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WO2014063443A1 - 自冷式热力做功方法 - Google Patents

自冷式热力做功方法 Download PDF

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Publication number
WO2014063443A1
WO2014063443A1 PCT/CN2013/001277 CN2013001277W WO2014063443A1 WO 2014063443 A1 WO2014063443 A1 WO 2014063443A1 CN 2013001277 W CN2013001277 W CN 2013001277W WO 2014063443 A1 WO2014063443 A1 WO 2014063443A1
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WO
WIPO (PCT)
Prior art keywords
heat
working fluid
jet
gas
power
Prior art date
Application number
PCT/CN2013/001277
Other languages
English (en)
French (fr)
Inventor
张玉良
Original Assignee
Zhang Yuliang
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Filing date
Publication date
Application filed by Zhang Yuliang filed Critical Zhang Yuliang
Publication of WO2014063443A1 publication Critical patent/WO2014063443A1/zh

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Classifications

    • 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
    • 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
    • F04F5/20—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 for evacuating
    • F04F5/22—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 for evacuating of multi-stage type
    • 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
    • F04F5/44—Component parts, details, or accessories not provided for in, or of interest apart from, groups F04F5/02 - F04F5/42
    • 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
    • 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

Definitions

  • the invention belongs to the field of thermal power.
  • thermodynamics The second law of thermodynamics is that the basics of thermodynamics have never been passively shaken, but obeying its regular thermal work system must discharge heat from low-temperature heat sources and always cause huge energy waste.
  • the single-cycle work process has a thermal efficiency of only close to 50%, such as gas turbines. Thermal efficiency is less than 40%, although
  • ⁇ liquefaction, heat the heat pump through the heat recovery heat exchanger to heat the already liquefied working fluid, and then absorb the air through the liquid working medium to heat up into the expander to do work, which is also in reality.
  • the cause of the error ⁇ (1) is similar, and the heat exchanger cannot exchange heat without temperature difference. Even if it starts to work, it will eventually stop working because the cooling capacity is gradually reduced.
  • the above scheme does not consider the heat pump process and the expansion work process.
  • the main task of the heat pump should be to liquefy or cool the gas working fluid without the need for high-parameter heat removal, and not fully utilize the advantages of the heat pump.
  • the jet refrigeration technology can obtain supercooled liquid, which can produce liquefied gas with lower temperature than the saturated gas before liquefaction, which is beneficial to the continuous realization of regenerative heat transfer.
  • the traditional jet aspirator has a large flow loss due to the existence of the throat zoom structure, and its structure and performance have great improvement in space, plus a simple non-rotating member and the working medium is heated by the liquid pumping force.
  • the power consumption compression work is the smallest, that is, there is a large room for improvement in the performance of the jet pumping refrigeration technology. Summary of the invention
  • the object of the present invention is to greatly improve the efficiency of the work of heat, and even the work of a single heat source.
  • the heat system completes the discharge heat Q 2 after the work is completed by the heat pump with the lowest possible parameter recovery, and the heat pump discharge heat absorbs the compression work after being absorbed by the expansion work process, and finally absorbs the heat absorption process of the working medium through the heat recovery cycle.
  • Qi so that the thermal system absorbs heat from the heat source to reduce Q2 under the same thermal cycle, so that some or all of the Q 2 is only circulated inside the system without discharging to the outside, maximizing the thermal efficiency.
  • the specific scheme is that the working fluid of the thermal system absorbs heat from the heat source, including the heating process of the working medium from the low temperature state to the heat source, the expansion process of the power source after entering the expansion working system, and the completion.
  • the low-temperature gas working fluid that expands the work (the low-temperature gas working medium that uses air as the working medium is the air that is inhaled from the environment).
  • the heat-dissipating process of releasing heat is performed, and the thermal system performs work from the heating process and the expansion. After the process to the heat removal process, it will heat up again.
  • thermodynamic cycle process is realized, which is characterized in that: the working medium absorbs heat from the heat source of the dry ambient temperature (such as fuel combustion or waste heat or geothermal heat and solar heat), or heat source from or below ambient temperature (for example)
  • the heat source in the natural environment such as air or lake water, absorbs the heat
  • the thermal system the process of absorbing heat from the low-temperature gas working medium in the process of absorbing heat in the process of heat removal, and the expansion of the mountain is done by R into ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇
  • the expansion work system absorbs the heat pump and releases the heat.
  • 3 ⁇ 4 ⁇ 3 ⁇ 4 The heat exchanger heats up or directly absorbs its enamel.
  • the heat process can be expanded by the mountain.
  • W 1 Connect the power supply or the power supply of the mountain gate to provide power.
  • the heat is 3 ⁇ 4, and the internal circulation does not absorb heat from the outside.
  • the heat absorbed by the system is all external work, Jii J - 'T'. . : '1 using the ⁇ -type cycle to do external work, 1 ( 1 cold-type thermal work system can achieve exhaust heat: personal ten from the environment to absorb heat rniiu equivalent to * to the environment to heat, Hi in the single heat source work, one Special case ⁇ U Refrigeration into heating system, only / internal compression 1 j expansion work 3 ⁇ 4, its external output heat is equal to the absorption of heat from the heat source _. ⁇ ; 3 ⁇ 4 transport ⁇ ⁇ does not strictly follow the single - ⁇ heat source work [ ⁇ Cold-type thermal work, especially in the beginning of the cycle, ⁇ ' ⁇ makes the system work.
  • a jet-type heat exchange heat pump method is proposed.
  • the working fluid absorbs heat from a low-temperature environment or a low-temperature working medium through expansion work, and is characterized by: a cyclone structure is adopted for a heat exchange unit that absorbs heat in a low-temperature environment or a low-temperature working medium.
  • the heat absorbing medium is injected tangentially or obliquely into the cyclone through the nozzle jet. After high-speed jet cooling, it absorbs heat through the wall of the cyclone and the external working medium or environment, and then enters the exhaust pipe for discharge.
  • the heat exchanger adopts a heat exchanger composed of a heat exchange unit or one or more heat exchangers of the Chuanchuan, such as; ⁇ 1 parallel combination .
  • the heat pump of a cold-type thermal work system can be used to heat the heat pump or to use a jet-cooling process or a steam-cooling process or a compression-cooling process: I: mass reduction or liquefaction, or
  • the jet-swirl heat exchange heat pump and the helium are used (the kind of cooling or liquefaction process of the working fluid is one of the group's.)
  • the pumping refrigeration or the pumping refrigeration process makes a part of the working fluid liquefied and will inevitably lead to another - part of the gas refrigerant enthalpy plus ffl fi, ⁇ by expanding the flow after the temperature rises to a so-called jet cooling effect of the heat pump through the power system the heat pump means lemma [Hugh: I: 1 j qualitative difference between the pressure of the condenser, the condenser mining.
  • Chuan has a jet cyclone separation method
  • a jet cyclone has adopted a sluice structure or a casing with a built-in drum structure, and a cold gas working medium (here, a W that is cooled or nearly saturated with a saturated skin to achieve injection)
  • the liquefied gas working medium is sprayed into the jet cyclone in a tangential direction to realize jet liquefaction and gas-liquid separation, and the non-condensed gas is discharged from the outlet.
  • the condenser is condensed by single or multiple series or series-parallel combination.
  • Gas out "1 channel adopts straight-through mode or use increase
  • the method of collecting the flow of the swirling force; the so-called extraction steaming process means that the heat pump power system extracts the vapor in the evaporation chamber to maintain the evaporation chamber in a supercooled state, and the supercooled liquid working medium and the liquefaction cause the gas working medium to be exchanged through the heat exchanger. Heat or directly pumped into the condenser through a circulation pump to cool and liquefy the cold gas working fluid.
  • the compressed cooling and liquefaction process refers to gas
  • the process of heat recovery and cooling or liquefaction by the heat exchanger after the temperature is reduced, that is, the heat generated by the heat pump effect is absorbed by the heat exchanger.
  • the thermal process can produce 3 ⁇ 4 critical conditions for cooling (or lower liquid or gas working fluids, working for a closed cycle single heat source, L: ⁇ mining / ⁇ ) jet refrigeration process or extraction steam process in circulation A 3 ⁇ 4 plus heat exchanger is required between the working fluids to ensure that the low temperature gas source reaches the required parameters.
  • the expansion work system or the heat pump system W uses a jet helium gas to provide a power source or pumping power for the expander to create a nozzle or a hot 3 ⁇ 4 system, which reduces the cost and simplifies the system.
  • the injection helium system 3 ⁇ 4 uses a staged ejector pumping, or a single-stage or multi-stage cyclic jet pumping, or a combination of cycle or parallel connection or cycle and series.
  • the nozzle of the same stage of the jet pumping system adopts a single nozzle distribution or a multi-nozzle distribution
  • the injection method adopts a direct current or a swirling flow or an oblique swirling flow between the two, the jet and the jet
  • the diffuser tube adopts a straight tube structure or a single-stage or multi-stage circulating ejector jet and a diffuser tube adopts a throat type zoom structure.
  • the so-called cyclic jet pumping refers to the air source after the pumping and pumping process of each stage of pumping and pumping, and the final stage pumping pumping is the exhaust of the heat power conversion device after the expansion work.
  • the invention also proposes a single-stage multi-cycle bad jet pumping method, wherein the power source feeds the nozzle to extract a low gas source, and the characteristic is: the jet pumping process adopts a multi-stage injection multi-cycle mode, the circulation pipeline iiS The scoop tube passing through one end of the ejector receives a part of the high-speed airflow to generate a punching or a rushing flow is adopted at one end by a tangential opening inside the ejector to receive a part of the high-speed airflow, and the other end is circulated by the jet suction, and the spraying method adopts a direct current or a swirling method.
  • the multi-stage injection multi-cycle method avoids repeated compression and injection of the working fluid, which simplifies the structure and improves the internal circulation efficiency.
  • a typical self-cooling thermal system ⁇ -type cycle is a gas-powered system.
  • the fuel provides a heat source for the system working fluid in the combustion chamber and oxidant combustion, and can be used as a swell-exhaust pumping system expander or a nozzle to expand the work system.
  • the power gas source first enters the circulating jet pumping system and then enters the expander or the spray mountain circulating jet pumping system to provide the fairy pump power or the compressed air power for the heat pump system, or uses the system waste heat for the working fluid cold liquefaction or reduction process. Thermal power.
  • the liquid working medium boosts the heat absorption to become the power source.
  • the thermal boosting method refers to the thermal boosting container. When the discharge flow rate is restricted or sealed, the pressure will rise significantly to achieve heating.
  • Boost which can reduce the internal power consumption of the self-cooling thermal system, can be combined with a hydraulic pump or a combination of 3 ⁇ 4 boost and thermal boost.
  • the self-cooling thermal work method can do the work of a single heat source.
  • the objective h proves that there is an error in the second thermodynamics, which is at least one-sided and will have an important impact on thermodynamics. It can be summarized as follows: (1) System Internal heat work The process "cold source” is a must, but the heat source can be created by a heat pump [3 ⁇ 4 cold". The external cold source is not necessary. The overall thermal cycle system can be independent of the second law of thermodynamics to achieve a single heat source. (2) The system does the functional heat source temperature and the system pressure and the physical properties of the working medium. The ambient air or water resources have approximate constant temperature heat, which is available energy. The air energy engine can be fully realized, and the pure air energy engine heat is received.
  • the environment is ultimately bound to be released into the environment without affecting the environment.
  • the maximum thermal efficiency is 1, which theoretically decreases infinitely close to 1 as the boiling point of the selected working fluid decreases.
  • Gas contains both heat generated by fuel chemical energy and air heat. If air heat is not included in the heat source, the fuel engine's fuel thermal efficiency may be greater than one.
  • the heat pump process power consumption is a must for a single heat source work system. Even if the system is insulated from the external environment, at least the internal working fluid flow loss will increase the internal heat pump power consumption. The thermal system can absorb heat from a single heat source. It is completely converted into work but it is impossible to affect the external environment and internal heat pump power consumption at the same time.
  • the work of a single heat source is to circulate Q2 within the system without discharging it outward. The heat efficiency is increased by reducing the heat absorbed from the heat source, but the power output of the system cannot be increased.
  • a new method of self-cooling thermal work is proposed, which not only can greatly improve the thermal efficiency but also achieve a single heat source work, has good 3 ⁇ 4 utility, can be used in any energy power system, and the air energy engine will be widely used. .
  • the liquid working temperature obtained is always lower than the temperature before liquefaction, which creates conditions for increasing the low-temperature heat recovery heat exchanger, indicating that the thermal system can be completely Creating a low-temperature heat source does not require an external environment to provide the most critical problem for a single heat source.
  • the use of the circulating jet pumping power system for thermal expansion work and the liquefaction of the gas working fluid for jet or extraction refrigeration creates the advantages of high efficiency and low wood formation, which can adapt to the high parameters provided by any system and can solve the small unit.
  • the serious volume loss problem of the thermal system has the advantage of no rotating parts, and it is easy to achieve isothermal expansion or reheat expansion in the process of absorbing air heat expansion work, so that the self-cooling thermal system including the air energy engine has good practicability.
  • the traditional gas thermodynamic cycle can improve the temperature environment of the turbine rotor while satisfying high parameters and high efficiency.
  • the thermal boosting method is used to make the thermal system rotate less or even without rotating mechanical work, and achieve no power consumption, and it has better practicability in small air units such as air conditioners.
  • Compressed air forced air heat exchange not only avoids the heat exchanger frosting caused by low temperature working fluid, but also can improve the initial parameters to reduce the volume of the thermal system, increase the power output, and make the air work system especially air. The practical performance of the engine has been greatly improved.
  • the invention also proposes a combination of a jet swirl heat exchange heat pump and a compression refrigeration type temperature liquefaction method, which can realize the liquefaction of the working medium under high pressure and temperature, so that the system can avoid the problems of dehumidification and frosting, and is more optimized and practical. Other areas of industrial heat exchange are also important.
  • a new method for gas liquefaction is provided.
  • the working temperature of the cooling and heating system is 3 ⁇ 4 air, the liquefaction ratio can be reduced to output liquefied air or liquid nitrogen.
  • the present invention will contribute to energy conservation and consumption reduction in the industrial and civil sectors, and is generally extremely important for energy development. DRAWINGS
  • Figure 1 is a schematic diagram of a closed self-cooling thermal power cycle.
  • FIG. 2 is a schematic view of a jet cyclone in an injection refrigeration liquefaction system.
  • Figure 3 is a schematic view showing the structure of the jet cyclone with the drum added.
  • Figure 4 is a graph of six temperature entropies for the self-cooling thermal work process.
  • Figure 5 is a schematic diagram of the self-cooling thermal work cycle in parallel with the liquefaction process.
  • Figure 6 is a schematic diagram of a self-cooling thermal power cycle in parallel with the liquefaction process of extraction steam and the process of doing work.
  • Figure 7 is a schematic diagram of a ⁇ or multi-stage through-tube jet aspirator.
  • Fig. 8A is a schematic diagram of a split type multi-stage series circulating jet pumping system using a reheating method and a gas turbine.
  • Fig. 8B is a schematic view showing the K-mode of the split type jet air extractor.
  • Figure 9 is a schematic diagram of a series of parallel and cyclic combined composite ejector aspirator.
  • Figure 10 is a schematic diagram of the principle of a single-stage injection multi-cycle jet aspirator built into the circulation line.
  • Figure 1 is a schematic diagram of the principle of a single-stage multi-cycle jet aspirator with a combination of internal and external circulation.
  • Figure 1 2 is a schematic diagram of the principle of a single-stage multi-cycle jet aspirator external to the circulation line.
  • Figure 13 is a schematic illustration of two internal stampings for a single-stage, multi-cycle injector.
  • Figure 14 is a schematic illustration of the lateral pumping mode of a single stage multi-cycle injector.
  • Figure 15 is a schematic view showing the structure of a jet cyclone heat exchanger.
  • Figure 16 is a schematic diagram of a self-cooling engine using a multi-stage multi-cycle injector and compression-cooled cooling.
  • Figure 17 is a schematic illustration of a self-cooling engine employing a multi-stage, multi-cycle injector and compression-cooled refrigeration.
  • Figure 18 is a schematic diagram of a self-cooling engine using a compressor and compression-cooled cooling.
  • Figure 19 is a schematic diagram of a gas turbine system in a jet pumping system in a jet pumping system.
  • Figure 20 is a schematic view of the combustion chamber cloth S in the circulation pipe of the jet pumping system.
  • Figure 21 is a schematic diagram of a self-cooling thermodynamic cycle using thermal boosting.
  • Figure 22 is a schematic diagram of a self-cooling thermodynamic cycle for cooling or heating. detailed description
  • Embodiment 1 closed self-cooling thermodynamic cycle:
  • the closed-type self-cooling thermodynamic cycle uses a jet refrigeration liquefaction system 101 to achieve gas refrigerant heat liquefaction, using a cyclic jet aspirator 109 and a gas turbine unit 10 (or other type of expander).
  • the expansion work system is combined to provide pumping and jetting power to the refrigeration liquefaction system.
  • the working fluid can generally be air, nitrogen, C02 or lower boiling point.
  • the gas such as the mouse M may also be a high boiling point gas such as water vapor.
  • the liquid working medium generated by the refrigerating and liquefying system 101 is boosted by the pump 103, and the heat is absorbed by the regenerative heat exchangers 104, 105 and 106, and then absorbed by the heater 108 to absorb the heat of the heat source.
  • Evaporation or gasification (below the critical temperature is called evaporation supercritical called gasification) ⁇ degree into ⁇ rise into a power source.
  • the power gas source enters the expansion work system, that is, the circulating jet air extractor 109 and the gas turbine 1 1 0 work to discharge the low temperature gas working medium, and the low temperature gas working medium is cooled by the heat recovery heat exchanger to become a cold gas working medium (cold gas working medium)
  • This 3 ⁇ 4 refers to a gas working medium that can be sprayed and liquefied by cooling to a saturated or near-saturated temperature.
  • the cold gas working fluid is injected into the jet cyclone 101 through the nozzle 14 (also as a jet refrigeration liquefier or condensation).
  • the inner part is condensed and liquefied and separated by gas and liquid.
  • the liquid working medium enters the lower storage tank 102, and the pump 103 is pressurized from the pipeline below the storage tank to start a new heat cycle.
  • the uncondensed cold gas passes back from the upper outlet pipe.
  • the heat exchanger 105 absorbs the heat of the low-temperature gas discharged from the system, and then is heated by the flow-through diffuser 1 13 to be pumped away by the circulating jet aspirator 109 (the regenerative heat exchanger is connected by a dotted line on the left and right sides).
  • the heat transfer relationship and heat transfer direction are independent of the heat exchanger structure. The following figures are similar to the dotted line unless otherwise specified.
  • the regenerative heat transfer should ensure that the temperature of the gas working fluid drops enough to become the cold air source needed for the refrigeration liquefaction, and at the same time reduce the heat source consumption to improve the thermal efficiency.
  • the heat exchange amount can be selected according to the needs, and should be as far as possible to achieve the exhaust heat all the regenerative cycle work, heat recovery
  • the heat exchanger can be used in series or parallel ⁇ ⁇ according to the flow force of the low-temperature gas working medium, or it can be arranged in series with each other.
  • the heat recovery heat transfer is added to satisfy the liquefaction of the working fluid as much as possible.
  • the specific needs may not be limited to the layout.
  • the valve 1 1 1 and the valve 1 12 are used to adjust the ratio of the work of the gas turbine to the load of the refrigeration liquefaction system.
  • the overall work capacity of the thermal system is generally adjusted by the mountain pump 103, and is also adjusted to match the heat load of the heater 108.
  • the jet aspirator 109 is generally indicated for all types of jet extractors, and is not limited to the single-nozzle three-stage circulation structure shown.
  • a similar heater 108 indicates any heating mode, such as boiler heating, residual heat heating, High-temperature equipment cools the heat, radiates solar energy, uses the atmosphere or sea water to heat it, and uses the atmosphere as a heat source to become an air-energy engine.
  • FIG. 1 shows a closed cycle, which can increase the external heat sink or external heat dissipation heat pump in the exhaust gas working channel to be a self-cooling thermal cycle that is partially discharged to the outside of the system, or can be drawn in the drawing according to the need.
  • the ⁇ or ⁇ 2 or point on the road or discharge line is separated into an open cycle.
  • A is a schematic diagram of the main structure of the jet cyclone
  • B is a schematic diagram of a nozzle tangential injection
  • a broken line indicates a jet flow direction
  • C is a schematic diagram of a flow guiding device 121.
  • the flow guiding device is mainly for changing the swirling flow into a linear flow to recover the swirling flow force and decelerating the diffusing pressure.
  • the guiding vane may be a plurality of pieces or a volute diffusing "single piece" structure.
  • the pumping and gas turbine exhaust of the jet aspirator 109 causes a gas pressure to generate a pressure difference inside and outside the condenser, and the low-temperature gas working fluid is injected into the cyclone through the nozzle 1 14 to achieve jet cooling and liquefaction.
  • the gas and liquid are separated, and the uncondensed gas is discharged from the outlet pipe 123.
  • the cyclone separator can be used in a single or multiple series or parallel manner, and the straight through structure in the outlet passage or the flow guiding diffuser 121 is used to recover and utilize the cyclone power reduction. Small refrigeration liquefaction system resistance.
  • the condensed liquid working medium is collected and collected in the storage tank 102, and the swirling flow is increased by the flow guiding diffuser 122.
  • FIG. 3 The inside of the present invention is shown in Fig. 3, in which the main shaft casing 13 1 and the rotating drum 132 are formed, and the upper and lower ends of the rotating drum extend outwardly and the short shafts are respectively supported by the upper and lower grid brackets of the outer casing (using a grid type)
  • the bracket is for the convenience of airflow.
  • the cryogenic liquid medium is sprayed from the nozzles on both sides of the casing and passes through the gap of the drum side grid to tangentially enter the inside of the drum to generate a swirling flow.
  • the 133 can be designed to be combined with a guide vane into a -3 ⁇ 4 structure.
  • the separated liquid working fluid flows downward from the inner wall of the rotor downward from the gap of the lower side of the drum and the gap of the lower side of the grid.
  • the addition of the rotating drum can greatly reduce the resistance of the jet cyclone, and can fully utilize the advantages of low cost, high efficiency, simple and reliable injection cooling, and the magnetic suspension bearing can better adapt to the jet and high speed.
  • the temperature entropy diagram shown in Fig. 4A is used to approximate the cycle process, the outer ring represents the Carnot cycle (ie, the work cycle), and the inner ring represents the reverse card.
  • Connaught cycle ie heat pump cycle
  • three dashed small boxes represent the three heat exchange processes of the heat pump cycle and the fsj of the work cycle, ! ⁇
  • T 2 corresponds to the condensation temperature
  • the internal and external circulation shown in the figure is not completely closed to clearly indicate the transfer process of Q 2 throughout the cycle.
  • Heat pump power consumption W P absorbs heat process heat Q 2 generates heat of Q2+W P into the expansion work system to do work W P , the remaining heat Q2 is absorbed by the heat absorption process through the heat recovery heat exchanger, so the wood should be from the heat source Endothermic ( ⁇ )
  • the self-cooling thermodynamic cycle can use heat pump to create a cold source below ambient temperature.
  • the heater (including the reheater) can absorb various special heat sources such as gas and various kinds.
  • Residual heat and solar radiation, etc. are pure air energy engines only when absorbing air energy.
  • the regenerative heat exchanger is distributed as shown in Figure 1, corresponding to B in Figure 4, all Q 2 needs to be recovered to increase the initial temperature ⁇ Increase the exhaust gas working temperature T3, set the minimum reheating temperature to meet the needs of a single heat source for work.
  • ⁇ working fluid condensation temperature ⁇ , latent heat R, liquid H medium heat ratio C, exhaust gas working medium constant pressure Specific heat CP, there is
  • T 4 R / C+T2 (2 )
  • the low-temperature condensing pressure is a large atmospheric pressure, and the working fluid is nitrogen gas with a formula of (1).
  • the temperature is 263K (-10 ⁇ ).
  • the reheater can be added in Figure 5. 221 corresponds to the reheat expansion (or isothermal expansion) shown in C of Fig. 4 as much as possible so that ⁇ 3 is larger than ⁇ 4.
  • ⁇ denotes an entropy-expanded air-energy engine, which can be used in Figure 6.
  • the regenerative heat exchange mode is shown, that is, in order to satisfy the heat recovery process from the expansion work process that absorbs the heat of the heat pump.
  • the condensing pressure at a low temperature is one atmosphere.
  • the formula ( 4 is about 910K (637°C), which is beyond ⁇ (55CTC for general thermal power units).
  • the scheme of reducing the number of reheat cycles is equivalent to reducing R.
  • F denotes a circulation mode in which the thermal circulation discharge working medium is cooled by compression cooling to a low-temperature compressed gas without liquefaction, and a constant temperature or a constant entropy expansion process may be employed, and the expansion work process may be used to heat back to the heat absorption process.
  • the heat pump process is indicated by a broken line.
  • the heat pump exhaust gas separated by the jet cyclone liquefaction process can directly reach the temperature of T5 by diversion and diffusion, if it is preheated by heat recovery.
  • T 4 corresponding to the re-flow and diffusion
  • the temperature of the TV can be reached.
  • the temperature of the expanded working medium is increased, and the temperature is increased.
  • One of the characteristics of the ring-jet expansion work is that the heat of the final-stage absorption heat pump is automatically uploaded with the cycle injection step by step, which is especially beneficial to the step-by-step iHl heat of the iil cold work cycle, which ensures the heat recovery requirement of the single heat source work.
  • the circulating jet pumping system provides the pumping power for the thermal system at the final stage.
  • the heat pump process obviously consumes only a part of the power of the power source.
  • the heat pump exhaust gas reaches the T5 ⁇ and can directly go to the endothermic process. Reheating is not absorbed by the first expansion process, and at least part of the heat pump exhaust can be made.
  • the heat pump exhaust gas working medium can also absorb the heat of the partial expansion work process to increase the heat recovery temperature.
  • the heat pump heat recovery to the heat absorption process will reduce the system output power, and the general shaft power reduction is WP.
  • any conventional thermal power cycle can always recover Q2 through a suitable expansion process, heat pump process and heat recovery process, and then achieve a single heat source work.
  • Figure 6 uses a steam extraction refrigeration liquefaction system.
  • the mountain circulation jet extraction system extracts the vapor in the evaporation chamber to maintain the supercooled state.
  • the supercooled liquid working fluid is pumped into the condenser 218 through the circulation pump 215 to spray and mix the gas.
  • the low-temperature gas working fluid discharged by the turbine is cooled and liquefied by the cold gas working medium cooled by two sets of parallel regenerative heat exchangers, and part of the liquid working medium in the condenser enters the evaporator through the throttling channel or nozzle 217 to realize the circulating liquefaction process.
  • the circulation ⁇ is changed to the nozzle ⁇
  • the swirling flow is beneficial.
  • the extraction liquid cooling also makes the obtained liquid working temperature always lower than the pre-liquefaction gas temperature, which ensures the continuous stable operation of the refrigerating liquefaction and the regenerative heat exchange. Although there is throttling loss, there is no jet swirling compared to the injection cooling. The resulting high speed flow loss.
  • an auxiliary jet aspirator 219 is added in front of the working fluid liquefaction system in the heat pump process, and the cold gas working medium first enters the auxiliary jet aspirator to extract the working fluid liquefaction system. After the gas working fluid, it enters the working fluid liquefaction system, and is also applicable to other heat pump working fluid liquefaction schemes.
  • the working fluid liquefaction system can also adopt two or more series-parallel combinations, which can be selected according to specific conditions in practical applications.
  • the heater 221 is added to the circulation line of the circulating jet pumping system to reheat.
  • the reheating process or the isothermal process may be arranged in one of the following ways, (I) between the segmented expanders; (2) on the swirling casing of the composite jet pumping process; (3) during the jet pumping process Between two stages of injection; (4) on the circulation path of the cyclic jet pumping process; (5) combined in any two or more ways in h.
  • Increasing the thermal efficiency or output capacity of the self-cooling thermal work system only needs to increase the initial parameter pressure and temperature, while the pure air energy engine can be used to work at a constant temperature heat source to increase the capacity by increasing the pressure to increase the temperature or reheat process.
  • the large thermal system can be used.
  • Multi-stage hydraulic pump boost, small thermal system uses a plunger pump or other positive displacement pump to increase pressure, and low-boiling gas working medium is beneficial to utilize air energy, such as air or nitrogen.
  • the regenerative heat exchanger can be arranged in series or in parallel according to the flow direction of the low-temperature gas working medium, or can be arranged in series with each other.
  • the countercurrent heat exchange should be used to reduce T 4 as much as possible, and the regenerative heat transfer is increased to satisfy as much as possible.
  • Q 2 is all reheated and meets the needs of working fluid liquefaction. According to the specific needs, the regenerative arrangement can be not limited.
  • the heat pump system can use the heat pump process to absorb some or all of the heat released by the low-temperature gas working medium during the heat-discharging process or to absorb the heat of the partial expansion process.
  • the thermal system can be used for the expansion process or the expansion process. Absorbing part or all of the heat released by the heat pump process, the temperature or pressure of the thermal system working fluid that absorbs heat from the heat pump is not higher than the highest parameter of the power source; the heat system can adopt a regenerative process, and the regenerative high temperature exotherm has an expansion process. Or the heat removal process or both, the regenerative low temperature endothermic end has a heating process or a heat pump process endothermic working medium or both.
  • Mode 2 new jet aspirator:
  • FIG. 7 The multi-stage circulating jet aspirator is different, as shown in Figure 7 is a straight-through tube swirling jet aspirator.
  • the injection and diffuser process abandons the conventional throat scaling structure and adopts a straight-through tube (not limited to the same diameter). i can be gradually expanded or tapered.
  • the method of swirl injection where A represents a single-stage injection structure, B represents a porous injection schematic, C and D represent oblique swirl injection, wood tail has a flow guide, and E is a straight-through
  • the tube is a multi-stage circulating jet aspirator.
  • FIG. 8A is a split type multi-stage series circulating jet pumping system adopting a reheating mode combined with a gas turbine; the jet air extractor shown in FIG. 8B is arranged in a split-flow type, which can be at a high speed at a minimum temperature.
  • the swirling state is heat exchanged with the outside world, and the cyclone structure is advantageous for adopting high-efficiency heat exchange structures and materials, such as corrugated or ribbed structures and high-strength aluminum alloy casings, etc., the overall process is beneficial to achieve similarity to isothermal expansion. Reheating the heat process.
  • Figure 9 is a schematic view showing the structure of a combined injection aspirator in series parallel and cyclic combination, which can be used for high vacuum pumping and compression.
  • FIG 10 is a schematic diagram of a single-nozzle multi-cycle jet aspirator built into a circulation line.
  • the power gas source enters the nozzle from the nozzle 231.
  • the circulation line 232 receives the high-speed airflow through the scoop tube to generate the stamping while the other end is sucked by the jet.
  • the other Rj-like circulation lines are also subjected to high-speed punching through a scoop tube inside one end of the injector and by a jet stream at the other end (dotted arrows indicate airflow flow process), and finally through the exhaust pipe 233
  • the external low-pressure gas working medium is mixed and decelerated and then discharged from the outlet pipe 234.
  • the nozzle jet method can be a single nozzle or a multi-nozzle jet, either a linear jet or a tangential swirl jet or an oblique swirl jet between the two, and the swirling tube 234 can be used.
  • the flow diversion and expansion measures should be increased, and the swirling flow and the diversion flow are as shown in ⁇ and C in Fig. 2 or the volute structure is adopted, which is beneficial to The heat exchange is also beneficial to reduce the resistance to the inner circulation pipeline.
  • the nozzle structure in the circulation pipeline reduces the nozzle loss of repeated injection.
  • FIG. 11 is a schematic diagram of a single-stage multi-cycle combined jet aspirator with a built-in and outer crust in the circulation line
  • Figure 12 is a schematic diagram of a single-stage multi-cycle jet aspirator externally to the circulation line, which is convenient for any stage. Loops and external connections increase application flexibility.
  • Fig. 11 is a schematic diagram of a single-stage multi-cycle combined jet aspirator with a built-in and outer crust in the circulation line
  • Figure 12 is a schematic diagram of a single-stage multi-cycle jet aspirator externally to the circulation line, which is convenient for any stage. Loops and external connections increase application flexibility.
  • FIG. 13 is a schematic view of the lateral pumping mode of the single-stage multi-cycle injector, which means that the single-stage multi-cycle jet air extractor can also increase the elbow pumping at the wood end and increase the direct flow of the deflector 315 to the rear jet. It can be used in the same way as a conventional jet aspirator.
  • the various embodiments of the induction jet pumping system can be divided into the following types.
  • the jet pumping system adopts single-stage jet pumping, or adopts a multi-stage or multi-stage circulating jet pumping, or a gas supply mode from a power source. It can be divided into a composite jet pumping with cycle and series or parallel combination or cycle and series and parallel combination (as shown in Figure 9); the same nozzle of the jet pumping system adopts single nozzle split or multi-nozzle distribution, jetting
  • the method adopts direct current (in line injection, general injection mode of ordinary injector) or swirling or oblique swirling between the two.
  • the jet and diffuser adopt straight-through pipe structure or multi-stage circulating injector.
  • the jet and expansion pipe adopts a throat type zoom structure, and the circulation mode can be divided into a single-stage injection single cycle. Ring (such as the cycle injector in Figure 1 only when the last stage pumping is used) or multi-stage injection multi-cycle (such as the composite injector of Figure 1) or single-stage injection multi-cycle (as shown in Figure 10 or 1 1)
  • the structure adopts the circulation pipeline built-in (as shown in Figure 10) or external (such as the traditional injection method or Figure 14) or the internal and external combination (Figure 11).
  • Embodiment 3 self-cooling thermodynamic cycle using compression and cooling liquefaction:
  • the working medium absorbs heat from the low temperature environment or the low temperature working medium by the expansion work
  • the characteristics are: the heat exchange unit adopts the cyclone The structure, the heat absorbing medium is tangentially or obliquely entered into the cyclone through the nozzle jet, and the spraying process is similar to the jet swirling flow shown in FIG. 2, and the high-speed jet is cooled and then absorbs heat through the wall of the cyclone and the external working medium or environment. Then, it is discharged into the exhaust pipe, and a straight-through mode is adopted in the exhaust pipe or a deflector method that increases the recovery swirling force is adopted.
  • the built-in exhaust pipe can reduce the volume, and the B exhaust pipe can be designed to reduce the resistance by large diameter.
  • the heat exchange process can use a heat exchanger composed of a single heat exchange unit or use two or more heat exchange units.
  • the heat exchangers can be combined in parallel.
  • the low temperature working fluid or the ambient air flows in the direction of the dotted arrow through the peripheral channel of the cyclone to exchange heat with the internal working medium, and the periphery of the cyclone can also adopt a heat exchange diaphragm to increase the heat exchange area to replace the passage, and can pass the fan.
  • Direct 3 ⁇ 4 working fluid or ambient air heat transfer can also be heated by compressed hot gas or direct heat source.
  • W m 16 is a self-cooling; it air-powered jet power circulation system, compressors 34] and 342 and gas turbines 35.
  • the shaft is operated, and the first stage compressor 341 and the secondary compressor 342 and the jet swirl type
  • the heat exchanger 353 and the surface heat exchanger of the single-stage multi-cycle composite injector 347 constitute a two-stage compression heat pump system. Air is drawn from the compressor 341 into the system and is compressed into the ejector surface heat exchanger. After cooling, the 347 enters the secondary compressor 342 and compresses again, then enters the heat exchanger 353 and cools down again to achieve liquefaction.
  • the liquefied air is boosted by the pump 354 and heated by the heater 346 to be heated to a power source to enter the single-stage multi-cycle ejector 347 for expansion work, and the air extracted from the suction line 348 is mixed and pressurized, and then discharged from the outlet pipe 349.
  • Part of the power to the gas turbine 351 is to satisfy the operation of the compressor, and the rest is to generate jet power through the nozzle 350.
  • the outer layer of the single-stage multi-cycle injector 347 employs a sandwich heat exchange structure, and the heating compressor 341 provides compressed hot air to form an approximately constant temperature expansion process inside the injector. Meanwhile, the heater 346 can also provide compressed hot air by the heating compressor 34. . It is also possible to use other heat sources such as gas-fired heaters 346 or 347 to become gas-powered engines.
  • a jet air extractor 361 is used to replace the secondary compressor on the basis of FIG. 16, and the power source of the jet aspirator 361 is derived from the initial power source of the expansion work system. It can also come from a source of power in the process of expanding work.
  • the refrigerating liquefied power gas source is connected in parallel with the gas turbine and is divided into two, one of which provides power to the nozzles of the two jet swirl heat exchange heat pumps through the line 363, and the second enters the jet swirl heat exchange heat pump through the line 364.
  • the increased jet pumping system can either provide the compressed hot air for the heat exchanger that absorbs the heat of the air as shown in Fig. 16, or the compressed air source for the compressed cooling or liquefaction process.
  • the cold jet pumping heat system can specifically supply compressed gas into an air pump system, and the heat generated by the compressed gas can be recovered by the system, and the heat generated by the conventional air pump compression cannot be recycled by the system.
  • an air energy engine system the heating compressor 372, the working fluid compressor 371, the high pressure expander 378, the low pressure expander 377, and the residual heat expander 376 work coaxially, according to the working direction of the working fluid.
  • Quality compressor 371 Two jet swirl heat pumps 379 are disposed in front and rear, and the mountain low pressure expander 377 provides jet cooling power, and the air flow discharged by the heat pump process is recovered into the waste heat expander. ⁇ The low-pressure expander adds a 3 ⁇ 4 heat exchanger, and the mountain heating DI reducer 372 supplies the hot air flow to the power source heater and the reheater through the heater 375, and the heated airflow from the heat exchanger enters the residual heat expansion.
  • the machine 0 receives the expansion work, and the heating compressor can ensure that T1 is greater than T4, which is good for normal operation even in cold winters.
  • the addition valve 374 can adjust the compression of the hot gas by controlling the external exhaust volume to achieve adjustment of the system operation and output power. Regardless of axial flow, centrifugal or positive displacement, compressors and expanders are very mature in the industrial field, either coaxially or independently, making it easy to implement simple and reliable engines, but compared to the cost of using a cyclic jet pumping system. high. Such an engine system can be started by adding liquid working medium as in the foregoing embodiments and heating.
  • each of the examples in the embodiment adopts a two-stage cooling compression liquefaction mode, and a multi-stage cooling compression optimization scheme can also be adopted in practical applications.
  • the ⁇ example uses the pumping force after liquefaction, and in fact, it can be used for re-cooling or isothermal compression. The cycle process is as shown in Fig. 4F, and liquefaction is insufficient.
  • heat exchangers that absorb air heat use compressed hot air or forced air heat transfer, compressed hot air or forced air can be supplied by a mountain compressor or fan, or composite jet pumping Provided by the system.
  • the heat transfer forced heat exchange can avoid the problem of frost on the surface of the heat exchanger during the heat absorption process of the liquefied gas.
  • the jet pumping system uses air as the working fluid, it can also extract the low temperature working fluid to provide a compressed air source for the compression cooling or liquefaction process, or specialize in the production of compressed air.
  • Embodiment 4 self-cooling gas engine:
  • Figure 19 shows a jet engine (or gas turbine) employing a self-cooling liquefaction process with a combustion chamber disposed within the composite jet aspirator 406, air and pressurized fuel (provided by the mountain line 405) for combustion absorption in the combustion chamber.
  • the heat energy released by the combustion is expanded into a gas source of a gas turbine or a nozzle after circulating injection expansion in the composite injector.
  • the jet refrigeration liquefaction system employs a two-stage series-connected jet cyclone liquefier, the mountain circulation jet degassers 404 and 403 respectively provide primary compressed air and secondary compressed air, and the circulatory jet air extractor 406 provides pumping for the liquefaction system.
  • the aerodynamics completes the heat pump process, and the heater 402 absorbs heat from the combustion chamber and absorbs heat from the engine.
  • the air liquefaction does not have to be lower than the ambient temperature, so a conventional compression cooling method can be used, for example, the cooling medium is not taken from the compressed gas source but directly through the line 408.
  • the air, jet cyclone heat exchanger 409 can also be replaced with a conventional gas heat exchanger, but the result is that the air liquefaction system is relatively bulky. It is also possible to pass the cooling water through the line 408 by a conventional water cooling method, and the jet air extractor 406 can recover the heat of the cooling water by extracting the steam in the cooling water tank by the combined jet pumping method.
  • the thermal system can provide heat source for the system working fluid through fuel combustion. It can be used in one of the following ways: (1) combustor cloth. Before the working fluid is boosted and then enters the jet pumping system, the working medium enters the combustion chamber to absorb the fuel combustion heat to become gas power. (2) When the jet pumping expansion work system is arranged separately, as shown in Fig. 8 ⁇ or 8 ⁇ , the split arrangement or only the stage where the combustion chamber is arranged, the combustion is arranged in the jet pumping system. Between the stage injectors, the working fluid coming out of the front stage injector enters the combustion chamber and is heated to become a gas-powered gas source and then enters the next stage injector; (3) the pressurized fuel is directly injected into the primary or secondary of the jet pumping system.
  • the power source makes the jet pumping system have the function of the combustion chamber; (4) using the boiler method, the fuel and air or oxygen are burned in the combustion chamber, and the pressure is boosted. After the working fluid is absorbed into the combustion chamber or the heater in the flue, it becomes the power source; (5) After the working fluid is boosted, it absorbs heat through the combustion system of the combustion chamber or absorbs the residual heat of the engine or both heat absorption processes. There are; (6) the combination of mode (5) and one of the first four.
  • the thermal system can adopt single-stage injection single cycle or • Ti-stage injection multi-cycle or multi-stage injection multi-cycle and other injections: W! gas system, power gas
  • the source of the power from the beginning of S can also be used to expand the power source during the work process. It is used to expand the power process to power the expander or spray or heat pump or to jet the air blower or draft fan in the raft cycle. Or pressurizing the gas (replace the expander or nozzle with a jet aspirator) to provide a source of power, or to provide a compressed air source for the compression cold or liquefaction process of the heat pump process (see 403 in Figure 19).
  • Embodiment 5 a self-cooling thermodynamic cycle using thermal boosting:
  • Figure 21 is a self-cooling thermodynamic cycle of intermittently working thermal boosting, which is characterized by the use of a closed vessel to increase the force significantly.
  • the Hawthorn heat exchanger provides hot two sets of booster vessels. 508 pay f ⁇ L complement work to provide relatively stable pressure for the system.
  • the boosting vessel 508 receives the liquid heat-discharging process of the system or the liquid working fluid produced by the condenser of the liquefaction system, and is connected to the pipeline through a one-way valve, and the guiding performance can be realized by mechanical turbulence or electric control, but such
  • the working mode can rely on gravity flow, and a circulation pump plus a check valve can be used for convenience control.
  • the jet suction type residual gas power recovery device 504 is added, and the injection pumping structure may be a single stage or a multi-stage composite jet pumping, and the valve 502, the valve 503, the valve 506 and the valve 507 are added, and the two under the riser container are
  • the check valve is combined to form a switching valve group, and the switching valve group is controlled by the control system to connect or isolate the boosting vessel and the boosting pipeline and the residual gas power recovery device H 504, so that the two boosting vessels are alternated.
  • the thermal system maintains a stable working pressure and recovers the residual power before each filling of the liquid level.
  • the gas-liquid separator 509 and the pump 501 are added to the heating passage of the boosting vessel 508, and the boosting mode combining the thermal boosting and the pumping boosting can be realized, and the one-way valve can be added to the front outlet of the pump 501 to realize the thermal boost independent. Work and switch with the pump T.
  • the self-cooling thermal work system is used in an air-energy engine, the low power intensity is slightly weaker due to the temperature parameter, but the pump power consumption can be reduced to improve the system power output.
  • the air-powered jet power system can be used for single-nozzle injection or multi-nozzle injection because of the low injection temperature.
  • the system is simple and low-cost, and can be used in both air and ground mobile equipment.
  • thermal boost system and the pump 501 complement each other to prevent the pump from operating in ultra-low temperature liquid nitrogen or liquid air environments.
  • the thermal boosting mode can also adopt a single boosting vessel staged operation, eliminating the valve group alternating control and the residual gas power recovery device 504, and the simple features can be used for the small micro thermal power generation system, and the battery can be supplemented or directly used.
  • One or more of the 3 ⁇ 4 systems work simultaneously to complement the discontinuity.
  • the liquid working fluid generated by the heat removal process of the thermal system adopts thermal boosting.
  • thermal boosting refers to increasing the receiving volume of the pressurized container and receiving the liquid working medium.
  • the valve is added or the check valve and the circulating pump are added, the liquid working fluid in the boosting vessel is boosted by heating, and the intermittent or complementary boosting is realized by controlling single or multiple boosting vessels; or hydraulic power is used.
  • the pump or the volumetric pump is boosted; or the gas-liquid separator 509 is added to the heating passage of the thermal boosting vessel, and the pump 501 is added to the liquid passage to realize the combined pressure increase of the heat and the pumping force.
  • Embodiment 6 self-cooling heat pump heating or cooling: As shown in Fig. 22, the jet swirl heat exchange heat pump cycle, the heat output of the heat exchanger 603 is increased between the final stage of the circulating jet pumping system and the expander, and the outlet of the liquefaction system and the jet extractor are The pumping port asks for the cooling source of the heat exchanger 605, and the heat system realizes the cooling or heating when the self-cooling heat work is completed.
  • the cost of the compressor is not simple and reliable.
  • the heat source of the self-cooling thermal system may be air energy or fuel, etc.
  • the heat exchanger that can increase the external heat output may be connected with the expander ⁇ in parallel or in place of the expander;
  • the heat process increases the heat output of the heat exchanger or the heat source is 3 ⁇ 4 ⁇ 4 plus the heat source of the heat absorption heat exchanger, or both of the output sources are used.
  • the power can be directly generated by the expander 604 to provide the lii force to the pump 601 (such as the cabinet). ⁇ The two are connected by the dotted line), so that the heater 602 can be used to provide heat into the heat-cooling and heating unit, which is not like nj. It does not consume power, and it is also cooled by heat and cold.
  • the thermal system adopts the power supply independent working mode
  • the W provides energy or liquefied gas storage system to provide dynamic or stable power.
  • the thermal inertia characteristics of the mountain or the heating zone generally allow the heat pump system to have fluctuations.
  • the air conditioner often works intermittently. Therefore, the self-cooling heat pump adopts the thermal boosting mode of a single thermal booster, and may even not be used. Pumping can greatly simplify the system's maximum cost advantage.
  • Embodiment 7 improvement of the cyclone
  • the working mode of the jet vortex is very important for the liquefaction of the gas-off working fluid and the simplified efficiency of the jet aspirator.
  • the rapid swirling flow has a large flow loss due to the centrifugal pressure, except for the internal 3 ⁇ 4 shown in Figure 4.
  • the method of expanding the work process or the heat pump process is adopted.
  • the swirler wall is corrugated, for example, a sinusoidal wave surface is used, and the jet gas is mainly at a small peak.
  • the ratio of the surface of the surface has a flow force, and the wave valley ill has a vortex because the suction pressure of the high-speed jet is very small « 3 ⁇ 4 ⁇
  • the state flow loss is small, and the ratio of the waveform and the wavelength to the diameter of the wall is to be set.
  • the flow loss of the swirling flow ⁇ is the magnitude of the person. Outer W, ⁇ ⁇ to 3 ⁇ 4 River swirler corrugated tubular wall of the inner cylinder and distributed pores or slits, Suo-tau mass strikes the inner tube; ⁇ :.
  • Embodiment 8 high boiling point thermal cycle
  • the heat pump system firstly liquefies the high boiling point working fluid during the liquefaction process of the mixed working fluid, and the high boiling point working fluid after liquefaction is heated and heated.
  • Power gas source, low boiling point working fluid pumping cycle, the most typical is steam plus nitrogen or carbon dioxide or air.
  • Another method for improving the circulation of high-boiling working fluids is to adopt a double-cycle or multi-cycle method in which a high-boiling working fluid cycle is combined with a low-boiling working fluid cycle, for example, a heat-discharging process of a steam thermodynamic cycle is a heat source of a nitrogen thermodynamic cycle.
  • the high-boiling working fluid thermal cycle absorbs the heat source to work
  • the low-boiling working fluid thermal cycle absorbs the heat of the high-boiling working fluid thermal cycle and juxtaposes the heat pump process and the regenerative process satisfying the quenching type thermal work cycle, which can overcome the high boiling point work.
  • the thermal cycle is adapted to the temperature limit and overcomes the problem that ⁇ is lower than ⁇ 4.
  • the invention is a basic innovation and has a wide range of applications, and is not limited to the mode described in the mode (1).

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Abstract

一种自冷式热力做功方法，热力系统的工质从热源吸热做功，包括工质从低温状态升压吸热后成为动力气源的升温过程、动力气源进入膨胀做功系统后的膨胀做功过程，以及完成膨胀做功的低温气体工质进一步释放热量的排热过程，热力系统从升温过程、膨胀做功过程到排热过程后再到升温过程后实现热力循环过程，采用热泵过程使完成膨胀做功的气体工质降温或液化，热泵过程释放热量时工质的温度或压力参数小于动力源最大参数，由膨胀做功过程吸收热泵过程释放的部分或全部热量共同做功，采用了回热过程使系统排热最终由系统吸热过程吸收。同时公开了一种喷射旋流换热式热泵方法和喷射抽气方法。

Description

自冷式热力做功方法 技术领域
本发明属于热能动力领域。
背景技术
热力学第二定律是热力学基础结论从來没有被动摇， 但是遵守其规律热力做功系统必须 向低温热源排热而总是造成巨大的能源浪费， 例如单循环做功过程热效率最高只接近 50%， 如燃气轮机热效率不足 40%, 虽然 | | f'jij— 流热力学领域没有质疑的报道， 这并没有阻止人们 对其探索与思考， 尤其能源危机 环境破坏严重的今天， 任何可能的突破都是非常重要的。 为¾现 ·热源做功冇 -些解决方案， 遗憾的是还没有切实可行的案例， 归纳起来有以下几 种方案， Π ) 用热泵产热使热量在膨胀机做功， 这甲已被否定， 现实中理想的逆卡诺循环不 可能存在； （ 2 )认为定温过程膨胀做功比定熵过程多， 采用逆卡诺循环制冷源或制液体工质， 然后定温膨胀做功， 这同样足被 诺定律 定的， 因为 tt何可逆循环的热效率都和卡诺循环 相等。 ( 3 ) 利用热泵使气休. Ί :质液化， 将热泵排热通过回热换热器加热已经液化的工质, 再通过液体工质吸收空气能升温进入膨胀机做功， 这同样是现实中无法存在的， 错误的原因 Ί ( 1 )类似， 而且换热器不可能没有温差而交换热量， 即使开始能工作也会因为制冷量逐歩 衰减而最终停止工作。
尽管如此， 有以下几种情况使单一热源做功存在可能， 一、 上述方案没有把热泵过程与 膨胀做功过程分丌來考虑， 热泵过程温差越小制热系数越大而做功过程温差越大做功越多， 热泵主要任务应该是将气体工质液化或降温而没必要高参数排热， 没有充分灵活利用热泵优 势。 二、 喷射制冷技术可获得过冷液， 可以产生比液化前饱和气体温度更低的液化气， 有利 于持续实现回热换热。三、传统的喷射抽气器因为存在喉管缩放结构导致流动损失大效率低， 其结构与性能有很大的改进空问， 加上简单无转动件而且工质在液态泵力升压受热产生动力 消耗压缩功最小， 即喷射抽气制冷技术性能存在很大的提升空间。 发明内容
本发明的目的： 大幅度提 '热力做功效率， 乃至 ¾现单一热源做功。
本发明的技术方案： 热力系统通过热泵尽可能低参数回收完成做功后的排放热 Q2， 热泵 排放热通过膨胀做功过程吸收后回收压缩功， 通过回热循环最终使工质吸热升温过程吸收了 Qi , 使热力系统在满足同样热力循环的^提下向热源吸热量减少 Q2， 实现部分或全部 Q2只 在系统内部循环而不向外排放， 最大程度提高热效率。
具体方案为， 热力系统的工质从热源吸收热量做功， 包括了工质从低温状态升压吸热后 成为动力气源的升温过程、 动力气源进入膨胀做功系统后的膨胀做功过程， 以及完成膨胀做 功的低温气体工质（对于以空气为工质的丌式循环这単.的低温气体工质是从环境吸入的空气） 进一歩释放热量的排热过程， 热力系统从升温过程、 膨胀做功过程到排热过程后再到升温过 程后实现热力循环过程， 其特征是： 工质从^干环境温度的热源 （例如燃料燃烧或余热或地 热及太阳能热力等） 吸收了热最， 或从 于或低于环境温度的热源 （例如自然环境中的空气 或湖水海水等热源〕 吸收了热傲； 热力系统; β川了热 ¾过程吸收排热过程中低温气体工质释 放的部分成全部热量， 山膨胀做功过 R成 ι^Ί ΐ ΐ膨胀做功过程 升温过程吸收热泵过程释放的 部分或 ^部热量， 可以尽 nj'能降低热¾排热 或 力以减小热泵能耗： 热力系统釆 ffl了 L 'ι热高温端^膨胀做功过 w或排热过 或 ：- 都冇， | 1热低温端 w升温过稃或热 过¾吸热 T质或者 者都冇， | |热过 W通过从 端 Ι(ϋ低温端传热满足 Q2回收与循环。整 体方案的实质是热力系统内部丄质依然^ / 低温度之 循环丄作， liij对外》Γ以做釗 H收部 分或 部 rt.热实现大幅度捉 热效牢.， JK1、循环 : !'.作过 可以理解为: 热泵耗功 WP吸收热 力过程排放热 Q2后产 Q2+WP的热 进入膨胀做功系统做功 WP, 将剩余的热量 Q2通过 0热换热器被升温过程吸收， 这样本应该从热源吸热 的工质升温过程只需从热源吸热 Q- Q. - Q2 , 因为做功也是 Q Q2 , 因此 W=Q热效率为 1而不需要向冷源排热实现单一热源做功。 这说明， 只要解决好回热循环， ^少 n¾论卜. [ ^冷式热力循环可以利用热泵自动创造低于环 境温度的冷源， 可以从 气中吸热做功 liu成为纯 能发动机。
--般情况膨胀做功系统吸收热泵过 释放热 的方式¾}¾换热器换热或直接吸收其排放 丄质， 热 过程可以山膨胀做功过 W 1 接提供动 或山 门的动力装 提供动力。
冷式热力做功系统采用闭式循环 功时， 热 ¾过¾厲于内循环不从外吸热 tii不对外排 热， 系统从热源吸收的热量全部对外做功， Jii J - 'T'. 热源做功。 ：'1采用幵式循环对外做功吋， 1(1冷式热力做功系统可以做到排放热 :个人十从环境吸收热 rniiu等效于 *向环境排热， Hi 于单 ·热源做功， 其中一种特殊情况^ U 制冷成制热系统， 只/ 内部 压缩1 j膨胀的做功 过¾， 其对外输出热量等于从热源吸收热 Μ_。 ι;¾际运 ίΐ中不严格遵守单- ·热源做功的 [^冷 式热力做功方式， 尤其开始循坏， ι'ί使系统工作 活性。
提出一种喷射旋流换热式热泵方法，工质通过膨胀做功从低温环境或低温工质吸取热量， 其特征是： 向低温环境或低温工质吸热的换热单元采用旋流器结构， 吸热工质通过喷嘴喷射 切向或斜向进入旋流器， 高速喷射降温后通过旋流器壁与外部工质或环境吸热， 然后进入排 气管排出， 在排气管内采用: 通方式或采川増加 W收旋流动力的导流器方式， 换热过程采用 个换热单元构成的换热器或采川 个或多个换热 儿^成换热器， 如; {1并联组合。
1冷式热力做功系统的热泵过 ^可以 ¾川 ^射旋流换热式热泵， 或者采用了喷射制冷过 ¾或抽汽制冷过程或压缩冷却过程使 休: I：质降^或液化， 或者采用了喷射旋流换热式热泵 与后 Ξ (种使工质降温或液化过程之一组 ^的 'Λ. 采川了唢射制冷或抽气制冷过程使一部分 工质液化同时必然会使另 -部分气体工质焓 ffl fi加，通过^流扩 后温度上升形成热泵效应。 所谓的喷射制冷过稃是指热泵动力系统 〔休: I：质1 j冷凝器之 产生压力差， 冷凝器采川了 喷射旋流器分离方式， 喷射旋流器采川了 的売休结构或采用壳体加内置转筒结构， 冷气 体工质 （这里指经过降温成为饱和或接近饱和 皮的 W以实现喷射液化的气体工质） 通过喷 嘴沿切线方向喷射进入喷射旋流器实现喷射制冷液化并气液分离， 未冷凝气从出口排出， 冷 凝器采用单个或多个串连或串并联结合的方式， 冷凝气出「1通道中采用直通方式或釆用增 加回收旋流动力的导流器方式； 所谓的抽汽制冷过程是指热泵动力系统抽取蒸发室内蒸汽使 蒸发室维持过冷状态， 过冷液体工质与液化 令气体工质通过换热器换热或通过循环泵直接 泵入冷凝器混合使冷气体工质降温液化， 冷凝器内部分液态工质通过节流通道或喷嘴进入蒸 发室实现循环液化过程； 所¾的压缩冷却液化过程是指气休工质经过 缩升温后被换热器吸 热降温或液化的过程， 即 热泵效应产生的热 ffl被换热器吸收。 热¾过程可以产生比制冷 (ΐί/ 更低的液体或气体工质， 为闭式循环单一热源做功创造了 ¾关键的条件， L:屮采/ Τ]喷射制冷 过程或抽汽制冷过程在循环工质之间需要¾加问热换热器确保低温气源达到需要的参数。
膨胀做功系统或热泵系统 W以采用喷射拙气过 fi!为膨胀机成喷管或热 ¾系统提供动力气 源或抽气动力， 可降低成本简化系统。 这 提出新的喷射讪 系统， 喷射讪气系统 ¾用了 级唢射抽气， 或者采 ffl了单级或多级循环喷射抽气， 或 采 ffl了循环 Ψ眹或并联结合或者 循环与串联及并联结合的复合喷射抽气； 喷射抽气系统的同级喷嘴采用了单喷嘴分布或多喷 嘴分布， 喷射方式采用了直流或旋流或者介于二者之间的斜向旋流式， 射流与扩压管采用了 直通管结构或者单级或多级循环喷射器的射流与扩压管采用喉管式缩放结构。 所谓的循环喷 射抽气是指喷射抽气过程中每级抽气抽収的足卜级抽 i 缩做功后的气源， 末级抽气抽収的 是热功转换装置经膨胀做功后的尾气或 它气源， 实现逐 ^循环抽气逐 ^ 人循环流量到木 级集屮膨胀做功， 单级循环喷射抽 直接抽取热功转换装 膨胀做功后的½气。 循环喷射抽 气动力系统原理的实; ^是， 无论足循环仙取本系统排 (还迠抽取 它气源， 都是动力气源抽 入被抽气源并对被抽入气源 缩做功的过程， ^参数动力 ^源/ 做功过 W屮参数降低换來质 贵流量增加而做功能力不下降， 即动力不减， 通过; I；联 ^并联及循环喷射抽气的
现高参数高效率运行。
本发明同时提出一种单级多循坏喷射抽气方法， 动力气源迎过喷嘴喷射抽取低^气源， 其特征是： 喷射抽气过程采用了^级喷射多循环方式， 循环管路 iiS过一端在喷射器内部的勺 管接收部分高速气流产生冲压或者通过一端在喷射器内部采用切向开口接收部分高速气流产 生冲压而另一端受射流抽吸实现循环流动， 喷射方式采用了直流或旋流或者介于二者之 I'nJ的 斜向旋流， 结构方式采用了循环管路内置或外置或内外结合布貿:， 喷嘴分布方式采用了单喷 嘴分布或多喷嘴分布。 ^级喷射多循环方式避免了工质反复压缩与喷射， 可简化结构并提高 内部流通效率。
一 -种典型的自冷式热力系统丌式循环是燃气动力系统， 燃料在燃烧室与氧化剂燃烧为系 统工质提供热源， 可以 ώ循环唢射抽气系统 膨胀机或喷管 成膨胀做功系统， 动力气源先 进入循环喷射抽气系统再进入膨胀机或喷 山循环唢射抽气系统为热泵系统提供仙气动力 或压气动力， 或者利用系统余热为工质 冷式液化或降 ^过程½供热动力。
液体工质升压吸热成为动力气源的过^可采川热力升 方式， 所 的热力升压^指热力 升压容器在排出流量受限制或密闭的条件下受热其压力会显著上升实现加热升压， 可减少自 冷热力系统内部功耗增加做功能力，可以采用液力泵或容枳¾升压与热力升压相结合的方式。
自冷式热力做功方法可以做到单一热源做功， 客观 h证明了热力学第二定俅存在错误， 至少是片面的， 将对热力学产 重要影响， 可总结为以下儿个方而： （1 ) 系统内部热力做功 过程 "冷源"是必须的， 但可以通过热泵 [¾冷创造 "冷源"， 外部冷源不是必须的， 整体的热 力循环系统可以不受热力学第二定律约束而实现单一热源做功。 （2 ) 系统做功能力山热源温 度与系统压力及工质物理性质决 ，环境空气或水资源具有的近似恒温热量是可利用的能源， 空气能发动机完全可以实现， 纯空气能发动机热量収之于环境最终也必然释放于环境而对环 境不产生影响。 ( 3 ) 无论利用空气能还是传统能源做功， 最大热效率为 1， 理论上随所选工 质沸点降低可以无限接近 1。 （4 ) 燃气既包括了燃料化学能产生的热量也包括了空气热量， 如果空气热量不计入热源则燃气发动机的燃料热效率可大于 1。 ( 5 ) 热泵过程耗功 （或耗能） 是单一热源做功系统必须的， 即使系统与外部环境绝热至少内部工质流动损失也会增加内部 热泵耗功， 热力系统可以从单一热源吸热使之完全转化为功但不可能同时对外部环境及内部 热泵耗功不产生影响。 （6 ) 同等热力系统条件下， 单一热源做功是将 Q2在系统内循环而不向 外排放， 因减少了 中从热源吸热量而提高了热效率， 但不能增加系统动力输出。
这早.涉及的工质气或气体的概念是包括空气、 烟气、 蒸汽、 湿空气及氟利品等各种单一 的或混合的气态工质的广义概念， 膨胀机是指包括气轮机及螺杆式膨胀机等各种使工质膨胀 对外做功的设备， 以下问。本发明足在专利屮请 CN201210165823.0 ( ·¾ PCT/CN2012/000724 , 内容相同） 基础上完成的， 涉及范围广将结合具体实施方式进一歩说明。 本发明的优点：
1 . 提出自冷式热力做功新方法，不仅可以大幅度提高热效率而且可以实现单一热源做 功， 有很好的¾用性， 儿乎可以用于任何能源动力系统屮， 空气能发动机将得到普遍利用。
2. 提出多种低参数热泵循环的气体工质液化方案，获得的液态工质温度总是比液化前 温度更低， 为增加低温回热换热器创造了条件， 说明热力系统完全可以 "自创低温热源" 而 不需要外部环境提供， 解决了单一热源做功最关键的难题。
3. 采用循环喷射抽气动力系统为热力膨胀做功及喷射或抽汽制冷的气体工质液化过 稃创造了高效率低成木的优势， 既可以适应任何系统提供的高参数又可以解决小机组热力系 统的严重的容积损失难题， 具有无转动件做功优势， 而且在吸收空气热量膨胀做功的过程中 容易实现等温膨胀或再热膨胀， 使自冷式热力系统包括空气能发动机具有很好实用性。 对传 统的燃气热力循环在满足高参数高效率同时可很好的改善涡轮转子的温度环境。
4. 采用热力升压方法使热力系统转动机械更少甚至无转动机械工作， 实现无功耗升 压， 在空调等小薇型机组具有更好的实用性。
5. 采用压缩空气强制通风换热， 不仅避免了低温工质带来的换热器结霜问题， 而且可 以提高初参数减小热力系统体积， 增大功率输出， 使空气能做功系统尤其空气能发动机的实 用性能大幅度提高。
6. 本发明同时提出一种喷射旋流换热式热泵与压缩制冷式降温液化方式组合，可实现 较高压力与温度下的工质液化使系统避免除湿结霜等问题而更加优化实用， 对于工业其它热 交换领域也有重要意义。
7. 提出采用柱塞泵及螺杆泵或其它高压容积泵为液化工质升压，在燃机系统中提出将 燃烧室布置在复合喷射抽气膨胀做功系统的过程中避免直接承受工质最高压力， 为发动机追 求高参数高效率大功率之极限扫清了障碍。
8. 为气体液化提供了新方法， 冷热力做功系统的工质¾ 空气时， 减少动力输出 ¾ 加工质液化比例就可以输出液化空气或液氮。
9. 本发明将对工业及民用领域节能降耗， 对能源开发将产 普遍枳极意义。 附图说明
图 1是闭式自冷式热力做功循环原理图。
图 2是喷射制冷液化系统中的喷射旋流器示意图。
图 3是增加了转筒的喷射旋流器结构简图。
图 4是自冷式热力做功过程的六种温熵图。
图 5做功过程与液化过程并联的自冷式热力做功循环原理图。
图 6是抽汽制冷液化过程与做功过程并联的自冷式热力做功循环的原理图。
图 7是 ^级或多级直通管喷射抽气器原理图。
图 8A是分体式多级串联循环喷射抽气系统采用了再热方式与气轮机组合示意 I 。 图 8B是旋流式喷射抽气器分体布 K方式示意图。
图 9是串并联及循环结合的复合唢射抽气器结^示意图。
图 10是循环管路内置的单级喷射多循环喷射抽气器原理示意图。
图 1 1是循环管路内外布置结合的单级多循环喷射抽气器原理示意图。
图 1 2是循环管路外置的单级多循环喷射抽气器原理示意图。
图 1 3是单级多循环喷射器的两种内部冲压示意图。
图 14是单级多循环喷射器的侧向抽气方式示意图。
图 15是喷射旋流换热器结构简图。
图 1 6是采用^级多循环喷射器与压縮冷却制冷的自冷式发动机示意图。
图 17是采用多级多循环喷射器与压缩冷却制冷的自冷式发动机示意图。
图 1 8是采用压缩机与压缩冷却制冷的自冷式发动机示意图。
图 1 9是燃烧室布贾在喷射抽气系统喷射管内的燃气轮机系统示意图。
图 20是燃烧室布 S在喷射抽气系统循环管内示意图。
图 21是采用热力升压的自冷式热力循环示意图。
图 22是制冷或制热的自冷式热力循环示意图。 具体实施方式
实施方式 1， 闭式自冷热力循环：
如附图 1所示的闭式自冷热力循环， 采用了喷射制冷液化系统 101实现气体工质排热液 化， 采用循环喷射抽气器 109与气轮机组 1 10 (或其它类型膨胀机） 组成膨胀做功系统同时 为制冷液化系统提供抽气与喷射动力， 工质一般可以是沸点低于常温的空气、 氮气、 C02或 者鼠 M 等气体， 也可以是水蒸气等高沸点气体。 沿箭头所示工质流动方向， 制冷液化系统 101产生的液态工质经泵 103升压后， 经过回热换热器 104、 105及 1 06 吸收热量后再经过加 热器 108吸收热源热量， 实现蒸发或气化 （低于临界温度称为蒸发超临界称为气化） ^度进 ^上升成为动力气源。 动力气源进入膨胀做功系统即循环喷射抽气器 109及气轮机 1 1 0做 功后排放低温气体工质， 低温气体工质经过回热换热器降温后成为冷气体工质 （冷气体工质 这 ¾专指经过降温成为饱和或接近饱和温度的可以实现喷射液化的气体工质， 以下冋）， 冷气 体工质经过喷嘴 1 14喷射进入喷射旋流器 101 (同时也是喷射制冷液化器或冷凝器） 内部分 冷凝液化并气液分离， 液体工质进入下面的储存箱 102， 从储存箱下面的管道进入泵 103升 压丌始新的热力循环， 未冷凝过冷气体从上部出口管通过回热换热器 105吸收系统排放的低 温气体热量后经过导流扩压器 1 13扩压升温后被循环喷射抽气器 109抽走 （回热换热器采用 左右两侧 0路上虚线框连接表示换热关系及传热方向， 与换热器结构无关， 以下各附图类似 虚线方式除专门说明外与此同意）。回热换热应确保气体工质温度下降足以成为制冷液化需要 的冷气源， 同时减少热源消耗提高热效率， 换热量可根据需要选择， 应该尽可能达到排放热 全部回热循环工作， 回热换热器按低温气体工质的流动力'向可以釆用串联或并联 Ακ， 或者 采用了互相间隔串联布置， 增加回热换热是满足尽可能使 Q2全部回热同时满足工质液化需 要， 根据具体需要可以不局限图示布置方式。 阀 1 1 1与阀 1 12用于调节气轮机做功与制冷液 化系统负荷比例， 热力系统整体做功容量一般山泵 103调节， 也 ^以配合加热器 108的热负 荷调节。
需要说明的是， 喷射抽气器 109为所有喷射抽气器种类一般性表示， 不局限于图示单喷 嘴三级循环结构， 类似的加热器 108表示任何加热方式， 例如锅炉加热， 余热加热、 高温设 备冷却吸热、 太阳能辐射、 利用大气或海水加热等， 采用大气为热源时成为空气能发动机。 另外， 附图 1所示为闭式循环， 可以在排放气体工质通道增加对外散热器或对外散热的热泵 成为部分向系统外排放的自冷式热力循环， 也可以根据需要在图中抽气管路或排放管路上的 Κι或 Κ2或 点分开成为开式循环。
附图 2是喷射制冷液化系统中的喷射旋流 ·器， 其中 A为喷射旋流器主体结构示意图， B 为喷嘴切向喷射示意图， 虚线表示喷射流动方向， C为导流装置 121 结构示意图， 导流装置 主要是为了将旋流改为直线流回收旋流动力并减速扩压， 导流叶片可以是多片也可以是蜗壳 扩压式 "单片"结构。 ώ于喷射抽气器 1 09的抽气与气轮机排气使气体工质在凝汽器内外产 生压力差， 低温气体工质通过喷嘴 1 14沿切线方向喷射进入旋流分离器实现喷射降温液化并 气液分离， 未冷凝气从出口管 123排出， 旋流分离器可以采用单个或多个串联或并联的方式， 出口通道中采用直通结构或采用导流扩压装置 121 回收和利用气旋动力减小制冷液化系统阻 力。 冷凝的液态工质下降收集到储存箱 102内， 也可以增加导流扩压装置 122后旋流增加压 力。
附图 3所示的内部增加了转筒的喷射旋流器， 主要山外壳 13 1与转筒 132组成， 转筒上 下端向外延伸有短轴分别由外壳上下栅板式支架支撑 （采用栅板式支架是为方便气流通过）， 低温液体工质从外壳两侧的喷嘴喷射后经过转筒侧栅板的间隙沿切向进入转筒内部产生旋流 并带动转筒转动， 旋流逐渐下移然后从中间出口通道螺旋上升， 并从转筒上侧栅板间隙以及 外壳出口通道内转筒支架栅板 133问隙流出喷射旋流器， 支架栅板 133可以设计为与导流叶 片合二为 - ¾结构。 分离出的液体工质顺转子内壁旋流向下从转筒下侧栅板 I'nj隙以及下侧支 栅板 l j隙流出。 增加转筒可以大幅度减小喷射旋流器的阻力， 可充分发挥喷射制冷低成本 高效率简单可靠的优势， 如果采用磁悬浮轴承可更好适应射流与高转速。
为进一 ^说明自冷式热力做功方法的原理，采用如附图 4屮 A所示的温熵图近似表示其 循环过程， 外环表示卡诺循环 （即做功循环）， 内环表示逆卡诺循环 （即热泵循环）， 三个虚 线小方框表示热泵循环与做功循环之 fsj的三个热交换过程， ！^对应系统动力气源初温或热源 温度， T2对应冷凝温度， 图示的内外循环没有完全封闭是为清楚表示 Q2在整个循环中传递 过程。 热泵耗功 WP吸收热力过程排放热量 Q2后产生 Q2+WP的热量进入膨胀做功系统做功 WP， 将剩余的热量 Q2通过回热换热器被吸热过程吸收， 这样木应该从热源吸热（^的工质升 温过程只需从热源吸热 Q= Qi- Q2， 因为做功也是 Qi-Q2， 因此 W=Q热效率为 1而不需要向 冷源排热， 实现单一热源做功。 这说明， 只要解决好回热， 至少在理论上自冷式热力循环可 以利用热泵 动创造低于环境温度的冷源， 加热器 （包括再热器） 可以吸收各种专门的热源 如燃气、 各种余热及太阳能辐射等， 只吸收空气能时即为纯空气能发动机。 回热换热器采用 附图 1所示分布时， 对应附图 4中 B , 将 Q2全部回收需要提高初温 Τ 进而提高排放气体工 质温度 T3， 设定满足单一热源做功需要的最低回热温度为 Τ .ι， 工质冷凝温度 Τ， 潜热 R , 升 H后液态工质比热 C , 排放气体工质定压比热 CP, 则有
Figure imgf000009_0001
Q2只有气化潜热， 则有
T 4 = R / C+T2 (2 )
低温冷凝压力为一个大气压强， 工质采用氮气以 （1 ) 式计算的 Τ.ί约为 263K ( -10Γ ), 对于 空气能发动机因为环境空气温度 Τι有限，可采用附图 5增加再热器 221对应附图 4中 C所示 的再热膨胀 （或等温膨胀） 尽可能使 Τ3大于 Τ4。 对于采用附图 4中 D所示的朗肯循环丙为 存在蒸发吸热可将 Τ4控制到或接近蒸发温度， 与 Β所示采用了定熵膨胀的空气能发动机， 都 可以采用附图 6所示的回热换热方式， 即为了满足 须从吸收了热泵排热的膨胀做功过程回 热到吸热过程。对于附图 4中 Ε的水蒸气再热循环在低温冷凝压力为一个大气压以（2 )式计 算 Τ4约为 910K ( 637°C )， 超出了 ΤΊ (一般火电机组为 55CTC ) , 只能采用减少再热级数的方 案， 等效于减小了 R。 附图 4中 F表示热力循环排放工质通过压缩冷却降温为低温压缩气体 而不液化的循环方式， 可以采用定温或定熵膨胀过程， 可以采用膨胀做功过程向吸热过程回 热。
如附图 4中 C所示用虚线表示了热泵过程，经过喷射旋流液化过程分离出的热泵排热气 体工质可直接经导流扩压可达到 T5的温度， 如果先经过回热预热到 T4对应温度再导流扩压 则可以达到 TV的温度， 进入膨胀做功系统后使膨胀过的工质热量增加温度升高， 而且多级循 环喷射式膨胀做功的一个特点是会把末级吸收热泵的热量自动随循环喷射逐级上传， 特别有 利于 iil冷式做功循环的逐级 iHl热， 可确保单一热源做功的回热要求。 事实上， 循环喷射抽气 系统是在末级为热 系统提供抽气动力的， 热泵过程显然只消耗了动力气源的一部分动力， 热泵排热气体工质达到 T5吋，可以直接向吸热过程回热而不用经过先被膨胀做功过程吸收， 至少部分热泵排热可以这样 ^成。 为尽可能满足单 --热源做功回热要求， 热泵排热气体工质 还可以先吸收部分膨胀做功过程的热量提高回热温度。 只是， 热泵排热回热到吸热过程会降 低系统输出动力， 一般轴功下降幅度为 WP。 综上所述， 任何采用传统的热力做功循环总是可 以通过合适的膨胀做功过程、 热泵过程及回热过程回收 Q2， 进而实现单一热源做功。
另外， 与附图 1膨胀机与工质冷却液化系统采用串联的方式不同， 附图 5与附图 6采用 了并联， 有利于强化制冷动力。 附图 6采用了抽汽制冷液化系统， 山循环喷射抽汽系统抽取 蒸发 ¾ 216内蒸汽使芄维持过冷状态， 过冷液体工质通过循环泵 215泵入冷凝器 218喷淋混 合使來自气轮机排出的低温气体工质经过两组并联的回热换热器降温后的冷气体工质降温液 化， 冷凝器内部分液态工质通过节流通道或喷嘴 217进入蒸发器实现循环液化过程， 节流通 逍改为喷嘴^产生旋流有利十增加循坏泵入口静 Hi fin节能。 通过在热泵过程中分离出的将要 进入膨胀做功系统的在扩 ffi升温之前的冷气体工质增加回热换热使喷射抽气动力系统与制冷 液化系统很好实现高低温隔离， 有利于喷射动力系统采用定温或再热膨胀过程。 采用抽汽制 冷同样使获得的液态工质温度总是比液化前气体温度更低， 可确保制冷液化与回冷换热的持 续稳定工作， 虽然存在节流损失但是相比喷射制冷没有喷射旋流产生的高速流动损失。
为优化工质液化前的温度、 力及流量参数， 在热泵过程中的工质液化系统前增加了辅 助喷射抽气器 219， 冷气体工质先进入辅助喷射抽气器抽取工质液化系统内气体工质后再进 入工质液化系统， 也适用于其它热泵式工质液化方案。 另外， 工质液化系统也可以采用两个 或多个串并联组合， 在实际应用中可根据具体情况选择。
在附图 5所示的自冷式热力系统中在循环喷射抽气系统的循环管路上增加了加热器 221 起到再热作用。 再热过程或等温过程可以布置为以下方式之一， （I )在分段膨胀机之间； （2 ) 在复合喷射抽气过程的旋流外壳上； （3 ) 在喷射抽气过程中的两级喷射之间； （4 ) 在循环喷 射抽气过程的循环通道上； （5 ) 以 h任意两种或多种方式组合。 提高自冷式热力做功系统热 效率或输出容量只需提高初参数压力与温度即可， 而纯空气能发动机屈于恒温热源做功可通 过提高压力增加定温或再热过程提高容量， 大型热力系统可以采用多级液力泵升压， 小型热 力系统采用柱塞泵或其它容积泵提高压力， 选择低沸点气体工质有利于利用空气能， 如空气 或氮气。 回热换热器按低温气体工质的流动方向可以采用串联或并联布置， 或者采用了互相 间隔串联布置， 一般应 ¾采用逆流换热尽量降低 T4， 增加回热换热是满足尽可能使 Q2全部 回热同时满足工质液化需要， 根据具体需要可以不局限图示回热布置方式。
综上所述， 热力系统可以采用热泵过程吸收排热过程中低温气体工质释放的部分或全部 热量或者吸收部分膨胀做功过程的热量， 热力系统可以 ώ膨胀做功过程或者 ώ膨胀做功过程 与升温过程吸收热泵过程释放的部分或全部热量， 吸收热泵排热的热力系统工质的温度或压 力不高于动力气源最高参数； 热力系统可以采用回热过程， 回热高温放热端有膨胀做功过程 或排热过程或者二者都有， 回热低温吸热端有升温过程或热泵过程吸热工质或者二者都有。 施方式 2， 新的喷射抽气器：
附图 1、 附图 5及附图 6屮 ！到的多级循环喷射抽气器不同， 如附图 7所示为直通管 旋流式唢射抽气器， 喷射与扩压过程放弃传统的喉管缩放结构而采用直通管 （不局限等直径 i 可以渐扩或渐缩） 旋流喷射的方式， 其中 A表示单级喷射结构简图， B表示多孔喷射 示意图， C 与 D表示斜向旋流喷射示意图， 木尾有导流装置， E为直通管旋流式多级循环喷 射抽气器。
附图 8A 是分体式多级串联循环喷射抽气系统采用了再热方式与气轮机组合； 附图 8B 所示的喷射抽气器分体布置的是旋流喷射特点， 可以在最低温度的高速旋流状态与外界热交 换， 其旋流器结构有利于采用高效换热结构与材料， 如波纹状或肋片结构及高强度铝合金外 壳等， 整体过程有利于实现与等温膨胀接近等效的再热热力过程。 附图 9是串联并联及循环 结合的复合喷射抽气器结构示意图， 可用于高真空抽气并压缩。
附图 10是循环管路内置的单喷嘴多循环喷射抽气器原理图， 动力气源从喷嘴 231 进入 ^射器， 循环管路 232通过勺管接收高速气流产生冲压而另一端受射流抽吸实现循环流动， Rj样其它 ^个循环管路也通过一端在喷射器内部的勺管接收高速冲压而另一端受射流抽吸实 现循环流动（虚线箭头表示气流流动过程）， 最终通过抽气管 233从外抽入低压气体工质混合 并减速扩 后从出口管 234排出， 图中为简明只显示了单侧循环， 也可以采用上下双侧循环， 或者在同一圆周上布冒：多个勺管循环的方式， 喷嘴喷气方式可以采用单喷嘴或多喷嘴喷射， 可以是直线喷射也可以采用切向旋流喷射或采用介于二者之间的斜向旋流喷射， 采用旋流方 式时出门管 234应增加导流扩压措施， 其旋流与导流如附图 2中的 Β与 C所示的结构或采用 蜗壳结构， 这样有利于通过外壳换热也有利于减小与内循环管路的阻力， 这种循环管路内賈 苹喷嘴结构减少了反复喷射的喷嘴损失， 因结构简单可通过增加长度、 直径或循环次数减小 射流或旋流流速损失， 有利于用于直接从外壳吸热的实现等温膨胀过程。 附图 11是循环管路 内置与外青结合的单级多循环复合喷射抽气器原理图，附图 12是循环管路外置的单级多循环 喷射抽气器原理图， 方便任一级循环与外部连接， 增加应用灵活性实用性。 附图 13中 Α与 Β 分别表示每个循环管路通过一端在喷射器内部的勺管接收部分高速气流产生冲压或者通过一 端在喷射器内部采用切向开口接收部分高速气流产生冲压而另一端受射流抽吸实现循环流 动。 附图 14是单级多循环喷射器的侧向抽气方式示意图， 表示单级多循环喷射抽气器也可以 在木端增加弯管抽气与增加导流器 315直接向后喷射气流， 这样可以与传统喷射抽气器侧向 抽气使用方式一样。
归纳喷射抽气系统各种实施方式可分为以下几种， 喷射抽气系统采用了单级喷射抽气， 或者采用了^级或多级循环喷射抽气， 或者从动力气源供气方式又可以分为采用了循环与串 联或并联结合或者循环与串联及并联结合的复合喷射抽气 （如附图 9) ; 喷射抽气系统的同级 喷嘴采用了单喷嘴分 ^或多喷嘴分布， 喷射方式采用了直流 （沿直线喷射， 普通喷射器的普 遍喷射方式） 或旋流或者介于二者之间的斜向旋流式， 射流与扩压管采用了直通管结构或者 多级循环喷射器的射流与扩 管采用喉管式缩放结构， 循环方式可分为采用了单级喷射单循 环 （如附图 1 中循环喷射器只采用末级喷射抽气时） 或多级喷射多循环 （如附图 1的复合喷 射器） 或单级喷射多循环 （如附图 10或 1 1 )， 结构方式采用了循环管路内置 （如附图 10 ) 或 外置 （如传统喷射方式或附图 14 ) 或内外结合 資 （如附图 11 )。
实施方式 3， 采用压缩与冷却液化方式的自冷热力循环：
附 1¾ 1 5 足唢射旋流换热式热 ¾ΐ的两种喷射旋流换热方式， 工质通过膨胀做功从低温环 境或低温工质吸取热量， 其特征是： 换热单元采用旋流器结构， 吸热工质通过喷嘴喷射切向 或斜向进入旋流器， 喷射过程与附图 2所示喷射旋流类似， 高速喷射降温后通过旋流器壁与 外部工质或环境吸热， 然后进入排气管排出， 在排气管内采用直通方式或采用增加回收旋流 动力的导流器方式。其中 Α排气管路内置可以减小体积， B排气管路可大直径设计减小阻力， 换热过程可以釆用单个换热单元构成的换热器或采用两个或多个换热单元组成换热器, 可以 ΐ并联结合。 低温工质或环境空气按照虚线箭头方向流动经过旋流器外围通道与内部工质换 热， 旋流器外围也可以采用换热膜片等方式增大换热面积的方式取代通道， 可以通过风扇直 接 ¾工质或环境空气换热， 也可以通过压缩热气加热或直接的热源加热。
W m 16是一种自冷； it空气能喷气动力循环系统， 压缩机 34】及 342与气轮机 35〗 问轴 工作， 其屮一级压缩机 341 及二级压缩机 342与喷射旋流式换热器 353及单级多循环复合喷 射器 347的表面换热器组成双级压缩式热泵系统。 空气从压缩机 341开始被抽入系统并目.被 压缩进入喷射器表面换热器 347降温后进入二级 缩机 342再次压缩， 然后进入换热器 353 再次降温实现液化。 液化空气经泵 354升压经加热器 346加热气化升温为动力气源进入单级 多循环喷射器 347膨胀做功， 将从抽气管路 348抽取的空气混合升压后从出口管 349排出， - 部分为气轮机 351提供动力满足压缩机工作， 其余经喷管 350产生喷气动力。 单级多循环 喷射器 347外层采用夹层换热结构， 加热压缩机 341提供压缩热空气使喷射器内部形成近 似定温膨胀过程， 同时， 加热器 346也可以由加热压缩机 34】提供压缩热空气。 也可以 ώ其 它热源如通过燃气加热加热器 346或 347则成为燃气动力发动机。
如附图 1 7所示是在附图 16的基础上采用了喷射抽气器 361压缩工质取代二级压缩机， 喷射抽气器 361 的动力气源来自膨胀做功系统最初的动力气源， 也可以来自膨胀做功过程中 的动力气源。 制冷液化动力气源与气轮机并联并且一分为二， 其一通过管路 363为两个喷射 旋流换热式热泵的喷嘴提供动力， 其二通过管路 364进入喷射旋流换热式热泵 365被降温， 然后降温后的工质被喷射抽气器 361杣走二次压缩， 增加了换热器 362为二次压缩后工质降 温， 然后工质进入热泵换热器继续降温实现液化。 与附图 16比， 最大的优势是利用制冷动力 气源取代一级压缩机与利用喷射抽气器取代二级压缩机实现压缩冷却液化工质。
这说明， 增加喷射抽气系统既可以象附图 16那样抽収空气为吸收空气热量的换热器提 供压缩热空气， 也可以抽取工质为压缩冷却或液化过程提供压缩气源， ώ说明自冷式喷射抽 气热力系统可以专门对外提供压缩气体成为一种气泵系统， 而且压缩气体产生的热量可以被 系统回收， 而传统的气泵压缩产生的热量无法被系统回收利用。
如附图 18所示的是一种空气能发动机系统， 加热压缩机 372、 工质压缩机 371、 高压膨 胀机 378、 低压膨胀机 377 以及余热膨胀机 376同轴工作， 按工质流动方向工质压缩机 371 的前后布置了两个喷射旋流式热泵 379， 山低压膨胀机 377提供喷射制冷动力， 热泵过程排 出的气流进入余热膨胀机回收。 卨低压膨胀机之 Μ增加了 ¾热器， 山加热 DI缩机 372通过加 热器 375同吋为动力气源加热器及再热器提供热气流， 从冉热器出来的加热气流尾气进入余 热膨胀机 0收膨胀功，加热压缩机可以确保 T1大于 T4有利于即使寒冷的冬天也能正常工作。 增加阀 374可以通过控制对外排气量调节压缩热 气的 ΠΙ力进而实现对系统工作及输出动力 的调节。 无论轴流式、 离心式还是容积式， 压缩机与膨胀机在工业领域都非常成熟， 或同轴 或独立安装， 容易实现简单可靠的发动机， 但与采用循环喷射抽气系统相比其成本较高。 这 种发动机系统可以采用与前述各实施例一样添加液态工质后加热就可以启动。 另外， 本实施 方式中各例都采用了二级冷却压缩液化方式，实际应用中也可以采用多级冷却压缩优化方案。 再有， ^例都采用液化后泵力升压， 事实上可以采用再冷压缩或等温压缩， 循环过程如附图 4屮 F所示， 液化不足必须的。
在空气能发动机系统或其它自冷式热力系统中， 吸收空气热量的换热器采用压缩热空气 或通风强制换热方式， 压缩热风或强制通风可山压缩机或风机提供， 或者 复合喷射抽气系 统提供。 ^缩热风强制换热可以避免液化气体工质吸热过程换热器表面结霜的难题。事实上， 喷射抽气系统采用空气为工质时，也可以抽取低温工质为压缩冷却或液化过程提供压缩气源， 或者专门生产压缩空气。
实施方式 4， 自冷式燃气发动机：
附图 19所示是采用了自冷式液化过程的喷气发动机 （或燃气轮机）， 燃烧室布置在复合 喷射抽气器 406内部， 空气及有压燃料 （山管路 405提供） 在燃烧室内燃烧吸收燃烧释放的 热能并且在复合喷射器内循环喷射膨胀后成为燃气轮机或喷管的动力气源。 喷射制冷液化系 统采用了二级串连的喷射旋流液化器， 山循环喷射杣气器 404及 403分别提供一级压缩空气 及二级压缩空气， ώ循环喷射抽气器 406为液化系统提供抽气动力完成热泵过程，加热器 402 可吸收燃烧室保温散热热量， 也可以吸收发动机余热。
因为燃气动力产生的热源温度远高于环境温度， 空气液化不必低于环境温度， 因此可以 采用传统的压缩冷却方式， 例如将冷却工质不是引自压缩气源而是通过管路 408直接通入空 气， 喷射旋流换热器 409 也可以换成普通的气 气换热器， 但是这样结果是空气液化系统体 积比较大。 也可以采用传统的水冷方式通过管路 408通入冷却水， 喷射抽气器 406可采用复 合喷射抽气方式通过抽取冷却水容器内蒸汽回收冷却水热量。
热力系统通过燃料燃烧为系统工质提供热源可以采用以下方式之一， （ 1 )燃烧室布.實在 工质升压后进入喷射抽气系统之前，工质进入燃烧室吸收燃料燃烧热成为燃气动力气源； （2 ) 喷射抽气膨胀做功系统分体布置时，如附图 8Α或 8Β所示的分体布置或只有布置燃烧室的级 问分体， 燃烧布置在喷射抽气系统中的两级喷射器之间， 从前级喷射器出来的工质进入燃烧 室燃烧升温成为燃气动力气源后进入下一级喷射器； （3 ) 有压燃料直接喷入喷射抽气系统的 初级或次级或任意级喷射管内或扩压管内 （如附图 19中 406， 包括采用附图 7中 Ε所示喷射 器结构） 或直接喷入循环管内 （如附图 20中 410 ) 与工质燃烧成为燃气动力气源， 使喷射抽 气系统兼备燃烧室功能； （4 ) 采用锅炉方式， 燃料与空气或氧气在燃烧燃烧室内燃烧， 升压 后的工质通过燃烧室内或其烟道中 置的加热器吸热成为动力气源； （5 ) 工质升压后先通过 燃烧室的保温系统吸热或吸收发动机余热或 两种吸热过程都有； （6 )方式（5 )与前四种之 一的组合。
综合以上^实施方式屮&种喷射抽气器使川方式， 热力系统可以采用单级喷射单循环或 •Ti级喷射多循环或多级喷射多循环等各种喷射： W!气系统， 动力气源來自 S初的动力气源也可 以來 ^膨胀做功过程中的动力气源， 用于膨胀做功过程为膨胀机或喷 或热泵提供动力或在 丌式循环中为喷射抽气式鼓风机或引风机或压气设各（将膨胀机或喷管换为喷射抽气器即可） 提供动力气源， 或者用于为热泵过程的压缩冷如或液化过程提供压缩气源 （如附图 19 中的 403及 404 )或抽气动力， 或者用于加热过程扯¾¾气为吸收空气热量的换热器提供压缩热空 气 （如在附图 16中可以采用循环喷射器替代压缩机 341， 在附图 18中采用循环喷射器代替 压缩机 372 )， 或者以上使用方式中两种或多种组合。
实施方式 5， 采用热力升压的自冷式热力循环：
附图 21 是采 j†j了间断工作式热力升压的自冷式热力循环， 利用封闭容器采用加热方式 可使 力显著升高的特点， 山冋热换热器提供热 两组升压容器 508交 f^L补工作为系统提 供相对稳定的压力。 升压容器 508接收系统排热过程或液化系统冷凝器产生的液态工质， ： 者通过单向阀与管路连通， 其 向导通性能可采用机械 Θ动方式或电动控制方式实现， 但这 样的工作方式 能依赖重力流动， 为方便控制可以采用循环泵加单向阀的方式。 增加喷射抽 气式余气动力回收装置 504，喷射抽气结构可以是单级也可以多级复合喷射抽气，增加阀 502、 阀 503、 阀 506及阀 507， 与两个升 Π容器下面的单向阀， 共同组成切换阀组， 通过控制系统 控制切换阀组使升压容器与升压管路及余气动力回收装 H 504之间的 ^通或隔离， 实现两个 升压容器在交替补充液位的过程中热力系统可维持稳定的工作压力， 并在每次补充液位前先 回收余气动力。 在升压容器 508的加热通道上增加气液分离器 509及泵 501， 可实现热力升 压与泵力升压结合的升压方式， 在泵 501 前出口增加单向阀可实现热力升压独立工作以及与 泵组合 T.作的自 ώ切换。 自冷式热力做功系统用于空气能发动机时， 因为温度参数低动力强 度稍弱些但是可以减少泵功消耗提升系统动力输出。 空气能动力的喷气动力系统因喷射温度 低， 可以单个喷管喷射也可采用多喷嘴喷射缩短射稃， 系统简单低成本无论空中还是地面移 动设备都可采用。 热力升压系统与泵 501 组合可以优势互补， 可避免泵在超低温的液氮或液 空环境工作。 另外， 热力升压方式也可以采用单个升压容器阶段式工作， 省掉阀组交替控制 及余气动力回收装置 504， 其简单特点可用于小微型热力发电系统， 可采用蓄电池补充或者 直接采用两个或多个发¾系统同时工作补充间断性。
总结自冷式热力循环中升压方式， 热力系统排热过程产生的液态工质采用热力升压， 所 谓的热力升压是指增加升压容器接收液体工质， 并且在接收液体工质的通道上增加了 ^向阀 或者增加了单向阀与循环泵， 通过加热使升压容器内液体工质升压， 通过控制单个或多个升 压容器实现间断式或互补升压； 或者采用液力泵或容积泵升压； 或者在热力升压容器的加热 通道上增加气液分离器 509， 其液体通道上增加泵 501实现热力与泵力组合升压。
实施方式 6， 自冷式热泵制热或制冷： 如附图 22所示的喷射旋流换热式热泵循环， 循环喷射抽气系统的末级与膨胀机之间增 加了换热器 603制热输出热力，在液化系统出口与喷射抽气器的抽气口之问布覽了换热器 605 制冷输出冷源， 热力系统在完成自冷式热力做功循坏的问时实现了制冷或制热， 不用压缩机 成本低简单可靠。 因此， 自冷式热力系统的热源可以是空气能， 也可以是燃料等， 可以增加 对外输出热力的换热器与膨胀做功系统中的膨胀机 Φ联或并联或取代膨胀机； 可以在在吸热 过程增加换热器输出冷源或在热泵过¾¾加吸热换热器输出冷源， 或 两种输出冷源方式都 采用， 可以通过膨胀机 604发电直接为泵 601提供 lii力 (如阁屮二者之间虚线连接所示）, 这 样就可以通过加热器 602提供热力成为热力制冷制热机组， 不似 nj.以不消耗 力， 还 nj'以热 屯冷联产。 当热力系统采用 供电力独立工作方式时运行屮容 发生不稳定现象， W以 ¾加 蓄 池储能或液化气储能系统提供^动说或稳定动力。 W外， 山于制冷或制热冈热惯性特点一 般允许热泵系统存在波动性， 例如空调经常是间断性工作的， 因此自冷式热泵采用单个热力 升压器的热力升压方式， 甚至可以不用泵压， 可大幅度简化系统具有最大的低成本优势。
书
实施方式 7， 旋流器的改进
喷射旋流的工作方式对气休工质液化及喷射抽气器简化 效率都冇重耍 义， 速旋流因为存在离心压力存在流动损失大的 题， 除采 fij附图 4所示的内 ¾转筒的方式改善 外，这甩提出膨胀做功过程或热泵过程采川喷射旋流丄作方式的设 ^其旋流器壁采 波纹状， 例如采用正弦波状表面波纹， 射流气体主要在波峰很小比例的面枳有流动附力， 波谷 ill然有 涡流因为高速射流的抽吸作用压力很小« ¾^【 状态流动损失很小， 要合现设讣波形及 波长与器壁直径的比例， 喷射旋流设^的流动损失^人幅度卜降。 W外， ώ πΓ以旋流器¾川 筒壁为波纹状并且分布了微孔或缝隙的内筒， -Τ.质唢射到内筒 ;Λ: /Ι·:旋流， 微孔或缝隙分流出 液体工质从内筒外侧收集， 这样 nj减小因为液化在器壁液膜增厚导致的流动损失与气液反¾： 混流导致的气液分离效率下降。
实施方式 8， 高沸点工质热力循环
在沸点较高的水蒸气循环热力系统中， 为尽可能降低排放温度总是使凝汽器内部达到很 高的真空度， 这使得自冷式液化过程气液分离难度增大潜热增加设备体积也增大许多， 为克 服这些问题提出采用两种或多种混合气体工质工作， 热泵系统使混合工质降温液化过程中首 先使高沸点工质液化， 液化后的高沸点工质被升 加热成为动力气源， 低沸点工质参 抽气 循环过程， 最典型的就是水蒸气加氮气或二氧化碳或空气。 另外一种采用高沸点工质循环改 进的方法是采用高沸点工质循环与低沸点工质循环结合的双循环或多循环方式， 例如水蒸气 热力循环的排热过程为氮气热力循环的热源， 高沸点工质热力循环吸收热源做功， 低沸点工 质热力循环吸收高沸点工质热力循环的排热并 置了满足 Π冷式热力做功循环的热泵过程与 回热过程， 可克服采用高沸点工质热力循环适应温度范 了限的不足， 以及克服 τι低于 Τ4 的问题。 本发明为基础创新， 适用范围广泛， 不局限于¾施方式所述范 (1。

Claims

WO 2014/063443 权 利 要 求 书 PCT/CN2013/001277
1、 自冷式热力做功方法， 属于热能动力领域， 热力系统的工质从热源吸热做功， 包括了 工质从低温状态升压吸热后成为动力气源的升温过程、 动力气源进入膨胀做功系统后的膨胀 做功过程， 以及完成膨胀做功的低温气体工质进一步释放热量的排热过程， 热力系统从升温 过程、 膨胀做功过程到排热过程后再到升温过稃后实现热力循环过程， 其特征是： 工质从高 于环境温度的热源吸收了热量， 或从等于或低于环境温度的热源吸收了热量； 热力系统采用 了热泵过程吸收排热过程中低温气体工质释放的部分或全部热量， 膨胀做功过程或者 ώ膨 胀做功过程与升温过程吸收热泵过程释放的部分或全部热量； 热力系统采用了回热过程， 回 热高温端有膨胀做功过 或排热过程或者二 #都有， 热低温端有升温过程或热泵过程吸热 工质或者二者都有。
2、 一种喷射旋流换热式热泵方法， 工质通过膨胀做功从低温环境或低温工质吸取热量， 其特征是： 向低温环境或低温工质吸热的换热单元采用旋流器结构， 吸热工质通过喷嘴喷射 切向或斜向进入旋流器， 高速喷射降温后通过旋流器壁与外部工质或环境吸热， 然后进入排 气管排出， 在排气管内采用直通方式或采用增加回收旋流动力的导流器方式， 换热过程采用 单个换热单元构成的换热器或采用两个或多个换热单元组成换热器。
3、 如权利要求 1所述的自冷式热力做功方法， 其特征是： 热泵过程采用了喷射旋流换热 式热泵或者采用了喷射制冷过程或抽汽制冷过程或压缩冷却过程使气体工质降温或液化， 或 者采用了喷射旋流换热式热泵与后三种使工质降温或液化过程之一组合的方式； 所谓的喷射 制冷过程是指热泵动力系统使 体 : 1 :质 冷凝器之间产 ^ΓΚ力 ， 冷凝器采 ffl了喷射旋流器 分离方式， 喷射旋流器采 了^ ^的½体结构或 ¾川壳体加内靑转筒结构， 冷气体工质通过 喷嘴沿切线方向喷射进入喷射旋流器实现唢射制冷液化并 液分离， 未冷凝气从出 υ排出， 未冷凝气出口通道中采用直通方式或采用增加回收旋流动力的导流器方式； 所谓的抽汽制冷 过程是指热泵动力系统抽取蒸发室内蒸汽使蒸发室维持过冷状态， 过冷液体工质与液化前冷 气体工质通过换热器换热或通过循环泵直接泵入冷凝器混合使冷气体工质降温液化， 冷凝器 内部分液态工质通过节流通道或喷嘴进入蒸发室实现循环液化过程； 所谓的压缩冷却过程是 指气体工质经过压缩升温后被换热器吸热降温或液化的过程。
4、 一种新的喷射抽气方法， 动力气源通过喷嘴喷射抽取低压气源， 其特征是： 喷射抽气 系统采用了单级喷射抽气， 或者采用了 Φ·级或多级循环喷射抽气， 或者采用了循环与串联或 并联结合或者循环与串联及并联结合的 合喷射抽气； 喷射抽气系统的同级喷嘴采用了单喷 嘴分布或多喷嘴分布， 喷射方式采用了直流或旋流或者介于二者之间的斜向旋流式， 射流与 扩压管采用了直通管结构或者多级循环喷射器的射流与扩压管采用喉管式缩放结构。
5、 一种单级多循环喷射抽气方法， 动力气源通过喷嘴喷射抽取低压气源， 其特征是： 喷 射抽气过程采用了单级喷射多循环方式， 循环管路通过一端在喷射器内部的勺管接收部分高 速气流产生冲压或者采用切向开口接收部分高速气流产生冲压而另一端受射流或旋流抽吸实 现循环流动， 喷射方式采用了直流或旋流或者介于二者之间的斜向旋流， 结构方式采用了循 环管路内置或外置或内外结合布置， 喷嘴分布方式采用了单喷嘴分布或多喷嘴分布。
6、 如权利要求 1所述的自冷式热力做功方法，其特征是：热力系统采用了喷射抽气系统， WO 2014/063443 权 利 要 求 书 PCT/CN2013/001277 动力气源来自热力系统最初的动力气源或来自膨胀做功过程中的动力气源， 用于膨胀做功过 程为膨胀机或喷管或热泵提供动力或在开式循环中为喷射抽气式鼓风机或引风机或压缩机提 供动力气源； 或者用于为热泵过程的压缩冷却或液化过程提供压缩气源或抽气动力， 或者用 于加热过程抽取空气为吸收空气热量的换热器提供压缩热空气， 或者以上使用方式中两种或 多种组合。
7、 如权利要求 3或 6所述的自冷式热力做功方法， 其特征是： 在热泵过程中的工质液 化系统前增加了辅助喷射抽气器， 冷气体工质先进入辅助喷射抽气器抽取工质液化系统内气 体工质后再进入工质液化系统。
8、 如权利要求 1所述的自冷式热力做功方法， 其特征是： 工质的膨胀做功过程采用了再 热或等温加热过程， 再热或等温过程布置为以下方式之一， ( 1 ) 在分段膨胀机之间； （2 ) 在 喷射抽气过程的旋流外壳上； （3 ) 在多级喷射抽气过程中的两级之间； （4 ) 在循环喷射抽气 过程的循环通道上； （5 ) 以上任意两种或多种方式组合。
9、 权利要求 6的自冷式热力做功方法， 其特征是： 热力系统通过燃料燃烧提供热源并 采用以下方式之一， （1 ) 燃烧室布置在工质升压后进入喷射抽气系统之前， 工质进入燃烧室 吸收燃料燃烧热升温成为燃气动力气源； （2 ) 燃烧室布置在喷射抽气系统中的 W级喷射器之 间， 从前级喷射器出来的工质进入燃烧室燃烧升温成为燃气动力气源后进入下- 级喷射器；
( 3 )有压燃料直接喷入喷射抽气系统的初级或次级或任意级喷射管内或扩压管内或循环管内 与工质燃烧成为燃气动力气源； （4 ) 燃烧 ¾¾用锅炉方式， 升^后的工质通过燃烧 ¾内或其 烟道中布置的加热器吸热成为动力气源； （ 5 ) 工质升 if;: 先通过燃烧 的保^系统吸热或吸 收发动机余热或者两种吸热过程都有； （6 ) 方式 （5 ) 与^四种方式之一的组合。
10、 如权利要求 1所述的自冷式热力做功方法， 其特征是： 排热过程产生的液态工质采 用热力升压， 所谓的热力升压是指增加升压容器接收液体工质， 并且在接收液体工质的通道 上增加了单向阀或者增加了单向阀与循环泵， 通过加热使升压容器内液体工质升压， 通过控 制单个或多个升压容器实现间断式或互补升压； 或者采用液力泵或容积泵升压； 或者在热力 升压容器的加热通道上增加气液分离器， 其液体通道上增加泵实现热力与泵力组合升压。
1 1、 如权利要求 1所述的自冷式热力做功方法， 用于制热或制冷， 其特征是： 增加对外 输出热力的换热器与膨胀做功系统中的膨胀机串联或并联或取代膨胀机； 在吸热过程增加换 热器输出冷源或在热泵过程增加吸热换热器输出冷源， 或者两种输出冷源方式都采用。
12、 如权利要求 1所述的自冷式热力做功方法，其特征是：热力系统采用独立工作方式， 增加蓄电池储能系统或液化气储能系统提供启动或稳定动力。
13、 如权利要求 1所述的自冷式热力做功方法， 其特征是： 膨胀做功过程或热泵过程采 用喷射旋流方式的设备其旋流器壁采用了波纹状， 或者旋流器采 ffl筒壁为波纹状并且分布了 微孔或缝隙的内筒， 工质喷射到内筒产生旋流， 微孔或缝隙分流出液体工质从内筒外侧收集。
14、 如权利要求 1所述的自冷式热力做功方法， 其特征是： 采用了混合气体工质； 或者 采用了高沸点工质循环与低沸点工质循环结合的双循环或多循环方式， 前者吸收热源做功， 后者以前者的排热为热源， 后者布賈了满 自冷式热力做功循环的热泵过程与回热过程。
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