A two-phase radiator and cooling system

Abstract

This invention relates to the field of heat dissipation technology, specifically disclosing a two-phase radiator and cooling system, including a shell and an outlet pipe. The shell forms an inner cavity, and has a liquid inlet and a gas outlet, which are respectively connected to the inner cavity so that the liquid working fluid enters the inner cavity through the liquid inlet, exchanges heat with a heat source, and evaporates into a gaseous working fluid, which is then discharged through the gas outlet. The outlet pipe is located outside the shell and includes a first end and a second end opposite to each other. The first end is connected to the gas outlet to form an inlet end, and the second end forms an outlet end, with the cross-sectional area of ​​the outlet pipe gradually decreasing from the first end to the second end. In this application, by setting an outlet pipe at the gas outlet, and the cross-sectional area of ​​the outlet pipe gradually decreasing from the first end to the second end, a pressure difference is formed between the first end and the second end. Under this pressure difference, the gas can be accelerated to be discharged from the inner cavity, reducing the saturation temperature of the working fluid in the two-phase radiator and improving the heat transfer performance of the two-phase radiator.

Description

Technical Field

[0001] This invention relates to the field of heat dissipation technology, and more specifically, to a two-phase radiator and cooling system. Background Technology

[0002] A two-phase radiator is a device that utilizes the latent heat generated during the phase transition between a liquid and a gaseous state for efficient heat exchange. Forced convection two-phase radiators combine the characteristics of forced convection and two-phase flow (liquid and gas) to achieve better heat dissipation. In a forced convection two-phase radiator, the coolant is forced (usually by a pump) through a heat source, absorbs heat, evaporates into a gas, and is then guided to the cooling area (such as a condenser or heat sink), condenses back into a liquid, and releases heat, completing the cycle.

[0003] In data center heat dissipation, with the increase in power density and the higher requirements for energy efficiency, two-phase heat sinks are gradually becoming one of the preferred solutions for data center heat dissipation, as they avoid the limitations of traditional air cooling methods.

[0004] In the process of realizing this invention, the inventors discovered at least the following problems in the prior art:

[0005] Steam cannot easily escape from the cavity of a two-phase radiator, causing steam to accumulate inside the cavity and resulting in a higher saturation pressure. This, in turn, increases the saturation temperature of the working fluid inside the two-phase radiator, thus reducing the heat dissipation efficiency of the two-phase radiator. Summary of the Invention

[0006] In view of this, the purpose of the present invention is to provide a two-phase radiator and cooling system, the structural design of which can effectively solve the problem of reduced heat dissipation efficiency caused by steam accumulation in the two-phase radiator.

[0007] To achieve the above objectives, the present invention provides the following technical solution:

[0008] A two-phase radiator, comprising:

[0009] The housing has an inner cavity and is provided with a liquid inlet and a gas outlet. The liquid inlet and the gas outlet are respectively connected to the inner cavity so that the liquid working fluid enters the inner cavity through the liquid inlet, exchanges heat with the heat source, evaporates into a gaseous working fluid, and is discharged through the gas outlet.

[0010] An exhaust pipe is located outside the housing and includes a first end and a second end opposite to each other. The first end is connected to the gas outlet to form an air inlet, and the second end forms an air outlet. The cross-sectional area of ​​the exhaust pipe gradually decreases from the first end to the second end.

[0011] Optionally, in the above two-phase radiator, the cavity of the exhaust pipe is frustum-shaped.

[0012] Optionally, in the above two-phase radiator, the end face of the housing with the gas outlet is inclined relative to the horizontal plane, and the gas outlet is located at the end with a relatively higher vertical height relative to the two ends in the inclined direction of the end face.

[0013] Optionally, the above-mentioned two-phase radiator further includes an exhaust drive component connected to the exhaust pipe, the exhaust drive component being used to discharge the gas in the inner cavity through the exhaust pipe.

[0014] Optionally, the above-mentioned two-phase radiator further includes a capillary porous layer disposed on the housing. The capillary porous layer divides the inner cavity into a gaseous cavity and a liquid cavity. The gas outlet is connected to the gaseous cavity, and the liquid inlet is connected to the liquid cavity. At least a portion of the wall surface of the housing is made of a thermally conductive material so that the liquid working fluid in the liquid cavity can be heated and evaporated to form a gaseous working fluid, which then enters the gaseous cavity.

[0015] Optionally, in the above two-phase radiator, the liquid cavity includes a flow channel and a liquid accumulation chamber, the liquid accumulation chamber is connected to the liquid inlet, the flow channel is connected to the liquid accumulation chamber, and the capillary porous layer covers the opening of the flow channel.

[0016] Optionally, the above-mentioned two-phase radiator is provided with multiple flow channel grooves, and the multiple flow channel grooves are distributed in a grid pattern and interconnected with each other.

[0017] Optionally, in the above two-phase radiator, the flow channel groove is formed on the inner wall of the housing, and the inner wall of the housing forms the liquid accumulation cavity.

[0018] Optionally, in the above two-phase radiator, the liquid cavity further includes a communicating channel corresponding to the flow channel groove, one end of the communicating channel is connected to the liquid accumulation cavity, and the other end is connected to the corresponding flow channel groove.

[0019] Optionally, in the above two-phase radiator, the housing includes:

[0020] The main housing has the flow channel groove disposed thereon. The inner wall of the main housing is also provided with a first groove. The bottom of the first groove is provided with a second groove and a connecting groove. The connecting groove is connected to the second groove and the flow channel groove respectively.

[0021] A cover plate is disposed in the first groove, and the cover plate covers the opening of the connecting groove to form the connecting flow channel, and the cover plate covers the opening of the second groove to form the liquid accumulation cavity.

[0022] Optionally, in the above two-phase radiator, the main housing includes:

[0023] The substrate, wherein the flow channel groove, the first groove, the second groove and the connecting groove are all formed on the substrate;

[0024] A top cover is disposed on the substrate and forms the inner cavity with the substrate.

[0025] The two-phase radiator provided by this invention includes a housing and an exhaust pipe. The housing has an inner cavity and is provided with a liquid inlet and a gas outlet, which are respectively connected to the inner cavity. This allows a liquid working fluid to enter the inner cavity through the liquid inlet, exchange heat with a heat source, and evaporate into a gaseous working fluid, which is then discharged through the gas outlet. The exhaust pipe is located outside the housing and includes a first end and a second end. The first end is connected to the gas outlet to form an inlet end, and the second end forms an outlet end. The cross-sectional area of ​​the exhaust pipe gradually decreases from the first end to the second end.

[0026] The two-phase heat sink provided by this invention allows liquid working fluid to enter the inner cavity through the liquid inlet, exchange heat with the heat source, and evaporate into gaseous working fluid. The gaseous working fluid is discharged through the gas outlet and flows into the condenser for condensation. The condensed liquid working fluid is driven back to the liquid inlet to complete one cycle, thereby achieving effective heat dissipation for the device.

[0027] In this application, an outlet pipe is provided at the gas outlet, and the cross-sectional area of ​​the outlet pipe gradually decreases from the first end to the second end, according to Bernoulli's equation:

[0028]

[0029] In the formula, u A Let u be the cross-sectional velocity at the second end of the outlet pipe. B P is the cross-sectional velocity at the first end of the outlet pipe. A P is the static pressure at the cross-section of the second end of the exhaust pipe. B The static pressures H at the cross-section of the first end of the exhaust pipe are respectively. A H is the height of the cross-section at the second end of the exhaust pipe. B Let be the height of the cross-section at the first end of the outlet pipe, g be the acceleration due to gravity, and ρ be the density of the fluid. Because the cross-sectional area of ​​the lumen at the first end of the outlet pipe is relatively large, the flow velocity u at the cross-section at the first end of the outlet pipe is... B Smaller, static pressure P B The cross-sectional area of ​​the lumen at the second end of the exhaust pipe is relatively large. Correspondingly, the cross-sectional area of ​​the second end of the exhaust pipe is smaller, therefore the u-shape of the cross-section at the second end of the exhaust pipe is larger. A The flow velocity is relatively high, and the static pressure P A The pressure difference P is relatively small. Therefore, there is a pressure difference P between the second and first ends of the outlet pipe. B -P A In P B -P AThe pressure difference accelerates the outflow of gas from the inner cavity, preventing the accumulation of gaseous working fluid within the cavity and reducing the pressure inside the sealed cavity. This, in turn, lowers the saturation temperature of the working fluid inside the two-phase radiator, improving its heat dissipation efficiency.

[0030] In some embodiments, a capillary porous layer is provided inside the housing, which physically separates the inner cavity of the housing into a gaseous cavity and a liquid cavity. This achieves physical isolation between the gaseous and liquid cavities, preventing entrainment interference between the gaseous and liquid working fluids within the cavities and avoiding instability phenomena such as pressure pulsations. Furthermore, the liquid working fluid can form a thin liquid film on the capillary porous layer. During evaporation and boiling, the bubbles in the thin liquid film grow faster, detach more quickly, and detach more frequently, resulting in more effective liquid replenishment. This means that bubbles are more easily removed from the heated surface. Therefore, during the boiling of the thin liquid film vapor, the convective heat transfer coefficient is larger, and the heat transfer effect is stronger, making this two-phase radiator more suitable for heat dissipation of high-power devices.

[0031] To achieve the above objectives, the present invention also provides a cooling system comprising any of the aforementioned two-phase radiators. Since the aforementioned two-phase radiators possess the aforementioned technical effects, the cooling system comprising the two-phase radiators should also possess the corresponding technical effects. Attached Figure Description

[0032] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0033] Figure 1 This is a schematic diagram of a two-phase heat sink according to a specific embodiment of the present invention;

[0034] Figure 2 This is a front view of the housing according to a specific embodiment of the present invention;

[0035] Figure 3 This is a schematic diagram of the housing structure according to another specific embodiment of the present invention;

[0036] Figure 4 for Figure 3 The main view;

[0037] Figure 5 This is a schematic diagram of the assembly of the substrate, cover plate, and capillary porous layer.

[0038] Figure 6 An exploded view of the substrate, cover plate, and capillary porous layer;

[0039] Figure 7 This is a schematic diagram of the substrate structure;

[0040] Figure 8 This is a schematic diagram of the cover plate structure;

[0041] Figure 9 This is a front view of the capillary porous layer;

[0042] Figure 10 for Figure 9 Top view;

[0043] Figure 11 for Figure 9 A bottom view;

[0044] Figure 12 This is a schematic diagram of the cooling system according to a specific embodiment of the present invention.

[0045] Figure label:

[0046] 1-Two-phase radiator; 2-Condenser; 3-Pump; 4-Heat source;

[0047] 11-Shell; 12-Capillary porous layer; 13-Inner cavity; 14-Exhaust pipe; 15-Exhaust drive component;

[0048] 101-Liquid inlet; 102-Gas outlet; 131-Gaseous cavity; 132-Liquid cavity; 1321-Flow channel groove; 1322-Liquid accumulation cavity; 1323-Connecting flow channel; 1121-Liquid inlet pipe; 104-First groove; 105-Second groove; 106-Connecting groove; 107-Apartment through hole; 111-Main shell; 1111-Base plate; 1112-Top cover; 112-Cover plate;

[0049] 121-Metal mesh layer; 122-Capillary porous media layer; 123-Needle rib. Detailed Implementation

[0050] This invention discloses a two-phase radiator and cooling system to avoid the accumulation of gaseous working fluid in the cavity, reduce the saturation pressure in the cavity, and improve the heat dissipation efficiency of the two-phase radiator.

[0051] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0052] The two-phase radiator provided in this application utilizes an outlet pipe at the gas outlet, with the cross-sectional area of ​​the outlet pipe gradually decreasing from one end connected to the gas outlet to the other. This change in the cross-sectional area creates a pressure difference between the two ends of the outlet pipe, accelerating the discharge of the gaseous working fluid from the inner cavity through the gas outlet and the outlet pipe. Specifically, the two-phase radiator of this application can be a forced convection two-phase radiator, using a pump or other driving device to drive the medium flow. However, the two-phase radiator of this application is not limited to forced convection two-phase radiators; for example, it can utilize factors such as gravity to drive the medium flow without a driving device. The following embodiments mainly describe the structure and fit of the shell and the outlet pipe.

[0053] In some embodiments, please refer to Figures 1-2 The two-phase radiator provided by this invention includes a housing 11 and an exhaust pipe 14. The housing 11 forms an inner cavity 13, and is provided with a liquid inlet 101 and a gas outlet 102, which are respectively connected to the inner cavity 13. It is understood that the portion of the housing 11 other than the liquid inlet 101 and gas outlet 102 should be sealed, i.e., forming a closed inner cavity 13 except for the liquid inlet 101 and gas outlet 102. The housing 11 can be a one-piece housing 11, or, for ease of molding and sealing, a split housing 11, sealed and connected by conventional sealing methods. The liquid inlet 101 and gas outlet 102 are located in the housing 11. The liquid working fluid enters the inner cavity through the liquid inlet 101, exchanges heat with the heat source, and evaporates into a gaseous working fluid, which is then discharged through the gas outlet 102. Understandably, at least a portion of the casing 11 is made of a thermally conductive material to conduct heat from the heat source. This allows the liquid working fluid to absorb heat from the heat source and evaporate into a gaseous working fluid, thus dissipating heat from the heat source. Simultaneously, the gaseous working fluid is discharged through the gas outlet 102.

[0054] The vent pipe 14 is located outside the housing 11 and includes a first end and a second end. The first end is connected to the gas outlet 102 to form an inlet end, and the second end forms an outlet end. The cross-sectional area of ​​the vent pipe 14 gradually decreases from the first end to the second end. The gaseous working fluid enters the vent pipe 14 through the gas outlet 102 from the first end and exits from the second end. The cross-sectional area of ​​the vent pipe 14 varies to guide the flow of the gaseous working fluid. It is understood that the vent pipe 14 and the housing 11 can be an integral structure, such as the vent pipe 14 being part of the housing 11, or the vent pipe 14 and the housing 11 can be a separate structure sealed by a conventional sealing method. The first end of the vent pipe 14 is connected to the housing and located at the gas outlet 102. For example, the gas outlet 102 is not smaller than the cross-sectional area of ​​the first end of the vent pipe 14, such that the shape and size of the cavity at the first end of the vent pipe 14 are the same as those of the gas outlet 102. In this application, the shape of the cavity of the vent pipe 14 is mainly defined; the shape of the outer wall of the vent pipe 14 can be set as needed and is not specifically limited here. For example, the wall thickness of the vent pipe 14 is uniform throughout.

[0055] Using the two-phase heat sink provided by this invention, the liquid working fluid enters the inner cavity 13 through the liquid inlet 101, and evaporates into a gaseous working fluid after exchanging heat with the heat source. The gaseous working fluid is discharged from the gas outlet 102 through the gas outlet pipe 14 and flows into the condenser for condensation. The condensed liquid working fluid is driven back to the liquid inlet 101 to complete one cycle, thereby achieving effective heat dissipation for the device.

[0056] In this application, an exhaust pipe 14 is provided, and the cross-sectional area of ​​the exhaust pipe 14 gradually decreases from the first end to the second end. According to Bernoulli's equation:

[0057]

[0058] In the formula, u A The cross-sectional velocity u at the second end of the outlet pipe 14 B P is the cross-sectional velocity at the first end of the outlet pipe 14. A P is the static pressure at the cross-section of the second end of the exhaust pipe 14. B The static pressure H at the cross-section of the first end of the exhaust pipe 14 are respectively. A H is the height of the cross-section at the second end of the exhaust pipe 14. B Let be the height of the cross-section at the first end of the exhaust pipe 14, and g be the acceleration due to gravity. Because the cross-sectional area of ​​the cavity at the first end of the exhaust pipe 14 is relatively large, the flow velocity u at the cross-section of the first end of the exhaust pipe 14 is... B Smaller, static pressure P B The cross-sectional area of ​​the lumen at the second end of the exhaust pipe 14 is relatively large. Correspondingly, the cross-sectional area of ​​the second end of the exhaust pipe 14 is smaller, therefore the u-shape of the cross-section at the second end of the exhaust pipe 14 is relatively small. AThe flow velocity is relatively high, and the static pressure P A The pressure difference P is relatively small. Therefore, there is a pressure difference P between the second end and the first end of the exhaust pipe 14. B -P A In P B -P A The pressure difference accelerates the gas exit from the inner cavity, preventing the accumulation of gaseous working fluid in the inner cavity 13 and reducing the pressure in the inner cavity 13. This, in turn, lowers the saturation temperature of the working fluid in the two-phase radiator and improves the heat dissipation efficiency of the two-phase radiator.

[0059] In some embodiments, the cavity of the vent pipe 14 is frustoconical. A boss-shaped vent pipe 14 is provided on the housing 11, and the cavity of the vent pipe 14 is frustoconical, meaning the cross-section of the vent pipe 14 is circular, and the radius of the circular cross-section gradually decreases from the first end to the second end. This design satisfies the requirement that the cross-sectional area of ​​the cavity gradually decreases from the first end to the second end, while also ensuring a smooth transition around the cavity without dead corners, facilitating the discharge of gaseous working fluid.

[0060] In some embodiments, please refer to Figure 3 and Figure 4 The end face of the housing 11 with the gas outlet 102 is inclined relative to the horizontal plane, and the gas outlet 102 is located at the end with the relatively higher vertical height relative to the two ends of the inclined direction of the end face. For example, the bottom surface of the housing 11 is flat, the gas outlet is located on the top surface of the housing 11, and the top surface is inclined away from the end away from the gas outlet 102 towards the end with the gas outlet 102, moving away from the bottom surface. Figure 3 and Figure 4 The top surface slopes upwards from left to right. By tilting the end face of the housing 11 where the gas outlet 102 is located, the steam generated by the heat source diffuses within the cavity. For example, the steam generated by the heat source in the middle region diffuses outwards, and some of the steam diffuses to a region with a smaller cross-section at one end, forming a high-pressure zone. The other part diffuses to one end of the gas outlet 102. Due to its larger cross-section and volume, the pressure formed at the same mass of steam at the gas outlet 102 is smaller. Therefore, the steam is more likely to flow to the region with a larger cross-section, and thus more likely to accumulate near the gas outlet 102, and then be discharged through the outlet pipe 14. The tilted surface and the shape of the outlet pipe 14 cavity form a double-flow guiding structure, accelerating the discharge of the gaseous working fluid in the inner cavity.

[0061] In some embodiments, the two-phase heat sink further includes an exhaust drive component 15 connected to the exhaust pipe 14, used to discharge gas in the inner cavity 13 through the exhaust pipe 14. For example, the exhaust drive component 15 is a fan. When the heat source, such as the chip, has a high power and generates a large amount of gaseous working fluid in the inner cavity, the flow guiding device alone cannot effectively discharge the gaseous working fluid. The exhaust drive component 15 can accelerate the discharge of gas, reduce the saturation pressure in the inner cavity, lower the saturation temperature of evaporation and boiling, increase the heat transfer temperature difference, and improve the heat transfer performance of the two-phase heat sink.

[0062] In some embodiments, please refer to Figure 1 and Figure 2 The two-phase radiator also includes a capillary porous layer 12. The capillary porous layer 12 is disposed within the housing 11, dividing the inner cavity 13 into a gaseous cavity 131 and a liquid cavity 132. On one hand, the micropores within the capillary porous layer 122 have a certain capillary effect, allowing the liquid in the liquid cavity 132 to fully wet the capillary porous layer 12. On the other hand, due to the relatively large flow resistance coefficient of the capillary porous layer 12, it is difficult for the liquid in the liquid cavity 132 to seep into the gaseous cavity 131 through the porous medium layer. The gas outlet 102 is connected to the gaseous cavity 131, and the liquid inlet 101 is connected to the liquid cavity 132. At least a portion of the walls of the housing 11 are made of a thermally conductive material. It is understood that the entire housing 11 can be made of a thermally conductive material, or only a portion of the walls of the housing can be made of a thermally conductive material. In use, the housing 11 can be fitted with a heat source by a wall surface made of thermally conductive material. The heat from the heat source is conducted through the housing 11 to the liquid working fluid in the liquid cavity 132, so that the liquid working fluid can be heated and evaporated to form a gaseous working fluid, which then enters the gas cavity 131. It should be noted that when the capillary porous layer 12 divides the inner cavity 13 into the gas cavity 131 and the liquid cavity 132, the above-mentioned vent pipe 14 can accelerate the discharge of the gaseous working fluid in the gas cavity 131.

[0063] Liquid working fluid enters liquid cavity 132 through liquid inlet 101. Under the action of capillary force, the liquid in liquid cavity 132 can wet the capillary porous dielectric layer 122 located on top of it. At the same time, through the heat conduction of the shell 11, the liquid working fluid in liquid cavity 132 can be heated and evaporated to form gaseous working fluid, which enters gas cavity 131. After the vapor accumulates in gas cavity 131, it is discharged from gas outlet 102 and flows into condenser 2 for condensation. The condensed subcooled liquid is driven back to liquid inlet 101 to complete a cycle, achieving effective heat dissipation for the device.

[0064] By setting a capillary porous layer 12 inside the shell 11, the inner cavity 13 of the shell 11 is physically separated into a gaseous cavity 131 and a liquid cavity 132. That is, the gaseous cavity 131 and the liquid cavity 132 achieve physical isolation between gas and liquid, and solve the problem of entrainment interference between steam and liquid working fluid in the cavity.

[0065] In some embodiments, at least a portion of the wall surface of the housing 11 with the capillary porous layer 12 is made of a thermally conductive material, or at least the portion of the housing 11 adjacent to the wall surface with the capillary porous layer 12 is made of a thermally conductive material. It is understood that the housing 11 can be entirely made of a thermally conductive material, or only the wall surface with the capillary porous layer 12 or its adjacent surface can be made of a thermally conductive material. In use, a heat source can be attached to the wall surface of the housing 11 with the capillary porous layer 12 or its adjacent surface, and the heat from the heat source is conducted to the capillary porous layer 12 through the housing 11. The heat from the device is conducted to the capillary porous layer 12 through the housing 11, causing a phase change in the liquid working fluid within the capillary porous layer 12, generating vapor. Because the liquid working fluid can form a thin liquid film on the capillary porous layer 12, the bubbles in the thin liquid film grow faster and detach faster and more frequently during evaporation and boiling. The replenishment of the liquid working fluid is more effective, meaning that the bubbles are more likely to detach from the heated surface, which improves the detachment speed of the bubbles and the stability of the system operation. Therefore, when the thin liquid film vapor boils, the convective heat transfer coefficient is larger and the heat transfer effect is stronger, making this two-phase radiator more suitable for heat dissipation of high-power devices.

[0066] In some embodiments, the two-phase radiator is a forced convection two-phase radiator. Under the action of capillary force and forced convection, the liquid working fluid in the liquid cavity 132 can fully wet the capillary porous media layer 122 located on top of it. Due to the forced convection, the wettability of the capillary porous layer 12 of the two-phase radiator is improved, avoiding the problem of capillary limit caused by insufficient capillary liquid supply leading to burn-out.

[0067] In some embodiments, the liquid cavity 132 includes a flow channel 1321 and a liquid accumulation cavity 1322. The liquid accumulation cavity 1322 is connected to the liquid inlet 101, and the flow channel 1321 is connected to the liquid accumulation cavity 1322. A capillary porous layer 12 covers the opening of the flow channel 1321. The liquid accumulation cavity 1322 provides a large accommodating space for the liquid working fluid. The coolant enters the liquid accumulation cavity 1322 through the liquid inlet 101 and is then guided to the capillary porous layer 12 through the flow channel 1321. The flow path of the liquid working fluid correspondingly includes the liquid inlet 101, the liquid accumulation cavity 1322, the flow channel 1321, and the channels of the capillary porous layer 12. On the one hand, the flow channel 1321 can guide the liquid working fluid. On the other hand, the capillary porous layer 12 is easily formed above the flow channel 1321. Liquid is supplied to the capillary porous layer 12 through the narrow flow channel 1321, achieving near-thin film boiling. This avoids traditional pool boiling, reduces the impact of the boiling liquid level on bubble detachment, and greatly improves its heat dissipation capacity. For example, the width of the flow channel 1321 is much smaller than the width of the liquid accumulation chamber 1322.

[0068] In some specific examples, multiple flow channels 1321 are provided, and these multiple flow channels 1321 are distributed in a crisscross pattern in a grid-like manner and are interconnected. It should be noted that "multiple" in this application refers to two or more. By setting multiple flow channels 1321 and distributing them in a grid-like manner, the liquid working fluid can flow into the grid-like distribution of the flow channels 1321, thus forming a larger overall distribution area, which can cooperate with the larger capillary porous layer 12, thereby improving the heat dissipation efficiency of the two-phase heat sink.

[0069] In some embodiments, please refer to Figures 5-7 The flow channel 1321 is formed on the inner wall of the housing 11, and the inner wall of the housing 11 forms a liquid accumulation cavity 1322. The flow channel 1321 on the inner wall of the housing 11, and the liquid accumulation cavity 1322 formed by the inner wall of the housing 11, results in a simple structure. In other embodiments, a separate component can be provided inside the housing 11, and a flow channel 1321 can be formed on this component, or a liquid accumulation cavity can be provided within this component.

[0070] When the flow channel 1321 is formed on the inner wall of the housing 11, for example, at least the area of ​​the housing 11 where the flow channel 1321 is provided is made of a thermally conductive material.

[0071] In some embodiments, the liquid cavity 132 further includes a communicating channel 1323 corresponding to the flow channel 1321. One end of the communicating channel 1323 is connected to the liquid accumulation cavity 1322, and the other end is connected to the corresponding flow channel 1321. The liquid accumulation cavity 1322 is connected to the flow channel 1321 through the communicating channel 1323, allowing the liquid working medium to enter the flow channel 1321 along the communicating channel 1323. Specifically, the flow path of the liquid working medium includes the liquid inlet 101, the liquid accumulation cavity 1322, the communicating channel 1323, the flow channel 1321, and the pores of the capillary porous layer 12. By setting the length and path of the communicating channel 1323, the different positional distribution requirements of the liquid accumulation cavity 1322 and the flow channel 1321 can be met.

[0072] In some embodiments, please refer to Figure 1 , Figure 7 and Figure 8 The housing 11 includes a main housing 111 and a cover plate 112. A flow channel 1321 is disposed in the main housing 111. The inner wall of the main housing 111 also has a first groove 104. The bottom of the first groove 104 has a second groove 105 and a connecting groove 106, which communicate with both the second groove 105 and the flow channel 1321. The bottom of the first groove 104 forms a recessed platform, on which the second groove 105 and the connecting groove 106 are formed. It is understood that the length of the second groove 105 is less than the length of the first groove 104, or the width of the second groove 105 is less than the width of the first groove 104, or both the length and width of the second groove 105 are less than the length and width of the first groove 104. For example, the width of the connecting groove 106 is much smaller than the width of the second groove 105. In this embodiment, several straight channels and grid-like flow channels connected to the liquid accumulation cavity 1322 are formed on the sidewall. The straight channels are also known as connecting flow channels 1323, and the grid-like flow channels are also known as flow channel grooves 1321. The number of connecting grooves 106 is specifically the same as the number of flow channel grooves 1321 extending in the same direction. For example, Figure 5 As shown, there are five flow channel grooves 1321 extending laterally and eight flow channel grooves 1321 extending longitudinally, and the corresponding five connecting grooves 106 are provided and extend laterally.

[0073] A cover plate 112 is disposed in the first groove 104, covering the opening of the connecting groove 106 to form a connecting flow channel 1323, and covering the opening of the second groove 105 to form a liquid accumulation cavity 1322. The shell 11 adopts a split structure, utilizing the cooperation of the main shell 111 and the cover plate 112, by opening the first groove 104, the second groove 105, and the connecting groove 106 on the main shell 111, and sealing them with the cover plate 112, thereby forming the liquid accumulation cavity 1322 and the connecting flow channel 1323. The cover plate 112 and the main shell 111 form a sealed gas cavity 131. As described above, the structure is simple, facilitates the molding of the shell 11, and enables effective drainage of the liquid working fluid.

[0074] For example, the first groove 104 is a quadrilateral groove, such as a rectangular groove, the second groove 105 is a quadrilateral groove, such as a rectangular groove, the cover plate 112 is a quadrilateral plate, such as a rectangular plate, the bottom surface of the cover plate 112 is in contact with the bottom of the groove of the first groove 104, and the four sides of the cover plate 112 are in contact with and sealed to the four sides of the first groove 104.

[0075] In some embodiments, the cover plate 112 is provided with a liquid inlet pipe 1121, and the main housing 111 is provided with a clearance through hole 107. The liquid inlet pipe 1121 is disposed in the clearance through hole 107 and is sealed to the main housing 111. The top opening of the liquid inlet pipe 1121 forms a liquid inlet 101. The shape of the liquid inlet pipe 1121 can be set as needed and is not specifically limited here. The top of the liquid inlet pipe 1121 can be higher than the top surface of the main housing 111, or flush with or slightly lower than the top surface of the main housing 111. Here, the top surface refers to the top outer wall surface of the main housing 111. Of course, the top of the liquid inlet pipe 1121 should not be lower than the top inner wall surface of the main housing 111. With the above configuration, the structure is simple and ensures that the liquid inlet 101 can be exposed from the main housing 111, which is convenient for connection with the cooling system pipeline. Furthermore, the liquid inlet pipe 1121 can be connected to the liquid accumulation chamber 1322, while not connected to the gas chamber 131, ensuring reliable physical isolation between the gas and liquid phases.

[0076] In some embodiments, please refer to Figure 1The main housing 111 includes a substrate 1111 and a top cover 1112. The flow channel 1321, the first groove 104, the second groove 105, and the connecting groove 106 are all formed on the substrate 1111. The top cover 1112 is disposed on the substrate 1111 and forms an inner cavity 13 with the substrate 1111. The main housing 111 adopts a split structure to facilitate the forming of the flow channel 1321, the first groove 104, the second groove 105, and the connecting groove 106. It is understood that the top cover 1112 and the substrate 1111 should be sealed together; the specific sealing method can be conventional sealing methods such as bonding or sealing rings. The shape of the top cover 1112 can be set as needed to form a closed inner cavity 13 with the substrate 1111, and can be separated into a gas cavity 131 and a liquid cavity 132 by a capillary porous layer 12. The gas outlet 102 is specifically located on the top cover 1112. For example, the substrate 1111 is plate-shaped, and the top cover 1112 includes a top plate and side plates connected around the top plate. As shown in the figure, the substrate 1111 is rectangular, and the top cover 1112 includes a top plate and front, rear, left, and right side plates connected to the front, rear, left, and right sides of the top plate. It can be understood that the top plate, front side plate, rear side plate, left side plate, and right side plate can be either an integral structure or a separate structure connected by conventional fixing methods.

[0077] In some specific examples, the vent pipe 14 is located on the top cover 1112. Specifically, the top plate of the top cover 1112 is inclined upward from left to right, and the vent pipe 14 is located on the right side of the top plate.

[0078] In some embodiments, please refer to Figures 9-11 The capillary porous layer 12 includes a metal mesh layer 121 and a capillary porous media layer 122 disposed on the metal mesh layer 121. The metal mesh layer 121 faces the liquid cavity 132, and the capillary porous media layer 122 faces the gas cavity 131. The metal mesh layer 121 provides a forming base for the capillary porous media layer 122 and can be well connected to the shell 11. Furthermore, the metal mesh layer 121 provides a certain capillary force to cooperate with the capillary porous media layer 122. The capillary porous media layer 122 utilizes the capillary force formed by its porous structure to adsorb the liquid working fluid.

[0079] In some embodiments, the capillary porous layer 12 further includes ribs 123 disposed on the capillary porous dielectric layer 122. By forming ribs 123 on the capillary porous dielectric layer 122, the expanded area of ​​the capillary porous dielectric layer 122 is further increased, thereby improving the heat dissipation efficiency of the two-phase heat sink.

[0080] In some specific examples, the wire mesh layer 121 is sintered onto the inner wall of the shell 11, and the capillary porous media layer 122 is sintered or electrodeposited onto the wire mesh layer 121. When preparing the capillary porous layer 12, the wire mesh can first be sintered onto the inner wall of the shell 11. If the inner wall of the shell 11 has multiple flow channels 1321 distributed in a grid pattern, one or more layers of wire mesh are sintered onto the flow channels 1321. After the wire mesh is sintered and fixed, the capillary porous media layer 122 is prepared on top of it by copper powder sintering or electrodeposition. To increase the expanded area of ​​the capillary porous media layer 122, several needle ribs 123 can be further sintered or electrodeposited onto the capillary porous media layer 122.

[0081] In some specific examples, the housing 11 includes a substrate 1111, a cover plate 112, and a top cover 1112. The substrate 1111 has a first groove 104, a second groove 105, a connecting groove 106, and a flow channel groove 1321. A capillary porous layer 12 is disposed on and connected to the flow channel groove 1321. The capillary porous layer 12 physically isolates the liquid working fluid in the mesh-distributed first channel from the vapor in the sealed gas cavity 131 formed by the top cover 1112 and the substrate 1111. The capillary porous layer 12 itself has a relatively large flow resistance coefficient, making it difficult for the liquid working fluid in the mesh-distributed flow channel groove 1321 to permeate into the gas cavity 131.

[0082] For example, taking a pump-driven two-phase radiator as an example, its working principle is as follows: the liquid working fluid returning from the liquid pipeline enters the liquid accumulation chamber 1322 through the liquid inlet 101 of the cover plate 112, and the liquid working fluid in the liquid accumulation chamber 1322 is distributed to each mesh channel groove 1321 after passing through several connecting channels 1323.

[0083] The liquid working medium overflows from the top of the flow channel 1321. Under the action of pumping and capillary force, the liquid working medium can fully wet the capillary porous layer 12 located on top of it. Due to the action of active pumping, the problem of capillary limit caused by insufficient capillary liquid supply can be avoided.

[0084] A heat source (such as a chip) is located at the bottom of the substrate 1111. Heat is transferred to the capillary porous layer 12 through the thermal conductivity of the substrate 1111 and the thermal conductivity of the walls forming the flow channel grooves 1321 on the substrate 1111. The heat conducted to the capillary porous layer 12 causes the liquid working fluid inside the capillary porous layer 12 to undergo a phase change, generating vapor. After the vapor accumulates in the gas chamber 131, it is discharged from the gas outlet 102, flows through the gas pipeline into the condenser 2 for condensation, and the condensed subcooled liquid is driven by the pump 3 to return to the liquid inlet 101 of the heat sink, thus completing one cycle.

[0085] Based on the two-phase radiator provided in the above embodiments, the present invention also provides a cooling system, which includes any one of the two-phase radiators in the above embodiments. Since this cooling system uses the two-phase radiator in the above embodiments, the beneficial effects of this cooling system are explained in the above embodiments.

[0086] Please see Figure 12 In some embodiments, the cooling system includes a condenser 2, a pump 3, and any of the aforementioned two-phase radiators 1. The gas outlet 102 of the two-phase radiator 1 is connected to the inlet of the condenser 2, and the outlet of the condenser 2 is connected to the liquid inlet 101 of the two-phase radiator 1 via the pump 3. The active liquid supply method driven by the pump 3 to the capillary porous layer 12 solves the capillary limit problem caused by insufficient capillary liquid supply to the capillary porous layer 12.

[0087] The various embodiments in this specification are described in a progressive manner, with each embodiment focusing on the differences from other embodiments. The same or similar parts between the various embodiments can be referred to each other.

[0088] The above description of the disclosed embodiments enables those skilled in the art to make or use the invention. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the general principles defined herein may be implemented in other embodiments without departing from the spirit or scope of the invention. Therefore, the invention is not to be limited to the embodiments shown herein, but is to be accorded the widest scope consistent with the principles and novel features disclosed herein.

Claims

1. A two-phase radiator, characterized in that, include: The housing (11) has an inner cavity (13) and is provided with a liquid inlet (101) and a gas outlet (102). The liquid inlet (101) and the gas outlet (102) are respectively connected to the inner cavity (13) so that the liquid working fluid enters the inner cavity (13) through the liquid inlet (101) and evaporates into a gaseous working fluid after exchanging heat with the heat source. The gaseous working fluid is discharged through the gas outlet (102). An exhaust pipe (14) is provided outside the housing (11) and includes a first end and a second end opposite to each other. The first end is connected to the gas outlet (102) to form an air inlet end, and the second end forms an air outlet end. The cross-sectional area of ​​the exhaust pipe (14) gradually decreases from the first end to the second end. It also includes a capillary porous layer (12) disposed on the shell (11). The capillary porous layer (12) divides the inner cavity (13) into a gaseous cavity (131) and a liquid cavity (132). The gas outlet (102) is connected to the gaseous cavity (131), and the liquid inlet (101) is connected to the liquid cavity (132). At least part of the wall surface of the shell (11) is made of a thermally conductive material so that the liquid working fluid in the liquid cavity (132) can be heated and evaporated to form a gaseous working fluid, which then enters the gaseous cavity (131). Under capillary action, the liquid in the liquid cavity (132) can fully wet the capillary porous layer (12) and form a thin liquid film on the capillary porous layer (12). The shell (11) has at least a portion of the wall surface of the capillary porous layer (12) as a heat-conducting material, or the portion of the shell (11) adjacent to the wall surface of the capillary porous layer (12) is a heat-conducting material, so that the heat from the heat source is conducted to the capillary porous layer (12) through the shell (11), causing the liquid working fluid of the capillary porous layer (12) to undergo a phase change. The liquid cavity (132) includes a flow channel (1321) and a liquid accumulation cavity (1322). The liquid accumulation cavity (1322) is connected to the liquid inlet (101). The flow channel (1321) is connected to the liquid accumulation cavity (1322). The capillary porous layer (12) covers the opening of the flow channel (1321). The housing (11) includes: The main housing (111) has a flow channel groove (1321) provided on the main housing (111). The inner wall of the main housing (111) is also provided with a first groove (104), and the bottom of the first groove (104) is provided with a second groove (105). A cover plate (112) is disposed in the first groove (104), and the cover plate (112) covers the opening of the second groove (105) to form the liquid accumulation cavity (1322).

2. The two-phase radiator according to claim 1, characterized in that, The lumen of the air outlet pipe (14) is frustum-shaped.

3. The two-phase radiator according to claim 1, characterized in that, The end face of the housing (11) with the gas outlet (102) is inclined relative to the horizontal plane, and the gas outlet (102) is located at the end with a relatively higher vertical height relative to the two ends in the inclined direction of the end face.

4. The two-phase radiator according to claim 1, characterized in that, It also includes an exhaust drive component (15) connected to the exhaust pipe (14), the exhaust drive component (15) being used to discharge the gas in the inner cavity (13) through the exhaust pipe (14).

5. The two-phase radiator according to any one of claims 1-4, characterized in that, The system has multiple flow channels (1321), which are arranged in a grid pattern and interconnected.

6. The two-phase radiator according to claim 5, characterized in that, The flow channel (1321) is formed on the inner wall of the housing (11), and the inner wall of the housing (11) forms the liquid accumulation cavity (1322).

7. The two-phase radiator according to any one of claims 1-4, characterized in that, The liquid cavity (132) also includes a connecting channel (1323) corresponding to the flow channel groove (1321). One end of the connecting channel (1323) is connected to the liquid accumulation cavity (1322), and the other end is connected to the corresponding flow channel groove (1321).

8. The two-phase radiator according to claim 7, characterized in that, The bottom of the first groove (104) is provided with a connecting groove (106), which is connected to the second groove (105) and the flow channel groove (1321) respectively; The cover plate (112) covers the opening of the connecting groove (106) to form the connecting channel (1323).

9. The two-phase radiator according to claim 8, characterized in that, The main housing (111) includes: The substrate (1111), the flow channel groove (1321), the first groove (104), the second groove (105) and the connecting groove (106) are all formed on the substrate (1111); A top cover (1112) is disposed on the substrate (1111) and together with the substrate (1111) forms the inner cavity (13).

10. A cooling system comprising a condenser (2), a pump (3), and a radiator, characterized in that, The radiator is a two-phase radiator (1) as described in any one of claims 1-9, the gas outlet (102) of the two-phase radiator (1) is connected to the inlet of the condenser (2), and the outlet of the condenser (2) is connected to the liquid inlet (101) of the two-phase radiator through the pump (3).

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