air conditioner

Abstract

This air conditioner (100) comprises a refrigerant circuit (RC) and a blower (32). A refrigerant flow path switching mechanism (RF) is configured to switch the refrigerant circuit (RC) such that refrigerant flows in order through a reheater (21), a first expansion valve (23), and a cooler (22) in a first switching state. The refrigerant flow path switching mechanism (RF) is configured to switch the refrigerant circuit (RC) such that the refrigerant flows in order through the reheater (21), the first expansion valve (23), and the cooler (22) in a second switching state. The reheater (21) and the cooler (22) are configured such that in both the first switching state and the second switching state, air blown by the blower (32) passes through the cooler (22) and then through the reheater (21).

Description

[Technical Field]

[0001] The present disclosure relates to an air conditioner. [Background technology]

[0002] An air conditioner is known that includes an outdoor unit with an outdoor heat exchanger that functions as a condenser, an indoor unit with a first indoor heat exchanger that functions as a cooler and a second indoor heat exchanger that functions as a reheater, and a compressor that circulates refrigerant through the outdoor heat exchanger, the first indoor heat exchanger, and the second indoor heat exchanger. In this air conditioner, air cooled and dehumidified by the first indoor heat exchanger is heated by the second indoor heat exchanger, thereby individually adjusting the temperature and humidity of the air blown out from the indoor unit into the space to be air-conditioned. Such an air conditioner is described, for example, in Japanese Patent Laid-Open Publication No. 2002-89998 (Patent Document 1). [Prior art documents] [Patent documents]

[0003] [Patent Document 1] Japanese Patent Application Laid-Open No. 2002-89998 Summary of the Invention [Problem to be solved by the invention]

[0004] However, the air conditioner described in the publication uses only one four-way valve as a refrigerant flow switching mechanism. Therefore, when cooling-dominated operation and heating-dominated operation are performed corresponding to the two switching states of the four-way valve, the direction of refrigerant flow through the indoor unit is reversed between cooling-dominated operation and heating-dominated operation. Therefore, the indoor heat exchanger functioning as a cooler and the indoor heat exchanger functioning as a reheater are interchanged between cooling-dominated operation and heating-dominated operation. As a result, in either cooling-dominated operation or heating-dominated operation, air heated by the reheater is cooled by the cooler, resulting in insufficient dehumidification.

[0005] The present disclosure has been made in consideration of the above-mentioned problems, and its purpose is to provide an air conditioner in which the direction of refrigerant flowing through the reheater and the cooler can be the same in both cooling-dominated operation and heating-dominated operation. [Means for solving the problem]

[0006] The air conditioner of the present disclosure includes a refrigerant circuit and a blower. The refrigerant circuit has a compressor, a six-way valve, an outdoor heat exchanger, a reheater, a first expansion valve, and a cooler, and is configured to circulate a refrigerant. The blower is configured to be able to blow air to the reheater and the cooler. The six-way valve is configured to be switchable between a first switching state and a second switching state. In the first switching state, the six-way valve is configured to switch the refrigerant circuit so that the refrigerant flows in the following order: compressor, six-way valve, outdoor heat exchanger, six-way valve, reheater, first expansion valve, six-way valve, and cooler. In the second switching state, the six-way valve is configured to switch the refrigerant circuit so that the refrigerant flows in the following order: compressor, six-way valve, reheater, first expansion valve, six-way valve, outdoor heat exchanger, six-way valve, and cooler. The reheater and the cooler are configured so that, in both the first switching state and the second switching state, the air blown by the blower passes through the cooler and then passes through the reheater. [Effects of the Invention]

[0007] In the air conditioner of the present disclosure, the refrigerant flow switching mechanism is configured to switch the refrigerant circuit so that the refrigerant flows through the reheater and then the cooler in either the first switching state or the second switching state, thereby making it possible to maintain the same direction of refrigerant flow through the reheater and the cooler in both cooling-dominated operation and heating-dominated operation. [Brief explanation of the drawings]

[0008] [Figure 1] FIG. 1 is a refrigerant circuit diagram of a cooling-dominated operation of an air conditioner according to Embodiment 1. [Figure 2] FIG. 1 is a refrigerant circuit diagram of a heating-dominated operation of an air conditioner according to Embodiment 1. [Figure 3]3 is a schematic diagram of a first switching state of a rotary six-way valve of the air conditioner according to the first embodiment. FIG. [Figure 4] 4 is a schematic diagram of a second switching state of the rotary six-way valve of the air conditioner according to the first embodiment. FIG. [Figure 5] 3 is a schematic diagram showing a first switching state of the sliding six-way valve of the air conditioner according to the first embodiment. FIG. [Figure 6] 4 is a schematic diagram showing a second switching state of the sliding six-way valve of the air conditioner according to the first embodiment. FIG. [Figure 7] FIG. 10 is a refrigerant circuit diagram of the air conditioner according to the second embodiment in cooling-dominated operation. [Figure 8] FIG. 10 is a refrigerant circuit diagram of a heating-dominated operation of an air conditioner according to a second embodiment. [Figure 9] FIG. 10 is a refrigerant circuit diagram of the air conditioner according to the third embodiment in cooling-dominated operation. [Figure 10] FIG. 10 is a refrigerant circuit diagram of a heating-dominated operation of an air conditioner according to a third embodiment. [Figure 11] FIG. 10 is a refrigerant circuit diagram of a cooling-dominated operation of an air conditioner according to a fourth embodiment. [Figure 12] FIG. 10 is a refrigerant circuit diagram of a heating-dominated operation of an air conditioner according to a fourth embodiment. [Figure 13] FIG. 10 is a refrigerant circuit diagram of the air conditioner according to the fifth embodiment in cooling-dominated operation. [Figure 14] FIG. 11 is a refrigerant circuit diagram of a heating-dominated operation of an air conditioner according to a fifth embodiment. [Figure 15] FIG. 13 is a refrigerant circuit diagram of the air conditioner according to the sixth embodiment in cooling-dominated operation. [Figure 16] FIG. 13 is a refrigerant circuit diagram of a heating-dominated operation of an air conditioner according to a sixth embodiment. [Figure 17] FIG. 13 is a perspective view of a reheater and a cooler of an air conditioner according to a seventh embodiment. DETAILED DESCRIPTION OF THE INVENTION

[0009] Hereinafter, embodiments will be described with reference to the drawings. In the following, the same or corresponding parts will be denoted by the same reference characters and description thereof will not be repeated.

[0010] Embodiment 1 The configuration of an air conditioner 100 according to the first embodiment will be described with reference to FIG.

[0011] <Device configuration> Fig. 1 is a refrigerant circuit diagram of an air conditioner 100 pertaining 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 a first pipe 1, a second pipe 2, a third pipe 3, a fourth pipe 4, a fifth pipe 5, a sixth pipe 6, a compressor 11, a six-way valve 12, an outdoor heat exchanger 13, a reheater 21, a cooler 22, and a first expansion valve 23.

[0012] In the refrigerant circuit RC, a compressor 11, a six-way valve 12, an outdoor heat exchanger 13, a reheater 21, a cooler 22, and a first expansion valve 23 are connected by a first pipe 1, a second pipe 2, a third pipe 3, a fourth pipe 4, a fifth pipe 5, and a sixth pipe 6.

[0013] The first pipe 1 connects the compressor 11 and the six-way valve 12. The second pipe 2 connects the six-way valve 12 and the outdoor heat exchanger 13. The third pipe 3 connects the outdoor heat exchanger 13 and the six-way valve 12. The fourth pipe 4 connects the six-way valve 12 and the reheater 21. The fifth pipe 5 connects the reheater 21 and the six-way valve 12 via a first expansion valve 23. The sixth pipe 6 connects the six-way valve 12 and the cooler 22.

[0014] In the first switching state, the refrigerant circuit RC is configured so that the refrigerant flows in the following order: compressor 11, first pipe 1, six-way valve 12, second pipe 2, outdoor heat exchanger 13, third pipe 3, six-way valve 12, fourth pipe 4, reheater 21, fifth pipe 5, first expansion valve 23, fifth pipe 5, six-way valve 12, sixth pipe 6, and cooler 22.

[0015] In the second switching state, the refrigerant circuit RC is configured so that the refrigerant flows in the following order: compressor 11, first pipe 1, six-way valve 12, fourth pipe 4, reheater 21, fifth pipe 5, first expansion valve 23, fifth pipe 5, six-way valve 12, third pipe 3, outdoor heat exchanger 13, second pipe 2, six-way valve 12, sixth pipe 6, and cooler 22.

[0016] 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 types of refrigerants. However, the refrigerant may be a single refrigerant.

[0017] 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 a second pipe 2 and a third 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 blower 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, a first 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 first 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 passage 31.

[0018] The compressor 11 is configured to compress the refrigerant. The compressor 11 is configured to compress the refrigerant that it draws in and then discharge the refrigerant. The compressor 11 is configured, for example, to have a variable capacity. The compressor 11 is configured, for example, to change its capacity by adjusting the rotation speed of the compressor 11 based on an instruction from the control device CD.

[0019] The six-way valve 12 is configured to be switchable between a first switching state and a second switching state. The six-way valve 12 is configured to be switchable between the first switching state and the second switching state based on, for example, an instruction from the control device CD. In the first switching state, the six-way valve 12 is configured to switch so that the refrigerant flows through the refrigerant circuit RC in the following order: compressor 11, six-way valve 12, outdoor heat exchanger 13, six-way valve 12, reheater 21, first expansion valve 23, six-way valve 12, and cooler 22. The six-way valve 12 is in the first switching state during cooling-dominated operation.

[0020] In the second switching state, the six-way valve 12 is configured to switch the refrigerant circuit RC so that the refrigerant flows in the order of the compressor 11, the six-way valve 12, the reheater 21, the first 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 in the second switching state during heating-dominated operation.

[0021] The six connection ports (first connection port P1 to sixth connection port P6) of the six-way valve 12 are connected to the first pipe 1, the second pipe 2, the third pipe 3, the fourth pipe 4, the fifth pipe 5, and the sixth pipe 6, respectively. The first connection port P1 is connected to the second pipe 2. The second connection port P2 is connected to the sixth pipe 6. The third connection port P3 is connected to the fifth pipe 5. The fourth connection port P4 is connected to the third pipe 3. The fifth connection port P5 is connected to the fourth pipe 4. The sixth connection port P6 is connected to the first pipe 1.

[0022] In the first switching state of the six-way valve 12, a refrigerant circuit RC is formed that passes through the compressor 11, the first pipe 1, the six-way valve 12, the second pipe 2, the outdoor heat exchanger 13, the third pipe 3, the six-way valve 12, the fourth pipe 4, the reheater 21, the first expansion valve 23, the fifth pipe 5, the six-way valve 12, the sixth pipe 6, and the cooler 22, and then returns to the compressor 11. In the first switching state of the six-way valve 12, the sixth connection port P6 is connected to the first connection port P1, the third connection port P3 is connected to the second connection port P2, and the fifth connection port P5 is connected to the fourth connection port P4.

[0023] In the second switching state of the six-way valve 12, a refrigerant circuit RC is formed that passes through the compressor 11, the first pipe 1, the six-way valve 12, the fourth pipe 4, the reheater 21, the first expansion valve 23, the fifth pipe 5, the six-way valve 12, the third pipe 3, the outdoor heat exchanger 13, the second pipe 2, the six-way valve 12, the sixth pipe 6, and the cooler 22, and then returns to the compressor 11. In the second switching state of the six-way valve 12, the second connection port P2 is connected to the first connection port P1. The fourth connection port P4 is connected to the third connection port P3. The sixth connection port P6 is connected to the fifth connection port P5.

[0024] 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 that condenses the refrigerant in cooling-dominated operation. The outdoor heat exchanger 13 is configured to function as an evaporator that evaporates the refrigerant in heating-dominated 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 that passes through the plurality of fins.

[0025] The control device CD is configured to perform calculations, instructions, etc. to control each device, etc. of the air conditioner 100. The control device CD is electrically connected to the compressor 11, the six-way valve 12, the first expansion valve 23, the blower 32, etc., and is configured to control the operation of these devices.

[0026] 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 that condenses the refrigerant in cooling-dominated operation and heating-dominated operation. The reheater 21 is, for example, a fin-and-tube heat exchanger having a plurality of fins and heat transfer tubes that pass through the plurality of fins.

[0027] 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 in cooling-dominated operation and heating-dominated operation. The cooler 22 is, for example, a fin-and-tube heat exchanger having a plurality of fins and a heat transfer tube that passes through the plurality of fins.

[0028] The first expansion valve 23 is configured to reduce the pressure of the refrigerant condensed in the condenser by expanding it. The first expansion valve 23 is configured to reduce the pressure of the refrigerant condensed by the reheater 21 in cooling-dominated operation and heating-dominated operation. The first expansion valve 23 is, for example, an electromagnetic expansion valve. The first expansion valve 23 is configured to change the amount of pressure reduction by adjusting the opening degree of the first expansion valve 23 based on an instruction from the control device CD, for example.

[0029] Air passage 31 is provided in the housing of indoor unit 20. Reheater 21 and cooler 22 are arranged in air passage 31. Fan 32 is configured to be able to blow air to reheater 21 and cooler 22. Reheater 21 and cooler 22 are arranged side by side in the direction of the flow of air blown by fan 32. Reheater 21 is arranged downwind of cooler 22 in the flow of air blown by fan 32. In air passage 31, cooler 22 is arranged upstream of reheater 21.

[0030] 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 so that, in either the first switching state or the second switching state, the air blown by the blower 32 passes through the cooler 22 and then passes through the reheater 21. The reheater 21 and the cooler 22 are configured so that, while the blower 32 is operating, the air passes through the cooler 22 and then passes through the reheater 21, regardless of whether the six-way valve 12 is in the first switching state or the second switching state.

[0031] The reheater 21 and the cooler 22 may be configured so that the refrigerant flows countercurrently to the air flow. Both the reheater 21 and the cooler 22 have a heat transfer tube flow path configuration in which the air and the refrigerant flow countercurrently. The reheater 21 and the cooler 22 each have an upwind heat transfer tube and a downwind heat transfer tube. The upwind heat transfer tube is connected to the downwind heat transfer tube. In cooling-dominated operation and heating-dominated operation, the refrigerant flows from the downwind heat transfer tube to the upwind heat transfer tube. In both cooling-dominated operation and heating-dominated operation, the refrigerant flowing inside the heat transfer tubes of the reheater 21 and the cooler 22 flows countercurrently to the air flowing outside the heat transfer tubes.

[0032] Next, the operation of the air conditioner 100 according to the first embodiment will be described. <Cooling-based operation> First, the cooling-dominated operation of the air conditioner 100 according to the first embodiment will be described with reference to Fig. 1. Cooling-dominated operation is an operation in which the amount of air cooled in the cooler 22 is greater than the amount of air heated in the reheater 21, and the outdoor heat exchanger 13 functions as a condenser, so that surplus heat released by the heat pump is released to the outside air. In cooling-dominated operation, the air that has passed through the reheater 21 has a lower temperature and a lower moisture content than the air before passing through the cooler 22.

[0033] In cooling-dominant operation, the six-way valve 12 is switched to the first switching state as shown by the solid line in Fig. 1. The vapor refrigerant compressed to a high temperature and high pressure by the compressor 11 flows out into the first pipe 1, passes through the six-way valve 12, and flows into the outdoor heat exchanger 13 via the second pipe 2. The outdoor heat exchanger 13 functions as a condenser. The high-temperature, high-pressure vapor refrigerant dissipates heat to the outdoor air introduced into the outdoor heat exchanger 13 by the outdoor blower 14. As a result, the high-temperature, high-pressure vapor refrigerant condenses and becomes a high-temperature, high-pressure gas-liquid two-phase refrigerant.

[0034] The high-temperature, high-pressure two-phase gas-liquid refrigerant flows out into the third pipe 3, passes through the six-way valve 12, and flows into the reheater 21 via the fourth pipe 4. The reheater 21 functions as a condenser. The high-temperature, high-pressure two-phase gas-liquid refrigerant dissipates heat to the air introduced into the reheater 21 by the blower 32. As a result, the high-temperature, high-pressure two-phase gas-liquid refrigerant condenses into high-pressure liquid refrigerant. This high-pressure liquid refrigerant flows into the first expansion valve 23.

[0035] This high-pressure liquid refrigerant expands and is reduced in pressure by the first expansion valve 23, becoming a low-temperature, low-pressure, two-phase gas-liquid refrigerant. This low-temperature, low-pressure, two-phase gas-liquid refrigerant flows out into the fifth pipe 5, passes through the six-way valve 12, and flows into the cooler 22 via the sixth 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, two-phase gas-liquid refrigerant evaporates and becomes a low-pressure vapor refrigerant. The low-pressure vapor refrigerant is then drawn into the compressor 11. In cooling-dominated operation, the refrigerant subsequently circulates through the refrigerant circuit RC by the same process.

[0036] The reheater 21 and the cooler 22 share an air duct 31 and a blower 32. The air guided through the air duct 31 by the blower 32 is first cooled and dehumidified by passing through the cooler 22. This lowers the temperature of the air and reduces the moisture content of the air. After passing through the cooler 22, the air is guided into the air duct 31 and heated by passing through the reheater 21. This increases the temperature of the air. Note that the reheater 21 does not generally perform humidification, so the moisture content of the air remains the same before and after passing through the reheater 21. After passing through the reheater 21, the air is guided into the air duct 31 and blown out into the space to be air-conditioned.

[0037] After being cooled and dehumidified in the cooler 22, the air is heated as needed in the reheater 21, so the amount of dehumidification and the temperature of the air can be adjusted independently. This makes it possible to supply air at the temperature and humidity set by the user to the space to be air-conditioned.

[0038] <Heating-dominant operation> Next, the heating-dominated operation of the air conditioner 100 according to the first embodiment will be described with reference to Fig. 2. Heating-dominated operation is an operation in which the amount of air heated in the reheater 21 is greater than the amount of air cooled in the cooler 22, and the outdoor heat exchanger 13 functions as an evaporator, so that surplus cold energy as a heat pump is released to the outside air. In heating-dominated operation, the air that has passed through the reheater 21 has a higher temperature and a lower moisture content than the air before passing through the cooler 22.

[0039] In heating-dominant operation, the six-way valve 12 is switched to the second switching state as shown by the solid line in Figure 2. The vapor refrigerant compressed to a high temperature and high pressure by the compressor 11 flows out into the first pipe 1, passes through the six-way valve 12, and flows into the reheater 21 via the fourth pipe 4. The reheater 21 functions as a condenser. The high-temperature, high-pressure vapor refrigerant dissipates heat to the air introduced into the reheater 21 by the blower 32. As a result, the high-temperature, high-pressure vapor refrigerant condenses and becomes a high-pressure liquid refrigerant. This high-pressure liquid refrigerant flows into the first expansion valve 23.

[0040] This high-pressure liquid refrigerant expands and is reduced in pressure by the first expansion valve 23, becoming a low-temperature, low-pressure, two-phase gas-liquid refrigerant. This low-temperature, low-pressure, two-phase gas-liquid refrigerant flows out into the fifth pipe 5, passes through the six-way valve 12, and flows into the outdoor heat exchanger 13 via the third pipe 3. The outdoor heat exchanger 13 functions as an evaporator. The low-temperature, low-pressure, two-phase gas-liquid refrigerant partially evaporates by absorbing heat from the outdoor air introduced into the outdoor heat exchanger 13 by the outdoor blower 14. The low-temperature, low-pressure, two-phase gas-liquid refrigerant then flows into the six-way valve 12 via the second pipe 2, and flows into the cooler 22 via the sixth pipe 6.

[0041] 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 and becomes a low-pressure vapor refrigerant. This low-pressure vapor refrigerant is drawn into the compressor 11. In heating-dominated operation, the refrigerant subsequently circulates through the refrigerant circuit RC in the same manner.

[0042] As in cooling-dominated operation, the air guided through air duct 31 by blower 32 is cooled and dehumidified in cooler 22, then heated in reheater 21 and blown out into the space to be air-conditioned. Therefore, the amount of dehumidification of the air and the air temperature can be adjusted independently. As a result, air at the temperature and humidity set by the user can be supplied to the space to be air-conditioned.

[0043] Next, the effects of the air conditioner 100 according to the first embodiment will be described. In the air conditioner according to the first embodiment, the six-way valve 12 is configured to be switched so that the refrigerant flows through the refrigerant circuit RC in the order of the reheater 21 and the cooler 22 in either the first switching state or the second switching state. The six-way valve 12 is in the first switching state in cooling-dominated operation and in the second switching state in heating-dominated operation. This allows the direction of refrigerant flow through the reheater 21 and the cooler 22 to be the same in both cooling-dominated operation and heating-dominated operation. Therefore, in both cooling-dominated operation and heating-dominated operation, the air cooled and dehumidified in the cooler 22 can be heated in the reheater 21. This allows air at a temperature and humidity set by the user to be supplied to the space to be air-conditioned.

[0044] Furthermore, the reheater 21 and the cooler 22 are configured so that, in both the first switching state and the second switching state, the air blown by the blower 32 passes through the cooler 22 and then through the reheater 21. Therefore, in both the cooling-dominated operation and the heating-dominated operation, the air can be cooled and dehumidified and then reheated. Therefore, sufficient dehumidification can be performed in both the cooling-dominated operation and the heating-dominated operation.

[0045] In particular, since sufficient dehumidification can be achieved during heating-dominated operation, heating-dominated operation can be utilized for drying and dehumidifying the space to be air-conditioned. For this reason, the air conditioner 100 according to Embodiment 1 can also be used for drying food and ingredients.

[0046] Furthermore, in cooling-dominated operation, refrigerant that has passed through the outdoor heat exchanger 13 flows through the reheater 21. In heating-dominated operation, refrigerant that has passed through the outdoor heat exchanger 13 flows through the cooler 22. Therefore, the amount of heat exchanged by the refrigerant can be easily adjusted by adjusting the effective heat transfer area of ​​the outdoor heat exchanger 13. Furthermore, the amount of heat exchanged by the refrigerant can be easily adjusted by adjusting the rotation speed of the outdoor blower 14. Since the refrigerant whose heat quantity (internal energy) has been adjusted in the outdoor heat exchanger 13 can be supplied to the reheater 21 or the cooler 22, the amount of heat exchanged in the reheater 21 or the cooler 22 can be continuously adjusted. Therefore, the air conditioner 100 can be operated with a stable discharge temperature from the indoor unit 20.

[0047] According to the air conditioner of the first embodiment, in the first switching state, the refrigerant circuit RC is configured so that the refrigerant flows in the following order: compressor 11, first pipe 1, six-way valve 12, second pipe 2, outdoor heat exchanger 13, third pipe 3, six-way valve 12, fourth pipe 4, reheater 21, fifth pipe 5, first expansion valve 23, fifth pipe 5, six-way valve 12, sixth pipe 6, and cooler 22. In the second switching state, the refrigerant circuit RC is configured so that the refrigerant flows in the following order: compressor 11, first pipe 1, six-way valve 12, fourth pipe 4, reheater 21, fifth pipe 5, first expansion valve 23, fifth pipe 5, six-way valve 12, third pipe 3, outdoor heat exchanger 13, second pipe 2, six-way valve 12, sixth pipe 6, and cooler 22. Therefore, in either the first switching state or the second switching state, the refrigerant can flow through the refrigerant circuit RC in the order of the reheater 21 and the cooler 22.

[0048] In the air conditioner 100 according to the first embodiment, the refrigerant is a mixed refrigerant. A mixed refrigerant, which is a mixture of two or more types of refrigerants, is generally non-azeotropic, and therefore the temperature during the gas-liquid phase change is not constant. As a result, a temperature gradient occurs in the heat exchanger as the mixed refrigerant changes phase. This necessitates optimal design of the heat exchanger. In the air conditioner 100 according to the first embodiment, the reheater 21 and the cooler 22 can be specially designed, making it possible to achieve a high-performance air conditioner 100 even when using a mixed refrigerant.

[0049] In the air conditioner 100 according to the first embodiment, the reheater 21 and the cooler 22 are configured so that the refrigerant flows countercurrently to the air flow. This makes it possible to utilize the temperature gradient of the mixed refrigerant in the heat exchanger to reduce the heat exchange temperature difference between the air and the refrigerant. This allows the air conditioner 100 to operate at high performance.

[0050] The temperature of a non-azeotropic refrigerant rises as the refrigerant evaporates. Therefore, by configuring the air and refrigerant to flow in a counter-current manner in the cooler 22, which functions as an evaporator, the temperature rise in the direction of the refrigerant flow and the temperature drop in the direction of the air flow interact with each other, thereby reducing the heat exchange temperature difference between the air and refrigerant throughout the entire cooler 22.

[0051] Furthermore, since the temperature of a non-azeotropic refrigerant decreases as the refrigerant condenses, by configuring the air and refrigerant to flow in countercurrent fashion in the reheater 21, which functions as a condenser, the temperature decrease in the direction of refrigerant flow and the temperature increase in the direction of air flow interact with each other, thereby reducing the heat exchange temperature difference between the air and refrigerant throughout the entire reheater 21.

[0052] The position of blower 32 is not limited to the upstream of air passage 31 of cooler 22 as shown in Figures 1 and 2. Blower 32 may be located between cooler 22 and reheater 21 in air passage 31, or may be located downstream of reheater 21 in air passage 31.

[0053] 3 and 4, the six-way valve 12 may be of a rotary type. FIG. 3 is a schematic diagram of the rotary six-way valve 12 in a first switching state. FIG. 4 is a schematic diagram of the rotary six-way valve 12 in a second switching state. The rotary six-way valve 12 has a valve seat 12a and a valve element 12b configured to be rotatable relative to the valve seat 12a. The rotation of the valve element 12b relative to the valve seat 12a switches the flow path between the first switching state and the second switching state.

[0054] 5 and 6, the six-way valve 12 may have a sliding configuration. FIG. 5 is a schematic diagram of the sliding six-way valve 12 in a first switching state. FIG. 6 is a schematic diagram of the sliding six-way valve 12 in a second switching state. The sliding six-way valve 12 has a valve seat 12a and a valve element 12b configured to be slidable relative to the valve seat 12a. The valve element 12b slides relative to the valve seat 12a, thereby switching the flow path between the first switching state and the second switching state.

[0055] Embodiment 2 Unless otherwise specified, the air conditioner 100 according to the second embodiment has the same configuration, operation, and effects as the air conditioner 100 according to the first embodiment.

[0056] The configuration of an 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. Compared to the air conditioner 100 according to embodiment 1, the air conditioner 100 according to embodiment 2 has a configuration in which the connection positions of the fifth pipe 5 and the sixth pipe 6 with respect to the six-way valve 12 are swapped.

[0057] The six connection ports (first connection port P1 to sixth connection port P6) of the six-way valve 12 are connected to the first pipe 1, the second pipe 2, the third pipe 3, the fourth pipe 4, the fifth pipe 5, and the sixth pipe 6, respectively. The first connection port P1 is connected to the second pipe 2. The second connection port P2 is connected to the fifth pipe 5. The third connection port P3 is connected to the sixth pipe 6. The fourth connection port P4 is connected to the third pipe 3. The fifth connection port P5 is connected to the fourth pipe 4. The sixth connection port P6 is connected to the first pipe 1.

[0058] In the first switching state, the refrigerant circuit RC is configured so that the refrigerant flows in the following order: compressor 11, first pipe 1, six-way valve 12, second pipe 2, outdoor heat exchanger 13, third pipe 3, six-way valve 12, fourth pipe 4, reheater 21, fifth pipe 5, first expansion valve 23, fifth pipe 5, six-way valve 12, sixth pipe 6, and cooler 22.

[0059] In the second switching state, the refrigerant circuit RC is configured so that the refrigerant flows in the following order: compressor 11, first pipe 1, six-way valve 12, fourth pipe 4, reheater 21, fifth pipe 5, first expansion valve 23, fifth pipe 5, six-way valve 12, second pipe 2, outdoor heat exchanger 13, third pipe 3, six-way valve 12, sixth pipe 6, and cooler 22.

[0060] Next, the operation of the air conditioner 100 according to the second embodiment will be described with reference to FIGS.

[0061] 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 cooling-dominated operation of the air conditioner 100 according to embodiment 2, the refrigerant flows through the refrigerant circuit RC via the compressor 11, first pipe 1, six-way valve 12, second pipe 2, outdoor heat exchanger 13, third pipe 3, six-way valve 12, fourth pipe 4, reheater 21, first expansion valve 23, fifth pipe 5, six-way valve 12, sixth pipe 6, and cooler 22, before returning to the compressor 11.

[0062] Referring to Figure 8, in heating-dominated operation of the air conditioner 100 according to embodiment 2, the refrigerant flows through the refrigerant circuit RC via the compressor 11, the first pipe 1, the six-way valve 12, the fourth pipe 4, the reheater 21, the first expansion valve 23, the fifth pipe 5, the six-way valve 12, the second pipe 2, the outdoor heat exchanger 13, the third pipe 3, the six-way valve 12, the sixth pipe 6, and the cooler 22, before returning to the compressor 11.

[0063] Next, the effects of the air conditioner 100 according to the second embodiment will be described. According to the air conditioner 100 of the second embodiment, in the first switching state, the refrigerant circuit RC is configured so that the refrigerant flows in the following order: compressor 11, first pipe 1, six-way valve 12, second pipe 2, outdoor heat exchanger 13, third pipe 3, six-way valve 12, fourth pipe 4, reheater 21, fifth pipe 5, first expansion valve 23, fifth pipe 5, six-way valve 12, sixth pipe 6, and cooler 22. In the second switching state, the refrigerant circuit RC is configured so that the refrigerant flows in the following order: compressor 11, first pipe 1, six-way valve 12, fourth pipe 4, reheater 21, fifth pipe 5, first expansion valve 23, fifth pipe 5, six-way valve 12, second pipe 2, outdoor heat exchanger 13, third pipe 3, six-way valve 12, sixth pipe 6, and cooler 22. Therefore, in either the first switching state or the second switching state, the refrigerant can flow through the refrigerant circuit RC in the order of the reheater 21 and the cooler 22.

[0064] In the air conditioner 100 according to the second embodiment, the air flow direction guided by the outdoor blower 14 to the outdoor heat exchanger 13 is the same in both cooling-dominated operation and heating-dominated operation. By making the refrigerant flow direction inside the outdoor heat exchanger 13 the same in both the first and second switching states of the six-way valve 12, heat exchange between the air and the refrigerant in the outdoor heat exchanger 13 can be counterflow in both cooling-dominated operation and heating-dominated operation. Because the temperatures of the air and the refrigerant change in accordance with the heat exchange, by performing heat exchange in a counterflow manner, the heat exchange temperature difference between the air and the refrigerant can be made smaller across the entire outdoor heat exchanger 13 compared to a parallel-flow heat exchange method. This allows the performance and power consumption of the air conditioner 100 to be optimized.

[0065] In particular, in recent years, many mixtures of high-performance refrigerants with refrigerants that have low global warming potential or slow combustion rates have been proposed in order to reduce the global warming impact when refrigerant leaks from the air conditioner 100 and to reduce the refrigerant combustion rate when refrigerant leaks.

[0066] A mixed refrigerant, which is a mixture of two or more types of refrigerants, generally has non-azeotropic properties, in which temperature changes occur during the phase change processes of evaporation and condensation. The countercurrent heat exchange in the outdoor heat exchanger 13 of the second embodiment is particularly effective when a mixed refrigerant, which is a mixture of two or more types of refrigerants, is enclosed in the air conditioner 100.

[0067] Since the temperature of a non-azeotropic refrigerant decreases as the refrigerant condenses, in cooling-dominated operation, the air and refrigerant flow in countercurrent fashion in the outdoor heat exchanger 13, which functions as a condenser, so that the temperature decrease in the refrigerant flow direction and the temperature increase in the air flow direction interact with each other. This reduces the heat exchange temperature difference between the air and refrigerant throughout the entire outdoor heat exchanger 13.

[0068] In addition, since the temperature of a non-azeotropic refrigerant rises as the refrigerant evaporates, in heating-dominated operation, by making the air and refrigerant flow countercurrently in the outdoor heat exchanger 13, which functions as an evaporator, the temperature rise in the refrigerant flow direction and the temperature drop in the air flow direction interact with each other. This makes it possible to reduce the heat exchange temperature difference between the air and refrigerant throughout the entire outdoor heat exchanger 13.

[0069] Embodiment 3 Unless otherwise specified, the air conditioner 100 according to the third embodiment has the same configuration, operation, and effects as the air conditioner 100 according to the first embodiment.

[0070] The configuration of an 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 it has a liquid receiver 24.

[0071] In the air conditioner 100 according to the third embodiment, the refrigerant circuit RC has a liquid receiver 24. The liquid receiver 24 is disposed in the refrigerant circuit RC between the reheater 21 and the first expansion valve 23. The liquid receiver 24 is configured to store refrigerant.

[0072] Next, the operation of the air conditioner 100 according to the third embodiment will be described with reference to FIGS.

[0073] 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 cooling-dominated operation of the air conditioner 100 according to embodiment 3, the refrigerant flows through the refrigerant circuit RC, passing through the compressor 11, the first pipe 1, the six-way valve 12, the second pipe 2, the outdoor heat exchanger 13, the third pipe 3, the six-way valve 12, the fourth pipe 4, the reheater 21, the receiver 24, the first expansion valve 23, the fifth pipe 5, the six-way valve 12, the sixth pipe 6, and the cooler 22, before returning to the compressor 11.

[0074] Referring to Figure 10, in heating-dominated operation of the air conditioner 100 according to embodiment 3, the refrigerant flows through the refrigerant circuit RC via the compressor 11, the first pipe 1, the six-way valve 12, the fourth pipe 4, the reheater 21, the receiver 24, the first expansion valve 23, the fifth pipe 5, the six-way valve 12, the third pipe 3, the outdoor heat exchanger 13, the second pipe 2, the six-way valve 12, the sixth pipe 6, and the cooler 22, before returning to the compressor 11.

[0075] Next, the effects of the air conditioner 100 according to the third embodiment will be described. In cooling-dominated operation, when the amount of heat dissipated in the outdoor heat exchanger 13 decreases, the amount of liquid refrigerant remaining inside the outdoor heat exchanger 13 decreases. In an air conditioner 100 that does not have a refrigerant amount adjustment mechanism, the amount of refrigerant charged becomes excessive relative to the appropriate refrigerant amount for that operation, which raises concerns about operational malfunctions due to excessive increases in the compressor discharge refrigerant temperature or pressure.

[0076] In the air conditioner 100 according to the third embodiment, the receiver 24 is disposed in the refrigerant circuit RC between the reheater 21 and the first expansion valve 23. This makes it possible to adjust the amount of available refrigerant in the air conditioner 100 and thereby realize an optimum operating point for the compressor 11.

[0077] Furthermore, in order to prevent refrigerant flow noise, it is desirable to supply liquid refrigerant to the first expansion valve 23. By arranging the receiver 24 upstream of the first expansion valve 23 in the refrigerant flow, the refrigerant at the inlet of the first expansion valve 23 can be stably maintained in a liquid state.

[0078] Embodiment 4 Unless otherwise specified, the air conditioner 100 according to the fourth embodiment has the same configuration, operation, and effects as the air conditioner 100 according to the third embodiment.

[0079] The configuration of an 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 it has a second expansion valve 25.

[0080] In the air conditioner 100 according to the fourth embodiment, the refrigerant circuit RC has a second expansion valve 25. The second expansion valve 25 is disposed in the refrigerant circuit RC between the reheater 21 and the receiver 24. The second expansion valve 25 is configured so that its opening degree can be adjusted.

[0081] Next, the operation of the air conditioner 100 according to the fourth embodiment will be described with reference to FIGS.

[0082] 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 cooling-dominated operation of the air conditioner 100 according to embodiment 4, the refrigerant flows through the refrigerant circuit RC, passing through the compressor 11, the first pipe 1, the six-way valve 12, the second pipe 2, the outdoor heat exchanger 13, the third pipe 3, the six-way valve 12, the fourth pipe 4, the reheater 21, the second expansion valve 25, the receiver 24, the first expansion valve 23, the fifth pipe 5, the six-way valve 12, the sixth pipe 6, and the cooler 22, before returning to the compressor 11.

[0083] Referring to Figure 12, in heating-dominated operation of the air conditioner 100 according to embodiment 4, the refrigerant flows through the refrigerant circuit RC via the compressor 11, the first pipe 1, the six-way valve 12, the fourth pipe 4, the reheater 21, the second expansion valve 25, the receiver 24, the first expansion valve 23, the fifth pipe 5, the six-way valve 12, the third pipe 3, the outdoor heat exchanger 13, the second pipe 2, the six-way valve 12, the sixth pipe 6, and the cooler 22, before returning to the compressor 11.

[0084] Next, the effects of the air conditioner 100 according to the fourth embodiment will be described. In the air conditioner 100 according to the fourth embodiment, the second expansion valve 25 is disposed in the refrigerant circuit RC between the reheater 21 and the receiver 24. The refrigerant pressure inside the receiver 24 can be adjusted by adjusting the opening degree of the second expansion valve 25. This makes it possible to actively adjust the amount of liquid refrigerant stored inside the receiver 24, compared to the third embodiment. Therefore, the air conditioner 100 can be operated more stably.

[0085] In the first to fourth embodiments, it is preferable that the refrigerant inlet of the reheater 21 be positioned higher in the direction of gravity than the refrigerant outlet, in order to stably supply liquid refrigerant to the first expansion valve 23 or the second expansion valve 25. That is, the reheater 21 has a refrigerant inlet and a refrigerant outlet. The refrigerant inlet of the reheater 21 is positioned higher in the direction of gravity than the refrigerant outlet.

[0086] In this configuration, the liquid refrigerant remaining in the reheater 21 is gradually discharged due to gravity, so the inlet refrigerant can be kept in a liquid state in the first expansion valve 23 or the second expansion valve 25. Therefore, the air conditioner 100 can be operated stably.

[0087] Embodiment 5. Unless otherwise specified, the air conditioner 100 according to the fifth embodiment has the same configuration, operation, and effects as the air conditioner 100 according to the second embodiment.

[0088] The configuration of an 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 differs from the air conditioner 100 according to embodiment 2 in terms of the outdoor heat exchanger 13.

[0089] The refrigerant circuit RC has a first refrigerant shut-off mechanism 15 and a second refrigerant shut-off mechanism 16. The first refrigerant shut-off mechanism 15 and the second refrigerant shut-off mechanism 16 are, for example, solenoid valves.

[0090] The outdoor heat exchanger 13 has a first heat exchange section 13a and a second heat exchange section 13b. The first heat exchange section 13a and the second heat exchange section 13b are arranged in parallel to each other in the refrigerant circuit RC. The first heat exchange section 13a has a larger internal volume than the second heat exchange section 13b. The first refrigerant closing mechanism 15 is connected to the inlet of the first heat exchange section 13a. The second refrigerant closing mechanism 16 is connected to the outlet of the first heat exchange section 13a.

[0091] The refrigerant circuit RC also has a bypass circuit 17. The bypass circuit 17 has a bypass pipe 17a and a flow rate adjustment mechanism 17b. The bypass pipe 17a is connected to the second pipe 2 and the third 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 arranged in parallel with the outdoor heat exchanger 13 in the refrigerant circuit RC. The bypass circuit 17 is arranged between the six-way valve 12 and the outdoor heat exchanger 13 in the refrigerant circuit RC.

[0092] 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 cooling-dominated operation of the air conditioner 100 according to embodiment 5, the refrigerant flows through the refrigerant circuit RC via the compressor 11, first pipe 1, six-way valve 12, second pipe 2, outdoor heat exchanger 13 and bypass circuit 17, third pipe 3, six-way valve 12, fourth pipe 4, reheater 21, first expansion valve 23, fifth pipe 5, six-way valve 12, sixth pipe 6, and cooler 22, before returning to the compressor 11.

[0093] Referring to Figure 14, in heating-dominated operation of the air conditioner 100 according to embodiment 5, the refrigerant flows through the refrigerant circuit RC via the compressor 11, the first pipe 1, the six-way valve 12, the fourth pipe 4, the reheater 21, the first expansion valve 23, the fifth pipe 5, the six-way valve 12, the second pipe 2, the outdoor heat exchanger 13, the bypass circuit 17, the third pipe 3, the six-way valve 12, the sixth pipe 6, and the cooler 22, and then back to the compressor 11.

[0094] Next, the effects of the air conditioner 100 according to the fifth embodiment will be described. The amount of heat released from condensation and the amount of heat received from evaporation in the outdoor heat exchanger 13 can be adjusted by reducing the rotation speed of the outdoor blower 14 to reduce the amount of outdoor air introduced to the outdoor heat exchanger 13. Furthermore, the first heat exchange section 13a and the second heat exchange section 13b of the outdoor heat exchanger 13 are arranged in parallel to each other in the refrigerant circuit RC. This blocks the refrigerant flow in part of the outdoor heat exchanger 13, further reducing the amount of heat exchanged in the outdoor heat exchanger 13. Therefore, the stable adjustment range of the heat exchange amounts in the reheater 21 and the cooler 22 can be expanded.

[0095] Furthermore, by circulating the refrigerant through the bypass circuit 17 and not circulating the refrigerant through the outdoor heat exchanger 13, the amount of heat exchanged in the outdoor heat exchanger 13 can be finely adjusted. This makes it possible to increase the amount of heat exchanged in the reheater 21 during cooling-dominated operation. Furthermore, it makes it possible to increase the amount of heat exchanged in the cooler 22 during heating-dominated operation. Therefore, the adjustment range of the blown air temperature and blown air humidity by the air conditioner 100 can be expanded.

[0096] Embodiment 6 Unless otherwise specified, the air conditioner 100 according to the sixth embodiment has the same configuration, operation, and effects as the air conditioner 100 according to the fifth embodiment.

[0097] The configuration of an air conditioner 100 pertaining to embodiment 6 will be described with reference to Fig. 15. Fig. 15 is a refrigerant circuit diagram of the air conditioner 100 pertaining to embodiment 6. The air conditioner 100 pertaining to embodiment 6 differs from the air conditioner 100 pertaining to embodiment 5 in that it has a second refrigerant shut-off mechanism 16. The second refrigerant shut-off mechanism 16 is a check valve.

[0098] 15 and 16, the operation of air conditioner 100 according to the sixth embodiment is basically the same as that of the fifth embodiment.

[0099] Next, the effects of the air conditioner 100 according to the sixth embodiment will be described. In the air conditioner 100 according to the sixth embodiment, the second refrigerant shut-off mechanism 16 is a check valve. Because the refrigerant flows in the same direction inside the outdoor heat exchanger 13 in both cooling-dominated operation and heating-dominated operation, a check valve can be used as the second refrigerant shut-off mechanism 16. Because check valves are less expensive and smaller than solenoid valves, refrigerant shut-off can be achieved at low cost and in a small space.

[0100] Embodiment 7 Unless otherwise specified, the air conditioner 100 according to the seventh embodiment has the same configuration, operation, and effects as the air conditioner 100 according to the first embodiment.

[0101] The configurations of the reheater 21 and the cooler 22 according to the seventh embodiment will be described with reference to Fig. 17. Fig. 17 is a perspective view of the reheater 21 and the cooler 22 according to the seventh embodiment.

[0102] The reheater 21 has an internal volume smaller than that of the cooler 22. The reheater 21 has a first heat transfer tube T1. The cooler 22 has a second heat transfer tube T2. For example, the inner diameter of the first heat transfer tube T1 may be equal to the inner diameter of the second heat transfer tube T2, and the length of the first heat transfer tube T1 may be shorter than the length of the second heat transfer tube T2.

[0103] The reheater 21 has a plurality of first fins F1. The cooler 22 has a plurality of second fins F2. The plurality of first fins F1 have a total surface area smaller than that of the plurality of second fins F2. For example, the length of the first fins F1 may be shorter than the length of the second fins F2, and the number of first fins F1 may be smaller than the number of second fins F2.

[0104] Next, the effects of the air conditioner 100 according to the seventh embodiment will be described. In the air conditioner 100 according to the seventh embodiment, the reheater 21 has an internal volume smaller than that of the cooler 22. Because the air that has been cooled once in the cooler 22 is reheated in the reheater 21, 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. For this reason, even if the reheater 21 is designed to be smaller and have a smaller internal volume than the cooler 22, the reheater 21 can still demonstrate the heat dissipation capacity required for a preset target blown air temperature.

[0105] Furthermore, by designing the internal volume of the reheater 21 to be small, it is possible to reduce the amount of change in the amount of liquid refrigerant stored in the reheater 21 caused by adjustment of the heat exchange amount in the reheater 21. This makes it possible to suppress excessive increases in the compressor discharge refrigerant temperature and pressure. Furthermore, when the liquid receiver 24 is provided, its adjustment capacity can be reduced, allowing the liquid receiver 24 to be made smaller.

[0106] In the air conditioner 100 according to the seventh embodiment, the first fins F1 have a smaller total surface area than the second fins F2. When downsizing the reheater 21, the total surface area of ​​the first fins F1 that come into contact with the air of the reheater 21 can be designed to be smaller than the total surface area of ​​the second fins F2 that come into contact with the air of the cooler 22, thereby making it possible to configure the reheater 21 and the air conditioner 100 inexpensively and compactly.

[0107] Furthermore, when a reheater 21 and a cooler 22 are placed inside the air duct 31, by designing the reheater 21 to be small and the cooler 22 to be large, it is possible to realize a configuration that exhibits optimal performance within the design dimensional constraints of the air conditioner 100.

[0108] The embodiments disclosed herein should be considered to be illustrative in all respects and not restrictive. The scope of the present disclosure is defined by the claims, not the above description, and is intended to include all modifications within the meaning and scope of the claims. [Explanation of symbols]

[0109] 1 First pipe, 2 Second pipe, 3 Third pipe, 4 Fourth pipe, 5 Fifth pipe, 6 Sixth pipe, 10 Outdoor unit, 11 Compressor, 12 Six-way valve, 13 Outdoor heat exchanger, 13a First heat exchange section, 13b Second heat exchange section, 14 Outdoor blower, 15 First refrigerant closing mechanism, 16 Second refrigerant closing mechanism, 17 Bypass circuit, 17a Bypass piping, 17b Flow rate adjustment mechanism, 20 Indoor unit, 21 Reheater, 22 Cooler, 23 First expansion valve, 24 Receiver, 25 Second expansion valve, 31 Air duct, 32 Blower, 100 Air conditioner, F1 First fin, F2 Second fin, T1 First heat transfer tube, T2 Second heat transfer tube, RC Refrigerant circuit.

Claims

1. a refrigerant circuit configured to circulate a refrigerant, the refrigerant circuit having a compressor, a six-way valve, an outdoor heat exchanger, a reheater, a first expansion valve, and a cooler; a blower configured to blow air to 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 In the first switching state, the refrigerant circuit is configured to be switched so that the refrigerant flows through 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 in this order; and In the second switching state, the refrigerant circuit is configured to be switched so that the refrigerant flows 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 so that, in either the first switching state or the second switching state, the air blown by the blower passes through the cooler before passing through the reheater.

2. the refrigerant circuit includes 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, 2. The air conditioner of claim 1, wherein in the second switching state, the refrigerant circuit is configured so that the refrigerant flows in the following order: 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 refrigerant circuit includes 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, 2. The air conditioner of claim 1, wherein in the second switching state, the refrigerant circuit is configured so that the refrigerant flows in the following order: 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 claim 1 , wherein the refrigerant is a mixed refrigerant.

5. the refrigerant circuit has a receiver, The air conditioner according to claim 1 , wherein the receiver is disposed in the refrigerant circuit between the reheater and the first expansion valve.

6. the refrigerant circuit has a second expansion valve, The air conditioner according to claim 5, wherein the second expansion valve is disposed in the refrigerant circuit between the reheater and the receiver.

7. the reheater has a refrigerant inlet and a refrigerant outlet; The air conditioner according to claim 1 , wherein the refrigerant inlet is located higher in the direction of gravity than the refrigerant outlet.

8. the refrigerant circuit has a first refrigerant shut-off mechanism and a second refrigerant shut-off mechanism, the outdoor heat exchanger has a first heat exchange section and a second heat exchange section, the first heat exchange unit and the second heat exchange unit are arranged in parallel with each other in the refrigerant circuit, The first heat exchange unit has a larger internal volume than the second heat exchange unit, the first refrigerant shut-off mechanism is connected to an inlet of the first heat exchanger; The air conditioner according to claim 1 , wherein the second refrigerant shut-off mechanism is connected to an outlet of the first heat exchanger.

9. The refrigerant circuit has a bypass circuit, The air conditioner according to claim 8 , wherein 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 shut-off mechanism is a check valve.

11. The air conditioner according to claim 1 , wherein the reheater has an internal volume smaller than that of the cooler.

12. the reheater has a plurality of first fins; the cooler has a plurality of second fins; The air conditioner according to claim 1 , wherein the first fins have a total surface area smaller than that of the second fins.

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