[go: up one dir, main page]

EP1108136A1 - Common rail injector - Google Patents

Common rail injector

Info

Publication number
EP1108136A1
EP1108136A1 EP00952859A EP00952859A EP1108136A1 EP 1108136 A1 EP1108136 A1 EP 1108136A1 EP 00952859 A EP00952859 A EP 00952859A EP 00952859 A EP00952859 A EP 00952859A EP 1108136 A1 EP1108136 A1 EP 1108136A1
Authority
EP
European Patent Office
Prior art keywords
injector
pressure accumulator
common rail
injection
nozzle
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
EP00952859A
Other languages
German (de)
French (fr)
Other versions
EP1108136B1 (en
Inventor
Jaroslaw Hlousek
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 EP1108136A1 publication Critical patent/EP1108136A1/en
Application granted granted Critical
Publication of EP1108136B1 publication Critical patent/EP1108136B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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
    • 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
    • F02M63/0003—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure
    • F02M63/0007—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure using electrically actuated valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F7/00—Casings, e.g. crankcases
    • F02F2007/0097—Casings, e.g. crankcases for large diesel engines
    • 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
    • F02M2200/30—Fuel-injection apparatus having mechanical parts, the movement of which is damped
    • 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 common rail injector for the injection of fuel in a common rail injection system of an internal combustion engine, in particular a large diesel internal combustion engine, with an injector housing which is connected to a central high-pressure accumulator and in which a nozzle needle against the biasing force of a nozzle spring, which is accommodated in a nozzle spring chamber, is axially displaceable by the injector housing which is connected to a central high-pressure accumulator and in which a nozzle needle against the biasing force of a nozzle spring, which is accommodated in a nozzle spring chamber, is axially displaceable by the
  • a high-pressure pump delivers the fuel to the central one
  • High-pressure accumulator which is referred to as a common rail. High-pressure lines lead from the high-pressure accumulator to the individual injectors, which are assigned to the engine cylinders. The injectors are individually controlled by the engine electronics. The rail pressure is applied to a pressure-balanced 3/2-way solenoid valve, which keeps the high-pressure holes to the conventional injection nozzle depressurized. Only when the solenoid is energized does the 3/2-way solenoid valve open the connection from the rail to the injection nozzle, and the fuel reaches the combustion chamber via the nozzle needle raised against the spring force. The start and end of spraying are thus determined by the start and end of the energization of the magnet. The duration of energization is decisive for the injection quantity.
  • High-pressure accumulators have a negative impact on the starting behavior and the dynamic behavior of the injection system because the time required for a change in the system pressure increases.
  • the object of the invention is to improve the damping behavior in a common rail injection system.
  • the task is with a common rail injector for the injection of fuel in a common rail injection system of an internal combustion engine, in particular a large diesel engine, with one
  • Injector housing which is connected to a central high-pressure accumulator and in which a nozzle needle can be axially displaced against the biasing force of a nozzle spring, which is accommodated in a nozzle spring chamber, in order to adjust the start of injection and the injection quantity depending on the position of a 3/2-way valve , solved in that in the injector housing
  • Injector pressure accumulator is integrated, which is connected to the central high pressure accumulator regardless of the position of the 3/2-way valve.
  • the pressure accumulator serves to dampen the pressure waves emanating from the central pressure accumulator during and after the injection.
  • a special embodiment of the invention is characterized in that the volume of the injector pressure accumulator is 10 to 20 times the maximum injection quantity. This value has proven to be particularly advantageous in tests carried out in the context of the present invention.
  • a further special embodiment of the invention is characterized in that the injector pressure accumulator is connected to an unpressurized space via a damping unit integrated in the injector housing.
  • the total volume of the injector pressure accumulator and the central high pressure accumulator can be as a result of the
  • the damping unit comprises a damping throttle and a safety valve.
  • the central high-pressure accumulator is normally equipped with a safety valve that opens when there is excess pressure. This can e.g. be the case when the system pressure control loop is not working properly. In the event of mechanical failure of the safety valve controlled by the system pressure control loop, major damage can occur to the internal combustion engine. System security is increased by integrating the safety valve into the injector housing.
  • the safety valve normally provided on the central high-pressure accumulator can be omitted.
  • Screw plug is integrated, which is screwed into the injector housing between the nozzle spring chamber and the injector pressure accumulator.
  • This embodiment has the advantage that it can be implemented particularly simply and inexpensively.
  • Another particular embodiment of the invention is characterized in that the injector pressure accumulator is connected to a fuel tank via the damping unit integrated in the injector housing. This provides the advantage that the injector pressure accumulator is relieved to the fuel tank if the pressure in the injector accumulator is greater than the system pressure.
  • the figure shows an embodiment of an injector 1 according to the invention in longitudinal section.
  • a conventional injection nozzle 2 is formed at the end of the injector 1 which is directed downward in the figure.
  • the solenoid valve 3 is controlled by a control unit 4.
  • the control unit 4 is coupled to a central high-pressure accumulator 5 and a fuel pump unit 6.
  • the fuel pump unit 6 delivers fuel from a fuel tank 7 into the central high-pressure accumulator 5.
  • the fuel delivered in the fuel pump unit is subjected to high pressure.
  • the fuel pressurized with high pressure comes from the central high pressure accumulator 5 via a
  • An injector pressure accumulator 10 is formed in the injector housing 9.
  • the injector pressure accumulator 10 is covered by a section of a longitudinal bore through the injector housing 9 educated.
  • the injector pressure accumulator 10 is connected to the central high pressure accumulator 5 via the high pressure line 8.
  • the end of the injector pressure accumulator 10 facing away from the injection nozzle 2 opens into a valve bore 11 which extends transversely to the longitudinal axis of the injector 1.
  • a valve piston 12 is received in the valve bore 11.
  • the valve piston 12 is axially displaceable in the valve bore 11 between two valve positions, which are defined by valve seats 13 and 14.
  • valve spring 22 which is accommodated in a valve spring chamber 21, pushes the valve piston 12 to the right.
  • the injector pressure accumulator 10 is connected to the fuel tank 7 via an unpressurized drain line 15.
  • the solenoid valve 3 When the solenoid valve 3 is energized, the valve piston 12 moves against the biasing force of the valve spring 22 to the left.
  • the connection between the injector pressure accumulator 10 and the unpressurized drain line 15 is closed and a connection between the
  • Injector pressure accumulator 10 released via the valve bore 11 to a high pressure bore 16.
  • the high-pressure fuel can pass through the high-pressure bore 16 from the injector pressure accumulator 10 to the injection nozzle 2.
  • a nozzle needle 17 can be moved back and forth against the biasing force of a nozzle spring 18.
  • the nozzle spring 18 is accommodated in a nozzle spring chamber 19, which is formed by a section of the longitudinal bore through the injector housing 9.
  • the nozzle spring chamber 19 is connected to the valve spring chamber 21 via a bore 20.
  • the valve spring chamber 21 in turn is connected to the drain line via a bore 23 J th 1 CD L ⁇ o ⁇ ⁇

Landscapes

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

Abstract

The invention relates to a common rail injector for injecting fuel in a common rail injection system of an internal combustion engine, especially a large diesel engine, comprising an injector housing (9), which is connected to a central high pressure reservoir (5) and in which a nozzle needle (17) can be axially displaced against the prestressing force of a nozzle spring (18) in order to regulate the beginning of the injection process and the injection quantity according to the position of a 3/2-way valve (3). Said nozzle spring is located in a nozzle spring chamber (19). The aim of the invention is to improve the damping behaviour in a common rail injection system. To this end, an injector pressure reservoir (10) is integrated into the injector housing (9). Said injector pressure reservoir (10) is connected to the central high pressure reservoir (5) independently of the position of the 3/2-way valve (3).

Description

Common-Raii- InjektorCommon Raii injector
Stand der TechnikState of the art
Die Erfindung betrifft einen Common-Rail-Injektor zur Einspritzung von Kraftstoff in einem Common-Rail- Einspritzsystem einer Brennkraftmaschine, insbesondere einer Großdieselbrennkraftmaschine, mit einem Injektorgehäuse, das mit einem zentralen Hochdruckspeicher in Verbindung steht und in dem eine Düsennadel gegen die Vorspannkraft einer Düsenfeder, die in einem Düsenfederraum aufgenommen ist, axial verschiebbar ist, um denThe invention relates to a common rail injector for the injection of fuel in a common rail injection system of an internal combustion engine, in particular a large diesel internal combustion engine, with an injector housing which is connected to a central high-pressure accumulator and in which a nozzle needle against the biasing force of a nozzle spring, which is accommodated in a nozzle spring chamber, is axially displaceable by the
Spritzbeginn und die Einspritzmenge in Abhängigkeit von der Stellung eines 3/2-Wegeventils einzustellen.Start spraying and the injection quantity depending on the position of a 3/2-way valve.
In Common-Rail-Einspritzsystemen fördert eine Hochdruckpumpe den Kraftstoff in den zentralenIn common rail injection systems, a high-pressure pump delivers the fuel to the central one
Hochdruckspeicher, der als Common-Rail bezeichnet wird. Von dem Hochdruckspeicher führen Hochdruckleitungen zu den einzelnen Injektoren, die den Motorzylindern zugeordnet sind. Die Injektoren werden einzeln von der Motorelektronik angesteuert. Der Raildruck steht an einem druckausgeglichenen 3/2-Wegemagnetventil an, das die Hochdruckbohrungen zur konventionellen Einspritzdüse drucklos hält. Erst bei einer Bestromung des Magneten öffnet das 3/2-Wegemagnetventil die Verbindung vom Rail zur Einspritzdüse, und der Kraftstoff gelangt über die gegen die Federkraft angehobene Düsennadel in den Verbrennungsraum. Spritzbeginn und Spritzende werden also durch Beginn und Ende der Bestromung des Magneten bestimmt. Die Bestromungsdauer ist maßgebend für die Einspritzmenge.High-pressure accumulator, which is referred to as a common rail. High-pressure lines lead from the high-pressure accumulator to the individual injectors, which are assigned to the engine cylinders. The injectors are individually controlled by the engine electronics. The rail pressure is applied to a pressure-balanced 3/2-way solenoid valve, which keeps the high-pressure holes to the conventional injection nozzle depressurized. Only when the solenoid is energized does the 3/2-way solenoid valve open the connection from the rail to the injection nozzle, and the fuel reaches the combustion chamber via the nozzle needle raised against the spring force. The start and end of spraying are thus determined by the start and end of the energization of the magnet. The duration of energization is decisive for the injection quantity.
Im Betrieb des Einspritzsystems treten Druckwellen auf, die in dem zentralen Hochdruckspeicher gedämpft werden. Um eine gute Dämpfungswirkung zu erzielen, muss das Volumen des zentralen Hochdruckspeichers ausreichend dimensioniert sein. Mit zunehmenden Volumen des zentralenDuring the operation of the injection system, pressure waves occur which are damped in the central high-pressure accumulator. In order to achieve a good damping effect, the volume of the central high-pressure accumulator must be large enough. With increasing volume of the central
Hochdruckspeichers werden jedoch das Startverhalten und das dynamische Verhalten des Einspritzsystems negativ beeinflusst, weil die für eine Änderung des Systemdrucks erforderliche Zeit zunimmt.High-pressure accumulators, however, have a negative impact on the starting behavior and the dynamic behavior of the injection system because the time required for a change in the system pressure increases.
Aufgabe der Erfindung ist, das Dämpfungsverhalten in einem Common-Rail-Einspritzsystem zu verbessern.The object of the invention is to improve the damping behavior in a common rail injection system.
Die Aufgabe ist bei einem Common-Rail-Injektor zur Einspritzung von Kraftstoff in einem Common-Rail- Einspritzsystem einer Brennkraftmaschine, insbesondere einer Großdieselbrennkraftmaschine, mit einemThe task is with a common rail injector for the injection of fuel in a common rail injection system of an internal combustion engine, in particular a large diesel engine, with one
Injektorgehäuse, das mit einem zentralen Hochdruckspeicher in Verbindung steht und in dem eine Düsennadel gegen die Vorspannkraft einer Düsenfeder, die in einem Düsenfederraum aufgenommen ist, axial verschiebbar ist, um den Spritzbeginn und die Einspritzmenge in Abhängigkeit von der Stellung eines 3/2-Wegeventils einzustellen, dadurch gelöst, dass in das Injektorgehäuse einInjector housing, which is connected to a central high-pressure accumulator and in which a nozzle needle can be axially displaced against the biasing force of a nozzle spring, which is accommodated in a nozzle spring chamber, in order to adjust the start of injection and the injection quantity depending on the position of a 3/2-way valve , solved in that in the injector housing
Injektordruckspeicher integriert ist, der unabhängig von der Stellung des 3/2-Wegeventils mit dem zentralen Hochdruckspeicher in Verbindung steht. Der Druckspeicher dient dazu, die während und nach der Einspritzung von dem zentralen Druckspeicher ausgehenden Druckwellen zu dämpfen.Injector pressure accumulator is integrated, which is connected to the central high pressure accumulator regardless of the position of the 3/2-way valve. The pressure accumulator serves to dampen the pressure waves emanating from the central pressure accumulator during and after the injection.
Eine besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, dass das Volumen des Injektordruckspeichers das 10- bis 20-Fache der maximalen Einspritzmenge beträgt. Dieser Wert hat sich bei im Rahmen der vorliegenden Erfindung durchgeführten Versuchen als besonders vorteilhaft erwiesen.A special embodiment of the invention is characterized in that the volume of the injector pressure accumulator is 10 to 20 times the maximum injection quantity. This value has proven to be particularly advantageous in tests carried out in the context of the present invention.
Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, dass der Injektordruckspeicher über eine in das Injektorgehäuse integrierte Dämpfungseinheit mit einem drucklosen Raum in Verbindung steht. Das Gesamtvolumen des Injektordruckspeichers und des zentralen Hochdruckspeichers kann in Folge der mit derA further special embodiment of the invention is characterized in that the injector pressure accumulator is connected to an unpressurized space via a damping unit integrated in the injector housing. The total volume of the injector pressure accumulator and the central high pressure accumulator can be as a result of the
Dämpfungseinheit erzielten Dämpfung erheblich reduziert werden.Damping unit damping achieved can be significantly reduced.
Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, dass die Dämpfungseinheit eine Dämpfungsdrossel und ein Sicherheitsventil umfasst . Normalerweise ist der zentrale Hochdruckspeicher mit einem Sicherheitsventil ausgestattet, das bei Überdruck öffnet. Das kann z.B. der Fall sein, wenn der Systemdruckregelkreis nicht richtig funktioniert. Bei einem eventuellen mechanischen Versagen des von dem Systemdruckregelkreis gesteuerten Sicherheitsventils können an der Brennkraftmaschine große Schäden auftreten. Durch die Integration des Sicherheitsventils in das Injektorgehäuse wird die Systemsicherheit erhöht. Außerdem kann das normalerweise an dem zentralen Hochdruckspeicher vorgesehene Sicherheitsventil entfallen.Another special embodiment of the invention is characterized in that the damping unit comprises a damping throttle and a safety valve. The central high-pressure accumulator is normally equipped with a safety valve that opens when there is excess pressure. This can e.g. be the case when the system pressure control loop is not working properly. In the event of mechanical failure of the safety valve controlled by the system pressure control loop, major damage can occur to the internal combustion engine. System security is increased by integrating the safety valve into the injector housing. In addition, the safety valve normally provided on the central high-pressure accumulator can be omitted.
Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, dass die Dämpfungsdrossel in eineAnother special embodiment of the invention is characterized in that the damping throttle in one
Verschlussschraube integriert ist, die zwischen dem Düsenfederraum und dem Injektordruckspeicher in das Injektorgehäuse eingeschraubt ist. Diese Ausführungsart hat den Vorteil, dass sie besonders einfach und kostengünstig realisiert werden kann. Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, dass der Injektordruckspeicher über die in das Injektorgehäuse integrierte Dämpfungseinheit mit einem Kraftstofftank in Verbindung steht. Das liefert den Vorteil, dass der Injektordruckspeicher zum Kraftstofftank entlastet wird, wenn der Druck in dem Injektorspeicher größer als der Systemdruck ist .Screw plug is integrated, which is screwed into the injector housing between the nozzle spring chamber and the injector pressure accumulator. This embodiment has the advantage that it can be implemented particularly simply and inexpensively. Another particular embodiment of the invention is characterized in that the injector pressure accumulator is connected to a fuel tank via the damping unit integrated in the injector housing. This provides the advantage that the injector pressure accumulator is relieved to the fuel tank if the pressure in the injector accumulator is greater than the system pressure.
Weitere Vorteile, Merkmale und Einzelheiten der Erfindung ergeben sich aus der nachfolgenden Beschreibung, in der unter Bezugnahme auf die Zeichnung ein Ausführungsbeispiel der Erfindung im Einzelnen beschrieben ist. Dabei können die in den Ansprüchen und in der Beschreibung erwähnten Merkmale jeweils einzeln für sich oder in beliebiger Kombination erfindungswesentlich sein.Further advantages, features and details of the invention result from the following description, in which an embodiment of the invention is described in detail with reference to the drawing. The features mentioned in the claims and in the description can each be essential to the invention individually or in any combination.
Die Figur zeigt eine Ausführungsform eines erfindungsgemäßen Injektors 1 im Längsschnitt. An dem in der Figur nach unten gerichteten Ende des Injektors 1 ist eine herkömmliche Einspritzdüse 2 ausgebildet. An dem anderen Ende des Injektors 1 befindet sich ein Magnetventil 3. Das Magnetventil 3 wird durch eine Steuereinheit 4 gesteuert. Die Steuereinheit 4 ist mit einem zentralen Hochdruckspeicher 5 und einer Kraftstoffpumpeneinheit 6 gekoppelt. Die Kraftstoffpumpeneinheit 6 fördert Kraftstoff aus einem Kraftstofftank 7 in den zentralen Hochdruckspeicher 5. Gleichzeitig wird der geförderte Kraftstoff in der Kraftstoffpumpeneinheit mit Hochdruck beaufschlagt. Der mit Hochdruck beaufschlagte Kraftstoff gelangt aus dem zentralen Hochdruckspeicher 5 über eineThe figure shows an embodiment of an injector 1 according to the invention in longitudinal section. A conventional injection nozzle 2 is formed at the end of the injector 1 which is directed downward in the figure. At the other end of the injector 1 there is a solenoid valve 3. The solenoid valve 3 is controlled by a control unit 4. The control unit 4 is coupled to a central high-pressure accumulator 5 and a fuel pump unit 6. The fuel pump unit 6 delivers fuel from a fuel tank 7 into the central high-pressure accumulator 5. At the same time, the fuel delivered in the fuel pump unit is subjected to high pressure. The fuel pressurized with high pressure comes from the central high pressure accumulator 5 via a
Hochdruckleitung 8 in ein längliches Injektorgehäuse 9, das den Grundkörper des Injektors 1 darstellt.High-pressure line 8 in an elongated injector housing 9, which represents the main body of the injector 1.
In dem Injektorgehäuse 9 ist ein Injektordruckspeicher 10 ausgebildet. Der Injektordruckspeicher 10 wird von einem Abschnitt einer Längsbohrung durch das Injektorgehäuse 9 gebildet. Der Injektordruckspeicher 10 steht über die Hochdruckleitung 8 mit dem zentralen Hochdruckspeicher 5 in Verbindung. Das von der Einspritzdüse 2 abgewandte Ende des Injektordruckspeichers 10 mündet in eine Ventilbohrung 11, die sich quer zur Längsachse des Injektors 1 erstreckt. In der Ventilbohrung 11 ist ein Ventilkolben 12 aufgenommen. Der Ventilkolben 12 ist zwischen zwei Ventilstellungen, die durch Ventilsitze 13 und 14 definiert sind, in der Ventilbohrung 11 axial verschiebbar.An injector pressure accumulator 10 is formed in the injector housing 9. The injector pressure accumulator 10 is covered by a section of a longitudinal bore through the injector housing 9 educated. The injector pressure accumulator 10 is connected to the central high pressure accumulator 5 via the high pressure line 8. The end of the injector pressure accumulator 10 facing away from the injection nozzle 2 opens into a valve bore 11 which extends transversely to the longitudinal axis of the injector 1. A valve piston 12 is received in the valve bore 11. The valve piston 12 is axially displaceable in the valve bore 11 between two valve positions, which are defined by valve seats 13 and 14.
Durch die Vorspannkraft einer Ventilfeder 22, die in einem Ventilfederraum 21 aufgenommen ist, wird der Ventilkolben 12 nach rechts gedrückt. In dieser Ventilstellung steht der Injektordruckspeicher 10 über eine drucklose Ablaufleitung 15 mit dem Kraftstofftank 7 in Verbindung. Wenn das Magnetventil 3 bestromt wird, verschiebt sich der Ventilkolben 12 gegen die Vorspannkraft der Ventilfeder 22 nach links. Dabei wird die Verbindung zwischen dem Injektordruckspeicher 10 und der drucklosen Ablaufleitung 15 geschlossen und eine Verbindung zwischen demThe biasing force of a valve spring 22, which is accommodated in a valve spring chamber 21, pushes the valve piston 12 to the right. In this valve position, the injector pressure accumulator 10 is connected to the fuel tank 7 via an unpressurized drain line 15. When the solenoid valve 3 is energized, the valve piston 12 moves against the biasing force of the valve spring 22 to the left. The connection between the injector pressure accumulator 10 and the unpressurized drain line 15 is closed and a connection between the
Injektordruckspeicher 10 über die Ventilbohrung 11 zu einer Hochdruckbohrung 16 freigegeben.Injector pressure accumulator 10 released via the valve bore 11 to a high pressure bore 16.
Durch die Hochdruckbohrung 16 kann der mit Hochdruck beaufschlagte Kraftstoff aus dem Injektordruckspeicher 10 zur Einspritzdüse 2 gelangen. In der Einspritzdüse 2 ist eine Düsennadel 17 gegen die Vorspannkraft einer Düsenfeder 18 hin- und herbewegbar. Die Düsenfeder 18 ist in einem Düsenfederraum 19 aufgenommen, der von einem Abschnitt der Längsbohrung durch das Injektorgehäuse 9 gebildet wird.The high-pressure fuel can pass through the high-pressure bore 16 from the injector pressure accumulator 10 to the injection nozzle 2. In the injection nozzle 2, a nozzle needle 17 can be moved back and forth against the biasing force of a nozzle spring 18. The nozzle spring 18 is accommodated in a nozzle spring chamber 19, which is formed by a section of the longitudinal bore through the injector housing 9.
Wenn der Druck ausreicht, um die Düsennadel 17 von ihrem Sitz abzuheben, wird der Kraftstoff eingespritzt.When the pressure is sufficient to lift the nozzle needle 17 from its seat, the fuel is injected.
Der Düsenfederraum 19 steht über eine Bohrung 20 mit dem Ventilfederraum 21 in Verbindung. Der Ventilfederraum 21 wiederum steht über eine Bohrung 23 mit der Ablaufleitung J t h1 CD LΠ o Π σThe nozzle spring chamber 19 is connected to the valve spring chamber 21 via a bore 20. The valve spring chamber 21 in turn is connected to the drain line via a bore 23 J th 1 CD LΠ o Π σ
ς pJ:ς pJ:
3"3 '
Φ aΦ a
PJ a aPJ a a
PJPJ
ΩΩ
3" 3 "
(ϋ w(ϋ w
H- a cnH- a cn
Ό μ- rrΌ μ- rr
NN
C a tQC a tQ

Claims

Ansprüche Expectations
1. Common-Rail -Injektor zur Einspritzung von Kraftstoff in einem Common-Rail-Einspritzsystem einer Brennkraftmaschine, insbesondere einer Großdieselbrennkraftmaschine, mit einem Injektorgehäuse (9), das mit einem zentralen Hochdruckspeicher (5) in Verbindung steht und in dem eine Düsennadel (17) gegen die Vorspannkraft einer Düsenfeder (18), die in einem Düsenfederraum (19) aufgenommen ist, axial verschiebbar ist, um den Spritzbeginn und die Einspritzmenge in Abhängigkeit von der Stellung eines 3/2- Wegeventils (3) einzustellen, dadurch gekennzeichnet, dass in das Injektorgehäuse (9) ein Injektordruckspeicher (10) integriert ist, der unabhängig von der Stellung des 3/2- Wegeventils (3) mit dem zentralen Hochdruckspeicher (5) in Verbindung steht .1. Common rail injector for the injection of fuel in a common rail injection system of an internal combustion engine, in particular a large diesel internal combustion engine, with an injector housing (9) which is connected to a central high pressure accumulator (5) and in which a nozzle needle (17 ) against the biasing force of a nozzle spring (18), which is accommodated in a nozzle spring chamber (19), is axially displaceable in order to adjust the start of injection and the injection quantity depending on the position of a 3/2-way valve (3), characterized in that an injector pressure accumulator (10) is integrated into the injector housing (9) and is connected to the central high pressure accumulator (5) regardless of the position of the 3/2-way valve (3).
2. Injektor nach Anspruch 1, dadurch gekennzeichnet, dass das Volumen des Injektordruckspeichers (10) das 10- bis 20- Fache der maximalen Einspritzmenge beträgt.2. Injector according to claim 1, characterized in that the volume of the injector pressure accumulator (10) is 10 to 20 times the maximum injection quantity.
3. Injektor nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Injektordruckspeicher (10) über eine in das Injektorgehäuse (9) integrierte Dämpfungseinheit (25, 26, 27) mit einem drucklosen Raum (19) in Verbindung steht.3. Injector according to one of the preceding claims, characterized in that the injector pressure accumulator (10) is connected to a pressure-free space (19) via a damping unit (25, 26, 27) integrated in the injector housing (9).
4. Injektor nach Anspruch 3, dadurch gekennzeichnet, dass die Dämpfungseinheit eine Dämpfungsdrossel (26) und ein Sicherheitsventil (27) umfasst.4. Injector according to claim 3, characterized in that the damping unit has a damping throttle (26) and a Safety valve (27) comprises.
5. Injektor nach Anspruch 4, dadurch gekennzeichnet, dass die Dämpfungsdrossel (26) in eine Vεrschlussschraube (25) integriert ist, die zwischen dem Düsenfederraum (19) und dem Injektordruckspeicher (10) in das Injektorgehäuse (9) eingeschraubt ist .5. Injector according to claim 4, characterized in that the damping throttle (26) is integrated in a Vεrschluß Screw (25) which is screwed between the nozzle spring chamber (19) and the injector pressure accumulator (10) in the injector housing (9).
6. Injektor nach Anspruch 4 oder 5, dadurch gekennzeichnet, dass der Injektordruckspeicher (10) über die in das6. Injector according to claim 4 or 5, characterized in that the injector pressure accumulator (10) via the in the
Injektorgehäuse (9) integrierte Dämpfungseinheit (25, 26, 27) mit einem Kraftstofftank (7) in Verbindung steht. Injector housing (9) integrated damping unit (25, 26, 27) is connected to a fuel tank (7).
EP00952859A 1999-06-24 2000-06-21 Common rail injector Expired - Lifetime EP1108136B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19928906A DE19928906A1 (en) 1999-06-24 1999-06-24 Common rail injector
DE19928906 1999-06-24
PCT/DE2000/002028 WO2001000986A1 (en) 1999-06-24 2000-06-21 Common rail injector

Publications (2)

Publication Number Publication Date
EP1108136A1 true EP1108136A1 (en) 2001-06-20
EP1108136B1 EP1108136B1 (en) 2005-02-09

Family

ID=7912355

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00952859A Expired - Lifetime EP1108136B1 (en) 1999-06-24 2000-06-21 Common rail injector

Country Status (5)

Country Link
US (1) US6561165B1 (en)
EP (1) EP1108136B1 (en)
JP (1) JP2003503629A (en)
DE (2) DE19928906A1 (en)
WO (1) WO2001000986A1 (en)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10060811A1 (en) * 2000-12-07 2002-06-13 Bosch Gmbh Robert Fuel injection system for internal combustion engines
DE10060812A1 (en) * 2000-12-07 2002-06-13 Bosch Gmbh Robert Fuel injection system for internal combustion engines
DE10103089A1 (en) 2001-01-24 2002-08-08 Bosch Gmbh Robert 3/2-way valve
DE10105031A1 (en) * 2001-02-05 2002-08-14 Bosch Gmbh Robert Device for damping pressure pulsations in high-pressure injection systems
DE10348291B4 (en) * 2003-10-17 2012-06-06 Mtu Friedrichshafen Gmbh Device for fastening a fuel injector for an internal combustion engine
US6997165B2 (en) * 2003-12-19 2006-02-14 Caterpillar Inc. Pressure control valve for a fuel system
WO2006081829A1 (en) * 2005-02-02 2006-08-10 Man Diesel A/S A large two-stroke diesel engine with hydraulically actuated exhaust gas valves
CN101487405B (en) * 2005-02-02 2012-05-30 曼柴油机和涡轮公司,德国曼柴油机和涡轮欧洲股份公司的联营公司 Crosshead type large two-stroke diesel engine
US8474437B2 (en) * 2007-08-21 2013-07-02 Toyota Jidosha Kabushiki Kaisha Fuel injection controlling apparatus of internal combustion engine
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

Family Cites Families (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4246876A (en) * 1979-01-19 1981-01-27 Stanadyne, Inc. Fuel injection system snubber valve assembly
US4306680A (en) * 1980-05-12 1981-12-22 General Motors Corporation Compression operated injector
AT378242B (en) 1981-07-31 1985-07-10 Berchtold Max Prof FUEL INJECTION SYSTEM FOR INTERNAL COMBUSTION ENGINES, ESPECIALLY DIESEL ENGINES
DE3151065C2 (en) 1981-12-23 1986-03-20 Daimler-Benz Ag, 7000 Stuttgart Fuel injector for internal combustion engines
JPS60192872A (en) * 1984-03-15 1985-10-01 Nippon Denso Co Ltd Accumulator type fuel injection valve
DE3521427A1 (en) * 1985-06-14 1986-12-18 Robert Bosch Gmbh, 7000 Stuttgart FUEL INJECTION DEVICE
JP2550528B2 (en) * 1986-06-12 1996-11-06 トヨタ自動車株式会社 Fuel injection device for internal combustion engine
JPS6371561A (en) * 1986-09-13 1988-03-31 Kubota Ltd Diesel engine accumulator fuel injector
US4911127A (en) * 1989-07-12 1990-03-27 Cummins Engine Company, Inc. Fuel injector for an internal combustion engine
US5012786A (en) * 1990-03-08 1991-05-07 Voss James R Diesel engine fuel injection system
US5295469A (en) * 1990-07-09 1994-03-22 Nippondenso Co., Ltd. Safety valve for fuel injection apparatus
JP3191562B2 (en) * 1994-05-23 2001-07-23 トヨタ自動車株式会社 Combustion method for compression ignition type internal combustion engine
DE4341545A1 (en) * 1993-12-07 1995-06-08 Bosch Gmbh Robert Fuel injection device for internal combustion engines
DE4341543A1 (en) * 1993-12-07 1995-06-08 Bosch Gmbh Robert Fuel injection device for internal combustion engines
DE4417950C1 (en) * 1994-05-21 1995-05-11 Mtu Friedrichshafen Gmbh Injection system
DE4427378C2 (en) * 1994-08-03 1996-07-11 Bosch Gmbh Robert Solenoid valve-controlled injection nozzle for fuel injection into the combustion chamber of a diesel engine
DE19715234A1 (en) * 1997-04-12 1998-06-25 Daimler Benz Ag Valve for fuel injection system of internal combustion engine
DE19716220B4 (en) 1997-04-18 2007-08-23 Robert Bosch Gmbh Fuel injection unit for internal combustion engines

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO0100986A1 *

Also Published As

Publication number Publication date
DE50009469D1 (en) 2005-03-17
JP2003503629A (en) 2003-01-28
WO2001000986A1 (en) 2001-01-04
US6561165B1 (en) 2003-05-13
DE19928906A1 (en) 2001-01-11
EP1108136B1 (en) 2005-02-09

Similar Documents

Publication Publication Date Title
EP2016278B1 (en) Pressure control valve with limp-home and ventilation function
DE102007062176A1 (en) Pressure control valve for regulating the pressure in a high pressure fuel accumulator
WO2005075811A1 (en) Fuel injector with a direct controlled injection valve member
DE4414242A1 (en) Fuel injection device for internal combustion engines
DE19939418A1 (en) Fuel injection system for an internal combustion engine
DE19630938C2 (en) Fuel supply line with a volume flow control valve and volume flow control valve
DE19939420A1 (en) Fuel injection method and system for an internal combustion engine
EP1125045B1 (en) Fuel injection system for an internal combustion engine
EP1108136A1 (en) Common rail injector
EP1466087A1 (en) Injector for high pressure fuel injection
DE102017201580A1 (en) Non-return throttle valve for a high-pressure accumulator
WO2001031193A2 (en) Fuel injector with integrated flow restrictor
WO2009098112A1 (en) Compact injection device with reduced tendency to form vapor bubbles
DE19939425B4 (en) Fuel injection system for an internal combustion engine
EP1144842A1 (en) Injector for a fuel injection system for internal combustion engines comprising an injector needle that projects into the valve control space
DE19923421C2 (en) injector
DE102007029969A1 (en) Fast-acting fuel injector for high injection pressures
DE10334615A1 (en) Pressure control valve for storage fuel injection system
EP2733345A1 (en) Pressure control valve for a high pressure storage tank of a combustion engine
EP1115968B1 (en) Common rail injector
DE19839579C1 (en) Two=stage filtering system for fuel supply to injectors
DE102007001365A1 (en) Common rail injector, for injecting e.g. petrol, into combustion chamber of internal combustion engine, has switching chamber connected with low pressure area by connecting channel that is closed and opened by control valve
DE19963370A1 (en) Pump injector unit with pre-injection
EP1503073B1 (en) Unit injector
DE19952511B4 (en) Common rail injector

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE

AX Request for extension of the european patent

Free format text: AL;LT;LV;MK;RO;SI

17P Request for examination filed

Effective date: 20010704

17Q First examination report despatched

Effective date: 20040129

RBV Designated contracting states (corrected)

Designated state(s): DE FR GB IT

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB IT

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: GERMAN

REF Corresponds to:

Ref document number: 50009469

Country of ref document: DE

Date of ref document: 20050317

Kind code of ref document: P

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 20050517

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

ET Fr: translation filed
26N No opposition filed

Effective date: 20051110

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20090618

Year of fee payment: 10

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20090623

Year of fee payment: 10

Ref country code: DE

Payment date: 20090825

Year of fee payment: 10

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20090627

Year of fee payment: 10

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20100621

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20110228

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20100621

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20110101

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20100630

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20100621