Refrigeration cycle device

Abstract

A refrigeration cycle device (100) of the present application includes a heat exchanger (50) having a plurality of heat transfer fins (2) and a plurality of heat transfer tubes (1), and a refrigerant flow adjusting portion (5) that adjusts a flow direction of a refrigerant, the heat exchanger (50) being divided into a first heat exchanger region (3) and a second heat exchanger region (4). The refrigerant flow adjusting portion (5) adjusts the flow of the refrigerant so that, in either case where the heat exchanger (50) functions as an evaporator or a condenser, the flow direction (8) of air in the first heat exchanger region (3) is opposite to the flow direction (9, 10) of the refrigerant.

Description

Technical Field

[0001] This invention relates to a refrigeration cycle device that uses a refrigeration cycle and a heat pump cycle. Background Technology

[0002] In the heat pump device described in Patent Document 1, multiple bypass pipes and on / off valves or multiple four-way valves are used, so that in the outdoor and indoor heat exchangers, in either cooling or heating, the flow direction of the refrigerant is relative to the flow direction of the air.

[0003] Figure 3 This is the structure of a heat pump device using the four-way valve disclosed in multiple patent documents 1, representing the state during heating operation. At this time, the refrigerant flows in direction 30, representing the refrigerant flow direction during heating operation. The refrigerant flowing from the compressor 21 returns to the compressor 21 via the four-way valve 27, the utilization-side four-way valve 28, the utilization-side heat exchanger 22, the utilization-side four-way valve 28, the throttling device 26, the heat source-side four-way valve 29, the heat source-side heat exchanger 23, the heat source-side four-way valve 29, and the four-way valve 27.

[0004] Air, serving as an external fluid, is supplied to the heat exchanger 22 via the side fan 24. Additionally, air, also serving as an external fluid, is supplied to the heat exchanger 23 via the heat source side fan 25. Each heat exchanger operates in a relative flow configuration where the refrigerant flow direction is opposite to the external fluid flow direction 32.

[0005] During cooling operation, the four-way valve 27, the utilization-side four-way valve 28, and the heat source-side four-way valve 29 are switched. As a result, the refrigerant flowing from the compressor 21 flows in the direction 31, which indicates the refrigerant flow direction during cooling operation. At this time, in either the utilization-side heat exchanger 22 or the heat source-side heat exchanger 23, there is a relative flow where the refrigerant flow direction is opposite to the external fluid flow direction 32.

[0006] Furthermore, in the heat pump device disclosed in Patent Document 2, instead of using an on / off valve or a four-way valve, a check valve bridges the refrigerant circuit. For the heat exchanger, in either heating or cooling mode, the airflow direction is opposite to the refrigerant flow direction.

[0007] Existing technical documents

[0008] Patent documents

[0009] Patent Document 1: Japanese Patent Application Publication No. 59-115945

[0010] Patent Document 2: Japanese Patent Application Publication No. 7-190528 Summary of the Invention

[0011] The present invention provides a refrigeration cycle device in which, in either the case where the heat exchanger functions as an evaporator or as a condenser, the air flow direction is opposite to the refrigerant flow direction, and the cross-sectional area of ​​the refrigerant flow path can be adjusted, thereby achieving excellent performance of the heat exchanger and improving operating efficiency.

[0012] One aspect of the refrigeration cycle apparatus of the present invention includes: a heat exchanger having multiple heat transfer fins and multiple heat transfer tubes; and a refrigerant flow regulating section for regulating the flow direction of the refrigerant. The heat exchanger is divided into multiple first heat exchanger zones, and the refrigerant flow regulating section is connected to the first heat exchanger zones. The first heat exchanger zones are regulated by the refrigerant flow regulating section so that the refrigerant flows from the downwind side to the upwind side both when the heat exchanger functions as an evaporator and when it functions as a condenser.

[0013] Another embodiment of the refrigeration cycle apparatus of the present invention includes: a heat exchanger having multiple heat transfer fins and multiple heat transfer tubes; and a refrigerant flow regulating section for regulating the flow direction of the refrigerant. The heat exchanger is divided into a first heat exchanger zone and a second heat exchanger zone, and the refrigerant flow regulating section is connected to the first heat exchanger zone. The first heat exchanger zone is regulated by the refrigerant flow regulating section so that, in either the case where the heat exchanger functions as an evaporator or as a condenser, the refrigerant flows from the downwind side to the upwind side. In the second heat exchanger zone, the flow direction of the refrigerant is not regulated.

[0014] The refrigeration cycle device of the present invention can achieve excellent heat exchange performance. Attached Figure Description

[0015] Figure 1 This is a structural diagram of the refrigeration cycle device in Embodiment 1 of the present invention.

[0016] Figure 2 This is a structural diagram of the refrigeration cycle device in Embodiment 2 of the present invention.

[0017] Figure 3 This is a structural diagram of an existing heat pump device. Detailed Implementation

[0018] (Insights that form the basis of this invention, etc.)

[0019] In recent years, from the perspective of preventing global warming, the operating efficiency of air conditioners has been given attention, and many technologies aimed at improving operating efficiency have been proposed.

[0020] The heat exchanger, which facilitates heat exchange between refrigerant and air, is a crucial component that significantly impacts the operating efficiency of air conditioners. One representative type of heat exchanger is the finned tube heat exchanger, which has fins to promote heat exchange, allowing the refrigerant to flow within the tubes. Plate-finned tubes are used in indoor air conditioning units and similar applications. These tubes are constructed by stacking multiple fins and passing through multiple tubes arranged in rows. In many cases, there are also multiple rows of tubes.

[0021] In the condenser, the refrigerant changes from a superheated gaseous state to a gas-liquid two-phase state, and finally to a subcooled liquid state. Considering condenser efficiency, the refrigerant temperature preferably increases from the upwind side to the downwind side. Therefore, a relative flow of the refrigerant from the downwind side to the upwind side is preferred. Similarly, in the evaporator, the structure where the refrigerant flows from the downwind side to the upwind side improves performance compared to the structure where the refrigerant flows from the upwind side to the downwind side. However, in the evaporator, the performance degradation when the refrigerant flows from the upwind side to the downwind side compared to the structure where it flows from the downwind side to the upwind side is not as significant as in the condenser.

[0022] In air conditioning units such as indoor air conditioners, single-component refrigerants or azeotropic mixtures are typically used. When the heat exchanger functions as a condenser, it creates a relative flow where the refrigerant flows from the downwind side to the upwind side. When it functions as an evaporator, the pressure loss of the refrigerant lowers the temperature of the refrigerant on the downwind side, thereby improving heat exchange efficiency.

[0023] In an evaporator, if the refrigerant pressure is constant, the refrigerant absorbs heat and evaporates at a roughly constant temperature in either a single-component refrigerant or a simulated azeotropic mixture.

[0024] However, in the case of non-azeotropic refrigerant mixtures, the evaporation temperature of the refrigerant rises as evaporation proceeds. This change in evaporation temperature has a significant impact on the performance of the heat exchanger.

[0025] Therefore, considering the impact of evaporation temperature variations in non-azeotropic refrigerant mixtures on performance, a device has been proposed in which the refrigerant flow is relative to the air flow in both cooling and heating operations. In these prior art techniques, a structure is achieved where the refrigerant in the heat exchanger flows relative to the air flow in either cooling or heating operation, thereby improving the heat exchanger's performance. However, the inventors have noted that, as will be explained below, there is room for further improvement in the heat exchanger's performance.

[0026] As the refrigerant undergoes a phase change from gas to liquid, its density changes significantly, leading to variations in the refrigerant flow velocity within the pipe. A higher refrigerant flow velocity results in increased heat transfer and pressure loss characteristics on the inner surface of the pipe. Therefore, there exists an optimal flow velocity corresponding to the refrigerant's wettability. Optimization of the refrigerant flow velocity is achieved by adjusting the cross-sectional area of ​​the refrigerant flow path by changing the number of passages (which are arranged in parallel) or the pipe diameter. Preferably, the cross-sectional area of ​​the refrigerant flow path decreases as the refrigerant's wettability increases.

[0027] Here, the inventors discovered the following problem: In condensers, a small refrigerant outlet flow path cross-sectional area is preferred, while in evaporators, a large refrigerant outlet flow path cross-sectional area is preferred. That is, in heat exchangers where the refrigerant flows in a relative direction during both condensation and evaporation, the refrigerant flow path cross-sectional area cannot be adjusted. To solve this problem, the inventors have formulated this invention.

[0028] The embodiments will now be described in detail with reference to the accompanying drawings. However, sometimes unnecessary detailed descriptions will be omitted. For example, detailed descriptions of known matters or repetitive descriptions of substantially the same structure may be omitted.

[0029] Furthermore, the accompanying drawings and the following description are provided to enable those skilled in the art to fully understand the invention, and are not intended to limit the scope of the claims.

[0030] (Implementation Method 1)

[0031] Figure 1 This diagram shows the structure of the refrigeration cycle device 100 in Embodiment 1. Other examples of the refrigeration cycle device 100 include air conditioners such as indoor air conditioners and commercial air conditioners, as well as vending machines and display cases.

[0032] [1-1. Structure]

[0033] Figure 1 The refrigeration cycle device 100 shown includes a finned tube heat exchanger 40 composed of multiple heat transfer tubes 1 and multiple heat transfer fins 2. The heat exchanger 40 is configured with two rows of airflow 12 and 13 relative to the airflow direction 8. The heat transfer fins 2 have a surface perpendicular to the heat transfer tubes 1. Figure 1 There are multiple layers stacked in the depth direction.

[0034] In embodiment 1, the heat exchanger 40 is divided into two zones. Figure 1In this heat exchanger 40, there are two zones: the first heat exchanger zone 3a and the first heat exchanger zone 3b. The number of passages in the heat transfer tubes connected in parallel differs between the two zones. The first heat exchanger zone 3a has four passages, while the first heat exchanger zone 3b has two passages. Furthermore, the number of passages refers to the number of flow paths for the refrigerant flowing in parallel within the heat exchanger 40.

[0035] A refrigerant circuit 5a, serving as a refrigerant flow regulator, is connected to a check valve bridge in the first heat exchanger zone 3a. Therefore, regardless of whether the heat exchanger 40 is used as a condenser or an evaporator, the refrigerant flows from the lower air column 13 to the upper air column 12 in the first heat exchanger zone 3a. A refrigerant circuit 5b, also serving as a refrigerant flow regulator, is connected to a check valve bridge in the first heat exchanger zone 3b. Therefore, regardless of whether the heat exchanger 40 is used as a condenser or an evaporator, the refrigerant flows from the lower air column 13 to the upper air column 12 in the first heat exchanger zone 3b.

[0036] The refrigerant circuit 5a, which serves as a refrigerant flow regulating unit, is constructed by connecting four check valves 11 in a loop. The refrigerant circuit 5a is connected to the first refrigerant connection port 6, the lower air column 13 of the first heat exchanger zone 3a, the upper air column 12 of the first heat exchanger zone 3a, and the refrigerant circuit 5b. The refrigerant circuit 5b, which also serves as a refrigerant flow regulating unit, is constructed by connecting four check valves 11 in a loop. The refrigerant circuit 5b is connected to the second refrigerant connection port 7, the lower air column 13 of the first heat exchanger zone 3b, the upper air column 12 of the first heat exchanger zone 3b, and the refrigerant circuit 5a. Furthermore, in addition to the refrigerant circuits 5a and 5b shown in this embodiment, the refrigerant flow regulating units 5a and 5b can also be constructed using on / off valves or switching valves.

[0037] The first refrigerant connection port 6 is the refrigerant inlet when the heat exchanger 40 is used as a condenser, and the refrigerant outlet when the heat exchanger 40 is used as an evaporator. The second refrigerant connection port 7 is the refrigerant outlet when the heat exchanger 40 is used as a condenser, and the refrigerant inlet when the heat exchanger 40 is used as an evaporator.

[0038] The type of refrigerant used in the heat exchanger of the refrigeration cycle apparatus of the present invention is not limited, and single-component refrigerants, near-azeotropic mixtures of refrigerants, or non-azeotropic mixtures of refrigerants may also be used.

[0039] [1-2. Actions]

[0040] The operation and function of the refrigeration cycle device configured as described above will be explained below.

[0041] When the heat exchanger 40 functions as a condenser, the refrigerant flows in the same direction as during condensation (refrigerant flow direction 9). That is, gaseous refrigerant flows in from the first refrigerant connection port 6, passes through the check valve bridge refrigerant circuit 5a (which acts as a refrigerant flow regulator), the first heat exchanger zone 3a, returns to the check valve bridge refrigerant circuit 5a, and flows to the check valve bridge refrigerant circuit 5b (also acting as a refrigerant flow regulator). In the first heat exchanger zone 3a, there are four parallel-connected heat transfer pipes, and the refrigerant flows from the downwind column 13 to the upwind column 12. Afterward, the refrigerant flows from the check valve bridge refrigerant circuit 5b through the first heat exchanger zone 3b, returns to the check valve bridge refrigerant circuit 5b, and flows to the second refrigerant connection port 7. In the first heat exchanger zone 3b, there are two parallel-connected heat transfer pipes, and the refrigerant flows from the downwind column 13 to the upwind column 12.

[0042] When the heat exchanger 40 functions as an evaporator, the refrigerant flows in the same direction as during evaporation (refrigerant flow direction 10). That is, the gas-liquid two-phase refrigerant flows in from the second refrigerant connection 7, passes through the check valve bridge refrigerant circuit 5b (which acts as a refrigerant flow regulator), the first heat exchanger zone 3b, returns to the check valve bridge refrigerant circuit 5b, and flows to the check valve bridge refrigerant circuit 5a (which also acts as a refrigerant flow regulator). In the first heat exchanger zone 3b, there are two parallel heat transfer pipes, and the refrigerant flows from the downflow column 13 to the upflow column 12. Afterwards, the refrigerant flows from the check valve bridge refrigerant circuit 5a through the first heat exchanger zone 3a, returns to the check valve bridge refrigerant circuit 5a, and flows to the first refrigerant connection 6. In the first heat exchanger zone 3a, there are four parallel heat transfer pipes, and the refrigerant flows from the downflow column 13 to the upflow column 12.

[0043] In Embodiment 1, whether the heat exchanger 40 functions as an evaporator or a condenser, the first heat exchanger zones 3a and 3b are both relative flows where the refrigerant flows from the downflow zone 13 to the upflow zone 12. This results in good heat exchange characteristics. The number of passages is 4 in the first heat exchanger zone 3a where the proportion of gaseous refrigerant is increased, and 2 in the first heat exchanger zone 3b where the proportion of liquid refrigerant is increased. Thus, by setting the number of passages, i.e., setting the refrigerant flow path cross-sectional area, according to the state of the refrigerant, good heat exchange characteristics can be obtained.

[0044] [1-3. Effects, etc.]

[0045] As described above, in this embodiment, the refrigeration cycle device includes a heat exchanger 40 composed of multiple heat transfer fins 2 and multiple heat transfer tubes 1, and a refrigerant flow regulating section 5 for regulating the flow direction of the refrigerant. The heat exchanger 40 is divided into multiple first heat exchanger zones 3 (first heat exchanger zone 3a, first heat exchanger zone 3b). The refrigerant flow regulating section 5 is connected to the first heat exchanger zones 3. In either the case where the heat exchanger 40 functions as an evaporator or as a condenser, the first heat exchanger zones 3 are regulated by the refrigerant flow regulating section 5 to make the refrigerant flow from the downwind side to the upwind side.

[0046] Therefore, in either case where the heat exchanger functions as an evaporator or a condenser, the airflow direction can be made to flow in a relative direction to the refrigerant flow direction. Furthermore, the heat exchanger 40 is divided into multiple first heat exchanger zones 3, thereby allowing for flexible setting of the refrigerant flow path cross-sectional area corresponding to the refrigerant's wettability. Thus, a refrigeration cycle device capable of achieving excellent heat exchange performance can be provided.

[0047] As described in this embodiment, the heat exchanger may also include multiple first heat exchanger zones 3 with different numbers of passages. That is, the number of passages connected in parallel between the multiple first heat exchanger zones 3 may also be configured differently.

[0048] Therefore, it is possible to set the refrigerant flow path cross-sectional area corresponding to the refrigerant's wettability.

[0049] Alternatively, as shown in this embodiment, a check valve bridge refrigerant circuit can also be used as the refrigerant flow regulating unit 5.

[0050] Therefore, no control mechanism for regulating refrigerant flow is needed, and no electricity is required. This allows for the provision of a refrigeration cycle device that achieves excellent heat exchange performance while being inexpensive and easy to manage.

[0051] In addition, in this embodiment, a non-azeotropic refrigerant mixture can also be used as the refrigerant.

[0052] Therefore, refrigerants with low global warming potential can be used. Furthermore, even when using non-azeotropic refrigerants with temperature glide characteristics, the structure according to the present invention can provide a refrigeration cycle device with excellent heat exchange performance.

[0053] (Implementation Method 2)

[0054] The following uses Figure 2The refrigeration cycle apparatus of Embodiment 2 will be described. Furthermore, in Embodiment 2, the differences from Embodiment 1 will be mainly explained. In Embodiment 2, structures that are the same as or equivalent to those in Embodiment 1 will be labeled with the same symbols. Additionally, in Embodiment 2, descriptions that are repeated in Embodiment 1 are sometimes omitted.

[0055] Figure 2 This is a structural diagram showing the refrigeration cycle device 100 in Embodiment 2.

[0056] [2-1. Structure]

[0057] In embodiment 2, the heat exchanger 50 is divided into two zones. Figure 2 The two zones are the first heat exchanger zone 3 and the second heat exchanger zone 4. The first heat exchanger zone 3 has four parallel-connected heat transfer tubes. The second heat exchanger zone 4 has two passages in the downwind column 13. These two passages merge into one passage between the downwind column 13 and the upwind column 12 in the second heat exchanger zone 4. Therefore, the second heat exchanger zone 4 has one passage in the upwind column 12.

[0058] A refrigerant circuit 5, serving as a refrigerant flow regulator, is connected to the first heat exchanger zone 3. Therefore, regardless of whether the heat exchanger 50 is used as a condenser or an evaporator, the refrigerant flows from the downwind column 13 to the upwind column 12 in the first heat exchanger zone 3. Furthermore, multiple first heat exchanger zones 3 may exist, and the number of passages in the parallel-connected heat transfer tubes in multiple first heat exchanger zones 3 may differ from one another.

[0059] The second heat exchanger section 4 is connected to a check valve bridge refrigerant circuit 5, which serves as a refrigerant flow regulating section, but the refrigerant flow direction is not regulated. Therefore, as shown by the refrigerant flow direction 9 during condensation, the refrigerant flows from the lower air column 13 to the upper air column 12 during condensation, and as shown by the refrigerant flow direction 10 during evaporation, the refrigerant flows from the upper air column 12 to the lower air column 13 during evaporation.

[0060] The refrigerant circuit 5, which serves as a refrigerant flow regulating section, consists of four check valves 11 connected in a ring. The refrigerant circuit 5 is connected to the first refrigerant connection port 6, the lower air column 13 of the first heat exchanger zone 3, the upper air column 12 of the first heat exchanger zone 3, and the lower air column 13 of the second heat exchanger zone 4.

[0061] [2-2. Action]

[0062] The operation and function of the refrigeration cycle device configured as described above will be explained below.

[0063] When heat exchanger 50 functions as a condenser, the refrigerant flows in the same direction as during condensation (refractive refrigerant flow direction 9). That is, gaseous refrigerant flows in from the first refrigerant connection port 6, passes through the check valve bridge refrigerant circuit 5 (which acts as a refrigerant flow regulating section), the first heat exchanger zone 3, returns to the check valve bridge refrigerant circuit 5, and flows to the second heat exchanger zone 4 and the second refrigerant connection port 7. In the first heat exchanger zone 3, there are four parallel-connected heat transfer pipe passages, and the refrigerant flows from the downwind column 13 to the upwind column 12. In the second heat exchanger zone 4, there are two parallel-connected heat transfer pipe passages. In the second heat exchanger zone 4, the refrigerant flows through the two passages of the downwind column 13. After passing through the downwind column 13, the two passages merge into one, and the refrigerant flows in one passage of the upwind column 12, flowing to the second refrigerant connection port 7.

[0064] When heat exchanger 50 functions as an evaporator, the refrigerant flows in the same direction as during evaporation (flow direction 10). That is, the gas-liquid two-phase refrigerant flows in from the second refrigerant connection 7, passes through the second heat exchanger zone 4, the check valve bridge refrigerant circuit 5 (which acts as a refrigerant flow regulator), and the first heat exchanger zone 3, returns to the check valve bridge refrigerant circuit 5, and flows to the first refrigerant connection 6. In the second heat exchanger zone 4, the refrigerant flows through one passage in the upper air column 12. After passing through the upper air column 12, this passage becomes two passages, with the refrigerant flowing through the two passages in the lower air column 13 to the first refrigerant connection 6. In the first heat exchanger zone 3, the number of passages in the parallel-connected heat transfer tubes is four, and the refrigerant flows from the lower air column 13 to the upper air column 12.

[0065] In Embodiment 2, in the first heat exchanger zone 3, whether the heat exchanger 50 functions as an evaporator or as a condenser, the refrigerant flows in a relative flow from the lower air column 13 to the upper air column 12. This results in excellent heat exchange characteristics.

[0066] Furthermore, by setting the number of passages as follows: four passages in the first heat exchanger zone 3, where the proportion of gaseous refrigerant increases, and two and one passages in the second heat exchanger zone 4, where the proportion of liquid refrigerant increases. In this way, by setting the number of passages corresponding to the state of the refrigerant, i.e., the refrigerant flow path cross-sectional area, good heat exchange characteristics can be obtained.

[0067] Here, in the second heat exchanger zone 4, during condensation, there is a relative flow where the air flow direction is opposite to the refrigerant flow direction; on the other hand, during evaporation, there is a parallel flow where the air flow direction is parallel to the refrigerant flow direction. When the heat exchanger 50 functions as an evaporator, the second heat exchanger zone 4 corresponds to the beginning of refrigerant evaporation, where the refrigerant is in a gas-liquid two-phase state. Conversely, the first heat exchanger zone 3 corresponds to the end of refrigerant evaporation. Therefore, compared to the first heat exchanger zone 3, the second heat exchanger zone 4 has a limited impact on the overall evaporation performance reduction of the heat exchanger 50. Furthermore, in Figure 2 In the second heat exchanger zone 4 shown, the number of passages in the section flowing from the upper air column 12 to the lower air column 13 is doubled, meaning the refrigerant flow path cross-sectional area is doubled, resulting in a significant decrease in refrigerant pressure. In the second heat exchanger zone 4, as this pressure decreases, the temperature of the refrigerant in the upper air column 12 is higher than the temperature of the refrigerant in the lower air column 13. That is, in the second heat exchanger zone 4, the temperature distribution of the refrigerant is relative to the airflow direction, achieving good heat exchange performance.

[0068] [2-3. Effects, etc.]

[0069] As described above, in this embodiment, the refrigeration cycle device includes a heat exchanger 50 composed of multiple heat transfer fins 2 and multiple heat transfer tubes 1; and a refrigerant flow regulating section 5 for regulating the flow direction of the refrigerant. The heat exchanger 50 is divided into one or more first heat exchanger zones 3 and second heat exchanger zones 4. The refrigerant flow regulating section 5 is connected to the first heat exchanger zone 3. In the first heat exchanger zone 3, the refrigerant flow regulating section 5 regulates the flow so that the refrigerant flows from the downwind side to the upwind side in either the case where the heat exchanger 50 functions as an evaporator or as a condenser. The flow direction of the refrigerant in the second heat exchanger zone 4 is not regulated.

[0070] Therefore, in either case where the heat exchanger functions as an evaporator or a condenser, the airflow direction can be made to flow in a relative direction to the refrigerant flow direction. Furthermore, the refrigerant flow path cross-sectional area can be set to correspond to the refrigerant's wettability. Additionally, compared to the structure of Embodiment 1, the number of refrigerant flow regulating sections can be reduced. Thus, excellent heat exchange performance can be achieved, and a cost-effective refrigeration cycle device can be provided.

[0071] As described in this embodiment, when the heat exchanger functions as a condenser, the second heat exchanger zone 4 can also be configured such that the refrigerant flows from the downwind side to the upwind side.

[0072] Therefore, when the heat exchanger functions as a condenser, in the second heat exchanger zone 4, the refrigerant flow direction becomes a relative flow, opposite to the air flow direction, resulting in good heat exchange performance. Conversely, when the heat exchanger functions as an evaporator, in the second heat exchanger zone 4, the refrigerant flow direction is parallel to the air flow direction. However, compared to the condenser, the reduction in heat exchange performance due to the refrigerant flow direction being parallel to the air flow direction is not significant.

[0073] In addition, as described in this embodiment, in the second heat exchanger zone 4, the number of passages of the parallel-connected heat transfer tubes 1 can be such that the number of passages on the downwind side is greater than the number of passages on the upwind side.

[0074] Therefore, even without using the refrigerant flow regulating section 5, the temperature of the refrigerant flowing in the heat transfer tubes 1 of the upper air column 12 can be made closer to the air temperature than the temperature of the refrigerant flowing in the heat transfer tubes 1 of the lower air column 13. This improves heat exchange efficiency. Consequently, excellent heat exchange performance can be achieved, and a cost-effective heat exchanger can be provided.

[0075] In addition, as described in this embodiment, for a heat exchanger, the number of passages of the heat transfer tubes 1 connected in parallel in the second heat exchanger zone 4 may be less than the number of passages of the heat transfer tubes 1 connected in parallel in the first heat exchanger zone 3.

[0076] Therefore, it is possible to set the number of passages corresponding to the state of the refrigerant, i.e., the cross-sectional area of ​​the refrigerant flow path, and to obtain good heat exchange characteristics.

[0077] Industrial availability

[0078] As described above, the refrigeration cycle device of the present invention provides excellent heat exchange performance, and its technology is not limited to air conditioners, but can also be widely applied to vending machines and display cases for cooling and heating.

[0079] Explanation of reference numerals in the attached figures

[0080] 1 heat transfer tube

[0081] 2 heat transfer fins

[0082] 3, 3a, 3b First heat exchanger zone

[0083] 4 Second heat exchanger zone

[0084] 5. Check valve bridge refrigerant circuit (refrigerant flow regulating section)

[0085] 5a Check Valve Bridge Refrigerant Circuit (Refrigerant Flow Regulation Section)

[0086] 5b Check Valve Bridge Refrigerant Circuit (Refrigerant Flow Regulation Section)

[0087] 6 First refrigerant connection port

[0088] 7 Second refrigerant connection port

[0089] 8. Direction of air flow

[0090] 9. Refrigerant flow direction during condensation

[0091] 10. Refrigerant flow direction during evaporation

[0092] 11 Check valve

[0093] 12 Upwind column

[0094] 13 Downwind column

[0095] 40 Heat Exchanger

[0096] 50 heat exchanger

[0097] 100 Refrigeration cycle device.

Claims

1. A refrigeration cycle device, characterized in that, include: A heat exchanger having multiple heat transfer fins and multiple heat transfer tubes; and The first refrigerant flow regulating section and the second refrigerant flow regulating section regulate the flow direction of the refrigerant. The heat exchanger is divided into multiple first heat exchanger zones. The first refrigerant flow regulating section and the second refrigerant flow regulating section are respectively connected to the plurality of first heat exchanger zones. The first refrigerant flow regulating section and the second refrigerant flow regulating section are adjusted so that, in either the case where the heat exchanger functions as an evaporator or as a condenser, the refrigerant flows from the downwind side to the upwind side in all of the plurality of first heat exchanger zones. The heat exchanger has multiple first heat exchanger zones with different numbers of passages. During operation of the heat exchanger as an evaporator, the refrigerant flows in the following order: first refrigerant flow regulating section, first heat exchanger zone with fewer passages, second refrigerant flow regulating section, and first heat exchanger zone with more passages.

2. The refrigeration cycle device as described in claim 1, characterized in that: The heat exchanger also includes a second heat exchanger zone. The flow direction of the refrigerant in the second heat exchanger zone was not regulated.

3. The refrigeration cycle device as described in claim 2, characterized in that: The second heat exchanger zone is configured such that, when the heat exchanger functions as a condenser, the refrigerant flows from the downwind side to the upwind side.

4. The refrigeration cycle device as described in claim 2 or 3, characterized in that: In the second heat exchanger zone, the number of parallel-connected passages is greater on the downwind side than on the upwind side.

5. The refrigeration cycle device as described in claim 3, characterized in that: The number of parallel connected pathways is less in the second heat exchanger zone than in the first heat exchanger zone.

6. The refrigeration cycle apparatus according to any one of claims 1 to 3, characterized in that: The refrigerant flow regulating section is a check valve bridge refrigerant circuit.

7. The refrigeration cycle apparatus according to any one of claims 1 to 3, characterized in that: The refrigerant is a non-azeotropic mixture.

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