A control method of a phase change cold plate cooling system

Abstract

The present application relates to the technical field of refrigeration system, and specifically relates to a control method of a phase change cold plate cooling system, which comprises a first heat exchanger, a second heat exchanger, a third heat exchanger, an adjusting pipeline, a compressor, a driving pump, a liquid collecting main pipe, a gas collecting main pipe and a cooling branch; the adjusting pipeline is provided with a first flow adjusting valve; and the control method further comprises a heat exchange temperature detection step, a supercooling degree detection step, a superheating degree detection step and an adjusting step. By adjusting the rotating speed of the compressor, the opening degree of the first flow adjusting valve and the opening degree of the second flow adjusting valve, the refrigerant in the cooling plate can be kept in the gas-liquid two-phase region as much as possible; the refrigerant in the two-phase region boils in the cooling plate, the heat transfer coefficient is high, and the temperature of the battery in the battery box is reduced; the surface temperature of the cooling plate remains unchanged when the refrigerant is in the two-phase region, and the consistency of the internal temperature of the energy storage battery box is improved.

Description

Technical Field

[0001] This invention relates to the field of refrigeration system technology, and more specifically to a control method for a phase change cold plate cooling system. Background Technology

[0002] The performance, safety, and lifespan of energy storage batteries are affected by temperature. Excessively high temperatures can reduce battery life and even lead to thermal runaway. Battery boxes consist of multiple individual cells, and large temperature differences between cells can cause uneven charging and discharging, affecting battery life. Localized high temperatures within the battery box may cause internal short circuits in the batteries, further increasing the temperature and raising the risk of thermal runaway.

[0003] There are currently three types of refrigeration available on the market:

[0004] 1. Air-cooled direct expansion refrigeration: The cooling evaporator side is supplied with cold air by a fan. In this solution, due to the battery air duct problem, the battery temperature difference is concentrated between 8-10℃, which greatly affects the efficiency of the energy storage system.

[0005] 2. Ethylene glycol aqueous solution cold plate cooling: The ethylene glycol aqueous solution flows inside the cold plate. This method is inefficient, and poor layout can easily lead to uneven solution flow distribution among the cold plates, resulting in inconsistent battery temperatures. Currently, this type of system typically has a battery temperature difference of 5-8℃. Furthermore, liquid leakage poses a risk of short circuits to the battery.

[0006] Third, immersion liquid cooling uses insulating liquid to immerse the battery, which has high efficiency and good battery temperature difference of 2-5℃. However, the insulating liquid is expensive, the initial investment is large, and maintenance is very difficult. Summary of the Invention

[0007] The purpose of this invention is to address the aforementioned shortcomings in the prior art by providing a control method for a phase change cold plate cooling system.

[0008] The objective of this invention is achieved through the following technical solution: a control method for a phase change cold plate cooling system, comprising a first heat exchanger, a second heat exchanger, a third heat exchanger, a regulating pipeline, a compressor, a drive pump, a liquid collection main pipe, a gas collection main pipe, and several cooling branches; the first heat exchanger includes a first channel and a second channel; the third heat exchanger includes a third channel and a fourth channel; the first channel, the compressor, the second heat exchanger, and the third channel are sequentially connected end-to-end; the regulating pipeline is connected in parallel with the third channel; the regulating pipeline is equipped with a first flow regulating valve; one end of the second channel is connected to one end of the drive pump; the... The other end of the drive pump is connected to one end of the liquid collection main pipe through the fourth channel; the other end of the second channel is connected to one end of the gas collection main pipe; the cooling branch is located between the other end of the liquid collection main pipe and the other end of the gas collection main pipe; each cooling branch includes a liquid collection branch pipe, a gas collection branch pipe, a second flow regulating valve, and multiple cold plate assemblies; the cold plate assembly is provided with a cooling plate; one end of the liquid collection branch pipe is connected to the other end of the liquid collection main pipe; the other end of the liquid collection branch pipe is connected to one end of the gas collection branch pipe through the cold plate assembly; the other end of the gas collection branch pipe is connected to the other end of the gas collection main pipe; the second flow regulating valve is located in the liquid collection branch pipe;

[0009] It also includes the following steps:

[0010] Heat exchange temperature detection steps: Detect the actual temperature value at one end of the second channel and compare it with the preset temperature value;

[0011] Subcooling detection steps: Detect the actual subcooling value of the manifold and compare it with the preset subcooling value;

[0012] Superheat detection steps: Detect the actual superheat value of the gas collecting branch pipe and compare it with the preset superheat value;

[0013] Adjustment steps: Adjust the compressor speed according to the comparison between the actual temperature value and the preset temperature value; adjust the opening of the first flow regulating valve according to the comparison between the actual subcooling value and the preset subcooling value; adjust the opening of the second flow regulating valve according to the comparison between the actual superheat value and the preset superheat value, so that a gas-liquid mixture is formed in the cooling plate.

[0014] The present invention is further configured such that a first temperature sensor is provided at one end of the second channel; the first temperature sensor is used to detect the actual temperature value at one end of the second channel.

[0015] The present invention is further configured such that the liquid collection manifold is provided with a second temperature sensor and a second pressure sensor;

[0016] In the subcooling detection step, the corresponding second saturation temperature value is calculated based on the pressure value detected by the second pressure sensor; the actual subcooling value of the manifold is obtained by subtracting the temperature value detected by the second temperature sensor from the second saturation temperature value.

[0017] The present invention is further configured such that the gas collecting branch pipe is equipped with a third temperature sensor and a third pressure sensor;

[0018] In the superheat detection step, the corresponding third saturation temperature value is calculated based on the pressure value detected by the third pressure sensor; the actual superheat value of the gas collecting branch is obtained by subtracting the third saturation temperature value from the temperature value detected by the third temperature sensor.

[0019] The present invention is further configured such that, in the adjustment step, when the actual temperature value at one end of the second channel is greater than the preset temperature value, the actual temperature value at one end of the second channel is reduced by increasing the compressor speed to increase the heat exchange; when the actual temperature value at one end of the second channel is less than the preset temperature value, the actual temperature value at one end of the second channel is increased by reducing the compressor speed to decrease the heat exchange.

[0020] The present invention is further configured such that, in the adjustment step, when the actual value of the subcooling of the main liquid collector is greater than the preset value of subcooling, the opening of the first flow regulating valve is reduced to decrease the flow rate of refrigerant through the regulating pipeline, the flow rate of refrigerant through the third channel is increased, and the heating amount of the refrigerant at the inlet of the main liquid collector is increased, thereby reducing the actual value of the subcooling of the main liquid collector.

[0021] When the actual subcooling value of the main liquid collector is less than the preset subcooling value, the refrigerant flow through the regulating pipeline is increased by increasing the opening of the first flow regulating valve, the refrigerant flow through the third channel is reduced, and the heating amount of the refrigerant at the inlet of the main liquid collector is reduced, thereby increasing the actual subcooling value of the main liquid collector.

[0022] The present invention is further configured such that, in the adjustment step, when the actual value of the superheat of the gas collecting branch pipe is greater than the preset value of the superheat, the opening of the second flow regulating valve is increased to increase the flow rate of the refrigerant through the cold plate assembly, thereby increasing the heat exchange at the cooling plate and thus reducing the superheat of the gas collecting branch pipe.

[0023] When the actual superheat value of the gas collecting branch pipe is less than the preset superheat value, the flow rate of refrigerant through the cold plate assembly is reduced by adjusting the opening of the second flow regulating valve, thereby reducing the heat exchange at the cooling plate and increasing the superheat of the gas collecting branch pipe.

[0024] The present invention is further configured such that the preset value of the supercooling is 0℃-2℃.

[0025] The present invention is further configured such that the preset value of the superheat is 1℃-3℃.

[0026] The present invention is further configured such that a liquid storage tank is provided between the drive pump and one end of the second channel; a needle valve or a first pressure sensor is provided between the liquid storage tank and one end of the second channel;

[0027] It also includes refrigerant detection and adjustment steps: detecting the refrigerant level in the receiver tank, and adding refrigerant at the needle valve when the level is low.

[0028] The beneficial effects of this invention are as follows: By adjusting the compressor speed, the opening of the first flow regulating valve, and the opening of the second flow regulating valve, this invention can keep the refrigerant in the cooling plate in the gas-liquid two-phase region as much as possible. When in the two-phase region, the refrigerant boils in the cooling plate, resulting in a high heat transfer coefficient and reducing the temperature of the battery in the battery box. When in the two-phase region, the surface temperature of the cooling plate remains unchanged, improving the temperature uniformity inside the energy storage battery box. Attached Figure Description

[0029] The invention will be further illustrated with reference to the accompanying drawings, but the embodiments in the drawings do not constitute any limitation on the invention. For those skilled in the art, other drawings can be obtained based on the following drawings without any creative effort.

[0030] Figure 1 This is a system schematic diagram of the present invention;

[0031] Figure 2 This is the control principle diagram of the present invention;

[0032] The components are as follows: 1. First heat exchanger; 11. First channel; 12. Second channel; 13. First temperature sensor; 14. Needle valve; 21. Second heat exchanger; 22. Compressor; 3. Third heat exchanger; 31. Third channel; 32. Fourth channel; 4. Regulating pipeline; 41. First flow regulating valve; 51. Drive pump; 52. Liquid collection main pipe; 53. Second temperature sensor; 54. Second pressure sensor; 55. Gas collection main pipe; 56. Liquid storage tank; 6. Cooling branch; 61. Liquid collection branch pipe; 62. Second flow regulating valve; 63. Gas collection branch pipe; 65. Third temperature sensor; 66. Third pressure sensor; 7. Cold plate assembly; 71. Cooling plate. Detailed Implementation

[0033] The present invention will be further described in conjunction with the following embodiments.

[0034] Depend on Figures 1 to 2As can be seen, the control method of the phase change cold plate cooling system described in this embodiment includes a first heat exchanger 1, a second heat exchanger 21, a third heat exchanger 3, a regulating pipeline 4, a compressor 22, a drive pump 51, a liquid collection main pipe 52, a gas collection main pipe 55, and several cooling branch pipes 6; the first heat exchanger 1 includes a first channel 11 and a second channel 12; the third heat exchanger 3 includes a third channel 31 and a fourth channel 32; the first channel 11, compressor 22, second heat exchanger 21, and third channel 31 are connected end to end in sequence; the regulating pipeline 4 is arranged in parallel with the third channel 31; the regulating pipeline 4 is provided with a first flow regulating valve 41; one end of the second channel 12 is connected to one end of the drive pump 51; the drive pump 51... The other end of the first channel 12 is connected to one end of the main liquid collection pipe 52 via the fourth channel 32; the other end of the second channel 12 is connected to one end of the main gas collection pipe 55; the cooling branch 6 is located between the other end of the main liquid collection pipe 52 and the other end of the main gas collection pipe 55; each cooling branch 6 includes a liquid collection branch pipe 61, a gas collection branch pipe 63, a second flow regulating valve 62, and multiple cold plate assemblies 7; the cold plate assembly 7 is provided with a cooling plate 71; one end of the liquid collection branch pipe 61 is connected to the other end of the main liquid collection pipe 52; the other end of the liquid collection branch pipe 61 is connected to one end of the gas collection branch pipe 63 via the cold plate assembly 7; the other end of the gas collection branch pipe 63 is connected to the other end of the main gas collection pipe 55; the second flow regulating valve 62 is located on the liquid collection branch pipe 61;

[0035] It also includes the following steps:

[0036] Heat exchange temperature detection steps: Detect the actual temperature value at one end of the second channel 12 and compare it with the preset temperature value;

[0037] Subcooling detection steps: Detect the actual subcooling value of the liquid collection manifold 52 and compare it with the preset subcooling value;

[0038] Superheat detection steps: Detect the actual superheat value of the gas collecting branch pipe 63 and compare it with the preset superheat value;

[0039] Adjustment steps: Adjust the speed of compressor 22 according to the comparison between the actual temperature value and the preset temperature value; adjust the opening of the first flow regulating valve 41 according to the comparison between the actual subcooling value and the preset subcooling value; adjust the opening of the second flow regulating valve 62 according to the comparison between the actual superheat value and the preset superheat value, so that a gas-liquid mixture is formed in the cooling plate 71.

[0040] Specifically, in the control method of the phase change cold plate cooling system described in this embodiment, when in use, the first channel 11, compressor 22, second heat exchanger 21, third channel 31 and regulating pipeline 4 constitute a compression refrigeration system, and the refrigerant flows in two directions: first channel 11-compressor 22-second heat exchanger 21-third channel 31-first channel 11, and first channel 11-compressor 22-second heat exchanger 21-regulating pipeline 4-first channel 11;

[0041] In addition, the second channel 12, drive pump 51, fourth channel 32, liquid collection main pipe 52, cooling branch pipe 6 and gas collection main pipe 55 constitute a cold plate cooling system, and the refrigerant flow direction is as follows: second channel 12-drive pump 51-fourth channel 32-liquid collection main pipe 52-liquid collection branch pipe 61-cold plate assembly 7-gas collection branch pipe 63-gas collection main pipe 55-second channel 12.

[0042] Through the above settings, the speed of compressor 22 can be adjusted according to the comparison between the actual temperature value and the preset temperature value, thereby changing the heat exchange of the first heat exchanger 1 and thus changing the outlet temperature at the second channel 12. In addition, by setting a first flow regulating valve 41, the opening of the first flow regulating valve 41 can be adjusted according to the comparison between the actual subcooling value and the preset subcooling value, thereby changing the refrigerant flow of the third channel 31 and thus changing the inlet temperature of the liquid collection manifold 52. Furthermore, a second flow regulating valve 62 is set in each cooling branch 6 to detect the actual superheat value of the gas collecting branch 63 and compare it with the preset superheat value to control the opening of the second flow regulating valve 62, thereby changing the flow of refrigerant through the cold plate assembly 7, changing the heat exchange of the cooling plate 71, and thus adjusting the temperature value of the gas collecting branch 63.

[0043] In this embodiment, by adjusting the speed of the compressor 22, the opening of the first flow regulating valve 41, and the opening of the second flow regulating valve 62, the refrigerant in the cooling plate 71 can be kept in the gas-liquid two-phase critical region as much as possible. When in the two-phase region, the refrigerant boils in the cooling plate, resulting in a high heat transfer coefficient and reducing the temperature of the battery in the battery box. When in the two-phase region, the surface temperature of the cooling plate 71 remains unchanged, improving the temperature consistency inside the energy storage battery box.

[0044] In the control method of the phase change cold plate cooling system described in this embodiment, a first temperature sensor 13 is provided at one end of the second channel 12; the first temperature sensor 13 is used to detect the actual temperature value at one end of the second channel 12. In the adjustment step of the control method of the phase change cold plate cooling system described in this embodiment, when the actual temperature value at one end of the second channel 12 is greater than the preset temperature value, the actual temperature value at one end of the second channel 12 is reduced by increasing the speed of the compressor 22 to increase the heat exchange; when the actual temperature value at one end of the second channel 12 is less than the preset temperature value, the actual temperature value at one end of the second channel 12 is increased by decreasing the speed of the compressor 22 to decrease the heat exchange.

[0045] Specifically, the low-temperature refrigerant of the compression refrigeration system absorbs heat from the refrigerant of the cold plate cooling system in the first heat exchanger 1. The first temperature sensor 13 is used to measure the actual temperature of the refrigerant at the outlet of the second channel 12 in the first heat exchanger 1. When the actual temperature is higher than the set temperature, the speed of the compressor 22 is increased to increase the heat exchange and lower the actual temperature. When the actual temperature is lower than the set temperature or the set temperature range, the speed of the compressor 22 is reduced to decrease the heat exchange and raise the actual temperature, thereby keeping the evaporation temperature of the refrigerant in the cold plate cooling system within a reasonable and suitable range, thereby controlling the temperature of the battery in the battery box to remain within a reasonable range.

[0046] The control method of a phase change cold plate cooling system described in this embodiment includes a second temperature sensor 53 and a second pressure sensor 54 in the liquid collection manifold 52.

[0047] In the subcooling detection step, the corresponding second saturation temperature value is calculated based on the pressure value detected by the second pressure sensor 54; the actual subcooling value of the liquid collection manifold 52 is obtained by subtracting the temperature value detected by the second temperature sensor 53 from the second saturation temperature value.

[0048] In the control method of the phase change cold plate cooling system described in this embodiment, when the actual value of the subcooling of the liquid collection manifold 52 is greater than the preset value of subcooling, the opening of the first flow regulating valve 41 is reduced to decrease the flow rate of refrigerant through the regulating pipe 4, and the flow rate of refrigerant through the third channel 31 is increased to increase the heating amount of the refrigerant at the inlet of the liquid collection manifold 52, thereby reducing the actual value of the subcooling of the liquid collection manifold 52.

[0049] When the actual subcooling value of the main liquid collector 52 is less than the preset subcooling value, the opening of the first flow regulating valve 41 is increased to increase the refrigerant flow through the regulating pipe 4, while the refrigerant flow through the third channel 31 is reduced, thereby reducing the amount of refrigerant heated at the inlet of the main liquid collector 52, which in turn increases the actual subcooling value of the main liquid collector 52.

[0050] Specifically, when the actual subcooling value is greater than 0, the subcooled refrigerant enters the cold plate assembly 7 and undergoes sensible heat exchange, causing the refrigerant temperature to rise and the cooling plate 71 temperature to rise as well, resulting in poor temperature uniformity between the batteries. Therefore, it is necessary to control the actual subcooling value to a small value (the preset subcooling value) so that the refrigerant can enter the two-phase region in the cooling plate 71 as quickly as possible. Through the above adjustment, the actual subcooling value is eventually made equal to the preset subcooling value. The refrigerant with low subcooling value is more likely to become a gas-liquid mixed two-phase state after passing through the throttling valve of the cold plate assembly 7, making the temperature at the cooling plate 71 more uniform and the temperature difference smaller, ultimately making the temperature between the batteries in the battery box tend to be uniform.

[0051] The control method of the phase change cold plate cooling system described in this embodiment includes a third temperature sensor 65 and a third pressure sensor 66 in the gas collecting branch pipe 63.

[0052] In the superheat detection step, the corresponding third saturation temperature value is calculated based on the pressure value detected by the third pressure sensor 66; the actual superheat value of the gas collecting branch pipe 63 is obtained by subtracting the third saturation temperature value from the temperature value detected by the third temperature sensor 65.

[0053] In the control method of the phase change cold plate cooling system described in this embodiment, when the actual value of the superheat of the gas collecting branch pipe 63 is greater than the preset value of the superheat, the opening of the second flow regulating valve 62 is increased to increase the flow rate of the refrigerant through the cold plate assembly 7, thereby increasing the heat exchange at the cooling plate 71 and reducing the superheat of the gas collecting branch pipe 63.

[0054] When the actual superheat value of the gas collecting branch pipe 63 is less than the preset superheat value, the flow rate of refrigerant through the cold plate assembly 7 is reduced by adjusting the opening of the second flow regulating valve 62, thereby reducing the heat exchange at the cooling plate 71 and increasing the superheat of the gas collecting branch pipe 63.

[0055] Specifically, when the actual superheat value is greater than 0, the refrigerant at the outlet of the cold plate assembly 7 is in a gaseous state. When the refrigerant is in a gaseous state in the last part of the cold plate assembly 7, its temperature rise is large, which is not conducive to the uniformity of the surface temperature of the cooling plate 71 and makes the temperature uniformity between the batteries in the battery box worse. Therefore, it is necessary to control the actual superheat value to a small value (the superheat preset value) so that the refrigerant is kept in a two-phase region of gas-liquid mixture in the cooling plate 71.

[0056] Through the above adjustments, the actual superheat value is finally made equal to the preset superheat value. This keeps the refrigerant in the cooling plate 71 in a two-phase region of gas-liquid mixture, thereby making the temperature at the cooling plate 71 more uniform and the temperature difference smaller, ultimately making the temperature between the batteries in the battery box tend to be uniform.

[0057] The control method for a phase change cold plate cooling system described in this embodiment has a preset subcooling value of 0℃-2℃. This setting facilitates a more uniform gas-liquid two-phase state, resulting in a more uniform temperature and smaller temperature difference at the cooling plate 71, ultimately leading to a more consistent temperature between the batteries within the battery box.

[0058] The control method for a phase change cold plate cooling system described in this embodiment has a superheat preset value of 1℃-3℃. Through this setting, the refrigerant in the cooling plate 71 can be kept in a two-phase region that maintains a gas-liquid mixture, thereby making the temperature at the cooling plate 71 more uniform, reducing the temperature difference, and ultimately making the temperature between the batteries in the battery box more consistent.

[0059] In this embodiment, a control method for a phase change cold plate cooling system is described, wherein a liquid storage tank 56 is provided between the drive pump 51 and one end of the second channel 12; a needle valve 14 or a first pressure sensor is provided between the liquid storage tank 56 and one end of the second channel 12.

[0060] It also includes a refrigerant detection and adjustment procedure: detect the refrigerant level in the liquid receiver 56, and when the level is low, add refrigerant at the needle valve 14.

[0061] Specifically, when the drive pump 51 is at a low speed, the liquid receiver 56 is used to store excess refrigerant. The refrigerant level in the liquid receiver 56 can be used to determine whether the refrigerant in the cold plate cooling system is sufficient. When there is a lack of refrigerant, refrigerant is added at the needle valve 14 by an external refrigerant charging machine.

[0062] In this embodiment, the refrigerant boils in the cooling plate 71, exhibiting a high heat transfer coefficient, which solves the heat dissipation problem of high heat flux density energy storage batteries. A phase change process occurs within the cooling plate 71, ensuring that the refrigerant exists in both gas and liquid phases, and that the temperature of the cooling plate 71 remains essentially constant, thus guaranteeing the temperature uniformity of the energy storage battery. Compared to a gas-liquid two-phase state, the pure liquid refrigerant allows for better flow distribution, ensuring uniform flow distribution. At atmospheric pressure, the refrigerant is gaseous; if the cooling plate 71 is damaged, causing refrigerant leakage, the refrigerant will instantly vaporize, preventing short circuits in the energy storage battery and ensuring battery safety. For immersion liquid cooling, the problems of initial investment and maintenance difficulties are solved. It also effectively ensures the temperature uniformity of the cooling plate 71 and the stability of the system.

[0063] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention, and are not intended to limit the scope of protection of the present invention. Although the present invention has been described in detail with reference to preferred embodiments, those skilled in the art should understand that modifications or equivalent substitutions can be made to the technical solutions of the present invention without departing from the essence and scope of the technical solutions of the present invention.

Claims

1. A control method for a phase change cold plate cooling system, characterized in that: The system includes a first heat exchanger (1), a second heat exchanger (21), a third heat exchanger (3), a regulating pipeline (4), a compressor (22), a drive pump (51), a liquid collection main pipe (52), a gas collection main pipe (55), and several cooling branches (6); the first heat exchanger (1) includes a first channel (11) and a second channel (12); the third heat exchanger (3) includes a third channel (31) and a fourth channel (32); the first channel (11), the compressor (22), the second heat exchanger (21), and the third channel (31) are connected end to end in sequence; the regulating pipeline (4) is connected in parallel with the third channel (31); the regulating pipeline (4) is equipped with a first flow regulating valve (41); one end of the second channel (12) is connected to one end of the drive pump (51); the other end of the drive pump (51) is connected through the fourth channel. One end of the channel (32) is connected to one end of the liquid collection main pipe (52); the other end of the second channel (12) is connected to one end of the gas collection main pipe (55); the cooling branch (6) is located between the other end of the liquid collection main pipe (52) and the other end of the gas collection main pipe (55); each cooling branch (6) includes a liquid collection branch pipe (61), a gas collection branch pipe (63), a second flow regulating valve (62), and multiple cold plate assemblies (7); the cold plate assembly (7) is provided with a cooling plate (71); one end of the liquid collection branch pipe (61) is connected to the other end of the liquid collection main pipe (52); the other end of the liquid collection branch pipe (61) is connected to one end of the gas collection branch pipe (63) through the cold plate assembly (7); the other end of the gas collection branch pipe (63) is connected to the other end of the gas collection main pipe (55); the second flow regulating valve (62) is located on the liquid collection branch pipe (61); It also includes the following steps: Heat exchange temperature detection steps: Detect the actual temperature value at one end of the second channel (12) and compare it with the preset temperature value; Subcooling detection steps: Detect the actual subcooling value of the liquid collection manifold (52) and compare it with the preset subcooling value; Superheat detection steps: Detect the actual superheat value of the gas collecting branch pipe (63) and compare it with the preset superheat value; Adjustment steps: Adjust the speed of compressor (22) according to the comparison between actual temperature value and preset temperature value, adjust the opening of first flow regulating valve (41) according to the comparison between actual subcooling value and preset subcooling value, and adjust the opening of second flow regulating valve (62) according to the comparison between actual superheat value and preset superheat value, so that a gas-liquid mixture is formed in cooling plate (71).

2. The control method for a phase change cold plate cooling system according to claim 1, characterized in that: A first temperature sensor (13) is provided at one end of the second channel (12); the first temperature sensor (13) is used to detect the actual temperature value at one end of the second channel (12).

3. The control method for a phase change cold plate cooling system according to claim 1, characterized in that: The main liquid collection pipe (52) is equipped with a second temperature sensor (53) and a second pressure sensor (54); In the supercooling detection step, the corresponding second saturation temperature value is calculated based on the pressure value detected by the second pressure sensor (54); The actual value of the subcooling of the main liquid collector (52) is obtained by subtracting the temperature value detected by the second temperature sensor (53) from the second saturation temperature value.

4. The control method for a phase change cold plate cooling system according to claim 1, characterized in that: The gas collecting branch pipe (63) is equipped with a third temperature sensor (65) and a third pressure sensor (66); In the superheat detection step, the corresponding third saturation temperature value is calculated based on the pressure value detected by the third pressure sensor (66); the actual superheat value of the gas collecting branch pipe (63) is obtained by subtracting the third saturation temperature value from the temperature value detected by the third temperature sensor (65).

5. The control method for a phase change cold plate cooling system according to claim 1, characterized in that: In the adjustment step, when the actual temperature value at one end of the second channel (12) is greater than the preset temperature value, the actual temperature value at one end of the second channel (12) is reduced by increasing the speed of the compressor (22) to increase the heat exchange; when the actual temperature value at one end of the second channel (12) is less than the preset temperature value, the actual temperature value at one end of the second channel (12) is increased by reducing the speed of the compressor (22) to decrease the heat exchange.

6. The control method for a phase change cold plate cooling system according to claim 1, characterized in that: In the adjustment step, when the actual value of the subcooling of the main liquid collector (52) is greater than the preset value of subcooling, the opening of the first flow regulating valve (41) is reduced to decrease the flow rate of refrigerant through the regulating pipeline (4), increase the flow rate of refrigerant in the third channel (31), and increase the heating amount of refrigerant at the inlet of the main liquid collector (52), thereby reducing the actual value of the subcooling of the main liquid collector (52). When the actual value of the subcooling of the main liquid collector (52) is less than the preset value of subcooling, the refrigerant flow through the regulating pipe (4) is increased by increasing the opening of the first flow regulating valve (41), the refrigerant flow through the third channel (31) is reduced, and the amount of heating of the refrigerant at the inlet of the main liquid collector (52) is reduced, thereby increasing the actual value of the subcooling of the main liquid collector (52).

7. The control method for a phase change cold plate cooling system according to claim 1, characterized in that: In the adjustment step, when the actual value of the superheat of the gas collecting branch pipe (63) is greater than the preset value of superheat, the flow rate of refrigerant through the cold plate assembly (7) is increased by increasing the opening of the second flow regulating valve (62), thereby increasing the heat exchange at the cooling plate (71) and thus reducing the superheat of the gas collecting branch pipe (63). When the actual superheat value of the gas collecting branch pipe (63) is less than the preset superheat value, the flow rate of refrigerant through the cold plate assembly (7) is reduced by adjusting the opening of the second flow regulating valve (62), thereby reducing the heat exchange at the cooling plate (71) and increasing the superheat of the gas collecting branch pipe (63).

8. The control method for a phase change cold plate cooling system according to claim 1, characterized in that: The preset value for the supercooling is 0℃-2℃.

9. The control method for a phase change cold plate cooling system according to claim 1, characterized in that: The preset value for superheat is 1℃-3℃.

10. The control method for a phase change cold plate cooling system according to claim 1, characterized in that: A liquid storage tank (56) is provided between the drive pump (51) and one end of the second channel (12); a needle valve (14) or a first pressure sensor is provided between the liquid storage tank (56) and one end of the second channel (12); It also includes a refrigerant detection and adjustment step: detect the refrigerant level in the liquid receiver (56), and when the level is low, add refrigerant at the needle valve (14).

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