Double-row heat exchanger
By introducing multiple sub-tubes into the first manifold, the refrigerant can directly enter the second heat exchange tube after the first sub-tubes converge, which solves the problem of uneven refrigerant distribution in the double-row heat exchanger and improves the heat exchange performance and frosting time under low temperature conditions.
Patent Information
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- SANHUA(HANGZHOU) MICRO CHANNEL HEAT EXCHANGER CO LTD
- Filing Date
- 2025-04-17
- Publication Date
- 2026-05-05
AI Technical Summary
In existing dual-row heat exchangers with multiple manifolds, the uneven distribution of refrigerant in the second row leads to short-circuiting, affecting the frosting time and heat exchange performance under low-temperature conditions.
By introducing multiple sub-tubes in the first manifold, the refrigerant directly enters the second heat exchange tube for heat exchange after the first sub-tubes converge, reducing the number of refrigerant distributions and improving the uniformity of the second flow.
It enhances the uniformity of refrigerant flow in the second row of the double-row heat exchanger, prolongs the frosting time under low-temperature conditions, and improves low-temperature heat exchange performance.
Smart Images
Figure CN224202277U_ABST
Abstract
Description
Technical Field
[0001] This application relates to the field of heat exchange technology, specifically to a double-row heat exchanger for a heat pump. Background Technology
[0002] For dual-row heat exchangers with multiple manifolds, the refrigerant usually needs to be distributed twice before entering the second row of heat exchangers for heat exchange. That is, after the first distribution, the refrigerant enters multiple heat exchange tubes in the first row for heat exchange, and then, after being merged through the manifolds, it is distributed a second time to multiple heat exchange tubes in the second row for heat exchange again. This second distribution results in poorer uniformity of refrigerant distribution compared to the first row. Uneven distribution exacerbates the problem of excessive refrigerant flowing towards the heat exchanger outlet in areas with high refrigerant levels, creating a short circuit. This shortens the frosting time under low-temperature conditions (above 7 degrees Celsius) and affects the low-temperature heat exchange performance of the dual-row heat exchanger. Utility Model Content
[0003] This application provides a double-row heat exchanger that can reduce the number of distributions and improve the uniformity of refrigerant flow in the second row of the double-row heat exchanger.
[0004] The dual-row heat exchanger provided in this application includes a distribution component, a first manifold, a flow collector, a plurality of first heat exchange tubes, and a plurality of second heat exchange tubes. The distribution component is arranged at intervals from the first manifold. The first heat exchange tubes connect the lumen of the distribution component and the first manifold. The second heat exchange tubes are at least partially located on one side of the width direction of the first heat exchange tubes and connect the lumen of the first manifold and the flow collector. The first manifold includes a plurality of first sub-tubes, which are arranged along the length direction of the first manifold. The number of first heat exchange tubes connected to one first sub-tube is at least two, and one second heat exchange tube is connected to one first sub-tube.
[0005] In this double-row heat exchanger, the first manifold includes multiple first sub-tubes, with at least two first heat exchange tubes connected to one first sub-tube, and one second heat exchange tube connected to one first sub-tube. When the double-row heat exchanger operates as an evaporator, the refrigerant is distributed by the distributor and enters each first heat exchange tube for heat exchange, and then enters the first sub-tube. Since one second heat exchange tube is connected to one first sub-tube, the refrigerant can directly flow into the corresponding connected second heat exchange tube for heat exchange after converging in the first sub-tubes. When the refrigerant enters the second heat exchange tube from the first sub-tube, it no longer needs to be distributed a second time, thereby reducing the number of refrigerant distributions required by the double-row heat exchanger and improving the uniformity of refrigerant flow in the second row of the double-row heat exchanger. Attached Figure Description
[0006] Figure 1 A schematic diagram of the structure of the double-row heat exchanger provided in this application in a specific embodiment;
[0007] Figure 2 for Figure 1 A schematic diagram of the planar structure of a double-row heat exchanger;
[0008] Figure 3 for Figure 1 A schematic diagram of the structure of the double-row heat exchanger on the other side;
[0009] Figure 4 A schematic diagram of the structure of the double-row heat exchanger provided in this application in another specific embodiment;
[0010] Figure 5 for Figure 4 A schematic diagram of the planar structure of a double-row heat exchanger;
[0011] Figure 6 for Figure 4 A schematic diagram of the structure of the double-row heat exchanger on the other side;
[0012] Figure 7 for Figure 4 A partial cross-sectional view of the double-row heat exchanger on the side.
[0013] Figure 8 A schematic diagram of the structure of the double-row heat exchanger provided in this application in yet another specific embodiment;
[0014] Figure 9 This is a schematic diagram of the structure of the fin provided in this application in a specific embodiment.
[0015] Reference numerals: Distributor 1, Second manifold 11, Second sub-pipe 111, First opening 112, Distributor head 12, Distributor pipe 13, Third manifold 14, Third sub-pipe 141, Fourth sub-pipe 142, Second opening 143, First pipe 15, Third opening 151, First partition 16, Second through hole 161, First manifold 2, First sub-pipe 21, First heat exchange pipe 3, First channel 31, Second heat exchange pipe 4, First pipe section 41, First bend section 42, Second channel 43, Collector 5, Fin 6, First slot 61, First through hole 62, Drainage groove 63.
[0016] The accompanying drawings, which are incorporated in and form part of this specification, illustrate embodiments consistent with this application and, together with the description, serve to explain the principles of this application. Detailed Implementation
[0017] To better understand the technical solution of this application, the embodiments of this application will be described in detail below with reference to the accompanying drawings.
[0018] The terminology used in the embodiments of this application is for the purpose of describing particular embodiments only and is not intended to be limiting of this application. The singular forms “a,” “the,” and “the” used in the embodiments of this application and the appended claims are also intended to include the plural forms unless the context clearly indicates otherwise.
[0019] It should be understood that the term "and / or" used in this article is merely a description of the relationship between related objects, indicating that three relationships can exist. For example, A and / or B can represent: A existing alone, A and B existing simultaneously, and B existing alone. Additionally, the character " / " in this article generally indicates that the preceding and following related objects have an "or" relationship.
[0020] It should be noted that the directional terms such as "upper," "lower," "left," and "right" described in the embodiments of this application are used to describe the angles shown in the accompanying drawings and should not be construed as limiting the embodiments of this application. Furthermore, in the context, it should be understood that when it is mentioned that an element is connected "upper" or "lower" to another element, it can be directly connected to the other element "upper" or "lower," or indirectly connected to the other element "upper" or "lower" through an intermediate element.
[0021] like Figure 1-9 As shown in the figure, this application embodiment provides a double-row heat exchanger, which can reduce the number of refrigerant distributions, thereby improving the uniformity of refrigerant flow in the second row of the double-row heat exchanger. Specifically, the double-row heat exchanger mainly includes a distribution component 1, a first manifold 2, a flow collector 5, a plurality of first heat exchange tubes 3, and a plurality of second heat exchange tubes 4. The distribution component 1 is arranged at intervals with the first manifold 2. The first heat exchange tube 3 connects the cavity of the distribution component 1 and the first manifold 2. The second heat exchange tube 4 is located at least partially on one side of the width direction of the first heat exchange tube 3 (when the double-row heat exchanger is working as an evaporator, one side of the first heat exchange tube 3 is the windward side, and one side of the second heat exchange tube 4 is the leeward side). The second heat exchange tube 4 connects the cavity of the first manifold 2 and the manifold 5. The first manifold 2 includes a plurality of first sub-pipes 21, which are arranged along the length direction of the first manifold 2. The number of first heat exchange tubes 3 connected to one first sub-pipe 21 is at least two. A second heat exchange tube 4 is connected to the cavity of one first sub-pipe 21.
[0022] In this embodiment, the first manifold 2 includes multiple first sub-pipes 21, with at least two first heat exchange tubes 3 connected to one first sub-pipe 21, and one second heat exchange tube 4 connected to one first sub-pipe 21. When the double-row heat exchanger operates as an evaporator, the refrigerant is distributed by the distributor 1 and enters each of the first heat exchange tubes 3 for heat exchange, and then enters the first sub-pipe 21. Since one second heat exchange tube 4 is connected to one first sub-pipe 21, the refrigerant can directly flow into the corresponding connected second heat exchange tube 4 for heat exchange after converging in the first sub-pipe 21. When the refrigerant enters the second heat exchange tube 4 from the first sub-pipe 21, there is no need for a second distribution of the refrigerant, reducing the number of refrigerant distributions required by the double-row heat exchanger, thereby improving the uniformity of the refrigerant flow in the second row (within the second heat exchange tube 4) of the double-row heat exchanger.
[0023] It should be further noted that the multiple first sub-pipes 21 in the first manifold 2 are isolated from each other, meaning that the lumens of two adjacent first sub-pipes 21 are not interconnected. The first sub-pipe 21 can be a single pipe body, or it can be formed by dividing the first manifold 2 using partitions or other spacers. Generally, the latter has lower manufacturing costs and is therefore preferred. Furthermore, the length of the first sub-pipe 21 and the number of first heat exchange tubes 3 connected to the first sub-pipe 21 can be determined and preset based on various factors such as the distribution performance of the distribution component 1 and the size of the double-row heat exchanger; these are not specifically limited in this document.
[0024] In this embodiment, a plurality of first heat exchange tubes 3 are arranged at intervals along the length direction of the first manifold 2. Correspondingly, a plurality of second heat exchange tubes 4 are also arranged at intervals along the length direction of the first manifold 2. Fins 6 can also be provided between at least some of the adjacent first heat exchange tubes 3 and / or second heat exchange tubes 4. The heat exchange efficiency can be increased by the fins 6. The specific structure of the fins 6 will be described in subsequent embodiments.
[0025] like Figure 1-3 As shown, in one specific embodiment, the distribution component 1 includes a second manifold 11, which includes a plurality of second sub-pipes 111. The plurality of second sub-pipes 111 are arranged along the length direction of the second manifold 11. The pipe wall of the second sub-pipe 111 is provided with a first opening 112, which communicates with the cavity of the second sub-pipe 111. When the double-row heat exchanger is working as an evaporator, the refrigerant enters the second sub-pipe 111 from the first opening 112.
[0026] In this embodiment, the distribution component 1 includes a second manifold 11. By dividing the second manifold 11 into multiple second sub-pipes 111, the refrigerant entering the double-row heat exchanger is distributed. This allows the refrigerant entering the double-row heat exchanger to enter the first heat exchange tube 3 more evenly after being divided into multiple parts.
[0027] Similar to the first sub-pipe 21, the multiple second sub-pipes 111 are also mutually isolated, meaning that adjacent second sub-pipes 111 are not connected to each other. The multiple second sub-pipes 111 can be formed by separating the second manifold 11 using partitions or other spacers. The length and number of the second sub-pipes 111 can be determined based on factors such as the number of connected first heat exchange tubes 3 and the size of the double-row heat exchanger. Furthermore, the number of first heat exchange tubes 3 connecting the same group of second sub-pipes 111 and first sub-pipes 21 can be the same or different. For example, the same multiple first heat exchange tubes 3 can connect only one second sub-pipe 111 and another first sub-pipe 21, allowing the refrigerant in one second sub-pipe 111 to completely enter another first sub-pipe 21. Alternatively, some of the multiple first heat exchange tubes 3 connected to the second sub-pipe 111 can be connected to one of the first sub-pipes 21, while other parts of the first heat exchange tubes 3 can be connected to other adjacent first sub-pipes 21. This will not be elaborated upon in this paper.
[0028] like Figure 2 As shown, in one specific embodiment, the distribution member 1 further includes a plurality of first partitions 16, the first partitions 16 being at least partially located within the cavity of the second sub-tube 111, the first partitions 16 having at least one second through hole 161, the second through hole 161 communicating with the cavities of the second sub-tube 111 on both sides of the first partitions 16.
[0029] In this embodiment, a first partition 16 with a second through hole 161 is also provided inside the second sub-tube 111. Generally, the first partition 16 is located below the first opening 112. This can prevent the liquid refrigerant from all accumulating into the first heat exchange tube 3 at the bottom of the second sub-tube 111 due to gravity, thereby enabling the refrigerant to enter the first heat exchange tube 3 at each position more evenly and further improving the uniformity of refrigerant distribution.
[0030] It should be noted that the position and number of the first spacers 16 can be determined based on factors such as the length of the second sub-tube 111 and the position of the first opening 112. For example, if the second sub-tube 111 is long and the number of inserted first heat exchange tubes 3 is large, then more first spacers 16 can be spaced out. Additionally, when the first opening 112 is closer to the lower side of the second sub-tube 111, the first spacers 16 can also be located above the first opening 112. This prevents some of the vaporized refrigerant from directly entering the uppermost first heat exchange tube 3 of the second sub-tube 111, thereby improving the uniformity of refrigerant distribution. Therefore, the position of the first spacers 16 can be flexibly set, and this paper does not impose specific limitations on the position and number of the first spacers 16.
[0031] like Figure 4-6As shown, in another specific embodiment, the number of distribution components 1 is multiple. Specifically, the distribution component 1 includes a liquid dispensing head 12 and at least two liquid dispensing pipes 13. One end of the liquid dispensing pipe 13 is connected to the cavity of the first heat exchange tube 3, and the other end of the liquid dispensing pipe 13 is connected to the liquid dispensing head 12. The number of liquid dispensing pipes 13 can be determined according to the number of first heat exchange tubes 3 that need to be connected. If the number of liquid dispensing pipes 13 in the same distribution component 1 is less than two, the number of distribution components 1 required will increase, resulting in increased costs. On the other hand, if the number of liquid dispensing pipes 13 is too large, it will cause uneven distribution. Therefore, generally speaking, the number of liquid dispensing pipes 13 is 3 to 5.
[0032] In this embodiment, the refrigerant entering the double-row heat exchanger is distributed by a liquid distributor 12 and at least two liquid distributor pipes 13. Compared with the second manifold 11 in the previous embodiment, the distribution method of the liquid distributor 12 and liquid distributor pipes 13 in this embodiment can effectively reduce the amount of refrigerant injected. In addition, the liquid distribution method by the liquid distributor 12 can also make the refrigerant distribution more uniform, thereby improving the heat exchange performance of the double-row heat exchanger to a certain extent.
[0033] like Figure 8 As shown, in another specific embodiment, the distribution component 1 includes a third manifold 14 and a first pipe 15. The third manifold 14 includes a third sub-pipe 141 and a fourth sub-pipe 142, which are arranged along the length of the third manifold 14. The first pipe 15 connects the lumens of the third sub-pipe 141 and the fourth sub-pipe 142. The wall of the third sub-pipe 141 is provided with a second opening 143, which communicates with the lumen of the third sub-pipe 141.
[0034] In this embodiment, a third manifold 14 and a first manifold 15 are used to distribute the incoming refrigerant. The refrigerant enters the third sub-manifold 141 through the second opening 143. Part of the incoming refrigerant flows along the extension direction of the first manifold 15 and enters the first heat exchange tubes 3 at various locations (during this process, the first manifold 15 can guide the refrigerant and promote the mixing and flow of gaseous and liquid refrigerant). Another part of the refrigerant can enter the fourth sub-manifold 142 through the first manifold 15 and enter the first heat exchange tubes 3 connected to the fourth sub-manifold 142 for heat exchange. This flow distribution method can reduce the accumulation of refrigerant in the third sub-manifold 141, promote the flow of refrigerant, and thus improve the uniformity of distribution.
[0035] In the above three embodiments, different embodiments of the dispensing component 1 have been described. Of course, the dispensing component 1 can also be other devices or components that can dispense refrigerant, which will not be described in detail here.
[0036] like Figure 8As shown, in one specific embodiment, the first pipe 15 is located inside the third manifold 14, and the length direction of the first pipe 15 extends at least partially along the length direction of the third manifold 14. "At least partially along the length direction of the third manifold 14" means that the length direction of the first pipe 15 can extend completely along the length direction of the third manifold 14, or only a portion of the pipe body can extend along the length direction of the third manifold 14. The wall of the first pipe 15 is provided with at least one third opening 151, located on the side of the first pipe 15 away from the fourth sub-pipe 142. The third opening 151 communicates with the lumen of the first pipe 15. Generally, the third opening 151 penetrates the opposite sidewall of the first pipe 15.
[0037] It is understandable that during the flow of refrigerant, gaseous refrigerant is lighter than liquid refrigerant and is more likely to accumulate in the upper part of the first tube 15, resulting in slow refrigerant flow and hindering refrigerant flow and distribution. Therefore, setting the third opening 151 on the side of the first tube 15 away from the fourth sub-tube 142 (the upper part of the first tube 15) allows the accumulated refrigerant to enter the fourth sub-tube 142 better, thereby effectively solving the above problem.
[0038] like Figure 1-6 As shown, in one specific embodiment, the second heat exchange tube 4 includes a first tube segment 41 and a first bend segment 42. There are multiple first tube segments 41, which are arranged at intervals along the length of the first manifold 2. The first bend segments 42 are connected in series with each of the multiple first tube segments 41. The number and spacing of the first tube segments 41 are not specifically limited herein; generally, they can be adjusted and preset according to the number and spacing of the first heat exchange tubes 3.
[0039] In this embodiment, one side of the first heat exchange tube 3 can be the windward side, and correspondingly, one side of the second heat exchange tube 4 is the leeward side. After the refrigerant has undergone heat exchange through multiple first heat exchange tubes 3, the refrigerant in the first sub-tube 21 can directly enter the corresponding second heat exchange tube 4, and then flow along the arrangement direction of multiple first tube segments 41 and pass through multiple first tube segments 41. This arrangement can make the flow path of the refrigerant in the second heat exchange tube 4 longer. Taking the evaporation condition as an example, this can ensure that the refrigerant in each loop can be fully superheated, enhancing the heat exchange effect. At the same time, the longer flow path can also effectively prevent the problem of different outlet temperatures of the refrigerant in each loop due to distribution issues, thereby playing a role in balancing the outlet temperature to a certain extent.
[0040] like Figure 7As shown, in one specific embodiment, the first heat exchange tube 3 includes a plurality of first channels 31, the length direction of the first channels 31 extends along the length direction of the first heat exchange tube 3, and the plurality of first channels 31 are arranged at intervals along the width direction of the first heat exchange tube 3. The second heat exchange tube 4 includes at least one second channel 43, and the second channel 43 connects the cavity of the first sub-tube 21 and the manifold 5.
[0041] Specifically, in this embodiment, the first heat exchange tube 3 can be a multi-channel microchannel flat tube, while the second heat exchange tube 4 can be a single-channel round or elliptical tube, etc. Because microchannel flat tubes have better heat exchange performance, one side of the first heat exchange tube 3 can be used as the windward side to enhance the heat exchange performance of the double-row heat exchanger, while the second heat exchange tube 4 can be used as the leeward side. After being combined with the fins 6, it can be used to improve the drainage and defrosting capabilities of the double-row heat exchanger. In addition, the manifold 5 can be the same as the first manifold 2, that is, the manifold 5 is a manifold pipe. The refrigerant flowing in the second heat exchange tube 4 eventually flows into the manifold 5 for confluence, and finally flows out of the double-row heat exchanger through the manifold 5.
[0042] like Figure 7 As shown, in a specific embodiment, if the sum of the flow cross-sectional areas of the multiple first channels 31 of a first heat exchange tube 3 is defined as S1, the number of first heat exchange tubes 3 connected to a first sub-tube 21 is N, and the flow cross-sectional area of the second channel 43 of a second heat exchange tube 4 is S2, then S1 and S2 satisfy: 0.6≤S2 / N*S1≤1, thereby reducing the amount of refrigerant charged while ensuring heat exchange performance.
[0043] like Figure 9 As shown, in one specific embodiment, the double-row heat exchanger further includes a plurality of thin-plate fins 6, which are stacked and spaced apart. Each fin 6 has a plurality of first slots 61 and a plurality of first through holes 62. The first slots 61 and the first through holes 62 are spaced apart along the width direction of the fins 6. A first heat exchange tube 3 is disposed in at least a portion of the first slots 61 along the arrangement direction of the fins 6, and a second heat exchange tube 4 is disposed in at least a portion of the first through holes 62 along the arrangement direction of the fins 6.
[0044] In this embodiment, the first heat exchange tube 3 can be a flat tube, while the second heat exchange tube 4 can be a single-channel round tube or an elliptical tube, etc. Therefore, the shapes of the first slot 61 and the first through hole 62 correspond to the first heat exchange tube 3 and the second heat exchange tube 4, respectively. That is, the first slot 61 is a flat slot shape, while the first through hole 62 is a round hole or an elliptical hole shape, and its hole wall is a circular ring or an elliptical ring. After inserting different types of heat exchange tubes, the fin structure can be better combined with different types of heat exchange tubes, thereby achieving better drainage performance and heat exchange performance of the double-row heat exchanger.
[0045] Specifically, because the heat exchange effect is better on the windward side of a double-row heat exchanger during operation, the flat tubes have more and smaller holes, ensuring that the refrigerant flowing through each small hole maintains a high heat exchange efficiency. In contrast, the round or elliptical tubes have much larger holes than the microchannel holes, resulting in most of the refrigerant not directly contacting the heat exchange tube wall, leading to lower heat transfer efficiency. Therefore, a flat tube can be installed on one side of the first slot 61 as the windward side, while a round or elliptical tube can be installed on one side of the first through hole 62 as the leeward side.
[0046] Furthermore, the first slot 61 and the first through hole 62 are arranged on the same fin 6, that is, the first heat exchange tube 3 in the first row and the second heat exchange tube 4 in the rear row share the same fin. Compared with the split fin structure in the double-row heat exchanger, the fin 6 in this embodiment is an integrated structure of front and rear rows. This can avoid the problem of increased wind resistance and affected drainage performance caused by the staggered arrangement of fins.
[0047] like Figure 9 As shown, in one specific embodiment, the fin 6 also has a drainage groove 63, which is located between the first slot 61 and the first through hole 62. The length direction of the drainage groove 63 extends at least partially along the length direction of the fin 6, and the drainage groove 63 is recessed on one side of the thickness direction of the fin 6.
[0048] Combination Figure 9 It is known that since the opening of the first slot 61 extends through one side of the fin 6, condensate on that side is prone to accumulate. The first through-hole 62 has a complete peripheral wall, allowing drainage from both sides. Furthermore, the round tube, compared to the flat tube, is narrower and has a circular arc surface, so it does not obstruct water flow in the direction of gravity. The flat tube, being wider, obstructs water flow from top to bottom, resulting in poorer drainage. Therefore, by arranging the first slot 61 with a flat tube facing the windward side, the condensate near the first slot 61 can be blown by the wind to the vicinity of the drain groove 63 and the first through-hole 62, thus being better discharged outside the fin 6, improving drainage while ensuring sufficient heat exchange. Therefore, this embodiment of the application, by combining the first slot 61 and the first through-hole 62 on the same fin, improves the drainage performance of the fin 6 while maintaining heat exchange performance in a double-row heat exchanger. In addition, the fin 6 may also include other structures such as flanges and windows, which will not be elaborated upon here.
[0049] The above examples illustrate the principles and implementation methods of this application. The descriptions of the embodiments are merely for the purpose of helping to understand the methods and core ideas of this application. It should be noted that those skilled in the art can make various improvements and modifications to this application without departing from its principles, and these improvements and modifications should also fall within the protection scope of this application.
Claims
1. A double-row heat exchanger, characterized in that, The device includes a distribution component (1), a first manifold (2), a flow collector (5), a plurality of first heat exchange tubes (3) and a plurality of second heat exchange tubes (4). The distribution component (1) is arranged at intervals with the first manifold (2). The first heat exchange tubes (3) connect the distribution component (1) and the cavity of the first manifold (2). The second heat exchange tubes (4) are located at least partially on one side of the width direction of the first heat exchange tubes (3). The second heat exchange tubes (4) connect the first manifold (2) and the cavity of the flow collector (5). The first manifold (2) includes a plurality of first sub-tubes (21). The plurality of first sub-tubes (21) are arranged along the length direction of the first manifold (2). The number of first heat exchange tubes (3) connected to one first sub-tube (21) is at least two. One second heat exchange tube (4) is connected to one first sub-tube (21).
2. The double-row heat exchanger according to claim 1, characterized in that, The distribution component (1) includes a second manifold (11), which includes a plurality of second sub-pipes (111). The plurality of second sub-pipes (111) are arranged along the length of the second manifold (11). The wall of the second sub-pipe (111) is provided with a first opening (112), which communicates with the cavity of the second sub-pipe (111).
3. The double-row heat exchanger according to claim 2, characterized in that, The distribution component (1) further includes a plurality of first partitions (16), each first partition (16) being at least partially located within the cavity of the second sub-tube (111), each first partition (16) having at least one second through hole (161) communicating with the cavities of the second sub-tube (111) on both sides of the first partition (16).
4. The double-row heat exchanger according to claim 1, characterized in that, The number of the distribution components (1) is multiple. The distribution component (1) includes a liquid distribution head (12) and at least two liquid distribution tubes (13). One end of the liquid distribution tube (13) is connected to the lumen of the first heat exchange tube (3), and the other end of the liquid distribution tube (13) is connected to the liquid distribution head (12).
5. The double-row heat exchanger according to claim 1, characterized in that, The distribution component (1) includes a third manifold (14) and a first pipe (15). The third manifold (14) includes a third sub-pipe (141) and a fourth sub-pipe (142). The third sub-pipe (141) and the fourth sub-pipe (142) are arranged along the length of the third manifold (14). The first pipe (15) connects the lumens of the third sub-pipe (141) and the fourth sub-pipe (142). The wall of the third sub-pipe (141) is provided with a second opening (143), which is connected to the lumen of the third sub-pipe (141).
6. The double-row heat exchanger according to claim 5, characterized in that, The first tube (15) is located inside the third manifold (14), and the length direction of the first tube (15) extends at least partially along the length direction of the third manifold (14). The tube wall of the first tube (15) is provided with at least one third opening (151), the third opening (151) is located on the side of the first tube (15) away from the fourth sub-tube (142), and the third opening (151) communicates with the lumen of the first tube (15).
7. The double-row heat exchanger according to any one of claims 1-6, characterized in that, The second heat exchange tube (4) includes a first tube section (41) and a first bend section (42). There are multiple first tube sections (41), and multiple first tube sections (41) are arranged at intervals along the length direction of the first manifold (2). The first bend section (42) is connected in series with multiple first tube sections (41).
8. The double-row heat exchanger according to claim 7, characterized in that, The first heat exchange tube (3) includes a plurality of first channels (31), the length direction of the first channel (31) extends along the length direction of the first heat exchange tube (3), and the plurality of first channels (31) are arranged at intervals along the width direction of the first heat exchange tube (3). The second heat exchange tube (4) includes at least one second channel (43), and the second channel (43) connects the first sub-tube (21) and the cavity of the manifold (5).
9. The double-row heat exchanger according to claim 8, characterized in that, Let S1 be the sum of the flow cross-sectional areas of the multiple first channels (31) of a first heat exchange tube (3), N be the number of first heat exchange tubes (3) connected to a first sub-tube (21), and S2 be the flow cross-sectional area of the second channel (43) of a second heat exchange tube (4). Then S1 and S2 satisfy: 0.6≤S2 / N*S1≤1.
10. The double-row heat exchanger according to any one of claims 1-6 or 8-9, characterized in that, The double-row heat exchanger also includes a plurality of fins (6), which are stacked and arranged in layers. Each fin (6) has a plurality of first slots (61) and a plurality of first through holes (62). The first slots (61) and the first through holes (62) are spaced apart along the width direction of the fins (6). The first heat exchange tube (3) is disposed in at least a portion of the first slots (61) along the arrangement direction of the fins (6), and the second heat exchange tube (4) is disposed in at least a portion of the first through holes (62) along the arrangement direction of the fins (6).
11. The double-row heat exchanger according to claim 10, characterized in that, The fin (6) also has a drainage groove (63) located between the first slot (61) and the first through hole (62). The drainage groove (63) extends at least partially along the length direction of the fin (6) and is recessed into one side of the thickness direction of the fin (6).