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WO2011150676A1 - Low-entropy mixed combustion ultra-supercritical thermal power system - Google Patents

Low-entropy mixed combustion ultra-supercritical thermal power system Download PDF

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Publication number
WO2011150676A1
WO2011150676A1 PCT/CN2011/000921 CN2011000921W WO2011150676A1 WO 2011150676 A1 WO2011150676 A1 WO 2011150676A1 CN 2011000921 W CN2011000921 W CN 2011000921W WO 2011150676 A1 WO2011150676 A1 WO 2011150676A1
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Prior art keywords
working
combustion chamber
boiler
entropy
low
Prior art date
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Ceased
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PCT/CN2011/000921
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French (fr)
Chinese (zh)
Inventor
靳北彪
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Individual
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Individual
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Priority claimed from CN2011100343440A external-priority patent/CN102313273A/en
Priority claimed from CN2011101289763A external-priority patent/CN102313274A/en
Application filed by Individual filed Critical Individual
Publication of WO2011150676A1 publication Critical patent/WO2011150676A1/en
Anticipated expiration legal-status Critical
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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
    • F01K3/00—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein
    • F01K3/18—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein having heaters
    • F01K3/24—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein having heaters with heating by separately-fired heaters
    • F01K3/242—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein having heaters with heating by separately-fired heaters delivering steam to a common mains
    • 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
    • F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
    • F01K7/16—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type
    • F01K7/22—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type the turbines having inter-stage steam heating

Definitions

  • the invention relates to the field of thermal energy and power, and in particular to a thermodynamic system.
  • the external combustion thermodynamic system is currently widely used, such as thermal power plants, but the working temperature of the most advanced ultra-supercritical external combustion thermodynamic system is only about 630 degrees, which is caused by external combustion heating. It is necessary to pass through the heat transfer wall of the boiler, so the heat transfer wall of the boiler not only has to withstand the high pressure of the working medium, but also withstands the high temperature above the working temperature. Therefore, under the premise of the existing material technology, the working medium cannot be used. The temperature and pressure continue to increase. Therefore, there is an urgent need to invent a thermodynamic system with a higher working temperature and pressure.
  • a low-entropy co-firing high-supercritical thermodynamic system comprising a boiler, a boiler working chamber, a working mechanism and a combustion chamber, wherein the combustion chamber is provided with a combustion chamber working inlet, a combustion chamber working outlet, an oxidant inlet and a fuel An inlet, an oxidant source is in communication with the oxidant inlet via an oxidant high pressure supply system, the fuel source being in communication with the fuel inlet via a fuel high pressure supply system, the combustion chamber being all disposed within the boiler working chamber or the combustion a chamber portion is disposed in the working fluid chamber of the boiler or the combustion chamber is disposed outside the boiler;
  • the working fluid chamber of the boiler is in communication with the working fluid inlet of the combustion chamber, and the working fluid outlet of the combustion chamber is in communication with the working mechanism.
  • a supercharger is provided at the inlet of the combustion chamber, and the supercharger pressurizes the working fluid in the combustion chamber.
  • the work mechanism is coupled to the generator.
  • the low-entropy co-firing high-supercritical thermodynamic system further includes a condensing cooler, a working fluid outlet of the working mechanism is in communication with a cooled fluid inlet of the condensing cooler, and a cooled fluid outlet of the condensing cooler
  • An inlet of the liquid high pressure return pump is in communication, and an outlet of the liquid high pressure return pump is in communication with the working fluid chamber of the boiler, and the working fluid liquefied by the condensing cooler is returned by the liquid high pressure reflux pump Flow into the working chamber of the boiler.
  • a power unit is disposed at the outlet of the combustion chamber, and the power unit outputs power to the supercharger.
  • the work mechanism outputs power to the supercharger.
  • a non-condensable gas outlet is provided at the outlet of the condensed cooler to be cooled.
  • a residual working fluid outlet is provided at the inlet of the cooled fluid of the condensing cooler and/or at the outlet of the cooled fluid of the condensing cooler.
  • the power unit is disposed coaxially with the supercharger.
  • the working mechanism is disposed coaxially with the supercharger.
  • the working mechanism is set as a power turbine or as a piston type working mechanism.
  • the supercharger is set as an impeller type compressor or a piston type compressor.
  • the power unit is configured as an impeller type power unit or a piston type power unit.
  • the fuel in the fuel source is set to be a hydrocarbon, a carbon oxyhydroxide or a hydrogen gas.
  • the oxidant in the oxidant source is set to liquid oxygen, high pressure gaseous oxygen or aqueous hydrogen peroxide.
  • the fuel in the fuel source is set to a metal fuel, and a working metal compound separator is disposed in the combustion chamber and/or before the work mechanism and/or after the work mechanism.
  • the condensing cooler is set as a water drying tower.
  • a regenerator is arranged at the outlet of the working fluid of the working mechanism.
  • the supercharger is an impeller type compressor
  • the working mechanism is set as a power turbine
  • the power turbine outputs power to the impeller type compressor
  • the impeller type compressor the impeller type compressor
  • the A combustion chamber and a high pressure zone of the power turbine are disposed within the working fluid chamber of the boiler.
  • the combustion chamber inlet is set as an intake port of a ramjet engine
  • the combustion chamber is set as a press engine combustion chamber
  • the combustion chamber working outlet is a ramjet engine diffuser gas outlet.
  • a method for improving the efficiency and environmental protection of the low-energy co-firing high-supercritical thermodynamic system that is, the temperature and pressure of the gas working fluid that starts the work are in accordance with the adiabatic relationship.
  • a low-entropy co-firing high-supercritical thermodynamic system comprising a boiler and a work mechanism, wherein a gas working fluid outlet of the boiler is in communication with a gas working medium inlet of the working mechanism, and the liquid working medium inlet of the boiler is adjusted Flow and pressure, adjusting the flow rate at the gas working fluid outlet of the boiler, adjusting the addition of the boiler
  • the heat of the gas is higher than 30. 5 MPa, and the gas working temperature at the gas working outlet of the boiler is higher than 880K.
  • thermodynamic system A method for improving the efficiency and environmental protection of the low-entropy co-firing high-supercritical thermodynamic system, wherein the temperature and pressure of the gaseous working fluid at the outlet of the gas working fluid of the boiler are in an adiabatic relationship.
  • the principle of the invention is that the high temperature and high pressure working medium generated by the working fluid chamber of the boiler is heated in the combustion chamber by means of internal heating (that is, the combustion reaction is carried out in the working medium from the working chamber of the boiler) to absorb heat from the working medium.
  • the pressurized working fluid enters the working mechanism to perform external work.
  • the low-energy co-firing high-supercritical thermodynamic system disclosed by the invention not only can improve the efficiency of the thermodynamic system, but also can effectively utilize rough fuels (such as coal, biomass, etc.) and fine fuels (such as gasoline, diesel, hydrogen, Metal fuels, etc., make fuel resources more fully utilized.
  • rough fuels such as coal, biomass, etc.
  • fine fuels such as gasoline, diesel, hydrogen, Metal fuels, etc.
  • the low-energy co-firing high-supercritical thermodynamic system disclosed in the present invention refers to a metal that directly undergoes a violent chemical reaction with oxygen or a metal that reacts with water to generate hydrogen (hydrogen reaction with oxygen), such as metal aluminum. Or metal magnesium, etc.
  • the main purpose of the use of the metal fuel is to avoid the generation of non-condensable carbon dioxide after combustion; the so-called working metal compound separator refers to a device for separating metal compounds produced by burning a metal fuel.
  • the intake port of the so-called ramjet engine of the present invention refers to the air inlet of the intake port of the ramjet engine
  • the so-called ramjet engine combustion chamber refers to the space where the gas which is pressurized by the blasting engine intake passage is pressurized by the diffusing zone.
  • the so-called ramjet diffuser gas outlet refers to the gas high pressure zone before entering the nozzle in the ramjet engine. The purpose of this structure is to use the ramjet engine inlet to accelerate the working fluid and then pressurize the diffuser zone to increase the working capacity of the working fluid after the temperature is increased by the combustion chamber.
  • the temperature of the vaporization chamber wall is much higher than the temperature of the internal working medium because it is the external combustion heating method, which results in the above
  • the pressure and temperature of the working fluid are severely limited.
  • the low-energy co-firing high-supercritical thermal power system disclosed by the present invention as a technical means for further improving the working temperature or working temperature and pressure, a method of mixing and heating in the working phase is adopted, that is, a burning flame Directly mixed with the working fluid, the heat generated by this combustion can directly transfer heat to the working medium without passing through the solid interface, so that the temperature of the working medium can be far
  • the temperature of the container or the pipe wall carrying the working medium is higher than the temperature of the working medium, and the low-energy co-firing high-supercritical thermal power system disclosed by the invention can greatly improve the temperature of the working fluid based on the existing material technology. Pressure, ultimately improving the efficiency of the thermodynamic system.
  • the flow rate and pressure of the liquid working fluid inlet of the boiler are adjusted, the flow rate at the gas working fluid outlet of the boiler is adjusted, and the heating intensity of the boiler is adjusted to make the gas at the gas working outlet of the boiler 5MPa, 38MPa, 37. 5MPa, 38MPa, 38. 5MPa, 38MPa, 37MPa, 36. 5MPa, 37MPa, 37. 5MPa, 38MPa, 38MPa, 37. 5MPa, 38MPa, 38. 5MPa 39MPa, 39. 5MPa or more than 40MPa.
  • adjusting the flow rate and pressure of the liquid working fluid inlet of the boiler, adjusting the flow rate at the gas working fluid outlet of the boiler, and adjusting the heating intensity of the boiler to make the gas at the gas working outlet of the boiler Working temperature is higher than 885 ⁇ , 890 ⁇ , 895 ⁇ , 900 ⁇ , 905 ⁇ , 910 ⁇ , 915 ⁇ , 920 ⁇ , 925 ⁇ , 930 ⁇ , 935 ⁇ , 940 ⁇ , 945 ⁇ , 950 ⁇ , 955 ⁇ , 960 ⁇ , 965 ⁇ , 970 ⁇ , 975 ⁇ , 980 ⁇ , 985 ⁇ , 990 ⁇ , 995 ⁇ Or higher than 1000 ⁇ .
  • the combustion chamber, the combustion chamber and the chamber in order to increase the pressure-receiving capacity from the combustion chamber to the high-pressure region of the working mechanism, the combustion chamber, the combustion chamber and the chamber may be connected
  • the communication channel of the work mechanism and/or the heat insulation lining is disposed in the working mechanism.
  • the combustion chamber, the communication passage connecting the combustion chamber and the working mechanism, and/or the working mechanism may be Properly cooled to lower the temperature of their walls and increase their pressure bearing capacity.
  • the so-called environmental protection is an indicator for measuring the pollution emission of the thermal power system, and the environmentally-friendly high-heat power system emits less pollution, and the environmentally-friendly low-heat power system emits more pollution.
  • the so-called working medium in the low entropy co-firing high supercritical thermal power system disclosed by the invention may be water or other medium, and the working medium entering the working mechanism may be in a wet state, a superheat state, a critical state, a supercritical state. , ultra-supercritical state or higher pressure temperature state.
  • the so-called high supercriticality of the present invention includes not only the working medium in a superheated state, a critical state, a supercritical state, and an ultra-supercritical state, but also a working temperature at a higher temperature and pressure state.
  • FIG. 19 is a relationship diagram of temperature enthalpy and pressure enthalpy of the gas working medium, and the curve indicated by 0-AH is a gas-based adiabatic relationship curve of 0 points passing through state parameters of 298 ⁇ and 0.1 MPa; Gas The actual state point of the working fluid, the curve shown by EBD is the adiabatic relationship curve through point B, the pressures of point A and point B are the same; the curve shown by F-G is through 2800K and 10MPa (that is, the current internal combustion engine is about to start work) The working point of the gas working fluid is adiabatic.
  • P is the pressure of the gaseous working fluid
  • ⁇ is the temperature of the gaseous working fluid
  • the so-called adiabatic relationship includes the following three cases: 1.
  • the state parameter of the gas working medium ie, the temperature and pressure of the working medium
  • the state parameter of the gaseous working medium is on the adiabatic relationship curve of the working medium, that is, the state parameter of the gaseous working medium.
  • the point is on the curve shown by 0-AH in Fig. 19; 2.
  • the state parameter of the gas working fluid ie the temperature and pressure of the working medium
  • the state parameter of the gas working fluid (ie, the temperature and pressure of the working fluid) is on the right side of the adiabatic relationship curve of the working fluid, that is, the state parameter of the gas working fluid.
  • the point is on the right side of the curve shown by 0-AH in Fig.
  • the temperature of the gas working fluid is not higher than the temperature calculated from the adiabatic relationship of the gas working fluid plus 1000K sum, 950K sum, and 900K And, add 850K, add 800K, add 750K, add 700K and add 650K, add 600K and add 550K, add 500K and add 450K and add 400K And, add 350K, add 300K and add 250K , plus 200K sum, force U 190K sum, force U 180K sum, force ⁇ 170K sum, plus 160K sum, force ⁇ 150K sum, force!] 140K sum, force ⁇ 130K sum, force ⁇ 120K, and force Q 110K sum, plus 100K sum, add 90K sum, add 80K sum, add 70K sum, add 60K sum, add 50K sum, add 40K sum, add 30K and or Not higher than the sum of 20K, that is, as shown in Fig.
  • the actual state point of the gas working medium is point B
  • point A is the point on the adiabatic relationship curve of the same pressure as point B, points A and B
  • the temperature difference between the two should be less than 1000 ⁇ , 900 ⁇ , 850 ⁇ , 800 ⁇ , 750 ⁇ , 700 ⁇ , 650 ⁇ , 600 ⁇ , 550 ⁇ , 500 ⁇ , 450 ⁇ , 400 ⁇ , 350 ⁇ , 300 ⁇ , 250 ⁇ , 200 ⁇ , 190 ⁇ , 180 ⁇ , 170 ⁇ , 160 ⁇ , 150 ⁇ , 140 ⁇ , 130 ⁇ 120 ⁇ , 1 10 ⁇ , 100 ⁇ , 90 ⁇ , 80 ⁇ , 70 ⁇ , 60 ⁇ , 50 ⁇ , 40 ⁇ , 30 ⁇ or less than 20.
  • the so-called adiabatic relationship may be any one of the above three cases, that is, the state parameter of the gas working medium to be started to work (ie, the temperature and pressure of the gas working medium) is as shown in FIG.
  • the adiabatic process curve shown through the defect is in the left region of the E-BD.
  • gas working fluid that is about to start work refers to entering the working mechanism. Gas working fluid.
  • an engine system i.e., a thermodynamic system
  • the state parameters of the gaseous working medium i.e., the temperature and pressure of the gaseous working medium
  • adjusting the external combustion heating intensity of the boiler and the flow rate of the external output working fluid of the boiler to adjust the state (ie, temperature and pressure) of the gaseous working medium in the working fluid chamber of the boiler, and adjusting the combustion chamber
  • the internal combustion heating intensity causes the temperature and pressure of the gaseous working fluid to be started to work in an adiabatic relationship.
  • the combustion chamber in the low-energy co-firing high-supercritical thermal power system disclosed in the present invention, in the structure in which the combustion chamber is entirely disposed in the working fluid chamber of the boiler, not only the heat loss of the combustion chamber can be reduced, but also The outside of the combustion chamber is subjected to external pressure from the working fluid in the working chamber of the boiler, so that the pressure bearing capacity of the combustion chamber can be reduced; in particular, when the working fluid inlet is installed at the combustion chamber When the pressure is applied, the pressure in the combustion chamber is greatly increased. In this case, if the combustion chamber is disposed in the working fluid chamber of the boiler, the structural strength of the combustion chamber is greatly reduced. The cost of the combustion chamber is reduced.
  • the work mechanism is set as a power turbine and power is output to the supercharger using the power turbine, if the supercharger, the combustion chamber, and the power turbine are The high pressure zone is disposed in the working fluid chamber of the boiler, which reduces the manufacturing cost of the system.
  • the so-called combustion chamber of the present invention refers to a container in which combustion (violent exothermic chemical reaction) can occur in the interior;
  • the so-called boiler working chamber refers to the working medium produced by the storage boiler after being heated, and the working medium at this time may be steam. , superheated steam, critical state working fluid, supercritical working fluid, ultra-supercritical working fluid or higher temperature pressure working medium;
  • the so-called working mechanism means that all energy can be converted into high-temperature and high-pressure working medium
  • Mechanical equipment that outputs outwards such as a conventional reciprocating cylinder piston mechanism, a power turbine, a nozzle, etc.
  • a supercharger is a device that can pressurize a working medium, and can be an impeller compressor.
  • the so-called condensing cooler is a device that can cool and condense the working medium. It can be a radiator, a heat exchanger, or a water drying tower. Refers to the gas that does not condense in the condensing cooler; the so-called residual working fluid refers to the excess working fluid produced by the combustion chemical reaction; the so-called connectivity means direct communication, Indirectly connected or controlled by a pump, a control valve, etc.; a so-called power unit means a power provided for powering the supercharger that can utilize the working fluid in the low-energy co-firing high-supercritical thermodynamic system to generate power Institutions, such as turbines or pistons Handle linkage mechanism, etc.
  • components, units or systems such as valves, pumps and corresponding control devices are provided at appropriate locations in accordance with known techniques.
  • the low-entropy co-firing high-supercritical thermodynamic system disclosed by the present invention not only has high efficiency, but also can fully utilize fuel resources.
  • Figure 1 is a schematic view of Embodiment 1 of the present invention.
  • Figure 2 is a schematic view of Embodiment 2 of the present invention.
  • Figure 3 is a schematic view of Embodiment 3 of the present invention.
  • Figure 4 is a schematic view of Embodiment 4 of the present invention.
  • Figure 5 is a schematic view of Embodiment 5 of the present invention.
  • Figure 6 is a schematic view of Embodiment 6 of the present invention.
  • Figure 7 is a schematic view of Embodiment 7 of the present invention.
  • Figure 8 is a schematic view of Embodiment 8 of the present invention.
  • Figure 9 is a schematic view of Embodiment 9 of the present invention.
  • Figure 10 is a schematic view of Embodiment 10 of the present invention.
  • Figure 11 is a schematic view of Embodiment 11 of the present invention.
  • Figure 12 is a schematic view of Embodiment 12 of the present invention.
  • Figure 13 is a schematic view of Embodiment 13 of the present invention.
  • Figure 14 is a schematic view of Embodiment 14 of the present invention.
  • Figure 15 is a schematic view of Embodiment 15 of the present invention.
  • Figure 16 is a schematic view of Embodiment 16 of the present invention.
  • Figure 17 is a schematic view showing Embodiment 17 of the present invention.
  • Figure 18 is a schematic view of Embodiment 18 of the present invention.
  • Figure 19 is a graph showing the relationship between the temperature T of the gas working fluid and the pressure P;
  • Figure 20 is a schematic view of Embodiment 19 of the present invention.
  • the low-energy co-firing high-supercritical thermal power system shown in FIG. 1 includes a boiler 1, a boiler working chamber 2, a working mechanism 3, and a combustion chamber 4, and the combustion chamber 4 is provided with a combustion chamber working inlet 401, A combustion chamber working outlet 402, an oxidant inlet 403 and a fuel inlet 404, the oxidant source 5 is in communication with the oxidant inlet 403 via an oxidant high pressure supply system 501, and the fuel source 6 is in communication with the fuel inlet 404 via a high pressure fuel supply system 601.
  • the combustion chambers 4 are all disposed in the working fluid chamber 2 of the boiler, the working fluid chamber 2 of the boiler is in communication with the working fluid inlet 401 of the combustion chamber, the working fluid outlet 402 of the combustion chamber and the working mechanism 3 connected.
  • the low-entropy co-firing high-supercritical thermodynamic system further includes a condensing cooler 10, and a working fluid outlet of the working mechanism 3 is in communication with a cooled fluid inlet of the condensing cooler 10, and the condensing cooler 10 is The cooling fluid outlet is in communication with an inlet of the liquid high pressure return pump 11, the outlet of the liquid high pressure return pump 11 is in communication with the boiler working chamber 2, and the condensing cooler is operated by the liquid high pressure return pump 1 1 10
  • the liquefied working fluid is returned to the working fluid chamber 2 of the boiler, and the temperature and pressure of the working fluid which is about to start work are in accordance with the adiabatic relationship.
  • the fuel in the fuel source 6 is a hydrocarbon, a carbon oxyhydroxide or a hydrogen gas.
  • the oxidizing agent in the oxidant source 5 is set to be liquid oxygen, high pressure gaseous oxygen or an aqueous hydrogen peroxide solution.
  • the low-entropy co-firing high-supercritical thermodynamic system shown in FIG. 2 differs from Embodiment 1 in that:
  • the combustion chamber 4 is partially disposed within the working fluid chamber 2 of the boiler.
  • the purpose of this setting can not only reduce The heat loss of the combustion chamber, and the external pressure of the working fluid in the working chamber of the boiler is externally and inwardly pressurized, so that the pressure bearing capacity of the combustion chamber can be reduced.
  • the low-entropy co-firing high-supercritical thermodynamic system shown in Fig. 3 differs from the first embodiment in that the combustion chamber 4 is disposed outside the boiler 1.
  • the low entropy co-firing high supercritical thermal power system shown in FIG. 4 is different from the third embodiment in that: a supercharger 7 is disposed at the combustion chamber inlet 401, and the supercharger 7 is The working fluid in the combustion chamber 4 is pressurized, and a power unit 8 is disposed at the combustion chamber outlet 402.
  • the power unit 8 outputs power to the pressure device 7, and the power unit 8 and the supercharging unit
  • the device 7 is coaxially disposed, and a connecting shaft of the power unit 8 and the ram 7 is disposed in the combustion chamber 4.
  • FIG. 5 a low-entropy co-firing high-supercritical thermodynamic system as shown in FIG. 5, which differs from Embodiment 4 in that: the power unit 8 is coaxially disposed with the supercharger 7, and the power unit 8 is The connecting shaft of the supercharger 7 is provided outside the combustion chamber 4, and the purpose of this arrangement is to reduce the heat load requirement for the connecting shaft and to reduce the manufacturing cost.
  • a low-entropy co-firing high-supercritical thermodynamic system as shown in FIG. 6 differs from the third embodiment in that: a supercharger 7 is provided at the combustion chamber inlet 401, and the supercharger 7 is The working fluid in the combustion chamber 4 is pressurized, the working mechanism 3 outputs power to the supercharger 7, and the working mechanism 3 is disposed coaxially with the supercharger 7.
  • the low entropy co-firing high supercritical thermal power system shown in FIG. 7 is different from the embodiment 5 in that the working mechanism is connected to the generator 9 and is disposed at the outlet of the condensed cooler 10 to be cooled.
  • the gas outlet port 12 is not condensed, and the work mechanism is set as the power turbine 301.
  • the low entropy co-firing high supercritical thermal power system shown in FIG. 8 differs from the first embodiment in that: the working mechanism is set as a piston type working mechanism 302, and the cooled fluid in the condensing cooler 10 Enter A residual working fluid outlet 13 is provided at the mouth and at the outlet of the chilled fluid of the condensing cooler 10. In a specific implementation, a residual working fluid outlet 13 may also be provided at the inlet of the cooled fluid of the condensing cooler 10 or at the outlet of the cooled fluid of the condensing cooler 10.
  • the low entropy co-firing high supercritical thermal power system shown in FIG. 9 is different from the first embodiment in that: the low entropy co-firing high supercritical thermal power system further includes a supercharger and a power unit, and the supercharger
  • the impeller type compressor 701 is used, and the power unit is an impeller type power unit 801.
  • the low entropy co-firing high supercritical thermal power system shown in FIG. 10 differs from the embodiment 6 in that: the low entropy co-firing high supercritical thermal power system further includes a supercharger and a power unit 8, the supercharging The compressor is set as a piston compressor 702, and the power unit 8 is a piston type power unit.
  • the low-entropy co-firing high-supercritical thermodynamic system shown in Fig. 11 differs from the third embodiment in that an insulating lining 40 is provided inside the wall of the combustion chamber 4.
  • the low entropy co-firing high supercritical thermal power system shown in Fig. 12 differs from the third embodiment in that a heat dissipating structure 110 is provided outside the wall of the combustion chamber 4.
  • the low entropy co-firing high supercritical thermal power system shown in FIG. 13 differs from the first embodiment in that: the fuel in the fuel source 6 is set as a metal fuel, in the combustion chamber 4 and/or in the The working metal compound separator 405 is disposed before the working mechanism 3 and/or after the working mechanism 3.
  • the low entropy co-firing high supercritical thermal power system shown in Fig. 14 differs from the third embodiment in that the condensing cooler 10 is set as the water drying tower 100.
  • the low-entropy co-firing high-supercritical thermodynamic system shown in Fig. 15 differs from the third embodiment in that a regenerator 200 is provided at the working medium outlet of the working mechanism 3.
  • Example 16 The low entropy co-firing high supercritical thermal power system shown in FIG. 16 differs from the third embodiment in that: the combustion chamber working inlet is set as the intake port 4001 of the ramjet, and the combustion chamber 4 is set to be stamped. In the engine combustion chamber 400, the combustion chamber working fluid outlet is set as a ramjet diffuser gas outlet 4002. In this way, the gas working medium can be compressed by the diffusing zone of the ramjet engine, and the function of the gas working fluid can be improved.
  • the low entropy co-firing high supercritical thermal power system shown in FIG. 17 is different from the third embodiment in that: the low entropy co-firing high supercritical thermal power system further includes a supercharger, and the working mechanism is set as a power Turbine 301, the squeezing device is set as an impeller compressor 701, the power turbine 301 is disposed in the combustion chamber working outlet 402, and the power turbine 301 is opposite to the impeller compressor The 701 outputs power while outputting power externally.
  • the low entropy co-firing high supercritical thermal power system shown in FIG. 18 differs from the fourth embodiment in that: the supercharger is an impeller type compressor 701, and the working mechanism 3 is set as a power turbine. 301, the power turbine 301 outputs power to the impeller compressor 701, and the high pressure zone of the impeller compressor 701, the combustion chamber 4, and the power turbine 301 is disposed in the boiler Within the mass chamber 2.
  • the low-energy co-firing high-supercritical thermal power system shown in FIG. 20 includes a boiler 1 and a work mechanism 3, and the gas working fluid outlet of the boiler 1 communicates with the gas working medium inlet of the working mechanism 3, and the adjustment center
  • the flow rate and pressure of the liquid working fluid inlet of the boiler 1 are adjusted, the flow rate at the gas working fluid outlet of the boiler 1 is adjusted, and the heating intensity of the boiler 1 is adjusted to make the gas working fluid at the gas working outlet of the boiler 1 5MPa, 36MPa, 37MPa, 37MPa, 36MPa, 36MPa, 37MPa, 36MPa, 37MPa, 36MPa, 36MPa, 37MPa, 37MPa, 36MPa, 37MPa, 37MPa, 37MPa, 37MPa, 37MPa, 37MPa, 37. 5MPa, 38MPa, 3MPa, 32MPa, 32. 5MPa, 32MPa, 32.

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

Abstract

Disclosed is a low-entropy mixed combustion ultra-supercritical thermal power system, which includes a boiler (1), a boiler medium chamber (2), an exergonic mechanism (3) and a combustion chamber (4). The combustion chamber (4) is provided with a medium inlet (401), a medium outlet (402), an oxidizing agent inlet (403), and a fuel inlet (404). The oxidizing agent source (5) is communicated with the oxidizing agent inlet (403) via a high-pressure oxidizing agent supply system (501), and the fuel source (6) is communicated with the fuel inlet (404) via a high-pressure fuel supply system (601). The combustion chamber (4) is wholly, or partly, arranged in the boiler medium chamber (2), or is arranged outside of the boiler medium chamber (2). The boiler medium chamber (2) is communicated with the combustion chamber medium inlet (401), and the combustion chamber medium outlet (402) is communicated with the exergonic mechanism (3).

Description

说 明 书  Description

低熵混燃高超临界热动力系统  Low entropy co-firing high supercritical thermodynamic system

技术领域 Technical field

本发明涉及热能与动力领域， 尤其是一种热动力系统。  The invention relates to the field of thermal energy and power, and in particular to a thermodynamic system.

技术背景 technical background

外燃热动力系统目前应用十分广泛， 如热电厂等， 但是目前最先进超超临 界的外燃热动力系统的工质温度也仅有 630度左右，其原因是外燃加热方式所 致， 因为热量要穿过锅炉的传热壁， 所以锅炉传热壁不仅要承受工质的高压作 用， 而且还要承受高于工质温度的高温作用， 所以在现有材料技术的前提下， 无法使工质的温度和压力继续提高。 因此， 急需发明一种具有更高工质温度和 压力的热动力系统。  The external combustion thermodynamic system is currently widely used, such as thermal power plants, but the working temperature of the most advanced ultra-supercritical external combustion thermodynamic system is only about 630 degrees, which is caused by external combustion heating. It is necessary to pass through the heat transfer wall of the boiler, so the heat transfer wall of the boiler not only has to withstand the high pressure of the working medium, but also withstands the high temperature above the working temperature. Therefore, under the premise of the existing material technology, the working medium cannot be used. The temperature and pressure continue to increase. Therefore, there is an urgent need to invent a thermodynamic system with a higher working temperature and pressure.

发明内容 Summary of the invention

为了解决上述问题， 本发明提出的技术方案如下：  In order to solve the above problems, the technical solution proposed by the present invention is as follows:

一种低熵混燃高超临界热动力系统， 包括锅炉、 锅炉工质腔、 作功机构和 燃烧室， 所述燃烧室上设有燃烧室工质入口、 燃烧室工质出口、 氧化剂入口和 燃料入口， 氧化剂源经氧化剂高压供送系统与所述氧化剂入口连通， 燃料源经 燃料高压供送系统与所述燃料入口连通，所述燃烧室全部设置在所述锅炉工质 腔内或所述燃烧室部分设置在所述锅炉工质腔内或所述燃烧室设置在所述锅 炉外；  A low-entropy co-firing high-supercritical thermodynamic system, comprising a boiler, a boiler working chamber, a working mechanism and a combustion chamber, wherein the combustion chamber is provided with a combustion chamber working inlet, a combustion chamber working outlet, an oxidant inlet and a fuel An inlet, an oxidant source is in communication with the oxidant inlet via an oxidant high pressure supply system, the fuel source being in communication with the fuel inlet via a fuel high pressure supply system, the combustion chamber being all disposed within the boiler working chamber or the combustion a chamber portion is disposed in the working fluid chamber of the boiler or the combustion chamber is disposed outside the boiler;

所述锅炉工质腔与所述燃烧室工质入口连通，所述燃烧室工质出口与所述 作功机构连通。  The working fluid chamber of the boiler is in communication with the working fluid inlet of the combustion chamber, and the working fluid outlet of the combustion chamber is in communication with the working mechanism.

在所述燃烧室工质入口处设增压器，所述增压器对所述燃烧室内的工质增 压。  A supercharger is provided at the inlet of the combustion chamber, and the supercharger pressurizes the working fluid in the combustion chamber.

所述作功机构与发电机连接。  The work mechanism is coupled to the generator.

所述低熵混燃高超临界热动力系统还包括冷凝冷却器，所述作功机构的工 质出口与所述冷凝冷却器的被冷却流体入口连通，所述冷凝冷却器的被冷却流 体出口与液体高压回流泵的入口连通，所述液体高压回流泵的出口与所述锅炉 工质腔连通，在所述液体高压回流泵的作用下被所述冷凝冷却器液化的工质回 流到所述锅炉工质腔内。 The low-entropy co-firing high-supercritical thermodynamic system further includes a condensing cooler, a working fluid outlet of the working mechanism is in communication with a cooled fluid inlet of the condensing cooler, and a cooled fluid outlet of the condensing cooler An inlet of the liquid high pressure return pump is in communication, and an outlet of the liquid high pressure return pump is in communication with the working fluid chamber of the boiler, and the working fluid liquefied by the condensing cooler is returned by the liquid high pressure reflux pump Flow into the working chamber of the boiler.

在所述燃烧室工质出口处设动力单元，所述动力单元对所述增压器输出动 力。  A power unit is disposed at the outlet of the combustion chamber, and the power unit outputs power to the supercharger.

所述作功机构对所述增压器输出动力。  The work mechanism outputs power to the supercharger.

在所述冷凝冷却器的被冷却流体出口处设不凝气体导出口。  A non-condensable gas outlet is provided at the outlet of the condensed cooler to be cooled.

在所述冷凝冷却器的被冷却流体入口处和 /或在所述冷凝冷却器的被冷却 流体出口处设余量工质导出口。  A residual working fluid outlet is provided at the inlet of the cooled fluid of the condensing cooler and/or at the outlet of the cooled fluid of the condensing cooler.

所述动力单元与所述增压器同轴设置。  The power unit is disposed coaxially with the supercharger.

所述作功机构与所述增压器同轴设置。  The working mechanism is disposed coaxially with the supercharger.

所述作功机构设为动力透平或设为活塞式作功机构。  The working mechanism is set as a power turbine or as a piston type working mechanism.

所述增压器设为叶轮式压縮机或活塞式压縮机。  The supercharger is set as an impeller type compressor or a piston type compressor.

所述动力单元设为叶轮式动力单元或活塞式动力单元。  The power unit is configured as an impeller type power unit or a piston type power unit.

所述燃料源内的燃料设为碳氢化合物、 碳氢氧化合物或设为氢气。  The fuel in the fuel source is set to be a hydrocarbon, a carbon oxyhydroxide or a hydrogen gas.

所述氧化剂源内的氧化剂设为液氧、 高压气态氧或过氧化氢水溶液。 所述燃料源内的燃料设为金属燃料， 在所述燃烧室内和 /或在所述作功机 构前和 /或在所述作功机构后设工质金属化合物分离器。  The oxidant in the oxidant source is set to liquid oxygen, high pressure gaseous oxygen or aqueous hydrogen peroxide. The fuel in the fuel source is set to a metal fuel, and a working metal compound separator is disposed in the combustion chamber and/or before the work mechanism and/or after the work mechanism.

所述冷凝冷却器设为晾水塔。  The condensing cooler is set as a water drying tower.

在所述作功机构的工质出口处设回热器。  A regenerator is arranged at the outlet of the working fluid of the working mechanism.

所述增压器设为叶轮式压縮机， 所述作功机构设为动力透平， 所述动力透 平对所述叶轮式压縮机输出动力， 所述叶轮式压縮机、所述燃烧室和所述动力 透平的高压区设在所述锅炉工质腔内。  The supercharger is an impeller type compressor, the working mechanism is set as a power turbine, the power turbine outputs power to the impeller type compressor, the impeller type compressor, the A combustion chamber and a high pressure zone of the power turbine are disposed within the working fluid chamber of the boiler.

所述燃烧室工质入口设为冲压发动机的进气口，所述燃烧室设为冲压发动 机燃烧室， 所述燃烧室工质出口设为冲压发动机扩压区气体出口。  The combustion chamber inlet is set as an intake port of a ramjet engine, the combustion chamber is set as a press engine combustion chamber, and the combustion chamber working outlet is a ramjet engine diffuser gas outlet.

一种提高所述低熵混燃高超临界热动力系统效率和环保性的方法，即将开 始作功的气体工质的温度和压力符合类绝热关系。  A method for improving the efficiency and environmental protection of the low-energy co-firing high-supercritical thermodynamic system, that is, the temperature and pressure of the gas working fluid that starts the work are in accordance with the adiabatic relationship.

一种低熵混燃高超临界热动力系统， 包括锅炉和作功机构， 所述锅炉的气 体工质出口与所述作功机构的气体工质入口连通，调整所述锅炉的液体工质入 口的流量和压力， 调整所述锅炉的气体工质出口处的流量， 调整所述锅炉的加 热强度使所述锅炉的气体工质出口处的气体工质压力大于 30. 5MPa， 使所述锅 炉的气体工质出口处的气体工质温度高于 880K。 A low-entropy co-firing high-supercritical thermodynamic system, comprising a boiler and a work mechanism, wherein a gas working fluid outlet of the boiler is in communication with a gas working medium inlet of the working mechanism, and the liquid working medium inlet of the boiler is adjusted Flow and pressure, adjusting the flow rate at the gas working fluid outlet of the boiler, adjusting the addition of the boiler The heat of the gas is higher than 30. 5 MPa, and the gas working temperature at the gas working outlet of the boiler is higher than 880K.

一种提高所述低熵混燃高超临界热动力系统效率和环保性的方法，所述锅 炉的气体工质出口处的气体工质的温度和压力符合类绝热关系。  A method for improving the efficiency and environmental protection of the low-entropy co-firing high-supercritical thermodynamic system, wherein the temperature and pressure of the gaseous working fluid at the outlet of the gas working fluid of the boiler are in an adiabatic relationship.

本发明的原理是将由所述锅炉工质腔产生的高温高压工质在所述燃烧室 内通过相内加热的方式（即燃烧反应在来自锅炉工质腔的工质中进行）使工质 吸收热量提高温度，或者将来自锅炉工质腔的高温高压工质经所述增压器增压 后在所述燃烧室内通过相内加热的方式使工质的温度和压力都进一步提高， 升 温后或升温升压后的工质进入所述作功机构对外作功。  The principle of the invention is that the high temperature and high pressure working medium generated by the working fluid chamber of the boiler is heated in the combustion chamber by means of internal heating (that is, the combustion reaction is carried out in the working medium from the working chamber of the boiler) to absorb heat from the working medium. Increasing the temperature, or heating the high-temperature and high-pressure working fluid from the working chamber of the boiler through the supercharger, and further heating the temperature and pressure of the working medium by means of internal heating in the combustion chamber, after heating or heating up The pressurized working fluid enters the working mechanism to perform external work.

本发明所公开的低熵混燃高超临界热动力系统， 不仅可以提高热动力系统 的效率， 而且还可以有效利用粗糙燃料（如煤、 生物质等）和精细燃料（如汽 油、 柴油、 氢气、 金属燃料等）， 使燃料资源得到更加充分的利用。  The low-energy co-firing high-supercritical thermodynamic system disclosed by the invention not only can improve the efficiency of the thermodynamic system, but also can effectively utilize rough fuels (such as coal, biomass, etc.) and fine fuels (such as gasoline, diesel, hydrogen, Metal fuels, etc., make fuel resources more fully utilized.

本发明所公开的低熵混燃高超临界热动力系统，所谓的金属燃料是指直接 与氧发生剧烈化学反应的金属或与水反应产生氢气 （氢气与氧发生化学反应） 的金属， 例如金属铝或金属镁等。金属燃料的使用的主要目的是规避在燃烧后 产生不凝气二氧化碳； 所谓的工质金属化合物分离器是指将金属燃料燃烧后产 生的金属化合物进行分离的装置。  The low-energy co-firing high-supercritical thermodynamic system disclosed in the present invention refers to a metal that directly undergoes a violent chemical reaction with oxygen or a metal that reacts with water to generate hydrogen (hydrogen reaction with oxygen), such as metal aluminum. Or metal magnesium, etc. The main purpose of the use of the metal fuel is to avoid the generation of non-condensable carbon dioxide after combustion; the so-called working metal compound separator refers to a device for separating metal compounds produced by burning a metal fuel.

本发明所谓的冲压发动机的进气口是指冲压发动机进气道的空气入口，所 谓的冲压发动机燃烧室是指由冲压发动机进气道进入的气体经扩压区增压后 的气体所在的空间，所谓的冲压发动机扩压区气体出口是指冲压发动机中进入 喷管之前的气体高压区。这一结构的目的是利用冲压发动机进气道将工质加速 再经扩压区增压后经所述燃烧室增温后提高工质的作功能力。  The intake port of the so-called ramjet engine of the present invention refers to the air inlet of the intake port of the ramjet engine, and the so-called ramjet engine combustion chamber refers to the space where the gas which is pressurized by the blasting engine intake passage is pressurized by the diffusing zone. The so-called ramjet diffuser gas outlet refers to the gas high pressure zone before entering the nozzle in the ramjet engine. The purpose of this structure is to use the ramjet engine inlet to accelerate the working fluid and then pressurize the diffuser zone to increase the working capacity of the working fluid after the temperature is increased by the combustion chamber.

在传统的利用锅炉工质腔产生高温高压工质的热动力系统中， 由于是外燃 加热方式， 所以汽化室壁的温度要远高于其内部工质的温度， 这就造成了如上 所述工质的压力和温度都严重受限制的状况。而在本发明所公开的低熵混燃高 超临界热动力系统中， 作为进一步提高工质温度或工质温度和压力的技术手 段， 是采用了在工质相内混合加热的方式， 即将燃烧火焰直接与工质混合， 这 种燃烧产生的热量不经固体界面直接对工质传热的方式可以使工质的温度远 高于承载此工质的容器或管道壁的温度， 为此， 本发明所公开的低熵混燃高超 临界热动力系统可以在现有材料技术的基础上大幅度提高作功工质的温度和 压力， 最终提高热动力系统的效率。 In the conventional thermodynamic system that uses the boiler working chamber to generate high temperature and high pressure working fluid, the temperature of the vaporization chamber wall is much higher than the temperature of the internal working medium because it is the external combustion heating method, which results in the above The pressure and temperature of the working fluid are severely limited. In the low-energy co-firing high-supercritical thermal power system disclosed by the present invention, as a technical means for further improving the working temperature or working temperature and pressure, a method of mixing and heating in the working phase is adopted, that is, a burning flame Directly mixed with the working fluid, the heat generated by this combustion can directly transfer heat to the working medium without passing through the solid interface, so that the temperature of the working medium can be far The temperature of the container or the pipe wall carrying the working medium is higher than the temperature of the working medium, and the low-energy co-firing high-supercritical thermal power system disclosed by the invention can greatly improve the temperature of the working fluid based on the existing material technology. Pressure, ultimately improving the efficiency of the thermodynamic system.

本发明中， 调整所述锅炉的液体工质入口的流量和压力， 调整所述锅炉的 气体工质出口处的流量， 调整所述锅炉的加热强度使所述锅炉的气体工质出口 处的气体工质压力大于 31 MPa、 31 . 5MPa、 32MPa、 32. 5MPa、 33MPa、 33. 5MPa、 34MPa、 34. 5MPa、 35MPa、 35. 5MPa、 36MPa、 36. 5MPa、 37MPa、 37. 5MPa 38MPa、 38. 5MPa 39MPa、 39. 5MPa或大于 40MPa。  In the present invention, the flow rate and pressure of the liquid working fluid inlet of the boiler are adjusted, the flow rate at the gas working fluid outlet of the boiler is adjusted, and the heating intensity of the boiler is adjusted to make the gas at the gas working outlet of the boiler 5MPa, 38MPa, 37. 5MPa, 38MPa, 38. 5MPa, 38MPa, 37MPa, 36. 5MPa, 37MPa, 37. 5MPa, 38MPa, 38MPa, 37. 5MPa, 38MPa, 38. 5MPa 39MPa, 39. 5MPa or more than 40MPa.

本发明中， 调整所述锅炉的液体工质入口的流量和压力， 调整所述锅炉的 气体工质出口处的流量，调整所述锅炉的加热强度使所述锅炉的气体工质出口 处的气体工质温度高于 885Κ、 890Κ、 895Κ、 900Κ、 905Κ、 910Κ、 915Κ、 920Κ、 925Κ、 930Κ、 935Κ、 940Κ、 945Κ、 950Κ、 955Κ、 960Κ、 965Κ、 970Κ、 975Κ、 980Κ、 985Κ、 990Κ、 995Κ或高于 1000Κ。  In the present invention, adjusting the flow rate and pressure of the liquid working fluid inlet of the boiler, adjusting the flow rate at the gas working fluid outlet of the boiler, and adjusting the heating intensity of the boiler to make the gas at the gas working outlet of the boiler Working temperature is higher than 885Κ, 890Κ, 895Κ, 900Κ, 905Κ, 910Κ, 915Κ, 920Κ, 925Κ, 930Κ, 935Κ, 940Κ, 945Κ, 950Κ, 955Κ, 960Κ, 965Κ, 970Κ, 975Κ, 980Κ, 985Κ, 990Κ, 995Κ Or higher than 1000Κ.

本发明所公开的低熵混燃高超临界热动力系统中， 为了增加从所述燃烧室 到所述作功机构高压区的承压能力， 可在所述燃烧室、 连接所述燃烧室和所述 作功机构的连通通道和 /或所述作功机构内设隔热衬。 为了增加从所述燃烧室 到所述作功机构高压区的承压能力， 可以对所述燃烧室、 连接所述燃烧室和所 述作功机构的连通通道和 /或所述作功机构进行适当冷却， 以降低它们的壁的 温度， 增大其承压能力。  In the low-energy co-firing high-supercritical thermodynamic system disclosed in the present invention, in order to increase the pressure-receiving capacity from the combustion chamber to the high-pressure region of the working mechanism, the combustion chamber, the combustion chamber and the chamber may be connected The communication channel of the work mechanism and/or the heat insulation lining is disposed in the working mechanism. In order to increase the pressure bearing capacity from the combustion chamber to the high pressure region of the working mechanism, the combustion chamber, the communication passage connecting the combustion chamber and the working mechanism, and/or the working mechanism may be Properly cooled to lower the temperature of their walls and increase their pressure bearing capacity.

本发明中， 所谓的环保性是衡量热动力系统污染排放的指标， 环保性高热 动力系统排放污染少， 环保性低热动力系统排放污染多。  In the present invention, the so-called environmental protection is an indicator for measuring the pollution emission of the thermal power system, and the environmentally-friendly high-heat power system emits less pollution, and the environmentally-friendly low-heat power system emits more pollution.

本发明所公开的低熵混燃高超临界热动力系统中所谓的工质可以是水或 其他介质，进入所述作功机构的工质可以处于含湿状态、过热状态、临界状态、 超临界状态、 超超临界状态或更高压力温度状态。  The so-called working medium in the low entropy co-firing high supercritical thermal power system disclosed by the invention may be water or other medium, and the working medium entering the working mechanism may be in a wet state, a superheat state, a critical state, a supercritical state. , ultra-supercritical state or higher pressure temperature state.

本发明所谓的高超临界不仅包括工质处于过热状态、 临界状态、超临界状 态和超超临界状态， 还包括工质处于更高温度压力状态。  The so-called high supercriticality of the present invention includes not only the working medium in a superheated state, a critical state, a supercritical state, and an ultra-supercritical state, but also a working temperature at a higher temperature and pressure state.

本发明中，图 19是气体工质的温度 Τ和压力 Ρ的关系图， 0-A-H所示曲线 是通过状态参数为 298Κ和 0. 1 MPa的 0点的气体工质绝热关系曲线； B点为气 体工质的实际状态点， E-B-D所示曲线是通过 B点的绝热关系曲线， A点和 B 点的压力相同； F- G所示曲线是通过 2800K和 10MPa (即目前内燃机中即将开 始作功的气体工质的状态点） 的工质绝热关系曲线。 In the present invention, FIG. 19 is a relationship diagram of temperature enthalpy and pressure enthalpy of the gas working medium, and the curve indicated by 0-AH is a gas-based adiabatic relationship curve of 0 points passing through state parameters of 298 Κ and 0.1 MPa; Gas The actual state point of the working fluid, the curve shown by EBD is the adiabatic relationship curve through point B, the pressures of point A and point B are the same; the curve shown by F-G is through 2800K and 10MPa (that is, the current internal combustion engine is about to start work) The working point of the gas working fluid is adiabatic.

本发明中， 图 19中的 = cr^中的/是气体工质绝热指数， P是气体工质 的压力， Γ是气体工质的温度， （：是常数。  In the present invention, / in the = cr^ in Fig. 19 is the adiabatic index of the gas working fluid, P is the pressure of the gaseous working fluid, and Γ is the temperature of the gaseous working fluid, (: is a constant.

本发明中， 所谓的类绝热关系包括下列三种情况： 1.气体工质的状态参数 (即工质的温度和压力）点在所述工质绝热关系曲线上， 即气体工质的状态参 数点在图 19中 0-A-H所示曲线上； 2.气体工质的状态参数 （即工质的温度和 压力） 点在所述工质绝热关系曲线左侧， 即气体工质的状态参数点在图 19 中 0-A-H所示曲线的左侧； 3.气体工质的状态参数 （即工质的温度和压力） 点在 所述工质绝热关系曲线右侧， 即气体工质的状态参数点在图 19中 0-A-H所示 曲线的右侧，但是气体工质的温度不高于由此气体工质的压力按绝热关系计算 所得温度加 1000K的和、 加 950K的和、 加 900K的和、 加 850K的和、 加 800K 的和、 加 750K的和、 加 700K的和、 加 650K的和、 加 600K的和、 加 550K的 和、 加 500K的和、 加 450K的和、 加 400K的和、 加 350K的和、 加 300K的和、 加 250K的和、 加 200K的和、 力 U 190K的和、 力 U 180K的和、 力 Π 170K的和、 加 160K的和、力卩 150K的和、力!] 140K的和、力卩 130K的和、力卩 120K的和、力 Q 110K 的和、 加 100K的和、 加 90K的和、 加 80K的和、 加 70K的和、 加 60K的和、 加 50K的和、 加 40K的和、 加 30K的和或不高于加 20K的和， 即如图 19所示， 所述气体工质的实际状态点为 B点， A点是压力与 B点相同的绝热关系曲线上 的点， A点和 B点之间的温差应小于 1000Κ、 900Κ、 850Κ、 800Κ、 750Κ、 700Κ、 650Κ、 600Κ、 550Κ、 500Κ、 450Κ、 400Κ、 350Κ、 300Κ、 250Κ、 200Κ、 190Κ、 180Κ、 170Κ、 160Κ、 150Κ、 140Κ、 130Κ、 120Κ、 1 10Κ、 100Κ、 90Κ、 80Κ、 70Κ、 60Κ、 50Κ、 40Κ、 30Κ或小于 20Κ。  In the present invention, the so-called adiabatic relationship includes the following three cases: 1. The state parameter of the gas working medium (ie, the temperature and pressure of the working medium) is on the adiabatic relationship curve of the working medium, that is, the state parameter of the gaseous working medium. The point is on the curve shown by 0-AH in Fig. 19; 2. The state parameter of the gas working fluid (ie the temperature and pressure of the working medium) is on the left side of the adiabatic relationship curve of the working fluid, that is, the state parameter point of the gas working fluid. On the left side of the curve shown by 0-AH in Figure 19; 3. The state parameter of the gas working fluid (ie, the temperature and pressure of the working fluid) is on the right side of the adiabatic relationship curve of the working fluid, that is, the state parameter of the gas working fluid. The point is on the right side of the curve shown by 0-AH in Fig. 19, but the temperature of the gas working fluid is not higher than the temperature calculated from the adiabatic relationship of the gas working fluid plus 1000K sum, 950K sum, and 900K And, add 850K, add 800K, add 750K, add 700K and add 650K, add 600K and add 550K, add 500K and add 450K and add 400K And, add 350K, add 300K and add 250K , plus 200K sum, force U 190K sum, force U 180K sum, force Π 170K sum, plus 160K sum, force 卩 150K sum, force!] 140K sum, force 卩 130K sum, force 卩120K, and force Q 110K sum, plus 100K sum, add 90K sum, add 80K sum, add 70K sum, add 60K sum, add 50K sum, add 40K sum, add 30K and or Not higher than the sum of 20K, that is, as shown in Fig. 19, the actual state point of the gas working medium is point B, and point A is the point on the adiabatic relationship curve of the same pressure as point B, points A and B The temperature difference between the two should be less than 1000Κ, 900Κ, 850Κ, 800Κ, 750Κ, 700Κ, 650Κ, 600Κ, 550Κ, 500Κ, 450Κ, 400Κ, 350Κ, 300Κ, 250Κ, 200Κ, 190Κ, 180Κ, 170Κ, 160Κ, 150Κ, 140Κ, 130Κ 120Κ, 1 10Κ, 100Κ, 90Κ, 80Κ, 70Κ, 60Κ, 50Κ, 40Κ, 30Κ or less than 20.

本发明中，所谓类绝热关系可以是上述三种情况中的任何一种，也就是指: 即将开始作功的气体工质的状态参数（即气体工质的温度和压力）点在如图 19 所示的通过 Β点的绝热过程曲线 E- B-D的左侧区域内。  In the present invention, the so-called adiabatic relationship may be any one of the above three cases, that is, the state parameter of the gas working medium to be started to work (ie, the temperature and pressure of the gas working medium) is as shown in FIG. The adiabatic process curve shown through the defect is in the left region of the E-BD.

本发明中，所谓的即将开始作功的气体工质是指即将进入所述作功机构的 的气体工质。 In the present invention, the so-called gas working fluid that is about to start work refers to entering the working mechanism. Gas working fluid.

本发明中， 将即将开始作功的气体工质的状态参数（即气体工质的温度和 压力） 符合类绝热关系的发动机系统 （即热动力系统） 定义为低熵发动机。  In the present invention, an engine system (i.e., a thermodynamic system) in which the state parameters of the gaseous working medium (i.e., the temperature and pressure of the gaseous working medium) to be started to work is classified as a low-entropy engine is defined.

本发明中，调整所述锅炉的外燃加热强度及所述锅炉对外输出工质的流量 进而调整所述锅炉工质腔内的气体工质的状态 （即温度和压力）， 调整所述燃 烧室的内燃加热强度使即将开始作功的气体工质的温度和压力符合类绝热关 系。  In the present invention, adjusting the external combustion heating intensity of the boiler and the flow rate of the external output working fluid of the boiler to adjust the state (ie, temperature and pressure) of the gaseous working medium in the working fluid chamber of the boiler, and adjusting the combustion chamber The internal combustion heating intensity causes the temperature and pressure of the gaseous working fluid to be started to work in an adiabatic relationship.

本发明所公开的低熵混燃高超临界热动力系统中，在将所述燃烧室全部设 在所述锅炉工质腔的结构中， 不仅可以减少所述燃烧室的热量损失， 而且由于 所述燃烧室外部受到所述锅炉工质腔内的工质由外向内的压力作用，所以可以 减少对所述燃烧室的承压能力的要求；特别是当在所述燃烧室工质入口处设置 增压器时， 所述燃烧室内的压力会大幅度增加， 在这种情况下， 如果将所述燃 烧室设置在所述锅炉工质腔内， 会大大减少对所述燃烧室结构强度的要求， 减 少所述燃烧室的造价。在将所述作功机构设为动力透平并利用所述动力透平对 所述增压器输出动力的结构中， 如果将所述增压器、所述燃烧室和所述动力透 平的高压区设置在所述锅炉工质腔内， 会减少系统的制造成本。  In the low-energy co-firing high-supercritical thermal power system disclosed in the present invention, in the structure in which the combustion chamber is entirely disposed in the working fluid chamber of the boiler, not only the heat loss of the combustion chamber can be reduced, but also The outside of the combustion chamber is subjected to external pressure from the working fluid in the working chamber of the boiler, so that the pressure bearing capacity of the combustion chamber can be reduced; in particular, when the working fluid inlet is installed at the combustion chamber When the pressure is applied, the pressure in the combustion chamber is greatly increased. In this case, if the combustion chamber is disposed in the working fluid chamber of the boiler, the structural strength of the combustion chamber is greatly reduced. The cost of the combustion chamber is reduced. In a configuration in which the work mechanism is set as a power turbine and power is output to the supercharger using the power turbine, if the supercharger, the combustion chamber, and the power turbine are The high pressure zone is disposed in the working fluid chamber of the boiler, which reduces the manufacturing cost of the system.

本发明所谓的燃烧室是指一切可以在其内部发生燃烧 （剧烈放热化学反 应） 的容器； 所谓锅炉工质腔是指存储锅炉受热后所产生的工质， 此时的工质 可以是蒸气、 过热蒸气、 临界状态工质、 超临界状态工质、 超超临界状态工质 或更高温度压力状态的工质； 所谓的作功机构是指一切可以将高温高压工质的 能量转化为机械功向外输出的机械设备， 如传统往复式的气缸活塞机构， 动力 透平， 喷管等； 所谓增压器是指一切可以对工质增压的装置， 可以是叶轮式压 縮机， 也可以是活塞式压縮机等； 所谓冷凝冷却器是指一切可以将工质降温冷 却、 冷凝的装置， 它可以是散热器， 也可以是热交换器， 还可以是晾水塔； 所 谓不凝气是指在冷凝冷却器中不冷凝的气体； 所谓余量工质是指因为燃烧化学 反应而产生的多余的工质； 所谓连通是指直接连通、 间接连通或经泵、 控制阀 等受控连通； 所谓动力单元是指为了给所述增压器提供动力而设置的可以利用 所述低熵混燃高超临界热动力系统中的工质产生动力的机构， 如透平或活塞曲 柄连杆机构等。 The so-called combustion chamber of the present invention refers to a container in which combustion (violent exothermic chemical reaction) can occur in the interior; the so-called boiler working chamber refers to the working medium produced by the storage boiler after being heated, and the working medium at this time may be steam. , superheated steam, critical state working fluid, supercritical working fluid, ultra-supercritical working fluid or higher temperature pressure working medium; the so-called working mechanism means that all energy can be converted into high-temperature and high-pressure working medium Mechanical equipment that outputs outwards, such as a conventional reciprocating cylinder piston mechanism, a power turbine, a nozzle, etc.; a supercharger is a device that can pressurize a working medium, and can be an impeller compressor. It can be a piston compressor, etc.; the so-called condensing cooler is a device that can cool and condense the working medium. It can be a radiator, a heat exchanger, or a water drying tower. Refers to the gas that does not condense in the condensing cooler; the so-called residual working fluid refers to the excess working fluid produced by the combustion chemical reaction; the so-called connectivity means direct communication, Indirectly connected or controlled by a pump, a control valve, etc.; a so-called power unit means a power provided for powering the supercharger that can utilize the working fluid in the low-energy co-firing high-supercritical thermodynamic system to generate power Institutions, such as turbines or pistons Handle linkage mechanism, etc.

本发明中应根据公知技术，在适当位置设阀、泵和相应的控制装置等部件、 单元或系统。  In the present invention, components, units or systems such as valves, pumps and corresponding control devices are provided at appropriate locations in accordance with known techniques.

本发明的有益效果如下： The beneficial effects of the present invention are as follows:

本发明所公开的低熵混燃高超临界热动力系统， 不仅效率高， 而且还可以 充分利用燃料资源。  The low-entropy co-firing high-supercritical thermodynamic system disclosed by the present invention not only has high efficiency, but also can fully utilize fuel resources.

附图说明 DRAWINGS

图 1为本发明的实施例 1的示意图；  Figure 1 is a schematic view of Embodiment 1 of the present invention;

图 2为本发明的实施例 2的示意图；  Figure 2 is a schematic view of Embodiment 2 of the present invention;

图 3为本发明的实施例 3的示意图；  Figure 3 is a schematic view of Embodiment 3 of the present invention;

图 4为本发明的实施例 4的示意图；  Figure 4 is a schematic view of Embodiment 4 of the present invention;

图 5为本发明的实施例 5的示意图；  Figure 5 is a schematic view of Embodiment 5 of the present invention;

图 6为本发明的实施例 6的示意图；  Figure 6 is a schematic view of Embodiment 6 of the present invention;

图 7为本发明的实施例 7的示意图；  Figure 7 is a schematic view of Embodiment 7 of the present invention;

图 8为本发明的实施例 8的示意图；  Figure 8 is a schematic view of Embodiment 8 of the present invention;

图 9为本发明的实施例 9的示意图；  Figure 9 is a schematic view of Embodiment 9 of the present invention;

图 10为本发明的实施例 10的示意图；  Figure 10 is a schematic view of Embodiment 10 of the present invention;

图 1 1为本发明的实施例 11的示意图；  Figure 11 is a schematic view of Embodiment 11 of the present invention;

图 12为本发明的实施例 12的示意图；  Figure 12 is a schematic view of Embodiment 12 of the present invention;

图 13为本发明的实施例 13的示意图；  Figure 13 is a schematic view of Embodiment 13 of the present invention;

图 14为本发明的实施例 14的示意图；  Figure 14 is a schematic view of Embodiment 14 of the present invention;

图 15为本发明的实施例 15的示意图；  Figure 15 is a schematic view of Embodiment 15 of the present invention;

图 16为本发明的实施例 16的示意图；  Figure 16 is a schematic view of Embodiment 16 of the present invention;

图 17为本发明的实施例 17的示意图；  Figure 17 is a schematic view showing Embodiment 17 of the present invention;

图 18为本发明的实施例 18的示意图；  Figure 18 is a schematic view of Embodiment 18 of the present invention;

图 19为气体工质的温度 T和压力 P的关系图；  Figure 19 is a graph showing the relationship between the temperature T of the gas working fluid and the pressure P;

图 20为本发明的实施例 19的示意图。  Figure 20 is a schematic view of Embodiment 19 of the present invention.

图中： 1锅炉、 2锅炉工质腔、 3作功机构、 4燃烧室、 5氧化剂源、 In the picture: 1 boiler, 2 boiler working chamber, 3 working mechanism, 4 combustion chamber, 5 oxidant source,

6燃料源、 7增压器、 8动力单元、 9发电机、 10冷凝冷却器、  6 fuel source, 7 supercharger, 8 power unit, 9 generator, 10 condensing cooler,

11液体高压回流泵、 12不凝气体导出口、 13余量工质导出口、  11 liquid high pressure return pump, 12 non-condensable gas outlet, 13 balance of working fluid outlet,

401燃烧室工质入口、 402燃烧室工质出口、 403氧化剂入口、  401 combustion chamber working fluid inlet, 402 combustion chamber working fluid outlet, 403 oxidant inlet,

404燃料入口、 501氧化剂高压供送系统、 601燃料高压供送系统、  404 fuel inlet, 501 oxidant high pressure supply system, 601 fuel high pressure supply system,

301动力透平、 302活塞式作功机构、 701叶轮式压縮机、  301 power turbine, 302 piston type working mechanism, 701 impeller compressor,

702活塞式压縮机、 801叶轮式动力单元、 405工质金属化合物分离器、 100晾水塔、 200回热器、 400冲压发动机燃烧室、  702 piston compressor, 801 impeller power unit, 405 working metal compound separator, 100 water tower, 200 regenerator, 400 ram engine combustion chamber,

4001冲压发动机的进气口、 4002冲压发动机扩压区气体出口  4001 ramjet engine inlet, 4002 ramjet diffuser zone gas outlet

具体实施方式 detailed description

实施例 1  Example 1

如图 1所示的低熵混燃高超临界热动力系统， 包括锅炉 1、 锅炉工质腔 2、 作功机构 3和燃烧室 4， 所述燃烧室 4上设有燃烧室工质入口 401、 燃烧室工 质出口 402、 氧化剂入口 403和燃料入口 404， 氧化剂源 5经氧化剂高压供送 系统 501与所述氧化剂入口 403连通， 燃料源 6经燃料高压供送系统 601与所 述燃料入口 404连通， 所述燃烧室 4全部设置在所述锅炉工质腔 2内， 所述锅 炉工质腔 2与所述燃烧室工质入口 401连通，所述燃烧室工质出口 402与所述 作功机构 3连通。所述低熵混燃高超临界热动力系统还包括冷凝冷却器 10，所 述作功机构 3的工质出口与所述冷凝冷却器 10的被冷却流体入口连通， 所述 冷凝冷却器 10的被冷却流体出口与液体高压回流泵 11的入口连通，所述液体 高压回流泵 11的出口与所述锅炉工质腔 2连通，在所述液体高压回流泵 1 1的 作用下被所述冷凝冷却器 10液化的工质回流到所述锅炉工质腔 2内， 即将开 始作功的气体工质的温度和压力符合类绝热关系。所述燃料源 6内的燃料设为 碳氢化合物、碳氢氧化合物或设为氢气。所述氧化剂源 5内的氧化剂设为液氧、 高压气态氧或过氧化氢水溶液。  The low-energy co-firing high-supercritical thermal power system shown in FIG. 1 includes a boiler 1, a boiler working chamber 2, a working mechanism 3, and a combustion chamber 4, and the combustion chamber 4 is provided with a combustion chamber working inlet 401, A combustion chamber working outlet 402, an oxidant inlet 403 and a fuel inlet 404, the oxidant source 5 is in communication with the oxidant inlet 403 via an oxidant high pressure supply system 501, and the fuel source 6 is in communication with the fuel inlet 404 via a high pressure fuel supply system 601. The combustion chambers 4 are all disposed in the working fluid chamber 2 of the boiler, the working fluid chamber 2 of the boiler is in communication with the working fluid inlet 401 of the combustion chamber, the working fluid outlet 402 of the combustion chamber and the working mechanism 3 connected. The low-entropy co-firing high-supercritical thermodynamic system further includes a condensing cooler 10, and a working fluid outlet of the working mechanism 3 is in communication with a cooled fluid inlet of the condensing cooler 10, and the condensing cooler 10 is The cooling fluid outlet is in communication with an inlet of the liquid high pressure return pump 11, the outlet of the liquid high pressure return pump 11 is in communication with the boiler working chamber 2, and the condensing cooler is operated by the liquid high pressure return pump 1 1 10 The liquefied working fluid is returned to the working fluid chamber 2 of the boiler, and the temperature and pressure of the working fluid which is about to start work are in accordance with the adiabatic relationship. The fuel in the fuel source 6 is a hydrocarbon, a carbon oxyhydroxide or a hydrogen gas. The oxidizing agent in the oxidant source 5 is set to be liquid oxygen, high pressure gaseous oxygen or an aqueous hydrogen peroxide solution.

实施例 2  Example 2

如图 2所示的低熵混燃高超临界热动力系统，其与实施例 1的区别在于：。 所述燃烧室 4部分设置在所述锅炉工质腔 2内。这样设置的目的不仅可以减少 所述燃烧室的热量损失，而且由于所述燃烧室外部受到所述锅炉工质腔内的工 质由外向内的压力作用， 所以可以减少对所述燃烧室的承压能力的要求。 The low-entropy co-firing high-supercritical thermodynamic system shown in FIG. 2 differs from Embodiment 1 in that: The combustion chamber 4 is partially disposed within the working fluid chamber 2 of the boiler. The purpose of this setting can not only reduce The heat loss of the combustion chamber, and the external pressure of the working fluid in the working chamber of the boiler is externally and inwardly pressurized, so that the pressure bearing capacity of the combustion chamber can be reduced.

实施例 3  Example 3

如图 3所示的低熵混燃高超临界热动力系统， 其与实施例 1的区别在于： 所述燃烧室 4设置在所述锅炉 1外。  The low-entropy co-firing high-supercritical thermodynamic system shown in Fig. 3 differs from the first embodiment in that the combustion chamber 4 is disposed outside the boiler 1.

实施例 4  Example 4

如图 4所示的低熵混燃高超临界热动力系统， 其与实施例 3的区别在于： 在所述燃烧室工质入口 401处设增压器 7， 所述增压器 7对所述燃烧室 4内的 工质增压， 在所述燃烧室工质出口 402处设动力单元 8， 所述动力单元 8对所 述増压器 7输出动力， 所述动力单元 8与所述增压器 7同轴设置， 并且所述动 力单元 8与所述増压器 7的连接轴设在所述燃烧室 4内。  The low entropy co-firing high supercritical thermal power system shown in FIG. 4 is different from the third embodiment in that: a supercharger 7 is disposed at the combustion chamber inlet 401, and the supercharger 7 is The working fluid in the combustion chamber 4 is pressurized, and a power unit 8 is disposed at the combustion chamber outlet 402. The power unit 8 outputs power to the pressure device 7, and the power unit 8 and the supercharging unit The device 7 is coaxially disposed, and a connecting shaft of the power unit 8 and the ram 7 is disposed in the combustion chamber 4.

实施例 5  Example 5

如图 5所示的低熵混燃高超临界热动力系统， 其与实施例 4的区别在于： 所述动力单元 8与所述增压器 7同轴设置，并且所述动力单元 8与所述增压器 7的连接轴设在所述燃烧室 4外， 这样设置的目的是为了减少对所述连接轴的 热负荷要求， 减少制造成本。  a low-entropy co-firing high-supercritical thermodynamic system as shown in FIG. 5, which differs from Embodiment 4 in that: the power unit 8 is coaxially disposed with the supercharger 7, and the power unit 8 is The connecting shaft of the supercharger 7 is provided outside the combustion chamber 4, and the purpose of this arrangement is to reduce the heat load requirement for the connecting shaft and to reduce the manufacturing cost.

实施例 6  Example 6

如图 6所示的低熵混燃高超临界热动力系统， 其与实施例 3的区别在于： 在所述燃烧室工质入口 401处设增压器 7， 所述增压器 7对所述燃烧室 4内的 工质增压， 所述作功机构 3对所述增压器 7输出动力， 所述作功机构 3与所述 增压器 7同轴设置。  a low-entropy co-firing high-supercritical thermodynamic system as shown in FIG. 6 differs from the third embodiment in that: a supercharger 7 is provided at the combustion chamber inlet 401, and the supercharger 7 is The working fluid in the combustion chamber 4 is pressurized, the working mechanism 3 outputs power to the supercharger 7, and the working mechanism 3 is disposed coaxially with the supercharger 7.

实施例 7  Example 7

如图 7所示的低熵混燃高超临界热动力系统， 其与实施例 5的区别在于： 所述作功机构与发电机 9连接， 在所述冷凝冷却器 10的被冷却流体出口处设 不凝气体导出口 12， 所述作功机构设为动力透平 301。  The low entropy co-firing high supercritical thermal power system shown in FIG. 7 is different from the embodiment 5 in that the working mechanism is connected to the generator 9 and is disposed at the outlet of the condensed cooler 10 to be cooled. The gas outlet port 12 is not condensed, and the work mechanism is set as the power turbine 301.

实施例 8  Example 8

如图 8所示的低熵混燃高超临界热动力系统， 其与实施例 1的区别在于： 所述作功机构设为活塞式作功机构 302，在所述冷凝冷却器 10的被冷却流体入 口处和所述冷凝冷却器 10的被冷却流体出口处设余量工质导出口 13。 具体实施时， 还可以在所述冷凝冷却器 10的被冷却流体入口处或在所述 冷凝冷却器 10的被冷却流体出口处设余量工质导出口 13。 The low entropy co-firing high supercritical thermal power system shown in FIG. 8 differs from the first embodiment in that: the working mechanism is set as a piston type working mechanism 302, and the cooled fluid in the condensing cooler 10 Enter A residual working fluid outlet 13 is provided at the mouth and at the outlet of the chilled fluid of the condensing cooler 10. In a specific implementation, a residual working fluid outlet 13 may also be provided at the inlet of the cooled fluid of the condensing cooler 10 or at the outlet of the cooled fluid of the condensing cooler 10.

实施例 9  Example 9

如图 9所示的低熵混燃高超临界热动力系统， 其与实施例 1的区别在于： 所述低熵混燃高超临界热动力系统还包括增压器和动力单元，所述增压器设为 叶轮式压縮机 701， 所述动力单元设为叶轮式动力单元 801。  The low entropy co-firing high supercritical thermal power system shown in FIG. 9 is different from the first embodiment in that: the low entropy co-firing high supercritical thermal power system further includes a supercharger and a power unit, and the supercharger The impeller type compressor 701 is used, and the power unit is an impeller type power unit 801.

实施例 10  Example 10

如图 10所示的低熵混燃高超临界热动力系统，其与实施例 6的区别在于： 所述低熵混燃高超临界热动力系统还包括增压器和动力单元 8， 所述增压器设 为活塞式压縮机 702， 所述动力单元 8设为活塞式动力单元。  The low entropy co-firing high supercritical thermal power system shown in FIG. 10 differs from the embodiment 6 in that: the low entropy co-firing high supercritical thermal power system further includes a supercharger and a power unit 8, the supercharging The compressor is set as a piston compressor 702, and the power unit 8 is a piston type power unit.

实施例 11  Example 11

如图 11所示的低熵混燃高超临界热动力系统，其与实施例 3的区别在于： 在所述燃烧室 4壁的内侧设隔热衬 40。  The low-entropy co-firing high-supercritical thermodynamic system shown in Fig. 11 differs from the third embodiment in that an insulating lining 40 is provided inside the wall of the combustion chamber 4.

实施例 12  Example 12

如图 12所示的低熵混燃高超临界热动力系统，其与实施例 3的区别在于： 在所述燃烧室 4壁的外侧设散热结构 110。  The low entropy co-firing high supercritical thermal power system shown in Fig. 12 differs from the third embodiment in that a heat dissipating structure 110 is provided outside the wall of the combustion chamber 4.

实施例 13  Example 13

如图 13所示的低熵混燃高超临界热动力系统，其与实施例 1的区别在于： 所述燃料源 6内的燃料设为金属燃料， 在所述燃烧室 4内和 /或在所述作功机 构 3前和 /或在所述作功机构 3后设工质金属化合物分离器 405。  The low entropy co-firing high supercritical thermal power system shown in FIG. 13 differs from the first embodiment in that: the fuel in the fuel source 6 is set as a metal fuel, in the combustion chamber 4 and/or in the The working metal compound separator 405 is disposed before the working mechanism 3 and/or after the working mechanism 3.

实施例 14  Example 14

如图 14所示的低熵混燃高超临界热动力系统，其与实施例 3的区别在于: 所述冷凝冷却器 10设为晾水塔 100。  The low entropy co-firing high supercritical thermal power system shown in Fig. 14 differs from the third embodiment in that the condensing cooler 10 is set as the water drying tower 100.

实施例 15  Example 15

如图 15所示的低熵混燃高超临界热动力系统，其与实施例 3的区别在于: 在所述作功机构 3的工质出口处设回热器 200。  The low-entropy co-firing high-supercritical thermodynamic system shown in Fig. 15 differs from the third embodiment in that a regenerator 200 is provided at the working medium outlet of the working mechanism 3.

实施例 16 如图 16所示的低熵混燃高超临界热动力系统，其与实施例 3的区别在于: 所述燃烧室工质入口设为冲压发动机的进气口 4001，所述燃烧室 4设为冲压发 动机燃烧室 400， 所述燃烧室工质出口设为冲压发动机扩压区气体出口 4002。 这样可以利用冲压发动机的扩压区对气体工质进行压縮，提高气体工质的作功 能力。 Example 16 The low entropy co-firing high supercritical thermal power system shown in FIG. 16 differs from the third embodiment in that: the combustion chamber working inlet is set as the intake port 4001 of the ramjet, and the combustion chamber 4 is set to be stamped. In the engine combustion chamber 400, the combustion chamber working fluid outlet is set as a ramjet diffuser gas outlet 4002. In this way, the gas working medium can be compressed by the diffusing zone of the ramjet engine, and the function of the gas working fluid can be improved.

实施例 1 7  Example 1 7

如图 17所示的低熵混燃高超临界热动力系统，其与实施例 3的区别在于： 所述低熵混燃高超临界热动力系统还包括增压器，所述作功机构设为动力透平 301，所述増压器设为叶轮式压縮机 701，所述动力透平 301设在所述燃烧室工 质出口 402内，所述动力透平 301对所述叶轮式压縮机 701输出动力的同时对 外输出动力。  The low entropy co-firing high supercritical thermal power system shown in FIG. 17 is different from the third embodiment in that: the low entropy co-firing high supercritical thermal power system further includes a supercharger, and the working mechanism is set as a power Turbine 301, the squeezing device is set as an impeller compressor 701, the power turbine 301 is disposed in the combustion chamber working outlet 402, and the power turbine 301 is opposite to the impeller compressor The 701 outputs power while outputting power externally.

实施例 18  Example 18

如图 18所示的低熵混燃高超临界热动力系统，其与实施例 4的区别在于: 所述增压器设为叶轮式压縮机 701， 所述作功机构 3设为动力透平 301， 所述 动力透平 301对所述叶轮式压縮机 701输出动力， 所述叶轮式压縮机 701、 所 述燃烧室 4和所述动力透平 301的高压区设在所述锅炉工质腔 2内。  The low entropy co-firing high supercritical thermal power system shown in FIG. 18 differs from the fourth embodiment in that: the supercharger is an impeller type compressor 701, and the working mechanism 3 is set as a power turbine. 301, the power turbine 301 outputs power to the impeller compressor 701, and the high pressure zone of the impeller compressor 701, the combustion chamber 4, and the power turbine 301 is disposed in the boiler Within the mass chamber 2.

实施例 19  Example 19

如图 20所示的低熵混燃高超临界热动力系统， 包括锅炉 1和作功机构 3， 所述锅炉 1的气体工质出口与所述作功机构 3的气体工质入口连通，调整所述 锅炉 1的液体工质入口的流量和压力，调整所述锅炉 1的气体工质出口处的流 量，调整所述锅炉 1的加热强度使所述锅炉 1的气体工质出口处的气体工质压 力大于 30. 5MPa、 31 MPa、 31 . 5MPa、 32MPa、 32. 5MPa、 33MPa、 33. 5MPa、 34MPa、 34. 5MPa、 35MPa、 35. 5MPa、 36MPa、 36. 5MPa、 37MPa、 37. 5MPa、 38MPa、 38. 5MPa、 39MPa、 39. 5MPa或大于 40MPa， 使所述锅炉 1的气体工质出口处的气体工质温 度高于 880Κ、 885Κ、 890Κ、 895Κ、 900Κ、 905Κ、 910Κ、 915Κ、 920Κ、 925Κ、 930Κ、 935Κ、 940Κ、 945Κ、 950Κ、 955Κ、 960Κ、 965Κ、 970Κ、 975Κ、 980Κ、 985Κ、 990Κ、 995Κ或高于 1000Κ,并使所述锅炉 1的气体工质出口处的气体工质的温度和压 力符合类绝热关系。 显然， 本发明不限于以上实施例， 根据本领域的公知技术和本发明所公开 的技术方案， 可以推导出或联想出许多变型方案， 所有这些变型方案， 也应认 为是本发明的保护范围。 The low-energy co-firing high-supercritical thermal power system shown in FIG. 20 includes a boiler 1 and a work mechanism 3, and the gas working fluid outlet of the boiler 1 communicates with the gas working medium inlet of the working mechanism 3, and the adjustment center The flow rate and pressure of the liquid working fluid inlet of the boiler 1 are adjusted, the flow rate at the gas working fluid outlet of the boiler 1 is adjusted, and the heating intensity of the boiler 1 is adjusted to make the gas working fluid at the gas working outlet of the boiler 1 5MPa, 36MPa, 37MPa, 37MPa, 36MPa, 36MPa, 37MPa, 36MPa, 36MPa, 37MPa, 37. 5MPa, 38MPa, 3MPa, 32MPa, 32. 5MPa, 32MPa, 32. 5MPa, 33MPa, 33. 5MPa, 34MPa, 34. 5MPa, 35MPa, 35. 5MPa, 36MPa, 36. 5MPa, 37MPa, 37. 5MPa, 38MPa 38. 5MPa, 39MPa, 39. 5MPa or more than 40MPa, so that the gas working temperature at the gas working outlet of the boiler 1 is higher than 880Κ, 885Κ, 890Κ, 895Κ, 900Κ, 905Κ, 910Κ, 915Κ, 920Κ, 925Κ, 930Κ, 935Κ, 940Κ, 945Κ, 950Κ, 955Κ, 960Κ, 965Κ, 970Κ, 975Κ, 980Κ, 985Κ, 990Κ, 995Κ or higher than 1000Κ, and make the working fluid at the gas working outlet of the boiler 1 Temperature and pressure in line with adiabatic Department. It is apparent that the present invention is not limited to the above embodiments, and many variations can be derived or conceived according to the well-known art in the art and the technical solutions disclosed in the present invention, and all such modifications are also considered to be the scope of protection of the present invention.

Claims

权 利 要 求 Rights request 1、一种低熵混燃高超临界热动力系统， 包括锅炉（1 )、 锅炉工质腔（2)、 作功机构 （3) 和燃烧室 （4)， 其特征在于： 所述燃烧室 （4) 上设有燃烧室工 质入口（401 )、燃烧室工质出口（402)、氧化剂入口（403)和燃料入口（404)， 氧化剂源 （5)经氧化剂高压供送系统（501 ) 与所述氧化剂入口 （403)连通， 燃料源 （6) 经燃料高压供送系统 （601 ) 与所述燃料入口 （404) 连通， 所述 燃烧室 （4) 全部设置在所述锅炉工质腔 （2) 内或所述燃烧室 （4) 部分设置 在所述锅炉工质腔 （2) 内或所述燃烧室 （4) 设置在所述锅炉 （1 ) 外；  1. A low-entropy co-firing high-supercritical thermodynamic system comprising a boiler (1), a boiler working chamber (2), a working mechanism (3) and a combustion chamber (4), characterized in that: the combustion chamber ( 4) a combustion chamber inlet (401), a combustion chamber outlet (402), an oxidant inlet (403) and a fuel inlet (404), and an oxidant source (5) via an oxidant high pressure supply system (501) The oxidant inlet (403) is in communication, and the fuel source (6) is in communication with the fuel inlet (404) via a fuel high pressure supply system (601), and the combustion chamber (4) is all disposed in the boiler working chamber ( 2) inside or the combustion chamber (4) is partially disposed in the boiler working chamber (2) or the combustion chamber (4) is disposed outside the boiler (1); 所述锅炉工质腔（2) 与所述燃烧室工质入口 （401 ) 连通， 所述燃烧室工 质出口 （402) 与所述作功机构 （3) 连通。  The boiler working chamber (2) is in communication with the combustion chamber inlet (401), and the combustion chamber outlet (402) is in communication with the working mechanism (3). 2、 根据权利要求 1 所述低熵混燃高超临界热动力系统， 其特征在于： 在 所述燃烧室工质入口 （401 )处设增压器 （7)， 所述增压器 （7) 对所述燃烧室 2. The low-entropy co-firing high-supercritical thermal power system according to claim 1, wherein: a supercharger (7) is provided at the combustion chamber inlet (401), and the supercharger (7) For the combustion chamber (4) 内的工质增压。 (4) The working fluid is pressurized. 3、 根据权利要求 1 所述低熵混燃高超临界热动力系统， 其特征在于： 所 述作功机构 （3) 与发电机 （9) 连接。  3. The low entropy co-firing high supercritical thermal power system according to claim 1, characterized in that: said working mechanism (3) is connected to the generator (9). 4、 根据权利要求 1 所述低熵混燃高超临界热动力系统， 其特征在于： 所 述低熵混燃高超临界热动力系统还包括冷凝冷却器 （10)， 所述作功机构 （3) 的工质出口与所述冷凝冷却器（10) 的被冷却流体入口连通， 所述冷凝冷却器 4. The low entropy co-firing high supercritical thermal power system according to claim 1, wherein: said low entropy co-firing high supercritical thermal power system further comprises a condensing cooler (10), said working mechanism (3) a working fluid outlet is in communication with a cooled fluid inlet of the condensing cooler (10), the condensing cooler ( 10) 的被冷却流体出口与液体高压回流泵（11 ) 的入口连通， 所述液体高压 回流泵（11 )的出口与所述锅炉工质腔（2)连通，在所述液体高压回流泵（11 ) 的作用下被所述冷凝冷却器（10)液化的工质回流到所述锅炉工质腔（2) 内。 The cooled fluid outlet of (10) is in communication with the inlet of the liquid high pressure return pump (11), the outlet of the liquid high pressure return pump (11) is in communication with the boiler working chamber (2), in the liquid high pressure return pump The working fluid liquefied by the condensing cooler (10) under the action of (11) is returned to the working fluid chamber (2) of the boiler. 5、 根据权利要求 2所述低熵混燃高超临界热动力系统， 其特征在于： 在 所述燃烧室工质出口 （402)处设动力单元（8)， 所述动力单元（8)对所述增 压器 （7) 输出动力。  5. The low-entropy co-firing high-supercritical thermal power system according to claim 2, wherein: a power unit (8) is disposed at the combustion chamber outlet (402), and the power unit (8) is opposite The supercharger (7) outputs power. 6、 根据权利要求 2所述的低熵混燃高超临界热动力系统， 其特征在于： 所述作功机构 （3) 对所述增压器 （7)输出动力。  The low-entropy co-firing high-supercritical thermodynamic system according to claim 2, characterized in that the work mechanism (3) outputs power to the supercharger (7). 7、 根据权利要求 6所述低熵混燃高超临界热动力系统， 其特征在于： 在 所述冷凝冷却器 （10) 的被冷却流体出口处设不凝气体导出口 （12)。 7. The low entropy co-firing high supercritical thermal power system according to claim 6, characterized in that a non-condensable gas outlet (12) is provided at the outlet of the condensed cooler (10) to be cooled. 8、 根据权利要求 6所述低熵混燃高超临界热动力系统， 其特征在于： 在 所述冷凝冷却器 （10) 的被冷却流体入口处和 /或在所述冷凝冷却器 （10) 的 被冷却流体出口处设余量工质导出口 （13)。 8. The low-entropy co-firing high-supercritical thermodynamic system according to claim 6, characterized by: at the inlet of the condensed cooler (10) and/or at the condensing cooler (10) A residual working fluid outlet (13) is provided at the outlet of the cooling fluid. 9、 根据权利要求 3所述低熵混燃高超临界热动力系统， 其特征在于： 所 述动力单元 （8) 与所述増压器 （7) 同轴设置。  9. The low entropy co-firing high supercritical thermal power system according to claim 3, characterized in that: said power unit (8) is disposed coaxially with said squeezing device (7). 10、 根据权利要求 4所述低熵混燃高超临界热动力系统， 其特征在于： 所 述作功机构 （3) 与所述增压器 （7) 同轴设置。  10. The low entropy co-firing high supercritical thermal power system according to claim 4, characterized in that: said working mechanism (3) is coaxially arranged with said supercharger (7). 11、 根据权利要求 1所述低熵混燃高超临界热动力系统， 其特征在于： 所 述作功机构 （3) 设为动力透平 （301 )或设为活塞式作功机构 （302)。  A low-entropy co-firing high-supercritical thermal power system according to claim 1, characterized in that said working mechanism (3) is set as a power turbine (301) or as a piston type working mechanism (302). 12、 根据权利要求 2所述低熵混燃高超临界热动力系统， 其特征在于： 所 述增压器 （7) 设为叶轮式压縮机 （701 ) 或活塞式压縮机 （702)。  12. The low entropy co-firing high supercritical thermal power system according to claim 2, wherein: said supercharger (7) is an impeller compressor (701) or a piston compressor (702). 13、 根据权利要求 3所述低熵混燃高超临界热动力系统， 其特征在于： 所 述动力单元 （8) 设为叶轮式动力单元 （801 ) 或活塞式动力单元。  13. The low entropy co-firing high supercritical thermal power system according to claim 3, wherein: the power unit (8) is an impeller type power unit (801) or a piston type power unit. 14、 根据权利要求 1所述低熵混燃高超临界热动力系统， 其特征在于： 所 述燃料源 （6) 内的燃料设为碳氢化合物、 碳氢氧化合物或设为氢气。  The low entropy co-firing high supercritical thermal power system according to claim 1, wherein the fuel in the fuel source (6) is a hydrocarbon, a carbon oxyhydroxide or a hydrogen gas. 15、 根据权利要求 1所述低熵混燃高超临界热动力系统， 其特征在于： 所 述氧化剂源 （5) 内的氧化剂设为液氧、 高压气态氧或过氧化氢水溶液。  The low entropy co-firing high supercritical thermal power system according to claim 1, wherein the oxidant in the oxidant source (5) is set to be liquid oxygen, high pressure gaseous oxygen or aqueous hydrogen peroxide solution. 16、 根据权利要求 1所述低熵混燃高超临界热动力系统， 其特征在于： 所 述燃料源 （6) 内的燃料设为金属燃料， 在所述燃烧室 （4) 内和 /或在所述作 功机构（3)前和 /或在所述作功机构（3) 后设工质金属化合物分离器 （405)。  16. The low entropy co-firing high supercritical thermal power system according to claim 1, wherein: the fuel in the fuel source (6) is set to be a metal fuel, in the combustion chamber (4) and/or in A working metal compound separator (405) is disposed before the working mechanism (3) and/or after the working mechanism (3). 17、 根据权利要求 6所述低熵混燃高超临界热动力系统， 其特征在于： 所 述冷凝冷却器 （10) 设为晾水塔 （100)。  17. The low entropy co-firing high supercritical thermal power system according to claim 6, wherein: said condensing cooler (10) is set as a water drying tower (100). 18、 根据权利要求 1所述低熵混燃高超临界热动力系统， 其特征在于： 在 所述作功机构 （3) 的工质出口处设回热器 （200)。  18. The low entropy co-firing high supercritical thermal power system according to claim 1, wherein: a regenerator (200) is disposed at a working fluid outlet of said working mechanism (3). 19、 根据权利要求 2所述低熵混燃高超临界热动力系统， 其特征在于： 所 述增压器（ 7 )设为叶轮式压縮机（ 701 )，所述作功机构（ 3 )设为动力透平（ 301 )， 所述动力透平 （301 )对所述叶轮式压縮机 （701 )输出动力， 所述叶轮式压縮 机 （701 )、 所述燃烧室 （4)和所述动力透平 （301 ) 的高压区设在所述锅炉工 质腔 （2) 内。 19. The low-entropy co-firing high-supercritical thermal power system according to claim 2, wherein: said supercharger (7) is an impeller type compressor (701), and said working mechanism (3) is provided. a power turbine (301), the power turbine (301) outputs power to the impeller compressor (701), the impeller compressor (701), the combustion chamber (4), and The high pressure zone of the power turbine (301) is located in the boiler worker Inside the mass chamber (2). 20、 根据权利要求 1所述低熵混燃高超临界热动力系统， 其特征在于： 所 述燃烧室工质入口 （401 )设为冲压发动机的进气口 （4001 )， 所述燃烧室 （4) 设为冲压发动机燃烧室 （400)， 所述燃烧室工质出口 （402) 设为冲压发动机 扩压区气体出口 （4002)。  20. The low-entropy co-firing high-supercritical thermal power system according to claim 1, wherein: the combustion chamber working inlet (401) is set as an intake port (4001) of the ramjet, and the combustion chamber (4) A ramjet combustion chamber (400) is provided, and the combustion chamber working outlet (402) is set as a ramjet diffuser gas outlet (4002). 21、 一种提高权利要求 1至 20任意之一所述低熵混燃高超临界热动力系 统效率和环保性的方法， 其特征在于： 即将开始作功的气体工质的温度和压力 符合类绝热关系。  A method for improving the efficiency and environmental friendliness of a low-entropy co-firing high-supercritical thermodynamic system according to any one of claims 1 to 20, characterized in that: the temperature and pressure of the gaseous working fluid to be started to work are in accordance with the adiabatic relationship. 22、 一种低熵混燃高超临界热动力系统， 包括锅炉 （1 )和作功机构（3)， 其特征在于： 所述锅炉 （1 ) 的气体工质出口与所述作功机构 （3) 的气体工质 入口连通， 调整所述锅炉 （1 ) 的液体工质入口的流量和压力， 调整所述锅炉 22. A low-entropy co-firing high-supercritical thermodynamic system comprising a boiler (1) and a work mechanism (3), characterized in that: a gas working fluid outlet of the boiler (1) and the working mechanism (3) The gas working medium inlet is connected, adjusting the flow rate and pressure of the liquid working inlet of the boiler (1), and adjusting the boiler ( 1 )的气体工质出口处的流量，调整所述锅炉（1 )的加热强度使所述锅炉（1 ) 的气体工质出口处的气体工质压力大于 30. 5MPa， 使所述锅炉（1 )的气体工质 出口处的气体工质温度高于 880K。 The pressure of the gas working fluid at the gas working outlet of the boiler (1) is greater than 30. 5 MPa, so that the boiler ( 1) The gas working fluid at the outlet of the gas working fluid is higher than 880K. 23、 一种提高权利要求 22所述低熵混燃高超临界热动力系统效率和环保 性的方法， 其特征在于： 所述锅炉 （1 ) 的气体工质出口处的气体工质的温度 和压力符合类绝热关系。  23. A method of improving the efficiency and environmental friendliness of a low entropy co-firing high supercritical thermal power system of claim 22, characterized by: temperature and pressure of a gaseous working fluid at a gas working fluid outlet of said boiler (1) Meet the class of adiabatic relationship.
PCT/CN2011/000921 2010-06-01 2011-05-31 Low-entropy mixed combustion ultra-supercritical thermal power system Ceased WO2011150676A1 (en)

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