JP2013108729A - Air conditioner - Google Patents

Abstract

PROBLEM TO BE SOLVED: To suppress ice-up phenomenon in a heating operation after a defrosting operation, in an air conditioner executing the heating operation and the inverse cycle defrosting operation.SOLUTION: This air conditioner (1) includes an antifreeze heat exchanger (25) capable of heating a lower side of an outdoor heat exchanger (23) by a part of a refrigerant compressed in a compressing mechanism (21), and executes an antifreeze control in restarting of heating by allowing a part of the refrigerant compressed by the compressing mechanism (21), to flow to the antifreeze heat exchanger (25) at an initial period of restarting of the heating operation after the defrosting operation.

Description

  The present invention relates to an air conditioner, and more particularly to an air conditioner that performs a heating operation and a reverse cycle defrosting operation.

  Conventionally, there is an air conditioner that performs heating operation and reverse cycle defrosting operation. In such an air conditioner, when heating operation is performed under a condition where the outside air temperature is low, frost formation occurs in the outdoor heat exchanger that functions as a refrigerant evaporator. The frost generated in the outdoor heat exchanger in the heating operation is melted by performing the reverse cycle defrosting operation, and is discharged as drain water through the bottom plate of the outdoor unit disposed below the outdoor heat exchanger. Here, in the reverse cycle defrosting operation, the refrigerant is circulated in the order of the compressor, the outdoor heat exchanger, and the indoor heat exchanger, so that the outdoor heat exchanger is heated by the refrigerant compressed in the compressor. Driving. Moreover, the bottom plate of the outdoor unit functions as a drain pan.

  However, under conditions where the outside air temperature is low, the drain water generated during the reverse cycle defrosting operation may freeze on the lower side of the outdoor heat exchanger. Such freezing of drain water may cause excessive ice growth (ice-up phenomenon) on the lower side of the outdoor heat exchanger.

  On the other hand, as shown in patent document 1 (Unexamined-Japanese-Patent No. 2009-127939), the auxiliary heat exchanger was provided in the lower part side of the outdoor heat exchanger, and it was compressed in the compressor at the time of reverse cycle defrosting operation. There is an air conditioner configured to heat an auxiliary heat exchanger with a part of a refrigerant.

  In the said conventional air conditioning apparatus, freezing of drain water at the time of a defrost operation can be prevented.

  However, for a while after the defrosting operation is completed, the drain water melted by performing the defrosting operation exists on the lower side of the outdoor heat exchanger, and the drain water continues to be discharged. Thereafter, when the heating operation is resumed, there is a possibility that the drain water is frozen before the drain water is discharged under a condition where the outside air temperature is low. For this reason, in the said conventional air conditioning apparatus, freezing of drain water at the time of the heating operation after a defrost operation cannot be prevented, and there exists a possibility that an ice-up phenomenon may generate | occur | produce.

  The subject of this invention is suppressing the generation | occurrence | production of the ice-up phenomenon at the time of the heating operation after a defrost operation in the air conditioning apparatus which performs a heating operation and a reverse cycle defrost operation.

  An air conditioner according to a first aspect performs a heating operation by circulating a refrigerant in the order of a compression mechanism, an indoor heat exchanger, and an outdoor heat exchanger, and the compression mechanism, the outdoor heat exchanger, and the indoor heat exchange. It is an air conditioner that performs a defrosting operation by circulating refrigerant in the order of the units. In this air conditioner, a freezing prevention heat exchanger capable of heating the lower side of the outdoor heat exchanger with a part of the refrigerant compressed in the compression mechanism is provided, and the heating operation after the defrosting operation is performed. In the early stage of restart, freeze prevention control at the time of resuming heating is performed in which a part of the refrigerant compressed in the compression mechanism is passed through the freeze prevention heat exchanger.

  In this air conditioner, during the heating operation after the defrosting operation, a part of the refrigerant compressed in the compression mechanism is caused to flow through the antifreezing heat exchanger, so that the outdoor heat is removed after the defrosting operation under a condition where the outside air temperature is low. The drain water present on the lower side of the exchanger can be discharged without freezing. For this reason, in this air conditioner, it is possible to suppress the occurrence of the ice-up phenomenon during the heating operation after the defrosting operation.

  Here, in the heating operation after the defrosting operation, flowing a part of the refrigerant compressed in the compression mechanism to the anti-freezing heat exchanger reduces the flow rate of the refrigerant sent to the indoor heat exchanger. , Will reduce the heating capacity.

  Therefore, in this air conditioner, as described above, a part of the refrigerant compressed in the compression mechanism is allowed to flow to the antifreezing heat exchanger only in the early stage of the heating operation after the defrosting operation. I have to. For this reason, in this air conditioning apparatus, the fall of the heating capability in the heating operation after a defrost operation can be suppressed.

  Thereby, in this air conditioning apparatus, generation | occurrence | production of the ice-up phenomenon at the time of the heating operation after a defrost operation can be suppressed, suppressing the fall of the heating capability in the heating operation after a defrost operation.

  In the air conditioner according to the second aspect, the air conditioner according to the second aspect performs the freeze prevention control at the time of resuming heating when the outside air temperature is equal to or lower than a predetermined outside air temperature.

  In this air conditioner, after the defrosting operation, only when the outside air temperature at which the drain water existing on the lower side of the outdoor heat exchanger is likely to freeze is low, anti-freezing control when resuming heating is performed, and the outside air temperature is high. In this case, it is possible to avoid the freeze prevention control when resuming heating.

  Thereby, in this air conditioning apparatus, the fall of the heating capability in the heating operation after a defrost operation can further be suppressed.

  In the air conditioner according to the third aspect, the air conditioner according to the first or second aspect performs the anti-freezing control when resuming heating until a predetermined time elapses after the defrosting operation.

  In this air conditioner, since the freeze prevention control at the time of resuming heating is managed by time, the time necessary for discharging drain water present on the lower side of the outdoor heat exchanger after defrosting operation is taken into consideration. be able to.

  Thereby, in this air conditioning apparatus, the freeze prevention control at the time of resuming heating can be appropriately performed in consideration of the time required for discharging drain water.

  The air conditioner according to the fourth aspect is the air conditioner according to the third aspect. As the outside air temperature decreases, the outside air humidity increases, or the operating time of the defrosting operation increases. Increase time.

  The amount of drain water present on the lower side of the outdoor heat exchanger after the defrosting operation varies depending on the outside air temperature, the outside air humidity, or the operation time of the defrosting operation. Specifically, the amount of drain water increases as the outside air temperature decreases, the outside air humidity increases, or the operating time of the defrosting operation increases. For this reason, it is preferable to change also about the predetermined time of anti-freezing control at the time of heating resumption according to the outside air temperature, the outside air humidity, or the operating time of the defrosting operation.

  Therefore, in this air conditioner, as described above, the predetermined time is increased as the outside air temperature decreases, the outside air humidity increases, or the operating time of the defrosting operation increases. For this reason, in this air conditioning apparatus, it is possible to consider the amount of drain water that changes depending on the outside air temperature, the outside air humidity, or the operating time of the defrosting operation.

  Thereby, in this air conditioner, it is possible to appropriately perform the freeze prevention control at the time of resuming heating in consideration of a change in the amount of drain water due to conditions such as the outside air temperature.

  An air conditioner according to a fifth aspect is the air conditioner according to any one of the first to third aspects, further comprising a flow rate adjusting valve for varying a flow rate of the refrigerant flowing through the antifreezing heat exchanger. As the outside air temperature decreases, the outside air humidity increases, or the operating time of the defrosting operation increases, the opening degree of the flow control valve is increased.

  The amount of drain water present on the lower side of the outdoor heat exchanger after the defrosting operation varies depending on the outside air temperature, the outside air humidity, or the operation time of the defrosting operation. Specifically, the amount of drain water increases as the outside air temperature decreases, the outside air humidity increases, or the operating time of the defrosting operation increases. For this reason, it is preferable to change the flow rate of the refrigerant flowing through the antifreezing heat exchanger in the antifreezing control when resuming heating depending on the outside air temperature, the outside air humidity, or the operating time of the defrosting operation.

  Therefore, in this air conditioner, as described above, the opening degree of the flow control valve is increased as the outside air temperature decreases, the outside air humidity increases, or the operating time of the defrosting operation increases. The flow rate of the refrigerant is increased. For this reason, in this air conditioning apparatus, it is possible to consider the amount of drain water that changes depending on the outside air temperature, the outside air humidity, or the operating time of the defrosting operation.

  Thereby, in this air conditioner, it is possible to appropriately perform the freeze prevention control at the time of resuming heating in consideration of a change in the amount of drain water due to conditions such as the outside air temperature.

  As described above, according to the present invention, the following effects can be obtained.

  In the air conditioner according to the first aspect, it is possible to suppress the occurrence of the ice-up phenomenon during the heating operation after the defrosting operation while suppressing a decrease in the heating capacity during the heating operation after the defrosting operation.

  In the air conditioning apparatus according to the second aspect, it is possible to further suppress a decrease in the heating capacity in the heating operation after the defrosting operation.

  In the air conditioning apparatus according to the third aspect, it is possible to appropriately perform the anti-freezing control when resuming the heating in consideration of the time required for discharging the drain water.

  In the air conditioner according to the fourth aspect, it is possible to appropriately perform the freeze prevention control when resuming heating in consideration of a change in the amount of drain water due to conditions such as the outside air temperature.

  In the air conditioner according to the fifth aspect, the antifreezing control at the time of resuming heating can be appropriately performed in consideration of a change in the amount of drain water due to conditions such as the outside air temperature.

It is a schematic structure figure of the air harmony device concerning a 1st embodiment of the present invention. It is a schematic diagram which shows the lower part side of the outdoor heat exchanger containing the heat exchanger for freezing prevention, and the baseplate of an outdoor unit. It is a control block diagram of the air conditioning apparatus concerning 1st Embodiment. It is a schematic block diagram which shows the flow of the refrigerant | coolant at the time of air_conditionaing | cooling operation and defrost operation of the air conditioning apparatus concerning 1st Embodiment. It is a schematic block diagram which shows the flow of the refrigerant | coolant at the time of the heating operation of the air conditioning apparatus concerning 1st Embodiment. It is a flowchart of antifreezing control at the time of heating resumption of the air harmony device concerning a 1st embodiment. It is a schematic block diagram which shows the flow of the refrigerant | coolant at the time of freeze prevention control at the time of the heating resumption of the air conditioning apparatus concerning 1st Embodiment. It is a flowchart of the freeze prevention control at the time of heating resumption of the air conditioning apparatus concerning the modification 1 of 1st Embodiment. It is a schematic block diagram of the air conditioning apparatus concerning the modification 2 of 1st Embodiment of this invention. It is a flowchart of the freeze prevention control at the time of heating resumption of the air conditioning apparatus concerning the modification 2 of 1st Embodiment. It is a schematic block diagram of the air conditioning apparatus concerning 2nd Embodiment of this invention. It is a control block diagram of the air conditioning apparatus concerning 2nd Embodiment. It is a schematic block diagram which shows the flow of the refrigerant | coolant at the time of the air_conditionaing | cooling operation and single stage defrost operation of the air conditioning apparatus concerning 2nd Embodiment. It is a schematic block diagram which shows the flow of the refrigerant | coolant at the time of the single stage heating operation of the air conditioning apparatus concerning 2nd Embodiment. It is a schematic block diagram which shows the flow of the refrigerant | coolant at the time of the two-stage heating operation of the air conditioning apparatus concerning 2nd Embodiment. It is a schematic block diagram which shows the flow of the refrigerant | coolant at the time of the two-stage defrost operation of the air conditioning apparatus concerning 2nd Embodiment. It is a flowchart of the freeze prevention control at the time of the heating resumption of the air conditioning apparatus concerning 2nd Embodiment. It is a schematic block diagram which shows the flow of the refrigerant | coolant at the time of freeze prevention control at the time of the heating resumption of the air conditioning apparatus concerning 2nd Embodiment.

  DESCRIPTION OF EMBODIMENTS Hereinafter, embodiments of an air conditioner according to the present invention will be described based on the drawings.

-First embodiment-
(1) Configuration of Air Conditioner FIG. 1 is a schematic configuration diagram of an air conditioner 1 according to the first embodiment of the present invention. The air conditioning apparatus 1 is an apparatus used for air conditioning in a room such as a building by performing a vapor compression refrigeration cycle. The air conditioner 1 mainly includes a single outdoor unit 2, a plurality (in this case, two) of indoor units 5 and 6, and a liquid refrigerant communication pipe that connects the outdoor unit 2 and the indoor units 5 and 6. 7 and a gas refrigerant communication pipe 8. That is, the vapor compression refrigerant circuit 10 of the air conditioner 1 is configured by connecting the outdoor unit 2, the indoor units 5 and 6, the liquid refrigerant communication tube 7 and the gas refrigerant communication tube 8. . Note that the number of indoor units 5 and 6 is not limited to two, and may be one or three or more.

<Indoor unit>
The indoor units 5 and 6 are installed by embedding or hanging in a ceiling of a room such as a building or hanging on a wall surface of the room. The indoor units 5 and 6 are connected to the outdoor unit 2 via the liquid refrigerant communication pipe 7 and the gas refrigerant communication pipe 8 and constitute a part of the refrigerant circuit 10.

  Next, the configuration of the indoor units 5 and 6 will be described. In addition, since the indoor unit 5 and the indoor unit 6 have the same configuration, only the configuration of the indoor unit 5 will be described here, and the configuration of the indoor unit 6 is the 50th number indicating each part of the indoor unit 5. The reference numerals in the 60s are attached instead of the reference numerals, and description of each part is omitted.

  The indoor unit 5 mainly has an indoor expansion valve 51 and an indoor heat exchanger 52.

  The indoor expansion valve 51 is a device that adjusts the pressure and flow rate of the refrigerant flowing through the indoor unit 5. The indoor expansion valve 51 has one end connected to the liquid side of the indoor heat exchanger 52 and the other end connected to the liquid refrigerant communication tube 7. Here, an electric expansion valve is used as the indoor expansion valve 51.

  The indoor heat exchanger 52 is a heat exchanger that functions as a refrigerant evaporator during cooling operation to cool indoor air and functions as a refrigerant condenser during heating operation to heat indoor air. The indoor heat exchanger 52 has a liquid side connected to the indoor expansion valve 51 and a gas side connected to the gas refrigerant communication tube 8. Here, the indoor heat exchanger 52 is a cross-fin type fin-and-tube heat exchanger composed of heat transfer tubes and a large number of fins. The type of the indoor heat exchanger 52 is not limited to the cross fin type fin-and-tube type heat exchanger, and other types such as a laminated heat exchanger using corrugated fins or flat tubes, for example. It may be a type of heat exchanger.

  The indoor unit 5 has an indoor fan 53 for supplying indoor air as supply air after sucking indoor air into the indoor unit 5 and exchanging heat with the refrigerant in the indoor heat exchanger 52. . Here, as the indoor fan 53, a centrifugal fan or a multi-blade fan driven by an indoor fan motor 53a is used.

  The indoor unit 5 includes an indoor side control unit 54 that controls the operation of each unit constituting the indoor unit 5. And the indoor side control part 54 has a microcomputer, memory, etc. for controlling the indoor unit 5, and between the remote controllers (not shown) for operating the indoor unit 5 separately. Control signals and the like can be exchanged, and control signals and the like can be exchanged with the outdoor unit 2 via the transmission line 9a.

<Outdoor unit>
The outdoor unit 2 is installed outside a building or the like. The outdoor unit 2 is connected to the indoor units 5 and 6 via the liquid refrigerant communication pipe 7 and the gas refrigerant communication pipe 8 and constitutes a part of the refrigerant circuit 10.

  Next, the configuration of the outdoor unit 2 will be described. The outdoor unit 2 mainly includes a compressor 21 as a compression mechanism, a switching mechanism 22, an outdoor heat exchanger 23, an outdoor expansion valve 24, and a freezing prevention heat exchanger 25.

  The compressor 21 is a device that compresses the low-pressure refrigerant in the refrigeration cycle until the pressure becomes high. The compressor 21 has a hermetic structure in which a rotary type or scroll type positive displacement compression element (not shown) is rotationally driven by a compressor motor 21a. The compressor 21 has a first gas refrigerant pipe 26a connected to the suction side and a second gas refrigerant pipe 26b connected to the discharge side. The first gas refrigerant pipe 26 a is a refrigerant pipe that connects the suction side of the compressor 21 and the first port 22 a of the switching mechanism 22. The second gas refrigerant pipe 26 b is a refrigerant pipe that connects the discharge side of the compressor 21 and the second port 22 b of the switching mechanism 22. Here, although one compressor 21 constitutes a compression mechanism, a compression mechanism may be constituted by connecting a plurality of compressors 21 in parallel.

  The switching mechanism 22 is a mechanism for switching the direction of refrigerant flow in the refrigerant circuit 10. The switching mechanism 22 causes the outdoor heat exchanger 23 to function as a condenser for the refrigerant compressed in the compressor 21 during the cooling operation and the defrosting operation, and causes the indoor heat exchangers 52 and 62 to function as the outdoor heat exchanger 23. Is switched to function as an evaporator for the refrigerant condensed in step. That is, the switching mechanism 22 switches between the second port 22b and the third port 22c and the first port 22a and the fourth port 22d during the cooling operation and the defrosting operation. Thereby, the discharge side (here, the second gas refrigerant pipe 26b) of the compressor 21 and the gas side (here, the third gas refrigerant pipe 26c) of the outdoor heat exchanger 23 are connected (switching in FIG. 1). (See solid line for mechanism 22). Moreover, the suction side (here, the first gas refrigerant pipe 26a) of the compressor 21 and the gas refrigerant communication pipe 8 side (here, the fourth gas refrigerant pipe 26d) are connected (of the switching mechanism 22 of FIG. 1). (See solid line). Further, the switching mechanism 22 causes the outdoor heat exchanger 23 to function as an evaporator of the refrigerant condensed in the indoor heat exchangers 42 and 52 during the heating operation, and compresses the indoor heat exchangers 52 and 62 in the compressor 21. Switch to function as a condenser for the refrigerant. That is, during the heating operation, the switching mechanism 22 switches the second port 22b and the fourth port 22d to communicate and the first port 22a and the third port 22c to communicate. Thereby, the discharge side (here, the second gas refrigerant pipe 26b) of the compressor 21 and the gas refrigerant communication pipe 8 side (here, the fourth gas refrigerant pipe 26d) are connected (the switching mechanism 22 in FIG. 1). See the dashed line). Moreover, the suction side (here, the first gas refrigerant pipe 26a) of the compressor 21 and the gas side (here, the third gas refrigerant pipe 26c) of the outdoor heat exchanger 23 are connected (the switching mechanism in FIG. 1). (See dashed line 22). The third gas refrigerant pipe 26 c is a refrigerant pipe that connects the third port 22 c of the switching mechanism 22 and the gas side of the outdoor heat exchanger 23. The fourth gas refrigerant pipe 26d is a refrigerant pipe that connects the fourth port 22d of the switching mechanism 22 and the gas refrigerant communication pipe 8 side. Here, the switching mechanism 22 is a four-way switching valve. Here, the configuration of the switching mechanism 22 is not limited to the four-way switching valve, and may be, for example, a configuration in which a plurality of electromagnetic valves or the like are connected so as to perform the above switching function.

  The outdoor heat exchanger 23 is a heat exchanger that functions as a refrigerant condenser during a cooling operation and a defrosting operation, and functions as a refrigerant evaporator during a heating operation. The outdoor heat exchanger 23 has a liquid side connected to the liquid refrigerant pipe 26e and a gas side connected to the third gas refrigerant pipe 26c. The liquid refrigerant pipe 26e is a refrigerant pipe that connects the liquid side of the outdoor heat exchanger 23 and the liquid refrigerant communication pipe 7 side. Here, the outdoor heat exchanger 23 is a cross-fin type fin-and-tube heat exchanger composed of heat transfer tubes and a large number of fins. The type of the outdoor heat exchanger 23 is not limited to a cross fin type fin-and-tube type heat exchanger, and other types such as a laminated heat exchanger using corrugated fins or flat tubes, for example. It may be a type of heat exchanger.

  The outdoor expansion valve 24 is a device that adjusts the pressure and flow rate of the refrigerant flowing through the outdoor unit 2. The outdoor expansion valve 24 is provided in the liquid refrigerant pipe 26e. Here, an electric expansion valve is used as the outdoor expansion valve 24.

  The antifreezing heat exchanger 25 is a heat exchanger that heats the lower side of the outdoor heat exchanger 23 with a part of the refrigerant compressed in the compressor 21 as a compression mechanism. The antifreezing heat exchanger 25 is provided in the hot gas bypass pipe 27. Here, the anti-freezing heat exchanger 25 is a cross-fin type fin-and-tube heat exchanger composed of heat transfer tubes and a large number of fins, and as shown in FIG. 2, an outdoor heat exchanger. 23 is integrated with the lower part. Specifically, the outdoor heat exchanger 23 and the antifreezing heat exchanger 25 are configured as an integral fin-and-tube heat exchanger, and the heat transfer tubes and fins on the upper side are the outdoor heat exchanger 23. The heat transfer tubes and fins on the lower side constitute a heat exchanger 25 for preventing freezing. The lower end portion of the freeze prevention heat exchanger 25 is disposed on the bottom plate 2 a of the outdoor unit 2 that functions as a drain pan that receives drain water generated in the outdoor heat exchanger 23 and the freeze prevention heat exchanger 25. The bottom plate 2 a is formed with a discharge port 2 b so that drain water received on the bottom plate 2 a can be discharged out of the outdoor unit 2. Here, FIG. 2 is a schematic view showing the lower side of the outdoor heat exchanger 23 including the freeze-preventing heat exchanger 25 and the bottom plate 2 a of the outdoor unit 2. The type of the anti-freezing heat exchanger 25 is not limited to the cross-fin type fin-and-tube type heat exchanger, for example, a laminated heat exchanger using corrugated fins or flat tubes, etc. Other types of heat exchangers may be used.

  The hot gas bypass pipe 27 is a refrigerant pipe that branches a part of the refrigerant compressed in the compressor 21. One end side of the hot gas bypass pipe 27 is connected so as to branch from a middle portion of the second gas refrigerant pipe 26c, and the other end side is connected to the liquid side of the outdoor heat exchanger 23 of the liquid refrigerant pipe 26e and the outdoor expansion valve 24. It is connected to join the part between. A hot gas decompression mechanism 27a, a hot gas opening / closing mechanism 27b, and a hot gas check mechanism 27c are provided at a portion of the hot gas bypass pipe 27 on the outlet side of the heat exchanger 25 for preventing freezing. The hot gas decompression mechanism 27a is a device that decompresses the refrigerant. Here, a capillary tube is used as the hot gas decompression mechanism 27a. The hot gas opening / closing mechanism 27b is opened when a part of the refrigerant compressed in the compressor 21 is branched into the hot gas bypass pipe 27, and a part of the refrigerant compressed in the compressor 21 is branched into the hot gas bypass pipe 27. It is a device that can be closed if not. Here, an electromagnetic valve is used as the hot gas opening / closing mechanism 27b. The hot gas check mechanism 27c is a mechanism that allows the flow of the refrigerant from the outlet side of the antifreezing heat exchanger 25 to the liquid refrigerant tube 26e side and blocks the flow in the reverse direction. Here, a check valve is used as the hot gas check mechanism 27c.

  The outdoor unit 2 has an outdoor fan 28 for sucking outdoor air into the outdoor unit 2, exchanging heat with the refrigerant in the outdoor heat exchanger 23, and then discharging the air outside the outdoor unit 2. . Here, as the outdoor fan 28, an axial fan or the like driven by an outdoor fan motor 28a is used. Further, as shown in FIG. 2, the anti-freezing heat exchanger 25 is integrated with the lower part of the outdoor heat exchanger 23. Therefore, the outdoor fan 28 is not only the outdoor heat exchanger 23 but also the anti-freezing heat. Outdoor air is also supplied to the exchanger 25.

  The outdoor unit 2 is provided with various sensors. Specifically, the outdoor unit 2 is mainly provided with a suction pressure sensor 29a, a discharge pressure sensor 29b, an outdoor heat exchange temperature sensor 29c, and an outdoor temperature sensor 29d. The suction pressure sensor 29a is a pressure sensor that detects the suction pressure Ps of the compressor 21 corresponding to the low pressure in the refrigeration cycle. The discharge pressure sensor 29b is a pressure sensor that detects the discharge pressure Pd of the compressor 21 corresponding to the high pressure in the refrigeration cycle. The outdoor heat exchange temperature sensor 29 c is a temperature sensor that detects the temperature Tb of the refrigerant flowing through the outdoor heat exchanger 23. The outside air temperature sensor 29d is a temperature sensor that detects the outside air temperature Ta in the outdoor unit 2.

  The outdoor unit 2 also has an outdoor control unit 30 that controls the operation of each part constituting the outdoor unit 2. And the outdoor side control part 30 has a microcomputer, memory, etc. for controlling the outdoor unit 2, and connects the transmission line 9a between the indoor side control parts 54 and 64 of the indoor units 5 and 6. It is possible to exchange control signals and the like through the network. That is, the control part 9 which performs operation control of the whole air conditioning apparatus 1 is comprised by the indoor side control parts 54 and 64, the outdoor side control part 30, and the transmission line 9a which connects between the control parts 30,54,64. Yes.

  As illustrated in FIG. 3, the control unit 9 is configured to perform various devices and valves 21 a, 22, 24, 27 b, 28 a, 51, 53 a, 61, 63 a based on various operation settings and detection values of the various sensors 29 a to 29 d. Can be controlled. Here, FIG. 3 is a control block diagram of the air conditioner 1.

<Refrigerant communication pipe>
Refrigerant communication pipes 7 and 8 are refrigerant pipes constructed on site when the air conditioner 1 is installed at an installation location such as a building, and installation conditions such as an installation location and a combination of an outdoor unit and an indoor unit. Those having various lengths and tube diameters are used.

  As described above, the refrigerant circuit 10 of the air conditioner 1 is configured by connecting the outdoor unit 2, the indoor units 5 and 6, and the refrigerant communication pipes 7 and 8. The air conditioner 1 is operated by the control unit 9 including the indoor side control units 54 and 64 and the outdoor side control unit 30, and various operations such as a cooling operation, a heating operation, and a defrosting operation described below. Can be done.

(2) Operation of the Air Conditioner The air conditioner 1 can mainly perform a cooling operation, a heating operation, and a defrosting operation. The cooling operation is an operation in which the refrigerant is circulated mainly in the order of the compressor 21, the outdoor heat exchanger 23, and the indoor heat exchangers 52 and 62 as a compression mechanism in order to cool the indoor air. The heating operation is an operation in which the refrigerant is circulated mainly in the order of the compressor 21 as the compression mechanism, the indoor heat exchangers 52 and 62, and the outdoor heat exchanger 23 in order to heat the indoor air. In order to melt the frost generated in the outdoor heat exchanger 23 by the heating operation, the defrosting operation is mainly performed in the order of the compressor 21, the outdoor heat exchanger 23, and the indoor heat exchangers 52 and 62 as a compression mechanism. It is an operation to circulate. That is, the defrosting operation is a so-called reverse cycle defrosting operation in which the flow direction of the refrigerant is reversed from that of the heating operation. Hereinafter, operations during various operations of the air conditioner 1 will be described.

<Cooling operation>
First, the cooling operation will be described with reference to FIG. Here, FIG. 4 is a schematic configuration diagram illustrating the flow of the refrigerant during the cooling operation of the air-conditioning apparatus 1.

  During the cooling operation, the switching mechanism 22 is switched to the state indicated by the solid line in FIG. 4, that is, the communication between the second port 22b and the third port 22c and the communication between the first port 22a and the fourth port 22d. Do. Thus, in the refrigerant circuit 10, the outdoor heat exchanger 23 functions as a condenser for the refrigerant compressed in the compressor 21, and the indoor heat exchangers 52 and 62 are evaporated in the outdoor heat exchanger 23. A refrigeration cycle is made to function as a vessel.

  In the refrigerant circuit 10, low-pressure gas refrigerant in the refrigeration cycle is sucked into the compressor 21 and compressed to become high-pressure gas refrigerant. This high-pressure gas refrigerant is sent to the outdoor heat exchanger 23 through the switching mechanism 22, exchanges heat with the outdoor air supplied by the outdoor fan 28, and condenses to become a high-pressure liquid refrigerant. The high-pressure liquid refrigerant is sent to the indoor expansion valves 51 and 61 through the outdoor expansion valve 24 and the liquid refrigerant communication pipe 7, and is reduced in pressure to become a low-pressure refrigerant. The low-pressure refrigerant is sent to the indoor heat exchangers 52 and 62, exchanges heat with the indoor air supplied by the indoor fans 53 and 63, and evaporates to become a low-pressure gas refrigerant. The low-pressure gas refrigerant is again sucked into the compressor 21 through the gas refrigerant communication pipe 8 and the switching mechanism 22.

  During this cooling operation, the hot gas opening / closing mechanism 27b is opened. For this reason, a part of the high-pressure refrigerant that is compressed in the compressor 21 and flows through the second gas refrigerant pipe 26 b is branched to the hot gas bypass pipe 27. The high-pressure refrigerant branched into the hot gas bypass pipe 27 is sent to the antifreezing heat exchanger 25 to heat the lower side of the outdoor heat exchanger 23. That is, the antifreezing heat exchanger 25 functions as a refrigerant condenser, similarly to the outdoor heat exchanger 23. Thereby, a part of the high-pressure gas refrigerant compressed in the compressor 21 is sent to the antifreezing heat exchanger 25 through the hot gas bypass pipe 27 and exchanges heat with the outdoor air supplied by the outdoor fan 28. It goes and condenses to become a high-pressure liquid refrigerant. The high-pressure liquid refrigerant is sent to the liquid refrigerant pipe 26e through the hot gas decompression mechanism 27a, the hot gas opening / closing mechanism 27b, and the hot gas check mechanism 27c, and merges with the high-pressure liquid refrigerant from the outdoor heat exchanger 23. Thus, in the air conditioner 1, not only the outdoor heat exchanger 23 but also the antifreezing heat exchanger 25 functions as a refrigerant condenser during the cooling operation. Thereby, in the air conditioner 1, cooling of the refrigerant sent to the indoor heat exchangers 52 and 62 is promoted during the cooling operation, compared to a case where only the outdoor heat exchanger 23 functions as a refrigerant condenser, The cooling capacity is improved.

<Heating operation>
Next, the heating operation will be described with reference to FIG. Here, FIG. 5 is a schematic configuration diagram illustrating the flow of the refrigerant during the heating operation of the air-conditioning apparatus 1.

  During the heating operation, the switching mechanism 22 is switched to the state indicated by the broken line in FIG. 5, that is, the communication between the second port 22b and the fourth port 22d and the communication between the first port 22a and the third port 22c. Do. Thus, in the refrigerant circuit 10, the outdoor heat exchanger 23 functions as an evaporator for the refrigerant condensed in the indoor heat exchangers 42 and 52, and the indoor heat exchangers 52 and 62 are compressed in the compressor 21. A refrigeration cycle is performed to function as a condenser.

  In the refrigerant circuit 10, low-pressure gas refrigerant in the refrigeration cycle is sucked into the compressor 21 and compressed to become high-pressure gas refrigerant. The high-pressure gas refrigerant is sent to the indoor heat exchangers 52 and 62 through the switching mechanism 22 and the gas refrigerant communication pipe 8, exchanges heat with indoor air supplied by the indoor fans 53 and 63, and condenses to high pressure. It becomes a liquid refrigerant. The high-pressure liquid refrigerant is sent to the outdoor expansion valve 24 through the indoor expansion valves 51 and 61 and the liquid refrigerant communication pipe 7, and is decompressed to become a low-pressure refrigerant. The low-pressure refrigerant is sent to the outdoor heat exchanger 23, exchanges heat with outdoor air supplied by the outdoor fan 28, and evaporates to become a low-pressure gas refrigerant. This low-pressure gas refrigerant is again sucked into the compressor 21 through the switching mechanism 22.

  During this heating operation, the hot gas opening / closing mechanism 27b is closed except when performing anti-freezing control when resuming heating, which will be described later. For this reason, the high-pressure refrigerant that is compressed in the compressor 21 and flows through the second gas refrigerant pipe 26b is not branched to the hot gas bypass pipe 27 except when the anti-freezing control at the time of resuming heating described later is performed. That is, during the heating operation, the refrigerant does not flow through the anti-freezing heat exchanger 25, except when performing anti-freezing control when resuming heating, which will be described later. As described above, in the air conditioner 1, all the high-pressure gas refrigerant compressed in the compressor 21 is heated in the indoor heat exchangers 52 and 62 except for the case where the antifreezing control at the time of resuming heating described later is performed during the heating operation. To be sent to. Thus, in the air conditioning apparatus 1, the flow rate of the refrigerant sent to the indoor heat exchangers 52 and 62 is larger than that in the case where the refrigerant is passed through the antifreezing heat exchanger 25 during the heating operation, and the heating capacity is increased. The decline of the is suppressed.

<Defrosting operation>
Next, the defrosting operation will be described with reference to FIG. Here, FIG. 4 is a schematic configuration diagram illustrating the flow of the refrigerant during the defrosting operation of the air conditioner 1.

  As described above, the defrosting operation is a reverse cycle defrosting operation in which the refrigerant flow direction is reversed from the heating operation. Therefore, during the defrosting operation, the switching mechanism 22 is in the state indicated by the solid line in FIG. 4, that is, the second port 22b and the third port 22c are communicated, and the first port 22a and the fourth port 22d are connected. Change the communication. As a result, in the refrigerant circuit 10, the outdoor heat exchanger 23 functions as a condenser for the refrigerant compressed in the compressor 21, and the indoor heat exchangers 52 and 62 are operated in the outdoor heat, as in the above cooling operation. A refrigeration cycle that functions as an evaporator for the refrigerant condensed in the exchanger 23 is performed.

  Here, the defrosting operation is performed when the controller 9 determines that frost formation has occurred in the outdoor heat exchanger 23 during the heating operation. This determination is performed based on the temperature Tb of the refrigerant flowing through the outdoor heat exchanger 23 detected by the outdoor heat exchanger temperature sensor 29c and the accumulated time of the heating operation. For example, when it is detected that the temperature Tb of the refrigerant detected by the outdoor heat exchanger temperature sensor 29c has decreased to a predetermined temperature or less that can be regarded as frost formation in the outdoor heat exchanger 23, or heating If the accumulated time of operation has passed a predetermined time that can be regarded as frost formation in the outdoor heat exchanger 23, it is determined that frost formation has occurred in the outdoor heat exchanger 23. When the temperature and time conditions are not reached, it is determined that frost formation has not occurred in the outdoor heat exchanger 23.

  In the refrigerant circuit 10, the refrigerant circulates in the same flow direction as that in the cooling operation. Then, the high-pressure refrigerant that is compressed by the compressor 21 and flows through the second gas refrigerant pipe 26 b is sent to the outdoor heat exchanger 23 through the switching mechanism 22 to heat the outdoor heat exchanger 23. Thereby, the frost generated in the outdoor heat exchanger 23 in the heating operation is melted to become drain water, and passes through the anti-freezing heat exchanger 25 integrated with the outdoor heat exchanger 23 to the lower side of the outdoor heat exchanger 23. It collects on the bottom plate 2a of the outdoor unit 2 as a drain pan arranged. The drain water accumulated on the bottom plate 2a is discharged out of the outdoor unit 2 through a discharge port 2b formed on the bottom plate 2a.

  Then, the defrosting operation ends when the control unit 9 determines that the defrosting of the outdoor heat exchanger 23 has been completed. This determination is performed based on the temperature Tb of the refrigerant flowing through the outdoor heat exchanger 23 detected by the outdoor heat exchanger temperature sensor 29c and the operating time of the defrosting operation. For example, when it is detected that the refrigerant temperature Tb detected by the outdoor heat exchanger temperature sensor 29c is equal to or higher than a temperature at which frost can be regarded as melted, or the operation time of the defrosting operation is a predetermined time. When the time has elapsed, it is determined that the defrosting of the outdoor heat exchanger 23 has been completed, and when the temperature condition or time condition has not been reached, the defrosting of the outdoor heat exchanger 23 is completed. It is determined that it is not.

  During this defrosting operation, the hot gas opening / closing mechanism 27b is opened as in the above cooling operation. For this reason, a part of the high-pressure refrigerant that is compressed in the compressor 21 and flows through the second gas refrigerant pipe 26 b is branched to the hot gas bypass pipe 27. The high-pressure refrigerant branched into the hot gas bypass pipe 27 is sent to the antifreezing heat exchanger 25 to heat the lower side of the outdoor heat exchanger 23. That is, the anti-freezing heat exchanger 25 functions as a heater for drain water melted by performing the defrosting operation. As a result, during the defrosting operation, the drain water from the outdoor heat exchanger 23 is heated on the lower side of the outdoor heat exchanger 23 and then collected on the bottom plate 2a of the outdoor unit 2 as a drain pan. Discharged outside. As described above, in the air conditioner 1, during the defrosting operation, the anti-freezing heat exchanger 25 heats the drain water generated in the outdoor heat exchanger 23 on the lower side of the outdoor heat exchanger 23. Yes. Thereby, in the air conditioning apparatus 1, the drain water from the outdoor heat exchanger 23 can be prevented from freezing on the lower side of the outdoor heat exchanger 23 during the defrosting operation, and the drain water is outside the outdoor unit 2. Therefore, the occurrence of an ice-up phenomenon during the defrosting operation is suppressed.

<Freezing prevention control when resuming heating>
As described above, in the air conditioning apparatus 1, during the defrosting operation, a part of the high-pressure refrigerant compressed in the compressor 21 is caused to flow through the antifreezing heat exchanger 25, thereby drain water during the defrosting operation. Can be prevented from freezing.

  However, for a while after the defrosting operation is completed, the drain water melted by performing the defrosting operation exists on the lower side of the outdoor heat exchanger 23, and the drain water to the outside of the outdoor unit 2 is present. Emission continues. Thereafter, when the heating operation is resumed, there is a possibility that the drain water is frozen before the drain water is discharged under a condition where the outside air temperature Ta is low. For this reason, freezing of drain water at the time of heating operation after defrosting operation cannot be prevented, and an ice-up phenomenon may occur.

  Therefore, in the air conditioner 1, anti-freezing control at the time of resuming heating is performed so that a part of the refrigerant compressed in the compressor 21 flows to the anti-freezing heat exchanger 25 in the early stage of resuming the heating operation after the defrosting operation. I have to.

  Next, this anti-freezing control when resuming heating will be described with reference to FIGS. Here, FIG. 6 is a flowchart of the freeze prevention control at the time of resuming the heating of the air conditioner 1. FIG. 7 is a schematic configuration diagram illustrating the flow of the refrigerant during the freeze prevention control at the time of resuming the heating of the air-conditioning apparatus 1.

  First, the control part 9 determines whether it is the heating operation after a defrost operation in step S1. If it is determined in step S1 that the heating operation is performed after the defrosting operation, the process proceeds to step S2 in which it is determined whether or not an outside air temperature condition that requires anti-freezing control when resuming heating is satisfied.

  In step S2, the control unit 9 determines whether or not the outside air temperature Ta detected by the outside air temperature sensor 29d is equal to or lower than a predetermined outside air temperature Tas. In step S2, when the outside air temperature Ta is equal to or lower than a predetermined outside air temperature Tas, that is, when the outside air temperature condition is satisfied, the process proceeds to steps S3 to S5 for executing the freeze prevention control at the time of resuming heating. On the other hand, when the outside air temperature Ta is higher than the predetermined outside air temperature Tas, that is, when the outside air temperature condition is not satisfied, the heating operation is resumed without performing the freeze prevention control at the time of resuming the heating in steps S3 to S5. Here, the predetermined outside air temperature Tas is set in view of whether or not the drain water present on the lower side of the outdoor heat exchanger 23 may be frozen after the defrosting operation, and is, for example, the melting point of water. It is set to 0 ° C. The predetermined outside air temperature Tas is stored in advance in a memory or the like of the control unit 9 and can be changed by a switch (not shown) or a remote controller (not shown) provided in the control unit 9. It is like that.

  And the control part 9 starts the freeze prevention control at the time of heating resumption which flows a part of refrigerant | coolant compressed in the compressor 21 to the freezing prevention heat exchanger 25 in step S3. That is, in the refrigerant circuit 10, the same refrigeration cycle as that in the heating operation is performed, and the hot gas opening / closing mechanism 27b is opened. For this reason, a part of the high-pressure refrigerant that is compressed in the compressor 21 and flows through the second gas refrigerant pipe 26 b is branched to the hot gas bypass pipe 27. The high-pressure refrigerant branched into the hot gas bypass pipe 27 is sent to the antifreezing heat exchanger 25 to heat the lower side of the outdoor heat exchanger 23. That is, the antifreezing heat exchanger 25 functions as a heater for drain water existing on the lower side of the outdoor heat exchanger 23 after the defrosting operation. Here, since the outlet of the hot gas bypass pipe 27 is connected to a portion of the liquid refrigerant pipe 26e through which the low-pressure refrigerant flows downstream of the outdoor expansion valve 24, the flow rate of the refrigerant flowing through the hot gas bypass pipe 27 is high. It is easy to be secured. The refrigerant that has heated the drain water in the antifreezing heat exchanger 25 condenses in the antifreezing heat exchanger 25, but then merges with the refrigerant flowing through the liquid refrigerant pipe 26e and functions as a refrigerant evaporator. Therefore, the refrigerant condensed in the antifreezing heat exchanger 25 remains in a liquid state and is not sucked into the compressor 21. As a result, during the heating operation after the defrosting operation, the drain water present on the lower side of the outdoor heat exchanger 23 is heated in the antifreezing heat exchanger 25 and then the bottom plate 2a of the outdoor unit 2 as a drain pan. It accumulates on the top and is discharged out of the outdoor unit 2. As described above, in the air conditioner 1, the anti-freezing heat exchanger 25 heats the drain water present on the lower side of the outdoor heat exchanger 23 during the heating operation after the defrosting operation. Thereby, in the air conditioning apparatus 1, in the heating operation after the defrosting operation, the drain water existing on the lower side of the outdoor heat exchanger 23 can be discharged without freezing after the defrosting operation. Occurrence of ice-up phenomenon during heating operation after operation is suppressed.

  And control part 9 judges whether predetermined time ts passed after defrost operation in Step S4, and when predetermined time ts passed, it shifts to processing of Step S5. Here, the predetermined time ts is set to about several minutes in consideration of the time required to discharge the drain water present on the lower side of the outdoor heat exchanger 23 after the defrosting operation. The predetermined time ts is stored in advance in a memory or the like of the control unit 9 and can be changed by a switch (not shown) or a remote controller (not shown) provided in the control unit 9. It has become. And the control part 9 complete | finishes freezing prevention control at the time of heating resumption in step S5, and transfers to normal heating operation. That is, in the refrigerant circuit 10, the same refrigeration cycle as that in the heating operation is performed, and the hot gas opening / closing mechanism 27b is closed. For this reason, during the heating operation after the defrosting operation, a predetermined time ts for discharging the drain water existing on the lower side of the outdoor heat exchanger 23 after the defrosting operation without freezing, that is, after the defrosting operation. Only when the heating operation is restarted, the freeze prevention control is performed when heating is restarted. Here, in the heating operation after the defrosting operation, flowing a part of the refrigerant compressed in the compressor 21 to the anti-freezing heat exchanger 25 means that the flow rate of the refrigerant sent to the indoor heat exchangers 52 and 62 is reduced. This will reduce the heating capacity. However, in the air conditioning apparatus 1, as described above, a part of the refrigerant compressed in the compressor 21 is transferred to the antifreezing heat exchanger 25 only in the initial stage of restarting the heating operation in the heating operation after the defrosting operation. I try to make it flow. For this reason, in the air conditioning apparatus 1, the fall of the heating capability in the heating operation after a defrost operation is suppressed.

  As described above, in the air conditioner 1, it is possible to suppress the occurrence of the ice-up phenomenon during the heating operation after the defrosting operation while suppressing the decrease in the heating capacity during the heating operation after the defrosting operation. Yes.

(3) Features of the air conditioner The air conditioner 1 of the present embodiment has the following features.

<A>
In the air conditioner 1, in the heating operation after the defrosting operation, a part of the refrigerant compressed in the compressor 21 as the compression mechanism is caused to flow to the antifreezing heat exchanger 25, so that the outside air temperature Ta is low. The drain water present on the lower side of the outdoor heat exchanger 23 can be discharged without freezing after the defrosting operation. For this reason, in the air conditioning apparatus 1, generation | occurrence | production of the ice-up phenomenon at the time of the heating operation after a defrost operation can be suppressed.

  Here, in the heating operation after the defrosting operation, flowing a part of the refrigerant compressed in the compressor 21 to the anti-freezing heat exchanger 25 means that the flow rate of the refrigerant sent to the indoor heat exchangers 52 and 62 is reduced. This will reduce the heating capacity.

  Therefore, in the air conditioner 1, as described above, a part of the refrigerant compressed in the compressor 21 is transferred to the antifreezing heat exchanger 25 only in the initial stage of restarting the heating operation in the heating operation after the defrosting operation. It is made to flow (that is, freeze prevention control when resuming heating). For this reason, in the air conditioning apparatus 1, the fall of the heating capability in the heating operation after a defrost operation can be suppressed.

  Thereby, in the air conditioning apparatus 1, generation | occurrence | production of the ice-up phenomenon at the time of the heating operation after a defrost operation can be suppressed, suppressing the fall of the heating capability in the heating operation after a defrost operation.

<B>
In the air conditioner 1, the anti-freezing control when resuming heating is performed when the outside air temperature Ta is equal to or lower than a predetermined outside air temperature Tas. For this reason, in the air conditioner 1, only under conditions where the outside air temperature Ta at which the drain water present on the lower side of the outdoor heat exchanger 23 may freeze after the defrosting operation is low (in this case, 0 ° C. or less). When the heating is resumed, the freeze prevention control is performed. Under the condition where the outside air temperature Ta is high (in this case, higher than 0 ° C.), the freeze prevention control when the heating is resumed can be omitted.

  Thereby, in the air conditioning apparatus 1, the fall of the heating capability in the heating operation after a defrost operation can further be suppressed.

<C>
In the air conditioner 1, the freeze prevention control at the time of resuming heating is performed until a predetermined time ts elapses after the defrosting operation. That is, in the air conditioner 1, since the freeze prevention control at the time of resuming heating is managed by time, the time required for discharging the drain water present on the lower side of the outdoor heat exchanger 23 after the defrosting operation. Can be considered.

  Thereby, in the air conditioning apparatus 1, the freeze prevention control at the time of resuming heating can be appropriately performed in consideration of the time required for discharging drain water.

(4) Modification 1
In the air conditioning apparatus 1 of the above embodiment, the predetermined time ts of the freeze prevention control at the time of resuming heating can be changed by a switch (not shown), a remote controller (not shown), etc., but automatically according to the operating conditions. It is not intended to be changed.

  However, the amount of drain water present on the lower side of the outdoor heat exchanger 23 after the defrosting operation varies depending on the outside air temperature Ta, the outside air humidity, or the operation time of the defrosting operation. Specifically, as the outside air temperature Ta decreases, the amount of drain water increases as the outside air humidity increases or the operating time of the defrosting operation increases. For this reason, it is preferable to change also about predetermined time ts of anti-freezing control at the time of heating resumption by outside air temperature Ta, outside air humidity, or operating time of defrosting operation.

  Therefore, in the air conditioner 1 of the present modification, the predetermined time ts is set to increase as the outside air temperature Ta decreases, the outside air humidity increases, or the operating time of the defrosting operation increases. (See step S3 in FIG. 8). For this reason, in the air conditioning apparatus 1 of this modification, the amount of drain water that varies depending on the outside air temperature Ta can be taken into consideration. When the predetermined time ts of the freeze prevention control at the time of resuming heating can be changed by the outside air humidity, it is necessary to provide a humidity sensor in the outdoor unit 2 although not shown here.

  Thereby, in the air conditioning apparatus 1 of this modification, the freeze prevention control at the time of resuming heating can be appropriately performed in consideration of the change in the amount of drain water due to conditions such as the outside air temperature Ta.

(5) Modification 2
In the air conditioner 1 of the above embodiment and the modification 1 thereof, the hot gas opening / closing mechanism 27b provided in the hot gas bypass pipe 27 is an electromagnetic valve, and therefore, in the freeze prevention control at the time of resuming heating, heat exchange for freeze prevention is performed. The flow rate of the refrigerant flowing through the vessel 25 cannot be varied.

  However, the amount of drain water present on the lower side of the outdoor heat exchanger 23 after the defrosting operation varies depending on the outside air temperature Ta, the outside air humidity, or the operation time of the defrosting operation. Specifically, the amount of drain water increases as the outside air temperature Ta decreases, the outside air humidity increases, or the operating time of the defrosting operation increases. For this reason, it is preferable to change also the flow volume of the refrigerant | coolant which flows into the heat exchanger 25 for anti-freezing in the anti-freezing control at the time of heating resumption according to the outside temperature Ta, the outside air humidity, or the operating time of the defrosting operation.

  Therefore, in the air conditioner 1 of this modification, the hot gas bypass pipe 27 is provided with a hot gas flow rate adjustment valve 27d for changing the flow rate of the refrigerant flowing through the antifreezing heat exchanger 25 (see FIG. 9). As the outside air temperature Ta becomes lower, the outside air humidity becomes higher, or the operating time of the defrosting operation becomes longer, the opening degree of the hot gas flow rate control valve 27d in the freeze prevention control at the time of resuming heating is set to be increased. (See step S3 in FIG. 10). For this reason, in the air conditioning apparatus 1 of the present modification, the amount of drain water that changes depending on the outside air temperature Ta, the outside air humidity, or the operating time of the defrosting operation can be taken into consideration. In addition, in order to be able to change the opening degree of the hot gas flow rate control valve 27d for the antifreezing control at the time of resuming heating depending on the outside air humidity, it is necessary to provide a humidity sensor in the outdoor unit 2 although not shown here.

  Thereby, in the air conditioning apparatus 1 of this modification, the freeze prevention control at the time of resuming heating can be appropriately performed in consideration of the change in the amount of drain water due to conditions such as the outside air temperature Ta.

-Second Embodiment-
(1) Configuration of Air Conditioner FIG. 11 is a schematic configuration diagram of an air conditioner 1 according to the second embodiment of the present invention. The air conditioning apparatus 1 is an apparatus used for air conditioning in a room such as a building by performing a vapor compression refrigeration cycle. The air conditioner 1 mainly includes one outdoor unit 2, one intermediate unit 4, a plurality of (here, two) indoor units 5 and 6, an outdoor unit 2, a functional unit 4, and an indoor unit. A liquid refrigerant communication pipe 7 and a gas refrigerant communication pipe 8 for connecting the units 5 and 6 are provided. That is, the vapor compression refrigerant circuit 10 of the air conditioner 1 is connected to the outdoor unit 2, the functional unit 4, the indoor units 5 and 6, the liquid refrigerant communication pipe 7 and the gas refrigerant communication pipe 8. It is constituted by. Note that the number of indoor units 5 and 6 is not limited to two, and may be one or three or more.

<Indoor unit>
The indoor units 5 and 6 are installed by embedding or hanging in a ceiling of a room such as a building or hanging on a wall surface of the room. The indoor units 5 and 6 are connected to the functional unit 4 via a first liquid refrigerant communication tube 7a which is a part of the liquid refrigerant communication tube 7 and a second gas refrigerant communication tube 8a which is a part of the gas refrigerant communication tube 8. And constitutes a part of the refrigerant circuit 10.

  Next, the configuration of the indoor units 5 and 6 will be described. In addition, since the indoor unit 5 and the indoor unit 6 have the same configuration, only the configuration of the indoor unit 5 will be described here, and the configuration of the indoor unit 6 is the 50th number indicating each part of the indoor unit 5. The reference numerals in the 60s are attached instead of the reference numerals, and description of each part is omitted.

  The indoor unit 5 mainly has an indoor expansion valve 51 and an indoor heat exchanger 52.

  The indoor expansion valve 51 is a device that adjusts the pressure and flow rate of the refrigerant flowing through the indoor unit 5. The indoor expansion valve 51 has one end connected to the liquid side of the indoor heat exchanger 52 and the other end connected to the first liquid refrigerant communication pipe 7a. Here, an electric expansion valve is used as the indoor expansion valve 51.

  The indoor heat exchanger 52 is a heat exchanger that functions as a refrigerant evaporator during cooling operation to cool indoor air and functions as a refrigerant condenser during heating operation to heat indoor air. The indoor heat exchanger 52 has a liquid side connected to the indoor expansion valve 51 and a gas side connected to the first gas refrigerant communication pipe 8a. Here, the indoor heat exchanger 52 is a cross-fin type fin-and-tube heat exchanger composed of heat transfer tubes and a large number of fins. The type of the indoor heat exchanger 52 is not limited to the cross fin type fin-and-tube type heat exchanger, and other types such as a laminated heat exchanger using corrugated fins or flat tubes, for example. It may be a type of heat exchanger.

  The indoor unit 5 has an indoor fan 53 for supplying indoor air as supply air after sucking indoor air into the indoor unit 5 and exchanging heat with the refrigerant in the indoor heat exchanger 52. . Here, as the indoor fan 53, a centrifugal fan or a multi-blade fan driven by an indoor fan motor 53a is used.

  The indoor unit 5 includes an indoor side control unit 54 that controls the operation of each unit constituting the indoor unit 5. And the indoor side control part 54 has a microcomputer, memory, etc. for controlling the indoor unit 5, and between the remote controllers (not shown) for operating the indoor unit 5 separately. Control signals and the like can be exchanged, and control signals and the like can be exchanged with the outdoor unit 2 and the functional unit 4 via the transmission line 9a.

<Outdoor unit>
The outdoor unit 2 is installed outside a building or the like. The outdoor unit 2 is connected to the functional unit 4 via a second liquid refrigerant communication tube 7b that is a part of the liquid refrigerant communication tube 7 and a second gas refrigerant communication tube 8b that is a part of the gas refrigerant communication tube 8. And constitutes a part of the refrigerant circuit 10.

  Next, the configuration of the outdoor unit 2 will be described. The outdoor unit 2 mainly includes a low-stage compressor 21 that constitutes the compression mechanism 20 together with a high-stage compressor 32 (described later) of the functional unit 4, a switching mechanism 22, 31, an outdoor heat exchanger 23, an outdoor unit It has an expansion valve 24 and a heat exchanger 25 for preventing freezing.

  The low stage compressor 21 is a device that compresses the refrigerant. The low stage compressor 21 has a hermetic structure in which a rotary type or scroll type positive displacement compression element (not shown) is rotationally driven by a low stage compressor motor 21a. The low-stage compressor 21 has a first gas refrigerant pipe 26a connected to the suction side and a second gas refrigerant pipe 26b connected to the discharge side. The first gas refrigerant pipe 26 a is a refrigerant pipe that connects the suction side of the low-stage compressor 21 and the first port 22 a of the first switching mechanism 22. The second gas refrigerant pipe 26 b is a refrigerant pipe that connects the discharge side of the low-stage compressor 21 and the second port 22 b of the first switching mechanism 22. Here, one low-stage compressor 21 constitutes the compression mechanism 20 together with the high-stage compressor 32. However, a plurality of low-stage compressors 21 connected in parallel and a high stage The compression mechanism 20 may be configured with the side compressor 32.

  The switching mechanisms 22 and 31 are mechanisms for switching the direction of refrigerant flow in the refrigerant circuit 10. The switching mechanisms 22 and 31 function the outdoor heat exchanger 23 as a condenser of the refrigerant compressed in the low-stage compressor 21 during the cooling operation and the defrosting operation, and the indoor heat exchangers 52 and 62 Switching is performed so as to function as an evaporator of the refrigerant condensed in the outdoor heat exchanger 23. In other words, the first switching mechanism 22 switches between the second port 22b and the third port 22c and the first port 22a and the fourth port 22d during the cooling operation and the defrosting operation. . In addition, the second switching mechanism 31 switches between the second port 31b and the third port 31c and the first port 31a and the fourth port 31d during the cooling operation and the defrosting operation. . As a result, the discharge side of the low-stage compressor 21 (here, the second gas refrigerant pipe 26b) and the gas side of the outdoor heat exchanger 23 (here, the third gas refrigerant pipe 26c) are connected (FIG. 11 (see the solid line of the first switching mechanism 22). Moreover, the suction side of the low-stage compressor 21 (here, the first gas refrigerant pipe 26a) and the second gas refrigerant communication pipe 8b side (here, the fifth gas refrigerant pipe 26f and the sixth gas refrigerant pipe 26g) Are connected (see the solid line of the second switching mechanism 31 in FIG. 11). Further, the switching mechanisms 22 and 31 cause the outdoor heat exchanger 23 to function as an evaporator of the refrigerant condensed in the indoor heat exchangers 42 and 52 during the heating operation, and the indoor heat exchangers 52 and 62 are set on the lower stage side. Switching to function as a condenser for the refrigerant compressed in the compressor 21 is performed. That is, during the heating operation, the first switching mechanism 22 switches the second port 22b and the fourth port 22d to communicate with each other and the first port 22a and the third port 22c to communicate with each other. In addition, during the heating operation, the second switching mechanism 31 performs switching so that the second port 31b and the fourth port 31d communicate with each other and the first port 31a and the third port 31c communicate with each other. As a result, the discharge side (here, the second gas refrigerant pipe 26b) of the low-stage compressor 21 and the gas refrigerant communication pipe 8 side (here, the fourth gas refrigerant pipe 26d and the fifth gas refrigerant pipe 26f) are connected. They are connected (see the broken line of the second switching mechanism 31 in FIG. 11). In addition, the suction side (here, the first gas refrigerant pipe 26a) of the low-stage compressor 21 and the gas side (here, the third gas refrigerant pipe 26c) of the outdoor heat exchanger 23 are connected (FIG. 11). (Refer to the broken line of the first switching mechanism 22). The third gas refrigerant pipe 26 c is a refrigerant pipe that connects the third port 22 c of the first switching mechanism 22 and the gas side of the outdoor heat exchanger 23. The fourth gas refrigerant pipe 26 d is a refrigerant pipe that connects a middle portion of the second gas refrigerant pipe 26 b and the fourth port 31 d of the second switching mechanism 31. The fifth gas refrigerant pipe 26f is a refrigerant pipe that connects the second port 31b of the second switching mechanism 31 and the second gas refrigerant communication pipe 8b side. Here, the first switching mechanism 22 is a four-way switching valve. And the 4th port 22d of the 1st switching mechanism 22 is connected to the 1st gas refrigerant pipe 26a through the 7th gas refrigerant pipe 26h consisting of a capillary tube with very large channel resistance. For this reason, almost no refrigerant flows through the seventh gas refrigerant pipe 26h, so that the first switching mechanism 22 functions as a three-way valve having the first to third ports 22a to 22c. ing. The first port 31a of the second switching mechanism 31 is connected to the sixth gas refrigerant pipe 26g through an eighth gas refrigerant pipe 26i made of a capillary tube having a very large flow path resistance. For this reason, almost no refrigerant flows through the eighth gas refrigerant pipe 26a, whereby the second switching mechanism 31 functions as a three-way valve having the second to fourth ports 31b to 31d. ing. Here, the configuration of the switching mechanisms 22 and 31 is not limited to that using two four-way switching valves. For example, the switching mechanisms 22 and 31 may be configured by one four-way switching valve or a plurality of electromagnetic A configuration in which valves and the like are connected so as to perform the switching function described above may be used.

  The outdoor heat exchanger 23 is a heat exchanger that functions as a refrigerant condenser during a cooling operation and a defrosting operation, and functions as a refrigerant evaporator during a heating operation. The outdoor heat exchanger 23 has a liquid side connected to the first liquid refrigerant pipe 26e and a gas side connected to the third gas refrigerant pipe 26c. The first liquid refrigerant pipe 26e is a refrigerant pipe that connects the liquid side of the outdoor heat exchanger 23 and the second liquid refrigerant communication pipe 7b side. Here, the outdoor heat exchanger 23 is a cross-fin type fin-and-tube heat exchanger composed of heat transfer tubes and a large number of fins. The type of the outdoor heat exchanger 23 is not limited to a cross fin type fin-and-tube type heat exchanger, and other types such as a laminated heat exchanger using corrugated fins or flat tubes, for example. It may be a type of heat exchanger.

  The outdoor expansion valve 24 is a device that adjusts the pressure and flow rate of the refrigerant flowing through the outdoor unit 2. The outdoor expansion valve 24 is provided in the first liquid refrigerant pipe 26e. Here, an electric expansion valve is used as the outdoor expansion valve 24.

  The antifreezing heat exchanger 25 is a heat exchanger that heats the lower side of the outdoor heat exchanger 23 with a part of the refrigerant compressed in the low-stage compressor 21 constituting the compression mechanism 20. The antifreezing heat exchanger 25 is provided in the hot gas bypass pipe 27. Here, the anti-freezing heat exchanger 25 is a cross-fin type fin-and-tube heat exchanger composed of heat transfer tubes and a large number of fins, and as shown in FIG. 2, an outdoor heat exchanger. 23 is integrated with the lower part. Specifically, the outdoor heat exchanger 23 and the antifreezing heat exchanger 25 are configured as an integral fin-and-tube heat exchanger, and the heat transfer tubes and fins on the upper side are the outdoor heat exchanger 23. The heat transfer tubes and fins on the lower side constitute a heat exchanger 25 for preventing freezing. The lower end portion of the freeze prevention heat exchanger 25 is disposed on the bottom plate 2 a of the outdoor unit 2 that functions as a drain pan that receives drain water generated in the outdoor heat exchanger 23 and the freeze prevention heat exchanger 25. The bottom plate 2 a is formed with a discharge port 2 b so that drain water received on the bottom plate 2 a can be discharged out of the outdoor unit 2. Here, FIG. 2 is a schematic view showing the lower side of the outdoor heat exchanger 23 including the freeze-preventing heat exchanger 25 and the bottom plate 2 a of the outdoor unit 2. The type of the anti-freezing heat exchanger 25 is not limited to the cross-fin type fin-and-tube type heat exchanger, for example, a laminated heat exchanger using corrugated fins or flat tubes, etc. Other types of heat exchangers may be used.

  The hot gas bypass pipe 27 is a refrigerant pipe that branches a part of the refrigerant compressed in the low-stage compressor 21. One end side of the hot gas bypass pipe 27 is connected so as to branch from a middle portion of the second gas refrigerant pipe 26c, and the other end side is connected to the liquid side of the outdoor heat exchanger 23 of the first liquid refrigerant pipe 26e and the outdoor expansion valve. 24 is connected so as to join the portion between the two. A hot gas decompression mechanism 27a, a hot gas opening / closing mechanism 27b, and a hot gas check mechanism 27c are provided at a portion of the hot gas bypass pipe 27 on the outlet side of the heat exchanger 25 for preventing freezing. The hot gas decompression mechanism 27a is a device that decompresses the refrigerant. Here, a capillary tube is used as the hot gas decompression mechanism 27a. The hot gas opening / closing mechanism 27b is opened when a part of the refrigerant compressed in the low stage compressor 21 is branched into the hot gas bypass pipe 27, and is compressed in the low stage compressor 21 by the hot gas bypass pipe 27. This is a device that can be closed when a part of the refrigerant is not branched. Here, an electromagnetic valve is used as the hot gas opening / closing mechanism 27b. The hot gas check mechanism 27c is a mechanism that allows the refrigerant to flow from the outlet side of the antifreezing heat exchanger 25 to the first liquid refrigerant pipe 26e and blocks the flow in the reverse direction. Here, a check valve is used as the hot gas check mechanism 27c. Here, as will be described later, in order to increase the heating capacity in a condition where the outside air temperature is low, a functional unit is connected between the outdoor unit 2 and the indoor units 5 and 6 to thereby perform a two-stage compression refrigeration cycle. To be able to do. An outdoor heat exchanger 23 in which frost formation occurs is provided in the outdoor unit 2. Therefore, the freeze prevention heat exchanger 25 is provided in the outdoor unit 2, and the refrigerant compressed in the low-stage compressor 21 provided in the outdoor unit 2 is used as a heating source for the freeze prevention heat exchanger 25. The hot gas bypass pipe 27 that uses the section is provided. As a result, the hot gas bypass pipe 27 is configured to be accommodated in the outdoor unit 2 so as not to be configured to straddle between the outdoor unit 2 and the functional unit 4.

  The outdoor unit 2 has an outdoor fan 28 for sucking outdoor air into the outdoor unit 2, exchanging heat with the refrigerant in the outdoor heat exchanger 23, and then discharging the air outside the outdoor unit 2. . Here, as the outdoor fan 28, an axial fan or the like driven by an outdoor fan motor 28a is used. Further, as shown in FIG. 2, the anti-freezing heat exchanger 25 is integrated with the lower part of the outdoor heat exchanger 23. Therefore, the outdoor fan 28 is not only the outdoor heat exchanger 23 but also the anti-freezing heat. Outdoor air is also supplied to the exchanger 25.

  The outdoor unit 2 is provided with various sensors. Specifically, the outdoor unit 2 is mainly provided with a suction pressure sensor 29a, a discharge pressure sensor 29b, an outdoor heat exchange temperature sensor 29c, and an outdoor temperature sensor 29d. The suction pressure sensor 29 a is a pressure sensor that detects the suction pressure Ps of the low-stage compressor 21. The discharge pressure sensor 29b is a pressure sensor that detects the discharge pressure Pd1 of the low-stage compressor 21. The outdoor heat exchange temperature sensor 29 c is a temperature sensor that detects the temperature Tb of the refrigerant flowing through the outdoor heat exchanger 23. The outside air temperature sensor 29d is a temperature sensor that detects the outside air temperature Ta in the outdoor unit 2.

  The outdoor unit 2 also has an outdoor control unit 30 that controls the operation of each part constituting the outdoor unit 2. The outdoor control unit 30 includes a microcomputer, a memory, and the like for controlling the outdoor unit 2. Between the indoor side control units 54 and 64 of the indoor units 5 and 6 and the functional unit 4. Control signals and the like can be exchanged via the transmission line 9a.

<Functional unit>
The functional unit 4 is a unit that enables a two-stage compression refrigeration cycle by being connected between the outdoor unit 2 and the indoor units 5 and 6 in order to increase the heating capacity in a condition where the outside air temperature is low. It is installed outside the building. The functional unit 4 is connected to the indoor units 5 and 6 via the first liquid refrigerant communication tube 7a and the first gas refrigerant communication tube 8a, and the second liquid refrigerant communication tube 7b and the second gas refrigerant communication tube. It is connected to the outdoor unit 2 via 8b and constitutes a part of the refrigerant circuit 10.

  Next, the configuration of the functional unit 4 will be described. The functional unit 4 mainly includes a high-stage compressor 32 that constitutes the compression mechanism 20 together with the low-stage compressor 21 of the outdoor unit 2, a gas-liquid separator 33, a ninth gas refrigerant pipe 34a, and a second liquid. And a refrigerant pipe 34b.

  The ninth gas refrigerant tube 34a is a refrigerant tube that connects the first gas refrigerant communication tube 8a and the second gas refrigerant communication tube 8b. A first gas refrigerant opening / closing mechanism 35 is provided in the ninth gas refrigerant pipe 34a. Here, an electromagnetic valve is used as the first gas refrigerant opening / closing mechanism 35.

  The second liquid refrigerant pipe 34b is a refrigerant pipe that connects the first liquid refrigerant communication pipe 7a and the second liquid refrigerant communication pipe 7b. The second liquid refrigerant pipe 34b has a third liquid refrigerant pipe 34c and a fourth liquid refrigerant pipe 34d connected in parallel to the third liquid refrigerant pipe 34c. The third liquid refrigerant pipe 34c is a refrigerant pipe for flowing a refrigerant from the second liquid refrigerant communication pipe 7b toward the first liquid refrigerant communication pipe 7a. A first liquid refrigerant check mechanism 36 is provided in the third liquid refrigerant pipe 34c. The first liquid refrigerant check mechanism 36 is a mechanism that allows the flow of refrigerant from the second liquid refrigerant communication pipe 7b side to the first liquid refrigerant communication pipe 7a side and blocks the flow in the reverse direction. Here, a check valve is used as the first liquid refrigerant check mechanism 36. The fourth liquid refrigerant pipe 34d is a refrigerant pipe for flowing the refrigerant from the first liquid refrigerant communication pipe 7a toward the second liquid refrigerant communication pipe 7b. The fourth liquid refrigerant pipe 34d is provided with a first liquid refrigerant opening / closing mechanism 37 and a second liquid refrigerant check mechanism 38. Here, an electromagnetic valve is used as the first liquid refrigerant opening / closing mechanism 37. The second liquid refrigerant check mechanism 38 is a mechanism that allows the flow of refrigerant from the first liquid refrigerant communication pipe 7a side to the second liquid refrigerant communication pipe 7b side and blocks the flow in the reverse direction. Here, a check valve is used as the second liquid refrigerant check mechanism 38.

  The high stage compressor 32 is a device that compresses the refrigerant. The high stage compressor 32 has a hermetic structure in which a rotary type or scroll type positive displacement compression element (not shown) is rotationally driven by a high stage compressor motor 32a. The high stage compressor 32 has a tenth gas refrigerant pipe 34e connected to the suction side and an eleventh gas refrigerant pipe 34f connected to the discharge side. The tenth gas refrigerant pipe 34e connects the suction side of the high-stage compressor 32 and the portion of the ninth gas refrigerant pipe 34a closer to the second gas refrigerant communication pipe 8b than the first gas refrigerant opening / closing mechanism 35. It is. A high stage suction expansion valve 39 is provided in the tenth gas refrigerant pipe 34e. The high-stage suction expansion valve 39 is opened when the refrigerant compressed in the low-stage compressor 21 is sucked into the high-stage compressor 32 and further compressed, and the refrigerant compressed in the low-stage compressor 21 is high. This is a device that can be closed when the stage-side compressor 32 is not inhaled. Here, an electric expansion valve is used as the high stage intake expansion valve 39. The eleventh gas refrigerant pipe 34f connects the discharge side of the high-stage compressor 32 and the portion of the ninth gas refrigerant pipe 34a closer to the first gas refrigerant communication pipe 8a than the first gas refrigerant open / close mechanism 35. It is.

  The gas-liquid separator 33 is a device that introduces the refrigerant flowing through the second liquid refrigerant pipe 34b and separates it into a gas refrigerant and a liquid refrigerant. Here, a vertical cylindrical container is used as the gas-liquid separator 33. A fifth liquid refrigerant pipe 34g, a sixth liquid refrigerant pipe 34h, and a twelfth gas refrigerant pipe 34i are connected to the gas-liquid separator 33. The fifth liquid refrigerant pipe 34g includes a portion of the fourth liquid refrigerant pipe 34d closer to the first liquid refrigerant communication pipe 7a than the first liquid refrigerant open / close mechanism 37 and the second liquid refrigerant check mechanism 38 and the gas-liquid separator 33. It is a refrigerant | coolant pipe | tube connecting between the refrigerant | coolant inlets formed in the up-down direction center part. The fifth liquid refrigerant pipe 34g is provided with a second liquid refrigerant opening / closing mechanism 40 and a third liquid refrigerant check mechanism 41. Here, an electromagnetic valve is used as the second liquid refrigerant opening / closing mechanism 40. The third liquid refrigerant check mechanism 41 is a mechanism that allows the flow of refrigerant from the second liquid refrigerant pipe 34b side to the refrigerant inlet side of the gas-liquid separator 33 and blocks the flow in the reverse direction. Here, a check valve is used as the third liquid refrigerant check mechanism 41. The sixth liquid refrigerant pipe 34h includes a portion of the fourth liquid refrigerant pipe 34d closer to the second liquid refrigerant communication pipe 7b than the first liquid refrigerant open / close mechanism 37 and the second liquid refrigerant check mechanism 38 and the gas-liquid separator 33. It is a refrigerant pipe connecting between the liquid refrigerant outlet formed in the lower part. A fourth liquid refrigerant check mechanism 42 is provided in the sixth liquid refrigerant pipe 34h. The fourth liquid refrigerant check mechanism 42 is a mechanism that allows the flow of refrigerant from the liquid refrigerant outlet side of the gas-liquid separator 33 to the second liquid refrigerant pipe 34b side and blocks the flow in the reverse direction. Here, a check valve is used as the fourth liquid refrigerant check mechanism 42. The twelfth gas refrigerant pipe 34i is between a portion of the tenth gas refrigerant pipe 34e closer to the higher stage compressor 32 than the higher stage suction expansion valve 39 and a gas refrigerant outlet formed at the upper part of the gas-liquid separator 33. It is a refrigerant pipe which connects.

  The functional unit 4 is provided with various sensors. Specifically, the functional unit 4 is mainly provided with a discharge pressure sensor 43. The discharge pressure sensor 43 is a pressure sensor that detects the discharge pressure Pd2 of the high-stage compressor 32.

  In addition, the functional unit 4 includes a function side control unit 44 that controls the operation of each unit constituting the functional unit 4. The function side control unit 44 includes a microcomputer, a memory, and the like for controlling the function unit 4, and controls the indoor side control units 54 and 64 of the indoor units 5 and 6 and the outdoor side control of the outdoor unit 2. Control signals and the like can be exchanged with the unit 30 via the transmission line 9a. That is, the operation control of the entire air conditioner 1 is performed by the indoor side control units 54 and 64, the outdoor side control unit 30, the function side control unit 44, and the transmission line 9a connecting the control units 30, 44, 54 and 64. The control part 9 to perform is comprised.

  As illustrated in FIG. 12, the control unit 9 is configured to perform various devices and valves 21 a, 22, 24, 27 b, 28 a, 32 a, 35, 37 based on various operation settings and detection values of the various sensors 29 a to 29 d, 43. , 39, 40, 51, 53a, 61, 63a can be controlled. Here, FIG. 12 is a control block diagram of the air conditioner 1.

<Refrigerant communication pipe>
Refrigerant communication pipes 7 and 8 are refrigerant pipes constructed on site when the air conditioner 1 is installed at an installation location such as a building, and installation conditions such as an installation location and a combination of an outdoor unit and an indoor unit. Those having various lengths and tube diameters are used.

  As described above, the refrigerant circuit 10 of the air conditioner 1 is configured by connecting the outdoor unit 2, the functional unit 4, the indoor units 5 and 6, and the refrigerant communication tubes 7 and 8. The air conditioner 1 is controlled by the control unit 9 including the indoor side control units 54 and 64, the function side control unit 44, and the outdoor side control unit 30, and the cooling operation, heating operation, and removal described below. Various operations such as frost operation can be performed.

(2) Operation of the Air Conditioner The air conditioner 1 can mainly perform a cooling operation, a heating operation, and a defrosting operation. The cooling operation is an operation in which the refrigerant is circulated mainly in the order of the compression mechanism 20, the outdoor heat exchanger 23, and the indoor heat exchangers 52 and 62 in order to cool the indoor air. Here, the cooling operation is a single-stage compression refrigeration cycle in which only the low-stage compressor 21 of the compression mechanism 20 is operated. The heating operation is an operation in which the refrigerant is circulated mainly in the order of the compression mechanism 20, the indoor heat exchangers 52 and 62, and the outdoor heat exchanger 23 in order to heat the indoor air. The heating operation includes a single-stage heating operation under a condition where the outside air temperature is high and a two-stage heating operation under a condition where the outside air temperature is low. The single-stage heating operation performs a single-stage compression refrigeration cycle in which only the low-stage compressor 21 of the compression mechanism 20 is operated. The two-stage heating operation performs a two-stage compression refrigeration cycle that operates both the low-stage compressor 21 and the high-stage compressor 32 in the compression mechanism 20. The defrosting operation is an operation in which mainly the compression mechanism 20, the outdoor heat exchanger 23, and the indoor heat exchangers 52 and 62 are circulated in order in order to melt the frost generated in the outdoor heat exchanger 23 by the heating operation. is there. That is, the defrosting operation is a so-called reverse cycle defrosting operation in which the flow direction of the refrigerant is reversed from that of the heating operation. As in the heating operation, the defrosting operation includes a single-stage defrosting operation under a condition where the outside air temperature is high and a two-stage defrosting operation under a condition where the outside air temperature is low. The single-stage defrosting operation performs a single-stage compression refrigeration cycle in which only the low-stage compressor 21 of the compression mechanism 20 is operated. The two-stage defrosting operation performs a two-stage compression refrigeration cycle that operates both the low-stage compressor 21 and the high-stage compressor 32 in the compression mechanism 20. Hereinafter, operations during various operations of the air conditioner 1 will be described.

<Cooling operation>
First, the cooling operation will be described with reference to FIG. Here, FIG. 13 is a schematic configuration diagram illustrating the flow of the refrigerant during the cooling operation of the air-conditioning apparatus 1.

  During the cooling operation, the switching mechanisms 22 and 31 are in the state indicated by the solid lines in FIG. 13, that is, the first switching mechanism 22 is connected to the second port 22b and the third port 22c, and the first port 22a Switching for connecting the fourth port 22d is performed. For the second switching mechanism 31, switching is performed for connecting the second port 31b and the third port 31c and for connecting the first port 31a and the fourth port 31d. I do. Further, the first gas refrigerant opening / closing mechanism 35 is opened, and the first liquid refrigerant opening / closing mechanism 37, the high-stage suction expansion valve 39, and the second liquid refrigerant opening / closing mechanism 40 are closed. Thereby, in the refrigerant circuit 10, the outdoor heat exchanger 23 is made to function as a condenser of the refrigerant | coolant compressed in the low stage side compressor 21, and the indoor heat exchangers 52 and 62 were condensed in the outdoor heat exchanger 23. A single-stage compression refrigeration cycle is performed which functions as a refrigerant evaporator.

  In this refrigerant circuit 10, low-pressure gas refrigerant in the refrigeration cycle is sucked into the low-stage compressor 21 and compressed to become high-pressure gas refrigerant. This high-pressure gas refrigerant is sent to the outdoor heat exchanger 23 through the first switching mechanism 22, exchanges heat with outdoor air supplied by the outdoor fan 28, and condenses to become a high-pressure liquid refrigerant. The high-pressure liquid refrigerant is sent to the indoor expansion valves 51 and 61 through the outdoor expansion valve 24, the second liquid refrigerant communication pipe 7b, the first liquid refrigerant check mechanism 36, and the first liquid refrigerant communication pipe 7a, and decompressed. It becomes a low-pressure refrigerant. The low-pressure refrigerant is sent to the indoor heat exchangers 52 and 62, exchanges heat with the indoor air supplied by the indoor fans 53 and 63, and evaporates to become a low-pressure gas refrigerant. The low-pressure gas refrigerant is sucked into the low-stage compressor 21 again through the first gas refrigerant communication pipe 8a, the first gas refrigerant open / close mechanism 35, the second gas refrigerant communication pipe 8b, and the second switching mechanism 31. .

  During this cooling operation, the hot gas opening / closing mechanism 27b is opened. For this reason, a part of the high-pressure refrigerant that is compressed in the low-stage compressor 21 and flows through the second gas refrigerant pipe 26 b is branched to the hot gas bypass pipe 27. The high-pressure refrigerant branched into the hot gas bypass pipe 27 is sent to the antifreezing heat exchanger 25 to heat the lower side of the outdoor heat exchanger 23. That is, the antifreezing heat exchanger 25 functions as a refrigerant condenser, similarly to the outdoor heat exchanger 23. Thereby, a part of the high-pressure gas refrigerant compressed in the low-stage compressor 21 is sent to the anti-freezing heat exchanger 25 through the hot gas bypass pipe 27 and the outdoor air supplied by the outdoor fan 28 and Heat exchange is performed to condense into a high-pressure liquid refrigerant. The high-pressure liquid refrigerant is sent to the liquid refrigerant pipe 26e through the hot gas decompression mechanism 27a, the hot gas opening / closing mechanism 27b, and the hot gas check mechanism 27c, and merges with the high-pressure liquid refrigerant from the outdoor heat exchanger 23. Thus, in the air conditioner 1, not only the outdoor heat exchanger 23 but also the antifreezing heat exchanger 25 functions as a refrigerant condenser during the cooling operation. Thereby, in the air conditioner 1, cooling of the refrigerant sent to the indoor heat exchangers 52 and 62 is promoted during the cooling operation, compared to a case where only the outdoor heat exchanger 23 functions as a refrigerant condenser, The cooling capacity is improved.

<Single stage heating operation>
Next, a single stage heating operation is demonstrated using FIG. Here, FIG. 14 is a schematic configuration diagram showing a refrigerant flow during the single-stage heating operation of the air-conditioning apparatus 1.

  As described above, the single-stage heating operation is a heating operation performed under conditions where the outside air temperature is high, that is, under conditions where it is easy to ensure the heating capacity. Here, the single-stage heating operation is performed when the outside air temperature Ta detected by the outside air temperature sensor 29d is equal to or higher than a predetermined first outside air temperature Tas1 (for example, 5 ° C.).

  At the time of single-stage heating operation, the switching mechanisms 22 and 31 are in the state indicated by the broken lines in FIG. 14, that is, the first switching mechanism 22 is connected to the second port 22b and the fourth port 22d, and the first port The second switching mechanism 31 communicates the second port 31b and the fourth port 31d and communicates the first port 31a and the third port 31c with each other. Change the mode. In addition, the first gas refrigerant opening / closing mechanism 35 and the first liquid refrigerant opening / closing mechanism 37 are opened, and the high stage suction expansion valve 39 and the second liquid refrigerant opening / closing mechanism 40 are closed. As a result, in the refrigerant circuit 10, the outdoor heat exchanger 23 functions as an evaporator for the refrigerant condensed in the indoor heat exchangers 42 and 52, and the indoor heat exchangers 52 and 62 are compressed in the low-stage compressor 21. A single-stage compression refrigeration cycle is performed that functions as a condenser for the refrigerated refrigerant.

  In this refrigerant circuit 10, low-pressure gas refrigerant in the refrigeration cycle is sucked into the low-stage compressor 21 and compressed to become high-pressure gas refrigerant. The high-pressure gas refrigerant passes through the first switching mechanism 22, the second switching mechanism 31, the second gas refrigerant communication pipe 8b, the first gas refrigerant opening / closing mechanism 35, and the first gas refrigerant communication pipe 8a, and the indoor heat exchangers 52 and 62. The heat is exchanged with the indoor air supplied by the indoor fans 53 and 63 to condense into a high-pressure liquid refrigerant. The high-pressure liquid refrigerant is expanded outdoors through the indoor expansion valves 51 and 61, the first liquid refrigerant communication pipe 7a, the first liquid refrigerant open / close mechanism 37, the second liquid refrigerant check mechanism 38, and the second liquid refrigerant communication pipe 7b. The low-pressure refrigerant that is sent to the valve 24 and decompressed to become a low-pressure refrigerant is sent to the outdoor heat exchanger 23 to evaporate by exchanging heat with the outdoor air supplied by the outdoor fan 28. It becomes a low-pressure gas refrigerant. This low-pressure gas refrigerant is again sucked into the low-stage compressor 21 through the first switching mechanism 22.

  During this single stage heating operation, the hot gas opening / closing mechanism 27b is closed. For this reason, the high-pressure refrigerant that is compressed in the low-stage compressor 21 and flows through the second gas refrigerant pipe 26 b is not branched to the hot gas bypass pipe 27. That is, during the single-stage heating operation, the refrigerant does not flow through the antifreezing heat exchanger 25. As described above, in the air conditioner 1, all of the high-pressure gas refrigerant compressed in the low-stage compressor 21 is sent to the indoor heat exchangers 52 and 62 during the single-stage heating operation. As described above, in the air conditioner 1, the flow rate of the refrigerant sent to the indoor heat exchangers 52 and 62 is larger in the single-stage heating operation than in the case of flowing the refrigerant through the antifreezing heat exchanger 25, The decrease in heating capacity is suppressed.

<Two-stage heating operation>
Next, the two-stage heating operation will be described with reference to FIG. Here, FIG. 15 is a schematic configuration diagram illustrating the flow of the refrigerant during the two-stage heating operation of the air-conditioning apparatus 1.

  As described above, the two-stage heating operation is a heating operation performed under a condition where the outside air temperature is low, that is, a condition where it is difficult to ensure the heating capacity. Here, the two-stage heating operation is performed when the outside air temperature Ta detected by the outside air temperature sensor 29d is lower than a predetermined first outside air temperature Tas1 (for example, 5 ° C.).

  During the two-stage heating operation, the switching mechanisms 22 and 31 are in the state indicated by the broken line in FIG. 15, that is, for the first switching mechanism 22, the second port 22b and the fourth port 22d are communicated, and the first port The second switching mechanism 31 communicates the second port 31b and the fourth port 31d and communicates the first port 31a and the third port 31c with each other. Change the mode. Further, the high-stage intake expansion valve 39 and the second liquid refrigerant opening / closing mechanism 40 are opened, and the first gas refrigerant opening / closing mechanism 35 and the first liquid refrigerant opening / closing mechanism 37 are closed. Thereby, in the refrigerant circuit 10, the outdoor heat exchanger 23 functions as an evaporator of the refrigerant condensed in the indoor heat exchangers 42 and 52, and the indoor heat exchangers 52 and 62 are connected to the low-stage compressor 21 and the high-pressure side compressor 21. A two-stage compression refrigeration cycle that functions as a condenser for the refrigerant compressed in the stage-side compressor 32 is performed.

  In the refrigerant circuit 10, the low-pressure gas refrigerant in the refrigeration cycle is sucked into the low-stage compressor 21 and compressed to become an intermediate-pressure gas refrigerant. This intermediate-pressure gas refrigerant is sucked into the high-stage compressor 32 through the first switching mechanism 22, the second switching mechanism 31, the second gas refrigerant communication pipe 8b, and the high-stage suction expansion valve 39, and is compressed and pressurized. Gas refrigerant. This high-pressure gas refrigerant is sent to the indoor heat exchangers 52 and 62 through the first gas refrigerant communication pipe 8a, and is condensed by exchanging heat with the indoor air supplied by the indoor fans 53 and 63. Becomes a refrigerant. This high-pressure liquid refrigerant is sent to the gas-liquid separator 33 through the indoor expansion valves 51 and 61, the first liquid refrigerant communication pipe 7a, the second liquid refrigerant open / close mechanism 40, and the third liquid refrigerant check mechanism 41, It is separated into a refrigerant and a liquid refrigerant. The gas refrigerant separated in the gas-liquid separator 33 is sucked into the high stage compressor 32. Further, the liquid refrigerant separated in the gas-liquid separator 33 is sent to the outdoor expansion valve 24 through the fourth liquid refrigerant check mechanism 42 and the second liquid refrigerant communication pipe 7b, and is depressurized to be a low-pressure refrigerant. Become. The low-pressure refrigerant is sent to the outdoor heat exchanger 23, exchanges heat with outdoor air supplied by the outdoor fan 28, and evaporates to become a low-pressure gas refrigerant. This low-pressure gas refrigerant is again sucked into the low-stage compressor 21 through the first switching mechanism 22.

  During this two-stage heating operation, the hot gas opening / closing mechanism 27b is closed except when performing anti-freezing control when resuming heating, which will be described later. For this reason, the intermediate-pressure refrigerant that is compressed in the low-stage compressor 21 and flows through the second gas refrigerant pipe 26b is branched to the hot gas bypass pipe 27, except when performing anti-freezing control at the time of resuming heating described later. There is nothing. That is, during the two-stage heating operation, the refrigerant does not flow through the anti-freezing heat exchanger 25 except when performing anti-freezing control when resuming heating described later. As described above, in the air conditioning apparatus 1, during the two-stage heating operation, all of the intermediate-pressure gas refrigerant compressed in the low-stage compressor 21 is high except for the case where anti-freezing control at the time of heating restart described later is performed. It is compressed in the stage side compressor 32 to become a high-pressure gas refrigerant, and is sent to the indoor heat exchangers 52 and 62. As described above, in the air conditioner 1, the flow rate of the refrigerant sent to the indoor heat exchangers 52 and 62 is increased in the two-stage heating operation as compared with the case where the refrigerant is passed through the freeze prevention heat exchanger 25. The decrease in heating capacity is suppressed.

<Single stage defrosting operation>
Next, the single stage defrosting operation will be described with reference to FIG. Here, FIG. 13 is a schematic configuration diagram illustrating the flow of the refrigerant during the single-stage defrosting operation of the air-conditioning apparatus 1.

  The single-stage defrosting operation is a defrosting operation performed under a condition in which the outside air temperature is high, like the heating operation. Here, similarly to the single-stage heating operation, the single-stage defrosting operation is performed when the outside air temperature Ta detected by the outside air temperature sensor 29d is equal to or higher than a predetermined first outside air temperature Tas1.

  As described above, the single-stage defrosting operation is a reverse cycle defrosting operation in which the refrigerant flow direction is reversed from the single-stage heating operation. Therefore, during the single-stage defrosting operation, the switching mechanisms 22 and 31 are in the state indicated by the solid line in FIG. 13, that is, the first switching mechanism 22 is connected to the second port 22b and the third port 22c, and The first port 22a and the fourth port 22d are switched to communicate with each other, the second switching mechanism 31 is connected to the second port 31b and the third port 31c, and the first port 31a and the fourth port are communicated. Switching to communicate with 31d is performed. Further, the first gas refrigerant opening / closing mechanism 35 is opened, and the first liquid refrigerant opening / closing mechanism 37, the high-stage suction expansion valve 39, and the second liquid refrigerant opening / closing mechanism 40 are closed. Thereby, in the refrigerant circuit 10, the outdoor heat exchanger 23 is made to function as a condenser of the refrigerant | coolant compressed in the low stage side compressor 21, and the indoor heat exchangers 52 and 62 were condensed in the outdoor heat exchanger 23. A single-stage compression refrigeration cycle is performed which functions as a refrigerant evaporator.

  Here, the single-stage defrosting operation is performed when the control unit 9 determines that frost formation has occurred in the outdoor heat exchanger 23 during the heating operation. This determination is performed based on the temperature Tb of the refrigerant flowing through the outdoor heat exchanger 23 detected by the outdoor heat exchanger temperature sensor 29c and the accumulated time of the heating operation. For example, when it is detected that the temperature Tb of the refrigerant detected by the outdoor heat exchanger temperature sensor 29c has decreased to a predetermined temperature or less that can be regarded as frost formation in the outdoor heat exchanger 23, or heating If the accumulated time of operation has passed a predetermined time that can be regarded as frost formation in the outdoor heat exchanger 23, it is determined that frost formation has occurred in the outdoor heat exchanger 23. When the temperature and time conditions are not reached, it is determined that frost formation has not occurred in the outdoor heat exchanger 23.

  In the refrigerant circuit 10, the refrigerant circulates in the same flow direction as that in the cooling operation. Then, the high-pressure refrigerant that is compressed by the low-stage compressor 21 and flows through the second gas refrigerant pipe 26 b is sent to the outdoor heat exchanger 23 through the switching mechanism 22 to heat the outdoor heat exchanger 23. Thereby, the frost generated in the outdoor heat exchanger 23 in the heating operation is melted to become drain water, and passes through the anti-freezing heat exchanger 25 integrated with the outdoor heat exchanger 23 to the lower side of the outdoor heat exchanger 23. It collects on the bottom plate 2a of the outdoor unit 2 as a drain pan arranged. The drain water accumulated on the bottom plate 2a is discharged out of the outdoor unit 2 through a discharge port 2b formed on the bottom plate 2a.

  The single-stage defrosting operation ends when the control unit 9 determines that the defrosting of the outdoor heat exchanger 23 has been completed. This determination is made based on the temperature Tb of the refrigerant flowing through the outdoor heat exchanger 23 detected by the outdoor heat exchanger temperature sensor 29c and the operation time of the single-stage defrosting operation. For example, when it is detected that the temperature Tb of the refrigerant detected by the outdoor heat exchanger temperature sensor 29c is equal to or higher than a temperature at which frost can be regarded as melted, or the operation time of the single-stage defrosting operation When the predetermined time or more has elapsed, it is determined that the defrosting of the outdoor heat exchanger 23 has been completed, and when the temperature condition or time condition has not been reached, the defrosting of the outdoor heat exchanger 23 has been completed. It is determined that it has not been completed.

  During this single-stage defrosting operation, the hot gas opening / closing mechanism 27b is opened as in the above cooling operation. For this reason, a part of the high-pressure refrigerant that is compressed in the low-stage compressor 21 and flows through the second gas refrigerant pipe 26 b is branched to the hot gas bypass pipe 27. The high-pressure refrigerant branched into the hot gas bypass pipe 27 is sent to the antifreezing heat exchanger 25 to heat the lower side of the outdoor heat exchanger 23. That is, the anti-freezing heat exchanger 25 functions as a heater for drain water melted by performing a single-stage defrosting operation. As a result, during the single-stage defrosting operation, the drain water from the outdoor heat exchanger 23 is heated on the lower side of the outdoor heat exchanger 23 and then collected on the bottom plate 2a of the outdoor unit 2 as a drain pan. It is discharged out of the unit 2. Thus, in the air conditioner 1, during the single-stage defrosting operation, the freeze prevention heat exchanger 25 heats the drain water generated in the outdoor heat exchanger 23 on the lower side of the outdoor heat exchanger 23. It has become. Thereby, in the air conditioning apparatus 1, the drain water from the outdoor heat exchanger 23 is quickly discharged | emitted out of the outdoor unit 2 at the time of a single stage defrost operation.

<Two-stage defrosting operation>
Next, the two-stage defrosting operation will be described with reference to FIG. Here, FIG. 16 is a schematic configuration diagram illustrating the flow of the refrigerant during the two-stage defrosting operation of the air-conditioning apparatus 1.

  Similar to the heating operation, the two-stage defrosting operation is a defrosting operation performed under a condition where the outside air temperature is low. Here, similarly to the two-stage heating operation, the two-stage defrosting operation is performed when the outside air temperature Ta detected by the outside air temperature sensor 29d is lower than the predetermined first outside air temperature Tas1.

  As described above, the two-stage defrosting operation is a reverse cycle defrosting operation in which the refrigerant flow direction is reversed from the two-stage heating operation. Therefore, during the two-stage defrosting operation, the switching mechanisms 22 and 31 are in the state indicated by the solid line in FIG. 16, that is, the first switching mechanism 22 is connected to the second port 22b and the third port 22c, and The first port 22a and the fourth port 22d are switched to communicate with each other, the second switching mechanism 31 is connected to the second port 31b and the third port 31c, and the first port 31a and the fourth port are communicated. Switching to communicate with 31d is performed. Further, the first gas refrigerant opening / closing mechanism 35 and the second liquid refrigerant opening / closing mechanism 40 are opened, and the first liquid refrigerant opening / closing mechanism 37 and the high stage suction expansion valve 39 are closed. Thereby, in the refrigerant circuit 10, the outdoor heat exchanger 23 is caused to function as a condenser for the refrigerant compressed in the high-stage compressor 32 and the low-stage compressor 21, and the indoor heat exchangers 52 and 62 are operated outdoors. A two-stage compression refrigeration cycle that functions as an evaporator for the refrigerant condensed in the heat exchanger 23 is performed.

  Here, similarly to the single-stage defrosting operation, the two-stage defrosting operation is performed when the controller 9 determines that frost formation has occurred in the outdoor heat exchanger 23 during the heating operation. Since the content of this determination is the same as the content of the determination in the single stage defrosting operation, the description is omitted here.

  In the refrigerant circuit 10, the gas refrigerant is sucked into the low stage compressor 21 and compressed to become a high-pressure gas refrigerant. This high-pressure gas refrigerant is sent to the outdoor heat exchanger 23 through the first switching mechanism 22 to heat the outdoor heat exchanger 23. Thereby, the frost generated in the outdoor heat exchanger 23 in the heating operation is melted to become drain water, and passes through the anti-freezing heat exchanger 25 integrated with the outdoor heat exchanger 23 to the lower side of the outdoor heat exchanger 23. It collects on the bottom plate 2a of the outdoor unit 2 as a drain pan arranged. The drain water accumulated on the bottom plate 2a is discharged out of the outdoor unit 2 through a discharge port 2b formed on the bottom plate 2a. The high-pressure refrigerant that has melted frost in the outdoor heat exchanger 24 is sent to the outdoor expansion valve 24 to be depressurized. A part of the decompressed refrigerant is sent to the indoor expansion valves 51 and 61 through the second liquid refrigerant communication pipe 7b, the first liquid refrigerant check mechanism 36 and the first liquid refrigerant communication pipe 7a, and the rest The second liquid refrigerant communication pipe 7b, the first liquid refrigerant check mechanism 36, the second liquid refrigerant open / close mechanism 40, and the third liquid refrigerant check mechanism 41 are sent to the gas-liquid separator 33. The low-pressure refrigerant sent to the indoor expansion valves 51 and 61 is sent to the ninth gas refrigerant pipe 34a through the indoor expansion valves 51 and 61, the indoor heat exchangers 52 and 62, and the first gas refrigerant communication pipe 8a. The low-pressure refrigerant sent to the gas-liquid separator 33 is sucked into the high-stage compressor 32 and compressed, sent to the ninth gas refrigerant pipe 34a, and sent to the indoor expansion valves 51 and 61 and the indoor It merges with the refrigerant sent to the ninth gas refrigerant pipe 34a through the heat exchangers 52 and 62. The refrigerant merged in the ninth gas refrigerant pipe 34 a is again sucked into the low-stage compressor 21 through the first gas refrigerant opening / closing mechanism 35, the second gas refrigerant communication pipe 8 b and the second switching mechanism 31.

  Then, the two-stage defrosting operation ends when the control unit 9 determines that the defrosting of the outdoor heat exchanger 23 has been completed, similarly to the single-stage defrosting operation. Since the content of this determination is the same as the content of the determination in the single stage defrosting operation, the description is omitted here.

  During the two-stage defrosting operation, the hot gas opening / closing mechanism 27b is opened in the same manner as in the single-stage defrosting operation. For this reason, a part of the high-pressure refrigerant that is compressed in the low-stage compressor 21 and flows through the second gas refrigerant pipe 26 b is branched to the hot gas bypass pipe 27. The high-pressure refrigerant branched into the hot gas bypass pipe 27 is sent to the antifreezing heat exchanger 25 to heat the lower side of the outdoor heat exchanger 23. That is, the anti-freezing heat exchanger 25 functions as a heater for drain water melted by performing the two-stage defrosting operation. Thus, during the two-stage defrosting operation, the drain water from the outdoor heat exchanger 23 is heated on the lower side of the outdoor heat exchanger 23 and then collected on the bottom plate 2a of the outdoor unit 2 as a drain pan. It is discharged out of the unit 2. Thus, in the air conditioner 1, during the two-stage defrosting operation, the antifreezing heat exchanger 25 heats the drain water generated in the outdoor heat exchanger 23 on the lower side of the outdoor heat exchanger 23. It has become. Thereby, in the air conditioning apparatus 1, drain water is quickly discharged out of the outdoor unit 2 during the two-stage defrosting operation. In particular, the two-stage defrosting operation is performed under a condition where the outside air temperature is lower than the condition of the outside air temperature at which the single stage defrosting operation is performed (that is, when the outside air temperature Ta is lower than the predetermined first outside air temperature Tas1). The drain water from the outdoor heat exchanger 23 can be prevented from freezing on the lower side of the outdoor heat exchanger 23, and the occurrence of the ice-up phenomenon during the two-stage defrosting operation is suppressed.

<Freezing prevention control when resuming heating>
As described above, in the air conditioning apparatus 1, during the defrosting operation, a part of the high-pressure refrigerant compressed by the low-stage compressor 21 is caused to flow through the antifreezing heat exchanger 25 during the defrosting operation. Freezing of drain water in can be prevented.

  However, for a while after the defrosting operation is completed, the drain water melted by performing the defrosting operation exists on the lower side of the outdoor heat exchanger 23, and the drain water to the outside of the outdoor unit 2 is present. Emission continues. Thereafter, when the heating operation is resumed, there is a possibility that the drain water is frozen before the drain water is discharged under a condition where the outside air temperature Ta is low. For this reason, the freezing of drain water at the time of the two-stage heating operation after the defrosting operation cannot be prevented, and an ice-up phenomenon may occur.

  Therefore, in the air conditioner 1, in the initial stage of restart of the two-stage heating operation after the defrosting operation, a part of the refrigerant compressed in the low-stage compressor 21 is flown to the freezing prevention heat exchanger 25 when the heating is restarted. Preventive control is performed.

  Next, this anti-freezing control when resuming heating will be described with reference to FIGS. 17 and 18. Here, FIG. 17 is a flowchart of the freeze prevention control at the resumption of heating of the air conditioner 1. FIG. 18 is a schematic configuration diagram illustrating the flow of the refrigerant during the freeze prevention control at the time of resuming heating of the air-conditioning apparatus 1.

  First, the control part 9 determines whether it is the two-stage heating operation after a defrost operation in step S1. In this step S1, when it is determined that the two-stage heating operation is performed after the defrosting operation, the process proceeds to the process of step S2 for determining whether or not an outside air temperature condition that requires the anti-freezing control when resuming heating is satisfied. .

  In step S2, the controller 9 determines whether or not the outside air temperature Ta detected by the outside air temperature sensor 29d is equal to or lower than a predetermined second outside air temperature Tas2. In this step S2, when the outside air temperature Ta is equal to or lower than the predetermined second outside air temperature Tas2, that is, when the outside air temperature condition is satisfied, the process proceeds to the processing of steps S3 to S5 for executing the anti-freezing control when resuming heating. . On the other hand, when the outside air temperature Ta is higher than the predetermined second outside air temperature Tas2, that is, when the outside air temperature condition is not satisfied, the two-stage heating operation is performed without performing the freeze prevention control at the time of resuming the heating in steps S3 to S5. Resume. Here, the predetermined second outside air temperature Tas2 is set in view of whether or not the drain water present on the lower side of the outdoor heat exchanger 23 may be frozen after the defrosting operation. Is set to 0 ° C. The predetermined second outside air temperature Tas2 is lower than the first outside air temperature Tas1, which is a temperature at which switching between the single-stage heating operation and the two-stage heating operation is performed. The predetermined second outside air temperature Tas2 is stored in advance in a memory or the like of the control unit 9, and is changed by a switch (not shown) or a remote controller (not shown) provided in the control unit 9. Can be done.

  Then, in step S3, the control unit 9 starts the anti-freezing control at the resumption of heating in which a part of the refrigerant compressed by the low-stage compressor 21 is passed to the anti-freezing heat exchanger 25. That is, in the refrigerant circuit 10, the same refrigeration cycle as in the above-described two-stage heating operation is performed, and the hot gas opening / closing mechanism 27b is opened. For this reason, a part of the high-pressure refrigerant that is compressed in the low-stage compressor 21 and flows through the second gas refrigerant pipe 26 b is branched to the hot gas bypass pipe 27. The high-pressure refrigerant branched into the hot gas bypass pipe 27 is sent to the antifreezing heat exchanger 25 to heat the lower side of the outdoor heat exchanger 23. That is, the antifreezing heat exchanger 25 functions as a heater for drain water existing on the lower side of the outdoor heat exchanger 23 after the defrosting operation. Here, since the outlet of the hot gas bypass pipe 27 is connected to a portion of the liquid refrigerant pipe 26e through which the low-pressure refrigerant flows downstream of the outdoor expansion valve 24, the flow rate of the refrigerant flowing through the hot gas bypass pipe 27 is high. It is easy to be secured. The refrigerant that has heated the drain water in the antifreezing heat exchanger 25 condenses in the antifreezing heat exchanger 25, but then merges with the refrigerant flowing through the liquid refrigerant pipe 26e and functions as a refrigerant evaporator. Therefore, the refrigerant condensed in the freezing prevention heat exchanger 25 remains in a liquid state and is not sucked into the low-stage compressor 21. As a result, during the two-stage heating operation after the defrosting operation, the drain water present on the lower side of the outdoor heat exchanger 23 is heated in the freezing prevention heat exchanger 25 and then the outdoor unit 2 as a drain pan. It accumulates on the bottom plate 2 a and is discharged out of the outdoor unit 2. Thus, in the air conditioner 1, the anti-freezing heat exchanger 25 heats the drain water present on the lower side of the outdoor heat exchanger 23 during the two-stage heating operation after the defrosting operation. Yes. Thereby, in the air conditioning apparatus 1, in the two-stage heating operation after the defrosting operation, the drain water present on the lower side of the outdoor heat exchanger 23 can be discharged without freezing after the defrosting operation. Occurrence of the ice-up phenomenon during the two-stage heating operation after the defrosting operation is suppressed.

  And control part 9 judges whether predetermined time ts passed after defrost operation in Step S4, and when predetermined time ts passed, it shifts to processing of Step S5. Here, the predetermined time ts is set to about several minutes in consideration of the time required to discharge the drain water present on the lower side of the outdoor heat exchanger 23 after the defrosting operation. The predetermined time ts is stored in advance in a memory or the like of the control unit 9 and can be changed by a switch (not shown) or a remote controller (not shown) provided in the control unit 9. It has become. And the control part 9 complete | finishes freezing prevention control at the time of heating resumption in step S5, and transfers to normal two-stage heating operation. That is, in the refrigerant circuit 10, the same refrigeration cycle as in the above-described two-stage heating operation is performed, and the hot gas opening / closing mechanism 27b is closed. For this reason, during the two-stage heating operation after the defrosting operation, the predetermined time ts for discharging the drain water existing on the lower side of the outdoor heat exchanger 23 after the defrosting operation without freezing, that is, the defrosting operation. Only when the subsequent two-stage heating operation is restarted, the anti-freezing control at the time of restarting heating is performed. Here, during the two-stage heating operation after the defrosting operation, flowing a part of the refrigerant compressed in the low-stage compressor 21 to the anti-freezing heat exchanger 25 is sent to the indoor heat exchangers 52 and 62. Since the flow rate of the refrigerant to be reduced is reduced, the heating capacity is reduced. However, in the air conditioner 1, as described above, only a part of the refrigerant compressed in the low-stage compressor 21 is used for preventing freezing only in the initial stage of restarting the two-stage heating operation in the heating operation after the defrosting operation. It is made to flow to the heat exchanger 25. For this reason, in the air conditioning apparatus 1, the fall of the heating capability in the heating operation after a defrost operation is suppressed.

  As described above, the air conditioner 1 can suppress the occurrence of the ice-up phenomenon during the two-stage heating operation after the defrosting operation while suppressing the decrease in the heating capacity in the heating operation after the defrosting operation. It has become.

(3) Features of the air conditioner The air conditioner 1 that performs the two-stage compression refrigeration cycle as in the present embodiment also has the same features as the air conditioner 1 of the first embodiment.

<A>
That is, in the air conditioner 1, during the two-stage heating operation after the defrosting operation, a part of the refrigerant compressed in the compression mechanism 20 (here, the low-stage compressor 21) is transferred to the antifreezing heat exchanger 25. By flowing, the drain water present on the lower side of the outdoor heat exchanger 23 is frozen after the defrosting operation under conditions where the outside air temperature Ta is low (here, the outside air temperature Ta is equal to or less than the second outside air temperature Tas2). It can discharge without. For this reason, in the air conditioning apparatus 1, generation | occurrence | production of the ice-up phenomenon at the time of the two-stage heating operation after a defrost operation can be suppressed.

  Here, during the two-stage heating operation after the defrosting operation, flowing a part of the refrigerant compressed in the low-stage compressor 21 to the anti-freezing heat exchanger 25 is sent to the indoor heat exchangers 52 and 62. Since the flow rate of the refrigerant to be reduced is reduced, the heating capacity is reduced.

  Therefore, in the air conditioner 1, as described above, a part of the refrigerant compressed in the low-stage compressor 21 is used for preventing freezing only in the initial stage of restarting the two-stage heating operation in the heating operation after the defrosting operation. It is made to flow to the heat exchanger 25 (that is, freeze prevention control when resuming heating). For this reason, in the air conditioning apparatus 1, the fall of the heating capability in the heating operation after a defrost operation can be suppressed.

  Thereby, in the air conditioning apparatus 1, generation | occurrence | production of the ice-up phenomenon at the time of the two-stage heating operation after a defrost operation can be suppressed, suppressing the fall of the heating capability in the heating operation after a defrost operation.

<B>
In the air conditioner 1, the antifreezing control at the time of resuming heating is performed when the outside air temperature Ta is equal to or lower than a predetermined second outside air temperature Tas2. For this reason, in the air conditioner 1, only under conditions where the outside air temperature Ta at which the drain water present on the lower side of the outdoor heat exchanger 23 may freeze after the defrosting operation is low (in this case, 0 ° C. or less). When the heating is resumed, the freeze prevention control is performed. Under the condition where the outside air temperature Ta is high (in this case, higher than 0 ° C.), the freeze prevention control when the heating is resumed can be omitted.

  Thereby, in the air conditioning apparatus 1, the fall of the heating capability in the heating operation after a defrost operation can further be suppressed.

<C>
In the air conditioner 1, the freeze prevention control at the time of resuming heating is performed until a predetermined time ts elapses after the defrosting operation. That is, in the air conditioner 1, since the freeze prevention control at the time of resuming heating is managed by time, the time required for discharging the drain water present on the lower side of the outdoor heat exchanger 23 after the defrosting operation. Can be considered.

  Thereby, in the air conditioning apparatus 1, the freeze prevention control at the time of resuming heating can be appropriately performed in consideration of the time required for discharging drain water.

(4) Modified Example In the air conditioner 1 of the above embodiment, as in the modified example 1 (see FIG. 8) of the air conditioner 1 of the first embodiment, the outside air humidity increases as the outside temperature Ta decreases. As the operating time of the defrosting operation becomes longer, the predetermined time ts may be set longer.

  Moreover, in the air conditioning apparatus 1 of the said embodiment, the heat exchanger 25 for antifreezing is added to the hot gas bypass pipe 27 similarly to the modification 2 (refer FIG.9 and FIG.10) of the air conditioning apparatus 1 of 1st Embodiment. The hot gas flow rate adjustment valve 27d for changing the flow rate of the refrigerant flowing through the refrigerant is provided, and the heating is resumed as the outside air temperature Ta becomes low, the outside air humidity becomes high, or the operation time of the defrosting operation becomes long. You may set so that the opening degree of the hot gas flow control valve 27d in a time freezing prevention control may be enlarged.

  Thereby, also in the air conditioning apparatus 1 of this modification, the change of the amount of drain water by conditions, such as external temperature Ta, is considered similarly to the modifications 1 and 2 of the air conditioning apparatus 1 of 1st Embodiment. In addition, it is possible to appropriately perform anti-freezing control when resuming heating.

-Other embodiments-
As mentioned above, although embodiment of this invention and its modification were demonstrated based on drawing, specific structure is not restricted to the said embodiment and its modification, It can change in the range which does not deviate from the summary of invention. It is.

  In the above embodiment and its modifications, the present invention is applied to an air conditioner that can be switched between cooling and heating by switching between cooling operation, heating operation, and reverse cycle defrosting operation, but is not limited thereto, for example, The present invention may be applied to a heating-only air conditioner that performs switching between heating operation and reverse cycle defrosting operation but does not perform cooling operation.

  The present invention relates to an air conditioner that performs a heating operation and a reverse cycle defrosting operation.

DESCRIPTION OF SYMBOLS 1 Air conditioning apparatus 20 Compression mechanism 21 Compressor (compression mechanism)
23 Outdoor Heat Exchanger 25 Freezing Prevention Heat Exchanger 52, 62 Indoor Heat Exchanger 27d Hot Gas Flow Control Valve (Flow Control Valve)

JP 2009-127939 A

  The present invention relates to an air conditioner, and more particularly to an air conditioner that performs a heating operation and a reverse cycle defrosting operation.

  Conventionally, there is an air conditioner that performs heating operation and reverse cycle defrosting operation. In such an air conditioner, when heating operation is performed under a condition where the outside air temperature is low, frost formation occurs in the outdoor heat exchanger that functions as a refrigerant evaporator. The frost generated in the outdoor heat exchanger in the heating operation is melted by performing the reverse cycle defrosting operation, and is discharged as drain water through the bottom plate of the outdoor unit disposed below the outdoor heat exchanger. Here, in the reverse cycle defrosting operation, the refrigerant is circulated in the order of the compressor, the outdoor heat exchanger, and the indoor heat exchanger, so that the outdoor heat exchanger is heated by the refrigerant compressed in the compressor. Driving. Moreover, the bottom plate of the outdoor unit functions as a drain pan.

  However, under conditions where the outside air temperature is low, the drain water generated during the reverse cycle defrosting operation may freeze on the lower side of the outdoor heat exchanger. Such freezing of drain water may cause excessive ice growth (ice-up phenomenon) on the lower side of the outdoor heat exchanger.

  On the other hand, as shown in patent document 1 (Unexamined-Japanese-Patent No. 2009-127939), the auxiliary heat exchanger was provided in the lower part side of the outdoor heat exchanger, and it was compressed in the compressor at the time of reverse cycle defrosting operation. There is an air conditioner configured to heat an auxiliary heat exchanger with a part of a refrigerant.

  In the said conventional air conditioning apparatus, freezing of drain water at the time of a defrost operation can be prevented.

  However, for a while after the defrosting operation is completed, the drain water melted by performing the defrosting operation exists on the lower side of the outdoor heat exchanger, and the drain water continues to be discharged. Thereafter, when the heating operation is resumed, there is a possibility that the drain water is frozen before the drain water is discharged under a condition where the outside air temperature is low. For this reason, in the said conventional air conditioning apparatus, freezing of drain water at the time of the heating operation after a defrost operation cannot be prevented, and there exists a possibility that an ice-up phenomenon may generate | occur | produce.

  The subject of this invention is suppressing the generation | occurrence | production of the ice-up phenomenon at the time of the heating operation after a defrost operation in the air conditioning apparatus which performs a heating operation and a reverse cycle defrost operation.

An air conditioner according to a first aspect performs a heating operation by circulating a refrigerant in the order of a compression mechanism, an indoor heat exchanger, and an outdoor heat exchanger, and the compression mechanism, the outdoor heat exchanger, and the indoor heat exchange. It is an air conditioner that performs cooling operation and defrosting operation by circulating refrigerant in the order of the units. In this air conditioner, the lower part of the outdoor heat exchanger is heated by a part of the refrigerant compressed by the compression mechanism so that the refrigerant can be merged with the liquid side of the outdoor heat exchanger. In the initial stage of resuming the heating operation after the defrosting operation , when the outside air temperature is equal to or lower than the predetermined outside air temperature, resuming the heating that causes a part of the refrigerant compressed in the compression mechanism to flow to the antifreezing heat exchanger time have rows antifreeze control, even during the cooling operation, flowing a part of the refrigerant compressed in the compression mechanism to the heat exchanger for freezing prevention.

  In this air conditioner, during the heating operation after the defrosting operation, a part of the refrigerant compressed in the compression mechanism is caused to flow through the antifreezing heat exchanger, so that the outdoor heat is removed after the defrosting operation under a condition where the outside air temperature is low. The drain water present on the lower side of the exchanger can be discharged without freezing. For this reason, in this air conditioner, it is possible to suppress the occurrence of the ice-up phenomenon during the heating operation after the defrosting operation.

  Here, in the heating operation after the defrosting operation, flowing a part of the refrigerant compressed in the compression mechanism to the anti-freezing heat exchanger reduces the flow rate of the refrigerant sent to the indoor heat exchanger. , Will reduce the heating capacity.

  Therefore, in this air conditioner, as described above, a part of the refrigerant compressed in the compression mechanism is allowed to flow to the antifreezing heat exchanger only in the early stage of the heating operation after the defrosting operation. I have to. For this reason, in this air conditioning apparatus, the fall of the heating capability in the heating operation after a defrost operation can be suppressed.

  Thereby, in this air conditioning apparatus, generation | occurrence | production of the ice-up phenomenon at the time of the heating operation after a defrost operation can be suppressed, suppressing the fall of the heating capability in the heating operation after a defrost operation.

In addition, this air conditioner performs the freeze prevention control when resuming heating when the outside air temperature is equal to or lower than a predetermined outside air temperature.

  In this air conditioner, after the defrosting operation, only when the outside air temperature at which the drain water existing on the lower side of the outdoor heat exchanger is likely to freeze is low, anti-freezing control when resuming heating is performed, and the outside air temperature is high. In this case, it is possible to avoid the freeze prevention control when resuming heating.

  Thereby, in this air conditioning apparatus, the fall of the heating capability in the heating operation after a defrost operation can further be suppressed.

Further, in this air conditioner, a heat exchanger for freezing prevention is provided so that the refrigerant can be merged with the liquid side of the outdoor heat exchanger, and a part of the refrigerant compressed by the compression mechanism is also used during cooling operation. It flows through the heat exchanger for freezing prevention.

  Thereby, in this air conditioning apparatus, cooling of the refrigerant sent to the indoor heat exchanger is promoted during the cooling operation, and the cooling capacity can be improved.

The air conditioning apparatus according to the second aspect is the air conditioning apparatus according to the first aspect, wherein the anti-freezing control when resuming heating is performed until a predetermined time elapses after the defrosting operation.

  In this air conditioner, since the freeze prevention control at the time of resuming heating is managed by time, the time necessary for discharging drain water present on the lower side of the outdoor heat exchanger after defrosting operation is taken into consideration. be able to.

  Thereby, in this air conditioning apparatus, the freeze prevention control at the time of resuming heating can be appropriately performed in consideration of the time required for discharging drain water.

The air conditioner according to the third aspect is the air conditioner according to the second aspect, as the outside air temperature decreases, the outside air humidity increases, or the operating time of the defrosting operation increases. Increase time.

  The amount of drain water present on the lower side of the outdoor heat exchanger after the defrosting operation varies depending on the outside air temperature, the outside air humidity, or the operation time of the defrosting operation. Specifically, the amount of drain water increases as the outside air temperature decreases, the outside air humidity increases, or the operating time of the defrosting operation increases. For this reason, it is preferable to change also about the predetermined time of anti-freezing control at the time of heating resumption according to the outside air temperature, the outside air humidity, or the operating time of the defrosting operation.

  Therefore, in this air conditioner, as described above, the predetermined time is increased as the outside air temperature decreases, the outside air humidity increases, or the operating time of the defrosting operation increases. For this reason, in this air conditioning apparatus, it is possible to consider the amount of drain water that changes depending on the outside air temperature, the outside air humidity, or the operating time of the defrosting operation.

  Thereby, in this air conditioner, it is possible to appropriately perform the freeze prevention control at the time of resuming heating in consideration of a change in the amount of drain water due to conditions such as the outside air temperature.

An air conditioner according to a fourth aspect is the air conditioner according to the first or second aspect , further comprising a flow rate adjustment valve for varying the flow rate of the refrigerant flowing through the antifreezing heat exchanger, and the outside air temperature. The degree of opening of the flow rate control valve is increased as the humidity becomes lower, the outside air humidity becomes higher, or the operating time of the defrosting operation becomes longer.

  The amount of drain water present on the lower side of the outdoor heat exchanger after the defrosting operation varies depending on the outside air temperature, the outside air humidity, or the operation time of the defrosting operation. Specifically, the amount of drain water increases as the outside air temperature decreases, the outside air humidity increases, or the operating time of the defrosting operation increases. For this reason, it is preferable to change the flow rate of the refrigerant flowing through the antifreezing heat exchanger in the antifreezing control when resuming heating depending on the outside air temperature, the outside air humidity, or the operating time of the defrosting operation.

  Therefore, in this air conditioner, as described above, the opening degree of the flow control valve is increased as the outside air temperature decreases, the outside air humidity increases, or the operating time of the defrosting operation increases. The flow rate of the refrigerant is increased. For this reason, in this air conditioning apparatus, it is possible to consider the amount of drain water that changes depending on the outside air temperature, the outside air humidity, or the operating time of the defrosting operation.

  Thereby, in this air conditioner, it is possible to appropriately perform the freeze prevention control at the time of resuming heating in consideration of a change in the amount of drain water due to conditions such as the outside air temperature.

  As described above, according to the present invention, the following effects can be obtained.

In the air conditioner according to the first aspect, it is possible to suppress the occurrence of the ice-up phenomenon during the heating operation after the defrosting operation while suppressing a decrease in the heating capacity during the heating operation after the defrosting operation. Moreover, the fall of the heating capability in the heating operation after a defrost operation can further be suppressed. Furthermore, during the cooling operation, cooling of the refrigerant sent to the indoor heat exchanger is promoted, and the cooling capacity can be improved.

In the air conditioner according to the second aspect , it is possible to appropriately perform the freeze prevention control at the time of resuming heating in consideration of the time required for discharging the drain water.

In the air conditioner according to the third aspect , it is possible to appropriately perform the freeze prevention control when resuming heating in consideration of a change in the amount of drain water due to conditions such as the outside air temperature.

In the air conditioner according to the fourth aspect , it is possible to appropriately perform the freeze prevention control when resuming heating in consideration of a change in the amount of drain water due to conditions such as the outside air temperature.

It is a schematic structure figure of the air harmony device concerning a 1st embodiment of the present invention. It is a schematic diagram which shows the lower part side of the outdoor heat exchanger containing the heat exchanger for freezing prevention, and the baseplate of an outdoor unit. It is a control block diagram of the air conditioning apparatus concerning 1st Embodiment. It is a schematic block diagram which shows the flow of the refrigerant | coolant at the time of air_conditionaing | cooling operation and defrost operation of the air conditioning apparatus concerning 1st Embodiment. It is a schematic block diagram which shows the flow of the refrigerant | coolant at the time of the heating operation of the air conditioning apparatus concerning 1st Embodiment. It is a flowchart of antifreezing control at the time of heating resumption of the air harmony device concerning a 1st embodiment. It is a schematic block diagram which shows the flow of the refrigerant | coolant at the time of freeze prevention control at the time of the heating resumption of the air conditioning apparatus concerning 1st Embodiment. It is a flowchart of the freeze prevention control at the time of heating resumption of the air conditioning apparatus concerning the modification 1 of 1st Embodiment. It is a schematic block diagram of the air conditioning apparatus concerning the modification 2 of 1st Embodiment of this invention. It is a flowchart of the freeze prevention control at the time of heating resumption of the air conditioning apparatus concerning the modification 2 of 1st Embodiment. It is a schematic block diagram of the air conditioning apparatus concerning 2nd Embodiment of this invention. It is a control block diagram of the air conditioning apparatus concerning 2nd Embodiment. It is a schematic block diagram which shows the flow of the refrigerant | coolant at the time of the air_conditionaing | cooling operation and single stage defrost operation of the air conditioning apparatus concerning 2nd Embodiment. It is a schematic block diagram which shows the flow of the refrigerant | coolant at the time of the single stage heating operation of the air conditioning apparatus concerning 2nd Embodiment. It is a schematic block diagram which shows the flow of the refrigerant | coolant at the time of the two-stage heating operation of the air conditioning apparatus concerning 2nd Embodiment. It is a schematic block diagram which shows the flow of the refrigerant | coolant at the time of the two-stage defrost operation of the air conditioning apparatus concerning 2nd Embodiment. It is a flowchart of the freeze prevention control at the time of the heating resumption of the air conditioning apparatus concerning 2nd Embodiment. It is a schematic block diagram which shows the flow of the refrigerant | coolant at the time of freeze prevention control at the time of the heating resumption of the air conditioning apparatus concerning 2nd Embodiment.

  DESCRIPTION OF EMBODIMENTS Hereinafter, embodiments of an air conditioner according to the present invention will be described based on the drawings.

-First embodiment-
(1) Configuration of Air Conditioner FIG. 1 is a schematic configuration diagram of an air conditioner 1 according to the first embodiment of the present invention. The air conditioning apparatus 1 is an apparatus used for air conditioning in a room such as a building by performing a vapor compression refrigeration cycle. The air conditioner 1 mainly includes a single outdoor unit 2, a plurality (in this case, two) of indoor units 5 and 6, and a liquid refrigerant communication pipe that connects the outdoor unit 2 and the indoor units 5 and 6. 7 and a gas refrigerant communication pipe 8. That is, the vapor compression refrigerant circuit 10 of the air conditioner 1 is configured by connecting the outdoor unit 2, the indoor units 5 and 6, the liquid refrigerant communication tube 7 and the gas refrigerant communication tube 8. . Note that the number of indoor units 5 and 6 is not limited to two, and may be one or three or more.

<Indoor unit>
The indoor units 5 and 6 are installed by embedding or hanging in a ceiling of a room such as a building or hanging on a wall surface of the room. The indoor units 5 and 6 are connected to the outdoor unit 2 via the liquid refrigerant communication pipe 7 and the gas refrigerant communication pipe 8 and constitute a part of the refrigerant circuit 10.

  Next, the configuration of the indoor units 5 and 6 will be described. In addition, since the indoor unit 5 and the indoor unit 6 have the same configuration, only the configuration of the indoor unit 5 will be described here, and the configuration of the indoor unit 6 is the 50th number indicating each part of the indoor unit 5. The reference numerals in the 60s are attached instead of the reference numerals, and description of each part is omitted.

  The indoor unit 5 mainly has an indoor expansion valve 51 and an indoor heat exchanger 52.

  The indoor expansion valve 51 is a device that adjusts the pressure and flow rate of the refrigerant flowing through the indoor unit 5. The indoor expansion valve 51 has one end connected to the liquid side of the indoor heat exchanger 52 and the other end connected to the liquid refrigerant communication tube 7. Here, an electric expansion valve is used as the indoor expansion valve 51.

  The indoor heat exchanger 52 is a heat exchanger that functions as a refrigerant evaporator during cooling operation to cool indoor air and functions as a refrigerant condenser during heating operation to heat indoor air. The indoor heat exchanger 52 has a liquid side connected to the indoor expansion valve 51 and a gas side connected to the gas refrigerant communication tube 8. Here, the indoor heat exchanger 52 is a cross-fin type fin-and-tube heat exchanger composed of heat transfer tubes and a large number of fins. The type of the indoor heat exchanger 52 is not limited to the cross fin type fin-and-tube type heat exchanger, and other types such as a laminated heat exchanger using corrugated fins or flat tubes, for example. It may be a type of heat exchanger.

  The indoor unit 5 has an indoor fan 53 for supplying indoor air as supply air after sucking indoor air into the indoor unit 5 and exchanging heat with the refrigerant in the indoor heat exchanger 52. . Here, as the indoor fan 53, a centrifugal fan or a multi-blade fan driven by an indoor fan motor 53a is used.

  The indoor unit 5 includes an indoor side control unit 54 that controls the operation of each unit constituting the indoor unit 5. And the indoor side control part 54 has a microcomputer, memory, etc. for controlling the indoor unit 5, and between the remote controllers (not shown) for operating the indoor unit 5 separately. Control signals and the like can be exchanged, and control signals and the like can be exchanged with the outdoor unit 2 via the transmission line 9a.

<Outdoor unit>
The outdoor unit 2 is installed outside a building or the like. The outdoor unit 2 is connected to the indoor units 5 and 6 via the liquid refrigerant communication pipe 7 and the gas refrigerant communication pipe 8 and constitutes a part of the refrigerant circuit 10.

  Next, the configuration of the outdoor unit 2 will be described. The outdoor unit 2 mainly includes a compressor 21 as a compression mechanism, a switching mechanism 22, an outdoor heat exchanger 23, an outdoor expansion valve 24, and a freezing prevention heat exchanger 25.

  The compressor 21 is a device that compresses the low-pressure refrigerant in the refrigeration cycle until the pressure becomes high. The compressor 21 has a hermetic structure in which a rotary type or scroll type positive displacement compression element (not shown) is rotationally driven by a compressor motor 21a. The compressor 21 has a first gas refrigerant pipe 26a connected to the suction side and a second gas refrigerant pipe 26b connected to the discharge side. The first gas refrigerant pipe 26 a is a refrigerant pipe that connects the suction side of the compressor 21 and the first port 22 a of the switching mechanism 22. The second gas refrigerant pipe 26 b is a refrigerant pipe that connects the discharge side of the compressor 21 and the second port 22 b of the switching mechanism 22. Here, although one compressor 21 constitutes a compression mechanism, a compression mechanism may be constituted by connecting a plurality of compressors 21 in parallel.

  The switching mechanism 22 is a mechanism for switching the direction of refrigerant flow in the refrigerant circuit 10. The switching mechanism 22 causes the outdoor heat exchanger 23 to function as a condenser for the refrigerant compressed in the compressor 21 during the cooling operation and the defrosting operation, and causes the indoor heat exchangers 52 and 62 to function as the outdoor heat exchanger 23. Is switched to function as an evaporator for the refrigerant condensed in step. That is, the switching mechanism 22 switches between the second port 22b and the third port 22c and the first port 22a and the fourth port 22d during the cooling operation and the defrosting operation. Thereby, the discharge side (here, the second gas refrigerant pipe 26b) of the compressor 21 and the gas side (here, the third gas refrigerant pipe 26c) of the outdoor heat exchanger 23 are connected (switching in FIG. 1). (See solid line for mechanism 22). Moreover, the suction side (here, the first gas refrigerant pipe 26a) of the compressor 21 and the gas refrigerant communication pipe 8 side (here, the fourth gas refrigerant pipe 26d) are connected (of the switching mechanism 22 of FIG. 1). (See solid line). Further, the switching mechanism 22 causes the outdoor heat exchanger 23 to function as an evaporator of the refrigerant condensed in the indoor heat exchangers 42 and 52 during the heating operation, and compresses the indoor heat exchangers 52 and 62 in the compressor 21. Switch to function as a condenser for the refrigerant. That is, during the heating operation, the switching mechanism 22 switches the second port 22b and the fourth port 22d to communicate and the first port 22a and the third port 22c to communicate. Thereby, the discharge side (here, the second gas refrigerant pipe 26b) of the compressor 21 and the gas refrigerant communication pipe 8 side (here, the fourth gas refrigerant pipe 26d) are connected (the switching mechanism 22 in FIG. 1). See the dashed line). Moreover, the suction side (here, the first gas refrigerant pipe 26a) of the compressor 21 and the gas side (here, the third gas refrigerant pipe 26c) of the outdoor heat exchanger 23 are connected (the switching mechanism in FIG. 1). (See dashed line 22). The third gas refrigerant pipe 26 c is a refrigerant pipe that connects the third port 22 c of the switching mechanism 22 and the gas side of the outdoor heat exchanger 23. The fourth gas refrigerant pipe 26d is a refrigerant pipe that connects the fourth port 22d of the switching mechanism 22 and the gas refrigerant communication pipe 8 side. Here, the switching mechanism 22 is a four-way switching valve. Here, the configuration of the switching mechanism 22 is not limited to the four-way switching valve, and may be, for example, a configuration in which a plurality of electromagnetic valves or the like are connected so as to perform the above switching function.

  The outdoor heat exchanger 23 is a heat exchanger that functions as a refrigerant condenser during a cooling operation and a defrosting operation, and functions as a refrigerant evaporator during a heating operation. The outdoor heat exchanger 23 has a liquid side connected to the liquid refrigerant pipe 26e and a gas side connected to the third gas refrigerant pipe 26c. The liquid refrigerant pipe 26e is a refrigerant pipe that connects the liquid side of the outdoor heat exchanger 23 and the liquid refrigerant communication pipe 7 side. Here, the outdoor heat exchanger 23 is a cross-fin type fin-and-tube heat exchanger composed of heat transfer tubes and a large number of fins. The type of the outdoor heat exchanger 23 is not limited to a cross fin type fin-and-tube type heat exchanger, and other types such as a laminated heat exchanger using corrugated fins or flat tubes, for example. It may be a type of heat exchanger.

  The outdoor expansion valve 24 is a device that adjusts the pressure and flow rate of the refrigerant flowing through the outdoor unit 2. The outdoor expansion valve 24 is provided in the liquid refrigerant pipe 26e. Here, an electric expansion valve is used as the outdoor expansion valve 24.

  The antifreezing heat exchanger 25 is a heat exchanger that heats the lower side of the outdoor heat exchanger 23 with a part of the refrigerant compressed in the compressor 21 as a compression mechanism. The antifreezing heat exchanger 25 is provided in the hot gas bypass pipe 27. Here, the anti-freezing heat exchanger 25 is a cross-fin type fin-and-tube heat exchanger composed of heat transfer tubes and a large number of fins, and as shown in FIG. 2, an outdoor heat exchanger. 23 is integrated with the lower part. Specifically, the outdoor heat exchanger 23 and the antifreezing heat exchanger 25 are configured as an integral fin-and-tube heat exchanger, and the heat transfer tubes and fins on the upper side are the outdoor heat exchanger 23. The heat transfer tubes and fins on the lower side constitute a heat exchanger 25 for preventing freezing. The lower end portion of the freeze prevention heat exchanger 25 is disposed on the bottom plate 2 a of the outdoor unit 2 that functions as a drain pan that receives drain water generated in the outdoor heat exchanger 23 and the freeze prevention heat exchanger 25. The bottom plate 2 a is formed with a discharge port 2 b so that drain water received on the bottom plate 2 a can be discharged out of the outdoor unit 2. Here, FIG. 2 is a schematic view showing the lower side of the outdoor heat exchanger 23 including the freeze-preventing heat exchanger 25 and the bottom plate 2 a of the outdoor unit 2. The type of the anti-freezing heat exchanger 25 is not limited to the cross-fin type fin-and-tube type heat exchanger, for example, a laminated heat exchanger using corrugated fins or flat tubes, etc. Other types of heat exchangers may be used.

  The hot gas bypass pipe 27 is a refrigerant pipe that branches a part of the refrigerant compressed in the compressor 21. One end side of the hot gas bypass pipe 27 is connected so as to branch from a middle portion of the second gas refrigerant pipe 26c, and the other end side is connected to the liquid side of the outdoor heat exchanger 23 of the liquid refrigerant pipe 26e and the outdoor expansion valve 24. It is connected to join the part between. A hot gas decompression mechanism 27a, a hot gas opening / closing mechanism 27b, and a hot gas check mechanism 27c are provided at a portion of the hot gas bypass pipe 27 on the outlet side of the heat exchanger 25 for preventing freezing. The hot gas decompression mechanism 27a is a device that decompresses the refrigerant. Here, a capillary tube is used as the hot gas decompression mechanism 27a. The hot gas opening / closing mechanism 27b is opened when a part of the refrigerant compressed in the compressor 21 is branched into the hot gas bypass pipe 27, and a part of the refrigerant compressed in the compressor 21 is branched into the hot gas bypass pipe 27. It is a device that can be closed if not. Here, an electromagnetic valve is used as the hot gas opening / closing mechanism 27b. The hot gas check mechanism 27c is a mechanism that allows the flow of the refrigerant from the outlet side of the antifreezing heat exchanger 25 to the liquid refrigerant tube 26e side and blocks the flow in the reverse direction. Here, a check valve is used as the hot gas check mechanism 27c.

  The outdoor unit 2 has an outdoor fan 28 for sucking outdoor air into the outdoor unit 2, exchanging heat with the refrigerant in the outdoor heat exchanger 23, and then discharging the air outside the outdoor unit 2. . Here, as the outdoor fan 28, an axial fan or the like driven by an outdoor fan motor 28a is used. Further, as shown in FIG. 2, the anti-freezing heat exchanger 25 is integrated with the lower part of the outdoor heat exchanger 23. Therefore, the outdoor fan 28 is not only the outdoor heat exchanger 23 but also the anti-freezing heat. Outdoor air is also supplied to the exchanger 25.

  The outdoor unit 2 is provided with various sensors. Specifically, the outdoor unit 2 is mainly provided with a suction pressure sensor 29a, a discharge pressure sensor 29b, an outdoor heat exchange temperature sensor 29c, and an outdoor temperature sensor 29d. The suction pressure sensor 29a is a pressure sensor that detects the suction pressure Ps of the compressor 21 corresponding to the low pressure in the refrigeration cycle. The discharge pressure sensor 29b is a pressure sensor that detects the discharge pressure Pd of the compressor 21 corresponding to the high pressure in the refrigeration cycle. The outdoor heat exchange temperature sensor 29 c is a temperature sensor that detects the temperature Tb of the refrigerant flowing through the outdoor heat exchanger 23. The outside air temperature sensor 29d is a temperature sensor that detects the outside air temperature Ta in the outdoor unit 2.

  The outdoor unit 2 also has an outdoor control unit 30 that controls the operation of each part constituting the outdoor unit 2. And the outdoor side control part 30 has a microcomputer, memory, etc. for controlling the outdoor unit 2, and connects the transmission line 9a between the indoor side control parts 54 and 64 of the indoor units 5 and 6. It is possible to exchange control signals and the like through the network. That is, the control part 9 which performs operation control of the whole air conditioning apparatus 1 is comprised by the indoor side control parts 54 and 64, the outdoor side control part 30, and the transmission line 9a which connects between the control parts 30,54,64. Yes.

  As illustrated in FIG. 3, the control unit 9 is configured to perform various devices and valves 21 a, 22, 24, 27 b, 28 a, 51, 53 a, 61, 63 a based on various operation settings and detection values of the various sensors 29 a to 29 d. Can be controlled. Here, FIG. 3 is a control block diagram of the air conditioner 1.

<Refrigerant communication pipe>
Refrigerant communication pipes 7 and 8 are refrigerant pipes constructed on site when the air conditioner 1 is installed at an installation location such as a building, and installation conditions such as an installation location and a combination of an outdoor unit and an indoor unit. Those having various lengths and tube diameters are used.

  As described above, the refrigerant circuit 10 of the air conditioner 1 is configured by connecting the outdoor unit 2, the indoor units 5 and 6, and the refrigerant communication pipes 7 and 8. The air conditioner 1 is operated by the control unit 9 including the indoor side control units 54 and 64 and the outdoor side control unit 30, and various operations such as a cooling operation, a heating operation, and a defrosting operation described below. Can be done.

(2) Operation of the Air Conditioner The air conditioner 1 can mainly perform a cooling operation, a heating operation, and a defrosting operation. The cooling operation is an operation in which the refrigerant is circulated mainly in the order of the compressor 21, the outdoor heat exchanger 23, and the indoor heat exchangers 52 and 62 as a compression mechanism in order to cool the indoor air. The heating operation is an operation in which the refrigerant is circulated mainly in the order of the compressor 21 as the compression mechanism, the indoor heat exchangers 52 and 62, and the outdoor heat exchanger 23 in order to heat the indoor air. In order to melt the frost generated in the outdoor heat exchanger 23 by the heating operation, the defrosting operation is mainly performed in the order of the compressor 21, the outdoor heat exchanger 23, and the indoor heat exchangers 52 and 62 as a compression mechanism. It is an operation to circulate. That is, the defrosting operation is a so-called reverse cycle defrosting operation in which the flow direction of the refrigerant is reversed from that of the heating operation. Hereinafter, operations during various operations of the air conditioner 1 will be described.

<Cooling operation>
First, the cooling operation will be described with reference to FIG. Here, FIG. 4 is a schematic configuration diagram illustrating the flow of the refrigerant during the cooling operation of the air-conditioning apparatus 1.

  During the cooling operation, the switching mechanism 22 is switched to the state indicated by the solid line in FIG. 4, that is, the communication between the second port 22b and the third port 22c and the communication between the first port 22a and the fourth port 22d. Do. Thus, in the refrigerant circuit 10, the outdoor heat exchanger 23 functions as a condenser for the refrigerant compressed in the compressor 21, and the indoor heat exchangers 52 and 62 are evaporated in the outdoor heat exchanger 23. A refrigeration cycle is made to function as a vessel.

  In the refrigerant circuit 10, low-pressure gas refrigerant in the refrigeration cycle is sucked into the compressor 21 and compressed to become high-pressure gas refrigerant. This high-pressure gas refrigerant is sent to the outdoor heat exchanger 23 through the switching mechanism 22, exchanges heat with the outdoor air supplied by the outdoor fan 28, and condenses to become a high-pressure liquid refrigerant. The high-pressure liquid refrigerant is sent to the indoor expansion valves 51 and 61 through the outdoor expansion valve 24 and the liquid refrigerant communication pipe 7, and is reduced in pressure to become a low-pressure refrigerant. The low-pressure refrigerant is sent to the indoor heat exchangers 52 and 62, exchanges heat with the indoor air supplied by the indoor fans 53 and 63, and evaporates to become a low-pressure gas refrigerant. The low-pressure gas refrigerant is again sucked into the compressor 21 through the gas refrigerant communication pipe 8 and the switching mechanism 22.

  During this cooling operation, the hot gas opening / closing mechanism 27b is opened. For this reason, a part of the high-pressure refrigerant that is compressed in the compressor 21 and flows through the second gas refrigerant pipe 26 b is branched to the hot gas bypass pipe 27. The high-pressure refrigerant branched into the hot gas bypass pipe 27 is sent to the antifreezing heat exchanger 25 to heat the lower side of the outdoor heat exchanger 23. That is, the antifreezing heat exchanger 25 functions as a refrigerant condenser, similarly to the outdoor heat exchanger 23. Thereby, a part of the high-pressure gas refrigerant compressed in the compressor 21 is sent to the antifreezing heat exchanger 25 through the hot gas bypass pipe 27 and exchanges heat with the outdoor air supplied by the outdoor fan 28. It goes and condenses to become a high-pressure liquid refrigerant. The high-pressure liquid refrigerant is sent to the liquid refrigerant pipe 26e through the hot gas decompression mechanism 27a, the hot gas opening / closing mechanism 27b, and the hot gas check mechanism 27c, and merges with the high-pressure liquid refrigerant from the outdoor heat exchanger 23. Thus, in the air conditioner 1, not only the outdoor heat exchanger 23 but also the antifreezing heat exchanger 25 functions as a refrigerant condenser during the cooling operation. Thereby, in the air conditioner 1, cooling of the refrigerant sent to the indoor heat exchangers 52 and 62 is promoted during the cooling operation, compared to a case where only the outdoor heat exchanger 23 functions as a refrigerant condenser, The cooling capacity is improved.

<Heating operation>
Next, the heating operation will be described with reference to FIG. Here, FIG. 5 is a schematic configuration diagram illustrating the flow of the refrigerant during the heating operation of the air-conditioning apparatus 1.

  During the heating operation, the switching mechanism 22 is switched to the state indicated by the broken line in FIG. 5, that is, the communication between the second port 22b and the fourth port 22d and the communication between the first port 22a and the third port 22c. Do. Thus, in the refrigerant circuit 10, the outdoor heat exchanger 23 functions as an evaporator for the refrigerant condensed in the indoor heat exchangers 42 and 52, and the indoor heat exchangers 52 and 62 are compressed in the compressor 21. A refrigeration cycle is performed to function as a condenser.

  In the refrigerant circuit 10, low-pressure gas refrigerant in the refrigeration cycle is sucked into the compressor 21 and compressed to become high-pressure gas refrigerant. The high-pressure gas refrigerant is sent to the indoor heat exchangers 52 and 62 through the switching mechanism 22 and the gas refrigerant communication pipe 8, exchanges heat with indoor air supplied by the indoor fans 53 and 63, and condenses to high pressure. It becomes a liquid refrigerant. The high-pressure liquid refrigerant is sent to the outdoor expansion valve 24 through the indoor expansion valves 51 and 61 and the liquid refrigerant communication pipe 7, and is decompressed to become a low-pressure refrigerant. The low-pressure refrigerant is sent to the outdoor heat exchanger 23, exchanges heat with outdoor air supplied by the outdoor fan 28, and evaporates to become a low-pressure gas refrigerant. This low-pressure gas refrigerant is again sucked into the compressor 21 through the switching mechanism 22.

  During this heating operation, the hot gas opening / closing mechanism 27b is closed except when performing anti-freezing control when resuming heating, which will be described later. For this reason, the high-pressure refrigerant that is compressed in the compressor 21 and flows through the second gas refrigerant pipe 26b is not branched to the hot gas bypass pipe 27 except when the anti-freezing control at the time of resuming heating described later is performed. That is, during the heating operation, the refrigerant does not flow through the anti-freezing heat exchanger 25, except when performing anti-freezing control when resuming heating, which will be described later. As described above, in the air conditioner 1, all the high-pressure gas refrigerant compressed in the compressor 21 is heated in the indoor heat exchangers 52 and 62 except for the case where the antifreezing control at the time of resuming heating described later is performed during the heating operation. To be sent to. Thus, in the air conditioning apparatus 1, the flow rate of the refrigerant sent to the indoor heat exchangers 52 and 62 is larger than that in the case where the refrigerant is passed through the antifreezing heat exchanger 25 during the heating operation, and the heating capacity is increased. The decline of the is suppressed.

<Defrosting operation>
Next, the defrosting operation will be described with reference to FIG. Here, FIG. 4 is a schematic configuration diagram illustrating the flow of the refrigerant during the defrosting operation of the air conditioner 1.

  As described above, the defrosting operation is a reverse cycle defrosting operation in which the refrigerant flow direction is reversed from the heating operation. Therefore, during the defrosting operation, the switching mechanism 22 is in the state indicated by the solid line in FIG. 4, that is, the second port 22b and the third port 22c are communicated, and the first port 22a and the fourth port 22d are connected. Change the communication. As a result, in the refrigerant circuit 10, the outdoor heat exchanger 23 functions as a condenser for the refrigerant compressed in the compressor 21, and the indoor heat exchangers 52 and 62 are operated in the outdoor heat, as in the above cooling operation. A refrigeration cycle that functions as an evaporator for the refrigerant condensed in the exchanger 23 is performed.

  Here, the defrosting operation is performed when the controller 9 determines that frost formation has occurred in the outdoor heat exchanger 23 during the heating operation. This determination is performed based on the temperature Tb of the refrigerant flowing through the outdoor heat exchanger 23 detected by the outdoor heat exchanger temperature sensor 29c and the accumulated time of the heating operation. For example, when it is detected that the temperature Tb of the refrigerant detected by the outdoor heat exchanger temperature sensor 29c has decreased to a predetermined temperature or less that can be regarded as frost formation in the outdoor heat exchanger 23, or heating If the accumulated time of operation has passed a predetermined time that can be regarded as frost formation in the outdoor heat exchanger 23, it is determined that frost formation has occurred in the outdoor heat exchanger 23. When the temperature and time conditions are not reached, it is determined that frost formation has not occurred in the outdoor heat exchanger 23.

  In the refrigerant circuit 10, the refrigerant circulates in the same flow direction as that in the cooling operation. Then, the high-pressure refrigerant that is compressed by the compressor 21 and flows through the second gas refrigerant pipe 26 b is sent to the outdoor heat exchanger 23 through the switching mechanism 22 to heat the outdoor heat exchanger 23. Thereby, the frost generated in the outdoor heat exchanger 23 in the heating operation is melted to become drain water, and passes through the anti-freezing heat exchanger 25 integrated with the outdoor heat exchanger 23 to the lower side of the outdoor heat exchanger 23. It collects on the bottom plate 2a of the outdoor unit 2 as a drain pan arranged. The drain water accumulated on the bottom plate 2a is discharged out of the outdoor unit 2 through a discharge port 2b formed on the bottom plate 2a.

  Then, the defrosting operation ends when the control unit 9 determines that the defrosting of the outdoor heat exchanger 23 has been completed. This determination is performed based on the temperature Tb of the refrigerant flowing through the outdoor heat exchanger 23 detected by the outdoor heat exchanger temperature sensor 29c and the operating time of the defrosting operation. For example, when it is detected that the refrigerant temperature Tb detected by the outdoor heat exchanger temperature sensor 29c is equal to or higher than a temperature at which frost can be regarded as melted, or the operation time of the defrosting operation is a predetermined time. When the time has elapsed, it is determined that the defrosting of the outdoor heat exchanger 23 has been completed, and when the temperature condition or time condition has not been reached, the defrosting of the outdoor heat exchanger 23 is completed. It is determined that it is not.

  During this defrosting operation, the hot gas opening / closing mechanism 27b is opened as in the above cooling operation. For this reason, a part of the high-pressure refrigerant that is compressed in the compressor 21 and flows through the second gas refrigerant pipe 26 b is branched to the hot gas bypass pipe 27. The high-pressure refrigerant branched into the hot gas bypass pipe 27 is sent to the antifreezing heat exchanger 25 to heat the lower side of the outdoor heat exchanger 23. That is, the anti-freezing heat exchanger 25 functions as a heater for drain water melted by performing the defrosting operation. As a result, during the defrosting operation, the drain water from the outdoor heat exchanger 23 is heated on the lower side of the outdoor heat exchanger 23 and then collected on the bottom plate 2a of the outdoor unit 2 as a drain pan. Discharged outside. As described above, in the air conditioner 1, during the defrosting operation, the anti-freezing heat exchanger 25 heats the drain water generated in the outdoor heat exchanger 23 on the lower side of the outdoor heat exchanger 23. Yes. Thereby, in the air conditioning apparatus 1, the drain water from the outdoor heat exchanger 23 can be prevented from freezing on the lower side of the outdoor heat exchanger 23 during the defrosting operation, and the drain water is outside the outdoor unit 2. Therefore, the occurrence of an ice-up phenomenon during the defrosting operation is suppressed.

<Freezing prevention control when resuming heating>
As described above, in the air conditioning apparatus 1, during the defrosting operation, a part of the high-pressure refrigerant compressed in the compressor 21 is caused to flow through the antifreezing heat exchanger 25, thereby drain water during the defrosting operation. Can be prevented from freezing.

  However, for a while after the defrosting operation is completed, the drain water melted by performing the defrosting operation exists on the lower side of the outdoor heat exchanger 23, and the drain water to the outside of the outdoor unit 2 is present. Emission continues. Thereafter, when the heating operation is resumed, there is a possibility that the drain water is frozen before the drain water is discharged under a condition where the outside air temperature Ta is low. For this reason, freezing of drain water at the time of heating operation after defrosting operation cannot be prevented, and an ice-up phenomenon may occur.

  Therefore, in the air conditioner 1, anti-freezing control at the time of resuming heating is performed so that a part of the refrigerant compressed in the compressor 21 flows to the anti-freezing heat exchanger 25 in the early stage of resuming the heating operation after the defrosting operation. I have to.

  Next, this anti-freezing control when resuming heating will be described with reference to FIGS. Here, FIG. 6 is a flowchart of the freeze prevention control at the time of resuming the heating of the air conditioner 1. FIG. 7 is a schematic configuration diagram illustrating the flow of the refrigerant during the freeze prevention control at the time of resuming the heating of the air-conditioning apparatus 1.

  First, the control part 9 determines whether it is the heating operation after a defrost operation in step S1. If it is determined in step S1 that the heating operation is performed after the defrosting operation, the process proceeds to step S2 in which it is determined whether or not an outside air temperature condition that requires anti-freezing control when resuming heating is satisfied.

  In step S2, the control unit 9 determines whether or not the outside air temperature Ta detected by the outside air temperature sensor 29d is equal to or lower than a predetermined outside air temperature Tas. In step S2, when the outside air temperature Ta is equal to or lower than a predetermined outside air temperature Tas, that is, when the outside air temperature condition is satisfied, the process proceeds to steps S3 to S5 for executing the freeze prevention control at the time of resuming heating. On the other hand, when the outside air temperature Ta is higher than the predetermined outside air temperature Tas, that is, when the outside air temperature condition is not satisfied, the heating operation is resumed without performing the freeze prevention control at the time of resuming the heating in steps S3 to S5. Here, the predetermined outside air temperature Tas is set in view of whether or not the drain water present on the lower side of the outdoor heat exchanger 23 may be frozen after the defrosting operation, and is, for example, the melting point of water. It is set to 0 ° C. The predetermined outside air temperature Tas is stored in advance in a memory or the like of the control unit 9 and can be changed by a switch (not shown) or a remote controller (not shown) provided in the control unit 9. It is like that.

  And the control part 9 starts the freeze prevention control at the time of heating resumption which flows a part of refrigerant | coolant compressed in the compressor 21 to the freezing prevention heat exchanger 25 in step S3. That is, in the refrigerant circuit 10, the same refrigeration cycle as that in the heating operation is performed, and the hot gas opening / closing mechanism 27b is opened. For this reason, a part of the high-pressure refrigerant that is compressed in the compressor 21 and flows through the second gas refrigerant pipe 26 b is branched to the hot gas bypass pipe 27. The high-pressure refrigerant branched into the hot gas bypass pipe 27 is sent to the antifreezing heat exchanger 25 to heat the lower side of the outdoor heat exchanger 23. That is, the antifreezing heat exchanger 25 functions as a heater for drain water existing on the lower side of the outdoor heat exchanger 23 after the defrosting operation. Here, since the outlet of the hot gas bypass pipe 27 is connected to a portion of the liquid refrigerant pipe 26e through which the low-pressure refrigerant flows downstream of the outdoor expansion valve 24, the flow rate of the refrigerant flowing through the hot gas bypass pipe 27 is high. It is easy to be secured. The refrigerant that has heated the drain water in the antifreezing heat exchanger 25 condenses in the antifreezing heat exchanger 25, but then merges with the refrigerant flowing through the liquid refrigerant pipe 26e and functions as a refrigerant evaporator. Therefore, the refrigerant condensed in the antifreezing heat exchanger 25 remains in a liquid state and is not sucked into the compressor 21. As a result, during the heating operation after the defrosting operation, the drain water present on the lower side of the outdoor heat exchanger 23 is heated in the antifreezing heat exchanger 25 and then the bottom plate 2a of the outdoor unit 2 as a drain pan. It accumulates on the top and is discharged out of the outdoor unit 2. As described above, in the air conditioner 1, the anti-freezing heat exchanger 25 heats the drain water present on the lower side of the outdoor heat exchanger 23 during the heating operation after the defrosting operation. Thereby, in the air conditioning apparatus 1, in the heating operation after the defrosting operation, the drain water existing on the lower side of the outdoor heat exchanger 23 can be discharged without freezing after the defrosting operation. Occurrence of ice-up phenomenon during heating operation after operation is suppressed.

  And control part 9 judges whether predetermined time ts passed after defrost operation in Step S4, and when predetermined time ts passed, it shifts to processing of Step S5. Here, the predetermined time ts is set to about several minutes in consideration of the time required to discharge the drain water present on the lower side of the outdoor heat exchanger 23 after the defrosting operation. The predetermined time ts is stored in advance in a memory or the like of the control unit 9 and can be changed by a switch (not shown) or a remote controller (not shown) provided in the control unit 9. It has become. And the control part 9 complete | finishes freezing prevention control at the time of heating resumption in step S5, and transfers to normal heating operation. That is, in the refrigerant circuit 10, the same refrigeration cycle as that in the heating operation is performed, and the hot gas opening / closing mechanism 27b is closed. For this reason, during the heating operation after the defrosting operation, a predetermined time ts for discharging the drain water existing on the lower side of the outdoor heat exchanger 23 after the defrosting operation without freezing, that is, after the defrosting operation. Only when the heating operation is restarted, the freeze prevention control is performed when heating is restarted. Here, in the heating operation after the defrosting operation, flowing a part of the refrigerant compressed in the compressor 21 to the anti-freezing heat exchanger 25 means that the flow rate of the refrigerant sent to the indoor heat exchangers 52 and 62 is reduced. This will reduce the heating capacity. However, in the air conditioning apparatus 1, as described above, a part of the refrigerant compressed in the compressor 21 is transferred to the antifreezing heat exchanger 25 only in the initial stage of restarting the heating operation in the heating operation after the defrosting operation. I try to make it flow. For this reason, in the air conditioning apparatus 1, the fall of the heating capability in the heating operation after a defrost operation is suppressed.

  As described above, in the air conditioner 1, it is possible to suppress the occurrence of the ice-up phenomenon during the heating operation after the defrosting operation while suppressing the decrease in the heating capacity during the heating operation after the defrosting operation. Yes.

(3) Features of the air conditioner The air conditioner 1 of the present embodiment has the following features.

<A>
In the air conditioner 1, in the heating operation after the defrosting operation, a part of the refrigerant compressed in the compressor 21 as the compression mechanism is caused to flow to the antifreezing heat exchanger 25, so that the outside air temperature Ta is low. The drain water present on the lower side of the outdoor heat exchanger 23 can be discharged without freezing after the defrosting operation. For this reason, in the air conditioning apparatus 1, generation | occurrence | production of the ice-up phenomenon at the time of the heating operation after a defrost operation can be suppressed.

  Here, in the heating operation after the defrosting operation, flowing a part of the refrigerant compressed in the compressor 21 to the anti-freezing heat exchanger 25 means that the flow rate of the refrigerant sent to the indoor heat exchangers 52 and 62 is reduced. This will reduce the heating capacity.

  Therefore, in the air conditioner 1, as described above, a part of the refrigerant compressed in the compressor 21 is transferred to the antifreezing heat exchanger 25 only in the initial stage of restarting the heating operation in the heating operation after the defrosting operation. It is made to flow (that is, freeze prevention control when resuming heating). For this reason, in the air conditioning apparatus 1, the fall of the heating capability in the heating operation after a defrost operation can be suppressed.

  Thereby, in the air conditioning apparatus 1, generation | occurrence | production of the ice-up phenomenon at the time of the heating operation after a defrost operation can be suppressed, suppressing the fall of the heating capability in the heating operation after a defrost operation.

<B>
In the air conditioner 1, the anti-freezing control when resuming heating is performed when the outside air temperature Ta is equal to or lower than a predetermined outside air temperature Tas. For this reason, in the air conditioner 1, only under conditions where the outside air temperature Ta at which the drain water present on the lower side of the outdoor heat exchanger 23 may freeze after the defrosting operation is low (in this case, 0 ° C. or less). When the heating is resumed, the freeze prevention control is performed. Under the condition where the outside air temperature Ta is high (in this case, higher than 0 ° C.), the freeze prevention control when the heating is resumed can be omitted.

  Thereby, in the air conditioning apparatus 1, the fall of the heating capability in the heating operation after a defrost operation can further be suppressed.

<C>
In the air conditioner 1, the freeze prevention control at the time of resuming heating is performed until a predetermined time ts elapses after the defrosting operation. That is, in the air conditioner 1, since the freeze prevention control at the time of resuming heating is managed by time, the time required for discharging the drain water present on the lower side of the outdoor heat exchanger 23 after the defrosting operation. Can be considered.

  Thereby, in the air conditioning apparatus 1, the freeze prevention control at the time of resuming heating can be appropriately performed in consideration of the time required for discharging drain water.

(4) Modification 1
In the air conditioning apparatus 1 of the above embodiment, the predetermined time ts of the freeze prevention control at the time of resuming heating can be changed by a switch (not shown), a remote controller (not shown), etc., but automatically according to the operating conditions. It is not intended to be changed.

  However, the amount of drain water present on the lower side of the outdoor heat exchanger 23 after the defrosting operation varies depending on the outside air temperature Ta, the outside air humidity, or the operation time of the defrosting operation. Specifically, as the outside air temperature Ta decreases, the amount of drain water increases as the outside air humidity increases or the operating time of the defrosting operation increases. For this reason, it is preferable to change also about predetermined time ts of anti-freezing control at the time of heating resumption by outside air temperature Ta, outside air humidity, or operating time of defrosting operation.

  Therefore, in the air conditioner 1 of the present modification, the predetermined time ts is set to increase as the outside air temperature Ta decreases, the outside air humidity increases, or the operating time of the defrosting operation increases. (See step S3 in FIG. 8). For this reason, in the air conditioning apparatus 1 of this modification, the amount of drain water that varies depending on the outside air temperature Ta can be taken into consideration. When the predetermined time ts of the freeze prevention control at the time of resuming heating can be changed by the outside air humidity, it is necessary to provide a humidity sensor in the outdoor unit 2 although not shown here.

  Thereby, in the air conditioning apparatus 1 of this modification, the freeze prevention control at the time of resuming heating can be appropriately performed in consideration of the change in the amount of drain water due to conditions such as the outside air temperature Ta.

(5) Modification 2
In the air conditioner 1 of the above embodiment and the modification 1 thereof, the hot gas opening / closing mechanism 27b provided in the hot gas bypass pipe 27 is an electromagnetic valve, and therefore, in the freeze prevention control at the time of resuming heating, heat exchange for freeze prevention is performed. The flow rate of the refrigerant flowing through the vessel 25 cannot be varied.

  However, the amount of drain water present on the lower side of the outdoor heat exchanger 23 after the defrosting operation varies depending on the outside air temperature Ta, the outside air humidity, or the operation time of the defrosting operation. Specifically, the amount of drain water increases as the outside air temperature Ta decreases, the outside air humidity increases, or the operating time of the defrosting operation increases. For this reason, it is preferable to change also the flow volume of the refrigerant | coolant which flows into the heat exchanger 25 for anti-freezing in the anti-freezing control at the time of heating resumption according to the outside temperature Ta, the outside air humidity, or the operating time of the defrosting operation.

  Therefore, in the air conditioner 1 of this modification, the hot gas bypass pipe 27 is provided with a hot gas flow rate adjustment valve 27d for changing the flow rate of the refrigerant flowing through the antifreezing heat exchanger 25 (see FIG. 9). As the outside air temperature Ta becomes lower, the outside air humidity becomes higher, or the operating time of the defrosting operation becomes longer, the opening degree of the hot gas flow rate control valve 27d in the freeze prevention control at the time of resuming heating is set to be increased. (See step S3 in FIG. 10). For this reason, in the air conditioning apparatus 1 of the present modification, the amount of drain water that changes depending on the outside air temperature Ta, the outside air humidity, or the operating time of the defrosting operation can be taken into consideration. In addition, in order to be able to change the opening degree of the hot gas flow rate control valve 27d for the antifreezing control at the time of resuming heating depending on the outside air humidity, it is necessary to provide a humidity sensor in the outdoor unit 2 although not shown here.

  Thereby, in the air conditioning apparatus 1 of this modification, the freeze prevention control at the time of resuming heating can be appropriately performed in consideration of the change in the amount of drain water due to conditions such as the outside air temperature Ta.

-Second Embodiment-
(1) Configuration of Air Conditioner FIG. 11 is a schematic configuration diagram of an air conditioner 1 according to the second embodiment of the present invention. The air conditioning apparatus 1 is an apparatus used for air conditioning in a room such as a building by performing a vapor compression refrigeration cycle. The air conditioner 1 mainly includes one outdoor unit 2, one intermediate unit 4, a plurality of (here, two) indoor units 5 and 6, an outdoor unit 2, a functional unit 4, and an indoor unit. A liquid refrigerant communication pipe 7 and a gas refrigerant communication pipe 8 for connecting the units 5 and 6 are provided. That is, the vapor compression refrigerant circuit 10 of the air conditioner 1 is connected to the outdoor unit 2, the functional unit 4, the indoor units 5 and 6, the liquid refrigerant communication pipe 7 and the gas refrigerant communication pipe 8. It is constituted by. Note that the number of indoor units 5 and 6 is not limited to two, and may be one or three or more.

<Indoor unit>
The indoor units 5 and 6 are installed by embedding or hanging in a ceiling of a room such as a building or hanging on a wall surface of the room. The indoor units 5 and 6 are connected to the functional unit 4 via a first liquid refrigerant communication tube 7a which is a part of the liquid refrigerant communication tube 7 and a second gas refrigerant communication tube 8a which is a part of the gas refrigerant communication tube 8. And constitutes a part of the refrigerant circuit 10.

  Next, the configuration of the indoor units 5 and 6 will be described. In addition, since the indoor unit 5 and the indoor unit 6 have the same configuration, only the configuration of the indoor unit 5 will be described here, and the configuration of the indoor unit 6 is the 50th number indicating each part of the indoor unit 5. The reference numerals in the 60s are attached instead of the reference numerals, and description of each part is omitted.

  The indoor unit 5 mainly has an indoor expansion valve 51 and an indoor heat exchanger 52.

  The indoor expansion valve 51 is a device that adjusts the pressure and flow rate of the refrigerant flowing through the indoor unit 5. The indoor expansion valve 51 has one end connected to the liquid side of the indoor heat exchanger 52 and the other end connected to the first liquid refrigerant communication pipe 7a. Here, an electric expansion valve is used as the indoor expansion valve 51.

  The indoor heat exchanger 52 is a heat exchanger that functions as a refrigerant evaporator during cooling operation to cool indoor air and functions as a refrigerant condenser during heating operation to heat indoor air. The indoor heat exchanger 52 has a liquid side connected to the indoor expansion valve 51 and a gas side connected to the first gas refrigerant communication pipe 8a. Here, the indoor heat exchanger 52 is a cross-fin type fin-and-tube heat exchanger composed of heat transfer tubes and a large number of fins. The type of the indoor heat exchanger 52 is not limited to the cross fin type fin-and-tube type heat exchanger, and other types such as a laminated heat exchanger using corrugated fins or flat tubes, for example. It may be a type of heat exchanger.

  The indoor unit 5 has an indoor fan 53 for supplying indoor air as supply air after sucking indoor air into the indoor unit 5 and exchanging heat with the refrigerant in the indoor heat exchanger 52. . Here, as the indoor fan 53, a centrifugal fan or a multi-blade fan driven by an indoor fan motor 53a is used.

  The indoor unit 5 includes an indoor side control unit 54 that controls the operation of each unit constituting the indoor unit 5. And the indoor side control part 54 has a microcomputer, memory, etc. for controlling the indoor unit 5, and between the remote controllers (not shown) for operating the indoor unit 5 separately. Control signals and the like can be exchanged, and control signals and the like can be exchanged with the outdoor unit 2 and the functional unit 4 via the transmission line 9a.

<Outdoor unit>
The outdoor unit 2 is installed outside a building or the like. The outdoor unit 2 is connected to the functional unit 4 via a second liquid refrigerant communication tube 7b that is a part of the liquid refrigerant communication tube 7 and a second gas refrigerant communication tube 8b that is a part of the gas refrigerant communication tube 8. And constitutes a part of the refrigerant circuit 10.

  Next, the configuration of the outdoor unit 2 will be described. The outdoor unit 2 mainly includes a low-stage compressor 21 that constitutes the compression mechanism 20 together with a high-stage compressor 32 (described later) of the functional unit 4, a switching mechanism 22, 31, an outdoor heat exchanger 23, an outdoor unit It has an expansion valve 24 and a heat exchanger 25 for preventing freezing.

  The low stage compressor 21 is a device that compresses the refrigerant. The low stage compressor 21 has a hermetic structure in which a rotary type or scroll type positive displacement compression element (not shown) is rotationally driven by a low stage compressor motor 21a. The low-stage compressor 21 has a first gas refrigerant pipe 26a connected to the suction side and a second gas refrigerant pipe 26b connected to the discharge side. The first gas refrigerant pipe 26 a is a refrigerant pipe that connects the suction side of the low-stage compressor 21 and the first port 22 a of the first switching mechanism 22. The second gas refrigerant pipe 26 b is a refrigerant pipe that connects the discharge side of the low-stage compressor 21 and the second port 22 b of the first switching mechanism 22. Here, one low-stage compressor 21 constitutes the compression mechanism 20 together with the high-stage compressor 32. However, a plurality of low-stage compressors 21 connected in parallel and a high stage The compression mechanism 20 may be configured with the side compressor 32.

  The switching mechanisms 22 and 31 are mechanisms for switching the direction of refrigerant flow in the refrigerant circuit 10. The switching mechanisms 22 and 31 function the outdoor heat exchanger 23 as a condenser of the refrigerant compressed in the low-stage compressor 21 during the cooling operation and the defrosting operation, and the indoor heat exchangers 52 and 62 Switching is performed so as to function as an evaporator of the refrigerant condensed in the outdoor heat exchanger 23. In other words, the first switching mechanism 22 switches between the second port 22b and the third port 22c and the first port 22a and the fourth port 22d during the cooling operation and the defrosting operation. . In addition, the second switching mechanism 31 switches between the second port 31b and the third port 31c and the first port 31a and the fourth port 31d during the cooling operation and the defrosting operation. . As a result, the discharge side of the low-stage compressor 21 (here, the second gas refrigerant pipe 26b) and the gas side of the outdoor heat exchanger 23 (here, the third gas refrigerant pipe 26c) are connected (FIG. 11 (see the solid line of the first switching mechanism 22). Moreover, the suction side of the low-stage compressor 21 (here, the first gas refrigerant pipe 26a) and the second gas refrigerant communication pipe 8b side (here, the fifth gas refrigerant pipe 26f and the sixth gas refrigerant pipe 26g) Are connected (see the solid line of the second switching mechanism 31 in FIG. 11). Further, the switching mechanisms 22 and 31 cause the outdoor heat exchanger 23 to function as an evaporator of the refrigerant condensed in the indoor heat exchangers 42 and 52 during the heating operation, and the indoor heat exchangers 52 and 62 are set on the lower stage side. Switching to function as a condenser for the refrigerant compressed in the compressor 21 is performed. That is, during the heating operation, the first switching mechanism 22 switches the second port 22b and the fourth port 22d to communicate with each other and the first port 22a and the third port 22c to communicate with each other. In addition, during the heating operation, the second switching mechanism 31 performs switching so that the second port 31b and the fourth port 31d communicate with each other and the first port 31a and the third port 31c communicate with each other. As a result, the discharge side (here, the second gas refrigerant pipe 26b) of the low-stage compressor 21 and the gas refrigerant communication pipe 8 side (here, the fourth gas refrigerant pipe 26d and the fifth gas refrigerant pipe 26f) are connected. They are connected (see the broken line of the second switching mechanism 31 in FIG. 11). In addition, the suction side (here, the first gas refrigerant pipe 26a) of the low-stage compressor 21 and the gas side (here, the third gas refrigerant pipe 26c) of the outdoor heat exchanger 23 are connected (FIG. 11). (Refer to the broken line of the first switching mechanism 22). The third gas refrigerant pipe 26 c is a refrigerant pipe that connects the third port 22 c of the first switching mechanism 22 and the gas side of the outdoor heat exchanger 23. The fourth gas refrigerant pipe 26 d is a refrigerant pipe that connects a middle portion of the second gas refrigerant pipe 26 b and the fourth port 31 d of the second switching mechanism 31. The fifth gas refrigerant pipe 26f is a refrigerant pipe that connects the second port 31b of the second switching mechanism 31 and the second gas refrigerant communication pipe 8b side. Here, the first switching mechanism 22 is a four-way switching valve. And the 4th port 22d of the 1st switching mechanism 22 is connected to the 1st gas refrigerant pipe 26a through the 7th gas refrigerant pipe 26h consisting of a capillary tube with very large channel resistance. For this reason, almost no refrigerant flows through the seventh gas refrigerant pipe 26h, so that the first switching mechanism 22 functions as a three-way valve having the first to third ports 22a to 22c. ing. The first port 31a of the second switching mechanism 31 is connected to the sixth gas refrigerant pipe 26g through an eighth gas refrigerant pipe 26i made of a capillary tube having a very large flow path resistance. For this reason, almost no refrigerant flows through the eighth gas refrigerant pipe 26a, whereby the second switching mechanism 31 functions as a three-way valve having the second to fourth ports 31b to 31d. ing. Here, the configuration of the switching mechanisms 22 and 31 is not limited to that using two four-way switching valves. For example, the switching mechanisms 22 and 31 may be configured by one four-way switching valve or a plurality of electromagnetic A configuration in which valves and the like are connected so as to perform the switching function described above may be used.

  The outdoor heat exchanger 23 is a heat exchanger that functions as a refrigerant condenser during a cooling operation and a defrosting operation, and functions as a refrigerant evaporator during a heating operation. The outdoor heat exchanger 23 has a liquid side connected to the first liquid refrigerant pipe 26e and a gas side connected to the third gas refrigerant pipe 26c. The first liquid refrigerant pipe 26e is a refrigerant pipe that connects the liquid side of the outdoor heat exchanger 23 and the second liquid refrigerant communication pipe 7b side. Here, the outdoor heat exchanger 23 is a cross-fin type fin-and-tube heat exchanger composed of heat transfer tubes and a large number of fins. The type of the outdoor heat exchanger 23 is not limited to a cross fin type fin-and-tube type heat exchanger, and other types such as a laminated heat exchanger using corrugated fins or flat tubes, for example. It may be a type of heat exchanger.

  The outdoor expansion valve 24 is a device that adjusts the pressure and flow rate of the refrigerant flowing through the outdoor unit 2. The outdoor expansion valve 24 is provided in the first liquid refrigerant pipe 26e. Here, an electric expansion valve is used as the outdoor expansion valve 24.

  The antifreezing heat exchanger 25 is a heat exchanger that heats the lower side of the outdoor heat exchanger 23 with a part of the refrigerant compressed in the low-stage compressor 21 constituting the compression mechanism 20. The antifreezing heat exchanger 25 is provided in the hot gas bypass pipe 27. Here, the anti-freezing heat exchanger 25 is a cross-fin type fin-and-tube heat exchanger composed of heat transfer tubes and a large number of fins, and as shown in FIG. 2, an outdoor heat exchanger. 23 is integrated with the lower part. Specifically, the outdoor heat exchanger 23 and the antifreezing heat exchanger 25 are configured as an integral fin-and-tube heat exchanger, and the heat transfer tubes and fins on the upper side are the outdoor heat exchanger 23. The heat transfer tubes and fins on the lower side constitute a heat exchanger 25 for preventing freezing. The lower end portion of the freeze prevention heat exchanger 25 is disposed on the bottom plate 2 a of the outdoor unit 2 that functions as a drain pan that receives drain water generated in the outdoor heat exchanger 23 and the freeze prevention heat exchanger 25. The bottom plate 2 a is formed with a discharge port 2 b so that drain water received on the bottom plate 2 a can be discharged out of the outdoor unit 2. Here, FIG. 2 is a schematic view showing the lower side of the outdoor heat exchanger 23 including the freeze-preventing heat exchanger 25 and the bottom plate 2 a of the outdoor unit 2. The type of the anti-freezing heat exchanger 25 is not limited to the cross-fin type fin-and-tube type heat exchanger, for example, a laminated heat exchanger using corrugated fins or flat tubes, etc. Other types of heat exchangers may be used.

  The hot gas bypass pipe 27 is a refrigerant pipe that branches a part of the refrigerant compressed in the low-stage compressor 21. One end side of the hot gas bypass pipe 27 is connected so as to branch from a middle portion of the second gas refrigerant pipe 26c, and the other end side is connected to the liquid side of the outdoor heat exchanger 23 of the first liquid refrigerant pipe 26e and the outdoor expansion valve. 24 is connected so as to join the portion between the two. A hot gas decompression mechanism 27a, a hot gas opening / closing mechanism 27b, and a hot gas check mechanism 27c are provided at a portion of the hot gas bypass pipe 27 on the outlet side of the heat exchanger 25 for preventing freezing. The hot gas decompression mechanism 27a is a device that decompresses the refrigerant. Here, a capillary tube is used as the hot gas decompression mechanism 27a. The hot gas opening / closing mechanism 27b is opened when a part of the refrigerant compressed in the low stage compressor 21 is branched into the hot gas bypass pipe 27, and is compressed in the low stage compressor 21 by the hot gas bypass pipe 27. This is a device that can be closed when a part of the refrigerant is not branched. Here, an electromagnetic valve is used as the hot gas opening / closing mechanism 27b. The hot gas check mechanism 27c is a mechanism that allows the refrigerant to flow from the outlet side of the antifreezing heat exchanger 25 to the first liquid refrigerant pipe 26e and blocks the flow in the reverse direction. Here, a check valve is used as the hot gas check mechanism 27c. Here, as will be described later, in order to increase the heating capacity in a condition where the outside air temperature is low, a functional unit is connected between the outdoor unit 2 and the indoor units 5 and 6 to thereby perform a two-stage compression refrigeration cycle. To be able to do. An outdoor heat exchanger 23 in which frost formation occurs is provided in the outdoor unit 2. Therefore, the freeze prevention heat exchanger 25 is provided in the outdoor unit 2, and the refrigerant compressed in the low-stage compressor 21 provided in the outdoor unit 2 is used as a heating source for the freeze prevention heat exchanger 25. The hot gas bypass pipe 27 that uses the section is provided. As a result, the hot gas bypass pipe 27 is configured to be accommodated in the outdoor unit 2 so as not to be configured to straddle between the outdoor unit 2 and the functional unit 4.

  The outdoor unit 2 has an outdoor fan 28 for sucking outdoor air into the outdoor unit 2, exchanging heat with the refrigerant in the outdoor heat exchanger 23, and then discharging the air outside the outdoor unit 2. . Here, as the outdoor fan 28, an axial fan or the like driven by an outdoor fan motor 28a is used. Further, as shown in FIG. 2, the anti-freezing heat exchanger 25 is integrated with the lower part of the outdoor heat exchanger 23. Therefore, the outdoor fan 28 is not only the outdoor heat exchanger 23 but also the anti-freezing heat. Outdoor air is also supplied to the exchanger 25.

  The outdoor unit 2 is provided with various sensors. Specifically, the outdoor unit 2 is mainly provided with a suction pressure sensor 29a, a discharge pressure sensor 29b, an outdoor heat exchange temperature sensor 29c, and an outdoor temperature sensor 29d. The suction pressure sensor 29 a is a pressure sensor that detects the suction pressure Ps of the low-stage compressor 21. The discharge pressure sensor 29b is a pressure sensor that detects the discharge pressure Pd1 of the low-stage compressor 21. The outdoor heat exchange temperature sensor 29 c is a temperature sensor that detects the temperature Tb of the refrigerant flowing through the outdoor heat exchanger 23. The outside air temperature sensor 29d is a temperature sensor that detects the outside air temperature Ta in the outdoor unit 2.

  The outdoor unit 2 also has an outdoor control unit 30 that controls the operation of each part constituting the outdoor unit 2. The outdoor control unit 30 includes a microcomputer, a memory, and the like for controlling the outdoor unit 2. Between the indoor side control units 54 and 64 of the indoor units 5 and 6 and the functional unit 4. Control signals and the like can be exchanged via the transmission line 9a.

<Functional unit>
The functional unit 4 is a unit that enables a two-stage compression refrigeration cycle by being connected between the outdoor unit 2 and the indoor units 5 and 6 in order to increase the heating capacity in a condition where the outside air temperature is low. It is installed outside the building. The functional unit 4 is connected to the indoor units 5 and 6 via the first liquid refrigerant communication tube 7a and the first gas refrigerant communication tube 8a, and the second liquid refrigerant communication tube 7b and the second gas refrigerant communication tube. It is connected to the outdoor unit 2 via 8b and constitutes a part of the refrigerant circuit 10.

  Next, the configuration of the functional unit 4 will be described. The functional unit 4 mainly includes a high-stage compressor 32 that constitutes the compression mechanism 20 together with the low-stage compressor 21 of the outdoor unit 2, a gas-liquid separator 33, a ninth gas refrigerant pipe 34a, and a second liquid. And a refrigerant pipe 34b.

  The ninth gas refrigerant tube 34a is a refrigerant tube that connects the first gas refrigerant communication tube 8a and the second gas refrigerant communication tube 8b. A first gas refrigerant opening / closing mechanism 35 is provided in the ninth gas refrigerant pipe 34a. Here, an electromagnetic valve is used as the first gas refrigerant opening / closing mechanism 35.

  The second liquid refrigerant pipe 34b is a refrigerant pipe that connects the first liquid refrigerant communication pipe 7a and the second liquid refrigerant communication pipe 7b. The second liquid refrigerant pipe 34b has a third liquid refrigerant pipe 34c and a fourth liquid refrigerant pipe 34d connected in parallel to the third liquid refrigerant pipe 34c. The third liquid refrigerant pipe 34c is a refrigerant pipe for flowing a refrigerant from the second liquid refrigerant communication pipe 7b toward the first liquid refrigerant communication pipe 7a. A first liquid refrigerant check mechanism 36 is provided in the third liquid refrigerant pipe 34c. The first liquid refrigerant check mechanism 36 is a mechanism that allows the flow of refrigerant from the second liquid refrigerant communication pipe 7b side to the first liquid refrigerant communication pipe 7a side and blocks the flow in the reverse direction. Here, a check valve is used as the first liquid refrigerant check mechanism 36. The fourth liquid refrigerant pipe 34d is a refrigerant pipe for flowing the refrigerant from the first liquid refrigerant communication pipe 7a toward the second liquid refrigerant communication pipe 7b. The fourth liquid refrigerant pipe 34d is provided with a first liquid refrigerant opening / closing mechanism 37 and a second liquid refrigerant check mechanism 38. Here, an electromagnetic valve is used as the first liquid refrigerant opening / closing mechanism 37. The second liquid refrigerant check mechanism 38 is a mechanism that allows the flow of refrigerant from the first liquid refrigerant communication pipe 7a side to the second liquid refrigerant communication pipe 7b side and blocks the flow in the reverse direction. Here, a check valve is used as the second liquid refrigerant check mechanism 38.

  The high stage compressor 32 is a device that compresses the refrigerant. The high stage compressor 32 has a hermetic structure in which a rotary type or scroll type positive displacement compression element (not shown) is rotationally driven by a high stage compressor motor 32a. The high stage compressor 32 has a tenth gas refrigerant pipe 34e connected to the suction side and an eleventh gas refrigerant pipe 34f connected to the discharge side. The tenth gas refrigerant pipe 34e connects the suction side of the high-stage compressor 32 and the portion of the ninth gas refrigerant pipe 34a closer to the second gas refrigerant communication pipe 8b than the first gas refrigerant opening / closing mechanism 35. It is. A high stage suction expansion valve 39 is provided in the tenth gas refrigerant pipe 34e. The high-stage suction expansion valve 39 is opened when the refrigerant compressed in the low-stage compressor 21 is sucked into the high-stage compressor 32 and further compressed, and the refrigerant compressed in the low-stage compressor 21 is high. This is a device that can be closed when the stage-side compressor 32 is not inhaled. Here, an electric expansion valve is used as the high stage intake expansion valve 39. The eleventh gas refrigerant pipe 34f connects the discharge side of the high-stage compressor 32 and the portion of the ninth gas refrigerant pipe 34a closer to the first gas refrigerant communication pipe 8a than the first gas refrigerant open / close mechanism 35. It is.

  The gas-liquid separator 33 is a device that introduces the refrigerant flowing through the second liquid refrigerant pipe 34b and separates it into a gas refrigerant and a liquid refrigerant. Here, a vertical cylindrical container is used as the gas-liquid separator 33. A fifth liquid refrigerant pipe 34g, a sixth liquid refrigerant pipe 34h, and a twelfth gas refrigerant pipe 34i are connected to the gas-liquid separator 33. The fifth liquid refrigerant pipe 34g includes a portion of the fourth liquid refrigerant pipe 34d closer to the first liquid refrigerant communication pipe 7a than the first liquid refrigerant open / close mechanism 37 and the second liquid refrigerant check mechanism 38 and the gas-liquid separator 33. It is a refrigerant | coolant pipe | tube connecting between the refrigerant | coolant inlets formed in the up-down direction center part. The fifth liquid refrigerant pipe 34g is provided with a second liquid refrigerant opening / closing mechanism 40 and a third liquid refrigerant check mechanism 41. Here, an electromagnetic valve is used as the second liquid refrigerant opening / closing mechanism 40. The third liquid refrigerant check mechanism 41 is a mechanism that allows the flow of refrigerant from the second liquid refrigerant pipe 34b side to the refrigerant inlet side of the gas-liquid separator 33 and blocks the flow in the reverse direction. Here, a check valve is used as the third liquid refrigerant check mechanism 41. The sixth liquid refrigerant pipe 34h includes a portion of the fourth liquid refrigerant pipe 34d closer to the second liquid refrigerant communication pipe 7b than the first liquid refrigerant open / close mechanism 37 and the second liquid refrigerant check mechanism 38 and the gas-liquid separator 33. It is a refrigerant pipe connecting between the liquid refrigerant outlet formed in the lower part. A fourth liquid refrigerant check mechanism 42 is provided in the sixth liquid refrigerant pipe 34h. The fourth liquid refrigerant check mechanism 42 is a mechanism that allows the flow of refrigerant from the liquid refrigerant outlet side of the gas-liquid separator 33 to the second liquid refrigerant pipe 34b side and blocks the flow in the reverse direction. Here, a check valve is used as the fourth liquid refrigerant check mechanism 42. The twelfth gas refrigerant pipe 34i is between a portion of the tenth gas refrigerant pipe 34e closer to the higher stage compressor 32 than the higher stage suction expansion valve 39 and a gas refrigerant outlet formed at the upper part of the gas-liquid separator 33. It is a refrigerant pipe which connects.

  The functional unit 4 is provided with various sensors. Specifically, the functional unit 4 is mainly provided with a discharge pressure sensor 43. The discharge pressure sensor 43 is a pressure sensor that detects the discharge pressure Pd2 of the high-stage compressor 32.

  In addition, the functional unit 4 includes a function side control unit 44 that controls the operation of each unit constituting the functional unit 4. The function side control unit 44 includes a microcomputer, a memory, and the like for controlling the function unit 4, and controls the indoor side control units 54 and 64 of the indoor units 5 and 6 and the outdoor side control of the outdoor unit 2. Control signals and the like can be exchanged with the unit 30 via the transmission line 9a. That is, the operation control of the entire air conditioner 1 is performed by the indoor side control units 54 and 64, the outdoor side control unit 30, the function side control unit 44, and the transmission line 9a connecting the control units 30, 44, 54 and 64. The control part 9 to perform is comprised.

  As illustrated in FIG. 12, the control unit 9 is configured to perform various devices and valves 21 a, 22, 24, 27 b, 28 a, 32 a, 35, 37 based on various operation settings and detection values of the various sensors 29 a to 29 d, 43. , 39, 40, 51, 53a, 61, 63a can be controlled. Here, FIG. 12 is a control block diagram of the air conditioner 1.

<Refrigerant communication pipe>
Refrigerant communication pipes 7 and 8 are refrigerant pipes constructed on site when the air conditioner 1 is installed at an installation location such as a building, and installation conditions such as an installation location and a combination of an outdoor unit and an indoor unit. Those having various lengths and tube diameters are used.

  As described above, the refrigerant circuit 10 of the air conditioner 1 is configured by connecting the outdoor unit 2, the functional unit 4, the indoor units 5 and 6, and the refrigerant communication tubes 7 and 8. The air conditioner 1 is controlled by the control unit 9 including the indoor side control units 54 and 64, the function side control unit 44, and the outdoor side control unit 30, and the cooling operation, heating operation, and removal described below. Various operations such as frost operation can be performed.

(2) Operation of the Air Conditioner The air conditioner 1 can mainly perform a cooling operation, a heating operation, and a defrosting operation. The cooling operation is an operation in which the refrigerant is circulated mainly in the order of the compression mechanism 20, the outdoor heat exchanger 23, and the indoor heat exchangers 52 and 62 in order to cool the indoor air. Here, the cooling operation is a single-stage compression refrigeration cycle in which only the low-stage compressor 21 of the compression mechanism 20 is operated. The heating operation is an operation in which the refrigerant is circulated mainly in the order of the compression mechanism 20, the indoor heat exchangers 52 and 62, and the outdoor heat exchanger 23 in order to heat the indoor air. The heating operation includes a single-stage heating operation under a condition where the outside air temperature is high and a two-stage heating operation under a condition where the outside air temperature is low. The single-stage heating operation performs a single-stage compression refrigeration cycle in which only the low-stage compressor 21 of the compression mechanism 20 is operated. The two-stage heating operation performs a two-stage compression refrigeration cycle that operates both the low-stage compressor 21 and the high-stage compressor 32 in the compression mechanism 20. The defrosting operation is an operation in which mainly the compression mechanism 20, the outdoor heat exchanger 23, and the indoor heat exchangers 52 and 62 are circulated in order in order to melt the frost generated in the outdoor heat exchanger 23 by the heating operation. is there. That is, the defrosting operation is a so-called reverse cycle defrosting operation in which the flow direction of the refrigerant is reversed from that of the heating operation. As in the heating operation, the defrosting operation includes a single-stage defrosting operation under a condition where the outside air temperature is high and a two-stage defrosting operation under a condition where the outside air temperature is low. The single-stage defrosting operation performs a single-stage compression refrigeration cycle in which only the low-stage compressor 21 of the compression mechanism 20 is operated. The two-stage defrosting operation performs a two-stage compression refrigeration cycle that operates both the low-stage compressor 21 and the high-stage compressor 32 in the compression mechanism 20. Hereinafter, operations during various operations of the air conditioner 1 will be described.

<Cooling operation>
First, the cooling operation will be described with reference to FIG. Here, FIG. 13 is a schematic configuration diagram illustrating the flow of the refrigerant during the cooling operation of the air-conditioning apparatus 1.

  During the cooling operation, the switching mechanisms 22 and 31 are in the state indicated by the solid lines in FIG. 13, that is, the first switching mechanism 22 is connected to the second port 22b and the third port 22c, and the first port 22a Switching for connecting the fourth port 22d is performed. For the second switching mechanism 31, switching is performed for connecting the second port 31b and the third port 31c and for connecting the first port 31a and the fourth port 31d. I do. Further, the first gas refrigerant opening / closing mechanism 35 is opened, and the first liquid refrigerant opening / closing mechanism 37, the high-stage suction expansion valve 39, and the second liquid refrigerant opening / closing mechanism 40 are closed. Thereby, in the refrigerant circuit 10, the outdoor heat exchanger 23 is made to function as a condenser of the refrigerant | coolant compressed in the low stage side compressor 21, and the indoor heat exchangers 52 and 62 were condensed in the outdoor heat exchanger 23. A single-stage compression refrigeration cycle is performed which functions as a refrigerant evaporator.

  In this refrigerant circuit 10, low-pressure gas refrigerant in the refrigeration cycle is sucked into the low-stage compressor 21 and compressed to become high-pressure gas refrigerant. This high-pressure gas refrigerant is sent to the outdoor heat exchanger 23 through the first switching mechanism 22, exchanges heat with outdoor air supplied by the outdoor fan 28, and condenses to become a high-pressure liquid refrigerant. The high-pressure liquid refrigerant is sent to the indoor expansion valves 51 and 61 through the outdoor expansion valve 24, the second liquid refrigerant communication pipe 7b, the first liquid refrigerant check mechanism 36, and the first liquid refrigerant communication pipe 7a, and decompressed. It becomes a low-pressure refrigerant. The low-pressure refrigerant is sent to the indoor heat exchangers 52 and 62, exchanges heat with the indoor air supplied by the indoor fans 53 and 63, and evaporates to become a low-pressure gas refrigerant. The low-pressure gas refrigerant is sucked into the low-stage compressor 21 again through the first gas refrigerant communication pipe 8a, the first gas refrigerant open / close mechanism 35, the second gas refrigerant communication pipe 8b, and the second switching mechanism 31. .

  During this cooling operation, the hot gas opening / closing mechanism 27b is opened. For this reason, a part of the high-pressure refrigerant that is compressed in the low-stage compressor 21 and flows through the second gas refrigerant pipe 26 b is branched to the hot gas bypass pipe 27. The high-pressure refrigerant branched into the hot gas bypass pipe 27 is sent to the antifreezing heat exchanger 25 to heat the lower side of the outdoor heat exchanger 23. That is, the antifreezing heat exchanger 25 functions as a refrigerant condenser, similarly to the outdoor heat exchanger 23. Thereby, a part of the high-pressure gas refrigerant compressed in the low-stage compressor 21 is sent to the anti-freezing heat exchanger 25 through the hot gas bypass pipe 27 and the outdoor air supplied by the outdoor fan 28 and Heat exchange is performed to condense into a high-pressure liquid refrigerant. The high-pressure liquid refrigerant is sent to the liquid refrigerant pipe 26e through the hot gas decompression mechanism 27a, the hot gas opening / closing mechanism 27b, and the hot gas check mechanism 27c, and merges with the high-pressure liquid refrigerant from the outdoor heat exchanger 23. Thus, in the air conditioner 1, not only the outdoor heat exchanger 23 but also the antifreezing heat exchanger 25 functions as a refrigerant condenser during the cooling operation. Thereby, in the air conditioner 1, cooling of the refrigerant sent to the indoor heat exchangers 52 and 62 is promoted during the cooling operation, compared to a case where only the outdoor heat exchanger 23 functions as a refrigerant condenser, The cooling capacity is improved.

<Single stage heating operation>
Next, a single stage heating operation is demonstrated using FIG. Here, FIG. 14 is a schematic configuration diagram showing a refrigerant flow during the single-stage heating operation of the air-conditioning apparatus 1.

  As described above, the single-stage heating operation is a heating operation performed under conditions where the outside air temperature is high, that is, under conditions where it is easy to ensure the heating capacity. Here, the single-stage heating operation is performed when the outside air temperature Ta detected by the outside air temperature sensor 29d is equal to or higher than a predetermined first outside air temperature Tas1 (for example, 5 ° C.).

  At the time of single-stage heating operation, the switching mechanisms 22 and 31 are in the state indicated by the broken lines in FIG. 14, that is, the first switching mechanism 22 is connected to the second port 22b and the fourth port 22d, and the first port The second switching mechanism 31 communicates the second port 31b and the fourth port 31d and communicates the first port 31a and the third port 31c with each other. Change the mode. In addition, the first gas refrigerant opening / closing mechanism 35 and the first liquid refrigerant opening / closing mechanism 37 are opened, and the high stage suction expansion valve 39 and the second liquid refrigerant opening / closing mechanism 40 are closed. As a result, in the refrigerant circuit 10, the outdoor heat exchanger 23 functions as an evaporator for the refrigerant condensed in the indoor heat exchangers 42 and 52, and the indoor heat exchangers 52 and 62 are compressed in the low-stage compressor 21. A single-stage compression refrigeration cycle is performed that functions as a condenser for the refrigerated refrigerant.

  In this refrigerant circuit 10, low-pressure gas refrigerant in the refrigeration cycle is sucked into the low-stage compressor 21 and compressed to become high-pressure gas refrigerant. The high-pressure gas refrigerant passes through the first switching mechanism 22, the second switching mechanism 31, the second gas refrigerant communication pipe 8b, the first gas refrigerant opening / closing mechanism 35, and the first gas refrigerant communication pipe 8a, and the indoor heat exchangers 52 and 62. The heat is exchanged with the indoor air supplied by the indoor fans 53 and 63 to condense into a high-pressure liquid refrigerant. The high-pressure liquid refrigerant is expanded outdoors through the indoor expansion valves 51 and 61, the first liquid refrigerant communication pipe 7a, the first liquid refrigerant open / close mechanism 37, the second liquid refrigerant check mechanism 38, and the second liquid refrigerant communication pipe 7b. The low-pressure refrigerant that is sent to the valve 24 and decompressed to become a low-pressure refrigerant is sent to the outdoor heat exchanger 23 to evaporate by exchanging heat with the outdoor air supplied by the outdoor fan 28. It becomes a low-pressure gas refrigerant. This low-pressure gas refrigerant is again sucked into the low-stage compressor 21 through the first switching mechanism 22.

  During this single stage heating operation, the hot gas opening / closing mechanism 27b is closed. For this reason, the high-pressure refrigerant that is compressed in the low-stage compressor 21 and flows through the second gas refrigerant pipe 26 b is not branched to the hot gas bypass pipe 27. That is, during the single-stage heating operation, the refrigerant does not flow through the antifreezing heat exchanger 25. As described above, in the air conditioner 1, all of the high-pressure gas refrigerant compressed in the low-stage compressor 21 is sent to the indoor heat exchangers 52 and 62 during the single-stage heating operation. As described above, in the air conditioner 1, the flow rate of the refrigerant sent to the indoor heat exchangers 52 and 62 is larger in the single-stage heating operation than in the case of flowing the refrigerant through the antifreezing heat exchanger 25, The decrease in heating capacity is suppressed.

<Two-stage heating operation>
Next, the two-stage heating operation will be described with reference to FIG. Here, FIG. 15 is a schematic configuration diagram illustrating the flow of the refrigerant during the two-stage heating operation of the air-conditioning apparatus 1.

  As described above, the two-stage heating operation is a heating operation performed under a condition where the outside air temperature is low, that is, a condition where it is difficult to ensure the heating capacity. Here, the two-stage heating operation is performed when the outside air temperature Ta detected by the outside air temperature sensor 29d is lower than a predetermined first outside air temperature Tas1 (for example, 5 ° C.).

  During the two-stage heating operation, the switching mechanisms 22 and 31 are in the state indicated by the broken line in FIG. 15, that is, for the first switching mechanism 22, the second port 22b and the fourth port 22d are communicated, and the first port The second switching mechanism 31 communicates the second port 31b and the fourth port 31d and communicates the first port 31a and the third port 31c with each other. Change the mode. Further, the high-stage intake expansion valve 39 and the second liquid refrigerant opening / closing mechanism 40 are opened, and the first gas refrigerant opening / closing mechanism 35 and the first liquid refrigerant opening / closing mechanism 37 are closed. Thereby, in the refrigerant circuit 10, the outdoor heat exchanger 23 functions as an evaporator of the refrigerant condensed in the indoor heat exchangers 42 and 52, and the indoor heat exchangers 52 and 62 are connected to the low-stage compressor 21 and the high-pressure side compressor 21. A two-stage compression refrigeration cycle that functions as a condenser for the refrigerant compressed in the stage-side compressor 32 is performed.

  In the refrigerant circuit 10, the low-pressure gas refrigerant in the refrigeration cycle is sucked into the low-stage compressor 21 and compressed to become an intermediate-pressure gas refrigerant. This intermediate-pressure gas refrigerant is sucked into the high-stage compressor 32 through the first switching mechanism 22, the second switching mechanism 31, the second gas refrigerant communication pipe 8b, and the high-stage suction expansion valve 39, and is compressed and pressurized. Gas refrigerant. This high-pressure gas refrigerant is sent to the indoor heat exchangers 52 and 62 through the first gas refrigerant communication pipe 8a, and is condensed by exchanging heat with the indoor air supplied by the indoor fans 53 and 63. Becomes a refrigerant. This high-pressure liquid refrigerant is sent to the gas-liquid separator 33 through the indoor expansion valves 51 and 61, the first liquid refrigerant communication pipe 7a, the second liquid refrigerant open / close mechanism 40, and the third liquid refrigerant check mechanism 41, It is separated into a refrigerant and a liquid refrigerant. The gas refrigerant separated in the gas-liquid separator 33 is sucked into the high stage compressor 32. Further, the liquid refrigerant separated in the gas-liquid separator 33 is sent to the outdoor expansion valve 24 through the fourth liquid refrigerant check mechanism 42 and the second liquid refrigerant communication pipe 7b, and is depressurized to be a low-pressure refrigerant. Become. The low-pressure refrigerant is sent to the outdoor heat exchanger 23, exchanges heat with outdoor air supplied by the outdoor fan 28, and evaporates to become a low-pressure gas refrigerant. This low-pressure gas refrigerant is again sucked into the low-stage compressor 21 through the first switching mechanism 22.

  During this two-stage heating operation, the hot gas opening / closing mechanism 27b is closed except when performing anti-freezing control when resuming heating, which will be described later. For this reason, the intermediate-pressure refrigerant that is compressed in the low-stage compressor 21 and flows through the second gas refrigerant pipe 26b is branched to the hot gas bypass pipe 27, except when performing anti-freezing control at the time of resuming heating described later. There is nothing. That is, during the two-stage heating operation, the refrigerant does not flow through the anti-freezing heat exchanger 25 except when performing anti-freezing control when resuming heating described later. As described above, in the air conditioning apparatus 1, during the two-stage heating operation, all of the intermediate-pressure gas refrigerant compressed in the low-stage compressor 21 is high except for the case where anti-freezing control at the time of heating restart described later is performed. It is compressed in the stage side compressor 32 to become a high-pressure gas refrigerant, and is sent to the indoor heat exchangers 52 and 62. As described above, in the air conditioner 1, the flow rate of the refrigerant sent to the indoor heat exchangers 52 and 62 is increased in the two-stage heating operation as compared with the case where the refrigerant is passed through the freeze prevention heat exchanger 25. The decrease in heating capacity is suppressed.

<Single stage defrosting operation>
Next, the single stage defrosting operation will be described with reference to FIG. Here, FIG. 13 is a schematic configuration diagram illustrating the flow of the refrigerant during the single-stage defrosting operation of the air-conditioning apparatus 1.

  The single-stage defrosting operation is a defrosting operation performed under a condition in which the outside air temperature is high, like the heating operation. Here, similarly to the single-stage heating operation, the single-stage defrosting operation is performed when the outside air temperature Ta detected by the outside air temperature sensor 29d is equal to or higher than a predetermined first outside air temperature Tas1.

  As described above, the single-stage defrosting operation is a reverse cycle defrosting operation in which the refrigerant flow direction is reversed from the single-stage heating operation. Therefore, during the single-stage defrosting operation, the switching mechanisms 22 and 31 are in the state indicated by the solid line in FIG. 13, that is, the first switching mechanism 22 is connected to the second port 22b and the third port 22c, and The first port 22a and the fourth port 22d are switched to communicate with each other, the second switching mechanism 31 is connected to the second port 31b and the third port 31c, and the first port 31a and the fourth port are communicated. Switching to communicate with 31d is performed. Further, the first gas refrigerant opening / closing mechanism 35 is opened, and the first liquid refrigerant opening / closing mechanism 37, the high-stage suction expansion valve 39, and the second liquid refrigerant opening / closing mechanism 40 are closed. Thereby, in the refrigerant circuit 10, the outdoor heat exchanger 23 is made to function as a condenser of the refrigerant | coolant compressed in the low stage side compressor 21, and the indoor heat exchangers 52 and 62 were condensed in the outdoor heat exchanger 23. A single-stage compression refrigeration cycle is performed which functions as a refrigerant evaporator.

  Here, the single-stage defrosting operation is performed when the control unit 9 determines that frost formation has occurred in the outdoor heat exchanger 23 during the heating operation. This determination is performed based on the temperature Tb of the refrigerant flowing through the outdoor heat exchanger 23 detected by the outdoor heat exchanger temperature sensor 29c and the accumulated time of the heating operation. For example, when it is detected that the temperature Tb of the refrigerant detected by the outdoor heat exchanger temperature sensor 29c has decreased to a predetermined temperature or less that can be regarded as frost formation in the outdoor heat exchanger 23, or heating If the accumulated time of operation has passed a predetermined time that can be regarded as frost formation in the outdoor heat exchanger 23, it is determined that frost formation has occurred in the outdoor heat exchanger 23. When the temperature and time conditions are not reached, it is determined that frost formation has not occurred in the outdoor heat exchanger 23.

  In the refrigerant circuit 10, the refrigerant circulates in the same flow direction as that in the cooling operation. Then, the high-pressure refrigerant that is compressed by the low-stage compressor 21 and flows through the second gas refrigerant pipe 26 b is sent to the outdoor heat exchanger 23 through the switching mechanism 22 to heat the outdoor heat exchanger 23. Thereby, the frost generated in the outdoor heat exchanger 23 in the heating operation is melted to become drain water, and passes through the anti-freezing heat exchanger 25 integrated with the outdoor heat exchanger 23 to the lower side of the outdoor heat exchanger 23. It collects on the bottom plate 2a of the outdoor unit 2 as a drain pan arranged. The drain water accumulated on the bottom plate 2a is discharged out of the outdoor unit 2 through a discharge port 2b formed on the bottom plate 2a.

  The single-stage defrosting operation ends when the control unit 9 determines that the defrosting of the outdoor heat exchanger 23 has been completed. This determination is made based on the temperature Tb of the refrigerant flowing through the outdoor heat exchanger 23 detected by the outdoor heat exchanger temperature sensor 29c and the operation time of the single-stage defrosting operation. For example, when it is detected that the temperature Tb of the refrigerant detected by the outdoor heat exchanger temperature sensor 29c is equal to or higher than a temperature at which frost can be regarded as melted, or the operation time of the single-stage defrosting operation When the predetermined time or more has elapsed, it is determined that the defrosting of the outdoor heat exchanger 23 has been completed, and when the temperature condition or time condition has not been reached, the defrosting of the outdoor heat exchanger 23 has been completed. It is determined that it has not been completed.

  During this single-stage defrosting operation, the hot gas opening / closing mechanism 27b is opened as in the above cooling operation. For this reason, a part of the high-pressure refrigerant that is compressed in the low-stage compressor 21 and flows through the second gas refrigerant pipe 26 b is branched to the hot gas bypass pipe 27. The high-pressure refrigerant branched into the hot gas bypass pipe 27 is sent to the antifreezing heat exchanger 25 to heat the lower side of the outdoor heat exchanger 23. That is, the anti-freezing heat exchanger 25 functions as a heater for drain water melted by performing a single-stage defrosting operation. As a result, during the single-stage defrosting operation, the drain water from the outdoor heat exchanger 23 is heated on the lower side of the outdoor heat exchanger 23 and then collected on the bottom plate 2a of the outdoor unit 2 as a drain pan. It is discharged out of the unit 2. Thus, in the air conditioner 1, during the single-stage defrosting operation, the freeze prevention heat exchanger 25 heats the drain water generated in the outdoor heat exchanger 23 on the lower side of the outdoor heat exchanger 23. It has become. Thereby, in the air conditioning apparatus 1, the drain water from the outdoor heat exchanger 23 is quickly discharged | emitted out of the outdoor unit 2 at the time of a single stage defrost operation.

<Two-stage defrosting operation>
Next, the two-stage defrosting operation will be described with reference to FIG. Here, FIG. 16 is a schematic configuration diagram illustrating the flow of the refrigerant during the two-stage defrosting operation of the air-conditioning apparatus 1.

  Similar to the heating operation, the two-stage defrosting operation is a defrosting operation performed under a condition where the outside air temperature is low. Here, similarly to the two-stage heating operation, the two-stage defrosting operation is performed when the outside air temperature Ta detected by the outside air temperature sensor 29d is lower than the predetermined first outside air temperature Tas1.

  As described above, the two-stage defrosting operation is a reverse cycle defrosting operation in which the refrigerant flow direction is reversed from the two-stage heating operation. Therefore, during the two-stage defrosting operation, the switching mechanisms 22 and 31 are in the state indicated by the solid line in FIG. 16, that is, the first switching mechanism 22 is connected to the second port 22b and the third port 22c, and The first port 22a and the fourth port 22d are switched to communicate with each other, the second switching mechanism 31 is connected to the second port 31b and the third port 31c, and the first port 31a and the fourth port are communicated. Switching to communicate with 31d is performed. Further, the first gas refrigerant opening / closing mechanism 35 and the second liquid refrigerant opening / closing mechanism 40 are opened, and the first liquid refrigerant opening / closing mechanism 37 and the high stage suction expansion valve 39 are closed. Thereby, in the refrigerant circuit 10, the outdoor heat exchanger 23 is caused to function as a condenser for the refrigerant compressed in the high-stage compressor 32 and the low-stage compressor 21, and the indoor heat exchangers 52 and 62 are operated outdoors. A two-stage compression refrigeration cycle that functions as an evaporator for the refrigerant condensed in the heat exchanger 23 is performed.

  Here, similarly to the single-stage defrosting operation, the two-stage defrosting operation is performed when the controller 9 determines that frost formation has occurred in the outdoor heat exchanger 23 during the heating operation. Since the content of this determination is the same as the content of the determination in the single stage defrosting operation, the description is omitted here.

  In the refrigerant circuit 10, the gas refrigerant is sucked into the low stage compressor 21 and compressed to become a high-pressure gas refrigerant. This high-pressure gas refrigerant is sent to the outdoor heat exchanger 23 through the first switching mechanism 22 to heat the outdoor heat exchanger 23. Thereby, the frost generated in the outdoor heat exchanger 23 in the heating operation is melted to become drain water, and passes through the anti-freezing heat exchanger 25 integrated with the outdoor heat exchanger 23 to the lower side of the outdoor heat exchanger 23. It collects on the bottom plate 2a of the outdoor unit 2 as a drain pan arranged. The drain water accumulated on the bottom plate 2a is discharged out of the outdoor unit 2 through a discharge port 2b formed on the bottom plate 2a. The high-pressure refrigerant that has melted frost in the outdoor heat exchanger 24 is sent to the outdoor expansion valve 24 to be depressurized. A part of the decompressed refrigerant is sent to the indoor expansion valves 51 and 61 through the second liquid refrigerant communication pipe 7b, the first liquid refrigerant check mechanism 36 and the first liquid refrigerant communication pipe 7a, and the rest The second liquid refrigerant communication pipe 7b, the first liquid refrigerant check mechanism 36, the second liquid refrigerant open / close mechanism 40, and the third liquid refrigerant check mechanism 41 are sent to the gas-liquid separator 33. The low-pressure refrigerant sent to the indoor expansion valves 51 and 61 is sent to the ninth gas refrigerant pipe 34a through the indoor expansion valves 51 and 61, the indoor heat exchangers 52 and 62, and the first gas refrigerant communication pipe 8a. The low-pressure refrigerant sent to the gas-liquid separator 33 is sucked into the high-stage compressor 32 and compressed, sent to the ninth gas refrigerant pipe 34a, and sent to the indoor expansion valves 51 and 61 and the indoor It merges with the refrigerant sent to the ninth gas refrigerant pipe 34a through the heat exchangers 52 and 62. The refrigerant merged in the ninth gas refrigerant pipe 34 a is again sucked into the low-stage compressor 21 through the first gas refrigerant opening / closing mechanism 35, the second gas refrigerant communication pipe 8 b and the second switching mechanism 31.

  Then, the two-stage defrosting operation ends when the control unit 9 determines that the defrosting of the outdoor heat exchanger 23 has been completed, similarly to the single-stage defrosting operation. Since the content of this determination is the same as the content of the determination in the single stage defrosting operation, the description is omitted here.

  During the two-stage defrosting operation, the hot gas opening / closing mechanism 27b is opened in the same manner as in the single-stage defrosting operation. For this reason, a part of the high-pressure refrigerant that is compressed in the low-stage compressor 21 and flows through the second gas refrigerant pipe 26 b is branched to the hot gas bypass pipe 27. The high-pressure refrigerant branched into the hot gas bypass pipe 27 is sent to the antifreezing heat exchanger 25 to heat the lower side of the outdoor heat exchanger 23. That is, the anti-freezing heat exchanger 25 functions as a heater for drain water melted by performing the two-stage defrosting operation. Thus, during the two-stage defrosting operation, the drain water from the outdoor heat exchanger 23 is heated on the lower side of the outdoor heat exchanger 23 and then collected on the bottom plate 2a of the outdoor unit 2 as a drain pan. It is discharged out of the unit 2. Thus, in the air conditioner 1, during the two-stage defrosting operation, the antifreezing heat exchanger 25 heats the drain water generated in the outdoor heat exchanger 23 on the lower side of the outdoor heat exchanger 23. It has become. Thereby, in the air conditioning apparatus 1, drain water is quickly discharged out of the outdoor unit 2 during the two-stage defrosting operation. In particular, the two-stage defrosting operation is performed under a condition where the outside air temperature is lower than the condition of the outside air temperature at which the single stage defrosting operation is performed (that is, when the outside air temperature Ta is lower than the predetermined first outside air temperature Tas1). The drain water from the outdoor heat exchanger 23 can be prevented from freezing on the lower side of the outdoor heat exchanger 23, and the occurrence of the ice-up phenomenon during the two-stage defrosting operation is suppressed.

<Freezing prevention control when resuming heating>
As described above, in the air conditioning apparatus 1, during the defrosting operation, a part of the high-pressure refrigerant compressed by the low-stage compressor 21 is caused to flow through the antifreezing heat exchanger 25 during the defrosting operation. Freezing of drain water in can be prevented.

  However, for a while after the defrosting operation is completed, the drain water melted by performing the defrosting operation exists on the lower side of the outdoor heat exchanger 23, and the drain water to the outside of the outdoor unit 2 is present. Emission continues. Thereafter, when the heating operation is resumed, there is a possibility that the drain water is frozen before the drain water is discharged under a condition where the outside air temperature Ta is low. For this reason, the freezing of drain water at the time of the two-stage heating operation after the defrosting operation cannot be prevented, and an ice-up phenomenon may occur.

  Therefore, in the air conditioner 1, in the initial stage of restart of the two-stage heating operation after the defrosting operation, a part of the refrigerant compressed in the low-stage compressor 21 is flown to the freezing prevention heat exchanger 25 when the heating is restarted. Preventive control is performed.

  Next, this anti-freezing control when resuming heating will be described with reference to FIGS. 17 and 18. Here, FIG. 17 is a flowchart of the freeze prevention control at the resumption of heating of the air conditioner 1. FIG. 18 is a schematic configuration diagram illustrating the flow of the refrigerant during the freeze prevention control at the time of resuming heating of the air-conditioning apparatus 1.

  First, the control part 9 determines whether it is the two-stage heating operation after a defrost operation in step S1. In this step S1, when it is determined that the two-stage heating operation is performed after the defrosting operation, the process proceeds to the process of step S2 for determining whether or not an outside air temperature condition that requires the anti-freezing control when resuming heating is satisfied. .

  In step S2, the controller 9 determines whether or not the outside air temperature Ta detected by the outside air temperature sensor 29d is equal to or lower than a predetermined second outside air temperature Tas2. In this step S2, when the outside air temperature Ta is equal to or lower than the predetermined second outside air temperature Tas2, that is, when the outside air temperature condition is satisfied, the process proceeds to the processing of steps S3 to S5 for executing the anti-freezing control when resuming heating. . On the other hand, when the outside air temperature Ta is higher than the predetermined second outside air temperature Tas2, that is, when the outside air temperature condition is not satisfied, the two-stage heating operation is performed without performing the freeze prevention control at the time of resuming the heating in steps S3 to S5. Resume. Here, the predetermined second outside air temperature Tas2 is set in view of whether or not the drain water present on the lower side of the outdoor heat exchanger 23 may be frozen after the defrosting operation. Is set to 0 ° C. The predetermined second outside air temperature Tas2 is lower than the first outside air temperature Tas1, which is a temperature at which switching between the single-stage heating operation and the two-stage heating operation is performed. The predetermined second outside air temperature Tas2 is stored in advance in a memory or the like of the control unit 9, and is changed by a switch (not shown) or a remote controller (not shown) provided in the control unit 9. Can be done.

  Then, in step S3, the control unit 9 starts the anti-freezing control at the resumption of heating in which a part of the refrigerant compressed by the low-stage compressor 21 is passed to the anti-freezing heat exchanger 25. That is, in the refrigerant circuit 10, the same refrigeration cycle as in the above-described two-stage heating operation is performed, and the hot gas opening / closing mechanism 27b is opened. For this reason, a part of the high-pressure refrigerant that is compressed in the low-stage compressor 21 and flows through the second gas refrigerant pipe 26 b is branched to the hot gas bypass pipe 27. The high-pressure refrigerant branched into the hot gas bypass pipe 27 is sent to the antifreezing heat exchanger 25 to heat the lower side of the outdoor heat exchanger 23. That is, the antifreezing heat exchanger 25 functions as a heater for drain water existing on the lower side of the outdoor heat exchanger 23 after the defrosting operation. Here, since the outlet of the hot gas bypass pipe 27 is connected to a portion of the liquid refrigerant pipe 26e through which the low-pressure refrigerant flows downstream of the outdoor expansion valve 24, the flow rate of the refrigerant flowing through the hot gas bypass pipe 27 is high. It is easy to be secured. The refrigerant that has heated the drain water in the antifreezing heat exchanger 25 condenses in the antifreezing heat exchanger 25, but then merges with the refrigerant flowing through the liquid refrigerant pipe 26e and functions as a refrigerant evaporator. Therefore, the refrigerant condensed in the freezing prevention heat exchanger 25 remains in a liquid state and is not sucked into the low-stage compressor 21. As a result, during the two-stage heating operation after the defrosting operation, the drain water present on the lower side of the outdoor heat exchanger 23 is heated in the freezing prevention heat exchanger 25 and then the outdoor unit 2 as a drain pan. It accumulates on the bottom plate 2 a and is discharged out of the outdoor unit 2. Thus, in the air conditioner 1, the anti-freezing heat exchanger 25 heats the drain water present on the lower side of the outdoor heat exchanger 23 during the two-stage heating operation after the defrosting operation. Yes. Thereby, in the air conditioning apparatus 1, in the two-stage heating operation after the defrosting operation, the drain water present on the lower side of the outdoor heat exchanger 23 can be discharged without freezing after the defrosting operation. Occurrence of the ice-up phenomenon during the two-stage heating operation after the defrosting operation is suppressed.

  And control part 9 judges whether predetermined time ts passed after defrost operation in Step S4, and when predetermined time ts passed, it shifts to processing of Step S5. Here, the predetermined time ts is set to about several minutes in consideration of the time required to discharge the drain water present on the lower side of the outdoor heat exchanger 23 after the defrosting operation. The predetermined time ts is stored in advance in a memory or the like of the control unit 9 and can be changed by a switch (not shown) or a remote controller (not shown) provided in the control unit 9. It has become. And the control part 9 complete | finishes freezing prevention control at the time of heating resumption in step S5, and transfers to normal two-stage heating operation. That is, in the refrigerant circuit 10, the same refrigeration cycle as in the above-described two-stage heating operation is performed, and the hot gas opening / closing mechanism 27b is closed. For this reason, during the two-stage heating operation after the defrosting operation, the predetermined time ts for discharging the drain water existing on the lower side of the outdoor heat exchanger 23 after the defrosting operation without freezing, that is, the defrosting operation. Only when the subsequent two-stage heating operation is restarted, the anti-freezing control at the time of restarting heating is performed. Here, during the two-stage heating operation after the defrosting operation, flowing a part of the refrigerant compressed in the low-stage compressor 21 to the anti-freezing heat exchanger 25 is sent to the indoor heat exchangers 52 and 62. Since the flow rate of the refrigerant to be reduced is reduced, the heating capacity is reduced. However, in the air conditioner 1, as described above, only a part of the refrigerant compressed in the low-stage compressor 21 is used for preventing freezing only in the initial stage of restarting the two-stage heating operation in the heating operation after the defrosting operation. It is made to flow to the heat exchanger 25. For this reason, in the air conditioning apparatus 1, the fall of the heating capability in the heating operation after a defrost operation is suppressed.

  As described above, the air conditioner 1 can suppress the occurrence of the ice-up phenomenon during the two-stage heating operation after the defrosting operation while suppressing the decrease in the heating capacity in the heating operation after the defrosting operation. It has become.

(3) Features of the air conditioner The air conditioner 1 that performs the two-stage compression refrigeration cycle as in the present embodiment also has the same features as the air conditioner 1 of the first embodiment.

<A>
That is, in the air conditioner 1, during the two-stage heating operation after the defrosting operation, a part of the refrigerant compressed in the compression mechanism 20 (here, the low-stage compressor 21) is transferred to the antifreezing heat exchanger 25. By flowing, the drain water present on the lower side of the outdoor heat exchanger 23 is frozen after the defrosting operation under conditions where the outside air temperature Ta is low (here, the outside air temperature Ta is equal to or less than the second outside air temperature Tas2). It can discharge without. For this reason, in the air conditioning apparatus 1, generation | occurrence | production of the ice-up phenomenon at the time of the two-stage heating operation after a defrost operation can be suppressed.

  Here, during the two-stage heating operation after the defrosting operation, flowing a part of the refrigerant compressed in the low-stage compressor 21 to the anti-freezing heat exchanger 25 is sent to the indoor heat exchangers 52 and 62. Since the flow rate of the refrigerant to be reduced is reduced, the heating capacity is reduced.

  Therefore, in the air conditioner 1, as described above, a part of the refrigerant compressed in the low-stage compressor 21 is used for preventing freezing only in the initial stage of restarting the two-stage heating operation in the heating operation after the defrosting operation. It is made to flow to the heat exchanger 25 (that is, freeze prevention control when resuming heating). For this reason, in the air conditioning apparatus 1, the fall of the heating capability in the heating operation after a defrost operation can be suppressed.

  Thereby, in the air conditioning apparatus 1, generation | occurrence | production of the ice-up phenomenon at the time of the two-stage heating operation after a defrost operation can be suppressed, suppressing the fall of the heating capability in the heating operation after a defrost operation.

<B>
In the air conditioner 1, the antifreezing control at the time of resuming heating is performed when the outside air temperature Ta is equal to or lower than a predetermined second outside air temperature Tas2. For this reason, in the air conditioner 1, only under conditions where the outside air temperature Ta at which the drain water present on the lower side of the outdoor heat exchanger 23 may freeze after the defrosting operation is low (in this case, 0 ° C. or less). When the heating is resumed, the freeze prevention control is performed. Under the condition where the outside air temperature Ta is high (in this case, higher than 0 ° C.), the freeze prevention control when the heating is resumed can be omitted.

  Thereby, in the air conditioning apparatus 1, the fall of the heating capability in the heating operation after a defrost operation can further be suppressed.

<C>
In the air conditioner 1, the freeze prevention control at the time of resuming heating is performed until a predetermined time ts elapses after the defrosting operation. That is, in the air conditioner 1, since the freeze prevention control at the time of resuming heating is managed by time, the time required for discharging the drain water present on the lower side of the outdoor heat exchanger 23 after the defrosting operation. Can be considered.

  Thereby, in the air conditioning apparatus 1, the freeze prevention control at the time of resuming heating can be appropriately performed in consideration of the time required for discharging drain water.

(4) Modified Example In the air conditioner 1 of the above embodiment, as in the modified example 1 (see FIG. 8) of the air conditioner 1 of the first embodiment, the outside air humidity increases as the outside temperature Ta decreases. As the operating time of the defrosting operation becomes longer, the predetermined time ts may be set longer.

  Moreover, in the air conditioning apparatus 1 of the said embodiment, the heat exchanger 25 for antifreezing is added to the hot gas bypass pipe 27 similarly to the modification 2 (refer FIG.9 and FIG.10) of the air conditioning apparatus 1 of 1st Embodiment. The hot gas flow rate adjustment valve 27d for changing the flow rate of the refrigerant flowing through the refrigerant is provided, and the heating is resumed as the outside air temperature Ta becomes low, the outside air humidity becomes high, or the operation time of the defrosting operation becomes long. You may set so that the opening degree of the hot gas flow control valve 27d in a time freezing prevention control may be enlarged.

  Thereby, also in the air conditioning apparatus 1 of this modification, the change of the amount of drain water by conditions, such as external temperature Ta, is considered similarly to the modifications 1 and 2 of the air conditioning apparatus 1 of 1st Embodiment. In addition, it is possible to appropriately perform anti-freezing control when resuming heating.

-Other embodiments-
As mentioned above, although embodiment of this invention and its modification were demonstrated based on drawing, specific structure is not restricted to the said embodiment and its modification, It can change in the range which does not deviate from the summary of invention. It is.

  In the above embodiment and its modifications, the present invention is applied to an air conditioner that can be switched between cooling and heating by switching between cooling operation, heating operation, and reverse cycle defrosting operation, but is not limited thereto, for example, The present invention may be applied to a heating-only air conditioner that performs switching between heating operation and reverse cycle defrosting operation but does not perform cooling operation.

  The present invention relates to an air conditioner that performs a heating operation and a reverse cycle defrosting operation.

DESCRIPTION OF SYMBOLS 1 Air conditioning apparatus 20 Compression mechanism 21 Compressor (compression mechanism)
23 Outdoor Heat Exchanger 25 Freezing Prevention Heat Exchanger 52, 62 Indoor Heat Exchanger 27d Hot Gas Flow Control Valve (Flow Control Valve)

JP 2009-127939 A

Claims (5)

Refrigerant is circulated in the order of the compression mechanism (20, 21), the indoor heat exchanger (52, 62), and the outdoor heat exchanger (23) for heating operation, and the compression mechanism, the outdoor heat exchanger, and In the air conditioner for performing the defrosting operation by circulating the refrigerant in the order of the indoor heat exchanger,
A freezing prevention heat exchanger (25) capable of heating the lower side of the outdoor heat exchanger by a part of the refrigerant compressed in the compression mechanism;
In the initial stage of resuming the heating operation after the defrosting operation, performing antifreezing control at the time of resuming heating, in which a part of the refrigerant compressed in the compression mechanism is passed to the antifreezing heat exchanger,
Air conditioner (1). The freeze prevention control at the time of resuming heating is performed when the outside air temperature is equal to or lower than a predetermined outside air temperature.
The air conditioner (1) according to claim 1. The heating prevention restart freeze prevention control is performed until a predetermined time elapses after the defrosting operation.
The air conditioner (1) according to claim 1 or 2. Increasing the predetermined time as the outside air temperature decreases, the outside air humidity increases, or the operation time of the defrosting operation increases.
The air conditioner (1) according to claim 3. A flow rate adjusting valve (27d) for varying the flow rate of the refrigerant flowing through the anti-freezing heat exchanger (25);
Increasing the opening of the flow control valve as the outside air temperature decreases, the outside air humidity increases, or the operating time of the defrosting operation increases.
The air conditioning apparatus (1) according to any one of claims 1 to 3.

Images