A battery module bracket structure

Abstract

This application relates to the field of power battery technology, and in particular to a battery module support structure, including at least two supports connected to adjacent supports via a connecting part. Each support has several module receiving cavities, and a positioning module is detachably connected to each module receiving cavity. The inner wall of the battery receiving cavity within the positioning module has several air duct guide ribs, which protrude radially inward along the battery receiving cavity and extend in a pseudo-spiral shape in the same direction. The battery receiving cavities of the at least two supports arranged side by side are coaxially configured, and a pseudo-spiral gap flow channel is formed between the outer wall of the battery inside and the inner wall of the battery receiving cavity. This application, through the detachable positioning module, can adapt to batteries of different specifications. By utilizing the pseudo-spiral flow channel to extend the airflow path and enhance the turbulence effect, it improves heat exchange efficiency, effectively adapting to batteries of different specifications and improving the temperature control capability of the battery module.

Description

Technical Field

[0001] This application relates to the field of power battery technology, and in particular to a battery module support structure. Background Technology

[0002] With the rapid rise of the global new energy vehicle industry, the performance of power batteries, as the core power module, directly determines the vehicle's range, power performance, and safety reliability. Lithium-ion batteries, with their outstanding advantages such as high operating voltage, long cycle life, and high energy density, have become the mainstream technology for power batteries. In 2025, the global installed capacity of lithium-ion power batteries exceeded 1235 GWh, accounting for 88% of the automotive sector, demonstrating a significant dominant position.

[0003] In existing technologies, as the new energy vehicle market continues to demand higher driving range and faster charging speeds, the development of high energy density and high-rate charging technologies has brought severe thermal management challenges to lithium battery modules. If the large amount of heat generated during charging and discharging cannot be dissipated in time, it will lead to battery performance degradation, shortened lifespan, and even thermal runaway accidents. An ideal thermal management system needs to precisely control the battery operating temperature within the optimal range of 20-35℃ with an internal temperature difference of no more than 5℃. This has become a key technical bottleneck for improving the overall performance of lithium battery modules and ensuring operational safety. Currently, commercially available thermal management systems mainly include three categories: liquid cooling, phase change materials, and air cooling. Among them, air cooling systems have irreplaceable value in fields such as power tools, light electric vehicles, drones, and small and medium-sized energy storage systems due to their advantages of simple structure, low cost, high reliability, and lightweight design. Based on system structure, air cooling systems can be divided into two core technical routes: parallel channel air cooling systems and vortex-induced air cooling systems. The former, as a traditional solution, consists of parallel channel pipes, manifolds, heat dissipation fins, fans, and air ducts. Based on the principle of axial convection heat transfer, it fixes the heat source through the shell frame and relies on the fan to drive the cooling medium to force convection heat dissipation along the axial direction of the battery array. However, it has significant technical defects. Thermodynamically, due to the geometric characteristics of the parallel channel, the contact time and effective heat transfer area between the cooling medium and the battery surface are insufficient, resulting in low heat exchange efficiency. Fluid dynamically, under normal operating conditions, the Reynolds number is in the laminar flow range, and the continuous thickening of the thermal boundary layer inside the battery box forms a thermal resistance layer, leading to a decrease in the Nusselt number and weakening the convective heat transfer intensity. In terms of temperature uniformity, the axial heat dissipation mode causes significant... The obvious axial temperature gradient, with a battery temperature difference of 10-15K between the airflow inlet and outlet areas, not only affects the consistency of battery module performance but also accelerates the aging process and increases the risk of thermal runaway. The latter, as an improved solution, is based on the principle of eddy generation and boundary layer disruption mechanism. It uses a flow guide device to generate rotating eddies in the airflow, inducing the surrounding air to participate in heat exchange to improve airflow uniformity and reduce dead zones. By using the entrainment effect, it forms a controllable secondary airflow and vortex structure in the gaps between battery modules, which can effectively disrupt the continuous development of the thermal boundary layer, enhance the intensity of fluid turbulence, increase the Nusselt number by 30-50%, and significantly optimize heat exchange efficiency. However, it also has obvious shortcomings. It has extremely high requirements for the spatial arrangement of battery modules, the geometric accuracy of flow guide elements, and the consistency of battery box packaging. Small dimensional deviations can seriously affect the stability and effectiveness of the eddy field. Moreover, compared with the traditional air-cooled system, it has more parts and a more complex structure, which is not conducive to the lightweighting of battery modules. Its precision manufacturing process and strict quality control system also significantly increase the manufacturing cost, which creates a prominent contradiction with the inherent economic advantages of the air-cooled system.

[0004] In summary, there is an urgent need for an innovative structural solution that can retain the advantages of simplicity and low cost of air-cooled systems while significantly improving heat exchange efficiency and reducing the temperature difference between batteries, so as to break through the existing technical bottlenecks and promote the efficient application of air-cooled thermal management systems in more scenarios. Summary of the Invention

[0005] The purpose of this application is to provide a battery module support structure to solve the problems of low heat exchange efficiency and large temperature difference in existing parallel flow channel air cooling systems, as well as the complex structure, high cost, and unfavorable lightweight nature of eddy current induced air cooling systems, while retaining the core advantages of air cooling and meeting the thermal management requirements of battery modules.

[0006] The embodiments of this application can be implemented through the following technical solutions:

[0007] A battery module support structure includes at least two supports, which are connected to each other via a connecting part. Each support has a plurality of module receiving cavities. A positioning module is detachably connected to each module receiving cavity. A battery receiving cavity is provided in the positioning module. A plurality of air duct guide ribs are provided on the inner wall of the battery receiving cavity. The plurality of air duct guide ribs protrude inward along the radial direction of the battery receiving cavity and extend in a pseudo-spiral shape at an inclination in the same direction.

[0008] At least two of the brackets are arranged side by side with their battery receiving cavities coaxially aligned and housing batteries. The outer wall of the battery contacts the air duct guide rib and forms a pseudo-spiral gap flow channel with the inner wall of the battery receiving cavity.

[0009] Furthermore, the positioning module has multiple models, and the inner diameter of the battery housing cavity and / or the geometric parameters of the air duct guide ribs are different for different models of the positioning module.

[0010] Furthermore, the angle of the air duct guide rib relative to the battery axis The design is for 15°-45°.

[0011] Furthermore, along the axial direction of the battery, the inclination angles of the air duct guide ribs arranged coaxially side by side in the two battery receiving cavities are different, wherein the inclination angle of the air duct guide ribs adjacent to the airflow inlet area of ​​the fan is smaller than the inclination angle of the air duct guide ribs far from the airflow outlet area.

[0012] Furthermore, the inclination angle of the air duct guide ribs in the airflow inlet area adjacent to the fan is set to a small inclination angle of 15°-25°.

[0013] Furthermore, the inclination angle of the air duct guide ribs in the airflow outlet area away from the fan is set to a large inclination angle of 25°-45°.

[0014] Furthermore, the number of air duct guide ribs provided in a single battery housing cavity is 8-16, and they are evenly distributed along the inner wall of the battery housing cavity.

[0015] Furthermore, the arrangement of guide ribs in different battery cavities varies in density. The number and density of guide ribs at the airflow inlet near the fan are less than the number and density of guide ribs at the airflow outlet far from the fan.

[0016] Furthermore, the cross-section of the air duct guide rib is semi-circular, trapezoidal, or rectangular, and the radial height of the air duct guide rib along the inner wall of the battery receiving cavity is set between 0.5mm and 2mm.

[0017] Furthermore, the two adjacent positioning modules arranged in parallel are supported by the connecting part and form a gap distribution. A gap is reserved between the air duct guide ribs in the two adjacent battery receiving cavities arranged in parallel, and the gap value is between 10% and 15% of the total axial length of the cylindrical battery.

[0018] The battery module support structure provided in the embodiments of this application has at least the following beneficial effects:

[0019] (1) The heat exchange efficiency is significantly improved. This application uses the air duct guide ribs to guide the airflow to form a pseudo-spiral air duct, which can actively break the thermal boundary layer on the battery surface and enhance the convective heat transfer effect. Compared with the traditional parallel flow channel air cooling system, the heat exchange efficiency of this structure is improved by 30%~50%; under the premise of meeting the same heat dissipation requirements, the fan power can be reduced or the air duct size can be reduced, further optimizing the system's lightweight level.

[0020] (2) Excellent temperature uniformity: All batteries are cooled within a pseudo-spiral air duct with a consistent structure, effectively avoiding the axial temperature gradient problem of traditional parallel flow channel air cooling systems, while ensuring the circumferential temperature uniformity of individual batteries. The maximum temperature difference inside the battery pack can be controlled within 5℃, which greatly improves the performance consistency of the battery module and extends the cycle life.

[0021] (3) It is highly versatile and low in cost. The core function of this structure is achieved by the cooperation between the bracket body and the battery mounting hole module, without the need for additional parts. For different models of cylindrical batteries, only the mold of the battery mounting hole module needs to be modified for production, which is highly versatile. At the same time, the overall structure is easy to assemble, and hardly increases the manufacturing and installation costs, which has significant economic advantages.

[0022] (4) It has wide applicability and high robustness. This structure is compatible with both passive and active air cooling modes. The system has a low failure rate and can be operated without maintenance after installation. It is not only suitable for active forced air cooling scenarios equipped with fans, but also can give full play to the temperature equalization function in low-power application scenarios that rely on natural convection. It has a wide range of applications. Attached Figure Description

[0023] Figure 1This is a schematic diagram of the overall structure of a battery module bracket structure according to this application;

[0024] Figure 2a , Figure 2b These are schematic diagrams showing the disassembled state of a single stent in this application from different perspectives;

[0025] Figure 3 This is a side sectional view of the battery housing cavity in this application;

[0026] Figure 4 This is a cross-sectional schematic diagram of the positioning module in this application.

[0027] Numbers in the diagram

[0028] 1-Bracket; 11-Module housing cavity; 12-Positioning module; 13-Battery housing cavity; 131-Air duct guide rib; 15-Metal heat-conducting ring; 2-Connecting part; 3-Battery. Detailed Implementation

[0029] The present application will now be further described based on preferred embodiments and with reference to the accompanying drawings.

[0030] Furthermore, for ease of understanding, various components on the drawings have been enlarged or reduced, but this is not intended to limit the scope of protection of this application.

[0031] Singular forms of words also include plural meanings, and vice versa.

[0032] In the description of the embodiments of this application, 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 commonly used when the product of this application is in use, they are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation on this application. In addition, in the description of this application, in order to distinguish different units, the terms "first," "second," etc. are used in this specification, but these are not limited by the manufacturing order, nor should they be construed as indicating or implying relative importance. Their names may differ in the detailed description and claims of this application.

[0033] The vocabulary used in this specification is for illustrative purposes and is not intended to limit the scope of this application. It should also be noted that, unless otherwise expressly specified and limited, the terms "set," "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, a direct connection, or an indirect connection via an intermediate medium; or they can refer to the internal communication between two components. Those skilled in the art will understand the specific meaning of these terms in this application.

[0034] like Figures 1 to 3 As shown, a battery module support structure includes at least two supports 1 arranged side by side, with adjacent supports 1 connected by a connecting part 2. Each support 1 has a plurality of module receiving cavities 11. A positioning module 12 is detachably connected to each module receiving cavity 11. A battery receiving cavity 13 is provided in the positioning module 12. A plurality of air duct guide ribs 131 are provided on the inner wall of the battery receiving cavity 13. The plurality of air duct guide ribs 131 protrude inward along the radial direction of the battery receiving cavity 13 and extend obliquely in the same direction in a pseudo-spiral shape.

[0035] Furthermore, at least two of the battery housing cavities 13 of the brackets 1 are coaxially arranged in parallel, and each cavity houses a battery 3. The outer wall of the battery 3 contacts the air duct guide rib 131, and a pseudo-spiral gap flow channel is formed between the battery 3 and the inner wall of the battery housing cavity 13. When cooling air flows over the battery surface, under the guidance and compression of the pseudo-spiral air duct guide rib 131, the flow direction changes from a simple axial motion to a combined axial and rotational motion, causing the airflow to form an approximately spiral-like flow trajectory around the battery, i.e., a "pseudo-spiral air duct". This pseudo-spiral air duct differs from the traditional closed spiral channel. It guides the airflow through discrete guide ribs, eliminating the need for a complex closed pipe structure. This not only simplifies the structure and reduces costs but also enhances the uniformity of airflow contact with the battery surface, improving heat exchange efficiency.

[0036] In some preferred embodiments, the positioning module 12 has multiple models, and the inner diameter of the battery receiving cavity 13 of the positioning module 12 of different models is different. Furthermore, the inclination angle and material of the air duct guide rib 131 of the battery receiving cavity 13 can be set to be different to correspond to the outer diameter of the battery of different sizes, so as to meet the performance requirements of fixing, air guiding and heat conduction of cylindrical batteries of different models.

[0037] Specifically, the positioning module 12 can be selected according to the outer diameter specifications of the cylindrical battery 3. The positioning module 12 employs differentiated guide rib parameter design for different regions of the battery 3 of this type: for example, in high heat load regions (such as the airflow outlet), a large-angle, high-density arrangement of the airflow guide ribs 131 is configured to enhance the turbulence effect at the airflow end and strengthen heat exchange efficiency; in low heat load regions (such as the airflow inlet), a small-angle, low-density arrangement of the airflow guide ribs 131 is used to reduce system airflow resistance and optimize the overall flow resistance distribution. This zoned differentiated design can significantly improve the overall heat exchange efficiency of the air-cooled system.

[0038] In some preferred embodiments, the outer wall of the positioning module 12 and the inner wall of the module accommodating cavity 11 are connected by mutually cooperating grooves or protrusions for precise assembly through mutually adapted grooves and protrusions.

[0039] In some preferred embodiments, the angle of the air duct guide rib 131 relative to the battery axis is... Designed to be 15°-45°, this angle range allows for sufficient rotational component to be supplied to the airflow, ensuring a spiral flow effect while avoiding excessive flow resistance, thus achieving a balance between heat exchange efficiency and flow resistance loss.

[0040] In some preferred embodiments, the air duct guide ribs 131 arranged coaxially in parallel within the two module accommodating cavities 11 along the axial direction of the battery 3 have different inclination angles. Specifically, the inclination angle of the air duct guide ribs 131 in the airflow inlet region adjacent to the fan is smaller than that of the air duct guide ribs 131 in the airflow outlet region. This is because the airflow velocity is higher and the heat load is relatively smaller in the airflow inlet region. The smaller inclination angle design can reduce the initial flow resistance while guiding the airflow to form a rotational component, avoiding excessive pressure drop at the inlet. On the other hand, the airflow velocity decreases and the heat load increases significantly in the airflow outlet region far from the fan. The larger inclination angle design can enhance airflow disturbance, effectively destroy the thickened thermal boundary layer on the battery surface, optimize the flow resistance distribution, and improve heat exchange efficiency. Preferably, the fan is generally arranged at one end along the axial direction of the battery 3. Correspondingly, the airflow inlet region and the airflow outlet region usually refer to the regions distributed at both ends along the axial direction of the battery 3.

[0041] This application achieves three core thermal management enhancement effects through a pseudo-spiral air duct structural design, as follows:

[0042] On the one hand, by disrupting the thermal boundary layer and increasing the heat transfer intensity, the airflow guided by the air duct guide rib 131 to form a spiral forward trajectory can continuously sweep the surface of the battery module, effectively disrupting the static air boundary layer formed in the laminar flow state, so that the high temperature surface of the battery 3 is always in full contact with the low temperature fresh airflow, greatly increasing the system Nusselt number and enhancing the convective heat transfer efficiency.

[0043] On the other hand, by extending the effective heat exchange path and increasing the heat exchange time, the low-temperature airflow entering the battery pack changes from the traditional linear motion to a spiral motion. Within a space with a fixed battery length, the contact path between the airflow and the battery surface is significantly extended, increasing the heat exchange time and thus improving the overall heat exchange efficiency.

[0044] Furthermore, by achieving a self-equalizing temperature effect and reducing the temperature difference in the battery pack, the air duct guide ribs 131 in each battery housing cavity 13 maintain a consistent structure, enabling all batteries to achieve similar enhanced cooling effects. At the same time, the formed pseudo-spiral air duct can promote the circumferential temperature uniformity of a single battery 3. Combined with the integrated structural design of the bracket, it ensures the consistency of cooling conditions between each battery 3, effectively reducing the temperature difference of the entire battery pack and avoiding the axial temperature gradient problem present in the parallel flow channel air cooling system.

[0045] In some preferred embodiments, the inclination angle of the air duct guide rib 131 in the airflow inlet area adjacent to the fan is set to a small inclination angle of 15°-25°, and the inclination angle of the air duct guide rib 131 in the airflow outlet area away from the fan is set to a large inclination angle of 25°-45°. This is to adapt to the flow velocity and heat load variation characteristics of the airflow in the flow channel, achieve a precise balance between resistance control and heat exchange enhancement, and ensure the overall heat dissipation effect and temperature uniformity of the battery module.

[0046] In some preferred embodiments, the number of air duct guide ribs 131 provided in a single battery receiving cavity 13 is 8-16, and they are evenly distributed along the inner wall of the module receiving cavity 11. This is to ensure that the airflow forms a stable and uniform pseudo-spiral flow trajectory on the battery surface, so that all areas around the battery can fully contact the cooling airflow, while avoiding local flow channel blockage or airflow dead zones caused by uneven distribution of guide ribs, thus taking into account both heat exchange efficiency and temperature uniformity.

[0047] In some preferred embodiments, the arrangement of guide ribs 131 within different battery accommodating cavities 13 varies in density. The number and density of guide ribs 131 near the airflow inlet of the fan are less than those at the airflow outlet far from the fan. This is because the airflow kinetic energy is higher near the airflow inlet, and an effective vortex can be formed without strong guidance. In this case, appropriately reducing the number and density of guide ribs can leave a wider airflow channel to ensure high-speed flow of cooling gas. Specifically, 8-12 guide ribs can be evenly distributed. At the airflow outlet far from the fan, the airflow kinetic energy is significantly reduced, and it is necessary to compensate for the kinetic energy loss by strengthening the structural guidance to maintain a stable guiding effect. In this case, the number and density of guide ribs can be appropriately increased, specifically 12-16 guide ribs can be evenly distributed.

[0048] In some preferred embodiments, the cross-section of the air duct guide rib 131 is semi-circular, trapezoidal or rectangular, and the radial height of the air duct guide rib 131 along the inner wall of the battery receiving cavity is set between 0.5mm and 2mm. This can accurately guide the airflow direction through the protruding structure without excessively occupying the flow channel space or hindering the airflow velocity, thus balancing the guiding effect and the flow efficiency.

[0049] When the cross-sectional shape of the air duct guide rib 131 is arc-shaped or semi-circular, its interference with the mainstream airflow is low, making it suitable for the airflow inlet area. The design goal of the guide rib in this area is high flowability, requiring low resistance to drive the airflow to form a spiral flow, avoiding excessive initial pressure drop at the inlet.

[0050] When the cross-section of the air duct guide rib 131 is rectangular, it has a clear fixed separation point, which can stably generate a strong vortex and has outstanding airflow disturbance capability, making it more suitable for the heat dissipation area of ​​the airflow outlet. This area has a thick thermal boundary layer, which requires strong disturbance to break through the insulation layer, and the heat load is large, so the heat exchange effect needs to be enhanced; at the same time, the cooling airflow is about to reach the outlet, and the large flow resistance will not have an excessive impact on the overall heat dissipation performance.

[0051] When the cross-sectional shape of the air duct guide rib 131 is trapezoidal, its performance is between that of arc-shaped, semi-circular and rectangular guide ribs, which is relatively balanced and has both airflow and heat dissipation properties, making it suitable for the performance transition zone in the middle section of the battery pack.

[0052] In some preferred embodiments, the height of the air duct guide rib 131 can be designed with fixed dimensions in stages according to the model and outer diameter of the cylindrical battery. The specific adaptation rules are as follows:

[0053] For small-diameter cylindrical batteries with a diameter of less than 20mm (such as 18650 cylindrical batteries), the radial height of the air duct guide rib 131 is set to 0.5mm.

[0054] For medium-diameter cylindrical batteries with a diameter of 21-25mm (such as the 21700 cylindrical battery), the radial height of the air duct guide rib 131 is set to 1mm.

[0055] For cylindrical batteries with a diameter of 26-35mm (such as the 26650 cylindrical battery), the radial height of the air duct guide rib 131 is set to 1.5mm.

[0056] For ultra-large diameter cylindrical batteries with a diameter of 36mm or more (such as the 4680 cylindrical battery), the radial height of the air duct guide rib 131 is set to 2mm.

[0057] After ensuring the assembly of batteries of different specifications, the flow channel structure meets the requirements of geometric similarity and flow field dynamics similarity. This can reduce the difficulty of mold modification and component manufacturing, and achieve near-optimal heat dissipation performance within similar working conditions, ultimately achieving a balance between heat dissipation effect and manufacturing cost.

[0058] It should be added that the design of this invention aims to integrate the advantages of the above-mentioned solutions and avoid their shortcomings. Relying on the modular design of the battery housing cavity, the battery housing cavity upstream and downstream of the air duct is designed with differentiated zones. Specifically: in the airflow inlet area, guide ribs with small inclination angle, small arrangement density and arc or semi-circular cross-section are used to maximize the flow guidance performance and ensure that the airflow forms a stable spiral flow with low resistance; in the middle section of the battery pack, guide ribs with medium inclination angle, medium arrangement density and trapezoidal cross-section are used to achieve a balanced adaptation of flow guidance and heat dissipation through transition parameter design; in the airflow outlet area, guide ribs with large inclination angle, high arrangement density and rectangular cross-section are used to maximize the enhancement of airflow disturbance capability and heat transfer performance and efficiently destroy the thickened thermal boundary layer.

[0059] In some preferred embodiments, such as Figure 4 As shown, the bracket 1 and the positioning module 12 are made of flame-retardant plastic or aluminum alloy, and the battery housing cavity 13 is made of thermally conductive engineering plastic. A thin metal thermally conductive ring 15 is embedded in the inner layer of the air duct guide rib 131. The thermally conductive engineering plastic and the embedded metal thermally conductive ring 15 work together to distribute heat evenly among the battery modules. The air duct guide rib 131 is responsible for optimizing the airflow organization of the pseudo-spiral air duct. The embedded metal material can significantly improve the structural strength of the battery housing cavity 13 and extend its service life.

[0060] By adopting this thermally conductive and air-conducting composite functional design, the bracket 1 and the battery housing 13 achieve both axial airflow guidance and radial thermal conductivity. After the improvement, the heat generated by the battery module can be dissipated simultaneously through both conduction and convection, which not only enhances the overall heat dissipation performance of the system and ensures the structural strength of the airflow guide ribs 131, but also further reduces the maximum temperature difference between batteries and improves the temperature uniformity within the battery module.

[0061] In some preferred embodiments, at least two of the supports 1 are arranged side-by-side and supported by the connecting portion 2 in a gap distribution, so that there is a gap between the air duct guide ribs 131 in two adjacent battery receiving cavities 13. When the cooling gas flows through the battery mounting hole, due to viscosity, a thin layer is formed with a velocity that gradually increases from zero at the hole wall to the mainstream velocity; this is the velocity boundary layer. Simultaneously, a temperature boundary layer is also formed, with its temperature gradually changing from the wall temperature to the mainstream temperature. At the beginning of the air duct guide rib 131, the boundary layer thickness is very thin, the temperature gradient is large, and heat transfer is intense. As the airflow continues along the continuous air duct guide ribs 131, the boundary layer continuously thickens, the thermal resistance increases, and the heat transfer effect significantly decreases.

[0062] To overcome this performance bottleneck of continuous long ribs, the present invention changes the continuous long spiral air duct guide rib 131 to a segmented discontinuous air duct guide rib 131 structure, with a specific interval between each segment of rib.

[0063] In some preferred embodiments, two adjacent positioning modules 12 arranged in parallel are supported by a connecting part 2 and form a gap distribution. A gap is reserved between the air duct guide ribs 131 in the two adjacent battery receiving cavities 13 arranged in parallel, and the gap value is between 10% and 15% of the total axial length of the cylindrical battery 3.

[0064] This design effectively avoids the accumulation of temperature and velocity boundary layers by controlling the regeneration cycle of the boundary layer. When the cooling airflow reaches the end of a section of the duct guide rib 131, the original thick boundary layer separates from the wall due to the abrupt change in the flow cross-section, generating certain vortices. In the interval region between two parallel duct guide ribs 131, the vortices generated by the boundary layer mix with the main airflow of the duct, promoting the mixing of hot and cold fluids and breaking the stable state of the thermal boundary layer. When the cooling airflow reaches the beginning of the next section of the duct guide rib 131, a new thin boundary layer begins to reform. Due to the sufficient mixing of vortices in the interval region, the fluid temperature reaching this point is closer to the mainstream temperature, restoring a large temperature gradient, and the heat transfer process becomes more intense again. At the same time, because the airflow velocity is higher and the heat load is lower near the airflow inlet, the thermal boundary layer is generally thinner, so a smaller interval is required. However, the airflow velocity is lower and the heat load is higher near the airflow outlet, resulting in a thicker thermal boundary layer, requiring stronger disturbance performance to break the thermal boundary layer, thus requiring a larger interval.

[0065] In the design of the lengths of the three segmented guide ribs and the two discontinuous layers in between, this invention proposes two different design principles to optimize the heat dissipation performance of the system, addressing the contradiction between the non-uniformity of the airflow field and the temperature field:

[0066] 1. Ideal attenuation principle: Dynamically compensate for cooling airflow attenuation along the path.

[0067] This principle addresses the core issues of temperature rise, velocity reduction, and efficiency degradation in cooling airflow during its flow. The design strictly adheres to the principle of airflow attenuation along the airflow path, with parameters such as the length and height of discontinuities and guide ribs increasing gradually along the airflow direction. This design effectively provides stronger disturbances and a longer recovery zone for the attenuating airflow at the rear, precisely compensating for its cooling capacity and allocating the most airflow guidance resources to the end with the worst heat dissipation conditions, aiming to achieve higher heat dissipation efficiency. For example, taking a standard 70mm high 21700 cylindrical battery as an example, the first guide rib is 14mm long, accounting for 20%; the first discontinuity height is 7mm, accounting for 10%; the second guide rib is 17.5mm long, accounting for 25%; the second discontinuity height is 10.5mm, accounting for 15%; and the third guide rib is 21mm long, accounting for 30%. This design principle is suitable for scenarios where the battery itself generates heat uniformly, but the airflow path is long and airflow attenuation is significant, effectively eliminating high heat at the end and ensuring temperature uniformity. If the design seriously violates this principle, it will lead to excessive cooling at the front end and insufficient heat dissipation at the rear end, resulting in a huge axial temperature difference, which will endanger the safety and life of the battery pack.

[0068] 2. Uniform heat dissipation principle: aligning and enhancing heat dissipation in the battery core area.

[0069] This principle addresses the inherent characteristics of cylindrical batteries, such as uneven heat generation and the central area often being the hottest zone. In its design, it breaks away from the conventional uniform structure, allocating heat dissipation resources according to the intensity of heat sources, and specifically enhancing heat dissipation in the battery's core area. Specifically, when the total structural length is limited, the longest continuous guide ribs and those with the greatest disturbance intensity are prioritized in the middle section of the battery to achieve saturated heat dissipation from the core heat source. This prioritizes ensuring the efficiency of the central core area with the highest heat load, preventing excessive overall battery temperature rise and resulting in better temperature uniformity across the battery pack. Compensation is achieved at the ends by increasing the height of guide ribs and other non-length dimensions. For example, taking a standard 70mm high 21700 model cylindrical battery as an example, the first guide rib is 10.5mm long, accounting for 15%; the first discontinuity height is 7mm, accounting for 10%; the second guide rib is 24.5mm long, accounting for 35%; the second discontinuity height is 10.5mm, accounting for 15%; and the third guide rib is 17.5mm long, accounting for 25%. This design principle is key to solving the problem of internal heat accumulation in batteries and achieving highly integrated designs. It is suitable for modules with high concentration of battery heat generation or extremely compact spaces. If the design seriously violates this principle, heat dissipation resources will be misconfigured, resulting in insufficient cooling of the core hot areas. Even if the end temperature is controllable, the overall temperature rise of the battery pack and safety risks will still worsen.

[0070] These two length design principles constitute a systematic solution to address different major contradictions. Through a quantifiable and implementable gradient passive structural design, the upper limit of efficiency and the lower limit of safety of the air-cooled system can be significantly improved without the need for additional active control.

[0071] The specific embodiments of this application have been described in detail above. For those skilled in the art, several improvements and modifications can be made to this application without departing from the principle of this application, and these improvements and modifications also fall within the protection scope of the claims of this application.

Claims

1. A battery module support structure, characterized in that: It includes at least two supports (1), and two adjacent supports (1) are connected by a connecting part (2). Each support (1) is provided with a plurality of module receiving cavities (11). A positioning module (12) is detachably connected in the module receiving cavity (11). A battery receiving cavity (13) is provided in the positioning module (12). A plurality of air duct guide ribs (131) are provided on the inner wall of the battery receiving cavity (13). The plurality of air duct guide ribs (131) protrude inward along the radial direction of the battery receiving cavity (13) and extend in a pseudo-spiral shape in the same direction. At least two of the brackets (1) are arranged in parallel and their battery receiving cavities (13) are coaxially arranged and contain batteries (3). The outer wall of the battery (3) is in contact with the air duct guide rib (131) and forms a pseudo-spiral gap flow channel with the inner wall of the battery receiving cavity (13). Along the axial direction of the battery (3), the inclination angles of the air duct guide ribs (131) in the two battery receiving cavities (13) arranged coaxially are different. The inclination angle of the air duct guide rib (131) adjacent to the airflow inlet area of ​​the fan is smaller than the inclination angle of the air duct guide rib (131) far from the airflow outlet area.

2. The battery module bracket structure according to claim 1, characterized in that: The positioning module (12) has multiple models, and the inner diameter of the battery receiving cavity (13) and / or the geometric parameters of the air duct guide rib (131) of different models of the positioning module (12) are not the same.

3. The battery module bracket structure according to claim 1, characterized in that: The angle of the air duct guide rib (131) relative to the battery axis The design is for 15°-45°.

4. The battery module bracket structure according to claim 1, characterized in that: The inclination angle of the air duct guide rib (131) in the airflow inlet area adjacent to the fan is set to a small inclination angle of 15°-25°.

5. The battery module bracket structure according to claim 1, characterized in that: The inclination angle of the air duct guide rib (131) in the airflow outlet area away from the fan is set to a large inclination angle of 25°-45°.

6. The battery module bracket structure according to claim 1, characterized in that: The number of air duct guide ribs (131) provided in a single battery receiving cavity (13) is 8-16, and they are evenly distributed along the inner wall of the battery receiving cavity (13).

7. The battery module bracket structure according to claim 1, characterized in that: The arrangement of guide ribs (131) in different battery cavities (13) has different density. The number and density of guide ribs (131) at the airflow inlet near the fan are less than the number and density of guide ribs (131) at the airflow outlet far from the fan.

8. The battery module bracket structure according to claim 1, characterized in that: The cross-section of the air duct guide rib (131) is semi-circular, trapezoidal or rectangular, and the radial height of the air duct guide rib (131) along the inner wall of the battery receiving cavity (13) is set between 0.5mm and 2mm.

9. The battery module bracket structure according to claim 1, characterized in that: The two adjacent positioning modules (12) arranged in parallel are supported by the connecting part (2) and form a gap distribution. The air duct guide ribs (131) in the two adjacent battery receiving cavities (13) arranged in parallel are reserved with a gap value between 10% and 15% of the total axial length of the cylindrical battery (3).

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