Cooling assembly, battery pack and energy storage device

Abstract

The utility model relates to the technical field of energy storage, particularly provides a cooling assembly, a battery pack and an energy storage device, and aims to solve the problems of large temperature difference and poor temperature uniformity of a liquid inlet side and a liquid outlet side of a battery cooling assembly. Therefore, the cooling assembly comprises a heat exchange pipe set and a first collecting pipe. The heat exchange tube group comprises a plurality of heat exchange tubes; a first flow channel and a second flow channel which are not communicated with each other are arranged in the first collecting pipe, the first flow channel is provided with a water injection port and first communication ports which are communicated with one ends of the multiple heat exchange pipes in a one-to-one correspondence mode, and the second flow channel is provided with a water drainage port and second communication ports which are communicated with the other ends of the multiple heat exchange pipes in a one-to-one correspondence mode. The first flow channel and the second flow channel which are not communicated with each other are arranged in the single collecting pipe, so that the problems of non-uniform flow distribution caused by parallel pipelines and large temperature difference between the liquid inlet side and the liquid outlet side of the parallel pipelines are solved, the temperature change of cooling liquid in each heat exchange pipe is more consistent, and the temperature distribution of each part of the battery is more balanced.

Description

Technical Field

[0001] This utility model relates to the field of energy storage technology, specifically providing a cooling component, a battery pack, and an energy storage device. Background Technology

[0002] With the rapid development of the new energy industry, battery energy storage systems are increasingly widely used in electric vehicles, grid peak shaving, and other fields. However, battery modules generate a large amount of heat during operation. If heat dissipation is not timely, it can easily lead to problems such as localized overheating and uneven temperature distribution, which in turn can cause battery performance degradation, shortened cycle life, and even the risk of thermal runaway. Therefore, an efficient and reliable cooling system has become a key technology to ensure the safe and stable operation of battery packs.

[0003] Traditional battery cooling solutions often employ a parallel harmonica tube flow channel design to achieve coolant flow and heat exchange. However, this traditional design has significant drawbacks. Firstly, because all the parallel harmonica tubes receive coolant from the same side, the coolant exits from the other side after sufficient heat exchange within the module, resulting in a large temperature difference between the inlet and outlet sides. Secondly, in the parallel harmonica tubes, the farther the tube is from the inlet, the longer the coolant travels, leading to increased flow resistance and reduced flow rate. This reduced flow rate directly degrades the cooling effect, further exacerbating the differences in cooling performance between the individual harmonica tubes.

[0004] Therefore, a new technical solution is needed in this field to solve the above problems. Utility Model Content

[0005] The present invention aims to solve the above-mentioned technical problems, namely, to solve the problems of large temperature difference between the liquid inlet and outlet sides and poor temperature uniformity of existing battery cooling components.

[0006] In a first aspect, the present invention provides a cooling assembly. The cooling assembly includes: a heat exchange tube group and a first manifold, wherein the heat exchange tube group includes a plurality of heat exchange tubes; the first manifold has a first flow channel and a second flow channel that are not interconnected, the first flow channel having a water inlet and a first connecting port corresponding to one end of the plurality of heat exchange tubes, and the second flow channel having a drain outlet and a second connecting port corresponding to the other end of the plurality of heat exchange tubes.

[0007] In the preferred embodiment of the above-mentioned cooling assembly, the first manifold has a tubular structure and is sealed at both ends. A horizontal baffle is provided in the first manifold, and the horizontal baffle divides the space inside the first manifold to form the first flow channel and the second flow channel distributed vertically.

[0008] In the preferred embodiment of the cooling assembly described above, the first baffle is horizontally arranged in the first manifold.

[0009] In the preferred embodiment of the cooling assembly described above, the first partition divides the space in the first manifold into equal volumes, so that the volumes of the first flow channel and the second flow channel are equal.

[0010] In the preferred embodiment of the cooling assembly described above, both the first and second connecting ports are located on one side of the first manifold, and both the water inlet and the drain outlet are located on the other side of the first manifold opposite to the first connecting port.

[0011] In the preferred embodiment of the cooling assembly described above, a first cavity and a second cavity are sequentially provided in the first manifold along the length of the first manifold, near the water inlet. The first cavity is connected to the water inlet and the first flow channel, respectively, and the second cavity is connected to the drain outlet and the second flow channel, respectively.

[0012] In the preferred embodiment of the cooling assembly described above, a second baffle is provided in the first manifold, and the second baffle separates the first flow channel and the second flow channel from the first cavity and the second cavity.

[0013] In the preferred embodiment of the cooling assembly described above, two through holes are spaced apart on the second partition plate. The first flow channel communicates with the first cavity through one of the through holes, and the second flow channel communicates with the second cavity through the other through hole.

[0014] In the preferred embodiment of the cooling assembly described above, the second baffle is vertically arranged in the first manifold.

[0015] In the preferred embodiment of the cooling assembly described above, a third partition is further provided in the first manifold, and the first cavity and the second cavity are separated by the third partition.

[0016] In the preferred embodiment of the cooling assembly described above, the third baffle is vertically disposed in the first manifold.

[0017] In the preferred embodiment of the cooling assembly described above, the third partition separates the first cavity and the second cavity into equal volumes.

[0018] In the preferred embodiment of the above-mentioned cooling assembly, the water inlet and the drain outlet are located at the same height position of the first manifold, and / or the water inlet and the drain outlet have the same diameter.

[0019] In the preferred embodiment of the above-mentioned cooling assembly, the first manifold is a square tube.

[0020] In the preferred embodiment of the above-mentioned cooling assembly, each heat exchange tube includes two tube sections arranged along the length of the first manifold, one of which is connected to the first communication port and the other is connected to the second communication port, and the coolant in adjacent tube sections flows in opposite directions.

[0021] In the preferred embodiment of the cooling assembly described above, the heat exchange tube is a U-shaped tube, and the heat exchange tube further includes a bend, with the ends of the two tube bodies away from the first manifold respectively connected to the two ends of the bend.

[0022] In the preferred embodiment of the cooling assembly described above, multiple heat exchange tubes are nested together.

[0023] In the preferred embodiment of the above-mentioned cooling assembly, multiple sets of heat exchange tubes are provided, and the multiple sets of heat exchange tubes are arranged sequentially along the length direction of the first manifold. The coolant flows in opposite directions in the two outermost tube sections of two adjacent sets of heat exchange tubes that are close to each other.

[0024] In the preferred embodiment of the cooling assembly described above, the cooling assembly further includes a second manifold, which is spaced apart from the first manifold. The second manifold has a return cavity, and the ends of the two pipe sections away from the first manifold are connected to the return cavity.

[0025] In the preferred embodiment of the cooling assembly described above, a plurality of reflux chambers are arranged sequentially along the length of the second manifold, and the plurality of reflux chambers correspond one-to-one with the plurality of heat exchange tubes.

[0026] In the preferred embodiment of the above-mentioned cooling assembly, at least a portion of the tube body is provided with a bent pipe joint at its end.

[0027] In the preferred embodiment of the cooling assembly described above, a support plate is provided at intervals in the heat exchange tube, and the support plate divides the space inside the heat exchange tube into multiple channels.

[0028] In a second aspect, the present invention also provides a battery pack, the battery pack including a housing, a battery module and a cooling component as described in any one of the above, wherein the battery module and the cooling component are both installed in the housing.

[0029] In the preferred embodiment of the above-mentioned battery pack, the housing is provided with a first through hole and a second through hole spaced apart from each other. A sealing block is provided in both the first through hole and the second through hole. A water inlet connector and a water outlet connector are respectively provided in the two sealing blocks. The water inlet connector is connected to the water inlet, and the water outlet connector is connected to the drain outlet.

[0030] In the preferred embodiment of the above battery pack, a first groove is provided in both the first through hole and the second through hole, and a first rib adapted to the corresponding first groove is provided on the surface of each sealing block.

[0031] In the preferred embodiment of the above-mentioned battery pack, a third through hole is provided on both of the sealing blocks, and the water inlet connector and the water outlet connector are respectively inserted through the corresponding third through hole. A second rib is provided on the wall of each third through hole, and a second groove adapted to the second rib is provided on the surface of the water inlet connector and the water outlet connector respectively.

[0032] In the preferred embodiment of the above-mentioned battery pack, at the end of each of the third through holes, the surface of the sealing block protrudes outward to form a third rib, the third rib surrounds the third through hole, and a fourth rib corresponding to the third rib is respectively provided on the surface of the water inlet connector and the water outlet connector, the third rib being able to abut against the fourth rib.

[0033] In the preferred embodiment of the above battery pack, the housing is provided with an installation groove, and a plurality of heat exchange tubes are installed in the installation groove.

[0034] In the preferred embodiment of the above battery pack, the width of the battery module is greater than the width of the mounting slot.

[0035] In the preferred embodiment of the above battery pack, the depth of the mounting groove is greater than the height of the heat exchange tube.

[0036] In a third aspect, the present invention also provides an energy storage device, the energy storage device including the aforementioned battery pack, and the battery pack being provided in multiple portions.

[0037] Those skilled in the art will understand that this utility model provides a cooling assembly, which includes a heat exchange tube group and a first manifold. The heat exchange tube group includes multiple heat exchange tubes; the first manifold has a first flow channel and a second flow channel that are not interconnected. The first flow channel has a water inlet and a first connecting port that corresponds to one end of each of the multiple heat exchange tubes. The second flow channel has a drain outlet and a second connecting port that corresponds to the other end of each of the multiple heat exchange tubes. This technical solution effectively reduces the temperature difference of the battery module and improves the temperature uniformity of the battery module. Specifically, by designing independent flow channels within the first manifold, the problem of uneven flow distribution due to resistance differences in parallel pipelines and large temperature differences between the inlet and outlet sides of the parallel pipelines is eliminated, ensuring consistent flow rates for each heat exchange tube. Furthermore, by setting non-interconnected first and second flow channels within a single manifold, the directional distribution and recovery of coolant are achieved respectively. This design simplifies the pipeline connection structure, reduces system complexity, and the compact design results in a smaller space occupied by the cooling assembly, thereby improving space utilization. Attached Figure Description

[0038] The preferred embodiments of this utility model are described below with reference to the accompanying drawings, in which:

[0039] Figure 1 This is a schematic diagram of the cooling component of this utility model. Figure 1 ;

[0040] Figure 2 This is a schematic diagram of the cooling component of this utility model. Figure 2 ;

[0041] Figure 3 This is a schematic diagram of the heat exchange tube of this utility model;

[0042] Figure 4 This is a schematic diagram of the structure of the first manifold of this utility model. Figure 1 ;

[0043] Figure 5 This is a schematic diagram of the structure of the first manifold of this utility model. Figure 2 ;

[0044] Figure 6 This is a cross-section of the first manifold of this utility model. Figure 1 ;

[0045] Figure 7 This is a schematic diagram of the heat exchange tube of this utility model;

[0046] Figure 8 This is a cross-sectional view of the heat exchange tube of this utility model;

[0047] Figure 9 This is a schematic diagram of the cooling component of this utility model. Figure 3 ;

[0048] Figure 10 This is a schematic diagram of the structure of the second manifold of this utility model;

[0049] Figure 11 This is a schematic diagram of the structure of the first manifold of this utility model. Figure 3 ;

[0050] Figure 12 This is a cross-section of the first manifold of this utility model. Figure 2 ;

[0051] Figure 13 This is an installation structure diagram of the cooling component of this utility model;

[0052] Figure 14 This is a schematic diagram of the sealing block of this utility model. Figure 1 ;

[0053] Figure 15 This is a schematic diagram of the sealing block of this utility model. Figure 2 ;

[0054] Figure 16 yes Figure 13 A magnified view of a section at point A in the middle;

[0055] Figure 17 yes Figure 1 A magnified view of a section at point B in the middle;

[0056] Figure 18 This is a cross-sectional view of the sealing block of this utility model;

[0057] Figure 19 This is a schematic diagram of the installation groove and heat exchange tube of this utility model.

[0058] List of reference numerals in the attached diagram:

[0059] 100. Battery module;

[0060] 1. Heat exchanger tube assembly; 11. Heat exchanger tube; 111. Tube body; 112. Bend section; 113. Bend joint; 114. Support plate;

[0061] 2. First manifold; 21. First flow channel; 211. Water inlet; 212. First connecting port; 22. Second flow channel; 221. Drain outlet; 222. Second connecting port; 23. First partition; 24. First cavity; 25. Second cavity; 26. Second partition; 27. Third partition;

[0062] 3. Second manifold; 31. Return chamber; 32. Fourth baffle;

[0063] 4. Housing; 41. First through hole; 42. Second through hole; 43. First groove; 44. Mounting groove;

[0064] 5. Sealing block; 51. Third through hole; 52. First rib; 53. Second rib; 54. Third rib;

[0065] 6. Water inlet connector; 61. Second groove; 62. Fourth rib;

[0066] 7. Water outlet connector. Detailed Implementation

[0067] Preferred embodiments of the present invention will now be described with reference to the accompanying drawings. Those skilled in the art should understand that these embodiments are merely illustrative of the technical principles of the present invention and are not intended to limit the scope of protection of the present invention. For example, although the following embodiments are described in conjunction with a battery pack, the cooling assembly provided by the present invention is equally applicable to other products that need to solve the problem of poor cooling performance.

[0068] It should be noted that, in the description of this utility model, unless otherwise explicitly specified and limited, the terms "set" and "connection" should be interpreted broadly, for example, they can refer to a fixed connection, a detachable connection, or an integral connection. Those skilled in the art can understand the specific meaning of the above terms in this utility model according to the specific circumstances.

[0069] Based on the problems of large temperature difference and poor temperature uniformity between the inlet and outlet liquid sides of existing battery cooling components pointed out in the background art, this utility model provides a cooling component that aims to effectively solve the problems of large temperature difference and poor temperature uniformity between the inlet and outlet liquid sides of battery cooling components by optimizing the structure of the heat exchange tube and the manifold.

[0070] Example 1

[0071] like Figures 1 to 6 As shown, this embodiment provides a cooling assembly, which includes a heat exchange tube group 1 and a first manifold 2. The heat exchange tube group 1 includes multiple heat exchange tubes 11; the first manifold 2 has a first flow channel 21 and a second flow channel 22 that are not interconnected. The first flow channel 21 has a water inlet 211 and a first connecting port 212 that corresponds to one end of each of the multiple heat exchange tubes 11. The second flow channel 22 has a drain outlet 221 and a second connecting port 222 that corresponds to the other end of each of the multiple heat exchange tubes 11.

[0072] The heat exchange tube assembly 1 consists of multiple heat exchange tubes 11. The heat exchange tubes 11 are key components in the cooling assembly for achieving heat exchange. The coolant flows inside the heat exchange tubes 11 and exchanges heat with the outside environment, thereby cooling the battery.

[0073] The first manifold 2 is internally designed with a first flow channel 21 and a second flow channel 22 that are not interconnected. The first flow channel 21 is provided with a water inlet 211 for injecting coolant into the first flow channel 21. The first flow channel 21 is also provided with a first connecting port 212 that corresponds to one end of each of the multiple heat exchange tubes 11, ensuring that the coolant can be smoothly distributed to each heat exchange tube 11. The second flow channel 22 is provided with a drain port 221 for discharging the coolant that has absorbed heat from the first manifold 2. The second flow channel 22 is also provided with a second connecting port 222 that corresponds to the other end of each of the multiple heat exchange tubes 11, so that the coolant flowing out of the heat exchange tubes 11 can be collected and discharged.

[0074] The cooling assembly provided in this embodiment, through the independent design of the first flow channel 21 and the second flow channel 22 in the first manifold 2, allows the coolant to be distributed relatively evenly into each heat exchange tube 11 when entering the heat exchange tube group 1, and to be collected relatively centrally when flowing out, thus avoiding excessive local temperature differences caused by uneven flow of the coolant on the inlet and outlet sides. After the coolant has flowed and exchanged heat sufficiently in the heat exchange tubes 11, its temperature is relatively uniform when discharged from the drain port 221, effectively reducing the temperature difference between the inlet and outlet sides.

[0075] Furthermore, multiple heat exchange tubes 11 are connected to the first flow channel 21 and the second flow channel 22 of the first manifold 2, respectively, allowing the coolant to flow relatively evenly in each heat exchange tube 11 and exchange heat with the battery. This design ensures that all parts of the battery receive a relatively consistent cooling effect, improves the temperature uniformity of battery cooling, helps the battery operate in a more stable temperature environment, extends battery life, and improves the overall performance of the battery.

[0076] Furthermore, by using a single manifold (first manifold 2), system complexity can be reduced and space utilization improved. Compared to traditional solutions, this invention significantly enhances system compactness and ease of maintenance while ensuring heat dissipation performance.

[0077] Preferably, such as Figure 5 and 6 As shown, the first manifold 2 has a tubular structure and is sealed at both ends. A first baffle 23 is provided in the first manifold 2. The first baffle 23 divides the space inside the first manifold 2 to form a first flow channel 21 and a second flow channel 22 distributed vertically.

[0078] The first manifold 2 is designed as a tubular structure, which is easy to process and shape, and has good mechanical strength and stability, and can withstand the pressure inside the cooling system and the influence of the external environment.

[0079] A first baffle 23 is provided in the first manifold 2, dividing the space within the first manifold 2 into two independent regions distributed vertically, forming a first flow channel 21 and a second flow channel 22 respectively. This design allows the coolant to flow independently in the first flow channel 21 and the second flow channel 22 without interference, ensuring the orderly operation of the cooling system and avoiding energy loss and reduced cooling efficiency caused by the mixing of hot and cold liquids. Furthermore, it makes the cooling component structure more compact, reducing the space occupied by the system inside the battery pack, which is beneficial for improving the energy density and space utilization of the battery pack.

[0080] Preferably, such as Figure 6 As shown, the first partition 23 is horizontally arranged in the first manifold 2.

[0081] The horizontally arranged first baffle 23 makes the flow direction of the coolant in the first flow channel 21 and the second flow channel 22 more stable. After entering the first flow channel 21, the coolant can flow to each heat exchange tube 11 in a relatively stable state due to the horizontal arrangement of the first baffle 23, avoiding complex eddies and turbulence in the flow channel caused by the inclined or vertical arrangement of the baffle.

[0082] Preferably, the first partition 23 divides the space in the first manifold 2 into equal volumes so that the volumes of the first flow channel 21 and the second flow channel 22 are equal.

[0083] When the volumes of the first flow channel 21 and the second flow channel 22 are equal, during normal operation of the cooling system, if the injection and discharge rates of the coolant remain relatively stable, the amount of coolant entering the first flow channel 21 and the amount of coolant discharged from the second flow channel 22 are more likely to reach a dynamic balance. This balance helps reduce coolant flow fluctuations caused by differences in flow channel volumes, making the distribution of coolant in each heat exchange tube 11 more uniform, thereby ensuring the stability and consistency of the overall cooling effect of the cooling assembly.

[0084] Preferably, such as Figure 5 and Figure 11 As shown, the first connecting port 212 and the second connecting port 222 are both located on one side of the first manifold 2, and the water inlet 211 and the drain outlet 221 are both located on the other side of the first manifold 2 opposite to the first connecting port 212.

[0085] With this structural design, after the coolant enters the first flow channel 21 through the inlet 211, it can flow along a relatively straight path inside the first manifold 2 to the first connecting port 212, enter the heat exchange tube 11 for heat exchange, then flow out through the second connecting port 222 into the second flow channel 22, and finally be discharged from the drain port 221. This relatively straight and clear flow path reduces the turning and tortuous movement of the coolant within the flow channel, lowers flow resistance, allows the coolant to flow more smoothly, and improves the circulation efficiency of the coolant.

[0086] Preferably, such as Figure 3 As shown, each heat exchange tube 11 includes two tube sections 111 arranged along the length of the first manifold 2. One tube section 111 is connected to the first communication port 212, and the other tube section 111 is connected to the second communication port 222. The coolant flows in opposite directions in the two adjacent tube sections 111.

[0087] Because the coolant flows in opposite directions, the temperature distribution of the coolant within the heat exchange tube 11 is more uniform. The different flow directions of the coolant allow for better coverage of different parts of the battery, preventing localized overheating or underheating, improving the uniformity of battery cooling, and helping the battery operate in a more stable temperature environment, thus extending its lifespan.

[0088] Furthermore, this reverse flow design fully utilizes the flow characteristics of the coolant, allowing it to form a more rational flow pattern within the heat exchanger tube assembly 1. The reverse flow of coolant between adjacent tube sections 111 creates a pressure gradient, promoting uniform distribution of coolant throughout the entire heat exchanger tube assembly 1, reducing dead zones, and improving coolant utilization.

[0089] Preferably, such as Figures 1 to 3 As shown, the heat exchange tube 11 is a U-shaped tube, and the heat exchange tube 11 also includes a bent tube section 112. The ends of the two tube sections 111 that are away from the first manifold 2 are respectively connected to the two ends of the bent tube section 112.

[0090] The U-shaped tube design allows for a more efficient arrangement of the heat exchange tubes 11 within a limited space. Compared to straight heat exchange tubes 11, the U-shaped tube increases the flow path length of the coolant within the heat exchange tubes 11 without significantly increasing space usage, thereby achieving better cooling performance within the limited space of the battery cooling system and improving space utilization.

[0091] In addition, the U-shaped tube design allows the coolant to be distributed more evenly within the heat exchange tube 11. Due to the connection of the bend 112, the coolant can flow more smoothly between the two tube sections 111, so that all parts of the battery can receive a more consistent cooling effect, further improving the temperature uniformity of battery cooling and helping to improve the overall performance and lifespan of the battery.

[0092] Preferably, such as Figure 1 and Figure 2 As shown, multiple heat exchange tubes 11 are nested together.

[0093] The nested arrangement of multiple heat exchange tubes 11 makes full use of limited space, allowing more heat exchange tubes 11 to be arranged in the same space, increasing the contact area between the coolant and the battery. This enables the cooling assembly to achieve efficient cooling in a more compact space, contributing to improved integration of the entire battery system.

[0094] Preferably, such as Figure 1 and Figure 2 As shown, multiple sets of heat exchange tube groups 1 are provided. The multiple sets of heat exchange tube groups 1 are arranged sequentially along the length direction of the first manifold 2. The coolant flows in opposite directions in the two outermost tube sections 111 of two adjacent sets of heat exchange tube groups 1.

[0095] The arrangement of multiple heat exchange tube groups 1 along the length of the first manifold 2 can significantly increase the contact area between the cooling components and the battery pack, allowing more of the outer walls of the heat exchange tubes 11 to participate in the heat exchange process, thus effectively improving heat dissipation efficiency.

[0096] Furthermore, the sequential arrangement of the heat exchanger tube group 1 along the length of the first manifold 2 ensures more uniform heat dissipation across the battery pack. This avoids excessive heat dissipation in some areas due to overly dense heat exchanger tubes 11, while other areas experience insufficient heat dissipation, thus guaranteeing a uniform temperature distribution across the battery pack.

[0097] It should be noted that the multiple heat exchange tube groups 1 are arranged sequentially along the length of the first manifold 2. They can be arranged either with adjacent heat exchange tube groups 1 abutting each other or with adjacent heat exchange tube groups 1 spaced apart. This utility model does not limit the specific way in which the multiple heat exchange tube groups 1 are arranged sequentially along the length of the first manifold 2.

[0098] Because the coolant flows in opposite directions in the outermost sections 111 of adjacent heat exchange tube groups 1, the temperature distribution of the coolant between adjacent heat exchange tube groups 1 is more uniform. The coolant flowing in different directions can better cover different parts of the battery, avoiding local overheating or underheating, thereby improving the uniformity of battery cooling.

[0099] Preferably, such as Figure 8 As shown, a support plate 114 is provided at intervals in the heat exchange tube 11, and the support plate 114 divides the space inside the heat exchange tube 11 into multiple channels.

[0100] In this embodiment, a multi-channel structure is formed by spaced support plates 114 in the heat exchange tubes 11. This generates local turbulence in the coolant during flow, disrupting the boundary layer and improving the convective heat transfer coefficient. Furthermore, the surface of the support plates 114 is in direct contact with the coolant, increasing the heat exchange area. Compared to single-channel tubes, the multi-channel design significantly improves heat exchange efficiency. Moreover, the support plates 114 can form longitudinal reinforcing ribs, significantly improving the bending stiffness of the heat exchange tubes 11 and reducing their deformation.

[0101] It should be noted that the heat exchange tube 11 in this embodiment is made of a high thermal conductivity metal material (such as aluminum alloy or copper alloy) to ensure that heat can be quickly transferred from the battery pack to the internal coolant. In addition, the outer diameter of the heat exchange tube 11 can be designed according to the spatial layout and cooling requirements of the battery pack, and the wall thickness must meet the pressure requirements. This embodiment does not specifically limit the outer diameter of the heat exchange tube 11.

[0102] Preferably, such as Figure 7 As shown, at least a portion of the pipe body 111 has a bent pipe joint 113 at its end.

[0103] The bend joint 113 allows for precise adjustment of the direction and angle of the tube body 111, ensuring that the tube body 111 ultimately lies on the same horizontal plane. The flatness of multiple tube bodies 111 ensures a more uniform flow of the cooling medium within each heat exchange tube 11. The contact area and contact conditions between each heat exchange tube 11 and the external environment or the object to be cooled are essentially consistent, avoiding localized differences in heat exchange efficiency caused by unevenness in the heat exchange tubes 11, thereby improving the heat exchange uniformity of the entire cooling assembly.

[0104] For example, such as Figure 1 As shown, in this embodiment, one end of the heat exchange tube 11 body 111 is provided with a bend joint 113, while the end of the other end of the heat exchange tube 111 is not provided with a bend joint 113, thereby satisfying the connection requirements between the tube body 111 and the first manifold 2 in this embodiment.

[0105] It should be noted that in other embodiments, bent pipe joints 113 may also be provided at the ends of both tube sections 111 of the heat exchange tube 11. Such adjustments and changes in the specific number of bent pipe joints 113 do not deviate from the principle and scope of this utility model, and should be limited to the protection scope of this utility model.

[0106] Example 2

[0107] like Figures 1 to 6 As shown, this embodiment provides a cooling assembly, which includes a heat exchange tube group 1 and a first manifold 2. The heat exchange tube group 1 includes multiple heat exchange tubes 11; the first manifold 2 has a first flow channel 21 and a second flow channel 22 that are not interconnected. The first flow channel 21 has a water inlet 211 and a first connecting port 212 that corresponds to one end of each of the multiple heat exchange tubes 11. The second flow channel 22 has a drain outlet 221 and a second connecting port 222 that corresponds to the other end of each of the multiple heat exchange tubes 11.

[0108] The heat exchange tube assembly 1 consists of multiple heat exchange tubes 11. The heat exchange tubes 11 are key components in the cooling assembly for achieving heat exchange. The coolant flows inside the heat exchange tubes 11 and exchanges heat with the outside environment, thereby cooling the battery.

[0109] The first manifold 2 is internally designed with a first flow channel 21 and a second flow channel 22 that are not interconnected. The first flow channel 21 is provided with a water inlet 211 for injecting coolant into the first flow channel 21. The first flow channel 21 is also provided with a first connecting port 212 that corresponds to one end of each of the multiple heat exchange tubes 11, ensuring that the coolant can be smoothly distributed to each heat exchange tube 11. The second flow channel 22 is provided with a drain port 221 for discharging the coolant that has absorbed heat from the first manifold 2. The second flow channel 22 is also provided with a second connecting port 222 that corresponds to the other end of each of the multiple heat exchange tubes 11, so that the coolant flowing out of the heat exchange tubes 11 can be collected and discharged.

[0110] The cooling assembly provided in this embodiment, through the independent design of the first flow channel 21 and the second flow channel 22 in the first manifold 2, allows the coolant to be distributed relatively evenly into each heat exchange tube 11 when entering the heat exchange tube group 1, and to be collected relatively centrally when flowing out, thus avoiding excessive local temperature differences caused by uneven flow of the coolant on the inlet and outlet sides. After the coolant has flowed and exchanged heat sufficiently in the heat exchange tubes 11, its temperature is relatively uniform when discharged from the drain port 221, effectively reducing the temperature difference between the inlet and outlet sides.

[0111] Furthermore, multiple heat exchange tubes 11 are connected to the first flow channel 21 and the second flow channel 22 of the first manifold 2, respectively, allowing the coolant to flow relatively evenly in each heat exchange tube 11 and exchange heat with the battery. This design ensures that all parts of the battery receive a relatively consistent cooling effect, improves the temperature uniformity of battery cooling, helps the battery operate in a more stable temperature environment, extends battery life, and improves the overall performance of the battery.

[0112] Furthermore, by using a single manifold (first manifold 2), system complexity can be reduced and space utilization improved. Compared to traditional solutions, this invention significantly enhances system compactness and ease of maintenance while ensuring heat dissipation performance.

[0113] Preferably, such as Figure 6 As shown, the first manifold 2 has a tubular structure and is sealed at both ends. A first baffle 23 is provided in the first manifold 2. The first baffle 23 divides the space inside the first manifold 2 to form a first flow channel 21 and a second flow channel 22 distributed vertically.

[0114] The first manifold 2 is designed as a tubular structure, which is easy to process and shape, and has good mechanical strength and stability, and can withstand the pressure inside the cooling system and the influence of the external environment.

[0115] A first baffle 23 is provided in the first manifold 2, dividing the space within the first manifold 2 into two independent regions distributed vertically, forming a first flow channel 21 and a second flow channel 22 respectively. This design allows the coolant to flow independently in the first flow channel 21 and the second flow channel 22 without interference, ensuring the orderly operation of the cooling system and avoiding energy loss and reduced cooling efficiency caused by the mixing of hot and cold liquids. Furthermore, it makes the cooling component structure more compact, reducing the space occupied by the system inside the battery pack, which is beneficial for improving the energy density and space utilization of the battery pack.

[0116] Preferably, such as Figure 6 As shown, the first partition 23 is horizontally arranged in the first manifold 2.

[0117] The horizontally arranged first baffle 23 makes the flow direction of the coolant in the first flow channel 21 and the second flow channel 22 more stable. After entering the first flow channel 21, the coolant can flow to each heat exchange tube 11 in a relatively stable state due to the horizontal arrangement of the first baffle 23, avoiding complex eddies and turbulence in the flow channel caused by the inclined or vertical arrangement of the baffle.

[0118] Preferably, the first partition 23 divides the space in the first manifold 2 into equal volumes so that the volumes of the first flow channel 21 and the second flow channel 22 are equal.

[0119] When the volumes of the first flow channel 21 and the second flow channel 22 are equal, during normal operation of the cooling system, if the injection and discharge rates of the coolant remain relatively stable, the amount of coolant entering the first flow channel 21 and the amount of coolant discharged from the second flow channel 22 are more likely to reach a dynamic balance. This balance helps reduce coolant flow fluctuations caused by differences in flow channel volumes, making the distribution of coolant in each heat exchange tube 11 more uniform, thereby ensuring the stability and consistency of the overall cooling effect of the cooling assembly.

[0120] Preferably, such as Figure 5 and Figure 11 As shown, the first connecting port 212 and the second connecting port 222 are both located on one side of the first manifold 2, and the water inlet 211 and the drain outlet 221 are both located on the other side of the first manifold 2 opposite to the first connecting port 212.

[0121] With this structural design, after the coolant enters the first flow channel 21 through the inlet 211, it can flow along a relatively straight path inside the first manifold 2 to the first connecting port 212, enter the heat exchange tube 11 for heat exchange, then flow out through the second connecting port 222 into the second flow channel 22, and finally be discharged from the drain port 221. This relatively straight and clear flow path reduces the turning and tortuous movement of the coolant within the flow channel, lowers flow resistance, allows the coolant to flow more smoothly, and improves the circulation efficiency of the coolant.

[0122] Preferably, such as Figure 9 As shown, each heat exchange tube 11 includes two tube sections 111 arranged along the length of the first manifold 2. One tube section 111 is connected to the first communication port 212, and the other tube section 111 is connected to the second communication port 222. The coolant flows in opposite directions in the two adjacent tube sections 111.

[0123] Because the coolant flows in opposite directions, the temperature distribution of the coolant within the heat exchange tube 11 is more uniform. The different flow directions of the coolant allow for better coverage of different parts of the battery, preventing localized overheating or underheating, improving the uniformity of battery cooling, and helping the battery operate in a more stable temperature environment, thus extending its lifespan.

[0124] Furthermore, this reverse flow design fully utilizes the flow characteristics of the coolant, allowing for a more rational flow pattern within the heat exchanger tube assembly 1. The reverse flow of coolant between adjacent tube sections 111 creates a pressure gradient, promoting uniform distribution of the coolant throughout the entire heat exchanger tube assembly 1, reducing dead zones, and improving coolant utilization. Preferably, as... Figure 8 and Figure 9 As shown, the cooling assembly also includes a second manifold 3, which is spaced apart from the first manifold 2. The second manifold 3 has a return cavity 31, and the ends of the two tube sections 111 that are away from the first manifold 2 are connected to the return cavity 31.

[0125] like Figure 9 As shown, in this embodiment, a second manifold 3 is added on the basis of the existing first manifold 2 and heat exchange tube group 1, and the second manifold 3 is arranged at intervals with the first manifold 2, forming a relatively independent yet mutually cooperating coolant circulation structure.

[0126] The arrangement of the second manifold 3 creates a reasonable and orderly flow path for the coolant between the heat exchange tube 11 and the manifold. The coolant enters the heat exchange tube 11 from the first manifold 2, and after sufficient heat exchange within the heat exchange tube 11, it can smoothly flow into the return chamber 31 of the second manifold 3, avoiding disorderly flow and accumulation of coolant within the system and improving the efficiency of coolant circulation.

[0127] Furthermore, the return chamber 31 of the second manifold 3 can play a certain role in buffering and stabilizing the flow of coolant. During the coolant circulation process, the return chamber 31 can balance the flow rate and pressure of coolant in different heat exchange tubes 11, reduce the impact of uneven flow rate or pressure fluctuations on the cooling effect and battery system, and enhance the stability and reliability of the cooling system.

[0128] Preferably, such as Figure 10 As shown, multiple reflux chambers 31 are arranged sequentially along the length of the second manifold 3, and each of the multiple reflux chambers 31 corresponds to a multiple heat exchange tube 11.

[0129] Each heat exchange tube 11 corresponds to an independent return chamber 31, making the flow of coolant in each heat exchange tube 11 relatively independent and without interference. This avoids problems such as uneven flow and pressure fluctuations caused by mutual influence of coolant flow in different heat exchange tubes 11, ensuring that each heat exchange tube 11 can circulate coolant according to the designed flow rate and pressure, thereby improving the consistency and stability of the cooling effect.

[0130] Preferably, such as Figure 10 As shown, along the length of the second manifold 3, a plurality of fourth baffles 32 are provided at intervals in the second manifold 3, and the fourth baffles 32 divide the space in the second manifold 3 to form a plurality of return cavities 31.

[0131] By setting the fourth baffle 32, the internal space of the second manifold 3 can be precisely divided into multiple independent return chambers 31, ensuring that each return chamber 31 can form good communication and isolation with the corresponding heat exchange tube 11, ensuring the independent flow of coolant between each heat exchange tube 11 and the corresponding return chamber 31, avoiding the mixing and interference of coolant in different heat exchange tubes 11, and improving the operating accuracy and stability of the cooling system.

[0132] Preferably, such as Figure 10 As shown, the fourth partition 32 is vertically installed in the second manifold 3.

[0133] The vertical arrangement of the fourth baffle 32 makes full use of the internal space of the second manifold 3. While ensuring the formation of an independent return cavity 31, this arrangement reduces the additional space occupied by the baffle, allowing for a more rational layout of the cooling components within a limited space.

[0134] Furthermore, the vertically arranged fourth baffle 32 provides structural support for the second manifold 3. During the operation of the cooling assembly, the fourth baffle 32 can enhance the overall strength of the second manifold 3, reduce the risk of deformation or damage to the second manifold 3 caused by factors such as coolant flow or external vibration, and improve the reliability and service life of the cooling assembly.

[0135] Preferably, such as Figure 8 As shown, a support plate 114 is provided at intervals in the heat exchange tube 11, and the support plate 114 divides the space inside the heat exchange tube 11 into multiple channels.

[0136] In this embodiment, a multi-channel structure is formed by spaced support plates 114 in the heat exchange tubes 11. This generates local turbulence in the coolant during flow, disrupting the boundary layer and improving the convective heat transfer coefficient. Furthermore, the surface of the support plates 114 is in direct contact with the coolant, increasing the heat exchange area. Compared to single-channel tubes, the multi-channel design significantly improves heat exchange efficiency. Moreover, the support plates 114 can form longitudinal reinforcing ribs, significantly improving the bending stiffness of the heat exchange tubes 11 and reducing their deformation.

[0137] It should be noted that the heat exchange tube 11 in this embodiment is made of a high thermal conductivity metal material (such as aluminum alloy or copper alloy) to ensure that heat can be quickly transferred from the battery pack to the internal coolant. In addition, the outer diameter of the heat exchange tube 11 can be designed according to the spatial layout and cooling requirements of the battery pack, and the wall thickness must meet the pressure requirements. This embodiment does not specifically limit the outer diameter of the heat exchange tube 11.

[0138] Preferably, such as Figure 7 As shown, at least a portion of the pipe body 111 has a bent pipe joint 113 at its end.

[0139] The bend joint 113 allows for precise adjustment of the direction and angle of the tube body 111, ensuring that the tube body 111 ultimately lies on the same horizontal plane. The flatness of multiple tube bodies 111 ensures a more uniform flow of the cooling medium within each heat exchange tube 11. The contact area and contact conditions between each heat exchange tube 11 and the external environment or the object to be cooled are essentially consistent, avoiding localized differences in heat exchange efficiency caused by unevenness in the heat exchange tubes 11, thereby improving the heat exchange uniformity of the entire cooling assembly.

[0140] For example, such as Figure 9 As shown, in this embodiment, one end of each of the two pipe sections 111 is provided with a bend joint 113, while the other end is not provided with a bend joint 113. Furthermore, the bend joints 113 on the two pipe sections 111 are on different sides to meet the connection requirements of the two ends of the pipe section 111 in this embodiment to the first manifold 2 and the second manifold 3, respectively.

[0141] It should be noted that in other embodiments, the bend joints 113 on the two pipe sections 111 can be located on the same side to accommodate different connection requirements. Furthermore, bend sections 113 can be provided at both ends of the two pipe sections 111. Such adjustments and changes to the specific location and number of bend joints 113 do not deviate from the principles and scope of this utility model and should be limited to the protection scope of this utility model.

[0142] Example 3

[0143] The only difference between this embodiment and Embodiment 1 is that the structure of the first manifold 2 in this embodiment is different from that in Embodiment 1. The first manifold 2 in this embodiment is an improvement on the first manifold 2 in Embodiment 1.

[0144] Preferably, such as Figure 11 and Figure 12 As shown, in this embodiment, based on the first manifold 2 of embodiment one, a first cavity 24 and a second cavity 25 are sequentially opened in the first manifold 2 along the length direction of the first manifold 2 near the water inlet 211. The first cavity 24 is connected to the water inlet 211 and the first flow channel 21 respectively, and the second cavity 25 is connected to the drain outlet 221 and the second flow channel 22 respectively.

[0145] By setting up the first cavity 24 and the second cavity 25, the flow path of the coolant within the first manifold 2 is made clearer and more orderly. After entering through the inlet 211, the coolant undergoes initial buffering and distribution within the first cavity 24, and then flows smoothly into the first flow channel 21. After completing heat exchange, it flows into the second cavity 25 through the second flow channel 22, and then exits through the drain outlet 221. This avoids disordered flow or localized accumulation of coolant within the first manifold 2, thus improving the efficiency of coolant circulation.

[0146] Preferably, such as Figure 12 As shown, a second baffle 26 is provided in the first manifold 2, which separates the first flow channel 21 and the second flow channel 22 from the first cavity 24 and the second cavity 25.

[0147] The second baffle 26 clearly defines the flow paths of the coolant in different areas. After entering the first cavity 24 through the inlet 211, the coolant can only flow and exchange heat in the first flow channel 21. After heat exchange, the coolant enters the second flow channel 22, then flows into the second cavity 25 and is discharged from the drain outlet 221. This clear zoning avoids random mixing and turbulence of the coolant between different flow channels and cavities, ensuring that the coolant flows orderly along the designed path, thus improving the operating efficiency and stability of the cooling system.

[0148] Preferably, such as Figure 12 As shown, the second partition 26 is vertically disposed in the first manifold 2.

[0149] The vertically arranged second baffle 26 occupies a relatively regular space within the first manifold 2, which can make full use of the internal space of the first manifold 2. While ensuring the separation function, it reduces the space occupied by other components and coolant flow space, which helps to improve the space utilization of the entire cooling assembly and enable the cooling assembly to achieve a more reasonable layout in a limited space.

[0150] For example, two through holes (not shown in the figure) are provided on the second partition 26 at intervals. The first flow channel 21 is connected to the first cavity 24 through one of the through holes, and the second flow channel 22 is connected to the second cavity 25 through the other through hole.

[0151] Preferably, such as Figure 11 As shown, a third partition 27 is also provided in the first manifold 2, and the first cavity 24 and the second cavity 25 are separated by the third partition 27.

[0152] By setting a third baffle 27, the coolant can flow in two independent channels (first cavity 24 and second cavity 25). This split-flow design can introduce coolants of different temperatures, flow rates, or characteristics into the two cavities according to actual cooling needs, achieving zoned flow and independent control of the coolant.

[0153] Preferably, such as Figure 11 As shown, the third partition 27 is vertically installed in the first manifold 2.

[0154] The vertically positioned third baffle 27 helps guide the coolant through the first cavity 24 and the second cavity 25 in a more regular flow pattern, reducing eddies and turbulence caused by irregular obstacles encountered during coolant flow. Eddies and turbulence increase coolant flow resistance, leading to increased energy loss. The vertical third baffle 27 makes coolant flow smoother, reduces flow resistance, thereby reducing pressure loss during cooling system operation and improving coolant circulation efficiency.

[0155] Preferably, the third partition 27 separates the first cavity 24 and the second cavity 25 into equal volumes.

[0156] Since the first cavity 24 and the second cavity 25 have the same volume, it helps to reduce the fluctuation of coolant flow caused by the difference in flow channel volume, and makes the distribution of coolant in each heat exchange tube 11 more uniform, thereby ensuring the stability and consistency of the overall cooling effect of the cooling assembly.

[0157] Preferably, such as Figure 11 As shown, the water inlet 211 and the drain outlet 221 are located at the same height in the first manifold 2, and the water inlet 211 and the drain outlet 221 have the same diameter.

[0158] The water inlet 211 and the drain outlet 221 are at the same height, which helps maintain the pressure balance of the coolant at the inlet and outlet. During the coolant entry and exit process, the pressure distribution is more uniform, reducing the pressure gradient caused by the height difference, allowing the coolant to flow more smoothly, improving the uniformity of coolant distribution in the system, and thus enhancing the cooling effect.

[0159] Since the inlet 211 and outlet 221 have the same diameter, the coolant flow rates they can pass through per unit time are similar. During the operation of the cooling system, the coolant enters through the inlet 211, undergoes heat exchange through the heat exchange tube 11, and then exits through the outlet 221. The design of the same diameter ensures that the inflow and outflow flow rates of the coolant can match each other, avoiding the flow imbalance problem caused by the difference in diameter, and enabling the cooling system to operate stably.

[0160] Preferably, such as Figure 11 and Figure 12 As shown, the first manifold 2 is a square tube.

[0161] By setting the first manifold 2 as a square tube, the height of the first cavity 24 and the second cavity 25 are consistent with the height of the first manifold 2, thereby allowing the diameter of the water inlet 211 and the drain outlet 221 to be set larger, so as to improve the heat exchange capacity of the cooling unit.

[0162] For example, compared to Embodiment 1, in this embodiment, the first manifold 2, while having the same cross-sectional area as the manifold in Embodiment 1, can have larger orifice diameters for the water inlet 211 and the drain outlet 221. This is because in Embodiment 1, the first flow channel 21 and the second flow channel 22 are vertically distributed, so the water inlet 211 can only be opened at the upper part of the first manifold 2, and the drain outlet 221 can only be opened at the lower part of the first manifold 2. In this embodiment, the heights of the first cavity 24 and the second cavity 25 are the same as the height of the first manifold 2, thereby allowing the orifice diameters of the water inlet 211 and the drain outlet 221 to be larger, achieving greater flow capacity and further improving the heat dissipation effect on the battery.

[0163] For example, if the cross-sectional height of the first manifold 2 in both Embodiment 1 and this embodiment is 20mm, then when the cross-sectional heights of the first flow channel 21 and the second flow channel 22 in Embodiment 1 are the same, the maximum diameter of the water inlet 211 and the drain outlet 221 will not exceed 10mm. However, in this embodiment, since the heights of the first cavity 24 and the second cavity 25 are the same as the height of the first manifold 2, the diameters of the water inlet 211 and the drain outlet 221 can be greater than 10mm, and can be close to 20mm. The diameters of the water inlet 211 and the drain outlet 221 can be expanded to 1.5-2 times the diameters of the water inlet 211 and the drain outlet 221 in Embodiment 1, which greatly increases the flow rate of the coolant in the heat exchange tube 11 and improves the cooling effect on the battery.

[0164] Example 4

[0165] The only difference between this embodiment and embodiment two is that the structure of the first manifold 2 in this embodiment is different from that in embodiment two. The first manifold 2 in this embodiment is an improvement on the first manifold 2 in embodiment two.

[0166] Preferably, such as Figure 11 and Figure 12 As shown, in this embodiment, based on the first manifold 2 of embodiment two, a first cavity 24 and a second cavity 25 are sequentially opened in the first manifold 2 along the length direction of the first manifold 2 near the water inlet 211. The first cavity 24 is connected to the water inlet 211 and the first flow channel 21 respectively, and the second cavity 25 is connected to the drain outlet 221 and the second flow channel 22 respectively.

[0167] By setting up the first cavity 24 and the second cavity 25, the flow path of the coolant within the first manifold 2 is made clearer and more orderly. After entering through the inlet 211, the coolant undergoes initial buffering and distribution within the first cavity 24, and then flows smoothly into the first flow channel 21. After completing heat exchange, it flows into the second cavity 25 through the second flow channel 22, and then exits through the drain outlet 221. This avoids disordered flow or localized accumulation of coolant within the first manifold 2, thus improving the efficiency of coolant circulation.

[0168] Preferably, such as Figure 12 As shown, a second baffle 26 is provided in the first manifold 2, which separates the first flow channel 21 and the second flow channel 22 from the first cavity 24 and the second cavity 25.

[0169] The second baffle 26 clearly defines the flow paths of the coolant in different areas. After entering the first cavity 24 through the inlet 211, the coolant can only flow and exchange heat in the first flow channel 21. After heat exchange, the coolant enters the second flow channel 22, then flows into the second cavity 25 and is discharged from the drain outlet 221. This clear zoning avoids random mixing and turbulence of the coolant between different flow channels and cavities, ensuring that the coolant flows orderly along the designed path, thus improving the operating efficiency and stability of the cooling system.

[0170] Preferably, such as Figure 12 As shown, the second partition 26 is vertically disposed in the first manifold 2.

[0171] The vertically arranged second baffle 26 occupies a relatively regular space within the first manifold 2, which can make full use of the internal space of the first manifold 2. While ensuring the separation function, it reduces the space occupied by other components and coolant flow space, which helps to improve the space utilization of the entire cooling assembly and enable the cooling assembly to achieve a more reasonable layout in a limited space.

[0172] For example, two through holes (not shown in the figure) are provided on the second partition 26 at intervals. The first flow channel 21 is connected to the first cavity 24 through one of the through holes, and the second flow channel 22 is connected to the second cavity 25 through the other through hole.

[0173] Preferably, such as Figure 11 As shown, a third partition 27 is also provided in the first manifold 2, and the first cavity 24 and the second cavity 25 are separated by the third partition 27.

[0174] By setting a third baffle 27, the coolant can flow in two independent channels (first cavity 24 and second cavity 25). This split-flow design can introduce coolants of different temperatures, flow rates, or characteristics into the two cavities according to actual cooling needs, achieving zoned flow and independent control of the coolant.

[0175] Preferably, such as Figure 11 As shown, the third partition 27 is vertically installed in the first manifold 2.

[0176] The vertically positioned third baffle 27 helps guide the coolant through the first cavity 24 and the second cavity 25 in a more regular flow pattern, reducing eddies and turbulence caused by irregular obstacles encountered during coolant flow. Eddies and turbulence increase coolant flow resistance, leading to increased energy loss. The vertical third baffle 27 makes coolant flow smoother, reduces flow resistance, thereby reducing pressure loss during cooling system operation and improving coolant circulation efficiency.

[0177] Preferably, the third partition 27 separates the first cavity 24 and the second cavity 25 into equal volumes.

[0178] Since the first cavity 24 and the second cavity 25 have the same volume, it helps to reduce the fluctuation of coolant flow caused by the difference in flow channel volume, and makes the distribution of coolant in each heat exchange tube 11 more uniform, thereby ensuring the stability and consistency of the overall cooling effect of the cooling assembly.

[0179] Preferably, such as Figure 11 As shown, the water inlet 211 and the drain outlet 221 are located at the same height in the first manifold 2, and the water inlet 211 and the drain outlet 221 have the same diameter.

[0180] The water inlet 211 and the drain outlet 221 are at the same height, which helps maintain the pressure balance of the coolant at the inlet and outlet. During the coolant entry and exit process, the pressure distribution is more uniform, reducing the pressure gradient caused by the height difference, allowing the coolant to flow more smoothly, improving the uniformity of coolant distribution in the system, and thus enhancing the cooling effect.

[0181] Since the inlet 211 and outlet 221 have the same diameter, the coolant flow rates they can pass through per unit time are similar. During the operation of the cooling system, the coolant enters through the inlet 211, undergoes heat exchange through the heat exchange tube 11, and then exits through the outlet 221. The design of the same diameter ensures that the inflow and outflow flow rates of the coolant can match each other, avoiding the flow imbalance problem caused by the difference in diameter, and enabling the cooling system to operate stably.

[0182] Preferably, such as Figure 11 and Figure 12 As shown, the first manifold 2 is a square tube.

[0183] By setting the first manifold 2 as a square tube, the height of the first cavity 24 and the second cavity 25 are consistent with the height of the first manifold 2, thereby allowing the diameter of the water inlet 211 and the drain outlet 221 to be set larger, so as to improve the heat exchange capacity of the cooling unit.

[0184] For example, compared to Embodiment 2, in this embodiment, while maintaining the same cross-sectional area as the first manifold 2 in Embodiment 2, the diameters of the water inlet 211 and the drain outlet 221 can be increased. This is because in Embodiment 2, the first flow channel 21 and the second flow channel 22 are vertically distributed, so the water inlet 211 can only be opened at the upper part of the first manifold 2, and the drain outlet 221 can only be opened at the lower part of the first manifold 2. In this embodiment, the heights of the first cavity 24 and the second cavity 25 are the same as the height of the first manifold 2, thereby allowing the diameters of the water inlet 211 and the drain outlet 221 to be larger, achieving greater flow capacity and further improving the heat dissipation effect on the battery.

[0185] For example, if the cross-sectional height of the first manifold 2 in both Embodiment 2 and this embodiment is 20mm, then when the cross-sectional heights of the first flow channel 21 and the second flow channel 22 in Embodiment 2 are the same, the maximum diameter of the water inlet 211 and the drain outlet 221 will not exceed 10mm. However, in this embodiment, since the heights of the first cavity 24 and the second cavity 25 are the same as the height of the first manifold 2, the diameters of the water inlet 211 and the drain outlet 221 can be greater than 10mm, and can be close to 20mm. The diameters of the water inlet 211 and the drain outlet 221 can be expanded to 1.5-2 times the diameters of the water inlet 211 and the drain outlet 221 in Embodiment 2, which greatly increases the flow rate of the coolant in the heat exchange tube 11 and improves the cooling effect on the battery.

[0186] In addition, such as Figure 13 As shown, this utility model also provides a battery pack, which includes a housing 4 and a battery module 100 (e.g., ...). Figure 2 As shown in the diagram and in any of the above embodiments, the cooling assembly, battery module 100, and cooling assembly are all installed in the housing 4.

[0187] Preferably, such as Figure 13 and Figure 14 As shown, the box body 4 has a first through hole 41 and a second through hole 42 spaced apart from each other. A sealing block 5 is provided in both the first through hole 41 and the second through hole 42. A water inlet connector 6 and a water outlet connector 7 are respectively passed through the two sealing blocks 5. The water inlet connector 6 is connected to the water inlet 211, and the water outlet connector 7 is connected to the drain outlet 221.

[0188] This utility model provides two spaced-apart through holes, namely a first through hole 41 and a second through hole 42, on the housing 4. Both through holes are equipped with sealing blocks 5. The function of the sealing blocks 5 is to ensure the airtightness of the housing 4 and prevent external water, dust and other impurities from entering the housing 4 and damaging the battery module 100 and cooling components, thereby improving the service life and reliability of the battery pack.

[0189] Preferably, such as Figure 14 and Figure 16 As shown, a first groove 43 is provided in both the first through hole 41 and the second through hole 42, and a first rib 52 adapted to the corresponding first groove 43 is provided on the surface of each sealing block 5.

[0190] The fitting design of the first protruding rib 52 and the first groove 43 forms a physical interlocking structure. This interlocking effectively prevents external impurities from entering the interior of the housing 4 through the tiny gap between the sealing block 5 and the through hole. Compared to simply relying on the sealing block 5's own material to adhere to the inner wall of the through hole, this adds an extra layer of sealing protection, greatly improving the reliability of the seal and preventing moisture, dust, and other contaminants from damaging the battery module 100 and cooling components inside the housing 4. Furthermore, the structure of the first protruding rib 52 embedded in the first groove 43 restricts the movement of the sealing block 5, keeping it in the correct installation position and ensuring that the sealing effect is not reduced by external forces, further guaranteeing the airtightness of the housing 4.

[0191] Preferably, such as Figure 15 , Figure 16 and Figure 17 As shown, in one embodiment, both sealing blocks 5 are provided with a third through hole 51, and the water inlet connector 6 and the water outlet connector 7 are respectively inserted through the corresponding third through hole 51. A second rib 53 is provided on the hole wall of each third through hole 51, and a second groove 61 adapted to the corresponding second rib 53 is provided on the surface of the water inlet connector 6 and the water outlet connector 7 respectively.

[0192] Based on the primary sealing achieved between the sealing block 5 and the through hole of the housing 4 through the first protruding rib 52 and the first groove 43, the second protruding rib 53 on the wall of the third through hole 51 cooperates with the second groove 61 on the surface of the water inlet connector 6 and the water outlet connector 7 to form a secondary sealing defense. This multi-level sealing structure can effectively prevent coolant from leaking from the connection between the connector and the third through hole 51, avoiding damage to other components inside the battery pack by the coolant, and preventing external impurities from entering the housing 4 from this connection, thus comprehensively ensuring the stability of the internal environment of the battery pack.

[0193] Furthermore, the fit between the second rib 53 and the second groove 61 increases the sealing contact area, and this interlocking structure can better adapt to minor deformations of the component caused by factors such as temperature changes and vibration, maintaining the effectiveness of the seal at all times. Compared to simply relying on the tight fit between the joint and the inner wall of the third through hole 51, this greatly improves the reliability of the seal and reduces the risk of coolant leakage.

[0194] Preferably, such as Figure 18 As shown, in another embodiment, at the end of each third through hole 51, the surface of the sealing block 5 protrudes outward to form a third rib 54, the third rib 54 surrounds the third through hole 51, and a fourth rib 62 corresponding to the third rib 54 is respectively provided on the surface of the water inlet connector 6 and the water outlet connector 7, the third rib 54 can abut against the fourth rib 62.

[0195] The third rib 54 at one end of the third through hole 51 can tightly abut against the fourth rib 62 on the surfaces of the inlet connector 6 and the outlet connector 7. This abutment forms a structure similar to a "buckle" or "sealing engagement," creating a tight connection between the inlet connector 6, the outlet connector 7, and the sealing block 5. This tight fit forms multiple sealing lines, effectively preventing coolant leakage from the connection between the inlet connector 6 and the outlet connector 7 and the sealing block 5. Even during long-term use of the battery pack, when factors such as vibration and temperature changes cause minor deformation of the sealing components, the rib abutment structure can still maintain good sealing performance, thereby better protecting key components such as the battery module 100 inside the battery pack from coolant corrosion, improving the service life and reliability of the battery pack.

[0196] Preferably, such as Figure 19 As shown, the housing 4 has an installation groove 44, and multiple heat exchange tubes 11 are installed in the installation groove 44.

[0197] This invention utilizes a mounting slot 44 within the housing 4 to install the heat exchange tube assembly 1, making full use of the internal space of the housing 4. Compared to randomly placing the heat exchange tubes 11 within the housing 4, the mounting slot 44 allows the heat exchange tube assembly 1 to be arranged more compactly within the limited space, freeing up more space for other components such as the battery module 100. This helps improve the overall space utilization of the battery pack, enabling it to accommodate more battery cells while maintaining a smaller volume, thereby increasing energy density.

[0198] By positioning and installing the heat exchange tube assembly 1 through the mounting slot 44, a reasonable layout of the internal components of the battery pack can be achieved. The relative position between the heat exchange tube assembly 1 and the battery module 100 can be precisely controlled, preventing the heat exchange tube 11 from shifting or deforming due to vibration, impact, or other factors during battery pack use. This facilitates more efficient heat exchange between the coolant and the battery module 100 as the coolant flows within the heat exchange tube 11, thereby improving heat exchange efficiency, enhancing cooling effect, and effectively reducing the operating temperature of the battery module 100. At the same time, it also avoids mutual interference between components caused by unreasonable layout, improving the overall structural compactness and operational stability of the battery pack.

[0199] In addition, the heat exchanger tube assembly 1 and the battery module 100 need to be connected and fixed in a certain way. For example, thermally conductive adhesive can be injected into the gap between the heat exchanger tube assembly 1 and the battery module 100. The thermally conductive adhesive has good thermal conductivity and can quickly conduct the heat generated by the battery module 100 to the heat exchanger tube assembly 1, and then the heat exchanger tube assembly 1 dissipates the heat.

[0200] When thermally conductive adhesive is applied to the gap between the heat exchanger tube assembly 1 and the battery module 100, the sidewall of the mounting groove 44 can block the adhesive, preventing it from overflowing from the gap. This ensures that the adhesive is fully and evenly filled within the gap, improving its utilization rate and connection effect. Consequently, the amount of adhesive used can be reduced without compromising heat exchange efficiency. Preferably, the width of the battery module 100 is greater than the width of the mounting groove 44.

[0201] Preferably, the width of the battery module 100 is greater than the width of the mounting groove 44. This allows the heat exchange tube assembly 1 to be installed closer to the battery module 100. The increased contact area between the heat exchange tube assembly 1 and the battery module 100 allows the coolant to absorb more heat generated by the battery module 100 as it flows within the heat exchange tubes 11, accelerating heat transfer and improving heat exchange efficiency. This helps to control the operating temperature of the battery module 100 within a more suitable range, ensuring stable battery performance and extending battery life.

[0202] In one embodiment, the width of the battery module 100 is 20-60 mm larger than the width of the mounting slot 44.

[0203] A width range of 20–60 mm allows the heat exchange tube assembly 1 to be more evenly distributed around the battery module 100, achieving uniform heat absorption. This avoids localized overheating and improves the overall temperature consistency of the battery module 100. For example, in the edge and center areas of the battery module 100, heat can be transferred more evenly to the cooling system, preventing inconsistent battery performance due to excessive temperature differences, which in turn affects the overall performance and lifespan of the battery pack.

[0204] Given the limited dimensions of the battery pack housing, a width difference of 20–60 mm allows for more efficient space allocation. While ensuring effective cooling, this allows for the placement of as many battery cells as possible, improving the battery pack's space utilization and energy density.

[0205] Of course, in other embodiments, the width of the battery module 100 is 10mm, 15mm, 70mm, 80mm, etc., larger than the width of the mounting slot 44. This value can be adaptively adjusted according to specific working conditions and heat dissipation requirements, etc., and this utility model does not make specific limitations here.

[0206] In another embodiment, the width of the mounting slot 44 is less than the width of the battery module 100, but 0.6 times greater than the width of the battery module 100.

[0207] The width of the mounting slot 44 is 0.6 times greater than the width of the battery module 100, ensuring sufficient contact area between the heat exchange tube assembly 1 and the battery module 100 for heat exchange. When the coolant flows within the heat exchange tube 11, it can fully absorb the heat generated by the battery module 100, avoiding low heat exchange efficiency due to insufficient contact area. This maintains the battery module 100 operating within a suitable temperature range, ensuring stable battery performance and extending battery cycle life.

[0208] This size ratio helps to create a relatively uniform layout of the heat exchanger tube assembly 1 around the battery module 100, allowing heat to be transferred more evenly from the battery module 100 to the coolant. This avoids localized overheating or undercooling of the battery module 100 and improves the overall temperature uniformity of the battery module 100.

[0209] Of course, in other embodiments, the width of the slot can also be 0.8 times, 0.9 times, etc., greater than the width of the battery module 100. The specific multiple relationship can be adaptively adjusted according to specific operating conditions and heat dissipation requirements, etc., and this utility model does not make specific limitations here.

[0210] Preferably, the depth of the mounting groove 44 is greater than the height of the heat exchange tube 11.

[0211] This structural design allows the heat exchange tube 11 to be fully embedded in the mounting groove 44, ensuring a more secure fixation. Through appropriate fixing methods (such as clips or brackets), the heat exchange tube 11 maintains a stable position within the mounting groove 44, reducing displacement or loosening caused by vibration, impact, or other factors. This helps ensure the normal operation of the cooling system, preventing changes in the position of the heat exchange tube 11 from affecting the cooling effect or even damaging the battery module 100 or other components.

[0212] The deeper mounting groove 44 can provide a certain degree of protection for the heat exchange tube 11, preventing it from being damaged by collisions or compression from external objects. During the transportation, installation, and use of the battery pack, the mounting groove 44 can provide a relatively safe space for the heat exchange tube 11, reducing the risk of rupture or leakage of the heat exchange tube 11 and improving the reliability and safety of the cooling system.

[0213] Furthermore, if the battery pack requires replacement of heat exchange tubes 11 with different specifications during subsequent upgrades or maintenance, the design of the mounting slot 44, with a depth greater than the height of the heat exchange tubes 11, provides a certain degree of compatibility. As long as the height of the heat exchange tubes 11 varies within a certain range, they can be adapted to the mounting slot 44, reducing the need for large-scale modifications to the mounting slot 44 due to changes in the specifications of the heat exchange tubes 11, and improving the maintainability and scalability of the battery pack.

[0214] For example, in this utility model, the difference between the depth of the mounting groove 44 and the height of the heat exchange tube 11 is 0.5 to 2 mm.

[0215] By setting a height difference of 0.5 to 2 mm, the slight deformation tolerance of the heat exchange tube 11 can be effectively absorbed, avoiding direct hard contact between the battery module 100 and the battery cell due to tolerance issues, preventing structural deformation and damage, and ensuring the overall structural stability and safety of the battery module 100.

[0216] A height difference of 0.5–2 mm ensures a suitable gap between the heat exchange tube 11 and the battery module 100. Filling this gap with thermally conductive adhesive guarantees efficient heat transfer from the battery module 100 to the heat exchange tube 11 without excessively large gaps leading to high thermal resistance and affecting heat exchange performance. Optimizing the heat conduction path improves the heat exchange efficiency of the battery thermal management system, helping to maintain the battery module 100 within a suitable operating temperature range, extending battery life, and enhancing battery system performance.

[0217] It should be noted that in other embodiments, the difference between the depth of the mounting groove 44 and the height of the heat exchange tube 11 can be 3mm, 4mm, or other values. For example, the difference between the depth of the mounting groove 44 and the height of the heat exchange tube 11 can depend on the level of process control. If the process control precision is high and the deformation tolerance of the heat exchange tube 11 is small, the height difference can be relatively small; conversely, if the process control is difficult and the deformation tolerance is large, the height difference needs to be appropriately increased to ensure the adaptability of the structure. Of course, the difference between the depth of the mounting groove 44 and the height of the heat exchange tube 11 can also be adaptively adjusted according to specific operating conditions and heat dissipation requirements. This utility model does not specifically limit the difference between the depth of the mounting groove and the height of the heat exchange tube 11.

[0218] Preferably, multiple battery modules 100 and cooling components are provided, with each battery module 100 corresponding to each cooling component.

[0219] Each battery module 100 is equipped with an independent cooling component, which can precisely dissipate heat according to the thermal characteristics of the corresponding battery module 100. During operation, different battery modules 100 may have different heat generation and heat distribution due to differences in individual battery cells, charging and discharging states, and their positions in the battery pack. The independent cooling component can adjust parameters such as the flow rate, velocity, and temperature of the coolant to achieve more efficient heat exchange, ensuring that each battery module 100 operates within a suitable temperature range and avoiding localized overheating or overcooling.

[0220] Furthermore, the one-to-one correspondence between multiple battery modules 100 and cooling components forms a parallel heat dissipation mechanism. Each cooling component operates independently without interference, enabling simultaneous heat dissipation for multiple battery modules 100, significantly improving the overall heat dissipation efficiency of the battery pack. Compared to using a single cooling component to centrally dissipate heat from multiple battery modules 100, parallel heat dissipation avoids heat dissipation delays and inefficiencies caused by heat concentration and excessively long heat dissipation paths, allowing the battery pack to better cope with high-power operation and other high-heat-generating conditions.

[0221] This utility model also provides an energy storage device (not shown in the figure), which includes the above-mentioned battery pack, and the battery pack is provided with multiple batteries.

[0222] The technical solution of this utility model has been described in conjunction with the preferred embodiments shown in the accompanying drawings. However, it will be readily understood by those skilled in the art that the protection scope of this utility model is obviously not limited to these specific embodiments. Without departing from the principle of this utility model, those skilled in the art can make equivalent changes or substitutions to the relevant technical features, and the technical solutions after these changes or substitutions will all fall within the protection scope of this utility model.

Claims

1. A cooling assembly, characterized in that, The cooling assembly includes: A heat exchange tube assembly (1) comprising a plurality of heat exchange tubes (11); The first manifold (2) has a first flow channel (21) and a second flow channel (22) that are not interconnected. The first flow channel (21) is provided with a water inlet (211) and a first connecting port (212) that is connected to one end of each of the multiple heat exchange tubes (11). The second flow channel (22) is provided with a drain outlet (221) and a second connecting port (222) that is connected to the other end of each of the multiple heat exchange tubes (11).

2. The cooling assembly according to claim 1, characterized in that, The first manifold (2) has a tubular structure and is sealed at both ends. A first partition (23) is provided in the first manifold (2). The first partition (23) divides the space inside the first manifold (2) to form the first flow channel (21) and the second flow channel (22) distributed vertically.

3. The cooling assembly according to claim 2, characterized in that, The first partition (23) is horizontally arranged in the first manifold (2).

4. The cooling assembly according to claim 2, characterized in that, The first partition (23) divides the space in the first manifold (2) into equal volumes so that the volumes of the first flow channel (21) and the second flow channel (22) are equal.

5. The cooling assembly according to claim 2, characterized in that, The first connecting port (212) and the second connecting port (222) are both located on one side of the first collecting pipe (2), and the water inlet (211) and the drain outlet (221) are both located on the other side of the first collecting pipe (2) opposite to the first connecting port (212).

6. The cooling assembly according to claim 5, characterized in that, On the side near the water inlet (211), along the length of the first manifold (2), a first cavity (24) and a second cavity (25) are sequentially provided in the first manifold (2). The first cavity (24) is connected to the water inlet (211) and the first flow channel (21) respectively, and the second cavity (25) is connected to the drain outlet (221) and the second flow channel (22) respectively.

7. The cooling assembly according to claim 6, characterized in that, The first manifold (2) is provided with a second partition (26), which separates the first flow channel (21) and the second flow channel (22) from the first cavity (24) and the second cavity (25).

8. The cooling assembly according to claim 7, characterized in that, The second partition (26) has two through holes spaced apart. The first flow channel (21) is connected to the first cavity (24) through one of the through holes, and the second flow channel (22) is connected to the second cavity (25) through the other through hole.

9. The cooling assembly according to claim 7, characterized in that, The second partition (26) is vertically disposed in the first manifold (2).

10. The cooling assembly according to claim 6, characterized in that, The first manifold (2) is also provided with a third partition (27), and the first cavity (24) and the second cavity (25) are separated by the third partition (27).

11. The cooling assembly according to claim 10, characterized in that, The third partition (27) is vertically disposed in the first manifold (2).

12. The cooling assembly according to claim 10, characterized in that, The third partition (27) separates the first cavity (24) and the second cavity (25) into equal volumes.

13. The cooling assembly according to claim 6, characterized in that, The water inlet (211) and the drain outlet (221) are located at the same height position of the first manifold (2), and / or the water inlet (211) and the drain outlet (221) have the same diameter.

14. The cooling assembly according to claim 6, characterized in that, The first manifold (2) is a square tube.

15. The cooling assembly according to claim 1, characterized in that, Each heat exchange tube (11) includes two tube sections (111) arranged along the length of the first manifold (2), one of the tube sections (111) being connected to the first communication port (212) and the other tube section (111) being connected to the second communication port (222), and the coolant in adjacent tube sections (111) flowing in opposite directions.

16. The cooling assembly according to claim 15, characterized in that, The heat exchange tube (11) is a U-shaped tube, and the heat exchange tube (11) also includes a bent tube section (112). The ends of the two tube sections (111) away from the first manifold (2) are respectively connected to the two ends of the bent tube section (112).

17. The cooling assembly according to claim 16, characterized in that, Multiple heat exchange tubes (11) are nested together.

18. The cooling assembly according to claim 16, characterized in that, The heat exchange tube group (1) is provided in multiple sets, and the multiple sets of heat exchange tube groups (1) are arranged sequentially along the length direction of the first manifold (2). The coolant flows in opposite directions in the two outermost tube sections (111) of two adjacent sets of heat exchange tube groups (1).

19. The cooling assembly according to claim 15, characterized in that, The cooling assembly also includes a second manifold (3), which is spaced apart from the first manifold (2). The second manifold (3) has a return cavity (31), and the ends of the two pipe sections (111) away from the first manifold (2) are connected to the return cavity (31).

20. The cooling assembly according to claim 19, characterized in that, Multiple reflux chambers (31) are arranged sequentially along the length of the second manifold (3), and each of the multiple reflux chambers (31) corresponds to a multiple heat exchange tube (11).

21. The cooling assembly according to claim 20, characterized in that, Along the length of the second manifold (3), a plurality of fourth partitions (32) are provided at intervals in the second manifold (3), and the fourth partitions (32) divide the space in the second manifold (3) to form a plurality of return cavities (31).

22. The cooling assembly according to claim 21, characterized in that, The fourth partition (32) is vertically disposed in the second manifold (3).

23. The cooling assembly according to claim 15, characterized in that, At least part of the pipe body (111) has a bend joint (113) at its end.

24. The cooling assembly according to claim 1, characterized in that, The heat exchange tube (11) is provided with a support plate (114) at intervals, and the support plate (114) divides the space inside the heat exchange tube (11) into multiple channels.

25. A battery pack, characterized in that, It includes a housing (4), a battery module (100), and a cooling assembly as described in any one of claims 1 to 24, wherein the battery module (100) and the cooling assembly are both installed in the housing (4).

26. The battery pack according to claim 25, characterized in that, The housing (4) has a first through hole (41) and a second through hole (42) spaced apart from each other. Both the first through hole (41) and the second through hole (42) are provided with sealing blocks (5). A water inlet connector (6) and a water outlet connector (7) are respectively passed through the two sealing blocks (5). The water inlet connector (6) is connected to the water inlet (211), and the water outlet connector (7) is connected to the drain outlet (221).

27. The battery pack according to claim 26, characterized in that, Both the first through hole (41) and the second through hole (42) are provided with a first groove (43), and the surface of each sealing block (5) is provided with a first rib (52) that matches the corresponding first groove (43).

28. The battery pack according to claim 26, characterized in that, Both sealing blocks (5) are provided with a third through hole (51). The water inlet connector (6) and the water outlet connector (7) are respectively inserted into the corresponding third through hole (51). A second rib (53) is provided on the hole wall of each third through hole (51). A second groove (61) adapted to the second rib (53) is provided on the surface of the water inlet connector (6) and the water outlet connector (7).

29. The battery pack according to claim 28, characterized in that, At the end of each of the third through holes (51), the surface of the sealing block (5) is raised outward to form a third rib (54), the third rib (54) surrounds the third through hole (51), and a fourth rib (62) corresponding to the third rib (54) is respectively provided on the surface of the water inlet connector (6) and the water outlet connector (7), the third rib (54) can abut against the fourth rib (62).

30. The battery pack according to claim 25, characterized in that, The housing (4) has an installation groove (44) in which a plurality of heat exchange tubes (11) are installed.

31. The battery pack according to claim 30, characterized in that, The width of the battery module (100) is greater than the width of the mounting slot (44).

32. The battery pack according to claim 30, characterized in that, The depth of the mounting groove (44) is greater than the height of the heat exchange tube (11).

33. An energy storage device, characterized in that, The energy storage device includes the battery pack of claim 25, and the battery pack is provided in multiple forms.

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