Finned heat exchanger and air conditioning system

Abstract

The invention relates to a finned heat exchanger and an air conditioning system. The finned heat exchanger comprises fins and a refrigerant pipe. Each fin is provided with a mounting through hole and a first heat-resistant through hole, the first heat-resistant through hole is located in the first direction of the mounting through hole, and the first direction is the reverse direction of the airflow direction; and the refrigerant pipe is attached to the inner wall of the mounting through hole. By the adoption of the fin type heat exchanger, the frosting rate of the edge, located in the windward area of the refrigerant pipe, of the fin type heat exchanger can be delayed, then the shutdown defrosting frequency of the fin type heat exchanger can be reduced, and the overall heat exchange performance of the fin type heat exchanger is improved.

Description

Technical Field

[0001] The present disclosure relates to the technical field of heat exchange, and particularly to a finned heat exchanger and an air conditioning system. Background Art

[0002] Finned heat exchangers are widely used in the outdoor units of air conditioning systems due to their high heat exchange efficiency and other characteristics.

[0003] A finned heat exchanger includes a refrigerant pipe and a plurality of fins. Low-temperature refrigerant flows in the refrigerant pipe. The plurality of fins are arranged at intervals, and each fin is sleeved on the outer circle of the refrigerant pipe and is connected to the refrigerant pipe. During the operation of the heat exchanger, air passes through the gaps between adjacent two fins and exchanges heat with the heat exchanger.

[0004] However, when air passes through the heat exchanger, due to the blocking effect of the refrigerant pipe, the gas flow velocity in the region in front of the refrigerant pipe between adjacent two fins is relatively low. In the case of high air humidity, the positions on the fins corresponding to this region, especially the edge positions of the fins, will quickly frost, thereby causing the gap between adjacent two fins to become narrow or even completely blocked by the frost layer, seriously affecting the heat exchange performance. Summary of the Invention

[0005] Embodiments of the present disclosure provide a finned heat exchanger and an air conditioning system, which can solve the technical problems existing in the related art. The technical solutions are as follows:

[0006] In a first aspect, embodiments of the present disclosure provide a finned heat exchanger, and the finned heat exchanger includes fins and a refrigerant pipe;

[0007] The fin has an installation through-hole and a first heat-blocking through-hole. The first heat-blocking through-hole is located in a first direction of the installation through-hole, and the first direction is the reverse direction of the air flow direction;

[0008] The refrigerant pipe is in contact with the inner wall of the installation through-hole.

[0009] In a possible implementation manner, the first heat-blocking through-hole is a long-strip through-hole, and the length direction of the first heat-blocking through-hole is parallel to the first edge of the fin, and the first edge is located in the first direction of the installation through-hole.

[0010] In a possible implementation manner, the installation through-hole is a circular through-hole, and the length L1 of the first heat-blocking through-hole in the perpendicular direction of the air flow direction is greater than or equal to the inner diameter D1 of the installation through-hole.

[0011] In a possible implementation, the wall surface of the fin further has a first region and a second region. The first region is located in the first direction of the mounting through-hole, and the second region is located in the second direction of the mounting through-hole. The second direction is perpendicular to the first direction;

[0012] The wall surface of the fin further has a first flow guiding structure, which is located between the mounting through-hole and the first heat insulation through-hole, and is used to guide part of the air flow flowing to the first region to the second region.

[0013] In a possible implementation, the fin further has a second heat insulation through-hole, and the second heat insulation through-hole is located on the side of the first flow guiding structure close to the mounting through-hole.

[0014] In a possible implementation, the first flow guiding structure and the second heat insulation through-hole are formed by a punching and flanging process.

[0015] In a possible implementation, the wall surface of the fin further has a second region and a third region. The second region is located in the second direction of the mounting through-hole, the second direction is perpendicular to the first direction, and the third region is located in the air flow direction of the mounting through-hole;

[0016] The wall surface of the fin further has a second flow guiding structure, which is located in the air flow direction of the mounting through-hole, and is used to guide part of the air flow flowing to the second region to the third region.

[0017] In a possible implementation, the fin further has a third heat insulation through-hole, and the third heat insulation through-hole is located on the side of the second flow guiding structure far from the mounting through-hole.

[0018] In a possible implementation, the second flow guiding structure and the third heat insulation through-hole are formed by a punching and flanging process.

[0019] In a second aspect, an embodiment of the present disclosure provides an air conditioning system, and the air conditioning system includes the finned heat exchanger in the first aspect and its possible implementations.

[0020] The technical solutions provided by the embodiments of the present disclosure at least include the following beneficial effects:

[0021] An embodiment of the present disclosure provides a finned heat exchanger. In this finned heat exchanger, the fin has an installation through-hole and a first heat insulation through-hole. The first heat insulation through-hole is located in a first direction of the installation through-hole, and the first direction is the reverse direction of the air flow direction. The refrigerant pipe is in contact with the inner wall of the installation through-hole. In this way, the first heat insulation through-hole is provided on the fin, and the first heat insulation through-hole can block the heat transfer path between the edge of the fin and the installation through-hole. Since the first heat insulation through-hole is located in the reverse direction of the air flow direction of the installation through-hole, that is, the first heat insulation through-hole is provided on the fin corresponding to the windward area of the refrigerant pipe. This makes the temperature of the edge position of the fin corresponding to the windward area of the refrigerant pipe relatively high under the action of the first heat insulation through-hole blocking the heat transfer path. Thus, after gaseous water is liquefied into liquid water and adheres to this position, the frosting speed of the liquid water can be delayed, and further, the defrosting frequency of the finned heat exchanger during shutdown can be reduced, and the overall heat transfer performance of the finned heat exchanger can be improved.

[0022] It should be understood that the above general description and the following detailed description are only exemplary and explanatory, and cannot limit the present disclosure. BRIEF DESCRIPTION OF THE DRAWINGS

[0023] In order to more clearly illustrate the technical solutions in the embodiments of the present disclosure, the following will briefly introduce the drawings required for the description of the embodiments. Obviously, the drawings in the following description are only some embodiments of the present disclosure. For those of ordinary skill in the art, without creative efforts, other drawings can be obtained based on these drawings.

[0024] Figure 1 is a schematic structural diagram of a fin shown in an embodiment of the present disclosure;

[0025] Figure 2 is a schematic structural diagram of a fin shown in an embodiment of the present disclosure;

[0026] Figure 3 is a schematic structural diagram of a fin shown in an embodiment of the present disclosure;

[0027] Figure 4 is a schematic structural diagram of a fin shown in an embodiment of the present disclosure;

[0028] Figure 5 is a schematic structural diagram of a fin shown in an embodiment of the present disclosure;

[0029] Figure 6 is a schematic structural diagram of a fin shown in an embodiment of the present disclosure;

[0030] Figure 7 is a schematic structural diagram of a finned heat exchanger shown in an embodiment of the present disclosure;

[0031] Figure 8It is a schematic structural diagram of a fin shown in an embodiment of the present disclosure;

[0032] Figure 9 It is a schematic structural diagram of a fin shown in an embodiment of the present disclosure.

[0033] Legend Explanation

[0034] 100, air flow direction; 101, first region; 102, second region; 103, third region;

[0035] 1, fin; 1a, first edge;

[0036] 11, mounting through-hole; 12, first heat-resistant through-hole; 13, first flow-guiding structure; 14, second heat-resistant through-hole; 15, second flow-guiding structure; 16, third heat-resistant through-hole;

[0037] 131, first convex structure; 132, second convex structure; 151, third convex structure; 152, fourth convex structure;

[0038] 2, refrigerant pipe;

[0039] 201, first port; 202, second port;

[0040] 21, branch pipe; 22, connecting pipe;

[0041] 3, heat-resistant member. Detailed Embodiments

[0042] To make the objectives, technical solutions, and advantages of the present disclosure clearer, the following will further describe the embodiments of the present disclosure in detail with reference to the accompanying drawings.

[0043] Unless otherwise defined, the technical terms or scientific terms used herein shall have the ordinary meanings understood by those of ordinary skill in the field to which the present disclosure pertains. The "first", "second", "third", and similar terms used in the patent disclosure specification and claims of the present disclosure do not denote any order, quantity, or importance, but are only used to distinguish different components. Similarly, terms such as "a" or "one" do not denote a quantity limitation, but indicate the existence of at least one. The terms "including" or "comprising" and similar terms mean that the elements or objects appearing before "including" or "comprising" cover the elements or objects listed after "including" or "comprising" and their equivalents, and do not exclude other elements or objects. The terms "connected" or "coupled" and similar terms are not limited to physical or mechanical connections, but may include electrical connections, whether direct or indirect. The terms "upper", "lower", "left", "right", etc. are only used to represent relative positional relationships, and when the absolute position of the described object changes, the relative positional relationships may also change accordingly.

[0044] At present, finned heat exchangers are widely used in the outdoor units of air conditioning systems due to their low layout cost and high heat transfer efficiency. A finned heat exchanger includes refrigerant pipes and a plurality of fins. The plurality of fins are arranged at intervals, and each fin is sleeved on the outer circle of the refrigerant pipe. In the working state, low-temperature refrigerant flows in the refrigerant pipe, and the wall temperature of the refrigerant pipe is relatively low. Since the fin is closely attached to the outer wall of the refrigerant pipe, the temperature of the fin is also relatively low. In practice, air exchanges heat with the low-temperature fin and the low-temperature refrigerant pipe through the gap between two adjacent fins. The temperature of the refrigerant in the pipe rises. During this process, due to the blocking effect of the refrigerant pipe, the gas flow velocity in the area in front of the refrigerant pipe between two adjacent fins is relatively low. Moreover, since the air carries a certain amount of water vapor, when the water vapor encounters the low-temperature fin and the low-temperature refrigerant pipe, a phase change will occur, changing from a gaseous state to a liquid state, and adhering to the fin in the form of liquid water. This causes the area on the fin in front of the refrigerant pipe, especially the edge position of the fin farther away from the refrigerant pipe, to quickly adhere to liquid water. And because the temperature at this position is relatively low, the liquid water will quickly frost, which will further cause the gap between two adjacent fins to become narrow, and the gap between two adjacent fins may even be completely blocked by the frost layer, seriously affecting the heat transfer performance.

[0045] An embodiment of the present disclosure provides a finned heat exchanger, which includes fin 1 and refrigerant pipe 2.

[0046] Among them, fin 1 has an installation through hole 11 and a first heat insulation through hole 12. The first heat insulation through hole 12 is located in the first direction of the installation through hole 11, and the first direction is the reverse direction of the air flow direction 100. The refrigerant pipe 2 passes through the installation through hole 11 and is in contact with the inner wall.

[0047] In this way, a first heat insulation through hole 12 is provided on fin 1. The first heat insulation through hole 12 can block the heat transfer path between the edge of fin 1 and the installation through hole 11. Since the first heat insulation through hole 12 is located in the reverse direction of the air flow direction 100 of the installation through hole 11, that is, the first heat insulation through hole 12 is provided on the fin corresponding to the windward area of the refrigerant pipe 2. This makes the edge position of the fin corresponding to the windward area of the refrigerant pipe 2 have a higher temperature under the action of the first heat insulation through hole 12 blocking the heat transfer path. Thus, after gaseous water is liquefied and adheres to this position, the frosting speed of the liquid water can be delayed, and further, the defrosting frequency of the finned heat exchanger during shutdown can be reduced, and the overall heat transfer performance of the finned heat exchanger can be improved.

[0048] Figure 7 is an overall schematic diagram of a finned heat exchanger provided by an embodiment of the present disclosure, as Figure 7As shown, the finned heat exchanger includes fins 1 and refrigerant pipes 2. The fins 1 have a thin plate-like structure. There are mounting through holes 11 on the fins 1. The axis of the mounting through holes 11 is perpendicular to the fins 1. The mounting through holes 11 are used to accommodate the refrigerant pipes 2.

[0049] In some possible embodiments, referring to Figure 7 , the finned heat exchanger includes a plurality of fins 1 arranged at intervals, and the plurality of fins 1 are arranged in parallel.

[0050] Optionally, the distance between two adjacent fins 1 can be equal.

[0051] In this way, the assembly difficulty between the fins 1 and the refrigerant pipes 2 can be reduced.

[0052] [[ID=၁၄]]Exemplarily, the distance between two adjacent fins 1 can be 0.3 mm.

[0053] The embodiments of the present disclosure do not limit the distance between two adjacent fins 1. Those skilled in the art can set it according to the actual heat exchange scenario, heat exchange requirements, etc.

[0054] In one example, as Figure 7 [[ID=၂၂]]shown, the refrigerant pipe 2 can include a plurality of branch pipes 21 and a plurality of connecting pipes 22.

[0055] In implementation, each fin 1 can have a plurality of mounting through holes 11. The diameters of the plurality of mounting through holes 11 are all equal and equal to the outer diameter of the branch pipe 21. For different fins 1, the axes of the mounting through holes 11 at the same height coincide. The branch pipes 21 sequentially pass through a plurality of fins 1 arranged in parallel, and the outer walls of the branch pipes 21 are respectively in contact with the inner walls of the plurality of mounting through holes 11 at the same height. The ends of two adjacent branch pipes 21 are connected and communicated through the connecting pipe 22.

[0056] In this way, the size of the fins 1 can be set larger. Then, when the wind flowing along the air flow direction 100 passes through the gap between two adjacent fins 1, the contact area between the wind and the fins 1 is larger, which can increase the contact area between the refrigerant pipe 2 and the fins 1. At the same time, the same fin 1 can be in contact with multiple segments of the refrigerant pipe 2, which can increase the heat exchange efficiency of the finned heat exchanger.

[0057] Next, each part of the finned heat exchanger will be introduced separately:

[0058] I. Fins 1

[0059] The fins 1 are components in the finned heat exchanger for increasing the heat exchange area.

[0060] In one example, as Figure 1 shown, the fins 1 have a rectangular plate-like structure. The edges of the fins 1 are arranged parallel to the air flow direction 100.

[0061] In this way, when the air flow passes through the gap between two adjacent fins 1, the air flow field can be kept stable, thereby reducing the noise.

[0062] The fin 1 can be a rectangular plate structure, a circular plate structure, or an oval plate structure. The embodiments of the present disclosure do not limit the shape of the fin 1.

[0063] As Figure 1 shown, the fin 1 has a mounting through hole 11 and a first heat insulation through hole 12. The first heat insulation through hole 12 is located in the first direction of the mounting through hole 11, and the first direction is the reverse direction of the air flow direction 100. The mounting through hole 11 is used to accommodate the refrigerant pipe 2.

[0064] In this way, along the air flow direction 100, the first heat insulation through hole 12 is arranged on the front side of the mounting through hole 11 (that is, the first heat insulation through hole 12 is arranged in the windward direction of the mounting through hole 11). The first heat insulation through hole 12 can block the heat transfer path from the mounting through hole 11 to the edge of the windward area of the fin 1, thereby increasing the temperature at the edge position of the windward area of the fin 1 during the working state, delaying the frosting rate, and improving the overall heat exchange efficiency of the fin heat exchanger.

[0065] The shape of the mounting through hole 11 and the shape of the first heat insulation through hole 12 can be the same or different. For example, the shape of the mounting through hole 11 can be circular, the shape of the first heat insulation through hole 12 can be rectangular, or the shapes of both the mounting through hole 11 and the first heat insulation through hole 12 are rectangular. The embodiments of the present disclosure do not limit the shapes of the mounting through hole 11 and the first heat insulation through hole 12.

[0066] The forming processes of the mounting through hole 11 and the first heat insulation through hole 12 can be the same or different. For example, both the mounting through hole 11 and the first heat insulation through hole 12 can be formed by stamping, or the mounting through hole 11 can be formed by CNC (Computer Numerical Control) cutting process, and the first heat insulation through hole 12 can be formed by stamping. The embodiments of the present disclosure do not limit the forming processes of the mounting through hole 11 and the first heat insulation through hole 12.

[0067] In one example, as Figure 3 shown, the shape of the mounting through hole 11 can be circular, the shape of the first heat insulation through hole 12 can be rectangular, and the length L1 of the first heat insulation through hole 12 in the perpendicular direction of the air flow direction 100 is equal to the inner diameter D1 of the mounting through hole 11.

[0068] In another example, the shape of the mounting through hole 11 can be circular, the shape of the first heat insulation through hole 12 can be rectangular, and the length L1 of the first heat insulation through hole 12 in the perpendicular direction of the air flow direction 100 is greater than the inner diameter D1 of the mounting through hole 11.

[0069] In this way, along the air flow direction 100, the first heat-blocking through hole 12 is arranged in the windward area of the mounting through hole 11. The first heat-blocking through hole 12 can completely block the heat transfer path from the mounting through hole 11 to the edge of the windward area of the fin 1, thereby increasing the temperature at the edge of the windward area of the fin 1 during the working state, delaying the frosting rate, and improving the overall heat transfer efficiency of the fin heat exchanger.

[0070] In implementation, for any fin 1, in the axial direction of the mounting through hole 11, the fin 1 has opposite first and second wall surfaces. Arranging the first heat-blocking through hole 12 can not only increase the contact area between the fin 1 and the air flow, but also cause local crosstalk to the air flow, that is, cause the air flow to flow crosswise between the first and second wall surfaces, so as to improve the overall heat transfer efficiency of the fin heat exchanger.

[0071] Exemplarily, the length of the first heat-blocking through hole 12 in the air flow direction 100 can be less than or equal to 0.1 mm.

[0072] In this way, it can be ensured that the fin 1 has the ability to block the heat transfer path while ensuring that the fin 1 has greater mechanical strength.

[0073] In some possible embodiments, as Figure 1 shown, the fin 1 has a rectangular plate-like structure, and the first heat-blocking through hole 12 is a long strip through hole. The length direction of the long strip through hole is parallel to the first edge 1a of the fin 1, where the first edge 1a is the edge of the fin 1 in the first direction of the mounting through hole 11.

[0074] In implementation, the fin heat exchanger is usually arranged vertically, that is, the first edge 1a of the fin 1 is perpendicular to the air flow direction 100. In this way, setting the length direction of the long strip through hole to be parallel to the first edge 1a of the fin 1 can completely block the heat transfer path from the mounting through hole 11 to the windward area of the fin 1 with the smallest opening size, thereby improving the overall strength of the fin 1.

[0075] In some possible embodiments, the fin 1 further has a first flow guiding structure 13.

[0076] As Figure 4 shown, the wall surface of the fin 1 further has a first flow guiding structure 13. The first flow guiding structure 13 is located between the mounting through hole 11 and the first heat-blocking through hole 12 and is used to guide part of the air flow flowing to the first area 101 to the second area 102.

[0077] Among them, the first area 101 is in the first direction of the mounting through hole 11, the second area 102 is in the second direction of the mounting through hole 11, and the second direction is perpendicular to the first direction.

[0078] In one example, the first flow guiding structure 13 can be a sheet-like convex structure, and the flow guiding surface (not shown) of the convex structure is a plane, and there is a preset included angle between the flow guiding surface and the air flow direction 100.

[0079] In implementation, the first flow guiding structure 13 is arranged between the installation through hole 11 and the first heat insulation through hole 12. The first flow guiding structure 13 can guide a part of the air flow flowing to the first area 101 to the second area 102, thereby reducing the air flow rate in direct contact with the refrigerant pipe 2.

[0080] Thus, since the air flow rate in direct contact with the refrigerant pipe 2 is reduced, the liquid water liquefied and adhering to the outer wall of the refrigerant pipe 2 is correspondingly reduced, and thus the frosting speed of the outer wall of the refrigerant pipe 2 can be delayed.

[0081] Exemplarily, as Figure 8 shown, the first flow guiding structure 13 includes a first convex structure 131 and a second convex structure 132. The first convex structure 131 is located above the axis of the installation through hole 11, and the second convex structure 132 is located below the axis of the installation through hole 11.

[0082] Referring to Figure 8 , the first convex structure 131 has a first flow guiding surface (not shown). The first flow guiding surface is the wall surface of the first convex structure 131 away from the installation through hole 11. The first flow guiding surface is a plane, and there is a first preset included angle between the first flow guiding surface and the air flow direction 100. The value range of the first preset included angle is 30° to 60°. The second convex structure 132 has a second flow guiding surface (not shown). The second flow guiding surface is the wall surface of the second convex structure 132 away from the installation through hole 11. The second flow guiding surface is a plane, and there is a second preset included angle between the second flow guiding surface and the air flow direction 100. The value range of the second preset included angle is 120° to 150°.

[0083] In one example, the first convex structure 131 and the second convex structure 132 can be respectively arranged on the first wall surface and the second wall surface of the fin 1.

[0084] Optionally, the first convex structure 131 located on the first wall surface and the first convex structure 131 located on the second wall surface can be symmetrically distributed with respect to the fin 1, and the second convex structure 132 located on the first wall surface and the second convex structure 132 located on the second wall surface can be symmetrically distributed with respect to the fin 1.

[0085] [[ID=(26)]]Optionally, both the first convex structure 131 and the second convex structure 132 can be perpendicular to the fin 1.

[0086] Exemplarily, the heights of the first convex structure 131 and the second convex structure 132 can be the same, and can both be 0.1 mm.

[0087] Thus, for any fin, the first flow guiding structures 13 are provided on both side walls thereof. That is, for the gaps on both sides of the fin 1, the frosting speed at the corresponding positions of the refrigerant pipe 2 can be delayed under the action of the first flow guiding structures 13, thereby improving the overall heat exchange efficiency of the fin heat exchanger.

[0088] The first convex structure 131 and the second convex structure 132 can be integrally formed with the fin 1, or can be connected to the wall surface of the fin 1 after being processed and formed separately. The embodiments of the present disclosure do not limit this.

[0089] Exemplarily, when the first convex structure 131 and the second convex structure 132 and the fin 1 are partially processed and formed, the first convex structure 131 and the second convex structure 132 can be fixedly connected to the fin 1 by welding.

[0090] In some possible embodiments, the fin 1 further has a second heat blocking through hole 14.

[0091] As Figure 4 shown, the second heat blocking through hole 14 is located on one side of the first flow guiding structure 13 close to the mounting through hole 11.

[0092] In implementation, the second heat blocking through hole 14 is arranged on one side of the first flow guiding structure 13 close to the mounting through hole 11. The second heat blocking through hole 14 can block the heat transfer path between the mounting through hole 11 and the first flow guiding structure 13, thereby increasing the temperature at the position of the first flow guiding structure 13 during the working state, delaying the frosting rate at the position of the first flow guiding structure 13, and improving the overall heat exchange efficiency of the fin heat exchanger.

[0093] Optionally, as Figure 4 shown, the second heat blocking through hole 14 is adjacent to the edge of the first flow guiding structure 13.

[0094] In this way, the processing difficulty of the second heat blocking through hole 14 is reduced.

[0095] In one example, the first flow guiding structure 13 includes a first convex structure 131 and a second convex structure 132. The fin 1 has a plurality of second heat blocking through holes 14. One of the second heat blocking through holes 14 is located on one side of the first convex structure 131 close to the mounting through hole 11, and the other second heat blocking through hole 14 is located on one side of the second convex structure 132 close to the mounting through hole 11.

[0096] In implementation, a plurality of second heat-blocking through holes 14 are respectively disposed on one side of the first convex structure 131 close to the mounting through hole 11 and on one side of the second convex structure 132 close to the mounting through hole 11. The second heat-blocking through holes 14 can block the heat transfer path between the mounting through hole 11 and the first convex structure 131 and the second convex structure 132, thereby increasing the temperature at the position of the first diversion structure 13 during the working state, delaying the frosting rate at the position of the first diversion structure 13, and improving the overall heat exchange efficiency of the finned heat exchanger.

[0097] In one example, the first diversion structure 13 and the second heat-blocking through holes 14 can be formed by a process of punching and flanging.

[0098] In implementation, the first convex structure 131 and the corresponding second heat-blocking through holes 14 can be formed by a process of punching and flanging, and the second convex structure 132 and the corresponding second heat-blocking through holes 14 can be formed by a process of punching and flanging. That is, during the punching process, part of the fins are folded towards the axis direction of the mounting through hole 11 to form the first convex structure 131 and the second convex structure 132.

[0099] In this way, the processing efficiency of the first diversion structure 13 and the second heat-blocking through holes 14 can be improved, and the cost can be reduced.

[0100] In some possible embodiments, the fin 1 further has a second diversion structure 15.

[0101] As Figure 5 shown, the fin 1 further has a second diversion structure 15 on its wall surface. The second diversion structure 15 is located on the air flow direction 100 of the mounting through hole 11 and is used to divert part of the air flow flowing to the second area 102 to the third area 103.

[0102] Among them, the second area 102 is located in the second direction of the mounting through hole 11. The second direction is perpendicular to the first direction, and the third area 103 is located on the air flow direction 100 of the mounting through hole 11.

[0103] In one example, the second diversion structure 15 can be a sheet-like convex structure. The diversion surface (not shown) of the convex structure is a plane, and there is a preset angle between the diversion surface and the air flow direction 100.

[0104] In implementation, the second diversion structure 15 is disposed on the air flow direction 100 of the mounting through hole 11. The second diversion structure 15 can divert part of the air flow flowing to the second area 102 to the third area 103, thereby reducing the air flow volume contacted by the leeward area of the second area 102.

[0105] In this way, since the amount of air flow contacting the leeward area of the second area 102 (relative to the air flow direction 100) is reduced, the amount of liquefied and attached liquid water corresponding to the position on the fin 1 corresponding to the leeward area of the second area 102 is correspondingly reduced, thereby delaying the frosting speed in this area. Moreover, the amount of air flow contacting the leeward area of the refrigerant pipe 2 (relative to the air flow direction 100) is increased, and the heat exchange capacity of the leeward area of the refrigerant pipe 2 can be fully utilized, thereby enhancing the overall heat exchange capacity of the finned heat exchanger.

[0106] Exemplarily, as Figure 9 shown, the second flow guiding structure 15 includes a third convex structure 151 and a fourth convex structure 152. The third convex structure 151 is located above the axial direction of the mounting through hole 11, and the fourth convex structure 152 is located below the axial direction of the mounting through hole 11.

[0107] Referring to Figure 9 , the third convex structure 151 has a third flow guiding surface (not shown), the third flow guiding surface is the wall surface of the third convex structure 151 away from the mounting through hole 11, the third flow guiding surface is a plane, and there is a first preset angle between the third flow guiding surface and the air flow direction 100. The value range of the first preset angle is 120° to 150°. The fourth convex structure 152 has a fourth flow guiding surface (not shown), the fourth flow guiding surface is the wall surface of the fourth convex structure 152 away from the mounting through hole 11, the fourth flow guiding surface is a plane, and there is a second preset angle between the fourth flow guiding surface and the air flow direction 100. The value range of the second preset angle is 30° to 60°.

[0108] In one example, the third convex structure 151 and the fourth convex structure 152 can be respectively arranged on the first wall surface and the second wall surface of the fin 1.

[0109] Optionally, the third convex structure 151 on the first wall surface and the third convex structure 151 on the second wall surface can be symmetrically distributed with respect to the fin 1, and the fourth convex structure 152 on the first wall surface and the fourth convex structure 152 on the second wall surface can be symmetrically distributed with respect to the fin 1.

[0110] Optionally, both the third convex structure 151 and the fourth convex structure 152 can be perpendicular to the fin 1.

[0111] Exemplarily, the heights of the third convex structure 151 and the fourth convex structure 152 can be the same, and can both be 0.1 mm.

[0112] Thus, for any fin, there are second flow guiding structures 15 on both side wall surfaces thereof. That is, for the gaps on both sides of the fin 1, under the action of the second flow guiding structure 15, the frosting speed at the corresponding positions in the leeward area of the second area 102 can be delayed, thereby improving the overall heat exchange efficiency of the fin heat exchanger. Moreover, the air flow rate contacted by the leeward area of the refrigerant pipe 2 (relative to the air flow direction 100) can be increased, and the heat exchange capacity of the leeward area of the refrigerant pipe 2 can be fully utilized, thereby improving the overall heat exchange capacity of the fin heat exchanger.

[0113] The third convex structure 151 and the fourth convex structure 152 can be integrally formed with the fin 1, or can be connected to the wall surface of the fin 1 after being processed and formed separately. The embodiments of the present disclosure do not limit this.

[0114] Exemplarily, when the third convex structure 151 and the fourth convex structure 152 and the fin 1 are partially processed and formed, the third convex structure 151 and the fourth convex structure 152 can be fixedly connected to the fin 1 by welding.

[0115] In some possible embodiments, the fin 1 further has a third heat blocking through hole 16.

[0116] As Figure 5 shown, the third heat blocking through hole 16 is located on the side of the second flow guiding structure 15 close to the installation through hole 11.

[0117] In implementation, the third heat blocking through hole 16 is arranged on the side of the second flow guiding structure 15 far from the installation through hole 11. The third heat blocking through hole 16 can block the heat transfer path between the installation through hole 11 and the leeward edge of the fin 1, thereby increasing the temperature at the leeward edge position of the fin 1 in the working state, delaying the frosting rate at the leeward edge position of the fin 1, and improving the overall heat exchange efficiency of the fin heat exchanger.

[0118] Optionally, as Figure 5 shown, the third heat blocking through hole 16 is adjacent to the edge of the second flow guiding structure 15.

[0119] In this way, the processing difficulty of the third heat blocking through hole 16 is reduced.

[0120] In one example, the second flow guiding structure 15 includes a third convex structure 151 and a fourth convex structure 152. The fin 1 has a plurality of third heat blocking through holes 16. One third heat blocking through hole 16 is located on the side of the third convex structure 151 far from the installation through hole 11, and the other third heat blocking through hole 16 is located on the side of the fourth convex structure 152 far from the installation through hole 11.

[0121] In implementation, a plurality of third heat-blocking through holes 16 are respectively disposed on a side of the third convex structure 151 away from the mounting through hole 11 and on a side of the fourth convex structure 152 away from the mounting through hole 11. The third heat-blocking through holes 16 can block the heat transfer path between the mounting through hole 11 and the leeward edge of the fin 1, and thus can increase the temperature at the leeward edge position of the fin 1 during the working state, delay the frosting rate at this position, and improve the overall heat transfer efficiency of the fin heat exchanger.

[0122] In one example, the second flow guiding structure 15 and the third heat-blocking through holes 16 can be formed by a process of punching and flanging.

[0123] In implementation, the third convex structure 151 and the corresponding third heat-blocking through holes 16 can be formed by a process of punching and flanging, and the fourth convex structure 152 and the corresponding third heat-blocking through holes 16 can be formed by a process of punching and flanging. That is, during the punching process, part of the fin is folded towards the axis direction of the mounting through hole 11 to form the third convex structure 151 and the fourth convex structure 152.

[0124] In this way, the processing efficiency of the second flow guiding structure 15 and the third heat-blocking through holes 16 can be improved, and the cost can be reduced.

[0125] In some possible embodiments, as Figure 6 shown, the fin 1 has a first flow guiding structure 13 and a second flow guiding structure 15, and the fin 1 further has a second heat-blocking through hole 14 and a third heat-blocking through hole 16.

[0126] For the specific structures of the first flow guiding structure 13, the second flow guiding structure 15, the second heat-blocking through hole 14 and the third heat-blocking through hole 16, reference can be made to the above introduction of the first flow guiding structure 13, the second flow guiding structure 15, the second heat-blocking through hole 14 and the third heat-blocking through hole 16, and the description will not be repeated here.

[0127] In some possible embodiments, the fin heat exchanger further includes a heat-blocking member 3.

[0128] As Figure 2 shown, the heat-blocking member 3 is located in the first heat-blocking through hole 12 and is connected to the fin 1.

[0129] In implementation, the thermal conductivity of the heat-blocking member 3 is less than that of the fin 1. The shape and size of the heat-blocking member 3 match the shape and size of the first heat-blocking through hole 12. The heat-blocking member 3 is filled in the first heat-blocking through hole 12, and has a smooth transition with the wall surface of the fin 1 and is connected to the fin 1.

[0130] Optionally, the wall surface of the heat-blocking member 3 can be flush with the wall surface of the fin 1.

[0131] In this way, the smoothness in the windward area of the installation through-hole 11 can be improved. Furthermore, when the water vapor in the air is cooled and liquefied, it is not easy to adhere to the fin 1, which can delay the frosting speed of the fin 1 and improve the heat exchange efficiency.

[0132] The material of the heat insulation member 3 can be ceramic or gypsum. The embodiments of the present disclosure do not limit the material of the heat insulation member 3.

[0133] In some examples, the fin 1 further has a second heat insulation through-hole 14 and a third heat insulation through-hole 16, and the finned heat exchanger includes a plurality of heat insulation members 3.

[0134] In implementation, the thermal conductivity coefficients of the plurality of heat insulation members 3 are all smaller than that of the fin 1, and the shape and size of the heat insulation member 3 match the shape and size of the corresponding heat insulation through-hole. That is, for the heat insulation member 3 located in the second heat insulation through-hole 14, the shape and size of the heat insulation member 3 match the shape and size of the second heat insulation through-hole 14; for the heat insulation member 3 located in the third heat insulation through-hole 16, the shape and size of the heat insulation member 3 match the shape and size of the third heat insulation through-hole 16. The plurality of heat insulation members 3 are respectively disposed in the second heat insulation through-hole 14 and the third heat insulation through-hole 16 and are connected to the fin 1.

[0135] The positions and shapes of the second heat insulation through-hole 14 and the third heat insulation through-hole 16 can refer to the content introduced above, and will not be described repeatedly here.

[0136] In implementation, the heat insulation member 3 is filled in the second heat insulation through-hole 14 and the third heat insulation through-hole 16, and is smoothly transitioned with the wall surface of the fin 1 and is connected to the fin 1. The wall surface of the heat insulation member 3 can be flush with the wall surface of the fin 1.

[0137] In this way, the smoothness in the windward area of the installation through-hole 11 can be improved, and the smoothness in the leeward area of the installation through-hole 11 can also be improved. Furthermore, when the water vapor in the air is precooled and liquefied, it is not easy to adhere to the fin 1, which can delay the frosting speed of the fin 1 and improve the heat exchange efficiency.

[0138] II. Refrigerant pipe 2

[0139] The refrigerant pipe 2 is a component in the finned heat exchanger for transporting the refrigerant.

[0140] As Figure 7 shown, the refrigerant pipe 2 includes a plurality of branch pipes 21 and a plurality of connecting pipes 22. The plurality of branch pipes 21 are arranged in parallel. Each branch pipe 21 respectively passes through a plurality of fins 1 arranged at intervals and is in contact with the inner walls of a plurality of installation through-holes 11.

[0141] Refer to Figure  7, the ends of two adjacent branch pipes 21 are connected through a connecting pipe 22. The lowermost branch pipe 21 of the refrigerant pipe 2 has a first port 201, and the lowermost branch pipe 21 of the refrigerant pipe 2 has a second port 202.

[0142] In implementation, the refrigerant flows into the finned heat exchanger through the first port 201, and flows out of the finned heat exchanger through the second port 202 after passing through multiple branch pipes 21 and multiple connecting pipes 22 in sequence.

[0143] The connection manner between the branch pipe 21 and the connecting pipe 22 can be welding or clamping, and the embodiments of the present disclosure do not limit this.

[0144] The technical solutions provided by the embodiments of the present disclosure at least include the following beneficial effects:

[0145] The embodiments of the present disclosure provide a finned heat exchanger. In this finned heat exchanger, the fin 1 has an installation through-hole 11 and a first heat insulation through-hole 12. The first heat insulation through-hole 12 is located in the first direction of the installation through-hole 11, and the first direction is the reverse direction of the air flow direction 100. The refrigerant pipe 2 passes through the installation through-hole 11 and is in contact with the inner wall of the installation through-hole 11. In this way, the first heat insulation through-hole 12 is provided on the fin 1, and the first heat insulation through-hole 12 can block the heat transfer path between the edge of the fin 1 and the installation through-hole 11. Since the first heat insulation through-hole 12 is located in the reverse direction of the air flow direction 100 of the installation through-hole 11, that is, the first heat insulation through-hole 12 is provided on the fin corresponding to the windward area of the refrigerant pipe 2. This makes the temperature of the edge position of the fin corresponding to the windward area of the refrigerant pipe 2 relatively high under the action of the first heat insulation through-hole 12 blocking the heat transfer path. Thus, after gaseous water is liquefied into liquid water and adheres to this position, the frosting speed of the liquid water can be delayed, and further, the defrosting frequency of the finned heat exchanger during shutdown can be reduced, and the overall heat transfer performance of the finned heat exchanger can be improved.

[0146] The embodiments of the present disclosure provide an air conditioning system, and this air conditioning system includes the above-mentioned finned heat exchanger.

[0147] The above are only the optional embodiments of the present disclosure, and are not intended to limit the present disclosure. Any modifications, equivalent replacements, improvements, etc. made within the spirit and principle of the present disclosure shall be included within the protection scope of the present disclosure.

Claims

1. A finned heat exchanger, characterized in that: The finned heat exchanger comprises fins (1) and refrigerant tubes (2); The fin (1) has a mounting through hole (11) and a first heat-resistance through hole (12), wherein the first heat-resistance through hole (12) is located in a first direction of the mounting through hole (11), and the first direction is opposite to the airflow direction (100); The refrigerant pipe (2) is in contact with the inner wall of the mounting through hole (11).

2. The finned heat exchanger according to claim 1, characterized in that: The first heat-resistance through hole (12) is a long strip through hole, the length direction of the first heat-resistance through hole (12) is parallel to the first edge (1a) of the fin (1), and the first edge (1a) is located in the first direction of the mounting through hole (11).

3. The finned heat exchanger according to claim 1, characterized in that: The mounting through hole (11) is a circular through hole, and the length L1 of the first heat-resistance through hole (12) in the direction perpendicular to the airflow direction (100) is greater than or equal to the inner diameter D1 of the mounting through hole (11).

4. The finned heat exchanger according to claim 1, characterized in that: The wall surface of the fin (1) further comprises a first region (101) and a second region (102), wherein the first region (101) is located in a first direction of the mounting through hole (11), and the second region (102) is located in a second direction of the mounting through hole (11), and the second direction is perpendicular to the first direction; The wall surface of the fin (1) also has a first flow-guiding structure (13), which is located between the mounting through hole (11) and the first heat-resisting through hole (12) and is used to guide part of the airflow flowing to the first area (101) to the second area (102).

5. The finned heat exchanger according to claim 4, characterized in that: The fin (1) further has a second heat-resistant through hole (14), and the second heat-resistant through hole (14) is located on a side of the first flow-guiding structure (13) close to the mounting through hole (11).

6. The finned heat exchanger according to claim 5, characterized in that: The first flow-guiding structure (13) and the second heat-resisting through hole (14) are formed by a punching and flanging process.

7. The finned heat exchanger according to claim 1, characterized in that: The wall surface of the fin (1) further comprises a second region (102) and a third region (103), wherein the second region (102) is located in a second direction of the mounting through hole (11), the second direction being perpendicular to the first direction, and the third region (103) is located in the airflow direction (100) of the mounting through hole (11); The wall surface of the fin (1) also has a second flow-guiding structure (15), which is located in the airflow direction (100) of the mounting through hole (11) and is used to guide part of the airflow flowing to the second area (102) to the third area (103).

8. The finned heat exchanger according to claim 7, characterized in that: The fin (1) further comprises a third heat-resistance through hole (16), and the third heat-resistance through hole (16) is located on a side of the second flow-guiding structure (15) away from the mounting through hole (11).

9. The finned heat exchanger according to claim 8, characterized in that: The second flow-guiding structure (15) and the third heat-resisting through hole (16) are formed by a punching and flanging process.

10. An air conditioning system, characterized in that: The air conditioning system includes the fin heat exchanger according to any one of claims 1 to 9.

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