Heat exchanger

Abstract

The heat exchanger comprises a first header part, a second header part and a plurality of heat exchange pipes, the first header part comprises a first header, the first header is provided with a first connector, the second header part comprises a second header, the second header and the first header are arranged at intervals, and the heat exchange pipes communicate with the first header and the second header; the first header part further comprises a flow guide part, at least part of the flow guide part is located in a pipe cavity of the first header, and the flow guide part is located between the first connector and a pipe opening of the heat exchange pipe. One face perpendicular to the length direction of the heat exchange pipe is defined as a first projection face, and on the first projection face, the projection of the flow guide piece can shield the projection of the first connector and / or shield the projection of the pipe opening of the heat exchange pipe; the 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 heat exchanger for a heat pump. Background Technology

[0002] A distribution pipe can be installed within a manifold of a heat exchanger to improve the uniformity of refrigerant distribution when the heat exchanger is operating as an evaporator. However, because the heat exchanger tubes need to be inserted to a certain depth into the manifold, and the distribution pipe cannot be too large to ensure refrigerant flow rate and distribution performance, this can easily lead to an excessively large gap between the distribution pipe and the manifold. After the refrigerant enters the manifold from the inlet, most of the refrigerant will pass through this gap and directly enter the heat exchanger tubes in the vicinity of the inlet, reducing the amount of refrigerant flowing upwards into other heat exchanger tubes, resulting in uneven refrigerant distribution within the heat exchanger. Utility Model Content

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

[0004] The heat exchanger provided in this application includes a first manifold section, a second manifold section, and a plurality of heat exchange tubes. The first manifold section includes a first manifold with a first interface. The second manifold section includes a second manifold, which is arranged at a distance from the first manifold. The heat exchange tubes connect the first manifold and the second manifold. The first manifold section further includes a flow guide, which is at least partially located within the cavity of the first manifold and between the first interface and the opening of the heat exchange tube. A surface perpendicular to the length direction of the heat exchange tube is defined as a first projection surface. On the first projection surface, the projection of the flow guide can cover the projection of the first interface and / or cover at least part of the projection of the opening of the heat exchange tube.

[0005] The flow guide of the heat exchanger is located between the first interface and the inlet of the heat exchange tube, and the projection of the flow guide on the first projection plane can cover the projection of the first interface and / or at least part of the projection of the heat exchange tube inlet. Therefore, when the heat exchanger operates as an evaporator, the flow guide can block the refrigerant flowing from the first interface to the heat exchange tube inlet to a certain extent, reducing the refrigerant flow rate that directly enters the heat exchange tube after entering from the first interface. This allows more refrigerant to flow along the length of the flow guide and enter each heat exchange tube, thereby improving the uniformity of refrigerant distribution in the heat exchanger. Attached Figure Description

[0006] Figure 1 A schematic diagram of the structure of the heat exchanger provided in this application in a specific embodiment;

[0007] Figure 2 for Figure 1A top-view projection of the flow guide and heat exchange tubes on the first projection plane;

[0008] Figure 3 A schematic diagram of the structure of the first manifold section provided in this application in a specific embodiment;

[0009] Figure 4 A schematic diagram of the structure of the first manifold section provided in this application in a second specific embodiment;

[0010] Figure 5 A schematic diagram of the structure of the first manifold section provided in this application in a third specific embodiment;

[0011] Figure 6 A schematic diagram of the structure of the first manifold section provided in this application in a fourth specific embodiment;

[0012] Figure 7 A schematic diagram of the structure of the heat exchanger provided in this application in another specific embodiment.

[0013] Reference numerals: First manifold 1, First manifold 11, First interface 111, First pipe section 112, Second pipe section 113, First separator 12, Flow guide 13, First pipe 131, First plate 132, Second pipe 133, First sidewall 134, Second sidewall 135, First arc-shaped section 136, Second separator 14, Gap hole 141, First hole 15, Interface pipe 16, Second hole 161, Second manifold 2, Second manifold 21, Heat exchanger pipe 3, First projected surface 4.

[0014] 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

[0015] 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.

[0016] It should be understood that the described embodiments are merely a part of the technical solutions of this application, and not all of them. All other technical solutions obtained by those skilled in the art based on the technical solutions in this application without inventive effort are within the scope of protection of this application.

[0017] 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.

[0018] 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.

[0019] 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.

[0020] like Figure 1-7 As shown in the figure, this application provides a heat exchanger, which includes a first manifold section 1, a second manifold section 2, and a plurality of heat exchange tubes 3. The first manifold section 1 includes a first manifold 11 with a first interface 111. The second manifold section 2 includes a second manifold 21, which is arranged at a distance from the first manifold 11. The heat exchange tubes 3 connect the first manifold 11 and the second manifold 21. The first manifold section 1 also includes a flow guide 13, which is at least partially located in the cavity of the first manifold 11 and between the first interface 111 and the opening of the heat exchange tubes 3. A surface perpendicular to the length direction of the heat exchange tubes 3 is defined as a first projection surface. On the first projection surface, the projection of the flow guide 13 can cover the projection of the first interface 111 and / or cover at least part of the projection of the opening of the heat exchange tubes 3.

[0021] It should be noted that the heat exchange tube 3 in the embodiments of this application can be a microchannel flat tube, a small round tube, or other types of heat exchange tubes, without specific limitations. Furthermore, in the embodiments of this application, the term "at least partially" in descriptions such as "at least partially located within" should be interpreted broadly. For example, "the flow guide 13 is at least partially located within the first manifold 11," meaning that the flow guide 13 can be completely located within the first manifold 11, or only partially located within the first manifold 11, and can be adjusted according to the actual scenario and assembly requirements. Other expressions in the following text have similar meanings; therefore, they will not be elaborated upon further.

[0022] In this embodiment, the flow guide 13 of the heat exchanger is located between the first interface 111 and the inlet of the heat exchange tube 3, and the projection of the flow guide 13 on the first projection plane 4 can cover the projection of the first interface 111 and / or cover at least part of the projection of the inlet of the heat exchange tube 3. Therefore, when the heat exchanger is working as an evaporator, the flow guide 13 can block the refrigerant flowing from the first interface 111 to the inlet of the heat exchange tube 3 to a certain extent, reducing the flow rate of refrigerant that directly enters the heat exchange tube 3 after entering from the first interface 111, so that more refrigerant flows along the length direction of the flow guide 13 and is distributed, thereby improving the uniformity of refrigerant distribution in the heat exchanger.

[0023] Furthermore, when the heat exchanger operates as an evaporator, the refrigerant entering the heat exchanger is in a two-phase state of gas and liquid. Since the gas portion flows faster than the liquid portion, after the refrigerant enters the first manifold 11 from the first inlet 111, the heat exchange tubes 3 in the vicinity of the first inlet 111 not only receive more refrigerant but also exhibit a higher proportion of gaseous refrigerant than liquid refrigerant, resulting in uneven gas-liquid distribution. Therefore, the obstruction formed by the flow guide 13 at least directly opposite the first inlet 111 not only reduces the amount of refrigerant entering but also promotes the mixing of gaseous and liquid refrigerant after the refrigerant impacts the flow guide 13, thereby improving the uniformity of the refrigerant's gas-liquid distribution.

[0024] like Figure 2 As shown, in one specific embodiment, if the width of the flow guide 13 projected on the first projection plane is defined as L1, and the length of the heat exchange tube 3 projected on the first projection plane is defined as L2, then: L1≥L2.

[0025] like Figure 1 As shown, in one specific embodiment, the first manifold 1 further includes a first partition 12, which is at least partially located within the first manifold 11. The first manifold 11 includes a first pipe section 112 and a second pipe section 113, which are located on opposite sides of the first partition 12. A flow guide 13 connects the first pipe section 112 and the second pipe section 113. A first interface 111 is located in the first pipe section 112 and is close to the first partition 12.

[0026] Specifically, in this embodiment, the first separator 12 can be a separator plate. By separating the first manifold 11 with the first separator 12 to form the first pipe segment 112 and the second pipe segment 113, the refrigerant can be prevented from falling out due to gravity after entering from the first interface 111. When the guide member 13 is not connecting the first pipe segment 112 and the second pipe segment 113, the first separator 12 can completely isolate the first pipe segment 112 and the second pipe segment 113 (i.e., the refrigerant does not flow). After the guide member 13 connects the first pipe segment 112 and the second pipe segment 113, a portion of the refrigerant in the first pipe segment 112 can enter the second pipe segment 113 through the guide member 13. Since the refrigerant flows from high pressure to low pressure, and the first pipe section 112 is connected to the first interface 111, its internal pressure is greater than that of the second pipe section 113. This allows the refrigerant to continuously flow from the first pipe section 112 to the second pipe section 113, enabling the refrigerant in both pipe sections to flow better and facilitating the uniform distribution of the refrigerant.

[0027] In this embodiment, the first interface 111 being close to the first separator 12 means that the distance from the first interface 111 to the first separator 12 is much smaller than the distance from the first interface 111 to the other end of the first pipe segment 112. Generally, in order to reduce the falling and sinking of refrigerant after entering through the first interface 111, the distance between the bottom of the first interface 111 and the first separator 12 is the distance between 1-3 heat exchange tubes 3. The specific distance can be determined based on factors such as the diameter of the first manifold 11 and the size of the heat exchange tubes, which will not be elaborated upon in this article.

[0028] like Figure 2-3 As shown, in one specific embodiment, the flow guide 13 includes a first pipe 131 and at least one first plate 132. The length direction of the first pipe 131 extends at least partially along the length direction of the first manifold 11. The first pipe 131 is located within the first pipe section 112 and the second pipe section 113. The first plate 132 is located within the first pipe section 112 and is disposed on at least one side of the first pipe 131 along a first direction, which is the width direction of the heat exchange tube 3.

[0029] In this embodiment, the flow guide 13 includes a first pipe 131 and at least one first plate 132. By using the first plate 132 to block the refrigerant, the diameter of the first pipe 131 does not need to be increased to shield the refrigerant. The refrigerant can directly enter the heat exchange tube 3 near the first interface 111 simply by using the first plate 132. The connection between the first pipe 131 and the first plate 132 can be in various ways, such as an integral structure, the two can be connected by welding, or the side wall of the first pipe 131 can be provided with a groove, and the first plate 132 can be snapped into the groove, etc. This document does not specifically limit the method.

[0030] like Figure 2-3 As shown, in one specific embodiment, the number of first plates 132 is at least two, and the at least two first plates 132 are respectively located on both sides of the first pipe 131 along the first direction; if the minimum gap between the first plate 132 on one side and the inner wall of the first pipe segment 112 is defined as L3, and the minimum gap between the first plate 132 on the other side and the inner wall of the first pipe segment 112 is defined as L4, then: L3 > L4.

[0031] A 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 of the heat exchanger can improve its heat exchange efficiency to some extent. In this embodiment, the minimum gap between the first plate 132 on one side and the inner wall of the first pipe section 112 is larger than the gap between the first plate 132 on the other side and the inner wall of the first pipe section 112. This difference in gaps allows more refrigerant to enter the heat exchange tube 3 on the side with the larger gap as it flows along the length of the first pipe 131 and the first plate 132. The first plate 132 on the side with the smaller gap can impede the flow of refrigerant, reducing the amount of refrigerant passing through. Therefore, by designating the side with the larger gap as the windward side and the side with the smaller gap as the leeward side, more refrigerant can flow to the windward side, thereby improving the heat exchanger's heat exchange efficiency.

[0032] In addition, when the heat exchange tube 3 is a microchannel flat tube, the flat tube hole of the heat exchange tube 3 can be set as a non-uniform hole, that is, the flow cross-sectional area of ​​the flat tube hole of the heat exchange tube 3 is larger on the windward side (the side with larger gap) and smaller on the leeward side (the side with smaller gap). This allows the heat exchange tube 3 to accommodate more refrigerant flow on the windward side and reduce the refrigerant flow on the leeward side. When used together, it can achieve a better heat exchange effect.

[0033] like Figure 4 As shown, in one specific embodiment, if the direction from the second pipe segment 113 to the first pipe segment 112 is defined as the second direction, then along the second direction, the gap between the first plate 132 on at least one side and the inner wall of the first pipe segment 112 gradually increases.

[0034] During the process of refrigerant flowing and distributing along the length of the guide member 13, the refrigerant is distributed into the heat exchange tube 3 while flowing. The higher up (from the second pipe section 113 to the first pipe section 112), the smaller the refrigerant flow rate. Therefore, by gradually increasing the gap between the first plate 132 and the inner wall of the first pipe section 112 along the direction from the second pipe section 113 to the first pipe section 112, the amount of refrigerant entering the heat exchange tube 3 in the area near the first interface 111 can be reduced. At the same time, in the higher area, because the gap is larger, more refrigerant can enter more easily, thereby balancing the refrigerant flow rate at each position to a certain extent and making the distribution more uniform.

[0035] It should be noted that the process of gradually increasing gap between the first plate 132 and the inner wall of the first pipe section 112 can be linear or step-like, as long as the trend of gradually increasing gap is maintained along the second direction. Therefore, this paper does not make specific limitations on the shape of the change.

[0036] like Figure 5 As shown, in one specific embodiment, the flow guide 13 includes a second pipe 133, the length direction of the second pipe 133 extends at least partially along the length direction of the first manifold 11, and the second pipe 133 is located within the first pipe section 112 and the second pipe section 113; the width of the portion of the second pipe 133 located within the first pipe section 112 projected on the first projection plane is greater than the length of the heat exchange tube 3 projected on the first projection plane.

[0037] In this embodiment, the width of the portion of the second tube 133 located within the first tube segment 112 projected on the first projection plane is greater than the length of the heat exchange tube 3 projected on the first projection plane. That is, the diameter of the second tube 133 in the width direction of the heat exchange tube 3 is greater than the width of the heat exchange tube 3, thereby enabling the second tube 133 to shield the heat exchange tube 3 and reduce the refrigerant flow rate of the refrigerant that directly enters the nearby area of ​​the heat exchange tube 3 after entering from the first interface 111.

[0038] It should be noted that because the diameter of the second tube 133 in the width direction of the heat exchange tube 3 is larger than the width of the heat exchange tube 3, but in order to ensure the flow velocity of the refrigerant after entering the second tube 133, the flow cross-sectional area of ​​the second tube 133 cannot be increased too much. Therefore, the diameter of the second tube 133 in the length direction of the heat exchange tube 3 needs to be smaller than its diameter in the width direction. For example, the second tube 133 can be set as an elliptical tube or a rectangular tube to meet the flow cross-sectional area requirements. Generally speaking, although a rectangular tube can meet the flow cross-sectional area requirements, it will generate greater flow resistance than an elliptical tube. Therefore, when the second tube 133 is an elliptical tube, the pressure drop generated by the refrigerant is smaller, making it more suitable for distribution.

[0039] like Figure 6As shown, in one specific embodiment, the second tube 133 includes a first sidewall 134 and a second sidewall 135, the first sidewall 134 and the second sidewall 135 facing the heat exchange tube 3, the second sidewall 135 having a first arc-shaped segment 136, the first arc-shaped segment 136 being recessed within the first sidewall 134.

[0040] In this embodiment, the second tube 133 has a first arc-shaped segment 136 recessed within the first sidewall 134 on the side facing the heat exchange tube 3. This allows for a larger area between the second tube 133 and the heat exchange tube 3. During refrigerant flow, some refrigerant can collide with the first arc-shaped segment 136, thereby promoting the mixing of gaseous and liquid refrigerant and resulting in a more uniform gas-liquid mixture of refrigerant entering the heat exchange tube 3. Specifically, due to the presence of the first arc-shaped segment 136, when the two-phase refrigerant rushes towards the heat exchange tube 3 along the outer arc surface of the second tube 133, some refrigerant will collide with the wall of the first tube segment 112 or the first arc-shaped segment 136. A turbulent zone is formed between the inner wall of the first tube segment 112 and the first arc-shaped segment 136, allowing the refrigerant to mix before entering the heat exchange tube 3, thereby improving the heat exchange capacity of the evaporator.

[0041] like Figure 1 and Figure 3-4 As shown, in one specific embodiment, the sidewall of the flow guide 13 is provided with at least one first hole 15. The first hole 15 is located on the side of the flow guide 13 away from the first interface 111. The diameter of the first hole 15 is defined as d1, and the inner diameter of the flow guide 13 is defined as d2. Then: 1 / 3d2≤d1≤2 / 3d2.

[0042] During the refrigerant distribution process within the first pipe section 112, a significant amount of refrigerant tends to accumulate on the side furthest from the first interface 111. Therefore, placing the first hole 15 on the side of the guide member 13 furthest from the first interface 111 allows the accumulated refrigerant to enter the guide member 13 through the first hole 15, and then flow along the inner cavity of the guide member 13 into the second pipe section 113, improving refrigerant flow and thus enhancing distribution performance. Generally, the first hole 15 can be two sets of through holes penetrating the sidewall of the guide member 13. Furthermore, if the diameter of the first hole 15 is too small, liquid refrigerant will not easily enter the hole, resulting in insufficient liquid in the second pipe section 113 and preventing the heat exchanger from fully utilizing its heat exchange efficiency. Conversely, if the diameter of the first hole 15 is too large and the pressure difference on both sides of the guide 13 cannot be maintained well, the two-phase refrigerant will easily undergo gas-liquid separation in the first pipe section 112 due to the influence of gravity. Therefore, the diameter of the first hole 15 should be controlled within a suitable range, that is, 1 / 3d2≤d1≤2 / 3d2 in this embodiment.

[0043] like Figure 7As shown, in one specific embodiment, the first manifold 1 further includes a second partition 14, which is at least partially located within the first pipe section 112. The second partition 14 has a first channel that connects the cavities of the first pipe section 112 on both sides of the second partition 14.

[0044] Similar to the embodiments described above, the second separator 14 can also be a separator plate. However, unlike the first separator 12, the function of the second separator 14 is to reduce the flow cross-sectional area of ​​the refrigerant through the first channel, thereby spraying the refrigerant. This increases the refrigerant flow rate and also allows the sprayed gaseous refrigerant to mix with the liquid refrigerant to a certain extent, thus improving the distribution performance. There are various ways to connect the second separator 14 to the first pipe segment 112, such as integral molding or setting a slot in the wall of the first pipe segment 112, inserting the second separator 14 into the first pipe segment 112, and then welding it in place.

[0045] like Figure 7 As shown, in one specific embodiment, the first channel includes a gap hole 141, which is disposed between the outer wall of the guide member 13 and the second partition member 14, and penetrates the second partition member 14 along its thickness direction. The number of gap holes 141 can be one or more, and can be preset according to the diameter of the gap hole 141, the position of the second partition member 14, the diameter of the first pipe section 112, and the refrigerant charge, etc., which are not specifically limited herein.

[0046] like Figure 7 As shown, in one specific embodiment, the first manifold 1 further includes an interface pipe 16, which is connected to the first interface 111. The interface pipe 16 includes at least one second hole 161, which is located inside the first pipe segment 112, and the opening direction of the second hole 161 is oriented toward or inclined to the length direction of the first pipe segment 112.

[0047] As mentioned above, after the refrigerant enters through the first interface 111, most of it enters the heat exchange tube 3 in the vicinity of the first interface 111, resulting in uneven distribution. In this embodiment, an interface pipe 16 with an opening facing or inclined to the length of the first pipe segment 112 is added. This allows the refrigerant to enter the first manifold 11 through the second hole 161 of the interface pipe 16, and the spray direction of the refrigerant is approximately parallel to or at a certain angle to the first manifold 11. Since the gaseous part is faster and lighter than the liquid part, this allows the gaseous refrigerant to carry the liquid refrigerant upwards, instead of directly entering the heat exchange tube 3 in the vicinity of the first interface 111. This reduces the amount of refrigerant in the heat exchange tube 3 in the vicinity of the first interface 111, making the refrigerant distribution in the first manifold 11 more even. At the same time, the refrigerant rises more effectively, further reducing the situation where the refrigerant cannot rise and there is little or no refrigerant at the top position (the side away from the first interface 111).

[0048] 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 heat exchanger, characterized in that, The device includes a first manifold section (1), a second manifold section (2), and a plurality of heat exchange tubes (3). The first manifold section (1) includes a first manifold (11) having a first interface (111). The second manifold section (2) includes a second manifold (21) spaced apart from the first manifold (11). The heat exchange tubes (3) connect the first manifold (11) and the second manifold (21). The first manifold section (1) also includes a flow guide (13), which is at least partially located within the cavity of the first manifold (11) and between the first interface (111) and the opening of the heat exchange tube (3). A surface perpendicular to the length direction of the heat exchange tube (3) is defined as a first projection surface. On the first projection surface, the projection of the flow guide (13) can cover the projection of the first interface (111) and / or cover at least part of the projection of the opening of the heat exchange tube (3).

2. The heat exchanger according to claim 1, characterized in that, Let L1 be the width of the flow guide (13) projected onto the first projection plane, and L2 be the length of the heat exchange tube (3) projected onto the first projection plane. Then: L1≥L2.

3. The heat exchanger according to claim 1 or 2, characterized in that, The first manifold (1) further includes a first partition (12), which is at least partially located within the cavity of the first manifold (11). The first manifold (11) includes a first pipe section (112) and a second pipe section (113), which are located on opposite sides of the first partition (12). The guide (13) connects the first pipe section (112) and the second pipe section (113). The first interface (111) is located in the first pipe section (112) and is close to the first partition (12).

4. The heat exchanger according to claim 3, characterized in that, The flow guide (13) includes a first pipe (131) and at least one first plate (132). The first pipe (131) is located within the first pipe section (112) and the second pipe section (113), and the length direction of the first pipe (131) extends at least partially along the length direction of the first manifold (11). The first plate (132) is located within the first pipe section (112), and the first plate (132) is disposed on at least one side of the first pipe (131) along a first direction, the first direction being the width direction of the heat exchange tube (3).

5. The heat exchanger according to claim 4, characterized in that, The number of the first plate (132) is at least two, and the at least two first plates (132) are located on both sides of the first pipe (131) along the first direction; the minimum gap between the first plate (132) on one side and the inner wall of the first pipe segment (112) is defined as L3, and the minimum gap between the first plate (132) on the other side and the inner wall of the first pipe segment (112) is defined as L4, then: L3 > L4.

6. The heat exchanger according to claim 4 or 5, characterized in that, The direction from the second pipe segment (113) to the first pipe segment (112) is defined as the second direction. Along the second direction, the gap between the first plate (132) on at least one side and the inner wall of the first pipe segment (112) gradually increases.

7. The heat exchanger according to claim 3, characterized in that, The flow guide (13) includes a second pipe (133), which is located within the first pipe section (112) and the second pipe section (113), and the length direction of the second pipe (133) extends at least partially along the length direction of the first manifold (11); the width of the portion of the second pipe (133) located within the first pipe section (112) projected onto the first projection plane is greater than the length of the heat exchange tube (3) projected onto the first projection plane.

8. The heat exchanger according to claim 7, characterized in that, The second tube (133) includes a first sidewall (134) and a second sidewall (135), the first sidewall (134) and the second sidewall (135) facing the heat exchange tube (3), the second sidewall (135) having a first arc-shaped segment (136), the first arc-shaped segment (136) being recessed within the first sidewall (134).

9. The heat exchanger according to any one of claims 1-2, 4-5, or 7-8, characterized in that, The sidewall of the flow guide (13) is provided with at least one first hole (15). The first hole (15) is located on the side of the flow guide (13) away from the first interface (111). The diameter of the first hole (15) is defined as d1, and the inner diameter of the flow guide (13) is defined as d2. Then: 1 / 3d2≤d1≤2 / 3d2.

10. The heat exchanger according to any one of claims 4-5 or 7-8, characterized in that, The first manifold (1) further includes a second partition (14), which is at least partially located within the first pipe section (112). The second partition (14) has a first channel that connects the lumens of the first pipe section (112) on both sides of the second partition (14).

11. The heat exchanger according to claim 10, characterized in that, The first channel includes a gap hole (141), which is disposed between the outer wall of the guide (13) and the second partition (14), and the gap hole (141) penetrates the second partition (14) along the thickness direction of the second partition (14).

12. The heat exchanger according to any one of claims 4-5 or 7-8, characterized in that, The first manifold (1) further includes an interface pipe (16), which is connected to the first interface (111). The interface pipe (16) includes at least one second hole (161), which is located inside the first pipe segment (112), and the opening direction of the second hole (161) is oriented toward or inclined to the length direction of the first pipe segment (112).

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