CN117803477B - Electro-hydraulic thermal complementary electromechanical system based on fuel oil - Google Patents

Electro-hydraulic thermal complementary electromechanical system based on fuel oil Download PDF

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Publication number
CN117803477B
CN117803477B CN202311776380.3A CN202311776380A CN117803477B CN 117803477 B CN117803477 B CN 117803477B CN 202311776380 A CN202311776380 A CN 202311776380A CN 117803477 B CN117803477 B CN 117803477B
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Prior art keywords
valve
hydraulic
heat
heat exchanger
energy
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CN117803477A (en
Inventor
程定斌
谭靖麒
陈丽君
倪诗旸
常诚
张啸
王小平
潘俊
高赞军
刘成
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AVIC Jincheng Nanjing Engineering Institute of Aircraft Systems
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AVIC Jincheng Nanjing Engineering Institute of Aircraft Systems
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C7/00—Features, components parts, details or accessories, not provided for in, or of interest apart form groups F02C1/00 - F02C6/00; Air intakes for jet-propulsion plants
    • F02C7/22—Fuel supply systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C7/00—Features, components parts, details or accessories, not provided for in, or of interest apart form groups F02C1/00 - F02C6/00; Air intakes for jet-propulsion plants
    • F02C7/22—Fuel supply systems
    • F02C7/224—Heating fuel before feeding to the burner
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/26—Reciprocating-piston liquid engines adapted for special use or combined with apparatus driven thereby
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03G—SPRING, WEIGHT, INERTIA OR LIKE MOTORS; MECHANICAL-POWER PRODUCING DEVICES OR MECHANISMS, NOT OTHERWISE PROVIDED FOR OR USING ENERGY SOURCES NOT OTHERWISE PROVIDED FOR
    • F03G7/00—Mechanical-power-producing mechanisms, not otherwise provided for or using energy sources not otherwise provided for
    • F03G7/04—Mechanical-power-producing mechanisms, not otherwise provided for or using energy sources not otherwise provided for using pressure differences or thermal differences occurring in nature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B21/00—Machines, plants or systems, using electric or magnetic effects
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/40—Fluid line arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
    • F28D20/02—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00 using latent heat

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)

Abstract

The invention relates to an electro-hydraulic thermal complementary electromechanical system based on fuel oil, which comprises: the system comprises a fuel tank, a ram air door, an electronic system, a fuel oil heat absorption subsystem, an electric refrigeration subsystem, a hydraulic refrigeration subsystem, a thermoelectric generation subsystem, a thermoelectric liquid supply subsystem, a hydraulic generation subsystem, a first liquid cooling circulation subsystem, a second liquid cooling circulation subsystem and an evaporation circulation subsystem; the fuel tank stores fuel; the electronic supply system comprises a fuel oil power generation device, an energy storage device and a bus bar; the electric refrigeration subsystem consumes electric energy to be converted into refrigerating capacity, the hydraulic refrigeration subsystem consumes hydraulic energy to be converted into refrigerating capacity, the temperature difference power generation subsystem recovers waste heat to be converted into electric energy, the temperature difference liquid supply subsystem recovers waste heat to be converted into hydraulic energy, and the hydraulic power generation subsystem consumes hydraulic energy to be converted into electric energy; the problem that the energy on the machine is directly wasted is solved.

Description

Electro-hydraulic thermal complementary electromechanical system based on fuel oil
Technical Field
The invention relates to the technical field of aviation electromechanics, in particular to an electro-hydraulic thermal complementary electromechanical system based on fuel oil.
Background
The onboard high-power equipment brings greatly increased electric energy, hydraulic energy and refrigerating capacity requirements for the aircraft platform. The implementation of the high-power equipment system requires comprehensive consideration of constraints such as space, weight, power supply, liquid supply, heat dissipation and the like which can be provided by the aircraft platform. In order to ensure the stable operation of the high-power equipment and reduce the influence of the high-power equipment on an aircraft platform, the volume, the weight, the electric energy/hydraulic energy supply, the thermal management and the like of the high-power equipment power supply, liquid supply and the thermal management system are required to be optimally designed. When the onboard high-power equipment operates, the power supply, the liquid supply and the heating power are all time-varying according to specific working requirements. If the design mode of the power supply, liquid supply and thermal management system of the high-power equipment is the same as the conventional mode, the maximum power supply must be not less than the peak power requirement of the high-power equipment, the maximum liquid supply must be not less than the peak hydraulic power requirement of the high-power equipment, and the maximum refrigerating capacity must be not less than the peak refrigerating capacity requirement of the high-power equipment, so that the volume and weight of the power supply system, the liquid supply system and the thermal management system are larger. Meanwhile, in most of the time in the load pulsation period, the electric energy, hydraulic energy and refrigerating capacity demands are far lower than design peaks, the operation efficiency of a power supply system, a liquid supply system and a thermal management system is greatly reduced, and the capacity waste is caused. However, the existing onboard high-power equipment power supply, liquid supply and thermal management systems are mainly designed in a discrete mode, an independent energy system is adopted, energy flows of all subsystems are independent, idle energy sources of all subsystems cannot be mutually utilized, and recyclable energy in the power supply system, the liquid supply system and the thermal management system is directly dissipated.
In addition, the power supply amount of the power supply system, the power supply amount of the liquid supply system and the refrigerating capacity of the thermal management system are fixed values in design, and a plurality of sets of architectures are required to be designed to meet the fluctuating power supply, liquid supply and heat dissipation requirements in a certain range. In operation, the total amount of fuel stored in the fuel tank is fixed, and the total carrying capacity of the fuel needs to meet both the supply and liquid supply demands as an energy source and the refrigeration demand as a heat sink. When the power supply and liquid supply demands are too large, excessive fuel oil is carried to cause heat sink redundancy, and when the refrigerating capacity demands are too large, energy source redundancy is caused.
Disclosure of Invention
The invention aims to overcome the defects of the technology, and provides an electro-hydraulic thermal complementary electromechanical system based on fuel oil, which aims to solve the problem of low operation efficiency of power supply, liquid supply and thermal management.
In a first aspect, the present invention provides an electro-mechanical system for electro-hydraulic thermal complementation based on fuel, comprising: the system comprises a fuel tank, a ram air door, an electronic system, a fuel oil heat absorption subsystem, an electric refrigeration subsystem, a hydraulic refrigeration subsystem, a thermoelectric generation subsystem, a thermoelectric liquid supply subsystem, a hydraulic generation subsystem, a first liquid cooling circulation subsystem, a second liquid cooling circulation subsystem and an evaporation circulation subsystem; the fuel tank stores fuel; the electronic supply system comprises a fuel oil power generation device, an energy storage device and a bus bar; the electric refrigeration subsystem consumes electric energy to be converted into refrigerating capacity, the hydraulic refrigeration subsystem consumes hydraulic energy to be converted into refrigerating capacity, the temperature difference power generation subsystem recovers waste heat to be converted into electric energy, the temperature difference liquid supply subsystem recovers waste heat to be converted into hydraulic energy, and the hydraulic power generation subsystem consumes hydraulic energy to be converted into electric energy; the fuel in the fuel tank flows through the condenser to absorb heat of the condenser, then flows through the hydraulic oil heat exchanger to absorb heat of the hydraulic oil heat exchanger, and is used as a heat sink for heat management of the electrohydraulic heat complementary electromechanical system; the fuel oil with raised temperature after heat absorption is conveyed to an auxiliary power device to be mixed with air for combustion, high-temperature gas is generated to impact a turbine to rotate, the turbine drives a gear box, the gear box drives a generator to rotate to generate electric energy, high-power equipment on the aircraft is powered, the high-power equipment is used as an energy source for power supply of an electrohydraulic thermal complementary electromechanical system,
When the mechanical driving hydraulic pump is adopted for liquid supply, the gear box drives the mechanical driving hydraulic pump to work to generate hydraulic energy for supplying liquid for the high-power equipment executing mechanism, and the hydraulic energy is used as an energy source for supplying liquid for the electrohydraulic thermal complementary electromechanical system;
When the electric pump is used for supplying liquid, the electric energy generated by rotation of the generator simultaneously supplies power for the electric pump, the electric pump works to generate hydraulic energy for supplying liquid for the executing mechanism of the high-power equipment, and the hydraulic energy is used as an energy source for supplying liquid for the electro-hydraulic thermal complementary electromechanical system.
In some embodiments, the first liquid cooled circulation subsystem comprises: the device comprises a high heat flux cooling device, a first liquid pump and a first liquid storage tank; the heat is generated in the working process of the high-power equipment, the heat is transferred to the high-heat-flux-density cooling device, the first refrigerating medium in the first liquid storage tank is conveyed to the high-heat-flux-density cooling device through the first liquid pump, the temperature of the first refrigerating medium rises after absorbing the heat generated by the high-power equipment, the temperature of the first refrigerating medium is reduced after the first refrigerating medium is taken away by a first heat exchanger, the residual heat is taken away by the first refrigerating medium through a phase-change heat storage heat exchanger, the first refrigerating medium returns to the first liquid storage tank, and the first liquid cooling circulation subsystem completes a first liquid cooling circulation loop.
In some embodiments, the second liquid cooling subsystem comprises: the phase change heat storage heat exchanger, the second liquid pump and the second liquid storage tank; the second refrigerating medium in the second liquid storage tank is conveyed to the phase-change heat storage heat exchanger through the second liquid pump, the temperature of the second refrigerating medium is increased after absorbing heat stored in the phase-change heat storage heat exchanger, the temperature of the second refrigerating medium is reduced after being taken away by a third heat exchanger, the second refrigerating medium is taken away by the residual heat through the evaporator and returns to the second liquid storage tank, and the second liquid cooling circulation subsystem completes a second liquid cooling circulation loop.
In some embodiments, the evaporation cycle subsystem comprises: evaporator, throttle valve, condenser and compressor; the liquid refrigerant in the evaporator absorbs the heat transferred to the evaporator by the second liquid cooling circulation subsystem and evaporates to become gaseous refrigerant, the gaseous refrigerant is compressed to be high-pressure gas after entering the compressor, the high-pressure gaseous refrigerant enters the condenser to emit heat to become liquid refrigerant, the liquid refrigerant enters the throttle valve and throttles and expands to be low-pressure liquid, and the evaporation circulation subsystem completes the evaporation circulation loop.
In some embodiments, the electric refrigeration subsystem comprises an electric refrigeration device, and the hydraulic refrigeration subsystem comprises a hydraulic refrigeration device; the electric refrigerating device consumes electric energy and transfers heat from the first heat exchanger with lower temperature to the second heat exchanger with higher temperature; the hydraulic refrigeration device consumes hydraulic energy and transfers heat from a first heat exchanger having a lower temperature to a second heat exchanger having a higher temperature.
In some embodiments, the thermoelectric generation subsystem comprises a thermoelectric generation device, and the thermoelectric liquid supply subsystem comprises a thermoelectric liquid supply device; the thermoelectric generation device converts heat energy into electric energy through thermoelectric generation by utilizing the temperature difference between the third heat exchanger and the fourth heat exchanger, and transmits the electric energy to the bus bar inlet; the temperature difference liquid supply device converts heat energy into hydraulic energy through temperature difference liquid supply by utilizing the temperature difference between the third heat exchanger and the fourth heat exchanger, and the hydraulic energy is conveyed to the high-power equipment executing mechanism.
In some embodiments, the hydraulic power generation subsystem includes an accumulator, a hydraulic motor, and a generator. The accumulator stores high-pressure oil, the high-pressure oil drives the hydraulic motor to rotate to generate mechanical energy, the hydraulic motor drives the generator to rotate to generate electricity, the mechanical energy is converted into electric energy, and the electric energy is transmitted to the bus bar inlet.
In some embodiments, the electrohydraulic thermal complementary system using fuel oil as an energy source and a heat sink comprises twenty three valves, a first valve is arranged between the high heat flux density cooling device and the phase change heat storage heat exchanger, a second valve is arranged between the high heat flux density cooling device and the first heat exchanger, a third valve is arranged between the phase change heat storage heat exchanger and the evaporator, a fourth valve is arranged between the phase change heat storage heat exchanger and the third heat exchanger, a fifth valve is arranged between the throttle valve and the fourth heat exchanger, a sixth valve is arranged between the throttle valve and the evaporator, a seventh valve is arranged between the fuel tank and the condenser, an eighth valve is arranged between the fuel tank and the auxiliary power device, a ninth valve is arranged between the first heat exchanger and the electric refrigeration device, a tenth valve is arranged between the electric refrigeration device and the second heat exchanger, an eleventh valve is arranged between the first heat exchanger and the hydraulic refrigeration device, the twelfth valve is arranged between the hydraulic refrigerating device and the second heat exchanger, the thirteenth valve is arranged between the third heat exchanger and the thermoelectric generation device, the fourteenth valve is arranged between the thermoelectric generation device and the fourth heat exchanger, the fifteenth valve is arranged between the third heat exchanger and the thermoelectric liquid supply device, the sixteenth valve is arranged between the thermoelectric liquid supply device and the fourth heat exchanger, the seventeenth valve is arranged between the condenser when the ram air is used as a heat sink and the hydraulic oil heat exchanger, the eighteenth valve is arranged between the condenser when the ram air is used as a heat sink and the second heat exchanger, the nineteenth valve is arranged between the condenser when the fuel oil is used as a heat sink and the second heat exchanger, the twentieth valve is arranged between the hydraulic refrigerating device and the hydraulic pump, the twelfth valve is arranged between the thermoelectric liquid supply device and the oil filter, the twenty second valve is arranged between the pressure accumulator and the hydraulic motor, and the twenty third valve is arranged between the hydraulic heat exchanger and the external environment.
In some embodiments, the bus bar comprises four inlets and five outlets, the first inlet is connected to the first generator, the second inlet is connected to the thermoelectric generation device, the third inlet is connected to the second generator, the fourth inlet is connected to the energy storage device, the first outlet is connected to the high power device, the second outlet is connected to the first liquid pump, the third outlet is connected to the second liquid pump, the fourth outlet is connected to the electric refrigeration device, and the fifth outlet is connected to the compressor.
The technical scheme provided by the invention has the following beneficial effects:
The invention increases the fuel oil heat absorption scheme to realize that the heat of the heat management system is utilized to improve the efficiency of the power supply system and the liquid supply system; an electric refrigeration scheme is added to realize the consumption of electric energy to supplement refrigeration capacity; the hydraulic refrigeration scheme is added to realize the consumption of hydraulic energy to supplement the refrigeration capacity; the thermoelectric generation scheme is added to realize waste heat recycling and supplementing electric energy; the temperature difference liquid supply scheme is added to realize waste heat recycling and supplementing hydraulic energy; the hydraulic power generation scheme is added to realize the consumption of hydraulic energy to supplement electric energy, and the power supply system, the liquid supply system and the thermal management system are integrated by adopting an integrated design of an energy source and a heat sink, so that the problems of limited carrying space, limited power supply, limited liquid supply and insufficient heat sink of high-power equipment are solved.
The invention aims at the fluctuating power supply, liquid supply and heat dissipation requirements in a certain range, and realizes the mutual conversion and utilization of electric energy, hydraulic energy and heat energy by adopting different steps according to a plurality of discrimination standards such as whether the power supply quantity of a power supply system meets the total requirements, whether the refrigerating capacity of a heat management system meets the requirements, whether the complementary generating capacity of a fuel oil heat absorption scheme meets the total requirement difference, whether the complementary hydraulic energy of a temperature difference liquid supply scheme meets the total requirement difference, whether the complementary refrigerating capacity of a temperature difference generating device meets the total requirement difference, whether the electric energy consumed by an electric refrigerating device is less than the redundancy quantity of electric energy of a system, whether the hydraulic energy consumed by a hydraulic refrigerating device is less than the redundancy quantity of hydraulic energy of the system, whether the hydraulic energy consumed by the hydraulic generating device is less than the redundancy quantity of hydraulic energy of the system, and the like, so as to avoid redesign the system architecture, and flexibly match with equipment with different power in a certain range.
According to the invention, the opening degrees of the regulating valve and the ram air door can be used for regulating the range of the fuel oil heat absorption capacity, so that the power generation lifting capacity of a fuel oil heat absorption scheme can be flexibly regulated and controlled; the flow entering the heat exchanger can be regulated, the supplementary refrigerating capacity of the electric refrigerating device and the electric energy required to be consumed can be flexibly regulated, the supplementary refrigerating capacity and the supplementary electric energy of the thermoelectric power generation device can be flexibly regulated, the supplementary refrigerating capacity of the hydraulic refrigerating device and the hydraulic energy required to be consumed can be flexibly regulated, the supplementary refrigerating capacity and the supplementary hydraulic energy of the thermoelectric liquid supply device can be flexibly regulated, and the supplementary electric energy of the hydraulic motor driven generator can be flexibly regulated; the integrated control system has the advantages that the integrated control form of electricity, liquid and heat is added under the same framework, the autonomous adaptive control capability is improved, and the integrated energy efficiency optimization is realized, so that the requirement of the airborne high-power equipment for accurate control according to the load period is met.
It is to be understood that both the foregoing general description and the following detailed description are exemplary and explanatory only and are not restrictive of the invention as claimed.
Drawings
The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate embodiments consistent with the disclosure and together with the description, serve to explain the principles of the disclosure.
FIG. 1 shows a schematic diagram of an electro-mechanical system for performing electro-thermal complementation based on fuel oil in accordance with the present invention;
fig. 2 shows a schematic diagram of another electromechanical system for electric heat complementation based on fuel oil according to the invention.
Detailed Description
The disclosure will now be discussed with reference to several exemplary embodiments. It should be understood that these embodiments are discussed only to enable those of ordinary skill in the art to better understand and thus practice the present disclosure, and are not meant to imply any limitation on the scope of the present disclosure.
As used herein, the term "comprising" and variants thereof are to be interpreted as meaning "including but not limited to" open-ended terms. The term "based on" is to be interpreted as "based at least in part on". The terms "one embodiment" and "an embodiment" are to be interpreted as "at least one embodiment. The term "another embodiment" is to be interpreted as "at least one other embodiment".
The fuel oil is used as the energy source of the power supply system and the liquid supply system and the heat sink of the thermal management system. The fuel in the fuel tank flows through a condenser of the thermal management system to absorb heat of the thermal management system, then flows through a hydraulic oil heat exchanger of the liquid supply system to absorb heat of the liquid supply system, the fuel with raised temperature after heat absorption is conveyed to an auxiliary power device to be mixed with air for combustion, high-temperature gas is generated to impact a turbine to rotate, the turbine drives a gear box, the gear box drives a generator to rotate to generate electric energy, and the electric energy is used for supplying power for high-power equipment on the aircraft and is used as an energy source of the power supply system. When the mechanical driving hydraulic pump is adopted for liquid supply, the gear box drives the mechanical driving hydraulic pump to work to generate hydraulic energy, so that liquid is supplied to the high-power equipment executing mechanism, and the hydraulic energy is used as an energy source of a liquid supply system; when the electric pump is used for supplying liquid, the electric energy generated by rotation of the generator simultaneously supplies power for the electric pump, and the electric pump works to generate hydraulic energy for supplying liquid for the executing mechanism of the high-power equipment and is used as an energy source of the liquid supply system. The integrated design of energy (electric energy and hydraulic energy) sources and heat sinks is adopted to integrate a power supply system, a liquid supply system and a thermal management system, so that the problems of limited carrying space, limited power supply, limited liquid supply and insufficient heat sinks of high-power equipment are solved.
However, the electric energy, the hydraulic energy and the heat energy generated by the system in the existing design are not converted and utilized, when the refrigerating capacity in the system is insufficient, the power supply system cannot consume the electric energy to supplement the refrigerating capacity, and the liquid supply system cannot consume the hydraulic energy to supplement the refrigerating capacity; when the electric energy in the system is insufficient, the heat management system cannot recycle waste heat to supplement the electric energy, and the liquid supply system cannot consume hydraulic energy to supplement the electric energy; when the hydraulic energy in the system is insufficient, the thermal management system cannot recycle the waste heat to supplement the hydraulic energy.
The embodiment of the invention discloses an electro-hydraulic thermal complementary electromechanical system based on fuel oil, which is shown in figure 1 and comprises the following components: the system comprises a fuel tank, a ram air door, an electronic system, a fuel oil heat absorption subsystem, an electric refrigeration subsystem, a hydraulic refrigeration subsystem, a thermoelectric generation subsystem, a thermoelectric liquid supply subsystem, a hydraulic generation subsystem, a first liquid cooling circulation subsystem, a second liquid cooling circulation subsystem and an evaporation circulation subsystem; the fuel tank stores fuel; the electronic supply system comprises a fuel oil power generation device, an energy storage device and a bus bar; the electric refrigeration subsystem consumes electric energy to be converted into refrigerating capacity, the hydraulic refrigeration subsystem consumes hydraulic energy to be converted into refrigerating capacity, the temperature difference power generation subsystem recovers waste heat to be converted into electric energy, the temperature difference liquid supply subsystem recovers waste heat to be converted into hydraulic energy, and the hydraulic power generation subsystem consumes hydraulic energy to be converted into electric energy; the fuel in the fuel tank flows through the condenser to absorb heat of the condenser, then flows through the hydraulic oil heat exchanger to absorb heat of the hydraulic oil heat exchanger, and is used as a heat sink for heat management of the electrohydraulic heat complementary electromechanical system; the fuel oil with raised temperature after heat absorption is conveyed to an auxiliary power device to be mixed with air for combustion, high-temperature gas is generated to impact a turbine to rotate, the turbine drives a gear box, the gear box drives a generator to rotate to generate electric energy, high-power equipment on the aircraft is powered by the electric generator to serve as an energy source for supplying power to an electrohydraulic thermal complementary electromechanical system, and when a mechanical driving hydraulic pump is adopted for supplying liquid, the gear box drives the mechanical driving hydraulic pump to work to generate hydraulic energy for supplying liquid to an executing mechanism of the high-power equipment to serve as the energy source for supplying liquid to the electrohydraulic thermal complementary electromechanical system; when the electric pump is used for supplying liquid, the electric energy generated by rotation of the generator simultaneously supplies power for the electric pump, the electric pump works to generate hydraulic energy for supplying liquid for the executing mechanism of the high-power equipment, and the hydraulic energy is used as an energy source for supplying liquid for the electro-hydraulic thermal complementary electromechanical system.
In some embodiments, the first liquid cooled circulation subsystem comprises: the device comprises a high heat flux cooling device, a first liquid pump and a first liquid storage tank; the heat is generated in the working process of the high-power equipment, the heat is transferred to the high-heat-flux-density cooling device, the first refrigerating medium in the first liquid storage tank is conveyed to the high-heat-flux-density cooling device through the first liquid pump, the temperature of the first refrigerating medium rises after absorbing the heat generated by the high-power equipment, the temperature of the first refrigerating medium is reduced after the first refrigerating medium is taken away by a first heat exchanger, the residual heat is taken away by the first refrigerating medium through a phase-change heat storage heat exchanger, the first refrigerating medium returns to the first liquid storage tank, and the first liquid cooling circulation subsystem completes a first liquid cooling circulation loop.
In some embodiments, the second liquid cooling subsystem comprises: the phase change heat storage heat exchanger, the second liquid pump and the second liquid storage tank; the second refrigerating medium in the second liquid storage tank is conveyed to the phase-change heat storage heat exchanger through the second liquid pump, the temperature of the second refrigerating medium is increased after absorbing heat stored in the phase-change heat storage heat exchanger, the temperature of the second refrigerating medium is reduced after being taken away by a third heat exchanger, the second refrigerating medium is taken away by the residual heat through the evaporator and returns to the second liquid storage tank, and the second liquid cooling circulation subsystem completes a second liquid cooling circulation loop.
In some embodiments, the evaporation cycle subsystem comprises: evaporator, throttle valve, condenser and compressor; the liquid refrigerant in the evaporator absorbs the heat transferred to the evaporator by the second liquid cooling circulation subsystem and evaporates to become gaseous refrigerant, the gaseous refrigerant is compressed to be high-pressure gas after entering the compressor, the high-pressure gaseous refrigerant enters the condenser to emit heat to become liquid refrigerant, the liquid refrigerant enters the throttle valve and throttles and expands to be low-pressure liquid, and the evaporation circulation subsystem completes the evaporation circulation loop.
In some embodiments, the electric refrigeration subsystem comprises an electric refrigeration device, and the hydraulic refrigeration subsystem comprises a hydraulic refrigeration device; the electric refrigerating device consumes electric energy and transfers heat from the first heat exchanger with lower temperature to the second heat exchanger with higher temperature; the hydraulic refrigeration device consumes hydraulic energy and transfers heat from a first heat exchanger having a lower temperature to a second heat exchanger having a higher temperature.
In some embodiments, the thermoelectric generation subsystem comprises a thermoelectric generation device, and the thermoelectric liquid supply subsystem comprises a thermoelectric liquid supply device; the thermoelectric generation device converts heat energy into electric energy through thermoelectric generation by utilizing the temperature difference between the third heat exchanger and the fourth heat exchanger, and transmits the electric energy to the bus bar inlet; the temperature difference liquid supply device converts heat energy into hydraulic energy through temperature difference liquid supply by utilizing the temperature difference between the third heat exchanger and the fourth heat exchanger, and the hydraulic energy is conveyed to the high-power equipment executing mechanism.
In some embodiments, the hydraulic power generation subsystem includes an accumulator, a hydraulic motor, and a generator. The accumulator stores high-pressure oil, the high-pressure oil drives the hydraulic motor to rotate to generate mechanical energy, the hydraulic motor drives the generator to rotate to generate electricity, the mechanical energy is converted into electric energy, and the electric energy is transmitted to the bus bar inlet.
In some embodiments, the electrohydraulic thermal complementary system using fuel oil as an energy source and a heat sink comprises twenty three valves, a first valve is arranged between the high heat flux density cooling device and the phase change heat storage heat exchanger, a second valve is arranged between the high heat flux density cooling device and the first heat exchanger, a third valve is arranged between the phase change heat storage heat exchanger and the evaporator, a fourth valve is arranged between the phase change heat storage heat exchanger and the third heat exchanger, a fifth valve is arranged between the throttle valve and the fourth heat exchanger, a sixth valve is arranged between the throttle valve and the evaporator, a seventh valve is arranged between the fuel tank and the condenser, an eighth valve is arranged between the fuel tank and the auxiliary power device, a ninth valve is arranged between the first heat exchanger and the electric refrigeration device, a tenth valve is arranged between the electric refrigeration device and the second heat exchanger, an eleventh valve is arranged between the first heat exchanger and the hydraulic refrigeration device, the twelfth valve is arranged between the hydraulic refrigerating device and the second heat exchanger, the thirteenth valve is arranged between the third heat exchanger and the thermoelectric generation device, the fourteenth valve is arranged between the thermoelectric generation device and the fourth heat exchanger, the fifteenth valve is arranged between the third heat exchanger and the thermoelectric liquid supply device, the sixteenth valve is arranged between the thermoelectric liquid supply device and the fourth heat exchanger, the seventeenth valve is arranged between the condenser when the ram air is used as a heat sink and the hydraulic oil heat exchanger, the eighteenth valve is arranged between the condenser when the ram air is used as a heat sink and the second heat exchanger, the nineteenth valve is arranged between the condenser when the fuel oil is used as a heat sink and the second heat exchanger, the twentieth valve is arranged between the hydraulic refrigerating device and the hydraulic pump, the twenty first valve is arranged between the thermoelectric liquid supply device and the oil filter, the twenty second valve is arranged between the pressure accumulator and the hydraulic motor, and the twenty third valve is arranged between the hydraulic heat exchanger and the external environment.
In some embodiments, the bus bar comprises four inlets and five outlets, the first inlet is connected to the first generator, the second inlet is connected to the thermoelectric generation device, the third inlet is connected to the second generator, the fourth inlet is connected to the energy storage device, the first outlet is connected to the high power device, the second outlet is connected to the first liquid pump, the third outlet is connected to the second liquid pump, the fourth outlet is connected to the electric refrigeration device, and the fifth outlet is connected to the compressor.
In some embodiments, when the electro-mechanical system for electro-hydraulic thermal complementation based on fuel absorbs heat solely from the fuel, the first valve, the third valve, the sixth valve, the seventh valve, the eighth valve, the seventeenth valve are in an open state, the second valve, the fourth valve, the fifth valve, the ninth valve, the tenth valve, the eleventh valve, the twelfth valve, the tenth valve, the fourteenth valve, the fifteenth valve, the sixteenth valve, the eighteenth valve, the nineteenth valve, the twentieth valve, the twenty-first valve, the twenty-second valve, and the twenty-third valve are in a closed state; the first, second and fourth inlets of the bus bar are in a closed state, and the third, fourth, first, second, third and fifth outlets of the bus bar are in an open state.
In some embodiments, when the electromechanical system that performs electrohydraulic thermal complementation based on fuel alone performs thermoelectric generation, the first valve, the third valve, the fourth valve, the fifth valve, the sixth valve, the eighth valve, the tenth valve, the fourteenth valve, the seventeenth valve are in an open state, and the second valve, the seventh valve, the ninth valve, the tenth valve, the eleventh valve, the twelfth valve, the fifteenth valve, the sixteenth valve, the eighteenth valve, the nineteenth valve, the twentieth valve, the twenty-first valve, the twenty-second valve, and the twenty-third valve are in a closed state; the first inlet, the fourth outlet of the bus bar are in a closed state, and the second inlet, the third inlet, the fourth inlet, the first outlet, the second outlet, the third outlet and the fifth outlet of the bus bar are in an open state.
In some embodiments, when the electro-hydraulic thermal complementary electromechanical system based on fuel alone performs hydraulic power generation, the first valve, the third valve, the sixth valve, the eighth valve, the seventeenth valve, and the twenty-second valve are in an open state, and the second valve, the fourth valve, the fifth valve, the seventh valve, the ninth valve, the tenth valve, the eleventh valve, the twelfth valve, the tenth valve, the fourteenth valve, the fifteenth valve, the sixteenth valve, the eighteenth valve, the nineteenth valve, the twentieth valve, the twenty-first valve, and the twenty-third valve are in a closed state; the second inlet and the fourth outlet of the bus bar are in a closed state, and the first inlet, the third inlet, the fourth inlet, the first outlet, the second outlet, the third outlet, and the fifth outlet of the bus bar are in an open state.
In some embodiments, when the electromechanical system for electrohydraulic thermal complementation based on fuel is solely used for temperature difference liquid supply, the first valve, the third valve, the fourth valve, the fifth valve, the sixth valve, the eighth valve, the fifteenth valve, the sixteenth valve, the seventeenth valve and the twenty-first valve are in an open state, and the second valve, the seventh valve, the ninth valve, the tenth valve, the eleventh valve, the twelfth valve, the tenth valve, the thirteenth valve, the fourteenth valve, the eighteenth valve, the nineteenth valve, the twentieth valve, the twenty-second valve and the twenty-third valve are in a closed state; the first, second and fourth inlets of the bus bar are in a closed state, and the third, fourth, first, second, third and fifth outlets of the bus bar are in an open state.
In some embodiments, when the electro-hydraulic thermal complementary electromechanical system based on fuel is used for electric refrigeration alone, the first valve, the second valve, the third valve, the sixth valve, the eighth valve, the ninth valve, the tenth valve, the seventeenth valve and the eighteenth valve are in an open state, and the fourth valve, the fifth valve, the seventh valve, the eleventh valve, the twelfth valve, the tenth third valve, the fourteenth valve, the fifteenth valve, the sixteenth valve, the nineteenth valve, the twentieth valve, the twenty first valve, the twenty second valve and the twenty third valve are in a closed state; the first inlet, the second inlet, the third inlet, the fourth inlet, the first outlet, the second outlet, the third outlet, the fourth outlet, and the fifth outlet of the bus bar are in a closed state, and the third inlet, the fourth inlet, the first outlet, the second outlet, the third outlet, the fourth outlet, and the fifth outlet of the bus bar are in an open state.
In some embodiments, when the electro-hydraulic thermal complementary electromechanical system based on fuel is used for hydraulic refrigeration alone, the first valve, the second valve, the third valve, the sixth valve, the eighth valve, the eleventh valve, the twelfth valve, the seventeenth valve, the eighteenth valve, the twentieth valve are in an open state, and the fourth valve, the fifth valve, the seventh valve, the ninth valve, the tenth third valve, the fourteenth valve, the fifteenth valve, the sixteenth valve, the nineteenth valve, the twenty-first valve, the twenty-second valve, and the twenty-third valve are in a closed state; the first, second and fourth inlets of the bus bar are in a closed state, and the third, fourth, first, second, third and fifth outlets of the bus bar are in an open state.
In some embodiments, when the electro-mechanical system for electro-hydraulic thermal complementation based on fuel absorbs heat and supplies liquid at the same time, the first valve, the third valve, the fourth valve, the fifth valve, the sixth valve, the seventh valve, the eighth valve, the fifteenth valve, the sixteenth valve, the seventeenth valve and the twenty-first valve are in an open state, and the second valve, the ninth valve, the tenth valve, the eleventh valve, the twelfth valve, the tenth valve, the fourteenth valve, the eighteenth valve, the nineteenth valve, the twentieth valve, the twenty-second valve and the twenty-third valve are in a closed state; the first, second and fourth inlets of the bus bar are in a closed state, and the third, fourth, first, second, third and fifth outlets of the bus bar are in an open state.
In some embodiments, when the electromechanical system that performs electrohydraulic thermal complementation based on fuel performs thermoelectric generation and electric refrigeration simultaneously, the first valve, the second valve, the third valve, the fourth valve, the fifth valve, the sixth valve, the eighth valve, the ninth valve, the tenth valve, the third valve, the fourteenth valve, the seventeenth valve, the eighteenth valve are in an open state, and the seventh valve, the eleventh valve, the twelfth valve, the fifteenth valve, the sixteenth valve, the nineteenth valve, the twentieth valve, the twenty-first valve, the twenty-second valve, and the twenty-third valve are in a closed state; the first inlet of the bus bar is in a closed state, and the second, third, fourth, first, second, third, fourth and fifth outlets of the bus bar are in an open state.
In some embodiments, when the electro-mechanical system for electro-hydraulic thermal complementation based on fuel absorbs heat, generates electricity by temperature difference and generates electricity by hydraulic pressure simultaneously, the first valve, the third valve, the fourth valve, the fifth valve, the sixth valve, the seventh valve, the eighth valve, the tenth third valve, the fourteenth valve, the seventeenth valve and the twenty-second valve are in an open state, and the second valve, the ninth valve, the tenth valve, the eleventh valve, the twelfth valve, the fifteenth valve, the sixteenth valve, the eighteenth valve, the nineteenth valve, the twentieth valve, the twenty-first valve and the twenty-third valve are in a closed state; the fourth outlet of the bus bar is in a closed state, and the first, second, third, fourth, first, second, third and fifth outlets of the bus bar are in an open state.
In the above embodiment, when the fuel oil heat absorption scheme is not adopted, the fuel oil in the fuel tank is delivered to the auxiliary power unit through the eighth valve as the energy source of the power supply system and the liquid supply system.
When the fuel oil heat absorption scheme is adopted, fuel oil in the fuel tank flows through a condenser of the evaporation circulation loop after passing through a seventh valve, heat transferred by the heat management system is absorbed, fuel oil with increased temperature flows through a second heat exchanger of the electric refrigeration scheme after passing through a nineteenth valve, heat transferred by a first heat exchanger of the liquid cooling circulation loop is absorbed, fuel oil with further increased temperature flows through a hydraulic oil heat exchanger, heat transferred by the liquid supply system is absorbed, and finally, the fuel oil is conveyed to an auxiliary power device, is mixed with air and combusted, high-temperature gas is generated to impact a turbine to rotate, the turbine drives a gear box, and the gear box drives a generator to rotate to generate electric energy, so that power is supplied to high-power equipment on the aircraft and the high-power equipment is used as an energy source of a power supply system. When the temperature of the fuel oil is increased, the combustion efficiency is higher, more mechanical energy is generated, more electric energy is generated by the generator, and more hydraulic energy is generated by the operation of the mechanically driven hydraulic pump and the electric pump.
In the above embodiment, the mechanical driving hydraulic pump converts mechanical energy generated by the auxiliary power device into hydraulic energy, hydraulic oil is pumped in from the oil tank and outputs high-pressure oil, the high-pressure oil is filtered by oil to remove solid impurities, the pressure and flow rate are regulated by the control valve, the high-power equipment executing mechanism is pushed to do work, or the electric pump consumes electric energy to generate hydraulic energy, hydraulic oil is pumped in from the oil tank and outputs high-pressure oil, the high-pressure oil is filtered by oil to remove solid impurities, and the pressure and flow rate are regulated by the control valve, so that the high-power equipment executing mechanism is pushed to do work.
Based on the same inventive concept, the invention introduces fuel oil heat absorption, electric refrigeration, hydraulic refrigeration, thermoelectric generation, thermoelectric liquid supply and hydraulic power generation, and can have the capability of mutual conversion and utilization of electric energy, hydraulic energy and heat energy. The method for carrying out electric heating liquid complementation based on fuel oil comprises the following steps:
When a mechanically driven hydraulic pump is used for the supply,
In the first case, when the power supply amount of the power supply system is lower than the total requirement, namely the power generation amount W C of the power generation system and the power supply amount W D of the energy storage device are smaller than the power requirement W 1 of the high-power device, the power requirement W 2 of the first liquid pump, the power requirement W 3 of the second liquid pump and the power requirement W 5 of the compressor; meanwhile, the liquid supply amount of the liquid supply system is higher than the total demand, namely the hydraulic energy output P hydraulic pump hydraulic energy output of the mechanical drive hydraulic pump is greater than the hydraulic energy demand P High power device actuator requirements of the high-power equipment executing mechanism; the refrigerating capacity of the thermal management system is higher than the total demand, namely the condenser heat exchange capacity Q lnq +the hydraulic oil heat exchange capacity Q Hydraulic oil heat exchanger > the refrigerating capacity demand Q High power equipment requirements of the high-power equipment and the refrigerating capacity demand Q Liquid supply system demand of the liquid supply system.
Step one: the fuel absorbs heat independently, the first valve, the third valve, the sixth valve, the seventh valve, the eighth valve and the seventeenth valve are in an open state, and the second valve, the fourth valve, the fifth valve, the ninth valve, the tenth valve, the eleventh valve, the twelfth valve, the tenth third valve, the fourteenth valve, the fifteenth valve, the sixteenth valve, the eighteenth valve, the nineteenth valve, the twentieth valve, the twenty-first valve, the twenty-second valve and the twenty-third valve are in a closed state; the first, second and fourth inlets of the bus bar are in a closed state, and the third, fourth, first, second, third and fifth outlets of the bus bar are in an open state.
In terms of thermal management, the refrigeration capacity of the thermal management system is higher than the total demand. For the first liquid cooling circulation loop, the heating value of the high-power equipment is equal to the heat exchange quantity of the phase-change heat storage heat exchanger, namely Q High power equipment =Qxbhrq; for the second liquid cooling circulation loop, the heat stored by the phase change heat storage heat exchanger is transferred to the evaporator of the evaporation circulation loop, namely Q xbhrq=Qzfq. For the evaporative circulation loop, the heat from the evaporator is transferred to the condenser and then carried away by the fuel, i.e., Q zfq=Qlnq. For the hydraulic oil circulation loop, when the liquid supply system works, heat is generated by mechanical friction of the hydraulic pump, hydraulic friction of the control valve and the pipeline, and the temperature of the hydraulic oil rises after the hydraulic oil absorbs the heat. The hydraulic oil with the increased temperature flows through the hydraulic oil heat exchanger, heat in the liquid supply system is transferred to the fuel oil and then returns to the oil tank, and the hydraulic oil circulation loop, namely Q Hydraulic oil heat exchanger =Q liquid supply system , is completed. In summary, for thermal management systems, a fuel oil heat absorption scheme is adopted, which has no influence on the refrigerating capacity, but the heat sink is changed from ram air to fuel oil.
In the aspect of power supply, a fuel oil heat absorption scheme is adopted, fuel oil flows through a condenser to absorb heat transferred to the condenser by a heat management system, then flows through a hydraulic oil heat exchanger to absorb heat transferred to the hydraulic oil heat exchanger by a liquid supply system, the fuel oil after heat absorption is finally conveyed to an auxiliary power device and is combusted after being mixed with air to generate high-temperature gas to impact a turbine to rotate, the turbine drives a gear box, and the gear box drives a generator to rotate to generate electric energy, so that power is supplied to high-power equipment on board and used as an energy source of a power supply system. Assuming that the total power generation efficiency of the auxiliary power device driving the generator before heat absorption is eta 1 and the total power generation capacity is W C; after absorbing the heat of the heat management system and the liquid supply system, the auxiliary power device drives the total power generation efficiency of the generator to be improved by eta 2, the total power generation capacity is improved to W C'=WC*η2/η1, and the total power supply capacity is W C'+WD.
In the aspect of a liquid supply system, a mechanical driving hydraulic pump converts mechanical energy generated by an auxiliary power device into hydraulic energy, hydraulic oil is pumped in from an oil tank and outputs high-pressure oil, the high-pressure oil is filtered by oil to remove solid impurities, and then the pressure and the flow are regulated by a control valve to push an actuating mechanism of high-power equipment to do work. Under the condition of neglecting various losses, hydraulic energy output by the mechanically driven hydraulic pump is used for pushing the high-power equipment executing mechanism to do work. Assuming that the total liquid supply efficiency of the mechanical driving hydraulic pump driven by the auxiliary power device before heat absorption is eta 3 and the total hydraulic energy output is P hydraulic pump hydraulic energy output ; after absorbing the heat of the heat management system and the liquid supply system, the auxiliary power device drives the total liquid supply efficiency of the mechanically driven hydraulic pump to be improved by eta 4, and then the total hydraulic energy output is improved to P hydraulic pump hydraulic energy output '=P hydraulic pump hydraulic energy output *η4/η3. If W C'+WD≥W1+W2+W3+W5 is adopted, the fuel oil heat absorption scheme improves the power generation efficiency, can meet the power supply requirement of the system, and can realize electric energy supplement by introducing the fuel oil heat absorption scheme. The opening degree of the seventh valve and the opening degree of the ram air door are adjusted, so that the range of the fuel oil heat absorption capacity can be adjusted flexibly between 0~Q lnq+Q Hydraulic oil heat exchanger , and the power generation lifting capacity of the fuel oil heat absorption scheme can be adjusted flexibly. At this time, because the liquid supply amount of the liquid supply system is greater than or equal to the total demand, and the hydraulic energy is supplemented; the refrigerating capacity of the thermal management system is greater than or equal to the total demand. Therefore, the regulation and control range only depends on the electric energy requirement of the high-power equipment system, and the hydraulic energy and the refrigerating capacity requirement of the high-power equipment system do not need to be considered. If W C'+WD<W1+W2+W3+W5, the fuel oil heat absorption scheme cannot meet the requirement, and the second step needs to be continued.
Step two: the temperature difference power generation is independently carried out, and the first valve, the third valve, the fourth valve, the fifth valve, the sixth valve, the eighth valve, the tenth valve, the fourteenth valve and the seventeenth valve are in an open state, and the second valve, the seventh valve, the ninth valve, the tenth valve, the eleventh valve, the twelfth valve, the fifteenth valve, the sixteenth valve, the eighteenth valve, the nineteenth valve, the twentieth valve, the twenty-first valve, the twenty-second valve and the twenty-third valve are in a closed state; the first inlet, the fourth outlet of the bus bar are in a closed state, and the second inlet, the third inlet, the fourth inlet, the first outlet, the second outlet, the third outlet and the fifth outlet of the bus bar are in an open state.
In terms of thermal management systems, the refrigeration capacity of the thermal management system is higher than the total demand. For the first liquid cooling circulation loop, the heating value of the high-power equipment is equal to the heat exchange quantity of the phase-change heat storage heat exchanger, namely Q High power equipment =Qxbhrq; and for the second liquid cooling circulation loop, part of heat stored by the phase change heat storage heat exchanger is taken away by the third heat exchanger and then is recycled for power generation, and the residual heat is transmitted to the evaporation circulation loop through the evaporator, namely Q xbhrq=Qhrq3+Qzfq. For the thermoelectric power generation scheme, part of heat taken away by the third heat exchanger is recovered to generate power, and the rest is transmitted to the evaporation circulation loop through the fourth heat exchanger, namely Q hrq3=WB +Qhrq4. Assuming that the efficiency of thermoelectric generation is η 5, the amount of thermoelectric generation is W B=Qhrq3*η5, and the amount of heat Q hrq4=Qhrq3-WB=Qhrq3(1-η1 taken away by the fourth heat exchanger). For the evaporation circulation loop, the heat of the evaporator and the fourth heat exchanger is transferred to the condenser and then taken away by the heat sink, namely Qlnq=Qzfq+Qhrq4=Qzfq+Qhrq3(1-η5)=Qxbhrq-Qhrq3*η5. for the hydraulic oil circulation loop, when the liquid supply system works, the mechanical friction of the hydraulic pump, the hydraulic friction of the control valve and the pipeline and the like can generate heat, and the temperature of the hydraulic oil rises after absorbing the heat. The hydraulic oil with the increased temperature flows through the hydraulic oil heat exchanger, heat in the liquid supply system is transferred to the ram air and then returns to the oil tank, and a hydraulic oil circulation loop, namely Q Hydraulic oil heat exchanger =Q liquid supply system , is completed. In summary, for the thermal management system, a thermoelectric generation scheme is adopted to supplement the refrigerating capacity of Q hrq3*η5.
In the aspect of a liquid supply system, a mechanical driving hydraulic pump converts mechanical energy generated by an auxiliary power device into hydraulic energy, hydraulic oil is pumped in from an oil tank and outputs high-pressure oil, the high-pressure oil is filtered by oil to remove solid impurities, and then the pressure and the flow are regulated by a control valve to push an actuating mechanism of high-power equipment to do work. Under the condition of neglecting various losses, hydraulic energy output by the mechanically driven hydraulic pump is used for pushing the high-power equipment executing mechanism to do work, namely P hydraulic pump hydraulic energy output =P High-power equipment actuating mechanism . The temperature difference power generation scheme is adopted, so that the liquid supply amount of the liquid supply system is not influenced.
In the aspect of a power supply system, a thermoelectric generation scheme is adopted, so that the thermoelectric generation capacity W B=Qhrq3*η5 is supplemented, and the total power supply capacity is W B+WC+WD. If Q hrq3*η5≥W1+W2+W3+W5-(WC+WD), the supplementary generated energy can meet the power supply requirement of the system, and the electric energy can be supplemented by introducing thermoelectric generation. The range (Q hrq3+Qzfq=Qxbhrq) of Q hrq3 can be adjusted by adjusting the opening degree of the third valve and the opening degree of the fourth valve, namely, the control can be flexibly carried out between 0~Q xbhrq, and the complementary power generation amount can be flexibly controlled. At this time, because the liquid supply amount of the liquid supply system is greater than or equal to the total demand; the refrigerating capacity of the thermal management system is greater than or equal to the total demand, and the refrigerating capacity is supplemented. Therefore, the regulation and control range only depends on the electric energy requirement of the high-power equipment system, and the hydraulic energy and the refrigerating capacity requirement of the high-power equipment system do not need to be considered. If Q hrq3*η5<W1+W2+W3+W5-(WC+WD), the thermoelectric generation scheme cannot meet the requirement, and the step three needs to be continued.
Step three: when hydraulic power generation is performed alone, the first, third, sixth, eighth, seventeenth, and twenty-second valves are in an open state, and the second, fourth, fifth, seventh, ninth, tenth, eleventh, twelfth, tenth, fourteenth, fifteenth, sixteenth, eighteenth, nineteenth, twentieth, twenty-first, and twenty-third valves are in a closed state; the second inlet and the fourth outlet of the bus bar are in a closed state, and the first inlet, the third inlet, the fourth inlet, the first outlet, the second outlet, the third outlet, and the fifth outlet of the bus bar are in an open state.
In terms of thermal management systems, the refrigeration capacity of the thermal management system is higher than the total demand. For the first liquid cooling circulation loop, the heating value of the high-power equipment is equal to the heat exchange quantity of the phase-change heat storage heat exchanger, namely Q High power equipment =Qxbhrq; for the second liquid cooling circulation loop, the heat stored by the phase change heat storage heat exchanger is transferred to the evaporation circulation loop through the evaporator, namely Q xbhrq=Qzfq. For the evaporative circulation loop, the heat of the evaporator is transferred to the condenser and then carried away by the heat sink, i.e., Q lnq=Q High power equipment . For the hydraulic oil circulation loop, when the liquid supply system works, heat is generated by mechanical friction of the hydraulic pump, hydraulic friction of the control valve and the pipeline, and the temperature of the hydraulic oil rises after the hydraulic oil absorbs the heat. The hydraulic oil with the increased temperature flows through the hydraulic oil heat exchanger, heat in the liquid supply system is transferred to the fuel oil and then returns to the oil tank, and the hydraulic oil circulation loop, namely Q Hydraulic oil heat exchanger =Q liquid supply system , is completed. In summary, for the thermal management system, the hydraulic power generation scheme is adopted, so that the refrigerating capacity of the thermal management system is not influenced.
In the aspect of a liquid supply system, a mechanical driving hydraulic pump converts mechanical energy generated by an auxiliary power device into hydraulic energy, hydraulic oil is pumped in from an oil tank and outputs high-pressure oil, the high-pressure oil is filtered by oil to remove solid impurities, and then the pressure and the flow are regulated by a control valve to push an actuating mechanism of high-power equipment to do work. The high-pressure oil stored in the accumulator pushes the hydraulic motor to generate mechanical energy, and drives the generator to rotate for power generation. For the hydraulic power generation scheme, part of hydraulic energy output by the mechanical driving hydraulic pump is stored in the accumulator, and the rest of hydraulic energy passes through the oil filter and the control valve and pushes the high-power equipment executing mechanism to do work, namely P hydraulic pump hydraulic energy output =P Pressure accumulator +P High-power equipment actuating mechanism . Assuming that the total operation efficiency of the hydraulic power generation is η 6, the hydraulic power generation amount W A=P Pressure accumulator *η6. In summary, by adopting the hydraulic power generation scheme, the output power provided by the liquid supply system to the actuating mechanism is reduced by P Pressure accumulator , and the hydraulic power generation W A=P Pressure accumulator *η6 is supplemented.
In the aspect of a power supply system, a hydraulic power generation scheme is adopted, the hydraulic power generation capacity W A=P Pressure accumulator *η6 is supplemented, and the total power supply capacity is W A+WC+WD.
If P Pressure accumulator *η6≥W1+W2+W3+W5-(WC+WD), the supplementary generated energy can meet the electric energy requirement of the system, and the electric energy can be supplemented by introducing hydraulic power generation. The range (P Pressure accumulator +P High-power equipment actuating mechanism =P hydraulic pump hydraulic energy output ) of P Pressure accumulator can be adjusted by adjusting the opening of the twenty-second valve, so that the supplementary power generation amount can be flexibly regulated and controlled. At this time, since the liquid supply amount of the liquid supply system is equal to or greater than the total demand and the hydraulic energy consumption is performed, P hydraulic pump hydraulic energy output -P Pressure accumulator ≥P High power device actuator requirements needs to be satisfied, that is, the hydraulic energy consumed by the hydraulic power generation device is not greater than the redundancy amount of the hydraulic energy of the system. If P hydraulic pump hydraulic energy output -P Pressure accumulator <P High power device actuator requirements or P Pressure accumulator *η6<W1+W2+W3+W5-(WC+WD) the hydraulic power generation scheme is not satisfactory and step four needs to be continued.
Step four: simultaneously adopting a fuel oil heat absorption scheme, a temperature difference power generation scheme and a hydraulic power generation scheme, wherein the first valve, the third valve, the fourth valve, the fifth valve, the sixth valve, the seventh valve, the eighth valve, the tenth valve, the fourteenth valve, the seventeenth valve and the twenty-second valve are in an open state, and the second valve, the ninth valve, the tenth valve, the eleventh valve, the twelfth valve, the fifteenth valve, the sixteenth valve, the eighteenth valve, the nineteenth valve, the twentieth valve, the twenty-first valve and the twenty-third valve are in a closed state; the fourth outlet of the bus bar is in a closed state, and the first, second, third, fourth, first, second, third and fifth outlets of the bus bar are in an open state.
For the thermal management system, the temperature difference power generation scheme is adopted, the refrigerating capacity of Q hrq3*η1 is supplemented, and the fuel oil heat absorption scheme and the hydraulic power generation scheme are adopted to have no influence on the refrigerating capacity.
For the liquid supply system, a fuel oil heat absorption scheme is adopted, and after the heat of the thermal management system and the liquid supply system is absorbed, an auxiliary power device drives the total liquid supply efficiency of the mechanically driven hydraulic pump to be improved by eta 4, so that the total hydraulic energy output is improved to P hydraulic pump hydraulic energy output '= P hydraulic pump hydraulic energy output *η4/η3; by adopting the hydraulic power generation scheme, the output power provided by the liquid supply system to the actuating mechanism is reduced by P Pressure accumulator .
For the power supply system, a fuel oil heat absorption scheme is adopted, and after heat of the thermal management system and the liquid supply system is absorbed, the auxiliary power device drives the total power generation efficiency of the generator to be improved by eta 2, so that the total power generation capacity is improved to W C'=WC*η2/η1; the temperature difference power generation scheme is adopted, so that the temperature difference power generation W B=Qhrq3*η5 is supplemented; the hydraulic power generation scheme is adopted, the hydraulic power generation capacity W A=P Pressure accumulator *η6 is supplemented, and the total power supply capacity is W A+WB+WC'+WD.
If Qhrq3*η5+P Pressure accumulator *η6≥W1+W2+W3+W5-(WC'+WD),, the power generation capacity can be supplemented to meet the power requirement of the system, and the power supplement can be realized by introducing a fuel oil heat absorption scheme, a temperature difference power generation scheme and a hydraulic power generation scheme. The range (Q hrq3+Qzfq=Qxbhrq) of the Q hrq3 can be adjusted by adjusting the opening degrees of the third valve and the fourth valve, namely the temperature difference power generation can be flexibly regulated and controlled between 0~Q xbhrq, and the complementary power generation amount of the temperature difference power generation can be flexibly regulated and controlled. The range (P Pressure accumulator +P High-power equipment actuating mechanism = P hydraulic pump hydraulic energy output ) of P Pressure accumulator can be adjusted by adjusting the opening degree of the twenty-second valve, namely the complementary power generation amount of the hydraulic power generation can be flexibly regulated and controlled. The opening degree of the seventh valve and the opening degree of the ram air door are adjusted, so that the range of the fuel oil heat absorption capacity can be adjusted flexibly between 0~Q lnq+Q Hydraulic oil heat exchanger , and the power generation lifting capacity of the fuel oil heat absorption scheme can be adjusted flexibly. At this time, since the liquid supply amount of the liquid supply system is greater than or equal to the total demand, and the hydraulic energy is lifted and consumed, P hydraulic pump hydraulic energy output '-P Pressure accumulator >P High power device actuator requirements needs to be satisfied, that is, the difference between the hydraulic energy lifted by the hydraulic power generation device and the hydraulic energy consumed is not greater than the redundancy of the hydraulic energy of the system. If P hydraulic pump hydraulic energy output '-P Pressure accumulator <P High power device actuator requirements or Qhrq3*η5+P Pressure accumulator *η6<W1+W2+W3+W5-(WC'+WD), is not capable of meeting the requirements by adopting a fuel oil heat absorption scheme, a temperature difference power generation scheme and a hydraulic power generation scheme, the capacity and the flow of the fuel tank need to be redesigned, and the eighth valve is adjusted to increase the fuel flow.
When the liquid supply amount of the liquid supply system is lower than the total requirement, namely the hydraulic energy output P hydraulic pump hydraulic energy output of the mechanical drive hydraulic pump is less than the hydraulic energy requirement P High power device actuator requirements of the high-power equipment executing mechanism; the power supply quantity of the power supply system is higher than the total demand, namely the generated energy W C of the power generation system, the power supply quantity W D of the energy storage device, the power demand W 1 of the high-power device, the power demand W 2 of the first liquid pump, the power demand W 3 of the second liquid pump and the power demand W 5 of the compressor; meanwhile, the refrigerating capacity of the thermal management system is higher than the total demand, namely the condenser heat exchange capacity Q lnq +the hydraulic oil heat exchange capacity Q Hydraulic oil heat exchanger > the refrigerating capacity demand Q High power equipment requirements of the high-power equipment and the refrigerating capacity demand Q Liquid supply system demand of the liquid supply system.
Step five: the fuel absorbs heat independently, the first valve, the third valve, the sixth valve, the seventh valve, the eighth valve and the seventeenth valve are in an open state, and the second valve, the fourth valve, the fifth valve, the ninth valve, the tenth valve, the eleventh valve, the twelfth valve, the tenth third valve, the fourteenth valve, the fifteenth valve, the sixteenth valve, the eighteenth valve, the nineteenth valve, the twentieth valve, the twenty-first valve, the twenty-second valve and the twenty-third valve are in a closed state; the first, second and fourth inlets of the bus bar are in a closed state, and the third, fourth, first, second, third and fifth outlets of the bus bar are in an open state.
In the aspect of a heat management system, a fuel oil heat absorption scheme is adopted, so that the refrigerating capacity is not influenced, but the heat sink is changed into fuel oil from ram air.
In the aspect of a power supply system, a fuel oil heat absorption scheme is adopted, and after heat of a thermal management system and a liquid supply system is absorbed, an auxiliary power device drives the total power generation efficiency of a generator to be improved by eta 2, so that the total power generation capacity is improved to W C'=WC*η2/η1, and the total power supply capacity is W C'+WD.
In the aspect of a liquid supply system, a mechanical driving hydraulic pump converts mechanical energy generated by an auxiliary power device into hydraulic energy, hydraulic oil is pumped in from an oil tank and outputs high-pressure oil, the high-pressure oil is filtered by oil to remove solid impurities, and then the pressure and the flow are regulated by a control valve to push an actuating mechanism of high-power equipment to do work. Under the condition of neglecting various losses, hydraulic energy output by the mechanically driven hydraulic pump is used for pushing the high-power equipment executing mechanism to do work. Assuming that the total liquid supply efficiency of the mechanical driving hydraulic pump driven by the auxiliary power device before heat absorption is eta 3 and the total hydraulic energy output is P hydraulic pump hydraulic energy output ; after absorbing the heat of the heat management system and the liquid supply system, the auxiliary power device drives the total liquid supply efficiency of the mechanically driven hydraulic pump to be improved by eta 4, and then the total hydraulic energy output is improved to P hydraulic pump hydraulic energy output '=P hydraulic pump hydraulic energy output *η4/η3.
If P hydraulic pump hydraulic energy output *η4/η3≥P High power device actuator requirements is adopted, the fuel oil heat absorption scheme can improve the liquid supply efficiency, can meet the hydraulic energy requirement of the system, and can realize the hydraulic energy supplement by introducing the fuel oil heat absorption scheme. The opening degree of the seventh valve and the opening degree of the ram air door are adjusted, so that the range of the heat absorption quantity of the fuel can be flexibly adjusted and controlled between 0~Q lnq+Q Hydraulic oil heat exchanger , and the hydraulic energy lifting quantity of a fuel heat absorption scheme is flexibly adjusted and controlled. At this time, because the power supply amount of the power supply system is greater than or equal to the total demand, and the electric energy is supplemented; the refrigerating capacity of the thermal management system is greater than or equal to the total demand. Therefore, the regulation and control range only depends on the hydraulic energy requirement of the high-power equipment system, and the electric energy and refrigerating capacity requirements of the high-power equipment system do not need to be considered. If P hydraulic pump hydraulic energy output *η4/η3<P High power device actuator requirements , the fuel oil heat absorption scheme cannot meet the requirement, and the step six needs to be continued.
Step six: the temperature difference liquid supply is independently carried out, and the first valve, the third valve, the fourth valve, the fifth valve, the sixth valve, the eighth valve, the fifteenth valve, the sixteenth valve, the seventeenth valve and the twenty first valve are in an open state, and the second valve, the seventh valve, the ninth valve, the tenth valve, the eleventh valve, the twelfth valve, the tenth valve, the fourteenth valve, the eighteenth valve, the nineteenth valve, the twentieth valve, the twenty second valve and the twenty third valve are in a closed state; the first, second and fourth inlets of the bus bar are in a closed state, and the third, fourth, first, second, third and fifth outlets of the bus bar are in an open state.
In terms of thermal management systems, the refrigeration capacity of the thermal management system is higher than the total demand. For the first liquid cooling circulation loop, the heating value of the high-power equipment is equal to the heat exchange quantity of the phase-change heat storage heat exchanger, namely Q High power equipment =Qxbhrq; and for the second liquid cooling circulation loop, part of heat stored by the phase change heat storage heat exchanger is taken away by the third heat exchanger and then is recycled for liquid supply, and the residual heat is transmitted to the evaporation circulation loop through the evaporator, namely Q xbhrq=Qhrq3+Qzfq. For the temperature difference liquid supply scheme, part of heat taken away by the third heat exchanger is recovered for liquid supply, and the rest is transmitted to the evaporation circulation loop through the fourth heat exchanger. Assuming that the efficiency of the temperature difference liquid supply is eta 7, the hydraulic energy output P Hydraulic energy output of temperature difference liquid supply device =Qhrq3*η7 of the temperature difference liquid supply device, namely the heat Q hrq4=Qhrq3-P Temperature difference liquid supply device =Qhrq3(1-η7 taken away by the fourth heat exchanger is provided. For the evaporation circulation loop, the heat of the evaporator and the fourth heat exchanger is transferred to the condenser and then taken away by the heat sink, namely Qlnq=Qzfq+Qhrq4=Qzfq+Qhrq3(1-η7)=Qxbhrq-Qhrq3*η7. for the hydraulic oil circulation loop, when the liquid supply system works, the mechanical friction of the hydraulic pump, the hydraulic friction of the control valve and the pipeline and the like can generate heat, and the temperature of the hydraulic oil rises after absorbing the heat. The hydraulic oil with the increased temperature flows through the hydraulic oil heat exchanger, heat in the liquid supply system is transferred to the heat sink and then returns to the oil tank, and the hydraulic oil circulation loop, namely Q Hydraulic oil heat exchanger =Q liquid supply system , is completed. In summary, for the thermal management system, a temperature difference liquid supply scheme is adopted, and the refrigerating capacity of Q hrq3*η7 is supplemented.
In the aspect of a liquid supply system, a mechanical driving hydraulic pump converts mechanical energy generated by an auxiliary power device into hydraulic energy, and hydraulic oil is pumped in from an oil tank and high-pressure oil is output; the temperature difference liquid supply device is driven by the temperature difference between the inlet of the secondary refrigerant third heat exchanger and the inlet of the refrigerant evaporator, converts heat energy into hydraulic energy through a temperature difference liquid supply technology, and outputs high-pressure oil. The high-pressure oil liquid which is jointly output by the mechanical driving hydraulic pump and the temperature difference liquid supply device is subjected to oil filtration to remove solid impurities, and then the high-power equipment executing mechanism is pushed to do work after the pressure and the flow are regulated by the control valve. Under the condition of neglecting various losses, hydraulic energy output by the mechanical driving hydraulic pump and hydraulic energy output by the temperature difference liquid supply device are jointly used for pushing the high-power equipment executing mechanism to do work, namely P High-power equipment actuating mechanism =P hydraulic pump hydraulic energy output +P Hydraulic energy output of temperature difference liquid supply device . The temperature difference liquid supply scheme is adopted, and the hydraulic energy output P Hydraulic energy output of temperature difference liquid supply device =Qhrq3*η7 is supplemented.
In the aspect of a power supply system, a temperature difference liquid supply scheme is adopted, and the power generation capacity of the power supply system is not influenced.
If Q hrq3*η7≥P High power device actuator requirements -P hydraulic pump hydraulic energy output is adopted, the supplementing hydraulic energy can meet the hydraulic energy requirement of the system, and the supplementing of the hydraulic energy can be realized by introducing temperature difference liquid supply. The range (Q hrq3+Qzfq=Qxbhrq) of the Q hrq3 can be adjusted by adjusting the opening degrees of the third valve and the fourth valve, namely the temperature difference liquid supply can be flexibly regulated and controlled between 0~Q xbhrq, and the supplementary liquid supply quantity of the temperature difference liquid supply can be flexibly regulated and controlled. At this time, since the power supply amount of the power supply system is equal to or larger than the total demand; the refrigerating capacity of the thermal management system is greater than or equal to the total demand, and the refrigerating capacity is supplemented. Therefore, the regulation and control range only depends on the hydraulic energy requirement of the high-power equipment system, and the electric energy and refrigerating capacity requirements of the high-power equipment system do not need to be considered. If Q hrq3*η7<P High power device actuator requirements -P hydraulic pump hydraulic energy output , the solution supply scheme with temperature difference can not meet the requirement, and the step seven needs to be continued.
Step seven: simultaneously carrying out a fuel oil heat absorption scheme and temperature difference liquid supply, wherein the first valve, the third valve, the fourth valve, the fifth valve, the sixth valve, the seventh valve, the eighth valve, the fifteenth valve, the sixteenth valve, the seventeenth valve and the twenty-first valve are in an open state, and the second valve, the ninth valve, the tenth valve, the eleventh valve, the twelfth valve, the tenth valve, the fourteenth valve, the eighteenth valve, the nineteenth valve, the twentieth valve, the twenty-second valve and the twenty-third valve are in a closed state; the first, second and fourth inlets of the bus bar are in a closed state, and the third, fourth, first, second, third and fifth outlets of the bus bar are in an open state.
In the aspect of a thermal management system, a fuel oil heat absorption scheme is adopted, so that the refrigerating capacity is not influenced; the temperature difference liquid supply scheme is adopted, and the refrigerating capacity of Q hrq3*η7 is supplemented.
In the aspect of a power supply system, a fuel oil heat absorption scheme is adopted, and the total power generation amount is increased to W C'=WC*η2/η1; the temperature difference liquid supply scheme is adopted, so that the generated energy is not influenced.
In the aspect of a liquid supply system, a fuel oil heat absorption scheme is adopted, and the total hydraulic energy output is increased to P hydraulic pump hydraulic energy output '=P hydraulic pump hydraulic energy output *η4/η3; the temperature difference liquid supply scheme is adopted, and the hydraulic energy output P Hydraulic energy output of temperature difference liquid supply device =Qhrq3*η7 is supplemented.
If Q hrq3*η7+P hydraulic pump hydraulic energy output *η4/η3≥P High power device actuator requirements is adopted, the supplementing hydraulic energy can meet the hydraulic energy requirement of the system, and the hydraulic energy supplementing can be realized by introducing a fuel oil heat absorption scheme and a temperature difference liquid supply scheme. The range (Q hrq3+Qzfq=Qxbhrq) of the Q hrq3 can be adjusted by adjusting the opening of the third valve and the opening of the fourth valve, namely the temperature difference liquid supply can be flexibly regulated and controlled between 0~Q xbhrq, and the supplementary liquid supply quantity of the temperature difference liquid supply can be flexibly regulated and controlled; the opening degree of the seventh valve and the opening degree of the ram air door are adjusted, so that the range of the heat absorption quantity of the fuel can be flexibly adjusted and controlled between 0~Q lnq+Q Hydraulic oil heat exchanger , and the hydraulic energy lifting quantity of a fuel heat absorption scheme is flexibly adjusted and controlled. At this time, because the power supply amount of the power supply system is greater than or equal to the total demand, and the power generation amount is increased; the refrigerating capacity of the thermal management system is greater than or equal to the total demand, and the refrigerating capacity is supplemented. Therefore, the regulation and control range only depends on the hydraulic energy requirement of the high-power equipment system, and the electric energy and refrigerating capacity requirements of the high-power equipment system do not need to be considered. If Q hrq3*η7+P hydraulic pump hydraulic energy output *η4/η3<P High power device actuator requirements , the fuel tank capacity and flow rate can not be redesigned by adopting the scheme of simultaneously adopting fuel heat absorption and temperature difference liquid supply, and the eighth valve is regulated to increase the fuel flow rate.
And in the third condition, when the refrigerating capacity of the thermal management system is lower than the total demand, namely the condenser heat exchange capacity Q lnq +the hydraulic oil heat exchange capacity Q Hydraulic oil heat exchanger is smaller than the refrigerating capacity demand Q High power equipment requirements of the high-power equipment and the refrigerating capacity demand Q Liquid supply system demand of the liquid supply system. The power supply quantity of the power supply system is higher than the total demand, namely the generated energy W C of the power generation system, the power supply quantity W D of the energy storage device, the power demand W 1 of the high-power device, the power demand W 2 of the first liquid pump, the power demand W3 of the second liquid pump and the power demand W 5 of the compressor; meanwhile, the liquid supply amount of the liquid supply system is higher than the total requirement, namely the hydraulic energy output P hydraulic pump hydraulic energy output of the mechanical drive hydraulic pump is greater than the hydraulic energy requirement P High power device actuator requirements of the actuating mechanism of the high-power equipment.
Step eight: the electric refrigeration scheme is adopted, and the first valve, the second valve, the third valve, the sixth valve, the eighth valve, the ninth valve, the tenth valve, the seventeenth valve and the eighteenth valve are in an open state, and the fourth valve, the fifth valve, the seventh valve, the eleventh valve, the twelfth valve, the tenth valve, the fourteenth valve, the fifteenth valve, the sixteenth valve, the nineteenth valve, the twentieth valve, the twenty first valve, the twenty second valve and the twenty third valve are in a closed state; the first inlet, the second inlet, the third inlet, the fourth inlet, the first outlet, the second outlet, the third outlet, the fourth outlet, and the fifth outlet of the bus bar are in a closed state, and the third inlet, the fourth inlet, the first outlet, the second outlet, the third outlet, the fourth outlet, and the fifth outlet of the bus bar are in an open state.
In terms of thermal management systems, the refrigeration capacity of the thermal management system is lower than the total demand. For the first liquid cooling circulation loop, a part of the heating value of the high-power equipment is taken away by the first heat exchanger and then is transmitted to the second heat exchanger through the electric refrigerating device, and the residual heat is stored in the phase-change heat storage heat exchanger, namely Q High power equipment requirements =Qhrq2+Qxbhrq; for the electric refrigeration scheme, the electric refrigeration device consumes electric energy, the heat exchanged by the first heat exchanger is completely transferred to the second heat exchanger, and then is taken away by a heat sink with higher temperature, namely Q hrq1=Qhrq2. Assume that the efficiency of electric refrigeration is η 8, and the electric energy W 4=Qhrq1/η8 is consumed. Supplementing the refrigerating capacity of Q hrq1=Qhrq2. For the second liquid cooling circulation loop, the heat stored by the phase change heat storage heat exchanger is transferred to the evaporation circulation loop through the evaporator, namely Q xbhrq=Qzfq. For the evaporative circulation loop, the heat of the evaporator is transferred to the condenser and then carried away by the heat sink. I.e., Q zfq=Qlnq. For the thermal management system, an electric refrigeration scheme is adopted, so that Q hrq1/η8 electric energy is consumed, and the refrigeration capacity of Q hrq1 is supplemented. For the hydraulic oil circulation loop, the heat exchange capacity of the hydraulic oil heat exchanger is equal to the refrigerating capacity requirement of the liquid supply system, namely Q Hydraulic oil heat exchanger =Q liquid supply system .
In the aspect of a power supply system, an electric refrigeration scheme is adopted, the power supply capacity W 4 of the electric refrigeration device is consumed, and the total requirement is W 1+W2+W3+W4+W5.
In the aspect of the liquid supply system, an electric refrigeration scheme is adopted, and the liquid supply amount of the liquid supply system is not influenced.
If Q hrq1≥Q High power equipment requirements -Qlnq is adopted, the supplementing refrigerating capacity can meet the refrigerating capacity requirement of the system, and the refrigerating capacity supplement can be realized by introducing an electric refrigerating scheme. The first valve is fully opened, the size of Q xbhrq is unchanged and always the maximum value is achieved due to insufficient refrigerating capacity, the range (Q hrq1=Q High power equipment requirements -Qxbhrq) of the Q hrq1 can be adjusted by adjusting the opening of the second valve, namely the range can be flexibly adjusted and controlled between 0~Q High power equipment requirements -Qxbhrq, the supplementary refrigerating capacity can be flexibly adjusted and controlled, and the refrigerating capacity requirement is met at any moment. At this time, the power supply amount of the power supply system is greater than or equal to the total demand, and the power consumption is performed, and W 4≤W1+W2+W3+W5-(WC+WD needs to be satisfied), that is, the power consumed by the electric refrigeration device is not greater than the redundancy amount of the system power. If Q hrq1<Q High power equipment requirements -Qlnq, or W 4>W1+W2+W3+W5-(WB+WC), then the refrigeration and power requirements cannot be met simultaneously with the electric refrigeration scheme, and step nine needs to be continued.
Step nine: hydraulic refrigeration is carried out independently, and the first valve, the second valve, the third valve, the sixth valve, the eighth valve, the eleventh valve, the twelfth valve, the seventeenth valve, the eighteenth valve and the twentieth valve are in an open state, and the fourth valve, the fifth valve, the seventh valve, the ninth valve, the tenth valve, the fourteenth valve, the fifteenth valve, the sixteenth valve, the nineteenth valve, the twenty first valve, the twenty second valve and the twenty third valve are in a closed state; the first, second and fourth inlets of the bus bar are in a closed state, and the third, fourth, first, second, third and fifth outlets of the bus bar are in an open state.
In terms of thermal management systems, the refrigeration capacity of the thermal management system is lower than the total demand. For the first liquid cooling circulation loop, a part of the heating value of the high-power equipment is taken away by the first heat exchanger and then is transmitted to the second heat exchanger through the hydraulic refrigerating device, and the residual heat is stored in the phase-change heat storage heat exchanger, and the Q High power equipment =Qhrq2+Qxbhrq; for the hydraulic refrigeration scheme, the hydraulic refrigeration device consumes hydraulic energy, and the heat exchanged by the first heat exchanger is completely transferred to the second heat exchanger and then taken away by a heat sink with higher temperature. Assuming that the efficiency of hydraulic refrigeration is η 9, the hydraulic energy P Hydraulic refrigerating device =Qhrq1/η9 is consumed. Supplementing the refrigerating capacity of Q hrq1=Qhrq2. For the second liquid cooling circulation loop, the heat stored by the phase change heat storage heat exchanger is transferred to the evaporation circulation loop through the evaporator, namely Q xbhrq=Qzfq. For the evaporative circulation loop, the heat of the evaporator is transferred to the condenser and then carried away by the heat sink, i.e., Q zfq=Qlnq. For the thermal management system, a hydraulic refrigeration scheme is adopted, so that the hydraulic energy of Q hrq1/η9 is consumed, and the refrigeration capacity of Q hrq1 is supplemented.
In the aspect of a power supply system, a hydraulic refrigeration scheme is adopted, so that the power supply quantity of the power supply system is not influenced.
In the aspect of a liquid supply system, a mechanical driving hydraulic pump converts mechanical energy generated by an auxiliary power device into hydraulic energy, hydraulic oil is pumped in from an oil tank and outputs high-pressure oil, a part of the high-pressure oil is filtered by oil to remove solid impurities, and then the pressure and the flow are regulated by a control valve to push an actuating mechanism of high-power equipment to do work. The other part of the high-pressure oil liquid passes through the liquid supply refrigerating device, consumes hydraulic energy, fully transfers the heat exchanged by the first heat exchanger to the second heat exchanger, and then is taken away by a heat sink with higher temperature. By adopting the hydraulic refrigeration scheme, the liquid supply system consumes Q hrq1/η9 hydraulic energy and supplements the hydraulic refrigeration quantity Q hrq1.
If Q hrq1≥Q High power equipment requirements -Qlnq is adopted, the supplementing refrigerating capacity can meet the refrigerating capacity requirement of the system, and the refrigerating capacity supplement can be realized by introducing a hydraulic refrigerating scheme. The first valve is fully opened, the size of Q xbhrq is unchanged and always the maximum value is achieved due to insufficient refrigerating capacity, the range (Q hrq1=Q High power equipment requirements -Qxbhrq) of the Q hrq1 can be adjusted by adjusting the opening of the second valve, namely the range can be flexibly adjusted and controlled between 0~Q High power equipment requirements -Qxbhrq, the supplementary refrigerating capacity can be flexibly adjusted and controlled, and the refrigerating capacity requirement is met at any moment. At this time, the liquid supply amount of the liquid supply system is equal to or greater than the total demand, and the hydraulic energy consumption is performed, so that P Hydraulic refrigerating device ≤P hydraulic pump hydraulic energy output -P High power device actuator requirements needs to be satisfied, that is, the hydraulic energy consumed by the hydraulic refrigerating device is not greater than the redundancy amount of the hydraulic energy of the system. If Q hrq1<Q High power equipment requirements -Qlnq, or P Hydraulic refrigerating device >P hydraulic pump hydraulic energy output -P High power device actuator requirements , the hydraulic refrigeration scheme is not capable of meeting both the refrigeration and liquid supply demands, and step ten needs to be continued.
Step ten: simultaneously adopting a thermoelectric power generation and electric refrigeration scheme, wherein the first valve, the second valve, the third valve, the fourth valve, the fifth valve, the sixth valve, the eighth valve, the ninth valve, the tenth valve, the fourteenth valve, the seventeenth valve and the eighteenth valve are in an open state, and the seventh valve, the eleventh valve, the twelfth valve, the fifteenth valve, the sixteenth valve, the nineteenth valve, the twentieth valve, the twenty first valve, the twenty second valve and the twenty third valve are in a closed state; the first inlet of the bus bar is in a closed state, and the second, third, fourth, first, second, third, fourth and fifth outlets of the bus bar are in an open state.
In terms of thermal management systems, the refrigeration capacity of the thermal management system is lower than the total demand. For the first liquid cooling circulation loop, a part of the heating value of the high-power equipment is taken away by the first heat exchanger and then is transmitted to the second heat exchanger through the electric refrigerating device, and the residual heat is stored in the phase-change heat storage heat exchanger, namely Q High power equipment =Qhrq2+Qxbhrq; for the electric refrigeration scheme, the electric refrigeration device consumes electric energy, and heat exchanged by the first heat exchanger is completely transferred to the second heat exchanger and then taken away by a heat sink with higher temperature. Assuming that the electric refrigeration efficiency is eta 8, the consumed electric energy W 4=Qhrq1/η8 supplements the refrigeration capacity of Q hrq1=Qhrq2. And for the second liquid cooling circulation loop, part of heat stored by the phase change heat storage heat exchanger is taken away by the third heat exchanger and then is recycled for power generation, and the residual heat is transmitted to the evaporation circulation loop through the evaporator, namely Q xbhrq=Qhrq3+Qzfq. For the thermoelectric power generation scheme, part of heat taken away by the third heat exchanger is recovered to generate power, and the rest is transmitted to the evaporation circulation loop through the fourth heat exchanger, namely Q hrq3=WB+Qhrq4. Assuming that the efficiency of thermoelectric generation is η 5, the thermoelectric generation amount W B=Qhrq3*η5 is the heat Q hrq4=Qhrq3-WB=Qhrq3(1-η5 taken away by the fourth heat exchanger). For the evaporation circulation loop, the heat of the evaporator and the fourth heat exchanger is transferred to the condenser and then taken away by the heat sink, namely Qlnq=Qzfq+Qhrq4=Qzfq+Qhrq3(1-η5)=Qxbhrq-Qhrq3*η5. for the hydraulic oil circulation loop, the heat exchange capacity of the hydraulic oil heat exchanger is equal to the refrigerating capacity requirement of the liquid supply system, namely Q Hydraulic oil heat exchanger =Q liquid supply system . In summary, for the thermal management system, an electric refrigeration scheme is adopted, so that Q hrq1/η8 electric energy is consumed, and the refrigeration capacity of Q hrq1 is supplemented; the refrigeration capacity of Q hrq3*η5 is supplemented by adopting a thermoelectric generation scheme.
In the aspect of a power supply system, a thermoelectric generation scheme is adopted, so that the thermoelectric generation capacity W B is supplemented, and the total power supply capacity is W B+WC+WD; by adopting the electric refrigeration scheme, the power supply W 4 of the electric refrigeration device is consumed, and the total demand is W 1+W2+W3+W4+W5.
In the aspect of the liquid supply system, an electric refrigeration scheme and a thermoelectric generation scheme are adopted, so that the liquid supply amount of the liquid supply system is not influenced.
If Q hrq1+Qhrq3*η5≥Q High power equipment requirements -Qlnq is adopted, the refrigeration capacity is supplemented by adopting the electric refrigeration and thermoelectric generation schemes at the same time, so that the system refrigeration capacity requirement can be met, and the refrigeration capacity supplement can be realized. The opening degree of the first valve and the opening degree of the second valve are adjusted, the ranges of Q hrq1 and Q xbhrq can be adjusted, and the electric refrigerating scheme can be flexibly regulated and controlled to supplement refrigerating capacity; and then the opening degree of the third valve and the opening degree of the fourth valve can be used for adjusting the range (Q hrq3+Qzfq=Qxbhrq) of the Q hrq3, and the temperature difference power generation scheme can be flexibly adjusted and controlled between 0~Q xbhrq, namely the cooling capacity can be flexibly adjusted and controlled to supplement the cooling capacity. At this time, the power supply amount of the power supply system is greater than or equal to the total demand, and the power consumption and the supplementation are performed at the same time, so that the requirement of W B-W4≤W1+W2+W3+W5-(WC+WD is satisfied, that is, the difference value between the power generated by the thermoelectric generation device and the power consumed by the electric refrigeration device is not greater than the redundancy amount of the system power. If Q hrq1+Qhrq3*η5<Q High power equipment requirements -Qlnq, or W B-W4>W1+W2+W3+W5-(WC+WD), the refrigeration capacity and power demand cannot be met simultaneously by both thermoelectric generation and electric refrigeration schemes, and the fuel tank capacity and flow rate need to be redesigned to increase the fuel flow rate by adjusting the seventh valve.
When the electric pump is used for supplying liquid, as shown in fig. 2, the power generation amount W C of the power generation system and the power supply amount W D of the energy storage device need to satisfy the power demand W 1 of the high-power device, the power demand W 2 of the first liquid pump, the power demand W 3 of the second liquid pump, the power demand W 5 of the electric motor, and the power demand W 6 of the electric motor. Compared with the method for feeding liquid by adopting a mechanical driving hydraulic pump, the electric energy requirement W 6 of the electric pump is increased, and other application schemes are consistent with the method for adopting the mechanical driving hydraulic pump.

Claims (10)

1. An electro-mechanical system for electro-hydraulic thermal complementation based on fuel, comprising: the system comprises a fuel tank, a ram air door, an electronic system, a fuel oil heat absorption subsystem, an electric refrigeration subsystem, a hydraulic refrigeration subsystem, a thermoelectric generation subsystem, a thermoelectric liquid supply subsystem, a hydraulic generation subsystem, a first liquid cooling circulation subsystem, a second liquid cooling circulation subsystem and an evaporation circulation subsystem; the fuel tank stores fuel; the power supply system comprises a fuel oil power generation device, an energy storage device and a bus bar; the electric refrigeration subsystem consumes electric energy to be converted into refrigerating capacity, the hydraulic refrigeration subsystem consumes hydraulic energy to be converted into refrigerating capacity, the temperature difference power generation subsystem recovers waste heat to be converted into electric energy, the temperature difference liquid supply subsystem recovers waste heat to be converted into hydraulic energy, and the hydraulic power generation subsystem consumes hydraulic energy to be converted into electric energy; the fuel in the fuel tank flows through the condenser to absorb heat of the condenser, then flows through the hydraulic oil heat exchanger to absorb heat of the hydraulic oil heat exchanger, and is used as a heat sink for heat management of the electrohydraulic heat complementary electromechanical system; the fuel oil with raised temperature after heat absorption is conveyed to an auxiliary power device to be mixed with air for combustion, high-temperature gas is generated to impact a turbine to rotate, the turbine drives a gear box, the gear box drives a generator to rotate to generate electric energy, high-power equipment on the aircraft is powered, the high-power equipment is used as an energy source for power supply of an electrohydraulic thermal complementary electromechanical system,
When the mechanical driving hydraulic pump is adopted for liquid supply, the gear box drives the mechanical driving hydraulic pump to work to generate hydraulic energy for supplying liquid for the high-power equipment executing mechanism, and the hydraulic energy is used as an energy source for supplying liquid for the electrohydraulic thermal complementary electromechanical system;
When the electric pump is used for supplying liquid, the electric energy generated by rotation of the generator simultaneously supplies power for the electric pump, the electric pump works to generate hydraulic energy for supplying liquid for the executing mechanism of the high-power equipment, and the hydraulic energy is used as an energy source for supplying liquid for the electro-hydraulic thermal complementary electromechanical system.
2. The electro-mechanical system for electrohydraulic thermal complementation based on fuel of claim 1 wherein said first liquid cooled recirculation subsystem includes: the device comprises a high heat flux cooling device, a first liquid pump and a first liquid storage tank; the high-power equipment produces heat in the working process, heat transfer is for high heat flux density cooling device, first secondary refrigerant in the first liquid storage tank is passed through first liquid pump carries to high heat flux density cooling device, first secondary refrigerant absorbs the heat that high-power equipment produced back temperature rise, first secondary refrigerant is taken away partial heat after the heat exchanger and is reduced in temperature, first secondary refrigerant is taken away surplus heat through the phase change heat storage heat exchanger, get back to first liquid storage tank, first liquid cooling circulation subsystem accomplishes first liquid cooling circulation loop.
3. The electro-mechanical system for electro-hydraulic thermal complementation based on fuel of claim 2, wherein said second liquid cooled circulation subsystem comprises: the phase change heat storage heat exchanger, the second liquid pump and the second liquid storage tank; the second refrigerating medium in the second liquid storage tank is conveyed to the phase-change heat storage heat exchanger through a second liquid pump, the temperature of the second refrigerating medium rises after absorbing heat stored by the phase-change heat storage heat exchanger, the temperature of the second refrigerating medium decreases after being taken away by part of heat through a third heat exchanger, the second refrigerating medium is taken away by the rest heat through an evaporator and returns to the second liquid storage tank, and the second liquid cooling circulation subsystem completes a second liquid cooling circulation loop.
4. An electro-mechanical system for electro-hydraulic thermal complementation based on fuel according to claim 3, wherein said evaporation cycle subsystem comprises: evaporator, throttle valve, condenser and compressor; the liquid refrigerant in the evaporator absorbs heat transferred to the evaporator by the second liquid cooling circulation subsystem and evaporates to become gaseous refrigerant, the gaseous refrigerant enters the compressor and is compressed to be high-pressure gas, the high-pressure gaseous refrigerant enters the condenser to emit heat to become liquid refrigerant, the liquid refrigerant enters the throttle valve and throttles and expands to be low-pressure liquid, and the evaporation circulation subsystem completes an evaporation circulation loop.
5. An electro-mechanical system for electrohydraulic thermal complementation based on fuel of claim 4 wherein said electric refrigeration subsystem includes an electric refrigeration unit and said hydraulic refrigeration subsystem includes a hydraulic refrigeration unit; the electric refrigerating device consumes electric energy and transfers heat from a first heat exchanger with lower temperature to a second heat exchanger with higher temperature; the hydraulic refrigeration device consumes hydraulic energy and transfers heat from a first heat exchanger with a lower temperature to a second heat exchanger with a higher temperature.
6. The electro-mechanical system for electrohydraulic thermal complementation based on fuel of claim 5 wherein said thermoelectric generation subsystem includes a thermoelectric generation device and said thermoelectric liquid supply subsystem includes a thermoelectric liquid supply device; the thermoelectric generation device converts heat energy into electric energy through thermoelectric generation by utilizing the temperature difference between the third heat exchanger and the fourth heat exchanger, and transmits the electric energy to the busbar inlet; the temperature difference liquid supply device converts heat energy into hydraulic energy through temperature difference liquid supply by utilizing the temperature difference between the third heat exchanger and the fourth heat exchanger, and the hydraulic energy is conveyed to the high-power equipment executing mechanism.
7. The electro-mechanical system for electrohydraulic thermal complementation based on fuel oil according to claim 6, wherein the electro-thermal complementation system using fuel oil as a power source and a heat sink comprises twenty-three valves, a first valve is arranged between the high heat flux cooling device and the phase-change heat storage heat exchanger, a second valve is arranged between the high heat flux cooling device and the first heat exchanger, a third valve is arranged between the phase-change heat storage heat exchanger and the evaporator, a fourth valve is arranged between the phase-change heat storage heat exchanger and the third heat exchanger, a fifth valve is arranged between the throttle valve and the fourth heat exchanger, a sixth valve is arranged between the throttle valve and the evaporator, a seventh valve is arranged between the fuel tank and the condenser, an eighth valve is arranged between the fuel tank and the auxiliary power device, a ninth valve is arranged between the first heat exchanger and the electric refrigerating device, a tenth valve is arranged between the electric refrigerating device and the second heat exchanger, an eleventh valve is arranged between the first heat exchanger and the hydraulic refrigerating device, a twelfth valve is arranged between the hydraulic refrigerating device and the second heat exchanger, a thirteenth valve is arranged between the third heat exchanger and the thermoelectric generation device, a fourteenth valve is arranged between the thermoelectric generation device and the fourth heat exchanger, a fifteenth valve is arranged between the third heat exchanger and the thermoelectric liquid supply device, a sixteenth valve is arranged between the thermoelectric liquid supply device and the fourth heat exchanger, a seventeenth valve is arranged between a condenser when ram air is used as a heat sink and a hydraulic oil heat exchanger, an eighteenth valve is arranged between the condenser when ram air is used as the heat sink and the second heat exchanger, a nineteenth valve is arranged between the condenser when fuel oil is used as the heat sink and the second heat exchanger, a twentieth valve is arranged between the hydraulic refrigerating device and the hydraulic pump, a second eleventh valve is arranged between the thermoelectric liquid supply device and the oil filter, the twenty-second valve is arranged between the pressure accumulator and the hydraulic motor, and the twenty-third valve is arranged between the hydraulic heat exchanger and the external environment.
8. The electro-mechanical system for electrohydraulic thermal complementation based on fuel of claim 7, wherein said bus bar includes four inlets and five outlets, a first inlet connected to a first generator, a second inlet connected to said thermoelectric generator, a third inlet connected to a second generator, a fourth inlet connected to said energy storage device, a first outlet connected to said high power device, a second outlet connected to said first fluid pump, a third outlet connected to said second fluid pump, a fourth outlet connected to said electric refrigeration device, and a fifth outlet connected to said compressor.
9. The electro-mechanical system for electro-hydraulic thermal complementation based on fuel of claim 8, wherein when the electro-hydraulic thermal complementation system using fuel as an energy source and a heat sink is used for absorbing heat of fuel alone, the first valve, the third valve, the sixth valve, the seventh valve, the eighth valve and the seventeenth valve are in an open state, and the second valve, the fourth valve, the fifth valve, the ninth valve, the tenth valve, the eleventh valve, the twelfth valve, the tenth valve, the fourteenth valve, the fifteenth valve, the sixteenth valve, the eighteenth valve, the nineteenth valve, the twentieth valve, the twenty first valve, the twenty second valve and the twenty third valve are in a closed state; the first, second and fourth inlets of the bus bar are in a closed state, and the third, fourth, first, second, third and fifth outlets of the bus bar are in an open state.
10. The electro-mechanical system for electro-hydraulic thermal complementation based on fuel according to claim 9, wherein when the electro-hydraulic thermal complementation system using fuel as an energy source and a heat sink is used for thermoelectric generation alone, the first valve, the third valve, the fourth valve, the fifth valve, the sixth valve, the eighth valve, the tenth valve, the fourteenth valve and the seventeenth valve are in an open state, and the second valve, the seventh valve, the ninth valve, the tenth valve, the eleventh valve, the twelfth valve, the fifteenth valve, the sixteenth valve, the eighteenth valve, the nineteenth valve, the twentieth valve, the twenty first valve, the twenty second valve and the twenty third valve are in a closed state; the first inlet, the fourth outlet of the bus bar are in a closed state, and the second inlet, the third inlet, the fourth inlet, the first outlet, the second outlet, the third outlet and the fifth outlet of the bus bar are in an open state.
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GB201420343D0 (en) * 2014-11-17 2014-12-31 Demetair Systems A waste heat recovery system combined with compressed air energy storage
CN117360779A (en) * 2023-12-08 2024-01-09 中国航空工业集团公司金城南京机电液压工程研究中心 Electric heating complementary system with fuel oil as power source and heat sink

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