EP1117921B1 - Fuel injector for a common rail fuel system - Google Patents

Fuel injector for a common rail fuel system Download PDF

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Publication number
EP1117921B1
EP1117921B1 EP00962182A EP00962182A EP1117921B1 EP 1117921 B1 EP1117921 B1 EP 1117921B1 EP 00962182 A EP00962182 A EP 00962182A EP 00962182 A EP00962182 A EP 00962182A EP 1117921 B1 EP1117921 B1 EP 1117921B1
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EP
European Patent Office
Prior art keywords
nozzle
nozzle needle
space
pressure
fuel
Prior art date
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Expired - Lifetime
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EP00962182A
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German (de)
French (fr)
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EP1117921A1 (en
Inventor
Dieter Kienzler
Patrick Mattes
Wolfgang Stoecklein
Friedrich Boecking
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Robert Bosch GmbH
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Robert Bosch GmbH
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/21—Fuel-injection apparatus with piezoelectric or magnetostrictive elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
    • F02M2547/003—Valve inserts containing control chamber and valve piston

Definitions

  • the invention relates to a common rail injector for Injection of fuel in a common rail injection system an internal combustion engine, the one Injector housing having a fuel inlet, the with a central high-pressure fuel storage outside the injector housing and with a pressure chamber within the Injector housing communicates, from the high pressure applied fuel depending on the position a control valve is injected, which ensures that in a longitudinal bore of an injector axially against the biasing force of a nozzle spring in a Nozzle spring space is included, reciprocable Nozzle needle lifts off a seat when the pressure in the Pressure chamber is greater than the pressure in a control room, the connected via an inlet throttle with the fuel inlet is.
  • common-rail injection systems promotes a High pressure pump the fuel in the central High-pressure accumulator, which is referred to as common rail.
  • high-pressure accumulator From the high-pressure accumulator lead high-pressure lines to the individual injectors assigned to the engine cylinders are.
  • the injectors are individually from the engine electronics driven.
  • the rail pressure is in the pressure chamber and on to the control valve. When the control valve opens, it raises Nozzle needle against the biasing force of the nozzle spring of hers Seat off, and high-pressure fuel is injected into the combustion chamber.
  • the object of the invention is a common rail injector to be provided using conventional Injectors significantly higher nozzle needle speeds allowed.
  • the injector according to the invention be simple and inexpensive to produce.
  • the task is with a common rail injector for Injection of fuel in a common rail injection system an internal combustion engine, the one Injector housing having a fuel inlet, the with a central high-pressure fuel storage outside the injector housing and with a pressure chamber within the Injector housing communicates, from the high pressure applied fuel depending on the position a control valve is injected, which ensures that in a longitudinal bore of the injector axially against the biasing force of a nozzle spring in a Nozzle spring space is included, reciprocable Nozzle needle lifts off a seat when the pressure in the Pressure chamber is greater than the pressure in a control room, the connected via an inlet throttle with the fuel inlet is solved by the fact that the control room of a cylindrical space is formed in which a on the Brennraumfernen trained end of the nozzle needle Control pin is slidable under sealing action, and that the nozzle spring chamber in the region of the combustion chamber remote end of Nozzle needle is arranged outside the control room.
  • the nozzle spring in the control room accommodate. But the space of the Nozzle spring unfavorable to the function of the injector impact. To get acceptable closing speeds too reach, is a high spring stiffness necessary, which in turn requires a large amount of space. This increases the control chamber volume, and that Behavior of the injector deteriorates. Of this will be in particular the determination of the injection timing and the Injection length impaired. In addition, enlarged get the required tax amount, so the Overall efficiency decreases and the risk of excessive Fuel heating exists.
  • the invention provides the Advantage that the control chamber and the nozzle spring chamber on Brennraumfernen end of the nozzle needle are combined can, without the volume of the control room of the Space of the nozzle spring depends.
  • a particular embodiment of the invention is characterized characterized in that the fuel feed into the Nozzle spring chamber opens and that at the nozzle needle between the nozzle spring chamber and the pressure chamber at least one Flattening is formed.
  • the flattening becomes one Flow connection between the nozzle spring chamber and the Created pressure chamber through which the injected Fuel from the fuel inlet into the pressure chamber arrives.
  • the existing with conventional injectors Bore to the pressure chamber can be omitted.
  • Another particular embodiment of the invention is characterized in that the control room in one Valve piece is formed, which has a central Drain hole with an outlet throttle and a valve seat having. Through the central drain hole is a Connection between the control room and one Relief room created.
  • the valve seat acts with a Control valve member of a 2/2-way valve together, the Injection course of the injector according to the invention controls.
  • the inlet throttle in the Valve piece or integrated into the nozzle needle can be in the form of a bore or a groove exhibit. For manufacturing and / or cost reasons is the one or other embodiment preferable.
  • Another particular embodiment of the invention is characterized in that the nozzle needle through the Control pin is guided. Due to that inventive principle occurs in the unactuated Condition no internal leakage on the guide. Leading to lower specific consumption values.
  • Another particular embodiment of the invention is characterized in that the nozzle needle at its close to the combustion chamber.
  • the additional guide the nozzle needle increases the reliability and the Life of the injector.
  • Another particular embodiment of the invention is characterized in that at the nozzle needle a step is formed, which is a stop for a spring plate forms.
  • the spring plate forms an abutment for the Nozzle spring and at the same time the stroke stop for the Nozzle needle.
  • the first shown in Figure 1 in longitudinal section Embodiment of the injector according to the invention has a total of 1 designated injector on.
  • the Injector housing 1 comprises a nozzle body 2, which with its lower free end into the combustion chamber of the supplying internal combustion engine protrudes. With his upper, Brennraumfernen end face of the nozzle body 2 by means a clamping nut 5 axially against a holding body. 4 braced. On the holding body 4 is an inner circumferential Girth 26 formed. Supported on the peripheral web 26 a valve piece 3 with a collar.
  • nozzle body 2 In the nozzle body 2 is an axial longitudinal bore. 6 spared. In the longitudinal bore 6 is a nozzle needle. 8 received axially displaceable. At the top 9 of the Nozzle needle 8 is a sealing surface formed with a sealing seat which cooperates with the nozzle body 2 is trained. When the tip 9 of the nozzle needle 8 with its sealing surface in contact with the sealing seat, an injection hole 10 is closed in the nozzle body 2. When the nozzle needle tip 9 lifts off its seat, is with High-pressure fuel through the injection hole 10th in the combustion chamber of the internal combustion engine to be supplied injected.
  • the nozzle needle 8 has three regions with different diameters d 1 , d 2 and d 3 .
  • the diameter d 2 is largest, and the diameter d 1 and d 3 are the same size in the present embodiment, but may also have different diameters.
  • the combustion chamber remote end of the nozzle needle 8 with the diameter d 3 forms a control pin 12 which is guided axially displaceably in a central bore 14 in the valve piece 3.
  • the central bore 14 and the combustion chamber remote end face of the control pin 12 of the nozzle needle 8 limit a control room 15.
  • the control room 15 is over a Fuel outlet 16 with a (not shown) Relief space connectable.
  • an outlet throttle 17 is provided in the fuel drain 16 .
  • a Control valve member 18 With help of a Control valve member 18, the fuel outlet 16 be opened and closed.
  • the inlet throttle 19 connects the control chamber 15 with a nozzle spring chamber 20.
  • the nozzle spring chamber 20 communicates with a fuel inlet 24, through which high-pressure fuel passes from the rail (not shown) into the nozzle spring chamber 20.
  • a nozzle spring 21 is arranged in the nozzle spring chamber 20.
  • the nozzle spring 21 is supported with its one end on the peripheral web 26 of the holding body 4. With its other end, the nozzle spring 21 is supported on a spring plate 22.
  • the biasing force of the nozzle spring 21 is transmitted from the spring plate 22 to the nozzle needle 8.
  • a step 23 is formed on the nozzle needle 8 between the control pin 12 with the diameter d 3 and the portion of the nozzle needle 8 with the diameter d 2 .
  • a flattening 25 is formed in the section of the nozzle needle 8 with the diameter d 2 .
  • the flattening 25 creates a connection between the nozzle spring chamber 20 and a pressure chamber 27, which forms a fuel reservoir.
  • the biasing force of the nozzle spring 21 then ensures that the tip 9 of the nozzle needle 8 remains in abutment with its associated seat on the nozzle body 2. In this position of the nozzle needle 8 no injection takes place.
  • the valve piece 3 and the control valve member 18 form a Servo valve.
  • the servo valve can be as simple or be executed double-switching valve.
  • a magnet or a piezo can be used.
  • the inlet throttle 19 in the valve piece 3. From manufacturing and cost reasons, the inlet throttle can also in a other component, e.g. the nozzle needle 8, be formed. It is important that the nozzle spring 21 outside of Control room 15 is located. The preload or the stroke can be adjusted by the thickness of the spring plate 22 become. Instead of a flattening 25 can also several Flattened be attached to the nozzle needle 8. The out the flattening resulting flow cross-section is correct with the inlet bore of a conventional nozzle match.
  • the inlet throttle is not in the Valve piece 3 but arranged in the nozzle needle 8. With High pressure applied fuel passes through a Radial bore 31 and an axial bore 30 with a Inlet throttle 29 in the control room 15th
  • the inlet throttle has the shape of a Axialnut 35 which is attached to the control pin 12. Through the axial groove 35 passes at high pressure Fuel from the area of the flattening 25 at the Nozzle needle 8 in the control room 15th

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (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, which system has an injector housing (1) with a fuel inlet (24) that is in communication with a central high-pressure fuel reservoir outside the injector housing (1) and with a pressure chamber (27) inside the injector housing (1), from which fuel subjected to high pressure is injected as a function of the position of a control valve (18) that assures that a nozzle needle (8), which is movable back and forth and received in a longitudinal bore (6) of the injector axially counter to the prestressing force of a nozzle spring (21) that is received in a nozzle spring chamber (20), lifts from a seat when the pressure in the pressure chamber (27) is greater than the pressure in a control chamber (30) that communicates with the fuel inlet (24) via an inlet throttle (19).To achieve markedly higher nozzle needle speeds, the control chamber (15) is formed by a cylindrical chamber, in which a control peg (12), embodied on the end of the nozzle needle (8) remote from the combustion chamber, is displaceable causing a sealing effect, and that the nozzle spring chamber (20) is disposed outside the control chamber (15), in the region of the end of the nozzle needle (8) remote from the combustion chamber.

Description

Stand der TechnikState of the art

Die Erfindung betrifft einen Common-Rail-Injektor zur Einspritzung von Kraftstoff in einem Common-Rail-Einspritzsystem einer Brennkraftmaschine, der ein Injektorgehäuse mit einem Kraftstoffzulauf aufweist, der mit einem zentralen Kraftstoffhochdruckspeicher außerhalb des Injektorgehäuses und mit einem Druckraum innerhalb des Injektorgehäuses in Verbindung steht, aus dem mit Hochdruck beaufschlagter Kraftstoff in Abhängigkeit von der Stellung eines Steuerventils eingespritzt wird, das dafür sorgt, dass eine in einer Längsbohrung eines Injektors axial gegen die Vorspannkraft einer Düsenfeder, die in einem Düsenfederraum aufgenommen ist, hin und her bewegbare Düsennadel von einem Sitz abhebt, wenn der Druck in dem Druckraum größer als der Druck in einem Steuerraum ist, der über eine Zulaufdrossel mit dem Kraftstoffzulauf verbunden ist.The invention relates to a common rail injector for Injection of fuel in a common rail injection system an internal combustion engine, the one Injector housing having a fuel inlet, the with a central high-pressure fuel storage outside the injector housing and with a pressure chamber within the Injector housing communicates, from the high pressure applied fuel depending on the position a control valve is injected, which ensures that in a longitudinal bore of an injector axially against the biasing force of a nozzle spring in a Nozzle spring space is included, reciprocable Nozzle needle lifts off a seat when the pressure in the Pressure chamber is greater than the pressure in a control room, the connected via an inlet throttle with the fuel inlet is.

In Common-Rail-Einspritzsystemen fördert eine Hochdruckpumpe den Kraftstoff in den zentralen 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 in dem Druckraum und an dem Steuerventil an. Wenn das Steuerventil öffnet, hebt die Düsennadel gegen die Vorspannkraft der Düsenfeder von ihrem Sitz ab, und mit Hochdruck beaufschlagter Kraftstoff wird in den Verbrennungsraum eingespritzt.In common-rail injection systems promotes a High pressure pump the fuel in the central High-pressure accumulator, which is referred to as common rail. From the high-pressure accumulator lead high-pressure lines to the individual injectors assigned to the engine cylinders are. The injectors are individually from the engine electronics driven. The rail pressure is in the pressure chamber and on to the control valve. When the control valve opens, it raises Nozzle needle against the biasing force of the nozzle spring of hers Seat off, and high-pressure fuel is injected into the combustion chamber.

Bei herkömmlichen Injektoren, wie sie beispielsweise aus der DE 197 24 637 A1 bekannt sind, kommen relativ lange Düsennadeln zum Einsatz. Im Betrieb wirken auf die Düsennadel infolge der hohen Drücke und der schnellen Lastwechsel sehr große Kräfte. Diese Kräfte führen dazu, dass die Düsennadel in Längsrichtung gedehnt und gestaucht wird. Das wiederum hat zur Folge, dass der Düsennadelhub in Abhängigkeit von den auf die Düsennadel wirkenden Kräfte variiert.In conventional injectors, as for example DE 197 24 637 A1 are known to come relatively long Nozzle needles used. In operation affect the Nozzle needle as a result of high pressures and fast Load changes very large forces. These forces cause that the nozzle needle stretched and compressed in the longitudinal direction becomes. This in turn means that the nozzle needle stroke in Dependence on the forces acting on the nozzle needle varied.

Wegen seiner großen Massenträgheit und seiner großen Baulänge weist auch der aus der US 5,915,623 bekannte Injektor diese Nachteile auf. Bei diesem Injektor ist im Anschluss an die Düsennadel ein Steuerkolben vorgesehen, der in den Steuerraum des Injektors ragt.Because of its great inertia and its big inertia Length has also known from US 5,915,623 Injector to these disadvantages. This injector is in Connection to the nozzle needle provided a control piston, which protrudes into the control chamber of the injector.

Aufgabe der Erfindung ist es, einen Common-Rail-Injektor bereitzustellen, der unter Verwendung von konventionellen Einspritzdüsen deutlich höhere Düsennadelgeschwindigkeiten erlaubt. Außerdem soll der erfindungsgemäße Injektor einfach aufgebaut und kostengünstig herstellbar sein.The object of the invention is a common rail injector to be provided using conventional Injectors significantly higher nozzle needle speeds allowed. In addition, the injector according to the invention be simple and inexpensive to produce.

Die Aufgabe ist bei einem Common-Rail-Injektor zur Einspritzung von Kraftstoff in einem Common-Rail-Einspritzsystem einer Brennkraftmaschine, der ein Injektorgehäuse mit einem Kraftstoffzulauf aufweist, der mit einem zentralen Kraftstoffhochdruckspeicher außerhalb des Injektorgehäuses und mit einem Druckraum innerhalb des Injektorgehäuses in Verbindung steht, aus dem mit Hochdruck beaufschlagter Kraftstoff in Abhängigkeit von der Stellung eines Steuerventils eingespritzt wird, das dafür sorgt, dass eine in einer Längsbohrung des Injektors axial gegen die Vorspannkraft einer Düsenfeder, die in einem Düsenfederraum aufgenommen ist, hin und her bewegbare Düsennadel von einem Sitz abhebt, wenn der Druck in dem Druckraum größer als der Druck in einem Steuerraum ist, der über eine Zulaufdrossel mit dem Kraftstoffzulauf verbunden ist, dadurch gelöst, dass der Steuerraum von einem zylinderförmigen Raum gebildet wird, in dem ein an dem brennraumfernen Ende der Düsennadel ausgebildeter Steuerzapfen unter Dichtwirkung verschiebbar ist, und dass der Düsenfederraum im Bereich des brennraumfernen Endes der Düsennadel außerhalb des Steuerraumes angeordnet ist. Es ist auch denkbar, die Düsenfeder in dem Steuerraum unterzubringen. Dabei kann sich aber der Bauraum der Düsenfeder ungünstig auf die Funktion des Injektors auswirken. Um akzeptable Schließgeschwindigkeiten zu erreichen, ist eine hohe Federsteifigkeit notwendig, die wiederum einen großen Bauraum erfordert. Dadurch vergrößert sich das Steuerraumvolumen, und das Verhalten des Injektors verschlechtert sich. Davon werden insbesondere die Festlegung des Einspritzzeitpunkts und der Einspritzlänge beeinträchtigt. Darüber hinaus vergrößert sich die erforderliche Steuermenge, so dass der Gesamtwirkungsgrad sinkt und die Gefahr einer übermäßigen Kraftstofferwärmung besteht. Die Erfindung liefert den Vorteil, dass der Steuerraum und der Düsenfederraum am brennraumfernen Ende der Düsennadel kombiniert werden können, ohne dass das Volumen des Steuerraums von dem Bauraum der Düsenfeder abhängt. Deshalb ist es möglich, eine Düsenfeder mit einer hohen Federsteifigkeit einzubauen, die ein gutes Schließen der Düsennadel gewährleistet. Dadurch können die Einspritzdauer und der Einspritzzeitpunkt exakt festgelegt werden. Mit dem erfindungsgemäßen Injektor können beim Öffnen und Schließen Düsennadelgeschwindigkeiten realisiert werden, die größer als 1 m/s sind. Wegen des in dem Steuerraum verschiebbaren Steuerzapfens kann der Düsennadeldurchmesser beliebig gewählt werden. Durch die Trennung von Funktionsmaß, das z.B. 3 mm betragen kann, und Fertigungsmaß, das z.B. 4 mm betragen kann, werden die Fertigungskosten reduziert. The task is with a common rail injector for Injection of fuel in a common rail injection system an internal combustion engine, the one Injector housing having a fuel inlet, the with a central high-pressure fuel storage outside the injector housing and with a pressure chamber within the Injector housing communicates, from the high pressure applied fuel depending on the position a control valve is injected, which ensures that in a longitudinal bore of the injector axially against the biasing force of a nozzle spring in a Nozzle spring space is included, reciprocable Nozzle needle lifts off a seat when the pressure in the Pressure chamber is greater than the pressure in a control room, the connected via an inlet throttle with the fuel inlet is solved by the fact that the control room of a cylindrical space is formed in which a on the Brennraumfernen trained end of the nozzle needle Control pin is slidable under sealing action, and that the nozzle spring chamber in the region of the combustion chamber remote end of Nozzle needle is arranged outside the control room. It is also conceivable, the nozzle spring in the control room accommodate. But the space of the Nozzle spring unfavorable to the function of the injector impact. To get acceptable closing speeds too reach, is a high spring stiffness necessary, which in turn requires a large amount of space. This increases the control chamber volume, and that Behavior of the injector deteriorates. Of this will be in particular the determination of the injection timing and the Injection length impaired. In addition, enlarged get the required tax amount, so the Overall efficiency decreases and the risk of excessive Fuel heating exists. The invention provides the Advantage that the control chamber and the nozzle spring chamber on Brennraumfernen end of the nozzle needle are combined can, without the volume of the control room of the Space of the nozzle spring depends. That's why it's possible a nozzle spring with a high spring stiffness incorporate a good closing of the nozzle needle guaranteed. This allows the duration of injection and the Injection time to be set exactly. With the Injector according to the invention can be opened and closed Nozzle needle speeds are realized that are larger than 1 m / s. Because of the displaceable in the control room Control pin, the nozzle needle diameter can be arbitrary to get voted. By the separation of functional measure, the e.g. May be 3 mm, and manufacturing dimension, e.g. 4 mm can be, the manufacturing costs are reduced.

Eine besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, dass der Kraftstoffzulauf in den Düsenfederraum mündet und dass an der Düsennadel zwischen dem Düsenfederraum und dem Druckraum mindestens eine Abflachung ausgebildet ist. Durch die Abflachung wird eine Strömungsverbindung zwischen dem Düsenfederraum und dem Druckraum geschaffen, durch die der einzuspritzende Kraftstoff aus dem Kraftstoffzulauf in den Druckraum gelangt. Die bei herkömmlichen Injektoren vorhandene Bohrung zum Druckraum kann entfallen.A particular embodiment of the invention is characterized characterized in that the fuel feed into the Nozzle spring chamber opens and that at the nozzle needle between the nozzle spring chamber and the pressure chamber at least one Flattening is formed. The flattening becomes one Flow connection between the nozzle spring chamber and the Created pressure chamber through which the injected Fuel from the fuel inlet into the pressure chamber arrives. The existing with conventional injectors Bore to the pressure chamber can be omitted.

Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, dass der Steuerraum in einem Ventilstück ausgebildet ist, das eine zentrale Ablaufbohrung mit einer Ablaufdrossel und einem Ventilsitz aufweist. Durch die zentrale Ablaufbohrung wird eine Verbindung zwischen dem Steuerraum und einem Entlastungsraum geschaffen. Der Ventilsitz wirkt mit einem Steuerventilglied eines 2/2-Wegeventils zusammen, das den Einspritzverlauf des erfindungsgemäßen Injektors steuert.Another particular embodiment of the invention is characterized in that the control room in one Valve piece is formed, which has a central Drain hole with an outlet throttle and a valve seat having. Through the central drain hole is a Connection between the control room and one Relief room created. The valve seat acts with a Control valve member of a 2/2-way valve together, the Injection course of the injector according to the invention controls.

Weitere besondere Ausführungsarten der Erfindung sind dadurch gekennzeichnet, dass die Zulaufdrossel in das Ventilstück oder in die Düsennadel integriert ist. Die Zulaufdrossel kann die Form einer Bohrung oder einer Nut aufweisen. Aus Fertigungs- und/oder Kostengründen ist die eine oder andere Ausführungsart vorzuziehen.Other particular embodiments of the invention are characterized in that the inlet throttle in the Valve piece or integrated into the nozzle needle. The Inlet throttle can be in the form of a bore or a groove exhibit. For manufacturing and / or cost reasons is the one or other embodiment preferable.

Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, dass die Düsennadel durch den Steuerzapfen geführt ist. Bedingt durch das erfindungsgemäße Funktionsprinzip tritt im unbetätigten Zustand keine innere Leckage an der Führung auf. Das führt zu geringeren spezifischen Verbrauchswerten.Another particular embodiment of the invention is characterized in that the nozzle needle through the Control pin is guided. Due to that inventive principle occurs in the unactuated Condition no internal leakage on the guide. Leading to lower specific consumption values.

Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, dass die Düsennadel an ihrem brennraumnahen Ende geführt ist. Die zusätzliche Führung der Düsennadel erhöht die Betriebssicherheit und die Lebensdauer des Injektors.Another particular embodiment of the invention is characterized in that the nozzle needle at its close to the combustion chamber. The additional guide the nozzle needle increases the reliability and the Life of the injector.

Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, dass an der Düsennadel eine Stufe ausgebildet ist, die einen Anschlag für einen Federteller bildet. Der Federteller bildet ein Widerlager für die Düsenfeder und gleichzeitig den Hubanschlag für die Düsennadel. Durch die Wahl einer geeigneten Dicke des Federtellers kann sowohl die Vorspannkraft der Düsenfeder als auch der Düsennadelhub eingestellt werden.Another particular embodiment of the invention is characterized in that at the nozzle needle a step is formed, which is a stop for a spring plate forms. The spring plate forms an abutment for the Nozzle spring and at the same time the stroke stop for the Nozzle needle. By choosing a suitable thickness of the Spring plate can both the biasing force of the nozzle spring as well as the nozzle needle stroke can be adjusted.

Weitere Vorteile, Merkmale und Einzelheiten der Erfindung ergeben sich aus der nachfolgenden Beschreibung, in der unter Bezugnahme auf die Zeichnung verschiedene Ausführungsbeispiele der Erfindung im Einzelnen beschrieben sind. Dabei können die in den Ansprüchen und in der Beschreibung erwähnten Merkmale jeweils einzeln für sich oder in beliebiger Kombination erfindungswesentlich sein. In der Zeichnung zeigen:

Figur 1:
ein erstes Ausführungsbeispiel eines erfindungsgemäßen Injektors mit Zulaufdrossel im Ventilstück;
Figur 2:
ein zweites Ausführungsbeispiel eines erfindungsgemäßen Injektors mit Zulaufdrossel in der Düsennadel;
Figur 3:
ein drittes Ausführungsbeispiel eines erfindungsgemäßen Injektors mit einer Drosselnut in der Düsennadel; und
Figur 4:
ein viertes Ausführungsbeispiel eines erfindungsgemäßen Injektors mit Drosselnut und separater Nadelführung.
Further advantages, features and details of the invention will become apparent from the following description in which, with reference to the drawings, various embodiments of the invention are described in detail. The features mentioned in the claims and in the description may each be essential to the invention individually or in any desired combination. In the drawing show:
FIG. 1:
a first embodiment of an injector according to the invention with inlet throttle in the valve piece;
FIG. 2:
A second embodiment of an injector according to the invention with inlet throttle in the nozzle needle;
FIG. 3:
A third embodiment of an injector according to the invention with a throttle groove in the nozzle needle; and
FIG. 4:
A fourth embodiment of an injector according to the invention with throttling groove and separate needle guide.

Das in Figur 1 im Längsschnitt dargestellte erste Ausführungsbeispiel des erfindungsgemäßen Injektors weist ein insgesamt mit 1 bezeichnetes Injektorgehäuse auf. Das Injektorgehäuse 1 umfasst einen Düsenkörper 2, der mit seinem unteren freien Ende in den Brennraum der zu versorgenden Brennkraftmaschine ragt. Mit seiner oberen, brennraumfernen Stirnfläche ist der Düsenkörper 2 mittels einer Spannmutter 5 axial gegen einen Haltekörper 4 verspannt. An dem Haltekörper 4 ist ein innen umlaufender Umfangssteg 26 ausgebildet. An dem Umfangssteg 26 stützt sich ein Ventilstück 3 mit einem Bund ab.The first shown in Figure 1 in longitudinal section Embodiment of the injector according to the invention has a total of 1 designated injector on. The Injector housing 1 comprises a nozzle body 2, which with its lower free end into the combustion chamber of the supplying internal combustion engine protrudes. With his upper, Brennraumfernen end face of the nozzle body 2 by means a clamping nut 5 axially against a holding body. 4 braced. On the holding body 4 is an inner circumferential Girth 26 formed. Supported on the peripheral web 26 a valve piece 3 with a collar.

In dem Düsenkörper 2 ist eine axiale Längsbohrung 6 ausgespart. In der Längsbohrung 6 ist eine Düsennadel 8 axial verschiebbar aufgenommen. An der Spitze 9 der Düsennadel 8 ist eine Dichtfläche ausgebildet, die mit einem Dichtsitz zusammenwirkt, der an dem Düsenkörper 2 ausgebildet ist. Wenn sich die Spitze 9 der Düsennadel 8 mit ihrer Dichtfläche in Anlage an dem Dichtsitz befindet, ist ein Spritzloch 10 in dem Düsenkörper 2 verschlossen. Wenn die Düsennadelspitze 9 von ihrem Sitz abhebt, wird mit Hochdruck beaufschlagter Kraftstoff durch das Spritzloch 10 in den Brennraum der zu versorgenden Brennkraftmaschine eingespritzt.In the nozzle body 2 is an axial longitudinal bore. 6 spared. In the longitudinal bore 6 is a nozzle needle. 8 received axially displaceable. At the top 9 of the Nozzle needle 8 is a sealing surface formed with a sealing seat which cooperates with the nozzle body 2 is trained. When the tip 9 of the nozzle needle 8 with its sealing surface in contact with the sealing seat, an injection hole 10 is closed in the nozzle body 2. When the nozzle needle tip 9 lifts off its seat, is with High-pressure fuel through the injection hole 10th in the combustion chamber of the internal combustion engine to be supplied injected.

Ausgehend von der Spitze 9 weist die Düsennadel 8 drei Bereiche mit unterschiedlichen Durchmessern d1, d2 und d3 auf. Der Durchmesser d2 ist am größten, und die Durchmesser d1 und d3 sind im vorliegenden Ausführungsbeispiel gleich groß, können aber auch unterschiedliche Durchmesser aufweisen. Das brennraumferne Ende der Düsennadel 8 mit dem Durchmesser d3 bildet einen Steuerzapfen 12, der in einer zentralen Bohrung 14 in dem Ventilstück 3 axial verschiebbar geführt ist.Starting from the tip 9, the nozzle needle 8 has three regions with different diameters d 1 , d 2 and d 3 . The diameter d 2 is largest, and the diameter d 1 and d 3 are the same size in the present embodiment, but may also have different diameters. The combustion chamber remote end of the nozzle needle 8 with the diameter d 3 forms a control pin 12 which is guided axially displaceably in a central bore 14 in the valve piece 3.

Die zentrale Bohrung 14 und die brennraumferne Stirnfläche des Steuerzapfens 12 der Düsennadel 8 begrenzen einen Steuerraum 15. Der Steuerraum 15 ist über einen Kraftstoffablauf 16 mit einem (nicht dargestellten) Entlastungsraum verbindbar. In dem Kraftstoffablauf 16 ist eine Ablaufdrossel 17 vorgesehen. Mit Hilfe eines Steuerventilgliedes 18 kann der Kraftstoffablauf 16 geöffnet und geschlossen werden.The central bore 14 and the combustion chamber remote end face of the control pin 12 of the nozzle needle 8 limit a control room 15. The control room 15 is over a Fuel outlet 16 with a (not shown) Relief space connectable. In the fuel drain 16 is an outlet throttle 17 is provided. With help of a Control valve member 18, the fuel outlet 16 be opened and closed.

Durch eine Zulaufdrossel 19 kann Kraftstoff in den Steuerraum 15 gelangen. Die Zulaufdrossel 19 verbindet den Steuerraum 15 mit einem Düsenfederraum 20. Der Düsenfederraum 20 steht mit einem Kraftstoffzulauf 24 in Verbindung, durch den mit Hochdruck beaufschlagter Kraftstoff von dem (nicht dargestellten) Rail in den Düsenfederraum 20 gelangt. In dem Düsenfederraum 20 ist eine Düsenfeder 21 angeordnet. Die Düsenfeder 21 stützt sich mit ihrem einen Ende an dem Umfangssteg 26 des Haltekörpers 4 ab. Mit ihrem anderen Ende stützt sich die Düsenfeder 21 an einem Federteller 22 ab. Die Vorspannkraft der Düsenfeder 21 wird von dem Federteller 22 auf die Düsennadel 8 übertragen. Zu diesem Zweck ist an der Düsennadel 8 zwischen dem Steuerzapfen 12 mit dem Durchmesser d3 und dem Abschnitt der Düsennadel 8 mit dem Durchmesser d2 eine Stufe 23 ausgebildet.Through an inlet throttle 19 fuel can enter the control chamber 15. The inlet throttle 19 connects the control chamber 15 with a nozzle spring chamber 20. The nozzle spring chamber 20 communicates with a fuel inlet 24, through which high-pressure fuel passes from the rail (not shown) into the nozzle spring chamber 20. In the nozzle spring chamber 20, a nozzle spring 21 is arranged. The nozzle spring 21 is supported with its one end on the peripheral web 26 of the holding body 4. With its other end, the nozzle spring 21 is supported on a spring plate 22. The biasing force of the nozzle spring 21 is transmitted from the spring plate 22 to the nozzle needle 8. For this purpose, a step 23 is formed on the nozzle needle 8 between the control pin 12 with the diameter d 3 and the portion of the nozzle needle 8 with the diameter d 2 .

In dem Abschnitt der Düsennadel 8 mit dem Durchmesser d2 ist eine Abflachung 25 ausgebildet. Die Abflachung 25 schafft eine Verbindung zwischen dem Düsenfederraum 20 und einem Druckraum 27, der ein Kraftstoffreservoir bildet. Wenn der Kraftstoffablauf 16 durch das Steuerventilglied 18 verschlossen ist, herrscht in dem Steuerraum 15 und dem Druckraum 27 Raildruck. Die Vorspannkraft der Düsenfeder 21 sorgt dann dafür, dass die Spitze 9 der Düsennadel 8 an ihrem zugehörigen Sitz an dem Düsenkörper 2 in Anlage bleibt. In dieser Stellung der Düsennadel 8 findet keine Einspritzung statt.In the section of the nozzle needle 8 with the diameter d 2 a flattening 25 is formed. The flattening 25 creates a connection between the nozzle spring chamber 20 and a pressure chamber 27, which forms a fuel reservoir. When the fuel outlet 16 is closed by the control valve member 18, prevails in the control chamber 15 and the pressure chamber 27 rail pressure. The biasing force of the nozzle spring 21 then ensures that the tip 9 of the nozzle needle 8 remains in abutment with its associated seat on the nozzle body 2. In this position of the nozzle needle 8 no injection takes place.

Wenn das Steuerventilglied 18 den Kraftstoffablauf 16 öffnet, sinkt der Druck in dem Steuerraum 15 ab. In dem Druckraum 27 herrscht nach wie vor Raildruck. Das führt dazu, dass die Düsennadel 8 mit ihrer Spitze 9 von dem zugehörigen Sitz abhebt, und Kraftstoff in den Brennraum der Brennkraftmaschine eingespritzt wird. Wenn das Steuerventilglied 18 den Kraftstoffablauf 16 wieder schließt, steigt der Druck in dem Steuerraum 15 an, was dazu führt, dass die Düsennadel 8 schließt.When the control valve member 18, the fuel drain 16 opens, the pressure in the control chamber 15 decreases. By doing Pressure chamber 27 still prevails rail pressure. Leading to that the nozzle needle 8 with its tip 9 of the associated seat lifts, and fuel into the combustion chamber the internal combustion engine is injected. If that Control valve member 18, the fuel outlet 16 again closes, the pressure in the control chamber 15 increases, which causes the nozzle needle 8 closes.

Das Ventilstück 3 und das Steuerventilglied 18 bilden ein Servoventil. Das Servoventil kann als einfach- oder doppelschaltendes Ventil ausgeführt sein. Als Steller können ein Magnet oder ein Piezo eingesetzt werden. Bei dem in Figur 1 dargestellten Ausführungsbeispiel befindet sich die Zulaufdrossel 19 in dem Ventilstück 3. Aus Fertigungs- und Kostengründen kann die Zulaufdrossel auch in einem anderen Bauteil, z.B. der Düsennadel 8, ausgebildet sein. Wichtig ist, dass sich die Düsenfeder 21 außerhalb des Steuerraums 15 befindet. Die Vorspannung bzw. der Hub können durch die Dicke des Federtellers 22 eingestellt werden. Statt der einen Abflachung 25 können auch mehrere Abflachungen an der Düsennadel 8 angebracht sein. Der aus den Abflachungen resultierende Durchflussquerschnitt stimmt mit der Zulaufbohrung einer herkömmlichen Düse überein.The valve piece 3 and the control valve member 18 form a Servo valve. The servo valve can be as simple or be executed double-switching valve. As a steller a magnet or a piezo can be used. In which is shown in Figure 1 embodiment the inlet throttle 19 in the valve piece 3. From manufacturing and cost reasons, the inlet throttle can also in a other component, e.g. the nozzle needle 8, be formed. It is important that the nozzle spring 21 outside of Control room 15 is located. The preload or the stroke can be adjusted by the thickness of the spring plate 22 become. Instead of a flattening 25 can also several Flattened be attached to the nozzle needle 8. The out the flattening resulting flow cross-section is correct with the inlet bore of a conventional nozzle match.

Wenn keine Einspritzung stattfindet, wird die Düsennadel 8 durch den Raildruck in den Sitz gepresst. Die Summe aus Steuerraum- und Düsenfederschließkraft überwiegt gegenüber der Sitzkraft am Nadelsitz. Die Einspritzung wird durch die Druckentlastung des Steuerraums 15 eingeleitet. Die Düsennadel 8 hebt sich aus dem Sitz und schlägt im Endhub mit dem Federteller 22 am Ventilstück 3 an. Die Öffnungs- und Schließgeschwindigkeit wird bei festem Ablauf/Zulauf-Verhältnis von dem Querschnitt des Steuerzapfens 12 bestimmt, dessen verdrängtes Volumen wie eine zusätzliche Quelle (beim Öffnen) bzw. Senke (beim Schließen) wirkt. Um die Kräftebilanz zwischen Nadelsitz und Steuerzapfen nicht einseitig zu verschieben, müsste man bei konventionellen Common-Rail-Systemen mit Druckstange den Nadeldurchmesser von 4 mm auf etwa 3 bis 3,5 mm verkleinern. Problematisch ist hierbei die Fertigungs- und Kostenseite. Der Vorteil der Erfindung liegt darin, dass der hydraulisch wirksame Durchmesser unabhängig vom geometrisch vorgegebenen Nadeldurchmesser ist. Sobald das Steuerventilglied 18 wieder schließt, steigt der Druck im Steuerraum 15 an, und die Düsennadel 8 geht in den Sitz zurück.If no injection takes place, the nozzle needle 8 pressed into the seat by the rail pressure. The sum of Control chamber and nozzle spring closing force outweighs the seat force at the needle seat. The injection is through the Pressure relief of the control chamber 15 initiated. The Nozzle needle 8 lifts out of the seat and hits the final stroke with the spring plate 22 on the valve piece 3. The opening and closing speed becomes fixed drain / feed ratio from the cross section of the control pin 12th certainly, its displaced volume like an extra Source (when opening) or sink (when closing) works. Around the balance of forces between needle seat and control pin not to move one-sidedly, one would have to be conventional Common rail systems with push rod the needle diameter from 4 mm to about 3 to 3.5 mm. Problematic Here is the manufacturing and cost side. The advantage The invention is that the hydraulically effective Diameter independent of the geometric given Needle diameter is. Once the control valve member 18 closes again, the pressure in the control room 15 increases, and the nozzle needle 8 goes back into the seat.

Das in Figur 2 dargestellte Ausführungsbeispiel entspricht weitgehend dem in Figur 1 dargestellten ersten Ausführungsbeispiel der Erfindung. Der Einfachheit halber werden zur Bezeichnung gleicher Teile dieselben Bezugszeichen verwendet. Außerdem wird, um Wiederholungen zu vermeiden, auf die vorstehende ausführliche Beschreibung des ersten Ausführungsbeispiels verwiesen. Im Folgenden wird nur auf die Unterschiede zwischen den beiden Ausführungsbeispielen eingegangen. Bei der ausführlichen Beschreibung der in den Figuren 3 und 4 dargestellten Ausführungsbeispiele wird analog vorgegangen.The embodiment shown in Figure 2 corresponds largely the first shown in Figure 1 Embodiment of the invention. For simplicity become the same for designating equal parts Reference numeral used. It also gets to repetitions to avoid the above detailed description of the first embodiment. Hereinafter will only focus on the differences between the two Embodiments received. At the detailed Description of the shown in Figures 3 and 4 Embodiments will proceed analogously.

Bei dem in Figur 2 dargestellten zweiten Ausführungsbeispiel ist die Zulaufdrossel nicht in dem Ventilstück 3 sondern in der Düsennadel 8 angeordnet. Mit Hochdruck beaufschlagter Kraftstoff gelangt über eine Radialbohrung 31 und eine Axialbohrung 30 mit einer Zulaufdrossel 29 in den Steuerraum 15.In the second shown in Figure 2 Embodiment, the inlet throttle is not in the Valve piece 3 but arranged in the nozzle needle 8. With High pressure applied fuel passes through a Radial bore 31 and an axial bore 30 with a Inlet throttle 29 in the control room 15th

Bei dem in Figur 3 dargestellten dritten Ausführungsbeispiel hat die Zulaufdrossel die Form einer Axialnut 35, die an dem Steuerzapfen 12 angebracht ist. Durch die Axialnut 35 gelangt mit Hochdruck beaufschlagter Kraftstoff aus dem Bereich der Abflachung 25 an der Düsennadel 8 in den Steuerraum 15.In the third shown in Figure 3 Embodiment, the inlet throttle has the shape of a Axialnut 35 which is attached to the control pin 12. Through the axial groove 35 passes at high pressure Fuel from the area of the flattening 25 at the Nozzle needle 8 in the control room 15th

Bei dem in Figur 4 dargestellten Ausführungsbeispiel ist im Unterschied zu dem vorangegangenen dritten Ausführungsbeispiel eine zusätzliche Führung 38 an dem brennraumnahen Ende der Düsennadel 8 ausgebildet. Mehrere Abflachungen 39 sorgen für eine Strömungsverbindung von dem Druckraum 27 zur Düsennadelspitze 9.In the embodiment shown in Figure 4 is in Difference to the previous third Embodiment, an additional guide 38 on the formed close to the combustion chamber end of the nozzle needle 8. Several Flats 39 provide a flow connection of the Pressure chamber 27 to the nozzle needle tip 9.

Claims (10)

  1. Common-rail injector for the injection of fuel in a common-rail injection system of an internal combustion engine, the said injector having an injector housing (1) with a fuel inflow (24) which is connected, outside the injector housing (1), to a central high-pressure fuel accumulator and, inside the injector housing (1), to a pressure space (27), out of which fuel acted upon by high pressure is injected as a function of the position of a control valve (18) which ensures that a nozzle needle (8), moveable to and fro in a longitudinal bore (6) of the injector axially counter to the prestressing force of a nozzle spring (21) received in a nozzle-spring space (20), lifts off from a seat when the pressure in the pressure space (27) is higher than the pressure in a control space (15) which is connected to the fuel inflow (24) via an inflow throttle (19), characterized in that the control space (15) is formed by a cylindrical space, in which a control pin (12) formed at that end of the nozzle needle (8) which is remote from the combustion space can be displaced, at the same time exerting a sealing action, in that the nozzle-spring space (20) is arranged outside the control space (15), in the region of that end of the nozzle needle (8) which is remote from the combustion space, and in that the nozzle-spring space (20) partially surrounds the nozzle needle (8).
  2. Common-rail injector according to Claim 1, characterized in that the fuel inflow (24) issues into the nozzle-spring space (20), and in that at least one flattening (25) is formed on the nozzle needle (8), between the nozzle-spring space (20) and the pressure space (27).
  3. Common-rail injector according to one of the preceding claims, characterized in that the control space (15) is formed in a valve piece (3) which has a central outflow bore (16) with an outflow throttle (17) and a valve seat.
  4. Common-rail injector according to Claim 3, characterized in that the inflow throttle is provided in a bore (19) in the valve piece (3), the said bore connecting the control space (15) to the nozzle-spring space (20).
  5. Common-rail injector according to Claim 3, characterized in that the inflow throttle (30, 31; 35) is integrated into the nozzle needle (8).
  6. Common-rail injector according to Claim 5, characterized in that the inflow throttle (29) is arranged in a central bore (30) in the nozzle needle (8), the said bore being connected to the nozzle-spring space (20) via a radial bore (31).
  7. Common-rail injector according to Claim 5, characterized in that the inflow throttle is formed by a groove (35) which runs in the longitudinal direction of the nozzle needle (8) and which is provided on the control pin (12).
  8. Common-rail injector according to one of the preceding claims, characterized in that the nozzle needle (8) is guided by the control pin (12).
  9. Common-rail injector according to one of the preceding claims, characterized in that the nozzle needle (8) is guided at its end (38) near the combustion space.
  10. Common-rail injector according to one of the preceding claims, characterized in that a step (23), which constitutes an abutment for a spring plate (22), is formed on the nozzle needle (8).
EP00962182A 1999-08-04 2000-08-01 Fuel injector for a common rail fuel system Expired - Lifetime EP1117921B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19936667 1999-08-04
DE19936667A DE19936667A1 (en) 1999-08-04 1999-08-04 Common rail injector
PCT/DE2000/002530 WO2001011219A1 (en) 1999-08-04 2000-08-01 Common rail injector

Publications (2)

Publication Number Publication Date
EP1117921A1 EP1117921A1 (en) 2001-07-25
EP1117921B1 true EP1117921B1 (en) 2005-04-27

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP00962182A Expired - Lifetime EP1117921B1 (en) 1999-08-04 2000-08-01 Fuel injector for a common rail fuel system

Country Status (8)

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US (1) US6726121B1 (en)
EP (1) EP1117921B1 (en)
JP (1) JP2003506620A (en)
KR (1) KR20010079991A (en)
AT (1) ATE294325T1 (en)
CZ (1) CZ20011136A3 (en)
DE (2) DE19936667A1 (en)
WO (1) WO2001011219A1 (en)

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DE10111783B4 (en) * 2001-03-12 2005-10-20 Bosch Gmbh Robert injection
DE10152173A1 (en) * 2001-10-23 2003-04-30 Bosch Gmbh Robert Solenoid valve for controlling an injection valve
DE10220931C1 (en) * 2002-05-10 2003-11-27 Siemens Ag Injector for fuel injection
AU2003900748A0 (en) * 2003-02-13 2003-03-06 Vaporate Pty Ltd Fuel delivery system
AT500889B8 (en) * 2004-08-06 2007-02-15 Bosch Gmbh Robert DEVICE FOR INJECTING FUEL IN THE COMBUSTION ENGINE OF AN INTERNAL COMBUSTION ENGINE
CN100385109C (en) 2005-01-18 2008-04-30 侯德洋 Micro displacement variable cross-section uniform fine atomization combined type oil spout device
DE102017000911B3 (en) * 2017-02-02 2018-06-28 L'orange Gmbh arrangement
US11585452B2 (en) 2019-12-03 2023-02-21 Woodward, Inc. Fuel nozzle with reduced flow tolerance
CN113250876B (en) * 2021-06-18 2022-04-26 中国北方发动机研究所(天津) Slide valve type common rail oil sprayer
CN116753096B (en) * 2023-08-11 2023-10-13 山西焦煤集团正仁煤业有限公司 Oil supply part structure for coal mine truck

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Also Published As

Publication number Publication date
ATE294325T1 (en) 2005-05-15
KR20010079991A (en) 2001-08-22
EP1117921A1 (en) 2001-07-25
DE50010158D1 (en) 2005-06-02
CZ20011136A3 (en) 2002-01-16
DE19936667A1 (en) 2001-02-22
WO2001011219A1 (en) 2001-02-15
JP2003506620A (en) 2003-02-18
US6726121B1 (en) 2004-04-27

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