EP2836696B1 - Injector of a modular common-rail fuel injection system with throughflow limiter - Google Patents

Injector of a modular common-rail fuel injection system with throughflow limiter Download PDF

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Publication number
EP2836696B1
EP2836696B1 EP13715200.5A EP13715200A EP2836696B1 EP 2836696 B1 EP2836696 B1 EP 2836696B1 EP 13715200 A EP13715200 A EP 13715200A EP 2836696 B1 EP2836696 B1 EP 2836696B1
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EP
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Prior art keywords
injector
holding body
pressure
injector according
accumulator
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EP13715200.5A
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German (de)
French (fr)
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EP2836696A1 (en
Inventor
Martin Bernhaupt
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Robert Bosch GmbH
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Robert Bosch GmbH
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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
    • F02M55/02—Conduits between injection pumps and injectors, e.g. conduits between pump and common-rail or conduits between common-rail and injectors
    • F02M55/025—Common rails
    • 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
    • F02M63/0056—Throttling valves, e.g. having variable opening positions throttling the flow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/28—Details of throttles in fuel-injection apparatus
    • 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
    • F02M2200/40—Fuel-injection apparatus with fuel accumulators, e.g. a fuel injector having an integrated fuel accumulator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/80—Fuel injection apparatus manufacture, repair or assembly
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/80—Fuel injection apparatus manufacture, repair or assembly
    • F02M2200/803—Fuel injection apparatus manufacture, repair or assembly using clamp elements and fastening means; e.g. bolts or screws
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/80—Fuel injection apparatus manufacture, repair or assembly
    • F02M2200/8076—Fuel injection apparatus manufacture, repair or assembly involving threaded members

Definitions

  • the invention relates to an injector of a modular common rail fuel injection system having a high-pressure accumulator integrated in the injector body, the injector having an injection nozzle with axially displaceably guided, surrounded by a nozzle chamber nozzle needle, a high-pressure accumulator with the nozzle chamber connecting high-pressure line and a holding body, the the front side with the component forming the high-pressure accumulator, in particular storage tube is screwed and through which the high-pressure line passes, wherein a flow restrictor for limiting the amount of fuel delivered from the high-pressure accumulator to the injection nozzle is arranged downstream of the high-pressure accumulator.
  • Such an injector is in the DE 10210282 A1 described.
  • Modular common rail systems are characterized in that part of the storage volume present in the system is present in the injectors themselves.
  • Modular common-rail systems are used in particularly large engines, in which the individual injectors may be mounted at a considerable distance from each other.
  • the sole use of a common rail for all injectors is not useful in such engines, as it would come to a massive slump in injection pressure due to the long lines during injection, so with prolonged injection duration, the injection rate would noticeably break.
  • it is therefore intended to arrange a high-pressure accumulator inside each injector.
  • Such a design is referred to as a modular structure, since each injector has its own high-pressure accumulator and thus can be used as a stand-alone module.
  • a high-pressure accumulator Under a high-pressure accumulator is not to be understood a common line, but it is a pressure-resistant vessel with an inlet and outlet whose diameter compared to the high pressure lines is significantly increased so that from the high-pressure accumulator a certain amount of injection can be delivered without causing an immediate pressure drop.
  • leaks can occur under unfavorable conditions, be it in the piping system or through defective injectors. Injectors with jamming nozzle needles, which lead to continuous injections into the combustion chamber, can cause considerable damage. These damages can lead to the fire of the vehicle or to the destruction of the engine.
  • flow rate limiter with closing function are known, which close the inlet to the affected injector when a maximum withdrawal amount from the high-pressure accumulator is exceeded, and thus decouple the high-pressure injection side from the injection valve side.
  • flow restrictors are usually arranged upstream of the storage volume.
  • top-feed injectors the fuel is supplied via a high-pressure port of the injector at the top of the high-pressure accumulator
  • the flow restrictor is usually attached to the upper end of the injector.
  • side-feed injectors the supply of the fuel takes place via a lance which contacts the injector laterally
  • the flow restrictor is usually arranged in front of the pressure pipe stub in a T-piece.
  • the flow restrictor housing is either pressed into the injector holder body or mounted with a retaining ring in the holding body.
  • Flow restrictors which are arranged in terms of flow in front of the storage volume, inherently have the disadvantage that they are to set much inaccurate. The reasons for this are the dead time and the damping effect of the storage volume and the influence of different fuel parameters such as temperature and viscosity or the fuel type (diesel or heavy oil).
  • a further disadvantage of the flow restrictor arranged in the flow medium in front of the storage volume is that a considerably larger amount can still be injected when closing the flow restrictor due to the expansion volume of the high-pressure accumulator. This property is repeatedly classified as very critical, especially in the very conservative business of large marine engines.
  • the installation of the flow restrictor at the top of Topfeed injectors also increase the mass there and thus worsen the vibration load capacity of the injector. Sidefeed injectors require a complex T-piece. Thus, two different solutions are required for the two injector concepts, which increases the variety of components.
  • Flow restrictors which are installed according to the storage volume (see eg DE102007025050 ), require in the pressed construction a press fit in the holding body or in a mounting with locking ring complex Bohrungsverschneidungen. Both constructions are very unfavorable in terms of fatigue strength in the extreme pressure loads prevailing in common-rail systems. For example, in systems with a system pressure of 2200 bar pressure loads of up to 2500 bar can be observed.
  • the present invention therefore aims to increase the fatigue strength, wherein in the holding body in particular interference fits and punctures for retaining rings or additional critical Bohrungsverschneidungen should be avoided. Furthermore, the same design concept for topfeed and sidefeed injectors should be used. Overall should be created with the same component cost as in the prior art training with a functionally optimal flow restrictor without the high pressure capacity of the holding body or the high-pressure accumulator is adversely affected.
  • the invention provides an injector according to claim 1.
  • the flow restrictor is inserted between the holding body and the storage tube, the benefits of flow moderately built according to the storage volume flow restrictors are used. Characterized in that the flow restrictor is inserted between the holding body and the storage tube and fixed by the screwing of the holding body and storage tube, eliminating the need for pressing or securing using a locking ring, and there is a very simple construction, which has a high fatigue strength.
  • the flow restrictor is in this case held only by the axial force generated during screwing of the holding body with the storage tube and clamped between these two components without the need for further fasteners as it were.
  • a preferred development of the invention provides that the holding body and the flow restrictor component are secured against rotation by means of an axial fixing pin.
  • the flow restrictor has a shoulder with a conical first sealing surface which cooperates with a formed on a shoulder of the storage tube conical sealing surface.
  • Another high-pressure-tight connection is preferably achieved in that the flow restrictor component on the end face facing the holding body has a conical second sealing surface which cooperates with a conical sealing surface formed on an end face of the holding body.
  • the arrangement of an anti-rotation in the form of locking pins can be omitted.
  • the further high-pressure line is designed as a resonator line, which is connected to the high-pressure accumulator via a resonator throttle.
  • the fluid connection of the flow restrictor to the two high-pressure lines can also take place in such a way that the high-pressure line and the additional high-pressure line are connected to the flow restrictor via a bore intersection formed in the flow restrictor component.
  • This embodiment is particularly advantageous for sidefeed injectors, where it is necessary that when closing the flow restrictor no amount of fuel directly from the side fuel inlet to the injector (bypass of the flow restrictor) can flow.
  • connection of the fuel supply to the high pressure accumulator is preferably such that the injector has a side port for the fuel supply, which communicates with an inlet bore, the first portion is formed in the holding body and the second portion passes through the flow restrictor axially.
  • a bypass of the flow restrictor is preferably prevented in that the flow restrictor component on the end face facing the holding body has a planar second sealing surface which cooperates with the planar end face of the holding body.
  • the flow restrictor component comprises a housing with a high-pressure accumulator-side housing inlet and a housing body-side housing outlet, a longitudinally displaceable in a chamber of the housing between a starting position and an end position and against the flow direction spring-biased closing member. This connects the housing inlet and housing outlet hydraulically via at least one throttle having a channel channel and further controls a flow connection between the housing inlet and the housing outlet.
  • a retaining ring fixed in the flow restrictor component defines the starting position of the closing member.
  • FIG. 1 the schematic structure of an injector of a modular common rail fuel injection system according to the prior art
  • Fig. 2 a detailed view of the injector in area II of Fig. 1 in a first training
  • Fig. 3 a detailed view of the injector in a second embodiment
  • Fig. 4 a detailed view of the injector in a third embodiment
  • Fig. 5 a detailed view of the injector in a fourth embodiment.
  • an injector 1 having an injection nozzle 2, a throttle plate 3, a valve plate 4, a holding body 5 and a high pressure accumulator 6, wherein a screwed to the holding body 5 nozzle retaining nut 7, the injection nozzle 2, the throttle plate 3 and the valve plate. 4 holds together.
  • the solenoid valve 13 is closed, so that high-pressure fuel from the high-pressure accumulator 6 via the high-pressure line 8, the cross-connection 9 and the inlet throttle 10 flows into the control chamber 11 of the injection nozzle 2, the outflow from the control chamber 11 via the outlet throttle 12 but at the valve seat of the solenoid valve 13 is blocked.
  • a resonator 20 may be arranged with a high pressure storage side resonator 21, with which occurring pressure peaks can be lowered more quickly.
  • topfeed injector The supply of high-pressure fuel from a high-pressure pump not shown in the injector 1, via a arranged on the top of the injector 1 high-pressure port 22 (topfeed injector).
  • the fuel supply via a side of the injector 1, in particular on the holding body 5 arranged high-pressure port 23, and a high-pressure accumulator 6 leading inlet bore 24 made (sidefeed injector).
  • FIGS. 2 to 5 show a view of the detail X of the Fig. 1 with the flow restrictor arranged between the storage tube 25, the high-pressure accumulator 6 and the holding body 5.
  • the trainings according to FIGS. 2 to 5 is that the flow rate regulator is formed in a separate flow restrictor component 26.
  • the flow restrictor member 26 has a first axial portion 27 and a second axial portion 28, the second axial portion 28 having a larger outer diameter than the first axial portion 27 axial portion 28, the flow restrictor 26 has a shoulder with a tapered first sealing surface 29 which cooperates with a formed on a shoulder 30 of the storage tube 25 conical mating sealing surface.
  • the shoulder 30 of the storage tube 25 is connected via an annular groove-like recess 31 with a thinner walled, provided with an internal thread 33 portion 32 of the storage tube 25.
  • the flow restrictor 26 is inserted between the holding body 5 and the storage tube 25 and fixed by the screw connection of these two components. In this case, the flow restrictor 26 is secured by means of pins 34 against rotation.
  • the seal to the holding body 5 takes place in the embodiment according to the Fig. 2, 3rd and 5 via a flat sealing point, which is formed by a plane face formed on the end face facing the holding body 5, which cooperates with the planar end face of the holding body 5.
  • the flow restrictor member 26 has an inlet 36 and an outlet 37.
  • a displaceably guided in the axial direction piston 39 is arranged, which is pressed by means of the compression spring 40 against the retaining ring 41.
  • the piston 39 has a blind hole 42, which communicates on the one hand with the inlet 36 and on the other hand via a throttle bore 43 with the outlet 37.
  • the amount of injection is removed from the chamber 38.
  • the piston 39 moves against the spring force in the direction of the lower sealing seat 44, without, however, reaching it.
  • the compression spring 40 pushes the piston 39 back to the starting position.
  • the chamber 38 is in this case filled via the throttle 43 again.
  • the piston 39 moves so far that the sealing seat 44 is reached and the injection is terminated.
  • the throttle 43 creates a pressure loss between the present in the blind hole 42 fuel and the chamber 38.
  • a defined throttle flow is exceeded, the piston 39 moves against the spring force in the direction of the lower sealing seat 44 and thus ends the injection.
  • a single high-pressure line 8 is provided which extends through the holding body 5.
  • the fuel passing through the flow restrictor 26 passes directly into the high-pressure line 8 via a bore section 48.
  • a further high-pressure line 20 is arranged, which is designed as a resonator and communicates with the fuel supply via a resonator throttle 21.
  • the two high-pressure lines 8 and 20 are by a in the Flow restrictor 26 trained Bohrungsverschneidung 45 fueled.
  • the sealing of the flow restrictor 26 to the holding body 5 can also be done via a cone seal 46 in topfeed injectors.
  • the pins 34 can be omitted for the rotation.
  • the conical sealing surfaces forming the conical seal 46 in this case delimit a hollow space 47 into which, on the one hand, the outlet 37 and, on the other hand, the high-pressure lines 8 and 20 open.
  • Fig. 5 it is a sidefeed injector, in which the fuel is fed via the inlet bore 24 from the holding body 5 via the flow restrictor 26 into the high-pressure accumulator 6.
  • the inlet bore 24 opens in this case via a storage throttle 49 in the high-pressure accumulator. 6

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)

Description

Die Erfindung betrifft einen Injektor eines modularen Common-Rail-Kraftstoffeinspritzsystems mit einem im Injektorkörper integrierten Hochdruckspeicher, wobei der Injektor eine Einspritzdüse mit darin axial verschieblich geführter, von einem Düsenraum umgebener Düsennadel, eine den Hochdruckspeicher mit dem Düsenraum verbindende Hochdruckleitung und einen Haltekörper aufweist, der stirnseitig mit dem den Hochdruckspeicher bildenden Bauteil, insbesondere Speicherrohr verschraubt ist und durch den die Hochdruckleitung verläuft, wobei strömungsmäßig nach dem Hochdruckspeicher ein Durchflussbegrenzer zum Begrenzen der aus dem Hochdruckspeicher zur Einspritzdüse geförderten Kraftstoffmenge angeordnet ist.The invention relates to an injector of a modular common rail fuel injection system having a high-pressure accumulator integrated in the injector body, the injector having an injection nozzle with axially displaceably guided, surrounded by a nozzle chamber nozzle needle, a high-pressure accumulator with the nozzle chamber connecting high-pressure line and a holding body, the the front side with the component forming the high-pressure accumulator, in particular storage tube is screwed and through which the high-pressure line passes, wherein a flow restrictor for limiting the amount of fuel delivered from the high-pressure accumulator to the injection nozzle is arranged downstream of the high-pressure accumulator.

Ein derartiger Injektor ist in der DE 10210282 A1 beschrieben.Such an injector is in the DE 10210282 A1 described.

Modulare Common-Rail-Systeme sind dadurch gekennzeichnet, dass ein Teil des im System vorhandenen Speichervolumens in den Injektoren selbst vorhanden ist. Modulare Common-Rail-Systeme kommen bei besonders großen Motoren zum Einsatz, bei welchen die einzelnen Injektoren unter Umständen in erheblichem Abstand voneinander angebracht sind. Die alleinige Verwendung eines gemeinsamen Rails für alle Injektoren ist bei solchen Motoren nicht sinnvoll, da es aufgrund der langen Leitungen während der Einspritzung zu einem massiven Einbruch im Einspritzdruck kommen würde, sodass bei längerer Spritzdauer die Einspritzrate merklich einbrechen würde. Bei solchen Motoren ist es daher vorgesehen, einen Hochdruckspeicher im Inneren eines jeden Injektors anzuordnen. Eine solche Bauweise wird als modularer Aufbau bezeichnet, da jeder einzelne Injektor über seinen eigenen Hochdruckspeicher verfügt und somit als eigenständiges Modul eingesetzt werden kann. Unter einem Hochdruckspeicher ist hierbei nicht eine gewöhnliche Leitung zu verstehen, sondern es handelt sich um ein druckfestes Gefäß mit einer Zu- bzw. Ableitung, dessen Durchmesser im Vergleich zu den Hochdruckleitungen deutlich vergrößert ist, damit aus dem Hochdruckspeicher eine gewisse Einspritzmenge abgegeben werden kann, ohne dass es zu einem sofortigen Druckabfall kommt.Modular common rail systems are characterized in that part of the storage volume present in the system is present in the injectors themselves. Modular common-rail systems are used in particularly large engines, in which the individual injectors may be mounted at a considerable distance from each other. The sole use of a common rail for all injectors is not useful in such engines, as it would come to a massive slump in injection pressure due to the long lines during injection, so with prolonged injection duration, the injection rate would noticeably break. In such engines, it is therefore intended to arrange a high-pressure accumulator inside each injector. Such a design is referred to as a modular structure, since each injector has its own high-pressure accumulator and thus can be used as a stand-alone module. Under a high-pressure accumulator is not to be understood a common line, but it is a pressure-resistant vessel with an inlet and outlet whose diameter compared to the high pressure lines is significantly increased so that from the high-pressure accumulator a certain amount of injection can be delivered without causing an immediate pressure drop.

Bei Common-Rail-Systemen können unter ungünstigen Umständen Leckagen auftreten, sei es im Leitungssystem oder durch defekte Einspritzventile. Einspritzventile mit klemmenden Düsennadeln, die zu Dauereinspritzungen in den Brennraum führen, können erhebliche Schäden verursachen. Diese Schäden können zum Brand des Fahrzeuges oder zur Zerstörung des Motors führen. Zur Vermeidung dieser Gefahren sind Durchflussmengenbegrenzer mit Schließfunktion bekannt, die bei Überschreiten einer maximalen Entnahmemenge aus dem Hochdruckspeicher den Zulauf zu dem betroffenen Injektor verschließen und damit den einspritzpumpenseitigen Hochdruck von der Einspritzventilseite abkoppeln.In common rail systems, leaks can occur under unfavorable conditions, be it in the piping system or through defective injectors. Injectors with jamming nozzle needles, which lead to continuous injections into the combustion chamber, can cause considerable damage. These damages can lead to the fire of the vehicle or to the destruction of the engine. To avoid these dangers flow rate limiter with closing function are known, which close the inlet to the affected injector when a maximum withdrawal amount from the high-pressure accumulator is exceeded, and thus decouple the high-pressure injection side from the injection valve side.

Durchflussbegrenzer sind bei Injektoren mit integriertem Hochdruckspeicher strommäßig meist vor dem Speichervolumen angeordnet. Bei sogenannten Top-Feed-Injektoren (die Zuführung des Kraftstoffes erfolgt über einen Hochdruckanschluss des Injektors an der Oberseite des Hochdruckspeichers) ist der Durchflussbegrenzer meist am oberen Ende des Injektors angebracht. Bei sogenannten Side-Feed-Injektoren (die Zuführung des Kraftstoffes erfolgt über eine den Injektor seitlich kontaktierende Lanze) ist der Durchflussbegrenzer meist vor dem Druckrohrstutzen in einem T-Stück angeordnet. Weiters gibt es auch Anordnungen, bei denen der Durchflussbegrenzer strommäßig nach dem Speichervolumen angeordnet ist. Hier ist das Durchflussbegrenzer-Gehäuse entweder in den Injektor-Haltekörper eingepresst oder mit einem Sicherungsring im Haltekörper montiert.In the case of injectors with integrated high-pressure accumulator, flow restrictors are usually arranged upstream of the storage volume. In so-called top-feed injectors (the fuel is supplied via a high-pressure port of the injector at the top of the high-pressure accumulator), the flow restrictor is usually attached to the upper end of the injector. In the case of so-called side-feed injectors (the supply of the fuel takes place via a lance which contacts the injector laterally), the flow restrictor is usually arranged in front of the pressure pipe stub in a T-piece. Furthermore, there are also arrangements in which the flow restrictor is arranged according to the current storage volume. Here, the flow restrictor housing is either pressed into the injector holder body or mounted with a retaining ring in the holding body.

Durchflussbegrenzer, welche strommäßig vor dem Speichervolumen angeordnet sind, haben prinzipbedingt den Nachteil, dass diese wesentlich ungenauer einzustellen sind. Die Gründe hierfür liegen in der Totzeit und der Dämpfwirkung des Speichervolumens und am Einfluss von verschiedenen Kraftstoffparametern wie Temperatur und Viskosität oder dem Kraftstofftyp (Diesel oder Schweröl). Ein weiterer Nachteil der strommäßig vor dem Speichervolumen angeordneten Durchflussbegrenzer ist, dass beim Schließen des Durchflussbegrenzers auf Grund des Expansionsvolumens des Hochdruckspeichers eine erheblich größere Menge noch eingespritzt werden kann. Diese Eigenschaft wird speziell im sehr konservativen Geschäft der großen Marinemotoren immer wieder als sehr kritisch eingestuft. Die Montage des Durchflussbegrenzers am oberen Ende von Topfeed-Injektoren erhöht dort außerdem die Masse und verschlechtert dadurch die Vibrationsbelastbarkeit des Injektors. Bei Sidefeed-Injektoren ist ein aufwändiges T-Stück erforderlich. Für die beiden Injektorkonzepte benötigt man somit zwei verschiedene Lösungen, was die Bauteilevielfalt erhöht.Flow restrictors, which are arranged in terms of flow in front of the storage volume, inherently have the disadvantage that they are to set much inaccurate. The reasons for this are the dead time and the damping effect of the storage volume and the influence of different fuel parameters such as temperature and viscosity or the fuel type (diesel or heavy oil). A further disadvantage of the flow restrictor arranged in the flow medium in front of the storage volume is that a considerably larger amount can still be injected when closing the flow restrictor due to the expansion volume of the high-pressure accumulator. This property is repeatedly classified as very critical, especially in the very conservative business of large marine engines. The installation of the flow restrictor at the top of Topfeed injectors also increase the mass there and thus worsen the vibration load capacity of the injector. Sidefeed injectors require a complex T-piece. Thus, two different solutions are required for the two injector concepts, which increases the variety of components.

Durchflussbegrenzer, welche strommäßig nach dem Speichervolumen verbaut werden (s. z.B. DE102007025050 ), erfordern bei der eingepressten Bauweise eine Presspassung im Haltekörper oder bei einer Montage mit Sicherungsring komplexe Bohrungsverschneidungen. Beide Konstruktionen sind sehr ungünstig bezüglich Dauerfestigkeit bei den bei Common-Rail-Systemen herrschenden extremen Druckbelastungen. So sind bei Systemen mit einem Systemdruck von 2200 bar Druckbelastungen von bis zu 2500 bar zu beobachten. Die vorliegende Erfindung zielt daher darauf ab, die Dauerfestigkeit zu erhöhen, wobei im Haltekörper insbesondere Presspassungen und Einstiche für Sicherungsringe oder zusätzliche kritische Bohrungsverschneidungen vermieden werden sollen. Weiters soll ein- und dasselbe Konstruktionskonzept für Topfeed- und für Sidefeed-Injektoren verwendet werden. Insgesamt soll bei gleichem Bauteilaufwand wie im Stand der Technik eine Ausbildung mit einem funktional optimalen Durchflussbegrenzer geschaffen werden, ohne dass die Hochdruck-Belastbarkeit des Haltekörpers oder des Hochdruckspeichers negativ beeinflusst wird.Flow restrictors, which are installed according to the storage volume (see eg DE102007025050 ), require in the pressed construction a press fit in the holding body or in a mounting with locking ring complex Bohrungsverschneidungen. Both constructions are very unfavorable in terms of fatigue strength in the extreme pressure loads prevailing in common-rail systems. For example, in systems with a system pressure of 2200 bar pressure loads of up to 2500 bar can be observed. The present invention therefore aims to increase the fatigue strength, wherein in the holding body in particular interference fits and punctures for retaining rings or additional critical Bohrungsverschneidungen should be avoided. Furthermore, the same design concept for topfeed and sidefeed injectors should be used. Overall should be created with the same component cost as in the prior art training with a functionally optimal flow restrictor without the high pressure capacity of the holding body or the high-pressure accumulator is adversely affected.

Zur Lösung dieser Aufgabe sieht die Erfindung einen Injektor gemäß Anspruch 1 vor. Dadurch, dass der Durchflussbegrenzer zwischen dem Haltekörper und dem Speicherrohr eingelegt ist, werden die Vorteile von strommäßig nach dem Speichervolumen verbauten Durchflussbegrenzern genützt. Dadurch, dass der Durchflussbegrenzer zwischen dem Haltekörper und dem Speicherrohr eingelegt und durch die Verschraubung von Haltekörper und Speicherrohr fixiert ist, entfällt die Notwendigkeit eines Einpressens oder eines Sicherns mit Hilfe eines Sicherungsrings, und es entsteht eine überaus einfache Konstruktion, die eine hohe Dauerfestigkeit aufweist. Das Durchflussbegrenzerbauteil wird hierbei lediglich durch die beim Verschrauben des Haltkörpers mit dem Speicherrohr erzeugte axiale Kraft gehalten und zwischen diesen beiden Bauteilen ohne die Notwendigkeit weitere Befestigungsmittel gleichsam eingeklemmt.To solve this problem, the invention provides an injector according to claim 1. The fact that the flow restrictor is inserted between the holding body and the storage tube, the benefits of flow moderately built according to the storage volume flow restrictors are used. Characterized in that the flow restrictor is inserted between the holding body and the storage tube and fixed by the screwing of the holding body and storage tube, eliminating the need for pressing or securing using a locking ring, and there is a very simple construction, which has a high fatigue strength. The flow restrictor is in this case held only by the axial force generated during screwing of the holding body with the storage tube and clamped between these two components without the need for further fasteners as it were.

Damit das beim Verschrauben des Haltekörpers mit dem Speicherrohr auf das Durchflussbegrenzerbauteil wirkende Drehmoment nicht zu einem Verdrehen des Durchflussbegrenzerbauteils führt, sieht eine bevorzugte Weiterbildung der Erfindung vor, dass der Haltekörper und das Durchflussbegrenzerbauteil mittels eines axialen Fixierstiftes verdrehgesichert sind.In order that the torque acting on the flow restrictor component during screwing of the holding body does not lead to a rotation of the flow restrictor component, a preferred development of the invention provides that the holding body and the flow restrictor component are secured against rotation by means of an axial fixing pin.

Um einerseits ein sicheres Halten des Durchflussbegrenzerbauteils und andererseits eine hochdruckdichte Verbindung zu schaffen, ist bevorzugt vorgesehen, dass das Durchflussbegrenzerbauteil eine Schulter mit einer kegeligen ersten Dichtfläche aufweist, die mit einer an einem Absatz des Speicherrohrs ausgebildeten kegeligen Dichtfläche zusammenwirkt.On the one hand to provide a secure hold of the flow restrictor and on the other hand a high pressure-tight connection, it is preferably provided that the flow restrictor has a shoulder with a conical first sealing surface which cooperates with a formed on a shoulder of the storage tube conical sealing surface.

Eine weitere hochdruckdichte Verbindung wird bevorzugt dadurch erreicht, dass das Durchflussbegrenzerbauteil an der dem Haltekörper zugewandten Stirnseite eine kegelige zweite Dichtfläche aufweist, die mit einer an einer Stirnseite des Haltekörpers ausgebildeten kegeligen Dichtfläche zusammenwirkt. In diesem Falle kann die Anordnung einer Verdrehsicherung in der Form von Sicherungsstiften entfallen.Another high-pressure-tight connection is preferably achieved in that the flow restrictor component on the end face facing the holding body has a conical second sealing surface which cooperates with a conical sealing surface formed on an end face of the holding body. In this case, the arrangement of an anti-rotation in the form of locking pins can be omitted.

Im Falle einer kegeligen Dichtfläche zwischen dem Durchflussbegrenzerbauteil und dem Haltekörper muss bei Topfeed-Injektoren keine unmittelbare Verbindung des Durchflussbegrenzers mit der Hochdruckbohrung des Haltekörpers erfolgen, sondern es kann die Ausbildung so getroffen sein, dass die kegelige zweite Dichtfläche des Durchflussbegrenzerbauteils einen zwischen Haltekörper und Durchflussbegrenzerbauteil ausgebildeten Hohlraum begrenzt. Die Verbindung erfolgt dann über den genannten Hohlraum, was von besonderem Vorteil ist, wenn durch den Haltekörper eine parallel zur Hochdruckleitung geschaltene weitere Hochdruckleitung verläuft, die einerseits mit dem Düsenraum und andererseits mit dem Hochdruckspeicher in Verbindung steht. Hierbei münden sowohl die Hochdruckleitung als auch die weitere Hochdruckleitung in den genannten Hohlraum, sodass beide Leitungen mit über den Durchflussbegrenzer fließendem Kraftstoff versorgt werden.In the case of a conical sealing surface between the flow restrictor and the holder body must not be made with top-feed injectors direct connection of the flow restrictor with the high-pressure bore of the holder body, but it can be made such that the conical second sealing surface of the flow restrictor formed between a holding body and flow restrictor Cavity limited. The connection then takes place via the said cavity, which is particularly advantageous if a further parallel to the high-pressure line connected further high-pressure line passes through the holding body, which is on the one hand with the nozzle chamber and on the other hand with the high-pressure accumulator in combination. In this case, both the high-pressure line and the further high-pressure line open into the said cavity, so that both lines are supplied with fuel flowing through the flow restrictor.

Besonders bevorzugt ist die weitere Hochdruckleitung hierbei als Resonatorleitung ausgebildet, die über eine Resonatordrossel mit dem Hochdruckspeicher in Verbindung steht.Particularly preferably, the further high-pressure line is designed as a resonator line, which is connected to the high-pressure accumulator via a resonator throttle.

Die strömungsmäßige Verbindung des Durchflussbegrenzers mit den beiden Hochdruckleitungen kann alternativ aber auch so erfolgen, dass die Hochdruckleitung und die weitere Hochdruckleitung über eine in dem Durchflussbegrenzerbauteil ausgebildete Bohrungsverschneidung mit dem Durchflussbegrenzer in Verbindung stehen. Diese Ausführung ist insbesondere auch für Sidefeed-Injektoren vorteilhaft, bei denen es erforderlich ist, dass beim Schließen des Durchflussbegrenzers keine Kraftstoffmenge direkt vom seitlichen Kraftstoffzulauf zur Einspritzdüse (Bypass des Durchflussbegrenzers) fließen kann.Alternatively, the fluid connection of the flow restrictor to the two high-pressure lines can also take place in such a way that the high-pressure line and the additional high-pressure line are connected to the flow restrictor via a bore intersection formed in the flow restrictor component. This embodiment is particularly advantageous for sidefeed injectors, where it is necessary that when closing the flow restrictor no amount of fuel directly from the side fuel inlet to the injector (bypass of the flow restrictor) can flow.

Bei Sidefeed-Injektoren erfolgt die Verbindung der Kraftstoffversorgung mit dem Hochdruckspeicher bevorzugt so, dass der Injektor einen seitlichen Anschluss für die Kraftstoffversorgung aufweist, der mit einer Zulaufbohrung in Verbindung steht, deren erster Abschnitt im Haltekörper ausgebildet ist und deren zweiter Abschnitt das Durchflussbegrenzerbauteil axial durchsetzt. Ein Bypass des Durchflussbegrenzers wird hierbei bevorzugt dadurch verhindert, dass das Durchflussbegrenzerbauteil an der dem Haltekörper zugewandten Stirnseite eine plane zweite Dichtfläche aufweist, die mit der planen Stirnseite des Haltekörpers zusammenwirkt.In Sidefeed injectors, the connection of the fuel supply to the high pressure accumulator is preferably such that the injector has a side port for the fuel supply, which communicates with an inlet bore, the first portion is formed in the holding body and the second portion passes through the flow restrictor axially. In this case, a bypass of the flow restrictor is preferably prevented in that the flow restrictor component on the end face facing the holding body has a planar second sealing surface which cooperates with the planar end face of the holding body.

Die Ausbildung des Durchflussbegrenzers als eigenes Bauteil erhöht die Flexibilität bei dessen konstruktiver Ausbildung. Erfindungsgemäß ist in diesem Zusammenhang vorgesehen, dass das Durchflussbegrenzerbauteil ein Gehäuse mit einem hochdruckspeicherseitigen Gehäuseeinlass und einem haltekörperseitigen Gehäuseauslass, ein in einer Kammer des Gehäuses zwischen einer Ausgangsstellung und einer Endstellung längsverschiebbares und entgegen der Strömungsrichtung federvorgespanntes Schließglied umfasst. Dieses verbindet über wenigstens einen eine Drossel aufweisenden Kanal den Gehäuseeinlass und Gehäuseauslass miteinander hydraulisch und steuert weiters eine Strömungsverbindung zwischen dem Gehäuseeinlass und dem Gehäuseauslass.The design of the flow restrictor as a separate component increases the flexibility in its structural design. According to the invention, it is provided in this connection that the flow restrictor component comprises a housing with a high-pressure accumulator-side housing inlet and a housing body-side housing outlet, a longitudinally displaceable in a chamber of the housing between a starting position and an end position and against the flow direction spring-biased closing member. This connects the housing inlet and housing outlet hydraulically via at least one throttle having a channel channel and further controls a flow connection between the housing inlet and the housing outlet.

Insbesondere kann vorgesehen sein, dass ein in dem Durchflussbegrenzerbauteil fixierter Sicherungsring die Ausgangsstellung des Schließglieds definiert.In particular, it may be provided that a retaining ring fixed in the flow restrictor component defines the starting position of the closing member.

Die Erfindung wird nachfolgend anhand von in der Zeichnung dargestellten Ausführungsbeispielen näher erläutert. In dieser zeigen Fig. 1 den schematischen Aufbau eines Injektors eines modularen Common-Rail-Kraftstoffeinspritzsystems gemäß dem Stand der Technik, Fig. 2 eine Detailansicht des Injektors im Bereich II der Fig. 1 in einer erste Ausbildung, Fig. 3 eine Detailansicht des Injektors in einer zweiten Ausbildung, Fig. 4 eine Detailansicht des Injektors in einer dritten Ausbildung und Fig. 5 eine Detailansicht des Injektors in einer vierten Ausbildung.The invention will be explained in more detail with reference to embodiments shown in the drawing. In this show Fig. 1 the schematic structure of an injector of a modular common rail fuel injection system according to the prior art, Fig. 2 a detailed view of the injector in area II of Fig. 1 in a first training, Fig. 3 a detailed view of the injector in a second embodiment, Fig. 4 a detailed view of the injector in a third embodiment and Fig. 5 a detailed view of the injector in a fourth embodiment.

In Fig. 1 ist ein Injektor 1 dargestellt, der eine Ein-spritzdüse 2, eine Drosselplatte 3, eine Ventilplatte 4, einen Haltekörper 5 und einen Hochdruckspeicher 6 aufweist, wobei eine mit dem Haltekörper 5 verschraubte Düsenspannmutter 7 die Einspritzdüse 2, die Drosselplatte 3 und die Ventilplatte 4 zusammenhält. Im Ruhezustand ist das Magnetventil 13 geschlossen, sodass Hochdruckkraftstoff aus dem Hochdruckspeicher 6 über die Hochdruckleitung 8, die Querverbindung 9 und die Zulaufdrossel 10 in den Steuerraum 11 der Einspritzdüse 2 strömt, der Abfluss aus dem Steuerraum 11 über die Ablaufdrossel 12 aber am Ventilsitz des Magnetventils 13 blockiert ist. Der im Steuerraum 11 anliegende Systemdruck drückt gemeinsam mit der Kraft der Düsenfeder 14 die Düsennadel 15 in den Düsennadelsitz 16, sodass die Spritzlöcher 17 verschlossen sind. Wird der Elektromagnet des Magnetventils 13 betätigt, gibt es den Durchfluss über den Magnetventilsitz frei, und Kraftstoff strömt aus dem Steuerraum 11 durch die Ablaufdrossel 12, den Magnetventilankerraum und die Niederdruckbohrung 18 zurück in den nicht dargestellten Kraftstofftank. Es stellt sich ein durch die Strömungsquerschnitte von Zulaufdrossel 10 und Ablaufdrossel 12 definierter Gleichgewichtsdruck im Steuerraum 11 ein, der so gering ist, dass der im Düsenraum 19 anliegende Systemdruck die im Düsenkörper längs verschieblich geführte Düsennadel 15 zu öffnen vermag, sodass die Spritzlöcher 17 freigegeben werden und eine Einspritzung erfolgt.In Fig. 1 an injector 1 is shown having an injection nozzle 2, a throttle plate 3, a valve plate 4, a holding body 5 and a high pressure accumulator 6, wherein a screwed to the holding body 5 nozzle retaining nut 7, the injection nozzle 2, the throttle plate 3 and the valve plate. 4 holds together. In the idle state, the solenoid valve 13 is closed, so that high-pressure fuel from the high-pressure accumulator 6 via the high-pressure line 8, the cross-connection 9 and the inlet throttle 10 flows into the control chamber 11 of the injection nozzle 2, the outflow from the control chamber 11 via the outlet throttle 12 but at the valve seat of the solenoid valve 13 is blocked. The one in the control room 11 applied system pressure presses together with the force of the nozzle spring 14, the nozzle needle 15 in the nozzle needle seat 16, so that the injection holes 17 are closed. If the solenoid of the solenoid valve 13 is actuated, it releases the flow through the solenoid valve seat, and fuel flows from the control chamber 11 through the outlet throttle 12, the solenoid valve armature chamber and the low pressure bore 18 back into the fuel tank, not shown. A equilibrium pressure defined in the control chamber 11 by the flow cross-sections of inlet throttle 10 and outlet throttle 12 is so small that the system pressure applied in the nozzle chamber 19 is able to open the nozzle needle 15, which is displaceable longitudinally in the nozzle body, so that the spray holes 17 are released and an injection takes place.

Sobald das Magnetventil 13 geschlossen wird, wird der Ablaufweg des Kraftstoffes durch die Ablaufdrossel 12 gesperrt. Über die Zulaufdrossel 10 wird im Steuerraum 11 wieder Kraftstoffdruck aufgebaut, was eine zusätzliche Schließkraft erzeugt, welche die hydraulische Kraft auf die Druckschulter der Düsennadel 15 vermindert und die Kraft der Düsenfeder 14 übersteigt. Die Düsennadel 15 verschließt den Weg zu den Einspritzöffnungen 17, wodurch der Einspritzvorgang beendet wird.As soon as the solenoid valve 13 is closed, the drainage path of the fuel is blocked by the outlet throttle 12. Via the inlet throttle 10, fuel pressure is again built up in the control chamber 11, which generates an additional closing force which reduces the hydraulic force on the pressure shoulder of the nozzle needle 15 and exceeds the force of the nozzle spring 14. The nozzle needle 15 closes the way to the injection openings 17, whereby the injection process is terminated.

Parallel zur Hochdruckbohrung 8 kann eine Resonatorleitung 20 mit einer hochdruckspeicherseitigen Resonatordrossel 21 angeordnet sein, mit welcher auftretende Druckspitzen rascher abgesenkt werden können.Parallel to the high pressure bore 8, a resonator 20 may be arranged with a high pressure storage side resonator 21, with which occurring pressure peaks can be lowered more quickly.

Die Zuführung des Hochdruckkraftstoffs von einer nicht näher dargestellten Hochdruckpumpe in den Injektor 1, kann über einen an der Oberseite des Injektors 1 angeordneten Hochdruckanschluss 22 erfolgen (Topfeed-Injektor). Alternativ kann die Kraftstoffzuführung über einen seitlich am Injektor 1, insbesondere an dem Haltekörper 5 angeordneten Hochdruckanschluss 23, sowie eine zum Hochdruckspeicher 6 führende Zulaufbohrung 24 erfolgen (Sidefeed-Injektor).The supply of high-pressure fuel from a high-pressure pump not shown in the injector 1, via a arranged on the top of the injector 1 high-pressure port 22 (topfeed injector). Alternatively, the fuel supply via a side of the injector 1, in particular on the holding body 5 arranged high-pressure port 23, and a high-pressure accumulator 6 leading inlet bore 24 made (sidefeed injector).

Die Figuren 2 bis 5 zeigen eine Ansicht des Details X der Fig. 1 mit dem zwischen dem Speicherrohr 25, dem Hochdruckspeicher 6 und dem Haltekörper 5 angeordneten Durchflussbegrenzer. Den Ausbildungen gemäß den Figuren 2 bis 5 ist gemeinsam, dass der Durchflussbregenzer in einem eigenen Durchflussbegrenzerbauteil 26 ausgebildet ist. Das Durchflussbegrenzerbauteil 26 weist einen ersten axialen Abschnitt 27 und einen zweiten axialen Abschnitt 28 auf, wobei der zweite axiale Abschnitt 28 einen größeren Außendurchmesser aufweist, als der erste axiale Abschnitt 27. Am zweiten axialen Abschnitt 28 weist das Durchflussbegrenzerbauteil 26 eine Schulter mit einer kegeligen ersten Dichtfläche 29 auf, die mit einer an einem Absatz 30 des Speicherrohrs 25 ausgebildeten kegeligen Gegendichtfläche zusammenwirkt. Der Absatz 30 des Speicherrohrs 25 ist über eine ringnutartige Ausnehmung 31 mit einem dünnwandigeren, mit einem Innengewinde 33 versehenen Abschnitt 32 des Speicherrohrs 25 verbunden. Das Durchflussbegrenzerbauteil 26 wird zwischen den Haltekörper 5 und das Speicherrohr 25 eingelegt und durch die Verschraubung dieser beiden Bauteile fixiert. Dabei wird das Durchflussbegrenzerbauteil 26 mittels Stiften 34 gegen das Verdrehen gesichert. Die Abdichtung zum Haltekörper 5 erfolgt bei der Ausbildung gemäß den Fig. 2, 3 und 5 über eine Flachdichtstelle, welche von einer an der dem Haltekörper 5 zugewandten Stirnseite ausgebildeten Plandichtfläche ausgebildet wird, welche mit der planen Stirnseite des Haltekörpers 5 zusammenwirkt.The FIGS. 2 to 5 show a view of the detail X of the Fig. 1 with the flow restrictor arranged between the storage tube 25, the high-pressure accumulator 6 and the holding body 5. The trainings according to FIGS. 2 to 5 In common is that the flow rate regulator is formed in a separate flow restrictor component 26. The flow restrictor member 26 has a first axial portion 27 and a second axial portion 28, the second axial portion 28 having a larger outer diameter than the first axial portion 27 axial portion 28, the flow restrictor 26 has a shoulder with a tapered first sealing surface 29 which cooperates with a formed on a shoulder 30 of the storage tube 25 conical mating sealing surface. The shoulder 30 of the storage tube 25 is connected via an annular groove-like recess 31 with a thinner walled, provided with an internal thread 33 portion 32 of the storage tube 25. The flow restrictor 26 is inserted between the holding body 5 and the storage tube 25 and fixed by the screw connection of these two components. In this case, the flow restrictor 26 is secured by means of pins 34 against rotation. The seal to the holding body 5 takes place in the embodiment according to the Fig. 2, 3rd and 5 via a flat sealing point, which is formed by a plane face formed on the end face facing the holding body 5, which cooperates with the planar end face of the holding body 5.

Das Durchflussbegrenzerbauteil 26 weist einen Einlass 36 und einen Auslass 37 auf. In einer Kammer 38 ist ein in axialer Richtung verschieblich geführter Kolben 39 angeordnet, der mittels der Druckfeder 40 gegen den Sicherungsring 41 gedrückt wird. Der Kolben 39 weist ein Sackloch 42 auf, das einerseits mit dem Einlass 36 und andererseits über eine Drosselbohrung 43 mit dem Auslass 37 in Verbindung steht. Im Betrieb wird die Einspritzmenge aus der Kammer 38 entnommen. Dadurch bewegt sich der Kolben 39 gegen die Federkraft in Richtung zum unteren Dichtsitz 44, ohne diesen allerdings zu erreichen. Während der Nicht-Einspritzzeit drückt die Druckfeder 40 den Kolben 39 in die Ausgangsstellung zurück. Die Kammer 38 wird hierbei über die Drossel 43 wieder befüllt. Falls die Einspritzmenge einen definierten Maximalwert überschreitet, bewegt sich der Kolben 39 so weit, dass der Dichtsitz 44 erreicht wird und die Einspritzung beendet wird. Durch die Drossel 43 entsteht ein Druckverlust zwischen dem im Sackloch 42 vorhandenen Kraftstoff und der Kammer 38. Bei Überschreiten eines definierten Drosseldurchflusses bewegt sich der Kolben 39 gegen die Federkraft in Richtung des unteren Dichtsitzes 44 und beendet damit die Einspritzung.The flow restrictor member 26 has an inlet 36 and an outlet 37. In a chamber 38 a displaceably guided in the axial direction piston 39 is arranged, which is pressed by means of the compression spring 40 against the retaining ring 41. The piston 39 has a blind hole 42, which communicates on the one hand with the inlet 36 and on the other hand via a throttle bore 43 with the outlet 37. In operation, the amount of injection is removed from the chamber 38. As a result, the piston 39 moves against the spring force in the direction of the lower sealing seat 44, without, however, reaching it. During the non-injection time, the compression spring 40 pushes the piston 39 back to the starting position. The chamber 38 is in this case filled via the throttle 43 again. If the injection amount exceeds a defined maximum value, the piston 39 moves so far that the sealing seat 44 is reached and the injection is terminated. By the throttle 43 creates a pressure loss between the present in the blind hole 42 fuel and the chamber 38. When a defined throttle flow is exceeded, the piston 39 moves against the spring force in the direction of the lower sealing seat 44 and thus ends the injection.

Bei der Ausbildung gemäß Fig. 2 ist eine einzige Hochdruckleitung 8 vorgesehen, die sich durch den Haltekörper 5 erstreckt. Der den Durchflussbegrenzer 26 passierende Kraftstoff gelangt über einen Bohrungsabschnitt 48 unmittelbar in die Hochdruckleitung 8.In the training according to Fig. 2 a single high-pressure line 8 is provided which extends through the holding body 5. The fuel passing through the flow restrictor 26 passes directly into the high-pressure line 8 via a bore section 48.

Bei der Ausbildung gemäß Fig. 3 ist im Haltekörper 5 parallel zur Hochdruckleitung 8 eine weitere Hochdruckleitung 20 angeordnet, die als Resonatorleitung ausgebildet ist und über eine Resonatordrossel 21 mit der Kraftstoffversorgung in Verbindung steht. Die beiden Hochdruckleitungen 8 und 20 werden durch eine im
Durchflussbegrenzerbauteil 26 ausgebildete Bohrungsverschneidung 45 mit Kraftstoff versorgt.In the training according to Fig. 3 is in the holding body 5 parallel to the high-pressure line 8, a further high-pressure line 20 is arranged, which is designed as a resonator and communicates with the fuel supply via a resonator throttle 21. The two high-pressure lines 8 and 20 are by a in the
Flow restrictor 26 trained Bohrungsverschneidung 45 fueled.

Bei der Ausbildung gemäß Fig. 4 ist dargestellt, dass die Abdichtung des Durchflussbegrenzerbauteils 26 zum Haltekörper 5 bei Topfeed-Injektoren auch über eine Kegeldichtung 46 erfolgen kann. In diesem Fall können die Stifte 34 für die Verdrehsicherung entfallen. Die die Kegeldichtung 46 ausbildenden kegeligen Dichtflächen begrenzen hierbei einen Hohlraum 47, in den einerseits der Auslass 37 und andererseits die Hochdruckleitungen 8 und 20 münden.In the training according to Fig. 4 It is shown that the sealing of the flow restrictor 26 to the holding body 5 can also be done via a cone seal 46 in topfeed injectors. In this case, the pins 34 can be omitted for the rotation. The conical sealing surfaces forming the conical seal 46 in this case delimit a hollow space 47 into which, on the one hand, the outlet 37 and, on the other hand, the high-pressure lines 8 and 20 open.

Bei der Ausbildung gemäß Fig. 5 handelt es sich um einen Sidefeed-Injektor, bei welchem der Kraftstoff über die Zulaufbohrung 24 vom Haltekörper 5 über das Durchflussbegrenzerbauteil 26 in den Hochdruckspeicher 6 geführt wird. Die Zulaufbohrung 24 mündet hierbei über eine Speicherdrossel 49 in den Hochdruckspeicher 6.In the training according to Fig. 5 it is a sidefeed injector, in which the fuel is fed via the inlet bore 24 from the holding body 5 via the flow restrictor 26 into the high-pressure accumulator 6. The inlet bore 24 opens in this case via a storage throttle 49 in the high-pressure accumulator. 6

Claims (15)

  1. Injector of a modular common-rail fuel injection system, having a high-pressure accumulator integrated in the injector body, wherein the injector has an injection nozzle with a nozzle needle (15) which is guided axially displaceably therein and which is surrounded by a nozzle chamber (19), the injector has a high-pressure line (8) which connects the high-pressure accumulator (6) to the nozzle chamber, and the injector has a holding body (5) which is screwed at a face side to the component, in particular accumulator pipe (25), which forms the high-pressure accumulator, through which holding body the high-pressure line runs, wherein, downstream of the high-pressure accumulator in terms of flow, there is arranged a throughflow limiter (26) for limiting the fuel quantity delivered from the high-pressure accumulator to the injection nozzle, characterized in that the throughflow limiter (26) is formed as a separate component which is placed between the holding body (5) and the accumulator pipe (25) and which is fixed by way of the screw connection of holding body (5) and accumulator pipe (25), wherein the throughflow limiter component (26) comprises a housing with a high-pressure-accumulator-side housing inlet (36) and a holding-body-side housing outlet (37) and has a closing element (39) which is longitudinally displaceable in a chamber (38) of the housing between an initial position and an end position and which is spring-preloaded counter to the flow direction.
  2. Injector according to Claim 1, characterized in that the holding body (5) and the throughflow limiter component (26) are secured against relative rotation by way of an axial pin (34).
  3. Injector according to Claim 1 or 2, characterized in that the throughflow limiter component (26) has a shoulder with a conical first sealing surface (29) which interacts with a conical sealing surface formed on a shoulder (30) of the accumulator pipe (25).
  4. Injector according to Claim 1, 2 or 3, characterized in that the throughflow limiter component (26) has, on the face side facing toward the holding body (5), a conical second sealing surface which interacts with a conical sealing surface formed on a face side of the holding body (5).
  5. Injector according to Claim 4, characterized in that the conical second sealing surface of the throughflow limiter component (26) delimits a cavity (47) formed between holding body (5) and throughflow limiter component (26).
  6. Injector according to one of Claims 1 to 5, characterized in that a further high-pressure line (20) connected in parallel with the high-pressure line (8) runs through the holding body (5), which further high-pressure line is connected at one side to the nozzle chamber (19) and at the other side to the high-pressure accumulator (6).
  7. Injector according to Claim 6, characterized in that the further high-pressure line (20) is in the form of a resonator line which is connected via a resonator throttle (21) to the high-pressure accumulator (6).
  8. Injector according to Claim 6 or 7, characterized in that the high-pressure line (8) and the further high-pressure line (20) open into the cavity (47).
  9. Injector according to Claim 6 or 7, characterized in that the high-pressure line (8) and the further high-pressure line (20) are connected to the throughflow limiter via a bore intersection (45) formed in the throughflow limiter component (26).
  10. Injector according to Claim 9, characterized in that the outlet (37) opens into the bore intersection (45).
  11. Injector according to one of Claims 1 to 10, characterized in that the injector (1) has a lateral port (23) for the fuel supply, which port is connected to a feed bore (24) whose first section is formed in the holding body (5) and whose second section extends axially through the throughflow limiter component (26).
  12. Injector according to one of Claims 1 to 11, characterized in that the throughflow limiter component (26) has, on the face side facing toward the holding body (5), a planar second sealing surface (35) which interacts with the planar face side of the holding body (5).
  13. Injector according to one of Claims 1 to 12, characterized in that the closing element (39) hydraulically connects the housing inlet (36) and the housing outlet (37) to one another via at least one duct which has a throttle (43), and said closing element furthermore controls a flow connection between the housing inlet (36) and the housing outlet (37).
  14. Injector according to Claim 12, characterized in that a securing ring (41) which is fixed in the throughflow limiter component (26) defines the initial position of the closing element (39).
  15. Injector according to Claim 13 or 14, characterized in that the throughflow limiter component (26) has a first, inlet-side axial section (27) and a second, outlet-side axial section (28), wherein the second section (28) has a larger diameter than the first section (27).
EP13715200.5A 2012-04-10 2013-04-08 Injector of a modular common-rail fuel injection system with throughflow limiter Active EP2836696B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ATA424/2012A AT512277B1 (en) 2012-04-10 2012-04-10 Injector of a modular common rail fuel injection system with flow restrictor
PCT/EP2013/057268 WO2013153010A1 (en) 2012-04-10 2013-04-08 Injector of a modular common-rail fuel injection system with throughflow limiter

Publications (2)

Publication Number Publication Date
EP2836696A1 EP2836696A1 (en) 2015-02-18
EP2836696B1 true EP2836696B1 (en) 2016-10-19

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Application Number Title Priority Date Filing Date
EP13715200.5A Active EP2836696B1 (en) 2012-04-10 2013-04-08 Injector of a modular common-rail fuel injection system with throughflow limiter

Country Status (5)

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EP (1) EP2836696B1 (en)
JP (1) JP5936764B2 (en)
KR (1) KR102049218B1 (en)
AT (1) AT512277B1 (en)
WO (1) WO2013153010A1 (en)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013013234A1 (en) * 2013-08-08 2015-02-12 Man Diesel & Turbo Se Injector for a fuel supply system of an internal combustion engine and fuel supply system
CN112761837A (en) * 2021-01-25 2021-05-07 哈尔滨工程大学 Modular supercharged variable-oil-injection ultrahigh-pressure diesel engine common-rail fuel system
CN114151248B (en) * 2021-11-19 2023-10-13 哈尔滨工程大学 Liquid ammonia direct cooling-diesel oil dual-fuel integrated hybrid power system

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19860476A1 (en) 1998-12-28 2000-07-06 Bosch Gmbh Robert Fuel injection system
DE10210282A1 (en) 2002-03-08 2003-09-25 Bosch Gmbh Robert Device for injecting fuel into stationary internal combustion engines
GB0508665D0 (en) * 2005-04-28 2005-06-08 Man B & W Diesel Ltd Fuel injector
DE102005056133A1 (en) 2005-11-23 2007-05-24 L'orange Gmbh Injector for combustion engine, has actuator and control chamber whereby pressure reservoir is arranged between control valve and nozzle body
DE102007025050B3 (en) 2007-05-29 2008-10-16 L'orange Gmbh High-pressure injection injector for internal combustion engines with a kinkload-increasing control rod support over high-pressure fuel
WO2009033304A1 (en) * 2007-09-13 2009-03-19 Ganser-Hydromag Ag Fuel injection device

Also Published As

Publication number Publication date
AT512277B1 (en) 2013-07-15
JP5936764B2 (en) 2016-06-22
JP2015512493A (en) 2015-04-27
KR20140147100A (en) 2014-12-29
KR102049218B1 (en) 2020-01-08
EP2836696A1 (en) 2015-02-18
AT512277A4 (en) 2013-07-15
WO2013153010A1 (en) 2013-10-17

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