Fin structure and heat exchanger

Abstract

The utility model relates to a fin structure and a heat exchanger, the fin structure comprises a first fin row and a second fin row which are alternately arranged along a main flow direction, the first fin row and the second fin row respectively extend along a preset extension direction Y, and the preset extension direction Y is not parallel to the main flow direction; the first fin row is provided with a plurality of first circulating grooves distributed in the preset extending direction Y, and the second fin row is provided with a plurality of second circulating grooves distributed in the preset extending direction Y; the first circulation grooves and the second circulation grooves are arranged in a staggered mode in the preset extending direction Y, so that the first circulation grooves in the non-two-end positions of the first fin row communicate with the two second circulation grooves of the adjacent second fin row, and the second circulation grooves in the non-two-end positions of the second fin row can communicate with the two first circulation grooves of the adjacent first fin row; and the circulation direction of the first circulation groove is different from that of the second circulation groove. According to the fin structure and the heat exchanger, the problems that an electric drive heat exchanger is poor in heat exchange performance and large in oil side flow resistance are solved.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of oil cooling heat exchange devices, in particular to a fin structure and a heat exchanger. BACKGROUND

[0002] Compared with traditional cars, new energy vehicles add battery coolers, electric drive coolers and other electronic (DC / DC, charger) coolers, etc. Among them, the electric drive cooler generally includes driving motor, motor controller, differential and reducer and other components. As the power output element of electric vehicles, the healthy operation of the driving motor is particularly important, especially the operating temperature of the driving motor has an important influence on the service life and operation of the driving motor. If the temperature of the driving motor is too high, the driving motor will be damaged, thereby affecting the driving stability, safety and other aspects. Therefore, it is particularly important to accurately control the operating temperature of the electric drive (mainly the driving motor).

[0003] The electric drive cooler is usually of a plate type structure, and the cold side and the hot side fluids flow in adjacent channels and produce heat exchange. The cold side fluid is usually antifreeze, and the hot side fluid is usually engine oil. The channels usually have fins inside to achieve the effect of strengthening heat exchange. The typical operating condition of the electric drive heat exchanger is high viscosity (hot side) and low flow rate. Therefore, to improve the heat exchange performance of the electric drive heat exchanger, the heat exchange capacity of the hot side (engine oil side) is generally strengthened. CONTENT OF THE UTILITY MODEL

[0004] Therefore, it is necessary to provide a fin structure and a heat exchanger to solve the problems of poor heat exchange performance and large flow resistance of the oil side of the existing electric drive heat exchanger.

[0005] The fin structure provided by the present application comprises a first fin row and a second fin row arranged alternately along a main flow direction, the first fin row and the second fin row extend along a preset extension direction Y, the preset extension direction Y and the main flow direction are not parallel, the first fin row is provided with a plurality of first flow-through grooves distributed along the preset extension direction Y, and the second fin row is provided with a plurality of second flow-through grooves distributed along the preset extension direction Y; along the preset extension direction Y, the first flow-through grooves and the second flow-through grooves are arranged in a staggered manner, so that the first flow-through grooves at positions other than the two ends of the first fin row can communicate with two second flow-through grooves of the adjacent second fin row, the second flow-through grooves at positions other than the two ends of the second fin row can communicate with two first flow-through grooves of the adjacent first fin row, and the flow-through directions of the first flow-through grooves and the second flow-through grooves are different.

[0006] In one of the embodiments, along the main flow direction, the first flow-through grooves are inclinedly arranged towards the direction close to the first end of the fin structure, the second flow-through grooves are inclinedly arranged towards the direction close to the second end of the fin structure, and the first end and the second end of the fin structure are oppositely arranged along the preset extension direction Y.

[0007] In one embodiment, one or both of the first flow channel and the second flow channel are bent.

[0008] In one embodiment, the bending direction of the first flow channel is opposite to that of the second flow channel.

[0009] In one embodiment, along the main flow direction, the flow area of ​​the first flow channel tends to increase, while the flow area of ​​the second flow channel tends to decrease.

[0010] In one embodiment, the first flow channel includes a first sub-channel and a second sub-channel, and the first fin row includes multiple sets of first side plates, a first top plate, a second side plate, and a first bottom plate connected in sequence. The first side plates, the first top plate, and the second side plates form a first sub-channel with its opening facing downwards, and the second side plates, the first bottom plate, and the first side plates form a second sub-channel with its opening facing upwards. The first sub-channel and the second sub-channel are alternately arranged along the length direction of the first fin row. The second flow channel includes a third sub-channel and a fourth sub-channel, and the second fin row includes multiple sets of third side plates, a second top plate, a fourth side plate, and a second bottom plate connected in sequence. The third side plates, the second top plate, and the fourth side plates form a third sub-channel with its opening facing downwards, and the fourth side plates, the second bottom plate, and the third side plates form a fourth sub-channel with its opening facing upwards. The third sub-channel and the fourth sub-channel are alternately arranged along the length direction of the second fin row.

[0011] In one embodiment, the width of the first top plate along the predetermined extension direction Y is smaller than the spacing between adjacent first bottom plates along the predetermined extension direction Y;

[0012] And / or, the width of the second top plate along the preset extension direction Y is less than the spacing between the adjacent second bottom plates along the preset extension direction Y.

[0013] In one embodiment, the first wing row and the second wing row are integrally formed.

[0014] This application also provides a heat exchanger, which includes a chip and the fin structure described in any of the above embodiments. The chip includes a first perforation area, a fin mounting area and a second perforation area arranged along a preset extension direction Y. The first perforation area and the second perforation area are respectively provided with channel holes. The fin structure is mounted on the fin mounting area.

[0015] In one embodiment, the channel hole includes a first channel hole, a first perforation area is provided with a plurality of first diversion protrusions and two first channel holes, the first channel hole and the edge of the chip are spaced apart to form a first flow channel, the first channel hole and the fin structure are spaced apart to form a second flow channel, the two first channel holes are spaced apart to form a third flow channel, the first flow channel, the second flow channel and the third flow channel are interconnected in pairs, and the first diversion protrusion is provided at the connection points of the first flow channel, the second flow channel and the third flow channel to divert the fluid.

[0016] In one embodiment, the channel hole includes a second channel hole, the second perforation area is provided with a plurality of second diversion protrusions and two second channel holes, the second channel hole and the edge of the chip are spaced apart to form a fourth flow channel, the second channel hole and the fin structure are spaced apart to form a fifth flow channel, the two second channel holes are spaced apart to form a sixth flow channel, the fourth flow channel, the fifth flow channel and the sixth flow channel are interconnected in pairs, and the two connecting points of the fourth flow channel, the fifth flow channel and the sixth flow channel are provided with second diversion protrusions to divert the fluid.

[0017] Compared with the prior art, the fin structure and heat exchanger provided in this application, firstly, the alternating arrangement of the first and second fin rows causes the fluid to form staggered flow paths in adjacent channels, prolonging the contact time between the fluid and the fin structure; the preset extension direction Y is not parallel to the main flow direction (such as perpendicular or inclined), which can increase the turbulence of the fluid between the fin structures and enhance the heat exchange effect.

[0018] Furthermore, the first flow channel (or second flow channel) at the non-end positions can connect two adjacent second flow channels (or first flow channels) to form a multi-level cross flow channel. This not only expands the heat exchange area, but the staggered arrangement also reduces the straightness of the flow channel, avoids fluid "short circuits," and ensures sufficient heat exchange.

[0019] Furthermore, the flow directions of the first and second flow channels are different (e.g., the inclination directions are opposite), which can further disrupt the flow field and enhance the disturbance. On the one hand, it can reduce the flow resistance of high-viscosity fluids. On the other hand, it can also reduce the flow boundary layer of the fluid by changing the flow direction of the fluid, weaken the influence of the previous boundary layer on the heat exchange effect of the subsequent fin structure, and enhance the heat exchange performance of the fin structure.

[0020] In summary, by alternating the arrangement of the first and second fins and by changing the direction of the first and second flow channels, the heat exchange efficiency on the hot side (oil side) can be significantly improved, while reducing the flow resistance of the fluid. Attached Figure Description

[0021] To more clearly illustrate the technical solutions in the embodiments of this application or the conventional technology, the drawings used in the description of the embodiments or the conventional technology will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0022] Figure 1 A partial structural schematic diagram of a heat exchanger according to an embodiment of this application;

[0023] Figure 2 for Figure 1 A partial structural diagram of the fin structure shown;

[0024] Figure 3 This is a schematic diagram of the fin structure in Example 1;

[0025] Figure 4 This is a temperature cloud map of the fin structure in Example 1;

[0026] Figure 5 This is a schematic diagram of the fin structure in Example 2;

[0027] Figure 6 This is a temperature cloud map of the fin structure in Example 2;

[0028] Figure 7 This is a schematic diagram of the fin structure in Example 3;

[0029] Figure 8 This is a temperature cloud map of the fin structure in Example 3.

[0030] Reference numerals: 100, First fin row; 110, First side plate; 120, First top plate; 130, Second side plate; 140, First bottom plate; 200, Second fin row; 210, Third side plate; 220, Second top plate; 230, Fourth side plate; 240, Second bottom plate; 300, First flow channel; 310, First dividing channel; 320, Second dividing channel; 400, Second flow channel; 410, Third dividing channel; 420, First... 500. Chip; 510. First perforation area; 511. First channel hole; 512. First diversion protrusion; 513. First flow channel; 514. Second flow channel; 515. Third flow channel; 520. Fin mounting area; 530. Second perforation area; 1000. Fin structure; 531. Second channel hole; 532. Second diversion protrusion; 533. Fourth flow channel; 534. Fifth flow channel; 535. Sixth flow channel. Detailed Implementation

[0031] Compared to traditional vehicles, new energy vehicles add battery coolers, electric drive coolers, and other electronic (DC / DC, Charger) coolers. The electric drive cooler typically includes components such as the drive motor, motor controller, differential, and reducer. As the power output component of an electric vehicle, the healthy operation of the drive motor is particularly important, especially its operating temperature, which significantly impacts its lifespan and performance. Excessive drive motor temperature can cause damage, consequently affecting driving stability and safety. Therefore, accurate temperature control of the electric drive unit (primarily the drive motor) is crucial.

[0032] Electric drive heat exchangers typically have a plate-type structure, where cold-side and hot-side fluids flow and exchange heat within adjacent channels. The cold-side fluid is usually antifreeze, while the hot-side fluid is usually engine oil. Fins are typically added inside the channels to enhance heat exchange. The typical operating conditions of an electric drive heat exchanger are high viscosity (hot side) and low flow rate. Therefore, improving the heat exchange performance of an electric drive heat exchanger is generally achieved by enhancing the heat exchange capacity of the hot side (engine oil side).

[0033] Please see Figures 1-8 In order to solve the problems of poor heat exchange performance and large flow resistance on the oil side of existing electric heat exchangers, this application provides a finned structure 1000 and a heat exchanger (including but not limited to oil coolers, water coolers or other media coolers and other heat exchange devices).

[0034] The fin structure 1000 includes a first fin row 100 and a second fin row 200 arranged alternately along the main flow direction. The first fin row 100 and the second fin row 200 extend along a preset extension direction Y, which is not parallel to the main flow direction. The first fin row 100 is provided with a plurality of first flow grooves 300 distributed along the preset extension direction Y, and the second fin row 200 is provided with a plurality of second flow grooves 400 distributed along the preset extension direction Y.

[0035] It should be noted that the main flow direction can be a straight inlet / outlet direction X, or a curved flow direction, such as a U-shaped or S-shaped direction, etc., which will not be listed here.

[0036] Along the preset extension direction Y, the first flow groove 300 and the second flow groove 400 are staggered so that the first flow groove 300 at the non-end positions of the first fin row 100 can connect with the two second flow grooves 400 of the adjacent second fin row 200, and the second flow groove 400 at the non-end positions of the second fin row 200 can connect with the two first flow grooves 300 of the adjacent first fin row 100. The flow direction of the first flow groove 300 is different from that of the second flow groove 400.

[0037] It should be noted that the preset extension direction Y is usually the width direction of the heat exchanger, the liquid inlet / outlet direction X is the length direction of the heat exchanger, and multiple fin structures 1000 are stacked along the height direction.

[0038] First, the alternating arrangement of the first fin row 100 and the second fin row 200 creates staggered flow paths for the fluid in adjacent channels, extending the contact time between the fluid and the fin structure 1000. The preset extension direction Y is not parallel to the inlet / outlet direction X (such as perpendicular or inclined), which can increase the turbulence of the fluid between the fin structures 1000 and enhance the heat transfer effect.

[0039] Furthermore, the first flow channel 300 (or the second flow channel 400) at the non-end positions can connect two adjacent second flow channels 400 (or first flow channels 300) to form a multi-level cross flow channel. This not only expands the heat exchange area, but the staggered arrangement also reduces the straightness of the flow channel, avoids fluid "short circuits", and ensures sufficient heat exchange.

[0040] Furthermore, the flow directions of the first flow channel 300 and the second flow channel 400 are different (e.g., the inclination directions are opposite), which can further disturb the flow field and enhance the disturbance. On the one hand, it can reduce the flow resistance of high-viscosity fluids. On the other hand, the fins can also reduce the flow boundary layer of the fluid by changing the flow direction of the fluid, weaken the influence of the previous boundary layer on the heat exchange effect of the subsequent fin structure 1000, and enhance the heat exchange performance of the fin structure 1000.

[0041] In summary, by alternating the arrangement of the first fin row 100 and the second fin row 200 and by changing the direction of the first flow groove 300 and the second flow groove 400, the heat exchange efficiency on the hot side (oil side) can be significantly improved, while reducing the flow resistance of the fluid.

[0042] like Figure 2 As shown, in one embodiment, the first flow channel 300 includes a first sub-channel 310 and a second sub-channel 320, and the first fin row 100 includes multiple sets of first side plates 110, first top plates 120, second side plates 130 and first bottom plates 140 connected in sequence. The first side plates 110, first top plates 120 and second side plates 130 surround to form a first sub-channel 310 with its opening facing downwards, and the second side plates 130, first bottom plates 140 and first side plates 110 surround to form a second sub-channel 320 with its opening facing upwards. The first sub-channel 310 and the second sub-channel 320 are arranged alternately along the length direction of the first fin row 100.

[0043] Correspondingly, such as Figure 2As shown, the second flow channel 400 includes a third channel 410 and a fourth channel 420. The second fin row 200 includes multiple sets of third side plates 210, second top plates 220, fourth side plates 230 and second bottom plates 240 connected in sequence. The third side plates 210, second top plates 220 and fourth side plates 230 surround to form a third channel 410 with its opening facing downward. The fourth side plates 230, second bottom plates 240 and third side plates 210 surround to form a fourth channel 420 with its opening facing upward. The third channel 410 and the fourth channel 420 are arranged alternately along the length of the second fin row 200.

[0044] This configuration, with alternating upper and lower openings, forces the fluid to flow alternately at the upper and lower positions of the fin structure 1000, increasing the contact frequency between the fluid and the surface of the fin structure 1000. Furthermore, the downward-facing opening of the first slot 310 (or the third slot 410) guides the fluid downwards, while the upward-facing opening of the second slot 320 (or the fourth slot 420) provides reverse guidance, creating a three-dimensional cross-flow that avoids the limitations of planar flow and thus improves heat transfer uniformity.

[0045] Furthermore, in one embodiment, as Figure 2 As shown, the width of the first top plate 120 along the preset extension direction Y is smaller than the spacing of the adjacent first bottom plate 140 along the preset extension direction Y.

[0046] This configuration improves the stress stability of the fin structure 1000. On the other hand, the smaller width of the first top plate 120 reduces obstruction to the upstream fluid, while the larger spacing between adjacent first bottom plates 140 provides more flow distribution paths and balances the flow distribution of each channel.

[0047] In one embodiment, such as Figure 2 As shown, the width of the second top plate 220 along the preset extension direction Y is smaller than the spacing of the adjacent second bottom plate 240 along the preset extension direction Y.

[0048] This configuration improves the stress stability of the fin structure 1000. On the other hand, the smaller width of the second top plate 220 reduces obstruction to the upstream fluid, while the larger spacing between adjacent second bottom plates 240 provides more flow distribution paths, balancing the flow distribution of each channel.

[0049] Example 1

[0050] In this embodiment, as Figure 3 and Figure 4 As shown, along the main flow direction, the first flow groove 300 is inclined toward the direction close to the first end of the fin structure 1000, and the second flow groove 400 is inclined toward the direction close to the second end of the fin structure 1000. The first end and the second end of the fin structure 1000 are arranged opposite each other along the preset extension direction Y.

[0051] With this configuration, the first flow channel 300 guides the fluid to disperse towards the first end, and the second flow channel 400 guides the fluid to disperse towards the second end, forming a bidirectional flow distribution. This avoids fluid accumulation in a single direction and reduces local pressure peaks. Furthermore, the bidirectionally inclined first and second flow channels 300 force the fluid to turn multiple times within the fin structure 1000, covering a wider area, reducing dead zones caused by flow inertia, and improving heat exchange efficiency.

[0052] Specifically, the preset extension direction Y is the left-right direction, and the main flow direction is the front-back direction. The first flow groove 300 of the first fin row 100 is inclined to the left end (first end) of the fin structure 1000 within a range of 1° to 60°, and the second flow groove 400 of the second fin row 200 is inclined to the right end (second end) within a range of 1° to 60°.

[0053] And, as Figure 3 and Figure 4 As shown, the geometric parameters of the fin structure 1000 consist of peak spacing Fp, height Fh, material thickness Ft, tooth pitch Lp, offset distance Lt, tilt angle La, and oblique stretching direction angle α. After the first side plate 110 and the second side plate 130 are obliquely opened to the left along the oblique stretching direction angle α, the third side plate 210 and the fourth side plate 230 are obliquely opened to the right along α. Simultaneously, adjacent first fin rows 100 and second fin rows 200 are offset by a distance Lt. Because the opening directions of the first fin row 100 and the second fin row 200 are different and there is an offset distance, a significant turbulence effect is generated on the fluid passing through the fin structure 1000, thereby improving heat transfer performance.

[0054] Example 2

[0055] In this embodiment, as Figure 5 and Figure 6 As shown, one or both of the first flow groove 300 and the second flow groove 400 are bent. That is, only the first flow groove 300 may be bent, only the second flow groove 400 may be bent, or both the first flow groove 300 and the second flow groove 400 may be bent.

[0056] This configuration serves two purposes. First, the tortuous first flow channel 300 and second flow channel 400 increase the tortuosity of the fluid path, enhance turbulent mixing, disrupt the boundary layer, and improve the heat transfer coefficient. Second, the opposite bending directions of the first flow channel 300 and second flow channel 400 create a counteracting effect, further intensifying turbulence and reducing the proportion of laminar flow.

[0057] Furthermore, in one embodiment, the bending direction of the first flow channel 300 is opposite to that of the second flow channel 400.

[0058] This configuration generates a counterbalancing effect, further enhancing turbulent mixing, disrupting the boundary layer, and increasing the heat transfer coefficient.

[0059] However, it should be noted that the bending direction of the first flow channel 300 and the bending direction of the second flow channel 400 can be the same or asymmetrical.

[0060] Specifically, in one embodiment, the first flow groove 300 is C-shaped and the second flow groove 400 is reverse C-shaped. The bending radius of the first flow groove 300 and the second flow groove 400 ranges from 1 mm to 100 mm, and the bending angle of the first flow groove 300 and the second flow groove 400 ranges from 1° to 180°.

[0061] In another embodiment, both the first flow channel 300 and the second flow channel 400 are bent in a zigzag shape. The fin structure 1000 is composed of peak spacing Fp, height Fh, material thickness Ft, tooth pitch Lp, offset distance Lt, tilt angle La, and oblique stretching direction angle β. After the first side plate 110 and the second side plate 130 are obliquely stretched to the left along the oblique stretching direction angle β, the stretching length is Lp / 3. Then, after being stretched by Lp / 3 along the vertical straight edge direction, they are obliquely stretched to the right along the oblique stretching direction angle β, with the stretching length also being Lp / 3. After the second fin row 200 is offset by a distance Lt relative to the first fin row 100, the third side plate 210 and the fourth side plate 230 are obliquely stretched to the right along the oblique stretching direction angle β, with the stretching length being Lp / 3. Then, they are stretched by Lp / 3 along the vertical straight edge direction, and then obliquely stretched to the left along the oblique stretching direction angle β, with the stretching length also being Lp / 3.

[0062] It should be noted that different stretch lengths can be set for different locations.

[0063] Example 3

[0064] In this embodiment, as Figure 7 and Figure 8 As shown, along the main flow direction, the flow area of ​​the first flow channel 300 tends to increase, while the flow area of ​​the second flow channel 400 tends to decrease.

[0065] This design allows for the reduction of impact pressure from high-speed fluids by increasing the area of ​​the first flow channel (300), while the reduction of the area of ​​the second flow channel (400) accelerates the flow of low-speed fluids, thus balancing the overall flow velocity differences. Furthermore, the gradient design reduces pressure loss caused by abrupt changes in cross-sectional area and avoids heat accumulation problems caused by excessively low local flow velocities.

[0066] For example, the cross-sectional area of ​​the first flow channel 300 gradually increases from the inlet to the outlet (it can start from 20 mm). 2 Increased to 30mm 2The cross-sectional area of ​​the second flow channel 400 gradually decreases (it can start from 30mm). 2 Reduced to 20mm 2 ).

[0067] Specifically, the fin structure 1000 consists of peak spacing Fp, height Fh, material thickness Ft, tooth pitch Lp, staggered distance Lt, tilt angle La, and oblique stretching direction angle γ. The third side plate 210 and the fourth side plate 230 of the second flow channel 400 are obliquely stretched inward along the oblique stretching direction angle γ, with a stretching length of Lp / 2. The first side plate 110 and the second side plate 130 of the first flow channel 300 are obliquely stretched outward along the oblique stretching direction angle γ, and the staggered distance Lt between the two rows constitutes a unit cycle.

[0068] In one embodiment, the first wing row 100 and the second wing row 200 are integrally formed structures.

[0069] That is, the first side plate 110, the first top plate 120, the second side plate 130, the first bottom plate 140, the third side plate 210, the second top plate 220, the fourth side plate 230, and the second bottom plate 240 are formed by stamping the same sheet metal part.

[0070] This design, with its one-piece molding, avoids weak points at welding or splicing points, enhances the overall mechanical strength of the fin structure 1000, and adapts to high-pressure working conditions.

[0071] It should be noted that the first top plate 120 can be flat (to increase the welding area with the plate) or bent.

[0072] However, this is not the only embodiment. In other embodiments, the first wing row 100 and the second wing row 200 may also be welded structures.

[0073] This application also provides a heat exchanger, which includes a chip 500 and a fin structure 1000 as described in any of the above embodiments. The chip 500 includes a first perforation area 510, a fin mounting area 520 and a second perforation area 530 arranged along a preset extension direction Y. The first perforation area 510 and the second perforation area 530 are respectively provided with channel holes. The fin structure 1000 is mounted on the fin mounting area 520.

[0074] This design integrates the fin mounting area 520 with the perforation area, shortening the fluid path and improving space utilization.

[0075] In one embodiment, the first perforation area 510 is provided with a plurality of first diversion protrusions 512 and two first channel holes 511. The first channel holes 511 and the edge of the chip 500 are spaced apart to form a first flow channel 513. The first channel holes 511 and the fin structure 1000 are spaced apart to form a second flow channel 514. The two first channel holes 511 are spaced apart to form a third flow channel 515. The first flow channel 513, the second flow channel 514 and the third flow channel 515 are interconnected. The first diversion protrusions 512 are provided at the points where the first flow channel 513, the second flow channel 514 and the third flow channel 515 are connected to each other to divert the fluid.

[0076] With this configuration, the first diversion protrusion 512 forces the fluid to be distributed at the bifurcation of the flow channel, avoiding the flow distribution not meeting the demand due to inertia. Furthermore, the three flow channels (first flow channel 513, second flow channel 514, and third flow channel 515) are connected in pairs to form redundant paths, so even if one flow channel is blocked, the flow can still be maintained through the other flow channels.

[0077] It should be noted that the first diversion protrusion 512 and the adjacent plate need to be welded together to increase the connection strength.

[0078] Specifically, in one embodiment, the first diversion protrusion 512 is hemispherical or cylindrical, and the first channel hole 511 is circular or elliptical.

[0079] In one embodiment, the second perforation area 530 is provided with a plurality of second diversion protrusions 532 and two second channel holes 531. The second channel holes 531 and the edge of the chip 500 are spaced apart to form a fourth flow channel 533. The second channel holes 531 and the fin structure 1000 are spaced apart to form a fifth flow channel 534. The two second channel holes 531 are spaced apart to form a sixth flow channel 535. The fourth flow channel 533, the fifth flow channel 534 and the sixth flow channel 535 are interconnected. The second diversion protrusions 532 are provided at the connection points of the fourth flow channel 533, the fifth flow channel 534 and the sixth flow channel 535 to divert the fluid.

[0080] With this configuration, the second diversion protrusion 532 forces the fluid to be distributed at the bifurcation of the flow channel, avoiding insufficient flow distribution due to inertia. Furthermore, the three flow channels (fourth flow channel 533, fifth flow channel 534, and sixth flow channel 535) are connected in pairs to form redundant paths, so even if one flow channel is blocked, flow can still be maintained through the other flow channels.

[0081] It should be noted that the second diversion protrusion 532 and the adjacent plate need to be welded together to increase the connection strength.

[0082] Specifically, in one embodiment, the second diversion protrusion 532 is hemispherical or cylindrical, and the second channel hole 531 is circular or elliptical.

[0083] In one embodiment, the fin structure 1000 can also be used in other scenarios requiring heat exchange (mainly scenarios with low flow rates and low pressure drop requirements), such as heat dissipation of condensers, evaporators, and controllers, where the fin structure 1000 can be arranged.

[0084] The technical features of the above embodiments can be combined in any way. For the sake of brevity, not all possible combinations of the technical features in the above embodiments 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.

[0085] The embodiments described above are merely illustrative of several implementation methods of this application, and while the descriptions are relatively specific and detailed, they should not be construed as limiting the scope of the patent application. It should be noted that those skilled in the art can make various modifications and improvements without departing from the concept of this application, and these all fall within the scope of protection of this application. Therefore, the patent protection scope of this application should be determined by the appended claims.

[0086] In the description of this application, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc., indicating the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this application.

[0087] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one of that feature. In the description of this application, "multiple" means at least two, such as two, three, etc., unless otherwise explicitly specified.

[0088] In this application, unless otherwise expressly specified and limited, the terms "installation," "connection," "joining," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components, unless otherwise expressly limited. Those skilled in the art can understand the specific meaning of the above terms in this application according to the specific circumstances.

[0089] In this application, unless otherwise expressly specified and limited, "above" or "below" the second feature can mean that the first feature is in direct contact with the second feature, or that the first feature is in indirect contact with the second feature through an intermediate medium. Furthermore, "above," "on top of," and "over" the second feature can mean that the first feature is directly above or diagonally above the second feature, or simply that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature can mean that the first feature is directly below or diagonally below the second feature, or simply that the first feature is at a lower horizontal level than the second feature.

[0090] It should be noted that when an element is referred to as being "fixed to" or "set on" another element, it can be directly on the other element or there may be an intervening element. When an element is considered to be "connected to" another element, it can be directly connected to the other element or there may be an intervening element. The terms "vertical," "horizontal," "upper," "lower," "left," "right," and similar expressions used herein are for illustrative purposes only and do not represent the only possible implementation.

[0091] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this application belongs. The terminology used herein in the specification of this application is for the purpose of describing particular embodiments only and is not intended to be limiting of the application. The term "and / or" as used herein includes any and all combinations of one or more of the associated listed items.

Claims

1. A finned structure, characterized in that, It includes a first wing row (100) and a second wing row (200) arranged alternately along the main flow direction. The first wing row (100) and the second wing row (200) extend along a preset extension direction Y, which is not parallel to the main flow direction. The first wing row (100) is provided with a plurality of first flow grooves (300) distributed along the preset extension direction Y, and the second wing row (200) is provided with a plurality of second flow grooves (400) distributed along the preset extension direction Y. Along a predetermined extension direction Y, the first flow groove (300) and the second flow groove (400) are staggered so that the first flow groove (300) at the non-end positions of the first fin row (100) can connect to the two second flow grooves (400) of the adjacent second fin row (200), and the second flow groove (400) at the non-end positions of the second fin row (200) can connect to the two first flow grooves (300) of the adjacent first fin row (100). The flow direction of the first flow groove (300) is different from the flow direction of the second flow groove (400).

2. The fin structure according to claim 1, characterized in that, Along the main flow direction, the first flow groove (300) is inclined toward the direction close to the first end of the fin structure (1000), and the second flow groove (400) is inclined toward the direction close to the second end of the fin structure (1000). The first end and the second end of the fin structure (1000) are arranged opposite each other along a preset extension direction Y.

3. The fin structure according to claim 1, characterized in that, One or both of the first flow channel (300) and the second flow channel (400) are bent.

4. The fin structure according to claim 3, characterized in that, The bending direction of the first flow groove (300) is opposite to that of the second flow groove (400).

5. The fin structure according to claim 1, characterized in that, Along the main flow direction, the flow area of ​​the first flow channel (300) tends to increase, while the flow area of ​​the second flow channel (400) tends to decrease.

6. The fin structure according to claim 1, characterized in that, The first flow channel (300) includes a first sub-channel (310) and a second sub-channel (320). The first fin array (100) includes multiple sets of first side plates (110), first top plates (120), second side plates (130) and first bottom plates (140) connected in sequence. The first side plates (110), the first top plates (120) and the second side plates (130) surround the first sub-channel (310) with its opening facing downward. The second side plates (130), the first bottom plates (140) and the first side plates (110) surround the second sub-channel (320) with its opening facing upward. The first sub-channel (310) and the second sub-channel (320) are arranged alternately along the length direction of the first fin array (100). The second flow channel (400) includes a third sub-channel (410) and a fourth sub-channel (420). The second fin array (200) includes multiple sets of third side plates (210), second top plates (220), fourth side plates (230), and second bottom plates (240) connected in sequence. The third side plates (210), second top plates (220), and fourth side plates (230) surround the third sub-channel (410) with its opening facing downwards. The fourth side plates (230), second bottom plates (240), and third side plates (210) surround the fourth sub-channel (420) with its opening facing upwards. The third sub-channel (410) and the fourth sub-channel (420) are arranged alternately along the length of the second fin array (200).

7. The fin structure according to claim 6, characterized in that, The width of the first top plate (120) along the preset extension direction Y is smaller than the distance between the adjacent first bottom plates (140) along the preset extension direction Y; And / or, the width of the second top plate (220) along the preset extension direction Y is less than the spacing between the adjacent second bottom plates (240) along the preset extension direction Y.

8. The fin structure according to claim 1, characterized in that, The first wing row (100) and the second wing row (200) are integrally formed structures.

9. A heat exchanger, characterized in that, The device includes a chip (500) and a fin structure (1000) as described in any one of claims 1-8. The chip (500) includes a first perforation area (510), a fin mounting area (520), and a second perforation area (530) disposed along a predetermined extension direction Y. The first perforation area (510) and the second perforation area (530) are respectively used to provide channel holes for fluid inlet and outlet. The fin structure (1000) is mounted on the fin mounting area (520).

10. The heat exchanger according to claim 9, characterized in that, The channel hole includes a first channel hole (511). The first perforation area (510) is provided with a plurality of first diversion protrusions (512) and two first channel holes (511). The first channel hole (511) and the edge of the chip (500) are spaced apart to form a first flow channel (513). The first channel hole (511) and the fin structure (1000) are spaced apart to form a second flow channel (514). The two first channel holes (511) are spaced apart to form a third flow channel (515). The first flow channel (513), the second flow channel (514) and the third flow channel (515) are interconnected in pairs. The first diversion protrusion (512) is provided at the connection points between the first flow channel (513), the second flow channel (514) and the third flow channel (515) to divert the fluid.

11. The heat exchanger according to claim 9, characterized in that, The channel hole includes a second channel hole (531). The second perforation area (530) is provided with a plurality of second diversion protrusions (532) and two second channel holes (531). The second channel hole (531) and the edge of the chip (500) are spaced apart to form a fourth flow channel (533). The second channel hole (531) and the fin structure (1000) are spaced apart to form a fifth flow channel (534). The two second channel holes (531) are spaced apart to form a sixth flow channel (535). The fourth flow channel (533), the fifth flow channel (534) and the sixth flow channel (535) are interconnected in pairs. The second diversion protrusion (532) is provided at the connection points of the fourth flow channel (533), the fifth flow channel (534) and the sixth flow channel (535) to divert the fluid.

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