WO2021065913A1

WO2021065913A1 - Evaporator and refrigeration cycle device equipped with same

Info

Publication number: WO2021065913A1
Application number: PCT/JP2020/036920
Authority: WO
Inventors: 熊倉　英二; 岩田　育弘; 山田　拓郎; 隆平加治; 智己廣川
Original assignee: ダイキン工業株式会社
Priority date: 2019-09-30
Filing date: 2020-09-29
Publication date: 2021-04-08
Also published as: CN114450546A; EP4040084A1; CN114450546B; JP7425282B2; JP2021055957A; US20220214085A1; EP4040084A4

Abstract

The present invention provides an evaporator of a refrigeration cycle device in which a non-azeotropic mixed refrigerant is sealed, such that the frost resistance and heat exchange performance can be improved. If the notch opening side is upwind of the air flow, since the difference in temperature between the air and the evaporator surface can be increased, the heat exchange performance is improved but frost is easily formed. If the notch opening side is located downwind, the frost resistance is increased but the heat exchange performance is decreased. In particular, since the refrigerant used is a non-azeotropic mixed refrigerant, the temperature of the refrigerant tends to drop on the inlet side of the evaporator due to the temperature gradient, and frost is likely to occur. However, since a first heat exchange unit (23a) is formed with the notch opening side being located downwind in the air flow direction, the frost resistance can be increased by using at least the inlet side of the evaporator as the first heat exchange unit (23a).

Description

Evaporator and refrigeration cycle equipment equipped with it

Regarding the evaporator of the refrigeration cycle device in which the non-azeotropic mixed refrigerant is sealed.

As an evaporator of a refrigeration cycle device, there is a form in which the distribution of a plurality of heat transfer tubes is largely biased to either the windward side or the leeward side with respect to the center of the heat transfer fins. For example, in the evaporator described in Patent Document 1 (WO2017 / 183180), elongated holes having a major axis extending in the width direction of the fins are provided at predetermined intervals in a direction orthogonal to the width direction and the thickness direction of the fins. A laminated heat exchanger in which a flat tube is inserted in an elongated hole.

In an evaporator as described above, if the center in the width direction of the entire flat tube group is arranged on the wind side of the air with respect to the center in the width direction of the fins, the temperature difference between the air temperature and the surface of the heat exchanger can be large. The replacement performance is improved, but frost is easily formed. Conversely, if the center of the entire flat tube group in the width direction is placed on the leeward side of the center of the fin in the width direction, the frost bearing capacity (ability to suppress frost formation) increases, but the heat exchange performance tends to decrease. There is.

In particular, in the non-co-boiling mixed refrigerant, the composition differs between the liquid phase and the gas phase, so in the evaporator, the refrigerant temperature at the inlet is lower than that at the outlet, and if the flat tube is biased to the wind side, frost is likely to occur.

In Patent Document 1, the distance between the flat tube and the wind-up edge of the fin is examined from the viewpoint of drainage of condensed water and molten water, but the refrigerant flowing in the evaporator is specified as a non-azeotropic mixed refrigerant. The case has not been investigated in terms of frost resistance (ability to suppress frost formation) and / or heat exchange performance.

Therefore, there is a problem of providing an evaporator having improved frost resistance and / or heat exchange performance in an evaporator of a refrigeration cycle apparatus in which a non-azeotropic mixed refrigerant is sealed.

The evaporator according to the first aspect is an evaporator of a refrigeration cycle device in which a non-azeotropic mixed refrigerant is sealed, and includes a plurality of fins and a plurality of heat transfer tubes. The plurality of fins are arranged at predetermined intervals in the plate thickness direction. The plurality of heat transfer tubes penetrate the plurality of fins in the plate thickness direction. A first heat exchange section is formed in the evaporator. In the first heat exchange section, when a plurality of heat transfer tubes are viewed from the fin plate thickness direction as a heat transfer tube group, the distribution center of the heat transfer tube group in the air flow direction is leeward of the fin center in the air flow direction. Located in.

In this evaporator, since the enclosed refrigerant is a non-azeotropic mixed refrigerant, the refrigerant temperature at the inlet of the evaporator is lower than that at the outlet, and frost is likely to occur. However, for example, if the refrigerant inlet side is the first heat exchange section, the distribution center of the heat transfer tube group is located leeward of the center of the fin in the air flow direction, so that the distribution center of the heat transfer tube group is the center of the fin. It is less likely to frost than when it is located upwind.

The evaporator according to the second viewpoint is the evaporator according to the first viewpoint, and the second heat exchange portion is further formed. In the second heat exchange section, the distribution center of the heat transfer tube group is located on the windward side of the center of the fin in the air flow direction.

In this evaporator, the temperature of the non-co-boiling mixed refrigerant rises from the inlet to the outlet of the evaporator. Therefore, on the outlet side, the heat exchange performance is more important than the frost resistance, and the distribution center of the heat transfer tube group. Is preferably located upwind of the center of the fin in the direction of air flow.

Therefore, in addition to the first heat exchange section of the first aspect, the second heat exchange section in which the distribution center of the heat transfer tube group is located on the windward side of the fin center in the air flow direction is formed. For example, the first heat exchange unit can be arranged on the inlet side of the evaporator, and the second heat exchange unit can be arranged on the outlet side of the evaporator. In this way, it is possible to try to combine heat exchange units suitable for the temperature of the refrigerant in the evaporator.

The evaporator according to the third aspect is the evaporator according to the second aspect, and the third heat exchange portion is further formed. In the third heat exchange section, the distribution center of the heat transfer tube group substantially coincides with the center of the fin in the air flow direction.

In this evaporator, for example, the first heat exchange section is on the inlet side of the evaporator, the second heat exchange section is on the outlet side of the evaporator, and the third heat exchange section is between the first heat exchange section and the second heat exchange section. The part can be arranged. In this way, it is possible to try to combine heat exchange units suitable for the temperature of the refrigerant in the evaporator.

The evaporator according to the fourth aspect is the evaporator according to the second aspect, and the first heat exchange section and the second heat exchange section are integrated.

The evaporator according to the fifth aspect is the evaporator according to the third aspect, and the first heat exchange section and at least one of the second heat exchange section and the third heat exchange section are integrated. ..

The evaporator according to the sixth aspect is an evaporator of a refrigeration cycle device in which a non-azeotropic mixed refrigerant is sealed, and includes a plurality of fins and a plurality of heat transfer tubes. The plurality of fins are arranged at predetermined intervals in the plate thickness direction. The plurality of heat transfer tubes penetrate the plurality of fins in the plate thickness direction. The evaporator is formed with a first heat exchange section and a second heat exchange section. In the first heat exchange section, the distance from the windward end of the heat transfer tube located on the windward side in the air flow direction to the windward end of the fin is the first dimension. The second heat exchange section has a second dimension in which the distance from the windward end of the heat transfer tube located most upwind in the air flow direction to the windward end of the fin is smaller than the first dimension.

In this evaporator, since the temperature of the non-azeotropic mixed refrigerant rises from the inlet to the outlet of the evaporator, it is preferable to emphasize the frost resistance on the inlet side and the heat exchange performance on the outlet side.

For example, the first heat exchange unit can be arranged on the inlet side of the evaporator, and the second heat exchange unit can be arranged on the outlet side of the evaporator. In this way, it is possible to try a combination suitable for the refrigerant temperature in the evaporator.

The evaporator according to the seventh aspect is the evaporator according to the sixth aspect, and the third heat exchange portion is further formed. In the third heat exchange section, the distance from the windward end of the heat transfer tube located on the windward side in the air flow direction to the windward end of the fin, and the heat transfer tube located on the windward side in the air flow direction. The distance from the leeward end to the leeward end of the fin is equal.

The evaporator according to the eighth aspect is the evaporator according to the sixth aspect, and the first heat exchange part and the second heat exchange part are integrated.

The evaporator according to the ninth aspect is the evaporator according to the seventh aspect, and the first heat exchange section and at least one of the second heat exchange section and the third heat exchange section are integrated. ..

The evaporator according to the tenth aspect is an evaporator of a refrigeration cycle device in which a non-azeotropic mixed refrigerant is sealed, and includes a plurality of fins and a plurality of heat transfer tubes. The plurality of fins are arranged at predetermined intervals in the plate thickness direction. The plurality of heat transfer tubes penetrate the plurality of fins in the plate thickness direction. The fin has a plurality of notches. The notches are aligned in a direction orthogonal to both the air flow direction and the plate thickness direction. The heat transfer tube is a flat multi-hole tube that is inserted into the notch. A first heat exchange section is formed in the evaporator. In the first heat exchange section, the opening side of the notch is located leeward in the air flow direction.

In this evaporator, when the opening side of the notch is on the windward side of the air flow, the temperature difference between the air temperature and the surface of the evaporator can be large, so that the heat exchange performance is improved but frost is easily formed. On the contrary, when the opening side of the notch is leeward, the frost bearing capacity increases but the heat exchange performance decreases. In particular, since the refrigerant used is a non-azeotropic mixed refrigerant, the temperature of the refrigerant tends to decrease on the inlet side of the evaporator due to the temperature gradient, and frost is likely to occur.

However, since the first heat exchange section is formed in which the opening side of the notch is located leeward in the air flow direction, the frost bearing capacity is increased by setting at least the inlet side of the evaporator as the first heat exchange section. be able to.

The evaporator according to the eleventh viewpoint is the evaporator according to the tenth viewpoint, and the second heat exchange portion is further formed. In the second heat exchange section, the opening side of the notch is located upwind in the air flow direction.

In this evaporator, for example, a first heat exchange unit can be arranged on the inlet side of the evaporator and a second heat exchange unit can be arranged on the outlet side of the evaporator. In this way, it is possible to try a combination suitable for the refrigerant temperature in the evaporator.

The evaporator according to the twelfth viewpoint is the evaporator according to the eleventh viewpoint, and the first heat exchange part and the second heat exchange part are integrated.

The refrigeration cycle device according to the thirteenth viewpoint is a refrigeration cycle device provided with an evaporator according to any one of the first to the twelfth viewpoints. The non-azeotropic mixed refrigerant contains any of HFC refrigerants, HFO refrigerants, CF3I, and natural refrigerants.

The refrigeration cycle device according to the 14th viewpoint is a refrigeration cycle device provided with an evaporator according to any one of the 1st to 12th viewpoints. The non-azeotropic mixed refrigerant contains any of R32, R1132 (E), R1234yf, R1234ze, CF3I and CO2.

The refrigeration cycle device according to the fifteenth viewpoint is a refrigeration cycle device provided with an evaporator according to any one of the first to twelfth viewpoints. The non-azeotropic mixed refrigerant contains at least R1132 (E), R32 and R1234yf.

The refrigeration cycle device according to the 16th viewpoint is a refrigeration cycle device provided with an evaporator according to any one of the 1st to 12th viewpoints. The non-azeotropic mixed refrigerant contains at least R1132 (E), R1123 and R1234yf.

The refrigeration cycle device according to the 17th viewpoint is a refrigeration cycle device provided with an evaporator according to any one of the 1st to 12th viewpoints. The non-azeotropic mixed refrigerant contains at least R1132 (E) and R1234yf.

The refrigeration cycle device according to the 18th viewpoint is a refrigeration cycle device provided with an evaporator according to any one of the 1st to 12th viewpoints. The non-azeotropic mixed refrigerant contains at least R32, R1234yf, and at least one of R1132a and R1114.

The refrigeration cycle device according to the 19th viewpoint is a refrigeration cycle device provided with an evaporator according to any one of the 1st to 12th viewpoints. The non-azeotropic mixed refrigerant contains at least R32, CO2, R125, R134a, and R1234yf.

The refrigeration cycle device according to the twentieth viewpoint is a refrigeration cycle device provided with an evaporator according to any one of the first to twelfth viewpoints. The non-azeotropic mixed refrigerant contains at least R1132 (Z) and R1234yf.

FIG. 6 is a schematic configuration diagram of an air conditioner as a refrigerating device according to an embodiment of the present disclosure. Schematic front view of the indoor heat exchanger. External perspective view of the outdoor heat exchanger. PH diagram of non-azeotropic mixed refrigerant. The perspective view of the 1st heat exchange part of the outdoor heat exchanger which concerns on 1st Embodiment. The perspective view of the 2nd heat exchange part of the outdoor heat exchanger which concerns on 1st Embodiment. The schematic perspective view of the outdoor heat exchanger which used the 1st heat exchange part and the 2nd heat exchange part together. The schematic perspective view of another outdoor heat exchanger which used the 1st heat exchange part and the 2nd heat exchange part together. The perspective view of the 1st heat exchange part of the outdoor heat exchanger which concerns on 2nd Embodiment. The perspective view of the 2nd heat exchange part of the outdoor heat exchanger which concerns on 2nd Embodiment. The perspective view of the 3rd heat exchange part of the outdoor heat exchanger which concerns on the modification of 2nd Embodiment. The perspective view of the 1st heat exchange part of the outdoor heat exchanger which concerns on 3rd Embodiment. The perspective view of the 2nd heat exchange part of the outdoor heat exchanger which concerns on 3rd Embodiment. The perspective view of the 3rd heat exchange part of the outdoor heat exchanger which concerns on the modification of 3rd Embodiment.

<First Embodiment>
(1) Configuration of Air Conditioning Device 1 FIG. 1 is a schematic configuration diagram of an air conditioning device 1 according to an embodiment of the present disclosure. In FIG. 1, the air conditioner 1 is a refrigerating device that performs a cooling operation and a heating operation by a vapor compression refrigeration cycle.

The refrigerant circuit 10 of the air conditioner 1 is configured by connecting the outdoor unit 2 and the indoor unit 4 via the liquid refrigerant connecting pipe 5 and the gas refrigerant connecting pipe 6.

The refrigerant sealed in the refrigerant circuit 10 is a non-azeotropic mixed refrigerant. The non-azeotropic mixed refrigerant contains any of HFC refrigerants, HFO refrigerants, CF3I, and natural refrigerants.

(1-1) Indoor unit 4
The indoor unit 4 is installed indoors and constitutes a part of the refrigerant circuit 10. The indoor unit 4 includes an indoor heat exchanger 41, an indoor fan 42, and an indoor control unit 44.

(1-1-1) Indoor heat exchanger 41
The indoor heat exchanger 41 functions as a refrigerant evaporator during the cooling operation to cool the indoor air. Further, the indoor heat exchanger 41 functions as a radiator of the refrigerant during the heating operation to heat the indoor air. The inlet side of the refrigerant of the indoor heat exchanger 41 during the cooling operation is connected to the liquid refrigerant connecting pipe 5, and the outlet side of the refrigerant is connected to the gas refrigerant connecting pipe 6.

FIG. 2 is a front view of the indoor heat exchanger 41. In FIG. 2, the indoor heat exchanger 41 is a cross-fin type heat exchanger. The indoor heat exchanger has a heat transfer fin 412 and a heat transfer tube 411.

The heat transfer fin 412 is a flat plate made of thin aluminum. A plurality of through holes are formed in the heat transfer fin 412. The heat transfer tube 411 has a straight tube 411a inserted into the through hole of the heat transfer fin 412, and a

U-shaped tube

411b, 411c that connects the ends of the adjacent straight tubes 411a.

The straight tube 411a comes into close contact with the heat transfer fin 412 by being inserted into the through hole of the heat transfer fin 412 and then expanded. The straight pipe 411a and the first U-shaped pipe 411b are integrally formed. The second U-shaped pipe 411c is connected to the end of the straight pipe 411a by welding, brazing, or the like after the straight pipe 411a is inserted into the through hole of the heat transfer fin 412 and expanded.

(1-1-2) Indoor fan 42
The indoor fan 42 sucks indoor air into the indoor unit 4, exchanges heat with the refrigerant in the indoor heat exchanger 41, and then supplies the air to the room. As the indoor fan 42, a centrifugal fan, a multi-blade fan, or the like is adopted. The indoor fan 42 is driven by the indoor fan motor 43.

(1-1-3) Indoor control unit 44
The indoor control unit 44 controls the operation of each unit constituting the indoor unit 4. The indoor control unit 44 has a microcomputer and a memory for controlling the indoor unit 4.

The indoor control unit 44 transmits and receives control signals and the like to and from a remote controller (not shown). Further, the indoor control unit 44 transmits and receives a control signal and the like via the transmission line 8a to and from the outdoor control unit 38 of the outdoor unit 2.

(1-2) Outdoor unit 2
The outdoor unit 2 is installed outdoors and constitutes a part of the refrigerant circuit 10. The outdoor unit 2 includes a compressor 21, a four-way switching valve 22, an outdoor heat exchanger 23, an expansion valve 26, a liquid side closing valve 27, and a gas side closing valve 28.

(1-2-1) Compressor 21
The compressor 21 is a device that compresses the low-pressure refrigerant in the refrigeration cycle. The compressor 21 rotates and drives a positive displacement compression element (not shown) such as a rotary type or a scroll type by a compressor motor 21a.

In the compressor 21, the suction pipe 31 is connected to the suction side, and the discharge pipe 32 is connected to the discharge side. The suction pipe 31 is a refrigerant pipe that connects the suction side of the compressor 21 and the four-way switching valve 22. The discharge pipe 32 is a refrigerant pipe that connects the discharge side of the compressor 21 and the four-way switching valve 22.

The accumulator 29 is connected to the suction pipe 31. The accumulator 29 separates the inflowing refrigerant into a liquid refrigerant and a gas refrigerant, and causes only the gas refrigerant to flow to the suction side of the compressor 21.

(1-2-2) Four-way switching valve 22
The four-way switching valve 22 switches the direction of the refrigerant flow in the refrigerant circuit 10. The four-way switching valve 22 causes the outdoor heat exchanger 23 to function as a refrigerant radiator and the indoor heat exchanger 41 to function as a refrigerant evaporator during cooling operation.

The four-way switching valve 22 connects the discharge pipe 32 of the compressor 21 and the first gas refrigerant pipe 33 of the outdoor heat exchanger 23 during the cooling operation, and further connects the suction pipe 31 of the compressor 21 and the second gas refrigerant. It is connected to the pipe 34 (see the solid line of the four-way switching valve 22 in FIG. 1).

Further, the four-way switching valve 22 switches to a heating cycle state in which the outdoor heat exchanger 23 functions as a refrigerant evaporator and the indoor heat exchanger 41 functions as a refrigerant radiator during the heating operation. ..

The four-way switching valve 22 connects the discharge pipe 32 of the compressor 21 and the second gas refrigerant pipe 34 during the heating operation, and further connects the suction pipe 31 of the compressor 21 and the first gas refrigerant of the outdoor heat exchanger 23. It is connected to the pipe 33 (see the broken line of the four-way switching valve 22 in FIG. 1).

Here, the first gas refrigerant pipe 33 is a refrigerant pipe that connects the four-way switching valve 22 and the refrigerant inlet during the cooling operation of the outdoor heat exchanger 23. The second gas refrigerant pipe 34 is a refrigerant pipe that connects the four-way switching valve 22 and the gas side closing valve 28.

(1-2-3) Outdoor heat exchanger 23
The outdoor heat exchanger 23 functions as a radiator of the refrigerant during the cooling operation. Further, the outdoor heat exchanger 23 functions as a refrigerant evaporator during the heating operation. One end of the liquid refrigerant pipe 35 is connected to the refrigerant outlet during the cooling operation of the outdoor heat exchanger 23. The other end of the liquid refrigerant pipe 35 is connected to the expansion valve 26.

The details of the outdoor heat exchanger 23 will be described in the chapter [(3) Detailed structure of the outdoor heat exchanger 23].

(1-2-4) Expansion valve 26
The expansion valve 26 is an electric expansion valve. The expansion valve 26 decompresses the high-pressure refrigerant sent from the outdoor heat exchanger 23 to a low pressure during the cooling operation. Further, the expansion valve 26 reduces the high-pressure refrigerant sent from the indoor heat exchanger 41 to a low pressure during the heating operation.

(1-2-5) Liquid side closing valve 27 and gas side closing valve 28
The liquid side closing valve 27 is connected to the liquid refrigerant connecting pipe 5. The gas side closing valve 28 is connected to the gas refrigerant connecting pipe 6. The liquid side closing valve 27 is located downstream of the expansion valve 26 in the refrigerant circulation direction during the cooling operation. The gas side closing valve 28 is located upstream of the four-way switching valve 22 in the refrigerant circulation direction during cooling operation.

(1-2-6) Outdoor fan The outdoor unit 2 includes an outdoor fan 36. The outdoor fan 36 sucks outdoor air into the outdoor unit 2, exchanges heat with the refrigerant in the outdoor heat exchanger 23, and then discharges the air to the outside. A propeller fan or the like is adopted as the outdoor fan 36. The outdoor fan 36 is driven by the outdoor fan motor 37.

(1-2-7) Outdoor control unit 38
The outdoor control unit 38 controls the operation of each unit constituting the outdoor unit 2. The outdoor control unit 38 has a microcomputer and a memory for controlling the outdoor unit 2.

The outdoor control unit 38 transmits and receives a control signal and the like via the transmission line 8a to and from the indoor control unit 44 of the indoor unit 4.

(1-3)

Refrigerant connecting pipes

5 and 6
The refrigerant connecting

pipes

5 and 6 are refrigerant pipes to be installed on-site when the air conditioner 1 is installed at an installation location such as a building. As the refrigerant connecting

pipes

5 and 6, pipes having an appropriate length and diameter are adopted according to the installation location and the installation conditions such as the combination of the outdoor unit 2 and the indoor unit 4.

(2) Basic operation of the air conditioner Next, the basic operation of the air conditioner 1 will be described with reference to FIG. The air conditioner 1 can perform a cooling operation and a heating operation as basic operations.

(2-1) Cooling operation During the cooling operation, the four-way switching valve 22 is switched to the cooling cycle state (the state shown by the solid line in FIG. 1). In the refrigerant circuit 10, the low-pressure gas refrigerant in the refrigeration cycle is sucked into the compressor 21, compressed, and then discharged.

The high-pressure gas refrigerant discharged from the compressor 21 is sent to the outdoor heat exchanger 23 via the four-way switching valve 22.

The high-pressure gas refrigerant sent to the outdoor heat exchanger 23 exchanges heat with the outdoor air supplied from the outdoor fan 36 in the outdoor heat exchanger 23 that functions as a radiator to dissipate heat, and is a high-pressure liquid refrigerant. become. The high-pressure liquid refrigerant is sent to the expansion valve 26.

The high-pressure liquid refrigerant sent to the expansion valve 26 is depressurized to the low pressure of the refrigeration cycle by the expansion valve 26 to become a low-pressure gas-liquid two-phase state refrigerant. The low-pressure gas-liquid two-phase refrigerant decompressed by the expansion valve 26 is sent to the indoor heat exchanger 41 via the liquid-side closing valve 27 and the liquid-refrigerant connecting pipe 5.

The low-pressure gas-liquid two-phase refrigerant sent to the indoor heat exchanger 41 evaporates by exchanging heat with the indoor air supplied from the indoor fan 42 in the indoor heat exchanger 41. As a result, the indoor air is cooled, and then the cooled air is supplied to the room to cool the room.

The low-pressure gas refrigerant evaporated in the indoor heat exchanger 41 is sucked into the compressor 21 again via the gas refrigerant connecting pipe 6, the gas side closing valve 28, and the four-way switching valve 22.

(2-2) Heating operation During the heating operation, the four-way switching valve 22 is switched to the heating cycle state (the state shown by the broken line in FIG. 1). In the refrigerant circuit 10, the low-pressure gas refrigerant in the refrigeration cycle is sucked into the compressor 21, compressed, and then discharged.

The high-pressure gas refrigerant discharged from the compressor 21 is sent to the indoor heat exchanger 41 via the four-way switching valve 22, the gas side closing valve 28, and the gas refrigerant connecting pipe 6.

The high-pressure gas refrigerant sent to the indoor heat exchanger 41 exchanges heat with the indoor air supplied from the indoor fan 42 in the indoor heat exchanger 41 to dissipate heat, and becomes a high-pressure liquid refrigerant. As a result, the room air is heated, and then the heated air is supplied to the room to heat the room.

The high-pressure liquid refrigerant radiated by the indoor heat exchanger 41 is sent to the expansion valve 26 via the liquid refrigerant connecting pipe 5 and the liquid side closing valve 27.

The high-pressure liquid refrigerant sent to the expansion valve 26 is depressurized to the low pressure of the refrigeration cycle by the expansion valve 26 to become a low-pressure gas-liquid two-phase state refrigerant. The low-pressure gas-liquid two-phase refrigerant decompressed by the expansion valve 26 is sent to the outdoor heat exchanger 23.

The low-pressure gas-liquid two-phase refrigerant sent to the outdoor heat exchanger 23 exchanges heat with the outdoor air supplied from the outdoor fan 36 in the outdoor heat exchanger 23 to evaporate, and is a low-pressure gas refrigerant. become.

The low-pressure refrigerant evaporated in the outdoor heat exchanger 23 is sucked into the compressor 21 again through the four-way switching valve 22.

(3) Detailed Description of Outdoor Heat Exchanger 23 (3-1) Structure FIG. 3 is an external perspective view of the outdoor heat exchanger 23. In FIG. 3, the outdoor heat exchanger 23 is a laminated heat exchanger. The outdoor heat exchanger 23 includes a plurality of flat tubes 231 and a plurality of heat transfer fins 232.

(3-1-1) Flat tube 231
The flat tube 231 is a multi-hole tube. The flat tube 231 is formed of aluminum or an aluminum alloy, and has a flat surface portion 231a serving as a heat transfer surface and a plurality of internal flow paths 231b through which a refrigerant flows.

The flat pipes 231 are arranged in a plurality of stages so as to be stacked with a space (ventilation space) in a state where the flat surface portion 231a is directed vertically.

(3-1-2) Heat transfer fin 232
The heat transfer fin 232 is a fin made of aluminum or an aluminum alloy. The heat transfer fins 232 are arranged in a ventilation space sandwiched between vertically adjacent flat tubes 231 and are in contact with the flat surface portion 231 a of the flat tubes 231.

The heat transfer fin 232 is formed with a notch 232c (see FIGS. 5A and 5B) into which the flat tube 231 is inserted. After the flat tube 231 is inserted into the notch 232c of the heat transfer fin 232, the heat transfer fin 232 and the flat surface portion 231a of the flat tube 231 are joined by brazing or the like.

(3-1-3)

Header

233a, 233b
The

headers

233a and 233b are connected to both ends of the flat tubes 231 arranged in a plurality of stages in the vertical direction. The

headers

233a and 233b have a function of supporting the flat pipe 231, a function of guiding the refrigerant to the internal flow path of the flat pipe 231, and a function of collecting the refrigerant coming out of the internal flow path.

When the outdoor heat exchanger 23 functions as an evaporator of the refrigerant, the refrigerant flows into the first header 233a. The refrigerant that has flowed into the first header 233a is distributed substantially evenly to each internal flow path of the flat pipe 231 of each stage, and flows toward the second header 233b. The refrigerant flowing through each internal flow path of the flat pipe 231 at each stage absorbs heat from the air flow flowing through the ventilation space via the heat transfer fins 232. The refrigerant flowing through each internal flow path of the flat pipe 231 of each stage collects at the second header 233b and flows out from the second header 233b.

When the outdoor heat exchanger 23 functions as a radiator of the refrigerant, the refrigerant flows into the second header 233b. The refrigerant that has flowed into the second header 233b is distributed substantially evenly to each internal flow path of the flat pipe 231 of each stage, and flows toward the first header 233a. The refrigerant flowing through each internal flow path of the flat tube 231 of each stage dissipates heat to the air flow flowing through the ventilation space via the heat transfer fins 232. The refrigerant flowing through each internal flow path of the flat pipe 231 of each stage collects in the first header 233a and flows out from the first header 233a.

(3-2) Suppression of frost formation FIG. 4 is a PH diagram of a non-azeotropic mixed refrigerant. In FIG. 4, the refrigerant temperature rises toward the evaporator outlet. Since the non-cobo-boiling mixed refrigerant has different compositions in the liquid phase and the vapor phase, there is a "temperature gradient" in which the evaporation start temperature and the end temperature in the evaporator are different. Due to this temperature gradient, the inlet temperature of the evaporator tends to drop, and frost tends to form during the heating operation.

FIG. 5A is a perspective view of the first heat exchange section 23a of the outdoor heat exchanger 23 according to the first embodiment. In FIG. 5A, in the first heat exchange portion 23a, the opening side of the notch 232c is located leeward in the air flow direction.

FIG. 5B is a perspective view of the second heat exchange section 23b of the outdoor heat exchanger 23 according to the first embodiment. In FIG. 5B, the opening side of the notch 232c is located upwind in the air flow direction.

In the second heat exchange section 23b shown in FIG. 5B, since the opening of the notch 232c is located on the windward side in the air flow direction, the temperature difference between the air temperature and the surface of the heat exchanger is large, and the heat exchange performance is high. Although it improves, it has the characteristic of being easily frosted.

On the other hand, in the first heat exchange section 23a shown in FIG. 5A, since the opening of the notch 232c is located leeward in the air flow direction, the air temperature and the surface of the heat exchanger are compared with those of the second heat exchange section 23b. Since the temperature difference with is small, frost formation is suppressed.

Therefore, in the present embodiment, the first heat exchange portion 23a is formed on the inlet side of the outdoor heat exchanger 23 that functions as an evaporator.

(3-3) Improvement of heat exchange performance As described above, in the first heat exchange unit 23a, the temperature difference between the air temperature and the surface of the heat exchanger is smaller than that in the second heat exchange unit 23b, so that the heat exchange performance Decreases. Therefore, it is not preferable in terms of performance that the entire outdoor heat exchanger 23 is composed of the first heat exchanger 23a.

Therefore, in the present embodiment, the first heat exchange unit 23a and the second heat exchange unit 23b are used in combination to suppress frost formation and improve the heat exchange performance.

FIG. 6A is a schematic perspective view of the outdoor heat exchanger 23 in which the first heat exchange unit 23a and the second heat exchange unit 23b are used in combination. Further, FIG. 6B is a schematic perspective view of another outdoor heat exchanger 23'using the first heat exchange unit 23a'and the second heat exchange unit 23b' in combination.

In FIG. 6A, when the outdoor heat exchanger 23 functions as an evaporator of the refrigerant, the refrigerant flowing into the first header 233a is distributed substantially evenly to each internal flow path 231b of the flat pipe 231 of each stage. It flows toward the second header 233b. The non-azeotropic mixed refrigerant tends to lower the temperature at the inlet of the evaporator and easily frost. Therefore, a certain section from the first header 233a to the second header 233b is composed of the first heat exchange section 23a to suppress frost formation.

On the other hand, since the temperature of the non-co-boiling mixed refrigerant rises toward the evaporator outlet, the portion between the first heat exchange section 23a and the second header 233b is the second heat exchange section in order to improve the heat exchange performance. It is composed of 23b.

By arranging the first heat exchange unit 23a on the inlet side of the evaporator and the second heat exchange unit 23b on the outlet side of the evaporator in this way, it is possible to improve the heat exchange performance while suppressing frost formation. it can.

Further, in FIG. 6B, when the outdoor heat exchanger 23'functions as an evaporator of the refrigerant, the refrigerant flowing into the lower stage of the first header 233a' flows into each internal flow path of the flat pipe 231 in each lower stage. It is distributed almost evenly to 231b'and flows toward the second header 233b'.

The refrigerant that has reached the lower stage of the second header 233b'collects once, passes through the bent pipe 234, and flows into the upper stage of the second header 233b'. After that, the refrigerant is distributed substantially evenly to each internal flow path 231b of the flat pipe 231 in each upper stage, and flows toward the second header 233b'.

The non-azeotropic mixed refrigerant tends to lower the temperature at the evaporator inlet and easily frost. Therefore, the section from the lower part of the first header 233a'to the lower part of the second header 233b' is composed of the first heat exchange section 23a'to suppress frost formation.

On the other hand, since the temperature of the non-co-boiling mixed refrigerant rises toward the evaporator outlet, the second heat is formed in the section from the upper stage of the first header 233b'to the upper stage of the first header 233a' in order to improve the heat exchange performance. It is composed of a replacement unit 23b'.

By arranging the first heat exchange unit 23a'on the evaporator inlet side and the second heat exchange unit 23b' on the evaporator outlet side in this way, the heat exchange performance is improved while suppressing frost formation. be able to.

(4) Features (4-1)
In the first heat exchange section 23a of the outdoor heat exchanger 23, the opening side of the notch 232c of the heat transfer fin 232 is located leeward in the air flow direction. When the outdoor heat exchanger 23 functions as an evaporator, the frost formation resistance (ability to suppress frost formation) is increased by arranging the non-azeotropic mixed refrigerant so that the inlet side becomes the first heat exchange portion 23a. Can be done.

(4-2)
Further, the first heat exchange section 23a is arranged on the inlet side of the non-co-boiling mixed refrigerant, and the second heat exchange section 23b in which the opening of the notch 232c is located on the windward side in the air flow direction is arranged on the outlet side. By doing so, it is possible to improve the heat exchange performance while suppressing frost formation.

(4-3)
The first heat exchange unit 23a and the second heat exchange unit 23b are integrated.

(5) Modification Example The first heat exchange section 23a is arranged on the inlet side of the outdoor heat exchanger 23 that functions as an evaporator, the second heat exchange section 23b is placed on the outlet side, and the first heat exchange section 23a and the first A third heat exchange unit 23c may be arranged between the two heat exchange units 23b.

In the third heat exchange unit 23c, the distribution center of the flat tube 231 in the width direction coincides with the center of the heat transfer fin 232 in the air flow direction.

The technical significance of this modification is that it is possible to attempt a combination of heat exchange units suitable for the refrigerant temperature in the outdoor heat exchanger 23 that functions as an evaporator, and as a result, heat exchange is performed while suppressing frost formation. Performance can be improved.

Note that the first heat exchange unit 23a and at least one of the second heat exchange unit 23b and the third heat exchange unit 23c may be integrated.

<Second Embodiment>
In the first embodiment, as the outdoor heat exchanger 23, a laminated heat exchanger in which the flat tube 231 is inserted into the notch 232c provided in the heat transfer fin 232 is adopted.

In the second embodiment, as the outdoor heat exchanger 23, a laminated heat exchanger in which a flat tube is penetrated through an elongated hole provided in a heat transfer fin is adopted.

(1) Suppression of Frost Formation FIG. 7A is a perspective view of the first heat exchange section 123a of the outdoor heat exchanger 23 according to the second embodiment. In FIG. 7A, in the first heat exchange portion 123a, the distance from the windward end of the flat tube 231M located on the windward side of the air flow direction to the windward end of the heat transfer fin 232M is the first dimension D1. is there.

FIG. 7B is a perspective view of the second heat exchange unit 123b of the outdoor heat exchanger 23 according to the second embodiment. In FIG. 7B, in the second heat exchange unit 123b, the distance from the windward end of the flat tube 231M located on the windward side of the air flow direction to the windward end of the heat transfer fin 232M is from the first dimension D1. Is also a small second dimension D2.

The second heat exchange portion 123b shown in FIG. 7B is the distance from the wind-up end of the flat tube 231M located on the most upwind side in the air flow direction to the wind-up end of the heat transfer fin 232M (second dimension D2). However, since it is smaller than the distance (first dimension D1) in the first heat exchange section 123a, the temperature difference between the air temperature and the surface of the heat exchanger is large, and the heat exchange performance is improved, but frost is easily formed. have.

On the other hand, in the first heat exchange portion 123a shown in FIG. 7A, the distance from the windward end of the flat tube 231M located on the windward side of the air flow direction to the windward end of the heat transfer fin 232M is the second heat. Since it is larger than the distance (second dimension D2) in the exchange unit 123b, the temperature difference between the air temperature and the heat exchanger surface is smaller than that in the second heat exchange unit 123b, and frost formation is suppressed.

Therefore, in the second embodiment, the first heat exchange section 123a is formed on the inlet side of the outdoor heat exchanger 23 that functions as an evaporator.

(2) Improvement of heat exchange performance As described above, in the first heat exchange unit 123a, the temperature difference between the air temperature and the surface of the heat exchanger is smaller than that in the second heat exchange unit 123b, so that the heat exchange performance is deteriorated. To do. Therefore, it is not preferable in terms of performance that the entire outdoor heat exchanger 23 is composed of the first heat exchanger 123a.

Therefore, in the second embodiment, similarly to the first embodiment, the first heat exchange unit 123a and the second heat exchange unit 123b are used in combination to suppress frost formation and improve the heat exchange performance. There is. In FIGS. 6A and 6B, the first heat exchange unit 23a of the first embodiment is replaced with the “first heat exchange unit 123a”, and the second heat exchange unit 23b of the first embodiment is replaced with the “second heat exchange unit 123b”. By substituting with, it is also applied in the second embodiment.

In FIG. 6A, when the outdoor heat exchanger 23 functions as an evaporator of the refrigerant, the refrigerant flowing into the first header 233a is distributed substantially evenly to each internal flow path of the flat pipe of each stage, and the second It flows toward the header 233b. The non-azeotropic mixed refrigerant tends to lower the temperature at the inlet of the evaporator and easily frost. Therefore, a certain section from the first header 233a to the second header 233b is composed of the first heat exchange unit 123a to suppress frost formation.

On the other hand, since the temperature of the non-co-boiling mixed refrigerant rises toward the evaporator outlet, the portion between the first heat exchange section 123a and the second header 233b is the second heat exchange section in order to improve the heat exchange performance. It is composed of 123b.

By arranging the first heat exchange unit 123a on the inlet side of the evaporator and the second heat exchange unit 123b on the outlet side of the evaporator in this way, it is possible to improve the heat exchange performance while suppressing frost formation. it can.

(3) Features of the second embodiment (3-1)
Since the temperature of the non-azeotropic mixed refrigerant rises from the inlet to the outlet of the evaporator, it is necessary to emphasize the frost bearing capacity (ability to suppress frost formation) on the inlet side and the heat exchange performance on the outlet side. preferable.

Therefore, the first heat exchange unit 123a is arranged on the inlet side of the outdoor heat exchanger 23 that functions as an evaporator, and the second heat exchange unit 123b is arranged on the outlet side, which is a combination suitable for the refrigerant temperature in the evaporator. Can be tried.

(3-2)
The first heat exchange unit 123a and the second heat exchange unit 123b are integrated.

(4) Modification Example The first heat exchange unit 123a is arranged on the inlet side of the outdoor heat exchanger 23 that functions as an evaporator, the second heat exchange unit 123b is arranged on the outlet side, and the first heat exchange unit 123a and the first heat exchanger unit 123a are arranged. A third heat exchange unit may be arranged between the two heat exchange units 123b.

FIG. 7C is a perspective view of the third heat exchange unit 123c of the outdoor heat exchanger 23 according to the modified example of the second embodiment. In FIG. 7C, the third heat exchange unit 123c has a distance D3 from the windward end of the flat tube 231M located on the windward side of the air flow direction to the windward end of the heat transfer fin 232M, and the air flow. The distance from the leeward end of the flat tube 231M located most leeward in the direction to the leeward end of the heat transfer fin 232M is equal.

Note that the first heat exchange unit 123a and at least one of the second heat exchange unit 123b and the third heat exchange unit 123c may be integrated.

<Third Embodiment>
In the first embodiment and the second embodiment, a laminated heat exchanger was adopted as the outdoor heat exchanger 23. In the third embodiment, a cross fin type heat exchanger is adopted as the outdoor heat exchanger 23.

(1) Suppression of Frost Frost FIG. 8A is a perspective view of the first heat exchange section 223a of the outdoor heat exchanger 23 according to the third embodiment. In FIG. 8A, in the first heat exchange unit 223a, when a plurality of heat transfer tubes 231N are viewed from the plate thickness direction of the heat transfer fins 232N as a heat transfer tube group, the distribution center of the heat transfer tube group in the air flow direction is the air. It is located leeward of the center of the heat transfer fin 232N in the flow direction.

FIG. 8B is a perspective view of the second heat exchange section 223b of the outdoor heat exchanger 23 according to the third embodiment. In FIG. 8B, in the second heat exchange section 223b, the distribution center of the heat transfer tube group in the air flow direction is located on the windward side of the center of the heat transfer fin 232N in the air flow direction.

In the second heat exchange section 223b shown in FIG. 8B, since the distribution center of the heat transfer tube group is located on the windward side of the center of the heat transfer fin 232N in the air flow direction, it is the most upwind in the air flow direction. The distance from the wind-up end of the located heat transfer tube 231N to the wind-up end of the heat transfer fins 232N is smaller than the distance at the first heat exchange section 223a, resulting in air temperature and heat exchanger surface. The heat exchange performance is improved due to the large temperature difference between the air and the air, but it has the characteristic of being easily frosted.

On the other hand, in the first heat exchange unit 223a shown in FIG. 8A, since the distribution center of the heat transfer tube group in the air flow direction is located leeward of the center of the heat transfer fin 232N in the air flow direction, the air The distance from the wind-up end of the heat transfer tube 231N located most upwind in the flow direction to the wind-up end of the heat transfer fins 232N is larger than the distance in the second heat exchange section 223b, and as a result, the first 2 Compared with the heat exchange unit 223b, the temperature difference between the air temperature and the surface of the heat exchanger is small, and frost formation is suppressed.

Therefore, in the third embodiment, the first heat exchange section 223a is formed on the inlet side of the outdoor heat exchanger 23 that functions as an evaporator.

(2) Improvement of heat exchange performance As described above, in the first heat exchange unit 223a, the temperature difference between the air temperature and the surface of the heat exchanger is smaller than that in the second heat exchange unit 223b, so that the heat exchange performance is deteriorated. To do. Therefore, it is not preferable in terms of performance that the entire outdoor heat exchanger 23 is composed of the first heat exchanger 223a.

Therefore, in the third embodiment, similarly to the first embodiment and the second embodiment, the first heat exchange unit 223a and the second heat exchange unit 223b are used in combination to suppress frost formation and perform heat exchange performance. We are trying to improve. In FIGS. 6A and 6B, the first heat exchange unit 23a of the first embodiment is replaced with the “first heat exchange unit 223a”, and the second heat exchange unit 23b of the first embodiment is replaced with the “second heat exchange unit 223b”. By substituting with, it is also applied in the third embodiment.

In FIG. 6A, when the outdoor heat exchanger 23 functions as an evaporator of the refrigerant, the refrigerant flowing into the first header 233a is distributed substantially evenly to the heat transfer tubes of each stage and toward the second header 233b. It flows. The non-azeotropic mixed refrigerant tends to lower the temperature at the inlet of the evaporator and easily frost. Therefore, a certain section from the first header 233a to the second header 233b is composed of the first heat exchange section 223a to suppress frost formation.

On the other hand, since the temperature of the non-co-boiling mixed refrigerant rises toward the evaporator outlet, the portion between the first heat exchange section 223a and the second header 233b is the second heat exchange section in order to improve the heat exchange performance. It is composed of 223b.

By arranging the first heat exchange unit 223a on the evaporator inlet side and the second heat exchange unit 223b on the evaporator outlet side in this way, it is possible to improve the heat exchange performance while suppressing frost formation. it can.

(3) Features of the third embodiment (3-1)
Since the temperature of the non-azeotropic mixed refrigerant rises from the inlet to the outlet of the evaporator, it is necessary to emphasize the frost bearing capacity (ability to suppress frost formation) on the inlet side and the heat exchange performance on the outlet side. preferable.

Therefore, the first heat exchange unit 223a is arranged on the inlet side of the outdoor heat exchanger 23 that functions as an evaporator, and the second heat exchange unit 223b is arranged on the outlet side, which is a combination suitable for the refrigerant temperature in the evaporator. Can be tried.

(3-2)
The first heat exchange unit 223a and the second heat exchange unit 223b are integrated.

(4) Modification example The first heat exchange unit 23a is arranged on the inlet side of the outdoor heat exchanger 23 that functions as an evaporator, the second heat exchange unit 23b is arranged on the outlet side, and the first heat exchange units 223a and the first A third heat exchange unit may be arranged between the two heat exchange units 223b.

FIG. 8C is a perspective view of the third heat exchange section 223c of the outdoor heat exchanger 23 according to the modified example of the third embodiment. In FIG. 8C, in the third heat exchange unit 223c, the distribution center of the heat transfer tube group in the air flow direction coincides with the center of the fin in the air flow direction.

Note that the first heat exchange unit 223a and at least one of the second heat exchange unit 223b and the third heat exchange unit 223c may be integrated.

<Others>
In each of the above embodiments, it is stated that the non-azeotropic mixed refrigerant contains any one of HFC refrigerant, HFO refrigerant, CF3I, and natural refrigerant, but more specifically, the following (A) to (G) A non-azeotropic mixed refrigerant corresponding to any of them is desirable.

(A)
A non-azeotropic mixed refrigerant containing any of R32, R1132 (E), R1234yf, R1234ze, CF3I and CO2.

(B)
A non-azeotropic mixed refrigerant containing at least R1132 (E), R32, and R1234yf.

(C)
A non-azeotropic mixed refrigerant containing at least R1132 (E), R1123 and R1234yf.

(D)
A non-azeotropic mixed refrigerant containing at least R1132 (E) and R1234yf.

(E)
A non-azeotropic mixed refrigerant containing at least R32, R1234yf, and at least one of R1132a and R1114.

(F)
A non-azeotropic mixed refrigerant containing at least R32, CO2, R125, R134a, and R1234yf.

(G)
A non-azeotropic mixed refrigerant containing at least R1132 (Z) and R1234yf.

Although the embodiments of the present disclosure have been described above, it will be understood that various modifications of the forms and details are possible without departing from the purpose and scope of the present disclosure described in the claims. ..

The present disclosure is widely applicable to a refrigerating apparatus capable of performing a cooling operation and a heating operation.

1 Air conditioner (refrigerator)
23 Outdoor heat exchanger (evaporator)
23a 1st heat exchange part 23b 2nd heat exchange part 23c 3rd heat exchange part 123a 1st heat exchange part 123b 2nd heat exchange part 123c 3rd heat exchange part 223a 1st heat exchange part 223b 2nd heat exchange part 223c 3 Heat exchange section 231 Flat tube (heat transfer tube)
231M flat tube (heat transfer tube)
231N Heat Transfer Tube 232 Heat Transfer Fin 232c Notch 232M Heat Transfer Fin 232N Heat Transfer Fin

WO2017 / 183180

Claims

An evaporator of a refrigeration cycle device in which a non-azeotropic mixed refrigerant is sealed.
Multiple fins (232) lined up at predetermined intervals in the plate thickness direction,
A plurality of heat transfer tubes (231) penetrating the plurality of fins in the plate thickness direction,
With
When the plurality of heat transfer tubes are viewed from the thickness direction of the fins as a heat transfer tube group, the distribution center of the heat transfer tube group in the air flow direction is located leeward of the center of the fins in the air flow direction. The first heat exchange section (23a) is formed.
Evaporator.
A second heat exchange portion (23b) is further formed in which the distribution center of the heat transfer tube group is located on the windward side of the center of the fin in the air flow direction.
The evaporator according to claim 1.
A third heat exchange portion is further formed in which the distribution center of the heat transfer tube group coincides with the center of the fin in the air flow direction.
The evaporator according to claim 2.
The first heat exchange unit and the second heat exchange unit are integrated.
The evaporator according to claim 2.
The first heat exchange unit, at least one of the second heat exchange unit and the third heat exchange unit is integrated.
The evaporator according to claim 3.
An evaporator of a refrigeration cycle device in which a non-azeotropic mixed refrigerant is sealed.
Multiple fins (232) lined up at predetermined intervals in the plate thickness direction,
A plurality of heat transfer tubes (231) penetrating the plurality of fins in the plate thickness direction,
With
The first heat exchange section (23a), in which the distance from the windward end of the heat transfer tube located most upwind in the air flow direction to the windward end of the fin is the first dimension,
The second heat exchange section (23b), which is the second dimension in which the distance from the windward end of the heat transfer tube located most upwind in the air flow direction to the windward end of the fin is smaller than the first dimension. When,
Is formed,
Evaporator.
The distance from the windward end of the heat transfer tube located most upwind in the air flow direction to the windward end of the fin,
The distance from the leeward end of the heat transfer tube located on the leeward side of the air flow direction to the leeward end of the fin,
Are equal, a third heat exchange is further formed,
The evaporator according to claim 6.
The first heat exchange unit and the second heat exchange unit are integrated.
The evaporator according to claim 6.
The first heat exchange unit, at least one of the second heat exchange unit and the third heat exchange unit is integrated.
The evaporator according to claim 7.
An evaporator of a refrigeration cycle device in which a non-azeotropic mixed refrigerant is sealed.
Multiple fins (232) lined up at predetermined intervals in the plate thickness direction,
A plurality of heat transfer tubes (231) penetrating the plurality of fins in the plate thickness direction,
With
The fin has a plurality of notches (232c) arranged in a direction orthogonal to both the air flow direction and the plate thickness direction.
The heat transfer tube is a flat multi-hole tube that is inserted into the notch.
A first heat exchange portion (23a) is formed, in which the opening side of the notch is located leeward in the air flow direction.
Evaporator.
A second heat exchange portion (23b) is further formed, in which the opening side of the notch is located upwind of the air flow direction.
The evaporator according to claim 10.
The first heat exchange unit and the second heat exchange unit are integrated.
The evaporator according to claim 11.
The evaporator according to any one of claims 1 to 12 is provided.
The non-azeotropic mixed refrigerant contains any of an HFC refrigerant, an HFO refrigerant, CF3I, and a natural refrigerant.
Refrigeration cycle equipment.
The evaporator according to any one of claims 1 to 12 is provided.
The non-azeotropic mixed refrigerant contains any of R32, R1132 (E), R1234yf, R1234ze, CF3I and CO2.
Refrigeration cycle equipment.
The evaporator according to any one of claims 1 to 12 is provided.
The non-azeotropic mixed refrigerant contains at least R1132 (E), R32, and R1234yf.
Refrigeration cycle equipment.
The evaporator according to any one of claims 1 to 12 is provided.
The non-azeotropic mixed refrigerant contains at least R1132 (E), R1123 and R1234yf.
Refrigeration cycle equipment.
The evaporator according to any one of claims 1 to 12 is provided.
The non-azeotropic mixed refrigerant contains at least R1132 (E) and R1234yf.
Refrigeration cycle equipment.
The evaporator according to any one of claims 1 to 12 is provided.
The non-azeotropic mixed refrigerant comprises at least R32, R1234yf, and at least one of R1132a and R1114.
Refrigeration cycle equipment.
The evaporator according to any one of claims 1 to 12 is provided.
The non-azeotropic mixed refrigerant contains at least R32, CO2, R125, R134a, and R1234yf.
Refrigeration cycle equipment.
The evaporator according to any one of claims 1 to 12 is provided.
The non-azeotropic mixed refrigerant contains at least R1132 (Z) and R1234yf.
Refrigeration cycle equipment.