EP2339269B1 - Air conditioner - Google Patents

Air conditioner Download PDF

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Publication number
EP2339269B1
EP2339269B1 EP10252001.2A EP10252001A EP2339269B1 EP 2339269 B1 EP2339269 B1 EP 2339269B1 EP 10252001 A EP10252001 A EP 10252001A EP 2339269 B1 EP2339269 B1 EP 2339269B1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
refrigerant
pipe
expansion valve
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.)
Not-in-force
Application number
EP10252001.2A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2339269A3 (en
EP2339269A2 (en
Inventor
Shunji Itakura
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.)
Fujitsu General Ltd
Original Assignee
Fujitsu General 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
Application filed by Fujitsu General Ltd filed Critical Fujitsu General Ltd
Publication of EP2339269A2 publication Critical patent/EP2339269A2/en
Publication of EP2339269A3 publication Critical patent/EP2339269A3/en
Application granted granted Critical
Publication of EP2339269B1 publication Critical patent/EP2339269B1/en
Not-in-force 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
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/02—Subcoolers
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers
    • 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2509—Economiser valves

Definitions

  • the present invention relates to an air conditioner having a reversible refrigerating cycle. More particularly, it relates to an air conditioner having a double-pipe heat exchanger in a liquid-side refrigerant pipe connecting an outdoor heat exchanger and an indoor heat exchanger to each other.
  • a refrigerating cycle having a double-pipe heat exchanger to increase the degree of supercooling As one of refrigerating cycles applied to an air conditioner, a refrigerating cycle having a double-pipe heat exchanger to increase the degree of supercooling has been known.
  • some of a high-pressure liquid refrigerant condensed by a condenser is split and decompressed, and is heat-exchanged with a mainstream high-pressure liquid refrigerant.
  • FIG. 3 One example thereof is explained with reference to FIG. 3 .
  • Document US 2006/196225 A1 discloses an improvement system of energy efficiency for a refrigeration cycle is comprised of an auxiliary heat exchanger unit for heat-exchanging between refrigerant liquid having high pressure and refrigerant vapor having low pressure and a cabinet which houses a pressure support value placed at an inlet of an inner pipe of the auxiliary heat exchanger unit. A pressure of the refrigerant liquid having high pressure condensed at the outdoor heat exchanger is decreased by the pressure support value, and a condensed pressure of the outdoor heat exchanger is maintained.
  • a refrigerating cycle 1B of this conventional example includes, as a basic configuration, a compressor 10, a four-way valve 20, an outdoor heat exchanger 30, and an indoor heat exchanger 40, and the discharge side of the compressor 10 is connected to either one of the outdoor heat exchanger 30 and the indoor heat exchanger 40 via the four-way valve 20.
  • the discharge side of the compressor 10 is connected to the outdoor heat exchanger 30, the outdoor heat exchanger 30 functions as a condenser, and the indoor heat exchanger 40 functions as an evaporator.
  • the discharge side of the compressor 10 is connected to the indoor heat exchanger 40, the indoor heat exchanger 40 functions as a condenser, and the outdoor heat exchanger 30 functions as an evaporator.
  • a condensed liquid refrigerant is mainly caused to flow. Therefore, the refrigerant pipe connecting the outdoor heat exchanger 30 and the indoor heat exchanger 40 to each other is usually called a liquid-side refrigerant pipe 50.
  • the liquid-side refrigerant pipe 50 is provided with a double-pipe heat exchanger 60. Also, between the double-pipe heat exchanger 60 and the outdoor heat exchanger 30, a heating expansion valve 51 is provided, and between the double-pipe heat exchanger 60 and the indoor heat exchanger 40, a cooling expansion valve 52 is provided.
  • the double-pipe heat exchanger 60 consists, for example, of an inner pipe and an outer pipe arranged coaxially, and a high-pressure liquid refrigerant is caused to flow in the inner pipe.
  • a bypass pipe 61 branched from the liquid-side refrigerant pipe 50 is connected, and the bypass pipe 61 is provided with a bypass expansion valve 62.
  • a two-way valve 53 and a three-way valve 54 provided on both sides of the indoor heat exchanger 40 are connection pipes for connecting the indoor heat exchanger 40 to the refrigerating cycle when the air conditioner is installed.
  • the heating expansion valve 51 is fully opened, and the cooling expansion valve 52 is throttled to a predetermined degree of opening, so that the refrigerant flows as indicated by the solid-line arrow marks in FIG. 3 .
  • the cooling expansion valve 52 is fully opened, and the heating expansion valve 51 is throttled to a predetermined degree of opening, so that the refrigerant flows as indicated by the broken-line arrow marks in FIG. 3 .
  • the high-pressure liquid refrigerant (mainstream) condensed by the outdoor heat exchanger 30 or the indoor heat exchanger 40 is caused to flow.
  • a low-pressure two-phase refrigerant that is split from the mainstream high-pressure liquid refrigerant and decompressed by the bypass expansion valve 62 is caused to flow.
  • the low-pressure two-phase refrigerant is heat-exchanged with the mainstream high-pressure liquid refrigerant and is evaporated, and the mainstream high-pressure liquid refrigerant is cooled.
  • the degree of opening of the bypass expansion valve 62 is controlled so that the degree of supercooling of the high-pressure liquid refrigerant becomes a target degree of supercooling.
  • the low-pressure two-phase refrigerant is evaporated by the heat exchange with the high-pressure liquid refrigerant, and is returned to a suction pipe 11 of the compressor 10 as a low-pressure gas refrigerant (for example, refer to Japanese Patent Application Publication No. 2006-23073 ).
  • the solid line indicates the mainstream of the high-pressure liquid refrigerant flowing in the liquid-side refrigerant pipe 50
  • the dash-and-dot line indicates a bypass stream flowing in the bypass pipe 61.
  • FIG. 4A shows a refrigerating cycle in which the refrigerant circulates in the optimum state. Even if the refrigerant reaches the indoor heat exchanger 40 in the optimum state with the degree of supercooling being A and the mainstream and the bypass stream are mixed with each other, a state of gas phase is established.
  • the low-pressure two-phase refrigerant that is split from the mainstream and decompressed by the bypass expansion valve 62 evaporates in the double-pipe heat exchanger 60, and becomes in an overheated state of (c1).
  • the mainstream evaporates in the indoor heat exchanger 40 and returns to the compressor 10 in the state of (a1), and on the suction side of the compressor 10, (a1) and (c1) are mixed with each other, and the state of (b1) is formed.
  • the temperature of the bypass stream at the outlet of the double-pipe heat exchanger 60 is monitored to suppress the flow rate of bypass stream.
  • the circulation amount of refrigerant in the evaporator (for example, the indoor heat exchanger 40) is only the amount of the mainstream, so that the heat exchange amount sometimes comes short.
  • an object of the present invention is to provide an air conditioner having a double-pipe heat exchanger in a refrigerating cycle, wherein the degree of opening of a bypass expansion valve can be controlled easily without liquid return to a compressor and without considering the state of a low-pressure two-phase refrigerant in the double-pipe heat exchanger.
  • the present invention provides an air conditioner including a refrigerating cycle in which a double-pipe heat exchanger is provided in a liquid-side refrigerant pipe between an outdoor heat exchanger and an indoor heat exchanger which are selectively connected to the discharge side of a compressor via a four-way valve; a heating expansion valve is provided between the outdoor heat exchanger and the double-pipe heat exchanger; a cooling expansion valve is provided between the indoor heat exchanger and the double-pipe heat exchanger; and in the double-pipe heat exchanger, a high-pressure liquid refrigerant flowing in the liquid-side refrigerant pipe is heat-exchanged with a gas-liquid low-pressure two-phase refrigerant which is formed by decompressing some of the high-pressure liquid refrigerant by a bypass expansion valve, wherein a low-pressure refrigerant outflow portion of the double-pipe heat exchanger is branched in a fork form; one branch is connected to the refrigerant pipe between the outdoor heat exchanger and the heating expansion valve
  • the heating expansion valve is fully opened and the cooling expansion valve is throttled to a predetermined degree of opening; and the low-pressure refrigerant heat-exchanged by the double-pipe heat exchanger is supplied to the indoor heat exchanger on the evaporator side via the second valve means together with the refrigerant decompressed by the cooling expansion valve.
  • the cooling expansion valve is fully opened and the heating expansion valve is throttled to a predetermined degree of opening; and the low-pressure refrigerant heat-exchanged by the double-pipe heat exchanger is supplied to the outdoor heat exchanger on the evaporator side via the first valve means together with the refrigerant decompressed by the heating expansion valve.
  • check valves which are opened with the low-pressure refrigerant outflow portion being on the high pressure side or solenoid valves which are opened and closed by an external signal may be used.
  • the refrigerant going out of the double-pipe heat exchanger is caused to flow to the evaporator side, the refrigerant is evaporated by the evaporator and is returned to the compressor even if not being evaporated completely by the double-pipe heat exchanger. Therefore, liquid return to the compressor can be eliminated.
  • the state of the low-pressure refrigerant in the double-pipe heat exchanger need not be considered, and the control has only to be carried out so that the degree of supercooling of the high-pressure liquid refrigerant becomes a target degree of supercooling. Therefore, the bypass expansion valve can be controlled easily.
  • the degree of supercooling of the high-pressure liquid refrigerant can be made high, so that the improvement in performance of the refrigerating cycle can be expected accordingly.
  • FIGS. 1 and 2 An embodiment of the present invention will now be described with reference to FIGS. 1 and 2 .
  • the present invention is not limited to this embodiment.
  • the same reference numerals are applied to elements that are essentially the same as the elements in the conventional example explained with reference to FIG. 3 .
  • a refrigerating cycle 1A in accordance with this embodiment includes, as a basic configuration, a compressor 10, a four-way valve 20, an outdoor heat exchanger 30, and an indoor heat exchanger 40.
  • the compressor 10 may be either a rotary compressor or a scroll compressor.
  • the discharge side of the compressor 10 is connected to either one of the outdoor heat exchanger 30 and the indoor heat exchanger 40 via the four-way valve 20, and in a liquid-side refrigerant pipe 50 that connects the outdoor heat exchanger 30 and the indoor heat exchanger 40 to each other, a double-pipe heat exchanger 60 is interposed.
  • a heating expansion valve 51 is provided between the outdoor heat exchanger 30 and the double-pipe heat exchanger 60, and between the indoor heat exchanger 40 and the double-pipe heat exchanger 60, a cooling expansion valve 52 is provided.
  • the double-pipe heat exchanger 60 consists, for example, of an inner pipe and an outer pipe arranged coaxially, and a high-pressure liquid refrigerant condensed by the outdoor heat exchanger 30 or the indoor heat exchanger 40 is caused to flow in the inner pipe.
  • This high-pressure liquid refrigerant caused to flow in the inner pipe is a mainstream.
  • a bypass pipe 61 branched from the liquid-side refrigerant pipe 50 is connected, and the bypass pipe 61 is provided with a bypass expansion valve 62.
  • Some of the high-pressure liquid refrigerant split from the bypass pipe 61 is decompressed, and flows in the outer pipe as a low-pressure two-phase refrigerant.
  • the high-pressure liquid refrigerant may be caused to flow on the outer pipe side, and the low-pressure two-phase refrigerant may be caused to flow on the inner pipe side.
  • a low-pressure refrigerant outflow portion 60a of the double-pipe heat exchanger 60 is connected to a refrigerant pipe portion 50a between the outdoor heat exchanger 30 and the heating expansion valve 51 via a first check valve 71, and is also connected to a refrigerant pipe portion 50b between the indoor heat exchanger 40 and the cooling expansion valve 52 via a second check valve 72.
  • the forward direction of flow is a direction directed from the low-pressure refrigerant outflow portion 60a to the refrigerant pipe portions 50a and 50b.
  • a solenoid valve that is opened and closed by an external signal may be used.
  • the four-way valve 20 is changed over to the state indicated by the solid line in FIG. 1 .
  • the heating expansion valve 51 is fully opened, the cooling expansion valve 52 is throttled to a predetermined degree of opening, and the refrigerant circulates as indicated by the solid-line arrow marks in FIG. 1 .
  • a high-pressure gas refrigerant discharged from the compressor 10 reaches the outdoor heat exchanger 30 through the four-way valve 20, being condensed into the high-pressure liquid refrigerant by the outdoor heat exchanger 30, and is further cooled by the double-pipe heat exchanger 60.
  • the high-pressure liquid refrigerant from which the degree of supercooling is removed by the double-pipe heat exchanger 60 is split in a portion of the bypass pipe 61.
  • One stream (the mainstream) is sent to the cooling expansion valve 52, and the other stream (a bypass stream) is sent to the bypass expansion valve 62.
  • bypass stream is decompressed into the gas-liquid low-pressure two-phase refrigerant by the bypass expansion valve 62, and is heat-exchanged with the high-pressure liquid refrigerant by the double-pipe heat exchanger 60 and is evaporated.
  • the refrigerant in the refrigerant pipe portion 50a on the outdoor heat exchanger 30 side has a pressure higher than the pressure of refrigerant at the low-pressure refrigerant outflow portion 60a
  • the refrigerant in the refrigerant pipe portion 50b on the indoor heat exchanger 40 side has a pressure lower than the pressure of refrigerant at the low-pressure refrigerant outflow portion 60a.
  • the evaporated gas refrigerant reaches the refrigerant pipe portion 50b via the second check valve 72, joining with the mainstream-side refrigerant decompressed by the cooling expansion valve 52, and is sent to the indoor heat exchanger 40 on the evaporator side.
  • the indoor heat exchanger 40 the refrigerant is heat-exchanged with indoor air and is evaporated, and the gas refrigerant is returned to the compressor 10 through a suction pipe 11 and an accumulator 12.
  • the flow rate of refrigerant in the refrigerating cycle is regulated by the cooling expansion valve 52, and the degree of opening of the bypass expansion valve 62 is controlled so that the degree of supercooling of the high-pressure liquid refrigerant becomes a target degree of supercooling.
  • the four-way valve 20 is changed over to the state indicated by the broken line in FIG. 1 .
  • the cooling expansion valve 52 is fully opened, the heating expansion valve 51 is throttled to a predetermined degree of opening, and the refrigerant circulates as indicated by the broken-line arrow marks in FIG. 1 .
  • the high-pressure gas refrigerant discharged from the compressor 10 reaches the indoor heat exchanger 40 through the four-way valve 20, and is condensed into the high-pressure liquid refrigerant by the indoor heat exchanger 40.
  • the high-pressure liquid refrigerant is split in the portion of the bypass pipe 61 in front of the double-pipe heat exchanger 60.
  • One stream (the mainstream) flows in the inner pipe of the double-pipe heat exchanger 60 and reaches the heating expansion valve 51, and the other stream (the bypass stream) is sent to the bypass expansion valve 62.
  • the bypass stream is decompressed into the gas-liquid low-pressure two-phase refrigerant by the bypass expansion valve 62, and is heat-exchanged with the high-pressure liquid refrigerant on the mainstream side by the double-pipe heat exchanger 60 and is evaporated.
  • the refrigerant in the refrigerant pipe portion 50b on the indoor heat exchanger 40 side has a pressure higher than the pressure of refrigerant at the low-pressure refrigerant outflow portion 60a
  • the refrigerant in the refrigerant pipe portion 50a on the outdoor heat exchanger 30 side has a pressure lower than the pressure of refrigerant at the low-pressure refrigerant outflow portion 60a.
  • the evaporated gas refrigerant reaches the refrigerant pipe portion 50a via the first check valve 71, joining with the mainstream-side refrigerant decompressed by the heating expansion valve 51, and is sent to the outdoor heat exchanger 30 on the evaporator side.
  • the refrigerant is heat-exchanged with the outside air and is evaporated, and the gas refrigerant is returned to the compressor 10 through the suction pipe 11 and the accumulator 12.
  • the flow rate of refrigerant in the refrigerating cycle is regulated by the heating expansion valve 51, and the degree of opening of the bypass expansion valve 62 is controlled so that the degree of supercooling of the high-pressure liquid refrigerant becomes the target degree of supercooling.
  • the gas-liquid low-pressure two-phase refrigerant need not be evaporated completely in the double-pipe heat exchanger 60. Therefore, a large amount of low-pressure two-phase refrigerant can be caused to flow in the double-pipe heat exchanger 60 by increasing the target degree of supercooling of the high-pressure liquid refrigerant.
  • the refrigerating cycle of the present invention (the case of cooling operation) is explained.
  • the solid line indicates the mainstream of the high-pressure liquid refrigerant flowing in the liquid-side refrigerant pipe 50
  • the dash-and-dot line indicates the bypass stream flowing in the bypass pipe 61.
  • the refrigerant is sucked into the compressor 10, and the compressed refrigerant becomes at high temperature and pressure (point x) and is condensed by the outdoor heat exchanger 30 (point a).
  • the refrigerant is heat-exchanged with the later-described bypass stream (g-f) by the double-pipe heat exchanger 60 and becomes in a supercooled state (point b), and is decompressed by the cooling expansion valve 52 (point d).
  • the bypass circuit some of the mainstream heat-exchanged by the double-pipe heat exchanger 60 is split in the bypass pipe 61, and is decompressed by the bypass expansion valve 62 (point g). Thereafter, the refrigerant is heat-exchanged with the mainstream (a-b) (point f). The mainstream and the bypass stream are joined with each other (point e) and flow into the indoor heat exchanger 30. The refrigerant is evaporated by the indoor heat exchanger 30, and is sucked into the compressor 10 (point D).
  • the bypass stream used in the double-pipe heat exchanger 60 does not return directly to the suction side of the compressor 10, and is heat-exchanged by the indoor heat exchanger 30, so that no wasteful refrigerant is generated. Therefore, the performance (COP) is improved. Also, since there is no fear of liquid back, supercooling can be performed until the refrigerant can be supplied to the indoor heat exchanger 30 in the optimum state.
EP10252001.2A 2009-12-25 2010-11-25 Air conditioner Not-in-force EP2339269B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2009293650A JP2011133177A (ja) 2009-12-25 2009-12-25 空気調和機

Publications (3)

Publication Number Publication Date
EP2339269A2 EP2339269A2 (en) 2011-06-29
EP2339269A3 EP2339269A3 (en) 2011-07-13
EP2339269B1 true EP2339269B1 (en) 2019-01-23

Family

ID=43873806

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10252001.2A Not-in-force EP2339269B1 (en) 2009-12-25 2010-11-25 Air conditioner

Country Status (6)

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US (1) US20110154847A1 (zh)
EP (1) EP2339269B1 (zh)
JP (1) JP2011133177A (zh)
CN (1) CN102109202B (zh)
AU (1) AU2010246508A1 (zh)
ES (1) ES2715928T3 (zh)

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2884205B1 (en) * 2012-10-18 2017-02-01 Daikin Industries, Ltd. Air conditioner
KR101474356B1 (ko) * 2013-07-18 2014-12-19 한국에너지기술연구원 수액기에 저장되는 냉매량이 조절되는 히트펌프 시스템
CN103900222B (zh) * 2014-03-07 2017-05-24 广东美的暖通设备有限公司 冷却空调器电控变频模块的方法及空调器
CN104266416B (zh) * 2014-09-29 2017-03-15 特灵空调系统(中国)有限公司 多联机节流与过冷控制机构
CN104534725A (zh) * 2015-01-23 2015-04-22 珠海格力电器股份有限公司 空调器
CN106032950A (zh) * 2015-03-18 2016-10-19 青岛海尔空调电子有限公司 一种空调系统
CN104848579B (zh) * 2015-05-05 2017-12-01 广东美的制冷设备有限公司 空调器及其热交换系统
JP6350577B2 (ja) * 2016-03-31 2018-07-04 ダイキン工業株式会社 空気調和装置
JP6341321B2 (ja) * 2016-06-30 2018-06-13 ダイキン工業株式会社 空気調和機
ES2900352T3 (es) * 2017-09-07 2022-03-16 Mitsubishi Electric Corp Dispositivo de acondicionamiento de aire
JP6863395B2 (ja) * 2019-02-18 2021-04-21 ダイキン工業株式会社 空気調和装置

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JPH09152195A (ja) * 1995-11-28 1997-06-10 Sanyo Electric Co Ltd 冷凍装置
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Also Published As

Publication number Publication date
US20110154847A1 (en) 2011-06-30
EP2339269A3 (en) 2011-07-13
AU2010246508A1 (en) 2011-07-14
EP2339269A2 (en) 2011-06-29
JP2011133177A (ja) 2011-07-07
CN102109202A (zh) 2011-06-29
ES2715928T3 (es) 2019-06-07
CN102109202B (zh) 2014-09-03

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