WO2007081021A1 - 空気調和機 - Google Patents
空気調和機 Download PDFInfo
- Publication number
- WO2007081021A1 WO2007081021A1 PCT/JP2007/050476 JP2007050476W WO2007081021A1 WO 2007081021 A1 WO2007081021 A1 WO 2007081021A1 JP 2007050476 W JP2007050476 W JP 2007050476W WO 2007081021 A1 WO2007081021 A1 WO 2007081021A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- refrigerant
- heat exchanger
- paths
- air conditioner
- path
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/0007—Indoor units, e.g. fan coil units
- F24F1/0059—Indoor units, e.g. fan coil units characterised by heat exchangers
- F24F1/0063—Indoor units, e.g. fan coil units characterised by heat exchangers by the mounting or arrangement of the heat exchangers
-
- 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
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
-
- 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
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/385—Dispositions with two or more expansion means arranged in parallel on a refrigerant line leading to the same evaporator
-
- 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
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2140/00—Control inputs relating to system states
- F24F2140/20—Heat-exchange fluid temperature
-
- 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
- F25B2600/2507—Flow-diverting valves
Definitions
- the present invention relates to an air conditioner, and more particularly to a configuration of an air conditioner including a flow divider that appropriately diverts a refrigerant to a plurality of paths in an indoor heat exchanger of the air conditioner.
- FIG. 5 shows a configuration of a general wall-mounted air conditioner (indoor unit) 21 in which the cross flow fan 29 is employed.
- first and second air suction grilles 23 and 24 are respectively formed on the upper surface of the main casing 20 of the air conditioner 21 and the upper front portion.
- An air outlet 25 is provided at a corner portion formed below the front surface of the main casing 20.
- air passages 27 are provided from the air suction grilles 23 and 24 toward the air outlet 25.
- An indoor heat exchanger having a V-shaped cross section facing the first and second air suction grilles 23 and 24 is provided in the upstream region of the air passage 27.
- the indoor heat exchanger 26 is a lambda heat exchanger.
- a cross flow fan 29, a tongue portion 22 and a scroll portion 30 are provided in the downstream area of the air passage 27, a cross flow fan 29, a tongue portion 22 and a scroll portion 30 are provided.
- the tongue portion 22 and the scroll portion 30 form a spiral fan-shaped housing.
- an impeller (fan opening) 29a of the cross flow fan 29 is installed so as to rotate along the arrow direction in FIG. .
- the tongue portion 22 is provided at a position facing the second air suction grill 24, and has a predetermined length along the outer diameter of the impeller (fan rotor) 29a of the crossflow fan 29. ! /
- the lower part of the tongue 22 is connected to an air flow guide 22b provided below the indoor heat exchanger 26 and also serving as a drain pan.
- the downstream portion of the air flow guide portion 22b extends toward the air outlet 25 together with the downstream portion 30b of the scroll portion 30 to form an air outlet passage 28 having a diffuser structure as shown. .
- a wind direction changing plate 31 is provided in an air blowing passage 28 located between the scroll portion 30 and an air flow guide portion 22b provided below the tongue portion 22.
- the tongue 22 has the shape shown in FIG. Then, the flow of the air from the impeller (fan rotor) 29a through the indoor heat exchanger 26 to the air outlet 25 from the cross fan 1 fan 29 is as a whole impeller (as indicated by the chain line arrow in FIG.
- the fan rotor flows along the direction orthogonal to the rotation axis of the impeller (fan rotor) 29a while being curved along the rotation direction of the 29a. Thereafter, the air flow is bent toward the air outlet 25 along the air outlet passage 28 and blown out from the front of the air conditioner 21.
- the indoor heat exchanger 26 for an air conditioner having such a configuration is divided into A part, B part, C part, and D part.
- the wind speed distribution during loading is analyzed.
- the wind speed at section C facing diagonally against the first air suction grille 23 where the wind speed at section D facing the second air suction grill 24 is the highest is lower than at section D. It is covered by a part of the upper part of the front surface of the main casing 20 and air does not flow straight into the section B.
- the wind speed is lower than the section C. Air is blocked by the tongue 22, and the wind speed is further reduced in part A than in part B.
- the refrigerant flowing into the indoor heat exchanger ⁇ 26 is distributed to each path of the indoor heat exchanger 26 main body.
- a flow divider 6 having a plurality of flow dividing paths 7a and 7b as shown in FIG. 6 is generally provided.
- the distribution ratio of the refrigerant in each flow dividing path 7a, 7b is determined in accordance with the rated operation.
- An expansion valve V and a refrigerant inlet 6a are provided at the inlet of the flow divider 6.
- the shunt path 7a passes through the high wind speed part 26a
- the shunt path 7b passes through the low wind speed part 26b.
- the refrigerant temperature at the outlet of each path 8A, 8B provided at the outlet of the indoor heat exchanger 26 are almost equal.
- the following problems arise due to the influence of different wind speed distributions depending on the position of the air passage of the indoor heat exchanger 26. That is, for example, as shown in the graph of FIG. 7, the refrigerant temperature at the exit of the paths 7a and 8A where the wind speed is high becomes high due to a sufficient heat exchange capacity.
- the wind speed is The refrigerant temperature at the outlet of the low pass 7b, 8B is lower than the refrigerant temperature at the outlet of the pass 7a, 8A because there is no room for heat exchange capacity (see ⁇ in FIG. 7).
- paths 7a and 8A with high wind speed are displayed in white, and paths 7b and 8B with low wind speed are displayed in S dot.
- Patent Document 1 JP-A-5-118682
- An object of the present invention is to improve heat exchange performance by appropriately controlling refrigerant drift between each path of a flow distributor corresponding to a heat exchanger for an air conditioner having a plurality of paths. It is to provide an air conditioner.
- an air provided with a compressor, a four-way valve, an outdoor heat exchanger ⁇ , an expansion device, and an indoor heat exchanger having a plurality of paths A harmony machine is provided.
- the above members are sequentially connected by a refrigerant pipe to form a refrigerant circuit.
- a shunt having a plurality of paths is disposed between the indoor heat exchanger having the plurality of noses and the expansion device.
- a refrigerant flow rate adjusting valve is provided in each of the plurality of paths of the flow divider. Compared to other paths, more refrigerant is allocated to a given nose with a high processing capacity in a given operating state and a higher refrigerant temperature at the outlet of the indoor heat exchange! Speak.
- the refrigerant in a predetermined operation state, is more actively distributed to the path having a sufficient processing capacity, so that the flow velocity in the pipe of the path increases.
- the difference between the temperature at the outlet of the indoor heat exchanger and the suction temperature widens. As a result, the capacity of the indoor heat exchanger is improved and the refrigeration capacity is improved.
- the predetermined operation state is an operation state at a low load, and when the load is low, the refrigerant flow rate adjustment valve in the path where the processing capacity is small and the refrigerant temperature at the outlet of the indoor heat exchanger is low is throttled. Therefore, a large amount of refrigerant flows through a predetermined path where the processing capacity is large and the refrigerant temperature at the outlet of the indoor heat exchanger becomes high.
- the refrigerant flow rate adjusting valve in the path where the processing capacity is reduced and the refrigerant temperature at the outlet of the indoor heat exchanger is reduced. Further, the flow rate in the pipe of the path is increased by allocating more refrigerant to a predetermined path having a sufficient processing capacity and a high wind speed. In addition, the difference between the temperature at the outlet of the indoor heat exchanger and the suction temperature widens. As a result, the heat exchange capacity is effectively improved and the refrigeration capacity is improved.
- the predetermined path is a path with a high wind speed
- the refrigerant flow rate adjustment valve of the path with the low wind speed is throttled, and there is a sufficient heat exchange capacity, so that the wind speed is high. Therefore, more refrigerant flows.
- the refrigerant flow rate adjustment valve in the path with low wind speed is throttled, and there is room in heat exchange capacity, and wind speed is low.
- the pipe flow velocity in the path increases.
- the difference between the temperature at the outlet of the indoor heat exchanger and the suction temperature widens. As a result, the heat exchange capacity is effectively improved and the refrigeration capacity is improved.
- the predetermined operation state is an operation state at a rated load, and at the rated load, the refrigerant flow rate adjusting valve of each path is fully opened, and the heat exchange capacity is fully exhibited. It is configured to be. According to this configuration, the refrigerant flow rate adjustment valve of each path is fully opened in the operation state at the rated load, and the heat exchange capability can be fully exhibited.
- FIG. 1 is a diagram showing a refrigeration circuit of an air conditioner according to a first preferred embodiment of the present invention.
- FIG. 2 is a diagram showing the configuration and operation of a heat exchanger having a plurality of paths and a shunt corresponding to each path of the heat exchanger in an air conditioner indoor unit.
- FIG. 3 is a graph showing the temperature at the outlet of the indoor heat exchanger by the shunt shown in FIG. 2 in comparison with the rated time and low load.
- FIG. 4 A configuration of a heat exchanger ⁇ having a plurality of paths and a shunt corresponding to each path of the heat exchanger ⁇ in the indoor unit of the air conditioner according to the second embodiment of the present invention.
- FIG. 5 is a diagram showing a configuration of an indoor unit of a conventional air conditioner.
- FIG. 6 is a diagram showing the configuration and operation of a heat exchanger provided with a plurality of paths and a shunt corresponding to the heat exchanger in an air conditioner indoor unit.
- FIG. 7 is a graph showing the temperature at the outlet of the indoor heat exchanger by the shunt shown in FIG. 6 in comparison with rated time and low load.
- FIG. 8 is a diagram showing the configuration and operation of a heat exchanger having a plurality of paths and a shunt corresponding to the heat exchanger in an indoor unit of an air conditioner according to the related art in which measures for outlet temperature are taken. .
- FIG. 9 is a graph showing the temperature at the outlet of the indoor heat exchanger by the shunt shown in FIG. 8 in comparison with rated time and low load.
- FIG. 1 and FIG. 2 show the configuration of the refrigeration circuit of the air conditioner according to the first embodiment of the present invention and the shunt portion thereof
- FIG. 3 shows the operation and effect of the configuration.
- the wind speed region of the heat exchange 26 part shown in FIG. 5 is divided into two parts, a low wind speed part A, B and a high wind speed part C, D. This is illustrated in the case where the number of paths of the 6 parts of the shunt is two according to the area.
- the air conditioner includes an outdoor unit 1 and an indoor unit 10.
- the outdoor unit 1 includes a compressor 2, a four-way valve 3, an outdoor heat exchanger 4, and a throttle device 5.
- the indoor unit 10 includes a flow divider 6, a refrigerant flow inlet 6a to the flow divider 6, a first flow diversion path 7a of the flow divider 6, a second flow diversion path 7b of the flow divider 6, an indoor heat exchanger 26, A first path 8A located at the outlet of the heat exchanger 26, a second path 8B located at the outlet of the indoor heat exchanger 26, and an expansion valve V are provided.
- Each member is connected by the first refrigerant pipe 9A and the second refrigerant pipe 9B.
- a reversible refrigerant circulation circuit as shown in FIG. 1 is constructed.
- first and second diversion paths 7a and 7b of the flow divider 6 are provided with first and second refrigerant flow rate adjustment valves V and V, respectively, which are electromagnetic valves whose opening degree can be adjusted electrically. .
- refrigerant distribution amount is controlled by individually controlling the opening degrees of the first and second refrigerant flow rate adjusting valves V, V by a predetermined control unit including a microcomputer, for example.
- the predetermined operation state is an operation state at a low load where the refrigerant flow amount to the refrigerant inlet 6a of the flow divider 6 is reduced, for example.
- the second shunt path 7b passes through the part 26b, and the wind speed is high
- the first shunt path 7a passes through the part 26a as shown in FIG.
- the wind speed in the first shunt path 7a where the wind speed in the second shunt path 7b is low and the wind speed in the first shunt path 7a is high, for example, there is no room for heat exchange capacity and the second shunt path 7b where the wind speed is low is low.
- the valve opening of the corresponding refrigerant flow rate adjustment valve V is throttled.
- the heat exchange capacity is sufficient, the wind speed is high, and more refrigerant flows in the first diversion path 7a than in the second diversion path 7b.
- the refrigerant is distributed more in the first diversion path 7a than in the second diversion path 7b, so that the pipe flow velocity in the first diversion path 7a with high wind speed is high.
- the difference ⁇ between the temperature at the outlet of the indoor heat exchanger 26 and the suction temperature increases.
- the capacity of the indoor heat exchange 26 is improved and the refrigeration capacity is improved.
- the first diversion path 7a is displayed in white
- the second diversion path 7b is displayed in force S dot.
- the heat exchange capacity of AC 26 is fully demonstrated. As a result of the above, according to the present embodiment, the temperature at the outlet of each path 8A, 8B of the indoor heat exchanger ⁇ 26 is simply equalized. Compared with this configuration, the heat exchange capacity of the indoor heat exchanger 26 for the air conditioner can be improved more effectively.
- FIG. 4 shows the configuration of the shunt and the indoor heat exchanger part of the air conditioner according to the second preferred embodiment of the present invention.
- the wind speed distribution area of the indoor heat exchange ⁇ 26 in FIG. 6 is between the low wind speed parts A and B and the high wind speed parts C and D.
- the best embodiment 2 has the following configuration. That is, the wind speed region force of heat exchange 26 in FIG. 6 is divided into four wind speed regions, for example, low wind speed region A, B, C and high wind velocity D.
- first, second, third, and fourth shunt paths 7a to 7d are provided, and in the same manner as in the best mode 1, the first to second shunt paths 7a to 7d are provided.
- 4 refrigerant flow rate adjustment valves V to V are provided.
- the first to fourth diversion paths 7a to 7d are provided, so that at least at the time of low load where the total refrigerant flow rate is reduced, there is a margin in processing capacity.
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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)
- Air Conditioning Control Device (AREA)
- Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)
Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
AU2007205443A AU2007205443B2 (en) | 2006-01-16 | 2007-01-16 | Air conditioner |
EP07706803.9A EP1975525A4 (en) | 2006-01-16 | 2007-01-16 | AIR CONDITIONER |
CN2007800017227A CN101360961B (zh) | 2006-01-16 | 2007-01-16 | 空调机 |
US12/087,100 US20090025420A1 (en) | 2006-01-16 | 2007-01-16 | Air Conditioner |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2006-007578 | 2006-01-16 | ||
JP2006007578A JP4120680B2 (ja) | 2006-01-16 | 2006-01-16 | 空気調和機 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2007081021A1 true WO2007081021A1 (ja) | 2007-07-19 |
Family
ID=38256422
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2007/050476 WO2007081021A1 (ja) | 2006-01-16 | 2007-01-16 | 空気調和機 |
Country Status (7)
Country | Link |
---|---|
US (1) | US20090025420A1 (ja) |
EP (1) | EP1975525A4 (ja) |
JP (1) | JP4120680B2 (ja) |
KR (1) | KR100973916B1 (ja) |
CN (2) | CN101149097B (ja) |
AU (1) | AU2007205443B2 (ja) |
WO (1) | WO2007081021A1 (ja) |
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JP5858824B2 (ja) * | 2012-03-01 | 2016-02-10 | 三菱電機株式会社 | マルチ形空気調和機 |
KR102025738B1 (ko) * | 2012-07-06 | 2019-09-27 | 삼성전자주식회사 | 냉장고 및 이에 구비되는 열교환기 |
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KR101425043B1 (ko) * | 2012-07-26 | 2014-08-01 | 엘지전자 주식회사 | 실외 열교환기 |
CN102829584A (zh) * | 2012-09-04 | 2012-12-19 | 海信科龙电器股份有限公司 | 空调器制冷*** |
JP6058145B2 (ja) * | 2013-08-28 | 2017-01-11 | 三菱電機株式会社 | 空気調和装置 |
WO2015063853A1 (ja) * | 2013-10-29 | 2015-05-07 | 株式会社日立製作所 | 冷凍サイクルおよび空気調和機 |
ES2593064T3 (es) * | 2013-11-28 | 2016-12-05 | Alfa Laval Corporate Ab | Sistema y método para el control dinámico de un intercambiador de calor |
US10139143B2 (en) * | 2013-12-17 | 2018-11-27 | Lennox Industries Inc. | Air conditioner with multiple expansion devices |
JP6297072B2 (ja) * | 2014-02-10 | 2018-03-20 | 三菱電機株式会社 | ヒートポンプ式給湯装置 |
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CN106016682B (zh) * | 2016-06-02 | 2019-01-15 | 青岛海尔空调器有限总公司 | 自然风空调换热装置及其控制方法、自然风空调 |
JP6741146B2 (ja) * | 2017-03-27 | 2020-08-19 | ダイキン工業株式会社 | 熱交換器及び冷凍装置 |
AU2018245192A1 (en) | 2017-03-27 | 2019-11-14 | Daikin Industries, Ltd. | Heat exchanger and refrigeration apparatus |
JPWO2018193518A1 (ja) * | 2017-04-18 | 2019-11-21 | 三菱電機株式会社 | 空気調和機 |
JP6882679B2 (ja) * | 2017-07-07 | 2021-06-02 | 株式会社椿本チエイン | テンショナ |
US11486617B2 (en) | 2017-10-27 | 2022-11-01 | Mitsubishi Electric Corporation | Refrigeration cycle apparatus |
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KR100437804B1 (ko) * | 2002-06-12 | 2004-06-30 | 엘지전자 주식회사 | 2배관식 냉난방 동시형 멀티공기조화기 및 그 운전방법 |
US7493775B2 (en) * | 2002-10-30 | 2009-02-24 | Mitsubishi Denki Kabushiki Kaisha | Air conditioner |
KR100463548B1 (ko) * | 2003-01-13 | 2004-12-29 | 엘지전자 주식회사 | 공기조화기용 제상장치 |
JP2005273923A (ja) * | 2004-03-23 | 2005-10-06 | Hitachi Home & Life Solutions Inc | 空気調和機 |
JP2005315309A (ja) * | 2004-04-28 | 2005-11-10 | Hitachi Home & Life Solutions Inc | 冷媒流量制御弁 |
-
2006
- 2006-01-16 JP JP2006007578A patent/JP4120680B2/ja not_active Expired - Fee Related
- 2006-12-28 CN CN2006101567452A patent/CN101149097B/zh not_active Expired - Fee Related
-
2007
- 2007-01-16 EP EP07706803.9A patent/EP1975525A4/en not_active Withdrawn
- 2007-01-16 WO PCT/JP2007/050476 patent/WO2007081021A1/ja active Application Filing
- 2007-01-16 CN CN2007800017227A patent/CN101360961B/zh not_active Expired - Fee Related
- 2007-01-16 KR KR1020087013407A patent/KR100973916B1/ko not_active IP Right Cessation
- 2007-01-16 US US12/087,100 patent/US20090025420A1/en not_active Abandoned
- 2007-01-16 AU AU2007205443A patent/AU2007205443B2/en not_active Ceased
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
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JPH04208363A (ja) * | 1990-11-30 | 1992-07-30 | Matsushita Seiko Co Ltd | 熱交換器分流装置 |
JPH05118682A (ja) * | 1991-10-25 | 1993-05-14 | Sharp Corp | 空気調和機 |
JPH05280829A (ja) * | 1992-03-31 | 1993-10-29 | Matsushita Seiko Co Ltd | 空気調和機 |
JP2000179968A (ja) * | 1998-12-18 | 2000-06-30 | Fujitsu General Ltd | 空気調和機の冷凍サイクル |
Non-Patent Citations (1)
Title |
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See also references of EP1975525A4 * |
Also Published As
Publication number | Publication date |
---|---|
CN101149097A (zh) | 2008-03-26 |
US20090025420A1 (en) | 2009-01-29 |
JP2007187420A (ja) | 2007-07-26 |
JP4120680B2 (ja) | 2008-07-16 |
CN101360961A (zh) | 2009-02-04 |
CN101360961B (zh) | 2012-05-23 |
KR20080071588A (ko) | 2008-08-04 |
AU2007205443A1 (en) | 2007-07-19 |
KR100973916B1 (ko) | 2010-08-03 |
EP1975525A1 (en) | 2008-10-01 |
EP1975525A4 (en) | 2014-07-23 |
CN101149097B (zh) | 2011-11-16 |
AU2007205443B2 (en) | 2010-05-27 |
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