WO2009122706A1 - 冷凍装置 - Google Patents
冷凍装置 Download PDFInfo
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- WO2009122706A1 WO2009122706A1 PCT/JP2009/001441 JP2009001441W WO2009122706A1 WO 2009122706 A1 WO2009122706 A1 WO 2009122706A1 JP 2009001441 W JP2009001441 W JP 2009001441W WO 2009122706 A1 WO2009122706 A1 WO 2009122706A1
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- WIPO (PCT)
- Prior art keywords
- refrigerant
- superheat degree
- change
- unit
- value
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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
- F25B13/00—Compression machines, plants or systems, with reversible cycle
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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
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
- F25B2313/0233—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel arrangements
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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
- 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
- F25B2313/0272—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using bridge circuits of one-way valves
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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
- 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
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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
- F25B2600/02—Compressor control
- F25B2600/021—Inverters therefor
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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
- F25B2600/21—Refrigerant outlet evaporator temperature
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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
- F25B2600/25—Control of valves
- F25B2600/2513—Expansion valves
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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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2117—Temperatures of an evaporator
- F25B2700/21171—Temperatures of an evaporator of the fluid cooled by the evaporator
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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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2117—Temperatures of an evaporator
- F25B2700/21174—Temperatures of an evaporator of the refrigerant at the inlet of the evaporator
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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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2117—Temperatures of an evaporator
- F25B2700/21175—Temperatures of an evaporator of the refrigerant at the outlet of the evaporator
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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
- 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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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
Definitions
- the present invention relates to a refrigeration apparatus including a refrigerant circuit that performs a refrigeration cycle, and more particularly to an operation control technology of a refrigeration apparatus including a refrigerant circuit to which a plurality of evaporators are connected.
- the target superheat degree is set lower than the current value. Then, a deviation occurs between the current refrigerant outlet superheat degree and the target superheat degree, and the opening of the indoor expansion valve is increased so as to reduce this deviation.
- the target degree of superheat is set higher than the current level. Then, a deviation occurs between the current refrigerant outlet superheat degree and the target superheat degree, and the opening of the indoor expansion valve is reduced so as to reduce this deviation.
- the heat exchange of each indoor unit is performed so that the indoor temperature of each indoor unit approaches the indoor set temperature.
- the set temperature is not determined in consideration of the power consumption of the compressor necessary for obtaining the heat exchange amount. For this reason, depending on the operating state of the refrigeration system, there is a problem that the power consumption of the compressor increases with respect to the desired heat exchange amount.
- a first invention includes a refrigerant circuit (21) having a variable capacity compressor (21), a plurality of evaporators (27), and an expansion mechanism (26) corresponding to each of the evaporators (27) for performing a refrigeration cycle ( 20), a capacity adjusting unit (6) for adjusting the capacity of the compressor (21) so that the evaporation temperature Te of the refrigerant circulating in the refrigerant circuit (20) approaches a predetermined set temperature Tem, Decompression of the refrigerant passing through the expansion mechanism (26) so that the refrigerant outlet superheat degree SH of the evaporator (27) approaches the target superheat degree SHs determined based on the heat exchange amount required for each of the evaporators (27). It is premised on a refrigeration apparatus including a decompression amount adjusting unit (9) for adjusting the amount.
- the capacity adjustment unit (6) decreases the capacity of the compressor (21) so that the current evaporation temperature Te approaches the set temperature Tem. Thereby, the power consumption of a compressor (21) can be made small compared with the change before setting temperature Tem.
- the decompression amount adjusting unit (9) sets the target superheat degree SHs to a value lower than the current value so as to compensate for the reduced heat exchange amount, and the current refrigerant outlet superheat degree SH is set to the set target superheat degree SHs.
- the pressure reduction amount of the refrigerant passing through the expansion mechanism (26) is reduced so that As a result, since the flow rate of the refrigerant flowing through each evaporator (27) increases, it is possible to prevent the heat exchange amount of each evaporator (27) from decreasing more than before changing the set temperature Tem.
- the predetermined value SHt is a lower limit value of the minimum target superheat degree SHsm when the change of the set temperature Tem is permitted. Therefore, the predetermined value SHt is preferably set to a value that does not allow the compressor (21) to perform a wet operation after the set temperature Tem is changed. Further, based on the relationship between the refrigerant outlet superheat degree SH and COP as shown in FIG. 3, the predetermined value SHt may be set so as to obtain the desired COP.
- the changing section (5) is based on a deviation between a smallest value and a predetermined value SHt among the target superheat degrees SHs determined for each of the evaporators (27).
- a determination unit (5a) for determining the amount of change of the set temperature Tem is provided.
- the changing unit (5) is configured to change the set temperature Tem to a value higher than the current value by the amount of change determined by the determining unit (5a).
- the change unit (5) is configured such that the evaporator (27) having a relatively large capacity among the plurality of evaporators (27) has the smallest target superheat degree SHs.
- the determination unit (5a) A correction unit (5b) for correcting the determined change amount to a small value is provided.
- the change amount determined by the determination unit (5a) can be corrected based on the capacity of the evaporator (27) having the minimum target superheat degree SHsm.
- the heat exchange amount of each evaporator (27) is set by providing the said change part (5)
- the power consumption of the compressor (21) can be made smaller than before the change of the set temperature Tem, while preventing the temperature Tem from decreasing before the change.
- the predetermined value SHt is preferably set to a value smaller than that of the chlorofluorocarbon refrigerant.
- the amount of change when the set temperature Tem is changed to a value higher than the present value can be set based on the deviation between the minimum target superheat degree SHsm and the predetermined value SHt. . Therefore, according to the operating condition of the refrigeration system, the power consumption of the compressor (21) for obtaining the heat exchange amount necessary for each evaporator is appropriately suppressed so that the coefficient of performance of the refrigeration system does not decrease. Can do.
- the change amount determined by the determination unit (5a) can be corrected based on the capacity of the evaporator (27) having the minimum target superheat degree SHsm. Therefore, according to the capacity
- the refrigerant outlet superheat degree SH becomes large as compared with the chlorofluorocarbon refrigerant, the refrigerant outlet superheat degree SH is controlled so as not to increase when the refrigerant outlet superheat degree SH becomes extremely small as in the refrigeration apparatus using carbon dioxide. As a result, the coefficient of performance of the refrigeration apparatus can be prevented from decreasing.
- FIG. 1 is a refrigerant circuit diagram of an air conditioner according to an embodiment of the present invention.
- FIG. 2 is a block diagram showing the configuration of the controller.
- FIG. 3 is a graph showing the relationship between the degree of superheat and COP.
- FIG. 1 shows a refrigerant circuit diagram in the air-conditioning apparatus of the present embodiment.
- the air conditioner (refrigeration apparatus) (10) of the present embodiment is a multi-type air conditioner including an outdoor unit (11) and a plurality of indoor units (12), and is configured to be capable of cooling and heating operations. Yes.
- the outdoor unit (11) is installed outdoors, and each indoor unit (12) is installed for each indoor space.
- the air conditioner (10) includes a refrigerant circuit (20), a controller (1), and a remote controller (7) corresponding to each indoor unit (12).
- the compressor (21) has a discharge side connected to the first port of the four-way switching valve (22) and a suction side connected to the second port of the four-way switching valve (22).
- the outdoor heat exchanger (23), the outdoor expansion valve (24), the check valve bridge circuit (in order from the third port to the fourth port of the four-way switching valve (22) 34), a receiver (25), an indoor expansion valve (26), and an indoor heat exchanger (27) are arranged in this order.
- Two indoor heat exchangers (27) are provided, and the indoor heat exchangers (27) are arranged in parallel with each other.
- An indoor expansion valve (26) is provided for each indoor heat exchanger (27).
- the check valve bridge circuit (34) includes first to fourth check valves (CV1, CV2, CV3, CV4), and the check valves are connected to each other by refrigerant piping as shown in FIG. ing.
- a refrigerant pipe extending from the outdoor expansion valve (24) is connected between the first check valve (CV1) and the fourth check valve (CV4).
- Refrigerant piping extending from each indoor expansion valve (26) joins and is connected between the second check valve (CV2) and the third check valve (CV3).
- the refrigerant pipe extending from the refrigerant inlet provided in the receiver (25) is connected between the third check valve (CV3) and the fourth check valve (CV4).
- a refrigerant pipe extending from a refrigerant outlet provided in the receiver (25) is connected between the first check valve (CV1) and the second check valve (CV2).
- the first check valve (CV1) is in a direction allowing the flow from the refrigerant outlet of the receiver (25) to the outdoor heat exchanger (23), and the second check valve (CV2) is in the receiver (25).
- the third check valve (CV3) allows the flow from each indoor expansion valve (26) to the refrigerant inlet of the receiver (25) in a direction that allows the flow from the refrigerant outlet to each indoor expansion valve (26).
- the fourth check valve (CV4) is attached in such a direction as to allow the flow from the outdoor heat exchanger (23) to the refrigerant inlet of the receiver (25).
- the indoor heat exchanger (27) serves as a condenser
- the outdoor heat exchanger (23) Each function as an evaporator.
- the refrigerant circuit (20) is provided with an indoor temperature sensor (31), a first refrigerant temperature sensor (32), and a second refrigerant temperature sensor (33).
- the indoor temperature sensor (31) detects the indoor air suction temperature Ta in the indoor heat exchanger (27).
- the first refrigerant temperature sensor (32) detects the refrigerant outlet temperature Tout of the indoor heat exchanger (27) when the refrigerant circulates in the cooling cycle in the refrigerant circuit (20).
- the second refrigerant temperature sensor (33) detects the refrigerant outlet temperature of the indoor heat exchanger (27) when the refrigerant circulates in the heating cycle in the refrigerant circuit (20).
- the refrigerant circuit (20) is provided with a high pressure sensor (36) for detecting the high pressure of the refrigerant circuit (20) and a low pressure sensor (35) for detecting the low pressure of the refrigerant circuit (20). ing.
- the four-way selector valve (22) is set to the second state.
- the outdoor heat exchanger (23) serves as an evaporator
- each indoor heat exchanger (27) serves as a radiator to perform a heating cycle.
- the refrigerant compressed to the supercritical region by the compressor (21) is discharged from the compressor (21).
- the refrigerant discharged from the compressor (21) branches after passing through the four-way switching valve (22) and flows to the indoor heat exchanger (27).
- the refrigerant flowing into the indoor heat exchanger (27) flows out of the indoor heat exchanger (27) after radiating heat to the indoor air.
- the room air is heated by heat radiation, and the heated room air is supplied into the room.
- the refrigerant that has flowed out of the indoor heat exchanger (27) flows into the indoor expansion valve (26).
- the refrigerant flowing into the indoor expansion valve (26) is depressurized from the supercritical region to a predetermined pressure, and then flows out of the indoor expansion valve (26).
- the superheat degree setting unit (4b) When the air conditioner (10) starts operation, the superheat degree setting unit (4b) outputs a predetermined value SHt serving as a threshold for determining whether or not to allow the change of the set temperature Tem. It is configured.
- the deviation e3 is calculated based on the minimum target superheat degree SHsm output from the minimum target superheat degree calculation unit (3) and the predetermined value SHt output from the superheat degree setting unit (4b). Specifically, the deviation e3 is a value obtained by subtracting a predetermined value SHt from the minimum target superheat degree SHsm, and this deviation e3 is input to the changing unit (5) together with the capacity value m.
- the determination unit (5a) has a function in which the relationship between the input deviation e3 and the setting change temperature Tes ′ before correction is predetermined. Based on this function, the deviation e3 is converted to a setting change temperature Tes' before correction.
- the setting change temperature Tes is obtained by integrating the correction rate to the setting change temperature Tes ′ before correction determined by the determination unit (5a). That is, when the capacity of the indoor heat exchanger (27) having the minimum target superheat degree SHsm is large, the setting change temperature Tes ′ before correction is corrected to a larger value, and the indoor heat exchange having the minimum target superheat degree SHsm is corrected. When the capacity of the container (27) is small, the setting change temperature Tes ′ before correction is corrected to a smaller value. And the said change part (5) outputs setting correction temperature Tes about this correct
Abstract
Description
2 過熱度算出部
3 最小目標過熱度算出部
4a 蒸発温度設定部
4b 過熱度設定部
5 変更部
5a 決定部
5b 補正部
6 インバータ制御部(容量調整部)
7 リモコン
8 目標過熱度設定部
9 膨張弁制御部(開度調整部)
10 空気調和装置
11 室外機
12 室内機
20 冷媒回路
21 圧縮機
22 四路切換弁
23 室外熱交換器
24 室外膨張弁
25 レシーバ
26 室内膨張弁(膨張弁)
27 室内熱交換器(蒸発器)
31 室内温度センサ
32 第1冷媒温度センサ
33 第2冷媒温度センサ
34 逆止弁ブリッジ回路
35 低圧圧力センサ
36 高圧圧力センサ
上記冷媒回路(20)は、冷媒として二酸化炭素が充填された閉回路であり、該冷媒回路(20)の高圧圧力が二酸化炭素の臨界圧力以上の値に設定される超臨界冷凍サイクルを行うように構成されている。
上記コントローラ(1)は、空気調和装置(10)の運転制御を行うものである。上記コントローラ(1)には、空気調和装置(10)の各部に設けられたセンサ類、及び空気調和装置(10)の運転指令を行うリモコン(7)が電気配線を介して接続されている。また、上記コントローラ(1)には、圧縮機(21)、インバータ、四路切換弁(22)、室外膨張弁(24)、室内膨張弁(26)等のアクチュエータ類が電気配線を介してそれぞれ接続されている。
〈冷房運転〉
次に、上記空気調和装置(10)の運転動作について説明する。
暖房運転時には、四路切換弁(22)が第2状態に設定される。そして、この状態で圧縮機(21)を起動すると、室外熱交換器(23)が蒸発器となり、各室内熱交換器(27)が放熱器となって暖房サイクルが行われる。
次に、冷房運転時に行われる運転制御について、図2を用いて説明する。まず、上記冷媒出口過熱度制御と上記圧縮機容量制御について説明した後、蒸発温度の設定変更制御について説明する。
本実施形態によれば、従来の空気調和装置とは違い、各室内熱交換器(27)の目標過熱度SHsに基づいて、設定温度Temを現在よりも高い値である設定変更温度Tesに変更することができる。そして、この設定変更温度Tesに蒸発温度Teが近づくことにより、各室内熱交換器(27)の熱交換量を設定温度Temの変更前よりも減少しないようにしつつ、圧縮機(21)の消費電力を設定温度Temの変更前に比べて小さくすることができる。したがって、複数の室内熱交換器(27)を有する冷媒回路(20)を備えた空気調和装置において、各室内熱交換器(27)に必要な熱交換量を得るための圧縮機(21)の消費電力をできるだけ抑えて、空気調和装置の成績係数(COP)が低下しないようにすることができる。
上記実施形態については、以下のような構成としてもよい。
Claims (4)
- 容量可変な圧縮機(21)と複数の蒸発器(27)と該各蒸発器(27)に対応する膨張機構(26)とを有して冷凍サイクルを行う冷媒回路(20)と、
該冷媒回路(20)を循環する冷媒の蒸発温度Teが予め定められた設定温度Temに近づくように圧縮機(21)の容量を調整する容量調整部(6)と、
上記各蒸発器(27)の冷媒出口過熱度SHが上記各蒸発器(27)に必要な熱交換量に基づいて定められた目標過熱度SHsに近づくように膨張機構(26)を通過する冷媒の減圧量を調整する減圧量調整部(9)とを備えた冷凍装置であって、
上記各蒸発器(27)ごとに定められた目標過熱度SHsのうち最も小さな値が所定値SHtよりも大きい場合には、上記設定温度Temを現在よりも高い値に変更する変更部(5)を備えていることを特徴とする冷凍装置。 - 請求項1において、
上記変更部(5)は、上記各蒸発器(27)ごとに定められた目標過熱度SHsのうち最も小さな値と所定値SHtとの偏差に基づいて、設定温度Temの変更量を決定する決定部(5a)を備え、
上記変更部(5)は、決定部(5a)が決定した変更量の分だけ設定温度Temを現在よりも高い値に変更するように構成されていることを特徴とする冷凍装置。 - 請求項2において、
上記変更部(5)は、複数の蒸発器(27)のうち相対的に大きい容量の蒸発器(27)が最も小さな目標過熱度SHsを有する場合に、上記決定部(5a)が決定した変更量を大きい値に補正し、相対的に小さい容量の蒸発器(27)が最も小さな目標過熱度SHsを有する場合に、上記決定部(5a)が決定した変更量を小さい値に補正する補正部(5b)を備えていることを特徴とする冷凍装置。 - 請求項1から3の何れか1つにおいて、
上記冷媒回路(20)を循環する冷媒は、二酸化炭素であることを特徴とする冷凍装置。
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP09726535.9A EP2270405B1 (en) | 2008-03-31 | 2009-03-30 | Refrigerating device |
CN2009801118101A CN101981389B (zh) | 2008-03-31 | 2009-03-30 | 制冷装置 |
ES09726535.9T ES2642164T3 (es) | 2008-03-31 | 2009-03-30 | Dispositivo de refrigeración |
US12/935,355 US8572995B2 (en) | 2008-03-31 | 2009-03-30 | Refrigeration system |
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EP (1) | EP2270405B1 (ja) |
JP (1) | JP5045524B2 (ja) |
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US8572995B2 (en) | 2013-11-05 |
CN101981389A (zh) | 2011-02-23 |
EP2270405A4 (en) | 2014-06-18 |
JP2009243810A (ja) | 2009-10-22 |
US20110023534A1 (en) | 2011-02-03 |
CN101981389B (zh) | 2012-11-14 |
EP2270405A1 (en) | 2011-01-05 |
EP2270405B1 (en) | 2017-08-30 |
JP5045524B2 (ja) | 2012-10-10 |
ES2642164T3 (es) | 2017-11-15 |
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