CO2 space efficient thermal management system with phase change cold storage equipment and control method of CO2 space efficient thermal management system

Abstract

The invention discloses a CO2 space efficient thermal management system with phase change cold storage equipment and a control method of the CO2 space efficient thermal management system, and belongs to a space device thermal management technology. According to the system, through the CO2 heat pump technology, the temperature of a refrigerant in the radiation radiator is increased, so that the unit area heat dissipating capacity of the radiation radiator is remarkably increased, and the size and emission quality needed by the radiation radiator are reduced; through application of the phase change cold storage equipment, flexible adjustment of the heat dissipating capacity can be achieved, the maximum installed power of the CO2 heat management system is remarkably reduced, and the capacity, the size and the emission quality of heat management equipment such as a compressor are remarkably reduced. In the control process, the dryness of the CO2 secondary refrigerant at the outlet of the heat source liquid cooling plate is regulated and controlled by starting and stopping the CO2 working medium pump and adjusting the rotating speed, the temperature uniformity of the distributed heat source is improved, and the temperature is kept within the optimal working temperature interval; and the refrigerating capacity of heat dissipation circulation of the heat pump is regulated and controlled through the rotating speed of the CO2 compressor so as to be matched with the heating value of the distributed heat source, and finally efficient heat management of the distributed heat source is achieved.

Description

Technical Field

[0001] The present invention belongs to the technical field of space device thermal management, and particularly relates to a CO 2 space efficient thermal management system with a phase change cold storage device and its control method. Background Art

[0002] With the development of space technology and the advancement of requirements for equipment lightweight and miniaturization, the power and energy flux density of electronic devices have increased significantly. Therefore, the problems of high heat load transmission and dissipation are becoming increasingly severe, and the importance of space device thermal management technology is becoming increasingly prominent.

[0003] Space heat dissipation mainly relies on a radiation radiator to achieve the radiation heat dissipation of the object to be cooled to the deep space environment. When space electronic devices operate, they are equivalent to distributed heat sources. Currently, most heat dissipation technologies use a coolant to centrally transfer the heat generated by the equipment to the radiation radiator, and then the radiation radiator uniformly radiates to the deep space environment. At the same time, distributed heat sources are mostly in an intermittent high-power operating state. If the coolant directly exchanges heat with the liquid cooling plate and then radiates heat, to match the heat generation of the device, a large heat dissipation area and radiator volume are required, which is contrary to the development direction of lightweight and miniaturization; at this time, the operating state of the radiator is also consistent with the working state of the device, and it only works intermittently for a short time, and the overall heat dissipation capacity is not fully utilized. Therefore, the technology for dissipating the intermittent high-power heat load of distributed heat sources needs to be developed urgently. Summary of the Invention

[0004] The purpose of the present invention is to overcome the above-mentioned disadvantages of the prior art and provide a CO 2 space efficient thermal management system with a phase change cold storage device and its control method to solve the heat dissipation problem of space distributed heat sources.

[0005] To achieve the above purpose, the present invention adopts the following technical solutions: A CO 2 space efficient thermal management system with a phase change cold storage device, including a heat pump heat dissipation cycle part and a pump-driven cooling cycle part that transfer heat through the phase change cold storage device; The heat pump heat dissipation cycle part includes a radiation radiator, and the pump-driven cooling cycle part includes a heat source liquid cooling plate; The coolant outlet of the heat source liquid cooling plate is communicated with the heat source inlet of the phase change cold storage device, the heat source outlet of the phase change cold storage device is connected with a coolant storage tank, and the outlet of the coolant storage tank is connected with a CO 2 working fluid pump, and the outlet of the CO 2 working fluid pump is communicated with the coolant inlet of the heat source liquid cooling plate; a distributed heat source is arranged on the heat source liquid cooling plate; The refrigerant outlet of the radiation radiator is connected to an expansion valve. The outlet of the expansion valve is communicated with the cold source inlet of the phase change energy storage device. The cold source outlet of the phase change energy storage device is connected to a CO 2 compressor. The outlet of the CO 2 compressor is communicated with the inlet of the radiation radiator; In the phase change energy storage device, the coolant transfers the heat absorbed from the heat source liquid cooling plate to the refrigerant, and the refrigerant dissipates the absorbed heat in the radiation radiator.

[0006] A further improvement of the present invention lies in: Preferably, the heat pump heat dissipation cycle part and the pump-driven cooling cycle part can operate in stages.

[0007] Preferably, the relationship satisfied by the heat transfer between the heat pump heat dissipation cycle part and the pump-driven cooling cycle part is:

[0008] where t s is the operating time of the heat pump heat dissipation cycle part, Q is the refrigeration capacity of the heat pump heat dissipation cycle part, P is the heat generation of the distributed heat source, and t r is the operating time of the distributed heat source.

[0009] Preferably, the mass of the phase change material in the phase change energy storage device satisfies the condition:

[0010] where m is the mass of the phase change material, L f is the latent heat of phase change, n is the margin coefficient, Q is the refrigeration capacity of the heat pump heat dissipation cycle part, P is the heat generation of the distributed heat source, and t r is the operating time of the distributed heat source.

[0011] A control method for a space efficient thermal management system with a phase change energy storage device as described above, including the following two cases: 2 Case 1, when the temperature of the heat source liquid cooling plate exceeds the upper limit of the set working temperature range, the CO working fluid pump starts, and the coolant absorbs heat in the heat source liquid cooling plate; the CO 2 working fluid pump adopts PID control, and adjusts the rotational speed of the working fluid pump according to the dryness target value of the CO 2 at the outlet of the heat source liquid cooling plate; 2 Case 2, the heat pump heat dissipation cycle takes the cycle average power of the distributed heat source as the refrigeration capacity control target, and adjusts the rotational speed of the CO compressor through PID control to adjust the heat absorbed by the refrigerant from the phase change energy storage device. 2 Case 2, the heat pump heat dissipation cycle takes the cycle average power of the distributed heat source as the refrigeration capacity control target, and adjusts the rotational speed of the CO

[0012] Preferably, in Case 1, if the CO dryness at the outlet of the heat source liquid cooling plate is higher than the set target value, 2 the rotational speed of the CO working fluid pump increases, 2 the CO flow rate increases, 2 and the dryness of the CO decreases; if the CO dryness at the outlet of the heat source liquid cooling plate is lower than the set target temperature value, 2 the rotational speed of the CO working fluid pump decreases, 2 and the dryness of the CO decreases. 2 2

[0013] Preferably, in Case 2, if the heat absorption of the refrigerant flowing through the phase change energy storage device is less than the average power of the distributed heat source, 2 the rotational speed of the compressor increases, the refrigerant flow rate increases, and the heat absorption of the refrigerant in the phase change energy storage device increases; if the 2 heat absorption of the refrigerant flowing through the phase change energy storage device is greater than the average power of the distributed heat source, 2 the rotational speed of the compressor decreases, the refrigerant flow rate decreases, and the heat absorption of the refrigerant in the phase change energy storage device decreases.

[0014] Preferably, in Case 1, if the temperature of the distributed heat source is lower than the lower limit of the working temperature range, 2 the working fluid pump stops running.

[0015] Preferably, if the temperature in the phase change energy storage device 2 is 2°C lower than the phase change temperature of the phase change material, 2 the compressor 4 stops running; if the temperature in the phase change energy storage device 2 is 2°C higher than the phase change temperature of the phase change material, 2 the rotational speed of the compressor 4 increases, and the heat absorption of the refrigerant from the phase change energy storage device 2 increases.

[0016] Compared with the prior art, the present invention has the following beneficial effects: The present invention discloses a CO space efficient thermal management system with a phase change energy storage device. The system improves the refrigerant temperature in the radiation radiator through a pump-driven cooling cycle and a heat pump heat dissipation cycle, significantly improves the heat dissipation per unit area of the radiation radiator, reduces the required size and launch mass of the radiation radiator; combined with the application of the phase change energy storage device, it realizes flexible adjustment of the heat dissipation, full utilization of the heat dissipation capacity of the radiation radiator, and reduction of the maximum installed power of the thermal management, further reducing the capacity, volume, and launch mass of the radiation radiator and thermal management related equipment. In addition, the distributed heat source and the phase change energy storage device are connected through a coolant, ensuring efficient and timely transmission of the heat generated by the distributed heat source to the phase change energy storage device, breaking through the limitation of the low thermal conductivity of the phase change material in the traditional heat pump-cool energy storage system. 2

[0017] The present invention also discloses a CO 2Space-efficient thermal management method, which improves the temperature uniformity of distributed heat sources and maintains the temperature within the optimal operating temperature range by regulating the start-stop and rotational speed of the CO 2 working fluid pump and the dryness of the secondary refrigerant at the outlet of the heat source liquid cooling plate. By regulating the rotational speed of the CO 2 compressor to control the refrigerating capacity of the heat pump cooling cycle and match the heat generation of the distributed heat source, high-efficiency thermal management of the distributed heat source is achieved. This method uses PID to regulate the rotational speed of the working fluid pump and the compressor to reasonably control the temperature and temperature uniformity of the distributed heat source. 2 compressor to control the refrigerating capacity of the heat pump cooling cycle and match the heat generation of the distributed heat source, high-efficiency thermal management of the distributed heat source is achieved. This method uses PID to regulate the rotational speed of the working fluid pump and the compressor to reasonably control the temperature and temperature uniformity of the distributed heat source. Description of the Drawings

[0018] Figure 1 Figure 2 is a diagram of a space-efficient thermal management system with a phase change energy storage device according to the present invention; Figure 2 Figure 2 is a control logic diagram of a space-efficient thermal management system with a phase change energy storage device according to the present invention.

[0019] Among them, 1 is the heat source liquid cooling plate, 2 is the phase change energy storage device, 3 is the secondary refrigerant storage tank, 4 is the CO 2 working fluid pump, 5 is the CO 2 compressor, 6 is the radiation radiator, and 7 is the expansion valve. Detailed Embodiments

[0020] The present invention will be further described in detail below with reference to the drawings: In the description of the present invention, it should be noted that the orientation or positional relationship indicated by the terms "center", "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer", etc. is based on the orientation or positional relationship shown in the drawings, and is only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of the present invention; the terms "first", "second", "third" are only used for descriptive purposes and cannot be construed as indicating or implying relative importance; in addition, unless otherwise clearly specified and limited, the terms "installed", "connected", "connected" should be understood in a broad sense, for example, it can be a fixed connection or a detachable connection; it can be directly connected or indirectly connected through an intermediate medium, and it can be the internal communication of two elements. For those of ordinary skill in the art, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0021] Please refer to Figure 1 as shown, the present invention provides a space-efficient thermal management system with a phase change energy storage device, which includes a heat source liquid cooling plate 1, a phase change energy storage device 2, a secondary refrigerant storage tank 3, CO 2 working fluid pump, 5 is the CO2 The working fluid pump 4, CO 2 compressor 5, radiation radiator 6 and expansion valve 7. Among them, the heat source liquid cooling plate 1, the phase change energy storage device 2, the coolant storage tank 3 and CO 2 the working fluid pump 4 constitute the pump-driven cooling cycle part, and the phase change energy storage device 2, CO 2 compressor 5, radiation radiator 6 and expansion valve 7 constitute the heat pump heat dissipation cycle part. The pump-driven cooling cycle part and the heat pump heat dissipation cycle part exchange heat through the phase change energy storage device 2 as the heat exchange hub. The phase change medium flowing in the pump-driven cooling cycle part is CO 2 coolant, and the phase change medium flowing in the heat pump heat dissipation cycle part is CO 2 refrigerant.

[0022] Specifically, in the pump-driven cooling cycle part, the coolant storage tank 3 stores coolant inside. The outlet of the coolant storage tank 3 is connected to the 2 inlet of the working fluid pump 4, and the outlet of the CO 2 working fluid pump 4 is connected to the inlet of the heat source liquid cooling plate 1. The outlet of the heat source liquid cooling plate 1 is connected to the heat source inlet of the phase change energy storage device 2. The heat source outlet of the phase change energy storage device 2 is connected to the inlet of the coolant storage tank 3.

[0023] In the pump-driven cooling cycle, under the action of the CO 2 working fluid pump 4, the two-phase CO 2 flows into the heat source liquid cooling plate 1 to exchange heat with the distributed heat source. By absorbing the heat generated by the distributed heat source on the heat source liquid cooling plate 1, the coolant CO 2 after heat absorption flows to the phase change energy storage device 2 to exchange heat with the phase change material and release heat. After heat release, the CO 2 flows through the coolant storage tank 3 and returns to the CO 2 working fluid pump 4, and so on in a cycle. The pump-driven cooling cycle can achieve efficient heat dissipation of the distributed heat source and ensure and maintain the appropriate temperature of the distributed heat source.

[0024] Specifically, in the heat pump heat dissipation cycle part, the cold source outlet of the phase change energy storage device 2 is connected to the 2 inlet of the compressor 5, and the outlet of the CO 2 compressor 5 is connected to the inlet of the radiation radiator 6. The outlet of the radiation radiator 6 is connected to the inlet of the expansion valve 7. The outlet of the expansion valve 7 is connected to the cold source inlet of the phase change energy storage device 2.

[0025] In the heat pump heat dissipation cycle, the low-temperature CO 2 flows through the phase change energy storage device 2, absorbs the heat inside the phase change energy storage device 2, and then passes through the CO 2 compressor 5 to be compressed to a high-temperature and high-pressure state and flows into the radiation radiator 6 to exchange radiation heat with the deep space environment. After heat dissipation, the CO 2After being throttled to a low-temperature and low-pressure state by the expansion valve 7, it flows towards the phase change energy storage device 2, and so on in a cycle. The heat pump heat dissipation cycle can make the refrigerant absorb the calorific value of the distributed heat source stored in the phase change energy storage device, and through the 2 action of the compressor 5, achieve the purpose of radiating heat at a higher temperature. The heat pump cycle can significantly increase the heat dissipation per unit radiation area, and realize the reduction of the size of the radiation heat exchanger 6 and the reduction of the emission quality.

[0026] The setting of this system enables the pump-driven cooling cycle to efficiently transfer the heat released by the distributed heat source to the phase change energy storage device 2 through the coolant for storage, achieving the purpose of distributed heat source thermal management; the heat pump heat dissipation cycle can absorb the heat in the phase change energy storage device 2, and realize the efficient heat dissipation of the refrigerant at a higher temperature in the radiation radiator 6, significantly reducing the size of the radiation radiator 6.

[0027] In some embodiments of the present invention, the internal flow channel design of the heat source liquid cooling plate 1 is based on microchannel technology, using wavy flow channels and fins to enhance perturbation and expand the surface to strengthen heat transfer, effectively improving the convective heat transfer coefficient and heat transfer area of the coolant, and significantly enhancing the heat transfer effect of the cold plate; in addition, a serpentine multi-pass flow channel structure is adopted to improve the temperature uniformity of the distributed heat source. Using a ceramic copper clad laminate as the substrate, the distributed heat source is welded on it, and then mechanically fastened to be connected with the base of the heat source liquid cooling plate, and thermal conductive silicone grease is filled in the gap to reduce the contact thermal resistance. The heat transfer between the distributed heat source and the coolant is realized through the heat source liquid cooling plate 1.

[0028] In some embodiments of the present invention, the coolant in the pump-driven cooling cycle part is CO 2 phase change working fluid, that is, CO 2 coolant, which can break through the limitation that the temperature of the single-phase fluid continuously rises along the flow channel and ensure the temperature uniformity of the distributed heat source. In addition, CO 2 has the advantages of large density and small volume, and the pressure loss and saturation temperature change caused by the frictional resistance along the pipeline are very small, strengthening the improvement of the temperature uniformity of the distributed heat source. At this time, the temperature of CO 2 is lower than the temperature of the distributed heat source to absorb the heat of the distributed heat source, and at the same time it is higher than the temperature of the phase change energy storage device 2 to effectively release heat, so as to realize the transmission and temporary storage of high heat load.

[0029] In some embodiments of the present invention, the phase change medium flowing in the heat pump heat dissipation cycle part is CO 2 refrigerant, the heat pump cycle is CO 2 transcritical cycle, and the cooling process with gradually decreasing fluid temperature is carried out in the radiation radiator 6. The CO 2The temperature is significantly increased compared with the traditional refrigerant cycle, and the average temperature of the radiation radiator 6 is significantly increased, which helps to reduce the size and emission mass of the radiation radiator 6.

[0030] Furthermore, the application of the phase change energy storage device 2 realizes the connection between the pump-driven cooling cycle and the heat pump heat dissipation cycle. When both the pump-driven cooling cycle and the heat pump heat dissipation cycle are operating, the phase change energy storage device 2 gradually stores the heat absorbed by the coolant through the heat source liquid cooling plate 1; when the device stops operating, the pump-driven cooling cycle stops accordingly, while the heat pump heat dissipation cycle continues to work, and the refrigerant continuously absorbs the heat in the phase change energy storage device 2, which can realize the decoupling of the operating states of the distributed heat source and the radiation radiator 6 and perform radiation heat dissipation with the average power of the distributed heat source cycle, further realizing the reduction of the size and emission mass of the radiation heat exchanger. In addition, due to the reduction of the maximum installed power of the thermal management system, the capacity, volume and emission mass of thermal management components such as the CO 2 compressor 5 also decrease accordingly. Finally, the reduction of the emission mass of the radiation radiator 6 can be more than 4 times the total emission mass of the compressor 5 and the phase change energy storage device 2, achieving the purpose of miniaturization and light weight of the device. 2 compressor 5 and the phase change energy storage device 2, achieving the purpose of miniaturization and light weight of the device. 2 compressor 5 and the phase change energy storage device 2, achieving the purpose of miniaturization and light weight of the device.

[0031] It should be noted that the coolant in the pump-driven cooling cycle and the refrigerant in the heat pump heat dissipation cycle flow into the phase change energy storage device 2 from different inlets and flow out from different outlets, and there is no direct heat exchange between them.

[0032] Furthermore, the powers of the pump-driven cooling cycle and the heat pump heat dissipation cycle are mutually matched. The operation time per unit cycle of the distributed heat source is t s , during which the operation time is t r , the heat generation is P, and the distributed heat source does not work for the remaining time. The cooling capacity of the heat pump heat dissipation cycle is Q, and the additional power consumption of the CO 2 compressor 5 is W. Therefore, for a single operation to ensure the appropriate temperature of the distributed heat source, the relationship between the energies satisfies:

[0033]

[0034] In the heat pump cycle, the CO 2 capacity of the compressor 5 is selected according to the calculated cooling capacity Q, and a certain margin is ensured.

[0035] Furthermore, the working temperature range of the distributed heat source is (T min , T max ), the set and optimal working temperature range is (T lo , T up ), and the set CO 2The heat transfer temperature difference between the secondary refrigerant and the distributed heat source is approximately , and the heat transfer temperature difference between the secondary refrigerant and the phase change material is approximately . The temperature control target of the distributed heat source is ; the phase change energy storage device 2 uses a paraffin-based phase change material with a phase change temperature of T p and a latent heat of phase change of L f . The mass m of the phase change material in the phase change energy storage device 2 should be able to cover the heat absorbed by the secondary refrigerant during the operation of the distributed heat source and ensure a certain margin, , where n is the margin coefficient.

[0036] Please refer to Figure 2 shown. The present invention provides a control method for a CO2 space efficient heat management system with a phase change energy storage device, which real-time monitors the temperature of the distributed heat source.

[0037] When the distributed heat source is in operation and the temperature exceeds the upper limit of the set working temperature range, that is, the temperature of the distributed heat source satisfies , the pump-driven cooling system is started, and the rotational speed of the CO 2 working medium pump 4 is controlled by PID, taking the dryness of the CO 2 at the outlet of the heat source liquid cooling plate 1 as the target, and adjusting the rotational speed of the CO 2 working medium pump 4. If the dryness x at the outlet is higher than the set target value, that is, when 2 , the rotational speed of the CO 2 working medium pump 4 increases, the CO 2 flow rate increases, the dryness at the outlet of the CO 2 is reduced, and the flow rate of the CO 2 is made to meet the requirements of phase change heat transfer and is located in the two-phase region to maintain temperature stability; if the dryness at the outlet of the CO 2 is lower than the set target temperature value, that is, when , the rotational speed of the CO 2 working medium pump 4 decreases, the CO 2 flow rate decreases, the dryness at the outlet of the CO 2 is increased, and the flow rate of the CO 2 is made to minimize the pressure loss and the energy consumption of the CO 2 working medium pump 4 on the basis of meeting the phase change heat transfer; if the two are basically equal, when , the rotational speed of the working medium pump 4 remains unchanged. Through the regulation of the rotational speed of the CO 2 working medium pump 4, the matching between the secondary refrigerant flow rate and the heat generation of the distributed heat source and the optimization of the temperature uniformity of the distributed heat source are achieved, and the temperature of the distributed heat source is maintained within the optimal working temperature range. When the operation of the distributed heat source stops, the pump-driven cooling cycle stops with a delay.

[0038] The heat pump heat dissipation cycle takes the periodic average power of the distributed heat source as the refrigerating capacity control target, adopts PID control, and uses CO 2 The rotational speed regulation of the compressor 4 for the cycle refrigerating capacity, that is, the heat absorption amount from the phase change energy storage device 2, realizes the flexible adjustment of the heat dissipation amount. If the CO 2 The heat absorption amount of the refrigerant flowing through the phase change energy storage device 2 is less than the average power of the distributed heat source, that is, Q < Q a , CO 2 The rotational speed of the compressor 4 increases, the refrigerant flow rate increases, and the heat absorption amount increases; if the CO 2 The heat absorption amount of the refrigerant flowing through the phase change energy storage device 2 is greater than the average power Q of the distributed heat source, Q > Q a , CO 2 The rotational speed of the compressor 4 decreases, the refrigerant flow rate decreases, and the heat absorption amount decreases; if the two are basically equal, the current rotational speed is maintained.

[0039] Furthermore, when the temperature T s of the phase change energy storage device 2 is lower than the phase change temperature T p -2 of the phase change material, it indicates that the stored cold amount in the variable energy storage tank 2 is sufficient at this time, and the CO 2 compressor 4 stops running. When the temperature T s of the phase change energy storage device 2 is higher than T p +2, it indicates that the heat dissipation amount of the heat pump cycle is insufficient compared with the heat generation amount of the distributed heat source at this time, and the set value Q a of the heat absorption amount of the refrigerant flowing through the phase change energy storage device 2 is increased.

[0040] In the description of the present invention, it should be understood that the orientation or positional relationship indicated by the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc. is based on the orientation or positional relationship shown in the drawings. It is only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of the present invention. In addition, the features defined with "first" and "second" may explicitly or implicitly include one or more of such features. In the description of the present invention, unless otherwise specified, the meaning of "a plurality" is two or more. In the description of the present invention, the first feature being "above" or "below" the second feature may include direct contact between the first and second features, or may include non-direct contact between the first and second features but through additional features therebetween.

[0041] In the description of the present invention, the first feature being "above", "over" and "on" the second feature includes the first feature being directly above and obliquely above the second feature, or simply indicating that the horizontal height of the first feature is higher than that of the second feature.

[0042] In the description of the present invention, it should be noted that, unless otherwise clearly specified and defined, the terms "mounted", "connected" and "coupled" shall be construed in a broad sense. For example, it may be a fixed connection, a detachable connection, or an integral connection; it may be a mechanical connection or an electrical connection; it may be directly connected or indirectly connected through an intermediate medium, and it may be the communication inside two elements. For those of ordinary skill in the art, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0043] In the description of this specification, the descriptions with reference to the terms "one embodiment", "some embodiments", "illustrative embodiments", "examples", "specific examples", or "some examples", etc. mean that the specific features, structures, materials, or characteristics described in connection with the embodiment or example are included in at least one embodiment or example of the present invention. In this specification, the schematic descriptions of the above terms do not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials, or characteristics described can be combined in a suitable manner in any one or more embodiments or examples.

[0044] Although the embodiments of the present invention have been shown and described, those of ordinary skill in the art can understand that various changes, modifications, substitutions, and variations can be made to these embodiments without departing from the principles and spirit of the present invention. The scope of the present invention is defined by the claims and their equivalents.

[0045] The above are only the preferred embodiments of the present invention, and are not intended to limit the present invention. Any modifications, equivalent substitutions, improvements, etc. made within the spirit and principle of the present invention shall be included in the protection scope of the present invention.

Claims

1. A CO2 space efficient thermal management system with phase change cold storage equipment, characterized in that: It includes a heat pump heat dissipation cycle part and a pump-driven cooling cycle part for transferring heat through a phase-change cold storage device (2); The heat pump heat dissipation cycle part comprises a radiation radiator (6), and the pump drive cooling cycle part comprises a heat source liquid cooling plate (1); The refrigerant outlet of the heat source liquid cooling plate (1) is connected to the heat source inlet of the phase change cold storage device (2), the heat source outlet of the phase change cold storage device (2) is connected to the refrigerant storage tank (3), the outlet of the refrigerant storage tank (3) is connected to the CO2 working fluid pump (4), and the outlet of the CO2 working fluid pump (4) is connected to the refrigerant inlet of the heat source liquid cooling plate (1); a distributed heat source is arranged on the heat source liquid cooling plate (1); The refrigerant outlet of the radiation radiator (6) is connected to an expansion valve (7), the outlet of the expansion valve (7) is in communication with the cold source inlet of the phase-change cold storage device (2), the cold source outlet of the phase-change cold storage device (2) is connected to a CO2 compressor (5), and the outlet of the CO2 compressor (5) is in communication with the inlet of the radiation radiator (6); In the phase-change cold storage device (2), the heat absorbed by the coolant from the heat source liquid cooling plate (1) is transferred to the refrigerant, and the refrigerant dissipates the absorbed heat in the radiation radiator (6).

2. A CO2 space efficient thermal management system with phase change cold storage equipment according to claim 1, characterized in that: The heat pump heat dissipation cycle part and the pump-driven cooling cycle part can be operated in stages.

3. A CO2 space efficient thermal management system with phase change cold storage equipment according to claim 1, characterized in that: The relationship between the heat transfer between the heat pump heat dissipation cycle and the pump-driven cooling cycle is: Among them, t s The operation time of the heat pump cooling cycle, Q is the cooling capacity of the heat pump cooling cycle, P is the calorific value of the distributed heat source, t r is the operating time of the distributed heat source.

4. A CO2 space efficient thermal management system with phase change cold storage equipment according to claim 1, characterized in that: The quality of the phase change material in the phase change cold storage device (2) satisfies the following conditions: Where m is the mass of phase change material, L f is the latent heat of phase change, n is the margin coefficient, Q is the cooling capacity of the heat pump heat dissipation cycle, P is the calorific value of the distributed heat source, t r is the operating time of the distributed heat source.

5. A method for controlling a CO2 space efficient thermal management system with a phase change cold storage device according to claim 1, characterized in that: This includes the following two situations: In case 1, when the temperature of the heat source liquid cooling plate (1) exceeds the upper limit of the set working temperature range, the CO2 working fluid pump (4) is started, and the coolant absorbs heat in the heat source liquid cooling plate (1); the CO2 working fluid pump (4) adopts PID control, and adjusts the working fluid pump speed according to the target value of the dryness of CO2 at the outlet of the heat source liquid cooling plate; In case 2, the heat pump heat dissipation cycle uses the periodic average power of the distributed heat source as the cooling capacity control target, controls the speed of the CO2 compressor (5) through PID, and adjusts the heat absorbed by the refrigerant from the phase change cold storage device (2).

6. A method for controlling a CO2 space efficient thermal management system with a phase change cold storage device according to claim 5, characterized in that: In case 1, if the CO2 dryness at the outlet of the heat source liquid cooling plate (1) is higher than the set target value, the rotation speed of the CO2 working fluid pump (4) is increased, the CO2 flow rate is increased, and the CO2 dryness is reduced; if the CO2 dryness at the outlet of the heat source liquid cooling plate (1) is lower than the set target temperature value, the rotation speed of the CO2 working fluid pump (4) is reduced, and the CO2 dryness is increased.

7. A method for controlling a CO2 space efficient thermal management system with a phase change cold storage device according to claim 5, characterized in that: In the second case, if the amount of heat absorbed by the refrigerant flowing through the phase change cold storage device (2) is less than the average power of the distributed heat source, the speed of the CO2 compressor (5) is increased, the refrigerant flow rate is increased, and the amount of heat absorbed by the refrigerant in the phase change cold storage device (2) is increased; if the amount of heat absorbed by the CO2 refrigerant flowing through the phase change cold storage device is greater than the average power of the distributed heat source, the speed of the CO2 compressor (5) is reduced, the refrigerant flow rate is reduced, and the amount of heat absorbed by the refrigerant in the phase change cold storage device (2) is reduced.

8. A method for controlling a CO2 space efficient thermal management system with a phase change cold storage device according to claim 5, characterized in that: In case 1, if the temperature of the distributed heat source is lower than the lower limit of the working range temperature, the CO2 working fluid pump (4) stops running.

9. A method for controlling a CO2 space efficient thermal management system with a phase change cold storage device according to claim 5, characterized in that: In the second case, if the temperature inside the phase change cold storage device (2) is 2°C lower than the phase change temperature of the phase change material, the CO2 compressor (5) stops running.

10. A method for controlling a CO2 space efficient thermal management system with a phase change cold storage device according to claim 5, characterized in that: If the temperature inside the phase change cold storage device (2) is 2° C. higher than the phase change temperature of the phase change material, the CO2 compressor (5) increases its rotation speed, thereby increasing the amount of heat absorbed by the refrigerant from the phase change cold storage device (2).

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