Collection-storage-dissipation integrated co-working medium heat management system and control method thereof

Abstract

The invention discloses a collection-storage-dissipation integrated co-working medium heat management system and a control method thereof. The system comprises a pump, a ball valve, a heat source, a heat collection cold plate, a phase change heat storage device module, a compressor, a condenser, a mass flow meter and a throttling valve. The phase change heat storage device module adopts a gas-liquid separator which is internally integrated with a solid-liquid phase change heat storage device and has a phase change heat storage function; an outlet of the pump is connected with an inlet of the heat collection cold plate through a ball valve; an outlet of the heat collection cold plate is connected with a side end inlet of the gas-liquid separator; the heat source is attached to the surface of the heat collection cold plate. An outlet in the lower end of the gas-liquid separator is connected with an inlet of the pump; a side end outlet of the gas-liquid separator is connected with an inlet of the compressor; an inlet and an outlet of the condenser are connected with an outlet of the compressor and an inlet of the flow meter respectively, and an outlet of the flow meter is connected with an inlet of the throttling valve. And an outlet of the throttle valve is connected with an inlet at the upper end of the gas-liquid separator. And higher mass heat storage density and heat storage power are realized.

Description

Technical Field

[0001] The present invention belongs to the technical field of heat dissipation of electronic equipment, and in particular to a collection-storage-dissipation integrated common working fluid thermal management system and a control method thereof. Background Art

[0002] Lasers, due to their high brightness, excellent directionality, monochromaticity, and coherence, have shown broad application prospects in defense, medicine, communications, industrial manufacturing, and space exploration. In recent years, with the significant increase in the power density per unit volume of lasers, the thermal management system of high-power lasers faces the following challenges:

[0003] (1) The peak power of high-power lasers has increased significantly, but their overall electro-optical conversion efficiency remains at 10% to 30%, which means that 70% to 90% of the input energy will be dissipated as heat, resulting in a heat generation power of up to 300kW.

[0004] (2) High-power lasers are developing towards integration and miniaturization. The space available for thermal management is shrinking, and the heat flux density of the heating surface may be as high as 300W / cm 2 ;

[0005] (3) The lightweight design of the thermal management system becomes another key challenge.

[0006] These factors place higher demands on the peak heat dissipation capacity of the high-power laser thermal management system.

[0007] Phase change heat storage technology achieves temporary storage of heat through the phase change process of the material. It has the advantages of stable heat storage process, high heat storage density and nearly constant temperature heat storage. It can achieve "peak shaving and valley filling" in the thermal management of intermittent heating equipment such as lasers. Introducing phase change heat storage technology in intermittent heating equipment such as lasers can effectively reduce the peak power of the thermal management system while suppressing excessive increase in the surface temperature of the equipment. Through this technology, heat is temporarily stored during the operation of the equipment, which can smooth the intermittent high-power heat dissipation demand, thereby transforming the unstable high-power heat dissipation process into a stable low-power heat dissipation process, significantly reducing the quality and power consumption of the thermal management system.

[0008] Currently, paraffin (PA) has become a commonly used phase change material in high-power laser thermal management systems due to its wide and adjustable phase change temperature range, stable chemical properties, no supercooling, low toxicity and low corrosiveness. However, paraffin has poor thermal conductivity, and its thermal conductivity coefficient is usually less than 0.2W / (m·K). To improve this problem, researchers have proposed a variety of thermal conductivity enhancement methods and phase change heat storage device structure optimization schemes. Although these methods can significantly improve the thermal conductivity and heat storage power of paraffin, they also significantly increase the mass of the device, resulting in a decrease in mass heat storage power, which makes it difficult to meet the lightweight requirements of the thermal management system.

[0009] Compared to traditional solid-liquid phase change thermal management systems, gas-liquid phase change thermal storage technology offers the advantages of high latent heat of phase change and low thermal resistance. While significantly reducing system mass, it can also increase mass heat storage efficiency, making it an ideal choice for lightweight thermal management system designs. While maintaining the structure of traditional high-power laser thermal management systems as much as possible, the introduction of gas-liquid phase change thermal storage technology is crucial for achieving the goal of lightweight thermal management systems. Summary of the Invention

[0010] The purpose of the present invention is to provide an integrated collection-storage-dissipation common working fluid thermal management system and its control method, so as to optimize the thermal management system design of intermittent heating equipment, realize efficient heat dissipation of intermittent heating equipment, avoid many adverse consequences caused by excessive temperature, ensure the stable operation of intermittent heating equipment in complex environments, and improve its overall working efficiency and reliability.

[0011] The technical solutions for achieving the purpose of the present invention are:

[0012] An integrated collection-storage-dissipation common working fluid thermal management system, comprising a pump, a ball valve, a heat source, a heat collection cold plate, a phase change heat storage device module, a compressor, a condenser, a mass flow meter and a throttle valve;

[0013] The phase change heat storage device module adopts a gas-liquid separator with a phase change heat storage function integrated with a solid-liquid phase change heat storage device;

[0014] The outlet of the pump is connected to the inlet of the heat collecting cold plate through a ball valve; the outlet of the heat collecting cold plate is connected to the side inlet of the gas-liquid separator; the heat source is in contact with the surface of the heat collecting cold plate; the lower outlet of the gas-liquid separator is connected to the inlet of the pump; the side outlet of the gas-liquid separator is connected to the inlet of the compressor; the inlet and outlet of the condenser are respectively connected to the outlet of the compressor and the inlet of the flow meter, and the outlet of the flow meter is connected to the inlet of the throttle valve; the outlet of the throttle valve is connected to the upper inlet of the gas-liquid separator.

[0015] A collection-storage-distribution integrated common working fluid thermal management system, the control method of which includes:

[0016] When time t=0, the gas-liquid separator is in the initial state, and the heat source starts to Heat is released, and at the same time the pump starts working, the ball valve opens, driving the saturated liquid cooling medium in the gas-liquid separator to pass through the heat collecting cold plate to absorb the heat from the heat source and turn into a gas-liquid two-phase state, and then return to the gas-liquid separator. The compressor does not work;

[0017] When time t = t c When the heat source stops releasing heat, the pump keeps working, the ball valve keeps opening, the gas-liquid separator completes the heat storage process and reaches the maximum heat storage state. At the same time, the compressor starts, the throttle valve opens, and the saturated gaseous working medium of the gas-liquid separator enters the compressor and is compressed. It then passes through the condenser to release the heat, and then passes through the flow meter and the throttle valve and enters the gas-liquid separator, completing the heat release cycle and releasing the heat stored in the gas-liquid separator.

[0018] When time t = t c +t s When the compressor stops running, the throttle valve closes, the gas-liquid separator completes heat release and returns to the initial state;

[0019] where t c , t s They are respectively the duration of heat flow from the heat source and the duration of heat stopping.

[0020] Compared with the prior art, the present invention has the following significant advantages:

[0021] To address the heat dissipation needs of intermittent heating equipment, this paper designs an integrated collection-storage-dissipation co-working fluid thermal management system and proposes a control method for this system. Compared with traditional thermal management methods based on solid-liquid phase change, this paper utilizes the existing liquid reservoir in the traditional system and redesigns it into an integrated device with gas-liquid phase change heat storage function, eliminating the original solid-liquid phase change heat storage device. This significantly improves heat storage efficiency and reduces system mass, achieving higher mass heat storage density and heat storage power. While optimizing the performance of traditional thermal management systems, this system has the potential for weight reduction, which is of great significance for achieving the goal of efficient and lightweight thermal management. BRIEF DESCRIPTION OF THE DRAWINGS

[0022] Figure 1 A schematic diagram of a circulation system for a collection-storage-dissipation integrated common working fluid thermal management system designed for the present invention.

[0023] Figure 2 Schematic diagram of the thermal characteristics of the heat source in an integrated collection-storage-dissipation common working fluid thermal management system designed for the present invention.

[0024] Figure 3The pressure-enthalpy diagram of the cycle principle of a collection-storage-dissipation integrated common working fluid thermal management system designed for this invention, where Figure 3 (a) is the pressure-enthalpy diagram of the pump-driven two-phase heat collection cycle principle; Figure 3 (b) is the principle pressure-enthalpy diagram of the phase change heat storage device module; Figure 3 (c) is the pressure-enthalpy diagram of the vapor compression refrigeration and heat dissipation cycle principle.

[0025] Figure 4 Schematic diagram of a control method for a collection-storage-dissipation integrated common working fluid thermal management system cycle designed for the present invention. DETAILED DESCRIPTION

[0026] The present invention will be described in detail below with reference to the accompanying drawings and in combination with embodiments. It should be noted that, unless there is a conflict, the embodiments and features in the embodiments of the present application can be combined with each other.

[0027] The following detailed description is an exemplary description, which is intended to provide further detailed description of the present invention. Unless otherwise indicated, all technical terms used in the present invention have the same meaning as those generally understood by those skilled in the art. The terms used in the present invention are only for describing specific embodiments, and are not intended to limit the exemplary embodiments according to the present invention.

[0028] Example 1

[0029] See also Figures 1 to 4 As shown, the present invention provides an integrated collection-storage-dissipation common working fluid thermal management system, comprising four parts: a pump-driven two-phase heat collection cycle module, a phase-change heat storage device module, a vapor compression refrigeration heat dissipation cycle module, and a control system. The pump-driven two-phase heat collection cycle module comprises: a pump 1, a ball valve 2, a heat source 3, and a heat collection cold plate 4, wherein the pump is a variable frequency pump; the phase-change heat storage device module comprises a gas-liquid separator 5 with a phase-change heat storage function, and a solid-liquid phase-change heat storage device 10 is integrated inside the gas-liquid separator 5 with a phase-change heat storage function; the vapor compression refrigeration cycle heat dissipation module comprises a compressor 6, a condenser 7, a mass flowmeter 8, and a throttle valve device 9, wherein the compressor is a variable frequency compressor; and the control system comprises two PID control modules, one for flow control and the other for maximum temperature difference control.

[0030] The gas-liquid separator 5 with phase change heat storage function adopts a phase change heat storage integrated design method of gas-liquid phase change and solid-liquid phase change coupling to balance the volume and mass of the device, forming a phase change heat storage device module ( Figure 1 The matching design of gas-liquid phase change heat storage power and solid-liquid phase change heat storage power and the mass m of the phase change heat storage device PCHS and volume V PCHS The limitation is closely related. When the rated heat storage power of the system is P PCWhen the pure gas-liquid phase change scheme is adopted, the mass and volume of the phase change heat storage device are m PCHS_gl and V PCHS_gl When the pure solid-liquid phase change scheme is adopted, the mass and volume of the phase change heat storage device are m PCHS_sl and V PCHS_sl , the following relationship exists:

[0031]

[0032] Therefore, when the rated heat storage power is The mass and volume limits of the phase change heat storage device are m PCHS and V PCHS When , assuming that the gas-liquid phase change heat storage power is α times the total rated heat storage power (0≤α≤1), and the solid-liquid phase change heat storage power is 1-α times the total rated heat storage power, then α satisfies the following conditions:

[0033] αm PCHS_gl +(1-α)m PCHS_sl =m PCHS

[0034] αV PCHS_gl +(1-α)V PCHS_sl =V PCHS

[0035] Among them, when α=0, that is, the phase change heat storage in the gas-liquid separator 5 with phase change heat storage function is completely completed by solid-liquid phase change, and when α=1, that is, the phase change heat storage in the gas-liquid separator 5 with phase change heat storage function is completely completed by gas-liquid phase change.

[0036] A collection-storage-dissipation integrated common working fluid thermal management system, wherein the outlet of the pump 1 is connected to the inlet of the ball valve 2, which is connected to the inlet of the heat collecting cold plate 4. The heat source 3 is bonded to the surface of the heat collecting cold plate 4 via a thermal expansion structure and thermal interface material. The outlet of the heat collecting cold plate 4 is connected to the side inlet a of a gas-liquid separator 5 with a phase change heat storage function. The lower outlet b of the gas-liquid separator 5 with a phase change heat storage function is connected to the inlet of the pump 1. The side outlet d of the gas-liquid separator 5 with a phase change heat storage function is connected to the inlet of the compressor 6. The inlet and outlet of the condenser 7 are respectively connected to the outlet of the compressor 6 and the inlet of a flow meter 8. The outlet of the flow meter 8 is connected to the inlet of a throttle valve 9, and the outlet of the throttle valve 9 is connected to the upper inlet c of the gas-liquid separator 5 with a phase change heat storage function.

[0037] Heat source 3 has intermittent heat flux density characteristics, and the heat flux of heat source 3 lasts for t c , the time to stop heating is t sIn addition, the vapor compression refrigeration heat dissipation cycle has an intermittent working characteristic. During an intermittent heat flow period, the pump-driven two-phase heat collection cycle and the vapor compression refrigeration heat dissipation cycle are started successively. The pump-driven two-phase heat collection cycle works first for a duration of t c , the steam compression refrigeration and heat dissipation cycle working time t s , and the heat collection capacity of the pump-driven two-phase heat collection cycle is the heat collection power within one cycle The heat dissipation power within one cycle of the vapor compression refrigeration heat dissipation cycle The following relationship is satisfied:

[0038]

[0039] When time t=0, the gas-liquid separator 5 with phase change heat storage function is in the initial state, and the heat source 3 starts to Heat is released, and at the same time, pump 1 starts working, ball valve 2 opens, driving the saturated liquid cooling medium in the gas-liquid separator 5 with phase change heat storage function from the lower end outlet b through the heat collecting cold plate 4 to absorb the heat from the heat source 3 and become a high-dryness gas-liquid two-phase state, and then sent back to the gas-liquid separator 5 with phase change heat storage function through the side end inlet a. The compressor 6 does not work; when time t=t c When t=t, the heat source stops releasing heat, the pump 1 continues to work, the ball valve 2 continues to open, the gas-liquid separator 5 with phase change heat storage function completes the heat storage process and reaches the maximum heat storage state. At the same time, the compressor 6 starts, the throttle valve 9 opens, and the saturated gaseous working medium at the side outlet d end of the gas-liquid separator 5 with phase change heat storage function enters the compressor 6 and is compressed to a high-temperature and high-pressure state. After passing through the condenser 7, the heat is released and becomes a high-pressure supercooled state. Then, it passes through the flow meter 8 and the throttle valve 9 in succession and becomes a low-pressure and low-dryness two-phase state. It enters the gas-liquid separator 5 with phase change heat storage function through the upper inlet c end, completing the heat release cycle and releasing the heat stored in the gas-liquid separator 5 with phase change heat storage function. When time t=t c +t s When , the compressor 6 stops running, the throttle valve 9 is closed, and the gas-liquid separator 5 with phase change heat storage function completes heat release and returns to the initial state.

[0040] The control system of a collection-storage-distribution integrated common working fluid thermal management system includes: maximum temperature difference control and flow control. Temperature sensors are installed on the heat source surface at the inlet and outlet ends of the cold plate 4, and the measured temperatures are T in and T out The inlet and outlet ends of the condenser 7 are equipped with integrated pressure stabilizing sensors, and the temperature and pressure measured at the inlet end are T c_i 、P c_i The temperature and pressure measured at the outlet are T c_o 、P c_o, used for data collection of system dynamic control. According to the measured temperature and pressure values, the working fluid thermophysical property database can be queried to obtain the enthalpy value of the working fluid corresponding state (for example, according to the temperature and pressure values ​​at the inlet end, the enthalpy value h of the heat collector cold plate inlet end can be queried). c_i , According to the temperature and pressure values ​​at the outlet, the enthalpy value h at the outlet of the collector cold plate can be obtained c_o ). Among them, the input of the maximum temperature difference controller is the temperature difference of the temperature sensors at the inlet and outlet ends of the heat collector cold plate 4, and the output is the frequency of the pump 1; the input of the flow controller is the working fluid flow of the vapor compression refrigeration heat dissipation cycle, and the output is the real-time frequency of the compressor 6. The target value of the maximum temperature difference control is the maximum temperature difference ΔT allowed on the surface of the heat source 3. max ; Target value of flow control The following conditions must be met:

[0041]

[0042] A collection-storage-dissipation integrated common working fluid thermal management system, with a lightweight design of a gas-liquid separator 5 having a phase change heat storage function, the specific steps are as follows:

[0043] Step 1: According to the working temperature requirements of the heat source 3, the design starting point boundary is clearly defined. When time t=0, the gas-liquid separator 5 with phase change heat storage function is in the initial state, the working medium is a low-dryness gas-liquid two-phase mixed state, the temperature is T0, the dryness is x0, and the pressure is P0; when time t=t c When the gas-liquid separator 5 with phase change heat storage function is in the maximum heat storage state, the working medium is a high-dryness gas-liquid two-phase mixed state, and the temperature is T m , dryness is x m , pressure is P m .

[0044] The second step is to calculate the total heat release Q of heat source 3 in one cycle. d , it is clear that the solid-liquid phase change heat storage in the gas-liquid separator 5 with phase change heat storage function is Q s1 The heat storage capacity Q of gas-liquid phase change heat storage s2 :

[0045]

[0046] The third step is to determine the mass m of the solid-liquid phase change thermal storage medium required. s1 (The design value of the melting rate of the solid-liquid phase change material is 0.75) and the mass m of the gas-liquid phase change working fluid s2 :

[0047] m s1 =Q s1 / 0.75h lh

[0048] m s2 =Q s2 / (h m -h0)

[0049] Among them, h lh is the latent heat of phase change of solid-liquid phase change material, h m It is the enthalpy value of the saturated gas in the high-dryness gas-liquid two-phase mixed state working medium when the gas-liquid separator 5 with phase change heat storage function is in the maximum heat storage state, and h0 is the enthalpy value of the saturated liquid working medium with a temperature of T0 at the initial state at time t=0.

[0050] That is, from time t=0 to t=t c The total mass of the gas-liquid separator 5 with phase change heat storage function is m s2 The working medium is vaporized from saturated liquid to saturated gas, so it is assumed that the mass of the liquid working medium in the gas-liquid separator 5 with phase change heat storage function in the initial state is m 5_l ,but:

[0051] m 5_l ≥m s2

[0052] The fourth step is to determine the volume V5 of the gas-liquid separator 5 with phase change heat storage function. When time t=t c When the gas-liquid separator 5 with phase change heat storage function is in the maximum heat storage state, the gas-liquid phase change working medium is in a high-dryness gas-liquid two-phase mixed state, and the temperature is T m , dryness is x m , the gas phase density is ρ m_v , the liquid density is ρ m_l When time t=0, the gas-liquid separator 5 with phase change heat storage function is in the initial state, the working medium is a low-dryness gas-liquid two-phase mixed state, the temperature is T0, the dryness is x0, the pressure is P0, and the gas phase density is ρ 0_l , the liquid density is ρ 0_v ; where density ρ can be obtained by querying the thermophysical properties database based on temperature and dryness value, V sl is the volume of the solid-liquid phase change heat storage device:

[0053] m 5_l / (1-x0)=(m 5_l -m s2 ) / (1-x m )

[0054]

[0055] The density of the liquid working medium in the gas-liquid separator 5 with phase change heat storage function in the initial state is ρ 0_lThe density of the gaseous working medium in the gas-liquid separator 5 with phase change heat storage function at the maximum heat storage state is ρ m_v The smaller the ratio, the smaller the volume V5 of the gas-liquid separator 5 with phase change heat storage function.

[0056] The material selection principle for the gas-liquid separator 5 with phase-change heat storage is low density ρ5 and high tensile strength σ. The wall thickness design of the gas-liquid separator 5 with phase-change heat storage needs to consider the compressive strength P. Taking a cylindrical tank structure as an example, assuming the bottom area of ​​the gas-liquid separator 5 with phase-change heat storage is S, the wall thickness d of the device is calculated as follows:

[0057] First determine the height h and inner diameter r of the device i :

[0058] h=V5 / S

[0059]

[0060] The wall thickness d can be calculated according to the pressure bearing capacity formula:

[0061] d=Pr i / σ

[0062] Then the outer diameter r o :

[0063] r o =r i +d

[0064] The volume V of the device wall 5w is the difference between the inner and outer volumes:

[0065] V 5w =π(r o 2 -r i 2 )h

[0066] The mass m5 of the gas-liquid separator 5 with phase change heat storage function:

[0067] m5=(V 5w +2Sd)ρ5

[0068] The pump-driven two-phase heat collection cycle module, the phase change heat storage device module, and the vapor compression refrigeration cycle heat dissipation module share the same cooling fluid. The method and steps for calibrating the fluid charge are as follows:

[0069] The first step is to determine the minimum filling volume of the system. At the initial state t = 0, the temperature inside the gas-liquid separator 5 with phase change heat storage function is T0, and the mass of liquid working medium is m 5_l Must be greater than the mass of the working fluid in an intermittent heat release process (m s2),Right now:

[0070] m 5_l ≥m s2

[0071] That is, the minimum working fluid mass in the gas-liquid separator 5 with phase change heat storage function is is the mass of gaseous working medium (m 5_v ) and the mass of liquid working fluid (m 5_l ) and:

[0072]

[0073] Assume that the internal volume of the thermal management system is V s At this time, the minimum mass of other thermal management system components and the working fluid in the pipeline, excluding the gas-liquid separator 5 with phase change heat storage function, is for:

[0074]

[0075] That is, at the initial state t=0, the minimum mass of the working fluid in the thermal management system (m s_min ')for:

[0076]

[0077] When the ambient temperature is the lowest, assuming that the working fluids in the pipeline and heat exchanger are all in liquid state, and the liquid working fluid in the gas-liquid separator 5 with phase change heat storage function is just 0, the minimum mass of the working fluid in the thermal management system (m s_min ”), the density of the gaseous working medium is ρ v , the density of the liquid working medium is ρ l :

[0078] m s_min ”=V5ρ v +(V s -V5)ρ l

[0079] In summary, the minimum filling volume of the system is m s_min Must meet:

[0080] m s_min =max(m s_min ',m s_min ”)

[0081] The second step is to determine the maximum filling volume m s_max When the ambient temperature is the highest, assuming that the working fluids in the pipeline and heat exchanger are all in gaseous state, and the gas-liquid separator 5 with phase change heat storage function can accommodate all the working fluids, that is, it reaches a full liquid state, then the maximum filling amount of the system must meet:

[0082] m 5_l =V5ρ l

[0083] m s_max =m 5_l +(V s -V5)ρ v

[0084] The fourth step is to determine the appropriate filling volume m of the system charge :

[0085] m s_min <m charge <m s_max

[0086] It is understood from common technical knowledge that the present invention may be implemented by other embodiments that do not depart from its spirit or essential features. Therefore, the embodiments disclosed above are, in all respects, merely illustrative and not exclusive. All modifications within the scope of the present invention or equivalent to the scope of the present invention are intended to be encompassed by the present invention.

Claims

1. A collection-storage-distribution integrated common working fluid thermal management system, characterized in that: It includes a pump, a ball valve, a heat source, a heat collecting cold plate, a phase change heat storage device module, a compressor, a condenser, a mass flow meter and a throttle valve; The phase change heat storage device module adopts a gas-liquid separator with a phase change heat storage function integrated with a solid-liquid phase change heat storage device; The outlet of the pump is connected to the inlet of the heat collecting cold plate through a ball valve; the outlet of the heat collecting cold plate is connected to the side inlet of the gas-liquid separator; the heat source is in contact with the surface of the heat collecting cold plate; the lower outlet of the gas-liquid separator is connected to the inlet of the pump; the side outlet of the gas-liquid separator is connected to the inlet of the compressor; the inlet and outlet of the condenser are respectively connected to the outlet of the compressor and the inlet of the flow meter, and the outlet of the flow meter is connected to the inlet of the throttle valve; the outlet of the throttle valve is connected to the upper inlet of the gas-liquid separator.

2. The integrated collection-storage-distribution common working fluid thermal management system according to claim 1, characterized in that: Its rated heat storage power is The mass and volume limits of the phase change heat storage device are m PCHS and V PCHS ,satisfy: αm PCHS_gl +(1-α)m PCHS_sl =m PCHS aV PCHS_gl +(1-α)V PCHS_sl =V PCHS where m PCHS_gl and V PCHS_gl are the mass and volume of the phase change heat storage device when the pure gas-liquid phase change scheme is adopted; m PCHS_sl and V PCHS_sl are the mass and volume of the phase change heat storage device when the pure solid-liquid phase change scheme is adopted; α is the multiple of the gas-liquid phase change heat storage power to the total capacity heat storage power; When α=0, the phase change heat storage in the gas-liquid separator is completely completed by the solid-liquid phase change. When α=1, the phase change heat storage in the gas-liquid separator is completely completed by the gas-liquid phase change.

3. The integrated collection-storage-distribution common working fluid thermal management system according to claim 1, characterized in that: A control system is provided for maximum temperature difference control and flow control; temperature sensors are installed on the heat source surfaces at the inlet and outlet ends of the cold plate respectively for collecting the inlet and outlet temperatures; pressure stabilizing integrated sensors are installed at the inlet and outlet ends of the condenser respectively for measuring the temperature and pressure at the inlet end and the temperature and pressure at the outlet end; The input of the maximum temperature difference control is the temperature difference of the temperature sensors at the inlet and outlet ends of the heat collector cold plate, and the output is the frequency of the pump; the input of the flow control is the working fluid flow of the vapor compression refrigeration heat dissipation cycle, and the output is the real-time frequency of the compressor; the target value of the maximum temperature difference control is the maximum temperature difference ΔT allowed on the heat source surface max ; Target value of flow control The following conditions must be met: where h c_i is the enthalpy value at the inlet of the heat collector cold plate, h c_o is the enthalpy value at the outlet of the collector cold plate, It is the heat dissipation power of the thermal management system in one cycle.

4. The integrated collection-storage-distribution common working fluid thermal management system according to claim 1, characterized in that: The volume V5 of the gas-liquid separator satisfies: where m 5_l is the mass of liquid working medium in the gas-liquid separator in the initial state, x m 、 are the dryness, liquid phase density and gas phase density of the gas-liquid two-phase working medium when the gas-liquid separator is in the maximum heat storage state, m s2 is the total mass of the working fluid that undergoes phase change; V sl is the volume of the solid-liquid phase change heat storage device.

5. The integrated collection-storage-distribution common working fluid thermal management system according to claim 1, characterized in that: The mass m5 of the gas-liquid separator meets the following requirements: m5=(v 5w +2Sd)ρ5 V 5w =π(r o 2 -r i 2 )h h=V5 / S d=Pr i / σ Where V 5w is the volume of the gas-liquid separator wall, S is the bottom area of ​​the gas-liquid separator wall, ρ5 is the material density of the gas-liquid separator, σ is the tensile strength, d is the wall thickness, r i is the inner diameter, r o is the outer diameter, and P is the compressive strength.

6. The integrated collection-storage-distribution common working fluid thermal management system according to claim 1, characterized in that: Its filling volume m charge satisfy: m s_min <m charge <m s_max m s_min =max(m s_min ',m s_min ”) m s_max =m 5_l +(V s -V5)ρ v m s_min ”=V5ρ v +(V s -V5)p l where m s_min is the minimum filling volume, m s_max is the maximum filling volume; m s_min ' is the minimum mass of the working fluid in the initial state, m s_min ”、ρ v , ρ l are the minimum mass of the working fluid when the liquid working fluid in the gas-liquid separator is just 0, the density of the gaseous working fluid, and the density of the liquid working fluid; m 5_l is the mass of liquid working medium in the gas-liquid separator, V s is the internal volume of the thermal management system; V5 is the volume of the gas-liquid separator; is the minimum working fluid mass in the gas-liquid separator; m s2 is the mass of the working fluid in an intermittent heat release process; ρ m_v , ρ m_l The gas phase density and liquid phase density of the working medium when the gas-liquid separator 5 is in the maximum heat storage state respectively.

7. The integrated collection-storage-distribution common working fluid thermal management system according to claim 1, characterized in that: Its control methods include: When time t=0, the gas-liquid separator is in the initial state, and the heat source starts to Heat is released, and at the same time the pump starts working, the ball valve opens, driving the saturated liquid cooling medium in the gas-liquid separator to pass through the heat collecting cold plate to absorb the heat from the heat source and turn into a gas-liquid two-phase state, and then return to the gas-liquid separator. The compressor does not work; When time t = t c When the heat source stops releasing heat, the pump keeps working, the ball valve keeps opening, the gas-liquid separator completes the heat storage process and reaches the maximum heat storage state. At the same time, the compressor starts, the throttle valve opens, and the saturated gaseous working medium of the gas-liquid separator enters the compressor and is compressed. It then passes through the condenser to release the heat, and then passes through the flow meter and the throttle valve and enters the gas-liquid separator, completing the heat release cycle and releasing the heat stored in the gas-liquid separator. When time t = t c +t s When the compressor stops running, the throttle valve closes, the gas-liquid separator completes heat release and returns to the initial state; where t c , t s They are respectively the duration of heat flow from the heat source and the duration of heat stopping.

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