WO2012163082A1 - 热力过程采用喷射抽气节能方法 - Google Patents

热力过程采用喷射抽气节能方法 Download PDF

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Publication number
WO2012163082A1
WO2012163082A1 PCT/CN2012/000724 CN2012000724W WO2012163082A1 WO 2012163082 A1 WO2012163082 A1 WO 2012163082A1 CN 2012000724 W CN2012000724 W CN 2012000724W WO 2012163082 A1 WO2012163082 A1 WO 2012163082A1
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Prior art keywords
jet
gas
power
pumping
source
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PCT/CN2012/000724
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English (en)
French (fr)
Inventor
张玉良
Original Assignee
Zhang Yuliang
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Publication of WO2012163082A1 publication Critical patent/WO2012163082A1/zh

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04F—PUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
    • F04F5/00—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow
    • F04F5/14—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow the inducing fluid being elastic fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04F—PUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
    • F04F5/00—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow
    • F04F5/14—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow the inducing fluid being elastic fluid
    • F04F5/16—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow the inducing fluid being elastic fluid displacing elastic fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04F—PUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
    • F04F5/00—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow
    • F04F5/54—Installations characterised by use of jet pumps, e.g. combinations of two or more jet pumps of different type
    • 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
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E20/00—Combustion technologies with mitigation potential
    • Y02E20/14—Combined heat and power generation [CHP]

Definitions

  • the invention belongs to the field of thermal power and refrigeration.
  • single-stage injection is generally used to realize vacuum pumping or several single-stage jet air extractors "series" (so-called “continuous connection” is from the pumping process, which is the current industry customary saying, from power
  • the gas source process is actually parallel () to achieve higher vacuum pumping.
  • single-stage nozzle jet aspirator is often used in energy-saving fields such as steam jet refrigeration, evaporative seawater desalination and steam recovery of other thermal systems, but its single-stage injection structure determines that it can only use medium and low parameter gas sources ( ⁇ Parameter high-efficiency steam turbines are multi-stage nozzles in series.)
  • the biggest problem is that the thermal efficiency is very low.
  • the low efficiency of single-stage jet pumping limits its application, and the advantage is that there is no need to rotate the machine during the pumping process.
  • Patent application CN200810182738.9 proposes a thermal boosting thermodynamic cycle method, which is an effective small steam unit to achieve high-parameter steam solution, but the small steam turbine generator required is difficult to have a corresponding high-parameter model. Due to the low thermal efficiency of small units, it has severely restricted its extensive development.
  • the object of the invention is to greatly increase the thermal efficiency of the thermal process and reduce the investment cost.
  • the technical scheme of the invention adopts the ⁇ parameter dynamic gas source in the thermal process to generate the jet through the composite jet pumping system, and the other air source is mixed and decelerated to provide power to the heat power conversion device, thereby realizing no rotation of the sucked air source.
  • the so-called composite jet pumping method means that the jet pumping system adopts one or more stages of cyclic jet pumping, or two of three series of pumping methods: series, parallel and cycle. Or three combinations, multi-stage cyclic jet pumping refers to two or more stages of cyclic jet pumping.
  • the so-called cyclic jet pumping refers to the process of jet pumping.
  • Each stage of pumping extraction is the air source after the lower stage suction compression work, and the last stage pumping extracts the exhaust gas or other gas source after the expansion of the heat work conversion device, to realize the stepwise cycle pumping and gradually increase the circulation flow to
  • the final stage concentrates the expansion work, and the single-stage cyclic jet pumping directly extracts the exhaust gas after the expansion of the work by the thermal power conversion device.
  • the essence of the principle of the composite jet pumping power system is that whether the exhaust of the system is exhausted or the other gas source is extracted, the process of pumping the power source into the pumped source and compressing the pumped air source is high.
  • the parameter power source reduces the parameter flow during the work process, and the mass flow rate increases.
  • the series of jet pumping devices can continuously expand the high-pressure gas source to the required low-pressure parameters, and the parallel connection can expand the high-temperature gas source multiple times and expand to the required one.
  • the composite jet pumping system creates a very favorable condition for realizing high temperature and high parameter power system, and can adapt to any high temperature flue gas generated by the combustion chamber, such as liquefied air or liquid oxygen and liquid fuel or even solid fuel. It is conducive to high-efficiency and high-efficiency operation of the thermal process. It also creates favorable conditions for flexible use of various heat sources in the book, such as: The working gas is compressed and boosted by the compressor or liquefied and then boosted by heat and evaporated to become a power source; the low-temperature power source passes the pressure The combustion chamber is warmed up, or the gas or other hot gas is pumped up by the jet pumping system.
  • a swirling jet refrigeration method is proposed.
  • the low temperature working fluid source is cooled by expansion and decompression, and the power system is characterized in that the power system uses a jet pumping system or a compressor or a fan to separate the low temperature gas source from the swirling gas and liquid.
  • a pressure difference is generated between the devices, and the low-temperature gas source enters the swirling gas-liquid separator through the nozzle to expand and atomize and generates a jet in the tangential direction to form a swirling flow to realize the gas-liquid separation, and the condensed liquid remains in the gas-liquid separator. It is discharged from the exhaust pipe, and the deflector is installed in the exhaust pipe or the exhaust pipe port.
  • the power system provides the pumping power to the exhaust pipe of the refrigeration system, or provides a pressurized air source for the nozzle, or at the same time provides the pumping power to the exhaust pipe to provide a pressurized gas source for the nozzle, which can realize the process of pumping refrigeration or jet cooling. Reduce or avoid throttling losses.
  • the solution provides a new low-cost solution for reducing thermal losses in thermal or refrigeration processes such as thermal or electric air conditioning, air liquefaction, desalination, and air dehumidification.
  • the composite jet pumping system avoids the direct contact of the gas turbine with high-temperature flue gas, which can well solve the low-parameter discharge of high-parameter operation of the thermodynamic process, and can fully exert the advantages of enthalpy efficiency.
  • the multi-hole injection simplifies the jetting device to shorten the jet length. It not only fits well with the multi-stage series-parallel composite cycle structure but also can be used for single-stage jet aspirator.
  • the combination of air liquefaction and thermal boosting facilitates the combustion system to achieve rich oxygen or pure oxygen combustion and direct combustion of liquid oxygen and liquid fuel.
  • the liquefied air in the system can not only realize low-cost energy storage, but also evaporate and boost the system during power generation operation, which can provide cold source without energy consumption and energy saving.
  • the high-efficiency composite jet thermal system can provide a low-temperature power source for the nozzle, which creates favorable conditions for the jet surface aerodynamic system.
  • the combination with the deflector bend plate is beneficial to make the use of aerodynamics in various mobile devices become common. .
  • thermodynamic cycle scheme can be used to describe the existing thermal power induced draft fan and blower.
  • the pressure water can be used to replace the water pump, and the liquid magnetic fluid can be driven to generate electricity, which can realize high-efficiency power generation without rotating machinery.
  • the invention is based on basic innovation and has a wide range of applications. It will surely play a role in energy conservation in more fields. DRAWINGS
  • Figure 1 is a simplified diagram of a three-stage tandem jet pumping process.
  • Figure 2 is a schematic diagram of a three-stage series cycle jet pumping process
  • Figure 2A is a split-cycle injector structure.
  • Figure 3 is a simplified diagram of a single stage cyclic jet pumping process.
  • Figure 4 is a simplified diagram of a multi-nozzle jet pumping structure.
  • Fig. 5 is a schematic view showing the principle of the nozzles forming a swirling flow pattern in an oblique direction.
  • Figure 6 is a schematic view of the split arrangement of the cyclone jet aspirator.
  • Figure 7 is a schematic diagram of the structure of a multi-stage tandem vacuum aspirator.
  • Figure 8 is a schematic diagram of a water source heat pump or refrigeration system.
  • Figure 9 is a schematic diagram of a vapor compression sea desalination system.
  • Figure 10 is a schematic diagram of a composite injection pumping gas turbine system.
  • Figure 11 is a schematic diagram of a composite injection pumping type non-pressure combustion gas turbine system.
  • Figure 12 is a two-layer composite jet pumping gas turbine in which an air compressor and a gas turbine are coaxially arranged.
  • Figure 13 is a composite jet pumping gas turbine cycle system using air liquefaction and thermal boosting.
  • Figure 14 is a schematic illustration of a multi-nozzle jet engine employing a composite jet pumping system.
  • Figure 15 is a schematic diagram of a jet engine system employing an air liquefaction and thermal boost system.
  • Figure 16 is a schematic diagram of a gas multiple jet engine power system that is powered by liquefied gas.
  • Figure 17 is a schematic diagram of an external thermal jet power system powered by liquefied gas.
  • Figure 18 is a hollow casing structure liquefied gas anti-frost heating pipe.
  • Figure 19 is a schematic illustration of a surface jet aerodynamic device.
  • Figure 20 is a schematic illustration of a surface jet aerodynamic device for a ground mobile device.
  • Figure 21 is a schematic illustration of a surface jet aerodynamic device for use in an airborne mobile device.
  • Figure 22 is a schematic diagram of a jet pumping heat system for a pneumatic volume pump system.
  • Figure 23 is a schematic diagram of a pneumatic volume pump system for submerged or deep mixing.
  • Figure 24 is a schematic view showing the structure of a liquid magnetic fluid generator.
  • Figure 25 is a schematic illustration of a combined jet pumping system for jet pumping refrigeration.
  • Fig. 26A is a swirling type jet cooling
  • Fig. 26B is a developed view of the deflector.
  • Figure 27 is a schematic diagram of a positive pressure gas source injection refrigeration mode of a composite injection pumping power system.
  • Figure 28 is a schematic diagram of the power mode of the compressor or fan.
  • Figure 29 is a schematic illustration of a thermal jet pumping chiller or heat pump.
  • Figure 30 is a schematic diagram of a compressor compression and injection pumping liquefaction combined refrigeration system.
  • Figure 31 is a schematic illustration of a liquid purification system incorporating a swirling jet refrigeration combined with a cyclone separator. detailed description
  • the three-stage series connection structure of the jet aspirator the high-parameter power gas source enters the main air inlet of the air extractor through the pipeline 1 , and is injected into the low-parameter gas source by the exhaust gas pipeline 4 after being sprayed through the nozzle 2 .
  • the throat pipe 3 enters the deceleration and expansion chamber to complete the first-stage pumping, and then enters the second-stage third-stage pumping process, and finally enters the gas turbine generator set 5 to expand the work, and then exhausts the exhaust gas through the pipeline 6, the arrow indicates the airflow.
  • Flow direction. 2 is a three-stage series simultaneous use of a circulating jet pumping structure.
  • Each stage of pumping extracts a gas source after the lower stage pumping and mixing and diffusing, and the last stage extracts the exhaust gas after the gas turbine expands and works, and is circulated and pumped.
  • the trachea 8 is connected.
  • Figure 2A shows a three-stage cyclic jet pumping structure for the split structure to facilitate the addition of heaters to the pipeline.
  • Figure 3 is a simplified diagram of the simplest single-stage circulating pumping system for extracting exhaust gas from a circulating pump.
  • the multi-stage pumping of one or more stages is determined according to the difference between the parameters of the power source and the rated parameters of the inlet of the gas turbine.
  • the source of the pumping source may be other equipment sources or may be selected for cyclic pumping or direct pumping of the atmosphere.
  • the parameters of the power source gradually decrease, and the mass flow rate gradually increases.
  • Each stage of the pumping cycle is similar to the heat recovery process, so it is an effective energy-saving heat process.
  • FIG. 4 is a multi-nozzle single-stage jet aspirator device, which is composed of a gas source chamber II, a nozzle 12, a pumping chamber 13 and a mixing tube 14, abandoning the conventional throat type zooming structure, and adopting a mixing and diffusing process to combine
  • the straight pipe structure can greatly shorten the length of the injector and reduce the flow resistance. If necessary, an involute tube or a reducer can be used.
  • Figure 8 and Figure 8 show that the multi-nozzle combination is distributed in a swirling manner from two different directions, and the guide vanes are distributed at the end of the mixing tube to change the steam flow from the swirling flow to the DC increasing pressure.
  • Figure 6 is a split arrangement of a swirling jet aspirator with a guide vane or deflector in or at the outlet.
  • the multi-nozzle distribution working mode of FIG. 5 and the cyclonic spraying mode of FIG. 6 are both for shortening the jet length and realizing rapid diffusion mixing of the two steam streams to improve the pumping efficiency, and not only well adapted to the multi-stage series-parallel composite structure. It is also needed and can also be used when used in a single stage jet aspirator.
  • Embodiment 2 thermal fan:
  • the multi-stage circulating composite jet aspirator as shown in Fig. 7 is generally used for vacuum pumping.
  • the power source is air or flue gas, it can also be used for thermal draft or thermal blast, especially for large fans. It avoids the loss of efficiency such as power processes and wind turbines, and can fully play the role of energy saving.
  • Embodiment 3 jet pumping water source heat pump -
  • the water source heat pump or refrigeration system shown in FIG. 8 adopts a composite jet pumping system using hot-pressed air as a power source to extract steam from the raw water tank 17 and obtain a steam condensing heat temperature to increase the temperature for the hot user. After the heat, the steam in the gas stream is further condensed into water, which is separated into the condensate tank 19 by gas and water, and the air is discharged, and the condensed water is collected and reused.
  • a large flow rate is generally required to maintain a stable temperature and liquid level. After the raw water is discharged from the water tank, it can be directly supplied with cooling or the heat exchanger 18 can be indirectly cooled.
  • a vapor compression sea desalination system as shown in Fig. 9 operates in an air venting state, and raw water enters the evaporator 23 from the valve 21 and is heated.
  • the steam is drawn into the composite jet aspirator 22 to be heated and then enters the condenser.
  • the heat is condensed within 24, and the condensed water is supplied by the water pump 26 to the outside of the system.
  • the degree of vacuum and flow of the system are controlled by the control valve 21 and the pump 25, and the combined injection aspirator 22 maintains a sufficient pressure difference between the inside and the outside of the condenser 24 to cause an evaporative condensation reaction. Only the principle of single-effect evaporation is shown in the drawing, which is also suitable for multi-effect evaporation.
  • Embodiment 5 a gas turbine power system or a gas turbine system:
  • the gas turbine power system with composite jet air extractor is easy to adapt to steam power gas source or other medium and low temperature gas source system, which can meet the high parameters of small and micro unit. Steam power generation.
  • the composite jet-exhausted gas turbine system in order to make the high-temperature flue gas heat work as much as possible to reduce the exhaust gas temperature, uses a two-layer composite jet pumping parallel and gas turbine group consisting of series-parallel composite injection. Pumping power system.
  • the system provides compressed air to the combustion chamber 31 by the air compressor 32, so that the fuel is combusted in the combustion chamber to generate gas.
  • the high temperature and high pressure power gas source enters the composite injection pumping system to expand and increase the mass flow rate, and then enters the front air turbine 33 first. After entering the final stage of the gas turbine, it becomes a low-parameter exhaust gas and is discharged.
  • the two stages of the gas turbine avoiding the low-pressure circulation injection can reduce the volume flow of the composite injection cycle and reduce the flow loss.
  • Figure 11 is a pressureless combustion gas turbine system using a three-layer composite jet pumping parallel process.
  • the compressed air source is supplied by the air compressor 35 to be the initial power source into the composite jet pumping system, and the non-compressed combustion chamber is first pumped.
  • the high-temperature gas in 34 starts the cooling and depressurization expansion work after the heating gas source reaches the appropriate parameter, and finally outputs the shaft power through the gas turbine.
  • the pressureless combustion chamber has a lower volume and pressure than the high-pressure combustion combustion chamber of the same power shown in Fig. 10
  • the non-pressure combustion chamber is more suitable for a large-capacity generator set without being restricted by the combustion chamber as a high-temperature pressure vessel, and may be a fuel oil. Gas-fired coal can also be pure oxygen or oxy-combustion.
  • the non-pressure hot gas source scheme is beneficial to many energy-saving projects for the utilization of industrial waste heat.
  • Figure 12 is also a two-layer composite jet pumping parallel mode.
  • the air compressor and the gas turbine are arranged coaxially.
  • the thermal process differs from that of Figure 10 in that the heat source of the heater 37 is derived from the heat dissipation protection or extraction of the combustion chamber and the injector temperature section. Flue gas heating, the exhaust of the first layer composite jet pumping system directly enters the front gas turbine 36 (defined by the direction of the gas flow), reduces the flow loss due to the reduced circulation amount, but increases the equipment cost, and the practical application can be Specific design requirements are selected.
  • Figure 13 is a composite jet pumping gas turbine circulation system using air liquefaction and thermal boosting.
  • the so-called thermal boosting is a process of closing and heating the working fluid in the pressure vessel 54, heating and boosting until the required pressure and temperature are required.
  • the evaporator 46 is supplied, and the steam is generated by the evaporator and then heated by the heat heater to become the power source for the combined jet pumping systems 49 and 40 (this diagram represents any desired form of jet pumping, the same below) .
  • Thermal boost and air liquefaction combination The working process is as follows: A.
  • the heater 55 is heated and boosted, and after being balanced with the evaporator 46, the check valve 45 is automatically turned on to output the liquefied air into the evaporator.
  • the valve 44 is opened, the check valve 45 is automatically closed, and the remaining air is sucked into the composite jet aspirator 40 through the jet air extractor 42 until the pressure is balanced.
  • the power source enters the composite jet pumping system 40 to provide the pumping cyclone air liquefier 50 with the pumping power, and the air is cooled and dehumidified from the heat exchangers 48 and 55 and passed through the tube.
  • the road 51 and the nozzle enter the low-temperature vacuum environment inside the liquefier tangentially, and the gas and liquid are separated by the swirling flow after the expansion and cooling, and the airflow is taken away by the composite jet aspirator 40 through the exhaust pipe, and the liquefied air is collected and collected.
  • the process of closing the valve 41 liquefied air is completed when the liquid level of the container 52 reaches the upper position.
  • the volume design of the evaporator thermodynamic booster is relatively small, so that the evaporator has liquid level fluctuation during the working process but does not affect the stable operation of the system.
  • a double thermal booster can be used to ensure sufficient temperature adaptation time. It is also possible to use a thin-walled tank intermediate insulation layer in the container.
  • the heat source of the superheater heater 43 may be boiler heating, solar high temperature heat collection, waste heat of boiler or engine or other production system, electric heating, etc., or a gas turbine may be directly used.
  • the open cycle is changed to a closed cycle, the air liquefaction is changed to a steam condenser, and the thermal boost system can be used for water vapor circulation.
  • thermal boost heating can be used to directly absorb the air temperature and pre-cool the air for the air liquefaction system, as shown by the dotted arrow in the figure (different with a dotted line, the same below), or it can be heated by a power system such as a gas turbine exhaust heat. .
  • the multi-nozzle jet engine of the composite jet pumping system is used.
  • the propeller and the compressor are coaxially mounted with the front air turbine 63, and the combustion chamber 61 generates pressurized gas through the jet aspirator 62.
  • the forward gas turbine 63 is powered, and a portion of the exhaust gas of the forward gas turbine is pumped away by the jet air extractor 62, and a portion is pumped away by the jet air extractor 64 to generate injection power at the outlet of the nozzle.
  • the jet engine system using the air liquefaction and thermal boosting system as shown in Fig. 15 provides a power source for the circulation system through the combustion chamber 66 and the thermal boosting system, and finally converts to a suitable temperature and pressure parameter for the nozzle group.
  • 68 provides power
  • the nozzle groups are connected to each other through the mother pipe 67, and the number of nozzles and the installation position can be freely designed as needed.
  • the thermodynamic cycle process is basically similar to that of FIG. 13, except that the exhaust pipe 69 of the composite jet pumping cycle extracts the exhaust of the air liquefaction system instead of the nozzle exhaust gas, and in fact can directly extract the atmosphere but affect the cycle efficiency. .
  • the filling liquefied gas composite jet pumping power system, the fuel tank 71 and the liquefied air (or liquid oxygen) tank 72 are respectively equipped with heaters to supply fuel and oxidant for the gas composite jet pumping power system 76.
  • the liquefied air tank 72 simultaneously supplies a power source for the composite jet pumping system 75, and the nozzle 74 is a heat power conversion device or a gas turbine.
  • Figure 17 is a canned liquefied gas power system using an external heat or an external combustion system to provide a heat source for the heaters 77 or 78.
  • the two sets of evaporative jet pumping systems are connected to each other by an exhaust line, which can be pumped to each other.
  • only one set of liquefied gas system can be used, that is, it can be an independent power system.
  • the book can be a waste heat utilization system.
  • Example 7 using a frost-proof heater for a liquefied gas pipeline or vessel:
  • Figure 18 shows a liquefied gas frost-proof heating pipeline, which is provided by an inner and outer tube set.
  • the inner tubes 78 and 79 are internally filled with liquid working medium, and gas is sealed between the inner and outer tubes, and the heat exchange coefficient of the heater is controlled by changing the pressure of the sealing gas or controlling the flow rate thereof by the control system. It can be adjusted to adapt to environmental changes and obtain maximum heat transfer efficiency at any time without frosting.
  • a similar liquefied gas container can also be made into an inner and outer layer frost-proof and heatable type.
  • the interlayer When the liquefied gas is stored in the pressure vessel, the interlayer is vacuum-insulated. When the pressure vessel is heated to generate power for the liquefied gas, the interlayer pressure is increased to increase the heat transfer coefficient. , can be well adapted to the needs of energy storage power systems.
  • the nozzle is provided with a power source by the composite injection heat system, and the temperature of the high-temperature power source is greatly reduced after the mass flow is increased by the composite jet pumping system, and the nozzle 81 can be directly used for the aerodynamic system.
  • the surface injection power system adds a flow deflecting plate 82 that controls the flow direction of the jet stream through the jet surface to form a surface jet and deflector combination system that lifts the jet stream through the surface of the flap. And the reverse thrust control in the same direction becomes the forward power of the mobile device.
  • Figure 21 is a diagram showing a combination of a pair of surface injection and diversion combined systems to form an aerodynamic system.
  • the power supply source switch and flow rate are distributed by the control valve system, wherein Figure A shows the left and right baffles to make the air flow consistently downward to make the air The power system generates a rising force.
  • Figure B shows that the right baffle moves down and exits the diversion to change the right jet direction to the right.
  • the control valve system redistributes the airflow to balance the lift with gravity and generate the required force to the left.
  • Figure C is the opposite of the effect shown in Figure B. The left side is directed directly and the right side is deflected downwards. The system produces a rightward pushing force.
  • the aerodynamic mobile device is powered by one or more sets of surface injection and diversion combined systems and controls the movement of the mobile device through the control system to control the distribution of the power source and the deflector, so that takeoff, landing, Moving states such as forward, backward, steering, and air hovering.
  • the deflector can also adopt other structural methods according to specific needs.
  • the aerodynamic system combining the surface injection and the deflector simultaneously utilizes the lift and reverse thrust to generate power, which is energy-saving and efficient and flexible and reliable.
  • the liquefied air or liquid nitrogen combined injection power system can provide a power source for the diaphragm pump or a pneumatic air pump for the volumetric pressure pump shown in Figure 22.
  • the power source is supplied to the pressurized water container 93 through the composite injection system 91, and the last residual gas is discharged from the exhaust pipe 92.
  • the water source is pressurized from the line 95 into the pressurized water container through the check valve, and then pressurized into the water supply pipe 94.
  • the control system controls the wide door to make the two sets of water pressure systems work alternately.
  • the composite jet pumping system alternately supplies the residual gas of the pressure water container alternately, and the pressurized water container alternately exhausts and automatically enters the water through the one-way valve.
  • the volumetric air pressure pump for liquid or deep wells the working principle is the same as that of Fig. 22, the two sets of pressurized water containers are adapted to the working environment and changed to the coaxial drum set structure, each pressurized water container.
  • the volumetric air pressure pump not only saves the power generation and electric links, but also saves the low-efficiency turbine rotor of the ordinary water pump. It uses a high-efficiency compound injection power system to provide a power source, which can adjust the flow rate steplessly, and the energy saving effect is remarkable.
  • the positive displacement air pump can also be used for other positive displacement pneumatic systems instead of the ordinary air pump to supply air to the pneumatic equipment.
  • the pressurized water container is changed to a compressed air container to become an air pump.
  • Embodiment 10 Magnetic fluid power generation -
  • liquid metal such as mercury or other magnetic fluid can be pressed to generate electricity through a magnetic fluid generator.
  • Figure 24 is a magnetic fluid generator.
  • the magnetic conductive casing 101 and the core 104 constitute a magnetic circuit.
  • the excitation coil 102 excites to generate a magnetic field, and the magnetic fluid enters the spiral pipeline from the pipeline 103 to cut the magnetic lines of force at high speed to make the armature coil. 105 generates current.
  • the armature coil can generate DC or AC according to different winding distribution.
  • the biggest advantage of magnetic fluid power generation is that there is no rotating machinery, and the magnetic fluid generator is convenient to use superconducting coil in the environment of liquid nitrogen composite jet thermal system. In turn, an electrolyte solution having a poor conductivity can be used as a magnetic fluid instead of a liquid metal.
  • a composite jet pumping system as shown in Figure 25 for deep pumping refrigeration the aerodynamic gas source entering the combined injection system 119 draws air from the pumping line 118 or draws the final stage exhaust as indicated by the dashed line.
  • the three-rent parallel parallel pumping system is finally exhausted from the evaporator 112 through the exhaust pipe 111, and discharged from the outlet 117 to the atmosphere, and the pumping process maintains a sufficient pressure difference in the evaporator 112 to throttle the air from the throttle.
  • the valve 115 After the valve 115 enters, it expands and cools down, and part of the condensate liquefies and settles to the bottom liquefied air.
  • the rest is pumped away from the exhaust pipe 111, and the liquefied air is controlled to be discharged through the valve 113.
  • This refrigeration or air liquefaction technique is simple and low cost without rotating machinery, but the throttle valve 115 produces a throttling loss (or loss of expansion work).
  • the low temperature gas source passes along the nozzle 123.
  • the tangential jet enters the swirling gas-liquid separator and expands and atomizes simultaneously to form a swirl (similar to that shown in Fig. 5B).
  • the deflector 121 is installed in the exhaust pipe and can also be installed at the nozzle.
  • the guide vane is deployed in a planar manner as shown in Fig. 26B.
  • the swirling flow is guided to a direct current and is expanded through the exhaust pipe. Press to recover the swirling flow force.
  • the cyclone separator can be used for cooling, and can adopt the power mode of the composite jet pumping depth as shown in FIG. 25, or the positive jet air source of the composite jet pumping power system as shown in FIG. Injection cooling method.
  • the use of positive pressure injection not only simplifies the composite jet pumping system, but also enables the multi-stage cyclone jet refrigeration unit to simultaneously drive the multi-stage jet pumping system with air or flue gas as the power source.
  • the stage drops to achieve step by step liquefied air or flue gas.
  • any jet pumping power refrigeration system can use a compressor or fan (fan is generally used for humid air cooling) instead of a mechanical air source liquefaction, as shown in Figure 28, provided by compressor 124.
  • the pressure system is simple and easy to use, and can be used for gas liquefaction or air dehumidification.
  • the compressor type rotary equipment investment has large operation and maintenance cost and high noise, and the two power modes can be appropriately selected in engineering applications.
  • Both thermal and electric power can be stored by swirling jet refrigerant air liquefaction, as shown in Fig. 28, which can realize air liquefaction energy storage with relatively high efficiency.
  • energy storage has more important meaning.
  • high-temperature air can be used to have conductive characteristics in the plasma state, and electricity plasma generation occurs. It is equipped with plasma discharge or plasma electromagnetic eddy current heating to obtain ultra-high temperature air, which provides thermal power for the thermal injection refrigeration air liquefaction system, achieving high efficiency and no transfer to mechanical energy storage.
  • plasma burners are widely used, and the theory of high-temperature flue gas plasma magnetic fluid power generation is relatively mature. Therefore, it is feasible to generate heat by using plasma to generate plasma discharge or magnetic induction.
  • the air is used as a low-temperature gas source to enter the cyclone-type refrigeration system 128 through the nozzle to generate liquefied air, and the liquefied air is heated and evaporated in the thermal boosting system to be injected.
  • the initial power source of the pumping system, the thermal booster and the evaporator in the thermal boosting system are essentially evaporative heat exchangers, and the jet pumping system provides pumping for the exhaust pipe 129 of the cyclone jet refrigeration system 128.
  • the aerodynamically generated liquefied air forms a circulating working system, and the evaporator heater provides a cold source to the outside (as indicated by the broken line in the figure).
  • the exhaust gas from the outlet of the jet extractor supplies a heat source to the outside.
  • the heater 127 provides a thermal power process for the initial power source. It only needs to be intermittently operated. With the change of the liquefied air storage amount in the system, whether the heating operation can be controlled by the valve 125 and the valve 126.
  • the heater 127 can use a heat exchanger or a combustion chamber to make the book system a thermal refrigeration or a heat pump, or a compressor to replace the heating system into a mechanical or electric refrigeration and heat pump.
  • a portion of the gaseous gas discharged from the jet pumping system enters the cyclone refrigeration system, and another portion enters the compressor 132 and is compressed to enter the condensing heat exchanger 131.
  • the liquid chemical produced by the cyclone refrigeration system and the condensing heat exchanger enters the evaporative heat exchanger, and the liquid chemical is heated and evaporated to become the power source of the jet pumping system, and the evaporative heat exchanger provides the cold source for the outside.
  • the condensing heat exchanger provides a heat source to the outside world.
  • the liquid purification process shown in FIG. 31 adopts a combination of a gas source injection refrigeration and a cyclone separator to realize liquid evaporative condensation purification, and the power gas source first enters the cyclone separator 136 to generate a swirl flow, and the original liquid spray system 135 is added.
  • the raw liquid is sprayed into the cyclone inside the cyclone separator, and the original liquid is partially evaporated to retain the liquid state after being heated, and the raw liquid vapor is separated by the swirling flow as the mixed gas flows through the exhaust pipe and the deflector to the outlet, and the unvaporized raw liquid It is separated by cyclone separation and discharged to the bottom.
  • the mixed gas stream separated from the cyclone separator enters the cyclone jet refrigeration system 137 through the nozzle, and the raw liquid vapor is condensed and separated and collected as a purifying liquid, and the remaining gas stream is discharged.
  • This liquid purification process essentially utilizes the principle of wet air cyclone jet cooling.
  • Example 15 Flue Gas Emission Reduction -
  • the scheme of Figure 31 can also be used for flue gas purification.
  • the flue gas enters the cyclone jet refrigeration system to achieve dehumidification, dust removal and liquefaction or solidification of gaseous oxides by moderate cooling.
  • Desulfurization, denitrification or carbon dioxide collection is carried out, and the single-stage system is used for mixing treatment or multi-stage system is used to remove the physical properties of different components of the flue gas according to different freezing points.
  • the jet pumping power system can be adjusted by the valve, or the final stage can be adjusted with adjustable nozzles.
  • the adjustable nozzles are at least mature in the jet engine field and can also meet gas turbines. It is also possible to use two sets of different sizes of jet-pumping power systems to provide thermal power to a gas turbine, and to achieve coarse adjustment by the start-stop state of the two sets of jet-pumping power systems, plus fine adjustment of the final adjustable nozzle and fuel adjustment. It can basically realize the wide range of high efficiency adjustment operation of the system.
  • the present invention is a basic innovation and has a wide range of application, and is not limited to the scope of the embodiments.

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Abstract

一种热力过程采用喷射抽气节能方法，喷射抽气系统采用循环抽气的方式，或者多级喷射抽气装置采用串联与并联与循环相结合的方式组成复合喷射系统，通过喷射抽气系统与做功设备结合，使高参数气源先进入喷射抽气系统再进入做功设备做功，实现高效运行。还公开了一种喷射制冷的方法。

Description

热力过程采用喷射抽气节能方法 技术领域
本发明属于热能动力及制冷领域。
背景技术
在热能动力领域总是追求大容量高参数机组的开发以追求高效率， 但是温度与压力两个 参数总是难以同时满足这一目的。 内燃机、 燃气轮机以及火箭发动机燃烧温度度高但是烟气 压力有限导致工作时排烟温度太髙， 燃说煤发电厂的蒸汽轮机组可获得超临界压力， 虽然温度 压力在汽轮机实现了同步降低达到低参数排放， 但是蒸汽温度初参数仅 550'C左右， 目前先 进的大型热力机组单机热效率都不超过 50%， 内燃机与燃气轮机热效率甚至不到 40%, 因此 还有很大节能空间。 一种解决办法是采用了燃气轮书机与蒸汽循环联合发电， 将燃气轮机的排 出的高温烟气再通过蒸汽循环发电， 总热效率可达 55%左右， 但是这种动力过程直接组合使 得系统复杂问题叠加导致投资成本与运行成本很大， 应用并不广泛。
在喷射抽气技术领域， 一般采用单级喷射实现真空抽气或几个单级喷射抽气器 "串联" (所谓 "串连"是从抽气流程而言， 是目前业内习惯说法， 从动力气源流程看实际为并联） 实现更高真空抽气。 目前单级喷嘴喷射抽气器常用于余热利用， 如蒸汽喷射制冷、 蒸发式海 水淡化及其它热力系统的蒸汽回收等节能领域， 但是其单级喷射结构决定其只能使用中低参 数气源（髙参数高效率汽轮机都是多级喷嘴串联做功)， 其最大的问题是热效率很低， 目前还 没有实现从动力气源流程看实现多级串联喷射结构的报道。 单级喷射抽气的低效率特点使其 应用受到局限， 而优点是抽气压气过程中无需转动机械。
另外， 微网分布式发电在电力安全、 可再生能源利用及用户釆用热电冷联产实现高效节 能方面有重要意义迫切需要小机组发电实现髙效率， 但是小型热力机组最大的问题是很难实 现高参数，尤其压力参数很难上去。专利申请 CN200810182738.9提出了热力升压式热力循环 方法， 是一种有效的小型蒸汽机组实现高参数蒸汽的解决方案， 但是需要的小型汽轮发电机 却很难有对应的高参数型号， 目前因小机组热效率低而严重制约其广泛发展。
在制冷与热泵领域， 制冷循环中工质膨胀制冷都是通过节流阔或细微管实现降压膨胀， 放弃利用膨胀功， 有资料提出采用液压马达等设备回收膨胀功但投资成本与效率都比较差。 发明内容
本发明的目的： 大幅度提高热力过程的热效率， 降低投资成本。
本发明的技术方案： 在热力过程中采用髙参数动力气源经过复合喷射抽气系统产生射流 抽吸其它气源混合减速后为热功转换装置提供动力， 实现对被抽吸气源的无转动机械的压缩 做功， 所谓复合喷射抽气方式是指喷射抽气系统采用了一级或多级循环喷射抽气方式， 或者 是采用了串联与并联与循环三种喷射抽气方式之中的两种或三种结合的方式， 多级循环喷射 抽气是指两级或者两级以上的循环喷射抽气方式。 所谓的循环喷射抽气是指喷射抽气过程中 每级抽气抽取的是下级抽气压縮做功后的气源， 末级抽气抽取的是热功转换装置经膨胀做功 后的尾气或其它气源， 实现逐步循环抽气逐步增大循环流量到末级集中膨胀做功， 单级循环 喷射抽气直接抽取热功转换装置膨胀做功后的尾气。
复合喷射抽气动力系统原理的实质是， 无论是循环抽取本系统排气还是抽取其它气源， 都是动力气源抽入被抽气源并对被抽入气源压縮做功的过程， 高参数动力气源在做功过程中 参数降低换来质量流量增加， 喷射抽气装置串联可使高压气源不断膨胀到需要的低压参数， 而并联可使高温气源多次压缩多次膨胀到需要的低温参数， 通过串联与并联及循环抽气的灵 活组合， 只要散热系统能保护髙温设备正常工作， 理论上可实现任何髙温烟气做功到接近环 境温度排放， 实现高参数高效率运行。说
采用复合喷射抽气系统为实现高温高参数动力系统创造了非常有利的条件， 可以适应燃 烧室产生的任何高温烟气，如由液化空气或液氧与液态燃料甚至固体燃料燃烧而成动力气源， 有利于热力过程高参数高效率运行。 也为灵活利用书各种热源做功节能创造了有利条件， 如： 工质气体被压縮机压縮升压或者被液化后通过热力升压并蒸发成为动力气源； 低温动力气源 通过有压燃烧室燃烧升温， 或者通过喷射抽气系统抽吸燃气或其它热气升温。 在太阳能或风 力发电储能方面， 甚至可以利用高温空气成为等离子态具有导电特点， 通过电力实现等离子 放电或等离子电磁涡流效应加热获得超髙温空气， 为热力喷射制冷空气液化系统提供动力， 实现高效率无转到机械储能； 以及通过换热器利用中低温热源升温， 或者釆用上述两种或多 种升温。
另外， 提出一种旋流喷射式制冷方法， 低温工质气源通过膨胀减压制冷， 其特征是动力 系统采用喷射抽气系统或者压縮机或者风机使低温气源与旋流式气液分离器之间产生压力 差， 低温气源经喷嘴进入旋流式气液分离器内膨胀雾化并沿切向产生射流形成旋流实现气液 分离后， 冷凝液体留在气液分离器内剩余气体从排气管排出， 导流器安装在排气管内或排气 管口。 动力系统为制冷系统排气管提供抽气动力， 或者为喷嘴提供有压气源， 或者同时为排 气管提供抽气动力为喷嘴提供有压气源， 可实现抽气制冷或喷射制冷过程中减小或避免节流 损失。 该方案为热力或电力空调、 空气液化、 海水淡化及空气除湿等热力或制冷过程减小节 流损失利用膨胀功提供新低成本方案。
这里涉及到的气的概念是包括空气、 烟气、 蒸汽及湿空气等各种气源或气态工质的广义 概念， 以下同。 本发明具体解决方案灵活多样， 将结合实施例进一步说明。 本发明的优点：
1. 复合喷射抽气系统与空气液化及热力升压方法结合，避免了气轮机直接接触高温烟 气， 可以很好解决热动力过程高参数运行低参数排放， 可充分发挥髙效率优势。
2. 多孔喷射可简化喷射装置縮短射流长度，不仅很好适应多级串并联复合循环结构需 要而且也可以在用于单级喷射抽气器时发挥优势。
3. 旋流喷射式制冷，可以避免节流损失，可实现无转动机械制冷式空气液化，在制冷、 储能、 海水淡化烟气净化等领域广泛发挥低成本髙效率的优势。 4. 复合喷射抽气热力循环与热力升压系统结合，可实现无转子发动机解决了发动机实 现高参数运行的必须克服耐高温的瓶颈。
5. 空气液化与热力升压结合方便燃烧系统实现富氧或纯氧燃烧以及液氧与液态燃料 直接燃烧。
6. 可用于小型微型热电冷储联产热力系统， 系统内液化空气不仅可以实现低成本储 能， 而且系统发电运行时蒸发升压可顺便为空调提供冷源不消耗能源， 高效节能。
7. 高效率的复合喷射热力系统可为喷管提供低温动力气源，为翼板表面喷射空气动力 系统创造了有利条件， 与导流弯板组合有利于使各种移动设备使用空气动力成为普遍。
8. 利用高效的热力循环方案可实说现热动力引风机及鼓风机，采用气压水的方式可替代 水泵， 也可以推动液态磁流体发电， 可实现无转动机械的高效发电。
9. 有利于太阳能、 生物能及各种余热通过空气液化实现高效储能及发电。
10. 本发明为基础创新， 适用面广， 必将会书在更多领域发挥节能作用。 附图说明
图 1是三级串连喷射抽气过程简图。
图 2是三级串联循环喷射抽气过程简图， 图 2A为分体循环喷射器结构。
图 3是单级循环喷射抽气过程简图。
图 4是多喷嘴喷射抽气结构简图。
图 5是喷嘴按斜向形成旋流方式分布的原理示意图。
图 6是旋流式喷射抽气器分体布置方式示意图。
图 7是多级串连真空抽气器结构简图。
图 8是水源热泵或制冷系统示意图。
图 9是一种蒸汽压缩式海淡化系统示意图。
图 10是复合喷射抽气式燃气轮机系统示意图。
图 11是复合喷射抽气式无压燃烧燃气轮机系统示意图。
图 12是空气压缩机和气轮机同轴布置的两层复合喷射抽气燃气轮机。
图 13是采用了空气液化及热力升压的复合喷射抽气气轮机循环系统。
图 14是采用了复合喷射抽气系统的多喷管喷气式发动机示意图。
图 15是采用了空气液化与热力升压系统的喷气式发动机系统示意图。
图 16是灌装液化气为动力的燃气复式喷射喷气动力系统示意图。
图 17是灌装液化气为动力的外热式喷气动力系统示意图。
图 18是空心套管结构液化气防霜加热管路。
图 19是表面喷射空气动力装置示意图。
图 20是表面喷射空气动力装置用于地面移动设备示意图。
图 21是表面喷射空气动力装置用于空中移动设备示意图。
图 22是喷射抽气热力系统用于气压容积水泵系统简图。 说 明 书 图 23是用于液下或深并的气压容积水泵系统简图。
图 24是液态磁流体发电机结构简图。
图 25是复合喷射抽气系统用于喷射抽气制冷示意图。
图 26A是旋流式喷射制冷， 图 26B是导流器展开图。
图 27是复合喷射抽气动力系统正压气源喷射制冷方式示意图。
图 28是压縮机或风机动力方式喷射抽气方式示意图。
图 29是热力喷射抽气制冷机或热泵的示意图。
图 30是压缩机压缩与喷射抽气液化联合制冷系统示意图。
图 31是采用旋流式喷射制冷与旋流分离器结合的液体净化系统示意图。 具体实施方式
实施例 1， .复合喷射抽气结构与原理：
如附图 1所示的喷射抽气器三级串连结构， 高参数动力气源经管路 1进入抽气器主气入 口， 通过喷嘴 2喷射后由抽气管路 4抽入低参数气源， 经喉管 3共同进入减速扩压室混合完 成一级抽气， 接着进入第二级第三级抽气过程， 最后进入气轮发电机组 5膨胀做功后经管路 6排出尾气， 图中箭头表示气流流动方向。 附图 2是三级串联同时釆用循环喷射抽气结构， 每级抽气抽取的是下级抽气混合扩压后的气源， 末级抽取经气轮机膨胀做功后的排气， 经过 循环抽气管 8连接。 附图 2A分体结构的三级循环喷射抽气结构， 方便在管路上增加加热器， 附图 3是最简单的单级循环抽气系统简图， 循环抽气抽取气轮机排气。
一般根据动力气源参数与气轮机入口额定参数的差别决定釆用一级或一级以上的多级抽 气， 被抽气源可以是其它设备来源或者选择循环抽气或者直接抽大气。 在喷射抽气热力过程 中动力气源参数逐渐降低质量流量逐步增加， 每级喷射抽气循环类似于回热过程， 因此是髙 效节能热力过程。
附图 4是多喷嘴单级喷射抽气器装置， 由气源室 I I、喷嘴 12、抽气室 13及混合管 14组 成， 放弃传统喉管式縮放结构， 采用混合与扩压过程合二为一的直管结构可大幅度縮短喷射 器长度减小流动阻力， 需要时也可以采用角度不大的渐开管或渐缩管。 附图 5的八、 B图是 从两个不同方向表示多喷嘴组合按斜向形成旋流方式分布， 混合管末端分布了导流叶片使汽 流从旋流变为直流增加压力。 附图 6是旋流式喷射抽气器分体布置方式， 排气管路内或出口 也有导流叶片或导流器。 附图 5多喷嘴分布工作方式与附图 6的旋流式喷射方式都是为缩短 射流长度并实现两种汽流迅速深度扩散混合以提高抽气效率， 不仅很好适应多级串并联复合 结构需要而且也可以在用于单级喷射抽气器时发挥优势。
实施例 2, 热力风机：
如附图 7所示的多级循环复合喷射抽气器， 一般情况用于真空抽气， 当动力气源是空气 或烟气时也可以用于热力引风或热力鼓风尤其用于大型风机， 避免了电力过程及风轮等效率 损失， 可充分发挥节能作用。
实施例 3， 喷射抽气式水源热泵- 说 明 书 如附图 8所示的水源热泵或制冷系统， 采用热压空气为动力气源的复合喷射抽气系统抽 取原水水箱 17内蒸汽混合压縮后获得蒸汽凝结热气温升高， 为热用户供热后，气流中蒸汽进 一步冷凝为水进入凝水水箱 19中经气水分离， 空气排出， 冷凝水收集回用。运行中原水水箱 中一般需要有较大流量维持稳定的温度和液位， 原水排出水箱后可直接供冷或者增加换热器 18间接供冷。
实施例 4, 单效或多效蒸馏：
如附图 9所示的一种蒸汽压缩式海淡化系统，在排空空气状态下工作， 原水从阀 21进入 蒸发器 23受热产生蒸汽被抽入复合喷射抽气器 22压缩升温后进入冷凝器 24内放热冷凝，凝 结水由水泵 26向系统外供水。在蒸馏过程中，由控制阀 21和泵 25控制系统的真空度和流量， 由复合喷射抽气器 22使冷凝器 24内外保持足够压力差发生蒸发冷凝反应。 附图中只显示了 单效蒸发原理， 同样适用于多效蒸发， 因为单级喷射抽气压缩式在海水淡化、 蒸馏水生产等 领域已为生产应用的公知技术， 本实施例只是说明采用多级复合喷射抽气取代单级喷射抽气 压缩将更适应高参数蒸汽动力， 更适合独立热力蒸馏系统， 更节能高效。
实施例 5， 气轮机动力系统或燃气轮机系统：
如附图 1、 2、 3及附图 4所示的配置了复合喷射抽气器的气轮机动力系统， 容易适合蒸 汽动力气源或其它中低温气源的系统，可满足小微机组高参数蒸汽发电。如附图 10所示为复 合喷射抽气式燃气轮机系统， 为了使高温烟气热能尽可能多做功降低排烟温度， 釆用了两层 复合喷射抽气并联与气轮机组组成的串并联复合喷射抽气动力系统。系统由空气压缩机 32为 燃烧室 31提供压缩空气，使燃料在燃烧室内燃烧产生燃气成为高温高压动力气源进入复合喷 射抽气系统中膨胀并增加质量流量，然后先进入前置气轮机 33再进入末级气轮机做功后成为 低参数尾气后排出， 气轮机分前后两级避免低压循环喷射可减少复合喷射循环体积流量， 减 小流动损失。
附图 11 是采用了三层复合喷射抽气并联过程的无压燃烧燃气轮机系统， 由空气压缩机 35提供压縮气源成为初始动力气源进入复合喷射抽气系统， 先抽吸无压燃烧室 34内高温燃 气为动力气源升温达到合适参数后开始降温降压膨胀做功， 最后通过气轮机输出轴功。 虽然 无压燃烧室比附图 10所示同功率的高压燃烧燃烧室的压力参数低体积大，但是无压燃烧室更 适合大容量发电机组而不受燃烧室为高温压力容器的限制， 可以是燃油、 燃气燃煤， 也可以 是纯氧或富氧燃烧， 另外无压热气源方案有利于许多工业余热尾气利用的节能工程。
附图 12也是两层复合喷射抽气并联方式， 空气压缩机和气轮机同轴布置， 热力过程与 附图 10区别是， 加热器 37的热源来自燃烧室及喷射器髙温段的散热保护或抽取烟气加热， 第一层复合喷射抽气系统的排气直接进入前置气轮机 36 (按气流方向定义）， 因减少了循环 量而减少了流动损失， 但是增加了设备成本， 实际应用可根据具体设计要求选择。
附图 13是采用了空气液化及热力升压的复合喷射抽气气轮机循环系统， 所谓热力升压 是将工质在压力容器 54 内封闭加热的过程， 加热升压直到需要的压力与温度再供给蒸发器 46，由蒸发器产生蒸汽再经过热加热器加热后成为动力气源为复合喷射抽气系统 49及 40 (这 种图示方式表示任何需要的喷射抽气形式， 以下同）提供动力。 热力升压与空气液化组合间 断式工作， 其过程如下： A， 热力升压器 54内补充液化空气后受加热器 55加热升压， 直到 与蒸发器 46平衡后下面单向阀 45自动导通输出液化空气进入蒸发器， 热力升压器液体排空 后打开阀 44， 单向阀 45自动关闭， 余气经喷射抽气器 42抽吸部分空气后进入复合喷射抽气 器 40直到压力平衡。 B， 在上述 A过程进行的同时打开控制阀 41动力气源进入复合喷射抽 气系统 40为喷射旋流式空气液化器 50提供抽气动力， 空气从换热器 48与 55降温除湿后通 过管路 51 及喷嘴沿切向进入液化器内部低温真空环境， 膨胀降温雾化后随旋流作用气液分 离， 气流经排气管被复合喷射抽气器 40抽走， 液化空气沉降后被收集到到底部容器 52内， 当容器 52液位达到上位后关闭阀 41液化空气过程完成。 C, 当八、 B过程都完成后容器 52 与热力升压器 54成为连通器， 单向阀说 53自动导通， 热力升压器开始补充液化空气， 补充完 成后关闭阀 44开启阀 41， A、 B过程重新开始。
一般相对蒸发器热力升压器容积设计的较小， 使蒸发器在工作过程中有液位波动但不影 响系统稳定工作， 在实际应用中为解决热力升压器书在急冷急热交替变化中工作， 可以采用双 热力升压器方式， 可确保有足够的温度适应时间， 也可以采用容器内设薄壁罐中间保温层的 方法。过热加热器 43的热源可以是锅炉加热、太阳能高温集热、锅炉或发动机或其它生产系 统余热以及电热等， 也可以直接采用燃气轮机。 另外， 将开式循环改为闭式循环， 将空气液 化改为蒸汽冷凝器， 热力升压系统就可以用于水蒸汽循环。
热力升压的特点是工质容易获得髙压参数而不受机组容量大小影响， 并且可以是不用水 或蒸汽的开式循环。 热力升压加热可以象图中虚线箭头（用虚线表示可有可无， 以下同）所 示采用直接吸收空气温度并为空气液化系统预冷空气， 也可以采用动力系统如气轮机排气余 热加热。
实施例 6， 喷气式发动机：
如附图 14所示的釆用了复合喷射抽气系统的多喷管喷气式发动机，螺旋桨、压缩机与前 置气轮机 63同轴安装， 燃烧室 61产生有压燃气经过喷射抽气器 62向前置气轮机 63提供动 力， 前置气轮机的排气一部分被喷射抽气器 62抽走， 一部分被喷射抽气器 64抽走并在其喷 管出口产生喷射动力。
如附图 15所示的采用了空气液化与热力升压系统的喷气式发动机系统， 通过燃烧室 66 及热力升压系统为循环系统提供动力气源最后转化为合适的温度压力参数为喷管组 68提供 动力， 喷管组通过母管 67互相联通， 可以按需要自由设计喷管数量与安装位置。热力循环过 程与附图 13基本类似， 不同的是复合喷射抽气循环的抽气管路 69抽取的是空气液化系统的 排气而不是喷管尾气， 事实上也可以直接抽取大气但会影响循环效率。
如附图 16所示的灌装液化气复合喷射抽气动力系统， 燃料罐 71与液化空气 （或液氧） 罐 72分别安装了加热器， 为燃气复合喷射抽气动力系统 76提供燃料与氧化剂， 液化空气罐 72同时为复合喷射抽气系统 75提供动力气源， 采用喷管 74为热功转换装置， 也可以是气轮 机。附图 17是采用了外热或外燃系统为加热器 77或 78提供热源的罐装液化气动力系统，两 套蒸发喷射抽气系统之间有抽气管路互相连接， 可按互为抽气与被抽气的方式构成互为备用 或补充的动力系统， 用于小型系统时可以只采用一套液化气系统， 即可以是独立动力系统也 说 明 书 可以是余热利用系统。
实施例 7， 液化气管路或容器采用防霜加热器：
液化气在热力升压成为动力气源系统中， 一个常见问题是蒸发器在加热中容易结霜影响 系统正常工作， 附图 18所示为一种液化气防霜加热管路， 由内外管套装组成， 内管 78和 79 内部通液态工质， 内外管夹层之间封存有气体， 通过控制系统改变封存气体的压力或者控制 其流速控制加热器换热系数， 因为这种加热管路换热系数可调因此可适应环境变化尽可能在 不结霜的前提下随时获得最大换热效率。 类似的液化气容器也可以采用这种方法做成内外层 防霜可加热型， 在压力容器存放液化气体时夹层抽真空保温， 当压力容器加热使液化气产生 动力时夹层充压增加换热系数， 可很好适应储能动力系统的需要。
实施例 8， 空气动力装置：
如附图 19所示，喷管由复合喷射热力系统提供动力气源，高温动力气源经过复合喷射抽 气系统增加质量流量后温度大幅度下降，用于空气动力系统时通过喷管 81可直接喷射到移动 设备机翼型表面或专门的翼板表面而不至于把表面烧坏， 因为喷管喷射流速总是比移动设备 周围空气流速大的多在产生反推力的同时会产生更大升力， 构成一种节能的表面喷射空气动 力系统。
如附图 20所示，表面喷射动力系统增加了控制喷射气流经过喷射表面后的流动方向的导 流弯板 82组成表面喷射与导流件组合系统，将喷射气流在经过翼板表面产生的升力和反推力 控制到同一方向成为移动设备前进动力。
附图 21是表示一对表面喷射与导流组合系统组合而成空气动力系统，动力气源开关与流 量由控制阀系统分配， 其中图 A表示左右两侧导流板使气流一致向下使空气动力系统产生向 上升力， 图 B表示右边导流板下移退出导流使右侧射流方向改为向右直射， 控制阀系统重新 分配气流使升力与重力平衡并向左产生需要强度的推动力， 图 C与图 B所示的作用相反， 左 边直射而右边向下导流， 系统产生向右推动力。 这样， 空气动力移动设备由一组或者多组表 面喷射与导流组合系统提供动力并且通过控制系统对动力气源分布及导流弯板的控制进而控 制移动设备移动状态， 可实现起飞、 降落、 前进、 后退、 转向及空中悬停等移动状态。
导流件除采用导流弯板结构外也可以根据具体需要采用其它结构方式， 表面喷射与导流 件组合的空气动力系统同时利用了升力与反推力产生动力，节能高效而且使用方式灵活可靠。
实施例 9, 容积式气压水泵：
液化空气或者液氮复合喷射动力系统可以为隔膜泵提供动力气源，也可以为附图 22所示 的容积式气压水泵提供动力气源。 动力气源经过复合喷射系统 91为压水容器 93供气， 从排 气管 92排放最后余气， 水源从管路 95经逆止阀进入压水容器后升压成给水进入给水管 94。 通过控制系统控制阔门使两组压水系统交替工作， 由复合喷射抽气系统交替供气交替抽吸压 水容器余气， 压水容器交替排气并通过单向阀自动进水出水。
如附图 23所示的用于液下或深井的容积式气压水泵， 工作原理与附图 22—样， 两组压 水容器适应工作环境改为同轴圆桶套装结构， 每个压水容器都有一个管路升出地面后通过控 制阀分别与进气管排气管及余气回收管连接。 容积式气压水泵不仅省掉了发电与电动环节，而且也省掉了普通水泵低效率的涡轮转子， 釆用高效率的复合喷射动力系统提供动力气源， 可以无级调节流量， 节能效果显著。类似的, 容积式气泵还可以用于其它容积式气动系统代替普通气泵为气动设备供气， 例如， 压水容器 改为压气容器而成为气泵。
实施例 10， 磁流体发电- 按照容积式气压水泵原理， 可以压动水银等液态金属或其它磁流体通过磁流体发电机发 电。 附图 24是一种磁流体发电机， 导磁外壳 101与铁心 104组成导磁回路， 由励磁线圈 102 励磁产生磁场， 磁流体从管路 103进入螺旋管路中高速流动切割磁力线使电枢线圈 105产生 电流， 电枢线圈按不同的缠绕分布方式说可以产生直流或交流电， 磁流体发电最大优势是没有 转动机械， 而且在液氮复合喷射热力系统环境下磁流体发电机很方便采用超导线圈， 进而可 以采用导电率较差的电解质溶液做磁流体取代液态金属。
实施例 11， 旋流喷射式制冷方法与空气液化：书
如附图 25所示的一种复合喷射抽气系统，用于深度抽气制冷，空气动力气源进入复合式 喷射系统 119从抽气管路 118抽吸空气或者按虚线所示抽取末级排气， 增加流量后进入三租 并联的抽气系统， 最终从蒸发器 112内通过排气管 111抽气， 从出口 117排到大气， 抽气过 程使蒸发器 112内维持足够压力差使空气从节流阀 115进入后膨胀降温， 部分冷凝液化沉降 到底部液化空气中其余从排气管 111被抽走， 液化空气通过阀 113控制排出。 这种制冷或空 气液化技术无转动机械简单低成本， 但是节流阀 115产生了节流损失（或称损失了膨胀功）。
如附图 26A所示， 为避免或减小喷射制冷过程中节流损失， 低温气源（这里低温是指气 源进入旋流喷射式制冷系统后可产生冷凝现象的适宜温度）经喷嘴 123沿切向喷射进入旋流 式气液分离器内部膨胀雾化同时形成旋流 （类似于附图 5B所示） 实现气液分离后， 液体留 在气液分离器底部容器内剩余气体从排气管 122排出， 导流器 121安装在排气管中也可以安 装在管口， 导流器导流叶片平面展开如附图 26B所示使旋转流动的气流引导为直流向上， 并 通过排气管扩压回收旋流动力。这种旋流式分离器用于制冷时可以采用如附图 25所示的复合 喷射抽气深度抽真空的动力方式，也可以采用如附图 27所示的复合喷射抽气动力系统正压气 源喷射制冷方式。 采用正压喷射不仅可简化复合喷射抽气系统， 而且当多级喷射抽气系统以 空气或烟气为动力气源时可以同时带动多级旋流喷射式制冷装置， 可实现随着压力参数逐级 下降实现逐级液化空气或烟气。
原理上任何喷射抽气动力制冷系统都可以采用压缩机或风机（风机一般用于湿空气制冷） 动力方式取代实现机械式气源液化，如附图 28所示的以压縮机 124提供的正压系统简单使用 方便， 可以用于气体液化也可以用于空气除湿， 但压縮机类转动设备投资大运行维护成本高 噪音大， 两种动力模式在工程应用中可合适选型各自发挥优势。
实施例 12, 电力储能：
无论热力还是电力都可以通过旋流式喷射制冷空气液化实现储能，附图 28所示可以实现 较髙效率的利用电力实现空气液化储能。 在太阳能或风力发电方面储能具有更要的意义， 为 实现高效低成本储能， 可以利用高温空气在等离子态具有导电特点， 通过电力等离子发生设 备实现等离子放电或等离子电磁涡流效应加热获得超高温空气， 为热力喷射制冷空气液化系 统提供热动力， 实现高效率无转到机械储能。 目前等离子燃烧器应用较多， 高温烟气等离子 态磁流体发电理论也比较成熟， 因此利用电力产生等离子放电或磁感应产生热力是可行的。
实施例 13， 制冷或热泵循环：
如附图 29所示的开式制冷或热泵循环示意图，空气做为低温气源通过喷嘴进入旋流喷射 式制冷系统 128产生液化空气， 由液化空气在热力升压系统内受热蒸发升压成为喷射抽气系 统的初始动力气源， 热力升压系统中的热力升压器及蒸发器实质上都是蒸发换热器， 由喷射 抽气系统为旋流喷射制冷系统 128的排气管 129提供抽气动力产生液化空气形成循环工作系 统， 由蒸发器加热器为外界提供冷源 （说如图中虚线所示） 由喷射抽气器出口排气向外界提供 热源。一般情况系统运行时由加热器 127为初始动力气源提供热动力过程只需间断运行即可， 随着系统内液化空气储存量的变化而定， 可通过阀 125与阀 126控制是否加热运行。 加热器 127可以采用换热器或者燃烧室等各种热力方式使书系统成为热力制冷或热泵， 也可以用压縮 机取代加热式热力系统成为机械式或电力制冷与热泵。
如附图 30所示，用于闭式制冷或热泵循环，喷射抽气系统的排出的气体工质一部分进入 旋流式制冷系统， 另一部分进入压缩机 132被压缩后进入冷凝换热器 131， 将旋流式制冷系 统与冷凝换热器产生的液化工质进入蒸发换热器， 液化工质受热蒸发升压成为喷射抽气系统 的动力气源， 由蒸发换热器为外界提供冷源由冷凝换热器为外界提供热源。
实施例 14, 海水淡化或液体净化：
附图 31所示的液体净化过程，采用气源喷射制冷与旋流分离器结合方式实现液体蒸发冷 凝式净化， 动力气源先进入旋流分离器 136产生旋流， 并增加原液喷淋系统 135向旋流分离 器内部喷入原液进入旋流， 原液受热后部分蒸发其余保留液态， 受旋流分离作用原液蒸汽随 气流一起成为混合气流通过排气管及导流器到出口， 未蒸发的原液被旋流分离沉降到底部排 出。 从旋流分离器分离出来的混合气流通过喷嘴进入旋流喷射式制冷系统 137， 使原液蒸汽 冷凝分离收集为净化液， 其余气流排出。 这种液体净化过程实质是利用了湿空气旋流喷射制 冷原理。
实施例 15， 烟气减排- 采用附图 31方案还可以用于烟气净化，烟气进入旋流喷射制冷系统经过适度制冷实现烟 气除湿、 除尘以及使气态氧化物以冷凝液化或固化方式实现脱硫、 脱硝或收集二氧化碳， 釆 用单级系统混合处理或采用多级系统分别按烟气中各成分不同凝点不同物理特性依次去除。
实施例 16， 喷射抽气动力系统运行调节
喷射抽气动力系统可以通过阀门调节负荷， 或者末级喷射采用可调喷嘴， 可调喷嘴至少 在喷气发动机领域比较成熟， 也可以遇到燃气轮机。 也可以采用两组大小不同容量喷射抽气 动力系统为一个气轮机提供热动力， 通过两组喷射抽气动力系统启停状态实现粗调， 加上末 级可调喷嘴以及燃料调节实现细调， 可基本实现系统大范围高效率调节运行。 本发明为基础创新， 适用范围广， 不局限于实施例所述范围。

Claims

权 利 要 求 书
1、 一种热力过程采用喷射抽气节能方法， 属于热能与流体动力过程， 动力气源通过喷射 抽气系统抽吸气流后实现混合流动， 其特征是： 喷射抽气系统采用了单级喷射抽气方式或者 复合喷射抽气方式； 所谓复合喷射抽气方式是指喷射抽气系统采用了一级或多级循环喷射抽 气方式， 或者采用了串联和并联以及循环三种喷射抽气方式中的两种或三种结合的方式。
2、 如权利要求 1所述的一种热力过程采用喷射抽气节能方法， 其特征是： 单级喷射器或 者复合喷射器中的单级喷射釆用了以下结构之一，
( 1 ) 多喷嘴结构；
(2) 混合与扩压过程采用直管结构取代喉管式缩放结构；
(3 ) 旋流式喷射抽气结构， 并增加导流叶片；
(4) 以上三种结构中任意两种或三种结合的结构。
3、 如权利要求 1所述的一种热力过程采用喷射抽气节能方法， 其特征是： 由液化空气或 液氧与液态燃料燃烧而成动力气源， 或者工质气体被压缩机压缩升压或者被液化后通过热力 升压并蒸发成为动力气源； 或者低温动力气源通过有压燃烧室燃烧升温， 或者通过喷射抽气 系统抽吸燃气或其它热气升温； 或者通过电力实现等离子放电或等离子电磁涡流效应加热升 温； 或者采用换热器加热升温， 或者同时采用了两种或多种上述升温方法。
4、 如权利要求 1所述的一种热力过程采用喷射抽气节能方法， 其特征是： 动力气源通过 喷射抽气系统至少实现以下用途之一：
( 1 ) 用于热力引风或热力鼓风：
(2) 为水源热泵或制冷系统提供抽气动力， 喷射抽气系统抽取水源容器内的蒸汽与 动力气流混合扩压后为用户供热， 或者抽出水源容器内蒸汽使水源降温成为冷 水为用户提供冷源；
(3) 为单效或多效蒸馏系统提供喷射抽气压縮动力；
(4) 为气轮机组提供动力气源， 末级循环喷射抽气抽取大气或气轮机尾气或前置气 轮机排气， 或者抽取其它系统来气；
(5) 为喷管提供气源成为喷气式发动机系统， 末级循环喷射抽气抽取大气或前置涡 轮机排气或抽取空气液化系统排气， 或者抽取其它系统来气。
5、 如权利要求 1所述的一种热力过程采用喷射抽气节能方法， 其特征是： 液化的工质气 管路或容器釆用了防霜加热器， 其加热管路或容器由内外管或容器套装组成， 内外夹层之间 封存有气体， 通过控制系统改变封存气体的压力或流速控制其换热系数。
6、 如权利要求 1所述的一种热力过程采用喷射抽气节能方法， 用于喷气发动机为移动设 备提供动力， 其特征是： 喷射抽气式喷气发动机的喷管喷射方向布置在移动设备的表面或布 置在翼板表面组成表面喷射空气动力系统。
7、 如权利要求 6所述的一种热力过程采用喷射抽气节能方法， 其特征是： 表面喷射动力 系统增加了控制喷射气流经过喷射表面后的流动方向的导流件组成表面喷射与导流组合系 统。
8、 如权利要求 6所述的一种热力过程釆用喷射抽气节能方法， 其特征是： 移动设备由一 权 利 要 求 书 组或者多组表面喷射与导流件系统提供动力并且通过控制系统对动力气源分布及导流件的控 制进而控制移动设备的移动状态。'
9、 如权利要求 1所述的一种热力过程采用喷射抽气节能方法， 用于容积式气动水泵或其 它容积式气动系统， 其特征是： 喷射抽气系统通过阔门控制为隔膜泵或者其它双容器或多容 器容积式气动系统交替供气， 并且交替抽取容器余气。
10、 如权利要求 9所述的一种热力过程釆用喷射抽气节能方法， 其特征是： 通过喷射 抽气式气动水泵或气泵系统压动液态金属或其它磁流体进入磁流体发电机发电。
11、 一种旋流喷射式制冷方法， 低温工质气源通过膨胀减压制冷， 其特征是： 动力系 统采用热力喷射抽气方式或者机械方式或者二者结合的方式使低温气源与旋流式气液分离器 之间产生压力差， 低温气源经喷嘴沿切向射流进入旋流式气液分离器内膨胀雾化， 同时形成 旋流实现气液分离后冷凝液体留在气液分离器内剩余气体从排气管排出， 在排气管内或排气 管口安装了引导旋流为直流的导流器或导流叶片， 至少实现了以下用途之一：
( 1 ) 用于低温气源液化或除湿， 采用单级或在动力系统不同压力段多级制冷液化；
(2) 用于电力储能， 采用电动压縮机为旋流喷射制冷式空气液化系统提供动力， 或 者采用电力等离子放电或等离子电磁涡流效应加热为喷射抽气系统提供热动力 进而为旋流喷射制冷式空气液化系统提供动力， 通过生产液化空气实现储能。
(3) 用于开式制冷或热泵循环， 空气做为低温气源通过喷嘴进入旋流喷射式制冷系 统产生液化空气，由液化空气受热蒸发升压成为喷射抽气系统的初始动力气源， 由液化空气蒸发换热器为外界提供冷源由喷射抽气器出口排气为外界提供热 源；
(4) 用于闭式制冷或热泵循环， 喷射抽气系统的排出的气体工质一部分做为低温气 源进入旋流喷射式制冷系统， 另一部分进入压缩机被压缩后进入冷凝换热器， 将旋流式制冷系统与冷凝换热器产生的液化工质进入蒸发换热器， 液化工质受 热蒸发升压成为喷射抽气系统的动力气源， 由蒸发换热器为外界提供冷源由冷 凝换热器为外界提供热源；
(5) 用于海水淡化或者其它液体净化， 采用旋流喷射式制冷与旋流分离器结合方式 实现液体蒸发冷凝式净化， 动力气源先进入旋流分离器产生旋流， 增加原液喷 淋系统向旋流分离器内喷入原液进入旋流， 从旋流分离器分离出来的混合气流 通过喷嘴进入旋流喷射制冷系统， 使混合气流中原液蒸汽冷凝分离收集为净化 液；
(6) 用于烟气净化， 烟气进入旋流喷射制冷系统经过适度制冷实现烟气除湿、 除尘 以及使气态氧化物以冷凝液化或固化方式实现脱硫、 脱硝或收集二氧化碳， 采 用单级系统混合处理或采用多级系统分别处理。
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