Heat dissipation air duct structure and energy storage container matched with heat dissipation air duct structure

Abstract

The invention belongs to the technical field of energy storage equipment, and particularly relates to a heat dissipation air duct structure and an energy storage container matched with the heat dissipation air duct structure. The air inlet is formed in one end of the air pipe main body, and a refrigerating medium can be input into the air pipe main body through the air inlet; the plurality of air outlets are distributed along the side edge of the air pipe main body, and the air outlets can convey a cooling medium in the air pipe main body to the battery units; and the multiple wind shields are fixed in the air pipe body at equal intervals, and the multiple wind shields are matched with the multiple air outlets one by one. The multiple wind shields with the lengths gradually increased are arranged in the air pipe body, and the opening length of the air outlet is adjusted so that the air volume can be balanced, the air volume attenuation phenomenon can be prevented, the overall cooling effect in the box body can be ensured, and the local high temperature phenomenon can be avoided.

Description

Technical Field

[0001] The present invention belongs to the technical field of energy storage equipment, and in particular relates to a heat dissipation air duct structure and an energy storage container adapted thereto. Background Art

[0002] With the rapid development of the new energy industry, energy storage containers, as the core carrier of battery systems, have a direct impact on battery life and operational safety due to their internal thermal management efficiency. In energy storage containers, battery packs are densely stacked and generate a large amount of heat during operation. If the heat cannot be dissipated evenly and promptly, it will cause localized excessive temperature rise, exacerbating battery aging and even triggering the risk of thermal runaway. Traditional cooling solutions rely on air conditioning systems to lower the ambient temperature, but using only a single air duct to deliver cool air makes it difficult to solve the problem of uneven heat dissipation between battery packs due to positional differences. There is an urgent need to optimize the air duct structure to achieve precise temperature control.

[0003] Existing energy storage containers often use a rear-open, straight-exhaust air duct design. As the cool air flows from the inlet to the outlet, the air volume gradually decreases along the way. This results in insufficient heat dissipation for battery packs farther from the inlet, significantly lower cooling efficiency than for battery packs closer to the inlet, creating localized high-temperature zones. This uneven heat dissipation not only reduces overall system energy efficiency but can also cause condensation due to large temperature differences, threatening battery stability.

[0004] In response to the above problems, this application document proposes a heat dissipation duct structure and an energy storage container adapted thereto to improve the above problems, thereby making the cooling effect inside the energy storage container more uniform. Summary of the Invention

[0005] The purpose of the present invention is to provide a heat dissipation air duct structure and an energy storage container adapted thereto, wherein a plurality of wind shields with increasing lengths are arranged inside the air duct body, and the opening length of the air outlet is adjusted to balance the air volume, prevent the phenomenon of air volume attenuation, ensure the overall cooling effect inside the box, and avoid the occurrence of local high temperature.

[0006] The technical solutions adopted by the present invention are as follows:

[0007] A heat dissipation duct structure, comprising:

[0008] An air duct body, the air duct body being capable of conveying a refrigerant medium;

[0009] An air inlet, which is provided at one end of the air duct body, through which a refrigerant medium can be input into the interior of the air duct body;

[0010] Multiple air outlets, the multiple air outlets are distributed along the side of the air duct body, and the air outlets can transport the cooling medium inside the air duct body to the battery unit;

[0011] Multiple wind deflectors, which are fixed equidistantly inside the duct main body. Each of the multiple wind deflectors is adapted to one of the multiple air outlets, and the lengths of the multiple air outlets increase sequentially from the end close to the duct main body to the end far from the duct main body.

[0012] The increasing lengths of the multiple wind deflectors are configured to balance the air mass flow rate at each air outlet, and the difference in gas mass flow rate between any two air outlets is less than 30%.

[0013] In a preferred embodiment, the length ratio of the wind deflector and the distance between two adjacent wind deflectors satisfy the first equation: y = ax 3 - bx 2 + cx - d, where y represents the length ratio of the wind deflector, x represents the distance between two adjacent wind deflectors, and a, b, c, and d are all fitting coefficients. According to the first fitting curve, a = 8.64, b = 12.88, c = 5.96, and d = 0.72.

[0014] In a preferred embodiment, the opening length ratio of the air outlet and the distance between two adjacent wind deflectors satisfy the second equation: z = - hx 3 + ix 2 - jx + k, where z represents the opening length ratio of the air outlet, x represents the distance between two adjacent wind deflectors, and h, i, j, and k are all fitting coefficients. According to the second fitting curve, h = 0.6626, i = 1.175, j = 0.4206, and k = 0.91.

[0015] In a preferred embodiment, the formula for calculating the length ratio of the wind deflector is: where y represents the length ratio of the wind deflector, L represents the length of the wind deflector, and W represents the cross-sectional width of the duct main body.

[0016] In a preferred embodiment, the formula for calculating the opening length ratio of the air outlet is: where z represents the opening length ratio of the air outlet, L1 represents the opening length of the air outlet, and L represents the length of the wind deflector.

[0017] In a preferred embodiment, the material of the duct main body is preferably one of the following materials: aluminum alloy, ABS, PP.

[0018] In a preferred embodiment, anti-condensation coatings are provided on both the inner wall and the outer wall of the duct main body.

[0019] An energy storage container includes a box body and a heat dissipation air duct structure described in any one of the above. A refrigeration module is assembled on the box body, and a plurality of battery pack modules are assembled inside the box body. The main air duct is fixed to the upper end inside the box body, and the air inlet, the refrigeration module, and the air outlets and the plurality of battery pack modules are all adapted to each other.

[0020] The technical effects achieved by the present invention are as follows:

[0021] In the present invention, by arranging a plurality of wind baffle plates with gradually increasing lengths inside the main air duct, and at the same time, adjusting the opening length of the air outlets, the opening lengths of the plurality of air outlets are gradually increased. Through the cooperation of the plurality of air outlets and the wind baffle plates, the air volume of the plurality of air outlets can be balanced, avoiding the phenomenon that the air volume gradually decays at the plurality of air outlets, ensuring the overall cooling effect inside the box body, and avoiding the phenomenon of local high temperature inside the box body. Description of the Drawings

[0022] Figure 1 is a schematic structural diagram of the main air duct in Embodiment 1 of the present invention;

[0023] Figure 2 is a rear view of the structure of the main air duct in Embodiment 1 of the present invention;

[0024] Figure 3 is a schematic structural diagram of the inside of the main air duct in Embodiment 1 of the present invention;

[0025] Figure 4 is a schematic partial structural diagram of the inside of the main air duct in Embodiment 1 of the present invention;

[0026] Figure 5 is a schematic structural diagram of the box body in Embodiment 2 of the present invention;

[0027] Figure 6 is a schematic structural diagram of the inside of the box body in Embodiment 2 of the present invention;

[0028] Figure 7 is a schematic diagram of the mass flow rate of a plurality of air outlets in Test Example 1 of the present invention;

[0029] Figure 8 is a schematic diagram of the mass flow rate of a plurality of air outlets in Test Example 3 and Test Example 4 of the present invention.

[0030] In the drawings, the list of components represented by each reference numeral is as follows:

[0031] 10. Main air duct; 11. Air inlet; 12. Air outlet; 13. Wind baffle plate; 20. Box body; 21. Refrigeration module; 22. Battery pack module. Detailed Embodiments

[0032] To make the above objects, features, and advantages of the present invention more apparent and understandable, the following provides a detailed description of the specific embodiments of the present invention in conjunction with the accompanying drawings of the specification.

[0033] In the following description, numerous specific details are set forth to facilitate a full understanding of the present invention. However, the present invention may also be implemented in other ways different from those described herein. Those skilled in the art can make similar generalizations without departing from the connotation of the present invention. Therefore, the present invention is not limited by the specific embodiments disclosed below.

[0034] Secondly, the so-called "one embodiment" or "embodiment" herein refers to a specific feature, structure, or characteristic that may be included in at least one implementation manner of the present invention. The phrase "in a preferred embodiment" that appears in different places in this specification does not necessarily refer to the same embodiment, nor is it an individual or selectively exclusive embodiment with other embodiments.

[0035] Furthermore, the present invention is described in detail in conjunction with schematic diagrams. When elaborating on the embodiments of the present invention, for ease of explanation, the cross-sectional views showing the device structure are enlarged locally out of proportion, and the schematic diagrams are only examples and should not limit the scope of protection of the present invention herein. In addition, in actual production, three-dimensional spatial dimensions including length, width, and depth should be included.

[0036] Embodiment 1

[0037] Please refer to the attached Figures 1 to 4 As shown, this is the first embodiment of the present invention. This embodiment provides a heat dissipation air duct structure, which is applied to a closed cavity component with multiple heat sources inside and a cooling requirement, such as an energy storage container, a power cabinet, etc. In this embodiment, taking the energy storage container as an example, it includes:

[0038] An air duct main body 10, and the air duct main body 10 can convey a refrigeration medium;

[0039] An air inlet 11, which is arranged at one end of the air duct main body 10, and through the air inlet 11, a refrigeration medium can be input into the interior of the air duct main body 10;

[0040] Multiple air outlets 12, which are distributed along the side of the air duct main body 10, and the air outlets 12 can convey the cooling medium inside the air duct main body 10 to the battery unit;

[0041] Multiple wind baffle plates 13, which are fixedly arranged at equal intervals inside the air duct main body 10. The multiple wind baffle plates 13 are in one-to-one correspondence with the multiple air outlets 12, and the lengths of the multiple air outlets 12 increase sequentially from the end close to the air duct main body 10 to the end far from the air duct main body 10;

[0042] The lengths of the multiple windshields 13 are configured to increase gradually to balance the air mass flow rate of each air outlet 12, and the difference in the gas mass flow rate between any two air outlets 12 is less than 20% of the box body.

[0043] It should be noted that in this embodiment, the refrigeration medium is the cold air of the air conditioner. Of course, the selection of the refrigeration medium can be based on the actual cooling target object. For example, when the cooling target object is an electrical cabinet, the cooling medium can be selected as the air outside the electrical cabinet. Here, it is not specifically limited.

[0044] In this embodiment, the cooling medium is input into the interior of the duct main body 10 through the air inlet 11. Under the guidance of the duct main body 10, the cooling medium flows inside the duct main body 10. When the cooling medium contacts the windshields 13 with gradually increasing lengths, part of the cooling medium is diverted by the windshields 13. Through the guidance of the windshields 13, the cooling medium in contact with the windshields 13 flows out from the corresponding air outlets 12. Through the coordinated cooperation of the multiple windshields 13 with gradually increasing lengths, the air mass flow rate of the multiple air outlets 12 is balanced, ensuring that the difference between the maximum and minimum mass flow rates in the multiple air outlets 12 is controlled within 20% of the box body, so that the cooling effect and cooling efficiency inside the energy storage container are more uniform.

[0045] In a preferred embodiment, the length ratio of the windshield 13 and the distance between two adjacent windshields 13 satisfy the first equation: y = ax 3 -bx 2 +cx - d, where y represents the length ratio of the windshield 13, x represents the distance between two adjacent windshields 13, and a, b, c, and d are all fitting coefficients. According to the first fitting curve, a = 8.64, b = 12.88, c = 5.96, and d = 0.72.

[0046] Furthermore, the calculation formula for the length ratio of the windshield 13 is: where y represents the length ratio of the windshield 13, L represents the length of the windshield 13, and W represents the cross-sectional width of the duct main body 10.

[0047] It should be noted that the value of W is a known fixed value, and the value of W has been determined before the production and processing of the duct main body 10.

[0048] In a preferred embodiment, the opening length ratio of the air outlet 12 and the distance between two adjacent windshields 13 satisfy the second equation: z = -hx 3 +ix 2-jx + k, where x represents the opening length ratio of the air outlet 12, x represents the distance between two adjacent wind deflectors 13, and h, i, j, and k are all fitting coefficients. According to the second fitting curve, h = 0.6626, i = 1.175, j = 0.4206, and k = 0.91.

[0049] Further, the calculation formula for the opening length ratio of the air outlet 12 is: where z represents the opening length ratio of the air outlet 12, L1 represents the opening length of the air outlet 12, and L represents the length of the wind deflector 13.

[0050] In a preferred embodiment, the material of the air duct main body 10 is preferably one of the following materials: stainless steel, aluminum alloy, ABS, PP, or other engineering plastics. Anti-condensation coatings are provided on both the inner and outer walls of the air duct main body 10. In this embodiment, the material of the air duct main body 10 is preferably aluminum alloy.

[0051] In this implementation, during the process of cooling the energy storage container, a cooling medium is transported through the air duct main body 10. There is a large temperature difference between the inside and outside of the air duct main body 10. The setting of the anti-condensation coating can prevent condensate from appearing on the surface of the air duct main body 10.

[0052] Embodiment 2

[0053] Please refer to Figures 5 to 6 , an energy storage container, including a box body 20 and a heat dissipation air duct structure according to any one of Embodiment 1. A refrigeration module 21 is assembled on the box body 20, and a plurality of battery pack modules 22 are assembled inside the box body 20. The air duct main body 10 is fixed to the upper end inside the box body 20, and the air inlet 11, the refrigeration module 21, and the air outlet 12 are all adapted to the plurality of battery pack modules 22 one by one.

[0054] It should be noted that the installation position of the refrigeration module 21 can be adjusted according to actual application requirements. In the prior art, there are mainly two types of installation positions for the refrigeration module 21. One is to install the refrigeration module 21 on the outer wall of the air duct main body 10, and the other is to separately open a temperature control chamber inside the air duct main body 10 and install the refrigeration module 21 on the inner wall of the temperature control chamber. Among them, regardless of which installation method the refrigeration module 21 adopts, the output end of the refrigeration module 21 needs to be connected to the air inlet 11. Since the above two installation methods are both existing mature applications, their specific structures and installation methods can be referred to the prior art, and no further elaboration and limitation will be made here.

[0055] In this embodiment, after starting the refrigeration module 21, the refrigeration module 21 conveys a cooling medium into the air inlet 11. The cooling flows along the inside of the air duct main body 10. When the cooling medium contacts the multiple baffle plates 13 in sequence, the baffle plates 13 sequentially shunt the cooling medium flowing inside the air duct main body 10. After being shunted, the cooling medium flows out from the air outlet 12 to cool the battery pack module 22. Through the coordinated cooperation of the multiple baffle plates 13 with increasing lengths, the air mass flow rate of the multiple air outlets 12 is balanced, ensuring that the difference between the maximum and minimum mass flow rates in the multiple air outlets 12 is controlled within 20% of the box body, so that the overall cooling effect and cooling efficiency inside the energy storage container are more uniform. At the same time, its air duct process is simple, and the old traditional energy storage container air duct can be improved at low cost. The cost of optimizing the process and production line for the container using this technical solution is relatively low.

[0056] Test example

[0057] Test preparation

[0058] Please refer to Figures 5 to 6 As shown, the number of battery pack modules 22 inside the box body 20 is set to 4, the number of air outlets 12 on the side of the air duct main body 10 is set to 4, and the air outlets 12 and the battery pack modules 22 are in one-to-one correspondence. The distance between two adjacent baffle plates 13 is set to 950 mm, and the width of the inner cross-section of the air duct main body 10 is set to 300 mm. Other parameters are adjusted adaptively according to different test examples.

[0059] Test example 1: Uniformity test of the air mass flow rate at the air outlets with equal-length air guiding plates

[0060] The lengths of all the baffle plates 13 are uniformly set to 150 mm (i.e., the length ratio y of the baffle plates 13 = 0.5). The ambient temperature is 25 °C, and the battery pack module 22 simulates the heat generation under the rated load. The refrigeration module 21 conveys a cooling medium into the air duct main body 10. The mass flow rate of each air outlet 12 is measured by a mass flow meter, and the percentage difference between the maximum and minimum mass flow rates under the condition of y = 0.5 is calculated. Gradually and uniformly shorten the lengths of the baffle plates 13 (it is necessary to keep the lengths of all the baffle plates 13 the same), repeat the above test steps, and respectively test the percentage differences between the maximum and minimum mass flow rates of the multiple air outlets 12 under the conditions that the lengths of the baffle plates 13 are 120 mm (y = 0.5), 90 mm (y = 0.5), and 45 mm (y = 0.5), and statistically analyze the results. The test results are shown in Table 1.

[0061] Table 1:

[0062] Operating condition Length ratio Maximum mass flow rate (Kg / s) Minimum mass flow rate (Kg / s) Flow rate difference (Max&Min) Operating condition 1 0.5 0.9825 0.0393 96％ Operating condition 2 0.4 0.0895 0.0474 47％ Operating condition 3 0.3 0.0758 0.0535 29％ Operating condition 4 0.15 0.079 0.0545 31％

[0063] Combined with Table 1 and Appendix Figure 7It can be seen that when the distance between two adjacent windshields 13 is 950 mm and the lengths of the windshields 13 are the same, as the length ratio of the windshields 13 decreases from 0.5 to 0.3, the difference between the maximum and minimum mass flow rates gradually decreases. When the length ratio of the windshields 13 decreases to 0.15, the difference between the maximum and minimum mass flow rates rises to 31%. It can be found that under the condition that the lengths of the windshields 13 are equal, the boundary of the difference between the maximum and minimum mass flow rates is between 29% and 30%.

[0064] Here, the calculation formula for the flow rate difference is as follows:

[0065] Test Example 2: Test on the Optimization Effect of Air Volume Distribution of Wind Deflectors with Increasing Length

[0066] The length ratios of multiple windshields 13 are sequentially increased along the air flow direction. From the end close to the air inlet 11 to the end far from the air inlet 11, the length ratios y of multiple windshields 13 are sequentially set to 0.1, 0.12, 0.15, and 0.5. A cooling medium is input into the main duct body 10 through the refrigeration module 21, and the mass flow rates of each air outlet 12 are measured by a mass flow meter, and the test data are recorded. Among them, multiple air outlets 12 are sequentially named the first air outlet, the second air outlet, the third air outlet, and the fourth air outlet from the end close to the air inlet 11 to the end far from the air inlet 11. See Table 2 for the test data.

[0067] Table 2:

[0068]

[0069] It can be seen from Table 2 that under the condition that the lengths of the windshields 13 increase sequentially, the difference between the maximum and minimum mass flow rates is reduced to 19.8%, which is nearly 10% optimized compared with the equal-length condition in Example 1. Among them, the mathematical relationship between the length ratio of the windshields 13 and the distance between the baffles can be fitted to obtain the first fitting curve, and the equation of the first fitting curve is: y = 8.64x 3 - 12.88x 2 + 5.96x - 0.72, where y represents the length ratio of the windshields 13 and x represents the distance between two adjacent windshields 13.

[0070] Test Example 3: Test on the Flow Rate Uniformity of Air Outlets with Fixed Opening Sizes

[0071] The opening lengths of all air outlets 12 are uniformly set to 120 mm, and the length of the wind deflector 13 is also uniformly set to 120 mm (i.e., z = 1). The ambient temperature is 25°C. The battery pack module 22 simulates the heat generation under rated load, and the cooling medium is conveyed into the main duct 10 through the refrigeration module 21. The mass flow rate of each air outlet 12 is measured by a mass flow meter, and the percentage difference between the maximum and minimum mass flow rates under the condition of z = 1 is calculated. The opening lengths of the air outlets 12 are gradually and uniformly shortened (while keeping the length of all wind deflectors 13 at 120 mm), and the above test steps are repeated. The percentage difference between the maximum and minimum mass flow rates of multiple air outlets 12 under the condition of the opening length of the air outlet 12 being 30 mm (z = 0.25) is tested, and the results are statistically analyzed. The test results are shown in Table 3.

[0072] Test Example 4: Optimization Test of Air Volume Distribution with Increasing Outlet Length

[0073] The lengths of all wind deflectors 13 are uniformly set to 120, and the opening lengths of multiple air outlets 12 increase sequentially from the end close to the air inlet 11 to the end far from the air inlet 11. The opening length ratios of multiple air outlets 12 are sequentially set to 0.75 / 0.833 / 0.916 / 1. The cooling medium is input into the main duct 10 through the refrigeration module 21. The mass flow rate of each air outlet 12 is measured by a mass flow meter, and the test data are recorded. The opening length ratios of the air outlets 12 are adjusted, and the above test steps are repeated. The mass flow rates of multiple air outlets 12 are respectively tested under the conditions of the opening length ratios of 0.875 / 0.916 / 0.958 / 1,

[0074] 0.875 / 0.9 / 0.983 / 1, and the difference between the maximum and minimum mass flow rates is calculated. The results are shown in Table 3.

[0075] Table 3:

[0076]

[0077] According to Appendix Figure 8 and Table 3, and by combining the test data of Working Condition 1 and Working Condition 2, it can be seen that as the opening length ratio of the air outlet 12 decreases, the difference between the maximum and minimum mass flow rates gradually increases. By combining the test data in Working Conditions 3 to 5, it can be seen that the mass flow rate difference in Working Condition 5 is the smallest. According to the data in Working Condition 5, the second fitting curve is fitted, and the equation of the second fitting curve is: z = -0.6626x 3 +1.175x 2 -0.4206x + 0.91;

[0078] It can be seen through testing that by arranging a plurality of wind baffle plates 13 with gradually increasing lengths inside the air duct main body 10, and at the same time, adjusting the opening lengths of the air outlets 12 so that the opening lengths of the plurality of air outlets 12 increase in sequence, through the cooperation of the plurality of air outlets 12 and the wind baffle plates 13, the air volume of the plurality of air outlets 12 can be balanced, avoiding the phenomenon that the air volume of the plurality of air outlets 12 gradually decays, ensuring the overall cooling effect inside the box body 20, and avoiding the phenomenon of local high temperature inside the box body 20.

[0079] The above is only the preferred embodiment of the present invention. It should be noted that for those of ordinary skill in the art in this technical field, without departing from the principle of the present invention, several improvements and retouches can still be made, and these improvements and retouches should also be regarded as the protection scope of the present invention. The structures, devices, and operation methods not specifically described and explained in the present invention, unless otherwise specified and limited, are implemented according to the conventional means in this field.

Claims

1. A heat dissipation air duct structure, characterized in that: Comprising: An air duct main body (10), and the air duct main body (10) is capable of transporting a refrigerating medium; An air inlet (11), which is arranged at one end of the air duct main body (10), and through the air inlet (11), the refrigerating medium can be input into the interior of the air duct main body (10); A plurality of air outlets (12), and the plurality of air outlets (12) are distributed along the side of the air duct main body (10), and the air outlets (12) can transport the cooling medium inside the air duct main body (10) to the battery unit; A plurality of windshields (13), and the plurality of windshields (13) are fixedly arranged at equal intervals inside the air duct main body (10), and the plurality of windshields (13) are in one-to-one correspondence with the plurality of air outlets (12), and the lengths of the plurality of air outlets (12) increase sequentially from one end close to the air duct main body (10) to the end far from the air duct main body (10); The increasing lengths of the plurality of windshields (13) are configured to balance the air mass flow rate of each air outlet (12), and the difference in the gas mass flow rate between any two air outlets (12) is less than 30%.

2. The heat dissipation air duct structure according to claim 1, characterized in that: The length ratio of the wind deflector (13) and the distance between two adjacent wind deflectors (13) satisfy the first equation: y = ax 3 - bx 2 + cx - d, where y represents the length ratio of the wind deflector (13), x represents the distance between two adjacent wind deflectors (13), and a, b, c, and d are all fitting coefficients.

3. The heat dissipation air duct structure according to claim 1, characterized in that: The opening length ratio of the air outlet (12) and the distance between two adjacent wind deflectors (13) satisfy the second equation: z = -hx 3 +ix 2 -jx + k, where z represents the opening length ratio of the air outlet (12), x represents the distance between two adjacent wind deflectors (13), and h, i, j, and k are all fitting coefficients.

4. A heat dissipation air duct structure according to claim 2, characterized in that: The length ratio calculation formula of the wind deflector (13) is as follows: Where y represents the length ratio of the wind deflector (13), L represents the length of the wind deflector (13), and W represents the cross-sectional width of the air duct main body (10).

5. The heat dissipation air duct structure according to claim 3, characterized in that: The opening length ratio calculation formula of the air outlet (12) is as follows: Where z represents the opening length ratio of the air outlet (12), L1 represents the opening length of the air outlet (12), and L represents the length of the wind deflector (13).

6. The heat dissipation air duct structure according to claim 1, characterized in that: The material of the air duct main body (10) is preferably one of the following materials: aluminum alloy, ABS, PP.

7. A heat dissipation air duct structure according to claim 1, characterized in that: Anti-condensation coatings are provided on both the inner wall and the outer wall of the air duct main body (10).

8. An energy storage container, characterized in that: Comprising a box body (20) and a heat dissipation air duct structure according to any one of claims 1 to 7, a refrigeration module (21) is assembled on the box body (20), a plurality of battery pack modules (22) are assembled inside the box body (20), the air duct main body (10) is fixed to the upper end inside the box body (20), and the air inlet (11) is in one-to-one correspondence with the refrigeration module (21) and the air outlets (12) are in one-to-one correspondence with the plurality of battery pack modules (22).

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