Heat exchanger and heat exchange device

Abstract

Provided in the present disclosure are a heat exchanger and a heat exchange device. The heat exchanger comprises a first flow collection tube, a second flow collection tube, a plurality of heat exchange tubes, first plates and a first connecting port, wherein the first flow collection tube comprises a first tube section and a second tube section, which are separated from each other, the first tube section and the second tube section being arranged in the lengthwise direction of the first flow collection tube; the second flow collection tube is spaced apart from the first flow collection tube; the plurality of heat exchange tubes bring the first flow collection tube into communication with the second flow collection tube; the first plates are at least partially located in the second flow collection tube, each first plate comprises a first channel, which brings the parts of the second flow collection tube on two sides of the first plate in the direction of thickness thereof into communication with each other, at least two first plates are provided, and the at least two first plates are spaced apart in the lengthwise direction of the second flow collection tube; the flow cross-sectional area of any one of at least two first channels is larger than that of the other first channel in a first direction, the first direction being a direction from the first tube section to the second tube section; and the first connecting port is located in the first tube section, and is in communication with the first tube section. By means of the heat exchanger, a refrigerant ejection effect can be improved.

Description

Heat exchanger and heat exchange device

[0001] CROSS-REFERENCE TO RELATED APPLICATIONS

[0002] This application claims priority and benefits of Chinese patent application number 202420287448.5 and filing date February 7, 2024. The entire contents of the above Chinese patent application are hereby incorporated by reference into this application. Technical Field

[0003] The present application relates to the field of heat exchange technology, and in particular to a heat exchanger and a heat exchange device. Background Art

[0004] In related technologies, most dual-pass heat exchangers distribute refrigerant by installing several identical perforated baffles within a manifold. These baffles create a spray effect on the refrigerant passing through it, improving the uniformity of gas-liquid mixing. However, this distribution method reduces the refrigerant flow rate toward the top of the manifold, resulting in a poorer spray effect for the baffles closer to the top, affecting refrigerant distribution. Summary of the Invention

[0005] A first aspect of an embodiment of the present application provides a heat exchanger that can improve the injection effect of a refrigerant.

[0006] A heat exchanger provided in a first aspect of the present application includes: a first header, the first header including a first pipe segment and a second pipe segment, the first pipe segment and the second pipe segment being arranged along a length direction of the first header;

[0007] a second header, the second header being spaced apart from the first header;

[0008] a plurality of heat exchange tubes, wherein the plurality of heat exchange tubes are connected to the first header and the second header;

[0009] a first plate, the first plate being at least partially located within the second header, the first plate including first channels communicating with the second header on both sides of the first plate along a thickness direction, the first plates being at least two in number, the at least two first plates being spaced apart along a length direction of the second header; a flow cross-sectional area of ​​one of the at least two first channels being greater than a flow cross-sectional area of ​​the other first channel along a first direction, the first direction being a direction from the first pipe segment to the second pipe segment;

[0010] The beneficial effects of the embodiments of the present application are:

[0011] When the heat exchanger of the embodiment of the present application works as an evaporator, the refrigerant enters the heat exchanger from the first pipe section, and then enters the second header through the connected heat exchange pipes. When the refrigerant passes through the second header, the first plate and the first channel in the second header can distribute the refrigerant. Since the flow cross-sectional area of ​​any first channel is larger than the flow cross-sectional area of ​​another first channel along the direction from the first pipe section to the second pipe section, as the refrigerant flow rate decreases, the first channel with a smaller flow cross-sectional area can have a better mixing and injection effect on the refrigerant.

[0012] The second aspect of the embodiment of the present application provides a heat exchange device, which includes at least two heat exchange parts, wherein the heat exchange parts are the heat exchangers in the embodiment of the first aspect, and the two adjacent heat exchangers are arranged along the length direction of the first header, and one heat exchanger is fixedly connected to the other adjacent heat exchanger.

[0013] The beneficial effects of the embodiments of the present application are:

[0014] The heat exchange device of the embodiment of the present application includes at least two heat exchangers in the embodiment of the first aspect. Since the heat exchanger in the embodiment of the first aspect has a better refrigerant injection effect when working as an evaporator, the heat exchange device also has better distribution performance when working as an evaporator.

[0015] It should be understood that the foregoing general description and the following detailed description are merely illustrative and are not restrictive of the present application. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] FIG1 is a schematic structural diagram of a heat exchanger provided in the present application in a specific embodiment;

[0017] FIG2 is a schematic structural diagram of a heat exchanger provided in the present application in a second specific embodiment;

[0018] FIG3 is a schematic structural diagram of a heat exchanger provided in the present application in a third specific embodiment;

[0019] FIG4 is a schematic structural diagram of the heat exchanger in direction A in FIG3 ;

[0020] FIG5 is a schematic structural diagram of a heat exchanger provided in the present application in a fourth specific embodiment;

[0021] FIG6 is a schematic structural diagram of a heat exchanger provided in the present application in a fifth specific embodiment;

[0022] FIG7 is a schematic structural diagram of a heat exchange device provided in the present application in a specific embodiment.

[0023] Figure markings: first header 1, first pipe section 11, second pipe section 12, second header 2, first end 21, heat exchange tube 3, first section 31, second section 32, bent section 33, first plate 4, first channel 41, first hole 411, first gap 412, first sub-plate 42, first surface 5, first interface 6, second interface 7, fin 8, first partition 9.

[0024] The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate embodiments consistent with the present application and, together with the description, serve to explain the principles of the present application. DETAILED DESCRIPTION

[0025] In order to better understand the technical solution of the present application, the embodiments of the present application are described in detail below with reference to the accompanying drawings.

[0026] It should be clear that the embodiments described are only part of the embodiments of this application, not all of the embodiments. Based on the embodiments in this application, all other embodiments obtained by ordinary technicians in this field without making creative work are within the scope of protection of this application.

[0027] The terms used in the embodiments of the present application are for the purpose of describing specific embodiments only and are not intended to limit the present application. The singular forms "a", "an", "the" and "the" used in the embodiments of the present application and the appended claims are also intended to include plural forms unless the context clearly indicates otherwise.

[0028] It should be understood that the term "and / or" as used herein is merely a description of the relationship between associated objects, indicating that three possible relationships exist. For example, "A and / or B" can represent: A exists alone, A and B exist simultaneously, or B exists alone. Furthermore, the character " / " in this document generally indicates that the associated objects are in an "or" relationship.

[0029] It should be noted that the directional words such as "upper", "lower", "left", and "right" described in the embodiments of the present application are described based on the angles shown in the accompanying drawings and should not be understood as limiting the embodiments of the present application. In addition, in the context, it should be understood that when it is mentioned that an element is connected to another element "on" or "under", it can not only be directly connected to the other element "on" or "under", but also be indirectly connected to the other element "on" or "under" through an intermediate element.

[0030] The heat exchanger in the embodiments of the present application is described in detail below with reference to the accompanying drawings. In the absence of conflict, the features of the following embodiments and implementations may complement or be combined with each other.

[0031] As shown in Figures 1-6, a first aspect of the present invention provides a heat exchanger capable of improving refrigerant distribution uniformity. The heat exchanger primarily comprises a first header 1, a second header 2, a plurality of heat exchange tubes 3, a first plate 4, and a first interface 6. The first header 1 comprises a first tube segment 11 and a second tube segment 12, which are arranged along the length of the first header 1; the second header 2 is spaced apart from the first header 1; the plurality of heat exchange tubes 3 connect the first header 1 and the second header 2; a first plate 4 is at least partially located within the second header 2, and comprises first channels 41, which connect the second headers 2 on both sides of the first plate 4 along the thickness direction. There are at least two first plates 4, which are spaced apart along the length of the second header 2; and one of the at least two first channels 41 has a larger cross-sectional area than the other first channel 41 along a first direction, where the first direction is from the first tube segment 11 to the second tube segment 12.

[0032] In this embodiment, the first and second headers 1 and 2 of the heat exchanger are hollow circular tubes. However, in other embodiments, to improve the pressure resistance of the first and second headers 1 and 2, the first and second headers 1 and 2 can also be configured as rectangular tubes with smaller cross-sectional areas or other shapes. The first and second headers 1 and 2 can be integrally formed or assembled from multiple parts. Furthermore, the first and second headers 1 and 2 can be parallel to each other or arranged at a certain angle. The specific configuration can be adjusted or preset based on actual usage requirements and installation environment, and is not specifically limited herein.

[0033] It should be noted that the first pipe section 11 and the second pipe section 12 are isolated from each other. Specifically, it means that the first pipe section 11 and the second pipe section 12 are not connected to each other under the premise that there are no other components to connect the two. When the heat exchanger is working, the refrigerant in the first pipe section 11 cannot directly enter the second pipe section 12. The first pipe section 11 and the second pipe section 12 can be isolated by a partition provided in the first manifold 1, or by welding two independent pipes. However, generally speaking, the isolation method using a partition has a lower manufacturing cost.

[0034] Furthermore, the first plate 4 being at least partially located within the second manifold 2 means that the first plate 4 can be completely located within the second manifold 2, for example, by welding the entire outer wall of the first plate 4 to the inner wall of the second manifold 2, thereby ensuring that the first plate 4 is entirely located within the lumen of the second manifold 2. Of course, the first plate 4 can also be only partially located within the second manifold 2. For example, when the first plate 4 is installed in the second manifold 2 by plugging, the area of ​​the first plate 4 needs to be slightly larger than the cross-section of the second manifold 2 to ensure stable fit between the first plate 4 and the second manifold 2, that is, the first plate 4 is partially located within the second manifold 2. The first manifold 1 further includes a first interface 6, which is located within the first pipe section 11 and communicates with the first pipe section 11.

[0035] The heat exchange tubes 3 in this embodiment can be microchannel flat tubes or single-channel or multi-channel circular tubes. Multiple heat exchange tubes 3 are arranged substantially parallel to one another. One of the first tube segment 11 and the second tube segment 12 serves as the refrigerant inlet and outlet, respectively. When the heat exchanger operates as an evaporator, the first tube segment 11 serves as the refrigerant inlet and the second tube segment 12 serves as the refrigerant outlet. However, when the heat exchanger operates as a condenser, the refrigerant flow direction is reversed, with the second tube segment 12 serving as the refrigerant inlet and the first tube segment 11 serving as the refrigerant outlet.

[0036] When the heat exchanger of the embodiment of the present application works as an evaporator, the refrigerant enters the heat exchanger from the first interface 6 of the first pipe segment 11, and then enters the second header 2 through the connected heat exchange tube 3. When the refrigerant passes through the second header 2, the first plate 4 and the first channel 41 in the second header 2 can distribute the refrigerant. Since the flow cross-sectional area of ​​any first channel 41 is larger than the flow cross-sectional area of ​​another first channel 41 along the direction from the first pipe segment 11 to the second pipe segment 12, as the refrigerant flow rate decreases, the first channel 41 with a smaller flow cross-sectional area can have a better mixing and injection effect on the refrigerant, thereby improving the distribution performance.

[0037] Taking the example of two first plates 4, refrigerant enters the heat exchanger through the first pipe segment 11 and then enters the second header 2 through the connected heat exchange tubes 3. All of the refrigerant is then distributed through the first first plate 4. Some of the refrigerant then flows into the heat exchange tubes 3 between the first and second first plates 4, while the remaining refrigerant is distributed through the second first plate 4. During this process, because the cross-sectional area of ​​the first channels 41 of the second first plate 4 is smaller than that of the first channels 41 of the first first plate 4, the reduced refrigerant can be better distributed, thereby improving distribution performance.

[0038] It should be noted that the heat exchanger in the embodiment of the present application divides the first pipe 1 into a first pipe section 11 and a second pipe section 12, that is, the refrigerant passes through at least two processes when passing through the heat exchanger. When the heat exchanger serves as an evaporator, the refrigerant enters from the first pipe section 11. Setting the length of the first pipe section 11 to be shorter can reduce the gas-liquid separation of the refrigerant in the first pipe section 11. The number of heat exchange tubes 3 connected to the first pipe section 11 is also correspondingly smaller. The distribution requirements of the refrigerant are lower when passing through this process, and the refrigerant can be distributed after entering the second pipe section 2. Therefore, the dual-process layout can reduce the distribution design requirements. At the same time, when the heat exchanger works as a condenser, the heat exchange tube 3 with the first pipe section 11 can also be used as the subcooling section of the heat exchanger to improve the heat exchange effect.

[0039] In a specific embodiment, if the flow cross-sectional area of ​​the second header 2 is defined as A1 and the flow cross-sectional area of ​​any first channel 41 is defined as A2, then A1 and A2 satisfy: 7 / 20≤A2 / A1≤1 / 2.

[0040] The first channel 41 can achieve a mixing and injection effect on the refrigerant, thereby distributing the gas-liquid two-phase refrigerant. It is understandable that the effect of the first channel 41 mainly depends on the size of its flow cross-sectional area. For example, when the flow cross-sectional area of ​​the first channel 41 is too large, the obstruction to the passage of the refrigerant is small, resulting in poor mixing and injection effects. However, when the flow cross-sectional area of ​​the first channel 41 is too small, the obstruction to the passage of the refrigerant is large, and less refrigerant passes through the first channel 41 per unit time, resulting in the refrigerant not being able to circulate in time and accumulating, thereby affecting the overall distribution effect. Therefore, when the flow cross-sectional area A2 of any first channel 41 and the flow cross-sectional area A1 of the second header 2 satisfy 7 / 20≤A2 / A1≤1 / 2, the first channel 41 can achieve a good mixing and injection effect, thereby further improving the uniformity of distribution.

[0041] Furthermore, when the flow cross-sectional area A2 of the first channel 41 accounts for 38% to 46% of the flow cross-sectional area A1 of the second header 2, the distribution effect is better, so that the flow rate of the refrigerant entering different heat exchange tubes 3 is more uniform. The principle is similar to that described above, so it will not be described in detail in this article.

[0042] As shown in Figure 2, in a specific embodiment, if a surface perpendicular to the first direction and passing through the second manifold 2 is defined as the first surface 5, on the first surface 5, the projection of one first channel 41 is at least partially offset from the projection of another adjacent first channel 41, that is, the projections of the two adjacent first channels 41 do not completely overlap. It should be noted that "offset" and "non-overlap" should be understood in a broad sense, that is, the projections of the two first channels 41 are not completely opposite. In addition, at least partial offset means that the two adjacent first channels 41 may not overlap at all, or may only partially overlap. The two adjacent first channels 41 arranged in an offset manner can play an alternating blocking role on the refrigerant, increase the time that the refrigerant stays between the two adjacent first channels 41, thereby better achieving the effect of distribution while flowing and improving the uniformity of distribution.

[0043] As shown in Figure 2, in a specific embodiment, the first channel 41 includes a first hole 411, the first hole 411 is located in the first plate 4, the number of the first hole 411 is at least one, and / or the first channel 41 includes a first gap 412, the first gap 412 is located between the first plate 4 and the tube wall of the second manifold 2.

[0044] In this embodiment, the first channel 41 distributes the refrigerant in the form of a first hole 411 and / or a first gap 412. The shapes of the first hole 411 and the first gap 412 can be circular or rectangular, or irregular, such as a combination of multiple shapes. Furthermore, the number of the first hole 411 and the first gap 412 can be one or more, and this is not specifically limited herein, as long as the first hole 411 and the first gap 412 can connect to the tube cavity of the second header 2 on both sides of the first plate 4. Furthermore, the first hole 411 and the first gap 412 can exist separately or simultaneously on the same first plate 4. The first hole 411 and / or the first gap 412 can cause the refrigerant to be ejected, thereby improving the overall distribution effect.

[0045] In addition, when the heat exchanger is in operation, due to the gravitational relationship between the gas-liquid two-phase refrigerant and the barrier effect of the first plate 4, the refrigerant flowing through each first plate 4 will not only have a reduced flow rate but also a pressure loss. Its flow velocity will become lower and lower along the flow direction of the refrigerant. Therefore, the number and position of the first holes 411 and the first gaps 412 can be adjusted according to actual distribution requirements. For example, while reducing the flow cross-sectional area of ​​the first holes 411 and / or the first gaps 412, the interval between two adjacent first plates 4 can be made closer to overcome the above-mentioned problem.

[0046] As shown in Figure 3-4, in a specific embodiment, the heat exchange tube 3 includes a first section 31, a second section 32 and a bent section 33, one end of the bent section 33 is connected to the first section 31, and the other end of the bent section 33 is connected to the second section 32, and the length direction of the first section 31 is parallel to the length direction of the second section 32.

[0047] In heat pump heat exchangers and heat exchangers of some air-conditioning systems, the heat exchange solution of a single row of heat exchange tubes 3 can no longer meet their heat exchange requirements well. Therefore, bending the heat exchange tubes 3 to make the original single row heat exchanger into a double row can better meet the heat exchange requirements of the heat exchanger.

[0048] As shown in Figure 5, in a specific embodiment, the heat exchanger also includes a second interface 7, which is located in the second pipe section 12 and is connected to the second pipe section 12; the heat exchanger has a working state, and in the working state, the length direction of the second header 2 is parallel to the direction of gravity, and the side of the second section 32 away from the first section 31 is the windward side.

[0049] In this embodiment, the heat exchanger is transformed into a double-row heat exchanger by bending. When the heat exchanger is working, the refrigerant realizes a flow path design of partial downstream and partial countercurrent in the entire heat exchanger. After experimental verification, it is confirmed that the heat exchanger performance of the double-row heat exchanger with a flow path design of partial downstream and partial countercurrent of the refrigerant is better than that of a full downstream design.

[0050] As shown in Figure 5, in one specific embodiment, the end of the first section 31 away from the curved section 33 is connected to the second header 2, and the end of the second section 32 away from the curved section 33 is connected to the first header 1. The length of the first section 31 is defined as L1, and the length of the second section 32 is defined as L2. L1 and L2 satisfy the following relationship: 2 / 3 ≤ L1 / L2 < 1. The different lengths of the first and second sections 31 and 32 allow the outlet section of the heat exchanger to face the wind from one side when used as an evaporator, which helps stabilize superheat. When used as a condenser, higher wind speeds during single-row heat exchange also stabilize subcooling.

[0051] As shown in FIG6 , in a specific embodiment, the second header 2 has a first end 21 in the length direction. Along the first direction, the first first plate 4 is defined as a first sub-plate 42, and the first end 21 is close to the first sub-plate 42. If the number of heat exchange tubes 3 between the first sub-plate 42 and the first end 21 is defined as N1, and the number of heat exchange tubes 3 connected to the first pipe section 11 is N2, then N1 and N2 satisfy: 1≤N2-N1≤3.

[0052] As shown in Figure 6, when the heat exchanger is positioned vertically, the first end 21 is the bottom end of the second header 2, and the first sub-plate 42 is the first first plate 4 near the bottom of the second header 2. The number N2 of heat exchange tubes 3 connecting the first pipe segment 11 and the number N1 of heat exchange tubes 3 between the first sub-plate 42 and the first end 21 satisfy 1 ≤ N2 - N1 ≤ 3. When the heat exchanger operates as an evaporator, after the refrigerant enters the first pipe segment 11, a portion of the refrigerant can directly enter the second header 2 above the first sub-plate 42 through the heat exchange tubes 3 connecting the upper portion of the first sub-plate 42 and the first pipe segment 11, thereby replenishing the refrigerant above the first sub-plate 42. As mentioned above, after passing through the obstruction of the first plate 4, the refrigerant not only has a reduced flow rate but also experiences pressure loss. The flow rate and flow rate decrease along the refrigerant's flow direction. Therefore, the connection method in this embodiment allows the refrigerant above the first sub-plate 42 to be replenished, thereby improving the uniformity of the refrigerant distribution above the first plate 4.

[0053] In addition, when the heat exchanger works as a condenser, a portion of the refrigerant flowing in the reverse direction can flow directly into the first pipe section 11 through the upper part of the first sub-plate 42 without passing through the first sub-plate 42, thereby reducing the barrier effect of the first sub-plate 42 on the refrigerant, reducing the flow resistance encountered by the refrigerant when flowing through this area, and improving the heat exchange efficiency of the heat exchanger when working as a condenser.

[0054] As shown in Figure 7, a second aspect of the present application provides a heat exchange device comprising at least two heat exchange sections, each of which is the heat exchanger described in the first aspect. Two adjacent heat exchangers are arranged along the length of the first header 1, with one heat exchanger fixedly connected to the other adjacent heat exchanger. The heat exchange device of the present application includes at least two heat exchangers described in the first aspect. Because the heat exchangers described in the first aspect distribute refrigerant more evenly when operating as evaporators, the heat exchange device also exhibits improved distribution performance when operating as an evaporator.

[0055] In a specific embodiment, the heat exchange device also includes fins 8, which are arranged at intervals on at least part of the heat exchange tubes 3 along the length direction of the first header 1. The fins 8 can be horizontally inserted fins or corrugated fins, and can be specifically preset according to the size of the heat exchanger and the use environment.

[0056] As shown in FIG7 , in another embodiment, the heat exchange device includes a first partition 9 and at least two heat exchange sections, each of which includes a first header 1, a second header 2, a plurality of heat exchange tubes 3, and a first plate 4. The first partition 9 is located between the first headers 1 of two adjacent heat exchangers and between the second headers 2 of two adjacent heat exchangers. The first header 1 includes a first tube segment 11 and a second tube segment 12, which are arranged along the length of the first header 1. The second header 2 is spaced apart from the first header 1. The plurality of heat exchange tubes 3 connect the first header 1 and the second header 2. The first plate 4 is at least partially located within the second header 2 and includes a first channel 41, which connects the second headers 2 on both sides of the first plate 4 along the thickness direction. There are at least two first plates 4, and the at least two first plates 4 are spaced apart along the length of the second header 2. Of the at least two first channels 41, the flow cross-sectional area of ​​one first channel 41 is larger than the flow cross-sectional area of ​​the other first channel 41 along a first direction, where the first direction is from the first tube segment 11 to the second tube segment 12.

[0057] In this embodiment, when multiple heat exchange parts are combined into a heat exchange device, if the inlet and outlet pipes use the same manifold (first manifold 1), the inlet cavity of the upper heat exchange part between two adjacent heat exchange parts will be adjacent to the outlet cavity of the next heat exchange part. At this time, the inlet cavity body will be adjacent to the outlet cavity body, forming a thermal bridge, affecting the state of the inlet and outlet refrigerants and reducing the heat exchange effect. Therefore, the thermal bridge effect is weakened by setting a first partition 9 to increase the thermal insulation effect. The first partition 9 can be a hollow partition or a partition material with low thermal conductivity.

[0058] The above are only preferred embodiments of the present application and are not intended to limit the present application. For those skilled in the art, various modifications and variations of the present application are possible. Any modifications, equivalent substitutions, improvements, etc. made within the spirit and principles of the present application shall be included in the scope of protection of the present application.

Claims

1. A heat exchanger comprising: A first header (1), the first header (1) comprising a first pipe section (11) and a second pipe section (12), the first pipe section (11) and the second pipe section (12) being arranged along a length direction of the first header (1); a second header (2), the second header (2) being spaced apart from the first header (1); a plurality of heat exchange tubes (3), wherein the plurality of heat exchange tubes (3) are connected to the first header (1) and the second header (2); A first plate (4), wherein the first plate (4) is at least partially located in the second header (2), the first plate (4) comprises a first channel (41), the first channel (41) is connected to the second header (2) on both sides of the first plate (4) along the thickness direction, the number of the first plates (4) is at least two, and at least two first plates (4) are arranged at intervals along the length direction of the second header (2); of the at least two first channels (41), the flow cross-sectional area of one first channel (41) is greater than the flow cross-sectional area of the other first channel (41) along a first direction, wherein the first direction is the direction from the first pipe section (11) to the second pipe section (12).

2. The heat exchanger according to claim 1, wherein The flow cross-sectional area of the second header (2) is defined as A1, and the flow cross-sectional area of any one of the first channels (41) is defined as A2, then A1 and A2 satisfy: 7 / 20≤A2 / A1≤1 / 2.

3. The heat exchanger according to claim 2, wherein: A surface perpendicular to the first direction and passing through the second header (2) is defined as a first surface (5), on which a projection of one first channel (41) is at least partially offset from a projection of another adjacent first channel (41).

4. The heat exchanger according to claim 2, wherein: The first channel (41) includes a first hole (411), the first hole (411) is located in the first plate (4), the number of the first hole (411) is at least one, and / or the first channel (41) includes a first gap (412), the first gap (412) is located between the first plate (4) and the tube wall of the second header (2).

5. The heat exchanger according to any one of claims 1 to 4, wherein: The first manifold (1) further comprises a first interface (6), the first interface (6) being located in the first pipe section (11), and the first interface (6) being in communication with the first pipe section (11); The heat exchange tube (3) comprises a first section (31), a second section (32) and a bent section (33); one end of the bent section (33) is connected to the first section (31), and the other end of the bent section (33) is connected to the second section (32); the length direction of the first section (31) is parallel to the length direction of the second section (32).

6. The heat exchanger according to claim 5, wherein: One end of the first section (31) away from the curved section (33) is connected to the second header (2), and one end of the second section (32) away from the curved section (33) is connected to the first header (1). The length of the first section (31) is defined as L1, and the length of the second section (32) is defined as L2. Then L1 and L2 satisfy: 2 / 3≤L1 / L2<1.

7. The heat exchanger according to claim 6, wherein: The heat exchanger further comprises a second interface (7), the second interface (7) being located in the second pipe section (12), and the second interface (7) being in communication with the second pipe section (12); The heat exchanger has a working state. In the working state, the length direction of the second header (2) is parallel to the direction of gravity, and the side of the second section (32) facing away from the first section (31) is the windward side.

8. The heat exchanger according to any one of claims 1 to 4 or 6 to 7, wherein: The second header (2) has a first end (21) in the length direction, and along the first direction, the first first plate (4) is defined as a first sub-plate (42), and the first end (21) is close to the first sub-plate (42); The number of the heat exchange tubes (3) between the first sub-plate (42) and the first end (21) is defined as N1, and the number of the heat exchange tubes (3) connected to the first pipe section (11) is defined as N2, then N1 and N2 satisfy: 1≤N2-N1≤3.

9. A heat exchange device comprising at least two heat exchange parts, wherein: The heat exchange part is a heat exchanger according to any one of claims 1 to 8, two adjacent heat exchangers are arranged along the length direction of the first header (1), and one heat exchanger is fixedly connected to the other adjacent heat exchanger.

10. The heat exchange device according to claim 9, further comprising: Fins (8), the fins (8) are arranged at intervals on at least a portion of the heat exchange tubes (3) along the length direction of the first header (1).

11. A heat exchange device, comprising a first partition (9) and at least two heat exchange parts, wherein the heat exchange parts comprise a first header (1), a second header (2), a plurality of heat exchange tubes (3), and a first plate (4), wherein the first partition (9) is located between the first headers (1) of two adjacent heat exchangers and between the second headers (2) of two adjacent heat exchangers; The first header (1) comprises a first pipe section (11) and a second pipe section (12), the first pipe section (11) and the second pipe section (12) being arranged along the length direction of the first header (1); the second header (2) is arranged at intervals from the first header (1); a plurality of heat exchange tubes (3) are connected to the first header (1) and the second header (2); The first plate (4) is at least partially located in the second header (2), the first plate (4) includes a first channel (41), the first channel (41) is connected to the second header (2) on both sides of the first plate (4) along the thickness direction, the number of the first plates (4) is at least two, and at least two first plates (4) are arranged at intervals along the length direction of the second header (2); among the at least two first channels (41), the flow cross-sectional area of one first channel (41) is greater than the flow cross-sectional area of the other first channel (41) along a first direction, and the first direction is the direction from the first pipe section (11) to the second pipe section (12).

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