WO2008072608A1 - 冷凍装置 - Google Patents
冷凍装置 Download PDFInfo
- Publication number
- WO2008072608A1 WO2008072608A1 PCT/JP2007/073820 JP2007073820W WO2008072608A1 WO 2008072608 A1 WO2008072608 A1 WO 2008072608A1 JP 2007073820 W JP2007073820 W JP 2007073820W WO 2008072608 A1 WO2008072608 A1 WO 2008072608A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- refrigerant
- pressure
- heat source
- pseudo
- temperature
- Prior art date
Links
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
- 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
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- 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
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- 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
- F25B2500/00—Problems to be solved
- F25B2500/19—Calculation of parameters
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- 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
- F25B2600/17—Control issues by controlling the pressure of the condenser
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- 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
- F25B2600/19—Refrigerant outlet condenser 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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2102—Temperatures at the outlet of the gas cooler
Definitions
- the present invention relates to a refrigeration apparatus, and more particularly to a refrigeration apparatus that performs a refrigeration cycle operation in which a high-pressure side becomes a pressure exceeding a critical pressure of a refrigerant.
- the refrigerant temperature at the outlet of the cooler is The refrigerant pressure range on the high pressure side where the coefficient of performance is near the maximum is defined as the set value of the refrigerant pressure on the high pressure side, and the opening of the throttle means is controlled so that the refrigerant pressure on the high pressure side becomes the set value.
- Patent Document 1 Patent No. 3679323
- the refrigerant temperature at the outlet of the cooler changes when the opening degree of the throttle means is controlled so that the refrigerant pressure on the high pressure side becomes a set value.
- the refrigerant pressure range on the high pressure side where the coefficient of performance is near the maximum also changes, so that the refrigerant pressure set value on the high pressure side after the refrigerant temperature at the outlet of the cooler changes is set.
- the set value of the high pressure side refrigerant pressure changes due to the control of the opening of the throttle means, etc. There is a problem that it takes time until.
- An object of the present invention is to enable a high-efficiency operation to be performed quickly in a refrigeration apparatus that performs a refrigeration cycle operation in which the high-pressure side becomes a pressure exceeding the critical pressure of the refrigerant.
- a refrigeration apparatus according to a first invention has a refrigerant circuit including a compressor, a cooler, an expansion mechanism, and a heater, and a refrigeration cycle operation in which a high pressure side becomes a pressure exceeding a critical pressure of the refrigerant.
- the refrigerant temperature at which the constant pressure specific heat of the refrigerant at the refrigerant pressure on the high pressure side of the refrigeration cycle is the maximum pseudo-condensation temperature, and this pseudo-condensation temperature and the refrigerant temperature at the outlet of the cooler
- the component devices are controlled so that the pseudo supercooling degree, which is the temperature difference between the two, falls within a predetermined temperature range.
- the refrigeration apparatus which is the power of the second invention, is the power of the first invention.
- the predetermined temperature range is set within a temperature range of 5 ° C to 12 ° C! / RU
- the inventor of the present application has found that the coefficient of performance is close to the maximum when the pseudo supercooling degree is within a temperature range of 5 ° C to 12 ° C. Therefore, in this refrigeration system, using such knowledge, a predetermined temperature range of the pseudo supercooling degree is obtained. By setting the temperature within the range of C to 12 ° C, high-efficiency operation with a maximum coefficient of performance is achieved.
- the refrigeration apparatus that is strong in the third invention uses the expansion mechanism as a constituent device in the refrigeration apparatus that is strong in the first or second invention.
- FIG. 1 is a schematic configuration diagram of an air conditioner as an embodiment of a refrigeration apparatus according to the present invention.
- FIG. 2 is a pressure-enthalpy diagram illustrating the refrigeration cycle.
- FIG. 3 is a graph showing the relationship between the pseudo supercooling degree and the coefficient of performance.
- FIG. 1 is a schematic configuration diagram of an air conditioner 1 as an embodiment of a refrigeration apparatus according to the present invention.
- the air conditioner 1 is an apparatus used for indoor air conditioning by performing a vapor compression refrigeration cycle operation.
- the air conditioner 1 includes a first refrigerant communication pipe 6 and a second refrigerant communication pipe 7 as refrigerant communication pipes that connect the heat source unit 2, the utilization unit 4, and the heat source unit 2 and the utilization unit 4.
- the vapor compression refrigerant circuit 10 of the air conditioner 1 of the present embodiment is configured by connecting the heat source unit 2, the utilization unit 4, and the refrigerant communication pipes 6 and 7.
- carbon dioxide is sealed as a refrigerant.
- the refrigerant circuit 10 is compressed to a pressure exceeding the critical pressure of the refrigerant, cooled, depressurized, heated and evaporated, and then compressed again.
- the refrigeration cycle operation is performed.
- the usage unit 4 is installed indoors, etc., and is connected to the heat source unit via the refrigerant communication pipes 6 and 7. 2 and is part of the refrigerant circuit 10.
- the usage unit 4 mainly has a usage-side refrigerant circuit 10 a that constitutes a part of the refrigerant circuit 10.
- the use side refrigerant circuit 10 a mainly has a use heat exchanger 41.
- the use-side heat exchanger 41 is a heat exchanger that functions as a refrigerant heater or cooler. One end of the use heat exchanger 41 is connected to the first refrigerant communication pipe 6, and the other end is connected to the second refrigerant communication pipe 7.
- the usage unit 4 includes a usage-side fan 42 for sucking indoor air into the unit and supplying it to the room again.
- the usage unit 4 includes a refrigerant flowing through the usage-side heat exchanger 41 and the indoor air. It is possible to exchange heat.
- the use side fan 42 is rotationally driven by a use side fan drive motor 42a.
- the utilization unit 4 is provided with various sensors. Specifically, when the use-side heat exchanger 41 is functioned as a refrigerant cooler, the use-side heat exchanger 41 that detects the cooler outlet refrigerant temperature Tco is provided at the outlet of the use-side heat exchanger 41. Sensor 43 is provided. In the present embodiment, the use side heat exchanger temperature sensor 43 is a thermistor.
- the usage unit 4 includes a usage-side control unit 44 that controls the operation of each unit constituting the usage unit 4.
- the usage-side control unit 44 includes a microcomputer, a memory, and the like provided for controlling the usage unit 4, and a remote controller (not shown) for operating the usage unit 4 individually. Control signals etc. can be exchanged between them, and control signals etc. can be exchanged with the heat source unit 2 via the transmission line 8a.
- the heat source unit 2 is installed outside the room and connected to the usage unit 4 via the refrigerant communication pipes 6 and 7, and the refrigerant circuit 10 is configured between the usage units 4.
- the heat source unit 2 mainly has a heat source side refrigerant circuit 10b that constitutes a part of the refrigerant circuit 10.
- the heat source side refrigerant circuit 10b mainly includes a compressor 21, a switching mechanism 22, a heat source side heat exchanger 23, a heat source side expansion mechanism 24, a first closing valve 25, and a second closing valve 26.
- the compressor 21 is a hermetic compressor driven by a compressor drive motor 21a.
- the switching mechanism 22 is a mechanism for switching the flow direction of the refrigerant in the refrigerant circuit 10, and during cooling, the heat source side heat exchanger 23 is used as a refrigerant cooler compressed by the compressor 21 and used.
- the side heat exchanger 41 In order for the side heat exchanger 41 to function as a heater for the refrigerant cooled in the heat source side heat exchanger 23, the discharge side of the compressor 21 and one end of the heat source side heat exchanger 23 are connected and the compressor 21 The suction side and the second shut-off valve 26 are connected (see the solid line of the switching mechanism 22 in FIG. 1).
- the use side heat exchanger 41 is used as a refrigerant cooler compressed by the compressor 21, and In order for the heat source side heat exchanger 23 to function as a heater for the refrigerant cooled in the use side heat exchanger 41, the discharge side of the compressor 21 and the second closing valve 26 are connected and the suction of the compressor 21 is connected. Side and one end of the heat source side heat exchanger 23 can be connected A capacity (see dashed switching mechanism 22 in FIG. 1).
- the switching mechanism 22 is a four-way switching valve connected to the suction side of the compressor 21, the discharge side of the compressor 21, the heat source side heat exchanger 23, and the second closing valve 26.
- the switching mechanism 22 is not limited to a four-way switching valve.
- the switching mechanism 22 has a function of switching the flow direction of the refrigerant as described above by combining a plurality of solenoid valves.
- the heat source side heat exchanger 23 is a heat exchanger that functions as a refrigerant cooler or a heater. One end of the heat source side heat exchanger 23 is connected to the switching mechanism 22, and the other end is connected to the heat source side expansion mechanism 24! /.
- the heat source unit 2 has a heat source side fan 27 for sucking outdoor air into the unit and discharging it outside the room again.
- the heat source side fan 27 can exchange heat between the outdoor air and the refrigerant flowing through the heat source side heat exchanger 23.
- the heat source side fan 27 is rotationally driven by a use side fan drive motor 27a.
- the heat source of the heat source side heat exchanger 23 may be another heat medium such as water, which is not limited to outdoor air.
- the heat source side expansion mechanism 24 is a mechanism for decompressing the refrigerant.
- the heat source side heat exchange is performed in order to adjust the flow rate of the refrigerant flowing in the heat source side refrigerant circuit 10b.
- This is an electric expansion valve connected to the other end of the vessel 23.
- One end of the heat source side expansion mechanism 24 is connected to the heat source side heat exchanger 23, and the other end is connected to the first closing valve 25.
- the first closing valve 25 is a valve to which a first refrigerant communication pipe 6 for exchanging refrigerant between the heat source unit 2 and the utilization unit 4 is connected, and is connected to the heat source side expansion mechanism 24. Yes.
- the second closing valve 26 is a valve to which a second refrigerant communication pipe 7 for exchanging refrigerant between the heat source unit 2 and the utilization unit 4 is connected, and is connected to the switching mechanism 22.
- the first and second shut-off valves 25 and 26 are three-way valves provided with service ports that can communicate with the outside of the refrigerant circuit 10.
- the heat source unit 2 is provided with various sensors. Specifically, a compressor discharge pressure sensor 28 for detecting the compressor discharge pressure Pd is provided on the discharge side of the compressor 21, and the heat source side heat exchanger 23 functions as a refrigerant cooler. In this case, a heat source side heat exchanger temperature sensor 29 for detecting the cooler outlet refrigerant temperature Tco is provided at the outlet of the heat source side heat exchanger 23. In the present embodiment, the heat source side heat exchanger temperature sensor 29 is a thermistor. Further, the heat source unit 2 includes a heat source side control unit 30 that controls the operation of each unit constituting the heat source unit 2. The heat source side control unit 30 includes a microcomputer, a memory, and the like provided for controlling the heat source unit 2, and is connected to the use side control unit 44 of the IJ unit 4. The control signal can be exchanged via the transmission line 8a.
- Refrigerant communication pipes 6 and 7 are refrigerant pipes installed on site when the air conditioner 1 is installed at the installation site.
- the refrigerant circuit 10 is configured by connecting the use side refrigerant circuit 10a, the heat source side refrigerant circuit 10b, and the refrigerant communication pipes 6 and 7.
- the air conditioner 1 of the present embodiment is a control that performs various operation controls of the air conditioner 1 by the use side control unit 44, the heat source side control unit 30, and the transmission line 8a that connects the control units 30 and 44.
- a control unit 8 is configured as a means.
- the control unit 8 can receive the detection signals of the various sensors 29 and 30, and can control the various component devices 21, 22, 24, 27, and 42 based on the detection signals. It's like! / [0016] (2) Operation of the air conditioner
- FIG. 2 is a pressure entry ruby diagram illustrating the refrigeration cycle in the present embodiment.
- the switching mechanism 22 is in the state indicated by the solid line in FIG. 1, that is, the discharge side of the compressor 21 is connected to the heat source side heat exchanger 23, and the suction side of the compressor 21 is connected to the second closing valve 26. It has become a state.
- the opening degree of the heat source side expansion mechanism 24 is adjusted.
- the shut-off valves 25 and 26 are opened.
- the low-pressure refrigerant (see point A in FIG. 2) is sucked into the compressor 21 and the critical pressure (that is, Then, it is compressed to a pressure exceeding Pep) in Fig. 2 and becomes a high-pressure refrigerant (see point B in Fig. 2). Thereafter, the high-pressure refrigerant is sent via the switching mechanism 22 to the heat source side heat exchanger 23 that functions as a refrigerant cooler, and performs heat exchange with the outdoor air supplied by the heat source side fan 27. It is cooled (see point C in Figure 2).
- the high-pressure refrigerant cooled in the heat-source side heat exchanger 23 is reduced in pressure by the heat-source side expansion mechanism 24 to become a low-pressure gas-liquid two-phase refrigerant (see point D in FIG. 2), and the first closing valve 25 And is sent to the utilization unit 4 via the first refrigerant communication pipe 6.
- the low-pressure gas-liquid two-phase refrigerant sent to the utilization unit 4 evaporates by being heated by exchanging heat with room air in the utilization-side heat exchanger 41 functioning as a refrigerant heater. It becomes a low-pressure refrigerant (see point A in Fig. 2).
- the low-pressure refrigerant heated by the use-side heat exchanger 41 is sent to the heat source unit 2 via the second refrigerant communication pipe 7, and the second closing valve 26 and the switching mechanism 22 are sent to the heat source unit 2. Then, it is sucked into the compressor 21 again. In this way, cooling is performed.
- the pseudo supercooling degree control using the heat source side expansion mechanism 24 is performed.
- This pseudo supercooling degree control is performed by the compressor pressure based on the refrigerant pressure on the high pressure side of the refrigeration cycle (here, the compressor discharge pressure Pd detected by the compressor discharge pressure sensor 28 or the compressor discharge pressure Pd). (The pressure calculated in consideration of the pressure loss from the discharge side to the heat source side heat exchanger 23))
- the temperature Tqc is a temperature difference between the pseudo condensing temperature Tqc and the refrigerant temperature at the outlet of the heat source side heat exchanger 23 (that is, the refrigerant outlet refrigerant temperature Tco detected by the heat source side heat exchanger temperature sensor 29).
- the degree of opening of the heat source side expansion mechanism 24 is adjusted so that the pseudo supercooling degree ATqsc is within a predetermined temperature range.
- FIG. 3 is a diagram showing the relationship between the pseudo supercooling degree ATqsc and the coefficient of performance.
- the refrigerant pressure range on the high pressure side where the coefficient of performance is near the maximum is defined as the set value of the refrigerant pressure on the high pressure side with respect to the refrigerant temperature Tco at the outlet of the cooler.
- the opening control of the heat source side expansion mechanism 24 is performed so that it becomes a set value, the refrigerant temperature Tco at the outlet of the cooler changes, and accordingly, the refrigerant pressure range on the high pressure side where the coefficient of performance is near the maximum also changes. Therefore, the opening degree of the heat source side expansion mechanism 24 must be repeatedly controlled so that the set value of the refrigerant pressure on the high pressure side after the cooler outlet refrigerant temperature Tco has changed, and the coefficient of performance is maximized. There is a problem that it takes time to get close.
- the present inventor examined the control amount in the refrigeration cycle having a correlation with the coefficient of performance in addition to the refrigerant pressure range on the high-pressure side with respect to the cooler outlet refrigerant temperature Tco, and as shown in FIG. We found that there was a correlation between the coefficient of performance and the pseudo supercooling degree ATqsc.
- the refrigerant temperature at which the constant pressure specific heat of the refrigerant becomes maximum is the pseudocondensation temperature Tqc (point E and boundary point Tcp in Fig. 2).
- the coefficient of performance would change around the maximum if the pseudo-supercooling degree ATqsc, which is the degree of cooling from the pseudo-condensation temperature Tqc, was within the specified temperature range.
- the predetermined temperature range of the pseudo supercooling degree ATqsc is within a temperature range of 5 ° C to 12 ° C as shown in FIG.
- a control method is employed in which one controlled variable, the pseudo supercooling degree ATqsc, is controlled within a predetermined temperature range.
- pseudo supercooling degree control is performed using the heat source side expansion mechanism 24, and the pseudo supercooling degree ATqsc is a lower limit value of a predetermined temperature range (for example, 5 ° C). If the temperature is smaller than), the opening degree of the heat source side expansion mechanism 24 is controlled to decrease, and the pseudo subcooling degree ATqsc increases the upper limit value of the predetermined temperature range (for example, 12 ° C). In addition, since the opening degree of the heat source side expansion mechanism 24 can be controlled to increase, the control responsiveness is good.
- the switching mechanism 22 is in the state shown by the broken line in FIG. 1, that is, the discharge side of the compressor 21 is connected to the second shut-off valve 26, and the suction side of the compressor 21 is connected to the heat source side heat exchanger 23. It has become a state.
- the opening degree of the heat source side expansion mechanism 24 is adjusted.
- the shut-off valves 25 and 26 are opened.
- the low-pressure refrigerant (see point A in FIG. 2) is sucked into the compressor 21 and the critical pressure (that is, Then, it is compressed to a pressure exceeding Pep) in Fig. 2 and becomes a high-pressure refrigerant (see point B in Fig. 2). Thereafter, the high-pressure refrigerant is sent to the utilization unit 4 via the switching mechanism 22, the second closing valve 26 and the second refrigerant communication pipe 7.
- the high-pressure refrigerant sent to the usage unit 4 is cooled by exchanging heat with room air in the usage-side heat exchanger 41 functioning as a refrigerant cooler (see point C in FIG. 2).
- the high-pressure refrigerant sent to the heat source unit 2 is depressurized by the heat-source side expansion mechanism 24 to become a low-pressure gas-liquid two-phase refrigerant (see point D in FIG. 2), and a heat source that functions as a refrigerant heater. It flows into the side heat exchanger 23. Then, the low-pressure gas-liquid two-phase refrigerant flowing into the heat source side heat exchanger 23 is supplied to the outdoor air supplied by the heat source side fan 27. The refrigerant evaporates into a low-pressure refrigerant (see point A in FIG. 2) and is sucked into the compressor 21 again via the switching mechanism 22. In this way, heating is performed.
- the pseudo supercooling degree control using the heat source side expansion mechanism 24 is performed!
- the pseudo condensing temperature Tqc and the refrigerant temperature at the outlet of the use side heat exchanger 41 that is, the refrigerant outlet refrigerant temperature Tco detected by the use side heat exchanger temperature sensor 43
- the difference between the temperature difference and the pseudo supercooling degree ATqsc is different from that during cooling Basically, the same control as during cooling can be performed. This operation can be realized quickly.
- the operation control in the cooling and heating including the pseudo supercooling degree control described above is performed by the control unit 8 functioning as the operation control unit. Specifically, the use side control unit 44, the heat source side control unit 30, and the control units 30, 44 This is done by the transmission line 8a) connecting them.
- the heat source side expansion mechanism 24 is used as a component device for performing the pseudo supercooling degree control.
- the compressor 21 is used and the compressor 21 is operated.
- the pseudo supercooling degree control may be performed by adjusting the capacity, and the pseudo supercooling degree may be controlled by adjusting the air volume of the heat source side fan 27 during cooling and using the heat source side fan 27.
- the use-side fan 42 may be used to adjust the air volume of the use-side fan 42 to perform the pseudo supercooling degree control.
- the present invention is applied to the separate air conditioner 1 in which the utilization unit 4 is connected to the heat source unit 2 via the refrigerant communication pipes 6 and 7.
- the present invention is not limited to this, and various refrigeration units are used.
- the present invention may be applied to an apparatus.
Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN2007800458323A CN101558267B (zh) | 2006-12-12 | 2007-12-11 | 制冷装置 |
EP07850386.9A EP2096377B1 (en) | 2006-12-12 | 2007-12-11 | Refrigeration apparatus |
ES07850386.9T ES2621156T3 (es) | 2006-12-12 | 2007-12-11 | Aparato de refrigeración |
US12/517,499 US7921670B2 (en) | 2006-12-12 | 2007-12-11 | Refrigeration apparatus |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2006-334042 | 2006-12-12 | ||
JP2006334042A JP4245044B2 (ja) | 2006-12-12 | 2006-12-12 | 冷凍装置 |
Publications (1)
Publication Number | Publication Date |
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WO2008072608A1 true WO2008072608A1 (ja) | 2008-06-19 |
Family
ID=39511629
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2007/073820 WO2008072608A1 (ja) | 2006-12-12 | 2007-12-11 | 冷凍装置 |
Country Status (6)
Country | Link |
---|---|
US (1) | US7921670B2 (ja) |
EP (1) | EP2096377B1 (ja) |
JP (1) | JP4245044B2 (ja) |
CN (2) | CN101858667B (ja) |
ES (1) | ES2621156T3 (ja) |
WO (1) | WO2008072608A1 (ja) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2009139014A (ja) * | 2007-12-06 | 2009-06-25 | Mitsubishi Electric Corp | 空気調和装置およびその運転制御方法 |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP5330074B2 (ja) * | 2009-04-24 | 2013-10-30 | パナソニック株式会社 | 床暖房パネル |
JP2011069570A (ja) * | 2009-09-28 | 2011-04-07 | Fujitsu General Ltd | ヒートポンプサイクル装置 |
WO2011099074A1 (ja) | 2010-02-12 | 2011-08-18 | 三菱電機株式会社 | 冷凍サイクル装置 |
CN108917133A (zh) * | 2018-07-27 | 2018-11-30 | 奥克斯空调股份有限公司 | 风机转速匹配方法、装置及空调器 |
CN112833522A (zh) * | 2019-11-22 | 2021-05-25 | 三花控股集团有限公司 | 一种控制系统及其控制方法 |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2001248920A (ja) * | 2000-03-06 | 2001-09-14 | Mitsubishi Electric Corp | 冷凍回路の制御装置 |
JP2004162945A (ja) * | 2002-11-11 | 2004-06-10 | Mitsubishi Electric Corp | 空気調和装置 |
Family Cites Families (21)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP3334507B2 (ja) * | 1996-09-13 | 2002-10-15 | 三菱電機株式会社 | 冷凍システム装置および冷凍システム装置の制御方法 |
US6321564B1 (en) * | 1999-03-15 | 2001-11-27 | Denso Corporation | Refrigerant cycle system with expansion energy recovery |
JP2001289537A (ja) * | 2000-04-10 | 2001-10-19 | Mitsubishi Heavy Ind Ltd | 圧力制御弁 |
EP1148307B1 (en) * | 2000-04-19 | 2004-03-17 | Denso Corporation | Heat-pump water heater |
JP4517529B2 (ja) * | 2000-07-21 | 2010-08-04 | 株式会社日本自動車部品総合研究所 | ヒートポンプサイクル、加熱装置、車両用暖房装置、暖房装置および蒸気圧縮式冷凍サイクル |
JP3679323B2 (ja) | 2000-10-30 | 2005-08-03 | 三菱電機株式会社 | 冷凍サイクル装置およびその制御方法 |
JP4492017B2 (ja) * | 2000-11-09 | 2010-06-30 | 株式会社デンソー | アキュムレータモジュール |
US6871511B2 (en) * | 2001-02-21 | 2005-03-29 | Matsushita Electric Industrial Co., Ltd. | Refrigeration-cycle equipment |
NO320664B1 (no) * | 2001-12-19 | 2006-01-16 | Sinvent As | System for oppvarming og kjoling av kjoretoy |
KR100567488B1 (ko) * | 2002-02-12 | 2006-04-03 | 마츠시타 덴끼 산교 가부시키가이샤 | 히트 펌프 급탕 장치 |
NO318864B1 (no) * | 2002-12-23 | 2005-05-18 | Sinvent As | Forbedret varmepumpesystem |
JP4232463B2 (ja) * | 2003-01-09 | 2009-03-04 | 株式会社デンソー | 空調装置 |
SE525022C2 (sv) * | 2003-04-17 | 2004-11-09 | Ep Technology Ab | Förångare och värmeväxlare med extern slinga |
US7127905B2 (en) * | 2003-12-19 | 2006-10-31 | Carrier Corporation | Vapor compression system startup method |
US7716943B2 (en) * | 2004-05-12 | 2010-05-18 | Electro Industries, Inc. | Heating/cooling system |
JP4179231B2 (ja) * | 2004-06-09 | 2008-11-12 | 株式会社デンソー | 圧力制御弁と蒸気圧縮式冷凍サイクル |
JP4118254B2 (ja) * | 2004-06-18 | 2008-07-16 | 三洋電機株式会社 | 冷凍装置 |
JP4613526B2 (ja) * | 2004-06-23 | 2011-01-19 | 株式会社デンソー | 超臨界式ヒートポンプサイクル装置 |
JP4581720B2 (ja) * | 2004-09-29 | 2010-11-17 | 株式会社デンソー | エジェクタを用いたサイクル |
JP4415835B2 (ja) * | 2004-11-24 | 2010-02-17 | 株式会社デンソー | 車両用冷凍サイクル装置 |
JP4799563B2 (ja) * | 2005-10-25 | 2011-10-26 | 三菱電機株式会社 | 空気調和装置、空気調和装置の冷媒充填方法、空気調和装置の冷媒充填状態判定方法、並びに空気調和装置の冷媒充填・配管洗浄方法 |
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2006
- 2006-12-12 JP JP2006334042A patent/JP4245044B2/ja active Active
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2007
- 2007-12-11 CN CN2010102110667A patent/CN101858667B/zh active Active
- 2007-12-11 WO PCT/JP2007/073820 patent/WO2008072608A1/ja active Application Filing
- 2007-12-11 US US12/517,499 patent/US7921670B2/en active Active
- 2007-12-11 EP EP07850386.9A patent/EP2096377B1/en active Active
- 2007-12-11 CN CN2007800458323A patent/CN101558267B/zh active Active
- 2007-12-11 ES ES07850386.9T patent/ES2621156T3/es active Active
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2001248920A (ja) * | 2000-03-06 | 2001-09-14 | Mitsubishi Electric Corp | 冷凍回路の制御装置 |
JP2004162945A (ja) * | 2002-11-11 | 2004-06-10 | Mitsubishi Electric Corp | 空気調和装置 |
Non-Patent Citations (1)
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See also references of EP2096377A4 * |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2009139014A (ja) * | 2007-12-06 | 2009-06-25 | Mitsubishi Electric Corp | 空気調和装置およびその運転制御方法 |
Also Published As
Publication number | Publication date |
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EP2096377B1 (en) | 2017-02-01 |
JP2008145066A (ja) | 2008-06-26 |
EP2096377A4 (en) | 2012-05-30 |
ES2621156T3 (es) | 2017-07-03 |
CN101558267A (zh) | 2009-10-14 |
CN101858667B (zh) | 2013-01-02 |
US7921670B2 (en) | 2011-04-12 |
US20100011805A1 (en) | 2010-01-21 |
EP2096377A1 (en) | 2009-09-02 |
CN101558267B (zh) | 2010-12-01 |
CN101858667A (zh) | 2010-10-13 |
JP4245044B2 (ja) | 2009-03-25 |
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