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EP1538331B1 - Soupape d'injection de carburant - Google Patents

Soupape d'injection de carburant Download PDF

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Publication number
EP1538331B1
EP1538331B1 EP20040105050 EP04105050A EP1538331B1 EP 1538331 B1 EP1538331 B1 EP 1538331B1 EP 20040105050 EP20040105050 EP 20040105050 EP 04105050 A EP04105050 A EP 04105050A EP 1538331 B1 EP1538331 B1 EP 1538331B1
Authority
EP
European Patent Office
Prior art keywords
fuel injection
injection valve
valve according
coupler
slave
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.)
Expired - Lifetime
Application number
EP20040105050
Other languages
German (de)
English (en)
Other versions
EP1538331A1 (fr
Inventor
Klaus Noller
Michael Huebel
Thomas Gerschwitz
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 EP1538331A1 publication Critical patent/EP1538331A1/fr
Application granted granted Critical
Publication of EP1538331B1 publication Critical patent/EP1538331B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/0603—Injectors peculiar thereto with means directly operating the valve needle using piezoelectric or magnetostrictive 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/08—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series the valves opening in direction of fuel 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
    • 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
    • F02M61/166—Selection of particular materials
    • 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
    • F02M61/167—Means for compensating clearance or thermal expansion
    • 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
    • F02M2200/16—Sealing of fuel injection apparatus not otherwise provided for
    • 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
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
    • F02M2200/707—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic with means for avoiding fuel contact with actuators, e.g. isolating actuators by using bellows or diaphragms

Definitions

  • the invention relates to a fuel injection valve according to the preamble of the main claim.
  • EP 0 477 400 A1 discloses an arrangement for an adaptive mechanical tolerance compensation acting in the stroke direction for a travel transformer of a piezoelectric actuator for a fuel injection valve.
  • the stroke of the actuator is transmitted via a hydraulic chamber.
  • the hydraulic chamber has a defined leak with a defined leak rate.
  • the stroke of the actuator is introduced via a master piston in the hydraulic chamber and transmitted via a slave piston to a driven element.
  • This element is for example a valve needle of a fuel injection valve.
  • a slave piston In the master cylinder, a slave piston is guided, which also closes the master cylinder and thereby forms the hydraulic chamber.
  • a spring In the hydraulic chamber, a spring is arranged, which presses apart the master cylinder and the slave piston.
  • this stroke movement is due to the pressure of a hydraulic fluid in the hydraulic chamber on the Transfer slave piston, since the hydraulic fluid in the hydraulic chamber can not compress and only a small proportion of the hydraulic fluid can escape through the annular gap during the short period of a stroke.
  • the slave piston In the resting phase, when the actuator exerts no pressure force on the master cylinder, the slave piston is pushed out of the cylinder by the spring and by the resulting negative pressure penetrates through the annular gap, the hydraulic fluid in the hydraulic chamber and fills it again.
  • the hydraulic coupler automatically adjusts to length expansions and pressure-related expansions of a fuel injection valve.
  • the sealing of the hydraulic medium takes place via sealing rings.
  • US 2002/0139863 A1 starts from a fuel injection valve with an actuator whose length changes, wherein the change in length of the actuator is coupled to a valve closing body, so that an extension of the actuator caused by an applied electrical voltage causes the valve closing body to be seated on the valve closing body brings the downstream end of the fuel injection valve in a sealing contact.
  • the fuel injection valve according to the invention with the characterizing features of the main claim has the advantage that the hydraulic medium of the coupler is permanently sealed and the space and the manufacturing cost is reduced.
  • the diameter feed engages or protrudes into a recess, wherein in a further development, the recess decreases in the case of an enlarging coupler volume.
  • the coupler can be made compact and the bias, with which the flexible portion acts on the hydraulic medium, be favorably influenced.
  • the throttle Due to the design of the throttle as a bore and the arrangement of the throttle in a throttle disk, the throttle can be very easily and inexpensively.
  • the hydraulic behavior of the coupler can be further advantageously adjusted.
  • the hydraulic behavior of the coupler can be further advantageously influenced.
  • FIGS. 1 and 2 Before the invention is described in more detail with reference to preferred embodiments, a fuel injection valve according to the prior art in its essential components in FIGS. 1 and 2 is briefly explained for better understanding. Matching components are provided in the figures with corresponding reference numerals.
  • the fuel injection valve 1 shown in FIG. 1 is in the form of a fuel injection valve 1 for fuel injection systems of mixture-compression spark-ignition internal combustion engines.
  • the fuel injection valve 1 is suitable in particular for the direct injection of fuel into a combustion chamber, not shown, of an internal combustion engine.
  • the fuel injection valve 1 comprises a housing 2, in which a provided with an Aktorumspritzung 3 piezoelectric or magnetostrictive actuator 4 is arranged.
  • the actuator 4 can be supplied by means of an electrical line 5, to which a protruding from the housing 2 electrical terminal 6, an electrical voltage can be supplied.
  • the actuator 4 is supported on the inflow side on a master piston 9 of a hydraulic coupler 7 and downstream of an actuator head 8.
  • the hydraulic coupler 7 further comprises a slave piston 10, a Compression spring 11, which acts on the hydraulic coupler 7 with a bias, and a compensation chamber 12 which is filled with a hydraulic medium.
  • the fuel is fed centrally via an inlet 14.
  • an actuating body 15 Downstream of the actuator head 8, an actuating body 15 is arranged, which acts on a valve needle 16.
  • the valve needle 16 has at its downstream end a valve closing body 17. This acts together with a valve seat surface 18, which is formed on a nozzle body 19, to form a sealing seat.
  • a return spring 20 acts on the valve needle 16 so that the fuel injection valve 1 remains in the de-energized state of the actuator 4 in the closed state. Furthermore, it ensures the return of the valve needle 16 after the injection phase.
  • the nozzle body 19 is fixed by means of a weld 21 in an inner housing 22, which seals the actuator 4 against the fuel.
  • the fuel flows from the inlet 14 between the housing 2 and the inner housing 22 to the sealing seat.
  • FIG. 2 shows a coupler 7 constructed similarly to the coupler shown in FIG.
  • Hydraulic couplers 7 in fuel injection valves 1 are usually designed on the one hand for conversion or translation of the stroke of the actuator 4 on the valve needle 16 and / or on the other hand to compensate for temperature-induced changes in length of the actuator 4 and the housing 2.
  • the latter is realized, as shown in the exemplary embodiment, by means of a coupler 7 designed as a second medium coupler, which contains a hydraulic medium not coming into contact with the fuel.
  • the hydraulic medium fills the compensation chamber 12 and a between master piston 9 and Slave piston 10 formed coupler volume 23, which is connected to the expansion chamber 12 via a throttle 24.
  • the compensation chamber 12 is disposed inside and outside the slave piston 10, wherein the two parts are connected by a transverse bore 31 and the outboard part of the compensation chamber 12 is sealed by means of a corrugated tube seal designed as flexible portion 13 relative to the fuel injector 1 flowing through the fuel.
  • hydraulic medium is exchanged between the coupler volume 23 via the throttle 24 with the compensation chamber 12.
  • the necessary filling pressure is applied via the pressure piston 11 arranged in the slave piston 10 in a pressure storage chamber 32. This is arranged between a first closure body 25 and a second closure body 26, the former having a groove 27 with a sealing ring 28 arranged therein for sealing the coupler space 12.
  • the filling of the coupler 7, for example in the production, with hydraulic medium takes place through a bore 29, which may be closed, for example by means of a pressed-in ball 30.
  • a disadvantage of the described design of the fuel injector 1 and the hydraulic coupler 7 is in particular that the leakage losses at the arranged in the groove 27 sealing ring 28 are relatively high. This reduces the fatigue strength of the fuel injection valve 1, since the hydraulic medium on the sealing ring 28 leaks over time into the pressure storage space 32 and thus also reduces the prestress applied by the compression spring 11. Thus, the coupler 7 undesirably changes its behavior in the fuel injection valve 1 over the lifetime. Due to the complicated design, the production of the coupler 7 is very expensive and the size increased unfavorably. In addition, in particular by the shape of the flexible portion, a relatively large capacity of the hydraulic medium necessary. But this increases the temperature dependence by the temperature expansion.
  • a remedy is provided by the embodiment described below of a designed as a second-medium coupler coupler 7, which is simple and inexpensive to manufacture, less expensive built, reliable continuous running and its behavior is less temperature-dependent.
  • FIG. 3 shows a non-inventive example of a coupler 7 for a fuel injection valve 1.
  • the slave piston 10 engages with a piston-shaped second slave section 35 into the essentially cylindrical master piston 9.
  • the slave piston 10 and the second slave section 35 are guided axially movably in the master piston 9 with a guide gap 38.
  • the guide gap 38 is relatively small, wherein the amount of hydraulic medium passing through the guide gap 38 during operation is negligibly small.
  • the guide gap 38 may exert a throttle function.
  • the slave piston 10 consists of a first slave section 34 and a second slave section 35, wherein in other embodiments, the slave piston 10 can also be made in one piece.
  • the first slave section 34 is cylindrical and tapers from a diameter which corresponds approximately to the diameter of the master piston 9, stepwise in the direction of the master piston 9, and the second slave section 35.
  • the first slave section 34 tapers at a step 40 and thus has a T-shaped cross-section.
  • the tapered part of the first slave portion 34 engages partially coaxially in the second slave portion 35 and is fixed there immovable, for example by pressing or welding.
  • the U-shaped diameter retraction 33 protrudes into the recess 39.
  • the flexible portion 13 In the region of the upper end of the flexible portion 13 on the circumference of the first slave portion 34, for example, cohesively, hermetically sealed. In the region of its lower end, the flexible portion 13 is circumferentially hermetically sealed to the master piston 9.
  • the slave piston 10 has a centered channel 29 which merges into a compensation channel 36 and is closed to the outside by a ball 30, which is introduced after filling the coupler 7 with hydraulic medium for closing the channel 29.
  • the compensation channel 36 which is formed in this embodiment as a stepped bore, ends at its the coupler volume 23 facing the end of a throttle plate 37, which has at least one designed as a relatively small bore, centered throttle 24.
  • the throttle 24 opens into the coupler volume 23.
  • the transverse bore 31 Approximately at the level of the transition of the channel 29 in the compensation channel 36 is the transverse bore 31, which can also be prepared by other molding methods than drilling.
  • the restrictor disk 37 is embedded in the surface of the second slave section 35 and, for example, joined to the second slave section 35 in a material-locking manner by welding.
  • the transverse bore 31 connects via the throttle 24, the coupler volume 23 with the expansion chamber 12th
  • FIG. 4 shows an exemplary embodiment of a fuel injection valve 1 according to the invention in the region of the coupler 7, similar to the exemplary embodiment from FIG. 3.
  • the channel 29 is arranged in the master piston 9.
  • the channel 29 opens directly into the coupler volume 23.
  • the compensation channel 36 connects the coupler volume 23, the compensation chamber 12 and a chamber 41 with each other.
  • the chamber 41 is formed in the slave piston 10, wherein in this embodiment, the chamber 41 by a first recess 44 which is centered in a first slave portion 34 above and laterally comprehensive attachment 43 is disposed, and by a second recess 45 at the upper end of the first slave section 34 is formed centered, is formed.
  • the recesses 44, 45 lie with the interposition of a membrane 42 hydraulically outwardly close to each other and thereby form the chamber 41.
  • the membrane 42 consists for example of an elastomer and divides the chamber 41 hermetically sealed into the first recess 44 and the second recess 45th Die second recess 45 is connected via the compensation channel 36 with the coupler volume 23 in connection.
  • the first recess 44 is, for example, with a gas filled with pressure and thus exerts a pressure on the hydraulic medium.
  • the internal coupler pressure can be generated via an additionally arranged in the chamber 41 spring, so that the interior 41 is depressurized.
  • the membrane 42 is elastic and consists of an elastomer, for example of Viton.
  • the attachment part 43 belonging to the slave piston 10 is connected, for example, by pressing and / or welding to the first slave section 34.
  • the flexible portion 13 is hermetically sealed at its upper end to the radially outer surface of the attachment 43.
  • the invention is also suitable for fuel injection valves 1 for self-igniting internal combustion engines and / or inwardly opening fuel injection valves.

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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)

Claims (17)

  1. Injecteur de carburant (1) comprenant un actionneur (4) piézoélectrique ou magnétostrictif qui actionne un obturateur de fermeture de soupape (17) coopérant avec une surface de siège de soupape (18) pour former un siège d'étanchéité, et comprenant un coupleur hydraulique (7) composé d'un piston entraîneur (9), d'un piston entraîné (10) et d'un volume de coupleur (23) formé entre ces derniers, le volume de coupleur (23) communiquant avec une chambre de compensation (12) par un étranglement (24), un segment flexible (13) délimitant au moins partiellement la chambre de compensation (12) et le volume de coupleur (23), l'étranglement (24) et la chambre de compensation (12) étant remplis d'un fluide hydraulique, la section flexible (13) étant élastique et présentant un renfoncement diamétral (33) de forme sensiblement en U, le caractère élastique du segment flexible (13) permettant de soumettre le fluide hydraulique à une pression, la chambre de compensation (12) communiquant avec une chambre (41),
    caractérisé en ce que
    la chambre (41) est divisée de manière étanche au fluide hydraulique en un premier évidement (44) et un second évidement (45) par une membrane élastique (42).
  2. Injecteur de carburant selon la revendication 1,
    caractérisé en ce que
    le renfoncement diamétral (33) s'engage ou fait saillie dans une cavité (39).
  3. Injecteur de carburant selon la revendication 2,
    caractérisé en ce que
    la cavité (39) rétrécit axialement lorsque le volume de coupleur (23) augmente.
  4. Injecteur de carburant selon la revendication 3,
    caractérisé en ce que
    le rétrécissement de la cavité (39) entraîne un accroissement de la précontrainte qu'exerce la section flexible (13) ou le renfoncement diamétral (33) sur le fluide hydraulique.
  5. Injecteur de carburant selon l'une des revendications 2 à 4,
    caractérisé en ce que
    la cavité (33) est constituée par un gradin (40) formé sur le piston entraîné (10) et par un bord supérieur du piston entraîneur (9) orienté vers le gradin (40).
  6. Injecteur de carburant selon l'une des revendications 2 à 5,
    caractérisé en ce que
    la cavité (33) se présente sous la forme d'une rainure annulaire.
  7. Injecteur de carburant selon l'une des revendications précédentes,
    caractérisé en ce que
    la chambre de compensation (12) est délimitée par le segment flexible (12), le piston entraîné (10) et le piston entraîneur (9).
  8. Injecteur de carburant selon l'une des revendications précédentes,
    caractérisé en ce que
    l'étranglement (24) est un alésage.
  9. Injecteur de carburant selon l'une des revendications précédentes,
    caractérisé en ce que
    le volume de coupleur (23) communique avec la chambre de compensation (12) par un canal de compensation (36) et un alésage transversal (31) disposé dans le piston entraîné (10).
  10. Injecteur de carburant selon l'une des revendications précédentes,
    caractérisé en ce que
    l'étranglement (24) est disposé dans une rondelle d'étranglement (37).
  11. Injecteur de carburant selon l'une des revendications précédentes,
    caractérisé en ce que
    le fluide hydraulique est un liquide huileux.
  12. Injecteur de carburant selon la revendication 1,
    caractérisé en ce que
    l'un (45) des deux évidements peut échanger du fluide hydraulique avec la chambre de compensation (12).
  13. Injecteur de carburant selon la revendication 12,
    caractérisé en ce que
    l'autre (44) des évidements est rempli d'un gaz sous pression.
  14. Injecteur de carburant selon la revendication 12,
    caractérisé en ce qu'
    un ressort produisant une pression intérieure de coupleur est disposé dans la chambre (41).
  15. Injecteur de carburant selon l'une des revendications 12 à 14,
    caractérisé en ce que
    la membrane (42) se compose d'élastomère, notamment de Viton.
  16. Injecteur de carburant selon l'une des revendications 12 à 15,
    caractérisé en ce que
    la chambre (41) est disposée entre une première section entraînée (34) du piston entraîné (10) et un élément de montage (43) raccordé à la première section entraînée (34).
  17. Injecteur de carburant selon la revendication 16,
    caractérisé en ce que
    la membrane (42) est serrée entre la première section entraînée (34) et l'élément de montage (43).
EP20040105050 2003-12-03 2004-10-14 Soupape d'injection de carburant Expired - Lifetime EP1538331B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2003157454 DE10357454A1 (de) 2003-12-03 2003-12-03 Brennstoffeinspritzventil
DE10357454 2003-12-03

Publications (2)

Publication Number Publication Date
EP1538331A1 EP1538331A1 (fr) 2005-06-08
EP1538331B1 true EP1538331B1 (fr) 2007-05-30

Family

ID=34442509

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20040105050 Expired - Lifetime EP1538331B1 (fr) 2003-12-03 2004-10-14 Soupape d'injection de carburant

Country Status (2)

Country Link
EP (1) EP1538331B1 (fr)
DE (2) DE10357454A1 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE602005005242T2 (de) * 2004-04-26 2009-04-02 Isuzu Motors Ltd. Längen-Ausgleichselement und dieses enthaltendes Kraftstoff-Einspritzventil
EP1780405B1 (fr) * 2005-10-26 2008-09-17 Siemens Aktiengesellschaft Injecteur, dispositif de compensation pour l'injecteur et moyen de transmission de pression pour le dispositif de compensation
EP1813805A1 (fr) * 2006-01-27 2007-08-01 Siemens VDO Automotive S.p.A. Ensemble de compensation pour un injecteur
DE602006016296D1 (de) * 2006-11-02 2010-09-30 Continental Automotive Gmbh Injektor zur Dosierung von Flüssigkeit
CN101903588B (zh) 2007-12-21 2012-10-10 Bsh博施及西门子家用器具有限公司 用于熨烫的装置
EP2078846B1 (fr) * 2008-01-14 2014-12-03 Continental Automotive GmbH Agencement d'actionneur et soupape à injection
DE102012202909A1 (de) * 2012-02-27 2013-08-29 Robert Bosch Gmbh Ventil zum Zumessen von Fluid

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0656162B2 (ja) * 1987-03-03 1994-07-27 トヨタ自動車株式会社 ストロ−ク可変装置
DE59010904D1 (de) * 1990-09-25 2000-05-31 Siemens Ag Anordnung für einen in Hubrichtung wirkenden adaptiven, mechanischen Toleranzausgleich für den Wegtransformator eines piezoelektrischen Aktors
WO1993006625A1 (fr) * 1991-09-27 1993-04-01 Siemens Aktiengesellschaft Transformateur hydraulique de deplacement pour l'organe piezoelectrique d'actionnement d'une soupape d'admission
DE19962177A1 (de) * 1999-12-22 2001-07-12 Siemens Ag Hydraulische Vorrichtung zum Übertragen einer Aktorbewegung
EP1325224B1 (fr) * 2000-10-11 2006-05-03 Siemens VDO Automotive Corporation Soupape sensible a la pression pour compensateur d'actionneur transistorise
DE10148594A1 (de) * 2001-10-02 2003-04-10 Bosch Gmbh Robert Brennstoffeinspritzventil
DE10149914A1 (de) * 2001-10-10 2003-04-24 Bosch Gmbh Robert Brennstoffeinspritzventil
DE10159749A1 (de) * 2001-12-05 2003-06-12 Bosch Gmbh Robert Brennstoffeinspritzventil
DE502004002718D1 (de) * 2003-02-27 2007-03-15 Bosch Gmbh Robert Brennstoffeinspritzventil

Also Published As

Publication number Publication date
DE502004003933D1 (de) 2007-07-12
EP1538331A1 (fr) 2005-06-08
DE10357454A1 (de) 2005-07-07

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