A new high-density tooth heat sink
Patent Information
- Application Number
- CN202522251516.X
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- Filing Date
- 2025-10-24
- Publication Date
- 2026-09-25
- Estimated Expiration
- 2035-10-24
AI Technical Summary
[0005]本申请为解决现有技术中，高功率设备需求下，传统的散热型材因接触面积设计局限致换热效率低、易积热影响设备，且自重高不便组装搬运、增物流仓储成本，在重量敏感场景应用受限的技术问题，提出一种新型高密齿散热器
[0016]本申请提供一种新型高密齿散热器，其包括基板，沿基板长度方向间隔设置的多个翅片，以及相邻两个翅片之间围合的气流道；其中，翅片包括垂直设于基板的翅片主板、设于主板一侧的第一换热组与另一侧的第二换热组，且第一换热组和第二换热组沿翅片主板中线中心对称，相邻翅片的两组换热组共同围合成气流道。本申请通过在翅片主板两侧中心对称设置第一换热组和第二换热组，使得气流与翅片的换热面积大幅增加，显著提升换热效率，避免高功率设备积热；同时对称结构在保证换热效果的前提下减轻自重。其具有结构简单、便于搬运、易于加工、便于推广实施的优点。
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Figure CN224805308U_ABST
Abstract
Description
Technical Field
[0001] This application belongs to the field of aluminum profile technology, specifically relating to a novel high-density toothed radiator. Background Technology
[0002] In existing technologies, heat sinks play a crucial role in the heat dissipation systems of electronic devices. As heat-generating devices become increasingly high-powered, the heat generated during operation increases dramatically. Heat sinks, through optimized structures, facilitate rapid heat dissipation, maintaining stable operation, ensuring the lifespan of electronic components, and ultimately improving overall device performance and reliability. They are widely used in communication equipment, industrial control devices, and other fields. However, some problems still need to be addressed with the mainstream heat dissipation profiles currently on the market.
[0003] While existing heat dissipation profiles are made of metal and rely on increasing the airflow contact area to improve heat exchange efficiency, the actual contact area design is limited and difficult to further improve. This results in consistently low heat exchange efficiency, often leading to heat accumulation problems when faced with the large amounts of heat generated by high-power equipment, thus affecting the normal operation of the equipment. At the same time, traditional heat dissipation profiles are relatively heavy, which not only increases the overall weight of the equipment, making it inconvenient to assemble and transport, but also increases logistics costs and warehousing difficulties during transportation. This severely restricts their application scope, especially in weight-sensitive scenarios such as portable electronic devices and aerospace electronic components.
[0004] Therefore, in order to comprehensively improve the heat exchange efficiency and lightweight performance of high-density toothed radiators and meet the usage needs in different scenarios, it is now urgent to improve the existing heat dissipation aluminum profile structure and material application to enhance the heat dissipation effect and ease of use of the equipment. Utility Model Content
[0005] This application proposes a novel high-density toothed radiator to address the technical problems of traditional heat dissipation profiles, which suffer from low heat exchange efficiency and easy heat accumulation affecting equipment due to limited contact area design under the requirements of high-power equipment, as well as their high weight making assembly and transportation inconvenient and increasing logistics and warehousing costs, thus limiting their application in weight-sensitive scenarios.
[0006] This application adopts the following solution: a novel high-density toothed heat sink, comprising a substrate, a plurality of fins spaced apart along the length of the substrate, and an airflow channel formed between two adjacent fins. Each fin includes a fin main plate perpendicularly disposed on the substrate, a first heat exchange group disposed on one side of the fin main plate, and a second heat exchange group disposed on the other side of the fin main plate. The first heat exchange group and the second heat exchange group are symmetrically disposed along the center line of the fin main plate, and the first heat exchange group and the second heat exchange group between two adjacent fins together form the airflow channel.
[0007] In some feasible embodiments, the first heat exchange group includes a plurality of first heat exchange teeth disposed on one side of the finned main board, the plurality of first heat exchange teeth being spaced apart along the height direction of the finned main board.
[0008] In some feasible embodiments, the second heat exchange group includes a plurality of second heat exchange teeth disposed on the other side of the finned main body, the plurality of second heat exchange teeth being spaced apart along the height direction of the finned main body, and the first heat exchange teeth and the second heat exchange teeth being staggered and spaced apart along the height direction of the finned main body.
[0009] In some feasible embodiments, a first heat exchange groove is provided between two adjacent first heat exchange teeth, and a second heat exchange groove is provided between two adjacent second heat exchange teeth. When multiple fins are spaced apart along the length direction of the substrate, the first heat exchange groove and the second heat exchange groove between two adjacent fins together form the airflow channel.
[0010] In some feasible embodiments, the first heat exchange tank is provided with a first partition plate, and the second heat exchange tank is provided with a second partition plate. When multiple fins are spaced apart along the length direction of the substrate, the first heat exchange tooth abuts against the second partition plate, and the second heat exchange tooth abuts against the first partition plate. The first heat exchange tooth, the second heat exchange tooth, the first partition plate, and the second partition plate together form the airflow channel.
[0011] In some feasible embodiments, the cross-sectional shape of the first heat exchange tooth is an isosceles trapezoid, and multiple first tooth grooves are provided on both the upper and lower sides of the first heat exchange tooth, with the multiple first tooth grooves spaced apart along the width direction of the first heat exchange tooth.
[0012] In some feasible embodiments, the cross-sectional shape of the second heat exchange tooth is an isosceles trapezoid, and multiple second tooth grooves are provided on both the upper and lower sides of the second heat exchange tooth, with the multiple second tooth grooves spaced apart along the width direction of the second heat exchange tooth.
[0013] In some feasible embodiments, the first partition is provided with a plurality of air holes, and the plurality of air holes are spaced apart along the length direction of the first partition.
[0014] In some feasible embodiments, both the substrate and the fins are made of aluminum alloy, and the substrate and the plurality of fins are integrally formed.
[0015] Compared with the prior art, this application has the following beneficial effects:
[0016] This application provides a novel high-density finned heat sink, comprising a substrate, a plurality of fins spaced apart along the length of the substrate, and an airflow channel enclosed between adjacent fins. Each fin includes a finned main plate perpendicular to the substrate, a first heat exchange group on one side of the main plate, and a second heat exchange group on the other side. The first and second heat exchange groups are symmetrically arranged along the centerline of the finned main plate, and the two heat exchange groups of adjacent fins together enclose the airflow channel. This application significantly increases the heat exchange area between the airflow and the fins by symmetrically arranging the first and second heat exchange groups on both sides of the finned main plate, thereby significantly improving heat exchange efficiency and preventing heat accumulation in high-power equipment. Simultaneously, the symmetrical structure reduces weight while maintaining heat exchange performance. It has the advantages of simple structure, easy handling, easy processing, and easy implementation. Attached Figure Description
[0017] Figure 1 This is a diagram showing the usage state of a novel high-density toothed radiator according to this application;
[0018] Figure 2 This application Figure 1 A magnified view of a section at point A in the middle;
[0019] Figure 3 This is a front view of a novel high-density toothed radiator according to this application;
[0020] Figure 4 This application Figure 3 A magnified view of a section at point B in the middle;
[0021] Figure 5 This is a schematic diagram of the assembly structure of the fins in this application;
[0022] Figure 6 This application Figure 5 A schematic diagram of the structure at point B. Detailed Implementation
[0023] Combination Figures 1 to 6 The following description further illustrates the technical solution proposed in this application. This application adopts the following technical solution: a novel high-density toothed radiator, comprising a substrate 1, a plurality of fins 2 spaced apart along the length of the substrate 1, and an airflow channel 3 formed between adjacent fins 2. Each fin 2 includes a finned main plate 4 vertically disposed on the substrate 1, a first heat exchange group 5 disposed on one side of the finned main plate 4, and a second heat exchange group 6 disposed on the other side of the finned main plate 4. The first heat exchange group 5 and the second heat exchange group 6 are symmetrically arranged along the centerline of the finned main plate 4. The first heat exchange group 5 and the second heat exchange group 6 between adjacent fins 2 together form the airflow channel 3, which is used for airflow passage.
[0024] This application provides a novel high-density finned heat sink, comprising a substrate, a plurality of fins spaced apart along the length of the substrate, and an airflow channel enclosed between adjacent fins. Each fin includes a finned main plate perpendicular to the substrate, a first heat exchange group on one side of the main plate, and a second heat exchange group on the other side. The first and second heat exchange groups are symmetrically arranged along the centerline of the finned main plate, and the two heat exchange groups of adjacent fins together enclose the airflow channel. This application significantly increases the heat exchange area between the airflow and the fins by symmetrically arranging the first and second heat exchange groups on both sides of the finned main plate, thereby significantly improving heat exchange efficiency and preventing heat accumulation in high-power equipment. Simultaneously, the symmetrical structure reduces weight while maintaining heat exchange performance. It has the advantages of simple structure, easy handling, easy processing, and easy implementation.
[0025] In actual implementation, the airflow flows along the airflow channel enclosed by adjacent fins. When the airflow passes through the airflow channel, it will fully contact the surface of the first heat exchange group, the second heat exchange group and the fin main board. The first heat exchange group and the second heat exchange group transfer the heat in the airflow to the outside, thereby reducing the temperature of the airflow. The symmetrically arranged first heat exchange group and second heat exchange group effectively expand the contact area between the airflow and the fins, thereby improving the heat exchange efficiency per unit time.
[0026] In this embodiment, the first heat exchange group 5 includes a plurality of first heat exchange teeth 50 disposed on one side of the finned main board 4, and the plurality of first heat exchange teeth 50 are spaced apart along the height direction of the finned main board 4.
[0027] In this embodiment, the second heat exchange group 6 includes a plurality of second heat exchange teeth 60 disposed on the other side of the finned main plate 4. The plurality of second heat exchange teeth 60 are spaced apart along the height direction of the finned main plate 4, and the first heat exchange teeth 50 and the second heat exchange teeth 60 are staggered and spaced apart along the height direction of the finned main plate 4.
[0028] In actual implementation, when the airflow flows along the airflow channel enclosed by adjacent fins, the staggered first and second heat exchange teeth will turbulently circulate the airflow. The staggered arrangement of the first and second heat exchange teeth causes the airflow to continuously collide with the first and second heat exchange teeth as it passes through the airflow channel, forming local turbulence in the airflow channel. This allows the airflow to fully contact the surfaces of the first and second heat exchange teeth respectively, further improving the heat exchange efficiency of the fins and maximizing the removal of heat from the airflow.
[0029] In this embodiment, a first heat exchange groove 7 is provided between two adjacent first heat exchange teeth 50, and a second heat exchange groove 8 is provided between two adjacent second heat exchange teeth 60. When multiple fins 2 are spaced apart along the length direction of the substrate 1, the first heat exchange groove 7 and the second heat exchange groove 8 between two adjacent fins 2 together form the airflow channel 3.
[0030] In this embodiment, the first heat exchange tank 7 is provided with a first partition 70, and the second heat exchange tank 8 is provided with a second partition 80. When multiple fins 2 are spaced apart along the length of the substrate 1, the first heat exchange tooth 50 abuts against the second partition 80, and the second heat exchange tooth 60 abuts against the first partition 70. The first heat exchange tooth 50, the second heat exchange tooth 60, the first partition 70, and the second partition 80 together form the airflow channel 3.
[0031] In actual implementation, when the airflow enters the airflow channel formed by adjacent fins, the structure of the first heat exchange tooth, the second heat exchange tooth, the first baffle and the second baffle extends the residence path of the airflow in the airflow channel, greatly increases the heat exchange time, maximizes the removal of heat from the airflow, and solves the problem of heat accumulation in high-power equipment.
[0032] In this embodiment, the cross-sectional shape of the first heat exchange tooth 50 is an isosceles trapezoid, and multiple first tooth grooves 90 are provided on both the upper and lower sides of the first heat exchange tooth 50. The multiple first tooth grooves 90 are spaced apart along the width direction of the first heat exchange tooth 50.
[0033] In this embodiment, the cross-sectional shape of the second heat exchange tooth 60 is an isosceles trapezoid, and multiple second tooth grooves 91 are provided on both the upper and lower sides of the second heat exchange tooth 60. The multiple second tooth grooves 91 are spaced apart along the width direction of the second heat exchange tooth 60.
[0034] In actual implementation, when the airflow flows along the airflow channel enclosed by adjacent fins, the first and second tooth grooves on the upper and lower sides of the first and second heat exchange teeth will create a turbulence effect on the airflow, which can significantly increase the contact area between the airflow and the fins, allowing the airflow to contact the inner walls of the first and second tooth grooves for heat exchange, prolonging the residence path of the airflow in the airflow channel, greatly increasing the heat exchange time, maximizing the removal of heat from the airflow, and effectively solving the heat accumulation problem of high-power equipment.
[0035] In this embodiment, the first partition 70 is provided with a plurality of air holes 71, and the plurality of air holes 71 are spaced apart along the length direction of the first partition 70.
[0036] In actual implementation, the first and second partitions have the same structure, and the second partition is also provided with an air hole 71. By setting air holes on the first and second partitions, on the one hand, when the airflow enters the airflow channel, the residence path of the airflow in the airflow channel can be effectively extended, and the heat exchange time can be greatly increased; on the other hand, the weight of the fins can be reduced through the hollow structure.
[0037] In this embodiment, both the substrate 1 and the fins 2 are made of aluminum alloy, and the substrate 1 and the plurality of fins 2 are integrally formed.
[0038] This application provides a novel high-density finned heat sink, comprising a substrate, a plurality of fins spaced apart along the length of the substrate, and an airflow channel enclosed between adjacent fins. Each fin includes a finned main plate perpendicular to the substrate, a first heat exchange group on one side of the main plate, and a second heat exchange group on the other side. The first and second heat exchange groups are symmetrically arranged along the centerline of the finned main plate, and the two heat exchange groups of adjacent fins together enclose the airflow channel. This application significantly increases the heat exchange area between the airflow and the fins by symmetrically arranging the first and second heat exchange groups on both sides of the finned main plate, thereby significantly improving heat exchange efficiency and preventing heat accumulation in high-power equipment. Simultaneously, the symmetrical structure reduces weight while maintaining heat exchange performance. It has the advantages of simple structure, easy handling, easy processing, and easy implementation.
[0039] The embodiments provided by this utility model have been described in detail above. Specific examples have been used to illustrate the principles and implementation methods of this utility model. The descriptions of the embodiments above are only for the purpose of helping to understand the method and core ideas of this utility model. It should be noted that those skilled in the art can make several improvements and modifications to this utility model without departing from the principles of this utility model, and these improvements and modifications also fall within the protection scope of the claims of this utility model.
Claims
1. A novel high-density toothed radiator, characterized in that, The system includes a substrate (1), a plurality of fins (2) spaced apart along the length of the substrate (1), and an airflow channel (3) formed between two adjacent fins (2). Each fin (2) includes a finned main plate (4) vertically disposed on the substrate (1), a first heat exchange group (5) disposed on one side of the finned main plate (4), and a second heat exchange group (6) disposed on the other side of the finned main plate (4). The first heat exchange group (5) and the second heat exchange group (6) are symmetrically disposed along the center line of the finned main plate (4). The first heat exchange group (5) and the second heat exchange group (6) between two adjacent fins (2) together form the airflow channel (3).
2. The novel high-density toothed radiator according to claim 1, characterized in that, The first heat exchange group (5) includes a plurality of first heat exchange teeth (50) disposed on one side of the finned main plate (4), and the plurality of first heat exchange teeth (50) are spaced apart along the height direction of the finned main plate (4).
3. A novel high-density toothed radiator according to claim 2, characterized in that, The second heat exchange group (6) includes a plurality of second heat exchange teeth (60) disposed on the other side of the finned main plate (4). The plurality of second heat exchange teeth (60) are spaced apart along the height direction of the finned main plate (4), and the first heat exchange teeth (50) and the second heat exchange teeth (60) are staggered along the height direction of the finned main plate (4).
4. A novel high-density toothed radiator according to claim 3, characterized in that, A first heat exchange groove (7) is provided between two adjacent first heat exchange teeth (50), and a second heat exchange groove (8) is provided between two adjacent second heat exchange teeth (60). When multiple fins (2) are spaced apart along the length direction of the substrate (1), the first heat exchange groove (7) and the second heat exchange groove (8) between two adjacent fins (2) together form the airflow channel (3).
5. A novel high-density toothed radiator according to claim 4, characterized in that, The first heat exchange tank (7) is provided with a first partition plate (70), and the second heat exchange tank (8) is provided with a second partition plate (80). When multiple fins (2) are spaced apart along the length direction of the substrate (1), the first heat exchange tooth (50) abuts against the second partition plate (80), and the second heat exchange tooth (60) abuts against the first partition plate (70). The first heat exchange tooth (50), the second heat exchange tooth (60), the first partition plate (70), and the second partition plate (80) together form the airflow channel (3).
6. A novel high-density toothed radiator according to claim 2, characterized in that, The first heat exchange tooth (50) has an isosceles trapezoidal cross-section. Multiple first tooth grooves (90) are provided on both the upper and lower sides of the first heat exchange tooth (50). The multiple first tooth grooves (90) are spaced apart along the width direction of the first heat exchange tooth (50).
7. A novel high-density toothed radiator according to claim 3, characterized in that, The cross-sectional shape of the second heat exchange tooth (60) is an isosceles trapezoid. The second heat exchange tooth (60) has multiple second tooth grooves (91) on both the upper and lower sides. The multiple second tooth grooves (91) are spaced apart along the width direction of the second heat exchange tooth (60).
8. A novel high-density toothed radiator according to claim 5, characterized in that, The first partition (70) is provided with a plurality of air holes (71), and the plurality of air holes (71) are spaced apart along the length direction of the first partition (70).
9. A novel high-density toothed radiator according to claim 5, characterized in that, The substrate (1) and the fins (2) are both made of aluminum alloy, and the substrate (1) and the multiple fins (2) are integrally formed.