Refrigeration Cycle Equipment

Abstract

To solve the problem that although a cross sectional area of a refrigerant outlet flow path is desirably small in a condenser, a cross sectional area of a refrigerant inlet flow path is desirably small in an evaporator, so that it is impossible to adjust the cross sectional area of a refrigerant flow path in a counterflow heat exchanger for both condensation and evaporation.SOLUTION: A refrigeration cycle device comprises a heat exchanger composed of a plurality of heat transfer fins and a plurality of heat transfer tubes, and refrigerant flow adjustment means of adjusting a direction of refrigerant flow. The heat exchanger comprises a first heat exchanger section and a second heat exchanger section, so that even in either case that the heat exchanger functions as an evaporator or condenser, it is possible to make the direction of air flow and the direction of refrigerant flow as counterflows, and reduce the number of refrigerant flow adjustment means.SELECTED DRAWING: Figure 2

Description

[Technical Field]

[0001] The present invention relates to a refrigeration cycle device for improving the operating efficiency of an air conditioner that performs air conditioning using a refrigeration and heat pump cycle. [Background technology]

[0002] The heat pump device described in Patent Document 1 uses multiple bypass pipes and on-off valves, or multiple four-way valves, so that the refrigerant flows counter to the air flow in the outdoor and indoor heat exchangers, whether cooling or heating.

[0003] 3 shows the configuration of the heat pump device when multiple four-way valves of Patent Document 1 are used, showing the state during heating operation, where the refrigerant flows in the refrigerant flow direction during heating operation 30. The refrigerant leaving the compressor 21 flows from the four-way valve 27 to the user-side four-way valve 28, the user-side heat exchanger 22, again to the user-side four-way valve 28, the expansion device 26, the heat-source-side four-way valve 29, the heat-source-side heat exchanger 23, again to the heat-source-side four-way valve 29, and again to the four-way valve 27 and back to the compressor 21.

[0004] A user-side fan 24 sends air, which is an external fluid, to the user-side heat exchanger 22, and a heat-source-side fan 25 sends air to the heat-source-side heat exchanger 23, and in both heat exchangers, the flow direction of the refrigerant is counter to the flow direction 32 of the external fluid.

[0005] When cooling operation begins, four-way valve 27, user-side four-way valve 28, and heat-source-side four-way valve 29 switch, and the refrigerant flows in the refrigerant flow direction 31 during cooling operation, but in both user-side heat exchanger 22 and heat-source-side heat exchanger 23, the refrigerant flow direction is countercurrent to the external fluid flow direction 32.

[0006] Furthermore, in Patent Document 2, instead of using an on-off valve or a four-way valve, a check valve bridge refrigerant circuit is used to make the air and refrigerant flow in opposite directions in the user-side heat exchanger during both heating and cooling. [Prior art documents] [Patent documents]

[0007] [Patent Document 1] Japanese Patent Application Publication No. 59-115945 [Patent Document 2] Japanese Patent Application Publication No. 7-190528 Summary of the Invention [Problem to be solved by the invention]

[0008] The present disclosure provides a refrigeration cycle device that achieves excellent performance of the heat exchanger by making the air flow direction and the refrigerant flow direction counter-current in either case where the heat exchanger functions as an evaporator or a condenser, and by making it possible to adjust the cross-sectional area of ​​the refrigerant flow path, thereby improving the operating efficiency of the air conditioner. [Means for solving the problem]

[0009] The refrigeration cycle device of the present disclosure includes a heat exchanger composed of a plurality of heat transfer fins and a plurality of heat transfer tubes, and a refrigerant flow adjustment means for adjusting the direction of refrigerant flow, the heat exchanger having a plurality of first heat exchanger sections, the refrigerant flow adjustment means being connected to the first heat exchanger sections, and the first heat exchanger sections being adjusted by the refrigerant flow adjustment means so that the refrigerant flows from the downwind side to the upwind side whether the heat exchanger functions as an evaporator or a condenser.

[0010] This allows the air and refrigerant to flow in opposite directions whether the heat exchanger functions as an evaporator or a condenser, and the refrigerant flow path cross-sectional area can be set according to the wetness of the refrigerant.

[0011] In addition, the refrigeration cycle device of the present disclosure includes a heat exchanger composed of a plurality of heat transfer fins and a plurality of heat transfer tubes, and a refrigerant flow adjustment means for adjusting the direction of refrigerant flow, the heat exchanger having a first heat exchanger section and a second heat exchanger section, the refrigerant flow adjustment means being connected to the first heat exchanger section, the first heat exchanger section being adjusted by the refrigerant flow adjustment means so that the refrigerant flows from the downwind side to the upwind side whether the heat exchanger functions as an evaporator or a condenser, and the refrigerant flow direction in the second heat exchanger section is not adjusted.

[0012] This allows the air and refrigerant to flow in opposite directions whether the heat exchanger functions as an evaporator or a condenser, and also reduces the number of refrigerant flow adjusting means. [Effects of the Invention]

[0013] The refrigeration cycle device of the present disclosure includes a plurality of first heat exchanger sections and a refrigerant flow adjusting means, so that the air flow direction and the refrigerant flow direction are counter-current to each other whether the heat exchanger functions as an evaporator or a condenser, and the refrigerant flow path cross-sectional area can be set according to the wetness of the refrigerant, thereby providing a refrigeration cycle device that can achieve excellent heat exchange performance.

[0014] Furthermore, the refrigeration cycle device of the present disclosure includes a first heat exchanger section, a second heat exchanger section, and a refrigerant flow control means, so that the air and refrigerant flow directions are counter-flowing in either case where the heat exchanger functions as an evaporator or a condenser, and the number of refrigerant flow control means can be reduced, thereby providing a refrigeration cycle device that can achieve excellent heat exchange performance and reduce costs. [Brief explanation of the drawings]

[0015] [Figure 1] Configuration diagram of a refrigeration cycle device according to a first embodiment [Figure 2] Configuration diagram of a refrigeration cycle device according to a second embodiment [Figure 3] Diagram of a conventional heat pump device DETAILED DESCRIPTION OF THE INVENTION

[0016] (Findings that formed the basis of this disclosure) In recent years, the operational efficiency of air conditioners has become increasingly important from the standpoint of preventing global warming, and numerous inventions have been proposed.

[0017] The heat exchanger, which exchanges heat between the refrigerant and the air, is one of the components that significantly affects the operating efficiency of an air conditioner. One typical heat exchanger configuration is a fin-tube heat exchanger, in which the refrigerant flows through tubes with fins to promote heat exchange. Room air conditioners and other similar devices use plate-fin tubes, which are configured by stacking multiple plate fins and arranging multiple tubes in rows so that they penetrate the plate fins. The tubes often have multiple rows.

[0018] In the condenser, the refrigerant changes from a superheated gas state to a two-phase gas-liquid state and finally to a supercooled liquid state. When considering the efficiency of the condenser, it is better for the refrigerant temperature to increase from the upwind side to the downwind side, so it is desirable for the refrigerant to flow in a counterflow direction from downwind to upwind. In the case of an evaporator, as with a condenser, performance can be improved by having the refrigerant flow from downwind to upwind, but the performance degradation when the refrigerant flows from upwind to downwind is not as great as in the case of a condenser.

[0019] Until now, room air conditioners and other air conditioners have often used single-component refrigerants or pseudo-azeotropic refrigerants. When the heat exchanger serves as a condenser, the refrigerant is configured to flow countercurrently from the downwind side to the upwind side, and in the evaporator, the refrigerant pressure loss is used to lower the downwind refrigerant temperature, thereby increasing heat exchange efficiency.

[0020] If the pressure of the refrigerant is constant in the evaporator, a single-component refrigerant or a quasi-azeotropic refrigerant mixture will absorb heat and evaporate at a substantially constant temperature.

[0021] However, in the case of a non-azeotropic refrigerant mixture, the evaporation temperature of the refrigerant increases as evaporation proceeds, which has a significant impact on the performance of the heat exchanger.

[0022] In light of this, devices that use counter-flow refrigerants in both cooling and heating modes have been proposed, taking into account the performance impact of non-azeotropic refrigerant mixtures. Conventional technology has been able to achieve counter-flow heat exchangers in both cooling and heating modes, improving performance, but it is still not sufficient.

[0023] The density of the refrigerant changes significantly as it changes phase from gas to liquid, which changes the flow rate of the refrigerant inside the pipe. If the refrigerant flow rate is high, the conflicting characteristics of heat transfer and pressure loss on the inner surface of the pipe increase, so there is a desirable flow rate depending on the wetness. The refrigerant flow rate can be optimized by changing the number of paths and pipe diameter, and by adjusting the cross-sectional area of ​​the refrigerant flow path; it is desirable to reduce the cross-sectional area of ​​the refrigerant flow path as the wetness increases.

[0024] However, while a small refrigerant outlet flow path cross-sectional area is desirable in a condenser, a large refrigerant outlet flow path cross-sectional area is desirable in an evaporator, and it was discovered that there was a problem in that the refrigerant flow path cross-sectional area could not be adjusted in a heat exchanger in which both condensation and evaporation are counter-flows.The subject matter of the present disclosure was created to solve this problem.

[0025] Therefore, the present disclosure provides a refrigeration cycle device that includes a first heat exchanger section, a second heat exchanger section, and a refrigerant flow adjustment means, thereby making the air flow direction and the refrigerant flow direction counter-flow in both the condenser and the evaporator, and reducing the number of refrigerant flow adjustment means.

[0026] Hereinafter, embodiments will be described in detail with reference to the drawings. However, unnecessary detailed description may be omitted. For example, detailed description of already well-known matters or redundant description of substantially the same configuration may be omitted.

[0027] The accompanying drawings and the following description are provided to enable those skilled in the art to fully understand the present disclosure, and are not intended to limit the subject matter described in the claims. (Embodiment 1) FIG. 1 shows a configuration diagram of a refrigeration cycle device according to the first embodiment.

[0028] [1-1.Configuration] The refrigeration cycle device shown in Fig. 1 includes a fin-tube heat exchanger consisting of a plurality of heat transfer tubes 1 and a plurality of heat transfer fins 2. The heat exchanger is configured in two rows, an upwind row 12 and a downwind row 13, in the air flow direction 8. The heat transfer fins 2 have surfaces perpendicular to the heat transfer tubes 1, and many of them are stacked in the depth direction of Fig. 1.

[0029] The heat exchanger of the first embodiment has two sections, a first heat exchanger section 3a and a first heat exchanger section 3b. The first heat exchanger section 3a and the first heat exchanger section 3b differ in the number of paths of the heat transfer tubes connected in parallel, with the first heat exchanger section 3a having four paths and the first heat exchanger section 3b having two paths.

[0030] The first heat exchanger section 3a is connected to a refrigerant flow regulation means 5a, a check valve bridge refrigerant circuit, which allows refrigerant to flow from the downwind row 13 to the upwind row 12 whether the heat exchanger is used as a condenser or an evaporator. The first heat exchanger section 3b is connected to a refrigerant flow regulation means 5b, a check valve bridge refrigerant circuit, which allows refrigerant to flow from the downwind row 13 to the upwind row 12 whether the heat exchanger is used as a condenser or an evaporator.

[0031] The refrigerant flow adjustment means 5a is a check valve bridge refrigerant circuit formed by connecting four check valves 11 in a ring, and is connected to the first refrigerant connection port 6, the downwind row 13 of the first heat exchanger section 3a, the upwind row 12 of the first heat exchanger section 3a, and the refrigerant flow adjustment means 5b. The refrigerant flow adjustment means 5b is a check valve bridge refrigerant circuit formed by connecting four check valves 11 in a ring, and is connected to the second refrigerant connection port 7, the downwind row 13 of the first heat exchanger section 3b, the upwind row 12 of the first heat exchanger section 3b, and the refrigerant flow adjustment means 5a. On-off valves or switching valves may also be used as the refrigerant flow adjustment means 5a and 5b.

[0032] The first refrigerant connection port 6 is a connection port that serves as a refrigerant inlet when the heat exchanger is used as a condenser, and as a refrigerant outlet when the heat exchanger is used as an evaporator. The second refrigerant connection port 7 is a connection port that serves as a refrigerant outlet when the heat exchanger is used as a condenser, and as a refrigerant inlet when the heat exchanger is used as an evaporator.

[0033] The type of refrigerant used in the heat exchanger is not limited, and a single component refrigerant, a near-azeotropic mixed refrigerant, a non-azeotropic mixed refrigerant, or the like may be used.

[0034] [1-2. Operation] The operation and function of the refrigeration cycle device configured as above will now be described.

[0035] When the heat exchanger functions as a condenser, the refrigerant flows in a condensing refrigerant flow direction 9, as shown in FIG. 9, from the first refrigerant connection port 6 as a gas refrigerant, through the refrigerant flow adjustment means 5a and the first heat exchanger section 3a, returns to the refrigerant flow adjustment means 5a, and then flows to the refrigerant flow adjustment means 5b. In the first heat exchanger section 3a, the number of paths of the heat transfer tubes connected in parallel is divided into four, and the refrigerant flows from the downwind row 13 to the upwind row 12. The refrigerant then flows from the refrigerant flow adjustment means 5b through the first heat exchanger section 3b, returns to the refrigerant flow adjustment means 5b, and then flows to the second refrigerant connection port 7. In the first heat exchanger section 3b, the number of paths of the heat transfer tubes connected in parallel is divided into two, and the refrigerant flows from the downwind row 13 to the upwind row 12.

[0036] When the heat exchanger functions as an evaporator, the refrigerant flows in a gas-liquid two-phase state from the second refrigerant connection port 7, passes through the refrigerant flow control means 5b and the first heat exchanger section 3b, returns to the refrigerant flow control means 5b, and then flows to the refrigerant flow control means 5a, as shown in refrigerant flow direction 10 during evaporation. In the first heat exchanger section 3b, the number of paths of the heat transfer tubes connected in parallel is divided into two, and the refrigerant flows from the downwind row 13 to the upwind row 12. The refrigerant then flows from the refrigerant flow control means 5a through the first heat exchanger section 3a, returns to the refrigerant flow control means 5a, and flows to the first refrigerant connection port 6. In the first heat exchanger section 3a, the number of paths of the heat transfer tubes connected in parallel is divided into four, and the refrigerant flows from the downwind row 13 to the upwind row 12.

[0037] In the first embodiment, whether the heat exchanger functions as an evaporator or a condenser, the first heat exchanger sections 3a, 3b have a counterflow arrangement in which the refrigerant flows from the downwind row 13 to the upwind row 12, thereby achieving good heat exchange characteristics. The number of paths, i.e., the refrigerant flow path cross-sectional area, is set according to the state of the refrigerant, with four paths in the first heat exchanger section 3a where the proportion of gas refrigerant is high and two paths in the first heat exchanger section 3b where the proportion of liquid refrigerant is high, thereby achieving good heat exchange characteristics.

[0038] [1-3. Effects, etc.] As described above, in this embodiment, the refrigeration cycle apparatus includes a heat exchanger composed of a plurality of heat transfer fins 2 and a plurality of heat transfer tubes 1, and a refrigerant flow adjustment means 5 that adjusts the flow direction of the refrigerant. The heat exchanger has a plurality of first heat exchanger sections 3. The refrigerant flow adjustment means 5 is connected to the first heat exchanger sections 3. The refrigerant flow adjustment means 5 adjusts the first heat exchanger sections 3 so that the refrigerant flows from the downwind side to the upwind side, whether the heat exchanger functions as an evaporator or a condenser.

[0039] This allows the air and refrigerant to flow counter-currently, regardless of whether the heat exchanger functions as an evaporator or a condenser, and the refrigerant flow cross-sectional area can be set according to the wetness of the refrigerant, thereby providing a refrigeration cycle device that can achieve excellent heat exchange performance.

[0040] As in this embodiment, the heat exchanger may include a plurality of first heat exchanger sections 3 each having a different number of paths.

[0041] This allows the refrigerant flow passage cross-sectional area to be set according to the wetness of the refrigerant.

[0042] In this embodiment, the refrigerant flow adjusting means 5 may use a check valve bridge refrigerant circuit.

[0043] This eliminates the need for a control means or the need to use electricity to adjust the flow of the refrigerant, making it possible to provide a refrigeration cycle device that not only achieves excellent heat exchange performance but is also inexpensive and easy to use.

[0044] In this embodiment, a non-azeotropic refrigerant mixture may be used as the refrigerant.

[0045] This makes it possible to use a refrigerant with a small global warming potential, and even when a non-azeotropic refrigerant mixture having temperature slip characteristics is used, it is possible to provide a refrigeration cycle device with excellent heat exchange performance. (Embodiment 2) Hereinafter, the second embodiment will be described with reference to FIG. 2. In the second embodiment, differences from the first embodiment will be mainly described. In the second embodiment, the same or equivalent configurations as in the first embodiment will be denoted by the same reference numerals. In the second embodiment, descriptions that overlap with the first embodiment will be omitted.

[0046] FIG. 2 shows a configuration diagram of a refrigeration cycle device according to the second embodiment.

[0047] [2-1.Configuration] The heat exchanger of the second embodiment has two sections: a first heat exchanger section 3 and a second heat exchanger section 4. The first heat exchanger section 3 has four paths of heat transfer tubes connected in parallel, and the second heat exchanger section 4 has two paths in the downwind row 13, two paths that merge to form one path between the downwind row 13 and the upwind row 12, and one path in the upwind row 12.

[0048] A check valve bridge refrigerant circuit, which is a refrigerant flow control means 5, is connected to the first heat exchanger section 3, so that the refrigerant flows from the downwind row 13 to the upwind row 12 whether the heat exchanger is used as a condenser or an evaporator. Note that there may be a plurality of first heat exchanger sections 3, and each first heat exchanger section 3 may have a different number of paths of heat transfer tubes connected in parallel.

[0049] The second heat exchanger section 4 is connected to a check valve bridge refrigerant circuit, which is a refrigerant flow adjustment means 5, but the refrigerant flow direction is not adjusted. In the case of refrigerant flow direction 9 during condensation, the refrigerant flows from the downwind row 13 to the upwind row 12, and in the case of refrigerant flow direction 10 during evaporation, the refrigerant flows from the upwind row 12 to the downwind row 13.

[0050] The refrigerant flow control means 5 is a check valve bridge refrigerant circuit consisting of four check valves 11 connected in a ring, and is connected to the first refrigerant connection port 6, the downwind row 13 of the first heat exchanger section 3, the upwind row 12 of the first heat exchanger section 3, and the downwind row 13 of the second heat exchanger section 4.

[0051] [2-2. Operation] The operation and function of the refrigeration cycle device configured as above will now be described.

[0052] When the heat exchanger functions as a condenser, the refrigerant flows in a condensing refrigerant flow direction 9, as shown in FIG. 1, from the first refrigerant connection port 6 as a gas refrigerant, passes through the refrigerant flow adjustment means 5 and the first heat exchanger section 3, returns to the refrigerant flow adjustment means 5, and then flows to the second heat exchanger section 4 and the second refrigerant connection port 7. In the first heat exchanger section 3, the number of paths of the heat transfer tubes connected in parallel is divided into four, and the refrigerant flows from the downwind row 13 to the upwind row 12. In the second heat exchanger section 4, the number of paths of the heat transfer tubes connected in parallel is divided into two, and the refrigerant flows through the downwind row 13. After flowing through the downwind row 13, the two paths merge to form one path, which flows through the upwind row 12 and then to the second refrigerant connection port 7.

[0053] When the heat exchanger functions as an evaporator, the refrigerant flows in a gas-liquid two-phase state from the second refrigerant connection port 7, passes through the second heat exchanger section 4, the refrigerant flow adjustment means 5, and the first heat exchanger section 3, returns to the refrigerant flow adjustment means 5, and flows to the first refrigerant connection port 6, as shown in the refrigerant flow direction 10 during evaporation. In the second heat exchanger section 4, the refrigerant flows in one pass through the upwind row 12, and after flowing through the upwind row 12, it makes two passes and flows through the downwind row 13 and then to the first refrigerant connection port 6. In the first heat exchanger section 3, the number of passes of the heat transfer tubes connected in parallel is divided into four, and the refrigerant flows from the downwind row 13 to the upwind row 12.

[0054] In embodiment 2, the first heat exchanger section 3 has a counterflow from the downwind row 13 to the upwind row 12, whether the heat exchanger functions as an evaporator or a condenser, thereby achieving good heat exchange characteristics.

[0055] The number of paths, i.e., the refrigerant flow path cross-sectional area, is set according to the state of the refrigerant: four paths in the first heat exchanger section 3, where the proportion of gas refrigerant is high, and two paths and one path in the second heat exchanger section 4, where the proportion of liquid refrigerant is high, thereby achieving good heat exchange characteristics.

[0056] In the second heat exchanger section 4, the air and refrigerant flow countercurrently during condensation, but parallelly during evaporation. In the second heat exchanger section 4, the refrigerant is in a gas-liquid two-phase state at the start of evaporation, and the impact on the overall evaporation performance of the heat exchanger is limited compared to the first heat exchanger section 3, where evaporation ends. In the second heat exchanger section 4 shown in Figure 2, the number of paths doubles when the refrigerant flows from the upwind row 12 to the downwind row 13, meaning the refrigerant flow cross-sectional area doubles. This significantly reduces the refrigerant pressure, and as a result, the refrigerant temperature in the upwind row 12 is higher than that in the downwind row 13. This results in a counter-current temperature distribution, resulting in good heat exchange performance.

[0057] [2-3. Effects, etc.] As described above, in this embodiment, the refrigeration cycle apparatus includes a heat exchanger composed of a plurality of heat transfer fins 2 and a plurality of heat transfer tubes 1, and a refrigerant flow adjustment means 5 that adjusts the flow direction of the refrigerant. The heat exchanger has one or more first heat exchanger sections 3 and a second heat exchanger section 4. The refrigerant flow adjustment means 5 is connected to the first heat exchanger section 3. The refrigerant flow adjustment means 5 adjusts the flow of the refrigerant in the first heat exchanger section 3 from the downwind side to the upwind side, whether the heat exchanger functions as an evaporator or a condenser. The flow direction of the refrigerant in the second heat exchanger section 4 is not adjusted.

[0058] This allows the air and refrigerant to flow counter-currently whether the heat exchanger functions as an evaporator or a condenser, and the refrigerant flow cross-sectional area can be set according to the wetness of the refrigerant, and the number of refrigerant flow adjustment means can be reduced, thereby achieving excellent heat exchange performance and providing an inexpensive refrigeration cycle device.

[0059] As in this embodiment, the second heat exchanger section 4 may be configured such that the refrigerant flows from downwind to upwind when the heat exchanger functions as a condenser.

[0060] As a result, when the heat exchanger functions as a condenser, the air and refrigerant flow in opposite directions, resulting in good heat exchange performance.When the heat exchanger functions as an evaporator, the air and refrigerant flow in parallel directions, but the deterioration in heat exchange performance is not as great as when it functions as a condenser.

[0061] In this embodiment, the second heat exchanger section 4 may be configured such that the number of paths of the heat transfer tubes 1 connected in parallel on the downwind side is greater than the number of paths on the upwind side.

[0062] As a result, the temperature of the refrigerant flowing through the heat transfer tubes 1 in the upwind row 12 can be made closer to the air temperature than the temperature of the refrigerant flowing through the heat transfer tubes 1 in the downwind row 13, without using the refrigerant flow adjustment means 5, thereby improving the heat exchange efficiency. Therefore, it is possible to provide an inexpensive heat exchanger that achieves excellent heat exchange performance.

[0063] In this embodiment, the number of paths of the heat transfer tubes 1 connected in parallel in the heat exchanger may be set so that the number of paths of the second heat exchanger section 4 is smaller than the number of paths of the first heat exchanger section 3.

[0064] This allows the number of paths, i.e., the sectional area of ​​the refrigerant flow path, to be set according to the state of the refrigerant, thereby achieving good heat exchange characteristics. [Industrial Applicability]

[0065] As described above, the heat exchanger of the present invention is used in air conditioners that perform air conditioning using refrigeration and heat pump cycles, and provides good heat exchange performance.The technology is not limited to air conditioners, but can also be widely applied to vending machines, showcases, and other devices that perform both cooling and heating, and can provide good results. [Explanation of symbols]

[0066] 1 Heat transfer tube 2 Heat transfer fins 3, 3a, 3b First heat exchanger section 4 Second heat exchanger section 5, 5a, 5b Refrigerant flow adjusting means 6 First refrigerant connection port 7 Second refrigerant connection port 8 Air flow direction 9 Refrigerant flow direction during condensation 10 Refrigerant flow direction during evaporation 11 Check valve 12 Windward Row 13 Leeward row

Claims

1. a heat exchanger including a plurality of heat transfer fins and a plurality of heat transfer tubes, and a first refrigerant flow adjustment means and a second refrigerant flow adjustment means for adjusting a flow direction of a refrigerant, the heat exchanger having a plurality of first heat exchanger sections, the first refrigerant flow adjustment means and the second refrigerant flow adjustment means being connected to the first heat exchanger sections, and the first heat exchanger sections being adjusted by the refrigerant flow adjustment means so that the refrigerant flows from the downwind side to the upwind side whether the heat exchanger functions as an evaporator or a condenser; The heat exchanger has a plurality of first heat exchanger sections with different numbers of paths, and during operation in which the heat exchanger functions as an evaporator, the refrigerant flows in the following order: first refrigerant flow control means, the first heat exchanger section with the fewer paths, second refrigerant flow control means, and the first heat exchanger section with the greater number of paths.

2. 2. The refrigeration cycle apparatus according to claim 1, wherein the heat exchanger further comprises a second heat exchanger section, the second heat exchanger section having an unregulated refrigerant flow direction.

3. 3. The refrigeration cycle device according to claim 2, wherein the second heat exchanger section is configured so that the refrigerant flows from the downwind side to the upwind side when the heat exchanger functions as a condenser.

4. 4. The refrigeration cycle apparatus according to claim 2, wherein the second heat exchanger section is configured such that the number of paths of the heat transfer tubes connected in parallel is greater on the downwind side than on the upwind side.

5. The refrigeration cycle device according to any one of claims 3 to 4, characterized in that the number of paths of the heat transfer tubes connected in parallel to the heat exchanger is smaller in the second heat exchanger section than in the first heat exchanger section.

6. 6. The refrigeration cycle device according to claim 1, wherein the refrigerant flow adjusting means is a check valve bridge refrigerant circuit.

7. 7. The refrigeration cycle device according to claim 1, wherein the refrigerant is a non-azeotropic refrigerant mixture.

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