Two-phase cold plate, liquid cooling device, and electronic device

Abstract

The application discloses a two-phase cold plate, a liquid cooling device and electronic equipment, and belongs to the technical field of heat exchange. The two-phase cold plate comprises a plurality of plate bodies which are spaced apart and oppositely arranged along a first direction. The two oppositely arranged plate bodies respectively comprise a first wall surface and a second wall surface which are oppositely arranged along the first direction, so as to define a heat exchange flow channel between the two oppositely arranged plate bodies. The first wall surface comprises a plurality of first sub-wall surfaces which are adjacently arranged, and the second wall surface comprises a plurality of second sub-wall surfaces which are adjacently arranged along a flow direction defined by the heat exchange flow channel, and the flow direction intersects the first direction. The first intersection point and the second intersection point are arranged in a staggered manner along the flow direction. Through the above technical scheme, the heat exchange working medium can also maintain uniform gas-liquid two-phase distribution in the entire heat exchange flow channel, and problems such as bubble retention and local dryness are avoided.

Description

Technical Field

[0001] This application relates to the field of heat exchange technology, and in particular to a two-phase cold plate, a liquid cooling device, and electronic equipment. Background Technology

[0002] As the computing power requirements for training large-scale artificial intelligence models continue to increase, the heat flux density of mainstream server chips has exceeded 800~1200 W / cm². Traditional single-phase liquid cooling technology, which relies on the sensible heat absorption of liquid, can no longer meet the heat dissipation requirements of the next generation of high-performance electronic devices.

[0003] Among related technologies, microchannel two-phase cooling, with its latent heat transfer characteristics, achieves a heat transfer coefficient 5 to 10 times that of single-phase liquid cooling. Its compact structure makes it a core heat dissipation path in high heat flux density scenarios. The flow boiling scheme further reduces flow resistance and optimizes temperature uniformity. However, existing flow boiling schemes still have design limitations regarding the evolution of the flow channel cross-section and the multi-channel flow distribution mechanism: under high heat flux density conditions, bubbles near the wall tend to adhere and aggregate, forming an adiabatic gas film. This, along with issues such as localized backflow and uneven flow distribution, can lead to localized drying and wall overheating, resulting in poor heat transfer stability and long-term reliability of the two-phase cold plate. Summary of the Invention

[0004] This application provides a two-phase cold plate, a liquid cooling device, and an electronic device to at least partially solve the above-mentioned technical problems.

[0005] In a first aspect, this application provides a two-phase cold plate, the two-phase cold plate comprising a plurality of plates spaced apart and arranged opposite to each other along a first direction, wherein two oppositely arranged plates each comprise a first wall surface and a second wall surface arranged opposite to each other along the first direction, thereby defining a heat exchange channel between the two oppositely arranged plates. Along the flow direction defined by the heat exchange channel, the first wall surface includes a plurality of adjacent first sub-wall surfaces, and the second wall surface includes a plurality of adjacent second sub-wall surfaces, wherein the flow direction intersects with the first direction; Wherein, two adjacent first sub-walls are defined as first wall units, and two adjacent second sub-walls are defined as second wall units. The first wall unit includes a first intersection point where the two first sub-walls intersect, and the second wall unit includes a second intersection point where the two second sub-walls intersect. The first intersection point and the second intersection point are staggered along the flow direction.

[0006] In some embodiments, the misalignment distance between the first intersection point and the second intersection point along the flow direction is d, the dimension of the first wall unit along the flow direction is L1, and the dimension of the second wall unit along the flow direction is L2. Then d satisfies L1 and L2: 0 <d<min(L1,L2)。

[0007] In some embodiments, the first wall surface includes two adjacent first sub-wall surfaces, one of which has an unfolded dimension of a1, and the second wall surface includes two adjacent second sub-wall surfaces, one of which is disposed opposite to the first sub-wall surface, and the unfolded dimension of the second sub-wall surface is a2. Then a1 and a2 satisfy: a1=a2.

[0008] In some embodiments, the unfolded dimension of the other first sub-wall of the two adjacent first sub-walls included in the first wall is b1, and the unfolded dimension of the other second sub-wall of the two adjacent second sub-walls included in the second wall, which is disposed opposite to the first sub-wall, is b2. Then b1 and b2 satisfy: b1=b2.

[0009] In some embodiments, the two adjacent first sub-walls included in the first wall have unfolded dimensions a1 and b1 in the flow direction, respectively, and a1 and b1 satisfy: a1=b1.

[0010] In some embodiments, the two adjacent second sub-walls included in the second wall have unfolded dimensions a2 and b2 in the flow direction, respectively, and a2 and b2 satisfy: a2=b2.

[0011] In some embodiments, when the two adjacent first sub-walls have the same unfolded dimensions in the flow direction, and the two adjacent second sub-walls included in the second wall have the same unfolded dimensions in the flow direction, the unfolded dimensions of the first sub-walls included in the first wall and the unfolded dimensions of the second sub-walls included in the second wall are set to be equal in the flow direction.

[0012] In some embodiments, the first wall surface includes a first included angle between two adjacent first sub-wall surfaces, and the second wall surface includes a second included angle between two adjacent second sub-wall surfaces, wherein the first included angle and the second included angle are set to be equal.

[0013] In some embodiments, the dimension of the first wall unit along the flow direction is L1, and the dimension of the second wall unit along the flow direction is L2. Then, L1 and L2 satisfy: L1 = L2.

[0014] In some embodiments, the first wall includes two adjacent first sub-walls, one of which has an unfolded dimension of a1, and the second wall includes two adjacent second sub-walls, one of which is disposed opposite to the first sub-wall, has an unfolded dimension of a2. Then a1 and a2 satisfy: a1≠a2.

[0015] In some embodiments, the unfolded dimension of the other first sub-wall of the two adjacent first sub-walls included in the first wall is b1, and the unfolded dimension of the other second sub-wall of the two adjacent second sub-walls included in the second wall, which is disposed opposite to the first sub-wall, is b2. Then b1 and b2 satisfy: b1≠b2.

[0016] In some embodiments, the two adjacent first sub-walls included in the first wall have unfolded dimensions a1 and b1 in the flow direction, respectively, and a1 and b1 satisfy: a1≠b1.

[0017] In some embodiments, the two adjacent second sub-walls included in the second wall have unfolded dimensions a2 and b2 in the flow direction, respectively, and a2 and b2 satisfy: a2≠b2.

[0018] In some embodiments, when the unfolded dimensions of the two adjacent first sub-walls in the flow direction are set to be different, and the unfolded dimensions of the two adjacent second sub-walls included in the second wall are set to be different in the flow direction, the two adjacent first sub-walls included in the first wall have a first included angle, and the two adjacent second sub-walls included in the second wall have a second included angle, wherein the first included angle and the second included angle are set to be different.

[0019] In some embodiments, the two-phase cold plate further includes a plurality of fins; at least one of the fins is provided protruding on both the first sub-wall surface and the second sub-wall surface; Along the flow direction, the fins located on the first sub-wall are offset and parallel to the fins located on the second sub-wall.

[0020] In some embodiments, along the height direction of the plate, the fins located on the first sub-wall and the fins located on the second sub-wall are at different height positions.

[0021] In some embodiments, the two-phase cold plate further includes a fluid distribution component located on one side of the plate along the height direction of the plate body; The fluid distribution component has a first fluid distribution channel and a second fluid distribution channel connected through the heat exchange channel. The first fluid distribution channel defines a first fluid direction, which is parallel to the second fluid distribution channel defines a second fluid direction, and both are perpendicular to the flow direction.

[0022] In some embodiments, the two-phase cold plate further includes: Substrate, the plate bodies are sequentially spaced on the substrate along a first direction; and A cover is disposed on the substrate to form a receiving space with the substrate, and the cover is disposed within the receiving space; The cover has a liquid inlet and a liquid outlet, and the fitted flow direction defined by the fluid path from the liquid inlet to the liquid outlet intersects or is parallel to the flow direction.

[0023] In a second aspect, a liquid cooling device is provided, comprising a two-phase cold plate as described above.

[0024] Thirdly, an electronic device is provided, including a heating element and a two-phase cold plate as described above or a liquid cooling device as described above.

[0025] In the two-phase cold plate of this application embodiment, the two-phase cold plate includes multiple plates spaced apart and arranged opposite to each other along a first direction. Each pair of oppositely arranged plates includes a first wall and a second wall arranged opposite to each other along the first direction, defining a heat exchange channel between the two oppositely arranged plates. Along the flow direction defined by the heat exchange channel, the first wall includes multiple adjacent first sub-walls, and the second wall includes multiple adjacent second sub-walls. The flow direction intersects with the first direction. Two adjacent first sub-walls are defined as a first wall unit, and two adjacent second sub-walls are defined as a second wall unit. A first wall unit includes a first intersection point where the two first sub-walls intersect, and a second wall unit includes a second intersection point where the two second sub-walls intersect. The first and second intersection points are staggered along the flow direction. Through the above technical solution, on the one hand, the heat exchange medium can maintain a stable gas-liquid two-phase distribution throughout the heat exchange channel, avoiding heat transfer deterioration and flow instability caused by bubble aggregation, thus improving the heat transfer performance and flow stability of two-phase flow under high heat flux density. Based on the technical solution of staggering the first and second intersection points along the flow direction, the heat exchange medium can achieve more complex turbulent flow behavior. Even under high heat flux density conditions, the heat exchange medium can maintain a uniform gas-liquid two-phase distribution in the entire heat exchange channel, avoiding problems such as bubble retention and local drying.

[0026] Other features and advantages of this application will be described in detail in the following detailed description section. Attached Figure Description

[0027] To more clearly illustrate the technical solutions in the embodiments of this application, the accompanying drawings used in the description of the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0028] To gain a more complete understanding of this application and its beneficial effects, the following description will be provided in conjunction with the accompanying drawings, wherein the same reference numerals in the following description denote the same parts.

[0029] Figure 1 This is an exploded view of the overall structure of the two-phase cold plate provided in an exemplary embodiment of this application; Figure 2 This is a schematic diagram of the positional structure of the two-phase cold plate and the substrate provided in an exemplary embodiment of this application; Figure 3 yes Figure 2 An enlarged schematic diagram of part A in the middle; Figure 4 yes Figure 3 Enlarged schematic diagram of part B; Figure 5 This is a schematic diagram of the positional structure of the plate and substrate of another two-phase cold plate provided in an exemplary embodiment of this application; Figure 6 yes Figure 5 An enlarged schematic diagram of section C; Figure 7 yes Figure 6 An enlarged schematic diagram of section D in the middle; Figure 8 This is a schematic diagram of the positional structure of another two-phase cold plate provided in an exemplary embodiment of this application; Figure 9 yes Figure 8 An enlarged schematic diagram of section E in the middle; Figure 10 yes Figure 8 A top-view schematic diagram of the overall structure of the two-phase cold plate; Figure 11 yes Figure 10 Enlarged schematic diagram of section H in the middle; Figure 12 yes Figure 8 A frontal view of the overall structure of the two-phase cold plate shown; Figure 13 This is a schematic diagram of the positional structure of another two-phase cold plate provided in an exemplary embodiment of this application; Figure 14 yes Figure 13 Enlarged schematic diagram of section J in the middle; Figure 15 yes Figure 14 A frontal view of the overall structure of the two-phase cold plate shown; Figure 16 This is a schematic diagram of the positional structure of another two-phase cold plate provided in an exemplary embodiment of this application; Figure 17 yes Figure 16A top-view schematic diagram of the overall structure of the two-phase cold plate; Figure 18 This is a schematic diagram showing that the fitting flow direction is perpendicular to the flow direction in an exemplary embodiment of this application.

[0030] Explanation of reference numerals in the attached figures: 10. Two-phase cold plate; 100. Plate body; 100a. Heat exchange channel; 110. The first wall; 111. The first sub-wall; 120. Second wall; 121. Second sub-wall; 200, fin; 400, substrate; 500, cover; 500a, liquid inlet; 500b, liquid outlet; F3, fitted flow direction; 300, fluid distribution component; 300a, first fluid distribution channel; 300b, second fluid distribution channel; F1, First fluid direction; F2, Second fluid direction; F, Flow direction; A1, First wall element; A2, Second wall element; M1, First intersection point; M2, Second intersection point. Detailed Implementation

[0031] The technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only a part of the embodiments of this application, and not all of them. All other embodiments obtained by those skilled in the art based on the embodiments of this application without creative effort are within the protection scope of this application. Furthermore, it should be understood that the specific embodiments described herein are only for illustration and explanation of this application and are not intended to limit this application.

[0032] In this application, unless otherwise stated, directional terms such as "upper" and "lower" generally refer to the upper and lower positions of the device in its actual use or operating state, specifically the drawing directions in the accompanying drawings; while "inner" and "outer" refer to the outline of the device. Furthermore, in the description of this application, the term "comprising" means "including but not limited to". The terms first, second, third, etc., are used merely as illustrative purposes and do not impose numerical requirements or establish a numerical order.

[0033] In this application, "and / or" describes the relationship between related objects, indicating that three relationships can exist. For example, A and / or B can represent: A existing alone, A and B existing simultaneously, or B existing alone. A and B can be singular or plural.

[0034] In the description of this application, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "linking" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection between two components. Those skilled in the art can understand the specific meaning of the above terms in this application according to the specific circumstances.

[0035] The use of "applies to" or "configured to" in this application implies open and inclusive language, which does not exclude the applicability to or configuration to devices performing additional tasks or steps. Additionally, the use of "based on" implies openness and inclusivity, because processes, steps, calculations, or other actions "based on" one or more of the stated conditions or values ​​may in practice be based on additional conditions or values ​​beyond those stated.

[0036] In this application, the term "exemplary" is used to mean "used as an example, illustration, or description." Any embodiment described as "exemplary" in this application is not necessarily to be construed as being more preferred or advantageous than other embodiments. The following description is provided to enable any person skilled in the art to make and use this application. Details are set forth in the following description for purposes of explanation. It should be understood that those skilled in the art will recognize that this application can be made without using these specific details. In other instances, well-known structures and processes are not described in detail to avoid obscuring the description of this application with unnecessary detail. Therefore, this application is not intended to be limited to the embodiments shown, but is consistent with the broadest scope of the principles and features disclosed in this application.

[0037] Based on the technical problems mentioned in the background, in the existing microchannel two-phase cooling technology field, the working fluid undergoes phase change vaporization during operation to enhance heat transfer by utilizing latent heat. Under high heat flux density conditions, the working fluid experiences bubble retention in the flow channel, accompanied by problems such as local backflow and uneven flow distribution. Bubbles adhere to the wall surface, causing the formation of local dry areas, which in turn leads to a decrease in heat transfer performance and reduced flow stability. In particular, bubble retention causes large bubbles to accumulate in the flow channel and may develop into embolisms, which seriously restricts the reliable operation of the heat dissipation system.

[0038] For example, in the heat dissipation application of high-density artificial intelligence servers in data centers, when the server chip is under high load, the heat flux density in the microchannel of the cold plate increases, and the heat exchange medium generates bubbles due to boiling. The bubbles continuously adhere to the wall in the flow channel and coalesce to form large bubbles, causing uneven local temperature distribution and increased flow resistance. The system's operational stability is directly affected, and the backflow phenomenon further exacerbates the bubble retention problem, leading to a deterioration in heat exchange efficiency.

[0039] If the aforementioned bubble retention problem is not resolved, bubble plugging may completely block the flow channel, causing the cooling function to fail, the chip temperature to continue to rise, the risk of hardware damage to increase, and the reliability of the heat dissipation system to decrease significantly, thus having adverse consequences for the long-term stable operation of high-density computing devices.

[0040] Based on this, this application provides a two-phase cold plate 10, a liquid cooling device, and an electronic device that can improve heat dissipation efficiency.

[0041] The first aspect of this application, with reference to Figure 1 , Figure 2 and Figure 3 A two-phase cold plate 10 is provided, comprising a plurality of plates 100 spaced apart and arranged opposite to each other along a first direction. Each pair of oppositely arranged plates 100 includes a first wall surface 110 and a second wall surface 120 arranged opposite to each other along the first direction, defining a heat exchange channel 100a between the two oppositely arranged plates 100. Along the flow direction F defined by the heat exchange channel 100a, the first wall surface 110 includes a plurality of adjacent first sub-wall surfaces 111, and the second wall surface 120 includes a plurality of adjacent second sub-wall surfaces 121. The flow direction F intersects with the first direction.

[0042] Wherein, two adjacent first sub-walls 111 are defined as first wall unit A1, and two adjacent second sub-walls 121 are defined as second wall unit A2. Then, the first wall unit A1 includes the first intersection point M1 where the two first sub-walls 111 intersect, and the second wall unit A2 includes the second intersection point M2 where the two second sub-walls 121 intersect. The first intersection point M1 and the second intersection point M2 are staggered along the flow direction F.

[0043] It should be understood that the plate 100 in this embodiment is a component constituting the main structure of the two-phase cold plate 10, and is typically made of a thermally conductive material. It defines the heat exchange channel 100a and exchanges heat with the heating element. Exemplarily, the plate 100 can be formed using different materials and manufacturing processes, such as connecting thin metal plates by stamping, welding, or brazing. The plates 100 are arranged at a predetermined spacing to define the heat exchange channel 100a for the flow of the heat exchange medium. For example, multiple parallel copper or aluminum plates can be used. The heat exchange channel 100a defined between two oppositely arranged plates 100 is the channel through which the heat exchange medium flows within the two-phase cold plate 10. The flow direction F is the overall direction in which the heat exchange medium moves within the heat exchange channel 100a.

[0044] refer to Figure 4In this embodiment, the first wall surface 110 and the second wall surface 120 are two opposing inner surfaces defining the heat exchange channel 100a. The heat exchange medium flows between the first wall surface 110 and the second wall surface 120 and exchanges heat. The first sub-wall surface 111 and the second sub-wall surface 121 are partial wall surface segments constituting the first wall surface 110 and the second wall surface 120, respectively. The first sub-wall surface 111 and the second sub-wall surface 121 are respectively arranged opposite to each other along the flow direction F, together forming the overall contour of the corresponding wall surface. In this embodiment, the first wall surface 110 may be composed of a series of alternating first sub-wall surfaces 111, forming a sawtooth or wavy contour. The second wall surface 120 may also be composed of similar or different second sub-wall surfaces 121.

[0045] Please continue to refer to this. Figure 3 The first wall unit A1 is a periodic structural unit constructed from two adjacent first sub-walls 111, and is a repeating unit constituting the geometry of the first wall 110. The second wall unit A2 is a periodic structural unit constructed from two adjacent second sub-walls 121, and is a repeating unit constituting the geometry of the second wall 120.

[0046] The first intersection point M1 is the connection point of two adjacent first sub-walls 111 in the first wall unit A1, and the second intersection point M2 is the connection point of two adjacent second sub-walls 121 in the second wall unit A2. The first intersection point M1 and the second intersection point M2 are offset along the flow direction F, meaning that they are not directly aligned in the flow direction F, but rather have a certain relative displacement, which can affect the fluid dynamics and heat transfer characteristics within the flow channel. The first intersection point M1 is the turning point (e.g., the apex of a crest or trough) connecting two adjacent first sub-walls 111. Similarly, the second intersection point M2 is the turning point (e.g., the apex of a crest or trough) connecting two adjacent second sub-walls 121112. Referring to the figure, in the embodiments of this application, the first intersection point M1 and the second intersection point M2 are both the apex of the crests of the corresponding sub-walls.

[0047] Therefore, by staggering the first intersection point M1 and the second intersection point M2, more complex fluid disturbances and mixing can be generated within the heat exchange channel 100a. When the heat exchange medium flows through the staggered intersection points and sub-walls, the fluid boundary layer is periodically disrupted and rebuilt, thereby enhancing the heat transfer effect near the wall. For example, at the first intersection point M1, the fluid may be accelerated or deflected, while at the second intersection point M2, the fluid will experience different disturbances. Because these intersection points are staggered, the fluid path within the channel becomes more tortuous, increasing local shear forces, which helps to suppress bubble adhesion and growth and promotes timely bubble detachment. As a result, the flow of the heat exchange medium within the heat exchange channel 100a is more uniform, avoiding localized drying and wall overheating, thereby improving the heat transfer stability and long-term reliability of the two-phase cold plate 10.

[0048] Furthermore, the periodic arrangement of the sub-walls provides continuous turning and impact, generating strong turbulent disturbances within the heat exchange channel 100a. This enhances convective heat transfer between the heat exchange medium and the first wall 110 and second wall 120, improving the efficiency of heat transfer from the heating element to the heat exchange medium. On the other hand, the heat exchange medium impacts the walls of the heat exchange channel 100a more frequently and intensely, accelerating bubble formation and detachment, preventing the formation and attachment of large bubbles. The turbulent disturbances generated within the heat exchange channel 100a can impact bubbles attached to the first wall 110 and second wall 120. Due to the frequent impact of the heat exchange medium on the first wall 110 and second wall 120, small bubbles generated on the walls are less likely to remain in localized areas for extended periods and aggregate into large bubbles. Even if bubbles do form, the strong turbulence breaks them into smaller bubbles, which are then carried away by the heat exchange medium.

[0049] Through the above technical solution, on the one hand, the heat transfer medium can maintain a stable gas-liquid two-phase distribution throughout the entire heat exchange channel 100a, avoiding heat transfer deterioration and flow instability caused by bubble aggregation, thus improving the heat transfer performance and flow stability of two-phase flow under high heat flux density. Based on the technical solution of staggering the first intersection point M1 and the second intersection point M2 in the flow direction F, the heat transfer medium can achieve more complex turbulent flow behavior. Even under high heat flux density conditions, the heat transfer medium can maintain a uniform gas-liquid two-phase distribution throughout the entire heat exchange channel 100a, avoiding problems such as bubble retention and localized drying. This technical solution is structurally simple, easy to implement, and effectively suppresses phenomena such as bubble retention, localized drying, and bubble embolism blocking the flow channel that exist in related technologies.

[0050] To improve the stability of two-phase heat transfer, in some embodiments, please refer to... Figure 3 Let the dimensions of the first wall element A1 and the second wall element A2 along the flow direction F be L, and the misalignment distance between the first intersection point and the second intersection point M2 along the flow direction F be d. Then d satisfies L1 and L2: 0 <d<min(L1,L2)。

[0051] It should be understood that the misalignment distance d refers to the relative displacement of the first intersection point M1 and the second intersection point M2 along the flow direction F. By adopting this technical solution, the two side walls of the flow channel are not completely symmetrical or parallel, but form a misaligned structure.

[0052] The dimension L1 of the first wall surface unit A1 along the flow direction F refers to the distance along the flow direction F between two opposite ends of two adjacent first sub-wall surfaces 111 that form the first wall surface unit A1 along the flow direction F, which defines the length of the disturbance region experienced by the heat exchange working fluid when passing through the first wall surface unit A1. For example, the dimension L1 can be adjusted by changing the length of the first sub-wall surface 111.

[0053] The dimension L2 of the second wall surface unit A2 along the flow direction F refers to the distance along the flow direction F between two opposite ends of two adjacent second sub-wall surfaces 121 that form the second wall surface unit A2 along the flow direction F, which defines the length of the disturbance region experienced by the heat exchange working fluid when passing through the second wall surface unit A2. For example, the dimension L2 can be adjusted by changing the length of the second sub-wall surface 121.

[0054] The condition satisfied by d, L1 and L2, which is 0<d<min(L1, L2), defines the value range of the staggered distance d, ensuring that there is effective staggering between the first intersection point M1 and the second intersection point M2, and the staggering amount is neither too large nor too small. Wherein, min(L1, L2) represents the smaller value between L1 and L2. The function of this condition is to ensure that the fluid can generate effective disturbance when passing through the staggered structure, avoiding the problem that the disturbance effect is not obvious when the heat exchange working fluid goes around the disturbance structure, and preventing flow channel blockage or sharp increase of pressure drop caused by excessive staggering. This enables the heat exchange working fluid to be subjected to effective periodic impact and disturbance when flowing through each wall surface unit, and meanwhile avoids the negative effects brought by extreme geometric configurations.

[0055] Through the above technical solution, that is, defining the dimension L of the wall surface unit along the flow direction F and the staggered distance d, and making them satisfy 0<d<min(L1, L2), the present application can effectively solve the problems of non-uniform flow impact intensity distribution, local flow dead zone or excessive flow resistance in the heat exchange flow channel 100a caused by the lack of definite constraints on the proportion between the staggered distance and the overall dimension of the wall surface unit in traditional solutions. On one hand, it ensures that when the heat exchange working fluid flows through the heat exchange flow channel 100a, it can continuously and uniformly be subjected to periodic wall impact and turbulent disturbance, so that the heat exchange working fluid can more effectively break the bubble field and accelerate the separation of bubbles from the wall surface while enhancing boiling heat exchange, thereby significantly inhibiting the retention of bubbles and the formation of large bubbles. On the other hand, by limiting the staggered distance d between 0 and min(L1, L2), it avoids the violent fluctuation of the effective flow cross-sectional area of the flow channel caused by excessive staggering, thereby effectively reducing unnecessary flow resistance and ensuring the stability of flow. While achieving efficient two-phase heat exchange, it significantly improves the uniformity and controllability of the disturbance of the heat exchange working fluid in the flow channel, effectively avoids local dry-out and heat transfer deterioration, thereby improving the overall heat dissipation performance and operation reliability of the two-phase cold plate 10.

[0056] By way of example, taking the wall units configured as zigzag units, the dimension of the zigzag unit corresponding to the first wall unit A1 in the flow direction F can be set as L1, for example, L1 may be 6 mm, and the dimension of the zigzag unit corresponding to the second wall unit A2 in the flow direction F can be set as L2, for example, L2 may be 7 mm. Then min(L1, L2) is 6 mm. In order to ensure the effectiveness of heat exchange working fluid disturbance and flow stability, the staggered distance d can be set as 1 millimeter. At this time, the staggered distance d and the projection dimension L satisfy 0 < 1 mm < 6 mm, that is, 0 < d < min(L1, L2). In this way, when the heat exchange working fluid flows through the heat exchange flow channel 100a, due to the 1-millimeter stagger between the first intersection point M1 and the second intersection point M2, the heat exchange working fluid will be periodically guided to impact the two side wall surfaces, thereby generating local vortices and turbulence, effectively destroying the boundary layer and promoting boiling heat exchange. At the same time, since the staggered distance d is limited to a range smaller than the dimension of any wall unit, fluid short-circuiting or local dead zones that may be caused by excessive staggering are avoided, and insufficient disturbance caused by too small staggering is also prevented, so that the fluid can form a more uniform and effective disturbance flow field in the heat exchange flow channel 100a, thereby significantly improving the overall heat exchange efficiency of the two-phase cold plate 10 on the premise of ensuring a reasonable pressure drop.

[0057] In some embodiments, the staggered distance d and the projection dimension L satisfy: d = 0.25×min(L1, L2).

[0058] Through the above technical solution, setting the staggered distance d as a quarter of the projection dimension L effectively solves the problem of uneven distribution of impact disturbance intensity on the two side wall surfaces of the flow channel. The technical solution of d = 0.25×min(L1, L2) forms a structure of quarter-period staggered arrangement, which provides uniform and symmetrical disturbance of the heat exchange working fluid in the full length range of the heat exchange flow channel 100a, enabling the heat exchange working fluid to continuously and efficiently impact the first wall surface 110 and the second wall surface 120, thereby significantly enhancing the turbulent boiling heat exchange effect. While maximizing the bubble breaking efficiency, the flow resistance in the heat exchange flow channel 100a is optimized, local high-resistance regions or flow dead zones caused by improper staggered distance are avoided, and the optimal balance between heat exchange performance and flow resistance is achieved.

[0059] In other achievable embodiments, the staggered distance d and the projection dimension L may also satisfy: d = 0.4×min(L1, L2), 0.5×min(L1, L2), 0.6×min(L1, L2), 0.7×min(L1, L2), which is subject to actual settings.

[0060] In some embodiments, the first wall 110 includes two adjacent first sub-walls 111, one of which has an unfolded dimension of a1, and the second wall 120 includes two adjacent second sub-walls 121, one of which is disposed opposite to the first sub-wall 111, has an unfolded dimension of a2. Then a1 and a2 satisfy: a1=a2.

[0061] It should be understood that "relative arrangement" refers to two sub-walls being opposite each other in the flow channel width direction perpendicular to the flow direction F and the first direction. For example, the first wall unit A1 of the first wall 110 is constructed as a sawtooth structure, wherein the unfolded dimension a1 of the forward-leaning first sub-wall 111a along the flow direction F is 5 mm, and the corresponding second sub-wall 121a in the second wall unit A2 of the second wall 120 opposite to it in the flow channel width direction is also set to have an unfolded dimension a2 of 5 mm along the flow direction F.

[0062] By setting the unfolded dimensions of the corresponding first sub-wall 111 and second sub-wall 121 to be equal, it can be ensured that the disturbance intensity of the heat transfer medium impacting the two walls remains balanced when flowing through the staggered first wall unit A1 and second wall unit A2. On the one hand, when the heat transfer medium impacts the second sub-wall 121 from the first sub-wall 111, the size-matched a1 and a2 can prevent the fluid from impacting the dead corner of the flow channel due to one side being too short, or from causing a sudden increase in local flow resistance due to one side being too long, thus ensuring the stability of periodic turbulent disturbances. On the other hand, it can keep the nucleation and detachment frequency of bubbles on both walls consistent, avoiding temperature unevenness caused by bubble retention on one side.

[0063] It should be noted that in this example, it is not limited to a fully symmetrical layout where a1=a2 and b1=b2. That is, as long as a1=a2 and b1≠b2 is satisfied (i.e., the two first sub-walls 111 of the first wall 110 have different unfolded dimensions), the needs of flow field control can be met as long as the unfolded dimensions of the corresponding upper and lower sub-walls satisfy a1=a2.

[0064] In some embodiments, the unfolded dimension of the other first sub-wall 111 of the two adjacent first sub-walls 111 included in the first wall 110 is b1, and the unfolded dimension of the other second sub-wall 121 of the two adjacent second sub-walls 121 included in the second wall 120, which is disposed opposite to the first sub-wall 111, is b2. Then b1 and b2 satisfy: b1=b2.

[0065] It should be understood that in this example, the first sub-wall 111, which includes two adjacent first sub-walls 111, refers to another first sub-wall 111 within the same wall unit, and the unfolded dimension of the other first sub-wall 111 along the flow direction F is b1. In this example, the second sub-wall 121, which is disposed opposite to the other first sub-wall 111, has an unfolded dimension of b2 along the flow direction F. Therefore, b1 = b2.

[0066] For example, the unfolded dimension b1 of the first sub-wall 111b is set to 3mm, and the unfolded dimension b2 of the second sub-wall 121b directly opposite it is also set to 3mm.

[0067] By setting the unfolded dimensions of another set of first sub-walls 111 and second sub-walls 121 that are relatively arranged to be equal, a synergistic effect can be achieved with the aforementioned a1=a2 setting corresponding to the first set of first sub-walls 111 and second sub-walls 121. That is, when the heat exchange medium flows along the flow direction F, it first impacts the first set of first sub-walls 111 and second sub-walls 121 with matching dimensions, completing the first periodic turbulent disturbance. Then it turns to impact the other set of first sub-walls 111 and second sub-walls 121. Since b1=b2, the wall constraint strength of the fluid is consistent. It will not cause the fluid to flow into the dead corner of the flow channel due to one side of the sub-wall being too short, nor will it cause a sudden increase in local flow resistance due to one side of the sub-wall being too long. This ensures the continuity of the disturbance intensity throughout the entire flow cycle and further avoids bubbles from attaching, coalescing, and forming a gas film in the latter half of the flow channel.

[0068] In this example, an asymmetric layout can be set where b1=b2 and a1≠a2, so that the large bubble can be broken in advance by differentiating the first half.

[0069] It should be understood that in the aforementioned technical solution, the length L1 of the first wall unit A1 and the length L2 of the second wall unit A2 can be different dimensions. For example, a1 corresponding to the first sub-wall 111a and a2 corresponding to the second sub-wall 121a are set to be equal, while b1 corresponding to the first sub-wall 111121b and b2 corresponding to the second sub-wall 121a are set to be unequal. Since L1≠L2 (e.g., L1 is less than L2), the first included angle σ1 and the second included angle σ2 are also unequal, that is, σ1 is less than σ2. In this example, only a1=a2, so the first wall unit A1 and the second wall unit A2 have different shapes.

[0070] In some embodiments, the two adjacent first sub-walls 111 included in the first wall 110 are set to have equal unfolded dimensions in the flow direction F.

[0071] That is, reference Figure 4The unfolded dimensions of the two adjacent first sub-walls 111 included in the first wall 110 in the flow direction F can be defined as a1 and b1 respectively, then a1=b1 in the same first wall unit A1.

[0072] In the first wall 110, the unfolded dimensions of two adjacent first sub-walls 111 in the flow direction F are set to be equal. That is, the unfolded dimensions of the first sub-walls 111 constituting the first wall 110 in the flow direction F are uniform. In this way, it can be ensured that the geometric constraints and disturbances experienced by the heat exchange medium when flowing through the first wall 110 are periodic and consistent. For example, the first sub-wall 111 may be composed of a series of inclined segments with the same horizontal dimension, forming a sawtooth or wavy structure; or, the first sub-wall 111 may be composed of a series of arc segments with the same chord length or arc length projection, and the first wall 110 formed is wavy.

[0073] In some embodiments, the two adjacent second sub-walls 121 included in the second wall 120 are set to have equal unfolded dimensions in the flow direction F.

[0074] In other words, please continue to refer to [the relevant information]. Figure 4 The unfolded dimensions of the two adjacent second sub-walls 121 included in the second wall 120 in the flow direction F can be defined as a2 and b2 respectively, then a2=b2 in the same second wall unit A2.

[0075] In the second wall 120, the two adjacent second sub-walls 121 included therein have their unfolded dimensions in the flow direction F equal. That is, the unfolded dimensions of the second sub-walls 121 constituting the second wall 120 in the flow direction F are uniform, making the second wall 120 have geometric periodicity and consistent disturbance in the flow direction F. Exemplarily, the second sub-wall 121 can adopt a similar structural form to the first sub-wall 111, for example, consisting of a series of inclined segments, wavy segments, or arc-shaped segments with the same horizontal projection size. This equal setting of unfolded dimensions provides a stable disturbance environment for the heat exchange medium.

[0076] In this embodiment, based on the aforementioned staggered arrangement of the two wall units, this embodiment ensures that the unfolded dimensions of adjacent sub-walls in the first wall 110 or the second wall 120 are consistent. This ensures that the state that the cooling medium can be changed by remains highly consistent as the heat exchange medium flows through each periodic wall unit. That is, the identical unfolded dimensions ensure that the periodic disturbances experienced by the heat exchange medium in the flow direction F are highly regular. The heat exchange medium can obtain uniform turbulent disturbance intensity over the entire flow channel length, thereby ensuring uniform and efficient bubble breakage throughout the entire flow channel length. This prevents bubbles from coalescing or stagnating in specific areas due to insufficient disturbance, improves the stability of the gas-liquid two-phase flow within the heat exchange channel 100a, ensures continuous efficient heat exchange, effectively suppresses localized drying and heat transfer deterioration, and further enhances the overall heat dissipation performance and reliability of the two-phase cold plate 10.

[0077] In some embodiments, when the two adjacent first sub-walls 111 included in the first wall unit A1 have the same unfolded dimensions in the flow direction F, and the two adjacent second sub-walls 121 included in the second wall unit have the same unfolded dimensions in the flow direction F, the unfolded dimensions of the first sub-wall 111 in the flow direction F and the unfolded dimensions of the second sub-wall 121 in the flow direction F are set to be equal.

[0078] In this configuration, the two adjacent first sub-walls 111 of the first wall unit A1 have equal unfolded dimensions in the flow direction F, i.e., a1 = b1. Similarly, the two adjacent second sub-walls 121 of the second wall unit A2 have equal unfolded dimensions in the flow direction F, i.e., a2 = b2. The unfolded dimensions of the first sub-wall 111 and the second sub-wall 121 in the flow direction F are also equal, i.e., a1 = b1 = a2 = b2.

[0079] Through the above technical solution, by setting the dimensions of the wall units on both sides of the flow channel symmetrically to achieve consistency in the dynamic characteristics of the heat exchange medium inside the heat exchange flow channel 100a, the unfolded dimensions of the sub-wall of the first wall 110 and the sub-wall of the second wall 120 are further set to be equal. In this way, the two walls can provide synchronous constraints when the heat exchange medium flows through the flow channel, and the disturbance frequency of the heat exchange medium in the flow channel tends to be consistent with that of the two walls, thereby generating more regular and controllable turbulent disturbances on the cross-section of the heat exchange flow channel 100a. On the one hand, it can effectively avoid flow field turbulence caused by excessive differences in the dimensions of the two side walls, ensuring that the heat exchange medium can impact the wall in a more stable manner within the flow channel, thereby more efficiently breaking up the bubble field and suppressing the formation of large bubbles, thus improving the overall heat exchange stability of the cold plate. On the other hand, combined with the structure of the first intersection point M1 and the second intersection point M2 being staggered, the impact effect of the staggered structure on the heat exchange medium is further enhanced, so that the heat exchange medium can more effectively generate strong turbulent disturbances under periodic staggered impact, thereby accelerating the generation and detachment of bubbles, avoiding the formation and attachment of large bubbles, and effectively breaking up the bubble field, preventing bubbles from accumulating and forming emboli that block the flow channel, thereby improving the overall heat exchange stability of the two-phase cold plate 10.

[0080] For example, please continue to refer to Figure 4 Given a1=b1 and a2=b2, we set a1=b1=a2=b2. For example, we can set a1, a2, b1, and b2 to 10 mm to ensure that the geometric periodicity of the upper and lower side walls of the heat exchange channel 100a is consistent in the flow direction F. When the heat exchange medium flows through the heat exchange channel 100a, due to the synchronous matching of the projected dimensions of the side wall units, the heat exchange medium, while being impacted by the misaligned walls, can maintain a high degree of consistency in the frequency and intensity of disturbances on the side walls, thereby forming a uniform and strong turbulent field across the entire channel cross-section. In this example, the size L1 of the first wall unit A1 and the size L2 of the second wall unit A2 can be set to be unequal. In this case, the first included angle σ1 and the second included angle σ2 are not equal.

[0081] In some embodiments, the first wall 110 includes two adjacent first sub-walls 111 with a first included angle, and the second wall 120 includes two adjacent second sub-walls 121 with a second included angle, wherein the first included angle and the second included angle are set to be equal, that is, σ1=σ2.

[0082] It should be understood that the first wall surface 110 includes a first included angle between two adjacent first sub-wall surfaces 111, that is, the included angle between two adjacent first sub-wall surfaces 111 constituting the first wall surface unit A1. In a sawtooth structure, the first included angle can be the interior angle of the sawtooth; in a wavy structure, the first included angle can refer to the angle at the crest or trough of the wave. The magnitude of this first included angle directly affects the degree of deflection and velocity gradient of the heat exchange medium flowing through this region.

[0083] The second included angle between two adjacent second sub-walls 121 of the second wall surface 120 is the same as the first included angle, that is, the included angle between two adjacent second sub-walls 121 constituting the second wall surface unit A2. For example, in the case where the second wall surface 120 is constructed as a sawtooth structure, the second included angle can be the interior angle of the sawtooth; in the case where the second wall surface 120 is constructed as a wavy structure, the second included angle can refer to the tangent angle at the crest or trough of the wave. The size of the second included angle directly affects the degree of deflection and velocity gradient of the heat exchange medium flowing through this region.

[0084] Therefore, in this embodiment, by setting the included angle of the first wall unit A1 and the included angle of the second wall unit A2 to be equal, it is ensured that the geometric turning constraints experienced by the heat exchange medium as it flows through the walls on both sides of the flow channel are equivalent in angle. In this example, please refer to... Figure 4 The first included angle between the two first sub-walls 111 of the first wall unit A1 is defined as σ1, and the second included angle between the two second sub-walls 121 of the second wall unit A2 is defined as σ2, that is, σ1=σ2. In this example, a1=a2, b1=b2, and σ1=σ2. The relationship between a1 and b1, and a2 and b2 is not limited.

[0085] Based on the aforementioned technical solution, which involves the first intersection point M1 and the second intersection point M2 being staggered along the flow direction F, the solution further determines that the two adjacent first sub-walls 111 of the first wall surface 110 have a first included angle, and the two adjacent second sub-walls 121 of the second wall surface 120 have a second included angle, with the first included angle and the second included angle being equal. This technical solution ensures that the geometrical turning constraints experienced by the heat exchange medium as it flows through the two side walls are consistent in angle. Specifically, the first intersection point M1 and the second intersection point M2 are staggered along the flow direction F, and the unfolded dimensions of the sub-walls are uniform with equal included angles. When the heat exchange medium is periodically impacted and disturbed by the staggered wall surfaces, the disturbance intensity and direction change provided by the two side walls tend to be symmetrical, avoiding uneven force on the heat exchange medium on the two side walls. This effectively prevents the heat exchange medium from flowing off-center or drying out due to excessive local constraints. On the other hand, in this way, while maintaining the strong turbulent disturbance and bubble breaking effect brought about by the misaligned non-parallel walls, the flow field distribution in the channel is more stable and uniform, ensuring the synergy and balance of the heat transfer performance of both walls, thereby avoiding the problem of local heat transfer performance imbalance.

[0086] For example, please continue to refer to Figure 4 Taking the first wall 110 and the second wall 120 as an example with a sawtooth structure, the heat exchange channel 100a is composed of sawtooth-shaped walls. The first wall 110 is composed of isosceles triangular sawtooth units, and the dimensions of two adjacent first sub-walls 111 of each sawtooth unit in the flow direction F are both set to L1. Similarly, the second wall 120 is also composed of a series of isosceles triangular sawtooth units, and the dimensions of two adjacent second sub-walls 121 of each sawtooth unit in the flow direction F are both set to L2. Furthermore, a first included angle σ1, for example, 120 degrees, is formed between two adjacent first sub-walls 111 of each wall unit in the first wall 110. A second included angle σ2, also for example, 120 degrees, is formed between two adjacent second sub-walls 121 of each wall unit in the second wall 120. In this configuration, the first included angle σ1 and the second included angle σ2 are set to be equal. When the heat exchange medium flows through the heat exchange channel 100a, although the first intersection point M1 and the second intersection point M2 are staggered, the unfolded dimensions and included angles of the sub-walls of the two side wall units are equal. When the heat exchange medium is impacted by the wall, the disturbance provided by the two side walls is balanced in intensity and direction. This helps to maintain the uniform distribution of the gas-liquid two-phase flow in the channel and avoids the heat exchange medium from being excessively deflected to one side wall, thereby ensuring the heat exchange efficiency and stability of the entire heat exchange channel 100a.

[0087] To improve the overall heat exchange performance of the heat exchange channel 100a, in some embodiments, please refer to... Figure 4 The first wall element A1 has a dimension of L1 along the flow direction F, and the second wall element A2 has a dimension of L2 along the flow direction F. Then L1 and L2 satisfy: L1=L2.

[0088] Specifically, after the heat exchange medium impacts and disturbs the first wall unit A1, it will be constrained and impacted again by the second wall unit A2 within the same or similar flow distance. This ensures that the heat exchange medium obtains a uniform and continuous turbulent boiling heat transfer effect throughout the heat exchange channel 100a, avoiding the uneven spatial distribution of heat exchange medium disturbances caused by the size mismatch of the two wall units. This effectively prevents bubble retention or heat transfer deterioration in local areas due to insufficient disturbance, as well as flow instability that may be caused by excessive disturbance. The technical solution of using wall units with equal projected dimensions, working in conjunction with staggered wall units, provides a stable and efficient heat exchange environment for heat exchange medium disturbance, thereby improving the overall heat exchange performance balance of the heat exchange channel 100a.

[0089] For example, please continue to refer to Figure 4 Both the first wall unit A1 and the second wall unit A2 can adopt a sawtooth structure. That is, the sawtooth period length of the first wall unit A1 (i.e., the size of a complete sawtooth waveform in the flow direction F) can be equal to the sawtooth period length of the second wall unit A2. For example, if the first wall unit A1 is composed of a series of isosceles triangles, the size of one period in the flow direction F is L1; the second wall unit A2 is also composed of the same isosceles triangles, and the projected size of one period in the flow direction F is L2. In the embodiments of this application, L1 is equal to L2.

[0090] In other embodiments, the first wall unit A1 and the second wall unit A2 may both adopt a wavy, S-shaped, or arc-shaped structure.

[0091] Through the above technical solution, when the heat exchange medium flows through the heat exchange channel 100a, although there is a misalignment between the first intersection point M1 and the second intersection point M2, the interaction period between the heat exchange medium and the wall units on both sides remains consistent in the flow direction F. This effectively solves the problem of uneven distribution of heat exchange medium disturbance caused by improper setting of wall unit size, thereby avoiding fluctuations in heat exchange efficiency in local areas.

[0092] As another feasible implementation of this application, based on the aforementioned technical solution of L1=L2, please refer to... Figure 5 , Figure 6 and Figure 7In some embodiments, the two adjacent first sub-walls 111 included in the first wall 110 are set to have different unfolded dimensions in the flow direction F. That is, the unfolded dimension of one of the two adjacent first sub-walls 111a included in the first wall 110 is a1, and the unfolded dimension of one of the two adjacent second sub-walls 121 included in the second wall 120, which is disposed opposite to the first sub-wall 111a, is a2. Then a1 and a2 satisfy: a1≠a2.

[0093] As another feasible implementation of this application, based on the aforementioned L1=L2 technical solution, in some embodiments, the unfolded dimensions of the two adjacent second sub-walls 121 included in the second wall 120 in the flow direction F are set to be different. That is, the unfolded dimension of the other first sub-wall 111b of the two adjacent first sub-walls 111 included in the first wall 110 is b1, and the unfolded dimension of the other second sub-wall 121b of the two adjacent second sub-walls 121 included in the second wall 120, which is disposed opposite to the first sub-wall 111b, is b2. Then b1 and b2 satisfy: b1≠b2.

[0094] Here, the unfolded dimensions a1, a2, b1, and b2 refer to the lengths measured along the actual geometry of the wall surface, not its projected length in the flow direction F. For example, if the sub-wall surface is inclined or curved, its unfolded dimensions will be larger than its projected size in the flow direction F. These dimensions determine the actual path length and contact area of ​​the heat transfer medium as it flows through the sub-wall surface. By adjusting these unfolded dimensions, the fluid velocity, pressure loss, and heat transfer intensity with the wall in a localized region can be altered. For example, the unfolded dimensions of the sub-wall surface can be designed as the length of a straight segment or the arc length of a curved segment.

[0095] The fact that a1 and a2 are not equal, and that b1 and b2 are not equal, indicates that there is a difference in the unfolded dimensions of the first sub-wall 111 and the second sub-wall 121, which are arranged opposite each other, in the heat exchange channel 100a. This inequality introduces a local asymmetry in the channel geometry. When the fluid flows through these asymmetric walls, more complex flow patterns are generated, such as induced secondary flow, enhanced turbulent mixing, or altered boundary layer development.

[0096] Based on the above technical solution, which ensures that the dimensions L1 and L2 of the first wall unit A1 and the second wall unit A2 are equal along the flow direction F, a further technical solution is introduced where the unfolded dimensions of the relatively arranged first sub-wall 111 and the second sub-wall 121 are unequal. This local geometric asymmetry can effectively enhance fluid disturbance and mixing within the heat exchange channel 100a, breaking the symmetrical flow field, thereby improving the heat exchange efficiency between the fluid and the wall without significantly increasing the overall flow resistance.

[0097] Specifically, when the heat exchange medium passes through corresponding sub-walls of varying sizes, it generates stronger shear forces, eddies, or secondary flows, resulting in a thinner boundary layer and reduced heat transfer resistance. This allows the two-phase cold plate 10 to remove heat more efficiently, making it particularly suitable for applications requiring precise control of local heat exchange performance or handling high heat flux densities, thereby improving the overall thermal management performance of the cold plate.

[0098] In some embodiments, based on the aforementioned technical solution of L1=L2, the two adjacent first sub-walls 111 included in the first wall 110 have unfolded dimensions of a1 and b1 in the flow direction F, respectively, and a1 and b1 satisfy: a1≠b1.

[0099] In some embodiments, based on the aforementioned technical solution of L1=L2, the two adjacent second sub-walls 121 included in the second wall 120 have unfolded dimensions of a2 and b2 in the flow direction F, respectively, and a2 and b2 satisfy: a2≠b2.

[0100] The first wall surface 110 includes two adjacent first sub-wall surfaces 111 with unfolded dimensions a1 and b1 in the flow direction F, respectively, where a1 ≠ b1. This means that on the first wall surface 110, the two adjacent first sub-wall surfaces 111 constituting a first wall surface unit A1 have different unfolded dimensions along the flow direction F. For example, the unfolded dimension of a first sub-wall surface 111a can be designed to be larger or smaller than the unfolded dimension of its adjacent first sub-wall surface 111b. This asymmetry can be achieved in various ways, such as by changing the physical length of the two adjacent first sub-wall surfaces 111, or by changing their tilt angle relative to the flow direction F, or by combining both methods.

[0101] The second wall 120 includes two adjacent second sub-walls 121 with unfolded dimensions a2 and b2 in the flow direction F, respectively, where a2 ≠ b2. This means that on the second wall 120, the two adjacent second sub-walls 121 constituting a second wall unit A2 have different unfolded dimensions along the flow direction F. This can also be achieved by changing the physical length or tilt angle of the second sub-walls 121, thereby introducing asymmetry within the second wall unit A2.

[0102] Based on the technical solution described above where the dimensions L1 of the first wall unit A1 and L2 of the second wall unit A2 of the two-phase cold plate 10 are equal, this application introduces geometric asymmetry within each wall unit by ensuring that the unfolded dimensions a1 and b1 of the two adjacent first sub-walls 111 included in the first wall 110 are not equal in the flow direction F, and the unfolded dimensions a2 and b2 of the two adjacent second sub-walls 121 included in the second wall 120 are not equal in the flow direction F. This results in the fluid, when passing through the heat exchange channel 100a, not only experiencing macroscopic disturbances due to the misaligned arrangement, but also continuously encountering irregular wall structure changes at the microscopic level. Specifically, when the fluid flows through adjacent sub-walls with unequal unfolded dimensions, its velocity, pressure distribution, and boundary layer development undergo non-periodic and drastic changes, thereby generating more complex and intense eddies. This internal asymmetry, combined with the staggered arrangement of the first intersection point M1 and the second intersection point M2 along the flow direction F, and the fact that the dimensions L1 of the first wall unit A1 along the flow direction F and the dimensions L2 of the second wall unit A2 along the flow direction F are equal but the corresponding sub-wall dimensions are unequal, works together on the heat exchange medium. This effectively breaks any possible local stable flow state, continuously promotes the lateral mixing and longitudinal disturbance of the fluid, thereby maximizing the contact area and convective heat transfer intensity between the fluid and the heat exchange wall, thus improving the overall heat exchange efficiency of the two-phase cold plate 10, and helping to avoid local overheating, ensuring that heat is transferred uniformly and efficiently from the heat source.

[0103] In some embodiments, when the unfolded dimensions of two adjacent first sub-walls 111 in the flow direction F are different, and the unfolded dimensions of two adjacent second sub-walls 121 included in the second wall 120 in the flow direction F are different, there is a first included angle between the two adjacent first sub-walls 111 included in the first wall 110, and a second included angle between the two adjacent second sub-walls 121 included in the second wall 120, wherein the first included angle and the second included angle are different.

[0104] As mentioned above, refer to Figure 7The fact that the unfolded dimensions of two adjacent first sub-wall surfaces 111 in the flow direction F are set to be different, and the unfolded dimensions of two adjacent second sub-wall surfaces 121 included in the second wall surface 120 in the flow direction F are also set to be different, means that on the first wall surface 110 and the second wall surface 120 constituting the heat exchange channel 100a, the unfolded dimensions of adjacent sub-wall surface segments on each wall surface are different along the flow direction F of the heat exchange medium. That is, a1≠b1, a2≠b2. Based on this, the first included angle and the second included angle are set to be different, that is, the included angle on the first wall surface 110 and the included angle on the second wall surface 120 are different in value. For example, the first included angle on the first wall surface 110 can be designed as 110°, while the second included angle on the second wall surface 120 can be designed as 120°.

[0105] refer to Figure 7 The first included angle between the two first sub-walls 111 of the first wall unit A1 is defined as σ1, and the second included angle between the two second sub-walls 121 of the second wall unit A2 is defined as σ2, that is, σ1≠σ2.

[0106] In this embodiment, the included angles corresponding to the first wall 110 and the second wall 120 are set differently, which further enhances the asymmetry of the constraint of the heat exchange medium on both sides of the heat exchange channel 100a. This causes the heat exchange medium to be subjected to impacts and disturbances of different intensities and directions when it flows through the first wall 110 and the second wall 120, so as to guide the heat exchange medium to generate complex vortex motion, enhance turbulent disturbance, and effectively break the bubble field in the heat exchange channel 100a.

[0107] Furthermore, enhanced turbulent disturbance not only accelerates the bubble generation and detachment process of the heat exchange medium, effectively preventing the formation and adhesion of large bubbles, but also, through the synergistic effect of the asymmetric disturbance fields on both sides of the walls, more effectively breaks up the already formed bubble field, preventing bubble aggregation and blockage of the flow channel. Based on the aforementioned staggered arrangement technical solution, the technical solution provided in this application further limits the angle between the first wall 110 and the second wall 120, which can more effectively control the asymmetric disturbance intensity experienced by the heat exchange medium on both sides of the heat exchange channel 100a, thereby achieving optimal turbulent boiling heat exchange matching, significantly improving the bubble breaking effect, and ensuring the stability and heat exchange efficiency of the two-phase flow.

[0108] In some embodiments, reference Figure 7 The first sub-wall 111 included in the first wall 110 and the second sub-wall 121 included in the second wall 120 have different unfolded dimensions in the flow direction F.

[0109] In other words, when the unfolded dimensions of the two first sub-walls 111 included in the first wall unit A1 are set to be different, and the unfolded dimensions of the two second sub-walls 121 included in the second wall unit A2 are set to be different, the unfolded dimensions of all sub-walls are set to be different. That is, a1≠a2≠b1≠b2 in the figure.

[0110] By using the above technical solution, the unfolded dimensions of all sub-walls are set differently. Combined with the staggered arrangement of the first intersection point M1 and the second intersection point M2 of the wall units on both sides of the heat exchange channel 100a, and the equal dimensions of the first wall unit A1 and the second wall unit A2, a more complex and non-uniform turbulent field can be induced in the heat exchange medium. This can cause the frequency and intensity of the disturbance experienced by the heat exchange medium in the heat exchange channel 100a to be out of sync, thereby more effectively disrupting the regular arrangement of bubbles in the channel and preventing the continuous adhesion of bubbles in specific wall areas.

[0111] In another feasible implementation, refer to Figure 7 This can be achieved by setting the dimensions of two wall units to be equal, while setting unequal included angles between adjacent sub-walls, and by setting the unfolded dimensions of all sub-walls to be different, as well as staggering the first intersection point M1 and the second intersection point M2. In this example, all sub-walls are not parallel. Based on actual heat exchange requirements, a non-uniform turbulent field is constructed within the heat exchange channel 100a, thereby enabling targeted intervention of the gas-liquid two-phase flow at different locations. This significantly improves the heat exchange stability and bubble suppression capability of the two-phase cold plate 10 under complex operating conditions, and enhances the flexibility of flow field control.

[0112] In another feasible implementation, based on the fact that the dimensions of the two wall units are equal and the endpoints of the two wall units are aligned, the technical solution of setting unequal included angles between adjacent sub-walls, the technical solution of setting different unfolded dimensions of all sub-walls, and the technical solution of staggering the first intersection point M1 and the second intersection point M2, can improve the heat transfer stability and bubble suppression capability of the two-phase cold plate 10 under complex working conditions, and enhance the flexibility of flow field control.

[0113] In some embodiments, please refer to Figures 8 to 15 The two-phase cold plate 10 also includes a plurality of fins 200; at least one fin 200 is protruding from both the first sub-wall surface 111 and the second sub-wall surface 121. In particular, along the flow direction F, the fins 200 located on the first sub-wall surface 111 and the fins 200 located on the second sub-wall surface 121 are arranged in a staggered parallel manner.

[0114] It should be understood that the fins 200 are protruding structures disposed on the first sub-wall surface 111 and the second sub-wall surface 121. The function of the fins 200 is to increase the heat exchange surface area and enhance the fluid turbulence of the heat exchange medium. Exemplarily, the fins 200 can adopt various geometric shapes, such as rectangular, triangular, wavy, or S-shaped, to adapt to different fluid dynamics and heat exchange requirements. The fins 200 can be integrally formed with the flow channel wall, for example, by processes such as casting, extrusion, or additive manufacturing; or they can be connected to the wall by means of welding, bonding, or mechanical fixing.

[0115] In this embodiment, at least one fin 200 protrudes from both the first sub-wall 111 and the second sub-wall 121. That is, fin 200 structures are arranged on both sides of the heat exchange channel 100a to ensure the heat exchange enhancement effect across the entire channel cross-section, and to effectively compensate for the loss of effective heat exchange area that may be caused by the misaligned arrangement of the walls of the heat exchange channel 100a, and to ensure that the heat exchange medium is disturbed by the fins 200 when flowing through both sides of the wall.

[0116] In the embodiments of this application, please refer to Figure 10 and Figure 11 The fins 200 can be uniformly distributed along the flow direction F on the first sub-wall 111 and the second sub-wall 121 to provide continuous disturbance and heat exchange area. Of course, they can also be non-uniformly distributed along the flow direction F according to the heat load distribution or fluid characteristics. For example, higher density fins 200 can be provided in areas with higher heat load or at the fluid inlet.

[0117] Along the flow direction F, the fins 200 located on the first sub-wall 111 and the fins 200 located on the second sub-wall 121 are arranged in a staggered parallel configuration. The parallel configuration means that the main axis direction of the fins 200 or the overall orientation of the fin array 200 is consistent with the flow direction F of the heat exchange medium.

[0118] The misalignment means that the fins 200 on the first sub-wall 111 and the fins 200 on the second sub-wall 121 are not perfectly aligned in the flow direction F, but rather offset to a certain extent. This misalignment causes the heat transfer medium to be alternately impacted and disturbed by the fins 200 on both sides of the wall as it passes through the heat exchange channel 100a, resulting in a more complex and intense turbulence effect. For example, the misalignment distance can be set to half the period length of the fins 200, or other non-zero distances that can effectively enhance fluid mixing and disturbance.

[0119] For example, refer to Figure 11The heat exchange channel 100a of the two-phase cold plate 10 can be illustrated by using a sawtooth-shaped first wall unit A1 and second wall unit A2, which are staggered along the flow direction F. In this example, a fin 200 is provided on the first sub-wall 111 before the first wall unit A1, and a fin 200 is provided on the second sub-wall 121 before the second wall unit A2. In this way, when the heat exchange medium flows in the heat exchange channel 100a, it will first encounter the fin 200 on one side of the wall and then the fin 200 on the other side of the wall, thereby generating continuous and alternating disturbances, which effectively promotes the fluid mixing and bubble breaking of the heat exchange medium.

[0120] For example, refer to Figure 12 Along the height direction of the plate 100, the fins 200 located on the first sub-wall 111 and the fins 200 located on the second sub-wall 121 are at the same height. For example, the length of the fins 200 is consistent with the height of the plate 100.

[0121] In some embodiments, reference Figure 13 and Figure 14 as well as Figure 15 Along the height direction of the plate 100, the fins 200 located on the first sub-wall 111 and the fins 200 located on the second sub-wall 121 are at different height positions.

[0122] Here, the direction along the height of the plate 100 refers to the direction perpendicular to the main plane of the cold plate and the main flow direction F of the heat exchange medium. In practical applications of the two-phase cold plate 10, the height direction of the plate 100 usually corresponds to the thickness direction of the cold plate or the direction perpendicular to the plane of the heat exchange channel 100a.

[0123] The fins 200 located on the first sub-wall 111 and the fins 200 located on the second sub-wall 121 are at different heights, meaning that the fins 200 on the first sub-wall 111 and the fins 200 on the second sub-wall 121 are not at the same horizontal height along the height direction of the plate 100. For example, the fin 200 on the first sub-wall 111 is located above the fin 200 on the second sub-wall 121. In this case, the two fins 200 are staggered.

[0124] For example, please continue to refer to Figure 15 The length of the fin 200 can be set to half that of the plate 100, and the two ends of the two fins 200 that are far apart can be aligned with the top of the plate 100, so that the two fins 200 are completely staggered.

[0125] Through the above technical solution, when the heat exchange medium flows through the heat exchange channel 100a, the disturbance sources on both sides of the wall are asymmetrically distributed on the cross section perpendicular to the flow direction F. This can effectively change the flow trajectory of the heat exchange medium in the heat exchange channel 100a and avoid the formation of stable symmetrical vortices or bubble stagnation zones between the two sides of the heat exchange medium.

[0126] The varying heights of the heat transfer medium, after flowing through the first sub-wall 111 fins 200, are immediately disturbed by the second sub-wall 121 fins 200 at different heights, achieving an alternating disturbance effect. This generates a more complex turbulent structure and enhances the mixing degree of the heat transfer medium across the flow channel cross-section. On one hand, it accelerates the breaking and detachment of bubbles, preventing the formation of a continuous gas film on the wall. On the other hand, by changing the scouring path of the heat transfer medium on the wall, it ensures a more uniform heat transfer intensity in each region of the flow channel, thereby effectively suppressing bubble embolism and improving overall heat transfer stability.

[0127] In this embodiment, in the two-phase cold plate 10, multiple plates 100 are spaced apart and arranged opposite each other along a first direction, defining a heat exchange channel 100a, and the first wall unit A1 and the second wall unit A2 are staggered along the flow direction F. Meanwhile, fins 200 are protruding from both the first sub-wall 111 and the second sub-wall 121, and along the flow direction F, the fins 200 on the first sub-wall 111 and the fins 200 on the second sub-wall 121 are staggered and parallel. Based on this, by further setting the fins 200 located on the first sub-wall 111 and the fins 200 located on the second sub-wall 121 at different heights in the height direction of the plate 100, the heat transfer medium is subjected not only to planar misalignment disturbances in the flow channel, but also to asymmetric disturbances in the vertical direction. This can more thoroughly destroy the boundary layer of the heat transfer medium, generate more intense turbulence, and thus significantly enhance the mixing and mass and heat transfer processes of the gas-liquid two phases. It further accelerates the generation, detachment and breakup of bubbles, effectively preventing the formation of stable large bubbles or gas films in the flow channel, thereby significantly improving the heat transfer efficiency and flow stability of the two-phase cold plate 10.

[0128] In some embodiments, please refer to Figure 16 and Figure 17 The two-phase cold plate 10 also includes a fluid distribution component 300, which is located on one side of the plate body 100 along the height direction of the plate body 100. The fluid distribution component 300 has a first fluid distribution channel 300a and a second fluid distribution channel 300b connected by a heat exchange channel 100a. The first fluid direction F1 defined by the first fluid distribution channel 300a and the second fluid direction F2 defined by the second fluid distribution channel 300b are arranged parallel to each other and are both perpendicular to the flow direction F.

[0129] In this embodiment, the fluid distribution component 300 is a structure used to uniformly distribute the heat exchange working fluid to each heat exchange channel 100a. The fluid distribution component 300 can be implemented in various forms; for example, it can be a manifold with multiple outlets or a distribution cavity with a complex internal flow channel network. The material of the fluid distribution component 300 can be selected according to application requirements; for example, it can be a metallic material such as copper or aluminum alloy, or a polymeric material such as engineering plastics.

[0130] The fluid distribution component 300 is located on one side of the plate 100 along the height direction of the plate 100, that is, the distribution component is arranged in the vertical direction of the two-phase cold plate 10, for example at the top of the plate 100, which can provide a pre-distribution area for the heat exchange medium, so that the flow rate can be balanced in a relatively independent level before entering the heat exchange channel 100a.

[0131] The two-phase cold plate 10 in this embodiment further includes a substrate 400 and a cover 500. Plates 100 are sequentially spaced on the substrate 400 along a first direction. Along the height direction of the plate 100, the fluid distribution member 300 is located on the side of the plate 100 away from the substrate 400. The cover 500 covers the substrate 400 and forms a receiving space, within which both the plate 100 and the fluid distribution member 300 are disposed. An inlet 500a and an outlet 500b are provided on the cover 500. The heat exchange medium enters the receiving space through the inlet 500a and flows into and out of the heat exchange channel 100a under the action of the fluid distribution member 300.

[0132] The first fluid distribution channel 300a and the second fluid distribution channel 300b are channels inside the fluid distribution member 300 used to guide and distribute the heat exchange medium. For example, they can be chambers formed by the body of the fluid distribution member 300. The function of the fluid distribution channels is to further refine the distribution of the fluid and ensure good uniformity of the fluid when it enters each heat exchange channel 100a. In the embodiments of this application, the cross-sectional shape of the fluid distribution channels can be set as, for example, rectangular or circular, to optimize the fluid resistance of the heat exchange medium and promote uniform flow.

[0133] The first fluid direction F1 defined by the first fluid distribution channel 300a and the second fluid direction F2 defined by the second fluid distribution channel 300b are arranged parallel to each other and perpendicular to the flow direction F. The parallel arrangement of the first fluid direction F1 and the second fluid direction F2 ensures a consistent flow path for the heat exchange medium within the fluid distribution component 300, helping to maintain flow balance. The perpendicularity of the fluid direction of the distribution channels to the flow direction F of the heat exchange channel 100a creates an orthogonal fluid introduction method, effectively reducing inlet effect losses when the fluid enters the heat exchange channel 100a and minimizing local resistance caused by sudden velocity changes at the channel inlet, thus allowing the heat exchange medium to enter the heat exchange region more smoothly.

[0134] A fluid distribution layer is constructed by adding a fluid distribution component 300 on one side of the plate 100 along its height direction, aiming to solve the problem of uniform flow distribution of the heat exchange medium when it enters the heat exchange channel 100a. The first fluid distribution channel 300a and the second fluid distribution channel 300b, located inside the fluid distribution component 300, communicate with the heat exchange channel 100a, enabling pre-distribution of the heat exchange medium entering the cold plate, ensuring a reasonable flow distribution before the fluid enters each heat exchange channel 100a. The parallel arrangement of the first fluid direction F1 and the second fluid direction F2, and their perpendicularity to the flow direction F within the heat exchange channel 100a, this orthogonal fluid introduction method effectively reduces inlet effect losses when the fluid enters the heat exchange channel 100a, and reduces local resistance caused by sudden changes in flow velocity at the channel inlet.

[0135] Through the above technical solution, the fluid distribution component 300 not only plays the role of flow balancing, but also, through its spatial coordination with the heat exchange channel 100a, enables the heat exchange medium to enter the heat exchange area more smoothly. This provides a stable flow field environment for the subsequent misaligned non-parallel wall surface to perform enhanced heat exchange and bubble breaking functions, avoiding the risk of local drying caused by uneven flow distribution, and achieving a balance and optimization of the overall heat dissipation performance and flow resistance of the cold plate.

[0136] Furthermore, the combination of the fluid distribution component 300 with the aforementioned misaligned non-parallel wall heat exchange channel 100a enables the cold plate to effectively meet the stringent requirements for uniform fluid distribution under high heat flux density while achieving efficient boiling heat exchange and bubble suppression, further enhancing the stability and reliability of the overall heat dissipation performance.

[0137] For example, the fluid distribution component 300 can be a manifold structure. This manifold extends along the top edge of the plate 100 and is integrally formed with the plate 100 or fixed to it by welding, bolting, or other methods. The manifold contains multiple parallel first fluid distribution channels 300a and second fluid distribution channels 300b. Each fluid distribution channel can be a rectangular cross-section channel separated by partitions. The fluid direction defined by the first fluid distribution channels 300a and second fluid distribution channels 300b forms a 90-degree angle with the flow direction F of the heat exchange channel 100a, i.e., it is introduced perpendicularly. For example, if the heat exchange channel 100a flows horizontally, the distribution channels inject the heat exchange medium vertically.

[0138] In this embodiment of the application, the fluid distribution component 300 can be configured to have multiple layers.

[0139] In some embodiments, as described above, the cover 500 has an outlet 500b for the inflow and outflow of the heat exchange medium into and out of the containment space. In this embodiment, the fitted flow direction F3 defined by the fluid path from the inlet 500a to the outlet 500b intersects with or is parallel to the first direction.

[0140] It should be understood that the fitted flow direction F3 refers to the mass-weighted average flow direction F within the entire domain of the heat exchange channel 100a during the complete flow process of the heat exchange medium flowing in from the inlet 500a, through the heat exchange channel 100a, and out from the outlet 500b. It is used to characterize the overall net displacement trend of the fluid within the heat exchange channel 100a. The determination of this fitted flow direction F3 needs to ignore the influence of transient and local flow disturbances such as local turbulent vortices, flow separation near the wall, and the reversal section within the channel, and only consider the macroscopic net flow vector of the fluid from the inlet 500a to the outlet 500b.

[0141] When the heat exchange medium has reciprocating flow (such as a backflow under the same side layout of inlet and outlet) in the heat exchange channel 100a, the fitted flow direction F3 is the remaining net displacement direction after the reciprocating flow is canceled out, which intersects or is parallel to the flow direction F defined by the heat exchange channel 100a.

[0142] In this embodiment of the application, the relationship between the relative positions of the inlet 500a and the outlet 500b and the flow direction is not limited. For example, the relative positional relationship between the inlet 500a and the outlet 500b includes: being on the same side of the cover 500, being on opposite sides of the cover 500, being on adjacent sides of the cover 500, or being at opposite corners of the cover 500.

[0143] For example, refer to Figure 1The inlet 500a and outlet 500b are located on opposite sides of the cover 500, and the fitted flow direction F3 defined by the heat exchange medium from the inlet 500a to the outlet 500b is parallel to the flow direction F defined by the heat exchange channel 100a. After entering through the inlet 500a, the heat exchange medium enters the containing space and flows along the flow direction F in the heat exchange channel 100a to the end of the heat exchange channel 100a, then passes upward through the cover 500 and is discharged from the outlet 500b on the opposite side.

[0144] As another feasible implementation, the two-phase cold plate 10 in this example includes a cover 500 and a substrate 400, as well as a plate 100 and a fluid distribution member 300 located within the accommodating space formed by the cover 500 and the substrate 400. The inlet 500a and outlet 500b are located on opposite sides of the cover 500, and the fitted flow direction F3 defined by the heat exchange medium from the inlet 500a to the outlet 500b intersects with the flow direction F defined by the heat exchange channel 100a. (Reference) Figure 18 The fitted flow direction F3 of the heat exchange medium from the inlet 500a to the outlet 500b is perpendicular to the flow direction F defined by the heat exchange channel 100a. After entering through the inlet 500a, the heat exchange medium enters the containing space and flows along the flow direction F within the fluid distribution component 300 and the heat exchange channel 100a to the end of the heat exchange channel 100a, then passes upwards through the cover 500 and exits through the outlet 500b on the opposite side.

[0145] In other embodiments, the inlet 500a and the outlet 500b may also be located on the same side of the cover 500. In this case, the fitted flow direction F3 defined by the heat exchange medium from the inlet 500a to the outlet 500b may be arranged to intersect with the flow direction F defined by the heat exchange channel 100a. Alternatively, the fitted flow direction F3 defined by the heat exchange medium from the inlet 500a to the outlet 500b may be arranged perpendicular to the flow direction F defined by the heat exchange channel 100a. There is no limitation on this.

[0146] In summary, the two-phase cold plate 10 in this embodiment effectively solves the bubble retention problem through the synergistic effect of staggered non-parallel arrangement and walls with different shapes, avoiding local drying and heat transfer deterioration, ensuring the stability of two-phase flow heat exchange, and improving heat dissipation performance. The heat exchange medium flows into the heat exchange channel 100a, and during the flow process, it continuously impacts the wall due to wall misalignment and is subjected to asymmetrical disturbance due to the different shapes of the two side walls. This strengthens turbulent boiling heat exchange, accelerates bubble detachment and breaks up the bubble field, and inhibits the formation of large bubbles. Finally, the gas-liquid two-phase heat exchange medium flows out of the heat exchange channel 100a. The heat exchange medium flowing in the heat exchange channel 100a undergoes phase change vaporization during operation to utilize latent heat to enhance heat exchange.

[0147] Secondly, a liquid cooling device is provided, including the two-phase cold plate 10 as described above.

[0148] The liquid cooling device in this embodiment includes the two-phase cold plate 10 described above, and therefore has all the beneficial effects of the two-phase cold plate 10 described above, which will not be elaborated here.

[0149] Thirdly, an electronic device is provided, including a heating element and the two-phase cold plate 10 as described above or the liquid cooling device as described above.

[0150] The electronic device in this application embodiment includes the above-mentioned two-phase cold plate 10 or liquid cooling device, and therefore has all the beneficial effects of the above-mentioned two-phase cold plate 10 or liquid cooling device, which will not be elaborated here.

[0151] The electronic devices in this application embodiment achieve a significant improvement in heat dissipation performance under high heat flux density conditions, providing reliable thermal management for high-power server chips and other electronic devices, and ensuring the stability of their computing performance during continuous high-load operation.

[0152] In the description of this application, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Therefore, a feature defined as "first" or "second" may explicitly or implicitly include one or more features. In the description of this application, "multiple" means two or more, unless otherwise explicitly specified.

[0153] In the above embodiments, the descriptions of each embodiment have different focuses. For parts not described in detail in a certain embodiment, please refer to the relevant descriptions in other embodiments.

[0154] The embodiments, implementation methods, and related technical features of this application can be combined and substituted for each other without conflict.

[0155] The above are merely preferred embodiments of this application and are not intended to limit this application in any way. Any simple modifications, equivalent changes, and alterations made to the above embodiments based on the technical essence of this application without departing from the scope of the technical solution of this application shall still fall within the scope of the technical solution of this application.

Claims

1. A two-phase cold plate (10), characterized in that, The two-phase cold plate (10) includes a plurality of plates (100) spaced apart and arranged opposite to each other along a first direction. Each of the two oppositely arranged plates (100) includes a first wall surface (110) and a second wall surface (120) arranged opposite to each other along the first direction, so as to define a heat exchange channel (100a) between the two oppositely arranged plates (100). Along the flow direction (F) defined by the heat exchange channel (100a), the first wall surface (110) includes a plurality of adjacent first sub-wall surfaces (111), and the second wall surface (120) includes a plurality of adjacent second sub-wall surfaces (121), and the flow direction (F) intersects with the first direction; Two adjacent first sub-walls (111) are defined as first wall units (A1), and two adjacent second sub-walls (121) are defined as second wall units (A2). The first wall unit (A1) includes a first intersection point (M1) where the two first sub-walls (111) intersect, and the second wall unit (A2) includes a second intersection point (M2) where the two second sub-walls (121) intersect. The first intersection point (M1) and the second intersection point (M2) are staggered along the flow direction (F).

2. The two-phase cold plate (10) according to claim 1, characterized in that, The misalignment distance between the first intersection point (M1) and the second intersection point (M2) along the flow direction (F) is d. The dimension of the first wall unit (A1) along the flow direction (F) is L1, and the dimension of the second wall unit (A2) along the flow direction (F) is L2. Then d satisfies L1 and L2: 0 <d<min(L1,L2)。 3. The two-phase cold plate (10) according to claim 1 or 2, characterized in that, The first wall surface (110) includes two adjacent first sub-wall surfaces (111), one of which has an unfolded dimension of a1. The second wall surface (120) includes two adjacent second sub-wall surfaces (121), one of which is opposite to the first sub-wall surface (111) and has an unfolded dimension of a2. Then a1 and a2 satisfy: a1=a2. and / or The first wall surface (110) includes two adjacent first sub-wall surfaces (111), and the unfolded size of the other first sub-wall surface (111) is b1. The second wall surface (120) includes two adjacent second sub-wall surfaces (121), and the unfolded size of the other second sub-wall surface (121) opposite to the first sub-wall surface (111) is b2. Then b1 and b2 satisfy: b1=b2.

4. The two-phase cold plate (10) according to any one of claims 1 to 3, characterized in that, The first wall surface (110) includes two adjacent first sub-wall surfaces (111) with unfolded dimensions a1 and b1 in the flow direction (F), respectively. Then a1 and b1 satisfy: a1 = b1; and / or The second wall (120) includes two adjacent second sub-walls (121) with unfolded dimensions a2 and b2 in the flow direction (F), respectively. Then a2 and b2 satisfy: a2=b2.

5. The two-phase cold plate (10) according to claim 4, characterized in that, When the two adjacent first sub-walls (111) included in the first wall surface are set to have equal unfolded dimensions in the flow direction (F), and the two adjacent second sub-walls (121) included in the second wall surface are set to have equal unfolded dimensions in the flow direction (F), the unfolded dimensions of the first sub-walls (111) included in the first wall surface (110) and the unfolded dimensions of the second sub-walls (121) included in the second wall surface (120) in the flow direction (F) are set to be equal.

6. The two-phase cold plate (10) according to any one of claims 3 to 5, characterized in that, The first wall surface (110) includes two adjacent first sub-wall surfaces (111) with a first included angle, and the second wall surface (120) includes two adjacent second sub-wall surfaces (121) with a second included angle, wherein the first included angle and the second included angle are set to be equal.

7. The two-phase cold plate (10) according to claim 1, characterized in that, The first wall unit (A1) has a dimension of L1 along the flow direction (F), and the second wall unit (A2) has a dimension of L2 along the flow direction (F). Then L1 and L2 satisfy: L1 = L2.

8. The two-phase cold plate (10) according to claim 7, characterized in that, The first wall surface (110) includes two adjacent first sub-wall surfaces (111), one of which has an unfolded dimension of a1. The second wall surface (120) includes two adjacent second sub-wall surfaces (121), one of which is disposed opposite to the first sub-wall surface (111), and has an unfolded dimension of a2. Then a1 and a2 satisfy: a1≠a2. and / or The first wall (110) includes two adjacent first sub-walls (111), and the unfolded size of the other first sub-wall (111) is b1. The second wall (120) includes two adjacent second sub-walls (121), and the unfolded size of the other second sub-wall (121) opposite to the first sub-wall (111) is b2. Then b1 and b2 satisfy: b1≠b2.

9. The two-phase cold plate (10) according to claim 8, characterized in that, The first wall surface (110) includes two adjacent first sub-wall surfaces (111) with unfolded dimensions a1 and b1 in the flow direction (F), respectively. Then a1 and b1 satisfy: a1 ≠ b1; and / or The second wall (120) includes two adjacent second sub-walls (121) with unfolded dimensions a2 and b2 in the flow direction (F), respectively. Then a2 and b2 satisfy: a2≠b2.

10. The two-phase cold plate (10) according to claim 9, characterized in that, When the unfolded dimensions of two adjacent first sub-walls (111) in the flow direction (F) are set to be different, and the unfolded dimensions of two adjacent second sub-walls (121) included in the second wall (120) in the flow direction (F) are set to be different, there is a first included angle between the two adjacent first sub-walls (111) included in the first wall (110), and there is a second included angle between the two adjacent second sub-walls (121) included in the second wall (120), and the first included angle and the second included angle are set to be different.

11. The two-phase cold plate (10) according to any one of claims 1 to 10, characterized in that, The two-phase cold plate (10) further includes a plurality of fins (200); at least one of the fins (200) is provided protruding on both the first sub-wall surface (111) and the second sub-wall surface (121). Along the flow direction (F), the fins (200) on the first sub-wall (111) and the fins (200) on the second sub-wall (121) are arranged in a staggered parallel configuration.

12. The two-phase cold plate (10) according to claim 11, characterized in that, Along the height direction of the plate (100), the fins (200) located on the first sub-wall (111) and the fins (200) located on the second sub-wall (121) are at different height positions.

13. The two-phase cold plate (10) according to any one of claims 1 to 12, characterized in that, The two-phase cold plate (10) also includes a fluid distribution component (300) located on one side of the plate body (100) along the height direction of the plate body (100); The fluid distribution component (300) has a first fluid distribution channel (300a) and a second fluid distribution channel (300b) connected through the heat exchange channel (100a). The first fluid distribution channel (300a) defines a first fluid direction (F1) and the second fluid distribution channel (300b) defines a second fluid direction (F2) which are parallel to each other and are both perpendicular to the flow direction (F).

14. The two-phase cold plate (10) according to any one of claims 1 to 13, characterized in that, The two-phase cold plate (10) also includes: A substrate (400), wherein the plate bodies (100) are sequentially spaced along a first direction on the substrate (400); and A cover (500) is disposed on the substrate (400) to form a receiving space with the substrate (400), and the plate (100) is disposed within the receiving space; The cover (500) has an inlet (500a) and an outlet (500b), and the fitted flow direction (F3) defined by the fluid path from the inlet (500a) to the outlet (500b) intersects or is parallel to the flow direction (F).

15. A liquid cooling device, characterized in that, Includes the two-phase cold plate (10) as described in any one of claims 1 to 14.

16. An electronic device, characterized in that, It includes a heating element and a two-phase cold plate (10) as described in any one of claims 1 to 14 or a liquid cooling device as described in claim 15.

Images