Heat exchanger

Abstract

The heat exchanger comprises a heat exchange tube and a header, the header is provided with a first cavity, the length direction of the heat exchange tube is defined as the first direction, the heat exchange tube is inserted into the header in the first direction, and the direction perpendicular to the first direction and the length direction of the header is defined as the second direction; the maximum size W1 of the first cavity in the second direction is greater than the maximum size L1 of the first cavity in the first direction; the plane perpendicular to the length direction of the header is defined as a first plane, the projection area of the part, inserted into the first cavity, of the heat exchange pipe on the first plane is S1, the projection area of the first cavity on the first plane is S, and S1 / S is larger than or equal to 3 / 10 and smaller than or equal to 9 / 10, so that the inner volume of the header is reduced, and the heat exchange effect of the heat exchanger is improved.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of heat exchange, in particular, the present application relates to a heat exchanger applied to the field of HVACR (heating, ventilation, air conditioning and refrigeration). BACKGROUND

[0002] In the related art, the heat exchanger comprises a header and a heat exchange tube, the end of the heat exchange tube is inserted into the header and communicates with the header; the heat exchange tube and the header are used in cooperation, if a heat exchange tube with a larger width is used to improve the capacity of the heat exchanger, a header with a larger diameter must also be used in cooperation, but the header with a larger diameter will bring a larger content volume, and the larger content volume of the header requires more refrigerant charge to ensure the heat exchange capacity of the heat exchanger, and also affects the uniformity of refrigerant distribution. SUMMARY

[0003] The present application provides a heat exchanger, which reduces the content volume of the header and is beneficial to improve the heat exchange effect of the heat exchanger.

[0004] The present application provides a heat exchanger, comprising a heat exchange tube and a header, the header has a first cavity, the length direction of the heat exchange tube is defined as a first direction, the heat exchange tube is inserted into the header along the first direction, the direction perpendicular to the first direction and perpendicular to the length direction of the header is defined as a second direction, the maximum size W1 of the first cavity in the second direction is greater than the maximum size L1 of the first cavity in the first direction; the plane perpendicular to the length direction of the header is defined as a first plane, the projection area of the part of the heat exchange tube inserted into the first cavity in the first plane is S1, and the projection area of the first cavity in the first plane is S, wherein: 3 / 10≤S1 / S≤9 / 10.

[0005] According to the heat exchanger of the present application, on the one hand, the heat exchange tube is inserted into the header along the first direction, the maximum size W1 of the first cavity of the header in the second direction is greater than the maximum size L1 in the first direction, which is beneficial to reduce the content volume of the first cavity of the header and reduce the refrigerant charge of the heat exchanger; on the other hand, the projection area S1 of the part of the heat exchange tube inserted into the first cavity in the first plane is greater than or equal to 3 / 10 of the projection area S of the first cavity in the first plane, so that the remaining cross-sectional area in the first cavity is reduced, the remaining volume in the first cavity is also correspondingly reduced, the flow space of the refrigerant in the first cavity is reduced, the flow rate is increased, the gas-liquid two-phase refrigerant is mixed more uniformly in the first cavity, and S1 / S≤9 / 10, so that the remaining cross-sectional area in the first cavity will not be too small to increase the flow resistance, so that the flow space of the refrigerant in the first cavity is within a suitable range, the flow rate of the refrigerant is increased, the gas-liquid two-phase refrigerant is mixed more uniformly in the first cavity, so that the gas-liquid refrigerant entering each heat exchange tube is more uniform, which is beneficial to improve the heat exchange effect of the heat exchanger. BRIEF DESCRIPTION OF DRAWINGS

[0006] Figure 1 A structure schematic view of a heat exchanger according to an embodiment of the present application;

[0007] Figure 2 A structure schematic view of a heat exchanger according to an embodiment of the present application;

[0008] Figure 3 A structure schematic view of a heat exchanger according to an embodiment of the present application;

[0009] Figure 4 A structure schematic view of a heat exchanger according to an embodiment of the present application;

[0010] Figure 5 A structure schematic view of a heat exchanger according to an embodiment of the present application;

[0011] Figure 6 A structure schematic view of a heat exchanger according to an embodiment of the present application;

[0012] Figure 7 A structure schematic view of a heat exchanger according to an embodiment of the present application;

[0013] Figure 8 A structure schematic view of a heat exchanger according to an embodiment of the present application;

[0014] Figure 9 A structure schematic view of a heat exchanger according to an embodiment of the present application;

[0015] Figure 10 A structure schematic view of a heat exchanger according to an embodiment of the present application;

[0016] Figure 11 A structure schematic view of a heat exchanger according to an embodiment of the present application;

[0017] Figure 12 A structure schematic view of a heat exchanger according to an embodiment of the present application;

[0018] Figure 13 A structure schematic view of a heat exchanger according to an embodiment of the present application;

[0019] Figure 14 A structure schematic view of a heat exchanger according to an embodiment of the present application;

[0020] Figure 15 A structure schematic view of a heat exchanger according to an embodiment of the present application;

[0021] Figure 16 A structure schematic view of a heat exchanger according to an embodiment of the present application.

[0022] wherein the heat exchanger 100,

[0023] header 1, first body member 11, second body member 12, first cavity 13, first hole 14, protruding portion 15, reinforcing portion 16, first recess 18, first end 1A, second end 1B;

[0024] heat exchange tube 2, connecting tube 3, first opening 31, first plate 4, second plate 5, fin 6;

[0025] The accompanying drawings, which are incorporated herein and constitute part of the specification, illustrate embodiments consistent with the application and, together with the description, serve to explain the principles of the application. DETAILED DESCRIPTION

[0026] For a better understanding of the technical solutions of the present application, the embodiments of the present application are described in detail below with reference to the drawings.

[0027] It should be clear that the described embodiments are only part of the technical solutions of the present application, rather than all of the technical solutions. Based on the technical solutions in the present application, all other technical solutions obtained by those of ordinary skill in the art without creative labor fall within the scope of protection of the present application.

[0028] 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 the plural forms, unless the context clearly indicates otherwise.

[0029] It should be understood that the term "and / or" used herein is only to describe the association relationship of the associated objects, which means that there can be three relationships, for example, A and / or B, which can represent the three cases of A alone, A and B together, and B alone. In addition, the character " / " in this paper generally represents that the front and rear associated objects are a "or" relationship.

[0030] It should be noted that the "up", "down", "left", "right" and other directional words described in the embodiments of the present application are described from the angle shown in the drawings, and should not be understood as limiting the embodiments of the present application. In addition, in the context, it should also be understood that when referring to an element connected to another element "on" or "under", it can be directly connected to another element "on" or "under", or indirectly connected to another element "on" or "under" through an intermediate element.

[0031] The heat exchanger of the embodiments of the present application is described below with reference to the drawings.

[0032] For the heat exchanger in air conditioning system using refrigerant vapor compression cycle, the refrigerant charge in the system depends on the content volume of the heat exchanger, and the excessive content volume of the heat exchanger leads to the increase of the refrigerant charge, and the excessive refrigerant charge will cause the negative effects such as the increase of production cost and the decrease of safety factor, so it is the key of the design and structure of the heat exchanger to reduce the content volume under the premise of ensuring the heat exchange performance.

[0033] The application provides a heat exchanger, which comprises heat exchange tubes 2 and a header 1, the header 1 has a first cavity 13, the length direction of the heat exchange tubes 2 is defined as a first direction, the heat exchange tubes 2 are inserted into the header 1 along the first direction, a direction perpendicular to the first direction and perpendicular to the length direction of the header is defined as a second direction, the maximum dimension W1 of the first cavity 13 in the second direction is greater than the maximum dimension L1 of the first cavity in the first direction, a plane perpendicular to the length direction of the header is defined as a first plane, the projection area of the part of the heat exchange tubes inserted into the first cavity in the first plane is S1, and the projection area of the first cavity in the first plane is S, wherein 3 / 10≤S1 / S≤9 / 10.

[0034] As shown in Figures 1-14 For the convenience of understanding, the first direction is the X direction in the figure, the second direction is the Y direction in the figure, the length direction of the header 1 is the Z direction in the figure, the first direction, the second direction and the length direction of the header 1 are generally perpendicular to each other, the plane perpendicular to the length direction of the header is the first plane, and the first plane is parallel to the first direction and the second direction. The header 1 has a first cavity 13, the heat exchange tubes 2 are inserted into the first cavity 13 of the header 1 along the first direction and communicate with the header 1, the maximum dimension W1 of the first cavity 13 in the second direction is greater than the maximum dimension L1 of the first cavity 13 in the first direction, which is beneficial to the insertion of the heat exchange tubes into the header 1, the length of the first cavity is the maximum length in the cavity of the header 1, the dimension L1 of the first cavity 13 of the header 1 in the first direction in which the heat exchange tubes 2 are inserted is less than the dimension W1 in the second direction, which is beneficial to the reduction of the content volume of the header 1 and the improvement of the flow rate of the refrigerant, the header 1 is generally flat, compared with the traditional circular header structure, the content volume of the first cavity 13 of the header is reduced, after the reduction of the content volume of the header 1, the refrigerant charge in the heat exchanger system is also reduced, which can reduce the cost, save energy and protect the environment, and after the reduction of the refrigerant charge, the safety factor of the heat exchanger is also improved.

[0035] The heat exchange pipe 2 is inserted into the first cavity 13 of the header 1 along the first direction, and the projected area S1 of the portion of the heat exchange pipe 2 inserted into the first cavity 13 on the first plane is greater than or equal to 3 / 10 of the projected area S of the first cavity on the first plane and less than or equal to 9 / 10 of the projected area S of the first cavity on the first plane, for example, S1 / S can be 0.4, 0.5, 0.55, 0.6, 0.7, 0.8, 0.9, etc., so that after the heat exchange pipe 2 is inserted into the header 1, the remaining cross-sectional area S-S1 of the first cavity 13 except for the inserted heat exchange pipe is greater than or equal to 1 / 10 and less than or equal to 7 / 10, and the remaining cross-sectional area of the first cavity 13 except for the inserted heat exchange pipe is defined as S2, S2=S-S1, S2 is the flowable cross-sectional area of the refrigerant, when S1 / S is greater than or equal to 3 / 10, the remaining cross-sectional area S2 of the first cavity 13 is reduced, and the remaining volume of the first cavity 13 of the header 1 is also correspondingly reduced, the remaining volume of the first cavity 13 of the header 1 is the flow space of the refrigerant, and the flow space of the refrigerant in the first cavity 13 of the header 1 is reduced, the flow velocity of the refrigerant in the first cavity is increased when the heat exchanger is in the working state, the gas-liquid refrigerant is mixed more uniformly in the first cavity, so that the gas-liquid refrigerant entering each heat exchange pipe 1 is more uniform, which is beneficial to improve the heat exchange effect of the heat exchanger.

[0036] For example, the projected area S1 of the portion of the heat exchange pipe 2 inserted into the first cavity 13 on the first plane is as shown in Figure 6 The flowable cross-sectional area S2 of the refrigerant in the first cavity 13 is as shown in Figure 6 The cross-sectional area S of the first cavity is the sum of the cross-sectional areas of S1 and S2.

[0037] It can be understood that when the projected area S1 of the portion of the heat exchange pipe 2 inserted into the first cavity 13 on the first plane is less than 3 / 10 of the cross-sectional area S of the first cavity, for example, the projected area S1 of the portion of the heat exchange pipe 2 inserted into the first cavity 13 on the first plane is 1 / 4 of the cross-sectional area S of the first cavity, the remaining cross-sectional area S-S1 of the first cavity 13 except for the inserted heat exchange pipe is 3 / 4, the remaining volume of the first cavity 13 of the header 1 is larger, and more refrigerant needs to be filled, and the flow space of the refrigerant in the first cavity 13 is large, the flow velocity of the refrigerant is low, and the gas-liquid refrigerant is more likely to separate in the first cavity 13, which cannot form a large flow velocity to make the refrigerant mix uniformly in the first cavity 13, affecting the heat exchange effect of the heat exchanger.

[0038] The projected area S1 of the partial heat exchange tube 2 inserted into the first cavity 13 in the first plane is less than or equal to 9 / 10 of the cross-sectional area S of the first cavity. When the projected area S1 of the partial heat exchange tube 2 inserted into the first cavity 13 in the first plane is greater than 9 / 10 of the cross-sectional area S of the first cavity, the remaining cross-sectional area S2 in the first cavity is less than 1 / 10, the flow space of the refrigerant in the first cavity 13 is small, the flow resistance of the refrigerant is increased, the flow of the refrigerant in the first cavity 13 is not conducive, the gas-liquid refrigerant cannot be uniformly mixed in the first cavity 13, the uniformity of the refrigerant distribution is not conducive, and the heat exchange effect of the heat exchanger is affected.

[0039] Therefore, 3 / 10≤S1 / S≤9 / 10 is set, that is, the projected area S1 of the partial heat exchange tube 2 inserted into the first cavity 13 in the first plane is greater than or equal to 3 / 10 of the cross-sectional area S of the first cavity and less than or equal to 9 / 10 of the projected area S of the first cavity in the first plane, so that the remaining cross-sectional area S-S1 of the first cavity 13 except the inserted heat exchange tube is greater than or equal to 1 / 10 and less than or equal to 7 / 10, so that the flow space of the refrigerant in the first cavity is in a suitable range, the flow rate is not too low because the flow space is too large, and the flow resistance is not too large because the flow space is too small, the flowable space in the first cavity 13 is in the range, the flow rate of the refrigerant is increased, the gas-liquid two-phase refrigerant is more uniformly mixed in the first cavity, so that the gas-liquid refrigerant entering each heat exchange tube is more uniform, which is conducive to improving the heat exchange effect of the heat exchanger.

[0040] When the heat exchanger 100 is applied, when the heat exchanger 100 is placed vertically or inclined along the length of the header 1, the gaseous refrigerant will flow upwards, and the liquid refrigerant will descend due to gravity. Because the internal volume of the header 1 in the present application is reduced, the flow space of the refrigerant is reduced, and the flow rate is increased, the influence of gravity on the liquid refrigerant is reduced, and through the setting of 3 / 10≤S1 / S≤9 / 10, the flow space of the refrigerant in the first cavity is in a suitable range, the flow rate is not too low because the flow space is too large, and the flow resistance is not too large because the flow space is too small, the flowable space in the first cavity 13 is in the range, the flow rate of the refrigerant is increased, the gas-liquid two-phase refrigerant is more uniformly mixed in the first cavity, so that the gas-liquid refrigerant entering each heat exchange tube is more uniform, which improves the uniformity of the refrigerant distribution of the entire heat exchanger and improves the heat exchange effect of the heat exchanger.

[0041] In some embodiments, the header 1 includes a first main body 11 and a second main body 12, and the pipe wall enclosing the header 1 includes at least part of the first main body 11 and at least part of the second main body 12. The first main body 11 extends along the length direction of the header 1, and the second main body 12 extends along the length direction of the header 1.

[0042] Specifically, as Figures 1-9As shown in the drawings, the header 1 comprises a first main body 11 and a second main body 12, the pipe wall of the header 1 is enclosed by at least part of the first main body 11 and at least part of the second main body 12, and the first cavity 13 of the header 1 is enclosed by at least part of the first main body 11 and at least part of the second main body 12. The first main body 11 extends along the length direction of the header 1, and the second main body 12 extends along the length direction of the header 1.

[0043] In some embodiments, the first main body 11 and the second main body 12 are in a split structure, and the connection part of the first main body 11 and the second main body 12 comprises a reinforcing part 16. The reinforcing part 16 is connected with the first main body and / or the second main body. The reinforcing part 16 is integrally arranged with the first main body 11, or the reinforcing part 16 is integrally arranged with the second main body 12, or the reinforcing part 16 is arranged in a split structure with the first main body 11 and the second main body 12.

[0044] In some embodiments, the first main body 11 and the second main body 12 are in a split structure, that is, the first main body 11 and the second main body 12 are two separate components. At least part of the first main body 11 and at least part of the second main body 12 enclose the pipe wall of the header 1. When the first main body 11 and the second main body 12 are in a split structure, the header 1 is more convenient to process. The header 1 further comprises a reinforcing part 16 connected with the first main body 11 and / or the second main body 12. Since the first main body 11 and the second main body 12 are in a split structure, and the header 1 is applied in a heat exchanger, refrigerant flows in the pipe cavity. If the connection part of the first main body 11 and the second main body 12 leaks, the refrigerant in the header 1 will leak, which affects the reliability and heat exchange effect of the heat exchanger. By arranging the reinforcing part 16, the strength of the connection part of the first main body 11 and the second main body 12 is increased, and the reliability of the heat exchanger is improved.

[0045] Specifically, as shown in the drawings, the first main body 11 and the second main body 12 are in a split structure, and the header 1 further comprises a reinforcing part 16. The reinforcing part 16 is integrally arranged with the first main body 11, or the reinforcing part 16 is integrally arranged with the second main body 12. Figures 2-5 , Figures 8-9 The reinforcing part 16 can be part of the first main body 11 or part of the second main body 12. The reinforcing part 16 is formed by overlapping the first main body 11 and the second main body 12 at the connection part for a certain length, so as to strengthen the structure of the connection part of the first main body 11 and the second main body 12, improve the strength of the header 1 at the connection part of the first main body 11 and the second main body 12, improve the reliability of the header 1, and is more convenient to process.

[0046] Specifically, Figure 2 , Figure 3 , Figure 8In some embodiments, the first body part 11 and the second body part 12 are integrated, and the reinforcing part 16 is integrated with the first body part 11 or the second body part 12, and part of the first body part 11 and part of the second body part 12 overlap in the first direction for a certain length, thereby forming the reinforcing part 16. Figure 4 and Figure 9 In some embodiments, the first body part 11 of the header 1 comprises a straight section and an arc section, the second body part 12 is in an arc shape, the first body part 11 comprises a reinforcing part 16 bent towards the second body part 12 to increase the strength of the connection between the first body part 11 and the second body part 12. Figure 5 In some embodiments, the first body part 11 of the header 1 is in an arc shape, the second body part 12 of the header 1 comprises a straight section, the second body part 12 comprises a reinforcing part 16 bent towards the first body part 11 to increase the strength of the connection between the first body part 11 and the second body part 12, improve the strength and reliability of the header, and facilitate processing.

[0047] In some embodiments, the reinforcing part 16 is separately provided from the first body part 11 and the second body part 12. That is, the reinforcing part 16 can also be separately provided and not integrated with the first body part 11 and the second body part 12, for example, an annular reinforcing part 16 or a reinforcing part 16 in a buckle structure is provided on the outer periphery of the first body part 11 and the second body part 12, so that the first body part 11 and the second body part 12 are more firmly connected, thereby improving the strength of the header 1.

[0048] In some embodiments, the first body part 11 and the second body part 12 are integrated, as shown in Figures 6-7 When the first body part 11 and the second body part 12 are integrated, the pipe wall enclosing the header 1 comprises the first body part 11 and the second body part 12, and when the first body part 11 and the second body part 12 are integrated, the header 1 has greater pressure resistance, reducing the risk of leakage of the header 1 and improving the reliability of the heat exchanger 100.

[0049] Optionally, when the first body part 11 and the second body part 12 are integrated, the header 1 can be processed by extrusion, drawing or other methods, which are not limited herein.

[0050] In some embodiments, the header 1 comprises a protruding part 15 and a first hole 14, the protruding part 15 is connected to the second body part 12, the first hole 14 is located in the first body part 11, the heat exchange pipe 2 is inserted into the header along the first hole 14, the end of part of the heat exchange pipe 2 abuts against the protruding part 15, and the end of the heat exchange pipe 2 has a gap with the second body part 12.

[0051] Specifically, as shown in Figure 7 and Figure 8As shown, the header 1 comprises a protruding part 15 connected with the second body part 12, the first hole 14 is located in the first body part 11, the heat exchange pipe 2 is inserted into the first cavity 13 of the header 1 along the first hole 14 from the first body part 11, the end of the heat exchange pipe 2 abuts against the protruding part 15, the protruding part 15 can limit the heat exchange pipe 2 inserted into the header 1, so that the heat exchange pipe 2 is inserted into the header 1 more deeply, and the residual volume in the header 1 is reduced to a greater extent, the flow space of the refrigerant in the first cavity is reduced, the flow rate of the refrigerant is improved, and the refrigerant is mixed more uniformly in the first cavity; at the same time, the end of the heat exchange pipe 2 has a predetermined gap with the second body part 12, so that the heat exchange pipe 2 inserted into the header 1 has a certain space to communicate with the first cavity 13, and the refrigerant flowing in or out of the end of the heat exchange pipe 2 better communicates with the first cavity 13 of the header 1, so as to ensure the heat exchange effect of the heat exchanger.

[0052] In some embodiments, the protruding part 15 is located in the first cavity 13, which can further reduce the flow space of the refrigerant in the first cavity 13, improve the flow rate of the refrigerant, and make the refrigerant more uniformly mixed in the first cavity, which is beneficial to improve the heat exchange effect of the heat exchanger.

[0053] Optionally, the protruding part 15 can be a protruding plate structure as shown in Figure 7 , or a plurality of protruding wave shapes as shown in Figure 8 , or other forms, which are not limited here as long as they can limit and have a certain gap between the end of the heat exchange pipe 2 and the second body part 12.

[0054] Optionally, the protruding part 15 can be an integral structure with the second body part 12, which is more convenient to process, or can be a separate structure with the second body part 12, which is not limited here.

[0055] In some embodiments, the first body part 11 and the second body part 12 can be provided in a plurality of structures, at least part of the first body part 11 comprises a straight line segment, and at least part of the second body part 12 comprises an arc line segment; or, at least part of the first body part 11 comprises an arc line segment, and at least part of the second body part 12 comprises a straight line segment; or, at least part of the first body part 11 comprises a straight line segment, and at least part of the second body part 12 comprises a straight line segment, the straight line segment comprises two or more straight line segments, the pipe wall enclosing the header 1 comprises a plurality of straight line segments, or at least part of the first body part 11 comprises an arc line segment, and at least part of the second body part 12 comprises an arc line segment.

[0056] Specifically, as shown in Figure 2 , Figure 3 , Figures 6-8As shown, at least a portion of the first main body 11 includes straight line segments, and at least a portion of the second main body 12 includes straight line segments. The straight line segments include two or more. The manifold 1 formed by the first main body 11 and the second main body 12 is generally a rectangular structure, but it can also be formed into other quadrilateral structures.

[0057] like Figure 4 As shown, the first main component 11 includes straight segments, and at least a portion of the second main component 12 includes curved segments; the manifold 1 is generally D-shaped. Figure 5 As shown, at least a portion of the first main body 11 includes an arc segment, the second main body 12 includes a straight segment, and the manifold 1 is generally D-shaped. Figure 9 As shown, at least a portion of the first main body 11 includes straight segments and curved segments, and the second main body 12 includes straight segments and curved segments, forming an irregular manifold 1 structure. Figure 10 As shown, at least a portion of the first main body 11 includes an arc segment, at least a portion of the second main body 12 includes an arc segment, and the manifold 1 formed by the first main body 11 and the second main body 12 is generally elliptical.

[0058] It is understandable that the structure of the first main component 11 and the second main component 12 can also be other structures, as long as it can be ensured that the length of the first cavity 13 of the manifold 1 in the second direction is greater than the length of the first cavity 13 in the first direction, and the flow space of the remaining refrigerant in the first cavity is within a suitable range after the heat exchange tube 2 is inserted into the first cavity 13. No restrictions are imposed here.

[0059] In some embodiments, the length of the portion of the heat exchange tube 2 inserted into the first cavity 13 is L, and the hydraulic diameter of the heat exchange tube 2 is W, wherein: 0.02W≤W1-W≤W, and / or, 0.1L≤L1-L≤L.

[0060] like Figure 3As shown, the length of the heat exchange tube 2 inserted into the first cavity 13 is L, where L is the maximum length of the heat exchange tube 2 inserted into the first cavity 13 of the manifold 1 along the first direction. The hydraulic diameter of the heat exchange tube 2 is W, which means that the length of the heat exchange tube 2 in the second direction is W. Define 0.1L≤L1-L≤L, 0.02W≤W1-W≤W, where L1-L is the remaining length in the first cavity 13 after the inserted heat exchange tube 2 in the first direction, and W1-W is the remaining dimension in the first cavity 13 after the inserted heat exchange tube 2 in the second direction. When L1-L is less than 0.1L and / or W1-W is less than 0.02W, the gap between the heat exchange tube 2 and the manifold 1 in the first cavity 13 is too small, and the refrigerant flow resistance inside the manifold 1 is too large. This will lead to uneven distribution of refrigerant in different heat exchange tubes 2, resulting in a decrease in the heat exchange efficiency of the heat exchanger. At the same time, the impact force between the refrigerant and the manifold 2 will also indirectly increase the refrigerant flow resistance in the heat exchange tube 2, affecting the heat exchange efficiency of the heat exchanger. When L1-L is greater than L, and / or W1-W is greater than W, the size of the first cavity 13 of the manifold 1 is too large, which cannot meet the design requirement of reducing the volume of the manifold. Furthermore, the refrigerant has too low a flow rate when flowing inside the first cavity 13, resulting in insufficient driving force and hindering the uniform mixing of gaseous and liquid refrigerant within the first cavity.

[0061] Therefore, by setting 0.02W≤W1-W≤W and / or 0.1L≤L1-L≤L, the flowable cross-sectional area of ​​the manifold 1 in the first cavity 13 is reduced after the heat exchange tube 1 is inserted into the manifold 1. The remaining volume in the first cavity 13 is reduced accordingly, and the flowable space of the refrigerant in the first cavity is reduced, which increases the flow rate of the refrigerant. Furthermore, the remaining flowable space in the first cavity 13 will not result in a low flow rate due to an excessively large flow space for the refrigerant, nor will it result in excessive flow resistance due to an excessively small flow space for the refrigerant. Within this range, the flowable space in the first cavity 13 can increase the flow rate of the refrigerant, and the gas-liquid refrigerant mixes more evenly in the first cavity, thereby making the gas-liquid refrigerant entering each heat exchange tube more uniform and improving the heat exchange effect of the heat exchanger.

[0062] Optionally, the heat exchange tube 2 can be a flat heat exchange tube or a round tube, without limitation. When the heat exchange tube is a flat heat exchange tube, the hydraulic diameter of the heat exchange tube 2 is W, which is the width of the flat heat exchange tube. When the heat exchange tube is a round heat exchange tube, the hydraulic diameter of the heat exchange tube 2 is W, which is the diameter of the round heat exchange tube.

[0063] In some embodiments, the heat exchanger 100 further includes a connecting pipe 3, which communicates with the manifold 1. The connecting pipe 3 includes a first opening 31 located on its radial side, and the connecting pipe 3 communicates with the manifold 1 through the first opening 31.

[0064] like Figure 11 and Figure 12As shown, the heat exchanger 100 further comprises a connecting pipe 3 connected with the header 1 and communicating with the first cavity 13 of the header 1, the connecting pipe 3 comprises an inlet connecting pipe and an outlet connecting pipe for refrigerant flowing into or out of the heat exchanger 100, realizing the connection of the heat exchanger 100 with other components and the heat exchange by the refrigerant flowing into or out of the heat exchanger 100. It can be understood that the inlet connecting pipe and the outlet connecting pipe of the heat exchanger are opposite in the evaporator working condition and the condenser working condition, the inlet connecting pipe in the evaporator working condition is the outlet connecting pipe in the condenser working condition, and the outlet connecting pipe in the evaporator working condition is the inlet connecting pipe in the condenser working condition. In the application of the heat exchanger 100, the position of the inlet connecting pipe and the position of the opening on the connecting pipe affect the position and direction of the refrigerant flowing into the heat exchanger 100, so the position of the inlet connecting pipe and the position of the opening have a more obvious effect on the heat exchange effect of the heat exchanger.

[0065] The connecting pipe 3 comprises a first opening 31 located on the side of the connecting pipe 3 in the radial direction, especially at the inlet connecting pipe. When the heat exchanger 100 is in working condition, when the refrigerant flows into the heat exchanger 100, it first flows into the header 1 through the connecting pipe 3. Since the internal volume of the header 1 in the present application is reduced, the flow space in the header 1 is reduced, and when the opening end of the connecting pipe is opposite to the pipe wall of the header 1, it will increase the difficulty of the refrigerant flowing in the length direction of the header 1. Therefore, the opening of the connecting pipe 3 is arranged on the side of the connecting pipe 3 in the radial direction, so that the connecting pipe 3 can communicate with the header 1 through the first opening 31 located on the side of the connecting pipe 3 in the radial direction, and the refrigerant can flow into or out of the first cavity 31 communicating with the first cavity 31 through the first opening 31. By changing the flow direction of the inlet refrigerant, the difficulty of the refrigerant flowing is reduced, the refrigerant flows better in the first cavity 13, and the heat exchange effect of the heat exchanger is improved.

[0066] As shown in the figure, Figure 12 The first opening 31 can be two, and the two first openings 31 are arranged along the circumference of the connecting pipe 3. Of course, the first opening 31 can also be one, and the first opening 31 can also be multiple. The multiple first openings 31 can be arranged along the axial direction of the connecting pipe 3, or the multiple first openings 31 can be arranged along the circumferential direction of the connecting pipe 3. The specific arrangement is not limited here, which can be arranged according to the structure and application of the heat exchanger.

[0067] It can be understood that the opening of the connecting pipe 3 can be arranged at the axial end of the connecting pipe 3, or the opening can be arranged at the axial end of the connecting pipe 3 and the radial direction of the connecting pipe 3, so as to improve the flow of the refrigerant in the first cavity 13 of the header and improve the uniformity of the refrigerant distribution.

[0068] In some embodiments, the manifold 1 has a first end 1A and a second end 1B in its length direction. When the connector 3 is close to the first end 1A relative to the second end 1B, the first opening 31 faces the direction from the first end 1A to the second end 1B; when the connector 3 is close to the second end 1B relative to the first end 1A, the first opening 31 faces the direction from the second end 1B to the first end 1A.

[0069] like Figure 11 As shown, the manifold 1 has a first end 1A and a second end 1B along its length. When the heat exchanger 100 is used, when the heat exchanger 100 is placed vertically or inclined along the length of the manifold 1, liquid refrigerant tends to accumulate in the lower part of the first cavity 13 of the manifold 1, that is, near the second end 1B of the manifold 1, while gaseous refrigerant tends to accumulate in the upper part of the first cavity 13 of the manifold 1, that is, near the first end 1A of the manifold 1.

[0070] When the connecting pipe 3 is positioned closer to the first end 1A than the second end 1B, the first opening 31 faces the direction from the first end 1A to the second end 1B. That is, when the heat exchanger is in use, if the connecting pipe 3 is positioned near the upper part of the manifold 1, the first opening 31 faces downwards. This allows the refrigerant on the inlet side to flow towards a greater flow space within the first cavity 13, resulting in better refrigerant flow within the first cavity 13 and more even refrigerant flow into the heat exchange tubes 2, thus improving the heat exchanger's distribution effect. When the connecting pipe 3 is located near the first end 1A of the manifold 1, although the liquid refrigerant will descend due to gravity, the smaller volume of the first cavity of the manifold 1 in this embodiment can better slow down the downward flow of the liquid refrigerant, making the gas-liquid refrigerant entering each heat exchange tube 1 more even, thereby ensuring the uniform distribution of refrigerant in the entire first cavity 13 of the manifold 1 and improving heat exchange efficiency.

[0071] When the connecting pipe 3 is positioned closer to the second end 1B relative to the first end 1A, the first opening 31 faces the direction from the second end 1B to the first end 1A. That is, when the connecting pipe 3 is near the lower part of the manifold 1, the first opening 31 faces upwards. This allows the refrigerant on the inlet side to flow towards a larger area within the first cavity 13, enabling better flow of the refrigerant within the first cavity 13 and resulting in a more uniform flow of refrigerant into the heat exchange tubes 2, thus improving the heat exchanger's distribution efficiency. When the connecting pipe 3 is located near the second end 1B of the manifold 1, the gaseous refrigerant will flow upwards, while the liquid refrigerant will descend due to gravity. However, the smaller volume of the first cavity of the manifold 1 in this embodiment increases the refrigerant flow rate, causing more liquid refrigerant to be sprayed upwards. This makes the gaseous and liquid refrigerant entering each heat exchange tube 1 more uniform, thereby ensuring the uniform distribution of refrigerant within the entire first cavity 13 of the manifold 1 and improving heat exchange efficiency.

[0072] In some embodiments, two or more connecting pipes 3 may be provided. The connecting pipes may be located at the upper, middle or lower part of the manifold 1. After the refrigerant enters the first cavity 13 of the manifold from the multiple connecting pipes, it flows into the nearby heat exchange tube 2 from the upper, middle or lower part of the manifold 1. This shortens the path of the refrigerant flow in the first cavity, making the gas-liquid refrigerant entering each heat exchange tube 1 more uniform, improving the distribution effect of the heat exchanger, and thus improving the heat exchange efficiency.

[0073] In some embodiments, the flow area of ​​the pipe 3 is S3, the flow area of ​​the first opening 31 is S4, and 0.5≤S4 / S3≤1.5.

[0074] Specifically, the flow area S3 of the connecting pipe 3 is the cross-sectional area of ​​the connecting pipe 3 in its radial direction, which is the flow area for refrigerant to flow into the connecting pipe 3. The flow area of ​​the first opening is S4, where 0.5 ≤ S4 / S3 ≤ 1.5. The first opening is located inside the first cavity 13 and is connected to the first cavity 13. The refrigerant flowing in from the connecting pipe 3 flows into the first cavity 13 of the manifold through the first opening. When S4 / S3 is less than 0.5, the flow area of ​​the first opening is smaller than that of the connecting pipe 3, resulting in too much flow resistance for the refrigerant inside the connecting pipe 3, which is not conducive to refrigerant flow. When S4 / S3 is greater than 1.5, the flow area of ​​the first opening 31 is too large, resulting in poor refrigerant injection and affecting the heat exchanger's heat exchange efficiency. Therefore, setting 0.5 ≤ S4 / S3 ≤ 1.5 ensures that the refrigerant flow velocity is within a suitable range when flowing from the connecting pipe 3 into the first cavity 13 of the manifold 1, which is beneficial to improving the heat exchanger's heat exchange efficiency.

[0075] The first opening 31 can be one, two, or more. When there is one first opening 31, the ratio of the flow area of ​​the first opening to the flow area of ​​the connecting pipe 3 is greater than or equal to 0.5 and less than or equal to 1.5. Alternatively, when there are two or more first openings 31, the ratio of the sum of the flow areas of the two or more first openings 31 to the flow area of ​​the connecting pipe 3 is greater than or equal to 0.5 and less than or equal to 1.5.

[0076] In some embodiments, the heat exchanger 100 further includes a second plate 5, the second plate 5 including a second hole 51 extending through the second plate 5, and at least a portion of the second plate 5 being located within the manifold 1.

[0077] like Figure 13 and Figure 14As shown, the heat exchanger 100 also includes a second plate 5, which includes a second hole 51 that penetrates the second plate 5. At least a portion of the second plate 5 is located inside the manifold 1. The second plate 5 with the second hole 51 is provided inside the heat exchanger 100. The second plate 5 can play a certain role in blocking the refrigerant, and the second hole 51 allows the refrigerant to still flow through the second hole 51 in the first cavity 13 of the manifold. Thus, the flow of the refrigerant in the first cavity 13 can be regulated by the second plate 5, so that the refrigerant can flow more evenly into each heat exchange tube 2, thereby improving the heat exchange effect of the heat exchanger.

[0078] Specifically, such as Figure 13 As shown, when the heat exchanger 100 is in operation, the refrigerant flows into the manifold 1 from the connecting pipe 3. The connecting pipe 1 is close to the upper part of the manifold 1. As the refrigerant flows downward, it passes through the second plate 5. The second plate 5 provides a certain degree of obstruction to the downward-flowing refrigerant, allowing it to flow slowly downward and preventing it from accumulating at the lower part of the manifold 1. The second plate 5 divides the first cavity 13 of the manifold into two or more sub-cavities that are connected along the length of the manifold 1. Thus, the refrigerant can flow from each sub-cavity into the corresponding heat exchange tube 2 to achieve heat exchange, making the gas-liquid refrigerant entering each heat exchange tube 1 more uniform, improving the uniform distribution of the refrigerant, and improving the heat exchange effect of the heat exchanger.

[0079] like Figure 14 As shown, when the heat exchanger 100 is in operation, the refrigerant flows into the manifold 1 from the connecting pipe 3. The connecting pipe 1 is close to the lower part of the manifold 1. As the refrigerant flows upward, it passes through the second plate 5. The second hole 51 of the second plate 5 has a certain spraying effect on the upward flowing refrigerant, which increases the flow rate of the refrigerant and prevents the refrigerant from accumulating in the lower part of the manifold 1. The second plate 5 divides the first cavity 13 of the manifold into two or more sub-cavities that are connected along the length of the manifold 1. Thus, the refrigerant can flow from each sub-cavity into the corresponding heat exchange tube 2 to achieve heat exchange, making the gas-liquid refrigerant entering each heat exchange tube 1 more uniform, improving the uniform distribution of the refrigerant, and improving the heat exchange effect of the heat exchanger.

[0080] In some embodiments, there are two or more second plates 5, and the heat exchanger 100 further includes a connecting pipe 3, which is connected to the manifold 1. The flow area of ​​the second hole 51 near the connecting pipe 3 is greater than or equal to the flow area of ​​the second hole 51 away from the connecting pipe 3, and / or the spacing between adjacent second plates 5 near the connecting pipe 3 is greater than or equal to the spacing between adjacent second plates 5 away from the connecting pipe 3.

[0081] Specifically, there are two or more second plates 5. The heat exchanger 100 includes a connecting pipe 3, which is connected to the manifold 1. When the heat exchanger is in operation, refrigerant flows into the manifold 1 from the connecting pipe 3. The flow area of ​​the second hole 51 near the connecting pipe 3 is larger than the flow area away from the second hole 51, and / or the spacing between adjacent second plates 5 near the connecting pipe 3 is larger than the spacing between adjacent second plates 5 away from the connecting pipe 3. The larger second hole 51 near the connecting pipe 3, or the larger spacing between adjacent second plates 5 near the connecting pipe 3, allows the refrigerant near the connecting pipe 3 to flow faster during the flow process, enabling the refrigerant to flow better into each heat exchange tube for heat exchange. The smaller second hole 51 away from the connecting pipe 3, or the smaller spacing between adjacent second plates 5, allows the refrigerant to have more force to block or spray, making the gas-liquid refrigerant entering each heat exchange tube 1 more uniform, improving the uniformity of refrigerant distribution, and thus improving the heat exchange efficiency.

[0082] like Figure 13 As shown, when the heat exchanger 100 is in operation, the connecting pipe 3 is located at the upper part near the manifold 1. The refrigerant flows into the manifold 1 from the connecting pipe 3. During the downward flow of the refrigerant, it passes through the second plate 5. The second plate 5 plays a certain role in blocking the downward flow of the refrigerant. The distance between adjacent second plates 5 located near the connecting pipe 3 is greater than the distance between adjacent second plates 5 located far from the connecting pipe 3. This makes the refrigerant at the second plate 5 located far from the connecting pipe 3 play a certain role in blocking the refrigerant during the downward flow of the refrigerant, resulting in a greater refrigerant velocity at that location. This makes the gas-liquid refrigerant entering each heat exchange tube 1 more uniform, improves the uniform distribution of the refrigerant, and improves the heat exchange effect of the heat exchanger.

[0083] like Figure 14 As shown, when the heat exchanger 100 is in operation, the connecting pipe 3 is located at the lower part near the manifold 1. The refrigerant flows into the manifold 1 from the connecting pipe 3. During the upward flow of the refrigerant, it passes through the second plate 5. The upward-flowing refrigerant generates a jetting effect through the second plate 5 with the second hole 51. The flow area of ​​the second hole 51 of the second plate 5 located near the connecting pipe 3 is larger than that of the second plate 5 located far from the connecting pipe 3. This allows the second plate 5 to exert a greater jetting effect on the flowing refrigerant at the position far from the connecting pipe 3, increasing the driving force for upward flow. This makes the gas-liquid refrigerant entering each heat exchange tube 1 more uniform, improves the uniform distribution of the refrigerant, and improves the heat exchange effect of the heat exchanger.

[0084] In some embodiments, there are two or more second plates 5, the flow area of ​​the second hole 51 near the connector 3 is equal to the flow area of ​​the second hole 51 away from the connector 3, and / or the spacing between adjacent second plates 5 near the connector 3 is equal to the spacing between adjacent second plates 5 away from the connector 3. The second plates 5 divide the first cavity 13 of the manifold into multiple sub-cavities that are connected along the length of the manifold 1, so that the refrigerant can flow from each sub-cavity into the corresponding heat exchange tube 2 to achieve heat exchange, making the gas-liquid refrigerant entering each heat exchange tube 1 more uniform, improving the uniform distribution of refrigerant, and improving the heat exchange effect of the heat exchanger.

[0085] Optionally, the structure of the second hole 51 can be set to a circular, triangular, polygonal, cross or other structure according to the actual application, and the second plate 5 can be set to one, two or more as needed, without any limitation.

[0086] In some embodiments, the heat exchanger 100 further includes a first plate 4, which is at least partially located within a first cavity 13. The first plate 4 divides the manifold 1 into at least two cavities, which are arranged adjacent to each other along the length of the manifold 1.

[0087] Specifically, such as Figure 15 As shown, the heat exchanger 100 includes a first plate 4, which is located in the first cavity 13 of the manifold 1. The first plate 4 divides the first cavity 13 into two adjacent cavities arranged along the length of the manifold 1. The two cavities are separated from each other, forming multiple refrigerant flow loops in the heat exchanger. This increases the flow path of the refrigerant in the heat exchanger, increases the heat exchange with the heat exchange tube 2, and improves the heat exchange effect. Furthermore, it reduces the height of a single flow path in the manifold 1, making the refrigerant mix more evenly in the cavity, and increasing the flow velocity of the refrigerant in a single cavity, further improving the heat exchange effect.

[0088] like Figure 15 As shown, the heat exchanger 100 includes two manifolds 1, and the heat exchange tubes 2 are connected to the two manifolds 1 at both ends along their length. The refrigerant flow path can be as follows: Figure 15 As shown by the arrows, the refrigerant flows into the heat exchanger 100 from the lower right connector 3. It first passes through the right manifold, then flows to the left through the heat exchange tube 2, then into the left manifold, then flows to the right through the heat exchange tube 2 again, and finally flows out from the left manifold. This forms multiple refrigerant flow loops, increasing the flow path of the refrigerant in the heat exchanger, increasing the heat exchange area, improving the heat exchange efficiency, and reducing the height of a single flow path in the manifold 1. The refrigerant mixes more evenly in the cavity, and the flow velocity of the refrigerant in a single cavity increases, further improving the heat exchange efficiency.

[0089] In heat exchanger applications, the arrangement of the first plate 4 can be adjusted according to the actual application. There can be only one first plate 4, or two or three. When two or more first plates 4 are set, the first cavity 13 can be divided into multiple cavities arranged adjacent to each other along the length of the manifold 1. These multiple cavities are spaced apart along the length of the manifold 1, forming more flow loops within the heat exchanger, increasing the flow area, and improving heat exchange efficiency. Of course, the first plate 4 can be set only in the left manifold, or only in the right manifold, or both the left and right manifolds can be equipped with the first plate 4. The specific arrangement depends on the situation and is not limited here.

[0090] In some embodiments, the heat exchanger 100 includes a first plate 4 and a second plate 5, wherein the second plate 5 includes a second hole 51 that penetrates through the second plate 5. That is, the heat exchanger can have both a first plate 4 and a second plate 5. The first plate 4 divides the manifold 1 into at least two independent cavities, forming multiple refrigerant flow loops. Within each independent cavity, a second plate 5 is provided, including a second hole 51. The second plate 5 with the second hole 51 further optimizes the refrigerant within the independent cavity, further improving the uniformity of refrigerant distribution within the first cavity 13, making the gas-liquid refrigerant entering each heat exchange tube 1 more uniform, and improving the heat exchange effect.

[0091] In some embodiments, the heat exchanger 100 further includes a third plate 7, and the manifold 1 has a first end 1A and a second end 1B in its length direction, with the third plate 7 disposed near the first end 1A and / or the second end 1B.

[0092] Specifically, such as Figure 16 As shown, the heat exchanger 100 also includes a third plate 7, which is located at the end of the manifold 1 along its length. The third plate can seal the end of the manifold 1 along its length. Near the first end 1A or the second end 1B, the manifold 1 includes a first recess 18. The first plate 7 can be inserted into the end of the manifold through the first recess 18 to achieve a sealing effect on the end of the manifold 1, which facilitates the processing of the manifold and improves the reliability of the manifold 1. After the first plate 7 is inserted into the end of the manifold 1, it is connected to the manifold 1 by welding.

[0093] Optionally, such as Figure 16 As shown, a protruding structure can be added to the end of the first plate 7. This protruding structure can increase the support points, improve the strength of the manifold, and make the contact with the manifold 1 tighter, resulting in better welding and improved reliability of the manifold.

[0094] Optionally, the first plate 4 or the second plate 5 can also be inserted into the manifold 1 and connected to the manifold in this manner, making the heat exchanger easier to manufacture. The first plate 4 and / or the second plate 5 can regulate the flow of refrigerant in the manifold 1, thereby improving the heat exchange efficiency of the heat exchanger.

[0095] In some embodiments, the heat exchanger 100 further includes fins 6, which can be welded to the heat exchange tubes 2. The fins 6 enhance the heat exchange between the heat exchanger 100 and the air, thereby improving the heat exchange performance of the heat exchanger. The fins 6 can be corrugated fins located between adjacent heat exchange tubes 2, or they can be horizontally inserted fins, flat fins, etc., spaced apart along the length of the heat exchange tubes 2, and there are no limitations on this.

[0096] 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 method 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 also fall within the protection scope of this application.

Claims

1. A heat exchanger, characterized by, The heat exchanger comprises: a heat exchange tube and a header, the header has a first cavity, the length direction of the heat exchange tube is defined as a first direction, the heat exchange tube is inserted into the header along the first direction, the direction perpendicular to the first direction and perpendicular to the length direction of the header is defined as a second direction, the maximum dimension W1 of the first cavity in the second direction is greater than the maximum dimension L1 of the first cavity in the first direction; the plane perpendicular to the length direction of the header is defined as a first plane, the projection area of the part of the heat exchange tube inserted into the first cavity in the first plane is S1, and the projection area of the first cavity in the first plane is S, wherein: 3 / 10≤S1 / S≤9 / 10.

2. The heat exchanger of claim 1, wherein The header comprises a first main body and a second main body, the tube wall enclosing the header comprises at least part of the first main body and at least part of the second main body, the first main body extends along the length direction of the header, and the second main body extends along the length direction of the header.

3. The heat exchanger of claim 2, wherein The first main body and the second main body are in a split structure, the header further comprises a reinforcing part, the reinforcing part is connected with the first main body and / or the second main body, the reinforcing part is integrally arranged with the first main body, or the reinforcing part is integrally arranged with the second main body, or the reinforcing part is arranged in a split structure with the first main body and the second main body.

4. The heat exchanger of claim 2, wherein The first main body and the second main body are in an integral structure.

5. The heat exchanger of claim 2, wherein The header further comprises a protruding part and a first hole, the protruding part is connected with the second main body, the first hole is located in the first main body, the heat exchange tube is inserted into the header along the first hole, and the end of part of the heat exchange tube abuts against the protruding part, the end of the heat exchange tube has a gap with the second main body.

6. The heat exchanger of claim 1, wherein The length of the part of the heat exchange tube inserted into the first cavity is L, and the hydraulic diameter of the heat exchange tube is W, wherein: 0.02W≤W1-W≤W, and / or, 0.1L≤L1-L≤L.

7. The heat exchanger according to any one of claims 1 to 6, characterized in that The heat exchanger further comprises a connecting pipe, the connecting pipe communicates with the header, the connecting pipe comprises a first opening, and the first opening is located on the side of the connecting pipe in the radial direction thereof.

8. The heat exchanger of claim 7, wherein The header has a first end and a second end in the length direction thereof, when the connecting pipe is close to the first end relative to the second end, the first opening faces the direction from the first end to the second end; when the connecting pipe is close to the second end relative to the first end, the first opening faces the direction from the second end to the first end.

9. The heat exchanger of claim 7, wherein The flow area of the connecting pipe is S3, the flow area of the first opening is S4, and 0.5≤S4 / S3≤1.

5.

10. The heat exchanger according to any one of claims 1-6, characterized in that The heat exchanger further comprises a second plate, the second plate comprises a second hole, the second hole penetrates through the second plate, and at least part of the second plate is located in the header.

11. The heat exchanger of claim 10, wherein The second plates are two or more, and the heat exchanger further comprises a connection pipe in communication with the header, the flow area of the second holes near the connection pipe is greater than or equal to the flow area of the second holes far from the connection pipe, and / or the distance between adjacent second plates near the connection pipe is greater than or equal to the distance between adjacent second plates far from the connection pipe.

12. The heat exchanger according to any one of claims 1-6, characterized in that The heat exchanger further comprises a first plate, which is at least partially located in the first cavity, and the first plate separates the header into at least two cavities, and the at least two cavities are arranged adjacent to each other along the length direction of the header. And / or, the heat exchanger further comprises a third plate, and the header has a first end and a second end in the length direction, and the third plate is arranged near the first end or the second end.

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