EP1252429A2 - Valve for the control of fluids - Google Patents

Valve for the control of fluids

Info

Publication number
EP1252429A2
EP1252429A2 EP01909462A EP01909462A EP1252429A2 EP 1252429 A2 EP1252429 A2 EP 1252429A2 EP 01909462 A EP01909462 A EP 01909462A EP 01909462 A EP01909462 A EP 01909462A EP 1252429 A2 EP1252429 A2 EP 1252429A2
Authority
EP
European Patent Office
Prior art keywords
valve
piston
pressure chamber
seat
slide
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
EP01909462A
Other languages
German (de)
French (fr)
Other versions
EP1252429B1 (en
Inventor
Friedrich Boecking
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1252429A2 publication Critical patent/EP1252429A2/en
Application granted granted Critical
Publication of EP1252429B1 publication Critical patent/EP1252429B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • F02M45/06—Pumps peculiar thereto
    • 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
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means
    • F02M59/468—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means using piezoelectric operating means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/50—Arrangements of springs for valves used in fuel injectors or fuel injection pumps
    • F02M2200/502—Springs biasing the valve member to the open position

Definitions

  • the invention relates to a valve for controlling liquids according to the preamble of claim 1.
  • a valve is known in which an actuating piston of a valve member is slidably arranged in a part of the stepped bore with a small 'diameter in a stepped bore of the valve housing , A larger piston movable by a piezo actuator is arranged in part of the stepped bore with a larger diameter.
  • a hydraulic pressure chamber filled with a pressure medium is formed between the two pistons, so that a hydraulic translation of a movement of the piezo actuator takes place. That is, when the big piston through the
  • Piezo actuator is moved by a certain distance, the actuating piston of the valve member makes a stroke increased by the transmission ratio of the piston diameter, since the piston of the piezo actuator has a larger area than the actuating piston of the valve member.
  • 3/2 control valves are also used, as is disclosed, for example, in US Pat. No. 5,738,075.
  • Such 3/2 control valves can be designed as seat slide or seat-seat valves.
  • the pressure from a rail is determined by means of a controllable piston via a pressure chamber and a booster piston to a control chamber from which the fuel is injected into the combustion chamber.
  • the pressure chamber is connected to a drain line in the non-actuated state, so that in
  • Pressure chamber leakage oil pressure prevails.
  • a connection between the high pressure area and the leakage oil area occurs for a short time, regardless of the type of valve (seat slide valve or seat-seat valve). This results in a so-called exhaust surge in the drain line. This hinders the relief of the control chamber of the valve until the valve has sealed the opening to the high pressure area.
  • valve according to the invention for controlling liquids' with the characterizing features of patent claim 1 has the advantage that such a surge pulse to the leakage oil line does not occur. This is prevented by connecting a slide element upstream of the seat of the control valve.
  • the slide element is arranged in the opening direction immediately in front of the area of the piston with which the piston sits on the valve seat. Depending on the stroke of the slide element, this enables a delayed opening of the passage between the inlet line and the pressure chamber, but an immediate closing of the passage between the inlet line and the pressure chamber. It can thus be ensured at any time when the control valve is switched over that there is no connection between the supply line and the leakage oil line.
  • the stroke of the piston for opening the connection between the inlet line and the pressure chamber is at least the same due to the provision of the slide element, but advantageously longer than a stroke for closing or opening a passage between the pressure chamber Control valve and the drain line. This can advantageously prevent the exhaust surge in the leak oil line. Furthermore, when the control valve is switched over, the relief of the control chamber is no longer impeded, since the slide element immediately seals off the high-pressure region.
  • the slide element of the piston is cylindrical.
  • the piston of the control valve is advantageously configured in two parts. This allows a seat slide valve with a pressure space arranged between them to be realized.
  • the control valve is particularly advantageously constructed as a force-balancing valve.
  • the guide diameter at the valve seat corresponds to the diameter of the slide element.
  • the piston of the control valve is also advantageously formed in one piece. This allows a 3/2-seat slide valve to be used as an exhaust valve.
  • the valve for controlling liquids is preferably designed as a 3/2-seat slide valve or as a 3/2-seat seat valve.
  • the valve according to the invention can thus be used to achieve a clear function of a control valve from the high-pressure inlet area into the leakage oil line without an exhaust surge.
  • the overlap on the leakage oil slide element can be optimized.
  • an optimal slide ratio can be formed from the respective stroke lengths.
  • the overlap should be selected so that there are no significant delays in the valve, but it is ensured that there is no discharge surge in the leak oil line.
  • Fig. 1 is a schematic sectional view of a fuel injection valve according to a first
  • Fig. 2 is a schematic partial sectional view of a fuel injection valve according to a second
  • valve according to the invention is used in a pressure-translated common rail injector.
  • the valve according to the invention is designed as a 3/2-seat slide control valve 1.
  • the fuel injection valve comprises the 3/2 control valve 1.
  • the control valve 1 consists of an actuating element 2 and a first piston 3 and a second piston 4.
  • an actuating element 2 for example, a Known magnetic actuator or a known piezo actuator can be used.
  • the first piston 3 consists of several piston sections 3a to 3e.
  • a first piston section 3a is cylindrical and is connected to the actuating element 2. This is followed by a second piston section 3b, which is concave and with a corresponding position of the piston 3 opens a first passage 10 on the valve seat. Subsequent to the second
  • Piston section 3b is followed by the third piston section designed as slide element 3c.
  • the third piston section 3 c is arranged directly on the valve seat or on the first passage 10.
  • the piston 2 further comprises an expanding fourth piston section 3d and a further cylindrical fifth piston section 3e.
  • the fifth piston section 3e is connected to a pressure chamber 6 arranged between the first piston 3 and the second piston 4.
  • the second piston 4 consists of a slide element 4a and a base body 4b.
  • the piston 4 is held in the open position by a spring 9, so that a second passage 5 between the pressure chamber 6 and a leakage oil line 8 is open.
  • the leakage oil pressure prevails in the pressure chamber 6 in the non-actuated state.
  • a guide diameter d on the first piston 3 is equal to one
  • control valve 1 is constructed as a force-balancing valve.
  • the pressure chamber 6 is also connected to a booster piston 11 via a line 19.
  • the multi-stage translator piston 11 is via a Return spring 12 is held in its initial position and communicates with a control chamber 15 with its smaller piston diameter.
  • the control chamber 15 is filled with fuel via a filling valve 13 and a fuel line 14. The fuel is emitted into an unshown combustion chamber via an injection nozzle 16 which is biased by a spring 17.
  • an overlap on the piston 4 can be optimized depending on the application by the slide ratio h 2 / h x .
  • the coverage (h 2 - h) will be extended (ie greater than 0) to ensure that no leakage oil surge occurs.
  • FIG. 2 shows a second exemplary embodiment of a valve according to the invention for controlling liquids.
  • This control valve 1 can also be used in a fuel injection valve. Since that
  • Fuel injection valve of the second embodiment in comparison with the first embodiment has only changes to the control valve 1, the other parts of the fuel injection valve in FIG. 2 and in the following description have been omitted, since these are accurate are formed as in the first embodiment. Furthermore, the same reference numerals are used in the second exemplary embodiment for similar parts as in the first exemplary embodiment.
  • the control valve 1 of the second exemplary embodiment has only one piston 3.
  • the piston comprises a plurality of piston sections 3a to 3e.
  • the piston 3 also has a first cylindrical piston section 3a and a second piston section 3b, which is concave.
  • the second piston section 3b is adjoined by a slide element 3c, which is arranged directly on the valve seat.
  • the piston 3 further comprises a fourth, tapering piston section 3d and a fifth, cylindrical piston section 3e, which is connected to an actuating element 2.
  • the piston 3 is partly arranged in a pressure chamber 6 and opens / closes the connection between an inlet line 7 from a rail and a booster piston connected to the pressure chamber 6 via a line 19 (not shown).
  • the control valve 1 also includes a leak oil line 8.
  • the operation of the control valve 1 according to the second embodiment is as follows.
  • the piston 3 is moved in the direction of the actuating element 2.
  • the fourth, tapering piston section 3d lifts off the piston seat at the first passage 10.
  • the slide element 3c is arranged directly after the second piston section 3b, the connection 10 between the high-pressure supply line 7 and the pressure chamber 6 is only opened when the edge of the slide element 3c facing the second piston section 3b has been guided past the valve seat 10. Since, as shown in Fig. 2, the stroke length h 2 of the slide element 3c is greater than the stroke length h provided at the second passage 5 between the first piston section 3a and the second piston section 3b, it is ensured that the connection between the pressure chamber 6 and the
  • Leakage oil line 8 is closed before the connection via the first passage 10 between the inlet line 7 and the pressure chamber 6 is opened.
  • the control valve 1 When the control valve 1 is closed, the connection between the inlet line 7 and the pressure chamber 6 is first closed before the passage 5 between the pressure chamber 6 and the leakage oil line 8 is opened.
  • the desired coverage (h x -h 2 ) can be set by the ratio of the 'stroke length h 2 of the slide element 3c to the stroke length ⁇ at the second passage 5.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Fluid-Driven Valves (AREA)
  • Control Of Non-Electrical Variables (AREA)
  • Control Of Fluid Pressure (AREA)
  • Safety Valves (AREA)

Abstract

The invention relates to a valve, for the control of fluids, with an inlet line (7) and a oil overflow line (8), which are each connected to a pressure chamber (6). Furthermore, a piston element (3, 4) is provided, which may be adjusted, by means of an actuator (2) and which opens a first through channel (10), between the inlet line (7) and the pressure chamber (6). The piston element (3, 4) has a slide element (3c), mounted directly on the piston seat (10). The stroke length (h2) of the slide element (3c), for opening the first through channe, is, thus, greater than, or equal to the stroke length (h1), for closing a second through channel (5), between the pressure chamber (6) and the oil overflow line (8).

Description

Ventil zum Steuern von Flüssigkeiten Valve for controlling liquids
Stand der TechnikState of the art
Die Erfindung betrifft ein Ventil zum Steuern von Flüssigkeiten gemäß der Gattung des Patentanspruchs 1. Aus der EP-0477401 AI ist ein Ventil bekannt, bei dem in einer Stufenbohrung des Ventilgehäuses ein Betätigungskolben eines Ventilglieds in einem Teil der Stufenbohrung mit kleinem 'Durchmesser verschiebbar angeordnet ist. Ein durch einen Piezoaktor bewegbarer größerer Kolben ist in einem Teil der Stufenbohrung mit größerem Durchmesser angeordnet. Zwischen den beiden Kolben ist ein mit einem Druckmedium gefüllter hydraulischer Druckraum ausgebildet, so daß eine hydraulische Übersetzung einer Bewegung des Piezoaktors erfolgt. Das heißt, wenn der große Kolben durch denThe invention relates to a valve for controlling liquids according to the preamble of claim 1. From EP-0477401 AI a valve is known in which an actuating piston of a valve member is slidably arranged in a part of the stepped bore with a small 'diameter in a stepped bore of the valve housing , A larger piston movable by a piezo actuator is arranged in part of the stepped bore with a larger diameter. A hydraulic pressure chamber filled with a pressure medium is formed between the two pistons, so that a hydraulic translation of a movement of the piezo actuator takes place. That is, when the big piston through the
Piezoaktor um eine bestimmte Wegstrecke bewegt wird, macht der Betätigungskolben des Ventilglieds einen um das Übersetzungsverhältnis des Kolbendurchmessers vergrößerten Hub, da der Kolben des Piezoaktors eine größere Fläche als der Betätigungskolben des Ventilglieds aufweist.Piezo actuator is moved by a certain distance, the actuating piston of the valve member makes a stroke increased by the transmission ratio of the piston diameter, since the piston of the piezo actuator has a larger area than the actuating piston of the valve member.
Bei derartigen Ventilen werden auch 3/2-Steuerventile eingesetzt, wie beispielsweise in der US 5,738,075 offenbart ist. Derartige 3/2-Steuerventile können als Sitz-Schieber oder Sitz-Sitz-Ventile ausgebildet sein. Hierbei wird beispielsweise der Druck aus einem Rail mittels eines steuerbaren Kolbens über einen Druckraum und einen Übersetzerkolben zu einem Steuerraum, aus welchem der Kraftstoff in den Verbrennungsraum eingespritzt wird, geführt. Hierbei ist im nichtbetätigten Zustand der Druckraum mit einer Leckölleitung verbunden, so daß imWith such valves, 3/2 control valves are also used, as is disclosed, for example, in US Pat. No. 5,738,075. Such 3/2 control valves can be designed as seat slide or seat-seat valves. Here, for example, the pressure from a rail is determined by means of a controllable piston via a pressure chamber and a booster piston to a control chamber from which the fuel is injected into the combustion chamber. Here, the pressure chamber is connected to a drain line in the non-actuated state, so that in
Druckraum Lecköldruck herrscht. Beim Umschalten des 3/2- Steuerventils tritt jedoch unabhängig von der Art des Ventils (Sitz-Schieber-Ventil oder Sitz-Sitz-Ventil) für eine kurze Zeit eine Verbindung zwischen dem Hockdruckbereich und dem Leckölbereich auf. Daraus resultiert ein sogenannter Absteuerstoß in die Leckölleitung. Hierdurch wird die Entlastung des Steuerraums des Ventils behindert, bis das Ventil die Öffnung zum Hochdruckbereich abgedichtet hat .Pressure chamber leakage oil pressure prevails. When the 3/2-way valve is switched over, a connection between the high pressure area and the leakage oil area occurs for a short time, regardless of the type of valve (seat slide valve or seat-seat valve). This results in a so-called exhaust surge in the drain line. This hinders the relief of the control chamber of the valve until the valve has sealed the opening to the high pressure area.
Vorteile der ErfindungAdvantages of the invention
Das erfindungsgemäße Ventil zum Steuern von Flüssigkeiten ' mit den kennzeichnenden Merkmalen des Patentanspruchs 1 hat den Vorteil, daß ein derartiger Absteuerstoß zur Leckölleitung nicht auftritt. Dies wird durch ein Vorschalten eines Schieberelements am Sitz des Steuerventils verhindert . Das Schieberelement wird dabei in Öffnungsrichtung unmittelbar vor dem Bereich des Kolbens angeordnet, mit dem der Kolben am Ventilsitz aufsitzt. Dies ermöglicht abhängig von dem Hubweg des Schieberelements eine verzögerte Öffnung des Durchlasses zwischen Zulaufleitung und Druckraum, aber ein sofortiges Schließen des Durchlasses zwischen Zulaufleitung und Druckraum. Somit kann zu jedem Zeitpunkt beim Umschalten des Steuerventils sichergestellt werden, daß keine Verbindung zwischen Zulaufleitung und Leckölleitung besteht. Der Hubweg des Kolbens zum Öffnen der Verbindung zwischen der Zulaufleitung und dem Druckraum ist durch Vorsehen des Schieberelements zumindest gleich, vorteilhaft jedoch größer als ein Hubweg zum Schließen bzw. Öffnen eines Durchlasses zwischen dem Druckraum des Steuerventils und der Leckölleitung. Dadurch kann vorteilhaft der Absteuerstoß in die Leckölleitung verhindert werden. Weiterhin vorteilhaft wird beim Umschalten des Steuerventils die Entlastung des Steuerraums nicht mehr behindert, da infolge des Schieberelements sofort eine Abdichtung zum Hochdruckbereich erfolgt.The valve according to the invention for controlling liquids' with the characterizing features of patent claim 1 has the advantage that such a surge pulse to the leakage oil line does not occur. This is prevented by connecting a slide element upstream of the seat of the control valve. The slide element is arranged in the opening direction immediately in front of the area of the piston with which the piston sits on the valve seat. Depending on the stroke of the slide element, this enables a delayed opening of the passage between the inlet line and the pressure chamber, but an immediate closing of the passage between the inlet line and the pressure chamber. It can thus be ensured at any time when the control valve is switched over that there is no connection between the supply line and the leakage oil line. The stroke of the piston for opening the connection between the inlet line and the pressure chamber is at least the same due to the provision of the slide element, but advantageously longer than a stroke for closing or opening a passage between the pressure chamber Control valve and the drain line. This can advantageously prevent the exhaust surge in the leak oil line. Furthermore, when the control valve is switched over, the relief of the control chamber is no longer impeded, since the slide element immediately seals off the high-pressure region.
In einer besonders vorteilhaften Weise ist das Schieberelement des Kolbens zylinderförmig ausgebildet. Hierdurch kann zum einen eine einfache Herstellung desIn a particularly advantageous manner, the slide element of the piston is cylindrical. In this way, on the one hand, simple manufacture of the
Schieberelements erreicht werden, andererseits wird dadurch insgesamt ein einfacher Aufbau des Steuerventils ermöglicht.Slide element can be achieved, on the other hand, this allows a simple structure of the control valve overall.
In vorteilhafter Weise ist der Kolben des Steuerventils zweiteilig ausgestaltet. Dadurch läßt sich ein Sitz- Schieber-Ventil mit einem dazwischen angeordneten Druckraum verwirklichen. Besonders vorteilhaft ist das Steuerventil dabei als kraftausgleichendes Ventil aufgebaut. Dabei ' entspricht der Führungsdurchmesser am Ventilsitz dem Durchmesser des Schieberelements.The piston of the control valve is advantageously configured in two parts. This allows a seat slide valve with a pressure space arranged between them to be realized. The control valve is particularly advantageously constructed as a force-balancing valve. The guide diameter at the valve seat corresponds to the diameter of the slide element.
Weiter vorteilhaft ist der Kolben des Steuerventils einstückig ausgebildet. Dadurch kann ein 3/2-Sitz-Schieber- Ventil als ein Auslaßventil eingesetzt werden.The piston of the control valve is also advantageously formed in one piece. This allows a 3/2-seat slide valve to be used as an exhaust valve.
Bevorzugt wird das Ventil zum Steuern von Flüssigkeiten als 3/2-Sitz-Schieber-Ventil oder als 3/2-Sitz-Sitz-Ventil ausgebildet werden.The valve for controlling liquids is preferably designed as a 3/2-seat slide valve or as a 3/2-seat seat valve.
Insgesamt kann somit mit dem erfindungsgemäßen Ventil eine eindeutige Funktion eines Steuerventils ohne Absteuerstoß aus dem Hochdruckzulaufbereich in die Leckölleitung erreicht werden. Durch Variation der Hublängen bzw. Hubwege des Schieberelements am Ventilsitz bzw. der Hublänge zum Schließen/Öffnen der Verbindung zur Leckölleitung kann die Überdeckung am Leckölschieberelement optimiert werden. Hierbei kann je nach Anwendungszweck ein aus den jeweiligen Hublängen optimales Schieberverhältnis gebildet werden. Hierbei sollte die Überdeckung so gewählt werden, daß keine nennenswerten Verzögerungen des Ventils auftreten, jedoch sichergestellt ist, daß kein Absteuerstoß in die Leckölleitung auftritt.Overall, the valve according to the invention can thus be used to achieve a clear function of a control valve from the high-pressure inlet area into the leakage oil line without an exhaust surge. By varying the stroke lengths or stroke paths of the slide element on the valve seat or the stroke length for closing / opening the connection to the leakage oil line, the overlap on the leakage oil slide element can be optimized. Depending on the application, an optimal slide ratio can be formed from the respective stroke lengths. The overlap should be selected so that there are no significant delays in the valve, but it is ensured that there is no discharge surge in the leak oil line.
Zeichnungdrawing
In der Zeichnung sind zwei Ausführungsbeispiele derIn the drawing, two embodiments of the
Erfindung dargestellt. Die Ausführungsbeispiele werden in der nachfolgenden Beschreibung näher erläutert. Es zeigt:Invention shown. The exemplary embodiments are explained in more detail in the description below. It shows:
Fig. 1 eine schematische Schnittansieht eines Kraftstoffeinspritzventils gemäß einem erstenFig. 1 is a schematic sectional view of a fuel injection valve according to a first
Ausführungsbeispiel der vorliegenden Erfindung; undEmbodiment of the present invention; and
Fig. 2 eine schematische Teilschnittansicht eines Kraftstoffeinspritzventils gemäß einem zweitenFig. 2 is a schematic partial sectional view of a fuel injection valve according to a second
Ausführungsbeispiel der vorliegenden Erfindung.Embodiment of the present invention.
Beschreibung der AusführungsbeispieleDescription of the embodiments
In dem in Fig. 1 dargestellten Ausführungsbeispiel findet das erfindungsgemäße Ventil Anwendung in einem druckübersetzten Common-Rail-Injector . Das erfindungsgemäße Ventil ist hierbei als ein 3/2-Sitz-Schieber-Steuerventil 1 ausgebildet.In the exemplary embodiment shown in FIG. 1, the valve according to the invention is used in a pressure-translated common rail injector. The valve according to the invention is designed as a 3/2-seat slide control valve 1.
In Fig. 1 ist ein Kraftstoffeinspritzventil gemäß einem ersten Ausführungsbeispiel der vorliegenden Erfindung dargestellt. Hierbei umfaßt das Kraftstoffeinspritzventil das 3/2 -Steuerventil 1. Das Steuerventil 1 besteht aus einem Stellelement 2 sowie einem ersten Kolben 3 und einem zweiten Kolben 4. Als Stellelement 2 kann beispielsweise ein bekannter Magnetsteller oder ein bekannter Piezosteller verwendet werden.1 shows a fuel injection valve according to a first exemplary embodiment of the present invention. Here, the fuel injection valve comprises the 3/2 control valve 1. The control valve 1 consists of an actuating element 2 and a first piston 3 and a second piston 4. As an actuating element 2, for example, a Known magnetic actuator or a known piezo actuator can be used.
Der erste Kolben 3 besteht aus mehreren Kolbenabschnitten 3a bis 3e. Ein erster Kolbenabschnitt 3a ist zylinderförmig ausgebildet und steht mit dem Stellelement 2 in Verbindung. Daran schließt sich ein zweiter Kolbenabschnitt 3b an, welcher konkav ausgebildet ist und bei entsprechender Stellung des Kolbens 3 einen ersten Durchlaß 10 am Ventilsitz freigibt. Anschließend an den zweitenThe first piston 3 consists of several piston sections 3a to 3e. A first piston section 3a is cylindrical and is connected to the actuating element 2. This is followed by a second piston section 3b, which is concave and with a corresponding position of the piston 3 opens a first passage 10 on the valve seat. Subsequent to the second
Kolbenabschnitt 3b folgt der als Schieberelement 3c ausgebildete dritte Kolbenabschnitt. Der dritte Kolbenabschnitt 3c ist direkt am Ventilsitz bzw. am ersten Durchlaß 10 angeordnet. Weiterhin umfaßt der Kolben 2 noch einen sich erweiternden vierten Kolbenabschnitt 3d sowie einen weiteren zylindrischen fünften Kolbenabschnitt 3e. Der fünfte Kolbenabschnitt 3e steht mit einem zwischen dem ersten Kolben 3 und dem zweiten Kolben 4 angeordneten Druckraum 6 in Verbindung .Piston section 3b is followed by the third piston section designed as slide element 3c. The third piston section 3 c is arranged directly on the valve seat or on the first passage 10. The piston 2 further comprises an expanding fourth piston section 3d and a further cylindrical fifth piston section 3e. The fifth piston section 3e is connected to a pressure chamber 6 arranged between the first piston 3 and the second piston 4.
Der zweite Kolben 4 besteht aus einem Schieberelement 4a sowie einem Grundkörper 4b. Bei nichtbetatigtem Steuerventil 1 wird der Kolben 4 durch eine Feder 9 in Offenstellung gehalten, so daß ein zweiter Durchlaß 5 zwischen dem Druckraum 6 und einer Leckölleitung 8 offen ist. Dadurch herrscht im nichtbetätigten Zustand im Druckraum 6 der Lecköldruck.The second piston 4 consists of a slide element 4a and a base body 4b. When the control valve 1 is not actuated, the piston 4 is held in the open position by a spring 9, so that a second passage 5 between the pressure chamber 6 and a leakage oil line 8 is open. As a result, the leakage oil pressure prevails in the pressure chamber 6 in the non-actuated state.
Bei dem in Fig. 1 dargestellten Steuerventil 1 ist ein Führungsdurchmesser d am ersten Kolben 3 gleich einemIn the control valve 1 shown in FIG. 1, a guide diameter d on the first piston 3 is equal to one
Schieberdurchmesser d2 am zweiten Kolben 4. Somit ist das Steuerventil 1 als ein kraftausgleichendes Ventil aufgebaut.Slider diameter d 2 on the second piston 4. Thus, the control valve 1 is constructed as a force-balancing valve.
Weiter steht der Druckraum 6 über eine Leitung 19 mit einem Übersetzerkolben 11 in Verbindung. Der mehrstufig ausgestaltete Übersetzerkolben 11 wird über eine Rückstellfeder 12 in seiner Ausgangsposition gehalten und steht mit seinem kleinerem Kolbendurchmesser mit einem Steuerraum 15 in Verbindung. Der Steuerraum 15 wird über ein Befüllungsventil 13 und eine Kraftstoffleitung 14 mit Kraftstoff befüllt. Der Kraftstoff wird über eine mittels einer Feder 17 vorgespannten Einspritzdüse 16 in einen nicht dargestellten Verbrennungsraum abgegeben.The pressure chamber 6 is also connected to a booster piston 11 via a line 19. The multi-stage translator piston 11 is via a Return spring 12 is held in its initial position and communicates with a control chamber 15 with its smaller piston diameter. The control chamber 15 is filled with fuel via a filling valve 13 and a fuel line 14. The fuel is emitted into an unshown combustion chamber via an injection nozzle 16 which is biased by a spring 17.
Nachfolgend wird die Wirkungsweise des Kraftstoffeinspritzventils beschrieben. Bei Betätigung desThe mode of operation of the fuel injection valve is described below. When pressing the
Stellelements 2 wird der Kolben 3 in Richtung des Druckraums 6 von seinem Ventilsitz fortbewegt. Beim Öffnen des Sitzes wird jedoch nicht sofort eine Verbindung zwischen der Zulaufleitung 7 aus dem Rail zum Druckraum 6 hergestellt, sondern es muß zuerst eine Schieberhöhe h2 desActuating element 2, the piston 3 is moved away from its valve seat in the direction of the pressure chamber 6. When the seat is opened, however, a connection is not immediately established between the feed line 7 from the rail to the pressure chamber 6, but first a slide height h 2 of
Schieberelements 3c überwunden werden, bevor diese Verbindung hergestellt ist. Infolge der Bewegung des Kolbens 3 in Richtung des Druckraums 6 wird der Kolben 4 entgegen ' der Federkraft der Feder 9 geschlossen. Dabei muß eine Hublänge hx am Schieberelement 4 überwunden werden. Da erfindungsgemäß die Hublänge h2 des Schieberelements 3c größer oder wenigstens gleich der Hublänge hx am Kolben 4 ist, ist somit sichergestellt, daß keine Verbindung zwischen der Zulaufleitung 7, in welcher Hochdruck herrscht, und der Leckölleitung 8 auftritt.Slider element 3c are overcome before this connection is made. As a result of the movement of the piston 3 in the direction of the pressure chamber 6, the piston 4 is closed against the spring force of the spring 9. A stroke length h x must be overcome on the slide element 4. Since, according to the invention, the stroke length h 2 of the slide element 3c is greater than or at least equal to the stroke length h x on the piston 4, it is thus ensured that there is no connection between the inlet line 7, in which high pressure prevails, and the leakage oil line 8.
Wenn der Kolben 3 die Hublänge h2 in Richtung des Druckraums 6 zurückgelegt hat, steht der Druckraum 6 mit der Hochdruckzulaufleitung 7 in Verbindung, so daß entgegen der Kraft der Rückstellfeder 12 ein hoher Druck amWhen the piston 3 has traveled the stroke length h 2 in the direction of the pressure chamber 6, the pressure chamber 6 is connected to the high-pressure feed line 7, so that a high pressure is applied to the force of the return spring 12
Übersetzerkolben 11 anliegt. Dieser hohe Druck wird infolge der unterschiedlichen Durchmesser des Übersetzerkolbens 11 auf den mit Kraftstoff gefüllten Steuerraum 15 übertragen. Dadurch wird über die an der Einspritzdüse 16 vorgesehene Druckschulter 18 die Kraft der Feder 17 überwunden und der Kraftstoff wird in den nicht dargestellten Brennraum eingespritzt .Translator piston 11 is present. This high pressure is transmitted to the control chamber 15 filled with fuel due to the different diameters of the booster piston 11. As a result, the force of the spring 17 is overcome via the pressure shoulder 18 provided on the injection nozzle 16 and the Fuel is injected into the combustion chamber, not shown.
Beim Rückstellen des Steuerventils 1 wird infolge der Hublänge des Schieberelements 3c die Verbindung zwischen der Zulaufleitung 7 und dem Druckraum 6 sofort unterbrochen, während der zweite Durchlaß 5 noch aufgrund des hohen Drucks im Druckraum 6 durch das Schieberelement 4a verschlossen ist. Erst wenn die Federkraft der Feder 9 größer als der Druck im Druckraum 6 wird, öffnet das Schieberelement 4a des Kolbens 4 den Durchlaß 5, so daß eine Verbindung zwischen dem Druckraum 6 und der Leckölleitung 8 freigegeben wird.When the control valve 1 is reset, the connection between the inlet line 7 and the pressure chamber 6 is immediately interrupted due to the stroke length of the slide element 3c, while the second passage 5 is still closed by the slide element 4a due to the high pressure in the pressure chamber 6. Only when the spring force of the spring 9 becomes greater than the pressure in the pressure chamber 6, does the slide element 4a of the piston 4 open the passage 5, so that a connection between the pressure chamber 6 and the leakage oil line 8 is released.
Somit ist immer eine eindeutige Funktion des Steuerventils 1 sowohl beim Öffnen als auch beim Schließen gewährleistet, ohne daß ein Absteuerstoß aus dem Druckraum 6 in die Leckölleitung 8 auftritt. Durch das Vorschalten des Schieberelements 3c in Öffnungsrichtung vor dem eigentlichen Öffnungsabschnitt 3d des Kolbens 3 können somit die im Stand der Technik vorhandenen Nachteile beseitigt werden.Thus, a clear function of the control valve 1 is always guaranteed, both when opening and when closing, without an exhaust surge occurring in the pressure chamber 6 into the leakage oil line 8. By connecting the slide element 3c in the opening direction in front of the actual opening section 3d of the piston 3, the disadvantages existing in the prior art can thus be eliminated.
Weiterhin kann durch das Schieberverhältnis h2/hx eine Überdeckung am Kolben 4 je nach Anwendung optimiert werden. In der Regel wird die Überdeckung (h2 - h ) verlängert werden (d.h. größer als 0 sein) , um sicherzustellen, daß kein Leckölstoß auftritt.Furthermore, an overlap on the piston 4 can be optimized depending on the application by the slide ratio h 2 / h x . Typically, the coverage (h 2 - h) will be extended (ie greater than 0) to ensure that no leakage oil surge occurs.
In Fig. 2 ist ein zweites Ausführungsbeispiel eines erfindungsgemäßen Ventils zum Steuern von Flüssigkeiten dargestellt. Dieses Steuerventil 1 kann ebenfalls bei einem Kraftstoffeinspritzventil eingesetzt werden. Da das2 shows a second exemplary embodiment of a valve according to the invention for controlling liquids. This control valve 1 can also be used in a fuel injection valve. Since that
Kraftstoffeinspritzventil des zweiten Ausführungsbeispiels im Vergleich mit dem ersten Ausführungsbeispiel nur Änderungen am Steuerventil 1 aufweist, ist auf eine Darstellung der weiteren Teile des Kraftstoffeinspritzventils in der Fig. 2 und in der nachfolgenden Beschreibung verzichtet worden, da diese genau wie im erste Ausführungsbeispiel ausgebildet sind. Weiterhin werden im zweiten Ausführungsbeispiel für gleichartige Teile gleiche Bezugszeichen wie im ersten Ausführungsbeispiel verwendet .Fuel injection valve of the second embodiment in comparison with the first embodiment has only changes to the control valve 1, the other parts of the fuel injection valve in FIG. 2 and in the following description have been omitted, since these are accurate are formed as in the first embodiment. Furthermore, the same reference numerals are used in the second exemplary embodiment for similar parts as in the first exemplary embodiment.
Das Steuerventil 1 des zweiten Ausführungsbeispiels weist im Gegensatz zum ersten Ausführungsbeispiel nur einen Kolben 3 auf. Der Kolben umfaßt mehrere Kolbenabschnitte 3a bis 3e. Der Kolben 3 weist ebenfalls einen ersten zylinderförmigen Kolbenabschnitt 3a und einen zweiten Kolbenabschnitt 3b auf, welcher konkav gebildet ist. An den zweiten Kolbenabschnitt 3b schließt sich ein Schieberelement 3c an, welches unmittelbar am Ventilsitz angeordnet ist. Weiter umfaßt der Kolben 3 einen vierten, sich verjüngenden Kolbenabschnitt 3d sowie einen fünften, zylinderförmigen Kolbenabschnitt 3e, welcher mit einem Stellelement 2 in Verbindung steht . Der Kolben 3 ist teilweise in einem Druckraum 6 angeordnet und öffnet/schließt die Verbindung zwischen einer Zulaufleitung ' 7 aus einem Rail und einem mit dem Druckraum 6 über eine Leitung 19 in Verbindung stehenden Übersetzerkolben (nicht dargestellt) . Weiterhin umfaßt das Steuerventil 1 auch eine Leckölleitung 8.In contrast to the first exemplary embodiment, the control valve 1 of the second exemplary embodiment has only one piston 3. The piston comprises a plurality of piston sections 3a to 3e. The piston 3 also has a first cylindrical piston section 3a and a second piston section 3b, which is concave. The second piston section 3b is adjoined by a slide element 3c, which is arranged directly on the valve seat. The piston 3 further comprises a fourth, tapering piston section 3d and a fifth, cylindrical piston section 3e, which is connected to an actuating element 2. The piston 3 is partly arranged in a pressure chamber 6 and opens / closes the connection between an inlet line 7 from a rail and a booster piston connected to the pressure chamber 6 via a line 19 (not shown). Furthermore, the control valve 1 also includes a leak oil line 8.
Die Wirkungsweise des Steuerventils 1 gemäß dem zweiten Ausführungsbeispiel ist wie folgt. Wenn das Stellelement betätigt wird, wird der Kolben 3 in Richtung des Stellelements 2 bewegt. Dadurch hebt der vierte, sich verjüngende Kolbenabschnitt 3d vom Kolbensitz an dem ersten Durchlaß 10 ab. Da jedoch im Anschluß an den zweiten Kolbenabschnitt 3b unmittelbar das Schieberelement 3c angeordnet ist, wird die Verbindung 10 zwischen der Hochdruckzulaufleitung 7 und dem Druckraum 6 erst geöffnet, wenn die dem zweiten Kolbenabschnitt 3b zugewandte Kante des Schieberelements 3c am Ventilsitz 10 vorbeigeführt worden ist. Da, wie in Fig. 2 dargestellt, die Hublänge h2 des Schieberelements 3c größer ist als die am zweiten Durchlaß 5 vorgesehene Hublänge h zwischen dem ersten Kolbenabschnitt 3a und dem zweiten Kolbenabschnitt 3b, wird sichergestellt, daß die Verbindung zwischen dem Druckraum 6 und derThe operation of the control valve 1 according to the second embodiment is as follows. When the actuating element is actuated, the piston 3 is moved in the direction of the actuating element 2. As a result, the fourth, tapering piston section 3d lifts off the piston seat at the first passage 10. However, since the slide element 3c is arranged directly after the second piston section 3b, the connection 10 between the high-pressure supply line 7 and the pressure chamber 6 is only opened when the edge of the slide element 3c facing the second piston section 3b has been guided past the valve seat 10. Since, as shown in Fig. 2, the stroke length h 2 of the slide element 3c is greater than the stroke length h provided at the second passage 5 between the first piston section 3a and the second piston section 3b, it is ensured that the connection between the pressure chamber 6 and the
Leckölleitung 8 geschlossen wird, bevor die Verbindung über den ersten Durchlaß 10 zwischen der Zulaufleitung 7 und dem Druckraum 6 geöffnet wird. Beim Schließen des Steuerventils 1 wird zuerst die Verbindung zwischen der Zulaufleitung 7 und dem Druckraum 6 geschlossen, bevor der Durchlaß 5 zwischen dem Druckraum 6 und der Leckölleitung 8 geöffnet wird.Leakage oil line 8 is closed before the connection via the first passage 10 between the inlet line 7 and the pressure chamber 6 is opened. When the control valve 1 is closed, the connection between the inlet line 7 and the pressure chamber 6 is first closed before the passage 5 between the pressure chamber 6 and the leakage oil line 8 is opened.
Somit wird auch beim zweiten erfindungsgemäßen Ausführungsbeispiel beim Umschalten des Steuerventils 1 ein Absteuerstoß in die Leckölleitung 8 in sicherer Weise verhindert. Weiterhin kann je nach Einsatzzweck die gewünschte Überdeckung (hx - h2) durch das Verhältnis der ' Hublänge h2 des Schieberelements 3c zur Hublänge ^ am zweiten Durchlaß 5 eingestellt werden.Thus, in the second exemplary embodiment according to the invention, when the control valve 1 is switched over, an exhaust surge in the leak oil line 8 is prevented in a safe manner. Furthermore, depending on the intended use, the desired coverage (h x -h 2 ) can be set by the ratio of the 'stroke length h 2 of the slide element 3c to the stroke length ^ at the second passage 5.
Die vorhergehende Beschreibung der Ausführungbeispiele gemäß der vorliegenden Erfindung dient nur zu illustrativen Zwecken und nicht zum Zwecke der Beschränkung der Erfindung. Im Rahmen der Erfindung sind verschiedene Änderungen undThe foregoing description of the exemplary embodiments according to the present invention is only for illustrative purposes and not for the purpose of limiting the invention. Various changes and modifications are within the scope of the invention
Modifikationen möglich, ohne den Umfang der Erfindung sowie ihre Äquivalente zu verlassen. Modifications are possible without leaving the scope of the invention and its equivalents.

Claims

Ansprüche Expectations
1. Ventil zum Steuern von Flüssigkeiten mit einer Zulaufleitung (7) und einer Leckölleitung (8) , welche jeweils mit einem Druckraum (6) in Verbindung stehen, und mit einem Kolbenelement (3, 4), welches durch ein1. Valve for controlling liquids with an inlet line (7) and a drain line (8), each of which is connected to a pressure chamber (6), and with a piston element (3, 4), which by a
Stellelement (2) verstellbar ist und einen ersten Durchlaß (10) zwischen der Zulaufleitung (7) und dem Druckraum (6) freigibt bzw. verschließt, dadurch gekennzeichnet, daß das Kolbenelement (3, 4) ein Schieberelement (3c) aufweist, welches unmittelbar amAdjusting element (2) is adjustable and opens or closes a first passage (10) between the inlet line (7) and the pressure chamber (6), characterized in that the piston element (3, 4) has a slide element (3c) which is directly connected at the
Sitz des Kolbenelements angeordnet ist, wobei das Schieberelement (3c) eine Hublänge (h2) zum Öffnen des ersten Durchlasses (10) aufweist, welche größer oder gleich einer Hublänge (h zum Schließen des zweiten Durchlasses ist.Seat of the piston element is arranged, the slide element (3c) having a stroke length (h 2 ) for opening the first passage (10), which is greater than or equal to a stroke length (h for closing the second passage).
2. Ventil zum Steuern von Flüssigkeiten nach Anspruch 1, dadurch gekennzeichnet, daß das Schieberelement (3c) zylinderförmig ausgebildet ist.2. Valve for controlling liquids according to claim 1, characterized in that the slide element (3c) is cylindrical.
3. Ventil zum Steuern von Flüssigkeiten nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß das Kolbenelement einen ersten Kolben (3) und einen zweiten Kolben (4) umfaßt. 3. Valve for controlling liquids according to claim 1 or 2, characterized in that the piston element comprises a first piston (3) and a second piston (4).
4. Ventil zum Steuern von Flüssigkeiten nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß das Kolbenelement (3) einstückig ausgebildet ist.4. Valve for controlling liquids according to claim 1 or 2, characterized in that the piston element (3) is integrally formed.
5. Ventil zum Steuern von Flüssigkeiten nach einem der5. Valve for controlling liquids according to one of the
Ansprüche 1 bis 4, dadurch gekennzeichnet, daß das Ventil als 3/2-Sitz-Schieber-Ventil ausgebildet ist.Claims 1 to 4, characterized in that the valve is designed as a 3/2-seat slide valve.
6. Ventil zum Steuern von Flüssigkeiten nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß das Ventil als 3/2-Sitz-Sitz-Ventil ausgebildet ist.6. Valve for controlling liquids according to one of claims 1 to 4, characterized in that the valve is designed as a 3/2-seat-seat valve.
7. Ventil zum Steuern von Flüssigkeiten nach einem der7. Valve for controlling liquids according to one of the
Ansprüche 1 bis 6, dadurch gekennzeichnet, daß das Ventil als kraftausgleichendes Ventil ausgebildet ist. Claims 1 to 6, characterized in that the valve is designed as a force-balancing valve.
EP01909462A 2000-01-22 2001-01-13 Valve for the control of fluids Expired - Lifetime EP1252429B1 (en)

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DE10002702A DE10002702A1 (en) 2000-01-22 2000-01-22 Valve for controlling liquids
PCT/DE2001/000122 WO2001053685A2 (en) 2000-01-22 2001-01-13 Valve for the control of fluids

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Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10002702A1 (en) * 2000-01-22 2001-08-02 Bosch Gmbh Robert Valve for controlling liquids
DE10141110A1 (en) * 2001-08-22 2003-03-20 Bosch Gmbh Robert Fuel injection device for internal combustion engines
JP4019934B2 (en) * 2002-12-26 2007-12-12 株式会社デンソー Control valve and fuel injection valve
DE10328245A1 (en) * 2003-06-24 2005-01-13 Robert Bosch Gmbh Fuel injection device for internal combustion engines
CN108506130B (en) * 2018-04-18 2024-06-11 莆田市博泰动力设备有限公司 Fuel injector capable of reducing dynamic leakage of high-pressure common rail fuel

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3477344A (en) * 1967-05-24 1969-11-11 United Aircraft Corp Fluid mechanical hysteretic device
DE3741526A1 (en) * 1987-12-08 1989-06-22 Bosch Gmbh Robert Seat valve
US5241935A (en) * 1988-02-03 1993-09-07 Servojet Electronic Systems, Ltd. Accumulator fuel injection system
ATE88971T1 (en) * 1990-09-26 1993-05-15 Knoblauch Georg Fa FLAT PACK CASSETTE FOR STORAGE OF LONG ITEMS.
DE4311627B4 (en) * 1993-04-08 2005-08-25 Robert Bosch Gmbh Fuel injection device for internal combustion engines
US5687693A (en) * 1994-07-29 1997-11-18 Caterpillar Inc. Hydraulically-actuated fuel injector with direct control needle valve
US5680988A (en) * 1995-01-20 1997-10-28 Caterpillar Inc. Axial force indentation or protrusion for a reciprocating piston/barrel assembly
DE19701879A1 (en) * 1997-01-21 1998-07-23 Bosch Gmbh Robert Fuel injection device for internal combustion engines
DE19716221B4 (en) * 1997-04-18 2007-06-21 Robert Bosch Gmbh Fuel injection device with pre-injection and main injection in internal combustion engines, in particular for hard to ignite fuels
DE19937713C1 (en) * 1999-08-10 2001-03-15 Siemens Ag Control valve arrangement for use in a fuel injector for internal combustion engines
DE10002702A1 (en) * 2000-01-22 2001-08-02 Bosch Gmbh Robert Valve for controlling liquids
DE10031278A1 (en) * 2000-06-27 2002-01-17 Bosch Gmbh Robert Fuel injection device for internal combustion engines

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO0153685A2 *

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DE50108611D1 (en) 2006-03-30
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WO2001053685A3 (en) 2001-12-06
CZ20022414A3 (en) 2004-03-17
HUP0301062A2 (en) 2003-08-28
JP2003520324A (en) 2003-07-02
US6736331B2 (en) 2004-05-18
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ES2255545T3 (en) 2006-07-01
ATE315174T1 (en) 2006-02-15

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