EP1629198B1 - Hermetic compressor - Google Patents

Hermetic compressor Download PDF

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Publication number
EP1629198B1
EP1629198B1 EP05741280A EP05741280A EP1629198B1 EP 1629198 B1 EP1629198 B1 EP 1629198B1 EP 05741280 A EP05741280 A EP 05741280A EP 05741280 A EP05741280 A EP 05741280A EP 1629198 B1 EP1629198 B1 EP 1629198B1
Authority
EP
European Patent Office
Prior art keywords
piston
cylinder
outer circumferential
hermetic compressor
circumferential surface
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 - Fee Related
Application number
EP05741280A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1629198A1 (en
Inventor
Ikutomo Umeoka
Makoto Katayama
Junichiro Yabiki
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.)
Panasonic Corp
Original Assignee
Matsushita Electric Industrial Co Ltd
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
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First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=34968133&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP1629198(B1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Matsushita Electric Industrial Co Ltd filed Critical Matsushita Electric Industrial Co Ltd
Publication of EP1629198A1 publication Critical patent/EP1629198A1/en
Application granted granted Critical
Publication of EP1629198B1 publication Critical patent/EP1629198B1/en
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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
    • F04B39/02—Lubrication
    • F04B39/0223—Lubrication characterised by the compressor type
    • F04B39/023—Hermetic compressors
    • 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
    • F04B39/0005—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 adaptations of pistons
    • 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
    • F04B39/0005—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 adaptations of pistons
    • F04B39/0022—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 adaptations of pistons piston rods
    • 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
    • F04B39/0094—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 crankshaft
    • 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
    • F04B39/122—Cylinder block
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B31/00—Compressor arrangements
    • F25B31/02—Compressor arrangements of motor-compressor units
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type
    • F05B2210/14—Refrigerants with particular properties, e.g. HFC-134a
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S417/00—Pumps
    • Y10S417/902—Hermetically sealed motor pump unit

Definitions

  • the present invention relates to a hermetic compressor used in a refrigerating cycle of a Refrigerator Freezer, etc.
  • Fig. 7 is a longitudinal sectional view showing a general hermetic compressor described in US Patent No. 5,228,843 ; and Fig. 8 is a perspective view showing a piston described in International Publication WO 02/02944 .
  • hermetic housing 1 houses motor element 4 consisting of stator 2 having winding portion 2a and rotor 3, and compression element 5 driven by motor element 4. Moreover, in the lower part of hermetic housing 1, oil 6 is contained.
  • Crankshaft 10 includes main shaft 11 to which rotor 3 is press-fitted and fixed and eccentric shaft 12 formed eccentric to main shaft 11. Inside main shaft 11, oil pump 13 is housed and an opening portion of oil pump 13 is disposed in oil 6.
  • Block 20 provided at the upper side of motor element 4 has cylinder 21 having a substantially cylindrical shape and bearing 22 for supporting main shaft 11. Piston 30 is inserted into cylinder 21 of block 20 capable of reciprocating sliding and coupled to eccentric shaft 12 via connecting means 41.
  • Piston 30 includes top surface 31, skirt surface 32 and outer circumferential surface 33. Furthermore, outer circumferential surface 33 includes seal surface 34, two guide surfaces 35 and removed portions 36.
  • seal surface 34 is a surface in the circumferential direction, which is formed so as to be brought into close contact with the inner circumferential surface of cylinder 21.
  • Guide surface 35 is formed so as to be brought into close contact with a part of the inner circumferential surface of cylinder 21 and extends substantially in parallel in the direction of the movement of piston 30.
  • Removed portion 36 is a concave portion that is not brought into close contact with the inner circumferential surface of cylinder 21.
  • an angle made by lines respectively connecting between central axis 37 of cylindrical piston 30 and two boundary edges 35a and 35b of guide surface 35 in the direction of the radius of piston 30 is generally 40° or less and preferably 30° or less.
  • piston 30 reciprocates in the horizontal direction in the drawing. In the vicinity of the bottom dead center, a part of the skirt side of piston 30 is protruded to the outside of cylinder 21. From this state, when piston 30 enters cylinder 21, that it is to say, when piston 30 moves in the right direction of Fig. 7, piston 30 is guided by guide surface 35 and thereby can enter cylinder 21 smoothly.
  • piston 30 is likely to be inclined in the vertical direction.
  • top surface 31 of piston 30 undergoes compression load of a refrigerant gas and furthermore, crankshaft 10 is pressed in the direction that is not the direction of a piston (downward direction in Fig. 7) via connecting means 41, and thereby the inclination of piston 30 in the vertical direction is likely to be increased.
  • a hermetic compressor according to the preamble of either claim 1 or 8 is known from prior art JP 2004 027969 .
  • Prior art US 5,860,395 discloses an apparatus and a method of cooling a piston by passing a stream of lubricating oil against the underside of the piston and more specifically by providing an enclosed reservoir space between the engine cylinder wall and the side wall of the piston formed by a depression in the piston and providing a passageway in the piston aimed to direct oil to a desired location on the underface of the piston.
  • a hermetic compressor as defined in claim 1 or claim 8 is provided.
  • the inventive compressor of claim 1 makes it possible to reduce sliding loss due to the reduction in a sliding area. Furthermore, by the sliding surface provided in the parallel and in the perpendicular direction of the piston pin, the inclination of the piston with respect to the cylinder is suppressed, thus suppressing the leakage of refrigerant. Furthermore, by supplying the sliding portion with oil through the under cut, the sealing property can be improved. With the above-mentioned effect, a hermetic compressor with high efficiency can be provided. Preferred embodiments of the inventive hermetic compressors are defined in the dependent claims.
  • Fig. 1 is a longitudinal sectional view showing a hermetic compressor in an exemplary embodiment of the present invention
  • Fig. 2 is an enlarged sectional view showing an element around a piston
  • Fig. 3 is a front view showing a piston
  • Fig. 4 is a sectional view of a part along line 4-4 of FIG. 3
  • Fig. 5 is an enlarged sectional view showing an end face of an under cut of a piston
  • Fig. 6 is an enlarged sectional view showing a tip of a piston.
  • housing 101 houses motor element 104 and compression mechanism 105 driven by motor element 104, and moreover contains oil 106.
  • Motor element 104 includes stator 102 and rotor 103, and enables inverter driving by using a control circuit, etc. controlled at plural operational frequencies including operation frequency that is not higher than power supply frequency.
  • the hermetic compressor of this exemplary embodiment uses hydrocarbon-based refrigerant Isobutane (or R600a).
  • Refrigerant R600a is a natural refrigerant with low global warming potential.
  • Crankshaft 110 includes main shaft 111 and eccentric shaft 112 and is disposed in substantially the vertical direction.
  • rotor 103 is press-fitted and fixed to main shaft 111 and eccentric shaft 112 is disposed eccentric to main shaft 111.
  • Oil supplying structure 120 includes centrifugal pump 122, vertical hole 123, and lateral hole 124.
  • centrifugal pump 122 formed inside of crankshaft 110 is opened in oil 106 with another end connected to viscosity pump 121.
  • One end of vertical hole 123 is connected to one end of viscosity pump 121 with another end opened in space inside housing 101.
  • Block 130 includes substantially cylindrical cylinder 131, main bearing 132 for supporting main shaft 111 and collision-portion 134 provided on the upper side of cylinder 131.
  • Cylinder 131 includes notch 135 provided on the upper side of the edge at the side of crankshaft 110.
  • Piston 140 is inserted into cylinder 131 capable of reciprocating sliding.
  • Piston 140 has piston pin hole 141 formed in parallel to the center axis of eccentric shaft 112.
  • piston pin hole 141 formed in parallel to the center axis of eccentric shaft 112.
  • piston pin 142 is fitted into piston pin hole 141.
  • Piston pin 142 is fixed to piston 140 by hollow cylindrical lock pin 143.
  • Piston pin 142 is connected to eccentric shaft 112 via connecting rod 146.
  • Hollow part 144 of piston pin 142 communicates with space inside housing 101 via vent hole 145.
  • Fig. 4 is a sectional view of a part of piston 140 taken along line 4-4 of FIG. 3, showing a state of cylindrical central axis 170 of the piston seen from the left direction.
  • under cut 153 is formed excluding a region with a predetermined width in parallel direction 147 with respect to the axis of piston pin 142 and a region with a predetermined width in the perpendicular direction 148 with respect to the axis of piston pin 142.
  • Total area of under cut 153 is not less than one half of an area of outer circumferential surface 150 of the piston.
  • angle ⁇ made by edge 180 of under cut 153 and outer circumferential surface 150 of the piston is set to be an acute angle.
  • the right end portion of piston 140 is provided with circumferentially formed land 190, on which under cut 153 is not formed, in a predetermined width from top surface 151.
  • outer circumferential surface 150 that does not belong to any of circumferentially formed land 190 and under cut 153 is referred to as axially formed land 192.
  • axially formed land 192 is provided in parallel to cylindrical central axis 170 and extends from circumferentially formed land 190 and reaches skirt surface 152.
  • axially formed lands 192 are formed in a predetermined width on an outer circumferential surfaces at 0°, 90°, 180° and 270° with respect to the cylinder axis as a center.
  • the width of axially formed land 192 is set so that angle ⁇ made by two lines linking between cylindrical central axis 170 of piston 140 and two boundary portions of axially formed land 192 in the direction of radius of the piston is set to 40° or less and preferably 30° or less.
  • upper sliding surface 154 and lower sliding surface 155 are provided in the vertical direction and side sliding surface 160 is provided in the direction of the side surface. These correspond to one or both of circumferentially formed land 190 and axially formed land 192.
  • annular grooves 191 are provided in the outer circumferential direction of the piston. Furthermore, on outer circumferential surface 150 of the piston, at both end portions of top surface 151 side and skirt surface 152 side, minute tapers 201 and 202 are provided.
  • centrifugal pump 122 By the rotation of crankshaft 110, centrifugal pump 122 is rotated so as to generate centrifugal force. By the centrifugal force, oil 106 moves upwardly in centrifugal pump 122 to reach viscosity pump 121. Oil 106 which reached viscosity pump 121 further moves upwardly in viscosity pump 121 and are scattered in housing 101 via vertical hole 123 and lateral hole 124.
  • oil 106 entering under cut 153 is accumulated in the vicinity of edge 180 of under cut 153.
  • oil 106 is carried to an inner part of cylinder 131.
  • oil 106 is drawn into between cylinder 131 and outer circumferential surface 150 of the piston so as to efficiently lubricate the vicinity of circumferentially formed land 190.
  • angle ⁇ made by edge 180 and outer circumferential surface 150 of the piton is made to be an acute angle, in accordance with the movement of piston 140, oil 106 is efficiently drawn into between cylinder 131 and outer circumferential surface 150 of the piston.
  • under cut 153 since four under cuts 153 are provided in the axial direction of piston 140, through under cut 153, oil 106 is supplied to the wide range of outer circumferential surface 150 of the piston.
  • crankshaft 110 is pressed toward the opposite direction to the piston and may be inclined.
  • piston 140 may be inclined in the vertical direction with respect to cylinder 131, thereby forming a part in which space between cylinder 131 and outer circumferential surface 150 of the piston may be broadened.
  • leakage of a refrigerant gas from the part may be accelerated.
  • the inclination of piston 140 may deteriorate the lubricant state between piston 140 and cylinder 131 and may increase a sliding noise.
  • the sliding loss generated when piston 140 reciprocates in cylinder 131 is in a state of fluid lubricant in which the loss is reduced in proportion to reduction of the sliding area.
  • the area of under cut 153 is set to not less than one half of the area of outer circumferential surface 150 of the piston, sliding loss of piston 140 is about one half.
  • under cut 153 always communicates with skirt surface 152.
  • another configuration mentioned below can provide the same effect because a high pressure gas is released into space inside housing 101. That is to say, without allowing under cut 153 to communicate with skirt surface 152, under cut 153 may be allowed to communicate with space inside housing 101 only in the vicinity of the bottom dead center, or under cut 153 may be allowed to communicate with piston pin hole 141.
  • joined oil 106 and the refrigerant gas are expanded and contracted repeatedly, so that the pressure is reduced, whereby a so-called labyrinth seal effect is generated and the sealing property with respect to the leakage of refrigerant from cylinder 131 is improved. From the effect mentioned above, oil supply to the circumferentially formed land is further promoted, the lubricant property can be more improved, and furthermore, high efficiency can be achieved.
  • minute tapers 201 and 202 provided at the end portions both at top surface 151 side and skirt surface 152 side of piston 140 is described.
  • oil 106 moves around circumferentially formed land 190 of piston 140 so as to improve the lubricant property of piston 140 and to also improve the sealing property.
  • piston 140 moves from the top dead center to the bottom dead center, by the wedge effect of minute taper 202 at the skirt surface 152 side, oil 106 enters minute taper 202 so as to form an oil film and lubricant property and sealing property are improved. That is to say, the presence of minute tapers 201 and 202 suppresses the leakage of refrigerant and reduces the sliding loss. Furthermore, high efficiency can be achieved.
  • the density of refrigerant R600a used in the hermetic compressor of this exemplary embodiment is smaller than the density of refrigerant R134a (1,1,1,2-tetrafluoroethane), which has been conventionally used in refrigerators. Therefore, when refrigerating ability that is the same as in a hermetic compressor using refrigerant R134a is intended to be obtained by using refrigerant R600a, cylinder capacity is increased and the outer diameter of piston 140 may be increased. Necessarily, the flow passage area for a refrigerant is increased and the amount of refrigerant leaking into housing 101 from cylinder 131 is likely to increase. However, in the hermetic compressor of this exemplary embodiment, since the inclination of piston 140 with respect to cylinder 131 can be suppressed, the efficiency can be improved.
  • crankshaft 110 may be provided with secondary axis which is provided on the same axis as main shaft 111 and opposed to main shaft with eccentric shaft 112 therebetween, and at the same time, a secondary bearing for supporting the secondary axis may be provided.
  • crankshaft 110 since crankshaft 110 is supported at both ends with eccentric shaft 112 sandwiched therebetween, resulting in effectively suppressing the inclination of piston 140 in the vertical direction with respect to cylinder 131. Consequently, since the behavior of piston 140 becomes stable, sliding loss can be reduced and the increase in noise can be suppressed, it is possible to realize a hermetic compressor with high efficiency and low noise property.
  • a hermetic compressor according to the present invention yields high productivity, and can increase efficiency and reliability, it can be widely applied to an application of a hermetic compressor of, for example, an air conditioner, a vending machine, and the like.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Compressor (AREA)
EP05741280A 2004-05-28 2005-05-11 Hermetic compressor Expired - Fee Related EP1629198B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2004159165A JP4337635B2 (ja) 2004-05-28 2004-05-28 密閉型圧縮機
PCT/JP2005/009006 WO2005116450A1 (en) 2004-05-28 2005-05-11 Hermetic compressor

Publications (2)

Publication Number Publication Date
EP1629198A1 EP1629198A1 (en) 2006-03-01
EP1629198B1 true EP1629198B1 (en) 2007-08-29

Family

ID=34968133

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05741280A Expired - Fee Related EP1629198B1 (en) 2004-05-28 2005-05-11 Hermetic compressor

Country Status (7)

Country Link
US (1) US20060257274A1 (ko)
EP (1) EP1629198B1 (ko)
JP (1) JP4337635B2 (ko)
KR (1) KR100701527B1 (ko)
CN (1) CN100430598C (ko)
DE (1) DE602005002205T2 (ko)
WO (1) WO2005116450A1 (ko)

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JP4760003B2 (ja) * 2004-12-14 2011-08-31 パナソニック株式会社 密閉型圧縮機
US9261104B2 (en) * 2005-09-19 2016-02-16 Ingersoll-Rand Company Air blower for a motor-driven compressor
BRPI0603568A (pt) * 2006-08-16 2008-04-08 Whirlpool Sa arranjo de montagem de pistão e haste de acionamento para compressor alternativo
JP4915205B2 (ja) * 2006-10-19 2012-04-11 パナソニック株式会社 圧縮機
US20100221129A1 (en) * 2007-02-23 2010-09-02 Seigo Yanase Hermetic compressor
AT10065U1 (de) * 2007-08-28 2008-08-15 Acc Austria Gmbh Kältemittelkompressor
US8702405B2 (en) * 2007-11-17 2014-04-22 Brian Leonard Verrilli Twisting translational displacement pump cartridge
WO2009088179A2 (en) * 2008-01-10 2009-07-16 Lg Electronics Inc. Reciprocating compressor
ATE551529T1 (de) * 2008-05-12 2012-04-15 Panasonic Corp Hermetischer verdichter
JP5753983B2 (ja) * 2009-10-27 2015-07-22 パナソニックＩｐマネジメント株式会社 密閉型圧縮機
JP5810273B2 (ja) * 2010-10-21 2015-11-11 パナソニックＩｐマネジメント株式会社 密閉型圧縮機および冷凍装置
JP2012197769A (ja) * 2011-03-23 2012-10-18 Panasonic Corp 密閉型圧縮機
BRPI1101929A2 (pt) * 2011-04-26 2015-07-14 Whirlpool Sa Biela para compressores de refrigeração
JP5492917B2 (ja) * 2012-02-01 2014-05-14 株式会社豊田自動織機 可変容量型斜板式圧縮機
WO2014103320A1 (ja) * 2012-12-27 2014-07-03 パナソニック株式会社 密閉型圧縮機及びそれを備える冷凍装置
WO2014115530A1 (ja) * 2013-01-22 2014-07-31 パナソニック株式会社 密閉型圧縮機および冷蔵庫
US10208743B2 (en) * 2016-10-07 2019-02-19 Westinghouse Air Brake Technologies Corporation Piston cylinder arrangement for an oil free compressor having cooling passageways and method of cooling wrist pin bearing surface
KR102351707B1 (ko) * 2017-06-20 2022-01-17 엘지전자 주식회사 왕복동식 압축기의 피스톤 및 그 제조방법
JP2020033873A (ja) * 2018-08-27 2020-03-05 日立グローバルライフソリューションズ株式会社 密閉形圧縮機及びこれを有する冷蔵庫

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Also Published As

Publication number Publication date
CN1771394A (zh) 2006-05-10
KR100701527B1 (ko) 2007-03-29
US20060257274A1 (en) 2006-11-16
JP2005337160A (ja) 2005-12-08
KR20060038921A (ko) 2006-05-04
DE602005002205D1 (de) 2007-10-11
WO2005116450A1 (en) 2005-12-08
CN100430598C (zh) 2008-11-05
JP4337635B2 (ja) 2009-09-30
DE602005002205T2 (de) 2007-12-20
EP1629198A1 (en) 2006-03-01

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