EP1923648B1 - Cooling/heating apparatus - Google Patents

Cooling/heating apparatus Download PDF

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Publication number
EP1923648B1
EP1923648B1 EP20070119518 EP07119518A EP1923648B1 EP 1923648 B1 EP1923648 B1 EP 1923648B1 EP 20070119518 EP20070119518 EP 20070119518 EP 07119518 A EP07119518 A EP 07119518A EP 1923648 B1 EP1923648 B1 EP 1923648B1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
refrigerant
housing
cooling
compressor
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
EP20070119518
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1923648A3 (en
EP1923648A2 (en
Inventor
Takeshi Sakaguchi
Yukio Yamaguchi
Makoto Kimura
Mototaka Tajika
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.)
Sanden Corp
Original Assignee
Sanden Corp
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 Sanden Corp filed Critical Sanden Corp
Publication of EP1923648A2 publication Critical patent/EP1923648A2/en
Publication of EP1923648A3 publication Critical patent/EP1923648A3/en
Application granted granted Critical
Publication of EP1923648B1 publication Critical patent/EP1923648B1/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
    • 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
    • F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
    • F25B29/003—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously of the compression type system
    • 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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D31/00—Other cooling or freezing apparatus
    • F25D31/005—Combined cooling and heating devices
    • 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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • 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
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel

Definitions

  • the present invention relates to a cooling/heating apparatus which has a plurality of housings and cools or heats the respective housings.
  • cooling/heating apparatus comprising a plurality of housings for housing goods and a refrigerant circuit including a first heat exchanger provided in each housing, a second heat exchanger provided outside the housings and a compressor. That cooling/heating apparatus is designed to cool or heat goods housed in each housing by each first heat exchanger which exchanges heat of a refrigerant and air in each housing.
  • the housing is heated by dissipating heat from the refrigerant to be discharged from the compressor.
  • the refrigerant in a low temperature flowing out of the first heat exchanger provided in the housing to be cooled is heat-exchanged, in the internal heat exchanger with the refrigerant having been heat-exchanged with the outside air in the second heat exchanger and dissipated heat, thus absorbing heat.
  • the temperature of the refrigerant sucked into by the compressor is approximately the same as the temperature of the outside air and a comparatively low temperature.
  • An object of the present invention is to provide a cooling/heating apparatus which allows improvement in heating efficiency in a first heat exchanger provided in a housing to be heated.
  • the present invention comprises: a plurality of housings housing goods; a first heat exchanger provided in each housing and respectively cooling or heating the housed goods; a second heat exchanger provided outside the housings; a compressor provided outside the housings; a third heat exchanger exchanging heat of a refrigerant flowing out of the first heat exchanger provided in each housing heating the goods of the plurality of housings with heat of the refrigerant sucked into by the compressor; and a fourth heat exchanger exchanging heat of the refrigerant circulating from the second heat exchanger toward the first heat exchanger provided in each housing cooling the goods with heat of the refrigerant flowing out of the first heat exchanger provided in each housing cooling the goods.
  • An automatic vending machine as a cooling/heating apparatus of the present invention comprises an automatic vending machine body 10 having opening in the front face and an outer door 20 opening and closing the front face of the automatic vending machine body 10.
  • the automatic vending machine body 10 has the inside partitioned into an upper portion and a lower portion. Thereby, the upper portion is provided with a product housing 30 and the lower portion is provided with a machine room 40.
  • the upper side, the rear side, the bottom side and the both of the left and the right sides of the product housing 30 are formed of a heat insulating material 31.
  • the front side of the product housing 30 is designed to be opened and closed by a heat insulating inner door 32.
  • the product housing 30 is partitioned into right-and-left blocks with a heat insulating partition plate 33 and is provided with a first housing 30a, a second housing 30b and a third housing 30c.
  • Each of the first housing 30a, the second housing 30b and the third housing 30c is provided with a plurality of product housing columns 34 capable of stacking and housing products vertically and of taking out the products one by one from the lower end side.
  • the first housing 30a is provided with a first evaporator 35a as a first heat exchanger for cooling the products housed in the first housing 30a; a first radiator 36a as a first heat exchanger for heating the products housed in the first housing 30a; a first fan 37a for distributing the air to be heat-exchanged with a refrigerant circulating through the first evaporator 35a or the first radiator 36a; and a first electric heater 38a for compensating for the heat amount falling short at the occasion of heating the product with the first radiator 36a.
  • the second housing 30b is provided with a second evaporator 35b as a first heat exchanger for cooling the products housed in the second housing 30b; a second radiator 36b as a first heat exchanger for heating the products housed in the second housing 30b; a second fan 37b for distributing the air to be heat-exchanged with the refrigerant circulating through the second evaporator 35b or the second radiator 36b; and a second electric heater 38b for compensating for the heat amount falling short at the occasion of heating the product with the second radiator 36b.
  • the third housing 30c is provided with a third evaporator 35c as a first heat exchanger for cooling the products housed in the third housing 30c and a third fan 37c for distributing the air to be heat-exchanged with the refrigerant circulating through the third evaporator 35c.
  • cooling and heating of the housed products can be switched in the first housing 30a and the second housing 30b.
  • the third housing 30c is arranged only to cool the products.
  • the machine room 40 is provided with an intake port and an exhaust port so as to distribute the outside air inside thereof.
  • the machine room 40 is provided inside thereof with a compressor 41 for compressing the refrigerant; a third radiator 42 as a second heat exchanger for releasing waste heat to the air being distributed inside the machine room 40; and a machine room fan 43 for distributing the outside air inside the machine room 40.
  • the compressor 41 is a two-stage compressor including a lower stage side compressing part 41a and a higher stage side compressing part 41b, compresses the sucked into refrigerant in the lower stage side compressing part 41a and compresses and discharges the refrigerant compressed in the lower stage side compressing part 41a further in the higher stage side compressing part 41b.
  • the two-stage compressor compresses a refrigerant in two stages and therefore can deal with high operation pressure and high differential pressure, and is applied to, for example, a refrigerant circuit which uses carbon dioxide and the like as a refrigerant.
  • a refrigerant circuit 50 as illustrated in FIG. 4 is configured in the product housing 30 and the machine room 40. Carbon dioxide being a natural refrigerant and being in a supercritical state on the high-pressure side is used as a refrigerant.
  • the refrigerant circuit 50 includes: the first evaporator 35a; the second evaporator 35b; the third evaporator 35c; the first radiator 36a; the second radiator 36b; the compressor 41; the third radiator 42; a first internal heat exchanger 51 as a fourth heat exchanger for exchanging heat of the refrigerant flowing out of the third radiator 42 with heat of the refrigerant flowing out of the first evaporator 35a, the second evaporator 15b and the third evaporator 15c; a second internal heat exchanger 52 as a third heat exchanger for exchanging heat of the refrigerant sucked into by the compressor 41 with heat of the refrigerant flowing out of the first radiator 36a and the second radiator 36b; first to third expansion valves 53a, 53b and 53c as first decompressor and a fourth expansion valve 53d as second decompressor for decompressing the refrigerant; and first to sixth electromagnetic valves 54a, 54b, 54c, 54d, 54e and 54f for opening
  • a refrigerant discharge side of the compressor 41 is connected to refrigerant inflow sides of the first radiator 36a and the second radiator 36b in parallel.
  • Flow paths on the refrigerant inflow sides of the first radiator 36a and the second radiator 36b are provided with the first electromagnetic valve 54a and the second electromagnetic valve 54b respectively.
  • Refrigerant outflow sides of the first radiator 36a and the second radiator 36b are connected to a high pressure refrigerant inflow side of the second internal heat exchanger 52 in parallel.
  • a high pressure refrigerant outflow side of the second internal heat exchanger 52 is connected to a refrigerant inflow side of the third radiator 42.
  • the refrigerant discharge side of the compressor 41 is connected to a flow path on the refrigerant inflow side of the third radiator 42 through the third electromagnetic valve 54c.
  • a refrigerant outflow side of the third radiator 42 is connected to a high pressure refrigerant inflow side of the first internal heat exchanger 51.
  • a high pressure refrigerant outflow side of the first internal heat exchanger 51 is connected to the first evaporator 35a, the second evaporator 35b and the third evaporator 35c in parallel.
  • Flow paths on refrigerant inflow sides of the first evaporator 35a, the second evaporator 35b and the third evaporator 35c are respectively provided with the first expansion valve 53a, the second expansion valve 53b and the third expansion valve 53c.
  • Flow paths on upstream sides of the first expansion valve 53a, the second expansion valve 53b and the third expansion valve 53c are respectively provided with the fourth electromagnetic valve 54d, the fifth electromagnetic valve 54e and the sixth electromagnetic valve 54f.
  • a flow path between the high pressure refrigerant outflow side of the first internal heat exchanger 51 and the fourth, fifth, and sixth electromagnetic valves 54d, 54e and 54f is provided with the fourth expansion valve 53d.
  • Refrigerant outflow sides of the first evaporator 35a, the second evaporator 35b and the third evaporator 35c are connected to a low pressure refrigerant inflow side of the first internal heat exchanger 51.
  • a low pressure refrigerant outflow side of the first internal heat exchanger 51 is connected to a low pressure refrigerant inflow side of the second internal heat exchanger 52.
  • a low pressure refrigerant outflow side of the second internal heat exchanger 52 is connected to a refrigerant absorption side of the compressor 41.
  • the first internal heat exchanger 51 and the second internal heat exchanger 52 are respectively double-pipe heat exchangers provided integrally by forming double pipes in a spiral shape as illustrated in FIG. 5 and connecting their low pressure side refrigerant flow paths each other.
  • the first internal heat exchanger 51 is arranged above the second internal heat exchanger 52 and the refrigerant on the low pressure side circulates from the first internal heat exchanger 51 toward the second internal heat exchanger 52.
  • the first internal heat exchanger 51 and the second internal heat exchanger 52 are covered by a heat insulating material for shielding heat exchange with the outside air.
  • a refrigerant inflow side 52a of an inner pipe of the second internal heat exchanger 52 is connected to the refrigerant outflow sides of the first radiator 36a and the second radiator 36b.
  • a refrigerant outflow side 52b of the inner pipe is connected to the refrigerant inflow side of the third radiator 42.
  • a refrigerant inflow side 52c of the outer pipe of the second internal heat exchanger 52 is connected to a refrigerant outflow side 51d of the outer pipe of the first internal heat exchanger 51.
  • a refrigerant outflow side 52d of the outer pipe of the second internal heat exchanger 52 is connected to the refrigerant absorption side of the compressor 41.
  • the automatic vending machine configured as described above will be described based on FIG. 6 for the case where the first housing 30a, the second housing 30b and the third housing 30c are all cooled.
  • the first electromagnetic valve 54a and the second electromagnetic valve 54b are closed; the third electromagnetic valve 54c, the fourth electromagnetic valve 54d, the fifth electromagnetic valve 54e and the sixth electromagnetic valve 54f are opened; and the first fan 37a, the second fan 37b, the third fan 37c, the compressor 41 and the machine room fan 43 are activated.
  • the refrigerant discharged from the compressor 41 circulates from the third electromagnetic valve 54c, the third radiator 42 to the high pressure side of the first internal heat exchanger 51 sequentially; circulates through the fourth expansion valve 53d; and, thereafter, is divided to flow into the flow paths provided with the fourth electromagnetic valve 54d, the fifth electromagnetic valve 54e and the sixth electromagnetic valve 54f.
  • the refrigerant circulating through the flow path provided with the fourth electromagnetic valve 54d circulates through the first expansion valve 53a and the first evaporator 35a to flow into the low pressure side of the first internal heat exchanger 51.
  • the refrigerant circulating through the flow path provided with the fifth electromagnetic valve 54e circulates through the second expansion valve 53b and the second evaporator 35b to flow into the low pressure side of the first internal heat exchanger 51.
  • the refrigerant circulating through the flow path provided with the sixth electromagnetic valve 54f circulates through the third expansion valve 53c and the third evaporator 35c to flow into the low pressure side of the first internal heat exchanger 51.
  • the refrigerant flowing out of the low pressure side of the first internal heat exchanger 51 passes through the low pressure side of the second internal heat exchanger 52 and is sucked into by the compressor 41.
  • the refrigerant does not circulate through the refrigerant flow path on the high pressure side of the second internal heat exchanger 52. Therefore, the refrigerant circulating through the refrigerant flow path on the low pressure side of the second internal heat exchanger 52 is sucked into by the compressor 41 without undergoing heat-exchange.
  • the second electromagnetic valve 54b, the third electromagnetic valve 54c and the fourth electromagnetic valve 54d are closed; the first electromagnetic valve 54a, the fifth electromagnetic valve 54e and the sixth electromagnetic valve 54f are opened; and the first fan 37a, the second fan 37b, the third fan 37c, the compressor 41, the compressor fan 41e and the machine room fan 43 are activated.
  • the refrigerant discharged from the compressor 41 circulates from the first electromagnetic valve 54a, the first radiator 36a, the high pressure side of the second internal heat exchanger 52, the third radiator 42 to the high pressure side of the internal heat exchanger 51 sequentially; circulates through the fourth expansion valve 53d; and, thereafter, is divided to flow into the flow paths provided with the fifth electromagnetic valve 54e and the sixth electromagnetic valve 54f.
  • the refrigerant circulating through the flow path provided with the fifth electromagnetic valve 54e circulates through the second expansion valve 53b and the second evaporator 35b to flow into the low pressure side of the first internal heat exchanger 51.
  • the refrigerant circulating through the flow path provided with the sixth electromagnetic valve 54f circulates through the third expansion valve 53c and the third evaporator 35c to flow into the low pressure side of the first internal heat exchanger 51.
  • the refrigerant flowing out of the low pressure side of the first internal heat exchanger 51 circulates through the low pressure side of the second internal heat exchanger 52 and is sucked into by the compressor 41.
  • the refrigerant flowing into the flow paths provided with the fourth electromagnetic valve 54d, the fifth electromagnetic valve 54e and the sixth electromagnetic valve 54f is decompressed to a predetermined pressure by the fourth expansion valve 53d and, thereafter, flows into respective flow paths. Therefore, the fourth electromagnetic valve 54d, the fifth electromagnetic valve 54e and the sixth electromagnetic valve 54f are less influenced by the pressure of the carbon dioxide refrigerant being in high pressure.
  • the first electromagnetic valve 54a, the third electromagnetic valve 54c and the fifth electromagnetic valve 54e are closed; the second electromagnetic valve 54b, the fourth electromagnetic valve 54d, and the sixth electromagnetic valve 54f are opened; and the first fan 37a, the second fan 37b, the third fan 37c, the compressor 41, the compressor fan 41e and the machine room fan 43 are activated.
  • the third electromagnetic valve 54c, the fourth electromagnetic valve 54d and the fifth electromagnetic valve 54e are closed; the first electromagnetic valve 54a, the second electromagnetic valve 54b and the sixth electromagnetic valve 54f are opened; and the first fan 37a, the second fan 37b, the third fan 37c, the compressor 41, the compressor fan 41e and the machine room fan 43 are activated.
  • the automatic vending machine of the present embodiment comprises the second internal heat exchanger 52 exchanging heat of the refrigerant flowing out of the first radiator 36a and the second radiator 36b with heat of the refrigerant sucked into by the compressor 41 and therefore the temperature of the refrigerant sucked into by the compressor 41 is increased to enable an increase in temperature of the refrigerant discharged from the compressor 41.
  • the amount of heat generated by the increased temperature of the refrigerant is utilized as a heating source for the first housing 30a and the second housing 30b. Thereby heating efficiency can be improved.
  • first housing 30a and the second housing 30b are respectively provided with the first radiator 36a and the second radiator 36b dedicated for heat dissipation and the first evaporator 35a and the second evaporator 35b dedicated for heat absorption, the number of the electromagnetic valves to be used can be reduced compared with the case of using a common heat exchanger for heat dissipation and heat absorption. Thereby, reduction in manufacturing cost can be intended.
  • the refrigerant discharged from the compressor 41 is caused to directly flow into the third radiator 42 without passing through the second internal heat exchanger 52. Therefore, at the occasion of cooling all of the first housing 30a, the second housing 30b and the third housing 30c, the refrigerant sucked into by the compressor 41 will not be heated by the refrigerant discharged from the compressor 41. Thereby, the temperature of the refrigerant discharged from the compressor 41 will not unnecessarily increase.
  • the refrigerant used in the refrigerant circuit 50 has been carbon dioxide.
  • the same effects as those of the above described embodiment can be obtained.
  • the decompressor of the refrigerant circuit 50 the first to the fourth expansion valves 53a, 53b, 53c and 53d have been used.
  • decompressor with a capillary tube and the like can be used.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Control Of Vending Devices And Auxiliary Devices For Vending Devices (AREA)
EP20070119518 2006-11-20 2007-10-29 Cooling/heating apparatus Expired - Fee Related EP1923648B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2006312889 2006-11-20

Publications (3)

Publication Number Publication Date
EP1923648A2 EP1923648A2 (en) 2008-05-21
EP1923648A3 EP1923648A3 (en) 2009-07-01
EP1923648B1 true EP1923648B1 (en) 2012-12-19

Family

ID=39032547

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20070119518 Expired - Fee Related EP1923648B1 (en) 2006-11-20 2007-10-29 Cooling/heating apparatus

Country Status (2)

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EP (1) EP1923648B1 (ja)
JP (1) JP5149588B2 (ja)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT202100000890A1 (it) * 2021-01-19 2022-07-19 Ali Group S R L Abbattitore di temperatura polivalente con ciclo invertibile, ad elevata efficienza

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5087482B2 (ja) * 2008-07-07 2012-12-05 サンデン株式会社 冷却加熱装置
KR101045188B1 (ko) 2011-04-22 2011-06-28 상 욱 김 초저온 해동 기계장치
JP2013185762A (ja) * 2012-03-08 2013-09-19 Fuji Electric Co Ltd 冷媒サイクル装置
CN105222470B (zh) * 2015-10-08 2017-08-08 浙江大学 即热即冷式跨临界循环自动售货装置及其供货方法
KR102473040B1 (ko) * 2018-01-10 2022-12-01 엘지전자 주식회사 냉장고
WO2019139389A1 (ko) 2018-01-10 2019-07-18 엘지전자 주식회사 냉장고
IT202100004079A1 (it) * 2021-02-22 2022-08-22 Arneg Armadio per l’esposizione e la conservazione di prodotti alimentari
CN113654301B (zh) * 2021-08-27 2023-03-31 中山市凯腾电器有限公司 一种双蒸发器制冷系统和制冷设备

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2004086726A (ja) * 2002-08-28 2004-03-18 Sanden Corp 食品冷却加温装置
JP2005107764A (ja) * 2003-09-30 2005-04-21 Sanden Corp 自動販売機
JP2005216111A (ja) * 2004-01-30 2005-08-11 Sanden Corp 自動販売機
JP2005226912A (ja) * 2004-02-12 2005-08-25 Sanyo Electric Co Ltd 加熱／冷却システム
JP4513441B2 (ja) * 2004-07-20 2010-07-28 パナソニック株式会社 冷却加温システムを有する自動販売機

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT202100000890A1 (it) * 2021-01-19 2022-07-19 Ali Group S R L Abbattitore di temperatura polivalente con ciclo invertibile, ad elevata efficienza
EP4030125A1 (en) * 2021-01-19 2022-07-20 Ali Group S.r.l. Multipurpose blast chiller with reversible cycle, with high efficiency

Also Published As

Publication number Publication date
EP1923648A3 (en) 2009-07-01
JP5149588B2 (ja) 2013-02-20
JP2008151496A (ja) 2008-07-03
EP1923648A2 (en) 2008-05-21

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