EP2635794A1 - Device for injecting fuel into the combustion chamber of an internal combustion engine - Google Patents

Device for injecting fuel into the combustion chamber of an internal combustion engine

Info

Publication number
EP2635794A1
EP2635794A1 EP11785565.0A EP11785565A EP2635794A1 EP 2635794 A1 EP2635794 A1 EP 2635794A1 EP 11785565 A EP11785565 A EP 11785565A EP 2635794 A1 EP2635794 A1 EP 2635794A1
Authority
EP
European Patent Office
Prior art keywords
resonator
pressure
holding body
pressure accumulator
line
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP11785565.0A
Other languages
German (de)
French (fr)
Other versions
EP2635794B1 (en
Inventor
Christian Graspeuntner
Gerhard Unterberger
Franz Guggenbichler
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2635794A1 publication Critical patent/EP2635794A1/en
Application granted granted Critical
Publication of EP2635794B1 publication Critical patent/EP2635794B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B17/00—Engines characterised by means for effecting stratification of charge in cylinders
    • F02B17/005—Engines characterised by means for effecting stratification of charge in cylinders having direct injection in the combustion chamber
    • 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
    • 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/14—Arrangements of injectors with respect to engines; Mounting of injectors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/168—Assembling; Disassembling; Manufacturing; Adjusting
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/31—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements
    • 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

Definitions

  • the invention relates to a device for injecting fuel into the combustion chamber of an internal combustion engine having at least one injector comprising an injector body which is equipped with a high-pressure accumulator, an axially displaceable guided in the injector nozzle needle, which is surrounded by a nozzle chamber, a high-pressure accumulator with the nozzle chamber connecting high-pressure line and a parallel to the high-pressure line connected resonator, which communicates with the nozzle chamber in communication and opens via a resonator in the high-pressure accumulator.
  • electronically controlled injection injectors are used to inject the fuel into the engine combustion chamber.
  • the servo valves used in these injectors cause the injection nozzle to close very quickly, so that the inertia of the fuel in the subsequent high-pressure bores causes strong pressure pulsations on the nozzle seat, which lead to severe wear here.
  • the resulting pressure peaks are in unfavorable cases by up to 500 bar above the rail pressure.
  • these pressure oscillations lead to strong fluctuations in the injection rate in the case of injection sequences that follow one another rapidly. If, for example, a pressure oscillation at the nozzle seat is induced by a pre-injection, then with a constant opening time of the nozzle needle for the second, subsequent injection, the injected quantity depends on whether the second injection occurred earlier in a maximum or in a minimum of the pressure oscillation.
  • One possible Low pressure oscillation at the injector in all operating states of the hydraulic system is therefore desirable.
  • EP 1 217 202 A1 it is known from EP 1 217 202 A1 to arrange a check valve and a dissipation element in a parallel circuit in a high-pressure reservoir (common rail) starting from a high-pressure bore which leads to an injector, as a result of which pressure oscillations cease more rapidly can be.
  • a cross section of the injection line reducing throttle known.
  • WO 2007/143768 AI can be found in a training, in which a parallel to the high-pressure line between the injector and high-pressure accumulator switched resonator is provided, the high-pressure accumulator side has a resonator.
  • the resonator throttle is preferably arranged at the inlet of the resonator line into the high-pressure accumulator.
  • the problem here is that in the transition region of the resonator choke voltages occur, which micro-movements are observed in a pressed into the body of the high-pressure accumulator rod-shaped resonator, so such a design of the resonator as pressed-rod resonator due to these micro-movements and beyond due to the limited Einpress concept is no longer applicable for system pressures of greater than 1800 bar.
  • the invention therefore aims to ensure a safe and stable arrangement of the resonator even at system pressures of greater than 1800 bar and to reduce the stresses in the transition region of the resonator or the high-pressure bore.
  • the invention essentially provides that the resonator line and the high-pressure line are formed at least in their section adjacent to the high-pressure accumulator in a holding body which is screwed into the storage tube forming the high-pressure accumulator ,
  • the holding body thus has both the high-pressure bore and the parallel arranged Re- sonatorbohrung of the resonator, wherein the fact that the holding body is screwed into the front side forming the high-pressure accumulator storage tube, leads to an immediate connection between the high-pressure accumulator and the holes of the resonator is made and due to the screw a very stable and for high system pressures suitable connection is achieved.
  • a preferred embodiment in this context provides that the holding body has a conical seat on the front side, with a conical seat on the storage tube to seal the connection between the holding body and storage tube cooperates.
  • a conical seat leads both to an effective seal and to a stabilization of the resonator throttle having the holding body, so that micro-movements are suppressed even at high system pressures.
  • the cone angle of the conical seat surface of the holding body is smaller than the cone angle of the conical seat of the storage tube, a circular contact between the storage tube and the holding body is achieved in the region of the conical seat, along this contact line a concentration of forces introduced into the respective contact partners takes place, and under certain circumstances, the edge of the storage tube can also be pressed into the conical seat surface of the holding body, which leads to a further stabilization.
  • the holding body has on the screwed into the storage tube end face surrounding the mouth of the resonator and the mouth of the high-pressure line annular recess.
  • the fluid pressure prevailing in the high-pressure accumulator can be utilized in order to introduce forces acting in the direction of the transition region into the holding body.
  • the forces acting on the holding body in the direction of the transition region from the outside in this case act as counter forces to the forces occurring in the resonator line in the transition region, so that overall a stabilizing effect is achieved and unwanted local stress states are avoided.
  • An improved effect is achieved in this context according to a preferred embodiment, when the annular recess is surrounded by an annular projection on the end face of the holding body having an end face against which the mouth of the resonator is set back in the axial direction.
  • the diameter of the holding ⁇ body corresponds to at least four times, preferably at least eight times the diameter of the resonator.
  • FIG. 2 shows a detail view in the region of the holding body and of the high-pressure accumulator
  • FIG. 3 shows a detailed view of the connecting region between resonator line and high-pressure accumulator.
  • an injector 1 is shown, which has 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 Tüsenspannmut- ter 7 the nozzle 2, the throttle plate. 3 and the valve plate 4 holds together.
  • the solenoid valve 13 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 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.
  • inlet throttle 10 and outlet throttle 12 set itself by the flow cross sections of inlet throttle 10 and outlet throttle 12 defined equilibrium pressure in the control chamber 11, which is so low that the voltage applied in the nozzle chamber 19 system pressure is able to open the nozzle body longitudinally displaceable guided nozzle needle 15 so that the spray holes 17 ' released and an injection takes place.
  • a resonator is used. This consists of a resonator 20, which has the same length and the same diameter as the high-pressure line 8, and a resonator 21, which is attached to the memory-side end of the resonator 20 and connects them to the memory 6.
  • the solenoid valve 13 When closing the solenoid valve 13, the pressure pulse generated at the nozzle seat 16 is propagated via the nozzle chamber 19 into the high-pressure line 8 and the resonator line 20.
  • the cone angle of the conical seat 23 of the holding body 5 is smaller than the cone angle of the tapered seat 24 of the storage tube 22, wherein the tapered seat 23 of the holding body 5 from the inner wall 26 of the storage tube 22 in the interior of the high - accumulator 6 protrudes.
  • the holding body 5 has an annular recess 27 surrounding the mouth of the resonator line 20 and the mouth of the high-pressure line 8 on the end face screwed into the storage tube 22.
  • the annular recess 27 is surrounded by an annular projection 28 on the end face of the holding body 5, which has an end face 29 against which the mouth of the resonator 20 and the resonator 21 is set back in the axial direction.

Landscapes

  • 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)
  • Manufacturing & Machinery (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

The invention relates to a device for injecting fuel into the combustion chamber of an internal combustion engine with at least one injector (1) comprising an injector body that is equipped with a high-pressure accumulator (6), a nozzle needle (15) which is guided in the injector (1) in an axially movable manner and which is surrounded by a nozzle chamber (19), a high-pressure line (8) that connects the high-pressure accumulator (6) to the nozzle chamber (19), and a resonator line (20) which is connected parallel to the high-pressure line (8) and which is connected to the nozzle chamber (19) and opens into the high-pressure accumulator (6) via a resonator throttle (21). The resonator line (20) and the high-pressure line (8) are formed in a retaining body (5) at least in the line section adjoining the high-pressure accumulator (6), said retaining body being screwed into the accumulator pipe (22) that forms the high-pressure accumulator (6) at the retaining body end face.

Description

Vorrichtung zum Einspritzen von Kraftstoff in den Brennraum einer Brennkraftmaschine Device for injecting fuel into the combustion chamber of an internal combustion engine

Die Erfindung betrifft eine Vorrichtung zum Einspritzen von Kraftstoff in den Brennraum einer Brennkraftmaschine mit wenigstens einem Injektor umfassend einen Injektorkörper, der mit einem Hochdruckspeicher ausgestattet ist, eine axial verschieblich im Injektor geführte Düsennadel, die von einem Düsenraum umgeben ist, eine den Hochdruckspeicher mit dem Düsenraum verbindende Hochdruckleitung und eine parallel zur Hochdruckleitung geschaltene Resonatorleitung, die mit dem Düsenraum in Verbindung steht und über eine Resonatordrossel in den Hochdruckspeicher mündet. In einem Common-Rail-System werden elektronisch gesteuerte Einspritzinjektoren zum Einspritzen des Kraftstoffs in den Motorbrennraum verwendet. Die in diesen Injektoren verwendeten Servoventile bewirken ein sehr schnelles Schließen der Einspritzdüse, sodass durch die Trägheit des Kraftstoffs in den anschließenden Hochdruckbohrungen starke Druckpulsationen am Düsensitz entstehen, die hier zu starkem Verschleiß führen. Die dabei auftretenden Druckspitzen liegen in ungünstigen Fällen um bis zu 500 bar über dem Raildruck. Diese Druckschwingungen führen bei schnell aufeinander folgenden Einspritzvorgängen überdies zu starken Schwankungen der Einspritzrate. Wird zum Beispiel durch eine Voreinspritzung eine Druckschwingung am Düsensitz induziert, so ist bei konstanter Öffnungszeit der Düsennadel für die zweite, nach- folgende Einspritzung die eingespritzte Menge davon abhängig, ob die zweite Einspritzung eher in einem Maximum oder in einem Minimum der Druckschwingung erfolgt ist. Eine möglichst geringe Druckschwingung am Injektor in allen Betriebszustän- den des hydraulischen Systems ist daher erstrebenswert. The invention relates to a device for injecting fuel into the combustion chamber of an internal combustion engine having at least one injector comprising an injector body which is equipped with a high-pressure accumulator, an axially displaceable guided in the injector nozzle needle, which is surrounded by a nozzle chamber, a high-pressure accumulator with the nozzle chamber connecting high-pressure line and a parallel to the high-pressure line connected resonator, which communicates with the nozzle chamber in communication and opens via a resonator in the high-pressure accumulator. In a common rail system, electronically controlled injection injectors are used to inject the fuel into the engine combustion chamber. The servo valves used in these injectors cause the injection nozzle to close very quickly, so that the inertia of the fuel in the subsequent high-pressure bores causes strong pressure pulsations on the nozzle seat, which lead to severe wear here. The resulting pressure peaks are in unfavorable cases by up to 500 bar above the rail pressure. Moreover, these pressure oscillations lead to strong fluctuations in the injection rate in the case of injection sequences that follow one another rapidly. If, for example, a pressure oscillation at the nozzle seat is induced by a pre-injection, then with a constant opening time of the nozzle needle for the second, subsequent injection, the injected quantity depends on whether the second injection occurred earlier in a maximum or in a minimum of the pressure oscillation. One possible Low pressure oscillation at the injector in all operating states of the hydraulic system is therefore desirable.

In der Patentliteratur werden zahlreiche Maßnahmen zur Ver- meidung von Druckschwingungen in hydraulischen Systemen beschrieben. Meist handelt es sich um Dämpfungsvolumina, Drosselanordnungen, Ventilanordnungen oder Kombinationen der genannten Maßnahmen. Am gängigsten sind Drosselanordnungen, die zur Dissipation der Strömungsenergie in statische Druckener- gie beitragen sollen. The patent literature describes numerous measures for avoiding pressure oscillations in hydraulic systems. These are usually damping volumes, throttle arrangements, valve arrangements or combinations of the measures mentioned. The most common are throttle arrangements, which should contribute to the dissipation of the flow energy into static pressure energy.

So ist es beispielsweise aus der EP 1 217 202 AI bekannt, in einer von einem Hochdruckspeicher (Common-Rail ) ausgehenden Hochdruckbohrung, welche zu einem Injektor führt, in einer Parallelschaltung ein Rückschlagventil sowie ein Dissipa- tionselement anzuordnen, wodurch Druckschwingungen rascher zum Abklingen gebracht werden können. For example, it is known from EP 1 217 202 A1 to arrange a check valve and a dissipation element in a parallel circuit in a high-pressure reservoir (common rail) starting from a high-pressure bore which leads to an injector, as a result of which pressure oscillations cease more rapidly can be.

Zur Minimierung von Druckpulsationen in einer Kraftstoffein- spritzleitung, welche von einer Hochdruckleitung gespeist wird, ist gemäß DE 160 785 AI an der Anschlussstelle zur Hochdruckleitung eine den Querschnitt der Einspritzleitung verringernden Drossel bekannt. Der WO 2007/143768 AI lässt sich eine Ausbildung entnehmen, bei welcher eine parallel zur Hochdruckleitung zwischen Injektor und Hochruckspeicher geschaltene Resonatorleitung vorgesehen ist, die hochdruckspeicherseitig eine Resonatordrossel aufweist. Bevorzugt ist die Resonatordrossel am Eintritt der Resonatorleitung in den Hochdruckspeicher angeordnet. In order to minimize pressure pulsations in a Kraftstoffein- injection line, which is fed by a high pressure line, according to DE 160 785 AI at the junction to the high pressure line, a cross section of the injection line reducing throttle known. WO 2007/143768 AI can be found in a training, in which a parallel to the high-pressure line between the injector and high-pressure accumulator switched resonator is provided, the high-pressure accumulator side has a resonator. The resonator throttle is preferably arranged at the inlet of the resonator line into the high-pressure accumulator.

Die aus der WO 2007/143768 AI bekannte Ausbildung sieht somit vor, dass die Hochdruckleitung in zwei voneinander unabhängi- ge Bereiche geteilt wird, von denen einer mit einer Drossel ausgestattet ist, sodass die Druckschwingungen, die am Düsensitz entstehen, in beiden Bereichen unterschiedlich reflektiert werden und sich die reflektierten Schwingungen aufgrund ihres Phasenversatzes nahezu auslöschen. Dabei wird die Funktion des hydraulischen Systems exakt wie jene ohne Drossel abgebildet, da nur die Leitungsschwingungen ausgelöscht werden . Problematisch ist hierbei jedoch, dass im Übergangsbereich der Resonatordrossel Spannungen auftreten, wobei bei einem in den Körper des Hochdruckspeichers eingepressten stabförmigen Resonatorelement Mikrobewegungen zu beobachten sind, sodass eine derartige Ausbildung des Resonatorkörpers als einge- presster Stabresonator aufgrund dieser Mikrobewegungen und darüber hinaus aufgrund der beschränkten Einpresskräfte für Systemdrücke von als größer als 1800 bar nicht mehr einsetzbar ist. Die Erfindung zielt daher darauf ab, auch bei Systemdrücken von größer 1800 bar eine sichere und stabile Anordnung des Resonatorelements sicherzustellen und die Spannungen im Übergangsbereich der Resonatordrossel bzw. der Hochdruckbohrung zu verringern. The known from WO 2007/143768 AI training thus provides that the high-pressure line in two independent from each other one of which is equipped with a throttle, so that the pressure oscillations that occur at the nozzle seat are reflected differently in both areas and the reflected oscillations due to their phase offset are almost extinguished. The function of the hydraulic system is reproduced exactly like those without a throttle, since only the line vibrations are extinguished. However, the problem here is that in the transition region of the resonator choke voltages occur, which micro-movements are observed in a pressed into the body of the high-pressure accumulator rod-shaped resonator, so such a design of the resonator as pressed-rod resonator due to these micro-movements and beyond due to the limited Einpresskräfte is no longer applicable for system pressures of greater than 1800 bar. The invention therefore aims to ensure a safe and stable arrangement of the resonator even at system pressures of greater than 1800 bar and to reduce the stresses in the transition region of the resonator or the high-pressure bore.

Zur Lösung dieser Aufgabe sieht die Erfindung ausgehend von einer Vorrichtung der eingangs genannten Art im Wesentlichen vor, dass die Resonatorleitung und die Hochdruckleitung zumindest in ihrem dem Hochdruckspeicher benachbarten Ab- schnitt in einem Haltekörper ausgebildet sind, der stirnseitig in das den Hochdruckspeicher bildende Speicherrohr eingeschraubt ist. Der Haltekörper weist somit sowohl die Hochdruckbohrung als auch die parallel dazu angeordnete Re- sonatorbohrung des Resonatorelements auf, wobei der Umstand, dass der Haltekörper stirnseitig in das den Hochdruckspeicher bildende Speicherrohr eingeschraubt ist, dazu führt, dass eine unmittelbare Verbindung zwischen dem Hochdruck- Speicher und den Bohrungen des Resonatorelements hergestellt wird und aufgrund der Schraubverbindung eine überaus stabile und für hohe Systemdrücke geeignete Verbindung erzielt wird. Die Schraubverbindung erlaubt es hierbei in einfacher Weise, ausreichende Anpresskräfte im Bereich eines Kegelsitzes auf- zubringen, wobei eine bevorzugte Ausbildung in diesem Zusammenhang vorsieht, dass der Haltekörper stirnseitig eine kegelige Sitzfläche aufweist, die mit einer kegeligen Sitzfläche am Speicherrohr zur Abdichtung der Verbindung zwischen Haltekörper und Speicherrohr zusammenwirkt. Ein derartiger Kegelsitz führt sowohl zu einer wirksamen Abdichtung als auch zu einer Stabilisierung des die Resonatordrossel aufweisenden Haltekörpers, sodass Mikrobewegungen auch bei hohen Systemdrücken unterbunden werden. Wenn, wie dies einer weiteren bevorzugten Ausbildung entspricht, der Kegelwinkel der kegeligen Sitzfläche des Haltekörpers kleiner ist als der Kegelwinkel der kegeligen Sitzfläche des Speicherrohrs, wird im Bereich des Kegelsitzes eine kreislinienförmige Kon- taktierung zwischen dem Speicherrohr und dem Haltekörper erreicht, wobei entlang dieser Berührungslinie eine Konzent- rierung von in die jeweiligen Kontaktpartner eingebrachten Kräften erfolgt, wobei es in diesem Bereich unter Umständen auch zu einem Eindrücken der Kante des Speicherrohrs in die kegelförmige Sitzfläche des Haltekörpers kommen kann, was zu einer weiteren Stabilisierung führt. To achieve this object, starting from a device of the aforementioned type, the invention essentially provides that the resonator line and the high-pressure line are formed at least in their section adjacent to the high-pressure accumulator in a holding body which is screwed into the storage tube forming the high-pressure accumulator , The holding body thus has both the high-pressure bore and the parallel arranged Re- sonatorbohrung of the resonator, wherein the fact that the holding body is screwed into the front side forming the high-pressure accumulator storage tube, leads to an immediate connection between the high-pressure accumulator and the holes of the resonator is made and due to the screw a very stable and for high system pressures suitable connection is achieved. The screw connection allows this in a simple manner to muster sufficient contact forces in the region of a conical seat, a preferred embodiment in this context provides that the holding body has a conical seat on the front side, with a conical seat on the storage tube to seal the connection between the holding body and storage tube cooperates. Such a conical seat leads both to an effective seal and to a stabilization of the resonator throttle having the holding body, so that micro-movements are suppressed even at high system pressures. If, as corresponds to a further preferred embodiment, the cone angle of the conical seat surface of the holding body is smaller than the cone angle of the conical seat of the storage tube, a circular contact between the storage tube and the holding body is achieved in the region of the conical seat, along this contact line a concentration of forces introduced into the respective contact partners takes place, and under certain circumstances, the edge of the storage tube can also be pressed into the conical seat surface of the holding body, which leads to a further stabilization.

Um im Übergangsbereich zwischen Resonatordrossel und Resonatorleitung das Auftreten von Spannungen zu minimieren, ist gemäß einer bevorzugten Weiterbildung vorgesehen, dass 4 In order to minimize the occurrence of stresses in the transition region between the resonator throttle and the resonator line, it is provided according to a preferred development that 4

- 5 - der Haltekörper an der in das Speicherrohr eingeschraubten Stirnseite eine die Mündung der Resonatorleitung und die Mündung der Hochdruckleitung umgebende ringförmige Vertiefung aufweist. Im Bereich einer derartigen ringförmigen Ver- tiefung kann der im Hochdruckspeicher herrschende Fluiddruck ausgenützt werden, um in Richtung des genannten Übergangsbereichs wirkende Kräfte in den Haltekörper einzuleiten. Die in Richtung des Übergangsbereichs von außen auf den Haltekörper einwirkenden Kräfte gelangen hierbei als Gegenkräfte zu den im genannten Übergangsbereich in der Resonatorleitung auftretenden Kräfte zur Wirkung, sodass insgesamt ein stabilisierender Effekt erreicht wird und unerwünschte lokale Spannungszustände vermieden werden. Eine verbesserte Wirkung wird in diesem Zusammenhang gemäß einer bevorzugten Weiterbildung erreicht, wenn die ringförmige Vertiefung von einem ringförmigen Vorsprung an der Stirnseite des Haltekörpers umgeben ist, der eine Stirnfläche aufweist, gegenüber der die Mündung der Resonatorleitung in axialer Richtung zurückversetzt angeordnet ist.  - 5 - the holding body has on the screwed into the storage tube end face surrounding the mouth of the resonator and the mouth of the high-pressure line annular recess. In the area of such an annular recess, the fluid pressure prevailing in the high-pressure accumulator can be utilized in order to introduce forces acting in the direction of the transition region into the holding body. The forces acting on the holding body in the direction of the transition region from the outside in this case act as counter forces to the forces occurring in the resonator line in the transition region, so that overall a stabilizing effect is achieved and unwanted local stress states are avoided. An improved effect is achieved in this context according to a preferred embodiment, when the annular recess is surrounded by an annular projection on the end face of the holding body having an end face against which the mouth of the resonator is set back in the axial direction.

Mit Vorteil ist vorgesehen, dass der Durchmesser des Halte¬ körpers mindestens dem vierfachen, bevorzugt mindestens dem achtfachen des Durchmessers der Resonatorleitung entspricht. It is advantageously provided that the diameter of the holding ¬ body corresponds to at least four times, preferably at least eight times the diameter of the resonator.

Die Erfindung wird nachfolgend anhand eines in der Zeichnung schematisch dargestellten Ausführungsbeispiels näher erläutert. In dieser zeigen Fig.l schematisch einen Querschnitt eines mit einem Hochdruckspeicher ausgestatteten Injektors, Fig.2 eine Detailansicht im Bereich des Haltekörpers und des Hochdruckspeichers und Fig.3 eine Detailansicht des Verbindungsbereichs zwischen Resonatorleitung und Hochdruckspeicher . In Fig. 1 ist ein Injektor 1 dargestellt, der eine Einspritzdüse 2, eine Drosselplatte 3, eine Ventilplatte 4, einen Haltekörper 5 und einen Hochdruckspeicher 6 aufweist, wobei eine mit dem Haltekörper 5 verschraubte Düsenspannmut- ter 7 die Düse 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 Düse 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 Düsen- nadelsitz 16, sodass die Spritzlöcher 17 verschlossen sind. Wird das Magnetventil 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. The invention will be explained in more detail with reference to an embodiment schematically illustrated in the drawing. 2 shows a detail view in the region of the holding body and of the high-pressure accumulator, and FIG. 3 shows a detailed view of the connecting region between resonator line and high-pressure accumulator. In Fig. 1, an injector 1 is shown, which has 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 Tüsenspannmut- ter 7 the 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 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 system pressure applied in the control chamber 11, together with the force of the nozzle spring 14, presses the nozzle needle 15 into the nozzle needle seat 16 so that the spray holes 17 are closed. If 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. It sets itself by the flow cross sections of inlet throttle 10 and outlet throttle 12 defined equilibrium pressure in the control chamber 11, which is so low that the voltage applied in the nozzle chamber 19 system pressure is able to open the nozzle body longitudinally displaceable guided nozzle needle 15 so that the spray holes 17 ' released and an injection takes place.

Aufgrund der Massenträgheit des Kraftstoffs in Speicher 6, Hochdruckleitung 8 und Düsenraum 19 kommt es direkt nach dem Schließen der Düsennadel 15 zu starken Druckschwingungen am Düsensitz 16, da der fließende Kraftstoff in sehr kurzer Zeit abgebremst werden müss. Zur Reduktion der Druckschwingungen kommt ein Resonator zum Einsatz. Dieser besteht aus einer Resonatorleitung 20, welche die gleiche Länge und den gleichen Durchmesser wie die Hochdruckleitung 8 aufweist, sowie einer Resonatordrossel 21, die am speicherseitigen Ende der Resonatorleitung 20 angebracht ist und diese mit dem Speicher 6 verbindet. Beim Schließen des Magnetventils 13 pflanzt sich der am Düsensitz 16 entstehende Druckpuls über den Düsenraum 19 in die Hochdruckleitung 8 und die Resonatorleitung 20 fort. Am Ende der Hochdruckleitung 8 erfolgt eine Reflexion des Druckpulses am offenen Ende am Übergang in den Speicher 6. Gleichzeitig wird der in der Resonatorleitung 20 laufende Druckpuls am geschlossenen Ende an der Resonatordrossel 21 reflektiert. Die beiden reflektierten .Druckpulse sind aufgrund der unterschiedlichen Reflexionsart (offenes bzw. geschlossenes Ende) um 180° pha- senverschoben, sodass sie sich beim Aufeinandertreffen im Düsenraum 19 auslöschen. Dadurch kommt es zu keinen weiteren Druckpulsen am Düsensitz 16, sodass hier deutlich weniger Verschleiß auftritt. In der Detailansicht gemäß Fig.2 ist ersichtlich, dass der Haltekörper 5 stirnseitig in das den Hochdruckspeicher 6 bildende Speicherrohr 22 eingeschraubt ist. Der Haltekörper 5 weist stirnseitig . eine kegelige Sitzfläche 23 auf, die mit einer kegeligen Sitzfläche 24 am Speicherrohr 22 zur Abdich- tung der Verbindung zwischen Haltekörper 5 und Speicherrohr 22 zusammenwirkt. Eine Ringdichtung 25 sorgt für eine zusätzliche Abdichtung. Due to the inertia of the fuel in memory 6, high-pressure line 8 and nozzle chamber 19, there are strong pressure oscillations on the nozzle seat 16 directly after closing the nozzle needle 15, since the flowing fuel must be braked in a very short time. To reduce the pressure oscillations, a resonator is used. This consists of a resonator 20, which has the same length and the same diameter as the high-pressure line 8, and a resonator 21, which is attached to the memory-side end of the resonator 20 and connects them to the memory 6. When closing the solenoid valve 13, the pressure pulse generated at the nozzle seat 16 is propagated via the nozzle chamber 19 into the high-pressure line 8 and the resonator line 20. At the end of the high pressure line 8, a reflection of the pressure pulse at the open end takes place at the transition into the memory 6. At the same time, the pressure pulse running in the resonator line 20 is reflected at the closed end on the resonator throttle 21. Due to the different reflection modes (open or closed end), the two reflected pressure pulses are phase-shifted by 180 ° so that they cancel each other out when they meet in the nozzle chamber 19. As a result, there are no further pressure pulses on the nozzle seat 16, so that significantly less wear occurs here. In the detail view according to FIG. 2 it can be seen that the holding body 5 is screwed into the storage tube 22 forming the high-pressure accumulator 6 at the front side. The holding body 5 has the front side . a conical seat surface 23 which cooperates with a conical seat surface 24 on the storage tube 22 for sealing the connection between the holding body 5 and the storage tube 22. A ring seal 25 provides an additional seal.

In Fig.3 ist ersichtlich, dass der Kegelwinkel der kegeligen Sitzfläche 23 des Haltekörpers 5 kleiner ist als der Kegelwinkel der kegeligen Sitzfläche 24 des Speicherrohrs 22, wobei die kegelige Sitzfläche 23 des Haltekörpers 5 von der Innenwand 26 des Speicherrohrs 22 in das Innere des Hoch- druckspeichers 6 vorragt. Weiters ist ersichtlich, dass der Haltekörper 5 an der in das Speicherrohr 22 eingeschraubten Stirnseite eine die Mündung der Resonatorleitung 20 und die Mündung der Hochdruckleitung 8 umgebende ringförmige Vertie- fung 27 aufweist. Dabei ist die ringförmige Vertiefung 27 von einem ringförmigen Vorsprung 28 an der Stirnseite des Haltekörpers 5 umgeben, der eine Stirnfläche 29 aufweist, gegenüber der die Mündung der Resonatorleitung 20 bzw. die Resonatordrossel 21 in axialer Richtung zurückversetzt ange- ordnet ist. In Figure 3 it can be seen that the cone angle of the conical seat 23 of the holding body 5 is smaller than the cone angle of the tapered seat 24 of the storage tube 22, wherein the tapered seat 23 of the holding body 5 from the inner wall 26 of the storage tube 22 in the interior of the high - accumulator 6 protrudes. Furthermore, it can be seen that the holding body 5 has an annular recess 27 surrounding the mouth of the resonator line 20 and the mouth of the high-pressure line 8 on the end face screwed into the storage tube 22. In this case, the annular recess 27 is surrounded by an annular projection 28 on the end face of the holding body 5, which has an end face 29 against which the mouth of the resonator 20 and the resonator 21 is set back in the axial direction.

Claims

Patentansprüche : Claims: 1. Vorrichtung zum Einspritzen von Kraftstoff in den Brenn- räum einer Brennkraftmaschine mit wenigstens einem Injektor1. An apparatus for injecting fuel into the combustion chamber of an internal combustion engine having at least one injector (1) umfassend einen Injektorkörper, der mit einem Hochdruckspeicher (6) ausgestattet ist, eine axial verschieblich im Injektor (1) geführte Düsennadel (15) , die von einem Düsenraum (19) umgeben ist, eine den Hochdruckspeicher (6) mit dem Düsenraum (19) verbindende Hochdruckleitung (8) und eine parallel zur Hochdruckleitung (8) geschaltene Resonatorleitung (20), die mit dem Düsenraum (19) in Verbindung steht und über eine Resonatordrossel (21) in den Hochdruckspeicher (6) mündet, dadurch gekennzeichnet, dass die Resonatorlei- tung (20) und die Hochdruckleitung (8) zumindest in ihrem dem Hochdruckspeicher (6) benachbarten Abschnitt in einem Haltekörper (5) ausgebildet sind, der stirnseitig in das den Hochdruckspeicher (6) bildende Speicherrohr (22) eingeschraubt ist. (1) comprising an injector body, which is equipped with a high pressure accumulator (6), an axially displaceable in the injector (1) guided nozzle needle (15), which is surrounded by a nozzle chamber (19), one the high-pressure accumulator (6) with the nozzle chamber (19) connecting the high pressure line (8) and a parallel to the high pressure line (8) switched resonator (20), which communicates with the nozzle chamber (19) and communicates via a resonator (21) in the high-pressure accumulator (6), characterized the resonator line (20) and the high-pressure line (8) are formed, at least in their section adjacent to the high-pressure accumulator (6), in a holding body (5) which is screwed into the storage tube (22) forming the high-pressure accumulator (6). 2. Vorrichtung nach Anspruch 1, dadurch gekennzeichnet, dass der Haltekörper (5) stirnseitig eine kegelige Sitzfläche (23) aufweist, die mit einer kegeligen Sitzfläche (24) am Speicherrohr (22) zur Abdichtung der Verbindung zwischen Haltekörper (5) und Speicherrohr (22) zusammenwirkt. 2. Apparatus according to claim 1, characterized in that the holding body (5) frontally a conical seat surface (23) which with a conical seat surface (24) on the storage tube (22) for sealing the connection between the holding body (5) and storage tube ( 22) cooperates. 3. Vorrichtung nach Anspruch 2, dadurch gekennzeichnet, dass der Kegelwinkel der kegeligen Sitzfläche (23) des Haltekörpers (5) kleiner ist als der Kegelwinkel der kegeligen Sitzfläche (24) des Speicherrohrs (22) . 3. A device according to claim 2, characterized in that the cone angle of the conical seat surface (23) of the holding body (5) is smaller than the cone angle of the conical seat surface (24) of the storage tube (22). 4. Vorrichtung nach Anspruch 2 oder 3, dadurch gekennzeichnet, dass die kegelige Sitzfläche (23) des Haltekörpers (5) von der Innenwand (26) des Speicherrohrs (22) in das Innere des Hochdruckspeichers (6) vorragt. 4. Apparatus according to claim 2 or 3, characterized in that the conical seat surface (23) of the holding body (5) from the inner wall (26) of the storage tube (22) projects into the interior of the high-pressure accumulator (6). 5. Vorrichtung nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, dass der Haltekörper (5) an der in das Speicherrohr (22) eingeschraubten Stirnseite eine die Mündung der Resonatorleitung (20) und die Mündung der Hochdruckleitung (8) umgebende ringförmige Vertiefung (27) aufweist. 5. Device according to one of claims 1 to 4, characterized in that the holding body (5) on the in the storage tube (22) screwed end face a mouth of the resonator (20) and the mouth of the high-pressure line (8) surrounding the annular recess ( 27). 6. Vorrichtung nach Anspruch 5, dadurch gekennzeichnet, dass die ringförmige Vertiefung (27) von einem ringförmigen Vorsprung (28) an der Stirnseite des Haltekörpers (5) umgeben ist., der eine Stirnfläche (29) aufweist, gegenüber der die Mündung der Resonatorleitung (20) in axialer Richtung zurückversetzt angeordnet ist. 6. The device according to claim 5, characterized in that the annular recess (27) by an annular projection (28) on the end face of the holding body (5) is surrounded., Which has an end face (29) opposite to the mouth of the resonator (20) is set back in the axial direction. 7. Vorrichtung nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, dass der Durchmesser des Haltekörpers (5) mindestens dem vierfachen, bevorzugt mindestens dem achtfa- chen des Durchmessers der Resonatorleitung (20) entspricht. 7. Device according to one of claims 1 to 6, characterized in that the diameter of the holding body (5) at least four times, preferably at least eight times the diameter of the resonator (20) corresponds.
EP20110785565 2010-11-02 2011-11-02 Device for injecting fuel into the combustion chamber of an internal combustion engine Active EP2635794B1 (en)

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AT0180910A AT509877B1 (en) 2010-11-02 2010-11-02 DEVICE FOR INJECTING FUEL IN THE COMBUSTION ENGINE OF AN INTERNAL COMBUSTION ENGINE
PCT/AT2011/000444 WO2012058703A1 (en) 2010-11-02 2011-11-02 Device for injecting fuel into the combustion chamber of an internal combustion engine

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Families Citing this family (29)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT512437B1 (en) * 2012-01-26 2014-03-15 Bosch Gmbh Robert DEVICE FOR INJECTING FUEL IN THE COMBUSTION ENGINE OF AN INTERNAL COMBUSTION ENGINE
AT512439B1 (en) * 2012-01-26 2013-12-15 Bosch Gmbh Robert DEVICE FOR INJECTING FUEL IN THE COMBUSTION ENGINE OF AN INTERNAL COMBUSTION ENGINE
AT512297B1 (en) * 2012-02-07 2013-07-15 Bosch Gmbh Robert THREAD CONNECTION OF HIGH-PRESSURE MEDIUM LEADING COMPONENTS OF AN INJECTION DEVICE FOR INTERNAL COMBUSTION ENGINES
AT511801B1 (en) * 2012-02-07 2013-03-15 Bosch Gmbh Robert METHOD FOR INFLUENCING THE THREADED GEOMETRY OF AN INTERNAL THREAD FOR INTERNAL COMBUSTION ENGINES
DE102012204659A1 (en) * 2012-03-22 2013-09-26 Man Diesel & Turbo Se Injector for a fuel supply system of an internal combustion engine and fuel supply system
DE102012208075A1 (en) * 2012-05-15 2013-11-21 Man Diesel & Turbo Se Injector for a fuel supply system of an internal combustion engine and fuel supply system
AT512960B1 (en) * 2012-05-22 2014-03-15 Bosch Gmbh Robert Injector of a modular common rail fuel injection system
AT513321A1 (en) * 2012-08-16 2014-03-15 Bosch Gmbh Robert Threaded connection for connecting components with high pressure medium
AT515933B1 (en) 2015-01-02 2016-01-15 Ge Jenbacher Gmbh & Co Og fuel injector
CN106762283A (en) * 2017-01-18 2017-05-31 哈尔滨工程大学 A kind of two-way oil-feed resonant mode electric-controlled fuel injector with ditch
CN106704064A (en) * 2017-01-18 2017-05-24 哈尔滨工程大学 Double-way oil inflow resonance pore plate type electrically-controlled oil injector
CN106593721A (en) * 2017-01-18 2017-04-26 哈尔滨工程大学 Double-path oil feeding resonance bypass type electrically controlled oil sprayer with engraved groove
CN106762278B (en) * 2017-01-18 2023-03-21 哈尔滨工程大学 Micro-dynamic oil return resonance bypass type electric control oil injector with hydraulic feedback
CN106762284A (en) * 2017-01-18 2017-05-31 哈尔滨工程大学 A kind of resonance bypass type electric-controlled fuel injector with ditch
CN106523223A (en) * 2017-01-18 2017-03-22 哈尔滨工程大学 Micro-dynamic oil return resonance bypass type electronic control oil injector
CN106593722A (en) * 2017-01-18 2017-04-26 哈尔滨工程大学 Resonance hole-plate type electronic control fuel injector with carved grooves
CN106523222A (en) * 2017-01-18 2017-03-22 哈尔滨工程大学 Double-way oil inlet resonance pore plate type electronic oil injector with engraved groove
CN106704065A (en) * 2017-01-18 2017-05-24 哈尔滨工程大学 Resonant type electronic control fuel injector with engraved groove
CN106593725A (en) * 2017-01-18 2017-04-26 哈尔滨工程大学 Resonance type electronic fuel injector
CN106762287B (en) * 2017-01-18 2023-03-21 哈尔滨工程大学 Resonant orifice plate type electric control oil injector with hydraulic feedback
CN106593719A (en) * 2017-01-18 2017-04-26 哈尔滨工程大学 Resonant bypass electric-controlled oil injector
CN106762279B (en) * 2017-01-18 2023-03-21 哈尔滨工程大学 Resonance bypass type electric control oil injector with hydraulic feedback
CN106593726A (en) * 2017-01-18 2017-04-26 哈尔滨工程大学 Resonant electrically controlled oil injector with oil fed through double paths
CN107035586B (en) * 2017-01-18 2023-01-03 哈尔滨工程大学 Micro-dynamic oil return resonant type electric control oil injector with hydraulic feedback
CN106762285A (en) * 2017-01-18 2017-05-31 哈尔滨工程大学 A kind of On Fluctuations oil return resonant mode electric-controlled fuel injector
US10544771B2 (en) * 2017-06-14 2020-01-28 Caterpillar Inc. Fuel injector body with counterbore insert
EP3502460B1 (en) * 2017-12-19 2024-03-13 Vitesco Technologies GmbH Fastening connector for securing two components together
DE102018217761A1 (en) * 2018-10-17 2020-04-23 Robert Bosch Gmbh Fuel injector
CN112196710A (en) * 2020-10-09 2021-01-08 一汽解放汽车有限公司 Fuel injector

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE160785C (en)
JP3385415B2 (en) 1997-01-30 2003-03-10 日野自動車株式会社 High pressure fuel pipe connection structure
JP3904121B2 (en) 1997-09-17 2007-04-11 株式会社日本自動車部品総合研究所 Accumulated fuel injection valve
JP2000205081A (en) 1999-01-06 2000-07-25 Usui Internatl Ind Co Ltd Accumulated fuel injection system for diesel internal combustion engine
GB2358898B (en) 1999-12-09 2002-04-24 Usui Kokusai Sangyo Kk Diesel engine fuel injection pipe
DE10060812A1 (en) 2000-12-07 2002-06-13 Bosch Gmbh Robert Fuel injection system for internal combustion engines
FR2818732B1 (en) 2000-12-22 2004-05-28 Renault METHOD FOR DAMPING PRESSURE WAVES IN A HYDRAULIC LINE, AND INJECTION DEVICE WITH A COMMON RAMP IMPLEMENTING THIS METHOD
DE10121891A1 (en) 2001-05-05 2002-11-07 Bosch Gmbh Robert Fuel injection valve for internal combustion engines
DE10210282A1 (en) * 2002-03-08 2003-09-25 Bosch Gmbh Robert Device for injecting fuel into stationary internal combustion engines
DE10307871A1 (en) 2003-02-25 2004-09-02 Robert Bosch Gmbh High pressure line for a fuel injection system
JP2004332602A (en) 2003-05-06 2004-11-25 Usui Kokusai Sangyo Kaisha Ltd Accumulator fuel injection system for diesel internal combustion engine
BRPI0613413B1 (en) 2005-07-18 2019-08-27 Ganser Hydromag accumulator injection system for an internal combustion engine
AT503660B1 (en) * 2006-06-13 2007-12-15 Bosch Gmbh Robert DEVICE FOR INJECTING FUEL IN THE COMBUSTION ENGINE OF AN INTERNAL COMBUSTION ENGINE
DE102006033937A1 (en) 2006-07-21 2008-01-24 Robert Bosch Gmbh fuel injector
DE102006051583A1 (en) 2006-11-02 2008-05-08 Robert Bosch Gmbh Fuel injector with storage volume segment
DE102008012637A1 (en) 2008-03-05 2009-09-10 Robert Bosch Gmbh Fuel injector for injecting fuel into combustion chamber of internal-combustion engine, has injector body, which has fuel inlet, injection opening, nozzle needle and nozzle area
AT511801B1 (en) * 2012-02-07 2013-03-15 Bosch Gmbh Robert METHOD FOR INFLUENCING THE THREADED GEOMETRY OF AN INTERNAL THREAD FOR INTERNAL COMBUSTION ENGINES

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2012058703A1 *

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AT509877A4 (en) 2011-12-15
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KR101479005B1 (en) 2015-01-05
WO2012058703A1 (en) 2012-05-10
US9447720B2 (en) 2016-09-20
RU2559096C2 (en) 2015-08-10
RU2013125451A (en) 2014-12-10
KR20130098397A (en) 2013-09-04
US20130220271A1 (en) 2013-08-29
JP2013541670A (en) 2013-11-14
JP5778291B2 (en) 2015-09-16
BR112013010712A2 (en) 2019-09-24
AT509877B1 (en) 2011-12-15
EP2635794B1 (en) 2015-05-06

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