A two-phase cold plate liquid cooling system control method, device and equipment

Abstract

The application discloses a two-phase cold plate type liquid cooling system control method, comprising the following steps: obtaining the working medium phase change temperature type of the cooling liquid in the two-phase cold plate type liquid cooling system; when the working medium phase change temperature type is a constant value, the working medium phase change rate of each branch is controlled to a preset value by controlling the system flow; when the working medium phase change temperature type is a range value, the working medium phase change rate of each branch is controlled to a preset value by controlling the phase change rate of each branch. The two-phase cold plate type liquid cooling system control method provided by the application improves the robustness of the control system, improves the system performance, and saves manpower. The application also discloses a two-phase cold plate type liquid cooling system control device, equipment and a storage medium, which have corresponding technical effects.

Description

Technical Field

[0001] This invention relates to the field of liquid cooling technology, and in particular to a control method, apparatus, equipment, and computer-readable storage medium for a two-phase cold plate liquid cooling system. Background Technology

[0002] With the power consumption of chips increasing exponentially, two-phase cold plate liquid cooling utilizes the latent heat transfer of liquid phase change to dissipate heat, resulting in extremely high heat dissipation efficiency and better temperature uniformity. It is an important direction for solving the heat dissipation problem of high heat flux density chips in the future.

[0003] However, in cold plate liquid cooling systems, multiple liquid cooling nodes are often connected in parallel. When using a two-phase cold plate liquid cooling system, it is difficult to distribute the flow rate of multiple parallel branches because each branch has a different heat load. This can lead to a stronger phase change boiling effect in branches with higher heat loads, resulting in greater flow resistance and a decrease in flow rate in those branches. This causes temperature curve oscillations and significantly reduces the robustness of the control system. Furthermore, the problem can only be identified and manually addressed after a branch has deteriorated, impacting system performance and wasting considerable manpower.

[0004] In summary, how to effectively solve the problems of low robustness of the control system, which affects system performance and wastes manpower in the current two-phase cold plate liquid cooling system control method is an urgent problem to be solved by those skilled in the art. Summary of the Invention

[0005] The purpose of this invention is to provide a control method for a two-phase cold plate liquid cooling system, which improves the robustness of the control system, enhances system performance, and saves manpower. Another purpose of this invention is to provide a control device, equipment, and computer-readable storage medium for a two-phase cold plate liquid cooling system.

[0006] To solve the above-mentioned technical problems, the present invention provides the following technical solution:

[0007] A control method for a two-phase cold plate liquid cooling system includes:

[0008] To obtain the phase change temperature type of the working fluid in a two-phase cold plate liquid cooling system;

[0009] When the working fluid phase change temperature type is a fixed value, the phase change rate of the working fluid in each branch is controlled to a preset value by controlling the flow rate of the system.

[0010] When the working fluid phase change temperature type is a range value, the working fluid phase change rate of each branch is controlled to the preset value by controlling the phase change rate of each branch.

[0011] In one specific embodiment of the present invention, when the working fluid phase change temperature type is a constant value, the phase change rate of the working fluid in each branch is controlled to a preset value by controlling the system flow rate, including:

[0012] When the working fluid phase change temperature type is a fixed value and the power consumption change ratio of each branch is consistent, the working fluid phase change rate of each branch is controlled to the preset value by adjusting the pump speed of the main pipeline and the valve opening of the main pipeline to adjust the output flow of the main pipeline.

[0013] In one specific embodiment of the present invention, when the working fluid phase change temperature type is a constant value, the phase change rate of the working fluid in each branch is controlled to a preset value by controlling the system flow rate, including:

[0014] When the working fluid phase change temperature type is a fixed value and the power consumption change ratio of each branch is inconsistent, the working fluid phase change rate of each branch is controlled to the preset value by adjusting the valve opening of each branch to adjust the flow rate of each branch.

[0015] In one specific embodiment of the present invention, the phase change rate of the working fluid in each branch is controlled to the preset value by adjusting the opening degree of the valves in each branch to regulate the flow rate of each branch, including:

[0016] The specific heat capacity, latent heat coefficient of the working fluid phase change, and phase change temperature of the working fluid are obtained.

[0017] Obtain the current working fluid phase change rate for each branch, and then filter out the branches whose current working fluid phase change rate is inconsistent with the preset value.

[0018] Obtain the device power consumption of each selected branch;

[0019] Read the actual branch monitoring flow from the branch flow meter of each selected branch;

[0020] Obtain the branch inlet temperature of each filtered branch;

[0021] Based on the specific heat capacity, the latent heat coefficient of the working fluid phase change, the working fluid phase change temperature, the inlet temperature of each branch, the power consumption of each device, and the actual monitored flow rate of each branch, the target branch flow rate value of each selected branch is calculated respectively.

[0022] Calculate the first error and the rate of change of the first error between the actual branch monitoring flow and the target branch flow value for each selected branch;

[0023] The first error and the rate of change of the first error are input to the fuzzy controller, and proportional-integral-derivative control is performed using the fuzzy controller to obtain the change of the first proportional adjustment coefficient, the change of the first integral adjustment coefficient, and the change of the first derivative adjustment coefficient.

[0024] Adjust the valve opening of each branch according to the changes in the first proportional adjustment coefficient, the first integral adjustment coefficient, and the first derivative adjustment coefficient corresponding to each selected branch.

[0025] Obtain the current working fluid phase change rate for each branch in the system;

[0026] When it is determined that there is a branch whose current working fluid phase change rate is inconsistent with the preset value, the step of filtering out the branches whose current working fluid phase change rate is inconsistent with the preset value is repeated until the working fluid phase change rate of each branch in the system is controlled to the preset value.

[0027] In one specific embodiment of the present invention, proportional-integral-derivative control is performed using the fuzzy controller to obtain the change in the first proportional adjustment coefficient, the change in the first integral adjustment coefficient, and the change in the first derivative adjustment coefficient, including:

[0028] The fuzzy controller is used to perform proportional-integral-derivative control on the opening degree of each branch valve through a fuzzy control algorithm, so as to obtain the change of the first proportional adjustment coefficient, the change of the first integral adjustment coefficient and the change of the first derivative adjustment coefficient corresponding to the opening degree of each branch valve.

[0029] In one specific embodiment of the present invention, controlling the phase transition rate of the working fluid in each branch to the preset value by controlling the phase transition rate of each branch includes:

[0030] The specific heat capacity and latent heat coefficient of the working fluid phase change are obtained;

[0031] Obtain the current working fluid phase change rate for each branch, and then filter out the branches whose current working fluid phase change rate is inconsistent with the preset value.

[0032] Obtain the branch inlet temperature, branch outlet temperature, branch inlet pressure, branch outlet pressure, equipment power consumption of the branch, and the current working fluid phase change temperature of the branch for each filtered branch.

[0033] The enthalpy of the working fluid at the inlet of each selected branch is calculated based on the branch inlet temperature and the branch inlet pressure.

[0034] Read the actual branch monitoring flow from the branch flow meter of each selected branch;

[0035] Based on the specific heat capacity, the latent heat coefficient of the working fluid phase change, the current working fluid phase change temperature, the inlet temperature of each branch, the power consumption of each device, and the actual monitored flow rate of each branch, the target branch flow rate value of each selected branch is calculated respectively.

[0036] Based on the enthalpy of the working fluid at the inlet of each selected branch, the power consumption of the equipment, and the flow rate of the target branch, calculate the enthalpy of the working fluid at the outlet of each selected branch.

[0037] The target working fluid phase change rate of each selected branch is calculated based on the enthalpy and pressure of the working fluid at the branch outlet.

[0038] Calculate the second error and the rate of change of the second error between the current working fluid phase change rate and the target working fluid phase change rate for each selected branch;

[0039] The second error and the rate of change of the second error are input to the fuzzy controller, and proportional-integral-derivative control is performed using the fuzzy controller to obtain the change of the second proportional adjustment coefficient, the change of the second integral adjustment coefficient, and the change of the second derivative adjustment coefficient.

[0040] Adjust the valve opening of each branch according to the changes in the second proportional adjustment coefficient, the second integral adjustment coefficient, and the second derivative adjustment coefficient corresponding to each selected branch.

[0041] Obtain the current working fluid phase change rate for each branch in the system;

[0042] When it is determined that there is a branch whose current working fluid phase change rate is inconsistent with the preset value, the step of filtering out the branches whose current working fluid phase change rate is inconsistent with the preset value is repeated until the working fluid phase change rate of each branch in the system is controlled to the preset value.

[0043] In one specific embodiment of the present invention, it further includes:

[0044] When there is a branch where the working fluid phase change rate adjustment time exceeds the preset time and the current working fluid phase change rate after adjustment exceeds the preset phase change rate threshold range, an alarm message is output.

[0045] A control device for a two-phase cold plate liquid cooling system, comprising:

[0046] The working fluid phase change temperature type acquisition module is used to acquire the working fluid phase change temperature type of the coolant in a two-phase cold plate liquid cooling system.

[0047] The system flow control module is used to control the phase change rate of the working fluid in each branch to a preset value by controlling the system flow when the working fluid phase change temperature type is a fixed value.

[0048] The branch phase change rate control module is used to control the phase change rate of the working fluid in each branch to the preset value when the working fluid phase change temperature type is a range value.

[0049] A control device for a two-phase cold plate liquid cooling system includes:

[0050] Memory, used to store computer programs;

[0051] A processor is used to execute the computer program to implement the steps of the control method for the two-phase cold plate liquid cooling system as described above.

[0052] A computer-readable storage medium storing a computer program, which, when executed by a processor, implements the steps of the control method for a two-phase cold plate liquid cooling system as described above.

[0053] The control method for a two-phase cold plate liquid cooling system provided by this invention obtains the phase change temperature type of the working fluid in the two-phase cold plate liquid cooling system; when the working fluid phase change temperature type is a fixed value, the phase change rate of the working fluid in each branch is controlled to a preset value by controlling the system flow rate; when the working fluid phase change temperature type is a range value, the phase change rate of the working fluid in each branch is controlled to a preset value by controlling the phase change rate of each branch.

[0054] As can be seen from the above technical solution, by pre-setting a preset value for the working fluid phase change rate of each branch to optimize heat exchange efficiency, the phase change temperature type of the coolant in the two-phase cold plate liquid cooling system is obtained. When the working fluid phase change temperature type is a fixed value, the phase change rate of each branch is controlled to the preset value by controlling the system flow rate. When the working fluid phase change temperature type is a range value, the phase change rate of each branch is controlled to the preset value by controlling the phase change rate of each branch. By selecting a control scheme that matches the working fluid phase change temperature type from two control schemes—system flow control and branch phase change rate control—the phase change rate of each branch is kept at the value with the highest heat exchange efficiency. This results in better dynamic response performance of the control system under sudden load changes. By monitoring the phase change rate of each branch in real time, the probability of abnormal situations such as working fluid burning out or no phase change is significantly reduced. This improves the robustness of the control system and enhances system performance. The control process is automated, saving manpower.

[0055] Accordingly, the present invention also provides a two-phase cold plate liquid cooling system control device, equipment, and computer-readable storage medium corresponding to the above-mentioned two-phase cold plate liquid cooling system control method, which have the above-mentioned technical effects, and will not be repeated here. Attached Figure Description

[0056] To more clearly illustrate the technical solutions in the embodiments of the present invention or related technologies, the drawings used in the description of the embodiments or related technologies will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0057] Figure 1 This is a flowchart illustrating the implementation of a control method for a two-phase cold plate liquid cooling system in an embodiment of the present invention.

[0058] Figure 2 This is a flowchart illustrating the implementation of another two-phase cold plate liquid cooling system control method in this invention.

[0059] Figure 3 This is a control architecture diagram of a two-phase cold plate liquid cooling system according to an embodiment of the present invention;

[0060] Figure 4 This is a structural block diagram of a two-phase cold plate liquid cooling system according to an embodiment of the present invention;

[0061] Figure 5 This is a schematic diagram of a fuzzy proportional-integral-derivative control principle in an embodiment of the present invention;

[0062] Figure 6 This is a flowchart illustrating the implementation of system flow control in an embodiment of the present invention;

[0063] Figure 7 This is a flowchart illustrating the implementation of branch working fluid phase change rate control in an embodiment of the present invention.

[0064] Figure 8 This is a flowchart illustrating the implementation of another control method for a two-phase cold plate liquid cooling system in an embodiment of the present invention.

[0065] Figure 9 This is a structural block diagram of a control device for a two-phase cold plate liquid cooling system according to an embodiment of the present invention;

[0066] Figure 10 This is a structural block diagram of a two-phase cold plate liquid cooling system control device according to an embodiment of the present invention;

[0067] Figure 11 This is a schematic diagram of the specific structure of a two-phase cold plate liquid cooling system control device provided in an embodiment of the present invention. Detailed Implementation

[0068] To enable those skilled in the art to better understand the present invention, the invention will be further described in detail below with reference to the accompanying drawings and specific embodiments. Obviously, the described embodiments are merely some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0069] See Figure 1 , Figure 1 This is a flowchart illustrating an implementation method for a two-phase cold plate liquid cooling system according to an embodiment of the present invention. The method may include the following steps:

[0070] S101: Obtain the phase change temperature type of the working fluid in a two-phase cold plate liquid cooling system.

[0071] The working fluid phase change temperature type includes types with a constant working fluid phase change temperature and types with a range of values. This section describes how to obtain the working fluid phase change temperature type in a two-phase cold plate liquid cooling system.

[0072] S102: When the working fluid phase change temperature type is a fixed value, the phase change rate of the working fluid in each branch is controlled to a preset value by controlling the flow rate of the system.

[0073] After obtaining the phase change temperature type of the coolant in the two-phase cold plate liquid cooling system, when the phase change temperature type is a constant, the system flow rate is controlled to adjust the phase change rate of the coolant in each branch to a preset value. For example, based on the heat transfer efficiency of the coolant at multiple phase change rates, the phase change rate with the highest heat transfer efficiency can be selected as the target value for the phase change rate of the coolant in each branch to be controlled. For instance, the preset value for the phase change rate of the coolant in each branch can be set to 60%.

[0074] S103: When the working fluid phase change temperature type is a range value, the working fluid phase change rate of each branch is controlled to the preset value by controlling the phase change rate of each branch.

[0075] After obtaining the phase change temperature type of the coolant in the two-phase cold plate liquid cooling system, when the phase change temperature type is within a range, the phase change rate of each branch is controlled to a preset value by controlling the phase change rate of each branch. For example, the phase change rate of each branch can be controlled by controlling the opening of the solenoid valves in each branch. By selecting a control scheme that matches the phase change temperature type from two control schemes—system flow control and branch phase change rate control—the flow resistance of any branch in the system can be controlled at a stable value, avoiding flow deterioration caused by abnormal vaporization due to power consumption fluctuations in the branch. At the same time, the phase change rate of each branch is monitored in real time, and the phase change rate of the coolant in each branch is controlled at the optimal value, thereby improving the heat exchange efficiency of each branch.

[0076] As can be seen from the above technical solution, by pre-setting the optimal phase change rate of the working fluid in each branch to achieve the best heat exchange efficiency, the phase change temperature type of the coolant in the two-phase cold plate liquid cooling system is obtained. When the working fluid phase change temperature type is a constant value, the system flow rate is controlled to bring the working fluid phase change rate of each branch to the preset value. When the working fluid phase change temperature type is within a range, the phase change rate of each branch is controlled to bring the working fluid phase change rate of each branch to the preset value. By selecting a control scheme that matches the working fluid phase change temperature type from two control schemes—system flow control and branch phase change rate control—the phase change rate of each branch is kept at the value with the highest heat exchange efficiency. This results in better dynamic response performance of the control system under sudden load changes. By monitoring the phase change rate of each branch in real time, the probability of abnormal situations such as working fluid burning out or no phase change is significantly reduced. This improves the robustness of the control system and enhances system performance. The control process is automated, saving manpower.

[0077] It should be noted that, based on the above embodiments, the present invention also provides corresponding improvements. In subsequent embodiments, steps identical or corresponding to those in the above embodiments can be referenced interchangeably, and their respective beneficial effects can also be referred to each other. These improvements will not be elaborated upon in the following improved embodiments.

[0078] See Figure 2 , Figure 2 This is a flowchart illustrating another implementation method for a two-phase cold plate liquid cooling system in an embodiment of the present invention. The method may include the following steps:

[0079] S201: Obtain the phase change temperature type of the working fluid in a two-phase cold plate liquid cooling system.

[0080] See Figure 3 , Figure 3 This is a control architecture diagram of a two-phase cold plate liquid cooling system according to an embodiment of the present invention. The main body may include pumps involved in regulation, main pipelines, cooling branch nodes and control systems, rack-mounted equipment, alarm modules, and heat exchangers and liquid storage tanks as the foundation of the liquid cooling system.

[0081] See Figure 4 , Figure 4 This is a structural block diagram of a two-phase cold plate liquid cooling system according to an embodiment of the present invention. The pump provides power to circulate the coolant, and its output flow rate and head can be changed by adjusting its speed. A flow meter is installed on the main pipeline to monitor the total system flow rate, and a temperature sensor is also installed on the main pipeline to monitor the inlet temperature of each branch. The main pipeline connects to the inlet and outlet of the branches via a manifold to distribute the coolant to each branch for cooling. Temperature and pressure sensors are arranged at the inlet and outlet of each branch to read the inlet and outlet working fluid parameters. Each branch inlet is equipped with a solenoid valve, and the flow rate through each branch is adjusted by regulating the valve opening. A heat exchanger is used for heat exchange and cooling of the coolant after phase change with the external primary side. The cooled liquid then recondenses into an unsaturated liquid and returns to the storage tank.

[0082] S202: When the working fluid phase change temperature type is a fixed value and the power consumption change ratio of each branch is inconsistent, the working fluid phase change rate of each branch is controlled to the preset value by adjusting the valve opening of each branch to adjust the flow rate of each branch.

[0083] When the working fluid phase change temperature is constant and the power consumption variation ratio of each branch is inconsistent, the flow rate of each branch is adjusted by regulating the valve opening of each branch, thereby controlling the working fluid phase change rate of each branch to a preset value. When the working fluid phase change temperature is constant and the power consumption variation ratio of each branch is inconsistent, the flow rate of each branch is adjusted by regulating the valve opening of each branch, achieving precise regulation of the flow rate of each branch.

[0084] In one specific embodiment of the present invention, adjusting the opening degree of each branch valve to regulate the flow rate of each branch and controlling the phase change rate of the working fluid in each branch to a preset value may include the following steps:

[0085] Step 1: Obtain the specific heat capacity of the coolant, the latent heat coefficient of the working fluid phase change, and the phase change temperature of the working fluid;

[0086] Step 2: Obtain the current working fluid phase change rate for each branch, and then filter out the branches whose current working fluid phase change rate is inconsistent with the preset value.

[0087] Step 3: Obtain the device power consumption of each selected branch;

[0088] Step 4: Read the actual branch monitoring flow from the branch flow meter of each selected branch;

[0089] Step 5: Obtain the inlet temperature of each selected branch;

[0090] Step 6: Calculate the target branch flow value for each selected branch based on the specific heat capacity, latent heat coefficient of the working fluid phase change, working fluid phase change temperature, inlet temperature of each branch, power consumption of each device, and actual monitored flow rate of each branch.

[0091] Step 7: Calculate the first error and the rate of change of the first error between the actual branch monitoring flow and the target branch flow value for each selected branch;

[0092] Step 8: Input the first error and the first error change rate into the fuzzy controller, and use the fuzzy controller to perform proportional-integral-derivative control to obtain the change of the first proportional adjustment coefficient, the change of the first integral adjustment coefficient, and the change of the first derivative adjustment coefficient;

[0093] Step 9: Adjust the valve opening of each branch according to the changes in the first proportional adjustment coefficient, the first integral adjustment coefficient, and the first derivative adjustment coefficient corresponding to each selected branch.

[0094] Step 10: Obtain the current working fluid phase change rate for each branch in the system;

[0095] Step 11: When it is determined that there is a branch where the current working fluid phase change rate is inconsistent with the preset value, return to the step in step 2 to filter out the branches where the current working fluid phase change rate is inconsistent with the preset value, until the working fluid phase change rate of each branch in the system is controlled to the preset value.

[0096] For ease of description, the above eleven steps can be combined for explanation.

[0097] Each branch is equipped with rack-mounted (IT) equipment, with n branches in total. During the initial pressurization test, all rack-mounted equipment in each branch can be pressurized to their maximum power consumption. At this point, the power of each branch is the same. To ensure that the flow rate of each branch is completely consistent, the flow resistance, phase change temperature, and rack-mounted equipment temperature of each branch must be consistent. The flow rate of the main pipeline needs to be evenly distributed to each branch. The flow rate of the main pipeline is F0, and the flow rate of each branch needs to be controlled at Fn = F0 / n. The power consumption of the rack-mounted equipment is Q1 = latent heat of the working fluid Q2 + sensible heat Q3, where sensible heat Q3 = cm(T1-Tn1), T1 is the phase change temperature of the working fluid, Tn1 is the inlet temperature of each branch, m is the mass flow rate of the branch, c is the specific heat capacity, and latent heat Q2 = Fn*L*0.6, where L is the latent heat coefficient of the working fluid phase change. The total flow rate F0 can be obtained as (Q1-cm(T1-Tn1)) / 0.6 / L*n.

[0098] When the working fluid phase change temperature is constant and the power consumption change ratio of each branch is inconsistent, the specific heat capacity c, latent heat coefficient L, and working fluid phase change temperature T1 of the coolant are obtained. The current working fluid phase change rate of each branch is obtained, and the current working fluid phase change rate of each branch is compared with the preset value. Branches whose current working fluid phase change rate is inconsistent with the preset value are selected. The power consumption Q1 of each selected branch is obtained, and the actual branch monitoring flow m in the branch flow meter of each selected branch is read. The branch inlet temperature Tn1 of each selected branch is obtained. Based on the specific heat capacity c, the latent heat coefficient L, the working fluid phase change temperature T1, the inlet temperature Tn1 of each branch, the power consumption Q1 of each equipment, and the actual branch monitoring flow m of each branch, the target branch flow value Fn of each selected branch is calculated. The calculation formula can be: Fn=(Q1-cm(T1-Tn1)) / 0.6 / L.

[0099] See Figure 5 , Figure 5This is a schematic diagram of a fuzzy proportional-integral-derivative (PID) control principle in an embodiment of the present invention. The first error E and the first error change rate Ec between the actual monitored flow rate and the target flow rate for each selected branch are calculated. These two values ​​are then input to a fuzzy controller. The fuzzy controller performs PID control according to a fuzzy control algorithm to obtain the first proportional adjustment coefficient change ΔKp, the first integral adjustment coefficient change ΔKi, and the first derivative adjustment coefficient change ΔKd. The valve opening of each branch is adjusted according to these values. After adjustment, the current working fluid phase change rate of each branch in the system is obtained, and then compared with the preset value. When it is determined that there is a branch whose current working fluid phase change rate is inconsistent with the preset value, the branches with inconsistent current working fluid phase change rates are selected again, and the target branch flow rate of each branch is calculated. The valve opening of each branch is adjusted using a fuzzy controller until the working fluid phase change rate of each branch in the system is controlled to the preset value. By calculating the target branch flow rate of each branch when the working fluid phase change temperature type is constant and the power consumption change ratio of each branch is inconsistent, and adjusting the valve opening of each branch using a fuzzy controller based on the calculation results, the working fluid phase change rate of each branch is adjusted to the optimal value. Through fuzzy adaptive proportional-integral-derivative control, the control system has better dynamic response performance under sudden load changes.

[0100] In proportional-integral-derivative (PID) control, increasing the proportional gain Kp may lead to instability in the closed-loop system. The integral gain Ki helps eliminate static error, but increasing Ki also increases overshoot, potentially causing instability. Increasing the derivative gain Kd speeds up the system response and shortens the settling time, but excessively increasing it can also destabilize the system. The tuning principles for these three parameters are as follows: the proportional gain Kp is set within the range of 1-10, the integral gain Ki within the range of 0.1-0.2, and the derivative gain Kd within the range of 0.1-1. The percentage change for large Δ values ​​is 10%, moderate is 5%, and small is 2%.

[0101] (1) When e·ec>0 and e>0, ec>0, Kp should decrease and Ki should increase. Therefore, △Kp is negative, △Ki is positive, and △Kd =0. When e·ec>0 and e<0, ec<0, Kp should increase. Therefore, △Kp is relatively large, △Ki is moderate, and △Kd remains relatively small.

[0102] (2) When e·ec<0, it means that the system error is decreasing. We should try to keep the original inputs Kp and Ki as much as possible. Therefore, ΔKp and ΔKi should also keep a small change.

[0103] (3) When e·ec=0 and e=0, if ec=0, it means that the system has reached the target opening and is stable, and the original inputs Kp and Ki are maintained; if ec≠0, it means that the system has only reached the target opening for a short time and is likely still in the oscillation stage, so △Kp, △Ki and △Kd remain at a small value.

[0104] (4) When e·ec=0 and e≠0, it means that the system control process has entered a steady state, but there is a certain steady state error. Therefore, △Kp is large and △Ki is moderate.

[0105] The above process enables precise proportional-integral-derivative (PID) control based on the relationship between error and error rate of change, thereby improving the accuracy of PID control.

[0106] In one specific embodiment of the present invention, proportional-integral-derivative control is performed using a fuzzy controller to obtain the change in the first proportional adjustment coefficient, the change in the first integral adjustment coefficient, and the change in the first derivative adjustment coefficient. This may include the following steps:

[0107] By using a fuzzy controller and a fuzzy control algorithm to perform proportional-integral-derivative control on the opening degree of each branch valve, the changes in the first proportional adjustment coefficient, the first integral adjustment coefficient, and the first derivative adjustment coefficient corresponding to the opening degree of each branch valve are obtained.

[0108] When using a fuzzy controller for proportional-integral-derivative (PID) control, the fuzzy controller employs a fuzzy control algorithm to perform PID control on the opening degree of each branch valve, obtaining the changes in the first proportional adjustment coefficient, the first integral adjustment coefficient, and the first derivative adjustment coefficient corresponding to the opening degree of each branch valve. This maps the branch flow control quantity to the branch valve opening degree, improving the convenience of branch working fluid phase change rate control.

[0109] S203: When the working fluid phase change temperature type is a range value, the working fluid phase change rate of each branch is controlled to the preset value by controlling the phase change rate of each branch.

[0110] In one specific embodiment of the present invention, when the working fluid phase change temperature type is a constant value, controlling the phase change rate of the working fluid in each branch to a preset value by controlling the system flow rate may include the following steps:

[0111] When the working fluid phase change temperature type is a constant and the power consumption change ratio of each branch is consistent, the working fluid phase change rate of each branch is controlled to the preset value by adjusting the pump speed of the main pipeline and the valve opening of the main pipeline to adjust the output flow of the main pipeline.

[0112] When the working fluid phase change temperature is constant and the power consumption change ratio of each branch is consistent (e.g., when the power consumption decrease ratio of each branch is exactly the same), the output flow rate of the main pipeline can be adjusted by regulating the pump speed and valve opening of the main pipeline, thereby controlling the working fluid phase change rate of each branch to a preset value. By adjusting only the pump speed of the main pipeline when the working fluid phase change temperature is constant and the power consumption change ratio of each branch is consistent, the working fluid phase change rate of each branch can be controlled to the optimal value, thus improving the adjustment efficiency of the working fluid phase change rate of each branch.

[0113] See Figure 6 , Figure 6 This is a flowchart illustrating a system flow control implementation in an embodiment of the present invention. During system flow control, the main pipeline flow setpoint is obtained, the actual outlet flow value is obtained, and the absolute value of the difference between the main pipeline flow setpoint and the actual outlet flow value is calculated. It is then determined whether the calculated absolute value of the difference is less than or equal to 0.51 pm. If the absolute value of the difference is less than or equal to 0.51 pm, it is further determined whether the actual outlet flow value is less than the main pipeline flow setpoint. If the actual outlet flow value is less than the main pipeline flow setpoint, the opening of the two-way valve in the main pipeline is increased by 0.5%. If the actual outlet flow value is not less than the main pipeline flow setpoint, it is determined whether the actual outlet flow value is greater than the main pipeline flow setpoint. If the actual outlet flow value is greater than the main pipeline flow setpoint, control ends; if the actual outlet flow value is not greater than the main pipeline flow setpoint, the opening of the two-way valve in the main pipeline is decreased by 0.5%. If the absolute value of the difference is greater than 0.51pm, it is determined whether the actual outlet flow rate is less than the main pipeline flow rate setpoint. If it is determined that the actual outlet flow rate is less than the main pipeline flow rate setpoint, the circulation pump speed is increased by 2%. If it is determined that the actual outlet flow rate is not less than the main pipeline flow rate setpoint, the circulation pump speed is decreased by 2%. Furthermore, after each control operation, it is further determined whether the actual outlet flow rate is equal to the main pipeline flow rate setpoint. If yes, the control ends; otherwise, the absolute value of the difference between the main pipeline flow rate setpoint and the actual outlet flow rate is compared again with the setpoint 0.51pm. 0.51pm is a value calculated based on experience and can be set and adjusted according to actual conditions.

[0114] See Figure 7 , Figure 7This is a flowchart illustrating the implementation of branch working fluid phase change rate control in an embodiment of the present invention. During the process of controlling the working fluid phase change rate in a system branch, a phase change rate setpoint is obtained, and the actual phase change rate of the branch is obtained. It is then determined whether the absolute value of the difference between the actual phase change rate and the setpoint is less than 5%. If the absolute value of the difference is less than or equal to 5%, it is further determined whether the actual phase change rate of the branch is greater than the setpoint. If the actual phase change rate of the branch is greater than the setpoint, the opening of the two-way valve in that branch is increased by 0.5%. If the actual phase change rate of the branch is not greater than the setpoint, it is determined whether the actual phase change rate is less than the setpoint. If the actual phase change rate is less than the setpoint, control ends. If the actual phase change rate is not less than the setpoint, the opening of the two-way valve in that branch is decreased by 0.5%. If the absolute value of the difference is greater than 5%, it is determined whether the actual value of the branch phase change rate is greater than the set value. If it is determined that the actual value of the branch phase change rate is greater than the set value, the circulation pump speed is increased by 2%. If it is determined that the actual value of the branch phase change rate is not greater than the set value, the circulation pump speed is decreased by 2%. Furthermore, after each control operation, it is further determined whether the actual value of the branch phase change rate is equal to the set value. If yes, the control ends; otherwise, the absolute value of the difference between the set value and the actual value of the branch phase change rate is compared again with the set value of 5%. 5% is a value calculated based on experience and can be set and adjusted according to actual conditions.

[0115] See Figure 8 , Figure 8 This is a flowchart illustrating another implementation method for a two-phase cold plate liquid cooling system in an embodiment of the present invention. The method may include the following steps:

[0116] S801: Obtain the phase change temperature type of the working fluid in a two-phase cold plate liquid cooling system.

[0117] S802: When the working fluid phase change temperature type is a fixed value, the phase change rate of the working fluid in each branch is controlled to a preset value by controlling the flow rate of the system.

[0118] S803: When the phase change temperature type of the working fluid is a range value, obtain the specific heat capacity of the coolant and the latent heat coefficient of the working fluid phase change.

[0119] When the phase change temperature type of the working fluid is within a range, obtain the specific heat capacity of the coolant and the latent heat coefficient of the working fluid phase change L.

[0120] S804: Obtain the current working fluid phase transition rate for each branch.

[0121] The phase transition rate of the working fluid in each branch is a change value, and the current phase transition rate of the working fluid in each branch is obtained.

[0122] S805: Select branches from the branches whose current working fluid phase change rate is inconsistent with the preset value.

[0123] After obtaining the current working fluid phase change rate of each branch, the current working fluid phase change rate of each branch is compared with the preset value, and the branches whose current working fluid phase change rate is inconsistent with the preset value are selected.

[0124] S806: Obtain the branch inlet temperature, branch outlet temperature, branch inlet pressure, branch outlet pressure, equipment power consumption of the branch, and the current working fluid phase change temperature of the branch for each selected branch.

[0125] After filtering out branches where the current working fluid phase change rate is inconsistent with the preset value, the branch inlet temperature T0, branch outlet temperature Tn, branch inlet pressure Pn1, branch outlet pressure Pn2, branch equipment power consumption Qn, and current working fluid phase change temperature T1 of each filtered branch are obtained.

[0126] S807: The enthalpy of the working fluid at the inlet of each branch is calculated based on the branch inlet temperature and branch inlet pressure.

[0127] After obtaining the inlet temperature T0 and inlet pressure Pn1 of each selected branch, the enthalpy Hn1 of the working fluid at the inlet of each selected branch is calculated based on the inlet temperature T0 and inlet pressure Pn1. The enthalpy Hn1 of the working fluid at the inlet of each selected branch can be calculated using the formula: H = f1(P,T), where f1(.) represents the function relating pipeline temperature, pressure, and enthalpy of the working fluid.

[0128] S808: Read the actual branch monitoring flow from the branch flowmeter of each selected branch.

[0129] Each branch is pre-set with a flow meter for flow monitoring. After filtering out branches where the current working fluid phase change rate is inconsistent with the preset value, the actual branch monitoring flow m in the branch flow meter of each filtered branch is read.

[0130] S809: Calculate the target branch flow value for each selected branch based on the specific heat capacity, latent heat coefficient of the working fluid phase change, current working fluid phase change temperature, inlet temperature of each branch, power consumption of each device, and actual branch monitoring flow.

[0131] After obtaining the specific heat capacity of the coolant and the latent heat coefficient of the working fluid phase change, as well as the current working fluid phase change temperature, the inlet temperature of each branch, the power consumption of each device, and the actual monitored flow rate of each branch, the target branch flow rate value of each selected branch is calculated. The calculation formula can be: Fn=(Qn-cm(T1-T0)) / 0.6 / L.

[0132] S810: Calculate the enthalpy of the working fluid at the inlet of each selected branch, the power consumption of the equipment, and the flow rate of the target branch.

[0133] After calculating the target branch flow value Fn for each selected branch, the branch outlet enthalpy value Hn2 for each selected branch is calculated based on the branch inlet working fluid enthalpy Hn1, equipment power consumption Qn, and target branch flow value Fn. The calculation formula is: Hn2=Hn1+Qn / Fn.

[0134] S811: Calculate the target working fluid phase change rate for each selected branch based on the enthalpy and pressure of the working fluid at the branch outlet.

[0135] After calculating the enthalpy Hn2 of the working fluid at the outlet of each selected branch, the target phase change rate of the working fluid for each selected branch is calculated based on the enthalpy Hn2 and the outlet pressure Pn2. The target phase change rate x of the selected branch can be calculated using the formula: x = f2(Hn2, Pn2), where f2(.) represents the function relating the outlet enthalpy, outlet pressure, and phase change rate of the working fluid.

[0136] S812: Calculate the second error and the second error change rate between the current working fluid phase change rate and the target working fluid phase change rate for each selected branch.

[0137] After calculating the target working fluid phase change rate for each selected branch, the second error and the second error change rate between the current working fluid phase change rate and the target working fluid phase change rate for each selected branch are calculated respectively.

[0138] S813: Input the second error and the rate of change of the second error into the fuzzy controller, and use the fuzzy controller to perform proportional-integral-derivative control to obtain the change of the second proportional adjustment coefficient, the change of the second integral adjustment coefficient, and the change of the second derivative adjustment coefficient.

[0139] After calculating the second error and the second error change rate between the current working fluid phase change rate and the target working fluid phase change rate for each selected branch, the second error and the second error change rate are input to the fuzzy controller. The fuzzy controller is then used for proportional-integral-derivative control to obtain the change in the second proportional adjustment coefficient, the change in the second integral adjustment coefficient, and the change in the second derivative adjustment coefficient.

[0140] S814: Adjust the valve opening of each branch according to the changes in the second proportional adjustment coefficient, the second integral adjustment coefficient, and the second derivative adjustment coefficient corresponding to each selected branch.

[0141] After calculating the changes in the second proportional adjustment coefficient, the second integral adjustment coefficient, and the second derivative adjustment coefficient, the valve opening of each branch is adjusted according to the changes in the second proportional adjustment coefficient, the second integral adjustment coefficient, and the second derivative adjustment coefficient corresponding to each selected branch.

[0142] S815: Obtain the current working fluid phase change rate of each branch in the system.

[0143] After adjusting the valve opening of each branch according to the changes in the second proportional adjustment coefficient, the second integral adjustment coefficient, and the second derivative adjustment coefficient corresponding to each selected branch, the current working fluid phase change rate of each branch in the system is obtained.

[0144] S816: Determine if there is a branch where the current working fluid phase change rate is inconsistent with the preset value. If yes, return to step S805; otherwise, end the control flow.

[0145] After obtaining the current working fluid phase change rate of each branch in the system, it is determined whether there are any branches whose current working fluid phase change rate is inconsistent with the preset value. If so, it means that the working fluid phase change rate of the branch with inconsistent working fluid phase change rate needs to be further adjusted. Then, the branches with inconsistent working fluid phase change rate are selected from each branch again for further working fluid phase change rate adjustment. If not, it means that the working fluid phase change rate of each branch has reached the optimal value and each branch is in the state of optimal heat exchange efficiency, and the control process ends.

[0146] By adjusting the valve opening of each branch according to the working fluid phase change rate when the working fluid phase change temperature is within a range, the optimal value of the working fluid phase change rate in each branch is achieved by using a fuzzy controller. Through fuzzy adaptive proportional-integral-derivative control, the control system exhibits better dynamic response performance under sudden load changes.

[0147] The parameter values ​​obtained when the working fluid phase change temperature type is a range value and the parameter values ​​of the same type obtained when the working fluid phase change temperature type is a fixed value can be distinguished by the first and second methods. This embodiment of the invention does not limit this.

[0148] In one specific embodiment of the present invention, the method may further include the following steps:

[0149] When there is a branch where the working fluid phase change rate adjustment time exceeds the preset time and the current working fluid phase change rate after adjustment exceeds the preset phase change rate threshold range, an alarm message is output.

[0150] When a branch has a working fluid phase change rate adjustment time exceeding a preset time and the adjusted current working fluid phase change rate exceeds a preset phase change rate threshold range, an alarm message is output. By issuing alarms for branches whose adjustment time exceeds the preset time and whose adjusted current working fluid phase change rate exceeds the preset phase change rate threshold range, maintenance personnel can be promptly notified to perform maintenance, thus improving system security.

[0151] It should be noted that the preset duration can be set and adjusted according to the actual situation. This embodiment of the invention does not limit this, such as it can be set to 20 seconds.

[0152] It should also be noted that the preset phase transition rate threshold range can be set and adjusted according to the actual situation. This embodiment of the invention does not limit this, such as it can be set to 40%-80%.

[0153] Corresponding to the above method embodiments, the present invention also provides a control device for a two-phase cold plate liquid cooling system. The control device for a two-phase cold plate liquid cooling system described below and the control method for a two-phase cold plate liquid cooling system described above can be referred to in correspondence with each other.

[0154] See Figure 9 , Figure 9 This is a structural block diagram of a two-phase cold plate liquid cooling system control device according to an embodiment of the present invention. The device may include:

[0155] The working fluid phase change temperature type acquisition module 91 is used to acquire the working fluid phase change temperature type of the coolant in a two-phase cold plate liquid cooling system.

[0156] The system flow control module 92 is used to control the phase change rate of the working fluid in each branch to a preset value by controlling the system flow when the working fluid phase change temperature type is a fixed value.

[0157] The branch phase change rate control module 93 is used to control the phase change rate of the working fluid in each branch to a preset value when the phase change temperature type of the working fluid is a range value.

[0158] As can be seen from the above technical solution, by pre-setting the preset value of the working fluid phase change rate of each branch to optimize the heat exchange efficiency, the phase change temperature type of the coolant in the two-phase cold plate liquid cooling system is obtained. When the working fluid phase change temperature type is a constant value, the system flow rate is controlled to bring the working fluid phase change rate of each branch to the preset value. When the working fluid phase change temperature type is within a range, the phase change rate of each branch is controlled to bring the working fluid phase change rate of each branch to the preset value. By selecting a control scheme that matches the working fluid phase change temperature type from two control schemes—system flow control and branch phase change rate control—the phase change rate of each branch is kept at the value with the highest heat exchange efficiency. This results in better dynamic response performance of the control system under sudden load changes. By monitoring the phase change rate of each branch in real time, the probability of abnormal situations such as working fluid burning out or no phase change is significantly reduced. This improves the robustness of the control system and enhances system performance. The control process is automated, saving manpower.

[0159] In one specific embodiment of the present invention, the system flow control module is specifically a module that, when the working fluid phase change temperature type is a fixed value and the power consumption change ratio of each branch is consistent, adjusts the main pipeline pump speed and the main pipeline valve opening to adjust the main pipeline output flow and control the working fluid phase change rate of each branch to a preset value.

[0160] In one specific embodiment of the present invention, the system flow control module is specifically a module that, when the working fluid phase change temperature type is a fixed value and the power consumption change ratio of each branch is inconsistent, adjusts the valve opening of each branch to adjust the flow rate of each branch and controls the working fluid phase change rate of each branch to a preset value.

[0161] In one specific embodiment of the present invention, the system flow control module includes:

[0162] The first fixed parameter acquisition submodule is used to acquire the specific heat capacity of the coolant, the latent heat coefficient of the working fluid phase change, and the working fluid phase change temperature.

[0163] The first branch filtering submodule is used to obtain the current working fluid phase change rate of each branch and filter out the branches whose current working fluid phase change rate is inconsistent with the preset value.

[0164] The first device power consumption acquisition submodule is used to acquire the device power consumption of each filtered branch.

[0165] The first flow reading submodule is used to read the actual branch monitoring flow from the branch flow meters of each selected branch;

[0166] The first branch inlet temperature acquisition submodule is used to acquire the branch inlet temperature of each filtered branch.

[0167] The first target branch flow value calculation submodule is used to calculate the target branch flow value of each selected branch based on the specific heat capacity, latent heat coefficient of working fluid phase change, working fluid phase change temperature, inlet temperature of each branch, power consumption of each device and actual monitored flow of each branch.

[0168] The first error and error change rate calculation submodule is used to calculate the first error and the first error change rate between the actual branch monitoring flow and the target branch flow value for each selected branch.

[0169] The first proportional-integral-derivative control submodule is used to input the first error and the first error change rate to the fuzzy controller, and use the fuzzy controller to perform proportional-integral-derivative control to obtain the change of the first proportional adjustment coefficient, the change of the first integral adjustment coefficient and the change of the first derivative adjustment coefficient.

[0170] The first branch valve opening adjustment submodule is used to adjust the valve opening of each branch according to the changes in the first proportional adjustment coefficient, the first integral adjustment coefficient, and the first derivative adjustment coefficient corresponding to each selected branch.

[0171] The first working fluid phase transition rate acquisition submodule is used to acquire the current working fluid phase transition rate of each branch in the system.

[0172] The first working fluid phase change rate control submodule is used to repeatedly execute the step of filtering out each branch whose current working fluid phase change rate is inconsistent with the preset value when it is determined that there is a branch whose current working fluid phase change rate is inconsistent with the preset value, until the working fluid phase change rate of each branch in the system is controlled to the preset value.

[0173] In one specific embodiment of the present invention, the first proportional-integral-derivative control submodule is specifically a module that uses a fuzzy controller to perform proportional-integral-derivative control on the opening degree of each branch valve through a fuzzy control algorithm, and obtains the change amount of the first proportional adjustment coefficient, the change amount of the first integral adjustment coefficient, and the change amount of the first derivative adjustment coefficient corresponding to the opening degree of each branch valve.

[0174] In one specific embodiment of the present invention, the branch phase transition rate control module includes:

[0175] The second fixed parameter acquisition submodule is used to obtain the specific heat capacity of the coolant and the latent heat coefficient of the working fluid phase change.

[0176] The second branch filtering submodule is used to obtain the current working fluid phase change rate of each branch and filter out the branches whose current working fluid phase change rate is inconsistent with the preset value.

[0177] The variable parameter acquisition submodule is used to acquire the branch inlet temperature, branch outlet temperature, branch inlet pressure, branch outlet pressure, equipment power consumption of the branch, and the current working fluid phase change temperature of the branch for each filtered branch.

[0178] The branch inlet working fluid enthalpy calculation submodule is used to calculate the branch inlet working fluid enthalpy of each selected branch based on the branch inlet temperature and branch inlet pressure.

[0179] The second flow reading submodule is used to read the actual branch monitoring flow from the branch flow meters of each selected branch;

[0180] The branch outlet working fluid enthalpy calculation submodule is used to calculate the branch outlet working fluid enthalpy of each selected branch based on the branch inlet working fluid enthalpy, equipment power consumption and target branch flow rate.

[0181] The target working fluid phase change rate calculation submodule is used to calculate the target working fluid phase change rate of each selected branch based on the branch outlet enthalpy and branch outlet pressure of each selected branch.

[0182] The second error and error change rate calculation submodule is used to calculate the second error and the second error change rate between the current working fluid phase change rate and the target working fluid phase change rate for each selected branch.

[0183] The second proportional-integral-derivative control submodule is used to input the second error and the rate of change of the second error into the fuzzy controller, and use the fuzzy controller to perform proportional-integral-derivative control to obtain the change of the second proportional adjustment coefficient, the change of the second integral adjustment coefficient, and the change of the second derivative adjustment coefficient.

[0184] The second branch valve opening adjustment submodule is used to adjust the valve opening of each branch according to the changes in the second proportional adjustment coefficient, the second integral adjustment coefficient, and the second derivative adjustment coefficient corresponding to each selected branch.

[0185] The second working fluid phase change rate acquisition submodule is used to acquire the current working fluid phase change rate of each branch in the system.

[0186] The second working fluid phase change rate control submodule is used to repeatedly execute the step of filtering out branches whose current working fluid phase change rate is inconsistent with the preset value when it is determined that there are branches whose current working fluid phase change rate is inconsistent with the preset value, until the working fluid phase change rate of each branch in the system is controlled to the preset value.

[0187] In one specific embodiment of the present invention, the device may further include:

[0188] The alarm message output module is used to output alarm messages when there is a branch where the working fluid phase change rate adjustment time exceeds the preset time and the current working fluid phase change rate after adjustment exceeds the preset phase change rate threshold range.

[0189] For the method embodiments described above, see [link to relevant documentation]. Figure 10 , Figure 10 This is a schematic diagram of the control device for a two-phase cold plate liquid cooling system provided by the present invention. The device may include:

[0190] Memory 332 is used to store computer programs;

[0191] The processor 322 is used to execute a computer program to implement the steps of the two-phase cold plate liquid cooling system control method of the above method embodiment.

[0192] For details, please refer to Figure 11 , Figure 11 This is a schematic diagram illustrating the specific structure of a two-phase cold plate liquid cooling system control device provided in this embodiment. The two-phase cold plate liquid cooling system control device can vary significantly due to different configurations or performance characteristics. It may include a processor (central processing unit, CPU) 322 (e.g., one or more processors) and a memory 332. The memory 332 stores one or more computer programs 342 or data 344. The memory 332 can be temporary or permanent storage. The program stored in the memory 332 may include one or more modules (not shown in the diagram), each module may include a series of instruction operations on the data processing device. Furthermore, the processor 322 may be configured to communicate with the memory 332 and execute the series of instruction operations stored in the memory 332 on the two-phase cold plate liquid cooling system control device 301.

[0193] The two-phase cold plate liquid cooling system control device 301 may also include one or more power supplies 326, one or more wired or wireless network interfaces 350, one or more input / output interfaces 358, and / or one or more operating systems 341.

[0194] The steps in the control method for the two-phase cold plate liquid cooling system described above can be implemented by the structure of the two-phase cold plate liquid cooling system control equipment.

[0195] Corresponding to the above method embodiments, the present invention also provides a computer-readable storage medium storing a computer program, which, when executed by a processor, can perform the following steps:

[0196] The phase change temperature type of the working fluid in the two-phase cold plate liquid cooling system is obtained; when the working fluid phase change temperature type is a fixed value, the phase change rate of the working fluid in each branch is controlled to a preset value by controlling the flow rate of the system; when the working fluid phase change temperature type is a range value, the phase change rate of the working fluid in each branch is controlled to a preset value by controlling the phase change rate of each branch.

[0197] The computer-readable storage medium may include various media capable of storing program code, such as USB flash drives, portable hard drives, read-only memory (ROM), random access memory (RAM), magnetic disks, or optical disks.

[0198] For a description of the computer-readable storage medium provided by the present invention, please refer to the above method embodiments; the present invention will not be described in detail here.

[0199] Corresponding to the above method embodiments, the present invention also provides a computer program product, including a computer program that, when executed by a processor, implements the steps of the control method for the two-phase cold plate liquid cooling system as described above.

[0200] The various embodiments in this specification are described in a progressive manner, with each embodiment focusing on its differences from other embodiments. Similar or identical parts between embodiments can be referred to interchangeably. For the apparatuses, devices, and computer-readable storage media disclosed in the embodiments, since they correspond to the methods disclosed in the embodiments, the descriptions are relatively simple; relevant parts can be referred to the method section.

[0201] This article uses specific examples to illustrate the principles and implementation methods of the present invention. The descriptions of the above embodiments are only for the purpose of helping to understand the technical solutions and core ideas of the present invention. It should be noted that for those skilled in the art, several improvements and modifications can be made to the present invention without departing from the principles of the present invention, and these improvements and modifications also fall within the protection scope of the present invention.

Claims

1. A two-phase cold plate liquid cooling system control method, characterized by, include: To obtain the phase change temperature type of the working fluid in a two-phase cold plate liquid cooling system; When the working fluid phase change temperature type is a fixed value, the phase change rate of the working fluid in each branch is controlled to a preset value by controlling the flow rate of the system. When the working fluid phase change temperature type is a range value, the working fluid phase change rate of each branch is controlled to the preset value by controlling the phase change rate of each branch. Among them, controlling the phase change rate of the working fluid in each branch to the preset value by controlling the phase change rate of each branch includes: The specific heat capacity and latent heat coefficient of the working fluid phase change are obtained; Obtain the current working fluid phase change rate for each branch, and then filter out the branches whose current working fluid phase change rate is inconsistent with the preset value. Obtain the branch inlet temperature, branch outlet temperature, branch inlet pressure, branch outlet pressure, equipment power consumption of the branch, and the current working fluid phase change temperature of the branch for each filtered branch. The enthalpy of the working fluid at the inlet of each selected branch is calculated based on the branch inlet temperature and the branch inlet pressure. Read the actual branch monitoring flow from the branch flow meter of each selected branch; Based on the specific heat capacity, the latent heat coefficient of the working fluid phase change, the current working fluid phase change temperature, the inlet temperature of each branch, the power consumption of each device, and the actual monitored flow rate of each branch, the target branch flow rate value of each selected branch is calculated respectively. Based on the enthalpy of the working fluid at the inlet of each selected branch, the power consumption of the equipment, and the flow rate of the target branch, calculate the enthalpy of the working fluid at the outlet of each selected branch. The target working fluid phase change rate of each selected branch is calculated based on the enthalpy value and pressure of the working fluid at the branch outlet. Calculate the second error and the rate of change of the second error between the current working fluid phase change rate and the target working fluid phase change rate for each selected branch; The second error and the rate of change of the second error are input to the fuzzy controller, and proportional-integral-derivative control is performed using the fuzzy controller to obtain the change of the second proportional adjustment coefficient, the change of the second integral adjustment coefficient, and the change of the second derivative adjustment coefficient. Adjust the valve opening of each branch according to the changes in the second proportional adjustment coefficient, the second integral adjustment coefficient, and the second derivative adjustment coefficient corresponding to each selected branch. Obtain the current working fluid phase change rate for each branch in the system; When it is determined that there is a branch whose current working fluid phase change rate is inconsistent with the preset value, the step of filtering out the branches whose current working fluid phase change rate is inconsistent with the preset value is repeated until the working fluid phase change rate of each branch in the system is controlled to the preset value.

2. The two-phase cold plate liquid cooling system control method of claim 1, wherein, When the working fluid phase change temperature type is a fixed value, the phase change rate of the working fluid in each branch is controlled to a preset value by controlling the flow rate of the system, including: When the working fluid phase change temperature type is a fixed value and the power consumption change ratio of each branch is consistent, the working fluid phase change rate of each branch is controlled to the preset value by adjusting the pump speed of the main pipeline and the valve opening of the main pipeline to adjust the output flow of the main pipeline.

3. The two-phase cold plate liquid cooling system control method of claim 1, wherein, When the working fluid phase change temperature type is a fixed value, the phase change rate of the working fluid in each branch is controlled to a preset value by controlling the flow rate of the system, including: When the phase change temperature type of the working medium is a constant value and the power consumption variation ratios of the branches are inconsistent, the phase change rates of the working medium in the branches are controlled to the preset value by adjusting the branch valve openings to adjust the branch flow rates.

4. The two-phase cold plate liquid cooling system control method of claim 3, wherein, The phase change rates of the working medium in the branches are controlled to the preset value by adjusting the branch valve openings to adjust the branch flow rates, including: obtaining the specific heat capacity of the cooling liquid, the latent heat coefficient of phase change of the working medium, and the phase change temperature of the working medium; obtaining the current phase change rates of the branches respectively, and screening the branches whose current phase change rates are inconsistent with the preset value from the branches; obtaining the device power consumptions of the screened branches respectively; reading the actual branch monitoring flow rates in the branch flow meters of the screened branches respectively; obtaining the branch inlet temperatures of the screened branches; calculating the target branch flow rate values of the screened branches respectively according to the specific heat capacity, the latent heat coefficient of phase change of the working medium, the phase change temperature of the working medium, the branch inlet temperatures, the device power consumptions, and the actual branch monitoring flow rates; calculating the first errors and the first error variation rates between the actual branch monitoring flow rates and the target branch flow rate values corresponding to the screened branches respectively; inputting the first errors and the first error variation rates into a fuzzy controller, and performing proportional-integral-derivative control by using the fuzzy controller to obtain a first proportional adjustment coefficient variation, a first integral adjustment coefficient variation, and a first derivative adjustment coefficient variation; adjusting the branch valve openings according to the first proportional adjustment coefficient variations, the first integral adjustment coefficient variations, and the first derivative adjustment coefficient variations corresponding to the screened branches respectively; obtaining the current phase change rates of the branches in the system respectively; when it is determined that there is a branch whose current phase change rate is inconsistent with the preset value, repeatedly performing the step of screening the branches whose current phase change rates are inconsistent with the preset value from the branches until the phase change rates of the working medium in the branches in the system are all controlled to the preset value.

5. The two-phase cold plate liquid cooling system control method of claim 4, wherein, The proportional-integral-derivative control by using the fuzzy controller obtains a first proportional adjustment coefficient variation, a first integral adjustment coefficient variation, and a first derivative adjustment coefficient variation, including: The proportional-integral-derivative control by using the fuzzy controller on the branch valve openings by a fuzzy control algorithm obtains a first proportional adjustment coefficient variation, a first integral adjustment coefficient variation, and a first derivative adjustment coefficient variation corresponding to the branch valve openings respectively.

6. The two-phase cold plate liquid cooling system control method of claim 1, wherein, Further including: when there is a branch whose phase change rate adjustment duration exceeds a preset duration and whose adjusted current phase change rate exceeds a preset phase change rate threshold range, outputting an alarm prompt information.

7. A two-phase cold plate liquid cooling system control device, characterized by, including: a working medium phase change temperature type acquisition module configured to acquire a working medium phase change temperature type of a cooling liquid in a two-phase cold plate liquid cooling system; a system flow control module configured to control the phase change rates of the working medium in the branches to a preset value by controlling a system flow rate when the phase change temperature type of the working medium is a constant value; a branch phase change rate control module configured to control the phase change rates of the working medium in the branches to the preset value by controlling the phase change rates of the branches when the phase change temperature type of the working medium is a range value; the branch phase change rate control module includes: The second constant parameter obtaining submodule is configured to obtain the specific heat capacity of the cooling liquid and the latent heat coefficient of the working medium phase change. The second branch screening submodule is configured to obtain the current working medium phase change rate of each branch respectively, and screen each branch with the current working medium phase change rate inconsistent with the preset value from the branches. The variable parameter obtaining submodule is configured to obtain the branch inlet temperature, the branch outlet temperature, the branch inlet pressure, the branch outlet pressure, the equipment power consumption of the screened branches, and the current working medium phase change temperature of the screened branches. The branch inlet working medium enthalpy value calculating submodule is configured to calculate the branch inlet working medium enthalpy value of the screened branches according to the branch inlet temperature and the branch inlet pressure. The second flow reading submodule is configured to read the actual branch monitoring flow in the branch flow meter of each screened branch respectively. The branch outlet working medium enthalpy value calculating submodule is configured to calculate the branch outlet working medium enthalpy value of the screened branches according to the branch inlet working medium enthalpy value, the equipment power consumption, and the target branch flow value of the screened branches. The target working medium phase change rate calculating submodule is configured to calculate the target working medium phase change rate of the screened branches according to the branch outlet working medium enthalpy value and the branch outlet pressure of the screened branches. The second error and error change rate calculating submodule is configured to calculate the second error and the second error change rate between the current working medium phase change rate and the target working medium phase change rate corresponding to each screened branch respectively. The second proportional-integral-derivative control submodule is configured to input the second error and the second error change rate into a fuzzy controller, and perform proportional-integral-derivative control by using the fuzzy controller to obtain the second proportional adjustment coefficient change, the second integral adjustment coefficient change, and the second differential adjustment coefficient change. The second branch valve opening degree adjusting submodule is configured to adjust the valve opening degree of each branch according to the second proportional adjustment coefficient change, the second integral adjustment coefficient change, and the second differential adjustment coefficient change corresponding to each screened branch respectively. The second working medium phase change rate obtaining submodule is configured to obtain the current working medium phase change rate of each branch in the system respectively. The second working medium phase change rate control submodule is configured to repeatedly perform the step of screening each branch with the current working medium phase change rate inconsistent with the preset value from the branches until the working medium phase change rates of the branches in the system are controlled to the preset value when it is determined that there is a branch with the current working medium phase change rate inconsistent with the preset value.

8. A two-phase cold plate liquid cooling system control device, characterized by, The computer readable storage medium stores a computer program, and the computer program is executed by the processor to implement the steps of the two-phase cold plate liquid cooling system control method according to any one of claims 1 to 6. The computer readable storage medium stores a computer program, and the computer program is executed by the processor to implement the steps of the two-phase cold plate liquid cooling system control method according to any one of claims 1 to 6. ​ 9. A computer-readable storage medium, characterized in that, ​

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