Liquid cooling plate and battery pack

Abstract

The application discloses a liquid cooling plate, which comprises a spiral flow channel and turbulence members arranged at intervals along the extension direction of the spiral flow channel, wherein the turbulence member comprises three turbulence ribs, at least one connecting rib and at least one arc-shaped wall, the connecting rib and the arc-shaped wall are arranged between adjacent turbulence ribs; one side of the turbulence rib towards the side wall of the spiral flow channel is in engagement with the side wall surface of the spiral flow channel as a first engagement surface; the turbulence rib is provided with an arc-shaped flow guide surface on the side away from the side wall surface of the spiral flow channel, the vertical distance between the arc top of the arc-shaped flow guide surface of the turbulence rib and the first engagement surface is W1, and the vertical distance between the arc top of the arc-shaped wall and the first engagement surface is W2, which is less than W1. The application also discloses a battery pack comprising battery monomers and the liquid cooling plate as described above. The scheme improves the heat transfer performance of the cooling liquid, improves the heat exchange efficiency, makes the cooling liquid flow more uniform, improves the temperature uniformity of the surface of the liquid cooling plate, and improves the heat dissipation performance of the battery.

Description

Technical Field

[0001] This invention relates to the field of battery heat dissipation technology, specifically to a liquid cooling plate. Background Technology

[0002] With the rapid development of new energy vehicles and portable electronic devices, lithium batteries, as the main energy storage unit, have been widely used in various high-energy-density devices. However, batteries generate a large amount of heat during charging and discharging. If the temperature is too high, it will seriously affect the safety, lifespan, and performance of lithium batteries. Currently, the mainstream thermal management technologies for lithium-ion batteries are air cooling and liquid cooling. Air cooling is simple in structure and low in cost, but its heat dissipation efficiency is limited by the heat capacity and thermal conductivity of air, making it difficult for the temperature of lithium-ion batteries to be evenly distributed and prone to local overheating problems. In contrast, liquid cooling systems, because the specific heat capacity and thermal conductivity of coolant are much higher than those of air, can provide higher heat dissipation efficiency and temperature uniformity, and are gradually becoming the mainstream solution for high-power thermal management. As the core component of the liquid cooling system, the internal flow channel structure design of the liquid cooling plate directly determines the flow characteristics and heat exchange performance of the coolant, thus affecting the maximum temperature, surface temperature uniformity, and long-term operational reliability of the object being cooled.

[0003] Currently, the widely used flow channel forms for liquid-cooled plates mainly include straight flow channels and S-shaped flow channels. For straight liquid-cooled plates, the structure is simple, typically employing a parallel multi-channel structure, with the coolant flowing in from the inlet and then branching to each parallel branch. However, due to the pressure gradient along the flow direction, the coolant has the highest pressure and fastest flow velocity near the inlet, decreasing with distance. The driving force weakens further away from the inlet, and the flow velocity gradually decreases. This leads to an imbalance in flow distribution across branches—faster flow velocity and stronger heat transfer near the inlet, and slower flow velocity and weaker heat transfer in the farther inlet. Low-velocity areas may even form dead zones, resulting in localized overheating, and the overall heat transfer capacity of the coolant is not fully utilized. Simultaneously, the shorter path of the straight flow channel means that the coolant near the inlet does not absorb enough heat before being discharged, and insufficient flow at the farther inlet prevents timely heat dissipation, further exacerbating the temperature gradient along the plate surface and resulting in severely uneven surface temperature distribution.

[0004] For S-shaped flow channels, the flow path of coolant is extended by multiple bends to increase the heat exchange area. However, the frequent bends cause the flow direction of coolant to change drastically at the bends. The flow velocity is high on the outside of the bend and low on the inside, resulting in severe local flow velocity unevenness. The heat exchange intensity varies greatly in different areas, thus limiting the heat exchange efficiency.

[0005] In summary, existing liquid cooling plates, whether using straight or S-shaped flow channels, generally suffer from fundamental defects such as insufficient heat exchange capacity of the coolant and uneven surface temperature distribution. Therefore, there is an urgent need to develop a liquid cooling plate structure that can improve the heat exchange capacity and surface temperature uniformity of the liquid cooling plate in order to solve the problems existing in the above-mentioned technologies. Summary of the Invention

[0006] The main technical problem to be solved by the present invention is to provide a liquid cooling plate that has good heat exchange capacity, uniform surface temperature, and small surface temperature difference.

[0007] To address the aforementioned technical problems, the present invention provides a liquid cooling plate, comprising a spiral flow channel and flow-dispersing elements spaced apart along the extension direction of the spiral flow channel. Each flow-dispersing element includes three flow-dispersing ribs, at least one connecting rib, and at least one arc-shaped wall. The connecting rib and the arc-shaped wall are disposed between adjacent flow-dispersing ribs. The side of the flow-dispersing rib facing the sidewall of the spiral flow channel is joined to the sidewall surface of the spiral flow channel to form a first joint surface. The flow-dispersing rib has an arc-shaped flow-guiding surface on its sidewall surface away from the spiral flow channel. The vertical distance W1 between the apex of the arc-shaped flow-guiding surface of the flow-dispersing rib and the first joint surface is less than W1.

[0008] In a preferred embodiment, the underside of the turbulence element along the thickness direction of the liquid cooling plate further includes a second mating surface that engages with the bottom wall of the spiral flow channel.

[0009] In a preferred embodiment, at least a portion of the connecting rib protrudes outward relative to the arcuate wall.

[0010] In a preferred embodiment: when there are two or more connecting ribs, the two or more connecting ribs are spaced apart along the length direction of the spoiler.

[0011] In a preferred embodiment: the connecting ribs are evenly arranged along the circumference of the spoiler.

[0012] In a preferred embodiment: a plurality of the aforementioned baffles are alternately arranged on both sides of the helical flow channel.

[0013] In a preferred embodiment: the turbulence rib is coaxially arranged with the arc-shaped wall.

[0014] In a preferred embodiment: the height between adjacent spoiler ribs is H1.

[0015] In a preferred embodiment, the system further includes a liquid inlet located at the starting end of the outer ring of the spiral flow channel.

[0016] The present invention also provides a battery pack, including a battery cell and a liquid cooling plate as described in any of the above claims, wherein the battery cell is disposed on the upper surface of the liquid cooling plate.

[0017] Compared with the prior art, the technical solution of the present invention has the following beneficial effects:

[0018] 1. This invention provides a liquid cooling plate with a spiral flow channel and a flow-turbing element disposed in the spiral flow channel. The three flow-turbing ribs are connected by the connecting ribs and arc-shaped walls of the flow-turbing element, so that the coolant generates continuous turbulence when flowing along a continuous spiral path inside the liquid cooling plate. The centrifugal force is used to continuously disrupt the fluid boundary layer, and eddies are induced by contacting multiple flow-turbing elements in the flow channel, thereby improving the heat transfer performance of the coolant, increasing the heat exchange efficiency, making the coolant flow velocity more uniform, and improving the temperature uniformity of the surface of the liquid cooling plate.

[0019] 2. The present invention provides a liquid cooling plate, wherein a flow-deflecting element is joined to the bottom wall of the spiral flow channel along the lower side of the liquid cooling plate in the thickness direction, thereby enhancing the connection reliability of the flow-deflecting element.

[0020] 3. The present invention provides a liquid cooling plate, wherein at least a portion of the connecting ribs protrudes outward relative to the arc-shaped wall, and the connecting ribs are evenly spaced along the length direction of the turbulence-disrupting element, so that the continuous velocity boundary layer and thermal boundary layer near the flow channel wall are subjected to periodic disturbance, thereby promoting the mixing of the low-temperature coolant in the core region of the flow channel with the high-temperature coolant in the near-wall region, thereby improving the convective heat transfer capacity and temperature uniformity of the liquid cooling plate.

[0021] 4. The present invention provides a liquid cooling plate, which, by setting baffles alternately arranged on both sides of the spiral flow channel, causes the flow direction, flow cross-sectional area and local velocity of the coolant to change periodically as it flows through adjacent baffles in sequence.

[0022] 5. The present invention provides a liquid cooling plate, wherein a flow-dispersing rib is coaxially arranged with the arc-shaped wall, and the vertical distance between the arc apex of the arc-shaped wall and the first joint surface is less than the vertical distance between the arc apex of the arc-shaped flow-guiding surface of the flow-dispersing rib and the first joint surface, forming a multi-layer arc-shaped profile to ensure a smooth connection between the flow-dispersing structure and the bottom wall of the flow channel.

[0023] 6. The present invention also provides a battery pack in which the heat exchange surface of the liquid cooling plate is attached to the bottom of the battery cell, so that the heat generated during the charging and discharging process of the battery is transferred to the liquid cooling plate through the bottom of the battery and carried away by the coolant flowing through the interior of the liquid cooling plate, resulting in good heat exchange effect. Attached Figure Description

[0024] Figure 1 This is a structural arrangement diagram of the battery on the liquid cooling plate in a preferred embodiment of the present invention;

[0025] Figure 2 This is a cross-sectional view of the spiral flow channel and turbulence-disrupting components in the liquid cooling plate in a preferred embodiment of the present invention;

[0026] Figure 3 This is a schematic diagram of the overall flow control component in a preferred embodiment of the present invention;

[0027] Figure 4This is a left view of the spoiler in a preferred embodiment of the present invention;

[0028] Figure 5 This is a cross-sectional view of the serpentine liquid cooling plate in a preferred embodiment of the present invention;

[0029] Figure 6 This is a cross-sectional view of the linear liquid cooling plate in a preferred embodiment of the present invention;

[0030] Figure 7 This is a temperature distribution cloud map of the contact surface between the liquid cooling plate with different flow channel structures and the battery in a preferred embodiment of the present invention;

[0031] Figure 8 This is a fluid velocity distribution trace diagram of the spiral liquid cooling plate in a preferred embodiment of the present invention;

[0032] Figure 9 This is a fluid velocity distribution trace diagram of the serpentine liquid cooling plate in a preferred embodiment of the present invention;

[0033] Figure 10 This is a fluid velocity distribution trace diagram of a linear liquid cooling plate in a preferred embodiment of the present invention;

[0034] Figure 11 This is a comparison diagram of the highest temperature and surface temperature difference of batteries with different flow channel structures in a preferred embodiment of the present invention;

[0035] Figure 12 This is a simulation design schematic diagram of the spiral flow channel and the turbulence-disrupting element in the liquid cooling plate in a preferred embodiment of the present invention.

[0036] Figure label:

[0037] 1-Break rib, 11-First joint surface, 12-Second joint surface, 13-Arc-shaped flow guide surface, 2-Connecting rib, 3-Arc-shaped wall, 4-Spiral flow channel, 5-Liquid cooling plate, 6-Liquid inlet, 7-Battery cell, 8-Break component. Detailed Implementation

[0038] The present invention will now be described in further detail with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the invention and not intended to limit it. Furthermore, it should be noted that, for ease of description, the accompanying drawings show only the parts relevant to the present invention, and not all of the structures.

[0039] In the description of this invention, unless otherwise explicitly specified and limited, the terms "connected," "linked," and "fixed" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components. Those skilled in the art can understand the specific meaning of the above terms in this invention based on the specific circumstances.

[0040] In this invention, unless otherwise explicitly specified and limited, "above" or "below" the second feature can include direct contact between the first and second features, or contact between the first and second features through another feature between them. Furthermore, "above," "over," and "on top" of the second feature includes the first feature directly above or diagonally above the second feature, or simply indicates that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature includes the first feature directly below or diagonally below the second feature, or simply indicates that the first feature is at a lower horizontal level than the second feature.

[0041] In the description of this embodiment, the terms "upper," "lower," "right," and "left," etc., refer to the orientation or positional relationship shown in the accompanying drawings. They are used only for ease of description and simplification of operation, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on the present invention. In addition, the terms "first" and "second" are used only for distinction in description and have no special meaning.

[0042] The liquid-cooled plate, i.e., the battery pack of this application, will be described in further detail below with reference to the accompanying drawings.

[0043] Reference Appendix Figure 1 This embodiment discloses a battery pack suitable for battery thermal management systems in energy storage, new energy vehicles, etc. It employs a battery pack composed of 24 9Ah lithium battery cells connected in series. The battery pack has a discharge rate of 1C, and the volumetric heat generation rate of each battery cell is 9000 W / m³. 3 The battery cell 7 is disposed on the upper surface of the liquid cooling plate 5. The heat exchange surface of the liquid cooling plate 5 is in contact with the bottom of the battery cell 7, so that the heat generated during battery charging and discharging is transferred to the liquid cooling plate 5 through the bottom of the battery and carried away by the coolant flowing inside the liquid cooling plate 5. Figure 1-2 As shown, the liquid cooling plate 5 is made of aluminum with good thermal conductivity, and its overall dimensions are 488mm×395mm×10mm.

[0044] This invention draws inspiration from the biological structural features of the spiral cavity and longitudinal ribs on the wall of a conch shell, and designs a biomimetic conch-shaped liquid cooling plate, such as... Figure 12 As shown, the spiral characteristics of the conch shell are first extracted. The conch shell is formed by the continuous growth of multiple spiral layers along the spiral direction, resulting in a continuous and complete overall structure. This is abstracted as a spiral flow channel 4. This structure can extend the heat exchange path of the coolant and increase the effective heat exchange area, making the flow channel coverage density and heat exchange path spacing in different areas more consistent. This helps to reduce the thermal resistance difference between different areas and suppress the formation of local high-temperature zones far from the flow channel. When the coolant flows through the spiral flow channel 4, it enters from the inlet 6 on the outer side of the liquid cooling plate 5, that is, the inlet is located at the starting end of the outer ring of the spiral flow channel. Then, it spirals from the outside to the center area in a gradually narrowing spiral shape. Adjacent flow channel segments are arranged sequentially at a preset interval, so that the coolant flows along a continuous spiral path inside the liquid cooling plate 5. The continuous bends create periodic turbulence in the coolant, and the centrifugal force continuously peels off the boundary layer on the wall, thereby enhancing the heat exchange between the wall and the fluid. Secondly, by extracting the structural features of the conch shell's arc-shaped shell surface and longitudinally growing ribs, including the turbulence ribs 1, connecting ribs 2, and arc-shaped walls 3, multiple layers of arc-shaped turbulence components 8 are formed. When the coolant flows through the turbulence components 8, it undergoes local contraction, acceleration, expansion, and deceleration sequentially between adjacent turbulence ribs 1, thereby changing the original velocity distribution and flow direction of the fluid. This causes the continuously developing velocity boundary layer and thermal boundary layer near the flow channel wall to be periodically disturbed, thus improving the convective heat transfer capacity between the coolant and the flow channel wall. Adjacent turbulence components 8 maintain a preset spacing and are alternately arranged on both sides of the spiral flow channel 4, so that the flow direction, flow cross-sectional area, and local velocity of the coolant change periodically as it flows through adjacent turbulence components 8.

[0045] like Figure 3 As shown, the flow-dispersing component 8 includes three flow-dispersing ribs 1, six connecting ribs 2, and an arc-shaped wall 3. The uppermost and lowermost flow-dispersing ribs 1 in the thickness direction of the liquid cooling plate are semi-circular arcs. The side of the flow-dispersing rib 1 facing the sidewall of the flow channel is a first mating surface 11, which facilitates mating with the sidewall of the flow channel. The side of the flow-dispersing rib 1 facing the top or bottom wall of the flow channel is a second mating surface 12, which facilitates mating with the top or bottom wall of the flow channel. The middle flow-dispersing rib 1 is arc-shaped. The flow-dispersing component 8 is fixedly connected to the flow channel wall, and the connection is reliable, which can resist the scouring of the coolant without loosening or falling off. As a simple alternative to this embodiment, the flow-dispersing component has at least one planar surface, which can be set facing the top, bottom, or sidewall of the flow channel, and also achieves a fixed connection with the flow channel. The turbulence rib 1 has an arc-shaped flow guide surface 13 on its side wall away from the spiral flow channel 4, which accelerates the liquid at the apex of the arc surface and allows it to smoothly converge at the trailing edge of the arc surface, thereby enhancing the local turbulence intensity around the turbulence rib 8 and improving heat transfer efficiency. At the same time, the arc-shaped surface can also improve the uniformity of the wake, further enhancing the heat transfer effect between the turbulence and the wall.

[0046] Three ribs 1 are arranged at intervals along the height of the deflector 8 and are interconnected by six connecting ribs 2. In a preferred embodiment, three ribs 1 are provided. However, it should be understood that the number of ribs 1 is not limited to this and can be increased accordingly in other embodiments based on the deflection requirements. An arc-shaped wall 3 is provided between adjacent connecting ribs 2; or the arc-shaped wall 3 is an integral structure, and the connecting ribs 2 are arranged at intervals along the length of the deflector 8. At least a portion of the connecting rib 2 protrudes outward relative to the arc-shaped wall 3, i.e., protrudes towards the arc-shaped flow-guiding surface 13. The connecting ribs 2 only serve to connect the ribs 1, and their number is not limited to a specific value; they can be set to one, two, or more according to the actual structural strength and connection requirements. Preferably, the connecting ribs 2 are evenly arranged along the circumference of the deflector 8. The angle between two adjacent connecting ribs 2 and the center position of the structure is θ; in this embodiment, θ is 18°. This arrangement subjectes the continuous velocity and thermal boundary layers near the flow channel wall to periodic disturbances, promoting the mixing of the low-temperature coolant in the core region and the high-temperature coolant near the wall, thereby improving the convective heat transfer capacity and temperature uniformity of the liquid cooling plate. Figure 3-4 As shown, the total length L of the baffle is 13mm, and the total height H is 8mm. The vertical distance between the apex of the arc-shaped flow-guiding surface of the baffle rib 1 and the first joint surface is W1, both W1 being 3.6mm. The spacing height H1 between adjacent baffle ribs is 1mm. The baffle rib 1 is coaxially arranged with the arc-shaped wall 3. The radius of the baffle rib 1 is smaller than the radius of the arc-shaped wall. The arc-shaped wall 3 is a transition area with a relatively large curvature, and its radius of curvature is 6.25mm. The vertical distance between the apex of the arc-shaped wall and the first joint surface is W2, and W2 is 2.77mm. Thus, a multi-layered arc-shaped baffle structure is formed, thereby creating a multi-layered arc-shaped profile to ensure a smooth connection between the baffle structure and the bottom wall of the flow channel.

[0047] To verify the heat transfer performance of the liquid cooling plate described in this invention, under simulation conditions with identical plate size, flow channel width, inlet flow rate, inlet temperature, and heat source power, traditional models of a serpentine liquid cooling plate and a straight liquid cooling plate were established for comparison. Figure 5 , Figure 6 As shown. The only differences between the liquid cooling plate of this invention and traditional liquid cooling plates are the flow channel shape and whether or not a flow-damping element is added, and a comparative analysis of heat dissipation performance is conducted. See also Figure 8-10 Simulation results of the contact surface temperature show that traditional straight flow channels generally suffer from uneven flow distribution, poor uniformity of cooling effect, and a tendency to form localized high-temperature areas. The highest temperature area of ​​traditional serpentine liquid cooling plates mainly occurs near the flow channel outlet, with a significant cumulative temperature rise along the flow path and obvious defects in temperature uniformity. Compared to the above-mentioned traditional structures, the spiral flow channel 4 of this invention can effectively ensure the uniformity of heat dissipation during battery operation and has superior surface temperature uniformity.

[0048] from Figure 7 The velocity distribution cloud maps of different liquid cooling plate structures show that the fluid in a straight liquid cooling plate cannot be evenly distributed to each designed flow channel; the fluid velocity decreases further away from the center flow channel. In a serpentine liquid cooling plate, the fluid is affected by centrifugal force, resulting in greater resistance at flow channel corners and forming localized low-velocity zones. The flow channel structure of this invention effectively enhances the centrifugal disturbance effect of the fluid. Combined with the flow-disrupting element 8 on the inner wall of the flow channel, it causes the fluid flow area to change periodically along the flow direction, continuously enhancing the local disturbance intensity and lateral mixing degree of the coolant, thereby improving the overall heat dissipation performance of the liquid cooling plate 5.

[0049] To better illustrate the cooling effect resulting from the different shapes of the traditional liquid cooling plate structure and the spiral flow channel 4, the highest battery temperature and the temperature difference on the surface of the liquid cooling plate were chosen as evaluation criteria. The highest battery temperature directly reflects the ultimate heat dissipation capacity of the liquid cooling plate, while the temperature difference on the surface of the liquid cooling plate determines the uniformity of cell degradation within the battery pack. Excessive temperature difference leads to asynchronous charging and discharging performance of the cells, significantly shortening the overall cycle life of the battery pack. Figure 11 It is evident that the heat transfer capacity of the spiral flow channel is significantly improved. To conduct a more comprehensive analysis of the flow channel as a whole, a comprehensive evaluation index, PEC (Performance Evaluation Criteria), is introduced to comprehensively weigh the benefits of enhanced heat transfer against the costs of increased flow resistance, objectively assessing the overall cost-effectiveness of the structural improvement. A PEC > 1 indicates that the benefits of enhanced heat transfer outweigh the costs of increased resistance, resulting in better overall performance than the benchmark structure; the higher the value, the better the overall performance. PEC = 1: Overall performance is on par with the benchmark structure. PEC < 1: The costs of increased resistance outweigh the benefits of enhanced heat transfer, resulting in poorer overall performance than the benchmark structure.

[0050] The calculation formula is as follows:

[0051]

[0052] In the formula, The Nusselt number is a core dimensionless number that characterizes the strength of convective heat transfer processes in a flow channel. The friction factor is the core dimensionless parameter that characterizes the resistance properties of fluid flow within a closed channel. and The numbers represent the Nusselt number and friction factor of the reference flow channel, respectively. Since the serpentine flow channel is a commonly used reinforced flow channel in engineering, it is selected as the comparison benchmark in this paper. Calculations show that the PEC value of the serpentine flow channel is 1, the PEC value of the straight flow channel is 1.78, and the PEC value of the spiral flow channel 4 is 1.83. The PEC of the spiral flow channel 4 is slightly higher than that of the straight flow channel, indicating better overall performance. The simulation results show that this invention can effectively improve battery heat dissipation performance.

[0053] The above description is merely a preferred embodiment of the present invention and is not intended to limit the scope of protection of the present invention. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the scope of protection of the present invention.

Claims

1. A liquid-cooled plate, characterized in that: The system includes a spiral flow channel and a flow-disrupting element spaced apart along the extension direction of the spiral flow channel. The flow-disrupting element includes three flow-disrupting ribs, at least one connecting rib, and at least one arc-shaped wall. The connecting rib and the arc-shaped wall are disposed between adjacent flow-disrupting ribs. The side of the turbulence rib facing the sidewall of the spiral channel is joined to the sidewall surface of the spiral channel to form a first joint surface; The turbulence rib has an arc-shaped flow-guiding surface on its side wall away from the spiral flow channel. The vertical distance between the arc apex of the arc-shaped flow-guiding surface of the turbulence rib and the first joint surface is W1. The vertical distance W2 between the arc apex of the arc-shaped wall and the first joint surface is less than W1.

2. The liquid cooling plate according to claim 1, characterized in that: The turbulence-disrupting element further includes a second mating surface that engages with the bottom wall of the spiral channel along the thickness direction of the liquid cooler plate and / or the upper side of the turbulence-disrupting element that engages with the bottom wall of the spiral channel along the thickness direction of the liquid cooler plate.

3. A liquid cooling plate according to claim 1, characterized in that: At least a portion of the connecting rib protrudes outward relative to the arcuate wall.

4. A liquid cooling plate according to claim 1, characterized in that: When there are two or more connecting ribs, the two or more connecting ribs are spaced apart along the length direction of the spoiler.

5. A liquid-cooled plate according to claim 4, characterized in that: The connecting ribs are evenly arranged along the circumference of the spoiler.

6. A liquid-cooled plate according to claim 1, characterized in that: Multiple of the aforementioned baffles are alternately arranged on both sides of the helical flow channel.

7. A liquid cooling plate according to claim 1, characterized in that: The turbulence ribs are coaxially arranged with the arc-shaped wall.

8. A liquid cooling plate according to claim 1, characterized in that: The height between adjacent spoiler ribs is H1.

9. A liquid-cooled plate according to claim 1, characterized in that: It also includes a liquid inlet, which is located at the starting end of the outer ring of the spiral flow channel.

10. A battery pack, characterized in that: It includes battery cells and a liquid cooling plate as described in any one of claims 1-9, wherein the array of battery cells is disposed on the upper surface of the liquid cooling plate.

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