Heat exchanger

Abstract

The present application provides a heat exchanger, comprising heat exchange tubes and headers. Each header has a first cavity; the length direction of each heat exchange tube is defined as a first direction, and the heat exchange tubes are inserted into the headers 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, and 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; a plane perpendicular to the length direction of the header is defined as a first plane, the projected area of the part of each heat exchange tube inserted into the first cavity onto the first plane is S1, and the projected area of the first cavity onto the first plane is S, wherein: 3 / 10≤S1 / S≤9 / 10, reducing the internal volume of the header, thereby facilitating improvement of a heat exchange effect of the heat exchanger.

Description

heat exchanger Cross-reference of related applications

[0001] This application claims priority and benefit to Chinese patent applications with application numbers 202411920075.1 and 202423201876.0, filed on December 24, 2024, the entire contents of which are hereby incorporated by reference. Technical Field

[0002] This application relates to the field of heat exchange technology, specifically, to a heat exchanger applied in the field of HVACR (Heating, Ventilation, Air Conditioning and Refrigeration). Background Technology

[0003] In related technologies, a heat exchanger includes a manifold and heat exchange tubes. The ends of the heat exchange tubes are inserted into and connected to the manifold. The heat exchange tubes and manifold are used together. If a wider heat exchange tube is used to improve the heat exchanger's capacity, a larger diameter manifold must also be used. However, a larger diameter manifold will result in a larger internal volume. A larger internal volume of the manifold requires a larger refrigerant charge to ensure the heat exchanger's heat exchange capacity and will also affect the uniformity of refrigerant distribution. Summary of the Invention

[0004] An embodiment of the first aspect of this application provides a heat exchanger, including a heat exchange tube and a manifold. The manifold 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 manifold along the first direction. A direction perpendicular to both the first direction and the length direction of the manifold 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. A plane perpendicular to the length direction of the manifold is defined as a first plane. The projected area of ​​the portion of the heat exchange tube inserted into the first cavity on the first plane is S1, and the projected area of ​​the first cavity on the first plane is S, where: 3 / 10 ≤ S1 / S ≤ 9 / 10.

[0005] According to a second aspect of this application, a heat exchanger is provided, including a heat exchange tube and a manifold. The manifold has a first cavity. The length direction of the heat exchange tube is defined as a first direction, and the heat exchange tube is inserted into the manifold along the first direction. Directions perpendicular to both the first direction and the length direction of the manifold are defined as second directions. 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 heat exchanger further includes a first plate, a flow guide, and a connecting pipe. At least a portion of the first plate and at least a portion of the flow guide are located within the first cavity. The first plate divides the first cavity, which includes a first sub-cavity and a second sub-cavity. The flow guide connects the first sub-cavity and the second sub-cavity. At least a portion of the flow guide is located within the first cavity. The connecting pipe is connected to the first sub-cavity. A plane perpendicular to the length direction of the manifold is defined as a first plane. The projected area of ​​the portion of the heat exchange tube inserted into the first cavity on the first plane is S1. The projected area of ​​the flow guide on the first plane is S2. The projected area of ​​the first cavity on the first plane is S, where 2 / 5 ≤ (S1 + S2) / S ≤ 9 / 10. Attached Figure Description

[0006] Figure 1 is a schematic diagram of the structure of a heat exchanger according to an embodiment of this application.

[0007] Figure 2 is a partial structural schematic diagram of the heat exchanger according to an embodiment of this application.

[0008] Figure 3 is a partial structural schematic diagram of the heat exchanger according to an embodiment of this application.

[0009] Figure 4 is a partial structural schematic diagram of the heat exchanger according to an embodiment of this application.

[0010] Figure 5 is a partial structural schematic diagram of the heat exchanger according to an embodiment of this application.

[0011] Figure 6 is a partial structural schematic diagram of the heat exchanger according to an embodiment of this application.

[0012] Figure 7 is a partial structural schematic diagram of the heat exchanger according to an embodiment of this application.

[0013] Figure 8 is a partial structural schematic diagram of the heat exchanger according to an embodiment of this application.

[0014] Figure 9 is a partial structural schematic diagram of the heat exchanger according to an embodiment of this application.

[0015] Figure 10 is a partial structural schematic diagram of the heat exchanger according to an embodiment of this application.

[0016] Figure 11 is a partial structural schematic diagram of the heat exchanger according to an embodiment of this application.

[0017] Figure 12 is a schematic diagram of the pipe-connecting structure according to an embodiment of this application.

[0018] Figure 13 is a partial structural schematic diagram of the heat exchanger according to an embodiment of this application.

[0019] Figure 14 is a partial structural schematic diagram of the heat exchanger according to an embodiment of this application.

[0020] Figure 15 is a partial structural schematic diagram of the heat exchanger according to an embodiment of this application.

[0021] Figure 16 is a partial structural schematic diagram of the heat exchanger according to an embodiment of this application.

[0022] Figure 17 is a schematic diagram of the heat exchanger according to an embodiment of this application.

[0023] Figure 18 is a partial cross-sectional view of the heat exchanger according to an embodiment of this application.

[0024] Figure 19 is a partial structural schematic diagram of the heat exchanger according to an embodiment of this application.

[0025] Figure 20 is a partial cross-sectional view of the heat exchanger according to an embodiment of this application.

[0026] Figure 21 is a partial cross-sectional view of the heat exchanger according to an embodiment of this application.

[0027] Figure 22 is a partial cross-sectional view of the heat exchanger according to an embodiment of this application.

[0028] Figure 23 is a partial cross-sectional view of the heat exchanger according to an embodiment of this application.

[0029] Figure 24 is a partial cross-sectional view of the heat exchanger according to an embodiment of this application.

[0030] Figure 25 is a partial cross-sectional view of the heat exchanger according to an embodiment of this application.

[0031] Figure 26 is a partial cross-sectional view of the heat exchanger according to an embodiment of this application.

[0032] Figure 27 is a partial cross-sectional view of the heat exchanger according to an embodiment of this application.

[0033] Figure 28 is a partial structural schematic diagram of the heat exchanger according to an embodiment of this application.

[0034] Figure 29 is a partial structural schematic diagram of the heat exchanger according to an embodiment of this application.

[0035] Figure 30 is a partial structural schematic diagram of the heat exchanger according to an embodiment of this application.

[0036] Figure 31 is a partial structural schematic diagram of the heat exchanger according to an embodiment of this application.

[0037] Figure 32 is a partial cross-sectional view of the heat exchanger according to an embodiment of this application.

[0038] Figure 33 is a partial cross-sectional view of the heat exchanger in an embodiment of this application.

[0039] Figure 34 is a partial cross-sectional view of the heat exchanger according to an embodiment of this application.

[0040] Figure 35 is a partial cross-sectional view of the heat exchanger according to an embodiment of this application.

[0041] Reference numerals: Heat exchanger 100, manifold 1, first main body 11, second main body 12, first cavity 13, first sub-cavity 131, second sub-cavity 132, third sub-cavity 133, first hole 14, protrusion 15, reinforcing part 16, protrusion 17, first recess 18, first end 1A, second end 1B; Heat exchange tube 2, third end 2A, fourth end 2B, connecting pipe 3, first opening 31, first plate 4, flow guide 5, flow guide pipe 51, first pipe section 511, bend section 512, inner recess 513, second hole 514, flow guide plate 52, first connecting part 53, second connecting part 54; fin 6; third plate 7, second plate 8, third hole 81.

[0042] The accompanying drawings, which are incorporated in and form part of this specification, illustrate embodiments consistent with this application and, together with the description, serve to explain the principles of this application. Detailed Implementation

[0043] To better understand the technical solution of this application, the embodiments of this application will be described in detail below with reference to the accompanying drawings.

[0044] It should be understood that the described embodiments are merely a part of the technical solutions of this application, and not all of them. All other technical solutions obtained by those skilled in the art based on the technical solutions in this application without inventive effort are within the scope of protection of this application.

[0045] The terminology used in the embodiments of this application is for the purpose of describing particular embodiments only and is not intended to be limiting of this application. The singular forms “a,” “the,” and “the” used in the embodiments of this application and the appended claims are also intended to include the plural forms unless the context clearly indicates otherwise.

[0046] It should be understood that the term "and / or" used in this article is merely a description of the relationship between related objects, indicating that three relationships can exist. For example, A and / or B can represent: A existing alone, A and B existing simultaneously, and B existing alone. Additionally, the character " / " in this article generally indicates that the preceding and following related objects have an "or" relationship.

[0047] It should be noted that the directional terms such as "upper," "lower," "left," and "right" described in the embodiments of this application are used to describe the angles shown in the accompanying drawings and should not be construed as limiting the embodiments of this application. Furthermore, in the context, it should be understood that when it is mentioned that an element is connected "upper" or "lower" to another element, it can be directly connected to the other element "upper" or "lower," or indirectly connected to the other element "upper" or "lower" through an intermediate element.

[0048] The heat exchanger of an embodiment of this application is described below with reference to the accompanying drawings.

[0049] For heat exchangers in air conditioning systems that use refrigerant vapor compression cycles, the amount of refrigerant charged in the system depends on the internal volume of the heat exchanger. If the internal volume of the heat exchanger is too large, the amount of refrigerant charged will increase. Excessive refrigerant charge will lead to negative effects such as increased production costs and reduced safety factor. Therefore, reducing the internal volume while ensuring heat exchange performance is the key to heat exchanger design and structure.

[0050] This application provides a heat exchanger 100, which includes a heat exchange tube 2 and a manifold 1. The manifold 1 has a first cavity 13. The length direction of the heat exchange tube 2 is defined as a first direction. The heat exchange tube 2 is inserted into the manifold 1 along the first direction. The directions perpendicular to the first direction and the length direction of the manifold are defined as second directions. 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.

[0051] In some embodiments, a plane perpendicular to the length direction of the manifold is defined as a first plane, the projected area of ​​the heat exchange tube inserted into the first cavity on the first plane is S1, and the projected area of ​​the first cavity on the first plane is S, wherein: 3 / 10≤S1 / S≤9 / 10.

[0052] As shown in Figures 1-14, for ease of understanding, the first direction is the X direction in the figure, the second direction is the Y direction in the figure, and the length direction of manifold 1 is the Z direction in the figure. The first direction, the second direction and the length direction of manifold 1 are roughly perpendicular to each other. The plane perpendicular to the length direction of manifold is the first plane, and the first plane is parallel to the first direction and the second direction. The manifold 1 has a first cavity 13. The heat exchange tube 2 is inserted into the first cavity 13 of the manifold 1 along a first direction and is connected to the manifold 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 for the insertion of the heat exchange tube into the manifold 1. The length of the first cavity is the maximum length inside the cavity of the manifold 1. The dimension L1 of the first cavity 13 of the manifold 1 in the first direction where the heat exchange tube 2 is inserted is smaller than the dimension W1 in the second direction, which is beneficial for reducing the internal volume of the manifold 1 and increasing the refrigerant flow rate. The manifold 1 is generally flat. Compared with the traditional circular manifold structure, the internal volume of the first cavity 13 of the manifold is reduced. After the internal volume of the manifold 1 is reduced, the amount of refrigerant charged in the heat exchanger system is also reduced, which can reduce costs, make it more energy-efficient and environmentally friendly. Moreover, the reduction in the amount of refrigerant charged also improves the safety factor of the heat exchanger.

[0053] The heat exchange tube 2 is inserted into the first cavity 13 of the manifold 1 along the first direction. The projected area S1 of the portion of the heat exchange tube 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. Thus, after the heat exchange tube 2 is inserted into the manifold 1, the remaining cross-sectional area S-S1 in the first cavity 13, excluding the inserted heat exchange tube, is greater than or equal to 1 / 10 and less than or equal to 7 / 10. The remaining cross-sectional area S-S1 in the first cavity 13, excluding the inserted heat exchange tube, is defined as... The cross-sectional area is S5, where S5 = S - S1. S5 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 S5 in the first cavity 13 decreases, and the remaining volume in the first cavity 13 of the manifold 1 also decreases accordingly. The remaining volume in the first cavity 13 of the manifold 1 is the flow space of the refrigerant. Reducing the flow space of the refrigerant in the first cavity 13 of the manifold 1 results in a reduced flow space and increased flow velocity of the refrigerant in the first cavity when the heat exchanger is in operation. This makes the gas-liquid refrigerant mix more evenly in the first cavity, thus making the gas-liquid refrigerant entering each heat exchange tube 2 more uniform, which is beneficial to improving the heat exchange effect of the heat exchanger.

[0054] For example, the projected area S1 of the heat exchange tube 2 inserted into the first cavity 13 on the first plane is shown in Figure 6, and the cross-sectional area S5 of the refrigerant in the first cavity 13 is shown in Figure 6. The cross-sectional area S of the first cavity is the sum of the cross-sectional areas S1 and S5.

[0055] Understandably, when the projected area S1 of the heat exchange tube 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, when the projected area S1 of the heat exchange tube 2 inserted into the first cavity 13 on the first plane accounts for 1 / 4 of the cross-sectional area S of the first cavity, the remaining cross-sectional area S-S1 in the first cavity 13, excluding the inserted heat exchange tube, is 3 / 4. The remaining volume in the first cavity 13 of the manifold 1 is large, requiring more refrigerant charge. Furthermore, the refrigerant has a large flow space in the first cavity 13, resulting in a low refrigerant flow rate. The gas and liquid refrigerants are more easily separated in the first cavity 13, making it difficult to form a large flow rate to ensure uniform mixing of the refrigerant in the first cavity 13, thus affecting the heat exchange effect of the heat exchanger.

[0056] The projected area S1 of the portion of the heat exchange tube 2 inserted into the first cavity 13 on 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 portion of the heat exchange tube 2 inserted into the first cavity 13 on the first plane is greater than 9 / 10 of the cross-sectional area S of the first cavity, the remaining cross-sectional area S5 in the first cavity is less than 1 / 10. The flow space of the refrigerant in the first cavity 13 is very small. At this time, the flow resistance of the refrigerant increases, which is not conducive to the flow of the refrigerant in the first cavity 13. The gas-liquid refrigerant cannot be uniformly mixed in the first cavity 13, which is not conducive to the uniformity of refrigerant distribution and affects the heat exchange effect of the heat exchanger.

[0057] Therefore, setting 3 / 10≤S1 / S≤9 / 10 means that the projected area S1 of the heat exchange tube 2 inserted into the first cavity 13 on 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 on the first plane. This makes the remaining cross-sectional area S-S1 in the first cavity 13, excluding the inserted heat exchange tube, greater than or equal to 1 / 10 and less than or equal to 7 / 10. This ensures that the refrigerant flow space in the first cavity is within a suitable range, preventing the flow velocity from being too low due to excessive flow space and the flow resistance from being too high due to insufficient flow space. Within this range, the flow velocity of the refrigerant increases, and the gas-liquid two-phase refrigerant mixes more evenly in the first cavity. This makes the gas-liquid refrigerant entering each heat exchange tube more uniform, which is beneficial to improving the heat exchange effect of the heat exchanger.

[0058] According to the heat exchanger of this application, on the one hand, the heat exchange tubes are inserted into the manifold along the first direction, and the maximum dimension W1 of the first cavity of the manifold in the second direction is greater than the maximum dimension L1 in the first direction, which helps to reduce the internal volume of the first cavity of the manifold and reduce the refrigerant charge of the heat exchanger; on the other hand, the projected area S1 of the heat exchange tubes inserted into the first cavity in the first plane is greater than or equal to 3 / 10 of the projected area S of the first cavity in the first plane, which reduces the remaining cross-sectional area in the first cavity and the remaining volume in the first cavity accordingly. The flow space of the refrigerant in the first cavity is reduced, the flow velocity is increased, and the gas-liquid two-phase refrigerant is mixed more evenly in the first cavity. Furthermore, S1 / S≤9 / 10 ensures that the remaining cross-sectional area in the first cavity is not too small and thus does not increase the flow resistance. Therefore, the flow space of the refrigerant in the first cavity is within a suitable range, the flow velocity of the refrigerant is increased, and the gas-liquid two-phase refrigerant is mixed 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.

[0059] When the heat exchanger 100 is used, if it is placed vertically or inclined along the length of the manifold 1, the gaseous refrigerant will flow upward and the liquid refrigerant will descend due to gravity. Since the internal volume of the manifold 1 in this application is reduced, the refrigerant flow space is reduced, the flow velocity is increased, and the gravitational influence of the liquid refrigerant is reduced. Furthermore, by setting 3 / 10≤S1 / S≤9 / 10, the flow space of the refrigerant in the first cavity is within a suitable range. The flow velocity will not be too low due to excessive flow space, nor will the flow resistance be too high due to insufficient flow space. With the flowable space in the first cavity 13 within this range, the flow velocity of the refrigerant increases, making the gas and liquid refrigerants mix more evenly in the first cavity. This makes the gas and liquid refrigerants entering each heat exchange tube more uniform, improving the uniformity of refrigerant distribution in the entire heat exchanger and improving the heat exchange effect of the heat exchanger.

[0060] The heat exchanger provided in this application reduces the internal volume of the manifold, which helps to improve the heat exchange efficiency of the heat exchanger.

[0061] In some embodiments, as shown in Figures 1-9 and 18, the manifold 1 includes a first main body 11 and a second main body 12, and the wall surrounding the manifold 1 includes at least a portion of the first main body 11 and at least a portion of the second main body 12. The first main body 11 extends along the length direction of the manifold 1, and the second main body 12 extends along the length direction of the manifold 1.

[0062] In some embodiments, the first main body 11 and the second main body 12 are an integral structure; or, the first main body 11 and the second main body 12 are separate structures.

[0063] Specifically, as shown in Figures 1-9, the manifold 1 includes a first main body 11 and a second main body 12. The wall surrounding the manifold 1 includes at least a portion of the first main body 11 and at least a portion of the second main body 12. The at least a portion of the first main body 11 and at least a portion of the second main body 12 surround and form the wall of the manifold 1, and surround and form the first cavity 13 of the manifold 1. The first main body 11 extends along the length direction of the manifold 1, and the second main body 12 extends along the length direction of the manifold 1.

[0064] In some embodiments, as shown in Figures 1-9, 18, 21-22, 24, 27 and 32, the first main body 11 and the second main body 12 are separate structures. The connection between the first main body 11 and the second main body 12 includes a reinforcing part 16. The reinforcing part 16 is connected to the first main body and / or the second main body. The reinforcing part 16 is integrally formed with the first main body 11, or integrally formed with the second main body 12, or separate from the first main body 11 and the second main body 12.

[0065] In some embodiments, the first main component 11 and the second main component 12 are separate structures, that is, the first main component 11 and the second main component 12 are two separate parts, and at least a portion of the first main component 11 and at least a portion of the second main component 12 enclose the pipe wall of the manifold 1. When the first main component 11 and the second main component 12 are separate structures, the manifold 1 is easier to process. The manifold 1 also includes a reinforcing part 16, which is connected to the first main component 11 and / or the second main component 12. Since the first main component 11 and the second main component 12 are separate structures, and the manifold 1 is used in a heat exchanger, with refrigerant flowing inside the pipe cavity, if a leak occurs at the connection between the first main component 11 and the second main component 12, it will cause refrigerant leakage in the manifold 1, affecting the reliability and heat exchange effect of the heat exchanger. By providing the reinforcing part 16, the strength of the connection between the first main component 11 and the second main component 12 is increased, thereby improving the reliability of the heat exchanger.

[0066] Specifically, as shown in Figures 2-5, 8-9, 18, 21-22, 24, 27, and 32, the first main body 11 and the second main body 12 are separate structures. The manifold 1 also includes a reinforcing part 16, which is integrally formed with the first main body 11 or the second main body 12. The reinforcing part 16 can be a part of the first main body 11 or a part of the second main body 12. By forming the reinforcing part 16 by overlapping the first main body 11 and the second main body 12 at the connection point by a certain length, the structure at the connection point of the first main body 11 and the second main body 12 is strengthened, the strength of the manifold 1 at the connection point of the first main body 11 and the second main body 12 is improved, the reliability of the manifold 1 is improved, and the processing is more convenient.

[0067] Specifically, in Figures 2, 3, 8, 18, and 24, the reinforcing part 16 is integrally formed with the first main body 11, or with the second main body 12. A portion of the first main body 11 and a portion of the second main body 12 overlap by a certain length in a first direction, thus forming the reinforcing part 16. In Figures 4 and 9, the first main body 11 of the manifold includes straight segments and curved segments, and the second main body 12 has an arc-shaped structure. The first main body 11 includes a reinforcing part 16 that bends towards the second main body 12 to increase the strength at the connection between the first and second main body 11. In Figure 5, the first main body 11 of the manifold 1 has an arc-shaped structure, and the second main body 12 of the manifold 1 includes straight segments. The second main body 12 includes a reinforcing part 16 that bends towards the first main body 11 to increase the strength at the connection between the first and second main body 11, improving the strength and reliability of the manifold and making processing easier.

[0068] In some embodiments, the reinforcing part 16 is separately provided from the first main body 11 and the second main body 12. That is, the reinforcing part 16 can also be provided independently, and is not an integral structure with the first main body 11 and the second main body 12. For example, an annular reinforcing part 16 or a snap-fit ​​reinforcing part 16 is provided on the outer periphery of the first main body 11 and the second main body 12, so that the connection between the first main body 11 and the second main body 12 is more secure, thereby improving the strength of the manifold 1.

[0069] In some embodiments, the first main body 11 and the second main body 12 are integral structures, as shown in Figures 6-7 and 20 and 25. When the first main body 11 and the second main body 12 are integral structures, the pipe wall surrounding the manifold 1 includes the first main body 11 and the second main body 12. When the first main body 11 and the second main body 12 are integrally arranged, the manifold 1 has greater pressure resistance, reduces the risk of leakage in the manifold 1, and improves the reliability of the heat exchanger 100. Optionally, when the first main body 11 and the second main body 12 are integral structures, the manifold 1 can be formed by extrusion, drawing, or other methods, which are not limited here.

[0070] In some embodiments, the general structure of the manifold 1 can be rectangular, D-shaped, elliptical, quadrilateral, or irregular in shape, and no limitation is made here.

[0071] In some embodiments, the manifold 1 includes a protrusion 15 and a first hole 14. The protrusion 15 is connected to the second body member 12, and the first hole 14 is located in the first body member 11. The heat exchange tube 2 is inserted into the manifold along the first hole 14, and a portion of the end of the heat exchange tube 2 abuts against the protrusion 15. The end of the heat exchange tube 2 has a gap with the second body member 12.

[0072] Specifically, as shown in Figures 7 and 8, the manifold 1 includes a protrusion 15 connected to the second main body 12. A first hole 14 is located in the first main body 11. The heat exchange tube 2 is inserted into the first cavity 13 of the manifold 1 from near the first main body 11 along the first hole 14. The end of the heat exchange tube 2 abuts against the protrusion 15. The protrusion 15 can limit the insertion of the heat exchange tube 2 into the manifold 1, allowing the heat exchange tube 2 to be inserted deeper into the manifold 1, reducing the remaining volume in the manifold 1 to a greater extent, reducing the flow space of the refrigerant in the first cavity, increasing the flow rate of the refrigerant, and making the refrigerant mix more evenly in the first cavity. At the same time, the end of the heat exchange tube 2 has a predetermined gap with the second main body 12, so that the heat exchange tube 2 inserted into the manifold 1 has a certain space to communicate with the first cavity 13, and the refrigerant flowing in or out from the end of the heat exchange tube 2 can better flow with the first cavity 13 of the manifold 1, ensuring the heat exchange effect of the heat exchanger.

[0073] In some embodiments, the protrusion 15 is located within the first cavity 13, which can further reduce the flow space of the refrigerant within the first cavity 13, increase the refrigerant flow rate, and make the refrigerant mix more evenly within the first cavity, thereby improving the heat exchange effect of the heat exchanger.

[0074] Optionally, the protrusion 15 can be a plate-like structure as shown in Figure 7, or multiple wavy shapes as shown in Figure 8, or other forms, which are not limited here, as long as they can serve as a limit and there is a certain gap between the end of the heat exchange tube 2 and the second main body 12.

[0075] Optionally, the protrusion 15 can be an integral structure with the second main body 12, which makes processing easier, or it can be a separate structure from the second main body 12. No limitation is made here.

[0076] In some embodiments, the first main body 11 and the second main body 12 can be configured in various ways. At least a portion of the first main body 11 includes a straight segment, and at least a portion of the second main body 12 includes an arc segment; or, at least a portion of the first main body 11 includes an arc segment, and at least a portion of the second main body 12 includes a straight segment; or, at least a portion of the first main body 11 includes a straight segment, and at least a portion of the second main body 12 includes a straight segment, wherein the straight segment includes two or more straight segments, and the pipe wall surrounding the manifold 1 includes multiple straight segments; or, at least a portion of the first main body 11 includes an arc segment, and at least a portion of the second main body 12 includes an arc segment.

[0077] Specifically, as shown in Figures 2, 3, and 6-8, 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.

[0078] As shown in Figure 4, the first main component 11 includes straight segments, and at least a portion of the second main component 12 includes curved segments, forming a generally D-shaped manifold 1. As shown in Figure 5, at least a portion of the first main component 11 includes curved segments, and the second main component 12 includes straight segments, forming a generally D-shaped manifold 1. As shown in Figure 9, at least a portion of the first main component 11 includes both straight and curved segments, and the second main component 12 includes both straight and curved segments, forming an irregular manifold 1 structure. As shown in Figure 10, at least a portion of the first main component 11 includes curved segments, and at least a portion of the second main component 12 includes curved segments, forming a generally elliptical manifold 1 enclosed by the first and second main components 11.

[0079] 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.

[0080] 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.

[0081] As shown in Figure 3, 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, and the hydraulic diameter of the heat exchange tube 2 is W, that is, 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 1 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.

[0082] 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 2 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 is such that the flow rate is not too low due to excessive flow space of the refrigerant, nor is the flow resistance too high due to insufficient flow space of 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.

[0083] 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.

[0084] 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.

[0085] As shown in Figures 11 and 12, the heat exchanger 100 also includes a connecting pipe 3, which is connected to the manifold 1 and communicates with the first cavity 13 of the manifold 1. The connecting pipe 3 includes an inlet pipe and an outlet pipe, used for refrigerant to flow into or out of the heat exchanger 100, realizing the connection between the heat exchanger 100 and other components, and achieving heat exchange through the inflow or outflow of refrigerant. It can be understood that the inlet and outlet pipes of the heat exchanger are reversed in evaporator and condenser operating conditions; the inlet pipe in evaporator operating condition is the outlet pipe in condenser operating condition, and vice versa. When the heat exchanger 100 is used, the position of the inlet pipe and the opening position on the pipe affect the refrigerant flow position and direction when the refrigerant flows into the heat exchanger 100. Therefore, the position of the inlet pipe and the opening position have a more significant impact on the heat exchange effect of the heat exchanger.

[0086] The connecting pipe 3 includes a first opening 31, which is located on the radial side of the connecting pipe 3, particularly at the inlet connecting pipe. When the heat exchanger 100 is in operation, when refrigerant flows into the heat exchanger 100, it first flows into the manifold 1 through the connecting pipe 3. Since the internal volume of the manifold 1 is reduced in this application, the flow space within the manifold 1 is reduced. When the end of the connecting pipe opening is directly opposite the pipe wall of the manifold 1, it increases the difficulty of refrigerant flow along the length of the manifold. Therefore, the opening of the connecting pipe 3 is located on the radial side of the connecting pipe 3. Thus, the connecting pipe 3 can communicate with the manifold 1 through the first opening 31 located on its radial side. Refrigerant can flow in or out from the first opening 31, which is connected to the first cavity 13. By changing the outflow direction of the inlet refrigerant, the difficulty of refrigerant flow is reduced, allowing the refrigerant to flow better within the first cavity 13, thereby improving the heat exchange effect of the heat exchanger.

[0087] As shown in Figure 12, there can be two first openings 31, which are arranged along the circumference of the pipe 3. Of course, there can also be one first opening 31 or multiple first openings 31. Multiple first openings 31 can be arranged at intervals along the axial direction of the pipe 3 or at intervals along the circumference of the pipe 3. The specific arrangement depends on the structure and application of the heat exchanger and is not limited here.

[0088] Understandably, depending on the actual application, the opening of the pipe 3 can be set at the axial end of the pipe 3, or the opening can be set at both the axial end of the pipe 3 and the radial end of the pipe 3, to improve the flow of refrigerant in the first cavity 13 of the manifold and improve the uniformity of refrigerant distribution.

[0089] 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.

[0090] As shown in Figure 11, 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.

[0091] As shown in Figure 19, when the position of the connecting pipe 3 is closer to the second end 1B than 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 close to the lower part of the manifold 1, the first opening 31 faces upward, so that the refrigerant on the inlet side can flow towards a position with more flow space in the first cavity 13, so that the refrigerant on the inlet side can flow better in the first cavity 13, and so that the refrigerant flows into the heat exchange tube 2 more evenly, thereby improving the heat exchange effect of the heat exchanger.

[0092] 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 more 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 2 more even, thereby ensuring the uniform distribution of refrigerant in the entire first cavity 13 of the manifold 1 and improving heat exchange efficiency.

[0093] 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 position with more space 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 distribution effect of the heat exchanger. 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 can increase the refrigerant flow rate, causing more liquid refrigerant to be sprayed upwards. This makes the gaseous and liquid refrigerant entering each heat exchange tube 2 more uniform, thereby ensuring the uniform distribution of refrigerant in the entire first cavity 13 of the manifold 1 and improving heat exchange efficiency.

[0094] 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 2 more uniform, improving the distribution effect of the heat exchanger, and thus improving the heat exchange efficiency.

[0095] 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.

[0096] 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.

[0097] 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.

[0098] In some embodiments, the heat exchanger 100 further includes a second plate 8, the second plate 8 including a third hole 81 extending through the second plate 8, and at least a portion of the second plate 8 being located within the manifold 1.

[0099] As shown in Figures 13 and 14, the heat exchanger 100 also includes a second plate 8, which includes a third hole 81 that penetrates the second plate 8. At least a portion of the second plate 8 is located inside the manifold 1. The second plate 8 with the third hole 81 installed inside the heat exchanger 100 can provide some obstruction to the refrigerant, while the third hole 81 allows the refrigerant to still flow through the third hole 81 in the first cavity 13 of the manifold. Thus, the second plate 8 can regulate the flow of the refrigerant in the first cavity 13, enabling the refrigerant to flow more evenly into each heat exchange tube 2 and improving the heat exchange efficiency of the heat exchanger.

[0100] Specifically, as shown in Figure 13, when the heat exchanger 100 is in operation, the refrigerant flows from the connecting pipe 3 into the manifold 1. The connecting pipe 3 is close to the upper part of the manifold 1. As the refrigerant flows downward, it passes through the second plate 8. The second plate 8 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 8 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 2 more uniform, improving the uniform distribution of the refrigerant, and improving the heat exchange effect of the heat exchanger.

[0101] As shown in Figure 14, when the heat exchanger 100 is in operation, the refrigerant flows into the manifold 1 from the connecting pipe 3. The connecting pipe 3 is close to the lower part of the manifold 1. As the refrigerant flows upward, it passes through the second plate 8. The third hole 81 of the second plate 8 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 8 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 2 more uniform, improving the uniform distribution of the refrigerant, and improving the heat exchange effect of the heat exchanger.

[0102] In some embodiments, there are two or more second plates 8, and the heat exchanger 100 further includes a connecting pipe 3, which is connected to the manifold 1. The flow area of ​​the third hole 81 near the connecting pipe 3 is greater than or equal to the flow area of ​​the third hole 81 away from the connecting pipe 3, and / or the spacing between adjacent second plates 8 near the connecting pipe 3 is greater than or equal to the spacing between adjacent second plates 8 away from the connecting pipe 3.

[0103] Specifically, there are two or more second plates 8. 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 third hole 81 near the connecting pipe 3 is larger than the flow area away from the third hole 81, and / or the spacing between adjacent second plates 8 near the connecting pipe 3 is larger than the spacing between adjacent second plates 8 away from the connecting pipe 3. The larger third hole 81 near the connecting pipe 3, or the larger spacing between adjacent second plates 8 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 third hole 81 away from the connecting pipe 3, or the smaller spacing between adjacent second plates 8, allows the refrigerant to have more force to block or spray, making the gas-liquid refrigerant entering each heat exchange tube 2 more uniform, improving the uniformity of refrigerant distribution, and thus improving the heat exchange efficiency.

[0104] As shown in Figure 13, 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 8. The second plate 8 plays a certain role in blocking the downward flow of the refrigerant. The distance between adjacent second plates 8 located near the connecting pipe 3 is greater than the distance between adjacent second plates 8 located far from the connecting pipe 3. This makes the refrigerant at the second plate 8 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 2 more uniform, improves the uniform distribution of the refrigerant, and improves the heat exchange effect of the heat exchanger.

[0105] As shown in Figure 14, 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 8. The upward-flowing refrigerant generates a jetting effect through the second plate 8 with the third hole 81. The flow area of ​​the third hole 81 of the second plate 8 located near the connecting pipe 3 is larger than that of the third hole 81 of the second plate 8 located away from the connecting pipe 3. This makes the second plate 8 exert a greater jetting effect on the flowing refrigerant at the position away from the connecting pipe 3, increasing the driving force for upward flow. This makes the gas-liquid refrigerant entering each heat exchange tube 2 more uniform, improves the uniform distribution of refrigerant, and improves the heat exchange effect of the heat exchanger.

[0106] In some embodiments, there are two or more second plates 8, the flow area of ​​the third hole 81 near the connector 3 is equal to the flow area of ​​the third hole 81 away from the connector 3, and / or the spacing between adjacent second plates 8 near the connector 3 is equal to the spacing between adjacent second plates 8 away from the connector 3. The second plates 8 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 2 more uniform, improving the uniform distribution of refrigerant, and improving the heat exchange effect of the heat exchanger.

[0107] Optionally, the structure of the third hole 81 can be set to a circular, triangular, polygonal, cross or other structure according to the actual application, and the second plate 8 can be set to one, two or more as needed, without any restrictions.

[0108] 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.

[0109] Specifically, as shown in Figure 15, 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.

[0110] As shown in Figure 15, the heat exchanger 100 includes two manifolds 1. The heat exchange tubes 2 are connected to the two manifolds 1 at both ends along their length. The refrigerant flow path can be shown by the arrow in Figure 15. After the refrigerant flows into the heat exchanger 100 from the lower right pipe 3, it first passes through the right manifold, flows to the left through the heat exchange tube 2, then enters the left manifold, flows to the right through the heat exchange tube 2, flows into the right manifold again, flows to the left through the heat exchange tube 2, 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 of the heat exchanger, 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.

[0111] 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, only in the right manifold, or in both the left and right manifolds. The specific setting depends on the situation and is not limited here.

[0112] In some embodiments, the heat exchanger 100 includes a first plate 4 and a second plate 8, wherein the second plate 8 includes a third hole 81 that penetrates through the second plate 8. That is, the heat exchanger can have both a first plate 4 and a second plate 8. 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 8 is provided, including a third hole 81. The second plate 8 with the third hole 81 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 2 more uniform, and improving the heat exchange effect.

[0113] 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.

[0114] Specifically, as shown in Figure 16, 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 third 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 its reliability. After the third plate 7 is inserted into the end of the manifold 1, it is connected to the manifold 1 by welding.

[0115] Optionally, as shown in Figure 16, a protruding structure can be added to the end of the third plate 7. This protruding structure can increase the support points, improve the strength of the manifold, and make closer contact with the manifold 1, resulting in better welding and improved reliability of the manifold.

[0116] Optionally, the first plate 4 or the second plate 8 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 8 can regulate the flow of refrigerant in the manifold 1, thereby improving the heat exchange efficiency of the heat exchanger.

[0117] 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.

[0118] This application embodiment also proposes a heat exchanger 100, including a heat exchange tube 2 and a manifold 1. The manifold 1 has a first cavity 13. The length direction of the heat exchange tube 2 is defined as a first direction. The heat exchange tube 2 is inserted into the manifold 1 along the first direction. The directions perpendicular to the first direction and the length direction of the manifold 1 are defined as second directions. 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. The plane perpendicular to the length direction of the manifold 1 is defined as a first plane. The projected area S1 of the portion of the heat exchange tube 1 inserted into the first cavity 13 in the first plane is S. The projected area S of the first cavity in the first plane is S, where: 3 / 10 ≤ S1 / S ≤ 9 / 10. The heat exchanger 100 also includes a first plate 4, a flow guide 5, and a connecting pipe 3. At least a portion of the first plate 4 is located inside the first cavity 13. The first plate 13 divides the first cavity 13. The first cavity 13 includes a first sub-cavity 131 and a second sub-cavity 132. The flow guide 5 connects the first sub-cavity 131 and the second sub-cavity 132. At least a portion of the flow guide 5 is located outside the first cavity 13. The connecting pipe 3 is connected to the first sub-cavity 131.

[0119] Specifically, as shown in Figures 31-32, for ease of understanding, the first direction is the X direction, the second direction is the Y direction, and the length direction of manifold 1 is the Z direction. The first direction, the second direction, and the length direction of manifold 1 are generally perpendicular to each other. Manifold 1 has a first cavity 13, and the heat exchange tube is inserted into the first cavity 13 of manifold 1 along the first direction and communicates with manifold 1. Optionally, manifold 1 includes a first hole 14, and the heat exchange tube 2 is inserted into manifold 1 along the first hole 14. 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 for the insertion of the heat exchange tube into manifold 1. The maximum dimension of the first cavity is the maximum length of the manifold 1 in the first and second directions. The maximum dimension L1 of manifold 1 in the first direction when the heat exchange tube 2 is inserted is less than the maximum dimension W1 of manifold 1 in the second direction, which is beneficial for reducing the internal volume of manifold 1. Manifold 1 is generally flat.

[0120] The heat exchange tube 2 is inserted into the first cavity 13 of the manifold 1 along the first direction. The projected area of ​​the portion of the heat exchange tube 2 inserted into the first cavity 13 on the first plane is S1, and the projected area of ​​the first cavity on the first plane is S. 3 / 10 ≤ S1 / S ≤ 9 / 10, that is, S1 is greater than or equal to 3 / 10 of S and less than or equal to 9 / 10 of S. For example, S1 / S can be 0.4, 0.5, 0.55, 0.6, 0.7, 0.8, 0.9, etc., such that 1 / 10 ≤ (S-S1) / S ≤ 7 / 10. In other words, after the heat exchange tube 2 is inserted into the manifold 1, the remaining projected area S-S1 in the first cavity 13, excluding the inserted heat exchange tube, is... The remaining projected area S-S1 in the first cavity 13 is greater than or equal to 1 / 10 and less than or equal to 7 / 10, which is the flowable area of ​​the refrigerant in the first cavity. When S1 / S is greater than or equal to 3 / 10, the remaining projected area in the first cavity 13 decreases, and the remaining internal volume in the first cavity 13 of the manifold 1 decreases accordingly. The remaining internal volume in the first cavity 13 of the manifold 1 is the flow space of the refrigerant. The flow space of the refrigerant in the first cavity decreases, and the flow rate of the refrigerant increases, so that the gas-liquid refrigerant is mixed more evenly in the first cavity, thereby making the gas-liquid refrigerant entering each heat exchange tube 1 more uniform and improving the heat exchange effect of the heat exchanger.

[0121] Understandably, when the projected area S1 of the heat exchange tube 2 inserted into the first cavity 13 on the first plane is less than 3 / 10 of the projected area S of the first cavity on the first plane, for example, when the projected area S1 of the heat exchange tube 2 inserted into the first cavity 13 on the first plane accounts for 1 / 5 of the cross-sectional area S of the first cavity, the remaining projected area S-S1 in the first cavity 13, excluding the inserted heat exchange tube, is 4 / 5. The remaining volume in the first cavity 13 of the manifold 1 is large, requiring more refrigerant charge. Furthermore, the refrigerant has a large flow space in the first cavity 13, resulting in a low refrigerant flow rate. The gas and liquid refrigerants are more easily separated in the first cavity 13, making it difficult to form a large flow rate to ensure uniform mixing of the refrigerant in the first cavity 13, thus affecting the heat exchange effect of the heat exchanger.

[0122] The projected area S1 of the portion of the heat exchange tube 2 inserted into the first cavity 13 on the first plane is less than or equal to 9 / 10 of the projected area S of the first cavity on the first plane. When the projected area S1 of the portion of the heat exchange tube 2 inserted into the first cavity 13 on the first plane is greater than 9 / 10 of the projected area S of the first cavity on the first plane, the remaining cross-sectional area in the first cavity is less than 1 / 10. The flow space of the refrigerant in the first cavity 13 is very small. At this time, the flow resistance of the refrigerant increases, which is not conducive to the flow of the refrigerant in the first cavity 13. The gas-liquid refrigerant cannot be uniformly mixed in the first cavity 13, which is not conducive to the uniformity of refrigerant distribution and affects the heat exchange effect of the heat exchanger.

[0123] Therefore, the projected area S1 of the heat exchange tube 2 inserted into the first cavity 13 on the first plane is set to be 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. This makes the remaining projected area S-S1 in the first cavity 13, excluding the inserted heat exchange tube, greater than 1 / 10 and less than 7 / 10. This ensures that the refrigerant flow space in the first cavity is within a suitable range, preventing the flow velocity from being too low due to excessive flow space and the flow resistance from being too high due to insufficient flow space. Within this range, the refrigerant flow velocity increases, and the gas-liquid two-phase refrigerant mixes more evenly in the first cavity. This makes the gas-liquid refrigerant entering each heat exchange tube 1 more uniform, which is beneficial to improving the heat exchange effect of the heat exchanger.

[0124] As shown in Figure 31, the heat exchanger 100 also includes a first plate 4, a flow guide 5, and a connecting pipe 3. The connecting pipe 3 can be an inlet connecting pipe. At least part of the first plate 4 is located inside the first cavity 13. The first plate 4 divides the first cavity 13 into a first sub-cavity 131 and a second sub-cavity 132. The first sub-cavity 131 and the second sub-cavity 132 are arranged adjacent to each other along the length direction of the manifold 1. The flow guide 5 connects the first sub-cavity 131 and the second sub-cavity 132. At least part of the flow guide 5 is located outside the first cavity 13. The connecting pipe 3 is connected to the first sub-cavity 131.

[0125] Since the flow guide 5 is located outside the first cavity 13, the position of the flow guide 5 does not need to be considered when designing the manifold 1. The first cavity of the manifold 1 can be set smaller, reducing the internal volume of the manifold 1 and increasing the refrigerant flow rate.

[0126] When the heat exchanger 100 is used and is vertically installed along the length of the manifold 1, the first sub-cavity 131 is located at the upper part of the length direction of the manifold 1, and the second sub-cavity is located at the lower part of the length direction of the manifold 1. After the refrigerant enters the first sub-cavity 131 through the connecting pipe 3, some of the refrigerant flows into the heat exchange tube 2 for heat exchange. Since the first sub-cavity 131 is located at the upper part, there is more gaseous refrigerant in the upper part of the first sub-cavity 131 after entering it. Through the guide 5, some of the gaseous refrigerant flows into the second sub-cavity 132. As a result, the liquid refrigerant in the lower part of the first sub-cavity 131 can more easily enter the upper part of the first sub-cavity 131, thus distributing the refrigerant within the first sub-cavity 131. The refrigerant flowing into the second sub-cavity 132 through the guide member 5 is further distributed within the second sub-cavity 132. The guide member 5 forms a refrigerant flow circulation within the first and second sub-cavities 131 and 132, thereby making the distribution of the refrigerant within the first and second sub-cavities 131 and 132 more uniform. Furthermore, due to the reduced internal volume of the manifold 1 in this application, the flow space within the first cavity 13 is reduced, resulting in a higher refrigerant flow rate and more uniform mixing of the gas-liquid two-phase refrigerant within the first cavity. This allows the refrigerant to flow more quickly within the first and second sub-cavities 131 and 132, resulting in a more uniform gas-liquid refrigerant entering each heat exchange tube. This further improves the uniformity of refrigerant distribution in the heat exchanger and enhances the heat exchange effect of the heat exchanger.

[0127] In this embodiment, the maximum dimension of the manifold 1 in the second direction is greater than the maximum dimension in the first direction, making the manifold generally flat. This reduces the internal volume of the manifold, which helps to reduce the refrigerant flow space within the manifold 1. Furthermore, 3 / 10 ≤ S1 / S ≤ 9 / 10. By setting the flow area within the first cavity of the manifold, the flow space of the refrigerant within the first cavity 13 is kept within a suitable range, increasing the refrigerant flow velocity within the first cavity and making the refrigerant mix more uniformly within the first cavity. Moreover, the flow guide forms a refrigerant flow circulation within the first and second sub-cavities, making the refrigerant distribution within the first and second sub-cavities more uniform. This results in a more uniform gas-liquid refrigerant entering each heat exchange tube, further improving the uniformity of refrigerant distribution in the heat exchanger and enhancing the heat exchange effect of the heat exchanger.

[0128] It is understandable that the first plate 4 can be two or more. When there are two first plates 4, the first cavity 13 can be divided into three sub-cavities spaced apart along the length of the manifold 1, so that the refrigerant can be distributed in multiple sub-cavities, thereby improving the uniformity of refrigerant distribution and improving the heat exchange effect of the heat exchanger.

[0129] In some embodiments, a plane perpendicular to the length direction of the manifold 1 is defined as the first plane, the projected area of ​​the heat exchange tube 2 inserted into the first cavity 13 is S1 on the first plane, the projected area of ​​the flow guide on the first plane is S2, and the projected area of ​​the first cavity on the first plane is S, wherein: 2 / 5≤(S1+S2) / S≤9 / 10.

[0130] In some embodiments, the flow area of ​​the guide member 5 is S6, where 1 / 10 < S6 / S < 4 / 5. Specifically, the flow area S6 of the guide member 5 is the cross-sectional area through which the refrigerant can flow within the guide member 5, and the projected area of ​​the first cavity 13 of the manifold 1 on the first plane is S, where 1 / 10 < S6 / S < 4 / 5. The flow guide 5 is used to guide the refrigerant from the first sub-cavity 131 into the second sub-cavity 132. When the ratio of the flow area of ​​the flow guide 5 to the projected area of ​​the first cavity 13 on the first plane is less than 0.1, the flow resistance within the flow guide 5 is too high, resulting in only a small amount of refrigerant flowing into the second sub-cavity 132. This leads to an uneven refrigerant distribution, with too much gaseous refrigerant in the upper part of the first sub-cavity 131 and too little refrigerant in the second sub-cavity 132. When the ratio is greater than 4 / 5, the dryness of the inlet refrigerant is generally around 0.2 when the heat exchanger is in evaporation mode, and the proportion of gaseous refrigerant is not very large. The space occupied by the flow guide 5 is too large, which is not conducive to reducing the internal volume of the manifold 1. Moreover, it will cause the flow space of the refrigerant in the first cavity 13 to be too small, resulting in increased flow resistance of the refrigerant and hindering the uniform distribution of the refrigerant. Therefore, when 1 / 10 < S6 / S < 4 / 5, the flow area of ​​the flow guide 5 can be guaranteed to be within a suitable range, which is more conducive to the flow and distribution of the refrigerant.

[0131] In some embodiments, the guide member 5 includes a first connecting portion 53 and a second connecting portion 54. The guide member 5 is connected to the first sub-cavity 131 through the first connecting portion 53 and to the second sub-cavity 132 through the second connecting portion 54.

[0132] Specifically, as shown in Figures 31-32, since the first plate 4 divides the first cavity 13 into a first sub-cavity 131 and a second sub-cavity 132 that are separated from each other, the flow guide 5 is connected to the first sub-cavity 131 through the first connecting part 53 and to the second sub-cavity through the second connecting part 54. Thus, the first sub-cavity 131 and the second sub-cavity 132 can be connected through the flow guide 5, so that the refrigerant in the first sub-cavity 131 can flow into the second sub-cavity 132 through the flow guide 5, making the distribution of refrigerant in the first sub-cavity 131 and the second sub-cavity 132 more uniform and improving the heat exchange performance of the heat exchanger.

[0133] In some embodiments, the first connecting portion 53 is located near the upper part of the guide member 5, close to the first sub-cavity 131. Since there is more gaseous refrigerant in the upper part of the first sub-cavity after the refrigerant enters the first sub-cavity 131, the gaseous refrigerant in the upper part of the first sub-cavity 131 can be better directed into the second sub-cavity 132, thereby improving the uniformity of refrigerant distribution.

[0134] Optionally, the first connecting part 53 can be a connecting hole, and the second connecting part 54 can be a connecting hole. The first sub-cavity 131 and the second sub-cavity 132 are connected by providing connecting holes on the guide member 5. The first connecting part 53 can be set to one, two or more as needed, and the second connecting part 54 can be set to one, two or more as needed. No limitation is made here.

[0135] In some embodiments, the flow guide 5 includes a flow guide tube 51, which includes a first tube segment 511. The first tube segment 511 connects to a first connecting portion 53 and a second connecting portion 54, and at least a portion of the first tube segment 511 is located outside the first cavity 13.

[0136] As shown in Figures 31 and 32, the flow guide 5 includes a flow guide pipe 51, which includes a first pipe section 511. The first pipe section 511 connects to a first connecting part 53 and a second connecting part 54. At least a portion of the first pipe section 511 is located outside the first cavity 13. This can be either a partial first pipe section 511 or the entire first pipe section 511 is located outside the first cavity 13, with only the first connecting part 53 connecting to the first sub-cavity 131 and the second connecting part 54 connecting to the second sub-cavity 132. The fact that at least a portion of the first pipe section 511 is located outside the first cavity 13 eliminates the need to reserve space for the flow guide 5 within the first cavity 13 of the manifold 1. This further reduces the internal volume of the manifold, decreases the refrigerant charge, improves the refrigerant flow rate, and simplifies manufacturing. Furthermore, the flow guide pipe 51 further enhances the uniformity of refrigerant distribution within the first cavity 13 of the manifold, thereby improving the heat exchanger's heat exchange efficiency.

[0137] In some embodiments, the following embodiments of the flow guide 5 are all applicable to the heat exchanger of this application. The embodiments of the flow guide 5 can be combined with the implementation of the flow guide 5 in the following embodiments, which will not be repeated here.

[0138] In some embodiments, the above-described embodiments of manifold 1 and the following embodiments of manifold 1 are applicable to the heat exchanger of this application. The embodiments of manifold 1 can be combined with the implementation methods described in the above embodiments and / or the following embodiments, which will not be repeated here.

[0139] In some embodiments, the heat exchanger 100 further includes fins 6. The embodiments of the fins 6 of the heat exchanger in this application can refer to the implementation methods described in the above embodiments, and will not be repeated here.

[0140] In related technologies, when a heat exchanger is used as an evaporator, gaseous and liquid refrigerants flow in the manifold. When the manifold is placed vertically, under the influence of gravity, there is more liquid refrigerant and less gaseous refrigerant in the heat exchange tubes near the bottom of the manifold, while there is more gaseous refrigerant and less liquid refrigerant in the heat exchange tubes near the top of the manifold. This results in uneven distribution of the gas and liquid refrigerants in the multiple heat exchange tubes, which reduces the heat exchange performance of the heat exchanger and affects its heat exchange effect.

[0141] An embodiment of this application also proposes a heat exchanger 100, including: a heat exchange tube 2 and a manifold 1. The manifold 1 has a first cavity 13. The length direction of the heat exchange tube 2 is defined as a first direction. The heat exchange tube 2 is inserted into the manifold 1 along the first direction. The directions perpendicular to the first direction and the length direction of the manifold 1 are defined as second directions. 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.

[0142] The heat exchanger 100 also includes a first plate 4, a flow guide 5, and a connecting pipe 3. At least a portion of the first plate 4 is located in the first cavity 13, and at least a portion of the flow guide 5 is located in the first cavity. The first plate 4 divides the first cavity 13. The first cavity 13 includes a first sub-cavity 131 and a second sub-cavity 132. The flow guide 5 connects the first sub-cavity 131 and the second sub-cavity 132, and the connecting pipe 3 connects to the first sub-cavity 131.

[0143] Define the plane perpendicular to the length direction of the manifold 1 as the first plane, the projected area of ​​the heat exchange tube 2 inserted into the first cavity 13 on the first plane as S1, the projected area of ​​the flow guide on the first plane as S2, and the projected area of ​​the first cavity on the first plane as S, where: 2 / 5≤(S1+S2) / S≤9 / 10.

[0144] Specifically, for ease of understanding, the first direction is the X direction in the figure, the second direction is the Y direction, and the length direction of the manifold 1 is the Z direction. The first direction, the second direction, and the length direction of the manifold 1 are generally perpendicular to each other. The manifold 1 has a first cavity 13, and the heat exchange tube 2 is inserted into the manifold 1 along the first direction and communicates with the manifold 1. Optionally, the manifold 1 includes a first hole 14, and the heat exchange tube 2 is inserted into the manifold 1 along the first hole 14. 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 for the insertion of the heat exchange tube into the manifold 1. The maximum dimension of the first cavity is the maximum length of the manifold 1 in the first and second directions. The maximum dimension L1 of the manifold 1 in the first direction when the heat exchange tube 2 is inserted is less than the maximum dimension W1 of the manifold 1 in the second direction, which is beneficial for reducing the internal volume of the manifold 1. The manifold 1 is generally flat. Compared with the traditional circular manifold structure, the internal volume of the first cavity 13 of the manifold 1 is reduced, which reduces the amount of refrigerant charged in the heat exchanger system, which can reduce costs, save energy and be more environmentally friendly. Moreover, the safety factor of the heat exchanger is also improved after the amount of refrigerant charged is reduced.

[0145] As shown in Figure 19, the heat exchanger 100 also includes a first plate 4, a flow guide 5, and a connecting pipe 3. The connecting pipe 3 can be an inlet connecting pipe. At least part of the first plate 4 is located in the first cavity 13. The first plate 4 divides the first cavity 13 into a first sub-cavity 131 and a second sub-cavity 132. The first sub-cavity 131 and the second sub-cavity 132 are arranged adjacent to each other along the length direction of the manifold 1. The flow guide 5 connects the first sub-cavity 131 and the second sub-cavity 132. At least part of the flow guide 5 is located in the first cavity 13. The connecting pipe 3 is connected to the first sub-cavity 131.

[0146] When the heat exchanger 100 is used and is vertically installed along the length of the manifold 1, the first sub-cavity 131 is located at the upper part of the length direction of the manifold 1, and the second sub-cavity is located at the lower part of the length direction of the manifold 1. After the refrigerant enters the first sub-cavity 131 through the connecting pipe 3, some of the refrigerant flows into the heat exchange tube 2 for heat exchange. Since the first sub-cavity 131 is located at the upper part, there is a relatively large amount of gaseous refrigerant in the upper part of the first sub-cavity 131. Through the guide member 5, some of the gaseous refrigerant flows into the second sub-cavity 132. Therefore, the liquid refrigerant in the lower part of the first sub-cavity 131 can more easily enter the upper part of the first sub-cavity 131, resulting in a more uniform distribution of the refrigerant within the first sub-cavity 131. The refrigerant flowing into the second sub-cavity 132 through the guide member 5 continues to be distributed within the second sub-cavity 132. The guide member 5 forms a refrigerant flow circulation within the first and second sub-cavities 131 and 132, thereby making the distribution of the refrigerant within the first and second sub-cavities 131 and 132 more uniform. Furthermore, due to the reduced internal volume of the manifold 1 in this application, the flow space within the first cavity 13 is reduced, resulting in a higher refrigerant flow rate. This allows the refrigerant to flow more quickly within the first and second sub-cavities 131 and 132, leading to more uniform mixing of the gas-liquid two-phase refrigerant within the first and second sub-cavities 131 and 132. Consequently, the gas-liquid refrigerant entering each heat exchange tube is more uniform, further improving the uniformity of refrigerant distribution in the heat exchanger and enhancing the heat exchange effect of the heat exchanger.

[0147] According to the heat exchanger of this application, the heat exchange tube is inserted into the manifold along a first direction. The maximum dimension of the first cavity of the manifold in the second direction is larger than the maximum dimension in the first direction, which helps to reduce the internal volume of the manifold. Furthermore, through the arrangement of the first plate and the guide member, the refrigerant, after entering the manifold, first enters the first sub-cavity through the connecting pipe. Part of the refrigerant flows into the heat exchange tube in the first sub-cavity for heat exchange. Since there is a relatively large amount of gaseous refrigerant in the upper part of the first sub-cavity after entering, the guide member directs some of the gaseous refrigerant into the second sub-cavity. This makes it easier for the liquid refrigerant in the lower part of the first sub-cavity to enter the upper part of the first sub-cavity, resulting in a more uniform distribution of the refrigerant within the first sub-cavity. The refrigerant flowing into the second sub-cavity through the guide member continues to be distributed within the second sub-cavity. The guide member forms a refrigerant flow circulation within the first and second sub-cavities, thereby... The refrigerant is more evenly distributed in the first and second sub-cavities. Furthermore, by setting 2 / 5≤(S1+S2) / S≤9 / 10, that is, the sum of the projected area S1 of the heat exchange tube inserted into the first cavity and the projected area S2 of the guide member in the first plane is greater than or equal to 2 / 5 of the projected area of ​​the first cavity of the manifold in the first plane and less than or equal to 9 / 10 of the projected area S of the first cavity in the first plane, the remaining cross-sectional area in the first cavity is reduced, and the remaining volume in the first cavity is also reduced accordingly. This allows the refrigerant to flow within the first cavity within a suitable range, increasing the refrigerant velocity and making the gas-liquid two-phase refrigerant mix more evenly in the first and second sub-cavities. As a result, the gas-liquid refrigerant entering each heat exchange tube is more evenly distributed, further improving the uniformity of refrigerant distribution in the heat exchanger and enhancing the heat exchange effect of the heat exchanger.

[0148] The heat exchanger provided in this application is beneficial to improving the refrigerant distribution effect and heat exchange efficiency of the heat exchanger.

[0149] The heat exchange tube 2 is inserted into the first cavity 13 of the manifold 1 along the first direction. The projected area of ​​the portion of the heat exchange tube 2 inserted into the first cavity 13 on the first plane is S1, the projected area of ​​the flow guide 5 on the first plane is S2, and the projected area of ​​the first cavity 13 on the first plane is S. 2 / 5 ≤ (S1 + S2) / S ≤ 9 / 10. For example, S1 / S can be 0.45, 0.5, 0.55, 0.6, 0.7, 0.8, 0.9, etc. S1 is the projected area of ​​the portion of the heat exchange tube inserted into the first cavity 13 on the first plane, S2 is the projected area of ​​the flow guide 5 on the first plane, and the flow guide 5 is located in the first cavity 13. S1 + S2 is the sum of the projected areas of the heat exchange tube 2 and the flow guide 5 occupying a certain projected area in the first cavity 13 on the first plane. The projected area of ​​the refrigerant in the first cavity is defined as S7, S7 = S - S1 - S2. S7 is the projected area of ​​the refrigerant in the first cavity 13 excluding the inserted heat exchange tube 2 and the flow guide 5. The remaining projected area of ​​the guide element 5, when 2 / 5≤(S1+S2) / S≤9 / 10, is 1 / 10≤(S-S1-S2) / S≤3 / 5. That is, the remaining projected area in the first cavity 13 after the inserted heat exchange tube 2 and the guide element 5 is greater than or equal to 1 / 10 and less than or equal to 3 / 5. The remaining projected area in the first cavity 13 is the flowable area of ​​the refrigerant. When (S1+S2) / S is greater than or equal to 2 / 5, (S-S1-S2) / S≤3 / 5. The remaining projected area in the first cavity 13 decreases, and the remaining volume in the first cavity 13 also decreases accordingly. The remaining volume in the first cavity 13 is the flow space of the refrigerant. The flow space of the refrigerant in the first cavity 13 of the manifold 1 is reduced, the flow rate of the refrigerant increases, and the gas-liquid two-phase refrigerant mixes more evenly in the first cavity, so that the gas-liquid refrigerant entering each heat exchange tube 2 is more uniform, which is beneficial to improving the heat exchange effect of the heat exchanger.

[0150] For example, the projected area S1 of the heat exchange tube 2 inserted into the first cavity 13 on the first plane can be as shown in Figure 18, and the projected area S2 of the flow guide 5 on the first plane can be the projected area of ​​the flow guide tube 51 on the first plane as shown in Figure 18. S2 can also be the projected area of ​​the third sub-cavity 133 formed by the flow guide plate 52 as shown in Figure 34 on the first plane.

[0151] The sum of the projected area S1 of the heat exchange tube 2 inserted into the first cavity 13 on the first plane and the projected area S2 of the guide member on the first plane is less than or equal to 9 / 10 of the cross-sectional area S of the first cavity. When (S1+S2) / S>9 / 10, the remaining projected area S-S1-S2 in the first cavity is less than 1 / 10, and the flow space of the refrigerant in the first cavity 13 is very small. At this time, the flow resistance of the refrigerant increases, which is not conducive to the flow of the refrigerant in the first cavity 13. The gas-liquid refrigerant cannot be uniformly mixed in the first cavity 13, which is not conducive to the uniformity of refrigerant distribution and affects the heat exchanger's heat exchange effect. When (S1+S2) / S<2 / 5, the remaining volume in the first cavity 13 of the manifold 1 is large, requiring more refrigerant charge. In addition, the refrigerant has a large flow space in the first cavity 13, and the refrigerant flow velocity is low. The gas-liquid refrigerant is more easily separated in the first cavity 13, and a large flow velocity cannot be formed to make the refrigerant mix uniformly in the first cavity 13, which affects the heat exchanger's heat exchange effect.

[0152] Therefore, setting 2 / 5≤(S1+S2) / S≤9 / 10 ensures that after inserting the heat exchange tube 2 and adding the guide 5, the remaining projected area in the first cavity 13 is within a suitable range. This reduces the flow space in the first cavity 13, increases the refrigerant flow rate, and ensures that the refrigerant flow rate is not too low due to excessive flow space, nor too high due to insufficient flow space. With the flowable space in the first cavity 13 within this range, the refrigerant flow rate increases, and the gas-liquid two-phase refrigerant mixes more evenly in the first cavity. This makes the gas-liquid refrigerant entering each heat exchange tube 2 more uniform, which is beneficial for improving the heat exchange effect of the heat exchanger.

[0153] This application utilizes a manifold whose maximum dimension in the second direction is greater than that in the first direction. The manifold is generally flat, reducing its internal volume and thus minimizing the refrigerant flow space within the manifold 1. A flow guide forms a refrigerant circulation within the first and second sub-cavities, resulting in a more uniform refrigerant distribution within both sub-cavities. Furthermore, 2 / 5 ≤ (S1 + S2) / S ≤ 9 / 10. By adjusting the flow area within the first cavity of the manifold, the refrigerant flow space within the first cavity 13 is kept within a suitable range, increasing the refrigerant velocity within the first cavity. This leads to more uniform refrigerant mixing within the first cavity, resulting in a more even distribution of gas-liquid refrigerant into each heat exchange tube. This further improves the uniformity of refrigerant distribution in the heat exchanger and enhances its heat exchange efficiency.

[0154] In some embodiments, when the first cavity 13 of the manifold 1 includes a first sub-cavity 131 and a second sub-cavity 132, the ratio of the length of the first sub-cavity 131 in the length direction of the manifold to the total length of the first cavity 13 in the manifold is greater than or equal to 0.5 and less than or equal to 0.9. The total length of the first cavity 13 in the manifold is the sum of the lengths of the first sub-cavity 131 and the length of the first sub-cavity 131 in the length direction of the manifold. When the heat exchanger is used as an evaporator, the dryness of the inlet refrigerant is generally below 0.5. When the ratio is less than 0.5, the size of the first sub-cavity 131 is small, and a large amount of two-phase refrigerant will be carried into the second sub-cavity 132, resulting in obvious gas-liquid stratification along the direction of gravity inside the refrigerant in the second sub-cavity 132. When the ratio is greater than 0.9, the size of the second sub-cavity 132 is too small, and it is easily filled by the refrigerant flowing in from the guide member 5, but a large amount of gas cannot flow in, thus causing uneven liquid distribution in the first sub-cavity 131. Therefore, setting this ratio within this range can ensure that the gaseous and liquid refrigerants can flow according to the planned process, which is more conducive to improving the uniform distribution of refrigerant in the entire first chamber 13 and improving the heat exchange effect of the heat exchanger.

[0155] It is understandable that the first plate 4 can be two or more. When there are two first plates 4, the first cavity 13 can be divided into three sub-cavities spaced apart along the length of the manifold 1, so that the refrigerant can be distributed in multiple sub-cavities, thereby improving the uniformity of refrigerant distribution and improving the heat exchange effect of the heat exchanger.

[0156] In some embodiments, the length of the portion of the heat exchange tube 2 inserted into the first cavity 13 is defined as L, and the maximum hydraulic diameter of the heat exchange tube 2 is defined as W, wherein: 0.02W≤W1-W≤W, and / or, 0.1L≤L1-L≤L.

[0157] As shown in Figure 18, the length of the heat exchange tube 2 inserted into the first cavity 13 is L, where L is the length of the heat exchange tube 2 inserted into the first cavity 13 of the manifold 1 along the first direction, and the hydraulic diameter of the heat exchange tube 2 is W, that is, 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 in the first direction after the inserted heat exchange tube 2, and W1-W is the remaining dimension in the first cavity 13 in the second direction after the inserted heat exchange tube 2. 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 exchanger's heat exchange effect. At the same time, the impact force between the refrigerant and the manifold 1 will also indirectly increase the refrigerant flow resistance in the heat exchange tube 2, affecting the heat exchanger's heat exchange effect. 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.

[0158] Therefore, by setting 0.02W≤W1-W≤W and / or 0.1L≤L1-L≤L, after the heat exchange tube 2 is inserted into the first cavity 13 of the manifold 1, the flowable area in the first cavity 13 of the manifold 1 is reduced, the flowable space in the first cavity is reduced, the flow rate of the refrigerant is increased, and the remaining flowable space in the first cavity 13 is not too large, resulting in a low flow rate, nor too small, resulting in excessive flow resistance. Within this range, the flowable space in the first cavity 13 increases 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, thus improving the heat exchange effect of the heat exchanger.

[0159] 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.

[0160] In some embodiments, the structure of manifold 1 in the above embodiments is applicable to the heat exchanger of this aspect. The structure of manifold 1 can be referred to the above embodiments, and will not be repeated here.

[0161] In some embodiments, the connector 3 includes a first opening 31 located on its radial side, and the connector 3 communicates with the first sub-cavity 131 through the first opening 31.

[0162] As shown in Figures 19 and 12, the connecting pipe 3 includes a first opening 31. The arrangement of the connecting pipe 3 and the first opening 31 can be referred to the embodiment of the connecting pipe 3 and the first opening 31 in the heat exchanger described above, and will not be repeated here.

[0163] Understandably, depending on the actual application, the opening of the connector 3 can be set at the axial end of the connector 3, or it can be set at both the end of the connector 3 and the radial direction of the connector 3, which is beneficial to the flow of refrigerant in the first cavity 13 of the manifold and improves the uniformity of refrigerant distribution.

[0164] In some embodiments, referring to Figures 11 and 19, 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.

[0165] In some embodiments, the guide member 5 includes a first connecting portion 53 and a second connecting portion 54. The guide member 5 is connected to the first sub-cavity 131 through the first connecting portion 53 and to the second sub-cavity 132 through the second connecting portion 54.

[0166] Specifically, as shown in Figures 19 and 28-33, since the first plate 4 divides the first cavity 13 into a first sub-cavity 131 and a second sub-cavity 132 that are separated from each other, the flow guide 5 is connected to the first sub-cavity 131 through the first connecting part 53 and to the second sub-cavity through the second connecting part 54. Thus, the first sub-cavity 131 and the second sub-cavity 132 can be connected through the flow guide 5, so that the refrigerant in the first sub-cavity 131 can flow into the second sub-cavity 132 through the flow guide 5, making the distribution of refrigerant in the first sub-cavity 131 and the second sub-cavity 132 more uniform and improving the heat exchange performance of the heat exchanger.

[0167] In some embodiments, the first connecting portion 53 is located near the upper part of the guide member 5, close to the first sub-cavity 131. Since there is more gaseous refrigerant in the upper part of the first sub-cavity after the refrigerant enters the first sub-cavity, the gaseous refrigerant in the upper part of the first sub-cavity 131 can be better directed into the second sub-cavity 132, thereby improving the uniformity of refrigerant distribution.

[0168] Optionally, the first connecting part 53 can be a connecting hole, and the second connecting part 54 can be a connecting hole. The first sub-cavity 131 and the second sub-cavity 132 are connected by providing connecting holes on the guide member 5. The first connecting part 53 can be set to one, two or more as needed, and the second connecting part 54 can be set to one, two or more as needed. No limitation is made here.

[0169] In some embodiments, the flow area of ​​the guide is S6, 1 / 10 < S6 / S < 4 / 5, and / or, 3 / 10 ≤ S1 / S ≤ 9 / 10.

[0170] Specifically, the flow area S6 of the guide member 5 is the cross-sectional area through which the refrigerant can flow within the guide member 5. The projected area of ​​the first cavity 13 of the manifold 1 on the first plane is S, where 1 / 10 < S6 / S < 4 / 5. The guide member 5 is used to guide the refrigerant from the first sub-cavity 131 into the second sub-cavity 132. When the ratio of the flow area of ​​the guide member to the projected area of ​​the first cavity 13 on the first plane is less than 0.1, the flow resistance within the guide member 5 is too high, resulting in only a small amount of refrigerant flowing into the second sub-cavity 132. Consequently, there is too much gaseous refrigerant in the upper part of the first sub-cavity 131 and too little refrigerant in the second sub-cavity 132, leading to an uneven refrigerant distribution. When the ratio is greater than 4 / 5, the dryness of the inlet refrigerant is generally around 0.2 when the heat exchanger is in the evaporation state, and the proportion of gaseous refrigerant is not very large. The space occupied by the guide member 5 is too large, which is not conducive to reducing the internal volume of the manifold 1. Moreover, it will cause the flow space of the refrigerant in the first cavity 13 to be too small, resulting in increased refrigerant flow resistance and hindering the uniform distribution of refrigerant. Therefore, when 1 / 10 < S6 / S < 4 / 5, the flow area of ​​the guide element 5 can be guaranteed to be within a suitable range, which is more conducive to the flow and distribution of refrigerant and improves the heat exchange effect of the heat exchanger.

[0171] In some embodiments, 3 / 10 ≤ S1 / S ≤ 9 / 10, the heat exchange tube 2 is inserted into the first cavity 13 of the manifold 1 along the first direction, and the projected area S1 of the portion of the heat exchange tube 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 plane of the first cavity and less than or equal to 9 / 10 of the projected area S of the first plane of the first cavity. This makes it so that after the heat exchange tube 2 is inserted into the manifold 1, the remaining projected area S-S1 in the first cavity 13, excluding the inserted heat exchange tube, is greater than or equal to 1 / 10 and less than or equal to 7 / 10. When S-S1 is within this range, the refrigerant flow space is within a suitable range, the refrigerant flow rate increases, and the gas-liquid refrigerant mixes more evenly in the first cavity, improving the heat exchange effect of the heat exchanger.

[0172] Understandably, when S1 / S is less than 3 / 10, the remaining volume in the first cavity 13 of manifold 1 is large, requiring a larger refrigerant charge. Furthermore, the large flow space within the first cavity 13 results in a low refrigerant velocity, making it easier for the gaseous and liquid refrigerants to separate. This prevents the formation of a large enough flow velocity for uniform mixing, thus affecting the heat exchanger's performance. When S1 / S > 9 / 10, the remaining cross-sectional area in the first cavity is less than 1 / 10, resulting in a small flow space for the refrigerant within the first cavity 13. This increases the refrigerant's flow resistance, hindering its movement within the cavity. The gaseous and liquid refrigerants cannot mix uniformly within the first cavity 13, negatively impacting the refrigerant's distribution and overall heat exchanger performance.

[0173] Therefore, by setting the projected area S1 of the heat exchange tube 2 inserted into the first cavity 13 to be 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 cross-sectional area S of the first cavity, even after adding the guide member 5 in the first cavity 13, the flow space of the refrigerant in the first cavity is still within a suitable range, the flow rate of the refrigerant increases, and the gas-liquid two-phase refrigerant mixes more evenly in the first cavity, thereby making the gas-liquid refrigerant entering each heat exchange tube 2 more uniform, which is beneficial to improving the heat exchange effect of the heat exchanger.

[0174] In some embodiments, the flow guide 5 includes a flow guide tube 51, which includes a first tube segment 511. The first tube segment 511 connects to a first connecting portion 53 and a second connecting portion 54, and at least a portion of the first tube segment 511 is located within the first cavity 13.

[0175] As shown in Figures 19-30, the flow guide 5 includes a flow guide pipe 51, which includes a first pipe section 511. At least a portion of the first pipe section 511 is located within the first cavity 13, that is, a portion of the first pipe section 511 is located within the first cavity 13, or all of the first pipe sections 511 are located within the first cavity 13. The first pipe section 511 is generally a straight circular pipe. The first pipe section 511 connects to a first connecting part 53 and a second connecting part 54. The first connecting part 53 is located on the first pipe section 511 of the first sub-cavity 131, and the second connecting part 54 is located on the first pipe section 511 of the first sub-cavity 132. After the refrigerant enters the first sub-cavity 131, there is a larger amount of gaseous refrigerant in the upper part of the first sub-cavity 131. Through the guide member 5, some of the gaseous refrigerant flows into the second sub-cavity 132. As a result, the liquid refrigerant in the lower part of the first sub-cavity 131 can more easily enter the upper part of the first sub-cavity 131, making the refrigerant distribution in the first sub-cavity 131 more uniform. Moreover, the refrigerant flowing into the second sub-cavity 132 through the guide member 5 continues to be distributed in the second sub-cavity 132. The guide member 5 forms a refrigerant flow circulation in the first sub-cavity 131 and the second sub-cavity 132, thereby making the refrigerant distribution in the first sub-cavity 131 and the second sub-cavity 132 more uniform. The gaseous and liquid refrigerant entering each heat exchange tube is more uniform, which further improves the uniformity of refrigerant distribution in the heat exchanger and improves the heat exchange effect of the heat exchanger.

[0176] In some embodiments, the manifold 1 includes a protrusion 17 that extends along the length direction of the manifold 1. The length of the protrusion 17 in a first direction is less than the maximum size of the first cavity 13 in the first direction, and / or the length of the protrusion 17 in a second direction is less than the maximum size of the first cavity 13 in the second direction. The protrusion 17 is used to place a guide tube.

[0177] Specifically, as shown in Figures 22-23, the manifold 1 includes a protrusion 17, a first main body 11, and a second main body 12. The first main body 11, or the second main body 12, or both the first and second main body 11 and 12 include the protrusion 17. The protrusion 17 is part of the wall of the manifold 1 and extends along the length of the manifold 1. The protrusion 17 communicates with the first cavity 13 and is used to place a guide tube. The maximum length of the protrusion 17 in the first direction is less than the maximum dimension of the first cavity 13 in the first direction, and / or the maximum length of the protrusion 17 in the second direction is less than the maximum length of the first cavity 13 in the second direction. The space in the protrusion 17 is sufficient to place the guide tube 51, thereby further reducing the internal volume of the manifold 1 and the refrigerant charge; and reducing the refrigerant flow space in the first cavity 13, further increasing the refrigerant flow rate, which is more conducive to improving the uniformity of refrigerant distribution and improving the heat exchange effect of the heat exchanger.

[0178] As shown in Figure 22, the second main body 12 of the manifold 1 includes a protrusion 17. The length of the protrusion 17 in the second direction is less than the maximum dimension W1 of the first cavity 13 in the second direction. The protrusion 17 is part of the pipe wall of the manifold 1. The protrusion 17, the first main body 11, and the second main body 12 form the first cavity 13 of the manifold 1. The protrusion 17 is arranged along the length direction of the manifold and is used to place the guide pipe 51. This further reduces the volume of the first cavity of the manifold 1, reduces the flow space in the first cavity 13, increases the refrigerant flow rate, and is more conducive to improving the uniformity of refrigerant distribution.

[0179] As shown in Figure 23, the manifold 1 includes a protrusion 17. The length of the protrusion 17 in the first direction is less than the maximum dimension L1 of the first cavity 13 in the first direction. The protrusion 17 is part of the pipe wall of the manifold 1. The protrusion 17, the first main body 11 and the second main body 12 of the manifold 1 form the first cavity 13 of the manifold 1. The protrusion 17 is arranged along the length direction of the manifold. The protrusion 17 is used to place the guide pipe 51, thereby further reducing the volume of the first cavity of the manifold 1, reducing the flow space in the first cavity 13, increasing the refrigerant flow rate, and making it more conducive to improving the uniformity of refrigerant distribution.

[0180] Understandably, the protrusion 17 can be a straight structure as shown in the figure, a protruding arc structure, or other structures, as long as the guide tube 51 can be placed, and there are no restrictions here.

[0181] In some embodiments, the guide tube 51 includes a bend section 512 connected to the first tube section 511, the bend section 512 is located in the second sub-cavity 132, and the second connecting portion 54 is located on the side near the bend section 512.

[0182] Specifically, as shown in Figure 28, the guide pipe 51 includes a bent section 512, which is connected to the first pipe section 511. The bent section 512 and the first pipe section 511 can be an integral structure. The bent section 512 is located in the second sub-cavity 132. The guide pipe 51 in the second sub-cavity 132 includes the bent section 512. The second connecting part 54 is located on the side close to the bent section 512, so that when the refrigerant flows to the second sub-cavity 132, it forms an upward spray when passing through the bent section 512, which helps to increase the flow rate of the refrigerant and bring more liquid refrigerant into the upper part of the second sub-cavity 132 for heat exchange. After flowing upward through the bent section 512, the refrigerant can cover more heat exchange tubes within the second sub-cavity 132, so that the refrigerant can be more evenly distributed in the second sub-cavity 132, making the gas-liquid refrigerant entering each heat exchange tube 2 more uniform, improving the uniformity of refrigerant distribution, and improving the heat exchange performance of the heat exchanger.

[0183] In some embodiments, the guide tube 51 includes a recess 513 located in the second sub-cavity 132. The recess 513 has a second hole 514 extending along the length direction of the manifold 1. The flow area of ​​the second hole 514 is smaller than the flow area of ​​the guide tube 51.

[0184] Specifically, as shown in Figure 29, the guide pipe 51 includes a concave portion 513 located in the second sub-cavity 132. The concave portion 513 has a second hole 514 extending along the length of the manifold 1, allowing refrigerant to flow through it. The flow area of ​​the second hole 514 is smaller than that of the guide pipe 51. When the refrigerant flows through the second hole 514, it is blocked by the concave portion 513, allowing some of the refrigerant to remain in the upper part of the second sub-cavity 132 and flow out from the second connecting portion 54 near the upper part of the second sub-cavity 132. The other part of the refrigerant flows downward through the second hole 514 and flows out from the second connecting portion 54 near the lower part of the second sub-cavity 132. When the refrigerant flows downward through the second hole 514, it forms a jet, making the refrigerant more evenly distributed in the second sub-cavity 132. This makes the gas-liquid refrigerant entering each heat exchange tube 2 more uniform, improving the uniformity of refrigerant distribution and enhancing the heat exchange effect.

[0185] In some embodiments, the flow area at the end of the guide member 5 in the second sub-cavity 132 is greater than the flow area of ​​the guide member 5 in the first sub-cavity 131.

[0186] In some embodiments, as shown in FIG30, the flow area at the end of the guide member 5 in the second sub-cavity 132 is larger than the flow area of ​​the guide member 5 in the first sub-cavity 131. The end of the guide member 5 is disposed near the upper part of the second sub-cavity 132. The second connecting part 54 can be disposed at the end of the guide member 5. When the refrigerant flows through the second sub-cavity 132, it begins to be sprayed at the upper part of the second sub-cavity 132, so that the refrigerant can better fill the entire second sub-cavity 132. As a result, the refrigerant can be more evenly distributed in the second sub-cavity 132, making the gas-liquid refrigerant entering each heat exchange tube more uniform, improving the uniformity of refrigerant distribution, and improving the heat exchange effect.

[0187] In some embodiments, the inner wall of the flow guide 5 may include a reinforcing structure, which may be a protrusion, a threaded structure, or other structures. When the refrigerant flows through the flow guide 5, the collision between the refrigerant and the inner wall of the flow guide 5 is increased when it passes through the protrusion or threaded structure. This can further increase the flow rate of the gas-liquid refrigerant in the flow guide 5, improve the impact force of the refrigerant, and make the refrigerant mix more evenly in the first cavity 13, thereby improving the refrigerant distribution effect and heat exchange performance.

[0188] In some embodiments, the flow guide 5 includes a flow guide plate 52, which extends along the length of the manifold 1. The manifold 1 also includes a third sub-cavity 133. The wall surrounding the third sub-cavity 133 includes at least a portion of the flow guide plate 52, a portion of the first main body 11, and / or a portion of the second main body 12. The third sub-cavity 133 extends along the length of the manifold. The third sub-cavity 133 is connected to the first sub-cavity 131 through a first connecting portion 53, and the third sub-cavity 133 is connected to the second sub-cavity 132 through a second connecting portion 54.

[0189] Specifically, as shown in Figures 33-35, the flow guide 5 includes a flow guide plate 52, which extends along the length of the manifold 1 and divides the manifold 1 into a third sub-cavity 133. The third sub-cavity 133 extends along the length of the manifold, and the wall surrounding the third sub-cavity 133 includes at least a portion of the flow guide plate 52, a portion of the first main body 11, and / or a portion of the second main body 12. The third sub-cavity 133 can be formed by the flow guide plate 52, a portion of the first main body 11, and / or a portion of the second main body 12.

[0190] The third sub-cavity 133 is connected to the first sub-cavity 131 through the first connecting part 53, and the third sub-cavity 133 is connected to the second sub-cavity 132 through the second connecting part 54. The first connecting part 53 is a through hole on the guide plate 52, and the second connecting part 54 is a through hole on the guide plate 52. The function of the third sub-cavity 133 formed by the guide plate 52 and the manifold 1 is the same as that of the guide pipe 51, which allows the refrigerant in the first sub-cavity 131 to flow into the second sub-cavity 132, thereby forming a refrigerant flow circulation in the first sub-cavity 131 and the second sub-cavity 132, and realizing the uniform distribution of refrigerant.

[0191] Specifically, when the heat exchanger is in operation, after the refrigerant enters the first chamber 13 of the manifold, it first flows into the first sub-chamber 131. A portion of the refrigerant flows into the heat exchange tubes near the first sub-chamber 131 for heat exchange, while another portion flows from the first connecting part 53 into the third sub-chamber 133. The third sub-chamber 133 extends along the length of the manifold. The refrigerant flowing into the third sub-chamber 133 flows downwards through the second connecting part 54 into the second sub-chamber 132. A portion of the refrigerant is then guided into the second sub-chamber 132 by the guide plate 52. Thus, the liquid refrigerant in the lower part of the first sub-chamber 131 is further... The refrigerant can easily enter the upper part of the first sub-cavity 131, making the refrigerant distribution in the first sub-cavity 131 more uniform. Moreover, the refrigerant flowing into the second sub-cavity 132 through the guide plate 52 continues to be distributed in the second sub-cavity 132. The guide plate 52 forms a refrigerant flow circulation in the first and second sub-cavities 131, thereby making the refrigerant distribution in the first and second sub-cavities 131 and 132 more uniform. The gas-liquid refrigerant entering each heat exchange tube 2 is more uniform, which further improves the uniformity of refrigerant distribution in the heat exchanger and improves the heat exchange effect of the heat exchanger.

[0192] As shown in Figures 33-34, the guide plate 52 is generally plate-shaped and extends along the length of the manifold 1. The guide plate 52, together with part of the first main body 11 and part of the second main body 12, forms a third sub-cavity 133, which extends along the length of the manifold 1.

[0193] As shown in Figure 33, the first connecting part 53 and the second connecting part 54 are connecting holes on the guide plate 52. The first connecting part 53 includes a connecting hole, and the second connecting part 54 includes a connecting hole. There can be one, two, or more connecting holes. The guide plate 52 is connected to the first sub-cavity 131 through the first connecting part 53, so that part of the refrigerant in the first sub-cavity 131 flows into the third sub-cavity 133 through the first connecting part 53. The refrigerant flowing in the third sub-cavity 133 is connected to the second sub-cavity 132 through the second connecting part 54, so that the refrigerant flows into the second sub-cavity 132 again, thereby realizing the connection between the first sub-cavity 131 and the second sub-cavity 132. The guide plate 52 forms a refrigerant flow circulation in the first sub-cavity 131 and the second sub-cavity 132, thereby improving the uniform distribution of the refrigerant.

[0194] As shown in Figure 35, the guide plate 52 is generally arc-shaped and extends along the length of the manifold 1. The guide plate 52 and part of the second main body 12 enclose a third sub-cavity 133. The guide plate 52 is connected to the first sub-cavity 131 through the first connecting part 53 and to the first sub-cavity 132 through the second connecting part 54. The guide plate 52 forms a refrigerant flow circulation in the first sub-cavity 131 and the second sub-cavity 132, improving the uniform distribution of the refrigerant.

[0195] Optionally, the guide plate 52 can be an integral structure with the second main body 12, or an integral structure with the manifold 1, or it can be a separate component placed in the first cavity 13 of the manifold. Alternatively, part of the guide plate 52 can be an integral structure with the first main body 11, and part of the guide plate 52 can be an integral structure with the second main body 12. No restrictions are imposed here.

[0196] In some embodiments, there can be two or more flow guides 5. Considering the different systems in which the heat exchanger is used, the corresponding heat exchanger sizes are also different. For heat exchangers with a long manifold 1, one flow guide may not be able to meet the need for uniform refrigerant distribution. The heat exchanger can be divided into two or more independent modules along the length of the manifold. Each module adopts the structure of the flow guide described above. The system's inlet pipe is connected to each independent module through a distributor or by setting multiple pipes, thereby improving the uniform refrigerant distribution effect of the entire heat exchanger.

[0197] In some embodiments, the flow guide 5 is located on one side of the heat exchange tube 2 in the second direction, and the flow guide 5 extends along the length direction of the manifold.

[0198] Specifically, as shown in Figures 23-28, the guide pipe 51 is located on one side of the heat exchange tube 2 in the second direction. As shown in Figure 34, the guide plate 52 is located on one side of the heat exchange tube 2 in the second direction. When the heat exchanger is in operation, the airflow flows through the heat exchanger 100 in the second direction. Generally speaking, the heat exchange effect is higher along the direction of airflow due to the larger air volume, and the heat exchange effect is slightly lower away from the direction of airflow. When the heat exchanger is in operation, after the refrigerant flows into the first sub-cavity 131 from the pipe 3, the refrigerant flow rate on the windward side is large due to the large air volume on the windward side, which can allow more refrigerant to flow into the heat exchange tube 2 for heat exchange. Moreover, the guide plate 5 is located on one side of the heat exchange tube 2 in the second direction, which can allow more gaseous refrigerant in the first sub-cavity 131 to flow into the second sub-cavity 132 for heat exchange. This makes reasonable use of the influence of air volume on the refrigerant, improves the distribution effect of the refrigerant, makes the gas-liquid refrigerant entering each heat exchange tube more uniform, and improves the overall heat exchange performance of the heat exchanger.

[0199] In some embodiments, the end of the heat exchange tube 2 includes a third end 2A and a fourth end 2B disposed opposite to each other along a second direction, and the flow area of ​​the first cavity 13 near the fourth end 2B is greater than the flow area of ​​the first cavity 13 near the third end 2A.

[0200] Specifically, as shown in Figures 25-27, the flow area of ​​the first cavity 13 near the fourth end 2B is larger than that of the first cavity 13 near the third end 2A. The heat exchange tube 2 has a larger flow area near the fourth end 2B. Therefore, when the heat exchanger is in use, when the airflow is along the direction from the fourth end 2B to the third end 2A, when the refrigerant flows into the first sub-cavity 131, there is more refrigerant near the fourth end 2B than near the third end 2A. Since the guide member 5 is near the fourth end 2B, it can allow more gaseous refrigerant in the first sub-cavity 131 to flow into the second sub-cavity 132 for heat exchange, thereby improving the overall refrigerant distribution in the first cavity 13 and improving the heat exchange effect of the heat exchanger.

[0201] In some embodiments, the end of the heat exchange tube 2 includes a third end 2A and a fourth end 2B disposed opposite to each other along a second direction, and the distance from the end of the heat exchange tube 2 near the fourth end 2B to the second body member 12 is greater than the distance from the end of the heat exchange tube 2 near the third end 2A to the second body member 12.

[0202] As shown in Figures 25-26, the distance from the end of heat exchange tube 2 near the fourth end 2B to the second main body 12 is greater than the distance from the end of heat exchange tube 2 near the third end 2A to the second main body 12. Heat exchange tube 2 has a larger flow cross-sectional area near the fourth end 2B than near the third end 2A. There is more refrigerant near the fourth end 2B than near the third end 2A. Therefore, when the refrigerant flows into the first sub-cavity 131, more refrigerant will flow into the guide member 5 located near the fourth end 2B. Through the guide member 5, more gaseous refrigerant in the first sub-cavity 131 flows into the second sub-cavity 132 for heat exchange, which improves the overall refrigerant distribution in the first cavity 13 of the heat exchanger and improves the heat exchange effect of the heat exchanger.

[0203] It is understandable that the distance from the fourth end 2B of the heat exchange tube 2 to the second main body 12 is greater than the distance from the third end 2A to the second main body 12. This distance can be a linear change as shown in Figure 25, a nonlinear change as shown in Figure 26, or other forms, which are not limited here.

[0204] In some embodiments, as shown in FIG27, the distance from the end of the heat exchange tube 2 to the second main body 12 is the same. The flow cross-sectional area of ​​the first cavity 13 near the fourth end 2B is larger than that of the first cavity 13 near the third end 2A. The flow space near the fourth end 2B is larger than that near the third end 2A. Therefore, when the refrigerant flows into the first sub-cavity 131, more refrigerant will flow into the guide member 5 located near the fourth end 2B. Through the guide member 5, more gaseous refrigerant in the first sub-cavity 131 flows into the second sub-cavity 132 for heat exchange, which improves the overall refrigerant distribution of the heat exchanger in the first cavity 13 and improves the heat exchange effect of the heat exchanger.

[0205] Understandably, the distance from the end of the heat exchange tube 2 to the second main body 12 can also be set to be the same, with the flow hole of the heat exchange tube 2 near the fourth end 2B being larger than that of the heat exchange tube 2 near the third end 2A. This makes the flow area of ​​the first cavity 13 near the fourth end 2B larger than that of the first cavity 13 near the third end 2A. Consequently, when the refrigerant flows into the first sub-cavity 131, more refrigerant will flow into the guide member 5 located near the fourth end 2B. Through the guide member 5, more gaseous refrigerant in the first sub-cavity 131 will flow into the second sub-cavity 132 for heat exchange, improving the overall refrigerant distribution in the first cavity 13 of the heat exchanger and enhancing the heat exchange effect of the heat exchanger. Of course, other structural designs can also be selected, and no restrictions are imposed here.

[0206] By using the non-uniform design at the end of heat exchange tube 2 or the non-uniform design of the first cavity of manifold 1, the flow area of ​​the first cavity 13 near the fourth end 2B is greater than the flow area of ​​the first cavity 13 near the third end 2A. Combined with the airflow changes during the application of the heat exchanger, the flow area near the windward side is greater than the flow area near the leeward side, which further optimizes the distribution of refrigerant and improves the heat exchange effect of the heat exchanger.

[0207] The connecting pipe 3 can be located near the end of the heat exchange tube 2 in the first direction, or near the fourth end 2B in the second direction, or near the third end 2A in the second direction. The specific location depends on the situation. As long as the connecting pipe 3 does not interfere with the position of the guide 5, there are no restrictions.

[0208] In some embodiments, as shown in FIG17, 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 direction of the heat exchange tubes 2, and there is no limitation herein.

[0209] It should be noted that any two or more embodiments of the heat exchanger in this application may be combined or integrated with each other without contradicting each other.

[0210] In this application, relational terms such as "first" and "second" are used merely to distinguish one entity or unit from another, and do not necessarily require or imply any such actual relationship or order between these entities or units. Furthermore, in this document, "multiple" means at least two, unless otherwise explicitly specified.

[0211] In this application, unless otherwise expressly specified and limited, the terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection, an electrical connection, or a connection that allows communication between components; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components, unless otherwise expressly limited. Those skilled in the art can understand the specific meaning of the above terms in this application based on the specific circumstances.

[0212] In this application, the terms "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., refer to a specific feature, structure, material, or characteristic described in connection with that embodiment or example, which is included in at least one embodiment or example of this application. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples. Moreover, without contradiction, those skilled in the art can combine and integrate the different embodiments or examples described in this specification, as well as the features of different embodiments or examples.

[0213] The above examples illustrate the principles and implementation methods of this application. The descriptions of the embodiments are merely for the purpose of helping to understand the methods and core ideas of this application. It should be noted that those skilled in the art can make various improvements and modifications to this application without departing from its principles, and these improvements and modifications also fall within the protection scope of this application.

Claims

1. A heat exchanger, characterized by, include: A heat exchange tube and a manifold, wherein the manifold 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 manifold along the first direction, and directions perpendicular to the first direction and the length direction of the manifold are 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; a plane perpendicular to the length direction of the manifold is defined as a first plane, the projected area of ​​the portion of the heat exchange tube inserted into the first cavity on the first plane is S1, and the projected area of ​​the first cavity on the first plane is S, wherein: 3 / 10 ≤ S1 / S ≤ 9 / 10.

2. The heat exchanger of claim 1, wherein The manifold includes a first main body and a second main body. The wall surrounding the manifold includes at least a portion of the first main body and at least a portion of the second main body. The first main body extends along the length direction of the manifold, and the second main body extends along the length direction of the manifold.

3. The heat exchanger of claim 2, wherein The first main body and the second main body are separate structures. The manifold also includes a reinforcing part, which is connected to the first main body and / or the second main body. The reinforcing part is integrally formed with the first main body, or integrally formed with the second main body, or separate from 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 an integral structure, or the first main body and the second main body are separate structures.

5. The heat exchanger of claim 2, wherein The manifold further includes a protrusion and a first hole. The protrusion is connected to the second main body component. The first hole is located in the first main body component. The heat exchange tube is inserted into the manifold along the first hole. A portion of the end of the heat exchange tube abuts against the protrusion. The end of the heat exchange tube has a gap with the second main body component.

6. The heat exchanger according to any one of claims 1 to 5, characterized in that The length 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 also includes a connecting pipe that communicates with the manifold, the connecting pipe including a first opening located on its radial side.

8. The heat exchanger of claim 7, wherein The manifold has a first end and a second end along its length. When the connecting pipe is closer 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 closer 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 according to claim 7 or 8, characterized in that The flow area of ​​the connecting pipe is S3, and the flow area of ​​the first opening is S4, where 0.5 ≤ S4 / S3 ≤ 1.

5.

10. The heat exchanger according to any one of claims 1 to 9, characterized in that The heat exchanger further includes a second plate, the second plate including a third hole that penetrates the second plate, and at least a portion of the second plate is located within the manifold.

11. The heat exchanger of claim 10, wherein The second plate is two or more, and the heat exchanger further includes a connecting pipe that communicates with the manifold. The flow area of ​​the third hole near the connecting pipe is greater than or equal to the flow area of ​​the third hole away from the connecting pipe, and / or the spacing between adjacent second plates near the connecting pipe is greater than or equal to the spacing between adjacent second plates away from the connecting pipe.

12. The heat exchanger according to any one of claims 1 to 11, characterized in that The heat exchanger further includes a first plate, which is at least partially located within the first cavity. The first plate divides the manifold into at least two cavities, and the at least two cavities are arranged adjacent to each other along the length of the manifold. And / or, the heat exchanger further includes a third plate, the manifold having a first end and a second end in its length direction, the third plate being disposed near the first end or the second end.

13. The heat exchanger according to any one of claims 1 to 11, characterized in that The heat exchanger further includes a first plate, a flow guide, and a connecting pipe. At least a portion of the first plate is located within the first cavity, and the first plate divides the first cavity. The first cavity includes a first sub-cavity and a second sub-cavity. The flow guide connects the first sub-cavity and the second sub-cavity. At least a portion of the flow guide is located outside the first cavity, and the connecting pipe is connected to the first sub-cavity.

14. The heat exchanger of claim 13, wherein The projected area of ​​the heat exchange tube inserted into the first cavity on the first plane is S1, the projected area of ​​the flow guide on the first plane is S2, and the projected area of ​​the first cavity on the first plane is S, where 2 / 5≤(S1+S2) / S≤9 / 10.

15. The heat exchanger according to claim 13 or 14, characterized in that The flow guide includes a first connecting portion and a second connecting portion. The flow guide is connected to the first sub-cavity through the first connecting portion and to the second sub-cavity through the second connecting portion.

16. The heat exchanger of claim 15, wherein The flow area of ​​the guide component is S6, where 1 / 10 < S6 / S < 4 / 5.

17. The heat exchanger according to claim 15 or 16, characterized in that The flow guide includes a flow guide tube, which includes a first tube segment that connects the first connecting portion and the second connecting portion, with at least a portion of the first tube segment located within the first cavity.

18. The heat exchanger according to claim 17, characterized in that, The manifold includes a protrusion that extends along the length of the manifold. The length of the protrusion in the first direction is less than the maximum size of the first cavity in the first direction, and / or the length of the protrusion in the second direction is less than the maximum size of the first cavity in the second direction. The protrusion is used to house the guide tube.

19. The heat exchanger according to claim 17 or 18, characterized in that The guide pipe includes a bend section that communicates with the first pipe section. The bend section is located in the second sub-cavity, and the second connecting portion is located on the side close to the bend section.

20. The heat exchanger of claim 17 or 18, wherein, The guide tube includes a concave portion located in the second sub-cavity. The concave portion has a second hole, which is arranged along the length of the manifold. The flow area of ​​the second hole is smaller than the flow area of ​​the guide tube.

21. The heat exchanger according to any one of claims 15 to 20, characterized in that The manifold includes a first main body and a second main body. The wall surrounding the manifold includes at least a portion of the first main body and at least a portion of the second main body. The flow guide includes a flow guide plate that extends along the length of the manifold. The manifold also includes a third sub-cavity. The wall surrounding the third sub-cavity includes at least a portion of the flow guide plate, a portion of the first main body, and / or a portion of the second main body. The third sub-cavity extends along the length of the manifold. The third sub-cavity communicates with the first sub-cavity through a first connecting portion and with the second sub-cavity through a second connecting portion.

22. The heat exchanger according to any one of claims 13 to 21, characterized in that The flow guide is located on one side of the heat exchange tube in the second direction, and the flow guide extends along the length direction of the manifold.

23. The heat exchanger of claim 22, wherein, The heat exchange tube has a third end and a fourth end that are arranged opposite to each other along the second direction, and the flow area of ​​the first cavity near the fourth end is greater than the flow area of ​​the first cavity near the third end.

24. A heat exchanger, characterized by include: The heat exchanger includes a heat exchange tube and a manifold. The manifold 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 manifold along the first direction. A second direction is defined as a direction perpendicular to both the first direction and the length direction of the manifold. 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 heat exchanger also includes a first plate, a flow guide, and a connecting pipe. At least a portion of the first plate and at least a portion of the flow guide are located within the first cavity. The first plate divides the first cavity. The first cavity includes a first sub-cavity and a second sub-cavity. The flow guide connects the first sub-cavity and the second sub-cavity. The connecting pipe connects to the first sub-cavity. A plane perpendicular to the length direction of the manifold is defined as a first plane. The projected area of ​​the portion of the heat exchange tube inserted into the first cavity on the first plane is S1. The projected area of ​​the flow guide on the first plane is S2. The projected area of ​​the first cavity on the first plane is S, where 2 / 5 ≤ (S1 + S2) / S ≤ 9 / 10.

25. The heat exchanger of claim 24, wherein, The flow guide includes a first connecting portion and a second connecting portion. The flow guide is connected to the first sub-cavity through the first connecting portion and to the second sub-cavity through the second connecting portion.

26. The heat exchanger of claim 25, wherein, The flow area of ​​the guide component is S6, 1 / 10 < S6 / S < 4 / 5, and / or, 3 / 10 ≤ S1 / S ≤ 9 / 10.

27. The heat exchanger according to any of claims 25 or 26, characterized in that The flow guide includes a flow guide tube, which includes a first tube segment that connects the first connecting portion and the second connecting portion, with at least a portion of the first tube segment located within the first cavity.

28. The heat exchanger of claim 27, wherein, The manifold includes a protrusion that extends along the length of the manifold. The length of the protrusion in the first direction is less than the maximum size of the first cavity in the first direction, and / or the length of the protrusion in the second direction is less than the maximum size of the first cavity in the second direction. The protrusion is used to house the guide tube.

29. The heat exchanger of claim 27 or 28, wherein, The guide pipe includes a bend section that communicates with the first pipe section. The bend section is located in the second sub-cavity, and the second connecting portion is located on the side close to the bend section.

30. The heat exchanger of claim 27 or 28, wherein, The guide tube includes a concave portion located in the second sub-cavity. The concave portion has a second hole, which is arranged along the length of the manifold. The flow area of ​​the second hole is smaller than the flow area of ​​the guide tube.

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