EP1203151A1 - Electrovanne bietagee destinee a un injecteur d'un moteur a combustion - Google Patents

Electrovanne bietagee destinee a un injecteur d'un moteur a combustion

Info

Publication number
EP1203151A1
EP1203151A1 EP00958208A EP00958208A EP1203151A1 EP 1203151 A1 EP1203151 A1 EP 1203151A1 EP 00958208 A EP00958208 A EP 00958208A EP 00958208 A EP00958208 A EP 00958208A EP 1203151 A1 EP1203151 A1 EP 1203151A1
Authority
EP
European Patent Office
Prior art keywords
valve
armature
spring
closing
injector
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
EP00958208A
Other languages
German (de)
English (en)
Other versions
EP1203151B1 (fr
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 EP1203151A1 publication Critical patent/EP1203151A1/fr
Application granted granted Critical
Publication of EP1203151B1 publication Critical patent/EP1203151B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0056—Throttling valves, e.g. having variable opening positions throttling the flow
    • 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
    • F02M45/08—Injectors 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
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0017—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means
    • F02M63/0021—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means characterised by the arrangement of mobile armatures
    • F02M63/0022—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means characterised by the arrangement of mobile armatures the armature and the valve being allowed to move relatively to each other
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0033—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat
    • F02M63/0036—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat with spherical or partly spherical shaped valve member ends
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0205—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively for cutting-out pumps or injectors in case of abnormal operation of the engine or the injection apparatus, e.g. over-speed, break-down of fuel pumps or injectors ; for cutting-out pumps for stopping the engine
    • F02M63/022—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively for cutting-out pumps or injectors in case of abnormal operation of the engine or the injection apparatus, e.g. over-speed, break-down of fuel pumps or injectors ; for cutting-out pumps for stopping the engine by acting on fuel control mechanism

Definitions

  • the invention relates to an injector for an injection system for internal combustion engines with a solenoid valve that controls the outflow of fuel through an outflow channel from a valve control chamber, wherein the solenoid valve has means for closing the outflow channel, one that can be actuated by an electro-magnet and with the means for Closing the drainage channel has an operative connection, a first valve spring and a second valve spring as well as a first stroke stop and a second stroke stop.
  • Two-stage solenoid valves for injectors of injection systems are known. With the first opening stage of the solenoid valve, the aim is to slowly open the nozzle needle of the injection nozzle, so that the precise measurement of small pre-injection quantities is facilitated. The second opening stage is used for the main injection. A high opening speed of the nozzle needle is desirable.
  • the armature of the solenoid valve is two in Series connected compression springs can be acted on against the opening direction of the solenoid valve. Until a first stroke stop is reached, only a first compression spring acts on the armature counter to the opening direction of the valve; after the armature has passed the first stroke stop, a second compression spring with the same direction of action also acts on the armature.
  • a disadvantage of this design is that the length of the solenoid valve is long due to the series connection. This is particularly problematic in the case of modern, compactly constructed engines and modern motor vehicles, since the available installation space is generally limited.
  • the series connection of two springs with the aid of an intermediate piece means that the natural frequencies of the solenoid valve are relatively low, which can have a disadvantageous effect on the operating behavior.
  • a two-stage valve of an injector actuated by a piezo actuator is known from DE OS 1974 1850.
  • this solenoid valve two valve springs are also connected in series, an intermediate ring being arranged between the two valve springs.
  • This valve also has the disadvantages mentioned above.
  • the invention has for its object to provide a two-stage solenoid valve for an injector, which is of compact construction and whose operating behavior is good at various frequencies.
  • an injector for an injection system for internal combustion engines with a solenoid valve which controls the outflow of fuel through an outflow channel from a valve control chamber, the solenoid valve means for closing the outflow channel, one of an electro-magnet Actuable and with the means for closing the drainage channel operatively connected armature, a first valve spring and a second valve spring and a first stroke stop, the first valve spring acting on the armature with a greater spring force in the closing direction, and from the closed position of the solenoid valve to When the first stroke stop is reached, the second valve spring acts on the armature in the opening direction with a smaller spring force.
  • first and second valve springs are compression or tension springs
  • a valve spring can be arranged on each side of the armature, so that the length of the valve springs does not additively to the overall length of the armature to the overall overall length of the solenoid valve. That is, at least one valve spring can be arranged in parallel, in particular concentrically with the armature, so that the overall length of the solenoid valve is reduced accordingly.
  • both valve springs can even be arranged in parallel, in particular concentrically with the armature, so that the overall length of the solenoid valve is further reduced.
  • Valve springs avoided their series connection, which has a favorable effect on the resonance behavior of the solenoid valve.
  • the first valve spring is between a housing of the injector and the end of the armature which is tensioned opposite the means for closing the drainage channel
  • the second valve spring is a pressure spring which is tensioned between the housing of the injector and the end of the armature which faces the means for closing the drainage channel, so that it is simple in construction and at the same time small space requirement of the solenoid valve is achieved.
  • the small space requirement is iu. a. attributable to the arrangement of the second valve spring between means for closing the drain channel and the armature.
  • the design of small pre-injection quantities is made possible in spite of the high opening speed of the nozzle needle during the main injection.
  • Another variant of the invention provides that the second valve spring acts on the armature via a displaceable intermediate ring, and that the path of the intermediate ring is limited by the first stroke stop, so that the first stroke stop can be easily and precisely fixed.
  • the path of the armature is limited by a second stroke stop, so that the opening of the solenoid valve in the main injection is fixed with great repeatability.
  • the means for closing the drain channel are operatively connected to the anchor via a push rod, so that there is a spatial separation between the means for closing the drain channel and the anchor. This also gives more space for the second valve spring.
  • the second valve spring and / or the intermediate ring is arranged concentrically with the push rod, so that the space requirement of the solenoid valve according to the invention decreases further.
  • the means for closing the drainage channel are a ball and a ball seat in the housing or a valve head arranged on the end of the pressure rod facing away from the armature and a correspondingly shaped valve seat in the housing, so that a reliable seal is provided in a simple manner of the drainage channel.
  • An embodiment of the invention provides that the injection system is a common rail injection system, so that the advantages according to the invention also benefit these injection systems.
  • FIG. 1 shows a schematic illustration of an injector according to the invention
  • Figure 2 shows an inventive two-stage solenoid valve
  • FIG. 1 timing diagrams for the solenoid valve.
  • an injector Via a high-pressure connection 1, fuel 3 is fed via an inlet duct 5 to an injection nozzle 7 and via an inlet throttle 9 into a valve control chamber 11.
  • the valve control chamber 11 is connected to a fuel return 17 via a drain channel 12 and an outlet throttle 13, which can be opened by a solenoid valve 15. Leakages of the solenoid valve 15 are discharged through the leakage drain 18.
  • the fuel 3 is shown in FIG. 1 as a black area.
  • the valve control chamber 11 is delimited by a valve piston 19.
  • a nozzle needle 21 connects to the valve piston 19 and prevents the pressurized fuel 3 from flowing between the injections into the combustion chamber (not shown).
  • the nozzle needle 21 has a cross-sectional change 23 from a larger diameter 25 to a smaller diameter 27. With its larger diameter 25, the nozzle needle 21 is guided in a housing 29.
  • the cross-sectional change 23 delimits a pressure space 31 of the injection nozzle 7
  • a nozzle spring 39 acting on a shoulder 37 of the nozzle needle 21 closes the injection nozzle 7 or the injector.
  • control and leakage quantities can be up to 50 mm 3 / stroke. They are returned to the fuel tank (not shown) via the fuel return 17.
  • FIG. 2 shows a solenoid valve 15 according to the invention.
  • the outlet throttle 13 is closed by a ball 41 of the solenoid valve 15. This is done indirectly via an armature 43, a pressure rod 44 connected to it and a first valve spring 45 by pressing the ball 41 into a ball seat 47 of the housing 29.
  • a second valve spring 57 is arranged between ball seat 47 and armature 43 and exerts a force counteracting first valve spring 45 on armature 43 via an intermediate ring 59.
  • the intermediate ring 59 can be displaced in the direction of the longitudinal axis of the armature 43 up to a first stroke stop 61.
  • FIG. 2 shows an embodiment in which the intermediate ring 59 is centered by the first stroke stop 61 by means of a recess 63.
  • the power with which Ball 41 is pressed into ball seat 47 in the illustrated operating state of solenoid valve 15 is the difference between the forces of first valve spring 45 and second valve spring 57.
  • an electromagnet 49 of the solenoid valve 15 is activated with a starting current I v .
  • the force of the electromagnet 49 acting on the armature 43 is dimensioned such that it exceeds the difference between the forces of the first valve spring 45 and the second valve spring 57 acting on the armature 43.
  • the armature 43 moves in the direction of the electromagnet 49 until the intermediate ring 59 rests on the first stroke stop 61.
  • the entire spring force of the first valve spring 45 acts counter to the force exerted on the armature 43 by the electromagnet 15.
  • the spring force of the first valve spring 45 is greater than the force of the electromagnet 15 when a current of the amount I v flows through it. Therefore, the armature 43 opens during the pre-injection only until the intermediate ring 59 rests on the first stroke stop 61; this stroke corresponds to the distance labeled 65 in FIG. 2.
  • other stroke stops are also conceivable.
  • the rebound of the second valve spring 57 can also be caused by one with the second
  • Valve spring connected tie rod or the like. be restricted.
  • the term of the first stroke stop is understood in connection with the present invention so that after. When the armature 43 reaches a certain stroke, the second valve spring 57 no longer acts on the armature 43.
  • fuel 3 can flow via the drain channel 12 and the outlet throttle 13 arranged therein from the valve control chamber 11 into an overlying cavity 51 and via the fuel return 17 to the not shown Drain the fuel tank so that the pressure in the valve control chamber 11 drops.
  • the inlet throttle 9 prevents complete pressure equalization between the inlet channel 5 shown in FIG. 1 and the valve control chamber 11. As soon as the pressure in the
  • Valve control chamber 11 hydraulic force acting on the end face 33 of the valve piston 19 is smaller than the hydraulic force acting on the cross-sectional change 23 shown in FIG. 1 and acting on the injection pressure, opens the nozzle needle 21 and the injection begins.
  • the opening speed of the nozzle needle 21 shown in FIG. 1 is determined by the flow difference between the inlet throttle 9 and outlet throttle 13.
  • Flow restrictor 13 and ball seat 47 and ball 41 are flow resistors connected in series. In the pre-injection, the flow resistance of the ball seat 47 and ball 41 is large because of the small stroke 65 of the armature 43. Therefore the opening speed is the
  • Nozzle needle 21 is relatively low in the pre-injection. This facilitates the design of small pre-injection quantities.
  • the main injection is triggered by the solenoid 49 of the solenoid valve 15 with the so-called
  • Opening the solenoid valve 15 has the following effects
  • the solenoid valve If the solenoid valve is already partially or even fully open, the distance between armature 43 and solenoid 49 is small. Because of the now smaller air gap between the armature 43 and the electromagnet 49, the force of the electromagnet 49 acting on the armature 43 is relatively large with the same current flow through the electromagnet 49. In this case, the solenoid 49 can also overcome the force of the first valve spring 45. In addition, the inertia forces of the armature 43 have already decreased at this stage of the opening of the solenoid valve 15.
  • the increased starting current I A is reduced to a lower holding current I H. This is possible because the air gap of the magnetic circuit is now is less.
  • the armature 43 is pressed in the direction of the ball 41 by the force of the first valve spring 45 and the ball 41 closes the flow restrictor 13.
  • the second valve spring 57 brakes as soon as the stroke falls below the 65 Anchor 43 and prevents excessive wear of the ball seat 47 and the ball 41.
  • the closing speed of the nozzle needle 21 is determined by the flow through the inlet throttle 9. The injection ends when the nozzle needle 21 rests on the nozzle needle seat 35.
  • FIG. 3 the time course of the actuation of the solenoid valve and the injector is shown qualitatively.
  • Figure 3a the armature stroke 69 of the solenoid valve is shown over time 71.
  • the armature stroke in the pre-injection is designated with "v” and the armature stroke in the main injection with "h". It can be seen from the comparison of the gradients that the opening speed of the solenoid valve in the main injection is greater than in the pre-injection. This can be achieved, for example, by a larger armature current compared to the pre-injection.
  • FIG. 3b shows the stroke of the injection nozzle 73 over time 71.
  • the vertical dashed lines attempted to represent the time delay between opening the actuation of the solenoid valve and opening or closing the injector.

Landscapes

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

Abstract

L'invention concerne une électrovanne biétagée (15) destinée à des injecteurs de systèmes d'injection de moteurs à combustion. Cette électrovanne est de construction simple et compacte étant donné qu'elle s'affranchit du montage en série d'un premier (45) et d'un deuxième (57) ressort de soupape.
EP00958208A 1999-08-09 2000-08-02 Electrovanne bietagee destinee a un injecteur d'un moteur a combustion Expired - Lifetime EP1203151B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19937559A DE19937559A1 (de) 1999-08-09 1999-08-09 Zweistufiges Magnetventil in kompakter Bauweise für einen Injektor eines Einspritzsystems für Brennkraftmaschinen
DE19937559 1999-08-09
PCT/DE2000/002578 WO2001011221A1 (fr) 1999-08-09 2000-08-02 Electrovanne bietagee destinee a un injecteur d'un moteur a combustion

Publications (2)

Publication Number Publication Date
EP1203151A1 true EP1203151A1 (fr) 2002-05-08
EP1203151B1 EP1203151B1 (fr) 2008-02-13

Family

ID=7917741

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00958208A Expired - Lifetime EP1203151B1 (fr) 1999-08-09 2000-08-02 Electrovanne bietagee destinee a un injecteur d'un moteur a combustion

Country Status (8)

Country Link
US (1) US6783086B1 (fr)
EP (1) EP1203151B1 (fr)
JP (1) JP2003524725A (fr)
AT (1) ATE386205T1 (fr)
CZ (1) CZ20011227A3 (fr)
DE (2) DE19937559A1 (fr)
HU (1) HUP0104906A3 (fr)
WO (1) WO2001011221A1 (fr)

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DE10131125A1 (de) * 2001-06-28 2002-09-12 Bosch Gmbh Robert Magnetventil mit gedämpftem, einteiligem Ankerelement
DE10161002A1 (de) * 2001-12-12 2003-07-03 Bosch Gmbh Robert Magnetventil zur Steuerung eines Einspritzventils einer Brennkraftmaschine
DE10230267A1 (de) * 2002-07-05 2004-01-22 Robert Bosch Gmbh Verfahren zur Ansteuerung einer Fluid-Dosiervorrichtung und Common-Rail-Injektor
DE502004007701D1 (de) * 2004-01-21 2008-09-04 Dualon Internat Holding S A Ventil für flüssigkeitseinspritzung
US7156368B2 (en) * 2004-04-14 2007-01-02 Cummins Inc. Solenoid actuated flow controller valve
AT500889B8 (de) * 2004-08-06 2007-02-15 Bosch Gmbh Robert Vorrichtung zum einspritzen von kraftstoff in den brennraum einer brennkraftmaschine
DE102005061409A1 (de) * 2005-12-22 2007-06-28 Robert Bosch Gmbh Elektromagnetisch betätigbares Ventil
JP4576345B2 (ja) * 2006-02-17 2010-11-04 日立オートモティブシステムズ株式会社 電磁式燃料噴射弁
KR101290899B1 (ko) * 2007-11-12 2013-07-29 현대자동차주식회사 자동차용 2단제어 분사노즐장치
DE102007056913A1 (de) * 2007-11-26 2009-05-28 Robert Bosch Gmbh Einspritzdüse für Kraftstoff mit Kugelventil
DE102008002019A1 (de) 2008-05-28 2009-12-03 Robert Bosch Gmbh Verfahren und Vorrichtung zur Ansteuerung eines Magnetventils
DE102009046822A1 (de) * 2009-11-18 2011-05-19 Robert Bosch Gmbh Schaltventil mit einem in einem Gehäuse bewegbaren Ventilelement
EP2333297B1 (fr) * 2009-12-11 2013-03-20 Continental Automotive GmbH Ensemble de soupape pour soupape d'injection et soupape d'injection
JP2012202251A (ja) * 2011-03-24 2012-10-22 Denso Corp インジェクタ
JP7208884B2 (ja) * 2019-11-26 2023-01-19 株式会社Soken 燃料噴射装置
DE102020212697B4 (de) 2020-10-08 2022-08-25 Ford Global Technologies, Llc Injektor, Dieselmotor und Kraftfahrzeug
JP2023018372A (ja) * 2021-07-27 2023-02-08 三菱重工エンジン＆ターボチャージャ株式会社 燃料噴射弁及び燃料噴射弁の駆動方法
CN114151248B (zh) * 2021-11-19 2023-10-13 哈尔滨工程大学 液氨直冷-柴油双燃料一体化混合动力系统

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Also Published As

Publication number Publication date
DE50014969D1 (de) 2008-03-27
US6783086B1 (en) 2004-08-31
CZ20011227A3 (cs) 2002-02-13
HUP0104906A2 (hu) 2002-04-29
JP2003524725A (ja) 2003-08-19
ATE386205T1 (de) 2008-03-15
DE19937559A1 (de) 2001-03-01
HUP0104906A3 (en) 2002-05-28
EP1203151B1 (fr) 2008-02-13
WO2001011221A1 (fr) 2001-02-15

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