An airborne liquid cooling system

Abstract

The present invention relates to the field of airborne environmental control, and in particular to an airborne liquid cooling system. The airborne liquid cooling system includes: a refrigerant circulation subsystem, which includes a first refrigerant circulation subsystem and a second refrigerant circulation subsystem of independent refrigeration circulation; a secondary coolant circulation subsystem, which includes a liquid storage tank, a booster pump, and a heat exchanger connected in sequence at both ends of the load inlet and outlet to form a secondary coolant circulation loop; wherein each refrigerant circulation subsystem includes a compressor, a condenser, a liquid storage, and a throttling element connected in sequence to form a loop; the outlet of the throttling element is connected to the refrigerant channel inlet of the heat exchanger, and the refrigerant channel outlet is connected to the compressor inlet; the booster pump includes a first booster pump and a second booster pump arranged in parallel. The airborne liquid cooling system can meet the heat dissipation requirements of airborne equipment, and can ensure the continuity of operation of airborne electronic equipment, ensure flight safety, and improve the life and reliability of airborne electronic systems.

Description

Technical Field

[0001] The present invention relates to the field of airborne environmental control, and in particular to an airborne liquid cooling system. Background Art

[0002] With the development of modern aircraft avionics technology and the continuous advancement of power device manufacturing technology for airborne electronic equipment, the assembly density and power density of airborne electronic equipment are constantly increasing. Cooling systems must not only solve the heat dissipation problem of high-power equipment and ensure the reliability of airborne equipment, but also meet the temperature consistency requirements of various equipment and components. Therefore, feasible cooling methods and excellent cooling effects have become increasingly important for the high reliability indicators of airborne electronic equipment. With the development of technologies such as carrier-based aircraft and unmanned aerial vehicles, more airborne electronic equipment needs to be arranged in a limited space, which puts higher demands on the miniaturization and lightweighting of airborne equipment.

[0003] At present, general airborne equipment adopts forced air cooling to dissipate heat. The forced air cooling refrigeration system is heavy and bulky, which is not conducive to the weight reduction and space expansion of the aircraft. In addition, the forced air cooling refrigeration system is limited by factors such as flight speed and altitude. As the heat load of airborne equipment continues to increase, the forced air cooling refrigeration system generally cannot meet the requirements of large heat exchange. Modern aircraft avionics technology is developing rapidly, and the cross-linking relationship between electronic equipment is becoming more and more numerous and complex, and the dependence on and requirements for airborne electronic equipment are also getting higher and higher. Therefore, how to develop a feasible cooling method, excellent cooling effect, lightweight and miniaturized airborne liquid cooling system to ensure the continuity of the operation of airborne heating equipment and realize the safe, efficient and reliable operation of airborne electronic equipment is exactly the problem that needs to be considered and solved in this field. Summary of the Invention

[0004] To address the problems mentioned in the above background technology of the existing forced air cooling refrigeration system, such as being heavy and bulky, and having cooling effects limited by environmental factors and unable to meet the requirements of large heat exchange capacity, the present invention provides an airborne liquid cooling system, comprising:

[0005] The refrigerant circulation subsystem includes a first refrigerant circulation subsystem and a second refrigerant circulation subsystem of independent refrigeration cycles;

[0006] The brine circulation subsystem includes a liquid storage tank, a booster pump, and a heat exchanger connected in sequence to the load inlet and outlet to form a brine circulation loop;

[0007] Among them, each refrigerant circulation subsystem includes a compressor, a condenser, a liquid reservoir and a throttling element which are connected in sequence to form a loop; the outlet of the throttling element is connected to the refrigerant channel inlet of the heat exchanger, and the refrigerant channel outlet is connected to the compressor inlet, so that the cooling capacity generated by the refrigerant circulation subsystem and the heat of the coolant circulation subsystem can be heat exchanged at the heat exchanger; the booster pump includes a first booster pump and a second booster pump arranged in parallel.

[0008] In one embodiment, the inlet section and outlet section of the branch where the first booster pump is located are respectively provided with a first valve and a first check valve, and the inlet section and outlet section of the branch where the second booster pump is located are respectively provided with a second valve and a second check valve.

[0009] In one embodiment, a condensing pressure regulating valve is provided on the inlet pipe or the outlet pipe of the condenser; a balancing branch is provided between the compressor and the liquid reservoir, one end of the balancing branch is connected to the outlet end of the compressor, and the other end is connected to the inlet end of the liquid reservoir, and a pressure differential valve is provided on the balancing branch so that the pressure differential valve is connected in parallel with the condenser and the condensing pressure regulating valve.

[0010] In one embodiment, a one-way valve is provided on the outlet pipeline of the compressor.

[0011] In one embodiment, an electric heater is provided in the liquid storage tank, and the electric heater is used to heat the coolant in the liquid storage tank.

[0012] In one embodiment, an expansion tank is provided on the top of the liquid storage tank; a pressure relief pipeline is provided on the liquid storage tank, a pressure relief valve is provided on the pressure relief pipeline, and an outlet end of the pressure relief pipeline is connected to the liquid collector.

[0013] In one embodiment, a flow meter, a liquid supply pressure sensor, and a liquid supply temperature sensor are provided on the inlet pipeline of the load.

[0014] In one embodiment, the branch line where the first booster pump is located and the branch line where the second booster pump is located merge into the main line and are connected to a heat exchanger. A filter is provided on the main line connecting the heat exchanger and the booster pump.

[0015] In one embodiment, the filter is a rotary self-sealing filter.

[0016] In one embodiment, the liquid storage tank is provided with a drain port for discharging the coolant in the liquid storage tank; the main pipe connecting the heat exchanger and the booster pump is provided with a liquid inlet and a filter in sequence along the coolant flow path.

[0017] Based on the above, compared with the prior art, the airborne liquid cooling system provided by the present invention has the following advantages:

[0018] The present invention adopts a compressor refrigerant circulation subsystem for refrigeration, solving the problem that the cooling effect of a forced air-cooled refrigeration system is limited by environmental factors and is difficult to meet the requirements of large heat exchange. The present invention also adopts a dual set of compressor refrigerant circulation subsystems (including a first refrigerant circulation subsystem and a second refrigerant circulation subsystem), each of which operates independently and rotates periodically. If one refrigerant circulation subsystem fails, the other can be started and immediately switched to a working state, thereby ensuring the normal operation of the system and improving the reliability of the equipment. Moreover, when the heat dissipation of the onboard equipment is large, the dual sets of compressor refrigerant circulation subsystems can operate simultaneously, thereby increasing the cooling capacity and expanding the temperature control range of the liquid cooling system. The opening of the refrigerant circulation subsystems can be combined according to different heat dissipation requirements, thereby improving the efficiency of the onboard power distribution.

[0019] The present invention integrates the refrigerant channels of the first refrigerant circulation subsystem and the second refrigerant circulation subsystem into the same heat exchanger to perform heat exchange with the secondary refrigerant circulation subsystem, thereby reducing the weight of the system and saving space for onboard equipment.

[0020] The coolant circulation subsystem of the present invention adopts a dual booster pump parallel design. The two booster pumps can be controlled and operated independently, and can be rotated periodically. If one booster pump fails, the other booster pump can be immediately switched to the working state, ensuring the normal operation of the liquid cooling system and improving the reliability of the equipment.

[0021] In summary, compared with the existing airborne air cooling form, the present invention achieves the cooling target faster and has a larger cooling capacity. In the face of airborne electronic products with different heat dissipation requirements, the present invention has more working combination forms and stronger scalability of cooling capacity. Under the condition of achieving the same cooling capacity target, it is smaller in size and lighter in weight than the existing airborne air cooling; each group of booster pumps and compressor refrigerant circulation subsystems can work independently, and the failure of a single booster pump will not affect the operation of the liquid cooling system, thereby ensuring the continuity of the operation of airborne electronic equipment, ensuring flight safety, and reserving sufficient time for crew support personnel to provide repair and maintenance services, thereby improving the life and reliability of the system.

[0022] Other features and beneficial effects of the present invention will be described in the following description, and in part will become apparent from the description, or will be understood by practicing the present invention. The objectives and other beneficial effects of the present invention can be achieved and obtained by the structures particularly pointed out in the description, claims and drawings. BRIEF DESCRIPTION OF THE DRAWINGS

[0023] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, a brief introduction will be given below to the drawings required for use in the embodiments or the description of the prior art. Obviously, the drawings described below are some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without any creative work. The positional relationships described in the drawings in the following description are based on the directions of the components drawn in the diagrams, unless otherwise specified.

[0024] Figure 1 A schematic diagram of the structure of an embodiment of the present invention Figure 1 ;

[0025] Figure 2 A schematic diagram of the structure of an embodiment of the present invention Figure 2 .

[0026] Reference numerals:

[0027] 100 Refrigerant circulation subsystem 110 Compressor 120 Check valve

[0028] 130 Condensing pressure regulating valve 140 Differential pressure valve 150 Condenser

[0029] 160 accumulator 170 throttling element 180 refrigerant channel

[0030] 100a First refrigerant circulation subsystem 110a First compressor 120a First check valve

[0031] System

[0032] 130a First condensing pressure regulating valve 140a First differential pressure valve 150a First condenser

[0033] 160a First accumulator 170a First throttling element 180a First refrigerant passage

[0034] 100b Second refrigerant circulation subsystem 110b Second compressor 120b Second check valve

[0035] System

[0036] 130b Second condensing pressure regulating valve 140b Second differential pressure valve 150b Second condenser

[0037] 160b Second accumulator 170b Second throttling element 180b Second refrigerant passage

[0038] 200 Coolant circulation subsystem 210 Liquid storage tank 220a First valve

[0039] 220b Second valve 230 Booster pump 230a First booster pump

[0040] 230b Second boost pump 240a First check valve 240b Second check valve

[0041] 250 filter 260 heat exchanger 261 coolant channel

[0042] 270 Load 271 Flowmeter 272 Liquid supply pressure sensor

[0043] 273 Liquid supply temperature sensor 211 Electric heater 212 Expansion tank

[0044] 213 pressure relief valve 214 liquid collector 215 liquid drain port

[0045] 251 Liquid inlet DETAILED DESCRIPTION

[0046] In order to make the purpose, technical solutions and advantages of the embodiments of the present invention clearer, the technical solutions in the embodiments of the present invention will be clearly and completely described below in conjunction with the drawings in the embodiments of the present invention. Obviously, the described embodiments are part of the embodiments of the present invention, not all of the embodiments; the technical features designed in different implementation modes of the present invention described below can be combined with each other as long as they do not conflict with each other; based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making creative work are within the scope of protection of the present invention.

[0047] In the description of the present invention, it should be noted that all terms used in the present invention (including technical terms and scientific terms) have the same meanings as those generally understood by ordinary technicians in the field to which the present invention belongs, and should not be understood as limiting the present invention; it should be further understood that the terms used in the present invention should be understood to have meanings consistent with the meanings of these terms in the context of this specification and in the relevant fields, and should not be understood in an idealized or overly formal sense, unless explicitly defined as such in the present invention.

[0048] The present invention provides Figure 1-2 An airborne liquid cooling system as shown in the embodiment includes:

[0049] The refrigerant circulation subsystem 100 includes a first refrigerant circulation subsystem 100a and a second refrigerant circulation subsystem 100b of independent refrigeration cycles;

[0050] The brine circulation subsystem 200 includes a liquid storage tank 210, a booster pump 230, and a heat exchanger 260, which are sequentially connected to the inlet and outlet ends of the load 270 to form a brine circulation loop;

[0051] Among them, each refrigerant circulation subsystem 100 includes a compressor 110, a condenser 150, a liquid reservoir 160 and a throttling element 170 connected in sequence to form a loop; the outlet of the throttling element 170 is connected to the inlet of the refrigerant channel 180 of the heat exchanger 260, and the outlet of the refrigerant channel 180 is connected to the inlet of the compressor 110, so that the cold energy generated by the refrigerant circulation subsystem 100 and the heat of the refrigerant circulation subsystem 200 are heat exchanged at the heat exchanger 260; the booster pump 230 includes a first booster pump 230a and a second booster pump 230b arranged in parallel.

[0052] Specifically, the connection route and working process of the refrigerant circulation subsystem 100 are as follows: each refrigerant circulation subsystem 100 includes a compressor 110, a condenser 150, a liquid accumulator 160, and a throttling element 170 connected in sequence to form a loop; the compressor 110 compresses the low-temperature, low-pressure refrigerant gas (i.e., the working fluid) into a high-temperature, high-pressure gas, and then sends the high-temperature, high-pressure refrigerant gas to the condenser 150 for cooling. The cooled refrigerant is then throttled and reduced in pressure by the throttling element 170, and the refrigerant becomes a low-temperature, low-pressure gas-liquid mixture. The refrigerant then enters the refrigerant channel 180 of the heat exchanger 260 for evaporation and gasification to absorb heat, so that it can exchange heat with the refrigerant of the refrigerant circulation subsystem 200. Finally, the refrigerant after absorbing heat is sucked into the compressor 110 for compression, and the cycle repeats itself. Among them, the condenser 150 selected in this embodiment is an air-cooled condenser 150, and the high-temperature, high-pressure refrigerant gas flowing through the condenser 150 is cooled by the external cooling airflow.

[0053] The refrigerant circulation subsystem 100 includes two sets of independently operated first refrigerant circulation subsystems 100a and second refrigerant circulation subsystems 100b. The structures of each refrigerant circulation subsystem 100 are the same, that is, the first refrigerant circulation subsystem 100a includes a first compressor 110a, a first condenser 150a, a first liquid accumulator 160a, and a first throttling element 170a connected in sequence to form a loop; the second refrigerant circulation subsystem 100b includes a second compressor 110a, a first condenser 150a, a first liquid accumulator 160a, and a first throttling element 170a connected in sequence to form a loop. 0b, a second condenser 150b, a second liquid accumulator 160b, and a second throttling element 170b; and the first refrigerant channel 180a and the second refrigerant channel 180b provided in the heat exchanger 260 are connected to the first refrigerant circulation subsystem 100a and the second refrigerant circulation subsystem 100b, respectively, so that the refrigerant channels 180 of the first refrigerant circulation subsystem 100a and the second refrigerant circulation subsystem 100b are integrated into the same heat exchanger 260 to perform heat exchange with the secondary refrigerant circulation subsystem 200;

[0054] The connection route and working process of the brine circulation subsystem 200 are as follows: the inlet of the liquid storage tank 210 is connected to the outlet of the load 270, the outlet end of the liquid storage tank 210 is connected to the inlet end of the booster pump 230, the outlet end of the booster pump 230 is connected to the inlet of the brine channel 261 of the heat exchanger 260, and the outlet of the brine channel 261 of the heat exchanger 260 is connected to the inlet of the load 270, forming a circulation loop; when in use, the brine in the liquid storage tank 210 is transported to the brine channel 261 of the heat exchanger 260 by the booster pump 230, and the cooling capacity of the refrigerant circulation subsystem 100 is heat-exchanged with the heat of the brine in the brine channel 261, and the temperature of the brine is reduced. Then, the brine that meets the temperature requirement is introduced into the load 270, and the temperature of the brine is increased after heat exchange in the load 270, and then it returns to the liquid storage tank 210, and the cycle is repeated to achieve the purpose of cooling the load 270;

[0055] Among them, the booster pump 230 includes two independently operated first booster pumps 230a and second booster pumps 230b arranged in parallel, that is, the outlet end of the liquid storage tank 210 is divided into two branches, which are respectively connected to the inlet ends of the first booster pump 230a and the second booster pump 230b, and then the outlet ends of the first booster pump 230a and the second booster pump 230b are merged into the main line and connected to the heat exchanger 260; adopting a dual booster pump 230 parallel design, the two booster pumps 230 can be controlled and operated independently.

[0056] The onboard liquid cooling system adopts the refrigerant circulation subsystem 100 composed of the compressor 110 group for refrigeration, which solves the problem that the cooling effect of the forced air cooling refrigeration system is limited by environmental factors and is difficult to meet the large heat exchange requirement; and adopts a double set of refrigerant circulation subsystems 100 (including a first refrigerant circulation subsystem 100a and a second refrigerant circulation subsystem 100b), each of which operates independently and rotates periodically. If one set of refrigerant circulation subsystems 100 fails, the other set can be started and switched to the working state immediately, ensuring the normal operation of the system and improving the reliability of the equipment; and when the heat dissipation of the onboard equipment is large, the double set of refrigerant circulation subsystems 100 can operate simultaneously, increasing the cooling capacity and expanding the temperature control range of the liquid cooling system. The opening of the refrigerant circulation subsystems 100 can be combined according to different heat dissipation requirements, thereby improving the efficiency of the onboard power distribution;

[0057] Moreover, the refrigerant channels 180 of the first refrigerant circulation subsystem 100a and the second refrigerant circulation subsystem 100b are integrated into the same heat exchanger 260 to perform heat exchange with the coolant circulation subsystem 200, which reduces the weight of the system and saves space for onboard equipment; the coolant circulation subsystem 200 adopts a dual booster pump 230 parallel design, and the two booster pumps 230 can be individually controlled and operated independently, and can be rotated periodically. If one of the booster pumps 230 fails, the other booster pump 230 can be immediately switched to the working state, ensuring the normal operation of the liquid cooling system and improving the reliability of the equipment.

[0058] It should be noted that the throttling element 170 in this embodiment is an expansion valve. According to the above design concept, the throttling element 170 may also adopt other existing throttling elements 170, such as a capillary tube, including but not limited to an expansion valve.

[0059] It should be noted that the condenser 150 described in this embodiment is an air-cooled condenser 150, which cools the high-temperature and high-pressure refrigerant gas flowing through the condenser 150 by the external cold air flow. According to the above design concept, the condenser 150 can also adopt other types of condensers 150 and other cooling methods, including but not limited to the scheme of this embodiment.

[0060] Preferably, the inlet section and outlet section of the branch where the first boosting pump 230a is located are respectively provided with a first valve 220a and a first check valve 240a, and the inlet section and outlet section of the branch where the second boosting pump 230b is located are respectively provided with a second valve 220b and a second check valve 240b.

[0061] like Figure 1-2 As shown, the inlet section and outlet section of the branch where the first boosting pump 230a is located are respectively provided with a first valve 220a and a first check valve 240a, and the inlet section and outlet section of the branch where the second boosting pump 230b is located are respectively provided with a second valve 220b and a second check valve 240b, that is, the outlet end of the liquid storage tank 210 is divided into two branches, which are respectively connected to the inlet ends of the first valve 220a and the second valve 220b, the outlet of the first valve 220a is connected to the inlet of the first boosting pump 230a, the outlet of the second valve 220b is connected to the inlet of the second boosting pump 230b, the outlet of the first boosting pump 230a is connected to the inlet of the first check valve 240a, and the outlet of the second boosting pump 230b is connected to the inlet of the second check valve 240b. The outlets of the first check valve 240a and the second check valve 240b merge into the main pipeline and are then connected to the inlet of the refrigerant channel 261 of the heat exchanger 260.

[0062] The inlets and outlets of the two booster pumps 230 are respectively provided with valves and check valves. When the booster pump 230 needs to be inspected or maintained, the first valve 220a or the second valve 220b can be closed to disconnect the booster pump 230 from the system, and the faulty pump can be quickly isolated from the system. The booster pump 230 can be inspected or replaced without draining the refrigerant circulation subsystem 200. If any one of the booster pumps 230 is removed, the other booster pump 230 can operate normally, and the refrigerant circulation subsystem 200 can operate normally, thereby improving the maintainability of the equipment. A check valve is provided at the outlet end of the booster pump 230 to prevent the refrigerant from flowing back.

[0063] Preferably, in this embodiment, the first valve 220a and the second valve 220b are ball valves;

[0064] The ball valve has the characteristics of low resistance and can quickly close and block the fluid. It should be noted that, according to the above design concept, the first valve 220a and the second valve 220b can also adopt other types of valves, including but not limited to the ball valves described in the preferred embodiment.

[0065] Preferably, a condensing pressure regulating valve 130 is provided on the inlet pipe or the outlet pipe of the condenser 150; a balancing branch is provided between the compressor 110 and the liquid reservoir 160, one end of the balancing branch is connected to the outlet end of the compressor 110, and the other end is connected to the inlet end of the liquid reservoir 160, and a differential pressure valve 140 is provided on the balancing branch so that the differential pressure valve 140 is connected in parallel with the condenser 150 and the condensing pressure regulating valve 130.

[0066] like Figure 1-2 In the embodiment shown, the exhaust port (i.e., outlet end) of compressor 110 is connected to the inlet end of condensing pressure regulating valve 130, which is connected to the inlet end of condenser 150, which is connected to the inlet end of liquid accumulator 160. A balancing branch pipe is provided between compressor 110 and liquid accumulator 160, one end of which is connected to the exhaust port (i.e., outlet end) of compressor 110 and the other end to the inlet end of liquid accumulator 160. A differential pressure valve 140 is provided on the balancing branch pipe, so that differential pressure valve 140 is connected in parallel with condenser 150 and condensing pressure regulating valve 130. Both refrigerant circulation subsystems 100 are equipped with the above-described structure, i.e., the first refrigerant circulation subsystem 100a is equipped with a corresponding first condensing pressure regulating valve 130a, a balancing branch pipe, and a first differential pressure valve 140a, and the second refrigerant circulation subsystem 100b is equipped with a corresponding second condensing pressure regulating valve 130b, a balancing branch pipe, and a second differential pressure valve 140b.

[0067] When the refrigerant circulation subsystem 100 is in operation, if the condensing pressure is too high, the exhaust temperature of the compressor 110 will rise, the compression ratio will increase, the cooling capacity will decrease, and the power consumption will increase. The higher the condensing pressure, the greater the above-mentioned adverse effects. The high condensing pressure is mainly seen in summer, and the condensing pressure should be reduced as much as possible at this time. When the refrigerant circulation subsystem 100 is in operation, the condensing pressure may be too low under low temperature conditions, and the pressure difference before and after the throttling element 170 (such as the expansion valve) is too small, resulting in insufficient liquid supply power. At the same time, the liquid is easily vaporized before entering the throttling element 170, affecting the refrigerant flow capacity of the throttling element 170, and easily causing liquid shortage in the heat absorption area (i.e., the refrigerant channel 180), resulting in a significant decrease in the cooling capacity of the unit. It can be seen that when the refrigerant circulation subsystem 100 is in operation, if the condensing pressure is too high or too low, it will have an adverse effect on the operation of the equipment. Therefore, in the preferred embodiment, by controlling the fluctuation range of the condensing pressure, it is beneficial to further improve the economy and reliability of the equipment operation.

[0068] By setting a condensing pressure regulating valve 130 at the inlet of the condenser 150 and using it in conjunction with the pressure differential valve 140 on the balancing branch pipe, the condensing pressure is kept within a normal range; specifically, Figure 1-2 In the embodiment shown, the process of the condensing pressure regulating valve 130 and the pressure differential valve 140 cooperating to regulate the condensing pressure is as follows: the regulating range of the condensing pressure regulating valve 130 is 5 to 17.5 bar, and the initial value is 10 bar. By adjusting its "adjusting nut", the set value of the condensing pressure regulating valve 130 can be adjusted within the allowable range. When the inlet pressure reaches the set value, the condensing pressure regulating valve 130 opens, indicating that the pressure value in the condenser 150 has also reached the set value, which can ensure that the condenser 150 operates within the set value range; before the condensing pressure does not reach the set value of the condensing pressure regulating valve 130, the condensing pressure regulating valve 130 is closed. Since the initial value of the pressure differential valve 140 in the balancing branch is 1.4 bar when it is opened, when the pressure differential valve 140 When the pressure difference ΔP before and after reaches the initial value, the valve plate in the pressure differential valve 140 begins to open, bypassing the refrigerant from the compressor 110 to the liquid accumulator 160. When the pressure difference reaches 3 bar, the pressure differential valve 140 reaches the maximum opening. Since the high-pressure hot air from the compressor 110 directly enters the liquid accumulator 160, the condensing pressure of the unit is increased at startup, thereby ensuring that the condensing pressure of the unit is relatively stable when the outdoor temperature is very low; when the condensing pressure of the air conditioner recovers and the pressure difference before and after the condenser 150 is lower than the initial setting value of the pressure differential valve 140, the pressure differential valve 140 closes, ensuring that the balancing branch is closed when the condensing pressure regulating valve 130 is opened, thereby keeping the condensing pressure within the normal range and ensuring that the compressor 110 operates at the optimal condensing pressure.

[0069] Similarly, except for Figure 1-2In addition to the solution of disposing the condensing pressure regulating valve 130 on the inlet pipe of the condenser 150 in the illustrated embodiment, according to the above-mentioned design concept, the condensing pressure regulating valve 130 may also be disposed on the outlet pipe of the condenser 150, and the differential pressure valve 140 on the balancing branch pipe is connected in parallel with the condenser 150 and the condensing pressure regulating valve 130. Based on this arrangement, the condensing pressure can also be maintained within a normal range. Its operating principle is similar to that of the solution of disposing the condensing pressure regulating valve 130 on the inlet pipe of the condenser 150, and will not be repeated here.

[0070] It should be noted that the condensing pressure regulating valve 130 is an existing pressure regulating valve, also known as a self-operated pressure regulating valve. The pressure regulating valve is an existing energy-saving device that does not require external energy but relies solely on the pressure change of the regulating medium itself to automatically adjust the pressure; the differential pressure valve 140 is also an existing valve. According to the above design concept, those skilled in the art can select existing suitable models of pressure regulating valves and differential pressure valves 140 according to their needs; regarding the process of adjusting the condensing pressure in the embodiment, the specific adjustment range (5~17.5bar) and initial value (10bar) of the specific condensing pressure regulating valve 130, the initial value (1.4bar) and the pressure differential value at maximum opening (3bar) of the differential pressure valve 140 are described. These parameters are only used to illustrate the technical solution of the present invention, and are not intended to limit it. Those skilled in the art can make adaptive adjustments to it, and such adjustments do not cause the essence of the corresponding technical solution to deviate from the scope of the technical solution of each embodiment of the present invention.

[0071] Preferably, a one-way valve 120 is provided on the outlet pipeline of the compressor 110 .

[0072] When the condensing pressure regulating valve 130 is installed on the outlet pipe of the condenser 150, a one-way valve 120 is installed on the outlet pipe of the compressor 110. That is, the exhaust port of the compressor 110 is connected to the inlet of the one-way valve 120, and the outlet of the one-way valve 120 is connected to the inlet of the condenser 150. The refrigerant gas compressed by the compressor 110 flows through the one-way valve 120 and then enters the condenser 150. Both refrigerant circulation subsystems 100 are equipped with one-way valves 120 on the outlet pipes of the compressors 110. That is, the outlet pipe of the first compressor 110a of the first refrigerant circulation subsystem 100a is equipped with a first one-way valve 120a, and the outlet pipe of the second compressor 110b of the second refrigerant circulation subsystem 100b is equipped with a second one-way valve 120b. This arrangement prevents the liquid refrigerant in the condenser 150 from flowing back into the compressor 110, causing liquid hammer when the compressor 110 is started and damaging the compressor 110.

[0073] When the condensing pressure regulating valve 130 is set on the inlet pipe of the condenser 150, the condensing pressure regulating valve 130 is set in front of the inlet of the condenser 150. The condensing pressure regulating valve 130 can also act as a one-way valve. Therefore, the one-way valve 120 can also be discarded at this time.

[0074] Preferably, an electric heater 211 is provided in the liquid storage tank 210 , and the electric heater 211 is used to heat the coolant in the liquid storage tank 210 .

[0075] Liquid storage tank 210 is equipped with an electric heater 211. When the ambient temperature is low, the brine temperature also decreases, the brine viscosity increases, and the flow resistance increases accordingly, which increases the starting resistance of booster pump 230. At this time, electric heater 211 can be turned on to preheat the brine, which can significantly reduce the starting resistance of booster pump 230, ensure the normal starting of booster pump 230, prevent booster pump 230 from being blocked for a long time, and extend the life of booster pump 230. In low temperature conditions, it can also provide a stable heat flow to onboard electronic equipment or onboard batteries, allowing them to start and operate at the appropriate temperature.

[0076] When the electric heater 211 is in working state, the first refrigerant circulation subsystem 100a and the second refrigerant circulation subsystem 100b of the refrigerant circulation subsystem 100 are in standby state; when the load 270 is small and lower than the cooling capacity of the refrigerant circulation subsystem 100 with a single set of compressors 110, the first refrigerant circulation subsystem 100a and the second refrigerant circulation subsystem 100b can perform periodic rotation work; when the load 270 is large and higher than the cooling capacity of the refrigerant circulation subsystem 100 with a single set of compressors 110, the first refrigerant circulation subsystem 100a and the second refrigerant circulation subsystem 100b are started at the same time to provide cooling for the load 270. Through the coordinated operation of the electric heater 211 in the liquid storage tank 210, the first refrigerant circulation subsystem 100a and the second refrigerant circulation subsystem 100b, the utilization efficiency of the onboard power distribution is improved, the reliability of the onboard liquid cooling system is increased, and the life of the unit is extended.

[0077] Preferably, an expansion tank 212 is provided on the top of the liquid storage tank 210 ; a pressure relief pipeline is provided on the liquid storage tank 210 , a pressure relief valve 213 is provided on the pressure relief pipeline, and an outlet end of the pressure relief pipeline is connected to a liquid collector 214 .

[0078] Liquid storage tank 210 is equipped with an expansion tank 212, which can maintain constant pressure in the system and maintain internal pressure balance. A pressure relief line is installed on the liquid storage tank 210, and a pressure relief valve 213 is installed on the pressure relief line. When the system pressure reaches a safe operating pressure, it automatically opens to discharge air or liquid from the brine circulation subsystem 200, reducing the operating pressure and ensuring safe operation of the system. The outlet of the pressure relief line is connected to a liquid collector 214 to prevent the brine from flowing into the cabin. The liquid collector 214 can also be quickly removed, allowing waste liquid in the collector 214 to be cleaned during regular system maintenance.

[0079] Preferably, a flow meter 271 , a liquid supply pressure sensor 272 and a liquid supply temperature sensor 273 are provided on the inlet pipeline of the load 270 .

[0080] A flow meter 271, a liquid supply pressure sensor 272, and a liquid supply temperature sensor 273 are provided on the inlet pipeline of the load 270, that is, a flow meter 271, a liquid supply pressure sensor 272, and a liquid supply temperature sensor 273 are provided on the connecting pipeline between the heat exchanger 260 and the load 270. Such a setting can monitor the liquid supply status of the refrigerant circulation subsystem 200 in real time, and the control-on-board liquid cooling system can make judgments based on the collected data and adjust the working modes of the refrigerant circulation subsystem 100 and the booster pump 230.

[0081] Preferably, the branch line where the first booster pump 230a and the branch line where the second booster pump 230b are located merge into the main line and are connected to the heat exchanger 260. A filter 250 is provided on the main line connecting the heat exchanger 260 and the booster pump 230. The filter 250 filters and purifies the refrigerant flowing through.

[0082] Preferably, the filter 250 is a rotary self-sealing filter 250 .

[0083] The filter 250 is a rotary self-sealing filter 250, and the filter element can be replaced online, which improves the maintainability of the system;

[0084] Preferably, a pressure sensor is provided at the inlet of the filter 250, and the pressure sensor and the liquid supply pressure sensor 272 can be combined to determine dirt and blockage, and report dirt and blockage prompts so that operators can perform maintenance.

[0085] Preferably, the liquid storage tank 210 is provided with a drain port 215 for discharging the coolant in the liquid storage tank 210; the main pipe connecting the heat exchanger 260 and the booster pump 230 is provided with a liquid inlet 251 and a filter 250 along the coolant flow path.

[0086] The drain port 215 on the liquid storage tank 210 is used to discharge the refrigerant in the liquid storage tank 210. A liquid inlet 251 and a filter 250 are provided in sequence along the refrigerant flow path on the main line connecting the heat exchanger 260 and the booster pump 230. The liquid inlet 251 is used to replenish the refrigerant, and the newly replenished refrigerant is first filtered and purified by the filter 250 before entering the loop of the refrigerant circulation subsystem 200.

[0087] Preferably, the condenser 150 (i.e., the first condenser 150a and the second condenser 150b) is a microchannel heat exchanger 260 or a wire-and-tube heat exchanger 260. Preferably, the heat exchanger 260 is a plate heat exchanger 260 or a wire-and-tube heat exchanger 260. Preferably, the flowmeter 271 is a turbine flowmeter 271 or an ultrasonic flowmeter 271. Preferably, the compressor 110 (i.e., the first compressor 110a and the second compressor 110b) is a scroll compressor 110. It should be noted that the condenser 150, heat exchanger 260, flowmeter 271, and compressor 110 are existing devices. Based on the above design concept, those skilled in the art can adaptably select existing types or models of the condenser 150, heat exchanger 260, flowmeter 271, and compressor 110 according to their needs, including but not limited to the above-mentioned types of condenser 150, heat exchanger 260, flowmeter 271, and compressor 110.

[0088] In summary, compared with the prior art, the airborne liquid cooling system provided by the present invention has the following technical effects:

[0089] (1) The present invention adopts a refrigerant circulation subsystem 100 composed of a compressor 110 for refrigeration, thereby solving the problem that the cooling effect of a forced air-cooled refrigeration system is limited by environmental factors and is difficult to meet the requirements of large heat exchange. In addition, a double set of refrigerant circulation subsystems 100 is adopted, and each refrigerant circulation subsystem 100 operates independently and performs periodic rotation. If one set of refrigerant circulation subsystems 100 fails, the other set can be started and immediately switched to a working state, thereby ensuring the normal operation of the system and improving the reliability of the equipment. When the heat dissipation of the onboard equipment is large, the double set of refrigerant circulation subsystems 100 can operate simultaneously, thereby increasing the cooling capacity and expanding the temperature control range of the liquid cooling system. The opening of the refrigerant circulation subsystems 100 can be combined according to different heat dissipation requirements, thereby improving the efficiency of the onboard power distribution.

[0090] (2) The present invention integrates the refrigerant channels 180 of the first refrigerant circulation subsystem 100a and the second refrigerant circulation subsystem 100b into the same heat exchanger 260 to perform heat exchange with the secondary refrigerant circulation subsystem 200, thereby reducing the weight of the system and saving space for onboard equipment.

[0091] (3) The refrigerant circulation subsystem 200 of the present invention adopts a parallel design of dual booster pumps 230. The two booster pumps 230 can be controlled and operated independently, and can be rotated periodically. If one of the booster pumps 230 fails, the other booster pump 230 can be immediately switched to a working state, thereby ensuring the normal operation of the liquid cooling system and improving the reliability of the equipment.

[0092] (4) In the present invention, valves and check valves are respectively provided at the inlets and outlets of the two booster pumps 230. When the booster pump 230 needs to be inspected or maintained, the first valve 220a or the second valve 220b can be closed to disconnect the booster pump 230 from the system, and the faulty pump can be quickly isolated from the system. The booster pump 230 can be inspected or replaced without draining the refrigerant circulation subsystem 200. When any one of the booster pumps 230 is removed, the refrigerant circulation subsystem 200 can operate normally, thereby improving the maintainability of the equipment.

[0093] (5) The present invention installs an electric heater 211 in the liquid storage tank 210. In a low-temperature state, the electric heater 211 can preheat the coolant to ensure the normal start-up of the booster pump 230, thereby increasing the service life of the equipment; in a low-temperature state, the onboard electronic equipment can be preheated to enable it to start or operate at an appropriate temperature.

[0094] (6) The present invention installs a pressure relief valve 213 on the pressure relief pipeline on the liquid storage tank 210 to discharge the air in the refrigerant circulation subsystem 200; the outlet end of the pressure relief pipeline is connected to the liquid collector 214 to prevent the refrigerant from flowing into the cabin, and the liquid collector 214 can be quickly disassembled and cleaned during regular maintenance of the system.

[0095] (7) The present invention sets a flow meter 271, a liquid supply temperature sensor 273 and a liquid supply pressure sensor 272 on the inlet pipeline of the load 270, and accurately controls the flow and temperature based on the collected data, thereby improving work efficiency and reducing energy consumption.

[0096] (8) The filter 250 on the refrigerant circulation subsystem 200 is a rotary self-sealing filter 250, and the filter element can be replaced when the system contains liquid. Pressure sensors are provided on the inlet and outlet pipes of the filter 250, which can provide a dirt and blockage alarm, thereby increasing the maintainability of the equipment.

[0097] The present invention provides an airborne liquid cooling system that utilizes a refrigerant circulation subsystem 100 (including a first refrigerant circulation subsystem 100a and a second refrigerant circulation subsystem 100b) for cooling. The coolant is supplied by dual booster pumps 230 operating independently in parallel. Compared to existing airborne air cooling systems, this airborne liquid cooling system reaches its cooling target faster and has a greater cooling capacity. For airborne electronic products with different heat dissipation requirements, the present invention offers a wider range of working combinations and greater scalability in cooling capacity. While achieving the same cooling capacity target, it is smaller and lighter than existing airborne air cooling systems. Each set of booster pumps 230 and refrigerant circulation subsystem 100 can operate independently, and a failure of a single booster pump 230 does not affect the operation of the liquid cooling system. This ensures the continuity of operation of airborne electronic equipment, safeguards flight safety, and leaves ample time for crew support personnel to provide repair and maintenance services, thereby increasing the lifespan and reliability of the system.

[0098] In addition, those skilled in the art should understand that, although there are many problems in the prior art, each embodiment or technical solution of the present invention may be improved in only one or several aspects, without having to simultaneously solve all the technical problems listed in the prior art or background art. Those skilled in the art should understand that any content not mentioned in a claim should not be construed as limiting the claim.

[0099] Although terms such as refrigerant circulation subsystem, secondary refrigerant circulation subsystem, load, liquid storage tank, and booster pump are frequently used herein, the possibility of using other terms is not excluded. These terms are used only to more conveniently describe and explain the essence of the present invention; interpreting them as any additional limitations is contrary to the spirit of the present invention. In the description and claims of the embodiments of the present invention and the above-mentioned drawings, the terms "first," "second," and so on (if any) are used to distinguish similar objects and are not necessarily used to describe a specific order or sequence.

[0100] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention, rather than to limit it. Although the present invention has been described in detail with reference to the above embodiments, those skilled in the art should understand that they can still modify the technical solutions described in the above embodiments, or replace some or all of the technical features therein with equivalents. However, these modifications or replacements do not cause the essence of the corresponding technical solutions to deviate from the scope of the technical solutions of the embodiments of the present invention.

Claims

1. An airborne liquid cooling system, characterized in that: include: The refrigerant circulation subsystem includes a first refrigerant circulation subsystem and a second refrigerant circulation subsystem of independent refrigeration cycles; The brine circulation subsystem includes a liquid storage tank, a booster pump, and a heat exchanger connected in sequence to the load inlet and outlet to form a brine circulation loop; Each refrigerant circulation subsystem includes a compressor, a condenser, a liquid accumulator, and a throttling element connected in sequence to form a loop; the outlet of the throttling element is connected to the refrigerant channel inlet of the heat exchanger, and the refrigerant channel outlet is connected to the compressor inlet, so that the cooling energy generated by the refrigerant circulation subsystem and the heat of the secondary refrigerant circulation subsystem are heat-exchanged at the heat exchanger; the booster pump includes a first booster pump and a second booster pump arranged in parallel; The inlet section and outlet section of the branch where the first booster pump is located are respectively provided with a first valve and a first check valve, and the inlet section and outlet section of the branch where the second booster pump is located are respectively provided with a second valve and a second check valve; A condensing pressure regulating valve is provided on the inlet pipe or the outlet pipe of the condenser; A balancing branch pipe is provided between the compressor and the liquid accumulator, one end of the balancing branch pipe is connected to the outlet end of the compressor, and the other end is connected to the inlet end of the liquid accumulator, and a pressure differential valve is provided on the balancing branch pipe so that the pressure differential valve is connected in parallel with the condenser and the condensing pressure regulating valve; A one-way valve is provided on the outlet pipe of the compressor; an electric heater is provided in the liquid storage tank, and the electric heater is used to heat the coolant in the liquid storage tank; An expansion tank is provided on the top of the liquid storage tank; The liquid storage tank is provided with a pressure relief pipeline, the pressure relief pipeline is provided with a pressure relief valve, and the outlet end of the pressure relief pipeline is connected to the liquid collector; the inlet pipeline of the load is provided with a flow meter, a liquid supply pressure sensor and a liquid supply temperature sensor; The branch where the first booster pump is located and the branch where the second booster pump is located are connected to the heat exchanger after merging into the main line. A filter is provided on the main line connecting the heat exchanger and the booster pump; the filter is a rotary self-sealing filter.

2. The airborne liquid cooling system according to claim 1, characterized in that: The liquid storage tank is provided with a drain port for discharging the coolant in the liquid storage tank; the main pipe connecting the heat exchanger and the booster pump is provided with a liquid inlet and a filter in sequence along the coolant flow path.

Images