WO2006003967A1 - 空気調和装置 - Google Patents
空気調和装置 Download PDFInfo
- Publication number
- WO2006003967A1 WO2006003967A1 PCT/JP2005/012029 JP2005012029W WO2006003967A1 WO 2006003967 A1 WO2006003967 A1 WO 2006003967A1 JP 2005012029 W JP2005012029 W JP 2005012029W WO 2006003967 A1 WO2006003967 A1 WO 2006003967A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- refrigerant
- heat source
- source side
- circuit
- heat exchanger
- Prior art date
Links
- 239000003507 refrigerant Substances 0.000 claims abstract description 627
- 230000006835 compression Effects 0.000 claims abstract description 101
- 238000007906 compression Methods 0.000 claims abstract description 101
- 238000001816 cooling Methods 0.000 claims description 99
- 239000003921 oil Substances 0.000 claims description 96
- 230000006870 function Effects 0.000 claims description 59
- 239000010721 machine oil Substances 0.000 claims description 46
- 238000004378 air conditioning Methods 0.000 claims description 38
- 238000005057 refrigeration Methods 0.000 claims description 29
- 230000005494 condensation Effects 0.000 abstract description 21
- 238000009833 condensation Methods 0.000 abstract description 21
- 239000007788 liquid Substances 0.000 description 89
- 238000001704 evaporation Methods 0.000 description 63
- 238000004891 communication Methods 0.000 description 62
- 230000008020 evaporation Effects 0.000 description 60
- 238000010438 heat treatment Methods 0.000 description 58
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 25
- 238000010586 diagram Methods 0.000 description 15
- 230000004048 modification Effects 0.000 description 13
- 238000012986 modification Methods 0.000 description 13
- 230000005514 two-phase flow Effects 0.000 description 9
- 239000002826 coolant Substances 0.000 description 7
- 230000007423 decrease Effects 0.000 description 7
- 238000004781 supercooling Methods 0.000 description 4
- 230000000903 blocking effect Effects 0.000 description 3
- 239000010726 refrigerant oil Substances 0.000 description 2
- 238000009825 accumulation Methods 0.000 description 1
- 230000006837 decompression Effects 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000012856 packing Methods 0.000 description 1
- 229920005862 polyol Polymers 0.000 description 1
- -1 polyol ester Chemical class 0.000 description 1
- 239000011347 resin Substances 0.000 description 1
- 229920005989 resin Polymers 0.000 description 1
- 239000008400 supply water Substances 0.000 description 1
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
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
- F25B49/027—Condenser control 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
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B13/00—Compression machines, plants or systems, with reversible cycle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
-
- 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
- F25B2313/021—Indoor unit or outdoor unit with auxiliary heat exchanger not forming part of the indoor or outdoor unit
-
- 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
- F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
- F25B2313/02742—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using two four-way valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/13—Economisers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B31/00—Compressor arrangements
- F25B31/002—Lubrication
- F25B31/004—Lubrication oil recirculating arrangements
Definitions
- the present invention relates to an air conditioner, and more particularly to an air conditioner including a heat source side refrigerant circuit and a use side refrigerant circuit connected to the heat source side refrigerant circuit.
- a refrigerant evaporator there is a refrigeration apparatus provided with a vapor compression refrigerant circuit having a heat exchange configured such that a refrigerant flows in a lower force and an upper force flows out (for example, a patent) (Refer to Reference 1.)
- the specific gravity is lower than that of the refrigerant in order to prevent the refrigeration oil from accumulating in the evaporator, so it is separated into two layers and floats above the liquid level of the refrigerant.
- Refrigerating machine oil accumulated in a hot state is extracted near the refrigerant level and returned to the suction side of the compressor.
- a refrigeration apparatus including a vapor compression refrigerant circuit
- vapor compression having a heat source side refrigerant circuit having a plurality of heat source side heat exchanges and a plurality of utilization side refrigerant circuits connected to the heat source side refrigerant circuit.
- the flow rate of the refrigerant flowing into each heat source side heat exchanger can be adjusted. Is provided with a heat source side expansion valve.
- the air conditioning load of the plurality of use side refrigerant circuits as a whole decreases.
- the heat source side expansion valve is controlled to reduce the evaporation capacity by reducing the opening of the heat source side expansion valve.
- Heat source side heat exchange functioning as an evaporator by closing a part of the valve to reduce the evaporation capacity, or by making some of the heat source side heat exchangers function as condensers Control is performed to reduce the evaporation capacity by offsetting the evaporation capacity of the heat exchange on the heat source side that functions as an evaporator.
- the plurality of use side refrigerant circuits As the air conditioning load decreases, the amount of liquid refrigerant that accumulates in the heat source side heat exchanger is increased by reducing the opening of the heat source side expansion valve connected to the heat source side heat exchanger. Control to reduce the condensation capacity by reducing the heat transfer area. However, if control is performed to reduce the opening of the heat source side expansion valve, the refrigerant pressure on the downstream side of the heat source side expansion valve (specifically, between the heat source side expansion valve and the use side refrigerant circuit) tends to decrease.
- Patent Document 1 Japanese Patent Application Laid-Open No. 63-204074
- Patent Document 2 JP-A-3-260561
- Patent Document 3 Japanese Patent Laid-Open No. 3-129259
- the heat exchanger such as a plate heat exchanger configured so that the refrigerant flows in from the lower side and flows out from the upper side when it functions as the refrigerant evaporator
- the heat source side heat exchanger In this case, in order to prevent refrigeration oil from accumulating in the heat source side heat exchanger, it is necessary to maintain the liquid level of the refrigerant in the heat source side heat exchanger at a certain level or higher.
- the opening degree of the heat source side expansion valve Even if an attempt is made to reduce the amount of refrigerant flowing through the heat source side heat exchanger by reducing the size of the heat source side heat exchanger, the opening degree of the heat source side expansion valve is made too small due to the restriction of the coolant level in the heat source side heat exchanger. As a result, it is not possible to sufficiently control the evaporation capacity only by adjusting the opening of the heat source side expansion valve. As a result, some of the heat source side expansion valves are closed to function as an evaporator.
- Heat source side heat exchange that functions as an evaporator by reducing evaporation capacity by reducing the number of heat exchangers, or by making some of the heat source side heat exchanges ⁇ function as condensers Control to reduce the evaporation capacity by offsetting the evaporation capacity It has become necessary. [0005] For this reason, the number of parts is increased and the cost is increased by installing a plurality of heat source side heat exchangers, and a part of the plurality of heat source side heat exchangers functions as a condenser to evaporate capacity.
- the amount of refrigerant compressed in the compressor will increase by the amount of refrigerant condensed in the heat source side heat exchanger, and the air conditioning load force of the entire multiple refrigerant circuits on the usage side S Small operating conditions There is a problem that the cop becomes worse.
- the heat source side heat exchanger when the heat source side heat exchanger is caused to function as a refrigerant condenser by providing a pressure circuit in the refrigerant circuit, the use side refrigerant is decompressed over the heat source side expansion valve.
- the refrigerant sent from the heat source side expansion valve to the user side refrigerant circuit becomes a gas-liquid two-phase flow, and the force is also on the heat source side.
- the opening of the expansion valve decreases, the gas fraction of the refrigerant after the high-pressure gas refrigerant is merged from the pressurization circuit increases, and drift occurs between the multiple use-side refrigerant circuits.
- the opening degree of the heat source side expansion valve cannot be made sufficiently small.
- the number of parts increases and the cost increases due to the installation of multiple heat source side heat exchangers, and a part of the multiple heat source side heat exchangers function as an evaporator to reduce the condensation capacity.
- the amount of refrigerant compressed in the compressor is increased by the amount of refrigerant evaporated in the heat source side heat exchanger. There is a problem of getting worse.
- An object of the present invention is to provide an air conditioner having a heat source side refrigerant circuit and a utilization side refrigerant circuit connected to the heat source side refrigerant circuit, and to condense the condensing capacity of the heat source side heat exchanger to the heat source side expansion valve.
- the purpose of this is to expand the control range at the time of control.
- An air conditioner includes a heat source side refrigerant circuit and one or more use side refrigerant circuits.
- a path, a pressure circuit, and a cooler are provided.
- the heat source side refrigerant circuit is a heat source side expansion that depressurizes the refrigerant condensed in the heat source side heat exchanger when the compression mechanism, the heat source side heat exchanger, and the heat source side heat exchanger function as a condenser.
- the use side refrigerant circuit is connected to the heat source side refrigerant circuit, and is configured by connecting the use side heat exchanger and the use side expansion valve.
- the pressurization circuit is provided in the heat source side refrigerant circuit and is connected to the compression mechanism.
- the high-pressure gas refrigerant compressed in the V direction is combined with the refrigerant that is depressurized and sent to the use-side refrigerant circuit through the heat source side expansion valve.
- the cooler cools the refrigerant that is decompressed in the heat source side expansion valve and sent to the use side refrigerant circuit.
- the opening degree of the heat source side expansion valve cannot be made sufficiently small, in this air conditioner, the refrigerant that is decompressed by the heat source side expansion valve and sent to the use side refrigerant circuit is cooled by the cooler. Therefore, the gas refrigerant can be condensed, and it is not necessary to send a gas-liquid two-phase flow refrigerant having a large gas fraction to the use-side refrigerant circuit.
- control is performed to reduce the condensation capacity of the heat source side heat exchanger by reducing the opening of the heat source side expansion valve in accordance with the air conditioning load of the use side refrigerant circuit, and the pressurizing circuit Even if control is performed by combining high-pressure gas refrigerant and pressurizing, it is not necessary to send a gas-liquid two-phase flow refrigerant with a large gas fraction to the use-side refrigerant circuit. It is possible to expand the control range when the capacity is controlled by the heat source side expansion valve.
- An air conditioner according to a second aspect of the present invention is the air conditioner according to the first aspect of the present invention, wherein the pressurizing circuit is configured so that the high-pressure gas refrigerant merges between the heat source side expansion valve and the cooler. It is connected.
- the pressurization circuit is connected so that the high-pressure gas refrigerant joins between the heat source side expansion valve and the cooler! Therefore, the refrigerant whose temperature has been increased due to the merge of the high-pressure gas refrigerant is cooled by the cooler.
- a relatively high temperature cold heat source that does not require the use of a low temperature cold heat source can be used as the cold heat source for cooling the refrigerant in the cooler.
- An air conditioner according to a third invention is the air conditioner according to the first or second invention, wherein a part of the refrigerant sent from the heat source side heat exchanger to the utilization side refrigerant circuit is obtained.
- the heat source side refrigerant circuit is branched and introduced into the cooler, the refrigerant is reduced in pressure at the heat source side expansion valve and cooled to the use side refrigerant circuit, and then returned to the suction side of the compression mechanism.
- a cooling circuit connected to the heat source side refrigerant circuit.
- a part of the refrigerant sent from the heat source side heat exchanger to the utilization side refrigerant circuit is decompressed to a refrigerant pressure that can be returned to the suction side of the compression mechanism, and used as a cooling source for the cooler. Therefore, it is possible to obtain a cooling source having a temperature sufficiently lower than the temperature of the refrigerant that is decompressed by the heat source side expansion valve and sent to the use side refrigerant circuit. This one Thus, it is possible to cool the refrigerant that has been decompressed to the heat source side expansion valve and sent to the use side refrigerant circuit to the supercooled state.
- An air conditioner according to a fourth invention is the air conditioner according to the first to third inventions, wherein the heat source side heat exchange is configured such that the refrigerant flows in both the lower force and the upper force. It is possible to function as an evaporator.
- the air conditioner uses a combination of refrigerating machine oil and refrigerant that is not separated into two layers within a temperature range of 30 ° C or lower.
- the air conditioner further includes an oil return circuit that is connected to the lower portion of the heat source side heat exchanger and returns the refrigeration oil accumulated in the heat source side heat exchanger to the compression mechanism together with the refrigerant.
- This air conditioner is configured such that when the heat source side heat exchange functions as an evaporator, the refrigerant flows in from the lower side and flows out from the upper side force.
- a combination of refrigerating machine oil and refrigerant is used without separating into two layers.
- the evaporating temperature of the refrigerant in the heat source side heat exchanger is a temperature of 30 ° C. or lower when water or air is used as the heat source.
- the refrigerating machine oil accumulates in the heat source side heat exchanger in a state where it is mixed with the refrigerant that does not accumulate in the state of floating on the liquid level of the refrigerant in the heat source side heat exchanger. Become.
- the refrigerating machine oil accumulated in the heat source side heat exchanger is returned to the suction side of the compression mechanism together with the refrigerant by an oil return circuit connected to the lower part of the heat source side heat exchanger. For this reason, in order to prevent refrigerating machine oil from accumulating in the heat source side heat exchanger as in the conventional air conditioner, the liquid level of the refrigerant in the heat source side heat exchanger is set to a certain level or more. No need to maintain.
- control is performed to reduce the evaporation capability of the heat source side heat exchanger by reducing the opening of the heat source side expansion valve in accordance with the air conditioning load of the use side refrigerant circuit.
- the heat source side heat exchanger can be unified due to the restriction of the control width of the control of the evaporation capacity of the heat source side heat exchanger, which is limited only by the restriction of the control width of the control of the condensation capacity of the heat source side heat exchanger.
- a powerful air conditioner that could not be realized, it was possible to unify the heat source side heat exchange ⁇ , which was generated by installing multiple heat source side heat exchanges in the conventional air conditioner The increase in the number of parts and cost increase can be prevented, and when the air-conditioning load on the use-side refrigerant circuit is small and the COP under operating conditions deteriorates, the problem can be solved.
- FIG. 1 is a schematic refrigerant circuit diagram of an air conditioner according to an embodiment of the present invention.
- FIG. 2 is a diagram showing the overall schematic structure of a heat source side heat exchanger.
- FIG. 3 is an enlarged view of a portion C in FIG. 2, and shows a schematic structure of the lower part of the heat source side heat exchanger.
- FIG. 4 is a schematic refrigerant circuit diagram for explaining the operation of the air-conditioning apparatus in a heating operation mode.
- FIG. 5 is a schematic refrigerant circuit diagram for explaining the operation of the air-conditioning apparatus in a cooling operation mode.
- FIG. 6 is a schematic refrigerant circuit diagram for explaining the operation of the air-conditioning apparatus in the simultaneous heating and cooling operation mode (evaporation load).
- FIG. 7 is a schematic refrigerant circuit diagram for explaining the operation of the air-conditioning apparatus in the simultaneous heating and cooling operation mode (condensing load).
- FIG. 8 is a schematic refrigerant circuit diagram of an air-conditioning apparatus according to Modification 1.
- FIG. 9 is a schematic refrigerant circuit diagram for explaining the operation of the air-conditioning apparatus of Modification 1 in the heating operation mode.
- FIG. 10 is a schematic diagram for explaining the operation of the air-conditioning apparatus of Modification 1 in the cooling operation mode. It is a refrigerant circuit diagram.
- FIG. 11 is a schematic refrigerant circuit diagram of an air-conditioning apparatus according to Modification 2.
- FIG. 12 is a schematic refrigerant circuit diagram of an air-conditioning apparatus according to Modification 3.
- FIG. 13 is a schematic refrigerant circuit diagram of an air-conditioning apparatus according to Modification 4.
- FIG. 14 is a schematic refrigerant circuit diagram of an air-conditioning apparatus according to Modification 4.
- FIG. 1 is a schematic refrigerant circuit diagram of an air-conditioning apparatus 1 according to an embodiment of the present invention.
- the air conditioner 1 is an apparatus used for indoor air conditioning such as a building by performing a vapor compression refrigeration cycle operation.
- the air conditioner 1 is mainly composed of one heat source unit 2 and plural (in this embodiment, three).
- Use units 3, 4, and 5 and connection units 6, 7, and 8 connected to each use unit 3, 4, and 5, and heat source unit 2 and use units 3 and 4 through connection units 6, 7, and 8 , 5 and refrigerant communication pipes 9, 10, and 11, for example, a cooling unit for a certain air-conditioned space and a heating unit for another air-conditioned space.
- the vapor compression refrigerant circuit 12 of the air conditioner 1 of the present embodiment includes a heat source unit 2, utilization units 3, 4, 5, connection units 6, 7, 8, and refrigerant communication pipes 9, 10, 11 is connected.
- the refrigerant circuit 12 of the air conditioner 1 uses a combination of refrigerating machine oil and refrigerant that is not separated into two layers over a temperature range of 30 ° C. or lower. .
- a combination of such a refrigerant and refrigerating machine oil for example, there is a combination of R410A and a polyol ester (POE).
- the combination of refrigerating machine oil and refrigerant that does not separate into two layers in the temperature range of 30 ° C or lower is used when the heat source side heat exchanger 23 (described later) of the heat source unit 2 functions as an evaporator.
- Usage units 3, 4, and 5 are installed in the ceiling of a building or the like by suspending or hanging, or hanging on the wall of the building.
- the utilization units 3, 4, 5 are connected to the heat source unit 2 via the refrigerant communication pipes 9, 10, 11 and the connection units 6, 7, 8, and constitute a part of the refrigerant circuit 12.
- the usage unit 3 mainly constitutes a part of the refrigerant circuit 12, and the usage side refrigerant circuit 1 2a (the usage units 4 and 5 are provided with usage-side refrigerant circuits 12b and 12c, respectively).
- the use side refrigerant circuit 12a mainly includes a use side expansion valve 31 and a use side heat exchange 32.
- the use side expansion valve 31 is an electric expansion valve connected to the liquid side of the use side heat exchanger 32 in order to adjust the flow rate of the refrigerant flowing in the use side refrigerant circuit 12a. is there.
- the use side heat exchanger 32 is a cross-fin type fin 'and' tube type heat exchanger composed of heat transfer tubes and a large number of fins, and exchanges heat between the refrigerant and indoor air. It is a device for performing.
- the utilization unit 3 includes a blower fan (not shown) for supplying indoor air as supply air after sucking indoor air into the unit and exchanging heat. It is possible to exchange heat with the refrigerant flowing through the use side heat exchanger 32.
- the utilization unit 3 is provided with various sensors.
- a liquid side temperature sensor 33 for detecting the temperature of the liquid refrigerant is provided on the liquid side of the use side heat exchanger 32, and a gas side temperature for detecting the temperature of the gas refrigerant is provided on the gas side of the use side heat exchanger 32.
- Sensor 34 is provided.
- the utilization unit 3 is provided with an RA intake temperature sensor 35 for detecting the temperature of indoor air sucked into the unit.
- the usage unit 3 includes a usage-side control unit 36 that controls the operation of each unit constituting the usage unit 3.
- the use-side control unit 36 includes a microcomputer and a memory provided for controlling the use unit 3, and exchanges control signals and the like with a remote controller (not shown). Control signals etc. can be exchanged with the heat source unit 2.
- the heat source unit 2 is installed on the roof of a building, etc., and is connected to the usage units 3, 4, and 5 via the refrigerant communication pipes 9, 10, and 11, and between the usage units 3, 4, and 5,
- the refrigerant circuit 1 2 is configured.
- the heat source unit 2 mainly constitutes a part of the refrigerant circuit 12, and includes a heat source side refrigerant circuit 12d.
- the heat source side refrigerant circuit 10d mainly includes a compression mechanism 21, a first switching mechanism 22, a heat source side heat exchanger 23, a heat source side expansion valve 24, a receiver 25, a second switching mechanism 26, Side closing valve 27, high pressure gas side closing valve 28, low pressure gas side closing valve 29, first oil return circuit 101, pressurizing circuit 111, cooling A rejector 121 and a cooling circuit 122 are provided.
- the compression mechanism 21 mainly includes a compressor 21a, an oil separator 21b connected to the discharge side of the compressor 21a, and a second oil return circuit 2 that connects the oil separator 21b and the suction pipe 21c of the compressor 21a 2 Id.
- the compressor 21a is a positive displacement compressor capable of varying the operating capacity by inverter control.
- the oil separator 21b is a container for separating the refrigerating machine oil accompanying the high-pressure gas refrigerant compressed and discharged in the compressor 21a.
- the second oil return circuit 21d is a circuit for returning the refrigeration oil separated in the oil separator 21b to the compressor 21a.
- the second oil return circuit 21d mainly includes an oil return pipe 21e that connects the oil separator 21b and the suction pipe 21c of the compressor 21a, and a high pressure separated in the oil separator 21b that is connected to the oil return pipe 21e. And a capillary tube 21f for reducing the pressure of the refrigerating machine oil.
- the capillary tube 21f is a thin tube that depressurizes the high-pressure refrigeration oil separated in the oil separator 21b to the refrigerant pressure on the suction side of the compressor 21a.
- the compression mechanism 21 has only one compressor 21a as a compressor, but is not limited to this, and two or more compressors are connected in parallel according to the number of connected units. It may have been done.
- the first shelf structure 22 connects the discharge side of the compression mechanism 21 and the gas side of the heat source side heat exchanger 23 when the heat source side heat exchanger 23 functions as a condenser (hereinafter referred to as a condensation operation state).
- a condensation operation state When the heat source side heat exchanger 23 functions as an evaporator (hereinafter referred to as the evaporation operation state), the heat source side heat exchanger 23 is connected to the suction side of the compression mechanism 21 and the gas side of the heat source side heat exchanger 23.
- This is a four-way switching valve capable of switching the refrigerant flow path in the refrigerant circuit 12d, and its first port 22a is connected to the discharge side of the compression mechanism 21, and its second port 22b is on the heat source side.
- the first switching mechanism 22 connects the first port 22a and the second port 22b, and connects the third port 22c and the fourth port 22d (corresponding to the condensed operation state, (Refer to the solid line of the first structure 22 in Fig. 1), or connect the second port 22b and the third port 22c, and connect the first port 22c and the fourth port 22d (corresponding to the evaporation operation state) (Refer to the broken line in the first structure 22 in Fig. 1). It is.
- the heat source side heat exchanger 23 is a heat exchanger that can function as a refrigerant evaporator and a refrigerant condenser.
- the heat exchanger 23 uses a water as a heat source to exchange heat with the refrigerant. Heat exchanger.
- the gas side of the heat source side heat exchanger 23 is connected to the second port 22b of the first switching mechanism 22, and the liquid side is connected to the heat source side expansion valve 24.
- the heat source side heat exchanger 23 is formed by stacking a plurality of plate members 23a formed by a press cage or the like via a packing (not shown).
- a plurality of channels 23b and 23c extending in the vertical direction are formed in the plurality of channels, and refrigerant and water flow alternately in the channels 23b and 23c (specifically, the refrigerant flows in the channel 23b). Heat is exchanged by water flowing in the flow path 23c (see arrows A and B in FIG. 2).
- the plurality of flow paths 23b are in communication with each other at the upper end portion and the lower end portion thereof, and are connected to the gas side nozzle 23d and the liquid side nozzle 23e provided at the upper and lower portions of the heat source side heat exchange. ing.
- the gas side nozzle 23d is connected to the first structure 22, and the liquid side nozzle 23e is connected to the heat source side expansion valve 24.
- the heat source side heat exchanger 23 functions as an evaporator
- the refrigerant flows in from the liquid side nozzle 23e (ie, the lower side) and out of the gas side nozzle 23d (ie, the upper side).
- the heat source side heat exchanger 23 functions as a condenser
- the plurality of flow paths 23c are connected to each other at the upper end and the lower end, and are connected to the water inlet nozzle 23f and the water outlet nozzle 23g provided at the upper and lower portions of the heat source side heat exchanger 23. Has been.
- the water as the heat source is the water in the heat source side heat exchanger 23 through the water pipe (not shown) of the chilled water tower equipment and the boiler equipment power installed outside the air conditioner 1.
- the water pipe not shown
- the water outlet nozzle 23g After flowing in as supply water CWS from the inlet nozzle 23f and exchanging heat with the refrigerant, it flows out from the water outlet nozzle 23g and returned to the chilled water tower equipment and boiler equipment as discharged water CWR.
- a certain amount of water supplied from the cold water tower equipment or boiler equipment is supplied regardless of the flow rate of the refrigerant flowing in the heat source side heat exchanger 23.
- the heat source side expansion valve 24 is connected to the heat source side heat via the liquid refrigerant communication pipe 9 in the present embodiment.
- This is an electric expansion valve capable of adjusting the flow rate of the refrigerant flowing between the exchanger 23 and the use side refrigerant circuits 12a, 12b, and 12c, and is connected to the liquid side of the heat source side heat exchange.
- the receiver 25 is a container for temporarily storing the refrigerant flowing between the heat source side heat exchanger 23 and the use side refrigerant circuits 12a, 12b, and 12c. In the present embodiment, the receiver 25 is connected between the heat source side expansion valve 24 and the cooler 121.
- the second Kiriura structure 26 is used when the heat source unit 2 is used as a heat source unit for a cooling and heating simultaneous machine (see FIGS. 4 to 7), and a high-pressure gas refrigerant is sent to the use-side refrigerant circuits 12a, 12b, and 12c. (Hereinafter referred to as the heating load required operation state)
- the heat source unit 2 is used as a heat source unit for a cooling / heating switching machine (deformation) (Refer to Example 1, Figs.
- cooling operation state when switching between cooling and heating connects the high pressure gas side shut-off valve 28 and the suction side of the compression mechanism 21 to each other.
- it is a four-way switching valve capable of switching the refrigerant flow path in the heat source side refrigerant circuit 12d, and its first port 26a is connected to the discharge side of the compression mechanism 21, and its second port 26b is It is connected to the suction side of the compression mechanism 21 via a capillary tube 92.
- Its third port 26c is connected to the intake side of the compression mechanism 21, the fourth port 2 6d is connected to the high-pressure gas closing valve 28.
- the second mechanism 26 connects the first port 26a and the second port 26b, and also connects the third port 26c and the fourth port 26d (corresponding to the cooling operation state during cooling / heating switching). 1) (Refer to the solid line of the second switching mechanism 26 in FIG. 1), connect the second port 26b and the third port 26c, and connect the first port 26a and the fourth port 26d (heating load demand operation) It is possible to perform switching that corresponds to the state (see the broken line of the second switching mechanism 26 in FIG. 1).
- the liquid side shut-off valve 27, high-pressure gas side shut-off valve 28, and low-pressure gas side shut-off valve 29 are valves provided at the connection port with external equipment and piping (specifically, refrigerant communication piping 9, 10, and 11). It is.
- the liquid side closing valve 27 is connected to the cooler 121.
- the high pressure gas side closing valve 28 is connected to the fourth port 26 d of the second structure 26.
- the low pressure gas side closing valve 29 is connected to the suction side of the compression mechanism 21.
- the first oil return circuit 101 compresses the refrigerating machine oil accumulated in the heat source side heat exchanger 23 together with the refrigerant in the evaporation operation state, that is, when the heat source side heat exchanger 23 functions as an evaporator.
- This is a circuit that returns to mechanism 21.
- the first oil return circuit 101 mainly includes an oil return pipe 101a connecting the lower part of the heat source side heat exchanger 23 and the compression mechanism 21, an on-off valve 101b connected to the oil return pipe 101a, and a check valve 101c. And a cylindrical tube lOld.
- the oil return pipe 101a is provided at one end so that the lower force of the heat source side heat exchange can also extract the refrigerating machine oil together with the refrigerant. In this embodiment, as shown in FIG.
- the heat source side heat exchange is performed.
- This is a pipe that extends to the inside of the flow path 23b through which the refrigerant of the heat source side heat exchanger 23 flows through the pipe of the liquid side nozzle 23e provided in the lower part of the vessel 23.
- a communication hole 23h is provided in each plate member 23a (the same applies to the plurality of flow paths 23c).
- the oil return pipe 101a may be provided so as to penetrate the plurality of flow paths 23b (see the oil return pipe 101a indicated by the broken line in FIG. 3).
- the other end of the oil return pipe 101a is connected to the suction side of the compression mechanism 21 in this embodiment.
- the on-off valve 101b is connected so that the first oil return circuit 101 can be used as necessary, and is an electromagnetic valve capable of circulating and blocking refrigerant and refrigerating machine oil.
- the check valve 101c is a valve that allows only the lower force of the heat source side heat exchanger 23 and the lower force of the heat source side heat exchanger 23 to flow in the oil return pipe 101a toward the suction side of the compression mechanism 21.
- the capillary tube 101d is a thin tube that depressurizes the refrigerant and refrigerating machine oil extracted from the lower part of the heat source side heat exchanger 23 to the refrigerant pressure on the suction side of the compression mechanism 21.
- the pressure circuit 111 condenses the high-pressure gas refrigerant compressed in the compression mechanism 21 in the heat source side heat exchanger 23.
- This is a circuit that joins the refrigerant sent to the use side refrigerant circuits 12a, 12b, 12c after being depressurized in the heat source side expansion valve 24.
- the pressurizing circuit 111 mainly includes a pressurizing pipe 111a that connects the discharge side of the compression mechanism 21 and the downstream side of the heat source side expansion valve 24 (that is, between the heat source side expansion valve 24 and the liquid side closing valve 27), It has an open / close valve 11 lb connected to the pressurizing pipe 111a, a check valve 111c, and a capillary tube 11 Id.
- the calo pressure pipe 11 la is connected at one end between the outlet of the oil separator 21b of the compression mechanism 21 and the first ports 22a and 26a of the first and second structures 22 and 26.
- the other end of the pressurizing pipe 111a is connected between the heat source side expansion valve 24 and the receiver 25 in the present embodiment.
- the on-off valve 11 lb is an electromagnetic valve that is connected so that the pressurization circuit 111 can be used as necessary, and that can flow and shut off the refrigerant.
- the check valve 111c is a valve that only allows the refrigerant to flow in the pressurizing pipe 11la from the discharge side of the compression mechanism 21 toward the downstream side of the heat source side expansion valve 24.
- the capillary tube 11 Id is a thin tube that depressurizes the refrigerant extracted from the discharge side of the compression mechanism 21 to the refrigerant pressure downstream of the heat source side expansion valve 24.
- the cooler 121 In the condensing operation state, that is, when the heat source side heat exchanger 23 functions as a condenser, the cooler 121 is condensed in the heat source side heat exchange and then depressurized in the heat source side expansion valve 24 to be used side refrigerant circuit
- This is a heat exchanger that cools the refrigerant sent to 12a, 12b, and 12c.
- the cooler 121 is connected between the receiver 25 and the liquid side closing valve 27.
- the pressurization pipe 111a is connected between the heat source side expansion valve 24 and the cooler 121 so that the high-pressure gas refrigerant merges with the refrigerant depressurized in the heat source side expansion valve 24. It is connected to the.
- a double-pipe heat exchanger can be used as the cooler 121.
- the cooling circuit 122 When the cooling circuit 122 is in a condensing operation state, that is, when the heat source side heat exchanger 23 functions as a condenser, a part of the refrigerant sent from the heat source side heat exchange to the use side refrigerant circuits 12a, 12b, 12c is used as the heat source. Branched from the side refrigerant circuit 12d, introduced into the cooler 121, condensed in the heat source side heat exchanger 23, depressurized in the heat source side expansion valve 24, and sent to the usage side refrigerant circuits 12a, 12b, 12c This is a circuit connected to the heat source side refrigerant circuit 12d so as to return to the suction side of the compression mechanism 21 after the refrigerant to be cooled.
- the cooling circuit 122 mainly includes an introduction pipe 122a for introducing a part of the refrigerant sent from the heat source side heat exchanger 23 to the use side refrigerant circuits 12a, 12b, and 12c into the cooler 121, and a cooling connected to the introduction pipe 122a.
- a circuit side expansion valve 122b and a lead-out pipe 122c for returning the refrigerant that has passed through the cooler 121 to the suction side of the compression mechanism 21 are provided.
- one end of the introduction pipe 122 a is connected between the receiver 25 and the cooler 121.
- the other end of the introduction pipe 122a is connected to the inlet of the cooler 121 on the cooling circuit 122 side in this embodiment.
- the cooling circuit side expansion valve 122b is connected so that the cooling circuit 122 can be used as necessary, and the electric circuit capable of adjusting the flow rate of the refrigerant flowing through the cooling circuit 122. expansion It is a valve.
- one end of the outlet tube 122c is connected to the outlet of the cooler 121 on the cooling circuit 122 side.
- the other end of the outlet pipe 122c is connected to the suction side of the compression mechanism 21.
- the heat source unit 2 is provided with various sensors. Specifically, the heat source unit 2 includes a suction pressure sensor 93 that detects a suction pressure of the compression mechanism 21, a discharge pressure sensor 94 that detects a discharge pressure of the compression mechanism 21, and a discharge side of the compression mechanism 21. A discharge temperature sensor 95 for detecting the discharge temperature of the refrigerant and a cooling circuit outlet temperature sensor 96 for detecting the temperature of the refrigerant flowing through the outlet pipe 122c of the cooling circuit 122 are provided. Further, the heat source unit 2 includes a heat source side control unit 97 that controls the operation of each part constituting the heat source unit 2. The heat source side control unit 97 has a microcomputer memory provided for controlling the heat source unit 2, and uses side control units 36, 46, 46 of the usage units 3, 4, 5. Control signal etc. can be exchanged with 56! /.
- Connection units 6, 7, and 8 are installed indoors, such as in buildings, along with usage units 3, 4, and 5.
- the connection units 6, 7, 8 are interposed between the use units 3, 4, 5 and the heat source unit 2 together with the refrigerant communication pipes 9, 10, 11, and constitute a part of the refrigerant circuit 12,
- the connection units 6, 7, 8 are interposed between the use units 3, 4, 5 and the heat source unit 2 together with the refrigerant communication pipes 9, 10, 11, and constitute a part of the refrigerant circuit 12, The
- connection unit 6 and the connection units 7 and 8 have the same configuration, only the configuration of the connection unit 6 will be described here, and the configuration of the connection units 7 and 8 will be described respectively.
- Symbols in the 70's or 80's are attached instead of the symbols in the 60's indicating each part of 6 and the explanation of each part is omitted.
- the connection unit 6 mainly constitutes a part of the refrigerant circuit 12, and includes a connection side refrigerant circuit 12e (in the connection units 7 and 8, connection side refrigerant circuits 12f and 12g, respectively).
- the connection-side refrigerant circuit 12e mainly includes a liquid connection pipe 61, a gas connection pipe 62, a high pressure gas on / off valve 66, and a low pressure gas on / off valve 67.
- the liquid connection pipe 61 connects the liquid refrigerant communication pipe 9 and the use side expansion valve 31 of the use side refrigerant circuit 12a.
- the gas connection pipe 62 includes a high pressure gas connection pipe 63 connected to the high pressure gas refrigerant communication pipe 10, a low pressure gas connection pipe 64 connected to the low pressure gas refrigerant communication pipe 11, and a high pressure gas connection pipe 63. It has a confluence gas connection pipe 65 that joins the pipe 64 and has one stroke. Merged gas The connection pipe 65 is connected to the gas side of the use side heat exchange of the use side refrigerant circuit 12a.
- the high-pressure gas on-off valve 66 is connected to the high-pressure gas connection pipe 63 and is an electromagnetic valve capable of circulating and blocking the refrigerant.
- the low-pressure gas on-off valve 67 is connected to the low-pressure gas connection pipe 64 and is an electromagnetic valve capable of circulating and blocking the refrigerant.
- the connection unit 6 closes the high-pressure gas on-off valve 66 and opens the low-pressure gas on-off valve 67, and then connects the liquid through the liquid refrigerant communication pipe 9.
- connection pipe 61 The refrigerant flowing into the connection pipe 61 is sent to the use-side expansion valve 31 of the use-side refrigerant circuit 12a, decompressed by the use-side expansion valve 31, and evaporated in the use-side heat exchange, and then the combined gas connection pipe 65 and the low-pressure gas It can function to return to the low-pressure gas refrigerant communication pipe 11 through the connection pipe 64.
- the connection unit 6 closes the low pressure gas on / off valve 67 and opens the high pressure gas on / off valve 66, and opens the high pressure gas through the high pressure gas refrigerant communication pipe 10.
- connection unit 6 includes a connection-side control unit 68 that controls the operation of each unit constituting the connection unit 6.
- the connection side control unit 68 includes a microcomputer and a memory provided for controlling the connection unit 6, and exchanges control signals and the like with the use side control unit 36 of the use unit 3. Now that you can do that!
- the use side refrigerant circuits 12a, 12b, and 12c, the heat source side refrigerant circuit 12d, the refrigerant communication pipes 9, 10, and 11 and the connection side refrigerant circuits 12e, 12f, and 12g are connected, and the air The refrigerant circuit 12 of the harmony device 1 is configured.
- the air conditioner 1 of the present embodiment for example, it is possible to perform a so-called cooling / heating simultaneous operation such that the usage units 3 and 4 perform a cooling operation while the usage unit 5 performs a heating operation. Yes.
- the heat source side heat exchanger 23 when the heat source side heat exchanger 23 is caused to function as an evaporator, the first oil return circuit 101 is used, whereby the heat source side heat exchanger 23
- the range of control when the evaporation capacity is controlled by the heat source side expansion valve 24 has been expanded, and a wide range of evaporation capacity can be controlled by a single heat source side heat exchange. I can do it.
- the pressurization circuit 111 and the cooler 121 are used so that the heat source side heat exchanger 23
- the control range when the condensing capacity is controlled by the heat source side expansion valve 24 has been expanded, and a wide control range of the condensing capacity can be obtained by the single heat source side heat exchanger 23.
- the operation mode of the air conditioner 1 of the present embodiment includes a heating operation mode in which all the usage units 3, 4, and 5 are heated according to the air conditioning load of each usage unit 3, 4, and 5, and a usage unit 3 , 4 and 5 can be divided into a cooling operation mode in which the cooling operation is performed and a cooling and heating simultaneous operation mode in which some of the usage units 3, 4, and 5 perform the cooling operation while the other usage units perform the heating operation. it can.
- the operation mode can be divided into the operation mode (condensation operation state) when the heat source side heat exchanger 23 of the heat source unit 2 is operated as a condenser.
- the refrigerant circuit 12 of the air conditioner 1 is configured as shown in FIG. 4 (the refrigerant flow is attached to the refrigerant circuit 12 of FIG. 4). (See the arrow marked.) Specifically, in the heat source side refrigerant circuit 12d of the heat source unit 2, the first switching mechanism 22 is switched to the evaporation operation state (the state indicated by the broken line of the first switching mechanism 22 in FIG. 4), and the second switching mechanism By switching 26 to the heating load required operation state (the state indicated by the broken line of the second switching mechanism 26 in Fig.
- the heat source side heat exchange 23 functions as an evaporator and the high pressure gas refrigerant communication
- the high-pressure gas refrigerant compressed and discharged by the compression mechanism 21 can be supplied to the utilization units 3, 4, and 5 through the pipe 10! /.
- the opening degree of the heat source side expansion valve 24 is adjusted so as to depressurize the refrigerant.
- the on-off valve 111b of the pressurizing circuit 111 and the cooling circuit side expansion valve 122b of the cooling circuit 122 are closed, and a high-pressure gas refrigerant is combined with the refrigerant flowing between the heat source side expansion valve 24 and the receiver 25.
- connection units 6, 7, and 8 use side heat of usage units 3, 4, and 5 by closing low pressure gas on / off valves 67, 77, and 87 and opening high pressure gas on / off valves 66, 76, and 86
- the exchangers 32, 42 and 52 are in a state of functioning as a condenser.
- the usage side expansion valves 31, 41, and 51 are, for example, the degree of supercooling of the usage side heat exchangers 32, 42, and 52 (specifically, the liquid side temperature sensor 33, Opening according to the heating load of each usage unit, such as adjusting the opening based on the temperature difference between the refrigerant temperature detected by 43 and 53 and the refrigerant temperature detected by gas side temperature sensors 34, 44 and 54) The degree is adjusted.
- the high-pressure gas refrigerant compressed and discharged by the compressor 21a of the compression mechanism 21 is supplied to the high-pressure gas refrigerant in the oil separator 21b. Most of them are separated and sent to the second structure 26.
- the refrigerating machine oil separated in the oil separator 21b is returned to the suction side of the compressor 21a through the second oil return circuit 21d.
- the high-pressure gas refrigerant sent to the second structure 26 is sent to the high-pressure gas refrigerant communication pipe 10 through the first port 26a and the fourth port 26d of the second structure 26 and the high-pressure gas side closing valve 28.
- the high-pressure gas refrigerant sent to the high-pressure gas refrigerant communication pipe 10 is branched into three and sent to the high-pressure gas connection pipes 63, 73, 83 of the connection units 6, 7, 8.
- the high-pressure gas refrigerant sent to the high-pressure gas connection pipes 63, 73, 83 of the connection units 6, 7, 8 passes through the high-pressure gas on / off valves 66, 76, 86 and the merging gas connection pipes 65, 75, 85.
- Units 3, 4, and 5 are sent to the IJ side heat exchanger ⁇ 32, 42, 52.
- the high-pressure gas refrigerant sent to the use side heat exchangers 32, 42, 52 is heated with indoor air in the use side heat exchange ⁇ 32, 42, 52 of the use units 3, 4, 5 It is condensed by exchanging. On the other hand, indoor air is heated and supplied indoors.
- the refrigerant condensed in the use side heat exchangers 32, 42, 52 passes through the use side expansion valves 31, 41, 51. , Sent to the liquid connection pipes 61, 71, 81 of the connection units 6, 7, 8.
- the refrigerant sent to the liquid connection pipes 61, 71, 81 is sent to the liquid refrigerant communication pipe 9 to join.
- the refrigerant sent to the liquid refrigerant communication pipe 9 and joined together is sent to the receiver 25 through the liquid side closing valve 27 and the cooler 121 of the heat source unit 2.
- the refrigerant sent to the receiver 25 is temporarily stored in the receiver 25 and then decompressed by the heat source side expansion valve 24.
- the refrigerant decompressed by the heat source side expansion valve 24 is evaporated by exchanging heat with water as a heat source in the heat source side heat exchanger 23 to become a low-pressure gas refrigerant. Sent.
- the low-pressure gas refrigerant sent to the first mechanism 22 is returned to the suction side of the compression mechanism 21 through the second port 22b and the third port 22c of the first switching mechanism 22. In this way, the operation in the heating operation mode is performed.
- the heating load of each of the utilization units 3, 4, and 5 may be very small.
- the refrigerant evaporation capacity in the heat source side heat exchange 23 of the heat source unit 2 is reduced, and the heating load of the entire usage units 3, 4, 5 (that is, the usage side heat exchangers 32, 42, Must be balanced with a condensing load of 52).
- control is performed to reduce the evaporation amount of the refrigerant in the heat source side heat exchange by controlling the opening degree of the heat source side expansion valve 24 to be small.
- the control for reducing the opening degree of the heat source side expansion valve 24 is performed, the liquid level of the refrigerant in the heat source side heat exchanger is lowered.
- the heat exchange is configured such that the refrigerant flows in both the lower force and the upper force (see FIGS. 2 and 2). 3)), the refrigeration oil becomes difficult to be discharged together with the evaporated refrigerant, and the refrigeration oil is likely to accumulate.
- the air conditioning apparatus 1 of the present embodiment a combination of refrigerating machine oil and refrigerant that do not separate into two layers in a temperature range of 30 ° C or lower is used, and the first oil return circuit 101 is provided. .
- the on-off valve 101b of the first oil return circuit 101 is opened in the heating operation mode (that is, when the first Kuraura structure 22 is in the evaporation operation state), and the oil return pipe 101a.
- Refrigerator oil can be extracted from the heat source side heat exchanger through the heat source side heat exchanger 23 together with the refrigerant and returned to the compression mechanism 21 through the heat source side heat exchanger. Yes.
- the on-off valve 101b is opened when the heat source side heat exchanger 23 functions as a condenser, a part of the refrigerant condensed in the heat source side heat exchanger 23 is returned to the compression mechanism 21. Since the amount of refrigerant sent to the use-side refrigerant circuits 12a, 12b, and 12c decreases, the first switching mechanism 22 is closed when the first switching mechanism 22 is in the condensation operation state, and the first switching mechanism 22 is in the evaporation operation state.
- the liquid level of the refrigerant in the heat source side heat exchanger is reduced by performing control to reduce the opening degree of the heat source side expansion valve 24, It may be opened only when the refrigeration oil is accompanied by the evaporated refrigerant and is not easily discharged.
- the heat source side expansion valve 24 is not more than a predetermined opening.
- This predetermined opening degree is the opening degree of the heat source side expansion valve 24 in which the liquid level of the cooling medium in the heat source side heat exchanger 23 is lowered and the refrigerant oil is not easily discharged together with the evaporated refrigerant. Is determined experimentally and is determined based on the opening found experimentally.
- the refrigerant circuit 12 of the air conditioner 1 is configured as shown in FIG. 5 (the refrigerant flow is attached to the refrigerant circuit 12 of FIG. 5). (See the arrow marked.)
- the first switching mechanism 22 is switched to the condensation operation state (the state indicated by the solid line of the first switching mechanism 22 in FIG. 5), thereby Heat exchange is functioning as a condenser.
- the heat source side expansion valve 24 is in an opened state.
- connection units 6, 7, and 8 the high pressure gas on / off valves 66, 76, and 86 are closed and the low pressure gas on / off valve 6
- the usage side heat exchangers 32, 42, 5 2 of the usage units 3, 4, 5 function as evaporators, and the usage side heat exchange of the usage units 3, 4, 5 32, 42, 52 and the suction side of the compression mechanism 21 of the heat source unit 2 are connected via the low-pressure gas refrigerant communication pipe 11.
- the usage side expansion valves 31, 41, and 51 are, for example, the degree of superheat of the usage side heat exchangers 32, 42, and 52 (specifically, the liquid side temperature sensors 33, 43, The opening degree is adjusted according to the cooling load of each usage unit, such as the opening degree is adjusted based on the refrigerant temperature detected by 53 and the refrigerant temperature detected by the gas side temperature sensors 34, 44, 54). Speak.
- the high-pressure gas refrigerant compressed and discharged by the compressor 21a of the compression mechanism 21 is supplied from the refrigerating machine oil accompanying the high-pressure gas refrigerant in the oil separator 21b. Most of them are separated and sent to the first switching mechanism 22.
- the refrigerating machine oil separated in the oil separator 21b is returned to the suction side of the compressor 21a through the second oil return circuit 21d.
- the high-pressure gas refrigerant sent to the first switching mechanism 22 is sent to the heat source side heat exchanger 23 through the first port 22a and the second port 22b of the first switching mechanism 22.
- the high-pressure gas refrigerant sent to the heat source side heat exchanger 23 is condensed by exchanging heat with water as the heat source in the heat source side heat exchanger 23.
- the refrigerant condensed in the heat source side heat exchange 23 passes through the heat source side expansion valve 24, and then the high pressure gas refrigerant compressed and discharged by the compression mechanism 21 through the pressurizing circuit 111 joins (details will be described later).
- Sent to Resino 25 The refrigerant sent to the receiver 25 is temporarily stored in the receiver 25 and then sent to the cooler 121. Then, the refrigerant sent to the cooler 121 is cooled by exchanging heat with the refrigerant flowing through the cooling circuit 122 (details will be described later). Then, the refrigerant cooled in the cooler 121 is sent to the liquid refrigerant communication pipe 9 through the liquid side closing valve 27.
- the refrigerant sent to the liquid refrigerant communication pipe 9 is branched into three and sent to the liquid connection pipes 61, 71, 81 of the connection units 6, 7, 8. Then, the refrigerant sent to the liquid connection pipes 61, 71, 81 of the connection units 6, 7, 8 is sent to the use side expansion valves 31, 41, 51 of the use units 3, 4, 5.
- the refrigerant sent to the use side expansion valves 31, 41, 51 is used as the use side expansion valves 31, 41, 51.
- indoor air is cooled and supplied indoors. Then, the low-pressure gas refrigerant is sent to the merged gas connection pipes 65, 75, 85 of the connection units 6, 7, 8.
- the low-pressure gas refrigerant sent to the merged gas connection pipes 65, 75, 85 passes through the low-pressure gas on / off valves 67, 77, 87 and the low-pressure gas connection pipes 64, 74, 84 to the low-pressure gas refrigerant communication pipe 11. Sent to join.
- the low-pressure gas refrigerant sent to the low-pressure gas refrigerant communication pipe 11 and joined together is returned to the suction side of the compression mechanism 21 through the low-pressure gas side shut-off valve 29. In this way, the operation in the cooling operation mode is performed.
- each utilization unit 3, 4, and 5 may become very small.
- the refrigerant condensing capacity in the heat source side heat exchange 23 of the heat source unit 2 is reduced, and the cooling load (that is, the use side heat exchangers 32, 42, Must be balanced with an evaporation load of 52). Therefore, control is performed to reduce the amount of refrigerant condensed in the heat source side heat exchanger 23 by performing control to reduce the opening degree of the heat source side expansion valve 24.
- the opening of the heat source side expansion valve 24 By controlling the opening of the heat source side expansion valve 24 in this way, the amount of liquid refrigerant that accumulates in the heat source side heat exchanger increases! ] By reducing the effective heat transfer area, the condensation capacity is reduced.
- the high-pressure gas refrigerant compressed and discharged by the compression mechanism 21 is decompressed by the heat source side expansion valve 24 and used side refrigerant circuits 12a and 12b.
- 12c is provided with a pressurizing circuit 111 that joins the refrigerant sent to 12c.
- the on-off valve 111b of the pressurizing circuit 111 is opened in the cooling operation mode (that is, when the first switching mechanism 22 is in the condensing operation state), and is compressed through the pressurizing pipe 111a.
- the discharge side force of the heat source side expansion valve 24 can be merged downstream of the heat source side expansion valve 24. ing.
- the high pressure gas refrigerant is joined to the downstream side of the heat source side expansion valve 24 through the pressurization circuit 111, thereby The pressure of the downstream refrigerant can be increased.
- the high-pressure gas refrigerant is merged, whereby the refrigerant sent to the use-side refrigerant circuits 12a, 12b, 12c.
- the cooler 121 is further provided on the downstream side of the heat source side expansion valve 24.
- the high pressure gas refrigerant is joined to the downstream side of the heat source side expansion valve 24 through the pressurization circuit 111 to thereby control the heat source side expansion valve 24.
- the refrigerant that is depressurized by the heat source side expansion valve 24 and sent to the use side refrigerant circuits 12a, 12b, 12c is cooled by the cooler 121.
- the gas refrigerant can be condensed, and it is not necessary to send a gas-liquid two-phase flow refrigerant having a large gas fraction to the use-side refrigerant circuits 12a, 12b, and 12c.
- the pressurizing pipe 111a is connected between the heat source side expansion valve 24 and the receiver 25, so that the refrigerant on the downstream side of the heat source side expansion valve 24 has a high pressure.
- the gas refrigerant is joined, and the high-temperature gas refrigerant is joined to cool the refrigerant whose temperature is high by the cooler 121.
- the cooling circuit 122 is provided, and a part of the refrigerant sent from the heat source side heat exchanger 23 to the use side refrigerant circuits 12a, 12b, 12c. Is reduced to a refrigerant pressure that can be returned to the suction side of the compression mechanism 21, and this refrigerant is used as a cooling source for the cooler 121. Therefore, the refrigerant is reduced in pressure at the heat source side expansion valve 24 and used on the refrigerant circuits 12a, 12b.
- a cooling source having a temperature sufficiently lower than the temperature of the refrigerant sent to 12c can be obtained. For this reason, it is possible to cool the refrigerant, which is decompressed in the heat source side expansion valve 24, and sent to the use side refrigerant circuits 12a, 12b, 12c to a supercooled state.
- the cooling circuit side expansion valve 122b of the circuit 122 is based on, for example, the degree of superheat of the cooler 121 (calculated from the cooling medium temperature detected by the cooling circuit outlet temperature sensor 96 provided in the outlet pipe 122c of the cooling circuit 122). The opening degree is adjusted according to the flow rate and temperature of the refrigerant sent from the downstream side of the heat source side expansion valve 24 to the use side refrigerant circuits 12a, 12b, 12c.
- the usage unit 3 is in a cooling operation and the usage units 4 and 5 are in a heating / cooling simultaneous operation mode.
- the operation when the heat source side heat exchanger 23 of the heat source unit 2 is operated as an evaporator according to the air conditioning load (evaporation operation state) will be described.
- the refrigerant circuit 12 of the air conditioner 1 is configured as shown in FIG. 6 (refer to the arrows attached to the refrigerant circuit 12 of FIG. 6 for the refrigerant flow).
- the first switching mechanism 22 is set in the evaporation operation state (indicated by the broken line of the first mechanism 22 in FIG.
- the second structure 26 is switched to the heating load required operation state (the state indicated by the broken line of the second structure 26 in Fig. 6), thereby evaporating the heat source side heat exchanger 23.
- the high-pressure gas refrigerant compressed and discharged by the compression mechanism 21 can be supplied to the utilization units 4 and 5 through the high-pressure gas refrigerant communication pipe 10. Further, the opening degree of the heat source side expansion valve 24 is adjusted so as to depressurize the refrigerant.
- the on-off valve 11 lb of the pressurizing circuit 111 and the cooling circuit side expansion valve 122b of the cooling circuit 122 are closed, and a high-pressure gas refrigerant is merged with the refrigerant flowing between the heat source side expansion valve 24 and the receiver 25. Or the supply of the cold heat source to the cooler 121 is shut off, and the refrigerant flowing between the receiver 25 and the utilization units 3, 4, and 5 is not cooled.
- the use side heat exchanger 32 of the use unit 3 functions as an evaporator and the use side of the use unit 3
- the heat exchange 32 and the suction side of the compression mechanism 21 of the heat source unit 2 are connected via the low-pressure gas refrigerant communication pipe 11.
- the usage-side expansion valve 31 includes, for example, the degree of superheat of the usage-side heat exchanger 32 (specifically, the refrigerant temperature and the gas side temperature sensor detected by the liquid side temperature sensor 33).
- the degree of opening is adjusted according to the cooling load of the unit used, for example, the degree of opening is adjusted based on the temperature difference from the refrigerant temperature detected by the sensor 34).
- the low-pressure gas on-off valves 77 and 87 are closed and the high-pressure gas on-off valves 76 and 86 are opened, so that the heat exchange 42 and 52 on the user side 4 and 5 functions as a condenser. I try to let them.
- the usage side expansion valves 41 and 51 are, for example, the degree of supercooling of the usage side heat exchangers 4 and 52 (specifically, the refrigerant detected by the liquid side temperature sensors 43 and 53).
- the degree of opening is adjusted according to the heating load of each usage unit, for example, the degree of opening is adjusted based on the temperature and the refrigerant temperature detected by the gas side temperature sensors 44, 54).
- the high-pressure gas refrigerant compressed and discharged by the compressor 21a of the compression mechanism 21 is mostly contained in the high-pressure gas refrigerant in the oil separator 21b. Separated and sent to Second Unit 26.
- the refrigerating machine oil separated in the oil separator 21b is returned to the suction side of the compressor 21a through the second oil return circuit 21d.
- the high-pressure gas refrigerant sent to the second structure 26 is sent to the high-pressure gas refrigerant communication pipe 10 through the first port 26a and the fourth port 26d of the second structure 26 and the high-pressure gas side closing valve 28. It is done.
- the high-pressure gas refrigerant sent to the high-pressure gas refrigerant communication pipe 10 is branched into two and sent to the high-pressure gas connection pipes 73 and 83 of the connection units 7 and 8.
- the high-pressure gas refrigerant sent to the high-pressure gas connection pipes 73 and 83 of the connection units 7 and 8 passes through the high-pressure gas on / off valves 76 and 86 and the confluence gas connection pipes 75 and 85, and the usage-side heat of the use units 4 and 5 Sent to exchangers 42 and 52.
- the high-pressure gas refrigerant sent to the use side heat exchangers 42 and 52 is condensed by exchanging heat with indoor air in the use side heat exchangers 42 and 52 of the use units 4 and 5. On the other hand, indoor air is heated and supplied indoors.
- the refrigerant condensed in the use side heat exchangers 42 and 52 passes through the use side expansion valves 41 and 51 and then is sent to the liquid connection pipes 71 and 81 of the connection units 7 and 8.
- the refrigerant sent to the liquid connection pipes 71 and 81 is sent to the liquid refrigerant communication pipe 9 to be joined.
- the refrigerant sent to the use side expansion valve 31 is depressurized by the use side expansion valve 31, and then evaporated by exchanging heat with indoor air in the use side heat exchanger 32. It becomes a gas refrigerant.
- indoor air is cooled and supplied indoors.
- the low-pressure gas refrigerant is sent to the merged gas connection pipe 65 of the connection unit 6.
- the low-pressure gas refrigerant sent to the merged gas connection pipe 65 is sent to the low-pressure gas refrigerant communication pipe 11 through the low-pressure gas on-off valve 67 and the low-pressure gas connection pipe 64 and merges.
- the low-pressure gas refrigerant sent to the low-pressure gas refrigerant communication pipe 11 is returned to the suction side of the compression mechanism 21 through the low-pressure gas side closing valve 29.
- the remaining refrigerant excluding the refrigerant sent from the liquid refrigerant communication pipe 9 to the connection unit 6 and the utilization unit 3 is sent to the resin 25 through the liquid side closing valve 27 and the cooler 121 of the heat source unit 2.
- the refrigerant sent to the receiver 25 is temporarily stored in the receiver 25 and then decompressed by the heat source side expansion valve 24.
- the refrigerant depressurized by the heat source side expansion valve 24 is evaporated by exchanging heat with water as a heat source in the heat source side heat exchange 23 to become a low pressure gas refrigerant. Sent.
- the low-pressure gas refrigerant sent to the first structure 22 is returned to the suction side of the compression mechanism 21 through the second port 22b and the third port 22c of the first structure 22. In this way, the operation in the cooling and heating simultaneous operation mode (evaporation load) is performed.
- the heat source side heat exchange 23 requires an evaporation load, but the size may be very small. .
- the refrigerant evaporation capacity in the heat source side heat exchanger 23 of the heat source unit 2 is reduced, and the air conditioning load and balance of the entire usage units 3, 4, and 5 are reduced. I have to let it.
- the cooling load of the utilization unit 3 and the heating load of the utilization units 4 and 5 may be approximately the same load.
- the evaporation load of the heat source side heat exchanger 23 must be very small.
- the air conditioner 1 of this embodiment is divided into two layers in a temperature range of 30 ° C or lower. Because the combination of refrigeration oil and refrigerant that are not separated and the first oil return circuit 101 is provided, the refrigeration in the heat source side heat exchanger ⁇ 23 as described in the explanation of the heating operation mode described above. Prevents machine oil from accumulating ⁇ Cooling and heating simultaneous operation mode (condensation load)>
- the entire usage units 3, 4 and 5 are empty.
- the operation when the heat source side heat exchange 23 of the heat source unit 2 is operated as a condenser according to the control load (condensing operation state) will be described.
- the refrigerant circuit 12 of the air conditioner 1 is configured as shown in FIG. 7 (refer to the arrows attached to the refrigerant circuit 12 of FIG. 7 for the refrigerant flow).
- the first switching mechanism 22 is switched to the condensing operation state (the state indicated by the solid line of the first switching mechanism 22 in FIG. 7), and the second switching is performed.
- the mechanism 26 By switching the mechanism 26 to the heating load required operation state (the state indicated by the broken line in the second mechanism 26 in FIG. 7), the heat source side heat exchange 23 functions as an evaporator and the high pressure gas refrigerant communication pipe 10 is used.
- the high-pressure gas refrigerant compressed and discharged by the compression mechanism 21 can be supplied to the use unit 5.
- the heat source side expansion valve 24 is in an opened state.
- connection units 6 and 7 the high-pressure gas on-off valves 66 and 76 are closed and the low-pressure gas on-off valves 67 and 77 are opened, so that the use side heat exchangers 32 and 42 of the use units 3 and 4 are used as evaporators.
- the usage side heat exchange 32, 42 of the usage units 3, 4 and the suction side of the compression mechanism 21 of the heat source unit 2 are connected via the low-pressure gas refrigerant communication pipe 11. Yes.
- the usage side expansion valves 31 and 41 include, for example, the degree of superheat of the usage side heat exchange 32 and 42 (specifically, the coolant temperature detected by the liquid side temperature sensors 33 and 43).
- the opening degree is adjusted according to the cooling load of each usage unit, for example, the opening degree is adjusted based on the temperature difference between the refrigerant and the refrigerant temperature detected by the gas side temperature sensors 34 and 44.
- connection unit 8 the low pressure gas on / off valve 87 is closed and the high pressure gas on / off valve 86 is opened.
- the heat exchange on the use side of the use unit 5 is made to function as a condenser.
- the usage-side expansion valve 51 includes, for example, the degree of supercooling of the usage-side heat exchanger 52 (specifically, the refrigerant temperature detected by the liquid-side temperature sensor 53 and the gas-side temperature sensor 54.
- the degree of opening is adjusted according to the heating load of the unit used, such as the degree of opening is adjusted based on the detected temperature difference from the refrigerant temperature.
- the high-pressure gas refrigerant compressed and discharged by the compressor 21a of the compression mechanism 21 is stored in the high-pressure gas refrigerant in the oil separator 21b. Most of them are separated and sent to the first structure 22 and the second structure 26. The refrigerating machine oil separated in the oil separator 21b is returned to the suction side of the compressor 21a through the second oil return circuit 21d.
- the high-pressure gas refrigerant sent to the first switching mechanism 22 passes through the first port 22a and the second port 22b of the first switching mechanism 22, and the heat source Sent to side heat exchange 23.
- the high-pressure gas refrigerant sent to the heat source side heat exchanger 23 is condensed by exchanging heat with water as a heat source in the heat source side heat exchanger 23.
- the refrigerant condensed in the heat source side heat exchanger 23 passes through the heat source side expansion valve 24, and then the high pressure gas refrigerant compressed and discharged by the compression mechanism 21 through the pressurizing circuit 111 joins (details). Is sent to receiver 25).
- the refrigerant sent to the receiver 25 is temporarily stored in the receiver 25 and then sent to the cooler 121.
- the refrigerant sent to the cooler 121 is cooled by exchanging heat with the refrigerant flowing through the cooling circuit 122 (details will be described later).
- the refrigerant cooled in the cooler 121 is sent to the liquid refrigerant communication pipe 9 through the liquid side closing valve 27.
- the high-pressure gas refrigerant sent to the second mechanism 26 is the first port 26a and the fourth port 26d of the second switching mechanism 26. Then, it is sent to the high-pressure gas refrigerant communication pipe 10 through the high-pressure gas side closing valve 28.
- the high-pressure gas refrigerant sent to the high-pressure gas refrigerant communication pipe 10 is sent to the high-pressure gas connection pipe 83 of the connection unit 8.
- the high-pressure gas refrigerant sent to the high-pressure gas connection pipe 83 of the connection unit 8 is sent to the use-side heat exchanger 52 of the use unit 5 through the high-pressure gas on-off valve 86 and the merged gas connection pipe 85.
- the high-pressure gas refrigerant sent to the use-side heat exchanger 52 is condensed by exchanging heat with indoor air in the use-side heat exchanger 52 of the use unit 5. On the other hand, indoor air is heated and supplied indoors.
- the refrigerant condensed in the use side heat exchanger 52 is sent to the liquid connection pipe 81 of the connection unit 8 after passing through the use side expansion valve 51. Then, the refrigerant sent to the liquid connection pipe 81 is sent to the liquid refrigerant communication pipe 9, where the first switching mechanism 22, the heat source side heat exchanger 23, the heat source side expansion valve 24, the receiver 25, the cooler 121 and It is merged with the refrigerant sent to the liquid refrigerant communication pipe 9 through the liquid side closing valve 27.
- the refrigerant flowing through the liquid refrigerant communication pipe 9 is branched into two and sent to the liquid connection pipes 61 and 71 of the connection units 6 and 7. Then, the refrigerant sent to the liquid connection pipes 61 and 71 of the connection units 6 and 7 is sent to the use side expansion valves 31 and 41 of the use units 3 and 4.
- the refrigerant sent to the use side expansion valves 31 and 41 is depressurized by the use side expansion valves 31 and 41 and then exchanges heat with indoor air in the use side heat exchangers 32 and 42. It is evaporated and becomes a low-pressure gas refrigerant. On the other hand, indoor air is cooled and supplied indoors. Then, the low-pressure gas refrigerant is sent to the merged gas connection pipes 65 and 75 of the connection units 6 and 7.
- the low-pressure gas refrigerant sent to the merged gas connection pipes 65 and 75 is sent to the low-pressure gas refrigerant communication pipe 11 through the low-pressure gas on-off valves 67 and 77 and the low-pressure gas connection pipes 64 and 74 and merges.
- the low-pressure gas refrigerant sent to the low-pressure gas refrigerant communication pipe 11 is returned to the suction side of the compression mechanism 21 through the low-pressure gas side closing valve 29. In this way, the operation is performed in the cooling and heating simultaneous operation mode (condensation load).
- the heat source side heat exchange requires a condensing load, which may be very small.
- the refrigerant condensing capacity in the heat source side heat exchanger 23 of the heat source unit 2 is reduced, and the air conditioning load and balance of the entire usage units 3, 4, and 5 are reduced. I have to let it.
- the cooling load of the usage units 3 and 4 and the heating load of the usage unit 5 may be approximately the same load.
- the condensation load on the heat source side heat exchanger 23 must be very small. I have to.
- a high-pressure gas refrigerant is joined to the downstream side of the heat source side expansion valve 24 through the pressurization circuit 111 while performing control to reduce the opening degree of the heat source side expansion valve 24.
- control is performed to increase the pressure of the refrigerant on the downstream side of the heat source side expansion valve 24, and the refrigerant that is decompressed by the heat source side expansion valve 24 and sent to the use side refrigerant circuits 12a and 12b is cooled by the cooler 121. Since cooling is performed, the gas refrigerant can be condensed, and it is not necessary to send a gas-liquid two-phase flow refrigerant with a large gas fraction to the use-side refrigerant circuits 12a and 12b.
- the air conditioner 1 of the present embodiment has the following features.
- a heat source side refrigerant circuit 12d having a heat source side heat exchanger 23 configured so that refrigerant flows in from the lower side and flows out from the upper side.
- the refrigerant circuit 12 is configured to be connected to the use-side refrigerant circuits 12a, 12b, and 12c, and the refrigerating machine oil and refrigerant used in the refrigerant circuit 12 have a temperature range of 30 ° C or lower.
- the combination of refrigerating machine oil and refrigerant is not used.
- the evaporating temperature of the refrigerant in the heat source side heat exchanger 23 is a temperature of 30 ° C.
- the refrigerating machine oil accumulates in the heat source side heat exchanger 23 in a mixed state with the refrigerant that does not accumulate in the state of floating on the refrigerant level in the heat source side heat exchanger 23. It will be.
- the refrigerating machine oil accumulated in the heat source side heat exchanger 23 is returned to the suction side of the compression mechanism 21 together with the refrigerant by the first oil return circuit 101 connected to the lower part of the heat source side heat exchanger 23. ing.
- the refrigerant level in the heat source side heat exchanger is maintained at a certain level or higher in order to prevent refrigeration oil from accumulating in the heat source side heat exchanger. There is no need to do it.
- the evaporation capacity of the heat source side heat exchanger 23 is reduced by reducing the opening degree of the heat source side expansion valve 24 according to the air conditioning load of the use side refrigerant circuits 12a, 12b, 12c.
- the liquid level of the refrigerant in the heat source side heat exchanger is controlled.
- Refrigeration oil does not accumulate in the heat source side heat exchanger 23 even if the temperature drops, so the control range when controlling the evaporation capacity of the heat source side heat exchanger 23 with the heat source side expansion valve should be expanded. Is possible.
- the air conditioner 1 when a plurality of heat source side heat exchangers are provided and the heat source side heat exchange functions as an evaporator, some of the plurality of heat source side expansion valves are used.
- the number of heat source side heat exchangers ⁇ that function as evaporators and reducing the evaporation capacity, or by allowing some of the heat source side heat exchangers ⁇ to function as condensers Since it is not necessary to control to reduce the evaporation capacity by offsetting the evaporation capacity of the heat source side heat exchanger functioning as an evaporator, a wide range of evaporation capacity control can be obtained by a single heat source side heat exchange Will be able to.
- the first oil return circuit 101 is provided with the on-off valve 101b, and when the heat source side heat exchange 23 functions as a condenser, the on-off valve 101b is closed.
- the on-off valve 101b is closed.
- the opening of the heat source side expansion valve 24 corresponding to the coolant level at which refrigeration oil can accumulate in the heat source side heat exchange 23 as a predetermined opening, and the opening of the heat source side expansion valve 24 is By opening and closing the on-off valve 101b only when the opening is below the specified opening, It is possible to prevent the amount of refrigerant sent to the compression mechanism 21 from increasing without being evaporated in the heat source side heat exchanger 23.
- a plate-type heat exchanger is used as the heat source side heat exchanger 23. Due to its structure, a refrigerant is used to prevent refrigeration oil from collecting in the heat source side heat exchanger 23. It is difficult to extract the refrigerating machine oil that has floated and accumulated above the liquid level from the vicinity of the refrigerant level.
- the refrigerating machine oil is stored in the heat source side heat exchanger 23 in a state of being mixed with the refrigerant, and the refrigerating machine oil accumulated in the heat source side heat exchanger 23 is combined with the refrigerant in the heat source side heat. Even if a plate heat exchanger is used, the first oil return circuit 101 can be easily installed because it is only necessary to extract the lower force of the AC.
- the refrigerant condensed in the heat source side heat exchanger 23 functioning as a condenser is decompressed by the heat source side expansion valve 24 and sent to the use side refrigerant circuits 12a, 12b, 12c.
- the high-pressure gas refrigerant merges from the pressurizing circuit 111 and is pressurized, and the refrigerant pressure on the downstream side of the heat source side expansion valve 24 is increased.
- the refrigerant sent to the use-side refrigerant circuits 12a, 12b, 12c becomes a gas-liquid two-phase flow with a large gas fraction,
- the opening degree of the heat source side expansion valve 24 cannot be made sufficiently small, in the air conditioner 1, the pressure is reduced by the heat source side expansion valve 24 to the use side refrigerant circuits 12a, 12b, 12c. Since the refrigerant to be sent is cooled by the cooler 121, the gas refrigerant can be condensed, and a gas-liquid two-phase flow refrigerant having a large gas fraction in the use side refrigerant circuits 12a, 12b, 12c. You don't have to send
- the heat source side heat exchanger 23 is reduced in condensing capacity by reducing the opening degree of the heat source side expansion valve 24 according to the air conditioning load of the use side refrigerant circuits 12a, 12b, 12c. Even if the pressurization circuit 111 is used to control the pressure by combining high-pressure gas refrigerant, the gas-liquid two-phase refrigerant with a large gas fraction is not sent to the use-side refrigerant circuits 12a, 12b, 12c. Evaporative capacity of heat exchange on the heat source side It is possible to expand the control range when controlling the heat source side expansion valve 24.
- the air conditioner 1 when a plurality of heat source side heat exchangers are provided and the heat source side heat exchange functions as a condenser, as in the conventional air conditioner, some of the plurality of heat source side expansion valves are used.
- the number of heat source side heat exchangers ⁇ that function as evaporators and reducing the evaporation capacity, or by allowing some of the heat source side heat exchangers ⁇ to function as condensers Since it is not necessary to control to reduce the evaporation capacity by offsetting the evaporation capacity of the heat source side heat exchanger functioning as an evaporator, a wide range of condensation capacity control can be obtained by a single heat source side heat exchange Will be able to.
- the pressurization circuit 111 is connected so that the high-pressure gas refrigerant merges between the heat source side expansion valve 24 and the cooler 121. Therefore, the high-pressure gas refrigerant merges. Then, the refrigerant whose temperature has been increased is cooled by the cooler 121. As a result, a relatively high temperature cold heat source that does not require the use of a low temperature cold heat source can be used as the cold heat source for cooling the refrigerant in the cooler 121.
- a part of the refrigerant sent from the downstream side of the heat source side expansion valve 24 to the use side refrigerant circuits 12a, 12b, 12c is reduced to a refrigerant pressure that can be returned to the suction side of the compression mechanism 21. Since this is used as the cooling source for the cooler 121, the cooling source has a temperature sufficiently lower than the temperature of the refrigerant sent from the downstream side of the heat source side expansion valve 24 to the utilization side refrigerant circuit 12a, 12b, 12c. Can be obtained. As a result, the refrigerant sent from the downstream side of the heat source side expansion valve 24 to the use side refrigerant circuits 12a, 12b, 12c can be cooled to a supercooled state. Become ⁇ .
- water that is supplied in a constant amount is used as a heat source regardless of the flow control of the refrigerant flowing in the heat source side heat exchanger 23, and the heat source side heat is controlled by controlling the amount of water. It is impossible to control the evaporation capacity in the exchange. However, in the air conditioner 1, since the control range when the evaporation capacity or the condensation capacity of the heat source side heat exchanger 23 is controlled by the heat source side expansion valve 24 is expanded, it is not necessary to control the amount of water. Thus, it is possible to secure a control range when controlling the evaporation capability of the heat source side heat exchanger 23.
- the low-pressure gas refrigerant communication pipe 11 and the connection units 6, 7, and 8 necessary for enabling simultaneous operation of cooling and heating are omitted, and the usage units 3, 4 , 5 are directly connected to the liquid refrigerant communication pipe 9 and the high-pressure gas refrigerant communication pipe 10, and by switching the second switching mechanism 26, the high-pressure gas refrigerant communication pipe 10 is changed from the use unit 3, 4, 5 to the heat source unit 2.
- It can function as a pipe through which the returned low-pressure gas refrigerant flows, or it can function as a pipe through which the high-pressure gas refrigerant supplied from the heat source unit 2 to the utilization units 3, 4, and 5 flows. I have to.
- the heating operation mode will be described.
- the refrigerant circuit 12 of the air conditioner 1 is configured as shown in FIG. 9 (the refrigerant flow is attached to the refrigerant circuit 12 of FIG. 9). (See the arrow that appears.)
- the first Kiriura structure 22 is switched to the evaporation operation state (the state indicated by the broken line of the first switching mechanism 22 in FIG. 9), and the second Switching mechanism 26 requires heating load
- the demanding operation state the state indicated by the broken line of the second cut m «structure 26 in Fig.
- the heat source side heat exchanger 23 functions as an evaporator and the high-pressure gas refrigerant communication pipe 1 Through 0, the high-pressure gas refrigerant compressed and discharged by the compression mechanism 21 can be supplied to the utilization units 3, 4, and 5.
- the opening degree of the heat source side expansion valve 24 is adjusted so as to depressurize the refrigerant.
- the on-off valve 111b of the pressurizing circuit 111 and the cooling circuit side expansion valve 122b of the cooling circuit 122 are closed, and a high-pressure gas refrigerant is combined with the refrigerant flowing between the heat source side expansion valve 24 and the receiver 25.
- the supply of the cold heat source to the cooler 121 is cut off, and the refrigerant flowing between the receiver 25 and the utilization units 3, 4, and 5 is not cooled.
- the usage side expansion valves 31, 41, and 51 are, for example, the degree of supercooling of the usage side heat exchangers 32, 42, and 52 (specifically, the liquid side temperature sensors 33, 43). Adjust the opening according to the heating load of each unit used, such as adjusting the opening based on the temperature difference between the refrigerant temperature detected by 53 and the refrigerant temperature detected by gas side temperature sensors 34, 44, 54) It has been done.
- the high-pressure gas refrigerant compressed and discharged by the compressor 21a of the compression mechanism 21 is supplied to the high-pressure gas refrigerant in the oil separator 21b. Most of it is separated and sent to the second structure 26.
- the refrigerating machine oil separated in the oil separator 21b is returned to the suction side of the compressor 21a through the second oil return circuit 21d.
- the high-pressure gas refrigerant sent to the second structure 26 is sent to the high-pressure gas refrigerant communication pipe 10 through the first port 26a and the fourth port 26d of the second structure 26 and the high-pressure gas side closing valve 28. It is done.
- the high-pressure gas refrigerant sent to the high-pressure gas refrigerant communication pipe 10 is branched into three and sent to the use side heat exchangers 32, 42, 52 of the use units 3, 4, 5.
- the high-pressure gas refrigerant sent to the use side heat exchangers 32, 42, 52 exchanges heat with indoor air in the use side heat exchangers 32, 42, 52 of the use units 3, 4, 5. It is condensed by this. On the other hand, indoor air is heated and supplied indoors.
- the refrigerant condensed in the use side heat exchangers 32, 42, 52 passes through the use side expansion valves 31, 41, 51 and then is sent to the liquid refrigerant communication pipe 9 to join.
- the refrigerant sent to the liquid refrigerant communication pipe 9 and merged is closed on the liquid side of the heat source unit 2. It is sent to receiver 25 through chain valve 27 and cooler 121.
- the refrigerant sent to the receiver 25 is temporarily stored in the receiver 25 and then decompressed by the heat source side expansion valve 24.
- the refrigerant decompressed by the heat source side expansion valve 24 is evaporated by exchanging heat with water as a heat source in the heat source side heat exchanger 23 to become a low-pressure gas refrigerant.
- the low-pressure gas refrigerant sent to the first mechanism 22 is returned to the suction side of the compression mechanism 21 through the second port 22b and the third port 22c of the first switching mechanism 22. In this way, the operation in the heating operation mode is performed.
- the heating load of each of the utilization units 3, 4, and 5 may be very small, but in a temperature range of 30 ° C or lower! Refrigeration in the heat source side heat exchanger 23 in the same manner as in the heating operation mode of the air conditioner configured to be capable of simultaneous cooling and heating operation.
- the machine oil can be prevented from accumulating.
- the refrigerant circuit 12 of the air conditioner 1 is configured as shown in FIG. 10 (the refrigerant flow is attached to the refrigerant circuit 12 of FIG. 10). (See the arrow that appears.)
- the first notch structure 22 is switched to the condensing operation state (the state indicated by the solid line of the first switching mechanism 22 in FIG. 10), and the second By switching the switching mechanism 26 to the cooling operation state at the time of cooling / heating switching (the state indicated by the solid line of the second switching mechanism 26 in FIG.
- the heat source side heat exchange 23 functions as a condenser and a high-pressure gas refrigerant.
- the low-pressure gas refrigerant returned from the utilization units 3, 4, 5 to the heat source unit 2 through the communication pipe 10 can be sent to the suction side of the compression mechanism 21.
- the heat source side expansion valve 24 is in an opened state.
- the on-off valve 101b of the first oil return circuit 101 is closed, and the lower force of the heat source side heat exchange is also in a state in which the operation of extracting the refrigerating machine oil together with the refrigerant and returning it to the compressor mechanism 21 is not performed.
- the usage side expansion valves 31, 41, and 51 are, for example, the degree of superheat of the usage side heat exchangers 32, 42, and 52 (specifically, the liquid side temperature sensors 33, 43).
- the opening is adjusted.
- the high-pressure gas refrigerant compressed and discharged by the compressor 21a of the compression mechanism 21 is stored in the high-pressure gas refrigerant in the oil separator 21b. Most of them are separated and sent to the first switching mechanism 22.
- the refrigerating machine oil separated in the oil separator 21b is returned to the suction side of the compressor 21a through the second oil return circuit 21d.
- the high-pressure gas refrigerant sent to the first switching mechanism 22 is sent to the heat source side heat exchanger 23 through the first port 22a and the second port 22b of the first switching mechanism 22.
- the high-pressure gas refrigerant sent to the heat source side heat exchanger 23 is condensed by exchanging heat with water as the heat source in the heat source side heat exchanger 23.
- the refrigerant condensed in the heat source side heat exchange 23 passes through the heat source side expansion valve 24, and then the high pressure gas refrigerant compressed and discharged by the compression mechanism 21 through the pressurizing circuit 111 is joined to the receiver 25. Sent.
- the refrigerant sent to the receiver 25 is temporarily stored in the receiver 25 and then sent to the cooler 121.
- the refrigerant sent to the cooler 121 is cooled by exchanging heat with the refrigerant flowing through the cooling circuit 122. Then, the refrigerant cooled in the cooler 121 is sent to the liquid refrigerant communication pipe 9 through the liquid side closing valve 27.
- the refrigerant sent to the liquid refrigerant communication pipe 9 is branched into three and sent to the use side expansion valves 31, 41, 51 of the use units 3, 4, 5.
- the refrigerant sent to the use side expansion valves 31, 41, 51 is depressurized by the use side expansion valves 31, 41, 51, and then exchanges heat with indoor air in the use side heat exchangers 32, 42, 52. Is evaporated into a low-pressure gas refrigerant. On the other hand, indoor air is cooled and supplied indoors. Then, the low-pressure gas refrigerant is sent to the high-pressure gas refrigerant communication pipe 10 and merges.
- the low-pressure gas refrigerant that has been sent to the high-pressure gas refrigerant communication pipe 10 and joined therethrough passes through the high-pressure gas side closing valve 28 and the fourth port 26d and the third port 26c of the second structure 26, and the compression mechanism 21 It is returned to the suction side. In this way, the operation in the cooling operation mode is performed.
- the cooling load of each of the utilization units 3, 4, and 5 may be very small.
- the heat source side expansion valve 24 is controlled.
- the high-pressure gas refrigerant is joined through the pressurization circuit 111 downstream of the heat source side. Control is performed to increase the pressure of the refrigerant on the downstream side of the expansion valve 24, and the refrigerant that is decompressed by the heat source side expansion valve 24 and sent to the use side refrigerant circuits 12a, 12b, 12c is cooled by the cooler 121.
- the gas refrigerant can be condensed and the use side refrigerant circuits 12a, 12b, and 12c are supplied with gas. There is no need to send a gas-liquid two-phase refrigerant with a large fraction.
- the control range of the evaporation capacity control of the heat source side heat exchanger 23 by the heat source side expansion valve 24 and the control capacity of the heat source side heat exchanger 23 by the heat source side expansion valve 24 are controlled. Force to provide the heat source unit 2 with the first oil return circuit 101, the pressurizing circuit 111, the cooler 121 and the cooling circuit 122 in order to expand both the control width, for example, evaporation of the heat source side heat exchanger 23 If the control range of the capacity control is secured, but it is necessary to expand only the control range of the heat source-side heat exchanger 23 condensing capacity control, as shown in Fig. 11, pressurization Only the circuit 111, the cooler 121, and the cooling circuit 122 may be provided in the heat source unit 2 (that is, the first oil return circuit 101 may be omitted).
- four-way switching valves are used as the first switching mechanism 22 and the second switching mechanism 26, but the present invention is not limited to this.
- a three-way valve may be used as the mechanism 22 and the second mechanism 26.
- the flow rates of the refrigeration oil and refrigerant returned to the compression mechanism 21 from the lower part of the heat source side heat exchanger 23 functioning as an evaporator through the first oil return circuit 101 Is determined in accordance with the pressure loss between the lower part of the heat source side heat exchange functioning as an evaporator and the compression mechanism 21 in the first oil return circuit 101, for example, the heat source side heat exchanger functioning as an evaporator In the case where the pressure loss in the first oil return circuit 101 where the pressure loss in the pipe between the refrigerant outlet side of the heat source 23 and the heat source side heat exchanger 23 to the suction side of the compression mechanism 21 is small, etc.
- Heat source side heat exchanger 2 3 Refrigerating machine oil with sufficient flow rate to prevent accumulation of refrigerating machine oil in 3 and If the lower force of the heat source side heat exchanger 23 cannot be returned to the compression mechanism 21 through the first oil return circuit 101, a case may occur.
- the refrigerating machine oil and the refrigerant having a flow rate sufficient to prevent the refrigerating machine oil from accumulating in the heat source side heat exchanger 23 are supplied to the heat source through the first oil return circuit 101.
- the refrigerant outlet side of the heat source side heat exchanger 23 functioning as an evaporator and the suction of the compression mechanism 21 Gas refrigerant that is evaporated in the heat source side heat exchange 23 and returned to the suction side of the compression mechanism 21 is also supplied to the compression mechanism 21 through the first oil return circuit 101. You may make it further provide the pressure reduction mechanism 131 which can be pressure-reduced before joining with the refrigerating machine oil and refrigerant
- the pressure reducing mechanism 131 mainly includes an on-off valve 131a that also has an electromagnetic valve force connected to a pipe that connects the third port 22c of the first switching mechanism 22 and the suction side of the compression mechanism 21, and a bypass that bypasses the on-off valve 131a. It consists of 13 lb tube. A capillary tube 13 lc is connected to the bypass pipe 131b. In the pressure reducing mechanism 131, when the first oil return circuit 101 is used, the on-off valve 131a is closed so that only the bypass pipe 131b flows the gas refrigerant evaporated in the heat source side heat exchanger 23.
- the first oil return circuit 101 is provided.
- the pressure loss between the refrigerant outlet side of the heat source side heat exchanger 23 functioning as an evaporator and the suction side of the compression mechanism 21 is increased, and the heat source side heat is passed through the first oil return circuit 101.
- the lower force of the alternating force can also increase the flow rates of the refrigerating machine oil and the refrigerant returned to the compression mechanism 21.
- the pressure reducing mechanism is not the open / close valve 131a and the bypass pipe 131b such as the pressure reducing mechanism 131, and the third port 22c of the first mechanism 22 and the compression mechanism 21. It may be an electric expansion valve connected to a pipe connecting the suction side.
- the compression mechanism 21 is controlled from the refrigerant outlet side of the heat source side heat exchanger 23 that functions as a evaporator by performing control to reduce the opening degree.
- the pressure loss up to the suction side of the refrigerant can be increased so that the lower force of the heat source side heat exchanger 23 through the first oil return circuit 101 can also increase the flow rates of refrigerating machine oil and refrigerant returned to the compression mechanism 21.
- control can be performed to increase the opening (for example, fully open), so that it is sufficient to prevent refrigeration oil from accumulating in the heat source side heat exchanger 23.
- the refrigerating machine oil and the refrigerant having a proper flow rate can be reliably returned to the compression mechanism 21 through the first oil return circuit 101 and the lower force of the heat source side heat exchange.
- the heat source side heat exchange condensation capacity can be increased by using an air conditioner including a heat source side refrigerant circuit and a use side refrigerant circuit connected to the heat source side refrigerant circuit.
- the control range at the time of controlling with a valve can be expanded.
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- Thermal Sciences (AREA)
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Abstract
Description
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Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
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AU2005258520A AU2005258520B2 (en) | 2004-07-01 | 2005-06-30 | Air conditioner |
US10/578,674 US7395674B2 (en) | 2004-07-01 | 2005-06-30 | Air conditioner |
ES05765183.8T ES2661304T3 (es) | 2004-07-01 | 2005-06-30 | Acondicionador de aire |
EP05765183.8A EP1762796B1 (en) | 2004-07-01 | 2005-06-30 | Air conditioner |
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JP2004-195229 | 2004-07-01 | ||
JP2004195229A JP3781046B2 (ja) | 2004-07-01 | 2004-07-01 | 空気調和装置 |
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WO2006003967A1 true WO2006003967A1 (ja) | 2006-01-12 |
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Country Status (9)
Country | Link |
---|---|
US (1) | US7395674B2 (ja) |
EP (1) | EP1762796B1 (ja) |
JP (1) | JP3781046B2 (ja) |
KR (1) | KR100743344B1 (ja) |
CN (1) | CN100453924C (ja) |
AU (1) | AU2005258520B2 (ja) |
ES (1) | ES2661304T3 (ja) |
TR (1) | TR201802470T4 (ja) |
WO (1) | WO2006003967A1 (ja) |
Families Citing this family (17)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10257309A1 (de) * | 2002-11-30 | 2004-06-09 | Gast, Karl Heinz, Dipl.-Ing. (FH) | Verfahren und Einrichtungen zum Frostschutz in Heizungsanlagen |
JP3861891B2 (ja) * | 2004-08-04 | 2006-12-27 | ダイキン工業株式会社 | 空気調和装置 |
KR100758902B1 (ko) * | 2004-11-23 | 2007-09-14 | 엘지전자 주식회사 | 멀티 공기조화 시스템 및 그 제어방법 |
JP5055965B2 (ja) * | 2006-11-13 | 2012-10-24 | ダイキン工業株式会社 | 空気調和装置 |
KR20090022119A (ko) * | 2007-08-29 | 2009-03-04 | 엘지전자 주식회사 | 서비스밸브 결합체를 구비한 분리형 멀티에어컨 |
US9322562B2 (en) * | 2009-04-01 | 2016-04-26 | Mitsubishi Electric Corporation | Air-conditioning apparatus |
JP5313774B2 (ja) * | 2009-06-08 | 2013-10-09 | 日立アプライアンス株式会社 | 空気調和機 |
US8794020B2 (en) * | 2009-09-10 | 2014-08-05 | Mitsubishi Electric Corporation | Air-conditioning apparatus |
CN102695929B (zh) * | 2009-11-18 | 2014-07-30 | 三菱电机株式会社 | 冷冻循环装置及适用于该冷冻循环装置的信息传递方法 |
EP2927614B1 (en) * | 2012-11-29 | 2020-08-05 | Mitsubishi Electric Corporation | Air conditioning device |
CN103423917B (zh) * | 2013-07-10 | 2015-07-22 | 湖南富利来环保科技工程有限公司 | 空气源中央空调热水三联供热泵机组 |
JP6138364B2 (ja) * | 2014-05-30 | 2017-05-31 | 三菱電機株式会社 | 空気調和機 |
JP6248878B2 (ja) * | 2014-09-18 | 2017-12-20 | 株式会社富士通ゼネラル | 空気調和装置 |
CN105588362A (zh) * | 2015-11-09 | 2016-05-18 | 青岛海信日立空调系统有限公司 | 一种多联机空调系统及其控制方法 |
JP6599002B2 (ja) * | 2016-06-14 | 2019-10-30 | 三菱電機株式会社 | 空気調和装置 |
CN107559953B (zh) * | 2017-08-15 | 2020-02-04 | 广东美的暖通设备有限公司 | 多联机系统及其过冷回路阀体的控制方法和装置 |
DE102019008914A1 (de) * | 2019-12-20 | 2021-06-24 | Stiebel Eltron Gmbh & Co. Kg | Wärmepumpe mit optimiertem Kältemittelkreislauf |
Citations (3)
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JPH03129260A (ja) * | 1989-10-13 | 1991-06-03 | Matsushita Refrig Co Ltd | 多室型空気調和機 |
JPH0545022A (ja) * | 1991-08-09 | 1993-02-23 | Hitachi Ltd | 空気調和機 |
JPH07120076A (ja) * | 1993-10-20 | 1995-05-12 | Mitsubishi Electric Corp | 空気調和機 |
Family Cites Families (12)
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US4197719A (en) * | 1976-01-29 | 1980-04-15 | Dunham-Bush, Inc. | Tri-level multi-cylinder reciprocating compressor heat pump system |
US4270359A (en) * | 1978-12-07 | 1981-06-02 | Hummel Steven L | Solar heating system |
JPS63204074A (ja) | 1987-02-19 | 1988-08-23 | ダイキン工業株式会社 | 冷凍装置 |
JPH03129259A (ja) | 1989-10-13 | 1991-06-03 | Matsushita Refrig Co Ltd | 多室型空気調和機 |
JP2954259B2 (ja) | 1990-03-09 | 1999-09-27 | 株式会社日立製作所 | 空気調和機 |
JP3485379B2 (ja) * | 1995-04-06 | 2004-01-13 | サンデン株式会社 | 車両用空気調和装置 |
US5596878A (en) * | 1995-06-26 | 1997-01-28 | Thermo King Corporation | Methods and apparatus for operating a refrigeration unit |
US5826433A (en) * | 1997-03-25 | 1998-10-27 | Dube; Serge | Refrigeration system with heat reclaim and efficiency control modulating valve |
ES2228796T3 (es) * | 2000-01-21 | 2005-04-16 | Toshiba Carrier Corporation | Detector de cantidad de aceite, dispositivo de refrigeracion y acondicionador de aire. |
JP3815302B2 (ja) * | 2001-11-12 | 2006-08-30 | 株式会社デンソー | 車両用空調装置 |
US6684650B2 (en) * | 2002-01-24 | 2004-02-03 | Carrier Corporation | System and method for rapid defrost or heating in a mobile refrigeration unit |
JP3928470B2 (ja) * | 2002-04-26 | 2007-06-13 | 株式会社デンソー | 車両用空調装置 |
-
2004
- 2004-07-01 JP JP2004195229A patent/JP3781046B2/ja not_active Expired - Lifetime
-
2005
- 2005-06-30 TR TR2018/02470T patent/TR201802470T4/tr unknown
- 2005-06-30 WO PCT/JP2005/012029 patent/WO2006003967A1/ja not_active Application Discontinuation
- 2005-06-30 EP EP05765183.8A patent/EP1762796B1/en active Active
- 2005-06-30 ES ES05765183.8T patent/ES2661304T3/es active Active
- 2005-06-30 AU AU2005258520A patent/AU2005258520B2/en active Active
- 2005-06-30 US US10/578,674 patent/US7395674B2/en active Active
- 2005-06-30 CN CNB2005800015379A patent/CN100453924C/zh active Active
- 2005-06-30 KR KR1020067009899A patent/KR100743344B1/ko not_active IP Right Cessation
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
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JPH03129260A (ja) * | 1989-10-13 | 1991-06-03 | Matsushita Refrig Co Ltd | 多室型空気調和機 |
JPH0545022A (ja) * | 1991-08-09 | 1993-02-23 | Hitachi Ltd | 空気調和機 |
JPH07120076A (ja) * | 1993-10-20 | 1995-05-12 | Mitsubishi Electric Corp | 空気調和機 |
Also Published As
Publication number | Publication date |
---|---|
AU2005258520B2 (en) | 2008-01-24 |
CN1906452A (zh) | 2007-01-31 |
EP1762796A1 (en) | 2007-03-14 |
TR201802470T4 (tr) | 2018-03-21 |
AU2005258520A1 (en) | 2006-01-12 |
EP1762796B1 (en) | 2018-01-31 |
KR100743344B1 (ko) | 2007-07-26 |
CN100453924C (zh) | 2009-01-21 |
US7395674B2 (en) | 2008-07-08 |
ES2661304T3 (es) | 2018-03-28 |
JP2006017380A (ja) | 2006-01-19 |
US20070130978A1 (en) | 2007-06-14 |
KR20060097039A (ko) | 2006-09-13 |
EP1762796A4 (en) | 2013-12-18 |
JP3781046B2 (ja) | 2006-05-31 |
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