EP1276984A2 - Vanne de commande de liquides - Google Patents

Vanne de commande de liquides

Info

Publication number
EP1276984A2
EP1276984A2 EP01913616A EP01913616A EP1276984A2 EP 1276984 A2 EP1276984 A2 EP 1276984A2 EP 01913616 A EP01913616 A EP 01913616A EP 01913616 A EP01913616 A EP 01913616A EP 1276984 A2 EP1276984 A2 EP 1276984A2
Authority
EP
European Patent Office
Prior art keywords
valve
pressure
piston
throttle body
system pressure
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.)
Withdrawn
Application number
EP01913616A
Other languages
German (de)
English (en)
Inventor
Patrick Mattes
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 EP1276984A2 publication Critical patent/EP1276984A2/fr
Withdrawn legal-status Critical Current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
    • F02M51/00—Fuel-injection apparatus characterised by being operated 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
    • 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
    • F02M63/0026—Valves characterised by the valve actuating means electrical, e.g. using solenoid using piezoelectric or magnetostrictive actuators
    • 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
    • F02M63/0031—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
    • 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
    • F02M2200/705—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic with means for filling or emptying hydraulic chamber, e.g. for compensating clearance or thermal expansion

Definitions

  • the invention relates to a valve for controlling
  • Valves of this type for controlling liquids in which a valve closing member separates a low-pressure area in the valve from a high-pressure area, are known in practice, for example in fuel injectors, in particular common-rail injectors, or in pumps of motor vehicles in a wide variety of designs.
  • Such a valve is also known from EP 0 477 400 A1, the valve described therein being operable via a piezoelectric actuator and having an arrangement for a displacement transformer of the piezoelectric actuator acting in the stroke direction.
  • the actuator deflection is transmitted via a hydraulic chamber, which acts as a hydraulic transmission and Tolerance compensation element is used.
  • the hydraulic chamber closes a common one between two pistons delimiting it, of which one piston is designed with a smaller diameter and is connected to a valve closing element to be controlled, and the other piston is designed with a larger diameter and is connected to the piezoelectric actuator Working volume.
  • the hydraulic chamber is clamped between the pistons in such a way that the actuating piston makes a stroke that is increased by the ratio of the piston diameter when the larger piston is moved by a certain distance by the piezoelectric actuator.
  • tolerances can be compensated for via the working volume of the hydraulic chamber, for example due to different coefficients of thermal expansion of the materials used, and any setting effects without the valve closing member experiencing a change in its position.
  • the hydraulic system in the low pressure range in particular the hydraulic coupler, requires a system pressure. This will drop due to leakage if there is insufficient hydraulic fluid refill.
  • the filling of the system pressure range is achieved, for example, in common rail injectors known from practice, in which the system pressure is expediently generated in the valve itself and is kept as constant as possible even when the system is started of hydraulic fluid from the high pressure area of the fuel to be controlled into the low pressure area in which system pressure is to be realized. Filling is often carried out with the help of leak gaps, which are represented by leak or filling pins.
  • the system pressure is usually set by means of a valve, whereby the system pressure can also be kept constant for several common rail valves, for example.
  • the valve according to the invention for controlling liquids with the features of claim 1 or 2 has the advantage that a system pressure dependent on the pressure level in the high pressure range is provided for refilling the hydraulic chamber, with which the safe function of the hydraulic chamber is ensured as a hydraulic translator.
  • a valve according to the invention an increase in the system pressure at a high pressure level in the high-pressure area in the hydraulic chamber is possible, as a result of which the opening of the valve-closing member is supported against the high pressure present.
  • a reduced control voltage of the actuator unit which is preferably designed as a piezoelectric unit, is sufficient compared to a valve with a constant system pressure.
  • the valve according to the invention can therefore be equipped with a smaller and less expensive actuator unit.
  • the invention enables a defined refilling of the low pressure area, in particular the hydraulic chamber.
  • a very precise adjustment of the system pressure can take place through flow changes on the throttle body, which are carried out in a particularly preferred manner by hydroerosive rounding during assembly.
  • the valve according to the invention is thus characterized in addition to the reliable provision of the required system pressure in the entire engine map and also by low costs in manufacture and assembly. This is mainly due to the constructively simple before the design of the valve, which allows the variable system pressure in the hydraulic chamber to be defined by easily adjustable geometric parameters such as the throttle flow and the dimensions of the body along which the system pressure is reduced to low pressure.
  • valve according to the invention for controlling liquids are shown in the drawing and are explained in more detail in the following description. Show it
  • FIG. 1 shows a schematic, partial illustration of a first exemplary embodiment of the invention in a fuel injection valve for internal combustion engines in longitudinal section
  • FIG. 2 shows a simplified, partial illustration of a further exemplary embodiment of the invention in longitudinal section
  • FIG. 3 shows a simplified schematic diagram of an addition to the embodiments shown in FIGS. 1 and 2. Description of the embodiments
  • FIG. 1 shows a use of the valve according to the invention in a fuel injection valve 1 for internal combustion engines of motor vehicles.
  • the fuel injection valve 1 is designed as a common rail injector for the injection of preferably diesel fuel, the fuel injection being controlled via the pressure level in a valve control chamber 2 which is connected to a high pressure supply.
  • a valve member 3 is controlled via an actuator unit designed as a piezoelectric actuator 4, which is arranged on the side of the valve member 3 facing away from the valve control chamber and combustion chamber.
  • the piezoelectric actuator 4 is constructed in a conventional manner from a plurality of layers and has an actuator head 5 on its side facing the valve member 3 and an actuator base 6 on its side facing away from the valve member 3, which is supported on a wall of a valve body 7.
  • the valve member 3 is arranged axially displaceably in a longitudinal bore 10 of the valve body 7 and, in addition to the first piston 9, comprises a further second piston 11 which actuates a valve closing member 12 and is therefore also referred to as an actuating piston.
  • the pistons 9 and 11 ' are coupled to one another by means of a hydraulic transmission, which is designed as a hydraulic chamber 13 and transmits the deflection of the piezoelectric actuator 4.
  • the 13 includes between the two pistons 9 and 11 delimiting them, in which the diameter Al of the second piston 11 is smaller than the diameter A0 of the first piston 9, a common compensation volume in which there is a system pressure p_sys.
  • the valve member 3, its pistons 9 and 11 and the piezoelectric actuator 4 lie one behind the other on a common axis, the second piston 11 making a stroke increased by the ratio of the piston diameter when the larger first piston 9 by the piezoelectric actuator 4 by a certain one Distance is moved.
  • the compensation volume of the hydraulic chamber 13 allows compensation of tolerances due to temperature gradients in the component or different coefficients of thermal expansion of the materials used as well as any setting effects without influencing the position of the valve closing element 12 to be controlled.
  • valve closing member 12 At the end of the valve member 3 facing the valve control chamber 2, the ball-like valve closing member 12 cooperates with valve seats 14, 15 formed on the valve body 7, the valve closing member 12 having a low pressure region 16 with the system pressure p_sys from a high pressure region 17 with a high pressure or
  • Rail pressure p_R separates.
  • the valve seats 14, 15 are in a valve chamber 18 formed by the valve body 7, from which a leakage drain channel 19 leads away on the side of the valve seat 14 facing the piezoelectric actuator 4.
  • the valve chamber 18 can be connected to the valve control chamber 2 of the high pressure region 17 via the second valve seat 15 and an outlet throttle 20.
  • the valve control chamber 2 is only indicated in FIG. 1.
  • a movable valve control piston, not shown, is arranged in it. By means of its axial movements, the injection behavior of the fuel injection valve 1 is controlled in a manner known per se, the valve control chamber 2 being usually connected to an injection line which is connected to a high-pressure storage chamber (common rail) common to several fuel injection valves.
  • a further valve chamber 21 is provided, which is delimited by the valve body 7, the first piston 9 and a sealing element 22 connected to this and the valve body 7.
  • a leakage line 23 branches off from the valve chamber 21 in order to discharge leakage liquid.
  • a filling device 24 is provided. which is connected to the high pressure region 17.
  • the filling device 24 is formed with a channel-like cavity 25, in which a pin-like throttle body 26 with a continuous throttle bore 27 is pressed.
  • a line 27 leading to the high-pressure region 17 opens into the cavity 25, while a system pressure line 28 leading to the hydraulic chamber 13 branches off from the cavity 25 at the opposite end of the throttle body 26.
  • system pressure line 28 opens into a gap 29 surrounding the first piston 9, via which the system pressure opposes the valve chamber 21 and
  • Leakage line 23 is reduced.
  • the system pressure line 28 alternatively or additionally opens into a gap 30 surrounding the second piston 11, as is indicated by the line 28 'in dashed lines in the figures.
  • the indirect filling of the hydraulic chamber 13 serves in any case to improve the pressure holding capacity in the hydraulic chamber 13 during the control, but it is of course also possible to fill the hydraulic chamber 13 directly via the system pressure line 28.
  • the system pressure p_sys in the fuel injection valve 1 according to the invention shown in FIG. 1 is determined by geometrically fixing the throttle bore 27 in the throttle body 26 and the dimensions, ie the length and the diameter A0, of the first piston 9. As long as the system pressure p_sys is reduced towards the low pressure region 16, it is built up in the high pressure region 17 as a function of the present pressure p_R.
  • the coupler pressure or system pressure p__sys in the assembly can be set so that it varies depending on the pressure p_R prevailing in the high pressure region 17.
  • the system pressure p_sys which is reached after an injection after a certain refilling time, must not exceed a maximum permissible static system pressure or coupler pressure, which would lead to the valve opening independently without actuation of the piezoelectric unit 4. Accordingly, the gap dimensions on the pistons 9 and
  • the diameter A0 of the first piston 9 and the diameter AI of the second piston 11 are thus parameters for the geometric definition of the throttle body 26 and the first piston 9. Further parameters for their geometric definition include the diameter ratio of the pistons 9 and 11 and a seat diameter A2 of the first valve seat 14 and a spring force F_F of a spring 31, which in the present case is arranged between the valve closing member 12 and the second valve seat 15 and the valve closing member
  • FIG. 2 a section of a further exemplary embodiment of the fuel injection valve is tils shown, which works in principle like the fuel injector described for Figure 1. For reasons of clarity, functionally identical components are identified by the reference numerals used in FIG. 1.
  • a further throttle body 32 which is also designed like a sleeve with a throttle bore 34, is pressed into the cavity 25, which also receives the first throttle body 26, being connected upstream of a leakage line 35 branching off directly from the cavity 25.
  • the system pressure p_sys builds up in the cavity 25 and in the system pressure line 28 and the hydraulic chamber 13 as a function of the present pressure p_R in the high-pressure region 17.
  • FIG. 3 shows a basic illustration of a supplement to the embodiments according to FIG. 1 and FIG. 2, with the cavity 25 accommodating at least the first throttle body 26 being provided on the high pressure side
  • Cavity 36 is connected upstream with a solid 37 arranged therein.
  • This solid 37 which in the advantageous embodiment shown is piston-like, is axially movable in the cavity 36 and is arranged with play, whereby it serves at least primarily as a filter for throttling the downstream first throttle body 26. Filtering the high-pressure flow flowing to the first throttle body 26 is particularly advantageous in the case of a small throttle diameter of the first throttle body 26, as is often required in passenger cars. So that dirt particles do not clog the throttle bore 27 of the throttle body 26 here, these dirt particles, which are larger than a predefined gap dimension, are retained by the piston 37. Due to the preferably large gap dimension around the piston 37, this causes only a very small throttling.
  • the pressure divider function for setting the system pressure p_sys thus only takes place via the first throttle body 26 and the first piston 9 or the second throttle body 32.
  • the axial mobility of the piston 37 serving as a filter also ensures that its gap dimension, which can be, for example, 10 ⁇ m to 15 ⁇ m, is not clogged by the dirt particles becomes.
  • a spring device 39 is provided between the solid body or piston 37 and a throttle-side stop 38, by means of which the piston 37 can be displaced to a high-pressure side stop 40 in the high-pressure region 17 when the high pressure p_R drops is.
  • the piston 37 is moved at every start-up and shut-down phase, which frees the piston gap automatically.
  • the piston 37 is geometrically fixed as a function of the parameters already listed with regard to the throttle body dimensioning.
  • the fuel injection valve according to Figure 1, 2 or 3 operates in the manner described below.
  • valve closing member 12 When the fuel injector 1 is closed, i.e. If no voltage is present at the piezoelectric actuator 4, the valve closing member 12 is located on the upper valve seat 14 assigned to it and is pressed against the first valve seat 14 by the spring 31 with the spring preload F_F and mainly by the rail pressure p_R.
  • the first piston 9, which serves as an actuating piston penetrates into the compensation volume of the hydraulic chamber 13 when the temperature rises and pulls out of it Temperature reduction back without the overall closing and opening position of the valve closing member 12 and the fuel injection valve 1 being affected.
  • the piezoelectric actuator 4 When the valve is to be opened and an injection is to take place through the fuel injection valve 1, the piezoelectric actuator 4 is acted on by voltage, as a result of which it suddenly expands axially.
  • the piezoelectric actuator 4 is supported on the valve body 7 and builds up an opening pressure in the hydraulic chamber 13. Only when the valve 1 is in equilibrium in the hydraulic chamber 13 due to the system pressure p_sys, does the second piston 11 drive the valve closing member 12 out of its upper valve seat 14 into a central position between the two valve seats 14 and 15. At high rail pressure p_R, a greater force is exerted on the piezo side required to reach the equilibrium pressure in the hydraulic chamber 13.
  • the pressure in the hydraulic chamber 13 is also correspondingly increased when the rail pressure p_R is high.
  • the piezo-side force on the valve closing member 12 is increased with the same voltage on the piezoelectric actuator 4.
  • This increase in force corresponds to a substantially higher voltage which would have to be applied to the piezoelectric actuator 4.
  • the power reserve obtained can be used in the design of the valve, for example, to reduce the size of the piezoelectric actuator.
  • the energization of the piezoelectric actuator 4 is interrupted. Simultaneously with the return movement of the valve closing member 12, the hydraulic chamber 13 is refilled to the system pressure p_sys via the filling device 24.
  • the described embodiments each relate to a so-called double-seat valve, but the invention can of course also be applied to single-switching valves with only one valve seat.
  • the line 33 of the filling device 24 leading to the high-pressure region 17 is connected, as in the preferred embodiments shown, to the valve chamber 18, in which the valve closing member 12 can be moved between the valve seats 14 and 15.
  • the line 33 is connected in terms of flow to a high-pressure inlet from a high-pressure pump, for example to the valve control chamber 2 in the high-pressure region 17 or to the outlet throttle 20.

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)
  • Fuel-Injection Apparatus (AREA)
  • Electrically Driven Valve-Operating Means (AREA)
  • Fluid-Driven Valves (AREA)

Abstract

La présente invention concerne une vanne de commande de liquides, comprenant une unité d'actionneur (4), qui permet d'actionner un élément de vanne (3). Cet élément de vanne présente un premier piston (9) et un second piston (11), séparé du premier piston par une chambre hydraulique (13), et actionne un élément de fermeture de vanne (12), qui sépare une zone de basse pression (16), à la pression du système, d'une zone de haute pression (17). Afin de compenser les fuites, un dispositif de remplissage (24) pouvant être connecté à la zone de haute pression (17) est pourvu d'une cavité (25) dans laquelle un corps d'étranglement (26) est monté de façon qu'une conduite (33) menant à la zone de haute pression (17) débouche dans la cavité (25), à une extrémité du corps d'étranglement (26), et qu'à l'autre extrémité, une conduite de pression du système (28) menant à la transmission hydraulique bifurque. La pression du système s'élève en fonction d'une pression présente dans la zone de haute pression, de par la définition géométrique d'un orifice d'étranglement (27) dans le corps d'étranglement (26) et des dimensions du piston (9), le long duquel la pression de système (p-sys) est réduite. En variante, un second corps d'étranglement (32) pourvu d'un orifice d'étranglement (34) peut être monté dans la cavité (25), ce corps d'étranglement étant connecté en amont d'une conduite de fuite (35) qui dérive de la cavité (25) et la pression de système étant réduite le long de ce second corps d'étranglement.
EP01913616A 2000-04-20 2001-02-13 Vanne de commande de liquides Withdrawn EP1276984A2 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10019764 2000-04-20
DE10019764A DE10019764B4 (de) 2000-04-20 2000-04-20 Ventil zum Steuern von Flüssigkeiten
PCT/DE2001/000534 WO2001081752A2 (fr) 2000-04-20 2001-02-13 Vanne de commande de liquides

Publications (1)

Publication Number Publication Date
EP1276984A2 true EP1276984A2 (fr) 2003-01-22

Family

ID=7639565

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01913616A Withdrawn EP1276984A2 (fr) 2000-04-20 2001-02-13 Vanne de commande de liquides

Country Status (8)

Country Link
US (1) US6698711B2 (fr)
EP (1) EP1276984A2 (fr)
JP (1) JP2003532001A (fr)
KR (1) KR20020023239A (fr)
CZ (1) CZ20014521A3 (fr)
DE (1) DE10019764B4 (fr)
HU (1) HUP0202459A2 (fr)
WO (1) WO2001081752A2 (fr)

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Publication number Priority date Publication date Assignee Title
DE10043625C2 (de) * 2000-09-05 2003-03-27 Bosch Gmbh Robert Hydraulisch übersetztes Ventil
DE10048933A1 (de) * 2000-10-04 2002-05-02 Bosch Gmbh Robert Ventil zum Steuern von Flüssigkeiten
DE10112147A1 (de) * 2001-03-14 2002-09-19 Bosch Gmbh Robert Ventil zum Steuern von Flüssigkeiten
DE10157419A1 (de) * 2001-11-23 2003-06-12 Bosch Gmbh Robert Leckagereduzierte Druckversorgung für Kraftstoffinjektoren
DE10160191A1 (de) * 2001-12-07 2003-06-26 Bosch Gmbh Robert Kraftstoffinjektor mit fremdbetätigtem Steller und optimierter Systemdruckversorgung
JP3832401B2 (ja) 2002-08-07 2006-10-11 トヨタ自動車株式会社 燃料噴射装置
DE10333695A1 (de) * 2003-07-24 2005-03-03 Robert Bosch Gmbh Kraftstoffeinspritzvorrichtung
DE10333696A1 (de) * 2003-07-24 2005-02-24 Robert Bosch Gmbh Kraftstoffeinspritzvorrichtung
JP4264449B2 (ja) 2003-09-12 2009-05-20 シーメンス アクチエンゲゼルシヤフト 調量装置
DE102004015744A1 (de) * 2004-03-31 2005-10-13 Robert Bosch Gmbh Common-Rail-Injektor
DE102004027824A1 (de) * 2004-06-08 2006-01-05 Robert Bosch Gmbh Kraftstoffinjektor mit variabler Aktorübersetzung
KR100752182B1 (ko) 2005-10-12 2007-08-24 동부일렉트로닉스 주식회사 씨모스 이미지 센서 및 그 제조방법

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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
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Title
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Also Published As

Publication number Publication date
CZ20014521A3 (cs) 2003-04-16
WO2001081752A3 (fr) 2002-03-28
US20030098428A1 (en) 2003-05-29
KR20020023239A (ko) 2002-03-28
DE10019764A1 (de) 2001-10-31
DE10019764B4 (de) 2004-09-23
HUP0202459A2 (en) 2002-12-28
WO2001081752A2 (fr) 2001-11-01
US6698711B2 (en) 2004-03-02
JP2003532001A (ja) 2003-10-28

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