WO2015149448A1 - 一种原动机的半闭式正时定容热力循环方法及系统 - Google Patents

一种原动机的半闭式正时定容热力循环方法及系统 Download PDF

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Publication number
WO2015149448A1
WO2015149448A1 PCT/CN2014/082324 CN2014082324W WO2015149448A1 WO 2015149448 A1 WO2015149448 A1 WO 2015149448A1 CN 2014082324 W CN2014082324 W CN 2014082324W WO 2015149448 A1 WO2015149448 A1 WO 2015149448A1
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Prior art keywords
constant volume
type
working fluid
combustion
compression
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PCT/CN2014/082324
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English (en)
French (fr)
Inventor
张孔明
梁世希
金则兵
王科
张帆
朱建明
谢昕
周松景
周群
王彦超
姜进
刘敬平
廖诚
杨汉乾
Original Assignee
绿能高科集团有限公司
北京绿能高科天然气应用技术研究院有限公司
河南中原绿能高科有限责任公司
山东绿能燃气实业有限责任公司
包头中援绿能天然气有限公司
河南绿能融创燃气有限公司
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Publication of WO2015149448A1 publication Critical patent/WO2015149448A1/zh

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C3/00—Gas-turbine plants characterised by the use of combustion products as the working fluid
    • F02C3/04—Gas-turbine plants characterised by the use of combustion products as the working fluid having a turbine driving a compressor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C1/00—Gas-turbine plants characterised by the use of hot gases or unheated pressurised gases, as the working fluid
    • F02C1/04—Gas-turbine plants characterised by the use of hot gases or unheated pressurised gases, as the working fluid the working fluid being heated indirectly
    • F02C1/08—Semi-closed cycles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C5/00—Gas-turbine plants characterised by the working fluid being generated by intermittent combustion
    • F02C5/02—Gas-turbine plants characterised by the working fluid being generated by intermittent combustion characterised by the arrangement of the combustion chamber in the chamber in the plant
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C7/00—Features, components parts, details or accessories, not provided for in, or of interest apart form groups F02C1/00 - F02C6/00; Air intakes for jet-propulsion plants
    • F02C7/08—Heating air supply before combustion, e.g. by exhaust gases
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • the present invention relates to a prime mover, and more particularly to a semi-closed timing constant volume thermal cycle method and system for a prime mover.
  • the thermal cycle of internal combustion engine applications mainly includes Diesel cycle, Otto cycle, Atkinson cycle, Miller cycle, Brayton cycle, etc., among which Diesel cycle, Otto cycle, Atkinson cycle, Miller cycle mainly It should be on a conventional reciprocating piston internal combustion engine, and the Brayton cycle is mainly applied to a gas turbine.
  • Diesel cycle The large compression ratio is its advantage, but adiabatic compression, isobaric heating, and isovolumetric exotherm are its disadvantages.
  • the P-V indicator diagram is shown in Figure 2.
  • the theoretical thermal efficiency calculation formula is:
  • s is the compression ratio; is the heating expansion ratio; k is the specific heat ratio.
  • the conventional reciprocating piston internal combustion engine reuses the energy of the exhaust gas, and generally adopts an exhaust gas turbocharged method, such as a supercharged diesel engine or a supercharged gasoline engine.
  • an exhaust gas turbocharged method such as a supercharged diesel engine or a supercharged gasoline engine.
  • the use of exhaust gas turbocharging to obtain energy is not directly applied to the thermal system cycle work, but to increase the intake pressure, increase Inlet density, to reduce pumping losses and increase power density per unit volume to increase thermal efficiency.
  • the exhaust gas energy recovery uses a vane turbine and an impeller compressor, which is low in efficiency, high in speed and high in noise. Again, the exhaust gas still has a certain amount of energy after passing through the turbine, ie the temperature and pressure are not fully utilized.
  • the traditional reciprocating piston internal combustion engine has a high local combustion temperature (local maximum temperature up to 2800K), uneven oil and gas mixing, short main combustion process (30°CA), piston ring leakage, piston ring clearance and volume quenching. For other reasons, it causes high emissions on N0x, PM (on particulates, on diesel), HC and CO (on gasoline engines).
  • HCCI Homogeneous Compression Ignition
  • a gas turbine is a rotary power machine that uses a continuously flowing gas as a working fluid to convert thermal energy into mechanical energy.
  • gas turbine cycle consisting of three major components: compressor, constant volume combustion chamber and gas turbine is called simple cycle.
  • Most gas turbines use a simple circulation scheme. Because of its simple structure, it can reflect the unique advantages of gas turbines such as small size, light weight, fast start-up, and basically no need for cooling water.
  • the simple cycle of the gas turbine has a high discharge temperature (around 900 °C), resulting in a low thermal efficiency.
  • the pressurization is relatively low, the constant pressure combustion is employed, and the equal capacity is low, resulting in low thermal efficiency.
  • the exhaust gas passing through the gas turbine still has a certain energy, that is, the temperature and pressure are not fully utilized. Again, the gas turbine has low thermal efficiency in the event of a load change.
  • thermodynamic cycle of external combustion engine applications mainly includes Stirling cycle, Rankine cycle, Carnot cycle and the like. It takes a while for the Stirling cycle to respond to changes in the heat of the cylinder, which has a large heat loss and low thermal efficiency.
  • a steam turbine is a kind of high-heat efficiency thermal system. Its working principle is to draw the kinetic energy of water vapor (formed by heating water) into the kinetic energy of turbine rotation. It is the Rankine cycle.
  • Typical application of heat engines About 80% of the world's electricity is generated by turbine steam engines, which are especially suitable for thermal power generation and nuclear power generation.
  • the heating temperature in the heat engine should be increased as much as possible and the heat removal temperature should be lowered.
  • the thermal cycle of the steam turbine and the gas turbine cannot meet the above requirements well, and a combined cycle of the gas-steam turbine is proposed.
  • a multi-stage thermoelectric and heating system is proposed.
  • such thermal systems are large and complex in structure and should not be directly applied to vehicles.
  • the rotary engine directly converts the combustion expansion force of the combustible gas into drive torque.
  • the rotary engine eliminates the linear motion of the reciprocating engine. It does not need to use the crank slider mechanism and the valve timing mechanism.
  • the rotor rotates every revolution. Once, it has the advantage of high power rise and good adaptability to changing conditions compared with the general four-stroke engine that performs work twice every two revolutions. At the same power, the rotor engine has a small size, compact structure, small size, light weight, low vibration and noise, high inflation efficiency, high speed performance and great advantages. However, it also has fatal weaknesses, large sealing surface, poor working environment, difficulty in sealing, lubrication and cooling, fast wear of seals, large loss of leakage, high thermal stress of piston, poor reliability and low service life.
  • the Chinese patent CN102032049 A and the European patent EP 2578942 A2 disclose a method and system involving carbon sequestration and an engine, which are mainly applied to carbon sequestration, but do not adopt multi-stage moderate isothermal compression and voltage stabilization.
  • the pressure regulating and countercurrent heat exchange processes, in particular, the system and method do not employ a positive constant volume combustion and a specific working fluid closed cycle.
  • the system does not use the oxidant supply device, the system needs to draw in fresh air from the outside, and it is difficult to change the oxygen concentration of the mixture in the constant-capacity combustion chamber.
  • the gas such as nitrogen other than carbon dioxide is discharged into the environment. Therefore, the system does not make full use of the helium in the exhaust gas, nor can it be used in an oxygen-deficient environment such as water.
  • Chinese patent CN 102374026 A discloses a closed-loop Brayton cycle system and method, which comprises three subsystems, namely an open thermal energy generation system, a thermal power conversion loop system and a cooling loop system, and the thermal conversion system passes a heat
  • the exchanger transfers heat to the thermal conversion system. It takes a lot of space to realize the whole system. More importantly, the system uses steam power instead of gas power to work. It belongs to the external combustion type heat engine, and the heat energy generation subsystem does not recycle the working fluid, but directly discharges it to the atmosphere. .
  • Chinese patent CN 102454481 A discloses a combined cycle power plant of a carbon dioxide collection system, which mainly comprises a carbon dioxide collecting device, a heat recovery steam generator and a combustion exhaust gas recirculation device, which is not suitable for working under water and anoxic environment. More importantly, the system does not include oxygen supply, timing constant volume combustion and closed cycle of specific working fluids.
  • Chinese patent CN1138135A discloses an isothermal compression, an approximately constant volume combustion, an adiabatic full expansion and an isothermal heat release cycle, but the patent also does not employ a positive constant volume combustion and a specific working fluid closed cycle.
  • U.S. Patent No. PCT/US00/03711 discloses a method and apparatus for implementing turbine power, which mainly comprises a power turbine, a combustion exhaust heat exchange utilization, and a fuel and water heating conversion reaction device, wherein part of the combustion exhaust gas is recycled, but not specific.
  • the quality is always circulated, and the process of decarburization, isothermal compression and oxygen supply and the constant volumetric combustion are not carried out.
  • the system is also not suitable for operation under water and anoxic environment.
  • the fuel combustion efficiency, the heat work conversion efficiency, the power consumption of the compression process, the expansion work of the expansion process, the exhaust gas temperature, and the emission of pollutants should be reduced as much as possible.
  • the heating or combustion process can not achieve true constant-volume combustion, the thermal power conversion efficiency is not high, it is difficult to achieve full expansion work, no specific Closed circulation of working fluids, it is also impossible to achieve long-term clean combustion. Therefore, designing a thermal cycle and system with high thermal efficiency, low emission pollution, soft work, low exhaust noise, and low external suction and discharge of working fluids is of great significance for the realization of energy saving and emission reduction of internal combustion engines. It is also important to work or a power machine in an anoxic environment.
  • the present invention provides a semi-closed timing of the prime mover.
  • the heat capacity circulation method and system, the cycle process includes six process inherent processes, namely multi-stage compression interstage cooling process, countercurrent heat transfer process, timing constant volume combustion process, adiabatic expansion process, post-cooling process and carbon dioxide
  • the water removal process in some embodiments, also includes ancillary processes such as a regulated pressure regulation process and an oxidant and fuel mixing process.
  • the specific technical solution of the present invention is: a semi-closed timing constant volume thermal circulation method of a prime mover, wherein the thermal circulation method rotates at an angle of 360° or a two-stroke reciprocating engine with a rotor rotation angle of 360° or a two-stroke reciprocating engine Or the output shaft rotation angle of the four-stroke reciprocating engine is 720°, which is a cycle. It adopts two types of working fluids.
  • the first type of working fluid is the working medium that participates in the whole process of the thermal cycle. After combustion in the constant volume combustion chamber, it works through the expander.
  • the second type of working fluid is generated by the oxidant and fuel added before the constant-capacity combustion process, and participates in the timing constant-volume combustion process.
  • the thermal expansion process, the countercurrent heat transfer process, the post-cooling process, and finally the working fluid removed during the carbon dioxide and water removal process, the working fluid is no longer involved in the next thermodynamic cycle:
  • Step 1 Perform a multi-stage compression interstage cooling process: In this process, the first type of working medium is subjected to multi-stage compression, and the interstage cooling is performed to reduce the compression power consumption, and the first type of working medium compression end pressure is regulated. Pressure regulation
  • Step 2 Performing a countercurrent heat exchange process: In the process, the first type of working medium and the second type of work after the first type of working fluid after the pressure regulation and pressure recovery recovers the last thermal expansion and expansion work before entering the constant volume combustion chamber The quality of the enthalpy, directly participate in the heat cycle after the heat gain, in order to improve the initial temperature of the first type of working fluid and the second type of working fluid in the thermal cycle of the constant volume combustion chamber;
  • Step 3 Perform a positive constant volume combustion process:
  • the first type of working medium enters the constant volume combustion chamber after the countercurrent heat exchange process, and the oxidant supply device and the fuel supply device inject the oxidant and the fuel through the mixing injector
  • the constant volume combustion chamber is started and the constant volume combustion is started, and the volume of the constant volume combustion chamber is unchanged;
  • Step 4 Perform adiabatic expansion process: The process is independent of the multistage compression interstage cooling process and the timing constant volume combustion process. The working fluid discharged from the constant volume combustion chamber is fully expanded to output work, and the expansion ratio of the adiabatic expansion process is greater than the compression process. Boost ratio
  • Step 5 Perform a post-cooling process: In the process, the first type of working medium and the second type of working medium after expansion work enter the aftercooler through the countercurrent heat exchange device, and further cooled to ambient temperature;
  • Step 6 Perform carbon dioxide and water removal process: In this process, the carbon dioxide and water produced by the constant-capacity combustion process are removed, and the remaining working fluid continues to participate in the next thermal cycle.
  • the present invention also provides a semi-closed timing constant volume thermal circulation system of a prime mover, comprising: a multi-stage compression interstage cooling device, a constant voltage regulating device, a countercurrent heat exchange device, and an oxidant supply device , fuel supply device, hybrid injector, timing constant volume burner, expander, aftercooler, carbon dioxide and water removal device, wherein the multi-stage compression interstage cooling device compresses and intercools the working medium, and stabilizes
  • the pressure regulating device is connected to the pipeline. It is connected with the final stage compressor of the multistage compression interstage cooling device, and the countercurrent heat exchange device is connected to the constant voltage regulating device via the connecting pipe Pu, and the timing constant volume burner is connected to the countercurrent heat exchange device via the connecting pipe P12.
  • the oxidant supply device and the fuel supply device mix and combust the oxidant and the fuel through the mixing injector into the timing constant volume burner to generate carbon dioxide and water in the second type of working medium; the timing constant volume burner passes through the connecting pipe Road expander connected; P 2 is connected via the connection line after the countercurrent heat means work in the expander.
  • the first type of working medium enters the voltage regulating and regulating device after the multistage compression interstage cooling device, and the first type of working fluid flowing out from the voltage regulating and regulating device enters the countercurrent heat exchange device and enters the timing constant volume combustion.
  • the oxidant and the fuel provided by the oxidant supply device and the fuel supply device are injected into the timing constant-volume burner through the mixing ejector to be combusted to produce a second type of working medium, and enter the expander expansion work together with the first type of working medium.
  • the cycle thermal efficiency of the present invention mainly depends on the maximum combustion temperature and the external ambient temperature. Under the same conditions, the higher the maximum combustion temperature, the higher the heat source temperature, the higher the cycle thermal efficiency; the other the conditions are the same, the lower the external ambient temperature, ie the lower the cold source temperature, the thermal efficiency of the cycle The higher the rule is similar to Carnot's law, the closer to the Carnot cycle thermal efficiency (heat engine limit thermal efficiency) Rate).
  • the multistage compression interstage cooling process has a boost ratio of between 2.0 and 3.0.
  • the compression device can be operated in a high efficiency zone, and the interstage cooling process reduces the temperature of the fresh working fluid entering the compression process.
  • the compression process is approached to isothermal compression, reducing the compression effort of the compression device.
  • the compression device With independent oxygen supply, the compression device only needs to compress the first type of working fluid, which reduces the flow rate of the compressor, without compressing the oxidant during the constant pressure combustion process.
  • the oxidant of the combustion process is supplied by a set of independent oxidants. The device provides, thus reducing the compression work for the entire cycle, increasing the system output work without the need to draw in fresh air from the outside environment.
  • the working fluid that does not participate in combustion in the first type of working fluid in the thermal cycle of the present invention can be applied with inert gas, and the controlled working medium does not contain nitrogen, and the combustion temperature is higher than that of the conventional thermal system, as long as the control does not exceed the constant volume combustion.
  • the extreme temperature that the chamber can withstand, soot and HC can be burned without generating N0x. It is a clean and efficient combustion method, and this kind of working medium has a higher specific heat ratio, which can improve the thermal efficiency of the whole system. .
  • thermodynamic cycle of the present invention The post-cooling process is adopted in the thermodynamic cycle of the present invention, and the heat source working fluid (the working fluid from the expansion work) is further cooled from the counter-current heat exchange process, which helps to remove carbon dioxide and water generated by the combustion process, and reduces the discharge. Gas back pressure and increased expansion ratio, as well as reduced work in the compression process.
  • the thermal system is semi-closed, and does not need to directly discharge the combustion exhaust gas to the environment.
  • the invention reduces the heat taken away from the combustion exhaust gas, and recovers the promotion of the combustion exhaust gas.
  • the work, as well as the recovery of the amount of air leakage during the compression process and the combustion process, avoids leakage losses, thereby ensuring high thermal efficiency of the entire system.
  • the combustion process of the thermal system of the invention has small pressure fluctuation and soft work; after the work, the first type of working medium accounts for a large proportion and can be recycled, the second type of working medium is removed, no direct exhaust, no exhaust noise.
  • Figure 1 is an Otto cycle P-v diagram
  • Figure 2 is a Diesel cycle P-v diagram
  • Figure 3 is a Brayton cycle P-v diagram
  • FIG. 4 is a schematic diagram of a thermodynamic cycle according to an embodiment of the present invention
  • FIG. 5 is a schematic structural diagram of main components of a system according to an embodiment of the present invention
  • FIG. 5 is a schematic structural diagram of main components of a system according to an embodiment of the present invention
  • FIG. 6 is a schematic diagram of main pipeline components of a system according to an embodiment of the present invention.
  • FIG. 7 is a schematic structural view of a system oxidant supply device according to an embodiment of the present invention.
  • Figure 8 is a schematic view of a rotor type compressor of the present invention.
  • Figure 9 is a schematic view of the timing constant volume combustion system of the present invention.
  • Figure 10 is a schematic view of a timing constant volume burner of the present invention.
  • 1-positive constant volume burner 111-combustion chamber grille, 112-inlet, 113-exhaust, 114-combustion chamber block-type insulated inner wall, 14-fuel injector, 141-jet Injector, 2-expander, 3-counter-flow heat exchanger, 4-aftercooler, 5-carbon dioxide and water removal unit, 6-stage compressor, 61-stage compression inlet, 62-- Stage compression exhaust port, 63-second compressed air inlet, 64-second compressed exhaust port, 65-three-stage compressed air inlet, 66-three-stage compressed exhaust port, 67-compressor inner chamber rotor, 68-compressor rotary drive shaft, 69-compressor linkage, 7-stage intercooler, 8-stage compressor, 9-stage intercooler, 10-third compressor, 11-regulation Pressure device, 12-oxidant supply device, 1201-oxygen storage tank, 1202-pressure reducing valve, 1203-flow control valve, 1204-check valve, 1205-pressure gauge, 1206-connecting pipe, 1207-
  • the invention provides a semi-closed timing constant volume thermodynamic cycle method of a prime mover, wherein the thermodynamic cycle method uses a rotor rotation angle of a rotor engine 360° or a two-stroke reciprocating engine output shaft rotation angle 360° or four stroke reciprocating
  • the output shaft rotation angle of the engine is 720°, which is a cycle. It uses two types of working fluids.
  • the first type of working fluid is the working medium that participates in the whole process of the thermodynamic cycle. After combustion in the constant volume combustion chamber, it works through the expander. After the work is completed, the work is completed.
  • the second type of working fluid is timing constant combustion
  • the oxidant and fuel added before the burning process, and participate in the timing of the constant volume combustion process, the adiabatic expansion process, the countercurrent heat transfer process, the post-cooling process, and finally the working fluid removed during the carbon dioxide and water removal process, The working fluid is no longer involved in the next thermodynamic cycle:
  • Step 1 Perform a multi-stage compression interstage cooling process: In this process, the first type of working medium is subjected to multi-stage compression, and the interstage cooling is performed to reduce the compression power consumption, and the first type of working medium compression end pressure is regulated. Pressure regulation
  • the multistage compression interstage cooling process is to achieve near isothermal compression, the interstage cooling is used to reduce the next compression work, and the working fluid flowing through the compressor does not contain oxidant, further reducing the compression work;
  • the final pressure of compression affects the initial state pressure of the combustion chamber in the constant volume combustion chamber.
  • the device responsible for compression is independent of the constant volume burner, not the same set.
  • the voltage regulation and voltage regulation process is performed, the pressure wave generated by the compression process is eliminated, and the stable pressure is maintained, and the intake air amount entering the constant volume combustion chamber can be adjusted according to the change of the working condition.
  • Step 2 Performing a countercurrent heat exchange process: In the process, the first type of working medium and the second type of work after the first type of working fluid after the pressure regulation and pressure recovery recovers the last thermal expansion and expansion work before entering the constant volume combustion chamber The quality of the enthalpy, directly participate in the heat cycle after the heat gain, in order to improve the initial temperature of the first type of working fluid and the second type of working fluid in the thermal cycle of the constant volume combustion chamber;
  • the first type of working fluid after the completion of the adiabatic expansion process after the completion of the multistage compression interstage cooling process and the steady voltage regulation process is increased at a lower temperature.
  • the second type of working fluid is exothermic, the waste heat is recycled, and the heat utilization rate is improved.
  • Step 3 Perform a positive constant volume combustion process: In the process, the first type of working medium enters the constant volume combustion chamber after the countercurrent heat exchange process, and the oxidant supply device and the fuel supply device spray the oxidant and the fuel through the mixing injector into the constant volume The combustion chamber starts to form a constant volume combustion, and the volume of the constant volume combustion chamber remains unchanged;
  • the thermal system of the present invention performs positive-time constant-volume combustion in a positive-time constant-capacity combustion process
  • the positive-time constant-volume burner is a special-form combustion generating device based on constant-time constant volume.
  • the compression process, the expansion process and the combustion process are respectively completed in separate devices, and are interconnected by the timing device 15, and the working medium can realize a long-time constant-capacity combustion in the constant-capacity combustion chamber, until the fuel is fully burned out.
  • the high temperature and high pressure working medium is discharged into the constant volume combustion chamber and enters the expander 2. Since the oxidant and the fuel are independently supplied, the grid is filled in the combustion chamber for multi-point ignition.
  • the oxidant and the first type of circulating working medium are firstly mixed uniformly to become a homogeneous mixed gas, and homogeneous low-temperature lean combustion is achieved in the combustion process, and the combustion temperature is controlled at 1900-2100K. Effectively suppress the generation of harmful pollutants such as HC, C0, PM and NOx.
  • the oxidant is not mixed with the first type of circulating working medium, but is directly mixed with the fuel in the combustion chamber, and is combusted while being mixed, and high-temperature combustion is achieved during the combustion process.
  • the combustion temperature does not exceed the limit temperature that the constant volume combustion chamber can withstand, effectively suppressing the formation of PM, HC and CO, and no NOx formation. Therefore, the system can achieve the purpose of clean and efficient combustion.
  • Step 4 performing adiabatic expansion process: the process is not only independent of the multi-stage compression interstage cooling process and the timing constant volume combustion process, and the expansion ratio of the adiabatic expansion process is greater than the supercharging ratio of the compression process, and the purpose of fully expanding work can be achieved;
  • Step 5 Perform a post-cooling process: In the process, the first type of working medium and the second type of working medium after expansion work enter the aftercooler through the countercurrent heat exchange device, and further cooled to ambient temperature;
  • Step 6 Perform carbon dioxide and water removal process: In this process, the carbon dioxide and water produced by the constant-capacity combustion process are removed, that is, the second type of working fluid is removed, and the remaining first type of working fluid continues to participate in the next heat.
  • the cycle the demand for fresh working fluids is small, which is conducive to closed and underwater environment operation.
  • the present invention provides a semi-closed timing constant volume internal combustion thermodynamic cycle method in which thermal energy is converted into mechanical energy (work).
  • the main feature is that the heating mode is that the working fluid is firstly heated by the countercurrent heat exchange constant pressure, and then enters the constant volume combustion in the constant volume combustion chamber, and the residual heat after the expansion work is directly applied to the thermal power conversion.
  • the whole cycle is a cycle that is different from the existing cycle forms such as Otto cycle, Diesel cycle, mixed cycle and Stirling cycle.
  • the semi-closed timing constant volume internal combustion thermodynamic cycle of the invention realizes closed working fluid recirculation, and the first type of working medium retained by the process of removing carbon dioxide and water is returned to the multistage compression stage through the loop of the thermal system. During the cooling process, a semi-closed timing constant volume internal combustion thermodynamic cycle is completed, and then the above process is repeated.
  • thermodynamic cycle comprises two types of working fluids to participate in work. Since the whole system is provided with a circuit, it is particularly suitable for working with a relatively high specific single atom gas, such as helium in an inert gas. Etc., and the leakage generated during compression and expansion, energy can be recovered, thereby increasing the thermal efficiency of the entire thermal cycle.
  • the compression device does not need to compress the oxidant in the constant pressure combustion process, and the oxidant is provided by a set of independent oxidant supply devices, thereby reducing The compression work of the entire cycle.
  • thermodynamic cycle is shown in Figure 4.
  • abcdef is a multi-stage compression interstage cooling process, that is, a quasi-isothermal compression process
  • fg is a constant voltage regulation process
  • gh is a countercurrent heat transfer process I (countercurrent endothermic process)
  • h_i is a positive constant volume combustion process
  • i_j It is an adiabatic expansion process
  • jk is a countercurrent heat exchange process II (countercurrent exothermic process)
  • k-1 is a post-cooling process
  • 1-a is a carbon dioxide and water removal process.
  • the first type of working medium does not contain nitrogen, and the inert gas is used as its main component, and the working medium is below. Flow order to describe specific steps.
  • Step 1 Cool the three-stage compression stage
  • the first type of working medium pressure is increased to 2. 0-3. 0 times. After that, it enters the first-stage intercooler 7 through the connecting line P 6 22 to be cooled, and the working medium is in the state of point c, and the first isothermal compression is completed, as shown in the abc process in FIG.
  • Pa is the pressure of the working medium at the state point a, and the unit is MPa; the temperature at which the working medium is at the state point a, the unit is K.
  • T c T b -htelx (T b -T 0 )
  • P For the pressure of the working fluid at the state point c; htP 1 is the pressure loss of the working medium through the primary intercooler, Units of MPa; temperature state of the working fluid at point c in units of K; htel efficacy as a heat exchanger in the cooler t
  • the temperature for the external environment in ⁇ .
  • W i is the supercharged specific work of the first-stage compression process, and the unit is kj/kg.
  • w 2 c p(c) T c -c p(b) T b
  • W2 is the process specific work of the first-stage intercooling process, kj/kg; e P (b ), respectively, the working medium is at the state point Constant pressure specific heat of b and c, kJ/kg-Ko
  • the first type of working fluid enters the secondary compressor 8 through the connecting pipeline P 7 23 for the second pressurization.
  • the first type of working fluid pressure is increased to 2.0 ⁇ from the outlet pressure of the primary intercooler 7. 3.0 times, the working medium is in the point d state, and then enters the secondary intercooler 9 through the connecting pipe P s 24 to be cooled again, the working medium is in the point e state, and the second isothermal compression is completed, as shown in the cde process in FIG. 4 . .
  • Pd is the pressure of the working medium at the state point d
  • the unit is MPa
  • 2 is the supercharging ratio of the secondary compressor
  • the temperature is the K when the working medium is at the state point d
  • ⁇ 2 is the secondary compression
  • k is the specific heat ratio of the working fluid at the state point c.
  • T e T d -hte2x(T d -T 0 )
  • ⁇ is the pressure of the working medium at the state point e
  • ht P2 is the pressure loss of the working medium passing through the secondary intercooler, the unit is MPa
  • the temperature at the state point e, the unit is K
  • hte2 is the heat exchange efficiency of the primary intercooler.
  • W 4 is the process specific work of the secondary intercooling process, and the unit is kj/kg; (the pressure specific heat of the working medium at the state points d and e, respectively, in kJ/kg-K .
  • the first type of working fluid flowing out of the secondary intercooler 9 enters the third stage compressor 10 through the connecting line P 9 25 for the third pressurization, and the pressure of the first type of working fluid is further increased, which is two
  • the outlet pressure of the stage intercooler 9 is 2.0 to 3. 0 times, and the working medium is at the f point state, and the third approximate adiabatic compression is completed, as shown in the ef process in FIG. It is emphasized here that the first type of working fluid is not subjected to intercooling after the third compression, but is directly subjected to voltage regulation and voltage regulation, in order to make full use of the pressure energy.
  • Ef three-stage compression process In the formula, W5 is the supercharged specific work of the three-stage compression process, and the unit is kj/kg.
  • step 1 the voltage regulation process is performed.
  • the first type of working fluid is directly connected to the voltage regulator 11 through the connecting line ⁇ 26 to maintain the gas pressure at a certain value.
  • the pressure ratio is 2
  • the pressure is 7 bar.
  • the boost ratio is 2.
  • the pressure is 14 bar.
  • the gas pressure also increases, so that the working fluid entering the next-stage component maintains a stable pressure and flow, which not only adjusts the load of the entire system, but also ensures The system works intermittently, and continues to work stably.
  • the voltage regulation process is completed, as shown in the fg process in Figure 4.
  • thermodynamic cycle a voltage regulation and voltage regulation process.
  • thermodynamic cycle it is approximated that the thermodynamic parameters of the state point f and the state point g are equal.
  • the process includes a countercurrent endothermic process and a countercurrent exothermic process, wherein in the countercurrent endothermic process, the first type of working fluid flowing out of the steady voltage regulating device 11 enters the countercurrent heat exchange device 3 via the connecting line Pu27.
  • the heat source is derived from the first type of working medium and the second type of working medium discharged from the expander 2, and in the countercurrent heat exchange device 3, the first type of working medium flowing out of the steady voltage regulating device 11 absorbs heat and expands
  • the first type of working medium discharged from machine 2 and the second type of working medium are exothermic.
  • the first type of working fluid flowing out of the pressure regulating device 11 countercurrently absorbs heat, as shown in the g-h process in FIG.
  • W 6 C P( h) T h - C P( g) T g
  • Wf > is the process specific work of the countercurrent heat transfer process, kj/kg
  • C P(B) e P ( h) The specific pressure specific heat of the state points g and h, the unit is kJ/kg-K.
  • the combustion exhaust gas flowing out of the expander 2 enters the countercurrent heat exchange device 3 through the connecting pipe P 2 18 to further release heat, and transfers the heat to the constant pressure from the steady pressure regulating device to the timing.
  • the first type of working fluid (endothermic) of the burner 1. The temperature of the combustion exhaust gas discharged from the countercurrent heat exchanger is controlled at 120 °C left Right, to prevent condensation of water vapor.
  • the combustion exhaust gas completes the countercurrent heat exchange process, as shown in the jk process in FIG.
  • the first type of working fluid is subjected to preliminary isobaric expansion in the countercurrent heat exchange device 3.
  • the combustion exhaust gas is a working fluid discharged after the expansion machine 2 is working, and is a name of the working fluid in the thermal system at different stages.
  • T k ( C p(j) XT j _ C p(h) x T h + C p(g) XT g ) ⁇ C p(k)
  • Pk is the pressure of the working medium at the state point k
  • the unit is MPa; ht P4 is the pressure loss of the working medium through the countercurrent heat exchange device, the unit is MPa; the temperature of the working medium at the state point k, the unit is K; e p ( "for the working medium at the state point j Constant pressure specific heat, the unit is kJ/kg, K; e p (h ) is the constant pressure specific heat of the working medium at the state point h, the unit is kJ/kg, K; when the working medium is at the state point g Compressed specific heat, the unit is kJ/kg, K; e p « is the constant pressure specific heat of the working medium at the state point k, and the unit is kJ/kg-K.
  • W 9 C p(k) T k - C p(j) T j
  • N is the process specific work of the countercurrent heat transfer process II, in units of kj/kg.
  • Step 3 Complete the timing and constant volume combustion process:
  • the first type of working fluid flowing out of the countercurrent heat exchange device 3 enters the mixing injector 14 via the connecting line P 12 28, and the connecting line P 12 28 and the oxidant supplying device 12 meet at the mixing injector 14, A type of working fluid is combusted with the oxidant while mixing in the mixing injector 14.
  • the first type of working fluid is mixed with oxygen.
  • the volume pressure generated by the injected oxidant is considered to be the heat of the countercurrent heat transfer, that is, the pressure is inconvenient, the state pressure is p h , and the temperature of the oxidant No change, the state temperature is Th .
  • the oxygen-containing working medium flowing out of the mixing ejector 14 enters the timing constant volume burner 1 and is mixed with the fuel supplied from the fuel supply unit 13 at the inlet of the constant volume constant burner 1 to form a combustible mixture. Since the oxidant is supplied from the oxidant supply unit 12, the oxygen supply amount can be freely controlled as required, unlike the intake of fresh air from the external environment, and the fuel can be independently and freely controlled, so that the system can be easily formed into a thin one. mixed gas.
  • the fuel injected by the oxidant and fuel supply unit 13 then has a spark plug in the constant volume burner 1
  • the fuel and the oxidant are combusted in the constant volume constant burner 1 to generate carbon dioxide and water, and are heated together with other first type of working medium not involved in combustion to form a high temperature gas, which is discharged from the outlet of the constant volume burner 1 into the expander 2 .
  • the working fluid completes the positive-time constant-volume combustion heating process in the constant-capacity combustion chamber, as shown in the hi process in FIG.
  • the ratio of the oxidant volume in the cycle to the volume of the first type of working fluid is y, namely:
  • n is the number of carbon atoms in the fuel molecule
  • m is the number of hydrogen atoms in the fuel molecule
  • 9 is the heat released by the combustion.
  • the volume fraction of the first type of working fluid after combustion is calculated as:
  • the timing constant volume burner 1 is isolated from the intake process, and the high temperature gas discharged from the positive constant volume burner 1 enters the expander 2 through the connecting line PJ7 for full expansion work, expansion
  • the machine 2 externally outputs mechanical work under the driving of high temperature and high pressure gas, and at the same time drives the first stage compressor 6, the second stage compressor 8 and the third stage compressor 10 to rotate through the transmission shaft 16, thereby providing compression work for each stage compressor.
  • the gas is expanded in the expander 2 to perform work, as shown in the i-j process in FIG.
  • the pressure of the working medium at the state point j the unit is MPa; the expansion ratio of the working medium in the expansion process; and the temperature of the working medium at the state point j, the unit is ⁇ .
  • W8 is the process specific work of the first expansion process, the unit is kj/kg; respectively, the constant pressure specific heat of the working medium at the state point i, the unit is kj/kg, K; e p « is the process of ij, etc.
  • the specific pressure is the specific heat;
  • v i is the specific volume of the working medium at the state point i, the unit is m 3 /kg;
  • hl - lQSS is the heat loss rate of the first-stage expander.
  • the temperature of the combustion exhaust gas flowing out of the countercurrent heat exchanger 3 is about 170 to 180 ° C, and further cooling is required, which enters the aftercooler 4 via the connecting line P 3 19 .
  • the first type of working fluid and the second type of working fluid from the expander are in the aftercooler 4 is sufficiently cooled, the temperature can be close to the ambient temperature, and the water vapor portion is condensed, which causes a certain degree of dehydration.
  • the combustion exhaust gas is sufficiently cooled and subjected to preliminary dehydration in the aftercooler 4, as in the k-1 process in FIG.
  • T; T k - hte5 x (T k - T 0 )
  • Pl the pressure at the 1st point of the working medium, the unit is MPa;
  • ht P5 is the pressure loss of the cooler after the working medium passes, the unit is MPa
  • the temperature for the working medium at the state point h, the unit is K;
  • 1 ⁇ is the temperature of the working medium at the state point 1 , K;
  • hte5 is the heat exchange efficiency of the aftercooler.
  • W 10 C p(l) T l - C p(k) T k
  • WlQ is the process specific work of the aftercooler, the unit is kj/kg
  • the working medium is The constant pressure specific heat of the state points k and 1 is in kJ/kg-K.
  • the combustion exhaust gas discharged from the aftercooler 4 flows into the carbon dioxide and water removal device 5 via the connecting line P 4 20, and completely removes carbon dioxide or absorbs part of excess carbon dioxide in the device 5, and further removes moisture in the combustion exhaust gas.
  • This type of working fluid realizes an open cycle, and an appropriate amount of relatively pure first type working fluid is obtained.
  • the combustion exhaust gas flowing out of the carbon dioxide and water removal device 5 is converted into a fresh first type working medium, and returned to the inlet of the primary compressor 7 via the connecting line P 5 21 to start the next cycle, that is, the class The working fluid achieves a closed loop. At this point, the combustion exhaust gas completes the decarbonation and water removal, as in the 1-a process of Figure 4.
  • Pl is the pressure of the working medium at the state 1 point, the unit is MPa; after the combustion of the first type of working medium Volume ratio, the total removal efficiency of carbon dioxide and water, ht P5 is the pressure loss of the working medium after the cooler, the unit is MPa; the temperature of the working medium at the state point h, the unit is K; hte5 is the post-cooling Heat exchange performance of the device.
  • a semi-closed timing constant volume thermodynamic cycle is completed by the above six steps, and then the above steps are repeated.
  • Fuel heat input Cv ( 0 T " c v ⁇ ( ⁇ h) , T h
  • the semi-closed timing constant volume thermal cycle is completed to achieve the target thermal efficiency.
  • the invention adopts a semi-closed timing constant volume thermal system for realizing the thermal cycle, and has a special requirement and design for its structure and function.
  • the thermal system includes a multi-stage moderate isothermal compression device, a constant pressure regulator, a counterflow heat exchanger, a timing constant volume burner, an adiabatic expander, a recirculating refrigerant cooling device, and a carbon dioxide and water removal device.
  • the system is provided with a set of oxidant supply devices and a set of timing devices 15 to make the thermal cycle high in thermal efficiency, less in combustion and discharge of pollutants, soft in operation, low exhaust noise, and no need to inhale fresh air from the external environment.
  • the first type of working medium passes through the multi-stage compression stage cooling process, wherein the interstage cooling cools the working medium between the first stage compression and the latter stage compression, and undergoes countercurrent exchange after being regulated and regulated.
  • Thermal process I absorbing residual heat to achieve an isostatic heating process, and then, the first type of working fluid, oxidant and fuel undergo the said constant volume constant combustion process, after completing the positive constant volume combustion process, undergoing the adiabatic expansion process to perform external work
  • the reverse flow heat exchange process II the waste heat of the working fluid is transferred to the first type of working fluid flowing out of the pressure regulating device, which helps to improve the heat energy recovery rate.
  • the working medium undergoes the post-cooling process to further cool the working medium, and after the process of removing carbon dioxide and water, the second type of working medium is removed, and the remaining first type of working medium begins. The next thermal cycle.
  • the device for realizing the multi-stage compression interstage cooling process of the above thermal cycle can have various forms: a positive displacement compressor and a speed compressor, and the technical solution of the present invention can adopt: a rotor compressor, a counterflow heat exchanger, and combustion Room, rotor expander.
  • the rotor type engine has the characteristics of compact structure and stable operation. Due to its defects (large compression ratio and poor sealing environment), it has not been widely used.
  • the principle of the rotor engine is applied to compress the first type of working fluid.
  • the supercharging ratio is between 2.0 and 3.0, which is low compression ratio compression and low temperature compression, which overcomes the wear of the piston ring when the rotor engine is burned. Fast, the piston has large thermal stress and is difficult to seal.
  • the present invention can be applied to a rotor compressor.
  • the rotor compressor structure is shown in Figure 8, while the constant volume combustion chamber uses a timing constant volume burner, the structure and principle of which will be described below.
  • the rotor compressor structure forms three compression chambers, and the working fluid first passes through the first-stage compression air inlet 61, and after one compression, is discharged from the first-stage compression exhaust port 62, and after the intermediate cooling process, enters the second-stage compression again.
  • the intake port 63 after secondary compression, is discharged from the secondary compression exhaust port 64, after two stages of intermediate cooling, then enters the three-stage compressed intake port 65, and finally is discharged from the three-stage compressed exhaust port 66, wherein
  • the power is derived from the torque output from the compressor rotary drive shaft 68.
  • the compressor inner rotor 74 is fixed on the compressor rotary drive shaft 68.
  • the shaft linkage 63 moves along the compressor inner rotor 66. This acts as a seal. This makes full use of the high compression efficiency of the rotor engine, and because the compressor can achieve two compressions, the structure can be made very compact.
  • the oxygen supply to the thermal system is provided with a oxidant supply unit 12, which is responsible for providing the required oxidant for the constant combustion chamber so that the thermal system does not need to draw in air from the external environment (atmosphere). This is why the thermal system does not need to draw in air from the environment.
  • the structure is shown in Fig. 7.
  • the device comprises an oxygen storage tank 1201, a pressure reducing valve 1202, a flow control valve 1203, a check valve 1204, a pressure gauge 1205, a connecting pipe 1206 and a pipe 1207.
  • the oxidant supply unit 12 is connected to the mixing ejector 14 via a line 1207, and the amount of oxygen supplied is controlled by a flow control valve 1203.
  • the oxidant supply unit 12 is responsible for providing the required oxidant for the constant volume combustion chamber so that the thermal system does not need to draw in air from the external environment (atmosphere).
  • the apparatus includes an oxygen storage tank 1201, a pressure reducing valve 1202, a flow control valve 1203, a check valve 1204, a pressure gauge 1205, a connecting pipe 1206, and a line 1207. This is why the thermal system does not need to draw in air from the environment.
  • the oxidant supply amount is determined by the fuel injection amount and the highest combustion occurrence temperature in the timing constant volume burner 1, i.e., determined by the degree of lean burn, and the maximum combustion occurrence temperature of the first type of working fluid of the different components is different.
  • the voltage regulation and voltage regulation process is provided with a set of voltage regulation and pressure regulating device 11, and the device has a certain volume, which is about ten times the volume of the constant volume combustion chamber.
  • the device maintains a constant pressure and flow while maintaining the load on the entire system to ensure that the system performs intermittent work and continuous work.
  • the prime mover provides the required working fluid at start-up.
  • the timing constant volume combustion system of the timing constant volume combustion process has a structure as shown in FIG. 9, and includes a timing device 15, a timing constant volume burner 1, and the timing device 15 includes a timing driving device 154.
  • the constant volume combustion chamber includes a combustion chamber grill 111 and a combustion chamber tile-type insulated inner wall 114, and uniform combustion is achieved by the combustion chamber grill 111, and the combustion chamber tile-type insulating inner wall 114 is provided with a heat insulating coating.
  • the tile structure of the material is lapped to withstand high temperature difference changes and also reduce heat energy.
  • the timing drive device 154 directly controls the opening and closing times of the combustion chamber control valve I 151, the combustion chamber control valve II 152, and the control valve III 153 through the transmission.
  • the control valve I 151, the control valve II 152, the control valve III 153 and the isothermal compression process device 30 and the full expansion process device 314 are associated with each other by the timing drive device 124 to achieve a timed operation.
  • the combustion chamber control valve II 152 When the combustion process in the constant-capacity combustion system ends, the combustion chamber control valve II 152 is opened, the timing of the exhaust system in the constant-capacity combustion system begins, and the high-temperature high-pressure working medium pushes the expander to work, when the working pressure is expanded When the working medium pressure is lower than the pressure in the voltage regulator, the combustion chamber control valve 1 151 is opened, the timing of the intake air in the combustion system and the scavenging process start, and the working fluid and the pressure regulation entering the expander When the working medium of the pressure regulating device is the same, the scavenging process in the constant-capacity combustion system ends, the combustion chamber control valve II 152 is closed, and the working medium pressure and the constant pressure regulating pressure in the constant-combustion combustion chamber in the constant-capacity combustion system When the working fluid pressure in the device is the same, the combustion chamber control valve I 151 is closed to complete the intake process in the timing constant volume combustion system, at which time the combustion chamber control valve I 151
  • the opening and closing of the timing device 15 realizes that the timing constant volume combustion process, the multi-stage compression interstage cooling process and the multi-stage adiabatic expansion process work together according to a preset timing, and the constant volume combustion chamber exhausts and the intake air Disengaged, the intake air is disconnected from the exhaust gas, and the combustion is decoupled from the intake air and the exhaust gas, so that the heating process, the intake process, and the exhaust process are independent and related to each other.
  • the combustion is limited to the space of the constant volume combustion chamber, and the purpose of strictly controlling the constant volume combustion is achieved. Since the compression and expansion are independent of each other, the opening and closing time of the intake and exhaust valves is controlled by setting the valve timing of the timing device 15.
  • the combustion duration is up to 210°, while the combustion duration of a typical internal combustion engine is only 20 ⁇ 60°, and because of the long burning time, the combustion heat release rate and pressure The rate of increase is small, so the combustion is soft.
  • the constant-capacity combustion chamber has a structure with a grid to achieve uniform combustion. Due to the long burning time, the combustion mixture is uniformly mixed to make the fuel Fully burned, effectively suppresses the production of HC, CO and PM. By the lean combustion method, the combustion temperature is between 1900 and 2100K, which effectively suppresses the generation of NOJ.
  • the constant volume combustion chamber also has a combustion chamber tile-type insulated inner wall 114 which is made up of a tile structure with a heat insulating coating material, which can withstand high temperature difference changes and also reduce heat energy loss.
  • the intake and exhaust valves of the constant volume combustion chamber are not in the form of a valve, but in the form of a ball.
  • Such a structure enables the valve to be opened as soon as possible to minimize the throttling loss generated when the working fluid flows through the valve.
  • the hybrid injector 14 goes deep into the constant volume
  • the combustion chamber has a plurality of fuel injection holes 141, so that the fuel is evenly distributed as soon as possible.
  • the expander used in the adiabatic expansion process can take a variety of forms: a piston positive displacement expander, a turbo expander, etc., and the present invention is applicable to a rotary expander.
  • the piston expander needs to convert the linear motion of the piston into the rotary motion of the crankshaft, the conversion efficiency of the thermal power is not high, and the turboexpander has no high efficiency of the volumetric expander, so the rotor expander is used.
  • the present invention realizes constant volume combustion by the timing device 15, and the high temperature and high pressure gas after combustion needs to enter the expander on time. Since the expander in the form of a rotor is used, the high temperature and high pressure gas can be made as long as the timing of the rotor is controlled. The maximum amount of work is done, and the new exhaust valve is not required, reducing the throttling loss of the work gas. Since it is a constant volume combustion, the pressure after combustion is much higher than the pressure before combustion, and the pressure after expansion is close to the pressure before compression, so that the expansion ratio of the whole system is greater than the ratio.
  • the timing device 15 is independent of the timing constant volume combustion process, which is different from the working process of the conventional four-stroke internal combustion engine.
  • compression and expansion are related and independent, so that the expansion ratio cannot be too large.
  • the present invention enables the air intake, heating, and exhaust to work in an orderly manner by the timing device 15, and sufficient expansion can be achieved.
  • the expansion ratio of the expansion process is greater than the pressure ratio of the compression process, so that the expansion is fully expanded as much as possible.
  • the embodiment includes a multi-stage compression interstage cooling device, such as a primary compressor 6, a primary intercooler 7, a primary compressor 6, and a primary intercooler 7. 6 22.
  • a multi-stage compression interstage cooling device such as a primary compressor 6, a primary intercooler 7, a primary compressor 6, and a primary intercooler 7. 6 22.
  • the compressor is a rotor compressor; and comprises a voltage regulator 11 which is connected to the third stage compressor 10 of the multistage compression interstage cooling device via a connecting line ⁇ ⁇ 26 ,
  • the first type of working medium stores a sufficiently high pressure in the device; and comprises
  • the expander 2 is a rotor expander; Further comprising an aftercooling device, the aftercooler 4 is connected to the countercurrent heat exchange device 3 via a connecting line P 3 19 , and the combustion exhaust gas fully releases thermal energy in the aftercooler 4; finally comprising a decarbonation and water device, a decarbonation and water device 5 is connected to the aftercooler 4 via the connecting line P 4 20, and the decarbonation and water device 5 is connected to the primary compressor 6 via the connecting line P 5 21; the system device of one embodiment of the present patent is formed according to the above connecting sequence .
  • the semi-closed timing constant volume thermal circulation method of the prime mover may also include a single stage compression process, a single stage intermediate cooling process or a multistage expansion process, and the thermal cycle system may be a single stage compressor,
  • the working principle and characteristics of the multistage expander are the same as those of this embodiment.

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Abstract

一种原动机的半闭式正时定容热力循环方法及系统，其循环包括多级压缩级间冷却、逆流换热、正时定容燃烧、绝热膨胀、后冷却和二氧化碳和水脱除6个过程，是一种热功转化的热力循环。多级压缩级间冷却过程减少压缩耗功；逆流换热过程回收膨胀后工质的焓，参与热力循环；正时定容燃烧过程，有效抑制HC、CO、PM和NOx等有害污染物的产生；绝热膨胀过程，实现充分膨胀做功；后冷却过程将工质进一步冷却至环境温度，提高绝热膨胀过程的膨胀比；二氧化碳和水脱除过程将正时定容燃烧过程产生的二氧化碳和水脱除，余下工质继续参与下一次热力循环。为今后设计高效、低污染物排放和高性能的原动机提供了方向。

Description

一种原动机的半闭式正时定容热力循环方法及系统 相关申请
本申请主张如下优先权： 中国发明专利申请： 201410130949. 3， 题为 "一种原动 机的半闭式正时定容热力循环方法及系统"， 于 2014年 4月 2日提交。 技术领域
本发明涉及一种原动机，特别是一种原动机的半闭式正时定容热力循环方法及系 统。
背景技术
提高内燃机效率和降低排放对节约资源和保护环境均具有重要的积极作用。通过 改进的循环过程和燃烧组织方式， 可提升原动机效率和减少有害污染物的排放。 目前 内燃机应用的热力循环主要有狄塞尔循环、 奥托循环、 阿特金森循环、 米勒循环、 布 雷顿循环等， 其中狄塞尔循环、 奥托循环、 阿特金森循环、 米勒循环主要应在传统往 复式活塞内燃机上， 而布雷顿循环主要应用在燃气轮机上。
奥托循环： 等容加热是其优点， 但压缩比小、绝热压缩、等容放热是其缺点， P-V 示功图如 1所示。 其理论热效率计算公式为：
狄塞尔循环： 压缩比大是其优点， 但绝热压缩、 等压加热、 等容放热是其缺点， P-V示功图如 2所示。 其理论热效率计算公式为：
?7t = l- s1- k(pk - l)[k(p- 1)]- 1
布雷顿循环： 等压放热是其优点， 但其加热过程是等压过程， 其缺点是压缩比较 低、 等容度低和排温高。 P-V示功图如 3所示。 其理论热效率计算公式为：
/7t = l - s1- k
式中， s为压缩比； 为加热膨胀比； k为比热比。
为了提高内燃机的热效率， 传统往复式活塞内燃机对废气的能量进行再利用，一 般是采用废气涡轮增压方式， 如增压柴油机、 增压汽油机等。 然而， 采用废气涡轮增 压方式获得能量并未直接应用到热力系统循环做功中， 而是用来提高进气压力， 增加 进气密度， 以减少泵气损失和提高单位容积的功率密度来提高热效率。 其次， 尽管废 气涡轮增压器结构紧凑， 但废气能量回收采用叶片式涡轮机和叶轮式压缩机， 其效率 较低， 转速高， 噪声大。 再次， 废气通过涡轮机之后仍具有一定的能量， 即温度和压 力没有得到充分的利用。 最后， 传统往复式活塞内燃机由于燃烧局部温度较高（局部 最高温度可达 2800K)、 油气混合不均匀、 主燃烧过程短（ 30°CA)、 活塞环漏气、 活 塞环狭隙和体积淬熄等原因， 致使其 N0x、 PM (微粒， 柴油机上）、 HC和 CO (汽油机 上）排放高。 尽管目前科学界提出在往复式活塞内燃机上采用 HCCI (均质压燃点火) 方式可大大减少 NOx和 PM， 但是不管在柴油机上还是汽油机上其实现的工况范围非 常有限， 应用性难以得到推广。
燃气轮机是一种以连续流动的气体作为工质、把热能转换为机械能的旋转式动力 机械。在空气和燃气的主要流程中， 只有压缩机、 定容燃烧室和燃气透平这三大部件 组成的燃气轮机循环， 通称为简单循环。 大多数燃气轮机均采用简单循环方案。 因为 它的结构简单， 而且能体现出燃气轮机所特有的体积小、 重量轻、 起动快、 基本不用 冷却水等一系列优点。 但是， 简单循环的燃气轮机排温高（900°C左右）， 致使其热效 率不高。虽然在简单循环的基础上增加了一些过程， 包括压缩之间的冷却过程和排气 换热等过程， 但是， 其增压比较低， 采用定压燃烧， 等容度低， 致使其热效率低。 其 次， 通过燃气透平的废气仍具有一定的能量， 即温度和压力没有得到充分的利用。再 次， 燃气轮机在负荷变化的情况下， 热效率低。
目前外燃机应用的热动力循环主要有斯特林循环、 朗肯循环、 卡诺循环等。 斯特 林循环需要经过一段时间才能响应气缸的热量变化， 其热量损失较大， 热效率低。 蒸 汽轮机作为一种外燃机， 是一种高热效率的热力系统， 其工作原理是撷取（将水加热 后形成的）水蒸汽之动能转换为涡轮转动的动能的机械，是朗肯循环的典型应用热机。 世界上大约 80%的电是利用涡轮蒸汽机所产生， 其特别适用于火力发电和核能发电。 为了提高热机的效率， 应该尽可能地提高热机中的加热温度和降低排热温度。但是蒸 汽轮机和燃气轮机的热力循环都不能很好满足上述要求，则提出了燃气一蒸汽轮机联 合循环。 为了进一步提高能源的综合利用效率， 又提出多级热电并供热力系统。但该 类热力系统庞大， 结构复杂， 不宜直接应用在运载工具上。
转子发动机直接将可燃气的燃烧膨胀力转化为驱动扭矩。转子发动机取消了往复 式发动机的直线运动， 不需使用曲柄滑块机构和气门正时机构， 转子每旋转一圈就做 功一次， 与一般的四冲程发动机每旋转两圈才做功一次相比， 具有升功率高的优点， 变工况适应性好。在相同功率下转子发动机尺寸较小，结构紧凑，体积小，重量较轻， 而且振动和噪声较低， 充气效率高， 高速性能好， 具有较大优势。 但其也有致命的弱 点， 端面密封面大， 工作环境恶劣， 密封、 润滑、 冷却困难， 密封件磨损快， 泄露损 失大， 活塞热应力大， 可靠性差， 寿命低。
现已公开的相关专利中， 中国专利 CN102032049 A和欧洲专利 EP 2578942 A2 公开了一种涉及碳封存和发动机的方法和系统， 其主要应用于碳封存， 但没有采用多 级适度等温压缩、稳压调压和逆流换热过程， 特别是该系统和方法没有采用正时定容 燃烧和特定工质闭式循环。此外， 该系统没应用氧化剂供给装置， 系统做功需要从外 界吸入新鲜空气， 而且难以改变定容燃烧室内混合气的氧浓度， 同时做功后还要将二 氧化碳之外的氮气等气体排至环境中， 因此该系统没有充分利用排气中的焓， 也不能 应用在水中等缺氧环境当中工作。
中国专利 CN 102374026 A公布了一种封闭循环式布雷顿循环系统及方法， 其包 含 3个子系统， 分别是开式热能产生系统、 热功转换回路系统和冷却回路系统， 热工 转换系统通过一个热交换器将热量传递给热工转化系统。实现整个该系统需要较大空 间， 更重要的是该系统采用蒸汽动力做功而非燃气动力做功， 属于外燃式热机， 而且 热能产生子系统未对工质循环利用， 而是直接排至大气中。
中国专利 CN 102454481 A公布了一种二氧化碳收集系统的联合循环动力装置， 其主要包含二氧化碳收集装置、热回收蒸汽发生器和燃烧废气再循环装置， 该系统不 适合在水下和缺氧环境中工作， 更重要的是该系统未包含供氧、正时定容燃烧和特定 工质闭式循环。
中国专利 CN1138135A公开了一种等温压缩、 近似定容燃烧、 绝热完全膨胀和等 压放热循环， 但是该专利也没有采用正时定容燃烧和特定工质闭式循环。
美国专利 PCT/US00/03711公布了一种涡轮动力实现方法和装置， 其主要包含动 力涡轮、 燃烧废气换热利用和燃料 与水加热转化反应装置， 其中部分燃烧废气再循 环利用， 但不是特定工质始终循环， 而且未进行脱碳、 等温压缩和供氧的过程和正时 定容燃烧， 还有， 该系统也不适合在水下和缺氧环境中工作。
为了提高内燃机的热效率， 应该尽可能提高燃料燃烧效率、 热功转换效率， 降低 压缩过程的消耗功， 增大膨胀过程膨胀功， 降低排气温度， 同时减少排放污染物。 尽 管大部分专利都对多级压缩中间冷却和废气能量回收进行了阐述，但其加热或燃烧过 程不能实现真正的定容燃烧， 热功转换效率不高， 难以做到充分膨胀做功， 没有实现 特定工质闭式循环， 也无法实现超长时间清洁燃烧。 因此设计一种热效率高、排放污 染小、 工作柔和、 排气噪音小、 外界吸入和排出工质少的热力循环及系统， 对实现内 燃机的节能减排有十分重要有意义，对开发在水下作业或缺氧环境下的动力机械来说 也具有重要意义。
发明内容
为了解决常用内燃机热力循环存在的不足， 使热动力机械实现清洁高效定容燃 烧， 提高热效率， 以及解决不便于在水下工作等问题， 本发明提供了一种原动机的半 闭式正时定容热力循环方法及系统， 其循环过程包括六个过程固有过程， 分别是进行 多级压缩级间冷却过程、 逆流换热过程、 正时定容燃烧过程、 绝热膨胀过程、 后冷却 过程和二氧化碳与水脱除过程， 一些实施例中还包括辅助过程， 如稳压调压过程和氧 化剂和燃料混合过程。
本发明的具体技术方案是： 一种原动机的半闭式正时定容热力循环方法， 其中， 热力循环方法以转子发动机的转子自转角度 360°或二冲程往复发动机的输出轴旋转 角度 360°或四冲程往复发动机的输出轴旋转角度 720°为一个循环周期， 其采用两类 工质， 第一类工质是参与热力循环全部过程的工质， 在定容燃烧室内燃烧后通过膨胀 机做功， 做功完成后返回到一级压缩机入口， 继续参与下一次热力循环； 第二类工质 是正时定容燃烧过程前加入的氧化剂和燃料而产生的， 并参与正时定容燃烧过程、绝 热膨胀过程、 逆流换热过程、 后冷却过程的， 最后在二氧化碳与水脱除过程中脱除的 工质， 该工质不再参与下一次热力循环：
步骤 1、 进行多级压缩级间冷却过程： 该过程中， 对第一类工质进行多级压缩， 并通过级间冷却以减少压缩耗功， 对第一类工质压缩终了压力进行稳压调压；
步骤 2、 进行逆流换热过程： 该过程中， 稳压调压后的第一类工质在进入定容燃 烧室前回收上一次热力循环膨胀做功后的第一类工质和第二类工质的焓，直接收益热 量后参与本次热力循环，以提高定容燃烧室中本次热力循环的第一类工质和第二类工 质的初始温度；
步骤 3、 进行正时定容燃烧过程： 该过程中， 第一类工质经过逆流换热过程后进 入定容燃烧室，氧化剂供给装置和燃料供给装置将氧化剂和燃料通过混合喷射器喷入 定容燃烧室并开始正时定容燃烧， 定容燃烧室容积不变；
步骤 4、 进行绝热膨胀过程： 该过程独立于多级压缩级间冷却过程和正时定容燃 烧过程， 定容燃烧室排出的工质经充分膨胀对外输出功， 绝热膨胀过程的膨胀比大于 压缩过程的增压比；
步骤 5、 进行后冷却过程： 该过程中， 膨胀做功后的第一类工质和第二类工质经 过逆流换热装置后进入后冷却器， 进一步冷却至环境温度；
步骤 6、 进行二氧化碳和水脱除过程： 该过程中， 将正时定容燃烧过程产生的二 氧化碳和水脱除， 余下的工质继续参与下一次热力循环。
此外，本发明还提供了一种原动机的半闭式正时定容热力循环系统，其特征在于: 包括多级压缩级间冷却装置、 稳压调压装置、 逆流换热装置、 氧化剂供给装置、 燃料供给装置、 混合喷射器， 正时定容燃烧器、 膨胀机、 后冷却器、 二氧化碳与水脱 除装置， 其中， 多级压缩级间冷却装置对工质实现压缩及中冷， 稳压调压装置经连接 管路 。与多级压缩级间冷却装置的末级压缩机相连， 逆流换热装置经连接管路 Pu与 稳压调压装置相连， 正时定容燃烧器经连接管路 P12与逆流换热装置相连。
其中，氧化剂供给装置和燃料供给装置将氧化剂和燃料通过混合喷射器喷入正时 定容燃烧器混合并燃烧， 生成第二类工质中的二氧化碳和水； 正时定容燃烧器经连接 管路 与膨胀机相连； 在膨胀机中做功后经连接管路 P2与逆流换热装置相连。
其中， 第一类工质经多级压缩级间冷却装置后进入稳压调压装置， 从稳压调压装 置流出的第一类工质进入逆流换热装置吸热后进入正时定容燃烧器，氧化剂供给装置 和燃料供给装置提供的氧化剂和燃料经混合喷射器喷入正时定容燃烧器边混合边燃 烧产生第二类工质， 与第一类工质一并进入膨胀机膨胀做功， 并通过传动轴对外输出 功， 做功后经连接管路 P2进入逆流换热装置中放热， 之后从逆流换热装置流出的工 质进入后冷却器得到冷却， 之后经过二氧化碳与水脱除装置， 第二类工质被脱除， 第 一类工质开始下一次热力循环。
本发明的有益效果是-
1 ) 由热力循环效率表达式， 可得到： 本发明循环热效率主要取决于最高燃烧温 度和外部环境温度。在其它条件不变的情况下，最高燃烧温度越高，即热源温度越高， 循环热效率越高； 在其它条件不变的情况下， 外部环境温度越低， 即冷源温度越低， 循环热效率越高， 此规律与卡诺定律类似， 比较接近卡诺循环热效率（热机极限热效 率)。
2 ) 多级压缩级间冷却过程每一级增压比在 2. 0-3. 0之间， 可以使压缩装置在高 效率区运行， 级间冷却过程降低进入压缩过程的新鲜工质温度， 使压缩过程接近等温 压缩， 减少压缩装置的压缩耗功。
3 ) 逆流换热过程是回收了膨胀做功后的工质焓， 直接收益热量后参与热力循环 做功， 提高定容燃烧室中工质的初始温度， 增大了循环的热功转化率。
4) 采用独立供氧， 压缩装置只需压缩第一类工质， 减少了压缩机的工质流量， 而不需压缩定压燃烧过程中的氧化剂，燃烧过程的氧化剂是由一套独立氧化剂供给装 置提供， 因此减小了整个循环的压缩功， 增大系统输出功， 不需要从外部环境中吸入 新鲜空气。
5 ) 本发明热力循环中第一类工质中不参与燃烧的工质可应用惰性气体， 可控制 工质中不含氮气， 燃烧温度较常规热力系统燃烧温度高， 只要控制不超出定容燃烧室 所能承受的极限温度， 可将碳烟和 HC烧尽， 而又不会产生 N0x， 是一种清洁高效率 的燃烧方式， 而且该类工质比热比高， 可提高整个系统的热效率。
6 ) 本发明热力循环中采用后冷却过程， 将从逆流换热过程流出的热源工质 （来 自膨胀做功后的工质）进一步冷却， 有助于脱除燃烧过程产生的二氧化碳和水、 降低 排气背压和增大膨胀比， 以及减少压缩过程消耗功。
7 ) 该热力系统是半闭式的， 不需要向环境直接排出燃烧废气， 与其他开式循环 系统相比本发明减少了燃烧废气中所带走的热量， 回收了燃烧废气中所拥有的推动 功， 以及回收了在压缩过程和燃烧过程中的漏气量， 避免了泄露损失， 从而保证了整 个系统的热效率高。
8 )本发明热力系统燃烧过程压力波动小， 工作柔和； 做功后第一类工质占比大， 能循环利用， 第二类工质被脱除， 不直接排气， 无排气噪音。
9 ) 初级压缩机入口压力提高， 升功率同比例提升。
附图说明
图 1是奥托循环 P-v图；
图 2是狄塞尔循环 P-v图；
图 3是布雷顿循环 P-v图；
图 4为本发明实施例的热力循环示意图； 图 5为本发明实施例的系统主要部件结构示意图；
图 6为本发明实施例的系统主要管路部件示意图；
图 7为本发明实施例的系统氧化剂供给装置的结构示意图；
图 8为本发明转子式压缩机示意图；
图 9为本发明正时定容燃烧系统示意图；
图 10为本发明正时定容燃烧器示意图；
图中， 1-正时定容燃烧器、 111-燃烧室格栅、 112-进气道、 113-排气道、 114- 燃烧室瓦块式绝热内壁、 14-燃料喷射器、 141-喷射器喷孔、 2-膨胀机、 3-逆流换热 装置、 4-后冷却器、 5-二氧化碳和水脱除装置、 6-—级压缩机、 61-—级压缩进气口、 62-—级压缩排气口、 63-二级压缩进气口、 64-二级压缩排气口、 65-三级压缩进气口、 66-三级压缩排气口、 67-压缩机内腔转子、 68-压缩机旋转驱动轴、 69-压缩机联动装 置、 7-—级中冷器、 8-二级压缩机、 9-二级中冷器、 10-三级压缩机、 11-稳压调压装 置、 12-氧化剂供给装置、 1201-储氧罐、 1202-减压阀、 1203-流量控制阀、 1204-单 向阀、 1205-压力表、 1206-连接管、 1207-管路、 13-燃料供给装置、 14-混合喷射器、 15-正时装置、 151-燃烧室控制阀门 I、 152-燃烧室控制阀门 II、 153-控制阀门 III、 154-正时驱动装置、 16-传动轴、 17-连接管路 、 18-连接管路 P2、 19-连接管路 P3、 20-连接管路 P4、 21-连接管路 P5、 22-连接管路 P6、 23-连接管路 P7、 24-连接管路 Ps、 25-连接管路 P9、 26-连接管路 Ρω、 27-连接管路 Pu、 28-连接管路 P12、 29-火花塞、 30-等温压缩过程装置、 31-充分膨胀过程装置。
具体实施方式
为使本发明的目的、技术方案和优点更加清楚明了， 下面结合具体实施方式并参 照附图， 对本发明进一部详细说明。 应该理解， 这些描述只是示例性的， 而并非要限 制本发明的范围。 此外， 在以下说明中， 省略了对公知结构和技术的描述， 以避免不 必要的混淆本发明的概念。
本发明提供了一种原动机的半闭式正时定容热力循环方法， 其中， 热力循环方法 以转子发动机的转子自转角度 360°或二冲程往复发动机的输出轴旋转角度 360°或四 冲程往复发动机的输出轴旋转角度 720°为一个循环周期， 其采用两类工质， 第一类 工质是参与热力循环全部过程的工质，在定容燃烧室内燃烧后通过膨胀机做功，做功 完成后返回到一级压缩机入口， 继续参与下一次热力循环； 第二类工质是正时定容燃 烧过程前加入的氧化剂和燃料而产生的， 并参与正时定容燃烧过程、 绝热膨胀过程、 逆流换热过程、 后冷却过程的， 最后在二氧化碳与水脱除过程中脱除的工质， 该工质 不再参与下一次热力循环：
步骤 1、 进行多级压缩级间冷却过程： 该过程中， 对第一类工质进行多级压缩， 并通过级间冷却以减少压缩耗功， 对第一类工质压缩终了压力进行稳压调压；
该步骤中， 多级压缩级间冷却过程是为了实现接近等温压缩， 通过级间冷却以减 少下一次压缩耗功， 还有， 流经压缩机的工质不含氧化剂， 进一步降低压缩耗功； 压 缩最终压力影响定容燃烧室内燃烧初始状态压力，负责压缩的装置与定容燃烧器独立 开来， 不是同一套装置。
完成多级压缩级间冷却过程之后进行稳压调压过程，将压缩过程产生的压力波消 除， 维持稳定的压力， 保证进入定容燃烧室的进气量可按照工况的变化进行调整。
步骤 2、 进行逆流换热过程： 该过程中， 稳压调压后的第一类工质在进入定容燃 烧室前回收上一次热力循环膨胀做功后的第一类工质和第二类工质的焓，直接收益热 量后参与本次热力循环，以提高定容燃烧室中本次热力循环的第一类工质和第二类工 质的初始温度；
该步骤中，温度较低的完成多级压缩级间冷却过程和稳压调压过程后的第一类工 质吸热焓增， 温度较高的完成绝热膨胀过程后的第一类工质和第二类工质放热焓降， 余热回收利用， 提高热能利用率。
步骤 3、 进行正时定容燃烧过程： 该过程中， 第一类工质经过逆流换热过程后进 入定容燃烧室，氧化剂供给装置和燃料供给装置将氧化剂和燃料通过混合喷射器喷入 定容燃烧室并开始正时定容燃烧， 定容燃烧室容积不变；
该步骤中， 本发明所述热力系统在正时定容燃烧过程实行正时定容燃烧， 正时定 容燃烧器是基于正时定容的特殊形式燃烧发生装置。热力循环中压缩过程、膨胀过程 与燃烧过程分别在独立的装置内完成， 并通过正时装置 15相互关联， 工质在定容燃 烧室中可以实现超长时间定容燃烧， 等到燃料充分燃尽， 再将高温高压工质排出定容 燃烧室进入膨胀机 2。 由于氧化剂和燃料都是独立供应， 同时定容燃烧室内加格栅进 行多点着火。 当采用氮气作为第一类工质的主要成分时， 氧化剂与第一类循环工质先 混合均匀， 成为均质混合气， 在燃烧过程中实现均质低温稀薄燃烧， 燃烧温度控制在 1900-2100K之间， 有效抑制 HC、 C0、 PM和 NOx等有害污染物的生成。 当采用氩等惰 性气体作为第一类工质的主要成分时，氧化剂与第一类循环工质先不混合， 而是与燃 料在燃烧室内直接混合， 进行边混合边燃烧， 在燃烧过程中实现高温燃烧， 控制燃烧 温度不超过定容燃烧室所能承受的极限温度， 有效抑制 PM、 HC和 CO的生成， 无 NOx 生成。 因此该系统可达到清洁高效燃烧的目的。
步骤 4、 进行绝热膨胀过程： 该过程不仅独立于多级压缩级间冷却过程和正时定 容燃烧过程， 而且绝热膨胀过程的膨胀比大于压缩过程的增压比， 可以达到充分膨胀 做功的目的；
步骤 5、 进行后冷却过程： 该过程中， 膨胀做功后的第一类工质和第二类工质经 过逆流换热装置后进入后冷却器， 进一步冷却至环境温度；
步骤 6、 进行二氧化碳和水脱除过程： 该过程中， 将正时定容燃烧过程产生的二 氧化碳和水脱除即第二类工质脱除，余下的第一类工质继续参与下一次热力循环，对 新鲜工质需求量少， 有利于封闭和水下环境运行。
由此可见， 本发明提供了一种由热能转化为机械能（功）的半闭式正时定容内燃 热力循环方法。在本发明的循环中， 主要特点体现在加热方式是做功工质先经逆流换 热定压加热， 再进入定容燃烧室内的定容燃烧， 是将膨胀做功后的余热直接应用到热 功转化当中， 综合起来整个循环是一个有别于奥托循环、 狄赛尔循环、 混合循环和斯 特林循环等现有循环形式的循环。
本发明所述半闭式正时定容内燃热力循环实现闭式工质再循环，是将二氧化碳与 水脱除过程保留下来的第一类工质通过热力系统中回路返回到多级压缩级间冷却过 程， 完成一次半闭式正时定容内燃热力循环， 之后继续重复上述过程。
所述半闭式正时定容内燃热力循环是该热力循环包含两类工质参与做功，由于整 个系统设有回路， 特别适用比热比较高的单原子气体做工质， 如惰性气体中的氦等， 而且在压缩和膨胀过程中产生的泄露， 能量可以得到回收， 从而提高了整个热力循环 的热效率。
所述半闭式正时定容内燃热力循环中的多级压缩级间冷却过程，压缩装置不需压 缩定压燃烧过程中的氧化剂， 氧化剂是由一套独立氧化剂供给装置提供， 因此减小了 整个循环的压缩功。
以下将以三级压缩两级中冷热力循环系统为例详细说明本发明的半闭式正时定 容内燃热力循环方法。 该热力循环的 P-v图如图 4所示。 图中 a-b-c-d-e-f为多级压缩级间冷却过程， 即准等温压缩过程； f-g为稳压调压过程； g-h为逆流换热过程 I (逆流吸热过程）； h_i为正时定容燃烧过程； i_j为绝热膨胀过程； j-k为逆流换热过程 I I (逆流放热 过程）； k-1为后冷却过程； 1-a为二氧化碳与水脱除过程。
以图 4和图 5为例来描述采用所述热力循环的热力系统的基本实现步骤，该实施 例中， 第一类工质不含氮气， 并以惰性气体作为其主要成分， 下面以工质流向顺序来 叙述具体步骤。
步骤 1、 对三级压缩级间进行冷却
(1) 以一级压缩机 6入口端 a为始点， 第一类工质经一级压缩机 6增压后处于 b点状态，第一类工质压力提高到 2. 0-3. 0倍； 之后经连接管路 P622进入一级中冷器 7得到冷却，工质处于点 c状态， 到此完成第一次等温压缩， 如图 4中的 a-b-c过程。
状态点 a热力参数：
Figure imgf000012_0001
Ta 式中， Pa为工质在状态点 a的压力， 单位为 MPa; 为工质在状态点 a时的温 度， 单位为 K。
状态点 b热力参数：
pb = x crl
Tb = Ta +
Figure imgf000012_0002
式中， Pb为工质在状态点 b的压力，单位为 MPa; crl为一级压缩机的增压比； 为工质在状态点 b时的温度， 单位为 K; eel为一级压缩机的等熵效率； ka为工质在 状态点 a的比热比。
状态点 c热力参数：
Figure imgf000012_0003
Tc =Tb -htelx (Tb -T0) 式中， P。为工质在状态点 c 的压力； htP1为工质通过一级中冷器的压力损失， 单位为 MPa; 为工质在状态点 c的温度， 单位为 K; htel为一级中冷器的换热效能 t
。为外部环境的温度， 单位为 κ。
a-b一级压缩过程功耗：
Figure imgf000013_0001
式中， Wi为一级压缩过程的增压比功， 单位为 kj/kg。
b-c一级中冷过程功：
w2=cp(c)Tc-cp(b)Tb 式中， W2为一级中冷过程的过程比功， kj/kg; eP(b)、 分别为工质在状态点 b和 c的定压比热， kJ/kg-Ko
(2) 第一类工质经连接管路 P723进入二级压缩机 8进行第二次增压， 此时第一 类工质压力比一级中冷器 7出口压力又提高到 2.0~3.0倍，工质处于点 d状态，再经 连接管路 Ps24进入二级中冷器 9再次得到冷却， 工质处于点 e状态， 完成第二次等 温压缩， 如图 4中的 c-d-e过程。
状态点 d热力参数：
Pd = Pcxcr2
Figure imgf000013_0002
式中， Pd为工质在状态点 d的压力， 单位为 MPa; 2为二级压缩机的增压比； 为工质在状态点 d时的温度， 单位为 K; ∞2为二级压缩机的等熵效率； k。为工质 在状态点 c的比热比。
状态点 e热力参数：
Figure imgf000013_0003
Te=Td-hte2x(Td-T0) 式中， Ρε为工质在状态点 e的压力； htP2为工质通过二级中冷器的压力损失， 单位为 MPa; 为工质在状态点 e的温度， 单位为 K; hte2为一级中冷器的换热效能。 c-d 二级压缩过程功耗:
Figure imgf000014_0001
式中， W3为二级压缩过程的增压比功， 单位为 kj/kg。
d-e二级中冷过程功：
X -c T 式中， W4为二级中冷过程的过程比功， 单位为 kj/kg; ( 分别为工质在 状态点 d和 e的定压比热， 单位为 kJ/kg-K。
(3)、 从二级中冷器 9流出的第一类工质经连接管路 P925进入第三级压缩机 10 进行第三次增压， 第一类工质压力进一步提高， 是二级中冷器 9出口压力的 2. 0~3. 0 倍， 工质处于 f 点状态， 完成第三次近似绝热压缩， 如图 4中的 e-f过程。 在此着重 说明， 第一类工质在第三次压缩后没有进行中冷， 而是直接进行稳压调压， 目的是充 分利用压力能。
状态点 f热力参数：
Figure imgf000014_0002
式中， ^为工质在状态点 f 的压力， 单位为 MPa; ^为工质在状态点 g的压力， 单位为 MPa; ^为工质在状态点 f 时的温度， 单位为 K; ^为工质在状态点 g时的温 度， 单位为 K; cr3为三级压缩机的增压比； ce3为三级压缩机的等熵效率； ke为工 质在状态点 e的比热比。
e-f三级压缩过程：
Figure imgf000014_0003
式中， W5为三级压缩过程的增压比功， 单位为 kj/kg。
完成步骤 1后， 进行稳压调压过程， 第一类工质经连接管路 Ρ 26直接进入稳压 调压装置 11将气体压力维持在一定值， 例如增压比是 2时， 压力为 7bar， 增压比是 2. 5时， 压力为 14bar， 当进气压力增加， 则气体压力也随着增加， 使进入下一级部 件的工质保持稳定的压力和流量， 这不仅可以调节整个系统的负荷， 而且保证系统间 歇性做功， 持续稳定工作， 完成稳压调压过程， 如图 4中的 f-g过程。
此处 f到 g的过程是稳压调压过程， 在热力循环计算时， 近似认为状态点 f和状 态点 g的热力学参数相等。 f = Pg
τ =τ 步骤 2、 进行逆流换热过程
该过程包括了逆流吸热过程和逆流放热过程， 其中， 在进行逆流吸热过程中， 从 稳压调压装置 11流出的第一类工质经连接管路 Pu27进入逆流换热装置 3中进行预 热， 热源来自于膨胀机 2中排出的第一类工质和第二类工质， 在逆流换热装置 3中， 稳压调压装置 11流出的第一类工质吸热， 膨胀机 2排出的第一类工质和第二类工质 放热。 稳压调压装置 11流出的第一类工质逆流吸热焓升， 如图 4中的 g-h过程。
状态点 h热力参数：
Figure imgf000015_0001
式中， Ph为工质在状态点 h时的压力， 单位为 MPa; htP3为工质通过逆流换热装 置时的压力损失， 单位为 MPa; 为工质在状态点 h时的温度， 单位为 K; hte3为逆 流换热装置的换热效能； ^为工质在状态点 g时的温度， K; ^为工质在状态点 j时 的温度， K。
g-h逆流换热过程 I ：
W6 = C P(h)Th - C P(g)Tg 式中， Wf>为逆流换热过程的过程比功， kj/kg; CP(B) e P (h)分别为工质在状态点 g和 h的定压比热， 单位为 kJ/kg-K。
在进行逆流换热过程时， 从膨胀机 2流出的燃烧废气经连接管路 P218进入逆流 换热装置 3中进一步释放热量，并将热量传递给从稳压调压装置流向正时定容燃烧器 1 的第一类工质 （吸热）。 使得从逆流换热装置排出的燃烧废气温度控制在 120 °C左 右， 防止水蒸气发生冷凝。在此，燃烧废气完成逆流换热过程，如图 4中的 j-k过程。 第一类工质在逆流换热装置 3中得到初步等压膨胀。所述的燃烧废气是经过膨胀机 2 做功后排出的工质， 是热力系统中工质在不同阶段的一种名称。
状态点 k热力参数：
Figure imgf000016_0001
Tk = (Cp(j) X Tj _ Cp(h) x Th + Cp(g) X Tg ) ÷ Cp(k) 式中， Pk为工质在状态点 k时的压力， 单位为 MPa; htP4为工质通过逆流换热 装置的压力损失， 单位为 MPa; 为工质在状态点 k时的温度， 单位为 K; ep("为工 质在状态点 j时的定压比热， 单位为 kJ/kg，K; ep(h)为工质在状态点 h时的定压比热， 单位为 kJ/kg，K; 为工质在状态点 g时的定压比热， 单位为 kJ/kg，K; ep«为工 质在状态点 k时的定压比热， 单位为 kJ/kg-K。
j-k逆流换热过程 II：
W9 = Cp(k)Tk -Cp(j)Tj 式中， ％为逆流换热过程 II的过程比功， 单位为 kj/kg。
步骤 3、 完成正时定容燃烧过程：
完成步骤 2后， 从逆流换热装置 3流出的第一类工质经连接管路 P1228进入混合 喷射器 14， 连接管路 P1228和氧化剂供给装置 12在混合喷射器 14交汇， 第一类工质 与氧化剂在混合喷射器 14中边混合边燃烧。
此处第一类工质与氧混合， 在热力循环计算时， 近似认为喷入的氧化剂产生的体 积压力视为逆流换热吸热的热量， 即压力不便， 状态压力为 ph， 氧化剂的温度不变， 状态温度为 Th。
从混合喷射器 14流出的含氧工质进入正时定容燃烧器 1中， 并在正时定容燃烧 器 1的入口与燃料供给装置 13提供的燃料进行混合， 形成可燃混合气。 由于氧化剂 由氧化剂供给装置 12供给， 其供氧量可按照需求自由控制， 而不像从外部环境中吸 入新鲜空气那样， 又加之燃料也可独立地自由控制， 因此该系统可方便地形成稀薄的 混合气。 接着氧化剂和燃料供给装置 13喷射的燃料在正时定容燃烧器 1中有火花塞
29 点燃， 边混合边燃烧。 这里燃料与氧化剂集中在燃烧室中的一空间范围内， 可将 燃烧充分燃尽， 不会形成碳烟。燃烧完成后缸内平均温度较常规柴油机和汽油机缸内 的平均温度高， 而又不会生成 N0X。 通过正时装置 15使燃烧过程、 进气过程、 膨胀过 程既关联又相互独立， 氧化剂进入正时定容燃烧器 1时， 正时定容燃烧器 1与膨胀机 2相隔离， 没有工质交换； 氧化剂与燃料混合燃烧时， 正时定容燃烧器 1与进气过程 及膨胀机 2相隔离， 极度接近定容燃烧。燃料和氧化剂在正时定容燃烧器 1中燃烧生 成二氧化碳和水， 并与其他未参与燃烧的第一类工质一起受热形成高温气体， 从正时 定容燃烧器 1出口排出进入膨胀机 2。 到此， 工质在定容燃烧室完成正时定容燃烧加 热过程， 如图 4中的 h-i过程。
设循环中氧化剂体积与第一类工质体积（第一类工质与氧化剂的总体积）的比值 为 y， 即：
Figure imgf000017_0001
式中 为循环中氧化剂的体积， 为第一类工质的体积， 此处假定 ^ = 25 假定燃料分子式中只有 C和 Η元素， 并且 n/m的值为 ， 燃烧过程中 Q2过量空 气系数为《， 且《≥1 ;
Cn Hm + (n+— )02 = nC02 +— H20+q
n m 4 2 2
式中， n为燃料分子中碳原子数， m为燃料分子中氢原子数， 9为燃烧释放的热
燃烧完成后水认为是气态， 第一类工质在燃烧后的所占体积分数 计算公式为:
Figure imgf000017_0002
h-i正时定容燃烧过禾 '王; :
w7 = q
com— eff x (1 - hi _ comb) + cv(h) xTh ] ÷ cv(i)
Figure imgf000018_0001
式中， ^为工质在状态点 i时的温度，单位为 κ; q为燃料当量热值，单位为 kj/kg; eom_eff为燃烧效率； hl - eomb为定容燃烧室散热损失率； e V (w为工质在状态点 h 时的定容比热，单位为 kJ/kg，K; 《为工质在状态点 i时的定容比热，单位为 kJ/kg-K; 为工质在状态点 i时的压力， 单位为 MPa。
步骤 4、 绝热膨胀过程
正时定容燃烧结束后， 正时定容燃烧器 1与进气过程相隔离， 从正时定容燃烧器 1中排出的高温燃气经连接管路 PJ7进入膨胀机 2进行充分膨胀做功，膨胀机 2在高 温高压的燃气推动下对外输出机械功， 同时通过传动轴 16带动一级压缩机 6、 二级 压缩机 8和三级压缩机 10旋转， 为各级压缩机提供压缩功。 在此， 燃气在膨胀机 2 中完成膨胀做功， 如图 4中的 i-j过程。
状态点 j热力参数-
τ -τ
τ ■+Z
hte3 式中， 为工质在状态点 j时的压力， 单位为 MPa; 为工质在膨胀过程的膨胀 比; 为工质在状态点 j时的温度， 单位为 κ。
j一级膨胀过 ： w0 ) lOOOv; ( — ps ) （1— hi _ loss)
Figure imgf000018_0002
式中， W8为一级膨胀过程的过程比功， 单位为 kj/kg; 分别为工质在状态点 i的定压比热， 单位为 kj/kg，K; ep«为 i-j过程的等效定压比热； vi为工质在状态点 i时的比容， 单位为 m3/kg; hl -lQSS为一级膨胀机的散热损失率。
步骤 5、 后冷却过程
从逆流换热装置 3流出的燃烧废气的温度约为 170~180°C， 需要进一步冷却， 其 经连接管路 P319进入后冷却器 4。膨胀机流出的第一类工质和第二类工质在后冷却器 4中得到充分冷却， 温度可接近环境温度， 其中的水蒸气部分得到冷凝， 这起到一定 程度的脱水作用。在此， 燃烧废气在后冷却器 4中完成充分冷却和实现初步脱水， 如 图 4中的 k-1过程。
状态点1热力参数：
R = Pk "htp5
T; = Tk - hte5 x (Tk - T0) 式中， Pl为工质在状态1点时的压力， 单位为 MPa; htP5为工质通过后冷却器的 压力损失， 单位为 MPa; 为工质在状态点 h时的温度， 单位为 K; 1\为工质在状态 点1时的温度， K; hte5为后冷却器的换热效能。
i -k后冷却过程功：
W10 = Cp(l)Tl - Cp(k)Tk 式中， WlQ为后冷却器的过程比功， 单位为 kj/kg; cp« , ep("分别为工质在状态 点 k和 1的定压比热， 单位为 kJ/kg-K。
步骤 6、 二氧化碳与水脱除过程
从后冷却器 4排出的燃烧废气经连接管路 P420流入二氧化碳和水脱除装置 5，在 装置 5中彻底脱除二氧化碳或者吸收部分多余的二氧化碳，同时进一步脱除燃烧废气 中的水分，该类工质实现开式循环， 得到适量的较为纯净的第一类工质。 从二氧化碳 和水脱除装置 5中流出的燃烧废气转变为新鲜的第一类工质， 经连接管路 P521再次 返回到一级压缩机 7的入口处， 开始下一循环， 即该类工质实现闭式循环。 到此， 燃 烧废气完成了脱二氧化碳和水， 如图 4中的 1-a过程。
目前， 除二氧化碳和水有两种常用方法， 一是采用升压降温到二氧化碳超临界点 (温度在 31度，压力 7. 18MPa)， 此时二氧化碳为液体， 然后与水一起被排除； 二是 直接排水法， 通过将二氧化碳溶解于水中排除。
状态点 a热力参数：
Pa = Pl -{C + (l-C) - (100 - 7d )}
式中， Pl为工质在状态1点时的压力， 单位为 MPa; 为第一类工质的在燃烧后 的体积比， 二氧化碳和水总的脱除效率百分数， htP5为工质通过后冷却器的压力 损失， 单位为 MPa; 为工质在状态点 h时的温度， 单位为 K; hte5为后冷却器的换 热效能。
通过上述 6个步骤完成一次半闭式正时定容热力循环， 之后继续重复上述步骤。
整个循环热效率计算：
膨胀做功 -n级压缩耗功之和
循环热效率:
燃料热量输入
当忽略扫入膨胀过程少量的新鲜空气时：
膨胀做功 = (11— ωτ』 η级压缩耗功之和二 ^! ^1^ -l) + cn P((cc) (a -l) + cn P((ee)) (a — 1) + 当忽略燃料质量的加入时:
燃料热量输入 = Cv(0T「 cvΐ( τh),Th
k -1 k3 -1 k5 -1
(Cv^Ti- („ (cp(a)Ta(«k' -l) + cp(c)Tc(ak3 -l) + cp(e)Te(a ks -1) + ···) 所以， Cv(i)Ti ev(h)Th 假设： a) TH =TJ
(2) PJ = P
(3)其余损失忽略。
由以上 3个假设， 可得到:
Figure imgf000020_0001
τ
Τ; Τ; Ρ; Ρ; X 2)L = (ZL Pi n(l— k2)
即 T. Ph 即
Figure imgf000020_0002
把上两式代入效率计算式: η·^(α Kl -1)
?7 = 1- Cv(0 式中， 为压缩过程 （低温段） 比热比 （假设不变）； ^为膨胀过程 （高温段） 的比热比； 为单级增压比； n为压缩级数； 为外部环境温度， 单位为 K; Ti为燃 烧过程后温度， 单位为 K; ep(a)为工质在状态点 a时的定压比热， 单位为 kJ/kg-K; ep(h)为工质在状态点 h时的定压比热， 单位为 kJ/kg，K; 为工质在状态点 i时的 定容比热， 单位为 kJ/kg-K。
完成所述半闭式正时定容热力循环， 实现目标热效率。本发明采用了实现该热力 循环的半闭式正时定容热力系统， 其结构和功能有特殊的要求和设计。该热力系统包 括采用多级适度等温压缩装置、 稳压调压装置、 逆流换热装置、 正时定容燃烧器、 绝 热膨胀机、再循环工质冷却装置和二氧化碳与水脱除装置， 该热力系统并设有一套的 氧化剂供给装置和一套正时装置 15， 使该热力循环热效率高， 燃烧排放污染物少， 工作柔和， 排气噪音小， 且不需要从外部环境中吸入新鲜空气。
第一类工质经过所述多级压缩级间冷却过程， 其中， 级间冷却对前一级压缩与后 一级压缩之间的工质进行冷却， 通过稳压和调压作用后经历逆流换热过程 I， 吸收余 热实现等压加热过程，然后，第一类工质、氧化剂和燃料经历所述正时定容燃烧过程， 完成正时定容燃烧过程后， 经历所述绝热膨胀过程对外做功， 再经历所述逆流换热过 程 II， 将绝热膨胀做功后工质的余热传递给稳压调压装置流出的第一类工质， 有助 于提高热能回收利用率。 经逆流换热过程 II后的工质经历所述后冷却过程， 将工质 进一步冷却， 再经过所述脱除二氧化碳和水过程， 脱除第二类工质， 余下的第一类工 质开始下一个热力循环。
为实现上述热力循环的多级压缩级间冷却过程的装置可以有多种形式：容积式压 缩机、速度式压缩机，本发明技术解决方案可以采用：转子式压缩机、逆流换热装置、 燃烧室、 转子式膨胀机。
转子式发动机具有结构紧凑、 运转平稳的特点， 由于其缺陷（压缩比大， 密封环 境恶劣）， 并没有得到广泛的应用。 应用转子式发动机的原理来压缩第一类工质， 增 压比在 2. 0~3. 0之间， 是低增压比压缩， 也是低温压缩， 克服了转子式发动机燃烧做 功时活塞环磨损快， 活塞热应力大、 难以密封等缺点， 为充分利用其优点， 弥补其缺 陷， 本发明可应用转子压缩机。转子压缩机结构如图 8所示， 而定容燃烧室则采用正 时定容燃烧器， 其结构和原理将在下文叙述。 所述转子压缩机结构形成三个压缩腔， 工质首先经过一级压缩进气口 61， 经过 一次压缩后， 从一级压缩排气口 62排出， 经过中间冷却过程后， 再次进入二级压缩 进气口 63， 经过二次压缩后， 从二级压缩排气口 64排出， 经过二级中间冷却后， 然 后进入三级压缩进气口 65， 最后从三级压缩排气口 66排出， 其中的动力来自于压缩 机旋转驱动轴 68输出的扭矩， 压缩机内腔转子 67固定在压缩机旋转驱动轴 68上随 着轴同步旋转， 压缩机联动装置 69沿着压缩机内腔转子 67轮廓运动， 这样起到密封 作用。这样充分利用了转子式发动机压缩效率高的特点， 又由于一个压缩机可以实现 两次压缩， 同时还可以把结构做得十分紧凑。
所述热力系统的供氧设有一套氧化剂供给装置 12， 氧化剂供给装置 12负责为定 容燃烧室提供所需要的氧化剂， 使得该热力系统不需要从外部环境（大气）中吸入空 气。这也正是该热力系统不需要从环境中吸入空气的原因。其结构示意图如图 7所示， 该装置含有储氧罐 1201、减压阀 1202、流量控制阀 1203、单向阀 1204、压力表 1205、 连接管 1206和管路 1207。 该氧化剂供给装置 12通过管路 1207与混合喷射器 14相 连， 并通过流量控制阀 1203控制供氧量。该实施例中， 氧化剂供给装置 12负责为定 容燃烧室提供所需要的氧化剂， 使得该热力系统不需要从外部环境（大气）中吸入空 气。 该装置含有储氧罐 1201、 减压阀 1202、 流量控制阀 1203、 单向阀 1204、 压力表 1205、 连接管 1206和管路 1207。 这也正是该热力系统不需要从环境中吸入空气的原 因。 氧化剂供给量由燃料喷入量和正时定容燃烧器 1中的最高燃烧发生温度来确定， 即由稀燃程度来决定， 而且不同组分的第一类工质的最高燃烧发生温度不同。
所述稳压调压过程是设有一套稳压调压装置 11， 该装置具有一定的容积， 是定 容燃烧室容积的十倍左右。该装置一方面维持稳定的压力和流量， 同时还可以调节整 个系统的负荷， 保证系统间歇性做功和持续稳定工作； 另一方面为原动机在启动时提 供所需的工质。
所述正时定容燃烧过程的正时定容燃烧系统， 其结构如图 9所示， 包括正时装置 15、 正时定容燃烧器 1， 所述正时装置 15包括正时驱动装置 154、燃烧室控制阀门 I 151、燃烧室控制阀门 II 152，所述正时定容燃烧器 1包括混合喷射器 14、进气道 112、 定容燃烧室、 排气道 113。 所述定容燃烧室包括燃烧室格栅 111、 燃烧室瓦块式绝热 内壁 114， 通过所述燃烧室格栅 111实现均匀燃烧， 所述燃烧室瓦块式绝热内壁 114 是由具有绝热涂层材料的瓦块式结构搭接而成， 可以承受高温差变化， 也能减少热能 的散失。 正时驱动装置 154通过传动装置直接控制所述燃烧室控制阀门 I 151、 燃烧 室控制阀门 II 152和控制阀门 III153的开启和关闭的时间。控制阀门 I 151、控制阀门 II 152、 控制阀门 III153和等温压缩过程装置 30及充分膨胀过程装置 314通过正时驱 动装置 124相互关联， 实现按时序的运转。 当正时定容燃烧系统内燃烧过程结束时， 所述燃烧室控制阀门 II 152开启， 正时定容燃烧系统内排气过程开始， 高温高压工质 推动膨胀机做功， 当膨胀后工质压力低于稳压调压装置内工质压力时， 所述燃烧室控 制阀门 1 151开启， 正时定容燃烧系统内进气过程、 扫气过程开始， 当膨胀机内进入 的工质与稳压调压装置的工质相同时， 正时定容燃烧系统内扫气过程结束， 所述燃烧 室控制阀门 II 152关闭， 正时定容燃烧系统内定容燃烧室内的工质压力和稳压调压装 置内的工质压力相同时， 所述燃烧室控制阀门 I 151关闭， 完成正时定容燃烧系统内 进气过程， 此时所述燃烧室控制阀门 I 151和燃烧室控制阀门 II 152都是关闭状态， 通过所述混合喷射器 14喷射燃料混合物后，开始正时定容燃烧系统内定容燃烧过程。 当正时定容燃烧系统内扫气完成时， 所述控制阀门 III153开启， 当正时定容燃烧系统 内排气过程开始前， 所述控制阀门 III153关闭。
所述正时装置 15的开启和关闭实现所述正时定容燃烧过程、 多级压缩级间冷却 过程和多级绝热膨胀过程按预设时序协同工作， 定容燃烧室排气时与进气脱离关联， 进气时与排气脱离关联， 燃烧时与进气、 排气脱离关联， 使加热过程、 进气过程、 排 气过程既相互独立又相互关联。燃烧限定在定容燃烧室的空间范围内， 达到严格意义 定容燃烧的目的， 由于压缩和膨胀相互独立， 通过设定正时装置 15的气门定时， 控 制进排气门的开启和关闭时间， 实现超长时间燃烧， 以 360°为一个循环周期计， 燃 烧持续期最高至 210° ， 而一般内燃机的燃烧持续期仅为 20~60° ， 又由于燃烧时间 长， 故燃烧放热率和压力升高率小， 故燃烧柔和。
在该正时定容燃烧系统中定容燃烧器的结构如图 10所示， 定容燃烧室具有带格 栅的结构， 达到均匀燃烧的目的， 由于燃烧时间长， 燃烧混合物混合均匀， 使燃料充 分燃烧，有效抑制 HC、 CO和 PM的产生，通过稀薄燃烧方式，使燃烧温度在 1900-2100K 之间， 有效抑制 N0J产生。 定容燃烧室还带有由具有绝热涂层材料的瓦块式结构搭 接而成的燃烧室瓦块式绝热内壁 114， 可以承受高温差变化， 也能减少热能的散失。 同时定容燃烧室的进排气门不是气阀式，而是球形式，这样的结构能使气门尽快开启， 以最大程度减少工质流过气门时产生的节流损失。 另外， 混合喷射器 14深入到定容 燃烧室内腔， 并且有多个燃料喷射孔 141， 实现喷射时燃料尽快达到均匀分布。 所述绝热膨胀过程使用的膨胀机可以有多种形式： 活塞容积式膨胀机、涡轮膨胀 机等等， 本发明适用于转子式膨胀机。 由于活塞式膨胀机需要把活塞的直线运动转化 为曲轴的旋转运动， 热功转化效率不高， 而涡轮膨胀机没有容积式膨胀机效率高， 故 采用转子式膨胀机。 另一方面， 本发明通过正时装置 15实现定容燃烧， 燃烧后的高 温高压气体需要按时进入膨胀机， 由于采用转子形式膨胀机， 故只要控制好转子的正 时， 便可以使高温高压气体进行最大程度做功， 而且不用新增排气阀门， 减少了做功 的气体的节流损失。 由于是定容燃烧， 燃烧后的压力要远高于燃烧前的压力， 膨胀后 的压力则与压缩前的压力接近， 这样使得整个系统的膨胀比要大于要所比。
通过所述正时装置 15独立于所述正时定容燃烧过程， 此过程有别于传统四冲程 内燃机的工作过程， 传统工作过程中压缩与膨胀相关且不独立， 使膨胀比不能太大， 而本发明通过正时装置 15使进气、 加热、 排气有序协同工作， 能够实现充分膨胀， 膨胀过程的膨胀比大于压缩过程的增压比， 使膨胀尽可能实现充分膨胀。
参照图 5和图 6， 本实施例中包含多级压缩级间冷却装置， 如一级压缩机 6、 一 级中冷器 7、 一级压缩机 6与一级中冷器 7的连接管路 P622、 一级中冷器 7与二级压 缩机 8的连接管路 P723、 二级压缩机 8、 二级中冷器 9、 二级压缩机 8与二级中冷器 9的连接管路 Ps24、三级压缩机 10、二级中冷器 9与三级压缩机 10的连接管路 P925， 第一类工质在多级压缩级间冷却装置实现等效的等温压缩，在本实施例中所述压缩机 为转子压缩机； 包含稳压调压装置 11， 该装置与多级压缩级间冷却装置的第三级压 缩机 10经连接管路 Ρω26相连， 第一类工质在该装置中储存充分高的压力； 包含逆流 换热装置， 逆流换热装置 3与稳压调压装置 11经连接管路 Pu27相连， 从稳压调压装 置 11流出的第一类工质从燃烧废气的出口端进入逆流换热装置 3中， 吸热后从燃烧 废气的入口端流出； 包含气体混合装置， 混合喷射器 14与逆流换热装置 3经连接管 路 P1228相连，从逆流换热装置 3中流出的第一类工质在混合喷射器 14中与来自氧化 剂供给装置 12的氧化剂充分均匀混合； 包含正时定容燃烧器 1， 混合喷射器 14的出 口在正时定容燃烧器 1内， 从混合喷射器 14中流出的氧化剂和燃料进入正时定容燃 烧器 1中再次混合， 可燃混合气在正时定容燃烧器 1中由火花塞 29辅助点燃， 燃烧 后受热膨胀，并被排出；包含膨胀机 2，膨胀机 2与正时定容燃烧器 1经连接管路 PJ7 相连， 从正时定容燃烧器 1排出的高温燃气进入膨胀机 2中进行充分膨胀做功， 并通 过传动轴 16对外输入功， 高温燃气做功后转变为燃烧废气， 其经连接管路 P218进入 逆流换热装置 3中放热， 在本实施例中所述膨胀机 2为转子膨胀机； 还包含后冷却装 置， 后冷却器 4与逆流换热装置 3经连接管路 P319相连， 燃烧废气在后冷却器 4中 充分释放热能； 最后包含脱二氧化碳和水装置， 脱二氧化碳和水装置 5与后冷却器 4 经连接管路 P420相连，脱二氧化碳和水装置 5与一级压缩机 6经连接管路 P521相连; 按照上述连接次序形成本专利的一个实施例的系统装置。
其他实施方式：所述一种原动机的半闭式正时定容热力循环方法也可以包括单级 压缩过程、 单级中冷过程或多级膨胀过程， 热力循环系统可以是单级压缩机、 多级膨 胀机， 其工作原理与特征均与本实施例的相同。

Claims

权 利 要 求
1. 一种原动机的半闭式正时定容热力循环方法， 其特征在于： 该热力循环方法 以转子发动机的转子自转角度 360°或二冲程往复发动机的输出轴旋转角度 360°或四 冲程往复发动机的输出轴旋转角度 720°为一个循环周期， 其采用两类工质， 第一类 工质是参与热力循环全部过程的工质， 在定容燃烧室内燃烧后通过膨胀机做功， 做功 完成后返回到一级压缩机入口， 继续参与下一次热力循环； 第二类工质是正时定容燃 烧过程前加入的氧化剂和燃料而产生的， 并参与正时定容燃烧过程、 绝热膨胀过程、 逆流换热过程、 后冷却过程的， 最后在二氧化碳与水脱除过程中脱除的工质， 该工质 不再参与下一次热力循环：
步骤 1、 进行多级压缩级间冷却过程： 该过程中， 对第一类工质进行多级压缩， 并通过级间冷却以减少压缩耗功， 对第一类工质压缩终了压力进行稳压调压；
步骤 2、 进行逆流换热过程： 该过程中， 稳压调压后的第一类工质在进入定容燃 烧室前回收上一次热力循环膨胀做功后的第一类工质和第二类工质的焓，直接收益热 量后参与本次热力循环，以提高定容燃烧室中本次热力循环的第一类工质和第二类工 质的初始温度；
步骤 3、 进行正时定容燃烧过程： 该过程中， 第一类工质经过逆流换热过程后进 入定容燃烧室，氧化剂供给装置和燃料供给装置将氧化剂和燃料通过混合喷射器喷入 定容燃烧室并开始正时定容燃烧， 定容燃烧室容积不变；
步骤 4、 进行绝热膨胀过程： 该过程独立于多级压缩级间冷却过程和正时定容燃 烧过程， 定容燃烧室排出的工质经膨胀对外输出功， 绝热膨胀过程的膨胀比大于压缩 过程的增压比；
步骤 5、 进行后冷却过程： 该过程中， 膨胀做功后的第一类工质和第二类工质经 过逆流换热装置后进入后冷却器， 进一步冷却至环境温度；
步骤 6、 进行二氧化碳和水脱除过程： 该过程中， 将正时定容燃烧过程产生的二 氧化碳和水脱除， 余下的工质继续参与下一次热力循环。
2. 根据权利要求 1所述的原动机的半闭式正时定容热力循环方法， 其特征在于: 第一类工质包括惰性气体、二氧化碳或氮气及及经二氧化碳与水脱除过程后残存的部 分工质。
3. 根据权利要求 1所述的原动机的半闭式正时定容热力循环方法， 其特征在于: 多级压缩级间冷却过程中， 只需压缩第一类工质。
4. 根据权利要求 1所述的原动机的半闭式正时定容热力循环方法， 其特征在于: 多级压缩级间冷却过程和绝热膨胀过程分别在独立装置中完成，通过正时装置相互关 联。
5. 根据权利要求 1所述的原动机的半闭式正时定容热力循环方法， 其特征在于: 所述热力循环的热效率为：
V-i
Λ cv(1) Ta
η = 1 -
Cv(l) 式中， ki为压缩过程比热比； k2为膨胀过程的比热比； 为单级增压比； n为压 缩级数； Ta为外部环境温度，单位为 K; Ti为燃烧完成后状态 i点温度，单位为 K; eP(a) 为工质在多级压缩级间冷却过程前状态点 a时的定压比热，单位为 kJ/kg，K; eP(h)为 工质在定压燃烧过程前状态点 h时的定压比热， 单位为 kJ/kg，K; ev(1)为工质在绝热 膨胀过程前状态点 i时的定容比热， 单位为 kJ/kg，K; W为工质在定压燃烧过程前 状态点 h时的定容比热， 单位为 kJ/kg-K。
6. 一种应用权利要求 1所述的原动机的半闭式正时定容热力循环方法的三级压 缩两级中冷热力循环方法， 其特征在于：
步骤 1、 进行三级压缩级间冷却
(1) 以一级压缩机 （6) 入口端 a为始点， 第一类工质经一级压缩机 （6) 增压 后， 第一类工质压力提高到 2.0~3.0倍； 之后经连接管路 P6 (22) 进入一级中冷器 (7) 得到冷却， 完成第一次压缩及冷却过程；
(2)第一类工质经连接管路 P7 (23) 进入二级压缩机 （8)进行第二次增压， 第 一类工质压力提高到一级中冷器（7)出口压力的 2.0-3.0倍，之后经连接管路 Ps(24) 进入二级中冷器 （9) 得到冷却， 完成第二次压缩及冷却过程；
(3)第一类工质经连接管路 (25) 进入第三级压缩机 （10) 进行第三次增压， 第一类工质压力提高到二级中冷器 （9) 出口压力的 2. 0~3. 0倍， 完成第三次压缩过 程； 之后直接进入稳压调压装置 （11 ) 维持稳定的压力；
步骤 2、 进行逆流换热过程： 该过程中， 从稳压调压装置 （11 )流出的第一类工 质经连接管路 Pu ( 27) 进入逆流换热装置 （3) 中进行逆流换热， 热量来自于从膨胀 机（2) 中排出的工质余热， 排出的工质在逆流换热装置（3) 中放热得到冷却； 从膨 胀机（2)流出的燃烧废气经连接管路 P2 ( 18)进入逆流换热装置（3) 中进一步释放 热量， 并将热量传递给从稳压调压装置流向正时定容燃烧器 （1 ) 的第一类工质， 使 余热直接被利用到热力循环中；
步骤 3、 进行正时定容燃烧过程： 该过程中， 从逆流换热装置 （3) 流出的第一 类工质经连接管路 P12 ( 28) 进入正时定容燃烧器 （1 )， 氧化剂供给装置 （12) 和燃 料供给装置 （13)， 将氧化剂和燃料通过混合喷射器 （14) 喷入正时定容燃烧器 （1 ) 并燃烧， 生成第二类工质中的二氧化碳和水；
步骤 4、 进行绝热膨胀过程： 该过程中， 从正时定容燃烧器 （1 ) 中排出的高温 高压工质经连接管路 ( 17) 进入膨胀机 （2) 进行充分膨胀做功；
步骤 5、 进行后冷却过程： 该过程中， 从逆流换热装置 （3) 流出的第一类工质 和第二类工质经连接管路 P3 ( 19) 进入后冷却器 （4) 进行冷却后， 温度降低至环境 温度；
步骤 6、 进行二氧化碳和水脱除过程： 该过程中， 从后冷却器 （4) 流出的工质 经连接管路 P4 ( 20) 进入二氧化碳和水脱除装置 （5) 中脱除第二类工质， 余下的第 一类工质经连接管路 P5 ( 21 ) 参与下一次热力循环。
7. 根据权利要求 6所述的三级压缩两级中冷热力循环方法， 其特征在于： 第一 类工质与通过混合喷射器 （14) 喷入的氧化剂和燃料进入正时定容燃烧器 （1 ) 时， 不会进入膨胀机（2)， 通过正时装置（15)控制进排气门的开启和关闭时间， 实现超 长时间燃烧， 以 360°为一个循环周期计， 燃烧时间最高至 210° ， 压缩过程、 膨胀过 程与燃烧过程分别在独立的装置内完成， 并通过正时装置 （15) 相互关联。
8. —种应用权利要求 1所述的原动机的半闭式正时定容热力循环方法的热力循 环系统， 其特征在于： 包括多级压缩级间冷却装置、 稳压调压装置 （11 )、 逆流换热 装置 （3 )、 氧化剂供给装置 （12)、 燃料供给装置 （13)、 混合喷射器 （14)， 正时定 容燃烧器 （1 )、 膨胀机 （2)、 后冷却器 （4)、 二氧化碳与水脱除装置 （5)， 其中， 多 级压缩级间冷却装置对工质实现压缩及中冷，稳压调压装置（ 11)经连接管路 Ρ (26) 与多级压缩级间冷却装置的末级压缩机相连， 逆流换热装置（3)经连接管路 Pu (27) 与稳压调压装置 （11) 相连， 正时定容燃烧器 （1) 经连接管路 P12 (28) 与逆流换热 装置 （3) 相连；
其中， 氧化剂供给装置（12)和燃料供给装置（13)将氧化剂和燃料通过混合喷 射器 （14) 喷入正时定容燃烧器 （1) 混合并燃烧， 生成第二类工质中的二氧化碳和 水； 正时定容燃烧器 （1) 经连接管路 (17) 与膨胀机 （2) 相连； 在膨胀机 （2) 中做功后经连接管路 P2 (18) 与逆流换热装置 （3) 相连；
其中， 第一类工质经多级压缩级间冷却装置后进入稳压调压装置 （11)， 从稳压 调压装置 （11) 流出的第一类工质进入逆流换热装置 （3) 吸热后进入正时定容燃烧 器（1)， 氧化剂供给装置（12)和燃料供给装置（13)提供的氧化剂和燃料经混合喷 射器 （14) 喷入正时定容燃烧器 （1) 边混合边燃烧产生第二类工质， 与第一类工质 一并进入膨胀机 （2) 膨胀做功， 并通过传动轴 （16) 对外输出功， 做功后经连接管 路 P2 (18)进入逆流换热装置（3) 中放热， 之后从逆流换热装置 （3)流出的工质进 入后冷却器 （4) 得到冷却， 之后经过二氧化碳与水脱除装置 （5)， 第二类工质被脱 除， 第一类工质开始下一次热力循环。
9. 根据权利要求 8所述的热力循环系统， 其特征在于： 正时定容燃烧系统， 包 括正时装置（15)、正时定容燃烧器（ 1 );所述正时装置（ 15)包括正时驱动装置（154)、 燃烧室控制阀门 I (151)、 燃烧室控制阀门 II (152)、 控制阀门 111 (153); 所述正 时定容燃烧器（1)包括混合喷射器（14)、进气道（112)、定容燃烧室、排气道（113); 所述正时驱动装置 （154) 通过传动装置直接控制所述燃烧室控制阀门 I (151)、 燃 烧室控制阀门 II (152)和控制阀门 III (153) 的开启和关闭的时间； 当正时定容燃烧 系统内燃烧过程结束时， 所述燃烧室控制阀门 II (152) 开启， 正时定容燃烧系统内 排气过程开始， 高温高压工质推动膨胀机 （2) 做功， 当膨胀后工质压力低于稳压调 压装置内工质压力时， 所述燃烧室控制阀门 I (151) 开启， 正时定容燃烧系统内进 气过程、 扫气过程开始， 当膨胀机（2) 内进入的工质与稳压调压装置的工质相同时， 正时定容燃烧系统内扫气过程结束， 所述燃烧室控制阀门 II (152) 关闭， 正时定容 燃烧系统内定容燃烧室内的工质压力和稳压调压装置内的工质压力相同时，所述燃烧 室控制阀门 I (151) 关闭， 完成正时定容燃烧系统内进气过程， 此时所述燃烧室控 制阀门 I ( 151 ) 和燃烧室控制阀门 II ( 152) 都是关闭状态， 所述混合喷射器 （14) 喷射燃料混合物后， 开始正时定容燃烧系统内定容燃烧过程； 当正时定容燃烧系统内 扫气完成时， 所述控制阀门 III ( 153)开启， 当正时定容燃烧系统内排气过程开始前， 所述控制阀门 III ( 153) 关闭；
所述定容燃烧室包括燃烧室格栅（111 )、 燃烧室瓦块式绝热内壁（114)， 通过所 述燃烧室格栅（111 )实现均匀燃烧， 所述燃烧室瓦块式绝热内壁（114)是由具有绝 热涂层材料的瓦块式结构搭接而成。
10. 根据权利要求 8所述的热力循环系统， 其中： 多级压缩级间冷却装置设置为 三级压缩和二级中冷， 工质首先经过一级压缩进气口 （61 )， 经过一次压缩后， 从一 级压缩排气口 （62) 排出， 经过中间冷却过程后， 再次进入二级压缩进气口 （63)， 经过二次压缩后， 从二级压缩排气口 （64)排出， 经过二级中间冷却后， 然后进入三 级压缩进气口 （65)， 最后从三级压缩排气口 （65) 排出。
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