Liquid cooling device and anti-condensation control method thereof

Abstract

This invention discloses a liquid cooling device and its anti-condensation control method. The liquid cooling device includes: a heat dissipation mechanism having a heat dissipation pipe for circulating coolant, the heat dissipation pipe including a working section for heat exchange with a heat-generating device; an internal circulation branch, the inlet of which is connected to the outlet of the working section, and the outlet of which is connected to the inlet of the working section; a dehumidification device having a dehumidification pipe connected in parallel with the heat dissipation pipe, the internal circulation branch and / or the dehumidification pipe being equipped with valves for regulating the coolant flow rate; and a refrigeration system for providing coolant or cooling the coolant. This invention achieves a balance between heat dissipation capacity and anti-condensation effect, significantly improving the service life of the heat-generating device and the reliability of the liquid cooling device.

Description

Technical Field

[0001] This invention relates to the field of liquid cooling equipment technology, and in particular to liquid cooling equipment and its anti-condensation control method. Background Technology

[0002] Electronic components inside the cabinet continuously generate heat during operation, requiring timely heat dissipation to prevent overheating and damage. Liquid cooling is a common heat dissipation method, which uses a refrigeration system to provide low-temperature coolant. The coolant flows over the heat-generating components, carrying away the heat and effectively controlling their temperature. However, in extremely harsh and humid environments, this liquid cooling method can easily cause electronic components to short-circuit and burn out due to condensation.

[0003] For refrigeration systems using variable frequency control, condensation can be avoided by reducing the cooling output. However, this reduction in cooling output raises the coolant temperature, worsening the heat dissipation of electronic components and potentially affecting their performance over time. For refrigeration systems using fixed frequency control, the only way to reduce cooling output is by frequently starting and stopping the compressor, which compromises the overall reliability of the system.

[0004] Existing anti-condensation control schemes reduce the probability of condensation by lowering the humidity in the area where the heating device is located. These schemes are designed with a first liquid cooling pipe to lower the temperature of the heating device and a second liquid cooling pipe to lower the humidity in the area where the heating device is located. The drawback of this control scheme is that after the second liquid cooling pipe is turned on, the flow rate in the first liquid cooling pipe will be significantly reduced, which will affect the heat dissipation effect of the heating device, which is not conducive to the working performance of the heating device, and there is a risk of the heating device burning out at high temperature. Summary of the Invention

[0005] To address the shortcomings of existing anti-condensation control schemes that affect the heat dissipation effect of heat-generating devices, this invention proposes a liquid cooling device and its anti-condensation control method.

[0006] The technical solution adopted in this invention is to design a liquid cooling device, comprising:

[0007] A heat dissipation mechanism having heat dissipation pipes for circulating coolant, the heat dissipation pipes including a working section for heat exchange with heat-generating devices;

[0008] An internal circulation branch, the inlet of which is connected to the outlet of the working section, and the outlet of which is connected to the inlet of the working section.

[0009] Furthermore, it also includes: a dehumidification device having a dehumidification pipe connected in parallel with the heat dissipation pipe, and an internal circulation branch and / or a dehumidification pipe equipped with valves for regulating the flow of coolant.

[0010] Furthermore, liquid cooling equipment also includes a refrigeration system, which provides coolant or cools the coolant.

[0011] In some embodiments, the evaporator of the refrigeration system has a first branch and a second branch that exchange heat with each other. The first branch participates in the refrigerant circulation of the refrigeration system, and the second branch participates in the coolant circulation of the heat dissipation pipe and / or dehumidification pipe.

[0012] Furthermore, the liquid cooling equipment also includes: a sensor assembly and a controller; the sensor assembly is used to detect at least one of the following data: the coolant temperature at the inlet of the heat dissipation pipe, the supply temperature at the inlet of the working section, the supply flow rate at the inlet of the working section, and the dew point temperature of the area where the heat-generating device is located; the controller receives the detection data from the sensor assembly and adjusts the operating status of the liquid cooling equipment.

[0013] Furthermore, the operating status of the liquid cooling equipment includes at least one of the following: the coolant flow rate of the internal circulation branch, the coolant flow rate of the dehumidification pipeline, the compressor operating frequency of the refrigeration system, and the condenser fan speed of the refrigeration system.

[0014] Furthermore, the sensor assembly includes: a first temperature sensor installed at the inlet of the heat dissipation pipe, a second temperature sensor installed at the inlet of the working section, a first flow sensor installed at the inlet of the heat dissipation pipe, and a second flow sensor installed on the internal circulation branch; the coolant temperature is detected by the first temperature sensor, the supply temperature is detected by the second temperature sensor, and the supply flow rate is the sum of the coolant flow rates detected by the first flow sensor and the second flow sensor.

[0015] In some embodiments, both the heating element and the dehumidification device are located inside the cabinet of the liquid cooling equipment.

[0016] This invention also proposes an anti-condensation control method, which is applied to the aforementioned liquid cooling equipment and includes the following steps:

[0017] Obtain the liquid supply temperature at the inlet of the working section and the dew point temperature of the area where the heating element is located;

[0018] Compare the liquid supply temperature with the dew point temperature;

[0019] When the liquid supply temperature is less than the dew point temperature plus the preset margin δ1, the dew point temperature control strategy is executed to increase the liquid supply temperature and decrease the dew point temperature.

[0020] And / or when the supply temperature is ≥ dew point temperature + preset margin δ1, the set temperature control strategy is executed to make the supply temperature reach the set temperature range.

[0021] Furthermore, dew point temperature control strategies include:

[0022] Obtain the coolant temperature at the inlet of the heat dissipation pipes;

[0023] Compare the coolant temperature with the dew point temperature;

[0024] When the coolant temperature is greater than or equal to the dew point temperature minus the preset margin δ2, increase the coolant flow rate in the dehumidification pipeline and the internal circulation branch.

[0025] And / or when the coolant temperature is less than the dew point temperature minus the preset margin δ2, increase the coolant flow rate in the dehumidification pipeline and the internal circulation branch.

[0026] In some embodiments, if the liquid cooling equipment adopts a variable frequency refrigeration system, then in the dew point temperature control strategy, when the coolant temperature is greater than or equal to the dew point temperature minus a preset margin δ2, the cooling capacity of the refrigeration system is increased.

[0027] Furthermore, the temperature control strategy includes:

[0028] Compare the supply temperature with the set temperature;

[0029] Obtain the liquid supply flow rate at the inlet of the working section and compare it with the set flow rate;

[0030] Adjust the coolant flow rate of the dehumidification pipeline and the internal circulation pipeline based on the comparison results of the supply temperature and the supply flow rate.

[0031] Furthermore, setting temperature control strategies also includes:

[0032] If the supply temperature is greater than or equal to the set temperature plus the preset margin δ3, then when the supply flow rate is greater than or equal to the set flow rate plus the preset margin λ, increase the coolant flow rate of the dehumidification pipeline and decrease the coolant flow rate of the internal circulation branch.

[0033] And / or when the set flow rate - preset margin λ ≤ supply flow rate < set flow rate + preset margin λ, reduce the coolant flow rate in the dehumidification pipeline and the internal circulation branch;

[0034] And / or when the supply flow rate is less than the set flow rate minus the preset margin λ, reduce the coolant flow rate in the dehumidification pipeline and increase the coolant flow rate in the internal circulation branch.

[0035] Furthermore, setting temperature control strategies also includes:

[0036] If the set temperature - preset margin δ3 ≤ supply temperature < set temperature + preset margin δ3, then when the supply flow rate ≥ set flow rate + preset margin λ, increase the coolant flow rate of the dehumidification pipe and decrease the coolant flow rate of the internal circulation branch.

[0037] And / or when the set flow rate - preset margin λ ≤ liquid supply flow rate < set flow rate + preset margin λ, the dehumidification pipeline and internal circulation branch shall maintain the current state;

[0038] And / or when the supply flow rate is less than the set flow rate minus the preset margin λ, reduce the coolant flow rate in the dehumidification pipeline and increase the coolant flow rate in the internal circulation branch.

[0039] Furthermore, setting temperature control strategies also includes:

[0040] If the supply temperature is less than the set temperature minus the preset margin δ3, then when the supply flow rate is greater than or equal to the set flow rate plus the preset margin λ, increase the coolant flow rate of the dehumidification pipe and decrease the coolant flow rate of the internal circulation branch.

[0041] And / or when the set flow rate - preset margin λ ≤ supply flow rate < set flow rate + preset margin λ, reduce the coolant flow rate in the dehumidification pipeline and the internal circulation branch;

[0042] And / or when the supply flow rate is less than the set flow rate minus the preset margin λ, reduce the coolant flow rate in the dehumidification pipeline and increase the coolant flow rate in the internal circulation branch.

[0043] In some embodiments, if the liquid cooling equipment adopts a variable frequency refrigeration system, the cooling capacity of the refrigeration system is increased when the liquid supply temperature is greater than or equal to the set temperature plus the preset margin δ3.

[0044] And / or when the set temperature - preset margin δ3 ≤ supply temperature < set temperature + preset margin δ3, the refrigeration system maintains the current state;

[0045] And / or when the liquid supply temperature is less than the set temperature minus the preset margin δ3, reduce the cooling capacity of the refrigeration system.

[0046] In the above embodiments, the cooling capacity of the variable frequency refrigeration system is controlled by adjusting the compressor operating frequency and / or the condenser fan speed.

[0047] Furthermore, after each control strategy is executed, a set delay is waited before returning to reacquire the liquid supply temperature at the working section inlet and the dew point temperature of the area where the heating device is located.

[0048] Compared with the prior art, the present invention has the following beneficial effects:

[0049] 1. Design an internal circulation branch to control the temperature and flow rate of the coolant flowing through the heat-generating device, ensuring the heat dissipation effect of the heat-generating device;

[0050] 2. Design a dehumidification device to reduce the humidity in the area where the heating element is located, effectively prevent condensation from forming at the heating element, and gradually restore the heat dissipation capacity of the liquid cooling equipment;

[0051] 3. Adjust the operating status of the liquid cooling equipment according to parameters such as liquid supply temperature and dew point temperature. Through precise control strategies, both heat dissipation capacity and anti-condensation effect can be taken into account, which significantly improves the service life of heat-generating components and the reliability of liquid cooling equipment. Attached Figure Description

[0052] The present invention will now be described in detail with reference to the embodiments and accompanying drawings, wherein:

[0053] Figure 1 This is a connection diagram of the liquid cooling device of the present invention;

[0054] Figure 2 This is a schematic diagram of the piping inside the cabinet of this invention;

[0055] Figure 3 This is a flowchart illustrating the anti-condensation control method of the present invention;

[0056] Reference numerals: 1. Heating element; 2. Heat dissipation pipe; 21. Working section; 22. First temperature sensor; 23. Second temperature sensor; 24. First flow sensor; 3. Internal circulation branch; 31. Circulation pump; 32. Second flow sensor; 33. Second valve; 4. Dehumidification device; 41. Dehumidification pipe; 43. Water tray; 44. Drain pipe; 42. First valve; 5. Compressor; 6. Evaporator; 7. Condenser; 71. Condenser fan; 8. Liquid supply pump. Detailed Implementation

[0057] To make the technical problems to be solved, the technical solutions, and the beneficial effects of the present invention clearer, the present invention will be further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are only used to explain the present invention and are not intended to limit the present invention.

[0058] like Figure 1 As shown, the liquid cooling device proposed in this invention includes a heat dissipation mechanism and an internal circulation branch 3. The heat dissipation mechanism has a heat dissipation pipe 2 for circulating coolant. The heat dissipation pipe 2 includes a working section 21 that exchanges heat with the heat-generating device 1; that is, the working section 21 is part of the heat dissipation pipe 2. When the coolant in the heat dissipation pipe 2 flows through the working section, it exchanges heat with the heat-generating device 1. The coolant carries away the heat from the heat-generating device 1 and flows out from the working section 21, thereby cooling the heat-generating device 1. The inlet of the internal circulation branch 3 is connected to the outlet of the working section 21, and the outlet of the internal circulation branch 3 is connected to the inlet of the working section 21. That is, when the internal circulation branch 3 is connected, part of the coolant flowing out of the working section 21 will be returned to the inlet of the working section 21 through the internal circulation branch 3. The coolant sent out by the internal circulation branch 3 and the coolant flowing in from the inlet side of the heat dissipation pipe 2 are combined and then sent to the inlet of the working section 21. By adjusting the opening of the internal circulation branch 3, the temperature and flow rate of the coolant flowing through the heat-generating device 1 can be effectively controlled to ensure the heat dissipation effect of the heat-generating device 1.

[0059] The liquid cooling equipment also includes a dehumidification device 4, which has a dehumidification pipe 41 connected in parallel with the heat dissipation pipe 2. By designing the dehumidification device 4, the humidity in the area where the heat-generating device 1 is located is reduced, effectively preventing condensation at the heat-generating device. Moreover, after the air dries, the dew point temperature also decreases, which can provide more low-temperature coolant to the heat dissipation mechanism and gradually restore the heat dissipation capacity of the liquid cooling equipment. In order to balance dehumidification and heat dissipation effect, the internal circulation branch 3 and / or the dehumidification pipe 41 are equipped with valves for adjusting the coolant flow rate. The higher the coolant flow rate of the dehumidification pipe 41, the lower the coolant flow rate entering the heat dissipation pipe 2. At this time, the coolant flow rate of the internal circulation branch 3 is increased to maintain the coolant flow rate of the working section 21 at a basically constant level, thereby ensuring the heat dissipation effect of the heat-generating device 1.

[0060] As a preferred embodiment, the dehumidification pipe 41 is equipped with a first valve 42, and the internal circulation branch 3 is equipped with a second valve 33. The flow rate of the coolant in the dehumidification pipe 41 is controlled by opening or closing the first valve 42, and the flow rate of the coolant in the internal circulation branch 3 is controlled by opening or closing the second valve 33. It should be understood that there are various ways to control the flow rate of the dehumidification pipe 41 and the internal circulation branch 3, including but not limited to regulating valves. In some embodiments of the present invention, the internal circulation branch 3 is equipped with a circulation pump 31, which drives the flow of coolant in the internal circulation branch 3. The flow rate of the coolant in the internal circulation branch 3 can also be adjusted by controlling the rotation speed of the circulation pump 31.

[0061] The liquid cooling equipment also includes a refrigeration system, which has a compressor 5, a condenser 7, a throttling device, and an evaporator 6. The refrigeration system is used to provide coolant or to cool the coolant. The low-temperature coolant generated by the refrigeration system is provided to the heat dissipation pipe 2 and / or the dehumidification pipe 41 to dissipate heat from the heat-generating device 1 or to dehumidify the area where the heat-generating device 1 is located. In some embodiments, the evaporator 6 of the refrigeration system has a first branch and a second branch that exchange heat with each other. The first branch participates in the refrigerant circulation of the refrigeration system, and the second branch participates in the coolant circulation of the heat dissipation pipe 2 and / or the dehumidification pipe 41. The second branch is equipped with a liquid supply pump 8, which provides power to drive the coolant circulation, so that the coolant flowing out of the second branch is returned to the second branch after passing through the heat dissipation pipe 2 and / or the dehumidification pipe 41.

[0062] The liquid cooling equipment also includes a sensor assembly and a controller. The sensor assembly is used to detect at least one of the following data: the coolant temperature at the inlet of the heat dissipation pipe 2, the supply temperature at the inlet of the working section 21, the supply flow rate at the inlet of the working section 21, and the dew point temperature of the area where the heat-generating device 1 is located. The controller receives the detection data from the sensor assembly and adjusts the operating status of the liquid cooling equipment. The operating status of the liquid cooling equipment includes at least one of the following: the coolant flow rate of the internal circulation branch 3, the coolant flow rate of the dehumidification pipe 41, the compressor operating frequency of the refrigeration system, and the condenser fan speed of the refrigeration system. The means of adjusting the detection data and operating status can be designed according to the actual usage.

[0063] For example, for liquid cooling equipment using a variable frequency refrigeration system, the cooling capacity can be controlled by adjusting the compressor operating frequency, or the cooling capacity can be controlled by simultaneously adjusting the compressor operating frequency and the condenser fan speed. That is, the speed of the condenser fan 71 increases or decreases along with the compressor operating frequency. For liquid cooling equipment using a fixed frequency refrigeration system, the adjustment of its operating status excludes the compressor operating frequency and the condenser fan speed, and only adjusts the coolant flow rate of the internal circulation branch 3 and the dehumidification pipe 41.

[0064] In some embodiments of the present invention, the sensor assembly includes: a first temperature sensor 22, a second temperature sensor 23, a first flow sensor 24, and a second flow sensor 32. The first temperature sensor 22 is installed at the inlet of the heat dissipation pipe 2, and the coolant temperature is detected by the first temperature sensor 22. This coolant temperature is actually equivalent to the coolant temperature supplied by the evaporator 6. Since the heat dissipation pipe 2 is connected in parallel with the dehumidification pipe 41, this coolant temperature can also be equivalent to the coolant temperature at the inlet of the dehumidification pipe 41. The second temperature sensor 23 is installed at the inlet of the working section 21, and the supply temperature is detected by the second temperature sensor 23. This supply temperature is equivalent to the temperature after the coolant flowing into the inlet of the heat dissipation pipe 2 and the coolant supplied from the outlet of the internal circulation branch 3 merge, i.e., the temperature of the coolant actually supplied to the heat-generating device 1 for heat dissipation. The first flow sensor 24 is installed at the inlet of the heat dissipation pipe 2, and the second flow sensor 32 is installed on the internal circulation branch 3. The supply flow rate is the sum of the coolant flow rates detected by the first flow sensor 24 and the second flow sensor 32. The supply flow rate can also be directly detected by the flow sensor installed at the inlet of the working section 21.

[0065] It should be understood that there are various ways to install the sensor components. The above are just examples. The number, type and location of the sensors in this invention are not subject to any special restrictions.

[0066] like Figure 2As shown, in some embodiments of the present invention, both the heating element 1 and the dehumidification device 4 are located inside the cabinet of the liquid cooling equipment. The sensor assembly also includes a temperature and humidity sensor installed inside the cabinet, which calculates the current dew point temperature based on the ambient temperature and humidity detected by the temperature and humidity sensor. The heat dissipation mechanism is located at the bottom of the heating element 1, and the dehumidification device 4 is located below the heating element 1. A water collection tray 43 is located below the dehumidification pipe 41, and the water collection tray 43 is connected to a drain pipe 44 extending outside the cabinet. The coolant exchanges heat with the air through natural convection via fins, and the air condenses to produce condensate. The condensate dripping from the surface of the dehumidification device 4 falls into the water collection tray 43 and is then discharged outward through the drain pipe 44. The drain pipe 44 adopts a U-shaped bend design to ensure drainage capacity while maintaining the overall sealing performance of the cabinet.

[0067] like Figure 3 As shown, the present invention also proposes an anti-condensation control method for the above-mentioned liquid cooling equipment, which is executed by the controller. The specific control logic is as follows.

[0068] Obtain the liquid supply temperature at the inlet of the working section and the dew point temperature of the area where the heating element is located;

[0069] Compare the liquid supply temperature with the dew point temperature;

[0070] When the liquid supply temperature is less than the dew point temperature plus the preset margin δ1, it indicates that the air humidity is high and condensation is likely to occur. Therefore, the dew point temperature control strategy is implemented to increase the liquid supply temperature and decrease the dew point temperature.

[0071] And / or when the liquid supply temperature is greater than or equal to the dew point temperature plus the preset margin δ1, it indicates that the liquid supply temperature is too high and the risk of condensation is low. It is necessary to ensure the heat dissipation performance of the heat-generating device. Therefore, the set temperature control strategy is executed to make the liquid supply temperature reach the set temperature range.

[0072] For liquid-cooled equipment using variable frequency refrigeration systems, dew point temperature control strategies include:

[0073] Obtain the coolant temperature at the inlet of the heat dissipation pipes;

[0074] Compare the coolant temperature with the dew point temperature;

[0075] When the coolant temperature is greater than or equal to the dew point temperature minus the preset margin δ2, it indicates that the air humidity is high and the coolant temperature is high. Therefore, the cooling capacity of the refrigeration system should be increased and the coolant flow rate of the dehumidification pipeline should be increased to significantly increase the dehumidification capacity. At the same time, the coolant flow rate of the internal circulation branch should be increased to control the supply temperature and supply flow rate, reduce the risk of condensation, and ensure the heat dissipation effect of the heat-generating components.

[0076] And / or when the coolant temperature is less than the dew point temperature minus the preset margin δ2, it indicates that the air humidity is high and the coolant temperature is low. Therefore, it is only necessary to increase the coolant flow rate of the dehumidification pipeline to increase the dehumidification capacity, and at the same time increase the coolant flow rate of the internal circulation branch to control the supply temperature and supply flow rate, reduce the risk of condensation, and ensure the heat dissipation effect of the heat-generating devices.

[0077] For liquid cooling equipment using a fixed-frequency refrigeration system, dew point temperature control strategies include:

[0078] Obtain the coolant temperature at the inlet of the heat dissipation pipes;

[0079] Compare the coolant temperature with the dew point temperature;

[0080] When the coolant temperature is greater than or equal to the dew point temperature minus the preset margin δ2, it indicates that the air humidity is high and the coolant temperature is high. Therefore, the coolant flow rate of the dehumidification pipeline should be increased to increase the dehumidification capacity. At the same time, the coolant flow rate of the internal circulation branch should be increased to control the supply temperature and supply flow rate, reduce the risk of condensation, and ensure the heat dissipation effect of the heat-generating components.

[0081] And / or when the coolant temperature is less than the dew point temperature minus the preset margin δ2, it indicates that the air humidity is high and the coolant temperature is low, which can meet the low-temperature dehumidification requirements. Therefore, increase the coolant flow rate of the dehumidification pipeline to increase the dehumidification capacity. At the same time, increase the coolant flow rate of the internal circulation branch to control the supply temperature and supply flow rate, reduce the risk of condensation, and ensure the heat dissipation effect of the heat-generating devices.

[0082] For liquid cooling equipment using a variable frequency refrigeration system, the temperature control strategy includes:

[0083] Compare the supply temperature with the set temperature;

[0084] Obtain the liquid supply flow rate at the inlet of the working section and compare it with the set flow rate;

[0085] Based on the comparison results of the supply liquid temperature and the supply liquid flow rate, the cooling capacity of the refrigeration system is adjusted, and the coolant flow rate of the dehumidification pipeline and the internal circulation pipeline is adjusted at the same time. The specific adjustment is as follows.

[0086] The first type is where the liquid supply temperature is ≥ the set temperature + the preset margin δ3.

[0087] When the liquid supply flow rate is greater than or equal to the set flow rate plus the preset margin λ, it indicates that the liquid supply temperature is too high and the liquid supply flow rate is too large. Therefore, the cooling capacity of the refrigeration system should be increased to reduce the temperature of the coolant supplied to the heat dissipation pipe, thereby reducing the liquid supply temperature. At the same time, the coolant flow rate of the dehumidification pipe should be increased to reduce the liquid supply flow rate. Meanwhile, the coolant flow rate of the internal circulation branch should be reduced. After the heat exchange in the working section, the amount of coolant is reduced, thereby reducing the liquid supply flow rate and liquid supply temperature.

[0088] And / or when the set flow rate - preset margin λ ≤ supply flow rate < set flow rate + preset margin λ, it indicates that the supply flow rate is too high and the supply flow rate is moderate. Therefore, the cooling capacity of the refrigeration system is increased to reduce the temperature of the coolant supplied to the heat dissipation pipe, thereby reducing the supply flow rate. At the same time, the coolant flow rate of the dehumidification pipe is reduced to increase the coolant flow rate supplied to the heat dissipation pipe. Meanwhile, the coolant flow rate of the internal circulation branch is reduced, so that the amount of coolant after heat exchange in the working section is less, in order to maintain the balance of the supply flow rate and reduce the supply flow rate.

[0089] And / or when the liquid supply flow rate is less than the set flow rate minus the preset margin λ, it indicates that the liquid supply temperature is too high and the liquid supply flow rate is too low. Therefore, the cooling capacity of the refrigeration system is increased to reduce the temperature of the coolant supplied to the heat dissipation pipe, thereby reducing the liquid supply temperature. At the same time, the coolant flow rate of the dehumidification pipe is reduced to increase the coolant flow rate supplied to the heat dissipation pipe. The coolant flow rate of the internal circulation branch is also increased to increase the liquid supply flow rate. This also avoids condensation caused by excessively low liquid supply temperature.

[0090] The second type is: set temperature - preset margin δ3 ≤ supply temperature < set temperature + preset margin δ3.

[0091] When the liquid supply flow rate is greater than or equal to the set flow rate plus the preset margin λ, it indicates that the liquid supply temperature is moderate and the liquid supply flow rate is too large. Therefore, the refrigeration system maintains its current state, increases the coolant flow rate in the dehumidification pipe to reduce the coolant flow rate flowing into the heat dissipation pipe, reduces the liquid supply flow rate, and at the same time reduces the coolant flow rate in the internal circulation branch. As a result, the amount of coolant that flows into the working section after heat exchange is reduced, thereby reducing the liquid supply flow rate and maintaining the liquid supply temperature balance.

[0092] And / or when the set flow rate - preset margin λ ≤ liquid supply flow rate < set flow rate + preset margin λ, it indicates that the liquid supply temperature is constant and the liquid supply flow rate is moderate, and the refrigeration system, dehumidification pipeline and internal circulation branch maintain the current state.

[0093] And / or when the liquid supply flow rate is less than the set flow rate minus the preset margin λ, it indicates that the liquid supply temperature is moderate and the liquid supply flow rate is too small. Therefore, the refrigeration system maintains its current state, reduces the coolant flow rate of the dehumidification pipe to increase the coolant flow rate delivered to the heat dissipation pipe, and increases the coolant flow rate of the internal circulation branch to increase the liquid supply flow rate and maintain the liquid supply temperature balance.

[0094] The third type is when the liquid supply temperature is less than the set temperature minus the preset margin δ3.

[0095] When the liquid supply flow rate is greater than or equal to the set flow rate plus the preset margin λ, it indicates that the liquid supply temperature is too low and the liquid supply flow rate is too high. Therefore, the cooling capacity of the refrigeration system should be reduced to increase the temperature of the coolant supplied to the heat dissipation pipe, thereby increasing the liquid supply temperature. At the same time, the coolant flow rate of the dehumidification pipe should be increased to reduce the liquid supply flow rate. Meanwhile, the coolant flow rate of the internal circulation branch should be reduced. After the heat exchange in the working section, the amount of coolant is reduced, thereby reducing the liquid supply flow rate and increasing the liquid supply temperature.

[0096] And / or when the set flow rate - preset margin λ ≤ supply flow rate < set flow rate + preset margin λ, it indicates that the supply flow rate is too low and the supply flow rate is moderate. Therefore, the cooling capacity of the refrigeration system is reduced to increase the temperature of the coolant supplied to the heat dissipation pipe, thereby increasing the supply flow rate. At the same time, the coolant flow rate of the dehumidification pipe is reduced to increase the coolant flow rate supplied to the heat dissipation pipe. The coolant flow rate of the internal circulation branch is also reduced. After the heat exchange in the working section, the amount of coolant is reduced to maintain the balance of the supply flow rate and increase the supply flow rate.

[0097] And / or when the liquid supply flow rate is less than the set flow rate minus the preset margin λ, it indicates that the liquid supply temperature is too low and the liquid supply flow rate is too small. Therefore, the cooling capacity of the refrigeration system is reduced to increase the temperature of the coolant supplied to the heat dissipation pipe, thereby increasing the liquid supply temperature. At the same time, the coolant flow rate of the dehumidification pipe is reduced to increase the coolant flow rate supplied to the heat dissipation pipe. The coolant flow rate of the internal circulation branch is also increased to increase the liquid supply flow rate. This can also prevent condensation from occurring due to excessively low liquid supply temperature.

[0098] For liquid cooling equipment using a fixed-frequency refrigeration system, the temperature control strategy includes:

[0099] Compare the supply temperature with the set temperature;

[0100] Obtain the liquid supply flow rate at the inlet of the working section and compare it with the set flow rate;

[0101] Based on the comparison results of the supply temperature and the supply flow rate, only the coolant flow rate of the dehumidification pipeline and the internal circulation pipeline is adjusted, and the specific adjustment is as follows.

[0102] The first type is where the liquid supply temperature is ≥ the set temperature + the preset margin δ3.

[0103] When the liquid supply flow rate is greater than or equal to the set flow rate plus the preset margin λ, it indicates that the liquid supply temperature is too high and the liquid supply flow rate is too large. Therefore, the coolant flow rate of the dehumidification pipeline is increased to reduce the liquid supply flow rate. At the same time, the coolant flow rate of the internal circulation branch is reduced. After the heat exchange in the working section, the amount of coolant is reduced, thereby reducing the liquid supply flow rate and the liquid supply temperature.

[0104] And / or when the set flow rate - preset margin λ ≤ supply flow rate < set flow rate + preset margin λ, it indicates that the supply temperature is too high and the supply flow rate is appropriate. Therefore, reduce the coolant flow rate of the dehumidification pipeline to increase the coolant flow rate delivered to the heat dissipation pipeline, and at the same time reduce the coolant flow rate of the internal circulation branch. The amount of coolant after heat exchange in the working section will be less, so as to maintain the balance of the supply flow rate and reduce the supply temperature.

[0105] And / or when the supply flow rate is less than the set flow rate minus the preset margin λ, it indicates that the supply temperature is too high and the supply flow rate is too low. Therefore, reduce the coolant flow rate of the dehumidification pipe to increase the coolant flow rate delivered to the heat dissipation pipe, and at the same time increase the coolant flow rate of the internal circulation branch to increase the supply flow rate. This can also prevent condensation from occurring due to excessively low supply temperature.

[0106] The second type is: set temperature - preset margin δ3 ≤ supply temperature < set temperature + preset margin δ3.

[0107] When the supply flow rate is greater than or equal to the set flow rate plus the preset margin λ, it indicates that the supply temperature is moderate and the supply flow rate is too large. Therefore, the coolant flow rate of the dehumidification pipeline is increased to reduce the coolant flow rate flowing into the heat dissipation pipeline and reduce the supply flow rate. At the same time, the coolant flow rate of the internal circulation branch is reduced, so that the coolant after heat exchange in the working section is less, thereby reducing the supply flow rate and maintaining the supply temperature balance.

[0108] And / or when the set flow rate - preset margin λ ≤ supply flow rate < set flow rate + preset margin λ, it indicates that the supply temperature is constant and the supply flow rate is moderate, and the dehumidification pipeline and the internal circulation branch maintain the current state.

[0109] And / or when the supply flow rate is less than the set flow rate minus the preset margin λ, it indicates that the supply temperature is moderate and the supply flow rate is too small. Therefore, reduce the coolant flow rate of the dehumidification pipeline to increase the coolant flow rate delivered to the heat dissipation pipeline, and at the same time increase the coolant flow rate of the internal circulation branch to increase the supply flow rate and maintain the supply temperature balance.

[0110] The third type is when the liquid supply temperature is less than the set temperature minus the preset margin δ3.

[0111] When the supply flow rate is greater than or equal to the set flow rate plus the preset margin λ, it indicates that the supply temperature is too low and the supply flow rate is too high. Therefore, the coolant flow rate of the dehumidification pipeline is increased to reduce the supply flow rate. At the same time, the coolant flow rate of the internal circulation branch is reduced. After the heat exchange in the working section, the amount of coolant is reduced, thereby reducing the supply flow rate and increasing the supply temperature.

[0112] And / or when the set flow rate - preset margin λ ≤ supply flow rate < set flow rate + preset margin λ, it indicates that the supply temperature is too low and the supply flow rate is moderate. Therefore, reduce the coolant flow rate of the dehumidification pipeline to increase the coolant flow rate delivered to the heat dissipation pipeline, and at the same time reduce the coolant flow rate of the internal circulation branch. The amount of coolant after heat exchange in the working section will be less, so as to maintain the balance of supply flow rate and increase the supply temperature.

[0113] And / or when the supply flow rate is less than the set flow rate minus the preset margin λ, it indicates that the supply temperature is too low and the supply flow rate is too small. Therefore, reduce the coolant flow rate of the dehumidification pipe to increase the coolant flow rate delivered to the heat dissipation pipe, and at the same time increase the coolant flow rate of the internal circulation branch to increase the supply flow rate. This can also prevent condensation from occurring due to excessively low supply temperature.

[0114] In the above scheme, the cooling capacity of the variable frequency refrigeration system is controlled by adjusting the compressor operating frequency and / or the condenser fan speed. That is, the cooling capacity can be controlled by adjusting the compressor operating frequency alone, or the cooling capacity can be controlled by adjusting the compressor operating frequency and the condenser fan speed at the same time. In other words, the speed of the condenser fan increases or decreases together with the compressor operating frequency.

[0115] It should be noted that after each control strategy is executed, a set delay is waited before the system returns to reacquire the liquid supply temperature at the inlet of the working section and the dew point temperature of the area where the heating element is located. This means that the control strategy is adjusted in a timely manner according to the actual operating conditions of the liquid cooling equipment, so as to achieve a balance between heat dissipation capacity and anti-condensation effect, significantly improving the service life of the heating element and the reliability of the liquid cooling equipment.

[0116] like Figure 1 As shown, in some application examples of the present invention, the liquid cooling equipment adopts a variable frequency refrigeration system, and the evaporator 6 adopts a plate heat exchanger. When the equipment starts working, the liquid supply pump 8 is turned on, the circulation pump 31 is turned off, and the first valve 42 and the second valve 33 are both completely closed. At this time, the coolant is cooled by the plate heat exchanger and only flows to the heat-generating device 1. After the liquid cooling equipment operates stably, the controller acquires the detection data of the sensor components and adjusts the operating state of the liquid cooling equipment. The control logic executed by the controller has been described in detail above. The preferred control logic is configured with all the judgment conditions in the dew point temperature control strategy and the set temperature control strategy, that is, "and / or" in the above text is taken as "and". It should be understood that in practical applications, the control logic may only be configured with some of the judgment conditions in the dew point temperature control strategy and the set temperature control strategy.

[0117] It should be noted that the values ​​of preset margin δ1, preset margin δ2, preset margin δ3, preset margin λ, set temperature, set flow rate, set delay time, etc. are all designed according to specific application scenarios. For ease of understanding, some feasible data of the present invention are used as examples: preset margin δ1 is 2℃, preset margin δ2 is 2℃, preset margin δ3 is 5℃, preset margin λ is 10%, and set delay time is 5min.

[0118] It should be noted that the terminology used above is for describing specific embodiments only and is not intended to limit the exemplary embodiments of the present invention. When the terms "comprising" and / or "including" are used in this specification, they indicate the presence of features, steps, operations, devices, components, and / or combinations thereof. The order of execution of actions, steps, etc., in the apparatus and methods shown in the specification and drawings can be implemented in any order unless a specific order is expressly specified, and as long as the output of a previous process is not used in a subsequent process. Similar sequential terms used for ease of description do not imply that such an order must be followed.

[0119] Techniques, methods, and devices known to those skilled in the art may not be discussed in detail, but where appropriate, such techniques, methods, and devices should be considered part of the specification. In all examples shown and discussed herein, any specific values ​​should be interpreted as merely exemplary and not as limitations. Therefore, other examples of exemplary embodiments may have different values. It should be noted that similar reference numerals and letters in the following figures denote similar items; therefore, once an item is defined in one figure, it need not be further discussed in subsequent figures.

[0120] The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of the present invention should be included within the protection scope of the present invention.

Claims

1. Liquid cooling device, characterized in that include: A heat dissipation mechanism having heat dissipation pipes for circulating coolant, the heat dissipation pipes including a working section for heat exchange with a heat-generating device; An internal circulation branch, the inlet of which is connected to the outlet of the working section, and the outlet of which is connected to the inlet of the working section; A dehumidification device, wherein the dehumidification device has a dehumidification pipeline connected in parallel with the heat dissipation pipeline, and the internal circulation branch and / or the dehumidification pipeline are equipped with valves for adjusting the flow rate of coolant; The heating element and dehumidification device are both located inside the cabinet of the liquid cooling equipment.

2. The liquid cooling device of claim 1, wherein, Also includes: A refrigeration system, wherein the refrigeration system is used to provide the coolant or to cool the coolant.

3. The liquid cooling device of claim 2, wherein, The evaporator of the refrigeration system has a first branch and a second branch that exchange heat with each other. The first branch participates in the refrigerant circulation of the refrigeration system, and the second branch participates in the coolant circulation of the heat dissipation pipe and / or the dehumidification pipe.

4. The liquid cooling device of claim 2, wherein, Also includes: Sensor components and controllers; The sensor assembly is used to detect at least one of the following data: the coolant temperature at the inlet of the heat dissipation pipe, the supply temperature at the inlet of the working section, the supply flow rate at the inlet of the working section, and the dew point temperature of the area where the heating device is located. The controller receives the detection data from the sensor assembly and adjusts the operating status of the liquid cooling equipment.

5. The liquid cooling device of claim 4, wherein, The operating status of the liquid cooling equipment includes at least one of the following: the coolant flow rate of the internal circulation branch, the coolant flow rate of the dehumidification pipeline, the compressor operating frequency of the refrigeration system, and the condenser fan speed of the refrigeration system.

6. The liquid cooling device of claim 4, wherein, The sensor assembly includes: a first temperature sensor installed at the inlet of the heat dissipation pipe, a second temperature sensor installed at the inlet of the working section, a first flow sensor installed at the inlet of the heat dissipation pipe, and a second flow sensor installed on the internal circulation branch. The coolant temperature is detected by the first temperature sensor, the supply temperature is detected by the second temperature sensor, and the supply flow rate is the sum of the coolant flow rates detected by the first flow sensor and the second flow sensor.

7. The anti-condensation control method according to any one of claims 1 to 6, applied to the liquid cooling apparatus, characterized by, Includes the following steps: Obtain the liquid supply temperature at the inlet of the working section and the dew point temperature of the area where the heating element is located; Compare the liquid supply temperature with the dew point temperature; When the liquid supply temperature is less than the dew point temperature plus the preset margin δ1, the dew point temperature control strategy is executed to increase the liquid supply temperature and decrease the dew point temperature. And / or when the liquid supply temperature is ≥ dew point temperature + preset margin δ1, the set temperature control strategy is executed to make the liquid supply temperature reach the set temperature range.

8. The anti-condensation control method according to claim 7, characterized by, The dew point temperature control strategy includes: Obtain the coolant temperature at the inlet of the heat dissipation pipe; Compare the coolant temperature with the dew point temperature; When the coolant temperature is greater than or equal to the dew point temperature minus the preset margin δ2, increase the coolant flow rate in the dehumidification pipeline and the internal circulation branch. And / or when the coolant temperature is less than the dew point temperature minus the preset margin δ2, increase the coolant flow rate in the dehumidification pipeline and the internal circulation branch.

9. The anti-condensation control method according to claim 8, characterized by, If the liquid cooling equipment adopts a variable frequency refrigeration system, then in the dew point temperature control strategy, when the coolant temperature is greater than or equal to the dew point temperature minus the preset margin δ2, the cooling capacity of the refrigeration system is increased.

10. The anti-condensation control method according to claim 7, characterized in that, The set temperature control strategy includes: Compare the supply temperature with the set temperature; Obtain the liquid supply flow rate at the inlet of the working section and compare the liquid supply flow rate with the set flow rate; Adjust the coolant flow rate of the dehumidification pipeline and the internal circulation pipeline based on the comparison results of the supply temperature and the supply flow rate.

11. The anti-condensation control method according to claim 10, characterized in that, The set temperature control strategy also includes: If the supply temperature is greater than or equal to the set temperature plus the preset margin δ3, then when the supply flow rate is greater than or equal to the set flow rate plus the preset margin λ, increase the coolant flow rate of the dehumidification pipeline and decrease the coolant flow rate of the internal circulation branch. And / or when the set flow rate - preset margin λ ≤ supply flow rate < set flow rate + preset margin λ, reduce the coolant flow rate in the dehumidification pipeline and the internal circulation branch; And / or when the supply flow rate is less than the set flow rate minus the preset margin λ, reduce the coolant flow rate in the dehumidification pipeline and increase the coolant flow rate in the internal circulation branch.

12. The anti-condensation control method according to claim 10, characterized by, The set temperature control strategy also includes: If the set temperature - preset margin δ3 ≤ supply temperature < set temperature + preset margin δ3, then when the supply flow rate ≥ set flow rate + preset margin λ, increase the coolant flow rate of the dehumidification pipe and decrease the coolant flow rate of the internal circulation branch. And / or when the set flow rate - preset margin λ ≤ liquid supply flow rate < set flow rate + preset margin λ, the dehumidification pipeline and internal circulation branch shall maintain the current state; And / or when the supply flow rate is less than the set flow rate minus the preset margin λ, reduce the coolant flow rate in the dehumidification pipeline and increase the coolant flow rate in the internal circulation branch.

13. The anti-condensation control method according to claim 10, characterized by, The set temperature control strategy also includes: If the supply temperature is less than the set temperature minus the preset margin δ3, then when the supply flow rate is greater than or equal to the set flow rate plus the preset margin λ, increase the coolant flow rate of the dehumidification pipe and decrease the coolant flow rate of the internal circulation branch. And / or when the set flow rate - preset margin λ ≤ supply flow rate < set flow rate + preset margin λ, reduce the coolant flow rate in the dehumidification pipeline and the internal circulation branch; And / or when the supply flow rate is less than the set flow rate minus the preset margin λ, reduce the coolant flow rate in the dehumidification pipeline and increase the coolant flow rate in the internal circulation branch.

14. The anti-condensation control method according to claim 10, characterized by, If the liquid cooling equipment adopts a variable frequency refrigeration system, the cooling capacity of the refrigeration system will be increased when the liquid supply temperature is greater than or equal to the set temperature plus the preset margin δ3. And / or when the set temperature - preset margin δ3 ≤ supply temperature < set temperature + preset margin δ3, the refrigeration system maintains the current state; And / or when the liquid supply temperature is less than the set temperature minus the preset margin δ3, reduce the cooling capacity of the refrigeration system.

15. The anti-condensation control method according to claim 9 or 14, characterized by, The cooling capacity of the variable frequency refrigeration system is controlled by adjusting the compressor operating frequency and / or the condenser fan speed.

16. The anti-condensation control method according to any one of claims 7 to 14, characterized by, After each control strategy is executed, wait for the set delay time, and then return to reacquire the liquid supply temperature at the inlet of the working section and the dew point temperature of the area where the heating device is located.

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