Heat exchanger and heat exchanger plate therefor

Abstract

The present application relates to a kind of heat exchanger and its heat exchanger plate, heat exchanger plate includes base plate part and the partition part that protrudes relative to base plate part, base plate part has first sub base plate part and second sub base plate part, first sub base plate part and second sub base plate part are located at the two sides of partition part;Base plate part further has flow channel base plate part, flow channel base plate part connects first sub base plate part and second sub base plate part;Flow channel base plate part includes first flow channel base plate part and second flow channel base plate part, first flow channel base plate part is located at one end of partition part, and second flow channel base plate part is located at the other end of partition part, heat exchanger plate is applied in heat exchanger, fluid at first sub base plate part can simultaneously enter second sub base plate part through first flow channel base plate part and second flow channel base plate part, so, it can reduce the pressure drop of heat exchanger, and then can improve the heat transfer efficiency of heat exchanger.

Description

Technical Field

[0001] This invention relates to the field of thermal management technology, and in particular to a heat exchanger for a refrigeration system and its heat exchanger plates. 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 them. When the pressure drop in the heat exchanger is too high, the fluid cannot flow smoothly, increasing energy consumption and thus reducing the overall heat transfer efficiency of the heat exchanger. Summary of the Invention

[0003] Therefore, it is necessary to provide a heat exchanger with a lower pressure drop to address the above problems.

[0004] On the one hand, the technical solution adopted by the present invention is as follows:

[0005] A heat exchanger plate includes a base plate portion and a partition portion protruding relative to the base plate portion. The base plate portion has a first sub-base plate portion and a second sub-base plate portion, which are located on both sides of the partition portion.

[0006] The substrate portion further includes a flow channel substrate portion, which connects the first sub-substrate portion and the second sub-substrate portion; the flow channel substrate portion includes a first flow channel substrate portion and a second flow channel substrate portion, the first flow channel substrate portion being located at one end of the partition portion and the second flow channel substrate portion being located at the other end of the partition portion.

[0007] The heat exchanger plates of this application are used in a heat exchanger, and the fluid at the first sub-sub ...

[0008] On the other hand, the technical solution adopted by the present invention is as follows:

[0009] A heat exchanger includes a first inter-plate channel, wherein the plates forming the first inter-plate channel include heat exchanger plates, and the heat exchanger plates have partitions protruding toward the first inter-plate channel.

[0010] The first interplate channel has a first heat exchange area and a second heat exchange area, which are located on both sides of the partition.

[0011] The first interplate channel also has a flow port, which connects the first heat exchange area and the second heat exchange area; the flow port includes a first flow port and a second flow port, the first flow port being located at one end of the partition and the second flow port being located at the other end of the partition.

[0012] When the heat exchanger is in operation, the fluid in the first heat exchange zone can enter the second heat exchange zone through the first and second flow ports. This reduces the pressure drop of the heat exchanger and improves its heat transfer efficiency. Attached Figure Description

[0013] Figure 1 This is a schematic diagram of the heat exchanger of the present invention;

[0014] Figure 2 for Figure 1 A schematic diagram of the structure of the heat exchanger plates in the first embodiment;

[0015] Figure 3 for Figure 2 Another structural diagram from a different perspective;

[0016] Figure 4 This is a schematic diagram of the structure of a second embodiment of the heat exchanger plate of the present invention;

[0017] Figure 5 for Figure 4 A schematic diagram of the structure of the heat exchanger plates and heat exchange plates after assembly;

[0018] Figure 6 for Figure 5 Schematic diagram of the structure along the AA direction;

[0019] Figure 7 for Figure 5 Another structural diagram from a different perspective;

[0020] Figure 8 for Figure 7 A schematic diagram of the structure along the BB direction;

[0021] Figure 9 for Figure 4 A schematic diagram of the structure of the heat exchange plates in the diagram;

[0022] Figure 10 for Figure 4 A schematic diagram of the structure of the heat exchanger after the plates and fins are assembled.

[0023] Figure 11 for Figure 10 A schematic diagram of the structure of the fins in the diagram;

[0024] Figure 12 for Figure 11A schematic diagram of another embodiment of the fins;

[0025] Figure 13 for Figure 8 Another structural diagram from a different perspective;

[0026] Figure 14 for Figure 13 A cross-sectional view along the CC direction;

[0027] Figure 15 This is a schematic diagram of the structure of a second embodiment of the heat exchanger plate of the present invention;

[0028] Figure 16 This is a schematic diagram of the third embodiment of the heat exchanger plate of the present invention.

[0029] Reference numerals: 1. Heat exchanger; 2. Cover plate; 3. Heat exchange core; 4. Fluid inlet; 5. Fluid outlet; 6. First inter-plate channel; 7. Heat exchanger plate; 8. Inlet; 9. Outlet; 10. Base plate; 11. Separator; 12. First sub-base plate; 13. Second sub-base plate; 14. First flow channel base plate; 15. Second flow channel base plate; 16. Heat exchange zone; 17. First distribution zone; 18. Second distribution zone; 19. First flange; 20. Second flange 21. Edge; 22. Protrusion; 23. Heat exchange plate; 24. First heat exchange area; 25. Second heat exchange area; 26. First flow port; 27. Second flow port; 28. First end; 29. ​​Second end; 30. First partition; 31. Recess; 32. First top; 33. Bottom plate; 34. Fin; 35. First sub-fin; 36. Second sub-fin; 37. Clearance notch; 38. Reinforcing fin; 39. Opening. Detailed Implementation

[0030] To make the objectives, technical solutions, and advantages of the present invention 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 the invention and are not intended to limit the invention.

[0031] This embodiment discloses a heat exchanger 1, such as Figure 1 As shown, the device includes a cover plate 2 and a heat exchange core 3. The cover plate 2 has a fluid inlet 4 and a fluid outlet 5. The heat exchange core 3 includes multiple plates, which are stacked alternately to form multiple first inter-plate channels 6 and multiple second inter-plate channels. The multiple first inter-plate channels 6 and multiple second inter-plate channels are isolated from each other and are arranged alternately. Fluid enters the first inter-plate channels 6 in the heat exchange core 3 through the fluid inlet 4. The fluid in the first inter-plate channels 6 exchanges heat with the fluid in the second inter-plate channels through the plate walls and finally flows out from the fluid outlet 5.

[0032] like Figures 2-3 As shown, the heat exchanger plate 7 includes a base plate portion 10 and a partition portion 11 protruding relative to the base plate portion 10. The partition portion 11 has a first end 27 and a second end 28. The direction of the line connecting the first end 27 and the second end 28 is defined as a first direction X, and the direction perpendicular to the first direction X is defined as a second direction Y. The heat exchanger plate 7 has a first sub-base plate portion 12 and a second sub-base plate portion 13. Along the first direction X, the first sub-base plate portion 12 and the second sub-base plate portion 13 are respectively located on both sides of the partition portion 11. The base plate portion 10 also has a flow channel base plate portion, which connects the first sub-base plate portion 12 and the second sub-base plate portion 13. The flow channel base plate portion includes a first flow channel base plate portion 14 and a second flow channel base plate portion 15. Along the first direction X, the first flow channel base plate portion 14 is located at one end of the partition portion 11, and the second flow channel base plate portion 15 is located at the other end of the partition plate. When the pressure drop of the heat exchanger 1 is too high, the fluid cannot flow smoothly, which will lead to an increase in system energy consumption and thus reduce the overall heat transfer efficiency. The heat exchanger plate 7 is used in the heat exchanger 1. The fluid at the first sub-substrate portion 12 can simultaneously enter the second sub-substrate portion 13 through the first flow channel substrate portion 14 and the second flow channel substrate portion 15. In this way, the pressure drop of the heat exchanger 1 can be reduced, thereby improving the heat transfer efficiency of the heat exchanger 1.

[0033] like Figures 2-3As shown, the heat exchanger plate 7 has a distribution area and a heat exchange area 16. The distribution area includes a first distribution area 17 and a second distribution area 18. The first distribution area 17 is located on one side of the heat exchange area 16, and the second distribution area 18 is located on the other side of the heat exchange area 16. Along the first direction X, the extension length of the first flow channel substrate portion 14 is L1, and the extension length of the second flow channel substrate portion 15 is L2. L1 and L2 satisfy the following relationship: L1 < L2. The heat exchanger plate 7 also has an inlet 8, which is located in the first sub-substrate portion 14. The first flow channel substrate portion 14 is closer to the inlet 8 than the second flow channel substrate portion 15. The fluid first enters the first sub-substrate section 12 through inlet 8. Since the first flow channel substrate section 14 is closer to inlet 8 than the second flow channel substrate section 15, the fluid can more easily pass directly through the first flow channel substrate section 14 into the second sub-substrate section 13. If most of the fluid passes directly through the first flow channel substrate section 14 into the second sub-substrate section 13, and only a small amount of fluid passes through the heat exchange zone 16 and flows towards the second flow channel substrate section 15, it will lead to uneven fluid distribution and reduce the heat exchanger's heat exchange performance. Since the extension length L2 of the second flow channel substrate section 15 is greater than the extension length L1 of the first flow channel substrate section 14, the pressure drop of the fluid in the second flow channel substrate section 15 can be reduced, thereby encouraging more fluid to pass through the heat exchange zone 16 and flow towards the second flow channel substrate section 15, thus optimizing fluid distribution and improving the heat exchanger's heat exchange performance. Furthermore, L1 and L2 satisfy the following relationship: 6L1≤L2≤13L1, which can reduce the pressure drop while making the fluid distribution more uniform. For example, the first flow channel substrate portion 14 and the inlet 8 are both located in the first distribution area 17, and the second flow channel substrate portion 15 is located in the second distribution area 18. The heat exchanger plate 7 has a first flange 19 and a second flange 20, the first flange 19 is located in the first distribution area 17, the second flange 20 is located in the second distribution area 18, the distance from the end of the partition portion 11 near the first distribution area 17 to the first flange 19 is L1, and the distance from the end of the partition portion 11 near the second distribution area 18 to the second flange 20 is L2. Furthermore, the heat exchanger plate 7 also has an outlet 9, the outlet 9 is located in the second sub-substrate portion 13, and the first flow channel substrate portion 14 is closer to the outlet 9 than the second flow channel substrate portion 15. Fluid enters the first sub-substrate section through inlet 8. Part of the fluid can directly enter the second sub-substrate section through the first flow channel substrate section and flow out from outlet 9, thus reducing the pressure drop. Another part of the fluid enters the heat exchange zone 16 and undergoes heat exchange in the heat exchange zone 16. This part of the fluid then flows toward the second flow channel substrate section 15 and enters the second sub-substrate section 13 through the second flow channel substrate section 15. The fluid re-enters the heat exchange zone 16 and undergoes heat exchange in the heat exchange zone 16. Finally, it flows toward outlet 9 and flows out from outlet 9.

[0034] In this embodiment, as Figures 2-3 As shown, the partition 11 is strip-shaped, that is, the partition 11 is a strip-shaped protrusion; as Figure 15As shown, the partition 11 is wavy; or, as... Figure 16 As shown, the partition 11 is in the shape of a broken line; or, as... Figure 4 As shown, the partition 11 includes at least two protrusions 21, with adjacent protrusions 21 spaced apart along the first direction X. When the partition 11 is composed of multiple protrusions 21, there is a certain gap between adjacent protrusions 21, allowing a small amount of fluid to flow from the first sub-substrate portion 12 into the second sub-substrate portion 13 through this gap. When the partition 11 is wavy or zigzag-shaped, it can increase the turbulence of the fluid near the partition 11 and enhance heat transfer. Furthermore, the extension length of the partition 11 along the first direction X is L3, and the extension length of the partition 11 along the second direction Y is L4. L3 and L4 satisfy the following relationship: L3 > L4; L3 > L4, making the partition 11 elongated, i.e., the extension length of the partition 11 in the second direction Y is small. The heat transfer of the heat exchanger 1 is mainly concentrated in the sub-substrate portion. The small extension length of the partition 11 in the second direction Y can prevent the partition 11 from occupying too much of the sub-substrate portion and affecting the heat transfer performance of the heat exchanger 1.

[0035] like Figures 5-8 As shown, in heat exchanger 1, the partition portion 11 of heat exchanger plate 7 protrudes towards the first inter-plate channel 6. The plate forming the first inter-plate channel 6 also includes heat exchange plate 22. The partition portion 11 of heat exchanger plate 7 is fixedly connected to or clearance-fitted with the base plate portion of heat exchange plate 22, wherein the fixed connection includes welding. The first inter-plate channel 6 has a first heat exchange region 23 and a second heat exchange region 24. Along the first direction X, the first heat exchange region 23 and the second heat exchange region 24 are located on both sides of the partition portion 11, respectively. The first inter-plate channel 6 also has a flow port that connects the first heat exchange region 23 and the second heat exchange region 24. The flow port includes a first flow port 25 and a second flow port 26. Along the first direction, the first flow port 25 is located at one end of the partition portion 11, and the second flow port 26 is located at the other end of the partition portion 11. When the pressure drop of heat exchanger 1 is too high, the fluid cannot flow smoothly, which will lead to an increase in system energy consumption, thereby reducing the overall heat transfer efficiency. The fluid in the first heat exchange zone 23 can enter the second heat exchange zone 24 through the first flow port 25 and the second flow port 26. This reduces the pressure drop of the heat exchanger 1 and improves the heat transfer efficiency of the heat exchanger 1.

[0036] More detailed, exemplary, such as Figures 7-8As shown, the heat exchanger plate 7 has a first flange 19 and a second flange 20; the heat exchanger plate 7 and the heat exchange plate 22 are stacked to form a first inter-plate channel 6. The first end 27 is close to the first distribution area 17, and the second end 28 is close to the second distribution area 18; in the first distribution area 17, a portion of the first flange 19, the first flow channel substrate portion 14, the first end 27 of the partition portion 11, and a portion of the heat exchange plate 22 surround to form a first flow port 25; in the second distribution area 18, a portion of the second flange 20, the second flow channel substrate portion 15, the second end 28 of the partition portion 11, and a portion of the heat exchange plate 22 surround to form a second flow port 26.

[0037] like Figures 6-8 As shown, the inlet 8 of the heat exchanger plate 7 is located in the first heat exchange region 23, and the outlet 9 of the heat exchanger plate 7 is located in the second heat exchange region 24. The first flow port 25 is closer to the inlet 8 than the second flow port 26, and the flow cross-sectional area of ​​the first flow port 25 is smaller than that of the second flow port 26. For example, both the inlet 8 and the first flow port 25 are located in the first distribution region 17. The fluid first enters the first heat exchange zone 23 through inlet 8. Since the first flow port 25 is closer to inlet 8 than the second flow port 26, the fluid can more easily pass through the first flow port 25 into the second heat exchange zone 24. If most of the fluid directly enters the second heat exchange zone 24 through the first flow port 25, and only a small amount of fluid passes through the heat exchange zone 16 and flows toward the second flow port 26, it will lead to uneven fluid distribution and reduce the heat exchange performance of the heat exchanger. Since the flow cross-sectional area of ​​the second flow port 26 is larger than that of the first flow port 25, it can reduce the pressure drop of the fluid in the second flow port 26, thereby prompting more fluid to pass through the heat exchange zone 16 and flow toward the second flow port 26, thus optimizing the fluid distribution and improving the heat exchange performance of the heat exchanger 1.

[0038] like Figures 2-8 As shown, the heat exchanger plate 7 includes a base plate portion 10, which includes a first flow channel base plate portion 14 and a second flow channel base plate portion 15. The wall forming the first flow port 25 includes the first flow channel base plate portion 14, and the wall forming the second flow port 26 includes the second flow channel base plate portion 15. Along the first direction X, the extension length of the first flow channel base plate portion 14 is L1, and the extension length of the second flow channel base plate portion 15 is L2. L1 and L2 satisfy the following relationship: L1 < L2. Adjacent plates are stacked to form a first inter-plate channel 6. Along the stacking direction of the plates, the inter-plate distance at any position of adjacent plates remains unchanged. The larger the extension length of the sub-base plate portion, the larger the flow cross-sectional area of ​​the sub-base plate portion. The extension length L1 of the first flow channel base plate portion 14 is less than the extension length of the second flow channel base plate portion 15, so that the flow cross-sectional area of ​​the second flow port 26 is greater than the flow cross-sectional area of ​​the first flow port 25. In this way, the fluid distribution can be optimized, thereby improving the heat exchange performance of the heat exchanger 1.

[0039] like Figure 5 , Figure 6 , Figure 7 and Figure 8 As shown, the inlet 8, outlet 9, and first flow port 25 of the heat exchanger plate 7 are located on the same side of the first inter-plate channel 6. For example, the inlet 8, outlet 9, and first flow port 25 are all located in the first distribution area 17. Fluid enters the first heat exchange region 23 through the inlet 8. Part of the fluid can directly enter the second heat exchange region 24 through the first flow port 25 and flow out from the outlet 9, thus reducing the pressure drop. Another part of the fluid enters the heat exchange region 16 and undergoes heat exchange there. This part of the fluid then flows towards the second flow port 26 and enters the second heat exchange region 24 through the second flow port 26. The fluid re-enters the heat exchange region 16 and undergoes heat exchange there, finally flowing towards the outlet 9 and flowing out from the outlet 9.

[0040] like Figure 6 As shown, the first end 27 of the partition 11 is arc-shaped; and / or, the second end 28 of the partition 11 is arc-shaped. At fluid bends, the arc-shaped structure of the first end 27 and the second end 28 of the partition 11 can improve the uniformity of the flow field when the fluid flows through that location.

[0041] In this embodiment, as Figures 3-4 As shown, the partition 11 is strip-shaped, that is, the partition 11 is a strip-shaped protrusion; or, as Figure 14 As shown, the partition 11 is wavy; or, as... Figure 15 As shown, the partition 11 is in the shape of a broken line; or, as... Figure 4 As shown, the partition 11 includes at least two protrusions 21, with adjacent protrusions 21 spaced apart along the first direction X. When the partition 11 is composed of multiple protrusions 21, there is a certain gap between adjacent protrusions 21, allowing a small amount of fluid to flow from the first heat exchange region 23 into the second heat exchange region 24 through this gap. When the partition 11 is wavy or zigzag-shaped, it can increase the turbulence of the fluid near the partition 11, enhancing heat exchange. Furthermore, the extension length of the partition 11 along the first direction X is L3, and the extension length of the partition 11 along the second direction Y is L4. L3 and L4 satisfy the following relationship: L3 > L4. L3 > L4 makes the partition 11 elongated, meaning the extension length of the partition 11 in the second direction Y is relatively small. Since the heat exchange of the heat exchanger 1 is mainly concentrated in the heat exchange region, the smaller extension length of the partition 11 in the second direction Y can prevent the partition 11 from occupying too much of the heat exchange region and affecting the heat exchange performance of the heat exchanger 1.

[0042] like Figures 7-9As shown, the partition 11 includes a first partition 29 and a second partition 30. The first partition 29 protrudes more than the second partition 30 relative to the substrate 10. The first partition 29 is located away from the first flow port 25. The heat exchange plate 22 has a recessed portion 31 that is recessed away from the first inter-plate channel 6. That is, the recessed portion 31 protrudes towards the second inter-plate channel and forms an isolation portion. The first partition 29 is embedded in the recessed portion 31. The first partition 29 includes a first top 32, and the recessed portion 31 includes a bottom plate 33. The first top 32 and the bottom plate 33 are fixedly connected or clearance-fitted, wherein the fixed connection includes welding. Since the recessed portion 31 of the heat exchange plate 22 is recessed away from the first inter-plate channel 6, and the first partition 29 is embedded in the recessed portion 31, the direct entry of fluid from the recessed portion 31 into the second heat exchange region 24 can be reduced, thus reducing the impact on heat exchange efficiency. For example, the first interplate channel 6 is a water-side channel, and the heat exchanger plate 7 forming the water-side channel has a partition 11 protruding toward the water-side channel. In this way, the pressure drop on the water side can be reduced, thereby reducing energy consumption.

[0043] like Figures 10-14 As shown, the heat exchanger 1 also includes fins 34, each fin body comprising a first sub-fin portion 35 and a second sub-fin portion 36. The fins 34 have clearance notches 37, and along the second direction, the first sub-fin portion 35 and the second sub-fin portion 36 are located on opposite sides of the clearance notches 37. A reinforcing fin portion 38 may be provided between the first sub-fin portion 35 and the second sub-fin portion 36, having the same structure as the first sub-fin portion 35; alternatively, a gap may be provided between the first sub-fin portion 35 and the second sub-fin portion 36, thereby reducing the pressure drop of the fluid. Details are as follows:

[0044] In some implementations, such as Figure 11 As shown, the fin 34 also has at least one reinforcing fin portion 38, which is located between the first sub-fin portion 35 and the second sub-fin portion 36. One end of the reinforcing fin portion 38 is fixedly connected to the first sub-fin portion 35 or is an integral structure thereon, and the other end of the reinforcing fin portion 38 is fixedly connected to the second sub-fin portion 35 or is an integral structure thereon. Thus, on the one hand, the arrangement of the reinforcing fin portion 38 can improve the strength of the fin 34; on the other hand, it can improve the heat exchange efficiency at this location.

[0045] In other implementations, such as Figure 12 As shown, one side of the wall forming the clearance notch 37 has an opening 39. Compared to the structure of the reinforced fin portion 38 described above, the opening 39 on one side of the wall forming the clearance notch 37 reduces the obstruction to fluid flow, thereby further reducing the fluid pressure drop.

[0046] 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.

[0047] The above-described technical solutions merely illustrate several embodiments of the present invention, and while the descriptions are relatively specific and detailed, they should not be construed as limiting the scope of the invention patent. It should be noted that those skilled in the art can make various modifications without departing from the concept of the present invention, and these modifications all fall within the protection scope of the present invention.

Claims

1. A heat exchanger plate, characterized in that, The substrate includes a substrate portion (10) and a partition portion (11) protruding relative to the substrate portion (10). The substrate portion (10) has a first sub-substrate portion (12) and a second sub-substrate portion (13), which are located on both sides of the partition portion (11). The substrate portion (10) also has a flow channel substrate portion, which connects the first sub-substrate portion (12) and the second sub-substrate portion (13). The flow channel substrate portion includes a first flow channel substrate portion (14) and a second flow channel substrate portion (15), which are located at one end of the partition portion (11) and at the other end of the partition portion (11).

2. The heat exchanger plate according to claim 1, characterized in that, The partition (11) has a first end (27) and a second end (28), and the extension direction of the line connecting the first end (27) and the second end (28) is defined as the first direction X; along the first direction X, the extension length of the first flow channel substrate (14) is L1, and the extension length of the second flow channel substrate (15) is L2, and L1 and L2 satisfy the following relationship: L1 < L2; The heat exchanger plate (7) also has an inlet (8) located in the first sub-substrate portion (12), and the first flow channel substrate portion (14) is closer to the inlet (8) relative to the second flow channel substrate portion (15).

3. The heat exchanger plate according to claim 2, characterized in that, The heat exchanger plate (7) also has an outlet (9) located in the second sub-substrate portion (13), and the first flow channel substrate portion (14) is closer to the outlet (9) relative to the second flow channel substrate portion (15).

4. The heat exchanger plates according to any one of claims 1 to 3, characterized in that, The partition (11) is strip-shaped; or the partition (11) is wavy; or the partition (11) is zigzag-shaped; or the partition (11) includes at least two protrusions (21), and two adjacent protrusions (21) are arranged at intervals along the first direction X.

5. The heat exchanger plate according to claim 4, characterized in that, The direction perpendicular to the first direction X is defined as the second direction Y; the extension length of the partition (11) along the first direction X is L3, and the extension length of the partition (11) along the second direction Y is L4. L3 and L4 satisfy the following relationship: L3 > L4.

6. A heat exchanger, characterized in that, Includes a first inter-plate channel (6), the plates forming the first inter-plate channel (6) include heat exchanger plates (7), the heat exchanger plates (7) having a partition (11) protruding toward the first inter-plate channel (6); The first interplate channel (6) has a first heat exchange area (23) and a second heat exchange area (24), which are located on both sides of the partition (11); The first interplate channel (6) also has a flow port, which connects the first heat exchange area (23) and the second heat exchange area (24); the flow port includes a first flow port (25) and a second flow port (26), the first flow port (25) is located at one end of the partition (11), and the second flow port (26) is located at the other end of the partition (11).

7. The heat exchanger according to claim 6, characterized in that, The heat exchanger plate (7) also has an inlet (8) located in the first heat exchange area (23); the first flow port (25) is closer to the inlet (8) than the second flow port (26), and the flow cross-sectional area of ​​the first flow port (25) is smaller than the flow cross-sectional area of ​​the second flow port (26).

8. The heat exchanger according to claim 7, characterized in that, The heat exchanger plate (7) includes a base plate portion (10), which includes a first flow channel base plate portion (14) and a second flow channel base plate portion (15); the wall forming the first flow port (25) includes the first flow channel base plate portion (14), and the wall forming the second flow port (26) includes the second flow channel base plate portion (15). The partition (11) has a first end (27) and a second end (28), and the line connecting the first end (27) and the second end (28) is defined as the first direction X; along the first direction X, the extension length of the first flow channel substrate (14) is L1, and the extension length of the second flow channel substrate (15) is L2, and L1 and L2 satisfy the following relationship: L1 < L2.

9. The heat exchanger according to any one of claims 6 to 8, characterized in that, The heat exchanger plate (7) also has an outlet (9) located in the second heat exchange area (24); the inlet (8), the outlet (9) and the first flow port (25) are located on the same side of the first interplate channel (6).

10. The heat exchanger according to any one of claims 6 to 8, characterized in that, The dividing portion (11) is strip-shaped; or, the dividing portion (11) is wavy; or, the dividing portion (11) is zigzag-shaped; or, the dividing portion (11) includes at least two protrusions (21), with two adjacent protrusions (21) spaced apart along the first direction X.

11. The heat exchanger according to claim 10, characterized in that, The direction perpendicular to the first direction X is defined as the second direction Y; the extension length of the partition (11) along the first direction X is L3, and the extension length of the partition (11) along the second direction Y is L4. L3 and L4 satisfy the following relationship: L3 > L4.

12. The heat exchanger according to claim 11, characterized in that, The plate forming the first inter-plate channel (6) also includes a heat exchange plate (22), and the partition (11) includes a first partition (29), which is located away from the first flow port (25). The heat exchange plate (22) has a recessed portion (31) that is recessed away from the first inter-plate channel (6), and the first partition portion (29) is embedded in the recessed portion (31).

13. The heat exchanger according to any one of claims 6-8 and 11-12, characterized in that, The heat exchanger (1) further includes fins (34), the fins (34) include a fin body, the fin body includes a first sub-fin portion (35) and a second sub-fin portion (36); the fins (34) have a clearance notch (37), the first sub-fin portion (35) and the second sub-fin portion (36) are respectively located on both sides of the clearance notch (37); The fin (34) also has at least one reinforcing fin portion (38), which is located between the first sub-fin portion (35) and the second sub-fin portion (36). One end of the reinforcing fin portion (38) is fixedly connected to the first sub-fin portion (35) or is an integral structure thereon, and the other end of the reinforcing fin portion (38) is fixedly connected to the second sub-fin portion (36) or is an integral structure thereon. Alternatively, one side of the wall forming the clearance gap (37) may have an opening (39).

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