Integrated pump-driven two-phase flow system
Through the integrated liquid storage function in the evaporative cold plate and the dual-stage cyclone separation design, the problems of large volume and slow response of traditional two-phase flow systems are solved, and compact thermal management and stable heat dissipation of high-power electronic devices are achieved.
Patent Information
- Application Number
- CN202510681845.X
- Authority / Receiving Office
- CN · China
- Patent Type
- Applications(China)
- Current Assignee / Owner
- Filing Date
- 2025-05-26
- Publication Date
- 2025-07-22
AI Technical Summary
Traditional two-phase flow systems are too large in compact electronic devices, and the excessive filling of working fluid leads to slow response, and the incomplete gas-liquid separation affects the stability of the system.
The integrated pump-driven two-phase flow system is adopted, including a liquid storage evaporation refrigeration plate, a condenser, a gas-liquid separator, a power pump and a preheater. The liquid storage function is integrated on the evaporation refrigeration plate, combining the dual-stage cyclone gas-liquid separation and static pressure chamber design to reduce the system volume and improve dynamic response capabilities.
The system volume is reduced by 40%, and it has dynamic heat dissipation and regulation capabilities. It is suitable for compact thermal management of high-power electronic devices, improving system stability and heat dissipation efficiency.
Smart Images
Figure CN120358716A_ABST
Abstract
Description
Technical Field
[0001] The present invention relates to the technical field of two-phase flow heat dissipation, and in particular to an integrated pump-driven two-phase flow system. Background Art
[0002] With the rapid development of semiconductor technology, the integration degree and computing performance of chips have been continuously improved, resulting in a sharp increase in their power density. The heat flux densities generated by high-performance computing chips (such as CPUs, GPUs), artificial intelligence accelerators, and 5G communication modules have exceeded the heat dissipation limits of traditional air cooling and single-phase liquid cooling. If the heat cannot be exported in time, it will lead to an increase in the chip junction temperature, causing performance degradation, reduced reliability, and even permanent damage, seriously restricting the performance and service life of electronic devices.
[0003] Currently, the two-phase flow heat dissipation technology has become an effective solution to the heat dissipation problem of high-power chips due to its extremely high heat transfer coefficient and temperature uniformity. Traditional two-phase flow systems usually rely on a liquid storage tank to maintain the working fluid balance, but this design has obvious deficiencies in the chip-level heat dissipation scenario: the liquid storage tank increases the system volume and is difficult to meet the integration requirements of compact electronic devices; the excessive working fluid filling amount leads to slow response and cannot adapt to the dynamic load changes of the chip; incomplete gas-liquid separation easily causes the gas-phase working fluid to enter the pump body, resulting in cavitation loss of the pump body and affecting the system stability.
[0004] In addition, application scenarios such as data centers and edge computing devices have put forward higher requirements for the heat dissipation system: it is necessary to achieve kilowatt-level heat dissipation in a limited space while taking into account the energy efficiency ratio and noise control. Existing air cooling and single-phase liquid cooling solutions have approached their performance limits, while traditional two-phase flow systems are difficult to meet the high integration requirements. Therefore, developing a micro two-phase flow heat dissipation system without a liquid storage tank and with high reliability has become the key direction to break through the chip heat dissipation bottleneck. Summary of the Invention
[0005] The technical problem to be solved by the present invention is: in order to overcome the problems in the prior art that the liquid storage tank increases the system volume and is difficult to meet the integration requirements of compact electronic devices; the excessive working fluid filling amount leads to slow response and cannot adapt to the dynamic load changes of the chip; incomplete gas-liquid separation easily causes the gas-phase working fluid to enter the pump body, resulting in cavitation loss of the pump body and affecting the system stability, an integrated pump-driven two-phase flow system is provided.
[0006] The technical solution adopted by the present invention to solve its technical problems is as follows: An integrated pump-driven two-phase flow system includes a liquid storage type evaporative cold plate, a condenser, a gas-liquid separator, a power pump, and a preheater. The output end of the liquid storage type evaporative cold plate is connected to the input end of the condenser, the output end of the condenser is connected to the two-phase material inlet end of the gas-liquid separator, the gas-phase outlet of the gas-liquid separator is connected to the input end of the condenser, the liquid-phase outlet of the gas-liquid separator is connected to the input end of the power pump, the output end of the power pump is connected to the input end of the preheater, and the input end of the preheater is connected to the input end of the liquid storage type evaporative cold plate;
[0007] Two static pressure chambers and microfluidic channels are provided in the liquid storage type evaporative cold plate. The two static pressure chambers are connected by the microfluidic channels, and the microfluidic channels are located between the two static pressure chambers. By integrating the liquid storage function onto the liquid storage type evaporative cold plate, the volume of the pump-driven two-phase flow system is reduced by 40% compared to the traditional system, and it has the ability of dynamic heat dissipation adjustment, which is suitable for the compact thermal management of high-power electronic devices.
[0008] Furthermore, the static pressure chamber includes an upper section, a middle section, and a lower section that are connected in sequence from top to bottom. The working medium in the upper section on the right side of the liquid storage type evaporative cold plate can accumulate gravitational potential energy. The middle section on the right side of the liquid storage type evaporative cold plate is used to provide static pressure for the lower section on the right side of the liquid storage type evaporative cold plate. The lower section on the right side of the liquid storage type evaporative cold plate is communicated with the microfluidic channel to form a low-pressure outlet.
[0009] Furthermore, the middle part of the gas-liquid separator is provided with a two-phase material inlet end, the top surface of the gas-liquid separator is provided with a gas-phase outlet, the bottom surface of the gas-liquid separator is provided with a liquid-phase outlet, and a primary cyclone tube and a secondary divergent tube are arranged inside the gas-liquid separator. The input end of the primary cyclone tube is communicated with the two-phase material inlet end, the secondary divergent tube is located above the primary cyclone tube, and the secondary divergent tube is communicated with the primary cyclone tube.
[0010] Furthermore, the swirl angle of the primary cyclone tube of the gas-liquid separator is 15° ± 2°, and the primary cyclone tube is used for the preliminary separation of gas-liquid two phases and the removal of large liquid droplets.
[0011] Furthermore, the swirl angle of the secondary divergent tube of the gas-liquid separator is 30° ± 2°, and the secondary divergent tube is used for the fine separation of micron-sized liquid droplets.
[0012] Furthermore, the gas-liquid separator has a tapered section that contracts inward from top to bottom. The tapered section is located below the primary cyclone tube, and the cross-sectional area of the tapered section flow channel decreases from the inlet to the outlet in a ratio of 1:0.6 along the flow direction. The tapered section is used to accelerate the liquid-phase flow and inhibit gas-phase entrainment.
[0013] Furthermore, the swirl direction of the primary cyclone tube is opposite to the swirl direction of the secondary divergent tube.
[0014] Further, the pump-driven two-phase flow system further includes a throttle valve, which is arranged between the liquid storage type evaporative cold plate and the condenser.
[0015] Further, the pump-driven two-phase flow system further includes a flow meter, which is arranged between the gas-liquid separator and the power pump.
[0016] The beneficial effects of the present invention are as follows: An integrated pump-driven two-phase flow system provided by the present invention integrates the liquid storage function on the liquid storage type evaporative cold plate, so that the volume of the pump-driven two-phase flow system is reduced by 40% compared with the traditional system, has the ability of dynamic heat dissipation adjustment, and is suitable for the compact thermal management of high-power electronic devices. Description of the Drawings
[0017] The present invention will be further described below in conjunction with the drawings and embodiments.
[0018] Figure 1 is a schematic structural diagram of the present invention;
[0019] Figure 2 is a three-dimensional structural diagram of the liquid storage type evaporative cold plate of the present invention;
[0020] Figure 3 is a sectional structural diagram of the liquid storage type evaporative cold plate of the present invention;
[0021] Figure 4 is a structural diagram of the gas-liquid separator of the present invention.
[0022] In the figure: 1. Liquid storage type evaporative cold plate, 11. Static pressure chamber, 111. Upper section, 112. Middle section, 113. Lower section, 12. Microchannel, 2. Condenser, 3. Gas-liquid separator, 31. Two-phase material inlet end, 32. Gas phase outlet, 33. Liquid phase outlet, 34. Primary cyclone tube, 35. Secondary diverging tube, 36. Converging section, 4. Power pump, 5. Preheater, 6. Throttle valve, 7. Flow meter. Detailed Embodiments
[0023] Now, the present invention will be further described in detail with reference to the drawings. These drawings are all simplified schematic diagrams, only illustrating the basic structure of the present invention in a schematic manner, so they only show the components related to the present invention.
[0024] Such as Figure 1It is a schematic structural diagram of the present invention. An integrated pump-driven two-phase flow system includes a liquid storage type evaporative cold plate 1, a condenser 2, a gas-liquid separator 3, a power pump 4, and a preheater 5. The output end of the liquid storage type evaporative cold plate 1 is connected to the input end of the condenser 2. The output end of the condenser 2 is connected to the two-phase substance inlet end 31 of the gas-liquid separator 3. The gas phase outlet 32 of the gas-liquid separator 3 is connected to the input end of the condenser 2. The liquid phase outlet 33 of the gas-liquid separator 3 is connected to the input end of the power pump 4. The output end of the power pump 4 is connected to the input end of the preheater 5. The input end of the preheater 5 is connected to the input end of the liquid storage type evaporative cold plate 1;
[0025] Two static pressure chambers 11 and microchannel 12 are provided in the liquid storage type evaporative cold plate 1. The two static pressure chambers 11 are connected by the microchannel 12, and the microchannel 12 is located between the two static pressure chambers 11. The liquid storage type evaporative cold plate 1 is provided with vertically rectangular parallelepiped-shaped static pressure chambers 11 that are symmetric left and right. The static pressure chamber 11 is axially divided into three functional regions: upper, middle, and lower segments 111, 112, and 113, to release the circulating fluid according to the capacity requirement, and to achieve liquid level balance and uniform pressure distribution through the principle of communicating vessels and gravity assistance, ensuring stable delivery of the working fluid in the microchannel 12.
[0026] By integrating the liquid storage function on the liquid storage type evaporative cold plate 1, the volume of the pump-driven two-phase flow system is reduced by 40% compared with the traditional system. It has the ability of dynamic heat dissipation adjustment and is suitable for the compact thermal management of high-power electronic devices. The static pressure chamber 11 replaces the traditional liquid storage tank for liquid storage, and the flow equalizing effect of the microchannel 12 ensures uniform distribution of the working fluid, ultimately reducing the system volume and improving the heat dissipation efficiency.
[0027] As Figure 2 、 3 shown, the static pressure chamber 11 includes an upper segment 111, a middle segment 112, and a lower segment 113 that are connected in sequence from top to bottom. The working fluid in the upper segment 111 on the right side of the liquid storage type evaporative cold plate 1 can accumulate gravitational potential energy. The middle segment 112 on the right side of the liquid storage type evaporative cold plate 1 is used to provide static pressure for the lower segment 113 on the right side of the liquid storage type evaporative cold plate 1. The lower segment 113 on the right side of the liquid storage type evaporative cold plate 1 is connected to the microchannel to form a low-pressure outlet.
[0028] The chamber of the liquid storage type evaporative cold plate 1 is a vertically rectangular parallelepiped-shaped static pressure chamber 11 that is symmetric left and right. When the lowest working fluid mass is satisfied in the lower segment 113 on the right side of the liquid storage type evaporative cold plate 1, a microchannel 12 is provided at the same height as the static pressure chamber 11 on the left side of the liquid storage type evaporative cold plate 1 in the vertically rectangular parallelepiped shape. According to the principle of the communicating vessel, the static pressure received by the microchannel 12 is the same, and thus the flow rate into each microchannel 12 is the same, achieving the flow equalizing effect.
[0029] The capacity of the lower section 113 is the minimum working mass to meet the operation of the static pressure chamber, realizing the uniform distribution of the working medium in the liquid storage type evaporation cold plate 1 and the static pressure balance; the middle section 112 is the liquid storage section, providing static pressure for the lower section 113 and supplying the working medium to the system at the same time; the upper section 111 is the liquid storage section, where the working medium entering the static pressure chamber 11 on the right side of the liquid storage type evaporation cold plate 1 accumulates first, and at the same time has the function of providing static pressure for the lower section 113 on the left side of the liquid storage type evaporation cold plate 1.
[0030] The system no longer requires an independent expansion tank for liquid storage, which is achieved through the following structural optimizations: the uniformity error of the inlet pressure distribution of the microchannel 12 is ≤5%; the double-stage swirl design of the gas-liquid separator 3 reduces the gas phase residue rate to ≤5%, reducing the gas film thermal resistance in the microchannel; the flow path of the working medium from the left static pressure chamber 11 to the microchannel 12 is shortened by 50%, and the flow resistance is reduced by 30%.
[0031] A 40% volume reduction is achieved through the following design: the liquid storage type evaporation cold plate 1 with a double static pressure chamber 11 is adopted, and the circulating working medium is stored in the left static pressure chamber 11 of the liquid storage type evaporation cold plate 1. While realizing a more uniform flow rate in the microchannel 12, an independent expansion tank is no longer required for liquid storage. The microchannel 12 and the left static pressure chamber 11 are integrally designed to eliminate external connecting pipelines; the double-stage swirl structure of the two-stage gas-liquid separator 3 reduces the equipment height by 30%.
[0032] As Figure 4 shown, a two-phase material inlet end 31 is provided in the middle of the gas-liquid separator 3, a gas phase outlet 32 is provided on the top surface of the gas-liquid separator 3, a liquid phase outlet 33 is provided on the bottom surface of the gas-liquid separator 3, a primary swirl tube 34 and a secondary gradually expanding tube 35 are arranged inside the gas-liquid separator 3. The input end of the primary swirl tube 34 is communicated with the two-phase material inlet end 31, the secondary expansion tube is located above the primary swirl tube 34, and the secondary expansion tube is communicated with the primary swirl tube 34. The gas-liquid separator 3 adopts the primary swirl tube 34 and the secondary gradually expanding tube 35 to realize two-stage gas-liquid separation. The separated liquid phase is accelerated by the gradually shrinking section 36 at the lower end of the gas-liquid separator 3, significantly reducing the risk of pump cavitation and improving the utilization rate of the working medium.
[0033] The swirl angle of the primary swirl tube 34 of the gas-liquid separator 3 is 15°±2°, and the primary swirl tube 34 is used for the preliminary separation of gas-liquid two phases and the removal of large liquid droplets; the swirl angle of the secondary gradually expanding tube 35 of the gas-liquid separator 3 is 30°±2°, and the secondary gradually expanding tube 35 is used for the fine separation of micron-sized liquid droplets.
[0034] The gas-liquid separator 3 has a tapered section 36 that contracts inward from top to bottom. The tapered section 36 is located below the primary cyclone tube 34. The cross-sectional area of the flow channel of the tapered section 36 decreases from the inlet to the outlet at a ratio of 1:0.6 along the flow direction. The tapered section 36 is used to accelerate the flow of the liquid phase and suppress gas entrainment. The tapered section 36 is connected to the liquid phase outlet end of the primary divergent tube 34. The cross-sectional area of the flow channel gradually decreases along the flow direction, which is used to stabilize and accelerate the flow of the liquid phase working medium after separation.
[0035] The swirl direction of the primary swirl tube 34 is opposite to that of the secondary gradually expanding tube 35, and the separation inertia is enhanced by the double-stage reverse swirl.
[0036] The pump-driven two-phase flow system further includes a throttle valve 6 , which is arranged between the liquid storage evaporative cold plate 1 and the condenser 2 .
[0037] The pump-driven two-phase flow system also includes a flow meter 7, which is arranged between the gas-liquid separator 3 and the power pump 4. The flow meter 7 monitors data in real time to adjust the pump speed of the power pump 4 and the opening of the throttle valve 6 in a linked manner, and releases the working fluid in the static pressure chamber 11 in stages to accurately match the low, medium and high load heat dissipation requirements.
[0038] The working fluid flows from the right static pressure chamber 11 of the liquid storage evaporative cold plate 1 into the microfluidic channel 12, then flows into the left static pressure chamber and then into the conduit. The static pressure chamber replaces the traditional liquid storage tank to store liquid, and the flow equalization effect of the microfluidic channel ensures that the working fluid is evenly distributed, ultimately achieving a reduction in system volume and improved heat dissipation efficiency.
[0039] At low / steady load, the power pump 4 drives the static pressure chamber 11 to supply liquid, wherein part of the working fluid flows from the lower section 114 into the liquid storage evaporative cold plate 1. At instantaneous high load, when the working fluid demand increases suddenly, the middle section 112 is insufficiently supplied with liquid, and the system detects the flow gap through the flow meter, triggers the control logic to expand the throttle valve opening, and accelerates the circulation of the working fluid back to the upper section 111 cavity. In a short period of time, the liquid level in the left static pressure chamber 11 rises, the static pressure at the connection between the lower section 113 and the microchannel 12 increases, the amount of working fluid flowing into the microchannel 12 increases, the flow rate accelerates, and dynamic load response is achieved to supplement the working fluid gap. After a short period of time, the flow rate of the working fluid flowing into the upper section 111 and the working fluid flowing out of the lower section 113 are the same, and the liquid level in the left static pressure chamber stabilizes again.
[0040] When the entire system device starts to work, the power pump 4 starts and drives the working fluid to flow out from the right static pressure chamber 11 of the liquid storage type evaporative cold plate 1. The static pressure chamber 11 is a vertically symmetric rectangular parallelepiped structure, and the inside is naturally divided into a lower section 113, a middle section 112, and an upper section 111 by the static pressure gradient of the working fluid. In the steady-state operation stage, the lower section is directly connected to the microchannel 12, where the working fluid is evenly distributed and absorbs the heat generated by the electronic device, evaporating into a gas-liquid two-phase mixture. Different from the traditional system that relies on an independent liquid storage tank (requiring a liquid storage capacity of 300 ml), this system uses the static pressure chamber 11 to perform the liquid storage function, reducing the total liquid storage volume to 240 ml, with a 40% reduction in volume, and at the same time achieving a more uniform flow rate through the microchannel 12.
[0041] After the working fluid completes endothermic evaporation in the microchannel 12, it flows out of the liquid storage type evaporative cold plate 1 through the left static pressure chamber 11 and flows into the throttle valve 6 through a conduit. The throttle valve 6 adjusts the opening according to the real-time load change to control the flow rate and pressure of the working fluid. Subsequently, the working fluid enters the condenser 2 for condensation. The condensed working fluid often still has gas phase. The gas-liquid two-phase mixture enters the gas-liquid separator 3 and passes through the primary cyclone tube 34 (swirl angle 15°±2°) and the secondary diffuser tube 35 (swirl angle 30°±2°) in sequence from the two-phase material inlet end. In the primary cyclone tube 34, the large liquid droplets are thrown to the tube wall by centrifugal force, and the liquid phase is initially separated; the remaining gas phase carries micron-sized liquid droplets into the secondary diffuser tube 35, and further separation is carried out through reverse swirl, and finally the gas phase residue rate is reduced to ≤5%. The separated liquid phase accelerates and flows into the flow meter 7 through the tapered section 36 (the flow channel cross-sectional area decreases according to 1:0.6), while the separated gas phase returns to the condenser 2 through the outlet for condensation again, and after being converted into a liquid state, it participates in the cycle again. This process not only ensures the condensation effect of the working fluid but also reduces the cavitation risk of the pump.
[0042] When the temperature of the electronic device rises, the heat dissipation required by the system increases. The flow meter 7 calculates the working fluid gap and adjusts the throttle valve 6 to prompt the working fluid to accelerate and flow into the upper section 111 of the right static pressure chamber 11. Driven by the gravitational potential energy, the working fluid in the upper section 111 quickly replenishes the lower section 113. In a short time, the liquid level in the left static pressure chamber 11 rises, the static pressure at the connection between the lower section 113 and the micro-channel 12 increases, more working fluid flows into the micro-channel 12, and the flow rate accelerates. The liquid in the static pressure chamber 11 flows into the conduit at an accelerated rate to ensure the supply of the working fluid under instantaneous high load. After a short time, the flow rate of the working fluid flowing into the upper section 111 is the same as that flowing out of the lower section 113, and the liquid level in the static pressure chamber 11 stabilizes again. When the load decreases, the pump speed slows down, the opening of the throttle valve 6 shrinks, less working fluid enters the upper section 111, the liquid level in the static pressure chamber 11 drops, and the static pressure in the lower section 113 decreases to inhibit the release of the working fluid. After a short time, the redundant working fluid accumulates in the upper section 111 again. The flow rate of the working fluid flowing into the upper section 111 of the right static pressure chamber 11 is the same as that flowing out of the lower section 113. The flow rate of the liquid flowing into the lower section 113 of the left static pressure chamber 11 becomes smaller, and the liquid flowing out of the cold plate decreases, and the liquid level in the static pressure chamber 11 stabilizes again. Through this dynamic response mechanism, the system realizes the dynamic adjustment of the flow rate without the need to independently set an expansion tank, and the uniformity error of the inlet pressure distribution of the micro-channel 12 is ≤5%, making the flow distribution in the micro-channel 12 more uniform.
[0043] After heat exchange, the working fluid is in a gas-liquid mixed phase. After entering the condenser 2, it condenses into a liquid phase. However, the overall flow rate in the system is relatively fast, and the condenser 2 often cannot be completely condensed, and there is still some gas phase. The gas-liquid mixture enters the gas-liquid separator 3 and first impacts the primary swirl tube to generate a swirl, and realizes the primary gas-liquid separation under the action of gravity and centrifugal force. The remaining gas phase rises to the secondary divergent tube 35 to generate a reverse swirl to realize the secondary gas-liquid separation. After the gas-liquid separation is completed, the liquid phase flows into the pipeline through the convergent tube 36 at an accelerated rate, and the gas phase rises through the secondary gas outlet and returns to the condenser 2 for condensation again.
[0044] After the separated liquid-phase working fluid is pressurized by the power pump 4, it is preheated by the copper rod preheater 5, and finally returns to the micro-channel 12 of the evaporative cold plate, absorbs heat again and enters the next cycle. Through the integrated liquid storage function, two-stage swirl high-efficiency separation, optimized design of the micro-channel 12 and the static pressure chamber 11, the whole system realizes volume reduction, improvement of heat management ability and reduction of energy consumption, and its comprehensive performance is significantly better than the traditional two-phase flow system relying on an independent liquid storage tank.
[0045] Inspired by the ideal embodiments of the present invention described above, through the above description, relevant staff can make various changes and modifications completely within the scope of the technical idea of this invention without deviation. The technical scope of this invention is not limited to the content in the specification, and its technical scope must be determined according to the scope of the claims.
Claims
1. An integrated pump-driven two-phase flow system, characterized in that It includes a liquid storage type evaporative cold plate, a condenser, a gas-liquid separator, a power pump and a preheater. The output end of the liquid storage type evaporative cold plate is connected to the input end of the condenser. The output end of the condenser is connected to the two-phase substance inlet end of the gas-liquid separator. The gas phase outlet of the gas-liquid separator is connected to the input end of the condenser. The liquid phase outlet of the gas-liquid separator is connected to the input end of the power pump. The output end of the power pump is connected to the input end of the preheater. The input end of the preheater is connected to the input end of the liquid storage type evaporative cold plate; Two static pressure chambers and microfluidic channels are provided in the liquid storage type evaporative cold plate. The two static pressure chambers are connected by the microfluidic channels, and the microfluidic channels are located between the two static pressure chambers.
2. The integrated pump-driven two-phase flow system according to claim 1, wherein: The static pressure chamber includes an upper section, a middle section and a lower section connected in sequence from top to bottom. The working medium in the upper section on the right side of the liquid storage type evaporative cold plate can accumulate gravitational potential energy. The middle section on the right side of the liquid storage type evaporative cold plate is used to provide static pressure for the lower section on the right side of the liquid storage type evaporative cold plate. The lower section on the right side of the liquid storage type evaporative cold plate is communicated with the microfluidic channel to form a low-pressure outlet.
3. An integrated pump-driven two-phase flow system according to claim 1, characterized in that: The middle part of the gas-liquid separator is provided with a two-phase substance inlet end. The top surface of the gas-liquid separator is provided with a gas phase outlet. The bottom surface of the gas-liquid separator is provided with a liquid phase outlet. An primary cyclone tube and a secondary divergent tube are arranged inside the gas-liquid separator. The input end of the primary cyclone tube is communicated with the two-phase substance inlet end. The secondary divergent tube is located above the primary cyclone tube, and the secondary divergent tube is communicated with the primary cyclone tube.
4. An integrated pump-driven two-phase flow system according to claim 3, characterized in that: The swirl angle of the primary cyclone tube of the gas-liquid separator is 15°±2°, and the primary cyclone tube is used for preliminary separation of gas-liquid two phases and removal of large liquid droplets.
5. The integrated pump-driven two-phase flow system according to claim 3, wherein: The swirl angle of the secondary divergent tube of the gas-liquid separator is 30°±2°, and the secondary divergent tube is used for fine separation of micron-sized liquid droplets.
6. The integrated pump-driven two-phase flow system according to claim 3, wherein: The gas-liquid separator has a tapered section that contracts inward from top to bottom. The tapered section is located below the primary cyclone tube. The cross-sectional area of the tapered section flow path decreases from the inlet to the outlet in a ratio of 1:0.6 along the flow direction. The tapered section is used to accelerate the liquid phase flow and suppress gas phase entrainment.
7. The integrated pump-driven two-phase flow system according to claim 3, characterized in that: The swirl direction of the primary cyclone tube is opposite to the swirl direction of the secondary divergent tube.
8. An integrated pump-driven two-phase flow system as claimed in claim 1, characterized in that: This pump-driven two-phase flow system further includes a throttle valve, and the throttle valve is arranged between the liquid storage type evaporative cold plate and the condenser.
9. An integrated pump-driven two-phase flow system according to claim 1, characterized in that: This pump-driven two-phase flow system further includes a flow meter, and the flow meter is arranged between the gas-liquid separator and the power pump.