Heat exchanger and heat exchange device

Abstract

The utility model relates to a heat exchanger and a heat exchange device, the heat exchanger comprises a first collecting pipe, a second collecting pipe, a plurality of heat exchange pipes, a first plate and a first connector, the first collecting pipe comprises a first pipe section and a second pipe section which are separated from each other, and the first pipe section and the second pipe section are arranged in the length direction of the first collecting pipe; the second collecting pipes and the first collecting pipes are arranged at intervals; the plurality of heat exchange pipes are communicated with the first collecting pipe and the second collecting pipe; the first plates are at least partially located in the second collecting pipes, each first plate comprises a first channel, the first channels communicate with the second collecting pipes on the two sides of the first plates in the thickness direction, the number of the first plates is at least two, and the at least two first plates are arranged in the length direction of the second collecting pipes at intervals; in the at least two first channels, the circulation sectional area of any first channel is larger than the circulation sectional area of the other first channel in the first direction, and the first direction is the direction from the first pipe section to the second pipe section; the first connector is located on the first pipe section and communicates with the first pipe section. The heat exchanger can improve the uniformity of refrigerant distribution.

Description

Technical Field

[0001] 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

[0002] In the related art, most dual-pass heat exchangers distribute the refrigerant by setting a number of identical perforated baffles in one of the headers. The perforated baffles can produce a spray effect on the refrigerant passing through during the distribution process, thereby improving the uniformity of gas-liquid mixing. However, in the process of refrigerant distribution, this distribution method has the problem that the perforated baffles closer to the top of the header produce a poorer spray effect and distribution effect on the refrigerant, because the refrigerant flow rate decreases as it moves toward the top of the header, resulting in uneven refrigerant distribution. Utility Model Content

[0003] A first aspect of the present application provides a heat exchanger capable of improving the uniformity of refrigerant distribution.

[0004] 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 separated from each other, the first pipe segment and the second pipe segment being arranged along a length direction of the first header;

[0005] a second header, the second header being spaced apart from the first header;

[0006] A plurality of heat exchange tubes, wherein the plurality of heat exchange tubes are connected to the first header and the second header;

[0007] a first plate, the first plate being at least partially located in the second header, the first plate comprising a first channel, the first channel being connected to the second headers on both sides of the first plate along the thickness direction, the number of the first plates being at least two, and at least two first plates being arranged at intervals along the length direction of the second header; a flow cross-sectional area of ​​any of the at least two first channels being greater than a flow cross-sectional area of ​​another first channel along a first direction, the first direction being a direction from the first pipe segment to the second pipe segment;

[0008] A first interface, wherein the first interface is located in the first pipe section, and the first interface is communicated with the first pipe section.

[0009] The beneficial effects of this application are:

[0010] When the heat exchanger of the present application works as an evaporator, the refrigerant enters the heat exchanger from the first interface of the first pipe segment, and then enters the second header through the connected heat exchange tubes. 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 along the direction from the first pipe segment to the second pipe segment is larger than the flow cross-sectional area of ​​another first channel, 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, thereby improving the uniformity of refrigerant distribution.

[0011] A second aspect 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 two adjacent heat exchangers are arranged along the length direction of the first header, and one heat exchanger is fixedly connected to another adjacent heat exchanger.

[0012] The beneficial effects of this application are:

[0013] The heat exchange device of the present application includes at least two heat exchangers in the first aspect embodiment. Since the heat exchanger in the first aspect embodiment distributes the refrigerant more evenly when working as an evaporator, the heat exchange device also has better distribution performance when working as an evaporator.

[0014] It should be understood that the foregoing general description and the following detailed description are exemplary only and are not restrictive of the present application. BRIEF DESCRIPTION OF THE DRAWINGS

[0015] Figure 1 A schematic diagram of the structure of a heat exchanger provided in the present application in a specific embodiment;

[0016] Figure 2 A schematic structural diagram of the heat exchanger provided in the present application in a second specific embodiment;

[0017] Figure 3 A schematic diagram of the structure of the heat exchanger provided in the present application in a third specific embodiment;

[0018] Figure 4 for Figure 3 A-direction structural diagram of the middle heat exchanger;

[0019] Figure 5 A schematic diagram of the structure of the heat exchanger provided in the present application in a fourth specific embodiment;

[0020] Figure 6 A schematic structural diagram of a heat exchanger provided in the present application in a fifth specific embodiment;

[0021] Figure 7A schematic diagram of the structure of a heat exchange device provided in the present application in a specific embodiment.

[0022] Figure numerals: 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.

[0023] 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

[0024] 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.

[0025] It should be clear that the described embodiments are only part of the embodiments of the present application, rather than all the embodiments. Based on the embodiments in the present application, all other embodiments obtained by ordinary technicians in the field without creative work are within the scope of protection of the present application.

[0026] The terms used in the embodiments of the present application are only for the purpose of describing specific embodiments, and are not intended to limit the present application. The singular forms "a", "said" 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 other meanings.

[0027] It should be understood that the term "and / or" used in this article is only a description of the association relationship of associated objects, indicating that there can be three relationships. For example, A and / or B can represent: A exists alone, A and B exist at the same time, and B exists alone. In addition, the character " / " in this article generally indicates that the associated objects before and after are in an "or" relationship.

[0028] 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 at 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 is also necessary to understand that when it is mentioned that an element is connected to another element "upper" or "lower", it can not only be directly connected to another element "upper" or "lower", but also indirectly connected to another element "upper" or "lower" through an intermediate element.

[0029] The heat exchanger in the embodiment of the present application is described in detail below in conjunction with the accompanying drawings. In the absence of conflict, the features in the following embodiments and implementations may complement or be combined with each other.

[0030] like Figure 1-6 As shown, a first aspect of an embodiment of the present application provides a heat exchanger, which can improve the uniformity of refrigerant distribution. It mainly includes a first header 1, a second header 2, a plurality of heat exchange tubes 3, a first plate 4 and a first interface 6, wherein the first header 1 includes a first tube section 11 and a second tube section 12 separated from each other, and the first tube section 11 and the second tube section 12 are 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; a first plate 4, 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 headers 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; in at least two first channels 41, the flow cross-sectional area of ​​any first channel 41 is greater than the flow cross-sectional area of ​​another first channel 41 along the first direction, and the first direction is the direction from the first tube section 11 to the second tube section 12; the first interface 6 is located in the first tube section 11, and the first interface 6 is connected to the first tube section 11.

[0031] In this embodiment, the first header 1 and the second header 2 of the heat exchanger are hollow circular tubes, but in some other embodiments, in order to improve the pressure resistance of the first header 1 and the second header 2, the first header 1 and the second header 2 can also be set as rectangular tubes or tubes of other shapes with smaller flow cross-sectional areas, and the first header 1 and the second header 2 can be integrally formed or composed of multiple parts. In addition, the first header 1 and the second header 2 can be parallel to each other or arranged at a certain angle, which can be adjusted or preset according to actual use requirements and installation environment, etc., and this article does not make specific limitations on this.

[0032] It should be noted that the first pipe segment 11 and the second pipe segment 12 are isolated from each other, which means that the first pipe segment 11 and the second pipe segment 12 are not connected to each other without other components connecting the two. When the heat exchanger is working, the refrigerant in the first pipe segment 11 cannot directly enter the second pipe segment 12. The first pipe segment 11 and the second pipe segment 12 can be isolated by a partition plate set in the first header 1, or by welding two independent pipes. However, generally speaking, the isolation method using a partition plate has a lower manufacturing cost.

[0033] In addition, the first plate 4 is at least partially located in the second manifold 2, which means that the first plate 4 can be completely located in the second manifold 2, for example, the outer wall of the entire first plate 4 is fixedly connected to the inner wall of the second manifold 2 by welding or the like, so that the first plate 4 is completely located in the tube cavity of the second manifold 2; of course, the first plate 4 can also be only partially located in the second manifold 2. For example, when the first plate 4 is arranged in the second manifold 2 by plugging or the like, the area of ​​the first plate 4 needs to be slightly larger than the cross-section of the second manifold 2 to ensure stable cooperation between the first plate 4 and the second manifold 2, that is, the first plate 4 is partially located in the second manifold 2.

[0034] The heat exchange tube 3 in this embodiment can be a microchannel flat tube, or a single-channel or multi-channel round tube, and the multiple heat exchange tubes 3 are arranged substantially parallel to each other. One of the first tube section 11 and the second tube section 12 is an inlet tube for the refrigerant, and the other is an outlet tube for the refrigerant. When the heat exchanger works as an evaporator, the first tube section 11 is the inlet tube for the refrigerant, and the second tube section 12 is the outlet tube for the refrigerant. However, when the heat exchanger works as a condenser, the flow direction of the refrigerant is opposite, and the second tube section 12 is the inlet tube for the refrigerant, and the first tube section 11 is the outlet tube for the refrigerant.

[0035] 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, therefore, 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 uniformity of refrigerant distribution.

[0036] Taking the case where there are two first plates 4 as an example, after the refrigerant enters the heat exchanger from the first pipe section 11 and then enters the second header 2 through the connected heat exchange tubes 3, all the refrigerant that flows in will be distributed through the first first plate 4, and then a part of the refrigerant will flow into the heat exchange tube 3 between the first first plate 4 and the second first plate 4, and the other part of the refrigerant will be distributed through the second first plate 4. In this process, since the flow cross-sectional area of ​​the first channel 41 of the second first plate 4 is smaller than the flow cross-sectional area of ​​the first channel 41 of the first first plate 4, the reduced refrigerant can be better distributed, thereby improving the uniformity of refrigerant distribution.

[0037] It should be noted that the heat exchanger in the embodiment of the present application divides the first header 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 requirement of the refrigerant is lower when passing through this process, and the refrigerant can be distributed after entering the second header 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 supercooling section of the heat exchanger to improve the heat exchange effect.

[0038] In a specific embodiment, the flow cross-sectional area of ​​the second header 2 is defined as A 1 , the flow cross-sectional area of ​​any first channel 41 is A 2 , then A 1 and A 2 Satisfaction: 7 / 20≤A 2 / A 1 ≤1 / 2.

[0039] The first channel 41 can have the effect of mixing and spraying 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 spraying 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 the amount of refrigerant passing through the first channel 41 per unit time is small, resulting in the refrigerant not being able to circulate in time and accumulating, thereby affecting the overall distribution effect. Therefore, in any flow cross-sectional area A of the first channel 41, 2 The flow cross-sectional area A of the second header 2 1 Satisfy 7 / 20≤A 2 / A 1 When the flow rate is ≤1 / 2, the first channel 41 can achieve better mixing and injection effects, thereby further improving the uniformity of distribution.

[0040] Furthermore, in the first channel 41, the flow cross-sectional area A 2 Occupies the flow cross-sectional area A of the second header 2 1 When the percentage is 38% to 46%, 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.

[0041] like Figure 2As shown, in a specific embodiment, if a surface perpendicular to the first direction and passing through the second header 2 is defined as the first surface 5, on the first surface 5, the projection of one first channel 41 is at least partially misaligned with 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 "misalignment" and "non-overlapping" 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 misalignment means that the two adjacent first channels 41 may not overlap at all, or may only not overlap partially. The two adjacent first channels 41 arranged in a staggered manner can play an alternating blocking role on the refrigerant, increase the time 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.

[0042] like Figure 2 As shown, 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, and the first gap 412 is located between the first plate 4 and the tube wall of the second collector 2.

[0043] In this embodiment, the first channel 41 distributes the refrigerant in the form of the first hole 411 and / or the first gap 412. The shapes of the first hole 411 and the first gap 412 can be circular or rectangular, or irregular shapes, such as a combination of multiple shapes, etc. In addition, the number of the first hole 411 and the first gap 412 can also be one or more, which is not specifically limited in this article, as long as the first hole 411 and the first gap 412 can connect the tube cavity of the second header 2 on both sides of the first plate 4. In addition, the first hole 411 and the first gap 412 can exist separately or simultaneously on the same first plate 4, and the refrigerant is sprayed by the first hole 411 and / or the first gap 412, thereby improving the overall distribution effect.

[0044] In addition, when the heat exchanger is in operation, due to the gravity 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, and its flow velocity will become lower and lower along the flow direction of the refrigerant. Therefore, the number, position, etc. of the first holes 411 and the first gaps 412 can be adjusted according to actual distribution needs. 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.

[0045] like Figure 3-4As shown, 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.

[0046] 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 convert the original single row heat exchanger into a double row can better meet the heat exchange requirements of the heat exchanger.

[0047] like Figure 5 As shown, in a specific embodiment, the heat exchanger also includes a second interface 7, the second interface 7 is located in the second pipe section 12, and the second interface 7 is connected to the second pipe section 12; the heat exchanger has a working state, when in the working state, the length direction of the second header 2 is parallel to the gravity direction, and the side of the second section 32 away from the first section 31 is the windward side.

[0048] 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 partial downstream and partial countercurrent flow design in the entire heat exchanger. Experimental verification has confirmed that the heat exchanger performance of the double-row heat exchanger with a partial downstream and partial countercurrent flow design of the refrigerant is better than that of the full downstream design.

[0049] like Figure 5 As shown, in a 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 L. 1 , the length of the second segment 32 is L 2 , then L 1 and L 2 Satisfy: 2 / 3≤L 1 / L 2 <1. The different lengths of the first section 31 and the second section 32 can make the heat exchanger in the outlet section face the wind on one side when the heat exchanger is used as an evaporator, which is conducive to the stability of superheat. When used as a condenser, a higher wind speed during single-row heat exchange will also make the supercooling more stable.

[0050] like Figure 6 As shown, 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 N 1 , the number of heat exchange tubes 3 connected to the first pipe section 11 is N 2 , then N 1and N 2 Satisfies: 1≤N 2 -N 1 ≤3.

[0051] like Figure 6 As shown, when the heat exchanger is placed vertically, the first end 21 is an end at the bottom of the second header 2, and the first sub-plate 42 is the first first plate 4 close to the bottom of the second header 2. The number N of heat exchange tubes 3 connected to the first pipe section 11 is 2 The number N of heat exchange tubes 3 between the first sub-plate 42 and the first end 21 1 Satisfy 1≤N 2 -N 1 ≤3, when the heat exchanger works as an evaporator, after the refrigerant enters the first pipe section 11, a part of the refrigerant can directly enter the second header 2 on the upper part of the first sub-plate 42 through the heat exchange tube 3 connecting the upper part of the first sub-plate 42 and the first pipe section 11, thereby replenishing the refrigerant on the upper part of the first sub-plate 42. As mentioned above, after the refrigerant passes through the obstruction of the first plate 4, in addition to the reduction in the flow rate, there will also be pressure loss. Along the flow direction of the refrigerant, its flow rate and flow rate will become lower and lower. Therefore, the connection method in this embodiment can replenish the refrigerant on the upper part of the first sub-plate 42, thereby improving the uniformity of the distribution on the upper part of the first plate 4.

[0052] 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.

[0053] like Figure 7 As shown, the second aspect of the embodiment of the present application provides a heat exchange device, including at least two heat exchange parts, which are the heat exchangers in the embodiment of the first aspect, and two adjacent heat exchangers are arranged along the length direction of the first header 1, and one heat exchanger is fixedly connected to another adjacent heat exchanger. 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 distributes the refrigerant more evenly when working as an evaporator, the heat exchange device also has better distribution performance when working as an evaporator.

[0054] like Figure 7As shown, in a specific embodiment, the heat exchange device also includes fins 8 and a first partition 9. The fins 8 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, which can be preset according to the size of the heat exchanger and the use environment; 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.

[0055] In this embodiment, when multiple heat exchange parts are combined into one heat exchange device for use, if the inlet and outlet pipes use the same header (first header 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 and a thermal bridge will be formed, which will affect the state of the inlet and outlet refrigerants and reduce the heat exchange effect. Therefore, the thermal bridge effect is weakened by providing 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.

[0056] 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, the present application may have various modifications and variations. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present application shall be included in the protection scope of the present application.

Claims

1. A heat exchanger, characterized in that: include: A first header (1), the first header (1) comprising a first pipe section (11) and a second pipe section (12) which are separated from each other, the first pipe section (11) and the second pipe section (12) being arranged along the length direction of the first header (1); a second header (2), the second header (2) being arranged at an interval with 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), the first plate (4) being at least partially located in the second header (2), the first plate (4) comprising first channels (41), the first channels (41) being connected to the second headers (2) on both sides of the first plate (4) in a thickness direction, the number of the first plates (4) being at least two, at least two of the first plates (4) being arranged at intervals in a length direction of the second header (2); a flow cross-sectional area of ​​any of the at least two first channels (41) being greater than a flow cross-sectional area of ​​another of the first channels (41) in a first direction, the first direction being a direction from the first pipe section (11) to the second pipe section (12); A first interface (6), the first interface (6) is located in the first pipe section (11), and the first interface (6) is in communication with the first pipe section (11).

2. The heat exchanger according to claim 1, characterized in that: 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, characterized in that: A surface perpendicular to the first direction and passing through the second header (2) is defined as a first surface (5), and on the first surface (5), a projection of one of the first channels (41) is at least partially offset from a projection of another adjacent first channel (41).

4. The heat exchanger according to claim 2, characterized in that: The first channel (41) comprises 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) comprises 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, characterized in that: 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, characterized in that An end of the first section (31) away from the curved section (33) is connected to the second header (2), and an 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, characterized in that The heat exchanger further comprises a second interface (7), the second interface (7) being located in the second pipe section (12), 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 gravity direction, 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 1-4 or 6-7, characterized in that: 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 tube 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, characterized in that: 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 another adjacent heat exchanger.

10. The heat exchange device according to claim 9, characterized in that: The heat exchange device also includes: Fins (8), the fins (8) being arranged at intervals on at least a portion of the heat exchange tubes (3) along the length direction of the first header (1); A first partition (9), 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.

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