A gradient spoiler louver fin heat sink

Abstract

The application relates to the technical field of heat exchange equipment, and discloses a gradient turbulence louver fin radiator, which comprises a plurality of parallel flat tubes and wave-shaped fins arranged between the flat tubes, and the fins comprise base sheets and an array of inclined louver windows. The louver window array is sequentially provided with a guide area, a strengthening area and a transition area along the airflow direction: the window leaf opening angle of the guide area continuously increases; the angle of the strengthening area is greater than the end value of the guide area; and the angle of the transition area continuously decreases and the end value is not lower than the middle value of the guide area. The window leaf spacing is synchronously optimized, the spacing in the guide area continuously decreases, the spacing in the strengthening area is the minimum spacing, and the spacing in the transition area continuously increases. The design realizes the fine organization of air flow through the cooperation of the three areas, accurately matches the fin parameters with the physical state changes of air, significantly improves the heat exchange efficiency, effectively controls the flow resistance, optimizes the heat transfer path from the flat tube to air, eliminates the local heat exchange dead zone, and finally balances the high-efficiency heat exchange and low flow resistance, thereby improving the overall energy efficiency.

Description

Technical Field

[0001] This application relates to the field of heat exchange device technology, and in particular to a gradient turbulence type louvered finned radiator. Background Technology

[0002] Radiators are key components in thermal management systems, and their performance directly impacts the energy efficiency and reliability of numerous fields, including automobiles, air conditioning, and electronic equipment. In a typical radiator structure, multiple flat tubes are arranged in parallel, with corrugated fins between them to increase the heat exchange area on the air side. The coolant inside the tubes conducts heat through the tube walls to the fins, where it is ultimately carried away by the air flowing over the fin surface. However, this basic corrugated fin structure has significant performance limitations. Due to the singular airflow pattern on the fin surface and the relatively thick thermal boundary layer, the heat exchange efficiency is low, making it difficult to meet the high-efficiency heat dissipation requirements of modern cooling systems.

[0003] To overcome the performance limitations of basic corrugated fins, the industry has developed louvered fin structures. This structure cuts and guides the flowing air by stamping louvers with a certain angle onto the fin surface, disrupting the thermal boundary layer and thus enhancing heat transfer to some extent. However, existing louvered fin structures still have many inherent defects, the core problem being insufficient flow field organization capabilities.

[0004] First, the commonly adopted homogenized design concept makes it unable to adapt to the dynamic changes in the physical state (temperature, density, etc.) of air as it flows through the finned channels. This design mismatch with the flow state makes it difficult for existing structures to achieve precise guidance of fluid flow. Second, there is an irreconcilable contradiction between heat transfer efficiency and flow resistance: simply increasing the louver angle or fin density to enhance heat transfer often leads to a sharp increase in airflow resistance, resulting in a significant increase in fan energy consumption. A deeper problem is that existing louvered fins have insufficient control over micro-flows, and unreasonable flow separation and vortex dead zones easily form on the fin surface, causing some heat transfer areas to fail to be fully utilized, thus limiting the full exploitation of their heat transfer potential.

[0005] In summary, existing louvered fin technology lacks effective means for precise guidance and controllable disturbance of fluid flow, and cannot achieve the synergy of high-efficiency heat exchange and low flow resistance. This has become a technical bottleneck restricting further breakthroughs in radiator performance. Summary of the Invention

[0006] In view of this, this application proposes a gradient turbulence type louvered fin radiator, which aims to solve the technical problem that there is an inherent contradiction between heat exchange efficiency and flow resistance caused by the inefficient flow organization of existing louvered fins and their inability to adapt to changes in air flow state.

[0007] The technical solution of this application is implemented as follows: This application provides a gradient-flow louvered finned heat sink, comprising: Multiple parallel flat tubes; The wavy fins are disposed between adjacent flat tubes, the fins including a substrate and an array of louvers disposed on the inclined surface of the substrate; The louver array is divided into a guiding zone that accelerates and guides the fluid, an enhancement zone that violently disturbs the fluid to enhance heat exchange, and a transition zone that guides the fluid to drain smoothly. The opening angle of the louvers in the guiding zone increases continuously along the airflow direction; the opening angle of the louvers in the strengthening zone is greater than the opening angle at the end of the guiding zone; the opening angle of the louvers in the transition zone decreases continuously along the airflow direction, and the opening angle at the end of the transition zone is not less than the midpoint of the opening angle of the guiding zone. The slat spacing in the guide zone decreases continuously along the airflow direction, the slat spacing in the reinforcement zone is the minimum spacing in the louver array, and the slat spacing in the transition zone increases continuously along the airflow direction.

[0008] Based on the above technical solution, preferably, the opening angle of the window leaf in the guiding area increases linearly from 5°-10° to 20°-30°; the opening angle of the window leaf in the reinforcing area is 25°-35°; the opening angle of the window leaf in the transition area decreases linearly from the opening angle of the reinforcing area, and its end angle is 15°-25°.

[0009] Based on the above technical solution, preferably, the window leaf spacing in the guide area is linearly reduced from 1.6mm-2.0mm to 1.3mm-1.6mm; the window leaf spacing in the reinforcement area is 1.0mm-1.4mm; and the window leaf spacing in the transition area is linearly increased from the spacing in the reinforcement area to 1.5mm-1.9mm.

[0010] Based on the above technical solution, preferably, the surface of the window blade in the guiding zone is provided with strip-shaped guiding protrusions parallel to the airflow direction; the surface of the window blade in the strengthening zone is provided with randomly or interlaced turbulence excitation protrusions; and the surface of the window blade in the transition zone is provided with guiding grooves parallel to the airflow direction.

[0011] Based on the above technical solution, preferably, the height or depth of the strip-shaped flow guiding protrusion, the turbulence excitation protrusion and the flow guiding groove is 30-100um.

[0012] Based on the above technical solution, preferably, along the height of the fin perpendicular to the airflow direction, the area located on both sides of the inclined surface of the substrate with a width of 1-5mm is the first region, and the window opening angle of the first region is A° to B°; the area in the middle of the inclined surface of the substrate is the second region, and the window opening angle of the second region is C° to D°; wherein, A>D and B>C.

[0013] Based on the above technical solution, preferably, the venetian blind array is formed on an independent substrate, which is fixedly connected to the inclined surface of the substrate.

[0014] Based on the above technical solution, preferably, the louver array is provided on both the front and back sides of a single inclined surface of the substrate.

[0015] Based on the above technical solution, preferably, the length of the guiding area accounts for 30%-40% of the total length of the fin, the length of the reinforcing area accounts for 30%-40%, and the length of the transition area accounts for 10%-20%.

[0016] Based on the above technical solution, preferably, the surface of the flat tube is provided with a microgroove structure, and the root of the fin is brazed to the surface of the flat tube by brazing material filled into the microgroove structure.

[0017] This application has the following advantages over the prior art: 1) The gradient bleed louvered finned radiator disclosed in this application achieves refined organization of airflow through the coordinated design of the guiding zone, the strengthening zone, and the transition zone. The changes in fin parameters precisely match the physical state changes of air from low to high temperatures, significantly improving heat exchange efficiency and effectively controlling flow resistance. This structure optimizes the heat transfer path from the flat tube to the air, eliminates local heat exchange dead zones, and ultimately achieves a balance between high-efficiency heat exchange and low flow resistance, improving overall energy efficiency.

[0018] 2) By specifying the range of spacing parameters, the functions of the guiding zone, the strengthening zone, and the transition zone are precisely implemented. The spacing variation and the optimization of the window angle work together to expand the heat exchange area while controlling the flow resistance, accurately matching the changes in the physical state of the air, improving the heat transfer efficiency from the flat tube to the air, and ultimately achieving a balance between high-efficiency heat exchange and low flow resistance in the radiator.

[0019] 3) By setting specialized microstructures on the surface of the vents in different functional areas, cross-scale synergistic optimization is achieved in conjunction with changes in macroscopic parameters. The strip-shaped flow-guiding protrusions, turbulence-inducing protrusions, and flow-guiding grooves play key roles in "smooth flow field introduction," "violent heat transfer enhancement," and "smooth heat dissipation," respectively, precisely matching changes in the air's physical state and the heat flow distribution of the flat tube. This design achieves active control of the flow at the microscopic level, ultimately significantly improving the overall heat transfer efficiency and energy efficiency of the radiator from the flat tube to the air.

[0020] 4) By partitioning the fins along their height and setting the vent angles of the fins, the vent angles (A° to B°) in the high heat flux density region (first region) near the flat tube are set higher than those in the middle low heat flux density region (second region) (C° to D°), satisfying the conditions A>D and B>C. This achieves a precise match between the heat transfer intensity and heat flux distribution on the fin surface. This design allows the high heat flux region to enhance turbulence through large-angle vents, quickly removing heat transferred from the flat tube and preventing heat accumulation; while the low heat flux region uses small-angle vents to reduce flow resistance and avoid energy waste. Overall, this scheme significantly improves the heat transfer efficiency and energy efficiency of the radiator without substantially increasing the pressure drop, and optimizes the thermal management performance in the high-temperature region.

[0021] 5) By forming the louver array on a separate substrate, which is then fixedly connected to the beveled surface of the base plate, this separate structure decouples the louver forming process from the base plate manufacturing. This design brings multiple technical benefits: First, the integrity of the base plate structure is protected, and its resistance to vibration and thermal fatigue is enhanced; second, the louver array can achieve a high-density layout, and the reduction in the louver spacing significantly increases the heat exchange surface area and improves heat dissipation intensity; third, the airflow path is controlled, reducing eddy current energy loss and flow resistance; finally, modular production improves manufacturing yield, and the base plate can be pre-processed and standardized, reducing overall costs. Attached Figure Description

[0022] To more clearly illustrate the technical solutions in the embodiments of this application or the prior art, the drawings used in the description of the embodiments or the prior art 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.

[0023] Figure 1 This is a three-dimensional structural schematic diagram of the gradient turbulence type louvered finned heat sink disclosed in this application; Figure 2 This is a schematic diagram of the planar structure of the gradient turbulence type louvered finned heat sink disclosed in this application; Figure 3This is a side view of the gradient bleed louvered finned radiator disclosed in this application; Figure 4 This is a first-view three-dimensional structural diagram of the fin disclosed in this application; Figure 5 This is a schematic diagram of the fin and flat tube assembly structure disclosed in this application; Figure 6 This is a three-dimensional structural diagram of the venetian blind array disclosed in this application; Figure 7 This is a schematic diagram of the planar structure of the venetian blind array disclosed in this application; Figure 8 for Figure 3 Enlarged view of a portion of point A in the middle; Figure 9 for Figure 6 Enlarged view of a section at point B in the middle; Figure 10 for Figure 6 Enlarged view of a section at point C; Figure 11 for Figure 6 Enlarged view of a section at point D; Figure label: 1. Flat tube; 2. Fin; 21. Substrate; 22. Louver array; Q1. Guiding region; Q2. Reinforcement region; Q3. Transition region; 220. Window leaf; 2201. Strip-shaped flow guiding protrusion; 2202. Turbulence excitation protrusion; 2203. Flow guiding groove; 211. First region; 212. Second region; 23. Substrate; 11. Micro-trench structure. Detailed Implementation

[0024] To make the objectives, technical solutions, and advantages of this application clearer, the technical solutions of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, not all embodiments. Based on the embodiments of this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0025] In the description of the embodiments of this application, it should be noted that, unless otherwise explicitly specified and limited, the terms "connected" and "linked" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; 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. Those skilled in the art can understand the specific meaning of the above terms in the embodiments of this application based on the specific circumstances.

[0026] In the description of the embodiments of this application, it should be noted that the terms "center", "longitudinal", "lateral", "up", "down", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", and "outer" indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing the embodiments of 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. Therefore, they should not be construed as limitations on the embodiments of this application.

[0027] 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 one or more of that feature. In the description of this application, "multiple" means two or more, unless otherwise explicitly specified.

[0028] The embodiments of this application are described in detail below. Examples of these embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and intended to explain this application, and should not be construed as limiting this application.

[0029] The following disclosure provides numerous different embodiments or examples for implementing various structures of this application. To simplify the disclosure, specific examples of components and arrangements are described below. These are merely examples and are not intended to limit the scope of this application. Furthermore, reference numerals and / or letters may be repeated in different examples. Such repetition is for simplification and clarity and does not in itself indicate a relationship between the various embodiments and / or arrangements discussed. In addition, various specific examples of processes and materials are provided in this application; however, those skilled in the art will recognize the applicability of other processes and / or the use of other materials.

[0030] like Figure 1 As shown, combined with Figure 2-11 This application discloses a gradient turbulence type louvered fin radiator, which includes multiple parallel flat tubes 1 and wavy fins 2 disposed between adjacent flat tubes 1.

[0031] The flat tube 1 serves as a heat source, and the coolant inside it carries heat through the tube wall to the root of the fin 2. The fin 2 then enhances heat dissipation by increasing the heat exchange area and optimizing airflow.

[0032] Specifically, the function of the radiator is to transfer the heat of the coolant in the flat tube 1 to the air through the fins 2. The complete heat transfer path is: coolant in the flat tube 1 → tube wall of the flat tube 1 → root of the fins 2 (through the joint) → base plate 21 of the fins 2 → surface of the louver 220 → flowing air.

[0033] In this embodiment, the fin 2 consists of a substrate 21 and a louver array 22 disposed on the inclined surface of the substrate 21. The louver array 22 is divided into three functionally different regions along the airflow direction: a guiding region Q1, a strengthening region Q2, and a transition region Q3. This partitioned design allows the fin 2 to dynamically adapt to changes in the physical state of the air as it flows through the channel, thereby systematically improving the heat transfer efficiency from the flat tube 1 to the air.

[0034] The guide zone Q1 is used to prepare the flow field for efficient heat exchange and reduce the overall flow resistance of the flat tube 1 system.

[0035] Air enters through the inlet and first flows through the guide zone Q1 of fin 2, where the air temperature is lowest and the heat transfer potential is greatest. The guide zone Q1 employs a design with continuously increasing 220° angle and continuously decreasing spacing of the fins. Its purpose is not to immediately achieve maximum heat transfer, but rather to smoothly guide and accelerate the airflow. This design significantly reduces air inlet resistance and avoids flow separation, thereby reducing the power required to drive the airflow, which is crucial for the overall energy efficiency of the radiator system.

[0036] In this embodiment, the opening angle of the louvers 220 in the guiding zone Q1 continuously increases along the airflow direction. This gradual design allows the airflow to be smoothly accelerated and guided when entering the channel of fin 2, avoiding sudden flow separation or vortices at the inlet. The angle gradually increases from a small value, helping to reduce the initial impact resistance of the airflow and preparing for the subsequent enhanced heat transfer stage. As air flows through this region, its flow boundary layer is gradually disrupted, and the heat transfer process starts gently, laying the foundation for overall low flow resistance operation.

[0037] The enhanced zone Q2 is used for "violent" heat exchange in the area with the most concentrated heat, matching the heat flow input of the flat tube 1.

[0038] After the air flows through the guiding zone Q1, the temperature begins to rise, and the heat flux density on the surface of fin 2 reaches its peak due to its proximity to the flat tube 1. At this point, the large opening angle and minimum spacing design of the reinforcement zone Q2 begin to play a crucial role. These window blades 220 violently shear and turbulent the air, completely disrupting the thermal boundary layer, allowing cold air to directly impact the surface of fin 2 heated by the flat tube 1. This design directly addresses the critical aspect of "how the heat conducted from the flat tube 1 is carried away from the fin 2 most quickly," preventing heat accumulation at the root of fin 2, thereby reducing the average temperature of fin 2 itself and increasing the temperature difference between the flat tube 1 and fin 2. This, in turn, strengthens the driving force for heat conduction from the flat tube 1 to the fin 2. In this embodiment, the opening angle of the window blade 220 in the reinforcement zone Q2 is greater than the opening angle at the end of the guide zone Q1, forming the largest angle in the entire array. After the air flows through the guide zone Q1, its temperature rises, and its heat transfer capacity decreases. Increasing the window blade angle 220 at this point generates strong turbulent disturbances, disrupting the thermal boundary layer and forcing the air to fully contact the surface of the fin 2. This directly addresses the needs of the high heat flux density region at the root of the flat tube 1, rapidly removing the heat transferred from the flat tube 1 by enhancing the local heat transfer intensity, thus preventing heat accumulation at the base of the fin 2.

[0039] The transition zone Q3 is used to ensure that hot air is discharged smoothly and to maintain the continuous heat output of the flat tube 1.

[0040] After the air is heated and its heat exchange capacity decreases, the design of the transition zone Q3 (reduced angle, increased spacing) aims to reorganize the flow field, giving the airflow axial momentum and efficiently pushing the hot air carrying the heat from the flat tube 1 out of the flow channel. If the hot air stagnates, it will cause the temperature of the fins 2 to rise, reducing the temperature difference with the flat tube 1 and thus inhibiting further heat loss from the flat tube 1. Therefore, the smooth heat dissipation function of the transition zone Q3 is crucial to ensuring that the heat from the flat tube 1 can be continuously carried away and maintaining the long-term efficient operation of the radiator.

[0041] In this embodiment, the opening angle of the window blade 220 in the transition zone Q3 continuously decreases along the airflow direction, and its terminal angle is not lower than the midpoint of the opening angle of the guide zone Q1. This design avoids flow instability caused by abrupt parameter changes, instead reorganizing the flow field through a smooth attenuation of the angle. The reduced angle decreases the lateral shear force of the airflow, giving the air stronger axial momentum, thereby promoting the efficient exhaust of heated air. The lower limit constraint of the terminal angle prevents premature collapse of heat transfer capacity, ensuring that the region can still maintain effective disturbance. This avoids the temperature rise of fin 2 caused by hot air stagnation, maintains the temperature difference between the flat tube 1 and the fin 2, thereby ensuring continuous heat transfer from the flat tube 1 to the fin 2.

[0042] In this embodiment, the spacing of the louvers 220 in the guiding zone Q1 continuously decreases along the airflow direction, which increases the number of louvers 220 per unit length and gradually expands the heat exchange area. The synergistic effect of decreasing spacing and increasing angle enhances the heat exchange intensity under controllable resistance, ensuring that the heat from the flat tube 1 is effectively absorbed at the front end of the fins 2. The spacing of the louvers 220 in the strengthening zone Q2 is the smallest among the louver array 22. The dense arrangement of louvers 220 maximizes the heat exchange surface area and compensates for the heat exchange attenuation caused by the rise in air temperature through high-frequency disturbances, achieving efficient heat dissipation in the high heat load area in the middle of the flat tube 1. The spacing of the louvers 220 in the transition zone Q3 continuously increases, providing a wider channel for airflow, significantly reducing flow resistance, and assisting in the rapid discharge of hot air, thereby maintaining the stable heat output of the flat tube 1.

[0043] The gradient-flow louvered fin radiator disclosed in this application achieves refined airflow organization through the coordinated design of the guiding zone Q1, the strengthening zone Q2, and the transition zone Q3. The changes in the fin parameters precisely match the physical state changes of the air from low to high temperatures, significantly improving heat transfer efficiency and effectively controlling flow resistance. This structure optimizes the heat transfer path from the flat tube 1 to the air, eliminates local heat transfer dead zones, and ultimately achieves a balance between high-efficiency heat transfer and low flow resistance, improving overall energy efficiency.

[0044] In some embodiments, this application further defines the window opening angle parameter range of the guide zone Q1, the reinforcement zone Q2 and the transition zone Q3. These parameter ranges optimize the airflow organization on the surface of the fin 2, enabling the fin 2 to more accurately match the physical state changes of the air as it flows over the surface of the flat tube 1, thereby improving the heat transfer efficiency from the flat tube 1 to the air.

[0045] Specifically, the opening angle of the window blade 220 in the guiding zone Q1 increases linearly from 5°-10° to 20°-30°. This gradual design ensures smooth acceleration of the airflow at the inlet. The smaller initial angle (5°-10°) effectively reduces the initial impact resistance of the air, avoids flow separation, and creates low-resistance conditions for heat dissipation at the root of the flat tube 1. The gradual increase in angle to 20°-30° gently guides the airflow, gradually disrupting the thermal boundary layer and fully utilizing the high heat transfer potential of the air at low temperatures to orderly absorb the heat conducted from the flat tube 1.

[0046] The window opening angle of the louver 220 in the enhanced zone Q2 is set to a relatively large value of 25°-35°, targeting the critical stage where the air temperature rises and the heat exchange capacity decreases after flowing through the guide zone Q1. This angle range can generate strong turbulent disturbances, completely destroying the thermal boundary layer on the surface of fin 2, forcing the cold air to fully contact the heated surface of fin 2 in the flat tube 1. This design directly addresses the needs of the high heat flux density region in the middle of the flat tube 1, quickly removing the heat transferred from the flat tube 1 through high-intensity heat exchange, preventing heat accumulation at the base of fin 2, and maintaining the temperature difference driving force between the flat tube 1 and fin 2.

[0047] The opening angle of the 220° window blade in the transition zone Q3 decreases linearly from that in the reinforcement zone Q2, with the end angle controlled between 15° and 25°, achieving a smooth transition of the flow field. The reduced angle lowers the lateral shear force of the airflow and imparts axial momentum to the air, allowing the heated air to be smoothly discharged from the flow channel. An end angle of at least 15° ensures that this region retains sufficient turbulence capacity, preventing premature decay of heat transfer capacity and ensuring that heat from the flat tube 1 can be continuously discharged, preventing hot air stagnation that could lead to an increase in the temperature of the fins 2.

[0048] In some embodiments, this application further defines the range of window blade 220 spacing parameters for the guiding region Q1, the reinforcing region Q2, and the transition region Q3. These parameters optimize the airflow channel density on the surface of the fin 2 and, in conjunction with changes in the window opening angle, precisely control the airflow state, thereby improving the heat transfer efficiency from the flat tube 1 to the air.

[0049] The spacing of the louvers 220 in the guiding zone Q1 decreases linearly from 1.6mm-2.0mm to 1.3mm-1.6mm. This gradual design progressively increases the number of louvers 220 per unit area at the airflow inlet. The initially larger spacing (1.6mm-2.0mm) reduces the initial airflow resistance, allowing the airflow to smoothly enter the fin 2 channel; the gradual reduction in spacing to 1.3mm-1.6mm allows the heat exchange area to expand in an orderly manner, enhancing the intensity of convective heat transfer. This design ensures that the heat at the root of the flat tube 1 can be efficiently absorbed by the low-temperature air, while also preparing a denser set of disturbance points for the subsequent enhanced heat transfer stage.

[0050] The louver 220 spacing in the enhanced zone Q2 is set to a minimum of 1.0mm-1.4mm, targeting the critical stage where the temperature rises and heat exchange demand increases after the air flows through the guide zone Q1. This minimum spacing creates the highest louver 220 density across the entire fin 2, maximizing the heat exchange surface area and thoroughly disrupting the thermal boundary layer through high-frequency disturbances. This directly addresses the high heat flux density region in the middle of the flat tube 1, forcing the air to fully contact the fin 2 surface, quickly carrying away the heat transferred from the flat tube 1, and preventing heat accumulation at the base of the fin 2.

[0051] The spacing of the louvers 220 in the transition zone Q3 increases linearly from the spacing in the reinforcement zone Q2 to 1.5mm-1.9mm, providing a gradually widening channel for airflow. This increased spacing reduces flow resistance, imparts stronger axial momentum to the hot air, and facilitates its smooth exit from the flow channel. The end spacing is controlled within the range of 1.5mm-1.9mm to avoid flow separation caused by sudden channel expansion, ensuring that heat from the flat tube 1 can be continuously dissipated and maintaining the efficient operation of the radiator.

[0052] By specifying the range of spacing parameters, the functions of the guiding zone Q1, the strengthening zone Q2, and the transition zone Q3 are precisely implemented. The spacing variation and the optimized window angle work together to expand the heat exchange area while controlling the flow resistance, accurately matching the changes in the air's physical state, improving the heat transfer efficiency from the flat tube 1 to the air, and ultimately achieving a balance between high-efficiency heat exchange and low flow resistance in the radiator.

[0053] In some embodiments, this application also provides structural configurations for the surface structures of the window blades 220 in the guiding region Q1, the reinforcing region Q2, and the transition region Q3. These micro-geometric features, in conjunction with macro-level partition angles and spacing parameters, achieve refined control of the airflow state by applying disturbances of different natures to the airflow, thereby optimizing the heat transfer process from the flat tube 1 to the air.

[0054] Specifically, the surface of the window blade 220 in the guiding area Q1 is provided with strip-shaped guide protrusions 2201 parallel to the airflow direction. When air flows through this area, these low, streamlined protrusions can organize the low-speed airflow closely adhering to the surface of the window blade 220, generating stable, small-scale vortices. This flow organization method makes the mainstream air flow more closely to the surface of the window blade 220, effectively suppressing large-scale flow separation and significantly reducing intake resistance. The heat at the root of the flat tube 1 is conducted to the window blade 220 through the base plate 21 of the fin 2, and can be efficiently absorbed by the low-temperature air that is smoothly introduced under low flow resistance conditions, laying the foundation for high efficiency and low energy consumption in the entire heat exchange process.

[0055] The surface of the louver 220 in the enhanced zone Q2 is provided with randomly or staggered turbulence-inducing protrusions 2202. When air flows into this region from the guide zone Q1, the temperature has already increased, and the heat transfer driving force has decreased. These randomly distributed protrusions generate strong shearing, impact, and obstruction on the airflow, intentionally inducing multi-scale, high-intensity turbulence. This violent disturbance completely destroys the thermal boundary layer on the surface of the louver 220, forcing the cold air in the fluid core region to mix violently with the surface of the louver 220 heated by the flat tube 1. This directly addresses the needs of the high heat flux density region in the middle of the flat tube 1, rapidly removing a large amount of heat transferred from the flat tube 1 by maximally enhancing the local heat transfer intensity, preventing heat accumulation at the base of the fin 2, thereby maintaining an effective heat transfer temperature difference between the flat tube 1 and the fin 2.

[0056] The surface of the louver 220 in the transition zone Q3 is provided with guide grooves 2203 parallel to the airflow direction. When hot air carrying a large amount of heat from the flat tube 1 flows through this area, these axial grooves guide the fluid. They constrain and guide the turbulent air coming from the reinforcement zone Q2 like a track, aligning its rotation axis with the airflow direction and giving the vortex stronger axial momentum. This allows the vortex to move smoothly and orderly towards the outlet while maintaining a certain mixing capacity, avoiding disordered dissipation or backflow at the rear of the flow channel. This design ensures that the heated air can be discharged efficiently, preventing hot air stagnation from causing the temperature of the fins 2 to rise, thereby maintaining the driving force for the continuous heat extraction from the flat tube 1.

[0057] By setting specialized microstructures on the surface of the window blades 220 in different functional areas, cross-scale synergistic optimization is achieved in conjunction with changes in macroscopic parameters. The strip-shaped flow-guiding protrusions 2201, turbulence-inducing protrusions 2202, and flow-guiding grooves 2203 play key roles in "smooth flow field introduction," "violent heat transfer enhancement," and "smooth heat dissipation," respectively, precisely matching the changes in the physical state of the air and the heat flow distribution of the flat tube 1. This design achieves active control of the flow at the microscopic level, ultimately significantly improving the overall heat transfer efficiency and energy efficiency of the radiator from the flat tube 1 to the air.

[0058] In some embodiments, this application further defines the height or depth parameters of the guiding region Q1 strip-shaped flow-guiding protrusion 2201, the reinforcement region Q2 turbulence-inducing protrusion 2202, and the transition region Q3 flow-guiding groove 2203 to be in the range of 30-100 micrometers. This size range optimizes the geometry of the microstructure, balancing airflow disturbance and flow resistance, thereby finely controlling the airflow state and improving the heat transfer efficiency from the flat tube 1 to the air.

[0059] Specifically, the height of the strip-shaped guide protrusions 2201 in the guide zone Q1 is controlled within the range of 30-100 micrometers. This scale is sufficient to effectively disturb the boundary layer adjacent to the surface of the window blade 220. When air flows over the surface of the fins 2 heated by the flat tube 1, these low protrusions can generate stable small-scale vortices, straightening the airflow direction and reducing the risk of inlet flow separation. The lower limit of 30 micrometers ensures sufficient intervention in the boundary layer, while the upper limit of 100 micrometers avoids unnecessary pressure drop caused by excessive protrusions, creating low-resistance conditions for heat dissipation at the root of the flat tube 1.

[0060] The turbulence-inducing protrusions 2202 in the enhanced region Q2 also have a height of 30-100 micrometers. This size range allows them to exert a strong shearing effect on the mainstream air. After the air flows in from the guiding region Q1, its temperature rises and its heat transfer capacity decreases. These micrometer-sized protrusions, through their staggered distribution, induce multi-scale turbulence, completely disrupting the thermal boundary layer. The height is sufficient (≥30 micrometers) to ensure the intensity of the disturbance and promote vigorous mixing of the cold air with the heated surface of the window blades 220 of the flat tube 1; the maximum depth of 100 micrometers prevents excessive dissipation of flow energy and maintains the efficient heat dissipation of the flat tube 1.

[0061] The depth of the flow-guiding groove 2203 in the transition zone Q3 is set to 30-100 micrometers. This depth allows the groove to effectively capture and reorganize the airflow. When air carrying heat from the flat tube 1 flows through this region, the lower limit of the groove depth of 30 micrometers ensures the guiding ability of the vortex and imparts axial momentum to the airflow; the upper limit of the depth of 100 micrometers avoids energy loss caused by sudden expansion of the flow channel, promotes the smooth discharge of hot air, and maintains the heat transfer temperature difference between the flat tube 1 and the fin 2.

[0062] When the heat is conducted from the flat tube 1 to the root of the fin 2, the heat flux density is highest in the two sides of the fin 2 near the connection of the flat tube 1, while the heat flux density is lower in the middle of the fin 2. If a uniform window blade 220° angle design is adopted, it cannot adapt to this temperature gradient, which will lead to insufficient heat transfer in the high heat flux area or excessive disturbance in the low heat flux area, increasing resistance.

[0063] To address this problem, this application adopts the following solution: In this embodiment, along the height of the fins 2 perpendicular to the airflow direction, a region with a width of 1-5 mm on both sides of the inclined surface of the substrate 21 is defined as the first region 211, where the opening angle of the window blades 220 in this region ranges from A° to B°; the region in the middle of the inclined surface of the substrate 21 is defined as the second region 212, where the opening angle of the window blades 220 in this region ranges from C° to D°; and the conditions A>D and B>C are satisfied. This design ensures that the overall angle of the window blades 220 in the first region 211 (high heat flux region) is higher than that in the second region 212 (low heat flux region), achieving localized control of heat transfer intensity through angle differences.

[0064] When air flows across the surface of fin 2, the first region 211 on both sides of fin 2 has a higher temperature and greater heat flux density due to its proximity to the flat tube 1. This region uses a larger window opening angle (A° to B°) of 220, which exerts stronger shearing and turbulence on the airflow, severely disrupting the thermal boundary layer, increasing the local heat transfer coefficient, and quickly removing the concentrated heat transferred from the flat tube 1. Simultaneously, the second region 212 in the middle of fin 2 has a lower temperature and lower heat flux density. A smaller window opening angle (C° to D°) of 220 is used to generate gentle turbulence, ensuring basic heat transfer while avoiding unnecessary increases in flow resistance. The angle conditions A>D and B>C ensure that the minimum angle of the first region 211 is still higher than the maximum angle of the second region 212, preventing heat transfer lag in the high heat flux region due to insufficient angle, while also avoiding redundant pressure drop in the low heat flux region due to excessive angle.

[0065] This design achieves a precise match between the heat transfer capacity and heat flux density distribution on the fin 2 surface. The large angle of the first region 211 enhances heat transfer, preventing heat accumulation at the root of the flat tube 1 and maintaining an effective heat transfer temperature difference between the flat tube 1 and the fin 2. The small angle of the second region 212 optimizes flow resistance and improves system efficiency. Overall, this scheme improves the comprehensive heat transfer efficiency of the radiator through localized differentiated design without significantly increasing the total pressure drop, especially optimizing the thermal management performance in the high-temperature region.

[0066] As some embodiments, the opening angle of the window blades 220 in the first region 211 can be set to 27° to 30°, and the opening angle of the window blades 220 in the second region 212 can be set to 24° to 26°. These parameters satisfy the conditions A=27, D=26, B=30, and C=24. When air flows through the fins 2, the large-angle window blades 220 at 27°-30° on both sides generate strong turbulence in the high-temperature zone, rapidly dissipating heat from the flat tube 1; the window blades 220 at 24°-26° in the middle provide moderate disturbance, balancing heat transfer and resistance. This configuration makes the heat transfer distribution on the surface of the fins 2 more uniform, improving the overall heat dissipation performance.

[0067] At the height of the fin 2 perpendicular to the airflow direction, the opening angle of the louver 220 in each functional zone (guide zone Q1, reinforcement zone Q2, and transition zone Q3) is differentiated according to its relative position to the flat tube 1. Specifically, the opening angle (A° to B°) of the louver 220 in the region (first region 211) located on both sides of the inclined surface of the substrate 21 with a width of 1-5 mm is always greater than the opening angle (C° to D°) of the louver 220 in the middle region of the inclined surface (second region 212), and satisfies the conditions A>D and B>C.

[0068] This design stems from the uneven distribution of heat conducted by the flat tube 1 along the height of the fins 2: the heat flux density is highest in the two sides near the connection of the flat tube 1, while it is lower in the middle. In the guiding zone Q1, the larger angle of the two side windows 220° enhances the disturbance to the inlet airflow, quickly absorbing the heat transferred from the root of the flat tube 1, while the smaller angle in the middle reduces flow resistance. In the reinforcement zone Q2, the large angle on both sides further enhances turbulence, enabling efficient heat exchange in the high heat flux density area and preventing heat accumulation. In the transition zone Q3, the differentiated angle settings ensure that hot air is smoothly discharged from the high heat flux area, maintaining the heat transfer driving force between the flat tube 1 and the fins 2. Through this angle gradient optimization along the height, the heat transfer intensity and heat flux distribution on the surface of the fins 2 are precisely matched, thereby improving the overall heat transfer efficiency from the flat tube 1 to the air at the microscale.

[0069] In the traditional manufacturing process of louver fins 2, the louver array 22 is usually formed by stamping directly onto the inclined surface of the substrate 21. Although this one-piece stamping method is simple in structure, it has significant drawbacks. When louver arrays 22 need to be stamped on both sides of the inclined surface of the substrate 21, dense stamping holes will be formed on the substrate 21 material, resulting in a reduction in the effective load-bearing area of ​​the substrate 21, a significant weakening of structural strength, and easy deformation or breakage under vibration or thermal stress. More importantly, in order to avoid mutual interference between the louvers 220 on both sides, the louvers 220 must be staggered, which strictly limits the minimum spacing between the louvers 220, making it impossible to achieve a high-density layout, thereby reducing the heat transfer surface area per unit area and restricting the improvement of heat dissipation performance. In addition, the stamping holes on the inclined surface will form airflow short-circuit channels, causing the airflow on both sides of the inclined surface to interfere with each other through the holes, generating disordered vortices and airflow collisions, which not only increases flow resistance but also disrupts the designed flow field, resulting in a decrease in heat transfer efficiency.

[0070] To address the aforementioned issues, this application adopts a design scheme that separates the substrate 21 from the venetian blind array 22.

[0071] Specifically, the venetian blind array 22 of this application is formed on a separate substrate 23, which is then fixedly connected to the inclined surface of the substrate 21. This separate structure decouples the forming process of the venetian blinds from the manufacturing of the substrate 21: the substrate 23 can be made of a high-precision sheet material (such as aluminum foil) to separately stamp out a high-density, highly consistent venetian blind array 22, and then bonded to the inclined surface of the substrate 21 by brazing, bonding, or mechanical fixing. The connection layer between the substrate 23 and the substrate 21 ensures efficient heat conduction while avoiding damage to the strength of the substrate 21 due to direct stamping.

[0072] The core principle of the split design lies in functional modularity. The independent substrate 23 allows the louver array 22 to be precisely machined on specialized tooling, such as by stamping directly onto aluminum foil. The spacing between the louvers 220 can be significantly reduced (e.g., to 1.0-1.4 mm) beyond traditional limitations, thereby maximizing the heat exchange area. At the same time, the fixed connection between the substrate 23 and the base plate 21 isolates the direct crosstalk between the airflow on the front and back sides. The airflow can only flow along the designed path across the surface of the louvers 220, avoiding disorderly collisions. As an independent functional layer, the substrate 23 can optimize its thickness and material (e.g., by using a high thermal conductivity coating) to further improve heat transfer efficiency. The base plate 21 focuses on structural support, maintaining the mechanical stability of the corrugated overall structure.

[0073] This design brings multiple technical benefits: First, the structural integrity of the substrate 21 is protected, and its resistance to vibration and thermal fatigue is enhanced; second, the louver array 22 can achieve a high-density layout, and the reduction in the spacing of the louvers 220 significantly increases the heat exchange surface area and improves heat dissipation intensity; third, the airflow path is controlled, reducing eddy current energy loss and flow resistance; finally, modular production improves manufacturing yield, and the substrate 23 can be pre-processed and standardized, reducing overall costs.

[0074] In some embodiments, the louver array 22 is provided on both sides of a single inclined surface of the substrate 21. This means that each wavy fin 2 is equipped with a complete louver array 22 structure (including a guide region Q1, a reinforcement region Q2, and a transition region Q3) on both sides of the inclined surface, and the double-sided array is arranged in a mirror-symmetrical manner, working together to act on the air flowing through the inclined surface. This design allows one inclined unit of the fin 2 to handle airflow in both directions simultaneously, maximizing the utilization of the heat exchange area.

[0075] When air flows through the channels of fins 2 between the flat tubes 1, both the front and back sides of the inclined surface of the substrate 21 are simultaneously exposed to the airflow. The louver arrays 22 on the front and back sides work independently yet synergistically: when the guiding area Q1 on the front smoothly guides the airflow, the guiding area Q1 on the back side also accelerates the airflow on the other side; when the strengthening area Q2 on the front violently disturbs the air, the strengthening area Q2 on the back side also simultaneously strengthens heat transfer; when the transition area Q3 on the front guides the hot air to escape, the transition area Q3 on the back side ensures the smooth exhaust of the airflow on the other side. The double-sided array makes the airflow form a more uniform flow distribution within the channels of fins 2, avoiding temperature gradient imbalance caused by unilateral heat transfer. After heat is conducted from the flat tubes 1 to the substrate 21 of fins 2, it is simultaneously dissipated into the air through the louver arrays 22 on both sides, significantly shortening the heat transfer path and increasing the heat dissipation density.

[0076] By employing the above technical solution, the double-sided louver array 22 nearly doubles the effective heat exchange area of ​​the fins 2, directly improving the heat load capacity of the radiator per unit volume. Simultaneously, the double-sided symmetrical design eliminates vortices or dead zones that may arise from unilateral flow, reducing overall flow resistance and improving the stability of airflow organization. Combined with the heat input from the flat tube 1, this structure ensures that heat can be rapidly conducted from the flat tube 1 to both sides of the fins 2 and efficiently dissipated, avoiding localized overheating and improving the reliability and energy efficiency of the radiator.

[0077] In some embodiments, the louver array 22 is fixed to both sides of the inclined surface of the substrate 21 via an independent substrate 23. For example, the angle of the guide region Q1 louver 220 of the front array increases linearly from 5° to 20°, and the back array is arranged in a mirror image with the same parameters; the louver 220 spacing and secondary structures (such as strip-shaped flow guide protrusions 2201, turbulence excitation protrusions 2202, and flow guide grooves 2203) of the double-sided array are all set according to the rules of the aforementioned embodiments, forming a symmetrical flow control unit. When air flows through, the front and back arrays simultaneously perform a coordinated operation of accelerating, disturbing, and deflecting the airflow.

[0078] By setting up a louver array 22 on both sides of the inclined surface of the substrate 21, the heat exchange area of ​​the fins 2 is maximized and the airflow organization is optimized symmetrically on both sides. This structure enables the heat sink to significantly improve the heat exchange density within a limited space, while ensuring the uniformity and stability of the flow, further enhancing the heat transfer efficiency from the flat tube 1 to the air, and is suitable for high power density heat dissipation scenarios.

[0079] During radiator operation, as air flows through the channels of fin 2, its temperature, velocity, and heat transfer capacity dynamically change along the flow direction. If the partition length ratio is mismatched, for example, if the guiding zone Q1 is too short, it will lead to insufficient airflow acceleration and increased inlet resistance; if the reinforcing zone Q2 is too long, it may cause excessive dissipation of flow energy; and if the transition zone Q3 is insufficient, it will easily cause flow separation. Therefore, this embodiment optimizes the partition length ratio to make the fin 2 structure precisely adapt to the evolution of the air's physical state, thereby improving the heat transfer efficiency from the flat tube 1 to the air.

[0080] Specifically, the length of the guide zone Q1 accounts for 30%-40% of the total length of the fins 2. This proportion ensures that the airflow inlet section has sufficient space for smooth acceleration and flow field preparation. When air flows in from the channel between the flat tubes 1, the longer design of the guide zone Q1 allows the window opening angle of the louvers 220 to gradually increase, gently disrupting the thermal boundary layer, reducing impact resistance, and creating low-resistance conditions for heat dissipation at the root of the flat tubes 1. At the same time, this length range fully utilizes the high heat transfer potential of air at low temperatures, ensuring that the heat conducted by the flat tubes 1 is fully absorbed and avoiding local overheating.

[0081] The length of the enhanced zone Q2 also accounts for 30%-40% of the total length of fin 2, providing ample turbulence space for the core heat transfer stage. After the air flows through the guiding zone Q1, its temperature rises, and the heat transfer driving force weakens. The longer design of the enhanced zone Q2 allows the louvers 220 to continuously apply high-intensity turbulence, thoroughly disrupting the thermal boundary layer and forcing the cold air to mix violently with the heated surface of the fin 2 in the flat tube 1. This ensures that the heat in the high heat flux density region in the middle of the flat tube 1 is quickly carried away, preventing heat accumulation and maintaining an effective heat transfer temperature difference between the flat tube 1 and the fin 2.

[0082] The transition zone Q3 accounts for 10%-20% of the total length of fin 2. This proportion ensures flow stability while avoiding excessive space occupation. Although the transition zone Q3 is relatively short, it is sufficient to achieve flow field reorganization. The gradual change in the angle and spacing of the window blades 220° allows hot air to gain axial momentum and smoothly exit the flow channel. This prevents the temperature of fin 2 from rising due to hot air stagnation, ensures continuous heat dissipation from the flat tube 1, and reduces unnecessary flow resistance.

[0083] By optimizing the length ratio of the guiding zone Q1, the strengthening zone Q2, and the transition zone Q3, a dynamic match between the airflow state and the fin 2 structure is achieved. The guiding zone Q1 and the strengthening zone Q2 each account for 30%-40%, ensuring sufficient airflow acceleration and heat transfer enhancement; the transition zone Q3 accounts for 10%-20%, balancing flow efficiency and space occupancy. This proportional design maximizes the heat transfer intensity of fin 2 within a limited length while maintaining low flow resistance, improving the overall heat transfer efficiency from the flat tube 1 to the air, and enhancing the energy efficiency and reliability of the radiator.

[0084] In some embodiments, the surface of the flat tube 1 is provided with a microgroove structure 11, and the root of the fin 2 is brazed to the surface of the flat tube 1 by brazing material filled into the microgroove structure 11.

[0085] In some specific embodiments, the microgroove structure 11 can be a diamond grid pattern or an interlaced wave pattern, with a groove depth of 50±10μm.

[0086] In this embodiment, a microgroove structure 11 is fabricated on the surface of the flat tube 1, and the root of the fin 2 is metallurgically bonded to the flat tube 1 by brazing material filled into the microgrooves. The microgrooves increase the surface area and form three-dimensional anchor points. The brazing filler metal fills the grooves under capillary action, forming a three-dimensional interlock. During operation, the extra brazing filler metal stored in the microgrooves can compensate for the thermal deformation difference between the flat tube 1 and the fin 2 and absorb cyclic thermal stress. The groove structure also promotes uniform distribution of brazing filler metal, avoids voids, and reduces interfacial thermal resistance.

[0087] This design enhances the fatigue resistance of the connection through the synergistic effect of mechanical anchoring and metallurgical bonding; the brazing filler metal layer within the microgrooves enhances lateral heat diffusion and optimizes the heat flow path from the flat tube 1 to the fins 2; additional brazing filler metal reserves ensure that the interface remains intact after long-term use. This enables the radiator to maintain stable heat conduction under high temperature and temperature difference conditions, extending its service life.

[0088] The above description is merely a preferred embodiment of this application and is not intended to limit this application. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this application should be included within the protection scope of this application.

Claims

1. A gradient-flow louvered finned radiator, characterized in that, include: Multiple parallel flat tubes; A wavy fin is disposed between adjacent flat tubes, the fin including a substrate and an array of louvers disposed on the inclined surface of the substrate; The louver array is divided into a guiding zone that accelerates and guides the fluid, an enhancement zone that violently disturbs the fluid to enhance heat exchange, and a transition zone that guides the fluid to drain smoothly. The opening angle of the louvers in the guiding zone increases continuously along the airflow direction; the opening angle of the louvers in the strengthening zone is greater than the opening angle at the end of the guiding zone; the opening angle of the louvers in the transition zone decreases continuously along the airflow direction, and the opening angle at the end of the transition zone is not less than the midpoint of the opening angle of the guiding zone. The slat spacing in the guide zone decreases continuously along the airflow direction, the slat spacing in the reinforcement zone is the minimum spacing in the louver array, and the slat spacing in the transition zone increases continuously along the airflow direction.

2. The gradient turbulence type louvered fin radiator as described in claim 1, characterized in that: The opening angle of the slats in the guiding area increases linearly from 5°-10° to 20°-30°; the opening angle of the slats in the reinforcing area is 25°-35°; the opening angle of the slats in the transition area decreases linearly from the opening angle of the reinforcing area, and its end angle is 15°-25°.

3. The gradient bleed type louvered fin radiator as described in claim 2, characterized in that: The window leaf spacing in the guiding zone decreases linearly from 1.6mm-2.0mm to 1.3mm-1.6mm; the window leaf spacing in the reinforcing zone is 1.0mm-1.4mm; and the window leaf spacing in the transition zone increases linearly from the spacing in the reinforcing zone to 1.5mm-1.9mm.

4. The gradient bleed type louvered fin radiator as described in claim 1, characterized in that: The surface of the window blade in the guiding zone is provided with strip-shaped guide protrusions parallel to the airflow direction; the surface of the window blade in the strengthening zone is provided with randomly or interlaced turbulence excitation protrusions; and the surface of the window blade in the transition zone is provided with guide grooves parallel to the airflow direction.

5. The gradient bleed type louvered fin radiator as described in claim 4, characterized in that: The height or depth of the strip-shaped flow-guiding protrusion, the turbulence-excitation protrusion, and the flow-guiding groove is 30-100 μm.

6. The gradient bleed type louvered fin radiator as described in claim 1 or 4, characterized in that: Along the fin height perpendicular to the airflow direction, the area located on both sides of the substrate slope with a width of 1-5 mm is the first region, and the window opening angle of the first region is A° to B°; the area in the middle of the substrate slope is the second region, and the window opening angle of the second region is C° to D°; wherein, A>D and B>C.

7. The gradient turbulence type louvered fin radiator as described in claim 1, characterized in that: The louver array is formed on a separate substrate, which is fixedly connected to the inclined surface of the substrate.

8. The gradient bleed type louvered fin radiator as described in claim 7, characterized in that: The louver array is provided on both the front and back sides of a single bevel of the substrate.

9. The gradient turbulence type louvered fin radiator as described in claim 1, characterized in that: The length of the guiding zone accounts for 30%-40% of the total fin length, the length of the reinforcing zone accounts for 30%-40%, and the length of the transition zone accounts for 10%-20%.

10. The gradient bleed type louvered fin radiator as described in claim 1, characterized in that: The surface of the flat tube is provided with a microgroove structure, and the root of the fin is brazed to the surface of the flat tube by brazing material filled into the microgroove structure.

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