Refrigerant pump control method, power heat pipe system and readable storage medium

Abstract

The invention relates to the technical field of power heat pipe systems, in particular to a refrigerant pump control method for a power heat pipe system, computing equipment and a storage medium. The method comprises the steps that after a refrigerant pump is started, a first pressure value at an inlet of the refrigerant pump and a second pressure value at an outlet of the refrigerant pump are obtained; obtaining a pressure difference value according to a second pressure value and the first pressure value; if the pressure difference value is smaller than or equal to the first preset pressure value, the refrigerant pump is closed; and starting the refrigerant pump again, respectively obtaining the first pressure value and the second pressure value again, and obtaining the pressure difference value according to the second pressure value and the first pressure value until the pressure difference value is greater than the first preset pressure value, so that the refrigerant pump operates normally. According to the method, the cutoff phenomenon caused by the fact that the refrigerant cannot be pumped out can be avoided. Moreover, the interior of the pipeline can be vacuumized by repeatedly starting the refrigerant pump, so that the starting success rate of the refrigerant pump is increased.

Description

Technical Field

[0001] The present application relates to the technical field of power heat pipe systems, and in particular to a refrigerant pump control method, a power heat pipe system and a computer-readable storage medium. Background Art

[0002] Data centers are important technology platforms in the communications industry and are integrated to ensure the security of information transmission and storage. IT equipment, communication equipment, and UPS (UPS stands for Uninterruptible Power Supply, which is an uninterruptible power supply with energy storage devices) in data centers run uninterruptedly throughout the year. These devices generate a lot of heat. In order to prevent the equipment from overheating and damage, traditional computer room air conditioners use a single vapor compression refrigeration technology for temperature control. Since the computer room air conditioners in data centers have the characteristics of all-weather cooling operation, the energy consumption of air conditioners accounts for a large proportion of the equipment energy consumption, especially in the north or in winter. Since the outdoor temperature is much lower than the indoor temperature, the compressor still needs to consume power for cooling, which further increases the power consumption of the data center. When the outdoor ambient temperature is lower than a certain temperature, the use of heat pipe indirect cooling can shorten the operating time of the compression refrigeration unit, save energy, and extend the service life of the unit.

[0003] Heat pipes include power heat pipes, which refer to heat pipe systems with external circulation driving force. In the field of power heat pipes, their stability and reliability depend on the refrigerant pump. Once the refrigerant pump is disconnected, the refrigerant will not be able to circulate, and the system will not be able to provide cooling for the computer room, which will directly affect the operation of the power heat pipe.

[0004] Then, at present, when the refrigerant pump is started normally, the disturbance of the refrigerant at the inlet of the refrigerant pump is large, resulting in a rapid drop in the refrigerant pressure, making the refrigerant pump prone to flow interruption, affecting the operation of the unit. Summary of the invention

[0005] Based on this, it is necessary to provide a refrigerant pump control method, a power heat pipe system and a computer-readable storage medium that can ensure the normal startup of the refrigerant pump and prevent the refrigerant pump from being interrupted in order to solve the above technical problems.

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

[0007] In a first aspect, the present application provides a refrigerant pump control method for a power heat pipe system, the refrigerant pump control method for a power heat pipe system comprising:

[0008] After starting the refrigerant pump, respectively obtaining a first pressure value at the inlet and a second pressure value at the outlet of the refrigerant pump;

[0009] Obtaining a pressure difference value according to the second pressure value and the first pressure value;

[0010] If the pressure difference is less than or equal to a first preset pressure value, shutting down the refrigerant pump;

[0011] The refrigerant pump is started again, and the first pressure value and the second pressure value are respectively obtained again, and the pressure difference is obtained according to the second pressure value and the first pressure value, until the pressure difference is greater than the first preset pressure value, and the refrigerant pump operates normally.

[0012] In one embodiment, if the pressure difference is less than or equal to a first preset pressure value, shutting down the refrigerant pump includes:

[0013] Acquire a plurality of pressure difference values ​​within a preset time;

[0014] If the plurality of pressure difference values ​​are all less than or equal to the first preset pressure value, the refrigerant pump is turned off.

[0015] In one embodiment, restarting the refrigerant pump comprises:

[0016] After the refrigerant pump is turned off for a second preset time, the refrigerant pump is started again.

[0017] In one embodiment, after the refrigerant pump operates normally, the refrigerant pump control method for the power heat pipe system further includes:

[0018] Acquire a third pressure value and a fourth pressure value at the inlet of the refrigerant pump at a third preset time interval respectively;

[0019] determining a pressure change rate according to the third preset time, the third pressure value, and the fourth pressure value;

[0020] If the pressure change rate is greater than the change rate threshold, the heat exchange efficiency between the cold source side and the refrigerant in the power heat pipe system is reduced.

[0021] In one embodiment, the change rate threshold range is configured to be between 3 kPa / s and 5 kPa / s.

[0022] In one embodiment, after the refrigerant pump operates normally, the method for preventing the refrigeration pump from breaking off for the power heat pipe system further comprises:

[0023] Obtain the cooling demand of the load in the power heat pipe system;

[0024] According to the refrigeration demand, the superheat value of the refrigerant on one side of the refrigerant pump is set, and the power heat pipe system is operated at the superheat value.

[0025] In one embodiment, according to the cooling demand, setting the superheat value so that the power heat pipe system operates at the superheat value includes:

[0026] When the cooling demand is greater than or equal to a first cooling demand threshold, the superheat value is set to a first superheat value, and the power heat pipe system is operated at the first superheat value;

[0027] When the cooling demand is less than a first cooling demand threshold and greater than or equal to a second cooling demand threshold, the superheat value is set to a second superheat value, and the power heat pipe system is operated at the second superheat value;

[0028] When the cooling demand is less than the second cooling demand threshold, the superheat value is set to a third superheat value, and the power heat pipe system is operated at the third superheat value;

[0029] The first refrigeration demand threshold is smaller than the second refrigeration demand threshold, and the second refrigeration demand threshold is smaller than the third refrigeration demand threshold.

[0030] In one embodiment, the first superheat value ranges from -1°C to ≤2°, the second superheat value ranges from 1°≤ to ​​≤3°, and the third superheat value ranges from 2°≤ to ​​≤5°.

[0031] In a second aspect, the present application further provides a power heat pipe system, comprising a memory and a processor, wherein the memory stores a computer program, and the processor is configured to run the computer program to execute the refrigerant pump control method for the power heat pipe system described in the first aspect.

[0032] In a third aspect, the present application further provides a computer-readable storage medium having a computer program stored thereon, wherein when the computer program is executed by a processor, the refrigerant pump control method for a power heat pipe system described in the first aspect is implemented.

[0033] Compared with the prior art, the above-mentioned refrigerant pump control method for a power heat pipe system and the power heat pipe system obtain the pressure values ​​of the refrigerant at the inlet and outlet of the refrigerant pump after the refrigerant pump is started, thereby obtaining the pressure difference of the refrigerant between the outlet and the inlet and outlet. A small pressure difference indicates that the disturbance of the refrigerant at the inlet of the refrigerant pump is large. At this time, the refrigerant pump is turned off to avoid the phenomenon of the refrigerant being unable to be pumped out and the flow being cut off. In addition, by repeatedly starting the refrigerant pump, the inside of the pipeline can be evacuated, thereby increasing the success rate of starting the refrigerant pump. BRIEF DESCRIPTION OF THE DRAWINGS

[0034] In order to more clearly illustrate the technical solutions in the embodiments of the present application or the conventional technology, the drawings required for use in the embodiments or the conventional technology descriptions are briefly introduced below. Obviously, the drawings described below are only some embodiments of the present application. For ordinary technicians in this field, other drawings can be obtained based on these drawings without creative work.

[0035] Figure 1 This is an application environment diagram of a refrigerant pump control method for a power heat pipe system in an embodiment provided in the present application.

[0036] Figure 2 A schematic diagram of the structure of a power heat pipe system in an embodiment provided in the present application.

[0037] Figure 3 A schematic flow chart of a refrigerant pump control method for a power heat pipe system in an embodiment provided in the present application.

[0038] Figure 4 A schematic flow chart of a refrigerant pump control method for a power heat pipe system in another embodiment provided in the present application.

[0039] Figure 5 A schematic flow chart of a refrigerant pump control method for a power heat pipe system in another embodiment provided in the present application.

[0040] Figure 6 A schematic flow chart of a refrigerant pump control method for a power heat pipe system in another embodiment provided in the present application.

[0041] Figure 7 A schematic flow chart of a refrigerant pump control method for a power heat pipe system in another embodiment provided in the present application.

[0042] Figure 8 This is a diagram of the internal structure of a power heat pipe system in an embodiment provided in the present application.

[0043] Figure numerals: 102, power heat pipe system; 1021, power heat pipe; 1022, cold source side; 1023, refrigerant pump cabinet; 104, lower computer. DETAILED DESCRIPTION

[0044] In order to make the purpose, technical solution and advantages of the present application more clearly understood, the present application is further described in detail below in conjunction with the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are only used to explain the present application and are not used to limit the present application.

[0045] The refrigerant pump control method for a power heat pipe system provided in the embodiment of the present application can be applied to Figure 1In the application environment shown. Among them, the power heat pipe system 102 communicates with the lower computer 104 through the network. The data storage system can store data that the lower computer 104 needs to process. The data storage system can be integrated on the lower computer 104, or it can be placed on the cloud or other network servers. When the refrigerant pump is started, the lower computer 104 obtains the first pressure value at the inlet of the refrigerant pump and the second pressure value at the outlet respectively; the pressure difference is obtained according to the second pressure value and the first pressure value; if the pressure difference is less than or equal to the first preset pressure value, the refrigerant pump is turned off and started again, and the first pressure value and the second pressure value are obtained again respectively, and the pressure difference is obtained according to the second pressure value and the first pressure value, until the pressure difference is greater than the first preset pressure value, and the refrigerant pump operates normally. That is, the corresponding refrigerant pump operation information is sent to the corresponding power heat pipe system 102 through the communication network. Among them, such as Figure 2 As shown, the power heat pipe system 102 includes a power heat pipe 1021, a cold source side 1022, and a refrigerant pump cabinet 1023. The cold source side 1022 is mainly a side that provides coldness for the refrigerant, that is, the refrigerant that circulates heat exchange with one side of the power heat pipe 1021 provides coldness. Here, exemplarily, the cold source side 1022 is set as a heat pipe composite unit or a plate exchange system. The refrigerant circulating in the cold source side 1022 is defined as: refrigerant A, and the refrigerant circulating in one side of the power heat pipe 1021 is defined as: refrigerant B. The refrigerant pump cabinet 1023 serves as a power source to provide power for the refrigerant B circulation in one side of the power heat pipe 1021. Specifically, under the action of the refrigerant pump cabinet 1023, the refrigerant B circulates and exchanges heat with the inside of the machine room to provide coldness for the machine room. The heat-exchanged refrigerant B then exchanges heat with the refrigerant A on the cold source side 1022, so that the cooled refrigerant B continues to exchange heat with the inside of the machine room, and circulates in this way. The lower computer 104 can be a PCL, a single-chip microcomputer, etc.

[0046] In one embodiment, Figure 3 As shown, a refrigerant pump control method for a power heat pipe system is provided, and the method is applied to Figure 1 The method is described by taking the lower computer in the example as an example. It can be understood that the method can also be applied to a server, and can also be applied to a system including a lower computer and a server, and is implemented through the interaction between the lower computer and the server. In this embodiment, the method includes the following steps:

[0047] S10, after starting the refrigerant pump, respectively obtaining a first pressure value at the inlet of the refrigerant pump and a second pressure value at the outlet;

[0048] S20, obtaining a pressure difference value according to the second pressure value and the first pressure value;

[0049] S30, if the pressure difference is less than or equal to the first preset pressure value, turning off the refrigerant pump;

[0050] S40, restarting the refrigerant pump, and respectively obtaining the first pressure value and the second pressure value again, and obtaining a pressure difference according to the second pressure value and the first pressure value, until the pressure difference is greater than the first preset pressure value, and the refrigerant pump operates normally.

[0051] It is understandable that the inlet of the refrigerant pump is connected to the liquid storage tank, so that the refrigerant pump can extract refrigerant from the liquid storage tank into the refrigerant pump, thereby driving the refrigerant to circulate through the refrigerant pump. When the system is in the startup stage, the temperature of the cold source side 1022 is low, causing the inside of the liquid storage tank to be in a boiling state, and the refrigerant in the liquid storage tank cannot be pumped out by the refrigerant pump, that is, the refrigerant pump has a flow break phenomenon. In the above-mentioned refrigerant pump control method for the power heat pipe system, after the refrigerant pump is started, the pressure values ​​of the refrigerant at the inlet and outlet of the refrigerant pump are obtained, so as to obtain the pressure difference of the refrigerant between the outlet and the inlet and outlet. If the pressure difference is small, it means that the disturbance of the refrigerant at the inlet of the refrigerant pump is large. At this time, the refrigerant pump is turned off to avoid the phenomenon of flow break due to the inability to extract the refrigerant. In addition, by repeatedly starting the refrigerant pump, the inside of the pipeline can be evacuated, thereby increasing the success rate of starting the refrigerant pump.

[0052] In step S10, pressure sensors may be provided at the inlet and outlet of the refrigerant pump, respectively, so as to obtain the first pressure value and the second pressure value correspondingly through the pressure sensors. Of course, the pressure is not limited to the pressure sensor, and it may also be a pressure switch, a pressure gauge and other components.

[0053] Furthermore, the first pressure value and the second pressure value may be obtained after the first preset time when the refrigerant pump is started. Here, due to the fluctuation of the refrigerant in the system during the startup of the refrigerant pump, the pressure detection may be biased. Thus, by performing the detection after the first preset time, the influence of the pressure value deviation caused by the system fluctuation can be well avoided.

[0054] Preferably, the first preset time is set in the range of 15s-25s. It is understandable that the first preset time should not be too short or too long. If it is too short, it will be affected by system fluctuations, thereby causing pressure value detection deviation; if it is too long, if the pressure difference between the refrigerant at the outlet and the inlet and outlet is too small, the refrigerant pump will be cut off, affecting the stability of system operation.

[0055] Here, the weight of the first preset time can be set to 15s, 16s, 17s, 18s, 19s, 20s, 21s, 22s, 23s, 24s, 25s, etc. Of course, the specific value of the first preset time can be selected according to actual conditions. In this embodiment, the first preset time is set to 20s.

[0056] In one embodiment, in step S30, if the pressure difference is less than or equal to the first preset pressure value, the refrigerant pump is turned off. On the contrary, if the pressure difference is greater than the first preset pressure value, the refrigerant pump operates normally.

[0057] Further, the pressure difference=the second pressure value-the first pressure value.

[0058] like Figure 4 As shown, in step S30, if the pressure difference is less than or equal to the first preset pressure value, shutting down the refrigerant pump includes:

[0059] S31, obtaining multiple pressure difference values ​​within a preset time;

[0060] S32: If the multiple pressure difference values ​​are all less than or equal to the first preset pressure value, turn off the refrigerant pump.

[0061] It is understandable that by obtaining multiple pressure difference values ​​within a preset time, and then operating the refrigerant pump accordingly according to the multiple pressure difference values, the accuracy of controlling the refrigerant pump can be improved. Specifically, the first pressure value and the second pressure value can be obtained multiple times at equal intervals within the preset time, and multiple pressure difference values ​​can be calculated.

[0062] Here, the unit of the first preset pressure value is pressure (bar), and the first preset pressure value is set to 2bar. That is, when the pressure difference value or multiple pressure differences are less than or equal to 2bar, the refrigerant pump is turned off. Of course, the value of the first preset pressure value can be 1bar, 1.5bar, 2bar, 2.5bar, etc. The specific value of the first preset pressure value can be set according to actual conditions and is not limited here.

[0063] In step S31, the weight of the preset time can be set to 10s, 11s, 12s, 13s, 14s, 15s, 16s, 17s, 18s, 19s, 20s, etc. Of course, the specific value of the preset time can be selected according to actual conditions. In this embodiment, the preset time is set to 15s.

[0064] In step S40, restarting the refrigerant pump includes:

[0065] S41, after the refrigerant pump is turned off for a second preset time, starting the refrigerant pump again.

[0066] Here, the second preset time is set to be greater than or equal to 20s, for example, the value of the second preset time can be 20s, 21s, 22s, 23s, 24s, 25s, etc. Here, the second preset time can be set according to actual needs and is not limited here.

[0067] Further, step S41 may be repeated at least twice. If the refrigerant pump still fails to start and run normally after the two times, the refrigerant pump is turned off or a fault is output.

[0068] like Figure 5 As shown, in one embodiment, after the refrigerant pump operates normally, the refrigerant pump control method for the power heat pipe system further includes:

[0069] S50, obtaining a third pressure value and a fourth pressure value at the inlet of the refrigerant pump at a third preset time interval respectively;

[0070] S60, determining a pressure change rate according to a third preset time, a third pressure value, and a fourth pressure value;

[0071] S70: If the pressure change rate is greater than the change rate threshold, the heat exchange efficiency between the cold source side 1022 and the refrigerant in the power heat pipe system is reduced.

[0072] It is understandable that during the operation stage of the power heat pipe system, the refrigerant will also be disturbed, such as changes in load, adjustment of the control valve, etc., causing refrigerant fluctuations in the system. The fluctuation of the refrigerant can be characterized by a pressure value. The pressure change rate reflects the degree of refrigerant fluctuations. Therefore, in the present application, during the operation of the refrigerant pump, the heat exchange efficiency between the power cold source side 1022 and the refrigerant is controlled by obtaining the pressure change rate and according to the relationship between the pressure change rate and the change rate threshold, thereby achieving control of the third pressure value and the fourth pressure value of the refrigerant, and then adjusting the pressure change rate over time. In this way, the interruption of the refrigerant pump caused by the fluctuation of the refrigerant is reduced.

[0073] Here, when it is necessary to reduce the heat exchange efficiency between the cold source side 1022 and the refrigerant, the temperature of the heat exchange medium between the cold source side 1022 and the refrigerant can be increased, so that the temperature of the heat exchange medium and the refrigerant on the cold source side 1022 will decrease, thereby reducing the heat exchange rate between the heat exchange medium and the refrigerant, that is, reducing the heat exchange efficiency between the cold source side 1022 and the refrigerant. When it is necessary to increase the heat exchange efficiency of the refrigerant, the temperature of the heat exchange medium between the cold source side 1022 and the refrigerant can be reduced, so that the temperature difference between the heat exchange medium and the refrigerant on the cold source side 1022 will increase, thereby increasing the heat exchange rate between the heat exchange medium and the refrigerant, that is, increasing the heat exchange efficiency between the cold source side 1022 and the refrigerant.

[0074] For example, in this embodiment, see Figure 2 , the cold source side 1022 is set as a heat pipe composite unit, and the heat pipe composite unit mainly includes a compressor, an electronic expansion valve, a shell and tube heat exchanger, a gas-liquid separator and other structures. The main principle of the heat pipe composite unit providing a cold source is as follows: When the outdoor ambient temperature is high in summer, the compressor starts, and the compressor outputs high-temperature and high-pressure gaseous refrigerant A, which becomes medium-temperature and high-pressure liquid refrigerant A after condensation and heat dissipation by the outdoor condenser, and flows to the electronic expansion valve after filtration by the drying filter cartridge, and becomes low-temperature and low-pressure gas-liquid refrigerant A after throttling expansion. The liquid refrigerant A flows to the first channel of the shell and tube heat exchanger, and exchanges heat with the refrigerant B in the second channel of the shell and tube heat exchanger. The refrigerant A absorbs the heat of the refrigerant B and evaporates to become a medium-temperature gas and flows to the gas-liquid separator. The separated gaseous refrigerant A flows back to The compressor compresses and recirculates; the liquid refrigerant B (which may contain a small amount of gas) that has been cooled by heat exchange with refrigerant A flows through the refrigerant pump cabinet 1023 under the action of the refrigerant pump, and the liquid refrigerant B flows to the electronic expansion valve arranged at the power heat pipe 1021, and after throttling and expansion, it becomes a low-temperature and low-pressure gas. The liquid refrigerant B flows to the back plate of the power heat pipe 1021 and exchanges heat with the indoor ambient temperature, thereby cooling and dissipating the heat in the computer room of the data center; after absorbing the heat from the indoor environment, the refrigerant B evaporates and becomes a medium-temperature gas, which flows to the heat exchanger to exchange heat with the refrigerant A again, and then condenses into liquid refrigerant B to form a cycle. When the outdoor ambient temperature is low in winter and other conditions, the demand for cooling capacity is small (the room is cooled all year round), and the compressor stops running. At this time, refrigerant B directly uses the outdoor condenser to exchange heat with the outdoor low-temperature environment for condensation, and then flows to the power heat pipe 1021 through the refrigerant pump cabinet 1023 (at this time, the electronic expansion valve can be fully opened to a straight-through state, that is, no throttling, and the electronic expansion valve can be a large-caliber electronic expansion valve) to perform heat exchange and cooling in the room. The refrigerant B after absorbing heat is recycled to the room temperature condenser for condensation. In this way, it can be understood that the efficiency of heat exchange between the cold source side 1022 and the refrigerant B can be controlled by simply adjusting the temperature difference between refrigerant A and refrigerant B. Specifically, the temperature difference can be controlled by controlling the operating frequency of the compressor or starting and closing the compressor.

[0075] Specifically, in step S50, the units of the third pressure value and the fourth pressure value are Pa. The unit of the third preset time is second (s). That is, the pressure change rate is obtained as follows: pressure change rate = (third pressure value - fourth pressure value) / third preset time.

[0076] Preferably, the change rate threshold range is configured to be between 3kPa / s and 5kPa / s. It should be noted that if the change rate threshold is too large, it means that a faster response speed is required. At this time, the requirements of the cold source side 1022 will be higher, and the control cost will increase; if the change rate threshold is too small, it will cause frequent triggering of the cold source side 1022, which will also increase the control cost. Therefore, here, the change rate threshold range is configured to be between 3kPa / s and 5kPa / s.

[0077] Specifically, the value of the change rate threshold may be 3 kPa / s, 3.5 kPa / s, 4 kPa / s, 4.5 kPa / s, and 5 kPa / s. Of course, the specific value of the change rate threshold may be set according to actual needs.

[0078] like Figure 6 As shown, in one embodiment, after the refrigerant pump operates normally, the method for preventing the flow interruption of the refrigeration pump for the power heat pipe system also includes:

[0079] S110, obtaining the cooling demand of the load in the power heat pipe system;

[0080] S120, according to the refrigeration demand, set the superheat value of the refrigerant on the refrigerant pump side, and make the power heat pipe system operate at the superheat value. That is, set the superheat value of refrigerant B.

[0081] It can be understood that superheat refers to the difference between the superheat temperature and the saturation temperature of the refrigerant at the same evaporation pressure in the refrigeration cycle. By setting the superheat value of the refrigerant, the amount of refrigerant entering the end (evaporator) of the power heat pipe 1021 can be controlled. That is, according to this superheat value, how much refrigerant can be controlled to participate in heat exchange, so that the refrigeration demand meets the current requirements. Here, the refrigeration demand = (actual return air temperature - set temperature) / refrigeration deviation * 100% is calculated and judged. The return air temperature refers to the temperature of the air sucked from the inside of the end of the power heat pipe 1021. The end can be a back plate, between heat pipe rows, etc.

[0082] like Figure 7 As shown, further, in step S120, according to the cooling demand, setting the superheat value so that the power heat pipe system operates at the superheat value includes:

[0083] S121, when the cooling demand is greater than or equal to a first cooling demand threshold, setting the superheat value to a first superheat value, and operating the power heat pipe system at the first superheat value;

[0084] S122, when the cooling demand is less than the first cooling demand threshold and greater than or equal to the second cooling demand threshold, setting the superheat value to a second superheat value, and operating the power heat pipe system at the second superheat value;

[0085] S123, when the cooling demand is less than the second cooling demand threshold, setting the superheat value to a third superheat value, and operating the power heat pipe system at the third superheat value;

[0086] The first cooling demand threshold is smaller than the second cooling demand threshold.

[0087] In this way, according to different cooling needs, the operation of the corresponding power heat pipe system is further refined and controlled to ensure that there is enough refrigerant at the refrigerant pump to avoid the phenomenon of interruption. For example, when the cooling demand at the end of the power heat pipe is small, the superheat of the refrigerant in the end of the power heat pipe (in the back plate) can be increased. Specifically, by reducing the opening of the electronic expansion valve in the power heat pipe 1021, the amount of refrigerant in the heat exchanger is reduced, that is, the amount of refrigerant involved in the heat exchange is reduced, so that more refrigerant will be on one side of the liquid storage tank to avoid insufficient refrigerant inside the liquid storage tank, thereby preventing the refrigerant pump from interrupting. Generally speaking, reducing the opening of the electronic expansion valve in the power heat pipe 1021 will increase the superheat value; increasing the opening of the electronic expansion valve in the power heat pipe 1021 will reduce the superheat value. Here, the cooling demand at the end is actually the cooling demand required by the computer room.

[0088] In one embodiment, the first superheat value ranges from -1°C to ≤2°, the second superheat value ranges from 1°≤ to ​​≤3°, and the third superheat value ranges from 2°≤ to ​​≤5°.

[0089] Specifically, the first superheat value can be set to -1°C, -0.5°C, 0°C, 0.5°C, 1°C, 1.5°C, 2°C, etc. The second superheat value can be set to 1°C, 1.5°C, 2°C, 2.5°C, 3°C, etc. The third superheat value can be set to 2°C, 2.5°C, 3°C, 3.5°C, 4°C, 4.5°C, 5°C, etc.

[0090] For example, based on the above embodiments, Figures 3 to 7 As shown, a more specific refrigerant pump control method for a power heat pipe system includes:

[0091] After starting the refrigerant pump, obtain a first pressure value at the inlet of the refrigerant pump and a second pressure value at the outlet respectively; obtain a pressure difference according to the second pressure value and the first pressure value; if the pressure difference is less than or equal to the first preset pressure value, turn off the refrigerant pump; if the pressure difference is greater than the first preset pressure value, the refrigerant pump operates normally; start the refrigerant pump again, and obtain the first pressure value and the second pressure value respectively, obtain a pressure difference according to the second pressure value and the first pressure value, until the pressure difference is greater than the first preset pressure value and the refrigerant pump operates normally.

[0092] A plurality of pressure difference values ​​within a preset time range are obtained, and if the plurality of pressure difference values ​​are all less than or equal to a first preset pressure value, the refrigerant pump is turned off. After the refrigerant pump is turned off for a second preset time, the refrigerant pump is restarted. Here, the refrigerant pump is restarted after the refrigerant pump is turned off for a second preset time.

[0093] After the refrigerant pump operates normally, the third pressure value and the fourth pressure value at the refrigerant pump inlet are obtained at intervals of a third preset time, and if the pressure change rate is greater than the change rate threshold, the heat exchange efficiency between the cold source side 1022 and the refrigerant in the power heat pipe system is reduced. If the pressure change rate is greater than the change rate threshold, the heat exchange efficiency between the cold source side 1022 and the refrigerant in the power heat pipe system is increased.

[0094] After the refrigerant pump operates normally, the refrigeration demand of the load in the power heat pipe system is obtained, the superheat value is set according to the refrigeration demand, and the power heat pipe system is operated at the superheat value.

[0095] Specifically, when the cooling demand is greater than or equal to a first cooling demand threshold, the superheat value is set to the first superheat value, and the power heat pipe system operates at the first superheat value; when the cooling demand is less than the first cooling demand threshold, and greater than or equal to a second cooling demand threshold, the superheat value is set to the second superheat value, and the power heat pipe system operates at the second superheat value; when the cooling demand is less than the second cooling demand threshold, the superheat value is set to the third superheat value, and the power heat pipe system operates at the third superheat value.

[0096] It should be understood that, although the steps in the flowcharts involved in the above embodiments are displayed in sequence according to the indication of the arrows, these steps are not necessarily executed in sequence according to the order indicated by the arrows. Unless there is a clear explanation in this article, the execution of these steps is not strictly limited in order, and these steps can be executed in other orders. Moreover, at least a part of the steps in the flowcharts involved in the above embodiments may include multiple steps or multiple stages, and these steps or stages are not necessarily executed at the same time, but can be executed at different times, and the execution order of these steps or stages is not necessarily carried out in sequence, but can be executed in turn or alternately with other steps or at least a part of the steps or stages in other steps.

[0097] In one embodiment, a power heat pipe system is provided, which includes a processor, a memory, an input / output interface, a communication interface, a display unit and an input device. The processor, the memory and the input / output interface are connected through a system bus, and the communication interface, the display unit and the input device are connected to the system bus through the input / output interface. The processor of the power heat pipe system is used to provide computing and control capabilities. The memory of the power heat pipe system includes a non-volatile storage medium and an internal memory. The non-volatile storage medium stores an operating system and a computer program. The internal memory provides an environment for the operation of the operating system and the computer program in the non-volatile storage medium. The input / output interface of the power heat pipe system is used to exchange information between the processor and an external device. The communication interface of the power heat pipe system is used to communicate with an external terminal in a wired or wireless manner, and the wireless manner can be realized through WIFI, a mobile cellular network, NFC (near field communication) or other technologies. When the computer program is executed by the processor, a refrigerant pump control method for a power heat pipe system is realized. The display unit of the power heat pipe system is used to form a visually visible picture, which can be a display screen, a projection device or a virtual reality imaging device. The display screen can be a liquid crystal display screen or an electronic ink display screen, and the input device of the power heat pipe system can be a touch layer covered on the display screen, or a button, trackball or touchpad set on the power heat pipe system shell, or an external keyboard, touchpad or mouse.

[0098] Those skilled in the art will understand that Figure 8 The structure shown in the figure is only a block diagram of a part of the structure related to the scheme of the present application, and does not constitute a limitation on the power heat pipe system to which the scheme of the present application is applied. The specific power heat pipe system may include more or fewer components than those shown in the figure, or combine certain components, or have a different arrangement of components.

[0099] In one embodiment, a power heat pipe system is provided, including a memory and a processor, wherein a computer program is stored in the memory, and when the processor executes the computer program, the following steps are implemented:

[0100] After starting the refrigerant pump, respectively obtaining a first pressure value at an inlet of the refrigerant pump and a second pressure value at an outlet of the refrigerant pump;

[0101] Obtaining a pressure difference value according to the second pressure value and the first pressure value;

[0102] If the pressure difference is less than or equal to the first preset pressure value, turning off the refrigerant pump;

[0103] The refrigerant pump is started again, and the first pressure value and the second pressure value are respectively obtained again, and a pressure difference is obtained according to the second pressure value and the first pressure value, until the pressure difference is greater than the first preset pressure value, and the refrigerant pump operates normally.

[0104] In one embodiment, when the processor executes the computer program, the processor further implements the following steps:

[0105] Obtain multiple pressure difference values ​​within a preset time range;

[0106] If the multiple pressure difference values ​​are all less than or equal to the first preset pressure value, the refrigerant pump is turned off.

[0107] In one embodiment, when the processor executes the computer program, the processor further implements the following steps:

[0108] Acquire a third pressure value and a fourth pressure value at the inlet of the refrigerant pump at a third preset time interval respectively;

[0109] Determining a pressure change rate according to a third preset time, a third pressure value, and a fourth pressure value;

[0110] If the pressure change rate is greater than the change rate threshold, the heat exchange efficiency between the cold source side 1022 and the refrigerant in the power heat pipe system is reduced.

[0111] In one embodiment, when the processor executes the computer program, the processor further implements the following steps:

[0112] Obtain the cooling demand of the load in the power heat pipe system;

[0113] According to the refrigeration demand, the superheat value of the refrigerant on the refrigerant pump side is set, and the power heat pipe system is operated at the superheat value.

[0114] In one embodiment, when the processor executes the computer program, the processor further implements the following steps:

[0115] When the cooling demand is greater than or equal to the first cooling demand threshold, the superheat value is set to the first superheat value, and the power heat pipe system is operated at the first superheat value;

[0116] When the cooling demand is less than the first cooling demand threshold and greater than or equal to the second cooling demand threshold, the superheat value is set to the second superheat value, and the power heat pipe system is operated at the second superheat value;

[0117] When the cooling demand is less than the second cooling demand threshold, the superheat value is set to a third superheat value, and the power heat pipe system is operated at the third superheat value.

[0118] In one embodiment, a computer-readable storage medium is provided, on which a computer program is stored. When the computer program is executed by a processor, the following steps and the corresponding refrigerant pump control method for a power heat pipe system in any of the above embodiments are implemented:

[0119] After starting the refrigerant pump, respectively obtaining a first pressure value at an inlet of the refrigerant pump and a second pressure value at an outlet of the refrigerant pump;

[0120] Obtaining a pressure difference value according to the second pressure value and the first pressure value;

[0121] If the pressure difference is less than or equal to the first preset pressure value, turning off the refrigerant pump;

[0122] The refrigerant pump is started again, and the first pressure value and the second pressure value are obtained respectively, and a pressure difference is obtained according to the second pressure value and the first pressure value, until the pressure difference is greater than the first preset pressure value, and the refrigerant pump operates normally.

[0123] In one embodiment, a computer program product is provided, including a computer program, which, when executed by a processor, implements the following steps and the corresponding refrigerant pump control method for a power heat pipe system in any of the above embodiments:

[0124] After starting the refrigerant pump, respectively obtaining a first pressure value at an inlet of the refrigerant pump and a second pressure value at an outlet of the refrigerant pump;

[0125] Obtaining a pressure difference value according to the second pressure value and the first pressure value;

[0126] If the pressure difference is less than or equal to the first preset pressure value, turning off the refrigerant pump;

[0127] The refrigerant pump is started again, and the first pressure value and the second pressure value are respectively obtained again, and a pressure difference is obtained according to the second pressure value and the first pressure value, until the pressure difference is greater than the first preset pressure value, and the refrigerant pump operates normally.

[0128] It should be noted that the user information (including but not limited to user device information, user personal information, etc.) and data (including but not limited to data used for analysis, stored data, displayed data, etc.) involved in this application are all information and data authorized by the user or fully authorized by all parties, and the collection, use and processing of relevant data must comply with relevant laws, regulations and standards of relevant countries and regions.

[0129] Those skilled in the art can understand that all or part of the processes in the above-mentioned embodiment methods can be completed by instructing the relevant hardware through a computer program, and the computer program can be stored in a non-volatile computer-readable storage medium. When the computer program is executed, it can include the processes of the embodiments of the above-mentioned methods. Among them, any reference to the memory, database or other medium used in the embodiments provided in the present application can include at least one of non-volatile and volatile memory. Non-volatile memory can include read-only memory (ROM), magnetic tape, floppy disk, flash memory, optical memory, high-density embedded non-volatile memory, resistive random access memory (ReRAM), magnetoresistive random access memory (MRAM), ferroelectric random access memory (FRAM), phase change memory (PCM), graphene memory, etc. Volatile memory can include random access memory (RAM) or external cache memory, etc. As an illustration and not limitation, RAM can be in various forms, such as static random access memory (SRAM) or dynamic random access memory (DRAM). The database involved in each embodiment provided in this application may include at least one of a relational database and a non-relational database. Non-relational databases may include distributed databases based on blockchains, etc., but are not limited to this. The processor involved in each embodiment provided in this application may be a general-purpose processor, a central processing unit, a graphics processor, a digital signal processor, a programmable logic device, a data processing logic device based on quantum computing, etc., but are not limited to this.

[0130] The technical features of the above-described embodiments may be arbitrarily combined. To make the description concise, not all possible combinations of the technical features in the above-described embodiments are described. However, as long as there is no contradiction in the combination of these technical features, they should be considered to be within the scope of this specification.

[0131] The above-described embodiments only express several implementation methods of the present application, and the descriptions thereof are relatively specific and detailed, but they cannot be understood as limiting the scope of the patent application. It should be pointed out that, for a person of ordinary skill in the art, several variations and improvements can be made without departing from the concept of the present application, and these all belong to the protection scope of the present application. Therefore, the scope of patent protection of the present application shall be subject to the attached claims.

Claims

1. A refrigerant pump control method for a power heat pipe system, characterized in that: The refrigerant pump control method for the power heat pipe system includes: After starting the refrigerant pump, respectively obtaining a first pressure value at the inlet and a second pressure value at the outlet of the refrigerant pump; Obtaining a pressure difference value according to the second pressure value and the first pressure value; If the pressure difference is less than or equal to a first preset pressure value, shutting down the refrigerant pump; The refrigerant pump is started again, and the first pressure value and the second pressure value are respectively obtained again, and the pressure difference is obtained according to the second pressure value and the first pressure value, until the pressure difference is greater than the first preset pressure value, and the refrigerant pump operates normally.

2. The refrigerant pump control method for a power heat pipe system according to claim 1, characterized in that: If the pressure difference is less than or equal to the first preset pressure value, shutting down the refrigerant pump includes: Acquire a plurality of pressure difference values ​​within a preset time range; If the plurality of pressure difference values ​​are all less than or equal to the first preset pressure value, the refrigerant pump is turned off.

3. The refrigerant pump control method for a power heat pipe system according to claim 1 or 2, characterized in that: Restarting the refrigerant pump comprises: After the refrigerant pump is turned off for a second preset time, the refrigerant pump is started again.

4. The refrigerant pump control method for a power heat pipe system according to claim 1, characterized in that: After the refrigerant pump operates normally, the refrigerant pump control method for the power heat pipe system further includes: Acquire a third pressure value and a fourth pressure value at the inlet of the refrigerant pump at a third preset time interval respectively; determining a pressure change rate according to the third preset time, the third pressure value, and the fourth pressure value; If the pressure change rate is greater than the change rate threshold, the heat exchange efficiency between the cold source side and the refrigerant in the power heat pipe system is reduced.

5. The refrigerant pump control method for a power heat pipe system according to claim 4, characterized in that: The change rate threshold range is configured to be between 3 kPa / s and 5 kPa / s.

6. The refrigerant pump control method for a power heat pipe system according to claim 1, characterized in that: After the refrigerant pump operates normally, the method for preventing flow interruption of a refrigerant pump for a power heat pipe system further comprises: Obtain the cooling demand of the load in the power heat pipe system; According to the refrigeration demand, the superheat value of the refrigerant on one side of the refrigerant pump is set, and the power heat pipe system is operated at the superheat value.

7. The refrigerant pump control method for a power heat pipe system according to claim 6, characterized in that: According to the refrigeration demand, setting the superheat value so that the power heat pipe system operates at the superheat value includes: When the cooling demand is greater than or equal to a first cooling demand threshold, the superheat value is set to a first superheat value, and the power heat pipe system is operated at the first superheat value; When the cooling demand is less than a first cooling demand threshold and greater than or equal to a second cooling demand threshold, the superheat value is set to a second superheat value, and the power heat pipe system is operated at the second superheat value; When the cooling demand is less than the second cooling demand threshold, the superheat value is set to a third superheat value, and the power heat pipe system is operated at the third superheat value; The first cooling demand threshold is smaller than the second cooling demand threshold.

8. The refrigerant pump control method for a power heat pipe system according to claim 7, characterized in that: The first superheat value ranges from -1°C to ≤2°, the second superheat value ranges from 1°≤ to ​​≤3°, and the third superheat value ranges from 2°≤ to ​​≤5°.

9. A power heat pipe system, comprising a memory and a processor, characterized in that: The memory stores a computer program, and the processor is configured to run the computer program to execute the refrigerant pump control method for a power heat pipe system according to any one of claims 1 to 8.

10. A computer-readable storage medium having a computer program stored thereon, characterized in that: When the computer program is executed by a processor, the steps of the refrigerant pump control method for a power heat pipe system according to any one of claims 1 to 8 are implemented.

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