WO2020164255A1 - 换能方法和系统 - Google Patents

换能方法和系统 Download PDF

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Publication number
WO2020164255A1
WO2020164255A1 PCT/CN2019/112923 CN2019112923W WO2020164255A1 WO 2020164255 A1 WO2020164255 A1 WO 2020164255A1 CN 2019112923 W CN2019112923 W CN 2019112923W WO 2020164255 A1 WO2020164255 A1 WO 2020164255A1
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Prior art keywords
working fluid
fluid
storage tank
heat pump
fluid storage
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PCT/CN2019/112923
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English (en)
French (fr)
Inventor
孙诚刚
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Individual
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Individual
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Priority to US17/430,526 priority Critical patent/US20220341635A1/en
Priority to CA3133850A priority patent/CA3133850A1/en
Priority to CN201980091821.1A priority patent/CN113474599A/zh
Priority to KR1020217029416A priority patent/KR20210126100A/ko
Priority to JP2021547318A priority patent/JP2022520595A/ja
Priority to EP19914852.9A priority patent/EP3926257A4/en
Publication of WO2020164255A1 publication Critical patent/WO2020164255A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K13/00—General layout or general methods of operation of complete plants
    • 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
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K17/00—Using steam or condensate extracted or exhausted from steam engine plant
    • F01K17/02—Using steam or condensate extracted or exhausted from steam engine plant for heating purposes, e.g. industrial, domestic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
    • F01K25/08—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours
    • F01K25/10—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours the vapours being cold, e.g. ammonia, carbon dioxide, ether
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K27/00—Plants for converting heat or fluid energy into mechanical energy, not otherwise provided for
    • F01K27/02—Plants modified to use their waste heat, other than that of exhaust, e.g. engine-friction heat
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K3/00—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein
    • F01K3/08—Use of accumulators and the plant being specially adapted for a specific use
    • 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
    • F25B27/00—Machines, plants or systems, using particular sources of energy
    • F25B27/02—Machines, plants or systems, using particular sources of energy using waste heat, e.g. from internal-combustion engines
    • 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
    • F25B30/00—Heat pumps
    • F25B30/02—Heat pumps of the compression type
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/041—Details of condensers of evaporative condensers
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers
    • 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
    • F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02A—TECHNOLOGIES FOR ADAPTATION TO CLIMATE CHANGE
    • Y02A30/00—Adapting or protecting infrastructure or their operation
    • Y02A30/27—Relating to heating, ventilation or air conditioning [HVAC] technologies
    • Y02A30/274—Relating to heating, ventilation or air conditioning [HVAC] technologies using waste energy, e.g. from internal combustion engine

Definitions

  • the present invention relates to the technical field of energy conversion and energy storage, in particular to an energy conversion method and an energy conversion system, which can amplify and output the input electric energy for driving external equipment, such as driving a generator to generate electricity; in particular, also It relates to a distributed energy conversion method and a distributed energy conversion system, which can store the input electrical energy and amplify the output for driving external equipment, such as driving a generator to generate electricity.
  • the existing energy storage methods include pumped water storage, flywheel energy storage, chemical battery energy storage, compressed air energy storage, etc.
  • the energy efficiency ratios of the above methods are low and generally Will not exceed 0.8, and the investment required is large.
  • some of the heat and cold energy that can be reused are also discharged as waste heat from the system, resulting in energy waste and lower energy efficiency ratio.
  • the present invention proposes a distributed energy conversion method and system to overcome the above-mentioned problems, which are used to solve the disadvantages of low energy conversion efficiency, high investment, and actual implementation affected by terrain or geographic location in the prior art. Moreover, it can easily realize the conversion and storage of valley electricity in the time period when the power consumption of the grid is low, and then use the stored energy to supplement the power generation of the grid when the power consumption of the grid is large, and realize the efficient storage and delayed output of energy. And the overall energy efficiency ratio is significantly improved.
  • a distributed energy conversion method which includes:
  • the heated second fluid is used to heat the input pressure working fluid of the pneumatic engine to vaporize it into a pressure working fluid gas for actuating the pneumatic engine, and to heat the input pressure working fluid to reduce the temperature.
  • the fluid is reheated by the working fluid of the heat pump for reheating the input pressure working fluid of the pneumatic engine, so that the second fluid is cyclically heated and cooled;
  • the refrigerated first fluid is used to condense the output pressure working fluid gas of the pneumatic engine, and the output pressure working fluid gas of the pneumatic engine is condensed, and the heated first fluid is re-absorbed by heat by the working fluid of the heat pump to be cooled It is used to condense the working fluid gas of the output pressure of the pneumatic machine again, so that the first fluid is circulated for cooling and heating.
  • using the working fluid of the heat pump to absorb heat from the first fluid circulating in the first circulation circuit to cool the first fluid may include: using the working fluid of the heat pump to obtain the first fluid from the first fluid storage tank. The fluid absorbs heat to cool the first fluid, and the cooled first fluid is transported to the second fluid storage tank;
  • Using a heat pump to compress the working fluid after absorbing heat to further increase the temperature of the working fluid, for heating the second fluid circulating in the second circulation loop may include: the heat pump compresses the working fluid after absorbing heat to Further increasing the temperature of the working fluid is used to heat the second fluid from the third fluid storage tank, and the heated second fluid is transported to the fourth fluid storage tank;
  • Delivering the heated second fluid for heating the input pressure working fluid of the pneumatic machine to vaporize it into pressure working fluid gas for actuating the pneumatic machine may include: a heated second fluid from a fourth fluid storage tank The fluid is transported to heat the input pressure working fluid of the pneumatic machine to vaporize it into a pressure working fluid gas for actuating the pneumatic machine, and the second fluid heated to the input pressure working fluid is transported back to the third fluid storage. tank;
  • Delivering the refrigerated first fluid for condensing the output pressure working fluid gas of the pneumatic machine (J) may include: the refrigerated first fluid from the second fluid storage tank is transported for the purpose of condensing the output pressure of the pneumatic machine (J) The mass gas is condensed and then returned to the first fluid storage tank.
  • the refrigerated first fluid from the second fluid storage tank is conveyed for condensing the output pressure working fluid gas of the pneumatic engine, which may include: making the refrigerated first fluid from the second fluid storage tank The fluid flows through the first condenser, so as to condense the output pressure working medium gas of the pneumatic engine flowing into the first condenser to obtain the pressure working medium liquid, and the pressure working medium liquid returns to the steam generator as the input pressure working medium of the pneumatic engine ;
  • the heated second fluid from the fourth fluid storage tank is used to heat the input pressure working fluid of the pneumatic engine in the steam generator to vaporize it into a pressure working fluid gas when flowing through the steam generator. Pneumatic machine.
  • using the working fluid of the heat pump to absorb heat from the first fluid from the first fluid storage tank to cool the first fluid may include: flowing the working fluid of the heat pump through the evaporator, from flowing into the evaporator , The first fluid from the first fluid storage tank absorbs heat and evaporates, thereby cooling the first fluid;
  • the compressed working fluid of the heat pump flows into the second condenser to heat and condense the second fluid flowing into the second condenser from the third fluid storage tank, and then is transported and returned to the evaporator.
  • the method may further include:
  • the working fluid storage tank When the liquid level in the working fluid storage tank is higher than the predetermined first threshold, the working fluid storage tank is disconnected from the first condenser and connected to the steam generator, so that the working fluid storage tank can be condensed The resulting pressure working fluid is returned to the steam generator.
  • the method may further include:
  • the working fluid storage tank When the liquid level in the working fluid storage tank is lower than the predetermined second threshold, the working fluid storage tank is disconnected from the steam generator and reconnected with the first condenser, so that the condensed working fluid can flow into the working fluid.
  • the method may further include: when the working fluid storage tank is reconnected with the first condenser, using the pressure difference between the working fluid storage tank and the first condenser to drive the pneumatic generator to generate electricity ,
  • the generated electricity is preferably used for auxiliary heating of the second fluid in the fourth fluid storage tank.
  • the heat pump may include an electric motor and a compressor driven by the electric motor, and the method may further include: using at least a part of the second fluid from the third fluid storage tank to water-cool the electric motor, and deliver it after the water cooling Return to the fourth fluid storage tank;
  • the pneumatic machine is connected to the generator to drive the generator, and the method may further include: using at least a portion of the second fluid from the third fluid storage tank to water-cool the generator, and transfer it back to the fourth fluid storage tank after the water cooling. In the jar.
  • the secondary condenser is preferably adiabatic.
  • other components in the entire system, such as pipes, valves, etc., are also preferably insulated.
  • the first fluid may be brine, and the temperature of the first fluid heated by condensing the output pressure of the pneumatic engine gas, or the first fluid stored in the first fluid storage tank is preferably 0°C To 20°C, more preferably 0°C to 12°C, more preferably 12°C; the temperature of the first fluid heated by the working fluid of the heat pump or the first fluid stored in the second fluid storage tank is preferably -20 °C to 0 °C, more preferably -12 °C to 0 °C, more preferably -12 °C; and/or,
  • the second fluid may be water.
  • the temperature of the second fluid after heating and cooling the input pressure working fluid, or the second fluid stored in the third fluid storage tank is preferably 30°C to 50°C, more preferably 35°C
  • the temperature of the second fluid heated by the working fluid of the heat pump or the second fluid stored in the fourth fluid storage tank is preferably 90°C to 60°C, more preferably 40°C; To 65°C, more preferably 75°C; and/or,
  • the working medium of the heat pump can be CO 2
  • the pressure working medium of the pneumatic machine can be ammonia
  • a distributed energy conversion system which includes: a heat pump, a pneumatic engine, a first circulation loop for circulating a first fluid therein, and a The second circulation loop that circulates, where,
  • the heat pump is used to use its working fluid to absorb heat from the first fluid to cool the first fluid, and to compress the working fluid after absorbing heat to further increase the temperature of the working fluid, and to use its working fluid to cool the second fluid.
  • the fluid is heated;
  • the heated second fluid is used to heat the input pressure working fluid of the pneumatic machine to vaporize it into a pressure working fluid gas, which is used to actuate the pneumatic machine and heat the input pressure working fluid to reduce the temperature.
  • the working fluid of the heat pump is reheated for reheating the input pressure working fluid of the pneumatic engine, so that the second fluid is heated and cooled by circulation;
  • the refrigerated first fluid is used to condense the output pressure working fluid gas of the pneumatic engine, and to condense the output pressure working fluid gas of the pneumatic engine, and the heated first fluid is re-absorbed by the heat pump working fluid to cool down. It is used to condense the output pressure working fluid gas of the pneumatic engine again, so that the first fluid is circulated for cooling and heating.
  • the system may further include: a first fluid storage tank, a second fluid storage tank, a third fluid storage tank, and a fourth fluid storage tank, wherein the first fluid storage tank and the second fluid storage tank are located in the first fluid storage tank.
  • a circulation loop is used to store the first fluid, the third fluid storage tank and the fourth fluid storage tank are located in the second circulation loop to store the second fluid, and wherein:
  • the first fluid storage tank is used to store the first fluid that is heated by condensing the output pressure of the pneumatic engine gas
  • the heat pump is used to absorb heat from the first fluid from the first fluid storage tank with its working fluid.
  • the second fluid storage tank is used to store the refrigerated first fluid;
  • the third fluid storage tank is used to store the second fluid after heating and cooling the input pressure working fluid of the pneumatic engine, wherein the heat pump is used to heat the second fluid from the third fluid storage tank by using its working fluid, and the first The four-fluid storage tank is used to store the heated second fluid.
  • the system may further include a first condenser and a steam generator, wherein,
  • the first condenser is used to: when the refrigerated first fluid from the second fluid storage tank flows through the first condenser, it will condense the working fluid gas flowing into the first condenser and the output pressure of the pneumatic engine to obtain a pressure working fluid.
  • the pressure working fluid is returned to the steam generator as the input pressure working fluid of the pneumatic engine; the steam generator is used to: cause the heated second fluid from the fourth fluid storage tank to generate steam when flowing through the steam generator
  • the input pressure working medium of the pneumatic machine in the device is heated to vaporize into pressure working medium gas to activate the pneumatic machine.
  • the system may further include an evaporator and a second condenser, wherein,
  • the evaporator is used to make the working fluid of the heat pump absorb heat from the first fluid flowing into the evaporator and from the first fluid storage tank when flowing through the evaporator to evaporate, thereby cooling the first fluid;
  • the second condenser is used for : Make the compressed working fluid of the heat pump heat and condense the second fluid flowing into the second condenser from the third fluid storage tank when it flows through the second condenser, and then transport and return to the evaporator after heating .
  • the system may further include a working fluid storage tank, which is located at a lower position than the first condenser and is in fluid communication with the first condenser through the first valve, and generates steam through the second valve. Fluid communication,
  • the second valve when the first valve is in the open state, the second valve is in the closed state, so that the first condenser is in communication with the working fluid storage tank, while keeping the working fluid storage tank disconnected from the steam generator, so that the condensation is obtained
  • the pressure working fluid can flow into the working fluid storage tank by gravity
  • the first valve becomes closed and the second valve becomes open, so that the working fluid storage tank is disconnected from the first condenser. It is connected with the steam generator, so that the pressure working fluid in the working fluid storage tank can be returned to the steam generator.
  • the first valve when the liquid level in the working fluid storage tank is lower than the predetermined second threshold, the first valve becomes open and the second valve becomes closed, so that the working fluid storage tank is disconnected from the steam generator.
  • the communication is opened to reconnect with the first condenser, so that the pressure working fluid liquid obtained by condensation in the first condenser can flow into the working fluid storage tank, wherein the predetermined second threshold is lower than the predetermined first threshold.
  • first valve and the second valve may be electric valves.
  • the working fluid storage tank may also be in fluid communication with the first condenser through a third pipeline different from the first pipeline where the first valve is located, and the third pipeline includes a third pipeline connected in series.
  • Valves and pneumatic generators are also be in fluid communication with the first condenser through a third pipeline different from the first pipeline where the first valve is located, and the third pipeline includes a third pipeline connected in series.
  • the working fluid storage tank is also in fluid communication with the steam generator through a fourth pipeline that is different from the second pipeline where the second valve is located.
  • the fourth pipeline contains a fourth valve and a gas storage tank connected in series. The tank is connected between the steam generator and the fourth valve and is used to store vaporized pressure working fluid gas,
  • the third valve changes from an open state to a closed state, and the fourth valve changes from a closed state to an open state, considering that the first valve becomes closed at this time And the second valve becomes an open state, so that the working fluid storage tank is disconnected from the first condenser to communicate with the steam generator, so that the pressure working fluid in the working fluid storage tank can be returned to the steam generator;
  • the third valve changes from a closed state to an open state and the fourth valve changes from an open state to a closed state, thereby utilizing the internal and the first
  • the pressure difference between the inside of a condenser drives a pneumatic generator to generate electricity.
  • the generated electricity is preferably used to assist heating of the second fluid in the fourth fluid storage tank, and is connected to the first condenser inside the working fluid storage tank.
  • the first valve changes from a closed state to an open state.
  • the first valve and the second valve may be one-way valves, and the third valve and the fourth valve may be electric valves.
  • the heat pump may include an electric motor and a compressor driven by the electric motor, and at least a part of the second fluid from the third fluid storage tank is used for water-cooling the electric motor and returns to the fourth fluid storage tank after the water cooling; and /Or, the pneumatic machine is connected with the generator to drive the generator, and at least a part of the second fluid from the third fluid storage tank is used for water cooling of the generator, and returns to the fourth fluid storage tank after the water cooling.
  • the second condenser can be insulated.
  • other components in the entire system, such as pipes, valves, etc., are also preferably insulated.
  • the first fluid may be brine, and the temperature of the first fluid heated by condensing the output pressure of the pneumatic engine gas, or the first fluid stored in the first fluid storage tank is preferably 0°C To 20°C, more preferably 0°C to 12°C, more preferably 12°C; the temperature of the first fluid cooled by absorbing heat by the working fluid of the heat pump or the first fluid stored in the second fluid storage tank is preferably -20°C to 0°C, more preferably -12°C to 0°C, more preferably -12°C; and/or,
  • the second fluid may be water.
  • the temperature of the second fluid after heating and cooling the input pressure working fluid, or the second fluid stored in the third fluid storage tank is preferably 30°C to 50°C, more preferably 35°C
  • the temperature of the second fluid heated by the working fluid of the heat pump or the second fluid stored in the fourth fluid storage tank is preferably 90°C to 60°C, more preferably 40°C; To 65°C, more preferably 75°C; and/or,
  • the working medium of the heat pump can be CO 2
  • the pressure working medium of the pneumatic machine can be ammonia
  • the heat pump is used to heat the second fluid while cooling the first fluid, and the cooled first fluid is used for the output pressure of the pneumatic engine.
  • the gas is condensed and the exhaust pressure of the pneumatic machine is reduced.
  • the heated second fluid is used to heat the input pressure of the pneumatic machine and vaporize it to increase the pressure of the input pressure of the pneumatic machine, thereby greatly increasing The pressure difference between the working medium input end and the working medium output end of the pneumatic machine, thereby increasing the power of the pneumatic machine and increasing power generation.
  • the first fluid circulates in one circulation loop, and the second fluid circulates in another circulation loop, which will not discharge energy to the outside of the overall energy conversion system, thereby avoiding energy loss and improving the energy efficiency of the overall system ratio.
  • the first fluid condenses the output pressure working fluid gas of the pneumatic engine, it is also a process in which the first fluid absorbs the heat in the output pressure working fluid gas for energy storage.
  • the stored heat energy can be used for the working fluid absorption of the heat pump. Heat, thereby avoiding energy loss in the system.
  • the heat pump heats the second fluid for subsequent heating and vaporization of the input pressure working fluid of the pneumatic engine, and at the same time cools the first fluid for subsequent use
  • the output pressure of the pneumatic engine is condensed, so the heat pump uses both the sensible heat of the second fluid and the latent heat of the first fluid.
  • the waste heat carried in the exhaust steam after the work of the pneumatic engine's pressure working medium is also recovered by the refrigerated first fluid so that the subsequent heat pump working medium absorbs heat, so that the pneumatic engine's " "Waste heat” has also been reused.
  • the waste heat generated by the electric motor in the heat pump and the generator driven by the pneumatic machine can be water-cooled by the second fluid from the third fluid storage tank and then recycled into the fourth fluid storage tank for subsequent use.
  • the distributed energy conversion method and system of the present invention can be used to drive external equipment, such as driving a generator for power generation, so as to realize a distributed energy storage power generation method and system, which can significantly improve the energy efficiency ratio, thereby improving power generation efficiency, and through more
  • a fluid storage tank is used for energy storage, which can store the valley electricity in the grid at night, and then use the energy stored at night to generate electricity when the demand for electricity is large during the day, and significantly increase the output power.
  • the working fluid of the heat pump and the working fluid of the pneumatic machine directly exchange heat , Then obtain an energy conversion method and energy conversion system, which can realize the instantaneous amplification output of the input energy.
  • an energy conversion method including:
  • the working medium of the heat pump is used to absorb the heat of the output pressure working medium gas from the pneumatic machine to condense the output pressure working medium gas of the pneumatic machine to obtain the pressure working medium liquid, and the pressure working medium liquid is transported as the pneumatic machine Input pressure working fluid;
  • the heat pump is used to compress the working fluid after absorbing heat to raise the temperature of the working fluid so that the heat can be transferred to the input pressure working fluid of the pneumatic machine to be heated and vaporized into a pressure working fluid gas. After actuating the pneumatic machine, the pneumatic machine outputs the working fluid gas as the output pressure of the pneumatic machine;
  • the working fluid of the heat pump after the heat is transferred to the input pressure working fluid and the temperature is reduced is transported to absorb heat again from the output pressure working fluid gas of the pneumatic engine, so that the working fluid of the heat pump circulates for the suction Heat, warm up and cool down.
  • an energy conversion system which includes a heat pump, a pneumatic engine, a first evaporative condenser, and a second evaporative condenser, wherein the heat pump is connected to the first evaporative condenser through a pipeline, respectively And the second evaporative condenser is in fluid communication, and the first evaporative condenser is in fluid communication with the second evaporative condenser through the first pipeline, so that the working fluid of the heat pump can pass through the first evaporative condenser, the first pipeline, and The second evaporative condenser circulates; and the pneumatic machine is in fluid communication with the first evaporative condenser and the second evaporative condenser through pipelines, and the first evaporative condenser and the second evaporative condenser also pass through the The two pipelines are in fluid communication, so that the pressure working fluid of the pneumatic machine can circulate through the first e
  • the working medium of the heat pump is used to absorb heat from the output pressure working medium gas of the pneumatic machine in the first evaporative condenser to condense the output pressure working medium gas of the pneumatic machine to obtain the pressure working medium liquid, and the pressure
  • the working fluid is transported as the input pressure working fluid of the pneumatic machine;
  • the heat pump is used to compress the working fluid after absorbing heat to raise the temperature of the working fluid so as to heat the input pressure working fluid of the pneumatic engine in the second evaporative condenser to vaporize it into a pressure working fluid gas ,
  • the pressure working medium gas is used to actuate the pneumatic machine and then output by the pneumatic machine as the output pressure working medium gas of the pneumatic machine;
  • the working fluid of the heat pump after heating the input pressure working fluid in the second evaporative condenser and cooling down is used to transport to the first evaporative condenser and absorb again from the output pressure working fluid gas of the pneumatic engine Heat, so that the working fluid of the heat pump circulates to absorb heat, increase temperature, and decrease temperature.
  • Fig. 1 is a schematic diagram of a distributed energy conversion system according to an embodiment of the present invention
  • Fig. 2 is a partial schematic diagram of a distributed energy conversion system according to an embodiment of the present invention.
  • Fig. 3 is a schematic diagram of a distributed energy conversion method according to an embodiment of the present invention.
  • Figure 4 is a schematic diagram of an energy conversion system according to a variant embodiment of the present invention.
  • FIG. 5 is a schematic diagram of an energy conversion method according to another modified embodiment of the present invention.
  • Fig. 6 is a schematic diagram of an energy conversion system according to another modified embodiment of the present invention.
  • Fig. 1 is a schematic diagram of a distributed energy conversion system according to an embodiment of the present invention.
  • the distributed energy conversion system according to an embodiment of the present invention includes: a heat pump I, a pneumatic engine J, a circulation loop for circulating salt water therein, and a circulation loop for circulating water supply therein. ,among them,
  • the heat pump I is used to use its working fluid to absorb heat from the brine in the circulation loop to cool the brine, and to compress the heat-absorbed working fluid to further increase the temperature of the working fluid.
  • the water in a circulation loop is heated; in FIG. 1, the heat pump I includes, for example, an electric motor 8 and a compressor connected to the electric motor 8, and includes a working fluid pipeline connected to the compressor and a working fluid in the pipeline.
  • the heated water is used to heat the input pressure working medium of the pneumatic machine J to vaporize it into a pressure working medium gas for actuating the pneumatic machine J, and heat the input pressure working medium, and the cooled water is used by the heat pump
  • the working fluid of I is reheated for reheating the input pressure working fluid of the pneumatic machine J, so that the water is cyclically heated and cooled in the other circulation loop;
  • the refrigerated brine is used to condense the output pressure working medium gas of the pneumatic machine J, and condense the output pressure working medium gas of the pneumatic machine J, and the heated salt water is re-absorbed by the working medium of the heat pump I to be cooled for use. Yu condenses the output pressure of the pneumatic engine J again, so that the brine is circulated for cooling and heating in the circulation loop.
  • the circulation loop is used to circulate the brine and water in one direction, so that the brine is circulated for cooling and heating when circulating in the circulation loop, and the water is cyclically heated and cooled when circulating in the circulation loop.
  • These circulation loops can be designed according to needs, using various pipelines, valves, pumping devices, evaporators, condensers, steam generators, etc., according to needs, the circulation loops can also include temporary storage of brine and water respectively Fluid storage tank. Therefore, there is no particular limitation on the specific implementation of the circulation loop in the present invention, as long as it can circulate the brine and water therein so as to be refrigerated and heated by the circulation.
  • the condenser C in the distributed energy conversion system is used to make the refrigerated brine from the fluid storage tank E face the pneumatic motor J in the shell side of the condenser C when it flows through the tube side of the condenser C.
  • the output pressure working fluid gas (such as ammonia) is condensed to obtain a pressure working fluid liquid (ie liquid ammonia), which returns to the steam generator D as the input pressure working fluid (ie liquid ammonia) of the pneumatic engine J; steam
  • the generator D is used to: make the heated water from the fluid storage tank F flow through the tube pass of the steam generator D to heat the input pressure working medium of the pneumatic engine J in the shell pass of the steam generator D. It vaporizes into a pressure working medium gas to actuate the pneumatic engine J.
  • the distributed energy conversion system may also include an evaporator A and a condenser B.
  • the evaporator A is used to: make the working fluid of the heat pump I flow into the tube pass of the evaporator A when it flows through the shell pass of the evaporator A ,
  • the brine from the fluid storage tank G absorbs heat and evaporates, thereby cooling the brine;
  • the condenser B is used to: make the compressed working fluid of the heat pump I flow into the condenser B when passing through the shell side of the condenser B
  • the water in the pipe pass from the fluid storage tank H releases heat and condenses, and is transported and returned to the evaporator A after releasing the heat.
  • the heat pump I is used to cool the brine while heating the water, and the cooled brine is used to condense the output pressure of the pneumatic engine J to reduce the exhaust of the pneumatic engine J.
  • the heated water is used to heat and vaporize the input pressure of the pneumatic engine J to increase the pressure of the input pressure of the pneumatic engine J, thereby greatly increasing the input end of the pneumatic engine J.
  • the pressure difference between the output ends of the working medium that is, between the input pressure working medium gas of the pneumatic engine J and the output pressure working medium gas, that is, the output exhaust steam), thereby increasing the output power of the pneumatic engine J and increasing power generation.
  • the brine circulates in one circulation loop, and the water circulates in another circulation loop, so that energy will not be discharged to the outside of the overall energy conversion system, thereby avoiding energy loss and improving the energy efficiency ratio of the overall system.
  • the brine condenses the output pressure working fluid gas of the pneumatic engine J, it is also a process in which the salt water absorbs the heat in the output pressure working fluid gas to store energy.
  • the stored heat energy can be used for the heat absorption of the working fluid of the heat pump.
  • the "waste heat" generated when the heat pump I cools the brine is used by the heat pump I to heat the water, and there is no waste heat in the entire system.
  • the circulation circuit for the brine can be composed of the evaporator A, the fluid storage tank E, the condenser C, and the fluid storage tank G connected by pipes in sequence, and the fluid storage tank G and the evaporator A also pass through the pipes.
  • the pipeline is connected to form a closed circulation loop.
  • a pumping device (for example, water pump 4) is set in the pipeline to drive the brine to circulate in the circulation loop.
  • the pipe between the evaporator A and the fluid storage tank E A water pump 4 is provided on the road to transport the cooled brine in the evaporator A to the fluid storage tank E for storage; for example, a water pump 4 can be provided on the pipeline between the fluid storage tank E and the condenser C to remove The brine in the fluid storage tank E is transported to the condenser C; for example, a water pump can also be provided on the pipeline between the fluid storage tank G and the evaporator A to transport the brine from the fluid storage tank G to the evaporator A .
  • the present invention has no limitation on this, and a water pump can be installed in the designated pipeline according to actual needs.
  • the circulation circuit for water can be composed of condenser B, fluid storage tank F, steam generator D, and fluid storage tank H connected in sequence by pipelines, and fluid storage tank H and condenser B are also connected by pipelines Therefore, a closed circulation loop is formed, and a pumping device (for example, the water pump 4) is set at a required position in the pipeline to drive the water to circulate in the circulation loop.
  • a water pump 4 can be provided on the pipeline between the condenser B and the fluid storage tank F to transfer the heated water in the condenser B to the fluid storage tank F for storage; for example, it can be stored in the fluid storage tank F and steam.
  • a water pump 4 is provided on the pipeline between the generator D to deliver the water from the fluid storage tank F to the steam generator D; for example, it can also be provided on the pipeline between the fluid storage tank H and the condenser B
  • the water pump is used to transport water from the fluid storage tank H to the condenser B.
  • the present invention has no limitation on this, and a water pump can be installed in the designated pipeline according to actual needs.
  • salt water is used as the circulating fluid in one of the circulation loops
  • water i.e., ordinary fresh water
  • the present invention is not limited to the use of salt water and water as the circulating fluid.
  • other fluids can also be used, such as other types of liquids or even gases, as long as they can be maintained in a fluid state at the required operating temperature to facilitate circulation, so as to be compatible with the working fluid of the heat pump and the pressure of the pneumatic machine
  • the working fluid can be used for heat exchange at the specified temperature.
  • Those skilled in the art can determine the fluid suitable for circulating in the above-mentioned circulation loop according to the type, pressure, working temperature, etc.
  • salt water it refers to ordinary fresh water with a freezing point of 0°C.
  • the fluid storage tank G and the fluid storage tank E are respectively used for storing salt water at different temperatures in the circulation loop for the brine, and the fluid storage tank H and the fluid storage tank F are used in another circulation loop for the water. Used to store water at different temperatures.
  • the fluid storage tank G is used to store the brine that has been heated by condensing the output pressure of the pneumatic engine J. At this time, the temperature of the brine generally rises above zero, for example, it can be 0°C to 20°C, or 0°C to 0°C. 12°C, preferably 12°C, of course, it can also be set to other temperatures as necessary.
  • the heat pump I is used to use its working fluid to absorb heat from the brine from the fluid storage tank G to cool the brine, and the fluid storage tank E is used to store the cooled brine.
  • the temperature of the brine is generally cooled to below zero, for example, It is -20°C to 0°C, or -12°C to 0°C, preferably -12°C, of course, it can also be set to other temperatures as required.
  • the fluid storage tank H is used to store the water after heating and cooling the input pressure working fluid of the pneumatic machine J.
  • the temperature of the water is generally 20°C to 60°C, such as 30°C to 50°C, such as 35°C to 45°C It is preferably 40°C, but of course it can be set to other temperatures as needed.
  • the heat pump I is used to heat the water from the fluid storage tank H by its working medium, and the fluid storage tank F is used to store the heated water.
  • the temperature of the water is generally 90°C to 60°C, such as 80°C to 65°C.
  • the temperature is preferably 75°C, but of course it can be set to other temperatures as necessary.
  • the working medium of the heat pump I is, for example, CO 2
  • the pressure working medium of the pneumatic engine J is, for example, ammonia.
  • the working medium of the heat pump I and the pressure working medium of the pneumatic machine J can also use other types of media, as long as the evaporation and condensation can be achieved at the set temperature to interact with the external fluid (such as brine or water).
  • the pressure working medium of the pneumatic machine J can also be freon.
  • the heat pump I uses CO 2 as the working fluid (refrigerant) for transcritical operation, in order to obtain a higher cooling energy efficiency ratio for the evaporator A, it is better to make the evaporator A cool the brine to about -12°C. Hourly cooling energy efficiency ratio is about 2.
  • the heat pump I can also use other types of working fluids, as long as the heat pump I is allowed to absorb heat from the brine in the evaporator A and release heat to the water in the condenser B.
  • the temperature of the water in the fluid storage tank H is preferably 40°C; the temperature of the water in the fluid storage tank F is preferably 75°C, under these temperature conditions ,
  • the energy efficiency ratio of heat pump I to water heating is about 3.
  • liquid ammonia is used as the pressure working medium of the pneumatic engine J
  • the environmentally friendly refrigerant liquid ammonia when used, when the temperature of the water at the inlet of the tube pass of the steam generator D is 75°C and the temperature of the water at the outlet of the tube pass is 40°C , The vapor pressure of liquid ammonia vaporized in the shell side of steam generator D is 16.7KG.
  • the generated back pressure of the pneumatic machine J is about 6.7KG, so in this system, the pneumatic machine J The net pressure difference of about 10KG can be obtained, which is significantly improved compared with the prior art, thereby increasing the output power of the pneumatic machine J.
  • the pneumatic machine J is used to drive the generator for power generation, the power generation is significantly increased.
  • the fluid storage tanks, evaporators, condensers, steam generators, pipelines, valves, etc. in the system in the embodiment of the present invention are preferably insulated to avoid undesired heat exchange with the outside world.
  • the following specifically describes an exemplary process in which the output pressure working fluid gas of the pneumatic engine J is condensed in the condenser C and then returned to the steam generator D as the input pressure working fluid of the pneumatic engine J.
  • the energy conversion system of this embodiment may also include a working fluid storage tank 14, which is located at a lower position compared with the first condenser C and passes through the valve 13 and the first condenser C fluid It is in fluid communication with the steam generator D through the valve 18.
  • valve 18 when the valve 13 is in the open state, the valve 18 is in the closed state, so that the condenser C is in communication with the working fluid storage tank 14, while keeping the working fluid storage tank 14 disconnected from the steam generator D, so that the condensing
  • the pressure working fluid liquid obtained by condensation in the device C can flow into the working fluid storage tank 14 by gravity (or a pumping device); and, when the liquid level in the working fluid storage tank 14 is higher than the predetermined high liquid level threshold 19 At this time, the valve 13 is turned into a closed state and the valve 18 is turned into an open state, so that the working fluid storage tank 14 is disconnected from the condenser C and communicated with the steam generator D, so that the working fluid storage tank 14 can be The collected pressure working fluid is returned to the steam generator D to be subsequently vaporized as the input pressure working gas of the pneumatic engine J.
  • the valve 13 becomes open and the valve 18 becomes closed, so that the working fluid storage tank 14 is disconnected from the steam generator D.
  • the connection is opened and the condenser C is reconnected, the pressure working fluid liquid obtained by condensation in the condenser C can flow into the working fluid storage tank 14, wherein the predetermined low liquid level threshold 20 is lower than the predetermined high liquid level threshold 19.
  • the valve 13 and the valve 18 may be electric valves.
  • the sensor 15 for sensing the liquid level in the working fluid storage tank 14 detects that the liquid level is higher than the predetermined high liquid level threshold 19 or lower than the predetermined low liquid level.
  • the threshold value 20 is driven to open and close as described above.
  • valve 13 and the valve 18 may be one-way check valves.
  • the pressure working fluid is allowed to flow in the direction from the condenser C to the working fluid storage tank 14.
  • the valve 18 is opened, the pressure working fluid is allowed to flow in the direction from the working fluid storage tank 14 to the steam generator D.
  • the working fluid storage tank 14 can also be in fluid communication with the condenser C through a pipe different from the pipe where the valve 13 is located.
  • the different pipe contains the valve 12 and the pneumatic generator 11 connected in series, which can control the working fluid.
  • the pressure working medium gas above the pressure working medium liquid in the medium storage tank 14 flows to the condenser C; in addition, the working medium storage tank 14 also communicates with the steam generator D through a pipeline different from the pipeline where the valve 18 is located.
  • the different pipelines include a valve 16 and a gas storage tank 17 connected in series.
  • the gas storage tank 17 is connected between the steam generator D and the valve 16 and is used to vaporize the pneumatic engine from the steam generator D
  • the pressure working medium gas and the pneumatic working medium liquid carried by it are separated from each other and the vaporized pneumatic working medium gas is temporarily stored when necessary.
  • the valve 16 can control the pressure working medium gas generated in the steam generator D to flow to the working medium storage liquid.
  • the valve 12 and the valve 16 are electric valves, which are controlled by the sensing signal of the liquid level sensor 15; the gas storage tank 17 can also be replaced by other devices with a liquid-gas separation function.
  • the high-pressure gas in the gas storage tank 17 enters the work through the valve 16
  • the pressure in the working fluid storage tank 14 increases in the fluid storage tank 14, thereby causing the one-way valve 13 to close, and the one-way valve 18 is opened due to the gravity of the pressure working fluid in the working fluid storage tank 14.
  • the working fluid storage tank 14 is connected to the steam generator D, and the pressure working fluid can be returned to the steam generator D.
  • the liquid level in the working fluid storage tank 14 is lower than the predetermined low liquid level threshold 20
  • the liquid level sensor 15 is lower than the predetermined low liquid level threshold 20, and an electric signal is generated to drive the electric valve 12 to change from the closed state.
  • the electric valve 16 is driven from the open state to the closed state for the open state.
  • the pressure inside the working fluid storage tank 14 is greater than that inside the shell side of the condenser C (which supplies the pressure working fluid gas and liquid of the pneumatic engine J through it ), the pressure difference can be used to drive the pneumatic generator 11 to generate electricity.
  • the generated electricity is preferably used to heat up the heating tube 22 through the wire 23, so as to assist in heating the water in the fluid storage tank F and store the heat in Fluid storage tank F.
  • the one-way valve 13 changes from a closed state to an open state due to the gravity of the pressure working fluid in the condenser C; at this time, due to the shell side of the steam generator D
  • the internal pressure (which supplies the working fluid and gas of the pneumatic engine J) is greater than the pressure inside the working fluid storage tank 14, so that the one-way valve 18 changes from an open state to a closed state, so that the working fluid storage tank 14 is disconnected from the steam generator D.
  • the heat pump 1 includes an electric motor 8 and a compressor driven by the electric motor. At least a part of the water from the fluid storage tank H is used for water-cooling the electric motor 8 and is cooled by the water. Then return to the fluid storage tank F; and/or, the pneumatic machine J is connected to the generator to drive the generator, and at least a part of the water from the fluid storage tank H is used to cool the generator, and returns to the fluid storage tank F after the water cooling in. In this way, the heat generated by the mechanical movement of the equipment (including motors and generators, etc.) in the system can also be stored and utilized, avoiding waste heat.
  • Fig. 3 shows a schematic diagram of a distributed energy storage and energy conversion method according to an embodiment of the present invention.
  • the distributed energy conversion method of the embodiment of the present invention may include:
  • the working fluid of the heat pump I is used to absorb heat from the brine in the circulation loop to cool the brine, and the heat pump I is used to compress the heat-absorbed working fluid to further increase the temperature of the working fluid, which is used to use its working fluid for another The water in the circulation loop is heated;
  • the heated water is used to heat the input pressure working fluid of the pneumatic machine J to vaporize it into a pressure working fluid gas for actuating the pneumatic machine J, and the input pressure working fluid is heated and cooled.
  • the refrigerated brine is used to condense the output pressure of the pneumatic engine J, and condense the output pressure of the pneumatic engine J.
  • the heated brine is re-absorbed by the heat of the heat pump I and cooled to It is used to condense the output pressure working fluid gas of the pneumatic machine J again, so that the brine is circulated for cooling and heating in the circulation loop.
  • the circulation loop is used to circulate salt water and water in one direction, and has the same meaning as the circulation loop in the above embodiment.
  • the working fluid of the heat pump I can absorb heat from the brine from the fluid storage tank G to cool the brine, and the cooled brine is transported to the fluid storage tank E.
  • the heat pump I can also compress the working fluid after absorbing heat to further increase the temperature of the working fluid for heating the water from the fluid storage tank H, and the heated water is transported to the fluid storage tank F.
  • the heated water from the fluid storage tank F can be transported to heat the input pressure working fluid of the pneumatic machine J to vaporize it into a pressure working fluid gas for actuating the pneumatic machine J and heating the input pressure working fluid
  • the latter water is transported back to the fluid storage tank H.
  • the refrigerated brine from the fluid storage tank E is transported to condense the output pressure of the pneumatic engine J, and then returns to the fluid storage tank G.
  • the refrigeration and heating in the energy conversion method in the embodiment of the present invention can be realized by a condenser and an evaporator.
  • the refrigerated first fluid from the fluid storage tank E can flow through the tube side of the condenser C, so as to control the output pressure of the pneumatic engine J in the shell side of the condenser C.
  • ammonia gas is condensed to obtain a pressure working fluid (ie liquid ammonia), which is returned to the steam generator D as the input pressure working fluid of the pneumatic engine J (ie, liquid ammonia).
  • the heated water from the fluid storage tank F can be used to heat the input pressure working fluid of the pneumatic engine J in the shell side of the steam generator D when flowing through the tube side of the steam generator D to vaporize it into pressure
  • the working fluid gas thus actuates the pneumatic machine J.
  • the working fluid of the heat pump I can flow through the shell side of the evaporator A, and absorb heat from the brine flowing into the tube side of the evaporator A and from the fluid storage tank G. Evaporate, thereby cooling the brine.
  • the compressed working fluid of the heat pump I can flow into the shell side of the condenser B to heat and condense the water flowing into the tube side of the condenser B from the fluid storage tank H, and then be transported and returned to the evaporator A.
  • the "shell side" and "tube side” in the present invention can also be interchanged according to actual applications.
  • the configuration of the circulation circuit for salt water and the circulation circuit for water may have the same meaning as described in the above embodiment.
  • salt water is used as the circulating fluid in one of the circulation loops
  • water i.e., ordinary fresh water
  • the present invention is not limited to the use of salt water and water as the circulating fluid.
  • other fluids can also be used, such as other types of liquids or even gases, as long as they can be maintained in a fluid state at the required operating temperature to facilitate circulation, so as to be compatible with the working fluid of the heat pump and the pressure of the pneumatic machine
  • the working fluid can be used for heat exchange at the specified temperature.
  • the fluid storage tank G is used to store the brine that has been heated by condensing the output pressure of the pneumatic engine J. At this time, the temperature of the brine generally rises above zero, for example, it can be 0°C to 20°C, or 0°C to 0°C. 12°C, preferably 12°C, of course, it can also be set to other temperatures as necessary.
  • the heat pump I is used to use its working fluid to absorb heat from the brine from the fluid storage tank G to cool the brine, and the fluid storage tank E is used to store the cooled brine.
  • the temperature of the brine is generally cooled to below zero, for example, It is -20°C to 0°C, or -12°C to 0°C, preferably -12°C, of course, it can also be set to other temperatures as required.
  • the fluid storage tank H is used to store the water after heating and cooling the input pressure working fluid of the pneumatic machine J.
  • the temperature of the water is generally 20°C to 60°C, such as 30°C to 50°C, such as 35°C to 45°C It is preferably 40°C, but of course it can be set to other temperatures as needed.
  • the heat pump I is used to heat the water from the fluid storage tank H by its working medium, and the fluid storage tank F is used to store the heated water.
  • the temperature of the water is generally 90°C to 60°C, such as 80°C to 65°C.
  • the temperature is preferably 75°C, but of course it can be set to other temperatures as necessary.
  • the working medium of the heat pump I is, for example, CO 2
  • the pressure working medium of the pneumatic engine J is, for example, ammonia.
  • the working medium of the heat pump I and the pressure working medium of the pneumatic machine J can also use other types of media, as long as the evaporation and condensation can be achieved at the set temperature to interact with the external fluid (such as brine or water).
  • the pressure working medium of the pneumatic machine J can also be freon.
  • the heat pump I uses CO 2 as the working fluid (refrigerant) for transcritical operation, in order to obtain a higher cooling energy efficiency ratio for the evaporator A, it is better to make the evaporator A cool the brine to about -12°C. Hourly cooling energy efficiency ratio is about 2.
  • the heat pump I can also use other types of working fluids, as long as the heat pump I is allowed to absorb heat from the brine in the evaporator A and release heat to the water in the condenser B.
  • the temperature of the water in the fluid storage tank H is preferably 40°C; the temperature of the water in the fluid storage tank F is preferably 75°C, under these temperature conditions ,
  • the energy efficiency ratio of heat pump I to water heating is about 3.
  • liquid ammonia is used as the pressure working medium of the pneumatic engine J
  • the environmentally friendly refrigerant liquid ammonia when used, when the temperature of the water at the inlet of the tube pass of the steam generator D is 75°C and the temperature of the water at the outlet of the tube pass is 40°C , The vapor pressure of liquid ammonia vaporized in the shell side of steam generator D is 16.7KG.
  • the generated back pressure of the pneumatic machine J is about 6.7KG, so in this system, the pneumatic machine J
  • the net pressure difference of about 10KG can be obtained, which is significantly improved compared with the prior art, thereby increasing the output power of the pneumatic machine J.
  • the pneumatic machine J is used to drive the generator to generate electricity, the power generation is significantly increased, so that The energy efficiency ratio of the generator can reach about 5.
  • the following describes the process of condensing the output pressure working fluid gas of the pneumatic engine J into the steam generator D as the input pressure working fluid of the pneumatic engine J in the energy conversion method according to the embodiment of the present invention.
  • the method may further include:
  • the working fluid storage tank 14 when the liquid level in the working fluid storage tank 14 is lower than the predetermined low liquid level threshold 20, the working fluid storage tank 14 is disconnected from the steam generator D and reconnected with the condenser C, so that the pressure obtained by condensation The working fluid can flow into the working fluid storage tank 14, wherein the predetermined low liquid level threshold 20 is lower than the predetermined low liquid level threshold.
  • the pressure difference between the inside of the working fluid storage tank 14 and the inside of the condenser C can also be used to drive the pneumatic generator 11 to generate electricity.
  • the electricity generated is preferably used For auxiliary heating of the water in the fluid storage tank F.
  • the pneumatic motor J is connected with the generator to drive the generator, in order to reuse the heat generated by the mechanical movement in the system, the replacement according to the embodiment of the present invention
  • the energy method may further include: using at least a part of the water from the fluid storage tank H for water cooling of the electric motor 8 and sending it back to the fluid storage tank F after the water cooling; and using at least part of the water from the fluid storage tank H
  • the generator is water-cooled, and is transported back to the fluid storage tank F after the water-cooling.
  • fluid storage tank G, fluid storage tank E, fluid storage tank H, fluid storage tank F, working fluid storage tank 14, evaporator A, steam generator D, condenser C and/or Condenser B can be adiabatic.
  • the description of the circulation loop, the fluids such as brine and water, the working medium of the heat pump, and the pressure working medium of the pneumatic engine are consistent with the above-mentioned energy conversion system. No longer.
  • the overall idea of this specific application is: at night, with the help of heat pumps, using ice water and hot water as the carrier at night valley electricity, store heat (including sensible heat and latent heat) in fluid storage tanks E and F until valley electricity time End, this is the night energy storage mode.
  • the power generation mode is adopted, that is, the cold and heat stored in the fluid storage tanks E and F are comprehensively utilized for power generation.
  • the night energy storage mode and the day power generation mode alternately cycle.
  • waste heat is very common, and waste heat is not used in many cases. For example, take air conditioning refrigeration as an example. In summer, indoor cooling is required, but the outdoor unit of the air conditioner dissipates a lot of heat. This heat is regarded as waste heat and is discarded by people.
  • the "waste heat” is stored in a large fluid storage tank F through a heat pump using water as a carrier to heat the pressure working fluid in the steam generator D during the day ( For example, liquid ammonia or Freon) generates high-pressure steam, which drives a pneumatic engine to turn waste into treasure.
  • the heating energy efficiency ratio (COP) is 3.
  • the air conditioner heating As an example. In winter, heating is needed indoors. The outdoor unit of the air conditioner generates a large amount of cold energy, which is also discarded by people. However, there is no real "waste cold” in the present invention. Instead, the "waste cold” is stored in a large fluid storage tank E through a heat pump, using salt water as a carrier, and used to condense the exhaust steam of the pneumatic engine C during the day. At this time, the cold storage COP is 2.
  • the invention is characterized in that the two are used in synergy at the same time, and the energy efficiency ratio is high.
  • the exhaust steam after the expansion of high temperature and high pressure steam needs to be condensed into liquid. At this time, the huge condensation heat is discharged. This heat is equivalent to the vaporization heat (latent heat) of the same mass of water. The heat cannot be used, so the efficiency of the entire power generation system is greatly reduced, and the efficiency of the supercritical generator set does not exceed 45%.
  • the high-pressure working medium gas such as ammonia or freon gas
  • the exhaust steam is discharged into the condenser C. The difference is that the large amount of condensation heat generated is taken from the fluid storage.
  • the ice water in tank E is absorbed and stored without loss, so that it can be absorbed in evaporator A at night for use. Therefore, the present invention saves and utilizes the condensation heat of the pneumatic working fluid. At the same time, the ice water from the fluid storage tank E is used to greatly reduce the exhaust pressure of the pneumatic machine, increase the pressure difference between the input end and the output end of the pneumatic machine, and increase the power of the pneumatic machine and increase power generation.
  • the working fluid ie, refrigerant
  • the working fluid ie, refrigerant
  • the working fluid ie, refrigerant
  • the temperature drops
  • the generated cold energy is transferred to the tube side
  • it absorbs the heat from the warm water 1
  • the warm water 1 is made into -12°C ice water and stored in the fluid storage tank E.
  • the refrigerant vapor in the evaporator A is discharged into the condenser B by the compressor of the heat pump I and condensed into
  • the liquid refrigerant releases heat at the same time and then returns to the evaporator A through the pipe 2 to complete a refrigeration cycle.
  • the heat emitted by the condenser B during condensation is transferred to the low-temperature water 3 in the tube side of the condenser B to raise its temperature to 75°C and store it in the fluid storage tank F for standby, thereby completing the night energy storage mode.
  • the water pump 4 After 8 o'clock in the morning, the water pump 4 starts to work.
  • the high-temperature water in the fluid storage tank F enters the steam generator D, and the liquid ammonia in the shell side is heated and pressurized to generate high-pressure ammonia steam, which enters the pneumatic engine J through the pipeline 5 to expand and perform work , Drive the generator to generate electricity.
  • the exhaust steam generated in the pneumatic engine J enters the condenser G through the pipe 6 to condense and release heat. At the same time, it heats the low-temperature brine of -12°C from the fluid storage tank E.
  • the brine is heated to 0-12°C and stored in the fluid In the storage tank G, it is used at night, while reducing the exhaust pressure of the pneumatic machine J, increasing the pressure difference between the working fluid input end and the working fluid output end of the pneumatic engine, and increasing the power generation.
  • the ammonia liquid in the condenser C is transported back to the steam generator D to complete a working cycle and realize the daytime power generation mode.
  • the distributed energy conversion system of the present invention can be used in the fields of wind energy storage, valley electricity storage, thermal power generation and the like, and the present invention does not limit this.
  • the working fluid of the heat pump and the working fluid of the pneumatic engine exchange heat indirectly, that is, by means of the first circulation loop and its medium, and the second circulation loop and its medium. heat.
  • the energy storage link may not be required.
  • the energy storage link can be Elimination, that is, the first circulation loop and/or the second circulation loop in the distributed energy conversion method and distributed energy conversion system are removed, so that the working fluid of the heat pump and the working fluid of the pneumatic engine are directly exchanged for heat, and then another
  • the energy conversion method and energy conversion system can realize the instantaneous amplification and output of input energy.
  • the energy conversion system may include a heat pump I, a pneumatic engine J, an evaporative condenser K, and an evaporative condenser L, where the heat pump I are respectively in fluid communication with the evaporative condenser K and the evaporative condenser L through pipelines, and the evaporative condenser K and the evaporative condenser L are in fluid communication through the pipeline 30, so that the working fluid of the heat pump I can pass through the evaporative condenser K, the pipeline 30 and the evaporative condenser L circulate flow; and the pneumatic machine J is in fluid communication with the evaporative condenser K and the evaporative condenser L through the pipeline, and the evaporative condenser K and the evaporative condenser L are also The fluid communication through the pipeline 40 enables the pressure working fluid of the pneumatic
  • the working medium of the heat pump I is used to absorb heat from the output pressure working medium gas of the pneumatic machine J in the evaporative condenser K to condense the output pressure working medium gas of the pneumatic machine J to obtain a pressure working medium liquid, and the pressure working medium liquid It is conveyed as the input pressure working fluid of pneumatic machine J.
  • the heat pump I is used to compress the working fluid after absorbing the heat to increase its temperature, so as to heat the input pressure working fluid of the pneumatic machine J in the evaporative condenser L to vaporize it into a pressure working fluid gas.
  • the medium gas is used to actuate the pneumatic machine J and then output by the pneumatic machine J to become the output pressure working medium gas of the pneumatic machine J.
  • the input pressure working fluid of the pneumatic engine J is heated and the working fluid of the heat pump I after the temperature is lowered is used to transport to the evaporative condenser K to absorb heat from the output pressure working fluid gas of the pneumatic engine J again , So that the working fluid of the heat pump 1 circulates to perform the above-mentioned processes of heat absorption, heating and cooling.
  • the working fluid of the heat pump I can flow through the tube side of the evaporative condenser K and from the pressure working fluid of the pneumatic engine J flowing through the shell side of the evaporative condenser K to absorb heat and vaporize, and at the same time, it is vaporized.
  • the output pressure working fluid gas of the pneumatic engine J flowing through the shell side of the condenser K is condensed due to heat release.
  • the compressed working fluid of the heat pump I releases heat and condenses when it flows through the tube side of the evaporative condenser L, while the input pressure working fluid of the pneumatic engine J is used to absorb hot gas in the shell side of the evaporative condenser L ⁇ .
  • the energy conversion system in the foregoing modified embodiment may further include a working fluid storage tank 14, which is located at a lower position than the evaporative condenser K and is in fluid communication with the evaporative condenser K through a valve 13. And it is in fluid communication with the evaporative condenser L through the valve 18.
  • a working fluid storage tank 14 which is located at a lower position than the evaporative condenser K and is in fluid communication with the evaporative condenser K through a valve 13. And it is in fluid communication with the evaporative condenser L through the valve 18.
  • the working mode of the working fluid storage tank 14 and related valves is the same as in the above embodiment.
  • the valve 18 when the system is working, when the valve 13 is in the open state, the valve 18 is in the closed state, so that the evaporative condenser K is connected to the working fluid storage tank 14, while maintaining the working fluid storage tank 14 and the evaporative condenser L The connection is disconnected, so that the pressure working fluid liquid condensed in the evaporative condenser K flows into the working fluid storage tank 14, so that the pressure working fluid liquid level in the working fluid storage tank 14 becomes higher and higher.
  • the valve 13 When the pressure working fluid liquid level in the working fluid storage tank 14 is higher than the predetermined first threshold, the valve 13 becomes closed and the valve 18 becomes open, so that the working fluid storage tank 14 and the evaporative condenser K is disconnected and communicated with the evaporative condenser L, so that the pressure working fluid liquid obtained by condensation in the working fluid storage tank 14 can be returned to the evaporative condenser L.
  • the valve 13 becomes open and the valve 18 becomes closed, so that the working fluid storage tank 14 is disconnected from the evaporative condenser L Connected and re-connected with the evaporative condenser K, so that the pressure working fluid liquid obtained by condensation in the evaporative condenser K can flow into the working fluid storage tank 14.
  • the predetermined second threshold is lower than the predetermined first threshold.
  • the working fluid storage tank 14 can also be in fluid communication with the evaporative condenser K through a pipeline different from the pipeline in which the valve 13 is located, and the different pipeline contains a series of valves 12 and Auxiliary pneumatic machine 11'; in addition, the working fluid storage tank 14 is also in fluid communication with the evaporative condenser L through a pipeline different from the pipeline where the valve 18 is located.
  • the different pipeline includes a series-connected valve 16 and a storage tank.
  • the gas tank 17 is connected between the evaporative condenser L and the valve 16 and is used to vaporize the pneumatic machine pressure of the pneumatic machine J from the evaporative condenser L and the pneumatic machine it carries.
  • the pressure working fluid is separated from each other and the vaporized pneumatic working fluid gas is temporarily stored when necessary.
  • the gas storage tank 17 can also be replaced by other devices with a liquid-gas separation function.
  • necessary liquid-gas separation devices are also provided in the pipeline 5 as required so that the gasified pneumatic working fluid from the evaporative condenser L will be firstly combined with the gas from the evaporative condenser L.
  • the working fluid of the pneumatic machine pressure is separated and then sent to the pneumatic machine J.
  • a pipeline can also be drawn from the gas storage tank 17 to connect to the pressure working fluid inlet of the pneumatic engine J, instead of the pipeline 5, so that no additional liquid-gas separation device is required to share the gas storage tank 17 for liquid-gas separation.
  • the valve 12 When the system is running, when the liquid level in the working fluid storage tank 14 is higher than the predetermined first threshold, the valve 12 changes from an open state to a closed state and the valve 16 changes from a closed state to an open state; when the working fluid storage tank When the liquid level in 14 is lower than the predetermined second threshold, the valve 12 changes from a closed state to an open state and the valve 16 changes from an open state to a closed state, thereby using the difference between the interior of the working fluid storage tank 14 and the interior of the evaporative condenser K.
  • the pressure difference between the two drives the auxiliary pneumatic machine 11', and after the pressure balances between the working fluid storage tank 14 and the evaporative condenser K, the valve 13 changes from a closed state to an open state.
  • valve 13 and valve 18 are one-way valves, and valve 12 and valve 16 are electric valves.
  • the system may further include: an auxiliary heat pump 26, which is driven by an auxiliary pneumatic machine 11', so that the heat pump 26 extracts at least a part of the working fluid of the heat pump I from the evaporative condenser K and It is compressed to increase the temperature of the at least part of the working fluid, and then the at least part of the working fluid whose temperature has been increased and the working fluid compressed by the heat pump I and heated up are merged into the evaporative condenser L.
  • an auxiliary heat pump 26 which is driven by an auxiliary pneumatic machine 11', so that the heat pump 26 extracts at least a part of the working fluid of the heat pump I from the evaporative condenser K and It is compressed to increase the temperature of the at least part of the working fluid, and then the at least part of the working fluid whose temperature has been increased and the working fluid compressed by the heat pump I and heated up are merged into the evaporative condenser L.
  • auxiliary pneumatic machine 11' to drive the auxiliary heat pump 26 can make full use of the energy output by the auxiliary pneumatic machine 11', and the auxiliary heat pump 26 further reduces the evaporative type by extracting the working fluid of the heat pump I from the evaporative condenser K.
  • the temperature of the output pressure working medium gas of the pneumatic machine J in the condenser K, and the working medium heated by the compression by the auxiliary heat pump 26 further increases the heat transferred to the evaporative condenser L, that is, through the auxiliary heat pump 26,
  • the evaporative condenser K and the evaporative condenser L further increase the pressure difference between the pressure working medium gas input end and the pressure working medium gas output end of the pneumatic machine J, thereby further increasing the power of the pneumatic machine J.
  • the above-mentioned system may further include a liquid tank 27, as shown in FIG. 6, which shows a schematic diagram of an energy conversion system according to another modified embodiment of the present invention.
  • the working fluid storage tank 14 is a shell-and-tube type liquid storage tank that can exchange heat between two working fluids.
  • the pressure working fluid and pressure working fluid gas of the pneumatic machine J can be stored in the shell-and-tube type liquid storage tank. Flow in the shell side of the tank.
  • the working fluid output from the auxiliary heat pump 26 and/or the working fluid output from the heat pump 1 can be used to heat the liquid (for example, water) in the liquid tank 27, and the pressure working medium liquid in the shell-and-tube liquid storage tank is transported to Before the evaporative condenser L, the heated liquid from the liquid tank 27 is transported to the tube side of the shell-and-tube liquid storage tank for performing the pressure working fluid in the shell side of the shell-and-tube liquid storage tank. heating.
  • the pressure working fluid in the working fluid storage tank 14 When the temperature of the pressure working fluid in the working fluid storage tank 14 differs greatly from the temperature of the pressure working fluid and/or gas in the evaporative condenser L, the pressure working fluid in the working fluid storage tank 14 When the liquid enters the evaporative condenser L, it will affect the pressure stability of the pressure working medium gas delivered from the evaporative condenser L to the pneumatic machine J, which may affect the output power stability of the pneumatic machine J. Therefore, the inventors further the above methods to preheat the pressure working fluid in the working fluid storage tank 14, so as to reduce or prevent it from affecting the pressure work in the evaporative condenser L when it enters the evaporative condenser L. Therefore, the input pressure of the pneumatic machine J is more stable.
  • the liquid level of the pneumatic working fluid (by, for example, When the liquid level gauge is higher than the predetermined high liquid level threshold 19, before the liquid storage tank 14 is connected to the evaporative condenser L, the pump 24 in fluid communication with the liquid tank 27 is triggered to start the hot liquid in the liquid tank 27 It is transported to the tube side of the liquid storage tank 14 to raise the temperature of the pneumatic working fluid (such as CO 2 liquid at 0°C) in the shell side of the liquid storage tank 14 (for example, the temperature is raised to 30°C, and the pressure reaches 72kg/ cm 2 ).
  • the temperature of the pneumatic working fluid such as CO 2 liquid at 0°C
  • the pump 24 is triggered to stop running, and the pressure working medium liquid in the liquid storage tank 14 is allowed to enter the evaporative condensation In the condenser L, valve 16 and valve 18 are open at this time, valve 12 and valve 13 are closed, so that the liquid storage tank 14 is disconnected from the evaporative condenser K and connected with the evaporative condenser L.
  • the principle of gravity is used to store The pressure working fluid (ie, CO 2 liquid) heated in the liquid tank 14 automatically falls into the evaporative condenser L, so that the temperature of the pressure working fluid in the storage tank 14 and the evaporative condenser L is similar or consistent Under the circumstance, it is beneficial to keep the steam pressure output in the evaporative condenser L stable with small fluctuations, so as to stabilize the rotational speed of the pneumatic engine and stabilize the output voltage and current of the generator driven by it. As the liquid level of the pneumatic working fluid in the liquid storage tank 14 drops and drops below the predetermined low liquid level threshold of 20, the valves 16 and 18 are closed.
  • the pressure in the liquid storage tank 14 and the evaporation type The pressure in the condenser L is the same, that is, much higher than the pressure in the evaporative condenser K, so the valve 12 is opened at this time, and the remaining pressure working medium gas (such as high-pressure CO 2 gas) in the liquid storage tank 14 will be Enter the auxiliary pneumatic machine 11' to drive its operation, and further drive the auxiliary heat pump 26 to work, extract the heat pump working fluid gas in the tube pass of the evaporative condenser K, and make the pressure of the pneumatic machine J in the shell pass of the evaporative condenser K The working fluid is further cooled.
  • the remaining pressure working medium gas such as high-pressure CO 2 gas
  • an energy conversion method As shown in FIG. 5, the method may include:
  • the working fluid of the heat pump I uses the working fluid of the heat pump I to absorb heat from the output pressure working gas of the pneumatic machine J and condense the output pressure working gas of the pneumatic machine J to obtain the pressure working fluid, and transfer the pressure working fluid as the input pressure of the pneumatic machine J Working fluid; here, the working fluid of the heat pump I absorbs heat from the output pressure working fluid gas of the pneumatic engine J.
  • the two working fluids can directly exchange heat in the heat exchange device, or it can be indirectly, that is The working fluid of the heat pump I absorbs heat from other media through the heat exchange device, and the other medium absorbs heat from the output pressure working fluid gas of the pneumatic engine J through another heat exchange device, which is not specifically limited in the present invention.
  • the heat pump I is used to compress the working fluid after absorbing heat to raise the temperature of the working fluid so as to heat the input pressure working fluid of the pneumatic engine J to vaporize it into a pressure working fluid gas, and the pressure working fluid gas is used to actuate the pneumatic engine J is then output by the pneumatic machine J as the output pressure working medium gas of the pneumatic machine J; here, similarly, the working medium heated by the heat pump I heats the input pressure working medium of the pneumatic machine J when it is realized.
  • the working fluid exchanges heat directly in the heat exchange device, or indirectly, that is, the working fluid heated by the heat pump I heats other media through the heat exchange device, and the other media heats the pneumatic motor J through another heat exchange device.
  • the input pressure working fluid is not specifically limited in the present invention.
  • the working medium of the heat pump I after heating and cooling the input pressure working medium is transported to absorb heat again from the output pressure working medium gas of the pneumatic machine J, so that the working medium of the heat pump I circulates the heat absorption, heating and Cooling process.
  • the working fluid of the heat pump I is cyclically performing the processes of heat absorption, heating and cooling, while the pressure working fluid of the pneumatic engine J cyclically performs exothermic condensation, endothermic gasification, and work cooling. process.
  • the working medium of the heat pump I can be used in the evaporative condenser K to absorb heat from the working medium gas of the output pressure of the pneumatic machine J to condense the working medium gas of the output pressure of the pneumatic machine J.
  • the working fluid of the heat pump I can flow through the tube side of the evaporative condenser K to absorb heat and gasify, and the output pressure working fluid gas of the pneumatic engine J can flow into the shell side of the evaporative condenser K to release heat and condense.
  • the working medium of the heat pump I can be used in the evaporative condenser L to heat the working medium of the input pressure of the pneumatic engine J after it is heated.
  • the compressed working medium of the heat pump I can flow through the tube side of the evaporative condenser L to exothermic and condense, while the input pressure working medium of the pneumatic engine J absorbs heat and vaporizes in the shell side of the evaporative condenser L.
  • the medium flowing in the tube side and the shell side of the evaporative condenser K can also be interchanged, as long as the two can exchange heat as above, and the present invention does not limit this.
  • the energy conversion method may further include:
  • the working fluid storage tank 14 When the liquid level in the working fluid storage tank 14 is higher than the predetermined first threshold, the working fluid storage tank 14 is disconnected from the evaporative condenser K and communicated with the evaporative condenser L, so that the working fluid can be The pressure working fluid liquid obtained by condensation in the liquid storage tank 14 is returned to the second evaporative condenser L.
  • the working fluid storage tank 14 When the liquid level in the working fluid storage tank 14 is lower than the predetermined second threshold, the working fluid storage tank 14 is disconnected from the evaporative condenser L and reconnected with the evaporative condenser K, so that the evaporative condenser The pressure working fluid liquid obtained by condensation in the vessel K can flow into the working fluid storage tank 14, wherein the predetermined second threshold is lower than the predetermined first threshold.
  • the energy conversion method may further include: when the working fluid storage tank 14 and the evaporative condenser K are reconnected, using the difference between the inside of the working fluid storage tank 14 and the inside of the evaporative condenser K The pressure difference between drives the auxiliary pneumatic machine 11'.
  • the pneumatic motor (J) is connected to the generator for driving the generator, and the heat pump (I) , At least a part of the cooled working fluid output from the evaporative condenser L is used to cool the generator connected to the pneumatic machine J, and is sent back to the evaporative condenser K after the cooling, so that the motor The heat generated during operation is reused.
  • the auxiliary heat pump 26 can also be introduced to further provide the pressure difference between the working fluid input end and the working fluid output end of the pneumatic machine J, and to improve the pressure in the liquid storage tank 14.
  • the working fluid is preheated by the pneumatic machine pressure. This will be briefly described below in conjunction with FIG. 6.
  • the method may also include an auxiliary heat pump 26, which is driven by an auxiliary pneumatic machine 11', so that the heat pump 26 extracts at least a part of the working fluid of the heat pump I from the evaporative condenser K and compresses it to The temperature of the at least a part of the working fluid is increased, and then the at least part of the working fluid whose temperature has been increased and the working fluid compressed by the heat pump I and heated up are merged into the evaporative condenser L.
  • an auxiliary heat pump 26 which is driven by an auxiliary pneumatic machine 11', so that the heat pump 26 extracts at least a part of the working fluid of the heat pump I from the evaporative condenser K and compresses it to The temperature of the at least a part of the working fluid is increased, and then the at least part of the working fluid whose temperature has been increased and the working fluid compressed by the heat pump I and heated up are merged into the evaporative condenser L.
  • the above method may also include a liquid tank 27, as shown in FIG. 6.
  • the working fluid storage tank 14 is a shell-and-tube type liquid storage tank that can exchange heat between two working fluids.
  • the pressure working fluid and pressure working fluid gas of the pneumatic machine J can be stored in the shell-and-tube type liquid storage tank. Flow in the shell side of the tank.
  • the working fluid output from the auxiliary heat pump 26 and/or the working fluid output from the heat pump 1 can be used to heat the liquid in the liquid tank 27, and the pressure working fluid in the shell-and-tube liquid storage tank is transported to the evaporative condenser Before L, the heated liquid from the liquid tank 27 is transported to the tube side of the shell-and-tube liquid storage tank for heating the pressure working fluid in the shell side of the shell-and-tube liquid storage tank.
  • the contact with the liquid tank 27 is triggered.
  • the fluidly connected pump 24 is activated to transport the hot liquid in the liquid tank 27 to the tube side of the liquid storage tank 14 for transferring the pneumatic working fluid in the shell side of the liquid storage tank 14 (for example, CO 2 at 0°C). Liquid) is heated (for example, the temperature is raised to 30°C, and the pressure reaches 72 kg/cm 2 ).
  • the pump 24 is triggered to stop running, and the pressure working fluid in the liquid storage tank 14 is allowed to enter the evaporative condensation In the condenser L, the valve 16 and the valve 18 are open at this time, the valve 12 and the valve 13 are closed, so that the liquid storage tank 14 is disconnected from the evaporative condenser K and communicated with the evaporative condenser L.
  • the principle of gravity is used to store The pressure working fluid (ie, CO 2 liquid) heated in the liquid tank 14 automatically falls into the evaporative condenser L, so that the temperature of the pressure working fluid in the storage tank 14 and the evaporative condenser L is similar or consistent Under the circumstance, it is beneficial to keep the steam pressure output in the evaporative condenser L stable with small fluctuations, so as to stabilize the rotation speed of the pneumatic engine and stabilize the output voltage and current of the generator driven by it. As the liquid level of the pneumatic pressure working fluid in the liquid storage tank 14 drops and drops below the predetermined low liquid level threshold of 20, the valves 16 and 18 are closed.
  • the pressure in the liquid storage tank 14 and the evaporation type The pressure in the condenser L is the same, that is, much higher than the pressure in the evaporative condenser K, so at this time the valve 12 is opened, and the remaining pressure working medium gas (such as high-pressure CO 2 gas) in the liquid storage tank 14 will be Enter the auxiliary pneumatic machine 11' to drive its operation, and further drive the auxiliary heat pump 26 to work, extract the heat pump working fluid gas in the tube pass of the evaporative condenser K, and make the pressure of the pneumatic machine J in the shell pass of the evaporative condenser K The working fluid is further cooled.
  • the remaining pressure working medium gas such as high-pressure CO 2 gas
  • the evaporative condenser K, the evaporative condenser L, and/or the working fluid storage tank 14 may be insulated.
  • the working medium of the heat pump I may be ammonia NH 3
  • the pressure working medium of the pneumatic engine J may be carbon dioxide CO 2 .
  • the temperature and pressure of ammonia are: 0°C and 3.38kg/cm 2 respectively ; And/or, at the working fluid outlet of heat pump I, the temperature and pressure of ammonia are respectively: 40°C and 14.8kg/cm 2 ; and/or, at the pressure working fluid inlet of pneumatic engine J, the temperature and pressure of CO 2 are The pressure is: 40°C and 96kg/cm 2 ; and/or, at the outlet of the pressure working fluid of the pneumatic machine J, the temperature and pressure of CO 2 are: 0°C and 35 kg/cm 2 .
  • the above are only examples.
  • the temperature and pressure of the working fluid at each position can adjust the temperature and pressure of the working fluid at each position according to various parameters of the components in the system, for example, according to the energy efficiency ratio of heat pump I (including cooling energy efficiency ratio and heating energy efficiency ratio), heat pump
  • the working medium of I, the energy efficiency ratio of the pneumatic machine J, the pressure working medium of the pneumatic machine J, the heat exchange efficiency of the steam condenser, etc. are adjusted so that the energy conversion system can achieve a balanced and long-lasting operation as a whole.
  • the energy efficiency ratio of the heat pump I can be 5.76
  • the heating energy efficiency ratio is 3.36
  • the cooling energy efficiency ratio is 2.4.
  • the liquid ammonia in the tube side of the evaporative condenser K is extracted and gasified, and the cooling energy efficiency ratio is 2.4.
  • the CO 2 gas in the shell side of the condenser K condenses and absorbs the heat of CO 2 condensation at the same time, so that the overall temperature of the evaporative condenser K is maintained in a stable range to achieve equilibrium heat absorption (NH 3 ) and equilibrium heat release (CO 2 ) Run forever.
  • All equipment, pipes and valves of the whole system can be insulated and kept warm, no matter the outside temperature is high or low, it will not affect the operation of the system.
  • the auxiliary heat pump 26 is used to further increase the pressure difference between the working fluid input end and the working fluid output end of the pneumatic machine J.
  • modules in the embodiments can be combined into one module or unit or component, and in addition, they can be divided into multiple modules or units or components. Except that at least some of such features and/or processes or modules are mutually exclusive, any combination can be used to compare all features disclosed in this specification (including the accompanying claims, abstract and drawings) and any method or methods disclosed in this manner or All the processes or units of the equipment are combined. Unless expressly stated otherwise, each feature disclosed in this specification (including the accompanying claims, abstract and drawings) may be replaced by an alternative feature that provides the same, equivalent or similar purpose.

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Abstract

一种换能方法，包括：利用第一热泵(I)的工质吸收来自气动机(J)的输出压力工质气体的热量而将气动机(J)的输出压力工质气体冷凝得到压力工质液体，并将压力工质液体输送作为气动机(J)的输入压力工质；利用第一热泵(I)对吸收热量后的工质进行压缩以使该工质升温从而能够将热量输送给气动机(J)的输入压力工质使其加热汽化成压力工质气体，压力工质气体用于致动气动机(J)然后由气动机(J)输出作为气动机(J)的输出压力工质气体；将热量输送给输入压力工质而降温后的第一热泵(I)的工质被输送用于重新从气动机(J)的输出压力工质气体吸收热量，从而使得第一热泵(I)的工质循环进行所述吸热、升温和降温。

Description

换能方法和系统 技术领域
本发明涉及换能及储能技术领域，具体涉及一种换能方法和换能系统，其能够对输入的电能进行放大输出以用于驱动外部设备，例如驱动发电机进行发电；特别地，还涉及分布式换能方法和分布式换能系统，其能够对输入的电能储能，并且进行放大输出以用于驱动外部设备，例如驱动发电机进行发电。
背景技术
在国内外，现有的储能方法(例如储电方法)包括抽水蓄水储能、飞轮储能、化学电池储能、压缩空气储能等办法，但是以上几种方法的能效比低，一般不会超过0.8，而且所需投资大。此外，在实现这些方法的系统中，一些能够重复利用的热能和冷能也被作为废热而排出系统，造成能量浪费以及能效比降低。
另外，有些现有的储能方法需要利用特定的地形，例如山区、海边等，因此在具体实施时受到地理位置的限制，从而限制其实际的推广及应用。
因此，急需一种分布式换能方法和分布式换能系统，其能够实现比现有技术显著更高效的储能和能量输出。另外，还急需一种换能方法和系统，其能够重复利用现有换能系统中作为废冷和废热的能量以及热泵的高效率来实现电能的放大输出。
发明内容
鉴于上述问题，本发明提出了一种克服上述问题的分布式换能方法及系统，用于解决现有技术中存在的换能效率低下、投资昂贵、实际实施受地形或地理位置影响等缺陷，而且能够易于实现将电网用电量较少时间段内的谷电进行换能储存，然后在电网用电量较大时利用储存的能量为电网补充发电，实现能量的高效储存和延时输出，而且整体能效比显著提高。
依据本发明的第一方面，提供了一种分布式换能方法，其包括：
利用热泵的工质从在第一循环回路中循环流动的第一流体中吸收热量而对第一流体制冷；
利用热泵对吸收热量后的工质进行压缩以进一步提高工质的温度，用于对在第二循环回路中循环流动的第二流体进行加热；
输送经加热的第二流体用于对气动机的输入压力工质进行加热使其汽化成压力工质气体用于致动所述气动机，并且对输入压力工质进行加热而降温后的第二流体被热泵的工质重新加热以用于重新对气动机的输入压力工质进行加热，从而使得第二流体被循环加热和降温；
输送经制冷的第一流体用于对气动机的输出压力工质气体进行冷凝，并且对气动机的输出压力工质气体进行冷凝而升温后的第一流体被热泵的工质重新吸收热量而制冷以用于重新对气动机的输出压力工质气体进行冷凝，从而使得第一流体被循环制冷和升温。
根据一实施例，利用热泵的工质从在第一循环回路中循环流动的第一流体中吸收热量而对第一流体制冷可以包括：利用热泵的工质从来自第一流体储罐的第一流体中吸收热量而对第一流体制冷，且经制冷的第一流体被输送到第二流体储罐中；
利用热泵对吸收热量后的工质进行压缩以进一步提高工质的温度，用于对在第二循环回路中循环流动的第二流体进行加热可以包括：热泵对吸收热量后的工质进行压缩以进一步提高工质的温度用于对来自第三流体储罐的第二流体进行加热，经加热的第二流体被输送到第四流体储罐中；
输送经加热的第二流体用于对气动机的输入压力工质进行加热使其汽化成压力工质气体用于致动所述气动机可以包括：来自第四流体储罐的经加热的第二流体被输送用于对气动机的输入压力工质进行加热使其汽化成压力工质气体用于致动该气动机，并且对输入压力工质加热后的第二流体被输送回第三流体储罐；
输送经制冷的第一流体用于对气动机(J)的输出压力工质气体进行冷凝可以包括：来自第二流体储罐的经制冷的第一流体被输送用于对气动机的输出压力工质气体进行冷凝，然后返回到第一流体储罐中。
根据一实施例，来自第二流体储罐的经制冷的第一流体被输送用于对气动机的输出压力工质气体进行冷凝，可以包括：使来自第二流体储罐的经制冷的第一流体流经第一冷凝器，从而对流入第一冷凝器中的、气动机的输出压力工质气体进行冷凝得到压力工质液体，压力工质液体返回蒸汽发生器作为气动机的输入压力工质；
其中，来自第四流体储罐的经加热的第二流体用于在流经蒸汽发生器时 对蒸汽发生器内的、气动机的输入压力工质进行加热使其汽化成压力工质气体从而致动气动机。
根据一实施例，利用热泵的工质从来自第一流体储罐的第一流体中吸收热量而对第一流体制冷，可以包括：使热泵的工质流经蒸发器，从流入蒸发器中的、来自第一流体储罐的第一流体中吸收热量而蒸发，从而对第一流体制冷；
其中，热泵的压缩后的工质流入第二冷凝器中对流入第二冷凝器中的、来自第三流体储罐的第二流体进行加热而冷凝，然后被输送并返回蒸发器。
根据一实施例，在冷凝所得压力工质液体返回蒸汽发生器作为气动机的输入压力工质之前，所述方法还可以包括：
使第一冷凝器与工质储液罐连通，同时保持工质储液罐与蒸汽发生器断开连通，从而使冷凝所得压力工质液体流入工质储液罐中，并且，
当工质储液罐中的液位高于预定第一阈值时，使工质储液罐与第一冷凝器断开连通，并且与蒸汽发生器连通，从而能够使工质储液罐中冷凝所得压力工质液体返回蒸汽发生器中。
根据一实施例，所述方法还可以包括：
当工质储液罐中的液位低于预定第二阈值时，使工质储液罐与蒸汽发生器断开连通而与第一冷凝器重新连通，使得冷凝所得压力工质液体能够流入工质储液罐中，其中所述预定第二阈值低于所述预定第一阈值。
根据一实施例，所述方法还可以包括：在工质储液罐与第一冷凝器重新连通时，利用工质储液罐内部与第一冷凝器内部之间的压力差驱动气动发电机发电，所产生的电优选用于对第四流体储罐中的第二流体进行辅助加热。
根据一实施例，热泵可以包括电动机以及由电动机驱动的压缩机，所述方法还可以包括：将来自第三流体储罐的至少一部分第二流体用于对电动机进行水冷，并且在水冷后被输送回第四流体储罐中；
和/或，
气动机与发电机连接以驱动发电机，所述方法还可以包括：将来自第三流体储罐的至少一部分第二流体用于对发电机进行水冷，并且在水冷后被输送回第四流体储罐中。
根据一实施例，第一流体储罐、第二流体储罐、第三流体储罐、第四流体储罐、工质储液罐、蒸发器、蒸汽发生器、第一冷凝器和/或第二冷凝器优选是绝热的。此外，整个系统中的其它部件，例如管道、阀门等也优选为绝 热的。
根据一实施例，第一流体可以为盐水，对气动机的输出压力工质气体进行冷凝而升温后的第一流体、或者储存在第一流体储罐中的第一流体的温度优选为0℃至20℃，更优选为0℃至12℃，更优选为12℃；被热泵的工质加热后的第一流体、或者储存在第二流体储罐中的第一流体的温度优选为-20℃至0℃，更优选为-12℃至0℃，更优选为-12℃；和/或，
第二流体可以为水，对输入压力工质进行加热而降温后的第二流体、或者储存在第三流体储罐中的第二流体的温度优选为30℃至50℃，更优选为35℃至45℃，更优选为40℃；被热泵的工质加热后的第二流体、或者储存在第四流体储罐中的第二流体的温度优选为90℃至60℃，更优选为80℃至65℃，更优选为75℃；和/或，
热泵的工质可以为CO 2，且气动机的压力工质可以为氨。
依据本发明的另一方面，提供了一种分布式换能系统，其包括：热泵、气动机、用于供第一流体在其中循环流动的第一循环回路、以及用于供第二流体在其中循环流动的第二循环回路，其中，
热泵用于利用其工质从第一流体中吸收热量而对第一流体制冷，并且用于对吸收热量后的工质进行压缩以进一步提高工质的温度，用于利用其工质对第二流体进行加热；
经加热的第二流体用于对气动机的输入压力工质进行加热使其汽化成压力工质气体用于致动所述气动机，并且对输入压力工质进行加热而降温后的第二流体被热泵的工质重新加热以用于重新对气动机的输入压力工质进行加热，从而使得第二流体被循环加热和降温；
经制冷的第一流体用于对气动机的输出压力工质气体进行冷凝，并且对气动机的输出压力工质气体进行冷凝而升温后的第一流体被热泵的工质重新吸收热量而制冷以用于重新对气动机的输出压力工质气体进行冷凝，从而使得第一流体被循环制冷和升温。
根据一实施例，所述系统还可以包括：第一流体储罐、第二流体储罐、第三流体储罐和第四流体储罐，其中第一流体储罐和第二流体储罐位于第一循环回路中用于储存第一流体，第三流体储罐和第四流体储罐位于第二循环回路中用于储存第二流体，并且其中：
第一流体储罐用于储存对气动机的输出压力工质气体进行冷凝而升温后的第一流体，其中热泵用于用其工质从来自第一流体储罐的第一流体中吸 收热量而对第一流体制冷，第二流体储罐用于储存经制冷的所述第一流体；
第三流体储罐用于储存对气动机的输入压力工质进行加热而降温后的第二流体，其中热泵用于利用其工质对来自第三流体储罐的第二流体进行加热，且第四流体储罐用于储存经加热的所述第二流体。
根据一实施例，所述系统还可以包括第一冷凝器和蒸汽发生器，其中，
第一冷凝器用于：使来自第二流体储罐的经制冷的第一流体在流经第一冷凝器时对流入第一冷凝器中的、气动机的输出压力工质气体进行冷凝得到压力工质液体，该压力工质液体返回蒸汽发生器作为气动机的输入压力工质；蒸汽发生器用于：使来自第四流体储罐的经加热的第二流体在流经蒸汽发生器时对蒸汽发生器内的、气动机的输入压力工质进行加热使其汽化成压力工质气体从而致动气动机。
根据一实施例，所述系统还可以包括蒸发器和第二冷凝器，其中，
蒸发器用于：使热泵的工质在流经蒸发器时从流入蒸发器中的、来自第一流体储罐的第一流体中吸收热量而蒸发，从而对第一流体制冷；第二冷凝器用于：使热泵的压缩后的工质在流经第二冷凝器时对流入第二冷凝器中的、来自第三流体储罐的第二流体进行加热而冷凝，并在加热后输送并返回蒸发器。
根据一实施例，所述系统还可以包括工质储液罐，其与第一冷凝器相比位于更低位置且通过第一阀门与第一冷凝器流体连通，并且通过第二阀门与蒸汽发生器流体连通，
其中，当第一阀门处于打开状态时，第二阀门处于关闭状态，使得第一冷凝器与工质储液罐连通，同时保持工质储液罐与蒸汽发生器断开连通，从而使冷凝所得压力工质液体可以利用重力流入工质储液罐中；
并且，当工质储液罐中的液位高于预定第一阈值时，第一阀门变为关闭状态且第二阀门变为打开状态，使得工质储液罐与第一冷凝器断开连通而与蒸汽发生器连通，从而能使工质储液罐中的压力工质液体返回蒸汽发生器。
根据一实施例，当工质储液罐中的液位低于预定第二阈值时，第一阀门变为打开状态且第二阀门变为关闭状态，使工质储液罐与蒸汽发生器断开连通而与第一冷凝器重新连通，使得第一冷凝器中冷凝所得压力工质液体能够流入工质储液罐中，其中预定第二阈值低于预定第一阈值。
在这里，第一阀门和第二阀门可以为电动阀。
根据一实施例，工质储液罐还可以通过与第一阀门所处第一管路不同的 第三管路与第一冷凝器流体连通，所述第三管路中包含串接的第三阀门和气动发电机，
工质储液罐还通过与第二阀门所处第二管路不同的第四管路与蒸汽发生器流体连通，第四管路中包含串接的第四阀门和储气罐，该储气罐连接于蒸汽发生器与第四阀门之间且用于储存汽化的压力工质气体，
当工质储液罐中的液位高于预定第一阈值时，第三阀门由打开状态变为关闭状态而第四阀门由关闭状态变为打开状态,鉴于此时第一阀门变为关闭状态且第二阀门变为打开状态，使得工质储液罐与第一冷凝器断开连通而与蒸汽发生器连通，从而能够使工质储液罐中的压力工质液体返回蒸汽发生器中；当工质储液罐中的液位低于预定第二阈值时，第三阀门由关闭状态变为打开状态而第四阀门由打开状态变为关闭状态，从而利用工质储液罐内部与第一冷凝器内部之间的压力差驱动气动发电机发电，所产生的电优选用于对第四流体储罐中的第二流体进行辅助加热，并且在工质储液罐内部与第一冷凝器内部之间压力平衡后，第一阀门由关闭状态变为打开状态。
根据一实施例，第一阀门和第二阀门可以为单向阀，而第三阀门和第四阀门可以为电动阀。
根据一实施例，热泵可以包括电动机以及由该电动机驱动的压缩机，来自第三流体储罐的至少一部分第二流体用于对电动机进行水冷，并且在水冷后返回第四流体储罐中；和/或，气动机与发电机连接以驱动发电机，来自第三流体储罐的至少一部分第二流体用于对发电机进行水冷，并且在水冷后返回第四流体储罐中。
根据一实施例，第一流体储罐、第二流体储罐、第三流体储罐、第四流体储罐、工质储液罐、蒸发器、蒸汽发生器、第一冷凝器和/或第二冷凝器可以是绝热的。此外，整个系统中的其它部件，例如管道、阀门等也优选为绝热的。
根据一实施例，第一流体可以为盐水，对气动机的输出压力工质气体进行冷凝而升温后的第一流体、或者储存在第一流体储罐中的第一流体的温度优选为0℃至20℃，更优选为0℃至12℃，更优选为12℃；被热泵的工质吸收热量而制冷的第一流体、或者储存在第二流体储罐中的第一流体的温度优选为-20℃至0℃，更优选为-12℃至0℃，更优选为-12℃；和/或，
第二流体可以为水，对输入压力工质进行加热而降温后的第二流体、或者储存在第三流体储罐中的第二流体的温度优选为30℃至50℃，更优选为 35℃至45℃，更优选为40℃；被热泵的工质加热后的第二流体、或者储存在第四流体储罐中的第二流体的温度优选为90℃至60℃，更优选为80℃至65℃，更优选为75℃；和/或，
热泵的工质可以为CO 2，且气动机的压力工质可以为氨。
在本发明的分布式换能方法和分布式换能系统中，利用热泵在对第一流体制冷的同时对第二流体制热，经制冷的第一流体用于对气动机的输出压力工质气体进行冷凝及降低气动机的排气压力，同时经制热的第二流体用于对气动机的输入压力工质加热使其汽化以增加气动机的输入压力工质的压力，从而大幅提高了气动机的工质输入端与工质输出端之间的压力差，进而使气动机动力增强、发电增加。在这里，第一流体在一循环回路中循环，而第二流体在另一循环回路中循环，不会将能量排放到整体换能系统的外部，从而避免了能量损失，提高了整体系统的能效比。此外，第一流体在对气动机输出压力工质气体进行冷凝时，也是第一流体吸收输出压力工质气体中的热量进行储能的过程，所储存的热能能够用于供热泵的工质吸热，从而避免了系统内的能量损失。
换而言之，在本发明的分布式换能方法及系统中，不存在传统意义上的“废热”，因为这些“废热”在其它环节中都作为有用的能量进行了利用。例如就热泵的角度而言，热泵在对第二流体制热以便后续用于对气动机的输入压力工质进行加热而使其汽化的同时，会对第一流体进行制冷使其后续用于对气动机的输出压力工质气体进行冷凝，所以热泵既利用了第二流体的显热，又利用了第一流体的潜热。又例如，就气动机的角度而言，在气动机的压力工质做功后的乏汽中携带的余热也被经制冷的第一流体回收以便后续供热泵工质吸热，从而气动机的“废热”也得到了再利用。甚至热泵中的电动机以及由气动机驱动的发电机产生的废热，也可以通过来自第三流体储罐的第二流体对其进行水冷而回收到第四流体储罐中待后续加以利用。
本发明的分布式换能方法及系统能够用于驱动外部设备，例如驱动发电机进行发电，从而实现分布式储能发电方法和系统，其能够显著提高能效比，从而提高发电效率，而且通过多个流体储罐进行储能，能够实现储存电网中的夜间谷电，然后在白天用电需求大时利用夜间储存的能量发电输出，而且显著提高输出电量。
根据上述实施例的变型，如果将分布式换能方法和分布式换能系统的中的第一循环回路及第二循环回路去掉，改为热泵的工质与气动机的工质直接 进行热交换，则得到一种换能方法和换能系统，其能够实现输入能量的即时放大输出。
根据上述实施例的一变型，提供了一种换能方法，包括：
利用热泵的工质吸收来自气动机的输出压力工质气体的热量而将所述气动机的输出压力工质气体冷凝得到压力工质液体，并将所述压力工质液体输送作为所述气动机的输入压力工质；
利用热泵对吸收热量后的工质进行压缩以使所述工质升温从而能够将热量输送给气动机的所述输入压力工质使其加热汽化成压力工质气体，所述压力工质气体用于致动所述气动机然后由所述气动机输出作为所述气动机的输出压力工质气体；
将热量输送给所述输入压力工质而降温后的所述热泵的工质被输送用于重新从气动机的输出压力工质气体吸收热量，从而使得所述热泵的工质循环进行所述吸热、升温和降温。
根据上述实施例的另一变型，提供一种换能系统，其包括热泵、气动机、第一蒸发式冷凝器和第二蒸发式冷凝器，其中热泵分别通过管路与第一蒸发式冷凝器以及第二蒸发式冷凝器流体连通并且第一蒸发式冷凝器与第二蒸发式冷凝器通过第一管路流体连通，使得热泵的工质能够经由第一蒸发式冷凝器、第一管路以及第二蒸发式冷凝器循环流动；并且，气动机分别通过管路与第一蒸发式冷凝器以及第二蒸发式冷凝器流体连通并且第一蒸发式冷凝器与第二蒸发式冷凝器还通过第二管路流体连通，使得气动机的压力工质能够经由第一蒸发式冷凝器、第二管路以及第二蒸发式冷凝器循环流动，
其中，热泵的工质用于在第一蒸发式冷凝器中从气动机的输出压力工质气体吸收热量而将所述气动机的输出压力工质气体冷凝得到压力工质液体，并且所述压力工质液体被输送作为所述气动机的输入压力工质；
热泵用于对吸收热量后的工质进行压缩以使所述工质升温从而用于在第二蒸发式冷凝器中对气动机的所述输入压力工质进行加热使其汽化成压力工质气体，所述压力工质气体用于致动所述气动机然后由所述气动机输出作为所述气动机的输出压力工质气体；
在第二蒸发式冷凝器中对所述输入压力工质进行加热而降温后的所述热泵的工质被用于输送到第一蒸发式冷凝器中重新从气动机的输出压力工质气体吸收热量，从而使得所述热泵的工质循环进行所述吸热、升温和降温。
上述说明仅是本发明技术方案的概述，以便能够更清楚地了解本发明的 技术手段，从而可依照说明书的内容予以实施。为了让本发明的上述和其它目的、特征和优点能够更明显易懂，以下特举说明本发明的具体实施方式。
附图说明
通过阅读下文优选实施方式的详细描述，各种其他的优点和益处对于本领域普通技术人员将变得清楚明了。附图仅用于示出优选实施方式的目的，而并不认为是对本发明的限制。而且在整个附图中，用相同的参考符号表示相同的部件。在附图中：
图1是根据本发明实施例的分布式换能系统的示意图；
图2是根据本发明实施例的分布式换能系统的局部示意图；
图3是根据本发明实施例的分布式换能方法的示意图；
图4是根据本发明变型实施例的换能系统的示意图；
图5是根据本发明另一变型实施例的换能方法的示意图；
图6是根据本发明又一变型实施例的换能系统的示意图。
具体实施方式
下面将参照附图更详细地描述本公开的示例性实施例。虽然附图中显示了本公开的示例性实施例，然而应当理解，可以以各种形式实现本公开而不应被这里阐述的实施例所限制。相反，提供这些实施例是为了能够更透彻地理解本公开，并且能够将本公开的范围完整的传达给本领域的技术人员。
图1是根据本发明实施例的分布式换能系统的示意图。如图1所示，根据本发明一实施例的分布式换能系统包括：热泵I、气动机J、用于供盐水在其中循环流动的循环回路、及用于供水在其中循环流动的循环回路，其中，
热泵I用于利用其工质从循环回路中的盐水中吸收热量而对盐水制冷，并且用于对吸收热量后的工质进行压缩以进一步提高工质的温度，用于利用其工质对另一循环回路中的水进行加热；在图1中，热泵I例如包括电动机8以及与电动机8传动连接的压缩机，且包括与压缩机连接的工质管路以及管路中的工质。
经加热的水用于对气动机J的输入压力工质进行加热使其汽化成压力工质气体用于致动所述气动机J，并且对输入压力工质进行加热而降温后的水被热泵I的工质重新加热以用于重新对气动机J的输入压力工质进行加热，从而使水在所述另一循环回路中被循环加热和降温；
经制冷的盐水用于对气动机J的输出压力工质气体进行冷凝，并且对气动机J的输出压力工质气体进行冷凝而升温后的盐水被热泵I的工质重新吸收热量而制冷以用于重新对气动机J的输出压力工质气体进行冷凝，从而使得盐水在循环回路中被循环制冷和升温。
在本发明中，所述循环回路分别用于使盐水和水在其中单向循环，使得盐水在循环回路中循环时被循环制冷和升温，并且使得水在循环回路中循环时被循环加热和降温。这些循环回路中可以根据需要来设计，采用各种管路、阀门、泵送装置、蒸发器、冷凝器、蒸汽发生器等实现，根据需要，循环回路中也可以包括分别暂时储存盐水和水的流体储罐。因此，本发明中对循环回路的具体实现没有特别限制，只要其能够使其中的盐水和水循环流动以便被循环制冷和加热即可。
所述分布式换能系统中的冷凝器C用于：使来自流体储罐E的经制冷的盐水在流经冷凝器C的管程时对流入冷凝器C的壳程中的、气动机J的输出压力工质气体(例如氨气)进行冷凝得到压力工质液体(即液氨)，该压力工质液体返回蒸汽发生器D作为气动机J的输入压力工质(即液氨)；蒸汽发生器D用于：使来自流体储罐F的经加热的水在流经蒸汽发生器D的管程时对蒸汽发生器D的壳程内的、气动机J的输入压力工质进行加热使其汽化成压力工质气体从而致动气动机J。
所述分布式换能系统还可以包括蒸发器A和冷凝器B，蒸发器A用于：使热泵I的工质在流经蒸发器A的壳程时从流入蒸发器A的管程中的、来自流体储罐G的盐水中吸收热量而蒸发，从而对盐水制冷；冷凝器B用于：使热泵I的压缩后的工质在流经冷凝器B的壳程时对流入冷凝器B的管程中的、来自流体储罐H的水进行放热而冷凝，并在放热后输送并返回蒸发器A。
在本发明的分布式换能系统中，利用热泵I在对盐水制冷的同时对水制热，经制冷的盐水用于对气动机J的输出压力工质气体进行冷凝以降低气动机J的排气压力，同时经制热的水用于对气动机J的输入压力工质加热使其汽化以增加气动机J的输入压力工质的压力，从而大幅提高了气动机J的工质输入端与工质输出端之间(即气动机J的输入压力工质气体与输出压力工质气体即输出乏汽之间)的压力差，进而使气动机J的输出动力增强、发电增加。在这里，盐水在一循环回路中循环，而水在另一循环回路中循环，不会将能量排放到整体换能系统的外部，从而避免了能量损失，提高了整体系统的能效比。此外，盐水在对气动机J的输出压力工质气体进行冷凝时，也 是盐水吸收输出压力工质气体中的热量进行储能的过程，所储存的热能能够用于供热泵的工质吸热，从而避免了系统内的能量损失。而且，热泵I在对盐水进行制冷时产生的“废热”被热泵I用于对水进行加热而得以利用，整个系统内不存在废热。
在以上实施例中，用于盐水的循环回路可以由蒸发器A、流体储罐E、冷凝器C和流体储罐G通过管路依次连接构成，而且流体储罐G与蒸发器A也通过管路连接，从而形成封闭的循环回路，在管路中需要位置设置泵送装置(例如水泵4)来驱动盐水在循环回路中循环流动，例如可以在蒸发器A与流体储罐E之间的管路上设置水泵4，用于将蒸发器A中被冷却后的盐水输送到流体储罐E中储存；例如可以在流体储罐E与冷凝器C之间的管路上设置水泵4，用于将来自流体储罐E的盐水输送到冷凝器C中；还例如，也可以在流体储罐G与蒸发器A之间的管路上设置水泵，用于将盐水从流体储罐G输送到蒸发器A中。本发明对此没有限制，可以根据实际需要在指定管路中设置水泵。
类似的，用于水的循环回路可以由冷凝器B、流体储罐F、蒸汽发生器D和流体储罐H通过管路依次连接构成，且流体储罐H与冷凝器B也通过管路连接，从而形成封闭的循环回路，在管路中需要位置设置泵送装置(例如水泵4)来驱动水在循环回路中循环流动。例如可以在冷凝器B与流体储罐F之间的管路上设置水泵4，用于将冷凝器B中被加热后的水输送到流体储罐F中储存；例如可以在流体储罐F与蒸汽发生器D之间的管路上设置水泵4，用于将来自流体储罐F的水输送到蒸汽发生器D中；还例如，也可以在流体储罐H与冷凝器B之间的管路上设置水泵，用于将水从流体储罐H输送到冷凝器B中。本发明对此没有限制，可以根据实际需要在指定管路中设置水泵。
在本发明中，在其中一个循环回路中采用盐水作为循环流体，在另一个循环回路中采用水(即普通淡水)作为循环流体，但是本发明不限于采用盐水和水作为循环流体，在不冲突的情况下，也可以采用别的流体，例如别的类型的液体甚至气体，只要其能够在所需工作温度下保持为流体状态以便于循环流动，以便能够与热泵的工质和气动机的压力工质配合在指定温度下进行热交换即可。本领域技术人员完全可以根据系统中采用的热泵工质的类型、压力、工作温度等以及气动机采用的压力工质的类型、压力、工作温度等，确定适合于在上述循环回路中循环的流体。本发明各实施例中仅以采用盐水和水作为循环流体为例进行说明。之所以采用盐水作为第一流体，是因为需 要其在零度以下也能保持流动性，而且来源广泛，成本低廉；另外，当提及“水”时，是指具有0℃冰点的普通淡水。
如图1所示，流体储罐G和流体储罐E在用于盐水的循环回路中分别用于储存不同温度的盐水，流体储罐H和流体储罐F在用于水的另一循环回路中分别用于储存不同温度的水。
流体储罐G用于储存对气动机J的输出压力工质气体进行冷凝而升温后的盐水，此时盐水的温度一般升温到零度以上，例如可以是0℃至20℃，或者为0℃至12℃，优选为12℃，当然也可以根据需要设为其它温度。热泵I用于利用其工质从来自流体储罐G的盐水中吸收热量而对盐水制冷，且流体储罐E用于储存经制冷的盐水，此时盐水的温度一般制冷到零度以下，例如可以是-20℃至0℃，或者为-12℃至0℃，优选为-12℃，当然也可以根据需要设为其它温度。
流体储罐H用于储存对气动机J的输入压力工质进行加热而降温后的水，此时水的温度一般为20℃至60℃，例如30℃至50℃，例如35℃至45℃，优选为40℃，当然也可以根据需要设为其它温度。热泵I用于利用其工质对来自流体储罐H的水进行加热，且流体储罐F用于储存经加热的水，此时水的温度一般为90℃至60℃，例如80℃至65℃，优选为75℃，当然也可以根据需要设为其它温度。
这里，热泵I的工质例如采用CO 2，而气动机J的压力工质例如采用氨。当然这仅为举例说明，热泵I的工质和气动机J的压力工质也可以采用其它类型媒介，只要能够在设定温度下实现蒸发和冷凝从而与外部的流体(例如盐水或水)进行热交换即可。例如，气动机J的压力工质也可以采用氟利昂。
在热泵I采用CO 2作为工质(冷媒)跨临界运行的情况下，为了使蒸发器A得到较高的制冷能效比，使蒸发器A将盐水制冷到约-12℃是较佳的，此时制冷能效比为2左右。热泵I也可以采用其它类型的工质，只要允许热泵I能够从蒸发器A中的盐水中吸收热量并且对冷凝器B中的水释放热量。
为了保证热泵在冷凝器B中对水进行制热时的高能效比，流体储罐H中水的温度优选为40℃；流体储罐F中水的温度优选为75℃，在这些温度条件下，热泵I对水制热的能效比大约为3。
在气动机J的压力工质采用液氨时，例如采用环保型制冷剂液氨时，当蒸汽发生器D管程入口的水的温度为75℃且管程出口的水的温度为40℃时，液氨在蒸汽发生器D壳程中汽化产生的蒸汽压为16.7KG。此时，如果冷凝器 C管程入口的盐水温度为-12℃而管程出口的盐水温度为12℃，所产生的气动机J的背压为大约6.7KG，因此本系统中在气动机J上可获得约10KG的净压差，其相比现有技术得到显著提高，从而提高了气动机J的输出动力，在气动机J用于驱动发电机进行发电的情况显著提高了发电量，当然，根据实际实现时流入蒸汽发生器D中的水的温度、流入冷凝器C中的盐水的温度等，本领域技术人员能够选择适当的其它工质作为气动机J的压力工质，本发明对此不作限制。
本发明实施例中的系统中的各流体储罐、蒸发器、冷凝器、蒸汽发生器、管路、阀门等优选都是绝热的，以避免与外界发生不期望的热交换。
下面具体描述气动机J的输出压力工质气体在冷凝器C中冷凝后返回蒸汽发生器D作为气动机J的输入压力工质的示例性过程。
如图1和图2所示，本实施例的换能系统还可以包括工质储液罐14，其与第一冷凝器C相比位于更低位置且通过阀门13与第一冷凝器C流体连通，并且通过阀门18与所述蒸汽发生器D流体连通。其中，当阀门13处于打开状态时，阀门18处于关闭状态，使得冷凝器C与工质储液罐14连通，同时保持工质储液罐14与蒸汽发生器D断开连通，从而使在冷凝器C中冷凝所得压力工质液体可以利用重力(也可利用泵送装置)流入工质储液罐14中；并且，当工质储液罐14中的液位高于预定高液位阈值19时，使阀门13变为关闭状态且使阀门18变为打开状态，使得工质储液罐14与冷凝器C断开连通而与蒸汽发生器D连通，从而能使工质储液罐14中收集的压力工质液体返回蒸汽发生器D中以便后续被蒸发作为气动机J的输入压力工质气体。
此外，当工质储液罐14中的液位低于预定低液位阈值20时，阀门13变为打开状态且阀门18变为关闭状态，使工质储液罐14与蒸汽发生器D断开连通而与冷凝器C重新连通，使得冷凝器C中冷凝所得压力工质液体能够流入工质储液罐14中，其中预定低液位阈值20低于预定高液位阈值19。在这里，阀门13和阀门18可以为电动阀，由感测工质储液罐14中液位的传感器15在感测到该液位高于预定高液位阈值19或低于预定低液位阈值20时如上所述驱动而打开和关闭。
在本实施例的另一实现方式中，阀门13和阀门18可以为单向止回阀，阀门13打开时，允许压力工质液体沿着从冷凝器C到工质储液罐14的方向流动；当阀门18打开时，允许压力工质液体沿着从工质储液罐14到蒸汽发生器D的方向流动。此时，工质储液罐14还可以通过与阀门13所处管路不 同的管路与冷凝器C流体连通，该不同管路中包含串接的阀门12和气动发电机11，能够控制工质储液罐14中的压力工质液体上方的压力工质气体流动到冷凝器C中；另外，工质储液罐14还通过与阀门18所处管路不同的管路与蒸汽发生器D流体连通，该不同管路中包含串接的阀门16和储气罐17，该储气罐17连接于蒸汽发生器D与阀门16之间且用于将来自蒸汽发生器D的汽化的气动机压力工质气体与其携带的气动机压力工质液体彼此分离以及必要时暂时储存汽化的气动机压力工质气体，阀门16能够控制蒸汽发生器D中产生的压力工质气体流动到工质储液罐14中。在这里，阀门12和阀门16为电动阀，受液位传感器15的感测信号的控制；储气罐17也可以使用其它具有液气分离作用的装置来替代。
下面结合图2所示分布式换能系统的局部放大示意图，描述该实施例的以上另一实现方式中工质储液罐14及相关阀门的工作过程。当工质储液罐14中的液位高于预定高液位阈值19时，液位传感器15感测到液位高于预定高液位阈值19，将产生电信号用于驱动电动阀门12由打开状态变为关闭状态而驱动电动阀门16由关闭状态变为打开状态，此时，储气罐17中的高压气体(即蒸汽发生器D中汽化产生的压力工质气体)经过阀门16进入工质储液罐14中使得工质储液罐14中的压力增大，从而引起单向阀门13关闭，并且使得单向阀门18由于工质储液罐14中的压力工质重力作用而打开，从而使得工质储液罐14与蒸汽发生器D连通，压力工质液体能够回流到蒸汽发生器D中。当工质储液罐14中的液位低于预定低液位阈值20时，液位传感器15液位低于预定低液位阈值20，将产生电信号用于驱动电动阀门12由关闭状态变为打开状态而驱动电动阀门16由打开状态变为关闭状态，此刻，工质储液罐14内部的压力大于冷凝器C壳程内部(其供气动机J的压力工质气体和液体从中流过)的压力，从而可以利用该压力差驱动气动发电机11发电，所产生的电优选用于通过导线23使加热管22升温，从而对流体储罐F中的水进行辅助加热，将热量储存于流体储罐F中。而且，随着工质储液罐14内部的压力降低，单向阀门13由于冷凝器C中压力工质液体的重力作用而由关闭状态变为打开状态；此时，由于蒸汽发生器D壳程内部(其供气动机J的压力工质液体和气体从中流过)的压力大于工质储液罐14内部的压力，使得单向阀门18由打开状态变为关闭状态，从而工质储液罐14与蒸汽发生器D断开连通。此方式比传统上利用电泵来回流工质的方式节省大量电力，而且耐高压、不泄漏、效率更高。
在本发明实施例的分布式换能系统中，所述热泵I包括电动机8以及由该电动机驱动的压缩机，来自流体储罐H的至少一部分水用于对该电动机8进行水冷，且在水冷后返回流体储罐F中；和/或，气动机J与发电机连接以驱动发电机，来自流体储罐H的至少一部分水用于对发电机进行水冷，并且在水冷后返回流体储罐F中。通过这种方式，使得系统内设备(包括电动机和发电机等)的机械运动产生的热量也能得以储存和利用，避免废热产生。
下面结合图1至3描述根据本发明实施例的分布式换能方法。图3示出了根据本发明实施例的分布式储能换能方法的示意图。如图3所示，本发明实施例的分布式换能方法可以包括：
利用热泵I的工质从循环回路中的盐水中吸收热量而对盐水制冷，并且利用热泵I对吸收热量后的工质进行压缩以进一步提高工质的温度，用于利用其工质对另一循环回路中的水进行加热；
输送经加热的水用于对气动机J的输入压力工质液体进行加热使其汽化成压力工质气体用于致动所述气动机J，并且对输入压力工质进行加热而降温后的水被热泵I的工质重新加热以用于重新对气动机J的输入压力工质液体进行加热，从而使得水在所述另一循环回路中被循环加热和降温；
输送经制冷的盐水用于对气动机J的输出压力工质气体进行冷凝，并且对气动机J的输出压力工质气体进行冷凝而升温后的盐水被热泵I的工质重新吸收热量而制冷以用于重新对气动机J的输出压力工质气体进行冷凝，从而使得盐水在循环回路中被循环制冷和升温。
在本发明实施例中，所述循环回路分别用于使盐水和水在其中单向循环，与以上实施例中的循环回路具有相同的含义。
热泵I的工质可以从来自流体储罐G的盐水中吸收热量而对盐水制冷，且经制冷的盐水被输送到流体储罐E中。热泵I还可以对其吸收热量后的工质进行压缩以进一步提高工质的温度用于对来自流体储罐H的水进行加热，经加热的水被输送到流体储罐F中。来自流体储罐F的经加热的水可以被输送用于对气动机J的输入压力工质进行加热使其汽化成压力工质气体用于致动该气动机J，并且对输入压力工质加热后的水被输送回流体储罐H。来自流体储罐E的经制冷的盐水被输送用于对气动机J的输出压力工质气体进行冷凝，然后返回到流体储罐G中。
本发明实施例中的换能方法中的制冷和加热可以通过冷凝器和蒸发器实现。如图1所示，可以使来自流体储罐E的经制冷的第一流体流经冷凝器 C的管程，从而对流入冷凝器C的壳程中的、气动机J的输出压力工质气体(例如氨气)进行冷凝得到压力工质液体(即液氨)，该压力工质液体返回蒸汽发生器D作为气动机J的输入压力工质(即液氨)。来自流体储罐F的经加热的水可以用于在流经蒸汽发生器D的管程时对蒸汽发生器D的壳程内的、气动机J的输入压力工质进行加热使其汽化成压力工质气体从而致动该气动机J。
在根据本发明实施例的换能方法中，可以使热泵I的工质流经蒸发器A的壳程，从流入蒸发器A的管程中的、来自流体储罐G的盐水中吸收热量而蒸发，从而对盐水制冷。热泵I的压缩后的工质可以流入冷凝器B的壳程中对流入冷凝器B的管程中的、来自流体储罐H的水进行加热而冷凝，然后被输送并返回蒸发器A。在不冲突的情况下，本发明中的“壳程”和“管程”也可以根据实际应用而互换。
在本实施例中，用于盐水的循环回路和用于水的循环回路的构造可以具有与以上实施例中所述相同的含义。在本发明中，在其中一个循环回路中采用盐水作为循环流体，在另一个循环回路中采用水(即普通淡水)作为循环流体，但是本发明不限于采用盐水和水作为循环流体，在不冲突的情况下，也可以采用别的流体，例如别的类型的液体甚至气体，只要其能够在所需工作温度下保持为流体状态以便于循环流动，以便能够与热泵的工质和气动机的压力工质配合在指定温度下进行热交换即可。本领域技术人员完全可以根据系统中采用的热泵工质的类型、压力、工作温度等以及气动机采用的压力工质的类型、压力、工作温度等，确定适合于在上述循环回路中循环的流体。本发明各实施例中仅以采用盐水和水作为循环流体为例进行说明。之所以采用盐水作为第一流体，是因为需要其在零度以下也能保持流动性，而且来源广泛，成本低廉；另外，当提及“水”时，是指具有0℃冰点的普通淡水。
流体储罐G用于储存对气动机J的输出压力工质气体进行冷凝而升温后的盐水，此时盐水的温度一般升温到零度以上，例如可以是0℃至20℃，或者为0℃至12℃，优选为12℃，当然也可以根据需要设为其它温度。热泵I用于利用其工质从来自流体储罐G的盐水中吸收热量而对盐水制冷，且流体储罐E用于储存经制冷的盐水，此时盐水的温度一般制冷到零度以下，例如可以是-20℃至0℃，或者为-12℃至0℃，优选为-12℃，当然也可以根据需要设为其它温度。
流体储罐H用于储存对气动机J的输入压力工质进行加热而降温后的水， 此时水的温度一般为20℃至60℃，例如30℃至50℃，例如35℃至45℃，优选为40℃，当然也可以根据需要设为其它温度。热泵I用于利用其工质对来自流体储罐H的水进行加热，且流体储罐F用于储存经加热的水，此时水的温度一般为90℃至60℃，例如80℃至65℃，优选为75℃，当然也可以根据需要设为其它温度。
在这里，热泵I的工质例如采用CO 2，而气动机J的压力工质例如采用氨。当然这仅为举例说明，热泵I的工质和气动机J的压力工质也可以采用其它类型媒介，只要能够在设定温度下实现蒸发和冷凝从而与外部的流体(例如盐水或水)进行热交换即可。例如，气动机J的压力工质也可以采用氟利昂。
在热泵I采用CO 2作为工质(冷媒)跨临界运行的情况下，为了使蒸发器A得到较高的制冷能效比，使蒸发器A将盐水制冷到约-12℃是较佳的，此时制冷能效比为2左右。热泵I也可以采用其它类型的工质，只要允许热泵I能够从蒸发器A中的盐水中吸收热量并且对冷凝器B中的水释放热量。
为了保证热泵在冷凝器B中对水进行制热时的高能效比，流体储罐H中水的温度优选为40℃；流体储罐F中水的温度优选为75℃，在这些温度条件下，热泵I对水制热的能效比大约为3。
在气动机J的压力工质采用液氨时，例如采用环保型制冷剂液氨时，当蒸汽发生器D管程入口的水的温度为75℃且管程出口的水的温度为40℃时，液氨在蒸汽发生器D壳程中汽化产生的蒸汽压为16.7KG。此时，如果冷凝器C管程入口的盐水温度为-12℃而管程出口的盐水温度为12℃，所产生的气动机J的背压为大约6.7KG，因此本系统中在气动机J上可获得约10KG的净压差，其相比现有技术得到显著提高，从而提高了气动机J的输出动力，在气动机J用于驱动发电机进行发电的情况显著提高了发电量，使得发电机的能效比能够达到5左右。当然，根据实际实现时流入蒸汽发生器D中的水的温度、流入冷凝器C中的盐水的温度等，本领域技术人员能够选择适当的其它工质作为气动机J的压力工质，本发明对此不作限制。
下面描述根据本发明实施例的换能方法中将气动机J的输出压力工质气体冷凝所得压力工质液体返回蒸汽发生器D作为气动机J的输入压力工质的过程。
具体而言，在冷凝所得压力工质液体返回蒸汽发生器D作为气动机J的输入压力工质之前，所述方法还可以包括：
使冷凝器C与工质储液罐14连通，同时保持工质储液罐14与蒸汽发生 器D断开连通，从而使冷凝所得压力工质液体流入工质储液罐14中，并且，当工质储液罐14中的液位高于预定高液位阈值19时，使工质储液罐14与冷凝器C断开连通，并且与蒸汽发生器D连通，从而能够使工质储液罐14中冷凝所得压力工质液体返回蒸汽发生器D中。
此外，当工质储液罐14中的液位低于预定低液位阈值20时，使工质储液罐14与蒸汽发生器D断开连通而与冷凝器C重新连通，使得冷凝所得压力工质液体能够流入工质储液罐14中，其中预定低液位阈值20低于预定低液位阈值。
在工质储液罐14与冷凝器C重新连通时，还可以利用工质储液罐14内部与冷凝器C壳程内部之间的压力差驱动气动发电机11发电，所产生的电优选用于对流体储罐F中的水进行辅助加热。
如果热泵I包括电动机8以及由该电动机8驱动的压缩机，气动机J与发电机连接以驱动发电机，则为了将系统中的机械运动产生的热量加以再利用，根据本发明实施例的换能方法还可以包括：将来自流体储罐H的至少一部分水用于对电动机8进行水冷，并且在水冷后被输送回流体储罐F中；并且，将来自流体储罐H的至少一部分水用于对发电机进行水冷，并且在水冷后被输送回流体储罐F中。
与上述换能系统中类似，流体储罐G、流体储罐E、流体储罐H、流体储罐F、工质储液罐14、蒸发器A、蒸汽发生器D、冷凝器C和/或冷凝器B可以是绝热的。
在根据本发明实施例的以上换能方法中，对循环回路、盐水和水等流体、热泵的工质、气动机的压力工质的描述与以上所述换能系统中所述一致，在此不再赘述。
下面结合根据本发明实施例的换能系统和方法在发电领域中的具体应用，进一步说明本发明。
该具体应用的整体思路是：在夜间，借助热泵，利用夜间谷电以冰水及热水为载体，将热量(包括显热和潜热)储存于流体储罐E、F中，直至谷电时间结束，此为夜间储能模式。在白天采用发电模式，即，将储存于流体储罐E、F中的冷热综合利用进行发电。夜间储能模式和白天发电模式交替循环进行。
1、夜间储能模式具体说明
在人们的惯常思维中，产生废热是非常普遍的情况，很多时候并不会对 废热加以利用。例如以空调制冷为例，夏天室内需要制冷，但空调室外机大量散热，此热量被视为废热，是人们所抛弃的。然而，在本发明中没有真正的“废热”，而是通过热泵，以水为载体，将“废热”蓄热于大型流体储罐F中，供白天加热蒸汽发生器D中的压力工质(例如液氨或氟利昂)产生高压蒸汽，驱动气动机，实现变废为宝。此时，制热能效比(COP)为3。
从另一角度来说，以空调制热为例，冬天室内则需制热，空调室外机有大量冷量产生，同样是人们所抛弃的。然而，在本发明中没有真正的“废冷”，而是通过热泵，以盐水为载体，将“废冷”蓄冷于大型流体储罐E中，供白天用于冷凝气动机C的乏汽，此时蓄冷COP为2。
也就是说，人们通常不是单纯用热就是单纯用冷，并没有将冷热同时利用，而冷热都是能量。本发明的特点在于二者同时协同使用，能效比很高。
2、白天发电模式说明
传统火力发电时，高温高压蒸汽膨胀做功后的乏汽需冷凝成液体，此时巨大的冷凝热被排掉，此热量等同于同质量水的汽化热(潜热)，而发电系统对这一部分的热量无法利用，所以导致整个发电系统效率大幅下降，超临界发电机组效率也不超过45％。而本发明中，气动机的高压工质气体(例如氨气或氟利昂气体)在气动机中膨胀做功后，乏汽排入冷凝器C中，所不同的是产生的大量冷凝热被来自流体储罐E的冰水所吸收而储存，并不丢失，以备夜间在蒸发器A中被吸收加以利用。所以本发明保存并利用了气动机工质的冷凝热。同时利用来自流体储罐E的冰水大幅度降低气动机排气压力，增加气动机输入端与输出端之间的压力差，使气动机动力增强且发电增加。
在具体的示例性实现中，当热泵I夜间利用谷电工作时，管壳式蒸发器A壳程中的工质(即，制冷剂)沸腾蒸发，温度下降，产生的冷量传递给管程中的温水1，同时吸收其热量，将温水1制成﹣12℃冰水储存于流体储罐E中，蒸发器A中的制冷剂蒸汽经热泵I的压缩机排入冷凝器B中冷凝成液体制冷剂，同时放出热量然后经管道2返回蒸发器A中，完成一个制冷循环。冷凝器B在冷凝时发出的热量传递给冷凝器B管程中的低温水3，使其温度升高至75℃，并储存于流体储罐F中备用，从而完成夜间储能模式。
早晨8点以后，水泵4开始工作，流体储罐F中的高温水进入蒸汽发生器D中，对其壳程中的液氨加热升压产生高压氨蒸汽经管道5进入气动机J中膨胀做功，带动发电机发电。
气动机J中产生的乏汽经管道6进入冷凝器G中冷凝放热，同时加热从 流体储罐E中过来的﹣12℃的低温盐水，盐水被温升至0-12℃，储存于流体储罐G中，以备夜间使用，同时降低气动机J的排气压力，增加气动机的工质输入端与工质输出端之间的压差，增加发电量。此时冷凝器C中的氨液提被输送回蒸汽发生器D中，完成一个工作循环，实现白天发电模式。
本发明的分布式换能系统可用于风光蓄能、谷电储能、火力发电等领域，本发明对此不作限制。
上述实施例的分布式换能方法和系统中，热泵的工质与气动机的工质是间接进行换热，即，借助于第一循环回路及其介质以及第二循环回路及其介质进行换热。但是，发明人还发现，在有些应用场景中可能不需要储能环节，所以在以上结合图1至图3描述的分布式储能方法和分布式储能系统中，能够将其中的储能环节去除，即将分布式换能方法和分布式换能系统中的第一循环回路和/或第二循环回路去掉，从而改为热泵的工质与气动机的工质直接进行热交换，则得到另外的换能方法和换能系统，其能够实现输入能量的即时放大输出。下面结合附图4和图5进行具体描述，其中与图1和图2中相同的标号表示与图1和图2中相同功能的部件，下面不对其进行详细描述。
如图4所示，示出了根据本发明一变型实施例的换能系统的示意图，该换能系统可以包括热泵I、气动机J、蒸发式冷凝器K和蒸发式冷凝器L，其中热泵I分别通过管路与蒸发式冷凝器K以及蒸发式冷凝器L流体连通并且蒸发式冷凝器K与蒸发式冷凝器L通过管路30流体连通，使得热泵I的工质能够经由蒸发式冷凝器K、管路30以及蒸发式冷凝器L循环流动；并且，气动机J分别通过管路与蒸发式冷凝器K以及蒸发式冷凝器L流体连通并且蒸发式冷凝器K与蒸发式冷凝器L还通过管路40流体连通，使得气动机J的压力工质能够经由蒸发式冷凝器K、管路40以及蒸发式冷凝器L循环流动。
热泵I的工质用于在蒸发式冷凝器K中从气动机J的输出压力工质气体吸收热量而将气动机J的输出压力工质气体冷凝得到压力工质液体，并且该压力工质液体被输送作为气动机J的输入压力工质。
热泵I用于对吸收热量后的工质进行压缩以使其升温从而用于在蒸发式冷凝器L中对气动机J的输入压力工质进行加热使其汽化成压力工质气体，该压力工质气体用于致动气动机J然后由气动机J输出成为气动机J的输出压力工质气体。
在蒸发式冷凝器L中对气动机J的输入压力工质加热而降温后的热泵I的工质被用于输送到蒸发式冷凝器K中重新从气动机J的输出压力工质气体吸收热量，从而使得热泵I的工质循环进行上述吸热、升温和降温的过程。
作为示例，热泵I的工质可以从蒸发式冷凝器K的管程中流过而从蒸发 式冷凝器K的壳程中流过的气动机J的压力工质中吸热而气化，同时从蒸发式冷凝器K的壳程流过的气动机J的输出压力工质气体因放热而冷凝。
例如，热泵I的经压缩的工质在从蒸发式冷凝器L的管程中流过时放热冷凝，而气动机J的输入压力工质用于在蒸发式冷凝器L的壳程中吸热气化。
上述变型实施例中的换能系统还可以包括工质储液罐14，工质储液罐14与蒸发式冷凝器K相比位于更低位置且通过阀门13与蒸发式冷凝器K流体连通，并且通过阀门18与蒸发式冷凝器L流体连通。
工质储液罐14及相关阀门的工作方式与上述实施例中相同。例如，在系统工作时，当阀门13处于打开状态时，阀门18处于关闭状态，使蒸发式冷凝器K与工质储液罐14连通，同时保持工质储液罐14与蒸发式冷凝器L断开连通，从而使蒸发式冷凝器K中冷凝所得压力工质液体流入工质储液罐14中，从而工质储液罐14中的压力工质液体液位越来越高。而当工质储液罐14中的压力工质液体液位高于预定第一阈值时，阀门13变为关闭状态且阀门18变为打开状态，使工质储液罐14与蒸发式冷凝器K断开连通，并且与蒸发式冷凝器L连通，从而能够使工质储液罐14中冷凝所得压力工质液体返回蒸发式冷凝器L中。
相反，当工质储液罐14中的液位低于预定第二阈值时，阀门13变为打开状态且阀门18变为关闭状态，使工质储液罐14与蒸发式冷凝器L断开连通而与蒸发式冷凝器K重新连通，使得蒸发式冷凝器K中冷凝所得压力工质液体能够流入工质储液罐14中。在这里，预定第二阈值低于预定第一阈值。
为了进一步回收系统中的能量，工质储液罐14还可以通过与阀门13所处管路不同的管路与蒸发式冷凝器K流体连通，该不同的管路中包含串接的阀门12和辅助气动机11’；另外，工质储液罐14还通过与阀门18所处管路不同的管路与蒸发式冷凝器L流体连通，该不同的管路中包含串接的阀门16和储气罐17，该储气罐17连接于蒸发式冷凝器L与阀门16之间且用于将来自蒸发式冷凝器L的、气动机J的汽化的气动机压力工质气体与其携带的气动机压力工质液体彼此分离以及必要时暂时储存汽化的气动机压力工质气体。储气罐17也可以使用其它具有液气分离作用的装置来替代。本领域技术人员也可以理解，在管道5中也会根据需要设置必要的液气分离装置以使得来自蒸发式冷凝器L的气化的气动机压力工质气体会先与来自蒸发式冷凝器L的气动机压力工质液体分离然后被送往气动机J。可以理解，也可以从储气罐17引出管路以连接气动机J的压力工质入口，而不采用管路5，从而无需另外设置液气分离装置而共用储气罐17进行液气分离。
在系统运行时，当工质储液罐14中的液位高于预定第一阈值时，阀门12由打开状态变为关闭状态而阀门16由关闭状态变为打开状态；当工质储液罐14中的液位低于预定第二阈值时，阀门12由关闭状态变为打开状态而阀门16由打开状态变为关闭状态，从而利用工质储液罐14内部与蒸发式冷凝器K内部之间的压力差驱动辅助气动机11’，且在工质储液罐14内部与蒸发式冷凝器K内部之间压力平衡后，阀门13由关闭状态变为打开状态。
在上述变型例中，阀门13和阀门18为单向阀，阀门12和阀门16为电动阀。
如图6所示，在上述变型例中，所述系统还可以包括：辅助热泵26，其由辅助气动机11’驱动，使得热泵26从蒸发式冷凝器K抽取热泵I的至少一部分工质并将其压缩以提高所述至少一部分工质的温度，然后将提高温度后的所述至少一部分工质与被热泵I压缩而升温后的工质汇合流入蒸发式冷凝器L中。利用辅助气动机11’来驱动该辅助热泵26，能够充分利用辅助气动机11’输出的能量，并且该辅助热泵26通过从蒸发式冷凝器K中抽取热泵I的工质而进一步降低了蒸发式冷凝器K中气动机J的输出压力工质气体的温度，并且经辅助热泵26压缩而升温后的工质进一步增加了输送至蒸发式冷凝器L的热量，也就是说，通过辅助热泵26、蒸发式冷凝器K和蒸发式冷凝器L，进一步增大了气动机J的压力工质气体输入端与压力工质气体输出端之间的压力差，从而进一步增大了气动机J的功率。
在进一步变型中，上述系统还可以包括液体罐27，如图6所示，其中示出了根据本发明又一变型实施例的换能系统的示意图。在这里，工质储液罐14为能够在两种工质之间进行换热的管壳式储液罐，气动机J的压力工质液体和压力工质气体可以在该管壳式储液罐的壳程中流动。从辅助热泵26输出的工质和/或从热泵I输出的工质可以用于加热液体罐27中的液体(例如水)，并且在管壳式储液罐中的压力工质液体被输送到蒸发式冷凝器L之前，来自液体罐27中的经加热的液体被输送到该管壳式储液罐的管程中用于对管壳式储液罐的壳程中的压力工质液体进行加热。
当工质储液罐14中的压力工质液体的温度与蒸发式冷凝器L中的压力工质液体和/或气体的温度差别较大时，在工质储液罐14中的压力工质液体进入蒸发式冷凝器L时会影响从蒸发式冷凝器L输送给气动机J的压力工质气体的压力稳定性，从而可能影响气动机J的输出功率稳定性。因此，发明人进一步以上方法来对工质储液罐14中的压力工质液体进行预加热，从而减小 或避免其在进入蒸发式冷凝器L中时影响蒸发式冷凝器L中的压力工质的温度，从而使得气动机J的输入压力工质气体的压力更加稳定。
下面通过示例给出以上方案的更多细节。举例而言，当工质储液罐14(在该示例中为管壳式储液罐，或者其它能够在不同介质之间换热的装置)中的气动机压力工质的液位(由例如液位计测量)高于预定高液位阈值19时，在使得储液罐14与蒸发式冷凝器L连通之前，触发与液体罐27流体连通的泵24启动以将液体罐27中的热液体输送到储液罐14的管程中，用于将储液罐14壳程中的气动机压力工质液体(例如0℃的CO 2液体)升温(例如升温至30℃，压力达到72㎏/cm 2)。在储液罐14中的压力工质液体达到预定温度或者压力后(由温度或压力传感器25检测)，则触发泵24停止运转，并且允许储液罐14中的压力工质液体进入蒸发式冷凝器L中，此时阀门16和阀门18打开，阀门12和阀门13关闭，使储液罐14与蒸发式冷凝器K断开连通而与蒸发式冷凝器L形成连通，则利用重力原理，储液罐14中升温后的压力工质液体(即，CO 2液体)自动落入蒸发式冷凝器L中，这样在储液罐14和蒸发式冷凝器L中的压力工质液体温度相近或一致的情况下，有利于维持蒸发式冷凝器L中输出的蒸汽压力稳定而波动小，从而使气动机转速稳定且使得其驱动的发电机输出电压及电流稳定。随着储液罐14中的气动机压力工质的液位下降，且下降至低于预定低液位阈值20时,则阀门16和18关闭，此时储液罐14中的压力与蒸发式冷凝器L中的压力是一致的，即远高于蒸发式冷凝器K中的压力，所以此时将阀门12打开，储液罐14中剩余的压力工质气体(例如高压CO 2气体)会进入辅助气动机11’以驱动其运转，进一步带动辅助热泵26工作，抽取蒸发式冷凝器K的管程中的热泵工质气体，使蒸发式冷凝器K的壳程中的气动机J的压力工质进一步制冷。
根据本发明的另一变型例，还提供了一种换能方法，如图5所示，该方法可以包括：
利用热泵I的工质从气动机J的输出压力工质气体吸收热量而将气动机J的输出压力工质气体冷凝得到压力工质液体，并将压力工质液体输送作为气动机J的输入压力工质；在这里，热泵I的工质从气动机J的输出压力工质气体吸收热量在实现时可以是这两种工质在换热装置中直接换热，或者也可以是间接方式，即，热泵I的工质通过换热装置从其它介质吸收热量，并且所述其它介质通过另外的换热装置从气动机J的输出压力工质气体吸收热量，本发明对此不作具体限制。
利用热泵I对吸收热量后的工质进行压缩以使工质升温从而用于对气动 机J的输入压力工质进行加热使其汽化成压力工质气体，该压力工质气体用于致动气动机J然后由气动机J输出作为气动机J的输出压力工质气体；在这里，类似地，热泵I升温后的工质对气动机J的输入压力工质进行加热在实现时可以是这两种工质在换热装置中直接换热，或者也可以是间接方式，即，热泵I升温后的工质通过换热装置加热其它介质，并且所述其它介质通过另外的换热装置加热气动机J的输入压力工质，本发明对此不作具体限制。
对输入压力工质进行加热而降温后的热泵I的工质被输送用于重新从气动机J的输出压力工质气体吸收热量，从而使得热泵I的工质循环进行所述吸热、升温和降温过程。
在上述方法中，可以看出热泵I的工质在循环进行所述吸热、升温和降温的过程，同时气动机J的压力工质则循环进行放热冷凝、吸热气化以及做功降温的过程。
结合图4所示，利用热泵I的工质从气动机J的输出压力工质气体吸收热量而将气动机J的输出压力工质气体冷凝可以在蒸发式冷凝器K中进行。热泵I的工质可以从蒸发式冷凝器K的管程中流过而吸热气化，而气动机J的输出压力工质气体可以流入蒸发式冷凝器K的壳程中而放热冷凝。类似地，热泵I的工质升温后用于对气动机J的输入压力工质进行加热可以在蒸发式冷凝器L中进行。热泵I的经压缩的工质可以从蒸发式冷凝器L的管程中流过而放热冷凝，而气动机J的输入压力工质在蒸发式冷凝器L的壳程中吸热气化。当然，在这里，蒸发式冷凝器K的管程和壳程中流动的介质也可以互换，只要二者之间可以如上进行热交换即可，本发明对此不作限制。
将压力工质液体输送作为气动机J的输入压力工质的方式与上述结合附图1-3所述的方式一致，下面进行简要描述。
在将压力工质液体输送作为气动机J的输入压力工质之前，该换能方法还可以包括：
使蒸发式冷凝器K与工质储液罐14连通，同时保持工质储液罐14与蒸发式冷凝器L断开连通，从而使蒸发式冷凝器K中冷凝所得压力工质液体流入工质储液罐14中，并且，
当工质储液罐14中的液位高于预定第一阈值时，使工质储液罐14与蒸发式冷凝器K断开连通，并且与蒸发式冷凝器L连通，从而能够使工质储液罐14中冷凝所得压力工质液体返回第二蒸发式冷凝器L中。
当工质储液罐14中的液位低于预定第二阈值时，则使工质储液罐14与蒸发式冷凝器L断开连通而与蒸发式冷凝器K重新连通，使得蒸发式冷凝器K中冷凝所得压力工质液体能够流入工质储液罐14中，其中预定第二阈值低 于预定第一阈值。
为了进一步重复利用系统中的能量，该换能方法还可以包括：在工质储液罐14与蒸发式冷凝器K重新连通时，利用工质储液罐14内部与蒸发式冷凝器K内部之间的压力差驱动辅助气动机11’。
为了进一步回收气动机发电过程中的废热，在根据上述两个变型例的换能系统和换能方法中，气动机(J)与发电机连接以用于驱动发电机，将热泵(I)的、从蒸发式冷凝器L输出的至少一部分降温后的工质用于对与气动机J连接的发电机进行冷却，并且在所述冷却后被输送回蒸发式冷凝器K中，从而能够将电动机运转产生的热量进行重复利用。
在该方法中也可以如结合附图6所述的系统中那样引入辅助热泵26进一步提供气动机J的工质输入端与工质输出端之间的压力差，并且对储液罐14中的气动机压力工质液体进行预加热。以下结合图6对此进行简要描述。
如图6所示，在所述方法中，还可以包括辅助热泵26，其由辅助气动机11’驱动，使得热泵26从蒸发式冷凝器K抽取热泵I的至少一部分工质并将其压缩以提高所述至少一部分工质的温度，然后将提高温度后的所述至少一部分工质与被热泵I压缩而升温后的工质汇合流入蒸发式冷凝器L中。
在进一步变型中，上述方法中还可以包括液体罐27，如图6所示。在这里，工质储液罐14为能够在两种工质之间进行换热的管壳式储液罐，气动机J的压力工质液体和压力工质气体可以在该管壳式储液罐的壳程中流动。从辅助热泵26输出的工质和/或从热泵I输出的工质可以用于加热液体罐27中的液体，并且在管壳式储液罐中的压力工质液体被输送到蒸发式冷凝器L之前，来自液体罐27中的经加热的液体被输送到该管壳式储液罐的管程中用于对管壳式储液罐的壳程中的压力工质液体进行加热。
具体地，当工质储液罐14中的气动机压力工质的液位高于预定高液位阈值19时，在使得储液罐14与蒸发式冷凝器L连通之前，触发与液体罐27流体连通的泵24启动以将液体罐27中的热液体输送到储液罐14的管程中，用于将储液罐14壳程中的气动机压力工质液体(例如0℃的CO 2液体)升温(例如升温至30℃，压力达72㎏/cm 2)。在储液罐14中的压力工质液体达到预定温度或者压力后(由温度或压力传感器25检测)，则触发泵24停止运转，并且允许储液罐14中的压力工质液体进入蒸发式冷凝器L中，此时阀门16和阀门18打开，阀门12和阀门13关闭，使储液罐14与蒸发式冷凝器K断开连通而与蒸发式冷凝器L形成连通，则利用重力原理，储液罐14中升温后的压力工质液体(即，CO 2液体)自动落入蒸发式冷凝器L中，这样在储 液罐14和蒸发式冷凝器L中的压力工质液体温度相近或一致的情况下，有利于维持蒸发式冷凝器L中输出的蒸汽压力稳定而波动小，从而使气动机转速稳定且使得其驱动的发电机输出电压及电流稳定。随着储液罐14中的气动机压力工质的液位下降，且下降至低于预定低液位阈值20时,则阀门16和18关闭，此时储液罐14中的压力与蒸发式冷凝器L中的压力是一致的，即远高于蒸发式冷凝器K中的压力，所以此时将阀门12打开，储液罐14中剩余的压力工质气体(例如高压CO 2气体)会进入辅助气动机11’以驱动其运转，进一步带动辅助热泵26工作，抽取蒸发式冷凝器K的管程中的热泵工质气体，使蒸发式冷凝器K的壳程中的气动机J的压力工质进一步制冷。
在根据上述两个变型例的换能系统和换能方法中，蒸发式冷凝器K、蒸发式冷凝器L和/或工质储液罐14可以是绝热的。当然，整个系统中各个部件、管路是否绝热，可以根据需要来决定。另外，热泵I的工质可以为氨NH 3，且气动机J的压力工质可以为二氧化碳CO 2。
在根据上述两个变型例的换能系统和换能方法中，作为示例，可以设定：在热泵I的工质入口处，氨的温度和压力分别为：0℃和3.38kg/cm 2；和/或，在热泵I的工质出口处，氨的温度和压力分别为：40℃和14.8kg/cm 2；和/或，在气动机J的压力工质入口处，CO 2的温度和压力为：40℃和96kg/cm 2；和/或，在气动机J的压力工质出口处，CO 2的温度和压力为：0℃和35kg/cm 2。以上仅为示例，本领域技术人员能够根据系统中部件的各种参数来调整各位置处的工质温度和压力，例如根据热泵I的能效比(包括制冷能效比和制热能效比)、热泵I的工质、气动机J的能效比、气动机J的压力工质、蒸汽式冷凝器的换热效率等等来进行调整，使得该换能系统能够总体上达到平衡而持久的运行。在上述工质温度和压力下，例如热泵I的能效比可以采用5.76，其制热能效比为3.36而制冷能效比为2.4。
举例而言，当输入电网电力并驱动热泵I的压缩机运转时，蒸发式冷凝器K的管程中的液氨被抽取气化，实现制冷能效比为2.4，同时产生的冷量使蒸发式冷凝器K的壳程中的CO 2气体冷凝，同时吸收CO 2冷凝热，使蒸发式冷凝器K的整体温度保持在一个稳定范围，达到平衡吸热(NH 3)平衡放热(CO 2)持久运行。
在热泵I的压缩机制冷的同时，经压缩机压缩的氨气进入蒸发式冷凝器L的管程中冷凝放热，实现制热能效比3.36，同时此热量加热蒸发式冷凝器L的壳程中的CO 2液体，使得氨气液化、CO 2气化膨胀同步进行，获得高压CO 2气体进入气动机J中膨胀做功，带动与气动机J连接的发电机发电。若气动 机发电的整体效率按35﹪计算，将获得(3.36+2.4)*35％＝2的能效比，与现有技术相比能够大幅度提高整个系统的发电效率。
从以上变型例可以看出，本换能系统和换能方法有如下优势：
1、通过使热泵的工质闭路循环系统与气动机的工质闭路循环系统直接换热，综合利用了系统中产生的热量、冷量，维持蒸发式冷凝器K和L之间的温度平衡，通过增加气动机进口压力并降低气动机排口压力，增加了气动机工质进口和工质排口之间的压差，使气动机的动力增强，发电效率增加。
2、整个系统的所有设备、管道、阀门均可采用绝热保温，无论外界气温高低，都不影响系统的运行。
3、本系统内的用电设备极少，除了两只电动阀12和16(例如为电磁阀)几乎可以没有其他用电设备，对比火力发电厂中的自用电占比10-12﹪，显著节省能耗。
4、利用辅助热泵26进一步增加了气动机J的工质输入端与工质输出端之间的压力差。
5、通过对储液罐14中的气动机压力工质液体进行预加热，有利于气动机J的输出功率稳定。
在本说明书中描述了大量具体细节。然而，能够理解，本发明的实施例可以在没有这些具体细节的情况下实施。在一些实例中，并未详细示出公知的方法、结构和技术，以避免对本说明书的理解模糊不清。
本领域那些技术人员可以理解，可以对实施例中的装置中的模块进行自适应性地改变并且把它们设置在与该实施例不同的一个或多个装置中。可以把实施例中的若干模块组合成一个模块或单元或组件，以及此外可以把它们分成多个模块或单元或组件。除了这样的特征和/或过程或者模块中的至少一些是相互排斥之外，可以采用任何组合对本说明书(包括伴随的权利要求、摘要和附图)中公开的所有特征以及如此公开的任何方法或者设备的所有过程或单元进行组合。除非另外明确陈述，本说明书(包括伴随的权利要求、摘要和附图)中公开的每个特征可以由提供相同、等同或相似目的替代特征来代替。
应该注意的是上述实施例对本发明进行说明而不是对本发明进行限制，并且本领域技术人员在不脱离所附权利要求的范围的情况下可设计出替换实施例。

Claims (38)

  1. 一种换能方法，包括：
    利用第一热泵(I)的工质吸收来自气动机(J)的输出压力工质气体的热量而将所述气动机(J)的输出压力工质气体冷凝得到压力工质液体，并将所述压力工质液体输送作为所述气动机(J)的输入压力工质；
    利用第一热泵(I)对吸收热量后的工质进行压缩以使其升温从而能够将热量输送给气动机(J)的所述输入压力工质使其加热汽化成压力工质气体，所述压力工质气体用于致动所述气动机(J)然后由所述气动机(J)输出作为所述气动机(J)的输出压力工质气体；
    将热量输送给所述输入压力工质而降温后的所述第一热泵(I)的工质被输送用于重新从气动机(J)的输出压力工质气体吸收热量，从而使得所述第一热泵(I)的工质循环进行所述吸热、升温和降温。
  2. 根据权利要求1所述的方法，其中，
    所述利用第一热泵(I)的工质吸收来自气动机(J)的输出压力工质气体的热量而将所述气动机(J)的输出压力工质气体冷凝是在第一蒸发式冷凝器(K)中进行的，优选地，所述第一热泵(I)的工质从所述第一蒸发式冷凝器(K)的管程中流过而吸热气化，而所述气动机(J)的输出压力工质气体流入所述第一蒸发式冷凝器(K)的壳程中而放热冷凝；和/或，
    所述第一热泵(I)的工质升温后将热量输送给气动机(J)的所述输入压力工质使其加热是在第二蒸发式冷凝器(L)中进行的，优选地，所述第一热泵(I)的经压缩的工质从所述第二蒸发式冷凝器(L)的管程中流过而放热冷凝，而所述气动机(J)的输入压力工质在所述第二蒸发式冷凝器(L)的壳程中吸热气化。
  3. 根据权利要求1或2所述的方法，其中，在将所述压力工质液体输送作为所述气动机(J)的输入压力工质之前，所述方法还包括：
    使所述第一蒸发式冷凝器(K)与工质储液罐(14)连通，同时保持所述工质储液罐(14)与所述第二蒸发式冷凝器(L)断开连通，从而使所述第一蒸发式冷凝器(K)中冷凝所得所述压力工质液体流入所述工质储液罐(14)中，并且，
    当所述工质储液罐(14)中的液位高于预定第一阈值时，使所述工质储液罐(14)与所述第一蒸发式冷凝器(K)断开连通，并且与所述第二蒸发式冷凝器(L)连通，从而能够使所述工质储液罐(14)中冷凝所得所述压力工质液体返回所述第二蒸发式冷凝器(L)中。
  4. 根据权利要求3所述的方法，还包括：
    当所述工质储液罐(14)中的液位低于预定第二阈值时，使所述工质储液罐(14)与所述第二蒸发式冷凝器(L)断开连通而与所述第一蒸发式冷凝器(K)重新连通，使得所述第一蒸发式冷凝器(K)中冷凝所得压力工质液体能够流入所述工质储液罐(14)中，其中所述预定第二阈值低于所述预定第一阈值。
  5. 根据权利要求4所述的方法，还包括：在所述工质储液罐(14)与所述第一蒸发式冷凝器(K)重新连通时，利用所述工质储液罐(14)内部与所述第一蒸发式冷凝器(K)内部之间的压力差驱动辅助气动机(11’)。
  6. 根据权利要求5所述的方法，其中，
    利用所述辅助气动机(11’)驱动第二热泵(26)，使得第二热泵(26)从第一蒸发式冷凝器(K)抽取第一热泵(I)的至少一部分工质并将其压缩以提高所述至少一部分工质的温度，然后将提高温度后的所述至少一部分工质与被第一热泵(I)压缩而升温后的工质汇合流入所述第二蒸发式冷凝器(L)；
    优选地，所述工质储液罐(14)为管壳式储液罐，所述气动机(J)的压力工质液体和压力工质气体在所述管壳式储液罐的壳程中流动；利用从所 述第二热泵(26)输出的工质和/或从所述第一热泵(I)输出的工质来加热液体罐(27)中的液体，并且在所述管壳式储液罐中的压力工质液体被输送到第二蒸发式冷凝器(L)之前，将来自液体罐(27)中的经加热的液体输送到所述管壳式储液罐的管程中对管壳式储液罐的壳程中的压力工质液体进行加热。
  7. 根据权利要求1-6中任一项所述的方法，其中所述第一蒸发式冷凝器(K)、所述第二蒸发式冷凝器(L)和/或所述工质储液罐(14)是绝热的。
  8. 根据权利要求1-7中任一项所述的方法，其中，
    所述热泵(I)的工质为氨NH 3，且所述气动机(J)的压力工质为二氧化碳CO 2。
  9. 一种换能系统，包括热泵(I)、气动机(J)、第一蒸发式冷凝器(K)和第二蒸发式冷凝器(L)，
    其中热泵(I)分别通过管路与第一蒸发式冷凝器(K)以及第二蒸发式冷凝器(L)流体连通并且第一蒸发式冷凝器(K)与第二蒸发式冷凝器(L)通过第一管路流体连通，使得热泵(I)的工质能够经由第一蒸发式冷凝器(K)、第一管路以及第二蒸发式冷凝器(L)循环流动；并且，气动机(J)分别通过管路与第一蒸发式冷凝器(K)以及第二蒸发式冷凝器(L)流体连通并且第一蒸发式冷凝器(K)与第二蒸发式冷凝器(L)还通过第二管路流体连通，使得气动机(J)的压力工质能够经由第一蒸发式冷凝器(K)、第二管路以及第二蒸发式冷凝器(L)循环流动，
    其中，热泵(I)的工质用于在第一蒸发式冷凝器(K)中从气动机(J)的输出压力工质气体吸收热量而将所述气动机(J)的输出压力工质气体冷凝得到压力工质液体，并且所述压力工质液体被输送作为所述气动机(J)的输入压力工质；
    热泵(I)用于对吸收热量后的工质进行压缩以使所述工质升温从而用于在第二蒸发式冷凝器(L)中对气动机(J)的所述输入压力工质进行加热 使其汽化成压力工质气体，所述压力工质气体用于致动所述气动机(J)然后由所述气动机(J)输出作为所述气动机(J)的输出压力工质气体；
    在第二蒸发式冷凝器(L)中对所述输入压力工质进行加热而降温后的所述热泵(I)的工质被用于输送到第一蒸发式冷凝器(K)中重新从气动机(J)的输出压力工质气体吸收热量，从而使得所述热泵(I)的工质循环进行所述吸热、升温和降温。
  10. 根据权利要求9所述的系统，其中，
    所述热泵(I)的工质用于从所述第一蒸发式冷凝器(K)的管程中流过而吸热气化，而所述气动机(J)的输出压力工质气体用于流入所述第一蒸发式冷凝器(K)的壳程中而放热冷凝；和/或，
    所述热泵(I)的经压缩的工质用于从所述第二蒸发式冷凝器(L)的管程中流过而放热冷凝，而所述气动机(J)的输入压力工质用于在所述第二蒸发式冷凝器(L)的壳程中吸热气化。
  11. 根据权利要求9或10所述的系统，还包括工质储液罐(14)，其与所述第一蒸发式冷凝器(K)相比位于更低位置且通过第一阀门(13)与所述第一蒸发式冷凝器(K)流体连通，并且通过第二阀门(18)与所述第二蒸发式冷凝器(L)流体连通，
    其中，当第一阀门(13)处于打开状态时，第二阀门(18)处于关闭状态，使所述第一蒸发式冷凝器(K)与工质储液罐(14)连通，同时保持所述工质储液罐(14)与所述第二蒸发式冷凝器(L)断开连通，从而使所述第一蒸发式冷凝器(K)中冷凝所得所述压力工质液体流入所述工质储液罐(14)中，并且，
    当所述工质储液罐(14)中的液位高于预定第一阈值时，所述第一阀门(13)变为关闭状态且所述第二阀门(18)变为打开状态，使所述工质储液罐(14)与所述第一蒸发式冷凝器(K)断开连通，并且与所述第二蒸发式冷凝器(L)连通，从而能够使所述工质储液罐(14)中冷凝所得所述压力工质 液体返回所述第二蒸发式冷凝器(L)中。
  12. 根据权利要求11所述的系统，其中，
    当所述工质储液罐(14)中的液位低于预定第二阈值时，所述第一阀门(13)变为打开状态且所述第二阀门(18)变为关闭状态，使所述工质储液罐(14)与所述第二蒸发式冷凝器(L)断开连通而与所述第一蒸发式冷凝器(K)重新连通，使得所述第一蒸发式冷凝器(K)中冷凝所得压力工质液体能够流入所述工质储液罐(14)中，其中所述预定第二阈值低于所述预定第一阈值。
  13. 根据权利要求12所述的系统，其中，
    所述工质储液罐(14)还通过与所述第一阀门(13)所处管路不同的第三管路与所述第一蒸发式冷凝器(K)流体连通，所述第三管路中包含串接的第三阀门(12)和辅助气动机(11’)，
    所述工质储液罐(14)还通过与所述第二阀门(18)所处管路不同的第四管路与所述第二蒸发式冷凝器(L)流体连通，所述第四管路中包含串接的第四阀门(16)和储气罐(17)，所述储气罐(17)连接于所述第二蒸发式冷凝器(L)与所述第四阀门(16)之间且用于储存汽化的所述压力工质气体，
    当所述工质储液罐(14)中的液位高于所述预定第一阈值时，所述第三阀门(12)由打开状态变为关闭状态而所述第四阀门(16)由关闭状态变为打开状态；当所述工质储液罐(14)中的液位低于所述预定第二阈值时，所述第三阀门(12)由关闭状态变为打开状态而所述第四阀门(16)由打开状态变为关闭状态，从而利用所述工质储液罐(14)内部与所述第一蒸发式冷凝器(K)内部之间的压力差驱动辅助气动机(11’)，并且在所述工质储液罐(14)内部与所述第一蒸发式冷凝器(K)内部之间压力平衡后，所述第一阀门(13)由关闭状态变为打开状态。
  14. 根据权利要求13所述的系统，其中所述第一阀门(13)和第二阀门 (18)为单向阀，所述第三阀门(12)和第四阀门(16)为电动阀。
  15. 根据权利要求13所述的系统，还包括：
    第二热泵(26)，其由所述辅助气动机(11’)驱动，使得第二热泵(26)从第一蒸发式冷凝器(K)抽取第一热泵(I)的至少一部分工质并将其压缩以提高所述至少一部分工质的温度，然后将提高温度后的所述至少一部分工质与被第一热泵(I)压缩而升温后的工质汇合流入所述第二蒸发式冷凝器(L)；
    优选地，所述系统还包括液体罐(27)，并且所述工质储液罐(14)为管壳式储液罐，所述气动机(J)的压力工质液体和压力工质气体在所述管壳式储液罐的壳程中流动；从所述第二热泵(26)输出的工质和/或从所述第一热泵(I)输出的工质用于加热液体罐(27)中的液体，并且在所述管壳式储液罐中的压力工质液体被输送到第二蒸发式冷凝器(L)之前，来自液体罐(27)中的经加热的液体被输送到所述管壳式储液罐的管程中用于对管壳式储液罐的壳程中的压力工质液体进行加热。
  16. 根据权利要求9-15中任一项所述的系统，其中所述第一蒸发式冷凝器(K)、所述第二蒸发式冷凝器(L)和/或所述工质储液罐(14)是绝热的。
  17. 根据权利要求9-16中任一项所述的系统，其中，
    所述热泵(I)的工质为氨NH 3，且所述气动机(J)的压力工质为二氧化碳CO 2。
  18. 一种分布式换能方法，其特征在于，包括：
    利用热泵(I)的工质从在第一循环回路中循环流动的第一流体中吸收热量而对第一流体制冷；
    利用热泵(I)对吸收热量后的工质进行压缩以进一步提高工质的温度，用于对在第二循环回路中循环流动的第二流体进行加热；
    输送经加热的第二流体用于对气动机(J)的输入压力工质进行加热使其汽化成压力工质气体用于致动所述气动机(J)，并且对输入压力工质进行 加热而降温后的第二流体被热泵(I)的工质重新加热以用于重新对气动机(J)的输入压力工质进行加热，从而使得第二流体被循环加热和降温；
    输送经制冷的第一流体用于对气动机(J)的输出压力工质气体进行冷凝，并且对气动机(J)的输出压力工质气体进行冷凝而升温后的第一流体被热泵(I)的工质重新吸收热量而制冷以用于重新对气动机(J)的输出压力工质气体进行冷凝，从而使得第一流体被循环制冷和升温。
  19. 根据权利要求18所述的方法，其中，
    利用热泵(I)的工质从在第一循环回路中循环流动的第一流体中吸收热量而对第一流体制冷包括：利用热泵(I)的工质从来自第一流体储罐(G)的第一流体中吸收热量而对第一流体制冷，且经制冷的第一流体被输送到第二流体储罐(E)中；
    利用热泵(I)对吸收热量后的工质进行压缩以进一步提高工质的温度，用于对在第二循环回路中循环流动的第二流体进行加热包括：所述热泵(I)对其吸收热量后的工质进行压缩以进一步提高工质的温度用于对来自第三流体储罐(H)的第二流体进行加热，经加热的所述第二流体被输送到第四流体储罐(F)中；
    输送经加热的第二流体用于对气动机(J)的输入压力工质进行加热使其汽化成压力工质气体用于致动所述气动机(J)包括：来自所述第四流体储罐(F)的经加热的所述第二流体被输送用于对气动机(J)的输入压力工质进行加热使其汽化成压力工质气体用于致动所述气动机(J)，并且对所述输入压力工质加热后的所述第二流体被输送回所述第三流体储罐(H)；
    输送经制冷的第一流体用于对气动机(J)的输出压力工质气体进行冷凝包括：来自所述第二流体储罐(E)的经制冷的所述第一流体被输送用于对所述气动机(J)的输出压力工质气体进行冷凝，然后返回到所述第一流体储罐(G)中。
  20. 根据权利要求19所述的方法，其中，
    所述来自所述第二流体储罐(E)的经制冷的所述第一流体被输送用于对所述气动机(J)的输出压力工质气体进行冷凝，包括：使来自所述第二流体储罐(E)的经制冷的所述第一流体流经第一冷凝器(C)，从而对流入所述第一冷凝器(C)中的、所述气动机(J)的输出压力工质气体进行冷凝得到压力工质液体，所述压力工质液体返回蒸汽发生器(D)作为所述气动机(J)的所述输入压力工质；
    其中，来自所述第四流体储罐(F)的经加热的所述第二流体用于在流经所述蒸汽发生器(D)时对蒸汽发生器(D)内的、所述气动机(J)的输入压力工质进行加热使其汽化成所述压力工质气体从而致动所述气动机(J)。
  21. 根据权利要求19或20所述的方法，其中，
    所述利用热泵(I)的工质从来自第一流体储罐(G)的第一流体中吸收热量而对所述第一流体制冷，包括：使所述热泵(I)的工质流经蒸发器(A)，从流入所述蒸发器(A)中的、来自所述第一流体储罐(G)的第一流体中吸收热量而蒸发，从而对所述第一流体制冷；
    其中，热泵(I)的所述压缩后的工质流入第二冷凝器(B)中对流入第二冷凝器(B)中的、来自所述第三流体储罐(H)的第二流体进行加热而冷凝，然后被输送并返回蒸发器(A)。
  22. 根据权利要求20或21所述的方法，在所述冷凝所得压力工质液体返回蒸汽发生器(D)作为所述气动机(J)的输入压力工质之前，所述方法还包括：
    使所述第一冷凝器(C)与工质储液罐(14)连通，同时保持所述工质储液罐(14)与所述蒸汽发生器(D)断开连通，从而使冷凝所得所述压力工质液体流入所述工质储液罐(14)中，并且，
    当所述工质储液罐(14)中的液位高于预定第一阈值时，使所述工质储液罐(14)与所述第一冷凝器(C)断开连通，并且与所述蒸汽发生器(D)连通，从而能够使所述工质储液罐(14)中冷凝所得所述压力工质液体返回 所述蒸汽发生器(D)中。
  23. 根据权利要求22所述的方法，还包括：
    当所述工质储液罐(14)中的液位低于预定第二阈值时，使所述工质储液罐(14)与所述蒸汽发生器(D)断开连通而与所述第一冷凝器(C)重新连通，使得所述冷凝所得压力工质液体能够流入所述工质储液罐(14)中，其中所述预定第二阈值低于所述预定第一阈值。
  24. 根据权利要求23所述的方法，还包括：在所述工质储液罐(14)与所述第一冷凝器(C)重新连通时，利用所述工质储液罐(14)内部与所述第一冷凝器(C)内部之间的压力差驱动气动发电机(11)发电，所产生的电优选用于对所述第四流体储罐(F)中的第二流体进行辅助加热。
  25. 根据权利要求19-24中任一项所述的方法，其中，
    所述热泵(I)包括电动机以及由所述电动机驱动的压缩机，所述方法还包括：将来自所述第三流体储罐(H)的至少一部分第二流体用于对所述电动机进行水冷，并且在所述水冷后被输送回所述第四流体储罐(F)中；
    和/或，
    所述气动机(J)与发电机连接以驱动发电机，所述方法还包括：将来自所述第三流体储罐(H)的至少一部分第二流体用于对所述发电机进行水冷，并且在所述水冷后被输送回所述第四流体储罐(F)中。
  26. 根据权利要求19-25中任一项所述的方法，其中所述第一流体储罐(G)、所述第二流体储罐(E)、所述第三流体储罐(H)、所述第四流体储罐(F)、所述工质储液罐(14)、蒸发器(A)、蒸汽发生器(D)、第一冷凝器(C)和/或第二冷凝器(B)是绝热的。
  27. 根据权利要求18-26中任一项所述的方法，其中，
    所述第一流体为盐水，对气动机(J)的输出压力工质气体进行冷凝而升温后的第一流体的温度优选为0℃至20℃，更优选为0℃至12℃，更优选为12℃；被热泵(I)的工质吸收热量而制冷的第一流体的温度优选为-20℃ 至0℃，更优选为-12℃至0℃，更优选为-12℃；和/或，
    所述第二流体为水，对输入压力工质进行加热而降温后的第二流体的温度优选为30℃至50℃，更优选为35℃至45℃，更优选为40℃；被热泵(I)的工质加热后的第二流体的温度优选为90℃至60℃，更优选为80℃至65℃，更优选为75℃；和/或，
    所述热泵(I)的工质为CO 2，且所述气动机(J)的压力工质为氨。
  28. 一种分布式换能系统，其特征在于，包括：热泵(I)、气动机(J)、用于供第一流体在其中循环流动的第一循环回路、以及用于供第二流体在其中循环流动的第二循环回路，其中，
    热泵(I)用于利用其工质从第一流体中吸收热量而对第一流体制冷，并且用于对吸收热量后的工质进行压缩以进一步提高工质的温度，用于利用其工质对第二流体进行加热；
    经加热的第二流体用于对气动机(J)的输入压力工质进行加热使其汽化成压力工质气体用于致动所述气动机(J)，并且对输入压力工质进行加热而降温后的第二流体被热泵(I)的工质重新加热以用于重新对气动机(J)的输入压力工质进行加热，从而使得第二流体被循环加热和降温；
    经制冷的第一流体用于对气动机(J)的输出压力工质气体进行冷凝，并且对气动机(J)的输出压力工质气体进行冷凝而升温后的第一流体被热泵(I)的工质重新吸收热量而制冷以用于重新对气动机(J)的输出压力工质气体进行冷凝，从而使得第一流体被循环制冷和升温。
  29. 根据权利要求28所述的系统，还包括：第一流体储罐(G)、第二流体储罐(E)、第三流体储罐(H)和第四流体储罐(F)，其中第一流体储罐(G)和第二流体储罐(E)位于第一循环回路中用于储存第一流体，第三流体储罐(H)和第四流体储罐(F)位于第二循环回路中用于储存第二流体，并且其中：
    第一流体储罐(G)用于储存对所述气动机(J)的输出压力工质气体进 行冷凝而升温后的第一流体，其中热泵(I)用于利用其工质从来自第一流体储罐(G)的第一流体中吸收热量而对第一流体制冷，且第二流体储罐(E)用于储存经制冷的所述第一流体；
    第三流体储罐(H)用于储存对气动机(J)的输入压力工质进行加热而降温后的第二流体，其中热泵(I)用于利用其工质对来自第三流体储罐(H)的第二流体进行加热，且第四流体储罐(F)用于储存经加热的所述第二流体。
  30. 根据权利要求29所述的系统，还包括第一冷凝器(C)和蒸汽发生器(D)，其中，
    第一冷凝器(C)用于：使来自所述第二流体储罐(E)的经制冷的所述第一流体在流经第一冷凝器(C)时对流入所述第一冷凝器(C)中的、所述气动机(J)的输出压力工质气体进行冷凝得到压力工质液体，所述压力工质液体返回蒸汽发生器(D)作为所述气动机(J)的所述输入压力工质；
    蒸汽发生器(D)用于：使来自所述第四流体储罐(F)的经加热的所述第二流体在流经蒸汽发生器(D)时对蒸汽发生器(D)内的、所述气动机(J)的输入压力工质进行加热使其汽化成所述压力工质气体从而致动所述气动机(J)。
  31. 根据权利要求29或30所述的系统，还包括蒸发器(A)和第二冷凝器(B)，其中，
    所述蒸发器(A)用于：使所述热泵(I)的工质在流经蒸发器(A)时从流入蒸发器(A)中的、来自所述第一流体储罐(G)的第一流体中吸收热量而蒸发，从而对所述第一流体制冷；
    第二冷凝器(B)用于：使热泵(I)的所述压缩后的工质在流经第二冷凝器(B)时对流入第二冷凝器(B)中的、来自所述第三流体储罐(H)的第二流体进行加热而冷凝，并在加热后输送并返回蒸发器(A)。
  32. 根据权利要求30或31所述的系统，还包括工质储液罐(14)，其与所述第一冷凝器(C)相比位于更低位置且通过第一阀门(13)与所述第一 冷凝器(C)流体连通，并且通过第二阀门(18)与所述蒸汽发生器(D)流体连通，
    其中，当第一阀门(13)处于打开状态时，第二阀门(18)处于关闭状态，使得所述第一冷凝器(C)与工质储液罐(14)连通，同时保持所述工质储液罐(14)与所述蒸汽发生器(D)断开连通，从而使所述冷凝所得压力工质液体流入所述工质储液罐(14)中；
    并且，当所述工质储液罐(14)中的液位高于预定第一阈值时，所述第一阀门(13)变为关闭状态且所述第二阀门(18)变为打开状态，使得所述工质储液罐(14)与所述第一冷凝器(C)断开连通而与所述蒸汽发生器(D)连通，从而能够使所述工质储液罐(14)中所述冷凝所得压力工质液体返回所述蒸汽发生器(D)中。
  33. 根据权利要求32所述的系统，其中，
    当所述工质储液罐(14)中的液位低于预定第二阈值时，所述第一阀门(13)变为打开状态且所述第二阀门(18)变为关闭状态，使所述工质储液罐(14)与所述蒸汽发生器(D)断开连通而与所述第一冷凝器(C)重新连通，使得所述冷凝所得压力工质液体能够流入所述工质储液罐(14)中，其中所述预定第二阈值低于所述预定第一阈值。
  34. 根据权利要求33所述的系统，其中，
    所述工质储液罐(14)还通过与所述第一阀门(13)所处第一管路不同的第三管路与所述第一冷凝器(C)流体连通，所述第三管路中包含串接的第三阀门(12)和气动发电机(11)，
    所述工质储液罐(14)还通过与所述第二阀门(18)所处第二管路不同的第四管路与所述蒸汽发生器(D)流体连通，所述第四管路中包含串接的第四阀门(16)和储气罐(17)，所述储气罐(17)连接于所述蒸汽发生器(D)与所述第四阀门(16)之间且用于储存汽化的所述压力工质气体，
    当所述工质储液罐(14)中的液位高于所述预定第一阈值时，所述第三 阀门(12)由打开状态变为关闭状态而所述第四阀门(16)由关闭状态变为打开状态；当所述工质储液罐(14)中的液位低于所述预定第二阈值时，所述第三阀门(12)由关闭状态变为打开状态而所述第四阀门(16)由打开状态变为关闭状态，从而利用所述工质储液罐(14)内部与所述第一冷凝器(C)内部之间的压力差驱动气动发电机(11)发电，所产生的电优选用于对所述第四流体储罐(F)中的第二流体进行辅助加热，并且在所述工质储液罐(14)内部与所述第一冷凝器(C)内部之间压力平衡后，所述第一阀门(13)由关闭状态变为打开状态。
  35. 根据权利要求34所述的系统，其中所述第一阀门(13)和第二阀门(18)为单向阀，所述第三阀门(12)和第四阀门(16)为电动阀。
  36. 根据权利要求29-35中任一项所述的系统，其中，
    所述热泵(I)包括电动机以及由所述电动机驱动的压缩机，来自所述第三流体储罐(H)的至少一部分第二流体用于对所述电动机进行水冷，并且在所述水冷后返回所述第四流体储罐(F)中；
    和/或，
    所述气动机(J)与发电机连接以驱动发电机，来自所述第三流体储罐(H)的至少一部分第二流体用于对所述发电机进行水冷，并且在所述水冷后返回所述第四流体储罐(F)中。
  37. 根据权利要求29-36中任一项所述的系统，其中所述第一流体储罐(G)、所述第二流体储罐(E)、所述第三流体储罐(H)、所述第四流体储罐(F)、所述工质储液罐(14)、蒸发器(A)、蒸汽发生器(D)、第一冷凝器(C)和/或第二冷凝器(B)是绝热的。
  38. 根据权利要求28-37中任一项所述的系统，其中，
    所述第一流体为盐水，对气动机(J)的输出压力工质气体进行冷凝而升温后的第一流体的温度优选为0℃至20℃，更优选为0℃至12℃，更优选为12℃；被热泵(I)的工质吸收热量而制冷的第一流体的温度优选为-20℃ 至0℃，更优选为-12℃至0℃，更优选为-12℃；和/或，
    所述第二流体为水，对输入压力工质进行加热而降温后的第二流体的温度优选为30℃至50℃，更优选为35℃至45℃，更优选为40℃；被热泵(I)的工质加热后的第二流体的温度优选为90℃至60℃，更优选为80℃至65℃，更优选为75℃；和/或，
    所述热泵(I)的工质为CO 2，且所述气动机(J)的压力工质为氨。
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Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109798159B (zh) * 2019-02-13 2019-10-25 孙诚刚 分布式换能方法和系统
DE102019122810A1 (de) * 2019-08-26 2021-03-04 Eberspächer Climate Control Systems GmbH Fahrzeugtemperiersystem
WO2021248289A1 (zh) * 2020-06-08 2021-12-16 孙诚刚 换能方法和系统
CN113417709B (zh) * 2021-06-02 2022-04-22 中国科学院理化技术研究所 耦合高温热泵循环的液态空气储能方法及系统
CN113959122B (zh) * 2021-09-16 2023-03-31 青岛海尔空调电子有限公司 制冷系统、用于制冷系统的控制方法、控制装置
CN116335785B (zh) * 2021-12-16 2025-08-08 中国科学院广州能源研究所 一种海岛地热电淡冰联供系统
CN115597306A (zh) * 2022-11-09 2023-01-13 双良节能系统股份有限公司（Cn） 一种低沸点工质回收及储补装置
CN116608451B (zh) * 2023-06-05 2025-01-28 深圳爱图仕创新科技股份有限公司 循环冷却系统及照明设备
CN116839244B (zh) * 2023-09-01 2023-12-19 国网江苏省电力有限公司南京供电分公司 多热源热泵相变蓄能型冷热联供系统控制方法与装置
CN119268167B (zh) * 2024-09-24 2025-11-25 中国科学院理化技术研究所 大温差热泵相变储能系统及储能方法

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20030074895A1 (en) * 2001-10-24 2003-04-24 Mcfarland Rory S. Seal and valve systems and methods for use in expanders and compressors of energy conversion systems
CN1890458A (zh) * 2003-10-14 2007-01-03 布鲁厄斯能源公司 低温联合发电系统
WO2008106190A2 (en) * 2007-02-27 2008-09-04 Shirk Mark A Integrated electrochemical and thermochemical renewable energy production, storage, distribution and recycling system
CN203856601U (zh) * 2014-05-28 2014-10-01 孙诚刚 一种动力装置
CN208458304U (zh) * 2018-03-22 2019-02-01 烟台大学 一种间接换热的热泵装置
CN109798159A (zh) * 2019-02-13 2019-05-24 孙诚刚 分布式换能方法和系统

Family Cites Families (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
MX144884A (es) * 1976-07-30 1981-12-01 Deere & Co Mejoras a impulsor de turbocargador de ciclo rankine para motores de combustion interna
US4251996A (en) * 1979-06-01 1981-02-24 Carrier Corporation Heat reclaiming method and apparatus
CN86207494U (zh) * 1986-10-25 1988-03-16 北京航空学院 空气膨胀涡轮连续制冷装置
JP2611185B2 (ja) * 1994-09-20 1997-05-21 佐賀大学長 エネルギー変換装置
JP4686464B2 (ja) * 2004-09-17 2011-05-25 学校法人同志社 熱ポンプ、熱ポンプシステム及びランキンサイクル
JP2008292026A (ja) * 2007-05-23 2008-12-04 Ats Japan Corp 恒温維持装置。
DE102010010614B4 (de) * 2010-03-08 2012-01-26 GMK Gesellschaft für Motoren und Kraftanlagen mbH Verfahren und Vorrichtung zur Energieerzeugung in einer ORC-Anlage
SE535782C2 (sv) * 2011-03-21 2012-12-18 Skellefteaa Kraftaktiebolag Förfarande och system för återvinning av termisk energi från en ångtork
CN102679622A (zh) * 2012-05-22 2012-09-19 青岛大学 一种模块化变热容自匹配多温系统
CN103574987B (zh) * 2012-08-01 2015-09-02 吴春渊 冷热多功节能系统
ES2692118T3 (es) * 2014-05-05 2018-11-30 General Electric Technology Gmbh Sistema de almacenamiento y de descarga de energía eléctrica
BR112016030958A8 (pt) * 2014-06-30 2017-10-10 Kerbs Autotech Pty Ltd Sistema de recuperação de energia térmica do motor de combustão interna
US10113448B2 (en) * 2015-08-24 2018-10-30 Saudi Arabian Oil Company Organic Rankine cycle based conversion of gas processing plant waste heat into power
CN105571029A (zh) * 2016-01-27 2016-05-11 王昊 一种实现空调跨季度同步蓄冷蓄热的方法及设备
US9702597B1 (en) * 2016-02-18 2017-07-11 King Fahd University Of Petroleum And Minerals System and method for preventing absorbent crystallization in a continuously operating solar-powered absorption cooling system with hybrid storage
CN106288513A (zh) * 2016-09-30 2017-01-04 广州高菱能源技术有限公司 一种带相变蓄冷和蓄热的冷热两用热泵系统
CN107525302B (zh) * 2017-10-18 2018-05-22 王金宝 一种利用低温热能转换动力并制冷制热发电的装置及方法
TWI672433B (zh) * 2017-12-29 2019-09-21 明基能源技術股份有限公司 熱能回收系統
CN110118437B (zh) * 2019-05-05 2021-04-09 青岛海田设计事务所有限公司 一种用于海洋馆的废热回收利用系统及其工作方法
CN111780074A (zh) * 2020-06-09 2020-10-16 孙诚刚 外燃机系统和交通工具

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20030074895A1 (en) * 2001-10-24 2003-04-24 Mcfarland Rory S. Seal and valve systems and methods for use in expanders and compressors of energy conversion systems
CN1890458A (zh) * 2003-10-14 2007-01-03 布鲁厄斯能源公司 低温联合发电系统
WO2008106190A2 (en) * 2007-02-27 2008-09-04 Shirk Mark A Integrated electrochemical and thermochemical renewable energy production, storage, distribution and recycling system
CN203856601U (zh) * 2014-05-28 2014-10-01 孙诚刚 一种动力装置
CN208458304U (zh) * 2018-03-22 2019-02-01 烟台大学 一种间接换热的热泵装置
CN109798159A (zh) * 2019-02-13 2019-05-24 孙诚刚 分布式换能方法和系统

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP3926257A4 *

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