Liquid cooling plate

Abstract

The utility model discloses a liquid cooling plate which comprises an upper cover plate and a lower cover plate, and a main flow channel is formed between the upper cover plate and the lower cover plate; the water inlet nozzle is communicated with the water inlet of the main flow channel and is used for allowing a refrigerant to flow in; the water outlet nozzle is communicated with a water outlet, corresponding to the water inlet, of the main runner and is used for allowing a refrigerant to flow out; the heat exchange columns are arranged in the main flow channel, and the densities of the heat exchange columns in different areas in the main flow channel are different. According to the liquid cooling plate, the plurality of heat exchange columns are arranged, so that the structural strength of the liquid cooling plate can be enhanced, the contact area between a refrigerant and the flow channel wall can be increased, and the heat exchange efficiency is improved. Besides, the heat exchange columns with different densities are arranged in different areas, so that the flow distribution of the refrigerant in the flow channel can be optimized, the refrigerant is uniformly distributed, and the uniformity of the heat dissipation performance of the liquid cooling plate is improved.

Description

Technical Field

[0001] This utility model relates to the field of heat dissipation technology, and in particular to a liquid cooling plate. Background Technology

[0002] With the rapid development of new energy technologies, battery pack thermal management has become one of the key factors affecting the performance and safety of electric vehicles. In the thermal management system of battery packs, liquid cooling plates, as a highly efficient heat dissipation component, are widely used to reduce the operating temperature of battery modules, ensuring that they operate in optimal condition, thereby extending battery life and improving the overall system reliability.

[0003] Currently, conventional new energy battery pack liquid cooling plates mainly adopt a brazed liquid cooling plate design. This design uses brazing to tightly bond a flat cover plate to a flow channel plate formed by stamping and other processes, forming a closed refrigerant flow channel. Two water inlets are welded to the cover plate for refrigerant inlet and outlet. To cope with high heat flux density scenarios, welded fins are often added inside the flow channel to expand the heat exchange area and improve heat dissipation efficiency. However, brazed liquid cooling plates have a series of inherent drawbacks:

[0004] Energy consumption and cost issues: The brazing process requires high-temperature treatment in a large brazing furnace, which not only consumes a lot of energy, but also keeps the overall production cost high.

[0005] Surface deformation and flatness: The thermal stress generated during the brazing process often causes deformation of the liquid cooling plate surface, affecting the installation accuracy and heat dissipation effect. Some severely deformed products also need to be corrected a second time, which increases the production complexity and cost.

[0006] Manufacturing precision and yield: The brazing process has high requirements for materials, equipment and operating techniques. Any slight deviation may lead to poor welding, affecting the overall performance and reliability of the product and reducing the yield.

[0007] Given the limitations of brazed liquid cooling plates, liquid cooling plates produced using a blown expansion process have emerged as an alternative on the market. Blown liquid cooling plates typically consist of two cover plates, with a flow channel structure formed between them by high-pressure air blowing, simplifying the manufacturing process. However, this type of blown liquid cooling plate also has significant drawbacks:

[0008] Limited heat exchange area: The flow channels formed by traditional blowing process are relatively simple and cannot increase the heat exchange area through complex flow channel design like brazed liquid cooling plates, which limits the improvement of heat dissipation performance.

[0009] Uneven refrigerant distribution: The design of the blown liquid cooling plate often results in the refrigerant being diverted to two independent flow channels in the early stage. The lack of an effective flow distribution mechanism makes it difficult for the refrigerant temperature and flow rate in the two flow channels to be uniform, which in turn causes a large temperature difference inside the battery pack, affecting the thermal balance and performance consistency of the battery pack.

[0010] In summary, existing liquid cooling plate technologies face challenges in terms of cost control, production efficiency, heat dissipation performance, and manufacturing precision. Summary of the Invention

[0011] The purpose of this utility model is to solve at least one of the above-mentioned technical problems and to provide a liquid cooling plate that can not only enhance the structural strength of the liquid cooling plate, but also help improve the heat exchange efficiency. In addition, by setting heat exchange columns of different densities in different areas, the flow distribution of the refrigerant in the flow channel can be optimized, so that the refrigerant is evenly distributed and the uniformity of the heat dissipation performance of the liquid cooling plate can be improved.

[0012] The objective of this utility model is achieved through the following technical solution:

[0013] This utility model provides a liquid cooling plate, comprising:

[0014] An upper cover plate and a lower cover plate, wherein a main channel is formed between the upper cover plate and the lower cover plate;

[0015] The water inlet is connected to the water inlet of the main channel and is used for the inflow of refrigerant;

[0016] The water outlet is connected to the outlet of the main channel corresponding to the water inlet and is used for refrigerant flow.

[0017] Multiple heat exchange columns are arranged within the main flow channel, and the density of heat exchange columns varies in different regions within the main flow channel.

[0018] The beneficial effects of the above solution are as follows: By setting multiple heat exchange columns, this utility model not only enhances the structural strength of the liquid cooling plate, but also helps to increase the contact area between the refrigerant and the flow channel wall, thereby improving the heat exchange efficiency. In addition, by setting heat exchange columns of different densities in different areas, the flow distribution of the refrigerant in the flow channel can be optimized, resulting in a uniform refrigerant distribution and improving the uniformity of the heat dissipation performance of the liquid cooling plate.

[0019] Furthermore, the multiple heat exchange columns are arranged alternately within the main flow channel;

[0020] The refrigerant flows in a wavy or spiral pattern within the main channel.

[0021] The beneficial effects of the above scheme are as follows: This utility model arranges the heat exchange columns in an alternating manner in the main flow channel, which not only makes the refrigerant more disturbed during the flow process, which helps to evenly distribute the refrigerant and avoid local overheating, thereby improving the uniformity of the heat dissipation performance of the liquid cooling plate; it can also obtain a wave-shaped or spiral flow path, further increasing the contact time between the refrigerant and the flow channel wall, enhancing the turbulence effect, thereby improving the heat exchange efficiency.

[0022] Furthermore, the heat exchange column density at the inlet of the main channel is greater than the heat exchange column density at the outlet of the main channel.

[0023] The beneficial effects of the above solution are as follows: This invention uses high-density heat exchange columns at the inlet of the main flow channel, which helps to generate strong turbulence as soon as the refrigerant enters the main flow channel, quickly dispersing the refrigerant and ensuring it flows evenly into the main flow channel, avoiding localized temperature differences caused by uneven flow. Conversely, using lower-density heat exchange columns at the outlet reduces flow resistance and ensures smooth refrigerant outflow. Furthermore, by using heat exchange columns of varying densities in different areas of the main flow channel, a gradual heat exchange is achieved from the inlet to the outlet, improving the overall heat dissipation effect.

[0024] Furthermore, the main channel can be a straight main channel, a curved main channel, or a broken line main channel;

[0025] The straight main channel is composed of straight segments;

[0026] The curved main channel consists of straight segments and arc segments, and the shape of the curve includes U-shape, S-shape or serpentine.

[0027] The polygonal main channel is composed of straight segments and corner segments, and the angles of the corners include acute angles, right angles, obtuse angles and / or straight angles;

[0028] The arc-shaped segment or the corner segment divides the main flow channel into two or more refrigerant flow channels, and the heat exchange column density varies in different regions of different refrigerant flow channels.

[0029] The beneficial effects of the above solution are: this utility model provides a variety of main channel shapes, including straight, curved, and zigzag shapes, enabling the liquid cooling plate to adapt to different heat dissipation requirements and installation spaces. Straight main channels are suitable for simple heat dissipation needs, while curved and zigzag main channels are suitable for complex spatial layouts, effectively extending the refrigerant flow path, increasing heat exchange time, and improving heat dissipation performance.

[0030] Furthermore, the straight segment includes a first end, a middle section, and a second end arranged sequentially. The first end is the inlet of the refrigerant channel corresponding to the straight segment, and the second end is the outlet of the refrigerant channel corresponding to the straight segment.

[0031] The heat exchange column density at the first end is greater than the heat exchange column density in the middle, and the heat exchange column density in the middle is greater than or equal to the heat exchange column density at the second end.

[0032] The beneficial effects of the above solution are as follows: By setting heat exchange columns of different densities in different straight sections, this invention can optimize the flow and heat exchange effect of the refrigerant in the flow channel, helping to maintain stable heat exchange efficiency during the refrigerant flow process and avoiding problems such as local overheating or insufficient heat exchange. The high-density heat exchange column at the inlet helps to quickly disperse the refrigerant, the medium-density heat exchange column in the middle maintains flow uniformity, and the low-density heat exchange column at the outlet reduces flow resistance, ensuring smooth refrigerant outflow.

[0033] Furthermore, the main flow channel includes a first flow channel and a second flow channel, which run in the same direction and converge at their ends.

[0034] The beneficial effects of the above solution are: by setting up a first flow channel and a second flow channel, and making them run in the same direction and converge at the beginning and end, the refrigerant can be divided into two parts to flow in parallel, increasing the heat exchange area, which helps to improve heat dissipation efficiency, and ensures that the refrigerant is evenly distributed in the flow channel, avoiding local overheating.

[0035] Furthermore, a baffle is provided between the first flow channel and the second flow channel to allow the refrigerant entering the inlet to form two parallel parts.

[0036] The beneficial effects of the above solution are: the present invention sets a baffle between the first flow channel and the second flow channel, which can ensure that the refrigerant is evenly divided into two parts when entering the flow channel, improve the flow uniformity of the refrigerant, and avoid temperature differences caused by uneven flow distribution.

[0037] Furthermore, when the main channel is a curved main channel or a broken line main channel, the main channel includes at least two sequentially arranged straight line segments, and in two adjacent straight line segments:

[0038] One side of the arc segment connects to the second end of a straight line segment, and the other side of the arc segment connects to the first end of another straight line segment; or,

[0039] One side of the corner segment connects to the second end of a straight segment, and the other side of the corner segment connects to the first end of another straight segment.

[0040] The beneficial effects of the above solution are as follows: By setting the main flow channel to a curved or zigzag shape, this invention can extend the flow path of the refrigerant and increase the heat exchange time. The curved and corner sections help optimize the flow direction of the refrigerant and reduce flow resistance, avoid dead zones, and improve heat dissipation efficiency. Therefore, in a curved or zigzag main flow channel, by setting curved or corner sections between adjacent straight sections, a smooth transition and efficient flow of the refrigerant within the main flow channel are achieved, thereby improving heat exchange efficiency.

[0041] Furthermore, the main channel is a zigzag main channel, and includes a first straight segment, a second straight segment, and a corner segment with a flat angle;

[0042] One side of the corner segment with a flat angle connects to the second end of the first straight segment, and the other side of the corner segment with a flat angle connects to the first end of the second straight segment, so as to connect the refrigerant flow channel corresponding to the first straight segment and the refrigerant flow channel corresponding to the second straight segment.

[0043] The refrigerant flow path corresponding to the first straight segment and the refrigerant flow path corresponding to the second straight segment flow in opposite directions.

[0044] The beneficial effects of the above solution are: by setting a flat-angle corner segment to connect the first straight segment and the second straight segment, and making the two main channels run in opposite directions, this utility model not only helps to increase the heat dissipation area, but also reasonably reduces the volume of the liquid cooling plate.

[0045] Furthermore, the heat exchange column density in the inlet area of ​​the main channel is 15-20 columns / cm². 2 The heat exchange column density in the outlet area of ​​the main channel is 5~10 columns / cm². 2 ;

[0046] The refrigerant flows at a velocity of 0.5 m / s to 2 m / s in the main flow channel.

[0047] The beneficial effects of the above solution are: by limiting the heat exchange column density range of the inlet and outlet, as well as the flow velocity range of the refrigerant, this utility model can further optimize the flow and heat exchange effect of the refrigerant in the flow channel.

[0048] Compared with the prior art, the beneficial effects of this utility model include at least the following:

[0049] This invention enhances the structural strength of the liquid cooling plate by incorporating multiple heat exchange columns, thereby increasing the contact area between the refrigerant and the channel wall and improving heat exchange efficiency. Furthermore, by setting heat exchange columns of varying densities in different areas, the flow distribution of the refrigerant within the channel can be optimized, resulting in a more uniform refrigerant distribution and improving the uniformity of the liquid cooling plate's heat dissipation performance. Attached Figure Description

[0050] Figure 1This is a schematic diagram of the structure of a liquid cooling plate according to an embodiment of the present invention.

[0051] Figure 2 This is a schematic diagram of the structure of the mainstream channel in an embodiment of this utility model.

[0052] In the diagram: 1. Liquid cooling plate; 11. Lower cover plate; 12. Water inlet; 13. Water outlet; 14. Main flow channel; 1401. First flow channel; 1402. Second flow channel; 1403. Baffle; 1411. Water inlet; 1412. Water outlet; 1421. First straight section; 1422. Second straight section; 1423. Corner section; 1431. First end; 1432. Middle section; 1433. Second end; 144. Flow path; 15. Heat exchange column. Detailed Implementation

[0053] Exemplary embodiments will now be described more fully with reference to the accompanying drawings. However, these exemplary embodiments can be implemented in many forms and should not be construed as limited to the embodiments set forth herein; rather, these embodiments are provided to make the present invention more comprehensive and complete, and to fully convey the concept of the exemplary embodiments to those skilled in the art. The same reference numerals in the drawings denote the same or similar structures, and therefore repeated descriptions of them will be omitted.

[0054] The terms used to describe position and direction in this utility model are illustrated with the accompanying drawings, but changes can be made as needed, and all such changes are included within the scope of protection of this utility model.

[0055] Traditional finned brazed liquid cooling plates 1 are costly and complex to manufacture, and have relatively high flow resistance from the inlet 1411 to the outlet 1412, resulting in poor heat exchange performance. Existing blown liquid cooling plates 1 not only have a small heat dissipation area but also have high flow resistance, leading to unsatisfactory heat exchange performance.

[0056] To enhance the structural strength of the liquid cooling plate 1, increase the contact area between the refrigerant and the flow channel wall to improve heat exchange efficiency, and ensure that the refrigerant is evenly distributed in the main flow channel 14 to improve the uniformity of heat dissipation performance, the liquid cooling plate 1 of this utility model includes: an upper cover plate, a lower cover plate 11, a water inlet 12, a water outlet 13, and multiple heat exchange columns 15. The main flow channel 14 is formed between the upper cover plate and the lower cover plate 11 using a blowing technique, and heat exchange columns 15 with different densities are set in different areas of the main flow channel 14.

[0057] refer to Figure 1 The inlet 12 of this invention is connected to the inlet 1411 of the main channel 14 and is used for refrigerant inflow; the outlet 13 is connected to the outlet 1412 of the main channel 14 corresponding to the inlet 1411 and is used for refrigerant outflow. In application, the refrigerant is water or other suitable liquid cooling medium, such as ethylene glycol solution or nanofluid.

[0058] refer to Figure 1 In this invention, the heat exchange column 15 is disposed within the main flow channel 14, and the density of the heat exchange column 15 varies in different regions of the main flow channel 14. By distributing heat exchange columns 15 of different densities in different regions of the main flow channel 14, a gradual heat exchange can be achieved from the inlet 1411 to the outlet 1412, thereby improving the overall heat dissipation effect.

[0059] In application, the heat exchange column density 15 in the inlet 1411 region of the main channel 14 is greater than the heat exchange column density 15 in the outlet 1412 region of the main channel 14. The heat exchange column density 15 in the middle region of the main channel 14 is less than or equal to the heat exchange column density 15 in the inlet 1411 region of the main channel 14, but greater than or equal to the heat exchange column density 15 in the outlet 1412 region of the main channel 14.

[0060] In practical applications, the water flow connected to the inlet 1411 is columnar and concentrated, with relatively high water pressure. The high-density heat exchange columns 15 at the inlet 1411 not only increase flow resistance but also generate strong turbulence as soon as the refrigerant enters the main flow channel 14. This causes the water flow passing through the heat exchange columns 15 to split into two streams, achieving rapid dispersion of the refrigerant and ensuring uniform flow of the refrigerant into the main flow channel 14, avoiding localized temperature differences caused by uneven flow. At the outlet 1412, to reduce flow resistance and ensure smooth refrigerant outflow, lower-density heat exchange columns 15 are used. For example, the density of heat exchange columns 15 in the inlet 1411 area of ​​the main flow channel 14 is 15-20 columns / cm³. 2 The heat exchange column 15 density in the outlet 1412 area of ​​the main channel 14 is 5~10 columns / cm³. 2 .

[0061] refer to Figure 1 and Figure 2 The multiple heat exchange columns 15 of this invention are arranged alternately in the main channel 14, which can help the refrigerant to be evenly distributed, avoid local overheating, and thus improve the uniformity of heat dissipation performance of the liquid cooling plate 1.

[0062] In application, the staggered heat exchange columns 15 make the refrigerant flow path 144 in the main flow channel 14 wavy or spiral, thereby increasing the contact time between the refrigerant and the flow channel wall, enhancing the turbulence effect, and thus improving the heat exchange efficiency. In practical applications, the refrigerant flow velocity in the main flow channel 14 is 0.5 m / s to 2 m / s to reasonably control the heat exchange effect.

[0063] refer to Figure 1The main channel 14 of this utility model includes a first flow channel 1401 and a second flow channel 1402, and a partition 1403 is provided between the first flow channel 1401 and the second flow channel 1402 to form two parallel parts of the refrigerant entering the inlet 1411. In application, the first flow channel 1401 and the second flow channel 1402 run in the same direction and merge at their ends, which not only increases the heat dissipation area but also reasonably reduces the volume of the liquid cooling plate 1. It is suitable for dual-module products that require simultaneous temperature control and uniform temperature.

[0064] The main channel 14 of this utility model can be a straight main channel 14, a curved main channel 14, or a broken line main channel 14, to adapt to different heat dissipation requirements and installation space.

[0065] In applications requiring simple heat dissipation, a straight-line main channel 14, composed of straight segments, is used. For complex spatial layouts, a curved or polygonal main channel 14 is used.

[0066] In practical applications, the curved main flow channel 14 consists of straight segments and arc segments, with the curve shape including U-shape, S-shape, or serpentine; the zigzag main flow channel 14 consists of straight segments and corner segments 1423, with the corner angles including acute angles, right angles, obtuse angles, and / or straight angles. It is evident that the curved and zigzag main flow channels 14 not only effectively extend the refrigerant flow path 144, increase heat exchange time, and improve heat dissipation, but also are suitable for different application scenarios.

[0067] Furthermore, the arc-shaped segment or corner segment 1423 divides the main channel 14 into two or more refrigerant channels, that is, one straight segment corresponds to one refrigerant channel. When the main channel 14 is a straight main channel 14, the main channel 14 is regarded as a refrigerant channel.

[0068] refer to Figure 1 and Figure 2 The straight segment of this utility model includes a first end 1431, a middle part 1432, and a second end 1433 arranged sequentially. The first end 1431 is the inlet 1411 of the refrigerant channel corresponding to the straight segment, and the second end 1433 is the outlet 1412 of the refrigerant channel corresponding to the straight segment.

[0069] In application, the density of the heat exchange column 15 at the first end 1431 is greater than or equal to the density of the heat exchange column 15 at the middle part 1432, the density of the heat exchange column 15 at the middle part 1432 is greater than or equal to the density of the heat exchange column 15 at the second end 1433, and the density of the heat exchange column 15 at the first end 1431 is greater than the density of the heat exchange column 15 at the second end 1433.

[0070] In some embodiments, each segment of the refrigerant flow channel of this invention includes an inlet 1411 and an outlet 1412, and the density of the heat exchange columns 15 in different regions of different segments of the refrigerant flow channel is different. When the main flow channel 14 is a curved main flow channel 14, the main flow channel 14 includes at least two sequentially arranged straight segments, and in two adjacent straight segments: one side of the curved segment connects to the second end 1433 of a straight segment, and the other side of the curved segment connects to the first end 1431 of another straight segment.

[0071] In application, starting from the water inlet 12, the straight segments are sequentially numbered. The density of the heat exchange column 15 in the refrigerant flow channel corresponding to the (N+1)th straight segment is greater than the density of the heat exchange column 15 in the refrigerant flow channel corresponding to the Nth straight segment, where N is greater than or equal to 1. In practical application, the density of the heat exchange column 15 in the refrigerant flow channel area corresponding to the second end 1433 and the middle 1432 of the (N+1)th straight segment is greater than the density of the heat exchange column 15 in the refrigerant flow channel area corresponding to the second end 1433 and the middle 1432 of the Nth straight segment. This is to offset the local temperature rise of the battery pack caused by the rise in refrigerant temperature, reduce the temperature difference of the battery pack, and make the battery pack temperature uniform.

[0072] In some other embodiments, each segment of the refrigerant flow channel of this invention includes an inlet 1411 and an outlet 1412, and the density of the heat exchange columns 15 in different regions of different segments of the refrigerant flow channel is different. When the main flow channel 14 is a zigzag main flow channel 14, the main flow channel 14 includes at least two sequentially arranged straight segments, and in two adjacent straight segments: one side of the corner segment 1423 is connected to the second end 1433 of one straight segment, and the other side of the corner segment 1423 is connected to the first end 1431 of another straight segment.

[0073] In application, starting from the water inlet 12, the straight segments are sequentially numbered. The density of the heat exchange column 15 in the refrigerant flow channel corresponding to the (N+1)th straight segment is greater than the density of the heat exchange column 15 in the refrigerant flow channel corresponding to the Nth straight segment. In actual application, the density of the heat exchange column 15 in the refrigerant flow channel area corresponding to the second end 1433 and the middle 1432 of the (N+1)th straight segment is greater than the density of the heat exchange column 15 in the refrigerant flow channel area corresponding to the second end 1433 and the middle 1432 of the Nth straight segment. This is to offset the local temperature rise of the battery pack caused by the rise in refrigerant temperature, reduce the temperature difference of the battery pack, and make the battery pack temperature uniform.

[0074] In some preferred embodiments, when the battery pack requiring uniform heat dissipation includes four rows of battery packs arranged in parallel, and each row of battery packs has multiple battery cells, the main channel 14 of this utility model is a zigzag main channel 14, and includes a first straight segment 1421, a second straight segment 1422 and a corner segment 1423 with a flat angle.

[0075] In application, the first end 1431 of the first straight segment 1421 is connected to the inlet nozzle 12, and the second end 1433 of the second straight segment 1422 is connected to the outlet nozzle 13. One side of the angled corner segment 1423 is connected to the second end 1433 of the first straight segment 1421, and the other side of the angled corner segment 1423 is connected to the first end 1431 of the second straight segment 1422, thus connecting the refrigerant flow channels corresponding to the first and second straight segments 1421. Furthermore, the refrigerant flow channels corresponding to the first and second straight segments 1421 flow in opposite directions.

[0076] In practical applications, the density of heat exchange columns 15 in the refrigerant flow channel region corresponding to the first end 1431 of each straight segment is greater than the density of heat exchange columns 15 in the refrigerant flow channel regions corresponding to the second end 1433 and the middle 1432 of each straight segment. Furthermore, the density of heat exchange columns 15 in the refrigerant flow channel regions corresponding to the second end 1433 and the middle 1432 of the second straight segment 1422 is greater than the density of heat exchange columns 15 in the refrigerant flow channel regions corresponding to the second end 1433 and the middle 1432 of the first straight segment 1421.

[0077] Specifically, to ensure a uniform temperature for each battery cell and prevent any cell from overheating or underheating, which could lead to battery pack or battery failure, the heat exchange columns 15 at the first end 1431 of the first straight section 1421 evenly distribute the water flow as it enters from the inlet 12. The middle section 1432 and the second end 1433 of the first straight section 1421 have sparser heat exchange columns 15 to reduce flow resistance. After the water flows through the corner section 1423, the first end 1431 of the second straight section 1422 continues to evenly distribute the water flow.

[0078] Furthermore, during the first straight segment 1421, the temperature difference between the liquid cooling plate 1 and the refrigerant is relatively large, and the refrigerant absorbs heat and its temperature rises during the flow. Therefore, during the second straight segment 1422, the temperature difference between the liquid cooling plate 1 and the refrigerant is relatively small. Because the heat exchange area of ​​the flow channel is larger and the cross-sectional area is smaller in areas with high density of the heat exchange column 15, the refrigerant flow velocity is faster and the heat transfer coefficient is higher. Therefore, when the refrigerant flows through the first end 1431 and the middle part 1432 of the second straight segment 1422, the temperature rise of the refrigerant will compensate for the temperature difference between the liquid cooling plate 1 and the refrigerant, making the overall temperature difference of the liquid cooling plate 1 smaller, thereby ensuring that the overall temperature difference of the battery pack is smaller.

[0079] Although embodiments of the present invention have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting the present invention. Those skilled in the art can make changes, modifications, substitutions and alterations to the above embodiments within the scope of the present invention without departing from the principles and spirit of the present invention, and all such changes should fall within the protection scope of the claims of the present invention.

Claims

1. A liquid-cooled plate, characterized in that, include: An upper cover plate and a lower cover plate (11) form a main channel (14) between the upper cover plate and the lower cover plate (11); Water inlet (12) is connected to the water inlet (1411) of the main channel (14) and is used for refrigerant inflow; The water outlet (13) is connected to the water outlet (1412) of the main channel (14) corresponding to the water inlet (1411) and is used for refrigerant flow. Multiple heat exchange columns (15) are arranged in the main channel (14), and the density of heat exchange columns (15) in different regions of the main channel (14) is different.

2. The liquid cold plate of claim 1, wherein, Multiple heat exchange columns (15) are arranged alternately within the main flow channel (14); The flow path (144) of the refrigerant in the main channel (14) is wavy or spiral.

3. The liquid cold plate of claim 1, wherein, The density of the heat exchange column (15) at the inlet (1411) of the main channel (14) is greater than the density of the heat exchange column (15) at the outlet (1412) of the main channel (14).

4. The liquid cold plate of claim 1, wherein, The main channel (14) is a straight main channel (14), a curved main channel (14), or a broken line main channel (14); The straight main channel (14) is composed of straight segments; The curved main channel (14) consists of straight segments and arc segments, and the shape of the curve includes U-shape, S-shape or serpentine. The zigzag main channel (14) is composed of straight segments and corner segments (1423), and the angles of the corners include acute angles, right angles, obtuse angles and / or straight angles; The arc-shaped segment or the corner segment (1423) divides the main channel (14) into two or more refrigerant channels, and the heat exchange columns (15) in different regions of different refrigerant channels have different densities.

5. The liquid cold plate of claim 4, wherein, The straight segment includes a first end (1431), a middle part (1432), and a second end (1433) arranged in sequence. The first end (1431) is the inlet (1411) of the refrigerant channel corresponding to the straight segment, and the second end (1433) is the outlet (1412) of the refrigerant channel corresponding to the straight segment. The density of the heat exchange column (15) at the first end (1431) is greater than the density of the heat exchange column (15) in the middle part (1432), and the density of the heat exchange column (15) in the middle part (1432) is greater than or equal to the density of the heat exchange column (15) at the second end (1433).

6. The liquid cold plate of claim 4, wherein, The main channel (14) includes a first channel (1401) and a second channel (1402), which run in the same direction and converge at the beginning and end.

7. The liquid cold plate of claim 6, wherein, A baffle (1403) is provided between the first flow channel (1401) and the second flow channel (1402) to make the refrigerant entering the inlet (1411) form two parallel parts.

8. The liquid cold plate of claim 5, wherein, When the main channel (14) is a curved main channel (14) or a broken line main channel (14), the main channel (14) includes at least two sequentially arranged straight segments, and in two adjacent straight segments: One side of the arc segment connects to the second end of a straight segment (1433), and the other side of the arc segment connects to the first end of another straight segment (1431); or, One side of the corner segment (1423) is connected to the second end (1433) of a straight segment, and the other side of the corner segment (1423) is connected to the first end (1431) of another straight segment.

9. The liquid cooling plate according to claim 5, characterized in that, The main road (14) is a broken line type main road (14), and includes a first straight line segment (1421), a second straight line segment (1422) and a corner segment (1423) with a flat angle; One side of the angled corner segment (1423) is connected to the second end (1433) of the first straight segment (1421), and the other side of the angled corner segment (1423) is connected to the first end (1431) of the second straight segment (1422), so as to connect the refrigerant flow channel corresponding to the first straight segment (1421) and the refrigerant flow channel corresponding to the second straight segment (1422). The refrigerant flow path corresponding to the first straight segment (1421) and the refrigerant flow path corresponding to the second straight segment (1422) flow in opposite directions.

10. The liquid cold plate of claim 1, wherein, The density of heat exchange columns (15) in the inlet (1411) region of the main channel (14) is 15~20 columns / cm2, and the density of heat exchange columns (15) in the outlet (1412) region of the main channel (14) is 5~10 columns / cm2. The refrigerant has a flow velocity of 0.5 m / s to 2 m / s in the main flow channel (14).

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