestimmt, dass ein Netto-Abfluss von Kraftstoff aus der Steuerkammer 8 resultiert, der Kraftstoffdruck in der Steuerkammer 8 also abnimmt und das Ventilelement 10 von seinem Ventilsitz 16 abhebt und den Kraftstofffluss aus dem Druckraum 9 (Hochdruckbereich) über die Düsenlochanordnung 17 in den Brennraum der Brennkraftmaschine freigibt.In the second switching position, in which the
Soll nun der Einspritzvorgang beendet werden, d.h. das Ventilelement 10 auf seinen Ventilsitz 16 bewegt werden, so wird das Steuerventil 20 bzw. der Steuerkolben 21 von der zweiten Schaltstellung in die in
Es ist auch eine Ausführungsform realisierbar, bei der auf den Zulaufdrosselkanal 28 verzichtet wird. Ebenso ist eine Ausführungsform mit Zulaufdrosselkanal 28 realisierbar, bei der der Zulaufdrosselkanal 28 nicht von dem Zulaufkanal 27 abgezweigt ist, sondern beispielsweise unmittelbar aus dem Druckraum 9 in die Steuerkammer 8 geführt ist. Ebenso ist es denkbar, dass der Zulaufkanal 27 nicht aus der Hochdruckversorgungsleitung 2 innerhalb des Injektors 1, sondern aus dem Druckraum 9 abgezweigt ist.It is also an embodiment feasible, is dispensed with the
In
Der Injektor 1 gemäß
In der ersten Schaltstellung, in der der Steuerkolben 21 bzw. der halbkugelförmige Abschnitt 30 mit seiner ebenen Anlagefläche 22 an der ebenfalls ebenen Ventilsitzfläche 23 anliegt, wird lediglich der Zulaufkanal 27 bzw. der zweite Abschnitt 27b des Zulaufkanals 27 gesperrt, so dass Kraftstoff aus der Steuerkammer 8 über den Rückfüllkanal 35, der die Steuerkammer 8 dauerhaft mit der Ventilkammer 29 verbindet, in die Zwischenkammer 31 strömt und von dort aus über den Ablaufdrosselkanal 26 in den Vorratsbehälter 5. Auch bei dem gezeigten Ausführungsbeispiel sind der Durchflussquerschnitt des Zulaufdrosselkanals 28 und der Durchflussquerschnitt des Ablaufdrosselkanals 26 derart aufeinander abgestimmt, dass bei in der ersten Schaltstellung befindlichem Steuerventil 20 ein Nettoabfluss von Kraftstoff aus der Steuerkammer 8 resultiert und folglich das Ventilelement 10 von seinem Ventilsitz 16 abhebt und den Kraftstofffluss in den Brennraum der Brennkraftmaschine freigibt.In the first switching position, in which the
Bei beiden gezeigten Ausführungsbeispielen ist der Durchflussquerschnitt des Rückfüllkanals 35, der in dem Ausführungsbeispiel gemäß
Claims (10)
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE200710034318 DE102007034318A1 (en) | 2007-07-24 | 2007-07-24 | injector |
Publications (3)
Publication Number | Publication Date |
---|---|
EP2019198A2 true EP2019198A2 (en) | 2009-01-28 |
EP2019198A3 EP2019198A3 (en) | 2009-09-30 |
EP2019198B1 EP2019198B1 (en) | 2014-04-16 |
Family
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Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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EP20080104410 Not-in-force EP2019198B1 (en) | 2007-07-24 | 2008-06-13 | Injector |
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EP (1) | EP2019198B1 (en) |
DE (1) | DE102007034318A1 (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2014090444A1 (en) * | 2012-12-14 | 2014-06-19 | Robert Bosch Gmbh | Fuel injection valve |
WO2014166651A1 (en) * | 2013-04-11 | 2014-10-16 | Robert Bosch Gmbh | Fuel injection valve for internal combustion engines |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2003004856A1 (en) | 2001-06-29 | 2003-01-16 | Robert Bosch Gmbh | Fuel injector having injection curve shaping carried out by switchable throttling elements |
DE102004015744A1 (en) | 2004-03-31 | 2005-10-13 | Robert Bosch Gmbh | Common rail injector |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10254749A1 (en) * | 2002-11-23 | 2004-06-17 | Robert Bosch Gmbh | Fuel injection device with a 3/3-way control valve for injection course shaping |
DE10335211A1 (en) * | 2003-08-01 | 2005-02-17 | Robert Bosch Gmbh | Fuel injection device for an internal combustion engine |
DE10353169A1 (en) | 2003-11-14 | 2005-06-16 | Robert Bosch Gmbh | Injector for injecting fuel into combustion chambers of internal combustion engines, in particular piezo-controlled common rail injector |
DE102005010453A1 (en) * | 2005-03-08 | 2006-09-14 | Robert Bosch Gmbh | Fuel injection valve for internal combustion engines |
-
2007
- 2007-07-24 DE DE200710034318 patent/DE102007034318A1/en not_active Withdrawn
-
2008
- 2008-06-13 EP EP20080104410 patent/EP2019198B1/en not_active Not-in-force
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2003004856A1 (en) | 2001-06-29 | 2003-01-16 | Robert Bosch Gmbh | Fuel injector having injection curve shaping carried out by switchable throttling elements |
DE102004015744A1 (en) | 2004-03-31 | 2005-10-13 | Robert Bosch Gmbh | Common rail injector |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2014090444A1 (en) * | 2012-12-14 | 2014-06-19 | Robert Bosch Gmbh | Fuel injection valve |
WO2014166651A1 (en) * | 2013-04-11 | 2014-10-16 | Robert Bosch Gmbh | Fuel injection valve for internal combustion engines |
CN105102804A (en) * | 2013-04-11 | 2015-11-25 | 罗伯特·博世有限公司 | Fuel injection valve for internal combustion engines |
CN105102804B (en) * | 2013-04-11 | 2018-04-27 | 罗伯特·博世有限公司 | Fuelinjection nozzle for internal combustion engine |
Also Published As
Publication number | Publication date |
---|---|
EP2019198A3 (en) | 2009-09-30 |
DE102007034318A1 (en) | 2009-01-29 |
EP2019198B1 (en) | 2014-04-16 |
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