US20160209084A1 - Heat recovery refrigeration device - Google Patents
Heat recovery refrigeration device Download PDFInfo
- Publication number
- US20160209084A1 US20160209084A1 US14/915,018 US201414915018A US2016209084A1 US 20160209084 A1 US20160209084 A1 US 20160209084A1 US 201414915018 A US201414915018 A US 201414915018A US 2016209084 A1 US2016209084 A1 US 2016209084A1
- Authority
- US
- United States
- Prior art keywords
- heat
- refrigerant
- heat source
- source side
- usage
- 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.)
- Abandoned
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B13/00—Compression machines, plants or systems, with reversible cycle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
- F24F1/14—Heat exchangers specially adapted for separate outdoor units
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
- F24F1/14—Heat exchangers specially adapted for separate outdoor units
- F24F1/16—Arrangement or mounting thereof
-
- 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
- F25B39/00—Evaporators; Condensers
-
- F25B41/046—
-
- F25B41/062—
-
- 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
- F25B2313/007—Compression machines, plants or systems with reversible cycle not otherwise provided for three pipes connecting the outdoor side to the indoor side with multiple indoor units
-
- 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
- F25B2313/0231—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units with simultaneous cooling and heating
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
- F25B2313/0233—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel arrangements
-
- 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
- F25B2313/025—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units
- F25B2313/0253—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units in parallel arrangements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
- F25B2313/02743—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using three four-way valves
Definitions
- the present invention relates to a heat recovery refrigeration device and particularly relates to a heat recovery refrigeration device which includes a compressor, a plurality of heat source side heat exchangers, and a plurality of usage side heat exchangers and which is able to perform heat recovery between the usage side heat exchangers by sending refrigerant from the usage side heat exchanger which functions as a radiator for refrigerant to the usage side heat exchanger which functions as an evaporator for refrigerant.
- each of the usage side heat exchangers individually functions as an evaporator or a radiator for refrigerant and it is possible to perform heat recovery (here, perform a simultaneous air cooling and air heating operation where an air cooling operation and an air heating operation are performed simultaneously) between the usage side heat exchangers by sending refrigerant from the usage side heat exchanger which functions as a radiator for refrigerant to the usage side heat exchanger which functions as an evaporator for refrigerant.
- this heat recovery refrigeration device switching is possible so that the two heat source side heat exchangers individually function as an evaporator or a radiator for refrigerant and it is possible to perform switching with the two heat source side heat exchangers functioning as an evaporator or a radiator for refrigerant according to the heat load (evaporator load and radiator load) over all of the plurality of the usage side heat exchangers where heat recovery described above is also taken in consideration.
- both of the two heat source side heat exchangers function as evaporators or radiators for refrigerant in a case where the heat load over all of the plurality of the usage side heat exchangers is large, and only the heat source side heat exchanger where the heat exchange capacity is small functions as an evaporator or a radiator for refrigerant in a case where the heat load over all of the plurality of the usage side heat exchangers is small.
- the object of the present invention is a heat recovery refrigeration device which includes a compressor, a plurality of heat source side heat exchangers, and a plurality of usage side heat exchangers and which is able to perform heat recovery between the usage side heat exchangers wherein it is possible to provide a countermeasure for a case where the heat load over all of the plurality of usage side heat exchangers is small while suppressing reductions in operation performance.
- a heat recovery refrigeration device includes a compressor, a plurality of heat source side heat exchangers which are able to switch between individually functioning as an evaporator or a radiator for refrigerant, and a plurality of usage side heat exchangers which are able to switch between individually functioning as an evaporator or a radiator for refrigerant, and which is able to perform heat recovery between the usage side heat exchangers by sending refrigerant from the usage side heat exchanger which functions as a radiator for refrigerant to the usage side heat exchanger which functions as an evaporator for refrigerant.
- the plurality of heat source side heat exchangers have a first heat source side heat exchanger and a second heat source side heat exchanger which has a heat exchange capacity which is 1.8 times to 4.0 times of the first heat source side heat exchanger.
- the heat exchange capacity of the second heat source side heat exchanger is equal to or more than 1.8 times of the first heat source side heat exchanger as described above. For this reason, it is possible to widen the range over which it is possible to reduce the heat load in a case where only the first heat source side heat exchanger where the heat exchange capacity is small functions as an evaporator or a radiator for refrigerant. Due to this, it is possible to provide a countermeasure for a case where the heat load over all of the plurality of usage side heat exchangers is small. Moreover, here, the heat exchange capacity of the second heat source side heat exchanger is equal to or less than 4.0 times of the first heat source side heat exchanger as described above.
- a heat recovery refrigeration device is the heat recovery refrigeration device according to the first aspect wherein the first heat source side heat exchanger is arranged more to the upper side than the second heat source side heat exchanger.
- the two heat source side heat exchangers are arranged to be above and below each other as described above.
- the first heat source side heat exchanger is arranged at the lower side, there is a concern that the desired heat exchange performance will not be obtained due to a state being generated where all of the first heat source side heat exchanger is filled with liquid refrigerant (set below as “liquid sink”) since the heat exchange capacity is small.
- the first heat source side heat exchanger where the heat exchange capacity is small is arranged more to the upper side than the second heat source side heat exchanger where the heat exchange capacity is large as described above.
- the second heat source side heat exchanger where the heat exchange capacity is large is arranged on the lower side and it is possible for it to be difficult for liquid sink to be generated. Due to this, it is possible for a desired heat exchange performance to be exhibited in both of the heat exchange side heat exchangers in a case where the two heat source side heat exchangers are arranged to be above and below each other.
- a heat recovery refrigeration device is the heat recovery refrigeration device according to the first or second aspect wherein a first heat source side flow amount adjustment valve, where adjustment to its opening is possible, is connected with the liquid side of the first heat source side heat exchanger, and a second heat source side flow amount adjustment valve, where adjustment to its opening is possible, is connected with the liquid side of the second heat source side heat exchanger. Then, the rated Cv value of the second heat source side flow amount adjustment valve is larger than the Cv value of the first heat source side flow amount adjustment valve.
- the second heat source side flow amount adjustment valve is used so that the rated Cv value is larger than the first heat source side flow amount adjustment valve. Due to this, it is possible to appropriately adjust the flow amount of refrigerant which flows through each of the heat source side heat exchangers according to the heat exchange capacities of each of the heat source side heat exchangers.
- a heat recovery refrigeration device is the heat recovery refrigeration device according to any of the first to third aspects wherein a first header, which is for performing merging and branching of refrigerant between a plurality of heat transfer tubes which configure the first heat source side heat exchanger, is provided on the gas side of the first heat source side heat exchanger, and a second header, which is for performing merging and branching of refrigerant between a plurality of heat transfer tubes which configure the second heat source side heat exchanger, is provided on the gas side of the second heat source side heat exchanger. Then, the flow path cross sectional area of the second header is larger than the flow path cross sectional area of the first header.
- the second header is used so that the flow path cross sectional area is larger than the first header as described above. Due to this, it is possible to appropriately perform merging and branching of refrigerant between the plurality of heat transfer tubes which configure each of the heat source side heat exchangers and the headers according to the heat exchange capacities of each of the heat source side heat exchangers.
- FIG. 1 is an outline configuration diagram of a simultaneous air cooling and air heating operation air conditioner device as an embodiment of a heat recovery refrigeration device according to the present invention.
- FIG. 2 is a diagram illustrating an internal configuration of an outline of a heat source unit which configures the simultaneous air cooling and air heating operation air conditioner device.
- FIG. 3 is a diagram schematically illustrating the configuration of heat source side heat exchangers.
- FIG. 4 is a diagram illustrating actions (flow of refrigerant) in an air cooling operation mode (where the evaporator load is large) in the simultaneous air cooling and air heating operation air conditioner device.
- FIG. 5 is a diagram illustrating actions (flow of refrigerant) in an air cooling operation mode (where the evaporator load is small) in the simultaneous air cooling and air heating operation air conditioner device.
- FIG. 6 is a diagram illustrating actions (flow of refrigerant) in an air heating operation mode (where the radiator load is large) in the simultaneous air cooling and air heating operation air conditioner device.
- FIG. 7 is a diagram illustrating actions (flow of refrigerant) in an air heating operation mode (where the radiator load is small) in the simultaneous air cooling and air heating operation air conditioner device.
- FIG. 8 is a diagram illustrating actions (flow of refrigerant) in a simultaneous air cooling and air heating operation mode (where the evaporator load is dominant) in the simultaneous air cooling and air heating operation air conditioner device.
- FIG. 9 is a diagram illustrating actions (flow of refrigerant) in a simultaneous air cooling and air heating operation mode (where the radiator load is dominant) in the simultaneous air cooling and air heating operation air conditioner device.
- FIG. 10 is a diagram illustrating actions (flow of refrigerant) in a simultaneous air cooling and air heating operation mode (with a balance between the evaporator and radiator loads) in the simultaneous air cooling and air heating operation air conditioner device.
- FIG. 1 is an outline configuration diagram of a simultaneous air cooling and air heating operation air conditioner device 1 as an embodiment of the heat recovery refrigeration device according to the present invention.
- FIG. 2 is a diagram illustrating an internal configuration of an outline of a heat source unit 2 which configures the simultaneous air cooling and air heating operation air conditioner device 1 .
- FIG. 3 is a diagram schematically illustrating the configuration of heat source side heat exchangers 24 and 25 .
- the simultaneous air cooling and air heating operation air conditioner device 1 is a device which is used indoors in air cooling and air heating such as in buildings by performing a vapor compression type of refrigeration cycle operation.
- the simultaneous air cooling and air heating operation air conditioner device 1 mainly has one heat source unit 2 , a plurality (here, four) usage units 3 a , 3 b , 3 c , and 3 d , connecting units 4 a , 4 b , 4 c , and 4 d which are connected with each of the usage units 3 a , 3 b , 3 c , and 3 d , and refrigerant communication pipes 7 , 8 , and 9 which connect the heat source unit 2 and the usage units 3 a , 3 b , 3 c , and 3 d via the connecting units 4 a , 4 b , 4 c , and 4 d .
- a vapor compression type of refrigerant circuit 10 in the simultaneous air cooling and air heating operation air conditioner device 1 is configured by connecting the heat source unit 2 , the usage units 3 a , 3 b , 3 c , and 3 d , the connecting units 4 a , 4 b , 4 c , and 4 d , and the refrigerant communication pipes 7 , 8 , and 9 .
- the simultaneous air cooling and air heating operation air conditioner device 1 is configured so that it is possible for each of the usage units 3 a , 3 b , 3 c , and 3 d to individually perform an air cooling operation or an air heating operation and so that it is possible to perform heat recovery (here, perform a simultaneous air cooling and air heating operation where an air cooling operation and an air heating operation are performed simultaneously) between the usage units by sending refrigerant from the usage unit which performs an air heating operation to the usage unit which performs an air cooling operation.
- heat recovery here, perform a simultaneous air cooling and air heating operation where an air cooling operation and an air heating operation are performed simultaneously
- the simultaneous air cooling and air heating operation air conditioner device 1 is configured so that the heat load of the heat source unit 2 is balanced according to the heat load over all of the plurality of usage units 3 a , 3 b , 3 c , and 3 d where heat recovery described above (a simultaneous air cooling and air heating operation) is also taken in consideration.
- the usage units 3 a , 3 b , 3 c , and 3 d are arranged indoors such as in a building by being built into or hang down from the ceiling or the like or hang from an internal wall surface or the like.
- the usage units 3 a , 3 b , 3 c , and 3 d are connected with the heat source unit 2 via the refrigerant communication pipes 7 , 8 , and 9 and the connecting units 4 a , 4 b , 4 c , and 4 d and configure a portion of the refrigerant circuit 10 .
- the configuration of the usage units 3 a , 3 b , 3 c , and 3 d will be described.
- the usage unit 3 a and the usage units 3 b , 3 c , and 3 d have the same configuration, only the configuration of the usage unit 3 a will be described here and the subscripts “b”, “c”, and “d” are respectively added instead of the subscript “a” in the reference numerals, which indicate each section of the usage unit 3 a , to the configurations of the usage units 3 b , 3 c , and 3 d and the description of each section is omitted.
- the usage unit 3 a mainly configures a portion of the refrigerant circuit 10 and has a usage side refrigerant circuit 13 a (there are usage side refrigerant circuits 13 b , 13 c , and 13 d respectively in each of the usage units 3 b , 3 c , and 3 d ).
- the usage side refrigerant circuit 13 a mainly has a usage side flow amount adjustment valve 51 a and a usage side heat exchanger 52 a.
- the usage side flow amount adjustment valve 51 a is an electric expansion valve where adjustment to its opening is possible and which is connected with the liquid side of the usage side heat exchanger 52 a in order to perform adjustment of the flow amount of refrigerant which flows through the usage side heat exchanger 52 a and the like.
- the usage side heat exchanger 52 a is a device for performing heat exchange between refrigerant and indoor air and consists of, for example, a fin and tube type of heat exchanger which is configured using a plurality of heat transfer tubes and fins.
- the usage unit 3 a has an indoor fan 53 a for suctioning indoor air into the inside of the unit and supplying the indoor air indoors as supply air after heat exchange is carried out, and heat exchange between indoor air and refrigerant which flows through the usage side heat exchanger 52 a is possible.
- the indoor fan 53 a is driven using an indoor fan motor 54 a.
- the usage unit 3 a has a usage side control section 50 a which controls the actions of each of the sections 51 a and 54 a which configure the usage unit 53 a .
- the usage side control section 50 a has a microcomputer and a memory which are provided in order to perform control of the usage unit 3 a , and it is possible to perform transfer of control signals and the like with a remote controller (which is not shown in the diagrams) and to perform transfer of control signals and the like with the heat source unit 2 .
- the heat source unit 2 is arranged on the roof of a building or the like, is connected with the usage units 3 a , 3 b , 3 c , and 3 d via the refrigerant communication pipes 7 , 8 , and 9 , and configures the refrigerant circuit 10 along with the usage units 3 a , 3 b , 3 c , and 3 d.
- the heat source unit 2 mainly configures a portion of the refrigerant circuit 10 and has a heat source side refrigerant circuit 12 .
- the heat source side refrigerant circuit 12 mainly has a compressor 21 , a plurality (here, two) of heat exchange switching mechanisms 22 and 23 , a plurality (here, two) of heat source side heat exchangers 24 and 25 , a plurality (here, two) of heat source side flow amount adjustment valves 26 and 27 , a receiver 28 , a bridge circuit 29 , a high and low pressure switching mechanism 30 , a liquid side shutoff valve 31 , a high and low pressure gas side shutoff valve 32 , and a low pressure gas side shutoff valve 33 .
- the compressor 21 is a device for compressing refrigerant and consists of, for example, a positive displacement type of compressor such as a scroll type where it is possible to vary the operation capacity by controlling an inverter in a compressor motor 21 a.
- the first heat exchange switching mechanism 22 is a device where it is possible to switch the flow path of refrigerant inside the heat source side refrigerant circuit 12 so that the discharge side of the compressor 21 and the gas side of the first heat source side heat exchanger 24 are connected (refer to the solid line in the first heat exchange switching mechanism 22 in FIG. 1 ) in a case where the first heat source side heat exchanger 24 functions as a radiator for refrigerant (set below as a “radiator operation state”) and so that the suction side of the compressor 21 and the gas side of the first heat source side heat exchanger 24 are connected (refer to the dashed line in the first heat exchange switching mechanism 22 in FIG.
- the first heat source side heat exchanger 24 functions as an evaporator for refrigerant (set below as an “evaporator operation state”) and consists of, for example, a four-path switching valve.
- the second heat exchange switching mechanism 23 is a device where it is possible to switch the flow path of refrigerant inside the heat source side refrigerant circuit 12 so that the discharge side of the compressor 21 and the gas side of the second heat source side heat exchanger 25 are connected (refer to the solid line in the second heat exchange switching mechanism 23 in FIG.
- the second heat source side heat exchanger 25 functions as a radiator for refrigerant (set below as a “radiator operation state”) and so that the suction side of the compressor 21 and the gas side of the second heat source side heat exchanger 25 are connected (refer to the dashed line in the second heat exchange switching mechanism 23 in FIG. 1 ) in a case where the second heat source side heat exchanger 25 functions as an evaporator for refrigerant (set below as an “evaporator operation state”) and consists of, for example, a four-path switching valve.
- first heat source side heat exchanger 24 and the second heat source side heat exchanger 25 individually function as an evaporator or a radiator for refrigerant by modifying the switching states of the first heat exchange switching mechanism 22 and the second heat exchange switching mechanism 23 .
- the first heat source side heat exchanger 24 is a device for performing heat exchange between refrigerant and outdoor air and consists of, for example, a fin and tube type of heat exchanger which is configured using a plurality of heat transfer tubes and fins.
- the gas side of the first heat source side heat exchanger 24 is connected with the first heat exchange switching mechanism 22 and the liquid side of the first heat source side heat exchanger 24 is connected with the first heat source side flow amount adjustment valve 26 .
- the gas side of the first heat source side heat exchanger 24 is provided with a first header 24 a for performing merging and branching of refrigerant between a plurality of heat transfer tubes which configure the first heat source side heat exchanger 24 , and the first header 24 a is connected with the first heat exchange switching mechanism 22 .
- the liquid side of the first heat source side heat exchanger 24 is provided with a first flow divider 24 b for performing merging and branching of refrigerant between a plurality of heat transfer tubes which configure the first heat source side heat exchanger 24 , and the first flow divider 24 b is connected with the first heat source side flow amount adjustment valve 26 .
- the second heat source side heat exchanger 25 is a device for performing heat exchange between refrigerant and outdoor air and consists of, for example, a fin and tube type of heat exchanger which is configured using a plurality of heat transfer tubes and fins.
- the gas side of the second heat source side heat exchanger 25 is connected with the second heat exchange switching mechanism 23 and the liquid side of the second heat source side heat exchanger 25 is connected with the second heat source side flow amount adjustment valve 27 .
- the gas side of the second heat source side heat exchanger 25 is provided with a second header 25 a for performing merging and branching of refrigerant between a plurality of heat transfer tubes which configure the second heat source side heat exchanger 25 , and the second header 25 a is connected with the second heat exchange switching mechanism 23 .
- the liquid side of the second heat source side heat exchanger 25 is provided with a second flow divider 25 b for performing merging and branching of refrigerant between a plurality of heat transfer tubes which configure the second heat source side heat exchanger 25 , and the second flow divider 25 b is connected with the second heat source side flow amount adjustment valve 27 .
- the heat exchange capacities of the first heat source side heat exchanger 24 and the second heat source side heat exchanger 25 are different, and the heat exchange capacity of the second heat source side heat exchanger 25 is larger than the first heat source side heat exchanger 24 .
- the second heat source side heat exchanger 25 has a heat exchange capacity which is 1.8 times to 4.0 times of the first heat source side heat exchanger 24 .
- the first heat source side heat exchanger 24 where the heat exchange capacity is small is arranged on the upper side of the second heat source side heat exchanger 25 where the heat exchange capacity is large.
- first heat source side heat exchanger 24 and the second heat source side heat exchanger 25 are configured as an integral heat source side heat exchanger, and the upper portion functions as the first heat source side heat exchanger 24 by the heat transfer tubes which configure the upper portion being connected with the first header 24 a and the first flow divider 24 b and the lower portion functions as the second heat source side heat exchanger 25 by the heat transfer tubes which configure the lower portion being connected with the second header 25 a and the second flow divider 25 b .
- the flow path cross sectional area of the second header 25 a is larger than the first header 24 a .
- the inner diameter size of the second header 25 a is larger than the inner diameter size of the first header 24 a .
- the heat source unit 2 has an outdoor fan 34 for suctioning outdoor air into the inside of the unit and exhausting the outdoor air to the outside of the unit after heat exchange is carried out, and heat exchange between outdoor air and refrigerant which flows through the heat source side heat exchangers 24 and 25 is possible.
- the outdoor fan 34 is driven using an outdoor fan motor 34 a .
- a suction opening 2 a for suctioning outdoor air is formed in the side surface of the heat source unit 2
- an exhaust opening 2 b for exhausting outdoor air is formed in the top surface of the heat source unit 2
- the outdoor fan 34 is arranged at an upper portion of the heat source unit 2 .
- the first heat source side flow amount adjustment valve 26 is an electric expansion valve where adjustment to its opening is possible and which is connected with the liquid side of the first heat source side heat exchanger 24 in order to perform adjustment of the flow amount of refrigerant which flows through the first heat source side heat exchanger 24 and the like.
- the second heat source side flow amount adjustment valve 27 is an electric expansion valve where adjustment to its opening is possible and which is connected with the liquid side of the second heat source side heat exchanger 25 in order to perform adjustment of the flow amount of refrigerant which flows through the second heat source side heat exchanger 25 and the like.
- the rated Cv values of the first heat source side flow amount adjustment valve 26 and the second heat source side flow amount adjustment valve 27 are different, and the rated Cv value of the second heat source side flow amount adjustment valve 27 is larger than the rated Cv value of the first heat source side flow amount adjustment valve 26 .
- the receiver 28 is a container for temporarily retaining refrigerant which flows between the heat source side heat exchangers 24 and 25 and the usage side refrigerant circuits 13 a , 13 b , 13 c , and 13 d .
- a receiver input pipe 28 a is provided at an upper portion of the receiver 28 and a receiver output pipe 28 b is provided at a lower portion of the receiver 28 .
- a receiver input opening and closing valve 28 c where opening and closing control is possible is provided in the receiver input pipe 28 a . Then, the input pipe 28 a and the output pipe 28 b in the receiver 28 connect between the heat source side heat exchangers 24 and 25 and the liquid side shutoff valve 31 via the bridge circuit 29 .
- the bridge circuit 29 is a circuit which has a function of causing refrigerant to flow into the inside of the receiver 28 via the receiver input pipe 28 a and of causing refrigerant to flow out from the inside of the receiver 28 via the receiver output pipe 28 b in either a case where refrigerant flows from the heat source side heat exchangers 24 and 25 side toward the liquid side shutoff valve 31 side or a case where refrigerant flows from the liquid side shutoff valve 31 side toward the heat source side heat exchangers 24 and 25 side.
- the bridge circuit 29 has four check valves 29 a , 29 b , 29 c , and 29 d .
- the input check valve 29 a is a check valve which only permits passage of refrigerant from the heat source side heat exchangers 24 and 25 side to the receiver input pipe 28 a .
- the input check valve 29 b is a check valve which only permits passage of refrigerant from the liquid side shutoff valve 31 side to the receiver input pipe 28 a . That is, the input check valves 29 a and 29 b have a function of causing the passage of refrigerant from the heat source side heat exchangers 24 and 25 side or the liquid side shutoff valve 31 side to the receiver input pipe 28 a .
- the output check valve 29 c is a check valve which only permits passage of refrigerant from the receiver output pipe 28 b to the liquid side shutoff valve 31 side.
- the output check valve 29 d is a check valve which only permits passage of refrigerant from the receiver output pipe 28 b to the heat source side heat exchangers 24 and 25 side. That is, the output check valves 29 c and 29 d have a function of causing the passage of refrigerant from the receiver output pipe 28 b to the heat source side heat exchangers 24 and 25 side or the liquid side shutoff valve 31 side.
- the high and low pressure switching mechanism 30 is a device where it is possible to switch the flow path of refrigerant inside the heat source side refrigerant circuit 12 so that the discharge side of the compressor 21 and the high and low pressure gas side shutoff valve 32 are connected (refer to the dashed line in the high and low pressure switching mechanism 30 in FIG.
- the liquid side shutoff valve 31 , the high and low pressure gas side shutoff valve 32 , and the low pressure gas side shutoff valve 33 are valves which are provided at connection openings with external devices and pipes (in detail, with the refrigerant communication pipes 7 , 8 , and 9 ).
- the liquid side shutoff valve 31 is connected with the receiver input pipe 28 a or the receiver output pipe 28 b via the bridge circuit 29 .
- the high and low pressure gas side shutoff valve 32 is connected with the high and low pressure switching mechanism 30 .
- the low pressure gas side shutoff valve 33 is connected with the suction side of the compressor 21 .
- the heat source unit 2 has a heat source side control section 20 which controls actions of each of the sections 21 a , 22 , 23 , 26 , 27 , 28 c , 30 , and 34 a which configure the heat source unit 2 .
- the heat source side control section 20 has a microcomputer and a memory which are provided in order to perform control of the heat source unit 2 , and it is possible to perform transfer of control signals and the like with the usage side control sections 50 a , 50 b , 50 c , and 50 d in the usage units 3 a , 3 b , 3 c , 3 d.
- the connecting units 4 a , 4 b , 4 c , and 4 d are arranged indoors along with the usage units 3 a , 3 b , 3 c , and 3 d such as in a building.
- the connecting units 4 a , 4 b , 4 c , and 4 d are in between the usage units 3 a , 3 b , 3 c , and 3 d and the heat source unit 2 along with the refrigerant communication pipes 7 , 8 , and 9 and configures a portion of the refrigerant circuit 10 .
- the connecting unit 4 a and the connecting units 4 b , 4 c , and 4 d have the same configuration, only the configuration of the connecting unit 4 a will be described here and the subscripts “b”, “c”, and “d” are respectively added instead of the subscript “a” in the reference numerals, which indicate each section of the connecting unit 4 a , to the configurations of the connecting units 4 b , 4 c , and 4 d and the description of each section is omitted.
- the connecting unit 4 a mainly configures a portion of the refrigerant circuit 10 and has a connecting side refrigerant circuit 14 a (there are connecting side refrigerant circuits 14 b , 14 c , and 14 d respectively in each of the connecting units 4 b , 4 c , and 4 d ).
- the connecting side refrigerant circuit 14 a mainly has a liquid connecting pipe 61 a and a gas connecting pipe 62 a.
- the liquid connecting pipe 61 a connects the liquid refrigerant communication pipe 7 and the usage side flow amount adjustment valve 51 a in the usage side refrigerant circuit 13 a.
- the gas connecting pipe 62 a has a high pressure gas connecting pipe 63 a which is connected with the high and low pressure gas refrigerant communication pipe 8 , a low pressure gas connecting pipe 64 a which is connected with the low pressure gas refrigerant communication pipe 9 , and a merging gas connecting pipe 65 a where the high pressure gas connecting pipe 63 a and the low pressure gas connecting pipe 64 a merge.
- the merging gas connecting pipe 65 a is connected with the gas side of the usage side heat exchanger 52 a in the usage side refrigerant circuit 13 a .
- a high pressure gas opening and closing valve 66 a where opening and closing control is possible is provided in the high pressure gas connecting pipe 63 a
- a low pressure gas opening and closing valve 67 a where opening and closing control is possible is provided in the low pressure gas connecting pipe 64 a.
- the connecting unit 4 a to function so as to send refrigerant, which flows into the liquid connecting pipe 61 a via the liquid refrigerant communication pipe 7 , to the usage side heat exchanger 52 a via the usage side flow amount adjustment valve 51 a in the usage side refrigerant circuit 13 a and to return refrigerant, which evaporates due to heat exchange with indoor air in the usage side heat exchanger 52 a , to the low pressure gas refrigerant communication pipe 9 via the merging gas connecting pipe 65 a and the low pressure gas connecting pipe 64 a .
- the connecting unit 4 a to function so as to send refrigerant, which flows into the high pressure gas connecting pipe 63 a and the merging gas connecting pipe 65 a via the high and low pressure gas refrigerant communication pipe 8 , to the usage side heat exchanger 52 a in the usage side refrigerant circuit 13 a and to return refrigerant, which releases heat due to heat exchange with indoor air in the usage side heat exchanger 52 a , to the liquid refrigerant communication pipe 7 via the usage side flow amount adjustment valve 51 a and the liquid connecting pipe 61 a .
- the connecting unit 4 a Since not only the connecting unit 4 a but the connecting units 4 b , 4 c , and 4 d also have the same functions, switching is possible so that the usage side heat exchangers 52 a , 52 b , 52 c , and 52 d individually function as an evaporator or a radiator for refrigerant due to the connecting units 4 a , 4 b , 4 c , and 4 d.
- the connecting unit 4 a has a connecting side control section 60 a which controls the actions of each of the sections 66 a and 67 a which configure the connecting unit 4 a .
- the connecting side control section 60 a has a microcomputer and a memory which are provided in order to perform control of the connecting unit 4 a , and it is possible to perform transfer of control signals and the like with the usage side control section 50 a in the usage unit 3 a.
- the refrigerant circuit 10 in the simultaneous air cooling and air heating operation air conditioner device 1 is configured by connecting the usage side refrigerant circuits 13 a , 13 b , 13 c , and 13 d , the heat source side refrigerant circuit 12 , the refrigerant communication pipes 7 , 8 , and 9 , and the connecting side refrigerant circuits 14 a , 14 b , 14 c , and 14 d . Then, in the simultaneous air cooling and air heating operation air conditioner device 1 , it is possible to perform a simultaneous air cooling and air heating operation where, for example, the usage units 3 a and 3 b perform an air cooling operation and the usage units 3 c and 3 d perform an air heating operation.
- heat recovery is performed between the usage units 3 a , 3 b , 3 c , and 3 d by sending refrigerant from the usage side heat exchangers 52 a and 52 b which function as radiators for refrigerant to the usage side heat exchangers 52 c and 52 d which function as evaporators for refrigerant.
- the simultaneous air cooling and air heating operation air conditioner device 1 is configured as a heat recovery refrigeration device which includes the compressor 21 , the plurality (here, two) of heat source side heat exchangers 24 and 25 which are able to switch between individually functioning as an evaporator or a radiator for refrigerant, and the plurality (here, four) of usage side heat exchangers 52 a , 52 b , 52 c , and 52 d which are able to switch between individually functioning as an evaporator or a radiator for refrigerant and which is able to perform heat recovery between the usage side heat exchangers by sending refrigerant from the usage side heat exchanger which functions as a radiator for refrigerant to the usage side heat exchanger which functions as an evaporator for refrigerant.
- the heat exchange capacity of the second heat source side heat exchanger 25 is equal to or more than 1.8 times of the first heat source side heat exchanger 24 as described above.
- the simultaneous air cooling and air heating operation air conditioner device 1 It is possible to divide the operation modes of the simultaneous air cooling and air heating operation air conditioner device 1 into an air cooling operation mode (where the evaporator load is large), an air cooling operation mode (where the evaporator load is small), an air heating operation mode (where the radiator load is large), an air heating operation mode (where the radiator load is small), a simultaneous air cooling and air heating operation mode (where the evaporator load is dominant), a simultaneous air cooling and air heating operation mode (where the radiator load is dominant), and a simultaneous air cooling and air heating operation mode (with a balance between the evaporator and radiator loads).
- an air cooling operation mode where the evaporator load is large
- an air cooling operation mode where the evaporator load is small
- an air heating operation mode where the radiator load is large
- an air heating operation mode where the radiator load is small
- a simultaneous air cooling and air heating operation mode where the evaporator load is dominant
- a simultaneous air cooling and air heating operation mode where the radiator load is dominant
- the air cooling operation mode (where the evaporator load is large) is an operation mode which is only for the usage units which perform an air cooling operation (that is, an operation where the usage side heat exchanger functions as an evaporator for refrigerant) and which is where both of the heat source side heat exchangers 24 and 25 function as radiators for refrigerant with regard to the evaporator load over all of the usage units.
- the air cooling operation mode (where the evaporator load is small) is an operation mode which is only for the usage units which perform an air cooling operation (that is, an operation where the usage side heat exchanger functions as an evaporator for refrigerant) and which is where only the first heat source side heat exchanger 24 functions as a radiator for refrigerant with regard to the evaporator load over all of the usage units.
- the heat cooling operation mode (where the radiator load is large) is an operation mode which is only for the usage units which perform an air heating operation (that is, an operation where the usage side heat exchanger functions as a radiator for refrigerant) and which is where both of the heat source side heat exchangers 24 and 25 function as evaporators for refrigerant with regard to the radiator load over all of the usage units.
- the air heating operation mode (where the radiator load is small) is an operation mode which is only for the usage units which perform an air heating operation (that is, an operation where the usage side heat exchanger functions as a radiator for refrigerant) and which is where only the first heat source side heat exchanger 24 functions as an evaporator for refrigerant with regard to the radiator load over all of the usage units.
- the simultaneous air cooling and air heating operation mode (where the evaporator load is dominant) is an operation mode where there is a mixture of the usage units which perform an air cooling operation (that is, an operation where the usage side heat exchanger functions as an evaporator for refrigerant) and the usage units which perform an air heating operation (that is, an operation where the usage side heat exchanger functions as a radiator for refrigerant) and where only the first heat source side heat exchanger 24 functions as a radiator for refrigerant with regard to the evaporator load over all of the usage units in a case where the heat load over all of the usage units is dominated by the evaporator load.
- the simultaneous air cooling and air heating operation mode (where the radiator load is dominant) is an operation mode where there is a mixture of the usage units which perform an air cooling operation (that is, an operation where the usage side heat exchanger functions as an evaporator for refrigerant) and the usage units which perform an air heating operation (that is, an operation where the usage side heat exchanger functions as a radiator for refrigerant) and where only the first heat source side heat exchanger 24 functions as an evaporator for refrigerant with regard to the radiator load over all of the usage units in a case where the heat load over all of the usage units is dominated by the radiator load.
- the simultaneous air cooling and air heating operation mode (with a balance between the evaporator and radiator loads) is an operation mode where there is a mixture of the usage units which perform an air cooling operation (that is, an operation where the usage side heat exchanger functions as an evaporator for refrigerant) and the usage units which perform an air heating operation (that is, an operation where the usage side heat exchanger functions as a radiator for refrigerant) and where the first heat source side heat exchanger 24 functions as a radiator for refrigerant and the second heat source side heat exchanger 25 functions as an evaporator for refrigerant in a case where the evaporator load and the radiator load is balanced over all of the usage units.
- actions of the simultaneous air cooling and air heating operation air conditioner device 1 which include these operation modes are performed using the control sections 20 , 50 a , 50 b , 50 c , 50 d , 60 a , 60 b , 60 c , and 60 d described above.
- the refrigerant circuit 10 in the air conditioner device 1 is configured as shown in FIG. 4 (for the flow of refrigerant, refer to the arrows which are added to the refrigerant circuit 10 in FIG. 4 ) during the air cooling operation mode (where the evaporator load is large) when, for example, all of the usage units 3 a , 3 b , 3 c , and 3 d perform an air cooling operation (that is, an operation where all of the usage side heat exchangers 52 a , 52 b , 52 c , and 52 d function as evaporators for refrigerant) and both of the heat source side heat exchangers 24 and 25 function as radiators for refrigerant.
- an air cooling operation that is, an operation where all of the usage side heat exchangers 52 a , 52 b , 52 c , and 52 d function as evaporators for refrigerant
- both of the heat source side heat exchangers 24 and 25 function as radiators for refrigerant.
- both of the heat source side heat exchangers 24 and 25 function as radiators for refrigerant by the first heat exchange switching mechanism 22 switching to a radiator operation state (a state which is indicated by the solid line in the first heat exchange switching mechanism 22 in FIG. 4 ) and the second heat exchange switching mechanism 23 switching to a radiator operation state (a state which is indicated by the solid line in the second heat exchange switching mechanism 23 in FIG. 4 ).
- the high and low pressure switching mechanism 30 switches to an evaporator load dominant operation state (a state which is indicated by the solid line in the high and low pressure switching mechanism 30 in FIG. 4 ).
- the heat source side flow amount adjustment valves 26 and 27 adjust their openings and the receiver input opening and closing valve 28 c is in an open state.
- All of the usage side heat exchangers 52 a , 52 b , 52 c , and 52 d in the usage units 3 a , 3 b , 3 c , and 3 d function as evaporators for refrigerant due to the high pressure gas opening and closing valves 66 a , 66 b , 66 c , and 66 d and the low pressure gas opening and closing valves 67 a , 67 b , 67 c , and 67 d being in an open state in the connecting units 4 a , 4 b , 4 c , and 4 d , and there is a state where all of the usage side heat exchangers 52 a , 52 b , 52 c , and 52 d in the usage units 3 a , 3 b , 3 c , and 3 d and the
- high pressure gas refrigerant which is compressed by and discharged from the compressor 21 is sent to both of the heat source side heat exchangers 24 and 25 via the heat exchange switching mechanisms 22 and 23 . Then, the high pressure gas refrigerant which is sent to the heat source side heat exchangers 24 and 25 releases heat by heat exchange being performed with outdoor air which is the heat source which is supplied using the outdoor fan 34 in the heat source side heat exchangers 24 and 25 .
- the refrigerant which releases heat in the heat source side heat exchangers 24 and 25 is sent to the receiver 28 via the input check valve 29 a and the receiver input opening and closing valve 28 c by merging after the flow amount is adjusted in the heat source side flow amount adjustment valves 26 and 27 .
- the refrigerant which is sent to the receiver 28 is sent to the liquid refrigerant communication pipe 7 via the output check valve 29 c and the liquid side shutoff valve 31 after being temporarily retained inside the receiver 28 .
- the refrigerant which is sent to the liquid refrigerant communication pipe 7 is branched off four ways and is sent to the liquid connecting pipes 61 a , 61 b , 61 c , and 61 d in each of the connecting units 4 a , 4 b , 4 c , and 4 d .
- the refrigerant which is sent to the liquid connecting pipes 61 a , 61 b , 61 c , and 61 d is sent to the usage side flow amount adjustment valves 51 a , 51 b , 51 c , and 51 d in the usage units 3 a , 3 b , 3 c , and 3 d.
- the refrigerant which is sent to the usage side flow amount adjustment valves 51 a , 51 b , 51 c , and 51 d becomes low pressure gas refrigerant by evaporating due to heat exchange being performed with indoor air which is supplied using the indoor fans 53 a , 53 b , 53 c , and 53 d in the usage side heat exchangers 52 a , 52 b , 52 c , and 52 d after the flow amount is adjusted in the usage side flow amount adjustment valves 51 a , 51 b , 51 c , and 51 d .
- an air cooling operation is performed using the usage units 3 a , 3 b , 3 c , and 3 d by the indoor air being cooled and supplied indoors.
- the low pressure gas refrigerant is sent to the merging gas connecting pipes 65 a , 65 b , 65 c , and 65 d in the connecting units 4 a , 4 b , 4 c , and 4 d.
- the low pressure gas refrigerant which is sent to the merging gas connecting pipes 65 a , 65 b , 65 c , and 65 d merges due to being sent to the high and low pressure gas refrigerant communication pipe 8 via the high pressure gas opening and closing valves 66 a , 66 b , 66 c , and 66 d and the high pressure gas connecting pipes 63 a , 63 b , 63 c , and 63 d and merges due to being sent to the low pressure gas refrigerant communication pipe 9 via the low pressure gas opening and closing valves 67 a , 67 b , 67 c , and 67 d and the low pressure gas connecting pipes 64 a , 64 b , 64 c , and 64 d.
- the low pressure gas refrigerant which is sent to the gas refrigerant communication pipes 8 and 9 is returned to the suction side of the compressor 21 via the gas side shutoff valves 32 and 33 and the high and low pressure switching mechanism 30 .
- the refrigerant circuit 10 in the air conditioner device 1 is configured as shown in FIG. 5 (for the flow of refrigerant, refer to the arrows which are added to the refrigerant circuit 10 in FIG. 5 ) during the air cooling operation mode (where the evaporator load is small) when, for example, only the usage unit 3 a performs an air cooling operation (that is, an operation where only the usage side heat exchanger 52 a functions as an evaporator for refrigerant) and only the first heat source side heat exchanger 24 functions as a radiator for refrigerant.
- the first heat source side heat exchanger 24 functions as a radiator for refrigerant by the first heat exchange switching mechanism 22 switching to a radiator operation state (a state which is indicated by the solid line in the first heat exchange switching mechanism 22 in FIG. 5 ).
- the high and low pressure switching mechanism 30 switches to an evaporator load dominant operation state (a state which is indicated by the solid line in the high and low pressure switching mechanism 30 in FIG. 5 ).
- the first heat source side flow amount adjustment valve 26 adjusts its opening
- the second heat source side flow amount adjustment valve 27 is in a closed state
- the receiver input opening and closing valve 28 c is in an open state.
- Only the usage side heat exchanger 52 a in the usage unit 3 a functions as an evaporator for refrigerant due to the high pressure gas opening and closing valve 66 a and the low pressure gas opening and closing valve 67 a being in an open state and the high pressure gas opening and closing valves 66 b , 66 c , and 66 d and the low pressure gas opening and closing valves 67 b , 67 c , and 67 d being in a closed state in the connecting units 4 a , 4 b , 4 c , and 4 d , and there is a state where the usage side heat exchanger 52 a in the usage unit 3 a and the suction side of the compressor 21 in the heat source unit 2 are connected via the high and low pressure gas refrigerant communication pipe 8 and the low pressure gas refrigerant communication pipe 9 .
- the usage side flow amount adjustment valve 51 a adjusts its opening in the usage unit 3 a and the usage side flow amount adjustment valves 51 b , 51 c , and 51 d are in a closed state in the usage units 3 b , 3 c , and 3 d.
- high pressure gas refrigerant which is compressed by and discharged from the compressor 21 is sent to only the first heat source side heat exchanger 24 via the first heat exchange switching mechanism 22 .
- the high pressure gas refrigerant which is sent to the first heat source side heat exchanger 24 releases heat by heat exchange being performed with outdoor air which is the heat source which is supplied using the outdoor fan 34 in the first heat source side heat exchanger 24 .
- the refrigerant which releases heat in the first heat source side heat exchanger 24 is sent to the receiver 28 via the input check valve 29 a and the receiver input opening and closing valve 28 c after the flow amount is adjusted in the first heat source side flow amount adjustment valve 26 .
- the refrigerant which is sent to the receiver 28 is sent to the liquid refrigerant communication pipe 7 via the output check valve 29 c and the liquid side shutoff valve 31 after being temporarily retained inside the receiver 28 .
- the refrigerant which is sent to the liquid refrigerant communication pipe 7 is sent to only the liquid connecting pipe 61 a in the connecting unit 4 a . Then, the refrigerant which is sent to the liquid connecting pipe 61 a in the connecting unit 4 a is sent to the usage side flow amount adjustment valve 51 a in the usage unit 3 a.
- the refrigerant which is sent to the usage side flow amount adjustment valve 51 a becomes low pressure gas refrigerant by evaporating due to heat exchange being performed with indoor air which is supplied using the indoor fan 53 a in the usage side heat exchanger 52 a after the flow amount is adjusted in the usage side flow amount adjustment valve 51 a .
- an air cooling operation is performed using only the usage unit 3 a by the indoor air being cooled and supplied indoors.
- the low pressure gas refrigerant is sent to the merging gas connecting pipe 65 a in the connecting unit 4 a.
- the low pressure gas refrigerant which is sent to the merging gas connecting pipe 65 a is sent to the high and low pressure gas refrigerant communication pipe 8 via the high pressure gas opening and closing valve 66 a and the high pressure gas connecting pipe 63 a and is sent to the low pressure gas refrigerant communication pipe 9 via the low pressure gas opening and closing valve 67 a and the low pressure gas connecting pipe 64 a.
- the low pressure gas refrigerant which is sent to the gas refrigerant communication pipes 8 and 9 is returned to the suction side of the compressor 21 via the gas side shutoff valves 32 and 33 and the high and low pressure switching mechanism 30 .
- the refrigerant circuit 10 in the air conditioner device 1 is configured as shown in FIG. 6 (for the flow of refrigerant, refer to the arrows which are added to the refrigerant circuit 10 in FIG. 6 ) during the air heating operation mode (where the radiator load is large) when, for example, all of the usage units 3 a , 3 b , 3 c , and 3 d perform an air heating operation (that is, an operation where all of the usage side heat exchangers 52 a , 52 b , 52 c , and 52 d function as radiators for refrigerant) and both of the heat source side heat exchangers 24 and 25 function as evaporators for refrigerant.
- an air heating operation that is, an operation where all of the usage side heat exchangers 52 a , 52 b , 52 c , and 52 d function as radiators for refrigerant
- both of the heat source side heat exchangers 24 and 25 function as evaporators for refrigerant.
- both of the heat source side heat exchangers 24 and 25 function as evaporators for refrigerant by the first heat exchange switching mechanism 22 switching to an evaporator operation state (a state which is indicated by the dashed line in the first heat exchange switching mechanism 22 in FIG. 6 ) and the second heat exchange switching mechanism 23 switching to an evaporator operation state (a state which is indicated by the dashed line in the second heat exchange switching mechanism 23 in FIG. 6 ).
- the high and low pressure switching mechanism 30 switches to a radiator load dominant operation state (a state which is indicated by the dashed line in the high and low pressure switching mechanism 30 in FIG. 6 ).
- the heat source side flow amount adjustment valves 26 and 27 adjust their openings and the receiver input opening and closing valve 28 c is in an open state.
- All of the usage side heat exchangers 52 a , 52 b , 52 c , and 52 d in the usage units 3 a , 3 b , 3 c , and 3 d function as radiators for refrigerant due to the high pressure gas opening and closing valves 66 a , 66 b , 66 c , and 66 d being in an open state and the low pressure gas opening and closing valves 67 a , 67 b , 67 c , and 67 d being in a closed state in the connecting units 4 a , 4 b , 4 c , and 4 d , and there is a state where all of the usage side heat exchangers 52 a , 52 b , 52 c , and 52 d in the usage units 3 a , 3 b , 3 c , and 3
- high pressure gas refrigerant which is compressed by and discharged from the compressor 21 is sent to the high and low pressure gas refrigerant communication pipe 8 via the high and low pressure switching mechanism 30 and the high and low pressure gas side shutoff valve 32 .
- the high pressure gas refrigerant which is sent to the high and low pressure gas refrigerant communication pipe 8 is branched off four ways and is sent to the high pressure gas connecting pipes 63 a , 63 b , 63 c , and 63 d in each of the connecting units 4 a , 4 b , 4 c , and 4 d .
- the high pressure gas refrigerant which is sent to the high pressure gas connecting pipes 63 a , 63 b , 63 c , and 63 d is sent to the usage side heat exchangers 52 a , 52 b , 52 c , and 52 d in the usage units 3 a , 3 b , 3 c , and 3 d via the high pressure gas opening and closing valves 66 a , 66 b , 66 c , and 66 d and the merging gas connecting pipes 65 a , 65 b , 65 c , and 65 d.
- the high pressure gas refrigerant which is sent to the usage side heat exchangers 52 a , 52 b , 52 c , and 52 d releases heat by heat exchange being performed with indoor air which is supplied using the indoor fans 53 a , 53 b , 53 c , and 54 d in the usage side heat exchangers 52 a , 52 b , 52 c , and 52 d .
- an air heating operation is performed using the usage units 3 a , 3 b , 3 c , and 3 d by the indoor air being heated and supplied indoors.
- the refrigerant which releases heat in the usage side heat exchangers 52 a , 52 b , 52 c , and 52 d is sent to the liquid connecting pipes 61 a , 61 b , 61 c , and 61 d in the connecting units 4 a , 4 b , 4 c , and 4 d after the flow amount is adjusted in the usage side flow amount adjustment valves 51 a , 51 b , 51 c , and 51 d.
- the refrigerant which is sent to the liquid connecting pipes 61 a , 61 b , 61 c , and 61 d merges by being sent to the liquid refrigerant communication pipe 7 .
- the refrigerant which is sent to the liquid refrigerant communication pipe 7 is sent to the receiver 28 via the liquid side shutoff valve 31 , the input check valve 29 b , and the receiver input opening and closing valve 28 c .
- the refrigerant which is sent to the receiver 28 is sent to both of the heat source side flow amount adjustment valves 26 and 27 via the output check valve 29 d after being temporarily retained inside the receiver 28 .
- the refrigerant which is sent to the heat source side flow amount adjustment valves 26 and 27 becomes low pressure gas refrigerant by evaporating due to heat exchange being performed with outdoor air which is supplied using the outdoor fan 34 in the heat source side heat exchangers 24 and 25 after the flow amount is adjusted in the heat source side flow amount adjustment valves 26 and 27 and the low pressure gas refrigerant is sent to the heat exchange switching mechanisms 22 and 23 .
- the low pressure gas refrigerant which is sent to the heat exchange switching mechanisms 22 and 23 merges and is returned to the suction side of the compressor 21 .
- the refrigerant circuit 10 in the air conditioner device 1 is configured as shown in FIG. 7 (for the flow of refrigerant, refer to the arrows which are added to the refrigerant circuit 10 in FIG. 7 ) during the air heating operation mode (where the radiator load is small) when, for example, only the usage unit 3 a performs an air heating operation (that is, an operation where only the usage side heat exchanger 52 a functions as a radiator for refrigerant) and only the first heat source side heat exchanger 24 functions as an evaporator for refrigerant.
- the first heat source side heat exchanger 24 functions as an evaporator for refrigerant by the first heat exchange switching mechanism 22 switching to an evaporator operation state (a state which is indicated by the dashed line in the first heat exchange switching mechanism 22 in FIG. 7 ).
- the high and low pressure switching mechanism 30 switches to a radiator load dominant operation state (a state which is indicated by the dashed line in the high and low pressure switching mechanism 30 in FIG. 7 ).
- the first heat source side flow amount adjustment valve 26 adjusts its opening
- the second heat source side flow amount adjustment valve 27 is in a closed state
- the receiver input opening and closing valve 28 c is in an open state.
- Only the usage side heat exchanger 52 a in the usage unit 3 a functions as a radiator for refrigerant due to the high pressure gas opening and closing valve 66 a being in an open state and the high pressure gas opening and closing valves 66 b , 66 c , and 66 d and the low pressure gas opening and closing valves 67 a , 67 b , 67 c , and 67 d being in a closed state in the connecting units 4 a , 4 b , 4 c , and 4 d , and there is a state where the usage side heat exchanger 52 a in the usage unit 3 a and the discharge side of the compressor 21 in the heat source unit 2 are connected via the high and low pressure gas refrigerant communication pipe 8 .
- the usage side flow amount adjustment valve 51 a adjusts its opening in the usage unit 3 a and the usage side flow amount adjustment valves 51 b , 51 c , and 51 d are in a closed state in the usage units 3 b , 3 c , and 3 d.
- high pressure gas refrigerant which is compressed by and discharged from the compressor 21 is sent to the high and low pressure gas refrigerant communication pipe 8 via the high and low pressure switching mechanism 30 and the high and low pressure gas side shutoff valve 32 .
- the high pressure gas refrigerant which is sent to the high and low pressure gas refrigerant communication pipe 8 is sent to only the high pressure gas connecting pipe 63 a in the connecting unit 4 a .
- the high pressure gas refrigerant which is sent to the high pressure gas connecting pipe 63 a is sent to the usage side heat exchanger 52 a in the usage unit 3 a via the high pressure gas opening and closing valve 66 a and the merging gas connecting pipe 65 a.
- the high pressure gas refrigerant which is sent to the usage side heat exchanger 52 a releases heat by heat exchange being performed with indoor air which is supplied using the indoor fan 53 a in the usage side heat exchanger 52 a .
- an air heating operation is performed using only the usage unit 3 a by the indoor air being heated and supplied indoors.
- the refrigerant which releases heat in the usage side heat exchanger 52 a is sent to the liquid connecting pipe 61 a in the connecting units 4 a after the flow amount is adjusted in the usage side flow amount adjustment valve 51 a.
- the refrigerant which is sent to the liquid connecting pipe 61 a is sent to the liquid refrigerant communication pipe 7 .
- the refrigerant which is sent to the liquid refrigerant communication pipe 7 is sent to the receiver 28 via the liquid side shutoff valve 31 , the input check valve 29 b , and the receiver input opening and closing valve 28 c .
- the refrigerant which is sent to the receiver 28 is sent to only the first heat source side flow amount adjustment valve 26 via the output check valve 29 d after being temporarily retained inside the receiver 28 .
- the refrigerant which is sent to the first heat source side flow amount adjustment valve 26 becomes low pressure gas refrigerant by evaporating due to heat exchange being performed with outdoor air which is supplied using the outdoor fan 34 in the first heat source side heat exchanger 24 after the flow amount is adjusted in the first heat source side flow amount adjustment valve 26 and the low pressure gas refrigerant is sent to the first heat exchange switching mechanism 22 . Then, the low pressure gas refrigerant which is sent to the first heat exchange switching mechanism 22 is returned to the suction side of the compressor 21 .
- the refrigerant circuit 10 in the air conditioner device 1 is configured as shown in FIG. 8 (for the flow of refrigerant, refer to the arrows which are added to the refrigerant circuit 10 in FIG. 8 ) during the simultaneous air cooling and air heating operation mode (where the evaporator load is dominant) when, for example, the usage units 3 a , 3 b , and 3 c perform an air cooling operation and the usage unit 3 d performs an air heating operation (that is, an operation where the usage side heat exchangers 52 a , 52 b , and 52 c function as evaporators for refrigerant and the usage side heat exchanger 52 d functions as a radiator for refrigerant) and only the first heat source side heat exchanger 24 functions as a radiator for refrigerant.
- the first heat source side heat exchanger 24 functions as a radiator for refrigerant by the first heat exchange switching mechanism 22 switching to a radiator operation state (a state which is indicated by the solid line in the first heat exchange switching mechanism 22 in FIG. 8 ).
- the high and low pressure switching mechanism 30 switches to a radiator load dominant operation state (a state which is indicated by the dashed line in the high and low pressure switching mechanism 30 in FIG. 8 ).
- the first heat source side flow amount adjustment valve 26 adjusts its opening
- the second heat source side flow amount adjustment valve 27 is in a closed state
- the receiver input opening and closing valve 28 c is in an open state.
- the usage side heat exchangers 52 a , 52 b , and 52 c in the usage units 3 a , 3 b , and 3 c function as evaporators for refrigerant and the usage side heat exchanger 52 d in the usage unit 3 d functions as a radiator for refrigerant due to the high pressure gas opening and closing valve 66 d and the low pressure gas opening and closing valves 67 a , 67 b , and 67 c being in an open state and the high pressure gas opening and closing valves 66 a , 66 b , and 66 c and the low pressure gas opening and closing valve 67 d being in an closed state in the connecting units 4 a , 4 b , 4 c , and 4 d , and there is a state where the usage side heat exchangers 52 a , 52 b , and 52 c in the usage units 3 a , 3 b , and 3 c and the suction side of the compressor 21 in the heat source unit 2
- the refrigerant circuit 10 a portion of the high pressure gas refrigerant which is compressed by and discharged from the compressor 21 is sent to the high and low pressure gas refrigerant communication pipe 8 via the high and low pressure switching mechanism 30 and the high and low pressure gas side shutoff valve 32 and the remaining portion of the high pressure gas refrigerant which is compressed by and discharged from the compressor 21 is sent to the first heat source side heat exchanger 24 via the first heat exchange switching mechanism 22 .
- the high pressure gas refrigerant which is sent to the high and low pressure gas refrigerant communication pipe 8 is sent to the high pressure gas connecting pipe 63 d in the connecting unit 4 d .
- the high pressure gas refrigerant which is sent to the high pressure gas connecting pipe 63 d is sent to the usage side heat exchanger 52 d in the usage unit 3 d via the high pressure gas opening and closing valve 66 d and the merging gas connecting pipe 65 d.
- the high pressure gas refrigerant which is sent to the usage side heat exchanger 52 d releases heat by heat exchange being performed with indoor air which is supplied using the indoor fan 53 d in the usage side heat exchanger 52 d .
- an air heating operation is performed using the usage unit 3 d by the indoor air being heated and supplied indoors.
- the refrigerant which releases heat in the usage side heat exchanger 52 d is sent to the liquid connecting pipe 61 d in the connecting unit 4 d after the flow amount is adjusted in the usage side flow amount adjustment valve 51 d.
- the high pressure gas refrigerant which is sent to the first heat source side heat exchanger 24 releases heat by heat exchange being performed with outdoor air which is the heat source which is supplied using the outdoor fan 34 in the first heat source side heat exchanger 24 .
- the refrigerant which releases heat in the first heat source side heat exchanger 24 is sent to the receiver 28 via the input check valve 29 a and the receiver input opening and closing valve 28 c after the flow amount is adjusted in the first heat source side flow amount adjustment valve 26 .
- the refrigerant which is sent to the receiver 28 is sent to the liquid refrigerant communication pipe 7 via the output check valve 29 c and the liquid side shutoff valve 31 after being temporarily retained inside the receiver 28 .
- the refrigerant which is sent to the liquid connecting pipe 61 d with heat being released in the usage side heat exchanger 52 d is sent to the liquid refrigerant communication pipe 7 and merges with refrigerant which is sent to the liquid refrigerant communication pipe 7 with heat being released in the first heat source side heat exchanger 24 .
- the refrigerant which merges in the liquid refrigerant communication pipe 7 is branched off three ways and is sent to the liquid connecting pipes 61 a , 61 b , and 61 c in each of the connecting units 4 a , 4 b , and 4 c .
- the refrigerant which is sent to the liquid connecting pipes 61 a , 61 b , and 61 c is sent to the usage side flow amount adjustment valves 51 a , 51 b , and 51 c in the usage units 3 a , 3 b , and 3 c.
- the refrigerant which is sent to the usage side flow amount adjustment valves 51 a , 51 b , and 51 c becomes low pressure gas refrigerant by evaporating due to heat exchange being performed with indoor air which is supplied using the indoor fans 53 a , 53 b , and 53 c in the usage side heat exchangers 52 a , 52 b , and 52 c after the flow amount is adjusted in the usage side flow amount adjustment valves 51 a , 51 b , and 51 c .
- an air cooling operation is performed using the usage units 3 a , 3 b , and 3 c by the indoor air being cooled and supplied indoors.
- the low pressure gas refrigerant is sent to the merging gas connecting pipes 65 a , 65 b , and 65 c in the connecting units 4 a , 4 b , and 4 c.
- the low pressure gas refrigerant which is sent to the merging gas connecting pipes 65 a , 65 b , and 65 c merges due to being sent to the low pressure gas refrigerant communication pipe 9 via the low pressure gas opening and closing valves 67 a , 67 b , and 67 c and the low pressure gas connecting pipes 64 a , 64 b , and 64 c.
- the low pressure gas refrigerant which is sent to the low pressure gas refrigerant communication pipe 9 is returned to the suction side of the compressor 21 via the gas side shutoff valve 33 .
- the refrigerant circuit 10 in the air conditioner device 1 is configured as shown in FIG. 9 (for the flow of refrigerant, refer to the arrows which are added to the refrigerant circuit 10 in FIG. 9 ) during the simultaneous air cooling and air heating operation mode (where the radiator load is dominant) when, for example, the usage units 3 a , 3 b , and 3 c perform an air heating operation and the usage unit 3 d performs an air cooling operation (that is, an operation where the usage side heat exchangers 52 a , 52 b , and 52 c function as radiators for refrigerant and the usage side heat exchanger 52 d functions as an evaporator for refrigerant) and only the first heat source side heat exchanger 24 functions as an evaporator for refrigerant.
- the first heat source side heat exchanger 24 functions as an evaporator for refrigerant by the first heat exchange switching mechanism 22 switching to an evaporator operation state (a state which is indicated by the dashed line in the first heat exchange switching mechanism 22 in FIG. 9 ).
- the high and low pressure switching mechanism 30 switches to a radiator load dominant operation state (a state which is indicated by the dashed line in the high and low pressure switching mechanism 30 in FIG. 9 ).
- the first heat source side flow amount adjustment valve 26 adjusts its openings
- the second heat source side flow amount adjustment valve 27 is in a closed state
- the receiver input opening and closing valve 28 c is in an open state.
- the usage side heat exchangers 52 a , 52 b , and 52 c in the usage units 3 a , 3 b , and 3 c function as radiators for refrigerant and the usage side heat exchanger 52 d in the usage unit 3 d functions as an evaporator for refrigerant due to the high pressure gas opening and closing valves 66 a , 66 b , and 66 c and the low pressure gas opening and closing valve 67 d being in an open state and the high pressure gas opening and closing valve 66 d and the low pressure gas opening and closing valves 67 a , 67 b , and 67 c being in a closed state in the connecting units 4 a , 4 b , 4 c , and 4 d , and there is a state where the usage side heat exchanger 52 d in the usage unit 3 d and the suction side of the compressor 21 in the heat source unit 2 are connected via the low pressure gas refrigerant communication pipe 9 and there is a state where the
- high pressure gas refrigerant which is compressed by and discharged from the compressor 21 is sent to the high and low pressure gas refrigerant communication pipe 8 via the high and low pressure switching mechanism 30 and the high and low pressure gas side shutoff valve 32 .
- the high pressure gas refrigerant which is sent to the high and low pressure gas refrigerant communication pipe 8 is branched off three ways and is sent to the high pressure gas connecting pipes 63 a , 63 b , and 63 c in each of the connecting units 4 a , 4 b , and 4 c .
- the high pressure gas refrigerant which is sent to the high pressure gas connecting pipes 63 a , 63 b , and 63 c is sent to the usage side heat exchangers 52 a , 52 b , and 52 c in the usage units 3 a , 3 b , and 3 c via the high pressure gas opening and closing valves 66 a , 66 b , and 66 c and the merging gas connecting pipes 65 a , 65 b , and 65 c.
- the high pressure gas refrigerant which is sent to the usage side heat exchangers 52 a , 52 b , and 52 c releases heat by heat exchange being performed with indoor air which is supplied using the indoor fans 53 a , 53 b , and 53 c in the usage side heat exchangers 52 a , 52 b , and 52 c .
- an air heating operation is performed using the usage units 3 a , 3 b , and 3 c by the indoor air being heated and supplied indoors.
- the refrigerant which releases heat in the usage side heat exchangers 52 a , 52 b , and 52 c is sent to the liquid connecting pipes 61 a , 61 b , and 61 c in the connecting units 4 a , 4 b , and 4 c after the flow amount is adjusted in the usage side flow amount adjustment valves 51 a , 51 b , and 51 c.
- the refrigerant which is sent to the liquid connecting pipes 61 a , 61 b , and 61 c merges by being sent to the liquid refrigerant communication pipe 7 .
- a portion of the refrigerant which merges in the liquid refrigerant communication pipe 7 is sent to the liquid connecting pipe 61 d in the connecting unit 4 d and the remaining portion of the refrigerant which merges in the liquid refrigerant communication pipe 7 is sent to the receiver 28 via the liquid side shutoff valve 31 , the input check valve 29 b , and the receiver input opening and closing valve 28 c.
- the refrigerant which is sent to the liquid connecting pipe 61 d in the connecting unit 4 d is sent to the usage side flow amount adjustment valve 51 d in the usage unit 3 d.
- the refrigerant which is sent to the usage side flow amount adjustment valve 51 d becomes low pressure gas refrigerant by evaporating due to heat exchange being performed with indoor air which is supplied using the indoor fan 53 d in the usage side heat exchanger 52 d after the flow amount is adjusted in the usage side flow amount adjustment valve 51 d .
- an air cooling operation is performed using the usage unit 3 d by the indoor air being cooled and supplied indoors.
- the low pressure gas refrigerant is sent to the merging gas connecting pipe 65 d in the connecting unit 4 d.
- the low pressure gas refrigerant which is sent to the merging gas connecting pipe 65 d is sent to the low pressure gas refrigerant communication pipe 9 via the low pressure gas opening and closing valve 67 d and the low pressure gas connecting pipe 64 d.
- the low pressure gas refrigerant which is sent to the low pressure gas refrigerant communication pipe 9 is returned to the suction side of the compressor 21 via the gas side shutoff valve 33 .
- the refrigerant which is sent to the receiver 28 is sent to the first heat source side flow amount adjustment valve 26 via the output check valve 29 d after being temporarily retained inside the receiver 28 . Then, the refrigerant which is sent to the first heat source side flow amount adjustment valve 26 becomes low pressure gas refrigerant by evaporating due to heat exchange being performed with outdoor air which is supplied using the outdoor fan 34 in the first heat source side heat exchanger 24 after the flow amount is adjusted in the first heat source side flow amount adjustment valve 26 and the low pressure gas refrigerant is sent to the first heat exchange switching mechanism 22 .
- the low pressure gas refrigerant which is sent to the first heat exchange switching mechanism 22 is returned to the suction side of the compressor 21 by merging with the low pressure gas refrigerant which is returned to the suction side of the compressor 21 via the low pressure gas refrigerant communication pipe 9 and the gas side shutoff valve 33 .
- the refrigerant circuit 10 in the air conditioner device 1 is configured as shown in FIG. 10 (for the flow of refrigerant, refer to the arrows which are added to the refrigerant circuit 10 in FIG. 10 ) during the simultaneous air cooling and air heating operation mode (with a balance between the evaporator and radiator loads) when, for example, the usage units 3 a and 3 b perform an air cooling operation and the usage units 3 c and 3 d perform an air heating operation (that is, an operation where the usage side heat exchangers 52 a and 52 b function as evaporators for refrigerant and the usage side heat exchangers 52 c and 52 d functions as radiators for refrigerant), the first heat source side heat exchanger 24 functions as a radiator for refrigerant, and the second heat source side heat exchanger 25 functions as an evaporator for refrigerant.
- the first heat source side heat exchanger 24 functions as a radiator for refrigerant and the second heat source side heat exchanger 25 functions as an evaporator for refrigerant by the first heat exchange switching mechanism 22 switching to a radiator operation state (a state which is indicated by the solid line in the first heat exchange switching mechanism 22 in FIG. 10 ) and the second heat exchange switching mechanism 23 switching to an evaporator operation state (a state which is indicated by the dashed line in the second heat exchange switching mechanism 23 in FIG. 10 ).
- the high and low pressure switching mechanism 30 switches to a radiator load dominant operation state (a state which is indicated by the dashed line in the high and low pressure switching mechanism 30 in FIG. 10 ).
- the heat source side flow amount adjustment valves 26 and 27 adjust their openings.
- the usage side heat exchangers 52 a and 52 b in the usage units 3 a and 3 b function as evaporators for refrigerant and the usage side heat exchangers 52 c and 52 d in the usage units 3 c and 3 d function as radiators for refrigerant due to the high pressure gas opening and closing valves 66 c and 66 d and the low pressure gas opening and closing valves 67 a and 67 b being in an open state and the high pressure gas opening and closing valves 66 a and 66 b and the low pressure gas opening and closing valves 67 c and 67 d being in a closed state in the connecting units 4 a , 4 b , 4 c , and 4 d , and there is a state where the usage side heat exchangers 52 a and 52 b in the usage units 3 a and 3 b and the suction side of the compressor 21 in the heat source unit 2 are connected via the
- the refrigerant circuit 10 a portion of the high pressure gas refrigerant which is compressed by and discharged from the compressor 21 is sent to the high and low pressure gas refrigerant communication pipe 8 via the high and low pressure switching mechanism 30 and the high and low pressure gas side shutoff valve 32 and the remaining portion of the high pressure gas refrigerant which is compressed by and discharged from the compressor 21 is sent to the first heat source side heat exchanger 24 via the first heat exchange switching mechanism 22 .
- the high pressure gas refrigerant which is sent to the high and low pressure gas refrigerant communication pipe 8 is sent to the high pressure gas connecting pipe s 63 c and 63 d in the connecting units 4 c and 4 d .
- the high pressure gas refrigerant which is sent to the high pressure gas connecting pipes 63 c and 63 d is sent to the usage side heat exchangers 52 c and 52 d in the usage units 3 c and 3 d via the high pressure gas opening and closing valves 66 c and 66 d and the merging gas connecting pipes 65 c and 65 d.
- the high pressure gas refrigerant which is sent to the usage side heat exchangers 52 c and 52 d releases heat by heat exchange being performed with indoor air which is supplied using the indoor fans 53 c and 53 d in the usage side heat exchangers 52 c and 52 d .
- an air heating operation is performed using the usage units 3 c and 3 d by the indoor air being heated and supplied indoors.
- the refrigerant which releases heat in the usage side heat exchangers 52 c and 52 d is sent to the liquid connecting pipes 61 c and 61 d in the connecting units 4 c and 4 d after the flow amount is adjusted in the usage side flow amount adjustment valves 51 c and 51 d.
- the refrigerant which merges in the liquid refrigerant communication pipe 7 is branched off two ways and is sent to the liquid connecting pipes 61 a and 61 b in each of the connecting units 4 a and 4 b . Then, the refrigerant which is sent to the liquid connecting pipes 61 a and 61 b is sent to the usage side flow amount adjustment valves 51 a and 51 b in the usage units 3 a and 3 b.
- the refrigerant which is sent to the usage side flow amount adjustment valves 51 a and 51 b becomes low pressure gas refrigerant by evaporating due to heat exchange being performed with indoor air which is supplied using the indoor fans 53 a and 53 b in the usage side heat exchangers 52 a and 52 b after the flow amount is adjusted in the usage side flow amount adjustment valves 51 a and 51 b .
- an air cooling operation is performed using the usage units 3 a and 3 b by the indoor air being cooled and supplied indoors.
- the low pressure gas refrigerant is sent to the merging gas connecting pipes 65 a and 65 b in the connecting units 4 a and 4 b.
- the low pressure gas refrigerant which is sent to the merging gas connecting pipes 65 a and 65 b merges due to being sent to the low pressure gas refrigerant communication pipe 9 via the low pressure gas opening and closing valves 67 a and 67 b and the low pressure gas connecting pipes 64 a and 64 b.
- the low pressure gas refrigerant which is sent to the low pressure gas refrigerant communication pipe 9 is returned to the suction side of the compressor 21 via the gas side shutoff valve 33 .
- the high pressure gas refrigerant which is sent to the first heat source side heat exchanger 24 releases heat by heat exchange being performed with outdoor air which is the heat source which is supplied using the outdoor fan 34 in the first heat source side heat exchanger 24 . Then, most of the refrigerant which releases heat in the first heat source side heat exchanger 24 is sent to the second heat source side flow amount adjustment valve 27 after passing through the first heat source side flow amount adjustment valve 26 . For this reason, there is a state where the refrigerant which releases heat in the first heat source side heat exchanger 24 is not sent to the liquid refrigerant communication pipe 7 via the receiver 28 , the bridge circuit 29 , and the liquid side shutoff valve 31 .
- the refrigerant which is sent to the second heat source side flow amount adjustment valve 27 becomes low pressure gas refrigerant by evaporating due to heat exchange being performed with outdoor air which is supplied using the outdoor fan 34 in the second heat source side heat exchanger 25 after the flow amount is adjusted in the second heat source side flow amount adjustment valve 27 and the low pressure gas refrigerant is sent to the second heat exchange switching mechanism 23 .
- the low pressure gas refrigerant which is sent to the second heat exchange switching mechanism 23 is returned to the suction side of the compressor 21 by merging with the low pressure gas refrigerant which is returned to the suction side of the compressor 21 via the low pressure gas refrigerant communication pipe 9 and the gas side shutoff valve 33 .
- a countermeasure is performed so that the evaporator load and the radiator load of the two heat source side heat exchangers 24 and 25 cancelling each other out by the first heat source side heat exchanger 24 functioning as a radiator for refrigerant and the second heat source side heat exchanger 25 functioning as an evaporator for refrigerant as described above.
- the simultaneous air cooling and air heating operation air conditioner device 1 has the following characteristics.
- the heat exchange capacity of the second heat source side heat exchanger 25 is equal to or more than 1.8 times of the first heat source side heat exchanger 24 as described above. For this reason, it is possible to widen the range over which it is possible to reduce the heat load in a case where only the first heat source side heat exchanger 24 where the heat exchange capacity is small functions as an evaporator or a radiator for refrigerant in, for example, the air cooling operation mode (where the evaporator load is small), the simultaneous air cooling and air heating operation mode (where the evaporator load is dominant), the air heating operation mode (where the radiator load is small), and the simultaneous air cooling and air heating operation mode (where the radiator load is dominant) described above, compared to a case where the ratio of heat exchange capacities of the heat source side heat exchangers is small as in the background art.
- the heat exchange capacity of the second heat source side heat exchanger 25 is equal to or less than 4.0 times of the first heat source side heat exchanger 24 as described above.
- the two heat source side heat exchangers 24 and 25 are arranged to be above and below each other as described above. At this time, there is a tendency for it to be easy for liquid refrigerant to stagnate due to the head difference between the two heat source side heat exchangers in the heat source side heat exchanger which is arranged on the lower side compared to the heat source side heat exchanger which is arranged on the upper side. For this reason, when assuming that the first heat source side heat exchanger 24 is arranged at the lower side, there is a concern that the desired heat exchange performance will not be obtained due to a state being generated where all of the first heat source side heat exchanger 24 is filled with liquid refrigerant (set below as “liquid sink”) since the heat exchange capacity is small.
- liquid refrigerant set below as “liquid sink”
- the first heat source side heat exchanger 24 where the heat exchange capacity is small is arranged more to the upper side than the second heat source side heat exchanger 25 where the heat exchange capacity is large as described above.
- the second heat source side heat exchanger 25 where the heat exchange capacity is large is arranged on the lower side and it is possible for it to be difficult for liquid sink to be generated. Due to this, it is possible for a desired heat exchange performance to be exhibited in both of the heat exchange side heat exchangers 24 and 25 in a case where the two heat source side heat exchangers 24 and 25 are arranged to be above and below each other.
- the second heat source side flow amount adjustment valve 27 is used so that the rated Cv value is larger than the first heat source side flow amount adjustment valve 26 . Due to this, it is possible to appropriately adjust the flow amount of refrigerant which flows through each of the heat source side heat exchangers 24 and 25 according to the heat exchange capacities of each of the heat source side heat exchangers 24 and 25 .
- the second header 25 a is used so that the flow path cross sectional area is larger than the first header 24 a as described above. Due to this, it is possible to appropriately perform merging and branching of refrigerant between the plurality of heat transfer tubes which configure each of the heat source side heat exchangers 24 and 25 and the headers 24 a and 25 a according to the heat exchange capacities of each of the heat source side heat exchangers 24 and 25 .
- the example of the configuration of the simultaneous air cooling and air heating operation air conditioner device 1 is exemplified and described in the embodiment described above as the heat recovery refrigeration device where the present invention is applied but the present invention is not limited to this. That is, it is possible for the present invention to be applied as long as it is a configuration where a compressor, a plurality of heat source side heat exchangers, and a plurality of usage side heat exchangers are included and it is possible to perform heat recovery between the usage side heat exchangers by sending refrigerant from the usage side heat exchanger which functions as a radiator for refrigerant to the usage side heat exchanger which functions as an evaporator for refrigerant.
- heat recovery refrigeration devices which include a compressor, a plurality of heat source side heat exchangers, and a plurality of usage side heat exchangers, and which is able to perform heat recovery between the usage side heat exchangers by sending refrigerant from the usage side heat exchanger which functions as a radiator for refrigerant to the usage side heat exchanger which functions as an evaporator for refrigerant.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Air Conditioning Control Device (AREA)
- Other Air-Conditioning Systems (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
A heat recovery refrigeration device includes a compressor, a plurality of heat source side heat exchangers, and a plurality of usage side heat exchangers. The heat exchangers are switchable between individually functioning as an evaporator or a radiator. The heat recovery refrigeration device performs heat recovery between the usage side heat exchangers by sending the refrigerant from at least one of the usage side heat exchangers functioning as a radiator to at least one of the usage side heat exchangers functioning as an evaporator. The plurality of heat source side heat exchangers include a first heat source side heat exchanger and a second heat source side heat exchanger. The second heat source side heat exchanger has a heat exchange capacity 1.8 times to 4.0 times of the first heat source side heat exchanger.
Description
- The present invention relates to a heat recovery refrigeration device and particularly relates to a heat recovery refrigeration device which includes a compressor, a plurality of heat source side heat exchangers, and a plurality of usage side heat exchangers and which is able to perform heat recovery between the usage side heat exchangers by sending refrigerant from the usage side heat exchanger which functions as a radiator for refrigerant to the usage side heat exchanger which functions as an evaporator for refrigerant.
- There is a simultaneous air cooling and air heating operation air conditioner device in the background art which is one type of heat recovery refrigeration device with a configuration which includes a compressor, two outdoor heat exchangers which are heat source side heat exchangers, and a plurality of indoor heat exchangers which are usage side heat exchangers as shown in Patent Literature 1 (Japanese Laid-open Patent Application Publication No. H5-332637). In this heat recovery refrigeration device, switching is possible so that each of the usage side heat exchangers individually functions as an evaporator or a radiator for refrigerant and it is possible to perform heat recovery (here, perform a simultaneous air cooling and air heating operation where an air cooling operation and an air heating operation are performed simultaneously) between the usage side heat exchangers by sending refrigerant from the usage side heat exchanger which functions as a radiator for refrigerant to the usage side heat exchanger which functions as an evaporator for refrigerant. Moreover, in this heat recovery refrigeration device, switching is possible so that the two heat source side heat exchangers individually function as an evaporator or a radiator for refrigerant and it is possible to perform switching with the two heat source side heat exchangers functioning as an evaporator or a radiator for refrigerant according to the heat load (evaporator load and radiator load) over all of the plurality of the usage side heat exchangers where heat recovery described above is also taken in consideration.
- Here, in the heat recovery refrigeration device in the background art described above, since the heat load over all of the plurality of the usage side heat exchangers is reduced in a case where heat recovery is performed between the usage side heat exchangers, it is necessary for it to be possible to reduce the heat load over all of the two heat source side heat exchangers provide a countermeasure to this.
- With regard to this, two heat source side heat exchangers where the heat exchange capacities are different (here 3.5 horsepower and 5.0 horsepower) are adopted in the heat recovery refrigeration device in the background art described above. Then, both of the two heat source side heat exchangers function as evaporators or radiators for refrigerant in a case where the heat load over all of the plurality of the usage side heat exchangers is large, and only the heat source side heat exchanger where the heat exchange capacity is small functions as an evaporator or a radiator for refrigerant in a case where the heat load over all of the plurality of the usage side heat exchangers is small.
- However, in the two heat source side heat exchangers in the background art described above, there is a limit to the extent to which it is possible to reduce the heat load even if only the heat source side heat exchanger where the heat exchange capacity is small functions as an evaporator or a radiator for refrigerant since the ratio of heat exchange capacities of the two heat source side heat exchangers is small (the heat source side heat exchanger where the heat exchange capacity is large is approximately 1.4 times of the heat source side heat exchanger where the heat exchange capacity is small). For this reason, it is difficult to provide a countermeasure in the heat recovery refrigeration device in the background art described above for a case where the heat load over all of the plurality of usage side heat exchangers is small even when only the heat source side heat exchanger where the heat exchange capacity is small functions as an evaporator or a radiator for refrigerant.
- With regard to this, it is thought that a countermeasure could be provided in the heat recovery refrigeration device in the background art described above for a case where the heat load over all of the plurality of usage side heat exchangers is small by reducing the heat load over all of the two heat source side heat exchangers due to one out of the two heat source side heat exchangers functioning as an evaporator for refrigerant and the other out of the two heat source side heat exchangers functioning as a radiator for refrigerant, and the evaporator load and the radiator load of the heat exchangers cancelling each other out.
- However, since the flow amount of refrigerant which flows through the two heat source side heat exchangers is increased in the countermeasure described above where the evaporator load and the radiator load of the two heat source side heat exchangers cancel each other out, it is necessary for the operation capacity of the compressor to be increased in accompaniment with this and consequently there is a concern that the operation performance will be reduced in a case where the heat load over all of the plurality of usage side heat exchangers is small.
- The object of the present invention is a heat recovery refrigeration device which includes a compressor, a plurality of heat source side heat exchangers, and a plurality of usage side heat exchangers and which is able to perform heat recovery between the usage side heat exchangers wherein it is possible to provide a countermeasure for a case where the heat load over all of the plurality of usage side heat exchangers is small while suppressing reductions in operation performance.
- A heat recovery refrigeration device according to a first aspect includes a compressor, a plurality of heat source side heat exchangers which are able to switch between individually functioning as an evaporator or a radiator for refrigerant, and a plurality of usage side heat exchangers which are able to switch between individually functioning as an evaporator or a radiator for refrigerant, and which is able to perform heat recovery between the usage side heat exchangers by sending refrigerant from the usage side heat exchanger which functions as a radiator for refrigerant to the usage side heat exchanger which functions as an evaporator for refrigerant. Then, the plurality of heat source side heat exchangers have a first heat source side heat exchanger and a second heat source side heat exchanger which has a heat exchange capacity which is 1.8 times to 4.0 times of the first heat source side heat exchanger.
- Here, firstly, the heat exchange capacity of the second heat source side heat exchanger is equal to or more than 1.8 times of the first heat source side heat exchanger as described above. For this reason, it is possible to widen the range over which it is possible to reduce the heat load in a case where only the first heat source side heat exchanger where the heat exchange capacity is small functions as an evaporator or a radiator for refrigerant. Due to this, it is possible to provide a countermeasure for a case where the heat load over all of the plurality of usage side heat exchangers is small. Moreover, here, the heat exchange capacity of the second heat source side heat exchanger is equal to or less than 4.0 times of the first heat source side heat exchanger as described above. For this reason, it is possible for the flow amount of refrigerant which flows through the two heat source side heat exchangers as well as the operation capacity of the compressor to not become large in a case of performing the countermeasure where one out of the two heat source side heat exchangers functions as an evaporator for refrigerant and the other out of the two heat source side heat exchangers functions as a radiator for refrigerant, and the evaporator load and the radiator load of the two heat source side heat exchangers cancel each other out. Due to this, it is possible to provide a countermeasure for a case where the heat load over all of the plurality of usage side heat exchangers is small while suppressing reductions in operation performance.
- Here, in this manner, it is possible to provide a countermeasure for a case where the heat load over all of the plurality of usage side heat exchangers is small while suppressing reductions in operation performance.
- A heat recovery refrigeration device according to a second aspect is the heat recovery refrigeration device according to the first aspect wherein the first heat source side heat exchanger is arranged more to the upper side than the second heat source side heat exchanger.
- Here, firstly, the two heat source side heat exchangers are arranged to be above and below each other as described above. At this time, there is a tendency for it to be easy for liquid refrigerant to stagnate due to the head difference between the two heat source side heat exchangers in the heat source side heat exchanger which is arranged on the lower side compared to the heat source side heat exchanger which is arranged on the upper side. For this reason, when assuming that the first heat source side heat exchanger is arranged at the lower side, there is a concern that the desired heat exchange performance will not be obtained due to a state being generated where all of the first heat source side heat exchanger is filled with liquid refrigerant (set below as “liquid sink”) since the heat exchange capacity is small.
- Therefore, here, the first heat source side heat exchanger where the heat exchange capacity is small is arranged more to the upper side than the second heat source side heat exchanger where the heat exchange capacity is large as described above. For this reason, the second heat source side heat exchanger where the heat exchange capacity is large is arranged on the lower side and it is possible for it to be difficult for liquid sink to be generated. Due to this, it is possible for a desired heat exchange performance to be exhibited in both of the heat exchange side heat exchangers in a case where the two heat source side heat exchangers are arranged to be above and below each other.
- A heat recovery refrigeration device according to a third aspect is the heat recovery refrigeration device according to the first or second aspect wherein a first heat source side flow amount adjustment valve, where adjustment to its opening is possible, is connected with the liquid side of the first heat source side heat exchanger, and a second heat source side flow amount adjustment valve, where adjustment to its opening is possible, is connected with the liquid side of the second heat source side heat exchanger. Then, the rated Cv value of the second heat source side flow amount adjustment valve is larger than the Cv value of the first heat source side flow amount adjustment valve.
- Here, in regard to connecting the heat source side flow amount adjustment valves with the liquid side of each of heat source side heat exchangers, the second heat source side flow amount adjustment valve is used so that the rated Cv value is larger than the first heat source side flow amount adjustment valve. Due to this, it is possible to appropriately adjust the flow amount of refrigerant which flows through each of the heat source side heat exchangers according to the heat exchange capacities of each of the heat source side heat exchangers.
- A heat recovery refrigeration device according to a fourth aspect is the heat recovery refrigeration device according to any of the first to third aspects wherein a first header, which is for performing merging and branching of refrigerant between a plurality of heat transfer tubes which configure the first heat source side heat exchanger, is provided on the gas side of the first heat source side heat exchanger, and a second header, which is for performing merging and branching of refrigerant between a plurality of heat transfer tubes which configure the second heat source side heat exchanger, is provided on the gas side of the second heat source side heat exchanger. Then, the flow path cross sectional area of the second header is larger than the flow path cross sectional area of the first header.
- Here, in regard to providing the heads on the gas side of each of the heat source side heat exchangers, the second header is used so that the flow path cross sectional area is larger than the first header as described above. Due to this, it is possible to appropriately perform merging and branching of refrigerant between the plurality of heat transfer tubes which configure each of the heat source side heat exchangers and the headers according to the heat exchange capacities of each of the heat source side heat exchangers.
-
FIG. 1 is an outline configuration diagram of a simultaneous air cooling and air heating operation air conditioner device as an embodiment of a heat recovery refrigeration device according to the present invention. -
FIG. 2 is a diagram illustrating an internal configuration of an outline of a heat source unit which configures the simultaneous air cooling and air heating operation air conditioner device. -
FIG. 3 is a diagram schematically illustrating the configuration of heat source side heat exchangers. -
FIG. 4 is a diagram illustrating actions (flow of refrigerant) in an air cooling operation mode (where the evaporator load is large) in the simultaneous air cooling and air heating operation air conditioner device. -
FIG. 5 is a diagram illustrating actions (flow of refrigerant) in an air cooling operation mode (where the evaporator load is small) in the simultaneous air cooling and air heating operation air conditioner device. -
FIG. 6 is a diagram illustrating actions (flow of refrigerant) in an air heating operation mode (where the radiator load is large) in the simultaneous air cooling and air heating operation air conditioner device. -
FIG. 7 is a diagram illustrating actions (flow of refrigerant) in an air heating operation mode (where the radiator load is small) in the simultaneous air cooling and air heating operation air conditioner device. -
FIG. 8 is a diagram illustrating actions (flow of refrigerant) in a simultaneous air cooling and air heating operation mode (where the evaporator load is dominant) in the simultaneous air cooling and air heating operation air conditioner device. -
FIG. 9 is a diagram illustrating actions (flow of refrigerant) in a simultaneous air cooling and air heating operation mode (where the radiator load is dominant) in the simultaneous air cooling and air heating operation air conditioner device. -
FIG. 10 is a diagram illustrating actions (flow of refrigerant) in a simultaneous air cooling and air heating operation mode (with a balance between the evaporator and radiator loads) in the simultaneous air cooling and air heating operation air conditioner device. - An embodiment of a heat recovery refrigerant device according to the present invention will be described below based on the drawings. Here, the specific configuration of the heat recovery refrigeration device according to the present invention is not limited to the embodiment or the modified examples described below and modifications are possible within a scope which does not depart from the gist of the invention.
-
FIG. 1 is an outline configuration diagram of a simultaneous air cooling and air heating operationair conditioner device 1 as an embodiment of the heat recovery refrigeration device according to the present invention.FIG. 2 is a diagram illustrating an internal configuration of an outline of aheat source unit 2 which configures the simultaneous air cooling and air heating operationair conditioner device 1.FIG. 3 is a diagram schematically illustrating the configuration of heat sourceside heat exchangers air conditioner device 1 is a device which is used indoors in air cooling and air heating such as in buildings by performing a vapor compression type of refrigeration cycle operation. - The simultaneous air cooling and air heating operation
air conditioner device 1 mainly has oneheat source unit 2, a plurality (here, four)usage units units usage units refrigerant communication pipes heat source unit 2 and theusage units connecting units refrigerant circuit 10 in the simultaneous air cooling and air heating operationair conditioner device 1 is configured by connecting theheat source unit 2, theusage units units refrigerant communication pipes air conditioner device 1 is configured so that it is possible for each of theusage units air conditioner device 1 is configured so that the heat load of theheat source unit 2 is balanced according to the heat load over all of the plurality ofusage units - <Usage Units>
- The
usage units usage units heat source unit 2 via therefrigerant communication pipes units refrigerant circuit 10. - Next, the configuration of the
usage units usage unit 3 a and theusage units usage unit 3 a will be described here and the subscripts “b”, “c”, and “d” are respectively added instead of the subscript “a” in the reference numerals, which indicate each section of theusage unit 3 a, to the configurations of theusage units - The
usage unit 3 a mainly configures a portion of therefrigerant circuit 10 and has a usage siderefrigerant circuit 13 a (there are usage siderefrigerant circuits usage units refrigerant circuit 13 a mainly has a usage side flowamount adjustment valve 51 a and a usageside heat exchanger 52 a. - The usage side flow
amount adjustment valve 51 a is an electric expansion valve where adjustment to its opening is possible and which is connected with the liquid side of the usageside heat exchanger 52 a in order to perform adjustment of the flow amount of refrigerant which flows through the usageside heat exchanger 52 a and the like. - The usage
side heat exchanger 52 a is a device for performing heat exchange between refrigerant and indoor air and consists of, for example, a fin and tube type of heat exchanger which is configured using a plurality of heat transfer tubes and fins. Here, theusage unit 3 a has anindoor fan 53 a for suctioning indoor air into the inside of the unit and supplying the indoor air indoors as supply air after heat exchange is carried out, and heat exchange between indoor air and refrigerant which flows through the usageside heat exchanger 52 a is possible. Theindoor fan 53 a is driven using anindoor fan motor 54 a. - In addition, the
usage unit 3 a has a usageside control section 50 a which controls the actions of each of thesections usage unit 53 a. Then, the usageside control section 50 a has a microcomputer and a memory which are provided in order to perform control of theusage unit 3 a, and it is possible to perform transfer of control signals and the like with a remote controller (which is not shown in the diagrams) and to perform transfer of control signals and the like with theheat source unit 2. - <Heat Source Unit>
- The
heat source unit 2 is arranged on the roof of a building or the like, is connected with theusage units refrigerant communication pipes refrigerant circuit 10 along with theusage units - Next, the configuration of the
heat source unit 2 will be described. Theheat source unit 2 mainly configures a portion of therefrigerant circuit 10 and has a heat source siderefrigerant circuit 12. The heat source siderefrigerant circuit 12 mainly has acompressor 21, a plurality (here, two) of heatexchange switching mechanisms side heat exchangers amount adjustment valves receiver 28, abridge circuit 29, a high and lowpressure switching mechanism 30, a liquidside shutoff valve 31, a high and low pressure gasside shutoff valve 32, and a low pressure gasside shutoff valve 33. - Here, the
compressor 21 is a device for compressing refrigerant and consists of, for example, a positive displacement type of compressor such as a scroll type where it is possible to vary the operation capacity by controlling an inverter in acompressor motor 21 a. - The first heat
exchange switching mechanism 22 is a device where it is possible to switch the flow path of refrigerant inside the heat source siderefrigerant circuit 12 so that the discharge side of thecompressor 21 and the gas side of the first heat sourceside heat exchanger 24 are connected (refer to the solid line in the first heatexchange switching mechanism 22 inFIG. 1 ) in a case where the first heat sourceside heat exchanger 24 functions as a radiator for refrigerant (set below as a “radiator operation state”) and so that the suction side of thecompressor 21 and the gas side of the first heat sourceside heat exchanger 24 are connected (refer to the dashed line in the first heatexchange switching mechanism 22 inFIG. 1 ) in a case where the first heat sourceside heat exchanger 24 functions as an evaporator for refrigerant (set below as an “evaporator operation state”) and consists of, for example, a four-path switching valve. In addition, the second heatexchange switching mechanism 23 is a device where it is possible to switch the flow path of refrigerant inside the heat source siderefrigerant circuit 12 so that the discharge side of thecompressor 21 and the gas side of the second heat sourceside heat exchanger 25 are connected (refer to the solid line in the second heatexchange switching mechanism 23 inFIG. 1 ) in a case where the second heat sourceside heat exchanger 25 functions as a radiator for refrigerant (set below as a “radiator operation state”) and so that the suction side of thecompressor 21 and the gas side of the second heat sourceside heat exchanger 25 are connected (refer to the dashed line in the second heatexchange switching mechanism 23 inFIG. 1 ) in a case where the second heat sourceside heat exchanger 25 functions as an evaporator for refrigerant (set below as an “evaporator operation state”) and consists of, for example, a four-path switching valve. Then, switching is possible so that the first heat sourceside heat exchanger 24 and the second heat sourceside heat exchanger 25 individually function as an evaporator or a radiator for refrigerant by modifying the switching states of the first heatexchange switching mechanism 22 and the second heatexchange switching mechanism 23. - The first heat source
side heat exchanger 24 is a device for performing heat exchange between refrigerant and outdoor air and consists of, for example, a fin and tube type of heat exchanger which is configured using a plurality of heat transfer tubes and fins. The gas side of the first heat sourceside heat exchanger 24 is connected with the first heatexchange switching mechanism 22 and the liquid side of the first heat sourceside heat exchanger 24 is connected with the first heat source side flowamount adjustment valve 26. In detail, the gas side of the first heat sourceside heat exchanger 24 is provided with afirst header 24 a for performing merging and branching of refrigerant between a plurality of heat transfer tubes which configure the first heat sourceside heat exchanger 24, and thefirst header 24 a is connected with the first heatexchange switching mechanism 22. The liquid side of the first heat sourceside heat exchanger 24 is provided with afirst flow divider 24 b for performing merging and branching of refrigerant between a plurality of heat transfer tubes which configure the first heat sourceside heat exchanger 24, and thefirst flow divider 24 b is connected with the first heat source side flowamount adjustment valve 26. In addition, the second heat sourceside heat exchanger 25 is a device for performing heat exchange between refrigerant and outdoor air and consists of, for example, a fin and tube type of heat exchanger which is configured using a plurality of heat transfer tubes and fins. The gas side of the second heat sourceside heat exchanger 25 is connected with the second heatexchange switching mechanism 23 and the liquid side of the second heat sourceside heat exchanger 25 is connected with the second heat source side flowamount adjustment valve 27. In detail, the gas side of the second heat sourceside heat exchanger 25 is provided with a second header 25 a for performing merging and branching of refrigerant between a plurality of heat transfer tubes which configure the second heat sourceside heat exchanger 25, and the second header 25 a is connected with the second heatexchange switching mechanism 23. The liquid side of the second heat sourceside heat exchanger 25 is provided with asecond flow divider 25 b for performing merging and branching of refrigerant between a plurality of heat transfer tubes which configure the second heat sourceside heat exchanger 25, and thesecond flow divider 25 b is connected with the second heat source side flowamount adjustment valve 27. - Here, the heat exchange capacities of the first heat source
side heat exchanger 24 and the second heat sourceside heat exchanger 25 are different, and the heat exchange capacity of the second heat sourceside heat exchanger 25 is larger than the first heat sourceside heat exchanger 24. In detail, the second heat sourceside heat exchanger 25 has a heat exchange capacity which is 1.8 times to 4.0 times of the first heat sourceside heat exchanger 24. In addition, the first heat sourceside heat exchanger 24 where the heat exchange capacity is small is arranged on the upper side of the second heat sourceside heat exchanger 25 where the heat exchange capacity is large. In detail, the first heat sourceside heat exchanger 24 and the second heat sourceside heat exchanger 25 are configured as an integral heat source side heat exchanger, and the upper portion functions as the first heat sourceside heat exchanger 24 by the heat transfer tubes which configure the upper portion being connected with thefirst header 24 a and thefirst flow divider 24 b and the lower portion functions as the second heat sourceside heat exchanger 25 by the heat transfer tubes which configure the lower portion being connected with the second header 25 a and thesecond flow divider 25 b. In addition, the flow path cross sectional area of the second header 25 a is larger than thefirst header 24 a. In detail, the inner diameter size of the second header 25 a is larger than the inner diameter size of thefirst header 24 a. Then, theheat source unit 2 has anoutdoor fan 34 for suctioning outdoor air into the inside of the unit and exhausting the outdoor air to the outside of the unit after heat exchange is carried out, and heat exchange between outdoor air and refrigerant which flows through the heat sourceside heat exchangers outdoor fan 34 is driven using anoutdoor fan motor 34 a. Here, asuction opening 2 a for suctioning outdoor air is formed in the side surface of theheat source unit 2, anexhaust opening 2 b for exhausting outdoor air is formed in the top surface of theheat source unit 2, and theoutdoor fan 34 is arranged at an upper portion of theheat source unit 2. - The first heat source side flow
amount adjustment valve 26 is an electric expansion valve where adjustment to its opening is possible and which is connected with the liquid side of the first heat sourceside heat exchanger 24 in order to perform adjustment of the flow amount of refrigerant which flows through the first heat sourceside heat exchanger 24 and the like. In addition, the second heat source side flowamount adjustment valve 27 is an electric expansion valve where adjustment to its opening is possible and which is connected with the liquid side of the second heat sourceside heat exchanger 25 in order to perform adjustment of the flow amount of refrigerant which flows through the second heat sourceside heat exchanger 25 and the like. Here, the rated Cv values of the first heat source side flowamount adjustment valve 26 and the second heat source side flowamount adjustment valve 27 are different, and the rated Cv value of the second heat source side flowamount adjustment valve 27 is larger than the rated Cv value of the first heat source side flowamount adjustment valve 26. - The
receiver 28 is a container for temporarily retaining refrigerant which flows between the heat sourceside heat exchangers refrigerant circuits receiver input pipe 28 a is provided at an upper portion of thereceiver 28 and areceiver output pipe 28 b is provided at a lower portion of thereceiver 28. In addition, a receiver input opening and closingvalve 28 c where opening and closing control is possible is provided in thereceiver input pipe 28 a. Then, theinput pipe 28 a and theoutput pipe 28 b in thereceiver 28 connect between the heat sourceside heat exchangers side shutoff valve 31 via thebridge circuit 29. - The
bridge circuit 29 is a circuit which has a function of causing refrigerant to flow into the inside of thereceiver 28 via thereceiver input pipe 28 a and of causing refrigerant to flow out from the inside of thereceiver 28 via thereceiver output pipe 28 b in either a case where refrigerant flows from the heat sourceside heat exchangers side shutoff valve 31 side or a case where refrigerant flows from the liquidside shutoff valve 31 side toward the heat sourceside heat exchangers bridge circuit 29 has fourcheck valves input check valve 29 a is a check valve which only permits passage of refrigerant from the heat sourceside heat exchangers receiver input pipe 28 a. Theinput check valve 29 b is a check valve which only permits passage of refrigerant from the liquidside shutoff valve 31 side to thereceiver input pipe 28 a. That is, theinput check valves side heat exchangers side shutoff valve 31 side to thereceiver input pipe 28 a. Theoutput check valve 29 c is a check valve which only permits passage of refrigerant from thereceiver output pipe 28 b to the liquidside shutoff valve 31 side. Theoutput check valve 29 d is a check valve which only permits passage of refrigerant from thereceiver output pipe 28 b to the heat sourceside heat exchangers output check valves receiver output pipe 28 b to the heat sourceside heat exchangers side shutoff valve 31 side. - The high and low
pressure switching mechanism 30 is a device where it is possible to switch the flow path of refrigerant inside the heat source siderefrigerant circuit 12 so that the discharge side of thecompressor 21 and the high and low pressure gasside shutoff valve 32 are connected (refer to the dashed line in the high and lowpressure switching mechanism 30 inFIG. 1 ) in a case where high pressure gas refrigerant which is discharged from thecompressor 21 is sent to the usage siderefrigerant circuits side shutoff valve 32 and the suction side of thecompressor 21 are connected (refer to the solid line in the high and lowpressure switching mechanism 30 inFIG. 1 ) in a case where high pressure gas refrigerant which is discharged from thecompressor 21 is not sent to the usage siderefrigerant circuits - The liquid
side shutoff valve 31, the high and low pressure gasside shutoff valve 32, and the low pressure gasside shutoff valve 33 are valves which are provided at connection openings with external devices and pipes (in detail, with therefrigerant communication pipes side shutoff valve 31 is connected with thereceiver input pipe 28 a or thereceiver output pipe 28 b via thebridge circuit 29. The high and low pressure gasside shutoff valve 32 is connected with the high and lowpressure switching mechanism 30. The low pressure gasside shutoff valve 33 is connected with the suction side of thecompressor 21. - In addition, the
heat source unit 2 has a heat sourceside control section 20 which controls actions of each of thesections heat source unit 2. Then, the heat sourceside control section 20 has a microcomputer and a memory which are provided in order to perform control of theheat source unit 2, and it is possible to perform transfer of control signals and the like with the usageside control sections usage units - <Connecting Units>
- The connecting
units usage units units usage units heat source unit 2 along with therefrigerant communication pipes refrigerant circuit 10. - Next, the configuration of the connecting
units unit 4 a and the connectingunits unit 4 a will be described here and the subscripts “b”, “c”, and “d” are respectively added instead of the subscript “a” in the reference numerals, which indicate each section of the connectingunit 4 a, to the configurations of the connectingunits - The connecting
unit 4 a mainly configures a portion of therefrigerant circuit 10 and has a connecting side refrigerant circuit 14 a (there are connecting side refrigerant circuits 14 b, 14 c, and 14 d respectively in each of the connectingunits liquid connecting pipe 61 a and agas connecting pipe 62 a. - The
liquid connecting pipe 61 a connects the liquidrefrigerant communication pipe 7 and the usage side flowamount adjustment valve 51 a in the usage siderefrigerant circuit 13 a. - The
gas connecting pipe 62 a has a high pressuregas connecting pipe 63 a which is connected with the high and low pressure gasrefrigerant communication pipe 8, a low pressuregas connecting pipe 64 a which is connected with the low pressure gasrefrigerant communication pipe 9, and a merginggas connecting pipe 65 a where the high pressuregas connecting pipe 63 a and the low pressuregas connecting pipe 64 a merge. The merginggas connecting pipe 65 a is connected with the gas side of the usageside heat exchanger 52 a in the usage siderefrigerant circuit 13 a. A high pressure gas opening and closingvalve 66 a where opening and closing control is possible is provided in the high pressuregas connecting pipe 63 a, and a low pressure gas opening and closingvalve 67 a where opening and closing control is possible is provided in the low pressuregas connecting pipe 64 a. - Then, by setting a state where the low pressure gas opening and closing
valve 67 a is open when theusage unit 3 a is performing an air cooling operation, it is possible for the connectingunit 4 a to function so as to send refrigerant, which flows into theliquid connecting pipe 61 a via the liquidrefrigerant communication pipe 7, to the usageside heat exchanger 52 a via the usage side flowamount adjustment valve 51 a in the usage siderefrigerant circuit 13 a and to return refrigerant, which evaporates due to heat exchange with indoor air in the usageside heat exchanger 52 a, to the low pressure gasrefrigerant communication pipe 9 via the merginggas connecting pipe 65 a and the low pressuregas connecting pipe 64 a. In addition, by setting a state where the low pressure gas opening and closingvalve 67 a is closed and the high pressure gas opening and closingvalve 66 a is open when theusage unit 3 a is performing an air heating operation, it is possible for the connectingunit 4 a to function so as to send refrigerant, which flows into the high pressuregas connecting pipe 63 a and the merginggas connecting pipe 65 a via the high and low pressure gasrefrigerant communication pipe 8, to the usageside heat exchanger 52 a in the usage siderefrigerant circuit 13 a and to return refrigerant, which releases heat due to heat exchange with indoor air in the usageside heat exchanger 52 a, to the liquidrefrigerant communication pipe 7 via the usage side flowamount adjustment valve 51 a and theliquid connecting pipe 61 a. Since not only the connectingunit 4 a but the connectingunits side heat exchangers units - In addition, the connecting
unit 4 a has a connectingside control section 60 a which controls the actions of each of thesections unit 4 a. Then, the connectingside control section 60 a has a microcomputer and a memory which are provided in order to perform control of the connectingunit 4 a, and it is possible to perform transfer of control signals and the like with the usageside control section 50 a in theusage unit 3 a. - As above, the
refrigerant circuit 10 in the simultaneous air cooling and air heating operationair conditioner device 1 is configured by connecting the usage siderefrigerant circuits refrigerant circuit 12, therefrigerant communication pipes air conditioner device 1, it is possible to perform a simultaneous air cooling and air heating operation where, for example, theusage units usage units usage units side heat exchangers side heat exchangers air conditioner device 1 is configured as a heat recovery refrigeration device which includes thecompressor 21, the plurality (here, two) of heat sourceside heat exchangers side heat exchangers side heat exchanger 25 is equal to or more than 1.8 times of the first heat sourceside heat exchanger 24 as described above. - Next, the actions of the simultaneous air cooling and air heating operation
air conditioner device 1 will be described. - It is possible to divide the operation modes of the simultaneous air cooling and air heating operation
air conditioner device 1 into an air cooling operation mode (where the evaporator load is large), an air cooling operation mode (where the evaporator load is small), an air heating operation mode (where the radiator load is large), an air heating operation mode (where the radiator load is small), a simultaneous air cooling and air heating operation mode (where the evaporator load is dominant), a simultaneous air cooling and air heating operation mode (where the radiator load is dominant), and a simultaneous air cooling and air heating operation mode (with a balance between the evaporator and radiator loads). Here, the air cooling operation mode (where the evaporator load is large) is an operation mode which is only for the usage units which perform an air cooling operation (that is, an operation where the usage side heat exchanger functions as an evaporator for refrigerant) and which is where both of the heat sourceside heat exchangers side heat exchanger 24 functions as a radiator for refrigerant with regard to the evaporator load over all of the usage units. The heat cooling operation mode (where the radiator load is large) is an operation mode which is only for the usage units which perform an air heating operation (that is, an operation where the usage side heat exchanger functions as a radiator for refrigerant) and which is where both of the heat sourceside heat exchangers side heat exchanger 24 functions as an evaporator for refrigerant with regard to the radiator load over all of the usage units. The simultaneous air cooling and air heating operation mode (where the evaporator load is dominant) is an operation mode where there is a mixture of the usage units which perform an air cooling operation (that is, an operation where the usage side heat exchanger functions as an evaporator for refrigerant) and the usage units which perform an air heating operation (that is, an operation where the usage side heat exchanger functions as a radiator for refrigerant) and where only the first heat sourceside heat exchanger 24 functions as a radiator for refrigerant with regard to the evaporator load over all of the usage units in a case where the heat load over all of the usage units is dominated by the evaporator load. The simultaneous air cooling and air heating operation mode (where the radiator load is dominant) is an operation mode where there is a mixture of the usage units which perform an air cooling operation (that is, an operation where the usage side heat exchanger functions as an evaporator for refrigerant) and the usage units which perform an air heating operation (that is, an operation where the usage side heat exchanger functions as a radiator for refrigerant) and where only the first heat sourceside heat exchanger 24 functions as an evaporator for refrigerant with regard to the radiator load over all of the usage units in a case where the heat load over all of the usage units is dominated by the radiator load. The simultaneous air cooling and air heating operation mode (with a balance between the evaporator and radiator loads) is an operation mode where there is a mixture of the usage units which perform an air cooling operation (that is, an operation where the usage side heat exchanger functions as an evaporator for refrigerant) and the usage units which perform an air heating operation (that is, an operation where the usage side heat exchanger functions as a radiator for refrigerant) and where the first heat sourceside heat exchanger 24 functions as a radiator for refrigerant and the second heat sourceside heat exchanger 25 functions as an evaporator for refrigerant in a case where the evaporator load and the radiator load is balanced over all of the usage units. - Here, actions of the simultaneous air cooling and air heating operation
air conditioner device 1 which include these operation modes are performed using thecontrol sections - <Air Cooling Operation Mode (where the Evaporator Load is Large)>
- The
refrigerant circuit 10 in theair conditioner device 1 is configured as shown inFIG. 4 (for the flow of refrigerant, refer to the arrows which are added to therefrigerant circuit 10 inFIG. 4 ) during the air cooling operation mode (where the evaporator load is large) when, for example, all of theusage units side heat exchangers side heat exchangers - In detail, in the
heat source unit 2, both of the heat sourceside heat exchangers exchange switching mechanism 22 switching to a radiator operation state (a state which is indicated by the solid line in the first heatexchange switching mechanism 22 inFIG. 4 ) and the second heatexchange switching mechanism 23 switching to a radiator operation state (a state which is indicated by the solid line in the second heatexchange switching mechanism 23 inFIG. 4 ). In addition, the high and lowpressure switching mechanism 30 switches to an evaporator load dominant operation state (a state which is indicated by the solid line in the high and lowpressure switching mechanism 30 inFIG. 4 ). In addition, the heat source side flowamount adjustment valves valve 28 c is in an open state. All of the usageside heat exchangers usage units valves valves units side heat exchangers usage units compressor 21 in theheat source unit 2 are connected via the high and low pressure gasrefrigerant communication pipe 8 and the low pressure gasrefrigerant communication pipe 9. In theusage units amount adjustment valves - In this manner, in the
refrigerant circuit 10, high pressure gas refrigerant which is compressed by and discharged from thecompressor 21 is sent to both of the heat sourceside heat exchangers exchange switching mechanisms side heat exchangers outdoor fan 34 in the heat sourceside heat exchangers side heat exchangers receiver 28 via theinput check valve 29 a and the receiver input opening and closingvalve 28 c by merging after the flow amount is adjusted in the heat source side flowamount adjustment valves receiver 28 is sent to the liquidrefrigerant communication pipe 7 via theoutput check valve 29 c and the liquidside shutoff valve 31 after being temporarily retained inside thereceiver 28. - Then, the refrigerant which is sent to the liquid
refrigerant communication pipe 7 is branched off four ways and is sent to theliquid connecting pipes units liquid connecting pipes amount adjustment valves usage units - Then, the refrigerant which is sent to the usage side flow
amount adjustment valves indoor fans side heat exchangers amount adjustment valves usage units gas connecting pipes units - Then, the low pressure gas refrigerant which is sent to the merging
gas connecting pipes refrigerant communication pipe 8 via the high pressure gas opening and closingvalves gas connecting pipes refrigerant communication pipe 9 via the low pressure gas opening and closingvalves gas connecting pipes - Then, the low pressure gas refrigerant which is sent to the gas
refrigerant communication pipes compressor 21 via the gasside shutoff valves pressure switching mechanism 30. - In this manner, an operation in the air cooling operation mode (where the evaporator load is large) is performed.
- <Air Cooling Operation Mode (where the Evaporator Load is Small)>
- The
refrigerant circuit 10 in theair conditioner device 1 is configured as shown inFIG. 5 (for the flow of refrigerant, refer to the arrows which are added to therefrigerant circuit 10 inFIG. 5 ) during the air cooling operation mode (where the evaporator load is small) when, for example, only theusage unit 3 a performs an air cooling operation (that is, an operation where only the usageside heat exchanger 52 a functions as an evaporator for refrigerant) and only the first heat sourceside heat exchanger 24 functions as a radiator for refrigerant. - In detail, in the
heat source unit 2, only the first heat sourceside heat exchanger 24 functions as a radiator for refrigerant by the first heatexchange switching mechanism 22 switching to a radiator operation state (a state which is indicated by the solid line in the first heatexchange switching mechanism 22 inFIG. 5 ). In addition, the high and lowpressure switching mechanism 30 switches to an evaporator load dominant operation state (a state which is indicated by the solid line in the high and lowpressure switching mechanism 30 inFIG. 5 ). In addition, the first heat source side flowamount adjustment valve 26 adjusts its opening, the second heat source side flowamount adjustment valve 27 is in a closed state, and the receiver input opening and closingvalve 28 c is in an open state. Only the usageside heat exchanger 52 a in theusage unit 3 a functions as an evaporator for refrigerant due to the high pressure gas opening and closingvalve 66 a and the low pressure gas opening and closingvalve 67 a being in an open state and the high pressure gas opening and closingvalves valves units side heat exchanger 52 a in theusage unit 3 a and the suction side of thecompressor 21 in theheat source unit 2 are connected via the high and low pressure gasrefrigerant communication pipe 8 and the low pressure gasrefrigerant communication pipe 9. The usage side flowamount adjustment valve 51 a adjusts its opening in theusage unit 3 a and the usage side flowamount adjustment valves usage units - In this manner, in the
refrigerant circuit 10, high pressure gas refrigerant which is compressed by and discharged from thecompressor 21 is sent to only the first heat sourceside heat exchanger 24 via the first heatexchange switching mechanism 22. Then, the high pressure gas refrigerant which is sent to the first heat sourceside heat exchanger 24 releases heat by heat exchange being performed with outdoor air which is the heat source which is supplied using theoutdoor fan 34 in the first heat sourceside heat exchanger 24. Then, the refrigerant which releases heat in the first heat sourceside heat exchanger 24 is sent to thereceiver 28 via theinput check valve 29 a and the receiver input opening and closingvalve 28 c after the flow amount is adjusted in the first heat source side flowamount adjustment valve 26. Then, the refrigerant which is sent to thereceiver 28 is sent to the liquidrefrigerant communication pipe 7 via theoutput check valve 29 c and the liquidside shutoff valve 31 after being temporarily retained inside thereceiver 28. - Then, the refrigerant which is sent to the liquid
refrigerant communication pipe 7 is sent to only theliquid connecting pipe 61 a in the connectingunit 4 a. Then, the refrigerant which is sent to theliquid connecting pipe 61 a in the connectingunit 4 a is sent to the usage side flowamount adjustment valve 51 a in theusage unit 3 a. - Then, the refrigerant which is sent to the usage side flow
amount adjustment valve 51 a becomes low pressure gas refrigerant by evaporating due to heat exchange being performed with indoor air which is supplied using theindoor fan 53 a in the usageside heat exchanger 52 a after the flow amount is adjusted in the usage side flowamount adjustment valve 51 a. At the same time, an air cooling operation is performed using only theusage unit 3 a by the indoor air being cooled and supplied indoors. Then, the low pressure gas refrigerant is sent to the merginggas connecting pipe 65 a in the connectingunit 4 a. - Then, the low pressure gas refrigerant which is sent to the merging
gas connecting pipe 65 a is sent to the high and low pressure gasrefrigerant communication pipe 8 via the high pressure gas opening and closingvalve 66 a and the high pressuregas connecting pipe 63 a and is sent to the low pressure gasrefrigerant communication pipe 9 via the low pressure gas opening and closingvalve 67 a and the low pressuregas connecting pipe 64 a. - Then, the low pressure gas refrigerant which is sent to the gas
refrigerant communication pipes compressor 21 via the gasside shutoff valves pressure switching mechanism 30. - In this manner, an operation in the air cooling operation mode (where the evaporator load is small) is performed.
- <Air Heating Operation Mode (where the Radiator Load is Large)>
- The
refrigerant circuit 10 in theair conditioner device 1 is configured as shown inFIG. 6 (for the flow of refrigerant, refer to the arrows which are added to therefrigerant circuit 10 inFIG. 6 ) during the air heating operation mode (where the radiator load is large) when, for example, all of theusage units side heat exchangers side heat exchangers - In detail, in the
heat source unit 2, both of the heat sourceside heat exchangers exchange switching mechanism 22 switching to an evaporator operation state (a state which is indicated by the dashed line in the first heatexchange switching mechanism 22 inFIG. 6 ) and the second heatexchange switching mechanism 23 switching to an evaporator operation state (a state which is indicated by the dashed line in the second heatexchange switching mechanism 23 inFIG. 6 ). In addition, the high and lowpressure switching mechanism 30 switches to a radiator load dominant operation state (a state which is indicated by the dashed line in the high and lowpressure switching mechanism 30 inFIG. 6 ). In addition, the heat source side flowamount adjustment valves valve 28 c is in an open state. All of the usageside heat exchangers usage units valves valves units side heat exchangers usage units compressor 21 in theheat source unit 2 are connected via the high and low pressure gasrefrigerant communication pipe 8. In theusage units amount adjustment valves - In this manner, in the
refrigerant circuit 10, high pressure gas refrigerant which is compressed by and discharged from thecompressor 21 is sent to the high and low pressure gasrefrigerant communication pipe 8 via the high and lowpressure switching mechanism 30 and the high and low pressure gasside shutoff valve 32. - Then, the high pressure gas refrigerant which is sent to the high and low pressure gas
refrigerant communication pipe 8 is branched off four ways and is sent to the high pressuregas connecting pipes units gas connecting pipes side heat exchangers usage units valves gas connecting pipes - Then, the high pressure gas refrigerant which is sent to the usage
side heat exchangers indoor fans side heat exchangers usage units side heat exchangers liquid connecting pipes units amount adjustment valves - Then, the refrigerant which is sent to the
liquid connecting pipes refrigerant communication pipe 7. - Then, the refrigerant which is sent to the liquid
refrigerant communication pipe 7 is sent to thereceiver 28 via the liquidside shutoff valve 31, theinput check valve 29 b, and the receiver input opening and closingvalve 28 c. Then, the refrigerant which is sent to thereceiver 28 is sent to both of the heat source side flowamount adjustment valves output check valve 29 d after being temporarily retained inside thereceiver 28. Then, the refrigerant which is sent to the heat source side flowamount adjustment valves outdoor fan 34 in the heat sourceside heat exchangers amount adjustment valves exchange switching mechanisms exchange switching mechanisms compressor 21. - In this manner, an operation in the air heating operation mode (where the radiator load is large) is performed.
- <Air Heating Operation Mode (where the Radiator Load is Small)>
- The
refrigerant circuit 10 in theair conditioner device 1 is configured as shown inFIG. 7 (for the flow of refrigerant, refer to the arrows which are added to therefrigerant circuit 10 inFIG. 7 ) during the air heating operation mode (where the radiator load is small) when, for example, only theusage unit 3 a performs an air heating operation (that is, an operation where only the usageside heat exchanger 52 a functions as a radiator for refrigerant) and only the first heat sourceside heat exchanger 24 functions as an evaporator for refrigerant. - In detail, in the
heat source unit 2, only the first heat sourceside heat exchanger 24 functions as an evaporator for refrigerant by the first heatexchange switching mechanism 22 switching to an evaporator operation state (a state which is indicated by the dashed line in the first heatexchange switching mechanism 22 inFIG. 7 ). In addition, the high and lowpressure switching mechanism 30 switches to a radiator load dominant operation state (a state which is indicated by the dashed line in the high and lowpressure switching mechanism 30 inFIG. 7 ). In addition, the first heat source side flowamount adjustment valve 26 adjusts its opening, the second heat source side flowamount adjustment valve 27 is in a closed state, and the receiver input opening and closingvalve 28 c is in an open state. Only the usageside heat exchanger 52 a in theusage unit 3 a functions as a radiator for refrigerant due to the high pressure gas opening and closingvalve 66 a being in an open state and the high pressure gas opening and closingvalves valves units side heat exchanger 52 a in theusage unit 3 a and the discharge side of thecompressor 21 in theheat source unit 2 are connected via the high and low pressure gasrefrigerant communication pipe 8. The usage side flowamount adjustment valve 51 a adjusts its opening in theusage unit 3 a and the usage side flowamount adjustment valves usage units - In this manner, in the
refrigerant circuit 10, high pressure gas refrigerant which is compressed by and discharged from thecompressor 21 is sent to the high and low pressure gasrefrigerant communication pipe 8 via the high and lowpressure switching mechanism 30 and the high and low pressure gasside shutoff valve 32. - Then, the high pressure gas refrigerant which is sent to the high and low pressure gas
refrigerant communication pipe 8 is sent to only the high pressuregas connecting pipe 63 a in the connectingunit 4 a. The high pressure gas refrigerant which is sent to the high pressuregas connecting pipe 63 a is sent to the usageside heat exchanger 52 a in theusage unit 3 a via the high pressure gas opening and closingvalve 66 a and the merginggas connecting pipe 65 a. - Then, the high pressure gas refrigerant which is sent to the usage
side heat exchanger 52 a releases heat by heat exchange being performed with indoor air which is supplied using theindoor fan 53 a in the usageside heat exchanger 52 a. At the same time, an air heating operation is performed using only theusage unit 3 a by the indoor air being heated and supplied indoors. The refrigerant which releases heat in the usageside heat exchanger 52 a is sent to theliquid connecting pipe 61 a in the connectingunits 4 a after the flow amount is adjusted in the usage side flowamount adjustment valve 51 a. - Then, the refrigerant which is sent to the
liquid connecting pipe 61 a is sent to the liquidrefrigerant communication pipe 7. - Then, the refrigerant which is sent to the liquid
refrigerant communication pipe 7 is sent to thereceiver 28 via the liquidside shutoff valve 31, theinput check valve 29 b, and the receiver input opening and closingvalve 28 c. The refrigerant which is sent to thereceiver 28 is sent to only the first heat source side flowamount adjustment valve 26 via theoutput check valve 29 d after being temporarily retained inside thereceiver 28. Then, the refrigerant which is sent to the first heat source side flowamount adjustment valve 26 becomes low pressure gas refrigerant by evaporating due to heat exchange being performed with outdoor air which is supplied using theoutdoor fan 34 in the first heat sourceside heat exchanger 24 after the flow amount is adjusted in the first heat source side flowamount adjustment valve 26 and the low pressure gas refrigerant is sent to the first heatexchange switching mechanism 22. Then, the low pressure gas refrigerant which is sent to the first heatexchange switching mechanism 22 is returned to the suction side of thecompressor 21. - In this manner, an operation in the air heating operation mode (where the radiator load is small) is performed.
- <Simultaneous Air Cooling and Air Heating Operation Mode (where the Evaporator Load is Dominant)>
- The
refrigerant circuit 10 in theair conditioner device 1 is configured as shown inFIG. 8 (for the flow of refrigerant, refer to the arrows which are added to therefrigerant circuit 10 inFIG. 8 ) during the simultaneous air cooling and air heating operation mode (where the evaporator load is dominant) when, for example, theusage units usage unit 3 d performs an air heating operation (that is, an operation where the usageside heat exchangers side heat exchanger 52 d functions as a radiator for refrigerant) and only the first heat sourceside heat exchanger 24 functions as a radiator for refrigerant. - In detail, in the
heat source unit 2, only the first heat sourceside heat exchanger 24 functions as a radiator for refrigerant by the first heatexchange switching mechanism 22 switching to a radiator operation state (a state which is indicated by the solid line in the first heatexchange switching mechanism 22 inFIG. 8 ). In addition, the high and lowpressure switching mechanism 30 switches to a radiator load dominant operation state (a state which is indicated by the dashed line in the high and lowpressure switching mechanism 30 inFIG. 8 ). In addition, the first heat source side flowamount adjustment valve 26 adjusts its opening, the second heat source side flowamount adjustment valve 27 is in a closed state, and the receiver input opening and closingvalve 28 c is in an open state. The usageside heat exchangers usage units side heat exchanger 52 d in theusage unit 3 d functions as a radiator for refrigerant due to the high pressure gas opening and closingvalve 66 d and the low pressure gas opening and closingvalves valves valve 67 d being in an closed state in the connectingunits side heat exchangers usage units compressor 21 in theheat source unit 2 are connected via the low pressure gasrefrigerant communication pipe 9 and there is a state where the usageside heat exchanger 52 d in theusage unit 3 d and the discharge side of thecompressor 21 in theheat source unit 2 are connected via the high and low pressure gasrefrigerant communication pipe 8. In theusage units amount adjustment valves - In this manner, in the
refrigerant circuit 10, a portion of the high pressure gas refrigerant which is compressed by and discharged from thecompressor 21 is sent to the high and low pressure gasrefrigerant communication pipe 8 via the high and lowpressure switching mechanism 30 and the high and low pressure gasside shutoff valve 32 and the remaining portion of the high pressure gas refrigerant which is compressed by and discharged from thecompressor 21 is sent to the first heat sourceside heat exchanger 24 via the first heatexchange switching mechanism 22. - Then, the high pressure gas refrigerant which is sent to the high and low pressure gas
refrigerant communication pipe 8 is sent to the high pressuregas connecting pipe 63 d in the connectingunit 4 d. The high pressure gas refrigerant which is sent to the high pressuregas connecting pipe 63 d is sent to the usageside heat exchanger 52 d in theusage unit 3 d via the high pressure gas opening and closingvalve 66 d and the merginggas connecting pipe 65 d. - Then, the high pressure gas refrigerant which is sent to the usage
side heat exchanger 52 d releases heat by heat exchange being performed with indoor air which is supplied using theindoor fan 53 d in the usageside heat exchanger 52 d. At the same time, an air heating operation is performed using theusage unit 3 d by the indoor air being heated and supplied indoors. The refrigerant which releases heat in the usageside heat exchanger 52 d is sent to theliquid connecting pipe 61 d in the connectingunit 4 d after the flow amount is adjusted in the usage side flowamount adjustment valve 51 d. - In addition, the high pressure gas refrigerant which is sent to the first heat source
side heat exchanger 24 releases heat by heat exchange being performed with outdoor air which is the heat source which is supplied using theoutdoor fan 34 in the first heat sourceside heat exchanger 24. Then, the refrigerant which releases heat in the first heat sourceside heat exchanger 24 is sent to thereceiver 28 via theinput check valve 29 a and the receiver input opening and closingvalve 28 c after the flow amount is adjusted in the first heat source side flowamount adjustment valve 26. Then, the refrigerant which is sent to thereceiver 28 is sent to the liquidrefrigerant communication pipe 7 via theoutput check valve 29 c and the liquidside shutoff valve 31 after being temporarily retained inside thereceiver 28. - The refrigerant which is sent to the
liquid connecting pipe 61 d with heat being released in the usageside heat exchanger 52 d is sent to the liquidrefrigerant communication pipe 7 and merges with refrigerant which is sent to the liquidrefrigerant communication pipe 7 with heat being released in the first heat sourceside heat exchanger 24. - Then, the refrigerant which merges in the liquid
refrigerant communication pipe 7 is branched off three ways and is sent to theliquid connecting pipes units liquid connecting pipes amount adjustment valves usage units - Then, the refrigerant which is sent to the usage side flow
amount adjustment valves indoor fans side heat exchangers amount adjustment valves usage units gas connecting pipes units - Then, the low pressure gas refrigerant which is sent to the merging
gas connecting pipes refrigerant communication pipe 9 via the low pressure gas opening and closingvalves gas connecting pipes - Then, the low pressure gas refrigerant which is sent to the low pressure gas
refrigerant communication pipe 9 is returned to the suction side of thecompressor 21 via the gasside shutoff valve 33. - In this manner, an operation in the simultaneous air cooling and air heating operation mode (where the evaporator load is dominant) is performed. Then, in the simultaneous air cooling and air heating operation mode (where the evaporator load is dominant), heat recovery is performed between the usage
side heat exchangers side heat exchanger 52 d which functions as a radiator for refrigerant to the usageside heat exchangers - <Simultaneous Air Cooling and Air Heating Operation Mode (where the Radiator Load is Dominant)>
- The
refrigerant circuit 10 in theair conditioner device 1 is configured as shown inFIG. 9 (for the flow of refrigerant, refer to the arrows which are added to therefrigerant circuit 10 inFIG. 9 ) during the simultaneous air cooling and air heating operation mode (where the radiator load is dominant) when, for example, theusage units usage unit 3 d performs an air cooling operation (that is, an operation where the usageside heat exchangers side heat exchanger 52 d functions as an evaporator for refrigerant) and only the first heat sourceside heat exchanger 24 functions as an evaporator for refrigerant. - In detail, in the
heat source unit 2, only the first heat sourceside heat exchanger 24 functions as an evaporator for refrigerant by the first heatexchange switching mechanism 22 switching to an evaporator operation state (a state which is indicated by the dashed line in the first heatexchange switching mechanism 22 inFIG. 9 ). In addition, the high and lowpressure switching mechanism 30 switches to a radiator load dominant operation state (a state which is indicated by the dashed line in the high and lowpressure switching mechanism 30 inFIG. 9 ). In addition, the first heat source side flowamount adjustment valve 26 adjusts its openings, the second heat source side flowamount adjustment valve 27 is in a closed state, and the receiver input opening and closingvalve 28 c is in an open state. The usageside heat exchangers usage units side heat exchanger 52 d in theusage unit 3 d functions as an evaporator for refrigerant due to the high pressure gas opening and closingvalves valve 67 d being in an open state and the high pressure gas opening and closingvalve 66 d and the low pressure gas opening and closingvalves units side heat exchanger 52 d in theusage unit 3 d and the suction side of thecompressor 21 in theheat source unit 2 are connected via the low pressure gasrefrigerant communication pipe 9 and there is a state where the usageside heat exchangers usage units compressor 21 in theheat source unit 2 are connected via the high and low pressure gasrefrigerant communication pipe 8. In theusage units amount adjustment valves - In this manner, in the
refrigerant circuit 10, high pressure gas refrigerant which is compressed by and discharged from thecompressor 21 is sent to the high and low pressure gasrefrigerant communication pipe 8 via the high and lowpressure switching mechanism 30 and the high and low pressure gasside shutoff valve 32. - Then, the high pressure gas refrigerant which is sent to the high and low pressure gas
refrigerant communication pipe 8 is branched off three ways and is sent to the high pressuregas connecting pipes units gas connecting pipes side heat exchangers usage units valves gas connecting pipes - Then, the high pressure gas refrigerant which is sent to the usage
side heat exchangers indoor fans side heat exchangers usage units side heat exchangers liquid connecting pipes units amount adjustment valves - Then, the refrigerant which is sent to the
liquid connecting pipes refrigerant communication pipe 7. - A portion of the refrigerant which merges in the liquid
refrigerant communication pipe 7 is sent to theliquid connecting pipe 61 d in the connectingunit 4 d and the remaining portion of the refrigerant which merges in the liquidrefrigerant communication pipe 7 is sent to thereceiver 28 via the liquidside shutoff valve 31, theinput check valve 29 b, and the receiver input opening and closingvalve 28 c. - Then, the refrigerant which is sent to the
liquid connecting pipe 61 d in the connectingunit 4 d is sent to the usage side flowamount adjustment valve 51 d in theusage unit 3 d. - Then, the refrigerant which is sent to the usage side flow
amount adjustment valve 51 d becomes low pressure gas refrigerant by evaporating due to heat exchange being performed with indoor air which is supplied using theindoor fan 53 d in the usageside heat exchanger 52 d after the flow amount is adjusted in the usage side flowamount adjustment valve 51 d. At the same time, an air cooling operation is performed using theusage unit 3 d by the indoor air being cooled and supplied indoors. Then, the low pressure gas refrigerant is sent to the merginggas connecting pipe 65 d in the connectingunit 4 d. - Then, the low pressure gas refrigerant which is sent to the merging
gas connecting pipe 65 d is sent to the low pressure gasrefrigerant communication pipe 9 via the low pressure gas opening and closingvalve 67 d and the low pressuregas connecting pipe 64 d. - Then, the low pressure gas refrigerant which is sent to the low pressure gas
refrigerant communication pipe 9 is returned to the suction side of thecompressor 21 via the gasside shutoff valve 33. - In addition, the refrigerant which is sent to the
receiver 28 is sent to the first heat source side flowamount adjustment valve 26 via theoutput check valve 29 d after being temporarily retained inside thereceiver 28. Then, the refrigerant which is sent to the first heat source side flowamount adjustment valve 26 becomes low pressure gas refrigerant by evaporating due to heat exchange being performed with outdoor air which is supplied using theoutdoor fan 34 in the first heat sourceside heat exchanger 24 after the flow amount is adjusted in the first heat source side flowamount adjustment valve 26 and the low pressure gas refrigerant is sent to the first heatexchange switching mechanism 22. Then, the low pressure gas refrigerant which is sent to the first heatexchange switching mechanism 22 is returned to the suction side of thecompressor 21 by merging with the low pressure gas refrigerant which is returned to the suction side of thecompressor 21 via the low pressure gasrefrigerant communication pipe 9 and the gasside shutoff valve 33. - In this manner, an operation in the simultaneous air cooling and air heating operation mode (where the radiator load is dominant) is performed. Then, in the simultaneous air cooling and air heating operation mode (where the radiator load is dominant), heat recovery is performed between the usage
side heat exchangers side heat exchangers side heat exchanger 52 d which functions as an evaporator for refrigerant as described above. - <Simultaneous Air Cooling and Air Heating Operation Mode (with a Balance Between the Evaporator and the Radiator Loads)>
- The
refrigerant circuit 10 in theair conditioner device 1 is configured as shown inFIG. 10 (for the flow of refrigerant, refer to the arrows which are added to therefrigerant circuit 10 inFIG. 10 ) during the simultaneous air cooling and air heating operation mode (with a balance between the evaporator and radiator loads) when, for example, theusage units usage units side heat exchangers side heat exchangers side heat exchanger 24 functions as a radiator for refrigerant, and the second heat sourceside heat exchanger 25 functions as an evaporator for refrigerant. - In detail, in the
heat source unit 2, the first heat sourceside heat exchanger 24 functions as a radiator for refrigerant and the second heat sourceside heat exchanger 25 functions as an evaporator for refrigerant by the first heatexchange switching mechanism 22 switching to a radiator operation state (a state which is indicated by the solid line in the first heatexchange switching mechanism 22 inFIG. 10 ) and the second heatexchange switching mechanism 23 switching to an evaporator operation state (a state which is indicated by the dashed line in the second heatexchange switching mechanism 23 inFIG. 10 ). In addition, the high and lowpressure switching mechanism 30 switches to a radiator load dominant operation state (a state which is indicated by the dashed line in the high and lowpressure switching mechanism 30 inFIG. 10 ). In addition, the heat source side flowamount adjustment valves side heat exchangers usage units side heat exchangers usage units valves valves valves valves units side heat exchangers usage units compressor 21 in theheat source unit 2 are connected via the low pressure gasrefrigerant communication pipe 9 and there is a state where the usageside heat exchangers usage units compressor 21 in theheat source unit 2 are connected via the high and low pressure gasrefrigerant communication pipe 8. In theusage units amount adjustment valves - In this manner, in the
refrigerant circuit 10, a portion of the high pressure gas refrigerant which is compressed by and discharged from thecompressor 21 is sent to the high and low pressure gasrefrigerant communication pipe 8 via the high and lowpressure switching mechanism 30 and the high and low pressure gasside shutoff valve 32 and the remaining portion of the high pressure gas refrigerant which is compressed by and discharged from thecompressor 21 is sent to the first heat sourceside heat exchanger 24 via the first heatexchange switching mechanism 22. - Then, the high pressure gas refrigerant which is sent to the high and low pressure gas
refrigerant communication pipe 8 is sent to the high pressure gas connecting pipe s 63 c and 63 d in the connectingunits gas connecting pipes side heat exchangers usage units valves gas connecting pipes - Then, the high pressure gas refrigerant which is sent to the usage
side heat exchangers indoor fans side heat exchangers usage units side heat exchangers liquid connecting pipes units amount adjustment valves - The refrigerant which is sent to the
liquid connecting pipes side heat exchangers refrigerant communication pipe 7. - Then, the refrigerant which merges in the liquid
refrigerant communication pipe 7 is branched off two ways and is sent to theliquid connecting pipes units liquid connecting pipes amount adjustment valves usage units - Then, the refrigerant which is sent to the usage side flow
amount adjustment valves indoor fans side heat exchangers amount adjustment valves usage units gas connecting pipes units - Then, the low pressure gas refrigerant which is sent to the merging
gas connecting pipes refrigerant communication pipe 9 via the low pressure gas opening and closingvalves gas connecting pipes - Then, the low pressure gas refrigerant which is sent to the low pressure gas
refrigerant communication pipe 9 is returned to the suction side of thecompressor 21 via the gasside shutoff valve 33. - In addition, the high pressure gas refrigerant which is sent to the first heat source
side heat exchanger 24 releases heat by heat exchange being performed with outdoor air which is the heat source which is supplied using theoutdoor fan 34 in the first heat sourceside heat exchanger 24. Then, most of the refrigerant which releases heat in the first heat sourceside heat exchanger 24 is sent to the second heat source side flowamount adjustment valve 27 after passing through the first heat source side flowamount adjustment valve 26. For this reason, there is a state where the refrigerant which releases heat in the first heat sourceside heat exchanger 24 is not sent to the liquidrefrigerant communication pipe 7 via thereceiver 28, thebridge circuit 29, and the liquidside shutoff valve 31. Then, the refrigerant which is sent to the second heat source side flowamount adjustment valve 27 becomes low pressure gas refrigerant by evaporating due to heat exchange being performed with outdoor air which is supplied using theoutdoor fan 34 in the second heat sourceside heat exchanger 25 after the flow amount is adjusted in the second heat source side flowamount adjustment valve 27 and the low pressure gas refrigerant is sent to the second heatexchange switching mechanism 23. Then, the low pressure gas refrigerant which is sent to the second heatexchange switching mechanism 23 is returned to the suction side of thecompressor 21 by merging with the low pressure gas refrigerant which is returned to the suction side of thecompressor 21 via the low pressure gasrefrigerant communication pipe 9 and the gasside shutoff valve 33. - In this manner, an operation in the simultaneous air cooling and air heating operation mode (with a balance between the evaporator and radiator loads) is performed. Then, in the simultaneous air cooling and air heating operation mode (with a balance between the evaporator and radiator loads), heat recovery is performed between the usage
side heat exchangers side heat exchangers side heat exchangers side heat exchangers side heat exchanger 24 functioning as a radiator for refrigerant and the second heat sourceside heat exchanger 25 functioning as an evaporator for refrigerant as described above. - The simultaneous air cooling and air heating operation
air conditioner device 1 has the following characteristics. - <A>
- Here, firstly, the heat exchange capacity of the second heat source
side heat exchanger 25 is equal to or more than 1.8 times of the first heat sourceside heat exchanger 24 as described above. For this reason, it is possible to widen the range over which it is possible to reduce the heat load in a case where only the first heat sourceside heat exchanger 24 where the heat exchange capacity is small functions as an evaporator or a radiator for refrigerant in, for example, the air cooling operation mode (where the evaporator load is small), the simultaneous air cooling and air heating operation mode (where the evaporator load is dominant), the air heating operation mode (where the radiator load is small), and the simultaneous air cooling and air heating operation mode (where the radiator load is dominant) described above, compared to a case where the ratio of heat exchange capacities of the heat source side heat exchangers is small as in the background art. Due to this, it is possible to provide a countermeasure for a case where the heat load over all of the plurality of usageside heat exchangers side heat exchanger 25 is equal to or less than 4.0 times of the first heat sourceside heat exchanger 24 as described above. For this reason, it is possible for the flow amount of refrigerant which flows through the two heat sourceside heat exchangers compressor 21 to not become large in a case of performing the countermeasure where one out of the two heat sourceside heat exchangers side heat exchangers side heat exchangers side heat exchangers - Here, in this manner, it is possible to provide a countermeasure for a case where the heat load over all of the plurality of usage
side heat exchangers - <B>
- Here, firstly, the two heat source
side heat exchangers side heat exchanger 24 is arranged at the lower side, there is a concern that the desired heat exchange performance will not be obtained due to a state being generated where all of the first heat sourceside heat exchanger 24 is filled with liquid refrigerant (set below as “liquid sink”) since the heat exchange capacity is small. - Therefore, here, the first heat source
side heat exchanger 24 where the heat exchange capacity is small is arranged more to the upper side than the second heat sourceside heat exchanger 25 where the heat exchange capacity is large as described above. For this reason, the second heat sourceside heat exchanger 25 where the heat exchange capacity is large is arranged on the lower side and it is possible for it to be difficult for liquid sink to be generated. Due to this, it is possible for a desired heat exchange performance to be exhibited in both of the heat exchangeside heat exchangers side heat exchangers - <C>
- Here, in regard to connecting the heat source side flow
amount adjustment valves side heat exchangers amount adjustment valve 27 is used so that the rated Cv value is larger than the first heat source side flowamount adjustment valve 26. Due to this, it is possible to appropriately adjust the flow amount of refrigerant which flows through each of the heat sourceside heat exchangers side heat exchangers - <D>
- Here, in regard to providing the headers on the gas side of each of the heat source
side heat exchangers first header 24 a as described above. Due to this, it is possible to appropriately perform merging and branching of refrigerant between the plurality of heat transfer tubes which configure each of the heat sourceside heat exchangers headers 24 a and 25 a according to the heat exchange capacities of each of the heat sourceside heat exchangers - The example of the configuration of the simultaneous air cooling and air heating operation
air conditioner device 1 is exemplified and described in the embodiment described above as the heat recovery refrigeration device where the present invention is applied but the present invention is not limited to this. That is, it is possible for the present invention to be applied as long as it is a configuration where a compressor, a plurality of heat source side heat exchangers, and a plurality of usage side heat exchangers are included and it is possible to perform heat recovery between the usage side heat exchangers by sending refrigerant from the usage side heat exchanger which functions as a radiator for refrigerant to the usage side heat exchanger which functions as an evaporator for refrigerant. - It is possible for the present invention to be widely applied with regard to heat recovery refrigeration devices which include a compressor, a plurality of heat source side heat exchangers, and a plurality of usage side heat exchangers, and which is able to perform heat recovery between the usage side heat exchangers by sending refrigerant from the usage side heat exchanger which functions as a radiator for refrigerant to the usage side heat exchanger which functions as an evaporator for refrigerant.
-
- 1 SIMULTANEOUS AIR COOLING AND AIR HEATING OPERATION AIR CONDITIONER DEVICE (HEAT RECOVERY REFRIGERATION DEVICE)
- 21 COMPRESSOR
- 24 FIRST HEAT SOURCE SIDE HEAT EXCHANGER
- 24 a FIRST HEADER
- 25 SECOND HEAT SOURCE SIDE HEAT EXCHANGER
- 25 a SECOND HEADER
- 26 FIRST HEAT SOURCE SIDE FLOW AMOUNT ADJUSTMENT VALVE
- 27 SECOND HEAT SOURCE SIDE FLOW AMOUNT ADJUSTMENT VALVE
- 52 a, 52 b, 52 c, 52 d USAGE SIDE HEAT EXCHANGER
- <
Patent Literature 1> Japanese Laid-open Patent Application Publication No. H5-332637
Claims (8)
1. A heat recovery refrigeration device comprising:
a compressor;
a plurality of heat source side heat exchangers switchable between individually functioning as an evaporator or a radiator of refrigerant; and
a plurality of usage side heat exchangers switchable between individually functioning as an evaporator or a radiator of the refrigerant,
the heat recovery refrigeration device being configured to perform heat recovery between the usage side heat exchangers by sending the refrigerant from at least one of the usage side heat exchangers functioning as a radiator of the refrigerant to at least one of the usage side heat exchangers functioning as an evaporator of the refrigerant,
the plurality of heat source side heat exchangers including a first heat source side heat exchanger and a second heat source side heat exchanger, the second heat source side heat exchanger having a heat exchange capacity 1.8 times to 4.0 times of the first heat source side heat exchanger.
2. The heat recovery refrigeration device according to claim 1 , wherein
the first heat source side heat exchanger is arranged more to an upper side than the second heat source side heat exchanger.
3. The heat recovery refrigeration device according to claim 1 , wherein
a first heat source side flow amount adjustment valve is connected to a liquid side of the first heat source side heat exchanger, the first heat source side flow amount adjustment valve having an adjustable opening,
a second heat source side flow amount adjustment valve is connected with a liquid side of the second heat source side heat exchanger, the second heat source side flow amount adjustment valve having an adjustable opening, and
a rated Cv value of the second heat source side flow amount adjustment valve is larger than a rated Cv of the first heat source side flow amount adjustment valve.
4. The heat recovery refrigeration device according to claim 1 , wherein
a first header is provided on a gas side of the first heat source side heat exchanger, the first header merging and branching refrigerant between a plurality of heat transfer tubes of the first heat source side heat exchanger,
a second header is provided on a gas side of the second heat source side heat exchanger, the second header merging and branching refrigerant between a plurality of heat transfer tubes of the second heat source side heat exchanger, and
a flow path cross sectional area of the second header is larger than a flow path cross sectional area of the first header.
5. The heat recovery refrigeration device according to claim 2 , wherein
a first heat source side flow amount adjustment valve is connected to a liquid side of the first heat source side heat exchanger, the first heat source side flow amount adjustment valve having an adjustable opening,
a second heat source side flow amount adjustment valve is connected with a liquid side of the second heat source side heat exchanger, the second heat source side flow amount adjustment valve having an adjustable opening, and
a rated Cv value of the second heat source side flow amount adjustment valve is larger than a rated Cv of the first heat source side flow amount adjustment valve.
6. The heat recovery refrigeration device according to claim 5 , wherein
a first header is provided on a gas side of the first heat source side heat exchanger, the first header merging and branching refrigerant between a plurality of heat transfer tubes of the first heat source side heat exchanger,
a second header is provided on a gas side of the second heat source side heat exchanger, the second header merging and branching refrigerant between a plurality of heat transfer tubes of the second heat source side heat exchanger, and
a flow path cross sectional area of the second header is larger than a flow path cross sectional area of the first header.
7. The heat recovery refrigeration device according to claim 2 , wherein
a first header is provided on a gas side of the first heat source side heat exchanger, the first header merging and branching refrigerant between a plurality of heat transfer tubes of the first heat source side heat exchanger,
a second header is provided on a gas side of the second heat source side heat exchanger, the second header merging and branching refrigerant between a plurality of heat transfer tubes of the second heat source side heat exchanger, and
a flow path cross sectional area of the second header is larger than a flow path cross sectional area of the first header.
8. The heat recovery refrigeration device according to claim 3 , wherein
a first header is provided on a gas side of the first heat source side heat exchanger, the first header merging and branching refrigerant between a plurality of heat transfer tubes of the first heat source side heat exchanger,
a second header is provided on a gas side of the second heat source side heat exchanger, the second header merging and branching refrigerant between a plurality of heat transfer tubes of the second heat source side heat exchanger, and
a flow path cross sectional area of the second header is larger than a flow path cross sectional area of the first header.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2013181493A JP5772904B2 (en) | 2013-09-02 | 2013-09-02 | Heat recovery type refrigeration system |
JP2013-181493 | 2013-09-02 | ||
PCT/JP2014/072737 WO2015030173A1 (en) | 2013-09-02 | 2014-08-29 | Heat recovery-type refrigeration device |
Publications (1)
Publication Number | Publication Date |
---|---|
US20160209084A1 true US20160209084A1 (en) | 2016-07-21 |
Family
ID=52586720
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US14/915,018 Abandoned US20160209084A1 (en) | 2013-09-02 | 2014-08-29 | Heat recovery refrigeration device |
Country Status (6)
Country | Link |
---|---|
US (1) | US20160209084A1 (en) |
EP (1) | EP3026355B1 (en) |
JP (1) | JP5772904B2 (en) |
CN (1) | CN105492833A (en) |
AU (1) | AU2014312825B2 (en) |
WO (1) | WO2015030173A1 (en) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20170082332A1 (en) * | 2014-05-19 | 2017-03-23 | Mitsubishi Electric Corporation | Air-conditioning apparatus |
US20170198944A1 (en) * | 2014-05-28 | 2017-07-13 | Daikin Industries, Ltd. | Heat-recovery-type refrigeration apparatus |
US20220214055A1 (en) * | 2019-07-10 | 2022-07-07 | Mitsubishi Electric Corporation | Outdoor unit and air-conditioning apparatus |
US20220307745A1 (en) * | 2019-09-11 | 2022-09-29 | Gd Midea Air-Conditioning Equipment Co., Ltd. | Air conditioner and control method therefor |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP6700070B2 (en) * | 2016-03-04 | 2020-05-27 | 高砂熱学工業株式会社 | Water-to-steam heat exchange system and its operating method |
KR102478547B1 (en) | 2016-08-26 | 2022-12-16 | 이너테크 아이피 엘엘씨 | Cooling system and method using a flat tube heat exchanger with single-phase fluid and counterflow circuits |
CN107023948B (en) * | 2017-04-01 | 2020-05-29 | 青岛海尔空调器有限总公司 | Air conditioner and non-stop defrosting operation method thereof |
JP7185158B1 (en) * | 2021-10-07 | 2022-12-07 | ダイキン工業株式会社 | Heat source unit and air conditioner |
JP7260810B1 (en) * | 2021-10-07 | 2023-04-19 | ダイキン工業株式会社 | Heat source unit and air conditioner |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2001141379A (en) * | 1999-11-11 | 2001-05-25 | Showa Alum Corp | Compound heat exchanger |
JP2008249236A (en) * | 2007-03-30 | 2008-10-16 | Mitsubishi Electric Corp | Air conditioner |
US20100170295A1 (en) * | 2007-05-25 | 2010-07-08 | Mitsubishi Electric Corporation | Refrigeration cycle device |
US20120118533A1 (en) * | 2010-11-15 | 2012-05-17 | Lg Electronics Inc. | Air conditioner |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0464879A (en) * | 1990-07-04 | 1992-02-28 | Hitachi Ltd | Condenser |
JPH05332637A (en) * | 1992-05-29 | 1993-12-14 | Sanyo Electric Co Ltd | Air conditioner |
KR100348710B1 (en) * | 2000-04-17 | 2002-08-13 | 한국기계연구원 | Modular multi-pass multi-row flat tube evaporator |
WO2004025207A1 (en) * | 2002-09-10 | 2004-03-25 | Gac Corporation | Heat exchanger and method of producing the same |
JP4315714B2 (en) * | 2003-03-19 | 2009-08-19 | 三洋電機株式会社 | Air conditioning system and control method of air conditioning system |
CN101203720A (en) * | 2005-03-18 | 2008-06-18 | 开利商业冷藏公司 | Accumulator integration with exchanger header |
KR101282565B1 (en) * | 2006-07-29 | 2013-07-04 | 엘지전자 주식회사 | Multi-type air conditioner for cooling/heating the same time |
US20110056668A1 (en) * | 2008-04-29 | 2011-03-10 | Carrier Corporation | Modular heat exchanger |
-
2013
- 2013-09-02 JP JP2013181493A patent/JP5772904B2/en active Active
-
2014
- 2014-08-29 US US14/915,018 patent/US20160209084A1/en not_active Abandoned
- 2014-08-29 CN CN201480048228.6A patent/CN105492833A/en active Pending
- 2014-08-29 WO PCT/JP2014/072737 patent/WO2015030173A1/en active Application Filing
- 2014-08-29 AU AU2014312825A patent/AU2014312825B2/en active Active
- 2014-08-29 EP EP14839831.6A patent/EP3026355B1/en active Active
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2001141379A (en) * | 1999-11-11 | 2001-05-25 | Showa Alum Corp | Compound heat exchanger |
JP2008249236A (en) * | 2007-03-30 | 2008-10-16 | Mitsubishi Electric Corp | Air conditioner |
US20100170295A1 (en) * | 2007-05-25 | 2010-07-08 | Mitsubishi Electric Corporation | Refrigeration cycle device |
US20120118533A1 (en) * | 2010-11-15 | 2012-05-17 | Lg Electronics Inc. | Air conditioner |
Non-Patent Citations (1)
Title |
---|
Nagae JP H05-332637, IDS * |
Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20170082332A1 (en) * | 2014-05-19 | 2017-03-23 | Mitsubishi Electric Corporation | Air-conditioning apparatus |
US10976085B2 (en) * | 2014-05-19 | 2021-04-13 | Mitsubishi Electric Corporation | Air-conditioning apparatus |
US20170198944A1 (en) * | 2014-05-28 | 2017-07-13 | Daikin Industries, Ltd. | Heat-recovery-type refrigeration apparatus |
US9939180B2 (en) * | 2014-05-28 | 2018-04-10 | Daikin Industries, Ltd. | Heat-recovery-type refrigeration apparatus |
US20220214055A1 (en) * | 2019-07-10 | 2022-07-07 | Mitsubishi Electric Corporation | Outdoor unit and air-conditioning apparatus |
US11994306B2 (en) * | 2019-07-10 | 2024-05-28 | Mitsubishi Electric Corporation | Outdoor unit and air-conditioning apparatus |
US20220307745A1 (en) * | 2019-09-11 | 2022-09-29 | Gd Midea Air-Conditioning Equipment Co., Ltd. | Air conditioner and control method therefor |
Also Published As
Publication number | Publication date |
---|---|
WO2015030173A1 (en) | 2015-03-05 |
JP5772904B2 (en) | 2015-09-02 |
EP3026355A1 (en) | 2016-06-01 |
EP3026355B1 (en) | 2020-11-18 |
JP2015049000A (en) | 2015-03-16 |
AU2014312825B2 (en) | 2017-01-05 |
EP3026355A4 (en) | 2016-12-21 |
AU2014312825A1 (en) | 2016-04-28 |
CN105492833A (en) | 2016-04-13 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US20160209084A1 (en) | Heat recovery refrigeration device | |
US20180340700A1 (en) | Variable refrigerant flow system | |
US10760832B2 (en) | Air-conditioning apparatus | |
US9784481B2 (en) | Heat-recovery-type refrigerating apparatus | |
US11199342B2 (en) | Air conditioner | |
CN108195099B (en) | Variable frequency multi-split air conditioner and control method thereof | |
US20060090487A1 (en) | Air conditioner | |
US11268737B2 (en) | Refrigeration cycle apparatus | |
US11022354B2 (en) | Air conditioner | |
US10480837B2 (en) | Refrigeration apparatus | |
JP6123289B2 (en) | Air conditioning system | |
WO2015182484A1 (en) | Freezer device | |
WO2021106793A1 (en) | Refrigerant cycle system | |
US20220243990A1 (en) | Heat exchanger | |
KR20190081837A (en) | air-conditioning system | |
JP2018096575A (en) | Freezer | |
JP5839084B2 (en) | Refrigeration equipment | |
WO2021014520A1 (en) | Air-conditioning device | |
JP2017142027A (en) | Air conditioning device | |
JP2014126289A (en) | Air conditioning system | |
KR101622225B1 (en) | Air conditioner | |
CN107631515A (en) | Heat pump air conditioner unit | |
WO2023166558A1 (en) | Air conditioning device | |
JP4895891B2 (en) | Air conditioner | |
JP2021085542A (en) | Refrigerant cycle system |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: DAIKIN INDUSTRIES, LTD., JAPAN Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:KAWANO, SATOSHI;TAKEUCHI, TOMOHISA;KIMURA, SAYAKO;AND OTHERS;SIGNING DATES FROM 20141009 TO 20141010;REEL/FRAME:037842/0328 |
|
STPP | Information on status: patent application and granting procedure in general |
Free format text: FINAL REJECTION MAILED |
|
STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |