JP7630622B2 - Heat exchanger and refrigeration cycle device - Google Patents

Description

This disclosure relates to a heat exchanger and a refrigeration cycle device.

Multi-rowing of heat transfer tubes has been proposed as a means of improving the performance of heat exchangers in refrigeration cycle equipment. Because heat exchangers are mounted in a limited space, multi-rowing can improve the mounting density of the heat transfer tubes and increase the heat transfer area. For example, the heat exchanger of an indoor unit of an air conditioner described in JP 2014-40983 A (Patent Document 1) has multi-rowed heat transfer tubes.

JP 2014-40983 A

When a non-azeotropic refrigerant is used in a heat exchanger with multiple rows of heat transfer tubes, a heat exchange loss occurs when the refrigerant flows parallel to the air flow due to the effect of temperature distribution in the non-azeotropic refrigerant. The direction of the refrigerant flowing through the heat exchanger is opposite when the heat exchanger functions as a condenser and when it functions as an evaporator. For this reason, the refrigerant flows parallel to the air flow in either the condenser or the evaporator. This results in a decrease in heat exchange efficiency in either the condenser or the evaporator.

The present disclosure has been made in consideration of the above-mentioned problems, and its purpose is to provide a heat exchanger and refrigeration cycle device that can ensure average heat exchange efficiency in the condenser and evaporator while using a non-azeotropic refrigerant mixture.

The heat exchanger of the present disclosure includes a first heat transfer section having a plurality of first heat transfer tubes, and a non-azeotropic refrigerant flowing through the plurality of first heat transfer tubes of the first heat transfer section. The plurality of first heat transfer tubes are arranged in a line. The first heat transfer section includes a plurality of first heat transfer tubes arranged so that the flow of the non-azeotropic refrigerant flowing through the plurality of first heat transfer tubes is perpendicular to the flow of air flowing through the first heat transfer section. The heat exchanger further includes a second heat transfer section having a plurality of second heat transfer tubes. The second heat transfer section is arranged so as to be adjacent to the first heat transfer section. The plurality of second heat transfer tubes are arranged in a line, and are arranged in a line along the direction in which the plurality of first heat transfer tubes are arranged. The non-azeotropic refrigerant flows through the plurality of second heat transfer tubes of the second heat transfer section. The second heat transfer section includes a plurality of second heat transfer tubes arranged so that the flow of the non-azeotropic refrigerant flowing through the plurality of second heat transfer tubes is perpendicular to the flow of air flowing through the second heat transfer section. The inlet and outlet of the non-azeotropic refrigerant of each of the first heat transfer section and the second heat transfer section are connected to the heat exchanger inlet and the heat exchanger outlet, respectively. The inlet and outlet of the non-azeotropic refrigerant of each of the first heat transfer section and the second heat transfer section are disposed on opposite sides to each other.

According to the heat exchanger disclosed herein, it is possible to ensure average heat exchange efficiency in the condenser and evaporator while using a non-azeotropic refrigerant mixture.

1 is a refrigerant circuit diagram of a refrigeration cycle device according to a first embodiment. FIG. 5A and 5B are diagrams illustrating a heat exchanger and a blowing temperature distribution according to the first embodiment. 1 is a perspective view showing a schematic configuration of a heat exchanger according to a first embodiment of the present invention; 2 is a cross-sectional view illustrating a first heat transfer tube and a second heat transfer tube of the heat exchanger according to the first embodiment. FIG. FIG. 2 is a perspective view showing a schematic configuration of a capillary tube of the heat exchanger according to the first embodiment. 10 is a cross-sectional view that illustrates a schematic modification of the first heat transfer tube and the second heat transfer tube of the heat exchanger according to the first embodiment. FIG. 1 is a cross-sectional view illustrating a first modified example of the heat exchanger according to the first embodiment. FIG. FIG. 11 is a front view illustrating a schematic configuration of a second modified example of the heat exchanger according to the first embodiment. FIG. 1 shows the heat exchange efficiency of counterflow, parallel flow, and crossflow in a condenser and an evaporator. 4 is a diagram showing the relationship between refrigerant flow and refrigerant temperature in a condenser and an evaporator of the heat exchanger according to the first embodiment. FIG. 13A and 13B are diagrams illustrating a heat exchanger and a blowing temperature distribution according to the second embodiment. FIG. 11 is a cross-sectional view illustrating a modified example of the heat exchanger according to the second embodiment. FIG. 11 is a diagram showing the relationship between the refrigerant flow and the refrigerant temperature in a condenser and an evaporator of a heat exchanger according to the second embodiment. 13A and 13B are diagrams illustrating a heat exchanger and a blowing temperature distribution according to the third embodiment. FIG. 11 is a cross-sectional view illustrating a first modified example of the heat exchanger according to the third embodiment. FIG. 11 is a cross-sectional view illustrating a schematic configuration of a second modified example of the heat exchanger according to the third embodiment. FIG. 11 is a diagram showing the relationship between refrigerant flow and temperature in a condenser and an evaporator of a heat exchanger according to embodiment 3.

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

Embodiment 1.
A configuration of a refrigeration cycle apparatus 100 according to a first embodiment will be described with reference to Fig. 1. In the first embodiment, an air conditioner will be described as an example of the refrigeration cycle apparatus 100. In Fig. 1, solid arrows indicate the flow of refrigerant during cooling operation. In Fig. 1, dashed arrows indicate the flow of refrigerant during heating operation.

As shown in Figure 1, the refrigeration cycle device 100 includes a compressor 1, a four-way valve 2, an outdoor heat exchanger 3, an expansion valve 4, an indoor heat exchanger 5, an outdoor blower 6, an indoor blower 7, and a control device 8. The heat exchanger HE according to embodiment 1 is applied to the outdoor heat exchanger 3. The refrigeration cycle device 100 includes an outdoor unit 101 and an indoor unit 102 connected to the outdoor unit 101.

The refrigerant circuit 10 includes a compressor 1, a four-way valve 2, an outdoor heat exchanger 3, an expansion valve 4, and an indoor heat exchanger 5. The compressor 1, the four-way valve 2, the outdoor heat exchanger 3, the expansion valve 4, and the indoor heat exchanger 5 are connected by piping 20. The refrigerant circuit 10 is configured to circulate a refrigerant.

The refrigerant is a non-azeotropic refrigerant mixture. The non-azeotropic refrigerant mixture includes R32 and may include R1234yf as another refrigerant. The non-azeotropic refrigerant mixture may include R1123 or R1234ze as another refrigerant. The non-azeotropic refrigerant mixture may also be a mixture of three or more types of refrigerants.

The compressor 1, four-way valve 2, outdoor heat exchanger 3, expansion valve 4, outdoor blower 6 and control device 8 are housed in the outdoor unit 101. The indoor heat exchanger 5 and indoor blower 7 are housed in the indoor unit 102. The outdoor unit 101 and the indoor unit 102 are connected by a gas pipe 21 and a liquid pipe 22. A part of the piping 20 constitutes the gas pipe 21 and the liquid pipe 22.

During cooling operation, the refrigerant circuit 10 is configured so that the refrigerant circulates in the order of the compressor 1, four-way valve 2, outdoor heat exchanger 3, expansion valve 4, indoor heat exchanger 5, and four-way valve 2. During heating operation, the refrigerant circuit 10 is configured so that the refrigerant circulates in the order of the compressor 1, four-way valve 2, indoor heat exchanger 5, expansion valve 4, outdoor heat exchanger 3, and four-way valve 2.

Compressor 1 is configured to compress the refrigerant. Compressor 1 is for compressing the non-azeotropic refrigerant that flows into heat exchanger HE. Compressor 1 is configured to compress the refrigerant that is sucked in and discharge it. Compressor 1 may be configured to have a variable capacity. Compressor 1 may be configured so that its capacity can be changed by adjusting the rotation speed of compressor 1 based on instructions from control device 8.

The four-way valve 2 is configured to switch the flow of the refrigerant compressed by the compressor 1 to the outdoor heat exchanger 3 or the indoor heat exchanger 5. The four-way valve 2 has a first port P1 to a fourth port P4. The first port P1 is connected to the discharge side of the compressor 1. The second port P2 is connected to the suction side of the compressor 1. The third port P3 is connected to the outdoor heat exchanger 3. The fourth port P4 is connected to the indoor heat exchanger 5. The four-way valve 2 is configured to flow the refrigerant discharged from the compressor 1 to the outdoor heat exchanger 3 during cooling operation. During cooling operation, the third port P3 is connected to the first port P1 in the four-way valve 2, and the fourth port P4 is connected to the second port P2. The four-way valve 2 is also configured to flow the refrigerant discharged from the compressor 1 to the indoor heat exchanger 5 during heating operation. During heating operation, in the four-way valve 2, the fourth port P4 is connected to the first port P1, and the third port P3 is connected to the second port P2.

The outdoor heat exchanger 3 is configured to exchange heat between the refrigerant flowing inside the outdoor heat exchanger 3 and the air flowing outside the outdoor heat exchanger 3. The outdoor heat exchanger 3 is configured to function as a condenser that condenses the refrigerant during cooling operation, and to function as an evaporator that evaporates the refrigerant during heating operation.

The expansion valve 4 is configured to reduce the pressure of the refrigerant condensed in the condenser by expanding it. The expansion valve 4 is configured to reduce the pressure of the refrigerant condensed by the outdoor heat exchanger 3 during cooling operation, and to reduce the pressure of the refrigerant condensed by the indoor heat exchanger 5 during heating operation. The expansion valve 4 is, for example, an electromagnetic expansion valve.

The indoor heat exchanger 5 is configured to exchange heat between the refrigerant flowing inside the indoor heat exchanger 5 and the air flowing outside the indoor heat exchanger 5. The indoor heat exchanger 5 is configured to function as an evaporator that evaporates the refrigerant during cooling operation, and as a condenser that condenses the refrigerant during heating operation.

The outdoor blower 6 is configured to blow outdoor air to the outdoor heat exchanger 3. In other words, the outdoor blower 6 is configured to supply air to the outdoor heat exchanger 3.

The indoor blower 7 is configured to blow indoor air to the indoor heat exchanger 5. In other words, the indoor blower 7 is configured to supply air to the indoor heat exchanger 5.

The control device 8 is configured to perform calculations, instructions, etc. to control each device of the refrigeration cycle device 100. The control device 8 is electrically connected to the compressor 1, four-way valve 2, expansion valve 4, outdoor blower 6, indoor blower 7, etc., and is configured to control the operation of these devices.

The configuration of the outdoor heat exchanger 3 to which the heat exchanger HE of embodiment 1 is applied will be described in detail with reference to Figures 2 to 5. The heat exchanger HE of embodiment 1 may also be applied to the indoor heat exchanger 5. Figure 2 shows the relationship between the structure of the heat exchanger HE and the air outlet temperature distribution. The solid arrows in Figure 3 indicate the flow of refrigerant, and the hollow arrows in Figure 3 indicate the flow of air.

As shown in Figures 2 and 3, in this embodiment, the outdoor heat exchanger 3 has a heat exchange section 31, a header distributor 32, a gas-liquid two-phase distributor 33, and a non-azeotropic refrigerant.

The heat exchange section 31 includes a first heat exchange section 31a and a second heat exchange section 31b. The first heat exchange section 31a is arranged on the windward side in the air flow direction D1. The first heat exchange section 31a is arranged in a first row in the air flow direction D1. The second heat exchange section 31b is arranged on the downwind side in the air flow direction D1. The second heat exchange section 31b is arranged in a second row in the air flow direction D1.

The first heat exchange section 31a includes a first heat transfer section HP1. In this embodiment, the first heat exchange section 31a includes a plurality of first heat transfer sections HP1. The second heat exchange section 31b includes a second heat transfer section HP2. In this embodiment, the second heat exchange section 31b includes a plurality of second heat transfer sections HP2.

The first heat exchange section 31a has a plurality of first fins F1, a plurality of first heat transfer tubes T1, and a plurality of first connection sections C1. Each of the plurality of first fins F1 is configured in a plate shape. The plurality of first fins F1 are arranged so as to overlap each other. The material of the plurality of first fins F1 is, for example, aluminum.

The multiple first heat transfer tubes T1 penetrate the multiple first fins F1. The multiple first heat transfer tubes T1 are configured to extend linearly in an orthogonal direction D2 perpendicular to the air flow direction D1. The multiple first connection parts C1 are parts that connect the first heat transfer tubes T1 to each other on the outside of the multiple first fins F1. Each of the multiple first heat transfer tubes T1 is connected by each of the multiple first connection parts C1, so that the multiple first heat transfer tubes T1 and the multiple first connection parts C1 are configured to meander as a whole. The multiple first heat transfer tubes T1 and the multiple first connection parts C1 are made of a material such as copper or aluminum.

The first heat transfer section HP1 has a plurality of first heat transfer tubes T1. The plurality of first heat transfer tubes T1 are arranged in a row. The plurality of first heat transfer tubes T1 are arranged in a row direction D3 that intersects the air flow direction D1 and the perpendicular direction D2.

The first heat transfer section HP1 has a plurality of first heat transfer tubes T1 arranged so that the flow of the non-azeotropic refrigerant flowing through the plurality of first heat transfer tubes T1 is perpendicular to the flow of air flowing through the first heat transfer section HP1.

The second heat exchange section 31b has a plurality of second fins F2, a plurality of second heat transfer tubes T2, and a plurality of second connection sections C2. Each of the plurality of second fins F2 is configured in a plate shape. The plurality of second fins F2 are arranged so as to overlap each other. The material of the plurality of second fins F2 is, for example, aluminum.

The second heat transfer tubes T2 penetrate the second fins F2. The second heat transfer tubes T2 are configured to extend linearly in the perpendicular direction D2 perpendicular to the air flow direction D1. The second connection parts C2 are portions that connect the second heat transfer tubes T2 to each other on the outside of the second fins F2. The second heat transfer tubes T2 are connected to each other by the second connection parts C2, so that the second heat transfer tubes T2 and the second connection parts C2 are configured to meander as a whole. The second heat transfer tubes T2 and the second connection parts C2 are made of a material such as copper or aluminum.

The second heat transfer section HP2 has a plurality of second heat transfer tubes T2. The second heat transfer section HP2 is arranged adjacent to the first heat transfer section HP1. The plurality of second heat transfer tubes T2 are arranged in a row. The plurality of second heat transfer tubes T2 are arranged in a row along the direction in which the plurality of first heat transfer tubes T1 are arranged. The plurality of second heat transfer tubes T2 are arranged in a row direction D3 that intersects the air flow direction D1 and the perpendicular direction D2.

The non-azeotropic refrigerant flows through the multiple first heat transfer tubes T1 of the first heat transfer section HP1. The non-azeotropic refrigerant flows continuously through the multiple first heat transfer tubes T1 and the multiple first connection sections C1. The non-azeotropic refrigerant flows through the multiple second heat transfer tubes T2 of the second heat transfer section HP2. The non-azeotropic refrigerant flows continuously through the multiple second heat transfer tubes T2 and the multiple second connection sections C2.

When the outdoor heat exchanger 3 functions as a condenser, a header distributor 32 is provided at the heat exchanger inlet (condenser inlet), and a gas-liquid two-phase distributor 33 is provided at the heat exchanger outlet (condenser outlet). The gas-liquid two-phase distributor 33 is configured to evenly distribute the gas-liquid two-phase flow. The gas-liquid two-phase distributor 33 has a distributor 33a and a capillary tube 34.

3 and 4, each of the first heat transfer tubes T1 and the first connection parts C1 is a circular tube. Each of the second heat transfer tubes T2 and the second connection parts C2 is a circular tube.

2 and 5, the capillary tube 34 includes a first capillary tube 34a connected to the first heat exchange section 31a of the first row and a second capillary tube 34b connected to the second heat exchange section 31b of the second row. The inner diameter of the first capillary tube 34a may be larger than the inner diameter of the second capillary tube 34b. The length of the first capillary tube 34a may be longer than the length of the second capillary tube 34b.

Referring to Figure 6, in a modified example of the first heat transfer tube T1 and the second heat transfer tube T2 of the heat exchanger HE of embodiment 1, the first heat transfer tube T1 and the second heat transfer tube T2 are flat tubes.

Next, with reference to Figures 1 to 3, the operation of the refrigeration cycle device 100 of embodiment 1 will be explained.

The refrigeration cycle device 100 can selectively perform cooling operation and heating operation. During cooling operation, the refrigerant circulates through the refrigerant circuit 10 in the order of compressor 1, four-way valve 2, outdoor heat exchanger 3, expansion valve 4, indoor heat exchanger 5, and four-way valve 2. During cooling operation, the outdoor heat exchanger 3 functions as a condenser. Heat exchange occurs between the refrigerant flowing through the outdoor heat exchanger 3 and the air blown by the outdoor blower 6. During cooling operation, the indoor heat exchanger 5 functions as an evaporator. Heat exchange occurs between the refrigerant flowing through the indoor heat exchanger 5 and the air blown by the indoor blower 7.

The high-pressure gas refrigerant discharged from the compressor 1 flows through the header distributor 32 of the heat exchanger HE into the first heat transfer tube T1 of the first heat exchange section 31a of the first row and the second heat transfer tube T2 of the second heat exchange section 31b of the second row, and flows perpendicular to the air flow. At this time, by making the flow resistance of the first capillary tube 34a installed on the outlet side of the first heat exchange section 31a smaller than the flow resistance of the second capillary tube 34b installed on the outlet side of the second heat exchange section 31b, more refrigerant flows into the first capillary tube 34a than into the second capillary tube 34b. The high-pressure gas refrigerant exchanges heat with the air through the multiple first fins F1, the multiple first heat transfer tubes T1, the multiple second fins F2, and the multiple second heat transfer tubes T2, and becomes a high-pressure liquid refrigerant.

During heating operation, the refrigerant circulates through the refrigerant circuit 10 in the following order: compressor 1, four-way valve 2, indoor heat exchanger 5, expansion valve 4, outdoor heat exchanger 3, and four-way valve 2. During heating operation, the indoor heat exchanger 5 functions as a condenser. Heat exchange occurs between the refrigerant flowing through the indoor heat exchanger 5 and the air blown by the indoor blower 7. During heating operation, the outdoor heat exchanger 3 functions as an evaporator. Heat exchange occurs between the refrigerant flowing through the outdoor heat exchanger 3 and the air blown by the outdoor blower 6.

The low-pressure gas-liquid two-phase refrigerant with low dryness is decompressed and stirred by the distributor 33a of the gas-liquid two-phase distributor 33 of the heat exchanger HE, and is distributed with equal dryness in a gas-liquid two-phase spray state. By making the flow resistance of the first capillary tube 34a connected to the first heat exchange section 31a of the first row smaller than the flow resistance of the second capillary tube 34b connected to the second heat exchange section 31b of the second row, more refrigerant flows through the first capillary tube 34a than through the second capillary tube 34b. The low-pressure gas-liquid two-phase refrigerant with low dryness exchanges heat with air through the multiple first fins F1, the multiple first heat transfer tubes T1, the multiple first fins F1, and the multiple second heat transfer tubes T2 to become a low-pressure gas refrigerant.

Next, we will explain a modified example of the outdoor heat exchanger 3 to which the heat exchanger HE of embodiment 1 is applied.

With reference to Fig. 7, in the first modified example of the outdoor heat exchanger 3 according to the first embodiment, multiple header distributors 32 and gas-liquid two-phase distributors 33 are arranged in each row. In the first modified example of the outdoor heat exchanger 3 according to the first embodiment, two header distributors 32 and two gas-liquid two-phase distributors 33 are arranged. Two electronic expansion valves 35 are arranged downstream of each of the two gas-liquid two-phase distributors 33.

In addition, when the electronic expansion valve 35 is not provided, the inner diameter of the first capillary tube 34a connected to the first heat exchange section 31a of the first row is made larger than the inner diameter of the second capillary tube 34b connected to the second heat exchange section 31b of the second row. Furthermore, the length of the first capillary tube 34a connected to the first heat exchange section 31a of the first row is made longer than the length of the second capillary tube 34b connected to the second heat exchange section 31b of the second row.

With reference to Figure 8, in the second modification of the outdoor heat exchanger 3 according to the first embodiment, only the first heat exchange section 31a is shown for ease of explanation. The second heat exchange section 31b is configured similarly to the first heat exchange section 31a.

In the second modification of the outdoor heat exchanger 3 according to the first embodiment, the first fins F1 are corrugated fins. The first heat transfer tubes T1 are straight flat tubes. Each of the first fins F1 is disposed between each of the first heat transfer tubes T1. A header 36 is connected to both ends of each of the first heat transfer tubes T1.

Next, the effects of this embodiment will be described.
The heat exchange efficiency of the counterflow, parallel flow, and cross flow of the condenser and evaporator will be described with reference to Fig. 9. Counterflow, parallel flow, and cross flow indicate the relationship of the refrigerant flow to the air flow. In both the condenser and the evaporator, the heat exchange efficiency decreases in the order of counterflow, cross flow, and parallel flow.

With reference to FIG. 10, the refrigerant temperature of each path relative to the refrigerant flow when the heat exchanger HE in this embodiment functions as a condenser or an evaporator will be described. In the condenser, the refrigerant temperature decreases in both the first and second rows as the refrigerant flow increases. The refrigerant temperature in the first row is lower than the refrigerant temperature in the second row. In the evaporator, the refrigerant temperature increases in both the first and second rows as the refrigerant flow increases. The refrigerant temperature in the first row is higher than the refrigerant temperature in the second row.

According to the heat exchanger HE of this embodiment, the first heat transfer section HP1 has a plurality of first heat transfer tubes T1 arranged so that the flow of the non-azeotropic refrigerant flowing through the plurality of first heat transfer tubes T1 is perpendicular to the flow of air flowing through the first heat transfer section HP1. Therefore, the flow of the non-azeotropic refrigerant relative to the air flow is a cross flow. This makes it possible to increase the heat exchange efficiency compared to a parallel flow when the heat exchanger HE functions as either a condenser or an evaporator. Therefore, it is possible to ensure an average heat exchange efficiency in the condenser and the evaporator while using a non-azeotropic refrigerant.

If both the condenser and evaporator were to be counter-flow evaporators, the following problems would arise. First, the pressure loss of the high-pressure gas refrigerant would increase in the condenser due to the gas-liquid two-phase distributor 33. Also, the amount of refrigerant would increase due to the large capacity of the outlet header. Furthermore, the pressure loss in the extension piping section would increase. With the heat exchanger HE of this embodiment, these problems do not occur.

In addition, by making the flow resistance of the first capillary tube 34a smaller than that of the second capillary tube 34b, more refrigerant can flow through the first heat transfer tube T1 in the first row, which has a larger heat load. This reduces the difference in refrigerant outlet temperature between the first heat transfer tube T1 in the first row and the second heat transfer tube T2 in the second row, thereby increasing the heat exchange efficiency.

According to the refrigeration cycle device 100 of this embodiment, the heat exchanger HE is provided. Therefore, it is possible to provide a refrigeration cycle device 100 equipped with a heat exchanger HE that can ensure average heat exchange efficiency in the condenser and evaporator while using a non-azeotropic refrigerant mixture.

Embodiment 2.
Unless otherwise specified, the heat exchanger HE according to the second embodiment has the same configuration, operation, and effects as the heat exchanger HE according to the first embodiment.

With reference to FIG. 11, in the heat exchanger HE according to embodiment 2, the inlets and outlets for the non-azeotropic refrigerant of the first heat transfer section HP1 and the second heat transfer section HP2 are arranged on opposite sides to each other. In the first heat transfer section HP1, the refrigerant inlet is arranged at the topmost stage, and the refrigerant outlet is arranged at the bottommost stage. In the second heat transfer section HP2, the refrigerant inlet is arranged at the bottommost stage, and the refrigerant outlet is arranged at the topmost stage. In other words, the inlets and outlets for the non-azeotropic refrigerant of the first heat transfer section HP1 and the second heat transfer section HP2 are arranged upside down to each other.

Next, we will explain a modified example of the outdoor heat exchanger 3 to which the heat exchanger HE of embodiment 2 is applied.

With reference to Fig. 12, in a modified example of the outdoor heat exchanger 3 according to embodiment 2, the heat exchange section 31 includes a third heat exchange section 31c. The third heat exchange section 31c is arranged on the windward side of the first heat exchange section 31a in the air flow direction D1. The third heat exchange section 31c is arranged in the first row in the air flow direction D1.

The third heat exchange section 31c includes a third heat transfer section HP3. In this embodiment, the third heat exchange section 31c includes a plurality of third heat transfer sections HP3. The third heat exchange section 31c has a plurality of third fins F3, a plurality of third heat transfer tubes T3, and a plurality of third connection sections C3 (not shown). The plurality of third fins F3, the plurality of third heat transfer tubes T3, and the plurality of third connection sections C3 (not shown) are configured in the same manner as the plurality of first fins F1, the plurality of first heat transfer tubes T1, and the plurality of first connection sections C1 (not shown). The non-azeotropic refrigerant flows through the plurality of third heat transfer tubes T3 of the third heat transfer section HP3. The non-azeotropic refrigerant flows continuously through the plurality of third heat transfer tubes T3 and the plurality of third connection sections C3 (not shown).

The capillary tube 34 includes a third capillary tube 34c connected to the third heat exchanger 31c. The inner diameter of the third capillary tube 34c may be larger than the inner diameter of the first capillary tube 34a. The length of the third capillary tube 34c may be longer than the length of the first capillary tube 34a.

Next, the effects of this embodiment will be described.
The refrigerant temperature of each path in the refrigerant flow when the heat exchanger HE in this embodiment functions as a condenser or an evaporator will be described with reference to Fig. 13. Compared to the first embodiment, the difference in refrigerant temperature between the first and second rows is smaller in both the condenser and the evaporator.

In the heat exchanger HE according to the present embodiment, the inlet and outlet of the non-azeotropic refrigerant of each of the first heat transfer section HP1 and the second heat transfer section HP2 are arranged on opposite sides of each other. This makes it possible to average the temperature distribution of the air blown out in the height direction of the heat exchanger HE.

Therefore, when the heat exchanger HE is applied to the outdoor heat exchanger 3, the amount of frost formed during low outdoor air temperatures is uniformized, improving the average heating capacity. In addition, when the heat exchanger HE is applied to the indoor heat exchanger 5, dew splashing is less likely to occur, improving comfort and quality performance.

Embodiment 3.
Unless otherwise specified, the heat exchanger HE according to the third embodiment has the same configuration, operation, and effects as the heat exchanger HE according to the first and second embodiments.

Referring to FIG. 14, in the heat exchanger HE according to the third embodiment, the first heat transfer section HP1 and the second heat transfer section HP2 have a first pass PS1 and a second pass PS2. The first pass PS1 is arranged so that the flow of the non-azeotropic refrigerant flowing through the plurality of first heat transfer tubes T1 and the plurality of second heat transfer tubes T2 is parallel to the flow of air flowing through the first heat transfer section HP1 and the second heat transfer section HP2. The second pass PS2 is arranged so that the flow of the non-azeotropic refrigerant flowing through the plurality of first heat transfer tubes T1 and the plurality of second heat transfer tubes T2 is opposed to the flow of air flowing through the first heat transfer section HP1 and the second heat transfer section HP2. The first pass PS1 and the second pass PS2 are combined.

Next, we will explain a modified example of the outdoor heat exchanger 3 to which the heat exchanger HE of embodiment 3 is applied.

Referring to Figure 15, in variant 1 of the outdoor heat exchanger 3 relating to embodiment 3, the inlet and outlet of the non-azeotropic refrigerant mixture of the first heat transfer section HP1 and the second heat transfer section HP2 are arranged on opposite sides to each other.

16, in the second modification of the outdoor heat exchanger 3 according to the third embodiment, the heat exchange section 31 includes a third heat exchange section 31c. The third heat exchange section 31c is disposed between the first heat exchange section 31a and the second heat exchange section 31b in the air flow direction D1.

Next, the effects of this embodiment will be described.
The refrigerant temperature of each path in the refrigerant flow when the heat exchanger HE in this embodiment functions as a condenser or an evaporator will be described with reference to Fig. 17. Compared to the first embodiment, the difference in refrigerant temperature between the first and second rows is smaller in both the condenser and the evaporator.

According to the heat exchanger HE of this embodiment, the first path PS1 is arranged so that the flow of the non-azeotropic refrigerant flowing through the first heat transfer tubes T1 and the second heat transfer tubes T2 is parallel to the flow of air flowing through the first heat transfer section HP1 and the second heat transfer section HP2. The second path PS2 is arranged so that the flow of the non-azeotropic refrigerant flowing through the first heat transfer tubes T1 and the second heat transfer tubes T2 is opposite to the flow of air flowing through the first heat transfer section HP1 and the second heat transfer section HP2. This makes it possible to further average the air blowing temperature distribution in the height direction of the heat exchanger HE. This further uniforms the heat load of each path, thereby improving the heat exchange efficiency.

Therefore, when the heat exchanger HE is applied to the outdoor heat exchanger 3, the amount of frost formed during low outdoor air temperatures is uniformized, improving the average heating capacity. In addition, when the heat exchanger HE is applied to the indoor heat exchanger 5, dew splashing is less likely to occur, improving comfort and quality performance.

Furthermore, even if an electronic expansion valve 35 is not installed as in embodiment 1, there is no need to adjust the inner diameter and length of the capillary tube 34.

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

1 Compressor, 2 Four-way valve, 3 Outdoor heat exchanger, 4 Expansion valve, 5 Indoor heat exchanger, 6 Outdoor blower, 7 Indoor blower, 8 Control device, 10 Refrigerant circuit, 31 Heat exchange section, 31a First heat exchange section, 31b Second heat exchange section, 31c Third heat exchange section, 32 Header distributor, 33 Gas-liquid two-phase distributor, 100 Refrigeration cycle device, HE Heat exchanger, HP1 First heat transfer section, HP2 Second heat transfer section, HP3 Third heat transfer section, PS1 First pass, PS2 Second pass, T1 First heat transfer tube, T2 Second heat transfer tube, T3 Third heat transfer tube.

Claims (3)

A first heat transfer section having a plurality of first heat transfer tubes;
a non-azeotropic refrigerant flowing through the first heat transfer tubes of the first heat transfer section,
The plurality of first heat transfer tubes are arranged in a row,
the first heat transfer section includes a plurality of first heat transfer tubes arranged such that a flow of the non-azeotropic refrigerant flowing through the plurality of first heat transfer tubes is perpendicular to a flow of air flowing through the first heat transfer section,
Further comprising a second heat transfer section having a plurality of second heat transfer tubes;
The second heat transfer portion is disposed adjacent to the first heat transfer portion,
The second heat transfer tubes are arranged in a row along a direction in which the first heat transfer tubes are arranged,
The non-azeotropic refrigerant mixture flows through the second heat transfer tubes of the second heat transfer section,
the second heat transfer section includes a plurality of second heat transfer tubes arranged such that a flow of the non-azeotropic refrigerant flowing through the plurality of second heat transfer tubes is perpendicular to a flow of air flowing through the second heat transfer section,
an inlet and an outlet of the non-azeotropic refrigerant of each of the first heat transfer section and the second heat transfer section are connected to a heat exchanger inlet and a heat exchanger outlet, respectively;
A heat exchanger, wherein an inlet and an outlet for the non-azeotropic refrigerant in each of the first heat transfer section and the second heat transfer section are arranged opposite to each other. A first heat transfer section having a plurality of first heat transfer tubes;
a non-azeotropic refrigerant flowing through the first heat transfer tubes of the first heat transfer section,
The plurality of first heat transfer tubes are arranged in a row,
the first heat transfer section includes a plurality of first heat transfer tubes arranged such that a flow of the non-azeotropic refrigerant flowing through the plurality of first heat transfer tubes is perpendicular to a flow of air flowing through the first heat transfer section,
Further comprising a second heat transfer section having a plurality of second heat transfer tubes;
The second heat transfer portion is disposed adjacent to the first heat transfer portion,
The second heat transfer tubes are arranged in a row and in a direction in which the first heat transfer tubes are arranged,
The non-azeotropic refrigerant mixture flows through the second heat transfer tubes of the second heat transfer section,
the second heat transfer section includes a plurality of second heat transfer tubes arranged such that a flow of the non-azeotropic refrigerant flowing through the plurality of second heat transfer tubes is perpendicular to a flow of air flowing through the second heat transfer section,
an inlet and an outlet of the non-azeotropic refrigerant of each of the first heat transfer section and the second heat transfer section are connected to a heat exchanger inlet and a heat exchanger outlet, respectively;
the first heat transfer section and the second heat transfer section have a first path and a second path,
the first path is arranged such that a flow of the non-azeotropic refrigerant flowing through the plurality of first heat transfer tubes and the plurality of second heat transfer tubes is parallel to a flow of air flowing through the first heat transfer section and the second heat transfer section,
the second path is arranged such that the flow of the non-azeotropic refrigerant flowing through the plurality of first heat transfer tubes and the plurality of second heat transfer tubes faces the flow of air flowing through the first heat transfer section and the second heat transfer section. The heat exchanger according to claim 1 or 2 ;
a compressor for compressing the non-azeotropic refrigerant mixture flowing into the heat exchanger.

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