WO2012024898A1

WO2012024898A1 - Small temperature rise low-entropy mixed-fuel engine

Info

Publication number: WO2012024898A1
Application number: PCT/CN2011/001430
Authority: WO
Inventors: 靳北彪
Original assignee: Jin Beibiao
Priority date: 2010-08-27
Filing date: 2011-08-26
Publication date: 2012-03-01
Also published as: CN102588149B; CN102588149A

Abstract

A small temperature rise low-entropy mixed-fuel engine includes a combustion chamber, an expansive agent source (2) and a fuel source (3). The fuel source (3) is in communication with the combustion chamber through a fuel input control mechanism (30). The expansive agent source (2) is in communication with the combustion chamber through an expansive agent input control mechanism (20). The fuel input control mechanism (30) and the expansive agent input control mechanism (20) are controlled by a combustion control device (3020). The combustion chamber is designed to be a piston engine combustion chamber (101), and the pressure bearing capability of the piston engine combustion chamber (101) is greater than or equal to 4 MPa. Alternatively, the combustion chamber is designed to be a turbine combustion chamber (102), and the pressure bearing capability of the turbine combustion chamber (102) is greater than or equal to 2 MPa. The small temperature rise low-entropy mixed-fuel engine is efficient and environmentally friendly. Also provided is a method for improving the efficiency and environmental friendliness of the small temperature rise low-entropy mixed-fuel engine.

Description

Small temperature rise and low entropy co-firing engine

Technical field

This invention relates to the field of thermal energy and power, and more particularly to an engine.

Background technique

In order to improve the efficiency of conventional internal combustion engines (including piston internal combustion engines and internal combustion engines), many proposals have been made to inject expansion agents into the combustion chamber. However, there is no solution to explicitly inject the amount of expansion agent into the combustion chamber and the pressure state in the combustion chamber before injection. However, the amount of expansion agent injected into the combustion chamber and the pressure and temperature state in the combustion chamber before combustion affect the injection of the expansion agent into the combustion chamber of the internal combustion engine. One of the most important factors in the efficiency of an internal combustion engine in a solution. Therefore, it is necessary to clarify the amount of the expansion agent to be injected into the combustion chamber and the state parameter of the gas when the internal combustion engine is compressed, so that the combustion medium is injected into the combustion chamber and the combustion state parameter is more reasonable to improve the efficiency of the engine.

Summary of the invention

Two representative ways of the second law of thermodynamics are: 1. Kelvin's way of saying is "it is impossible to extract heat from a single heat source, so that it becomes completely useful without causing other changes." Sri Lanka's way of saying is "it is impossible to transfer heat from a low temperature object to a high temperature object without any other influence." In his 1824 paper entitled "The Power of Fire", Carnot proposed that the heat engine must work between two heat sources, extract heat from the high-temperature heat source, and transfer a part of the heat absorbed to the low-temperature heat source. Mechanical work. According to this conclusion, Kano proposed the famous Kano theorem, namely, 7 = 1 - Γ ₂ /7, (where, // is the cycle efficiency, 7; is the temperature of the high temperature heat source, and Γ ₂ is the temperature of the low temperature heat source. ), Carnot's theorem is a theorem with guiding significance in current heat engine theory. At present, the understanding of Carnot's theorem is: the heat extracted from the high-temperature heat source during the isothermal expansion of the working medium at the high-temperature heat source temperature is regarded as the heat of "absorbing heat from the high-temperature heat source" in the Carnot's theorem; The amount of heat emitted by the environment is considered to be the part of the heat in the Carnot's theorem "transmitting a part of the absorbed heat to the low-temperature heat source". However, in the actual heat engine cycle, the high-temperature heat source is artificially manufactured, and the low-temperature heat source is self-manufactured 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. For example, in an external combustion engine, if a swelling agent is injected into a working fluid at a high temperature heat source temperature and the expansion agent absorbs heat at a high temperature heat source temperature to increase or vaporize (including a criticalization process and overheating). Process) boosting, and the pressure parameter of the newly formed working medium (the so-called newly formed working medium including the original working medium and the expanding agent) reaches a state in which the temperature of the working medium is lower than even when the expansion is completed Substantially lower than the ambient temperature. The work output by such a cyclic process must be close to, equal to or exceed the heat absorbed from the high temperature heat source. In other words, the efficiency must be close to, equal to or exceed 100%, if the temperature of the working fluid of the expansion work is lower than At ambient temperature, it is impossible to dissipate heat from a low temperature heat source but can absorb heat from a low temperature heat source or be exported. The derived working fluid can be thrown into other heat sources at any temperature (including high temperature heat sources). For example, in an internal combustion engine, the high-temperature heat source of the internal combustion engine is the working fluid after the combustion of the fuel, and the low-temperature heat source (also referred to as the cold source) is the working medium after the expansion work, and the state of the working fluid after the expansion work is 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 parameter of the working fluid after the combustion of the fuel reaches a certain value, the temperature of the working fluid after the expansion work can be made lower or even 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, the efficiency must be close to, equal to or exceed 100%. If the temperature of the working fluid for expansion is lower than the ambient temperature, It is impossible to dissipate heat from a low temperature heat source but can absorb heat from a low temperature heat source or be derived, and the derived working fluid can be thrown into other heat sources at any temperature (including high temperature heat sources). On the surface, these two examples all create conditions that cannot be explained by existing thermodynamic theories and theorems. Therefore, the current understanding of the Carnot's theorem is misunderstood, so what is the so-called "heat from the high-temperature heat source" refers to which part of the heat, and the so-called "transfer a part of the absorbed heat to the low-temperature heat source" Which part of the heat is the part of the heat? The inventors believe 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 medium from the temperature of the low-temperature heat source to the temperature of the high-temperature heat source (including the temperature of the high-temperature heat source) The heat absorbed by the lower working medium from the high temperature heat source) (shown as Q in Figure 11) and the bottom heat of the working medium (the so-called bottom heat of the working medium refers to the absolute zero degree contained in the working medium at the low temperature heat source temperature itself). The calculated heat (shown as Qc in Figure 1) consists of two parts, and the so-called "transfer a part of the heat absorbed to the low-temperature heat source" is the heat that is discharged from the working medium to the environment ( As shown by q in Figure 1) and the bottom heat of the working fluid (shown as Qc in Figure 11), it consists of two parts. In other words, even if the working temperature after the expansion work is lower than the ambient temperature, the working fluid can not transfer heat to the environment, as long as the working medium after the expansion work is found, such as thrown into the environment or thrown into any temperature. In other heat sources (including high temperature heat sources), the heat engine can be cycled. Not only that, but in certain specific Under the condition, the low temperature working fluid after expansion work can be thrown into the high temperature heat source of the system (as shown by the dotted line in Qc-ML in Fig. 12). For example, the working fluid cooled and condensed after expansion work can be thrown into the combustion of the internal combustion engine. In the inner or boiler steam generator, for example, the exhaust gas in the air motor is thrown into the environment (in some air engines, the environment is the high-temperature heat source of the air motor), and for example, it will be absorbed from the working fluid after the expansion work. The hot liquid is thrown into the high temperature heat source. From this, it can be concluded that the heat engine can work under a heat source, and the heat engine can be cycled as long as the working fluid after the expansion work is derived. The derived working fluid after expansion can be thrown into a heat source lower than its own temperature, can be thrown into the same heat source as its own temperature, can be thrown into a heat source higher than its own temperature, can be thrown into In the high-temperature heat source, it can also be thrown into a heat source higher than the temperature of the high-temperature heat source; not only that, if the working medium after the expansion work 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. For example, the cooling medium for cooling the working fluid after the expansion work can be thrown into the high temperature heat source. Therefore, the necessary conditions for the operation of the heat engine are not two heat sources, but at least one heat source, at least one residual flow outlet (the so-called residual flow outlet refers to the outlet of the working fluid after the expansion work and/or the work after the expansion work) The outlet of the mass heat can be connected to any other heat source (including the high temperature heat source of the system), and in the structure in which the residual stream outlet is connected to the high temperature heat source, the heat machine only needs one heat source to circulate, In the structure in which the residual flow outlet is not in communication with the high temperature heat source, the heat engine needs at least two heat sources, and the residual flow outlet can only be when the residual flow outlet is in communication with a heat source having a temperature higher than the residual flow outlet. The outlet of the working fluid after the expansion work. The inventor's heat is: heat transfer and mass transfer during the operation of the heat engine may exist, 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 any other influence, but we can throw a low temperature object (such as a low temperature working medium) into a high temperature object (such as a high temperature working medium) through mass transfer ( That is, the process of throwing a low-temperature object into a high-temperature object) realizes the unrealizable process of "transferring heat from a low-temperature object to a high-temperature object." The conclusion that the heat transfer and mass transfer during the operation of the heat engine can exist, coexist or replace each other is the conclusion that the work of manufacturing a high-efficiency heat engine or manufacturing output equals the calorific value of the fuel or the work output is greater than the heat value of the fuel. The direction. FIG. 1 , FIG. 12 and FIG. 13 are three cycle diagrams of q>0, q=0, and q<0, respectively.

The inventor believes that the second law of thermodynamics can be explained by the following statement: The condition is not two heat sources, but at least one heat source, at least one residual stream outlet (the so-called residual stream outlet refers to the outlet of the working fluid after the expansion work and/or the heat outlet of the working medium after the expansion work) The residual flow outlet may be in communication with any other heat source (including a high temperature heat source of the system), and in the structure in which the residual flow outlet is in communication with the high temperature heat source, the heat engine only needs one heat source to circulate, in the residual flow The heat exchanger in the structure that is not connected to the high temperature heat source needs at least two heat sources. When the residual stream outlet is in communication with a heat source having a temperature higher than the residual stream outlet, the residual stream outlet can only be expanded after work. The export of working fluids. In his 1824 paper "The Power of Fire", Carnot proposed that "the heat engine must work between two heat sources, extract heat from the high-temperature heat source, and pass a part of the heat absorbed to the low-temperature heat source. Only in this way The discussion of obtaining mechanical work is only a special case of the inventor's claim to the second law of thermodynamics. Kano is a great scientist, but in his time the internal combustion engine was not born, and it may be because of this reason that Karno's thought was limited. Not only that, but only the temperature is reflected in the Carnot's theorem, and there is no pressure involved. This shows that it is very likely that Carnot first set two heat sources with different temperatures in the process of conceiving the Carnots theorem, and then let the heat engine (Most likely to be limited to external combustion engines) work between the two heat sources in a Carnot cycle, which is exactly the opposite of a real heat engine. Low temperature heat source for real heat engines

(also called cold source) is not pre-existing, but is determined by the state of the working fluid (temperature and pressure) under high temperature heat source and the thermodynamic properties of the working medium. In other words, the low temperature heat source of the actual heat engine (also called The cold source is not pre-existing, but is based on the state of the working fluid (temperature and pressure) under the high temperature heat source and the thermodynamic properties of the working medium. According to the state of the working fluid (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 which is self-made by the expansion process can be completely lower than the ambient temperature. In other words, the output work can be completely high. The heat extracted from the high temperature heat source. From this, it can be concluded that: under the premise of setting the temperature of the high-temperature heat source to the environmental temperature limit or the material temperature limit, it is necessary to increase the pressure of the working medium under the high-temperature heat source so as to make the working medium after the expansion work. The temperature is as low as possible to improve the efficiency of the engine. In reality, the efficiency of the heat engine is not determined by the temperature of the high temperature heat source and the ambient temperature, but by the value of the temperature and pressure in the high temperature heat source state. In other words, it is the temperature of the high temperature heat source and the heat source according to the high temperature. Lower working condition

(Temperature and pressure) and the thermodynamic properties of the working fluid are determined by the temperature of the low temperature heat source that is self-manufactured by the expansion process. Chemical energy is the source of energy for modern heat engines. However, the inventors believe that the use of chemical energy in conventional heat engines has considerable defects, and the root cause of these defects is that the understanding of an extremely important property of chemical energy is insufficient. Deep, that is, the understanding of the properties of chemical energy that can be input energy to the working fluid in any high-energy state (high temperature and high pressure) is not deep enough. In the present invention, for the convenience of explanation, the chemical energy is an attribute that can input energy to a working medium in any high-energy state (high temperature and high pressure) as a super-existence of chemical energy, and if the super-characteristics of chemical energy are fully utilized That is, the efficiency of the heat engine can be substantially improved. Now take the heat engine with compression stroke (process) and combustion products involved in work as an example: Figure 1 4, S, S ₂ and S ₃ are schematic diagrams of the heat machine with different compression strengths. , S ₂ and S ₃ sequentially increase, 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, regardless of the pressure How high the shrinking force does not affect the efficiency of the heat engine itself, but the higher the compression strength, the higher the chemical energy is to a higher grade. These higher grade chemical energy can be more in the process of work. Most of them are output in the form of work. If the state parameters are reasonable, they are increased by a considerable compression force to a relatively high grade of chemical energy. During the expansion work, the temperature of the working medium can be lowered to a level significantly lower than the standard state. , in turn, the work output by the heat engine is greater than the heat value of the fuel; S ₃₁ in Figure 14 is a process in which the temperature of the fuel is constant after the fuel burns out in the presence of a swelling agent, in the process, P ₂ = Pi represents the process of increasing the volume of the working fluid before and after combustion, and the output work W is close to the chemical energy Q _h , P ₂ >P, indicating that the working pressure before and after combustion increases, and the output work W is greater than the chemical energy Q _h . It can be seen that in order to produce a heat engine with a compression stroke (process) and combustion products involved in work, which is efficient or ultra-efficient (super efficient means that the output of the heat engine is equal to or greater than the chemical energy of the fuel), it must be: Significantly increase the compression force of the heat engine to transfer the chemical energy to the working medium at a relatively high energy level; 2. Rationalize the state parameters of the high temperature and high pressure working medium formed by the release of chemical energy (so-called "after chemical energy release" The rationalization of the state parameters of the formed high-temperature and high-pressure working medium means that the relationship between the pressure and the temperature of the working fluid after combustion can be made to bring the temperature of the working medium to work close to, equal to, or lower than the temperature by the introduction of the expanding agent or other means. Or substantially lower than the standard state temperature, the so-called other way is to greatly increase the strength of the engine compression stroke without the expansion agent, so that the pressure and temperature at the end of the compression stroke are at a relatively high state It can heat and heat the working fluid, as shown in the high-end position in Figure 18. Although this method does not produce an ultra-efficient engine, It is possible to manufacture a highly efficient engine, however, S The required temperature and pressure of the compressed working fluid are quite high, which will impose very demanding requirements on the material of the engine.) 3. Reasonable selection of working medium and/or expansion agent (so-called reasonable choice of working medium means selection of phase change heat is small) Moreover, the working fluid which is liquefied when the expansion work is set to a certain degree, the so-called rational selection of the expansion agent refers to a swelling agent which is selected to be liquefied when the expansion heat is small to a set degree. For external combustion engines, first, the working fluid must absorb heat at a relatively high pressure and temperature (using environment or other low-grade heat source to make the working medium at a relatively high temperature and pressure, then use chemical energy to heat the working medium. Second, the state parameters of the working fluid after the endotherm must be rationalized; Third, the reasonable selection of the working medium (the so-called reasonable choice of working medium refers to the selection of the phase change heat is small and the liquid is liquefied when the expansion work to the set level) quality). Figure 18 is a detailed calculation data of heating and warming up the working fluid by fuel combustion under the premise of different compression strength of the working medium. The vertical axis is pressure, the horizontal axis is temperature, and 0-H is adiabatic compression. The curves, A, - E, A _{2 -} E ₂ , A _{3 -} E ₃ , ..., A - E _n represent the straight line of heating and heating of the working medium by fuel combustion under different compression forces, and with the value of n The increase of compression, the compression strength continues to increase, as can be seen from Figure 18, the slope of the combustion temperature rise line gradually increases with the increase of compression strength; it is not difficult to reason, from the state point E, E _{2 in} Figure 18 E ₃ , ..., After starting the adiabatic expansion work, as the value of n increases, the temperature of the working medium is lower.

In the small temperature rise and low entropy co-firing engine disclosed by the present invention, FIG. 18 also illustrates that: the temperature excess in the conventional internal combustion engine is very serious, that is, in the conventional internal combustion engine, the temperature is far after the combustion compared with the pressure. Exceeding the necessary values, it can be said that the pressure is much lower than the necessary value compared with the temperature. From this point we can easily conclude that if we can find high-quality materials that can withstand higher temperatures and higher pressures, the pressure and temperature of the external combustion engine's working fluid should be P = C (where is constant) The corpse is the gas working fluid pressure, the temperature of the gas working fluid, the relationship of the adiabatic compression 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 P - The relationship between C and ^ is greatly improved, and a highly efficient external combustion engine can be manufactured. In this respect, the external combustion cycle is a cyclical way to create a higher efficiency than the internal combustion cycle. The small temperature rise and low entropy co-firing engine disclosed by the invention utilizes the respective advantages of the external combustion cycle and the internal combustion cycle, so that the efficiency of the engine is substantially improved.

After a more detailed analysis of the working process of a conventional internal combustion engine, we can draw the following conclusions: The highest energy state of the gas working fluid in the engine cylinder (ie, the gas working state when the combustion is just finished, at this time the gas working fluid Temperature and pressure are at the highest state throughout the cycle) are made up of two The process consists of: the first process is the adiabatic compression of the gas by the piston (actually approximately adiabatic compression). The temperature and pressure of the gas are in accordance with ρ = ςΓ^ (where ^ is a constant, Ρ is a gaseous working fluid) The pressure, Γ is the gas working temperature, the adiabatic compression index, and the adiabatic compression index of the air is 1. 4) for the boosting and warming (see the curve shown by 0-Α in Figure 17.) The second process is to inject fuel into the gas. The heat generated by the combustion chemical reaction is in the state of near isovolumic heating. The temperature and pressure of the gas are in accordance with P = C ₂ T (where (: ₂ is a constant) relationship. The warming pressurization is carried out (see the line shown by A - E in Fig. 17), and Fig. 17 is the pressure-temperature relationship diagram in which the vertical axis is the pressure coordinate and the horizontal axis is the temperature coordinate.) The two processes work together. The quality is at the beginning of the work, and the power stroke is performed according to the adiabatic expansion process (actually approximately adiabatic expansion) (see the curve shown by EF in Fig. 17). During this adiabatic expansion, the external output is At the same time, the working fluid is in accordance with = C ₃ r^ (where ₃ is The relationship of the constants is lowered by the temperature until the power stroke is completed (the state shown by point F). In other words, the highest energy state of the working medium is achieved by two different processes, and the highest energy state of the working medium reaches the work. The state at the end of the stroke is achieved by an adiabatic expansion process. Since the process of reaching the highest energy state includes a process of exothermic heating of the combustion chemical reaction, the relationship between temperature and pressure of this process is P = C ₂ T , It is difficult to see that the working medium has the highest energy state (see the state shown by point E in Fig. 17), and the temperature is in the "excess" state (the so-called "excess" temperature means that in order to reach a certain end state according to the relationship of adiabatic expansion, In the starting state, the actual temperature of the working medium is higher than the theoretically required temperature. In the present invention, the so-called end point state refers to a state close to zero point), and the "excess" temperature causes the curve of the expansion process to be in a high temperature position. (moving to the right in Figure 17. That is, the state of point F, that is, point F is on the right side of point 0), when the power stroke is completed, the temperature is still quite high. State (as shown by the point F on the curve shown by the curve EF in Fig. 17), it is easy to see from the state shown by the point F in Fig. 17. Γ ₂ (that is, the working fluid when the power stroke is completed) The temperature, that is, the temperature of the low-temperature heat source, is still in a high state, that is, there is still considerable heat in the working medium without success, and this part of the heat is completely discharged to the environment, so the efficiency will be in a low state. Figure 15 is a schematic diagram showing the relationship between the pressure and temperature of the gas working fluid after combustion in accordance with the temperature and pressure of the adiabatic compression process. The three points of point eight, point 8, and point C respectively indicate the state when the compression stroke is completed, and the point ΑΑ indicates The state reached after the combustion of the chemical reaction is started from the point ,, the point BB represents the state reached after the combustion of the chemical reaction from the point B, the point CC represents the state reached after the combustion of the chemical reaction from the point C, and the point 0 is the starting point of the compression stroke. Also inflated The end of the power stroke. Figure 16 is a schematic diagram showing the pressure value of the gas working fluid after combustion is greater than the pressure value determined by the relationship between the pressure and temperature of the adiabatic compression process. The three points of point, point B and point C respectively indicate when the compression stroke is completed. State; point AA indicates the state reached after burning chemical reaction from point A, point AAA indicates the end point reached by expansion of point AA; point BB indicates the state reached after burning chemical reaction from point B, point BBB indicates point by point The end point at which the BB expansion work is reached; the point CC indicates the state reached after the combustion of the chemical reaction from the point C, and the point CGC indicates the end point reached by the expansion of the point CC. Figure 1 7 is the intensity of different warming pressurization process and increasing the compression stroke when the compression stroke is completed, so that the temperature of the compressed gas reaches the environmental temperature limit or the material temperature limit and the temperature before or after combustion is constant or not obvious. Change, and the process diagram of the pressure increase greatly (including the comparison curve with the traditional internal combustion engine cycle); A-CC, A-BB, A-AA indicate different temperature rise and pressure rise process, point D indicates that the temperature of the compressed gas reaches the environmental protection temperature The state of the limit or material temperature limit at the end of the compression stroke, D-DD indicates the process of constant or no significant change in pressure before and after combustion, point DDD, point CCG, point BBB, point AAA, and point 0 Represents the end points of the expansion work for different processes. As shown in Fig. 15, Fig. 16, and Fig. 17, if we can find a way to make the pressure temperature state point of the burned working medium be at the pressure temperature curve 0-H of the adiabatic compression process or at adiabatic pressure. The pressure temperature curve of the shrinking process is 0-H to the left, and the working temperature after the expansion work can reach a temperature equal to 0, a temperature lower than 0, or a temperature lower than 0, which will The efficiency of the engine is greatly improved, and an engine whose output work is close to the fuel heat value, equal to the fuel heat value, or greater than the fuel heat value can be manufactured. If the pressure temperature state point of the burned working fluid is on the right side of the pressure temperature curve 0-H of the adiabatic compression process, although the engine whose output work is equal to the fuel heat value or greater than the fuel heat value cannot be produced, by burning The pressure temperature state point of the working fluid is as close as possible to the 0-H curve to achieve an increase in efficiency. However, if the pressure temperature state point of the burned working fluid is on the curve 0-H or on the left side of the curve 0-H, it is feasible to absorb all or part of the heat released by the combustion chemical reaction by the expansion agent. Increase the number of moles of gas working fluid that is about to start work, and the pressure of the working fluid after combustion is not lower than the formula / > = (corpse. ₊ PJ (77r.) ^ (where the corpse is the working pressure of the burning, P. is the working pressure of unburned and not introduced into the expansion agent after adiabatic compression, is the partial pressure formed by the expansion agent after combustion, Γ is the working temperature after combustion, 7 is not burned after adiabatic compression, not introduced The working temperature of the expanding agent, ^ is the adiabatic compression index, and the adiabatic compression index of the air is 1. 4) The determined pressure value, that is, the corpse value, thus ensuring the pressure temperature state of the working medium after combustion The point is on curve 0-H or on the left side of curve 0-H to achieve higher efficiency and better environmental friendliness. According to the above theory, the small temperature rise and low entropy co-firing engine disclosed in the present invention discloses the following technical solution: when the compression stroke/process is completed, 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 number of moles of gas working medium to be started, for example, the combustion absorbed by the expansion agent introduced into the combustion chamber as shown by A-GC, A-BB, A-AA in Fig. 17. The amount of heat released by the chemical reaction increases in order of 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 by the present invention also discloses another type. Technical solution: The compression of the gas is greatly increased, the temperature of the compressed gas reaches the environmental temperature limit or the material temperature limit, and the heat released by the combustion chemical reaction is completely introduced into the expansion agent of the combustion chamber. Absorption increases the number of moles of gaseous working fluid that is about to start work, forming a state in which the temperature before or after combustion is constant or does not change significantly, and the pressure is greatly increased (for example, as shown by D-DD in Fig. 17).

In the small temperature rise and low entropy co-firing engine disclosed in the present invention, a certain proportion of the heat released by the chemical reaction of the fuel combustion is absorbed by the expansion agent introduced into the combustion chamber to increase the number of moles of the gaseous working medium to be started to work. In the structure, the temperature and pressure in the combustion chamber will increase, but the pressure increase is composed of two factors: The first factor is that the working medium absorbs a part of the heat released by the combustion chemical reaction, causing the temperature of the working medium to rise. The constant temperature rise is considered), and then the pressure rises in a linear relationship; the second factor is that the expansion agent absorbs a part of the heat released by the combustion chemical reaction, causing the gas phase number in the combustion chamber to increase, resulting in an increase in pressure, which is not an increase in pressure. Due to the 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 pressure increase means that the pressure increase is not only greater than the pressure determined by >= C ₂ r Value, and greater than the pressure value determined by _{P = Cir} . The state created by the first factor is the state of over-temperature, and the state created by the second factor is the state of negative temperature excess. Scientifically controlling the amount of heat released by the chemical reaction of the fuel absorbed by the expansion agent can achieve control. The influence of the factor, and then the temperature rise and pressure rise after combustion, but the state point of the formed working fluid (the point determined by temperature and pressure) is on the left side of the 0-H curve shown in Figure 17. On the 0-H curve or on the right side of the 0-H curve but as close as possible to the 0-H curve.

The small temperature rising low entropy co-firing engine disclosed by the invention can not only absorb the total heat released by the fuel combustion, but also absorb a part of the compressed gas. The heat of the working fluid, in this case, the temperature of the working fluid to be started to work is lower than the working temperature at the end of the compression stroke/process.

Figure 19 is a comparison diagram of the cycle of the cycle of the small temperature rise and low entropy co-firing engine disclosed in the present invention and the cycle of the conventional internal combustion engine. The curve shown by abcda is a diagram of the cycle of the conventional internal combustion engine, in which abmsa The curve shown is that the pressure of the small temperature rise and low entropy co-firing engine disclosed in the present invention when the compression stroke is completed is slightly larger than the pressure at the end of the compression of the conventional internal combustion engine, but all or nearly all of the heat released by the combustion chemical reaction has been The expansion agent introduced into the combustion chamber absorbs the number of moles of gas working medium that is about to start work, and forms a cycle diagram of a state in which the temperature before or after combustion is constant or does not change significantly, and the pressure is greatly increased, in the figure, a - the curve shown by znta is the total or near-heat of the temperature of the small temperature rise and low entropy co-firing engine disclosed in the present invention when the compression stroke is completed, the temperature reaches the environmental temperature limit or the material temperature limit, and the combustion chemical reaction is released. All of the expansion agent introduced into the combustion chamber absorbs the number of moles of gaseous working fluid that is about to start work, forming before and after combustion. Of the same or did not change significantly, and the cycle indicator diagram of a substantial increase in the pressure state thereof. It is not difficult to see that the small temperature rise and low entropy co-firing engine disclosed by the present invention has higher efficiency and better environmental protection than conventional internal combustion engines.

In the present invention, FIG. 20 is a graph showing the relationship between the temperature T and the pressure P of the gas working medium, and the curve indicated by 0-A-H is a gas working adiabatic relationship curve passing through the zero point of the state parameter of 298 K and 0.1 MPa; Point B is the actual state point of the gas working fluid. The curve shown by EBD is the adiabatic relationship curve passing through point B. The pressures at point A and point B are the same; the curve shown by F-G is through 2800K and 10MPa (that is, the current internal combustion engine is about to The adiabatic relationship curve of the working point of the gaseous working fluid that starts work.

In the present invention, the so-called adiabatic relationship includes the following three cases: 1. The state parameter of the gaseous working fluid (ie, the temperature and pressure of the working medium) is on the adiabatic relationship curve of the working fluid, that is, the state parameter of the gaseous working fluid. The point is on the curve shown by 0-AH in Figure 20; 2. The state parameter of the gas working fluid (ie the temperature and pressure of the working medium) is on the left side of the adiabatic relationship curve of the working fluid, that is, the state parameter point of the gas working fluid. On the left side of the curve shown by 0-AH in Figure 20; 3. The state parameter of the gas working fluid (ie, the temperature and pressure of the working fluid) is on the right side of the adiabatic relationship curve of the working fluid, that is, the state parameter of the gas working fluid. The point is on the right side of the curve shown by 0-AH in Fig. 20, but the temperature of the gas working fluid is not higher than the temperature of the gas working fluid calculated by the adiabatic relationship plus the sum of 1000K, the sum of 950K, and 900K. And, add 850K and add 800K And, add 750K and, add 700K and, add 650K and add 600K and add 550K and add 500K and add 450K and add 400K and add 350K and add 300K And, add 250K and, add 200K and, force 1 90K and force H 180K, force [] 1 70K sum, add 1 60K sum, force Π 1 50K sum, force 卩 140K And sum of force B 130K, add 1 20K sum, add 1 10K sum, add 100K sum, add 90K sum, add 80K sum, add 70K sum, add 60K sum, plus 50K sum Add 40K sum, add 30K and or not to add 20K, that is, as shown in Figure 20, the actual working point of the gas working medium is point B, and point A is the same adiabatic relationship of pressure and point B. The point on the curve, the temperature difference between point A and point B should be less than 1 000Κ, 900Κ, 850Κ, 800Κ, 750Κ, 700Κ, 650Κ, 600Κ, 550Κ, 500Κ, 450Κ, 400Κ, 350Κ, 300Κ, 250Κ, 200Κ, 1 90Κ, 180Κ, 1 70Κ, 1 60Κ, 150Κ, 140Κ, 130Κ, 1 20Κ, 1 10Κ, 100Κ, 90Κ, 80Κ, 70Κ, 60Κ, 50Κ, 40Κ, 30Κ or small At 20 baht.

In the present invention, the so-called adiabatic relationship may be any one of the above three cases, that is, the state parameter of the gas working medium to be started working (ie, the temperature and pressure of the gas working medium) is as shown in FIG. 20 . The adiabatic process curve shown through the defect is in the left region of the EB-D.

In the present invention, the so-called gaseous working fluid which is about to start work refers to a gaseous working fluid when both the combustion reaction and the expansion agent introduction process are completed.

In the present invention, an engine system (i.e., a thermodynamic system) in which the state parameters of the gaseous working medium (i.e., the temperature and pressure of the gaseous working medium) to be started to work is classified as a low-entropy engine is defined.

In the present invention, the state (i.e., temperature, pressure, and mass) of the gaseous working medium charged in the combustion chamber is adjusted, the amount of fuel introduced into the combustion chamber is adjusted, and the amount of the expanding agent introduced into the system is caused to start work. The temperature and pressure of the gaseous working fluid are in a class of adiabatic relationships.

In the present invention, by cooling the gas working medium during the compression process or cooling the compressed gas working medium, the gas working medium is greatly pressurized (for example, multi-stage compression). By introducing a swelling agent into the combustion chamber, the temperature and pressure of the gaseous working fluid to be started to work are in an adiabatic relationship.

In order to produce an efficient and ultra efficient engine, the present invention proposes the following scheme:

A small temperature rise low entropy co-firing engine includes a combustion chamber, a source of expansion agent and a fuel source, the fuel source being in communication with the combustion chamber via a fuel introduction control mechanism, and the source of the expansion agent is introduced into the control machine via an expansion agent Constructed in communication with the combustion chamber, 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 a pressure of the piston engine combustion chamber is The capacity is greater than or equal to 4 MPa, or the combustion chamber is set to be a turbine combustion chamber, and the pressure capacity of the turbine combustion chamber is greater than or equal to 2 MPa.

An expansion agent heat absorption heat exchanger is disposed between the combustion chamber and the expansion agent source to cause the expansion agent in the expansion agent source to absorb heat in the expansion agent heat absorption heat exchanger.

The heat source of the expansion agent heat absorption heat exchanger is set as the residual heat of the small temperature rise low entropy co-firing engine. The expansion agent in the expansion agent source enters the combustion chamber after the endothermic heat in the expansion agent heat absorption heat exchanger reaches a critical state, a supercritical state, or an ultra-supercritical state.

The small temperature rise low entropy co-firing engine further includes an oxidant source and a gas communication passage, the gas communication passage communicates with an intake passage and an exhaust passage of the combustion chamber, and an exhaust gas discharge port is disposed on the exhaust passage, Providing an exhaust gas discharge control valve at the exhaust gas discharge outlet, wherein the oxidant source is connected to the combustion chamber via the oxidant introduction control mechanism or directly through the oxidant introduction control mechanism and the combustion The chamber is connected to communicate, and the oxidant introduction control means, the fuel introduction control means, and the expansion agent introduction control means are controlled by a combustion control means.

A gas-absorbing low-grade heat source heater is disposed on the gas communication passage.

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

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

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

The fuel in the fuel source is set to ethanol, the expansion agent in the expansion agent source is set to water, and the fuel source and the expansion agent source are set to be the same aqueous ethanol storage tank.

The combustion chamber is configured as an adiabatic combustion chamber.

A method for improving the efficiency and environmental protection of the small temperature rise and low entropy co-firing engine, adjusting a compression ratio of the engine in a structure in which the combustion chamber is set as the combustion chamber of the piston engine, so that the compression stroke is completed before combustion The temperature of the compressed gas is in 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 to the turbine combustion chamber to burn the turbine. The temperature of the pre-combustion gas is in the range of plus or minus 200 K of 1800 K; adjusting the amount of the expansion agent introduced into the expansion agent source in the combustion chamber and the amount of fuel introduced into the combustion source in the combustion chamber so that All or nearly all of the heat generated by the combustion of the fuel introduced into the fuel source of the combustion chamber is absorbed in the combustion chamber by the expansion agent introduced into the expansion agent source in the combustion chamber; adjusting the fuel in the The maximum gas temperature in the combustion chamber after combustion in the combustion chamber is below the harmful compound NOx formation temperature to improve the environmental friendliness of the engine.

A method for improving the efficiency and environmental friendliness of the small temperature rise and low entropy co-firing engine, adjusting an amount of expansion agent introduced into the expansion agent source in the combustion chamber and fuel introduced into the fuel source in the combustion chamber An amount such that all or nearly all of the heat generated by the combustion of the fuel in the fuel source introduced into the combustion chamber is absorbed in the combustion chamber by the expansion agent introduced into the expansion agent source in the combustion chamber; The temperature in the combustion chamber is substantially maintained at a constant pressure increase before and after combustion of the combustion chamber to increase the efficiency of the engine.

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

A method for improving the efficiency and environmental friendliness of the small temperature rise and low entropy co-firing engine, adjusting an amount of expansion agent introduced into the expansion agent source in the combustion chamber and fuel introduced into the fuel source in the combustion chamber The amount of 5% or more of the heat generated by the combustion of the fuel in the fuel source introduced into the combustion chamber is absorbed in the combustion chamber by the expansion agent introduced into the expansion agent source in the combustion chamber.

A method for improving the efficiency and environmental protection of the small temperature rise and low entropy co-combustion engine, adjusting the temperature of the gas working medium to be started to work below 2000K, adjusting the pressure of the gas working medium to be started to work to 15 Pa Above, the temperature and pressure of the gaseous working fluid that is about to start work are in accordance with the adiabatic relationship.

In the present invention, in the structure in which the combustion chamber is configured as the piston engine combustion chamber, the pressure capacity of the piston engine combustion chamber is greater than or equal to 4 MPa, 4. 5 MPa, 5 MPa, 5. 5 MPa, 6 MPa, 6 5WPa, 7MPa, 7. 5MPa, 8MPa, 8. 5MPa, 9MPa, 9. 5MPa, 10MPa, 10. 5MPa, 1 1 MPa, 11.5Pa, 12MPa, 12.5MPa, 13MPa, 13.5 Pa 14MPa, 14.5MPa, 15MPa, 15.5MPa, 16MPa, 16.5MPa, 17MPa, 17.5 Pa> 18MPa, 18.5MPa, 19MPa, 19.5 Pa 20MPa, 22MPa, 24MPa, 26MPa, 28MPa 30MPa, 32MPa, 34MPa, 36MPa, 38MPa or 40MPa or more, that is, the compression ratio of the engine is adjusted so that the pressure of the compressed gas when the compression stroke is completed is 4 MPa, 4.5 MPa, 5 MPa, 5.5 MPa, 6 MPa, 6.5. MPa, 7MPa, 7.5MPa, 8MPa, 8.5MPa, 9MPa 9.5MPa, 10MPa, 10.5MPa, 11MPa, 11.5Pa, 12MPa, 12.5 Pa 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, 28 Pa 30MPa, 32MPa, 34MPa, 36MPa, 38MPa or 40MPa or more; In the structure, the pressure capacity of the turbine combustion chamber is greater than or equal to 2 MPa, 2.5 MPa, 3 MPa, 3.5 MPa, 4 MPa, 4.5 MPa, 5 MPa, 5.5 MPa, 6 MPa, 6.5 Pa 7 MPa, 7.5 MPa, 8 MPa, 8.5 MPa, 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 40MPa or more, that is, adjusting the flow rate of the compressor and the power turbine to make the pressure in the combustion chamber of the turbine 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, 12.5 MPa, 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 34 MPa, 36 MPa, 38 MPa or 40 MPa or more.

In the present invention, the amount of the expansion agent introduced into the expansion agent source in the combustion chamber and the amount of fuel introduced into the combustion source in the combustion chamber are adjusted to cause fuel introduced into the fuel source of 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 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% Above, 50% or more, 55% or more, 60% or more, 65% or more, 70% or more, 75% or more, 80% or more, 85% or more, 90% or more, 95% or more, or 100% in the burning The cooking chamber is absorbed by the expanding agent introduced into the expansion agent source in the combustion chamber.

In the present invention, in the configuration in which the combustion chamber is a piston engine combustion chamber, the compression ratio of the engine is adjusted so that the compression stroke is completed. The temperature of the compressed gas before combustion is 1000 K or more, 1300 K or more, and 1500 K or more. 1800K or more, 2000K or more, 2300K or more, 2500K or more, 2800K or more, 3000K or more, 3200K or more, or 3500K or more, adjusting the volumetric flow ratio of the compressor and the power turbine in the structure in which the combustion chamber is set to the turbine combustion chamber The temperature of the gas before combustion in the turbine combustion chamber is 1000 K or more, 1300 K or more, 1500 K or more, 1800 K or more, 2000 K or more, 2300 K or more, 2500 K or more, 2800 K or more, 3000 K or more, 3200 K or more, or 3500 K or more.

The principle of the present invention is to increase the amount of fuel and expansion agent entering the combustion chamber by increasing the compression ratio of the engine to increase the temperature and pressure of the gas in the combustion chamber when the compression stroke or compression process is completed. A certain value of the calorific value of the combustion of the fuel in the combustion chamber is absorbed by the expansion agent to form an increase in the number of moles of the working medium, thereby increasing the working medium pressure and the temperature change amount is small or constant, and replacing the combustion chamber of the conventional internal combustion engine The working cycle mode for increasing the pressure of the gas working fluid is specifically: For the piston engine, the gas pressure and temperature before combustion of the combustion chamber exceed the conventional piston internal combustion engine by increasing the compression ratio of the piston internal combustion engine. Gas pressure and temperature, controlling the amount of fuel and expansion agent entering the combustion chamber and the temperature at which the expansion agent enters the combustion chamber so that as much of the heat released by the combustion of the fuel is absorbed by the expansion agent, greatly increasing combustion Indoor pressure, while temperature changes are small or constant; for turbines, Adjusting the volumetric flow ratio of the compressor and the turbine such that the gas pressure and temperature before combustion of the turbine combustor exceeds the gas pressure and temperature of the conventional turbine combustion chamber, controlling the amount of fuel and expansion agent entering the combustion chamber, and the expansion agent entering the The temperature at the combustion chamber causes the heat released by the combustion of as much fuel as possible to be absorbed by the expansion agent, greatly increasing the pressure in the combustion chamber, and the amount of temperature change is small or constant; thereby greatly improving the efficiency and environmental protection of the engine. Sex.

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

In the present invention, the so-called piston engine combustion chamber may be a four-stroke piston engine combustion chamber, or a two-stroke piston engine combustion chamber, a combustion chamber of the rotor piston engine, or may be inhaled. The compression stroke and the work exhaust stroke are combustion chambers of a piston engine composed of two sets of mechanisms.

In the present invention, the so-called low temperature heat source can also be referred to as a cold source, and is equivalent to a so-called cold source in some literatures.

In the present invention, the expansion agent heat absorption heat exchanger may 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, The temperature of the compressed gas is lowered.

In the present invention, the state of the working medium (temperature and pressure) under the high-temperature heat source refers to the state of the working fluid after the endothermic heat source is completed, that is, the temperature and pressure of the working medium; the so-called high-temperature heat source The state may be consistent with the state of the high temperature heat source or with the state of the high temperature heat source.

In the small temperature rise and low entropy co-firing engine disclosed in the present invention, the term "heat is absorbed by the expansion agent" means that the heat is used to heat the temperature expansion agent, the gasification expansion agent, the critical expansion agent and/or the superheat expansion agent; The critically-expanded expansion agent refers to a state in which the expansion agent is in a critical state, a supercritical state, an ultra-supercritical state, or a higher temperature and pressure state.

In the present invention, the so-called "small or constant temperature change" means that all or nearly all of the heat of the fuel is absorbed by the expansion agent, and the temperature of the gas in the combustion chamber is small or constant before and after combustion, and There is almost no excess temperature (the so-called excess temperature refers to the relationship of adiabatic expansion in order to reach a certain end state, the actual temperature of the working medium is higher than the theoretically required temperature in the starting state); according to this working mode, in the present invention In the disclosed small temperature rise and low entropy co-firing engine, after introducing fuel and expansion agent into a gas working medium compressed by a compression stroke (process) and generating a combustion chemical reaction, the gas pressure in the combustion chamber is close to , equal to or greater than the pressure value determined by the formula p = cr^

(where C is constant and the initial state of the working fluid and thermodynamic properties, P is the working fluid pressure after combustion, Γ is the working temperature after combustion, is the adiabatic compression index, and the adiabatic compression index of air In the case of 1.4), in other words, the relationship between the temperature and the pressure of the gas in the combustion chamber basically follows the relationship between the temperature and the pressure determined by the formula P = C7^i starting from the state at the beginning of the compression stroke. , or the pressure is greater than the pressure value determined by the formula p = cr^; this makes the temperature of the working fluid after the expansion work much lower than the exhaust temperature of the conventional internal combustion engine. Obviously, the degree of improvement of the efficiency is considerable.

In the small temperature rise and low entropy co-firing engine disclosed in the present invention, any two of the fuel, the oxidant (for example, compressed air or compressed oxygen-containing gas) and the expansion agent may be mixed beforehand and the third Mixed The combustion reaction may first occur between the oxidant and the fuel and then mixed with the expansion agent, or may occur when the three are mixed or after the three are mixed; a core combustion zone may be established in the combustion chamber, and the oxidant in the core combustion zone The fuel is directly combusted and then mixed with the expansion agent between the combustion core zone and the combustion chamber wall, so that the excessive temperature flame formed by direct combustion of the fuel and the oxidant can be separated from the combustion chamber wall by the expansion agent, thereby reducing the combustion chamber wall. The heat load.

The so-called expansion agent of the present invention refers to a working medium which does not participate in the combustion chemical reaction and absorbs heat and adjusts the number of moles of working medium and expands work. It may be a gas, a liquid, a critical substance, a gas liquefaction, such as water vapor, Carbon dioxide, helium, nitrogen, liquid carbon dioxide, liquid helium, liquid nitrogen or liquefied air.

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

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

The so-called gas-absorbing low-grade heat source heater of the present invention refers to a device for heating a gas working medium by using a low-grade heat source (such as exhaust heat, exhaust heat of a cooling system, etc.) as a heat source; the so-called gas heat-dissipating environment cooler means A device for cooling a gaseous working fluid by discharging heat of a gaseous working fluid into the environment; a so-called combustion control device means controlling the amount of fuel, the amount of expanding agent, and/or the amount of oxidizing agent, and the fuel, the expanding agent, and the oxidizing agent. The introduced phase controls the device for combustion; the so-called gas-liquid separator refers to a device that separates gas and liquid.

The so-called introduction control mechanism of the present invention refers to a system for supplying 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 thermodynamic system, the system including the valve, the pump and/or Or sensor, etc.

The so-called expander heat absorbing heat exchanger in the present invention refers to an expansion agent capable of absorbing heat by using ambient heat or the small temperature rise and low entropy co-firing engine residual heat (such as exhaust heat and residual heat of the cooling system) as a heat source. Heat exchanger.

The so-called environmentally friendly temperature limit in the present invention refers to the highest temperature that does not produce harmful pollutants, such as not producing The environmental temperature limit for raw nitrogen oxides is 1800K, etc.; the so-called material temperature limit refers to the maximum temperature that the material can withstand.

The expansion agent of the present invention can be recycled in the small temperature rise low entropy co-firing engine. The so-called fuel in the present invention refers to a substance which can undergo a vigorous redox reaction with oxygen in the sense of chemical combustion, and may be a gas, a liquid or a solid, and mainly includes gasoline, diesel, natural gas, hydrogen and gas, and fluidized fuel, Liquefied fuel or powdered solid fuel, etc. The so-called liquefied fuel refers to a fuel that is liquefied and is in a gaseous state at a normal temperature and a normal pressure state.

The small temperature rising low entropy co-firing engine disclosed by the invention can use hydrocarbon or carbon oxyhydroxide as fuel, for example, ethanol or ethanol aqueous solution, and use ethanol aqueous solution instead of original fuel and expansion agent, not only can prevent freezing, but also It is possible to replace the original fuel storage tank and the expansion agent storage tank with only one aqueous ethanol storage tank, and to change the ratio of the fuel and the expansion agent by adjusting the concentration of the aqueous ethanol solution. When necessary, a mixed solution of ethanol, water and hydrocarbon may be used in place of the fuel and expansion agent of the present invention, and the concentration thereof may be adjusted to meet the requirements of the small temperature rise and low entropy co-firing engine disclosed in the present invention. In the small temperature rising low entropy co-firing engine disclosed in the present invention, an aqueous hydrogen peroxide solution can be used instead of the oxidizing agent and the expanding agent, and the ratio of the oxidizing agent and the expanding agent can be adjusted by adjusting the concentration of the aqueous hydrogen peroxide solution, and a peroxidation can be used. The aqueous hydrogen storage tank replaces the oxidant storage tank and the expansion agent storage tank.

In the present invention, in some technical solutions, the working fluid temperature can reach several thousand degrees or even higher, and the working fluid pressure can reach several hundred atmospheres or even higher.

In the small temperature rise and low entropy co-firing engine disclosed in the present invention, by adjusting the gas temperature and pressure of the combustion chamber, the temperature and pressure of the working fluid after the expansion work can be adjusted to expand the work to the set expansion pressure. At the time, the working temperature drops to a relatively low level, such as near ambient temperature, below ambient temperature, or substantially below ambient temperature.

The term "engine" as used in the present invention refers to a mechanism that uses gas to drive a turbine to work, such as a gas turbine or a jet engine; the piston engine includes a piston type internal combustion engine, a rotor piston type internal combustion engine, and the like.

In the small temperature rise and low entropy co-firing engine disclosed in the present invention, since the temperature in the combustion chamber can be set below the nitrogen oxide formation temperature, even if liquid nitrogen is used as the expansion agent, nitrogen oxides are not generated (N0J). Liquid nitrogen can be introduced into the combustion chamber in liquid form, or can be introduced into the combustion chamber in a critical state, or can be introduced into the combustion chamber in the form of an ultra-high pressure gas. The so-called ultra-high pressure means that the pressure of the gas is not only high. The gas pressure in the combustion chamber when liquid nitrogen is introduced is higher than the pressure value determined by the formula P = C7^i; in the small temperature rise and low entropy co-firing engine disclosed in the present invention, liquid nitrogen is gas When the form is introduced into the combustion chamber, the pressure of nitrogen gas is higher than the gas pressure in the combustion chamber by 2 MPa, 3 MPa, 4 MPa, 5 MPa, 6 MPa, 7 MPa, 8 MPa, 9 MPa, 10 MPa 1 1 MPa, 1 2 MPa, 13 MPa, 14 MPa, 1 5MPa, 16 6MPa, 17 7MPa, 1 8 Pa 1 9MPa or 20MPa high.

The beneficial effects of the present invention are as follows:

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

DRAWINGS

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

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

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

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

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

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

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

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

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

Figure 10 is a schematic view showing the structure of a tenth embodiment of the present invention.

Figure 1 is a schematic diagram of the q>0 cycle of the present invention;

Figure 12 is a schematic diagram of the q=0 cycle of the present invention;

Figure 13 is a schematic diagram of the q<0 cycle of the present invention;

Figure 14 shows a schematic diagram of the operation of a heat engine with different compression forces;

Figure 15 is a schematic view showing the relationship between the pressure and temperature of the gaseous working fluid after combustion in accordance with the temperature and pressure of the adiabatic compression process;

Figure 16 is a schematic view showing the pressure value of the gas working fluid after combustion is greater than the pressure value determined by the relationship between the pressure and temperature of the adiabatic compression process;

Figure 17 shows the pressure-temperature relationship of the vertical axis as the pressure-slope horizontal axis as the temperature coordinate; Figure 18 is a schematic diagram showing the temperature-pressure relationship of the adiabatic expansion work at different points E; Figure 19 is a comparison diagram of the cycle of the cycle of the small temperature rise and low entropy co-firing engine disclosed in the present invention and the cycle of the conventional internal combustion engine;

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

In the picture:

1 combustion chamber, 2 expansion agent source, 3 fuel source, 5 oxidant source, 6 compressor, 7 power turbine, 9 gas communication passage, 10 inlet, 1 1 exhaust, 1 2 exhaust discharge, 13 rows Air release control valve, 16 oxidant introduction control mechanism, 18 gas exothermic environment cooler, 17 7 gas absorption 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 absorption heat exchanger, 3020 combustion control device, 1 100 gas liquid separator.

detailed description

Example 1

a small temperature rise and low entropy co-firing engine as shown in FIG. 1 , comprising a combustion chamber, an expansion agent source 2 and a fuel source 3, the combustion chamber being 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 4 MPa, the fuel source 3 is in communication with the combustion chamber via a fuel introduction control mechanism 30, and the expansion agent source 2 is communicated with the combustion chamber via an expansion agent introduction control mechanism 20, the fuel introduction control 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 has been introduced into the combustion chamber. Absorbing agent in the expansion agent source 2 in the combustion chamber; adjusting the compression ratio of the engine in the structure in which the combustion chamber is set to the piston engine combustion chamber 101 to be compressed when the compression stroke is completed The pressure of the gas is greater than the gas pressure at the end of the compression stroke of the conventional piston engine, and the temperature of the gas working fluid that is about to start work is adjusted to below 2000K, and the gas working fluid that is about to start work is adjusted. 1 5MPa or more to force the gas will begin work as working fluid temperature and pressure in line with the adiabatic relation classes. Adjusting a compression ratio of the engine in a configuration in which the combustion chamber is configured as the piston engine combustion chamber 101 such that a pressure of a compressed gas when the compression stroke is completed is greater than or equal to 4 MPa; In the structure of the piston engine combustion chamber 101, the compression ratio of the engine is adjusted such that the compression stroke is completed, and the temperature of the compressed gas before combustion is in the range of plus or minus 200K of 1 800 K, the fuel introduction control mechanism 30 and the The expansion agent introduction control mechanism 20 is subjected to the combustion control device 3020 Controlling all or nearly all of the heat generated by combustion of the fuel within the fuel source 3 entering the combustion chamber is absorbed by the expansion agent in the expansion agent source 2 that has been introduced into the combustion chamber After the combustion of the combustion chamber, the highest temperature in the combustion chamber is below the harmful compound NOx generation temperature to improve the environmental protection of the engine;

In the configuration in which the combustion chamber is set to the piston engine combustion chamber 101, the compression ratio of the engine is adjusted so that the temperature of the compressed gas before the combustion is completed is 1000 K or more.

5 MPa, 6.5 MPa, 7.5 MPa, 7.5 MPa, MPa, MPa, MPa, MPa, MPa, MPa, MPa, MPa, MPa, MPa, MPa, MPa, MPa, MPa, MPa, MPa, MPa, MPa, MPa, MPa, MPa, MPa, MPa, MPa, MPa 8MPa, 8. 5MPa, 9MPa, 9, 5MPa, 10 Pa 10. 5MPa, 1 1 MPa, 1 1 · 5Pa, 12 Pa 12. 5MPa, 13MPa, 1 3. 5MPa, 14MPa, 14. 5MPa, 15MPa, 15. 5MPa, 16 MPa, 6.5 MPa, 17 MPa, 1.7 MPa, 18 MPa, 18. 5 MPa, 1 9 MPa, 19. 5 MPa, 20 MPa, 22 MPa, 24 MPa, 26 MPa, 28 MPa, 30 MPa, 32 MPa, 34 MPa, 36 MPa, 38 MPa Or greater than or equal to 40 MPa;

The fuel introduction control mechanism 30 and the expansion agent introduction control mechanism 20 are controlled by the combustion control device 3020 to control 6% or more and 7% or more of the heat generated by combustion of the fuel 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, more than 1%, 18% or more, and 9% Above, 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% or more, 50% or more, 55% or more, 60% or more, 65% or more, 70% or more, 75% or more, 80% or more, 85% or more, 90% or more, 95% or more, or 100%, which are introduced into the combustion chamber in the combustion chamber Absorbing agent in the expander source 2 is absorbed;

Adjusting the compression ratio of the engine to complete the compression stroke. The temperature of the compressed gas before combustion is 1300K or more, 1500K or more, 1800K or more, 2000K or more, 2300K or more, 2500K or more, 2800K or more, 3000K or more, 3200K or more, or 3500K or more. .

Example 2

a small temperature rise and low entropy co-firing engine as shown in FIG. 2, which differs from Embodiment 1 in that: an expander heat absorption heat exchanger 1 020 is provided between the combustion chamber and the expansion agent source 2, 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 small temperature rise and low entropy co-firing engine shown in FIG. 3 is different from the embodiment 1 in that: the heat source of the expander heat absorption heat exchanger 1020 is set as the waste heat of the small temperature rise and low entropy co-firing engine. . The expansion agent in the expansion agent source 2 enters the combustion chamber after the endothermic state in the expansion agent heat absorption heat exchanger 1020 reaches a critical state, a supercritical state, or an ultra-supercritical state.

In a 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 to be the same ethanol aqueous solution tank. .

Example 4

The small temperature rise and low entropy co-firing engine shown in FIG. 4 is different from the embodiment 1 in that: the small temperature rise and low entropy co-firing engine further includes an oxidant source 5 and a gas communication passage 9, the gas communication passage 9 an intake passage 10 and an exhaust passage 1 connected to the combustion chamber, an exhaust gas discharge port 12 is disposed on the exhaust passage 1 1 , and an exhaust gas discharge control valve 13 is disposed at the exhaust gas discharge port 12 The oxidant source 5 is communicated with the combustion chamber via the oxidant introduction control mechanism 16 and directly communicated with the combustion chamber via the oxidant introduction control mechanism 16. The oxidant introduction control mechanism 16. The fuel introduction control mechanism 30 and the expansion agent introduction control mechanism 20 are controlled by a combustion control device 3020.

Example 5

The small temperature rise and low entropy co-firing engine shown in Fig. 5 differs from the embodiment 4 in that a gas-absorbing low-grade heat source heater 17 is provided on the gas communication passage 9.

Example 6

a small temperature rise and low entropy co-firing engine as shown in FIG. 6, which differs from Embodiment 4 in that: on the gas communication passage and/or on the intake passage and/or on the exhaust passage Gas exothermic environment cooler.

Example 7

a small temperature rise and low entropy co-firing engine as shown in FIG. 7 , comprising a combustion chamber, a swelling agent source 2 and a fuel source 3, which is different from Embodiment 1 in that: the combustion chamber is set as a turbine combustion chamber 102, The pressure capacity of the turbine combustion chamber 102 is greater than or equal to 2 MPa, and the flow rate of the compressor 6 and the power turbine 7 of the turbine is adjusted such that the pressure in the turbine combustion chamber 102 is greater than or equal to 2 MPa; Adjusting the volumetric flow ratio of the compressor 6 and the power turbine 7 of the turbine in the structure of the combustion chamber 102 The temperature of the gas before combustion in the turbine combustion chamber 102 is 1000 K or more.

5MPa,5MPa,5MPa,5. 5MPa,5MPa,5MPa,5MPa,5MPa,5MPa,5MPa,5MPa,5MPa,5MPa,5MPa,5MPa,5MPa,5MPa,5MPa,5MPa,5MPa,5MPa,5MPa,5MPa,5MPa,5MPa,5MPa,5MPa,5MPa,5MPa,5MPa,5MPa,5MPa,5MPa,5MPa,5MPa 5MPa, 6MPa, 6. 5MPa, 7MPa, 7. 5MPa, 8MPa, 8. 5MPa, 9MPa, 9. 5MPa, 10MPa, 10. 5MPa, 1 1 MPa, 1 1 . 5Pa, 12MPa, 12. 5MPa, 13MPa, 13 5MPa, 14MPa, 14. 5MPa, 1 5MPa, 15.5MPa, 16 6MPa, 16. 5MPa 1 7MPa, 1 7. 5 Pa 18MPa, 18. 5MPa, 1 9MPa, 1 9. 5MPa, 20MPa, 22MPa, 24MPa 26MPa, 28MPa, 30MPa, 32MPa, 34MPa, 36MPa, 38MPa or 40MPa or more; adjusting the volumetric flow ratio of the compressor 6 and the power turbine 7 of the turbine to make the temperature of the gas before combustion in the turbine combustion chamber 102 at 1300K Above, 1500K or more, 1800K or more, 2000K or more, 2300K or more, 2500K or more, 2800K or more, 3000K or more, 3200K or more, or 3500K or more.

Example 8

The small temperature rise and low entropy co-firing engine shown in Fig. 8 differs from the embodiment 7 in that: the expander source 2 is replaced by an oxidant source 5, and the oxidant source 5 is introduced into the control unit 16 via the oxidant. The turbine combustion chamber 102 is in communication.

Example 9

The small temperature rise and low entropy co-firing engine shown in FIG. 9 is different from the embodiment 5 in that: the small temperature rise and low entropy co-firing engine further includes an oxidant source 5, a gas communication passage 9, and a gas absorption low grade. a heat source heater 17 that communicates with the turbine combustion chamber 102 via an oxidant introduction control mechanism 16 that communicates with the intake passage 10 of the compressor 6 and the power turbine 7 The exhaust passage 1 1 is provided with an exhaust gas outlet 12, and an exhaust gas discharge valve 13 is provided at the exhaust gas discharge port 12, and the oxidant introduction control mechanism 16 and the fuel introduction The control mechanism 30, the expansion agent introduction control mechanism 20, and the exhaust gas release valve 13 are controlled by the combustion control device 3020.

Example 10

The small temperature rise and low entropy co-firing engine shown in FIG. 10 is different from the embodiment 1 in that: a gas-liquid separator 1 100 is disposed at the exhaust passage 11 of the combustion chamber, and the expander source 2 The liquid outlet of the gas-liquid separator 1 100 is used, and the liquid in the gas-liquid separator 1 100 is used as the expansion agent.

It is apparent that the present invention is not limited to the above embodiments, and is disclosed according to the well-known technology and the present invention in the art. The technical solutions can be deduced or associated with many variants, all of which are also considered to be the scope of protection of the present invention.

Claims

Rights request

A small temperature rising low entropy co-firing engine comprising a combustion chamber, a swelling agent source (2) and a fuel source (3), characterized in that: the fuel source (3) is controlled by a fuel introduction control mechanism (30) The combustion chamber is in communication, the expansion agent source (2) is in communication with the combustion chamber via a expansion agent introduction control mechanism (20), the fuel introduction control mechanism (30) and the expansion agent introduction control mechanism (20) Controlled by a combustion control device (3020); the combustion chamber is set as a piston engine combustion chamber (101), the piston engine combustion chamber (101) has a pressure bearing capacity of 4 MPa or more, or the combustion chamber is set to be a turbine The combustion chamber (102), the turbine combustion chamber (102) has a pressure bearing capacity of 2 MPa or more.

2. The small temperature rising low entropy co-firing engine according to claim 1, wherein: an expansion agent heat absorption heat exchanger (1020) is disposed between the combustion chamber and the expansion agent source (2), Expansion agent source

The expansion agent in (2) absorbs heat in the expansion agent heat absorption heat exchanger (1020).

3. The low temperature rise and low entropy co-firing engine according to claim 2, wherein: the heat source of said expander heat absorbing heat exchanger (1020) is set to a residual heat of said small temperature rise and low entropy co-firing engine.

4. The low temperature rise and low entropy co-firing engine according to claim 2, wherein: the expansion agent in the expansion agent source (2) absorbs heat in the expansion agent heat absorption heat exchanger (1020) The critical state, supercritical state or ultra-supercritical state is then entered into the combustion chamber.

5. The low temperature rise and low entropy co-firing engine according to claim 1, wherein: said small temperature rise and low entropy co-firing engine further comprises an oxidant source (5) and a gas communication passage (9), said gas communication a passage (9) connecting the intake passage (10) and the exhaust passage (1 1 ) of the combustion chamber, and an exhaust gas discharge port (12) is disposed on the exhaust passage (1 1 ) at the exhaust An exhaust gas discharge control valve (13) is disposed at the discharge port (12), and the oxidant source (5) is connected to the combustion chamber via the oxidant introduction control mechanism (16) via the oxidant inlet (10) or directly The oxidant introduction control mechanism (16) is in communication with the combustion chamber, and the oxidant introduction control mechanism (16), the fuel introduction control mechanism (30), and the expansion agent introduction control mechanism (20) are subjected to a combustion control device. (3020) Control.

6. The small temperature rise and low entropy co-firing engine according to claim 5, characterized in that: a gas heat absorbing low grade heat source heater (17) is arranged on the gas communication passage (9).

7. The low temperature rise and low entropy co-firing engine according to claim 5, characterized by: on said gas communication passage (9) and/or on said intake passage (10) and/or in said Exhaust duct (1 1 ) Gas exothermic environment cooler (18).

8. The low temperature rise and low enthalpy co-firing engine according to claim 1, wherein: a gas-liquid separator (1 100) is disposed at an exhaust passage (1 1 ) of said combustion chamber, said expansion agent source (2) A liquid outlet of the gas-liquid separator (1 100) is used, and a liquid in the gas-liquid separator (1 100) is used as the expansion agent.

9. The low temperature rise and low entropy co-firing engine according to claim 1, wherein: the expansion agent in the expansion agent source (2) is a gas liquefaction.

10. The low temperature rise and low entropy co-firing engine according to claim 1, wherein: the fuel in the fuel source (3) is set to ethanol, and the expansion agent in the expansion agent source (2) is set to water. The fuel source (3) and the expansion agent source (2) are set to be the same aqueous ethanol storage tank.

A small temperature rise and low entropy co-firing engine according to claim 1, wherein: said combustion chamber is set as an adiabatic combustion chamber.

12. A method of improving the efficiency and environmental friendliness of a small temperature rise and low entropy co-firing engine according to any one of claims 1 to 11, characterized in that: the combustion chamber is set as the piston engine combustion chamber

The structure of (101) adjusts the compression ratio of the engine such that the compression stroke is completed. The temperature of the compressed gas before combustion is in the range of plus or minus 200K of 1800K, and the combustion chamber is set to the turbine combustion chamber (102). The flow rate of the compressor (6) and the power turbine (7) is adjusted such that the temperature of the gas before combustion in the turbine combustion chamber (102) is within a range of plus or minus 200 K of 1800 K; adjustment is introduced into the combustion chamber. The amount of the expansion agent in the expansion agent source (2) and the amount of fuel introduced into the fuel source (3) in the combustion chamber are introduced into the fuel source (3) of the combustion chamber All or nearly all of the heat generated by the combustion of the fuel is absorbed in the combustion chamber by the expansion agent introduced into the expansion agent source (2) in the combustion chamber; adjusting the combustion of the fuel after combustion in the combustion chamber The highest gas temperature in the room is below the harmful compound NOx generation temperature to improve the environmental friendliness of the engine.

13. A method of improving the efficiency and environmental friendliness of a small temperature rise and low entropy co-combustion engine according to any one of claims 1 to 11, characterized in that: adjusting said expansion agent source introduced into said combustion chamber (2) The amount of the expanding agent and the amount of fuel introduced into the fuel source (3) in the combustion chamber to cause heat generated by combustion of the fuel introduced into the fuel source (3) of the combustion chamber All or nearly all of the expansion agent in the combustion chamber is introduced into the combustion chamber source (2) in the combustion chamber The temperature in the combustion chamber is substantially maintained at a constant pressure before and after combustion of the combustion chamber to increase the efficiency of the engine.

A method for improving the efficiency and environmental friendliness of a small temperature rise and low entropy co-firing engine according to any one of claims 1 to 11, characterized in that: the combustion chamber is set as the piston engine combustion chamber

In the structure of (101), the compression ratio of the engine is adjusted such that the compression stroke is completed, and the temperature of the compressed gas before combustion is 1000 K or more, and the compression is adjusted in the structure in which the combustion chamber is set to the turbine combustion chamber (102). The volumetric flow ratio of the machine (6) and the power turbine (7) is such that the temperature of the gas before combustion in the turbine combustion chamber (102) is above 1000K.

15. A method of improving the efficiency and environmental friendliness of a small temperature rise and low entropy co-combustion engine according to any one of claims 1 to 11, characterized in that: the expansion agent source introduced into the combustion chamber is adjusted (2) The amount of the expanding agent and the amount of fuel introduced into the fuel source (3) in the combustion chamber to cause heat generated by combustion of the fuel introduced into the fuel source (3) of the combustion chamber More than 5% of the expansion agent in the expansion agent source (2) introduced into the combustion chamber is absorbed in the combustion chamber.

16. A method for improving the efficiency and environmental friendliness of a small temperature rise and low entropy co-combustion engine according to any one of claims 1 to 11, characterized in that the temperature of the gas working medium to be started to work is adjusted to below 2000 K. Adjust the pressure of the gas working fluid that is about to start work to 15 MPa or more, so that the temperature and pressure of the gas working fluid that is about to start work are in line with the adiabatic relationship.