EP2807367B1 - 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 Download PDFInfo
- Publication number
- EP2807367B1 EP2807367B1 EP13710897.3A EP13710897A EP2807367B1 EP 2807367 B1 EP2807367 B1 EP 2807367B1 EP 13710897 A EP13710897 A EP 13710897A EP 2807367 B1 EP2807367 B1 EP 2807367B1
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- pressure
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- throttle
- nozzle
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- 239000000446 fuel Substances 0.000 title claims description 11
- 238000002485 combustion reaction Methods 0.000 title claims description 7
- 238000002347 injection Methods 0.000 claims description 38
- 239000007924 injection Substances 0.000 claims description 38
- 230000007704 transition Effects 0.000 claims description 12
- 230000010355 oscillation Effects 0.000 description 10
- 238000010276 construction Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 230000010349 pulsation Effects 0.000 description 2
- 238000004891 communication Methods 0.000 description 1
- 239000002828 fuel tank Substances 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 238000005457 optimization Methods 0.000 description 1
- 230000002035 prolonged effect Effects 0.000 description 1
- 230000000644 propagated effect Effects 0.000 description 1
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
- F02M55/008—Arrangement of fuel passages inside of injectors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/31—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements
- F02M2200/315—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements for damping fuel pressure fluctuations
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/40—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, which includes a high-pressure accumulator integrated in the injector body, an injection nozzle which comprises an axially displaceable nozzle needle, which is surrounded by a nozzle chamber, a high-pressure accumulator with the injection nozzle connecting high-pressure bore and a parallel to the high-pressure bore resonator bore comprises, which communicates with the injection nozzle and is connected via a resonator in the high-pressure accumulator.
- Injection injectors of this type are used in modular common rail systems, which are characterized in that a part of the existing storage volume in the system is present in the injector itself.
- 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 an ordinary line to understand, but it is at a High-pressure accumulator to a pressure-resistant vessel with an inlet and outlet, whose diameter is significantly increased compared to the high pressure lines, so that from the high-pressure accumulator a certain amount of injection can be delivered without causing an immediate pressure drop.
- WO 2007/143768 A1 One way of reducing pressure pulsations is the WO 2007/143768 A1 can be seen, wherein a parallel to the high-pressure line between the injection nozzle 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.
- said resonator system is able to accelerate the decay of the pressure oscillations, the first pressure peak which occurs immediately upon closing of the injection nozzle can not be lowered thereby.
- the invention therefore aims to lower as effectively as possible the first pressure peak occurring directly upon closing of the injection nozzle.
- the invention essentially provides, proceeding from a device of the type initially mentioned, that the high-pressure bore comprises a first section adjoining the high-pressure accumulator and a second section opening into the injector, wherein the first section has a larger flow cross-section than the second section.
- first and second portions directly adjoin one another.
- the transition from the larger flow cross section of the first section to the smaller flow cross section of the second section can take place here continuously or stepwise.
- the edge formed at the transition is preferably rounded.
- both the first and the second section has a circular flow cross-section.
- the first section of the high-pressure bore formed with a larger flow cross-section is formed as long as possible and thus brought as close as possible to the injection nozzle.
- a preferred development in this context provides that the length of the first section corresponds to at least twice, preferably at least three times, the length of the second section.
- An optimization of the effect achieved by the construction according to the invention can also be achieved by selecting the flow cross section of the first section as large as possible in relation to the flow cross section of the second section.
- a preferred embodiment provides that the flow cross section of the first section corresponds to at least 1.5 times, preferably at least twice, preferably at least three times, more preferably at least four times, the flow cross section of the second section.
- the inventive design is particularly advantageous for injectors to bear, in which the nozzle needle for controlling its opening and closing movement of the prevailing in a fuel-pressurized control chamber pressure in the axial direction can be acted upon, wherein the control chamber with an inlet throttle having inlet channel and a drain passage having flow channel is in communication and at least one inlet or outlet channel opening or closing control valve is provided with which the pressure in the control chamber is controlled, that the inlet throttle and the outlet throttle are formed in a throttle plate that the control valve in a valve plate is formed and that the high-pressure bore and the resonator bore to pass through the valve plate and the throttle plate.
- the injector is usually designed such that an injector and / or holding body accommodating the high-pressure accumulator, the valve plate, the throttle plate and the injection nozzle are held together by a nozzle retaining nut.
- the high-pressure bore and the resonator bore extend through the holding body, the valve plate and the throttle plate and thereby connect the high-pressure accumulator with the injection nozzle.
- the section of the high-pressure bore passing through the throttle plate and the valve plate it is particularly advantageous in the context of the invention for the section of the high-pressure bore passing through the throttle plate and the valve plate to form the second section thereof or a part of the second section.
- the flow cross-section is limited by design, since the resonator bore and the high-pressure bore on the valve assembly and the drain and possibly inlet throttle must be passed.
- the first section of the high-pressure bore is preferably formed in a holding body. which is arranged between the high-pressure accumulator and the valve plate.
- the transition from the first section into the second section of the high-pressure bore can be arranged, for example, at the transition of the holding body to the valve plate.
- a preferred development provides that the transition from the first section to the second section of the high-pressure bore is arranged in the holding body. At the transition from the holding body in the valve plate in this case, only the smaller cross section of the second section is sealed.
- the resonator throttle is arranged at the inlet of the resonator bore in the high-pressure accumulator.
- the length of the resonator bore is preferably matched to the length of the high-pressure bore so that the pressure oscillations induced by the injector are mutually weakened or extinguished.
- the length of the resonator bore between the injection nozzle and the resonator throttle and the length of the high-pressure line between the injection nozzle and the inlet of the high-pressure bore into the pressure accumulator are each preferably an integer multiple of the wavelength of the pressure oscillation induced by the injection nozzle.
- the length of the resonator bore between the nozzle front chamber and the resonator throttle preferably corresponds substantially to the length of the high-pressure line between the nozzle front chamber and the inlet of the high-pressure bore into the pressure accumulator.
- FIG.1 schematically a cross section of an equipped with a high-pressure accumulator injector according to the prior art
- Fig.2 a schematic representation of the course of the flow cross-section of the high-pressure line between the high-pressure accumulator and injector.
- an injector 1 having an injector 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 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.
- the voltage applied in the control chamber 11 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 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 turns through 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 injection holes 17 are 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.
- FIG. 2 shows a highly schematic representation of the injector 1, wherein the in Fig. 1 Functional components described in more detail, namely the memory 6, the holding body 5, the valve plate 4, the throttle plate 3 and the injection nozzle 2 are only outlined, without their individual components, as they are based on Fig. 1 described individually.
- Fig. 1 Functional components described in more detail, namely the memory 6, the holding body 5, the valve plate 4, the throttle plate 3 and the injection nozzle 2 are only outlined, without their individual components, as they are based on Fig. 1 described individually.
- the high-pressure bore 8 which connects the high-pressure accumulator 6 with the injection nozzle 2 in a first portion 8 'has a larger diameter compared to the prior art, namely a significantly larger diameter than in a second portion 8 "
- the transition between the first section 8 'and the second section 8 " is designated by 22 and is arranged in the holding body 5.
- the high-pressure bore has a relation to the prior art unaltered cross section, and in particular the same diameter as the resonator 20th
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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 eine Vorrichtung zum Einspritzen von Kraftstoff in den Brennraum einer Brennkraftmaschine mit wenigstens einem Injektor, der einen im Injektorkörper integrierten Hochdruckspeicher, eine Einspritzdüse, die eine axial verschieblich geführte Düsennadel umfasst, die von einem Düsenraum umgeben ist, eine den Hochdruckspeicher mit der Einspritzdüse verbindende Hochdruckbohrung und eine parallel zur Hochdruckbohrung geschaltene Resonatorbohrung umfasst, die mit der Einspritzdüse in Verbindung steht und über eine Resonatordrossel in den Hochdruckspeicher mündet.The invention relates to a device for injecting fuel into the combustion chamber of an internal combustion engine having at least one injector, which includes a high-pressure accumulator integrated in the injector body, an injection nozzle which comprises an axially displaceable nozzle needle, which is surrounded by a nozzle chamber, a high-pressure accumulator with the injection nozzle connecting high-pressure bore and a parallel to the high-pressure bore resonator bore comprises, which communicates with the injection nozzle and is connected via a resonator in the high-pressure accumulator.
Einspritzinjektoren dieser Art werden in modularen Common-Rail-Systemen verwendet, die dadurch gekennzeichnet sind, dass ein Teil des im System vorhandenen Speichervolumens im Injektor 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 bei einem Hochdruckspeicher 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.Injection injectors of this type are used in modular common rail systems, which are characterized in that a part of the existing storage volume in the system is present in the injector itself. 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 an ordinary line to understand, but it is at a High-pressure accumulator to a pressure-resistant vessel with an inlet and outlet, whose diameter is significantly increased compared to the high pressure lines, so that from the high-pressure accumulator a certain amount of injection can be delivered without causing an immediate pressure drop.
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. Beim Schließen der Einspritzdüse läuft der Kraftstoff gegen ein geschlossenes Leitungsende, wobei auf Grund der Trägheit des Kraftstoffes der Druck vor der Einspritzdüse deutlich ansteigt. Diese Druckspitze läuft in der Folge in der Hochdruckbohrung zwischen Einspritzdüse und dem Hochdruckspeicher hin und her, wobei am Düsensitz starke Druckpulsationen entstehen, die hier zu starkem Verschleiß führen. Die dabei auftretenden Druckspitzen liegen in ungünstigen Fällen um bis zu 500 bar über dem Raildruck.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 a very fast closing of the injector. When closing the injector, the fuel runs against a closed line end, wherein due to the inertia of the fuel, the pressure in front of the injector increases significantly. As a result, this pressure peak reciprocates in the high-pressure bore between the injection nozzle and the high-pressure accumulator, with strong pressure pulsations occurring at the nozzle seat, which lead to excessive wear here. The resulting pressure peaks are in unfavorable cases by up to 500 bar above the rail pressure.
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, nachfolgende 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 an der Einspritzdüse in allen Betriebszuständen des hydraulischen Systems ist daher erstrebenswert.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. The lowest possible pressure oscillation at the injection nozzle in all operating states of the hydraulic system is therefore desirable.
Eine Möglichkeit der Reduktion von Druckpulsationen ist der
Die aus der
Das genannte Resonatorsystem ist zwar in der Lage, das Abklingen der Druckschwingungen zu beschleunigen, die erste, unmittelbar beim Schließen der Einspritzdüse auftretende Druckspitze kann dadurch aber nicht abgesenkt werden.Although said resonator system is able to accelerate the decay of the pressure oscillations, the first pressure peak which occurs immediately upon closing of the injection nozzle can not be lowered thereby.
Die Erfindung zielt daher darauf ab, auch die erste, unmittelbar beim Schließen der Einspritzdüse auftretende Druckspitze möglichst wirksam abzusenken.The invention therefore aims to lower as effectively as possible the first pressure peak occurring directly upon closing of the injection nozzle.
Zur Lösung dieser Aufgabe sieht die Erfindung ausgehend von einer Vorrichtung der eingangs genannten Art im Wesentlichen vor, dass die Hochdruckbohrung einen ersten, an den Hochdruckspeicher anschließenden Abschnitt und einen zweiten, in die Einspritzdüse mündenden Abschnitt umfasst, wobei der erste Abschnitt einen größeren Durchflussquerschnitt aufweist als der zweite Abschnitt. Durch diese einfache Maßnahme wird erreicht, dass die gegen die geschlossene Einspritzdüse auflaufende Flüssigkeitssäule reduziert und damit die entsprechende Druckspitze abgesenkt wird.To achieve this object, the invention essentially provides, proceeding from a device of the type initially mentioned, that the high-pressure bore comprises a first section adjoining the high-pressure accumulator and a second section opening into the injector, wherein the first section has a larger flow cross-section than the second section. By this simple measure is achieved that against the closed injection nozzle Reduces accumulating liquid column and thus the corresponding pressure peak is lowered.
Bevorzugt schließen der erste und der zweite Abschnitt unmittelbar aneinander an. Der Übergang vom größeren Durchflussquerschnitt des ersten Abschnitts auf den kleineren Durchflussquerschnitt des zweiten Abschnitts kann hierbei kontinuierlich oder stufenartig erfolgen. Bei einem stufenartigen Übergang ist die am Übergang ausgebildete Kante bevorzugt abgerundet. Bevorzugt weist sowohl der erste als auch der zweite Abschnitt einen kreisrunden Durchflussquerschnitt auf.Preferably, the first and second portions directly adjoin one another. The transition from the larger flow cross section of the first section to the smaller flow cross section of the second section can take place here continuously or stepwise. In a step-like transition, the edge formed at the transition is preferably rounded. Preferably, both the first and the second section has a circular flow cross-section.
Zur Maximierung des durch die erfindungsgemäße Ausbildung erreichten Effekts wird der erste, mit größerem Durchflussquerschnitt ausgebildete Abschnitt der Hochdruckbohrung möglichst lange ausgebildet und damit möglichst nahe an die Einspritzdüse herangeführt. Eine bevorzugte Weiterbildung sieht in diesem Zusammenhang vor, dass die Länge des ersten Abschnitts wenigstens dem Doppelten, bevorzugt wenigstens dem Dreifachen der Länge des zweiten Abschnitts entspricht.In order to maximize the effect achieved by the construction according to the invention, the first section of the high-pressure bore formed with a larger flow cross-section is formed as long as possible and thus brought as close as possible to the injection nozzle. A preferred development in this context provides that the length of the first section corresponds to at least twice, preferably at least three times, the length of the second section.
Eine Optimierung des durch die erfindungsgemäße Ausbildung erreichten Effekts kann auch dadurch erreicht werden, dass der Durchflussquerschnitt des ersten Abschnitts im Verhältnis zum Durchflussquerschnitt des zweiten Abschnitts möglichst groß gewählt wird. Eine bevorzugte Ausbildung sieht hierbei vor, dass der Durchflussquerschnitt des ersten Abschnitts mindestens dem 1,5-fachen, bevorzugt mindestens dem 2-fachen, bevorzugt mindestens dem 3-fachen, besonders bevorzugt mindestens dem 4-fachen des Durchflussquerschnitts des zweiten Abschnitts entspricht.An optimization of the effect achieved by the construction according to the invention can also be achieved by selecting the flow cross section of the first section as large as possible in relation to the flow cross section of the second section. A preferred embodiment provides that the flow cross section of the first section corresponds to at least 1.5 times, preferably at least twice, preferably at least three times, more preferably at least four times, the flow cross section of the second section.
Die erfindungsgemäße Ausbildung kommt besonders vorteilhaft bei Injektoren zum Tragen, bei denen die Düsennadel zur Steuerung ihrer Öffnungs- und Schließbewegung von dem in einem mit Kraftstoff unter Druck speisbaren Steuerraum herrschenden Druck in axialer Richtung beaufschlagbar ist, wobei der Steuerraum mit einem eine Zulaufdrossel aufweisenden Zulaufkanal und einem eine Ablaufdrossel aufweisenden Ablaufkanal in Verbindung steht und wenigstens ein den Zu- oder Ablaufkanal öffnendes oder schließendes Steuerventil vorgesehen ist, mit dem der Druck im Steuerraum gesteuert wird, dass die Zulaufdrossel und die Ablaufdrossel in einer Drosselplatte ausgebildet sind, dass das Steuerventil in einer Ventilplatte ausgebildet ist und dass die Hochdruckbohrung und die Resonatorbohrung die Ventilplatte und die Drosselplatte durchsetzen. Der Injektor ist hierbei meist so ausgebildet, dass ein den Hochdruckspeicher beherbergender Injektor- und/oder Haltekörper, die Ventilplatte, die Drosselplatte und die Einspritzdüse von einer Düsenspannmutter zusammengehalten werden. Die Hochdruckbohrung und die Resonatorbohrung erstrecken sich dabei durch den Haltekörper, die Ventilplatte und die Drosselplatte und verbinden dadurch den Hochdruckspeicher mit der Einspritzdüse.The inventive design is particularly advantageous for injectors to bear, in which the nozzle needle for controlling its opening and closing movement of the prevailing in a fuel-pressurized control chamber pressure in the axial direction can be acted upon, wherein the control chamber with an inlet throttle having inlet channel and a drain passage having flow channel is in communication and at least one inlet or outlet channel opening or closing control valve is provided with which the pressure in the control chamber is controlled, that the inlet throttle and the outlet throttle are formed in a throttle plate that the control valve in a valve plate is formed and that the high-pressure bore and the resonator bore to pass through the valve plate and the throttle plate. In this case, the injector is usually designed such that an injector and / or holding body accommodating the high-pressure accumulator, the valve plate, the throttle plate and the injection nozzle are held together by a nozzle retaining nut. The high-pressure bore and the resonator bore extend through the holding body, the valve plate and the throttle plate and thereby connect the high-pressure accumulator with the injection nozzle.
Bei einem Injektor der oben genannten Art ist es im Rahmen der Erfindung besonders vorteilhaft, wenn der die Drosselplatte und die Ventilplatte durchsetzende Abschnitt der Hochdruckbohrung den zweiten Abschnitt derselben oder einen Teil des zweiten Abschnitts ausbildet. In diesem Abschnitt ist der Durchflussquerschnitt konstruktionsbedingt begrenzt, da die Resonatorbohrung und die Hochdruckbohrung an der Ventilanordnung bzw. der Ablauf- und ggf. Zulaufdrossel vorbeigeführt werden müssen. Der erste Abschnitt der Hochdruckbohrung hingegen ist bevorzugt in einem Haltekörper ausgebildet, der zwischen dem Hochdruckspeicher und der Ventilplatte angeordnet ist.In an injector of the abovementioned type, it is particularly advantageous in the context of the invention for the section of the high-pressure bore passing through the throttle plate and the valve plate to form the second section thereof or a part of the second section. In this section, the flow cross-section is limited by design, since the resonator bore and the high-pressure bore on the valve assembly and the drain and possibly inlet throttle must be passed. By contrast, the first section of the high-pressure bore is preferably formed in a holding body. which is arranged between the high-pressure accumulator and the valve plate.
Der Übergang vom ersten Abschnitt in den zweiten Abschnitt der Hochdruckbohrung kann beispielsweise am Übergang des Haltekörpers zur Ventilplatte angeordnet sein. Dies würde allerdings dazu führen, dass an dieser Stelle, an der die Ventilplatte und der Haltekörper dichtend aneinander gepresst sind, ein größerer Querschnitt der Hochdruckbohrung, nämlich der Querschnitt des ersten Abschnitts, abgedichtet werden muss. Um dies zu vermeiden, sieht eine bevorzugte Weiterbildung vor, dass der Übergang vom ersten Abschnitt in den zweiten Abschnitt der Hochdruckbohrung im Haltekörper angeordnet ist. Am Übergang vom Haltekörper in die Ventilplatte ist in diesem Fall nur mehr der kleinere Querschnitt des zweiten Abschnitts abzudichten.The transition from the first section into the second section of the high-pressure bore can be arranged, for example, at the transition of the holding body to the valve plate. However, this would mean that at this point, at which the valve plate and the holding body are pressed sealingly against one another, a larger cross-section of the high-pressure bore, namely the cross section of the first section, must be sealed. To avoid this, a preferred development provides that the transition from the first section to the second section of the high-pressure bore is arranged in the holding body. At the transition from the holding body in the valve plate in this case, only the smaller cross section of the second section is sealed.
Bevorzugt ist vorgesehen, dass die Resonatordrossel am Eintritt der Resonatorbohrung in den Hochdruckspeicher angeordnet ist.It is preferably provided that the resonator throttle is arranged at the inlet of the resonator bore in the high-pressure accumulator.
Bevorzugt ist die Länge der Resonatorbohrung auf die Länge der Hochdruckbohrung abgestimmt, sodass sich die vom Injektor induzierten Druckschwingungen gegenseitig abschwächen oder auslöschen.The length of the resonator bore is preferably matched to the length of the high-pressure bore so that the pressure oscillations induced by the injector are mutually weakened or extinguished.
Bevorzugt ist die Länge der Resonatorbohrung zwischen der Einspritzdüse und der Resonatordrossel sowie die Länge der Hochdruckleitung zwischen der Einspritzdüse und dem Eintritt der Hochdruckbohrung in den Druckspeicher jeweils ein ganzzahliges Vielfaches der Wellenlänge der von der Einspritzdüse induzierten Druckschwingung.The length of the resonator bore between the injection nozzle and the resonator throttle and the length of the high-pressure line between the injection nozzle and the inlet of the high-pressure bore into the pressure accumulator are each preferably an integer multiple of the wavelength of the pressure oscillation induced by the injection nozzle.
Bevorzugt entspricht die Länge der Resonatorbohrung zwischen dem Düsenvorraum und der Resonatordrossel im Wesentlichen der Länge der Hochdruckleitung zwischen dem Düsenvorraum und dem Eintritt der Hochdruckbohrung in den Druckspeicher.The length of the resonator bore between the nozzle front chamber and the resonator throttle preferably corresponds substantially to the length of the high-pressure line between the nozzle front chamber and the inlet of the high-pressure bore into the pressure accumulator.
Die Erfindung wird nachfolgend anhand eines in der Zeichnung schematisch dargestellten Ausführungsbeispiels näher erläutert. In dieser zeigen
In
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 muss. 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° phasenverschoben, 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.Due to the inertia of the fuel in
Allerdings ist die beschriebene Anordnung nicht in der Lage, auch die erste, unmittelbar beim Schließen der Einspritzdüse 2 auftretende Druckspitze abzusenken. In der Detaildarstellung gemäß
Claims (9)
- Device for injecting fuel into the combustion chamber of an internal combustion engine, with at least one injector (1), the at least one injector comprising a high-pressure accumulator (6) integrated in the injector body, comprising an injection nozzle (2) which comprises an axially displaceably guided nozzle needle (15) surrounded by a nozzle chamber (19), comprising a high-pressure bore (8) which connects the high-pressure accumulator (16) to the injection nozzle (2), and comprising a resonator bore (20) which is connected in parallel with respect to the high-pressure bore (8) and which is connected to the injection nozzle (2) and which issues, via a resonator throttle (21), into the high-pressure accumulator (6), characterized in that the high-pressure bore (8) comprises a first section (8'), which adjoins the high-pressure accumulator (6), and a second section (8''), which issues into the injection nozzle (2), wherein the first section (8') has a larger throughflow cross section than the second section (8'').
- Device according to Claim 1, characterized in that the first section (8') and the second section (8'') directly adjoin one another.
- Device according to Claim 1 or 2, characterized in that the length of the first section (8') corresponds to at least two times, preferably at least three times, the length of the second section (8'').
- Device according to Claim 1, 2 or 3, characterized in that the throughflow cross section of the first section (8') corresponds to at least 1.5 times, preferably at least 2 times, preferably at least 3 times, particularly preferably at least 4 times the throughflow cross section of the second section (8'').
- Device according to one of Claims 1 to 4, characterized in that the nozzle needle (15) can, for the control of its opening and closing movement, be acted on in an axial direction by the pressure prevailing in a control chamber (11) to which pressurized fuel can be fed, wherein the control chamber (11) is connected to an inflow duct (9), which has an inflow throttle (10), and to an outflow duct, which has an outflow throttle (12), and at least one control valve (13) is provided which opens or closes the inflow or outflow duct and by means of which the pressure in the control chamber (11) is controlled, in that the inflow throttle (10) and the outflow throttle (12) are formed in a throttle plate (3), in that the control valve (13) is formed in a valve plate (4), and in that the high-pressure bore (8) and the resonator bore (20) extend through the valve plate (4) and the throttle plate (3).
- Device according to Claim 5, characterized in that that section of the high-pressure bore (8) which extends through the throttle plate (3) and through the valve plate (4) forms the second section (8'') of said high-pressure bore or a part of the second section (8'').
- Device according to Claim 5 or 6, characterized in that the first section (8') of the high-pressure bore is formed in a holding body (5) which is arranged between the high-pressure accumulator (6) and the valve plate (4).
- Device according to Claim 7, characterized in that the transition (22) from the first section (8') to the second section (8'') of the high-pressure bore is arranged in the holding body (5).
- Device according to Claim 8, characterized in that the edge formed at the transition (22) is rounded.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
AT1042012A AT512439B1 (en) | 2012-01-26 | 2012-01-26 | DEVICE FOR INJECTING FUEL IN THE COMBUSTION ENGINE OF AN INTERNAL COMBUSTION ENGINE |
PCT/IB2013/000208 WO2013111007A1 (en) | 2012-01-26 | 2013-01-17 | Device for injecting fuel into the combustion chamber of an internal combustion engine |
Publications (2)
Publication Number | Publication Date |
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EP2807367A1 EP2807367A1 (en) | 2014-12-03 |
EP2807367B1 true EP2807367B1 (en) | 2015-10-14 |
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Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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EP13710897.3A Active EP2807367B1 (en) | 2012-01-26 | 2013-01-17 | Device for injecting fuel into the combustion chamber of an internal combustion engine |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP2807367B1 (en) |
AT (1) | AT512439B1 (en) |
WO (1) | WO2013111007A1 (en) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
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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 |
US9644590B2 (en) * | 2014-01-31 | 2017-05-09 | Cummins Inc. | Fuel injection pressure pulsation dampening system |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1518050B1 (en) * | 2002-07-02 | 2011-10-05 | Continental Automotive GmbH | Injector for an injection system |
AT501573B1 (en) * | 2006-06-13 | 2008-05-15 | Avl List Gmbh | HYDRAULIC DEVICE WITH AT LEAST ONE PRESSURE MEMORY |
AT503660B1 (en) * | 2006-06-13 | 2007-12-15 | Bosch Gmbh Robert | DEVICE FOR INJECTING FUEL IN THE COMBUSTION ENGINE OF AN INTERNAL COMBUSTION ENGINE |
AT509877B1 (en) * | 2010-11-02 | 2011-12-15 | Bosch Gmbh Robert | DEVICE FOR INJECTING FUEL IN THE COMBUSTION ENGINE OF AN INTERNAL COMBUSTION ENGINE |
-
2012
- 2012-01-26 AT AT1042012A patent/AT512439B1/en active
-
2013
- 2013-01-17 EP EP13710897.3A patent/EP2807367B1/en active Active
- 2013-01-17 WO PCT/IB2013/000208 patent/WO2013111007A1/en active Application Filing
Also Published As
Publication number | Publication date |
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EP2807367A1 (en) | 2014-12-03 |
WO2013111007A1 (en) | 2013-08-01 |
AT512439A1 (en) | 2013-08-15 |
AT512439B1 (en) | 2013-12-15 |
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