Double-row heat exchanger

Abstract

The double-row heat exchanger comprises a first heat exchange part and a second heat exchange part, the first heat exchange part comprises a first collecting pipe and a plurality of first heat exchange pipes, the first heat exchange pipes communicate with the first collecting pipe, the first collecting pipe comprises a first pipe section and a second pipe section, and the second heat exchange part is located on one side of the first heat exchange part in the thickness direction; the second heat exchange part comprises a second collecting pipe and a plurality of second heat exchange pipes, the second heat exchange pipes communicate with the second collecting pipe, and the second collecting pipe comprises a third pipe section and a fourth pipe section; the double-row heat exchanger further comprises a first communicating piece, a second communicating piece and a first flow guide piece, the first communicating piece communicates with the first pipe section and the fourth pipe section, the second communicating piece communicates with the third pipe section and the second pipe section, and at least part of the first flow guide piece is located in a pipe cavity of the fourth pipe section. The first pipe at least partially extends along the length direction of the fourth pipe section; the double-row heat exchanger can improve the uniformity of refrigerant distribution.

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] When a double-row heat exchanger is used as an evaporator or heat pump heat exchanger, the heat exchange performance of the first row on the windward side is better than that of the second row. Therefore, in related technologies, most double-row heat exchangers are arranged so that the refrigerant completely passes through the first row for heat exchange before entering the second row. However, after heat exchange in the first row, the dryness of the refrigerant increases. As a result, the vapor-liquid separation of the refrigerant is more severe when it enters the second row, leading to poorer uniformity of refrigerant distribution. In areas where there is a large amount of refrigerant, it will flow towards the outlet, forming a short-circuit phenomenon. This shortens the frosting time of the refrigerant in the heat exchanger and affects the low-temperature performance of the heat exchanger. Utility Model Content

[0003] This application provides a double-row heat exchanger that can improve the uniformity of refrigerant distribution.

[0004] The dual-row heat exchanger provided in this application includes a first heat exchange section and a second heat exchange section. The first heat exchange section includes a first manifold and a plurality of first heat exchange tubes. The first heat exchange tubes are connected to the first manifold. The first manifold includes a first tube segment and a second tube segment, which are arranged along the length direction of the first manifold. The second heat exchange section is located on one side of the thickness direction of the first heat exchange section. The second heat exchange section includes a second manifold and a plurality of second heat exchange tubes. The second heat exchange tubes are connected to the second manifold. The second manifold includes a third tube segment and a fourth tube segment, which are arranged along the length direction of the second manifold.

[0005] The double-row heat exchanger also includes a first connecting member, a second connecting member, and a first flow guide member. The first connecting member connects the first pipe segment and the fourth pipe segment, the second connecting member connects the third pipe segment and the second pipe segment, and the first flow guide member is at least partially located in the cavity of the fourth pipe segment. The first flow guide member includes a first pipe, and the first pipe extends at least partially along the length direction of the fourth pipe segment.

[0006] In operation, the first heat exchange section of this double-row heat exchanger can be positioned as the windward side. A portion of the refrigerant flowing in the first heat exchange section can be collected in the first pipe section and then enter the fourth pipe section of the second heat exchange section through the first connecting piece. The first pipe in the fourth pipe section acts as a guide for the refrigerant, allowing it to flow and distribute along its length. This helps reduce refrigerant vapor-liquid separation and improves the uniformity of refrigerant distribution in the fourth pipe section. Furthermore, a portion of the refrigerant flowing in the second heat exchange section can be collected in the third pipe section and then enter the second pipe section through the second connecting piece, subsequently undergoing flow heat exchange in the first heat exchange section. This staggered flow of the refrigerant between the first and second heat exchange sections reduces the change in refrigerant dryness as it moves from the first row to the second row, thereby reducing refrigerant vapor-liquid separation and improving the uniformity of refrigerant distribution. Attached Figure Description

[0007] Figure 1 A schematic diagram of the structure of the double-row heat exchanger provided in this application in a specific embodiment;

[0008] Figure 2 A schematic diagram of the structure of the double-row heat exchanger provided in this application in a second specific embodiment;

[0009] Figure 3 for Figure 2 A partial cross-sectional view of the double-row heat exchanger.

[0010] Figure 4 for Figure 2 A partial structural schematic diagram of the first flow guide in one specific embodiment;

[0011] Figure 5 for Figure 2 A top view of the first and second manifolds in a specific embodiment;

[0012] Figure 6 This is a schematic diagram of the flow path of the refrigerant in the first heat exchange section.

[0013] Figure 7 A schematic diagram of the structure of the double-row heat exchanger provided in this application in a third specific embodiment;

[0014] Figure 8 A schematic diagram of the structure of the double-row heat exchanger provided in this application in the fourth specific embodiment.

[0015] Reference numerals: First heat exchange section 1, first manifold 11, first pipe section 111, second pipe section 112, third sub-pipe section 113, fourth sub-pipe section 114, first heat exchange tube 12, third manifold 14, fifth pipe section 141, sixth pipe section 142, second heat exchange section 2, second manifold 21, third pipe section 211, fourth pipe section 212, first sub-pipe section 213, second sub-pipe section 214, second heat exchange tube 22, fourth manifold 24, seventh pipe section 241, eighth pipe section 242, first connecting member 3, second connecting member 4, first flow guide member 5, first pipe 51, first partition 52, second partition 53, second flow guide member 6, third partition 61, second pipe 62, fourth partition 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 1-8As shown in the figure, this application embodiment provides a double-row heat exchanger, which can improve the uniformity of refrigerant distribution. Specifically, the double-row heat exchanger mainly includes a first heat exchange section 1 and a second heat exchange section 2. The first heat exchange section 1 includes a first manifold 11 and a plurality of first heat exchange tubes 12. The plurality of first heat exchange tubes 12 are arranged at intervals along the length direction of the first manifold 11 and are connected to the first manifold 11. The first manifold 11 includes a first pipe section 111 and a second pipe section 112, which are arranged along the length direction of the first manifold 11. The second heat exchange section 2 is located on one side of the thickness direction of the first heat exchange section 1. The second heat exchange section 2 includes a second manifold 21 and a plurality of second heat exchange tubes 22. The plurality of second heat exchange tubes 22 are arranged at intervals along the length direction of the second manifold 21 and are connected to the second manifold 21. The second manifold 21 includes a third tube segment 211 and a fourth tube segment 212. The third tube segment 211 and the fourth tube segment 212 are arranged along the length direction of the second manifold 21.

[0022] In addition, the double-row heat exchanger also includes a first connecting member 3, a second connecting member 4 and a first flow guide member 5. The first connecting member 3 connects the first pipe section 111 and the fourth pipe section 212. The second connecting member 4 connects the third pipe section 211 and the second pipe section 112. The first flow guide member 5 is at least partially located in the cavity of the fourth pipe section 212. The first flow guide member 5 includes a first pipe 51, which extends at least partially along the length direction of the fourth pipe section 212.

[0023] In this embodiment, the first manifold 11 and the second manifold 21 can be an integral pipe structure or a separate pipe structure. The first manifold 11 includes a first pipe segment 111 and a second pipe segment 112 arranged along its length. Generally, the first pipe segment 111 and the second pipe segment 112 are not interconnected. The first pipe segment 111 and the second pipe segment 112 can be two independent pipe bodies, or they can be formed by separating the first manifold 11 through partitions or other partitions. Generally, the latter is simpler in process and lower in cost, so the latter is preferred in this embodiment. Correspondingly, the third pipe segment 211 and the fourth pipe segment 212 of the second manifold 21 are also not interconnected, and their specific structures can be the same as or similar to those of the first manifold 11, so they will not be described in detail here.

[0024] Furthermore, the first heat exchange tube 12 and the second heat exchange tube 22 can be microchannel flat tubes, single-channel circular tubes, or other forms of heat exchange tubes. Fins can also be provided between at least a portion of the spaced-apart first heat exchange tubes 12 and between at least a portion of the spaced-apart second heat exchange tubes 22, thereby increasing heat exchange efficiency. These fins can be flat fins, corrugated fins, or other fin structures; this is not specifically limited herein. In addition, the first connecting member 3 and the second connecting member 4 serve to connect the corresponding pipe sections respectively. Therefore, the first connecting member 3 and the second connecting member 4 can be common pipe fittings in the art, such as jumpers, which will not be elaborated upon further.

[0025] In this embodiment, during operation of the dual-row heat exchanger, the first heat exchange section 1 can be positioned as the windward side. A portion of the refrigerant flowing in the first heat exchange section 1 can be collected in the first pipe section 111 and then enter the fourth pipe section 212 of the second heat exchange section 2 through the first connecting member 3. The first pipe 51 in the fourth pipe section 212 can guide the refrigerant, allowing it to flow and distribute along the length of the first pipe 51, which helps reduce refrigerant vapor-liquid separation and improves the uniformity of refrigerant distribution in the fourth pipe section 212. Furthermore, a portion of the refrigerant flowing in the second heat exchange section 2 can be collected in the third pipe section 211 and then enter the second pipe section 112 through the second connecting member 4, subsequently undergoing flow heat exchange in the first heat exchange section 1. The staggered flow of the refrigerant between the first heat exchange section 1 and the second heat exchange section 2 reduces the change in refrigerant dryness as it moves from the first row to the second row, thereby reducing refrigerant vapor-liquid separation and improving the uniformity of refrigerant distribution.

[0026] like Figure 3-7 As shown, in one specific embodiment, the first guide member 5 further includes a first partition 52, the fourth pipe section 212 includes a first sub-pipe section 213 and a second sub-pipe section 214, the first sub-pipe section 213 and the second sub-pipe section 214 are respectively located on both sides of the first partition 52, the first pipe 51 connects the first sub-pipe section 213 and the second sub-pipe section 214, and the first connecting member 3 connects the first pipe section 111 and the first sub-pipe section 213.

[0027] In this embodiment, the fourth pipe segment 212 can be divided into a first sub-pipe segment 213 and a second sub-pipe segment 214 by the first partition 52. When the first sub-pipe segment 213 and the second sub-pipe segment 214 are not connected by the first pipe 51, the first sub-pipe segment 213 and the second sub-pipe segment 214 are not interconnected. After connecting the first sub-pipe segment 213 and the second sub-pipe segment 214 by the first pipe 51, the first pipe 51 can guide the refrigerant entering the first sub-pipe segment 213, so that the entering refrigerant flows and is distributed into each connected second heat exchange pipe 22 along the length direction of the first pipe 51. Another part of the refrigerant can enter the second sub-pipe segment 214 through the first pipe 51. This distribution method can reduce the accumulation of refrigerant in the first sub-pipe segment 213, promote the flow of refrigerant, and thus allow the liquid refrigerant and gaseous refrigerant to mix and flow further, making the distribution of refrigerant more uniform, thereby improving the heat exchange performance of the heat exchanger.

[0028] like Figure 3-7 As shown, in one specific embodiment, the first guide member 5 further includes a second partition 53. The second partition 53 is located in the cavity of the first sub-pipe section 213, and there is a preset gap between the second partition 53 and the pipe wall of the first sub-pipe section 213. Generally, the second partition 53 is located near the top of the first pipe 51. The second partition 53 can block the upward flowing refrigerant to a certain extent. Since the gaseous refrigerant is lighter, more gaseous refrigerant is blocked, allowing a portion of the gaseous refrigerant to be distributed into the second heat exchange tube 22 below the second partition 53 to balance the gas-liquid ratio. At the same time, the second partition 53 can also spray the passing refrigerant, promoting the gas-liquid mixing of this portion of the refrigerant to a certain extent and promoting the uniformity of distribution.

[0029] It should be noted that the second partition 53 can be of various shapes. It can be installed in the cavity of the first sub-pipe section 213 by sleeve on the outer wall of the first pipe 51 and fixedly connected to the first pipe 51. In addition, the second partition 53 can also be provided with through holes to allow a small amount of refrigerant to pass through. Such through holes can also play a role in spraying refrigerant.

[0030] like Figure 1-3 As shown, in one specific embodiment, the length of the first pipe segment 111 is less than the length of the second pipe segment 112, and / or the length of the third pipe segment 211 is less than the length of the fourth pipe segment 212. The first pipe segment 111 is adjacent to the third pipe segment 211, and the second pipe segment 112 is adjacent to the fourth pipe segment 212.

[0031] The dual-row heat exchanger described in this paper includes two flow paths. After the refrigerant enters the dual-row heat exchanger, one path of refrigerant enters the first pipe section 111 through part of the first heat exchange tube 12, and then enters the fourth pipe section 212 through the first connecting member 3. The other path of refrigerant enters the third pipe section 211 through part of the second heat exchange tube 22, and then enters the second pipe section 112 through the second connecting member 4. Since the first pipe section 111 is adjacent to the third pipe section 211, and the second pipe section 112 is adjacent to the fourth pipe section 212, this arrangement allows the refrigerant to flow alternately between the front and rear rows. This reduces the distribution and heat transfer differences caused by the small temperature difference and high dryness of the second heat exchange section 2 on the leeward side. The cross-flow pattern can guide some of the heat transfer deficit on the leeward side to the windward side, compensating for it with a high temperature difference. The staggered arrangement of the cross-flow paths also helps to ensure the heat transfer uniformity of the entire heat exchanger under uneven wind conditions.

[0032] Furthermore, the length of the first pipe section 111 is shorter than the length of the second pipe section 112, and / or the length of the third pipe section 211 is shorter than the length of the fourth pipe section 212. This allows components that play a guiding or distributing role (such as the first flow guide 5) to be concentrated in the second pipe section 112 and the fourth pipe section 212. In addition, this asymmetrical design can further utilize the difference in the temperature difference between the windward and leeward heat exchange, which is beneficial for controlling the different flow requirements of the two different loops by the difference in the number of heat exchange tubes (the first heat exchange tube 12 and the second heat exchange tube 22) according to the characteristics of the two different loops.

[0033] like Figure 3 and Figure 7 As shown, in one specific embodiment, the double-row heat exchanger further includes a second flow guide 6, which is located in the cavity of the second pipe section 112. The second flow guide 6 includes a third partition 61 and a second pipe 62. The second pipe section 112 includes a third sub-pipe section 113 and a fourth sub-pipe section 114, which are located on both sides of the third partition 61. The second pipe 62 extends at least partially along the length direction of the second pipe section 112 and connects the third sub-pipe section 113 and the fourth sub-pipe section 114. The second connecting member 4 connects the third pipe section 211 and the third sub-pipe section 113.

[0034] Similar to the function of the first guide member 5 in the above embodiment, the second guide member 6 is mainly used to guide and distribute the flow in the second pipe section 112. Its composition and principle are similar to those of the first guide member 5, so they will not be described in detail here.

[0035] like Figure 3 and Figure 7As shown, in one specific embodiment, the second guide member 6 further includes a fourth partition 63, which is located in the cavity of the third sub-pipe section 113, and a preset gap exists between the fourth partition 63 and the pipe wall of the third sub-pipe section 113. Similarly, the fourth partition 63 also plays a certain role in blocking and spraying the refrigerant, allowing a portion of the vaporized refrigerant to be distributed into the first heat exchange tube 12 below the fourth partition 63, thereby balancing the gas-liquid ratio. At the same time, the fourth partition 63 can also spray the passing refrigerant, promoting vapor-liquid mixing to a certain extent, thereby promoting the uniformity of refrigerant distribution.

[0036] like Figure 5 As shown, in one specific embodiment, if the minimum gap between the fourth spacer 63 on the side away from the second manifold 21 and the wall of the third sub-pipe segment 113 is defined as L1, and the minimum gap between the fourth spacer 63 on the side close to the second manifold 21 and the wall of the third sub-pipe segment 113 is defined as L2, then L1 > L2.

[0037] A double-row heat exchanger has a windward side and a leeward side during operation. It's understood that the heat exchange effect is better on the windward side. Therefore, directing more refrigerant to the windward side can improve the heat exchange effect of the double-row heat exchanger to a certain extent. In this embodiment, the minimum gap L1 between the fourth partition 63 and the inner wall of the third sub-pipe section 113 on the side away from the second manifold 21 is greater than the minimum gap L2 on the side closer to the second manifold 21. Therefore, with the first heat exchange section 1 as the windward side, the different gap sizes on the front and rear sides of the fourth partition 63 allow more refrigerant to pass through the side with the larger gap (windward side) after passing through the fourth partition 63, while less refrigerant passes through the side with the smaller gap (leeward side). Since the side with more refrigerant is the windward side, the heat exchange is more complete, resulting in a better heat exchange effect for the double-row heat exchanger.

[0038] In addition, the first heat exchange tube 12 can also be configured as a flat tube with non-uniform holes. The flow cross-sectional area of ​​the flat tube hole of the first heat exchange tube 12 is larger near the windward side (one side of gap L1) and smaller near the leeward side (one side of gap L2). This allows more refrigerant flow to be accommodated on the windward side of the first heat exchange tube 12, while reducing the refrigerant flow on the leeward side. When used together, this combination can achieve a better heat exchange effect.

[0039] like Figure 1-3 and Figure 7-8As shown, in one specific embodiment, the first heat exchange section 1 further includes a third manifold 14, which includes a fifth pipe segment 141 and a sixth pipe segment 142, which are arranged along the length of the third manifold 14; among the plurality of first heat exchange tubes 12, at least one first heat exchange tube 12 is connected to the fifth pipe segment 141 and the second pipe segment 112, a portion of the first heat exchange tubes 12 is connected to the fifth pipe segment 141 and the first pipe segment 111, and another portion of the first heat exchange tubes 12 is connected to the sixth pipe segment 142 and the second pipe segment 112.

[0040] like Figure 1-3 and Figure 7-8 As shown, in one specific embodiment, the second heat exchange section 2 further includes a fourth manifold 24, which includes a seventh pipe segment 241 and an eighth pipe segment 242, which are arranged along the length of the fourth manifold 24. Among the plurality of second heat exchange tubes 22, at least one second heat exchange tube 22 connects the seventh pipe segment 241 and the fourth pipe segment 242, a portion of the second heat exchange tubes 22 connects the seventh pipe segment 241 and the third pipe segment 211, and another portion of the second heat exchange tubes 22 connects the eighth pipe segment 242 and the fourth pipe segment 212.

[0041] In this embodiment, when the double-row heat exchanger operates as an evaporator, a portion of the refrigerant enters from the fifth pipe section 141, undergoes cross-flow heat exchange from front to back, and exits from the eighth pipe section 242 of the second row. Another portion of the refrigerant enters from the seventh pipe section 241, undergoes cross-flow heat exchange from back to front, and exits from the sixth pipe section 142 of the first row. This heat exchange tube connecting the fifth pipe section 141 and the second pipe section 112 can introduce a portion of the refrigerant into the second pipe section 112. Because the flow rate is faster, it can disturb the refrigerant flowing within the second pipe section 112, thereby promoting uniform refrigerant distribution. Furthermore, when the double-row heat exchanger is in condensation mode, the second guide element 6 increases flow resistance and the refrigerant flow path. Therefore, this connection method also allows a portion of the refrigerant in the second pipe section 112 to directly enter the fifth pipe section 141, thereby increasing the heat exchange performance of the double-row heat exchanger in condensation mode. Similarly, the second heat exchange tube 22, which connects the seventh tube segment 241 and the fourth tube segment 212, can also play a similar role, which will not be elaborated on in this article.

[0042] like Figure 6-8As shown, in one specific embodiment, if the number of first heat exchange tubes 12 connecting the sixth pipe segment 142 and the second pipe segment 112 is defined as A1, and the number of first heat exchange tubes 12 connecting the fifth pipe segment 141 and the first pipe segment 111 is defined as A2, then 1 / 10 ≤ A2 / A1 ≤ 2 / 5. Alternatively, if the number of second heat exchange tubes 22 connecting the eighth pipe segment 242 and the fourth pipe segment 212 is defined as A3, and the number of second heat exchange tubes 22 connecting the seventh pipe segment 241 and the third pipe segment 211 is defined as A4, then 1 / 10 ≤ A4 / A3 ≤ 2 / 5, and A1 ≥ A3, A2 ≤ A4.

[0043] When the double-row heat exchanger operates as an evaporator, the first heat exchange tube 12 connecting the fifth pipe section 141 and the first pipe section 111, and the second heat exchange tube 22 connecting the seventh pipe section 241 and the third pipe section 211, can serve as the auxiliary heat exchange section flow of the double-row heat exchanger. Correspondingly, the first heat exchange tube 12 connecting the sixth pipe section 142 and the second pipe section 112, and the second heat exchange tube 22 connecting the eighth pipe section 242 and the fourth pipe section 212 constitute the main heat exchange section flow of the double-row heat exchanger. When A2≤A4, the number of heat exchange tubes in the leeward auxiliary heat section is increased, while the number of heat exchange tubes in the windward auxiliary heat section is decreased. Since the refrigerant in the leeward auxiliary heat section flows into the upper part of the windward side, the number of tubes in the leeward auxiliary heat section increases. This increases the amount of refrigerant in this path, allowing more refrigerant to enter the main heat exchange section on the windward side. This fully utilizes the characteristic of the large temperature difference on the windward side, which allows for heating more refrigerant, thereby maximizing the advantages of the windward side and improving the overall heat exchange performance of the double-row heat exchanger.

[0044] Similarly, since the refrigerant in the auxiliary heating section on the windward side flows into the upper part of the main heat exchange section on the leeward side, the number of heat exchange tubes in the auxiliary heating section on the windward side is reduced. This results in a smaller amount of refrigerant entering the main heat exchange section on the leeward side. Because the temperature difference on the leeward side is smaller, less refrigerant can be heated. Therefore, by reducing the refrigerant supply based on the characteristics of the leeward side, a stable superheat is ensured in the leeward section. Due to the more balanced superheat, the overall performance of the dual-row heat exchanger is better. Therefore, the non-flush design of the auxiliary heating section and the main heating section in this embodiment can improve superheat stability and heat exchange efficiency.

[0045] like Figure 8 As shown, in one specific embodiment, the length of the first heat exchange tube 12 is less than the length of the second heat exchange tube 22. The length of the first heat exchange tube 12 is defined as L3 and the length of the second heat exchange tube 22 is defined as L4. Then, 1 / 20≤L4-L3 / L3≤1 / 10.

[0046] In this embodiment, the length of the first heat exchange tube 12 is less than the length of the second heat exchange tube 22, meaning that a portion of the second heat exchange tube 22 is not blocked by the first heat exchange tube 12. Fresh air can be directly blown into this part of the second heat exchange tube 22, improving the heat exchange effect of the second heat exchange tube 22 in this area. Specifically, this allows air that has not undergone heat exchange to directly exchange heat with the end on the leeward side, increasing the superheat of the leeward side outlet through a large temperature difference. Taking the evaporation condition as an example, this allows the refrigerant flowing out from the leeward side to achieve a greater superheat, balancing the outlet temperatures of the two rows and avoiding the problem of faster frost formation on the leeward side under frost conditions.

[0047] 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-pipe heat exchanger, characterized by, The device includes a first heat exchange section (1) and a second heat exchange section (2). The first heat exchange section (1) includes a first manifold (11) and a plurality of first heat exchange tubes (12). The first heat exchange tubes (12) are connected to the first manifold (11). The first manifold (11) includes a first tube segment (111) and a second tube segment (112). The first tube segment (111) and the second tube segment (112) are arranged along the length direction of the first manifold (11). The second heat exchange section (2) is located on one side of the thickness direction of the first heat exchange section (1). The second heat exchange section (2) includes a second manifold (21) and a plurality of second heat exchange tubes (22). The second heat exchange tubes (22) are connected to the second manifold (21). The second manifold (21) includes a third tube segment (211) and a fourth tube segment (212). The third tube segment (211) and the fourth tube segment (212) are arranged along the length direction of the second manifold (21). The double-row heat exchanger further includes a first connecting member (3), a second connecting member (4), and a first flow guide (5). The first connecting member (3) connects the first pipe section (111) and the fourth pipe section (212). The second connecting member (4) connects the third pipe section (211) and the second pipe section (112). The first flow guide (5) is at least partially located in the cavity of the fourth pipe section (212). The first flow guide (5) includes a first pipe (51), which extends at least partially along the length direction of the fourth pipe section (212).

2. The double-pass heat exchanger of claim 1, wherein The first guide member (5) further includes a first partition (52), and the fourth pipe section (212) includes a first sub-pipe section (213) and a second sub-pipe section (214). The first sub-pipe section (213) and the second sub-pipe section (214) are located on both sides of the first partition (52). The first pipe (51) connects the first sub-pipe section (213) and the second sub-pipe section (214). The first connecting member (3) connects the first pipe section (111) and the first sub-pipe section (213).

3. The double-pass heat exchanger of claim 2, wherein The first guide member (5) further includes a second partition (53), which is located in the cavity of the first sub-pipe section (213) and has a preset gap between the second partition (53) and the pipe wall of the first sub-pipe section (213).

4. The double-pass heat exchanger according to any one of claims 1-3, characterized in that, The length of the first pipe segment (111) is less than the length of the second pipe segment (112), and / or the length of the third pipe segment (211) is less than the length of the fourth pipe segment (212). The first pipe segment (111) is adjacent to the third pipe segment (211), and the second pipe segment (112) is adjacent to the fourth pipe segment (212).

5. The double-pass heat exchanger according to claim 4, characterized in that The double-row heat exchanger also includes a second flow guide (6), which is located in the cavity of the second pipe section (112). The second flow guide (6) includes a third partition (61) and a second pipe (62). The second pipe section (112) includes a third sub-pipe section (113) and a fourth sub-pipe section (114). The third sub-pipe section (113) and the fourth sub-pipe section (114) are located on both sides of the third partition (61). The second pipe (62) extends at least partially along the length direction of the second pipe section (112). The second pipe (62) connects the third sub-pipe section (113) and the fourth sub-pipe section (114). The second connecting member (4) connects the third pipe section (211) and the third sub-pipe section (113).

6. The double-pass heat exchanger according to claim 5, characterized in that The second flow guide (6) also includes a fourth partition (63), which is located in the cavity of the third sub-pipe section (113) and has a preset gap between the fourth partition (63) and the pipe wall of the third sub-pipe section (113).

7. The double-pass heat exchanger according to claim 6, characterized in that The minimum gap between the fourth partition (63) and the wall of the third sub-pipe segment (113) on the side away from the second manifold (21) is defined as L1, and the minimum gap between the fourth partition (63) and the wall of the third sub-pipe segment (113) on the side close to the second manifold (21) is defined as L2, then L1 > L2.

8. The double-pass heat exchanger according to any of claims 1-3 or 5-7, characterized in that, The first heat exchange section (1) further includes a third manifold (14), which includes a fifth pipe section (141) and a sixth pipe section (142). The fifth pipe section (141) and the sixth pipe section (142) are arranged along the length direction of the third manifold (14). Among the plurality of first heat exchange tubes (12), at least one first heat exchange tube (12) connects the fifth pipe section (141) and the second pipe section (112), a portion of the first heat exchange tubes (12) connect the fifth pipe section (141) and the first pipe section (111), and another portion of the first heat exchange tubes (12) connect the sixth pipe section (142) and the second pipe section (112).

9. The double-pass heat exchanger according to claim 8, characterized in that The second heat exchange section (2) further includes a fourth manifold (24), which includes a seventh pipe segment (241) and an eighth pipe segment (242), which are arranged along the length of the fourth manifold (24); among the plurality of second heat exchange tubes (22), at least one second heat exchange tube (22) connects the seventh pipe segment (241) and the fourth pipe segment (212), a portion of the second heat exchange tubes (22) connects the seventh pipe segment (241) and the third pipe segment (211), and another portion of the second heat exchange tubes (22) connects the eighth pipe segment (242) and the fourth pipe segment (212).

10. The double-pass heat exchanger according to claim 9, characterized in that Let A1 be the number of first heat exchange tubes (12) connecting the sixth pipe segment (142) and the second pipe segment (112), and let A2 be the number of first heat exchange tubes (12) connecting the fifth pipe segment (141) and the first pipe segment (111). Then 1 / 10≤A2 / A1≤2 / 5.

11. The double-pass heat exchanger according to claim 10, characterized in that Define the number of second heat exchange tubes (22) connecting the eighth pipe segment (242) and the fourth pipe segment (212) as A3, and the number of second heat exchange tubes (22) connecting the seventh pipe segment (241) and the third pipe segment (211) as A4. Then 1 / 10≤A4 / A3≤2 / 5, and A1≥A3, A2≤A4.

12. The double-pass heat exchanger according to any of claims 1-3 or 5-7 or 9-11, characterized in that, The length of the first heat exchange tube (12) is less than the length of the second heat exchange tube (22). The length of the first heat exchange tube (12) is defined as L3 and the length of the second heat exchange tube (22) is defined as L4. Then 1 / 20≤(L4-L3) / L3≤1 / 10.

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