WO2012100393A1 - Critical low-entropy mixed combustion circulating thermal power system - Google Patents

Abstract

Disclosed is a critical low-entropy mixed combustion circulating thermal power system, comprising a working mechanism (1), a continuous combustion chamber (2), a liquid oxidant source (3), and a fuel source (4). The liquid oxidant source (3) is in communication with the combustion chamber (2) through an oxidant high-pressure supply system (301), the fuel source (4) is in communication with the continuous combustion chamber (2) through a fuel high-pressure supply system (401), an oxidant in the liquid oxidant source (3) enters the continuous combustion chamber (2) in the form of a high-pressure liquid, and fuel in the fuel source (4) enters the continuous combustion chamber (2) at a high pressure. The oxidant high-pressure supply system (301), the fuel high-pressure supply system (401) and the continuous combustion chamber (2) are tolerant to a pressure greater than 15 MPa. The continuous combustion chamber (2) is in communication with at least one working mechanism (l), and the working mechanism (l) outputs power to the exterior. The critical low-entropy mixed combustion circulating thermal power system has the advantage of high efficiency, energy saving, and low emission. Also disclosed is a method for improving the efficiency and environmental protection performance of a critical low-entropy mixed combustion circulating thermal power system.

Description

 Description

 Critical low entropy co-firing cycle thermodynamic system

Technical field

 The invention relates to the field of thermal energy and power, and in particular to a thermodynamic system.

Background technique

In 1769, the birth of the external combustion engine directly triggered the first industrial revolution of mankind, and also created the Empire of Great Britain. The birth of the gasoline engine in 1883 and the birth of the diesel engine in 1897 marked the beginning of the era of man-made combustion from the era of external combustion. The internal combustion engine represented by gasoline engine and diesel engine has built the dynamic foundation of modern civilization and carried countless human dreams. It can be seen that both the external combustion engine and the internal combustion engine have made invaluable contributions to the progress of human civilization. Today, the design, R&D and production levels of a country's internal combustion and external combustion engines are the basic components of the country's overall national strength and a sign of the country's industrial level. All developed countries have invested in the field of internal combustion and external combustion engines. All engine R&D and manufacturing companies that represent the world level are also affiliated with developed countries. However, due to the thermodynamic circulation mode of the external combustion engine and the limitation of the thermodynamic circulation mode of the internal combustion engine, only part of the heat in the two circulation systems participates in the work cycle and also causes the value of the external combustion cycle system (ie, high temperature). temperature heat source) and a low combustion cycle system 7 ^ ₂ (i.e., the exhaust gas temperature) the problem of high, but can not solve the cause pollution problems, ultimately resulting in both an external combustion engine can not or thermal efficiency of the thermal power system (The ratio of output power to fuel calorific value) has been greatly improved in essence, and the problem of emission pollution cannot be fundamentally solved. In fact, the use of these two thermodynamic cycles to convert thermal energy to fossil energy and biomass energy is not only a huge waste of energy, but also a huge damage to the environment.

 It can be seen that a new cycle must be invented to substantially improve the thermal efficiency of the thermodynamic system and solve the problem of emissions.

Summary of the invention

The so-called co-firing cycle thermodynamic system of the present invention refers to a thermodynamic system in which all heat (or nearly all heat) after combustion of the fuel is involved in the work cycle. In order to realize all the heat (or almost all heat) after the combustion of the fuel, all the ways to participate in the work cycle can be used. One is to insulate the combustion chamber, and the other is to use the original working fluid to heat the combustion chamber wall in the combustion chamber. The absorption is brought back to the combustion chamber. For example Thermal engines, combined cycles, etc. are all forms of co-firing.

The so-called low entropy co-combustion cycle thermal power system of the present invention means that all heat (or nearly all heat) after combustion of the fuel is all involved in the work cycle, and the maximum pressure of the combustion chamber is significantly higher than that of the combustion chamber of the conventional thermodynamic system. The highest pressure. The temperature r ₂ of the low-temperature heat source of this system is much lower than that of the conventional internal combustion engine, and the temperature of the high-temperature heat source is 7; it is much higher than the highest temperature of the traditional external combustion cycle thermodynamic system, and the efficiency is significantly higher than the traditional heat. The efficiency of the power system. This system is the third generation of thermal power system (or third generation engine) after the external combustion cycle thermal power system and the internal combustion cycle thermal power system. The so-called critical low-entropy co-firing thermal power system refers to a low-entropy co-firing thermodynamic system in which the temperature and pressure in the combustion chamber are close to or exceed the critical temperature and critical pressure of the working medium.

In the critical low-entropy co-combustion cycle thermodynamic system disclosed in the present invention, the pressure and temperature of the original working fluid (ie, the working medium before combustion, including the oxidant, the fuel, the expanding agent, and the gas liquefaction) and the components are Independently controlled, so the maximum pressure and maximum temperature of the combustion chamber can be independently controlled, that is to say, this establishes the indoor working fluid pressure through the gas compression process in the traditional thermodynamic system (the so-called indoor original working fluid pressure means that it will burn The process of the combustion chamber pressure, which should meet the design requirements, is completely different. In the traditional thermodynamic system, the pressure and temperature of the original working fluid are interrelated, and the pressure is high, and the maximum pressure of combustion in the critical low-energy co-firing thermal power system disclosed in the present invention is not high. This means that the maximum temperature of the combustion chamber is high. To this end, scientifically and effectively adjust the maximum pressure and maximum temperature of the combustion chamber to produce a thermodynamic system with a low temperature of 低温_{2, which is} very low, or even significantly lower than the ambient temperature. When Γ _{2 is} low to a certain value, the thermal efficiency of such a thermodynamic system may exceed 100%. This thermodynamic system with a thermal efficiency exceeding 100% is defined in the present invention as an ultra-low entropy co-combustion cycle thermodynamic system. The ultra-low entropy co-firing thermal power system does not violate the law of conservation of energy, because: the calorific value of the fuel refers to the release of the fuel after it has reached a standard state (which can be regarded as an environmental state) after being burned under standard conditions. The heat. The low temperature heat source temperature _{2 of the} supercritical low entropy mixed combustion cycle thermal power system can be close to, lower than or substantially lower than the ambient temperature (that is, the temperature under the standard state of myopia). When the temperature of the low-temperature heat source _{2 is} significantly lower than the ambient temperature, it is equivalent to having more heat to participate in the work cycle. When the temperature is low to ₂ , the excess heat can make the system output work. The amount is greater than the calorific value of the fuel, so that the thermal efficiency is greater than 100%; 2. In the ultra-low entropy co-firing thermal power system, there are lower temperature heat sources in some cases, such as liquid oxygen, liquefied fuel, liquefaction. Swell Expansion agent (liquefied carbon dioxide), the original working medium in the so-called lower temperature low-temperature heat source can absorb the heat in the environment and/or the heat in the exhaust gas that has been involved in the work during the cycle, and bring the heat into The combustion chamber participates in the work cycle, which causes the heat involved in the work cycle to be greater than the heat released by the fuel combustion, so that the external output of the system can be greater than the heat released by the fuel combustion (ie, the heat value of the fuel), The so-called thermal efficiency is higher than 100%.

 The critical low-entropy co-combustion cycle thermal power system disclosed by the present invention does not inhale from the atmosphere under normal working conditions.

 In the present invention, FIG. 18 is a graph showing the relationship between the temperature T and the pressure P of the gas working medium, and the curve indicated by 0-AH is a gas working adiabatic relationship curve passing through the zero point of the state parameter of 298 K and 0.1 MPa; For the actual state point of the gas working fluid, the curve shown by E-BD is the adiabatic relationship curve through point B. The pressures at point A and point B are the same; the curve shown by FG is through 2800K and 10MPa (that is, the current internal combustion engine is about to start The working temperature adiabatic relationship curve of the working gas working point.

 In the present invention, > = cr^ in Fig. 18 is the gas working fluid adiabatic index, which is the pressure of the gas working fluid, Γ is the temperature of the gaseous working fluid, and C is a constant.

In the present invention, the so-called adiabatic relationship includes the following three cases: 1. The state parameter of the gaseous working fluid (ie, the temperature and pressure of the working medium) is on the adiabatic relationship curve of the working fluid, that is, the state parameter of the gaseous working fluid. The point is on the curve shown by 0-A-H in Figure 18; 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 of the gaseous working fluid. The parameter point is on the left side of the curve shown by 0-AH in Figure 18. 3. The state parameter of the gas working fluid (ie, the temperature and pressure of the working medium) is on the right side of the adiabatic relationship curve of the working fluid, that is, the gas working fluid. The state parameter point is on the right side of the curve shown by 0-AH in Fig. 18, but the temperature of the gas working fluid is not higher than the temperature of the gas working fluid calculated by the adiabatic relationship plus the sum of 1000K, plus 950K, plus 900K, and 850K, plus 800K, 750K, 700K, 650K, 600K, 550K, 500K, and 450K. Add 400K sum, add 350K sum, add 300K sum, add 250K sum, add 200K sum, force 1 sum of 90K, force [] 180K, force H 1 70K, plus 1 60K, force Q 150K, force 140K sum, force B 1 30K sum, force [] 120K sum Add 1 10K sum, add 100K sum, add 90K sum, add 80K sum, add 70K sum, add 60K sum, add 50K sum, add 40K sum, add 30K and or higher than Add 20K sum, as shown in Figure 18. The actual state point of the gas working fluid is point B, point A is the point on the same adiabatic relationship curve of pressure and point B, and the temperature difference between point A and point B should be less than 1000 Κ, 900 Κ, 850 Κ, 800 Κ, 750 Κ, 700Κ, 650Κ, 600Κ, 550Κ, 500Κ, 450Κ, 400Κ, 350Κ, 300Κ, 250Κ, 200Κ, 1 90Κ, 180Κ, 1 70Κ, 1 60Κ, 1 50Κ, 140Κ, 130Κ, 120Κ, 1 10Κ, 100Κ, 90Κ, 80Κ 70 Κ, 60 Κ, 50 Κ, 40 Κ, 30 Κ or less than 20 Κ.

 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. 18 . The adiabatic process curve shown by the defect is shown in the left side of the Ε-Β-D.

 In the present invention, the so-called gas working medium to be started to work is the gas working medium that is about to enter the working mechanism.

 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.

 In the present invention, the temperature, pressure and flow rate of the original working medium entering the continuous combustion chamber are adjusted, the amount of fuel introduced into the continuous combustion chamber is adjusted, and the amount of the gaseous working medium derived from the continuous combustion chamber is adjusted, and then the adjustment is about to be adjusted. The temperature of the gaseous working fluid that starts to work is below 2000 ,, and the pressure of the gaseous working fluid that is about to start work is adjusted to 15 MPa or more, so that the temperature and pressure of the gaseous working fluid that is about to start work are in accordance with the adiabatic relationship.

 In the present invention, the fuel may be ethanol or methanol, the expansion agent is water, and the fuel source and the liquid expansion agent source are mixed raw working fluid storage tanks, and the mixed raw medium is used. The storage tank is set to an ethanol aqueous solution or an aqueous methanol storage tank.

 The critical low-entropy co-combustion cycle thermal power system disclosed by the invention has the advantages that the original working medium is independently controllable, and the fuel can be adjusted not only by the electronic control but also the oxidant and the expansion agent, so the criticality disclosed by the present invention The low-entropy co-firing thermal power system has better load response.

In the present invention, the maximum pressure (pressure after combustion) of the continuous combustion chamber is determined by the composition of the original working fluid before combustion, the total pressure, the temperature, and the heat of combustion. The singularity of the continuous combustion chamber of the present invention is greater than 15. 5 MPa, 1 6 MPa, 1 6.5 MPa, 1 7 MPa, 1 7.5 MPa, 1 8 MPa, 1 8. 5MPa, 1 9MPa, 1 9. 5MPa, 20MPa, 20. 5MPa, 21 MPa, 21. 5MPa 22MPa, 22. 5MPa, 23MPa, 23· 5MPa, 24MPa, 24, 5MPa, 25MPa, 25. 5MPa, 26MPa, 26. 5MPa, 27MPa, 27. 5MPa, 28MPa, 28. 5MPa, 29MPa, 29. 5MPa, 30MPa, 31 Pa 32MPa, 33MPa, 34MPa, 35MPa, 36MPa, 37MPa, 38MPa, 39MPa, 40MPa, 41 MPa, 42 MPa, 43 MPa, 44 MPa, 45 MPa> 46 MPa, 47 MPa, 48 MPa, 49 MPa or 50 MPa. In order to achieve the highest pressure of continuous combustion chamber design, achieve high efficiency, low pollution and low heat load, the composition of the original working fluid (adjusting the composition, the heat capacity can be adjusted), pressure, temperature and oxygen content (affecting the heat release) Comprehensive control. In other words, by controlling the state and composition of the original working medium, the purpose of controlling the state of the gas in the continuous combustion chamber after the combustion chemical reaction is achieved. The maximum temperature in the continuous combustion chamber should match the highest pressure in the continuous combustion chamber. If the maximum temperature in the continuous combustion chamber is too high to match the highest pressure, the temperature of the working fluid will be too high after the work is completed, which is harmful and unprofitable.

 The principle of the disclosed critical low-entropy co-firing thermal power system is to continuously burn the fuel by continuously introducing oxidant and fuel into the continuous combustion chamber or continuously introducing oxidant, fuel and expansion agent or continuously introducing oxidant, fuel and gas liquefaction. Continuous combustion in a continuous combustion chamber under the controllable conditions of temperature and combustion pressure, forming a gas working medium or a critical gas working medium with a relatively high pressure and moderate temperature, and directly compressing work for compression, and working after expansion The working mechanism discharges the exhaust passage of the working mechanism, the working mechanism outputs power externally, the working mechanism may be a continuously operating power turbine, and the working mechanism may also be a cylinder piston working mechanism; In the structure in which the working mechanism is a cylinder piston working mechanism, a working fluid introduction control valve is provided between the continuous combustion chamber and the cylinder piston working mechanism.

 The function of the continuous combustion chamber in the critical low-energy hybrid combustion cycle thermal power system disclosed by the invention is equivalent to the boiler of the external combustion thermodynamic system, and the fundamental difference is that: the boiler in the external combustion thermodynamic system is externally heated, so The temperature of the working fluid cannot reach a very high level, and the continuous combustion chamber disclosed by the present invention generates a gaseous working medium or a critical gaseous working medium by means of internal combustion, and a gaseous working medium or a critical state produced by internal combustion. The temperature and pressure can meet or exceed the most advanced critical, supercritical or ultra-supercritical external combustion thermodynamic systems.

The specific technical solution of the disclosed critical low-entropy co-combustion cycle thermal power system is as follows: A critical low-entropy co-combustion cycle thermal power system, comprising a work mechanism, a continuous combustion chamber, a liquid oxidant source and a fuel source, a liquid oxidant source is in communication with the continuous combustion chamber via an oxidant high pressure supply system, the fuel source being in communication with the continuous combustion chamber via a high pressure fuel supply system, the liquid oxidation An oxidant in the source of the agent enters the continuous combustion chamber in the form of a high pressure liquid, the fuel in the fuel source entering the continuous combustion chamber in the form of a high pressure, the oxidant high pressure supply system, the high pressure supply system of the fuel And the continuous combustion chamber has a pressure bearing capacity greater than 15 MPa, and the continuous combustion chamber is in communication with at least one of the working mechanisms, and the working mechanism outputs power externally.

 The critical low entropy co-firing cycle thermodynamic system further includes a source of liquid expansion agent, the source of liquid expansion agent being in communication with the continuous combustion chamber via a high pressure supply system of the expansion agent, wherein the expansion agent in the source of the liquid expansion agent is The high pressure liquid form enters the continuous combustion chamber, and the expansion agent high pressure supply system has a pressure bearing capacity greater than 15 MPa.

 A critical low-entropy co-firing thermal power system includes a work mechanism, a continuous combustion chamber, a liquid oxidant source, a fuel source, and a liquid expansion agent source, and the liquid oxidant source is heated by an oxidant high-pressure supply system and then oxidant-heated An exchanger is in communication with the continuous combustion chamber, the fuel source is in communication with the continuous combustion chamber via a high pressure fuel supply system, and an oxidant in the liquid oxidant source absorbs heat in the oxidant heat absorption heat exchanger And entering the continuous combustion chamber in the form of a high pressure gas or critical state, the fuel in the fuel source entering the continuous combustion chamber in the form of a high pressure, the liquid expansion agent source being passed through the expansion agent high pressure supply system and the a continuous combustion chamber is connected, the expansion agent in the liquid expansion agent source enters the continuous combustion chamber in a high pressure liquid state, the oxidant high pressure supply system, the fuel high pressure supply system, and the expansion agent high pressure supply The system and the continuous combustion chamber have a pressure bearing capacity greater than 15 MPa, and the continuous combustion chamber is in communication with at least one of the working mechanisms, Foreign institutional power output power.

A critical low-entropy co-combustion cycle thermodynamic system includes a work mechanism, a continuous combustion chamber, a liquid oxidant source, a fuel source, and a gas liquefaction source, and the liquid oxidant source is directly or oxidized by the oxidant through the oxidant high pressure supply system a heat exchanger in communication with the continuous combustion chamber, the fuel source being in communication with the continuous combustion chamber via a high pressure fuel supply system, the oxidant in the liquid oxidant source absorbing heat in a high pressure liquid state or in the oxidant After the endothermic gasification in the heat exchanger, the continuous combustion chamber enters the high-pressure gas state, and the fuel in the fuel source enters the continuous combustion chamber in a high pressure form, and the gas liquefaction source passes through the gas liquefaction high pressure The feeding system is further connected to the continuous combustion chamber via a gas liquefaction heat-absorbing heat exchanger, and the gas liquefied material in the gas liquefaction source enters the continuous combustion chamber in the form of a high-pressure gas state or a critical state. Said oxidant high pressure supply system, said fuel high pressure supply system, said gas liquefaction high pressure supply system and said continuous combustion chamber pressure bearing energy Greater than 1 5MPa, The continuous combustion chamber is in communication with at least one of the work mechanisms, and the work mechanism externally outputs power. Adjusting the oxidant high pressure supply system, the fuel high pressure supply system, and the structure in a structure in which the oxidant high pressure supply system, the fuel high pressure supply system, and the expansion agent high pressure supply system are provided The supply amount of the expansion agent high pressure supply system and the ratio between each supply amount causes the expansion agent in the liquid expansion agent source to be in a critical state in the continuous combustion chamber; the high pressure supply system is provided in the oxidant In the structure of the high-pressure fuel supply system and the gas liquefaction high-pressure supply system, adjusting the supply of the oxidant high-pressure supply system, the fuel high-pressure supply system, and the gas liquefaction high-pressure supply system The ratio between the delivery amount and each supply amount causes the gaseous liquefied material within the gas liquefaction source to be in a critical state within the continuous combustion chamber.

 The expansion agent in the source of the liquid expansion agent is set to water, liquid nitrogen, liquid carbon dioxide or liquid helium. The oxidant in the liquid oxidant source is set to pure liquid oxygen, oxygen-containing gas liquefied, hydrogen peroxide or aqueous hydrogen peroxide.

 The fuel in the fuel source is set to hydrogen, a combustible hydrocarbon, a combustible carbonic acid hydroxide or an aqueous flammable alcohol solution.

 The expansion agent in the liquid expansion agent source is set to water, and the combustion temperature in the continuous combustion chamber is higher than

At 647K, the combustion pressure in the continuous combustion chamber is greater than 22 MPa.

 The continuous combustion chamber is configured as an adiabatic continuous combustion chamber.

 The working mechanism is configured as a cylinder piston working mechanism, and a working medium introduction control valve is disposed between the continuous combustion chamber and the cylinder piston working mechanism, and a high temperature and high pressure working medium produced in the continuous combustion chamber The working fluid introduction control valve is quantitatively introduced into the working function of the cylinder piston working mechanism in a positive 吋 relationship, and the working fluid after the expansion work is discharged through the exhaust valve of the cylinder piston working mechanism.

 The working mechanism is set as a cylinder piston working mechanism, and the cylinder piston working mechanism is set as a self-insulation type working mechanism.

The critical low-entropy co-combustion cycle thermal power system further includes an open combustion envelope disposed in the continuous combustion chamber and in communication with the continuous combustion chamber, the liquid oxidant source being supplied via an oxidant high pressure a system in communication with the open combustion envelope, the fuel source being in communication with the open combustion envelope via a fuel high pressure supply system, wherein the liquid expander source is expanded by a bulk agent in a structure comprising the liquid expander source a high pressure supply system in communication with the continuous combustion chamber, within the source of liquid expansion agent An expansion agent is introduced into the space between the open combustion envelope and the continuous combustion chamber to form a suspension of the high-pressure gaseous expansion agent against the combustion flame to improve the combustion environment and reduce combustion to the continuous combustion chamber of the continuous combustion chamber a heat load requirement of the wall; in the structure comprising the gas liquefaction source, the gas liquefaction source is in communication with the continuous combustion chamber via a gas liquefaction high pressure supply system, the gas liquefaction in the gas liquefaction source Introduced into the space between the open combustion envelope and the continuous combustion chamber to form a suspension of the combustion flame by the high pressure gaseous gas liquefaction to improve the combustion environment and reduce combustion to the continuous combustion chamber wall of the continuous combustion chamber Thermal load requirements.

 The critical low entropy co-firing thermal power system further includes a fluid premixing chamber, the liquid oxidant source, the fuel, in a structure including the liquid oxidant source, the fuel source, and the liquid expander source Any two or both of the source and the source of liquid expansion agent are in communication with a fluid premixing chamber, the fluid premixing chamber being in communication with the continuous combustion chamber; including the source of the liquid oxidant, the source of fuel, and In the structure of the gas liquefaction source, any two or a common of the liquid oxidant source, the fuel source, and the gas liquefaction source are in communication with a fluid premixing chamber, the fluid premixing chamber and the continuous The combustion chamber is connected.

 A gas-liquid separator is disposed on the exhaust passage of the working mechanism.

 a gas-liquid separator is disposed on an exhaust passage of the working mechanism, a liquid outlet of the gas-liquid separator is used as a source of the liquid expansion agent, and a liquid in the gas-liquid separator is circulated as the liquid expansion agent use.

 An exhaust cooler is disposed on the exhaust passage of the working mechanism.

 The work mechanism is set as a power turbine.

 A method of increasing the efficiency and environmental friendliness of the critical low entropy co-firing thermal power system, adjusting the purity of the liquid oxidant in the liquid oxidant source and/or adjusting the purity and calorific value of the fuel in the fuel source The combustion temperature in the continuous combustion chamber is higher than 800 K, and the combustion pressure in the continuous combustion chamber is greater than 15 MPa.

A method of increasing the efficiency and environmental friendliness of the critical low entropy co-firing thermal power system, adjusting the purity of the liquid oxidant in the liquid oxidant source and/or adjusting the purity and calorific value of the fuel in the fuel source and / or adjusting the amount of expansion agent in the liquid expansion agent source introduced into the continuous combustion chamber such that the combustion temperature in the continuous combustion chamber is higher than 800K, and the combustion pressure in the continuous combustion chamber is greater than 15MPa.

 A method of increasing the efficiency and environmental friendliness of the critical low entropy co-firing thermal power system, adjusting the purity of the liquid oxidant in the liquid oxidant source and/or adjusting the purity and calorific value of the fuel in the fuel source and / or adjusting the amount of gas liquefaction in the gas liquefaction source introduced into the continuous combustion chamber such that the combustion temperature in the continuous combustion chamber is above 800 K and the combustion pressure in the continuous combustion chamber is greater than 15 MPa.

 A method for improving the efficiency and environmental protection of the critical low-entropy co-combustion cycle thermal power system, adjusting the temperature of the gas working fluid to be started below 2000K, adjusting the pressure of the gas working fluid to be started to work to 15 MPa Above, the temperature and pressure of the gaseous working fluid that is about to start work are in accordance with the adiabatic relationship.

 The so-called piston work structure of the present invention refers to all the mechanisms for pushing the piston work by using the gas working medium, including the cylinder piston mechanism and other forms of the piston mechanism, such as the triangular piston work structure; the so-called power turbine refers to all the use of gas The working medium pushes the mechanism of the impeller and the turbine to work.

 The engine and the thermodynamic system are equivalent.

 In the present invention, the so-called critical state includes a critical state, a supercritical state, and an ultra-supercritical state; the so-called ultra-supercritical state refers to a higher temperature and pressure state than the supercritical state.

 The combustion mode in the present invention may be direct combustion of fuel and oxidant, mixed combustion of oxidant, fuel and expansion agent, or may establish a core combustion zone in the expansion agent in the continuous combustion chamber, in the core combustion zone. The oxidant and the fuel are directly combusted and mixed with the expansion agent, so that the excessive temperature flame formed by direct combustion of the fuel and the oxidant with the expansion agent is isolated from the continuous combustion chamber wall, thereby reducing the thermal load on the continuous combustion chamber wall.

The so-called open combustion envelope of the present invention refers to a completely open combustion zone or a partially open combustion zone in which mainly contains an oxidant, a fuel and a reaction product thereof, and contains no or only a small amount of a high-pressure gaseous expansion agent. The so-called partially open combustion zone refers to a non-closed space formed of a solid such as ceramic or other highly heat resistant material. The so-called completely open combustion zone refers to a combustion chemical reaction in which the oxidant and the fuel are mixed with the high-pressure gaseous expansion agent by adjusting the supply mode of the oxidant and the fuel, that is, the flame and the combustion reaction of the oxidant and the fuel by the high-pressure gaseous expansion agent The continuous combustion chamber is isolated. The purpose of setting up an open combustion envelope is to make the combustion chemical reaction more complete, easier and faster with fuel and oxygen, reduce the emission of carbon monoxide and hydrocarbons, and make the combustion high. The state surrounded by the pressurized gas expansion agent is equivalent to suspending the core combustion zone in the continuous combustion chamber, thereby forming an open combustion envelope and gas isolation of the continuous combustion chamber wall, thereby greatly reducing the thermal load on the continuous combustion chamber wall. Claim.

 In the present invention, the open combustion envelope is arranged to surround the flame formed by the combustion with the high-pressure gaseous expansion agent, thereby avoiding the direct contact of the wall of the continuous combustion chamber with the flame, thereby avoiding the direct heat transfer of the flame to the wall of the continuous combustion chamber. This essentially creates a new way of cooling the walls of the continuous combustion chamber. That is to say, the conventional internal combustion engine (including the gas turbine) is such that the flame directly contacts the continuous combustion chamber wall to cool the continuous combustion chamber wall, which inevitably results in a large amount of low-quality thermal energy and waste of energy. In the present invention, the structure is such that the flame is cooled by the expansion agent before contacting the continuous combustion chamber wall, and the heat obtained by the cooling remains in the working medium, thereby improving the energy utilization rate and further improving the thermal power. The thermal efficiency of the system.

 The so-called expansion agent of the present invention refers to a working medium that does not participate in the combustion chemical reaction to cool and adjust the number of moles of work and expand work, and may be water vapor, carbon dioxide, helium, nitrogen, liquid carbon dioxide, liquid helium or liquid. Nitrogen, etc. By so-called liquid expansion agent source is meant a device that provides a liquid expansion agent.

 The term "oxidant" as used in the present invention means an oxygen-containing gas such as pure oxygen, hydrogen peroxide or an aqueous hydrogen peroxide solution in which pure oxygen or other components do not generate harmful compounds during thermal power conversion. By oxidant source is meant any device, system or vessel that can provide an oxidant, such as a commercial oxygen source (ie a high pressure oxygen storage tank or a liquefied oxygen tank) and oxygen supplied by an on-site oxygen system in a thermodynamic system (eg membrane separation) Oxygen system) and so on.

 The so-called feeding system of the present invention refers to a system for supplying the original working medium to the continuous combustion chamber according to the requirements of the combustion conditions of the continuous combustion chamber of the thermodynamic system, including a supply passage such as a pipeline, a valve and a pump, and also Includes an ejector. The feeding system can be continuously supplied or intermittently, and can also be controlled to supply, such as timing delivery, adjustable flow supply, and the like.

The critical low entropy in the present invention as disclosed in co-combustion cycle thermodynamic system in order to significantly reduce Γ ₂ by way of high pressure refrigerant into the continuous primary combustion chamber, the combustion chamber so that the maximum continuous pressure significantly higher than the traditional combustion engine The highest pressure in the room will eventually achieve a significant reduction of ₂ goals. From the thermodynamic analysis, it is known that increasing the maximum pressure of the combustion chamber is the key to reducing the efficiency of ₂ , and in order to achieve this, the high pressure of the original working fluid must enter the combustion chamber.

Adiabatic thermodynamic systems are thermodynamic systems that have not been meaningful for a long time. It is believed that this system does not have the potential to increase the efficiency of the thermodynamic system. The result of these studies is: If the combustion chamber of the thermodynamic system is insulated, only increasing the temperature of the exhaust of the thermodynamic system does not have much potential to increase the efficiency of the thermodynamic system. The inventors analyzed this conclusion and its causes in detail, and concluded the following conclusions: 1. The combustion chambers of the adiabatic engines studied so far are in the pressure range of the conventional combustion chamber, and the adiabatic only increases the temperature of the combustion chamber. There is no increase in the pressure of the combustion chamber, nor does it give a solution to increase the pressure of the combustion chamber. Therefore, the result of the adiabatic is that the temperature increases and the expansion is insufficient due to insufficient pressure (the pressure at the end of the work is substantially equal to or higher than the ambient pressure). The end result is that the exhaust gas temperature is high and the efficiency is not improved. Second, people have a traditional idea, and the heat insulation is equal to the high temperature. Therefore, the temperature of the combustion chamber of the traditional adiabatic engine is very high. The high temperature brings a lot of troubles to the adiabatic engine, such as replacing the material of the combustion chamber, etc., resulting in high engine cost and reliability. Low sex. 3. Almost all of the research on adiabatic engines to date has focused on how to solve the materials and lubricants of the combustion chamber, but there is no research on how to increase the maximum pressure of the combustion chamber. It is because of the above three points that the traditional adiabatic engine has not improved efficiency. In the solution of the present invention, the original working medium enters the combustion chamber in a high-pressure gaseous state, and the pressure entering the combustion chamber can be adjusted according to design requirements. If the combustion chamber is set to be adiabatic, the pressure inside the combustion chamber can be reached. Very high level, so that a large expansion ratio can be formed, so even if the combustion chamber is adiabatic, the exhaust gas temperature can still reach a very low level, which inevitably leads to a great improvement in thermal efficiency. Moreover, in some aspects of the thermodynamic system of the present invention, a swelling agent is provided, the amount of the expanding agent can be adjusted to control the temperature of the adiabatic combustion chamber, and the temperature of the adiabatic combustion chamber can be brought close to the temperature of the conventional combustion chamber. In the system disclosed herein, the adiabatic combustion chamber can be fabricated using the materials of the currently proven adiabatic combustion chambers.

 The expansion agent of the present invention can be recycled in the critical low entropy co-firing thermal power system. In the structure in which the expansion agent is recycled, the expansion agent can be compressed and then passed to the continuous combustion chamber.

 The so-called work mechanism of the present invention refers to any device that can convert the energy of a high temperature and high pressure working medium into an external output of mechanical work, such as a piston crank mechanism, a turbine and a nozzle.

 The so-called continuous combustion chamber of the present invention refers to a container in which continuous combustion (violent exothermic chemical reaction) can occur inside.

The so-called fuel in the present invention refers to a substance which can undergo a vigorous redox reaction with oxygen in the sense of chemical combustion, and may be a gas, a liquid or a solid, and mainly includes gasoline, diesel, natural gas, Hydrogen and gas and fluidized fuels, liquefied fuels or powdered solid fuels. The liquefied fuel refers to a fuel that is liquefied and is in a gaseous state at a normal temperature and a normal pressure state.

 The critical low-entropy co-firing thermodynamic system disclosed in the present invention can use a hydrocarbon or a carbon hydrate as a fuel, such as an aqueous solution of ethanol or ethanol, and an aqueous solution of ethanol instead of the original fuel and expansion agent, not only can be antifreeze, but also It is possible to replace the original fuel storage tank and the expansion agent storage tank with only one aqueous ethanol storage tank, and to change the ratio of the fuel and the expansion agent by adjusting the concentration of the aqueous ethanol solution. When necessary, the fuel and the expansion agent of the present invention may be replaced with a mixed solution of ethanol, water and hydrocarbon, and the concentration thereof may be adjusted to meet the requirements of the critical low-entropy co-combustion cycle thermal power system disclosed in the present invention. In the critical low-entropy co-firing thermal power system disclosed in the present invention, an aqueous solution of hydrogen peroxide can be used instead of the oxidizing agent and the expanding agent, and the ratio of the oxidizing agent and the expanding agent can be adjusted by adjusting the concentration of the aqueous hydrogen peroxide solution, and a peroxidation can be used. The aqueous hydrogen storage tank replaces the oxidant storage tank and the expansion agent storage tank.

 The critical low-entropy co-combustion cycle thermal power system disclosed by the present invention can produce a thermodynamic system in which the exhaust gas temperature is close to the ambient temperature, lower than the ambient temperature, or substantially lower than the ambient temperature. In the structure in which the working mechanism is set as the cylinder piston working mechanism, if the exhaust gas temperature is low to a certain extent, the self-insulation of the thermodynamic system can be achieved. The so-called self-insulation means that the heat of the high-temperature and high-pressure working medium is transmitted to the cylinder wall, the piston top and the cylinder head at the beginning of the combustion explosion. In the process of work, because the temperature of the working medium is already low, it will be At the beginning of the work, the heat transferred to the cylinder wall, the piston top and the cylinder head is reabsorbed back into the working fluid, reducing the loss of heat and achieving the function equivalent to "insulation". In the self-insulated system, all the contacts with the working medium The outside of the pressure wall (cylinder wall, piston top and cylinder head) can be insulated without heat transfer, or a small amount of heat transfer can be generated according to the temperature requirements of the pressure wall to reduce the temperature of the pressure wall; a liquid passage or a liquid chamber may be disposed in or outside the pressure-receiving wall contacting the working medium, and the liquid passage or the liquid chamber is filled with liquid to ensure uniform heating of the pressure-bearing wall contacting the working medium. And use the heat storage of the liquid to optimize the change of the gas temperature in the cylinder, and a heat insulation layer can be arranged outside the liquid passage or the liquid chamber to reduce heat transfer to the environment.

 In the present invention, especially in a structure having an open combustion envelope, the working fluid temperature can reach several thousand degrees or higher, and the working fluid pressure can reach several hundred atmospheres or even higher.

The temperature and pressure of the work fluid of the critical low-entropy co-firing thermal power system disclosed by the invention can be When controlled to expand to the set expansion pressure, the working temperature drops to a relatively low level, such as near ambient temperature, below ambient temperature, or substantially below ambient temperature.

The beneficial effects of the present invention are as follows:

 The critical low-entropy co-combustion cycle thermal power system disclosed by the invention achieves high efficiency, energy saving and low emission, and is a new-generation thermodynamic system superior to the external combustion cycle thermal power system and the internal combustion cycle thermal power system.

 DRAWINGS

 1 is a schematic structural view of Embodiment 1 of the present invention;

 Figure 2 is a schematic structural view of Embodiments 2, 5 and 7 of the present invention;

 Figure 3 is a schematic structural view of Embodiment 3 and Embodiment 6 of the present invention;

 Figure 4 is a schematic structural view of Embodiment 4 of the present invention;

 Figure 5 is a schematic structural view of Embodiment 8 of the present invention;

 Figure 6 is a schematic structural view of Embodiment 9 of the present invention;

 Figure 7 is a schematic structural view of Embodiment 10 of the present invention;

 Figures 8, 9 and 10 are schematic views of the structure of the embodiment 1 of the present invention;

 1 , 12 and 13 are schematic structural views of an embodiment 1 2 of the present invention;

 14 and 15 are schematic structural views of Embodiment 13 of the present invention;

 Figure 16 is a schematic structural view of Embodiment 14 of the present invention;

 Figure 17 is a schematic structural view of Embodiment 15 of the present invention;

 Figure 18 is a graph showing the relationship between the temperature T of the gas working fluid and the pressure P.

 In the picture:

 1 work mechanism, 2 continuous combustion chamber, 3 liquid oxidant source, 4 fuel source, 5 liquid expander source, 6 gas liquefaction source, 12 power through, 22 continuous combustion chamber wall, 301 oxidant high pressure supply system, 400 fluid Premixing chamber, 401 fuel high pressure supply system, 402 oxidant heat absorption heat exchanger, 501 expansion agent high pressure supply system, 1 10 exhaust gas cooler, 601 gas liquefaction high pressure supply system, 602 gas liquefaction heat absorption heat Exchanger, 101 self-adiabatic work mechanism, 1 1 1 cylinder piston work mechanism, 1 12 working fluid introduction control valve, 1 1 3 exhaust valve, 1 100 gas-liquid separator, 2001 open combustion envelope.

detailed description

Example 1 A critical low-entropy co-combustion cycle thermodynamic system as shown in FIG. 1 includes a work mechanism 1, a continuous combustion chamber 2, a liquid oxidant source 3, and a fuel source 4, and the liquid oxidant source 3 is passed through an oxidant high-pressure supply system 301 and The continuous combustion chamber 2 is in communication, the fuel source 4 is in communication with the continuous combustion chamber 2 via a fuel high pressure supply system 401, and the oxidant in the liquid oxidant source 3 enters the continuous combustion chamber 2 in a high pressure liquid state. The fuel in the fuel source 4 enters the continuous combustion chamber 2 in the form of a high pressure, and the pressure bearing capacity of the oxidant high pressure supply system 301, the fuel high pressure supply system 401, and the continuous combustion chamber 2 is greater than 15 MPa. Adjusting the purity of the liquid oxidant in the liquid oxidant source 3 and/or adjusting the purity and calorific value of the fuel in the fuel source 4 such that the combustion temperature in the continuous combustion chamber 2 is higher than 800K, and the continuous The combustion pressure in the combustion chamber 2 is greater than 15 MPa; the continuous combustion chamber 2 is in communication with at least one of the work mechanisms 1, and the work mechanism 1 outputs power externally.

 In order to improve the efficiency and environmental protection of the critical low-entropy co-firing thermal power system, the temperature of the gas working fluid to be started to work is adjusted to below 2000K, and the pressure of the gas working fluid to be started to work is adjusted to 15 MPa or more. The temperature and pressure of the gas working fluid that is about to start work are in a class of adiabatic relationships. The oxidizing agent in the liquid oxidant source 3 is set to pure liquid oxygen, an oxygen-containing gas liquefied material, hydrogen peroxide or an aqueous hydrogen peroxide solution.

 Example 2

A critical low-entropy co-combustion cycle thermodynamic system as shown in FIG. 2, comprising a work mechanism 1, a continuous combustion chamber 2, a liquid oxidant source 3, a fuel source 4, and a liquid expander source 5, said liquid oxidant source 3 being oxidized by a oxidant The supply system 301 is in communication with the continuous combustion chamber 2 via an oxidant heat absorption heat exchanger 402. The fuel source 4 is in communication with the continuous combustion chamber 2 via a fuel high pressure supply system 401, the liquid oxidant source 3 The oxidant enters the continuous combustion chamber 2 in the form of a high pressure gas state or a critical state after absorbing heat in the oxidant heat absorbing heat exchanger 402, and the fuel in the fuel source 4 enters the continuous state in the form of high pressure. a combustion chamber 2, the liquid expansion agent source 5 is in communication with the continuous combustion chamber 2 via an expansion agent high pressure supply system 501, and the expansion agent in the liquid expansion agent source 5 enters the continuous combustion chamber in a high pressure liquid state 2. The oxidant high pressure supply system 301, the fuel high pressure supply system 401, the expansion agent high pressure supply system 501, and the continuous combustion chamber 2 have a pressure bearing capacity greater than 15 MPa, and the liquid oxidant source is adjusted. 3 Purity of the liquid oxidant and/or adjustment of the purity and calorific value of the fuel in the fuel source 4 and/or adjustment of the expansion agent in the liquid expansion agent source 5 into the continuous combustion The amount of chamber 2 is such that the combustion temperature in the continuous combustion chamber 2 is higher than 800 K and the combustion pressure in the continuous combustion chamber 2 is greater than 15 MPa; the continuous combustion chamber 2 and at least one of the working mechanisms 1 Connected, the work mechanism 1 outputs power to the outside.

 In order to improve the efficiency and environmental protection of the critical low-entropy co-firing thermal power system, the temperature of the gas working fluid to be started to work is adjusted to below 2000K, and the pressure of the gas working fluid to be started to work is adjusted to 15 MPa or more. The temperature and pressure of the gas working fluid that is about to start work are in a class of adiabatic relationships. The expansion agent in the liquid expansion agent source 5 is set to water, liquid nitrogen, liquid carbon dioxide or liquid helium.

 Example 3

 The critical low-entropy co-combustion cycle thermodynamic system shown in FIG. 3 includes a work mechanism 1, a continuous combustion chamber 2, a liquid oxidant source 3, a fuel source 4, and a gas liquefaction source 6, the liquid oxidant source 3 being oxidized by a oxidant The supply system 301 is in direct or re-connected with the continuous combustion chamber 2 via an oxidant heat absorption heat exchanger 402, which is in communication with the continuous combustion chamber 2 via a fuel high pressure supply system 401, the liquid oxidant source The oxidant in 3 is introduced into the continuous combustion chamber 2 in the form of a high-pressure gas in the form of a high-pressure liquid or in the oxidant heat-absorbing heat exchanger 402, and the fuel in the fuel source 4 is at a high pressure. Forming into the continuous combustion chamber 2, the gas liquefaction source 6 is in communication with the continuous combustion chamber 2 via a gas liquefaction high pressure supply system 601 via a gas liquefaction heat absorption heat exchanger 602, the gas liquefaction The gas liquefied material in the source 6 enters the continuous combustion chamber 2 in the form of a high pressure gaseous state or a critical state, the oxidant high pressure supply system 301, the fuel high pressure supply system 401. The gas liquefaction high-pressure supply system 601 and the continuous combustion chamber 2 have a pressure bearing capacity greater than 15 Pa, adjusting the purity of the liquid oxidant in the liquid oxidant source 3 and/or adjusting the fuel source 4 The purity and calorific value of the fuel in the fuel and/or the adjustment of the gas liquefaction in the gas liquefaction source 6 into the continuous combustion chamber 2 causes the combustion temperature in the continuous combustion chamber 2 to be higher than 800 K, and The combustion pressure in the continuous combustion chamber 2 is greater than 15 MPa; the continuous combustion chamber 2 is in communication with at least one of the work mechanisms 1, and the work mechanism 1 outputs power externally.

In order to improve the efficiency and environmental protection of the critical low-entropy co-firing thermal power system, the temperature of the gas working fluid to be started to work is adjusted to below 2000K, and the pressure of the gas working fluid to be started to work is adjusted to 15 MPa or more. The temperature and pressure of the gas working fluid that is about to start work are in a class of adiabatic relationships. The fuel in the fuel source 4 is set to hydrogen, combustible hydrocarbon, combustible carbon hydrate or combustible alcohol Solution. The gas liquefaction in the gas liquefaction source 6 is set to liquefied air, liquid nitrogen, liquid carbon dioxide or liquid helium.

 Example 4

 The critical low-entropy co-combustion cycle thermodynamic system shown in FIG. 4 differs from embodiment 3 in that: the liquid oxidant source 3 is passed through the oxidant heat-absorbing heat exchanger 402 and the oxidant heat-absorbing heat exchanger 402 and the continuous The combustion chamber 2 is in communication, and the oxidant in the liquid oxidant source 3 enters the continuous combustion chamber 2 in the form of a high pressure gas or a critical state after endothermic gasification in the oxidant heat absorption heat exchanger 402.

 In order to improve the efficiency and environmental protection of the critical low-entropy co-combustion cycle thermal power system, the temperature of the gas working fluid to be started to work is adjusted to below 2000K, and the pressure of the gas working fluid to be started to work is adjusted to be more than 15 MPa. The temperature and pressure of the gaseous working fluid that is about to start work are in accordance with the adiabatic relationship. The fuel in the fuel source 4 is set to hydrogen, a combustible hydrocarbon, a combustible carbonic acid hydroxide or a combustible alcohol solution. The gas liquefaction in the gas liquefaction source 6 is set to liquefied air, liquid gas, liquid carbon dioxide or liquid helium.

 Example 5

 The critical low-entropy co-combustion cycle thermodynamic system shown in FIG. 2 differs from the second embodiment in that: the oxidant high-pressure supply system 301, the fuel high-pressure supply system 401, and the expansion agent high pressure are provided. In the configuration of the feeding system 501, the supply amount of the oxidant high-pressure supply system 301, the fuel high-pressure supply system 401, and the expansion agent high-pressure supply system 501, and the ratio between each supply amount are adjusted. The expansion agent in the liquid expansion agent source 5 is brought to a critical state within the continuous combustion chamber 2.

 Example 6

 The critical low-entropy co-combustion cycle thermodynamic system shown in FIG. 3 differs from the third embodiment in that: the oxidant high-pressure supply system 301, the fuel high-pressure supply system 401, and the gas liquefaction are provided. In the structure of the high pressure supply system 601, the supply amount of the oxidant high pressure supply system 301, the fuel high pressure supply system 401, and the gas liquefaction high pressure supply system 601 and the supply amount are adjusted between each supply amount. The ratio causes the gas liquefied material within the gas liquefaction source 6 to be in a critical state within the continuous combustion chamber 2.

Example 7 The critical low-entropy co-combustion cycle thermodynamic system shown in FIG. 2 differs from the second embodiment in that: the expansion agent in the liquid expansion agent source 5 is set to water, and the combustion temperature in the continuous combustion chamber 2 is high. At 647K, the combustion pressure in the continuous combustion chamber 2 is greater than 22 MPa.

 Example 8

 The critical low-entropy co-combustion cycle thermodynamic system shown in FIG. 5 differs from the embodiment 1 in that: the continuous combustion chamber 2 is set as an adiabatic continuous combustion chamber, and the adiabatic continuous combustion chamber and three of the work are performed. The mechanism 1 is connected, and the work mechanism 1 outputs power to the outside.

 Example 9

 The critical low-entropy co-combustion cycle thermodynamic system shown in FIG. 6 differs from the embodiment 1 in that the critical low-entropy co-combustion cycle thermodynamic system further includes a liquid expansion agent source 5, and the liquid expansion agent source 5 The expansion agent high pressure supply system 501 is in communication with the continuous combustion chamber 2, and the expansion agent in the liquid expansion agent source 5 enters the continuous combustion chamber 2 in the form of a high pressure liquid, the expansion agent high pressure supply system 501 The pressure bearing capacity is greater than 15 MPa. The continuous combustion chamber 2 is provided as an adiabatic continuous combustion chamber, and the adiabatic continuous combustion chamber is in communication with three of the work mechanisms 1, and the work mechanism 1 outputs power to the outside.

 Example 10

 The critical low-entropy co-combustion cycle thermodynamic system shown in FIG. 7 differs from the first embodiment in that: the work mechanism 1 is set as a cylinder piston work mechanism 1 1 1, in the continuous combustion chamber 2 and the The working fluid introduction control valve 1 12 is disposed between the cylinder piston working mechanism 1 1 1 , and the high temperature and high pressure working medium generated in the continuous combustion chamber 2 is quantitatively introduced by the working medium introduction control valve 12 in a positive relationship. The cylinder piston working mechanism 1 1 1 expands work, and the working fluid after the expansion work is discharged through the exhaust valve 1 13 of the cylinder piston working mechanism 1 1 1 .

 Example 1 1

The critical low-entropy co-combustion cycle thermodynamic system shown in Figures 8, 9, and 10 differs from the second embodiment in that a gas-liquid separator 1 100 is disposed on the exhaust passage 1 of the work mechanism 1. The liquid outlet of the gas-liquid separator 1 100 is set as the liquid expansion agent source 5, and the liquid in the gas-liquid separator 1 100 is recycled as the liquid expansion agent. The working mechanism 1 is set as the cylinder piston working mechanism, and the cylinder piston working mechanism is set as the self-adiabatic working mechanism 101; the working mechanism in FIG. 9 is set as the cylinder piston. Mechanism 1 1 1 , the continuous combustion chamber 2 and two of the cylinder pistons work The mechanism 1 1 1 is connected; in FIG. 10, an exhaust cooler 1 10 is provided on the exhaust passage 11 of the work mechanism 1. Example 12

 The critical low-entropy co-combustion cycle thermal power system shown in FIGS. 1, 1 and 12 differs from Embodiment 2 or Embodiment 3 in that: the critical low-entropy co-combustion cycle thermal power system further includes an open combustion package. The open combustion envelope 2001 is disposed in the continuous combustion chamber 2 and is in communication with the continuous combustion chamber 2, and the liquid oxidant source 3 is passed through the oxidant high pressure supply system 301 and the open combustion envelope 2001 In connection, the fuel source 4 is in communication with the open combustion envelope 2001 via a fuel high pressure supply system 401. In the structure including the liquid expansion agent source 5, the liquid expansion agent source 5 is supplied via a high pressure agent of the expansion agent. System 501 is in communication with said continuous combustion chamber 2, and an expansion agent in said liquid expansion agent source 5 is introduced into the space between said open combustion envelope 2001 and said continuous combustion chamber 2 to form a high pressure gaseous expansion agent Suspension of the combustion flame, thereby improving the combustion environment, reduces the thermal load requirements of combustion on the continuous combustion chamber wall 22 of the continuous combustion chamber 2; in a structure comprising the gas liquefaction source, The gas liquefaction source is in communication with the continuous combustion chamber 2 via a gas liquefaction high pressure supply system, and the gas liquefied material in the gas liquefaction source is introduced into the open combustion envelope 2001 and the continuous combustion chamber 2 The space between the spaces to form a high pressure gaseous gas liquefaction suspension of the combustion flame and thereby improve the combustion environment reduces the thermal load requirements of the combustion on the continuous combustion chamber wall 22 of the continuous combustion chamber 2.

 Example 13

 The critical low-entropy co-combustion cycle thermal power system shown in FIG. 14 and FIG. 15 differs from the embodiment 2 or the embodiment 3 in that the critical low-entropy co-combustion cycle thermal power system further includes a fluid premixing chamber 400. In the structure including the liquid oxidant source 3, the fuel source 4, and the liquid expander source 5, any two of the liquid oxidant source 3, the fuel source 4, and the liquid expander source 5 Or in common with the fluid premixing chamber 400, the fluid premixing chamber 400 is in communication with the continuous combustion chamber 2 (as shown in Figure 14); including the liquid oxidant source 3, the fuel source 4 and the In the structure of the gas liquefaction source, any two or a common of the liquid oxidant source 3, the fuel source 4, and the gas liquefied source are in communication with a fluid premixing chamber 400, the fluid premixing chamber 400 It is in communication with the continuous combustion chamber 2 (as shown in Fig. 15).

Example 14 The critical low-entropy co-combustion cycle thermodynamic system shown in Fig. 16 differs from the first embodiment in that the work mechanism 1 is set as the power turbine 12.

 Example 15

 The critical low-entropy co-combustion cycle thermodynamic system shown in FIG. 17 differs from the second embodiment in that: the work mechanism 1 is set as a power turbine 12, and the exhaust passage 1 of the work mechanism 1 is 1 is provided with a gas-liquid separator 1 100, the liquid outlet of the gas-liquid separator 1 100 is set as the liquid expansion agent source 5, and the liquid in the gas-liquid separator 1 100 is recycled as the liquid expansion agent .

 It is apparent that the present invention is not limited to the above embodiments, and many variations can be deduced or conceived according to the known art in the art and the technical solutions disclosed in the present invention, all of which are also considered to be the scope of protection of the present invention.

Claims

Rights request  1. A critical low-entropy co-firing thermal power system, including a working mechanism (1), a continuous combustion chamber (2) a liquid oxidant source (3) and a fuel source (4), characterized in that: the liquid oxidant source (3) is connected to the continuous combustion chamber (2) via an oxidant high pressure supply system (301) The fuel source (4) is in communication with the continuous combustion chamber (2) via a fuel high pressure supply system (401), the liquid oxidant source The oxidant in (3) enters the continuous combustion chamber (2) in the form of a high pressure liquid, and the fuel in the fuel source (4) enters the continuous combustion chamber (2) in the form of a high pressure, the oxidant is supplied at a high pressure. Delivery system (301), the fuel high pressure supply system (401) and the continuous combustion chamber (2) have a pressure bearing capacity greater than 15 MPa, and the continuous combustion chamber (2) is in communication with at least one of the working mechanisms (1) The working mechanism (1) outputs power externally.  2. The critical low entropy co-firing cycle thermodynamic system according to claim 1, wherein: said critical low entropy co-firing cycle thermodynamic system further comprises a liquid expansion agent source (5), said liquid expansion agent source ( 5) communicating with the continuous combustion chamber (2) via an expansion agent high pressure supply system (501), the expansion agent in the liquid expansion agent source (5) entering the continuous combustion chamber in a high pressure liquid state (2) The expansion agent high pressure supply system (501) has a pressure bearing capacity greater than 15 MPa. 3. A critical low-entropy co-combustion cycle thermal power system comprising a work mechanism (1), a continuous combustion chamber (2), a liquid oxidant source (3), a fuel source (4), and a liquid expansion agent source (5), The utility model is characterized in that: the liquid oxidant source (3) is connected to the continuous combustion chamber (2) via an oxidant high-pressure supply system (30 Ό and then via an oxidant heat-absorbing heat exchanger (402), the fuel source (4) a fuel high pressure supply system (401) is in communication with the continuous combustion chamber (2), and an oxidant in the liquid oxidant source (3) is heated and vaporized in the oxidant heat absorption heat exchanger (402) to a high pressure a gaseous or critical state entering the continuous combustion chamber (2), the fuel in the fuel source (4) entering the continuous combustion chamber (2) in the form of a high pressure, the liquid expansion agent source (5) An expansion agent high pressure supply system (501) is in communication with the continuous combustion chamber (2), and the expansion agent in the liquid expansion agent source (5) enters the continuous combustion chamber (2) in a high pressure liquid state, An oxidant high pressure supply system (301), the fuel high pressure supply system (401), The expansion agent high pressure supply system (501) and the continuous combustion chamber (2) have a pressure bearing capacity greater than 15 MPa, and the continuous combustion chamber (2) is in communication with at least one of the working mechanisms (1). The power mechanism (1) outputs power externally. 4. A critical low-entropy co-combustion cycle thermal power system comprising a work mechanism (1), a continuous combustion chamber (2), a liquid oxidant source (3), a fuel source (4), and a gas liquefaction source (6), Characterized by: the liquid oxidant source (3) is in direct communication with the continuous combustion chamber (2) via an oxidant high pressure supply system (301) or via an oxidant heat absorption heat exchanger (402), the fuel source ( 4) communicating with the continuous combustion chamber (2) via a fuel high pressure supply system (401), the oxidant in the liquid oxidant source (3) being in the form of a high pressure liquid or in the oxidant heat absorption heat exchanger (402) After the endothermic gasification, the continuous combustion chamber (2) is introduced in the form of a high-pressure gas, and the fuel in the fuel source (4) enters the continuous combustion chamber (2) in the form of high pressure, the gas liquefaction The source (6) is in communication with the continuous combustion chamber (2) via a gas liquefaction high pressure supply system (601) and a gas liquefaction heat source (2), wherein the gas liquefaction source (6) is Gas liquefaction in the form of a high pressure gaseous state or a critical state Forming into the continuous combustion chamber (2), the oxidant high pressure supply system (301), the fuel high pressure supply system (401), the gas liquefaction high pressure supply system (601), and the continuous combustion room (2) The pressure bearing capacity is greater than 15 MPa, the continuous combustion chamber (2) and at least one of the working mechanisms (1) Connected, the work mechanism (1) outputs power externally.  5. The critical low-entropy co-combustion cycle thermal power system according to claim 2, 3 or 4, wherein: said oxidant high-pressure supply system (301), said fuel high-pressure supply system (401) And adjusting the oxidant high pressure supply system in the structure of the expansion agent high pressure supply system (501) (301), a supply amount of the fuel high-pressure supply system (401) and the expansion agent high-pressure supply system (501), and a ratio between each supply amount to cause the liquid expansion agent source (5) The expansion agent in the continuous combustion chamber (2) is in a critical state; the oxidant high pressure supply system (301), the fuel high pressure supply system (401) and the gas liquefaction high pressure supply are provided In the structure of the delivery system (601), the supply amount of the oxidant high pressure supply system (301), the fuel high pressure supply system (401), and the gas liquefaction high pressure supply system (601) are adjusted and each The ratio between the supply amounts causes the gas liquefaction in the gas liquefaction source (6) to be in a critical state within the continuous combustion chamber (2).  6. A critical low entropy co-firing cycle thermodynamic system according to claim 2 or 3, characterized in that the expansion agent in the liquid expansion agent source (5) is set to water, liquid nitrogen, liquid carbon dioxide or liquid helium. 7. The critical low entropy co-combustion cycle thermal power system according to claim 1, 3 or 4, characterized in that The oxidizing agent in the liquid oxidant source (3) is pure liquid oxygen, an oxygen-containing gas liquefied material, hydrogen peroxide or an aqueous hydrogen peroxide solution.  8. The critical low entropy co-firing cycle thermodynamic system according to claim 1, 3 or 4, characterized in that: the fuel in the fuel source (4) is set to hydrogen, combustible hydrocarbons, combustible carbon oxyhydroxide. Or a flammable alcohol solution.  9. The critical low-entropy co-combustion cycle thermal power system according to claim 2 or 3, wherein: the expansion agent in the liquid expansion agent source (5) is set to water, and the continuous combustion chamber (2) The combustion temperature is higher than 647 K, and the combustion pressure in the continuous combustion chamber (2) is greater than 22 MPa.  10. A critical low entropy co-combustion cycle thermodynamic system according to claim 1, 3 or 4, characterized in that said continuous combustion chamber (2) is provided as an adiabatic continuous combustion chamber.  11. The critical low-entropy co-combustion cycle thermal power system according to claim 1, 3 or 4, wherein: said working mechanism (1) is set as a cylinder piston working mechanism (111), said continuous combustion A working medium introduction control valve (112) is arranged between the chamber (2) and the cylinder piston working mechanism (111), and the high temperature and high pressure working medium generated in the continuous combustion chamber (2) is controlled by the working fluid. The valve (112) is quantitatively introduced into the working function of the cylinder piston working mechanism (111) according to the timing relationship, and the working fluid after the expansion work is passed through the exhaust valve (113) of the cylinder piston working mechanism (111). discharge.  12. The critical low-entropy co-combustion cycle thermal power system according to claim 1, 3 or 4, wherein: said working mechanism (1) is set as a cylinder piston working mechanism (111), said cylinder piston The work mechanism (111) is set to a self-adiabatic work mechanism (101). 13. The critical low-entropy co-combustion cycle thermal power system according to claim 2, 3 or 4, wherein: said critical low-enthalpy hybrid combustion cycle thermal power system further comprises an open combustion envelope (2001), said opening a combustion envelope (2001) is disposed in the continuous combustion chamber (2) and in communication with the continuous combustion chamber (2), the liquid oxidant source (3) is passed through the oxidant high pressure supply system (301) a combustion envelope (2001) connected, the fuel source (4) being in communication with the open combustion envelope (2001) via a fuel high pressure supply system (401), in a structure including the liquid expander source (5) The liquid expander source (5) is in communication with the continuous combustion chamber (2) via a bulk expander high pressure supply system (501), and the expander in the liquid expander source (5) is introduced into the open combustion In the space between the envelope (2001) and the continuous combustion chamber (2), to form a high-pressure gaseous expansion agent for the suspension of the combustion flame Further improving the combustion environment reduces the thermal load requirement of combustion on the continuous combustion chamber wall (22) of the continuous combustion chamber (2); in the structure comprising the gas liquefaction source (6), the gas liquefied source (6) communicating with the continuous combustion chamber (2) via a gas liquefaction high pressure supply system (601), the gas liquefied material in the gas liquefaction source (6) being introduced into the open combustion envelope (2001) And a space between the continuous combustion chamber (2) to form a high-pressure gaseous gas liquefaction suspension of the combustion flame to improve the combustion environment to reduce combustion to the continuous combustion chamber wall of the continuous combustion chamber (2) (22 ) Thermal load requirements.  14. The critical low-entropy co-combustion cycle thermal power system according to claim 2, 3 or 4, wherein: said critical low-entropy co-combustion cycle thermal power system further comprises a fluid premixing chamber (400), In the structure of the liquid oxidant source (3), the fuel source (4) and the liquid expansion agent source (5), the liquid oxidant source (3), the fuel source (4) and the liquid expansion Any two or both of the source (5) are in communication with a fluid premixing chamber (400), the fluid premixing chamber (400) being in communication with the continuous combustion chamber (2); 3), in the structure of the fuel source (4) and the gas liquefaction source (6), the liquid oxidant source (3), the fuel source (4) and the gas liquefaction source (6) Any two or a common one of them is in communication with a fluid premixing chamber (400) that is in communication with the continuous combustion chamber (2).  15. The critical low-entropy co-combustion cycle thermal power system according to claim 1, 3 or 4, characterized in that: a gas-liquid separator (1100) is arranged on the exhaust passage (11) of the working mechanism (1) ).  The critical low-entropy co-combustion cycle thermal power system according to claim 2 or 3, characterized in that: a gas-liquid separator (1100) is arranged on the exhaust passage (11) of the working mechanism (1), The liquid outlet of the gas-liquid separator (1100) is set as the liquid expansion agent source (5), and the liquid in the gas-liquid separator (1100) is recycled as the liquid expansion agent.  17. A critical low entropy co-combustion cycle thermal power system according to claim 1, 3 or 4, characterized in that - an exhaust gas cooler (110) is provided on the exhaust passage (11) of said working mechanism (1) ).  18. A critical low entropy co-combustion cycle thermal power system according to claim 1, 3 or 4, characterized in that said working mechanism (1) is set as a power turbine (12). 19. A method of increasing the efficiency and environmental friendliness of a critical low entropy co-firing thermal power system according to claim 1 or 2, characterized by: adjusting the purity of the liquid oxidant in said liquid oxidant source (3) And/or adjusting the purity and calorific value of the fuel in the fuel source (4) such that the combustion temperature in the continuous combustion chamber (2) is higher than 800K, and the combustion pressure in the continuous combustion chamber (2) More than 15 MPa.  20. A method of increasing the efficiency and environmental friendliness of a critical low entropy co-firing thermal power system of claim 3, characterized by: adjusting the purity and/or adjustment of the liquid oxidant in said source of liquid oxidant (3) The purity and calorific value of the fuel in the fuel source (4) and/or the amount of expansion agent introduced into the continuous combustion chamber (2) in the liquid expansion agent source (5) is such that the continuous combustion chamber (2) The combustion temperature inside is higher than 800K, and the combustion pressure in the continuous combustion chamber (2) is greater than 15 MPa.  21. A method of increasing the efficiency and environmental friendliness of a critical low entropy co-firing thermal power system of claim 4, characterized by: adjusting the purity and/or adjustment of the liquid oxidant in said source of liquid oxidant (3) The purity and calorific value of the fuel in the fuel source (4) and/or the amount of gas liquefied in the gas liquefaction source (6) introduced into the continuous combustion chamber (2) to cause the continuous combustion chamber ( 2) The combustion temperature inside is higher than 800K, and the combustion pressure in the continuous combustion chamber (2) is greater than 15 MPa.  22. A method for improving the efficiency and environmental friendliness of a critical low-entropy co-combustion cycle thermal power system according to claim 1, 2, 3 or 4, characterized in that the temperature of the gaseous working medium to be started to work is adjusted to below 2000 K. Adjust the pressure of the gas working fluid that is about to start work to 15 MPa or more, so that the temperature and pressure of the gas working fluid that is about to start work are in line with the adiabatic relationship.