WO2016071955A1 - 空気調和装置 - Google Patents
空気調和装置 Download PDFInfo
- Publication number
- WO2016071955A1 WO2016071955A1 PCT/JP2014/079213 JP2014079213W WO2016071955A1 WO 2016071955 A1 WO2016071955 A1 WO 2016071955A1 JP 2014079213 W JP2014079213 W JP 2014079213W WO 2016071955 A1 WO2016071955 A1 WO 2016071955A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- heat exchanger
- refrigerant
- flow path
- transfer tube
- heat transfer
- Prior art date
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B40/00—Subcoolers, desuperheaters or superheaters
- F25B40/02—Subcoolers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/89—Arrangement or mounting of control or safety devices
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/005—Compression machines, plants or systems with non-reversible cycle of the single unit type
-
- 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
- F25B30/00—Heat pumps
- F25B30/02—Heat pumps of the compression type
-
- 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
- F25B40/00—Subcoolers, desuperheaters or superheaters
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/40—Fluid line 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
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
- F25B9/006—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant containing more than one component
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
- F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2500/00—Problems to be solved
- F25B2500/05—Cost reduction
Definitions
- the present invention relates to an air conditioner, and more particularly to an air conditioner capable of both a cooling operation and a heating operation.
- an internal heat exchanger for exchanging heat between the refrigerant that flows out of the condenser and reaches the expansion device and the refrigerant that flows out of the evaporator increases the degree of supercooling of the refrigerant that flows out of the condenser
- a refrigeration cycle circuit There has been proposed an air conditioner that improves the performance. Further, even in a conventional air conditioner capable of both a cooling operation and a heating operation, the above-described internal heat exchanger is provided, and the degree of supercooling of the refrigerant flowing out of the condenser is increased so that the cooling operation and the heating operation are performed. Both have proposed improvements in the performance of the refrigeration cycle circuit (see Patent Documents 1 and 2).
- the air conditioning apparatus described in Patent Document 1 includes two internal heat exchangers on both sides of the expansion device in order to increase the degree of supercooling of the refrigerant that has flowed out of the condenser in both the cooling operation and the heating operation. ing. That is, the air conditioner described in Patent Document 1 is between the outdoor heat exchanger that serves as a condenser during cooling operation and the expansion device, and between the indoor heat exchanger that serves as a condenser during heating operation and the expansion device. Each has an internal heat exchanger.
- the air conditioner described in Patent Document 2 includes two expansion devices on both sides of the internal heat exchanger in order to increase the degree of supercooling of the refrigerant flowing out of the condenser in both the cooling operation and the heating operation. That is, the air conditioning apparatus described in Patent Document 2 is an expansion device that expands the refrigerant cooled by the internal heat exchanger during the cooling operation, and an expansion device that expands the refrigerant cooled by the internal heat exchanger during the heating operation. It has. Further, Patent Document 2 uses a single internal heat exchanger and a single expansion device to increase the degree of supercooling of the refrigerant flowing out of the condenser in both the cooling operation and the heating operation. In addition, an air conditioner provided with a bridge circuit composed of four check valves is also disclosed.
- Patent Document 2 in a conventional air conditioner capable of both cooling operation and heating operation, the degree of supercooling of the refrigerant flowing out of the condenser using one internal heat exchanger and one expansion device is disclosed. There is also disclosed one that increases the.
- this conventional air conditioner needs to provide a bridge circuit including four check valves in the refrigeration cycle circuit. For this reason, also in this conventional air conditioning apparatus, the problem that the cost of an air conditioning apparatus increases like the conventional air conditioning apparatus provided with two internal heat exchangers or expansion apparatuses, and air conditioning There was a problem that the apparatus would be enlarged.
- a bridge circuit composed of four check valves is provided in the refrigeration cycle circuit, when a gas-liquid two-phase refrigerant flows into the check valve, the valve reciprocates. There was also a problem that noise was generated by this.
- the present invention has been made to solve at least one of the above-described problems, and can perform both cooling operation and heating operation, and can increase the degree of supercooling of the refrigerant flowing out of the condenser. It is an object of the present invention to provide an air conditioner that can achieve cost reduction and space saving compared to the conventional air conditioner.
- An air conditioner includes a compressor that compresses refrigerant, a flow switching device that switches a flow path of refrigerant discharged from the compressor during cooling operation and heating operation, and a condenser during cooling operation.
- Heat source side heat exchanger that functions as an evaporator during heating operation
- an expansion device that expands and depressurizes the refrigerant
- use side heat that functions as an evaporator during cooling operation and functions as a condenser during heating operation
- a third flow path through which the refrigerant flows between the use-side heat exchanger and heat exchange between the refrigerant flowing through the first flow path and the refrigerant flowing through the second flow path during the cooling operation.
- An air conditioner includes a first flow path through which a refrigerant flows between an evaporator and a compressor, a second flow path through which a refrigerant flows between a heat source side heat exchanger and an expansion device, and an expansion device.
- a use side heat exchanger have a third flow path through which the refrigerant flows, heat exchange is performed between the refrigerant flowing through the first flow path and the refrigerant flowing through the second flow path during the cooling operation, and the first flow is performed during the heating operation.
- An internal heat exchanger configured to exchange heat between the refrigerant flowing through the flow path and the refrigerant flowing through the third flow path is provided.
- the air conditioning apparatus according to the present invention uses only one internal heat exchanger and one expansion device, and the degree of supercooling of the refrigerant flowing out of the condenser can be increased during both cooling and heating operations. It is possible to increase the performance of the refrigeration cycle circuit. Therefore, the air conditioning apparatus according to the present invention can achieve cost reduction and space saving as compared with the conventional one.
- FIG. 2 is a ph diagram (relationship between refrigerant pressure p and specific enthalpy h) for explaining an operating state of the air-conditioning apparatus according to Embodiment 1 of the present invention.
- It is sectional drawing which shows an example of the internal heat exchanger of the air conditioning apparatus which concerns on Embodiment 2 of this invention.
- It is sectional drawing which shows another example of the internal heat exchanger of the air conditioning apparatus which concerns on Embodiment 2 of this invention.
- FIG. 1 is a configuration diagram illustrating an air-conditioning apparatus according to Embodiment 1 of the present invention.
- arrows other than the leader line shown in FIG. 1 have shown the flow direction of the refrigerant
- the air conditioning apparatus 100 according to Embodiment 1 includes a refrigeration cycle in which a compressor 2, a flow path switching device 3, an outdoor heat exchanger 4, an expansion device 5, and an indoor heat exchanger 6 are sequentially connected by refrigerant piping.
- a circuit 1 is provided.
- the outdoor heat exchanger 4 corresponds to the heat source side heat exchanger of the present invention.
- the indoor heat exchanger 6 corresponds to the use side heat exchanger of the present invention.
- the compressor 2 sucks refrigerant and compresses the refrigerant to a high temperature and high pressure state.
- the kind of the compressor 2 is not specifically limited,
- the compressor 2 can be comprised using various types of compression mechanisms, such as a reciprocating, a rotary, a scroll, or a screw.
- the compressor 2 may be configured of a type that can be variably controlled by an inverter.
- a flow path switching device 3 is connected to the discharge port of the compressor 2.
- the flow path switching device 3 is, for example, a four-way valve, and switches the flow path of the refrigerant discharged from the compressor 2 between the cooling operation and the heating operation. Specifically, the flow path switching device 3 switches the connection destination of the discharge port of the compressor 2 to one of the outdoor heat exchanger 4 or the indoor heat exchanger 6, and connects the connection destination of the suction port of the compressor 2 to the outdoor heat exchanger. 4 or the other of the indoor heat exchanger 6.
- the refrigeration cycle circuit 1 includes the compressor 2, the outdoor heat exchanger 4, The expansion device 5 and the indoor heat exchanger 6 are sequentially connected by refrigerant piping.
- the refrigeration cycle circuit 1 of the air conditioner 100 has a circuit configuration in which the outdoor heat exchanger 4 functions as a condenser and the indoor heat exchanger 6 functions as an evaporator, and performs a cooling operation. Further, by connecting the discharge port of the compressor 2 to the indoor heat exchanger 6 and connecting the suction port of the compressor 2 to the outdoor heat exchanger 4, the refrigeration cycle circuit 1 includes the compressor 2, the indoor heat exchanger. 6. The expansion device 5 and the outdoor heat exchanger 4 are sequentially connected by refrigerant piping. That is, the refrigeration cycle circuit 1 of the air conditioner 100 has a circuit configuration in which the indoor heat exchanger 6 functions as a condenser and the outdoor heat exchanger 4 functions as an evaporator, and performs a heating operation.
- the suction port of the compressor 2 is connected to the heat exchanger functioning as an evaporator among the outdoor heat exchanger 4 and the indoor heat exchanger 6. At this time, the suction port of the compressor 2 is connected to the evaporator via the refrigerant pipe 11 connecting the evaporator and the flow path switching device 3 and the flow path switching device 3.
- the outdoor heat exchanger 4 is an air heat exchanger that exchanges heat between refrigerant flowing inside and outdoor air.
- an outdoor fan 4 a that supplies outdoor air to be heat exchanged to the outdoor heat exchanger 4 is provided around the outdoor heat exchanger 4. It is good to provide.
- This outdoor heat exchanger 4 is connected to an indoor heat exchanger 6 via an expansion device 5.
- the heat source side heat exchanger is not limited to the outdoor heat exchanger 4 of a pneumatic heat exchanger.
- the type of the heat source side heat exchanger may be appropriately selected according to the heat exchange target of the refrigerant. If water or brine is the heat exchange target, the heat source side refrigerant may be configured by the water heat exchanger.
- the expansion device 5 is an expansion valve, for example, and expands the refrigerant by decompressing it.
- the expansion device 5 is provided between the outdoor heat exchanger 4 and the indoor heat exchanger 6. Specifically, the outdoor heat exchanger 4 and the expansion device 5 are connected by a refrigerant pipe 12. The expansion device 5 and the indoor heat exchanger 6 are connected by a refrigerant pipe 13.
- the indoor heat exchanger 6 is an air heat exchanger that exchanges heat between the refrigerant flowing inside and the room air.
- an indoor blower 6a that supplies indoor air to be heat exchanged to the indoor heat exchanger 6 around the indoor heat exchanger 6 is provided. It is good to provide.
- a utilization side heat exchanger is not limited to the indoor heat exchanger 6 of a pneumatic heat exchanger.
- the type of the use side heat exchanger may be appropriately selected according to the heat exchange target of the refrigerant, and if the water or brine is the heat exchange target, the use side refrigerant may be configured by the water heat exchanger. In other words, the water or brine heat-exchanged with the refrigerant in the use side heat exchanger may be supplied indoors, and the cooling or heating may be performed with the water or brine supplied indoors.
- the air conditioning apparatus 100 includes an internal heat exchanger 20.
- the internal heat exchanger 20 includes a first flow path 21 through which refrigerant flows between the evaporator (the indoor heat exchanger 6 during the cooling operation and the outdoor heat exchanger 4 during the heating operation) and the compressor 2. It has the 2nd flow path 22 through which the refrigerant
- the internal heat exchanger 20 is configured to exchange heat between the refrigerant flowing through the first flow path 21, the refrigerant flowing through the second flow path 22, and the refrigerant flowing through the third flow path 23.
- the detailed configuration of the internal heat exchanger 20 will be described later.
- the air conditioner 100 configured as described above is provided with a control device 30 that controls the opening degree of the expansion device 5.
- a method for controlling the opening degree of the expansion device 5 various known methods can be adopted as long as the amount of refrigerant flowing through the indoor heat exchanger 6 can be controlled to an amount suitable for the air conditioning load (cooling load, heating load). it can.
- the control device 30 may control the opening degree of the expansion device 5 so that the difference between the temperature of the refrigerant discharged from the compressor 2 and the condensation temperature of the refrigerant flowing through the condenser falls within a specified temperature range. Good.
- the control device 30 determines that the difference between the temperature of the refrigerant flowing out of the first flow path 21 of the internal heat exchanger 20 and sucked into the compressor 2 and the evaporation temperature of the refrigerant flowing through the evaporator is a specified temperature range. You may control the opening degree of the expansion apparatus 5 so that it may become. Further, for example, the control device 30 may expand the expansion device so that the difference between the temperature of the refrigerant flowing out of the internal heat exchanger 20 and flowing into the expansion device 5 and the condensation temperature of the refrigerant flowing through the condenser falls within a specified temperature range. The opening degree of 5 may be controlled. In the first embodiment, the control device 30 is configured to control the rotational speeds of the compressor 2, the outdoor fan 4a, and the indoor fan 6a.
- the refrigerant circulating in the refrigeration cycle circuit 1 for example, R32 (difluoromethane), HFO1234yf (2,3,3,3-tetrafluoropropene), HFO1234ze (1, 3,3,3-tetrafluoropropene), HFO1123 (1,1,2-trifluoroethylene) and a refrigerant containing at least one of hydrocarbons are used.
- FIG. 2 is a front view showing the internal heat exchanger of the air-conditioning apparatus according to Embodiment 1 of the present invention.
- the refrigerant pipe 12 is shown shaded in order to facilitate the discrimination between the refrigerant pipe 12 and the refrigerant pipe 13.
- arrows other than the leader line shown in FIG. 2 have shown the flow direction of the refrigerant
- the internal heat exchanger 20 is connected to the outer periphery of the refrigerant pipe 11 between the evaporator and the compressor 2, and the refrigerant pipe 12 and the expansion between the outdoor heat exchanger 4 and the expansion device 5.
- a refrigerant pipe 12 between the apparatus 5 and the indoor heat exchanger 6 is wound. That is, in the internal heat exchanger 20 according to the first embodiment, the first heat transfer tube in which the first flow path 21 is formed is constituted by the refrigerant pipe 11 and the second heat transfer in which the second flow path 22 is formed.
- the heat pipe is constituted by the refrigerant pipe 12, and the third heat transfer pipe in which the third flow path 23 is formed is constituted by the refrigerant pipe 13.
- the refrigerant flowing through the same range of the refrigerant pipe 11 (the range where the refrigerant pipes 12 and 13 are wound) and the refrigerant flowing through the refrigerant pipes 12 and 13 exchange heat. It becomes the composition to do. That is, the internal heat exchanger 20 according to the first embodiment is as if the two internal heat exchangers described in Patent Document 1 are integrated and the flow path through which the refrigerant flowing out of the evaporator flows is made common. It becomes composition. For this reason, the internal heat exchanger 20 according to the first embodiment can achieve cost reduction and space saving compared to the two internal heat exchangers described in Patent Document 1.
- FIG. 3 is a ph diagram (relationship diagram between refrigerant pressure p and specific enthalpy h) for explaining the operating state of the air-conditioning apparatus according to Embodiment 1 of the present invention.
- the points A to F shown in FIG. 3 indicate the state of the refrigerant at the points A to F shown in FIG.
- movement of the air conditioning apparatus 100 which concerns on this Embodiment 1 is demonstrated using FIG.1 and FIG.3.
- the flow path in the flow path switching device 3 is a flow path indicated by a solid line in FIG.
- the refrigerant in the refrigeration cycle circuit 1 flows in the direction indicated by the solid line arrow in FIG.
- the compressor 2 when the compressor 2 is started, the refrigerant is sucked from the suction port of the compressor 2.
- This refrigerant becomes a high-temperature and high-pressure gaseous refrigerant and is discharged from the discharge port of the compressor 2 (point A in FIG. 3).
- the high-temperature and high-pressure gaseous refrigerant discharged from the compressor 2 flows into the outdoor heat exchanger 4, dissipates heat to the outdoor air, and flows out of the outdoor heat exchanger 4.
- the refrigerant that has flowed out of the outdoor heat exchanger 4 flows into the second flow path 22 of the internal heat exchanger 20 through the refrigerant pipe 12.
- the refrigerant is cooled to a low-temperature refrigerant that flows out of the indoor heat exchanger 6 and flows into the first flow path 21 of the internal heat exchanger 20. Therefore, the refrigerant that has flowed from the outdoor heat exchanger 4 into the second flow path 22 of the internal heat exchanger 20 becomes a liquid refrigerant and flows out of the internal heat exchanger 20 (point C in FIG. 3), and the expansion device 5. Flow into. In FIG.
- the refrigerant flowing through the first flow path 21 of the internal heat exchanger 20 and the refrigerant flowing through the second flow path 22 are in parallel flow.
- this refrigerant flow is only an example, and the refrigerant flowing through the first flow path 21 and the refrigerant flowing through the second flow path 22 may be made to counterflow.
- the liquid refrigerant that has flowed into the expansion device 5 is decompressed by the expansion device 5 to become a low-temperature gas-liquid two-phase state (point D in FIG. 3), and flows out of the expansion device 5.
- the low-temperature, gas-liquid two-phase refrigerant that has flowed out of the expansion device 5 flows into the indoor heat exchanger 6 through the refrigerant pipe 13 and the third flow path 23 of the internal heat exchanger 20. Since the refrigerant passing through the third flow path 23 of the internal heat exchanger 20 has a low temperature, it passes through the third flow path 23 with little heat exchange with the refrigerant flowing through the first flow path 21 of the internal heat exchanger 20. To do. In FIG.
- the refrigerant flowing through the first flow path 21 of the internal heat exchanger 20 and the refrigerant flowing through the third flow path 23 are opposed to each other.
- this refrigerant flow is only an example, and the refrigerant flowing through the first flow path 21 and the refrigerant flowing through the third flow path 23 may be made in parallel flow.
- the refrigerant that has flowed into the indoor heat exchanger 6 cools the room air and then flows out of the indoor heat exchanger 6 (point E in FIG. 3).
- coolant which flowed out from the outdoor heat exchanger 4 is cooled by the 2nd flow path 22 of the internal heat exchanger 20 as mentioned above, a supercooling degree increases.
- the refrigerant that has been decompressed by the expansion device 5 and has flowed into the indoor heat exchanger 6 has a small specific enthalpy h.
- the point D in FIG. 3 is close to the saturated liquid line side (left side).
- the air conditioning apparatus 100 according to Embodiment 1 can increase the amount of heat exchange in the indoor heat exchanger 6. That is, the performance of the refrigeration cycle circuit 1 can be improved.
- the refrigerant that has flowed out of the indoor heat exchanger 6 flows into the first flow path 21 of the internal heat exchanger 20 through the refrigerant pipe 11.
- this refrigerant is heated by the low-temperature refrigerant that flows out of the outdoor heat exchanger 4 and flows into the second flow path 22 of the internal heat exchanger 20.
- the refrigerant flowing into the first flow path 21 of the internal heat exchanger 20 becomes a gaseous refrigerant and flows out of the internal heat exchanger 20 (point F in FIG. 3). Therefore, the air-conditioning apparatus 100 according to Embodiment 1 can cause the refrigerant in the gas-liquid two-phase state to flow out from the indoor heat exchanger 6 (point E in FIG. 3).
- the internal heat exchanger 20 When the internal heat exchanger 20 is not provided, it is necessary to cause the gaseous refrigerant to flow out from the indoor heat exchanger 6 in order to prevent liquid back from occurring in the compressor 2. That is, in the indoor heat exchanger 6, a gaseous refrigerant flows near the outlet. However, the gaseous refrigerant has a poor heat transfer rate compared to the gas-liquid two-phase refrigerant. Since the air conditioner 100 according to Embodiment 1 includes the internal heat exchanger 20, the refrigerant in the gas-liquid two-phase state can flow out from the indoor heat exchanger 6, and thus the indoor heat exchanger 6. The heat transfer performance can be improved. Therefore, the performance of the refrigeration cycle circuit 1 can be further improved.
- the gaseous refrigerant that has flowed out of the first flow path 21 of the internal heat exchanger 20 is sucked from the suction port of the compressor 2 and is compressed again into a high-temperature and high-pressure gaseous refrigerant by the compressor 2.
- the refrigerant when the air-conditioning apparatus 100 is activated, the refrigerant is sleeping in the outdoor heat exchanger 4 or the like (because it is stored as a liquid refrigerant), so that the amount of refrigerant circulating in the refrigeration cycle circuit 1 is small. It has become. Even when refrigerant is leaking from the refrigeration cycle circuit 1, the amount of refrigerant circulating in the refrigeration cycle circuit 1 is small. In such a state where the amount of refrigerant circulating in the refrigeration cycle circuit 1 is small, the refrigerant flowing out of the outdoor heat exchanger 4 tends to be in a gas-liquid two-phase state (point B in FIG. 3).
- the gas-liquid two-phase refrigerant flows into the expansion device 5.
- the amount of refrigerant flowing through the expansion device 5 becomes unstable, and the high pressure and low pressure of the refrigeration cycle become unstable. Further, when the amount of refrigerant flowing through the expansion device 5 becomes unstable, noise is generated from the expansion device 5.
- the air-conditioning apparatus 100 according to the first embodiment that includes the internal heat exchanger 20 is configured such that the refrigerant in the gas-liquid two-phase state flows out of the outdoor heat exchanger 4 even when It is cooled by the heat exchanger 20 and becomes a liquid refrigerant and flows into the expansion device 5.
- the air-conditioning apparatus 100 according to Embodiment 1 can prevent the high pressure and low pressure of the refrigeration cycle from becoming unstable at the time of startup, and can prevent the expansion device 5 from generating noise. it can.
- coolant from the exit of the outdoor heat exchanger 4 to the internal heat exchanger 20 A liquid refrigerant may flow through the pipe, or a gas-liquid two-phase refrigerant may flow through the pipe.
- the state in which the liquid refrigerant flows through the refrigerant pipe from the outlet of the outdoor heat exchanger 4 to the internal heat exchanger 20 is a state in which the point B in FIG. 3 is shifted to the left side (supercooled liquid side) from the saturated liquid line. is there. That is, the refrigerant that has been decompressed by the expansion device 5 and has flowed into the indoor heat exchanger 6 is compared with the case where a gas-liquid two-phase refrigerant flows through the refrigerant pipe from the outlet of the outdoor heat exchanger 4 to the internal heat exchanger 20. As a result, the specific enthalpy h becomes small. In other words, the point D in FIG. 3 is close to the saturated liquid line side (left side).
- the gas-liquid two-phase is supplied to the refrigerant pipe from the outlet of the outdoor heat exchanger 4 to the internal heat exchanger 20.
- the amount of heat exchange in the indoor heat exchanger 6 can be further increased, and the performance of the refrigeration cycle circuit 1 can be further improved.
- the air conditioner 100 when a gas-liquid two-phase refrigerant flows through the refrigerant pipe from the outlet of the outdoor heat exchanger 4 to the internal heat exchanger 20, the internal heat exchanger is discharged from the outlet of the outdoor heat exchanger 4.
- the amount of refrigerant charged in the refrigeration cycle circuit 1 can be reduced.
- R32, HFO1234yf, HFO1234ze, HFO1123, and hydrocarbons are flammable refrigerants. For this reason, when these refrigerants are used, it is desired to prevent the refrigerant from leaking and staying in the room to reach the flammable concentration range.
- a refrigeration cycle circuit is configured by flowing a refrigerant in a gas-liquid two-phase state through the refrigerant pipe from the outlet of the outdoor heat exchanger 4 to the internal heat exchanger 20. Since the amount of the refrigerant in 1 can be reduced, the volume concentration of the refrigerant in the room can be prevented from reaching the combustible concentration region.
- the flow path in the flow path switching device 3 is a flow path indicated by a broken line in FIG.
- the refrigerant in the refrigeration cycle circuit 1 flows in the direction indicated by the dashed arrow in FIG. Specifically, when the compressor 2 is started, the refrigerant is sucked from the suction port of the compressor 2. The refrigerant becomes a high-temperature and high-pressure gaseous refrigerant and is discharged from the discharge port of the compressor 2. The high-temperature and high-pressure gaseous refrigerant discharged from the compressor 2 flows into the indoor heat exchanger 6, heats the indoor air, and flows out of the indoor heat exchanger 6.
- the refrigerant that has flowed out of the indoor heat exchanger 6 flows into the third flow path 23 of the internal heat exchanger 20 through the refrigerant pipe 13.
- the refrigerant is cooled to a low-temperature refrigerant that flows out of the outdoor heat exchanger 4 and flows into the first flow path 21 of the internal heat exchanger 20.
- the refrigerant that has flowed into the third flow path 23 of the internal heat exchanger 20 from the indoor heat exchanger 6 flows out of the internal heat exchanger 20 as a liquid refrigerant, and flows into the expansion device 5.
- the refrigerant flowing through the first flow path 21 of the internal heat exchanger 20 and the refrigerant flowing through the third flow path 23 are in parallel flow.
- this refrigerant flow is an example, and the refrigerant flowing through the first flow path 21 and the refrigerant flowing through the third flow path 23 may be made to counter flow.
- the liquid refrigerant that has flowed into the expansion device 5 is decompressed by the expansion device 5 to become a low-temperature gas-liquid two-phase state and flows out of the expansion device 5.
- the low-temperature gas-liquid two-phase refrigerant flowing out of the expansion device 5 flows into the outdoor heat exchanger 4 through the refrigerant pipe 12 and the second flow path 22 of the internal heat exchanger 20. Since the refrigerant passing through the second flow path 22 of the internal heat exchanger 20 has a low temperature, it passes through the second flow path 22 with little heat exchange with the refrigerant flowing through the first flow path 21 of the internal heat exchanger 20. To do. In FIG.
- the refrigerant flowing through the first flow path 21 of the internal heat exchanger 20 and the refrigerant flowing through the second flow path 22 are opposed.
- this refrigerant flow is an example, and the refrigerant flowing through the first flow path 21 and the refrigerant flowing through the second flow path 22 may be made to flow in parallel.
- the refrigerant that has flowed into the outdoor heat exchanger 4 absorbs heat from the outdoor air and then flows out of the outdoor heat exchanger 4.
- coolant which flowed out from the indoor heat exchanger 6 is cooled by the 3rd flow path 23 of the internal heat exchanger 20 as mentioned above, a supercooling degree increases.
- the refrigerant having been decompressed by the expansion device 5 and flowing into the outdoor heat exchanger 4 is in a state where the specific enthalpy h is small.
- the air conditioning apparatus 100 according to Embodiment 1 can increase the amount of heat exchange in the outdoor heat exchanger 4. That is, the performance of the refrigeration cycle circuit 1 can be improved.
- the refrigerant that has flowed out of the outdoor heat exchanger 4 flows into the first flow path 21 of the internal heat exchanger 20 through the refrigerant pipe 11.
- the refrigerant is heated by the low-temperature refrigerant that flows out of the indoor heat exchanger 6 and flows into the third flow path 23 of the internal heat exchanger 20.
- the refrigerant that has flowed into the first flow path 21 of the internal heat exchanger 20 flows out of the internal heat exchanger 20 as a gaseous refrigerant. Therefore, the air-conditioning apparatus 100 according to Embodiment 1 can cause the refrigerant in the gas-liquid two-phase state to flow out from the outdoor heat exchanger 4.
- the internal heat exchanger 20 When the internal heat exchanger 20 is not provided, it is necessary to cause the gaseous refrigerant to flow out from the outdoor heat exchanger 4 in order to prevent the liquid back from being generated in the compressor 2. That is, in the outdoor heat exchanger 4, a gaseous refrigerant flows near the outlet. However, the gaseous refrigerant has a poor heat transfer rate compared to the gas-liquid two-phase refrigerant. Since the air conditioner 100 according to Embodiment 1 includes the internal heat exchanger 20, the refrigerant in the gas-liquid two-phase state can flow out from the outdoor heat exchanger 4, and thus the outdoor heat exchanger 4. The heat transfer performance can be improved. Therefore, the performance of the refrigeration cycle circuit 1 can be further improved.
- the gaseous refrigerant that has flowed out of the first flow path 21 of the internal heat exchanger 20 is sucked from the suction port of the compressor 2 and is compressed again into a high-temperature and high-pressure gaseous refrigerant by the compressor 2.
- the refrigerant when the air-conditioning apparatus 100 is activated, the refrigerant is sleeping in the outdoor heat exchanger 4 or the like (because it is stored as a liquid refrigerant), so that the amount of refrigerant circulating in the refrigeration cycle circuit 1 is small. It has become. Even when refrigerant is leaking from the refrigeration cycle circuit 1, the amount of refrigerant circulating in the refrigeration cycle circuit 1 is small. In such a state where the amount of refrigerant circulating in the refrigeration cycle circuit 1 is small, the refrigerant flowing out of the indoor heat exchanger 6 tends to be in a gas-liquid two-phase state. For this reason, when the internal heat exchanger 20 is not provided, the gas-liquid two-phase refrigerant flows into the expansion device 5.
- the air-conditioning apparatus 100 according to the first embodiment that includes the internal heat exchanger 20 is configured so that the refrigerant in the gas-liquid two-phase state flows out of the indoor heat exchanger 6 even if the refrigerant flows out of the interior heat exchanger 6. It is cooled by the heat exchanger 20 and becomes a liquid refrigerant and flows into the expansion device 5. For this reason, the air-conditioning apparatus 100 according to Embodiment 1 can prevent the high pressure and low pressure of the refrigeration cycle from becoming unstable at the time of startup, and can prevent the expansion device 5 from generating noise. it can.
- coolant from the exit of the indoor heat exchanger 6 to the internal heat exchanger 20 A liquid refrigerant may flow through the pipe, or a gas-liquid two-phase refrigerant may flow through the pipe.
- the refrigerant that has been decompressed by the expansion device 5 and flows into the outdoor heat exchanger 4 becomes the outlet of the indoor heat exchanger 6.
- the specific enthalpy h is reduced.
- the gas-liquid two-phase is supplied to the refrigerant pipe from the outlet of the indoor heat exchanger 6 to the internal heat exchanger 20.
- the amount of heat exchange in the outdoor heat exchanger 4 can be further increased, and the performance of the refrigeration cycle circuit 1 can be further improved.
- the air conditioner 100 when a gas-liquid two-phase refrigerant flows through the refrigerant pipe from the outlet of the indoor heat exchanger 6 to the internal heat exchanger 20, the internal heat exchanger from the outlet of the indoor heat exchanger 6.
- the amount of refrigerant charged in the refrigeration cycle circuit 1 can be reduced.
- R32, HFO1234yf, HFO1234ze, HFO1123, and hydrocarbons are flammable refrigerants. For this reason, when these refrigerants are used, it is desired to prevent the refrigerant from leaking and staying in the room to reach the flammable concentration range.
- the refrigeration cycle circuit is configured such that the gas-liquid two-phase refrigerant flows through the refrigerant pipe from the outlet of the indoor heat exchanger 6 to the internal heat exchanger 20. Since the amount of the refrigerant in 1 can be reduced, the volume concentration of the refrigerant in the room can be prevented from reaching the combustible concentration region.
- the air-conditioning apparatus 100 according to Embodiment 1 uses only one internal heat exchanger 20 and one expansion device 5, and the refrigerant that has flowed out of the condenser during both the cooling operation and the heating operation. It is possible to improve the performance of the refrigeration cycle circuit 1 by increasing the degree of supercooling. Moreover, the air conditioning apparatus 100 according to Embodiment 1 does not need to provide a bridge circuit including four check valves in the refrigeration cycle circuit 1. Therefore, the air-conditioning apparatus 100 according to Embodiment 1 can achieve cost reduction and space saving as compared with the related art.
- FIG. The internal heat exchanger 20 that can be used in the air conditioner 100 is not limited to the internal heat exchanger 20 shown in FIG.
- the internal heat exchanger 20 shown in FIG. 2 includes a second flow path 22 through which the refrigerant between the outdoor heat exchanger 4 and the expansion device 5 flows, and between the expansion device 5 and the indoor heat exchanger 6.
- a third flow path 23 through which the refrigerant flows is provided in close proximity.
- the internal heat exchanger 20 When the internal heat exchanger 20 is configured in this way, the refrigerant flowing into the internal heat exchanger 20 from the condenser heats the refrigerant flowing into the evaporator through the internal heat exchanger 20, so that the heat of the evaporator The exchange amount may be slightly reduced.
- the internal heat exchanger 20 may be configured as in the second embodiment. Configurations not described in the second embodiment are the same as those in the first embodiment, and the same configurations as those in the first embodiment are denoted by the same reference numerals as those in the first embodiment.
- the internal heat exchanger 20 includes a second flow path 22 through which a refrigerant between the outdoor heat exchanger 4 and the expansion device 5 flows, and between the expansion device 5 and the indoor heat exchanger 6.
- a first flow path 21 through which the refrigerant between the evaporator and the compressor 2 flows is formed between the third flow path 23 through which the refrigerant flows.
- the internal heat exchanger 20 according to the second embodiment can be configured as follows, for example.
- FIG. 4 is a cross-sectional view showing an example of the internal heat exchanger of the air-conditioning apparatus according to Embodiment 2 of the present invention.
- FIG. 4 shows the internal heat exchanger 20 cut along the flow direction of the refrigerant flowing through the first flow path 21, the second flow path 22 and the third flow path 23.
- the arrows other than the leader line shown in FIG. 4 indicate the flow direction of the refrigerant. This flow direction of the refrigerant is merely an example, and the refrigerant may flow in a direction opposite to the arrow.
- the internal heat exchanger 20 shown in FIG. 4 has a configuration in which a first flow path 21, a second flow path 22, and a third flow path 23 are juxtaposed on a heat transfer member 24 made of, for example, metal. Further, the first flow path 21 is disposed between the second flow path 22 and the third flow path 23.
- the first flow path 21 is connected to the refrigerant pipe 11
- the second flow path 22 is connected to the refrigerant pipe 12
- the third flow path 23 is connected to the refrigerant pipe 13.
- the first flow path 21 is provided in the middle of the refrigerant pipe 11
- the second flow path 22 is provided in the middle of the refrigerant pipe 12
- the third flow path 23 is in the refrigerant. Provided in the middle of the pipe 13.
- the refrigerant flowing into the internal heat exchanger 20 from the condenser (the refrigerant flowing through one of the second flow path 22 or the third flow path 23) is exchanged internally. It is possible to suppress heating of the refrigerant (the refrigerant flowing through the other of the second flow path 22 or the third flow path 23) flowing into the evaporator through the vessel 20.
- the internal heat exchanger 20 according to the second embodiment is not limited to the internal heat exchanger 20 shown in FIG.
- 5 and 6 are sectional views showing another example of the internal heat exchanger of the air-conditioning apparatus according to Embodiment 2 of the present invention.
- 5 and 6 are cross-sectional views perpendicular to the flow direction of the refrigerant flowing through the first flow path 21, the second flow path 22, and the third flow path 23, and the internal heat exchanger 20 is cut.
- the internal heat exchanger 20 shown in FIGS. 5 and 6 includes a first heat transfer tube 25 in which a first flow path 21 is formed, a second heat transfer tube 26 in which a second flow path 22 is formed, and a third flow path. 3 has a third heat transfer tube 27 formed thereon. 5 and 6, the first heat transfer tube 25 is disposed inside the third heat transfer tube 27, and the second heat transfer tube 26 is disposed inside the first heat transfer tube 25. Yes. By configuring the internal heat exchanger 20 in this way, the second flow path 22 and the third flow path 23 are separated by the first flow path 21. Therefore, the internal heat exchanger 20 shown in FIG. 5 and FIG.
- the refrigerant (flowing through one of the three flow paths 23) is further prevented from heating the refrigerant flowing through the internal heat exchanger 20 into the evaporator (the refrigerant flowing through the second flow path 22 or the other of the third flow paths 23). it can.
- the first heat transfer tube 25, the second heat transfer tube 26, and the third heat transfer tube 27 are formed of circular tubes.
- the second heat transfer tube 26 and the third heat transfer tube 27 are formed by circular tubes, but the first heat transfer tube 25 is a multi-leaf heat transfer tube.
- a multi-leaf heat transfer tube is a heat transfer tube in which a plurality of protrusions (protruding paths) are formed on the outer periphery of the heat transfer tube.
- the multi-leaf heat transfer tube is a heat transfer tube in which a plurality of flow paths projecting to the outer peripheral side are formed when the heat transfer tube is cut in a cross section perpendicular to the flow direction of the refrigerant.
- the internal heat exchanger 20 shown in FIG. 5 can be configured only with a heat transfer tube having a simple shape. For this reason, the effect that the internal heat exchanger 20 shown in FIG. 5 can be easily manufactured compared with the internal heat exchanger shown in FIG. 6 is acquired. Further, the internal heat exchanger 20 shown in FIG. 6 increases the heat transfer area between the refrigerant flowing through the first flow path 21 and the refrigerant flowing through the third flow path 23, compared to the internal heat exchanger 20 shown in FIG. The effect that it can be obtained.
- the internal heat exchanger 20 shown in FIGS. 5 and 6 has a first heat transfer tube 25 arranged inside the second heat transfer tube 26 and a third heat transfer tube 27 arranged inside the first heat transfer tube 25.
- a first heat transfer tube 25 arranged inside the second heat transfer tube 26 and a third heat transfer tube 27 arranged inside the first heat transfer tube 25.
- 1 refrigeration cycle circuit 2 compressor, 3 flow switching device, 4 outdoor heat exchanger (heat source side heat exchanger), 4a outdoor blower, 5 expansion device, 6 indoor heat exchanger (use side heat exchanger), 6a Indoor fan, 11 refrigerant pipe, 12 refrigerant pipe, 13 refrigerant pipe, 20 internal heat exchanger, 21 first flow path, 22 second flow path, 23 third flow path, 24 heat transfer member, 25 first heat transfer pipe, 26 2nd heat transfer tube, 27 3rd heat transfer tube, 30 control device, 100 air conditioner.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
- Air Filters, Heat-Exchange Apparatuses, And Housings Of Air-Conditioning Units (AREA)
Abstract
Description
図1は、本発明の実施の形態1に係る空気調和装置を示す構成図である。なお、図1に示す引出線以外の矢印は、冷媒の流れ方向を示している。
本実施の形態1に係る空気調和装置100は、圧縮機2、流路切替装置3、室外熱交換器4、膨張装置5、及び、室内熱交換器6が順次冷媒配管で接続される冷凍サイクル回路1を備えている。
ここで、室外熱交換器4が、本発明の熱源側熱交換器に相当する。また、室内熱交換器6が、本発明の利用側熱交換器に相当する。
なお、内部熱交換器20の詳細構成については後述する。
冷房運転では、流路切替装置3内の流路は、図1に実線で示す流路となる。このため、圧縮機2が起動すると、冷凍サイクル回路1内の冷媒は、図1に実線矢印で示す方向に流れることとなる。詳しくは、圧縮機2が起動すると、圧縮機2の吸入口から冷媒が吸入される。そして、この冷媒は、高温高圧のガス状冷媒となって、圧縮機2の吐出口から吐出される(図3のA点)。圧縮機2から吐出された高温高圧のガス状冷媒は、室外熱交換器4に流入して室外空気に放熱し、室外熱交換器4から流出する。
暖房運転では、流路切替装置3内の流路は、図1に破線で示す流路となる。このため、圧縮機2が起動すると、冷凍サイクル回路1内の冷媒は、図1に破線矢印で示す方向に流れることとなる。詳しくは、圧縮機2が起動すると、圧縮機2の吸入口から冷媒が吸入される。そして、この冷媒は、高温高圧のガス状冷媒となって、圧縮機2の吐出口から吐出される。圧縮機2から吐出された高温高圧のガス状冷媒は、室内熱交換器6に流入して室内空気を加熱し、室内熱交換器6から流出する。
空気調和装置100に使用できる内部熱交換器20は、図2に示した内部熱交換器20に限定されるものではない。例えば、図2で示した内部熱交換器20の場合、冷媒配管12及び冷媒配管13の当該内部熱交換器20を構成する部分(冷媒配管11に巻き付けられた部分)が、近接して設けられる。つまり、図2で示した内部熱交換器20は、室外熱交換器4と膨張装置5との間の冷媒が流れる第2流路22と、膨張装置5と室内熱交換器6との間の冷媒が流れる第3流路23とが、近接して設けられている。このように内部熱交換器20を構成した場合、凝縮器から内部熱交換器20へ流入した冷媒が内部熱交換器20を通って蒸発器へ流入する冷媒を加熱することにより、蒸発器の熱交換量が若干小さくなってしまう場合がある。このような若干の懸念事項をも解消しようとする場合、本実施の形態2のように内部熱交換器20を構成してもよい。なお、本実施の形態2で記載されていない構成は実施の形態1と同様とし、実施の形態1と同様の構成には実施の形態1と同じ符号を付すこととする。
Claims (9)
- 冷媒を圧縮する圧縮機と、
冷房運転時と暖房運転時とで前記圧縮機から吐出される冷媒の流路を切り替える流路切替装置と、
冷房運転時には凝縮器として機能し、暖房運転時には蒸発器として機能する熱源側熱交換器と、
冷媒を膨張させて減圧させる膨張装置と、
冷房運転時には蒸発器として機能し、暖房運転時には凝縮器として機能する利用側熱交換器と、
前記蒸発器と前記圧縮機との間の冷媒が流れる第1流路、前記熱源側熱交換器と前記膨張装置との間の冷媒が流れる第2流路、及び、前記膨張装置と前記利用側熱交換器との間の冷媒が流れる第3流路を有し、冷房運転時に前記第1流路を流れる冷媒と前記第2流路を流れる冷媒とを熱交換させ、暖房運転時に前記第1流路を流れる冷媒と前記第3流路を流れる冷媒とを熱交換させる構成の内部熱交換器と、
を備えた空気調和装置。 - 前記内部熱交換器は、
前記第2流路を流れる冷媒及び前記第3流路を流れる冷媒が前記第1流路の同一範囲を流れる冷媒と熱交換する構成である請求項1に記載の空気調和装置。 - 前記内部熱交換器は、
前記第1流路が形成された第1伝熱管の外周部に、前記第2流路が形成された第2伝熱管及び前記第3流路が形成された第3伝熱管が巻き付けられた構成である請求項1又は請求項2に記載の空気調和装置。 - 前記内部熱交換器は、
前記第2流路と前記第3流路との間に、前記第1流路が形成された構成である請求項1又は請求項2に記載の空気調和装置。 - 前記内部熱交換器は、
伝熱部材に前記第1流路、前記第2流路及び前記第3流路が並設され、
前記第2流路と前記第3流路との間に前記第1流路が配置された構成である請求項4に記載の空気調和装置。 - 前記内部熱交換器は、
前記第1流路が形成された第1伝熱管、前記第2流路が形成された第2伝熱管、及び、前記第3流路が形成された第3伝熱管を有し、
前記第2伝熱管又は前記第3伝熱管の一方の内部に前記第1伝熱管が配置され、
前記第1伝熱管の内部に、前記第2伝熱管又は前記第3伝熱管の他方が配置された構成である請求項4に記載の空気調和装置。 - 前記第1伝熱管、前記第2伝熱管及び前記第3伝熱管が円管で形成されている請求項6に記載の空気調和装置。
- 前記第1伝熱管は、多葉状伝熱管である請求項6に記載の空気調和装置。
- R32、HFO1234yf、HFO1234ze、HFO1123及び炭化水素のうちの少なくとも1つを含む冷媒が用いられる請求項1~請求項8のいずれか一項に記載の空気調和装置。
Priority Applications (7)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/JP2014/079213 WO2016071955A1 (ja) | 2014-11-04 | 2014-11-04 | 空気調和装置 |
CN201480082960.5A CN107076467B (zh) | 2014-11-04 | 2014-11-04 | 空气调节装置 |
AU2014410881A AU2014410881B2 (en) | 2014-11-04 | 2014-11-04 | Air-conditioning apparatus |
US15/509,664 US10168069B2 (en) | 2014-11-04 | 2014-11-04 | Air-conditioning apparatus |
JP2015545235A JP5936785B1 (ja) | 2014-11-04 | 2014-11-04 | 空気調和装置 |
EP14905651.7A EP3217115B1 (en) | 2014-11-04 | 2014-11-04 | Air conditioning apparatus |
KR1020177013243A KR102014616B1 (ko) | 2014-11-04 | 2014-11-04 | 공기 조화 장치 |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/JP2014/079213 WO2016071955A1 (ja) | 2014-11-04 | 2014-11-04 | 空気調和装置 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2016071955A1 true WO2016071955A1 (ja) | 2016-05-12 |
Family
ID=55908711
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2014/079213 WO2016071955A1 (ja) | 2014-11-04 | 2014-11-04 | 空気調和装置 |
Country Status (7)
Country | Link |
---|---|
US (1) | US10168069B2 (ja) |
EP (1) | EP3217115B1 (ja) |
JP (1) | JP5936785B1 (ja) |
KR (1) | KR102014616B1 (ja) |
CN (1) | CN107076467B (ja) |
AU (1) | AU2014410881B2 (ja) |
WO (1) | WO2016071955A1 (ja) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2021014525A1 (ja) * | 2019-07-22 | 2021-01-28 | 三菱電機株式会社 | 空気調和装置および室外機 |
WO2023218612A1 (ja) * | 2022-05-12 | 2023-11-16 | 三菱電機株式会社 | 冷凍サイクル装置 |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
SE542346C2 (en) * | 2017-05-22 | 2020-04-14 | Swep Int Ab | Reversible refrigeration system |
CN108375255B (zh) * | 2017-12-29 | 2019-12-06 | 青岛海尔空调器有限总公司 | 空调器系统 |
CN108375248A (zh) * | 2017-12-29 | 2018-08-07 | 青岛海尔空调器有限总公司 | 空调器系统 |
CN108302839A (zh) * | 2017-12-29 | 2018-07-20 | 青岛海尔空调器有限总公司 | 空调器系统 |
CN111059615A (zh) * | 2019-12-20 | 2020-04-24 | 青岛海尔空调电子有限公司 | 多联机空调系统 |
WO2024158952A1 (en) * | 2023-01-25 | 2024-08-02 | Bergstrom, Inc. | Heat pump with multi-pass refrigerant circuit |
Citations (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0275863A (ja) * | 1988-09-09 | 1990-03-15 | Sharp Corp | 冷暖房装置 |
JPH11142007A (ja) * | 1997-11-06 | 1999-05-28 | Nippon Soken Inc | 冷凍サイクル |
JP2003097898A (ja) * | 2001-07-16 | 2003-04-03 | Daikin Ind Ltd | 熱交換器 |
JP2005127711A (ja) * | 2001-06-11 | 2005-05-19 | Daikin Ind Ltd | 冷媒回路 |
JP2006242403A (ja) * | 2005-02-28 | 2006-09-14 | Sanyo Electric Co Ltd | 冷媒サイクル装置 |
JP2007093167A (ja) * | 2005-09-30 | 2007-04-12 | Daikin Ind Ltd | 空気調和機用液ガス熱交換器 |
JP2008096093A (ja) * | 2006-09-11 | 2008-04-24 | Daikin Ind Ltd | 冷凍装置 |
JP2010175204A (ja) * | 2009-01-30 | 2010-08-12 | Fujitsu General Ltd | 冷凍空調装置 |
JP2011179689A (ja) * | 2010-02-26 | 2011-09-15 | Hitachi Appliances Inc | 冷凍サイクル装置 |
JP2012107858A (ja) * | 2012-01-30 | 2012-06-07 | Daikin Industries Ltd | 冷凍装置 |
JP2014132217A (ja) * | 2014-04-17 | 2014-07-17 | Topre Corp | 三重管式熱交換器を用いた冷凍装置 |
JP2014194313A (ja) * | 2013-03-29 | 2014-10-09 | Fujitsu General Ltd | 冷凍サイクル装置 |
Family Cites Families (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS61153356A (ja) | 1984-12-26 | 1986-07-12 | 三菱電機株式会社 | 多室形空気調和機の冷房運転制御装置 |
CA2080219A1 (en) * | 1991-11-04 | 1993-05-05 | Leroy John Herbst | Household refrigerator with improved refrigeration circuit |
JP3801006B2 (ja) | 2001-06-11 | 2006-07-26 | ダイキン工業株式会社 | 冷媒回路 |
US7114349B2 (en) * | 2004-12-10 | 2006-10-03 | Carrier Corporation | Refrigerant system with common economizer and liquid-suction heat exchanger |
JP2006242402A (ja) * | 2005-02-28 | 2006-09-14 | Sanyo Electric Co Ltd | 冷媒サイクル装置 |
EP1695849A1 (en) | 2005-02-28 | 2006-08-30 | Sanyo Electric Co., Ltd. | Refrigerant cycle unit |
JP4787070B2 (ja) * | 2006-05-30 | 2011-10-05 | サンデン株式会社 | 冷凍サイクル |
JP2010014351A (ja) * | 2008-07-04 | 2010-01-21 | Fujitsu General Ltd | 冷凍空調装置 |
KR20170069303A (ko) * | 2009-05-08 | 2017-06-20 | 허니웰 인터내셔널 인코포레이티드 | 열 펌프 온수기용 하이드로플루오로카본 냉매 조성물 |
-
2014
- 2014-11-04 CN CN201480082960.5A patent/CN107076467B/zh active Active
- 2014-11-04 AU AU2014410881A patent/AU2014410881B2/en active Active
- 2014-11-04 US US15/509,664 patent/US10168069B2/en active Active
- 2014-11-04 KR KR1020177013243A patent/KR102014616B1/ko active IP Right Grant
- 2014-11-04 EP EP14905651.7A patent/EP3217115B1/en active Active
- 2014-11-04 JP JP2015545235A patent/JP5936785B1/ja active Active
- 2014-11-04 WO PCT/JP2014/079213 patent/WO2016071955A1/ja active Application Filing
Patent Citations (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0275863A (ja) * | 1988-09-09 | 1990-03-15 | Sharp Corp | 冷暖房装置 |
JPH11142007A (ja) * | 1997-11-06 | 1999-05-28 | Nippon Soken Inc | 冷凍サイクル |
JP2005127711A (ja) * | 2001-06-11 | 2005-05-19 | Daikin Ind Ltd | 冷媒回路 |
JP2003097898A (ja) * | 2001-07-16 | 2003-04-03 | Daikin Ind Ltd | 熱交換器 |
JP2006242403A (ja) * | 2005-02-28 | 2006-09-14 | Sanyo Electric Co Ltd | 冷媒サイクル装置 |
JP2007093167A (ja) * | 2005-09-30 | 2007-04-12 | Daikin Ind Ltd | 空気調和機用液ガス熱交換器 |
JP2008096093A (ja) * | 2006-09-11 | 2008-04-24 | Daikin Ind Ltd | 冷凍装置 |
JP2010175204A (ja) * | 2009-01-30 | 2010-08-12 | Fujitsu General Ltd | 冷凍空調装置 |
JP2011179689A (ja) * | 2010-02-26 | 2011-09-15 | Hitachi Appliances Inc | 冷凍サイクル装置 |
JP2012107858A (ja) * | 2012-01-30 | 2012-06-07 | Daikin Industries Ltd | 冷凍装置 |
JP2014194313A (ja) * | 2013-03-29 | 2014-10-09 | Fujitsu General Ltd | 冷凍サイクル装置 |
JP2014132217A (ja) * | 2014-04-17 | 2014-07-17 | Topre Corp | 三重管式熱交換器を用いた冷凍装置 |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2021014525A1 (ja) * | 2019-07-22 | 2021-01-28 | 三菱電機株式会社 | 空気調和装置および室外機 |
JPWO2021014525A1 (ja) * | 2019-07-22 | 2021-11-18 | 三菱電機株式会社 | 空気調和装置および室外機 |
WO2023218612A1 (ja) * | 2022-05-12 | 2023-11-16 | 三菱電機株式会社 | 冷凍サイクル装置 |
Also Published As
Publication number | Publication date |
---|---|
AU2014410881A1 (en) | 2017-04-13 |
US20170284713A1 (en) | 2017-10-05 |
US10168069B2 (en) | 2019-01-01 |
CN107076467B (zh) | 2020-01-17 |
EP3217115A1 (en) | 2017-09-13 |
CN107076467A (zh) | 2017-08-18 |
EP3217115A4 (en) | 2018-07-18 |
JPWO2016071955A1 (ja) | 2017-04-27 |
AU2014410881B2 (en) | 2018-01-18 |
EP3217115B1 (en) | 2019-12-25 |
KR20170074917A (ko) | 2017-06-30 |
KR102014616B1 (ko) | 2019-08-26 |
JP5936785B1 (ja) | 2016-06-22 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
JP5936785B1 (ja) | 空気調和装置 | |
JP3982545B2 (ja) | 空気調和装置 | |
JP5847366B1 (ja) | 空気調和装置 | |
US7464563B2 (en) | Air-conditioner having a dual-refrigerant cycle | |
JP5908183B1 (ja) | 空気調和装置 | |
US20100058800A1 (en) | Air conditioning apparatus | |
US10126026B2 (en) | Refrigeration cycle apparatus | |
JP2005083741A (ja) | 熱交換器及び冷媒切り替え手段を有する空調装置 | |
WO2012101672A1 (ja) | 空気調和装置 | |
JP5277854B2 (ja) | 空気調和装置 | |
JP6576603B1 (ja) | 空気調和装置 | |
JP2018059638A (ja) | 熱交換器および冷凍サイクル装置 | |
WO2019198175A1 (ja) | 冷凍サイクル装置 | |
JP2012237518A (ja) | 空気調和機 | |
JP2007093167A (ja) | 空気調和機用液ガス熱交換器 | |
KR20050043089A (ko) | 히트 펌프 | |
KR102136749B1 (ko) | 공기 조화기 | |
WO2021166126A1 (ja) | 空気調和装置 | |
JP2015141006A (ja) | 空気調和装置 | |
JP2008196843A (ja) | 冷凍装置 |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
ENP | Entry into the national phase |
Ref document number: 2015545235 Country of ref document: JP Kind code of ref document: A |
|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 14905651 Country of ref document: EP Kind code of ref document: A1 |
|
WWE | Wipo information: entry into national phase |
Ref document number: 15509664 Country of ref document: US |
|
ENP | Entry into the national phase |
Ref document number: 2014410881 Country of ref document: AU Date of ref document: 20141104 Kind code of ref document: A |
|
NENP | Non-entry into the national phase |
Ref country code: DE |
|
ENP | Entry into the national phase |
Ref document number: 20177013243 Country of ref document: KR Kind code of ref document: A |
|
REEP | Request for entry into the european phase |
Ref document number: 2014905651 Country of ref document: EP |