EP1383999A2 - Dispositif d'injection de carburant pour moteur a combustion - Google Patents

Dispositif d'injection de carburant pour moteur a combustion

Info

Publication number
EP1383999A2
EP1383999A2 EP02740251A EP02740251A EP1383999A2 EP 1383999 A2 EP1383999 A2 EP 1383999A2 EP 02740251 A EP02740251 A EP 02740251A EP 02740251 A EP02740251 A EP 02740251A EP 1383999 A2 EP1383999 A2 EP 1383999A2
Authority
EP
European Patent Office
Prior art keywords
section
piston
pump
accumulator
chamber
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP02740251A
Other languages
German (de)
English (en)
Other versions
EP1383999B1 (fr
Inventor
Gérard Duplat
Raphael Pourret
Peter Voigt
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 EP1383999A2 publication Critical patent/EP1383999A2/fr
Application granted granted Critical
Publication of EP1383999B1 publication Critical patent/EP1383999B1/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
    • 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
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F02M59/366—Valves being actuated electrically
    • 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
    • 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
    • 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
    • F02M57/023—Injectors structurally combined with fuel-injection pumps characterised by the pump drive mechanical
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/20—Closing valves mechanically, e.g. arrangements of springs or weights or permanent magnets; Damping of valve lift
    • F02M61/205—Means specially adapted for varying the spring tension or assisting the spring force to close the injection-valve, e.g. with damping of valve lift
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/30—Fuel-injection apparatus having mechanical parts, the movement of which is damped
    • F02M2200/304—Fuel-injection apparatus having mechanical parts, the movement of which is damped using hydraulic 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
    • F02M2200/40—Fuel-injection apparatus with fuel accumulators, e.g. a fuel injector having an integrated fuel accumulator
    • 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
    • F02M2200/505—Adjusting spring tension by sliding spring seats

Definitions

  • the invention is based on one
  • Fuel injection device for an internal combustion engine according to the preamble of claim 1.
  • Such a fuel injection device is known from DE 39 00 763 AI.
  • This fuel injection device has a high-pressure fuel pump and a fuel injection valve for a cylinder of the internal combustion engine.
  • the high-pressure fuel pump has a pump piston which is driven by the internal combustion engine and delimits a pump work space, a connection of the pump work space to a relief space being controlled by an electrically controlled valve.
  • the fuel injection valve has an injection valve member, through which at least one injection opening is controlled and which can be moved in an opening direction against the force of a closing spring by the pressure prevailing in a pressure chamber connected to the pump work chamber.
  • the closing spring is supported on the one hand at least indirectly on the injection valve member and on the other hand at least indirectly on a storage piston.
  • the storage piston On its side facing away from the closing spring, the storage piston is acted upon by the pressure in the pump work space and can be moved in a stroke movement against the force of the closing spring.
  • the accumulator piston can be moved into the accumulator chamber from an initial position at low pressure in the pressure chamber, the deflection stroke movement of the accumulator piston in the accumulator chamber being limited by a stop.
  • the storage piston has a shaft part which is guided in a connecting bore between the storage space and the pump working space and a larger cross section outside the connecting bore in the storage space than on the shaft part.
  • the fuel injection device with the features according to claim 1 has the advantage that by forming the storage piston with the shaft part, the shaft section arranged in the connecting position in the closed position of the storage piston with a smaller cross-section and the shaft section immersed in the connecting bore during the evasive stroke movement has a larger cross-section, at the beginning of the evasive stroke movement there is less damping and with increasing evasive stroke movement there is greater damping of the movement of the accumulator piston, so that it hits the stop only at a low speed and does not cause any disturbing or less noise.
  • the embodiment according to claim 2 enables a stronger damping, which is only effective after a partial escape stroke of the storage piston.
  • the embodiment according to claim 3 enables a further reduction in the speed at which the storage piston hits the stop, since the effective cross-sectional area on the storage piston, to which the pressure in the pump work chamber acts, is reduced when the shaft section with the larger cross section is immersed.
  • FIG. 2 shows a detail designated by II in FIG. 1 in an enlarged representation with a storage piston in a starting position
  • FIG. 3 shows the storage piston in a cross section along line III-III in FIG. 2
  • FIG. 4 shows detail II with the accumulator piston in an alternative position.
  • the internal combustion engine has one or more cylinders, each for
  • Fuel injection valve 12 is provided. The
  • Fuel injection valve 12 are a so-called
  • High-pressure fuel pump 10 has a pump body 14, in which a pump piston 18 is tightly guided in a cylinder 16, which is supported by a cam 20 of a camshaft Internal combustion engine is driven against the force of a return spring 19 in one stroke.
  • the pump piston 18 delimits a pump working chamber 22 in the cylinder 16, in which fuel is compressed under high pressure during the delivery stroke of the pump piston 18.
  • fuel is supplied to the pump working chamber 22 from a fuel reservoir 24, for example by means of a feed pump.
  • the pump working chamber 22 has a connection to a relief chamber, which can serve as the fuel reservoir 24, for example, and which is controlled by an electrically controlled valve 23.
  • the electrically controlled valve 23 is connected to a control device 25.
  • the fuel injection valve 12 has a valve body 26 which can be formed in several parts and which is connected to the pump body 14.
  • an injection valve member 28 is guided to be longitudinally displaceable in a bore 30.
  • the bore 30 runs at least approximately parallel to the cylinder 16 of the pump body 14, but can also run at an incline to the latter.
  • the valve body 26 has at least one, preferably a plurality of injection openings 32 at its end region facing the combustion chamber of the cylinder of the internal combustion engine.
  • the injection valve member 28 has at its end region facing the combustion chamber an, for example, approximately conical sealing surface 34 which interacts with a valve seat 36, for example also approximately conical in the valve body 26 in its end region facing the combustion chamber, from or after which the injection openings 32 lead away.
  • valve body 26 there is an annular space 38 between the injection valve member 28 and the bore 30 towards the valve seat 36, which in its end region facing away from the valve seat 36 by a radial expansion of the bore 30 in passes a pressure chamber 40 surrounding the injection valve member 28.
  • the injection valve member 28 has a pressure shoulder 42 facing the valve seat 36 at the level of the pressure chamber 40 due to a reduction in cross section.
  • a prestressed closing spring 44 engages, by means of which the injection valve member 28 is pressed toward the valve seat 36.
  • the closing spring 44 is arranged in a spring chamber 46 which adjoins the bore 30.
  • the pressure chamber 40 is connected to the pump working chamber 22 via a channel 48 running through the valve body 26 and the pump body 14.
  • the closing spring 44 is supported on the one hand at least indirectly, for example via a spring plate, on the injection valve member 28 and on the other hand at least indirectly, for example likewise via a spring plate 51, on a storage piston 50.
  • the storage piston 50 is arranged with its end region facing the closing spring 44 in the spring space 46 and projects through a bore 52 in a partition 53 between a storage space 54 and the spring space 46 into the storage space 54.
  • the bore 52 has a smaller diameter than the spring space 46 and the storage space 54.
  • the storage piston 50 has an area 55 in the storage space 54 with a larger diameter than the bore 52, so that a stroke movement of the storage piston 50 into the spring space 46 thereby delimits is that the area 55 of the accumulator piston 50 comes to rest against the partition 53 as a stop.
  • a connecting bore 56 leads from the end facing away from the spring space 46 to the pump working space 22 through a partition 57.
  • the connecting bore 56 has a smaller diameter than the region 55 of the storage piston 50.
  • the storage piston 50 faces the connecting bore 56 Area 55 then a sealing surface 58 which is, for example, approximately conical.
  • the sealing surface 58 cooperates with the mouth of the connecting bore 56 in the storage space 54 on the partition 57 as a seat, which can also be approximately conical.
  • the storage piston 50 has a shaft 60 which projects into the connecting bore 56 and whose diameter is smaller than that of the region 55. Following the sealing surface 58, the shaft 60 initially has a substantially smaller diameter than the connecting bore 56 and then towards its free end a shaft part 62 with a diameter that is only slightly smaller than the diameter of the connecting bore 56.
  • the shaft part 62 is divided into a shaft section 63 with a larger cross section arranged towards the free end and a shaft section 64 with a smaller cross section arranged towards the shaft 60.
  • the shaft section 63 which is larger in cross section, has, for example, an at least approximately circular cross section and is designed in the shape of a circular cylinder.
  • the shank section 64 with a smaller cross section can also have an at least approximately circular cross section but with a smaller diameter than the shank section 63 and is designed in the form of a circular cylinder.
  • the smaller cross section of the shaft section 64 is preferably formed by at least one flat 65 from the shaft section 63. Only one, two, three or more flats 65 can be provided distributed over the circumference of the shaft section 64.
  • the full diameter of the shaft section 63 is preferably present between the flats 65, so that the shaft section 64 is also guided in the connecting bore 56.
  • a circular cylindrical shaft has a constant diameter of the shaft section 63 and on which the flats 65 are formed to form the shaft section 64 with a smaller cross section.
  • the flats 65 end at the transition to the shaft section 63 on the jacket of the shaft section 63 in control edges 66.
  • the storage piston 50 is driven by the force the closing spring 44 is held in its initial position against the pressure prevailing in the pump working chamber 22 when the force exerted on the accumulator piston 50 by the pressure in the pump working chamber 22 is less than the force of the closing spring 44.
  • the accumulator piston 50 is shown in its initial position in FIG.
  • the larger diameter region 55 of the storage piston 50 is reduced by the pressure prevailing in the pump working chamber 22 due to the pressure losses during the throttling through the gap 68 acts so that a greater force acts on the accumulator piston 50 against the closing spring 44.
  • the shaft section 64 of the storage piston 50 with a larger cross section is arranged outside the connecting bore 56 at the beginning of the evasive movement of the storage piston 50.
  • a throttle point 49 can be provided in the connection of the pressure chamber 40 to the pump work chamber 22 via the channel 49.
  • the throttling point 49 can also be omitted, so that the pressure chamber 40 has an unthrottled connection to the pump working chamber 22.
  • the connection of the connecting bore 56, in which the shaft part 62 of the accumulator piston 50 is arranged, to the pump work chamber 22 is likewise carried out via the Throttle point 49. It can also be provided that the pressure chamber 40 has an unthrottled connection to the pump work chamber 22 and the connection bore 56 is connected to the pump work chamber 22 via the throttle point 49.
  • the function of the fuel injection device is explained below.
  • the pump working chamber 22 is filled with fuel during the suction stroke of the pump piston 18.
  • the control valve 23 is initially open, so that no high pressure can build up in the pump work chamber 22.
  • the control valve 23 is closed by the control device 25, so that the pump working space 22 is separated from the fuel reservoir 24 and builds up in this high pressure. If the pressure in the pump work chamber 22 and in the pressure chamber 40 is so high that the force acting on the injection valve member 28 via the pressure shoulder 42 in the opening direction 29 is greater than the force of the closing spring 44, the injection valve member 28 moves in the opening direction 29 and gives the at least one injection opening 32 free, through which fuel is injected into the combustion chamber of the cylinder.
  • the accumulator piston 50 is in its initial position. The pressure in the pump work chamber 22 subsequently increases further in accordance with the profile of the cam 20.
  • the accumulator piston 50 executes its evasive stroke movement and moves into the accumulator chamber 54. This results in a pressure drop caused in the pump work chamber 22 and also the bias of the closing spring 44th increases, which is supported on the storage piston 50.
  • the pressure drop in the pump work chamber 22 and in the pressure chamber 40 results in a lower force in the opening direction 29 on the injection valve member 28 and, due to the increase in the pretension of the closing spring 44, there is an increased force in the closing direction on the injection valve member 28, so that it moves again in the closing direction is, with its sealing surface 34 comes to rest on the valve seat 36 and closes the injection openings 32, so that the fuel injection is interrupted.
  • the fuel injection valve 12 is only open for a short period of time and only a small amount of fuel is injected into the combustion chamber as a pre-injection.
  • the amount of fuel injected is essentially determined by the opening pressure of the accumulator piston 50, that is the pressure in the pump working chamber 22 at which the accumulator piston 50 begins its evasive stroke movement.
  • the opening stroke of the injection valve member 28 during the pre-injection can be hydraulically limited by a damping device.
  • a damping unit is known from DE 39 00 762 AI and the corresponding US Pat. No. 5,125,580 and DE 39 00 763 AI and the corresponding US Pat. No. 5,125,581, the content of which hereby belongs to the content of the present patent application.
  • the pressure in the pump work chamber 22 subsequently increases further in accordance with the profile of the cam 20, so that the pressure force acting on the injection valve member 28 increases again in the opening direction 29 and increases the closing force due to the increased preload of the closing spring 44, so that the
  • Fuel injection valve 12 opens again. A larger amount of fuel is injected over a longer period of time than during the pre-injection. The time period and the amount of fuel injected during this main injection are determined by the time at which the control valve 23 is opened again by the control device 25. After opening the control valve 23, the pump work chamber 22 is again with the
  • Fuel reservoir 24 connected so that it is relieved and the fuel injection valve 12 closes.
  • the storage piston 50 is moved back into its starting position by the force of the closing spring 44.
  • the time offset between the pilot injection and the main injection is mainly determined by the evasive stroke of the accumulator piston 50.

Landscapes

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

Abstract

L'invention concerne un dispositif d'injection de carburant comprenant une pompe haute pression à carburant (10) et une soupape d'injection de carburant (12) destinées à un cylindre d'un moteur à combustion. La pompe haute pression à carburant (10) comprend une chambre de travail (22) et la soupape d'injection de carburant (12) comprend un obturateur (28) permettant de commander au moins une ouverture d'injection (32) et pouvant être déplacé dans une direction d'ouverture (29) à l'encontre de la force d'un ressort de fermeture (44), lequel s'appuie d'un côté sur l'obturateur (28) et de l'autre côté sur un piston d'accumulation (50) déplaçable qui est soumis, du côté opposé au ressort de fermeture (44), à la pression régnant dans la chambre de travail (22) de la pompe. Le piston d'accumulation (50) peut être déplacé dans une chambre d'accumulation (54) à l'encontre de la force du ressort de fermeture (44), la course alternative du piston d'accumulation (50) dans la chambre d'accumulation (54) étant limitée par une butée (53). Ledit piston d'accumulation (50) comporte une partie de tige (64) de section inférieure qui, en position de départ, se trouve dans un alésage de liaison (56), ainsi qu'une partie de tige (63) de section supérieure qui est disposée à l'extérieur de l'alésage de liaison (56) vers la chambre de travail (22) de la pompe, la partie de tige (63) de section supérieure du piston d'accumulation (50) plongeant dans l'alésage de liaison (56) lors d'un déplacement alternatif dudit piston d'accumulation (50) dans la chambre d'accumulation (54).
EP02740251A 2001-04-21 2002-04-12 Dispositif d'injection de carburant pour moteur a combustion Expired - Lifetime EP1383999B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10119603A DE10119603A1 (de) 2001-04-21 2001-04-21 Kraftsotffeinspritzeinrichtung für eine Brennkraftmaschine
DE10119603 2001-04-21
PCT/DE2002/001367 WO2002086305A2 (fr) 2001-04-21 2002-04-12 Dispositif d'injection de carburant pour moteur a combustion

Publications (2)

Publication Number Publication Date
EP1383999A2 true EP1383999A2 (fr) 2004-01-28
EP1383999B1 EP1383999B1 (fr) 2006-06-14

Family

ID=7682229

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02740251A Expired - Lifetime EP1383999B1 (fr) 2001-04-21 2002-04-12 Dispositif d'injection de carburant pour moteur a combustion

Country Status (7)

Country Link
US (1) US6889661B2 (fr)
EP (1) EP1383999B1 (fr)
JP (1) JP2004519588A (fr)
DE (2) DE10119603A1 (fr)
HU (1) HUP0301200A2 (fr)
PL (1) PL359100A1 (fr)
WO (1) WO2002086305A2 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7900604B2 (en) * 2005-06-16 2011-03-08 Siemens Diesel Systems Technology Dampening stop pin
US7850580B2 (en) * 2007-12-07 2010-12-14 Johnson Health Tech Co., Ltd. Resistance exercise apparatus

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3041018C2 (de) * 1980-10-31 1986-03-20 Daimler-Benz Ag, 7000 Stuttgart Kraftstoffeinspritzeinrichtung für eine luftverdichtende Einspritzbrennkraftmaschine
DE3521428A1 (de) * 1985-06-14 1986-12-18 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzvorrichtung fuer brennkraftmaschinen
DE3900762A1 (de) 1989-01-12 1990-07-19 Voest Alpine Automotive Kraftstoffeinspritzduese mit hohlem ausweichkolben
DE3900763C2 (de) * 1989-01-12 1994-05-19 Robert Bosch Ag Wien Kraftstoffeinspritzdüse, insbesondere Pumpedüse, für eine Brennkraftmaschine
WO1990008256A1 (fr) 1989-01-12 1990-07-26 Voest-Alpine Automotive Gesellschaft M.B.H. Injecteur de carburant
DE3907569A1 (de) * 1989-03-09 1990-09-13 Bosch Gmbh Robert Kraftstoff-einspritzduese fuer brennkraftmaschinen
DE4421714A1 (de) * 1994-06-21 1996-01-04 Bosch Gmbh Robert Kraftstoffeinspritzsystem
DE19940558C2 (de) * 1998-09-16 2003-11-20 Siemens Ag Vorrichtung zum Verzögern des Auslenkens der Düsennadel eines Kraftstoffeinspritzventils
DE10032924A1 (de) * 2000-07-06 2002-01-24 Bosch Gmbh Robert Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen
DE20110130U1 (de) * 2001-06-19 2002-10-24 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO02086305A2 *

Also Published As

Publication number Publication date
DE10119603A1 (de) 2002-10-24
US20040025840A1 (en) 2004-02-12
WO2002086305A2 (fr) 2002-10-31
WO2002086305A3 (fr) 2003-01-03
DE50207204D1 (de) 2006-07-27
US6889661B2 (en) 2005-05-10
PL359100A1 (en) 2004-08-23
JP2004519588A (ja) 2004-07-02
HUP0301200A2 (en) 2003-08-28
EP1383999B1 (fr) 2006-06-14

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