Low-flow-resistance high-heat-exchange gas-liquid two-phase cold plate structure

Abstract

The application discloses a low-flow-resistance strong-heat-exchange gas-liquid two-phase cold plate structure, which comprises a cold plate main body, a main simulated heat source combination, an auxiliary simulated heat source combination, a liquid connector socket and a gas-liquid two-phase connector socket; the main simulated heat source combination and the auxiliary simulated heat source combination are attached to the front and back surfaces of the cold plate main body; the inside of the cold plate main body corresponding to the attachment position of the main simulated heat source combination is provided with a main simulated heat source adaptive flow channel area, and the inside of the cold plate main body corresponding to the attachment position of the auxiliary simulated heat source combination is provided with an auxiliary simulated heat source adaptive flow channel area; the liquid connector socket and the gas-liquid two-phase connector socket are arranged on the cold plate main body; the liquid connector socket is a working medium inlet in the inside of the cold plate main body; and the gas-liquid two-phase connector socket is a gas-liquid mixed state outlet of the cold plate main body. The application has the advantages of low flow resistance, strong heat exchange and stable gas-liquid two-phase flow.

Description

Technical Field

[0001] This invention belongs to the field of heat dissipation technology for electronic devices, specifically a low-flow-resistance, high-heat-exchange gas-liquid two-phase cold plate structure. Background Technology

[0002] As electronic devices evolve towards higher power and higher density, their heat dissipation requirements are becoming increasingly urgent. Gas-liquid two-phase cold plates, due to their advantages of high heat exchange efficiency and strong heat dissipation capacity, are gradually being applied in data centers, power electronic modules, new energy, communication and navigation, and other scenarios. However, existing cold plates have the following technical shortcomings:

[0003] (1) It is difficult to balance flow resistance and heat exchange efficiency: At present, cold plates mostly adopt series rectangular parallel flow channels. In order to improve the heat exchange effect, the flow channel length needs to be increased or a turbulence structure needs to be set, but this will lead to a significant increase in flow resistance and increase the power consumption of the system pump group.

[0004] (2) Uneven distribution of gas and liquid phases: Due to the lack of a dedicated flow-gathering structure design, the gas and liquid two-phase fluids are prone to stratification and backflow in the flow channel, resulting in local dry spots or overheating, which affects the heat transfer stability.

[0005] (3) Unreasonable design of turbulence structure: Most of the existing turbulence components are cylindrical, rhomboid or square. Although they can enhance heat transfer, they will cause a surge in local resistance, further aggravating the contradiction between flow resistance and heat transfer. Summary of the Invention

[0006] To address the shortcomings of existing technologies, the present invention aims to provide a low-flow-resistance, high-heat-exchange gas-liquid two-phase cold plate structure, achieving synergistic optimization of reduced flow resistance, enhanced heat exchange, and stable gas-liquid two-phase flow.

[0007] The technical solution to achieve the purpose of this invention is as follows: a low-flow-resistance, high-heat-exchange gas-liquid two-phase cold plate structure, comprising: a cold plate body, a main simulated heat source assembly, an auxiliary simulated heat source assembly, a liquid connector socket, and a gas-liquid two-phase connector socket. The main simulated heat source assembly and the auxiliary simulated heat source assembly are both attached to the front and back sides of the cold plate body. The interior of the cold plate body corresponding to the attachment position of the main simulated heat source assembly is provided with a main simulated heat source adaptation flow channel area, and the interior of the cold plate body corresponding to the attachment position of the auxiliary simulated heat source assembly is provided with an auxiliary simulated heat source adaptation flow channel area. The liquid connector socket and the gas-liquid two-phase connector socket are respectively disposed on the cold plate body. The liquid connector socket is the working fluid inlet inside the cold plate body, and the gas-liquid two-phase connector socket is the gas-liquid mixed state outlet of the cold plate body.

[0008] Preferably, the internal flow channels of the cold plate body include a main inlet flow channel, an auxiliary simulated heat source adaptation flow channel area, a main simulated heat source adaptation flow channel area, and an outlet flow channel. When the working fluid enters the cold plate body, it is divided into two paths in the main inlet flow channel. Most of the fluid flows to the main simulated heat source adaptation flow channel area to absorb the heat from the main simulated heat source combination, and a small portion of the fluid flows to the auxiliary simulated heat source adaptation flow channel area to absorb the heat from the auxiliary simulated heat source combination. After absorbing heat through convective heat transfer, the fluid converges in the outlet flow channel and flows out of the cold plate body.

[0009] Preferably, the main simulated heat source adaptation channel area includes a flow distribution cavity, a teardrop-shaped turbulence microchannel, a confluence cavity, and a parallel flow distribution microchannel structure. The fluid is guided and evenly distributed to the parallel flow distribution microchannel structure through the flow distribution cavity. The confluence cavity gathers the fluid working medium from the parallel flow distribution microchannel structure and flows to the outlet channel of the cold plate body. The teardrop-shaped turbulence microchannel is evenly arranged in each parallel flow distribution microchannel along the fluid flow direction.

[0010] Preferably, the flow splitting cavity is a rectangular cross-section static pressure cavity, and the interior of the flow splitting cavity is provided with flow splitting ribs. The flow splitting ribs have an airfoil cross-section, and the angle of attack of the flow splitting ribs increases at each point along the main flow direction.

[0011] Preferably, a flow-stabilizing protrusion is provided at the inlet of the confluence cavity. The flow-stabilizing protrusion is an arc-shaped or strip-shaped structure, which is used to suppress backflow and eddies generated when the gas-liquid two-phase fluids converge, thereby reducing flow resistance.

[0012] Preferably, the teardrop-shaped turbulence microchannel is an integrally formed teardrop-shaped protrusion, with adjacent rows of teardrop-shaped protrusions arranged alternately, and each pair of rows is an equally spaced rectangular array.

[0013] Preferably, the main simulated heat source assembly includes a simulated heating block, a fixed support, and a heating rod. The bottom of the simulated heating block is provided with a boss the size of a simulated hot spot, and the boss contacts the surface of the cold plate body through thermally conductive silicone grease. A cylindrical groove is provided in the middle of the simulated heating block, and the heating rod contacts the wall of the cylindrical groove of the simulated heating block through thermally conductive silicone grease. After the fixed support is fixedly connected to the simulated heating block, it is then connected and fixed to the cold plate.

[0014] Compared with the prior art, the significant advantages of this invention are:

[0015] (1) Low flow resistance: The parallel flow splitting microchannel design, combined with the teardrop-shaped streamlined turbulence structure, significantly reduces friction resistance and local resistance, is compatible with low-power pump sets, and reduces system energy consumption;

[0016] (2) Strong heat transfer: The teardrop-shaped turbulent structure enhances fluid turbulence mixing, destroys the thermal boundary layer, and greatly improves heat transfer efficiency, which can meet the heat dissipation requirements of high-power electronic devices;

[0017] (3) Two-phase stability: The flow splitting cavity is equipped with flow splitting ribs, and the flow stabilizing cavity is equipped with flow stabilizing protrusions to achieve uniform distribution and stable flow of gas and liquid phases, avoiding local dry spots, overheating and unstable flow.

[0018] (4) Reliable structure: The integrated molded turbulence structure and welding parting design ensure the strength of the cold plate structure and are suitable for long-term stable operation;

[0019] (5) Wide adaptability: The structure is compact and the number and size of the flow channels can be adjusted according to different heat source sizes, making it suitable for various scenarios such as data centers, IGBT modules, and communication and navigation equipment.

[0020] The present invention will now be described in further detail with reference to the accompanying drawings. Attached Figure Description

[0021] Figure 1 This is a schematic diagram of the overall structure of the gas-liquid two-phase cold plate.

[0022] Figure 2 This is a three-dimensional isometric view of the internal flow channel structure of the cold plate body.

[0023] Figure 3 This is a top view of the cross-sectional flow channel structure inside the cold plate.

[0024] Figure 4 This is a magnified view of a part of the teardrop-shaped turbulence structure of a parallel flow-diverting microchannel.

[0025] Figure 5 The main simulated heat source combination.

[0026] Figure 6 It is a heating block.

[0027] Figure 7 The main simulated heat source is fixed with a support.

[0028] Figure 8 To simulate the combination of heat sources. Detailed Implementation

[0029] The specific embodiments of the present invention will be further described in detail below with reference to the accompanying drawings.

[0030] A low-flow-resistance, high-heat-transfer gas-liquid two-phase cold plate structure reduces frictional resistance through a parallel flow-splitting microchannel structure, enhances heat transfer and suppresses local resistance through a teardrop-shaped turbulence microchannel structure, and optimizes fluid distribution and convergence through a gas-liquid two-phase flow-splitting and convergence structure. The three elements work together to achieve a balance between low flow resistance and high heat transfer. Specifically, it includes: a cold plate body (1), a main simulated heat source assembly (2), an auxiliary simulated heat source assembly (3), a liquid connector socket (4), and a gas-liquid two-phase connector socket (5). The main simulated heat source assembly (2) and the auxiliary simulated heat source assembly (3) are both attached to the front and back sides of the cold plate body (1). The cold plate body (1) corresponding to the attachment position of the main simulated heat source assembly (2) has a main simulated heat source adaptation flow channel area inside, and the cold plate body (1) corresponding to the attachment position of the auxiliary simulated heat source assembly (3) has an auxiliary simulated heat source adaptation flow channel area inside. The two flow channel areas have different flow channel structures and different heat transfer capabilities, namely a high heat transfer area and a general heat transfer area, respectively. The liquid connector socket (4) and the gas-liquid two-phase connector socket (5) are respectively installed on the cold plate body (1). The liquid connector socket (4) is the inlet of the working fluid inside the cold plate body (1), and the gas-liquid two-phase connector socket (5) is the outlet of the gas-liquid mixture of the cold plate body (1). The diameter of the gas-liquid two-phase connector socket (5) is larger than that of the liquid connector socket (4). After the liquid working fluid enters the cold plate body (1) through the gas-liquid two-phase connector socket (5), most of the working fluid flows through the main simulated heat source adaptation channel area, and a small part flows through the auxiliary simulated heat source adaptation channel area. After evaporating and absorbing the heat from the heat source, it becomes a gas-liquid mixture and flows out from the gas-liquid two-phase connector socket (5), completing the heat exchange process.

[0031] Preferably, the internal flow channels of the cold plate body (1) include a main liquid inlet flow channel (1-1), an auxiliary simulated heat source adaptation flow channel area (1-2), a main simulated heat source adaptation flow channel area (1-9), and an outlet flow channel (1-8). When the working fluid enters the cold plate body, it is divided into two paths in the main liquid inlet flow channel (1-1). Most of the fluid flows to the main simulated heat source adaptation flow channel area (1-9) to absorb the heat from the main simulated heat source combination, and a small part of the fluid flows to the auxiliary simulated heat source adaptation flow channel area (1-2) to absorb the heat from the auxiliary simulated heat source combination. After absorbing heat through convective heat transfer, the fluid converges and flows out of the cold plate body in the outlet flow channel (1-8). The auxiliary simulated heat source adaptation channel area is a parallel microchannel; the main simulated heat source adaptation channel area (1-9) includes a flow splitting cavity (1-3), a water droplet-shaped turbulence microchannel (1-5), a confluence cavity (1-7), and a parallel flow splitting microchannel structure, which reduces the frictional resistance of the gas-liquid two-phase fluid, reduces the difference in saturated temperature (evaporation temperature) of the working fluid along the flow direction, and improves the heat source temperature uniformity.

[0032] Preferably, the flow splitting cavity (1-3) is a rectangular cross-section static pressure cavity, and the interior of the flow splitting cavity is provided with flow splitting ribs (1-4). The flow splitting ribs have an airfoil cross-section to reduce vortex generation and flow resistance. The angle of attack of the flow splitting ribs increases at each point along the main flow direction to guide the fluid to be evenly distributed to each parallel microchannel.

[0033] Preferably, the manifold (1-7) gathers the working fluid from the parallel split microchannel structure and flows towards the outlet channel of the cold plate body (1), with the cross-sectional area of ​​the manifold increasing along the flow direction. A flow-stabilizing protrusion (1-6) is provided at the inlet of the manifold (1-7). The flow-stabilizing protrusion is an arc-shaped or strip-shaped structure used to suppress backflow and eddies generated during the convergence of the gas-liquid two-phase fluids, thereby reducing flow resistance.

[0034] Preferably, the teardrop-shaped turbulence microchannels (1-5) are located directly below the main hot spot. The teardrop-shaped turbulence structures are uniformly arranged along the fluid flow direction in each parallel branching microchannel, forming an integrally molded teardrop-shaped protrusion. Adjacent rows of teardrop-shaped turbulence structures are staggered, with each row forming an equally spaced rectangular array with a spacing of 3-8 mm. The specific spacing is adjusted according to the heat flux density of the heat source, for example, when the heat flux density is greater than 200 W / cm². 2 When the spacing is less than 5mm, the height of the turbulence protrusion is the same as the height of the flow channel. The teardrop-shaped turbulence protrusion has an arc-shaped front surface and a streamlined contraction surface on the back, which can enhance fluid turbulence mixing and heat transfer.

[0035] Preferably, the main simulated heat source assembly (2) consists of a simulated heating block (2-2), a fixed support (2-1), and a heating rod (2-3), simulating a high heat flux density heat source. The simulated heating block (2-2) has a protrusion at its bottom, simulating the size of a hot spot, which contacts the surface of the cold plate body (1) via thermally conductive silicone grease. A cylindrical groove is provided in the middle of the simulated heating block, and the heating rod (2-3) contacts the wall of the cylindrical groove of the simulated heating block via thermally conductive silicone grease. The fixed support (2-1) is fixedly connected to the simulated heating block and then to the cold plate, providing stability and reducing contact thermal resistance. The heat from the heating rod (2-3) is conducted to the simulated heating block (2-2), then through the protrusion (reducing the contact area and simulating the heat flux density of a hot spot), and finally transferred to the working fluid inside the cold plate body (1).

[0036] Preferably, the auxiliary simulated heat source combination (3) is similar to the main simulated heat source combination (2), with the heating block having no protrusions that reduce the cross-section, simulating a general heat flux density heat source.

[0037] Preferably, the cold plate body (1) is formed by welding a substrate and a flow channel plate, and the flow channels of the cold plate body (1) are all formed on the flow channel plate and integrally molded with the flow channel plate. The substrate is made of aluminum alloy, copper alloy or titanium alloy, and the material of the flow channel plate is the same as that of the substrate.

[0038] Example

[0039] like Figure 1 The aforementioned low-flow-resistance, high-heat-exchange gas-liquid two-phase cold plate structure includes a cold plate body (1), a main simulated heat source assembly (2), an auxiliary simulated heat source assembly (3), a liquid connector socket (4), and a gas-liquid two-phase connector socket (5). The main simulated heat source assembly (2) and the auxiliary simulated heat source assembly (3) are arranged on the front and back surfaces of the cold plate body (1). The main simulated heat source assembly (2) corresponds to a main simulated heat source adaptation flow channel area inside the cold plate body (1), and the auxiliary simulated heat source assembly (3) corresponds to an auxiliary simulated heat source adaptation flow channel area inside the cold plate body (1). The two flow channel areas have different flow channel structures and different heat exchange capacities, namely a high-heat-exchange zone and a general-heat-exchange zone, respectively. The liquid connector socket (4) is the working fluid inlet inside the cold plate body (1), and the gas-liquid two-phase connector socket (5) is the gas-liquid mixed state outlet of the cold plate body (1). The diameter of the gas-liquid two-phase connector socket (5) is larger than the diameter of the liquid connector socket (4). After the liquid working fluid enters the cold plate body (1) from the gas-liquid two-phase connector socket (5), most of the working fluid flows through the main simulated heat source adaptation channel area, and a small part flows through the auxiliary simulated heat source adaptation channel area. After evaporating and absorbing the heat source heat, it becomes a gas-liquid mixture and flows out from the gas-liquid two-phase connector socket (5), completing the heat exchange process.

[0040] like Figure 2-3 The internal flow channels of the cold plate body (1) include a main liquid inlet flow channel, an auxiliary simulated heat source adaptation flow channel area, a main simulated heat source adaptation flow channel area, and an outlet flow channel. The auxiliary simulated heat source adaptation flow channel area is a parallel microchannel; the main simulated heat source adaptation flow channel area is a parallel split microchannel structure, consisting of a split cavity, a water droplet-shaped turbulence microchannel, and a confluence cavity, which reduces the frictional resistance of the gas-liquid two-phase fluid, reduces the difference in saturated temperature (evaporation temperature) of the working fluid along the flow direction, and improves the heat source uniformity.

[0041] like Figure 3 The main simulated heat source adapter flow channel divider cavity is a rectangular cross-section static pressure cavity. The interior of the divider cavity is provided with a divider rib. The divider rib has an airfoil cross-section to reduce vortex generation and flow resistance. The angle of attack of the divider rib increases at each point along the main flow direction to guide the fluid to be evenly distributed to each parallel microchannel.

[0042] like Figure 3 The main simulated heat source adapts to the flow channel area, where the working fluid from the parallel branch flow channel is gathered in the manifold and flows towards the outlet flow channel of the cold plate body (1). The cross-sectional area of ​​the manifold increases along the flow direction. A flow stabilizing protrusion is provided at the inlet of the manifold. The flow stabilizing protrusion is an arc-shaped or strip-shaped structure used to suppress backflow and eddies generated when the gas-liquid two-phase fluids converge, thereby reducing flow resistance.

[0043] like Figure 4 The teardrop-shaped turbulence microchannels are located directly below the main hot spot. These teardrop-shaped turbulence structures are uniformly arranged along the fluid flow direction within each parallel branch channel, forming an integrated teardrop-shaped protrusion. Adjacent rows of these structures are staggered, with each row forming an equally spaced rectangular array with a spacing of 3-8 mm, adjusted according to the heat flux density of the heat source. For heat flux densities greater than 200 W / cm², the spacing is less than 5 mm. The height of the turbulence protrusions matches the height of the flow channels. The upstream face of each teardrop-shaped turbulence protrusion is an arc surface, while the downstream face is a streamlined contraction surface, which enhances fluid turbulence mixing and heat transfer.

[0044] like Figure 5 The main simulated heat source assembly (2) consists of a simulated heating block, a fixed support, and a heating rod, simulating a high heat flux density heat source.

[0045] like Figure 6 The simulated heating block has a boss at the bottom of the simulated hot spot, and the boss contacts the surface of the cold plate body (1) through thermally conductive silicone grease; a cylindrical groove is provided in the middle of the simulated heating block, and the heating rod contacts the cylindrical groove wall of the simulated heating block through thermally conductive silicone grease.

[0046] like Figure 7 The fixed support is used to fix the simulated heating block and then to the cold plate, which can stabilize the heating block and reduce the contact thermal resistance. The heat of the heating rod is conducted to the simulated heating block, and then through the boss (to reduce the contact area and simulate the heat flux density of the hot spot) to the cold plate body (1), and finally to the working fluid inside the cold plate body (1).

[0047] like Figure 8 The auxiliary simulated heat source combination (3) is similar to the main simulated heat source combination (2), with no protrusions on the heating block that reduce the cross-section, simulating a general heat flux density heat source.

Claims

1. A low-flow-resistance, high-heat-exchange gas-liquid two-phase cold plate structure, characterized in that, include: The main body of the cold plate (1), the main simulated heat source assembly (2), the auxiliary simulated heat source assembly (3), the liquid connector socket (4), and the gas-liquid two-phase connector socket (5) are attached to the front and back sides of the main body of the cold plate (1). The main simulated heat source assembly (2) and the auxiliary simulated heat source assembly (3) are attached to the cold plate body (1) at the attachment position of the main simulated heat source assembly (2). The main simulated heat source adaptation flow channel area is provided inside the cold plate body (1) at the attachment position of the auxiliary simulated heat source assembly (3). The liquid connector socket (4) and the gas-liquid two-phase connector socket (5) are respectively set on the cold plate body (1). The liquid connector socket (4) is the working fluid inlet inside the cold plate body (1), and the gas-liquid two-phase connector socket (5) is the gas-liquid mixed state outlet of the cold plate body (1).

2. The low flow resistance, high heat exchange, gas-liquid two-phase cold plate structure according to claim 1, characterized in that, The internal flow channels of the cold plate body (1) include a main liquid inlet flow channel (1-1), an auxiliary simulated heat source adaptation flow channel area (1-2), a main simulated heat source adaptation flow channel area (1-9), and an outlet flow channel (1-8). When the working fluid enters the cold plate body, it is divided into two paths in the main liquid inlet flow channel (1-1). Most of the fluid flows to the main simulated heat source adaptation flow channel area (1-9) to absorb the heat from the main simulated heat source combination, and a small part of the fluid flows to the auxiliary simulated heat source adaptation flow channel area (1-2) to absorb the heat from the auxiliary simulated heat source combination. After absorbing heat through convective heat transfer, the fluid converges and flows out of the cold plate body in the outlet flow channel (1-8).

3. The low flow resistance, high heat exchange, gas-liquid two-phase cold plate structure according to claim 2, characterized in that, The main simulated heat source adaptation channel area (1-9) includes a flow distribution cavity (1-3), a water droplet-shaped turbulence microchannel (1-5), a confluence cavity (1-7), and a parallel flow distribution microchannel structure. The fluid is guided and evenly distributed to the parallel flow distribution microchannel structure through the flow distribution cavity (1-3). The confluence cavity (1-7) gathers the working fluid from the parallel flow distribution microchannel structure and flows to the outlet channel (1-8) of the cold plate body (1). The water droplet-shaped turbulence microchannel (1-5) is evenly arranged in each parallel flow distribution microchannel along the fluid flow direction.

4. The low flow resistance, high heat exchange, gas-liquid two-phase cold plate structure according to claim 3, characterized in that, The flow splitting cavity (1-3) is a rectangular cross-section static pressure cavity. The flow splitting cavity is provided with a flow splitting rib (1-4) inside. The flow splitting rib has an airfoil cross-section, and the angle of attack of the flow splitting rib (1-4) increases at each point along the main flow direction.

5. The low flow resistance, high heat exchange, gas-liquid two-phase cold plate structure according to claim 3, characterized in that, The inlet of the confluence cavity (1-7) is provided with a flow stabilizing protrusion (1-6). The flow stabilizing protrusion is an arc-shaped or strip-shaped structure, which is used to suppress backflow and eddy current generated when the gas-liquid two-phase fluids converge, and reduce flow resistance.

6. The low flow resistance, high heat exchange, gas-liquid two-phase cold plate structure according to claim 3, characterized in that, The teardrop-shaped turbulence microchannel (1-5) is an integrally formed teardrop-shaped protrusion. Adjacent rows of teardrop-shaped protrusions are arranged alternately, and each pair of rows is a rectangular array with equal spacing.

7. The low flow resistance, high heat exchange, gas-liquid two-phase cold plate structure according to claim 6, characterized in that, The spacing between the two columns of teardrop-shaped protrusions in the equally spaced rectangular array is 3-8 mm, and the specific spacing value is adjusted according to the heat flux density of the heat source.

8. The low flow resistance, high heat exchange, gas-liquid two-phase cold plate structure according to claim 6, characterized in that, The height of the protrusions (1-6) is the same as the height of the flow channel. The front surface of the protrusions is an arc surface, and the back surface is a streamlined contraction surface.

9. The low flow resistance, high heat exchange, gas-liquid two-phase cold plate structure according to claim 1, characterized in that, The main simulated heat source assembly (2) includes a simulated heating block (2-2), a fixed support (2-1), and a heating rod (2-3). The bottom of the simulated heating block (2-2) is provided with a boss the size of a simulated hot spot. The boss contacts the surface of the cold plate body (1) through thermally conductive silicone grease. A cylindrical groove is provided in the middle of the simulated heating block (2-2). The heating rod (2-3) contacts the wall of the cylindrical groove of the simulated heating block (2-2) through thermally conductive silicone grease. After the fixed support (2-1) is fixedly connected to the simulated heating block (2-2), it is then connected and fixed to the cold plate.

10. The low flow resistance, high heat exchange, gas-liquid two-phase cold plate structure according to claim 9, characterized in that, The auxiliary simulated heat source assembly (3) has the same structure as the main simulated heat source assembly (2), and the simulated heating block has no protrusions with a smaller cross-section.

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