CN119343571A - Air conditioner - Google Patents

Abstract

An air conditioner (100) is provided with a Refrigerant Circuit (RC) and a blower (32). The refrigerant flow path switching mechanism (RF) is configured to be switched in the 1 st switching state so that the refrigerant flows in the Refrigerant Circuit (RC) in the order of the reheater (21), the 1 st expansion valve (23), and the cooler (22). The refrigerant flow path switching mechanism (RF) is configured to be switched in the 2 nd switching state so that the refrigerant flows in the Refrigerant Circuit (RC) in the order of the reheater (21), the 1 st expansion valve (23), and the cooler (22). The reheater (21) and the cooler (22) are configured such that the air blown by the blower (32) passes through the reheater (21) after passing through the cooler (22) in both the 1 st switching state and the 2 nd switching state.

Description

Air conditioner

Technical Field

The present disclosure relates to air conditioners.

Background

An air conditioner is known that includes an outdoor unit including an outdoor heat exchanger functioning as a condenser, an indoor unit including a1 st indoor heat exchanger functioning as a cooler and a2 nd indoor heat exchanger functioning as a reheater, and a compressor for circulating a refrigerant through the outdoor heat exchanger, the 1 st indoor heat exchanger, and the 2 nd indoor heat exchanger. In this air conditioner, the temperature and humidity of the air blown out from the indoor unit to the space to be air-conditioned are respectively adjusted by heating the air cooled and dehumidified by the 1 st indoor heat exchanger and by heating the air by the 2 nd indoor heat exchanger. Such an air conditioner is described in, for example, japanese patent application laid-open No. 2002-89998 (patent document 1).

Prior art literature

Patent literature

Patent document 1 Japanese patent laid-open No. 2002-89998

Disclosure of Invention

Problems to be solved by the invention

However, in the air conditioner described in the above publication, only one four-way valve is used as the refrigerant flow path switching mechanism. Therefore, when the cooling main operation and the heating main operation are performed in correspondence with the two switching states of the four-way valve, the direction of the refrigerant flowing through the indoor unit is reversed during the cooling main operation and the heating main operation. Therefore, the indoor heat exchanger functioning as a cooler and the indoor heat exchanger functioning as a reheater are replaced in the cooling main operation and the heating main operation. As a result, in either one of the cooling main operation and the heating main operation, the air heated by the reheater is cooled by the cooler, and therefore sufficient dehumidification cannot be performed.

The present disclosure has been made in view of the above-described problems, and an object thereof is to provide an air conditioner capable of making the directions of the refrigerant flowing through the reheater and the cooler the same in both the cooling main operation and the heating main operation.

Means for solving the problems

The air conditioner of the present disclosure includes a refrigerant circuit and a blower. The refrigerant circuit includes a compressor, a six-way valve, an outdoor heat exchanger, a reheater, a1 st expansion valve, and a cooler, and is configured to circulate a refrigerant. The blower is configured to blow air to the reheater and the cooler. The six-way valve is configured to be switchable between a1 st switching state and a2 nd switching state. The six-way valve is configured to be switched in the 1 st switching state such that the refrigerant flows in the refrigerant circuit in the order of the compressor, the six-way valve, the outdoor heat exchanger, the six-way valve, the reheater, the 1 st expansion valve, the six-way valve, and the cooler. The six-way valve is configured to be switched in the 2 nd switching state such that the refrigerant flows in the refrigerant circuit in the order of the compressor, the six-way valve, the reheater, the 1 st expansion valve, the six-way valve, the outdoor heat exchanger, the six-way valve, and the cooler. The reheater and the cooler are configured such that the air blown by the blower passes through the reheater after passing through the cooler, both in the 1 st switching state and in the 2 nd switching state.

Effects of the invention

According to the air conditioner of the present disclosure, the refrigerant flow path switching mechanism is configured to be switched such that the refrigerant flows in the refrigerant circuit in the order of the reheater and the cooler, both in the 1 st switching state and in the 2 nd switching state. Therefore, the directions of the refrigerant flowing through the reheater and the cooler can be made the same in both the cooling main operation and the heating main operation.

Drawings

Fig. 1 is a refrigerant circuit diagram of the cooling main operation of the air conditioner according to embodiment 1.

Fig. 2 is a refrigerant circuit diagram of the heating body operation of the air conditioner according to embodiment 1.

Fig. 3 is a schematic diagram of the 1 st switching state of the rotary six-way valve of the air conditioner according to embodiment 1.

Fig. 4 is a schematic diagram of the 2 nd switching state of the rotary six-way valve of the air conditioner according to embodiment 1.

Fig. 5 is a schematic diagram of the 1 st switching state of the sliding six-way valve of the air conditioner according to embodiment 1.

Fig. 6 is a schematic diagram of the 2 nd switching state of the sliding six-way valve of the air conditioner according to embodiment 1.

Fig. 7 is a refrigerant circuit diagram of the cooling main operation of the air conditioner according to embodiment 2.

Fig. 8 is a refrigerant circuit diagram of the heating body operation of the air conditioner according to embodiment 2.

Fig. 9 is a refrigerant circuit diagram of the cooling main operation of the air conditioner according to embodiment 3.

Fig. 10 is a refrigerant circuit diagram of the heating body operation of the air conditioner according to embodiment 3.

Fig. 11 is a refrigerant circuit diagram of the cooling main operation of the air conditioner according to embodiment 4.

Fig. 12 is a refrigerant circuit diagram of the heating body operation of the air conditioner according to embodiment 4.

Fig. 13 is a refrigerant circuit diagram of the cooling main operation of the air conditioner according to embodiment 5.

Fig. 14 is a refrigerant circuit diagram of the heating body operation of the air conditioner according to embodiment 5.

Fig. 15 is a refrigerant circuit diagram of the cooling main operation of the air conditioner according to embodiment 6.

Fig. 16 is a refrigerant circuit diagram of the heating body operation of the air conditioner according to embodiment 6.

Fig. 17 is a perspective view of a reheater and a cooler of an air conditioner according to embodiment 7.

Detailed Description

Hereinafter, embodiments will be described with reference to the drawings. In the following, the same or corresponding parts are denoted by the same reference numerals, and the description thereof will not be repeated.

Embodiment 1.

The structure of an air conditioner 100 according to embodiment 1 will be described with reference to fig. 1.

< Device Structure >

Fig. 1 is a refrigerant circuit diagram of an air conditioner 100 according to embodiment 1. As shown in fig. 1, the air conditioner 100 includes a refrigerant circuit RC, an outdoor fan 14, an air passage 31, a fan 32, and a control device CD. The refrigerant circuit RC includes a1 st pipe 1, a2 nd pipe 2, a3 rd pipe 3, a4 th pipe 4, a5 th pipe 5, a6 th pipe 6, a compressor 11, a six-way valve 12, an outdoor heat exchanger 13, a reheater 21, a cooler 22, and a1 st expansion valve 23.

In the refrigerant circuit RC, the compressor 11, the six-way valve 12, the outdoor heat exchanger 13, the reheater 21, the cooler 22, and the 1 st expansion valve 23 are connected by the 1 st pipe 1, the 2 nd pipe 2, the 3 rd pipe 3, the 4 th pipe 4, the 5 th pipe 5, and the 6 th pipe 6.

The 1 st pipe 1 connects the compressor 11 and the six-way valve 12. The 2 nd pipe 2 connects the six-way valve 12 and the outdoor heat exchanger 13. The 3 rd pipe 3 connects the outdoor heat exchanger 13 and the six-way valve 12. The 4 th pipe 4 connects the six-way valve 12 and the reheater 21. The 5 th pipe 5 connects the reheater 21 and the six-way valve 12 through the 1 st expansion valve 23. The 6 th pipe 6 connects the six-way valve 12 and the cooler 22.

In the 1 st switching state, the refrigerant circuit RC is configured such that the refrigerant flows in the order of the compressor 11, the 1 st pipe 1, the six-way valve 12, the 2 nd pipe 2, the outdoor heat exchanger 13, the 3 rd pipe 3, the six-way valve 12, the 4 th pipe 4, the reheater 21, the 5 th pipe 5, the 1 st expansion valve 23, the 5 th pipe 5, the six-way valve 12, the 6 th pipe 6, and the cooler 22.

In the 2 nd switching state, the refrigerant circuit RC is configured such that the refrigerant flows in the order of the compressor 11, the 1 st pipe 1, the six-way valve 12, the 4 th pipe 4, the reheater 21, the 5 th pipe 5, the 1 st expansion valve 23, the 5 th pipe 5, the six-way valve 12, the 3 rd pipe 3, the outdoor heat exchanger 13, the 2 nd pipe 2, the six-way valve 12, the 6 th pipe 6, and the cooler 22.

The refrigerant circuit RC is configured to circulate a refrigerant. The refrigerant is a mixed refrigerant. The mixed refrigerant is a mixture of two or more refrigerants. In addition, the refrigerant may be a single refrigerant.

The air conditioner 100 includes an outdoor unit 10 and an indoor unit 20. The outdoor unit 10 and the indoor unit 20 are connected by a2 nd pipe 2 and a 3 rd pipe 3. The outdoor unit 10 includes an outdoor heat exchanger 13 and an outdoor blower 14. The outdoor heat exchanger 13 and the outdoor fan 14 are housed in the outdoor unit 10. The indoor unit 20 includes a compressor 11, a six-way valve 12, a reheater 21, a cooler 22, a1 st expansion valve 23, an air passage 31, a blower 32, and a control device CD. The compressor 11, the six-way valve 12, the reheater 21, the cooler 22, the 1 st expansion valve 23, the blower 32, and the control device CD are housed in the indoor unit 20. The indoor unit 20 is provided with an air duct 31.

The compressor 11 is configured to compress a refrigerant. The compressor 11 is configured to compress and discharge the sucked refrigerant. The compressor 11 is configured to have a variable capacity, for example. The compressor 11 is configured to change the capacity by adjusting the rotation speed of the compressor 11 based on an instruction from the control device CD, for example.

The six-way valve 12 is configured to be switchable between a1 st switching state and a2 nd switching state. The six-way valve 12 is configured to switch between the 1 st switching state and the 2 nd switching state, for example, based on an instruction from the control device CD. The six-way valve 12 is configured to be switched in the 1 st switching state such that the refrigerant flows in the refrigerant circuit RC in the order of the compressor 11, the six-way valve 12, the outdoor heat exchanger 13, the six-way valve 12, the reheater 21, the 1 st expansion valve 23, the six-way valve 12, and the cooler 22. The six-way valve 12 is in the 1 st switching state during the cooling main operation.

The six-way valve 12 is configured to be switched in the 2 nd switching state such that the refrigerant flows in the refrigerant circuit RC in the order of the compressor 11, the six-way valve 12, the reheater 21, the 1 st expansion valve 23, the six-way valve 12, the outdoor heat exchanger 13, the six-way valve 12, and the cooler 22. The six-way valve 12 is set to the 2 nd switching state during the heating main operation.

The 6 connection ports (1 st connection port P1 to 6 th connection port P6) of the six-way valve 12 are connected to the 1 st pipe 1, 2 nd pipe 2,3 rd pipe 3,4 th pipe 4, 5 th pipe 5, and 6 th pipe 6, respectively. The 1 st connection port P1 is connected to the 2 nd pipe 2. The 2 nd connection port P2 is connected to the 6 th pipe 6. The 3 rd connection port P3 is connected to the 5 th pipe 5. The 4 th connection port P4 is connected to the 3 rd pipe 3. The 5 th connection port P5 is connected to the 4 th pipe 4. The 6 th connection port P6 is connected to the 1 st pipe 1.

In the 1 st switching state of the six-way valve 12, a refrigerant circuit RC is formed in which the refrigerant reaches the compressor 11 again through the compressor 11, the 1 st pipe 1, the six-way valve 12, the 2 nd pipe 2, the outdoor heat exchanger 13, the 3 rd pipe 3, the six-way valve 12, the 4 th pipe 4, the reheater 21, the 1 st expansion valve 23, the 5 th pipe 5, the six-way valve 12, the 6 th pipe 6, and the cooler 22. In the 1 st switching state of the six-way valve 12, the 1 st connection port P1 is connected to the 6 th connection port P6, the 2 nd connection port P2 is connected to the 3 rd connection port P3, and the 4 th connection port P4 is connected to the 5 th connection port P5.

In the 2 nd switching state of the six-way valve 12, a refrigerant circuit RC is formed in which the refrigerant reaches the compressor 11 again through the compressor 11, the 1 st pipe 1, the six-way valve 12, the 4 th pipe 4, the reheater 21, the 1 st expansion valve 23, the 5 th pipe 5, the six-way valve 12, the 3 rd pipe 3, the outdoor heat exchanger 13, the 2 nd pipe 2, the six-way valve 12, the 6 th pipe 6, and the cooler 22. In the 2 nd switching state of the six-way valve 12, the 1 st connection port P1 is connected to the 2 nd connection port P2. The 3 rd connection port P3 is connected to the 4 th connection port P4. The 5 th connection port P5 is connected to the 6 th connection port P6.

The outdoor heat exchanger 13 is configured to exchange heat between the refrigerant flowing inside the outdoor heat exchanger 13 and the air flowing outside the outdoor heat exchanger 13. The outdoor heat exchanger 13 is configured to function as a condenser for condensing the refrigerant during the cooling main operation. The outdoor heat exchanger 13 is configured to function as an evaporator that evaporates the refrigerant during the heating main operation. The outdoor heat exchanger 13 is, for example, a fin-and-tube heat exchanger having a plurality of fins and a heat transfer tube penetrating the plurality of fins.

The control device CD is configured to perform operations, instructions, and the like to control the respective devices and the like of the air conditioner 100. The control device CD is electrically connected to the compressor 11, the six-way valve 12, the 1 st expansion valve 23, the blower 32, and the like, and is configured to control the operations thereof.

The reheater 21 is configured to exchange heat between the refrigerant flowing inside the reheater 21 and the air flowing outside the reheater 21. The reheater 21 is configured to function as a condenser for condensing the refrigerant in the cooling main operation and the heating main operation. The reheater 21 is, for example, a fin-tube heat exchanger having a plurality of fins and a heat transfer tube penetrating the plurality of fins.

The cooler 22 is configured to exchange heat between the refrigerant flowing inside the cooler 22 and the air flowing outside the cooler 22. The cooler 22 is configured to function as an evaporator that evaporates the refrigerant during the cooling main operation and the heating main operation. The cooler 22 is, for example, a fin-tube heat exchanger having a plurality of fins and a heat transfer tube penetrating the plurality of fins.

The 1 st expansion valve 23 is configured to decompress the refrigerant condensed by the condenser by expanding the refrigerant. The 1 st expansion valve 23 is configured to decompress the refrigerant condensed by the reheater 21 in the cooling main operation and the heating main operation. The 1 st expansion valve 23 is, for example, an electromagnetic expansion valve. The 1 st expansion valve 23 is configured to change the amount of pressure reduction by adjusting the opening of the 1 st expansion valve 23 based on an instruction from the control device CD, for example.

The air duct 31 is provided in the casing of the indoor unit 20. The reheater 21 and the cooler 22 are disposed in the air duct 31. The blower 32 is configured to blow air to the reheater 21 and the cooler 22. The reheater 21 and the cooler 22 are arranged in the flow direction of the air blown by the blower 32. The reheater 21 is disposed downstream of the cooler 22 in the flow of the air blown by the blower 32. In the air passage 31, the cooler 22 is disposed upstream of the reheater 21.

The reheater 21 and the cooler 22 share the air passage 31 and the blower 32. The reheater 21 and the cooler 22 are configured such that the air blown by the blower 32 passes through the reheater 21 after passing through the cooler 22, both in the 1 st switching state and in the 2 nd switching state. The reheater 21 and the cooler 22 are configured such that, during operation of the blower 32, air passes through the reheater 21 after passing through the cooler 22, regardless of the 1 st switching state and the 2 nd switching state of the six-way valve 12.

The reheater 21 and the cooler 22 may be configured such that the flow of the refrigerant is opposite to the flow of the air. Both the reheater 21 and the cooler 22 have a heat transfer pipe flow path structure in which air and refrigerant flow in opposite directions. The reheater 21 and the cooler 22 have a heat transfer pipe on the upwind side and a heat transfer pipe on the downwind side, respectively. The heat transfer pipe on the windward side is connected with the heat transfer pipe on the leeward side. In the cooling main operation and the heating main operation, the refrigerant flows from the heat transfer pipe on the leeward side to the heat transfer pipe on the upwind side. In both the cooling main operation and the heating main operation, the refrigerant flowing through the heat transfer tubes of the reheater 21 and the cooler 22 and the air flowing through the outside of the heat transfer tubes are in opposite flows.

Next, the operation of the air conditioner 100 according to embodiment 1 will be described.

< Operation of Cooling body >

First, the cooling main operation of the air conditioner 100 according to embodiment 1 will be described with reference to fig. 1. The cooling main operation is an operation in which the cooling amount of air in the cooler 22 is larger than the heating amount of air in the reheater 21, and the outdoor heat exchanger 13 functions as a condenser, thereby radiating heat to the outside air as the remaining heat radiation amount of the heat pump. In the cooling main operation, the air passing through the reheater 21 has a lower temperature and a lower moisture content than the air before passing through the cooler 22.

In the cooling main operation, as shown by the solid line in fig. 1, the six-way valve 12 is switched to the 1 st switching state. The vapor refrigerant compressed to a high temperature and a high pressure in the compressor 11 flows out to the 1 st pipe 1, passes through the six-way valve 12, and flows into the outdoor heat exchanger 13 through the 2 nd pipe 2. The outdoor heat exchanger 13 functions as a condenser. The high-temperature and high-pressure vapor refrigerant radiates heat to the outdoor air introduced into the outdoor heat exchanger 13 by the outdoor blower 14. Thereby, the high-temperature and high-pressure vapor refrigerant is condensed to become a high-temperature and high-pressure gas-liquid two-phase refrigerant.

The high-temperature and high-pressure gas-liquid two-phase refrigerant flows out to the 3 rd pipe 3, passes through the six-way valve 12, and flows into the reheater 21 via the 4 th pipe 4. The reheater 21 functions as a condenser. The high-temperature and high-pressure gas-liquid two-phase refrigerant radiates heat to the air introduced into the reheater 21 by the blower 32. Thereby, the high-temperature and high-pressure gas-liquid two-phase refrigerant is condensed to become a high-pressure liquid refrigerant. The high-pressure liquid refrigerant flows into the 1 st expansion valve 23.

The high-pressure liquid refrigerant is expanded and decompressed by the 1 st expansion valve 23, and becomes a low-temperature low-pressure gas-liquid two-phase refrigerant. The low-temperature low-pressure gas-liquid two-phase refrigerant flows out to the 5 th pipe 5, passes through the six-way valve 12, and flows into the cooler 22 through the 6 th pipe 6. The cooler 22 functions as an evaporator. By absorbing heat from the air introduced into the cooler 22 by the blower 32, the low-temperature low-pressure gas-liquid two-phase refrigerant evaporates, thereby becoming a low-pressure vapor refrigerant. Thereafter, the low-pressure vapor refrigerant is sucked into the compressor 11. In the cooling main operation, the refrigerant is next circulated in the refrigerant circuit RC in the same manner.

The reheater 21 and the cooler 22 share the air passage 31 and the blower 32. The air guided in the air passage 31 by the blower 32 is first cooled and dehumidified by the cooler 22. This reduces the temperature of the air, and reduces the moisture content of the air. The air having passed through the cooler 22 is guided by the air duct 31, passes through the reheater 21, and is heated. Thereby, the temperature of the air rises. Since humidification is not generally performed in the reheater 21, the moisture content of the air does not change before and after passing through the reheater 21. The air having passed through the reheater 21 is guided by the duct 31 and blown out into the space to be air-conditioned.

The air is cooled and dehumidified by the cooler 22 and then heated by the reheater 21 as necessary, so that the amount of dehumidification of the air and the temperature of the air can be independently adjusted. Therefore, the air of the temperature and humidity set by the user can be supplied to the space to be air-conditioned.

< Operation of heating body >

Next, the heating main operation of the air conditioner 100 according to embodiment 1 will be described with reference to fig. 2. The heating main operation is an operation in which the heating amount of the air in the reheater 21 is larger than the cooling amount of the air in the cooler 22, and the outdoor heat exchanger 13 functions as an evaporator, thereby exhausting heat to the outside air as the remaining cooling heat amount of the heat pump. In the heating main operation, the air passing through the reheater 21 has a higher temperature and a lower moisture content than the air before passing through the cooler 22.

In the heating main operation, as shown by the solid line in fig. 2, the six-way valve 12 is switched to the 2 nd switching state. The vapor refrigerant compressed to a high temperature and a high pressure in the compressor 11 flows out to the 1 st pipe 1, passes through the six-way valve 12, and flows into the reheater 21 via the 4 th pipe 4. The reheater 21 functions as a condenser. The high-temperature and high-pressure vapor refrigerant radiates heat to the air introduced into the reheater 21 by the blower 32. Thereby, the high-temperature and high-pressure vapor refrigerant is condensed to become a high-pressure liquid refrigerant. The high-pressure liquid refrigerant flows into the 1 st expansion valve 23.

The high-pressure liquid refrigerant is expanded and decompressed by the 1 st expansion valve 23, and becomes a low-temperature low-pressure gas-liquid two-phase refrigerant. The low-temperature low-pressure gas-liquid two-phase refrigerant flows out to the 5 th pipe 5, passes through the six-way valve 12, and flows into the outdoor heat exchanger 13 via the 3 rd pipe 3. The outdoor heat exchanger 13 functions as an evaporator. By absorbing heat from the outdoor air introduced into the outdoor heat exchanger 13 by the outdoor blower 14, a part of the low-temperature low-pressure gas-liquid two-phase refrigerant evaporates. Thereafter, the low-temperature low-pressure gas-liquid two-phase refrigerant flows into the six-way valve 12 through the 2 nd pipe 2 and flows into the cooler 22 through the 6 th pipe 6.

The cooler 22 functions as an evaporator. By absorbing heat from the air introduced into the cooler 22 by the blower 32, the low-temperature low-pressure gas-liquid two-phase refrigerant evaporates, thereby becoming a low-pressure vapor refrigerant. The low-pressure vapor refrigerant is drawn into the compressor 11. In the heating main operation, the refrigerant is next circulated in the refrigerant circuit RC in the same manner.

The air guided in the air passage 31 by the blower 32 is cooled and dehumidified by the cooler 22, and then heated by the reheater 21, and blown out into the space to be air-conditioned, as in the cooling main operation. Therefore, the amount of dehumidification of the air and the temperature of the air can be independently adjusted, respectively. Therefore, the air of the temperature and humidity set by the user can be supplied to the space to be air-conditioned.

Next, the operational effects of the air conditioner 100 according to embodiment 1 will be described.

According to the air conditioner of embodiment 1, the six-way valve 12 is configured to be switched such that the refrigerant flows in the refrigerant circuit RC in the order of the reheater 21 and the cooler 22, both in the 1 st switching state and in the 2 nd switching state. The six-way valve 12 is set to the 1 st switching state during the cooling main operation and to the 2 nd switching state during the heating main operation. Therefore, the directions of the refrigerant flowing through the reheater 21 and the cooler 22 can be made the same in both the cooling main operation and the heating main operation. Therefore, the reheater 21 can heat the air cooled and dehumidified by the cooler 22, both during the cooling main operation and during the heating main operation. Therefore, the air of the temperature and humidity set by the user can be supplied to the space to be air-conditioned.

The reheater 21 and the cooler 22 are configured such that the air blown by the blower 32 passes through the reheater 21 after passing through the cooler 22, both in the 1 st switching state and in the 2 nd switching state. Therefore, in both the cooling main operation and the heating main operation, the air can be reheated after being cooled and dehumidified. Therefore, sufficient dehumidification can be performed in both the cooling main operation and the heating main operation.

In particular, since sufficient dehumidification can be performed during the heating main operation, the heating main operation can be used for drying and dehumidifying the air-conditioning target space. Therefore, the air conditioner 100 according to embodiment 1 can be used for drying food and materials.

In the cooling main operation, the refrigerant passing through the outdoor heat exchanger 13 flows to the reheater 21. In the heating main operation, the refrigerant passing through the outdoor heat exchanger 13 flows into the cooler 22. Therefore, by adjusting the effective heat transfer area of the outdoor heat exchanger 13, the heat exchange amount of the refrigerant is easily adjusted. In addition, by adjusting the rotation speed of the outdoor fan 14, the heat exchange amount of the refrigerant can be easily adjusted. Since the refrigerant whose heat (internal energy) has been adjusted in the outdoor heat exchanger 13 can be supplied to the reheater 21 or the cooler 22, the heat exchange amount in the reheater 21 or the cooler 22 can be continuously adjusted. Therefore, the operation of the air conditioner 100 in which the blowing temperature of the indoor unit 20 is stable can be realized.

According to the air conditioner of embodiment 1, in the 1 st switching state, the refrigerant circuit RC is configured such that the refrigerant flows in the order of the compressor 11, the 1 st pipe 1, the six-way valve 12, the 2 nd pipe 2, the outdoor heat exchanger 13, the 3 rd pipe 3, the six-way valve 12, the 4 th pipe 4, the reheater 21, the 5 th pipe 5, the 1 st expansion valve 23, the 5 th pipe 5, the six-way valve 12, the 6 th pipe 6, and the cooler 22. In the 2 nd switching state, the refrigerant circuit RC is configured such that the refrigerant flows in the order of the compressor 11, the 1 st pipe 1, the six-way valve 12, the 4 th pipe 4, the reheater 21, the 5 th pipe 5, the 1 st expansion valve 23, the 5 th pipe 5, the six-way valve 12, the 3 rd pipe 3, the outdoor heat exchanger 13, the 2 nd pipe 2, the six-way valve 12, the 6 th pipe 6, and the cooler 22. Therefore, the refrigerant can be caused to flow in the refrigerant circuit RC in the order of the reheater 21 and the cooler 22 in both the 1 st switching state and the 2 nd switching state.

According to the air conditioner 100 of embodiment 1, the refrigerant is a mixed refrigerant. Since a mixture of two or more refrigerants, i.e., a mixed refrigerant, is generally a non-azeotropic refrigerant, the temperature at the time of gas-liquid phase change is not constant. Thus, a temperature gradient is generated in the heat exchanger as the mixed refrigerant changes phase. Therefore, an optimal design of the heat exchanger is required. In the air conditioner 100 according to embodiment 1, since the reheater 21 and the cooler 22 can be specially designed, the air conditioner 100 with high performance can be realized even when the mixed refrigerant is used.

According to the air conditioner 100 of embodiment 1, the reheater 21 and the cooler 22 are configured such that the flow of the refrigerant is opposite to the flow of the air. Therefore, the temperature gradient in the heat exchanger of the mixed refrigerant can be used to reduce the heat exchange temperature difference between the air and the refrigerant. Therefore, high-performance operation of the air conditioner 100 can be achieved.

Since the temperature of the zeotropic refrigerant increases with the evaporation of the refrigerant, the temperature increase in the flow direction of the refrigerant and the temperature decrease in the flow direction of the air interact with each other by the structure in which the air and the refrigerant are caused to flow in the opposite direction in the cooler 22 functioning as an evaporator, and thus the heat exchange temperature difference between the air and the refrigerant can be reduced in the entire region of the cooler 22.

Further, since the temperature of the zeotropic refrigerant decreases with the condensation of the refrigerant, the temperature decrease in the flow direction of the refrigerant and the temperature increase in the flow direction of the air interact with each other by the structure in which the air and the refrigerant are caused to flow in the counter flow in the reheater 21 functioning as a condenser, and thus the heat exchange temperature difference between the air and the refrigerant can be reduced in the entire area of the reheater 21.

The position of the blower 32 is not limited to the upstream of the air passage 31 of the cooler 22 as shown in fig. 1 and 2. The blower 32 may be located between the cooler 22 and the reheater 21 in the air passage 31, or downstream of the air passage 31 of the reheater 21.

Referring to fig. 3 and 4, the six-way valve 12 may be configured to rotate. Fig. 3 is a schematic diagram of the 1 st switching state of the rotary six-way valve 12. Fig. 4 is a schematic diagram of the 2 nd switching state of the rotary six-way valve 12. The rotary six-way valve 12 includes a valve seat 12a and a valve body 12b configured to be rotatable with respect to the valve seat 12 a. By rotating the valve body 12b relative to the valve seat 12a, the flow path is switched between the 1 st switching state and the 2 nd switching state.

Referring to fig. 5 and 6, the six-way valve 12 may have a sliding type structure. Fig. 5 is a schematic diagram of the 1 st switching state of the sliding six-way valve 12. Fig. 6 is a schematic diagram of the 2 nd switching state of the sliding six-way valve 12. The sliding six-way valve 12 includes a valve seat 12a and a valve body 12b configured to be slidable with respect to the valve seat 12 a. By sliding the valve body 12b relative to the valve seat 12a, the flow path is switched between the 1 st switching state and the 2 nd switching state.

Embodiment 2.

The air conditioner 100 according to embodiment 2 has the same structure, operation, and effects as those of the air conditioner 100 according to embodiment 1 unless otherwise specified.

The configuration of the air conditioner 100 according to embodiment 2 will be described with reference to fig. 7. Fig. 7 is a refrigerant circuit diagram of the air conditioner 100 according to embodiment 2. The air conditioner 100 according to embodiment 2 has a structure in which the connection positions of the 5 th pipe 5 and the 6 th pipe 6 to the six-way valve 12 are exchanged as compared with the air conditioner 100 according to embodiment 1.

The 6 connection ports (1 st connection port P1 to 6 th connection port P6) of the six-way valve 12 are connected to the 1 st pipe 1,2 nd pipe 2,3 rd pipe 3,4 th pipe 4,5 th pipe 5, and 6 th pipe 6, respectively. The 1 st connection port P1 is connected to the 2 nd pipe 2. The 2 nd connection port P2 is connected to the 5 th pipe 5. The 3 rd connection port P3 is connected to the 6 th pipe 6. The 4 th connection port P4 is connected to the 3 rd pipe 3. The 5 th connection port P5 is connected to the 4 th pipe 4. The 6 th connection port P6 is connected to the 1 st pipe 1.

In the 1 st switching state, the refrigerant circuit RC is configured such that the refrigerant flows in the order of the compressor 11, the 1 st pipe 1, the six-way valve 12, the 2 nd pipe 2, the outdoor heat exchanger 13, the 3 rd pipe 3, the six-way valve 12, the 4 th pipe 4, the reheater 21, the 5 th pipe 5, the 1 st expansion valve 23, the 5 th pipe 5, the six-way valve 12, the 6 th pipe 6, and the cooler 22.

In the 2 nd switching state, the refrigerant circuit RC is configured such that the refrigerant flows in the order of the compressor 11, the 1 st pipe 1, the six-way valve 12, the 4 th pipe 4, the reheater 21, the 5 th pipe 5, the 1 st expansion valve 23, the 5 th pipe 5, the six-way valve 12, the 2 nd pipe 2, the outdoor heat exchanger 13, the 3 rd pipe 3, the six-way valve 12, the 6 th pipe 6, and the cooler 22.

Next, the operation of the air conditioner 100 according to embodiment 2 will be described with reference to fig. 7 and 8.

The operation of the air conditioner 100 according to embodiment 2 is basically the same as that of embodiment 1. Referring to fig. 7, in the cooling main operation of the air conditioner 100 according to embodiment 2, the refrigerant flows again to the compressor 11 through the compressor 11, the 1 st pipe 1, the six-way valve 12, the 2 nd pipe 2, the outdoor heat exchanger 13, the 3 rd pipe 3, the six-way valve 12, the 4 th pipe 4, the reheater 21, the 1 st expansion valve 23, the 5 th pipe 5, the six-way valve 12, the 6 th pipe 6, and the cooler 22 in the refrigerant circuit RC.

Referring to fig. 8, in the heating main operation of the air conditioner 100 according to embodiment 2, the refrigerant flows again to the compressor 11 through the compressor 11, the 1 st pipe 1, the six-way valve 12, the 4 th pipe 4, the reheater 21, the 1 st expansion valve 23, the 5 th pipe 5, the six-way valve 12, the 2 nd pipe 2, the outdoor heat exchanger 13, the 3 rd pipe 3, the six-way valve 12, the 6 th pipe 6, and the cooler 22 in the refrigerant circuit RC.

Next, the operational effects of the air conditioner 100 according to embodiment 2 will be described.

According to the air conditioner 100 of embodiment 2, in the 1 st switching state, the refrigerant circuit RC is configured such that the refrigerant flows in the order of the compressor 11, the 1 st pipe 1, the six-way valve 12, the 2 nd pipe 2, the outdoor heat exchanger 13, the 3 rd pipe 3, the six-way valve 12, the 4 th pipe 4, the reheater 21, the 5 th pipe 5, the 1 st expansion valve 23, the 5 th pipe 5, the six-way valve 12, the 6 th pipe 6, and the cooler 22. In the 2 nd switching state, the refrigerant circuit RC is configured such that the refrigerant flows in the order of the compressor 11, the 1 st pipe 1, the six-way valve 12, the 4 th pipe 4, the reheater 21, the 5 th pipe 5, the 1 st expansion valve 23, the 5 th pipe 5, the six-way valve 12, the 2 nd pipe 2, the outdoor heat exchanger 13, the 3 rd pipe 3, the six-way valve 12, the 6 th pipe 6, and the cooler 22. Therefore, the refrigerant can be caused to flow in the refrigerant circuit RC in the order of the reheater 21 and the cooler 22 in both the 1 st switching state and the 2 nd switching state.

In the air conditioner 100 according to embodiment 2, the air flow direction guided by the outdoor fan 14 to the outdoor heat exchanger 13 is the same in both the cooling main operation and the heating main operation. By making the flow direction of the refrigerant flowing through the outdoor heat exchanger 13 the same in both the 1 st switching state and the 2 nd switching state of the six-way valve 12, the heat exchange between the air in the outdoor heat exchanger 13 and the refrigerant can be made a counter flow system in both the cooling main operation and the heating main operation. Since the temperature of the air and the refrigerant changes with the heat exchange, by changing the heat exchange to the counter-flow method, the heat exchange temperature difference between the air and the refrigerant can be reduced in the entire area of the outdoor heat exchanger 13 as compared with the parallel flow heat exchange method. This can optimize the performance and power consumption of the air conditioner 100.

In particular, in recent years, for the purpose of reducing the influence on global warming when a refrigerant leaks from the air conditioner 100 and for the purpose of reducing the combustion speed of the refrigerant when the refrigerant leaks, a mixture of a refrigerant having high performance and a refrigerant having a small global warming coefficient or a refrigerant having a slow combustion speed has been proposed.

A mixture of two or more refrigerants, i.e., a mixed refrigerant, generally has non-azeotropic characteristics in which temperature changes occur during phase changes of evaporation and condensation. The heat exchange in the countercurrent mode in the outdoor heat exchanger 13 of embodiment 2 is particularly effective when a mixed refrigerant, which is a mixture of two or more types of refrigerant, is enclosed in the air conditioner 100.

Since the temperature of the non-azeotropic refrigerant decreases with the condensation of the refrigerant, the temperature decrease in the flow direction of the refrigerant and the temperature increase in the flow direction of the air interact with each other by making the air and the refrigerant flow in the opposite direction in the outdoor heat exchanger 13 functioning as a condenser during the cooling main operation. This makes it possible to reduce the difference in heat exchange temperature between the air and the refrigerant in the entire area of the outdoor heat exchanger 13.

Further, since the temperature of the non-azeotropic refrigerant increases with the evaporation of the refrigerant, the temperature increase in the flow direction of the refrigerant and the temperature decrease in the flow direction of the air interact with each other by making the air and the refrigerant flow in the opposite direction in the outdoor heat exchanger 13 functioning as an evaporator during the heating main operation. This makes it possible to reduce the difference in heat exchange temperature between the air and the refrigerant in the entire area of the outdoor heat exchanger 13.

Embodiment 3.

The air conditioner 100 of embodiment 3 has the same structure, operation, and effects as those of the air conditioner 100 of embodiment 1 unless otherwise specified.

The structure of the air conditioner 100 according to embodiment 3 will be described with reference to fig. 9. Fig. 9 is a refrigerant circuit diagram of the air conditioner 100 according to embodiment 3. The air conditioner 100 according to embodiment 3 differs from the air conditioner 100 according to embodiment 1 in that the liquid receiver 24 is provided.

In the air conditioner 100 according to embodiment 3, the refrigerant circuit RC has the receiver 24. The receiver 24 is disposed between the reheater 21 and the 1 st expansion valve 23 in the refrigerant circuit RC. The receiver 24 is configured to store a refrigerant.

Next, the operation of the air conditioner 100 according to embodiment 3 will be described with reference to fig. 9 and 10.

The operation of the air conditioner 100 according to embodiment 3 is basically the same as that of embodiment 1. Referring to fig. 9, in the cooling main operation of the air conditioner 100 according to embodiment 3, the refrigerant flows again to the compressor 11 through the compressor 11, the 1 st pipe 1, the six-way valve 12, the 2 nd pipe 2, the outdoor heat exchanger 13, the 3 rd pipe 3, the six-way valve 12, the 4 th pipe 4, the reheater 21, the receiver 24, the 1 st expansion valve 23, the 5 th pipe 5, the six-way valve 12, the 6 th pipe 6, and the cooler 22 in the refrigerant circuit RC.

Referring to fig. 10, in the heating main operation of the air conditioner 100 according to embodiment 3, the refrigerant flows again to the compressor 11 through the compressor 11, the 1 st pipe 1, the six-way valve 12, the 4 th pipe 4, the reheater 21, the receiver 24, the 1 st expansion valve 23, the 5 th pipe 5, the six-way valve 12, the 3 rd pipe 3, the outdoor heat exchanger 13, the 2 nd pipe 2, the six-way valve 12, the 6 th pipe 6, and the cooler 22 in the refrigerant circuit RC.

Next, the operational effects of the air conditioner 100 according to embodiment 3 will be described.

In the cooling main operation, when the heat radiation amount in the outdoor heat exchanger 13 decreases, the amount of liquid refrigerant that stagnates inside the outdoor heat exchanger 13 decreases. In the air conditioner 100 without the refrigerant amount adjustment mechanism, the filling amount of the refrigerant becomes excessively large with respect to the proper refrigerant amount for the operation, and thus there is a concern that the compressor discharge refrigerant temperature or the compressor discharge refrigerant pressure excessively increases to cause the operation failure.

In the air conditioner 100 according to embodiment 3, the receiver 24 is disposed between the reheater 21 and the 1 st expansion valve 23 in the refrigerant circuit RC. Thus, by adjusting the effective amount of refrigerant in the air conditioner 100, an appropriate operation point of the compressor 11 can be achieved.

In addition, for the purpose of preventing the refrigerant flow sound, it is preferable to supply the liquid refrigerant to the 1 st expansion valve 23. The receiver 24 is disposed upstream of the 1 st expansion valve 23 in the refrigerant flow, and thus the inlet refrigerant of the 1 st expansion valve 23 can be stably maintained in a liquid state.

Embodiment 4.

The air conditioner 100 of embodiment 4 has the same structure, operation, and effects as those of the air conditioner 100 of embodiment 3 unless otherwise specified.

The structure of the air conditioner 100 according to embodiment 4 will be described with reference to fig. 11. Fig. 11 is a refrigerant circuit diagram of the air conditioner 100 according to embodiment 4. The air conditioner 100 according to embodiment 4 differs from the air conditioner 100 according to embodiment 3 in that the air conditioner has the 2 nd expansion valve 25.

In the air conditioner 100 according to embodiment 4, the refrigerant circuit RC has the 2 nd expansion valve 25. The 2 nd expansion valve 25 is disposed between the reheater 21 and the receiver 24 in the refrigerant circuit RC. The 2 nd expansion valve 25 is configured to be adjustable in opening degree.

Next, the operation of the air conditioner 100 according to embodiment 4 will be described with reference to fig. 11 and 12.

The operation of the air conditioner 100 according to embodiment 4 is basically the same as that of embodiment 3. Referring to fig. 11, in the cooling main operation of the air conditioner 100 according to embodiment 4, the refrigerant flows again to the compressor 11 through the compressor 11, the 1 st pipe 1, the six-way valve 12, the 2 nd pipe 2, the outdoor heat exchanger 13, the 3 rd pipe 3, the six-way valve 12, the 4 th pipe 4, the reheater 21, the 2 nd expansion valve 25, the receiver 24, the 1 st expansion valve 23, the 5 th pipe 5, the six-way valve 12, the 6 th pipe 6, and the cooler 22 in the refrigerant circuit RC.

Referring to fig. 12, in the heating main operation of the air conditioner 100 according to embodiment 4, the refrigerant flows again to the compressor 11 through the compressor 11, the 1 st pipe 1, the six-way valve 12, the 4 th pipe 4, the reheater 21, the 2 nd expansion valve 25, the receiver 24, the 1 st expansion valve 23, the 5 th pipe 5, the six-way valve 12, the 3 rd pipe 3, the outdoor heat exchanger 13, the 2 nd pipe 2, the six-way valve 12, the 6 th pipe 6, and the cooler 22 in the refrigerant circuit RC.

Next, the operational effects of the air conditioner 100 according to embodiment 4 will be described.

According to the air conditioner 100 of embodiment 4, the 2 nd expansion valve 25 is disposed between the reheater 21 and the receiver 24 in the refrigerant circuit RC. By adjusting the opening degree of the 2 nd expansion valve 25, the refrigerant pressure inside the receiver 24 can be adjusted. As a result, the amount of liquid refrigerant stored in the liquid receiver 24 can be actively adjusted as compared with embodiment 3. Therefore, the air conditioner 100 can be operated more stably.

In embodiments 1 to 4, for the purpose of stably supplying the liquid refrigerant to the 1 st expansion valve 23 or the 2 nd expansion valve 25, it is preferable that the refrigerant inlet of the reheater 21 is located above the refrigerant outlet in the gravitational direction. That is, the reheater 21 has a refrigerant inflow port and a refrigerant outflow port. The refrigerant inflow port of the reheater 21 is located above the refrigerant outflow port in the gravitational direction.

In this configuration, since the liquid refrigerant retained in the reheater 21 is sequentially discharged by gravity, the inlet refrigerant in the 1 st expansion valve 23 or the 2 nd expansion valve 25 can be kept in a liquid state. Therefore, the air conditioner 100 can be operated stably.

Embodiment 5.

The air conditioner 100 according to embodiment 5 has the same structure, operation, and effects as those of the air conditioner 100 according to embodiment 2 unless otherwise specified.

The structure of the air conditioner 100 according to embodiment 5 will be described with reference to fig. 13. Fig. 13 is a refrigerant circuit diagram of the air conditioner 100 according to embodiment 5. The air conditioner 100 according to embodiment 5 is different from the air conditioner 100 according to embodiment 2 in the outdoor heat exchanger 13.

The refrigerant circuit RC has a1 st refrigerant shut-off mechanism 15 and a 2 nd refrigerant shut-off mechanism 16. The 1 st refrigerant closing mechanism 15 and the 2 nd refrigerant closing mechanism 16 are, for example, solenoid valves.

The outdoor heat exchanger 13 has a1 st heat exchange portion 13a and a2 nd heat exchange portion 13b. The 1 st heat exchanging portion 13a and the 2 nd heat exchanging portion 13b are arranged in parallel with each other in the refrigerant circuit RC. The 1 st heat exchange portion 13a has a larger inner volume than the 2 nd heat exchange portion 13b. The 1 st refrigerant closing mechanism 15 is connected to the inlet of the 1 st heat exchanging portion 13 a. The 2 nd refrigerant shut-off mechanism 16 is connected to the outlet of the 1 st heat exchange portion 13 a.

In addition, the refrigerant circuit RC has a bypass circuit 17. The bypass circuit 17 includes a bypass pipe 17a and a flow rate adjustment mechanism 17b. The bypass pipe 17a is connected to the 2 nd pipe 2 and the 3 rd pipe 3. The flow rate adjustment mechanism 17b is configured to be able to adjust the opening degree. The flow rate adjustment mechanism 17b is configured to be able to adjust the flow rate of the refrigerant flowing through the bypass circuit 17. The flow rate adjustment mechanism 17b is, for example, a solenoid valve. The bypass circuit 17 is disposed in parallel with the outdoor heat exchanger 13 in the refrigerant circuit RC. The bypass circuit 17 is disposed between the six-way valve 12 and the outdoor heat exchanger 13 in the refrigerant circuit RC.

The operation of the air conditioner 100 according to embodiment 5 is basically the same as that of embodiment 1. Referring to fig. 13, in the cooling main operation of the air conditioner 100 according to embodiment 5, the refrigerant flows again to the compressor 11 through the compressor 11, the 1 st pipe 1, the six-way valve 12, the 2 nd pipe 2, the outdoor heat exchanger 13, the bypass circuit 17, the 3 rd pipe 3, the six-way valve 12, the 4 th pipe 4, the reheater 21, the 1 st expansion valve 23, the 5 th pipe 5, the six-way valve 12, the 6 th pipe 6, and the cooler 22 in the refrigerant circuit RC.

Referring to fig. 14, in the heating main operation of the air conditioner 100 according to embodiment 5, the refrigerant flows again to the compressor 11 through the compressor 11, the 1 st pipe 1, the six-way valve 12, the 4 th pipe 4, the reheater 21, the 1 st expansion valve 23, the 5 th pipe 5, the six-way valve 12, the 2 nd pipe 2, the outdoor heat exchanger 13, the bypass circuit 17, the 3 rd pipe 3, the six-way valve 12, the 6 th pipe 6, and the cooler 22 in the refrigerant circuit RC.

Next, the operational effects of the air conditioner 100 according to embodiment 5 will be described.

The heat radiation amount of the condensation heat and the heat receiving amount of the evaporation heat in the outdoor heat exchanger 13 can be adjusted by decreasing the rotation speed of the outdoor blower 14, thereby decreasing the amount of the outdoor air introduced to the outdoor heat exchanger 13. Further, the 1 st heat exchange portion 13a and the 2 nd heat exchange portion 13b of the outdoor heat exchanger 13 are arranged in parallel with each other in the refrigerant circuit RC. As a result, the refrigerant flow in a part of the outdoor heat exchanger 13 is blocked, and thereby the heat exchange amount in the outdoor heat exchanger 13 can be further suppressed. Therefore, the stable adjustment range of the heat exchange amount in the reheater 21 and the cooler 22 can be increased.

Further, by allowing the refrigerant to flow through the bypass circuit 17 and not allowing the refrigerant to flow through the outdoor heat exchanger 13, the heat exchange amount in the outdoor heat exchanger 13 can be finely adjusted. This can increase the amount of heat exchange in the reheater 21 during the cooling main operation. In addition, the amount of heat exchange in the cooler 22 can be increased during the heating main operation. Accordingly, the adjustment range of the outlet air temperature and the outlet air humidity of the air conditioner 100 can be widened.

Embodiment 6.

The air conditioner 100 of embodiment 6 has the same structure, operation, and effects as those of the air conditioner 100 of embodiment 5 unless otherwise specified.

The configuration of the air conditioner 100 according to embodiment 6 will be described with reference to fig. 15. Fig. 15 is a refrigerant circuit diagram of the air conditioner 100 according to embodiment 6. The air conditioner 100 according to embodiment 6 is different from the air conditioner 100 according to embodiment 5 in the refrigerant closing mechanism 16 of the 2 nd embodiment. The 2 nd refrigerant closing mechanism 16 is a check valve.

Referring to fig. 15 and 16, the operation of air conditioner 100 according to embodiment 6 is basically the same as that of embodiment 5.

Next, the operational effects of the air conditioner 100 according to embodiment 6 will be described.

According to the air conditioner 100 of embodiment 6, the 2 nd refrigerant closing mechanism 16 is a check valve. In both the cooling main operation and the heating main operation, the refrigerant flow direction in the outdoor heat exchanger 13 is the same, and therefore, a check valve can be used as the 2 nd refrigerant closing means 16. The check valve is inexpensive and small compared to the solenoid valve, and thus can shut off the refrigerant in a cost-effective and space-saving manner.

Embodiment 7.

The air conditioner 100 according to embodiment 7 has the same structure, operation, and effects as those of the air conditioner 100 according to embodiment 1 unless otherwise specified.

The configuration of the reheater 21 and the cooler 22 according to embodiment 7 will be described with reference to fig. 17. Fig. 17 is a perspective view of the reheater 21 and the cooler 22 according to embodiment 7.

The reheater 21 has a smaller internal volume than the cooler 22. The reheater 21 has a1 st heat transfer pipe T1. The cooler 22 has a 2 nd heat transfer pipe T2. For example, the 1 st heat transfer tube T1 may have an inner diameter equal to the inner diameter of the 2 nd heat transfer tube T2, and the 1 st heat transfer tube T1 may have a length shorter than the 2 nd heat transfer tube T2.

The reheater 21 has a plurality of 1 st fins F1. The cooler 22 has a plurality of 2 nd fins F2. The 1 st fin F1 has a smaller surface area total value than the 2 nd fin F2. For example, the 1 st fin F1 may have a shorter length than the 2 nd fin F2, and the number of 1 st fins F1 may be smaller than the number of 2 nd fins F2.

Next, the operational effects of the air conditioner 100 according to embodiment 7 will be described.

According to the air conditioner 100 of embodiment 7, the reheater 21 has a smaller internal volume than the cooler 22. The air once cooled by the cooler 22 is reheated by the reheater 21, and therefore, the temperature difference between the refrigerant and the air in the reheater 21 is larger than the temperature difference between the refrigerant and the air in the cooler 22. Therefore, even if the reheater 21 is designed to be compact so as to be smaller than the cooler 22 and to have a smaller internal volume, the reheater 21 can exhibit a required heat radiation capability for a target blowout air temperature set in advance.

Further, by designing the inner volume of the reheater 21 to be small, the amount of change in the amount of liquid refrigerant stored in the reheater 21 due to adjustment of the amount of heat exchange in the reheater 21 can be reduced. Therefore, an excessive increase in the compressor discharge refrigerant temperature and the compressor discharge refrigerant pressure can be suppressed. In addition, when the liquid receiver 24 is provided, the adjustment capacity can be reduced, and therefore, the liquid receiver 24 can be miniaturized.

According to the air conditioner 100 of embodiment 7, the plurality of 1 st fins F1 have a smaller surface area total value than the plurality of 2 nd fins F2. In the case of miniaturizing the reheater 21, the total surface area of the 1 st fin F1 of the reheater 21 in contact with air is designed to be smaller than the total surface area of the 2 nd fin F2 of the cooler 22 in contact with air, so that the reheater 21 and the air conditioner 100 can be configured inexpensively and in a small size.

In addition, when the reheater 21 and the cooler 22 are disposed in the air duct 31, the reheater 21 is designed to be small and the cooler 22 is designed to be large, so that a configuration that exhibits optimal performance in terms of size constraints in the design of the air conditioner 100 can be realized.

The presently disclosed embodiments are considered in all respects to be illustrative and not restrictive. The scope of the present disclosure is indicated by the claims rather than by the foregoing description, and all changes that come within the meaning and range of equivalency of the claims are intended to be embraced therein.

Description of the reference numerals

1 St pipe, 2 nd pipe, 3 rd pipe, 4 th pipe, 5 th pipe, 6 th pipe, 10 th pipe, 11 th pipe, 12 th pipe, 13a st heat exchange portion, 13b st heat exchange portion, 14 nd pipe, 15 st refrigerant closing mechanism, 16 st refrigerant closing mechanism, 17 nd pipe, 17a bypass pipe, 17b flow regulating mechanism, 20 th pipe, 21 st pipe, reheater, 22 nd pipe, 23 st pipe, 1 st expansion valve, 24 th pipe, 25 th pipe, 2 nd expansion valve, 31 st pipe, 32 nd pipe, 100 nd pipe, F1 st pipe, F2 nd pipe, T1 st heat transfer pipe, T2 nd heat transfer pipe, RC: refrigerant circuit.

Claims (12)

1. An air conditioner comprising: a refrigerant circuit including a compressor, a six-way valve, an outdoor heat exchanger, a reheater, a first expansion valve, and a cooler, and configured to circulate a refrigerant; and a blower configured to blow air toward the reheater and the cooler, The six-way valve is configured to be switchable between a first switching state and a second switching state. The six-way valve is constructed as follows: In the first switching state, the refrigerant is switched so that the refrigerant flows in the refrigerant circuit in the order of the compressor, the six-way valve, the outdoor heat exchanger, the six-way valve, the reheater, the first expansion valve, the six-way valve, and the cooler, and In the second switching state, the refrigerant is switched so that the refrigerant flows in the refrigerant circuit in the order of the compressor, the six-way valve, the reheater, the first expansion valve, the six-way valve, the outdoor heat exchanger, the six-way valve, and the cooler. The reheater and the cooler are configured such that the air blown by the blower passes through the reheater after passing through the cooler regardless of whether in the first switching state or the second switching state. 2. The air conditioner according to claim 1, wherein: The refrigerant circuit comprises: a first pipe connecting the compressor and the six-way valve; a second pipe connecting the six-way valve and the outdoor heat exchanger; a third pipe connecting the outdoor heat exchanger and the six-way valve; a fourth pipe connecting the six-way valve and the reheater; a fifth pipe connecting the reheater and the six-way valve via the first expansion valve; and a sixth pipe connecting the six-way valve and the cooler, In the first switching state, the refrigerant circuit is configured so that the refrigerant flows in the order of the compressor, the first pipe, the six-way valve, the second pipe, the outdoor heat exchanger, the third pipe, the six-way valve, the fourth pipe, the reheater, the fifth pipe, the first expansion valve, the fifth pipe, the six-way valve, the sixth pipe, and the cooler. In the second switching state, the refrigerant circuit is constructed so that the refrigerant flows in the order of the compressor, the first pipe, the six-way valve, the fourth pipe, the reheater, the fifth pipe, the first expansion valve, the fifth pipe, the six-way valve, the third pipe, the outdoor heat exchanger, the second pipe, the six-way valve, the sixth pipe, and the cooler. 3. The air conditioner according to claim 1, wherein: The refrigerant circuit comprises: a first pipe connecting the compressor and the six-way valve; a second pipe connecting the six-way valve and the outdoor heat exchanger; a third pipe connecting the outdoor heat exchanger and the six-way valve; a fourth pipe connecting the six-way valve and the reheater; a fifth pipe connecting the reheater and the six-way valve via the first expansion valve; and a sixth pipe connecting the six-way valve and the cooler, In the first switching state, the refrigerant circuit is configured so that the refrigerant flows in the order of the compressor, the first pipe, the six-way valve, the second pipe, the outdoor heat exchanger, the third pipe, the six-way valve, the fourth pipe, the reheater, the fifth pipe, the first expansion valve, the fifth pipe, the six-way valve, the sixth pipe, and the cooler. In the second switching state, the refrigerant circuit is constructed so that the refrigerant flows in the order of the compressor, the first pipe, the six-way valve, the fourth pipe, the reheater, the fifth pipe, the first expansion valve, the fifth pipe, the six-way valve, the second pipe, the outdoor heat exchanger, the third pipe, the six-way valve, the sixth pipe, and the cooler. 4. The air conditioner according to any one of claims 1 to 3, wherein: The refrigerant is a mixed refrigerant. 5. The air conditioner according to any one of claims 1 to 4, wherein: The refrigerant circuit has a liquid receiver. The liquid receiver is disposed between the reheater and the first expansion valve in the refrigerant circuit. 6. The air conditioner according to claim 5, wherein: The refrigerant circuit has a second expansion valve. The second expansion valve is disposed between the reheater and the liquid receiver in the refrigerant circuit. 7. The air conditioner according to any one of claims 1 to 6, wherein: The reheater has a refrigerant inlet and a refrigerant outlet. The refrigerant inlet is located above the refrigerant outlet in the gravity direction. 8. The air conditioner according to any one of claims 1 to 7, wherein: The refrigerant circuit has a first refrigerant closing mechanism and a second refrigerant closing mechanism, The outdoor heat exchanger includes a first heat exchange portion and a second heat exchange portion. The first heat exchange part and the second heat exchange part are arranged in parallel with each other in the refrigerant circuit, and the first heat exchange part has a larger internal volume than the second heat exchange part. The first refrigerant closing mechanism is connected to the inlet of the first heat exchange part. The second refrigerant closing mechanism is connected to an outlet of the first heat exchange portion. 9. The air conditioner according to claim 8, wherein: The refrigerant circuit has a bypass circuit. The bypass circuit is arranged in parallel with the outdoor heat exchanger in the refrigerant circuit. 10. The air conditioner according to claim 8, wherein: The second refrigerant closing mechanism is a check valve. 11. The air conditioner according to any one of claims 1 to 10, wherein: The reheater has a smaller internal volume than the cooler. 12. The air conditioner according to any one of claims 1 to 11, wherein: The reheater has a plurality of first fins, The cooler has a plurality of second fins, The plurality of first fins have a smaller total surface area than the plurality of second fins.