Heat exchange fin, heat exchange tube, heat exchanger and air conditioner

Abstract

The invention provides a heat exchange fin, a heat exchange tube, a heat exchanger and an air conditioner. The heat exchange fin comprises a vertical fin and a heat exchange fin, wherein the vertical fin extends in the first preset direction and is arranged on a to-be-installed foundation; the first transverse fin and the second transverse fin are arranged on the vertical fin in an extending mode in the second preset direction which forms a preset angle with the first preset direction, the second transverse fin is located on the side, away from the foundation to be installed, of the first transverse fin, and the second transverse fin and the first transverse fin are oppositely arranged in a spaced mode so that a first evaporation cavity can be formed between the first transverse fin and the second transverse fin; wherein the first transverse fin is provided with a second evaporation cavity and a circulation opening communicated with the second evaporation cavity, and the circulation opening is communicated with the first evaporation cavity, so that a refrigerant in the first evaporation cavity flows into the second evaporation cavity through the circulation opening. By means of the technical scheme, the problem that in the prior art, the heat exchange performance of a heat exchange tube is poor can be solved.

Description

Technical Field

[0001] The present invention relates to the technical field of heat exchange fins, and in particular, to a heat exchange fin, a heat exchange tube, a heat exchanger, and an air conditioner. Background Art

[0002] Currently, during the operation of a falling film evaporator, liquid refrigerant will fall film and evaporate into gaseous refrigerant on the surface of the heat exchange tube, and the heat required for evaporation is provided by the heat transfer of the hot fluid in the heat exchange tube to the tube wall. Therefore, the heat exchange performance of the falling film evaporator is greatly affected by the structure of the heat exchange tube.

[0003] However, the heat exchange tubes of falling film evaporators in the prior art usually adopt a T-shaped fin design. This fin structure can achieve efficient falling film evaporation when the liquid film thickness outside the tube is small. However, when the liquid film thickness outside the tube is large, the T-shaped fins cannot provide sufficient heat exchange area and evaporation chamber structure for generating bubbles, resulting in the liquid film attached to the fins outside the heat exchange tube being unable to evaporate efficiently, affecting the overall heat exchange performance of the heat exchange tube. Summary of the Invention

[0004] The main object of the present invention is to provide a heat exchange fin, a heat exchange tube, a heat exchanger, and an air conditioner to solve the problem of poor heat exchange performance of the heat exchange tube in the prior art.

[0005] To achieve the above object, according to one aspect of the present invention, a heat exchange fin is provided, including:

[0006] Vertical fins extending along a first preset direction on a to-be-installed base;

[0007] First horizontal fins and second horizontal fins, both extending along a second preset direction that forms a preset angle with the first preset direction on the vertical fins. The second horizontal fin is located on the side of the first horizontal fin away from the to-be-installed base. The second horizontal fin is opposite to and spaced from the first horizontal fin to form a first evaporation chamber between the first horizontal fin and the second horizontal fin;

[0008] Wherein, the first horizontal fin has a second evaporation chamber and a communication port connected to the second evaporation chamber. The communication port is connected to the first evaporation chamber so that the refrigerant in the first evaporation chamber flows into the second evaporation chamber through the communication port.

[0009] Further, the first horizontal fin is opposite to and spaced from the to-be-installed base to form a third evaporation chamber between the first horizontal fin and the to-be-installed base;

[0010] The first horizontal fin also has an outflow port spaced from the communication port. Both the third evaporation chamber and the second evaporation chamber are connected to the outflow port.

[0011] Further, the first horizontal fin includes a top wall, a side wall, and a bottom wall connected in sequence. The top wall is opposite to the second horizontal fin, and the bottom wall is opposite to the to-be-installed base; wherein:

[0012] The circulation port is arranged on the top wall, and the outflow port is arranged on the side wall; and / or,

[0013] There are multiple outflow ports, and the multiple outflow ports are arranged at intervals; and / or,

[0014] The outflow port is a rectangular port, the long side of the rectangular port is greater than or equal to 0.1 mm and less than or equal to 0.3 mm; the short side of the rectangular port is greater than or equal to 0.01 mm and less than or equal to 0.04 mm.

[0015] Furthermore, there are multiple second evaporation chambers, the multiple second evaporation chambers are arranged at intervals, there are multiple circulation ports, and the multiple circulation ports and the multiple second evaporation chambers are arranged in one-to-one correspondence; and / or,

[0016] The minimum distance between the side of the second horizontal fin away from the first horizontal fin and the side of the first horizontal fin close to the second horizontal fin is greater than or equal to 0.05 mm and less than or equal to 0.15 mm; and / or,

[0017] The circulation port is a cross-shaped structure, the circulation port includes a first port part and a second port part that are perpendicular to each other, and the length of the first port part is greater than the length of the second port part; the length of the first port part is greater than or equal to 0.2 mm and less than or equal to 0.5 mm, and the minimum width of the first port part or the minimum width of the second port part is greater than or equal to 0.01 mm and less than or equal to 0.05 mm.

[0018] Furthermore, the heat exchange fin further includes a fin platform, the fin platform extends along a second preset direction and is arranged on the side of the vertical fin away from the foundation to be installed, at least part of the fin platform is opposite to and spaced from the second horizontal fin to form a fourth evaporation chamber between at least part of the fin platform and the second horizontal fin; wherein:

[0019] There are multiple fin platforms, the multiple fin platforms are arranged at intervals along the second preset direction, and a circulation gap is formed between adjacent two fin platforms to enable the refrigerant to flow into the fourth evaporation chamber through the circulation gap; or,

[0020] A through port is arranged on the fin platform, and the through port is communicated with the fourth evaporation chamber.

[0021] Furthermore, a communication port is arranged on the second horizontal fin, and both the fourth evaporation chamber and the first evaporation chamber are communicated with the communication port; wherein:

[0022] At least part of the communication port is arranged opposite to the circulation port; and / or,

[0023] The communication port has a cross-shaped structure. The communication port includes a third port and a fourth port that are perpendicular to each other. The length of the third port is greater than the length of the fourth port. The length of the third port is greater than or equal to 0.2 mm and less than or equal to 0.5 mm. The minimum width of the third port or the minimum width of the fourth port is greater than or equal to 0.01 mm and less than or equal to 0.05 mm.

[0024] Furthermore, the heat exchange fin further includes:

[0025] Micro vertical fins, which are arranged on the second horizontal fin along a first preset direction and are located on the side of the second horizontal fin away from the first horizontal fin. The micro vertical fins are opposite to and spaced from the vertical fins. The vertical fins, the micro vertical fins, and the second horizontal fin jointly enclose a fourth evaporation chamber.

[0026] Furthermore, the heat exchange fin further includes micro horizontal fins, which are arranged on the micro vertical fins along a second preset direction and are located on the side of the micro vertical fins away from the vertical fins; and / or,

[0027] Both the first horizontal fin and the second horizontal fin are inserted into the vertical fin. The two ends of the first horizontal fin respectively protrude from the opposite sides of the vertical fin. The two ends of the second horizontal fin respectively protrude from the opposite sides of the vertical fin; there are two micro vertical fins, and one of the two micro vertical fins is arranged at one end of the second horizontal fin, and the other micro vertical fin is arranged at the other end of the second horizontal fin.

[0028] Furthermore, the heat exchange fin further includes a fin platform, which is arranged on the side of the vertical fin away from the installation base along the second preset direction. At least part of the fin platform is opposite to and spaced from the second horizontal fin. The fin platform, the vertical fin, the micro vertical fin, and the second horizontal fin jointly enclose a fourth evaporation chamber; the fin platform includes a first fin platform and a second fin platform. The first fin platform is fixedly connected to the vertical fin, and the second fin platform is fixedly connected to the micro vertical fin; wherein:

[0029] The extension plane where the surface of the first fin platform away from the vertical fin is located coincides with the extension plane where the surface of the second fin platform away from the micro vertical fin is located; and / or,

[0030] The first fin platform and the second fin platform are spaced apart. The side surface of the first fin platform close to the second fin platform is opposite to and parallel to the side surface of the second fin platform close to the first fin platform; and / or,

[0031] The first fin platform has a rhombus structure, and the second fin platform has a triangular structure or a rhombus structure.

[0032] According to another aspect of the present invention, there is provided a heat exchange tube, which includes a tube body and the above-mentioned heat exchange fin. The outer wall of the tube body forms an installation base to be installed.

[0033] Further, the first transverse fin of the heat exchange fin is opposite to and spaced from the outer wall of the tube body. The heat exchange tube further includes a convex portion provided at the outer wall of the tube body. The convex portion encloses an inner cavity. One end of the convex portion away from the tube body encloses an opening communicating with the inner cavity, and the opening is opposite to the first transverse fin. Among them:

[0034] The height of the convex portion in the first preset direction is greater than or equal to 0.05 mm and less than or equal to 0.2 mm; and / or,

[0035] The convex portion is of a cylindrical structure, and the diameter of the inner cavity is greater than or equal to 0.05 mm and less than or equal to 0.2 mm; and / or,

[0036] There are multiple convex portions, and the multiple convex portions are spaced from each other.

[0037] Further, there are multiple heat exchange fins, and the multiple heat exchange fins are spaced along the circumferential direction of the tube body. There are multiple convex portions, and the multiple convex portions are spaced along the circumferential direction of the tube body between two adjacent heat exchange fins to form a convex portion group. There are multiple convex portion groups, and the multiple convex portion groups are spaced along the axial direction of the tube body. Among them, the number of convex portions is greater than or equal to 1 and less than or equal to 4; the number of convex portion groups is greater than or equal to 100 and less than or equal to 600; and / or,

[0038] The tube body includes a first tube wall and a second tube wall arranged oppositely. Along the vertical direction, the first tube wall is above the second tube wall. The convex portion is used to be arranged on the first tube wall and the second tube wall. Among them, the central angle corresponding to the first tube wall is greater than or equal to 40° and less than or equal to 180°, and the central angle corresponding to the second tube wall is greater than or equal to 20° and less than or equal to 60°.

[0039] According to another aspect of the present invention, a heat exchanger is provided, including: the above-mentioned heat exchange tube.

[0040] According to still another aspect of the present invention, an air conditioner is provided, including: the above-mentioned heat exchange tube.

[0041] Applying the technical solution of the present invention, through the first evaporation chamber formed between the first horizontal fin and the second horizontal fin and the second evaporation chamber in the first horizontal fin, steam is allowed to form and rise inside the evaporation chamber, reducing the time for bubbles to stay on the surface of the heat exchange fin structure, thereby improving the heat transfer coefficient. Through the flow ports provided on the first horizontal fin, the refrigerant in the first evaporation chamber can flow into the second evaporation chamber, which increases the contact area and path between the refrigerant and the fins, thereby enhancing the heat exchange efficiency. Especially in the case of a relatively thick liquid film, this structure allows the refrigerant to be more evenly distributed and utilize the entire surface of the heat exchange fins for evaporation. This structure of multiple evaporation chambers further increases the heat exchange area of the heat exchange fins and improves the heat exchange performance. In addition, by arranging the second evaporation chamber inside the first horizontal fin, it helps the refrigerant to fully flow into the second evaporation chamber and fill the second evaporation chamber, thereby achieving an almost full liquid evaporation effect inside the second evaporation chamber. In the full liquid state, the contact area between the fluid medium and the chamber wall increases, and the heat exchange efficiency improves. Since the thermal conductivity of the liquid is usually higher than that of the gas, full liquid evaporation can transfer heat energy from the fluid to the chamber wall more quickly and then to the external environment, ensuring a more uniform temperature distribution inside the evaporation chamber and avoiding local overheating or overcooling. Therefore, through the technical solution of the present invention, the problem of poor heat exchange performance of the heat exchange tubes in the prior art can be solved. BRIEF DESCRIPTION OF THE DRAWINGS

[0042] The specification drawings forming a part of this application are used to provide a further understanding of the present invention. The schematic embodiments of the present invention and their descriptions are used to explain the present invention and do not constitute an improper limitation of the present invention. In the drawings:

[0043] Figure 1 The partial structural schematic diagram of the heat exchange tube provided according to a specific embodiment of the present invention is shown;

[0044] Figure 2 Shown is Figure 1 The enlarged schematic diagram of the structure at A in

[0045] Figure 3 The partial structural schematic diagram of the heat exchange tube provided according to a specific embodiment of the present invention is shown;

[0046] Figure 4 The partial structural cross-sectional schematic diagram of the first horizontal fin and the vertical fin provided according to a specific embodiment of the present invention is shown;

[0047] Figure 5 The front view of the partial structure of the heat exchange tube provided according to a specific embodiment of the present invention is shown;

[0048] Figure 6 The top view of the first horizontal fin provided according to a specific embodiment of the present invention is shown;

[0049] Figure 7 Shows a top view of a second transverse fin provided according to a specific embodiment of the present invention;

[0050] Figure 8 Shows a top view of a partial structure of a heat exchange tube provided according to a specific embodiment of the present invention;

[0051] Figure 9 Shows a schematic diagram of the positional relationship between a tube body and a convex portion provided according to a specific embodiment of the present invention.

[0052] Among them, the above-mentioned drawings include the following reference numerals:

[0053] 1. Vertical fin;

[0054] 2. First transverse fin; 21. Second evaporation chamber; 22. Flow port; 221. First port; 222. Second port; 23. Outlet; 201. Top wall; 202. Side wall; 203. Bottom wall;

[0055] 3. Second transverse fin; 31. Communication port; 311. Third port; 312. Fourth port;

[0056] 4. First evaporation chamber;

[0057] 5. Third evaporation chamber;

[0058] 6. Fin platform; 61. Flow gap; 62. First fin platform; 63. Second fin platform; 64. Third fin platform;

[0059] 7. Fourth evaporation chamber;

[0060] 8. Micro vertical fin;

[0061] 9. Micro transverse fin;

[0062] 10. Tube body; 101. First tube wall; 102. Second tube wall;

[0063] 11. Convex portion; 111. Opening; 112. Convex portion group;

[0064] 12. Liquid film. Detailed implementation manners

[0065] It should be noted that, without conflict, the embodiments in the present application and the features in the embodiments may be combined with each other. The present invention will be described in detail below with reference to the drawings and in combination with the embodiments.

[0066] Such as Figures 1 to 9As shown in the figure, an embodiment of the present invention provides a heat exchange fin. The heat exchange fin includes a vertical fin 1, a first horizontal fin 2, and a second horizontal fin 3. The vertical fin 1 extends along a first preset direction and is arranged on the foundation to be installed; both the first horizontal fin 2 and the second horizontal fin 3 extend along a second preset direction which is at a preset angle to the first preset direction and are arranged on the vertical fin 1. The second horizontal fin 3 is located on the side of the first horizontal fin 2 away from the foundation to be installed. The second horizontal fin 3 is opposite to and spaced from the first horizontal fin 2 to form a first evaporation chamber 4 between the first horizontal fin 2 and the second horizontal fin 3. Among them, the first horizontal fin 2 has a second evaporation chamber 21 and a circulation port 22 communicating with the second evaporation chamber 21. The circulation port 22 communicates with the first evaporation chamber 4 so that the refrigerant in the first evaporation chamber 4 flows into the second evaporation chamber 21 through the circulation port 22.

[0067] By using the heat exchange fin provided by an embodiment of the present invention, through the first evaporation chamber 4 formed between the first horizontal fin 2 and the second horizontal fin 3 and the second evaporation chamber 21 in the first horizontal fin 2, steam is allowed to form and rise inside the evaporation chamber, reducing the time for bubbles to stay on the surface of the heat exchange fin structure, thereby improving the heat transfer coefficient. Through the circulation port 22 provided on the first horizontal fin 2, the refrigerant in the first evaporation chamber 4 can flow into the second evaporation chamber 21, which increases the contact area and path between the refrigerant and the fin, thereby enhancing the heat exchange efficiency. Especially when the liquid film 12 is relatively thick, this structure allows the refrigerant to be more evenly distributed and utilize the entire surface of the heat exchange fin for evaporation. This structure of multiple evaporation chambers further increases the heat exchange area of the heat exchange fin and improves the heat exchange performance. In addition, by arranging the second evaporation chamber 21 inside the first horizontal fin 2, it helps the refrigerant to fully flow into the second evaporation chamber 21 and fill the second evaporation chamber 21, thereby achieving an almost full liquid evaporation effect inside the second evaporation chamber 21. In the full liquid state, the contact area between the fluid medium and the chamber wall increases, and the heat exchange efficiency improves. Since the thermal conductivity of the liquid is usually higher than that of the gas, full liquid evaporation can transfer heat energy from the fluid to the chamber wall more quickly and then to the external environment, ensuring a more uniform temperature distribution inside the evaporation chamber and avoiding local overheating or overcooling. Therefore, through the heat exchange fin provided by this embodiment, the problem of poor heat exchange performance of the heat exchange tube in the prior art can be solved.

[0068] Specifically, the first preset direction and the second preset direction are perpendicular to each other.

[0069] Specifically, the foundation to be installed is the tube body 10 of the heat exchange tube. The heat exchange fin is arranged on the tube body 10 of the heat exchange tube. The first preset direction is the radial direction of the cross-section of the tube body 10, and the second preset direction is the circumferential direction of the cross-section of the tube body 10. In this way, the heat exchange performance of the heat exchange tube can be improved through the setting of the heat exchange fin.

[0070] In this embodiment, the vertical fin 1, the first horizontal fin 2, and the second horizontal fin 3 are all plate-like structures. Compared with other forms of fins, the plate-like structure can provide a larger surface contact area, thereby strengthening the heat exchange between the refrigerant and the fins and improving the heat exchange efficiency.

[0071] In a specific embodiment, the vertical fin 1 is inserted into the middle of the first horizontal fin 2, and the vertical fin 1 is inserted into the middle of the second horizontal fin 3.

[0072] In an embodiment not shown, the vertical fin 1 is inserted into the middle of the first horizontal fin 2, one end of the second horizontal fin 3 is connected to the vertical fin 1, and the other end extends beyond the vertical fin 1.

[0073] In an embodiment not shown, the vertical fin 1 is inserted into the middle of the second horizontal fin 3, one end of the first horizontal fin 2 is connected to the vertical fin 1, and the other end extends beyond the vertical fin 1.

[0074] In an embodiment not shown, one end of the first horizontal fin 2 is connected to the vertical fin 1, and the other end extends beyond the vertical fin 1; one end of the second horizontal fin 3 is connected to the vertical fin 1, and the other end extends beyond the vertical fin 1. The first horizontal fin 2, the second horizontal fin 3, and the vertical fin 1 together enclose the first evaporation chamber 4.

[0075] Specifically, the included angle between the extending direction of the first horizontal fin 2 and the extending direction of the second horizontal fin 3 is greater than or equal to 0° and less than 90°.

[0076] In this embodiment, the first horizontal fin 2 and the second horizontal fin 3 are parallel to each other. In this way, the space between the parallel first horizontal fin 2 and the second horizontal fin 3 is designed as the first evaporation chamber 4. This structure is beneficial to the uniform distribution of the refrigerant in the evaporation chamber, avoiding excessive local accumulation of liquid refrigerant, and thus ensuring the uniformity and efficiency of the heat exchange process.

[0077] Specifically, the first horizontal fin 2 is opposite to and spaced from the foundation to be installed, so as to form a third evaporation chamber 5 between the first horizontal fin 2 and the foundation to be installed. The first horizontal fin 2 also has an outlet 23 spaced from the circulation port 22, and both the third evaporation chamber 5 and the second evaporation chamber 21 are communicated with the outlet 23. With such a structural arrangement, by forming multiple evaporation chambers between the fin and the pipe body 10 and inside the fin itself, the design of multiple evaporation chambers allows the refrigerant to evaporate at different levels, increasing the contact area and time of the evaporation process, further enhancing the heat exchange performance, and also being able to better control and guide the flow of the refrigerant, thereby optimizing the distribution of the refrigerant on the surface of the heat exchange pipe and improving the evaporation efficiency.

[0078] In this embodiment, the first transverse fin 2 includes a top wall 201, a side wall 202, and a bottom wall 203 that are sequentially connected. The top wall 201 is disposed opposite to the second transverse fin 3, and the bottom wall 203 is disposed opposite to the foundation to be installed. The circulation port 22 is provided on the top wall 201, and the outflow port 23 is provided on the side wall 202. With such a structural arrangement, the design of the circulation port 22 on the top wall 201 and the outflow port 23 on the side wall 202 ensures the flow of the refrigerant. By providing the circulation port 22 and the outflow port 23 at different positions on the first transverse fin 2, the distribution and flow of the refrigerant in different evaporation chambers can be managed, thereby improving the control ability of the refrigerant evaporation process. When the refrigerant flows out from the outflow port 23, it can also impact the fluid in the lower evaporation chamber, continuously agitating the area, enhancing the fluid turbulence intensity here, and improving the heat transfer performance.

[0079] Specifically, there are multiple outflow ports 23, and the multiple outflow ports 23 are arranged at intervals. In this way, the design of the multiple outflow ports 23 ensures that the refrigerant can flow out from different positions, contributing to its uniform distribution on the surface of the heat exchange fins and avoiding the problem of local overheating. The outflow ports 23 arranged at intervals can also improve the hydrodynamic characteristics, prevent the mutual interference when the refrigerant flows out, ensure the smooth flow of the refrigerant, reduce the flow resistance, and thus increase the flow rate of the refrigerant to facilitate better agitation of the refrigerant in the third evaporation chamber 5.

[0080] Specifically, the outflow port 23 is a rectangular port or a circular port.

[0081] In a specific embodiment, the outflow port 23 is a rectangular port. The long side of the rectangular port is greater than or equal to 0.1 mm and less than or equal to 0.3 mm; the short side of the rectangular port is greater than or equal to 0.01 mm and less than or equal to 0.04 mm. The size design of the outflow port 23 directly affects the flow characteristics of the fluid. The specific size range of the rectangular port helps to accurately control the outflow flow rate of the refrigerant, thereby optimizing the evaporation process.

[0082] In this embodiment, there are multiple second evaporation chambers 21, and the multiple second evaporation chambers 21 are arranged at intervals. There are multiple circulation ports 22, and the multiple circulation ports 22 and the multiple second evaporation chambers 21 are arranged in one-to-one correspondence. With such a structural arrangement, the design of the multiple second evaporation chambers 21 provides more evaporation space, allowing for multi-point evaporation simultaneously, thereby improving the evaporation efficiency of the refrigerant. The multiple second evaporation chambers 21 reduce the volume of the evaporation chamber, making it easier to be filled with the entering refrigerant, and thus achieving the effect of full liquid evaporation and improving the heat transfer efficiency.

[0083] Specifically, as Figure 4 shown, the vertical fin 1 divides the inner cavity space of the first transverse fin 2 into two second evaporation chambers 21. Through the division by the vertical fin 1, the surface area of the inner cavity of the first transverse fin 2 is increased, and these surface areas can serve as additional areas for refrigerant evaporation, further enhancing the heat transfer ability.

[0084] Specifically, the minimum distance between the side of the second horizontal fin 3 away from the first horizontal fin 2 and the side of the first horizontal fin 2 close to the second horizontal fin 3 is greater than or equal to 0.05 mm and less than or equal to 0.15 mm. In this way, the minimum distance between the first horizontal fin 2 and the second horizontal fin 3 is defined, ensuring that the thickness of the first evaporation chamber 4 is appropriate, which can not only provide sufficient evaporation space but also not increase the thermal resistance due to the over-thick chamber.

[0085] As Figure 5 shown, the minimum distance between the side of the second horizontal fin 3 away from the first horizontal fin 2 and the side of the first horizontal fin 2 close to the second horizontal fin 3 is D, and 0.05 mm ≤ D ≤ 0.15 mm.

[0086] Specifically, the circulation port 22 is a circular port, a rectangular port or a cross-shaped port.

[0087] In a specific embodiment, the circulation port 22 is of a cross-shaped structure. The circulation port 22 includes a first port portion 221 and a second port portion 222 that are perpendicular to each other. The length of the first port portion 221 is greater than the length of the second port portion 222; the length of the first port portion 221 is greater than or equal to 0.2 mm and less than or equal to 0.5 mm, and the minimum width of the first port portion 221 or the minimum width of the second port portion 222 is greater than or equal to 0.01 mm and less than or equal to 0.05 mm. With such a structural arrangement, the cross-shaped circulation port 22 is beneficial for the liquid refrigerant to overcome the surface tension and enter the evaporation chamber, promoting the flow of the refrigerant. In particular, the arrangement of the first port portion 221 and the second port portion 222 enables the liquid refrigerant to be evenly dispersed in multiple directions when entering the second evaporation chamber 21, thereby forming a more uniform liquid film 12 in the evaporation chamber, which is beneficial to improving the heat exchange efficiency.

[0088] As Figure 6 shown, the length of the first port portion 221 is L1, and L1 is also equivalent to the overall length of the circulation port 22. The minimum width of the first port portion 221 is W1, and the minimum width of the second port portion 222 is W2. 0.2 mm ≤ L1 ≤ 0.5 mm; 0.01 mm ≤ W1 ≤ 0.05 mm; 0.01 mm ≤ W2 ≤ 0.05 mm.

[0089] As Figure 1As shown, in this embodiment, the heat exchange fin further includes a fin platform 6. The fin platform 6 extends along a second preset direction and is disposed on the side of the vertical fin 1 away from the foundation to be installed. At least a part of the fin platform 6 is opposite to and spaced from the second horizontal fin 3, so as to form a fourth evaporation chamber 7 between at least a part of the fin platform 6 and the second horizontal fin 3. With such a structural arrangement, the fin platform 6 makes the side of the vertical fin 1 away from the foundation to be installed form a flat surface, thereby realizing the function of uniform flow and liquid separation for the refrigerant falling onto the heat exchange fin, which is beneficial to the rapid spread of the dripping liquid refrigerant in the axial and circumferential directions of the heat exchange tube. The interval between the fin platform 6 and the second horizontal fin 3 forms the fourth evaporation chamber 7, which provides additional flow space and path for the refrigerant, increases the heat exchange area, also helps to optimize the distribution of the refrigerant on the heat exchange fin, reduces the phenomenon of local over-concentration, and ensures the uniform evaporation of the refrigerant.

[0090] In a specific embodiment, there are multiple fin platforms 6. The multiple fin platforms 6 are spaced along the second preset direction, and a flow gap 61 is formed between two adjacent fin platforms 6, so that the refrigerant flows into the fourth evaporation chamber 7 through the flow gap 61. By arranging the multiple fin platforms 6 at intervals, multiple flow gaps 61 are formed, enabling the refrigerant to flow more uniformly on the surface of the fin and quickly flow into the evaporation chamber below the fin platform 6, thereby improving the heat exchange efficiency.

[0091] In an embodiment not shown, a through-hole is provided on the fin platform 6, and the through-hole is communicated with the fourth evaporation chamber 7. The design of the through-hole enables more refrigerant to directly enter the fourth evaporation chamber 7, makes full use of the space of the evaporation chamber, improves the heat exchange capacity of the evaporation chamber, and helps to enhance the overall heat exchange efficiency.

[0092] As Figure 2 and Figure 8 shown, the fin platform 6 includes a first fin platform 62, a second fin platform 63, and a third fin platform 64. The first fin platform 62, the second fin platform 63, and the third fin platform 64 are all spaced from each other, so as to form a flow gap 61 between each fin platform 6.

[0093] Specifically, the side of the first fin platform 62 away from the vertical fin 1, the side of the second fin platform 63 away from the vertical fin 1, and the side of the third fin platform 64 away from the vertical fin 1 are all planar structures. In this way, the fin platform 6 with a planar structure provides more contact surfaces for the refrigerant, which is beneficial to improving the heat exchange efficiency between the refrigerant and the fin. And the surface of the fin platform 6 with a planar structure helps to reduce the resistance when the refrigerant flows through, improves the hydrodynamic characteristics of the refrigerant on the fin, ensures the smoothness and uniformity of the refrigerant flow, and further helps the refrigerant to quickly spread on the surface of the fin platform 6.

[0094] Specifically, the first fin platform 62, the second fin platform 63, and the third fin platform 64 are all plate-like structures.

[0095] In an embodiment not shown, the sides of the first fin platform 62 away from the vertical fin 1, the sides of the second fin platform 63 away from the vertical fin 1, and the sides of the third fin platform 64 away from the vertical fin 1 are all curved surface structures.

[0096] As Figure 2 and Figure 3 shown, a communication port 31 is provided on the second horizontal fin 3, and both the fourth evaporation chamber 7 and the first evaporation chamber 4 are connected to the communication port 31. With such a structural arrangement, the design of the communication port 31 establishes a direct fluid channel between the fourth evaporation chamber 7 and the first evaporation chamber 4, which is beneficial to the free flow and circulation of the refrigerant between different evaporation chambers and improves the utilization efficiency of the refrigerant. Through the communication port 31, the refrigerant can be more evenly distributed in each evaporation chamber, avoiding local overheating or overcooling, and improving the efficiency and stability of the entire heat exchange system.

[0097] Specifically, at least a part of the communication port 31 is disposed opposite to the flow port 22. In this way, the oppositely disposed communication port 31 and flow port 22 help to improve the hydrodynamic conditions, promote the smooth flow of the refrigerant between the evaporation chamber and the fins, and reduce the flow resistance.

[0098] Specifically, the communication port 31 is a circular port, a rectangular port or a cross-shaped port.

[0099] In a specific embodiment, the communication port 31 is a cross-shaped structure. The communication port 31 includes a third port part 311 and a fourth port part 312 that are perpendicular to each other. The length of the third port part 311 is greater than the length of the fourth port part 312. The length of the third port part 311 is greater than or equal to 0.2 mm and less than or equal to 0.5 mm, and the minimum width of the third port part 311 or the minimum width of the fourth port part 312 is greater than or equal to 0.01 mm and less than or equal to 0.05 mm. With such a structural arrangement, the cross-shaped communication port 31 is beneficial for the liquid refrigerant to overcome the surface tension and enter the evaporation chamber, promoting the flow of the refrigerant.

[0100] As Figure 7 shown, the length of the third port part 311 is L2, and L2 is also equivalent to the overall length of the communication port 31. The minimum width of the third port part 311 is W3, and the minimum width of the fourth port part 312 is W4. 0.2 mm ≤ L2 ≤ 0.5 mm; 0.01 mm ≤ W3 ≤ 0.05 mm; 0.01 mm ≤ W4 ≤ 0.05 mm.

[0101] In a specific embodiment, the communication port 31 has the same shape and size as the flow port 22.

[0102] As Figure 2As shown, in this embodiment, the heat exchange fin further includes micro vertical fins 8. The micro vertical fins 8 extend along a first preset direction and are arranged on the second horizontal fin 3 on the side away from the first horizontal fin 2. The micro vertical fins 8 are opposite to and spaced from the vertical fins 1. The vertical fins 1, the micro vertical fins 8, and the second horizontal fin 3 jointly enclose a fourth evaporation chamber 7. With such a structural arrangement, the micro vertical fins 8, the vertical fins 1, and the second horizontal fin 3 jointly enclose the fourth evaporation chamber 7, increasing the evaporation space of the refrigerant, thereby improving the total heat exchange area and heat exchange efficiency.

[0103] Specifically, the heat exchange fin further includes micro horizontal fins 9. The micro horizontal fins 9 extend along a second preset direction and are arranged on the micro vertical fins 8 on the side away from the vertical fins 1. With such a structural arrangement, by adding the micro horizontal fins 9, the flow and contact area of the refrigerant can be more precisely controlled, increasing the heat exchange area of the heat exchange fin, and thereby improving the heat exchange efficiency.

[0104] In a specific embodiment, both the first horizontal fin 2 and the second horizontal fin 3 are inserted into the vertical fin 1. The two ends of the first horizontal fin 2 respectively protrude from the opposite sides of the vertical fin 1, and the two ends of the second horizontal fin 3 respectively protrude from the opposite sides of the vertical fin 1; there are two micro vertical fins 8, and one of the two micro vertical fins 8 is arranged at one end of the second horizontal fin 3, and the other micro vertical fin 8 is arranged at the other end of the second horizontal fin 3. In this way, the insertion layout of the first horizontal fin 2 and the second horizontal fin 3 and their protrusion from both sides of the vertical fin 1 can enhance the structural rigidity of the heat exchange fin, prevent the fin from deforming due to refrigerant flow or temperature change, and improve the stability and reliability during long-term use.

[0105] Specifically, the vertical fins 1 and the micro vertical fins 8 are parallel to each other. The first horizontal fin 2, the second horizontal fin 3, and the micro horizontal fins 9 are parallel to each other.

[0106] Specifically, the heat exchange fin further includes a fin platform 6. The fin platform 6 extends along a second preset direction on the side of the vertical fin 1 away from the installation base to be installed. At least part of the fin platform 6 is opposite to and spaced from the second horizontal fin 3. The fin platform 6, the vertical fin 1, the micro vertical fins 8, and the second horizontal fin 3 jointly enclose the fourth evaporation chamber 7; the fin platform 6 includes a first fin platform 62 and a second fin platform 63. The first fin platform 62 is fixedly connected to the vertical fin 1, and the second fin platform 63 is fixedly connected to the micro vertical fin 8; wherein, the extension plane where the surface of the first fin platform 62 away from the vertical fin 1 is located coincides with the extension plane where the surface of the second fin platform 63 away from the micro vertical fin 8 is located. With such a structural arrangement, the design that the extension planes of the first fin platform 62 and the second fin platform 63 coincide helps to improve the hydrodynamic characteristics, avoid the refrigerant falling on the uneven fin platform 6, which affects the uniform flow and liquid separation of the refrigerant, thereby reducing the resistance when the refrigerant flows, and promoting the uniform distribution and efficient evaporation of the refrigerant.

[0107] Specifically, the heat exchange fin further includes a fin platform 6. The fin platform 6 extends along a second preset direction and is arranged on the side of the vertical fin 1 away from the foundation to be installed. At least part of the fin platform 6 is opposite to and spaced from the second horizontal fin 3. The fin platform 6, the vertical fin 1, the micro-vertical fin 8, and the second horizontal fin 3 jointly enclose a fourth evaporation chamber 7. The fin platform 6 includes a first fin platform 62 and a second fin platform 63. The first fin platform 62 is fixedly connected to the vertical fin 1, and the second fin platform 63 is fixedly connected to the micro-vertical fin 8. Among them, the first fin platform 62 and the second fin platform 63 are spaced apart, and the side surface of the first fin platform 62 close to the second fin platform 63 is opposite to and parallel to the side surface of the second fin platform 63 close to the first fin platform 62. With such a structural arrangement, the parallel side surface design of the first fin platform 62 and the second fin platform 63 helps to optimize the hydrodynamic characteristics. This parallel arrangement reduces the turbulence during the refrigerant flow, provides a smoother flow path, thereby helping the refrigerant to be more evenly distributed and flow in the fin structure, reducing the flow resistance, and improving the flow efficiency of the fluid.

[0108] Specifically, the heat exchange fin further includes a fin platform 6. The fin platform 6 extends along a second preset direction and is arranged on the side of the vertical fin 1 away from the foundation to be installed. At least part of the fin platform 6 is opposite to and spaced from the second horizontal fin 3. The fin platform 6, the vertical fin 1, the micro-vertical fin 8, and the second horizontal fin 3 jointly enclose a fourth evaporation chamber 7. The fin platform 6 includes a first fin platform 62 and a second fin platform 63. The first fin platform 62 is fixedly connected to the vertical fin 1, and the second fin platform 63 is fixedly connected to the micro-vertical fin 8. Among them, the first fin platform 62 has a rhombus structure, and the second fin platform 63 has a triangular structure or a rhombus structure.

[0109] In this embodiment, the fin platform 6 includes a first fin platform 62, a second fin platform 63, and a third fin platform 64. Among them, the third fin platform 64 is fixedly connected to the micro-vertical fin 8. The second fin platform 63 and the third fin platform 64 are alternately and spacedly arranged on the micro-vertical fin 8. The alternately and spacedly arranged second fin platform 63 and third fin platform 64 help to evenly disperse the refrigerant and avoid local overload. This layout ensures that the refrigerant can be evenly distributed along the entire length of the micro-vertical fin 8, improving the evaporation efficiency and heat exchange performance.

[0110] Specifically, there are multiple first fin platforms 62, and the multiple first fin platforms 62 are spaced along the circumferential direction of the tube body 10 on the vertical fin 1. There are multiple second fin platforms 63 and multiple third fin platforms 64, and the multiple second fin platforms 63 and the multiple third fin platforms 64 are alternately and spaced along the circumferential direction of the tube body 10 on the micro-vertical fin 8. The distribution of the multiple fin platforms 6 can significantly increase the heat exchange area, improve the contact opportunity between the fluid and the fin, thereby enhancing the heat exchange efficiency. The spaced arrangement of the multiple fin platforms 6 helps to improve the distribution of the refrigerant, ensuring that the refrigerant can evenly cover the outer surface of the tube body 10, avoiding excessive accumulation of the refrigerant in local areas, and improving the uniformity of evaporation.

[0111] Such as Figure 1 and Figure 8As shown, in a specific embodiment, the first fin platform 62 is a rhombus structure, the second fin platform 63 is a rhombus structure, and the third fin platform 64 is a triangular structure. The first fin platform 62 is located at the upper part of the vertical fin 1, and each vertical fin 1 has two first fin platforms 62 (the two first fin platforms 62 are symmetrically distributed in the circumferential direction of the heat exchange tube and there is a certain gap between them). The second fin platform 63 is located at the upper part of the micro-vertical fin 8 and is located on two micro-vertical fins 8 between two adjacent vertical fins 1. The third fin platform 64 is located at the middle position above the micro-vertical fin 8, and the two third fin platforms 64 are symmetrically distributed in the axial direction of the heat exchange tube. The rhombus fin platform and the triangular fin platform have excellent flow equalization and liquid distribution functions, which are beneficial to the spread of the dripping liquid refrigerant on the surface of the heat exchange fin.

[0112] In an embodiment not shown, the first fin platform 62, the second fin platform 63, and the third fin platform 64 are all circular structures.

[0113] In an embodiment not shown, the first fin platform 62, the second fin platform 63, and the third fin platform 64 are all oval structures.

[0114] In an embodiment not shown, the first fin platform 62, the second fin platform 63, and the third fin platform 64 are all rectangular structures.

[0115] Specifically, the first fin platform 62 and the vertical fin 1 are integrally provided. The second fin platform 63, the third fin platform 64, and the micro-vertical fin 8 are integrally provided.

[0116] Specifically, the fin platform 6, the vertical fin 1, the first horizontal fin 2, the second horizontal fin 3, the micro-vertical fin 8, and the micro-horizontal fin 9 together form the unit framework of the heat exchange fin.

[0117] An embodiment of the present invention provides a heat exchange tube, which includes a tube body 10 and the heat exchange fin provided in the above embodiment, and the outer wall of the tube body 10 forms a foundation for installation.

[0118] Using the heat exchange tube provided by an embodiment of the present invention, through the first evaporation chamber 4 formed between the first transverse fin 2 and the second transverse fin 3 and the second evaporation chamber 21 in the first transverse fin 2, steam is allowed to form and rise inside the evaporation chamber, reducing the time for bubbles to stay on the surface of the heat exchange fin structure, thereby improving the heat transfer coefficient. Through the flow port 22 provided on the first transverse fin 2, the refrigerant in the first evaporation chamber 4 can flow into the second evaporation chamber 21, which increases the contact area and path between the refrigerant and the fins, thereby enhancing the heat exchange efficiency. Especially when the liquid film 12 is relatively thick, this structure allows the refrigerant to be more evenly distributed and utilize the entire surface of the heat exchange fins for evaporation. This structure of the multi-layer evaporation chamber further increases the heat exchange area of the heat exchange fins and improves the heat exchange performance. In addition, by arranging the second evaporation chamber 21 inside the first transverse fin 2, it helps the refrigerant to fully flow into and fill the second evaporation chamber 21, thereby achieving an almost full liquid evaporation effect inside the second evaporation chamber 21. In the full liquid state, the contact area between the fluid medium and the chamber wall increases, and the heat exchange efficiency improves. Since the thermal conductivity of the liquid is usually higher than that of the gas, full liquid evaporation can transfer heat energy from the fluid to the chamber wall more quickly and then to the external environment, ensuring a more uniform temperature distribution inside the evaporation chamber and avoiding local overheating or overcooling. Therefore, through the heat exchange tube provided by this embodiment, the problem of poor heat exchange performance of the heat exchange tube in the prior art can be solved.

[0119] Specifically, the first transverse fin 2 of the heat exchange fin is opposite to and spaced from the outer wall of the tube body 10. The heat exchange tube further includes a protrusion 11, and the protrusion 11 is arranged at the outer wall of the tube body 10; the protrusion 11 encloses an inner cavity, and one end of the protrusion 11 away from the tube body 10 encloses an opening 111 communicating with the inner cavity, and the opening 111 is arranged opposite to the first transverse fin 2. With such a structural arrangement, the presence of the protrusion 11 increases the density of evaporation point vaporization cores that can be generated at the bottom of the third evaporation chamber 5, which is beneficial to reducing the thickness of the liquid film 12 in the top and bottom regions in the circumferential direction of the heat exchange tube and improving the heat exchange performance at this location. At the same time, it is beneficial to guide the remaining liquid refrigerant at the bottom of the heat exchange tube to form a liquid column, further reducing the area of the region with a relatively large thickness of the liquid film 12 at this location and reducing the heat transfer resistance.

[0120] Specifically, the height of the protrusion 11 in the first preset direction is greater than or equal to 0.05 mm and less than or equal to 0.2 mm. The appropriate height of the protrusion 11 can control the thickness of the liquid film 12 formed by the refrigerant at the first transverse fin 2, reduce the thermal resistance, and thus improve the heat exchange efficiency. An overly thick liquid film 12 will increase the resistance to heat transfer, while the appropriate height of the protrusion 11 helps to form a uniform and thin liquid film 12, which is beneficial to heat transfer.

[0121] Specifically, the protrusion 11 is of a cylindrical structure or a rectangular structure.

[0122] Specifically, the convex portion 11 has a cylindrical structure, and the diameter of the inner cavity is greater than or equal to 0.05 mm and less than or equal to 0.2 mm. In this way, the appropriate diameter range can promote the formation of fine bubbles during the evaporation of the refrigerant, and these bubbles can easily escape from the opening 111, avoiding the aggregation of bubbles and reducing the heat exchange performance.

[0123] Specifically, there are multiple convex portions 11, and the multiple convex portions 11 are arranged at intervals. In this way, the density of the evaporation point vaporization cores that can be generated at the bottom of the third evaporation chamber 5 is effectively increased, which is beneficial to reducing the thickness of the liquid film 12 in the top and bottom regions in the circumferential direction of the heat exchange tube and improving the heat exchange performance at this place.

[0124] In this embodiment, there are multiple heat exchange fins, and the multiple heat exchange fins are arranged at intervals in the circumferential direction of the tube body 10; there are multiple convex portions 11, and the multiple convex portions 11 are arranged at intervals in the circumferential direction of the tube body 10 between two adjacent heat exchange fins to form a convex portion group 112, and there are multiple convex portion groups 112, and the multiple convex portion groups 112 are arranged at intervals in the axial direction of the tube body 10; among them, the number of the convex portions 11 is greater than or equal to 1 and less than or equal to 4; the number of the convex portion groups 112 is greater than or equal to 100 and less than or equal to 600. With such a structural arrangement, by adjusting the number of the convex portions 11 and the convex portion groups 112, the designer can optimize the heat exchange performance according to different working environments and refrigerant types, so that it can maintain high-efficiency operation under various conditions.

[0125] Specifically, in the circumferential direction of the tube body 10, the number of the convex portions 11 is greater than or equal to 90 and less than or equal to 120.

[0126] Specifically, the multiple heat exchange fins are arranged at intervals in the circumferential direction of the tube body 10 to form fin groups, and there are multiple fin groups, and the multiple fin groups are arranged at intervals in the axial direction of the tube body 10 to form a channel gap for the liquid refrigerant to flow and the bubbles to overflow between the respective heat exchange fins.

[0127] Specifically, the multiple heat exchange fins are arranged in an array on the outer wall of the tube body 10. In the axial direction of the tube body 10, the minimum distance between two adjacent heat exchange fins is greater than or equal to 0.6 mm and less than or equal to 0.8 mm. In the circumferential direction of the tube body 10, the minimum distance between two adjacent heat exchange fins is greater than or equal to 0.6 mm and less than or equal to 0.8 mm.

[0128] Such as Figure 9As shown, due to the influence of the liquid gravity, the thickness of the liquid film 12 formed by the falling film is inconsistent in the circumferential direction of the heat exchange tube. The thickness of the liquid film 12 is larger and the thermal resistance is greater in the top and bottom regions (the top and bottom in the vertical direction). The tube body 10 includes a first tube wall 101 and a second tube wall 102 which are oppositely arranged; in the vertical direction, the first tube wall 101 is located above the second tube wall 102; the convex portion 11 is used to be arranged on the first tube wall 101 and the second tube wall 102; wherein, the central angle corresponding to the first tube wall 101 is greater than or equal to 40° and less than or equal to 180°, and the central angle corresponding to the second tube wall 102 is greater than or equal to 20° and less than or equal to 60°. With such a structural arrangement, by arranging the convex portion 11 at the corresponding positions of the first tube wall 101 and the second tube wall 102, the setting efficiency of the convex portion 11 can be effectively improved, the continuity of the liquid film 12 can be more pertinently disrupted, the thickness accumulation of the liquid film 12 can be reduced, the thermal resistance can be lowered, and the heat exchange performance can be improved.

[0129] As Figure 9 shown, the central angle corresponding to the first tube wall 101 is a, and the central angle corresponding to the second tube wall 102 is b. 40° ≤ a ≤ 180°; 20° ≤ b ≤ 60°.

[0130] In a specific embodiment, a = 80° and b = 40°.

[0131] In a specific embodiment, the tube body 10 is made of red copper or copper alloy.

[0132] In a specific embodiment, the heat exchange fins are made of red copper or copper alloy.

[0133] Specifically, when the heat exchange tube is working, the liquid refrigerant drips onto the surface of the heat exchange tube and quickly spreads circumferentially and axially along the heat exchange tube under the action of the fin platforms 6. While spreading circumferentially and axially along the heat exchange tube, the liquid refrigerant also quickly flows into the upper evaporation chamber (equivalent to the fourth evaporation chamber 7), the middle evaporation chamber (equivalent to the first evaporation chamber 4 and the second evaporation chamber 21), and the lower evaporation chamber (equivalent to the third evaporation chamber 5) of the heat exchange tube through the gaps between adjacent fin platforms 6 and the gaps existing axially and circumferentially in the heat exchange fins. This helps to reduce the thickness of the liquid film 12 flowing into the lower evaporation chamber and reduce the thermal resistance at this location. Further, the micro-cylindrical tanks (equivalent to the protrusions 11) distributed at the top and bottom regions in the circumferential direction of the bottom of the lower evaporation chamber (i.e., the locations with a large liquid film 12 thickness) are conducive to further reducing the area of the region with a relatively large liquid film 12 thickness at this location and reducing the heat transfer thermal resistance. The above structure is more applicable during large-flow falling film, contributing to the high efficiency and miniaturization of the shell-and-tube falling film evaporator. At the same time, part of the liquid refrigerant flowing into the upper evaporation chamber overcomes the surface tension and flows into the corresponding middle evaporation chamber from the cross-shaped grooves (equivalent to the communication ports 31) at its bottom, achieving an almost full-liquid evaporation effect inside it. The remaining refrigerant flows out from the rectangular grooves (equivalent to the outflow ports 23) on its side. The outflowing liquid refrigerant converges into the lower evaporation chamber, continuously agitating this area, enhancing the fluid turbulence intensity here, and improving the heat transfer performance.

[0134] Specifically, the heat exchange tube in this embodiment is a falling film evaporation tube.

[0135] An embodiment of the present invention provides a heat exchanger, which includes the heat exchange tube provided in the above embodiment.

[0136] An embodiment of the present invention provides an air conditioner, which includes the heat exchange tube provided in the above embodiment.

[0137] From the above description, it can be seen that the above embodiments of the present invention achieve the following technical effects:

[0138] 1. The multi-layer structure of the heat exchange fins expands the heat transfer area on the outer surface of the heat exchange tube, strengthens its heat transfer performance, and is conducive to the high efficiency and miniaturization of the shell-and-tube falling film evaporator;

[0139] 2. The setting of the fin platforms is conducive to the liquid refrigerant quickly spreading circumferentially and axially along the heat exchange tube, improving the falling film effect;

[0140] 3. The existence of the protrusions increases the density of vaporization core evaporation points that can be generated at the bottom of the lower evaporation chamber, which is conducive to reducing the liquid film thickness at the top and bottom regions in the circumferential direction of the falling film evaporation tube and improving the heat transfer performance at this location. At the same time, it is conducive to guiding the remaining liquid refrigerant at the bottom of the heat exchange tube to form a liquid column, further reducing the area of the region with a relatively large liquid film thickness at this location and reducing the heat transfer thermal resistance;

[0141] 4. The opening of the cross-shaped structure is conducive to the liquid refrigerant overcoming the surface tension and entering the evaporation cavity, promoting the flow of the refrigerant.

[0142] 5. The arrangement of the outflow port enables the outflowing liquid refrigerant to impact the fluid in the lower evaporation cavity, continuously agitating this area, enhancing the fluid turbulence intensity here, and improving the heat exchange performance.

[0143] It should be noted that the terms used herein are only for describing specific embodiments and are not intended to limit the exemplary embodiments according to the present application. As used herein, unless the context clearly indicates otherwise, the singular forms are also intended to include the plural forms. In addition, it should be understood that when the terms "comprising" and / or "including" are used in this specification, they specify the presence of features, steps, operations, devices, components, and / or combinations thereof.

[0144] Unless otherwise specifically stated, the relative arrangements, numerical expressions, and numerical values of the components and steps set forth in these embodiments do not limit the scope of the present application. At the same time, it should be understood that for the sake of convenience of description, the dimensions of the various parts shown in the drawings are not drawn in actual proportional relationships. Technologies, methods, and devices known to those of ordinary skill in the relevant art may not be discussed in detail, but where appropriate, the said technologies, methods, and devices should be regarded as part of the specification. In all the examples shown and discussed here, any specific value should be construed as merely exemplary and not as a limitation. Therefore, other examples of the exemplary embodiments may have different values. It should be noted that like reference numerals and letters denote like items in the following drawings, and thus, once an item is defined in one drawing, it does not need to be further discussed in subsequent drawings.

[0145] In the description of the present application, it should be understood that the orientation or positional relationships indicated by orientation words such as "front, rear, upper, lower, left, right", "lateral, vertical, perpendicular, horizontal", and "top, bottom" are generally based on the orientation or positional relationships shown in the drawings, and are only for the convenience of describing the present application and simplifying the description. Without contrary description, these orientation words do not indicate and imply that the device or element referred to must have a specific orientation or be constructed and operated in a specific orientation, and thus should not be construed as limiting the protection scope of the present application; the orientation words "inside, outside" refer to the inside and outside relative to the contour of each component itself.

[0146] For ease of description, spatial relative terms such as "above", "over", "on the upper surface", "upper", etc. may be used herein to describe the spatial positional relationship of one device or feature to other devices or features as shown in the figures. It should be understood that the spatial relative terms are intended to encompass different orientations in use or operation in addition to the orientation depicted in the figures. For example, if the device in the figures is inverted, a device described as "above" or "over" other devices or structures will then be positioned "below" or "under" the other devices or structures. Thus, the exemplary term "above" can include both the orientations of "above" and "below". The device may also be positioned in other different ways (rotated 90 degrees or in other orientations), and the corresponding interpretations of the spatial relative descriptions used herein will be made accordingly.

[0147] In addition, it should be noted that the use of terms such as "first" and "second" to define components is only for the convenience of differentiating the corresponding components. Without additional statements, the above terms have no special meanings, and thus should not be construed as limiting the scope of protection of the present application.

[0148] The above are only the preferred embodiments of the present invention and are not intended to limit the present invention. For those skilled in the art, the present invention may have various modifications and changes. Any modifications, equivalent replacements, improvements, etc. made within the spirit and principle of the present invention shall be included within the scope of protection of the present invention.

Claims

1. A heat exchange fin, characterized in that: include: The vertical wing (1) is extended along a first preset direction and arranged on a foundation to be installed; The first transverse wing (2) and the second transverse wing (3) are both extended on the vertical wing (1) along a second preset direction set at a preset angle to the first preset direction, the second transverse wing (3) is located on a side of the first transverse wing (2) away from the base to be installed, and the second transverse wing (3) is opposite to the first transverse wing (2) and is spaced apart from the first transverse wing (2) to form a first evaporation chamber (4) between the first transverse wing (2) and the second transverse wing (3); The first horizontal wing (2) has a second evaporation chamber (21) and a flow port (22) connected to the second evaporation chamber (21); the flow port (22) is connected to the first evaporation chamber (4) so ​​that the refrigerant in the first evaporation chamber (4) flows into the second evaporation chamber (21) through the flow port (22).

2. The heat exchange fin according to claim 1, characterized in that: The first transverse wing (2) is opposite to the base to be installed and is arranged at a distance, so as to form a third evaporation chamber (5) between the first transverse wing (2) and the base to be installed; The first transverse wing (2) also has an outflow port (23) spaced apart from the flow port (22), and the third evaporation chamber (5) and the second evaporation chamber (21) are both connected to the outflow port (23).

3. The heat exchange fin according to claim 2, characterized in that: The first transverse wing (2) comprises a top wall (201), a side wall (202) and a bottom wall (203) which are connected in sequence, the top wall (201) being arranged opposite to the second transverse wing (3), and the bottom wall (203) being arranged opposite to the foundation to be installed; wherein: The flow port (22) is arranged on the top wall (201), and the outflow port (23) is arranged on the side wall (202); and / or, There are multiple outlets (23), and the multiple outlets (23) are arranged at intervals from each other; and / or, The outflow port (23) is a rectangular port, the long side of which is greater than or equal to 0.1 mm and less than or equal to 0.3 mm; the short side of which is greater than or equal to 0.01 mm and less than or equal to 0.04 mm.

4. The heat exchange fin according to claim 1, characterized in that: There are a plurality of the second evaporation chambers (21), the plurality of the second evaporation chambers (21) are arranged at intervals, there are a plurality of the flow openings (22), the plurality of the flow openings (22) and the plurality of the second evaporation chambers (21) are arranged in a one-to-one correspondence; and / or, The minimum distance between a side of the second transverse wing (3) away from the first transverse wing (2) and a side of the first transverse wing (2) close to the second transverse wing (3) is greater than or equal to 0.05 mm and less than or equal to 0.15 mm; and / or, The flow port (22) is a cross-shaped structure, and the flow port (22) comprises a first port (221) and a second port (222) which are perpendicular to each other, the length of the first port (221) is greater than the length of the second port (222); the length of the first port (221) is greater than or equal to 0.2 mm and less than or equal to 0.5 mm, and the minimum width of the first port (221) or the minimum width of the second port (222) is greater than or equal to 0.01 mm and less than or equal to 0.05 mm.

5. The heat exchange fin according to claim 1, characterized in that: The heat exchange fin further comprises a fin platform (6), the fin platform (6) extending along the second preset direction and arranged on a side of the vertical fin (1) away from the base to be installed, at least a portion of the fin platform (6) being opposite to and spaced from the second transverse fin (3), so as to form a fourth evaporation chamber (7) between at least a portion of the fin platform (6) and the second transverse fin (3); wherein: There are a plurality of fin platforms (6), and the plurality of fin platforms (6) are arranged at intervals along the second preset direction, and a flow gap (61) is formed between two adjacent fin platforms (6), so that the refrigerant flows into the fourth evaporation chamber (7) through the flow gap (61); or, The wing platform (6) is provided with a through opening, and the through opening is connected to the fourth evaporation chamber (7).

6. The heat exchange fin according to claim 5, characterized in that: The second transverse wing (3) is provided with a communication port (31), and the fourth evaporation chamber (7) and the first evaporation chamber (4) are both connected to the communication port (31); wherein: At least a portion of the communication port (31) is arranged opposite to the flow port (22); and / or, The connecting opening (31) is a cross-shaped structure, and the connecting opening (31) includes a third opening portion (311) and a fourth opening portion (312) which are perpendicular to each other, the length of the third opening portion (311) is greater than the length of the fourth opening portion (312), the length of the third opening portion (311) is greater than or equal to 0.2 mm and less than or equal to 0.5 mm, and the minimum width of the third opening portion (311) or the minimum width of the fourth opening portion (312) is greater than or equal to 0.01 mm and less than or equal to 0.05 mm.

7. The heat exchange fin according to any one of claims 1 to 6, characterized in that: The heat exchange fins also include: A micro vertical wing (8) is extended along the first preset direction and arranged on the second horizontal wing (3) and is located on a side of the second horizontal wing (3) away from the first horizontal wing (2); the micro vertical wing (8) is opposite to the vertical wing (1) and is arranged at an interval; the vertical wing (1), the micro vertical wing (8) and the second horizontal wing (3) together form a fourth evaporation chamber (7).

8. The heat exchange fin according to claim 7, characterized in that: The heat exchange fin further comprises a micro transverse fin (9), wherein the micro transverse fin (9) is extended along the second preset direction and arranged on the micro vertical fin (8) and is located on a side of the micro vertical fin (8) away from the vertical fin (1); and / or, The first transverse wing (2) and the second transverse wing (3) are both inserted on the vertical wing (1), the two ends of the first transverse wing (2) protrude from the opposite sides of the vertical wing (1), and the two ends of the second transverse wing (3) protrude from the opposite sides of the vertical wing (1); there are two micro vertical wings (8), one of the two micro vertical wings (8) is arranged at one end of the second transverse wing (3), and the other micro vertical wing (8) is arranged at the other end of the second transverse wing (3).

9. The heat exchange fin according to claim 7, characterized in that: The heat exchange fin further comprises a fin platform (6), wherein the fin platform (6) is extended along the second preset direction and arranged on a side of the vertical fin (1) away from the base to be installed, at least a portion of the fin platform (6) is opposite to and spaced from the second transverse fin (3), and the fin platform (6), the vertical fin (1), the micro vertical fin (8) and the second transverse fin (3) together form the fourth evaporation chamber (7); the fin platform (6) comprises a first fin platform (62) and a second fin platform (63), wherein the first fin platform (62) is fixedly connected to the vertical fin (1), and the second fin platform (63) is fixedly connected to the micro vertical fin (8); wherein: The extended surface of the first wing platform (62) away from the vertical wing (1) coincides with the extended surface of the second wing platform (63) away from the micro vertical wing (8); and / or, The first wing platform (62) and the second wing platform (63) are arranged at intervals, and the side surface of the first wing platform (62) close to the second wing platform (63) and the side surface of the second wing platform (63) close to the first wing platform (62) are arranged opposite and parallel; and / or, The first wing platform (62) is a diamond-shaped structure, and the second wing platform (63) is a triangle structure or a diamond-shaped structure.

10. A heat exchange tube, characterized in that: It comprises a tube body (10) and the heat exchange fin according to any one of claims 1 to 9, wherein the outer wall of the tube body (10) forms a base to be installed.

11. The heat exchange tube according to claim 10, characterized in that: The first transverse fin (2) of the heat exchange fin is arranged opposite to the outer wall of the tube body (10) and is spaced apart from each other. The heat exchange tube further comprises a protrusion (11), which is arranged on the outer wall of the tube body (10). The protrusion (11) surrounds an inner cavity, and one end of the protrusion (11) away from the tube body (10) surrounds an opening (111) in communication with the inner cavity. The opening (111) is arranged opposite to the first transverse fin (2); wherein: The height of the protrusion (11) along the first preset direction is greater than or equal to 0.05 mm and less than or equal to 0.2 mm; and / or, The protrusion (11) is a cylindrical structure, and the diameter of the inner cavity is greater than or equal to 0.05 mm and less than or equal to 0.2 mm; and / or, There are a plurality of protrusions (11), and the plurality of protrusions (11) are arranged at intervals from each other.

12. The heat exchange tube according to claim 11, characterized in that: There are a plurality of heat exchange fins, and the plurality of heat exchange fins are arranged at intervals along the circumferential direction of the tube body (10); there are a plurality of protrusions (11), and the plurality of protrusions (11) are arranged at intervals between two adjacent heat exchange fins along the circumferential direction of the tube body (10) to form a protrusion group (112); there are a plurality of protrusion groups (112), and the plurality of protrusion groups (112) are arranged at intervals along the axial direction of the tube body (10); wherein the number of the protrusions (11) is greater than or equal to 1 and less than or equal to 4; the number of the protrusion groups (112) is greater than or equal to 100 and less than or equal to 600; and / or, The tube body (10) comprises a first tube wall (101) and a second tube wall (102) which are arranged opposite to each other; in the vertical direction, the first tube wall (101) is located above the second tube wall (102); the protrusion (11) is used to be arranged on the first tube wall (101) and the second tube wall (102); wherein the central angle corresponding to the first tube wall (101) is greater than or equal to 40° and less than or equal to 180°, and the central angle corresponding to the second tube wall (102) is greater than or equal to 20° and less than or equal to 60°.

13. A heat exchanger, characterized in that: include: The heat exchange tube according to any one of claims 10 to 12.

14. An air conditioner, characterized in that: include: The heat exchange tube according to any one of claims 10 to 12.

Images