Liquid cooling system and control method for electronic device

Abstract

The application provides a liquid cooling system and a control method suitable for an electronic device, and relates to the technical field of liquid cooling. The liquid cooling system comprises: a cooling supply component configured to supply cooling to an external electronic device through cooling liquid; a heat exchange component, a first end of the heat exchange component being configured to absorb heat of the cooling liquid in the cooling supply component to refrigerate the cooling liquid, and to convert liquid working medium in the heat exchange component into gaseous working medium and deliver the gaseous working medium to a second end of the heat exchange component; a condensing component configured to condense the gaseous working medium at the second end of the heat exchange component into liquid working medium, so that the liquid working medium is delivered to the first end of the heat exchange component to form a cycle; and a regulation component configured to adjust a flow rate of the gaseous working medium based on a condensing pressure at the second end of the heat exchange component, so that the condensing pressure reaches a target range.

Description

Technical Field

[0001] At least one embodiment of this application relates to the field of liquid cooling technology, and more particularly to a liquid cooling system and control method suitable for electronic devices. Background Technology

[0002] With the large-scale application of high-power processors and servers in intelligent computing centers, liquid cooling systems, as the core equipment for liquid cooling heat dissipation of electronic devices, undertake the task of heat exchange between the secondary coolant and the outdoor cold source.

[0003] Currently, liquid cooling systems primarily utilize plate heat exchangers for heat exchange to cool the coolant. However, plate heat exchangers have limited heat transfer density, requiring large temperature differences and large heat transfer areas to meet high-power cooling demands, resulting in large equipment size and high deployment costs. Furthermore, they struggle to cope with drastic changes in outdoor weather conditions, leading to poor stability in liquid cooling. Summary of the Invention

[0004] In view of this, this application provides a liquid cooling system and control method suitable for electronic devices, which at least partially solves the above-mentioned technical problems, uses a phase change working fluid to complete heat transfer, reduces the volume of the liquid cooling system, and maintains the stable operation of the liquid cooling system.

[0005] A first aspect of this application provides a liquid cooling system suitable for electronic devices, comprising: a cooling assembly configured to cool an external electronic device via a coolant; a heat exchange assembly, a first end of which is configured to absorb heat from the coolant within the cooling assembly to cool the coolant and to convert the liquid working fluid within the heat exchange assembly into a gaseous working fluid, which is then transported to a second end of the heat exchange assembly; a condensation assembly configured to condense the gaseous working fluid at the second end of the heat exchange assembly into a liquid working fluid, thereby circulating the liquid working fluid back to the first end of the heat exchange assembly; and a control assembly configured to adjust the flow rate of the gaseous working fluid based on the condensation pressure at the second end of the heat exchange assembly, such that the condensation pressure reaches a target range.

[0006] According to an embodiment of this application, the control component includes: a detection unit configured to detect the condensation pressure at the second end of the heat exchange component; a first control component configured to adjust the flow rate of the gaseous working fluid in the heat exchange component to a first flow rate range when the condensation pressure is less than or equal to a preset range; and a second control component configured to adjust the flow rate of the gaseous working fluid in the heat exchange component to a second flow rate range when the condensation pressure is greater than the preset range, wherein the second flow rate range is greater than the first flow rate range.

[0007] According to an embodiment of this application, the heat exchange assembly includes a plurality of heat exchange units arranged side by side. Each heat exchange unit includes: an evaporation section, which exchanges heat with the cooling assembly, such that the liquid working fluid in the evaporation section absorbs heat from the coolant in the cooling assembly and evaporates into a gaseous working fluid; a condensation section, which exchanges heat with the condensation assembly, such that the gaseous working fluid in the condensation section condenses into a liquid working fluid; a first conveying section, configured to convey the gaseous working fluid of the evaporation section to the condensation section; and a second conveying section, configured to convey the liquid working fluid of the condensation section to the evaporation section.

[0008] According to an embodiment of this application, the first control component includes a plurality of control units, the number of which is the same as the number of heat exchange units, and each control unit is disposed in a first conveying section of each heat exchange unit; the second control component includes: a plurality of bypass pipes, each connected to a first conveying section of a plurality of heat exchange units and connected in parallel with a control unit of the corresponding first conveying section, each bypass pipe having a first valve at its input end and a second valve at its output end; and a drive pump, connected to the plurality of bypass pipes and located between the first valve and the second valve, to adjust the flow rate of the gaseous working fluid in the heat exchange component to be within the second flow rate range.

[0009] According to an embodiment of this application, the heat exchange assembly further includes: a plurality of connecting valves, each connected to a first end of a plurality of heat exchange units; and a plurality of balancing valves, each of the balancing valves being connected between two adjacent connecting valves to balance the liquid level of the liquid working fluid in two adjacent heat exchange units.

[0010] According to an embodiment of this application, the cooling assembly includes: a liquid supply section for supplying coolant to the external electronic device, such that the coolant absorbs heat from the electronic device and cools the electronic device; a liquid return section for receiving the coolant after it has absorbed heat in the liquid supply section; a heat exchange section for receiving the coolant in the liquid return section, such that the heat exchange assembly absorbs heat from the coolant in the heat exchange section and cools the coolant, and supplies the cooled coolant back to the liquid supply section to form a circulation; and a circulation pump disposed in the liquid return section and configured to drive the flow of coolant.

[0011] According to an embodiment of this application, the cooling assembly further includes two temperature sensors, respectively disposed in the liquid supply section and the liquid return section, configured to detect the temperature difference of the coolant, and the circulation pump is configured to adjust the flow rate of the coolant in response to the temperature difference of the coolant.

[0012] According to an embodiment of this application, the first control component and the second control component are configured to adjust the number of openings of the control unit or the bypass pipe in response to the temperature of the temperature sensor of the liquid supply section, so as to adjust the number of operation of the heat exchange unit.

[0013] According to an embodiment of this application, the cooling assembly further includes two pressure sensors, respectively disposed in the liquid supply section and the liquid return section, configured to detect the pressure difference of the coolant, and the circulation pump is configured to adjust the flow rate of the coolant in response to the pressure difference of the coolant.

[0014] According to an embodiment of this application, the condensation assembly includes: a blower assembly configured to drive gas flow at the second end of the heat exchange assembly to remove heat from the gaseous working fluid at the second end of the heat exchange assembly, causing the gaseous working fluid to condense and transform into a liquid working fluid; and a spray assembly configured to spray liquid onto the second end of the heat exchange assembly to absorb heat from the gaseous working fluid at the second end of the heat exchange assembly, causing the gaseous working fluid to condense and transform into a liquid working fluid.

[0015] According to an embodiment of this application, the heat exchange assembly further includes fins disposed at the second end of the heat exchange assembly.

[0016] A second aspect of this application provides a control method for a liquid cooling system as described above, comprising: acquiring the condensation pressure at a second end of a heat exchange component; determining, based on the condensation pressure and a preset range, a control component to adjust the flow rate of a gaseous working fluid within the heat exchange component; wherein, when the condensation pressure is less than or equal to the preset range, the flow rate of the gaseous working fluid in the heat exchange component is adjusted to a first flow rate range, and when the condensation pressure is greater than the preset range, the flow rate of the gaseous working fluid in the heat exchange component is adjusted to a second flow rate range, wherein the second flow rate range is greater than the first flow rate range.

[0017] According to the liquid cooling system and control method for electronic devices provided in this application, the liquid cooling system uses an evaporation-condensation cycle of a phase change working fluid to complete heat transfer. Phase change heat transfer has the advantages of high heat transfer coefficient and small heat transfer temperature difference. Compared with traditional plate heat exchangers, liquid-liquid heat transfer can achieve high-power liquid cooling heat dissipation with a smaller heat transfer area, thereby reducing the size of the liquid cooling system. At the same time, the flow rate of the gaseous working fluid is regulated by a closed loop of condensation pressure, which can quickly adapt and adjust itself when outdoor weather conditions change drastically, and maintain the condensation pressure stably within a pre-set target range, ensuring the continuous and stable operation of the phase change cycle, ensuring the stability of the cooling components for external electronic devices, and maintaining the stable operation of the liquid cooling system. Attached Figure Description

[0018] The above and other objects, features and advantages of this application will become clearer from the following description of embodiments with reference to the accompanying drawings, in which:

[0019] Figure 1 A schematic diagram illustrating the principle of a liquid cooling system according to an embodiment of this application is shown.

[0020] Figure 2 The schematic diagram illustrates the principle of the heat exchange assembly and the control assembly according to an embodiment of this application;

[0021] Figure 3 A schematic diagram of a heat exchanger according to an embodiment of this application is shown.

[0022] Figure Labels

[0023] 1. Cooling assembly; 11. Liquid supply section; 12. Liquid return section; 13. Heat exchange section; 14. Circulation pump; 15. Temperature sensor; 16. Pressure sensor; 2. Heat exchange assembly; 21. Heat exchange unit; 211. Evaporation section; 212. Condensation section; 213. First conveying section; 214. Second conveying section; 22. Connecting valve; 23. Balancing valve; 24. Fins; 25. Heat exchanger; 3. Condensation assembly; 31. Blower assembly; 32. Spray assembly; 4. Control assembly; 41. First control assembly; 411. Control section; 42. Second control assembly; 421. Bypass pipe; 4211. First valve; 4212. Second valve; 422. Drive pump; 43. Detection section; 5. Flow meter. Detailed Implementation

[0024] To make the objectives, technical solutions, and advantages of this application clearer, the following detailed description is provided in conjunction with specific embodiments and the accompanying drawings.

[0025] The terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the scope of this application. The terms “comprising,” “including,” etc., as used herein indicate the presence of the stated features, steps, operations, and / or components, but do not exclude the presence or addition of one or more other features, steps, operations, or components.

[0026] All terms used herein, including technical and scientific terms, have the meanings commonly understood by those skilled in the art, unless otherwise defined. It should be noted that the terms used herein are to be interpreted in a manner consistent with the context of this specification, and not in an idealized or overly rigid way.

[0027] When using expressions such as "at least one of A, B, and C," the meaning should generally be interpreted according to the understanding of someone skilled in the art. For example, "a system having at least one of A, B, and C" should include, but is not limited to, systems having A alone, having B alone, having C alone, having A and B, having A and C, having B and C, and / or having A, B, and C. Similarly, when using expressions such as "at least one of A, B, or C," the meaning should generally be interpreted according to the understanding of someone skilled in the art. For example, "a system having at least one of A, B, or C" should include, but is not limited to, systems having A alone, having B alone, having C alone, having A and B, having A and C, having B and C, and / or having A, B, and C.

[0028] It should also be noted that the directional terms mentioned in the embodiments, such as "up," "down," "front," "back," "left," and "right," are only for reference to the directions in the accompanying drawings and are not intended to limit the scope of protection of this application. Throughout the drawings, the same elements are represented by the same or similar reference numerals. Conventional structures or constructions will be omitted where they may cause confusion in understanding this application.

[0029] This application proposes a liquid cooling system suitable for electronic devices. The liquid cooling system can be deployed inside a computing center to cool high-power electronic devices such as server racks, servers, switches, and graphics cards that employ liquid cooling architectures. The liquid cooling system includes a cooling component 1, a heat exchange component 2, a condensation component 3, and a control component 4. The cooling component 1 is configured to cool external electronic devices using a coolant. The first end of the heat exchange component 2 is configured to absorb heat from the coolant in the cooling component 1, cooling the coolant and converting the liquid working fluid in the heat exchange component 2 into a gaseous working fluid, which is then transported to the second end of the heat exchange component 2. The condensation component 3 is configured to condense the gaseous working fluid at the second end of the heat exchange component 2 back into a liquid working fluid, allowing the liquid working fluid to circulate back to the first end of the heat exchange component 2. The control component 4 is configured to adjust the flow rate of the gaseous working fluid based on the condensation pressure at the second end of the heat exchange component 2, ensuring that the condensation pressure reaches a target range.

[0030] In detail, the cooling component 1 is filled with liquid coolant. The coolant, acting as a heat exchange medium, circulates in a closed loop within the cooling component 1. Pipes from the cooling component 1 extend outwards to connect to the electronic equipment inside the cabinet. The coolant flows through the heat exchange points of the electronic equipment, absorbing the heat generated during operation and heating up. The heated coolant then flows back to the cooling component 1, where it exchanges heat with the first end of the heat exchange component 2, releasing heat. The cooled coolant is then output back to the electronic equipment, thus achieving continuous cooling for the electronic equipment.

[0031] The two ends of the heat exchange component 2 are the first end ( Figure 1 The right end of the middle heat exchanger assembly 2) and the second end ( Figure 1 (Left end of heat exchange component 2). Heat exchange component 2 serves as a phase change heat carrier, and is internally encapsulated with a phase change working fluid as the heat exchange medium.

[0032] The working fluid absorbs heat and evaporates at the first end of the heat exchange component 2, and releases heat and condenses at the second end, completing the heat transfer from the cooling component 1 to the condensing component 3. The first end of the heat exchange component 2 only transfers heat through heat exchange, and the phase change working fluid inside the heat exchange component 2 and the coolant of the cooling component 1 do not come into direct contact with each other, thus achieving physical isolation between the two media.

[0033] The condenser assembly 3 is located to the side or above the second end of the heat exchange assembly 2, continuously cooling the gaseous working fluid of the heat exchange assembly 2, causing the gaseous working fluid to complete a condensation phase change, thereby ultimately dissipating the heat of the liquid cooling system to the external environment. The condenser assembly 3 can be a fan, a cooling tower, or a vent that allows outdoor cold air or low-temperature airflow to pass through, enabling heat exchange between the second end of the heat exchange assembly 2 and an outdoor cold source, depending on actual needs.

[0034] The control component 4 may include a detection device and a corresponding controller (not shown in the figure) and an actuator. The signal acquisition end of the detection device is connected to the second end of the heat exchange component 2 to obtain the condensation pressure of the gaseous working fluid during the condensation phase change in real time. The signal output end of the detection device establishes a signal connection with the controller, and the actuator is connected to the gaseous working fluid flow path of the heat exchange component 2. It can output a driving action based on the acquired condensation pressure to change the flow rate of the gaseous working fluid, thereby adjusting the condensation pressure to reach the target range.

[0035] The condenser assembly 3 and the heat exchange assembly 2 constitute the primary circulation loop of the liquid cooling system. The condenser assembly 3 and the second end of the heat exchange assembly 2 can exchange heat to condense the gaseous working fluid of the heat exchange assembly 2 into a liquid working fluid and discharge the heat to the outdoor atmospheric environment.

[0036] The cooling component 1 constitutes the secondary circulation loop of the liquid cooling system. It can absorb the heat of electronic equipment and exchange heat with the first end of the heat exchange component 2 in the primary circulation loop, so that the liquid working fluid of the heat exchange component 2 evaporates and is converted into gaseous working fluid to transfer heat to the primary circulation loop.

[0037] During operation, after the cooling component 1 exchanges heat with the electronic equipment, the coolant carrying heat in the cooling component 1 transfers the heat to the first end of the heat exchange component 2, causing the liquid working fluid inside the heat exchange component 2 to evaporate and transform into a gaseous working fluid. Then, the gaseous working fluid is transported to the second end of the heat exchange component 2 due to the pressure difference. Subsequently, the condensing component 3 exchanges heat with the second end of the heat exchange component 2, continuously removing the heat carried by the gaseous working fluid at the second end of the heat exchange component 2, causing the gaseous working fluid to condense back into a liquid working fluid. The liquid working fluid flows back to the first end of the heat exchange component 2 by gravity, thus completing the phase change cycle of the working fluid. Simultaneously, the regulating component 4 works in conjunction with the heat exchange component 2, adjusting the flow rate of the gaseous working fluid inside the heat exchange component 2 based on the real-time collected condensation pressure at the second end of the heat exchange component 2, stabilizing the condensation pressure within a pre-set target range, and ensuring the continuous and stable operation of the phase change cycle.

[0038] It should be noted that the heat exchange component 2 can be a heat pipe, with a phase change working fluid encapsulated inside as the heat exchange medium. The condensation pressure characterizes the pressure of the liquid working fluid vapor at the second end (i.e., the condensation side) of the heat pipe, that is, the saturation pressure of the liquid working fluid at the condensation temperature, which can reflect the condensation temperature level and heat dissipation capacity of the second end of the heat exchange component 2.

[0039] In this implementation, the liquid cooling system uses an evaporation-condensation cycle of phase change working fluid to complete heat transfer. Phase change heat transfer has the advantages of high heat transfer coefficient and small temperature difference. Compared with traditional plate heat exchangers, liquid-liquid heat transfer can achieve high-power liquid cooling with a smaller heat exchange area, thereby reducing the size of the liquid cooling system. At the same time, the flow rate of the gaseous working fluid is regulated by a closed loop of condensation pressure, which allows for rapid adaptation and autonomous adjustment when outdoor weather conditions change drastically. This maintains the condensation pressure stably within a pre-set target range, ensuring the continuous and stable operation of the phase change cycle, guaranteeing the stability of the cooling supply component 1 to external electronic equipment, and maintaining the stable operation of the liquid cooling system.

[0040] In one exemplary embodiment, reference is made to Figure 1 and Figure 2 As shown, the control component 4 includes a detection unit 43, a first control component 41, and a second control component 42. The detection unit 43 is configured to detect the condensation pressure at the second end of the heat exchange component 2. The first control component 41 is configured to adjust the flow rate of the gaseous working fluid in the heat exchange component 2 to a first flow rate range when the condensation pressure is less than or equal to a preset range. The second control component 42 is configured to adjust the flow rate of the gaseous working fluid in the heat exchange component 2 to a second flow rate range when the condensation pressure is greater than the preset range, the second flow rate range being greater than the first flow rate range.

[0041] In detail, the detection unit 43 can be a pressure sensor 16. The acquisition end of the detection unit 43 is installed in the cavity at the second end of the heat exchange component 2, directly contacting the gaseous working fluid after heat exchange, and acquiring the condensation pressure in real time. The electrical output end of the detection unit 43 establishes electrical communication connections with the signal input ends of the first control component 41 and the second control component 42, respectively, and sends the acquired condensation pressure to the first control component 41 and the second control component 42 in real time.

[0042] Both the first control component 41 and the second control component 42 possess logical judgment and execution output capabilities, and can share the same controller or be two independent controllers. The first flow velocity range represents the low flow velocity range within the heat exchange component 2 where the working fluid circulates by generating its own pressure difference through phase change, requiring no additional mechanical power to drive the gaseous working fluid flow, i.e., internal drive mode. The second flow velocity range represents the flow velocity range higher than the first flow velocity, where the flow velocity of the gaseous working fluid can be forcibly accelerated by mechanical drive components, i.e., external drive mode.

[0043] When the condensing pressure returned by the detection unit 43 is less than or equal to the upper limit of the preset range, it indicates that the outdoor cold source is good. The first control component 41 operates and switches to the internal drive mode, maintaining the gaseous working fluid within the first flow rate range, that is, relying on the phase change pressure difference of the working fluid itself to complete the cycle. When the condensing pressure returned by the detection unit 43 exceeds the preset range, it indicates that the heat dissipation capacity on the condensing side is insufficient. At this time, the second control component 42 takes over and performs the adjustment action, switching to the external drive mode, increasing the flow rate of the gaseous working fluid to the second flow rate range, and accelerating the delivery rate of the gaseous working fluid from the first end to the second end.

[0044] In this implementation, the condensing pressure is used as the feedback quantity for closed-loop control, and two different flow rate ranges are divided for graded control, i.e., switching to internal drive mode or external drive mode. When the cold source conditions are good, the internal drive mode is switched by relying on the phase change self-generated pressure difference cycle, thereby reducing the input of mechanical components and reducing power consumption; when the condensing pressure exceeds the limit, the external drive mode is switched to forcibly accelerate the working fluid cycle, ensuring that the phase change cycle does not fail under high power conditions. While reducing energy consumption, the heat dissipation capacity of the liquid cooling system is also taken into account, maintaining the stable operation of the liquid cooling system and ensuring the stability of the cooling component 1 in supplying cooling to external electronic equipment.

[0045] In some embodiments, the preset range can be determined based on factors such as outdoor ambient temperature, liquid supply temperature of cooling component 1, and working fluid type, and is specifically determined according to actual needs.

[0046] In one exemplary embodiment, reference is made to Figure 1 , Figure 2 and Figure 3As shown, the heat exchange assembly 2 includes multiple heat exchange units 21 arranged side by side. Each heat exchange unit 21 includes an evaporation section 211, a condensation section 212, a first conveying section 213, and a second conveying section 214. The evaporation section 211 exchanges heat with the cooling assembly 1, causing the liquid working fluid in the evaporation section 211 to absorb heat from the coolant in the cooling assembly 1 and evaporate into a gaseous working fluid. The condensation section 212 exchanges heat with the condensation assembly 3, causing the gaseous working fluid in the condensation section 212 to condense into a liquid working fluid. The first conveying section 213 is configured to convey the gaseous working fluid from the evaporation section 211 to the condensation section 212. The second conveying section 214 is configured to convey the liquid working fluid from the condensation section 212 to the evaporation section 211.

[0047] In detail, multiple heat exchange units 21 are arranged side by side in the horizontal direction, and each heat exchange unit 21 is connected in parallel with each other, forming an independent phase change circulation branch. Figure 1 and Figure 2 Two heat exchange units 21 are shown in the diagram; the remaining heat exchange units 21 are omitted.

[0048] The heat exchange unit 21 can be a separate heat pipe with a separate evaporator section 211 and a separate condenser section 212. The evaporator section 211 is the first end heat exchange cavity of the heat exchange unit 21. The evaporator section 211 is arranged in close contact with the wall of the coolant flow channel of the cooling assembly 1 to form wall heat conduction. The heat of the coolant passes through the wall and is transferred into the interior of the evaporator section 211, causing the liquid working fluid contained in the evaporator section 211 to boil and evaporate to generate a gaseous working fluid. The condenser section 212 is arranged at the second end of the heat exchange unit 21. The condenser section 212 exchanges heat with the condenser assembly 3, causing the gaseous working fluid in the condenser section 212 to release heat and recondense into a liquid working fluid.

[0049] The first conveying section 213 is a gas phase pipeline, connecting the gas phase outlet of the evaporation section 211 and the gas phase inlet of the condensation section 212, serving as a conveying channel for the gaseous working fluid. The gaseous working fluid generated in the evaporation section 211 flows to the condensation section 212 via the first conveying section 213.

[0050] The second conveying section 214 is a liquid phase reflux pipeline, which connects the liquid phase outlet of the condensing section 212 and the liquid phase inlet of the evaporating section 211. The liquid working fluid generated by condensation flows back to the evaporating section 211 along the second conveying section 214 by gravity, thereby completing the complete phase change cycle inside a single heat exchange unit 21.

[0051] In this implementation, multiple heat exchange units 21 are connected in parallel to form a multi-stage heat pipe structure. The evaporation sections 211 of the multiple heat exchange units 21 exchange heat with the cooling assembly 1 to form a heat exchanger 25. The condensation sections 212 of the multiple heat exchange units 21 exchange heat with the condensation assembly 3. The phase change working fluid in each heat exchange unit 21 completes evaporation and condensation in an independent closed loop, without mixing with the coolant, ensuring the purity of the coolant medium in the secondary cooling circuit. If a single heat exchange unit 21 fails, it can be shut down individually, while the remaining heat exchange units 21 can continue to maintain system heat dissipation, improving the fault tolerance of the liquid cooling system.

[0052] In one exemplary embodiment, reference is made to Figure 1 and Figure 2 As shown, the heat exchange assembly 2 also includes a plurality of fins 24. The plurality of fins 24 are disposed at the condensation section 212 at the second end of the heat exchange assembly 2.

[0053] In detail, the fins 24 are assembled on the outer wall surface of the second end condenser section 212 of the heat exchange assembly 2, and the fins 24 and the outer wall of the condenser section 212 are in close contact. The fins 24 are assembled by means including but not limited to welding, snap-fit ​​connection, bolt connection or interference fit.

[0054] The fins 24 can be thin-plate heat exchange expansion structures. Multiple fins 24 are arranged at intervals along the length of the condenser section 212 of the heat exchange unit 21 to increase the heat exchange contact area between the condenser section 212 and the external air. The condenser assembly 3 drives the flowing air to sweep across the surface of the fins 24, thereby expanding the heat exchange area and enhancing the air convection heat transfer effect.

[0055] In this embodiment, fins 24 are provided on the outer wall of the condenser section 212 to expand the heat exchange area and improve the heat exchange efficiency, thereby reducing the power consumption of the condenser assembly 3.

[0056] In one exemplary embodiment, reference is made to Figure 1 and Figure 2 As shown, the first control component 41 includes a plurality of control units 411, the number of which is the same as the number of heat exchange units 21, and is respectively disposed in the first conveying section 213 of each heat exchange unit 21.

[0057] In detail, each control unit 411 of the first control assembly 41 is respectively assembled in the first delivery section 213 pipeline of each heat exchange unit 21. The control unit 411 can be a solenoid valve. The control unit 411 can independently perform opening or closing actions. When the control unit 411 is opened, the first delivery section 213 of the corresponding heat exchange unit 21 is turned on and can start phase change cycle operation. When the control unit 411 is closed, the first delivery section 213 of the corresponding heat exchange unit 21 is cut off, and the corresponding heat exchange unit 21 stops operating.

[0058] The second control component 42 includes multiple bypass pipes 421 and a drive pump 422. The multiple bypass pipes 421 are respectively connected to the first delivery section 213 of multiple heat exchange units 21 and are connected in parallel with the control section 411 of the corresponding first delivery section 213. Each bypass pipe 421 has a first valve 4211 at its input end and a second valve 4212 at its output end. The drive pump 422 is connected to the multiple bypass pipes 421 and is located between the first valve 4211 and the second valve 4212 to regulate the flow rate of the gaseous working fluid in the heat exchange component 2 to a second flow rate range.

[0059] In detail, each heat exchange unit 21's first conveying section 213 is connected to a bypass pipe 421, and the control section 411 of each heat exchange unit 21's first conveying section 213 is connected in parallel with the bypass pipe 421. The input end of the bypass pipe 421 is connected to the side of the first conveying section 213 near the evaporation section 211, and the output end of the bypass pipe 421 is connected to the side of the first conveying section 213 near the condensation section 212.

[0060] Each bypass pipe 421 is equipped with a first valve 4211 at its input end and a second valve 4212 at its output end. The first valve 4211 and the second valve 4212 can be solenoid valves. All bypass pipes 421 converge and connect to a drive pump 422. The drive pump 422 can be a magnetic levitation air pump. The drive pump 422 is located in the common pipe section between the first valve 4211 and the second valve 4212 of all bypass pipes 421, eliminating the need for a separate drive pump 422 for each heat exchange unit 21, thus reducing the number of components and controlling overall cost and equipment size.

[0061] During operation, when the liquid cooling system switches to internal drive mode, the control unit 411 is activated, and the first valve 4211 and the second valve 4212 corresponding to each bypass pipe 421 remain closed, and the drive pump 422 stops working. In this way, the gaseous working fluid flows through the first conveying unit 213 and the corresponding control unit 411, relying on the self-generated pressure difference due to phase change, and the flow velocity of the gaseous working fluid is within the first flow velocity range.

[0062] When the liquid cooling system switches to the external drive mode, the control unit 411 of the first delivery unit 213 of the heat exchange unit 21 is closed, the first valve 4211 and the second valve 4212 are opened, the drive pump 422 is started, and the gaseous working fluid can flow through the bypass pipe 421 through the drive pump 422. The drive pump 422 provides the mechanical driving force for gas phase circulation, forcibly increasing the flow velocity of the gaseous working fluid, so that the flow velocity of the gaseous working fluid is in the second flow velocity range.

[0063] In this implementation, each heat exchange unit 21 is equipped with an independent control unit 411, a bypass pipe 421, and a drive pump 422. The bypass pipe 421 and the drive pump 422 drive the flow of gaseous working fluid in an external drive mode, and the internal drive mode achieves circulation flow by relying on the self-generated pressure difference of phase change. The two modes do not interfere with each other, thereby achieving conflict-free switching between the internal drive mode and the external drive mode based on the condensation pressure.

[0064] In one exemplary embodiment, reference is made to Figure 1 and Figure 3 As shown, the heat exchange assembly 2 also includes multiple connecting valves 22 and multiple balancing valves 23. The multiple connecting valves 22 are respectively connected to the first end of multiple heat exchange units 21. Each balancing valve 23 is connected between two adjacent connecting valves 22 to balance the liquid level of the liquid working fluid in two adjacent heat exchange units 21.

[0065] In detail, each connecting valve 22 corresponds to the evaporation section 211 of each heat exchange unit 21. The interface of the connecting valve 22 is connected to the evaporation section 211 at the first end of the heat exchange unit 21. Adjacent connecting valves 22 are connected in series through pipelines and equipped with a balancing valve 23. The balancing valve 23 can be a liquid level balancing solenoid valve.

[0066] In this way, with the connecting valve 22 and the balancing valve 23 open, the evaporation sections 211 of adjacent heat exchange units 21 are interconnected, and the liquid working fluid can flow across the heat exchange units 21, so that the liquid working fluid level inside each heat exchange unit 21 tends to be consistent.

[0067] In this implementation, by using the connecting valve 22 and the balancing valve 23 to build a liquid working fluid level balancing pipeline across the heat exchange unit 21, the liquid working fluid level inside each parallel heat exchange unit 21 can be balanced, avoiding the problem of some heat exchange units 21 having too high a liquid level or too low a liquid level, which may lead to evaporation failure, and ensuring the operational stability of multiple parallel heat exchange units 21.

[0068] In one exemplary embodiment, reference is made to Figure 1 As shown, the condensation assembly 3 includes a blower assembly 31 and a spray assembly 32. The blower assembly 31 is configured to drive gas flow at the second end of the heat exchange assembly 2 to remove heat from the gaseous working fluid at the second end of the heat exchange assembly 2, causing the gaseous working fluid to condense and transform into a liquid working fluid. The spray assembly 32 is configured to spray liquid onto the second end of the heat exchange assembly 2 to absorb heat from the gaseous working fluid at the second end of the heat exchange assembly 2, causing the gaseous working fluid to condense and transform into a liquid working fluid.

[0069] In detail, the blower assembly 31 is arranged above the condenser section 212 at the second end of the heat exchange assembly 2. The blower assembly 31 includes a fan, which is arranged facing the condenser section 212. When the fan is running, it drives ambient air to continuously blow and flow over the outer wall of the condenser section 212, and the heat of the condenser section 212 is removed by air convection heat exchange.

[0070] The spray assembly 32 may include a spray pump and spray piping. The spray piping is positioned above the condenser section 212 and has spray holes. The spray pump drives water or other cooling medium to be delivered to the spray piping, so that the cooling medium flows through the spray holes and sprays downwards onto the outer surface of the condenser section 212. The spray medium evaporates on the surface of the condenser section 212, and the heat of the condenser section 212 is carried away by the evaporative cooling effect.

[0071] Both the blower assembly 31 and the spray assembly 32 are connected to the controller. The controller prioritizes adjusting the blower and spray assembly 32 based on the condensing pressure at the second end of the heat exchange assembly 2. When the condensing pressure decreases, the spray assembly 32 is shut down first, and then the speed of the blower assembly 31 is reduced. When the condensing pressure gradually increases, the fan speed of the blower assembly 31 is adjusted first. When the fan speed has reached its maximum and the condensing pressure is still too high, the spray assembly 32 is started to provide spray cooling. When the fan speed has reached its maximum and the spray assembly 32 has been turned on, but the condensing pressure still cannot be reduced, and the condensing pressure is greater than the preset range, the system switches to external drive mode. Specifically, the control unit 411 is closed, the first valve 4211 and the second valve 4212 are opened, the drive pump 422 is started, and the gaseous working fluid can flow through the drive pump 422 via the bypass pipe 421. The drive pump 422 provides the mechanical driving force for gas phase circulation, forcibly increasing the flow velocity of the gaseous working fluid, so that the flow velocity of the gaseous working fluid is within the second flow velocity range. The frequency of the drive pump 422 can be adjusted according to the condensing pressure to reduce the condensing pressure and bring it to the target range.

[0072] As the condensing pressure gradually decreases, first reduce the frequency of the drive pump 422, then turn off the spray assembly 32, and finally reduce the speed of the blower assembly 31. When both the air pump and the fan can maintain the condensing pressure below or equal to the preset range while operating at the lowest frequency, turn off the drive pump 422 and switch to internal drive mode.

[0073] In this implementation, the blower assembly 31 provides air cooling, while the spray assembly 32 provides evaporative cooling to assist in heat dissipation, and enables staged start-up. When the outdoor ambient temperature is low, condensation can be completed solely by the blower assembly 31, and the spray assembly 32 remains inactive most of the time, reducing system water and energy consumption. When the outdoor temperature is high and the air cooling capacity is insufficient, the spray assembly 32 is activated, and in conjunction with switching between external and internal drive modes, the liquid cooling system can quickly adapt and autonomously adjust to drastic changes in the outdoor environment, reducing energy consumption while maintaining the heat dissipation capacity of the liquid cooling system.

[0074] In some embodiments, the spraying medium of the spraying assembly 32 is circulating water, and a water collection tray and a return water pipeline are provided to collect and recycle the sprayed medium, thereby reducing water consumption.

[0075] In one exemplary embodiment, reference is made to Figure 1 and Figure 2 As shown, the cooling assembly 1 includes a supply section 11, a return section 12, a heat exchange section 13, and a circulation pump 14. The supply section 11 delivers coolant to external electronic devices, allowing the coolant to absorb heat from the electronic devices and cool them. The return section 12 receives the coolant that has absorbed heat from the supply section 11. The heat exchange section 13 receives the coolant from the return section 12, allowing the heat exchange assembly 2 to absorb heat from the coolant in the heat exchange section and cool it, then delivers the cooled coolant back to the supply section 11 to form a circulation. The circulation pump 14 is located in the return section 12 and is configured to drive the coolant flow.

[0076] Specifically, the supply section 11 is a pipeline channel for discharging low-temperature coolant. The supply section 11 extends an interface to connect to the coolant inlet of external electronic equipment. The return section 12 is a pipeline channel for the return of high-temperature coolant carrying heat. The return section 12 is equipped with a pipeline interface to receive the high-temperature coolant flowing from the electronic equipment.

[0077] The heat exchange section 13 is a cavity flow channel that exchanges heat with the first end of the heat exchange assembly 2. The high-temperature coolant flowing out of the return section 12 flows into the internal flow channel of the heat exchange section 13. The outer wall of the heat exchange section 13 is in close contact with the evaporation section 211 at the first end of the heat exchange assembly 2, so that the high-temperature coolant transfers heat to the evaporation section 211 of the heat exchange assembly 2. After the coolant is cooled down by heat release, it flows out of the heat exchange section 13 and into the supply section 11, and is sent to the electronic equipment again.

[0078] The circulating pump 14 is a variable circulation pump 14. The circulating pump 14 is installed in the pipeline of the return liquid section 12, and the pump body of the circulating pump 14 is connected to the fluid passage of the return liquid section 12. The circulating pump 14 provides flow power for the circulation of coolant in the cooling assembly 1, driving the coolant to flow sequentially through the return liquid section 12, the heat exchange section 13, the supply liquid section 11, and the external electronic equipment, thus completing the closed-loop circulation of the secondary side coolant.

[0079] In this embodiment, the supply section 11, return section 12, and heat exchange section 13 together form a complete secondary-side coolant circulation loop. The circulation pump 14 is arranged in the return-side pipeline to drive the coolant to circulate continuously and stably deliver the cooling medium to the electronic equipment. The heat exchange section 13 and the evaporation section 211 of the heat exchange assembly 2 complete heat transfer only through the wall surface. The coolant in the cooling assembly 1 and the phase change working fluid in the heat exchange assembly 2 are isolated from each other, effectively reducing the risk of leakage caused by the mixing of the two media.

[0080] In some embodiments, refer to Figure 1 and Figure 3 As shown, the pipeline of the heat exchange section 13 is arranged in a serpentine bend to increase the flow path of the coolant in the heat exchange section 13 within the heat exchanger 25, thereby increasing the heat exchange time with the working fluid in the evaporation section 211 of the heat exchange assembly 2 and improving the heat exchange efficiency.

[0081] In some embodiments, the liquid supply unit 11 and the liquid return unit 12 can be configured with multiple external branch pipelines, which can simultaneously connect to multiple electronic equipment cabinets to achieve centralized cooling of multiple cabinets.

[0082] In one exemplary embodiment, reference is made to Figure 1 and Figure 2 As shown, the cooling assembly 1 also includes two pressure sensors 16. The two pressure sensors 16 are respectively disposed in the supply section 11 and the return section 12, and are configured to detect the pressure difference between the coolant in the supply section 11 and the coolant in the return section 12. The circulation pump 14 is configured to adjust the coolant flow rate in response to the coolant pressure difference.

[0083] Specifically, two pressure sensors 16 are respectively mounted on the pipelines of the supply section 11 and the return section 12. The signal output terminals of the two pressure sensors 16 are connected to the controller to collect the coolant pressure in the pipelines of the supply section 11 and the return section 12, respectively. The controller calculates the pressure difference between the supply pressure and the return pressure, and transmits signals between the controller and the circulation pump 14.

[0084] During operation, the controller compares the detected actual supply and return hydraulic pressure difference with the set threshold. If the actual pressure difference is lower than the set threshold, the operating frequency of the circulation pump 14 is increased to increase the coolant flow rate and improve the supply and return hydraulic pressure difference. If the actual pressure difference is higher than the set threshold, the operating frequency of the circulation pump 14 is reduced to decrease the coolant flow rate and reduce the supply and return hydraulic pressure difference, thus maintaining a stable supply and return hydraulic pressure difference, i.e., differential pressure control mode.

[0085] In this implementation, the pressure difference between the supply and return coolant is obtained by collecting the pressure of the supply section 11 and the return section 12. Based on the pressure difference, the circulation pump 14 is frequency-controlled to achieve a pressure difference control mode. The flow rate of the circulation pump 14 can be adaptively adjusted according to the changes in the pipeline resistance of the external electronic equipment, so as to stably output coolant to the external electronic equipment and ensure a uniform and stable supply of coolant to the electronic equipment.

[0086] In one exemplary embodiment, reference is made to Figure 1 and Figure 2 As shown, the cooling assembly 1 also includes two temperature sensors 15. The two temperature sensors 15 are respectively disposed in the coolant supply section 11 and the coolant return section 12, and are configured to detect the temperature difference between the coolant in the coolant supply section 11 and the coolant in the coolant return section 12. The circulation pump 14 is configured to adjust the coolant flow rate in response to the coolant temperature difference.

[0087] Specifically, two temperature sensors 15 are respectively installed and fixed inside the supply section 11 pipeline and the return section 12 pipeline. The probes of the temperature sensors 15 directly contact the coolant flowing inside the pipelines, collecting the temperature of the coolant in the supply section 11 and the return section 12, respectively. The signal output terminals of the two temperature sensors 15 are connected to the controller, which calculates the temperature difference between the return section 12 and the supply section 11. The controller establishes a control signal connection with the circulation pump 14. Based on the calculated temperature difference, the controller outputs a frequency adjustment command to change the frequency of the circulation pump 14, thereby adjusting the output speed of the circulation pump 14 and thus adjusting the coolant circulation flow rate inside the cooling assembly 1.

[0088] During operation, when the actual temperature difference is higher than the set threshold, indicating that the coolant carries more heat per unit flow rate, the controller increases the frequency of the circulation pump 14, thereby increasing the coolant flow rate. When the actual temperature difference is lower than the set threshold, the controller decreases the frequency of the circulation pump 14, thereby reducing the coolant flow rate; this is the temperature difference control mode.

[0089] In this implementation, the temperature difference of the coolant is obtained by collecting the temperature of the supply section 11 and the return section 12. Based on the temperature difference, the frequency of the circulating pump 14 is adjusted, thereby adaptively and dynamically adjusting the flow rate of the coolant based on the total heat load of the electronic equipment. When the load is low, the speed of the circulating pump 14 is reduced, the power consumption of the circulating pump 14 is reduced, and the overall energy efficiency of the liquid cooling system is improved.

[0090] It should be noted that, depending on actual needs, the secondary side can switch between differential pressure control mode and temperature difference control mode. The primary side can switch between internal drive mode and external drive mode. Thus, the liquid cooling system control modes include internal drive-differential pressure control mode, external drive-differential pressure control mode, internal drive-temperature difference control mode, and external drive-temperature difference control mode.

[0091] In one exemplary embodiment, reference is made to Figure 1 and Figure 2 As shown, the first control component 41 and the second control component 42 are configured to adjust the number of times the control unit 411 or the bypass pipe 421 is opened in response to the temperature of the temperature sensor 15 of the liquid supply section 11, so as to adjust the number of times the heat exchange unit 21 is operated.

[0092] In detail, the liquid supply temperature signal collected by the temperature sensor 15 of the liquid supply section 11 is transmitted to the controller. The controller internally presets a target temperature range for the liquid supply temperature, compares the liquid supply temperature with the target temperature range, and generates control commands.

[0093] In internal drive mode, if the collected liquid supply temperature is higher than the target temperature range, it indicates that the total heat exchange capacity of the current liquid cooling system is insufficient to remove the heat from the electronic equipment. The first control component 41, in response to the controller's control command, increases the number of control units 411 activated, increasing the number of heat exchange units 21 operating in internal drive mode, thereby improving the total heat exchange capacity of the liquid cooling system. If the collected liquid supply temperature is lower than the target temperature range, it indicates that the liquid cooling system has excessive heat exchange capacity. The first control component 41, in response to the controller's control command, reduces the number of control units 411 activated, reducing the number of heat exchange units 21 operating, thereby reducing the heat exchange capacity of the liquid cooling system.

[0094] In external drive mode, when the collected liquid supply temperature is higher than the upper limit of the target temperature range, the second control component 42 responds to the controller's control command by increasing the number of bypass pipes 421 in operation, that is, activating the first valve 4211 and the second valve 4212 of the corresponding bypass pipe 421, increasing the number of heat exchange units 21 in operation in external drive mode, and improving the total heat exchange capacity of the liquid cooling system. When the collected liquid supply temperature is lower than the target temperature range, the second control component 42 responds to the controller's control command by decreasing the number of bypass pipes 421 in operation, that is, closing the first valve 4211 and the second valve 4212 of the corresponding bypass pipe 421, reducing the number of heat exchange units 21 in operation in external drive mode, reducing the heat exchange capacity of the liquid cooling system, and stabilizing the coolant temperature output by the liquid supply unit 11 within the target temperature range.

[0095] It should be noted that the connecting valve 22 corresponding to the evaporation section 211 of the heat exchange unit 21 that is put into operation is also opened, and the balancing valve 23 between adjacent connecting valves 22 that are in the open state is also opened accordingly, so as to balance the liquid level of the liquid working fluid in the heat exchange unit 21.

[0096] In this implementation, a multi-stage heat pipe structure formed by multiple parallel heat exchange units 21 is used, and the secondary-side liquid supply temperature is used as feedback. The number of heat exchange units 21 in operation is adjusted locally on the secondary side, thereby regulating the total heat exchange of the liquid cooling system. This eliminates the need to adjust the primary side, shortens the control transmission link, and results in a faster response to external electronic equipment load changes and transient impacts. It can quickly and accurately suppress temperature fluctuations. This overcomes the problems of response lag, limited adjustment accuracy, and low-load oscillation caused by traditional liquid cooling systems that rely solely on a single primary-side electric regulating valve for throttling and have a long control link.

[0097] Furthermore, the primary-side control and secondary-side control are divided into two relatively independent control paths. The condensation pressure at the second end of the primary-side heat exchange component 2 is regulated by the blower component 31, the spray component 32, and the first and second control components 41 to achieve automatic switching between internal and external drive modes. Depending on actual needs, the secondary side can select either a temperature difference control mode or a pressure difference control mode, and the temperature or pressure difference between the coolant in the supply section 11 and the return section 12 is regulated by the frequency of the circulating pump 14. The temperature of the coolant in the secondary-side supply section 11 is regulated by the number of heat exchange units 21 in operation. In this way, the liquid cooling system can quickly adapt and autonomously adjust when the load on electronic equipment and outdoor weather conditions change drastically simultaneously, ensuring continuous and stable operation of the phase change cycle, guaranteeing the stability of the cooling supply component 1 to external electronic equipment, and maintaining the stable operation of the liquid cooling system.

[0098] In one exemplary embodiment, reference is made to Figure 1 As shown, the liquid cooling system may also include a flow meter 5. The flow meter 5 is located in the return section 12 and is configured to monitor the flow rate of the coolant in the return section 12, so as to trigger an alarm when the coolant flow rate is lower than a safety threshold, thereby ensuring the safe operation of the liquid cooling system.

[0099] This application also provides a control method for a liquid cooling system, including operations S110-S120.

[0100] In S110, the condensation pressure at the second end of the heat exchange component 2 is obtained.

[0101] In step S120, based on the condensing pressure and a preset range, the flow rate of the gaseous working fluid in the heat exchange component 2 is determined by the regulating component 4. Specifically, when the condensing pressure is less than or equal to the preset range, the flow rate of the gaseous working fluid in the heat exchange component 2 is adjusted to a first flow rate range; when the condensing pressure is greater than the preset range, the flow rate of the gaseous working fluid in the heat exchange component 2 is adjusted to a second flow rate range, which is greater than the first flow rate range.

[0102] In detail, during the operation of the liquid cooling system, the condensing pressure at the second end of the heat exchange component 2 is continuously collected by the detection unit 43. The controller acquires the condensing pressure signal output by the detection unit 43. The controller internally stores a preset range of condensing pressure and compares the collected condensing pressure with the preset range. When the condensing pressure is less than or equal to the preset range, it indicates that the heat dissipation conditions on the condensing side are sufficient and no additional mechanical driving force is required. The first control component 41 of the control component 4 operates, controlling the gaseous working fluid to maintain the first flow rate range. The working fluid relies on the self-generated pressure difference generated by the phase change to complete the circulation flow. When the condensing pressure is greater than the preset range, it indicates that the current condensing heat dissipation capacity is insufficient. The control component 4 switches to the second control component 42 to operate, adjusting the flow rate of the gaseous working fluid to the second flow rate range. That is, mechanical power is provided by the drive pump 422 to accelerate the delivery of the gaseous working fluid, continue to collect the condensing pressure, and continuously regulate in a closed loop. The specifics are as described above and will not be repeated here.

[0103] According to the liquid cooling system and control method for electronic devices provided in this embodiment, the liquid cooling system uses an evaporation-condensation cycle of a phase change working fluid to complete heat transfer. Phase change heat transfer has the advantages of high heat transfer coefficient and small heat transfer temperature difference. Compared with traditional plate heat exchangers, liquid-liquid heat transfer can achieve high-power liquid cooling heat dissipation with a smaller heat transfer area, thereby reducing the volume of the liquid cooling system. At the same time, the flow rate of the gaseous working fluid is regulated by a closed loop of condensation pressure, so that it can quickly adapt and adjust itself when outdoor weather conditions change drastically, and maintain the condensation pressure stably within the preset target range, ensuring the continuous and stable operation of the phase change cycle, ensuring the stability of the cooling supply component 1 to external electronic devices, and maintaining the stable operation of the liquid cooling system.

[0104] The embodiments of this application have been described above. However, these embodiments are merely illustrative and not intended to limit the scope of this application. Although various embodiments have been described above, this does not mean that the measures in the various embodiments cannot be used advantageously in combination. The scope of this application is defined by the appended claims and their equivalents. Various substitutions and modifications can be made by those skilled in the art without departing from the scope of this application, and all such substitutions and modifications should fall within the scope of this application.

Claims

1. A liquid cooling system suitable for electronic devices, characterized in that, include: The cooling unit (1) is configured to cool external electronic equipment via a coolant; The heat exchange component (2) is configured to absorb the heat of the coolant in the cooling component (1) to cool the coolant and convert the liquid working fluid in the heat exchange component (2) into a gaseous working fluid and transport it to the second end of the heat exchange component (2). The condensation component (3) is configured to condense the gaseous working fluid at the second end of the heat exchange component (2) into a liquid working fluid, so that the liquid working fluid is transported to the first end of the heat exchange component (2) to form a cycle; The regulating component (4) is configured to adjust the flow rate of the gaseous working fluid based on the condensation pressure at the second end of the heat exchange component (2) so that the condensation pressure reaches the target range.

2. The liquid cooling system according to claim 1, characterized in that, The control component (4) includes: The detection unit (43) is configured to detect the condensation pressure at the second end of the heat exchange assembly (2); The first control component (41) is configured to adjust the flow rate of the gaseous working fluid of the heat exchange component (2) to a first flow rate range when the condensation pressure is less than or equal to a preset range. The second control component (42) is configured to adjust the flow rate of the gaseous working fluid of the heat exchange component (2) to a second flow rate range when the condensation pressure is greater than a preset range, the second flow rate range being greater than the first flow rate range.

3. The liquid cooling system according to claim 2, characterized in that, The heat exchange assembly (2) includes a plurality of heat exchange units (21) arranged side by side, each heat exchange unit (21) including: The evaporation section (211) exchanges heat with the cooling assembly (1), so that the liquid working fluid in the evaporation section (211) absorbs the heat of the coolant in the cooling assembly (1) and evaporates into a gaseous working fluid; The condenser (212) exchanges heat with the condenser assembly (3), causing the gaseous working fluid in the condenser (212) to condense and transform into a liquid working fluid; The first conveying unit (213) is configured to convey the gaseous working fluid of the evaporation unit (211) to the condensation unit (212); The second conveying unit (214) is configured to convey the liquid working fluid of the condensation unit (212) to the evaporation unit (211).

4. The liquid cooling system according to claim 3, characterized in that, The first control component (41) includes a plurality of control units (411), the number of which is the same as the number of heat exchange units (21), and is respectively disposed in the first conveying part (213) of each heat exchange unit (21); The second control component (42) includes: Multiple bypass pipes (421) are respectively connected to the first conveying section (213) of multiple heat exchange units (21) and are connected in parallel with the control section (411) of the corresponding first conveying section (213). Each bypass pipe (421) is provided with a first valve (4211) at its input end and a second valve (4212) at its output end. A drive pump (422) is connected to a plurality of the bypass pipes (421) and located between the first valve (4211) and the second valve (4212) to regulate the flow rate of the gaseous working fluid of the heat exchange assembly (2) to be within the second flow rate range.

5. The liquid cooling system according to claim 3, characterized in that, The heat exchange assembly (2) also includes: Multiple connecting valves (22) are respectively connected to the first end of multiple heat exchange units (21); Multiple balancing valves (23) are connected between two adjacent connecting valves (22) to balance the liquid level of the liquid working fluid in the two adjacent heat exchange units (21).

6. The liquid cooling system according to claim 4, characterized in that, The cooling assembly (1) includes: The coolant supply unit (11) delivers coolant to the external electronic device, so that the coolant absorbs the heat of the electronic device and cools the electronic device. The return section (12) receives the coolant that has absorbed heat from the supply section (11); The heat exchange section (13) receives the coolant from the return section (12), so that the heat exchange assembly (2) absorbs the heat of the coolant from the heat section to cool the coolant, and delivers the cooled coolant to the supply section (11) to form a cycle. A circulation pump (14) is provided in the return section (12) and is configured to drive the flow of coolant.

7. The liquid cooling system according to claim 6, characterized in that, The cooling assembly (1) also includes two temperature sensors (15) respectively located in the liquid supply section (11) and the liquid return section (12), configured to detect the temperature difference of the coolant, and the circulation pump (14) is configured to adjust the flow rate of the coolant in response to the temperature difference of the coolant.

8. The liquid cooling system according to claim 7, characterized in that, The first control component (41) and the second control component (42) are configured to adjust the number of times the control unit (411) or the bypass pipe (421) is opened in response to the temperature of the temperature sensor (15) of the liquid supply section (11), so as to adjust the number of times the heat exchange unit (21) is operated.

9. The liquid cooling system according to claim 6, characterized in that, The cooling assembly (1) also includes two pressure sensors (16) respectively disposed in the liquid supply section (11) and the liquid return section (12), configured to detect the pressure difference of the coolant, and the circulation pump (14) is configured to adjust the flow rate of the coolant in response to the pressure difference of the coolant.

10. The liquid cooling system according to claim 1, characterized in that, The condensation assembly (3) includes: The blower assembly (31) is configured to drive the gas flow at the second end of the heat exchange assembly (2) to remove the heat of the gaseous working fluid at the second end of the heat exchange assembly (2), so that the gaseous working fluid condenses and transforms into a liquid working fluid. The spray assembly (32) is configured to spray liquid onto the second end of the heat exchange assembly (2) to absorb heat from the gaseous working fluid at the second end of the heat exchange assembly (2), causing the gaseous working fluid to condense and transform into a liquid working fluid.

11. The liquid cooling system according to claim 1, characterized in that, The heat exchange assembly (2) further includes fins (24) disposed at the second end of the heat exchange assembly (2).

12. A control method for a liquid cooling system based on any one of claims 1 to 11, characterized in that, include: Obtain the condensation pressure at the second end of the heat exchange component (2); Based on the condensation pressure and the preset range, the control component (4) is used to adjust the flow rate of the gaseous working fluid in the heat exchange component (2); Wherein, when the condensation pressure is less than or equal to a preset range, the flow rate of the gaseous working fluid of the heat exchange component (2) is adjusted to a first flow rate range, and when the condensation pressure is greater than the preset range, the flow rate of the gaseous working fluid of the heat exchange component (2) is adjusted to a second flow rate range, wherein the second flow rate range is greater than the first flow rate range.

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