CN216721916U - Airborne liquid cooling system - Google Patents

Abstract

The utility model relates to the field of airborne environment control, in particular to an airborne liquid cooling system. This airborne liquid cooling system includes: a refrigerant circulation subsystem including a first refrigerant circulation subsystem and a second refrigerant circulation subsystem of independent refrigeration cycles; the secondary refrigerant circulation subsystem comprises a liquid storage tank, a booster pump and a heat exchanger which are sequentially connected with the inlet end and the outlet end of the load to form a secondary refrigerant circulation loop; each refrigerant circulation subsystem comprises a compressor, a condenser, a liquid storage device and a throttling element which are sequentially connected to form a loop; the outlet of the throttling element is connected with the inlet of a refrigerant channel of the heat exchanger, and the outlet of the refrigerant channel is connected with the inlet of the compressor; the booster pump comprises a first booster pump and a second booster pump which are arranged in parallel. The airborne liquid cooling system can meet the heat dissipation requirement of airborne equipment, can guarantee the working continuity of airborne electronic equipment, guarantees flight safety, and improves the service life and reliability of an airborne electronic system.

Description

Airborne liquid cooling system

Technical Field

The utility model relates to the field of airborne environmental control, in particular to an airborne liquid cooling system.

Background

With the development of modern aircraft avionics technology and the continuous progress of the manufacturing technology of power devices of airborne electronic equipment, the assembly density and the power density of the airborne electronic equipment are continuously improved, and a cooling system not only solves the heat dissipation problem of high-power equipment and meets the reliability work of the airborne equipment, but also meets the requirement of temperature consistency of each component of each equipment; therefore, a feasible cooling method and an excellent cooling effect become more and more important supports for providing high reliability indexes for the on-board electronic equipment. With the development of technologies such as shipboard aircrafts and unmanned aerial vehicles, more airborne electronic equipment needs to be arranged in a limited space, and higher requirements are provided for miniaturization and light weight of the airborne equipment.

At present, a common airborne device adopts a forced air cooling mode for heat dissipation, a refrigerating system of the forced air cooling has large weight and volume, and is not beneficial to weight reduction and space expansion of an aircraft, the refrigerating system of the forced air cooling is limited by factors such as flight speed, height and the like, and the refrigerating system of the forced air cooling can not meet the requirement of large heat exchange capacity generally along with the continuous improvement of the thermal load of the airborne device; modern aircraft avionics technology is rapidly developed, the cross-linking relation between electronic equipment is more and more complex, and the dependence and requirements on airborne electronic equipment are higher and higher, so that how to develop an airborne liquid cooling system which has feasible cooling mode, excellent cooling effect and portability and miniaturization to ensure the continuity of the work of airborne heating equipment and realize the safe, efficient and reliable operation of airborne electronic equipment is just a problem to be considered and solved in the field.

SUMMERY OF THE UTILITY MODEL

The problem that the existing forced air cooling refrigeration system in the background art has large weight and volume and the cooling effect is limited by environmental factors and is difficult to meet the requirement of large heat exchange amount is solved; the utility model provides an airborne liquid cooling system, comprising:

a refrigerant circulation subsystem including a first refrigerant circulation subsystem and a second refrigerant circulation subsystem of independent refrigeration cycles;

the secondary refrigerant circulation subsystem comprises a liquid storage tank, a booster pump and a heat exchanger which are sequentially connected with the inlet end and the outlet end of the load to form a secondary refrigerant circulation loop;

each refrigerant circulation subsystem comprises a compressor, a condenser, a liquid storage device and a throttling element which are sequentially connected to form a loop; the outlet of the throttling element is connected with the inlet of a refrigerant channel of the heat exchanger, and the outlet of the refrigerant channel is connected with the inlet of the compressor, so that the cold energy generated by the refrigerant circulation subsystem and the heat of the secondary refrigerant circulation subsystem exchange heat at the heat exchanger; the booster pump comprises a first booster pump and a second booster pump which are arranged in parallel.

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

In one embodiment, a condensing pressure regulating valve is arranged on an inlet pipeline or an outlet pipeline of the condenser; be equipped with the balance branch pipe between compressor and the reservoir, the one end of balance branch pipe is connected with the exit end of compressor, and the other end is connected with the entry end of reservoir, and is equipped with the differential pressure valve on the balance branch pipe to make differential pressure valve and condenser, condensing pressure governing valve parallel connection.

In one embodiment, a one-way valve is arranged on the outlet pipeline of the compressor.

In one embodiment, an electric heater is arranged in the liquid storage tank and used for heating the secondary refrigerant in the liquid storage tank.

In one embodiment, an expansion tank is arranged at 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 with the liquid collector.

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

In one embodiment, the branch where the first booster pump is located and the branch where the second booster pump is located are connected with the heat exchanger after being converged into the main pipeline, and a filter is arranged on the main pipeline connecting the heat exchanger and the booster pumps.

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

In one embodiment, the liquid storage tank is provided with a liquid discharging port for discharging secondary refrigerant in the liquid storage tank; and a main pipeline connected between the heat exchanger and the booster pump is sequentially provided with a liquid inlet and a filter along a secondary refrigerant flowing path.

Based on the above, compared with the prior art, the onboard liquid cooling system provided by the utility model has the following advantages:

the utility model adopts the compressor refrigerant circulating subsystem for refrigeration, and solves the problem that the cooling effect of the forced air-cooled refrigeration system is limited by environmental factors and is difficult to meet the requirement of large heat exchange amount; in addition, the utility model adopts double sets of compressor refrigerant circulating subsystems (comprising a first refrigerant circulating subsystem and a second refrigerant circulating subsystem), each refrigerant circulating subsystem operates independently to carry out cycle rotation, and when one set of refrigerant circulating subsystem fails, the other set of refrigerant circulating subsystem can be started to immediately switch to a working state, thereby ensuring the normal operation of the system and improving the reliability of the equipment; when airborne equipment has large heat dissipation capacity, the refrigerant circulation subsystems of the double compressors can run simultaneously, so that the refrigerating capacity is improved, the temperature control range of the liquid cooling system is expanded, the opening of the refrigerant circulation subsystems can be combined according to different heat dissipation requirements, and the airborne power distribution efficiency is improved;

the refrigerant channels of the first refrigerant circulation subsystem and the second refrigerant circulation subsystem are integrated into the same heat exchanger to exchange heat with the secondary refrigerant circulation subsystem, so that the weight of the system is reduced, and the space of airborne equipment is saved;

the secondary refrigerant circulation subsystem adopts the parallel design of the double booster pumps, the two booster pumps can independently control and operate, the cycle value can be carried out, one booster pump fails, and the other booster pump can be immediately switched to a working state, so that the normal operation of a liquid cooling system is ensured, and the reliability of equipment is improved;

compared with the existing airborne air cooling mode, the time for achieving the refrigeration target is faster, the refrigerating capacity is larger, the working combination mode is more, the expansibility of the refrigerating capacity is stronger in the face of airborne electronic products with different heat dissipation capacity requirements, and the size is smaller and the weight is lighter than that of the existing airborne air cooling mode under the condition of achieving the same refrigerating capacity target; each group of booster pumps and each compressor refrigerant circulation subsystem can work independently, the operation of the liquid cooling system is not influenced by the faults of the single booster pump, the working continuity of airborne electronic equipment is ensured, the flight safety is ensured, sufficient time is reserved for maintenance service provided for unit support personnel, and the service life and the reliability of the system are improved.

Additional features and advantages of the utility model will be set forth in the description which follows, and in part will be obvious from the description, or may be learned by practice of the utility model. The objectives and other advantages of the utility model will be realized and attained by the structure particularly pointed out in the written description and claims hereof as well as the appended drawings.

Drawings

In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings needed to be used in the description of the embodiments or the prior art will be briefly introduced below, and it is obvious that the drawings in the following description are some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to the drawings without creative efforts; in the following description, the drawings are illustrated in a schematic view, and the drawings are not intended to limit the present invention.

Fig. 1 is a first schematic structural diagram according to an embodiment of the present invention;

fig. 2 is a schematic structural diagram of a second embodiment of the present invention.

Reference numerals:

100 refrigerant circulation subsystem 110 compressor 120 check valve

130 condensing pressure regulating valve 140 differential pressure valve 150 condenser

160 accumulator 170 throttling element 180 refrigerant passage

100a first refrigerant circulation sub-system 110a first compressor 120a first check valve

130a first condensing pressure regulating valve 140a first differential pressure valve 150a first condenser

160a first accumulator 170a first throttling element 180a first refrigerant passage

100b second refrigerant circulation sub-system 110b second compressor 120b second check valve

130b second condensing pressure regulating valve 140b second differential pressure valve 150b second condenser

160b second accumulator 170b second throttling element 180b second refrigerant passage

200 coolant circulation subsystem 210 reservoir 220a first valve

220b second valve 230 booster pump 230a first booster pump

230b second booster pump 240a first check valve 240b second check valve

250 filter 260 heat exchanger 261 coolant channels

270 load 271 flowmeter 272 feed liquid pressure sensor

273 liquid supply temperature sensor 211 electric heater 212 expansion tank

213 relief valve 214 liquid trap 215 tap

251 liquid inlet

Detailed Description

In order to make the objects, 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 with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are some embodiments of the present invention, but not all embodiments; the technical features designed in the different embodiments of the present invention described below can be combined with each other as long as they do not conflict with each other; all other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.

In the description of the present invention, it is to be noted that all terms (including technical and scientific terms) used herein have the same meaning as commonly understood by one of ordinary skill in the art to which the present invention belongs, and are not to be construed as limiting the present invention; it will be further understood that terms used herein should be interpreted as having a meaning that is consistent with their meaning in the context of this specification and the relevant art and will not be interpreted in an idealized or overly formal sense unless expressly so defined herein.

The present invention provides an airborne liquid cooling system as shown in the embodiment of fig. 1-2, comprising:

a refrigerant-circulating subsystem 100 including a first refrigerant-circulating subsystem 100a and a second refrigerant-circulating subsystem 100b of independent refrigeration cycles;

a coolant circulation subsystem 200 including a liquid storage tank 210, a booster pump 230, and a heat exchanger 260, which are connected to the inlet and outlet ends of a load 270 in this order to form a coolant circulation circuit;

each refrigerant circulation subsystem 100 comprises a compressor 110, a condenser 150, an accumulator 160 and a throttling element 170 which are sequentially connected to form a loop; the outlet of the throttling element 170 is connected with the inlet of a refrigerant channel 180 of the heat exchanger 260, and the outlet of the refrigerant channel 180 is connected with the inlet of the compressor 110, so that the cold energy generated by the refrigerant circulation subsystem 100 and the heat energy of the secondary refrigerant circulation subsystem 200 exchange heat at the heat exchanger 260; the booster pumps 230 include a first booster pump 230a and a second booster pump 230b arranged in parallel.

Specifically, the connection route and the operation process of the refrigerant circulation subsystem 100 are as follows: each refrigerant circulation subsystem 100 comprises a compressor 110, a condenser 150, an accumulator 160 and a throttling element 170 which are sequentially connected to form a loop; the compressor 110 compresses low-temperature low-pressure refrigerant gas (i.e. working medium) into high-temperature high-pressure gas, then the high-temperature high-pressure gas of the refrigerant is sent to the condenser 150 for cooling, then the cooled refrigerant is throttled and depressurized by the throttling element 170, the refrigerant becomes a low-temperature low-pressure gas-liquid mixture, then the refrigerant enters the refrigerant channel 180 of the heat exchanger 260 for evaporation, gasification and heat absorption so as to exchange heat with the secondary refrigerant of the secondary refrigerant circulation subsystem 200, and finally the refrigerant after heat absorption is sucked and compressed by the compressor 110, thus the cycle is repeated; the condenser 150 in this embodiment is an air-cooled condenser 150, and cools the high-temperature and high-pressure refrigerant gas flowing through the condenser 150 by the external cooling airflow.

The refrigerant circulation subsystem 100 includes two sets of first and second refrigerant circulation subsystems 100a and 100b which operate independently, and each refrigerant circulation subsystem 100 has the same structure, that is, the first refrigerant circulation subsystem 100a includes a first compressor 110a, a first condenser 150a, a first accumulator 160a and a first throttling element 170a which are connected in sequence to form a loop; the second refrigerant circulation subsystem 100b comprises a second compressor 110b, a second condenser 150b, a second accumulator 160b and a second throttling element 170b which are sequentially connected to form a loop; a first refrigerant channel 180a and a second refrigerant channel 180b arranged in the heat exchanger 260 are respectively connected with the first refrigerant circulating subsystem 100a and the second refrigerant circulating subsystem 100b, and the refrigerant channels 180 of the first refrigerant circulating subsystem 100a and the second refrigerant circulating subsystem 100b are integrated into the same heat exchanger 260 to exchange heat with the secondary refrigerant circulating subsystem 200;

the connection route and the working process of the coolant circulation subsystem 200 are as follows: an inlet of the liquid storage tank 210 is connected with an outlet of the load 270, an outlet end of the liquid storage tank 210 is connected with an inlet end of the booster pump 230, an outlet end of the booster pump 230 is connected with an inlet of the secondary refrigerant channel 261 of the heat exchanger 260, and an outlet of the secondary refrigerant channel 261 of the heat exchanger 260 is connected with an inlet of the load 270 to form a circulation loop; when the system is used, the secondary refrigerant in the liquid storage tank 210 is conveyed to the secondary refrigerant channel 261 of the heat exchanger 260 through the booster pump 230, the cold energy of the refrigerant circulation subsystem 100 exchanges heat with the heat of the secondary refrigerant in the secondary refrigerant channel 261, the temperature of the secondary refrigerant is reduced, then the secondary refrigerant meeting the temperature requirement is guided into the load 270, the temperature of the secondary refrigerant is increased after the heat exchange of the load 270, and then the secondary refrigerant returns to the liquid storage tank 210, and the circulation is carried out in cycles so as to achieve the purpose of cooling the load 270;

the booster pumps 230 comprise a first booster pump 230a and a second booster pump 230b which are arranged in parallel and operate independently, that is, the outlet ends of the liquid storage tank 210 are 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 the outlet ends of the first booster pump 230a and the second booster pump 230b are merged into a main pipeline and then connected with the heat exchanger 260; by adopting the parallel design of the double booster pumps 230, the two booster pumps 230 can be independently controlled and independently operated.

The onboard liquid cooling system adopts the refrigerant circulation subsystem 100 formed by the compressor 110 group for refrigeration, and solves the problem that the cooling effect of the forced air cooling type refrigeration system is limited by environmental factors and is difficult to meet the requirement of large heat exchange capacity; and the adopted refrigerant circulation subsystems 100 are double sets (including a first refrigerant circulation subsystem 100a and a second refrigerant circulation subsystem 100b), each refrigerant circulation subsystem 100 operates independently to carry out cycle value, and if one refrigerant circulation subsystem 100 fails, the other refrigerant circulation subsystem can be started to immediately switch to a working state, so that the normal operation of the system is ensured, and the reliability of the equipment is improved; when the onboard equipment has larger heat dissipation capacity, the double refrigerant circulation subsystems 100 can run simultaneously, so that the refrigerating capacity is improved, the temperature control range of the liquid cooling system is expanded, the refrigerant circulation subsystems 100 can be opened and closed according to different heat dissipation requirements, and the onboard power distribution efficiency is improved;

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 exchange heat with the secondary refrigerant circulation subsystem 200, so that the weight of the system is reduced, and the space of onboard equipment is saved; the secondary refrigerant circulation subsystem 200 adopts the parallel design of the double booster pumps 230, the two booster pumps 230 can independently control and operate, the cycle value can be carried out, one booster pump 230 fails, and the other booster pump 230 can be immediately switched to the working state, so that the normal operation of the liquid cooling system is ensured, and the reliability of the equipment is improved.

It should be noted that: the throttling element 170 in this embodiment is an expansion valve, and according to the design concept, the throttling element 170 may also be other existing throttling elements 170, such as capillary tubes, including but not limited to expansion valves;

it should be noted that: the condenser 150 in this embodiment is an air-cooled condenser 150, and the high-temperature and high-pressure gas of the refrigerant flowing through the condenser 150 is cooled by an external cold airflow, and according to the above design concept, the condenser 150 may also adopt other types of condensers 150 and other cooling methods, including but not limited to this embodiment.

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

As shown in fig. 1-2, the inlet and outlet sections of the branch where the first booster pump 230a is located are respectively provided with a first valve 220a and a first check valve 240a, the inlet and outlet sections of the branch where the second booster 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 reservoir 210 is divided into two branches which are respectively connected to the inlet ends of a first valve 220a and a second valve 220b, the outlet end of the first valve 220a is connected to the inlet of a first booster pump 230a, the outlet end of the second valve 220b is connected to the inlet of a second booster pump 230b, the outlet end of the first booster pump 230a is connected to the inlet of a first check valve 240a, the outlet end of the second booster pump 230b is connected to the inlet of a second check valve 240b, and the outlet end of the first check valve 240a and the outlet end of the second check valve 240b are merged into a main pipeline and then connected to the inlet of the coolant channel 261 of the heat exchanger 260;

the inlets and the outlets of the two booster pumps 230 are respectively provided with a valve and a check valve, when the booster pumps 230 need to be overhauled or maintained, the first valve 220a or the second valve 220b can be closed, the connection between the booster pumps 230 and the system is disconnected, the fault pumps are quickly isolated from the system, the booster pumps 230 are overhauled or replaced under the condition that the secondary refrigerant circulation subsystem 200 is not drained, any one of the booster pumps 230 is disassembled, the other booster pump 230 can normally operate, the secondary refrigerant circulation subsystem 200 can normally operate, the maintainability of the equipment is improved, and the outlet ends of the booster pumps 230 are provided with check valves to prevent the secondary refrigerant from flowing back.

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

the ball valve has the characteristics of small resistance and capability of quickly closing and blocking fluid. It should be noted that, according to the design concept described above, the first valve 220a and the second valve 220b can also adopt other types of valves, including but not limited to the ball valve described in the preferred embodiment.

Preferably, a condensing pressure regulating valve 130 is disposed on an inlet pipeline or an outlet pipeline of the condenser 150; a balance branch pipe is arranged between the compressor 110 and the reservoir 160, one end of the balance branch pipe is connected with the outlet end of the compressor 110, the other end of the balance branch pipe is connected with the inlet end of the reservoir 160, and a differential pressure valve 140 is arranged on the balance branch pipe, so that the differential pressure valve 140 is connected with the condenser 150 and the condensing pressure regulating valve 130 in parallel.

As shown in the embodiment of fig. 1-2, the exhaust port (i.e., outlet port) of the compressor 110 is connected to the inlet port of the condensing pressure regulating valve 130, the outlet port of the condensing pressure regulating valve 130 is connected to the inlet port of the condenser 150, and the outlet port of the condenser 150 is connected to the inlet port of the reservoir 160; a balance branch pipe is arranged between the compressor 110 and the reservoir 160, one end of the balance branch pipe is connected with an exhaust port (i.e. outlet end) of the compressor 110, the other end of the balance branch pipe is connected with an inlet end of the reservoir 160, and a differential pressure valve 140 is arranged on the balance branch pipe, so that the differential pressure valve 140 is connected with the condenser 150 and the condensing pressure regulating valve 130 in parallel. The two refrigerant circulation subsystems 100 are provided with the above structure, that is, the first refrigerant circulation subsystem 100a is provided with the corresponding first condensing pressure regulating valve 130a, the balance branch pipe and the first differential pressure valve 140a, and the second refrigerant circulation subsystem 100b is provided with the corresponding second condensing pressure regulating valve 130b, the balance branch pipe and the second differential pressure valve 140 b.

When the refrigerant circulation subsystem 100 operates, if the condensing pressure is higher, the exhaust temperature of the compressor 110 will rise, the compression ratio is increased, the refrigerating capacity is reduced, the power consumption is increased, the higher the condensing pressure is, the larger the adverse effect is, the higher the condensing pressure is, mainly in summer, and the condensing pressure should be reduced as much as possible; when the air conditioner runs in winter, the condensing pressure may be too low under the condition of low temperature, the front-back pressure difference of the throttling element 170 (such as an expansion valve) is too small, the liquid supply power is insufficient, meanwhile, liquid is easy to gasify before entering the throttling element 170, the refrigerant circulation capacity of the throttling element 170 is affected, the liquid shortage in a heat absorption area (namely the refrigerant channel 180) is easy to cause, and the refrigerating capacity of a unit is greatly reduced; it is known that when the refrigerant circulation subsystem 100 operates, the condensing pressure is too high or too low, which may adversely affect the operation of the equipment, and therefore, by controlling the fluctuation range of the condensing pressure in the preferred embodiment, it is beneficial to further improve the economical efficiency and reliability of the operation of the equipment;

the condensing pressure is kept in a normal range by arranging a condensing pressure regulating valve 130 at the inlet of a condenser 150 and matching with a pressure difference valve 140 on a balance branch pipe for use; specifically, in the embodiment shown in fig. 1-2, the process of the condensation pressure regulating valve 130 and the differential pressure valve 140 cooperating to regulate the condensation pressure is as follows: the adjusting range of the condensing pressure adjusting valve 130 is 5-17.5 bar, the initial value is 10bar, the set value of the condensing pressure adjusting valve 130 can be adjusted within an allowable range by adjusting an adjusting nut of the condensing pressure adjusting valve, when the inlet pressure reaches the set value, the condensing pressure adjusting valve 130 is opened, the pressure value in the condenser 150 also reaches the set value at the moment, and the condenser 150 can be ensured to operate 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 in a closed state, the initial value of the pressure difference valve 140 in the balance branch pipe when being opened is 1.4bar, when the pressure difference value delta P between the front and the rear of the pressure difference valve 140 reaches the initial value, the valve sheet in the pressure difference valve 140 starts to be opened, the refrigerant from the compressor 110 is bypassed into the liquid storage 160, when the pressure difference value reaches 3bar, the pressure difference valve 140 reaches the maximum opening degree, and the condensing pressure of the unit when being started is improved because high-pressure hot gas from the compressor 110 directly enters the liquid storage 160, so that the condensing pressure of the unit can be relatively stable under the condition that the outdoor temperature is very low; when the condensing pressure of the air conditioner is increased again and the pressure difference value between the front and rear sides of the condenser 150 is lower than the initial setting value of the pressure difference valve 140, the pressure difference valve 140 is closed, so that the balance branch pipe is closed when the condensing pressure regulating valve 130 is opened, thereby maintaining the condensing pressure in a normal range and ensuring that the compressor 110 operates at the optimum condensing pressure.

Similarly, in addition to the solution of disposing the condensing pressure regulating valve 130 on the inlet pipeline of the condenser 150 as shown in the embodiment of fig. 1-2, the condensing pressure regulating valve 130 may be disposed on the outlet pipeline of the condenser 150 according to the above design concept, and the differential pressure valve 140 on the balance branch is connected in parallel with the condenser 150 and the condensing pressure regulating valve 130; based on the arrangement, the condensing pressure can be kept in a normal range, and the working principle is similar to the scheme that the condensing pressure regulating valve 130 is arranged on the inlet pipeline of the condenser 150, so that the description is not repeated;

it should be noted that the condensing pressure regulating valve 130 is an existing pressure regulating valve, which is also called a self-operated pressure regulating valve, and the pressure regulating valve is an existing energy-saving device that does not need external energy but automatically regulates pressure only by the pressure change of the regulating medium itself; the differential pressure valve 140 is also an existing valve, and according to the design concept, a person skilled in the art can select an existing pressure regulating valve and a differential pressure valve 140 with appropriate models according to requirements; in the process of adjusting the condensing pressure according to the embodiment, the specific adjusting range (5-17.5 bar) and the initial value (10bar) of the condensing pressure adjusting valve 130, the initial value (1.4bar) of the differential pressure valve 140, and the differential pressure value at the maximum opening degree (3bar) are described, these parameters are only used for illustrating the technical solution of the present invention, and are not limited thereto, and a person skilled in the art can adjust the parameters adaptively, and the adjustment does not make the essence of the corresponding technical solution depart from the scope of the technical solutions according to the embodiments of the present invention.

Preferably, a check valve 120 is disposed on the outlet pipeline of the compressor 110.

When the condensing pressure regulating valve 130 is disposed on the outlet pipeline of the condenser 150, the outlet pipeline of the compressor 110 is provided with the check valve 120, that is, the exhaust port of the compressor 110 is connected to the inlet of the check valve 120, the outlet of the check valve 120 is connected to the inlet of the condenser 150, and the refrigerant gas compressed by the compressor 110 flows through the check valve 120 and then enters the condenser 150; the two refrigerant circulation subsystems 100 are provided with a check valve 120 on an outlet pipe of the compressor 110, that is, a first check valve 120a is provided on an outlet pipe of the first compressor 110a of the first refrigerant circulation subsystem 100a, and a second check valve 120b is provided on an outlet pipe of the second compressor 110b of the second refrigerant circulation subsystem 100 b. With such an arrangement, the liquid refrigerant in the condenser 150 is prevented from flowing back to the compressor 110, causing liquid slugging at the start of the compressor 110, and damaging the compressor 110.

When the condensing pressure adjusting valve 130 is disposed on the inlet line of the condenser 150 and the condensing pressure adjusting valve 130 is disposed in front of the inlet of the condenser 150, the condensing pressure adjusting valve 130 may also function as a check valve, and thus, the check valve 120 may be omitted at this time.

Preferably, an electric heater 211 is disposed in the liquid storage tank 210, and the electric heater 211 is used for heating the coolant in the liquid storage tank 210.

The electric heater 211 is installed in the liquid storage tank 210, when the ambient temperature is low, the temperature of the secondary refrigerant is also reduced, the kinematic viscosity of the secondary refrigerant is increased, the flow resistance is correspondingly increased, the starting resistance of the booster pump 230 is increased, the electric heater 211 can be opened at the moment, the secondary refrigerant is preheated, the starting resistance of the booster pump 230 can be greatly reduced, the normal opening of the booster pump 230 is ensured, the long-time blocking of the booster pump 230 is prevented, and the service life of the booster pump 230 is prolonged. And can provide stable heat flow for the onboard electronic equipment or the onboard storage battery under the condition of low temperature, so that the onboard electronic equipment or the onboard storage battery can be started and operated at proper temperature.

When the electric heater 211 is in an operating state, the first refrigerant-circulating sub-system 100a and the second refrigerant-circulating sub-system 100b of the refrigerant-circulating sub-system 100 are in a standby state; when the load 270 is small and lower than the cooling capacity of the refrigerant-circulation sub-system 100 of the single compressor 110, the first refrigerant-circulation sub-system 100a and the second refrigerant-circulation sub-system 100b may perform the periodic duty; when the load 270 is higher than the refrigerating capacity of the refrigerant circulation subsystem 100 of the single compressor 110, the first refrigerant circulation subsystem 100a and the second refrigerant circulation subsystem 100b are simultaneously started to work as the load 270 to provide refrigerating capacity, and the electric heater 211 in the liquid storage tank 210, the first refrigerant circulation subsystem 100a and the second refrigerant circulation subsystem 100b are matched to operate, so that the utilization efficiency of onboard power distribution is improved, the reliability of the onboard liquid cooling system is improved, and the service life of the unit is prolonged.

Preferably, an expansion tank 212 is arranged at the top of the liquid storage tank 210; a pressure relief pipeline is arranged on the liquid storage tank 210, a pressure relief valve 213 is arranged on the pressure relief pipeline, and the outlet end of the pressure relief pipeline is connected with a liquid collector 214.

The liquid storage tank 210 is provided with an expansion tank 212 which can perform constant pressure on the system and maintain the pressure balance inside the system. A pressure relief pipeline is arranged on the liquid storage tank 210, a pressure relief valve 213 is arranged on the pressure relief pipeline, and the pressure relief pipeline can be automatically opened when the system pressure reaches the safe working pressure, is used for discharging air or liquid in the secondary refrigerant circulation subsystem 200, reducing the working pressure and ensuring the safe operation of the system, and the outlet end of the pressure relief pipeline is connected with a liquid collector 214, so that the secondary refrigerant can be prevented from flowing into the cabin; and the liquid trap 214 can be quickly disassembled, and the waste liquid in the liquid trap 214 can be cleaned when the system is regularly maintained.

Preferably, a flow meter 271, a liquid supply pressure sensor 272 and a liquid supply temperature sensor 273 are arranged on an inlet pipeline of the load 270.

A flow meter 271, a liquid supply pressure sensor 272 and a liquid supply temperature sensor 273 are arranged on an inlet pipeline of the load 270, namely, the flow meter 271, the liquid supply pressure sensor 272 and the liquid supply temperature sensor 273 are arranged on a connecting pipeline between the heat exchanger 260 and the load 270, so that the liquid supply state of the secondary refrigerant circulation subsystem 200 can be monitored in real time, and the onboard liquid cooling system can be controlled to judge according to acquired data and adjust the working modes of the refrigerant circulation subsystem 100 and the booster pump 230.

Preferably, a branch where the first booster pump 230a is located and a branch where the second booster pump 230b is located are connected to the heat exchanger 260 after being merged into the main pipeline, and a filter 250 is disposed on the main pipeline connecting the heat exchanger 260 and the booster pumps 230. The filter 250 provides a filtering and purifying function for the coolant passing therethrough.

Preferably, the filter 250 is a spin-on filter 250.

The filter 250 is a rotary self-sealing filter 250, so that the filter element can be replaced on line, and the maintainability of the system is improved;

preferably, a pressure sensor is arranged at the inlet of the filter 250, and the pressure sensor and the liquid supply pressure sensor 272 can be combined to perform filth blockage judgment and report a filth blockage prompt so that an operator can perform maintenance conveniently.

Preferably, the liquid storage tank 210 is provided with a liquid discharge port 215 for discharging the coolant in the liquid storage tank 210; an inlet 251 and a filter 250 are sequentially provided along a path through which the coolant flows on a main line connecting the heat exchanger 260 and the booster pump 230.

The liquid outlet 215 of the liquid storage tank 210 is used for discharging the coolant in the liquid storage tank 210, a liquid inlet 251 and a filter 250 are sequentially arranged on a main pipeline connecting the heat exchanger 260 and the booster pump 230 along a coolant flowing path, the liquid inlet 251 is used for supplementing the coolant, and the newly supplemented coolant firstly passes through the filter 250 for filtration and purification and then enters the loop of the coolant circulation subsystem 200.

Preferably, the condenser 150 (i.e., the first condenser 150a and the second condenser 150b) is a microchannel heat exchanger 260 or a wire-tube heat exchanger 260. Preferably, the heat exchanger 260 is a plate heat exchanger 260 or a wire tube heat exchanger 260. Preferably, the flow meter 271 is a turbine flow meter 271 or an ultrasonic flow meter 271. Preferably, the compressors 110 (i.e., the first compressor 110a and the second compressor 110b) are scroll compressors 110. It should be noted that the condenser 150, the heat exchanger 260, the flow meter 271 and the compressor 110 are existing devices, and according to the design concept, a person skilled in the art can adaptively select the existing type or model of the condenser 150, the heat exchanger 260, the flow meter 271 and the compressor 110 according to the requirement, including but not limited to the condenser 150, the heat exchanger 260, the flow meter 271 and the compressor 110.

In summary, compared with the prior art, the airborne liquid cooling system provided by the utility model has the following technical effects:

(1) the utility model adopts the refrigerant circulation subsystem 100 formed by the compressor 110 to refrigerate, solves the problem that the cooling effect of the forced air-cooled refrigeration system is limited by environmental factors and is difficult to meet the requirement of large heat exchange amount; and adopt the refrigerant circulation subsystem 100 of double sets, every refrigerant circulation subsystem 100 operates independently, carry on the cycle value, one set of refrigerant circulation subsystem 100 trouble another set can start and switch over to the working condition immediately, guarantee the normal operation of the system, has improved the reliability of the apparatus; when the heat dissipation capacity of the onboard equipment is large, the double sets of refrigerant circulation subsystems 100 can run simultaneously, so that the refrigerating capacity is improved, the temperature control range of the liquid cooling system is expanded, the opening of the refrigerant circulation subsystems 100 can be combined according to different heat dissipation requirements, and the onboard power distribution efficiency is improved;

(2) in the utility model, the refrigerant channels 180 of the first refrigerant circulating subsystem 100a and the second refrigerant circulating subsystem 100b are integrated into the same heat exchanger 260 to exchange heat with the secondary refrigerant circulating subsystem 200, thereby reducing the weight of the system and saving the space of airborne equipment;

(3) the secondary refrigerant circulation subsystem 200 adopts the parallel design of the double booster pumps 230, the two booster pumps 230 can independently control and operate, the cycle value can be carried out, one booster pump 230 fails, and the other booster pump 230 can be immediately switched to a working state, so that the normal operation of a liquid cooling system is ensured, and the reliability of equipment is improved.

(4) In the utility model, the inlets and the outlets of the two booster pumps 230 are respectively provided with the valve and the check valve, when the booster pumps 230 need to be overhauled or maintained, the first valve 220a or the second valve 220b can be closed, the connection between the booster pumps 230 and the system is disconnected, the fault pump is quickly isolated from the system, the booster pumps 230 are overhauled or replaced under the condition that the secondary refrigerant circulation subsystem 200 is not drained, any booster pump 230 is disassembled, the secondary refrigerant circulation subsystem 200 can normally work, and the maintainability of the equipment is improved.

(5) According to the utility model, the electric heater 211 is arranged in the liquid storage tank 210, and when the temperature is low, the electric heater 211 can preheat the secondary refrigerant to raise the temperature, so that the normal opening of the booster pump 230 is ensured, and the service life of the equipment is prolonged; the onboard electronic equipment can be preheated under the condition of low temperature, so that the onboard electronic equipment can be started or operated at a proper temperature.

(6) A pressure relief valve 213 is arranged on a pressure relief pipeline on a liquid storage tank 210 and is used for discharging air in a secondary refrigerant circulation subsystem 200; the outlet end of the pressure relief line is connected to the accumulator 214 to prevent coolant from flowing into the cabin interior, and the accumulator 214 can be quickly removed to allow the accumulator 214 to be cleaned during periodic system maintenance.

(7) According to the utility model, the flow meter 271, the liquid supply temperature sensor 273 and the liquid supply pressure sensor 272 are arranged on the inlet pipeline of the load 270, so that the flow and the temperature can be accurately controlled according to the acquired data, the working efficiency is improved, and the energy consumption is reduced.

(8) The filter 250 on the secondary refrigerant circulation subsystem 200 is a rotary self-sealing filter 250, the filter element can be replaced in the liquid-containing state of the system, and pressure sensors are arranged on the inlet and outlet pipelines of the filter 250, so that the filth blockage alarm can be performed, and the maintainability of the equipment is improved.

The machine-mounted liquid cooling system provided by the utility model adopts the refrigerant circulation subsystem 100 (comprising the first refrigerant circulation subsystem 100a and the second refrigerant circulation subsystem 100b) for refrigeration, and the liquid supply mode of secondary refrigerant adopts the double booster pumps 230 to be connected in parallel and operate independently. Compared with the existing airborne air cooling mode, the airborne liquid cooling system has the advantages that the time for achieving the refrigeration target is faster, the refrigerating capacity is larger, and in the face of airborne electronic products with different heat dissipation requirements, the airborne liquid cooling system has more working combination modes and stronger expansibility of the refrigerating capacity, and is smaller in volume and lighter in weight compared with the existing airborne air cooling system under the condition of achieving the same refrigerating capacity target; each group of booster pumps 230 and the refrigerant circulation subsystem 100 can work independently, the operation of the liquid cooling system is not affected by the fault of a single booster pump 230, the working continuity of airborne electronic equipment is guaranteed, the flight safety is guaranteed, sufficient time is reserved for maintenance service provided by unit support personnel, and the service life and the reliability of the system are improved.

In addition, it will be appreciated by those skilled in the art that, although there may be many problems with the prior art, each embodiment or aspect of the present invention may be improved only in one or several respects, without necessarily simultaneously solving all the technical problems listed in the prior art or in the background. It will be understood by those skilled in the art that nothing in a claim should be taken as a limitation on that claim.

Although terms such as refrigerant circulation subsystem, coolant circulation subsystem, load, tank, booster pump, etc. are used more often herein, the possibility of using other terms is not excluded. These terms are used merely to more conveniently describe and explain the nature of the present invention; they are to be construed as being without limitation to any additional limitations that may be imposed by the spirit of the present invention; the terms "first," "second," and the like in the description and in the claims, and in the drawings, if any, are used for distinguishing between similar elements and not necessarily for describing a particular sequential or chronological order.

Finally, it should be noted that: the above embodiments are only used to illustrate the technical solution of the present invention, and not to limit the same; while the utility model has been described in detail and with reference to the foregoing embodiments, it will be understood by those skilled in the art that: the technical solutions described in the foregoing embodiments may still be modified, or some or all of the technical features may be equivalently replaced; and the modifications or the substitutions do not make the essence of the corresponding technical solutions depart from the scope of the technical solutions of the embodiments of the present invention.

Claims (10)

1. An airborne liquid cooling system, comprising:

a refrigerant circulation subsystem including a first refrigerant circulation subsystem and a second refrigerant circulation subsystem of independent refrigeration cycles;

the secondary refrigerant circulation subsystem comprises a liquid storage tank, a booster pump and a heat exchanger which are sequentially connected with the inlet end and the outlet end of the load to form a secondary refrigerant circulation loop;

each refrigerant circulation subsystem comprises a compressor, a condenser, a liquid storage device and a throttling element which are sequentially connected to form a loop; the outlet of the throttling element is connected with the inlet of a refrigerant channel of the heat exchanger, and the outlet of the refrigerant channel is connected with the inlet of the compressor, so that the cold energy generated by the refrigerant circulation subsystem and the heat of the secondary refrigerant circulation subsystem exchange heat at the heat exchanger; the booster pump comprises a first booster pump and a second booster pump which are arranged in parallel.

2. The onboard liquid cooling system of claim 1, wherein: the inlet section and the 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 the outlet section of the branch where the second booster pump is located are respectively provided with a second valve and a second check valve.

3. The onboard liquid cooling system of claim 1, wherein: a condensing pressure regulating valve is arranged on an inlet pipeline or an outlet pipeline of the condenser;

a balance branch pipe is arranged between the compressor and the liquid storage device, one end of the balance branch pipe is connected with the outlet end of the compressor, the other end of the balance branch pipe is connected with the inlet end of the liquid storage device, and a pressure difference valve is arranged on the balance branch pipe so as to be connected with the condenser and the condensation pressure regulating valve in parallel.

4. The onboard liquid cooling system of claim 1, wherein: and a one-way valve is arranged on an outlet pipeline of the compressor.

5. The onboard liquid cooling system of claim 1, wherein: an electric heater is arranged in the liquid storage tank and used for heating secondary refrigerant in the liquid storage tank.

6. The onboard liquid cooling system of claim 1, wherein: an expansion tank is arranged at 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 with the liquid collector.

7. The onboard liquid cooling system of claim 1, wherein: and a flow meter, a liquid supply pressure sensor and a liquid supply temperature sensor are arranged on the inlet pipeline of the load.

8. The onboard liquid cooling system of claim 1, wherein: the branch where the first booster pump is located and the branch where the second booster pump is located are connected with the heat exchanger after being converged into the main pipeline, and a filter is arranged on the main pipeline connecting the heat exchanger and the booster pumps.

9. The airborne liquid cooling system of claim 8, wherein: the filter is a rotary self-sealing filter.

10. The airborne liquid cooling system of claim 8, wherein: the liquid storage tank is provided with a liquid discharge port for discharging secondary refrigerant in the liquid storage tank; and a main pipeline connected between the heat exchanger and the booster pump is sequentially provided with a liquid inlet and a filter along a secondary refrigerant flowing path.

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