CN202300716U - Small-temperature-rise and low-entropy mixed-combustion engine - Google Patents

Abstract

The utility model discloses a small temperature rise and low entropy mixed combustion engine, which comprises a combustion chamber, an expansion agent source and a fuel source, the fuel source communicates with the combustion chamber through a fuel introduction control mechanism, and the expansion agent source is expanded The agent introduction control mechanism is communicated with the combustion chamber, and the fuel introduction control mechanism and the expansion agent introduction control mechanism are controlled by the combustion control device; the combustion chamber is set as a piston engine combustion chamber, and the piston engine combustion chamber The pressure bearing capacity of the turbine combustion chamber is greater than or equal to 4MPa, or the combustion chamber is set as a turbine combustion chamber, and the pressure bearing capacity of the turbine combustion chamber is greater than or equal to 2MPa. The small temperature rise and low entropy co-combustion engine disclosed by the utility model has high efficiency and good environmental protection.

Description

Small temperature rise and low entropy co-combustion engine

technical field

The utility model relates to the field of thermal energy and power, in particular to an engine.

Background technique

In order to improve the efficiency of traditional internal combustion engines (including piston internal combustion engines and internal combustion turbines), many schemes have been proposed to inject expansion agent into the combustion chamber. But there is no plan to clearly inject the amount of expansion agent into the combustion chamber and the pressure state in the combustion chamber before injection. However, the amount of injection expansion agent into the combustion chamber and the pressure and temperature state in the combustion chamber before combustion are the factors that affect the injection of expansion agent into the combustion chamber of the internal combustion engine. One of the most important factors in the efficiency of the internal combustion engine in the scheme. Therefore, it is necessary to clarify the amount of expansion agent injected into the combustion chamber and the state parameters of the gas at the end of the compression process of the internal combustion engine, so that the state parameters of the working fluid after injection of the expansion agent into the combustion chamber and combustion occur are more reasonable, so as to improve the efficiency of the engine.

Contents of the invention

，（其中，

为循环效率，

为高温热源的温度，

为低温热源的温度），卡诺定理是目前热机理论中具有指导性意义的定理。目前人们对卡诺定理的理解是：将工质在高温热源温度下等温膨胀过程中从高温热源中吸取的热量视为卡诺定理中的“从高温热源吸取热量”的热量；把工质向环境排出的热量视为卡诺定理中的“把所吸取热量的一部分传递给低温热源”的那一部分热量。然而，在实际热机循环中，高温热源都是人为制造的，而低温热源都是根据高温热源下工质的状态（温度和压力）以及工质的热力学性质，膨胀过程自行制造的。例如，在外燃机中，如果向高温热源温度下的工质内注入膨胀剂并使膨胀剂在高温热源温度下吸收热量升压或发生气化（含临界化过程和过热过程）升压，而且使新形成的工质（所谓新形成的工质包括原来的工质和膨胀剂）的压力参数达到这样一种状态：即膨胀作功终了时工质的温度低于甚至大幅度低于环境温度。这样一个循环过程所输出的功一定会接近、等于或超过从高温热源中吸收的热量，换句话说，其效率一定会接近、等于或超过100%，如果膨胀作功的工质的温度低于环境温度，就不可能向低温热源排热但是可以从低温热源吸热或被导出，被导出的工质可以被抛入任何温度的其他热源（包括高温热源）。再例如在内燃机中，内燃机的高温热源是燃料燃烧后的工质，低温热源（也可称为冷源）是膨胀作功后的工质，而膨胀作功后的工质的状态是由燃料燃烧后的工质的状态所决定的。在这种情况下，如果控制燃烧过程使燃料燃烧后的工质的状态参数达到一定的值，就可以使膨胀作功后的工质的温度低于甚至大幅度低于环境温度，这样一个循环过程所输出的功一定会接近、等于或超过从高温热源中吸收的热量，换句话说，其效率一定会接近、等于或超过100%，如果膨胀作功的工质的温度低于环境温度，就不可能向低温热源排热但是可以从低温热源吸热或被导出，被导出的工质可以被抛入任何温度的其他热源（包括高温热源）。这两个例子从表面上看，都造成了用现有的热力学理论和定理无法解释的状况。因此，目前人们对卡诺定理的理解是存在误区的，那么所谓的“从高温热源吸取热量”的热量究竟是指哪一部分热量，以及所谓的“把所吸取热量的一部分传递给低温热源”的那一部分热量究竟是指哪一部分热量。本实用新型人认为“从高温热源吸取热量”的热量是由将工质从低温热源的温度被高温热源加热到高温热源的温度的过程中工质从高温热源中吸取的热量（含在高温热源温度下工质从高温热源吸取的热量）（如图11中的Q所示）和工质的底热（所谓工质的底热是指工质处于低温热源温度下本身所包含的从绝对零度算起的热量）（如图11中的Qc所示）两部分构成的，而所谓的“把所吸取热量的一部分传递给低温热源”的那一部分热量是由工质向环境排出的热量（如图11中的q所示）和工质的底热（如图11中的Qc所示）两部分构成的。换句话说，即便是膨胀作功后的工质温度低于环境温度，工质不能向环境传热，只要将膨胀作功后的工质找到去向，如抛入环境中或抛入任何温度的其他热源（包括高温热源）中，热机就可循环工作。不仅如此，在某些特定条件下，可以将膨胀作功后的低温工质抛入系统的高温热源中（如图12中Qc-M-T₂所示虚线方向），例如膨胀作功后降温冷凝的工质可以抛入内燃机的燃烧后的高温高压工质中，例如膨胀作功后的低温工质可以抛入热电系统的锅炉燃烧室内或锅炉蒸气发生器内，例如将气动发动机中的乏气抛入环境中（在某些气动发动机中环境就是气动发动机的高温热源），再例如将从膨胀作功后的工质吸收热量的液体抛入高温热源中。由此可以得出这样的结论：热机可以工作在一个热源之下，只要将膨胀作功后的工质导出，热机就可以循环工作。被导出的膨胀作功后的工质可以被抛入比自身温度低的热源中，可以被抛入与自身温度相同的热源中，可以被抛入比自身温度高的热源中，可以被抛入高温热源中，也可以被抛入比高温热源温度更高的热源中；不仅如此，膨胀作功后的工质如果只对外传热传给低温热源，受热的低温热源仍可以被抛入高温热源中，例如可以将用于冷却膨胀作功后的工质的冷却介质抛入高温热源中。因此，热机工作的必要条件并不是两个热源，而是至少一个热源，至少一个残留流出口（所谓的残留流出口是指膨胀作功后的工质的出口和/或膨胀作功后的工质的热量的出口），所述残留流出口可以与任何其他热源连通（包括系统的高温热源），在所述残留流出口与高温热源连通的结构中热机就只需要一个热源即可循环工作，在所述残留流出口不与高温热源连通的结构中热机就需要至少有两个热源，当所述残留流出口与温度高于所述残留流出口的热源连通时所述残留流出口只能是膨胀作功后的工质的出口。本实用新型人热为：热机工作过程中的热量传递和质量传递可以单一存在、共同存在或相互取代。不可能把热量从低温物体传到高温物体而不产生其他影响的说法是完全正确的，但是我们可以把低温物体（例如低温工质）抛入高温物体（例如高温工质），通过质量传递（即把低温物体抛入高温物体的过程）实现“把热量从低温物体传到高温物体”的这一不可实现过程。热机工作过程中的热量传递和质量传递可以单一存在、共同存在或相互取代的这一结论为制造高效热机或制造输出的功等于燃料的热值或制造输出的功大于燃料的热值的热机指明了方向。图11、图12和图13所示分别为q>0、q=0、q<0的三种循环示意图。 The two representative ways of elaborating the second law of thermodynamics are: 1. Kelvin's way of elaborating is "it is impossible to absorb heat from a single heat source so that it can be completely converted into useful work without causing other changes."; 2. Clausius Si's way of elaborating is "it is impossible to transfer heat from a low-temperature object to a high-temperature object without other effects." In his paper "On the Power of Fire" published in 1824, Carnot proposed that a heat engine must work between two heat sources, absorb heat from a high-temperature heat source, and transfer part of the absorbed heat to a low-temperature heat source. Mechanical work. And based on this conclusion, Carnot proposed the famous Carnot theorem, namely

,(in,

for cycle efficiency,

is the temperature of the high-temperature heat source,

is the temperature of the low-temperature heat source), Carnot's theorem is a theorem with guiding significance in the current heat engine theory. At present, people's understanding of Carnot's theorem is: the heat absorbed by the working medium from the high-temperature heat source during the isothermal expansion process at the temperature of the high-temperature heat source is regarded as the heat of "absorbing heat from the high-temperature heat source" in Carnot's theorem; The heat discharged from the environment is regarded as the part of heat that "transfers part of the absorbed heat to a low-temperature heat source" in Carnot's theorem. However, in the actual heat engine cycle, the high-temperature heat source is artificially manufactured, while the low-temperature heat source is self-manufactured according to the state (temperature and pressure) of the working fluid under the high-temperature heat source and the thermodynamic properties of the working fluid, and the expansion process. For example, in an external combustion engine, if an expansion agent is injected into the working medium at the temperature of the high-temperature heat source and the expansion agent absorbs heat at the temperature of the high-temperature heat source to increase the pressure or undergo gasification (including criticalization process and superheating process) to increase the pressure, and Make the pressure parameters of the newly formed working fluid (the so-called newly formed working fluid includes the original working fluid and the expansion agent) reach such a state: that is, the temperature of the working fluid at the end of the expansion work is lower than or even significantly lower than the ambient temperature . The output work of such a cyclic process must be close to, equal to or exceed the heat absorbed from the high-temperature heat source, in other words, its efficiency must be close to, equal to or exceed 100%, if the temperature of the working medium for expansion work is lower than If the ambient temperature is lower than the ambient temperature, it is impossible to discharge heat to the low-temperature heat source, but it can absorb or be exported from the low-temperature heat source, and the exported working fluid can be thrown into other heat sources of any temperature (including high-temperature heat sources). For another example in an internal combustion engine, the high-temperature heat source of the internal combustion engine is the working fluid after fuel combustion, and the low-temperature heat source (also called a cold source) is the working fluid after expansion, and the state of the working medium after expansion is determined by the fuel. Determined by the state of the working fluid after combustion. In this case, if the combustion process is controlled so that the state parameters of the working fluid after fuel combustion reach a certain value, the temperature of the working fluid after expansion and work can be lowered or even significantly lower than the ambient temperature. Such a cycle The work output by the process must be close to, equal to or exceed the heat absorbed from the high-temperature heat source, in other words, its efficiency must be close to, equal to or exceed 100%, if the temperature of the working medium for expansion is lower than the ambient temperature, It is impossible to discharge heat to the low-temperature heat source, but it can absorb or be exported from the low-temperature heat source, and the exported working fluid can be thrown into other heat sources of any temperature (including high-temperature heat sources). On the surface, these two examples have caused situations that cannot be explained by existing thermodynamic theories and theorems. Therefore, there are misunderstandings in people's understanding of Carnot's theorem at present, so which part of the heat does the so-called "absorbing heat from a high-temperature heat source" refer to, and the so-called "transfer part of the absorbed heat to a low-temperature heat source" Which part of the heat does that part of the heat refer to? The utility model believes that the heat of "absorbing heat from a high-temperature heat source" is the heat absorbed by the working medium from the high-temperature heat source during the process of heating the working fluid from the temperature of the low-temperature heat source to the temperature of the high-temperature heat source by the high-temperature heat source (contained in the high-temperature heat source The heat absorbed by the working fluid from the high-temperature heat source) (as shown by Q in Figure 11) and the bottom heat of the working fluid (the so-called bottom heat of the working fluid refers to the temperature from absolute zero contained in the working fluid at the temperature of the low-temperature heat source The calculated heat) (shown as Qc in Figure 11) is composed of two parts, and the so-called "transfer part of the absorbed heat to the low-temperature heat source" is the heat discharged from the working fluid to the environment (such as Shown by q in Figure 11) and the bottom heat of the working fluid (shown by Qc in Figure 11) are composed of two parts. In other words, even if the temperature of the working medium after expansion is lower than the ambient temperature, the working medium cannot transfer heat to the environment, as long as the working medium after expansion is found, such as throwing it into the environment or into any temperature Among other heat sources (including high-temperature heat sources), the heat engine can work in a cycle. Not only that, but under some specific conditions, the low-temperature working fluid after expansion and work can be thrown into the high-temperature heat source of the system (as shown by the dotted line in Qc-MT ₂ in Figure 12), for example, cooling and condensation after expansion and work The working medium can be thrown into the high-temperature and high-pressure working medium after combustion of the internal combustion engine. For example, the low-temperature working medium after expansion and work can be thrown into the boiler combustion chamber or boiler steam generator of the thermoelectric system. Into the environment (the environment is the high-temperature heat source of the air-driven engine in some air-driven engines), and for example, the liquid that absorbs heat from the working medium after expansion is thrown into the high-temperature heat source. From this, it can be concluded that the heat engine can work under a heat source, as long as the working medium after expansion is exported, the heat engine can work in a cycle. The exported working fluid after expansion can be thrown into a heat source with a lower temperature than itself, into a heat source with the same temperature as itself, into a heat source with a higher temperature than itself, or into The high-temperature heat source can also be thrown into a heat source with a higher temperature than the high-temperature heat source; not only that, if the working fluid after expansion is only transferred to the low-temperature heat source, the heated low-temperature heat source can still be thrown into the high-temperature heat source In the process, for example, the cooling medium used to cool the expanded working fluid can be thrown into the high-temperature heat source. Therefore, the necessary conditions for the work of the heat engine are not two heat sources, but at least one heat source, and at least one residual outflow port (the so-called residual outflow port refers to the outlet of the working medium after expansion and/or the working fluid after expansion work). The heat outlet of the mass), the residual outflow port can communicate with any other heat source (including the high-temperature heat source of the system), and in the structure in which the residual outflow port communicates with the high-temperature heat source, the heat engine only needs one heat source to work cyclically, In the structure where the residual outlet is not connected to a high-temperature heat source, the heat engine needs at least two heat sources. When the residual outlet is connected to a heat source whose temperature is higher than that of the residual outlet, the residual outlet can only be The outlet of the working fluid after expansion. The heat of the utility model is: heat transfer and mass transfer in the working process of the heat engine can exist alone, coexist or replace each other. It is completely correct to say that it is impossible to transfer heat from a low-temperature object to a high-temperature object without causing other effects, but we can throw a low-temperature object (such as a low-temperature working fluid) into a high-temperature object (such as a high-temperature working fluid), through mass transfer ( That is, the process of throwing a low-temperature object into a high-temperature object) to realize the unrealizable process of "transferring heat from a low-temperature object to a high-temperature object". The conclusion that heat transfer and mass transfer in the working process of a heat engine can exist alone, coexist or replace each other indicates that the manufacture of high-efficiency heat engines or heat engines whose work output is equal to the calorific value of the fuel or whose work output is greater than the calorific value of the fuel indicates direction. Fig. 11, Fig. 12 and Fig. 13 are schematic diagrams of three kinds of cycles with q>0, q=0 and q<0, respectively.

The inventor of the present invention thinks that the second law of thermodynamics can be interpreted with the following statement: the necessary conditions for the work of a heat engine are not two heat sources, but at least one heat source, and at least one residual outflow port (so-called residual outflow port refers to the expansion action. The outlet of the working fluid after work and/or the outlet of the heat of the working fluid after expansion), the residual outlet can be connected with any other heat source (including the high temperature heat source of the system), and the residual outlet can be connected with the high temperature In the structure where the heat source is connected, the heat engine only needs one heat source to work cyclically. In the structure where the residual outlet is not connected to the high-temperature heat source, the heat engine needs at least two heat sources. When the heat source of the residual outflow port is connected, the residual outflow port can only be the outlet of the working fluid after expansion. Carnot proposed in his paper "On the Power of Fire" published in 1824 that "the heat engine must work between two heat sources, absorb heat from the high-temperature heat source, and transfer part of the absorbed heat to the low-temperature heat source. The discussion of "obtaining mechanical work" is just a special case of the utility model to this statement of the second law of thermodynamics. Carnot was a great scientist, but in his time the internal combustion engine had not yet been born, and it may be for this reason that limited Carnot's thinking. Not only that, but only temperature is reflected in Carnot’s theorem, and no pressure is involved. This shows that it is very likely that Carnot first set up two heat sources with different temperatures in the process of conceiving Carnot’s theorem, and then let the heat engine (It is likely to be limited to external combustion engines) Work according to the Carnot cycle between these two heat sources, and this mode is just the opposite of the actual heat engine. The low-temperature heat source (also called cold source) of a real heat engine does not exist in advance, but is determined by the state (temperature and pressure) of the working fluid under the high-temperature heat source and the thermodynamic properties of the working fluid. In other words, the actual The low-temperature heat source (also called cold source) of the heat engine does not exist in advance, but is produced by itself according to the state (temperature and pressure) of the working medium under the high-temperature heat source and the thermodynamic properties of the working medium, and the expansion process. According to the state of the working medium (temperature and pressure) under the high-temperature heat source and the thermodynamic properties of the working medium, the temperature of the low-temperature heat source produced by the expansion process can be completely lower than the ambient temperature. In other words, the output work can be completely high. due to the heat absorbed from a high-temperature heat source. From this, it can be concluded that on the premise that the temperature of the high-temperature heat source is set to the environmental protection temperature limit or the material temperature limit, the pressure of the working medium under the high-temperature heat source should be increased as much as possible so that the pressure of the working medium after expansion works The temperature is kept as low as possible to increase the efficiency of the engine. In reality, the efficiency of a heat engine is not determined by the temperature of the high-temperature heat source and the ambient temperature, but by the values of the temperature and pressure in the state of the high-temperature heat source, in other words, by the temperature of the high-temperature heat source and the The state (temperature and pressure) of the lower working fluid and the thermodynamic properties of the working fluid are determined by the temperature of the low-temperature heat source produced by the expansion process.

Chemical energy is the source of energy for modern heat engines. However, the inventor believes that there are considerable defects in the utilization of chemical energy in traditional heat engines. The root cause of these defects is the understanding of an extremely important attribute of chemical energy It is not deep enough, that is, the understanding of chemical energy as the property that can almost input energy to any working fluid in high energy state (high temperature and high pressure) is not deep enough. In the utility model, for the convenience of explanation, chemical energy is defined as the property of chemical energy that can almost input energy to the working fluid under any high-energy state (high temperature and high pressure). By using it, the efficiency of the heat engine can be substantially improved. Let’s take a heat engine with a compression stroke (process) as an example to illustrate _: S ₁ , S ₂ and S ₃ in Figure 14 are schematic diagrams of heat engines with different compression forces _. S ₃ increases sequentially, and Q _h is the chemical energy of the fuel. Since the work required for the compression process can be recovered through the expansion process, assuming that both the compression process and the expansion process are reversible, no matter how high the compression force is, its own It does not affect the efficiency of the heat engine, but the higher the compression force, it is equivalent to raising the chemical energy to a higher grade. These higher-grade chemical energy can output a greater part of it in the form of work during the work process. If the state parameters are reasonable, the chemical energy raised to a relatively high level by a relatively large compression force can reduce the temperature of the working medium to a level significantly lower than the standard state in the process of expansion and work, and then make the output work of the heat engine greater than that of the fuel. calorific value; S ₃₁ in Figure 14 is the process in _which the temperature remains unchanged after the fuel burns to release chemical energy under the condition of the presence of an expander _. Large, the output work W is close to the process of chemical energy Q _h , P ₂ >P ₁ means that the pressure of the working medium increases before and after combustion, and the output work W is greater than the process of chemical energy Q _h . It can be seen that in order to manufacture a high-efficiency or super-efficient (super-high-efficiency means that the work output by the heat engine is equal to or greater than the chemical energy of the fuel), a heat engine with a compression stroke (process) and combustion products participating in work must: 1. Large Increase the compression force of the heat engine by a large margin to transfer chemical energy to the working fluid at a very high energy level; second, rationalize the state parameters of the high-temperature and high-pressure working fluid formed after the release of chemical energy (the so-called "formed after the release of chemical energy The rationalization of the state parameters of the high-temperature and high-pressure working fluid refers to the relationship between the pressure and temperature of the working fluid after combustion by introducing an expansion agent or other means so that the temperature of the working fluid after expansion and work is close to, equal to, lower than or greater than The range is lower than the standard state temperature. The so-called other method is to greatly increase the strength of the engine compression stroke without an expander, so that the pressure and temperature at the end of the compression stroke are in a relatively high state and then use chemical energy to treat the working medium. Carry out heating to raise the temperature, see the state shown in the high-end position in Fig. 18, although this method can't produce a super-efficient engine, it can produce a high-efficiency engine, but the required compressed working fluid temperature and pressure are quite high, and the There are very strict requirements on the material of the engine); 3. Reasonable selection of working fluid and/or expansion agent (the so-called reasonable selection of working fluid refers to the selection of a working fluid that has a small phase change heat and only liquefies when the expansion works to a set level , the so-called reasonable selection of expansion agent refers to the selection of expansion agent with small phase change heat and liquefaction when the expansion work reaches the set level). For external combustion engines, first, the working fluid must absorb heat at a relatively high pressure and temperature (use the environment or other low-grade heat sources to keep the working fluid at a relatively high temperature and pressure and then use chemical energy to heat the working fluid ); 2. It is necessary to rationalize the state parameters of the working fluid after absorbing heat; 3. Reasonable selection of the working fluid (the so-called reasonable selection of the working fluid refers to the selection of the working fluid with small phase change heat and liquefaction when the expansion work reaches the set level. quality). Figure 18 is a detailed calculation data diagram of using fuel combustion to heat and increase the pressure of the working medium under the premise of different compression strengths of the working medium. The vertical axis is the pressure, the horizontal axis is the temperature, 0-H is the adiabatic compression curve, A ₁ -E ₁ , A ₂ -E ₂ , A ₃ -E ₃ ,..., A _n -E _n represent the straight line of heating and pressure increase of the working medium by fuel combustion under different compression forces, and with the increase of n value , the compression force increases continuously. It can be seen from Figure 18 that the slope of the combustion temperature rise and pressure increase line gradually increases with the increase of the compression force; it is not difficult to infer that from the state points E ₁ , E ₂ , E ₃ ,… ..., E _n After adiabatic expansion works, as the value of n increases, the temperature of the working fluid becomes lower.

（其中，

是常数，

是气体工质压力，

是气体工质温度，为绝热压缩指数）的关系大幅度提高，或者如果我们能够找到一种新型加热方式使外燃机的工质的压力和温度按照的关系大幅度提高，就可以制造出高效外燃机。从这个方面上讲，外燃循环是具有制造出效率高于内燃循环的潜力的一种循环方式。本实用新型所公开的小温升低熵混燃发动机就是利用了外燃循环和内燃循环的各自优势，使发动机的效率实现本质性提高。 In the small temperature rise and low entropy co-combustion engine disclosed by the utility model, Fig. 18 also illustrates: the situation of excess temperature in the traditional internal combustion engine is very serious, that is to say, the temperature after combustion in the traditional internal combustion engine is much higher than the pressure. Much more than necessary, it can also be said that the pressure is much lower than necessary compared to the temperature. From this point, it is not difficult for us to draw such a conclusion: if we can find high-quality materials that can withstand higher temperatures and higher pressures, the pressure and temperature of the working medium of the external combustion engine can be adjusted according to

(in,

is a constant,

is the gas pressure,

is the gas temperature, is the relationship between the adiabatic compressibility index) is greatly improved, or if we can find a new heating method to make the pressure and temperature of the working fluid of the external combustion engine according to The relationship between the two is greatly improved, and a high-efficiency external combustion engine can be produced. In this respect, the external combustion cycle is a cycle that has the potential to be more efficient than the internal combustion cycle. The small temperature rise and low entropy co-combustion engine disclosed in the utility model utilizes the respective advantages of the external combustion cycle and the internal combustion cycle, so that the efficiency of the engine is substantially improved.

Through more in-depth detailed analysis of the working process of the traditional internal combustion engine, we can draw the following conclusions: the highest energy state of the gas working medium in the engine cylinder (that is, the state of the gas working medium when the combustion has just finished, and the state of the gas working medium at this time The temperature and pressure are at the highest state in the whole cycle) is composed of two processes: the first process is the adiabatic compression of the gas by the piston (actually, it is approximately adiabatic compression)

（其中，

是常数，

是气体工质压力，

是气体工质温度，

为绝热压缩指数，空气的绝热压缩指数为1.4）的关系进行增压增温（见图17中的O-A 所示的曲线）；第二个过程是向气体内喷入燃料由燃烧化学反应产生的热量在近乎等容加热的状态下将气体的温度和压力按照

（其中，

是常数）的关系进行增温增压（见图17中的A-E所示的直线，图17是纵轴为压力坐标横轴为温度坐标的压力温度关系图）。由这两个过程共同作用使工质处于作功即将开始状态，作功冲程是按照绝热膨胀过程（实际上是近似绝热膨胀）进行的（见图17中的E-F所示的曲线），在这个绝热膨胀过程中，在对外输出功的同时，工质按照

（其中，

是常数）的关系降压降温直至作功冲程完了（点F所示的状态）。换句话说，达到工质最高能量状态是通过两个不同过程实现的，而由工质最高能量状态达到作功冲程完了时的状态是由一个绝热膨胀过程实现的。由于达到能量最高状态的过程中包括了一个燃烧化学反应放热升温的过程，此过程的温度和压力关系式为

，不难看出工质最高能量状态下（见图17中的点E所示的状态），温度处于“过剩”状态（所谓的“过剩”温度是指按照绝热膨胀的关系为了达到某一终点状态，在起点状态下工质的实际温度高于理论上所需要的温度，在本实用新型中所谓的某一终点状态是指接近O点的状态），“过剩”的温度导致膨胀过程的曲线处于高温位置（在图17中向右移动，即点F的状态，也就是说，点F处于点O的右侧），形成作功冲程完了时，温度仍然相当高的状态（如图17中曲线E-F所示的曲线上的点F所示的状态），由图17中点F所示的状态不难看出，

（即作功冲程完了时的工质温度，也就是低温热源的温度）仍然处于较高状态，也就是说仍然有相当的热量在工质内而没有变成功，这部分热量全部白白排放至环境，因此，效率会处于较低状态。图15是描述燃烧后气体工质的压力和温度关系符合绝热压缩过程温度和压力关系的示意图，点A、点B、点C三点分别表示压缩冲程完了时的状态，点AA表示由点A开始燃烧化学反应后达到的状态，点BB表示由点B开始燃烧化学反应后达到的状态，点CC表示由点C开始燃烧化学反应后达到的状态，点O是压缩冲程的起点也是膨胀作功冲程的终点。图16是描述燃烧后气体工质的压力大于由绝热压缩过程的压力和温度的关系所确定的压力值的示意图，点A、点B、点C三点分别表示压缩冲程完了时的状态；点AA表示由点A开始燃烧化学反应后达到的状态，点AAA表示由点AA膨胀作功达到的终点；点BB表示由点B开始燃烧化学反应后达到的状态，点BBB表示由点BB膨胀作功达到的终点；点CC表示由点C开始燃烧化学反应后达到的状态，点CCC表示由点CC膨胀作功达到的终点。图17 是压缩冲程完了时不同增温增压过程和加大压缩冲程的力度，使被压缩气体的温度达到环保温度限值或材料温度限值且燃烧前后温度不变或者没有明显变化，而压力大幅增加的过程示意图（包括与传统内燃机循环的比较曲线）；A-CC、A-BB、A-AA表示不同升温升压过程，点D表示被压缩气体的温度达到环保温度限值或材料温度限值的压缩冲程完了时的状态，D-DD表示燃烧前后温度不变或者没有明显变化而压力大幅增加的过程，点DDD、点CCC、点BBB、点AAA和点O分别表示不同过程的膨胀作功终点。如图15、图16和图17所示，如果我们能够找到一种方法使燃烧后的工质的压力温度状态点处于绝热压缩过程的压力温度曲线O-H上或处于绝热压缩过程的压力温度曲线O-H左方，则膨胀作功后的工质温度将可达到等于O点的温度、低于O点的温度或大幅度低于O点的温度的状态，这样将使发动机的效率大幅度提高，而且可以制造出输出的功接近燃料热值、等于燃料热值或大于燃料热值的发动机。如果燃烧后的工质的压力温度状态点处于绝热压缩过程的压力温度曲线O-H右侧，虽然不能制造出输出的功等于燃料热值或大于燃料热值的发动机，但通过使燃烧后的工质的压力温度状态点尽可能靠近O-H曲线，以达到效率的提高。而要想使燃烧后的工质的压力温度状态点处于曲线O-H上或处于曲线O-H左方，可行的办法是使燃烧化学反应放出的热量的全部或部分被所述膨胀剂吸收增加即将开始作功的气体工质的摩尔数，形成燃烧后的工质压力不低于由公式

（其中，

是燃烧后的工质压力，

是绝热压缩后未燃烧未导入膨胀剂的工质压力，是燃烧后膨胀剂所形成的分压，

是燃烧后的工质温度，

是绝热压缩后未燃烧未导入膨胀剂的工质温度，为绝热压缩指数，空气的绝热压缩指数为1.4）所确定的压力值，即

值，这样就能保证燃烧后的工质的压力温度状态点处于曲线O-H上或处于曲线O-H左方，这样才能实现更高的效率和更好的环保性。本实用新型所公开的小温升低熵混燃发动机依据上述理论，公开了如下技术方案：在压缩冲程/过程完了时，使燃烧化学反应放出的热量的一定比例或全部被已导入所述燃烧室的膨胀剂吸收增加即将开始作功的气体工质的摩尔数，例如图17中A-CC、A-BB、A-AA所示被已导入所述燃烧室的膨胀剂所吸收的燃烧化学反应所放出的热量的量按A-AA、A-BB、A-CC依次增加；为了进一步提高效率和环保性，本实用新型所公开的小温升低熵混燃发动机还公开了另外一种技术方案：大幅度提高对气体的压缩力度，使被压缩气体的温度达到环保温度限值或材料温度限值，并且使燃烧化学反应放出的热量全部被已导入所述燃烧室的膨胀剂吸收增加即将开始作功的气体工质的摩尔数，形成燃烧前后温度不变或者没有明显变化，而压力大幅增加的状态（例如图17中D-DD所示）。 The temperature and pressure of the gas according to the

(in,

is a constant,

is the gas pressure,

is the gas temperature,

is the adiabatic compressibility index, and the adiabatic compressibility index of air is 1.4) to carry out pressurization and temperature increase (see the curve shown by OA in Figure 17); The heat changes the temperature and pressure of the gas according to the state of nearly constant volume heating

(in,

is a constant) to increase the temperature and pressurize (see the straight line shown by AE in Figure 17, Figure 17 is a pressure-temperature relationship diagram in which the vertical axis is the pressure coordinate and the horizontal axis is the temperature coordinate). The combined action of these two processes puts the working medium in the state of starting to perform work, and the work stroke is carried out according to the process of adiabatic expansion (actually, it is approximately adiabatic expansion) (see the curve shown by EF in Figure 17). In the process of adiabatic expansion, while outputting work externally, the working medium is in accordance with

(in,

is a constant) to reduce the pressure and cool down until the power stroke is over (the state shown by point F). In other words, the highest energy state of the working fluid is achieved through two different processes, and the state at the end of the power stroke from the highest energy state of the working fluid is achieved through a process of adiabatic expansion. Since the process of reaching the highest energy state includes a combustion chemical reaction exothermic heating process, the relationship between temperature and pressure in this process is

, it is not difficult to see that in the state of the highest energy of the working fluid (see the state shown at point E in Figure 17), the temperature is in the "excess" state (the so-called "excess" temperature refers to the relationship between adiabatic expansion in order to reach a certain end state , the actual temperature of the working fluid in the starting state is higher than the theoretically required temperature, the so-called end state in the present utility model refers to the state close to point O), the "excess" temperature causes the curve of the expansion process to be in the High temperature position (moving to the right in Figure 17, that is, the state of point F, that is to say, point F is on the right side of point O), forming a state where the temperature is still quite high when the power stroke is over (as shown in the curve in Figure 17 The state shown by point F on the curve shown by EF), it is not difficult to see from the state shown by point F in Figure 17,

(that is, the temperature of the working medium when the power stroke is over, that is, the temperature of the low-temperature heat source) is still in a high state, that is to say, there is still considerable heat in the working medium without becoming successful, and all this heat is discharged to the environment in vain , so the efficiency will be lower. Figure 15 is a schematic diagram describing the relationship between the pressure and temperature of the gaseous working medium after combustion conforming to the relationship between temperature and pressure in the adiabatic compression process. Points A, B, and C respectively represent the state when the compression stroke is over, and point AA represents the state obtained by point A The state reached after starting the combustion chemical reaction. Point BB represents the state achieved after starting the combustion chemical reaction from point B. Point CC represents the state achieved after starting the combustion chemical reaction from point C. Point O is the starting point of the compression stroke and also the expansion work end of stroke. Fig. 16 is a schematic diagram describing that the pressure of the gas working medium after combustion is greater than the pressure value determined by the relationship between the pressure and the temperature in the adiabatic compression process. Points A, B and C represent the state when the compression stroke is over; AA represents the state reached after starting the combustion chemical reaction from point A, point AAA represents the end point reached by the expansion and work of point AA; point BB represents the state achieved after the combustion chemical reaction begins from point B, and point BBB represents the state achieved by the expansion of point BB The end point reached by work; point CC represents the state reached after starting the combustion chemical reaction from point C, and point CCC represents the end point reached by the expansion of point CC. Figure 17 shows the different warming and boosting processes and increasing the strength of the compression stroke when the compression stroke is over, so that the temperature of the compressed gas reaches the environmental protection temperature limit or the material temperature limit, and the temperature before and after combustion remains unchanged or does not change significantly, while the pressure Significantly increased process diagrams (including comparison curves with traditional internal combustion engine cycles); A-CC, A-BB, A-AA indicate different temperature and pressure increase processes, and point D indicates that the temperature of the compressed gas reaches the environmental temperature limit or material temperature The state at the end of the compression stroke of the limit value, D-DD indicates the process in which the temperature remains unchanged or does not change significantly before and after combustion, but the pressure increases greatly, and the points DDD, CCC, BBB, AAA and O respectively indicate the expansion of different processes The end point of work. As shown in Figure 15, Figure 16 and Figure 17, if we can find a way to make the pressure-temperature state point of the working fluid after combustion be on the pressure-temperature curve OH of the adiabatic compression process or in the pressure-temperature curve OH of the adiabatic compression process On the left, the temperature of the working medium after expansion work will reach a state equal to the temperature of point O, a temperature lower than point O, or a temperature significantly lower than point O, which will greatly improve the efficiency of the engine, and Engines can be produced that output work that is close to, equal to, or greater than the heating value of the fuel. If the pressure-temperature state point of the combusted working fluid is on the right side of the pressure-temperature curve OH in the adiabatic compression process, although an engine whose output work is equal to or greater than the calorific value of the fuel cannot be produced, the combustion of the working fluid The pressure-temperature state point is as close as possible to the OH curve to achieve an increase in efficiency. And in order to make the pressure temperature state point of the working fluid after combustion on the curve OH or on the left side of the curve OH, the feasible way is to make all or part of the heat released by the combustion chemical reaction be absorbed by the expansion agent and increase is about to start to work. The number of moles of the working gas working fluid, the pressure of the working fluid after combustion is not lower than the formula

(in,

is the working fluid pressure after combustion,

is the working fluid pressure without burning and introducing expansion agent after adiabatic compression, is the partial pressure formed by the expansion agent after combustion,

is the temperature of the working fluid after combustion,

is the temperature of the working medium without burning and introducing expansion agent after adiabatic compression, is the adiabatic compressibility index, the pressure value determined by the adiabatic compressibility index of air is 1.4), namely

value, so as to ensure that the pressure and temperature state point of the working fluid after combustion is on the curve OH or on the left side of the curve OH, so as to achieve higher efficiency and better environmental protection. The small temperature rise and low entropy co-combustion engine disclosed by the utility model discloses the following technical scheme based on the above theory: when the compression stroke/process is over, a certain proportion or all of the heat released by the combustion chemical reaction is introduced into the combustion The expansion agent absorption of the chamber increases the mole number of the gaseous working medium that is about to start working, such as shown by A-CC, A-BB, and A-AA in Fig. 17. The amount of heat released by the reaction increases sequentially according to A-AA, A-BB, and A-CC; in order to further improve efficiency and environmental protection, the small temperature rise and low entropy co-combustion engine disclosed in the utility model also discloses another Technical solution: greatly increase the compression force of the gas, so that the temperature of the compressed gas reaches the environmental temperature limit or the material temperature limit, and all the heat released by the combustion chemical reaction is absorbed and increased by the expansion agent introduced into the combustion chamber The number of moles of the gas working medium that is about to start working will form a state where the temperature remains unchanged or does not change significantly before and after combustion, but the pressure increases greatly (such as shown in D-DD in Figure 17).

所确定的压力值，而且大于由

所确定的压力值。第一个因素所营造的状态是温度过剩状态，第二个因素所营造的状态是温度负过剩状态，科学控制被膨胀剂吸收的燃料燃烧化学反应所放出热量的量，可以实现控制这两种因素的影响力，进而实现燃烧后温度升高、压力升高，但所形成的工质的状态点（由温度和压力所决定的点）在图17所示O-H曲线的左侧或在O-H曲线上或在O-H曲线的右侧但尽可能靠近O-H曲线。 In the small temperature rise and low entropy co-combustion engine disclosed by the utility model, a certain proportion of the heat released by the chemical reaction of fuel combustion is absorbed by the expansion agent introduced into the combustion chamber to increase the mole number of the gas working medium that is about to start working In the structure of the combustion chamber, the temperature and pressure in the combustion chamber will both increase, but the increase in pressure is composed of two factors: the first factor is that the temperature of the working medium increases due to the absorption of part of the heat released by the combustion chemical reaction ( Considering the constant volume temperature rise), and then the pressure increases according to the linear relationship; the second factor is that the molar number of the gas phase in the combustion chamber increases due to the expansion agent absorbing a part of the heat released by the combustion chemical reaction, which leads to an increase in pressure, and this pressure increase It is not caused by temperature rise. Even if the temperature drops, the temperature is constant or the temperature increases, the pressure will increase significantly during this process. The so-called significant increase in pressure means that the value of the pressure increase is not only greater than that caused by

The pressure value determined by the

The determined pressure value. The state created by the first factor is a state of excess temperature, and the state created by the second factor is a state of negative excess temperature. Scientifically controlling the amount of heat released by the chemical reaction of fuel combustion absorbed by the expander can realize the control of these two The influence of factors, and then realize the temperature rise and pressure rise after combustion, but the state point of the formed working fluid (the point determined by the temperature and pressure) is on the left side of the OH curve shown in Figure 17 or in the OH curve On or to the right of the OH curve but as close to the OH curve as possible.

In the small temperature rise and low entropy co-combustion engine disclosed by the utility model, the expansion agent introduced into the combustion chamber can not only absorb all the heat released by fuel combustion, but also absorb a part of the heat of the compressed gas working medium. In this case, the temperature of the working fluid at the beginning of work is lower than the temperature of the working fluid at the end of the compression stroke/process.

Fig. 19 is a comparison diagram of the dynamometer of the cycle of the small temperature rise and low entropy co-combustion engine disclosed by the utility model and the cycle of the traditional internal combustion engine. The curve shown is that the pressure at the end of the compression stroke of the small temperature rise and low entropy co-combustion engine disclosed by the utility model is slightly higher than the pressure at the end of the compression of the traditional internal combustion engine, but all or almost all of the heat released by the combustion chemical reaction has been introduced The expansion agent in the combustion chamber absorbs and increases the number of moles of the gas working medium that is about to start working, forming a cyclic dynamometer diagram formed by a state in which the temperature remains unchanged or does not change significantly before and after combustion, and the pressure is greatly increased. In the figure, a-z-n-t-a The curve shown is that the temperature of the small temperature rise and low entropy co-combustion engine disclosed by the utility model reaches the environmental protection temperature limit or the material temperature limit when the compression stroke is over, and all or almost all of the heat released by the combustion chemical reaction has been completely eliminated. The expansion agent introduced into the combustion chamber absorbs and increases the number of moles of the gas working medium that is about to start working, forming a cyclic dynamometer diagram composed of a state in which the temperature remains unchanged or does not change significantly before and after combustion, but the pressure increases greatly. It is not difficult to see that the small temperature rise and low entropy co-combustion engine disclosed by the utility model has higher efficiency and better environmental protection than the traditional internal combustion engine.

In the present utility model, Fig. 20 is the relationship diagram of the temperature T of the gas working medium and the pressure P, the curve shown in O-A-H is the adiabatic relationship curve of the gas working medium passing through the point O whose state parameters are 298K and 0.1MPa; point B is the gas working medium The actual state point of the mass, the curve shown in E-B-D is the adiabatic relationship curve passing through point B, and the pressures at point A and point B are the same; state point) working fluid adiabatic relationship curve.

In the utility model, the so-called adiabatic relationship includes the following three situations: 1. The state parameters of the gas working medium (ie, the temperature and pressure of the working medium) point on the adiabatic relationship curve of the working medium, that is, the state of the working medium The parameter points are on the curve shown by O-A-H in Figure 20; 2. The state parameters of the gas working fluid (ie, the temperature and pressure of the working fluid) are on the left side of the adiabatic relationship curve of the working fluid, that is, the state parameters of the gas working fluid are at The left side of the curve shown in O-A-H in Fig. 20; 3. The state parameters of the gas working fluid (i.e. the temperature and pressure of the working fluid) are on the right side of the adiabatic relationship curve of the gas working fluid, that is, the state parameter points of the gas working fluid are in the figure On the right side of the curve shown by O-A-H in 20, but the temperature of the gas working medium is not higher than the sum of the temperature plus 1000K, the sum of 950K, the sum of 900K, and the sum of 850K calculated by the pressure of the gas working fluid according to the adiabatic relationship Sum, sum of 800K, sum of 750K, sum of 700K, sum of 650K, sum of 600K, sum of 550K, sum of 500K, sum of 450K, sum of 400K, sum of 350K Sum, sum of 300K, sum of 250K, sum of 200K, sum of 190K, sum of 180K, sum of 170K, sum of 160K, sum of 150K, sum of 140K, sum of 130K Sum, sum of 120K, sum of 110K, sum of 100K, sum of 90K, sum of 80K, sum of 70K, sum of 60K, sum of 50K, sum of 40K, sum of 30K and or not higher than the sum of 20K, that is, as shown in Figure 20, the actual state point of the gas working medium is point B, point A is the point on the adiabatic relationship curve with the same pressure as point B, point A and point B The temperature difference between points should be less than 1000K, 900K, 850K, 800K, 750K, 700K, 650K, 600K, 550K, 500K, 450K, 400K, 350K, 300K, 250K, 200K, 190K, 180K, 170K, 160K, 150K, 140K , 130K, 120K, 110K, 100K, 90K, 80K, 70K, 60K, 50K, 40K, 30K or less than 20K.

In the utility model, the so-called adiabatic relationship can be any one of the above three situations, that is to say: the state parameters of the gas working medium (that is, the temperature and pressure of the gas working medium) that are about to start working 20 shown in the left area of the adiabatic process curve E-B-D through point B.

In the utility model, the so-called gas working fluid that is about to start working refers to the gas working fluid when both the combustion reaction and the expansion agent introduction process are completed.

In the utility model, the engine system (ie, thermal power system) whose state parameters of the gas working medium (that is, the temperature and pressure of the gas working medium) that is about to start working conforms to the adiabatic relationship is defined as a low-entropy engine.

In the utility model, adjust the state (namely temperature, pressure and quality) of the gas working fluid charged into the combustion chamber, adjust the amount of fuel introduced into the combustion chamber and the amount of expansion agent introduced into the system so that the operation is about to start. The temperature and pressure of the working gas working medium conform to the adiabatic relationship.

In the utility model, by cooling the gas working medium during the compression process or cooling the compressed gas working medium, by increasing the pressure of the gas working medium (such as multi-stage compression), by adding The method of introducing the expansion agent into the combustion chamber makes the temperature and pressure of the gas working medium which is about to start working conform to the adiabatic relationship.

In order to manufacture high-efficiency and ultra-efficient motors, the utility model proposes the following proposals:

A low-temperature-rise low-entropy mixed-combustion engine, comprising a combustion chamber, an expander source and a fuel source, the fuel source communicates with the combustion chamber through a fuel introduction control mechanism, and the expander source communicates with the combustion chamber through an expansion agent introduction control mechanism The combustion chamber communicates, and the fuel introduction control mechanism and the expansion agent introduction control mechanism are controlled by a combustion control device; the combustion chamber is set as a piston engine combustion chamber, and the pressure bearing capacity of the piston engine combustion chamber is greater than equal to 4MPa, or the combustion chamber is set as a turbine combustion chamber, and the pressure bearing capacity of the turbine combustion chamber is greater than or equal to 2MPa.

An expansion agent heat absorption heat exchanger is arranged between the combustion chamber and the expansion agent source, so that the expansion agent in the expansion agent source absorbs heat in the expansion agent heat absorption heat exchanger.

The heat source of the expander heat-absorbing heat exchanger is set as the waste heat of the low-temperature rise low-entropy co-combustion engine.

The expansion agent in the expansion agent source enters the combustion chamber after absorbing heat in the expansion agent heat absorption heat exchanger and reaching a critical state, a supercritical state or an ultra-supercritical state.

The low-temperature-rise low-entropy mixed-combustion engine also includes an oxidant source and a gas communication channel, the gas communication channel communicates with the intake port and the exhaust port of the combustion chamber, and an exhaust outlet is provided on the exhaust port, An exhaust release control valve is provided at the exhaust outlet, and the oxidant source communicates with the combustion chamber through the oxidant introduction control mechanism and then through the intake port or directly communicates with the combustion chamber through the oxidant introduction control mechanism. The chamber is connected, and the oxidant introduction control mechanism, the fuel introduction control mechanism and the expander introduction control mechanism are controlled by the combustion control device.

A gas heat-absorbing low-grade heat source heater is arranged on the gas communication channel.

A gas exothermic ambient cooler is provided on the gas communication channel and/or on the intake channel and/or on the exhaust channel.

A gas-liquid separator is provided at the exhaust channel of the combustion chamber, the expansion agent source is set as a liquid outlet of the gas-liquid separator, and the liquid in the gas-liquid separator is used as the expansion agent.

The expansion agent in the expansion agent source is set as a gas liquefied product.

The fuel in the fuel source is set as ethanol, the expander in the expander source is set as water, and the fuel source and the expander source are set as the same ethanol aqueous storage tank.

The combustion chamber is set as an adiabatic combustion chamber.

A method for improving the efficiency and environmental protection of the small temperature rise low entropy co-combustion engine, in which the combustion chamber is set as the combustion chamber of the piston engine, the compression ratio of the engine is adjusted so that the compression stroke is completed before the combustion The temperature of the compressed gas is within the range of plus or minus 200K of 1800K, and the flow rate of the compressor and the power turbine is adjusted in the structure in which the combustion chamber is set as the turbine combustion chamber so that the temperature of the gas before combustion in the turbine combustion chamber is at 1800K within the range of plus or minus 200K; adjust the amount of expansion agent introduced into the expansion agent source in the combustion chamber and the amount of fuel introduced into the fuel source in the combustion chamber, so that the All or nearly all of the heat generated by the combustion of fuel in the fuel source is absorbed in the combustion chamber by the expansion agent in the expansion agent source that has been introduced into the combustion chamber; after the fuel is burned in the combustion chamber, the combustion chamber The maximum value of the gas temperature is below the harmful compound NOx generation temperature to improve the environmental protection of the engine.

A method for improving the efficiency and environmental protection of the low-temperature-rise low-entropy co-combustion engine, adjusting the amount of expansion agent introduced into the expansion agent source in the combustion chamber and the fuel introduced into the fuel source in the combustion chamber amount, so that all or almost all of the heat generated by the combustion of the fuel introduced into the fuel source in the combustion chamber is absorbed by the expander in the expander source introduced into the combustion chamber; the fuel Before and after combustion in the combustion chamber, the temperature in the combustion chamber remains substantially constant and the pressure increases to improve the efficiency of the engine.

A method for improving the efficiency and environmental protection of the small temperature rise low entropy co-combustion engine, in which the combustion chamber is set as the combustion chamber of the piston engine, the compression ratio of the engine is adjusted so that the compression stroke is completed before the combustion The temperature of the compressed gas is above 1000K. In the structure in which the combustion chamber is set as the turbine combustor, the volume flow ratio of the compressor and the power turbine is adjusted so that the temperature of the gas before combustion in the turbine combustor is above 1000K.

A method for improving the efficiency and environmental protection of the low-temperature-rise low-entropy co-combustion engine, adjusting the amount of expansion agent introduced into the expansion agent source in the combustion chamber and the fuel introduced into the fuel source in the combustion chamber The amount is such that more than 5% of the heat generated by the combustion of the fuel introduced into the fuel source into the combustion chamber is absorbed in the combustion chamber by the expander in the expander source introduced into the combustion chamber.

A method for improving the efficiency and environmental protection of the low-temperature-rise low-entropy co-combustion engine, adjusting the temperature of the gas working medium that is about to start working to below 2000K, and adjusting the pressure of the gas working medium that is about to start working to above 15MPa, Make the temperature and pressure of the gas working medium that is about to start working conform to the similar adiabatic relationship.

In the present utility model, in the structure in which the combustion chamber is set as the piston engine combustion chamber, the pressure bearing capacity of the piston engine combustion chamber is greater than or equal to 4MPa, 4.5MPa, 5MPa, 5.5MPa, 6MPa, 6.5MPa , 7MPa, 7.5MPa, 8MPa, 8.5MPa, 9MPa, 9.5MPa, 10MPa, 10.5MPa, 11MPa, 11.5Pa, 12MPa, 12.5MPa, 13MPa, 13.5MPa, 14MPa, 14.5MPa, 15MPa, 15.5MPa, 16MPa, 16.5MPa . The pressure of the compressed gas is greater than or equal to 4MPa, 4.5MPa, 5MPa, 5.5MPa, 6MPa, 6.5MPa, 7MPa, 7.5MPa, 8MPa, 8.5MPa, 9MPa, 9.5MPa, 10MPa, 10.5MPa, 11MPa, 11.5Pa, 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, 22MPa, 24MPa, 26MPa, 28MPa, 30MPa . 4MPa, 4.5MPa, 5MPa, 5.5MPa, 6MPa, 6.5MPa, 7MPa, 7.5MPa, 8MPa, 8.5MPa, 9MPa, 9.5MPa, 10MPa, 10.5MPa, 11MPa, 11.5Pa, 12MPa, 12.5MPa, 13MPa, 13.5MPa, or Greater than or equal to 40MPa, that is, adjust the flow rate of the compressor and power turbine to make The pressure in the combustion chamber of the turbine is greater than or equal to 2MPa, 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, 11MPa, 11.5Pa, 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 , 22MPa, 24MPa, 26MPa, 28MPa, 30MPa, 32MPa, 34MPa, 36MPa, 38MPa or greater than or equal to 40MPa.

In the present utility model, the amount of the expansion agent introduced into the expansion agent source in the combustion chamber and the amount of fuel introduced into the fuel source in the combustion chamber are adjusted so that the amount of the fuel introduced into the fuel source in the combustion chamber 6% or more, 7% or more, 8% or more, 9% or more, 10% or more, 11% or more, 12% or more, 13% or more, 14% or more, 15% or more, 16% or more of the heat generated by fuel combustion , 17% or more, 18% or more, 19% or more, 20% or more, 21% or more, 22% or more, 23% or more, 24% or more, 25% or more, 30% or more, 35% or more, 40% or more, 45% More than %, more than 50%, more than 55%, more than 60%, more than 65%, more than 70%, more than 75%, more than 80%, more than 85%, more than 90%, more than 95%, or 100% in the burning The chamber is absorbed by the expansion agent in the source of expansion agent that has been introduced into the combustion chamber.

In the utility model, in the structure in which the combustion chamber is set as the combustion chamber of the piston engine, the compression ratio of the engine is adjusted so that the temperature of the compressed gas before the compression stroke is completed is above 1000K, above 1300K, above 1500K, or above 1800K. Above, above 2000K, above 2300K, above 2500K, above 2800K, above 3000K, above 3200K or above 3500K, in the structure where the combustion chamber is set as the combustion chamber of the turbine, the volume flow ratio of the compressor and the power turbine is adjusted so that the The temperature of the gas before combustion in the turbine combustion chamber is above 1000K, above 1300K, above 1500K, above 1800K, above 2000K, above 2300K, above 2500K, above 2800K, above 3000K, above 3200K or above 3500K.

The principle of the utility model is that by increasing the compression ratio of the engine, the temperature and pressure of the gas in the combustion chamber when the compression stroke or the compression process is completed can be achieved, and the amount of fuel and expansion agent entering the combustion chamber can be adjusted. A certain value of the heat released by combustion is absorbed by the expansion agent in the combustion chamber to form an increase in the number of working fluid moles, thereby increasing the pressure of the working fluid while the temperature change is small or remains unchanged. The working cycle mode replaces the traditional internal combustion engine combustion chamber by relying on gas The working fluid temperature rises to obtain the working cycle mode of pressure increase, specifically: for a piston engine, by increasing the compression ratio of the piston internal combustion engine, the gas pressure and temperature before combustion in the combustion chamber exceed the gas pressure of the traditional piston internal combustion engine and temperature, control the amount of fuel and expansion agent entering the combustion chamber and the temperature when the expansion agent enters the combustion chamber so that as much heat as possible from the combustion of the fuel is absorbed by the expansion agent, greatly increasing the pressure in the combustion chamber , while the change in temperature is small or remains unchanged; for the turbine, by adjusting the volume flow ratio of the compressor and the turbine, the gas pressure and temperature before combustion in the turbine combustor are both higher than the gas pressure and temperature in the traditional turbine combustor, Control the amount of fuel and expansion agent entering the combustion chamber and the temperature when the expansion agent enters the combustion chamber so that as much heat as possible from fuel combustion is absorbed by the expansion agent, greatly increasing the pressure in the combustion chamber, while the temperature The amount of change is small or remains unchanged; thereby greatly improving the efficiency and environmental protection of the engine.

In the utility model, the main purpose of the heat released by fuel combustion is to be absorbed by the expansion agent, and not used to heat the gas working medium (especially the gas working medium before combustion).

In the utility model, the so-called piston engine combustion chamber can be a four-stroke piston engine combustion chamber, also can be a two-stroke piston engine combustion chamber, a rotor piston engine combustion chamber, and can also be an air intake compression stroke and a power exhaust The stroke is the combustion chamber of a piston engine composed of two sets of mechanisms.

In the utility model, the so-called low-temperature heat source can also be called the cold source, which is equivalent to the so-called cold source in some documents.

In the utility model, the expansion agent heat-absorbing heat exchanger can be set as a cooler of the compressed gas in the compression process (stroke), that is, the expansion agent is used to absorb the heat of the compressed gas during the compression process, so that the compressed gas The temperature of the gas decreases.

In the utility model, the so-called "state (temperature and pressure) of the working medium under the high-temperature heat source" refers to the state of the working medium after absorbing heat from the high-temperature heat source, that is, the temperature and pressure of the working medium; the so-called working medium under the high-temperature heat source The state of may be consistent with the state of the high-temperature heat source, or it may be inconsistent with the state of the high-temperature heat source.

In the small temperature rise and low entropy co-combustion engine disclosed in the utility model, the so-called "heat is absorbed by the expansion agent" means that the heat is used to heat the expansion agent, gasification expansion agent, critical expansion agent and/or superheated expansion agent The so-called critical expansion agent refers to making the expansion agent in a critical state, a supercritical state, an ultra-supercritical state or a higher temperature and pressure state.

是常量和工质的起始状态以及热力学物性有关，

是燃烧后的工质压力，是燃烧后的工质温度，

为绝热压缩指数，空气的绝热压缩指数为1.4），换句话说，所述燃烧室内的气体的温度和压力的关系基本遵循以压缩冲程开始时的状态为起点，以公式

所确定的温度和压力的关系，或者压力大于由公式

所确定的压力值；这就使得膨胀作功后的工质温度要大幅度低于传统内燃机的排气温度，显而易见，效率的提高程度是相当大的。 In the utility model, the so-called "small or constant temperature change" means that after the fuel is burned, all or almost all of the heat is absorbed by the expansion agent, and the gas temperature in the combustion chamber changes little or remains the same before and after combustion. And there is almost no excess temperature (the so-called excess temperature means that in order to reach a certain end state according to the relationship of adiabatic expansion, the actual temperature of the working fluid in the starting state is higher than the theoretically required temperature); according to this working mode, in this In the small temperature rise and low entropy co-combustion engine disclosed in the utility model, after the fuel and expansion agent are introduced into the compressed gas working medium in the compression stroke (process) and the combustion chemical reaction occurs, the gas pressure in the combustion chamber is close to , equal to or greater than given by the formula The determined pressure values (where,

is a constant related to the initial state and thermodynamic properties of the working fluid,

is the working fluid pressure after combustion, is the temperature of the working fluid after combustion,

is the adiabatic compression index, the adiabatic compression index of air is 1.4), in other words, the relationship between the temperature and pressure of the gas in the combustion chamber basically follows the state at the beginning of the compression stroke as the starting point, with the formula

The relationship between temperature and pressure is determined, or the pressure is greater than by the formula

The determined pressure value; this makes the temperature of the working medium after the expansion work to be significantly lower than the exhaust temperature of the traditional internal combustion engine. Obviously, the degree of improvement in efficiency is quite large.

In the small temperature rise and low entropy co-combustion engine disclosed in the utility model, any two of fuel, oxidant (such as compressed air or compressed oxygen-containing gas) and expansion agent can be mixed in advance and then mixed with the third , the combustion reaction can first occur between the oxidant and the fuel and then mix with the expansion agent, or it can occur when the three are mixed or after the three are mixed; a core combustion zone can be established in the combustion chamber, and in the core combustion zone, the oxidant and fuel After direct combustion, it is mixed with the expansion agent between the combustion core area and the combustion chamber wall, so that the high temperature flame formed by the direct combustion of fuel and oxidant can be isolated from the combustion chamber wall by the expansion agent, thereby reducing the combustion chamber wall heat load.

The so-called expansion agent of the utility model refers to the working medium that does not participate in the combustion chemical reaction to absorb heat and adjust the molar number of the working medium and expand the working medium, which can be gas, liquid, critical state substance, gas liquefied product, such as water vapor , carbon dioxide, helium, nitrogen, liquid carbon dioxide, liquid helium, liquid nitrogen or liquefied air, etc.

The so-called liquefied gas in the present invention refers to liquefied gas, such as liquid nitrogen, liquid carbon dioxide, liquid helium or liquefied air.

The so-called oxidizing agent of the utility model refers to the oxygen-containing gas that does not produce harmful compounds during the thermal power conversion process of pure oxygen or other components, such as liquefied air, hydrogen peroxide or hydrogen peroxide aqueous solution, etc. The so-called oxidant source refers to all devices, systems or containers that can provide oxidants, such as commercial oxygen sources (ie, high-pressure oxygen storage tanks or liquefied oxygen tanks) and oxygen provided by on-site oxygen generation systems in thermal power systems (such as membrane separation systems). oxygen system), etc.

The so-called gas heat-absorbing low-grade heat source heater in the utility model refers to a device that uses a low-grade heat source (such as exhaust waste heat, waste heat of the cooling system, etc.) as a heat source to heat the gas working medium; Refers to the device that cools the gas working medium by discharging the heat of the gas working medium into the environment; the so-called combustion control device refers to the device that controls the amount of fuel, the amount of expander and/or the amount of oxidant and the amount of fuel, expander and A device that controls combustion by the phase of oxidant introduction; the so-called gas-liquid separator refers to a device that separates gas and liquid.

The so-called introduction control mechanism of the utility model refers to the system that supplies the original working medium (fuel, expansion agent and/or oxidant) to the combustion chamber according to the requirements of the combustion conditions of the combustion chamber of the thermal power system. This system includes valves, pumps and /or sensors etc.

The so-called expansion agent heat-absorbing heat exchanger in the utility model refers to the expansion agent that uses the heat of the environment or the waste heat of the low-temperature-rise low-entropy co-combustion engine (such as exhaust heat and cooling system waste heat) as a heat source to absorb heat. Hot heat exchanger.

The so-called environmental protection temperature limit in the utility model refers to the highest temperature that does not produce harmful pollutants, such as the environmental protection temperature limit that does not produce nitrogen oxides is 1800K; the so-called material temperature limit refers to the maximum temperature that the material can withstand .

The expansion agent in the utility model can be recycled in the low-temperature-rise low-entropy co-combustion engine.

The so-called fuel in the utility model refers to all substances that can undergo violent oxidation-reduction reactions with oxygen in the sense of chemical combustion, which can be gas, liquid or solid, and mainly include gasoline, diesel oil, natural gas, hydrogen, coal gas and fluidized fuels. , liquefied fuel or powdered solid fuel, etc. The so-called liquefied fuel refers to a liquefied fuel that is gaseous at normal temperature and pressure.

The small temperature rise and low entropy co-combustion engine disclosed in the utility model can use hydrocarbons or hydrocarbon oxygen compounds as fuel, such as ethanol or ethanol aqueous solution, and use ethanol aqueous solution to replace the original fuel and expansion agent, which can not only prevent freezing, It is also possible to replace the original fuel storage tank and expansion agent storage tank with only one ethanol aqueous solution storage tank, and change the required ratio of fuel and expansion agent by adjusting the concentration of ethanol aqueous solution. When necessary, the mixed solution of ethanol, water and hydrocarbons can be used to replace the fuel and expansion agent in the utility model, and its concentration can be adjusted to meet the requirements of the small temperature rise and low entropy co-combustion engine disclosed in the utility model . In the small temperature rise and low entropy co-combustion engine disclosed by the utility model, the hydrogen peroxide aqueous solution can be used to replace the oxidant and the expansion agent, and the ratio of the oxidant and the expansion agent can be adjusted by adjusting the concentration of the hydrogen peroxide aqueous solution. The hydrogen peroxide aqueous solution storage tank replaces the oxidant storage tank and the expansion agent storage tank.

In the utility model, in some technical proposals, the temperature of the working medium can reach thousands of degrees or even higher, and the pressure of the working medium can reach hundreds of atmospheres or even higher.

In the small temperature rise and low entropy co-combustion engine disclosed by the utility model, by adjusting the temperature and pressure of the gas in the combustion chamber, the temperature and pressure of the working medium after expansion work can be adjusted so that when the work is successfully expanded to the set expansion When under pressure, the temperature of its working fluid drops to a relatively low level, such as close to ambient temperature, lower than ambient temperature or substantially lower than ambient temperature.

So-called turbine in the utility model refers to gas turbines, jet engines and other mechanisms that utilize gas to drive turbines to do work; so-called piston engines include piston internal combustion engines, rotor piston internal combustion engines, and the like.

所确定的压力值；本实用新型所公开的小温升低熵混燃发动机中，液氮以气体的形式导入所述燃烧室时，氮气的压力比所述燃烧室内的气体压力高2MPa、3MPa、4MPa、5MPa、6MPa、7MPa、8MPa、9MPa、10MPa、11MPa、12MPa、13MPa、14MPa、15MPa、16MPa、17MPa、18MPa、19MPa或高20MPa。 In the low-temperature rise and low-entropy co-combustion engine disclosed in the utility model, since the temperature in the combustion chamber can be set below the nitrogen oxide generation temperature, even if liquid nitrogen is used as the expansion agent, nitrogen oxides will not be produced ( NO _x ); liquid nitrogen can be introduced into the combustion chamber in liquid form, can also be introduced into the combustion chamber in a critical state, and can also be introduced into the combustion chamber in the form of ultra-high pressure gas. The so-called ultra-high pressure means that the pressure of the gas is not only higher than the gas pressure in the combustion chamber when liquid nitrogen is introduced, but also higher than the pressure determined by the formula

The determined pressure value; in the small temperature rise and low entropy co-combustion engine disclosed by the utility model, when liquid nitrogen is introduced into the combustion chamber in the form of gas, the pressure of nitrogen is 2MPa, 3MPa higher than the gas pressure in the combustion chamber , 4MPa, 5MPa, 6MPa, 7MPa, 8MPa, 9MPa, 10MPa, 11MPa, 12MPa, 13MPa, 14MPa, 15MPa, 16MPa, 17MPa, 18MPa, 19MPa or 20MPa higher.

The beneficial effects of the utility model are as follows:

The small temperature rise and low entropy co-combustion engine disclosed by the utility model has high efficiency and good environmental protection.

Description of drawings

What Fig. 1 shows is the structural representation of the utility model embodiment 1;

What Fig. 2 shows is the structural representation of the utility model embodiment 2;

What Fig. 3 shows is the structural representation of the utility model embodiment 3;

What Fig. 4 shows is the structural representation of the utility model embodiment 4;

What Fig. 5 shows is the structural representation of the utility model embodiment 5;

What Fig. 6 shows is the structural representation of the utility model embodiment 6;

What Fig. 7 shows is the structural representation of the utility model embodiment 7;

What Fig. 8 shows is the structural representation of the utility model embodiment 8;

What Fig. 9 shows is the structural representation of the utility model embodiment 9;

Figure 10 is a schematic structural view of Embodiment 10 of the present utility model.

What Fig. 11 shows is the schematic diagram of q>0 cycle of the present utility model;

What Fig. 12 shows is the q=0 cycle schematic diagram of the present utility model;

What Fig. 13 shows is the q<0 cycle schematic diagram of the present utility model;

What Fig. 14 shows is the working schematic diagram of the heat engine with different compression force;

Figure 15 is a schematic diagram of the utility model describing the pressure and temperature relationship of the combustion gas working medium in line with the temperature and pressure relationship of the adiabatic compression process;

Figure 16 is a schematic diagram of the utility model describing that the pressure of the gas working medium after combustion is greater than the pressure value determined by the relationship between the pressure and the temperature of the adiabatic compression process;

What Fig. 17 shows is the pressure-temperature relationship diagram that the vertical axis is the pressure coordinate and the horizontal axis is the temperature coordinate;

What Fig. 18 shows is the schematic diagram of the temperature and pressure relation of different E points starting adiabatic expansion work;

What Fig. 19 shows is the power indication comparison diagram of the cycle of the small temperature rise low entropy co-combustion engine disclosed by the utility model and the cycle of the traditional internal combustion engine;

Fig. 20 is a graph showing the relationship between the temperature T and the pressure P of the gas working fluid.

In the picture:

1 Combustion chamber, 2 Expander source, 3 Fuel source, 5 Oxidant source, 6 Compressor, 7 Power turbine, 9 Gas communication channel, 10 Intake port, 11 Exhaust port, 12 Exhaust discharge port, 13 Exhaust discharge Control valve, 16 oxidant introduction control mechanism, 18 gas exothermic environment cooler, 17 gas endothermic low-grade heat source heater, 20 expansion agent introduction control mechanism, 30 fuel introduction control mechanism, 101 piston engine combustion chamber, 102 turbine combustion Chamber, 1020 expansion agent heat-absorbing heat exchanger, 3020 combustion control device, 1100 gas-liquid separator.

Detailed ways

Example 1

The small temperature rise low entropy mixed combustion engine shown in Figure 1 comprises a combustion chamber, an expander source 2 and a fuel source 3, and the combustion chamber is set as a piston engine combustion chamber 101, and the piston engine combustion chamber 101 The pressure bearing capacity is greater than or equal to 4MPa, the fuel source 3 communicates with the combustion chamber through the fuel introduction control mechanism 30, the expansion agent source 2 communicates with the combustion chamber through the expansion agent introduction control mechanism 20, and the fuel introduction control mechanism 20 communicates with the combustion chamber. The mechanism 30 and the expansion agent introduction control mechanism 20 are controlled by the combustion control device 3020 to realize that more than 5% of the heat generated by the combustion of the fuel in the fuel source 3 entering the combustion chamber is introduced into the combustion chamber. The expansion agent in the expansion agent source 2 in the combustion chamber is absorbed; in the structure in which the combustion chamber is set as the piston engine combustion chamber 101, the compression ratio of the engine is adjusted so that the pressure of the compressed gas when the compression stroke is completed It is greater than the gas pressure at the end of the compression stroke of the traditional piston engine. Adjust the temperature of the gas working medium that is about to start working to below 2000K, and adjust the pressure of the gas working medium that is about to start working to above 15MPa, so that the gas that is about to start working The temperature and pressure of the working fluid conform to a similar adiabatic relationship. In the structure in which the combustion chamber is set as the piston engine combustion chamber 101, the compression ratio of the engine is adjusted so that the pressure of the compressed gas when the compression stroke is finished is greater than or equal to 4MPa; the combustion chamber is set as the piston engine In the structure of the combustion chamber 101, the compression ratio of the engine is adjusted so that the temperature of the compressed gas before combustion after the compression stroke is within the range of plus or minus 200K from 1800K, and the fuel introduction control mechanism 30 and the expansion agent introduction control mechanism 20 are controlled by The combustion control device 3020 controls all or almost all of the heat generated by the combustion of the fuel in the fuel source 3 entering the combustion chamber to be introduced into the expansion agent source 2 in the combustion chamber The expansion agent absorbs; after the fuel is burned in the combustion chamber, the maximum temperature in the combustion chamber is below the harmful compound NOx generation temperature to improve the environmental protection of the engine;

In the structure in which the combustion chamber is set as the piston engine combustion chamber 101, the compression ratio of the engine is adjusted so that the temperature of the compressed gas before the compression stroke is completed and burned is above 1000K.

During specific implementation, optionally, adjust the compression ratio of the engine so that the pressure of the compressed gas at the end of the compression stroke is greater than or equal to 4.5MPa, 5MPa, 5.5MPa, 6MPa, 6.5MPa, 7MPa, 7.5MPa, 8MPa, 8.5MPa, 9MPa , 9.5MPa, 10MPa, 10.5MPa, 11MPa, 11.5Pa, 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, 22MPa, 24MPa, 26MPa, 28MPa, 30MPa, 32MPa, 34MPa, 36MPa, 38MPa or greater than or equal to 40MPa;

The fuel introduction control mechanism 30 and the expansion agent introduction control mechanism 20 are controlled by the combustion control device 3020 to achieve more than 6% and more than 7% of the heat generated by the fuel combustion in the fuel source 3 entering the combustion chamber , 8% or more, 9% or more, 10% or more, 11% or more, 12% or more, 13% or more, 14% or more, 15% or more, 16% or more, 17% or more, 18% or more, 19% or more, 20% More than %, more than 21%, more than 22%, more than 23%, more than 24%, more than 25%, more than 30%, more than 35%, more than 40%, more than 45%, more than 50%, more than 55%, more than 60% , more than 65%, more than 70%, more than 75%, more than 80%, more than 85%, more than 90%, more than 95%, or 100% of the expansion agent source that has been introduced into the combustion chamber in the combustion chamber 2. Expansion agent absorption in 2;

Adjust the compression ratio of the engine so that the temperature of the compressed gas before combustion after the compression stroke is above 1300K, above 1500K, above 1800K, above 2000K, above 2300K, above 2500K, above 2800K, above 3000K, above 3200K or above 3500K.

Example 2

The difference between the small temperature rise and low entropy co-combustion engine shown in Figure 2 and Embodiment 1 is that an expander heat absorption heat exchanger 1020 is set between the combustion chamber and the expander source 2, so that all The expansion agent in the expansion agent source 2 absorbs heat in the expansion agent heat absorption heat exchanger 1020, and the combustion chamber is set as an adiabatic combustion chamber.

Example 3

The difference between the small temperature rise low entropy co-combustion engine shown in Figure 3 and Embodiment 1 is that the heat source of the expansion agent heat absorption heat exchanger 1020 is set as the waste heat of the small temperature rise low entropy co-combustion engine . The expansion agent in the expansion agent source 2 absorbs heat in the expansion agent heat absorption heat exchanger 1020 and reaches the critical state, supercritical state or ultra-supercritical state before entering the combustion chamber.

During specific implementation, the fuel in the fuel source 3 is set as ethanol, the expansion agent in the expansion agent source 2 is set as water, and the fuel source 3 and the expansion agent source 2 are set as the same aqueous ethanol storage tank .

Example 4

The small temperature rise low entropy mixed combustion engine shown in Figure 4 differs from Embodiment 1 in that: the small temperature rise low entropy mixed combustion engine also includes an oxidant source 5 and a gas communication channel 9, and the gas communication channel 9 communicates with the intake passage 10 and the exhaust passage 11 of the combustion chamber, an exhaust outlet 12 is provided on the exhaust passage 11, and an exhaust discharge control valve 13 is arranged at the exhaust outlet 12, so The oxidant source 5 communicates with the combustion chamber through the oxidant introduction control mechanism 16 and then through the air inlet 10 or directly communicates with the combustion chamber through the oxidant introduction control mechanism 16. The oxidant introduction control mechanism 16, the The fuel introduction control mechanism 30 and the expansion agent introduction control mechanism 20 are controlled by the combustion control device 3020 .

Example 5

The difference between the low-temperature rise and low-entropy co-combustion engine shown in FIG. 5 and Embodiment 4 is that a gas heat-absorbing low-grade heat source heater 17 is provided on the gas communication channel 9 .

Example 6

The difference between the small temperature rise and low entropy co-combustion engine shown in Figure 6 and Embodiment 4 is: on the gas communication channel and/or on the intake port and/or on the exhaust port Gas exothermic ambient cooler.

Example 7

The small temperature rise low entropy mixed combustion engine shown in Figure 7 includes a combustion chamber, an expander source 2 and a fuel source 3, and its difference from Embodiment 1 is that the combustion chamber is set as a turbine combustion chamber 102, and the The pressure bearing capacity of the turbine combustion chamber 102 is greater than or equal to 2MPa, and the flow rate of the compressor 6 and the power turbine 7 of the turbine is adjusted so that the pressure in the turbine combustion chamber 102 is greater than or equal to 2MPa; In the structure of the combustion chamber 102, the volume flow ratio of the compressor 6 of the turbine and the power turbine 7 is adjusted so that the temperature of the gas before combustion in the combustion chamber 102 of the turbine is above 1000K.

During specific implementation, the flow rate of the compressor 6 and the power turbine 7 of the turbine is adjusted so that the pressure in the combustion chamber 102 of the turbine 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, 11MPa, 11.5Pa, 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, 22MPa, 24MPa, 26MPa, 28MPa, 30MPa, 32MPa, 34MPa, 36MPa, 38MPa or greater than or equal to 40MPa; adjust the compressor of the turbine 6 The volume flow ratio with the power turbine 7 makes the temperature of the gas before combustion in the turbine combustion chamber 102 more than 1300K, more than 1500K, more than 1800K, more than 2000K, more than 2300K, more than 2500K, more than 2800K, more than 3000K, more than 3200K or more than 3500K above.

Example 8

The difference between the small temperature rise and low entropy co-combustion engine shown in Figure 8 is that the expansion agent source 2 is replaced by an oxidant source 5, and the oxidant source 5 communicates with the oxidant source 5 through an oxidant introduction control mechanism 16. The turbine combustor 102 communicates.

Example 9

The small temperature rise low entropy co-combustion engine shown in Figure 9 differs from Embodiment 5 in that: the small temperature rise low entropy co-combustion engine also includes an oxidant source 5, a gas communication channel 9 and a low-grade gas heat absorption A heat source heater 17, the oxidant source 5 communicates with the turbine combustor 102 through the oxidant introduction control mechanism 16, and the gas communication channel 9 communicates with the intake port 10 of the compressor 6 and the exhaust of the power turbine 7 Air passage 11, the exhaust side outlet 12 is set on the exhaust passage 11, the exhaust discharge valve 13 is set at the exhaust discharge outlet 12, the oxidant introduction control mechanism 16, the fuel introduction control mechanism 30 , the expansion agent introduction control mechanism 20 and the exhaust discharge valve 13 are controlled by the combustion control device 3020 .

Example 10

The difference between the small temperature rise and low entropy co-combustion engine shown in Figure 10 and Embodiment 1 is: a gas-liquid separator 1100 is set at the exhaust passage 11 of the combustion chamber, and the expansion agent source 2 is set to The liquid outlet of the gas-liquid separator 1100, the liquid in the gas-liquid separator 1100 is used as the expansion agent.

Obviously, the utility model is not limited to the above embodiments. According to the known technologies in the art and the technical solutions disclosed in the utility model, many variants can be deduced or associated, and all these variants should also be considered as part of the utility model. protected range.

Claims (11)

1. one kind little temperature rise low-entropy mixed-fuel engine; Comprise the firing chamber; Dilatant source (2) and fuel source (3); It is characterized in that: said fuel source (3) imports control mechanism (30) through fuel and is communicated with said firing chamber, and said dilatant source (2) imports control mechanism (20) through dilatant and is communicated with said firing chamber, and said fuel imports control mechanism (30) and said dilatant importing control mechanism (20) receives combustion control device (3020) control; Said firing chamber is made as reciprocating engine firing chamber (101); The bearing capacity of said reciprocating engine firing chamber (101) is more than or equal to 4MPa; Or said firing chamber is made as turbine combustion chamber (102), and the bearing capacity of said turbine combustion chamber (102) is more than or equal to 2MPa.

2. according to claim 1 little temperature rise low-entropy mixed-fuel engine; It is characterized in that: between said firing chamber and said dilatant source (2), establish dilatant endothermic heat exchanger (1020), the dilatant in the said dilatant source (2) is absorbed heat in said dilatant endothermic heat exchanger (1020).

3. like the said little temperature rise low-entropy mixed-fuel engine of claim 2, it is characterized in that: the thermal source of said dilatant endothermic heat exchanger (1020) is made as the waste heat of said little temperature rise low-entropy mixed-fuel engine.

4. like the said little temperature rise low-entropy mixed-fuel engine of claim 2, it is characterized in that: the dilatant in the said dilatant source (2) gets into said firing chamber after in said dilatant endothermic heat exchanger (1020), absorbing heat and reaching threshold state, supercritical state or ultra supercritical state again.

5. according to claim 1 little temperature rise low-entropy mixed-fuel engine; It is characterized in that: said little temperature rise low-entropy mixed-fuel engine also comprises oxidizer source (5) and gas communication passage (9); Said gas communication passage (9) is communicated with the intake duct (10) and the air outlet flue (11) of said firing chamber; On said air outlet flue (11), establish exhaust tapping hole (12); Locate to establish exhaust at said exhaust tapping hole (12) and emit control valve (13); Said oxidizer source (5) imports control mechanism (16) through oxygenant and is communicated with said firing chamber or directly is communicated with said firing chamber through said oxygenant importing control mechanism (16) through said intake duct (10) again, and said oxygenant imports control mechanism (16), said fuel imports control mechanism (30) and said dilatant importing control mechanism (20) receives combustion control device (3020) control.

6. like the said little temperature rise low-entropy mixed-fuel engine of claim 5, it is characterized in that: on said gas communication passage (9), establish gas heat absorption low-grade heat source heater (17).

7. like the said little temperature rise low-entropy mixed-fuel engine of claim 5, it is characterized in that: upward and/or at said intake duct (10) go up and/or on said air outlet flue (11), establish gas heat release ambient cooler (18) at said gas communication passage (9).

8. according to claim 1 little temperature rise low-entropy mixed-fuel engine; It is characterized in that: the air outlet flue (11) in said firing chamber locates to establish gas-liquid separator (1100); Said dilatant source (2) is made as the liquid outlet of said gas-liquid separator (1100), and the liquid in the said gas-liquid separator (1100) uses as said dilatant.

9. according to claim 1 little temperature rise low-entropy mixed-fuel engine is characterized in that: the dilatant in the said dilatant source (2) is made as the gas liquefaction thing.

10. according to claim 1 little temperature rise low-entropy mixed-fuel engine; It is characterized in that: the fuel in the said fuel source (3) is made as ethanol; Dilatant in the said dilatant source (2) is made as water, and said fuel source (3) and said dilatant source (2) are made as same ethanol water storage tank.

11. according to claim 1 little temperature rise low-entropy mixed-fuel engine is characterized in that: said firing chamber is made as insulated combustion chamber.

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