WO2005119061A1 - Compresseur - Google Patents

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Publication number
WO2005119061A1
WO2005119061A1 PCT/JP2005/003586 JP2005003586W WO2005119061A1 WO 2005119061 A1 WO2005119061 A1 WO 2005119061A1 JP 2005003586 W JP2005003586 W JP 2005003586W WO 2005119061 A1 WO2005119061 A1 WO 2005119061A1
Authority
WO
WIPO (PCT)
Prior art keywords
compressor
cylinder block
pressure
fastening
seal
Prior art date
Application number
PCT/JP2005/003586
Other languages
English (en)
Japanese (ja)
Inventor
Hiroshi Kanai
Original Assignee
Valeo Thermal Systems Japan Corporation
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 Valeo Thermal Systems Japan Corporation filed Critical Valeo Thermal Systems Japan Corporation
Priority to EP05719890A priority Critical patent/EP1775471A4/fr
Publication of WO2005119061A1 publication Critical patent/WO2005119061A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication
    • F04B27/1081—Casings, housings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/121—Casings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
    • F04B53/162—Adaptations of cylinders

Definitions

  • the present invention relates to a compressor used for a vehicle air conditioner or the like.
  • This prior art is an air conditioner using a carbon dioxide gas refrigerant, in which the safety coefficient of the design pressure of the indoor-side equipment disposed indoors among the equipment and refrigerant pipes constituting the refrigeration cycle constitutes the refrigeration cycle.
  • the safety factor of the design pressure of each device is higher than the safety factor.
  • the thickness of all the flow paths through which the refrigerant flows is higher than the safety factor.
  • Patent Document 1 Japanese Patent Application Laid-Open No. 2002-243320 (Claim 1, Paragraph No. 0014)
  • the present invention prevents the useless increase in the size and the number of fastening members by adjusting the surface pressure of the seal member sandwiched between a plurality of housing members, thereby preventing refrigerant leakage. It is an object of the present invention to provide a compressor that achieves safety, security, and downsizing simultaneously.
  • the present invention provides a method of integrating at least two housing members for accommodating a compression mechanism, a seal member sandwiched between the housing members, and a housing member and a seal member.
  • a surface pressure applied to the seal member generated by fastening by the fastening member is set such that a seal limit pressure of the seal member is larger than a maximum operating pressure of the compressor and It is characterized in that it is set to be smaller than the burst pressure (Claim 1).
  • the surface pressure is a pressure applied to the pressure contact surface between the seal member and the adjacent housing member by the fastening action of the fastening means, and can be measured using a known pressure-sensitive paper or the like.
  • the surface pressure is within a range of 2 to 5 times the surface pressure when the seal limit pressure is equal to the maximum working pressure. (Claim 2), particularly preferably within a range of 3 to 4 times.
  • the maximum operating pressure is in a range of 15 to 20 MPa (claim 3).
  • the seal member includes a metal substrate and rubber layers formed on both surfaces of the metal substrate.
  • the thickness is in the range of 0.2-0.8 mm! / ⁇ (Claim 4).
  • the seal member has a bead portion formed in a convex shape or a hill shape, and the height of the bead portion is 0.1-0. It is preferable that the distance be within a range of 4 mm (claim 5).
  • FIG. 9 shows an example of the configuration of the seal member 100.
  • reference numeral 105 denotes the convex bead portion (full bead)
  • reference numeral 106 denotes the hill-shaped bead portion (north bead).
  • the height of the bead portion is formed closer to the fastening member and lower.
  • the bead linear pressure indicating the acting force per unit distance applied to the bead portion at the time of fastening is within a range of 10 to 25 times the maximum operating pressure. (Claim 7).
  • the housing member includes a substantially cylindrical cylinder block in which a plurality of bores defining a compression chamber are bored, and a crank inside.
  • a front head that defines a chamber and seals one end surface of the cylinder block; and a rear head that defines a suction chamber and a discharge chamber therein and seals the other end surface of the cylinder block.
  • the fastening member may include a plurality of bolts penetrating through the vicinity of the outer edge of each of the front head, the cylinder block, and the rear head. Section 8).
  • the diameter of a pitch circle formed by connecting the gaps of the bolts is 110 mm or less! / (Claim 9).
  • the housing member has a cylinder block in which a plurality of bores that define a compression chamber are bored, and a crank chamber is defined therein. And a front head having a size and a shape enclosing the cylinder block and enclosing the cylinder block, and a suction chamber and a discharge chamber defined therein to seal the other end of the cylinder block.
  • a fastening portion wherein the fastening member comprises: a threaded portion formed on an outer wall near an end of the front head on the rear head side; a threaded portion screwed with the threaded portion; And a ring nut having a locking portion for locking the rear head.
  • the housing member has a cylinder block in which a plurality of bores defining a compression chamber are bored, and a crank chamber is defined therein. And a front head having a size and a shape enclosing the cylinder block and enclosing the cylinder block, and a suction chamber and a discharge chamber defined therein to seal the other end of the cylinder block.
  • a fastening part formed on an outer wall near an end of the front head on the rear head side, and an inner wall near an end on the front head side of the rear head. And a threaded portion that is screwed into the threaded portion.
  • the compressor according to the above-mentioned claim 11-11 is a refrigeration cycle using CO as a refrigerant.
  • the surface pressure of the seal member sandwiched between the plurality of housing members is optimized, so that the size and number of the fastening members needlessly increase. Prevention, refrigerant leakage prevention, safety assurance, and downsizing can be realized at the same time.
  • the housing can have a compact structure, which can contribute to downsizing.
  • FIG. 1 is a cross-sectional view showing a configuration example of a compressor according to the present invention.
  • FIG. 2 is a graph showing the relationship between the surface pressure of a seal member and the seal limit pressure of the seal member.
  • FIG. 3 is a top view showing a configuration example of a gasket sandwiched between a cylinder block and a suction valve.
  • FIG. 4 is a cross-sectional view of the gasket shown in FIG. 3 along the line AA.
  • FIG. 5 is a partially enlarged view of the gasket shown in FIG. 3, showing a center line of a bead portion.
  • FIG. 6 is a view showing an arrangement state of bolts as viewed from a rear head side.
  • FIG. 7 is a view showing a second housing structure.
  • FIG. 8 is a view showing a third housing structure.
  • FIG. 9 is a diagram showing a configuration example of a seal member, and structures of a convex bead portion (full bead) and a hill-shaped bead portion (half bead).
  • the compressor 1 shown in Fig. 1 constitutes a part of a refrigeration cycle that uses CO as a refrigerant and is used in a vehicle air conditioner.
  • the cylinder block 2 is a substantially cylindrical member, and a plurality of bores 20 are formed on the circumference thereof.
  • a compression chamber 21 for compressing the refrigerant is defined inside the bore 20.
  • the front head 3 is a member that seals one end surface of the cylinder block 2 and has a crank chamber 22 defined therein.
  • the rear head 4 is a member that seals the other end surface of the cylinder block 2, and has a suction chamber 25 and a discharge chamber 26 defined therein.
  • the drive shaft 5 is a substantially rod-shaped member.
  • the drive shaft 5 is rotatably held by bearings and seal members provided on the cylinder block 2 and the front head 3, and a portion 5a protruding from the front head 3 has an engine or It is connected to a pulley (not shown) rotated by a drive source such as a motor.
  • the swash plate mechanism 6 is disposed in the crank chamber 22 and includes a swash plate 30, a shower 31, an angle adjusting mechanism 32, a thrust flange 33, and the like, and converts the rotational force of the drive shaft 5 into a reciprocating motion of a piston 7.
  • the angle of the swash plate 30 is adjusted based on predetermined conditions.
  • the piston 7 is swingably connected to the shoe 31 and is slidably fitted in each of the bores 20.
  • a gasket 13, a suction valve 11, a valve plate 10, a discharge valve 12, and a gasket 14 are sandwiched between the cylinder block 2 and the rear head 4 in the order of the cylinder block 2 side force.
  • a gasket 15 is sandwiched between the block 2 and the front head 3.
  • Each of the front head 3, gasket 13, cylinder block 2, gasket 13, suction valve 11, valve plate 10, discharge valve 12, gasket 14, and rear head 4 includes a plurality (eight) of which penetrate the vicinity of each outer edge. It is fixed with a predetermined tightening force by bolts 40 and nuts 41.
  • the gasket 13, the suction valve 11, the valve plate 10, the discharge valve 12, the gasket 14, and the retainer 42 are fixed to a central portion of the cylinder block 2 by bolts 43.
  • the valve plate 10 is a disk-shaped member made of metal.
  • the valve plate 10 is a part of a suction passage 45 that communicates the suction chamber 25 with the compression chamber 21.
  • a discharge port constituting a part of a discharge passage 46 that communicates with the discharge chamber 26, a through hole that penetrates the bolt 40 at the outer edge, and a through hole that penetrates the bolt 43 at the center are provided.
  • the suction valve 11 is made of a metal plate, has a lead portion for opening and closing the suction passage 45, and allows a discharge port forming a part of the discharge passage 46 and the bolt 40 of the outer edge to pass therethrough.
  • a through-hole and a through-hole through which the bolt 43 in the central portion passes are formed.
  • the discharge valve 12 is formed of a metal plate, A suction port having a lead portion for opening and closing 46, a suction port constituting a part of the suction passage 45, a through hole for passing the bolt 40 of the outer edge portion, and a through hole for passing the bolt 43 of the central portion. Is drilled! / Puru.
  • the gaskets 13, 14, and 15 are members in which rubber layers are coated on both surfaces of a metal plate.
  • the gaskets 13, 14 disposed between the cylinder block 2 and the rear head have A communication hole that communicates the suction passage 45 and the discharge passage 46, a through hole that penetrates the bolt 40 at the outer edge, and an opening that penetrates the bolt 43 at the central portion are respectively formed.
  • a retainer 42 that restricts the operation of the lead portion of the discharge valve 12 in the opening direction is disposed in the opening at the center.
  • the gasket 15 disposed between the cylinder block 2 and the front head 3 is provided with a hole having the same diameter as the crank chamber 27 and a through hole through which the outer edge bolt 40 is passed. .
  • the front head 3, the cylinder block 2, the valve plate 10, and the rear head 4 constitute a housing member, and a gasket 13 serving as a seal member is provided between these housing members. , 14, 15 are sealed. If necessary, a predetermined sealing member may be provided between the valve plate 10 and the suction valve 11 and between the valve plate 10 and the discharge valve 12.
  • the surface pressure of the seal members (gaskets 13, 14, 15) generated by the fastening action of the bolt 40 as a fastening member is set as shown in FIG. Yes.
  • the surface pressure is the pressure applied to the pressure contact surface of the seal member (gasket 13, 14, 15) with the adjacent housing member (front head 3, cylinder block 2, rear block 4). It can be measured using It is necessary to obtain the relationship between the pressure measured by the pressure-sensitive paper and the tightening force of the fastening member (bolt 40) at that time through experiments or the like in advance.
  • the relationship between the surface pressure of the seal member and the seal limit pressure of the seal member (the limit pressure at which refrigerant leakage can be prevented) (curve X in FIG.
  • Pa indicates the maximum operating pressure of the compressor 1
  • Pb indicates the burst pressure of the compressor 1
  • P1 indicates the surface pressure when the seal limit pressure of the seal member becomes equal to the maximum operating pressure Pa.
  • the maximum operating pressure Pa is preferably within a range of 15-20 MPa. If an abnormally high pressure prevention means such as a relief valve is provided, the operating pressure It becomes.
  • the surface pressure of the seal member is set within a range R1 that is 2 to 5 times the surface pressure P1, and more preferably, within a range R2 that is 3 to 4 times the surface pressure P1.
  • the size or number of the fastening members can be made smaller than before, so that the compressor 1 can be made smaller and lighter.
  • the outer diameter of the compressor 1 can be reduced by about 10 mm and the weight can be reduced by 15 to 20%.
  • FIG. 3 shows a configuration of a gasket 13 disposed between the cylinder block 2 and the suction valve 11.
  • the gasket 13 is formed at a position facing each of the bores 20.
  • a communication hole 50 for communicating the compressor 21 with the suction passage 45 and the discharge passage 46, a bead portion 55 provided so as to surround the communication hole 50, and a bolt 40 of the outer edge portion are penetrated.
  • the above configuration is an example of the configuration of the gasket 13, and the shapes and numbers of the communication holes 50, the through holes 51, 52, and the bead portions 55, 56, 57, or the presence or absence of these should be changed as appropriate. And does not limit the present invention.
  • the bead portions 55, 56, and 57 may all have the shape of a force half bead, which is a full bead! (See FIG. 9).
  • FIG. 4 shows a cross section A—A of the gasket 13 having the above configuration.
  • the gasket 13 is formed by covering both surfaces of a metal plate 58 with rubber layers 59a and 59b.
  • Each of the bead portions 55, 56, 57 has a convex shape protruding toward the cylinder block 2 side.
  • the thickness t of the metal plate 58 is in the range of 0.2-0.8 mm, and the height of each bead portion 55, 56, 57 is in the range of 0.1-0.4 mm. The height increases as the distance from the through hole 51 through which the bolt 40 penetrates increases.
  • the height of the bead portion 56 formed around the through-hole 52 is hi
  • the height of the bead portion 55 formed around the communication hole 50 is h2
  • the height of the bead portion 55 near the outer edge of the gasket 13 is h2.
  • the bolt 40 which is a fastening member, Sealing properties can be reliably ensured even in a distant portion.
  • a bead linear pressure indicating an acting force per unit distance applied to the bead portions 55, 56, 57 at the time of fastening is within a range of 10 to 25 times the maximum working pressure Pa. .
  • the bead linear pressure is a value calculated by (total tightening force by bolt 40) Z (total distance of center lines of bead portions 55, 56, and 57).
  • the center lines of the bead portions 55, 56 and 57 are shown as L1 and L10 in FIG. 5, and the distance between the center lines L1 and L8 of the eight bead portions 55 (only L13 and L13 are shown in FIG. 5).
  • the sum (LI + L2 +... + L10) of the sum, the distance of the center line L9 of the bead portion 56, and the distance of the center line L10 of the bead portion 57 is the total distance.
  • the diameter Dc of the pitch circle C formed by connecting the intervals of the eight bolts 40 is within 110 mm! / ,. If the diameter Dc is too large, the central portion of the valve plate 10 or the like is likely to float due to the internal pressure.
  • the present invention may be a compressor 60 having a structure shown in FIG.
  • the housing member of the compressor 60 includes a cylinder block 61, a front head 62 having a size and shape that seals one end surface of the cylinder block 61 and wraps around the cylinder block 61, and the cylinder block 61.
  • a fastening member (or means) formed on an outer wall near an end of the front head 62 on the rear head 63 side;
  • a ring nut 70 having a threaded portion 66 for screwing with the screw 65 and a flange 67 for locking the peripheral edge of the rear head 63, and a bolt for fixing the cylinder block 61 to the rear head 63 (see FIG. (Not shown)).
  • a gasket 71 is sandwiched between the front head 62 and the rear head 63, and a gasket 72, a suction valve 73, and a valve plate 73 are arranged between the gasket 71 and the cylinder block 61 in order from the cylinder block 61 side. 74, the discharge valve 75 is clamped.
  • the surface pressure of the gasket 71 can be adjusted by the fastening force of the ring nut 70, and the surface pressure of the gasket 72 can be adjusted by the fastening force of the bolt.
  • the present invention may be a compressor 80 having a structure shown in FIG.
  • the housing member of the compressor 80 seals the cylinder block 81 and one end surface of the cylinder block 81.
  • a rear head 83 that seals the other end surface of the cylinder block 81, and has a fastening member (or means) of the front head 82.
  • a bolt (not shown) for fixing the cylinder block 81 to the rear head 83.
  • a gasket 91 is sandwiched between the front head 82 and the rear head 83, and a gasket 92, a suction valve 93, and a valve plate 94 are arranged between the gasket 91 and the cylinder block 81 in this order from the cylinder block 81 side. , The discharge valve 95 is clamped.
  • the surface pressure of the gasket 91 can be adjusted by the fastening force of the threaded portions 85 and 86, and the surface pressure of the gasket 92 can be adjusted by the fastening force of the bolt.
  • the present invention it is possible to prevent the size and the number of the fastening members from being unnecessarily increased by optimizing the surface pressure of the seal member sandwiched between the plurality of housing members. Therefore, it is possible to provide a compressor in which leakage of the refrigerant is prevented, safety is ensured, and downsizing is realized at the same time.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Abstract

Un compresseur dans lequel une pression de contact d'un élément de joint maintenu entre des éléments de logement est appropriée pour éviter que la taille et le nombre d'éléments de fixation n'augmentent inutilement, et en même temps, la fuite d'un réfrigérant est évitée, la sécurité est assurée, et le compresseur est réduit en taille. Un compresseur possède au moins deux éléments de logement pour recevoir un mécanisme de compression, un élément de joint maintenu entre les éléments de logement, et des éléments de fixation pour fixer intégralement les logements et l'élément de joint. Une pression de contact agissant sur l'élément de joint produite par fixation par les éléments de fixation est réglée pour qu'une pression limite de joint de l'élément de joint soit plus élevée que la pression de travail maximale du compresseur et plus faible que la pression de rupture du compresseur.
PCT/JP2005/003586 2004-06-03 2005-03-03 Compresseur WO2005119061A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP05719890A EP1775471A4 (fr) 2004-06-03 2005-03-03 Compresseur

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2004-165728 2004-06-03
JP2004165728A JP2005344625A (ja) 2004-06-03 2004-06-03 圧縮機

Publications (1)

Publication Number Publication Date
WO2005119061A1 true WO2005119061A1 (fr) 2005-12-15

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2005/003586 WO2005119061A1 (fr) 2004-06-03 2005-03-03 Compresseur

Country Status (3)

Country Link
EP (2) EP1775471A4 (fr)
JP (1) JP2005344625A (fr)
WO (1) WO2005119061A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010065600A (ja) * 2008-09-10 2010-03-25 Sanden Corp 流体機械

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JP2008064035A (ja) * 2006-09-07 2008-03-21 Toyota Industries Corp ピストン式圧縮機
JP4922729B2 (ja) * 2006-10-20 2012-04-25 三洋電機株式会社 圧縮機及びその製造方法
GB2477516A (en) 2010-02-04 2011-08-10 Agilent Technologies Inc A seal for an HPLC column

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JPS5372209A (en) * 1976-12-10 1978-06-27 Toyoda Autom Loom Works Ltd Compressor
JPS6372367U (fr) * 1986-10-30 1988-05-14
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JPH08296559A (ja) * 1995-04-21 1996-11-12 Iwata Air Compressor Mfg Co Ltd 往復空気圧縮機
JPH09137774A (ja) * 1995-11-15 1997-05-27 Toyota Autom Loom Works Ltd 圧縮機
JPH09264254A (ja) * 1996-01-26 1997-10-07 Toyota Autom Loom Works Ltd ピストン式圧縮機及びその組付方法
JPH11343974A (ja) * 1998-05-29 1999-12-14 Toyota Autom Loom Works Ltd 往復動型圧縮機
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JP2003065232A (ja) * 2001-08-28 2003-03-05 Toyota Industries Corp 圧縮機のシール構造
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JPS5159904U (fr) * 1974-11-05 1976-05-12
JPS5372209A (en) * 1976-12-10 1978-06-27 Toyoda Autom Loom Works Ltd Compressor
JPS6372367U (fr) * 1986-10-30 1988-05-14
JPH0625677U (ja) * 1988-06-24 1994-04-08 ビー・エス・アンド・ビー・セイフテイ・システムズ・インコーポレイテツド 複合破壊ディスクアセンブリ及びその破壊部材
JPH08296559A (ja) * 1995-04-21 1996-11-12 Iwata Air Compressor Mfg Co Ltd 往復空気圧縮機
JPH09137774A (ja) * 1995-11-15 1997-05-27 Toyota Autom Loom Works Ltd 圧縮機
JPH09264254A (ja) * 1996-01-26 1997-10-07 Toyota Autom Loom Works Ltd ピストン式圧縮機及びその組付方法
JPH11343974A (ja) * 1998-05-29 1999-12-14 Toyota Autom Loom Works Ltd 往復動型圧縮機
JP2002070739A (ja) * 2000-08-30 2002-03-08 Zexel Valeo Climate Control Corp 往復式冷媒圧縮機
JP2002364539A (ja) * 2001-06-07 2002-12-18 Sanden Corp 圧縮機
JP2003065232A (ja) * 2001-08-28 2003-03-05 Toyota Industries Corp 圧縮機のシール構造
JP2003293950A (ja) * 2002-04-01 2003-10-15 Sanden Corp 圧縮機のシール構造

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010065600A (ja) * 2008-09-10 2010-03-25 Sanden Corp 流体機械

Also Published As

Publication number Publication date
EP1775471A4 (fr) 2008-07-30
JP2005344625A (ja) 2005-12-15
EP1995461A1 (fr) 2008-11-26
EP1775471A1 (fr) 2007-04-18

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