High-load adaptive gas-liquid phase change vapor chamber

Abstract

The invention discloses a high-load adaptive gas-liquid phase change vapor chamber, the interior of the vapor chamber is a double-snakelike series channel with alternate reducing and multi-level channel design, and the channel is filled with a liquid working medium according to a certain volume ratio; a plurality of heat sources with different heat flux densities are arranged on an evaporation section of the gas-liquid phase change vapor chamber at unequal intervals, and meanwhile heat dissipation is conducted through condensation sections at the two ends. According to the vapor chamber, the cooperation of working medium flowing and heat transfer in channels on the two sides is enhanced through the series-connection type flow channel design, and it is ensured that the gas-liquid phase change vapor chamber is smoothly started and operated under the variable load environment condition; the alternative reducing channel increases the one-way capillary driving pressure difference and the matched flow resistance, and strengthens the working medium flowing driving force; the multi-level channel structure provides additional capillary force for assisting the liquid film to flow back and wet the evaporation section. The gas-liquid phase change vapor chamber has the advantages of being simple in structure, easy to miniaturize, high in heat transfer capacity, good in load adaptability and the like, and is suitable for the working mode of middle heating and two-end cooling.

Description

Technical Field

[0001] The invention relates to the technical field of two-phase heat transfer devices, and in particular to a high-load adaptable gas-liquid phase change vapor chamber. Background Art

[0002] Three-dimensional multi-layer array power-consuming devices are typical architectures of electronic information equipment such as integrated circuits, power battery packs, and airborne phased array radars. At present, power-consuming devices and equipment are developing rapidly in the direction of high integration and miniaturization. How to achieve efficient cooling and heat dissipation in confined spaces is crucial for the stable and reliable operation of power-consuming devices and equipment. Although conventional air-cooling and water-cooling active cooling solutions are mature in technology, there are still some shortcomings in dealing with efficient cooling and heat dissipation in confined spaces. For example, the air-cooling method itself has limited heat dissipation capacity, and the confined space further increases the wind resistance, which leads to worse heat dissipation effect; and if the water-cooling method is to achieve local heat dissipation close to the power-consuming device, it involves a complex three-dimensional water-cooling channel design, which is easy to cause uneven hydraulic pressure of the cooling fluid in each heat dissipation area, and further cause the problem of non-uniform thermal stress, affecting the reliability of the system. In addition, the water-cooling system also requires complex liquid storage and pumping devices to serve it.

[0003] In contrast, as a passive and efficient heat dissipation device that completely relies on heat drive, the vapor chamber has the advantages of simple structure, stability and reliability, high flexibility, easy matching with the heating surface, and strong heat transfer capacity. It has good application potential in complex heat dissipation problems in confined spaces. The working fluid of the conventional vapor chamber evaporates from the bottom hot end and condenses at the top cold end, and then the condensate is sucked back to the hot end surface by the internal capillary suction to re-evaporate to realize the evaporation-condensation cycle. However, this working mode based on capillary-driven condensate reflux is easily affected by gravity load, especially when the direction of gravity load is opposite to the direction of capillary suction force, it will directly hinder the reflux of condensate, thereby inducing the performance degradation or even failure of the vapor chamber. Compared with this working principle, the vapor chamber based on closed-loop micro-channel heat-driven gas-liquid oscillation phase change heat transfer can realize the superposition of thermal driving forces in multiple parallel channels, thereby expected to overcome the negative impact of gravity load on condensate reflux. Therefore, the vapor chamber based on the working principle of gas-liquid self-excited oscillation phase change heat transfer in micro-channels is expected to have better load adaptability, and also provide a new idea for the research and development of heat dissipation devices with high load adaptability. However, even for the above-mentioned vapor chamber that relies on heat-driven gas-liquid oscillation phase change heat transfer in micro-channels, it is still necessary to increase the number of bends to ensure sufficient thermal driving force in the channel when facing complex operating environments with actual variable loads or even overloads. Therefore, improving the design of the vapor chamber based on heat-driven gas-liquid oscillation phase change heat transfer in micro-channels and developing a gas-liquid phase change vapor chamber with high load adaptability is a solution.

[0004] Chinese invention patent application CN113251837A discloses a disc-shaped pulsating heat pipe temperature-averaging plate, in which a boiling tank is arranged at the center of a heat-conducting substrate to absorb the heat generated by a preset hot spot position. This central divergent structural characteristic determines that it is difficult to face the thermal management scenario of non-uniform multiple heat sources. Chinese invention patent application CN117029542A discloses a pulsating heat pipe with a spaced capillary wick and a preparation method thereof, which uses the suction force provided by the capillary wick structure to promote the reflux and rehydration of the working fluid in the evaporation section to improve the heat transfer limit, but the structure of the capillary wick itself will bring greater flow resistance and compress the flow space in the channel. Under the mutual game, the final improvement of heat transfer performance is relatively limited. Chinese invention patent application CN105547023A discloses a variable diameter pulsating heat pipe, which uses the difference in hydraulic diameter at the bend of the serpentine channel to form a large pressure difference to overcome the flow resistance brought by the micrometer-scale channel, so that the micro gas-liquid phase change heat-averaging plate can be started smoothly under variable load conditions, thereby achieving the purpose of improving heat transfer efficiency and load adaptability.

[0005] The above-mentioned existing technologies all attempt to improve the design of the working fluid flow channel inside the gas-liquid phase change vapor chamber to improve its heat transfer capacity and heat transfer limit. However, the current performance improvement scheme for the gas-liquid phase change vapor chamber still has many limitations, such as difficulty in coping with non-uniform multi-heat source conditions, increasing the condensate reflux capillary suction force while also significantly increasing the flow resistance, and limited load adaptability improvement. In view of the problem that the operation of traditional gas-liquid phase change vapor chambers is greatly negatively affected by changes in the load environment, it is necessary to develop high-efficiency heat transfer devices with higher load adaptability while taking into account excellent heat transfer performance and heat transfer limits. Summary of the invention

[0006] The problem to be solved by the present invention is to provide a high-load adaptable gas-liquid phase change heat sink, which can achieve effective thermal control of non-uniform multiple heat sources in confined spaces under variable load or even overload conditions by adopting a "central heating, two-end heat dissipation" working mode.

[0007] The present invention adopts the following technical scheme: a high-load adaptable gas-liquid phase change vapor chamber, suitable for a working mode of heating with multiple heat sources in the middle and cooling at both ends, with a lower base plate and an upper cover plate sealed and assembled by a vacuum diffusion welding process, and an internal working fluid flow channel adopting a double serpentine series channel;

[0008] The double serpentine series channel includes two half channels, which are mirror-symmetrical along the center line in the length direction of the long-width plane of the substrate; the two half channels respectively have n "U"-shaped elbows, which are connected in series through the upper and lower boundary straight channels to form n+1 parallel channels, and the hydraulic diameters of the channels on both sides of the "U"-shaped elbows are inconsistent, and an alternating variable diameter design is adopted;

[0009] The double serpentine series channel is a multi-level design, including a main channel and a secondary channel. The main channel is composed of double serpentine channels connected in series, and a number of secondary channels with equal hydraulic diameters are arranged at the top and bottom of each serpentine channel.

[0010] Furthermore, the gas-liquid phase change heat sink includes a condensation section and an evaporation section. The evaporation section adopts multi-heat source non-uniform heating. Multiple irregularly distributed heat sources with different heat flux densities are arranged in the evaporation section area. The heat is dissipated through the condensation sections at both ends. The condensation section area adopts air cooling or water cooling for heat dissipation.

[0011] Preferably, the hydraulic diameter of the double serpentine series channel of the gas-liquid phase change heat sink is 1 to 5 mm; the aspect ratio of the double serpentine series channel ranges from 0.25 to 1; the length ratio of the condensation section and the evaporation section of the gas-liquid phase change heat sink is 0.8 to 1.2.

[0012] Preferably, the number of "U"-shaped elbows n is ≥ 15, and the adjacent channels on both sides of the "U"-shaped elbow adopt an alternating variable diameter design, and the width ratio k of the adjacent channels on both sides ranges from 1.5 to 4:

[0013]

[0014] Among them, w1 and w2 represent the width of the wider side and narrower side channels of the same "U"-shaped elbow, respectively.

[0015] Preferably, the evaporation section adopts multi-heat source non-uniform heating, including a number of electric heating blocks distributed in a uniform array, the electric heating blocks are connected in parallel, and the several heating blocks form two heating units respectively used for the two half channels, and the heating power is independently controlled by independent DC power supplies; non-uniform heating is regulated by changing the relative size of the heat load applied to the heat transfer area on the left and right sides of the gas-liquid phase change heat sink.

[0016] Preferably, the condensing section adopts fin-fan coupled heat dissipation, and several groups of fin-fan coupled heat dissipation modules are symmetrically distributed on the upper and lower surfaces of the condensing section.

[0017] Preferably, the number of the secondary channels is 3 to 5, the height of the main channel is 3 to 6 times that of the secondary channels, and the width of the main channel is 5 to 10 times that of the secondary channels.

[0018] Preferably, the working medium flow channel inside the gas-liquid phase change heat sink is evacuated and sealed, and a filling hole is left at the midpoint of the long side of one side of the lower substrate, and the working medium is filled into the double serpentine series channel through the filling hole.

[0019] Preferably, the working fluid is selected according to the specific operating temperature range, including: methanol, ethanol, acetone, deionized water, FC-72, and the working fluid filling rate in the channel is 50% to 70%.

[0020] Furthermore, the heat transfer of the gas-liquid phase change heat spreader relies on the gas-liquid plugs randomly and continuously distributed in the double serpentine series channels under the action of surface tension. When the working fluid in the evaporation section in the middle of the heat spreader is heated and evaporated / boiled, the local pressure increases. The "bubble pump" effect generated in the evaporation section pushes the gas-liquid plugs in the channel to move to the condensation sections at both ends. While condensation releases heat, the local pressure decreases. The gas-liquid plugs in the double serpentine series channels perform reciprocating oscillation motion under the action of the non-uniform pressure difference between the hot and cold sections to transfer heat and mass.

[0021] Compared with the prior art, the present invention adopts the above technical solution and has the following technical effects:

[0022] 1. The flow and heat transfer of the working fluid in the mirror-symmetrical channel areas on both sides of the gas-liquid phase change heat spreader of the present invention have good synergy. When the working inclination angle changes, the operating load conditions of the heat spreader change accordingly. At this time, the side operating in the state of gravity can stimulate the start-up of the side in the state of gravity. When both sides of the heat spreader enter the quasi-stable operating state, the flow and heat transfer between the two sides can complement each other to achieve the excellent load adaptability of the heat spreader as a whole.

[0023] 2. The present invention adopts an alternatingly variable diameter non-uniform channel design, which generates a capillary pressure difference driving force with the same direction and a matching flow resistance difference through the difference in channel curvature radius at the "U"-shaped bends of the serpentine channel. The flow driving force generated in this way can be superimposed at each bend, which helps the gas-liquid two-phase working fluid in the heat spreader channel to enter a circulating flow state with higher heat transfer efficiency, thereby improving the heat transfer performance of the gas-liquid phase change heat spreader.

[0024] 3. In the multi-level channel design adopted by the present invention, the secondary channel with a smaller hydraulic diameter at the bottom of the main channel can not only provide nucleation sites to enhance boiling, but also provide additional capillary force for auxiliary condensation section working fluid to reflux and wet the evaporation section, thereby improving the heat transfer limit of the gas-liquid phase change heat sink. BRIEF DESCRIPTION OF THE DRAWINGS

[0025] Figure 1 A three-dimensional schematic diagram of a lower substrate with channels in a high-load adaptable gas-liquid phase change vapor chamber of the present invention;

[0026] Figure 2 A three-dimensional schematic diagram of the cover plate on the high-load adaptable gas-liquid phase change soaking plate of the present invention;

[0027] Figure 3 It is a schematic diagram of the processing and assembly process of the high-load adaptable gas-liquid phase change vapor chamber of the present invention;

[0028] Figure 4 This is a schematic diagram of the xoy cross-section channel structure of the high-load adaptable gas-liquid phase change heat sink of the present invention;

[0029] Figure 5It is a schematic diagram of the cross-sectional channel structure of the high-load adaptable gas-liquid phase change vapor chamber xoz of the present invention;

[0030] Figure 6 It is a schematic diagram of the principle of the alternating variable-diameter channels and multi-level channels of the high-load adaptable gas-liquid phase change vapor chamber of the present invention;

[0031] Figure 7 This is a schematic diagram of the structure of a device with simulated multi-heat source heating, air cooling and a rotating support in an embodiment of the present invention;

[0032] Figure 8 This is a comparison diagram of the wall temperature pulsation of the gas-liquid phase change vapor chamber and the uniform smooth channel gas-liquid phase change vapor chamber under the horizontal operation state of the embodiment when the heat load is 100W and 200W;

[0033] Fig. 9 It is a columnar comparison chart of equivalent thermal conductivity of the gas-liquid phase change vapor chamber of the embodiment and a solid 6063 aluminum alloy plate of the same specification under different working inclination angles and typical heat load conditions;

[0034] Fig.10 This is a columnar comparison chart of equivalent thermal conductivity of the vapor-liquid phase change vapor chamber of the embodiment and a solid 6063 aluminum alloy plate of the same specification under non-uniform heating and typical heat load conditions;

[0035] Explanation of symbols in the figure:

[0036] 1-lower substrate; 2-upper cover; 3-double serpentine series channel; 4-evaporation section; 5-liquid filling hole; 6-condensation section; 7-heating block; 8-heat dissipation ribs; 9-cooling fan; 10-gas-liquid phase change heat spreader; 11-rotating support platform; 12-positioning hole; 13-main channel; 14-secondary channel; 15-liquid phase; 16-capillary driven pressure difference; 17-welding package; 18-left heating area; 19-right heating area; 20-thin metal partition wall. DETAILED DESCRIPTION

[0037] In order to make the purpose, technical solution and advantages of the present invention clearer, the technical solution of the application is further elaborated in detail below in conjunction with the accompanying drawings. The described embodiments are only a part of the embodiments involved in the present invention. All non-innovative embodiments of other researchers in the field on this embodiment belong to the protection scope of the present invention. At the same time, for the step numbering in the embodiment of the present invention, it is only set for the convenience of explanation, and the order between the steps is not limited in any way. The execution order of each step in the embodiment can be adaptively adjusted according to the understanding of those skilled in the art.

[0038] In one embodiment of the present invention, a high load adaptable gas-liquid phase change vapor chamber, such as Figure 1 and Figure 2As shown, the gas-liquid phase change heat spreader 10 includes a lower base plate 1 and an upper cover plate 2 , the internal working fluid flow channel adopts a double serpentine series channel 3 , and a liquid filling hole 5 is reserved at the midpoint of the long side of one side of the lower base plate 1 .

[0039] like Figure 3 As shown, the upper cover plate 2 and the lower base plate 1 are welded and packaged 17, and the vacuum diffusion welding process is used for sealing and assembly. The two sides of the long sides are provided with mutually matching positioning holes 12 for positioning and fixing the heat spreader. The inside of the heat spreader after sealing and assembly needs to be evacuated. Acetone is selected as the working fluid of the heat spreader, and the liquid filling rate is 55%.

[0040] like Figure 4 As shown in the figure, a series of double serpentine channels are milled on the lower substrate 1 of the gas-liquid phase change heat sink 10, including heat transfer areas on both sides that are mirror-symmetrical about the center line in the length direction of the substrate xoy plane, and are interconnected through upper and lower boundary straight channels.

[0041] like Figure 5 As shown in the figure, the widths of two adjacent non-uniform main channels at the same "U"-shaped bend inside the gas-liquid phase change heat spreader 10 are 2.4 mm and 1.6 mm respectively, and the height is 1.2 mm. The bottom and top of the main channel are both provided with secondary channels separated by thin metal partitions 20, the number of channels is 4, the width is 0.25 mm, and the height is 0.2 mm.

[0042] Preferably, the serpentine loops in the heat transfer regions on both sides of this embodiment include 33 "U"-shaped bends (including 34 parallel channels along the length direction). The internal channels of the gas-liquid phase change heat plate 10, such as Figure 6 As shown, an alternating diameter change and multi-level channel improvement design is adopted, including a main channel 13 and a secondary channel 14. Through the alternating diameter change design, a capillary driven pressure difference 16 for driving the directional movement of the gas and liquid phases is generated at the interface where the gas plug contacts the liquid phase 15 on both sides of the channel. The multi-level channel improvement can also provide additional capillary driving force to assist the working fluid to reflux and wet the evaporation section.

[0043] Furthermore, the gas-liquid phase change heat sink includes a condensation section and an evaporation section. The evaporation section adopts multi-heat source non-uniform heating. Multiple irregularly distributed heat sources with different heat flux densities are arranged in the evaporation section area. The heat is dissipated through the condensation sections at both ends. The condensation section area adopts air cooling or water cooling for heat dissipation.

[0044] This embodiment constructs a heat transfer performance test device for a high-load adaptable gas-liquid phase change vapor chamber. Figure 7 As shown in , it includes a gas-liquid phase change heat sink 10, an electric heating block 7, heat dissipation ribs 8, a fan 9 and a rotating bracket 11.

[0045] The evaporation section 4 of the gas-liquid phase change heat spreader 10 is the heating area, which adopts multi-heat source non-uniform heating, including eight electric heating blocks distributed in a uniform array, the size of the electric heating block is 60mm×40mm, and the electric heating blocks are connected in parallel.

[0046] The two heating units composed of eight heating blocks control the heating power through independent DC power supplies to achieve independent control of the heating power of the left and right channel areas. The non-uniform heating is specifically controlled by changing the relative size of the heat load applied to the heat transfer area on the left and right sides of the heat spreader, which is quantitatively defined as the dimensionless thermal difference coefficient. The formula is as follows:

[0047]

[0048] Among them, Q 左 represents the heating power applied to the left heat transfer area 18, Q 右 represents the heating power applied to the right heat transfer area 19, Q 总 Represents the total heating power, the left heating area 18 is in the "hot on the bottom and cold on the top" gravity-following working mode, and the right heating area 19 is in the "cold on the bottom and hot on the top" reverse gravity working mode.

[0049] In particular, it is necessary to explain: It means that the heating power is fully applied to the right side. This means that the heating power is fully applied to the left side. This means that the heating power is more concentrated on the side with gravity. This means that the heating power is more concentrated on the anti-gravity side.

[0050] Furthermore, the condensation sections 6 at both ends of the gas-liquid phase change heat sink 10 are cooling areas, and the condensation sections 6 adopt a fin and fan coupled heat dissipation method, wherein four fin-fan coupled heat dissipation modules are symmetrically distributed on the upper and lower surfaces of the condensation section.

[0051] In addition, the vapor chamber heat transfer performance test platform also includes a rotating support base with a heating and cooling module for positioning, fixing and adjusting the working inclination of the vapor chamber. The rotating support platform can adjust the working inclination angle within the range of 0° to 180°. In the thermal performance test, the working inclination angle θ of the vapor chamber is 0°, 30°, 60° and 90°.

[0052] Figure 8 The comparison shows the wall temperature fluctuations of the high load adaptability gas-liquid phase change vapor chamber (referred to as the improved part) and the uniform smooth channel gas-liquid phase change vapor chamber (referred to as the prototype part) in the horizontal state heat transfer performance test when the heat load is 100W and 200W respectively. It can be seen that when the total heating power reaches 100W, the improved part can be started and operated smoothly, but the prototype part is still in a stagnant state.

[0053] As the heating power increases from 100W to 200W, the intermittent stagnation in the wall temperature change curve of the improved part gradually turns into continuous small-amplitude high-frequency pulsation, while the prototype part is still in a state of operation stagnation. At this time, the temperature difference between the evaporation section and the condensation section of the improved part is reduced, and the heat transfer performance is better.

[0054] In order to further quantify the performance advantages of the high load adaptability gas-liquid phase change vapor chamber proposed in the present invention, Fig. 9 and Fig.10 The comparison between the high load adaptability gas-liquid phase change vapor chamber and the same specification solid 6063 aluminum alloy plate under different heat loads (Q = 160W, 320W, 490W, 640W), working angles (θ = 0°, 30°, 60°, 90°) and dimensionless thermal coefficient With the increase of heat load, the thermal driving force of the working fluid in the channel is enhanced, and the equivalent thermal conductivity shows a trend of gradual increase.

[0055] As the working inclination angle increases, the equivalent thermal conductivity shows an opposite trend of gradually decreasing, but it can still maintain good heat transfer performance under reverse gravity operation conditions. In addition, the high load adaptability gas-liquid phase change heat sink has four typical dimensionless thermal coefficients. It can start smoothly and run stably under all conditions, and has excellent heat transfer capacity under non-uniform multi-heat source heating conditions.

[0056] It can be seen that the average equivalent thermal conductivity of the high-load adaptable gas-liquid phase change heat sink proposed in the present invention is 5.8 times that of the solid 6063 aluminum alloy plate of the same specification under the test conditions of a working inclination angle of 0° to 90°, and can even reach 10 times when the heat load is increased to 640W.

[0057] At the same time, under the premise of ensuring mechanical properties, its deadweight is only 82.6% of the solid 6063 aluminum alloy plate of the same specification. From the perspective of practical engineering application, the heat utilization system based on the gas-liquid phase change heat plate in the present invention can effectively utilize 86.1% of the heat generated on the surface of high-power consumption devices.

[0058] It can be seen that the "center heating, two-end heat dissipation" working mode adopted by the high-load adaptive gas-liquid phase change heat sink of the present invention can realize effective thermal control of non-uniform multiple heat sources in confined spaces under variable load or even overload conditions.

[0059] The above is only a preferred embodiment of the present invention. It should be pointed out that for ordinary technicians in this technical field, several improvements and modifications can be made without departing from the principle of the present invention. These improvements and modifications should also be regarded as the scope of protection of the present invention.

Claims

1. A high load adaptable gas-liquid phase change vapor chamber, characterized in that: The gas-liquid phase change heat spreader is sealed and assembled by a lower base plate (1) and an upper cover plate (2) through a vacuum diffusion welding process, and the internal working fluid flow channel adopts a double serpentine series channel (3); The double serpentine series channel includes two half channels, which are mirror-symmetrical along the center line in the length direction of the length-width plane of the substrate; the two half channels respectively have n "U"-shaped elbows, which are connected in series through the upper and lower boundary straight channels to form n+1 parallel channels, and the hydraulic diameters of the channels on both sides of the "U"-shaped elbows are inconsistent, and an alternating diameter change design is adopted; The double serpentine series channel is a multi-level design, comprising a main channel (13) and a secondary channel (14), wherein the main channel is composed of double serpentine channels connected in series, and a plurality of secondary channels (14) with equal hydraulic diameters are arranged at the top and bottom of each serpentine channel; The gas-liquid phase change vapor chamber is suitable for a working mode of heating with multiple heat sources in the middle and cooling at both ends.

2. The high load adaptable gas-liquid phase change vapor chamber according to claim 1, characterized in that: The gas-liquid phase change vapor chamber comprises a condensation section (6) and an evaporation section (4); the evaporation section (4) adopts multi-heat source non-uniform heating; a plurality of irregularly distributed heat sources with different heat flux densities are arranged in the evaporation section area; heat is dissipated through the condensation sections (6) at both ends; and the condensation section area adopts air cooling or water cooling for heat dissipation.

3. The high load adaptable gas-liquid phase change vapor chamber according to claim 2, characterized in that: The hydraulic diameter of the double serpentine series channel of the gas-liquid phase change heat spreader is 1 to 5 mm; the aspect ratio of the double serpentine series channel ranges from 0.25 to 1; and the length ratio of the condensation section (6) and the evaporation section (4) of the gas-liquid phase change heat spreader is 0.8 to 1.

2.

4. The high load adaptable gas-liquid phase change vapor chamber according to claim 3, characterized in that: The number of "U"-shaped elbows n≥15, the adjacent channels on both sides of the "U"-shaped elbow adopt an alternating variable diameter design, and the width ratio k of the adjacent channels on both sides ranges from 1.5 to 4: Among them, w1 and w2 represent the width of the wider and narrower side channels of the same "U"-shaped elbow, respectively.

5. The high load adaptable gas-liquid phase change vapor chamber according to claim 3, characterized in that: The evaporation section (4) adopts multi-heat source non-uniform heating, including a plurality of electric heating blocks distributed in a uniform array, the electric heating blocks are connected in parallel, and the plurality of heating blocks form two heating units respectively used for the two half channels, and the heating power is independently controlled by an independent DC power supply; The non-uniform heating is controlled by changing the relative size of the heat load applied to the left and right heat transfer areas of the gas-liquid phase change vapor chamber, which is quantitatively defined as the dimensionless heat difference coefficient The expression is as follows: Among them, Q 左 represents the heating power applied to the left heat transfer area, Q 右 represents the heating power applied to the heat transfer area on the right, Q 总 Represents the total heating power; It means that the heating power is fully applied to the right side. This means that the heating power is fully applied to the left side. This means that the heating power is more concentrated on the side with gravity. This means that the heating power is more concentrated on the anti-gravity side.

6. The high load adaptable gas-liquid phase change vapor chamber according to claim 3, characterized in that: The condensing section (6) adopts fin-fan coupled heat dissipation, and a plurality of groups of fin-fan coupled heat dissipation modules are symmetrically distributed on the upper and lower surfaces of the condensing section (6).

7. The high load adaptable gas-liquid phase change vapor chamber according to claim 1, characterized in that: The number of the secondary channels is 3 to 5, the height of the main channel is 3 to 6 times that of the secondary channels, and the width of the main channel is 5 to 10 times that of the secondary channels.

8. The high load adaptable gas-liquid phase change vapor chamber according to claim 1, characterized in that: The working medium flow channel inside the gas-liquid phase change heat spreader is evacuated and sealed, and a liquid filling hole (5) is reserved at the midpoint of the long side of one side of the lower substrate (1), and the working medium is filled into the double serpentine series channel (3) through the liquid filling hole (5).

9. The high load adaptable gas-liquid phase change vapor chamber according to claim 8, characterized in that: The working fluid is selected according to the specific operating temperature range, including: methanol, ethanol, acetone, deionized water, and FC-72, and the working fluid filling rate in the channel is 50% to 70%.

10. The high load adaptable gas-liquid phase change vapor chamber according to claim 9, characterized in that: The heat transfer of the gas-liquid phase change heat spreader relies on the gas-liquid plugs randomly and continuously distributed in the double serpentine series channels under the action of surface tension. When the working fluid in the evaporation section in the middle of the heat spreader is heated and evaporated / boiled, the local pressure increases. The "bubble pump" effect generated in the evaporation section pushes the gas-liquid plugs in the channel to move to the condensation sections at both ends. While condensation releases heat, the local pressure decreases. The gas-liquid plugs in the double serpentine series channels perform reciprocating oscillation motion under the action of the non-uniform pressure difference between the cold and hot sections to transfer heat and mass.

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