Heat exchanger

Abstract

This utility model relates to a heat exchanger, which includes an inter-plate channel with fins. The inter-plate channel has fins; the fins include multiple fin units, and the length direction of the fin unit is defined as a first direction; the multiple fin units are arranged along a second direction, and the first direction and the second direction intersect; the heat exchanger has an inlet; the fin unit has a first flat plate region and a turbulence region, with the first flat plate region being closer to the inlet than the turbulence region; along the first direction, the extension length of the fin unit is L1, and the extension length of the first flat plate region is L2, where L1 and L2 satisfy the following relationship: 0.01≤L2 / L1≤0.05. Thus, the fin unit has a first flat plate region, which is closer to the inlet than the turbulence region, and the extension length L2 of the first flat plate region and the extension length L1 of the fin unit satisfy the following relationship: 0.01≤L2 / L1≤0.05, so that the fins can both meet the heat exchange requirements and improve the strength of the fins at the inlet.

Description

Technical Field

[0001] This utility model relates to the field of thermal management technology, and in particular to a heat exchanger for a refrigeration system. Background Technology

[0002] Plate heat exchangers consist of multiple plates stacked together, with inter-plate channels formed between adjacent plates for fluid flow. Two fluids can flow on opposite sides of the plates to achieve heat exchange between the plates. Utility Model Content

[0003] In related technologies, finned structures are usually added to plate heat exchangers to improve their heat exchange performance; during the forming process, the root of the finned sidewall is thinned, reducing the strength of the fins; when the fins are subjected to fluid pressure, the fins near the inlet area are at risk of breaking.

[0004] Therefore, it is necessary to provide a heat exchanger that addresses the above problems and aims to improve the strength of the fins near the inlet.

[0005] On the one hand, the technical solution adopted by this utility model is as follows:

[0006] A heat exchanger, including an interplate channel having fins;

[0007] The fin includes multiple fin units, and the length direction of the fin unit is defined as the first direction X; the multiple fin units are arranged along the second direction Y, and the first direction X and the second direction Y intersect;

[0008] The heat exchanger has an inlet; the finned unit has a first flat plate region and a turbulence region, the first flat plate region being closer to the inlet relative to the turbulence region;

[0009] Along the first direction X, the extension length of the fin unit is L1, and the extension length of the first flat plate region is L2. L1 and L2 satisfy the following relationship: 0.01≤L2 / L1≤0.05.

[0010] The fins in this application have a first flat plate area, which is closer to the inlet than the turbulence area. The extension length L2 of the first flat plate area and the extension length L1 of the fin unit satisfy the following relationship: 0.01≤L2 / L1≤0.05, so that the fins can meet the heat exchange requirements and improve the strength of the fins at the inlet. Attached Figure Description

[0011] Figure 1 This is a schematic diagram of the heat exchanger of this utility model;

[0012] Figure 2 for Figure 1 A schematic diagram of the heat exchange core structure in the diagram;

[0013] Figure 3 for Figure 2 A cross-sectional view along the AA direction;

[0014] Figure 4 for Figure 2 A schematic diagram of the structure after the first plate and fins are assembled;

[0015] Figure 5 for Figure 4 A schematic diagram of the structure of the first plate in the middle;

[0016] Figure 6 for Figure 4 A schematic diagram of the structure of the fins in the diagram;

[0017] Figure 7 for Figure 6 Another structural diagram from a different perspective;

[0018] Figure 8 for Figure 6 A schematic diagram of the structure of one of the fin units;

[0019] Figure 9 for Figure 8 A structural diagram from one perspective;

[0020] Figure 10 for Figure 8 Another structural diagram from a different perspective;

[0021] Figure 11 for Figure 9 Cross-sectional view of the first flat plate area;

[0022] Figure 12 for Figure 9 A cross-sectional view of the second flat plate area.

[0023] Reference numerals: 1. Heat exchanger; 2. Heat exchange core; 3. First fluid inlet; 4. First fluid outlet; 5. Plate channel; 6. Agent-side channel; 7. Water-side channel; 8. Second fluid inlet; 9. Second fluid outlet; 10. Fin; 11. Fin unit; 12. Inlet; 13. First plate area; 14. Turbulence area; 15. Third end; 16. Fourth end; 17. First sidewall; 18. Second sidewall; 19. Top wall; 20. First fluid channel; 21. Second fluid channel; 22. First end; 23. Second end; 24. First fin portion; 2 5. Second fin section; 26. First turbulence section; 27. Second turbulence section; 28. First fin section; 29. ​​Second fin section; 30. First flow port; 31. Second flow port; 32. Third fin section; 33. Fourth fin section; 34. Third flow port; 35. Fourth flow port; 36. First base; 37. Second base; 38. First plate; 39. Second plate; 40. First distribution zone; 41. Heat exchange zone; 42. Second distribution zone; 43. Outlet; 44. Second flat plate zone; 45. Third fin section; 46. Fourth fin section. Detailed Implementation

[0024] To make the objectives, technical solutions, and advantages of this utility model clearer, the embodiments will be further described in detail below with reference to the accompanying drawings. It should be understood that the specific embodiments described herein are merely illustrative of this utility model and are not intended to limit its scope.

[0025] This embodiment discloses a heat exchanger 1, such as Figures 1-3 As shown, the device includes a heat exchange core 2, which has a first fluid inlet 3 and a first fluid outlet 4. The heat exchange core 2 comprises multiple plates, which are alternately stacked to form inter-plate channels 5. Each inter-plate channel 5 includes multiple agent-side channels 6 and multiple water-side channels 7, which are isolated from each other and arranged alternately. Fluid enters the agent-side channel 6 within the heat exchange core 2 through the first fluid inlet 3. The fluid entering the agent-side channel 6 exchanges heat with the fluid in the agent-side channel 6 through the plate walls and finally flows out from the first fluid outlet 4. The heat exchange core 2 also has a second fluid inlet 8 and a second fluid outlet 9. Fluid enters the water-side channel 7 within the heat exchange core 2 through the second fluid inlet 8. The fluid entering the water-side channel 7 exchanges heat with the fluid in the agent-side channel 6 through the plate walls and finally flows out from the second fluid outlet 9. It should be noted that the fluid in the agent-side channel 6 and the fluid in the water-side channel 7 can be the same fluid or two different fluids.

[0026] like Figures 3-8As shown, more specifically, the inter-plate channel 5 has fins 10, each fin comprising multiple fin units 11. The length direction of each fin unit 11 is defined as a first direction X. The multiple fin units 11 are arranged along a second direction Y, where the first direction X and the second direction Y intersect, wherein the intersection includes the first direction X and the second direction Y being perpendicular. The heat exchanger 1 has an inlet 12. Each fin unit has a first flat plate region 13 and a turbulence region 14. Along the first direction X, each fin unit 11 has a third end 15 and a fourth end 16. The inlet 12 is located at the third end 15 of the fin unit 11. The first flat plate region 13... The fin unit 11 is closer to the inlet 12 than the turbulence zone 14. Along the first direction X, the extension length of the fin unit 11 is L1, and the extension length of the first flat plate zone 13 is L2. L1 and L2 satisfy the following relationship: 0.01≤L2 / L1≤0.05. Wherein, L2 / L1 equals 0.01, L2 / L1 equals 0.02, L2 / L1 equals 0.03, L2 / L1 equals 0.04, or L2 / L1 equals 0.05. When L2 / L1 equals 0.01, the heat transfer performance of the fin is better. When L2 / L1 equals 0.05, the strength of the fin is greater. Fluid enters the interplate channel 5 from inlet 12. The fluid entering the interplate channel 5 passes through the first flat plate region 13 of the fin unit 11 and enters the turbulence region 14. Thus, the fin has a first flat plate region 13, which is close to the inlet 12 relative to the turbulence region 14. The extension length L2 of the first flat plate region 13 and the extension length L1 of the fin unit 11 satisfy the following relationship: 0.01≤L2 / L1≤0.05. This allows the fin unit 11 to meet the heat exchange requirements and improve the strength of the fin unit 11 at the inlet 12, thereby enabling the interplate channel 5 to withstand higher pressure.

[0027] In this embodiment, as Figures 3-8 As shown, the fin unit 11 includes a first sidewall 17, a second sidewall 18, and a top wall 19 connecting the first sidewall 17 and the second sidewall 18; a first fluid flow channel 20 is provided between the first sidewall 17 and the second sidewall 18; along the second direction Y, a second fluid flow channel 21 is provided between two adjacent fin units 10. Fluid enters the interplate channel 5 from the inlet 12, and the fluid in the interplate channel 5 flows within the first fluid flow channel 20 and the second fluid flow channel 21.

[0028] like Figures 8-11As shown, the first sidewall 17 has a first end 22, which is away from the top wall 19; the second sidewall 18 has a second end 23, which is also away from the top wall 19; the distance between the first end 22 of the first sidewall 17 and the second end 23 of the second sidewall 18 is T; T and L2 satisfy the following relationship: 0.3≤L2 / T≤5. The distance T between the first end 22 of the first sidewall 17 and the second end 23 of the second sidewall 18 has a significant impact on the strength of the fin 10. When the distance T and the extension length L2 of the first flat plate region 13 satisfy the following relationship: 0.3≤L2 / T≤5, the part of the fin 10 near the inlet 12 has higher strength.

[0029] like Figures 6-10 As shown, the first sidewall 17 has a first fin portion 24, and the second sidewall 18 has a second fin portion 25; the turbulence zone 14 includes a plurality of first turbulence portions 26 and a plurality of second turbulence portions 27, which are alternately arranged along a first direction; the first turbulence portion 26 includes a first fin portion 28 and a second fin portion 29, the first fin portion 28 being located on the first sidewall 17, and the second fin portion 29 being located on the second sidewall 18, with the first fin portion 28 facing the first fin portion 25. The first fluid channel 20 is recessed in the direction of the first fluid channel, and the second fin plate portion 29 protrudes in the direction away from the first fluid channel; thus, the first fin plate portion 28 and the second fin plate portion 29 can disturb the fluid flow to enhance heat transfer; wherein, the first fin plate portion 28 and the second fin plate portion 29 can form a sealing structure with the adjacent wall (such as a fin plate portion; or other fin plate portions adjacent to the first fin plate portion 28 or the second fin plate portion 29), or can form a flow port, as specifically described below:

[0030] The first implementation method, exemplarily, is as follows: Figures 6-10 As shown, a portion of the first sidewall 17 is recessed toward the first fluid flow channel 20 to form a first recessed portion, and the end of the first recessed portion away from the first sidewall 17 forms a first fin plate portion 28; a portion of the second sidewall 18 protrudes toward the direction away from the first fluid flow channel 20 to form a first protruding portion, and the end of the first protruding portion away from the first sidewall 17 forms a second fin plate portion 29; taking the first fin plate portion 28 and the first fin plate portion 24 being adjacent, and the second fin plate portion 29 and the second fin plate portion 25 being adjacent as an example, a seal is formed between the first fin plate portion 28 and the first fin plate portion 24, and similarly, a seal is formed between the second fin plate portion 29 and the second fin plate portion 25.

[0031] The second implementation method, such as Figures 6-10As shown, the turbulence zone 14 also has a first flow port 30 and a second flow port 31. The wall forming the first flow port 30 includes a first fin plate portion 28. The first flow port 30 connects the first fluid flow channel 20 and the second fluid flow channel 21. The wall forming the second flow port 31 includes a second fin plate portion 29. The second flow port 31 connects the first fluid flow channel 20 and the second fluid flow channel 21. Taking the first fin plate portion 28 and the first fin plate portion 24 as adjacent, and the second fin plate portion 29 and the second fin plate portion 25 as adjacent, the first flow port 30 is formed between the first fin plate portion 28 and the first fin plate portion 24. The first flow port 30 connects the first fluid flow channel 20 and the second fluid flow channel 21. Similarly, the second flow port 31 is formed between the second fin plate portion 29 and the second fin plate portion 25. The second flow port 31 connects the second fluid flow channel 21 and the first fluid flow channel 20.

[0032] like Figures 6-10 As shown, the second turbulence section 27 includes a third fin plate section 32 and a fourth fin plate section 33. The third fin plate section 32 is located on the first sidewall 17, and the fourth fin plate section 33 is located on the second sidewall 18. The third fin plate section 32 protrudes in a direction away from the first fluid flow channel 20, and the fourth fin plate section 33 is recessed in a direction towards the first fluid channel. In this way, the third fin plate section 32 and the fourth fin plate section 33 can turbulentize the fluid flow to enhance heat transfer. The third fin plate section 32 and the fourth fin plate section 33 can form a sealing structure with adjacent walls (such as fin plate sections; or other fin plate sections adjacent to the third fin plate section 32 or the fourth fin plate section 33), or they can form flow openings, as specifically described below:

[0033] The first implementation method, exemplarily, is as follows: Figures 6-10 As shown, a portion of the first sidewall 17 protrudes in the direction away from the first fluid flow channel 20 to form a second protrusion, and the end of the second protrusion away from the first sidewall 17 forms a third wing plate portion 32; a portion of the second sidewall 18 is recessed in the direction of the first fluid flow channel 20 to form a second recess, and the end of the second recess away from the first sidewall 17 forms a fourth wing plate portion 33; taking the third wing plate portion 32 adjacent to the first wing plate portion 28 and the fourth wing plate portion 33 adjacent to the second wing plate portion 29 as an example, the third wing plate portion 32 and the first wing plate portion 28 form a seal, and similarly, the fourth wing plate portion 33 and the second wing plate portion 29 form a seal.

[0034] The second implementation method, exemplarily, is as follows: Figures 6-10As shown, the turbulence zone 14 also has a third flow port 34 and a fourth flow port 35. The wall forming the third flow port 34 includes a third fin plate portion 32, and the third flow port 34 connects to the first fluid flow channel 20 and the second fluid flow channel 21. The wall forming the fourth flow port 35 includes a fourth fin plate portion 33, and the fourth flow port 35 connects to the first fluid flow channel 20 and the second fluid flow channel 21. Taking the third fin plate portion 32 adjacent to the first fin plate portion 28 and the fourth fin plate portion 33 adjacent to the second fin plate portion 29 as an example, the third flow port 34 is formed between the third fin plate portion 32 and the first fin plate portion 28, and the third flow port 34 connects to the first fluid flow channel 20 and the second fluid flow channel 21. Similarly, the fourth flow port 35 is formed between the fourth fin plate portion 33 and the second fin plate portion 29, and the fourth flow port 35 connects to the second fluid flow channel 21 and the first fluid flow channel 20.

[0035] like Figures 5-12 As shown, the first sidewall 17 has a first base 36, and the first fin portion 24 connects the first base 36 and the top wall 19; the second sidewall 18 has a second base 37, and the second fin portion 25 connects the second base 37 and the top wall 19; the angle between the extension direction of the first fin portion 24 and the extension direction of the second fin portion 25 is α; the thickness of both the first fin portion 24 and the second fin portion 25 is t1; α, t1, L2, and T satisfy the following relationship: 0.05≤L2×t1×cos(α / 2) / T≤0.8. Thus, the structural strength of the fins is positively correlated with the thickness t1 and the extension length L2 of the first flat plate region 13, and negatively correlated with the spacing T. In automotive heat exchanger applications, satisfying the condition 0.05≤L2×t1×cos(α / 2) / T≤0.8 satisfies both strength requirements and reduces product weight and production costs.

[0036] like Figure 5 As shown, heat exchanger 1 has a first distribution zone 40, a heat exchange zone 41, and a second distribution zone 42. The first distribution zone 40 is located on one side of the heat exchange zone 41, and the second distribution zone 42 is located on the other side of the heat exchange zone 41. The inlet 12 is located in the first distribution zone 40. Fins 10 are arranged in the heat exchange zone 41. Fluid is distributed in the first distribution zone 40 and the second distribution zone 42, and heat exchange is achieved in the heat exchange zone 41. The addition of fins 10 in the heat exchange zone 41 can increase the heat exchange efficiency of heat exchanger 1.

[0037] like Figures 3-8 As shown, the interplate channel 5 also has an outlet 43, which is located in the second distribution zone 42; the fluid in the interplate channel 5 flows out from the outlet 43; similarly, the fluid in the interplate channel 5 near the outlet 43 of the fin 10 also has a large pressure, which may cause the fin 10 to deform. Based on this, it is also necessary to increase the strength of the fin 10 near the outlet 43.

[0038] More detailed, such as Figures 3-8 As shown, fin 10 also has a second flat plate region 44, which is closer to outlet 43 relative to turbulence region 14; along the first direction, one end of heat exchange region 41 has inlet 12, and the other end of heat exchange region 41 has outlet 43; fin 10 is located in heat exchange region 41, with first flat plate region 13 of fin 10 close to inlet 12 and second flat plate region 44 of fin 10 close to outlet 43. Fluid enters interplate channel 5 from inlet 12, passes through first flat plate region 13 of fin unit into turbulence region 14, then enters second flat plate region 44, and finally flows out from outlet 43. The extension length of second flat plate region 44 along the first direction is L3, and L1 and L3 satisfy the following relationship: 0.01≤L3 / L1≤0.05. Where L3 / L1 equals 0.01, L3 / L1 equals 0.02, L3 / L1 equals 0.03, L3 / L1 equals 0.04, or L3 / L1 equals 0.05; when L3 / L1 equals 0.01, the heat transfer performance of the fin is better; when L3 / L1 equals 0.05, the strength of the fin is greater. Thus, the fin has a second plate region 44, which is closer to the outlet 43 than the turbulence region 14, and the extension length L3 of the second plate region 44 and the extension length L1 of the fin unit satisfy the following relationship: 0.01≤L3 / L1≤0.05, so that the fin 10 can not only meet the heat transfer requirements, but also improve the strength of the fin 10 at the outlet 43, thereby enabling the interplate channel 5 to withstand higher pressure.

[0039] like Figures 3-8 As shown, the plates forming the inter-plate channel 5 include a first plate 38 and a second plate 39, which are alternately stacked. Along the stacking direction, a flux-side channel 6 exists between the first plate 38 and one of its adjacent second plates 39, and a water-side channel 7 exists between the first plate 38 and the other adjacent second plate 39. The thicknesses of the flux-side channel 6 and the water-side channel 7 along the stacking direction may be the same or different. Within the flux-side channel 6, the top wall 19 of the fin unit is welded to the first plate 38, and the first base 36 and the second base 37 of the fin unit are welded to the second plate 39. Within the water-side channel 7, the top wall 19 of the fin unit is welded to the second plate 39, and the first base 36 and the second base 37 of the fin unit are welded to the first plate 38.

[0040] In this embodiment, as Figures 8-12As shown, the distance T between the first end 22 of the first sidewall 17 and the second end 23 of the second sidewall 18, and the extension length L3 of the second flat plate region 44 along the first direction, satisfy the following relationship: 0.3 ≤ L3 / T ≤ 5. The distance T between the first end 22 of the first sidewall 17 and the second end 23 of the second sidewall 18 has a significant impact on the strength of the fin 10. When the distance T and the extension length L3 of the second flat plate region 44 satisfy the following relationship: 0.3 ≤ L3 / T ≤ 5, the part of the fin 10 near the outlet has higher strength.

[0041] In this embodiment, as Figures 5-12 As shown, the first sidewall 17 also has a third fin portion 45, which is located in the second flat plate region 44. The second sidewall 18 also has a fourth fin portion 46, which is located in the second flat plate region 44. The angle between the extending direction of the third fin portion 45 and the extending direction of the fourth fin portion 46 is β. The thickness of both the third fin portion 45 and the fourth fin portion 46 is t2. The angle β between the extending direction of the third fin portion 45 and the extending direction of the fourth fin portion 46, the thickness t2, the extending length L3 of the second flat plate region 44 along the first direction, and the first The distance T between the first end 22 of the sidewall 17 and the second end 23 of the second sidewall 18 satisfies the following relationship: 0.05≤L3×t2×cos(β / 2) / T≤0.8. Thus, the structural strength of the fin is positively correlated with the thickness t2 and the extension length L3 of the second plate area 44, and negatively correlated with the distance T. In automotive heat exchanger applications, under the condition that 0.05≤L3×t2×cos(β / 2) / T≤0.8 is satisfied, the strength requirements can be met, and the weight of the product and the production cost can be reduced.

[0042] For example, such as Figure 3 , Figure 4 , Figure 5 , Figure 8 and Figure 11As shown, the interplate channel 5 includes a flux-side channel 6, which has fins 10. The distance T between the first end 22 of the first sidewall 17 and the second end 23 of the second sidewall 18 and the extension length L2 of the first plate region 13 satisfy the following relationship: 1.67≤L2 / T≤5. The distance T between the first end 22 of the first sidewall 17 and the second end 23 of the second sidewall 18 and the extension length L3 of the second plate region 44 satisfy the following relationship: 1.67≤L3 / T≤5. The fluid pressure in the flux-side channel 6 is relatively high. The finned unit near the inlet 12 and outlet requires high strength. The distance T between the first end 22 of the first sidewall 17 and the second end 23 of the second sidewall 18 and the extension length L2 of the first plate area satisfy the following relationship: 1.67≤L3 / T≤5. The distance T between the first end 22 of the first sidewall 17 and the second end 23 of the second sidewall 18 and the extension length L3 of the second plate area 44 satisfy the following relationship: 1.67≤L3 / T≤5. This allows the fin 10 to meet the pressure requirements of the agent-side channel 6.

[0043] For example, such as Figure 3 , Figure 4 , Figure 5 , Figure 8 and Figure 12 As shown, the interplate channel 5 includes a water-side channel 7. It should be noted that the fluid pressures in the agent-side channel 6 and the water-side channel 7 are different. Therefore, the fluid pressure experienced by the fins 10 in the agent-side channel 6 is different from that in the water-side channel 7. Typically, the fluid pressure in the agent-side channel 6 is greater than that in the water-side channel 7. The water-side channel 7 contains fins 10. The distance T between the first end 22 of the first sidewall 17 and the second end 23 of the second sidewall 18 satisfies the following relationship with the extension length L2 of the first plate region 13: 0.5 ≤ L2 / T ≤ 1.25. The distance T between the first end 22 of the first sidewall 17 and the second end 23 of the second sidewall 18, and the extension length L4 of the second plate region 44 satisfy the following relationship: 0.5 ≤ L3 / T ≤ 1.25. Compared to the agent-side channel 6, the fluid pressure of the water-side channel 7 is smaller. The distance T between the first end 22 of the first sidewall 17 and the second end 23 of the second sidewall 18 and the extension length L2 of the first plate area satisfy the following relationship: 0.5≤L2 / T≤1.25. When the distance T between the first end 22 of the first sidewall 17 and the second end 23 of the second sidewall 18 and the extension length L3 of the second plate area 44 satisfy the following relationship: 0.5≤L3 / T≤1.25, the fin 10 can meet the pressure requirements of the water-side channel 7.

[0044] like Figures 3-5As shown, the heat exchange of the fluid is mainly concentrated in the heat exchange zone 41. The extension length of the heat exchange zone 41 has a significant impact on the heat exchange effect of the heat exchanger 1; fins 10 are arranged within the heat exchange zone 41 to enhance heat exchange. Along the first direction, the extension length of the heat exchange zone 41 is L4; the extension length of the fin unit and the extension length of the heat exchange zone 41 can be equal or unequal, for example, such as... Figure 3 As shown, the extension length L1 of the finned unit and the extension length L4 of the heat exchange zone 41 satisfy the following relationship: 0.9≤L1 / L4≤1. Thus, the fins 10 basically cover the entire heat exchange zone 41 of the heat exchanger 1, giving the heat exchanger 1 a high heat exchange efficiency.

[0045] The technical features of the above-described technical solutions can be combined in any way. For the sake of brevity, not all possible combinations of the technical features in the above-described technical solutions are described. However, as long as there is no contradiction in the combination of these technical features, they should be considered to be within the scope of this specification.

[0046] The above-described embodiments are merely examples of several implementations of this application, and while the descriptions are relatively specific and detailed, they should not be construed as limiting the scope of the utility model patent. It should be noted that those skilled in the art can make various modifications without departing from the concept of this utility model, and these modifications all fall within the protection scope of this utility model.

Claims

1. A heat exchanger, characterized in that, Includes an inter-plate channel (5), the inter-plate channel (5) having fins (10); The fin (10) includes a plurality of fin units (11), and the length direction of the fin unit (11) is defined as the first direction X; the plurality of fin units (11) are arranged along the second direction Y, and the first direction X and the second direction Y intersect; The heat exchanger (1) has an inlet (12); the finned unit (11) has a first flat plate area (13) and a turbulence area (14), the first flat plate area (13) being closer to the inlet (12) relative to the turbulence area (14); Along the first direction X, the extension length of the fin unit (11) is L1, and the extension length of the first flat plate region (13) is L2. L1 and L2 satisfy the following relationship: 0.01≤L2 / L1≤0.

05.

2. The heat exchanger according to claim 1, characterized in that, The fin unit (11) includes a first sidewall (17), a second sidewall (18), and a top wall (19) connecting the first sidewall (17) and the second sidewall (18); The first sidewall (17) has a first end (22) that is away from the top wall (19); the second sidewall (18) has a second end (23) that is away from the top wall (19); the distance between the first end (22) of the first sidewall (17) and the second end (23) of the second sidewall (18) is T; T and L2 satisfy the following relationship: 0.3≤L2 / T≤5.

3. The heat exchanger according to claim 2, characterized in that, The first sidewall (17) has a first fin portion (24), and the second sidewall (18) has a second fin portion (25). The angle between the extending direction of the first fin portion (24) and the extending direction of the second fin portion (25) is α. The thickness of the first fin portion (24) and the second fin portion (25) is t1; α, t1, L2 and T satisfy the following relationship: 0.05≤L2×t1×cos(α / 2) / T≤0.

8.

4. The heat exchanger according to claim 2 or 3, characterized in that, The interplate channel (5) also has an outlet (43); the fin unit (11) also has a second plate area (44), which is closer to the outlet (43) relative to the turbulence area (14); the extension length of the second plate area (44) along the first direction X is L3, and L1 and L3 satisfy the following relationship: 0.01≤L3 / L1≤0.

05.

5. The heat exchanger according to claim 4, characterized in that, The extension length L3 of the second plate area (44) along the first direction X, and the distance T between the first end (22) of the first sidewall (17) and the second end (23) of the second sidewall (18) satisfy the following relationship: 0.3≤L3 / T≤5.

6. The heat exchanger according to claim 5, characterized in that, The first sidewall (17) also has a third fin portion (45), and the second sidewall (18) also has a fourth fin portion (46); the angle β between the extending direction of the third fin portion (45) and the extending direction of the fourth fin portion (46); The thickness of the third fin portion (45) and the fourth fin portion (46) is t2; β, t2, L3 and T satisfy the following relationship: 0.05≤L3×t2×cos(β / 2) / T≤0.

8.

7. The heat exchanger according to claim 5 or 6, characterized in that, The interplate channel (5) includes an agent-side channel (6), the agent-side channel (6) has the fins (10), T and L2 satisfy the following relationship: 1.67≤L2 / T≤5, T and L3 satisfy the following relationship: 1.67≤L3 / T≤5; And / or, the interplate channel (5) includes a water-side channel (7), the water-side channel (7) having the fins (10); T and L2 satisfy the following relationship: 0.5≤L2 / T≤1.25, T and L3 satisfy the following relationship: 0.5≤L3 / T≤1.

25.

8. The heat exchanger according to any one of claims 2, 3, 5 and 6, characterized in that, The heat exchanger (1) has a heat exchange zone (41); along the first direction X, the extension length of the heat exchange zone (41) is L4, and the extension length L4 of the heat exchange zone (41) and the extension length L1 of the fin unit (11) satisfy the following relationship: 0.9≤L1 / L4≤1.

9. The heat exchanger according to claim 8, characterized in that, A first fluid flow channel (20) is provided between the first sidewall (17) and the second sidewall (18); the turbulence zone (14) includes a plurality of first turbulence portions (26), each of which includes a first wing plate portion (28) and a second wing plate portion (29). The first wing plate portion (28) is located on the first sidewall (17), and the second wing plate portion (29) is located on the second sidewall (18). The first wing plate portion (28) is recessed relative to the first sidewall (17) toward the first fluid flow channel (20), and the second wing plate portion (29) protrudes toward the direction away from the first fluid flow channel (20).

10. The heat exchanger according to claim 9, characterized in that, The turbulence zone (14) further includes a plurality of second turbulence portions (27), and the plurality of first turbulence portions (26) and the plurality of second turbulence portions (27) are arranged alternately along the first direction X; the second turbulence portion (27) includes a third wing plate portion (32) and a fourth wing plate portion (33), the third wing plate portion (32) is located on the first sidewall (17), and the fourth wing plate portion (33) is located on the second sidewall (18); the third wing plate portion (32) protrudes relative to the first sidewall (17) in a direction away from the first fluid flow channel (20), and the fourth wing plate portion (33) is recessed relative to the second sidewall (18) in a direction towards the first fluid flow channel (20).

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