JP2016125736A - Storage air conditioner - Google Patents
Storage air conditioner Download PDFInfo
- Publication number
- JP2016125736A JP2016125736A JP2014266167A JP2014266167A JP2016125736A JP 2016125736 A JP2016125736 A JP 2016125736A JP 2014266167 A JP2014266167 A JP 2014266167A JP 2014266167 A JP2014266167 A JP 2014266167A JP 2016125736 A JP2016125736 A JP 2016125736A
- Authority
- JP
- Japan
- Prior art keywords
- heat storage
- heat exchanger
- refrigerant
- heat
- flow path
- 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.)
- Granted
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
-
- 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
- F24F11/00—Control or safety arrangements
- F24F11/89—Arrangement or mounting of control or safety devices
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
- F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary systems
-
- 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
- F25B41/22—Disposition of valves, e.g. of on-off valves or flow control valves between evaporator and compressor
-
- 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
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
-
- 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
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/003—Indoor unit with water as a heat sink or heat source
-
- 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
- F25B2313/0232—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units with bypasses
-
- 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
- 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
- F25B2400/24—Storage receiver heat
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Life Sciences & Earth Sciences (AREA)
- Sustainable Development (AREA)
- Air Conditioning Control Device (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
Description
この発明は、蓄熱式空気調和機に関する。 The present invention relates to a heat storage type air conditioner.
特許文献1に示すように、蓄熱媒体を冷熱源として利用して室内の空調を行う蓄熱式空気調和機が知られている。特許文献1では、蓄熱媒体を貯留する蓄熱タンクの中に、冷媒が通過する流路を有する蓄熱用熱交換器が配置されており、蓄熱媒体は、冷媒によって冷却される。蓄熱媒体としては、冷却によって包接水和物が生成される蓄熱材(例えば臭化テトラnブチルアンモニウム水溶液)が利用されている。また、特許文献1の蓄熱式空気調和機では、冷熱を蓄熱しつつ冷房を行う冷房蓄冷運転が行われる。 As shown in Patent Document 1, a heat storage type air conditioner that performs indoor air conditioning using a heat storage medium as a cold heat source is known. In Patent Document 1, a heat storage heat exchanger having a flow path through which a refrigerant passes is disposed in a heat storage tank that stores the heat storage medium, and the heat storage medium is cooled by the refrigerant. As the heat storage medium, a heat storage material (for example, an aqueous solution of tetra-n-butylammonium bromide) in which clathrate hydrate is generated by cooling is used. Moreover, in the heat storage type air conditioner of patent document 1, the air_conditioning | cooling storage operation which performs air_conditioning | cooling, storing cold heat is performed.
ところで、特許文献1に示された蓄熱式空気調和機において、蓄熱用熱交換器を蓄熱タンク(蓄熱槽)の外部に設置し、蓄熱用熱交換器と蓄熱タンクとの間を蓄熱媒体が循環する蓄熱回路を構成することが考えられる。このように構成した場合、冷房蓄冷運転が行われると、蓄熱タンクから蓄熱用熱交換器に流入した蓄熱媒体は、蓄熱用熱交換器を通過する間に蓄熱用熱交換器を流れる冷媒に吸熱されて冷却される。 By the way, in the heat storage type air conditioner shown in Patent Document 1, the heat storage heat exchanger is installed outside the heat storage tank (heat storage tank), and the heat storage medium circulates between the heat storage heat exchanger and the heat storage tank. It is conceivable to construct a heat storage circuit that performs this. In this configuration, when the cooling and regenerating operation is performed, the heat storage medium flowing into the heat storage heat exchanger from the heat storage tank absorbs heat into the refrigerant flowing through the heat storage heat exchanger while passing through the heat storage heat exchanger. To be cooled.
また、上記のような構成では、冷房蓄冷運転において、室内熱交換器における冷却能力(すなわち、冷房能力)を確保するために、圧縮機の吸入圧力を低下させて室内熱交換器における冷媒の蒸発圧力を低下させることが考えられる。例えば、室内熱交換器のガス端と圧縮機の吸入端との間の圧力損失が大きい場合(具体的には、室内熱交換器のガス端と圧縮機の吸入端との間の配管が長い場合や、室内熱交換器のガス端と圧縮機の吸入端との高低差が大きい場合など)、室内熱交換器における冷媒の蒸発圧力を冷房能力の確保のために必要な蒸発圧力に設定するために、圧縮機の吸入圧力が低めに設定される。また、室内の冷房負荷が増加して冷房能力が不足した場合、室内熱交換器における冷媒の蒸発圧力を低下させるために、圧縮機の吸入圧力が低くなる。 Further, in the above-described configuration, in the cooling storage operation, in order to secure the cooling capacity (that is, the cooling capacity) in the indoor heat exchanger, the suction pressure of the compressor is reduced to evaporate the refrigerant in the indoor heat exchanger. It is conceivable to reduce the pressure. For example, when the pressure loss between the gas end of the indoor heat exchanger and the suction end of the compressor is large (specifically, the piping between the gas end of the indoor heat exchanger and the suction end of the compressor is long) Or when the difference in elevation between the gas end of the indoor heat exchanger and the suction end of the compressor is large), the refrigerant evaporating pressure in the indoor heat exchanger is set to the evaporating pressure necessary for ensuring cooling capacity. Therefore, the suction pressure of the compressor is set low. Further, when the indoor cooling load increases and the cooling capacity is insufficient, the suction pressure of the compressor is lowered in order to reduce the evaporation pressure of the refrigerant in the indoor heat exchanger.
しかしながら、室内熱交換器における冷媒の蒸発圧力を低下させるために圧縮機の吸入圧力を低下させると、その圧縮機の吸入圧力の低下に伴って蓄熱用熱交換器における冷媒の蒸発圧力が低下して冷媒の蒸発温度が低下することになる。そのため、蓄熱用熱交換器において蓄熱媒体が冷却され過ぎて包接水和物(固体成分)が大量に生成され、その結果、蓄熱回路における蓄熱媒体の循環効率が低下するおそれがある。 However, if the suction pressure of the compressor is reduced to reduce the evaporation pressure of the refrigerant in the indoor heat exchanger, the evaporation pressure of the refrigerant in the heat storage heat exchanger decreases as the suction pressure of the compressor decreases. As a result, the evaporation temperature of the refrigerant decreases. Therefore, the heat storage medium is excessively cooled in the heat storage heat exchanger, and a large amount of clathrate hydrate (solid component) is generated. As a result, the circulation efficiency of the heat storage medium in the heat storage circuit may be reduced.
そこで、この発明は、冷房蓄冷運転において冷房能力を確保しつつ蓄熱媒体の循環効率の低下を抑制することが可能な蓄熱式空気調和機を提供することを目的とする。 Accordingly, an object of the present invention is to provide a regenerative air conditioner that can suppress a decrease in circulation efficiency of a heat storage medium while ensuring cooling capacity in a cooling and regenerating operation.
第1の発明は、圧縮機(21)と、室外熱交換器(22)と、室内熱交換器(27)と、該室外熱交換器(22)の液端および該室内熱交換器(27)の液端が接続される液冷媒流路(12)と、該室内熱交換器(27)のガス端が接続されるガス冷媒流路(13)と、一端が該液冷媒流路(12)に接続され他端が該ガス冷媒流路(13)に接続されるバイパス流路(14)とを有する冷媒回路(11)と、冷却により固体成分が生成される蓄熱媒体が流れる蓄熱回路(31)と、上記バイパス流路(14)と上記蓄熱回路(31)とに接続され、該バイパス流路(14)を流れる冷媒と該蓄熱回路(31)を流れる蓄熱媒体とを熱交換させる蓄熱用熱交換器(43)と、上記バイパス流路(14)において上記蓄熱用熱交換器(43)と上記ガス冷媒流路(13)との間に設けられる圧力調節機構(44)とを備え、上記冷媒回路(11)では、上記圧縮機(21)の吐出端が上記室外熱交換器(22)のガス端に接続され、該圧縮機(21)の吸入端が上記ガス冷媒流路(13)に接続され、該室外熱交換器(22)が凝縮器となり上記室内熱交換器(27)および上記蓄熱用熱交換器(43)が蒸発器となる冷房蓄冷サイクルが行われ、上記圧力調節機構(44)が、上記蓄熱用熱交換器(43)と上記ガス冷媒流路(13)との間を流れる冷媒の圧力を調節可能に構成されていることを特徴とする蓄熱式空気調和機である。 The first invention includes a compressor (21), an outdoor heat exchanger (22), an indoor heat exchanger (27), a liquid end of the outdoor heat exchanger (22), and the indoor heat exchanger (27 ) Is connected to the liquid refrigerant channel (12), the gas refrigerant channel (13) is connected to the gas end of the indoor heat exchanger (27), and one end is the liquid refrigerant channel (12). ) And a refrigerant circuit (11) having a bypass channel (14) whose other end is connected to the gas refrigerant channel (13), and a heat storage circuit in which a heat storage medium in which a solid component is generated by cooling flows ( 31), heat storage that is connected to the bypass passage (14) and the heat storage circuit (31), and exchanges heat between the refrigerant flowing through the bypass passage (14) and the heat storage medium flowing through the heat storage circuit (31). Pressure exchanger (43) and a pressure adjusting mechanism (4) provided between the heat storage heat exchanger (43) and the gas refrigerant channel (13) in the bypass channel (14) 4), in the refrigerant circuit (11), the discharge end of the compressor (21) is connected to the gas end of the outdoor heat exchanger (22), and the suction end of the compressor (21) A cooling and regenerating cycle is connected to the gas refrigerant flow path (13), and the outdoor heat exchanger (22) serves as a condenser and the indoor heat exchanger (27) and the heat storage heat exchanger (43) serve as an evaporator. Wherein the pressure adjusting mechanism (44) is configured to be capable of adjusting the pressure of the refrigerant flowing between the heat storage heat exchanger (43) and the gas refrigerant channel (13). It is a regenerative air conditioner.
上記第1の発明では、圧力調節機構(44)を設けることにより、冷房蓄冷運転(すなわち、冷媒回路(11)において冷房蓄冷サイクルが行われる場合)において、圧縮機(21)の吸入圧力よりも高くなるように蓄熱用熱交換器(43)における冷媒の蒸発圧力を調節することができる。これにより、圧縮機(21)の吸入圧力の低下に伴う蓄熱用熱交換器(43)における冷媒の蒸発圧力の低下を抑制することができ、蓄熱用熱交換器(43)における冷媒の蒸発温度が低くなり過ぎることを防止することができる。したがって、蓄熱用熱交換器(43)において蓄熱媒体が冷却され過ぎることを防止することができる。 In the first aspect of the invention, by providing the pressure adjusting mechanism (44), in the cooling and accumulating operation (that is, in the case where the cooling and accumulating cycle is performed in the refrigerant circuit (11)), the suction pressure of the compressor (21) is set. The evaporating pressure of the refrigerant in the heat storage heat exchanger (43) can be adjusted to be higher. Thereby, the fall of the evaporating pressure of the refrigerant | coolant in the heat storage heat exchanger (43) accompanying the fall of the suction pressure of a compressor (21) can be suppressed, and the evaporating temperature of the refrigerant | coolant in the heat storage heat exchanger (43) Can be prevented from becoming too low. Therefore, it is possible to prevent the heat storage medium from being overcooled in the heat storage heat exchanger (43).
第2の発明は、上記第1の発明において、上記冷房蓄冷サイクルが行われるように上記冷媒回路(11)を制御し、上記蓄熱用熱交換器(43)における冷媒の蒸発温度が予め設定された下限蒸発温度を下回らないように、上記圧力調節機構(44)における減圧量を調節する運転制御部(100)をさらに備えていることを特徴とする蓄熱式空気調和機である。 According to a second invention, in the first invention, the refrigerant circuit (11) is controlled so that the cooling and regenerative cycle is performed, and a refrigerant evaporation temperature in the heat storage heat exchanger (43) is preset. The regenerative air conditioner further includes an operation control unit (100) for adjusting the amount of pressure reduction in the pressure adjusting mechanism (44) so as not to fall below the lower limit evaporation temperature.
上記第2の発明では、蓄熱用熱交換器(43)における冷媒の蒸発圧力を適切に設定することができる。これにより、蓄熱用熱交換器(43)において蓄熱媒体を適切に冷却することができる。 In the said 2nd invention, the evaporation pressure of the refrigerant | coolant in the heat exchanger for heat storage (43) can be set appropriately. Thereby, a heat storage medium can be cooled appropriately in the heat storage heat exchanger (43).
第3の発明は、上記第1または第2の発明において、上記バイパス流路(14)が、上記蓄熱用熱交換器(43)と上記ガス冷媒流路(13)とを接続する第1流路部(14d)を有し、上記圧力調節機構(44)が、その開度を調節可能に構成されて上記第1流路部(14d)に設けられた圧力調節弁(45)を有していることを特徴とする蓄熱式空気調和機である。 According to a third aspect, in the first or second aspect, the bypass flow path (14) connects the heat storage heat exchanger (43) and the gas refrigerant flow path (13). A pressure control valve (45) provided in the first flow path portion (14d) having a passage portion (14d), the pressure adjustment mechanism (44) being configured to be capable of adjusting an opening degree thereof; It is the thermal storage type air conditioner characterized by having it.
上記第3の発明では、圧力調節弁(45)の開度を調節することにより、圧力調節機構(44)における減圧量を調整することができる。これにより、圧縮機(21)の吸入圧力よりも高くなるように蓄熱用熱交換器(43)における冷媒の蒸発圧力を調節することができ、蓄熱用熱交換器(43)において蓄熱媒体が冷却され過ぎることを防止することができる。 In the said 3rd invention, the pressure reduction amount in a pressure control mechanism (44) can be adjusted by adjusting the opening degree of a pressure control valve (45). Thereby, the evaporation pressure of the refrigerant in the heat storage heat exchanger (43) can be adjusted to be higher than the suction pressure of the compressor (21), and the heat storage medium is cooled in the heat storage heat exchanger (43). It is possible to prevent being overdone.
第4の発明は、上記第3の発明において、上記バイパス流路(14)が、上記第1流路部(14d)と並列に設けられて上記蓄熱用熱交換器(43)と上記ガス冷媒流路(13)とを接続する第2流路部(14e)をさらに有し、上記圧力調節機構(44)は、その開閉を切換可能に構成されて上記第2流路部(14e)に設けられた開閉弁(46)をさらに有していることを特徴とする蓄熱式空気調和機である。 In a fourth aspect based on the third aspect, the bypass flow path (14) is provided in parallel with the first flow path portion (14d), so that the heat storage heat exchanger (43) and the gas refrigerant are provided. A second flow path part (14e) for connecting the flow path (13) is further provided, and the pressure adjusting mechanism (44) is configured to be switchable between opening and closing, and is connected to the second flow path part (14e). The regenerative air conditioner further includes an on-off valve (46) provided.
上記第4の発明では、開閉弁(46)を開状態に設定して圧力調節弁(45)を全閉状態に設定することにより、開閉弁(46)を経由して蓄熱用熱交換器(43)とガス冷媒流路(13)との間に冷媒を流通させることができる。なお、開閉弁(46)における圧力損失は、圧力調節弁(45)における圧力損失よりも小さい。したがって、圧力調節弁(45)を経由して蓄熱用熱交換器(43)とガス冷媒流路(13)との間に冷媒を流通させる場合よりも、圧力調節機構(44)における圧力損失を低減することができる。これにより、冷房蓄冷運転とは異なる他の運転において、圧力調節機構(44)における圧力損失を低減することができる。 In the fourth aspect of the invention, by setting the on-off valve (46) to the open state and the pressure regulating valve (45) to the fully-closed state, the heat storage heat exchanger ( 43) and the gas refrigerant channel (13) can be circulated. Note that the pressure loss in the on-off valve (46) is smaller than the pressure loss in the pressure control valve (45). Therefore, the pressure loss in the pressure control mechanism (44) is less than when the refrigerant is circulated between the heat storage heat exchanger (43) and the gas refrigerant flow path (13) via the pressure control valve (45). Can be reduced. Thereby, the pressure loss in the pressure adjustment mechanism (44) can be reduced in another operation different from the cooling / storage operation.
第1および第3の発明によれば、蓄熱用熱交換器(43)において蓄熱媒体が冷却され過ぎることを防止することができるので、冷房蓄冷運転において、室内熱交換器における冷却能力(すなわち、冷房能力)を確保しつつ、蓄熱回路(31)における蓄熱媒体の循環効率の低下を抑制することができる。 According to the first and third inventions, it is possible to prevent the heat storage medium from being excessively cooled in the heat storage heat exchanger (43), so that in the cooling and cold storage operation, the cooling capacity in the indoor heat exchanger (that is, It is possible to suppress a decrease in the circulation efficiency of the heat storage medium in the heat storage circuit (31) while ensuring (cooling capacity).
第2の発明によれば、蓄熱用熱交換器(43)において蓄熱媒体を適切に冷却することができるので、冷房蓄冷運転において蓄冷を適切に行うことができる。 According to the second invention, since the heat storage medium can be appropriately cooled in the heat storage heat exchanger (43), cold storage can be appropriately performed in the cooling and cold storage operation.
第4の発明によれば、冷房蓄冷運転とは異なる他の運転において、圧力調節機構(44)における圧力損失を低減することができるので、他の運転を適切に行うことができる。 According to the fourth invention, the pressure loss in the pressure adjustment mechanism (44) can be reduced in another operation different from the cooling and regenerative operation, so that the other operation can be appropriately performed.
以下、実施の形態を図面を参照して詳しく説明する。なお、図中同一または相当部分には同一の符号を付しその説明は繰り返さない。 Hereinafter, embodiments will be described in detail with reference to the drawings. In the drawings, the same or corresponding parts are denoted by the same reference numerals, and description thereof will not be repeated.
(蓄熱式空気調和機)
図1は、実施形態による蓄熱式空気調和機(10)の構成例を示している。蓄熱式空気調和機(10)は、室外ユニット(20a)と室内ユニット(20b)と蓄熱ユニット(30)とで構成され、冷媒回路(11)と蓄熱回路(31)と予熱用熱交換器(41)と蓄熱用膨張弁(42)と蓄熱用熱交換器(43)と圧力調節機構(44)とコントローラ(100)とを備えている。
(Regenerative air conditioner)
Drawing 1 shows the example of composition of the heat storage type air harmony machine (10) by an embodiment. The heat storage type air conditioner (10) is composed of an outdoor unit (20a), an indoor unit (20b), and a heat storage unit (30). The refrigerant circuit (11), the heat storage circuit (31), and the preheat heat exchanger ( 41), a heat storage expansion valve (42), a heat storage heat exchanger (43), a pressure adjusting mechanism (44), and a controller (100).
〔冷媒回路〕
冷媒回路(11)には、冷媒が充填されている。そして、冷媒回路(11)では、冷媒が循環することによって冷凍サイクルが行われる。冷媒回路(11)は、圧縮機(21)と、室外熱交換器(22)と、室外膨張弁(23)と、室外側過冷却熱交換器(24)と、蓄熱側過冷却熱交換器(25)と、室内膨張弁(26)と、室内熱交換器(27)と、四方切換弁(28)とを有している。さらに、冷媒回路(11)は、液冷媒流路(12)とガス冷媒流路(13)とバイパス流路(14)と分岐流路(15)とを有している。
[Refrigerant circuit]
The refrigerant circuit (11) is filled with a refrigerant. And in a refrigerant circuit (11), a refrigerating cycle is performed when a refrigerant circulates. The refrigerant circuit (11) includes a compressor (21), an outdoor heat exchanger (22), an outdoor expansion valve (23), an outdoor subcooling heat exchanger (24), and a heat storage side subcooling heat exchanger. (25), an indoor expansion valve (26), an indoor heat exchanger (27), and a four-way switching valve (28). Furthermore, the refrigerant circuit (11) has a liquid refrigerant channel (12), a gas refrigerant channel (13), a bypass channel (14), and a branch channel (15).
室外ユニット(20a)は、室外に設置される。室外ユニット(20a)には、圧縮機(21)と室外熱交換器(22)と室外膨張弁(23)と室外側過冷却熱交換器(24)と四方切換弁(28)とが設けられている。また、室外ユニット(20a)には、室外熱交換器(22)に空気を搬送するための室外ファン(22a)が設けられている。 The outdoor unit (20a) is installed outdoors. The outdoor unit (20a) is provided with a compressor (21), an outdoor heat exchanger (22), an outdoor expansion valve (23), an outdoor supercooling heat exchanger (24), and a four-way switching valve (28). ing. The outdoor unit (20a) is provided with an outdoor fan (22a) for conveying air to the outdoor heat exchanger (22).
室内ユニット(20b)は、室内に設置される。室内ユニット(20b)には、室内膨張弁(26)と室内熱交換器(27)とが設けられている。また、室内ユニット(20b)には、室内熱交換器(27)に空気を搬送するための室内ファン(27a)が設けられている。 The indoor unit (20b) is installed indoors. The indoor unit (20b) is provided with an indoor expansion valve (26) and an indoor heat exchanger (27). The indoor unit (20b) is provided with an indoor fan (27a) for conveying air to the indoor heat exchanger (27).
蓄熱ユニット(30)は、室外ユニット(20a)と室内ユニット(20b)との間に接続され、室外ユニット(20a)の近傍に設置される。蓄熱ユニット(30)には、蓄熱側過冷却熱交換器(25)と蓄熱回路(31)と予熱用熱交換器(41)と蓄熱用膨張弁(42)と蓄熱用熱交換器(43)と圧力調節機構(44)とが設けられている。 The heat storage unit (30) is connected between the outdoor unit (20a) and the indoor unit (20b), and is installed in the vicinity of the outdoor unit (20a). The heat storage unit (30) includes a heat storage side subcooling heat exchanger (25), a heat storage circuit (31), a preheating heat exchanger (41), a heat storage expansion valve (42), and a heat storage heat exchanger (43). And a pressure adjusting mechanism (44).
〈圧縮機〉
圧縮機(21)は、その吐出端が四方切換弁(28)の第1ポートに接続され、その吸入端が四方切換弁(28)の第2ポートに接続されている。また、圧縮機(21)は、吸入した冷媒を圧縮して吐出する。さらに、圧縮機(21)は、その容量(回転数)を変更可能に構成されている。例えば、圧縮機(21)は、容量可変式の圧縮機によって構成され、図示しないインバータ回路によって回転数(運転周波数)が変更される。
<Compressor>
The compressor (21) has a discharge end connected to the first port of the four-way switching valve (28) and a suction end connected to the second port of the four-way switching valve (28). The compressor (21) compresses and discharges the sucked refrigerant. Furthermore, the compressor (21) is configured to be able to change its capacity (rotation speed). For example, the compressor (21) is constituted by a variable capacity compressor, and the rotation speed (operation frequency) is changed by an inverter circuit (not shown).
〈室外熱交換器〉
室外熱交換器(22)は、そのガス端が第1冷媒配管(11a)により四方切換弁(28)の第3ポートに接続され、その液端が第2冷媒配管(11b)により液冷媒流路(12)の一端に接続されている。なお、第2冷媒配管(11b)には、室外熱交換器(22)の液端から液冷媒流路(12)の一端へ向けて、室外膨張弁(23)と室外側過冷却熱交換器(24)とが順に設けられている。すなわち、室外熱交換器(22)の液端は、室外膨張弁(23)と室外側過冷却熱交換器(24)と順に介して液冷媒流路(12)に接続されている。また、室外熱交換器(22)は、室外ファン(22a)によって搬送された室外空気と冷媒とを熱交換させる。例えば、室外熱交換器(22)は、クロスフィンアンドチューブ式の熱交換器によって構成されている。
<Outdoor heat exchanger>
The outdoor heat exchanger (22) has a gas end connected to the third port of the four-way switching valve (28) by the first refrigerant pipe (11a), and a liquid end flowing through the second refrigerant pipe (11b). Connected to one end of the path (12). The second refrigerant pipe (11b) includes an outdoor expansion valve (23) and an outdoor subcooling heat exchanger from the liquid end of the outdoor heat exchanger (22) to one end of the liquid refrigerant flow path (12). (24) and are provided in order. That is, the liquid end of the outdoor heat exchanger (22) is connected to the liquid refrigerant flow path (12) through the outdoor expansion valve (23) and the outdoor subcooling heat exchanger (24) in this order. The outdoor heat exchanger (22) exchanges heat between the outdoor air conveyed by the outdoor fan (22a) and the refrigerant. For example, the outdoor heat exchanger (22) is configured by a cross fin and tube heat exchanger.
〈室外膨張弁〉
室外膨張弁(23)は、その開度を調節可能に構成され、その開度が調節されることにより冷媒の圧力や流量を調節する。例えば、室外膨張弁(23)は、電子膨張弁(電動弁)によって構成されている。
<Outdoor expansion valve>
The outdoor expansion valve (23) is configured to be adjustable in its opening, and the pressure and flow rate of the refrigerant are adjusted by adjusting the opening. For example, the outdoor expansion valve (23) is constituted by an electronic expansion valve (motorized valve).
〈室外側過冷却熱交換器〉
室外側過冷却熱交換器(24)は、高圧側通路(24a)と低圧側通路(24b)とを有している。高圧側通路(24a)は、第2冷媒配管(11b)に直列に挿入(接続)されている。低圧側通路(24b)は、補助配管(24d)に直列に挿入されている。補助配管(24d)は、その一端が第2冷媒配管(11b)の室外膨張弁(23)と室外側過冷却熱交換器(24)との間に位置する中途部に接続され、その他端が圧縮機(21)の吸入端に接続されている。そして、室外側過冷却熱交換器(24)は、高圧側通路(24a)を流れる冷媒と低圧側通路(24b)を流れる冷媒とを熱交換させて高圧側通路(24a)を流れる冷媒を過冷却するように構成されている。なお、補助配管(24d)には、低圧側通路(24b)を流れる冷媒の流量を調節するための室外側過冷却膨張弁(24c)が設けられている。
<Outdoor undercooling heat exchanger>
The outdoor supercooling heat exchanger (24) has a high-pressure side passage (24a) and a low-pressure side passage (24b). The high-pressure side passage (24a) is inserted (connected) in series with the second refrigerant pipe (11b). The low-pressure side passage (24b) is inserted in series with the auxiliary pipe (24d). One end of the auxiliary pipe (24d) is connected to a midway portion located between the outdoor expansion valve (23) of the second refrigerant pipe (11b) and the outdoor subcooling heat exchanger (24), and the other end is connected. Connected to the suction end of the compressor (21). The outdoor supercooling heat exchanger (24) heat-exchanges the refrigerant flowing through the high pressure side passage (24a) by exchanging heat between the refrigerant flowing through the high pressure side passage (24a) and the refrigerant flowing through the low pressure side passage (24b). It is configured to cool. The auxiliary pipe (24d) is provided with an outdoor supercooling expansion valve (24c) for adjusting the flow rate of the refrigerant flowing through the low pressure side passage (24b).
〈蓄熱側過冷却熱交換器〉
蓄熱側過冷却熱交換器(25)は、液冷媒流路(12)に設けられる。この例では、蓄熱側過冷却熱交換器(25)は、液冷媒流路(12)の他端寄りに配置されている。また、蓄熱側過冷却熱交換器(25)は、高圧側通路(25a)と低圧側通路(25b)とを有している。高圧側通路(25a)は、液冷媒流路(12)に直列に挿入されている。低圧側通路(25b)は、補助配管(25d)に直列に挿入されている。補助配管(25d)は、その一端が液冷媒流路(12)の中途部(液冷媒流路(12)の一端と蓄熱側過冷却熱交換器(25)との間に位置する中途部)に接続され、その他端がガス冷媒流路(13)に接続されている。そして、蓄熱側過冷却熱交換器(25)は、高圧側通路(25a)を流れる冷媒と低圧側通路(25b)を流れる冷媒とを熱交換させて高圧側通路(25a)を流れる冷媒を過冷却するように構成されている。なお、補助配管(25d)には、低圧側通路(25b)を流れる冷媒の流量を調節するための蓄熱側過冷却膨張弁(25c)が設けられている。
<Heat storage side subcooling heat exchanger>
The heat storage side subcooling heat exchanger (25) is provided in the liquid refrigerant flow path (12). In this example, the heat storage side subcooling heat exchanger (25) is disposed near the other end of the liquid refrigerant channel (12). The heat storage side subcooling heat exchanger (25) has a high pressure side passage (25a) and a low pressure side passage (25b). The high-pressure side passage (25a) is inserted in series with the liquid refrigerant passage (12). The low-pressure side passage (25b) is inserted in series with the auxiliary pipe (25d). One end of the auxiliary pipe (25d) is in the middle of the liquid refrigerant channel (12) (middle part located between one end of the liquid refrigerant channel (12) and the heat storage side subcooling heat exchanger (25)) The other end is connected to the gas refrigerant channel (13). The heat storage side subcooling heat exchanger (25) heat-exchanges the refrigerant flowing through the high pressure side passage (25a) by exchanging heat between the refrigerant flowing through the high pressure side passage (25a) and the refrigerant flowing through the low pressure side passage (25b). It is configured to cool. The auxiliary pipe (25d) is provided with a heat storage side subcooling expansion valve (25c) for adjusting the flow rate of the refrigerant flowing through the low pressure side passage (25b).
〈室内膨張弁〉
室内膨張弁(26)は、液冷媒流路(12)の他端と室内熱交換器(27)の液端とを接続する第3冷媒配管(11c)に設けられる。また、室内膨張弁(26)は、その開度を調節可能に構成され、その開度が調節されることにより冷媒の圧力や流量を調節する。例えば、室内膨張弁(26)は、電子膨張弁(電動弁)によって構成されている。
<Indoor expansion valve>
The indoor expansion valve (26) is provided in the third refrigerant pipe (11c) that connects the other end of the liquid refrigerant channel (12) and the liquid end of the indoor heat exchanger (27). Further, the indoor expansion valve (26) is configured to be able to adjust its opening, and the refrigerant pressure and flow rate are adjusted by adjusting the opening. For example, the indoor expansion valve (26) is configured by an electronic expansion valve (motorized valve).
〈室内熱交換器〉
室内熱交換器(27)は、その液端が第3冷媒配管(11c)により液冷媒流路(12)の他端に接続され、そのガス端が第4冷媒配管(11d)によりガス冷媒流路(13)の一端に接続されている。すなわち、室内熱交換器(27)の液端は、室内膨張弁(26)を介して液冷媒流路(12)に接続されている。また、室内熱交換器(27)は、室内ファン(27a)によって搬送された室内空気と冷媒とを熱交換させる。室内熱交換器(27)において熱交換された室内空気は、再び室内に供給される。例えば、室内熱交換器(27)は、クロスフィンアンドチューブ式の熱交換器によって構成されている。
<Indoor heat exchanger>
The indoor heat exchanger (27) has a liquid end connected to the other end of the liquid refrigerant flow path (12) by the third refrigerant pipe (11c), and a gas end connected to the gas refrigerant flow by the fourth refrigerant pipe (11d). Connected to one end of the path (13). That is, the liquid end of the indoor heat exchanger (27) is connected to the liquid refrigerant channel (12) via the indoor expansion valve (26). The indoor heat exchanger (27) exchanges heat between the indoor air conveyed by the indoor fan (27a) and the refrigerant. The indoor air heat-exchanged in the indoor heat exchanger (27) is supplied again into the room. For example, the indoor heat exchanger (27) is configured by a cross fin and tube heat exchanger.
〈四方切換弁〉
四方切換弁(28)は、蓄熱式空気調和機(10)の運転種類に応じて、第1〜第4ポートの接続状態を第1状態(図1の実線で示す状態)と第2状態(図1の破線で示す状態)とを切換可能に構成されている。なお、四方切換弁(28)の第4ポートは、第5冷媒配管(11e)によりガス冷媒流路(13)の他端に接続されている。
<4-way switching valve>
The four-way switching valve (28) has a connection state of the first to fourth ports in a first state (state shown by a solid line in FIG. 1) and a second state (in accordance with the operation type of the regenerative air conditioner (10)). The state indicated by the broken line in FIG. 1 is switchable. The fourth port of the four-way switching valve (28) is connected to the other end of the gas refrigerant flow path (13) by the fifth refrigerant pipe (11e).
〈バイパス流路〉
バイパス流路(14)は、その一端が液冷媒流路(12)に接続され、その他端がガス冷媒流路(13)に接続されている。また、バイパス流路(14)には、バイパス流路(14)の一端側(すなわち、液冷媒流路(12)側)から他端側(すなわち、ガス冷媒流路(13)側)へ向けて、予熱用熱交換器(41)と蓄熱用膨張弁(42)と蓄熱用熱交換器(43)と圧力調節機構(44)とが順に設けられている。
<Bypass channel>
The bypass channel (14) has one end connected to the liquid refrigerant channel (12) and the other end connected to the gas refrigerant channel (13). Further, the bypass channel (14) is directed from one end side (that is, liquid refrigerant channel (12) side) to the other end side (that is, gas refrigerant channel (13) side) of the bypass channel (14). Thus, a preheating heat exchanger (41), a heat storage expansion valve (42), a heat storage heat exchanger (43), and a pressure adjusting mechanism (44) are sequentially provided.
なお、液冷媒流路(12)では、バイパス流路(14)と液冷媒流路(12)との接続点(第1接続点(P1))は、蓄熱側過冷却熱交換器(25)の補助配管(25d)と液冷媒流路(12)との接続点(第2接続点(P2))よりも、液冷媒流路(12)の一端側(すなわち、第2冷媒配管(11b)側)に位置している。また、この例では、バイパス流路(14)は、第1主配管(14a)と第2主配管(14b)と第3主配管(14c)と第1分岐配管(14d)と第2分岐配管(14e)とを有している。第1主配管(14a)は、液冷媒流路(12)の中途部と予熱用熱交換器(41)とを接続する。第2主配管(14b)は、予熱用熱交換器(41)と蓄熱用熱交換器(43)とを接続する。第3主配管(14c)の一端は、蓄熱用熱交換器(43)に接続される。第1分岐配管(14d)は、第3主配管(14c)の他端とガス冷媒流路(13)とを接続する。第2分岐配管(14e)は、第1分岐配管(14d)と並列に設けられて第3主配管(14c)とガス冷媒流路(13)とを接続する。すなわち、第1分岐配管(14d)は、蓄熱用熱交換器(43)とガス冷媒流路(13)とを接続する配管(第1流路部)を構成している。第2分岐配管(14e)は、第1分岐配管(14d)と並列に設けられて蓄熱用熱交換器(43)とガス冷媒流路(13)とを接続する配管(第2流路部)を構成している。 In the liquid refrigerant channel (12), the connection point (first connection point (P1)) between the bypass channel (14) and the liquid refrigerant channel (12) is the heat storage side subcooling heat exchanger (25). One end side of the liquid refrigerant flow path (12) from the connection point (second connection point (P2)) between the auxiliary pipe (25d) and the liquid refrigerant flow path (12) (that is, the second refrigerant pipe (11b)) Side). In this example, the bypass channel (14) includes the first main pipe (14a), the second main pipe (14b), the third main pipe (14c), the first branch pipe (14d), and the second branch pipe. (14e). The first main pipe (14a) connects the midway part of the liquid refrigerant flow path (12) and the preheating heat exchanger (41). The second main pipe (14b) connects the preheating heat exchanger (41) and the heat storage heat exchanger (43). One end of the third main pipe (14c) is connected to the heat storage heat exchanger (43). The first branch pipe (14d) connects the other end of the third main pipe (14c) and the gas refrigerant channel (13). The second branch pipe (14e) is provided in parallel with the first branch pipe (14d) and connects the third main pipe (14c) and the gas refrigerant channel (13). That is, the first branch pipe (14d) constitutes a pipe (first flow path portion) that connects the heat storage heat exchanger (43) and the gas refrigerant flow path (13). The second branch pipe (14e) is provided in parallel with the first branch pipe (14d) and connects the heat storage heat exchanger (43) and the gas refrigerant flow path (13) (second flow path portion). Is configured.
〈分岐流路〉
分岐流路(15)は、その一端がバイパス流路(14)の中途部(蓄熱用熱交換器(43)と圧力調節機構(44)との間に位置する中途部)に接続され、その他端が液冷媒流路(12)の中途部(第1接続点(P1)と第2接続点(P2)との間に位置する中途部)に接続されている。すなわち、液冷媒流路(12)において、分岐流路(15)と液冷媒流路(12)との接続点(第3接続点(P3))は、第1接続点(P1)と第2接続点(P2)との間に位置している。
<Branch channel>
One end of the branch channel (15) is connected to the midway part of the bypass channel (14) (the midway part located between the heat storage heat exchanger (43) and the pressure control mechanism (44)). The end is connected to a midway part (midway part located between the first connection point (P1) and the second connection point (P2)) of the liquid refrigerant flow path (12). That is, in the liquid refrigerant flow path (12), the connection point (third connection point (P3)) between the branch flow path (15) and the liquid refrigerant flow path (12) is the first connection point (P1) and the second connection point. It is located between the connection point (P2).
〈開閉弁と逆止弁〉
また、冷媒回路(11)には、第1開閉弁(51)と第2開閉弁(52)と第3開閉弁(53)と、第1逆止弁(51a)と第2逆止弁(51b)と第3逆止弁(51c)とが設けられている。例えば、第1開閉弁(51)と第2開閉弁(52)と第3開閉弁(53)は、電磁弁によって構成されている。
<Open / close valve and check valve>
The refrigerant circuit (11) includes a first on-off valve (51), a second on-off valve (52), a third on-off valve (53), a first check valve (51a), and a second check valve ( 51b) and a third check valve (51c) are provided. For example, the first on-off valve (51), the second on-off valve (52), and the third on-off valve (53) are constituted by electromagnetic valves.
第1開閉弁(51)は、液冷媒流路(12)において第1接続点(P1)と第2接続点(P2)との間に設けられている。第1逆止弁(51a)は、第1開閉弁(51)と並列に接続されている。また、第1逆止弁(51a)は、後述する単純暖房運転において蓄熱側過冷却熱交換器(25)側から室外側過冷却熱交換器(24)側に向けて冷媒を流すように構成されている。 The first on-off valve (51) is provided between the first connection point (P1) and the second connection point (P2) in the liquid refrigerant channel (12). The first check valve (51a) is connected in parallel with the first on-off valve (51). The first check valve (51a) is configured to flow the refrigerant from the heat storage side subcooling heat exchanger (25) side toward the outdoor side subcooling heat exchanger (24) side in the simple heating operation described later. Has been.
第2開閉弁(52)は、蓄熱用膨張弁(42)と並列に接続されている。第2逆止弁(51b)は、第2開閉弁(52)と直列に接続されて蓄熱用膨張弁(42)と並列となっている。また、第2逆止弁(51b)は、予熱用熱交換器(41)側から蓄熱用熱交換器(43)側への冷媒の流れのみを許容する。 The second on-off valve (52) is connected in parallel with the heat storage expansion valve (42). The second check valve (51b) is connected in series with the second on-off valve (52) and is in parallel with the heat storage expansion valve (42). The second check valve (51b) allows only the refrigerant flow from the preheating heat exchanger (41) side to the heat storage heat exchanger (43) side.
第3開閉弁(53)は、分岐流路(15)に設けられている。第3逆止弁(51c)は、分岐流路(15)に設けられ、バイパス流路(14)側から液冷媒流路(12)側への冷媒の流れのみを許容する。 The third on-off valve (53) is provided in the branch channel (15). The third check valve (51c) is provided in the branch channel (15) and allows only the refrigerant flow from the bypass channel (14) side to the liquid refrigerant channel (12) side.
〔予熱用熱交換器〕
予熱用熱交換器(41)は、冷媒回路(11)のバイパス流路(14)と蓄熱回路(31)とに接続され、バイパス流路(14)を流れる冷媒と蓄熱回路(31)を流れる蓄熱媒体とを熱交換させる。具体的には、予熱用熱交換器(41)は、冷媒側通路(41a)と蓄熱側通路(41b)とを有する。冷媒側通路(41a)は、バイパス流路(14)に直列に挿入されている。この例では、冷媒側通路(41a)は、バイパス流路(14)の第1主配管(14a)と第2主配管(14b)との間に接続されている。蓄熱側通路(41b)は、蓄熱回路(31)に直列に挿入されている。そして、予熱用熱交換器(41)は、冷媒側通路(41a)を流れる冷媒と蓄熱側通路(41b)を流れる蓄熱媒体とを熱交換させる。
[Heat exchanger for preheating]
The preheating heat exchanger (41) is connected to the bypass passage (14) and the heat storage circuit (31) of the refrigerant circuit (11), and flows through the refrigerant flowing through the bypass passage (14) and the heat storage circuit (31). Heat exchange with the heat storage medium. Specifically, the preheating heat exchanger (41) includes a refrigerant side passage (41a) and a heat storage side passage (41b). The refrigerant side passage (41a) is inserted in series with the bypass passage (14). In this example, the refrigerant side passage (41a) is connected between the first main pipe (14a) and the second main pipe (14b) of the bypass flow path (14). The heat storage side passage (41b) is inserted in series with the heat storage circuit (31). The preheating heat exchanger (41) exchanges heat between the refrigerant flowing through the refrigerant side passage (41a) and the heat storage medium flowing through the heat storage side passage (41b).
〔蓄熱用膨張弁〕
蓄熱用膨張弁(42)は、バイパス流路(14)において予熱用熱交換器(41)と蓄熱用熱交換器(43)との間に設けられる。この例では、蓄熱用膨張弁(42)は、バイパス流路(14)の第2主配管(14b)に設けられている。また、蓄熱用膨張弁(42)は、その開度を調節可能に構成され、その開度が調節されることにより冷媒の圧力や流量を調節する。例えば、蓄熱用膨張弁(42)は、電磁膨張弁(電動弁)によって構成されている。
[Expansion valve for heat storage]
The heat storage expansion valve (42) is provided between the preheating heat exchanger (41) and the heat storage heat exchanger (43) in the bypass passage (14). In this example, the heat storage expansion valve (42) is provided in the second main pipe (14b) of the bypass flow path (14). Further, the heat storage expansion valve (42) is configured such that its opening degree can be adjusted, and the refrigerant pressure and flow rate are adjusted by adjusting the opening degree. For example, the heat storage expansion valve (42) is constituted by an electromagnetic expansion valve (motor valve).
また、蓄熱用膨張弁(42)には、圧力逃がし弁(42a)が並列に接続されている。圧力逃がし弁(42a)は、例えば、蓄熱式空気調和機(10)の運転停止時において蓄熱用熱交換器(43)側の圧力が許容値を超えた場合に、蓄熱用熱交換器(43)側の圧力を放出させるための弁である。 A pressure relief valve (42a) is connected in parallel to the heat storage expansion valve (42). The pressure relief valve (42a) is, for example, a heat storage heat exchanger (43) when the pressure on the heat storage heat exchanger (43) side exceeds an allowable value when the heat storage air conditioner (10) is stopped. ) A valve for releasing the pressure on the side.
〔蓄熱用熱交換器〕
蓄熱用熱交換器(43)は、冷媒回路(11)のバイパス流路(14)と蓄熱回路(31)とに接続され、バイパス流路(14)を流れる冷媒と蓄熱回路(31)を流れる蓄熱媒体とを熱交換させる。具体的には、蓄熱用熱交換器(43)は、冷媒側通路(43a)と蓄熱側通路(43b)とを有する。冷媒側通路(43a)は、バイパス流路(14)に直列に挿入される。この例では、冷媒側通路(43a)は、バイパス流路(14)の第2主配管(14b)と第3主配管(14c)との間に接続されている。蓄熱側通路(43b)は、蓄熱回路(31)に直列に挿入される。そして、蓄熱用熱交換器(43)は、冷媒側通路(43a)を流れる冷媒と蓄熱側通路(43b)を流れる蓄熱媒体とを熱交換させる。
[Heat exchanger for heat storage]
The heat storage heat exchanger (43) is connected to the bypass flow path (14) and the heat storage circuit (31) of the refrigerant circuit (11), and flows through the refrigerant flowing through the bypass flow path (14) and the heat storage circuit (31). Heat exchange with the heat storage medium. Specifically, the heat storage heat exchanger (43) includes a refrigerant side passage (43a) and a heat storage side passage (43b). The refrigerant side passage (43a) is inserted in series in the bypass passage (14). In this example, the refrigerant side passage (43a) is connected between the second main pipe (14b) and the third main pipe (14c) of the bypass flow path (14). The heat storage side passage (43b) is inserted in series with the heat storage circuit (31). The heat storage heat exchanger (43) exchanges heat between the refrigerant flowing through the refrigerant side passage (43a) and the heat storage medium flowing through the heat storage side passage (43b).
〔圧力調節機構〕
圧力調節機構(44)は、バイパス流路(14)において蓄熱用熱交換器(43)とガス冷媒流路(13)との間に設けられる。また、圧力調節機構(44)は、蓄熱用熱交換器(43)とガス冷媒流路(13)との間を流れる冷媒の圧力を調節可能に構成されている。
(Pressure adjustment mechanism)
The pressure adjusting mechanism (44) is provided between the heat storage heat exchanger (43) and the gas refrigerant channel (13) in the bypass channel (14). The pressure adjusting mechanism (44) is configured to be able to adjust the pressure of the refrigerant flowing between the heat storage heat exchanger (43) and the gas refrigerant flow path (13).
この例では、圧力調節機構(44)は、圧力調節弁(45)と流路開閉弁(46)とを有している。圧力調節弁(45)は、バイパス流路(14)の第1分岐配管(14d)に設けられている。また、圧力調節弁(45)は、その開度を調節可能に構成されている。例えば、圧力調節弁(45)は、電動弁によって構成されている。流路開閉弁(46)は、バイパス流路(14)の第2分岐配管(14e)に設けられている。また、流路開閉弁(46)は、その開閉を切換可能に構成されている。例えば、流路開閉弁(46)は、電磁弁によって構成されている。 In this example, the pressure adjustment mechanism (44) includes a pressure adjustment valve (45) and a flow path opening / closing valve (46). The pressure control valve (45) is provided in the first branch pipe (14d) of the bypass channel (14). Moreover, the pressure control valve (45) is comprised so that adjustment of the opening degree is possible. For example, the pressure control valve (45) is an electric valve. The flow path opening / closing valve (46) is provided in the second branch pipe (14e) of the bypass flow path (14). The flow path opening / closing valve (46) is configured to be able to switch between opening and closing. For example, the flow path opening / closing valve (46) is constituted by an electromagnetic valve.
〔蓄熱回路〕
蓄熱回路(31)には、蓄熱媒体が充填されている。蓄熱回路(31)では、蓄熱媒体を循環させる循環動作が行われる。蓄熱回路(31)は、蓄熱タンク(32)と循環ポンプ(33)とを備えている。
[Heat storage circuit]
The heat storage circuit (31) is filled with a heat storage medium. In the heat storage circuit (31), a circulation operation for circulating the heat storage medium is performed. The heat storage circuit (31) includes a heat storage tank (32) and a circulation pump (33).
〈蓄熱タンク〉
蓄熱タンク(32)は、中空の容器であって、蓄熱媒体を貯留する。例えば、蓄熱タンク(32)は、両端が閉塞された円筒状に形成され、その軸方向が上下方向となるように配置されている。蓄熱タンク(32)には、流出口と流入口とが形成されており、流出口は、例えば、流入口よりも上方に位置している。
<Heat storage tank>
The heat storage tank (32) is a hollow container and stores a heat storage medium. For example, the heat storage tank (32) is formed in a cylindrical shape closed at both ends, and is arranged so that its axial direction is the vertical direction. The heat storage tank (32) is formed with an outlet and an inlet, and the outlet is located above the inlet, for example.
〈循環ポンプ〉
循環ポンプ(33)は、蓄熱回路(31)において蓄熱タンク(32)と予熱用熱交換器(41)と蓄熱用熱交換器(43)の間で蓄熱媒体を循環させる。蓄熱媒体の循環方向は、次のとおりである。すなわち、蓄熱タンク(32)から流出した蓄熱媒体は、予熱用熱交換器(41)の蓄熱側通路(41b)を通過して循環ポンプ(33)を通過し、その後、蓄熱用熱交換器(43)の蓄熱側通路(43b)を通過して蓄熱タンク(32)に流入する。循環ポンプ(33)の運転のオン/オフや、循環ポンプ(33)によって搬送される蓄熱媒体の流量は、コントローラ(100)によって制御される。
<Circulation pump>
The circulation pump (33) circulates the heat storage medium among the heat storage tank (32), the preheating heat exchanger (41), and the heat storage heat exchanger (43) in the heat storage circuit (31). The circulation direction of the heat storage medium is as follows. That is, the heat storage medium that has flowed out of the heat storage tank (32) passes through the heat storage side passage (41b) of the preheating heat exchanger (41), passes through the circulation pump (33), and then passes through the heat storage heat exchanger ( It passes through the heat storage side passage (43b) of 43) and flows into the heat storage tank (32). The controller (100) controls on / off of the operation of the circulation pump (33) and the flow rate of the heat storage medium conveyed by the circulation pump (33).
〔蓄熱媒体〕
ここで、蓄熱媒体について説明する。蓄熱媒体には、冷却によって固体成分が生成される蓄熱材(より詳しくは、冷却によって0℃よりも高く20℃よりも低い温度にて固体成分が生成される蓄熱材)が採用される。なお、固体成分とは、その融点において液体から相転移(潜熱変化)し、発熱した状態にある成分を言う。固体成分の具体例としては、包接水和物などが挙げられる。
[Heat storage medium]
Here, the heat storage medium will be described. As the heat storage medium, a heat storage material in which a solid component is generated by cooling (more specifically, a heat storage material in which a solid component is generated at a temperature higher than 0 ° C. and lower than 20 ° C. by cooling) is employed. The solid component refers to a component that has undergone phase transition (latent heat change) from a liquid at its melting point and is in an exothermic state. Specific examples of the solid component include clathrate hydrate.
以下では、冷却によって包接水和物が生成される蓄熱材(すなわち、流動性を有する蓄熱材)を蓄熱媒体として採用する場合を例に挙げて説明する。このような蓄熱媒体の具体例としては、臭化テトラnブチルアンモニウムを含有する臭化テトラnブチルアンモニウム(TBAB:TetraButyl Ammonium Bromide)水溶液、トリメチロールエタン(TME:Trimethylolethane)水溶液、パラフィン系スラリーなどが挙げられる。例えば、臭化テトラnブチルアンモニウム水溶液は、安定的に冷却されてその水溶液の温度が水和物生成温度よりも低くなった過冷却状態でもその水溶液の状態を維持するが、この過冷却状態にて何らかのきっかけが与えられると、過冷却の溶液が包接水和物を含んだ溶液(すなわち、スラリー)へと遷移する。すなわち、臭化テトラnブチルアンモニウム水溶液は、過冷却状態を解消して、臭化テトラnブチルアンモニウムと水分子とからなる包接水和物(水和物結晶)が生成されて粘性の比較的高いスラリー状となる。ここで、過冷却状態とは、蓄熱媒体が水和物生成温度以下の温度となっても包接水和物が生成されずに溶液の状態を保っている状態を言う。逆に、スラリー状となっている臭化テトラnブチルアンモニウム水溶液は、加熱によりその水溶液の温度が水和物生成温度よりも高くなると、包接水和物が融解して流動性の比較的高い液状態(溶液)となる。 Hereinafter, a case where a heat storage material in which clathrate hydrate is generated by cooling (that is, a heat storage material having fluidity) is employed as a heat storage medium will be described as an example. Specific examples of such a heat storage medium include an aqueous solution of tetranbutylammonium bromide (TBAB) containing tetra nbutylammonium bromide, an aqueous solution of trimethylolethane (TME), and a paraffinic slurry. Can be mentioned. For example, an aqueous solution of tetra-n-butylammonium bromide maintains the state of the aqueous solution even in a supercooled state in which the aqueous solution is cooled stably and the temperature of the aqueous solution becomes lower than the hydrate formation temperature. When given some trigger, the supercooled solution transitions to a solution containing clathrate hydrate (ie, slurry). That is, the tetra-n-butylammonium bromide aqueous solution eliminates the supercooled state, and clathrate hydrates (hydrate crystals) composed of tetra-n-butylammonium bromide and water molecules are produced, resulting in relatively viscous viscosity. It becomes a high slurry state. Here, the supercooled state refers to a state where the clathrate hydrate is not generated and the state of the solution is maintained even when the heat storage medium becomes a temperature lower than the hydrate generation temperature. Conversely, when the aqueous solution of tetra-n-butylammonium bromide in a slurry state is heated, the temperature of the aqueous solution becomes higher than the hydrate formation temperature, the clathrate hydrate melts and the fluidity is relatively high. It becomes a liquid state (solution).
この実施形態では、蓄熱媒体として、臭化テトラnブチルアンモニウムを含有する臭化テトラnブチルアンモニウム水溶液を採用している。特に、蓄熱媒体は、調和濃度の近傍の濃度を有する媒体であることが好ましい。調和濃度とは、包接水和物が生成される前後において水溶液の濃度が変化しない濃度を意味する。この実施形態では、調和濃度を約40%とする。この場合の臭化テトラnブチルアンモニウム水溶液の水和物生成温度は、約12℃である。 In this embodiment, a tetra nbutylammonium bromide aqueous solution containing tetra nbutylammonium bromide is employed as the heat storage medium. In particular, the heat storage medium is preferably a medium having a concentration near the harmonic concentration. The harmonic concentration means a concentration at which the concentration of the aqueous solution does not change before and after the clathrate hydrate is formed. In this embodiment, the harmonic concentration is about 40%. In this case, the hydrate formation temperature of the aqueous solution of tetra-n-butylammonium bromide is about 12 ° C.
なお、蓄熱媒体の濃度に応じて、臭化テトラnブチルアンモニウム水溶液の水和物生成温度は変化する。例えば、蓄熱媒体の濃度が約20%である場合、水和物生成温度は、約8.5℃となる。 Note that the hydrate formation temperature of the aqueous solution of tetra-n-butylammonium bromide varies depending on the concentration of the heat storage medium. For example, when the concentration of the heat storage medium is about 20%, the hydrate formation temperature is about 8.5 ° C.
〔冷媒温度センサ〕
また、蓄熱式空気調和機(10)には、第1冷媒温度センサ(61)と第2冷媒温度センサ(62)とが設けられている。
(Refrigerant temperature sensor)
The regenerative air conditioner (10) is provided with a first refrigerant temperature sensor (61) and a second refrigerant temperature sensor (62).
第1冷媒温度センサ(61)は、蓄熱用熱交換器(43)の一端側(ガス冷媒流路(13)側)における冷媒の温度(第1冷媒温度)を検出する。この例では、第1冷媒温度センサ(61)は、蓄熱用熱交換器(43)の冷媒側通路(43a)の一端の近傍に設置され、設置場所の冷媒温度を第1冷媒温度として検出する。 A 1st refrigerant | coolant temperature sensor (61) detects the temperature (1st refrigerant | coolant temperature) of the refrigerant | coolant in the one end side (gas refrigerant flow path (13) side) of the heat exchanger for heat storage (43). In this example, the first refrigerant temperature sensor (61) is installed in the vicinity of one end of the refrigerant side passage (43a) of the heat storage heat exchanger (43), and detects the refrigerant temperature at the installation location as the first refrigerant temperature. .
第2冷媒温度センサ(62)は、蓄熱用熱交換器(43)の他端側(液冷媒流路(12)側)における冷媒の温度(第2冷媒温度)を検出する。この例では、第2冷媒温度センサ(62)は、蓄熱用熱交換器(43)の冷媒側通路(43a)の他端の近傍に設置され、設置場所の冷媒温度を第2冷媒温度として検出する。 The second refrigerant temperature sensor (62) detects the temperature of the refrigerant (second refrigerant temperature) on the other end side (liquid refrigerant flow path (12) side) of the heat storage heat exchanger (43). In this example, the second refrigerant temperature sensor (62) is installed in the vicinity of the other end of the refrigerant side passage (43a) of the heat storage heat exchanger (43), and detects the refrigerant temperature at the installation location as the second refrigerant temperature. To do.
〔コントローラ(運転制御部)〕
コントローラ(100)は、蓄熱式空気調和機(10)の各部を制御して蓄熱式空気調和機(10)の運転動作を制御する。この蓄熱式空気調和機(10)では、単純冷房運転と、単純暖房運転と、蓄冷運転と、利用冷房運転と、冷房蓄冷運転とが行われる。
[Controller (operation control unit)]
The controller (100) controls each part of the regenerative air conditioner (10) to control the operation of the regenerative air conditioner (10). In this heat storage type air conditioner (10), simple cooling operation, simple heating operation, cold storage operation, utilization cooling operation, and cooling cold storage operation are performed.
〔単純冷房運転〕
次に、図2を参照して、単純冷房運転について説明する。単純冷房運転とは、冷媒回路(11)の冷凍サイクルによって得られる冷熱のみを用いて室内の冷房を行う運転である。
[Simple cooling operation]
Next, the simple cooling operation will be described with reference to FIG. The simple cooling operation is an operation in which indoor cooling is performed using only the cooling heat obtained by the refrigeration cycle of the refrigerant circuit (11).
冷媒回路(11)では、室外熱交換器(22)が凝縮器となり室内熱交換器(27)が蒸発器となる冷凍サイクル(単純冷房サイクル)が行われる。一方、蓄熱回路(31)では、蓄熱媒体が循環しない。 In the refrigerant circuit (11), a refrigeration cycle (simple cooling cycle) in which the outdoor heat exchanger (22) serves as a condenser and the indoor heat exchanger (27) serves as an evaporator is performed. On the other hand, in the heat storage circuit (31), the heat storage medium does not circulate.
具体的には、四方切換弁(28)が第1状態に設定される。これにより、圧縮機(21)は、その吐出端が室外熱交換器(22)のガス端に接続され、その吸入端がガス冷媒流路(13)に接続される。また、第1開閉弁(51)が開状態に設定され、第2開閉弁(52)と第3開閉弁(53)が閉状態に設定される。室外膨張弁(23)の開度が全開状態に設定され、室内膨張弁(26)の開度が所定の開度(室内熱交換器(27)の出口における冷媒の過熱度が目標過熱度となる開度)に調節され、蓄熱用膨張弁(42)の開度が全閉状態に設定される。室外側過冷却膨張弁(24c)の開度が所定の開度に調節され、蓄熱側過冷却膨張弁(25c)の開度が全閉状態に設定される。圧力調節弁(45)の開度が全閉状態に設定され、流路開閉弁(46)が開状態に設定される。そして、圧縮機(21)と室外ファン(22a)と室内ファン(27a)が駆動状態に設定され、循環ポンプ(33)が停止状態に設定される。なお、これらの設定および調節は、コントローラ(100)による制御に応答して行われる。以下の説明においても同様である。 Specifically, the four-way selector valve (28) is set to the first state. Thereby, as for the compressor (21), the discharge end is connected to the gas end of an outdoor heat exchanger (22), and the suction | inhalation end is connected to a gas refrigerant flow path (13). Further, the first on-off valve (51) is set in the open state, and the second on-off valve (52) and the third on-off valve (53) are set in the closed state. The opening of the outdoor expansion valve (23) is set to a fully open state, and the opening of the indoor expansion valve (26) is set to a predetermined opening (the superheat degree of the refrigerant at the outlet of the indoor heat exchanger (27) is the target superheat degree). The opening degree of the heat storage expansion valve (42) is set to a fully closed state. The opening degree of the outdoor supercooling expansion valve (24c) is adjusted to a predetermined opening degree, and the opening degree of the heat storage side supercooling expansion valve (25c) is set to a fully closed state. The opening degree of the pressure control valve (45) is set to a fully closed state, and the flow path opening / closing valve (46) is set to an open state. Then, the compressor (21), the outdoor fan (22a), and the indoor fan (27a) are set to the drive state, and the circulation pump (33) is set to the stop state. These settings and adjustments are performed in response to control by the controller (100). The same applies to the following description.
圧縮機(21)から吐出された冷媒は、室外熱交換器(22)に流入し、室外熱交換器(22)において室外空気に放熱して凝縮する。室外熱交換器(22)から流出した冷媒は、全開状態の室外膨張弁(23)を通過して室外側過冷却熱交換器(24)に流入し、室外側過冷却熱交換器(24)において冷却される。室外側過冷却熱交換器(24)から流出した冷媒は、液冷媒流路(12)において開状態の第1開閉弁(51)と蓄熱側過冷却熱交換器(25)とを順に通過して室内膨張弁(26)に流入し、室内膨張弁(26)において減圧される。室内膨張弁(26)を通過した冷媒は、室内熱交換器(27)に流入し、室内熱交換器(27)において室内空気から吸熱して蒸発する。これにより、室内空気が冷却される。室内熱交換器(27)から流出した冷媒は、ガス冷媒流路(13)を通過して圧縮機(21)に吸入されて再び圧縮される。 The refrigerant discharged from the compressor (21) flows into the outdoor heat exchanger (22), dissipates heat to the outdoor air and condenses in the outdoor heat exchanger (22). The refrigerant that has flowed out of the outdoor heat exchanger (22) passes through the fully-expanded outdoor expansion valve (23) and flows into the outdoor subcooling heat exchanger (24), and the outdoor subcooling heat exchanger (24). Cooled. The refrigerant that has flowed out of the outdoor supercooling heat exchanger (24) sequentially passes through the first open / close valve (51) and the heat storage side supercooling heat exchanger (25) in the liquid refrigerant flow path (12). Flows into the indoor expansion valve (26) and is depressurized in the indoor expansion valve (26). The refrigerant that has passed through the indoor expansion valve (26) flows into the indoor heat exchanger (27), absorbs heat from the indoor air in the indoor heat exchanger (27), and evaporates. Thereby, indoor air is cooled. The refrigerant that has flowed out of the indoor heat exchanger (27) passes through the gas refrigerant channel (13), is sucked into the compressor (21), and is compressed again.
なお、圧力調節機構(44)の流路開閉弁(46)が開状態に設定されているので、蓄熱用熱交換器(43)の冷媒側通路(43a)に冷媒が溜まり込むことを防止することができる。 In addition, since the flow path on-off valve (46) of the pressure adjusting mechanism (44) is set to the open state, the refrigerant is prevented from collecting in the refrigerant side passage (43a) of the heat storage heat exchanger (43). be able to.
〔単純暖房運転〕
次に、図3を参照して、単純暖房運転について説明する。単純暖房運転とは、冷媒回路(11)の冷凍サイクルによって得られる温熱のみを用いて室内の暖房を行う運転である。
[Simple heating operation]
Next, the simple heating operation will be described with reference to FIG. The simple heating operation is an operation for heating the room using only the heat obtained by the refrigeration cycle of the refrigerant circuit (11).
冷媒回路(11)では、室内熱交換器(27)が凝縮器となり室外熱交換器(22)が蒸発器となる冷凍サイクル(単純暖房サイクル)が行われる。一方、蓄熱回路(31)では、蓄熱媒体が循環しない。 In the refrigerant circuit (11), a refrigeration cycle (simple heating cycle) is performed in which the indoor heat exchanger (27) serves as a condenser and the outdoor heat exchanger (22) serves as an evaporator. On the other hand, in the heat storage circuit (31), the heat storage medium does not circulate.
具体的には、四方切換弁(28)が第2状態に設定される。これにより、圧縮機(21)は、その吐出端がガス冷媒流路(13)に接続され、その吸入端が室外熱交換器(22)のガス端に接続される。また、第1開閉弁(51)と第2開閉弁(52)と第3開閉弁(53)が閉状態に設定される。室外膨張弁(23)の開度が所定の開度(室外熱交換器(22)の出口における冷媒の過熱度が目標過熱度となる開度)に調節され、室内膨張弁(26)の開度が所定の開度(室内熱交換器(27)の出口における冷媒の過冷却度が目標過冷却度となる開度)に調節され、蓄熱用膨張弁(42)の開度が全閉状態に設定される。室外側過冷却膨張弁(24c)の開度が全閉状態に設定され、蓄熱側過冷却膨張弁(25c)の開度が全閉状態に設定される。圧力調節弁(45)の開度が全閉状態に設定され、流路開閉弁(46)が閉状態に設定される。圧縮機(21)と室外ファン(22a)と室内ファン(27a)が駆動状態に設定され、循環ポンプ(33)が停止状態に設定される。 Specifically, the four-way selector valve (28) is set to the second state. Thereby, the discharge end of the compressor (21) is connected to the gas refrigerant flow path (13), and the suction end thereof is connected to the gas end of the outdoor heat exchanger (22). Further, the first on-off valve (51), the second on-off valve (52), and the third on-off valve (53) are set in a closed state. The opening degree of the outdoor expansion valve (23) is adjusted to a predetermined opening degree (the opening degree at which the refrigerant superheat degree at the outlet of the outdoor heat exchanger (22) becomes the target superheat degree), and the indoor expansion valve (26) is opened. The degree of opening is adjusted to a predetermined opening (the opening at which the degree of refrigerant subcooling at the outlet of the indoor heat exchanger (27) becomes the target subcooling degree), and the opening of the heat storage expansion valve (42) is fully closed Set to The opening degree of the outdoor supercooling expansion valve (24c) is set to a fully closed state, and the opening degree of the heat storage side supercooling expansion valve (25c) is set to a fully closed state. The opening degree of the pressure control valve (45) is set to a fully closed state, and the flow path opening / closing valve (46) is set to a closed state. The compressor (21), the outdoor fan (22a), and the indoor fan (27a) are set to the drive state, and the circulation pump (33) is set to the stop state.
圧縮機(21)から吐出された冷媒は、ガス冷媒流路(13)を通過して室内熱交換器(27)に流入し、室内熱交換器(27)において室内空気に放熱して凝縮する。これにより、室内空気が加熱される。室内熱交換器(27)から流出した冷媒は、室内膨張弁(26)を通過し、液冷媒流路(12)において蓄熱側過冷却熱交換器(25)と第3接続点(P3)と第1逆止弁(51a)と第1接続点(P1)とを順に通過し、室外側過冷却熱交換器(24)を通過して室外膨張弁(23)において減圧される。室外膨張弁(23)を通過した冷媒は、室外熱交換器(22)に流入し、室外熱交換器(22)において室外空気から吸熱して蒸発する。室外熱交換器(22)から流出した冷媒は、圧縮機(21)に吸入されて再び圧縮される。 The refrigerant discharged from the compressor (21) passes through the gas refrigerant flow path (13), flows into the indoor heat exchanger (27), and dissipates heat to the indoor air and condenses in the indoor heat exchanger (27). . Thereby, indoor air is heated. The refrigerant flowing out of the indoor heat exchanger (27) passes through the indoor expansion valve (26), and in the liquid refrigerant flow path (12), the heat storage side subcooling heat exchanger (25) and the third connection point (P3) It passes through the first check valve (51a) and the first connection point (P1) in order, passes through the outdoor supercooling heat exchanger (24), and is depressurized in the outdoor expansion valve (23). The refrigerant that has passed through the outdoor expansion valve (23) flows into the outdoor heat exchanger (22), and absorbs heat from outdoor air and evaporates in the outdoor heat exchanger (22). The refrigerant flowing out of the outdoor heat exchanger (22) is sucked into the compressor (21) and compressed again.
〔蓄冷運転〕
次に、図4を参照して、蓄冷運転について説明する。蓄冷運転とは、冷媒回路(11)の冷凍サイクルによって得られる冷熱を蓄熱回路(31)の蓄熱タンク(32)に蓄える運転である。
(Cool storage operation)
Next, the cold storage operation will be described with reference to FIG. The cold storage operation is an operation in which cold heat obtained by the refrigeration cycle of the refrigerant circuit (11) is stored in the heat storage tank (32) of the heat storage circuit (31).
冷媒回路(11)では、室外熱交換器(22)が凝縮器となり予熱用熱交換器(41)が過冷却器となり蓄熱用熱交換器(43)が蒸発器となる冷凍サイクル(蓄冷サイクル)が行われる。一方、蓄熱回路(31)では、循環動作(蓄熱媒体を循環させる動作)が行われる。 In the refrigerant circuit (11), the outdoor heat exchanger (22) serves as a condenser and the preheating heat exchanger (41) serves as a subcooler and the heat storage heat exchanger (43) serves as an evaporator (cold storage cycle). Is done. On the other hand, in the heat storage circuit (31), a circulation operation (an operation for circulating the heat storage medium) is performed.
具体的には、四方切換弁(28)が第1状態に設定される。これにより、圧縮機(21)は、その吐出端が室外熱交換器(22)のガス端に接続され、その吸入端がガス冷媒流路(13)に接続される。また、第1開閉弁(51)が開状態に設定され、第2開閉弁(52)と第3開閉弁(53)が閉状態に設定される。室外膨張弁(23)の開度が全開状態に設定され、室内膨張弁(26)の開度が全閉状態に設定され、蓄熱用膨張弁(42)の開度が所定の開度(蓄熱用熱交換器の出口における冷媒の蒸発温度が目標蒸発温度となる開度)に調節される。室外側過冷却膨張弁(24c)の開度が全閉状態に設定され、蓄熱側過冷却膨張弁(25c)の開度が全閉状態に設定される。圧力調節弁(45)の開度が全閉状態に設定され、流路開閉弁(46)が開状態に設定される。圧縮機(21)と室外ファン(22a)が駆動状態に設定され、室内ファン(27a)が停止状態に設定され、循環ポンプ(33)が駆動状態に設定される。なお、圧縮機(21)は、概ね一定の回転数で作動する。 Specifically, the four-way selector valve (28) is set to the first state. Thereby, as for the compressor (21), the discharge end is connected to the gas end of an outdoor heat exchanger (22), and the suction | inhalation end is connected to a gas refrigerant flow path (13). Further, the first on-off valve (51) is set in the open state, and the second on-off valve (52) and the third on-off valve (53) are set in the closed state. The opening of the outdoor expansion valve (23) is set to a fully open state, the opening of the indoor expansion valve (26) is set to a fully closed state, and the opening of the heat storage expansion valve (42) is set to a predetermined opening (heat storage). The degree of opening at which the refrigerant evaporating temperature at the outlet of the heat exchanger becomes the target evaporating temperature is adjusted. The opening degree of the outdoor supercooling expansion valve (24c) is set to a fully closed state, and the opening degree of the heat storage side supercooling expansion valve (25c) is set to a fully closed state. The opening degree of the pressure control valve (45) is set to a fully closed state, and the flow path opening / closing valve (46) is set to an open state. The compressor (21) and the outdoor fan (22a) are set to the drive state, the indoor fan (27a) is set to the stop state, and the circulation pump (33) is set to the drive state. The compressor (21) operates at a substantially constant rotational speed.
圧縮機(21)から吐出された冷媒は、室外熱交換器(22)に流入し、室外熱交換器(22)において室外空気に放熱して凝縮する。室外熱交換器(22)から流出した冷媒は、全開状態の室外膨張弁(23)と室外側過冷却熱交換器(24)とを順に通過して液冷媒流路(12)に流入する。液冷媒流路(12)に流入した冷媒は、第1接続点(P1)を通過してバイパス流路(14)に流入する。バイパス流路(14)に流入した冷媒は、予熱用熱交換器(41)の冷媒側通路(41a)に流入し、予熱用熱交換器(41)の冷媒側通路(41a)を通過する間に蓄熱側通路(41b)を流れる蓄熱媒体に放熱して冷却される。予熱用熱交換器(41)の冷媒側通路(41a)から流出した冷媒は、蓄熱用膨張弁(42)において減圧されて蓄熱用熱交換器(43)の冷媒側通路(43a)に流入し、蓄熱用熱交換器(43)の冷媒側通路(43a)を通過する間に蓄熱側通路(43b)を流れる蓄熱媒体から吸熱して蒸発する。蓄熱用熱交換器(43)の冷媒側通路(43a)から流出した冷媒は、圧力調節機構(44)の開状態の流路開閉弁(46)とガス冷媒流路(13)とを順に通過し、圧縮機(21)に吸入されて再び圧縮される。 The refrigerant discharged from the compressor (21) flows into the outdoor heat exchanger (22), dissipates heat to the outdoor air and condenses in the outdoor heat exchanger (22). The refrigerant flowing out of the outdoor heat exchanger (22) sequentially passes through the fully opened outdoor expansion valve (23) and the outdoor subcooling heat exchanger (24) and flows into the liquid refrigerant flow path (12). The refrigerant flowing into the liquid refrigerant channel (12) passes through the first connection point (P1) and flows into the bypass channel (14). The refrigerant flowing into the bypass channel (14) flows into the refrigerant side passage (41a) of the preheating heat exchanger (41) and passes through the refrigerant side passage (41a) of the preheating heat exchanger (41). The heat is transferred to the heat storage medium flowing through the heat storage side passage (41b) and cooled. The refrigerant flowing out from the refrigerant side passage (41a) of the preheating heat exchanger (41) is decompressed in the heat storage expansion valve (42) and flows into the refrigerant side passage (43a) of the heat storage heat exchanger (43). Then, while passing through the refrigerant side passage (43a) of the heat storage heat exchanger (43), it absorbs heat from the heat storage medium flowing through the heat storage side passage (43b) and evaporates. The refrigerant flowing out from the refrigerant side passage (43a) of the heat storage heat exchanger (43) sequentially passes through the open channel on-off valve (46) and the gas refrigerant channel (13) of the pressure adjustment mechanism (44). Then, it is sucked into the compressor (21) and compressed again.
なお、第1開閉弁(51)が開状態に設定されているので、バイパス流路(14)の第1接続点(P1)から室内膨張弁(26)に至る配管部(液管)に液冷媒が溜まり込むことになる。これにより、この配管部における冷媒の状態を単純冷房運転と同様の状態にすることができるので、余剰冷媒の発生を防止することができる。 In addition, since the 1st on-off valve (51) is set to the open state, it is liquid in the piping part (liquid pipe) from the 1st connection point (P1) of a bypass flow path (14) to an indoor expansion valve (26). The refrigerant will accumulate. Thereby, since the state of the refrigerant | coolant in this piping part can be made into the state similar to a simple cooling operation, generation | occurrence | production of an excess refrigerant | coolant can be prevented.
蓄熱回路(31)では、蓄熱タンク(32)から流出した蓄熱媒体は、予熱用熱交換器(41)の蓄熱側通路(41b)に流入し、予熱用熱交換器(41)の蓄熱側通路(41b)を通過する間に冷媒側通路(41a)を流れる冷媒によって加熱される。予熱用熱交換器(41)の蓄熱側通路(41b)から流出した蓄熱媒体は、循環ポンプ(33)を通過して蓄熱用熱交換器(43)の蓄熱側通路(43b)に流入し、蓄熱用熱交換器(43)の蓄熱側通路(43b)を通過する間に冷媒側通路(43a)を流れる冷媒によって冷却される。蓄熱用熱交換器(43)の蓄熱側通路(43b)から流出した蓄熱媒体は、蓄熱タンク(32)に流入する。このようにして、蓄熱タンク(32)に冷熱が蓄えられる。 In the heat storage circuit (31), the heat storage medium flowing out of the heat storage tank (32) flows into the heat storage side passage (41b) of the preheating heat exchanger (41), and the heat storage side passage of the preheating heat exchanger (41). Heated by the refrigerant flowing through the refrigerant side passage (41a) while passing through (41b). The heat storage medium flowing out from the heat storage side passage (41b) of the preheating heat exchanger (41) passes through the circulation pump (33) and flows into the heat storage side passage (43b) of the heat storage heat exchanger (43), Cooling is performed by the refrigerant flowing through the refrigerant side passage (43a) while passing through the heat storage side passage (43b) of the heat storage heat exchanger (43). The heat storage medium that has flowed out of the heat storage side passage (43b) of the heat storage heat exchanger (43) flows into the heat storage tank (32). In this way, cold heat is stored in the heat storage tank (32).
〔利用冷房運転〕
次に、図5を参照して、利用冷房運転について説明する。利用冷房運転とは、蓄熱タンク(32)に蓄えられた冷熱と冷媒回路(11)の冷凍サイクルによって得られる冷熱とを用いて室内の冷房を行う運転である。
[Use cooling operation]
Next, referring to FIG. 5, the use cooling operation will be described. The use cooling operation is an operation for cooling the room using the cold heat stored in the heat storage tank (32) and the cold heat obtained by the refrigeration cycle of the refrigerant circuit (11).
冷媒回路(11)では、室外熱交換器(22)が凝縮器となり予熱用熱交換器(41)および蓄熱用熱交換器(43)が過冷却器となり室内熱交換器(27)が蒸発器となる冷凍サイクル(利用冷房サイクル)が行われる。一方、蓄熱回路(31)では、循環動作が行われる。 In the refrigerant circuit (11), the outdoor heat exchanger (22) serves as a condenser, the preheating heat exchanger (41) and the heat storage heat exchanger (43) serve as a subcooler, and the indoor heat exchanger (27) serves as an evaporator. A refrigeration cycle (utilization cooling cycle) is performed. On the other hand, the circulation operation is performed in the heat storage circuit (31).
具体的には、四方切換弁(28)が第1状態に設定される。これにより、圧縮機(21)は、その吐出端が室外熱交換器(22)のガス端に接続され、その吸入端がガス冷媒流路(13)に接続される。また、第1開閉弁(51)が閉状態に設定され、第2開閉弁(52)と第3開閉弁(53)が開状態に設定される。室外膨張弁(23)の開度が全開状態に設定され、室内膨張弁(26)の開度が所定の開度(室内熱交換器の出口における冷媒の過熱度が目標過熱度となる開度)に調節され、蓄熱用膨張弁(42)の開度が全開状態に設定される。室外側過冷却膨張弁(24c)の開度が全閉状態に設定され、蓄熱側過冷却膨張弁(25c)の開度が所定の開度に調節される。圧力調節弁(45)の開度が全閉状態に設定され、流路開閉弁(46)が閉状態に設定される。圧縮機(21)と室外ファン(22a)と室内ファン(27a)が駆動状態に設定され、循環ポンプ(33)が駆動状態に設定される。 Specifically, the four-way selector valve (28) is set to the first state. Thereby, as for the compressor (21), the discharge end is connected to the gas end of an outdoor heat exchanger (22), and the suction | inhalation end is connected to a gas refrigerant flow path (13). Further, the first on-off valve (51) is set in a closed state, and the second on-off valve (52) and the third on-off valve (53) are set in an open state. The opening degree of the outdoor expansion valve (23) is set to a fully open state, and the opening degree of the indoor expansion valve (26) is a predetermined opening degree (an opening degree at which the superheat degree of the refrigerant at the outlet of the indoor heat exchanger becomes the target superheat degree. ) And the opening degree of the heat storage expansion valve (42) is set to a fully open state. The opening degree of the outdoor supercooling expansion valve (24c) is set to a fully closed state, and the opening degree of the heat storage side supercooling expansion valve (25c) is adjusted to a predetermined opening degree. The opening degree of the pressure control valve (45) is set to a fully closed state, and the flow path opening / closing valve (46) is set to a closed state. The compressor (21), the outdoor fan (22a), and the indoor fan (27a) are set to the driving state, and the circulation pump (33) is set to the driving state.
圧縮機(21)から吐出された冷媒は、室外熱交換器(22)に流入し、室外熱交換器(22)において室外空気に放熱して凝縮する。室外熱交換器(22)から流出した冷媒は、全開状態の室外膨張弁(23)と室外側過冷却熱交換器(24)とを順に通過して液冷媒流路(12)に流入する。液冷媒流路(12)に流入した冷媒は、第1接続点(P1)を通過してバイパス流路(14)に流入する。バイパス流路(14)に流入した冷媒は、予熱用熱交換器(41)の冷媒側通路(41a)に流入し、予熱用熱交換器(41)の冷媒側通路(41a)を通過する間に蓄熱側通路(41b)を流れる蓄熱媒体に放熱して冷却される。予熱用熱交換器(41)の冷媒側通路(41a)から流出した冷媒は、全開状態の蓄熱用膨張弁(42)および開状態の第2開閉弁(52)を通過して蓄熱用熱交換器(43)の冷媒側通路(43a)に流入し、蓄熱用熱交換器(43)の冷媒側通路(43a)を通過する間に蓄熱側通路(43b)を流れる蓄熱媒体に放熱して冷却される。蓄熱用熱交換器(43)の冷媒側通路(43a)から流出した冷媒は、開状態の第3開閉弁(53)と第3逆止弁(51c)とを順に通過して液冷媒流路(12)に流入し、液冷媒流路(12)において第3接続点(P3)と第2接続点(P2)とを順に通過して蓄熱側過冷却熱交換器(25)に流入し、蓄熱側過冷却熱交換器(25)において冷却される。蓄熱側過冷却熱交換器(25)において冷却された冷媒は、室内膨張弁(26)において減圧されて室内熱交換器(27)に流入し、室内熱交換器(27)において室内空気から吸熱して蒸発する。これにより、室内空気が冷却される。室内熱交換器(27)から流出した冷媒は、ガス冷媒流路(13)を通過して圧縮機(21)に吸入されて再び圧縮される。 The refrigerant discharged from the compressor (21) flows into the outdoor heat exchanger (22), dissipates heat to the outdoor air and condenses in the outdoor heat exchanger (22). The refrigerant flowing out of the outdoor heat exchanger (22) sequentially passes through the fully opened outdoor expansion valve (23) and the outdoor subcooling heat exchanger (24) and flows into the liquid refrigerant flow path (12). The refrigerant flowing into the liquid refrigerant channel (12) passes through the first connection point (P1) and flows into the bypass channel (14). The refrigerant flowing into the bypass channel (14) flows into the refrigerant side passage (41a) of the preheating heat exchanger (41) and passes through the refrigerant side passage (41a) of the preheating heat exchanger (41). The heat is transferred to the heat storage medium flowing through the heat storage side passage (41b) and cooled. The refrigerant flowing out of the refrigerant side passage (41a) of the preheating heat exchanger (41) passes through the fully open heat storage expansion valve (42) and the open second open / close valve (52) to exchange heat for heat storage. Into the refrigerant side passage (43a) of the heat exchanger (43) and dissipate heat to the heat storage medium flowing through the heat storage side passage (43b) while passing through the refrigerant side passage (43a) of the heat storage heat exchanger (43) and cool Is done. The refrigerant that has flowed out of the refrigerant side passage (43a) of the heat storage heat exchanger (43) passes through the third open / close valve (53) and the third check valve (51c) in the open state in order, and the liquid refrigerant flow path. (12), and sequentially passes through the third connection point (P3) and the second connection point (P2) in the liquid refrigerant flow path (12) and flows into the heat storage side subcooling heat exchanger (25), It cools in the heat storage side subcooling heat exchanger (25). The refrigerant cooled in the heat storage side supercooling heat exchanger (25) is decompressed in the indoor expansion valve (26) and flows into the indoor heat exchanger (27), and absorbs heat from indoor air in the indoor heat exchanger (27). And evaporate. Thereby, indoor air is cooled. The refrigerant that has flowed out of the indoor heat exchanger (27) passes through the gas refrigerant channel (13), is sucked into the compressor (21), and is compressed again.
蓄熱回路(31)では、蓄熱タンク(32)から流出した蓄熱媒体は、予熱用熱交換器(41)の蓄熱側通路(41b)に流入し、予熱用熱交換器(41)の蓄熱側通路(41b)を通過する間に冷媒側通路(41a)を流れる冷媒から吸熱する。予熱用熱交換器(41)の蓄熱側通路(41b)から流出した蓄熱媒体は、循環ポンプ(33)を通過して蓄熱用熱交換器(43)の蓄熱側通路(43b)に流入し、蓄熱用熱交換器(43)の蓄熱側通路(43b)を通過する間に冷媒側通路(43a)を流れる冷媒から吸熱する。蓄熱用熱交換器(43)の蓄熱側通路(43b)から流出した蓄熱媒体は、蓄熱タンク(32)に流入する。このようにして、蓄熱媒体から冷媒へ冷熱が付与される。 In the heat storage circuit (31), the heat storage medium flowing out of the heat storage tank (32) flows into the heat storage side passage (41b) of the preheating heat exchanger (41), and the heat storage side passage of the preheating heat exchanger (41). Heat is absorbed from the refrigerant flowing through the refrigerant side passage (41a) while passing through (41b). The heat storage medium flowing out from the heat storage side passage (41b) of the preheating heat exchanger (41) passes through the circulation pump (33) and flows into the heat storage side passage (43b) of the heat storage heat exchanger (43), Heat is absorbed from the refrigerant flowing through the refrigerant side passage (43a) while passing through the heat storage side passage (43b) of the heat storage heat exchanger (43). The heat storage medium that has flowed out of the heat storage side passage (43b) of the heat storage heat exchanger (43) flows into the heat storage tank (32). In this way, cold heat is applied from the heat storage medium to the refrigerant.
〔冷房蓄冷運転〕
次に、図6を参照して、冷房蓄冷運転について説明する。冷房蓄冷運転とは、冷媒回路(11)の冷凍サイクルによって得られた冷熱の一部を用いて室内の冷房を行いながら、残りの冷熱を蓄熱タンクに蓄える運転のことである。すなわち、冷房蓄冷運転では、蓄冷と冷房とが同時に行われる。
(Cooling / cooling operation)
Next, the cooling and accumulating operation will be described with reference to FIG. The cooling / storage operation is an operation in which the remaining cold energy is stored in the heat storage tank while the room is cooled using a part of the cold energy obtained by the refrigeration cycle of the refrigerant circuit (11). That is, cold storage and cooling are performed simultaneously in the cooling storage operation.
冷媒回路(11)では、室外熱交換器(22)が凝縮器となり予熱用熱交換器(41)が過冷却器となり室内熱交換器(27)および蓄熱用熱交換器(43)が蒸発器となる冷凍サイクル(冷房蓄冷サイクル)が行われる。一方、蓄熱回路(31)では、循環動作が行われる。 In the refrigerant circuit (11), the outdoor heat exchanger (22) is a condenser and the preheating heat exchanger (41) is a subcooler, and the indoor heat exchanger (27) and the heat storage heat exchanger (43) are evaporators. The refrigeration cycle (cooling storage cycle) is performed. On the other hand, the circulation operation is performed in the heat storage circuit (31).
具体的には、四方切換弁(28)が第1状態に設定される。これにより、圧縮機(21)は、その吐出端が室外熱交換器(22)のガス端に接続され、その吸入端がガス冷媒流路(13)に接続される。また、第1開閉弁(51)が開状態に設定され、第2開閉弁(52)と第3開閉弁(53)が閉状態に設定される。室外膨張弁(23)の開度が全開状態に設定され、室内膨張弁(26)の開度が所定の開度(室内熱交換器の出口における冷媒の過熱度が目標過熱度となる開度)に調節され、蓄熱用膨張弁(42)の開度が所定の開度(蓄熱用熱交換器(43)の出口における冷媒の過熱度が目標過熱度となる開度)に調節される。室外側過冷却膨張弁(24c)の開度が全閉状態に設定され、蓄熱側過冷却膨張弁(25c)の開度が所定の開度に調節される。圧力調節弁(45)の開度が所定の開度に調節され、流路開閉弁(46)が閉状態に設定される。圧縮機(21)と室外ファン(22a)と室内ファン(27a)が駆動状態に設定され、循環ポンプ(33)が駆動状態に設定される。 Specifically, the four-way selector valve (28) is set to the first state. Thereby, as for the compressor (21), the discharge end is connected to the gas end of an outdoor heat exchanger (22), and the suction | inhalation end is connected to a gas refrigerant flow path (13). Further, the first on-off valve (51) is set in the open state, and the second on-off valve (52) and the third on-off valve (53) are set in the closed state. The opening degree of the outdoor expansion valve (23) is set to a fully open state, and the opening degree of the indoor expansion valve (26) is a predetermined opening degree (an opening degree at which the superheat degree of the refrigerant at the outlet of the indoor heat exchanger becomes the target superheat degree. ) And the opening degree of the heat storage expansion valve (42) is adjusted to a predetermined opening degree (an opening degree at which the superheat degree of the refrigerant at the outlet of the heat storage heat exchanger (43) becomes the target superheat degree). The opening degree of the outdoor supercooling expansion valve (24c) is set to a fully closed state, and the opening degree of the heat storage side supercooling expansion valve (25c) is adjusted to a predetermined opening degree. The opening degree of the pressure control valve (45) is adjusted to a predetermined opening degree, and the flow path opening / closing valve (46) is set to a closed state. The compressor (21), the outdoor fan (22a), and the indoor fan (27a) are set to the driving state, and the circulation pump (33) is set to the driving state.
圧縮機(21)から吐出された冷媒は、室外熱交換器(22)に流入し、室外熱交換器(22)において室外空気に放熱して凝縮する。室外熱交換器(22)から流出した冷媒は、全開状態の室外膨張弁(23)と室外側過冷却熱交換器(24)とを順に通過して液冷媒流路(12)に流入する。液冷媒流路(12)に流入して第1接続点(P1)を通過した冷媒は、その一部が開状態の第1開閉弁(51)に流入し、その残部がバイパス流路(14)に流入する。開状態の第1開閉弁(51)を通過した冷媒は、蓄熱側過冷却熱交換器(25)に流入し、蓄熱側過冷却熱交換器(25)において冷却される。蓄熱側過冷却熱交換器(25)において冷却された冷媒は、室内膨張弁(26)において減圧されて室内熱交換器(27)に流入し、室内熱交換器(27)において室内空気から吸熱して蒸発する。これにより、室内空気が冷却される。室内熱交換器(27)から流出した冷媒は、ガス冷媒流路(13)に流入する。一方、バイパス流路(14)に流入した冷媒は、予熱用熱交換器(41)の冷媒側通路(41a)に流入し、予熱用熱交換器(41)の冷媒側通路(41a)を通過する間に蓄熱側通路(41b)を流れる蓄熱媒体に放熱して冷却される。予熱用熱交換器(41)の冷媒側通路(41a)から流出した冷媒は、蓄熱用膨張弁(42)において減圧されて蓄熱用熱交換器(43)の冷媒側通路(43a)に流入し、蓄熱用熱交換器(43)の冷媒側通路(43a)を通過する間に蓄熱側通路(43b)を流れる蓄熱媒体から吸熱して蒸発する。蓄熱用熱交換器(43)の冷媒側通路(43a)から流出した冷媒は、圧力調節機構(44)の圧力調節弁(45)において減圧されてガス冷媒流路(13)に流入する。ガス冷媒流路(13)では、室内熱交換器(27)を通過した冷媒と圧力調節機構(44)の圧力調節弁(45)を通過した冷媒とが合流して圧縮機(21)に吸入され、再び圧縮される。 The refrigerant discharged from the compressor (21) flows into the outdoor heat exchanger (22), dissipates heat to the outdoor air and condenses in the outdoor heat exchanger (22). The refrigerant flowing out of the outdoor heat exchanger (22) sequentially passes through the fully opened outdoor expansion valve (23) and the outdoor subcooling heat exchanger (24) and flows into the liquid refrigerant flow path (12). A part of the refrigerant that has flowed into the liquid refrigerant flow path (12) and passed through the first connection point (P1) flows into the first on-off valve (51) that is open, and the remainder is the bypass flow path (14 ). The refrigerant that has passed through the opened first on-off valve (51) flows into the heat storage side subcooling heat exchanger (25) and is cooled in the heat storage side subcooling heat exchanger (25). The refrigerant cooled in the heat storage side supercooling heat exchanger (25) is decompressed in the indoor expansion valve (26) and flows into the indoor heat exchanger (27), and absorbs heat from indoor air in the indoor heat exchanger (27). And evaporate. Thereby, indoor air is cooled. The refrigerant that has flowed out of the indoor heat exchanger (27) flows into the gas refrigerant channel (13). On the other hand, the refrigerant flowing into the bypass channel (14) flows into the refrigerant side passage (41a) of the preheating heat exchanger (41) and passes through the refrigerant side passage (41a) of the preheating heat exchanger (41). During this time, heat is radiated to the heat storage medium flowing through the heat storage side passage (41b) and cooled. The refrigerant flowing out from the refrigerant side passage (41a) of the preheating heat exchanger (41) is decompressed in the heat storage expansion valve (42) and flows into the refrigerant side passage (43a) of the heat storage heat exchanger (43). Then, while passing through the refrigerant side passage (43a) of the heat storage heat exchanger (43), it absorbs heat from the heat storage medium flowing through the heat storage side passage (43b) and evaporates. The refrigerant that has flowed out of the refrigerant side passage (43a) of the heat storage heat exchanger (43) is depressurized by the pressure adjusting valve (45) of the pressure adjusting mechanism (44) and flows into the gas refrigerant channel (13). In the gas refrigerant flow path (13), the refrigerant that has passed through the indoor heat exchanger (27) and the refrigerant that has passed through the pressure adjustment valve (45) of the pressure adjustment mechanism (44) merge and are sucked into the compressor (21). And compressed again.
蓄熱回路(31)では、蓄熱タンク(32)から流出した蓄熱媒体は、予熱用熱交換器(41)の蓄熱側通路(41b)に流入し、予熱用熱交換器(41)の蓄熱側通路(41b)を通過する間に冷媒側通路(41a)を流れる冷媒によって加熱される。予熱用熱交換器(41)の蓄熱側通路(41b)から流出した蓄熱媒体は、循環ポンプ(33)を通過して蓄熱用熱交換器(43)の蓄熱側通路(43b)に流入し、蓄熱用熱交換器(43)の蓄熱側通路(43b)を通過する間に冷媒側通路(43a)を流れる冷媒によって冷却される。蓄熱用熱交換器(43)の蓄熱側通路(43b)から流出した蓄熱媒体は、蓄熱タンク(32)に流入する。このようにして、蓄熱タンク(32)に冷熱が蓄えられる。 In the heat storage circuit (31), the heat storage medium flowing out of the heat storage tank (32) flows into the heat storage side passage (41b) of the preheating heat exchanger (41), and the heat storage side passage of the preheating heat exchanger (41). Heated by the refrigerant flowing through the refrigerant side passage (41a) while passing through (41b). The heat storage medium flowing out from the heat storage side passage (41b) of the preheating heat exchanger (41) passes through the circulation pump (33) and flows into the heat storage side passage (43b) of the heat storage heat exchanger (43), Cooling is performed by the refrigerant flowing through the refrigerant side passage (43a) while passing through the heat storage side passage (43b) of the heat storage heat exchanger (43). The heat storage medium that has flowed out of the heat storage side passage (43b) of the heat storage heat exchanger (43) flows into the heat storage tank (32). In this way, cold heat is stored in the heat storage tank (32).
このように、予熱用熱交換器(41)では、冷媒側通路(41a)を流れる冷媒によって蓄熱側通路(41b)を流れる蓄熱媒体が加熱される。これにより、蓄熱タンク(32)から流出した蓄熱媒体に含まれる包接水和物を融解させることができるので、蓄熱回路(31)において包接水和物が大量に生成されて蓄熱媒体の循環効率が低下することを抑制することができる。具体的には、予熱用熱交換器(41)から流出した蓄熱媒体が流れる配管部(蓄熱用熱交換器(43)の蓄熱側通路(43b)を含む)において蓄熱媒体の包接水和物が大量に生成されて蓄熱回路(31)を構成する配管が閉塞することを防止することができる。 Thus, in the preheating heat exchanger (41), the heat storage medium flowing through the heat storage side passage (41b) is heated by the refrigerant flowing through the refrigerant side passage (41a). As a result, the clathrate hydrate contained in the heat storage medium flowing out from the heat storage tank (32) can be melted, so that a large amount of clathrate hydrate is generated in the heat storage circuit (31) and the heat storage medium is circulated. It can suppress that efficiency falls. Specifically, the clathrate hydrate of the heat storage medium in the piping part (including the heat storage side passage (43b) of the heat storage heat exchanger (43)) through which the heat storage medium flowing out from the preheat heat exchanger (41) flows It is possible to prevent the pipes forming the heat storage circuit (31) from being blocked due to a large amount of being generated.
〔冷房蓄冷運転における制御〕
次に、図6に示した冷房蓄冷運転における制御(コントローラ(100)による制御)について説明する。冷房蓄冷運転では、コントローラ(100)は、室内側過熱度制御と、蓄熱側過熱度制御と、目標低圧圧力制御と、蓄熱側蒸発温度制御とを並行して行う。なお、以下で説明する温度および過熱度は、各種センサ(図示を省略)の検出値に基づいて検出することが可能である。
[Control in cooling storage operation]
Next, control (control by the controller (100)) in the cooling and regenerating operation shown in FIG. 6 will be described. In the cooling and regenerative operation, the controller (100) performs the indoor side superheat degree control, the heat storage side superheat degree control, the target low pressure control, and the heat storage side evaporation temperature control in parallel. Note that the temperature and the degree of superheat described below can be detected based on detection values of various sensors (not shown).
〈室内側過熱度制御〉
室内側過熱度制御では、コントローラ(100)は、室内熱交換器(27)の出口における冷媒の過熱度(以下、室内側冷媒過熱度と記載)が予め設定された室内側目標過熱度となるように、室内膨張弁(26)の開度を調節する。具体的には、コントローラ(100)は、室内側冷媒過熱度が室内側目標過熱度よりも大きくなると、室内膨張弁(26)の開度を増加させ、室内側冷媒過熱度が室内側目標過熱度よりも小さくなると、室内膨張弁(26)の開度を減少させる。なお、コントローラ(100)は、室内空気温度と予め設定された目標冷房温度との差(目標冷房温度から室内空気温度を減算して得られる差分値)が大きくなるほど、室内側目標過熱度が小さくなるように、室内側目標過熱度を設定する。
<Indoor superheat control>
In the indoor side superheat degree control, the controller (100) sets the superheat degree of the refrigerant at the outlet of the indoor heat exchanger (27) (hereinafter referred to as the indoor side refrigerant superheat degree) to a preset indoor side target superheat degree. Thus, the opening degree of the indoor expansion valve (26) is adjusted. Specifically, when the indoor-side refrigerant superheat degree becomes larger than the indoor-side target superheat degree, the controller (100) increases the opening degree of the indoor expansion valve (26), and the indoor-side refrigerant superheat degree becomes the indoor-side target superheat degree. When it is smaller than the degree, the opening degree of the indoor expansion valve (26) is decreased. The controller (100) decreases the indoor-side target superheat degree as the difference between the room air temperature and the preset target cooling temperature (the difference value obtained by subtracting the room air temperature from the target cooling temperature) increases. Set the indoor-side target superheat degree.
〈蓄熱側過熱度制御〉
蓄熱側過熱度制御では、コントローラ(100)は、蓄熱用熱交換器(43)の出口における冷媒の過熱度(以下、蓄熱側冷媒過熱度と記載)が予め設定された蓄熱側目標過熱度となるように、蓄熱用膨張弁(42)の開度を調節する。具体的には、コントローラ(100)は、蓄熱側冷媒過熱度が蓄熱側目標過熱度よりも大きくなると、室内膨張弁(26)の開度を増加させ、蓄熱側冷媒過熱度が蓄熱側目標過熱度よりも小さくなると、室内膨張弁(26)の開度を減少させる。なお、蓄熱側冷媒過熱度は、第1冷媒温度センサ(61)および第2冷媒温度センサ(62)の検出値に基づいて算出することが可能である。
<Heat storage side superheat control>
In the heat storage side superheat degree control, the controller (100) is configured such that the superheat degree of the refrigerant at the outlet of the heat storage heat exchanger (43) (hereinafter referred to as heat storage side refrigerant superheat degree) is set in advance. Thus, the opening degree of the heat storage expansion valve (42) is adjusted. Specifically, when the heat storage side refrigerant superheat degree becomes larger than the heat storage side target superheat degree, the controller (100) increases the opening of the indoor expansion valve (26), and the heat storage side refrigerant superheat degree becomes the heat storage side target superheat. When it is smaller than the degree, the opening degree of the indoor expansion valve (26) is decreased. The heat storage side refrigerant superheat degree can be calculated based on detection values of the first refrigerant temperature sensor (61) and the second refrigerant temperature sensor (62).
〈目標低圧圧力制御〉
目標低圧圧力制御では、コントローラ(100)は、冷媒回路(11)における低圧圧力(この例では、圧縮機(21)の吸入圧力)が予め設定された目標低圧圧力となるように、圧縮機(21)の回転数を制御する。具体的には、コントローラ(100)は、圧縮機(21)の吸入圧力が目標低圧圧力よりも高くなると、圧縮機(21)の回転数を増加させ、圧縮機(21)の吸入圧力が目標低圧圧力よりも低くなると、圧縮機(21)の回転数を減少させる。なお、コントローラ(100)は、冷房負荷(すなわち、室内空気温度と目標冷媒温度との差)が大きくなるほど、目標低圧圧力が低くなるように、目標低圧圧力を設定する。
<Target low pressure control>
In the target low pressure control, the controller (100) controls the compressor (100) so that the low pressure in the refrigerant circuit (11) (in this example, the suction pressure of the compressor (21)) becomes a preset target low pressure. 21) Control the rotation speed. Specifically, the controller (100) increases the rotation speed of the compressor (21) when the suction pressure of the compressor (21) becomes higher than the target low pressure, and the suction pressure of the compressor (21) becomes the target. When the pressure is lower than the low pressure, the rotational speed of the compressor (21) is decreased. The controller (100) sets the target low pressure so that the target low pressure decreases as the cooling load (that is, the difference between the room air temperature and the target refrigerant temperature) increases.
〈蓄熱側蒸発温度制御〉
蓄熱側蒸発温度制御では、コントローラ(100)は、蓄熱用熱交換器(43)における冷媒の蒸発温度(以下、蓄熱側蒸発温度と記載)が予め設定された下限蒸発温度を下回らないように、圧力調節機構(44)における減圧量を調節する。なお、下限蒸発温度は、蓄熱用熱交換器(43)における蓄熱媒体の冷却に適した冷媒の蒸発温度の温度範囲(以下、蒸発温度の適切範囲と記載)の下限温度に設定されている。蒸発温度の適切範囲は、蓄熱媒体の水和物生成温度と蓄熱用熱交換器(43)の大きさ(熱交換面積)とに基づいて設定することが可能である。例えば、臭化テトラnブチルアンモニウム水溶液を蓄熱媒体として用いる場合、蒸発温度の適切範囲は、約4℃〜7℃の範囲に設定され、下限蒸発温度は、4℃に設定される。
<Heat storage side evaporation temperature control>
In the heat storage side evaporation temperature control, the controller (100) prevents the refrigerant evaporation temperature (hereinafter referred to as heat storage side evaporation temperature) in the heat storage heat exchanger (43) from falling below a preset lower limit evaporation temperature. The amount of pressure reduction in the pressure adjusting mechanism (44) is adjusted. The lower limit evaporating temperature is set to the lower limit temperature of the refrigerant evaporating temperature suitable for cooling the heat storage medium in the heat storage heat exchanger (43) (hereinafter referred to as an appropriate evaporating temperature range). The appropriate range of the evaporation temperature can be set based on the hydrate formation temperature of the heat storage medium and the size (heat exchange area) of the heat storage heat exchanger (43). For example, when an aqueous solution of tetra n-butylammonium bromide is used as the heat storage medium, the appropriate range of the evaporation temperature is set to a range of about 4 ° C. to 7 ° C., and the lower limit evaporation temperature is set to 4 ° C.
この例では、コントローラ(100)は、蓄熱側蒸発温度が予め設定された基準蒸発温度となるように、圧力調節機構(44)の圧力調節弁(45)の開度を調節する。具体的には、コントローラ(100)は、蓄熱側蒸発温度が基準蒸発温度よりも低くなると、圧力調節弁(45)の開度を減少させ、蓄熱側蒸発温度が基準蒸発温度よりも高くなると、圧力調節弁(45)の開度を増加させる。なお、基準蒸発温度は、下限蒸発温度に所定温度(例えば、1℃)を加算して得られる温度(すなわち、下限蒸発温度よりも高い温度)に設定されてい
る。ただし、基準蒸発温度は、蒸発温度の適切範囲の上限温度と同一または上限温度よりも低い温度に設定されていることが好ましい。
In this example, the controller (100) adjusts the opening degree of the pressure adjustment valve (45) of the pressure adjustment mechanism (44) so that the heat storage side evaporation temperature becomes a preset reference evaporation temperature. Specifically, the controller (100) decreases the opening of the pressure control valve (45) when the heat storage side evaporation temperature becomes lower than the reference evaporation temperature, and when the heat storage side evaporation temperature becomes higher than the reference evaporation temperature, Increase the opening of the pressure control valve (45). The reference evaporation temperature is set to a temperature obtained by adding a predetermined temperature (for example, 1 ° C.) to the lower limit evaporation temperature (that is, a temperature higher than the lower limit evaporation temperature). However, the reference evaporation temperature is preferably set to a temperature that is the same as or lower than the upper limit temperature of the appropriate range of the evaporation temperature.
また、この例では、コントローラ(100)は、第2冷媒温度センサ(62)の検出値(すなわち、蓄熱用熱交換器(43)の冷媒入口温度)を蓄熱側蒸発温度とみなして蓄熱側蒸発温度制御を行うように構成されている。 In this example, the controller (100) regards the detected value of the second refrigerant temperature sensor (62) (that is, the refrigerant inlet temperature of the heat storage heat exchanger (43)) as the heat storage side evaporation temperature, and stores the heat on the heat storage side. It is configured to perform temperature control.
〈コントローラによる制御の具体例〉
冷房負荷が増加する(すなわち、室内空気温度が目標冷房温度よりも高くなる)と、目標低圧圧力が低下する。これにより、圧縮機(21)の吸入圧力が目標低圧圧力よりも高くなり、圧縮機(21)の回転数が増加して圧縮機(21)の吸入圧力が低下し、その結果、室内熱交換器(27)における冷媒の蒸発圧力が低下して室内熱交換器(27)における冷媒の蒸発温度が低下する。このようにして、室内熱交換器(27)における冷却能力(すなわち、冷房能力)が確保される。
<Specific examples of control by controller>
When the cooling load increases (that is, the indoor air temperature becomes higher than the target cooling temperature), the target low pressure is decreased. As a result, the suction pressure of the compressor (21) becomes higher than the target low pressure, the number of rotations of the compressor (21) increases and the suction pressure of the compressor (21) decreases, and as a result, indoor heat exchange The refrigerant evaporating pressure in the condenser (27) decreases, and the refrigerant evaporating temperature in the indoor heat exchanger (27) decreases. In this way, the cooling capacity (that is, the cooling capacity) in the indoor heat exchanger (27) is ensured.
一方、圧縮機(21)の吸入圧力の低下に伴い、蓄熱用熱交換器(43)における冷媒の蒸発圧力も低下する。これにより、蓄熱用熱交換器(43)における冷媒の蒸発温度が低下して第2冷媒温度センサ(62)の検出値(すなわち、蓄熱用熱交換器(43)の冷媒入口温度)も低下する。そして、蓄熱用熱交換器(43)の冷媒出口温度が基準蒸発温度よりも低くなると、圧力調節機構(44)の圧力調節弁(45)の開度が減少する。これにより、圧力調節弁(45)における冷媒の減圧量が増加し、蓄熱用熱交換器(43)における冷媒の蒸発圧力が上昇し、その結果、蓄熱用熱交換器(43)における冷媒の蒸発温度が上昇する。 On the other hand, as the suction pressure of the compressor (21) decreases, the evaporation pressure of the refrigerant in the heat storage heat exchanger (43) also decreases. Thereby, the evaporation temperature of the refrigerant in the heat storage heat exchanger (43) is lowered, and the detection value of the second refrigerant temperature sensor (62) (that is, the refrigerant inlet temperature of the heat storage heat exchanger (43)) is also lowered. . When the refrigerant outlet temperature of the heat storage heat exchanger (43) becomes lower than the reference evaporation temperature, the opening degree of the pressure adjustment valve (45) of the pressure adjustment mechanism (44) decreases. Thereby, the pressure reduction amount of the refrigerant in the pressure control valve (45) is increased, and the evaporation pressure of the refrigerant in the heat storage heat exchanger (43) is increased. As a result, the refrigerant is evaporated in the heat storage heat exchanger (43). The temperature rises.
〔実施形態による効果〕
以上のように、圧力調節機構(44)を設けることにより、冷房蓄冷運転(すなわち、冷媒回路(11)において冷房蓄冷サイクルが行われる場合)において、圧縮機(21)の吸入圧力よりも高くなるように蓄熱用熱交換器(43)における冷媒の蒸発圧力を調節することができる。これにより、圧縮機(21)の吸入圧力の低下に伴う蓄熱用熱交換器(43)における冷媒の蒸発圧力の低下を抑制することができ、蓄熱用熱交換器(43)における冷媒の蒸発温度が低くなり過ぎることを防止することができる。したがって、蓄熱用熱交換器(43)において蓄熱媒体が冷却され過ぎることを防止することができ、蓄熱回路(31)における蓄熱媒体の循環効率の低下を抑制することができる。この例では、蓄熱用熱交換器(43)において蓄熱媒体が冷却され過ぎて、包接水和物(すなわち、固体成分)が大量に生成されて蓄熱媒体の循環効率が低下すること(具体的には、包接水和物により蓄熱回路(31)の配管が閉塞されてしまうこと)を抑制することができる。このように、蓄熱用熱交換器(43)において蓄熱媒体が冷却され過ぎることを防止することができるので、冷房蓄冷運転において、室内熱交換器における冷却能力(すなわち、冷房能力)を確保しつつ、蓄熱回路(31)における蓄熱媒体の循環効率の低下を抑制することができる。
[Effects of the embodiment]
As described above, by providing the pressure adjustment mechanism (44), the cooling pressure storage operation (that is, when the cooling storage cycle is performed in the refrigerant circuit (11)) becomes higher than the suction pressure of the compressor (21). Thus, the evaporation pressure of the refrigerant in the heat storage heat exchanger (43) can be adjusted. Thereby, the fall of the evaporating pressure of the refrigerant | coolant in the heat storage heat exchanger (43) accompanying the fall of the suction pressure of a compressor (21) can be suppressed, and the evaporating temperature of the refrigerant | coolant in the heat storage heat exchanger (43) Can be prevented from becoming too low. Therefore, it is possible to prevent the heat storage medium from being excessively cooled in the heat storage heat exchanger (43), and it is possible to suppress a decrease in circulation efficiency of the heat storage medium in the heat storage circuit (31). In this example, the heat storage medium is excessively cooled in the heat storage heat exchanger (43), and a large amount of clathrate hydrate (that is, a solid component) is generated, thereby reducing the circulation efficiency of the heat storage medium (specifically (Clogging of the piping of the heat storage circuit (31) by the clathrate hydrate). Thus, since it is possible to prevent the heat storage medium from being excessively cooled in the heat storage heat exchanger (43), the cooling capacity (that is, the cooling capacity) in the indoor heat exchanger is ensured in the cooling and storing operation. The reduction in the circulation efficiency of the heat storage medium in the heat storage circuit (31) can be suppressed.
また、蓄熱用熱交換器(43)における冷媒の蒸発温度が下限蒸発温度を下回らないように圧力調節機構(44)における減圧量(具体的には、圧力調節弁(45)の開度)を調節することにより、蓄熱用熱交換器(43)における冷媒の蒸発圧力を適切に設定することができる。これにより、蓄熱用熱交換器(43)において蓄熱媒体を適切に冷却することができるので、冷房蓄冷運転において蓄冷を適切に行うことができる。 Also, the amount of pressure reduction in the pressure adjustment mechanism (44) (specifically, the opening of the pressure adjustment valve (45)) is set so that the evaporation temperature of the refrigerant in the heat storage heat exchanger (43) does not fall below the lower limit evaporation temperature. By adjusting, the evaporating pressure of the refrigerant in the heat storage heat exchanger (43) can be set appropriately. Thereby, since the heat storage medium can be appropriately cooled in the heat storage heat exchanger (43), cold storage can be appropriately performed in the cooling and cold storage operation.
圧力調節弁(45)を用いて圧力調節機構(44)を構成することにより、圧力調節弁(45)の開度を調節して圧力調節機構(44)における減圧量を調整することができる。これにより、圧縮機(21)の吸入圧力よりも高くなるように蓄熱用熱交換器(43)における冷媒の蒸発圧力を調節することができ、蓄熱用熱交換器(43)において蓄熱媒体が冷却され過ぎることを防止することができる。 By configuring the pressure control mechanism (44) using the pressure control valve (45), the amount of pressure reduction in the pressure control mechanism (44) can be adjusted by adjusting the opening of the pressure control valve (45). Thereby, the evaporation pressure of the refrigerant in the heat storage heat exchanger (43) can be adjusted to be higher than the suction pressure of the compressor (21), and the heat storage medium is cooled in the heat storage heat exchanger (43). It is possible to prevent being overdone.
圧力調節弁(45)と流路開閉弁(46)とを用いて圧力調節機構(44)を構成することにより、流路開閉弁(46)を開状態に設定して圧力調節弁(45)を全閉状態に設定することができる。これにより、流路開閉弁(46)を経由して蓄熱用熱交換器(43)とガス冷媒流路(13)との間に冷媒を流通させることができる。なお、流路開閉弁(46)における圧力損失は、圧力調節弁(45)における圧力損失よりも小さい。したがって、圧力調節弁(45)を経由して蓄熱用熱交換器(43)とガス冷媒流路(13)との間に冷媒を流通させる場合よりも、圧力調節機構(44)における圧力損失を低減することができる。これにより、冷房蓄冷運転とは異なる他の運転において、圧力調節機構(44)における圧力損失を低減することができ、他の運転を適切に行うことができる。 By constructing the pressure control mechanism (44) using the pressure control valve (45) and the flow path on / off valve (46), the flow path on / off valve (46) is set to the open state and the pressure control valve (45) Can be set to a fully closed state. Thereby, a refrigerant | coolant can be distribute | circulated between the heat exchanger for heat storage (43) and a gas refrigerant flow path (13) via a flow-path on-off valve (46). In addition, the pressure loss in the flow path opening / closing valve (46) is smaller than the pressure loss in the pressure control valve (45). Therefore, the pressure loss in the pressure control mechanism (44) is less than when the refrigerant is circulated between the heat storage heat exchanger (43) and the gas refrigerant flow path (13) via the pressure control valve (45). Can be reduced. Thereby, in another operation different from the cooling and regenerating operation, the pressure loss in the pressure adjusting mechanism (44) can be reduced, and the other operation can be appropriately performed.
(その他の実施形態)
蓄熱媒体は、臭化テトラnブチルアンモニウムを含有する臭化テトラnブチルアンモニウム水溶液以外の蓄熱材であってもよい。蓄熱媒体の濃度は、40%に限定されずともよい。
(Other embodiments)
The heat storage medium may be a heat storage material other than an aqueous solution of tetra nbutylammonium bromide containing tetra nbutylammonium bromide. The concentration of the heat storage medium may not be limited to 40%.
また、以上の実施形態を適宜組み合わせて実施してもよい。以上の実施形態は、本質的に好ましい例示であって、この発明、その適用物、あるいはその用途の範囲を制限することを意図するものではない。 Moreover, you may implement combining the above embodiment suitably. The above embodiments are essentially preferable examples, and are not intended to limit the scope of the present invention, its application, or its use.
以上説明したように、上述の蓄熱式空気調和機は、蓄熱媒体の蓄熱作用を利用して冷熱を蓄えることが可能な空気調和機として有用である。 As described above, the above-described heat storage type air conditioner is useful as an air conditioner that can store cold using the heat storage action of the heat storage medium.
10 蓄熱式空気調和機
11 冷媒回路
12 液冷媒流路
13 ガス冷媒流路
14 バイパス流路
14d 第1分岐配管(第1流路部)
14e 第2分岐配管(第2流路部)
15 分岐流路
20a 室外ユニット
20b 室内ユニット
21 圧縮機
22 室外熱交換器
22a 室外ファン
23 室外膨張弁
24 室外側過冷却熱交換器
25 蓄熱側過冷却熱交換器
26 室内膨張弁
27 室内熱交換器
27a 室内ファン
28 四方切換弁
30 蓄熱ユニット
31 蓄熱回路
32 蓄熱タンク
33 循環ポンプ
41 予熱用熱交換器
42 蓄熱側膨張弁
43 蓄熱用熱交換器
44 圧力調節機構
45 圧力調節弁
46 流路開閉弁(開閉弁)
51 第1開閉弁
52 第2開閉弁
53 第3開閉弁
61 第1冷媒温度センサ
62 第2冷媒温度センサ
100 コントローラ(運転制御部)
DESCRIPTION OF
14e Second branch pipe (second flow path)
15
51 First Open /
Claims (4)
冷却により固体成分が生成される蓄熱媒体が流れる蓄熱回路(31)と、
上記バイパス流路(14)と上記蓄熱回路(31)とに接続され、該バイパス流路(14)を流れる冷媒と該蓄熱回路(31)を流れる蓄熱媒体とを熱交換させる蓄熱用熱交換器(43)と、
上記バイパス流路(14)において上記蓄熱用熱交換器(43)と上記ガス冷媒流路(13)との間に設けられる圧力調節機構(44)とを備え、
上記冷媒回路(11)では、上記圧縮機(21)の吐出端が上記室外熱交換器(22)のガス端に接続され、該圧縮機(21)の吸入端が上記ガス冷媒流路(13)に接続され、該室外熱交換器(22)が凝縮器となり上記室内熱交換器(27)および上記蓄熱用熱交換器(43)が蒸発器となる冷房蓄冷サイクルが行われ、
上記圧力調節機構(44)は、上記蓄熱用熱交換器(43)と上記ガス冷媒流路(13)との間を流れる冷媒の圧力を調節可能に構成されている
ことを特徴とする蓄熱式空気調和機。 Compressor (21), outdoor heat exchanger (22), indoor heat exchanger (27), liquid end of the outdoor heat exchanger (22) and liquid end of the indoor heat exchanger (27) are connected The liquid refrigerant flow path (12), the gas refrigerant flow path (13) to which the gas end of the indoor heat exchanger (27) is connected, and the other end connected to the liquid refrigerant flow path (12). A refrigerant circuit (11) having a bypass channel (14) connected to the gas refrigerant channel (13),
A heat storage circuit (31) through which a heat storage medium in which a solid component is generated by cooling flows;
A heat storage heat exchanger connected to the bypass flow path (14) and the heat storage circuit (31) and exchanging heat between the refrigerant flowing through the bypass flow path (14) and the heat storage medium flowing through the heat storage circuit (31). (43)
A pressure adjusting mechanism (44) provided between the heat storage heat exchanger (43) and the gas refrigerant channel (13) in the bypass channel (14);
In the refrigerant circuit (11), the discharge end of the compressor (21) is connected to the gas end of the outdoor heat exchanger (22), and the suction end of the compressor (21) is connected to the gas refrigerant flow path (13 ), And the outdoor heat exchanger (22) serves as a condenser, and the indoor heat exchanger (27) and the heat storage heat exchanger (43) serve as an evaporator.
The pressure adjustment mechanism (44) is configured to be capable of adjusting the pressure of the refrigerant flowing between the heat storage heat exchanger (43) and the gas refrigerant flow path (13). Air conditioner.
上記冷房蓄冷サイクルが行われるように上記冷媒回路(11)を制御し、上記蓄熱用熱交換器(43)における冷媒の蒸発温度が予め設定された下限蒸発温度を下回らないように、上記圧力調節機構(44)における減圧量を調節する運転制御部(100)をさらに備えている
ことを特徴とする蓄熱式空気調和機。 In claim 1,
The pressure control is performed so that the refrigerant circuit (11) is controlled so that the cooling and regenerating cycle is performed, and the evaporation temperature of the refrigerant in the heat storage heat exchanger (43) does not fall below a preset lower limit evaporation temperature. The regenerative air conditioner further comprising an operation control unit (100) for adjusting the amount of pressure reduction in the mechanism (44).
上記バイパス流路(14)は、上記蓄熱用熱交換器(43)と上記ガス冷媒流路(13)とを接続する第1流路部(14d)を有し、
上記圧力調節機構(44)は、その開度を調節可能に構成されて上記第1流路部(14d)に設けられた圧力調節弁(45)を有している
ことを特徴とする蓄熱式空気調和機。 In claim 1 or 2,
The bypass channel (14) has a first channel part (14d) connecting the heat storage heat exchanger (43) and the gas refrigerant channel (13),
The pressure regulation mechanism (44) is configured to be adjustable in opening degree, and has a pressure regulation valve (45) provided in the first flow path portion (14d), and is a heat storage type. Air conditioner.
上記バイパス流路(14)は、上記第1流路部(14d)と並列に設けられて上記蓄熱用熱交換器(43)と上記ガス冷媒流路(13)とを接続する第2流路部(14e)をさらに有し、
上記圧力調節機構(44)は、その開閉を切換可能に構成されて上記第2流路部(14e)に設けられた開閉弁(46)をさらに有している
ことを特徴とする蓄熱式空気調和機。 In claim 3,
The bypass flow path (14) is provided in parallel with the first flow path portion (14d) to connect the heat storage heat exchanger (43) and the gas refrigerant flow path (13). Part (14e)
The pressure adjusting mechanism (44) is configured to be able to switch between opening and closing thereof, and further includes an on-off valve (46) provided in the second flow path portion (14e). Harmony machine.
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2014266167A JP6020550B2 (en) | 2014-12-26 | 2014-12-26 | Thermal storage air conditioner |
ES15872261T ES2833435T3 (en) | 2014-12-26 | 2015-12-22 | Thermal storage air conditioner |
PCT/JP2015/006407 WO2016103690A1 (en) | 2014-12-26 | 2015-12-22 | Regenerative air conditioner |
EP15872261.1A EP3249320B1 (en) | 2014-12-26 | 2015-12-22 | Thermal storage air conditioner |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2014266167A JP6020550B2 (en) | 2014-12-26 | 2014-12-26 | Thermal storage air conditioner |
Publications (2)
Publication Number | Publication Date |
---|---|
JP2016125736A true JP2016125736A (en) | 2016-07-11 |
JP6020550B2 JP6020550B2 (en) | 2016-11-02 |
Family
ID=56149751
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP2014266167A Expired - Fee Related JP6020550B2 (en) | 2014-12-26 | 2014-12-26 | Thermal storage air conditioner |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP3249320B1 (en) |
JP (1) | JP6020550B2 (en) |
ES (1) | ES2833435T3 (en) |
WO (1) | WO2016103690A1 (en) |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN107166586A (en) * | 2017-05-26 | 2017-09-15 | 郑州云海信息技术有限公司 | A kind of data center's energy-saving air conditioning system and adjusting method |
TWI665412B (en) * | 2017-08-30 | 2019-07-11 | 潤弘精密工程事業股份有限公司 | Housing system for heat balance and air conditioning system for energy-saving using the same |
EP3786547A1 (en) * | 2019-08-30 | 2021-03-03 | SAB Engineers GmbH | Cold storage system and associated method |
CN110360687B (en) * | 2019-09-02 | 2021-05-25 | 北京纳源丰科技发展有限公司 | Water-saving anti-freezing heat pipe air conditioning system for machine room |
Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0694284A (en) * | 1992-09-16 | 1994-04-05 | Hitachi Ltd | Air-conditioning machine |
JPH11118265A (en) * | 1997-10-20 | 1999-04-30 | Hitachi Ltd | Heat storage unit |
JPH11270920A (en) * | 1998-03-20 | 1999-10-05 | Mitsubishi Electric Corp | Multifunctional heat pump system and method of its operation control |
JP2006029738A (en) * | 2004-07-21 | 2006-02-02 | Mitsubishi Electric Corp | Heat storage type air conditioner |
JP2007010288A (en) * | 2005-07-04 | 2007-01-18 | Jfe Engineering Kk | Cooling and heating capacity enhancement method of existing heat pump type air conditioner, thermal storage unit device and heat pump type air conditioner using the device |
JP2008292122A (en) * | 2007-05-28 | 2008-12-04 | Kansai Electric Power Co Inc:The | Heat storage system and heat storage type air conditioner using same |
JP2011058650A (en) * | 2009-09-07 | 2011-03-24 | Hitachi Appliances Inc | Ice heat storage type refrigerating device |
KR20110076527A (en) * | 2009-12-29 | 2011-07-06 | (주)센도리 | The regenerative system air-conditioning apparatus |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN101360959B (en) * | 2006-01-20 | 2011-06-15 | 开利公司 | Method for controlling temperature of multiple chambers of refrigerating transporting apparatus |
WO2010099454A2 (en) * | 2009-02-28 | 2010-09-02 | Electrolux Home Products, Inc. | Method and apparatus for making clear ice |
US8511109B2 (en) * | 2009-07-15 | 2013-08-20 | Whirlpool Corporation | High efficiency refrigerator |
US9327577B2 (en) * | 2013-01-25 | 2016-05-03 | GM Global Technology Operations LLC | Vehicle heat pump system and method utilizing thermal storage |
-
2014
- 2014-12-26 JP JP2014266167A patent/JP6020550B2/en not_active Expired - Fee Related
-
2015
- 2015-12-22 EP EP15872261.1A patent/EP3249320B1/en active Active
- 2015-12-22 WO PCT/JP2015/006407 patent/WO2016103690A1/en active Application Filing
- 2015-12-22 ES ES15872261T patent/ES2833435T3/en active Active
Patent Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0694284A (en) * | 1992-09-16 | 1994-04-05 | Hitachi Ltd | Air-conditioning machine |
JPH11118265A (en) * | 1997-10-20 | 1999-04-30 | Hitachi Ltd | Heat storage unit |
JPH11270920A (en) * | 1998-03-20 | 1999-10-05 | Mitsubishi Electric Corp | Multifunctional heat pump system and method of its operation control |
JP2006029738A (en) * | 2004-07-21 | 2006-02-02 | Mitsubishi Electric Corp | Heat storage type air conditioner |
JP2007010288A (en) * | 2005-07-04 | 2007-01-18 | Jfe Engineering Kk | Cooling and heating capacity enhancement method of existing heat pump type air conditioner, thermal storage unit device and heat pump type air conditioner using the device |
JP2008292122A (en) * | 2007-05-28 | 2008-12-04 | Kansai Electric Power Co Inc:The | Heat storage system and heat storage type air conditioner using same |
JP2011058650A (en) * | 2009-09-07 | 2011-03-24 | Hitachi Appliances Inc | Ice heat storage type refrigerating device |
KR20110076527A (en) * | 2009-12-29 | 2011-07-06 | (주)센도리 | The regenerative system air-conditioning apparatus |
Also Published As
Publication number | Publication date |
---|---|
WO2016103690A1 (en) | 2016-06-30 |
EP3249320A1 (en) | 2017-11-29 |
EP3249320A4 (en) | 2018-10-17 |
ES2833435T3 (en) | 2021-06-15 |
EP3249320B1 (en) | 2020-09-30 |
JP6020550B2 (en) | 2016-11-02 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
JP6052380B2 (en) | Thermal storage air conditioner | |
JP6048566B2 (en) | Thermal storage air conditioner | |
WO2013046720A1 (en) | Hot-water-supplying, air-conditioning system | |
JP2015068620A (en) | Air conditioner | |
JP6020550B2 (en) | Thermal storage air conditioner | |
JP2016125721A (en) | Heat storage type air conditioner | |
JP2014126350A (en) | Air conditioner | |
JP6020548B2 (en) | Thermal storage air conditioner | |
JP2016125725A (en) | Heat storage type air conditioner | |
JP2016125714A (en) | Heat storage type air conditioner | |
WO2016103726A1 (en) | Heat-storage-type air conditioner | |
JP2015210029A (en) | Heat storage system and air conditioning system | |
JP5867539B2 (en) | Thermal storage tank unit and air conditioning system | |
JP2016125695A (en) | Storage air conditioner | |
JP2016125727A (en) | Heat storage type air conditioner | |
JP2016125713A (en) | Storage air conditioner | |
JP6350577B2 (en) | Air conditioner | |
JP2016125716A (en) | Storage air conditioner | |
JP2016125729A (en) | Heat storage type air conditioner | |
JP6052275B2 (en) | Thermal storage air conditioner | |
JP2016125719A (en) | Heat storage type air conditioner | |
JP2016125717A (en) | Storage air conditioner | |
JP2017141981A (en) | Storage type air conditioner | |
JP2017141981A5 (en) | ||
JP2015210027A (en) | Air conditioner |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
A521 | Request for written amendment filed |
Free format text: JAPANESE INTERMEDIATE CODE: A523 Effective date: 20160524 |
|
TRDD | Decision of grant or rejection written | ||
A01 | Written decision to grant a patent or to grant a registration (utility model) |
Free format text: JAPANESE INTERMEDIATE CODE: A01 Effective date: 20160906 |
|
A61 | First payment of annual fees (during grant procedure) |
Free format text: JAPANESE INTERMEDIATE CODE: A61 Effective date: 20160919 |
|
R151 | Written notification of patent or utility model registration |
Ref document number: 6020550 Country of ref document: JP Free format text: JAPANESE INTERMEDIATE CODE: R151 |
|
LAPS | Cancellation because of no payment of annual fees |