A control method for a wind-liquid fusion heating and cooling phase change cold plate temperature control system

Abstract

The present application relates to the technical field of refrigeration system, and particularly relates to a control method of a wind-liquid fusion cold and warm phase change cold plate temperature control system, which comprises an indoor heat exchanger, an outdoor heat exchanger, an intermediate heat exchanger, a four-way valve, a compressor, a driving pump, a liquid collecting main pipe, a gas collecting main pipe and a plurality of cooling branches. Each cooling branch comprises a liquid collecting branch pipe, a gas collecting branch pipe, a flow regulating valve and a plurality of cold plate assemblies. The control method further comprises a mode selection step, a cold plate temperature detection step, a gas collecting main pipe superheat detection step, a gas collecting branch pipe superheat detection step and an adjusting step. The present application enables the refrigerant in the cold plate assembly to be in a gas-liquid two-phase state as much as possible, while ensuring the uniformity of the flow rate of each flow path. In winter, the indoor air temperature can also be heated to keep the battery temperature within a reasonable range.

Description

Technical Field

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

[0002] The performance, safety, and lifespan of energy storage batteries are affected by temperature. Excessively high temperatures reduce battery life and can even lead to thermal runaway. Battery packs consist of multiple individual cells; large temperature differences between cells can cause uneven charging and discharging, impacting battery life. Localized high temperatures within the battery pack can lead to internal short circuits, further increasing the temperature and the risk of thermal runaway. Energy storage batteries are significantly affected by low temperatures; their charging and discharging performance deteriorates drastically in cold environments. Low-temperature discharge limits the initial discharge power, resulting in poor performance; low-temperature charging reduces the activity of the electrolyte and electrode materials, and improper high-current charging can permanently reduce the battery's usable capacity.

[0003] Currently available refrigeration methods include:

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

[0005] 2. Ethylene glycol aqueous solution cooling plate: The ethylene glycol aqueous solution flows inside the cooling plate, which is inefficient and can easily cause inconsistent battery temperatures; the lifespan of ethylene glycol aqueous solution is relatively short, generally requiring replacement every 3 to 5 years; at the same time, there is a risk of short circuit if the liquid leaks.

[0006] In addition, the current heating methods for energy storage batteries are PTC and heating film, both of which are inefficient. 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 wind-liquid fusion-type heating and cooling phase change cold plate temperature control system.

[0008] The objective of this invention is achieved through the following technical solution: a control method for a wind-liquid integrated cooling and heating phase change plate temperature control system, comprising an indoor heat exchanger, an outdoor heat exchanger, an intermediate heat exchanger, a four-way valve, a compressor, a drive pump, a liquid manifold, a gas manifold, and several cooling branches; the four-way valve is used to connect one end of the compressor to one end of the outdoor heat exchanger and the other end of the compressor to one end of the indoor heat exchanger, or to connect one end of the compressor to one end of the indoor heat exchanger and the other end of the compressor to one end of the outdoor heat exchanger; the other end of the outdoor heat exchanger is connected to the other end of the indoor heat exchanger; the intermediate heat exchanger includes a first... The system includes a first channel and a second channel; the first channel is located between one end of the outdoor heat exchanger and one end of the indoor heat exchanger; a solenoid valve is installed between the first channel and the other end of the outdoor heat exchanger; the second channel, drive pump, liquid collection main pipe, cooling branch pipe, and gas collection main pipe are connected end to end in sequence; each cooling branch pipe includes a liquid collection branch pipe, a gas collection branch pipe, a flow regulating valve, and multiple cold plate assemblies; one end of the liquid collection branch pipe is connected to 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 gas collection main pipe; the flow regulating valve is located on the liquid collection branch pipe; the cold plate assembly holds the components to be cooled;

[0009] It also includes the following steps:

[0010] Mode selection steps: Select either cooling mode or heating mode based on the indoor temperature;

[0011] Cold plate temperature detection steps: Detect the actual temperature of the component to be cooled and compare it with the preset temperature value;

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

[0013] Superheat detection steps for gas collecting branch pipe: Detect the actual value of the second superheat of the gas collecting branch pipe and compare it with the preset value of the second superheat;

[0014] Adjustment steps: Adjust the compressor speed according to the comparison between the actual temperature value and the preset temperature value; adjust the drive pump speed according to the comparison between the actual first superheat value and the preset first superheat value; adjust the opening of the flow regulating valve according to the comparison between the actual second superheat value and the preset second superheat value, so that a gas-liquid mixture is formed in the cold plate assembly.

[0015] The present invention is further configured such that the cold plate assembly includes a cooling plate, a throttle valve, and a first temperature sensor;

[0016] The other end of the liquid collecting branch pipe is connected to one end of the gas collecting branch pipe after passing through a throttle valve and a cooling plate in sequence; the heat dissipation component is located on the cooling plate; the first temperature sensor is located on the heat dissipation component; the first temperature sensor is used to detect the actual temperature value of the cold plate assembly.

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

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

[0019] The present invention is further configured such that a third temperature sensor and a third pressure sensor are provided between the gas collecting main pipe and the second channel;

[0020] In the superheat detection step of the gas collecting manifold, the corresponding third saturation temperature value is calculated based on the pressure value detected by the third pressure sensor; the actual value of the first superheat of the gas collecting manifold is obtained by subtracting the third saturation temperature value from the temperature value detected by the third temperature sensor.

[0021] The present invention is further configured such that, in the adjustment step, when the actual temperature value of the cold plate assembly is greater than the preset temperature value, the compressor speed is increased; when the actual temperature value of the cold plate assembly is less than the preset temperature value, the compressor speed is decreased.

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

[0023] The present invention is further configured such that, in the adjustment step, when the actual value of the first superheat of the gas collecting main pipe is greater than the preset value of the first superheat, the speed of the drive pump is increased to increase the flow rate of the refrigerant through the cooling branch, thereby reducing the actual value of the first superheat; when the actual value of the first superheat of the gas collecting main pipe is less than the preset value of the first superheat, the speed of the drive pump is reduced to decrease the flow rate of the refrigerant through the cooling branch, thereby increasing the actual value of the first superheat.

[0024] The present invention is further configured such that the preset value of the second superheat is 1℃-3℃.

[0025] The present invention is further configured such that the preset value of the first superheat is 1.5℃-3.5℃.

[0026] The present invention is further configured such that, in the mode selection step, when entering the cooling mode, the four-way valve connects one end of the compressor to one end of the outdoor heat exchanger and the other end of the compressor to one end of the indoor heat exchanger, and the solenoid valve is in the conducting state; when entering the heating mode, the four-way valve connects one end of the compressor to one end of the indoor heat exchanger and the other end of the compressor to one end of the outdoor heat exchanger, and the solenoid valve is in the closed state.

[0027] The beneficial effects of this invention are: the refrigerant in the cold plate assembly is kept in a gas-liquid two-phase state as much as possible, while ensuring the uniformity of flow rate in each flow path; in winter, it can also heat the indoor air temperature and keep the battery temperature within a reasonable range. Attached Figure Description

[0028] 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.

[0029] Figure 1 This is a system schematic diagram of the present invention;

[0030] Figure 2 This is the control principle diagram of the present invention;

[0031] The components are as follows: 1. Indoor heat exchanger; 2. Outdoor heat exchanger; 21. Solenoid valve; 3. Intermediate heat exchanger; 31. First channel; 32. Second channel; 41. Four-way valve; 42. Compressor; 51. Drive pump; 6. Liquid manifold; 7. Gas manifold; 71. Third temperature sensor; 72. Third pressure sensor; 8. Cooling branch; 81. Liquid manifold; 82. Flow regulating valve; 84. Gas manifold; 85. Second temperature sensor; 86. Second pressure sensor; 9. Cold plate assembly; 91. Cooling plate; 92. Throttling valve; 93. Component to be cooled; 94. First temperature sensor. Detailed Implementation

[0032] The present invention will be further described in conjunction with the following embodiments.

[0033] Depend on Figures 1 to 2As can be seen, the control method of the air-liquid integrated cooling and heating phase change plate temperature control system described in this embodiment includes an indoor heat exchanger 1, an outdoor heat exchanger 2, an intermediate heat exchanger 3, a four-way valve 41, a compressor 42, a drive pump 51, a liquid manifold 6, a gas manifold 7, and several cooling branches 8; the four-way valve 41 is used to connect one end of the compressor 42 to one end of the outdoor heat exchanger 2 and the other end of the compressor 42 to one end of the indoor heat exchanger 1, or to connect one end of the compressor 42 to one end of the indoor heat exchanger 1 and the other end of the compressor 42 to one end of the outdoor heat exchanger 2; the other end of the outdoor heat exchanger 2 is connected to the other end of the indoor heat exchanger 1; the intermediate heat exchanger 3 includes a first channel 31 and a second channel 32; the first channel 31 is located in... Between the other end of the outdoor heat exchanger 2 and one end of the indoor heat exchanger 1; a solenoid valve 21 is provided between the first channel 31 and the other end of the outdoor heat exchanger 2; the second channel 32, drive pump 51, liquid collection main pipe 6, cooling branch 8 and gas collection main pipe 7 are connected end to end in sequence; each cooling branch 8 includes a liquid collection branch pipe 81, a gas collection branch pipe 84, a flow regulating valve 82 and multiple cold plate assemblies 9; one end of the liquid collection branch pipe 81 is connected to the liquid collection main pipe 6; the other end of the liquid collection branch pipe 81 is connected to one end of the gas collection branch pipe 84 through the cold plate assembly 9; the other end of the gas collection branch pipe 84 is connected to the gas collection main pipe 7; the flow regulating valve 82 is provided on the liquid collection branch pipe 81; the cold plate assembly 9 holds a heat dissipation component 93; wherein the heat dissipation component 93 can be a battery box that needs to be cooled.

[0034] It also includes the following steps:

[0035] Mode selection steps: Select either cooling mode or heating mode based on the indoor temperature;

[0036] Cold plate temperature detection steps: Detect the actual temperature of the heat dissipation component 93 and compare it with the preset temperature value;

[0037] Superheat detection steps for gas collecting manifold 7: Detect the actual value of the first superheat of gas collecting manifold 7 and compare it with the preset value of the first superheat;

[0038] Superheat detection steps for gas collecting branch pipe 84: Detect the actual value of the second superheat of gas collecting branch pipe 84 and compare it with the preset value of the second superheat;

[0039] Adjustment steps: Adjust the speed of compressor 42 according to the comparison between the actual temperature value and the preset temperature value; adjust the speed of drive pump 51 according to the comparison between the actual value of first superheat and the preset value of first superheat; adjust the opening of flow regulating valve 82 according to the comparison between the actual value of second superheat and the preset value of second superheat, so that a gas-liquid mixture is formed in the cold plate assembly 9.

[0040] Specifically, when the system is in cooling mode, the four-way valve 41 connects one end of the compressor 42 to one end of the outdoor heat exchanger 2 and the other end of the compressor 42 to one end of the indoor heat exchanger 1, while the solenoid valve 21 is in the conducting state; at this time, the refrigerant flow of the compressor 42 circulation circuit is in two directions, one is compressor 42-four-way valve 41-outdoor heat exchanger 2-indoor heat exchanger 1-four-way valve 41-compressor 42, and the other is compressor 42-four-way valve 41-outdoor heat exchanger 2-first channel 31-four-way valve 41-compressor 42;

[0041] In addition, the second channel 32, drive pump 51, liquid collection main pipe 6, cooling branch pipe 8 and gas collection main pipe 7 constitute a cold plate cooling system, and the refrigerant flow direction is: second channel 32-drive pump 51-liquid collection main pipe 6-cooling branch pipe 8-gas collection main pipe 7-second channel 32.

[0042] With the above settings, the heat exchange of the intermediate heat exchanger 3 can be changed by controlling the speed of the compressor 42, thereby changing the temperature of the cooling branch 8; in addition, by setting a flow regulating valve 82 in each cooling branch 8, the flow rate of the refrigerant through the cold plate assembly 9 can be changed by changing the opening degree of the flow regulating valve 82, thereby changing the superheat of the outlet of the cold plate assembly 9; furthermore, the total circulating refrigerant flow rate can be increased by adjusting the speed of the drive pump 51, thereby changing the superheat of the outlet of the gas collecting manifold 7.

[0043] In this embodiment, the opening degree of the flow regulating valve 82 and the speed of the drive pump 51 are adjusted by the superheat degree of the outlet of the cold plate assembly 9 and the outlet of the gas collecting manifold 7, so that the refrigerant at the outlet of the cold plate assembly 9 is at a low superheat degree, and the refrigerant in the cold plate assembly 9 is as close to the two-phase region as possible. When it is in the two-phase region, the refrigerant boils in the cold plate assembly 9, the heat transfer coefficient is high, and the temperature of the battery in the heat dissipation component 93 (battery box) is reduced. When it is in the two-phase region, the surface temperature of the phase change cold plate assembly 9 remains unchanged, which improves the temperature consistency inside the heat dissipation component 93 (battery box).

[0044] When the system is in heating mode, the battery temperature is low due to the low indoor temperature in winter and the battery being in standby mode. If the battery needs to discharge at this time, the discharge power is limited, so it is necessary to keep the temperature of the standby battery within a reasonable range. First, the four-way valve 41 changes the direction of refrigerant flow, connecting one end of the compressor 42 to one end of the indoor heat exchanger 1 and the other end of the compressor 42 to one end of the outdoor heat exchanger 2, while keeping the solenoid valve 21 in the closed state. At this time, the outdoor heat exchanger 2 acts as an evaporator to absorb heat from the outdoor air, and the indoor heat exchanger 1 acts as a condenser to discharge heat, keeping the indoor temperature constant and the battery temperature within a reasonable range.

[0045] If the battery requires high current charging and discharging, the refrigerant direction of the four-way valve 41 is changed again, so that the outdoor heat exchanger 2 acts as a condenser, and the solenoid valve 21 reopens, keeping the battery temperature within a reasonable range.

[0046] This embodiment describes a control method for a wind-liquid fusion cooling-heating phase change cold plate temperature control system. The cold plate assembly 9 includes a cooling plate 91, a throttle valve 92, and a first temperature sensor 94. The other end of the liquid collection branch pipe 81 is connected to one end of the gas collection branch pipe 84 after passing through the throttle valve 92 and the cooling plate 91. A heat-dissipating component 93 is disposed on the cooling plate 91. The first temperature sensor 94 is disposed on the heat-dissipating component 93 and is used to detect the actual temperature value of the cold plate assembly 9. In the adjustment step of this embodiment's wind-liquid fusion cooling-heating phase change cold plate temperature control system, when the actual temperature value of the cold plate assembly 9 is greater than a preset temperature value, the speed of the compressor 42 is increased; when the actual temperature value of the cold plate assembly 9 is less than the preset temperature value, the speed of the compressor 42 is decreased. Through the above settings, the battery temperature can be controlled to remain within a reasonable range.

[0047] The control method of the air-liquid fusion cooling-heating phase change cold plate temperature control system described in this embodiment includes a second temperature sensor 85 and a second pressure sensor 86 in the gas collecting branch pipe 84; in the superheat detection step of the gas collecting branch pipe 84, the corresponding second saturation temperature value is calculated based on the pressure value detected by the second pressure sensor 86; the actual value of the second superheat of the gas collecting branch pipe 84 is obtained by subtracting the second saturation temperature value from the temperature value detected by the second temperature sensor 85. The control method of the air-liquid fusion cooling-heating phase change cold plate temperature control system described in this embodiment includes the following steps: In the adjustment step, when the actual value of the second superheat of the gas collecting branch pipe 84 is greater than the preset value of the second superheat, the opening of the flow regulating valve 82 is increased to increase the flow rate of the refrigerant through the cold plate assembly 9, thereby increasing the heat exchange at the cold plate assembly 9 and thus reducing the actual value of the second superheat; when the actual value of the second superheat of the gas collecting branch pipe 84 is less than the preset value of the second superheat, the opening of the flow regulating valve 82 is decreased to reduce the flow rate of the refrigerant through the cold plate assembly 9, thereby reducing the heat exchange at the cold plate assembly 9 and thus increasing the actual value of the second superheat.

[0048] Specifically, when the actual value of the second superheat is greater than 0, the refrigerant at the outlet of the cold plate assembly 9 is in a gaseous state. When the refrigerant is in a gaseous state in the last part of the cold plate assembly 9, its temperature rise is large, which is not conducive to the uniformity of the surface temperature of the cooling plate 91 of the cold plate assembly 9, and will make the temperature uniformity between the batteries worse. Therefore, it is necessary to control the superheat to a small value (the preset value of the second superheat) so that the refrigerant is kept in a two-phase region in the cooling plate 91 of the cold plate assembly 9. By adjusting the opening of the flow regulating valve 82, the flow rate of the refrigerant through the cold plate assembly 9 is changed, and the heat exchange at the cold plate assembly 9 is changed. Finally, the actual value of the second superheat is the same as the preset value of the second superheat.

[0049] The control method of the air-liquid fusion cooling-heating phase change cold plate temperature control system described in this embodiment includes a third temperature sensor 71 and a third pressure sensor 72 between the gas collecting main pipe 7 and the second channel 32. In the superheat detection step of the gas collecting main pipe 7, the corresponding third saturation temperature value is calculated based on the pressure value detected by the third pressure sensor 72. The actual value of the first superheat of the gas collecting main pipe 7 is obtained by subtracting the third saturation temperature value from the temperature value detected by the third temperature sensor 71. In the adjustment step of the air-liquid fusion cooling-heating phase change cold plate temperature control system described in this embodiment, when the actual value of the first superheat of the gas collecting main pipe 7 is greater than the preset value of the first superheat, the speed of the drive pump 51 is increased to increase the flow rate of refrigerant through the cooling branch 8, thereby reducing the actual value of the first superheat; when the actual value of the first superheat of the gas collecting main pipe 7 is less than the preset value of the first superheat, the speed of the drive pump 51 is decreased to reduce the flow rate of refrigerant through the cooling branch 8, thereby increasing the actual value of the first superheat.

[0050] Specifically, when the opening of the flow regulating valve 82 is increased, but after a period of time, the actual values ​​of the first superheat and the second superheat may still be too large, it indicates that further increasing the opening of the flow regulating valve 82 will have no effect, because the total circulating refrigerant flow of the cold plate cooling circulation system is insufficient. At this time, the speed of the drive pump 51 can be adjusted by the actual value of the first superheat to increase the total circulating refrigerant flow, so that the actual value of the first superheat is the same as the preset value of the first superheat.

[0051] The control method of the air-liquid fusion cooling-heating phase change cold plate temperature control system described in this embodiment has a second superheat preset value of 1℃-3℃. Through the above settings, the refrigerant in the cold plate assembly 9 can be kept in a two-phase region that maintains a gas-liquid mixture, thereby making the temperature at the cold plate assembly 9 more uniform, reducing the temperature difference, and ultimately making the temperature between the batteries in the battery box more consistent.

[0052] The control method of the air-liquid fusion cooling-heating phase change cold plate temperature control system described in this embodiment has a first superheat preset value of 1.5℃-3.5℃. Through the above settings, the refrigerant in the cold plate assembly 9 can be kept in a two-phase region that maintains a gas-liquid mixture, thereby making the temperature at the cold plate assembly 9 more uniform, reducing the temperature difference, and ultimately making the temperature between the batteries in the battery box tend to be uniform.

[0053] In the control method of the air-liquid integrated cooling and heating phase change cold plate temperature control system described in this embodiment, during the mode selection step, when entering the cooling mode, the four-way valve 41 connects one end of the compressor 42 to one end of the outdoor heat exchanger 2 and the other end of the compressor 42 to one end of the indoor heat exchanger 1, and the solenoid valve 21 is in the conducting state; when entering the heating mode, the four-way valve 41 connects one end of the compressor 42 to one end of the indoor heat exchanger 1 and the other end of the compressor 42 to one end of the outdoor heat exchanger 2, and the solenoid valve 21 is in the closed state.

[0054] Specifically, the above settings enable the indoor air temperature to be heated during winter, keeping the battery temperature within a reasonable range.

[0055] 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 of a wind-liquid fusion cold and warm type phase change cold plate temperature control system, characterized by: The application relates to a cooling system, which comprises an indoor heat exchanger (1), an outdoor heat exchanger (2), an intermediate heat exchanger (3), a four-way valve (41), a compressor (42), a driving pump (51), a liquid collecting main pipe (6), a gas collecting main pipe (7) and a plurality of cooling branches (8); the four-way valve (41) is used for connecting the exhaust port of the compressor (42) with one end of the outdoor heat exchanger (2) and connecting the suction port of the compressor (42) with one end of the indoor heat exchanger (1), or connecting the exhaust port of the compressor (42) with one end of the indoor heat exchanger (1) and connecting the suction port of the compressor (42) with one end of the outdoor heat exchanger (2); the other end of the outdoor heat exchanger (2) is connected with the other end of the indoor heat exchanger (1); the intermediate heat exchanger (3) comprises a first channel (31) and a second channel (32); the first channel (31) is arranged between the other end of the outdoor heat exchanger (2) and one end of the indoor heat exchanger (1); an electromagnetic valve (21) is arranged between the first channel (31) and the other end of the outdoor heat exchanger (2); the second channel (32), the driving pump (51), the liquid collecting main pipe (6), the cooling branch (8) and the gas collecting main pipe (7) are sequentially connected; each cooling branch (8) comprises a liquid collecting branch pipe (81), a gas collecting branch pipe (84), a flow regulating valve (82) and a plurality of cold plate assemblies (9); one end of the liquid collecting branch pipe (81) is connected with the liquid collecting main pipe (6); the other end of the liquid collecting branch pipe (81) is connected with one end of the gas collecting branch pipe (84) through the cold plate assembly (9); the other end of the gas collecting branch pipe (84) is connected with the gas collecting main pipe (7); the flow regulating valve (82) is arranged in the liquid collecting branch pipe (81); the cold plate assembly (9) is arranged with a heat radiating piece (93); The application further comprises the following steps: Mode selection step: selecting the refrigeration mode or the heating mode according to the indoor temperature; Cold plate temperature detection step: detecting the actual temperature value of the heat radiating piece (93) and comparing the actual temperature value with a preset temperature value; Gas collecting main pipe superheat degree detection step: detecting the first superheat degree actual value of the gas collecting main pipe (7) and comparing the first superheat degree actual value with a first superheat degree preset value; Gas collecting branch pipe superheat degree detection step: detecting the second superheat degree actual value of the gas collecting branch pipe (84) and comparing the second superheat degree actual value with a second superheat degree preset value; Adjustment step: adjusting the rotating speed of the compressor (42) according to the comparison between the actual temperature value and the preset temperature value, adjusting the rotating speed of the driving pump (51) according to the comparison between the first superheat degree actual value and the first superheat degree preset value, and adjusting the opening degree of the flow regulating valve (82) according to the comparison between the second superheat degree actual value and the second superheat degree preset value, so that a gas-liquid mixture is formed in the cold plate assembly (9).

2. The control method of the air-liquid fusion cold and warm phase change cold plate temperature control system according to claim 1, characterized in that: The cold plate assembly (9) comprises a cooling plate (91), a throttle valve (92) and a first temperature sensor (94). The other end of the collecting branch pipe (81) is communicated with one end of the collecting branch pipe (84) through a throttle valve (92) and a cooling plate (91) in sequence; the heat dissipation component (93) is arranged on the cooling plate (91); the first temperature sensor (94) is arranged on the heat dissipation component (93); the first temperature sensor (94) is used for detecting the actual temperature value of the cold plate assembly (9).

3. The control method of the air-liquid fusion cold and warm phase change cold plate temperature control system according to claim 1, characterized in that: The collecting branch pipe (84) is provided with a second temperature sensor (85) and a second pressure sensor (86); In the collecting branch pipe superheat degree detection step, the corresponding second saturation temperature value is calculated according to the pressure value detected by the second pressure sensor (86); The second superheat degree actual value of the collecting branch pipe (84) is obtained by subtracting the second saturation temperature value from the temperature value detected by the second temperature sensor (85).

4. The control method of the air-liquid fusion cold and warm phase change cold plate temperature control system according to claim 1, characterized in that: The third temperature sensor (71) and the third pressure sensor (72) are arranged between the collecting main pipe (7) and the second channel (32); In the collecting main pipe superheat degree detection step, the corresponding third saturation temperature value is calculated according to the pressure value detected by the third pressure sensor (72); and the first superheat degree actual value of the collecting main pipe (7) is obtained by subtracting the third saturation temperature value from the temperature value detected by the third temperature sensor (71).

5. The control method of the air-liquid fusion cold and warm phase change cold plate temperature control system according to claim 1, characterized in that: In the adjusting step, when the actual temperature value of the cold plate assembly (9) is greater than the temperature preset value, the rotating speed of the compressor (42) is increased; and when the actual temperature value of the cold plate assembly (9) is less than the temperature preset value, the rotating speed of the compressor (42) is decreased.

6. The control method of the air-liquid fusion cold and warm phase change cold plate temperature control system according to claim 1, characterized in that: In the adjusting step, when the second superheat degree actual value of the collecting branch pipe (84) is greater than the second superheat degree preset value, the opening of the flow regulating valve (82) is adjusted to increase the flow of the refrigerant through the cold plate assembly (9), so that the heat exchange amount at the cold plate assembly (9) is increased, and the second superheat degree actual value is reduced; and when the second superheat degree actual value of the collecting branch pipe (84) is less than the second superheat degree preset value, the opening of the flow regulating valve (82) is adjusted to reduce the flow of the refrigerant through the cold plate assembly (9), so that the heat exchange amount at the cold plate assembly (9) is reduced, and the second superheat degree actual value is increased.

7. The control method of the air-liquid fusion cold and warm phase change cold plate temperature control system according to claim 1, characterized in that: In the adjusting step, when the first superheat degree actual value of the collecting main pipe (7) is greater than the first superheat degree preset value, the rotating speed of the driving pump (51) is increased, the flow of the refrigerant through the cooling branch (8) is increased, and the first superheat degree actual value is reduced; When the first superheat degree actual value of the collecting main pipe (7) is less than the first superheat degree preset value, the rotating speed of the driving pump (51) is decreased, the flow of the refrigerant through the cooling branch (8) is reduced, and the first superheat degree actual value is increased. 8.The control method of the air-liquid fusion cold and warm phase change cold plate temperature control system according to claim 1, characterized in that: The second superheat degree preset value is 1-3℃. 9.The control method of the air-liquid fusion cold and warm phase change cold plate temperature control system according to claim 1, characterized in that: The first superheat degree preset value is 1.5-3.5℃.

10. The control method of the air-liquid fusion cold and warm phase change cold plate temperature control system according to claim 1, characterized in that: In the mode selection step, when entering the refrigeration mode, the four-way valve (41) communicates the discharge port of the compressor (42) with one end of the outdoor heat exchanger (2) and communicates the suction port of the compressor (42) with one end of the indoor heat exchanger (1), and the electromagnetic valve (21) is in the on state; when entering the heating mode, the four-way valve (41) communicates the discharge port of the compressor (42) with one end of the indoor heat exchanger (1) and communicates the suction port of the compressor (42) with one end of the outdoor heat exchanger (2), and the electromagnetic valve (21) is in the off state.

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