EP1013919A2 - Fuel injection valve - Google Patents

Fuel injection valve Download PDF

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Publication number
EP1013919A2
EP1013919A2 EP99124112A EP99124112A EP1013919A2 EP 1013919 A2 EP1013919 A2 EP 1013919A2 EP 99124112 A EP99124112 A EP 99124112A EP 99124112 A EP99124112 A EP 99124112A EP 1013919 A2 EP1013919 A2 EP 1013919A2
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EP
European Patent Office
Prior art keywords
valve
diffuser
fuel
pressure
fuel injection
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
EP99124112A
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German (de)
French (fr)
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EP1013919A3 (en
EP1013919B1 (en
Inventor
Walter Egler
Peter Boehland
Lorenz Betz
Ralf Hentschel
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication date
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Publication of EP1013919A2 publication Critical patent/EP1013919A2/en
Publication of EP1013919A3 publication Critical patent/EP1013919A3/en
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Publication of EP1013919B1 publication Critical patent/EP1013919B1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0017—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means
    • 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
    • F02M2200/04—Fuel-injection apparatus having means for avoiding effect of cavitation, e.g. erosion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/28—Details of throttles in fuel-injection apparatus

Definitions

  • the invention relates to a fuel injection valve according to the preamble of the patent claim from, as is known from EP-0 690 223 A2.
  • the present invention is therefore based on the problem of a fuel injection valve for high pressure injection of fuel from a central high pressure line to create in combustion chambers, in which the opening and closing process of the Switch valve and the fuel flow through the switch valve as accurately as possible becomes controllable.
  • the fuel valve according to the invention with the features of claim 1 has the Advantage that the hydraulic flow through the switching valve even at low Rail pressure and small valve lift can be precisely specified. To do this, the flow is ahead the switching valve with a specially designed throttle geometry expanded. After the contraction through the throttle inlet, the fuel flow spreads in the throttle geometry according to the invention in the direction of the throttle wall that the hydraulic flow through the optimal pressure difference at the valve is increased and the opening movement of the valve ball is supported away from the valve seat.
  • the flow resistance is reduced, so that even with a small switching valve stroke and a small rail pressure it becomes high Flow comes.
  • the high flow rate leads to a higher flow in the throttle Flow velocity.
  • the diameter of the diffuser is at Transition to the cone seat only slightly more than the seat diameter. Thereby the largest possible hydraulic cross section of the valve when lifting the Valve ball reached.
  • the fuel injection valve has a housing 2 on that with a connection 3 for supplying brought to injection pressure Fuel from a high-pressure fuel reservoir not shown is connected.
  • An injection valve needle 5 is arranged in the housing 2 of the fuel injection valve, which has a guide section 6, which is located within the pressure chamber 7 lying shoulder in a smaller diameter part 9 of the injector needle transforms. At the end of this part 9, which is smaller in diameter, it has one conical sealing surface 10, which cooperates with a valve seat 11 and thereby Injection openings 12 opens or closes depending on the position of the injection valve needle.
  • the pressure chamber 7 is permanently connected to the connection 3 via a pressure line 4, so that the pressure chamber 7 is constantly under high injection pressure.
  • the needle 5 will controlled via the pressure piece 21 and the control piston 13.
  • the control piston is immersed in a cylinder 14 in which it includes a control pressure chamber 15 at the end. This is in constant connection with connection 3 via a throttle bore 16.
  • a throttle bore 17 leads from the control pressure chamber 15, the outlet thereof opens into a relief chamber 18 via an electric valve 19.
  • the flow through the throttle bore 17 is controlled via the electric valve 19.
  • the relief room is connected to a return via an outlet connection 20 on the housing 2.
  • the fuel injection valve described above is supplied with high pressure from the high-pressure fuel reservoir via connection 3. This strives to raise the fuel injection valve needle 5 in action on the shoulder 9, so that fuel can flow from the pressure chamber 7 along the smaller diameter part 9 of the injection valve needle to the injection openings 12 and exit there.
  • This opening is counteracted by the spring 18, which alone is not sufficient, however, to hold the injection valve needle 5 in the firing position when the fuel pressure is high in the pressure chamber 7, but does so in the absence of high fuel pressure.
  • the task of closing continues to be carried out by the pressure in the control pressure chamber 15, which is the same as the pressure in the pressure chamber 7 when the electrically operated valve 19 is closed. Because of the larger end face of the control piston 14, the closing force predominates and the valve remains closed.
  • the electrically operated valve 19 is opened so that the pressure chamber 15 is decoupled from the throttle bore 16 and thus the opening force on the shoulder 8 predominates.
  • the electrically operated valve 10 is closed again.
  • 2 shows the two embodiments of the invention in section.
  • the upper part shows an embodiment with a throttle bore 31 which widens conically in the flow direction up to the conical seat of the ball valve 50.
  • the cone angles ⁇ are designed for maximum pressure recovery in the flow.
  • the lower part shows an embodiment in which the throttle bore 17, which widens conically in the flow direction with the angle ⁇ , and two diffusors 30 and 40 connected in series, also produce maximum pressure recovery.
  • the fuel flows from the pressure chamber 15 into the throttle bore 17 or 31 and gaining speed.
  • the static pressure in the flow is present in the area of the diffuser 30 the wall (see schematic representation of the fuel flow by arrows in Fig. 1), expands and is braked at the same time.
  • the second diffuser 40 amplifies this process, causing the static pressure within the flow in Flow direction increases.
  • This increased static pressure supports opening of the switching valve, the movement of the valve ball 50 in the direction of flow and accelerates hence the increase in fuel flow through the switching valve.
  • the increased fuel flow increases the tendency to cavitation at the beginning of the throttle.
  • the diameter of the second Diffuser 40 is only slightly smaller than the diameter of the valve seat line 52. This causes the valve ball 50 to move in the direction of flow (cf. double arrow in Fig. 1) released a maximum flow cross-section.
  • the throttle bore 15 is slightly tapered in the direction of flow and preferably has a cone angle ⁇ of up to 5 °
  • the throttle bore 17 are the two Diffusers 30, 40 or 31 and the valve seat 51 are collinearly aligned and form a total a funnel, the wider opening of which is closed by the valve ball 50 or is opened.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid Mechanics (AREA)
  • Electromagnetism (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

The fuel injection valve has a switching valve with a valve seat (51) and valve ball (50) that is raised from the seat in the open state and supplied by a pressure chamber (15) connected to a central high pressure line via a choke bore (17). The transition from the choke inlet to the valve seat form a diffuser. The diffuser can be conical, stepped or a combination of the two.

Description

Die Erfindung geht von einem Kraftstoffeinspritzventil gemäß der Gattung des Patentanspruchs aus, wie es durch die EP-0 690 223 A2 bekannt ist.The invention relates to a fuel injection valve according to the preamble of the patent claim from, as is known from EP-0 690 223 A2.

Bei sogenannten Common Rail Systemen werden die Einspritzdüsen für die verschiedenen Zylinder des Motors aus einer zentralen Hochdruckleitung mit Kraftstoff versorgt. Damit möglichst niedrige Abgaswerte, niedriger Kraftstoffverbrauch und ein ruhiger Motorlauf gewährleistet sind, müssen alle Einspritzventile den Kraftstoff exakt gleich in den Motor einspritzen. Dies kann nur gewährleistet werden, wenn alle Einspritzventile zum exakt gleichen Zeitpunkt bei einem Betriebspunkt das gleiche Öffnungsverhalten besitzen.In so-called common rail systems, the injection nozzles for the various Cylinder of the engine supplied with fuel from a central high pressure line. The lowest possible emission values, low fuel consumption and a quiet one Engine running are guaranteed, all fuel injectors must be in exactly the same fuel inject the engine. This can only be guaranteed if all injectors the same opening behavior at exactly the same time at an operating point have.

Zur genauen Steuerung des Einspritzvorganges mit Common Rail Systemen sind daher im Stand der Technik elektromagnetische oder piezogesteuerte Ventile bekannt, die sich vor dem eigentlichen Emspritzventil befinden. Bei einem solchen Kraftstoffeinspritzventil wird die Düsennadel über einen Steuerkolben bewegt. Der Steuerkolben wird über den Druck im Steuerraum bewegt. Die Präzision des Einspritzvorganges wird von der Bewegung des Steuerkolbens bestimmt, die vom Druck im Steuerraum und damit vom Durchfluß durch Drosseln und ein Schaltventil abhängt.For precise control of the injection process with common rail systems are therefore known in the prior art electromagnetic or piezo-controlled valves in front of the actual injection valve. With such a fuel injector the nozzle needle is moved over a control piston. The control piston will moved over the pressure in the control room. The precision of the injection process is determined by the movement of the control piston determined by the pressure in the control room and thus depends on the flow through throttles and a switching valve.

Der vorliegenden Erfindung liegt daher das Problem zugrunde, ein Kraftstoffeinspritzventil für eine Hochdruckeinspritzung von Kraftstoff aus einer zentralen Hochdruckleitung in Brennräume zu schaffen, bei welchem der Öffnungs- und Schließvorgang des Schaltventils und der durchgeflossene Kraftstoff durch das Schaltventil möglichst genau kontrollierbar wird. The present invention is therefore based on the problem of a fuel injection valve for high pressure injection of fuel from a central high pressure line to create in combustion chambers, in which the opening and closing process of the Switch valve and the fuel flow through the switch valve as accurately as possible becomes controllable.

Vorteile der ErfindungAdvantages of the invention

Das erfindungsgemäße Kraftstoffventil mit den Merkmalen des Anspruchs 1 hat den Vorteil, daß der hydraulische Durchfluß durch das Schaltventil auch bei niedrigem Raildruck und kleinem Ventilhub genau vorgebbar ist. Dazu wird die Strömung vor dem Schaltventil mit einer speziell gestalteten Drosselgeometrie gezielt eingeschnürt und erweitert. Nach der Kontraktion durch den Drosseleinlauf breitet sich die Kraftstoffströmung bei der erfindungsgemäßen Drosselgeometrie so in Richtung der Drosselwand aus, daß durch optimale Druckdifferenz am Ventil der hydraulische Durchfluß erhöht und die Öffnungsbewegung der Ventilkugel vom Ventilsitz weg unterstützt wird.The fuel valve according to the invention with the features of claim 1 has the Advantage that the hydraulic flow through the switching valve even at low Rail pressure and small valve lift can be precisely specified. To do this, the flow is ahead the switching valve with a specially designed throttle geometry expanded. After the contraction through the throttle inlet, the fuel flow spreads in the throttle geometry according to the invention in the direction of the throttle wall that the hydraulic flow through the optimal pressure difference at the valve is increased and the opening movement of the valve ball is supported away from the valve seat.

Durch die vorteilhafte Ausführung der Drossel wird der Strömungswiderstand herabgesetzt, so daß es schon bei kleinem Schaltventilhub und kleinem Raildruck zu einem hohen Durchfluß kommt. Der hohe Durchfluß führt im Einlauf in die Drossel zu hoher Strömungsgeschwindigkeit.Due to the advantageous design of the throttle, the flow resistance is reduced, so that even with a small switching valve stroke and a small rail pressure it becomes high Flow comes. The high flow rate leads to a higher flow in the throttle Flow velocity.

Deshalb fällt dort der statische Druck bis auf den Dampfdruck des Kraftstoffes ab, und es kommt zu Dampfbildung, d.h. Kavitation. Durch diesen Effekt, der mit der erfindungsgemäßen Drosselgeometrie bei möglichst kleinen Raildrücken und Schaltventilhüben eintritt, ist der hydraulische Durchfluß nur noch vom Druck vor der Drossel und der Einlaufgeometrie bestimmt (bei konstanter Kraftstofftemperatur und konstantem Kraftstofftyp) und ist unabhängig vom Ventilhub. Aufgrund des definierten hydraulischen Durchflusses wird der über die entsprechenden Schaltventile elektronisch gesteuerte Einspritzbeginn mehrerer Einspritzdüsen, die von einer gemeinsamen Hochdruckleitung versorgt werden, zuverlässig synchronisiert. Therefore, the static pressure drops there to the vapor pressure of the fuel, and steam formation occurs, i.e. Cavitation. Through this effect, that with the invention Throttle geometry with the smallest possible rail pressures and switching valve strokes occurs, the hydraulic flow is only from the pressure in front of the throttle and the inlet geometry (at constant fuel temperature and constant Fuel type) and is independent of the valve lift. Due to the defined hydraulic Flow is electronically controlled via the corresponding switching valves Start of injection of several injectors from a common high pressure line be supplied, reliably synchronized.

In den abhängigen Ansprüchen aufgeführte Maßnahmen definieren vorteilhafte Weiterbildungen und Verbesserungen des in Anspruch 1 angegebenen Kraftstoffeinspritzventils.Measures listed in the dependent claims define advantageous further developments and improvements to the fuel injector specified in claim 1.

Gemäß einer bevorzugten Ausführungsform ist der Durchmesser des Diffusors beim Übergang in den Kegelsitz nur geringfügig Meiner als der Sitzdurchmesser. Dadurch wird ein möglichst großer hydraulischer Querschnitt des Ventils beim Abheben der Ventilkugel erreicht.According to a preferred embodiment, the diameter of the diffuser is at Transition to the cone seat only slightly more than the seat diameter. Thereby the largest possible hydraulic cross section of the valve when lifting the Valve ball reached.

Zeichnungdrawing

Die Erfindung ist anhand von Fig. 1 und 2 näher erläutert. Es zeigen:

Fig. 1:
eine Schnittansicht eines gesamten Common Rail Injektors; und
Fig. 2
die beiden Ausführungsformen der Erfindung.
The invention is explained in more detail with reference to FIGS. 1 and 2. Show it:
Fig. 1:
a sectional view of an entire common rail injector; and
Fig. 2
the two embodiments of the invention.

Detaillierte Beschreibung der bevorzugten AusführungsformDetailed description of the preferred embodiment

In Fig. 1 ist ein Injektor dargestellt. Das Kraftstoffeinspritzventil weist ein Gehäuse 2 auf, das mit einem Anschluß 3 zur Zuführung von auf Einspritzdruck gebrachtem Kraftstoff aus einem nicht weiter gezeigten Kraftstoffhochdruckspeicher verbunden ist. In dem Gehäuse 2 des Kraftstoffeinspritzventils ist eine Einspritzventilnadel 5 angeordnet, die einen Führugnsabschnitt 6 aufweist, der über eine innerhalb des Druckraumes 7 liegende Schulter in einem im Durchmesser kleineren Teils 9 der Einspritzventilnadel übergeht. Am Ende dieses im Durchmesser kleineren Teils 9 weist dieser eine konisch Dichtfläche 10 auf, die mit einem Ventilsitz 11 zusammenwirkt und dabei die Einspritzöffnungen 12 je nach Stellung der Einspritzventilnadel öffnet oder schließt.An injector is shown in FIG. The fuel injection valve has a housing 2 on that with a connection 3 for supplying brought to injection pressure Fuel from a high-pressure fuel reservoir not shown is connected. An injection valve needle 5 is arranged in the housing 2 of the fuel injection valve, which has a guide section 6, which is located within the pressure chamber 7 lying shoulder in a smaller diameter part 9 of the injector needle transforms. At the end of this part 9, which is smaller in diameter, it has one conical sealing surface 10, which cooperates with a valve seat 11 and thereby Injection openings 12 opens or closes depending on the position of the injection valve needle.

Der Druckraum 7 ist über eine Druckleitung 4 ständig mit dem Anschluß 3 verbunden, so daß der Druckraum 7 ständig unter hohem Einspritzdruck steht. Die Nadel 5 wird über das Druckstück 21 und den Steuerkolben 13 gesteuert. Der Steuerkolben taucht in einen Zylinder 14 ein, in dem er stirnseitig einen Steuerdruckraum 15 einschließt. Dieser steht über eine Drosselbohrung 16 in ständiger Verbindung mit dem Anschluß 3. Weiterhin führt vom Steuerdruckraum 15 eine Drosselbohrung 17 ab, deren Austritt über ein elektrisches Ventil 19 in einen Entlastungsraum 18 mündet. Der Durchfluß durch die Drosselbohrung 17 wird über das elektrische Ventil 19 gesteuert. Der Entlastungsraum ist über einen Ablaufstutzen 20 am Gehäuse 2 mit einem Rücklauf verbunden.The pressure chamber 7 is permanently connected to the connection 3 via a pressure line 4, so that the pressure chamber 7 is constantly under high injection pressure. The needle 5 will controlled via the pressure piece 21 and the control piston 13. The control piston is immersed in a cylinder 14 in which it includes a control pressure chamber 15 at the end. This is in constant connection with connection 3 via a throttle bore 16. Furthermore, a throttle bore 17 leads from the control pressure chamber 15, the outlet thereof opens into a relief chamber 18 via an electric valve 19. The flow through the throttle bore 17 is controlled via the electric valve 19. The relief room is connected to a return via an outlet connection 20 on the housing 2.

Im Betrieb wird das oben beschriebenen Kraftstoffeinspritzventil von dem Kraftstoffhochdruckspeicher über den Anschluß 3 mit Hochdruck versorgt. Dieser ist bestrebt, in Einwirkung auf die Schulter 9 die Kraftstoffeinspritzventilnadel 5 anzuheben, so daß aus dem Druckraum 7 entlang des im Durchmesser kleineren Teils 9 der Einspritzventilnadel Kraftstoff zu den Einspritzöffnungen 12 fließen und dort austreten kann. Diesem Öffnen wirkt die Feder 18 entgegen, die allein jedoch nicht ausreicht, die Einspritzventilnadel 5 bei im Druckraum 7 anstehenden Kraftstoffhochdruck in Schießstellung zu halten, dies aber bei fehlendem Kraftstoffhochdruck tut. Die Aufgabe des Schließens übernimmt weiterhin der Druck im Steuerdruckraum 15, der bei geschlossenem elektrisch betätigten Ventil 19 gleich ist wie der Druck im Druckraum 7. Aufgrund der größeren Stirnfläche des Steuerkolbens 14 überwiegt die Schließkraft und das Ventil bleibt geschlossen. Zur Auslösung der Einspritzung wird das elektrisch betätigte Ventil 19 geöffnet, so daß der Druckraum 15 abgekoppelt durch die Drosselbohrung 16 entlastet wird und somit die Öffnungskraft auf die Schulter 8 überwiegt. Zur Beendigung des Einspritzvorgangs wird das elektrisch betätigte Ventil 10 wieder geschlossen.
In Fig. 2 sind die beiden Ausführungsformen der Erfindung im Schnitt gezeigt. Der obere Teil zeigt eine Ausführungsform mit einer sich in Strömungsrichtung konisch bis zum Kegelsitz des Kugelventils 50 erweiternden Drosselbohrung 31. Die Konuswinkel α werden auf maximalen Druckrückgewinn in der Strömung ausgelegt. Der untere Teil zeigt eine Ausführungsform bei ebenfalls durch die sich in Strömungsrichtung konisch mit dem Winkel α erweiternde Drosselbohrung 17 und zwei in Reihe geschaltene Diffüsoren 30 und 40 maximaler Druckrüickgewinn erzeugt wird.In operation, the fuel injection valve described above is supplied with high pressure from the high-pressure fuel reservoir via connection 3. This strives to raise the fuel injection valve needle 5 in action on the shoulder 9, so that fuel can flow from the pressure chamber 7 along the smaller diameter part 9 of the injection valve needle to the injection openings 12 and exit there. This opening is counteracted by the spring 18, which alone is not sufficient, however, to hold the injection valve needle 5 in the firing position when the fuel pressure is high in the pressure chamber 7, but does so in the absence of high fuel pressure. The task of closing continues to be carried out by the pressure in the control pressure chamber 15, which is the same as the pressure in the pressure chamber 7 when the electrically operated valve 19 is closed. Because of the larger end face of the control piston 14, the closing force predominates and the valve remains closed. To trigger the injection, the electrically operated valve 19 is opened so that the pressure chamber 15 is decoupled from the throttle bore 16 and thus the opening force on the shoulder 8 predominates. To end the injection process, the electrically operated valve 10 is closed again.
2 shows the two embodiments of the invention in section. The upper part shows an embodiment with a throttle bore 31 which widens conically in the flow direction up to the conical seat of the ball valve 50. The cone angles α are designed for maximum pressure recovery in the flow. The lower part shows an embodiment in which the throttle bore 17, which widens conically in the flow direction with the angle α, and two diffusors 30 and 40 connected in series, also produce maximum pressure recovery.

Der Kraftstoff strömt beim Einspritzen aus dem Druckraum 15 in die Drosselbohrung 17 oder 31 und gewinnt dabei an Geschwindigkeit. Gleichzeitig verringert sich der statische Druck in der Strömung. Im Bereich des Diffüsors 30 liegt die Strömung an der Wandung an (vergl. schematische Darstellung der Kraftstoffströmung durch Pfeile in Fig. 1), weitet sich auf und wird gleichzeitig abgebremst. Der zweite Diffusor 40 verstärkt diesen Vorgang, wodurch der statische Druck innerhalb der Strömung in Strömungsrichtung ansteigt. Dieser erhöhte statische Druck unterstützt beim Öffnen des Schaltventils die Bewegung der Ventilkugel 50 in Strömungsrichtung und beschleunigt daher die Zunahme des Kraftstoffflusses durch das Schaltventil. Gleichzeitig verstärkt der erhöhte Kraftstoffluß die Kavitationsneigung am Anfang der Drossel.When injected, the fuel flows from the pressure chamber 15 into the throttle bore 17 or 31 and gaining speed. At the same time, the static pressure in the flow. The flow is present in the area of the diffuser 30 the wall (see schematic representation of the fuel flow by arrows in Fig. 1), expands and is braked at the same time. The second diffuser 40 amplifies this process, causing the static pressure within the flow in Flow direction increases. This increased static pressure supports opening of the switching valve, the movement of the valve ball 50 in the direction of flow and accelerates hence the increase in fuel flow through the switching valve. At the same time The increased fuel flow increases the tendency to cavitation at the beginning of the throttle.

Gemäß einer besonders bevorzugten Ausführungsform ist der Durchmesser des zweiten Diffusors 40 nur geringfügig kleiner als der Durchmesser der Ventilsitzlinie 52 ausgebildet. Dadurch wird bei einer Bewegung der Ventilkugel 50 in Strömungsrichtung (vergl. Doppelpfeil in Fig. 1) ein maximaler Durchflußquerschnitt freigegeben.According to a particularly preferred embodiment, the diameter of the second Diffuser 40 is only slightly smaller than the diameter of the valve seat line 52. This causes the valve ball 50 to move in the direction of flow (cf. double arrow in Fig. 1) released a maximum flow cross-section.

Zur weiteren Verstärkung der Druckrückgewinnung und der Kavitationsneigung ist bevorzugt ferner die Drosselbohrung 15 leicht konisch in Strömungsrichtung erweitert und weist vorzugsweise einen Konuswinkel α bis zu 5° aufTo further increase pressure recovery and cavitation tendency is preferred furthermore, the throttle bore 15 is slightly tapered in the direction of flow and preferably has a cone angle α of up to 5 °

Wie aus der Figur 1 deutlich zu erkennen ist, sind die Drosselbohrung 17, die beiden Diffusoren 30, 40 oder 31 und der Ventilsitz 51 kollinear ausgerichtet und bilden insgesamt einen Trichter, dessen breitere Öffnung durch die Ventilkugel 50 verschlossen bzw. geöffnet wird.As can be clearly seen from FIG. 1, the throttle bore 17 are the two Diffusers 30, 40 or 31 and the valve seat 51 are collinearly aligned and form a total a funnel, the wider opening of which is closed by the valve ball 50 or is opened.

Claims (5)

Kraftstoffeinspritzventil für eine Hochdruckeinspritzung von Kraftstoff aus einer zentralen Hochdruckleitung in Brennräume einer Verbrennungskraftmaschine, das ein Schaltventil (19) mit einem Ventilsitz (51) und einer Ventilkugel (50) umfaßt, wobei die Ventilkugel (50) in geöffnetem Zustand, der von einem mit einer zentralen Hochdruckleitung in Wirkverbindung stehenden Druckraum (15) aus einer Drosselbohrung (17 oder 31) gespeist ist, vom Ventilsitz (51) abgehoben ist,
dadurch gekennzeichnet, daß
der Übergang vom Drosseleinlauf zum Ventilsitz (51) als Diffusor ausgebildet ist.Fuel injection valve for high-pressure injection of fuel from a central high-pressure line into combustion chambers of an internal combustion engine, which comprises a switching valve (19) with a valve seat (51) and a valve ball (50), the valve ball (50) in the open state, which is changed from one with a the central high-pressure line, the pressure chamber (15), which is in operative connection, is fed from a throttle bore (17 or 31) and is lifted off the valve seat (51),
characterized in that
the transition from the throttle inlet to the valve seat (51) is designed as a diffuser. Kraftstoffeinspritzventil nach Anspruch 1, dadurch gekennzeichnet, daß der Diffusor als konischer Diffusor (31), als Stufendiffusor (30, 40) oder als Kombination aus beiden ausgebildet ist, wobei der Diffusor so ausgebildet ist, daß sich die Kraftstoffströmung im wesentlichen an deren Wandung anlegt.Fuel injection valve according to Claim 1, characterized in that the diffuser as a conical diffuser (31), as a step diffuser (30, 40) or as Combination of both is formed, wherein the diffuser is designed such that the fuel flow essentially bears against its wall. Kraftstoffeinspritzventil nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß der Durchmesser beim Übergang in den Sitzkegel vorzugsweise nur geringfügig kleiner als der Sitzdurchmesser (51) ist.Fuel injection valve according to Claim 1 or 2, characterized in that that the diameter at the transition into the seat cone is preferably only slightly is smaller than the seat diameter (51). Kraftstoffeinspritzventil nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß der Diffusor so ausgebildet ist, daß sich die Strömung an die Wand anlegt und ein möglichst großer Druckrückgewinn erreichbar ist.Fuel injection valve according to one of Claims 1 to 3, characterized in that that the diffuser is designed so that the flow to the Creates a wall and the greatest possible pressure recovery can be achieved. Kraftstoffeinspritzventil nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß die Drosselbohrung, der gesamte Diffusor (40) und der Ventilsitz (51) einen Trichter ausbilden, gegenüber dessen Zentrumsöffnung die Ventilkugel bewegbar ist.Fuel injection valve according to one of Claims 1 to 4, characterized in that that the throttle bore, the entire diffuser (40) and the valve seat (51) form a funnel, opposite the center opening of the valve ball is movable.
EP99124112A 1998-12-22 1999-12-02 Fuel injection valve Expired - Lifetime EP1013919B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19859537 1998-12-22
DE19859537A DE19859537A1 (en) 1998-12-22 1998-12-22 Fuel injector

Publications (3)

Publication Number Publication Date
EP1013919A2 true EP1013919A2 (en) 2000-06-28
EP1013919A3 EP1013919A3 (en) 2002-02-13
EP1013919B1 EP1013919B1 (en) 2004-10-20

Family

ID=7892302

Family Applications (1)

Application Number Title Priority Date Filing Date
EP99124112A Expired - Lifetime EP1013919B1 (en) 1998-12-22 1999-12-02 Fuel injection valve

Country Status (4)

Country Link
US (1) US6276335B1 (en)
EP (1) EP1013919B1 (en)
JP (1) JP2000186647A (en)
DE (2) DE19859537A1 (en)

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WO2002014682A1 (en) * 2000-08-11 2002-02-21 Robert Bosch Gmbh Seat valve assembly, in particular for a fuel-injection system of an internal combustion engine
WO2008012133A1 (en) * 2006-07-24 2008-01-31 Robert Bosch Gmbh Servo valve controlled injector for injecting fuel in cylinder combustion chambers of internal combustion engines; in particular common-rail-injectors
WO2008092711A1 (en) * 2007-01-30 2008-08-07 Robert Bosch Gmbh Ball valve with reduced erosion behavior
WO2010060706A1 (en) * 2008-11-27 2010-06-03 Robert Bosch Gmbh Method for producing throttle holes having a low cavitation transition point
WO2012084682A1 (en) * 2010-12-22 2012-06-28 Continental Automotive Gmbh Magnetodynamic actuator and method for actuating a fuel injection valve
EP2290272A3 (en) * 2009-08-27 2013-08-21 Robert Bosch GmbH Cavitation erosion optimised ball seat valve

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JP2003113761A (en) 2001-08-01 2003-04-18 Denso Corp Fuel injection valve
DE10152173A1 (en) * 2001-10-23 2003-04-30 Bosch Gmbh Robert Solenoid valve for controlling an injection valve
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JP5051279B2 (en) * 2009-12-21 2012-10-17 株式会社デンソー Constant residual pressure valve
DE102013214589A1 (en) * 2013-07-25 2015-01-29 Robert Bosch Gmbh Switching valve for a fuel injector
DE102015204255A1 (en) * 2015-03-10 2016-09-15 Robert Bosch Gmbh Fuel injector for a fuel injection system
FR3055370B1 (en) * 2016-09-01 2020-05-01 Delphi Technologies Ip Limited COIL ASSEMBLY

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Cited By (8)

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Publication number Priority date Publication date Assignee Title
WO2002014682A1 (en) * 2000-08-11 2002-02-21 Robert Bosch Gmbh Seat valve assembly, in particular for a fuel-injection system of an internal combustion engine
WO2008012133A1 (en) * 2006-07-24 2008-01-31 Robert Bosch Gmbh Servo valve controlled injector for injecting fuel in cylinder combustion chambers of internal combustion engines; in particular common-rail-injectors
WO2008092711A1 (en) * 2007-01-30 2008-08-07 Robert Bosch Gmbh Ball valve with reduced erosion behavior
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WO2010060706A1 (en) * 2008-11-27 2010-06-03 Robert Bosch Gmbh Method for producing throttle holes having a low cavitation transition point
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EP2290272A3 (en) * 2009-08-27 2013-08-21 Robert Bosch GmbH Cavitation erosion optimised ball seat valve
WO2012084682A1 (en) * 2010-12-22 2012-06-28 Continental Automotive Gmbh Magnetodynamic actuator and method for actuating a fuel injection valve

Also Published As

Publication number Publication date
EP1013919A3 (en) 2002-02-13
DE59910896D1 (en) 2004-11-25
DE19859537A1 (en) 2000-07-06
EP1013919B1 (en) 2004-10-20
JP2000186647A (en) 2000-07-04
US6276335B1 (en) 2001-08-21

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