Two-phase cold plate type liquid cooling system control method, device and equipment

Abstract

The invention discloses a control method of a two-phase cold plate type liquid cooling system. The control method comprises the following steps: acquiring a working medium phase change temperature type of cooling liquid in the two-phase cold plate type liquid cooling system; when the working medium phase change temperature type is a fixed value, the working medium phase change rate of each branch is controlled to be a preset value by controlling the system flow; and when the working medium phase change temperature type is a range value, the working medium phase change rate of each branch is controlled to be a preset value by controlling the phase change rate of each branch. By applying the two-phase cold plate type liquid cooling system control method provided by the invention, the robustness of the control system is improved, the system performance is improved, and manpower is saved. The invention 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] The present invention relates to the field of liquid cooling technology, and in particular to a two-phase cold plate liquid cooling system control method, device, equipment and computer-readable storage medium. Background Art

[0002] As chip power consumption increases exponentially, two-phase cold plate liquid cooling uses the latent heat of liquid phase change to carry away heat. It has extremely high heat dissipation efficiency and better temperature uniformity. It is an important direction for solving the heat dissipation of high heat flux density chips in the future.

[0003] However, in the cold plate liquid cooling system, there are often multiple liquid cooling nodes in parallel. When using a two-phase cold plate liquid cooling system, it is difficult to distribute the flow of multiple parallel branches, because the branches have different heat loads, which will cause the phase change boiling effect of the branch with a large heat load to be stronger, the flow resistance to increase, and the flow of the branch to decrease, resulting in temperature curve oscillation, which greatly reduces the robustness of the control system. And it can only be identified and manually processed after a branch has deteriorated, which affects the system performance and greatly wastes manpower.

[0004] In summary, how to effectively solve the problems of low robustness of the control system, affecting system performance, wasting manpower, etc. in the current two-phase cold plate liquid cooling system control method is an urgent problem that technicians in this field need to solve. Summary of the invention

[0005] An object of the present invention is to provide a two-phase cold plate liquid cooling system control method, which improves the robustness of the control system, improves system performance, and saves manpower; another object of the present invention is to provide a two-phase cold plate liquid cooling system control device, equipment and computer-readable storage medium.

[0006] In order to solve the above technical problems, the present invention provides the following technical solutions:

[0007] A two-phase cold plate liquid cooling system control method, comprising:

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

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

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

[0011] In a specific embodiment of the present invention, when the working medium phase change temperature type is a fixed value, the phase change rate of the working medium in each branch is controlled to a preset value by controlling the system flow, 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 main line pump speed and the main line valve opening to adjust the main line output flow.

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

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

[0015] In a specific embodiment of the present invention, the phase change rate of the working medium in each branch is controlled to the preset value by adjusting the opening of each branch valve to adjust the flow rate of each branch, including:

[0016] Obtaining the specific heat capacity of the coolant, the working fluid phase change latent heat coefficient and the working fluid phase change temperature;

[0017] The current working fluid phase change rate of each branch is obtained respectively, and the branches whose current working fluid phase change rate is inconsistent with the preset value are selected from the branches;

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

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

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

[0021] Calculate the target branch flow value of each selected branch according to the specific heat capacity, the working fluid phase change latent heat coefficient, the working fluid phase change temperature, the inlet temperature of each branch, the power consumption of each device and the actual branch monitoring flow;

[0022] Calculate the first error and the first error change rate between the actual branch monitoring flow and the target branch flow value corresponding to each screened branch respectively;

[0023] Inputting the first error and the first error change rate into a fuzzy controller, and using the fuzzy controller to perform proportional-integral-differential control to obtain a first proportional adjustment coefficient change, a first integral adjustment coefficient change, and a first differential adjustment coefficient change;

[0024] Adjust the opening of each branch valve according to the first proportional adjustment coefficient change, the first integral adjustment coefficient change and the first differential adjustment coefficient change corresponding to each branch respectively selected;

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

[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 screening out branches whose current working fluid phase change rate is inconsistent with the preset value from each branch is repeated until the working fluid phase change rate of each branch in the system is controlled to the preset value.

[0027] In a specific implementation of the present invention, the fuzzy controller is used to perform proportional-integral-differential control to obtain a first proportional adjustment coefficient change, a first integral adjustment coefficient change, and a first differential adjustment coefficient change, including:

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

[0029] In a specific embodiment of the present invention, controlling the phase change rate of each branch working medium to the preset value by controlling the phase change rate of each branch includes:

[0030] Obtaining the specific heat capacity of the coolant and the latent heat coefficient of phase change of the working fluid;

[0031] The current working fluid phase change rate of each branch is obtained respectively, and the branches whose current working fluid phase change rate is inconsistent with the preset value are selected from the branches;

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

[0033] Calculating the branch inlet working fluid enthalpy of each branch selected according to the branch inlet temperature and the branch inlet pressure;

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

[0035] Calculate the target branch flow value of each selected branch according to the specific heat capacity, the working fluid phase change latent heat coefficient, the current working fluid phase change temperature, the inlet temperature of each branch, the power consumption of each device and the actual branch monitoring flow;

[0036] Calculate the working fluid enthalpy value at the branch outlet of each screened branch according to the branch inlet working fluid enthalpy value of each screened branch, the equipment power consumption and the target branch flow value;

[0037] Calculating the target working fluid phase change rate of each screened branch according to the branch outlet working fluid enthalpy value and branch outlet pressure of each screened branch;

[0038] Calculating respectively 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 corresponding to each of the screened branches;

[0039] Inputting the second error and the second error change rate into a fuzzy controller, and using the fuzzy controller to perform proportional-integral-differential control to obtain a second proportional adjustment coefficient change, a second integral adjustment coefficient change, and a second differential adjustment coefficient change;

[0040] Adjust the opening of each branch valve according to the second proportional adjustment coefficient change, the second integral adjustment coefficient change and the second differential adjustment coefficient change corresponding to each branch respectively selected;

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

[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 screening out branches whose current working fluid phase change rate is inconsistent with the preset value from each branch is repeated until the working fluid phase change rate of each branch in the system is controlled to the preset value.

[0043] In a specific embodiment of the present invention, it also includes:

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

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

[0046] A working fluid phase change temperature type acquisition module is used to obtain the working fluid phase change temperature type of the coolant in the two-phase cold plate liquid cooling system;

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

[0049] A two-phase cold plate liquid cooling system control device, comprising:

[0050] Memory for storing computer programs;

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

[0052] A computer-readable storage medium stores a computer program, and when the computer program is executed by a processor, the steps of the two-phase cold plate liquid cooling system control method as described above are implemented.

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

[0054] It can be seen from the above technical scheme that by presetting the preset value of the phase change rate of the branch working fluid that makes the heat exchange efficiency of each branch optimal, the working fluid 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 working fluid is controlled to the preset value by controlling the system flow. When the working fluid phase change temperature type is a range value, the phase change rate of each branch working fluid 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 the two control schemes of system flow control and each branch phase change rate control, the phase change rate of each branch is at the value with the highest heat exchange efficiency. The control system has better dynamic response performance under load mutation. By real-time monitoring of the phase change rate of each branch, the probability of branch working fluid drying or no phase change abnormality is greatly reduced. The robustness of the control system is improved, and the system performance is improved. The control process is completed automatically, saving manpower.

[0055] Correspondingly, 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 has the above-mentioned technical effects and will not be repeated here. BRIEF DESCRIPTION OF THE DRAWINGS

[0056] In order to more clearly illustrate the technical solutions in the embodiments of the present invention or related technologies, the drawings required for use in the embodiments or related technical descriptions are briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying creative work.

[0057] FIG1 is a flow chart of a control method for a two-phase cold plate liquid cooling system according to an embodiment of the present invention;

[0058] FIG2 is a flowchart of another implementation method of a two-phase cold plate liquid cooling system control method according to an embodiment of the present invention;

[0059] FIG3 is a control architecture diagram of a two-phase cold plate liquid cooling system according to an embodiment of the present invention;

[0060] FIG4 is a structural block diagram of a two-phase cold plate liquid cooling system according to an embodiment of the present invention;

[0061] FIG5 is a schematic diagram of a fuzzy proportional-integral-differential control principle in an embodiment of the present invention;

[0062] FIG6 is a flow chart of a system flow control implementation in an embodiment of the present invention;

[0063] FIG7 is a flow chart of a branch working fluid phase change rate control implementation in an embodiment of the present invention;

[0064] FIG8 is a flowchart of another implementation method of a two-phase cold plate liquid cooling system control method in an embodiment of the present invention;

[0065] FIG9 is a structural block diagram of a two-phase cold plate liquid cooling system control device according to an embodiment of the present invention;

[0066] FIG10 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] FIG. 11 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 DESCRIPTION

[0068] In order to enable those skilled in the art to better understand the scheme of the present invention, the present invention is further described in detail below in conjunction with the accompanying drawings and specific implementation methods. Obviously, the described embodiments are only part of the embodiments of the present invention, rather than all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

[0069] Referring to FIG. 1 , FIG. 1 is a flow chart of a control 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: Obtaining a working fluid phase change temperature type of a coolant in a two-phase cold plate liquid cooling system.

[0071] The working fluid phase change temperature type of the coolant includes a type in which the working fluid phase change temperature is a fixed value and a type in which the working fluid phase change temperature is a range value. Get the working fluid phase change temperature type of the coolant in the 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 system flow.

[0073] After obtaining the working fluid phase change temperature type of the coolant in the two-phase cold plate liquid cooling system, when the working fluid phase change temperature type is a fixed value, the working fluid phase change rate of each branch is controlled to a preset value by controlling the system flow. For example, according to the heat exchange efficiency of the coolant at multiple working fluid phase change rates, the working fluid phase change rate with the highest heat exchange efficiency can be selected from the various heat exchange efficiencies as the branch working fluid phase change rate target value to be controlled for each branch, such as the preset value of the branch working fluid phase change rate can be set to 60%.

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

[0075] After obtaining the working fluid phase change temperature type of the coolant in the two-phase cold plate liquid cooling 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 a preset value by controlling the phase change rate of each branch. For example, the phase change rate of the working fluid in each branch is controlled by controlling the opening of the solenoid valve of each branch. By selecting a control scheme that matches the working fluid phase change temperature type from the two control schemes of system flow control and phase change rate control of each branch, 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, and at the same time, the phase change rate of each branch is detected in real time, and the phase change rate of the working fluid in each branch is controlled at the optimal value, thereby improving the heat exchange efficiency of each branch.

[0076] It can be seen from the above technical scheme that by presetting the preset value of the phase change rate of the branch working fluid that makes the heat exchange efficiency of each branch optimal, the working fluid 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 working fluid is controlled to the preset value by controlling the system flow. When the working fluid phase change temperature type is a range value, the phase change rate of each branch working fluid 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 the two control schemes of system flow control and each branch phase change rate control, the phase change rate of each branch is at the value with the highest heat exchange efficiency. The control system has better dynamic response performance under load mutation. By real-time monitoring of the phase change rate of each branch, the probability of branch working fluid drying or no phase change abnormality is greatly reduced. The robustness of the control system is improved and the system performance is improved. The control process is completed automatically, saving manpower.

[0077] It should be noted that, based on the above embodiment, the embodiment of the present invention also provides corresponding improved solutions. In the subsequent embodiments, the same steps or corresponding steps as those in the above embodiment can be referenced to each other, and the corresponding beneficial effects can also be referenced to each other, which will not be repeated one by one in the following improved embodiments.

[0078] Referring to FIG. 2 , FIG. 2 is a flowchart of another implementation method of a two-phase cold plate liquid cooling system control method in an embodiment of the present invention. The method may include the following steps:

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

[0080] See Figure 3, which is a control architecture diagram of a two-phase cold plate liquid cooling system in an embodiment of the present invention. The overall body may include a pump involved in regulation, a main line, a cooling branch node and a control system, a rack loading device, an alarm module, and a heat exchanger and a liquid storage tank, etc., which are the basis of the liquid cooling system.

[0081] Refer to Figure 4, which is a structural block diagram of a two-phase cold plate liquid cooling system in an embodiment of the present invention. The pump provides the system with power to circulate the coolant, and the output flow rate and head can be changed by adjusting the speed. A flow meter is installed on the main line to monitor the total flow of the system. A temperature sensor is also installed on the main line to monitor the inlet temperature of each branch. The main line is connected to the branch inlet and outlet through a manifold, and the coolant is distributed to each branch for cooling. Temperature and pressure sensors are arranged at the inlet and outlet of the branch to read the inlet and outlet working fluid parameters. Each branch inlet is equipped with a solenoid valve to adjust the flow rate through each branch by adjusting the valve opening. The heat exchanger is used to exchange heat and cool the coolant after phase change with the external primary side. It is re-condensed into an unsaturated liquid and returned to the liquid storage tank.

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

[0083] When the working fluid phase change temperature type is a fixed value and the power consumption change ratio of each branch is inconsistent, the flow of each branch is adjusted by adjusting the opening of each branch valve, so as to control the phase change rate of each branch working fluid to the preset value. When the working fluid phase change temperature type is a fixed value and the power consumption change ratio of each branch is inconsistent, the flow of each branch is adjusted by adjusting the opening of each branch valve, so as to achieve precise regulation of the flow of each branch.

[0084] In a specific embodiment of the present invention, the phase change rate of the working medium in each branch is controlled to a preset value by adjusting the opening of each branch valve to adjust the flow rate of each branch, which may include the following steps:

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

[0086] Step 2: respectively obtain the current working fluid phase change rate of each branch, and select the branches whose current working fluid phase change rate is inconsistent with the preset value from each branch;

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

[0088] Step 4: respectively read the actual branch monitoring flow in the branch flow meter of each branch screened;

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

[0090] Step 6: Calculate the target branch flow value of each selected branch according to 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 branch monitoring flow;

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

[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-differential control to obtain a first proportional adjustment coefficient change, a first integral adjustment coefficient change, and a first differential adjustment coefficient change;

[0093] Step nine: adjusting the opening of each branch valve according to the first proportional adjustment coefficient change, the first integral adjustment coefficient change and the first differential adjustment coefficient change corresponding to each branch respectively screened;

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

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

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

[0097] Rack-mounted (IT) equipment is set in each branch, and the number of branches is n. During the initial operation pressure test, the rack-mounted equipment in each branch can be pressurized to the maximum power consumption. At this time, the power of each branch is the same. It is necessary to control the flow of each branch to be completely consistent to ensure the flow resistance, phase change temperature and temperature of the rack-mounted equipment in each branch. The main line flow needs to be evenly distributed to each branch. The main line flow is F0, and the flow of each branch needs to be controlled at Fn=F0 / n. The power consumption of rack-mounted equipment Q1=working fluid latent heat Q2+sensible heat Q3, sensible heat Q3=cm(T1-Tn1), T1 is the working fluid phase change temperature, the branch inlet temperature of each branch is Tn1, m is the branch mass flow, c is the specific heat capacity, latent heat Q2=Fn*L*0.6, L is the working fluid phase change latent heat coefficient, and the total flow F0=(Q1-cm(T1-Tn1)) / 0.6 / L*n can be obtained.

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

[0099] Refer to Figure 5, which is a fuzzy proportional integral differential control principle diagram in an embodiment of the present invention. The first error E and the first error change rate Ec between the actual branch monitoring flow and the target branch flow value corresponding to each screened branch are calculated respectively, and the first error E and the first error change rate Ec are input into the fuzzy controller, and the fuzzy controller is used to perform proportional integral derivative (PID) control according to the fuzzy control algorithm to obtain the first proportional adjustment coefficient change △Kp, the first integral adjustment coefficient change △Ki and the first differential adjustment coefficient change △Kd, and the valve opening of each branch is adjusted according to the first proportional adjustment coefficient change △Kp, the first integral adjustment coefficient change △Ki and the first differential adjustment coefficient change △Kd corresponding to each screened branch. After the adjustment is completed, the current working fluid phase change rate of each branch in the system is obtained respectively, and the current working fluid phase change rate of each branch is compared with the preset value again. When it is determined that there is a branch whose current working fluid phase change rate is inconsistent with the preset value, the branches whose current working fluid phase change rate is inconsistent with the preset value are screened again from the branches, and the target branch flow value of each branch is calculated, and the fuzzy controller is used to adjust the valve opening of each branch until the working fluid phase change rate of each branch in the system is controlled to the preset value. When the working fluid phase change temperature type is a fixed value and the power consumption change ratio of each branch is inconsistent, the target branch flow value of each branch is calculated, and the fuzzy controller is used to adjust the valve opening of each branch according to the calculation results, so that the working fluid phase change rate of each branch is adjusted to the optimal value. Through fuzzy adaptive proportional integral differential control, the control system has better dynamic response performance under load mutation.

[0100] In proportional-integral-differential control, the increase of the proportional adjustment coefficient Kp may cause instability of the closed-loop system. The integral adjustment coefficient Ki can help eliminate static errors, but as the integral adjustment coefficient Ki increases, the system overshoot will also increase, which may eventually lead to system instability. The increase of the differential adjustment coefficient Kd can speed up the system response and shorten the adjustment time, but unlimited increase may also make the system unstable. In this control process, the setting principles of the three parameters are as follows: the setting range of the proportional adjustment coefficient Kp is 1-10, the setting range of the integral adjustment coefficient Ki is 0.1-0.2, and the setting range of the differential adjustment coefficient Kd is 0.1-1. When the following △ value changes greatly, the change ratio is 10%, moderate is 5%, and small change ratio is 2%:

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

[0102] (2) When e·ec<0, it means that the system error is decreasing. We should try to keep the original input Kp and Ki, so △Kp and △Ki 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 input 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 to be in the oscillation stage, so △Kp, △Ki, and △Kd are maintained at small values.

[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, so △Kp is large and △Ki is moderate.

[0105] Through the above process, accurate proportional-integral-differential control is achieved based on the relationship between the error and the error change rate, thereby improving the accuracy of the proportional-integral-differential control.

[0106] In a specific embodiment of the present invention, using a fuzzy controller to perform proportional-integral-differential control to obtain a first proportional adjustment coefficient change, a first integral adjustment coefficient change, and a first differential adjustment coefficient change may include the following steps:

[0107] The fuzzy controller is used to perform proportional-integral-differential control on the opening of each branch valve through a fuzzy control algorithm to obtain the first proportional adjustment coefficient change, the first integral adjustment coefficient change and the first differential adjustment coefficient change corresponding to the opening of each branch valve.

[0108] When using the fuzzy controller for proportional-integral-differential control, the fuzzy controller is used to perform proportional-integral-differential control on the opening of each branch valve through the fuzzy control algorithm, and the first proportional adjustment coefficient change, the first integral adjustment coefficient change and the first differential adjustment coefficient change corresponding to the opening of each branch valve are obtained. Thus, the branch flow control amount is mapped to the branch valve opening, which improves the convenience of controlling the phase change rate of the branch working medium.

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

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

[0111] 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 a preset value by adjusting the main line pump speed and the main line valve opening to adjust the main line output flow.

[0112] When the working fluid phase change temperature type is a fixed value and the power consumption change ratio of each branch is consistent, such as when the power consumption reduction ratio of each branch is completely consistent, the output flow of the main line is adjusted by adjusting the main line pump speed and the main line valve opening, so as to control the phase change rate of each branch working fluid to a preset value. When the working fluid phase change temperature type is a fixed value and the power consumption change ratio of each branch is consistent, the phase change rate of each branch working fluid can be controlled to the optimal value by only adjusting the main line pump speed, thereby improving the regulation efficiency of the phase change rate of each branch working fluid.

[0113] Refer to Figure 6, which is a flow chart of a system flow control implementation in an embodiment of the present invention. In the process of system flow control, the main line flow setting value is obtained, the actual value of the outlet flow is obtained, the absolute value of the difference between the main line flow setting value and the actual value of the outlet flow is calculated, and it is determined whether the calculated absolute value of the difference is less than or equal to 0.51pm. If the absolute value of the difference is less than or equal to 0.51pm, it is further determined whether the actual value of the outlet flow is less than the main line flow setting value. If the actual value of the outlet flow is less than the main line flow setting value, the opening of the two-way valve of the main line is controlled to increase by 0.5%. If the actual value of the outlet flow is not less than the main line flow setting value, it is determined whether the actual value of the outlet flow is greater than the main line flow setting value. If the actual value of the outlet flow is greater than the main line flow setting value, the control is terminated. If the actual value of the outlet flow is not greater than the main line flow setting value, the opening of the two-way valve of the main line is controlled to decrease by 0.5%. If the absolute value of the difference is greater than 0.51pm, it is determined whether the actual value of the outlet flow is less than the set value of the main flow. When it is determined that the actual value of the outlet flow is less than the set value of the main flow, the speed of the circulation pump is increased by 2%. When it is determined that the actual value of the outlet flow is not less than the set value of the main flow, the speed of the circulation pump is reduced by 2%. And after each control, it is further determined whether the actual value of the outlet flow is equal to the set value of the main flow. If so, the control is terminated. If not, the absolute value of the difference between the set value of the main flow and the actual value of the outlet flow is compared with the set value of 0.51pm again. 0.51pm is a value calculated based on experience, which can be set and adjusted according to actual conditions.

[0114] Refer to Figure 7, which is a flow chart for implementing the phase change rate control of a branch working fluid in an embodiment of the present invention. In the process of the phase change rate of the system branch working fluid, the phase change rate setting value is obtained, the actual value of the branch phase change rate is obtained, and it is determined whether the absolute value of the difference between the actual value of the branch phase change rate and the phase change rate setting value 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 value of the branch phase change rate is greater than the phase change rate setting value. If the actual value of the branch phase change rate is greater than the phase change rate setting value, the two-way valve opening of the branch is controlled to increase by 0.5%. If the actual value of the branch phase change rate is not greater than the phase change rate setting value, it is determined whether the actual value of the branch phase change rate is less than the phase change rate setting value. If the actual value of the branch phase change rate is less than the phase change rate setting value, the control is terminated. If the actual value of the branch phase change rate is not less than the phase change rate setting value, the two-way valve opening of the branch is controlled to decrease 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 of the phase change rate. When it is determined that the actual value of the branch phase change rate is greater than the set value of the phase change rate, the circulating pump speed is increased by 2%. When it is determined that the actual value of the branch phase change rate is not greater than the set value of the phase change rate, the circulating pump speed is reduced by 2%. And after each control, it is further determined whether the actual value of the branch phase change rate is equal to the set value of the phase change rate. If so, the control is terminated. If not, the absolute value of the difference between the set value of the phase change rate and the actual value of the branch phase change rate is compared with the set value of 5%. 5% is a value calculated based on experience, which can be set and adjusted according to actual conditions.

[0115] Referring to FIG. 8 , FIG. 8 is a flowchart of another implementation method of a two-phase cold plate liquid cooling system control method in an embodiment of the present invention. The method may include the following steps:

[0116] S801: Obtaining a working fluid phase change temperature type of a coolant 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 system flow.

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

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

[0120] S804: Obtain the current working fluid phase change rate of each branch respectively.

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

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

[0123] After the current working fluid phase change rate of each branch is obtained, the current working fluid phase change rate of each branch is compared with a preset value, and branches whose current working fluid phase change rate is inconsistent with the preset value are screened out from the branches.

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

[0125] After screening out the branches whose 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 screened branch are obtained.

[0126] S807: Calculate the branch inlet working fluid enthalpy of each selected branch according to the branch inlet temperature and the branch inlet pressure.

[0127] After obtaining the branch inlet temperature T0 and the branch inlet pressure Pn1 of each branch screened, the branch inlet working fluid enthalpy Hn1 of each branch screened is calculated according to the branch inlet temperature T0 and the branch inlet pressure Pn1. For example, the branch inlet working fluid enthalpy of each branch screened can be calculated by the formula: H=f1(P,T), where f1(.) represents the function between the pipeline temperature, pressure and the working fluid enthalpy.

[0128] S808: Read the actual branch monitoring flow in the branch flow meter of each screened branch respectively.

[0129] A flow meter for flow monitoring is pre-installed in each branch. After the branches whose current working fluid phase change rate is inconsistent with the preset value are screened, the actual branch monitoring flow m in the branch flow meter of each screened branch is read respectively.

[0130] S809: Calculate the target branch flow value of each selected branch according to 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 branch monitoring flow.

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

[0132] S810: Calculate the branch outlet working fluid enthalpy value of each screened branch according to the branch inlet working fluid enthalpy value of each screened branch, the equipment power consumption and the target branch flow value.

[0133] After calculating the target branch flow value Fn of each screened branch, the branch outlet working fluid enthalpy value Hn2 of each screened branch is calculated according to the branch inlet working fluid enthalpy value Hn1 of each screened branch, the equipment power consumption Qn and the target branch flow value Fn. The calculation formula can be: Hn2=Hn1+Qn / Fn.

[0134] S811: Calculate the target working fluid phase change rate of each selected branch according to the branch outlet working fluid enthalpy value and branch outlet pressure of each selected branch.

[0135] After calculating the branch outlet working fluid enthalpy value Hn2 of each selected branch, the target working fluid phase change rate of each selected branch is calculated according to the branch outlet working fluid enthalpy value Hn2 and the branch outlet pressure Pn2 of each selected branch. For example, the target working fluid phase change rate x of each selected branch can be calculated by the formula: x=f2(Hn2,Pn2), where f2(.) represents the function between the outlet working fluid enthalpy value, the outlet pressure and the working fluid phase change rate.

[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 corresponding to each selected branch respectively.

[0137] After the target working fluid phase change rate of each screened branch is calculated, 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 corresponding to each screened branch are calculated respectively.

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

[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 corresponding to each screened branch, the second error and the second error change rate are input into the fuzzy controller, and the fuzzy controller is used to perform proportional, integral and differential control to obtain the second proportional adjustment coefficient change, the second integral adjustment coefficient change and the second differential adjustment coefficient change.

[0140] S814: adjusting the opening of each branch valve 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.

[0141] After calculating the second proportional regulation coefficient change, the second integral regulation coefficient change and the second differential regulation coefficient change, the valve opening of each branch is adjusted according to the second proportional regulation coefficient change, the second integral regulation coefficient change and the second differential regulation coefficient change corresponding to each screened branch.

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

[0143] After adjusting the opening of each branch valve according to the second proportional regulation coefficient change, the second integral regulation coefficient change and the second differential regulation coefficient change corresponding to each branch respectively, the current working medium phase change rate of each branch in the system is obtained respectively.

[0144] S816: Determine whether there is a branch where the current working fluid phase change rate is inconsistent with the preset value. If so, return to step S805, if not, end the control process.

[0145] After respectively obtaining the current working fluid phase change rate of each branch in the system, determine whether there is a branch whose current working fluid phase change rate is inconsistent with the preset value. If so, it means that it is necessary to further adjust the working fluid phase change rate of the branch whose working fluid phase change rate is inconsistent with the preset value, and again select the branches whose current working fluid phase change rate is inconsistent with the preset value from each branch for further adjustment of the working fluid phase change rate. If not, it means that the working fluid phase change rate of each branch has reached the optimal value, and each branch is in a state of optimal heat exchange efficiency, and the control process ends.

[0146] When the working fluid phase change temperature type is a range value, the fuzzy controller is used to adjust the valve opening of each branch according to the working fluid phase change rate of each branch, so that the working fluid phase change rate of each branch is adjusted to the optimal value. Through fuzzy adaptive proportional integral differential control, the control system has better dynamic response performance under load mutation.

[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, and the embodiment of the present invention does not limit this.

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

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

[0150] 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 prompt message is output. By issuing an alarm for branches where the adjustment time exceeds the preset time and the current working fluid phase change rate after adjustment exceeds the preset phase change rate threshold range, the operation and maintenance personnel can be prompted to perform maintenance in a timely manner, thereby improving system safety.

[0151] It should be noted that the preset duration can be set and adjusted according to actual conditions, and the embodiment of the present invention does not limit this. For example, it can be set to 20 seconds.

[0152] It should also be noted that the preset phase change rate threshold range can be set and adjusted according to actual conditions, and the embodiment of the present invention does not limit this. For example, it can be set to 40%-80%.

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

[0154] Referring to FIG. 9 , FIG. 9 is a structural block diagram of a two-phase cold plate liquid cooling system control device in an embodiment of the present invention, and 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 the 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 medium in each branch to a preset value by controlling the system flow when the working medium 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 each branch working medium to a preset value by controlling the phase change rate of each branch when the working medium phase change temperature type is a range value.

[0158] It can be seen from the above technical scheme that by presetting the preset value of the phase change rate of the branch working fluid that makes the heat exchange efficiency of each branch optimal, the working fluid 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 working fluid is controlled to the preset value by controlling the system flow. When the working fluid phase change temperature type is a range value, the phase change rate of each branch working fluid 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 the two control schemes of system flow control and each branch phase change rate control, the phase change rate of each branch is at the value with the highest heat exchange efficiency. The control system has better dynamic response performance under load mutation. By real-time monitoring of the phase change rate of each branch, the probability of branch working fluid drying or no phase change abnormality is greatly reduced. The robustness of the control system is improved and the system performance is improved. The control process is completed automatically, saving manpower.

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

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

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

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

[0163] The first branch screening submodule is used to obtain the current working fluid phase change rate of each branch respectively, and screen out the branches whose current working fluid phase change rate is inconsistent with the preset value from each branch;

[0164] The first device power consumption acquisition submodule is used to respectively acquire the device power consumption of each screened branch;

[0165] The first flow reading submodule is used to read the actual branch monitoring flow in the branch flow meter of each branch that has been screened;

[0166] The first branch inlet temperature acquisition submodule is used to obtain the branch inlet temperature of each screened branch;

[0167] The first target branch flow value calculation submodule is used to calculate the target branch flow value of each selected branch according to 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 branch monitoring flow;

[0168] A first error and error change rate calculation submodule, used to respectively calculate the first error and the first error change rate between the actual branch monitoring flow and the target branch flow value corresponding to each screened branch;

[0169] A first proportional-integral-differential control submodule is used to input the first error and the first error change rate into the fuzzy controller, and use the fuzzy controller to perform proportional-integral-differential control to obtain a first proportional adjustment coefficient change, a first integral adjustment coefficient change, and a first differential adjustment coefficient change;

[0170] The first branch valve opening adjustment submodule is used to adjust the opening of each branch valve according to the first proportional adjustment coefficient change, the first integral adjustment coefficient change and the first differential adjustment coefficient change corresponding to each screened branch;

[0171] The first working fluid phase change rate acquisition submodule is used to respectively acquire the current working fluid phase change 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 screening out branches whose current working fluid phase change rate is inconsistent with the preset value from each branch 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 a specific embodiment of the present invention, the first proportional-integral-differential control submodule is a module that uses a fuzzy controller to perform proportional-integral-differential control on the opening of each branch valve through a fuzzy control algorithm to obtain the first proportional adjustment coefficient change, the first integral adjustment coefficient change and the first differential adjustment coefficient change corresponding to the opening of each branch valve.

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

[0175] The second fixed value 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 screening submodule is used to obtain the current working fluid phase change rate of each branch respectively, and screen out the branches whose current working fluid phase change rate is inconsistent with the preset value from each branch;

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

[0178] The branch inlet working fluid enthalpy value calculation submodule is used to calculate the branch inlet working fluid enthalpy value of each selected branch according to the branch inlet temperature and the branch inlet pressure;

[0179] The second flow reading submodule is used to read the actual branch monitoring flow in the branch flow meter of each branch that has been screened;

[0180] The branch outlet working fluid enthalpy value calculation submodule is used to calculate the branch outlet working fluid enthalpy value of each screened branch according to the branch inlet working fluid enthalpy value of each screened branch, the equipment power consumption and the target branch flow value;

[0181] A target working fluid phase change rate calculation submodule is used to calculate the target working fluid phase change rate of each selected branch according to the branch outlet working fluid enthalpy value and branch outlet pressure of each selected branch;

[0182] A second error and error change rate calculation submodule, used to respectively 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 corresponding to each screened branch;

[0183] A second proportional-integral-differential control submodule is used to input the second error and the second error change rate into the fuzzy controller, and use the fuzzy controller to perform proportional-integral-differential control to obtain a second proportional adjustment coefficient change, a second integral adjustment coefficient change, and a second differential adjustment coefficient change;

[0184] The second branch valve opening adjustment submodule is used to adjust the opening of each branch valve 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;

[0185] The second working fluid phase change rate acquisition submodule is used to respectively 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 screening out branches whose current working fluid phase change rate is inconsistent with the preset value from each branch 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.

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

[0188] The alarm prompt information output module is used to output an alarm prompt information when there is a branch in which the working fluid phase change rate adjustment time exceeds the preset time and the adjusted current working fluid phase change rate exceeds the preset phase change rate threshold range.

[0189] Corresponding to the above method embodiment, referring to FIG. 10 , FIG. 10 is a schematic diagram of a two-phase cold plate liquid cooling system control device provided by the present invention, and the device may include:

[0190] A memory 332, for storing computer programs;

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

[0192] Specifically, please refer to FIG. 11, which is a schematic diagram of 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 may have relatively large differences due to different configurations or performances, and may include a processor (central processing units, CPU) 322 (for example, one or more processors) and a memory 332, and the memory 332 stores one or more computer programs 342 or data 344. Among them, the memory 332 can be a temporary storage or a permanent storage. The program stored in the memory 332 may include one or more modules (not shown in the figure), and each module may include a series of instruction operations in the data processing device. Furthermore, the processor 322 can be configured to communicate with the memory 332 to execute a series of instruction operations 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 further include one or more power supplies 326 , one or more wired or wireless network interfaces 350 , one or more input and output interfaces 358 , and / or one or more operating systems 341 .

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

[0195] Corresponding to the above method embodiment, the present invention further provides a computer-readable storage medium, on which a computer program is stored. When the computer program is executed by a processor, the following steps can be implemented:

[0196] Obtain the working fluid phase change temperature type of the coolant 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; 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: a USB flash drive, a mobile hard disk, a read-only memory (ROM), a random access memory (RAM), a magnetic disk or an optical disk, and other media that can store program codes.

[0198] For an introduction to the computer-readable storage medium provided by the present invention, please refer to the above method embodiment, and the present invention will not be elaborated here.

[0199] Corresponding to the above method embodiment, the present invention further provides a computer program product, including a computer program, which implements the steps of the above two-phase cold plate liquid cooling system control method when executed by a processor.

[0200] In this specification, each embodiment is described in a progressive manner, and each embodiment focuses on the differences from other embodiments. The same or similar parts between the embodiments can be referred to each other. For the devices, equipment and computer-readable storage media disclosed in the embodiments, since they correspond to the methods disclosed in the embodiments, the description is relatively simple, and the relevant parts can be referred to the method part description.

[0201] The principles and implementation methods of the present invention are described in this article using specific examples. The description of the above embodiments is only used to help understand the technical solution and core ideas of the present invention. It should be pointed out that for ordinary technicians in this technical field, without departing from the principles of the present invention, the present invention can also be improved and modified, and these improvements and modifications also fall within the scope of protection of the present invention.

Claims

1. A two-phase cold plate liquid cooling system control method, characterized in that: include: Obtain the working fluid phase change temperature type of the coolant in the two-phase cold plate liquid cooling system; When the working medium phase change temperature type is a fixed value, the phase change rate of the working medium in 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 phase change rate of the working medium in each branch is controlled to the preset value by controlling the phase change rate of each branch.

2. The two-phase cold plate liquid cooling system control method according to claim 1, characterized in that: When the working medium phase change temperature type is a fixed value, the phase change rate of the working medium in each branch is controlled to a preset value by controlling the system flow, 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 main line pump speed and the main line valve opening to adjust the main line output flow.

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

4. The two-phase cold plate liquid cooling system control method according to claim 3, characterized in that: By adjusting the opening of each branch valve to adjust the flow of each branch, the phase change rate of each branch working medium is controlled to the preset value, including: Obtaining the specific heat capacity of the coolant, the working fluid phase change latent heat coefficient and the working fluid phase change temperature; The current working fluid phase change rate of each branch is obtained respectively, and the branches whose current working fluid phase change rate is inconsistent with the preset value are selected from the branches; Obtain the device power consumption of each filtered branch respectively; Read the actual branch monitoring flow in the branch flow meter of each branch selected respectively; Obtain the branch inlet temperature of each screened branch; Calculate the target branch flow value of each selected branch according to the specific heat capacity, the working fluid phase change latent heat coefficient, the working fluid phase change temperature, the inlet temperature of each branch, the power consumption of each device and the actual branch monitoring flow; Calculate the first error and the first error change rate between the actual branch monitoring flow and the target branch flow value corresponding to each screened branch respectively; Inputting the first error and the first error change rate into a fuzzy controller, and using the fuzzy controller to perform proportional-integral-differential control to obtain a first proportional adjustment coefficient change, a first integral adjustment coefficient change, and a first differential adjustment coefficient change; Adjust the opening of each branch valve according to the first proportional adjustment coefficient change, the first integral adjustment coefficient change and the first differential adjustment coefficient change corresponding to each branch respectively selected; Obtain the current working fluid phase change rate of each branch in the system respectively; 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 screening out branches whose current working fluid phase change rate is inconsistent with the preset value from each branch is repeated until the working fluid phase change rate of each branch in the system is controlled to the preset value.

5. The two-phase cold plate liquid cooling system control method according to claim 4, characterized in that: The fuzzy controller is used to perform proportional-integral-differential control to obtain a first proportional adjustment coefficient change, a first integral adjustment coefficient change, and a first differential adjustment coefficient change, including: The fuzzy controller is used to perform proportional-integral-differential control on the opening of each branch valve through a fuzzy control algorithm to obtain the first proportional adjustment coefficient change, the first integral adjustment coefficient change and the first differential adjustment coefficient change corresponding to the opening of each branch valve.

6. The two-phase cold plate liquid cooling system control method according to claim 1, characterized in that: Controlling the phase change rate of each branch working medium to the preset value by controlling the phase change rate of each branch includes: Obtaining the specific heat capacity of the coolant and the latent heat coefficient of phase change of the working fluid; The current working fluid phase change rate of each branch is obtained respectively, and the branches whose current working fluid phase change rate is inconsistent with the preset value are selected from the branches; Obtain the branch inlet temperature, branch outlet temperature, branch inlet pressure, branch outlet pressure, branch equipment power consumption and current working fluid phase change temperature of each branch screened; Calculating the branch inlet working fluid enthalpy of each branch selected according to the branch inlet temperature and the branch inlet pressure; Read the actual branch monitoring flow in the branch flow meter of each branch selected respectively; Calculate the target branch flow value of each selected branch according to the specific heat capacity, the working fluid phase change latent heat coefficient, the current working fluid phase change temperature, the inlet temperature of each branch, the power consumption of each device and the actual branch monitoring flow; Calculate the working fluid enthalpy value at the branch outlet of each screened branch according to the branch inlet working fluid enthalpy value of each screened branch, the equipment power consumption and the target branch flow value; Calculating the target working fluid phase change rate of each screened branch according to the branch outlet working fluid enthalpy value and branch outlet pressure of each screened branch; Calculating respectively 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 corresponding to each of the screened branches; Inputting the second error and the second error change rate into a fuzzy controller, and using the fuzzy controller to perform proportional-integral-differential control to obtain a second proportional adjustment coefficient change, a second integral adjustment coefficient change, and a second differential adjustment coefficient change; Adjust the opening of each branch valve according to the second proportional adjustment coefficient change, the second integral adjustment coefficient change and the second differential adjustment coefficient change corresponding to each branch respectively selected; Obtain the current working fluid phase change rate of each branch in the system respectively; 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 screening out branches whose current working fluid phase change rate is inconsistent with the preset value from each branch is repeated until the working fluid phase change rate of each branch in the system is controlled to the preset value.

7. The two-phase cold plate liquid cooling system control method according to claim 6, characterized in that: Also includes: When there is a branch in which the working fluid phase change rate adjustment time exceeds the preset time and the adjusted current working fluid phase change rate exceeds the preset phase change rate threshold range, an alarm prompt message is output.

8. A two-phase cold plate liquid cooling system control device, characterized in that: include: A working fluid phase change temperature type acquisition module is used to obtain the working fluid phase change temperature type of the coolant in the two-phase cold plate liquid cooling system; A system flow control module, used to control the phase change rate of the working medium in each branch to a preset value by controlling the system flow when the working medium phase change temperature type is a fixed value; The branch phase change rate control module is used to control the phase change rate of each branch working medium to the preset value by controlling the phase change rate of each branch when the working medium phase change temperature type is a range value.

9. A two-phase cold plate liquid cooling system control device, characterized in that: include: Memory for storing computer programs; A processor, configured to implement the steps of the method according to any one of claims 1 to 7 when executing the computer program.

10. A computer-readable storage medium, characterized in that: The computer-readable storage medium stores a computer program, and when the computer program is executed by a processor, the steps of the two-phase cold plate liquid cooling system control method according to any one of claims 1 to 7 are implemented.

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