WO2004057180A1 - Soupape d'injection de carburant pour moteurs a combustion interne - Google Patents

Soupape d'injection de carburant pour moteurs a combustion interne Download PDF

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Publication number
WO2004057180A1
WO2004057180A1 PCT/DE2003/001734 DE0301734W WO2004057180A1 WO 2004057180 A1 WO2004057180 A1 WO 2004057180A1 DE 0301734 W DE0301734 W DE 0301734W WO 2004057180 A1 WO2004057180 A1 WO 2004057180A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
needle
valve seat
pressure
fuel injection
Prior art date
Application number
PCT/DE2003/001734
Other languages
German (de)
English (en)
Inventor
Thomas KÜGLER
Jochen Mertens
Hasiman ÜSKÜDAR
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
Priority to EP03813515A priority Critical patent/EP1576283A1/fr
Publication of WO2004057180A1 publication Critical patent/WO2004057180A1/fr

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
    • 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
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F02M61/1873—Valve seats or member ends having circumferential grooves or ridges, e.g. toroidal
    • 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
    • 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
    • F02M45/086—Having more than one injection-valve controlling discharge orifices
    • 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
    • F02M2200/28—Details of throttles in fuel-injection apparatus
    • 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
    • F02M2200/46—Valves, e.g. injectors, with concentric valve bodies

Definitions

  • the invention is based on a fuel injection valve for internal combustion engines, as is known, for example, from Offenlegungsschrift DE (normal valve) AI.
  • a fuel injection valve comprises a valve body, in which a piston-shaped valve needle is arranged to be longitudinally displaceable in a bore.
  • a pressure chamber is formed between the valve needle and the wall of the bore, which can be filled with fuel under high pressure.
  • the bore is delimited at its combustion chamber end by a valve seat, from which several injection openings extend.
  • valve needle The movement of the valve needle between the opening and closing position takes place here by two opposing forces: on the one hand by a closing force that acts on the valve needle in the direction of the valve seat, and on the other hand by an opening force that is generated hydraulically.
  • the valve needle has at least one pressure surface, which is preferably formed by a shoulder encircling the valve needle and is acted upon by the fuel in the pressure chamber.
  • the valve needle either moves into contact with the valve seat or lifts off from it. In modern internal combustion engines, it is very important that the actual injection timing exactly coincides with the timing predetermined by the control.
  • the fuel injection valve according to the invention with the characterizing features of claim 1 has the advantage that fluctuations in the injection timing are reduced, which are caused by pressure fluctuations in the pressure chamber.
  • a pressure surface is formed on the valve needle, which can be connected to the pressure chamber via a throttle point when the valve needle rests on the valve seat. Occurring pressure fluctuations are damped, so that the fuel pressure that acts effectively on the pressure surface has significantly lower pressure fluctuations than the pressure in the pressure chamber.
  • the point in time at which the valve needle lifts off the valve seat due to the hydraulic pressure on the pressure surface can thus be determined precisely, so that the injection begins at the optimum point in time.
  • the throttle point is opened when the valve needle is lifted off the valve seat.
  • the printing area is now acted upon by the full fuel pressure of the pressure chamber, so that the valve needle can be opened quickly.
  • the throttle point is formed by an annular gap between the valve seat and the valve needle.
  • the throttling point is opened quickly when the valve needle is lifted off the valve seat, and the strength of the throttling can be easily adjusted through the width of the annular gap.
  • the throttling effect depends not only on the design of the throttling point, but also on the volume of the space which is connected to the pressure chamber by the throttling point and which limits the pressure area of the valve needle.
  • the damping effect at the throttle point can be influenced via the depth and design of the annular groove.
  • the annular groove can also be formed so deep that a circumferential lip is formed on its outer edge, between which and the valve seat the throttle point is formed.
  • the pressure surface is formed as part of the valve sealing surface.
  • an annular groove is formed in the valve seat, between its radially outer edge and the pressure surface on the valve sealing surface the throttle gap is formed.
  • the valve needle can remain unchanged here compared to the valve needles otherwise used.
  • the valve needle is arranged in a hollow needle, which also interacts with the valve seat and, when in contact with the valve seat, interrupts the connection of the valve needle to the pressure chamber.
  • a hollow needle is used to control at least one further injection channel that extends from the valve seat.
  • an additional, second pressure surface is arranged on the valve needle, which is surrounded by a hollow needle, and is designed to face away from the valve seat to the pressure surface.
  • This second pressure surface is connected to the pressure chamber via an annular gap which is formed between the valve needle and the hollow needle and which forms a second throttle point.
  • the additional pressure area on the valve needle allows the hydraulic opening force to be divided between the pressure area and the second pressure area, which opens up a greater scope for design.
  • FIG. 1 shows a longitudinal section through an inventive
  • Fuel injection valve, Figure 2 is an enlarged view of the section designated by II of Figure 1, Figure 3 the same section as Figure 2 of another
  • FIG. 4 shows a longitudinal section through a further fuel injection valve according to the invention
  • FIG. 5 shows an enlarged view of the section of FIG. 4 designated by V
  • FIG. 6 shows an enlarged view of the section of FIG. 5 labeled VI. Description of the embodiment
  • a valve body 1 has a bore 2 which is delimited at its combustion chamber end by a conical valve seat 11. At least one, but usually a plurality of injection channels 14 emanate from the valve seat 11, which open into the combustion chamber of the internal combustion engine when the fuel injection valve is in the installed position.
  • a piston-shaped valve needle 7 is arranged to be longitudinally displaceable and is sealingly guided in a guide section 102 of the bore 2.
  • the valve needle 7 tapers towards the valve seat 11 to form a pressure shoulder 9 to a tapered section and merges at its end facing the valve seat 11 into a valve sealing surface 12 which is essentially conical.
  • a pressure chamber 5 is formed between the guide section 102 and the valve seat 11, which can be filled with fuel under high pressure via an inlet channel, not shown in the drawing and running in the valve body 1.
  • valve needle 7 interacts with the valve seat 11 in such a way that a valve is formed by which the pressure chamber 5 is connected to or separated from the injection channels 14.
  • the movement of the valve needle 7 takes place through the equilibrium of two forces: on the one hand, a closing force F acts on the end of the valve needle 7 facing away from the valve seat 11, which is directed in the direction of the valve seat 11 and presses the valve needle 7 against it. Due to the closing force, the valve needle 7 remains in its closed position in the absence of additional forces, thus closing the injection channels 14.
  • the closing force is directed against an opening force which is caused by the hydraulic force in the pressure chamber 5 fuel is generated on the valve needle 7.
  • the ratio of the two forces can be achieved either via the fuel pressure in the pressure chamber 5 and / or via a change in the closing force. Depending on which force prevails, the valve needle 7 slides into its closed or open position.
  • FIG. 2 shows an enlargement of the section from FIG. 1, designated II.
  • annular groove 20 is formed which surrounds the valve needle 7 over its entire circumference.
  • the annular groove 20 is delimited on the one hand by the first ring edge 22 and on the other hand by the second ring edge 24.
  • a throttle point 26 is formed, via which the annular space, which is delimited by the annular groove 20 and the valve seat 11 , is connected to the pressure chamber 5.
  • the annular groove 20 forms a pressure surface 30 which, in addition to the pressure shoulder 9, causes an opening force on the valve needle 7 when the pressure is applied accordingly.
  • the pressure surface 30 can have a larger or smaller hydraulically effective surface than the pressure shoulder 9. In any case, the closing force is dimensioned such that the pressure application of both the pressure shoulder 9 and the pressure surface 30 is necessary to move the valve needle 7 against the closing force is. If the valve needle 7 lifts off the valve seat 11, the throttle point 11 is opened and the fuel can flow from the pressure chamber 5 past the pressure surface 30 unhindered to the injection channels 14.
  • the functioning of the throttle point 26 is as follows: During the injection, fuel flows through the pressure chamber 5 in the direction of the injection channels between the valve sealing surface 12 and the valve seat 11 and becomes finally injected into the combustion chamber through the injection channels 14. By closing the fuel injection valve when the injection has ended, that is to say by placing the valve needle 7 on the valve seat 11, the fuel in motion in the pressure chamber 5 is braked abruptly. The kinetic energy of the fuel is converted into compression work, so that pressure oscillations form in the pressure chamber 5. By the beginning of the next injection, these pressure fluctuations may not have subsided, so that the pressure on the pressure surface 30 oscillates and there is no defined opening force on the valve needle 7.
  • the opening time of the valve needle 7 also fluctuates, and thus the start of the injection, since this is reached when the opening force exceeds the closing force.
  • the throttling point 26, transfers the pressure vibrations in the pressure chamber 5 only in a damped manner into the annular groove 20, so that a relatively constant pressure with only damped pressure vibrations prevails on the pressure surface 30.
  • This enables a precisely defined opening force on the valve needle 7, which thereby opens exactly at the calculated point in time, which is essential in particular in modern, high-speed internal combustion engines in order to enable low-noise and pollutant-free combustion.
  • the extent of the damping can be adjusted via the size of the throttle point 26 or the depth of the annular groove 20.
  • FIG. 3 shows a further exemplary embodiment of the fuel injection valve according to the invention.
  • the pressure surface 30 is here formed as part of the valve sealing surface 12, the pressure surface 30 extending between the first ring edge 22, which is formed at the transition of the valve sealing surface 12 to the tapered section of the valve needle 7, and the line shown in broken lines in the drawing.
  • the dashed line here indicates the edge on the combustion chamber side a seat ring groove 28, which is formed in the valve seat 11.
  • the throttle point 26 is formed, which functions in the same way as the throttle point 26 of the exemplary embodiment shown in FIG. As soon as the valve needle 7 lifts off the valve seat 11, the throttle point 26 is opened and the fuel can flow unhindered between the valve sealing surface 12 and the valve seat 11 through the injection channels 14.
  • FIG. 4 shows a longitudinal section through a further fuel injection valve according to the invention.
  • the structure of the valve body 1 and the bore 2 is essentially identical to the fuel injector shown in FIG. 1.
  • a further valve needle in the form of a hollow needle 8 is formed in the bore 2, in which the valve needle 7 is guided in the hollow needle 8 in a first guide region 35 on the combustion chamber side and in a second guide region 36 facing away from the combustion chamber.
  • An undercut is provided on the valve needle 7 between these guide regions 35, 36, so that the valve needle 7 is not guided in the hollow needle 8 here.
  • Both the valve needle 7 and the hollow needle 8 are at least temporarily acted upon by a closing force in the direction of the valve seat 11, the closing forces being applied to the end of the hollow needle 8 and the valve needle 7 facing away from the valve seat 11, for example by spring force or hydraulic forces.
  • two rows of injection channels are formed, each of which consist of a plurality of injection channels 14 and are arranged distributed over the circumference of the valve body 1. They form a first row of injection channels 114 and a second row of injection channels 214, the first row of injection channels 114 being arranged upstream of the second row of injection channels 214.
  • the hollow needle 8 cooperates with its outer valve sealing surface 16 with the valve seat 11, so that a valve is formed which controls the connection between the first injection channel row 114 and the pressure chamber 5 formed between the hollow needle 8 and the wall of the bore 2.
  • a valve is formed by the valve sealing surface 12 of the valve needle 7 and the valve seat 11, which opens and closes the connection between the pressure chamber 5 and the second row of injection channels 214, this second valve only becoming effective when the hollow needle 8 is connected to the pressure chamber 5 has already opened.
  • FIG. 5 the section of FIG. 4 labeled V is shown enlarged again.
  • the outer valve sealing surface 16 of the hollow needle 8 has two conical surfaces, at the transition of which a sealing edge 18 is formed, so that when the hollow needle rests on the valve seat 11, a high surface pressure occurs in this area and thus a secure seal is ensured at this point, even if there is a very high pressure in the pressure chamber 5.
  • a part of the outer valve sealing surface 16 of the hollow needle 8 is acted upon by the fuel pressure of the pressure chamber 5, so that this results in an opening force on the hollow needle 8 which is opposite to the closing force.
  • the valve needle 7 has an annular groove 20, as is also present in the injection valve shown in FIG. 2.
  • the pressure surface 30 is formed in the annular groove 20, the pressurization of which causes an opening force on the valve needle 7.
  • a second pressure surface 32 is formed on the valve needle 7 as a further, hydraulically active surface, which is formed by a shoulder in the valve needle 7 which directly adjoins the first guide section 35 of the valve needle 7.
  • the second printing surface 32 is by a Annular gap, which is formed between the valve needle 7 and the hollow needle 8, can be connected to the pressure chamber 5, this annular gap forming a second throttle point 34.
  • Both the pressure surface 30 and the second pressure surface 32 can thus be connected to the pressure chamber 5 via throttling points 26, 32.
  • the fuel flow to the second injection channel row 214 is opened in the manner already described above.
  • FIG. 6, is an enlargement of the section designated VI in FIG.
  • the fuel injection valve shown in FIGS. 4, 5 and 6 operates as follows: An increased fuel pressure in the pressure chamber 5 and / or a reduction in the closing force on the hollow needle 8 results in a hydraulic opening force on the pressure shoulder 9 and on the part the outer valve sealing surface 16, which is acted upon by the fuel of the pressure chamber 5. The hollow needle 8 then lifts off the valve seat 11 and fuel flows from the pressure chamber 5 to the outer row of injection channels 114, through which the fuel is injected into the combustion chamber of the internal combustion engine.
  • valve needle 7 By lifting the hollow needle 8 from the valve seat 11, the valve needle 7 is now acted upon by the fuel pressure of the pressure chamber 5, and in particular the pressure surface 30 and the second pressure surface 32 , are reduced by the throttling points 26, 32 so that a defined opening force is exerted on the valve needle 7. If the hydraulic opening forces on the valve needle 7 exceed the closing force, the valve needle 7 also lifts off the valve seat 11 and the second row of injection channels 214 is released. When the fuel injection valve closes at the end of the injection, the pressure in the pressure chamber 5 is reduced or the closing force on the valve needle 7 and Hollow needle 8 increased. As a result, they slide back into their closed position and the injection is ended.

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  • 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 une soupape d'injection de carburant présentant un corps de soupape (1), dans lequel est formé un alésage (2) délimité au niveau d'une extrémité par un siège de soupape duquel s'étend au moins un canal d'injection (14). Un pointeau de soupape (7) est placé dans ledit alésage (2) de façon à pouvoir coulisser longitudinalement, lequel pointeau présente, au niveau de son extrémité faisant face au siège de soupape (11), une surface d'étanchéité de soupape (12) par laquelle ce pointeau coopère avec le siège de soupape (11) pour ouvrir et fermer ledit canal d'injection (14). Une chambre de pression (5) pouvant être remplie de carburant sous pression est formée entre le pointeau de soupape (7) et la paroi de l'alésage (2). Une surface de pression (30) est formée sur ledit pointeau de soupape (7), laquelle surface fait face au siège de soupape (11) et peut être reliée à la chambre de pression (5) par l'intermédiaire d'un point d'étranglement (26) lorsque le pointeau de soupape (7) vient buter contre le siège de soupape (11).
PCT/DE2003/001734 2002-12-18 2003-05-28 Soupape d'injection de carburant pour moteurs a combustion interne WO2004057180A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP03813515A EP1576283A1 (fr) 2002-12-18 2003-05-28 Soupape d'injection de carburant pour moteurs a combustion interne

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2002159169 DE10259169A1 (de) 2002-12-18 2002-12-18 Kraftstoffeinspritzventil für Brennkraftmaschine
DE10259169.5 2002-12-18

Publications (1)

Publication Number Publication Date
WO2004057180A1 true WO2004057180A1 (fr) 2004-07-08

Family

ID=32403902

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2003/001734 WO2004057180A1 (fr) 2002-12-18 2003-05-28 Soupape d'injection de carburant pour moteurs a combustion interne

Country Status (4)

Country Link
EP (1) EP1576283A1 (fr)
CN (1) CN100593082C (fr)
DE (1) DE10259169A1 (fr)
WO (1) WO2004057180A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009028089A1 (de) 2009-07-29 2011-02-10 Robert Bosch Gmbh Kraftstoffeinspritzventil mit erhöhter Kleinmengenfähigkeit

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
TR200402050A2 (tr) * 2004-08-18 2006-03-21 Robert Bosch Gmbh Eşeksenli alansal temaslı çift oturma çaplı enjektör
DE102007013247A1 (de) * 2007-03-20 2008-09-25 Robert Bosch Gmbh Dichtkante für Kegelsitzventil
EP2239452A1 (fr) * 2009-03-30 2010-10-13 Delphi Technologies Holding S.à.r.l. Buse à injection
DE102021100754A1 (de) * 2021-01-15 2022-07-21 Marco Systemanalyse Und Entwicklung Gmbh Dosierventil

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1952816A (en) * 1931-04-04 1934-03-27 Bendix Res Corp Fuel injector
DE4115457A1 (de) * 1990-05-17 1991-11-21 Avl Verbrennungskraft Messtech Einspritzduese fuer eine brennkraftmaschine
DE19634933A1 (de) * 1996-08-29 1998-03-05 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
DE19834867A1 (de) * 1997-08-07 1999-02-11 Avl List Gmbh Einspritzdüse für eine direkt einspritzende Brennkraftmaschine
DE19931891A1 (de) * 1999-07-08 2001-01-18 Siemens Ag Kraftstoffeinspritzventil für eine Brennkraftmaschine
DE10031265A1 (de) * 2000-06-27 2002-01-10 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
DE10105681A1 (de) * 2001-02-08 2002-08-29 Siemens Ag Kraftstoffeinspritzventil für eine Brennkraftmaschine
DE10115216A1 (de) * 2001-03-28 2002-10-10 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1952816A (en) * 1931-04-04 1934-03-27 Bendix Res Corp Fuel injector
DE4115457A1 (de) * 1990-05-17 1991-11-21 Avl Verbrennungskraft Messtech Einspritzduese fuer eine brennkraftmaschine
DE19634933A1 (de) * 1996-08-29 1998-03-05 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
DE19834867A1 (de) * 1997-08-07 1999-02-11 Avl List Gmbh Einspritzdüse für eine direkt einspritzende Brennkraftmaschine
DE19931891A1 (de) * 1999-07-08 2001-01-18 Siemens Ag Kraftstoffeinspritzventil für eine Brennkraftmaschine
DE10031265A1 (de) * 2000-06-27 2002-01-10 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
DE10105681A1 (de) * 2001-02-08 2002-08-29 Siemens Ag Kraftstoffeinspritzventil für eine Brennkraftmaschine
DE10115216A1 (de) * 2001-03-28 2002-10-10 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009028089A1 (de) 2009-07-29 2011-02-10 Robert Bosch Gmbh Kraftstoffeinspritzventil mit erhöhter Kleinmengenfähigkeit

Also Published As

Publication number Publication date
EP1576283A1 (fr) 2005-09-21
CN100593082C (zh) 2010-03-03
DE10259169A1 (de) 2004-07-01
CN1717539A (zh) 2006-01-04

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