Double-refrigerant heat pipe type energy storage heat utilization management system

Abstract

The utility model discloses a double-refrigerant heat pipe type energy storage heat management system which comprises a primary side refrigerant system, a secondary side refrigerant system, a natural cooling system, a condensation fan, an intermediate heat exchanger and a three-way valve, the primary side refrigerant system comprises a compressor, a condenser and a throttling mechanism, the output end of the compressor is connected with the input end of the condenser, and the output end of the condenser is connected with the output end of the intermediate heat exchanger. The output end of the condenser is connected with the input end of the throttling mechanism; the secondary side refrigerant system comprises a liquid storage device and a cold plate. The technical effects are that four operation modes of mechanical refrigeration, heat pipe refrigeration, mixed refrigeration and low-temperature heating can be realized, a secondary side refrigerant directly enters the cold plate at the energy storage battery cluster side to directly cool the surface of the battery and carry out phase-change heat exchange, and the whole refrigeration pipeline is completely sealed and has no leakage risk, the phase-change heat exchange efficiency is high, and the service life of the battery is prolonged. The refrigeration efficiency of the compressor is further improved; and the running time of using a natural cold source all year round can be prolonged, the running time of the compressor is shortened, and the energy-saving effect is obvious.

Description

Technical Field

[0001] The utility model relates to the technical field of energy storage thermal management, and particularly relates to a thermal management system for energy storage using a dual-refrigerant heat pipe. Background Art

[0002] The structures of existing thermal management systems are mainly divided into two modes: mechanical refrigeration and natural cooling. Among them,

[0003] The operation process of the mechanical refrigeration mode is as follows: The refrigerant becomes a high-temperature and high-pressure refrigerant gas after passing through the compressor and enters the condenser. After heat exchange with outdoor air by the condensing fan, it becomes a high-pressure and medium-temperature liquid refrigerant. After passing through the dryer filter, it enters the throttling mechanism to become a low-temperature and low-pressure liquid refrigerant, and enters the plate heat exchanger to exchange heat with the coolant coming out of the cold plate on the battery cluster side to reduce the coolant temperature. After the refrigerant absorbs the heat of the coolant, it undergoes a phase change and becomes a refrigerant vapor with a certain degree of superheat, which is sucked into the compressor to complete a refrigeration cycle; The circulation pump sucks the coolant in the cold plate into the plate heat exchanger for heat exchange and cooling, and then enters the cold plate through the heater to exchange heat with the battery cluster, completing the single-phase heat exchange cycle on the secondary refrigerant side;

[0004] The operation process of the natural cooling mode is as follows: The circulation pump sucks the coolant in the cold plate, passes through the three-way valve and enters the natural cooling radiator, and exchanges heat with the outside air through the condensing fan. The cooled coolant returns to the cold plate through the heater and exchanges heat with the battery cluster, completing the single-phase heat exchange cycle on the secondary refrigerant side;

[0005] The make-up pump, make-up tank, and expansion tank are all components added to ensure that there is enough secondary refrigerant inside the secondary refrigerant side. The automatic air vent is added to discharge the air in the pipeline when filling the secondary refrigerant. The addition of these components cannot ensure the complete sealing of the system, and increases the risks of faults and leaks. There is a risk of secondary refrigerant leakage, and the secondary refrigerant evaporates in the non-fully sealed pipeline, so the secondary refrigerant side needs to be maintained regularly;

[0006] In the above thermal management system, the following problems mainly exist:

[0007] 1. The liquid cooling system needs to undergo two heat exchanges (refrigerant-secondary refrigerant, secondary refrigerant-battery cluster), with low heat exchange efficiency and high water pump power consumption, which is not conducive to energy-saving operation;

[0008] 2. Since the secondary refrigerant is for single-phase heat exchange and can only rely on temperature difference for heat exchange, it can only meet the heat exchange performance when the ambient temperature drops very low (usually below 0 °C). The time for using natural cooling in winter is relatively short, and the energy-saving rate is low;

[0009] 3. The pipeline on the secondary refrigerant side is complex, with many connecting components, low reliability, and the pipeline is not fully sealed, so the risk of secondary refrigerant leakage is large, and it is also easy to evaporate, requiring regular maintenance. Summary of the Utility Model

[0010] To this end, the present utility model provides a thermal management system for a dual-refrigerant heat pipe type energy storage to solve the above problems in the prior art.

[0011] In order to achieve the above object, the present utility model provides the following technical solutions:

[0012] According to a first aspect of the present utility model, a thermal management system for a dual-refrigerant heat pipe type energy storage includes a primary-side refrigerant system, a secondary-side refrigerant system, a natural cooling system, a condensation fan, an intermediate heat exchanger, and a three-way valve.

[0013] The primary-side refrigerant system includes a compressor, a condenser, and a throttling mechanism. The output end of the compressor is connected to the input end of the condenser, the output end of the condenser is connected to the input end of the throttling mechanism, the output end of the throttling mechanism is connected to the primary-side refrigerant input end of the intermediate heat exchanger, and the primary-side refrigerant output end of the intermediate heat exchanger is connected to the input end of the compressor.

[0014] The secondary-side refrigerant system includes a liquid receiver and a cold plate. The secondary-side refrigerant output end of the intermediate heat exchanger is connected to the input end of the liquid receiver, the output end of the liquid receiver is connected to the input end of the cold plate, and the output end of the cold plate is connected to the secondary-side refrigerant input end of the intermediate heat exchanger.

[0015] The natural cooling system includes a natural cooling radiator. The input end and the output end of the natural cooling radiator are respectively connected to the secondary-side refrigerant system. The three-way valve is used to control the connection and disconnection between the natural cooling system and the secondary-side refrigerant system.

[0016] The condensation fan is used to improve the heat exchange efficiency between the condenser and the air, and between the natural cooling radiator and the air.

[0017] Further, the primary-side refrigerant system further includes a dryer filter, and the dryer filter is arranged between the condenser and the throttling mechanism.

[0018] Further, the secondary-side refrigerant system further includes an electric heating tape, and the electric heating tape is arranged on the liquid receiver.

[0019] Further, the secondary-side refrigerant system further includes a distributor. The input end of the distributor is connected to the liquid receiver, the output end of the distributor is respectively connected to the input ends of a plurality of cold plates, and the output end of each cold plate is connected to the secondary-side refrigerant input end of the intermediate heat exchanger.

[0020] Further, the distributor is provided with a plurality of output ends, and each output end of the distributor is connected to one cold plate.

[0021] Further, the secondary refrigerant system further includes a refrigerant pump, and the refrigerant pump is arranged between the liquid storage device and the liquid distributor.

[0022] Further, the three-way valve is arranged between the cold plate and the intermediate heat exchanger. The input end of the three-way valve is connected to the output of the cold plate. The first output end of the three-way valve is connected to the input end of the natural cooling radiator. The second output end of the three-way valve is connected to the secondary refrigerant input end of the intermediate heat exchanger. The output end of the natural cooling radiator is communicated with the pipeline between the intermediate heat exchanger and the liquid storage device.

[0023] Further, the three-way valve is arranged between the intermediate heat exchanger and the liquid storage device. The first input end of the three-way valve is connected to the output end of the natural cooling radiator. The second input end of the three-way valve is connected to the secondary refrigerant output end of the intermediate heat exchanger. The output end of the three-way valve is connected to the input end of the liquid storage device. The output end of the cold plate is communicated with the input end of the natural cooling radiator, and the output end of the cold plate is communicated with the secondary refrigerant input end of the intermediate heat exchanger.

[0024] Further, the refrigerants in the primary refrigerant system and the secondary refrigerant system are hydrocarbon-based (HCs), hydrochlorofluorocarbon-based (HCFCs), hydrofluorocarbon-based (HFCs), or hydrofluoroolefin-based (HFOs).

[0025] Further, the refrigerant can be R22, R134A, R407C, R410A, R513A, R454B, R454C, R404A, R1234YF, R1234ZE, R32, R290, etc.

[0026] The utility model has the following advantages: It can realize four operation modes: mechanical refrigeration, heat pipe refrigeration (natural refrigeration), hybrid refrigeration, and low-temperature heating. Different modes can be flexibly selected according to different environmental conditions; complex components such as the secondary coolant side pipeline, circulation pump, plate heat exchanger, liquid supplementing pump, and liquid supplementing tank are removed. The secondary refrigerant directly enters the cold plate on the side of the energy storage battery cluster to directly cool the battery surface, with phase change heat transfer (primary refrigerant-secondary refrigerant-battery cluster). Moreover, the entire refrigeration pipeline is completely sealed (without an automatic exhaust valve and liquid supplementing tank), there is no leakage risk, and regular maintenance is not required. Since the secondary refrigerant directly enters the cold plate, the phase change heat transfer efficiency is high, the evaporation temperature can be increased, and the refrigeration efficiency of the compressor is further improved. When the ambient temperature is relatively low (usually below 15°C), the compressor does not operate, and the heat pipe mode is directly adopted to cool the battery. At the same time, the heat transfer efficiency of the refrigerant in the heat pipe mode is higher than that of single-phase temperature difference heat transfer, which can increase the annual operation duration using natural cold sources and reduce the operation duration of the compressor, with obvious energy-saving effects. Brief Description of the Drawings

[0027] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the following will briefly introduce the drawings required for the description of the embodiments or the prior art. Obviously, the drawings described below are only exemplary. For those of ordinary skill in the art, without creative efforts, other implementation drawings can also be obtained based on the provided drawings by extension.

[0028] The structures, ratios, sizes, etc. illustrated in this specification are only used to cooperate with the content disclosed in the specification for those who are familiar with this technology to understand and read, and are not used to limit the limiting conditions for the implementation of the present invention. Therefore, they do not have substantial technical significance. Any modification of the structure, change of the proportional relationship, or adjustment of the size, without affecting the effects that the present invention can produce and the purposes that can be achieved, should still fall within the scope covered by the technical content disclosed in the present invention.

[0029] Figure 1 It is the overall structural block diagram of a thermal management system for a double-refrigerant heat pipe type energy storage provided in some embodiments of the present invention.

[0030] Figure 2 It is the structural block diagram of a thermal management system for a double-refrigerant heat pipe type energy storage in the mechanical refrigeration mode provided in some embodiments of the present invention.

[0031] Figure 3 It is the structural block diagram of a thermal management system for a double-refrigerant heat pipe type energy storage in the heat pipe refrigeration mode provided in some embodiments of the present invention.

[0032] Figure 4 It is the structural block diagram of a thermal management system for a double-refrigerant heat pipe type energy storage in the hybrid refrigeration mode provided in some embodiments of the present invention.

[0033] Figure 5 It is the structural block diagram of a thermal management system for a double-refrigerant heat pipe type energy storage in the low-temperature heating mode provided in some embodiments of the present invention.

[0034] In the figure: 1. Compressor, 2. Condenser, 3. Natural cooling radiator, 4. Condensing fan, 5. Drier filter, 6. Throttling mechanism, 7. Intermediate heat exchanger, 8. Liquid receiver, 9. Electric heating tape, 10. Refrigerant pump, 11. Distributor, 12. Cold plate, 13. Three-way valve. Detailed Embodiments

[0035] The following specific embodiments illustrate the implementation manners of the present utility model. Those skilled in the art can easily understand other advantages and effects of the present utility model from the content disclosed in this specification. Obviously, the described embodiments are part of the embodiments of the present utility model, rather than all of them. Based on the embodiments of the present utility model, all other embodiments obtained by those of ordinary skill in the art without creative efforts shall fall within the protection scope of the present utility model.

[0036] Embodiment 1

[0037] As Figures 1 to 5 shown, a thermal management system for a double-refrigerant heat pipe type energy storage includes a primary-side refrigerant system, a secondary-side refrigerant system, a natural cooling system, a condensation fan 4, an intermediate heat exchanger 7, and a three-way valve 13.

[0038] The primary-side refrigerant system includes a compressor 1, a condenser 2, a drying filter 5, and a throttling mechanism 6. The throttling mechanism 6 can be an electronic expansion valve, a thermal expansion valve, etc. The output end of the compressor 1 is connected to the input end of the condenser 2, the output end of the condenser 2 is connected to the input end of the drying filter 5, the output end of the drying filter 5 is connected to the input end of the throttling mechanism 6, and the output end of the throttling mechanism 6 is connected to the primary-side refrigerant input end of the intermediate heat exchanger 7. The primary-side refrigerant output end of the intermediate heat exchanger 7 is connected to the input end of the compressor 1, thus forming a primary-side refrigerant circuit.

[0039] The secondary-side refrigerant system includes a liquid receiver 8, an electric heating tape 9, a refrigerant pump 10, a distributor 11, and a cold plate 12. The electric heating tape 9 is arranged on the liquid receiver and is used to heat the refrigerant in the liquid receiver. The secondary-side refrigerant output end of the intermediate heat exchanger 7 is connected to the input end of the liquid receiver 8. The output end of the liquid receiver 8 is connected to the input end of the refrigerant pump 10. The output end of the refrigerant pump 10 is connected to the input end of the distributor 11. The output end of the distributor 11 is connected to the input end of the cold plate 12. The output end of the cold plate 12 is connected to the secondary-side refrigerant input end of the intermediate heat exchanger 7, thus forming a secondary-side refrigerant circuit. Heat exchange is carried out between the primary-side refrigerant system and the secondary-side refrigerant system through the intermediate heat exchanger 7. The distributor 11 is used to evenly distribute the secondary-side refrigerant to each cold plate 12, and the cold plate 12 is used to perform heat exchange with the battery cluster.

[0040] The natural cooling system includes a natural cooling radiator 3. The input end and the output end of the natural cooling radiator 3 are respectively connected to the secondary-side refrigerant system. The three-way valve 13 is used to control the switching of the connection between the secondary-side refrigerant system and the secondary side of the intermediate heat exchanger 7 and the natural cooling radiator 3. The flow direction of the secondary-side refrigerant can be controlled through the three-way valve. The condensation fan 4 is used to accelerate the air flow around the condenser 2 and the natural cooling radiator 3.

[0041] The condenser 2 and the natural cooling radiator 3 are arranged side by side, and the condensation fan 4 is used to improve the heat exchange efficiency between the condenser 2 and the air, and between the natural cooling radiator 3 and the air.

[0042] In this embodiment, it should be noted that the three-way valve 13 is arranged between the cold plate 12 and the intermediate heat exchanger 7. Specifically, the installation position of the three-way valve 13 is as Figure 1 shown in the figure. The input end of the three-way valve 13 is connected to the output of the cold plate 12. The first output end of the three-way valve 13 ( Figure 1 the port corresponding to position I in the figure) is connected to the input end of the natural cooling radiator 3. The second output end of the three-way valve 13 ( Figure 1 the port corresponding to position II in the figure) is connected to the secondary refrigerant input end of the intermediate heat exchanger 7. The output end of the natural cooling radiator 3 is communicated with the pipeline between the secondary refrigerant output end of the intermediate heat exchanger 7 and the input end of the liquid storage device 8;

[0043] The refrigerant pump 10 is a non-essential component. When the intermediate heat exchanger 7 is higher than the cold plate 12 and the height difference is sufficient, the refrigerant pump 10 can be removed. At this time, the secondary side is a gravity heat pipe cycle;

[0044] The compressor 1 can be a fixed-frequency compressor or a variable-frequency compressor;

[0045] The refrigerant in the primary refrigerant system and the secondary refrigerant system is hydrocarbon (HCs), hydrochlorofluorocarbon (HCFCs), hydrofluorocarbon (HFCs) or hydrofluoroolefin (HFOs). Specifically, the refrigerant can be R22, R134A, R407C, R410A, R513A, R454B, R454C, R404A, R1234YF, R1234ZE, R32, R290, etc. The refrigerant in the primary refrigerant system and the secondary refrigerant system can be the same or different;

[0046] The distributor 11 is provided with a plurality of output ends, and each output end of the distributor 11 is connected to a cold plate 12.

[0047] Furthermore, it also includes sensors and controllers for detecting and controlling the operating states of each component to ensure that the thermal management system can automatically switch to the corresponding operating mode as needed; the entire management system can achieve four operating modes: mechanical refrigeration, heat pipe refrigeration (natural refrigeration), hybrid refrigeration, and low-temperature heating. The operating principles of the four operating modes are as follows:

[0048] Mechanical refrigeration mode, the operating principle is as Figure 2As shown, in this mode, the first output end of the three-way valve 13 is completely closed, the second output end of the three-way valve 13 is completely open, the compressor 1 is turned on, the refrigerant pump 10 is turned on, the compressor 1 sucks in the low-pressure superheated primary-side refrigerant vapor, enters the condenser 2, exchanges heat with the outside air through the condensing fan 4, the primary-side refrigerant becomes liquid, passes through the dryer filter 5, enters the throttling mechanism 6 for throttling and pressure reduction, and then enters the intermediate heat exchanger 7 to exchange phase-change heat with the secondary-side refrigerant. The refrigerant pump 10 extracts the secondary-side refrigerant liquid coming out of the intermediate heat exchanger 7 into the liquid receiver 8, evenly distributes it to each cold plate 12 for endothermic evaporation. After the refrigerant in the cold plate 12 exchanges heat with the battery cluster, it becomes gaseous refrigerant and enters the intermediate heat exchanger 7 through the second output end of the three-way valve 13 to exchange phase-change heat with the primary-side refrigerant, thus completing a mechanical refrigeration cycle. This mode is used when the ambient temperature is relatively high and natural refrigeration cannot be achieved using the ambient temperature, such as in summer;

[0049] The heat pipe refrigeration mode, that is, the natural refrigeration mode, has the operating principle as Figure 3 As shown, in this mode, the first output end of the three-way valve 13 is completely open, the second output end of the three-way valve 13 is completely closed, the compressor 1 is turned off, the refrigerant pump 10 is turned on, the refrigerant pump 10 sucks in the secondary-side refrigerant liquid in the liquid receiver 8, evenly distributes it to each cold plate 12 for endothermic evaporation, exchanges heat with the battery cluster and becomes gaseous refrigerant, and enters the natural cooling radiator 3 through the second output end of the three-way valve 13 to exchange phase-change heat with the outside ambient air through the condensing fan 4 to become liquid refrigerant, enters the liquid receiver 8, and is sucked in by the refrigerant pump 10 again, thus completing a heat pipe refrigeration cycle. This mode is used when the ambient temperature is relatively low and natural refrigeration can be fully achieved through the ambient temperature, such as in winter;

[0050] The hybrid refrigeration mode, with the operating principle as Figure 4As shown, in this mode, the second output end of the three-way valve 13 is opened first, and the first output end of the three-way valve 13 remains closed. At this time, the compressor 1 operates. After reaching the set temperature, the compressor 1 reduces its frequency until it stops or directly stops. Then the second output end of the three-way valve 13 is closed, and the first output end is opened. The refrigerant pump 10 operates continuously. When the temperature is higher than the set value and the starting condition of the compressor 1 is met, the compressor 1 is started again. The compressor 1 sucks in the low-pressure superheated refrigerant vapor on the primary side, enters the condenser 2, and exchanges heat through the condensation fan 4 with the outside air for phase change. The refrigerant on the primary side becomes liquid, passes through the dryer filter 5, enters the throttling mechanism 6 for throttling and pressure reduction, and then enters the intermediate heat exchanger 7 to exchange heat with the refrigerant on the secondary side for phase change. The refrigerant pump 10 sucks in the refrigerant liquid on the secondary side in the liquid receiver 8, enters the distributor 11, and is evenly distributed to each cold plate 12 for heat absorption and evaporation. After heat exchange with the battery cluster, it becomes gaseous refrigerant. The gaseous refrigerant enters the intermediate heat exchanger 7 through the second output end of the three-way valve 13 to exchange heat with the refrigerant on the primary side for phase change, and then becomes liquid refrigerant and enters the liquid receiver 8. During the shutdown period of the compressor 1, the gaseous refrigerant enters the natural cooling radiator 3 through the first output end of the three-way valve 13, exchanges heat through the condensation fan 4 with the outside air for phase change, becomes liquid refrigerant and enters the liquid receiver 8, and is sucked in by the refrigerant pump 10 again, thus completing a mixed refrigeration cycle.

[0051] Low-temperature heating mode, the operating principle is as Figure 5 As shown, in this mode, the first output end of the three-way valve 13 is completely closed, and the second output end of the three-way valve 13 is completely opened. The compressor 1 is closed, the condensation fan 4 is closed, the refrigerant pump 10 is opened, and the electric heating tape 9 is opened. After the electric heating tape 9 heats the refrigerant on the secondary side in the liquid receiver 8 to the set temperature, it is sucked in by the refrigerant pump 10 and evenly distributed to each cold plate 12, exchanges heat with the battery cluster for phase change, and heats the battery cluster to the required temperature. After the refrigerant on the secondary side after phase change heat exchange comes out of the cold plate 12, it passes through the second output end of the three-way valve 13, enters the intermediate heat exchanger 7, and then returns to the liquid receiver 8 to continue heating, thus completing a low-temperature heating cycle. This mode is used for the state where the temperature of the battery cluster is too low to start normally or the activity is poor.

[0052] The technical effects achieved by this embodiment are as follows: It can realize four operating modes: mechanical refrigeration, heat pipe refrigeration (natural refrigeration), mixed refrigeration, and low-temperature heating, and different modes can be flexibly selected according to different environmental conditions.

[0053] 1. When refrigeration is required in summer with high temperature, the mechanical refrigeration cycle is adopted. The refrigerant on the secondary side after phase change heat exchange directly enters the cold plate to cool the battery, with a smaller temperature difference loss compared to the conventional single-phase temperature difference heat exchange using water-based or other non-phase change heat carriers on the secondary side (usually more than 80% can be reduced), more energy-saving, and higher heat exchange efficiency.

[0054] 2. When refrigeration is required in winter with relatively low outdoor temperature, the heat pipe refrigeration cycle is adopted to make full use of the natural cold source. At this time, the compressor does not work, and only the cooling fan and the refrigerant pump work. The natural cold source exchanges heat with the refrigerant through phase change, which has higher heat exchange efficiency and is more energy-saving than water-based or other non-phase change secondary coolants, and the duration of using the natural cold source throughout the year is longer;

[0055] 3. In spring and autumn or during the transition with winter, the hybrid refrigeration mode is adopted. The compressor runs at low frequency or intermittently, and the refrigerant pump runs. The secondary refrigerant after refrigeration heat exchange directly enters the cold plate to cool the battery;

[0056] 4. When the temperature is relatively low in winter and the battery is not in a heating state, the electric heating tape is only used to heat the liquid storage tank in order to maintain the activity of the battery. At this time, the refrigerant pump runs in a low-speed cycle, and the heated refrigerant enters the cold plate to exchange heat through phase change to heat the battery. Because the capacity of the heated refrigerant is much less than that of water-based or other non-phase change secondary coolants, it consumes less power (usually only about 5%) than the traditional electric heating cycle and has higher efficiency;

[0057] In addition, components such as complex secondary coolant side pipelines, circulation pumps, plate heat exchangers, liquid filling pumps, and liquid filling tanks are removed. The secondary refrigerant directly enters the cold plate on the side of the energy storage battery cluster to directly cool the surface of the battery, and heat exchange through phase change (primary side refrigerant - secondary side refrigerant - battery cluster). Moreover, the entire refrigeration pipeline is completely sealed (without automatic exhaust valves and liquid filling tanks), there is no risk of leakage, and no regular maintenance is required. Since the secondary refrigerant directly enters the cold plate, the phase change heat exchange efficiency is high, the evaporation temperature can be increased, and the refrigeration efficiency of the compressor is further improved. When the ambient temperature is relatively low (usually below 15°C), the compressor does not run, and the heat pipe mode is directly adopted to cool the battery. At the same time, the heat exchange efficiency of the refrigerant in the heat pipe mode is higher than that of single-phase temperature difference heat exchange, which can increase the operation duration of using the natural cold source throughout the year, reduce the operation duration of the compressor, and the energy-saving effect is obvious.

[0058] Embodiment 2

[0059] As Figures 1 to 5 shown, another dual-refrigerant heat pipe type thermal management system for energy storage provided in this embodiment includes all the contents of Embodiment 1, and only the different parts will be described below.

[0060] In this embodiment, the three-way valve 13 is arranged between the intermediate heat exchanger 7 and the liquid storage tank 8, and the specific position of the three-way valve 13 is Figure 1 at position III (at this time, currently Figure 1At the installation position of the three-way valve shown in the figure, a three-way joint is used for connection. The first input end of the three-way valve 13 is connected to the output end of the natural cooling radiator 3. The second input end of the three-way valve 13 is connected to the secondary refrigerant output end of the intermediate heat exchanger 7. The output end of the three-way valve 13 is connected to the input end of the liquid receiver 8. There is a connection between the output end of the cold plate 12 and the input end of the natural cooling radiator 3, and the output end of the cold plate 12 is also connected to the secondary refrigerant input end of the intermediate heat exchanger 7.

[0061] In this embodiment, it should be noted that in Embodiment 1, the three ports of the three-way valve 13 are connected in a one-in-two-out form, while in this embodiment, the three ports of the three-way valve 13 are connected in a two-in-one-out form. The structure of the three-way valve 13 has not changed in the two connection methods, only the pipeline connection direction has been changed.

[0062] The three-way valve 13 can also be installed at positions I and II in Figure 1 using two two-way valves respectively, or installed at position III in Figure 1 using two two-way valves respectively. The function remains unchanged, and its working principle is basically the same as that in Embodiment 1, so it will not be elaborated here.

[0063] The technical effect achieved in this embodiment is that the installation position and form of the three-way valve 13 are variable, and it can be flexibly set according to the on-site environment during installation.

[0064] Although the present invention has been described in detail above with general descriptions and specific embodiments, based on the present invention, some modifications or improvements can be made, which are obvious to those skilled in the art. Therefore, these modifications or improvements made without departing from the spirit of the present invention all fall within the scope of protection required by the present invention.

[0065] Terms such as "upper", "lower", "left", "right", "middle", etc. cited in this specification are only for the convenience of clear narration and are not used to limit the scope of implementation of the present invention. The change or adjustment of their relative relationships, without substantial change in the technical content, should also be regarded as the scope of implementation of the present invention.

Claims

1. A dual-refrigerant heat pipe type energy storage thermal management system, characterized in that: It comprises a primary side refrigerant system, a secondary side refrigerant system, a natural cooling system, a condensing fan (4), an intermediate heat exchanger (7) and a three-way valve (13), The primary side refrigerant system comprises a compressor (1), a condenser (2) and a throttling mechanism (6); the output end of the compressor (1) is connected to the input end of the condenser (2); the output end of the condenser (2) is connected to the input end of the throttling mechanism (6); the output end of the throttling mechanism (6) is connected to the primary side refrigerant input end of the intermediate heat exchanger (7); and the primary side refrigerant output end of the intermediate heat exchanger (7) is connected to the input end of the compressor (1); The secondary side refrigerant system comprises a liquid reservoir (8) and a cold plate (12); the secondary side refrigerant output end of the intermediate heat exchanger (7) is connected to the input end of the liquid reservoir (8); the output end of the liquid reservoir (8) is connected to the input end of the cold plate (12); and the output end of the cold plate (12) is connected to the secondary side refrigerant input end of the intermediate heat exchanger (7); The natural cooling system comprises a natural cooling radiator (3), the input end and the output end of the natural cooling radiator (3) are respectively connected to the secondary side refrigerant system, and the three-way valve (13) is used to control the connection and closing of the natural cooling system and the secondary side refrigerant system; The condensing fan (4) is used to improve the heat exchange efficiency between the condenser (2) and the air, and between the natural cooling radiator (3) and the air.

2. A dual-refrigerant heat pipe type energy storage thermal management system according to claim 1, characterized in that: The primary-side refrigerant system further comprises a drying filter (5), wherein the drying filter (5) is arranged between the condenser (2) and the throttling mechanism (6).

3. A dual-refrigerant heat pipe type energy storage thermal management system according to claim 1, characterized in that: The secondary side refrigerant system further comprises an electric heating belt (9), and the electric heating belt (9) is arranged on the liquid storage tank (8).

4. A dual-refrigerant heat pipe type energy storage thermal management system according to claim 3, characterized in that: The secondary side refrigerant system also includes a liquid separator (11), the input end of the liquid separator (11) is connected to the liquid reservoir (8), the output end of the liquid separator (11) is respectively connected to the input ends of the plurality of cold plates (12), and the output end of each cold plate (12) is connected to the secondary side refrigerant input end of the intermediate heat exchanger (7).

5. A dual-refrigerant heat pipe type energy storage thermal management system according to claim 4, characterized in that: The liquid distributor (11) is provided with a plurality of output ends, and each output end of the liquid distributor (11) is connected to one of the cold plates (12).

6. A dual-refrigerant heat pipe type energy storage thermal management system according to claim 4, characterized in that: The secondary side refrigerant system further comprises a refrigerant pump (10), wherein the refrigerant pump (10) is arranged between the liquid reservoir (8) and the liquid distributor (11).

7. A dual-refrigerant heat pipe type energy storage thermal management system according to claim 1, characterized in that: The three-way valve (13) is arranged between the cold plate (12) and the intermediate heat exchanger (7); the input end of the three-way valve (13) is connected to the output of the cold plate (12); the first output end of the three-way valve (13) is connected to the input end of the natural cooling radiator (3); the second output end of the three-way valve (13) is connected to the secondary side refrigerant input end of the intermediate heat exchanger (7); and the output end of the natural cooling radiator (3) is connected to a pipeline between the intermediate heat exchanger (7) and the liquid storage tank (8).

8. The dual-refrigerant heat pipe type energy storage thermal management system according to claim 1, characterized in that: The three-way valve (13) is arranged between the intermediate heat exchanger (7) and the liquid reservoir (8); the first input end of the three-way valve (13) is connected to the output end of the natural cooling radiator (3); the second input end of the three-way valve (13) is connected to the secondary side refrigerant output end of the intermediate heat exchanger (7); the output end of the three-way valve (13) is connected to the input end of the liquid reservoir (8); the output end of the cold plate (12) is connected to the input end of the natural cooling radiator (3); and the output end of the cold plate (12) is connected to the secondary side refrigerant input end of the intermediate heat exchanger (7).

9. A dual-refrigerant heat pipe type energy storage thermal management system according to claim 1, characterized in that: The refrigerants in the primary-side refrigerant system and the secondary-side refrigerant system are hydrocarbons, hydrochlorofluorocarbons, hydrofluorocarbons or hydrofluoroolefins.

10. A dual-refrigerant heat pipe type energy storage thermal management system according to claim 9, characterized in that: The refrigerant can be R22, R134A, R407C, R410A, R513A, R454B, R454C, R404A, R1234YF, R1234ZE, R32, and R290.

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