EP0149598A2 - Injection nozzle for injection internal combustion engines - Google Patents

Injection nozzle for injection internal combustion engines Download PDF

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Publication number
EP0149598A2
EP0149598A2 EP85890010A EP85890010A EP0149598A2 EP 0149598 A2 EP0149598 A2 EP 0149598A2 EP 85890010 A EP85890010 A EP 85890010A EP 85890010 A EP85890010 A EP 85890010A EP 0149598 A2 EP0149598 A2 EP 0149598A2
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EP
European Patent Office
Prior art keywords
pressure
space
piston
control
chamber
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
EP85890010A
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German (de)
French (fr)
Other versions
EP0149598B1 (en
EP0149598A3 (en
Inventor
Jaroslaw Dipl. -Ing. 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.)
Voestalpine Metal Forming GmbH
Original Assignee
Voestalpine Metal Forming GmbH
Friedmann and Maier AG
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Publication date
Application filed by Voestalpine Metal Forming GmbH, Friedmann and Maier AG filed Critical Voestalpine Metal Forming GmbH
Publication of EP0149598A2 publication Critical patent/EP0149598A2/en
Publication of EP0149598A3 publication Critical patent/EP0149598A3/en
Application granted granted Critical
Publication of EP0149598B1 publication Critical patent/EP0149598B1/en
Expired legal-status Critical Current

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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
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/02—Injectors structurally combined with fuel-injection pumps
    • F02M57/022—Injectors structurally combined with fuel-injection pumps characterised by the pump drive
    • F02M57/025—Injectors structurally combined with fuel-injection pumps characterised by the pump drive hydraulic, e.g. with pressure amplification
    • F02M57/026—Construction details of pressure amplifiers, e.g. fuel passages or check valves arranged in the intensifier piston or head, particular diameter relationships, stop members, arrangement of ports or conduits
    • 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
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/02—Injectors structurally combined with fuel-injection pumps
    • F02M57/022—Injectors structurally combined with fuel-injection pumps characterised by the pump drive
    • F02M57/025—Injectors structurally combined with fuel-injection pumps characterised by the pump drive hydraulic, e.g. with pressure amplification
    • 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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • F02M59/105—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive hydraulic drive
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/20—Closing valves mechanically, e.g. arrangements of springs or weights or permanent magnets; Damping of valve lift
    • F02M61/205—Means specially adapted for varying the spring tension or assisting the spring force to close the injection-valve, e.g. with damping of valve lift
    • 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

Definitions

  • the invention relates to an injection nozzle for injection internal combustion engines with a pump for supplying the nozzle with fuel under predetermined pressure, in which the nozzle needle is immersed in a space that can be filled with fuel under pressure and held in the closed position and by the pressure in this space and a spring Pressure relief of this room can be opened.
  • a device can be found, for example, in DE-OS 27 56 088.
  • the filling of the nozzle needle chamber takes place as a function of the actuation of a multi-way valve, the filling process being ended in one position of this multi-way valve and pressure relief of the immersion chamber taking place at the same time.
  • the fuel can only be injected under the pressure at which it is made available to the storage space or the nozzle needle space.
  • the invention now aims to provide an injection nozzle of the type mentioned at the outset, with which the injection process can be controlled in a simple manner as a function of operating variables and the injection can take place even under a pressure which is higher than the pump pressure.
  • the invention consists essentially in the fact that the immersion space of the nozzle needle is connected to a high-pressure chamber via an outward opening check valve, that the high-pressure space is connected to a nozzle needle chamber, the effective area of the nozzle needle in the opening sense being multiplied by that Pump pressure is less than the sum of the effective area of the nozzle needle in the closing direction multiplied by the pump pressure and the force of the nozzle needle spring acting in the closing direction, that one end of a high-pressure piston is immersed in the high-pressure chamber, the other end of which is immersed in a control chamber, that in the control room Control piston is guided such that the control piston can be acted upon by the pump pressure on its side facing away from the control chamber, the effective cross section of the control piston being greater than the effective
  • the immersion space of the nozzle needle is connected to a high-pressure space via a check valve opening towards a high-pressure space
  • the pressure in the high-pressure chamber is increased by immersing the high-pressure piston in a control chamber, which in turn can be acted upon by the pump pressure via a throttle.
  • a correspondingly larger control piston can be brought into abutment against the high-pressure piston and, depending on the selected area difference of the high-pressure piston and the effective area of the control piston, a corresponding pressure build-up in the high-pressure chamber takes place when the pressure in the control chamber is relieved.
  • the nozzle needle is now lifted off due to the increased fuel pressure in the high-pressure chamber, this pressure increase being triggered indirectly by the pressure relief in the control chamber.
  • the pressure increase and the opening of the nozzle needle are controlled.
  • Controllable valve which is connected to the control chamber, can be designed in a manner known per se as a solenoid valve.
  • a shock-free system of the H ochtikkolbens ensure on the control piston, the configuration is devised in an advantageous manner so that the high pressure piston resiliently urged in the direction of the control piston is.
  • the immersion space of the nozzle needle can also accommodate the nozzle needle spring in a structurally particularly simple manner and can be designed as a nozzle needle spring space.
  • the design is advantageously made such that the high-pressure piston has at least one axial bore closed on one side and at least one radial bore connected to this axial bore, the open end of the axial bore opens into the high-pressure chamber, and the radial bore can be connected to the pressure line of the pump or the return line after a predetermined stroke of the high-pressure piston.
  • the injection process is ended by lowering the fuel pressure in the high-pressure chamber to a level at which the equilibrium position forces the nozzle needle to close.
  • a particularly rapid closing of the nozzle needle can be achieved in that the pressure equilibrium is not established against the pressure line of the pump, but by deriving the pressure into the return line.
  • a control device can be provided in a simple manner, which, depending on operating variables, e.g. Speed boost pressure or temperature or engine load, emits a signal for the excitation of the solenoid valve.
  • FIG. 1 shows a first embodiment of the injection nozzle according to the invention schematically in section
  • FIG. 2 shows a modified embodiment of the injection nozzle without the supply of fuel under pressure shown in FIG. 1 and the control device
  • FIG. 3 the electrical signal, valve, high-pressure piston stroke and needle stroke curve as a function of time.
  • Fig. 1 denotes a fuel tank, from which fuel is drawn off via a high-pressure pump 3 with the interposition of a fuel filter 2 and is pumped into a pressure tank 4.
  • 5 designates a pressure control mechanism by means of which the pressure in the pressure vessel 4 is kept constant. It is controlled by an electronic control unit, which is designated 6.
  • the fuel Via a line 7, the fuel reaches the injection unit 8 under pressure, first in a storage space 9 in which a control piston 10 is guided. From the storage space 9, the fuel passes through holes 11 into the nozzle needle spring space 12.
  • the check valve 13 When the check valve 13 is open, the fuel exits into a high pressure space 14 and passes through holes 15 from this high pressure space into the nozzle needle space 16.
  • the nozzle needle spring 17 is dimensioned so that the forces acting on the nozzle needle 18 in the opening direction are smaller than the forces acting in the closing direction, the forces acting in the closing direction arising from the force of the spring 17 and the liquid pressure on the end of the nozzle needle which dips into the nozzle needle spring chamber 12 Put together 18 exercised forces.
  • a high-pressure piston 20 is arranged between the high-pressure chamber 14 and a control chamber 19. One end of this high-pressure piston 20 dips into the control chamber 19 and is held in contact with the control piston 10 by side spring 21.
  • the effective area in the direction of the high-pressure chamber 14 of the high-pressure piston 20 is smaller than the area 22 of the control piston 10 acted upon by the fuel pressure.
  • the storage chamber 9 is connected to the control chamber 19 via a throttle 23 and the control chamber 19 is connected by a Electromagnetically actuated valve 24 completed. As soon as a pressure equalization between the storage chamber 9 and the control chamber 19 is established via the throttle 23, the force of the spring 21 can no longer be overcome and the high-pressure piston remains in a starting position in contact with the control piston 10.
  • the pressure in the control chamber 19 drops rapidly and the forces acting on the surface 22 of the control piston 10 enable the spring 21 to be overpressed, the high-pressure piston being able to exert a stroke h.
  • the increased fuel pressure in the high-pressure chamber 14 enables the nozzle needle 18 to be opened against the lower fuel pressure in the nozzle needle spring chamber 12 relative to this pressure and against the force of the nozzle needle spring 17. In this way, the injection process is triggered and the opening stroke of the nozzle needle is made possible.
  • the closing process of the nozzle needle 18 is determined in that the pressure in the high-pressure chamber 14 drops at least to the pressure level in the nozzle needle spring chamber 12. This takes place after the injection has ended and the high-pressure piston 20 is designed such that it has an axial bore 25 which is open on one side and radial bores 26 adjoining it.
  • the stroke of the high-pressure piston until the bores 26 are blended with bores 27 aligned with these bores is denoted by hf.
  • the pressure in the control chamber 19 increases due to the supply of fuel under pressure via the throttle bore 23.
  • the control piston 10 is in turn moved upward via its stroke h, the high-pressure piston 20 follows this stroke h due to the force of the spring 21.
  • the stroke h is defined by the duration over which the valve 24 remains closed, since as soon as this valve 24 is opened, a stroke in the opposite direction is triggered by the drop in pressure.
  • the duration of the valve 24 remaining in the closed state thus defines the stroke h of the control piston 10 and thus the metering of the injection quantity.
  • the embodiment according to FIG. 2 differs from the embodiment according to FIG. 1 only in that the transverse bore 27 of the high-pressure piston 20 is aligned with a bore 30 after passing through the stroke h f , which opens into the control chamber 19. Since the control chamber 19 is depressurized at this time and is connected to the return due to the open solenoid valve 24, the pressure in the high-pressure chamber 14 is relieved extremely quickly and the nozzle needle closes more quickly.
  • the solenoid valve 24 is configured differently.
  • the fuel quantity is metered when the valve 24 is electrically excited because the closing body 31 this valve 24 is only in the closed position when there is electrical excitation.
  • the electromagnetic valve 24 according to FIG. 1 is in the closed position in the idle state and the injection quantity is metered over the period over which the valve 24 according to FIG. 1 is de-energized.
  • the high-pressure piston 20 can carry out a stroke h f1 or a stroke h f2 , the smaller stroke naturally corresponding to a smaller injection quantity and thus a shorter injection time.
  • the needle stroke of the nozzle needle 18 is also shown in FIG. 3 and with a larger injection quantity, the start of injection is brought forward relative to the injection of a smaller injection quantity.
  • the start of injection corresponding to a stroke h f1 is denoted by the time t 1 and the start of injection taking place with a smaller piston stroke h f2 is denoted by t 2 .
  • OT top dead center is entered as the reference point for the chronological sequence.

Abstract

1. Injection device for injection internal combustion engines with a pump (3) for supplying the jet with fuel under pre-determined pressure, in which the jet needle (18) immerses in a space (12) that can be filled with fuel under pressure and is held in the closed position by the pressure in this space and a spring (17), whereby the immersion space (12) of the jet needle (18) is connected by means of an outwardly opening non-return valve (13) with a high-pressure space (14) and with a jet needle space (16), whereby the surface of the jet needle (18) effective in the opening phase multiplied by the pump pressure is smaller than the sum of the surface effective in the closed phase of the jet needle (18) multiplied by the pump pressure and the force of the jet needle spring (17) effective in the closed phase, whereby one and of a high-pressure piston (20) immerses in the high-pressure space (14), the other end of which immerses in a control space (19), in which a control piston (10) pressurised with pump pressure is driven, whereby the effective section of the control piston (10) is greater than the effective section of the high-pressure piston (20) and the control piston (10) during the injection process operates together force-coupled with the high-pressure piston (20), characterised in that the supply of fuel into the high-pressure space (14) takes place through the immersion space (12) of the jet needle spring and the non-return valve (13) which is provided in the connecting pipe between the immersion space (12) and the high-pressure space (14), that the control piston (10) can also be pressurised on its side turned away from the control space (19) with the pump pressure, that the control space (19) is connected by a throttle (23) with the working space (9) of the control piston (10) and that the control space (19) can be connected to the return pipe to initiate an injection process by the release of pressure through a controllable valve (24).

Description

Die Erfindung bezieht sich auf eine Einspritzdüse für Einspritzbrennkraftmaschinen mit einer Pumpe zur Versorgung der Düse mit Kraftstoff unter vorbestimmtem Druck, bei welcher die Düsennadel in einen mit Kraftstoff unter Druck füllbaren Raum eintaucht und durch den Druck in diesem Raum und eine Feder in Schließstellung gehalten und durch Druckentlastung dieses Raumes öffenbar ist. Eine derartige Einrichtung ist beispielsweise der DE-OS 27 56 088 zu entnehmen. Bei dieser bekannten Einrichtung erfolgt die -Füllung des Düsennadelraumes in Abhängigkeit von der Betätigung eines Mehrwegeventiles, wobei in einer Stellung dieses Mehrwegeventiles der Füllvorgang beendet und gleichzeitig eine Druckentlastung des Eintauchraumes erfolgt. Mit dieser bekannten Einrichtung kann der Kraftstoff immer nur unter demjenigen Druck eingespritzt werden, unter welchem er dem Speicherraum bzw. dem Düsennadelraum zur Verfügung gestellt wird.The invention relates to an injection nozzle for injection internal combustion engines with a pump for supplying the nozzle with fuel under predetermined pressure, in which the nozzle needle is immersed in a space that can be filled with fuel under pressure and held in the closed position and by the pressure in this space and a spring Pressure relief of this room can be opened. Such a device can be found, for example, in DE-OS 27 56 088. In this known device, the filling of the nozzle needle chamber takes place as a function of the actuation of a multi-way valve, the filling process being ended in one position of this multi-way valve and pressure relief of the immersion chamber taking place at the same time. With this known device, the fuel can only be injected under the pressure at which it is made available to the storage space or the nozzle needle space.

Die Erfindung zielt nun darauf ab, eine Einspritzdüse der eingangs genannten Art zu schaffen, mit welcher der Einspritzvorgang in einfacher Weise in Abhängigkeit von Betriebsgrößen gesteuert werden kann und die Einspritzung selbst unter einem gegenüber dem Pumpendruck erhöhten Druck erfolgen kann. Zur Lösung dieser Aufgabe besteht die Erfindung im wesentlichen darin, daß der Eintauchraum der Düsennadel über ein nach außen öffnendes Rückschlagventil mit einem Hochdruckraum in Verbindung steht, daß der Hochdruckraum mit einem Düsennadelraum in Verbindung steht, wobei die im öffnungssinne wirksame Fläche der Düsennadel multipliziert mit dem Pumpendruck kleiner ist als die Summe der im Schließsinne wirksamen Fläche der Düsennadel multipliziert mit dem Pumpendruck und der im Schließsinne wirkenden Kraft der Düsennadelfeder, daß in den Hochdruckraum ein Ende eines Hochdruckkolbens eintaucht, dessen anderes Ende in einen Steuerraum eintaucht, daß im Steuerraum ein Steuerkolben geführt ist, daß der Steuerkolben an seiner dem Steuerraum abgewandten Seite mit dem Pumpendruck beaufschlagbar ist, wobei der wirksame Querschnitt des Steuerkolbens größer ist als der wirksame Querschnitt des Hochdruckkolbens, daß der Steuerraum über eine Drossel mit dem Arbeitsraum des Steuerkolbens verbunden und über ein steuerbares Ventil mit der Rücklaufleitung verbindbar ist, und daß der Steuerkolben bei geöffnetem steuerbaren Ventil kraftschlüssig mit dem Hochdruckkolben zusammenwirkt. Dadurch, daß der Eintauchraum der Düsennadel über ein in Richtung zu einem Hochdruckraum öffnendes Rückschlagventil mit einem Hochdruckraum in Verbindung steht, wird es ermöglicht, den Druck in diesem Hochdruckraum durch einen gesonderten Hochdruckkolben zu erhöhen, wobei in diesem Falle das Rückschlagventil schließt. Die Erhöhung des Druckes in dem Hochdruckraum erfolgt dadurch, daß der Hochdruckkolben in einen Steuerraum eintaucht, welcher selbst wiederum mit dem Pumpendruck über eine Drossel beaufschlagbar ist. Durch Druckentlastung dieses Steuerraumes kann ein entsprechend größer bemessener Steuerkolben in Anschlag an den Hochdruckkolben gebracht werden und je nach gewählter Flächendifferenz des Hochdruckkolbens und der wirksamen Fläche des Steuerkolbens erfolgt bei einer Druckentlastung des Steuerraumes ein entsprechender Druckaufbau im Hochdruckraum. Ein Abheben der Düsennadel erfolgt nun aufgrund des erhöhten Kraftstoffdruckes im Hochdruckraum, wobei diese Druckerhöhung mittelbar durch die Druckentlastung Steuerraumes ausgelöst wurde. Durch Druckentlastung des Steuerraumes wird somit die Druckerhöhung und die öffnung der Düsennadel gesteuert.The invention now aims to provide an injection nozzle of the type mentioned at the outset, with which the injection process can be controlled in a simple manner as a function of operating variables and the injection can take place even under a pressure which is higher than the pump pressure. To achieve this object, the invention consists essentially in the fact that the immersion space of the nozzle needle is connected to a high-pressure chamber via an outward opening check valve, that the high-pressure space is connected to a nozzle needle chamber, the effective area of the nozzle needle in the opening sense being multiplied by that Pump pressure is less than the sum of the effective area of the nozzle needle in the closing direction multiplied by the pump pressure and the force of the nozzle needle spring acting in the closing direction, that one end of a high-pressure piston is immersed in the high-pressure chamber, the other end of which is immersed in a control chamber, that in the control room Control piston is guided such that the control piston can be acted upon by the pump pressure on its side facing away from the control chamber, the effective cross section of the control piston being greater than the effective cross section of the high pressure piston, that the control chamber is connected to the working chamber of the control piston via a throttle and via a controllable one Valve can be connected to the return line, and that the control piston interacts positively with the high-pressure piston when the controllable valve is open. Characterized in that the immersion space of the nozzle needle is connected to a high-pressure space via a check valve opening towards a high-pressure space, it is possible to increase the pressure in this high-pressure space by a separate high-pressure piston, in which case the check valve closes. The pressure in the high-pressure chamber is increased by immersing the high-pressure piston in a control chamber, which in turn can be acted upon by the pump pressure via a throttle. By relieving the pressure in this control chamber, a correspondingly larger control piston can be brought into abutment against the high-pressure piston and, depending on the selected area difference of the high-pressure piston and the effective area of the control piston, a corresponding pressure build-up in the high-pressure chamber takes place when the pressure in the control chamber is relieved. The nozzle needle is now lifted off due to the increased fuel pressure in the high-pressure chamber, this pressure increase being triggered indirectly by the pressure relief in the control chamber. By relieving the pressure in the control room, the pressure increase and the opening of the nozzle needle are controlled.

Fn., steuerbare Ventil, welches mit dem Steuerraum in Verbindung steht, kann hiebei in an sich bekannter Weise als Magnetventil ausgebildet sein. Um eine stoßfreie Anlage des Hochdruckkolbens am Steuerkolben sicherzustellen, ist die Ausbildung in vorteilhafter Weise so getroffen, daß der Hochdruckkolben federnd in Richtung zum Steuerkolben gedrückt ist. Der Eintauchraum der Düsennadel kann in konstruktiv besonders einfacher Weise auch die Düsennadelfeder aufnehmen und als Düsennadelfederraum ausgebildet sein.Fn. Controllable valve, which is connected to the control chamber, can be designed in a manner known per se as a solenoid valve. A shock-free system of the H ochdruckkolbens ensure on the control piston, the configuration is devised in an advantageous manner so that the high pressure piston resiliently urged in the direction of the control piston is. The immersion space of the nozzle needle can also accommodate the nozzle needle spring in a structurally particularly simple manner and can be designed as a nozzle needle spring space.

Um ein exaktes Schließen der Düsennadel nach Einspritzen eines vorbestimmten Volumens sicherzustellen, ist die Ausbildung in vorteilhafter Weise so getroffen, daß der Hochdruckkolben wenigstens eine einseitig geschlossene axiale Bohrung und wenigstens eine mit dieser axialen Bohrung in Verbindung stehende radiale Bohrung aufweist, wobei das offene Ende der axialen Bohrung in den Hochdruckraum mündet, und die radiale Bohrung nach einem vorbestimmten Hub des Hochdruckkolbens mit der Druckleitung der Pumpe oder der Rücklaufleitung verbindbar ist. Auf diese Weise wird der Einspritzvorgang dadurch beendet, daß der Kraftstoffdruck im Hochdruckraum auf ein Niveau abgesenkt wird, bei welchem die Gleichgewichtslage einen Schließvorgang der Düsennadel erzwingt. Ein besonders rasches Schließen der Düsennadel kann dadurch erzielt werden, daß das Druckgleichgewicht nicht gegen die Druckleitung der Pumpe, sondern durch Ableiten des Druckes in die Rücklaufleitung hergestellt wird.In order to ensure an exact closing of the nozzle needle after injection of a predetermined volume, the design is advantageously made such that the high-pressure piston has at least one axial bore closed on one side and at least one radial bore connected to this axial bore, the open end of the axial bore opens into the high-pressure chamber, and the radial bore can be connected to the pressure line of the pump or the return line after a predetermined stroke of the high-pressure piston. In this way, the injection process is ended by lowering the fuel pressure in the high-pressure chamber to a level at which the equilibrium position forces the nozzle needle to close. A particularly rapid closing of the nozzle needle can be achieved in that the pressure equilibrium is not established against the pressure line of the pump, but by deriving the pressure into the return line.

Da der Druckabbau im Steuerraum nicht nur den Aufbau eines gegenüber dem Pumpendruck erhöhten Druckes, sondern gleichzeitig auch die Auslösung des öffnungshubes der Düsennadel steuert, kann in einfacher Weise eine Steuereinrichtung vorgesehen sein, welche in Abhängigkeit von Betriebsgrößen, wie z.B. Drehzahlladedruck oder Temperatur oder Motorlast, ein Signal für die Erregung des Magnetventiles abgibt.Since the pressure reduction in the control chamber not only controls the build-up of a pressure that is higher than the pump pressure, but at the same time also triggers the opening stroke of the nozzle needle, a control device can be provided in a simple manner, which, depending on operating variables, e.g. Speed boost pressure or temperature or engine load, emits a signal for the excitation of the solenoid valve.

Die Erfindung wird nachfolgend an Hand von in der Zeichnung dargestellten Ausführungsbeispielen näher erläutert. In dieser zeigen Fig. 1 eine erste Ausbildungsform der erfindungsgemäßen Einspritzdüse schematisch im Schnitt, Fig. 2 eine abgewandelte Ausführungsform der Einspritzdüse ohne die in Fig. 1 dargestellte Versorgung mit Kraftstoff unter Druck und die Steuereinrichtung und Fig. 3 den elektrischen Signal-, Ventil-, Hochdruckkolbenhub- und Nadelhubverlauf in Abhängigkeit von der Zeit.The invention is explained in more detail below with reference to exemplary embodiments shown in the drawing. 1 shows a first embodiment of the injection nozzle according to the invention schematically in section, FIG. 2 shows a modified embodiment of the injection nozzle without the supply of fuel under pressure shown in FIG. 1 and the control device and FIG. 3 the electrical signal, valve, high-pressure piston stroke and needle stroke curve as a function of time.

In Fig. 1 ist mit 1 ein Kraftstoffbehälter bezeichnet, aus welchem unter Zwischenschaltung eines Kraftstoffilters 2 über eine Hochdruckpumpe 3 Kraftstoff abgezogen wird und in einen Druckbehälter 4 gepumpt wird. Mit 5 ist ein Drucksteuermechanismus bezeichnet, über welchen der Druck im Druckbehälter 4 konstant gehalten wird. Die Steuerung erfolgt durch eine elektronische Steuereinheit, welche mit 6 bezeichnet ist. Über eine Leitung 7 gelangt der Kraftstoff unter Druck zur Einspritzeinheit 8, und zwar zunächst in einen Speicherraum 9, in welchem ein Steuerkolben 10 geführt ist. Aus dem Speicherraum 9 gelangt der Kraftstoff über Bohrungen 11 in den Düsennadelfederraum 12. Bei geöffnetem Rückschlagventil 13 tritt der Kraftstoff in einen Hochdruckraum 14 aus und gelangt über Bohrungen 15 aus diesem Hochdruckraum in den Düsennadelraum 16. Die Düsennadelfeder 17 ist hiebei so bemessen, daß die auf die Düsennadel 18 im öffnungssinne ausgewirkten Kräfte kleiner sind als die im Schließsinne wirkenden Kräfte, wobei die im Schließsinne wirkenden Kräfte sich aus der Kraft der Feder 17 und den auf die Düsennadel im Schließsinne durch den Flüssigkeitsdruck auf das in den Düsennadelfederraum 12 eintauchende Ende der Düsennadel 18 ausgeübten Kräften zusammensetzen.In Fig. 1, 1 denotes a fuel tank, from which fuel is drawn off via a high-pressure pump 3 with the interposition of a fuel filter 2 and is pumped into a pressure tank 4. 5 designates a pressure control mechanism by means of which the pressure in the pressure vessel 4 is kept constant. It is controlled by an electronic control unit, which is designated 6. Via a line 7, the fuel reaches the injection unit 8 under pressure, first in a storage space 9 in which a control piston 10 is guided. From the storage space 9, the fuel passes through holes 11 into the nozzle needle spring space 12. When the check valve 13 is open, the fuel exits into a high pressure space 14 and passes through holes 15 from this high pressure space into the nozzle needle space 16. The nozzle needle spring 17 is dimensioned so that the forces acting on the nozzle needle 18 in the opening direction are smaller than the forces acting in the closing direction, the forces acting in the closing direction arising from the force of the spring 17 and the liquid pressure on the end of the nozzle needle which dips into the nozzle needle spring chamber 12 Put together 18 exercised forces.

Zwischen dem Hochdruckraum 14 und einem Steuerraum 19 ist ein Hochdruckkolben 20 angeordnet. Ein Ende dieses Hochdruckkolhens 20 taucht in den Steuerraum 19 ein und wird durch side Feder 21 in Anlage an den Steuerkolben 10 gehalten. Die in Richtung zum Hochdruckraum 14 wirksame Fläche des Hochdruckkolbens 20 ist hiebei kleiner als die vom Kraftstoffdruck beaufschlagte Fläche 22 des Steuerkolbens 10. Der Speicherraum 9 ist über eine Drossel 23 mit dem Steuerraum 19 verbunden und der Steuerraum 19 ist durch ein elektromagnetisch betätigbares Ventil 24 abgeschlossen. Sobald über die Drossel 23 ein Druckausgleich zwischen dem Speicherraum 9 und dem Steuerraum 19 hergestellt ist, kann die Kraft der Feder 21 nicht mehr überwunden werden und der Hochdruckkolben bleibt in einer Ausgangslage in Anlage an den Steuerkolben 10. Sobald das elektromagnetische Ventil 24 betätigt wird, erfolgt aufgrund des langsamen Zustromes von Kraftstoff über die Drossel 23 ein rasches Absinken des Druckes im Steuerraum 19 und die auf die Fläche 22 des Steuerkolbens 10 wirksamen Kräfte ermöglichen das Uberdrücken der Feder 21, wobei der Hochdruckkolben einen Hub h ausüben kann. Aufgrund der geringeren Querschnittsfläche des Hochdruckkolbens relativ zu der durch den Kraftstoffdruck beaufschlagten Fläche 22 des Steuerkolbens 10 wird im Hochdruckraum 14 nunmehr ein gegenüber dem Kraftstoffdruck erhöhter Druck aufgebaut, wobei das Rückschlagventil 13 schließt. Der erhöhte Kraftstoffdruck im Hochdruckraum 14 ermöglicht das öffnen der Düsennadel 18 gegen den relativ zu diesem Druck geringeren Kraftstoffdruck im Düsennadelfederraum 12 und gegen die Kraft der Düsennadelfeder 17. Auf diese Weise wird der Einspritzvorgang ausgelöst und der öffnungshub der Düsennadel ermöglicht.A high-pressure piston 20 is arranged between the high-pressure chamber 14 and a control chamber 19. One end of this high-pressure piston 20 dips into the control chamber 19 and is held in contact with the control piston 10 by side spring 21. The effective area in the direction of the high-pressure chamber 14 of the high-pressure piston 20 is smaller than the area 22 of the control piston 10 acted upon by the fuel pressure. The storage chamber 9 is connected to the control chamber 19 via a throttle 23 and the control chamber 19 is connected by a Electromagnetically actuated valve 24 completed. As soon as a pressure equalization between the storage chamber 9 and the control chamber 19 is established via the throttle 23, the force of the spring 21 can no longer be overcome and the high-pressure piston remains in a starting position in contact with the control piston 10. As soon as the electromagnetic valve 24 is actuated, due to the slow inflow of fuel via the throttle 23, the pressure in the control chamber 19 drops rapidly and the forces acting on the surface 22 of the control piston 10 enable the spring 21 to be overpressed, the high-pressure piston being able to exert a stroke h. Due to the smaller cross-sectional area of the high-pressure piston relative to the surface 22 of the control piston 10 acted upon by the fuel pressure, a pressure which is higher than the fuel pressure is now built up in the high-pressure chamber 14, the check valve 13 closing. The increased fuel pressure in the high-pressure chamber 14 enables the nozzle needle 18 to be opened against the lower fuel pressure in the nozzle needle spring chamber 12 relative to this pressure and against the force of the nozzle needle spring 17. In this way, the injection process is triggered and the opening stroke of the nozzle needle is made possible.

Der Schließvorgang der Düsennadel 18 wird dadurch bestimmt, daß der Druck im Hochdruckraum 14 zumindest auf das Druckniveau im Düsennadelfederraum 12 absinkt. Dies erfolgt nach beendeter Einspritzung und der Hochdruckkolben 20 ist so ausgebildet, daß er in seinem Inneren eine einseitig offene axiale Bohrung 25 und an diese anschließende radiale Bohrungen 26 aufweist. Der Hub des Hochdruckkolbens bis zum überschleifen der Bohrungen 26 mit mit diesen Bohrungen fluchtenden Bohrungen 27 wird durch hf bezeichnet. Sobald dieser Hub vom Hochdruckkolben 20 ausgeführt ist, wird der Druck im Hochdruckraum 14 über die axiale Bohrung 25 und die radiale Bohrung 26 gegenüber dem Zuführungsdruck der Pumpe 3 ausgeglichen, wodurch sich das Druckgleichgewicht so verschiebt, daß die Düsennadelfeder 17 die Düsennadel 18 wiederum in ihre Schließlage bewegt. Die Einspritzmenge wird hiebei durch den Förderhub hf des Hochdruckkolbens 20 definiert. Nach dem Spritzende bewegen sich sowohl der Hochdruckkolben 20 als auch der Steuerkolben 10 bis zur Anschlagfläche 28 des Steuerkolbens 10 weiter, solange das Ventil 24 geöffnet bleibt.The closing process of the nozzle needle 18 is determined in that the pressure in the high-pressure chamber 14 drops at least to the pressure level in the nozzle needle spring chamber 12. This takes place after the injection has ended and the high-pressure piston 20 is designed such that it has an axial bore 25 which is open on one side and radial bores 26 adjoining it. The stroke of the high-pressure piston until the bores 26 are blended with bores 27 aligned with these bores is denoted by hf. As soon as this stroke is carried out by the high-pressure piston 20, the pressure in the high-pressure chamber 14 is balanced via the axial bore 25 and the radial bore 26 with respect to the supply pressure of the pump 3, as a result of which the pressure balance is shifted, that the nozzle needle spring 17 in turn moves the nozzle needle 18 into its closed position. The injection quantity is hereby defined by the delivery stroke h f of the high-pressure piston 20. After the end of the spray, both the high-pressure piston 20 and the control piston 10 continue to move as far as the stop surface 28 of the control piston 10, as long as the valve 24 remains open.

Sobald das Ventil 24 geschlossen wird, steigt der Druck im Steuerraum 19 aufgrund der Zuführung von Kraftstoff unter Druck über die Drosselbohrung 23. Bei Erreichen eines bestimmten Druckes in diesem Steuerraum 19 wird der Steuerkolben 10 wiederum über seinen Hub h nach oben bewegt, wobei der Hochdruckkolben 20 auf Grund der Kraft der Feder 21 diesem Hub h folgt. Der Hub h wird hiebei durch die Dauer, über welche das Ventil 24 geschlossen bleibt, definiert, da, sobald dieses Ventil 24 geöffnet wird, durch den Druckabfall wiederum ein Hub in die Gegenrichtung ausgelöst wird. Die Dauer des Verbleibens des Ventils 24 in geschlossenem Zustand definiert somit den Hub h des Steuerkolbens 10 und damit die Zumessung der Einspritzmenge.As soon as the valve 24 is closed, the pressure in the control chamber 19 increases due to the supply of fuel under pressure via the throttle bore 23. When a certain pressure in this control chamber 19 is reached, the control piston 10 is in turn moved upward via its stroke h, the high-pressure piston 20 follows this stroke h due to the force of the spring 21. The stroke h is defined by the duration over which the valve 24 remains closed, since as soon as this valve 24 is opened, a stroke in the opposite direction is triggered by the drop in pressure. The duration of the valve 24 remaining in the closed state thus defines the stroke h of the control piston 10 and thus the metering of the injection quantity.

Die Ausbildung nach Fig. 2 unterscheidet sich von der Ausbildung nach Fig. 1 lediglich dadurch, daß die Querbohrung 27 des Hochdruckkolbens 20 nach Durchlaufen des Hubes hf mit einer Bohrung 30 fluchtet, welche in den Steuerraum 19 mündet. Da der Steuerraum 19 zu diesem Zeitpunkt drucklos ist und aufgrund des geöffneten Magnetventiles 24 mit dem Rücklauf in Verbindung steht, erfolgt hier ein überaus rasches Entlasten des Druckes im Hochdruckraum 14 und damit ein schnelleres Schließen der Düsennadel.The embodiment according to FIG. 2 differs from the embodiment according to FIG. 1 only in that the transverse bore 27 of the high-pressure piston 20 is aligned with a bore 30 after passing through the stroke h f , which opens into the control chamber 19. Since the control chamber 19 is depressurized at this time and is connected to the return due to the open solenoid valve 24, the pressure in the high-pressure chamber 14 is relieved extremely quickly and the nozzle needle closes more quickly.

Weiters ist bei der Ausbildung nach Fig. 2 das Magnetventil 24 anders ausgebildet. Im Gegensatz zur Ausbildung nach Fig. 1 erfolgt die Zumessung der Kraftstoffmenge dann, wenn das Ventil 24 elektrisch erregt ist, da der Schließkörper 31 dieses Ventiles 24 nur bei elektrischer Erregung in der Schließlage ist. Demgegenüber ist das elektromagnetische Ventil 24 gemäß Fig. 1 im Ruhezustand in der Schließlage und es erfolgt die Zumessung der Einspritzmenge über denjenigen Zeitraum, über welchen das Ventil 24 gemäß Fig. 1 stromlos ist.2, the solenoid valve 24 is configured differently. In contrast to the embodiment according to FIG. 1, the fuel quantity is metered when the valve 24 is electrically excited because the closing body 31 this valve 24 is only in the closed position when there is electrical excitation. In contrast, the electromagnetic valve 24 according to FIG. 1 is in the closed position in the idle state and the injection quantity is metered over the period over which the valve 24 according to FIG. 1 is de-energized.

Die Vorgänge, wie sie steuersignalseitig, bezüglich des Ventilhubes, der Kolbenhübe, und des Nadelhubes bei der Ausbildung nach Fig. 2 in zeitlicher Abfolge ablaufen, sind in Fig. 3 für zwei unterschiedliche Einspritzmengen schematisch erläutert. Da die Ausbildung des elektromagnetischen Ventiles so getroffen ist, daß die Zumessung durch die Länge des elektrischen Signales definiert ist, erfolgt bei Vorliegen eines Steuersignales ein Ventilhub und damit ein Schließvorgang des elektromagnetischen Ventiles 24. Die ausgezogene Linie entspricht hiebei der Zumessung einer größeren Einspritzmenge, wohingegen die strichlierte kürzerer Signaldauer dem kürzeren Ventilhub bzw. einer geringeren Einspritzmenge entsprechen. Je nach Dauer des Signales bzw. des Verbleibes des elektromagnetischen Ventiles 24 in der Schließlage kann der Hochdruckkolben 20 einen Hub hf1 oder einen Hub hf2 ausführen, wobei der kleinere Hub naturgemäß einer geringeren Einspritzmenge und damit einer verkürzten Einspritzzeit entspricht. Der Nadelhub der Düsennadel 18 ist gleichfalls in Fig. 3 dargestellt und bei einer größeren Einspritzmenge ergibt sich eine Vorverlegung des Einspritzbeginnes relativ zur Einspritzung einer geringeren Einspritzmenge. Der einem Hub hf1 entsprechende Einspritzbeginn wird durch die Zeit t1 und der bei einem kleineren Kolbenhub hf2 erfolgende Einspritzbeginn mit t2 bezeichnet. Mit OT ist hiebei der obere Totpunkt als Bezugspunkt für den zeitlichen Ablauf eingetragen.The processes as they occur on the control signal side, with respect to the valve stroke, the piston strokes, and the needle stroke in the embodiment according to FIG. 2, are explained schematically in FIG. 3 for two different injection quantities. Since the design of the electromagnetic valve is such that the metering is defined by the length of the electrical signal, a valve lift and thus a closing process of the electromagnetic valve 24 take place when a control signal is present. The solid line corresponds to the metering of a larger injection quantity, whereas the dashed shorter signal duration correspond to the shorter valve lift or a smaller injection quantity. Depending on the duration of the signal or the remaining of the electromagnetic valve 24 in the closed position, the high-pressure piston 20 can carry out a stroke h f1 or a stroke h f2 , the smaller stroke naturally corresponding to a smaller injection quantity and thus a shorter injection time. The needle stroke of the nozzle needle 18 is also shown in FIG. 3 and with a larger injection quantity, the start of injection is brought forward relative to the injection of a smaller injection quantity. The start of injection corresponding to a stroke h f1 is denoted by the time t 1 and the start of injection taking place with a smaller piston stroke h f2 is denoted by t 2 . With OT, top dead center is entered as the reference point for the chronological sequence.

Claims (6)

1. Einspritzdüse für Einspritzbrennkraftmaschinen, mit einer Pumpe (3) zur Versorgung der Düse mit Kraftstoff unter vorbestimmtem Druck, bei welcher die Düsennadel (18) in einen mit Kraftstoff unter Druck füllbaren Raum (12) eintaucht und durch den Druck in diesem Raum und eine Feder (17) in Schließstellung gehalten wird und durch Druckentlastung dieses Raumes (12) öffenbar ist, dadurch gekennzeichnet, daß der Eintauchraum (12) der Düsennadel (18) über ein nach außen öffnendes Rückschlagventil (13)-mit einem Hochdruckraum (14-) in Verbindung steht, daß der Hochdruckraum (14) mit einem Düsennadelraum (16) in Verbindung steht, wobei die im öffnungssinne wirksame Fläche der Düsennadel (18) multipliziert mit dem Pumpendruck kleiner ist als die Summe der im Schließsinne wirksamen Fläche der Düsennadel (18) multipliziert mit dem Pumpendruck und der im Schließsinne wirkenden Kraft der Düsennadelfeder (17), daß in den Hochdruckraum (14) ein Ende eines Hochdruckkolbens (20) eintaucht, dessen anderes Ende in einen Steuerraum (19) eintaucht, daß im Steuerraum (19) ein Steuerkolben (10) geführt ist, daß der Steuerkolben (10) an seiner dem Steuerraum (19)abgewandten Seite mit dem Pumpendruck beaufschlagbar ist, wobei der wirksame Querschnitt des Steuerkolbens (10) größer ist als der wirksame Querschnitt des Hochdruckkolbens (20), daß der Steuerraum (19) über eine Drossel (23) mit dem Arbeitsraum (9) des Steuerkolbens (10) verbunden und über ein steuerbares Ventil (24) mit der Rücklaufleitung verbindbar ist, und daß der Steuerkolben (10) bei geöffnetem steuerbaren Ventil (24) kraftschlüssig mit dem Hochdruckkolben (20) zusammenwirkt.1.Injection nozzle for injection internal combustion engines, with a pump (3) for supplying the nozzle with fuel under a predetermined pressure, in which the nozzle needle (18) is immersed in a fuel-fillable space (12) and by the pressure in this space and one Spring (17) is held in the closed position and can be opened by relieving pressure in this space (12), characterized in that the immersion space (12) of the nozzle needle (18) has an outward opening check valve (13) with a high-pressure space (14-) is connected that the high-pressure chamber (14) is connected to a nozzle needle chamber (16), the opening area of the nozzle needle (18) multiplied by the pump pressure being smaller than the sum of the area of the nozzle needle (18) effective in the closing direction. multiplied by the pump pressure and the force of the nozzle needle spring (17) acting in the closing direction, that one end of a high-pressure piston (20) dips into the high-pressure chamber (14) whose end is immersed in a control chamber (19) that a control piston (10) is guided in the control chamber (19), that the control piston (10) can be acted upon by the pump pressure on its side facing away from the control chamber (19), the effective cross section of the Control piston (10) is larger than the effective cross section of the high-pressure piston (20) that the control chamber (19) via a throttle (23) with the working chamber (9) of the control piston (10) and via a controllable valve (24) with the Return line can be connected, and that the control piston (10) interacts positively with the high-pressure piston (20) when the controllable valve (24) is open. z. Einspritzdüse nach Anspruch 1, dadurch gekennzeichnet, daß das steuerbare Ventil in an sich bekannter Weise als Magnetventil (24) ausgebildet ist.e.g. Injection nozzle according to claim 1, characterized in that the controllable valve is designed in a manner known per se as a solenoid valve (24). 3. Einspritzdüse nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß der Hochdruckkolben (20) federnd in Richtung zum Steuerkolben (10) gedrückt ist.3. Injection nozzle according to claim 1 or 2, characterized in that the high-pressure piston (20) is pressed resiliently in the direction of the control piston (10). 4. Einspritzdüse nach Anspruch 1, 2 oder 3, dadurch gekennzeichnet, daß der Eintauchraum (12) der Düsennadel (18) als Düsennadelfederraum ausgebildet ist.4. Injection nozzle according to claim 1, 2 or 3, characterized in that the immersion space (12) of the nozzle needle (18) is designed as a nozzle needle spring chamber. 5. Einspritzdüse nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß der Hochdruckkolben (20) wenigstens eine einseitig geschlossene axiale Bohrung (25) und wenigstens eine mit dieser axialen Bohrung (25) in Verbindung stehende radiale Bohrung (26) aufweist, wobei das offene Ende der axialen Bohrung (25) in den Hochdruckraum (14) mündet, und die radiale Bohrung (26) nach einem vorbestimmten Hub des Hochdruckkolbens (20) mit der Druckleitung (27) der Pumpe (3) oder der Rücklaufleitung (30) verbindbar ist.5. Injection nozzle according to one of claims 1 to 4, characterized in that the high-pressure piston (20) has at least one axial bore (25) closed on one side and at least one radial bore (26) connected to this axial bore (25), wherein the open end of the axial bore (25) opens into the high-pressure chamber (14), and the radial bore (26) after a predetermined stroke of the high-pressure piston (20) with the pressure line (27) of the pump (3) or the return line (30) is connectable. 6. Einspritzdüse nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, daß eine Steuereinrichtung (6) vorgesehen ist, welche in Abhängigkeit von Betriebsgrößen wie z.B. Drehzahl, Ladedruck, Motortemperatur oder Motorlast ein Signal für die Erregung des Magnetventiles (24) abgibt.6. Injection nozzle according to one of claims 1 to 5, characterized in that a control device (6) is provided which, depending on operating variables such as e.g. Speed, boost pressure, engine temperature or engine load emits a signal for the excitation of the solenoid valve (24).
EP19850890010 1984-01-16 1985-01-15 Injection nozzle for injection internal combustion engines Expired EP0149598B1 (en)

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AT118/84 1984-01-16
AT11884 1984-01-16

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Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2185530A (en) * 1986-01-22 1987-07-22 Dereco Dieselmotoren Forschung Fuel injection system for an internal combustion engine
DE3802136A1 (en) * 1987-01-30 1988-08-11 Volkswagen Ag Pump nozzle, especially for diesel internal combustion engines with direct fuel injection
EP0299337A2 (en) * 1987-07-08 1989-01-18 IVECO FIAT S.p.A. Fuel injection system for an internal combustion engine
WO1993007380A1 (en) * 1991-10-11 1993-04-15 Caterpillar Inc. Hydraulically-actuated electronically-controlled unit injector fuel system having variable control of actuating fluid pressure
US5271371A (en) * 1991-10-11 1993-12-21 Caterpillar Inc. Actuator and valve assembly for a hydraulically-actuated electronically-controlled injector
US5357912A (en) * 1993-02-26 1994-10-25 Caterpillar Inc. Electronic control system and method for a hydraulically-actuated fuel injection system
US5445129A (en) * 1994-07-29 1995-08-29 Caterpillar Inc. Method for controlling a hydraulically-actuated fuel injection system
US5447138A (en) * 1994-07-29 1995-09-05 Caterpillar, Inc. Method for controlling a hydraulically-actuated fuel injections system to start an engine
US5477828A (en) * 1994-07-29 1995-12-26 Caterpillar Inc. Method for controlling a hydraulically-actuated fuel injection system
US5492098A (en) * 1993-03-01 1996-02-20 Caterpillar Inc. Flexible injection rate shaping device for a hydraulically-actuated fuel injection system
US5529044A (en) * 1994-07-29 1996-06-25 Caterpillar Inc. Method for controlling the fuel injection rate of a hydraulically-actuated fuel injection system
EP0851117A1 (en) * 1996-12-26 1998-07-01 Isuzu Motors Limited Fuel injection system for internal combustion engines
EP0879954A3 (en) * 1997-05-20 2000-05-31 Stanadyne Automotive Corp. Common rail injector
WO2002088542A1 (en) * 2001-04-27 2002-11-07 Robert Bosch Gmbh Fuel injector comprising a sequential construction

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104847554A (en) * 2015-04-09 2015-08-19 中国第一汽车股份有限公司无锡油泵油嘴研究所 Electric control unit pump for diesel machine

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4098560A (en) * 1974-06-21 1978-07-04 Physics International Company Fuel injection pumps for internal combustion engines
GB2009842A (en) * 1977-12-09 1979-06-20 Lucas Industries Ltd Fuel injection systems
DE2756088A1 (en) * 1977-12-16 1979-06-21 Bosch Gmbh Robert Fuel injection valve for IC engine - has buffer volume with fuel at inlet pressure connected to underside of valve piston
DE2805785A1 (en) * 1978-02-11 1979-08-16 Bosch Gmbh Robert HIGH PRESSURE FUEL INJECTION DEVICE FOR COMBUSTION MACHINES
DE2927440A1 (en) * 1978-07-10 1980-01-24 Bendix Corp FUEL INJECTOR
DE2909233A1 (en) * 1979-03-09 1980-09-18 Bosch Gmbh Robert FUEL INJECTION DEVICE FOR INTERNAL COMBUSTION ENGINES
JPS5898654A (en) * 1981-12-07 1983-06-11 Nissan Motor Co Ltd Fuel injecting apparatus

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4098560A (en) * 1974-06-21 1978-07-04 Physics International Company Fuel injection pumps for internal combustion engines
GB2009842A (en) * 1977-12-09 1979-06-20 Lucas Industries Ltd Fuel injection systems
DE2756088A1 (en) * 1977-12-16 1979-06-21 Bosch Gmbh Robert Fuel injection valve for IC engine - has buffer volume with fuel at inlet pressure connected to underside of valve piston
DE2805785A1 (en) * 1978-02-11 1979-08-16 Bosch Gmbh Robert HIGH PRESSURE FUEL INJECTION DEVICE FOR COMBUSTION MACHINES
DE2927440A1 (en) * 1978-07-10 1980-01-24 Bendix Corp FUEL INJECTOR
DE2909233A1 (en) * 1979-03-09 1980-09-18 Bosch Gmbh Robert FUEL INJECTION DEVICE FOR INTERNAL COMBUSTION ENGINES
JPS5898654A (en) * 1981-12-07 1983-06-11 Nissan Motor Co Ltd Fuel injecting apparatus

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN, Band 7, Nr. 199 (M-240)[1344] 3. September 1983; & JP - A - 58 098 654 (NISSAN) 11.06.1983 *

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2185530B (en) * 1986-01-22 1989-12-06 Dereco Dieselmotoren Forschung Fuel injection system for an internal combustion engine
GB2185530A (en) * 1986-01-22 1987-07-22 Dereco Dieselmotoren Forschung Fuel injection system for an internal combustion engine
DE3802136A1 (en) * 1987-01-30 1988-08-11 Volkswagen Ag Pump nozzle, especially for diesel internal combustion engines with direct fuel injection
EP0299337A2 (en) * 1987-07-08 1989-01-18 IVECO FIAT S.p.A. Fuel injection system for an internal combustion engine
EP0299337A3 (en) * 1987-07-08 1989-10-18 IVECO FIAT S.p.A. Fuel injection system for an internal combustion engine
WO1993007380A1 (en) * 1991-10-11 1993-04-15 Caterpillar Inc. Hydraulically-actuated electronically-controlled unit injector fuel system having variable control of actuating fluid pressure
US5271371A (en) * 1991-10-11 1993-12-21 Caterpillar Inc. Actuator and valve assembly for a hydraulically-actuated electronically-controlled injector
US5357912A (en) * 1993-02-26 1994-10-25 Caterpillar Inc. Electronic control system and method for a hydraulically-actuated fuel injection system
US5492098A (en) * 1993-03-01 1996-02-20 Caterpillar Inc. Flexible injection rate shaping device for a hydraulically-actuated fuel injection system
US5445129A (en) * 1994-07-29 1995-08-29 Caterpillar Inc. Method for controlling a hydraulically-actuated fuel injection system
US5477828A (en) * 1994-07-29 1995-12-26 Caterpillar Inc. Method for controlling a hydraulically-actuated fuel injection system
US5447138A (en) * 1994-07-29 1995-09-05 Caterpillar, Inc. Method for controlling a hydraulically-actuated fuel injections system to start an engine
US5529044A (en) * 1994-07-29 1996-06-25 Caterpillar Inc. Method for controlling the fuel injection rate of a hydraulically-actuated fuel injection system
EP0851117A1 (en) * 1996-12-26 1998-07-01 Isuzu Motors Limited Fuel injection system for internal combustion engines
US5950601A (en) * 1996-12-26 1999-09-14 Isuzu Motors Limited Fuel injection system for engines
EP0879954A3 (en) * 1997-05-20 2000-05-31 Stanadyne Automotive Corp. Common rail injector
WO2002088542A1 (en) * 2001-04-27 2002-11-07 Robert Bosch Gmbh Fuel injector comprising a sequential construction

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DE3564470D1 (en) 1988-09-22
EP0149598B1 (en) 1988-08-17
EP0149598A3 (en) 1986-02-05

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