EP2022975B1 - Injector - Google Patents

Injector Download PDF

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Publication number
EP2022975B1
EP2022975B1 EP08104407A EP08104407A EP2022975B1 EP 2022975 B1 EP2022975 B1 EP 2022975B1 EP 08104407 A EP08104407 A EP 08104407A EP 08104407 A EP08104407 A EP 08104407A EP 2022975 B1 EP2022975 B1 EP 2022975B1
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EP
European Patent Office
Prior art keywords
control valve
duct
injector
control
valve
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP08104407A
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German (de)
French (fr)
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EP2022975A1 (en
Inventor
Hans-Christoph Magel
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication date
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Publication of EP2022975A1 publication Critical patent/EP2022975A1/en
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Publication of EP2022975B1 publication Critical patent/EP2022975B1/en
Not-in-force legal-status Critical Current
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • 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
    • F02M63/004—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing
    • 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
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails

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.
  • An injector for injecting fuel into a combustion chamber of an internal combustion engine in which a nozzle needle is exposed to a rear control surface of a control chamber.
  • the control chamber is permanently connected to the high-pressure region of a common rail via an inlet throttle channel.
  • the control chamber is associated with a control valve which connects a combined inlet and outlet throttle channel in a first switching position for closing the nozzle needle with the high pressure region and in a second switching position closes a sealing seat to the high pressure region and at the same time opens a sealing seat to the low pressure region.
  • An injector for injecting fuel with a 4/2-way valve for driving a nozzle needle goes out US 7111614 B1 out.
  • the hydraulic connection of a pressure chamber of the nozzle needle is switched to the high pressure region of the 4/2-way valve.
  • the same control valve switches an inlet throttle channel to a control chamber in the first switching position for opening the nozzle needle to a low-pressure region and in the second switching position for closing the nozzle needle to the high-pressure region towards free.
  • an injector which has an actuatable with an electromagnetic actuator control valve.
  • the control valve has an adjustable between two switching positions valve member, wherein in a first switching position of the control valve, a throttle-free inlet channel is hydraulically connected to a throttle-free vomichkanal, which in turn opens into a control chamber which is bounded by an end face of the valve element. In this way, a fast, throttle-free refilling of the control chamber and thus a fast closing behavior of the valve element of the injector can be achieved.
  • the invention has for its object to provide an injector, are minimized in the pressure oscillations in the control chamber with simultaneous realization of a fast valve element closing movement.
  • the invention is based on the idea that a backfilling channel is provided, which leads from the control valve into the control chamber, wherein in the first switching position of the control valve the backfill channel is hydraulically connected to the inlet channel, then that fuel from the high-pressure region via the inlet channel, the control valve and the rinse vorllkanal can flow into the control chamber, and that the connection between the remind spallkanal and the inlet channel is blocked in the second switching position of the control valve.
  • Theradyogllkanals is thereby activated by the control valve, that is, activated by a valve member of the control valve, such that the connection between the remind sympatuent and the inlet channel is blocked in the second switching position of the control valve and opened in the first switching position for fast refilling of the control chamber.
  • the concept of the invention can be implemented both in an injector with an electromagnetic actuator and in an injector with a piezoelectric actuator or with an actuator having a different principle of action.
  • the map slope, especially at high system pressures is reduced by, in addition to the rinse pump the inlet throttle channel is provided, which connects the control chamber - permanently - with the high pressure area.
  • the vibrations in the servo circuit are further reduced.
  • the opening speed of the valve element in a simple manner by adjusting the ratio of the flow cross-sections of the inlet throttle channel be tuned to the outlet throttle channel.
  • the inlet throttle channel can be branched off, for example, from a supply channel in the injector, which supplies a pressure chamber with high-pressure fuel.
  • an inlet throttle channel directly between the pressure chamber and the control chamber, wherein the inlet throttle channel, for example, in a sleeve-shaped, the control chamber radially outwardly limiting component is introduced.
  • the control valve comprises a valve member that is adjustable in particular in the axial direction, by the adjustment of which the at least two, preferably only two switching positions of the control valve are realized.
  • the valve member is in the first switching position, in which the inlet channel is open and the control chamber is connected via the inlet channel and the vomyogllkanal to the high pressure region, at a first control valve seat and in the second switching position at a second, the first control valve seat preferably axially opposed control valve seat ,
  • the two control valve seats identical or preferably different form, with at least one of the control valve seats is designed as a flat seat, conical seat, ball seat or slide edge.
  • the outlet throttle channel is arranged in the fuel flow direction between, preferably axially between the control chamber and the first control valve seat, so that the fuel at the second control valve seat fitting valve member (second switching position) from the control chamber to the first control valve seat and from there into the low-pressure area and the injector return can flow.
  • the outlet throttle channel is arranged in the direction of fuel flow behind the first control valve seat, so that the fuel can flow from the control chamber to the first control valve seat and past it through the outlet throttle channel into the low-pressure region and thus to the injector return in the case of the second control valve seat.
  • the inlet channel is provided with a throttle.
  • the valve element closing speed can be tuned improved.
  • a restriction may be provided in the inlet to the valve seat of the valve element, for example in the valve element guide, in order to improve the closing behavior of the valve element. If such a throttle is dispensed with, the effective injection pressure can be increased.
  • the provision of a throttle in the inlet channel improves the tolerance sensitivity of the injector.
  • control valve is designed as a valve pressure-balanced in the axial direction.
  • a pressure-balanced control valve One possibility for realizing a pressure-balanced control valve is that a preferably centric axial passage is provided in the valve member, through which the fuel in the second switching position can flow into the low-pressure region, wherein at befindlichem in the first switching position control valve, ie at the first control valve seat abutting valve member bears against both ends of the valve member low pressure and the guide diameter of the valve member are at least approximately identical.
  • 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 high-pressure supply line 2 preferably continues within the injector as a supply channel.
  • 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 (control amount) is discharged from a control chamber 8 and fed back to the high-pressure circuit via the high-pressure pump 4.
  • a one-piece valve element 10 in this embodiment is arranged within a belonging to a high-pressure region of the injector 1 pressure chamber 9, a one-piece valve element 10 in this embodiment is arranged.
  • a multi-part, in particular two-part design of the valve element 10, in particular with control rod and nozzle needle 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 a circumferential collar 15 of the valve element 10 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 a combustion chamber (not shown) of the internal combustion engine is locked. If, on the other hand, it is lifted from 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). It is conceivable to form the axial channels 18 as throttle channels.
  • a control valve 20 associated with the control chamber 20 (servo valve) is moved by means of an actuator 21 from a first switching position to a second switching position, wherein in the second switching position a branched off from the high-pressure supply line 2 inlet channel 22 with throttle 23 (alternatively throttle-free) is locked, so that the hydraulic connection between the high-pressure region of the injector 1 and the control chamber 8 is interrupted.
  • the throttle 23 in the inlet channel 22 is substantially larger than the inlet throttle 27.
  • the flow cross-sections of the inlet throttle 27 and the outlet throttle 25 are matched to one another in such a way that when befindlichem in the second switching position Control valve 20, a net outflow of fuel from the control chamber 8 results and as a result, the pressure in the control chamber 8 decreases and thus the valve element 10 lifts from its valve seat 16 in the plane of the drawing and thus the fuel flow from the pressure chamber 9 into the combustion chamber of the internal combustion engine releases.
  • the control valve 20 is transferred from the second switching position to the first switching position, in which a throttle-free vomichkanal 28, which leads from the control valve 20 into the control chamber 8 is hydraulically connected to the inlet channel 22, so that fuel from the high-pressure region via the inlet channel 22, the control valve 20 and the remind Stahlllkanal 28 can flow into the control chamber 8, whereby the pressure in the control chamber 8 increases rapidly.
  • the pressure increase of the control chamber 8 is assisted by the flowing into the control chamber 8 through the inlet throttle 26 fuel.
  • it is also an embodiment of the injector 1 without inlet throttle channel 26 can be realized.
  • the hydraulic connection of the control chamber 8 to the low-pressure region 6, ie the outlet throttle channel 24 is blocked, so that no fuel can flow into the low-pressure region 6.
  • the inlet throttle channel 26 is arranged in the flow direction between the control chamber 8 and the control valve 20.
  • the backfill channel 28 itself is not switched, but only the inlet channel 22, wherein also an embodiment with switchable backfill channel 28 can be realized.
  • FIG. 2 an alternative embodiment of an injector 1 is shown, which largely corresponds to the embodiment according to Fig. 1 corresponds, so that to avoid repetition essentially only to the differences from the embodiment according to Fig. 1 will be received.
  • the essential difference from the embodiment according to Fig. 1 consists in that the outlet throttle channel 24 with outlet throttle 25 is arranged downstream of the control valve 20, more precisely the control valve seats of the control valve 20.
  • a drain channel 29 is provided between the control chamber 8 and the control valve 20, by the fuel in the second switching position of the control valve 20 to the outlet throttle channel 24 and from there to the low pressure region 6 and 7 can flow to the return. It is conceivable that in the first switching position of the control valve 20 only the outlet throttle channel 24 is switched or additionally or alternatively the drain channel 29th
  • FIG. 3 is a structurally concrete possible embodiment of an injector 1 shown.
  • An essential part of the injector 1 is the control valve 20 with its elongated, piston-shaped valve member 30 which is fixedly formed with an armature plate 31 of the electromagnetic actuator 21 in this embodiment.
  • the valve member 20 is spring-loaded by a compression spring 32 in the direction of its first, formed as a flat seat control valve seat 33.
  • the valve member 30 is adjustable between the first control valve seat 33 and an opposing second, inner conical control valve seat 34. To adjust the valve member 30 of the first control valve seat 33 (first switching position) to rest on the second control valve seat 34 (second switching position) of the electromagnetic actuator 21 must be energized, whereas the energization is interrupted for returning to the first switching position.
  • Fig. 3 the first switching position of the valve member 30 is shown.
  • the valve member 30 abuts against its first control valve seat 33, whereby the connection of the control chamber 8 to the low-pressure region 6 and thus to the return line 7 is interrupted.
  • the over the high pressure supply line 2 and the supply channel 39 into the pressure chamber 9 flowing fuel passes through the throttle in this embodiment formed inlet channel 22 into a valve chamber 35 of the control valve 20 and from there via the remindzellkanal 28 in the control chamber 8, the same time permanently on the Inlet throttle 26 with inlet throttle 27 with the pressure chamber 9 (high pressure area) of the injector 1 is connected.
  • the inlet throttle channel 26 is introduced into a sleeve-shaped component 36 as a radial bore, wherein the sleeve-shaped member 36, the control chamber 8 the frontally delimiting valve member 10 leads and radially outwardly and axially upwardly bounds the control chamber 8.
  • the control chamber 8 is brought quickly to system pressure, so that the valve element 10 moves in the plane of the drawing down on its valve seat 16 and the nozzle hole assembly 17 is blocked in the sequence.
  • valve element 10 To open the nozzle hole arrangement 17, the valve element 10 must be moved upwards in the plane of the drawing, for which purpose the pressure in the control chamber 8 has to be lowered.
  • the electromagnetic actuator 21 is energized, whereby the valve member 30 moves upwards in the plane of the drawing and comes to bear against the second control valve seat 34.
  • the connection of the inlet channel 22 to the valve chamber 35 and thus to the backfill channel 28 and the control chamber 8 is interrupted.
  • valve member 30 since the valve member 30 is no longer applied to its first control valve seat 30, fuel from the control chamber 8 via the outlet throttle channel 24 with outlet throttle 25 in an intermediate chamber 37 radially outside the first control valve seat 33 and from there to the first control valve seat 33 passing by a Axialkanal 38 within the valve member 30 through the low pressure region 6 and thus to the return flow 7. As a result, the pressure in the control chamber 8 decreases and the valve element 10 lifts off from its valve seat 16, so that the injection process begins. In the switching phases of the control valve 20, there are (almost) no short circuit losses due to simultaneously open control valve seats, since both control valve seats 33, 34 are hydraulically connected to one another only via the outlet throttle channel 24 with outlet throttle 25.
  • Fig. 3 how out Fig. 3 can be seen, it is in the control valve 20 is a pressure balanced in the axial direction valve. This is achieved in that a first guide diameter D 1 and an axially spaced guide diameter D 2 of the valve member 30 are the same size and thus act in the two opposite axial directions with low pressure surfaces of the valve member 30 are equal.
  • throttling can be provided, for example in the region of the axial channels 18. Furthermore, a throttle can be provided in the inlet channel 22.
  • control valve seats 33,34 are arranged in a portion 40 of the injector 1, which projects into the pressure chamber 9 and thus is surrounded by fuel under high pressure.
  • control valve seats 33,34 are arranged in different chambers, namely the first control valve seat 33 in the valve chamber 35 and the second control valve seat 34 in the intermediate chamber 37, wherein the valve chamber 35 and the intermediate chamber 37 only via the outlet throttle channel 24th connected to a smaller flow area. Axially between the valve chamber 35 and the intermediate chamber 37, a guide portion for the valve member 30 is provided.

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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

The injector (1) has an outlet throttle channel (24) by which a control chamber (8) is connected with a low-pressure area (6) in the later switching position of the control valve (20). The control chamber is provided with the high pressure area connecting an inlet throttle channel (26).

Description

Stand der TechnikState of the art

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 dem Dokument DE 10 2006 036 446 A1 ist ein Injektor zum Einspritzen von Kraftstoff in einen Brennraum einer Brennkraftmaschine bekannt, bei dem eine Düsennadel mit einer rückwärtigen Steuerfläche einer Steuerkammer ausgesetzt ist. Die Steuerkammer steht über einen Zulaufdrosselkanal dauerhaft mit dem Hochdruckbereich eines Common-Rails in Verbindung. Der Steuerkammer ist ein Steuerventil zugeordnet, das einen kombinierten Zu- und Ablaufdrosselkanal in einer ersten Schaltstellung zum Schließen der Düsennadel mit dem Hochdruckbereich verbindet und in einer zweiten Schaltstellung einen Dichtsitz zum Hochdruckbereich schließt und gleichzeitig einen Dichtsitz zum Niederdruckbereich hin öffnet.From the document DE 10 2006 036 446 A1 An injector for injecting fuel into a combustion chamber of an internal combustion engine is known in which a nozzle needle is exposed to a rear control surface of a control chamber. The control chamber is permanently connected to the high-pressure region of a common rail via an inlet throttle channel. The control chamber is associated with a control valve which connects a combined inlet and outlet throttle channel in a first switching position for closing the nozzle needle with the high pressure region and in a second switching position closes a sealing seat to the high pressure region and at the same time opens a sealing seat to the low pressure region.

Ein Injektor zum Einspritzen von Kraftstoff mit einem 4/2-Wege-Ventil zum Ansteuern einer Düsennadel geht aus US 7111614 B1 hervor. Dabei wird von dem 4/2-Wege-Ventil die hydraulische Verbindung einer Druckkammer der Düsennadel zum Hochdruckbereich geschaltet. Das gleiche Steuerventil schaltet einen Zulaufdrosselkanal zu einem Steuerraum in der ersten Schaltstellung zum Öffnen der Düsennadel zu einem Niederdruckbereich und in der zweiten Schaltstellung zum Schließen der Düsennadel zum Hochdruckbereich hin frei.An injector for injecting fuel with a 4/2-way valve for driving a nozzle needle goes out US 7111614 B1 out. In this case, the hydraulic connection of a pressure chamber of the nozzle needle is switched to the high pressure region of the 4/2-way valve. The same control valve switches an inlet throttle channel to a control chamber in the first switching position for opening the nozzle needle to a low-pressure region and in the second switching position for closing the nozzle needle to the high-pressure region towards free.

Aus der DE 195 33 786 B4 ist weiterhin ein Injektor bekannt, der ein mit einem elektromagnetischen Aktuator betätigbares Steuerventil aufweist. Das Steuerventil weist ein zwischen zwei Schaltstellungen verstellbares Ventilglied auf, wobei in einer ersten Schaltstellung des Steuerventils ein drosselfreier Zulaufkanal hydraulisch mit einem drosselfreien Rückfüllkanal verbunden wird, welcher wiederum in eine Steuerkammer mündet, die von einer Stirnseite des Ventilelementes begrenzt ist. Auf diese Weise kann eine schnelle, drosselfreie Rückbefüllung der Steuerkammer und damit ein schnelles Schließverhalten des Ventilelementes des Injektors erzielt werden. In einer zweiten Schaltstellung des Steuerventils ist der drosselfreie Zulaufkanal gesperrt und die Steuerkammer ist über den Rückfüllkanal hydraulisch mit einem Niederdruckbereich des Injektors verbunden, so dass ein schneller Druckabfall in der Steuerkammer und damit ein schnelles Öffnungsverhalten des Ventilelementes realisiert werden kann. Nachteilig bei dem bekannten Injektor ist es jedoch, dass es zu Druckschwingungen in der Steuerkammer und damit zu Schwingungen bei der Ventilelementbewegung, insbesondere 30 bei der Ventilelementöffnungsbewegung kommen kann.From the DE 195 33 786 B4 Furthermore, an injector is known, which has an actuatable with an electromagnetic actuator control valve. The control valve has an adjustable between two switching positions valve member, wherein in a first switching position of the control valve, a throttle-free inlet channel is hydraulically connected to a throttle-free Rückfüllkanal, which in turn opens into a control chamber which is bounded by an end face of the valve element. In this way, a fast, throttle-free refilling of the control chamber and thus a fast closing behavior of the valve element of the injector can be achieved. In a second switching position of the control valve, the throttle-free inlet channel is blocked and the control chamber is hydraulically connected via the Rückfüllkanal with a low pressure region of the injector, so that a rapid pressure drop in the control chamber and thus a fast opening behavior of the valve element can be realized. A disadvantage of the known injector, however, is that it can lead to pressure oscillations in the control chamber and thus to vibrations in the valve element movement, in particular 30 in the valve element opening movement.

Offenbarung der ErfindungDisclosure of the invention Technische AufgabeTechnical task

Der Erfindung liegt die Aufgabe zugrunde, einen Injektor vorzuschlagen, bei dem Druckschwingungen in der Steuerkammer bei gleichzeitiger Realisierung einer schnellen Ventilelementschließbewegung minimiert werden.The invention has for its object to provide an injector, are minimized in the pressure oscillations in the control chamber with simultaneous realization of a fast valve element closing movement.

Technische LösungTechnical solution

Diese Aufgabe wird mit den Merkmalen des Anspruchs 1 gelöst. Vorteilhafte Weiterbildungen der Erfindungen sind in den Unteransprüchen angegeben.This object is achieved with the features of claim 1. Advantageous developments of the inventions are specified in the subclaims.

Der Erfindung liegt der Gedanke zugrunde, dass ein Rückfüllkanal vorgesehen ist, der von dem Steuerventil in die Steuerkammer führt, wobei in der ersten Schaltstellung des Steuerventils der Rückfüllkanal hydraulisch mit dem Zulaufkanal verbunden ist, so dass Kraftstoff aus dem Hochdruckbereich über den Zulaufkanal, das Steuerventil und den Rückfüllkanal in die Steuerkammer strömen kann, und dass die Verbindung zwischen dem Rückfüllkanal und dem Zulaufkanal in der zweiten Schaltstellung des Steuerventils gesperrt ist. Der Rückfüllkanals wird dabei vom Steuerventil, d.h. von einem Ventilglied des Steuerventils aktiv geschaltet, derart, dass die Verbindung zwischen dem Rückfüllkanal und dem Zulaufkanal in der zweiten Schaltstellung des Steuerventils gesperrt und in der ersten Schaltstellung zum schnellen Rückbefüllen der Steuerkammer geöffnet ist.The invention is based on the idea that a backfilling channel is provided, which leads from the control valve into the control chamber, wherein in the first switching position of the control valve the backfill channel is hydraulically connected to the inlet channel, then that fuel from the high-pressure region via the inlet channel, the control valve and the Rückfüllkanal can flow into the control chamber, and that the connection between the Rückfüllkanal and the inlet channel is blocked in the second switching position of the control valve. The Rückfüllkanals is thereby activated by the control valve, that is, activated by a valve member of the control valve, such that the connection between the Rückfüllkanal and the inlet channel is blocked in the second switching position of the control valve and opened in the first switching position for fast refilling of the control chamber.

Dadurch wird ein schnelles Rückbefüllen der Steuerkammer in der ersten Schaltstellung des Steuerventils und damit ein schnelles Ventilelementschließen ermöglicht, über den der Kraftstoff aus der Steuerkammer in der zweiten Schaltstellung des Steuerventils gedrosselt in den Niederdruckbereich des Injektors und damit zum Injektorrücklauf strömen kann. Durch das im Vergleich zum Stand der Technik langsamere Abströmen des Kraftstoffes aus der Steuerkammer werden Schwingungen beim Öffnungsvorgang des Ventilselementes in der Steuerkammer und damit bei der Öffnungsbewegung des Ventilelementes minimiert, wodurch die Kennfeldsteilheit auch bei hohen Systemdrücken im Hochdruckbereich des Injektors von über 2000 bar verringert wird. Ebenso wird die Toleranzempfindlichkeit des Injektors minimiert. Zudem kann der zeitliche Abstand zweier aufeinander folgender Einspritzungen - trotz des langsameren Abströmens durch den Ablaufdrosselkanal - aufgrund der Minimierung der Schwingungen in der Steuerkammer verringert werden.Characterized a quick refilling of the control chamber in the first switching position of the control valve and thus a fast valve element closing is enabled, via which the fuel from the control chamber throttled in the second switching position of the control valve in the low pressure region of the injector and thus can flow to the injector return. By compared to the prior art slower outflow of fuel from the control chamber vibrations during the opening process of the valve element in the control chamber and thus during the opening movement of the valve element are minimized, whereby the map slope is reduced even at high system pressures in the high pressure region of the injector of over 2000 bar , Likewise, the tolerance sensitivity of the injector is minimized. In addition, the time interval between two successive injections can be reduced due to the minimization of the vibrations in the control chamber, despite the slower outflow through the outlet throttle channel.

Das Konzept der Erfindung kann sowohl bei einem Injektor mit elektromagnetischem Aktuator als auch bei einem Injektor mit piezoelektrischem Aktuator oder auch mit einem Aktuator mit davon unterschiedlichem Wirkprinzip realisiert werden.The concept of the invention can be implemented both in an injector with an electromagnetic actuator and in an injector with a piezoelectric actuator or with an actuator having a different principle of action.

Die Kennfeldsteilheit, insbesondere bei hohen Systemdrücken wird reduziert, indem zusätzlich zu dem Rückfüllkanal der Zulaufdrosselkanal vorgesehen ist, der die Steuerkammer - dauerhaft - mit dem Hochdruckbereich verbindet. Hierdurch werden die Schwingungen im Servokreislauf noch weiter verringert. Durch das Vorsehen einer Zulaufdrossel kann die Öffnungsgeschwindigkeit des Ventilelementes auf einfache Weise durch die Abstimmung des Verhältnisses der Durchflussquerschnitte des Zulaufdrosselkanals zu dem Ablaufdrosselkanal abgestimmt werden. Der Zulaufdrosselkanal kann beispielsweise von einem Versorgungskanal im Injektor, der einen Druckraum mit unter Hochdruck stehendem Kraftstoff versorgt, abgezweigt werden. Zusätzlich oder alternativ ist es denkbar einen Zulaufdrosselkanal unmittelbar zwischen dem Druckraum und der Steuerkammer anzuordnen, wobei der Zulaufdrosselkanal beispielsweise in einem hülsenförmigen, die Steuerkammer radial außen begrenzenden Bauteil eingebracht ist.The map slope, especially at high system pressures is reduced by, in addition to the Rückfüllkanal the inlet throttle channel is provided, which connects the control chamber - permanently - with the high pressure area. As a result, the vibrations in the servo circuit are further reduced. By providing an inlet throttle, the opening speed of the valve element in a simple manner by adjusting the ratio of the flow cross-sections of the inlet throttle channel be tuned to the outlet throttle channel. The inlet throttle channel can be branched off, for example, from a supply channel in the injector, which supplies a pressure chamber with high-pressure fuel. Additionally or alternatively, it is conceivable to arrange an inlet throttle channel directly between the pressure chamber and the control chamber, wherein the inlet throttle channel, for example, in a sleeve-shaped, the control chamber radially outwardly limiting component is introduced.

Gemäß einer bevorzugten Ausführungsform umfasst das Steuerventil ein insbesondere in axialer Richtung verstellbares Ventilglied, durch dessen Verstellen die mindestens zwei, vorzugsweise ausschließlich zwei Schaltstellungen des Steuerventils realisiert werden. Dabei liegt das Ventilglied in der ersten Schaltstellung, in der der Zulaufkanal geöffnet und die Steuerkammer über den Zulaufkanal und den Rückfüllkanal mit dem Hochdruckbereich verbunden ist, an einem ersten Steuerventilsitz an und in der zweiten Schaltstellung an einem zweiten, dem ersten Steuerventilsitz vorzugsweise axial gegenüberliegenden Steuerventilsitz. Es liegt im Rahmen der Erfindung, die beiden Steuerventilsitze identisch oder vorzugsweise unterschiedlich auszubilden, wobei zumindest einer der Steuerventilsitze als Flachsitz, Kegelsitz, Kugelsitz oder Schieberkante ausgebildet ist.According to a preferred embodiment, the control valve comprises a valve member that is adjustable in particular in the axial direction, by the adjustment of which the at least two, preferably only two switching positions of the control valve are realized. In this case, the valve member is in the first switching position, in which the inlet channel is open and the control chamber is connected via the inlet channel and the Rückfüllkanal to the high pressure region, at a first control valve seat and in the second switching position at a second, the first control valve seat preferably axially opposed control valve seat , It is within the scope of the invention, the two control valve seats identical or preferably different form, with at least one of the control valve seats is designed as a flat seat, conical seat, ball seat or slide edge.

In Weiterbildung der Erfindung ist mit Vorteil vorgesehen, dass der Ablaufdrosselkanal in Kraftstoffströmungsrichtung zwischen, vorzugsweise axial zwischen der Steuerkammer und dem ersten Steuerventilsitz angeordnet ist, so dass der Kraftstoff bei an dem zweiten Steuerventilsitz anliegendem Ventilglied (zweite Schaltstellung) aus der Steuerkammer zu dem ersten Steuerventilsitz und von dort aus in den Niederdruckbereich und zum Injektorrücklauf strömen kann.In a further development of the invention is advantageously provided that the outlet throttle channel is arranged in the fuel flow direction between, preferably axially between the control chamber and the first control valve seat, so that the fuel at the second control valve seat fitting valve member (second switching position) from the control chamber to the first control valve seat and from there into the low-pressure area and the injector return can flow.

Alternativ ist der Ablaufdrosselkanal in Kraftstoffströmungsrichtung hinter dem ersten Steuerventilsitz angeordnet, so dass der Kraftstoff bei an dem zweiten Steuerventilsitz anliegenden Ventilglied aus der Steuerkammer zum ersten Steuerventilsitz und an diesem vorbei durch den Ablaufdrosselkanal in den Niederdruckbereich und damit zum Injektorrücklauf strömen kann.Alternatively, the outlet throttle channel is arranged in the direction of fuel flow behind the first control valve seat, so that the fuel can flow from the control chamber to the first control valve seat and past it through the outlet throttle channel into the low-pressure region and thus to the injector return in the case of the second control valve seat.

Von besonderem Vorteil ist eine Ausführungsform, bei der der Zulaufkanal mit einer Drossel versehen ist. Durch das Ausbilden des Zulaufkanals als Drosselkanal kann die Ventilelementschließgeschwindigkeit verbessert abgestimmt werden. Zusätzlich oder alternativ kann im Zulauf zum Ventilsitz des Ventilelementes, beispielsweise in der Ventilelementführung eine Drosselung vorgesehen werden, um das Schließverhalten des Ventilelementes zu verbessern. Wird auf eine solche Drossel verzichtet, kann der effektive Einspritzdruck erhöht werden. Ebenso wird durch das Vorsehen einer Drossel im Zulaufkanal die Toleranzempfindlichkeit des Injektors verbessert.Of particular advantage is an embodiment in which the inlet channel is provided with a throttle. By forming the inlet channel as a throttle channel, the valve element closing speed can be tuned improved. Additionally or alternatively, a restriction may be provided in the inlet to the valve seat of the valve element, for example in the valve element guide, in order to improve the closing behavior of the valve element. If such a throttle is dispensed with, the effective injection pressure can be increased. Likewise, the provision of a throttle in the inlet channel improves the tolerance sensitivity of the injector.

Um Aktuatoren mit möglichst geringer Leistungsaufnahme und in der Folge einem geringen Bauvolumen einsetzen zu können, ist eine Ausführungsform von Vorteil, bei der das Steuerventil als in axialer Richtung druckausgeglichenes Ventil ausgebildet ist.In order to use actuators with the lowest possible power consumption and consequently a small volume, an embodiment is advantageous in which the control valve is designed as a valve pressure-balanced in the axial direction.

Eine Möglichkeit zur Realisierung eines druckausgeglichenen Steuerventils besteht darin, dass in dem Ventilglied ein vorzugsweise zentrischer Axialkanal vorgesehen ist, durch den der Kraftstoff in der zweiten Schaltstellung in den Niederdruckbereich strömen kann, wobei bei in der ersten Schaltstellung befindlichem Steuerventil, also bei an dem ersten Steuerventilsitz anliegendem Ventilglied an beiden Stirnseiten des Ventilgliedes Niederdruck anliegt und die Führungsdurchmesser des Ventilgliedes zumindest näherungsweise identisch sind.One possibility for realizing a pressure-balanced control valve is that a preferably centric axial passage is provided in the valve member, through which the fuel in the second switching position can flow into the low-pressure region, wherein at befindlichem in the first switching position control valve, ie at the first control valve seat abutting valve member bears against both ends of the valve member low pressure and the guide diameter of the valve member are at least approximately identical.

Kurze Beschreibung der ZeichnungenBrief description of the drawings

Weitere Vorteile und Merkmale der Erfindung ergeben sich aus der nachfolgenden Beschreibung bevorzugter Ausführungsbeispiele sowie anhand der Zeichnungen; diese zeigen in:

Fig. 1:
eine schematische Darstellung eines Injektors mit einem als 4/2-Wegeventil ausgebildeten Steuerventil, bei dem ein Ablaufdrosselkanal zwischen der Steuerkammer und einem ersten Steuerventilsitz angeordnet ist,
Fig. 2:
eine schematische Darstellung eines als 4/2-Wegeventil ausgebildeten Injektors, bei dem der Ablaufdrosselkanal dem ersten Steuerventilsitz nachgeordnet ist und
Fig. 3:
einen Injektor mit einem Steuerventil, wobei eine konstruktiv vorteilhafte Ausführungsform des Steuerventils gezeigt ist.
Further advantages and features of the invention will become apparent from the following description of preferred embodiments and from the drawings; these show in:
Fig. 1:
a schematic representation of an injector with a designed as a 4/2-way valve control valve, in which a discharge throttle channel is arranged between the control chamber and a first control valve seat,
Fig. 2:
a schematic representation of a trained as a 4/2-way valve injector, wherein the outlet throttle channel is arranged downstream of the first control valve seat and
3:
an injector with a control valve, wherein a structurally advantageous embodiment of the control valve is shown.

Ausführungsformen der ErfindungEmbodiments of the invention

In den Figuren sind gleiche Bauteile und Bauteile mit der gleichen Funktion mit gleichen Bezugszeichen gekennzeichnet.In the figures, the same components and components with the same function with the same reference numerals.

In Fig. 1 ist stark schematisiert der Aufbau eines als Common-Rail-Injektor ausgebildeten Injektors 1 gezeigt. Der Injektor 1 wird über eine Hochdruckversorgungsleitung 2 aus einem Kraftstoff-Hochdruckspeicher 3 (Rail) mit unter hohem Druck (vorzugsweise höher als 2000 bar) stehendem Kraftstoff, insbesondere Dieselöl oder Benzin, versorgt. Die Hochdruckversorgungsleitung 2 setzt sich bevorzugt innerhalb des Injektors als Versorgungskanal fort. Der Kraftstoff-Hochdruckspeicher 3 wird von einer als Radialkolbenpumpe ausgebildeten Hochdruckpumpe 4 mit Kraftstoff aus einem auf Niederdruck liegendem Vorratsbehälter 5 versorgt. Ein Niederdruckbereich 6 des Injektors 1 ist über einen Rücklauf 7 mit dem Vorratsbehälter 5 hydraulisch verbunden. Der Druck im Niederdruckbereich 6 des Injektors 1 beträgt je nach Betriebszustand zwischen etwa 0 und 100 bar, vorzugsweise zwischen etwa 0 und 10 bar. Über den Rücklauf 7 wird eine später noch zu erläuternde Kraftstoffmenge (Steuermenge) aus einer Steuerkammer 8 abgeführt und über die Hochdruckpumpe 4 dem Hochdruckkreislauf wieder zugeführt.In 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 high-pressure supply line 2 preferably continues within the injector as a supply channel. 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. Depending on the operating state, 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. About the return 7, a fuel quantity to be explained later (control amount) is discharged from a control chamber 8 and fed back to the high-pressure circuit via the high-pressure pump 4.

Innerhalb eines zu einem Hochdruckbereich des Injektors 1 gehörenden Druckraum 9 ist ein in diesem Ausführungsbeispiel einteiliges Ventilelement 10 angeordnet. Alternativ ist eine mehrteilige, insbesondere zweiteilige Ausbildung des Ventilelementes 10, insbesondere 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. Andernends 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 valve element 10 in this embodiment is arranged. Alternatively, a multi-part, in particular two-part design of the valve element 10, in particular with control rod and nozzle needle conceivable. 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. At the other end, the closing spring 13 is supported a circumferential collar 15 of the valve element 10 and acts on this in the direction of its valve seat 16th

Wenn das Ventilelement 10 am Ventilsitz 16 anliegt, d.h. sich in einer Schließstellung befindet, ist der Kraftstoffaustritt aus einer Düsenlochanordnung 17 in einen 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. Es ist denkbar, die Axialkanäle 18 als Drosselkanäle auszubilden.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 a combustion chamber (not shown) of the internal combustion engine is locked. If, on the other hand, it is lifted from 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). It is conceivable to form the axial channels 18 as throttle channels.

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), mittels eines Aktuators 21 von einer ersten Schaltstellung in eine zweite Schaltstellung bewegt, wobei in der zweiten Schaltstellung ein von der Hochdruckversorgungsleitung 2 abgezweigter Zulaufkanal 22 mit Drossel 23 (alternativ drosselfrei) gesperrt ist, so dass die hydraulische Verbindung zwischen dem Hochdruckbereich des Injektors 1 und der Steuerkammer 8 unterbrochen ist. Bevorzugt ist die Drossel 23 im Zulaufkanal 22 wesentlich größer als die Zulaufdrossel 27. Hierdurch ist das Ventilelementschließverhalten unabhängig von dem Ventilelementöffnungsverhalten abstimmbar.So that the valve element 10 lifts off from its valve seat 16 and moves upward in the plane of the drawing, the fuel pressure within the control chamber 8 must be lowered. For this purpose, a control valve 20 associated with the control chamber 20 (servo valve) is moved by means of an actuator 21 from a first switching position to a second switching position, wherein in the second switching position a branched off from the high-pressure supply line 2 inlet channel 22 with throttle 23 (alternatively throttle-free) is locked, so that the hydraulic connection between the high-pressure region of the injector 1 and the control chamber 8 is interrupted. Preferably, the throttle 23 in the inlet channel 22 is substantially larger than the inlet throttle 27. As a result, the valve element closing behavior is independent of the valve element opening behavior tunable.

Beim Überführen des Steuerventils 20 von der ersten in die zweiten Schaltstellung müssen bevorzugt keine (großen) Räume auf Systemdruck gebracht werden, so dass keine ungewollten Schwingungen in der Steuerkammer 8 entstehen. In der zweiten Schaltstellung des als 4/2-Wegeventil ausgebildeten Steuerventils 20 strömt Kraftstoff aus der Steuerkammer 8 über einen Ablaufdrosselkanal 24 mit Ablaufdrossel 25 zum Niederdruckbereich 6 des Injektors 1 und von dort aus über den Rücklauf 7 zum Vorratsbehälter 5. Gleichzeitig strömt Kraftstoff (unabhängig von der Schaltstellung des Steuerventils 20) über einen Zulaufdrosselkanal 26 mit Zulaufdrossel 27 von dem Hochdruckbereich des Injektors 1 in die Steuerkammer 8, wobei der Zulaufdrosselkanal 27 in dem gezeigten Ausführungsbeispiel von dem Zulaufkanal 22 abgezweigt ist. Dabei sind die Durchflussquerschnitte der Zulaufdrossel 27 und der Ablaufdrossel 25 derart aufeinander abgestimmt, dass bei in der zweiten Schaltstellung befindlichem Steuerventil 20 ein Nettoabfluss von Kraftstoff aus der Steuerkammer 8 resultiert und in der Folge der Druck in der Steuerkammer 8 absinkt und somit das Ventilelement 10 von seinem Ventilsitz 16 in der Zeichnungsebene nach oben abhebt und damit den Kraftstofffluss aus dem Druckraum 9 in den Brennraum der Brennkraftmaschine freigibt.When transferring the control valve 20 from the first to the second switching position preferably no (large) spaces must be brought to system pressure, so that no unwanted vibrations in the control chamber 8 arise. In the second switching position of the control valve 20 designed as a 4/2-way valve, fuel flows out of the control chamber 8 via an outlet throttle channel 24 with outlet throttle 25 to the low-pressure region 6 of the injector 1 and from there via the return line 7 to the reservoir 5. Simultaneously, fuel flows (independently from the switching position of the control valve 20) via an inlet throttle channel 26 with inlet throttle 27 from the high-pressure region of the injector 1 into the control chamber 8, wherein the inlet throttle channel 27 is branched off from the inlet channel 22 in the embodiment shown. The flow cross-sections of the inlet throttle 27 and the outlet throttle 25 are matched to one another in such a way that when befindlichem in the second switching position Control valve 20, a net outflow of fuel from the control chamber 8 results and as a result, the pressure in the control chamber 8 decreases and thus the valve element 10 lifts from its valve seat 16 in the plane of the drawing and thus the fuel flow from the pressure chamber 9 into the combustion chamber of the internal combustion engine releases.

Soll nun der Einspritzvorgang beendet, d.h. das Ventilelement auf seinen Ventilsitz 16 bewegt werden, so wird das Steuerventil 20 von der zweiten Schaltstellung in die erste Schaltstellung überführt, in der ein drosselfreier Rückfüllkanal 28, der von dem Steuerventil 20 in die Steuerkammer 8 führt hydraulisch mit dem Zulaufkanal 22 verbunden wird, so dass Kraftstoff aus dem Hochdruckbereich über den Zulaufkanal 22, das Steuerventil 20 und den Rückfüllkanal 28 in die Steuerkammer 8 strömen kann, wodurch der Druck in der Steuerkammer 8 rapide ansteigt. Der Druckanstieg der Steuerkammer 8 wird unterstützt durch den in die Steuerkammer 8 durch den Zulaufdrosselkanal 26 strömenden Kraftstoff. Es ist jedoch auch eine Ausführungsform des Injektors 1 ohne Zulaufdrosselkanal 26 realisierbar. In der ersten Schaltstellung ist die hydraulische Verbindung der Steuerkammer 8 zum Niederdruckbereich 6, also der Ablaufdrosselkanal 24 gesperrt, so dass kein Kraftstoff in den Niederdruckbereich 6 abströmen kann.Now if the injection process is terminated, i. the valve element to be moved to its valve seat 16, the control valve 20 is transferred from the second switching position to the first switching position, in which a throttle-free Rückfüllkanal 28, which leads from the control valve 20 into the control chamber 8 is hydraulically connected to the inlet channel 22, so that fuel from the high-pressure region via the inlet channel 22, the control valve 20 and the Rückfüllkanal 28 can flow into the control chamber 8, whereby the pressure in the control chamber 8 increases rapidly. The pressure increase of the control chamber 8 is assisted by the flowing into the control chamber 8 through the inlet throttle 26 fuel. However, it is also an embodiment of the injector 1 without inlet throttle channel 26 can be realized. In the first switching position, the hydraulic connection of the control chamber 8 to the low-pressure region 6, ie the outlet throttle channel 24 is blocked, so that no fuel can flow into the low-pressure region 6.

Wie sich aus Fig. 1 ergibt, ist der Zulaufdrosselkanal 26 in Strömungsrichtung zwischen der Steuerkammer 8 und dem Steuerventil 20 angeordnet. Der Rückfüllkanal 28 selbst wird nicht geschaltet, sondern lediglich der Zulaufkanal 22, wobei auch eine Ausführungsform mit schaltbarem Rückfüllkanal 28 realisierbar ist.As it turned out Fig. 1 results, the inlet throttle channel 26 is arranged in the flow direction between the control chamber 8 and the control valve 20. The backfill channel 28 itself is not switched, but only the inlet channel 22, wherein also an embodiment with switchable backfill channel 28 can be realized.

In Fig. 2 ist ein alternatives Ausführungsbeispiel eines Injektors 1 gezeigt, das weitestgehend dem Ausführungsbeispiel gemäß Fig. 1 entspricht, so dass zur Vermeidung von Wiederholungen im Wesentlichen nur auf die Unterschiede zu dem Ausführungsbeispiel gemäß Fig. 1 eingegangen wird.In Fig. 2 an alternative embodiment of an injector 1 is shown, which largely corresponds to the embodiment according to Fig. 1 corresponds, so that to avoid repetition essentially only to the differences from the embodiment according to Fig. 1 will be received.

Der wesentliche Unterschied zu dem Ausführungsbeispiel gemäß Fig. 1 besteht darin, dass der Ablaufdrosselkanal 24 mit Ablaufdrossel 25 dem Steuerventil 20, genauer gesagt den Steuerventilsitzen des Steuerventils 20 nachgeordnet ist. Zur Anbindung des Ablaufdrosselkanals 24 ist ein Ablaufkanal 29 zwischen der Steuerkammer 8 und dem Steuerventil 20 vorgesehen, durch den Kraftstoff in der zweiten Schaltstellung des Steuerventils 20 zum Ablaufdrosselkanal 24 und von dort aus zum Niederdruckbereich 6 und zum Rücklauf 7 strömen kann. Dabei ist es denkbar, dass in der ersten Schaltstellung des Steuerventils 20 nur der Ablaufdrosselkanal 24 geschaltet wird oder zusätzlich oder alternativ der Ablaufkanal 29.The essential difference from the embodiment according to Fig. 1 consists in that the outlet throttle channel 24 with outlet throttle 25 is arranged downstream of the control valve 20, more precisely the control valve seats of the control valve 20. For connecting the outlet throttle channel 24, a drain channel 29 is provided between the control chamber 8 and the control valve 20, by the fuel in the second switching position of the control valve 20 to the outlet throttle channel 24 and from there to the low pressure region 6 and 7 can flow to the return. It is conceivable that in the first switching position of the control valve 20 only the outlet throttle channel 24 is switched or additionally or alternatively the drain channel 29th

In Fig. 3 ist eine konstruktiv konkretisierte mögliche Ausführungsform eines Injektors 1 gezeigt. Wesentlicher Bestandteil des Injektors 1 ist das Steuerventil 20 mit seinem länglichen, kolbenförmigen Ventilglied 30, das fest mit einer Ankerplatte 31 des in diesem Ausführungsbeispiel elektromagnetischen Aktuators 21 ausgebildet ist. Das Ventilglied 20 wird von einer Druckfeder 32 in Richtung auf seinen ersten, als Flachsitz ausgebildeten Steuerventilsitz 33 federkraftbeaufschlagt. Das Ventilglied 30 ist zwischen dem ersten Steuerventilsitz 33 und einem gegenüberliegenden zweiten, innenkonischen Steuerventilsitz 34 verstellbar. Zum Verstellen des Ventilgliedes 30 von dem ersten Steuerventilsitz 33 (erste Schaltstellung) zur Anlage an dem zweiten Steuerventilsitz 34 (zweite Schaltstellung) muss der elektromagnetische Aktuator 21 bestromt werden, wohingegen die Bestromung zum Rückstellen in die erste Schaltstellung unterbrochen wird.In Fig. 3 is a structurally concrete possible embodiment of an injector 1 shown. An essential part of the injector 1 is the control valve 20 with its elongated, piston-shaped valve member 30 which is fixedly formed with an armature plate 31 of the electromagnetic actuator 21 in this embodiment. The valve member 20 is spring-loaded by a compression spring 32 in the direction of its first, formed as a flat seat control valve seat 33. The valve member 30 is adjustable between the first control valve seat 33 and an opposing second, inner conical control valve seat 34. To adjust the valve member 30 of the first control valve seat 33 (first switching position) to rest on the second control valve seat 34 (second switching position) of the electromagnetic actuator 21 must be energized, whereas the energization is interrupted for returning to the first switching position.

In Fig. 3 ist die erste Schaltstellung des Ventilgliedes 30 gezeigt. Das Ventilglied 30 liegt an seinem ersten Steuerventilsitz 33 an, wodurch die Verbindung der Steuerkammer 8 zum Niederdruckbereich 6 und damit zum Rücklauf 7 unterbrochen ist. Der über die Hochdruckversorgungsleitung 2 und dem Versorgungskanal 39 in den Druckraum 9 strömende Kraftstoff gelangt über den in diesem Ausführungsbeispiel drosselfrei ausgebildeten Zulaufkanal 22 in eine Ventilkammer 35 des Steuerventils 20 und von dort aus über den Rückfüllkanal 28 in die Steuerkammer 8, die gleichzeitig dauerhaft über den Zulaufdrosselkanal 26 mit Zulaufdrossel 27 mit dem Druckraum 9 (Hochdruckbereich) des Injektors 1 verbunden ist. Der Zulaufdrosselkanal 26 ist dabei in ein hülsenförmiges Bauteil 36 als Radialbohrung eingebracht, wobei das hülsenförmige Bauteil 36, das die Steuerkammer 8 stirnseitig begrenzende Ventilelement 10 führt und radial außen sowie axial nach oben die Steuerkammer 8 begrenzt. In der ersten Schaltstellung wird die Steuerkammer 8 schnell auf Systemdruck gebracht, so dass sich das Ventilelement 10 in der Zeichnungsebene nach unten auf seinen Ventilsitz 16 bewegt und die Düsenlochanordnung 17 in der Folge versperrt ist.In Fig. 3 the first switching position of the valve member 30 is shown. The valve member 30 abuts against its first control valve seat 33, whereby the connection of the control chamber 8 to the low-pressure region 6 and thus to the return line 7 is interrupted. The over the high pressure supply line 2 and the supply channel 39 into the pressure chamber 9 flowing fuel passes through the throttle in this embodiment formed inlet channel 22 into a valve chamber 35 of the control valve 20 and from there via the Rückfüllkanal 28 in the control chamber 8, the same time permanently on the Inlet throttle 26 with inlet throttle 27 with the pressure chamber 9 (high pressure area) of the injector 1 is connected. The inlet throttle channel 26 is introduced into a sleeve-shaped component 36 as a radial bore, wherein the sleeve-shaped member 36, the control chamber 8 the frontally delimiting valve member 10 leads and radially outwardly and axially upwardly bounds the control chamber 8. In the first switching position, the control chamber 8 is brought quickly to system pressure, so that the valve element 10 moves in the plane of the drawing down on its valve seat 16 and the nozzle hole assembly 17 is blocked in the sequence.

Zum Öffnen der Düsenlochanordnung 17 muss das Ventilelement 10 in der Zeichnungsebene nach oben bewegt werden, wozu der Druck in der Steuerkammer 8 abgesenkt werden muss. Hierzu wird der elektromagnetische Aktuator 21 bestromt, wodurch sich das Ventilglied 30 in der Zeichnungsebene nach oben bewegt und zur Anlage an dem zweiten Steuerventilsitz 34 kommt. Hierdurch wird die Verbindung des Zulaufkanals 22 zur Ventilkammer 35 und damit zum Rückfüllkanal 28 und zur Steuerkammer 8 unterbrochen. Gleichzeitig, da das Ventilglied 30 nicht mehr an seinen ersten Steuerventilsitz 30 anliegt, kann Kraftstoff aus der Steuerkammer 8 über den Ablaufdrosselkanal 24 mit Ablaufdrossel 25 in eine Zwischenkammer 37 radial außerhalb des ersten Steuerventilsitzes 33 und von dort aus an dem ersten Steuerventilsitz 33 vorbei durch einen Axialkanal 38 innerhalb des Ventilgliedes 30 hindurch zum Niederdruckbereich 6 und damit zum Rücklauf 7 strömen. Hierdurch sinkt der Druck in der Steuerkammer 8 und das Ventilelement 10 hebt von seinem Ventilsitz 16 ab, so dass der Einspritzvorgang beginnt. In den Schaltphasen des Steuerventils 20 gibt es (nahezu) keine Kurzschlussverluste durch gleichzeitig geöffnete Steuerventilsitze, da beide Steuerventilsitze 33, 34 lediglich über den Ablaufdrosselkanal 24 mit Ablaufdrossel 25 hydraulisch miteinander verbunden sind.To open the nozzle hole arrangement 17, the valve element 10 must be moved upwards in the plane of the drawing, for which purpose the pressure in the control chamber 8 has to be lowered. For this purpose, the electromagnetic actuator 21 is energized, whereby the valve member 30 moves upwards in the plane of the drawing and comes to bear against the second control valve seat 34. As a result, the connection of the inlet channel 22 to the valve chamber 35 and thus to the backfill channel 28 and the control chamber 8 is interrupted. At the same time, since the valve member 30 is no longer applied to its first control valve seat 30, fuel from the control chamber 8 via the outlet throttle channel 24 with outlet throttle 25 in an intermediate chamber 37 radially outside the first control valve seat 33 and from there to the first control valve seat 33 passing by a Axialkanal 38 within the valve member 30 through the low pressure region 6 and thus to the return flow 7. As a result, the pressure in the control chamber 8 decreases and the valve element 10 lifts off from its valve seat 16, so that the injection process begins. In the switching phases of the control valve 20, there are (almost) no short circuit losses due to simultaneously open control valve seats, since both control valve seats 33, 34 are hydraulically connected to one another only via the outlet throttle channel 24 with outlet throttle 25.

Wie aus Fig. 3 zu erkennen ist, handelt es sich bei dem Steuerventil 20 um ein in axialer Richtung druckausgeglichenes Ventil. Dies wird dadurch erreicht, dass ein erster Führungsdurchmesser D1 und ein axial davon beabstandeter Führungsdurchmesser D2 des Ventilgliedes 30 gleich groß sind und somit die in die beiden gegenüberliegenden Axialrichtungen mit Niederdruck beaufschlagten Flächen des Ventilgliedes 30 gleich groß sind.How out Fig. 3 can be seen, it is in the control valve 20 is a pressure balanced in the axial direction valve. This is achieved in that a first guide diameter D 1 and an axially spaced guide diameter D 2 of the valve member 30 are the same size and thus act in the two opposite axial directions with low pressure surfaces of the valve member 30 are equal.

Zum Optimieren der Ventilelementbewegung kann, beispielsweise im Bereich der Axialkanäle 18 eine Drosselung vorgesehen werden. Weiterhin kann im Zulaufkanal 22 eine Drossel vorgesehen werden.In order to optimize the valve element movement, throttling can be provided, for example in the region of the axial channels 18. Furthermore, a throttle can be provided in the inlet channel 22.

Von besonderem Vorteil zur Reduzierung von Bauteilspannungen ist es, dass die Steuerventilsitze 33,34 (Schaltkanten) in einem Abschnitt 40 des Injektors 1 angeordnet sind, der in den Druckraum 9 hinein ragt und somit von unter Hochdruck stehendem Kraftstoff umgeben ist.Of particular advantage for the reduction of component voltages is that the control valve seats 33,34 (switching edges) are arranged in a portion 40 of the injector 1, which projects into the pressure chamber 9 and thus is surrounded by fuel under high pressure.

Ferner ist es von Vorteil, dass die Steuerventilsitze 33,34 in unterschiedlichen Kammern, nämlich der erste Steuerventilsitz 33 in der Ventilkammer 35 und der zweite Steuerventilsitz 34 in der Zwischenkammer 37 angeordnet sind, wobei die Ventilkammer 35 und die Zwischenkammer 37 nur über den Ablaufdrosselkanal 24 mit einem geringeren Durchflussquerschnitt verbunden ist. Axial zwischen der Ventilkammer 35 und der Zwischenkammer 37 ist ein Führungsabschnitt für das Ventilglied 30 vorgesehen.Further, it is advantageous that the control valve seats 33,34 are arranged in different chambers, namely the first control valve seat 33 in the valve chamber 35 and the second control valve seat 34 in the intermediate chamber 37, wherein the valve chamber 35 and the intermediate chamber 37 only via the outlet throttle channel 24th connected to a smaller flow area. Axially between the valve chamber 35 and the intermediate chamber 37, a guide portion for the valve member 30 is provided.

Claims (9)

  1. Injector for injecting fuel into a combustion chamber of an internal combustion engine, in particular common rail injector, having a valve element (10) which can be adjusted, as a function of the fuel pressure in a control chamber (8), between a closed position and an open position in which the flow of fuel is enabled, and having a control valve (20) which is assigned to the control chamber (8) and which is connected via an inflow duct (22) to a high-pressure region of the injector (1), with an outflow throttle duct (24) and an inflow throttle duct (26), which permanently connects the control chamber (8) to the high-pressure region, being provided, wherein in a first switching position of the control valve (20), the inflow duct (22) is open and the control chamber (8) is connected to the high-pressure region of the injector (1) and the control chamber (8) is separated from a low-pressure region (6), and wherein in a second switching position of the control valve (20), the inflow duct (22) is blocked and the control chamber (8) is connected via the outflow throttle duct (24) to the low-pressure region (6), characterized in that a back-filling duct (28) is provided which leads from the control valve (20) into the control chamber (8), and in that, in the first switching position of the control valve (20), the back-filling duct (28) is hydraulically connected to the inflow duct (22) and, in the second switching position of the control valve (20), the connection between the back-filling duct (28) and inflow duct (22) is blocked.
  2. Injector according to Claim 1, characterized in that the control valve (20) has an in particular axially adjustable valve member (30) which, in the first switching position, bears against a first valve seat (33) and, in the second switching position, bears against a second control valve seat (34).
  3. Injector according to Claim 2, characterized in that the outflow throttle duct (24) is arranged between the control chamber (8) and the first control valve seat (33) in the fuel flow direction.
  4. Injector according to Claim 2, characterized in that the outflow throttle duct (24) is arranged downstream of the first control valve seat (33) in the fuel flow direction.
  5. Injector according to Claim 1, characterized in that the inflow duct (22) is formed as a throttle duct.
  6. Injector according to one of the preceding claims, characterized in that the control valve (20) is designed as a valve which is at least approximately pressure-balanced in the axial direction.
  7. Injector according to Claim 2, characterized in that an axial duct (38) is provided in the valve member (30), via which axial duct (38) fuel flows into the low-pressure region (6) in the second switching position of the control valve (20).
  8. Injector according to one of Claims 2-7, characterized in that the control valve seats (33, 34) are arranged in a section (40), which is surrounded radially at the outside by highly pressurized fuel, of the injector (1).
  9. Injector according to one of Claims 2-8, characterized in that the two control valve seats (33, 34) are arranged in different chambers, between which chambers is preferably provided a guide section for the valve member (30) and which chambers are preferably connected to one another only via the outflow throttle duct (24).
EP08104407A 2007-07-24 2008-06-13 Injector Not-in-force EP2022975B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102007034319A DE102007034319A1 (en) 2007-07-24 2007-07-24 injector

Publications (2)

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EP2022975A1 EP2022975A1 (en) 2009-02-11
EP2022975B1 true EP2022975B1 (en) 2010-05-12

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EP08104407A Not-in-force EP2022975B1 (en) 2007-07-24 2008-06-13 Injector

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EP (1) EP2022975B1 (en)
AT (1) ATE467757T1 (en)
DE (2) DE102007034319A1 (en)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2615294A1 (en) 2012-01-13 2013-07-17 Delphi Technologies Holding S.à.r.l. Fuel injector
DE102012005319A1 (en) * 2012-03-19 2013-09-19 L'orange Gmbh Injector assembly for fuel injector of motor vehicle, has actuating element that generates pressure in fluid, which is increased with respect to system high pressure, where injector assembly is formed to be effective against pressure force
DE102017103082A1 (en) 2017-02-15 2018-03-15 L'orange Gmbh Fuel injection injector for an internal combustion engine

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19533786B4 (en) 1995-09-13 2004-02-12 Robert Bosch Gmbh Solenoid valve for controlling pressure media
DE10131618A1 (en) * 2001-06-29 2003-01-23 Bosch Gmbh Robert Fuel injector with switchable control room inlet
DE102004015744A1 (en) * 2004-03-31 2005-10-13 Robert Bosch Gmbh Common rail injector
US7111614B1 (en) 2005-08-29 2006-09-26 Caterpillar Inc. Single fluid injector with rate shaping capability
US7415969B2 (en) * 2006-02-28 2008-08-26 Caterpillar Inc. Fuel injector having recessed check top
DE102006036446A1 (en) 2006-08-04 2008-02-07 Robert Bosch Gmbh Injector for fuel injection system of internal-combustion engine, has control valve exhibiting valve body and valve piston, where area of valve body is subjected inside and outside with fuel, which stays under high pressure
DE102006056840A1 (en) * 2006-12-01 2008-06-05 Robert Bosch Gmbh fuel injector

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DE502008000639D1 (en) 2010-06-24
EP2022975A1 (en) 2009-02-11
DE102007034319A1 (en) 2009-01-29
ATE467757T1 (en) 2010-05-15

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