Oblique wave fin and heat exchanger

Abstract

The embodiment of the utility model provides an oblique wave fin and a heat exchanger, and relates to the field of heat exchange devices. The oblique wave fin comprises a fin body, the fin body is provided with a flow channel, the flow channel comprises a low-resistance area and a corrugated guide area, and the low-resistance area is connected with the corrugated guide area. After a cooling medium is communicated with the interior of the flow channel, along with flowing of the cooling medium, the corrugated guide area can guide the cooling medium in the corrugated guide area to the low-resistance area, so that more cooling medium participates in the heat exchange process to improve the heat exchange efficiency, and meanwhile, the heat exchange efficiency is improved. The flow state of the original cooling medium in the low-resistance area can be damaged when the cooling medium in the corrugated guide area flows to the low-resistance area, so that the heat exchange effect is enhanced, the laminar flow phenomenon is avoided, in addition, the flow speed of the cooling medium in the low-resistance area can be increased when the cooling medium in the corrugated guide area flows to the low-resistance area, and the heat exchange efficiency is improved. And the heat exchange effect is further enhanced. The embodiment of the utility model further provides a heat exchanger which comprises the oblique wave fins.

Description

Technical Field

[0001] This utility model relates to the field of heat exchange devices, and more specifically, to a sloping wave fin and a heat exchanger. Background Technology

[0002] Heat exchangers come in various forms, one way to classify them is based on whether they have fins or not, which can be divided into finless heat exchangers and finned heat exchangers. Finned heat exchangers have higher heat dissipation efficiency because they have a larger heat dissipation contact area.

[0003] For heat sources with high heat flux density (such as power chips, central control chips, etc.), finned heat exchangers are required to meet heat dissipation requirements. However, most of the fins in existing finned heat exchangers cannot guide the flowing cooling medium towards the heat source. Therefore, the cooling medium that is far from the heat source cannot effectively exchange heat with the heat source, resulting in low heat exchange efficiency. The heat exchange performance of the heat exchanger needs to be improved. Utility Model Content

[0004] This invention provides a sloping wave fin and a heat exchanger that can solve the above-mentioned problems.

[0005] The embodiments of this utility model can be implemented as follows:

[0006] An embodiment of this utility model provides a sloping wave fin, which includes: a fin body, the fin body having a flow channel; the flow channel includes a low-resistance region and a corrugated guiding region, the low-resistance region and the corrugated guiding region being connected, and the corrugated guiding region being able to guide the cooling medium to the low-resistance region.

[0007] Optionally, the fin body includes a straight portion, a transition portion, and a corrugated portion. The two sides of the transition portion are connected to the corrugated portion and the straight portion, respectively. The area where the straight portion is located is a low-resistance area, and the area where the corrugated portion is located is a corrugated guiding area.

[0008] Optionally, the cross-sectional shape of the fin body in the width direction is "C" shaped, and a straight portion is provided on at least one or both sides of the fin body in the height direction.

[0009] Optionally, the corrugated portion has continuous corrugated protrusions, which are inclined from one side of the fin body to the other side, with the proximal end of the corrugated protrusions close to the straight portion and the proximal end of the corrugated protrusions close to the input end of the cooling medium.

[0010] Optionally, the angle formed by the tilt direction of the corrugated protrusion and the length direction of the fin body is θ, where θ is an acute angle.

[0011] Optionally, the height of the flow channel is F. h The height of the low-resistance region, H1, is (0 to 0.3) * F. h .

[0012] Optionally, the spacing between adjacent fins is F. p The wavy peak height L of the fin body t = (0.25~2)*F p .

[0013] Optionally, the corrugation peak spacing L on the fin body p = (2~8)*L t .

[0014] Optionally, the fin body is provided with locking teeth, and adjacent fin bodies are stacked and connected by locking teeth.

[0015] Optionally, multiple fin bodies are stacked along their own width direction, and baffles are also provided along the stacking direction of the multiple fin bodies, with the baffles covering the outside of the fin bodies.

[0016] An embodiment of this utility model also provides a heat exchanger, including: a first substrate, a second substrate, and a plurality of oblique wave fins, wherein the first substrate and the second substrate are connected to form an inner cavity; the plurality of oblique wave fins are stacked and connected to form a stack body, the stack body is housed in the inner cavity, and the stack body is in contact with the inner wall of the first substrate and / or the second substrate.

[0017] The beneficial effects of this utility model embodiment:

[0018] The oblique corrugated fin includes a fin body with flow channels. These channels comprise a low-resistance region and a corrugated guiding region, which are connected. When cooling medium flows through the flow channels, the corrugated guiding region directs the cooling medium from its own region towards the low-resistance region, allowing more cooling medium to participate in the heat exchange process and improving heat exchange efficiency. Simultaneously, the flow of cooling medium from the corrugated guiding region to the low-resistance region disrupts the original flow state of the cooling medium in the low-resistance region, thereby enhancing the heat exchange effect and preventing laminar flow. Furthermore, the flow of cooling medium from the corrugated guiding region to the low-resistance region increases the flow velocity of the cooling medium in the low-resistance region, further enhancing the heat exchange effect.

[0019] The heat exchanger includes sloping wave fins, which have all the functions of sloping wave fins. Attached Figure Description

[0020] To more clearly illustrate the technical solutions of the embodiments of this utility model, the drawings used in the embodiments will be briefly introduced below. It should be understood that the following drawings only show some embodiments of this utility model and should not be regarded as a limitation on the scope. For those skilled in the art, other related drawings can be obtained based on these drawings without creative effort.

[0021] Figure 1 This is a schematic diagram of the stacked oblique wave fins provided in an embodiment of the present invention;

[0022] Figure 2 This is a partially enlarged schematic diagram of the oblique wave fin provided in an embodiment of this utility model;

[0023] Figure 3 This is an enlarged schematic diagram of the flow channel formed by the interlocking and stacking of the oblique wave fins provided in an embodiment of this utility model;

[0024] Figure 4 This is a schematic diagram of the oblique wave fins connected to the cooling medium in an embodiment of this utility model.

[0025] Figure 5 This is a schematic diagram illustrating the parameter annotations of the oblique wave fins provided in the embodiments of this utility model. Figure 1 ;

[0026] Figure 6 This is a schematic diagram illustrating the parameter annotations of the oblique wave fins provided in the embodiments of this utility model. Figure 2 ;

[0027] Figure 7 This is a schematic diagram illustrating the parameter annotations of the oblique wave fins provided in the embodiments of this utility model. Figure 3 ;

[0028] Figure 8 This is a schematic diagram of a sloping wave fin with low-resistance regions on both sides, provided in an embodiment of the present invention.

[0029] Figure 9 This is an enlarged schematic diagram of a flow channel formed by overlapping and stacking oblique wave fins with low resistance regions on both sides, as provided in an embodiment of this utility model.

[0030] Figure 10 This is a schematic diagram of the inclined wave fins with low resistance regions on both sides connected to the cooling medium in an embodiment of this utility model.

[0031] Figure 11 This is a schematic diagram of a heat exchanger with single-sided heat exchange provided in an embodiment of this utility model;

[0032] Figure 12 This is a schematic diagram of a heat exchanger with double-sided heat exchange provided in an embodiment of this utility model;

[0033] Figure 13 This is a diagram showing the relationship between the JF factor and the tilt angle θ of the corrugated protrusion in an embodiment of this utility model.

[0034] Figure 14In the embodiments of this utility model, the JF factor is related to (the height H1 of the low-resistance region: the height F of the flow channel). h Relationship diagram;

[0035] Figure 15 In the embodiments of this utility model, the JF factor and (the ripple peak height L of the fin body) are... t : Fin spacing F p Relationship diagram;

[0036] Figure 16 In the embodiments of this utility model, the JF factor and (the ripple peak height L of the fin body) are... t Distance L between the corrugations on the fin body p Relationship diagram.

[0037] Icons: 1-Fin body; 10-Straight section; 11-Transition section; 12-Corrugated section; 121-Corrugated protrusion; 13-Clamping tooth; 2-Flow channel; 20-Low resistance area; 21-Corrugated guide area; 3-Baffle; 4-First substrate; 5-Second substrate; 6-Stacked body; 7-Heat source. Detailed Implementation

[0038] To make the objectives, technical solutions, and advantages of the embodiments of this utility model clearer, the technical solutions of the embodiments of this utility model will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this utility model, and not all embodiments. The components of the embodiments of this utility model described and shown in the accompanying drawings can generally be arranged and designed in various different configurations.

[0039] Therefore, the following detailed description of the embodiments of the present invention provided in the accompanying drawings is not intended to limit the scope of the claimed invention, but merely to illustrate selected embodiments of the invention. All other embodiments obtained by those skilled in the art based on the embodiments of the present invention without inventive effort are within the scope of protection of the present invention.

[0040] It should be noted that similar labels and letters in the following figures indicate similar items. Therefore, once an item is defined in one figure, it does not need to be further defined and explained in subsequent figures.

[0041] In the description of this utility model, it should be noted that if terms such as "upper," "lower," "inner," or "outer" are used to indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, or the orientation or positional relationship in which the utility model product is usually placed during use, they are only for the convenience of describing this utility model 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 utility model.

[0042] Furthermore, the terms "first" and "second" are used only to distinguish descriptions and should not be interpreted as indicating or implying relative importance.

[0043] The terms “comprising,” “including,” or any other variations thereof are intended to cover a non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements includes not only those elements but also other elements not expressly listed, or elements inherent to such a process, method, article, or apparatus. Without further limitation, an element defined by the phrase “comprising one…” does not exclude the presence of other identical elements in the process, method, article, or apparatus that includes said element.

[0044] Unless otherwise explicitly specified and limited, terms such as "setup" and "connection" should be interpreted broadly. For example, "connection" can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium; it can be a connection within two components. Those skilled in the art can understand the specific meaning of the above terms in this utility model according to the specific circumstances.

[0045] It should be noted that, where there is no conflict, the features in the embodiments of this utility model can be combined with each other.

[0046] Water-cooled plate heat exchangers are widely used in thermal management of new energy vehicles, thermal management of supercomputing centers, and thermal management systems for energy storage. Taking new energy vehicles as an example, water-cooled plate applications include battery cooling plates, PTC cooling plates, central control chip cooling plates, and cooling plates for power chips such as IGBTs / SiC. Battery temperature control has a relatively low heat flux density, so a finless structure is generally used. However, due to the small heat dissipation contact area and high heat flux density of central control chips and power chips, a cold plate structure with densely welded fins is required to achieve a compact structure and high heat exchange efficiency to meet the chip's heat dissipation needs. Brazed finned chip cold plates typically include an upper substrate, fins, a lower substrate, and an outlet flange, which are stacked and brazed into a single unit. Depending on the application requirements, oxygen-free copper or aluminum alloy is generally used. The chip is fixed to the substrate of the cold plate using methods such as TIM adhesive, soldering, silver sintering, or copper sintering. Low-temperature coolant flows through the finned internal channels to cool the chip.

[0047] Currently, there are two main types of heat dissipation fins for cold plates of central control chips or power chips. The first type uses cold extrusion to directly extrude pin-fin structures onto the substrate. The most common type of a single pin-fin is a cylindrical needle shape, with the most common parameters being a cylindrical needle fin diameter of 1.5mm and a spacing >1mm. The density limit for pin-fins is a cylindrical needle fin diameter of 1mm and a spacing of 1mm. The cross-sectional profile of pin-fins can be made into elliptical or teardrop shapes to enhance heat transfer. In general, the performance of pin-fin structures has reached the limit of current processes. The second type involves brazing fins onto a smooth substrate. This type of fin is generally formed by stamping / rolling. Stamping / rolling fins cannot guarantee both a thick fin material (desired material thickness >0.25mm) and a small fin spacing (desired spacing <1mm) when the flow channel height is high (>2.5mm), thus hindering further improvements in heat transfer performance.

[0048] In view of this, an embodiment of the present invention provides a sloping wave fin and a heat exchanger. The sloping wave fin is applied to the heat exchanger and can solve the above problems. It will be described in detail below.

[0049] Please refer to Figures 1 to 4 The oblique wave fin includes a fin body 1, on which a flow channel 2 is provided. The flow channel 2 includes a low resistance region 20 and a corrugated guide region 21. The low resistance region 20 and the corrugated guide region 21 are connected. One side of the low resistance region 20 is used to connect with a heat source 7.

[0050] When the cooling medium is connected to the flow channel 2, it begins to flow along the low-resistance region 20 and the corrugated guide region 21. Because the resistance in the low-resistance region 20 is low, the cooling medium flows faster within it, thus increasing the heat exchange efficiency with the heat source 7. Secondly, as the cooling medium continues to flow within the flow channel 2, the corrugated guide region 21 gradually guides the cooling medium from its own region towards the low-resistance region 20. The cooling medium, as... Figure 4 The flow direction indicated by the arrows and guide lines in the corrugated guide area 21 allows the cooling medium, even those far from the heat source 7, to participate in the heat exchange process. Increased cooling medium exchange with the heat source 7 improves heat exchange efficiency. Simultaneously, the flow of the cooling medium from the corrugated guide area 21 towards the low-resistance area 20 disrupts the original flow state of the cooling medium in the low-resistance area 20, enhancing the heat exchange effect and preventing laminar flow. Furthermore, as the cooling medium flows from the corrugated guide area 21 towards the low-resistance area 20, it increases the pressure of the cooling medium within the low-resistance area 20, further accelerating the flow rate of the cooling medium and further enhancing the heat exchange effect.

[0051] The fin body 1 can take many forms, and this embodiment does not limit it. In this embodiment, the fin body 1 is a "C" shaped fin, that is, the cross-sectional shape of the fin body 1 in the width direction is "C". The following description will take the "C" shaped fin as an example.

[0052] The fin body 1 of the "C"-shaped fin includes a straight portion 10, a transition portion 11, and a corrugated portion 12. The two sides of the corrugated portion 12 are respectively connected to the transition portion 11, and the transition portion 11 on the side closer to the straight portion 10 is also connected to the straight portion 10. The area where the straight portion 10 is located is the low-drag area 20, and the area where the corrugated portion 12 is located is the corrugated guide area 21.

[0053] The corrugated portion 12 has continuous corrugated protrusions 121, which are evenly spaced and inclined from one side of the fin body 1 to the other. The two ends of the corrugated protrusions 121 are the proximal end and the distal end, respectively. The proximal end refers to the end closer to the cooling medium input end. The proximal end is close to the straight portion 10 so that the cooling medium in the corrugated guide region 21 can be guided to the low resistance region 20.

[0054] The oblique wave fin of this utility model divides the flow channel 2 region into a low-resistance region 20 and a corrugated guide region 21 by partitioning the flow channel 2 region. The corrugated guide region 21 has high resistance. When the flow channel 2 is connected to the cooling medium, the cooling medium in the corrugated guide region 21 will tend to flow from the high-resistance region to the low-resistance region 20. Moreover, the continuous corrugated protrusions 121 will cause the cooling medium in the corrugated guide region 21 to have a tendency to flow perpendicular to the arc surface of the corrugated protrusions 121, which strengthens the tendency of the cooling medium in the corrugated guide region 21 to flow towards the low-resistance region 20.

[0055] Since a straight portion 10 can be provided on one side of the corrugated portion 12 on the fin body 1 of the "C"-shaped fin, such as Figure 4 Alternatively, straight sections 10 can be provided on both sides of the corrugated section 12, such as... Figure 8 Therefore, two different fin forms are formed. When a straight section 10 is provided on one side of the corrugated section 12, the cooling medium in the corrugated guide region 21 flows towards the low-resistance region 20 where the straight section 10 is located. Therefore, the "C"-shaped fin is suitable for unilateral heat dissipation, and the heat source 7 is attached to the side of the "C"-shaped fin near the straight section 10. (Reference) Figures 8 to 10 When straight sections 10 are provided on both sides of the corrugated section 12, the inclination directions of the corrugated protrusions 121 connected to the straight sections 10 on both sides are opposite. This allows the cooling medium in the corrugated guide region 21 to flow to the low-resistance regions 20 on both sides. Figure 10 The arrows and guide lines in the middle flow in the direction, so the "C" shaped fins are suitable for heat dissipation on both sides at this time. The heat source 7 is attached to the "C" shaped fins on both sides near the straight part 10.

[0056] Of course, in order to prevent the cooling medium in the low resistance region 20 from forming laminar flow during flow, which is not conducive to heat exchange, protrusions, grooves, patterns, etc. can be provided in the flat part 10 to disturb the structure of the cooling medium. The density of these structures is lower than the density of the corrugated protrusions 121, and the height of these structures is lower than the height of the corrugated protrusions 121, so as to avoid the inability to guide the cooling medium to the low resistance region 20 or to create a large obstacle to the guidance of the cooling medium.

[0057] refer to Figures 5 to 7 The transition section 11 is used to transition the cooling medium from the corrugated guide region 21 to the low-resistance region 20. Therefore, the transition section 11 can achieve the transition by setting an arc-shaped surface. The smaller the height H2 of the transition section 11, the better, so as to avoid greater loss of the flow rate of the cooling medium. Generally, the height H2 of the transition section 11 is not greater than 0.6 mm.

[0058] Optionally, the angle formed by the tilting direction of the corrugated protrusion 121 and the length direction of the fin body 1 is θ, where θ is an acute angle and is generally between 20° and 79°. Through simulation experiments, it was found that θ has a better guiding effect when it is between 30° and 40°.

[0059] In this embodiment, the height of the low-resistance region 20 of the "C"-shaped fin is H1, and the height of the flow channel 2 is F. h The fin spacing of the fin body 1 is F. p The ripple peak height of fin body 1 is L t The corrugation peak spacing on the fin body 1 is L pThe height H1 of the low-resistance region 20 satisfies H1 = (0 ~ 0.3) * F h The height H1 here is not zero, and the height H1 includes 0.3F. h The ripple peak height L of fin body 1 t Satisfy L t = (0.25~2)*F p The height of the ripple peak here is L t Both include the endpoint values ​​of 0.25F on both sides. p With 2F p The distance L between the corrugation peaks on the fin body 1 p Satisfy L p = (2~8)*L t The distance between the ripple peaks here and L p Both include the endpoint values ​​2L on both sides. t With 8L t The material thickness of fin body 1 is F. t Thickness F t The thickness is 0.2mm to 0.5mm.

[0060] Refer again Figure 1 and Figure 2 The fin body 1 is provided with clamping teeth 13, which are located on both outer walls of the fin body 1. Adjacent fin bodies 1 are stacked along their width direction and connected by clamping teeth 13. Multiple clamping teeth 13 are sequentially clamped to form a shape as shown in the figure. Figure 1 The locking area is defined by the dashed box. The locking teeth 13 extend towards the width of the fin body 1. When multiple fin bodies 1 are stacked, the locking teeth 13 lock onto adjacent fin bodies 1, forming a tightly packed stack 6. Adjacent fin bodies 1 are connected by the locking teeth 13, ensuring reliable connection and eliminating the need for additional auxiliary connectors, thus reducing the number of components. Of course, the width and length of the stack 6 are determined by the number and length of the fin bodies 1, and can be designed and matched as needed in actual use.

[0061] After multiple fin bodies 1 are stacked and clamped, baffles 3 can be set on both sides of the width direction of the stack body 6. The baffles 3 cover the outside of the stack body 6, thereby protecting the fin bodies 1 and enhancing the integrity and clamping stability of the stack body 6.

[0062] The "C"-shaped fins in this embodiment can be processed individually, ensuring uniform fin thickness and a high flow channel 2 height. They can also be stacked at small intervals, resulting in a comprehensive heat exchange performance far exceeding that of current cold-extruded pin-fin structure fins. Moreover, compared to fins with open structures such as staggered teeth or louvers, the fin body 1 in this embodiment has a low-resistance region 20, resulting in lower resistance performance for the same performance.

[0063] The sloping fins of this embodiment divide the flow channel 2 region into a low-resistance region 20 and a corrugated guiding region 21. This guides the cooling medium in the corrugated guiding region 21 towards the low-resistance region 20, increasing the participation of the cooling medium in the heat exchange process and thus improving the heat exchange effect. For example, by attaching multiple high-heat chips to the outside of the low-resistance region 20 of the stack 6 along the length of the fin body 1, the cooling medium in the corrugated guiding region 21 will gradually shift towards the low-resistance region 20 as it continues to flow, thereby increasing the pressure of the cooling medium in the low-resistance region 20 and increasing the flow velocity of the cooling medium in the low-resistance region 20. This is beneficial for dissipating heat from the high-heat chips in the downstream heat dissipation area of ​​the fin body 1, avoiding the problem of uneven heat dissipation in the cooling medium flow direction of traditional heat dissipation fins, and also solving the problem of cooling medium stratification in the height direction of the fin body 1.

[0064] refer to Figure 11 and Figure 12 An embodiment of this utility model also provides a heat exchanger, including: a first substrate 4, a second substrate 5 and the aforementioned plurality of oblique wave fins, wherein the first substrate 4 and the second substrate 5 are connected and form an inner cavity.

[0065] Multiple oblique wave fins are stacked and connected to form a stack body 6, which is housed in an inner cavity. When one side of the stack body 6 has a low-resistance region 20, and the side of the stack body 6 with the low-resistance region 20 is in contact with the inner wall of the first substrate 4 or the second substrate 5, a single-sided heat exchanger is formed. Figure 11 Cooling cut-off edge Figure 11 The arrows and guide lines in the diagram indicate the direction of flow; when both sides of the stack 6 have low-resistance regions 20, and the low-resistance regions 20 on both sides of the stack 6 are in contact with the inner walls of the first substrate 4 and the second substrate 5 respectively, a double-sided heat exchanger is formed, such as... Figure 12 .

[0066] To verify the effectiveness of the heat exchanger in this embodiment and to optimize the relevant parameters, a CFD simulation model was established for simulation analysis. The simulation model is based on the single-sided heat exchange stack 6 described above.

[0067] The defined fin body 1 has a flow channel 2 height of 7mm and a fin spacing F. p It is 1.2mm thick, and the material thickness is F. t The corrugation transition height H2 is 0.5mm, with a thickness of 0.3mm. The calculation boundary is set as follows: six heat sources 7 are uniformly placed outside the stack 6, with a heat flux density of 150W / cm². 2 The temperature of the cooling medium connected is 60℃, and the inlet flow rate of the coolant is 0.5m / s. Based on the data obtained from simulation analysis, the heat transfer factor j and friction factor f of the fin body 1 are calculated.

[0068] The heat transfer factor j satisfies the following equation:

[0069]

[0070] In the formula, Nu is the Nusselt number; Re is the Reynolds number; Pr is the Prandtl number; and the Nusselt number, Reynolds number, and Prandtl number are all dimensionless numbers.

[0071] The friction factor f satisfies the following equation:

[0072]

[0073] In the formula, Δp is the pressure difference between the inlet and outlet of the cooling medium fluid, in Pa; D is the hydraulic diameter, in m; and ρ is the density of the cooling medium fluid, in kg / m³. 3 ;u m is the flow velocity of the cooling medium at point m, in m / s; l is the flow length of the cooling medium within the finned channel, in m.

[0074] The JF factor is selected as the comprehensive performance index of the fins. The JF factor satisfies the following equation:

[0075] JF = j / f 1 / 3

[0076] Plot a curve with each factor on the x-axis and the JF factor on the y-axis, and obtain the following: Figures 13 to 16 The graph shown.

[0077] Analysis of the curves shows that the tilt angle θ of the corrugated protrusion 121 should be within the range of 20° to 45°, and the height H1 of the low-resistance region 20 should be within (0.05 to 0.2)*F. h The ripple peak height L of fin body 1 t It should be within (0.35~0.65)*F p The optimized range for the corrugation peak height / corrugation peak spacing of the fin body 1 should be greater than 0.15 and less than 0.45.

[0078] The above description is merely a specific embodiment of this utility model, but the protection scope of this utility model is not limited thereto. Any variations or substitutions that can be easily conceived by those skilled in the art within the technical scope disclosed in this utility model should be included within the protection scope of this utility model. Therefore, the protection scope of this utility model should be determined by the protection scope of the claims.

Claims

1. A type of oblique wave fin, characterized in that, include: A fin body (1) having a flow channel (2); The flow channel (2) includes a low-resistance region (20) and a corrugated guide region (21), the low-resistance region (20) and the corrugated guide region (21) being connected, and the corrugated guide region (21) being able to guide the cooling medium to the low-resistance region (20).

2. The oblique wave fin according to claim 1, characterized in that, The fin body (1) includes a straight portion (10), a transition portion (11) and a corrugated portion (12). The two sides of the transition portion (11) are respectively connected to the corrugated portion (12) and the straight portion (10). The area where the straight portion (10) is located is the low resistance area (20), and the area where the corrugated portion (12) is located is the corrugated guide area (21).

3. The oblique wave fin according to claim 2, characterized in that, The fin body (1) has a "C" shaped cross-section in the width direction, and the straight portion (10) is provided on at least one or both sides of the fin body (1) in the height direction.

4. The oblique wave fin according to claim 3, characterized in that, The corrugated portion (12) has continuous corrugated protrusions (121) that are inclined from one side of the fin body (1) to the other side. The proximal end of the corrugated protrusions (121) is close to the straight portion (10) and the proximal end of the corrugated protrusions (121) is close to the input end of the cooling medium.

5. The oblique wave fin according to claim 4, characterized in that, The angle between the tilting direction of the corrugated protrusion (121) and the length direction of the fin body (1) is θ, where θ is an acute angle.

6. The oblique wave fin according to claim 1, characterized in that, The height of the flow channel (2) is F h The height H1 of the low-resistance region (20) is (0~0.3)*F h .

7. The oblique wave fin according to claim 1, characterized in that, The spacing between adjacent fin bodies (1) is F. p The wavy peak height L of the fin body (1) t = (0.25~2)*F p .

8. The oblique wave fin according to claim 7, characterized in that, The corrugation peak spacing L on the fin body (1) p = (2~8)*L t .

9. The oblique wave fin according to claim 1, characterized in that, The fin body (1) is provided with a locking tooth (13), and adjacent fin bodies (1) are stacked and connected by the locking tooth (13).

10. The oblique wave fin according to any one of claims 1 to 9, characterized in that, Multiple fin bodies (1) are stacked along their width direction, and baffles (3) are also provided along the stacking direction of the multiple fin bodies (1), the baffles (3) covering the outside of the fin bodies (1).

11. A heat exchanger, characterized in that, include: The first substrate (4), the second substrate (5), and a plurality of oblique wave fins as described in any one of claims 1 to 10, wherein the first substrate (4) is connected to the second substrate (5) and forms an inner cavity; the plurality of oblique wave fins are stacked and connected to form a stack body (6), the stack body (6) is housed in the inner cavity, and the stack body (6) is in contact with the inner wall of the first substrate (4) and / or the second substrate (5).

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