WO2011088752A1

WO2011088752A1 - Low-entropy mixed combustion circulating thermal power system

Info

Publication number: WO2011088752A1
Application number: PCT/CN2011/000105
Authority: WO
Inventors: 靳北彪
Original assignee: Jin Beibiao
Priority date: 2010-01-22
Filing date: 2011-01-21
Publication date: 2011-07-28
Also published as: CN102121434B; CN102121434A

Abstract

A low-entropy mixed combustion circulating thermal power system includes a working mechanism (1), a combustion chamber (2), an oxygen source (3), a fuel source (4) and an expansion agent source (5). The oxygen source (3) is communicated with the combustion chamber (2) through an oxygen high-pressure supply system (301), the fuel source (4) is communicated with the combustion chamber (2) through a fuel high-pressure supply system (401) and the expansion agent source (5) is communicated with the combustion chamber (2) through an expansion agent high-pressure supply system (501). An oxygen heat absorption heat exchanger (3011) is arranged in the oxygen high-pressure supply system (301) and the oxygen in the oxygen source (3) absorbs heat in the oxygen heat absorption heat exchanger (3011) to form a high-pressure gaseous oxygen. Then the high-pressure gaseous oxygen enters into the combustion chamber (2). An expansion agent heat absorption heat exchanger (5011) is arranged in the expansion agent high-pressure supply system (501) and the expansion agent in the expansion agent source (5) absorbs heat in the expansion agent heat absorption heat exchanger (5011) to form a high-pressure gaseous expansion agent. Then high-pressure gaseous expansion agent enters into the combustion chamber (2). The minimal pressure bearing capability of the oxygen high-pressure supply system (301) is greater than or equal to 2MPa, and the combustion chamber (2) is connected with the working mechanism (1) outputting power. The low-entropy mixed combustion circulating thermal power system realizes high efficiency, energy saving and low emission.

Description

Low entropy co-firing cycle thermodynamic system

Technical field

The invention relates to the field of thermal energy and power, in particular to a low-entropy co-combustion cycle thermal power 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 an internal combustion and external combustion engine in a country 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 η value of the external combustion cycle system (ie, the high temperature heat source). temperature, i.e. the working fluid temperature is about expansion work) ₂ value is low and the combustion cycle of the system (i.e., the temperature of the low temperature heat source, i.e. the expansion stroke / process finished when the working fluid temperature) the problem of high, more leads Unresolved pollution problems eventually lead to the inability of the external combustion engine or the internal combustion engine to significantly increase the thermal efficiency of the thermodynamic system (the ratio of output power to fuel heating value), and the problem of emissions pollution cannot be fundamentally solve. 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

In a thermodynamic system, if the combustion chamber is an adiabatic combustion chamber, the fuel will transfer the heat generated by the combustion to the product heated fluid and the in-phase heated fluid during combustion. If the combustion chamber is a non-adiabatic combustion chamber, the fuel will be burned when burned. Heat is transferred to the product heated fluid, the in-phase heated fluid, and the externally heated fluid. The so-called product heated fluid refers to the product of combustion chemical reaction (for example, carbon dioxide and water produced by combustion in a thermodynamic system burning hydrocarbons); the so-called in-phase heated fluid means that it is in the same phase as the combustion chemical reaction but does not participate. a chemically combusted fluid (for example, nitrogen in a thermodynamic system using air as an oxidant and carbon dioxide inherent in air); the so-called externally heated fluid refers to heat generated outside the combustion chemical reaction phase and subjected to combustion chemical reactions. The fluid (for example, the water vapor system of the external combustion engine and the cooling system of the internal combustion engine). According to the working principle of the external combustion cycle thermodynamic system and the internal combustion cycle thermodynamic system, it is easy to see that in the external combustion cycle thermodynamic system, only the external heated fluid participates in the work, while the product heated fluid and the phase heated fluid do not participate. Work (see Figure 20), although the product heated fluid and the internal heated fluid are thermally expanded during the combustion process but do not work externally, but the process of entropy increase is heated by the white, so there are quite a lot in the external combustion cycle system. The heat does not pass through the work channel, that is, it does not participate in the work cycle; in the internal combustion cycle system, only the product heated fluid and the in-phase heated fluid participate in the work, while the external heated fluid does not participate in the work (see Figure 21). For example, a cooling system of a conventional internal combustion thermodynamic system (internal combustion engine, gas turbine, etc.) (for example, a cylinder liner cooling system of an internal combustion engine) causes a large amount of heat to be externally operated, and an entropy increase process is performed, thereby generating a huge waste of heat energy. Therefore, in the internal combustion cycle system, there is also a considerable amount of heat that does not pass through the work channel, that is, it does not participate in the work cycle. In short, whether in the external combustion cycle thermal power system or in the internal combustion cycle thermal power system, a large amount of heat is discharged into the environment without being involved in work, and is wasted. In addition, the special heat transfer mode of the external combustion engine requires a large heat transfer temperature difference to ensure the heat transfer efficiency, due to the limitation of the performance of the heat transfer wall material of the working fluid generator (ie boiler), the value of the working medium is The temperature of the high-temperature heat source is low, and the value of the modern state-of-the-art external combustion fluid generator is only about 630 °C (such as steam in the boiler of the ultra-supercritical generator set), so even with the appropriate working fluid The 7^ ₂ value of the external combustion cycle (ie, the temperature of the low-temperature heat source) is reduced to several tens of degrees (ie, about 330 Kelvin), but since the value of 7 is not increased, the thermal efficiency of the external combustion cycle is still low. In the traditional internal combustion cycle, there are compression processes or compression strokes (such as gas turbine gas compression process, conventional internal combustion engine four-stroke cycle or two-stroke cycle compression stroke), but due to the structure and working fluid of the traditional thermodynamic system Limit of the process The pressure at the end of the compression stroke cannot reach a very high level. Even if the compression force is increased, it is difficult to set the pressure after the compression stroke to a very high level, otherwise it will not only consume too much energy (such as pressure). When the contraction stroke is over, the pressure is too high. Although the temperature and pressure after combustion can be significantly improved, the excessive heat consumption of the compression stroke will reduce the thermal efficiency of the whole system, and it may also be caused by excessive temperature. A large amount of NOx causes greater pollution to the environment. For this reason, the pressure in the combustion chamber of the conventional internal combustion thermodynamic system is difficult to reach a high level (generally, the piston type internal combustion engine is only about 15 WIPa, and the turbine is only about 3 MPa). Due to the existence of the equation =( ^ in the internal combustion thermodynamic cycle, and the Kelvin temperature and pressure of the high temperature heat source, respectively, ₂ and the Kelvin temperature and pressure of the low temperature heat source, respectively, K is the adiabatic compression index, and the air is adiabatic. The compression index is 1.4, so there is a basic approximation relationship of the pressure ratio equal to the temperature ratio of about 3.5. It can be seen that in order to reduce the enthalpy ₂ and thereby improve the heat conversion efficiency, it is necessary to make the combustion The pressure of the gas working fluid is greatly increased, reaching a pressure of several tens of MPa or higher. In order to make the gas pressure after the combustion of the original working fluid in the combustion chamber reach such a high level, it is necessary to make the working medium before combustion (ie, the original working medium). The pressure is quite high, preferably at a high pressure and low temperature (because the higher the pressure of the original working fluid charged into the combustion chamber, the lower the temperature, and the temperature after the working fluid expands. It will be lower and the efficiency will be higher). In the conventional internal combustion thermal power system, it is difficult to achieve the working medium (ie, the original working medium) before combustion in the combustion chamber. For this reason, the Γ _{2 is} generally high, reaching about 800 ° C. Therefore, in the traditional internal combustion cycle system, in order to improve efficiency, the main increase is 7, but the increase of 7 will generate a large amount of nitrogen oxides N0x, causing serious pollution to the environment, so the efficiency of the internal combustion cycle is not likely to reach more. High level. It can be seen that 7 in the external combustion cycle system cannot reach a higher level, and Γ ₂ in the internal combustion cycle system is unlikely to reach a lower level. This means that the thermal power conversion efficiency of the conventional external combustion cycle thermodynamic system and the internal combustion cycle thermodynamic system cannot reach a high level. If we carry out a more in-depth analysis, it is not difficult to see that the real driving force of the work process is pressure rather than temperature. Increasing the temperature is only a means of generating pressure. If the working pressure of the high temperature heat source is not high enough, no matter the system has How much heat can't realistically produce the work that should be done (because in reality the working medium pressure in the low-temperature heat source state can't be too low, generally higher than atmospheric pressure, can't achieve infinite expansion), according to the efficiency formula T/ (and / > ₂ for high temperature heat source pressure and low temperature heat source

The pressure is the adiabatic compression index, and the adiabatic compression index of the air is 1. 4) It can be seen that increasing the working fluid pressure in the high temperature heat source state is the only fundamental way to improve the efficiency and power density of the heat engine, and all added to the working medium. The amount of heat and the way of adding must be aimed at increasing the pressure of the working medium under the condition of high temperature heat source. Otherwise, the excessive temperature can only affect the life of the heat machine, put higher requirements on the material and cause more pollution. No benefit. The high temperature and high temperature of the high temperature heat source can achieve both high efficiency and low pollution, which is impossible in traditional internal combustion engines, because the temperature rise during compression is caused by the adiabatic compression process. The relationship between temperature and pressure is = Γ^ is a constant), caused by the combustion reaction The temperature rise is formed by the heat generated by the constant volume chemical reaction, that is, the relationship between temperature and pressure is Ρ = δ Γ (b is a constant, that is, the relationship between pressure and temperature is linear). In a conventional internal combustion engine, these two temperature rises are The process is directly superimposed and then adiabatic expansion works externally, which inevitably leads to over-temperature, which is the cause of low efficiency and high pollution of conventional internal combustion engines (so-called "excess temperature" refers to the temperature during adiabatic expansion. Relationship with pressure, in order to reach a certain end state, the actual temperature of the working fluid is higher than the theoretically required temperature at the starting point); In the conventional external combustion engine, it is difficult to make the high temperature heat source due to material limitations. The working temperature of the state is substantially improved (the working fluid pressure of the traditional external combustion engine is determined by the working temperature). If the working temperature is not high enough, the pressure cannot reach a higher level, and the working fluid cannot be used. Pressurize, otherwise there will be a phase change in the working fluid (except for the hot air machine). Currently, the steam temperature generated by the most advanced ultra-supercritical genset boiler is only 630 ° C or so, the pressure is around 300 atmospheres, so the efficiency of the traditional external combustion engine can not be improved substantially (if the temperature of the traditional external combustion engine can be increased to a few hundred degrees Celsius, the pressure is also more At high levels, the efficiency of the external combustion engine will be substantially improved).

It can be known from the above two aspects: Whether it is the external combustion cycle system or the internal combustion cycle system, there are inherent defects in the process of successful heat conversion. These congenital insufficiencies constitute the low heat efficiency and high pollution status of the traditional engine. That is, the best conventional engines use only about one-third of the fuel's chemical energy, while the other two-thirds are discharged into the environment as waste heat. Moreover, almost all conventional engines use natural air as an oxidant in both external combustion engines and internal combustion engines. Because natural air contains a large amount of nitrogen, in the circulation mode of conventional engines, it inevitably produces pollutants such as NOx. Serious pollution of the environment.

In summary, the circulation mode of the external combustion thermodynamic system and the internal combustion thermodynamic system severely limits the efficiency of thermal power conversion and causes unavoidable pollution emission problems. In the past few decades, in order to improve the efficiency and environmental protection of the engine, the developed countries all over the world have carried out large-scale research and development work, but the results are far from meeting the requirements of people and can never solve the internal combustion engine. And the inherent shortage of external combustion engines. This is like the era of cold weapons. No matter how well human beings are crafted, if there is no birth of gunpowder, weapons cannot make great progress anyway. In other words, in order to fundamentally solve the problem of engine efficiency and pollution, it is necessary to fundamentally get rid of the constraints of the external combustion cycle and the internal combustion cycle, and re-establish a new and better cycle mode after the external combustion cycle and the internal combustion cycle. Under the guidance of this new cycle, the third generation engine with high efficiency, low pollution or zero pollution (the first generation is an external combustion engine and the second generation is an internal combustion engine) is to fundamentally improve the efficiency of the engine. , the only option to reduce engine emissions.

A detailed analysis of the Cobraon equation = r can lead to the conclusion that the molar number of the working fluid is equivalent to the Kelvin temperature r of the working fluid from the perspective of functional contribution. From the thermal power conversion equation = β χ ^^, we can know that to get more work, one is to increase the pass through the work channel (ie, the reference

Ά

Adding the heat of the work cycle) (The G value here is the difference between the heat release amount of the fuel and the heat dissipation amount of the heat in the internal combustion engine. In the external combustion engine, the β value here is the heat release amount of the fuel and the waste heat of the exhaust heat. The difference is, the second is to increase the value of the thermal power conversion efficiency ϋ. For the thermodynamic efficiency equation; 7 = ^ = ^

Ά Q Ά

Mathematical calculations can be concluded: Efficiency; 7 though 7; (i.e. the temperature of the high temperature heat source) ₂ and functions (i.e., the low-temperature heat source temperature), but has a decisive efficiency ^ controlling effect ;, but not Gamma] ₂ 7 (See Figure 22). As shown in Figure 22, at? Under the premise of raising the 7; in order to obtain higher efficiency, otherwise the increase of 7 has little effect on improving efficiency. From the essence of the working process of the heat engine, no matter the heat engine, there are only two working processes: one is the working fluid preparation process, and it can also be said to be the process of manufacturing the working fluid. This is to use the heat to warm the working fluid and then use the temperature to rise. The process of pressure, the most important thing in this process It is the temperature of the working fluid, but the pressure of the working fluid; the other is the working process of the working medium through the working mechanism. In order to achieve efficient and low-pollution thermal power conversion and get more work, we can start from the following aspects: First, let all, almost all or more than the heat released by the combustion of the fuel participate in the work of thermal power through the work channel. That is to say, in the case of the adiabatic combustion chamber, the product heated fluid and the in-phase heated fluid are all involved in the work cycle, and in the case of the non-adiabatic combustion chamber, the product heated fluid, the in-phase heated fluid and the externally heated fluid are all involved. In addition, the best efforts are made to use the heat that is released into the environment after the work cycle (such as the exhaust heat of the internal combustion engine) to make this heat flow back into the system and participate in the work cycle again, so that participation in the work The heat of the cycle is close to, equal to or greater than the heat released by the combustion of the fuel, which essentially increases the value of β in the thermoelectric conversion equation ^ = β χ ^. Secondly, the pressure of the original working fluid in the combustion chamber is greatly increased, and the original working medium pressure of the combustion chamber can be greatly increased by the form of non-gas compression (for example, adding high pressure to the liquid raw working medium and then vaporizing into the combustion chamber under high pressure) In addition, the pressure of the working fluid is greatly improved, and the purpose of greatly reducing the value of ₂ is achieved after the work. Under the premise of ₂ low, do your best to improve within the scope of meeting environmental protection requirements and material requirements! Value (especially for the external combustion cycle thermal power system, increase 7; value is more important), and Γ, Γ ₂ and working moles are equal to the three. Thirdly, under the premise that the working fluid has sufficient pressure, set 7; in the temperature range with little or no NOx formation, that is, to achieve high working pressure and appropriate temperature, and reduce emissions of NOx and other pollutants; Or in some cases, oxygen is used instead of air to generate a combustion reaction in the combustion chamber and the fuel, completely eliminating NOx emissions, using the pressure of high pressure or high pressure to charge the combustion chamber, omitting the compression stroke of the engine, and improving environmental protection. At the same time improve the efficiency of the thermodynamic system.

In the first aspect, in order to solve the defects in the thermodynamic cycle mode of the internal combustion thermodynamic system and the external combustion thermodynamic system that only part of the combustion heat passes through the work channel and the combustion medium pressure is low, the present invention discloses a A low-entropy co-combustion cycle thermal power system. In this low entropy co-firing cycle thermal power The system enters the form of adiabatic combustion chamber by passing the high-pressure raw medium into the adiabatic combustion chamber, or by entering the high-pressure raw medium into the non-adiabatic combustion chamber by entering the inner passage of the high-pressure fluid absorption wall provided on the wall of the non-adiabatic combustion chamber, or The high-pressure raw fluid enters the non-adiabatic combustion chamber by first entering the high-pressure fluid heat-absorbing exhaust heat exchanger disposed on the exhaust passage of the thermodynamic system and the high-pressure fluid heat-absorbing wall passage provided on the wall of the non-adiabatic combustion chamber. In the form of a high-pressure raw fluid that first enters the high-pressure fluid-absorbing exhaust heat exchanger disposed on the exhaust passage of the thermodynamic system and then enters the non-adiabatic combustion chamber, so that all, nearly all or greater than the combustion of the fuel is released. The heat participates in the work cycle through the work channel. The imageable metaphor is as follows: The cooling system of the internal combustion engine no longer cools the combustion chamber wall (cylinder liner, cylinder head, etc.) by means of heat dissipation to the environment, but by bringing the heat from the combustion chamber wall back to the combustion chamber. The power channel (the so-called work channel refers to the channel through which the working fluid flows in the process of participating in the work cycle) or directly returns to the work channel while taking the role of the high-pressure working generator (equivalent to the boiler) The cooling of the combustion chamber wall is completed; the furnace of the boiler of the external combustion engine is no longer only responsible for the combustion heat release, but also bears the role of the combustion chamber of the internal combustion engine. This scheme fundamentally overcomes the disadvantages that only a part of the combustion heat in the traditional thermodynamic system (internal combustion thermodynamic system and external combustion thermodynamic system) participates in the work and the working pressure is low when burning, effectively increasing the participation in work. The heat of circulation increases the efficiency and environmental friendliness of the thermodynamic system. The function of the high-pressure fluid heat-absorbing exhaust heat exchanger provided on the exhaust passage is to recover the heat that is to be discharged to the environment after the work cycle (such as the residual heat of the exhaust of the internal combustion engine), and return the heat to the system to participate again. Power cycle, in this structure, the heat involved in the work cycle is in some cases higher than the heat released by the fuel combustion. The so-called original working fluid refers to the working medium that is not heated by internal combustion combustion, that is, the oxidant, the reducing agent and the expanding agent that enter the combustion chamber, and various phase change substances thereof. The so-called phase change material refers to the original working medium in different states. That is, gaseous, liquid or solid.

In the second aspect, in order to solve the traditional thermal power system, either 7; low (external combustion cycle), Or the problem of high (internal combustion cycle), the low-energy co-combustion cycle thermal power system disclosed by the present invention includes a scheme in which the original working medium enters the combustion chamber in a gaseous state in a high-pressure state to perform internal combustion heating in the combustion chamber, which The solution creates conditions for controlling the combustion temperature (ie, Γ, ) in the combustion chamber and increasing the combustion pressure. In this solution, since the pressure of the original working fluid entering the combustion chamber is established before the heating by the liquid pump, the pressure can reach a high level, so the working pressure after combustion will be greatly improved compared with the conventional thermodynamic system. , reaching a fairly high level, the working temperature in the combustion chamber is also significantly higher than the highest working temperature of the traditional external combustion cycle thermodynamic system. A large increase in the combustion pressure of the original working fluid in the combustion chamber will greatly reduce the temperature of the working fluid after completion of the work process (ie, ₂ ). This solution essentially solves the problem of either η low (external combustion cycle) or τ ₂ (internal combustion cycle) in the conventional thermodynamic system, which can substantially improve the thermal power conversion efficiency of the thermodynamic system.

In the third aspect, in order to solve the environmental problem, the temperature of the working fluid in the combustion chamber can be kept below the nitrogen oxide formation temperature, thereby avoiding the formation of bismuth, which is an effective solution, but it can also be replaced by oxygen. Air as an oxidant fundamentally solves the problem of emissions. The low entropy co-combustion cycle thermodynamic system disclosed in the present invention adopts a scheme in which oxygen is used instead of air as an oxidant. Oxygen is a commonly used chemical raw material with a relatively high liquefaction temperature, relatively easy storage, and low manufacturing costs. It can be directly burned with oxygen and fuel, or it can be mixed with oxygen, fuel and expansion agent. The latter can control the temperature of the combustion chamber to meet the thermal load requirements of the civil engine. To this end, an expander system is provided in certain aspects of the low entropy co-firing thermal power system disclosed in the present invention. The swelling agent refers to a working medium which does not participate in the combustion chemical reaction to cool and adjust the number of working hours of the working medium and expands the work. The use of oxygen or an oxygen-containing gas that does not produce harmful compounds during thermal power conversion as an oxidant for a thermodynamic cycle system is an important choice for solving the problem of emissions from thermal power conversion systems.

The so-called co-firing cycle thermodynamic system of the present invention refers to all the heat released by the combustion of the fuel or nearly All heat or all of the heat released from the combustion of the fuel is involved in the thermal power system of the work cycle (in the structure with the original working heat absorption and exhaust heat exchanger, the heat involved in the work cycle may be higher than the combustion of the fuel Heat). The so-called co-firing cycle of the present invention means that all of the heat released by the combustion of the fuel or nearly all of the heat or all of the heat released by the combustion of the fuel is involved in the cycle of the work cycle. In order to realize all the heat (or nearly all heat) after the combustion of the fuel is involved in the work cycle, three methods can be used, one is to insulate the combustion chamber, and the other is to use the original working fluid to enter the combustion chamber wall before entering the combustion chamber. The heat absorption is brought back to the combustion chamber or directly involved in the work. The third is to use the original working fluid to return the exhaust or exhaust waste to the combustion chamber or directly participate in the work. For example, adiabatic engines, combined cycles, etc. are all forms of a co-firing cycle.

The so-called low entropy co-firing cycle thermodynamic system of the present invention refers to all the heat released by the combustion of the fuel or nearly all the heat or all the heat released by the combustion of the fuel are all involved in the work cycle of the heat power system (with the original working heat absorption row) In the structure of the gas heat exchanger, the heat involved in the work cycle may be higher than the heat released by the fuel combustion. When the work mechanism is set as the piston type work mechanism, the highest pressure of the working medium is significantly higher than that of the conventional piston type internal combustion engine. The highest pressure of the chamber, when the working mechanism is set to be a non-piston working mechanism, the highest pressure of the working medium is significantly higher than the highest pressure of the combustion chamber of the conventional non-piston thermal power system, and the temperature of the low temperature heat source of the system is Γ ₂ The amplitude is lower than the exhaust temperature of the internal combustion engine, and the temperature of the high-temperature heat source is 7; it is much higher than the highest working temperature of the traditional external combustion cycle thermodynamic system, and the efficiency is essentially higher than that of the conventional thermodynamic system. Sexual improvement system. This system is a third generation thermodynamic system (defined as a third generation engine in the present invention) following the external combustion cycle thermodynamic system and the internal combustion cycle thermodynamic system. The so-called low entropy co-firing cycle of the present invention means that all the heat released by the combustion of the fuel or almost all the heat or more than the heat released by the combustion of the fuel are all involved in the work cycle, and the highest pressure of the working medium is substantially higher than that in the conventional thermodynamic system. The highest pressure of the working fluid and no circulation of excess temperature. In order to further improve the environmental friendliness of the so-called low entropy co-firing cycle thermodynamic system, oxygen-containing gas which does not generate harmful compounds during the heat work conversion process can be used as an oxidant of the low entropy co-firing cycle thermodynamic system. In the low-energy co-combustion cycle thermal power system disclosed by the present invention, since the pressure and temperature of the original working fluid and the components can be independently controlled, the maximum pressure and the maximum temperature of the combustion chamber can be independently controlled, that is, This establishes the indoor working fluid pressure in the conventional thermodynamic system through gas adiabatic or near adiabatic compression process (so-called indoor working fluid pressure refers to the pressure in the combustion chamber when it is to be burned, and this pressure should meet the design requirements). The process is completely different. In the conventional 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 low-energy co-combustion circulating thermal power system disclosed in the present invention does not mean The highest temperature of the working medium in the combustion chamber is high. For this reason, scientifically and effectively adjusting the highest pressure and the highest temperature of the working medium in the combustion chamber can produce a thermodynamic system in which the temperature Γ _{2 of the} low-temperature heat source is very low, or even substantially lower than the ambient temperature. When _{2 is} low to a certain value, the thermal efficiency of such a thermodynamic system may exceed 100%. This thermal power system with a thermal efficiency exceeding 100% is defined in the present invention as an ultra-low entropy co-combustion cycle thermodynamic system. The so-called ultra-low entropy co-combustion cycle of the present invention means that all the heat released by the combustion of the fuel participates in the work cycle, and the highest pressure of the working medium is significantly higher than the highest pressure of the working medium in the conventional thermodynamic system, and the working fluid expands. The temperature after work is significantly lower than the ambient temperature, and the thermal efficiency exceeds 100% of the cycle. The ultra-low entropy co-combustion cycle thermal power system does not violate the law of conservation of energy, and the reasons are as follows: 1. The calorific value of the fuel refers to the release of the fuel when it reaches a standard state (which can be approximated to an environmental state) after being burned under standard conditions. The heat. The low temperature heat source temperature of the ultra low entropy co-firing thermal power system can be close to, lower than or substantially lower than the ambient temperature (that is, the temperature in an approximate standard state). When the temperature of the low-temperature heat source Γ _{2 is} significantly lower than the ambient temperature, it is equivalent to having more heat to participate in the work cycle. When _{2 is} low to a certain extent, 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-combustion cycle thermodynamic system, there are lower temperature heat sources in some cases, such as liquid oxygen, liquefied fuel, Liquefied expansion agent (such as liquefied carbon dioxide, etc.), 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 these The heat is brought into the combustion chamber to participate 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 made larger than the fuel. The heat released by the combustion (i.e., the calorific value of the fuel) causes the so-called thermal efficiency to be higher than 100%.

The chemical energy can be added to the working medium with any high pressure and any high temperature, and as long as the chemical energy is added to the working medium in a scientific manner and then the working medium is expanded, the temperature of the working medium after the expansion work can be greatly increased. Temperature below standard (approx. ambient temperature). If the temperature of the working fluid after the expansion work is at a very low level, or the working medium in the expansion work is absorbed from the environment, the output of the system can be made larger than the chemical energy added. In this case, the grade of chemical energy can be considered to be higher than the mechanical energy (work).

The low-energy co-combustion cycle thermodynamic system disclosed in the present invention may have no compression process (stroke), a compression process (stroke) or a partial compression process (stroke) after the original working fluid enters the combustion chamber. The so-called increase in the pressure of the combustion chamber by means of non-gas compression does not mean that there must be any compression process without gas, but rather that there is no gas compression process, and the high-pressure gas is completely charged into the combustion chamber to establish the original labor. The pressure can also be filled with high-pressure gas into the combustion chamber after the compression process or part of the compression process to establish the indoor working fluid pressure, but the mainstream is to form a high-pressure gas by vaporizing or criticalizing the pressurized liquid.

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

The low-energy co-combustion cycle thermal power system disclosed by the invention has the advantages that the original working medium is independently controllable, can be controlled by electronic control or the like, can not only adjust the fuel, but also can adjust the oxygen and the expansion agent, so the invention is low The entropy co-combustion cycle thermal power system has a better load response.

The so-called carbonaceous compound of the present invention means a combustible compound containing carbon such as gasoline, diesel, alcohol or the like.

The so-called ultrahigh pressure liquid pump of the present invention refers to a liquid pump having an output pressure of 10 MPa or more. The pressure of the original working fluid entering the combustion chamber can be brought to or near 10 MPa or exceeds 10 MPa by the ultra-high pressure liquid pump.

The so-called self-liquefaction of the present invention means that the temperature is greatly reduced after the completion of the work stroke of the working medium, The process of liquefaction of a part of a working medium or part of a working medium or working medium.

The maximum working fluid pressure (combustion pressure) of the combustion chamber is determined by the composition of the original working fluid before combustion, the total pressure, the temperature, and whether the fuel combustion heat release and the combustion chamber volume change. In the structure of the piston-type working mechanism of the low-energy hybrid combustion cycle thermal power system disclosed in the present invention, the maximum working fluid pressure of the combustion chamber is greater than 15.5 MPa, 16 MPa, 16.5 MPa, 17 MPa, 17.5 MPa, 18MPa, 18.5MPa, 19MPa, 19.5MPa 20MPa, 20.5MPa, 21MPa, 21.5MPa, 22MPa, 22.5MPa, 23 Pa 23.5MPa, 24MPa, 24.5MPa, 25MPa, 25.5MPa, 26MPa, 26.5MPa, 27MPa, 27.5MPa, 28MPa 28.5 Pa 29MPa, 29.5MPa, 30MPa, 31MPa, 32MPa, 33MPa, 34MPa, 35 Pa 36WIPa, 37MPa, 38MPa, 39 Pa 40MPa, 41MPa, 42MPa, 43MPa, 44MPa, 45MPa, 46MPa, 47MPa, 48MPa, 49MPa or 50MPa; In the structure of the non-piston working mechanism of the low-energy hybrid combustion cycle thermodynamic system disclosed in the present invention, the maximum working pressure of the combustion chamber is greater than 2 MPa, 2.5 MPa, 3 MPa, 3.5 MPa, 4 MPa, 4.5. MPa, 5MPa, 5.5MPa, 6MPa> 6.5MPa, 7MPa, 7.5MPa, 8MPa, 8.5 Pa 9MPa, 9.5MPa, 10MPa, 10.5MPa, 11MPa, 11.5MPa, 12MPa, 12.5MPa, 13MPa, 13.5MPa, 14MPa, 14.5 MPa, 15 MPa, 15.5 MPa 16 MPa, 16.5 MPa, 17 MPa, 17.5 MPa> 18 MPa, 19 MPa, 20 MPa, 21 MPa, 22 MPa, 23 MPa, 24 MPa, 25 MPa, 26 MPa, 27 MPa, 28 MPa> 29 MPa or 30 MPa. In order to achieve the highest design pressure of the combustion chamber working fluid, to achieve high efficiency, low pollution and low combustion chamber heat load, the composition of the original working fluid (adjusting the composition, the heat capacity can be adjusted), pressure, temperature and oxygen content ( Affect the heat release) for comprehensive control. In other words, by controlling the state and composition of the original working fluid, the state of the gas in the combustion chamber after the combustion chemical reaction is controlled. The maximum temperature of the working fluid in the combustion chamber should match the highest pressure of the working fluid in the combustion chamber. If the maximum temperature of the working medium in the combustion chamber is too high and cannot match the highest pressure of the working medium, the temperature of the working medium will be too high after the work is completed, which is harmful. And no benefit.

The principle of the low-energy co-combustion cycle thermal power system disclosed by the present invention is to pass the high-pressure gasification of the original working fluid or to critically absorb the heat of the system and/or the heat in the environment and bring the heat back to the combustion chamber or through the combustion. The chamber establishes a high pressure state, which is greater than the combustion of the fuel in the structure of the intermittent combustion of the combustion chamber. The heat released or equal to the heat released by the combustion of the fuel or nearly equal to the heat released by the combustion of the fuel directly participates in the work cycle under the condition of exceeding the maximum pressure of the conventional combustion chamber working fluid; in the structure of the continuous combustion of the combustion chamber, the content is greater than the fuel The heat released by the combustion or the amount of heat released by the combustion of the fuel or the heat released by the combustion of the fuel is intermittently introduced into the piston type working mechanism through the control valve under the condition of exceeding the maximum pressure of the traditional combustion chamber working medium. A power cycle or continuous introduction of a non-piston work mechanism participates in the work cycle, and under conditions that meet the material and emission requirements, with sufficient pressure to match (ie, a lower r ₂ condition can be achieved) Maximize the maximum temperature of the working fluid in the combustion chamber to achieve high efficiency; if liquefaction recovery of the exhaust gas is required, the highest pressure matching the maximum temperature of the combustion chamber should be higher to obtain lower exhaust gas. The temperature is conducive to the cooling and / or liquefaction of the exhaust. The so-called criticalization refers to the process in which a substance changes from a non-critical state to a critical state or a supercritical state.

The specific technical scheme of the low-energy co-combustion cycle thermal power system disclosed by the present invention is as follows: A low-entropy co-combustion cycle thermal power system, comprising a work mechanism, a combustion chamber, an oxygen source and a fuel source, the oxygen source is oxygenated a high pressure supply system is in communication with the combustion chamber, the fuel source is in communication with the combustion chamber via a high pressure fuel supply system, and an oxygen absorption heat exchanger is disposed in the oxygen high pressure supply system, wherein the oxygen source is Oxygen absorbs heat in the oxygen heat-absorbing heat exchanger to form high-pressure gaseous oxygen or critical state oxygen into the combustion chamber, and the working mechanism is set as a non-piston type working mechanism or a piston type working mechanism; The minimum pressure capacity of the oxygen high pressure supply system in the structure in which the working mechanism is set to be a non-piston type working mechanism is greater than or equal to 2 MIPa, and the oxygen is in the structure in which the working mechanism is a piston type working mechanism. The minimum pressure capacity of the high pressure supply system is greater than or equal to 3 MPa _;

The combustion chamber is in communication with at least one of the work mechanisms, and the work mechanism externally outputs power. A low-entropy co-combustion cycle thermodynamic system includes a work mechanism, a combustion chamber, an oxygen source, a fuel source, and a source of expansion agent, wherein the oxygen source is in communication with the combustion chamber via an oxygen high pressure supply system, the fuel source The fuel high pressure supply system is in communication with the combustion chamber, and the expansion agent source is connected to the combustion chamber via a high pressure supply system of the expansion agent;

Providing an oxygen absorbing heat exchanger in the oxygen high pressure feeding system, wherein oxygen in the oxygen source is in the oxygen Absorbing heat in the endothermic heat exchanger to form high pressure gaseous oxygen or critical state oxygen entering the combustion chamber; providing an expansion agent heat absorption heat exchanger in the expansion agent high pressure supply system, the expansion agent in the expansion agent source Absorbing heat in the expansion agent heat absorption heat exchanger to form a high pressure gaseous expansion agent or a critical state expansion agent into the combustion chamber;

The working mechanism is set as a non-piston type working mechanism or a piston type working mechanism; in the structure in which the working mechanism is a non-piston type working mechanism, the oxygen high pressure feeding system and the expansion agent The lowest pressure bearing capacity of any one of the high pressure feeding systems is greater than or equal to 2 MPa; in the structure in which the working mechanism is a piston type working mechanism, the oxygen high pressure feeding system and the expansion agent are supplied with high pressure The minimum pressure capacity of either of the delivery systems is greater than or equal to 3 MPa _;

The combustion chamber is in communication with at least one of the work mechanisms, and the work mechanism externally outputs power. In a structure in which the fuel in the fuel source is a liquefied fuel, a fuel heat absorption heat exchanger is disposed in the fuel high pressure supply system, and the liquefied fuel in the fuel source absorbs heat in the fuel heat absorption heat exchanger A high pressure gaseous fuel or critical state fuel is formed into the combustion chamber.

Providing a high-pressure fluid heat-absorbing exhaust heat exchanger in an exhaust passage of the low-energy hybrid combustion cycle thermodynamic system; in the structure provided with the oxygen heat-absorbing heat exchanger, the oxygen heat-absorbing heat exchanger is provided a high-pressure fluid heat-absorbing exhaust heat exchanger; and/or in a structure provided with the expander heat-absorbing heat exchanger, the expander heat-absorbing heat exchanger is set to the high-pressure fluid heat-absorbing row Gas heat exchanger.

A high pressure fluid endothermic exhaust heat exchanger is disposed in an exhaust passage of the low entropy co-firing cycle thermodynamic system, and the fuel heat absorption heat exchanger is configured as the high pressure fluid endothermic exhaust heat exchanger.

Providing a high-pressure fluid heat-absorbing environment heat exchanger in the low-energy co-firing cycle heat power system; in the structure provided with the oxygen heat-absorbing heat exchanger, the oxygen heat-absorbing heat exchanger is set to the high pressure a fluid absorbing environment heat exchanger; and/or in the structure provided with the expansion agent heat absorbing heat exchanger, the expansion agent heat absorbing heat exchanger is configured as the high pressure fluid absorbing heat exchanger.

A high pressure fluid endothermic environment heat exchanger is disposed in the low entropy co-firing cycle thermodynamic system, and the fuel endothermic heat exchanger is configured as the high pressure fluid endothermic environment heat exchanger.

Providing a high-pressure fluid heat-absorbing wall inner passage in a combustion chamber wall of the combustion chamber; in the structure provided with the oxygen heat-absorbing heat exchanger, the oxygen heat-absorbing heat exchanger is set to absorb heat of the high-pressure fluid In the wall passage; and/or in the structure provided with the expansion agent heat absorption heat exchanger, the expansion agent heat absorption heat exchanger is provided The inner channel of the wall is absorbed by the high pressure fluid.

A high pressure fluid heat absorbing wall inner passage is provided in the combustion chamber wall of the combustion chamber, and the fuel heat absorbing heat exchanger is set as the inner passage of the high pressure fluid heat absorbing wall.

The low-twisted-combustion cycle thermal power system further includes an open combustion envelope disposed in the combustion chamber and in communication with the combustion chamber, the oxygen source being passed through an oxygen high pressure supply system and An open combustion envelope is connected, the fuel source is in communication with the open combustion envelope via a fuel high pressure supply system, and the expander source is communicated with the combustion chamber via a bulk expander high pressure supply system, wherein the expander source is An expansion agent is introduced into the space between the open combustion envelope and the combustion chamber wall of the 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 of the combustion chamber The thermal load requirements of the chamber wall.

The low entropy co-firing cycle thermodynamic system further includes an oxygen expansion agent premixing chamber, wherein the oxygen source is in communication with the combustion chamber via the oxygen high pressure supply system via the oxygen expansion agent premixing chamber a source of expansion agent is communicated with the combustion chamber via the expansion agent high pressure supply system and the oxygen expansion agent premixing chamber, the oxygen in the oxygen source and the expansion agent in the expansion agent source are in the oxygen The expansion agent premixing chamber is premixed and introduced into the combustion chamber.

The low entropy co-combustion cycle thermal power system further includes an oxy-fuel premixing chamber, wherein the oxygen source is communicated with the combustion chamber via the oxy-fuel high-pressure supply system via the oxy-fuel pre-mixing chamber, the fuel source The fuel high pressure supply system is further communicated with the combustion chamber via the oxy-fuel premixing chamber, and oxygen in the oxygen source and fuel in the fuel source are premixed in the oxyfuel premixing chamber It is then introduced into the combustion chamber.

The temperature of the original working medium after charging into the combustion chamber is equal to or lower than the temperature of the standard state.

The expansion agent is set as a gas liquefied material.

Providing a high-pressure fluid heat-absorbing exhaust heat exchanger in an exhaust passage of the low-enthalpy mixed-burn cycle thermal power system, the oxygen heat-absorbing heat exchanger, the expander heat-absorbing heat exchanger, and the fuel suction One, two or three heat exchangers in the heat exchanger are set to be heated by the heated fluid first entering the high pressure fluid heat absorbing exhaust heat exchanger and then entering the series heat in the passage of the high pressure fluid heat absorbing wall Switch group.

The fuel in the fuel source is set to be a carbon-containing compound; in a structure not including the expansion agent high-pressure supply system, an ultra-high pressure liquid is disposed in the oxygen high-pressure supply system and/or the fuel high-pressure supply system a pump; or in a structure including the expansion agent high pressure supply system, in the oxygen high pressure supply system, The expansion agent high pressure supply system and/or the high pressure supply system of the fuel is provided with an ultra high pressure liquid pump;

K—1 according to ^ 7 = adjusting the pressure of the ultrahigh pressure liquid pump under the premise of setting the pressure ₂ after expansion

The V body 2 output pressure further adjusts the indoor working fluid pressure so that the highest pressure and the highest temperature τ in the combustion chamber satisfy the low temperature heat source temperature of the low entropy co-combustion cycle thermodynamic system Γ ₂ reaches the carbon dioxide at the pressure of Ρ ₂ The liquefaction temperature is required to self-liquefy the exhaust gas of the low entropy co-firing thermal power system to achieve the purpose of recovering carbon dioxide in a liquid or solid state.

The combustion chamber disclosed in the present invention may be configured as a continuous combustion chamber in a structure communicating with the non-piston type working mechanism; the combustion chamber disclosed in the present invention may be provided in a structure communicating with the piston type working mechanism. The continuous combustion chamber may be a batch type combustion chamber, and when it is a continuous combustion chamber, a control valve is required between the continuous combustion chamber and the piston type working mechanism. When the combustion chamber of the present invention is set as a continuous combustion chamber and is connected with one or more piston type working mechanisms, the fuel supply system (including the high pressure common rail system and the electronic control system, etc.) in the conventional engine is cancelled. , which will greatly simplify the fuel supply system and make the combustion more efficient and environmentally friendly, because in this structure, the fuel has enough time to mix with oxygen or oxygen-containing gas, so that mixing and combustion are more sufficient. .

The so-called piston type thermodynamic system of the present invention refers to a thermodynamic system that utilizes a piston to work, and the so-called non-piston type thermodynamic system refers to a thermodynamic system that uses a mechanism other than a piston (such as an impeller) to perform work. The piston type working mechanism of the present invention refers to a mechanism that uses a piston to perform work, and the so-called non-piston type work mechanism refers to a mechanism that uses a mechanism other than a piston (such as an impeller) to perform work.

The temperature of the original working medium after the low-entropy mixed-burning cycle thermodynamic system disclosed in the present invention is charged into the combustion chamber is lower than 100 ° C, 50 ° C, 20 ° C, 10 ° C or 0 ° C. 5MPa。 The lowest pressure bearing capacity of the oxygen high pressure supply system is greater than or equal to 2. 5MPa, the lowest pressure bearing capacity of the oxygen high pressure supply system is greater than or equal to 2. 5MPa , 3MPa, 3. 5MPa, 4MPa, 4. 5MPa, 5MPa, 5. 5MPa, 6MPa, 6. 5MPa, 7MPa, 7. 5MPa, 8MPa, 8. 5MPa, 9MPa, 9. 5MPa, 10MPa> 10. 5MPa> 1 1 MPa, 1 1 . 5MPa 1 2MPa, 12. 5MPa, 13MPa, 13.5MPa, 14MPa, 14.5MPa, 15MPa, 15.5MPa, 16MPa, 16.5MPa, 17MPa,

17.5 Pa 18MPa, 18.5MPa, 19MPa 19.5MPa, 20MPa, 21MPa, 21.5MPa, 22MPa,

22.5MPa, 23MPa, 23.5MPa, 24MPa, 24.5MPa, 25MPa, 25.5MPa, 26MPa, 26.5MPa, 27MPa, 27.5MPa, 28MPa, 28.5 Pa 29MPa, 29.5MPa or 30MPa. In the structure in which only the oxygen high pressure feeding system is provided, when the working mechanism is set as a piston type working mechanism, the minimum pressure bearing capacity of the oxygen high pressure feeding system is 3.5 MPa or 4 MPa or more. 4.5MPa, 5MPa, 5.5MPa, 6MPa, 6.5MPa 7MPa, 7.5MPa, 8 Pa 8.5MPa, 9MPa, 9.5MPa, 10MPa, 10.5MPa, "MPa, 11.5MPa, 12MPa, 12.5MPa, 13MPa, 13.5MPa, 14MPa 14.5MPa, 15MPa, 15.5MPa, 16MPa, 16.5MPa, 17MPa, 17.5MPa, 18MPa,

18.5MPa, 19MPa, 19.5MPa, 20MPa, 21MPa, 21.5MPa, 22MPa, 22.5MPa, 23MPa,

23.5 MPa, 24 MPa, 24.5 MPa, 25 MPa, 25.5 Pa 26 MPa, 26.5 MPa, 27 MPa, 27.5 MPa, 28 Pa 28.5 MPa, 29 MPa, 29.5 MPa or 30 MPa. In the structure provided with the oxygen high pressure supply system and the expansion agent high pressure supply system, when the working mechanism is set as a non-piston type working mechanism, the oxygen high pressure supply system and the The minimum pressure capacity of any one of the expansion agent high pressure supply systems is greater than or equal to 2.5 MPa, 3 MPa, 3.5 MPa, 4 MPa, 4.5 MPa, 5 MPa, 5.5 MPa, 6 MPa, 6.5 MPa, 7 MPa, 7.5 MPa, 8 MPa, 8.5MPa, 9MPa, 9.5MPa, 10MPa, 10.5MPa, 11MPa, 11.5MPa, 12MPa, 12.5MPa, 13MPa, 13.5MPa, 14MPa, 14.5MPa, 15MPa, 15.5MPa, 16MPa, 16.5MPa 17MPa, 17.5 Pa. 18MPa, 18.5 MPa, 19MPa, 19.5MPa, 20MPa, 21MPa, 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 or 30MPa.

In the structure provided with the oxygen high pressure supply system and the expansion agent high pressure supply system, when the work mechanism is set as a piston type work mechanism, the oxygen high pressure supply system and the The minimum pressure capacity of either of the expansion agent high pressure supply systems is greater than or equal to 3.5 MPa, 4 MPa, 4.5 MPa, 5 Pa 5.5 MPa, 6 MPa, 6.5 MPa, 7 MPa, 7.5 MPa, 8 MPa, 8.5 MPa, 9 MPa, 9.5. MPa, 10MPa, 10. 5MPa, 1 1 MPa, 1 1 . 5MPa, 1 2MPa, 12. 5 Pa 1 3MPa, 13. 5MPa, 14MPa, 14. 5MPa, 15 MPa, 15. 5MPa, 16 MPa, 6.5 MPa, 1 7MPa, 17. 5MPa, 1 8MPa, 18. 5MPa, 1 9MPa, 1 9. 5MPa, 20 Pa 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 or 30MPa.

The engine and the thermodynamic system are equivalent.

The third generation engine is a new generation engine developed under the guidance of a low entropy co-firing cycle following an external combustion cycle engine and an internal combustion cycle engine, that is, the low entropy co-firing cycle thermodynamic system. The low entropy co-combustion cycle mode and the ultra-low entropy co-combustion cycle mode are a new cycle mode superior to the external combustion cycle and better than the internal combustion cycle, and are a more advanced cycle mode of thermal power conversion. Therefore, the low-entropy co-combustion cycle system must have higher efficiency than the external combustion cycle system, compared to the internal combustion cycle system. Under the guidance of this cycle mode, a new generation of heat engines, namely the third generation engine, which is superior to the external combustion engine and the internal combustion engine, which is efficient, energy-saving and low-polluting, will be developed. The so-called oxygen controllability of the present invention means that the oxygen can be precisely controlled by the control components such as the pressure pump, the temperature sensor, the pressure sensor, and the controlled electromagnetic valve before being charged into the combustion chamber, and the amount of the oxygen introduced into the cylinder. Since the amount of fuel can be easily and accurately controlled, oxygen can more easily form an optimal mixing ratio with the fuel in the combustion chamber, achieving a more ideal combustion state, and ultimately improving the efficiency and emissions of the system. In conventional engines, the amount of oxidant is determined by the piston or compressor, so it is difficult to get precise control.

In the low-energy hybrid combustion cycle thermodynamic system disclosed in the present invention, the high-pressure original working medium is introduced into the adiabatic combustion chamber, or the high-pressure raw material is firstly sucked into the high-pressure fluid provided on the non-adiabatic combustion chamber wall. The hot-walled passageway enters the form of a non-adiabatic combustion chamber, or by passing the high-pressure raw medium into a high-pressure fluid-absorbing exhaust heat exchanger disposed on the exhaust passage of the thermodynamic system and on the wall of the non-adiabatic combustion chamber. The high-pressure fluid-absorbing wall passage enters the form of a non-adiabatic combustion chamber, or enters the high-pressure fluid heat-absorbing exhaust heat exchanger provided on the exhaust passage of the thermodynamic system by entering the high-pressure raw medium. In the form of a hot combustion chamber, it is achieved that all, almost all or more than the heat released by the combustion of the fuel participates in the work cycle through the work channel. On the premise that all the heat released by the fuel combustion is involved in the work cycle, the higher the pressure of the original working fluid and the lower the temperature, the better the environmental protection of the thermodynamic system and the higher the efficiency.

According to the Kolaberon equation ^ = r, the molar number of the working fluid is equivalent to the Kelvin temperature of the working fluid from the perspective of the functional contribution. However, because the Kelvin temperature is based on 273.15, it is more difficult to multiply the Kelvin temperature if multiple work is to be obtained. Multiplying the number of moles ^ is relatively easy, and more work can be obtained, as explained below:

It is assumed that the temperature of the original working fluid before the combustion of the fuel is Γ. The working mole number is π. The heat released by the combustion of the fuel is ρ, then the temperature of the working fluid after the combustion of the fuel is T = 7 ₊ 2 / CM (where c and M are the specific heat capacity and mass of the working fluid after the fuel combustion, respectively), so the fuel is burned. Qualitative function

PV = n ₀ RT^nXT, +QICM); If the molar amount of working fluid is increased to 2«. (ie, doubled), the temperature of the original working fluid before the combustion of the fuel is still Γ. The heat released by the combustion of the fuel is still β, and the temperature of the working fluid after the combustion of the fuel is about Γ/=Γ. +Q/2CM, so the working force of the working fluid after fuel combustion after the increase of the number of moles is = n ₀ R _TL ' = 2" T _{O +} Q/2CM"). Therefore, before and after the increase in the number of moles, the difference in the functional force of the working medium is ^ -^^. /^. Obviously, the system can achieve higher functionality without increasing the number of moles and the initial temperature of the working fluid and the heat released by the fuel. In the low-energy co-firing thermodynamic system disclosed in the present invention, by adding a form of a swelling agent to increase the number of moles of the working medium, the function can be improved, that is, more work can be obtained when the conditions are mature.

In order to improve the working ability of the working medium, the traditional method is to increase the temperature of the working medium, and this method is correct and effective. However, from the above analysis, it can be seen that under the same heating conditions, the molar number of the working medium is effectively increased, although the temperature of the working medium is lowered, but due to the increase of the mole number, the functional force will be obtained. Significantly improved. Therefore, in the thermodynamic system, the molar number n and the working temperature T should be taken into consideration, and the fact that the molar number "and the working temperature T is equivalent to the functional force" is fully recognized.

The combustion mode in the present invention may be direct combustion of fuel and oxygen, or may be oxygen, fuel and expansion. Mixing combustion, it is also possible to establish a core combustion zone in the expansion agent in the combustion chamber, in which the oxygen and fuel are directly combusted and mixed with the expansion agent, so that the fuel and oxygen can be directly burned by the expansion agent. The excessively high temperature flame is isolated from the combustion chamber wall, thereby reducing the thermal load on the 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 oxygen, fuel and its reaction products are contained, containing no or only a small amount of 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 oxygen and fuel are mixed with a high-pressure gaseous expansion agent by adjusting the supply mode of oxygen and fuel, that is, a flame when the oxygen and the fuel are combusted by a high-pressure gaseous expansion agent. The combustion chamber is isolated. The purpose of setting up the open combustion envelope is to make the combustion chemical reaction more complete, easier and faster than the oxygen and oxygen, reduce the emission of carbon monoxide and hydrocarbons, and let the combustion be surrounded by the high-pressure gaseous expansion agent. It is equivalent to suspending the core combustion zone in the combustion chamber, thereby forming an open combustion envelope and gas isolation from the combustion chamber wall, thereby greatly reducing the heat load on the combustion chamber wall.

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 combustion chamber with the flame, thereby avoiding the direct heat transfer of the flame to the wall of the combustion chamber. A new cooling method for the walls of the combustion chamber is formed. That is to say, the traditional internal combustion engine (including the gas turbine) is that the flame directly contacts the combustion chamber wall and then cools the combustion chamber wall, which inevitably results in a large amount of low 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 combustion chamber wall, and the heat obtained by the cooling remains in the working medium, thereby improving the energy utilization rate and thereby improving the thermal power system. Thermal efficiency.

The so-called expansion agent of the present invention refers to a working medium which does not participate in the combustion chemical reaction to cool and adjust the number of moles of working medium, and which is a working fluid, such as water vapor, carbon dioxide, helium, nitrogen and water, Liquid carbon dioxide, liquid helium, liquid nitrogen, etc. The so-called expander source refers to a device that provides a gas expander or a liquid expander.

The so-called oxygen in the present invention refers to pure oxygen or oxygen which does not produce harmful compounds during thermal power conversion. Gas. The so-called oxygen source refers to all equipment, systems or vessels that can supply high-pressure oxygen or high-pressure oxygen-containing gas, such as commercial oxygen sources such as high-pressure oxygen storage tanks, liquefied oxygen tanks or hydrogen peroxide storage tanks, and on-site in thermal power systems. Oxygen system (such as membrane separation oxygen system). If the source of the expansion agent is water and the source of oxygen is hydrogen peroxide, the two may be disposed in the same storage tank, and the ratio of the oxygen to the expansion agent is adjusted by adjusting the concentration of the aqueous hydrogen peroxide solution.

The gas liquefied matter referred to in the present invention means a gas to be liquefied, such as liquid nitrogen, liquid helium, liquid carbon dioxide or liquefied air.

In the low-energy co-firing cycle thermodynamic system disclosed by the present invention, if the expansion agent is made into a gas liquefaction, not only the gas liquefaction can be utilized as a function of the expansion agent, but also the gas liquefaction can be utilized in the form of a pneumatic engine. The stored energy, this structure overcomes many of the shortcomings of conventional pneumatic engines, improves the efficiency and environmental friendliness of the system; this essentially constitutes an internal gas engine, and the so-called internal gas engine refers to the introduction of gas liquefaction into the combustion chamber of the internal combustion engine. , the gas liquefaction and the gas working medium in the cylinder are mixed and work simultaneously; if liquid nitrogen is used as the expansion agent, the temperature of the original working fluid into the combustion chamber and the amount of nitrogen introduced into the combustion chamber should be reduced. The combustion temperature in the combustion chamber avoids the formation of nitrogen oxides. Liquid nitrogen is safe, low in cost and abundant in resources. It can be produced by air-fractionation using cheap electricity such as Gudian. According to calculations, the energy density of liquid nitrogen is comparable to that of batteries, and it has a strong function. The latent heat of liquid nitrogen is only There are about 10% of water, so it is an excellent expansion agent.

In the low-energy hybrid combustion cycle thermodynamic system disclosed in the present invention, when introducing the original working fluid into the combustion chamber, the pressure of the original working medium should be increased as much as possible, and the critical state of the original working medium should be maintained as much as possible. The so-called critical state includes the critical state of the original working fluid, the supercritical state and the ultra-supercritical state.

The so-called feeding system of the present invention refers to a system for supplying the original working medium to the combustion chamber according to the requirements of the combustion conditions of the combustion chamber of the thermodynamic system, including a supply passage such as a pipeline, a valve and a pump, and may also include a spray. Device. The feeding system can be continuously supplied, or can be delivered intermittently, and can also be controlled to be supplied (such as timing delivery, adjustable flow supply, etc.). The heat source of the oxygen heat-absorbing heat exchanger, the expander heat-absorbing heat exchanger, and the fuel heat-absorbing heat exchanger in the present invention may be an environment or a low-quality heat source in the system, such as exhaust of a system.

The so-called high pressure fluid endothermic heat exchanger of the present invention refers to a heat exchanger capable of absorbing heat from a high pressure fluid from the environment. In some cases, the low-energy co-firing cycle thermodynamic system may not generate waste heat higher than the environment or generate only a small amount of waste heat higher than the environment, so that the original working medium entering the combustion chamber can sufficiently absorb low-grade heat to improve The efficiency of the thermodynamic system, so in this case a high pressure fluid absorbing ambient heat exchanger is provided. In the high-pressure fluid heat-absorbing environment heat exchanger, the original working medium may be transformed into a gas, or may not increase its own temperature without undergoing a phase change, because in the low-energy co-firing cycle thermodynamic system Some of the original working fluids may be in a low temperature gas state or a low temperature liquefaction state.

Conventional thermodynamic systems are mostly inhaled air or low-pressure oxygen-containing gas and then compressed into fuel combustion. Because of the piston or impeller or ramjet thermodynamic system, it is difficult to form a high compression stroke. Pressure, so the highest pressure in the combustion chamber in the most advanced traditional thermal power system is generally

At about 1 MPa, this pressure is far from being able to reduce 7 to a desired level, so efficiency cannot be improved. In the low-energy co-combustion cycle thermal power system disclosed by the present invention, in order to greatly reduce the manner of using the original working medium high pressure to enter the combustion chamber, the maximum pressure of the combustion chamber working fluid is significantly higher than that of the conventional internal combustion engine combustion chamber. The highest pressure, the ultimate goal is to achieve a significant reduction in Γ ₂ . From the thermodynamic analysis, it is known that increasing the maximum pressure of the working fluid in the combustion chamber is the key to reducing the efficiency of 7^ ₂ . In order to achieve this, the high pressure of the original working fluid must enter the combustion chamber.

In order to ensure that there is sufficient pressure to match the 7; and in the case that the material and emission can meet the requirements, in order to improve the efficiency of the thermodynamic system, it is necessary to increase the combustion as much as possible while reducing the Γ ₂ The highest temperature of the room; In order to increase the maximum temperature of the combustion chamber, it is necessary to reduce the amount of heat released by the original working fluid in the combustion chamber to absorb the combustion of the fuel. Therefore, it is necessary to use as much as possible the low-grade heat to vaporize the original working medium and enter the combustion chamber at a high pressure. This process essentially brings more low-grade heat back to the combustion chamber to reduce the amount of low-grade heat released by the combustion of the fuel, with the result that all or most of the heat released by the combustion of the fuel is high. Grade state, thereby improving the thermal power system The efficiency of the system. It can be seen that the high pressure entering the combustion chamber after the original working fluid is vaporized is crucial to improve the efficiency of the thermodynamic system.

The original working medium absorbs low-grade heat (the residual heat of the power system itself and/or the low-grade heat in the environment). The thermal power system entering the combustion chamber in the form of a gaseous or critical state and the heat of the original working fluid entering the combustion chamber in the form of a liquid The essential difference between the power system is a very important process to improve the efficiency of the thermodynamic system. Of course, according to the specific structure of the thermodynamic system, it is not necessary to vaporize all the original working fluids, but at least one or a part of the original working fluid should be used to put the residual heat of the thermodynamic system into the combustion chamber, which not only improves efficiency. , and the cooling system of the thermodynamic system can also be cancelled or partially cancelled. In the process of gasifying the original working fluid with low grade heat, it is necessary to maintain a high pressure state, otherwise the thermal efficiency of the thermodynamic system will be lowered. In order to realize this high-pressure process, in the present invention, the liquid precursor is pressurized by the liquid pump and then enters the gasification process, thereby saving both the pressurized energy and the gaseous state at a high pressure.

The adiabatic thermodynamic system is a thermodynamic system that has not been meaningful for a long time. It is currently considered that this system does not have the possibility of improving 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, 'the following conclusions are drawn: 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 combustion chamber. The temperature does not significantly increase 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 is almost equal to or higher than the environment after the work is completed). Pressure), the end result is that the exhaust temperature is high and the efficiency is not improved. Second, people have a traditional idea, adiabatic is equal to high temperature, so the temperature of the combustion chamber of the traditional adiabatic engine is very high, high temperature brings a lot of troubles to the adiabatic engine, such as the replacement of 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 it makes Traditional adiabatic engines have not been able to increase 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, and the temperature of the adiabatic combustion chamber can be controlled by adjusting the amount and properties of the expanding agent such that the temperature of the adiabatic combustion chamber approaches 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 in the present invention may be water, carbon dioxide, helium, and the like, and the expansion agent may be recycled in the low-energy co-firing cycle thermodynamic system. In the structure in which the expansion agent is recycled, the expansion agent may be first compressed into the combustion chamber or into the combustion chamber and then compressed, or the expansion agent may be liquefied, pressurized by a liquid pump, and then subjected to low-quality heat gasification to form a high pressure. The gaseous expansion agent enters the combustion chamber.

The so-called high-pressure fluid heat-absorbing wall inner passage in the present invention refers to a high-pressure fluid heating passage provided in the wall of the combustion chamber, and this passage heats the original working medium and also serves to cool the combustion chamber wall. Therefore, in some cases, the temperature and pressure of the original working fluid can reach a critical, supercritical, ultra-supercritical state or higher state, and the pressure-resistant and temperature-resistant performance of the inner passage of the high-pressure fluid heat absorbing wall must reach the original work. The requirement to enter the state of the combustion chamber. By setting the inner passage of the high-pressure fluid heat absorbing wall as the heat exchanger, the endothermic fluid is passed through the inner passage of the high-pressure fluid heat absorbing wall.

The so-called combustion chamber wall of the present invention refers to a hot wall corresponding to a surface that can be contacted by high-temperature and high-pressure gas generated by combustion in a combustion chamber. The so-called hot wall refers to a wall with a high temperature.

The so-called working mechanism of the present invention refers to any mechanism that can expand the high-pressure working fluid from the combustion chamber and output power through the high-pressure working fluid expansion process, such as a cylinder piston mechanism, a screw-type working mechanism, and a uniform.

The engine constituted by the so-called combustion chamber and cylinder piston mechanism of the present invention may be a piston engine without a compression stroke, or a top dead center combustion type piston engine after a compressionless stroke. So-called pressureless The top dead center combustion piston engine after the contraction stroke means that the cylinder is inflated when the piston is near the top dead center without a compression stroke, and the combustion chemical reaction occurs in the cylinder after the piston crosses the top dead center. engine. After the combustion explosion, the working medium pushes the piston down for the power stroke. When the piston approaches or will reach the bottom dead center, the exhaust valve is opened for exhausting; as the piston moves up, the exhaust stroke is performed. When the piston approaches or is in the top dead center position, the exhaust stroke is completed and the exhaust valve is closed to inflate the cylinder. This type of engine has a very high efficiency because there is no compression stroke and the working fluid in the cylinder reaches the maximum pressure to start work (increasing the torque of the engine) after the piston passes the top dead center position. Since the original working medium entering the combustion chamber is in a high pressure state in the present invention, no further compression is required.

The low-energy co-combustion cycle thermal power system disclosed in the present invention is set as a piston engine without compression stroke, and the cycle diagram of the system (ie, the power diagram) is respectively shown in the PV diagram shown in FIG. 23 (the Y-axis is the pressure P). The X axis is the volume V) and the P-T diagram shown in Fig. 24 (the Y axis is the pressure P and the X axis is the temperature T). In Figure 23, the line shown by A-E is the constant volume of the original working medium filled with the pressure increase curve, the line shown by E-B is the combustion explosion pressure curve, and the curve shown by BC is the pressure volume during the adiabatic expansion process. The curve of change, the curve shown by CDA is the pressure volume curve during the exhaust process. The curve shown by abcd-a in Fig. 24 is a schematic diagram showing the relationship between the pressure and temperature when the pressure of the original working fluid charged in the combustion chamber is equal to the pressure at the end of the compression stroke of the conventional internal combustion engine, and the curve indicated by aef-ga is when the combustion is performed. The original working medium pressure of the chamber is higher than the pressure temperature relationship when the compression of the conventional internal combustion engine is completed. The curve shown by ah-i-j-a is when the pressure of the original working fluid charged into the combustion chamber is greatly increased. The relationship between the pressure and temperature relationship, wherein the curves indicated by ab, ae, and ah are the constant working capacity of the original working medium, and the straight line shown by b-c, ef, h - i is the constant volume combustion explosion supercharging process. The curves shown by c-d, f_g, and i-j are adiabatic expansion processes, and the curves shown by da, ga, and ja are exhaust processes; it is not difficult to see that as the pressure of the original working fluid charged into the combustion chamber increases, The exhaust temperature of the system gradually decreases, which can be close to the ambient temperature or even significantly lower than the ambient temperature, thereby increasing the efficiency of the system; as the pressure of the original working fluid charged in the combustion chamber increases, the straight line of the constant pressure combustion explosion pressurization process (ie bc, ef, h-i Slope of the line) is gradually put The working mechanism of the present invention may be a nozzle, which may move in a straight line or a curve, or may be disposed on the rotating structure, and externally output power by the rotation of the rotating structure.

The oxygen source in the present invention can be set to high pressure oxygen, hydrogen peroxide (H ₂ O ₂ ) or low temperature liquid oxygen. Among them, low-temperature liquid oxygen has obvious advantages. The cost of liquid oxygen is only five or six cents per kilogram according to the current price, while burning one kilogram of fuel requires about 3.5 kilograms of oxygen. On the surface, the vehicle needs to load a considerable amount. Oxygen, but because the efficiency of the disclosed engine can be significantly improved, even up to twice the efficiency of the existing engine, the weight and volume can be significantly reduced, and the advantages and disadvantages are balanced. The disclosed engine still has good economy.

The so-called combustion chamber of the present invention refers to all the vessels in which combustion chemical reactions can occur inside, such as the combustion chamber of a conventional internal combustion engine, the combustion chamber of a gas turbine, the combustion chamber of a rocket, the combustion chamber of a power generation boiler of a power plant, and the combustion of a common boiler. Room and so on.

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, propane, alcohol, hydrogen and gas. Fluidized fuel, liquefied fuel or powdered solid fuel, etc. The term "liquefied fuel" means a fuel that is liquefied and is in a gaseous state under normal temperature and normal pressure.

The low-energy co-firing cycle thermodynamic system disclosed in the present invention can use hydrocarbon or carbon hydrate as a fuel, for example, an ethanol or ethanol aqueous solution, and an aqueous ethanol solution instead of a fuel and a swelling agent, not only can prevent freezing, but also can only An aqueous ethanol storage tank is used in place of the original fuel source and expansion agent source, and the amount of fuel and expansion agent required is varied by adjusting the concentration of the aqueous ethanol solution. When necessary, a mixed solution of ethanol, water and hydrocarbons (such as a mixture of alcohol, water and gasoline) may be used in place of the fuel and the expansion agent of the present invention, and the concentration thereof is adjusted to satisfy the low disclosed in the present invention. Requirements for entropy-combustion cycle thermal power systems.

In the low-energy hybrid combustion cycle thermodynamic system disclosed in the present invention, in the structure in which the working mechanism is a piston-type working mechanism, the exhaust gas temperature can be manufactured close to the ambient temperature, lower than the ambient temperature, or substantially low. Thermal power system at ambient temperature. If the exhaust temperature is low to a certain extent, thermal operation can be achieved. Self-insulation of the force system. 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 medium, 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 made according to the temperature requirements of the pressure wall to reduce the temperature of the pressure wall; In the self-insulation system, a liquid passage or a liquid chamber may be provided in or outside the pressure-receiving wall in contact with the working medium, and the liquid passage or the liquid chamber is filled with liquid to ensure the pressure contact with the working medium. The heat uniformity of the wall and the heat storage of the liquid optimize the change of the temperature of the gas in the cylinder, and a heat insulating layer may be disposed outside the liquid passage or the liquid chamber to reduce heat transfer to the environment.

In the low-energy co-firing cycle thermodynamic system disclosed in the present invention, in the structure in which the working mechanism is set as a non-piston type working mechanism (such as power transmission equal), when the expansion work is completed, the pressure of the working medium can be It is equal to or less than the ambient pressure to improve the efficiency. In this structure, the working medium passage through the working mechanism is drawn to a low pressure, and some or all of the working medium is condensed.

In the present invention, since the temperature of the liquid oxygen is low, the low temperature can be utilized to more effectively utilize the residual heat of the engine to improve the efficiency of the engine.

In the present invention, the disclosed low-energy co-firing cycle thermodynamic system can be compression-ignited, ignitable, and ignited by steam. By steam ignition is meant that the high temperature and pressure gaseous expansion agent ignites the reducing agent by raising the oxidant and reducing agent to a temperature and pressure sufficient for combustion. The combustion mode in the present invention may be continuous or intermittent.

In the low-energy co-firing cycle thermodynamic system disclosed in the present invention, a control valve, a pump, a sensor, a control unit, a fuel injector, a spark plug, etc. may be disposed at appropriate places according to well-known techniques and principles; Indirect communication through several processes (including mixing with other substances, etc.) or controlled connection via pumps, control valves, etc. When the working mechanism is set as the piston type working mechanism 吋, and the combustion in the combustion chamber is set to the continuous combustion mode, a control valve should be provided between the working mechanism and the combustion chamber. In order to provide the working medium intermittently (in a positive relationship), when the working mechanism is set as a piston type working mechanism, and when the combustion in the combustion chamber is set to the intermittent combustion mode, in the combustion chamber A control valve should be provided at the inlet of the original working fluid to provide the original working medium intermittently (in a positive relationship) to the combustion chamber.

In the invention, especially in the structure with an open combustion envelope, the working fluid temperature can reach a very high level, such as several thousand degrees or even higher, and the pressure of the working fluid can reach a high level, such as Hundreds or even thousands of atmospheres.

The present invention differs from the applicant's application number 2010101 18601. 4 in that the differences and advantages of the present invention are as follows:

At the same time, the expansion agent and the oxidant (oxygen) are heated and vaporized or criticalized by the combustion chamber waste heat and/or exhaust heat of the engine, and then directly injected into the cylinder through the high pressure supply system to perform combustion without the compression stroke, thereby eliminating the need for the compression stroke. The compressor piston and the compression stroke simplifies the structure of the engine and avoids the consumption of a large amount of mechanical work in the compression stroke, thereby increasing the efficiency of the entire engine. The patent application No. 2010101 18601. 4 only uses the expansion agent (cooling water). The waste heat of the engine is heated and injected into the cylinder, and the natural air is still sucked in, and the compression stroke is performed in the cylinder.

The present invention differs from the international patent of Application No. 2008/1 1 5330 A1 in that the differences and advantages of the present invention are as follows:

1. In addition to the oxidant and reducing agent, the present invention introduces a high pressure gaseous or critical state expansion agent into the combustion chamber, and the international patent application No. 2008/1 1 5330 A1 passes liquid water into the combustion chamber (ie, liquid water is made) For the use of expansion agent), but the direct injection of liquid water into the cylinder as a swelling agent has obvious drawbacks: that is, liquid water instantly absorbs a large amount of heat and vaporizes after entering the cylinder, which greatly reduces the temperature of the working fluid in the cylinder, thereby weakening The working function of the working fluid reduces the efficiency of the engine. In the present invention, the high-pressure gaseous or critical state expansion agent is injected into the cylinder as a expansion agent, that is, the vaporization process of the liquid water is taken outside the cylinder, so that the residual heat of the engine can be utilized to vaporize or criticalize the liquid water. This not only solves the problem that the liquid water vaporizes in the cylinder to weaken the working fluid, but also solves the problem that the residual heat of the engine is difficult to be effectively recycled due to the low thermal quality, thereby greatly improving the whole launching. Machine efficiency.

2. Compared with the international patent application No. 2008/1 1 5330 A1, the invention eliminates the compression piston and the compression stroke, simplifies the structure of the engine, and avoids consuming a large amount of mechanical work in the compression stroke, thereby improving The efficiency of the entire engine.

The present invention differs from the international patent of Application No. 2010/036095 A1 in that the differences and advantages of the present invention are manifested in -

1. In addition to the oxidizing agent and the reducing agent, the present invention passes the high-pressure gaseous or critical state expanding agent into the combustion chamber and the international patent application No. 2010/036095 A1 introduces liquid water or liquid ammonia into the combustion chamber.

(The liquid water or liquid ammonia water is used as a swelling agent), which also has the following disadvantages: that liquid water or liquid ammonia water absorbs a large amount of heat and vaporizes immediately after entering the cylinder, which greatly reduces the temperature of the working fluid in the cylinder, thereby weakening The working function of the working fluid reduces the efficiency of the engine. In the present invention, the high-pressure gaseous or critical state expansion agent is injected into the cylinder as a expansion agent, which is equivalent to taking the vaporization process of the liquid water to the outside of the cylinder, so that the residual heat of the engine can be utilized to vaporize or criticalize the liquid water. This not only solves the problem that the liquid water vaporizes in the cylinder to weaken the working fluid, but also solves the problem that the residual heat of the engine is difficult to be effectively recycled due to the low thermal quality, thereby greatly improving the efficiency of the entire engine.

2. Compared with the international patent application No. 2010/036095 A1, the invention forms a high pressure gaseous expansion agent into the cylinder, and forms an isolation between the combustion chamber and the cylinder, thereby effectively reducing the high temperature of the combustion chamber to the cylinder wall. The effect is to reduce the generation of waste heat and improve the thermal efficiency of the engine. The technical solution in the international patent application No. 2010/036095 A1 obviously does not have such a function.

3. The international patent of Application No. 2010/036095 A1 still has a partial compression stroke, and the present invention eliminates the compression stroke, avoiding the consumption of a large amount of mechanical work in the compression stroke, thereby improving the efficiency of the entire engine.

The beneficial effects of the present invention are as follows:

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

DRAWINGS

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

Figure 2 is a schematic view of Embodiment 2 of the present invention;

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

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

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

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

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

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

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

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

Figure 11 is a schematic view of Embodiment ^{11 of the} present invention;

Figure 12 is a schematic view of Embodiment 12 of the present invention;

Figures 1 3, 14 and 15 are schematic views of Embodiment 13 of the present invention;

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

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

Figure 18 is a schematic view of an embodiment 16 of the present invention;

Figure 19 is a schematic view of Embodiment 17 of the present invention;

Figure 20 is a schematic view showing three kinds of heated fluids of the external combustion engine of the present invention;

Figure 21 is a schematic view showing three kinds of heated fluids of the internal combustion engine of the present invention;

Thermal Power efficiency graph showing the relationship of FIG. 7 ₂ ;, 22 of the present invention;

23 is a schematic diagram showing the relationship between the pressure P and the volume V of the working cycle of the thermodynamic system of the present invention; and FIG. 24 is a schematic diagram showing the relationship between the pressure P and the temperature T of the working cycle of the thermodynamic system of the present invention. detailed description Example 1

The low-energy co-firing cycle thermodynamic system shown in FIG. 1 includes a work mechanism 1, a combustion chamber 2, an oxygen source 3, and a fuel source 4, and the oxygen source 3 communicates with the combustion chamber 2 via the oxygen high-pressure supply system 301, the fuel The source 4 is in communication with the combustion chamber 2 via the fuel high pressure supply system 401, and an oxygen heat absorption heat exchanger 301 1 is disposed in the oxygen high pressure supply system 301. The oxygen in the oxygen source 3 is sucked in the oxygen heat absorption heat exchanger 3011. The heat forms high-pressure gaseous oxygen into the combustion chamber 2, and the lowest pressure bearing capacity of the oxygen high-pressure supply system 301 is greater than or equal to 2 MPa _{; the} combustion chamber 2 is in communication with at least one working mechanism 1, and the working mechanism 1 outputs power externally. The oxygen source 3 is set as a cryogenic liquid oxygen storage tank. The temperature of the original working medium after charging into the combustion chamber 2 is equal to or lower than the temperature of the standard state, so that the pressure of the working medium after combustion can reach a higher level, thereby improving the thermal efficiency of the system.

Example 2

The low entropy co-combustion cycle thermodynamic system shown in FIG. 2 includes a work mechanism 1, a combustion chamber 2, an oxygen source 3, a fuel source 4, and an expander source 5, and the oxygen source 3 is oxidized by the oxygen high pressure supply system 301. The chamber 2 is connected, the fuel source 4 is connected to the combustion chamber 2 via the fuel high pressure supply system 401, and the expansion agent source 5 is connected to the combustion chamber 2 via the expansion agent high pressure supply system 501; the oxygen absorption heat is set in the oxygen high pressure supply system 301. The heat exchanger 301 1 , the oxygen in the oxygen source 3 absorbs heat in the oxygen heat absorption heat exchanger 3011 to form high pressure gaseous oxygen into the combustion chamber 2; the oxygen high pressure supply system 301 and/or the expansion agent high pressure supply system 501 The minimum pressure capacity is greater than or equal to 3 MPa; the combustion chamber 2 is in communication with at least one working mechanism 1, and the working mechanism 1 outputs power externally.

Example 3

The low-energy co-firing cycle thermodynamic system shown in FIG. 3 includes a work mechanism 1, a combustion chamber 2, an oxygen source 3, a fuel source 4, and an expander source 5, and the oxygen source 3 is oxidized by the oxygen high-pressure supply system 301. The chamber 2 is connected, the fuel source 4 is connected to the combustion chamber 2 via the fuel high pressure supply system 401, and the expansion agent source 5 is connected to the combustion chamber 2 via the expansion agent high pressure supply system 501; the expansion agent is disposed in the expansion agent high pressure supply system 501. The heat absorption heat exchanger 5011, the expansion agent in the expansion agent source 5 absorbs heat in the expansion agent heat absorption heat exchanger 501 1 to form a high pressure gaseous expansion agent into the combustion chamber 2; the oxygen high pressure supply system 301 and/or the expansion agent The lowest pressure bearing capacity of the high pressure feeding system 501 is greater than or equal to 4 MPa _{; the} combustion chamber 2 is in communication with at least one working mechanism 1, and the working mechanism 1 outputs power externally. The fuel in the fuel source 4 is set to be a carbonaceous compound; in the configuration without the expansion agent high pressure supply system 501, an ultrahigh pressure liquid pump is provided in the oxygen high pressure supply system 301 and/or the fuel high pressure supply system 401; In the structure including the expansion agent high pressure supply system 501, The oxygen high pressure supply system 301, the expansion agent high pressure supply system 501 and/or the fuel high pressure supply system 401 are provided with an ultrahigh pressure liquid pump;

K-1

According to = adjust the output of the ultra-high pressure liquid pump under the premise of setting the pressure Ρ ₂ after expansion

The pressure further adjusts the indoor working fluid pressure so that the highest pressure and maximum temperature 7 in the combustion chamber 2 satisfy the low temperature heat source temperature Γ ₂ of the low entropy co-combustion cycle thermal power system reaches the liquefaction temperature requirement of carbon dioxide at > ₂ pressure, thereby The exhaust of the low entropy co-firing thermal power system is self-liquefied to achieve the purpose of recovering carbon dioxide in a liquid or solid state.

In a specific implementation, the expansion agent may be a gas liquefaction, such as liquid nitrogen, liquid carbon dioxide, etc.; the oxidant in the oxygen source may be set as hydrogen peroxide, high pressure gaseous oxygen or liquid oxygen; Simplified structure, the oxygen source and the expansion agent source can be set to the same hydrogen peroxide storage tank, and/or the expansion agent source and the fuel source can be set to the same ethanol aqueous solution storage tank.

Example 4

The low entropy co-combustion cycle thermodynamic system shown in FIG. 4 differs from the embodiment 1 in that it includes a work mechanism 1, a combustion chamber 2, an oxygen source 3, a fuel source 4, and an expander source 5, and an oxygen source 3 The oxygen high pressure supply system 301 is in communication with the combustion chamber 2, and the fuel source 4 is in communication with the combustion chamber 2 via the fuel high pressure supply system 401. The expansion agent source 5 is connected to the combustion chamber 2 via the expansion agent high pressure supply system 501; An oxygen absorbing heat exchanger 301 is disposed in the feeding system 301, and oxygen in the oxygen source 3 absorbs heat in the oxygen absorbing heat exchanger 3011 to form high pressure gaseous oxygen to enter the combustion chamber 2; in the expanding agent high pressure feeding system 501 The expansion agent heat absorption heat exchanger 5011 is provided, and the expansion agent in the expansion agent source 5 absorbs heat in the expansion agent heat absorption heat exchanger 5011 to form a high pressure gaseous expansion agent to enter the combustion chamber 2; the oxygen high pressure supply system 301 and The lowest pressure capacity of the expansion agent high pressure supply system 501 is greater than or equal to 5 WIPa _{; the} combustion chamber 2 is in communication with at least one of the work mechanisms 1, and the work mechanism 1 outputs power externally.

Example 5

The low entropy co-combustion cycle thermodynamic system shown in FIG. 5 differs from the first embodiment in that: when the fuel in the fuel source 4 is a liquefied fuel, a fuel heat absorption heat supply is set in the fuel high pressure supply system 401. The converter 401 1, the liquefied fuel in the fuel source 4 absorbs heat in the fuel heat absorbing heat exchanger 401 1 to form high pressure gas fuel into the combustion chamber 2. The minimum pressure capacity of the oxygen high pressure supply system 301 is greater than or equal to 6 MPa.

Example 6

The low entropy co-combustion cycle thermodynamic system shown in FIG. 6 differs from the second embodiment in that: when the fuel in the fuel source 4 is a liquefied fuel, a fuel endothermic heat exchange is provided in the fuel high pressure supply system 401. The liquefied fuel in the fuel source 4 absorbs heat in the fuel heat absorbing heat exchanger 4011 to form high pressure gas fuel into the combustion chamber 2. The minimum pressure capacity of the oxygen high pressure supply system 301 and/or the expansion agent high pressure supply system 501 is greater than or equal to 7 MPa.

Example 7

The low-enthalpy hybrid combustion cycle thermodynamic system shown in FIG. 7 differs from the third embodiment in that: when the fuel in the fuel source 4 is a liquefied fuel, a fuel heat-absorbing heat exchange is provided in the fuel high-pressure supply system 401. The liquefied fuel in the fuel source 4 absorbs heat in the fuel heat absorbing heat exchanger 4011 to form high pressure gas fuel into the combustion chamber 2. The minimum pressure capacity of the oxygen high pressure supply system 301 and/or the expansion agent high pressure supply system 501 is greater than or equal to 8 MPa.

Example 8

The low entropy co-combustion cycle thermodynamic system shown in FIG. 8 differs from the embodiment 4 in that: when the fuel in the fuel source 4 is a liquefied fuel, a fuel endothermic heat exchange is provided in the fuel high pressure supply system 401. The liquefied fuel in the fuel source 4 absorbs heat in the fuel heat absorbing heat exchanger 4011 to form high pressure gas fuel into the combustion chamber 2. The minimum pressure capacity of the oxygen high pressure supply system 301 and/or the expansion agent high pressure supply system 501 is greater than or equal to 9 MPa.

Example 9

The low entropy co-combustion cycle thermodynamic system shown in FIG. 9 differs from the embodiment 8 in that a high-pressure fluid heat-absorbing exhaust heat exchanger 2301 is disposed in the exhaust passage 23 of the low-entropy co-combustion cycle thermal power system. The oxygen heat absorption heat exchanger 301 1 is set as the high pressure fluid heat absorption exhaust heat exchanger 2301, and the oxygen pressure high pressure supply system 301 and/or the expansion agent high pressure supply system 501 have a minimum pressure capacity of 10 MPa or more. In addition, one, two or three types of heat exchangers of the oxygen heat absorption heat exchanger 3011, the expansion agent heat absorption heat exchanger and the fuel heat absorption heat exchanger may be set as high pressure fluid heat absorption exhaust heat. Switch 2301.

Example 10 The low entropy co-combustion cycle thermodynamic system shown in FIG. 10 differs from the embodiment 8 in that: a high-pressure fluid endothermic environment heat exchanger 2302 is provided in the low-entropy co-combustion cycle thermodynamic system, and the oxygen absorption heat exchange is performed. The heat exchanger heat exchanger 501 1 and the fuel heat absorption heat exchanger 401 1 are both set as high pressure fluid heat absorbing environment heat exchanger 2302, oxygen high pressure supply system 301 and/or expansion agent high pressure supply system. The minimum pressure capacity of 501 is greater than or equal to 15 MPa. In addition, one or two kinds of heat exchangers of the oxygen heat absorption heat exchanger 3011, the expansion agent heat absorption heat exchanger 5011 and the fuel heat absorption heat exchanger 4011 may be set as high pressure fluid heat absorption environment heat. Switch 2302.

Example 1 1

The low entropy co-combustion cycle thermodynamic system shown in FIG. 11 differs from the embodiment 8 in that: a high-pressure fluid heat-absorbing wall inner passage 203 is provided in the combustion chamber wall 22 of the combustion chamber 2, and the oxygen absorption heat exchange is performed. The vessel 301 1 is set to the high pressure fluid heat absorption wall inner passage 203, and the oxygen pressure high pressure supply system 301 and/or the expansion agent high pressure supply system 501 have a minimum pressure capacity of 20 MPa or more. In addition, one, two or three types of heat exchangers of the oxygen heat absorption heat exchanger 3011, the expansion agent heat absorption heat exchanger and the fuel heat absorption heat exchanger may be set as the inner passage of the high pressure fluid heat absorption wall. 203.

Example 12

The low entropy co-combustion cycle thermodynamic system shown in FIG. 12 differs from the embodiment 11 in that a high-pressure fluid heat-absorbing exhaust heat exchanger is disposed in the exhaust passage 23 of the low-entropy co-combustion cycle thermal power system. 2301, the oxygen heat absorption heat exchanger 301 1 is set as a heated heat exchanger first enters the high pressure fluid heat absorption exhaust heat exchanger 2301 and then enters the series heat exchanger group in the high pressure fluid heat absorption wall inner passage 203, the oxygen high pressure supply system The minimum pressure capacity of the 301 and/or expander high pressure supply system 501 is greater than or equal to 25 MPa. In addition, one, two or three kinds of heat exchangers of the oxygen heat absorption heat exchanger 3011, the expansion agent heat absorption heat exchanger and the fuel heat absorption heat exchanger may be set as the heated fluid to enter the high pressure fluid first. The endothermic exhaust heat exchanger 2301 re-enters the series heat exchanger set within the high pressure fluid absorbing wall inner passage 203. In this embodiment, the original working medium passes through the high-pressure fluid heat-absorbing exhaust heat exchanger 2301 and then enters the passage of the high-pressure fluid heat absorbing wall.

The purpose of 203 is to further improve the utilization of heat.

Example 13

a low entropy co-combustion cycle thermodynamic system as shown in FIG. 13, FIG. 14 or FIG. 15, which is the same as Embodiment 2 The difference is that the low-entropy co-combustion cycle thermal power system further includes an open combustion envelope 2001, the open combustion envelope 2001 is disposed in the combustion chamber 2 and is in communication with the combustion chamber 2, and the oxygen source 3 is opened through the oxygen high-pressure supply system 301 The combustion envelope 2001 is connected, the fuel source 4 is connected to the open combustion envelope 2001 via the fuel high pressure supply system 401, and the expansion agent source 5 is connected to the combustion chamber 2 via the expansion agent high pressure supply system 501, and the expansion agent in the expansion agent source 5 Introduced into the space between the open combustion envelope 2001 and the combustion chamber wall 22 of the combustion chamber 2 to form a suspension of the combustion flame by the high pressure gaseous expansion agent to improve the combustion environment and reduce combustion to the combustion chamber wall 22 of the combustion chamber 2. The heat load requires that the minimum pressure capacity of the oxygen high pressure supply system 301 and/or the expander high pressure supply system 501 be greater than or equal to 30 MPa.

Example 14

The low entropy co-combustion cycle thermodynamic system shown in FIG. 16 differs from Embodiment 4 in that: the low entropy co-combustion cycle thermodynamic system further includes an oxygen expansion agent premixing chamber 100, and the oxygen source 3 The oxygen high pressure supply system 301 is further connected to the combustion chamber 2 via the oxygen expansion agent premixing chamber 100, and the expansion agent source 5 is expanded by the expansion agent high pressure supply system 501. The premixing chamber 100 is in communication with the combustion chamber 2, and the oxygen in the oxygen source 3 and the expanding agent in the expanding agent source 5 are premixed in the oxygen expanding agent premixing chamber 100 and introduced into the combustion. Room 2.

Example 1 5

The low entropy co-combustion cycle thermal power system shown in FIG. 17 is different from the embodiment 8 in that the low-energy co-combustion cycle thermal power system further includes an oxy-fuel premixing chamber 200, and the oxygen source 3 is The oxygen high pressure supply system 301 is further connected to the combustion chamber 2 via the oxy-fuel premixing chamber 200, and the fuel source 4 passes through the oxyfuel premixing chamber 200 via the fuel high pressure supply system 401. In communication with the combustion chamber 2, oxygen in the oxygen source 3 and fuel in the fuel source 4 are premixed in the oxyfuel premixing chamber 200 and introduced into the combustion chamber 2.

Example 1 6

The low entropy co-combustion cycle thermodynamic system shown in FIG. 18 differs from the first embodiment in that: the work mechanism 1 is a piston type work mechanism, and is disposed between the combustion chamber 2 and the work mechanism 1 There is a working medium supply control valve 1 101.

Example 1 7

The low entropy co-combustion cycle thermodynamic system shown in Fig. 19 differs from the second embodiment in that: The combustion chamber 2 is connected to the plurality of working mechanisms 1 , and between the combustion chamber 2 and each of the working mechanisms 1 , a working medium supply control valve 1 101 is provided, and the working mechanism 1 outputs power externally, and the working mechanism 1 is provided. It is a top dead center combustion type piston cylinder mechanism 40 after the compression stroke.

It is apparent that the present invention is not limited to the above embodiment, and many variations are possible. All modifications that can be directly derived or associated from the disclosure of the present invention are considered to be within the scope of the present invention.

Claims

Rights request

A low-energy co-firing thermal power system comprising a work mechanism (1), a combustion chamber (2), an oxygen source (3), and a fuel source (4), wherein: the oxygen source (3) An oxygen high pressure supply system (301) is in communication with the combustion chamber (2), and the fuel source (4) is in communication with the combustion chamber (2) via a fuel high pressure supply system (401), An oxygen absorption heat exchanger is provided in the supply system (301)

(3011), the oxygen in the oxygen source (3) absorbs heat in the oxygen heat-absorbing heat exchanger (3011) to form high-pressure gaseous oxygen or critical state oxygen into the combustion chamber (2), the work The mechanism (1) is set as a non-piston type working mechanism or a piston type working mechanism; in the structure in which the working mechanism (1) is set as a non-piston type working mechanism, the oxygen high pressure supply system (301) The minimum pressure bearing capacity is greater than or equal to 2 MPa, and the lowest pressure bearing capacity of the oxygen high pressure feeding system (301) in the structure of the working mechanism (1) is a piston type working mechanism is greater than or equal to 3 MPa;

The combustion chamber (2) is in communication with at least one of the work mechanisms (1), and the work mechanism (1) outputs power externally.

2. A low-entropy co-combustion cycle thermal power system comprising a work mechanism (1), a combustion chamber (2), an oxygen source (3), a fuel source (4) and a bulking agent source (5), characterized in that: The oxygen source (3) is in communication with the combustion chamber (2) via an oxygen high pressure supply system (301), and the fuel source (4) is passed through a fuel high pressure supply system (401) and the combustion chamber (2) Connected, the expansion agent source (5) is connected to the combustion chamber (2) via an expansion agent high pressure supply system (501);

An oxygen heat absorption heat exchanger (3011) is disposed in the oxygen high pressure supply system (301), and oxygen in the oxygen source (3) absorbs heat in the oxygen heat absorption heat exchanger (3011) to form a high pressure Gaseous oxygen or critical state oxygen enters the combustion chamber (2); an expansion agent heat absorption heat exchanger (5011) is disposed in the expansion agent high pressure supply system (501), in the expansion agent source (5) The expansion agent absorbs heat in the expansion agent heat absorption heat exchanger (5011) to form a high pressure gaseous expansion agent or critical state expansion agent into the combustion chamber (2);

The working mechanism (1) is set as a non-piston type working mechanism or a piston type working mechanism; in the structure in which the working mechanism (1) is set as a non-piston type working mechanism, the oxygen high pressure supply The lowest pressure capacity of either one of the system (301) and the expansion agent high pressure supply system (501) is greater than or equal to 2 MPa _; in the structure in which the working mechanism (1) is set as a piston type working mechanism , the lowest pressure of any one of the oxygen high pressure supply system (301) and the expansion agent high pressure supply system (501) The capacity is greater than or equal to 3 MPa;

The combustion chamber (2) is in communication with at least one of the work mechanisms (1). The work mechanism (1) outputs power externally.

3. The low entropy co-combustion cycle thermal power system according to claim 1 or 2, wherein: in the structure in which the fuel in the fuel source (4) is a liquefied fuel, in the high-pressure fuel supply system ( 401) providing a fuel heat absorption heat exchanger (4011), wherein the liquefied fuel in the fuel source (4) absorbs heat in the fuel heat absorption heat exchanger (4011) to form a high pressure gas fuel or a critical state fuel inlet Combustion chamber

(2).

4. The low-entropy co-combustion cycle thermal power system according to claim 1 or 2, wherein: the high-pressure fluid heat-absorbing exhaust heat is disposed in an exhaust passage (23) of the low-entropy co-combustion cycle thermal power system. Exchanger

(2301); in the structure provided with the oxygen heat-absorbing heat exchanger (3011), the oxygen heat-absorbing heat exchanger (3011) is set as the high-pressure fluid heat-absorbing exhaust heat exchanger (2301); And/or in the structure provided with the expansion agent heat absorption heat exchanger (5011), the expansion agent heat absorption heat exchanger (5011) is set as the high pressure fluid absorption heat exchanger (2301) .

5. The low-entropy co-combustion cycle thermal power system according to claim 3, wherein: a high-pressure fluid heat-absorbing exhaust heat exchanger is disposed in an exhaust passage (23) of said low-entropy co-combustion cycle thermal power system

(2301), the fuel heat absorbing heat exchanger (4011) is set as the high pressure fluid heat absorbing exhaust heat exchanger (2301).

6. The low-entropy co-combustion cycle thermal power system according to claim 1 or 2, wherein: a high-pressure fluid heat-absorbing environment heat exchanger (2302) is disposed in the low-energy co-firing cycle thermodynamic system; In the structure of the oxygen heat-absorbing heat exchanger (3011), the oxygen heat-absorbing heat exchanger (3011) is set as the high-pressure fluid heat-absorbing environment heat exchanger (2302); and/or In the structure of the expansion agent heat absorption heat exchanger (5011), the expansion agent heat absorption heat exchanger (5011) is set as the high pressure fluid heat absorption environment heat exchanger (2302).

7. The low-entropy co-combustion cycle thermal power system according to claim 3, wherein: a high-pressure fluid heat-absorbing environment heat exchanger (2302) is disposed in said low-entropy co-combustion cycle thermodynamic system, said fuel suction The heat exchanger (4011) is set to the high pressure fluid heat absorbing environment heat exchanger (2302).

8. The low entropy co-combustion cycle thermal power system according to claim 1 or 2, wherein: a high pressure fluid heat absorption wall inner passage (203) is disposed in the combustion chamber wall (22) of the combustion chamber (2); in the structure provided with the oxygen heat absorption heat exchanger (3011), the oxygen absorption heat An exchanger (3011) is provided as the high pressure fluid heat absorption wall inner passage (203); and/or in a structure provided with the expansion agent heat absorption heat exchanger (5011), the expansion agent heat absorption heat exchange The device (5011) is set to the high pressure fluid heat absorption wall inner passage (203).

9. The low-energy hybrid combustion cycle thermal power system according to claim 3, wherein: a high-pressure fluid heat-absorbing wall inner passage (203) is disposed in the combustion chamber wall (22) of the combustion chamber (2), The fuel heat absorbing heat exchanger (4011) is set as the high pressure fluid heat absorbing wall inner passage (203).

10. The low entropy co-combustion cycle thermal power system of claim 2, wherein: said low entropy co-combustion cycle thermal power system further comprises an open combustion envelope (2001), said open combustion envelope (2001) Provided in the combustion chamber (2) and in communication with the combustion chamber (2), the oxygen source (3) is connected to the open combustion envelope (2001) via an oxygen high pressure supply system (301). The fuel source (4) is in communication with the open combustion envelope (2001) via a fuel high pressure supply system (2001), the expander source

(5) communicating with the combustion chamber (2) via an expansion agent high pressure supply system (501), the expansion agent in the expansion agent source (5) being introduced into the open combustion envelope (2001) and the combustion a space between the combustion chamber walls (22) of the chamber (2) to form a high-pressure gaseous expansion agent to suspend the combustion flame to improve the combustion environment to reduce combustion to the combustion chamber wall of the combustion chamber (2) (22) Thermal load requirements.

11. The low entropy co-combustion cycle thermal power system according to claim 2, wherein: said low entropy co-combustion cycle thermal power system further comprises an oxygen expansion agent premixing chamber (100), said oxygen source (3) The oxygen high pressure supply system (301) is further connected to the combustion chamber (2) via the oxygen expansion agent premixing chamber (100), and the expansion agent source (5) is supplied through the expansion agent high pressure System (501) is in communication with said combustion chamber (2) via said oxygen expansion agent premixing chamber (100), oxygen in said oxygen source (3) and expansion agent in said expansion agent source (5) The combustion chamber (2) is introduced into the oxygen expansion agent premixing chamber (100) before being mixed.

12. The low entropy co-combustion cycle thermal power system according to claim 1 or 2, wherein: the low entropy co-combustion cycle thermal power system further comprises an oxy-fuel premixing chamber (200), the oxygen source (3) Passing through the oxygen high pressure supply system (301) through the oxy-fuel premixing chamber (200) to communicate with the combustion chamber (2), the fuel source (4) passing through the fuel high pressure supply system ( 401) passing the oxygen fuel premixing chamber (200) communicating with the combustion chamber (2), the oxygen in the oxygen source (3) and the fuel in the fuel source (4) are premixed in the oxyfuel premixing chamber (200) and introduced The combustion chamber (2).

A low-twisted-combustion cycle thermal power system according to claim 1 or 2, characterized in that the temperature of the original working medium charged in the combustion chamber (2) is equal to or lower than the temperature in the standard state.

14. The low entropy co-combustion cycle thermal power system according to claim 2, wherein: said expansion agent is a gas liquefaction.