WO2012034354A1

WO2012034354A1 - Low entropy explosion-exhaust engine of gas charging type using mixed fuel

Info

Publication number: WO2012034354A1
Application number: PCT/CN2011/001516
Authority: WO
Inventors: 靳北彪
Original assignee: Jin Beibiao
Priority date: 2010-09-13
Filing date: 2011-09-07
Publication date: 2012-03-22

Abstract

A low entropy explosion-exhaust engine of gas charging type using mixed fuel comprises a gas compressor (2) and an explosion-exhaust engine (3), wherein a gas inlet of the gas compressor (2) is provided as an inlet for low pressure oxygen-containing gas, and a compressed gas outlet of the gas compressor (2) is in communication with a combustion chamber gas charging port (301) of a combustion chamber (300) of the explosion-exhaust engine. The pressure sustaining capacity at the compressed gas outlet of the gas compressor is higher than 1 MPa, and there is no timing relation between the gas compressor and the explosion-exhaust engine. Such a low entropy explosion-exhaust engine of gas charging type using mixed fuel improves the energy-saving ability of an engine and makes it more environmentally friendly.

Description

Low entropy co-firing gas explosion engine

Technical field

This invention relates to the field of engines, and more particularly to a pneumatic blast engine.

Background technique

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

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

Summary of the invention

In a thermodynamic system, if the combustion chamber is an adiabatic combustion chamber, the fuel will transfer the heat generated by the combustion to the product heated fluid and the in-phase heated fluid during combustion. If the combustion chamber is a non-adiabatic combustion chamber, the fuel will be burned when burned. Heat transfer to product heated fluid, phase heated fluid, and external heat Fluid. The so-called product heated fluid refers to the product of combustion chemical reaction (for example, carbon dioxide and water produced by combustion in a thermodynamic system burning hydrocarbons); the so-called in-phase heated fluid means that it is in the same phase as the combustion chemical reaction but does not participate. a chemically combusted fluid (for example, nitrogen in a thermodynamic system using air as an oxidant and carbon dioxide inherent in air); the so-called externally heated fluid refers to heat generated outside the combustion chemical reaction phase and subjected to combustion chemical reactions. The fluid (for example, the water vapor system of the external combustion engine and the cooling system of the internal combustion engine). According to the working principle of the external combustion cycle thermodynamic system and the internal combustion cycle thermodynamic system, it is easy to see that in the external combustion cycle thermodynamic system, only the external heated fluid participates in the work, while the product heated fluid and the phase heated fluid do not participate. Work (see Figure 28), although the product heated fluid and the internal heated fluid are thermally expanded during the combustion process but do not work externally, but the process of entropy increase by heating is arbitrarily heated, so there are quite a lot in the external combustion cycle system. The heat does not pass through the work channel, that is, it does not participate in the work cycle; in the internal combustion cycle system, only the heated fluid and the heated fluid in the phase participate in the work, while the external heated fluid does not participate in the work (see Figure 29). For example, a cooling system of a conventional internal combustion thermodynamic system (internal combustion engine, gas turbine, etc.) (for example, a cylinder liner cooling system of an internal combustion engine) causes a large amount of heat to be externally operated, and an entropy increase process is performed, thereby generating a huge waste of heat energy. Therefore, in the internal combustion cycle system, there is also a considerable amount of heat that does not pass through the work channel, that is, it does not participate in the work cycle. In short, whether in the external combustion cycle thermal power system or in the internal combustion cycle thermal power system, a large amount of heat is discharged into the environment without being involved in work, and is wasted.

In addition, the special heat transfer mode of the external combustion engine requires a large heat transfer temperature difference to ensure the heat transfer efficiency, due to the limitation of the performance of the heat transfer wall material of the working fluid generator (ie boiler), the value of the working medium is The temperature of the high-temperature heat source is low, and the value of the modern state-of-the-art external combustion fluid generator is only about 60 (TC) (such as steam in the boiler of the ultra-supercritical generator set), so even with the appropriate working fluid ₂ value of the external combustion cycle (i.e., the low-temperature heat source temperature) is reduced to several tens of degrees (i.e. about 330 Kelvin), but can not increase the value of 7, so the external combustion thermal efficiency of the cycle remains relatively low. in the conventional internal combustion cycle, both Contains compression process or compression stroke (such as gas turbine gas pressure process, conventional internal combustion engine four-stroke cycle or two; medium-cycle cycle), but due to the limitation of the working mode of the traditional internal combustion thermodynamic system, the gas pressure at the end of the compression stroke It is impossible to reach a very high level, otherwise the temperature after combustion will be too high, not only will cause a large amount of NOx to cause environmental pollution, but also the material can not withstand due to excessive temperature. Therefore, the pressure in the combustion chamber of the conventional thermodynamic system is difficult to reach a high level (generally the piston internal combustion engine only 1 5MPa or so, and the turbine is only about 3MPa). Due to the existence of equations during the internal combustion thermodynamic cycle

Where 7; and P, respectively, the Kelvin temperature and pressure of the high temperature heat source, Γ ₂ and Ρ ₂ are respectively

The Kelvin temperature and pressure of the low-temperature heat source is the adiabatic compression index, and the adiabatic compression index of the air is 1.4, so there is a basic approximation of the pressure ratio equal to the temperature ratio of about 3.5. In order to reduce the enthalpy ₂ (ie, the exhaust gas temperature) and increase the heat transfer efficiency, it is necessary to increase the pressure of the gas working after combustion to a pressure of several tens of MPa or higher. In order to achieve the gas pressure after the combustion of the original working fluid in the combustion chamber reaches such a high level, the pressure of the working fluid before combustion (ie, the original working fluid) must be at a relatively high level, preferably at a high pressure and low temperature ( Because the higher the pressure of the original working fluid charged into the combustion chamber, the lower the temperature, the lower the temperature after the working fluid expands and the higher the efficiency. In the conventional internal combustion thermal power system, it is difficult to achieve the working medium (ie, the original working medium) before combustion in the combustion chamber. For this reason, the Γ _{2 is} generally high, reaching about 800 ° C. Therefore, in the traditional internal combustion cycle system, in order to improve efficiency, the increase is mainly 7, however, the increase of nitrogen oxides N0x is generated, which causes serious pollution to the environment, so the efficiency of the internal combustion cycle cannot be achieved. Higher level.

People ignore the state parameters of the working medium (that is, the working fluid that is about to start to expand work) in the high-temperature heat source state during the actual thermodynamic cycle and the state parameters of the working medium in the low-temperature heat source state (that is, the working medium when the expansion work is completed). The intrinsic correlation is only one-sidedly considered that the temperature ₂ of the working medium in the low temperature heat source state is the ambient temperature. Therefore, there is no way to adjust the Γ ₂ , and the efficiency can only be improved by increasing the temperature of the working medium under the high temperature heat source state; , in fact, a one-sided increase of 7; will lead to an increase of 7 ^ ₂ , and ultimately affect the improvement of engine efficiency, the inventors believe that the value of the temperature ₂ of the working medium in the low-temperature heat source state is the working medium of the high-temperature heat source state The state parameters are determined. Therefore, in order to improve the efficiency of the engine, it is necessary to reasonably select the state parameters of the working medium in the high temperature heat source state, that is, the pressure and temperature of the working medium in the high temperature heat source state.

It can be seen that it is impossible to reach a higher level in the external combustion cycle system, and it is impossible for the enthalpy ₂ in the internal combustion cycle system to reach a lower level. This means that the thermal power conversion efficiency of the conventional external combustion cycle thermodynamic system and the internal combustion cycle thermodynamic system cannot reach a high level.

If we conduct a more in-depth analysis, it is not difficult to see that the real driving force of the work process is pressure. It is not temperature. Increasing temperature is only a means of generating pressure. If the working fluid pressure in a high-temperature heat source is not high enough, no matter how much heat energy is in the system, it is impossible to realistically produce the due work (due to the fact that in the low-temperature heat source state in reality) The mass pressure cannot be too low, generally higher than atmospheric pressure, unable to achieve infinite expansion

1-^

Bulging), according to efficiency; 7 = 1 - and /^ are the working medium pressure under high temperature heat source and the working medium pressure of low temperature heat source respectively, which is the adiabatic compression index, and the adiabatic compression index of air is 1. 4) Increasing the working fluid pressure under high temperature heat source is the only fundamental way to improve the efficiency and power density of the heat engine. The amount of heat added to the working medium and the way of adding it must be aimed at increasing the working medium pressure under the high temperature heat source state. It is not a simple heating method to increase the temperature of the working fluid to achieve the purpose of boosting. Otherwise, the excessive temperature can only affect the life of the heat engine, put forward higher requirements on the material and cause greater pollution, and there is no harm. .

The high temperature and high temperature of the high temperature heat source can achieve both high efficiency and low pollution, which is impossible in traditional internal combustion engines, because the temperature rise during compression is caused by the adiabatic compression process. The relationship between temperature and pressure is /> = «Γ^ is a constant), and the temperature rise caused by the heat released by the combustion reaction has a limit effect on the pressure increase (the best effect of heating up to achieve the purpose of boosting) is The relationship between temperature and pressure is formed by the heat generated by the constant volume chemical reaction = (b is a constant, that is, the pressure and temperature are linear). In the conventional internal combustion engine, the two temperature rise processes are directly superimposed. Adiabatic expansion works externally, which inevitably leads to over-temperature, which is the cause of low efficiency and high pollution of conventional internal combustion engines. In traditional external combustion engines, it is difficult to make the high-temperature heat source due to material limitations. The working temperature of the working fluid has an essential improvement (the working fluid pressure of the traditional external combustion engine is determined by the working medium temperature, if the working temperature is not high enough, the pressure It is impossible to reach a higher level, nor can it pressurize the working fluid, otherwise it will produce a phase change of the working fluid (except for the heat engine). At present, the steam temperature generated by the most advanced ultra-supercritical generator boiler is only 630. Around °C, the pressure is around 300 atmospheres, so the efficiency of the traditional external combustion engine can not be improved substantially (if the temperature of the working fluid of the traditional external combustion engine can be increased to a few hundred degrees Celsius, the pressure is also higher. At the level, the efficiency of the external combustion engine will be substantially improved).

From the above two aspects, it can be concluded that whether it is an external combustion cycle system or an internal combustion cycle system, In the process of successful heat conversion, there are inherent deficiencies, which constitute the low thermal efficiency and high pollution status of traditional engines. That is, the best conventional engines use only about one-third of the fuel's chemical energy, while the other two-thirds are discharged into the environment as waste heat. Moreover, almost all conventional internal combustion engines use natural air as an oxidant. Because natural air contains a large amount of nitrogen, in the circulation mode of a conventional internal combustion engine, pollutants such as NOx are inevitably generated, which seriously pollutes the environment.

In summary, the circulation mode of the external combustion thermodynamic system and the internal combustion thermodynamic system severely limits the efficiency of thermal power conversion and causes unavoidable pollution emission problems.

In the past few decades, in order to improve the efficiency and environmental protection of the engine, the world, especially the developed countries, have carried out large-scale research and development work, but the results are far from satisfying people's requirements and will always be solved. There is no inherent deficiency in internal combustion engines and external combustion engines. This is like the era of cold weapons. No matter how well human beings are crafted, if there is no gunpowder, weapons can't make great progress anyway. In other words, in order to fundamentally solve the problem of engine efficiency and pollution, it is necessary to fundamentally get rid of the constraints of the external combustion cycle and the internal combustion cycle, and re-establish a new and better cycle mode after the external combustion cycle and the internal combustion cycle. Under the guidance of this new cycle, the third generation engine with high efficiency, low pollution or zero pollution (the first generation is an external combustion engine and the second generation is an internal combustion engine) is to fundamentally improve the efficiency of the engine. , the only option to reduce engine emissions.

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 immediately after the combustion explosion is completed, at this time the working fluid The temperature and pressure are at the highest state throughout the cycle. It consists of two processes: The first process is the adiabatic compression of the gas by the piston (actually approximately adiabatic compression). The pressure is pressurized and warmed according to the relationship of = C, r^ (where, is a constant) (see the curve shown by 0-A in Fig. 26); the second process is to inject fuel into the gas by combustion chemistry The heat generated by the reaction increases the temperature and pressure of the gas in a nearly isothermally heated state according to the relationship of P = C ₂ T (where ^ ₂ is a constant) (see the line shown by AB in Fig. 26). ). By the combination of these two processes, the working fluid is at the beginning of the work, and the power stroke is performed according to the adiabatic expansion process (actually, the adiabatic expansion is shown) (see the curve shown in BC in Fig. 26). In the adiabatic expansion process, while the external output is being output, the working fluid is in accordance with P = C ₃ r^ (its In the relationship between (: ₃ is a constant), the pressure is lowered until the power stroke is completed (the state shown in point C). In other words, the highest energy state of the working medium is achieved by two different processes, and the state in which the highest energy state of the working medium reaches the completion of the power 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 = C ₂ r, and it is not difficult to see the highest energy state of the working medium (see point in Fig. 26). The state shown in B), the temperature is in the "excess" state, that is, there is "excess temperature" (the so-called "excess temperature" refers to the relationship between the adiabatic expansion in order to reach a certain end state, the actual working condition in the starting state The temperature is higher than the theoretically required temperature), the "excess temperature" causes the curve of the expansion process to be at a high temperature position (moving to the right in Fig. 26, and Fig. 26 is the pressure temperature relationship diagram in which the vertical axis is the pressure coordinate and the horizontal axis is the temperature coordinate The state in which the work stroke is completed and the temperature is still relatively high (the state shown by the point C on the curve shown by the curve BG in Fig. 26) is not difficult to see from the state shown by the point C in Fig. 26. Γ ₂ (that is, the temperature of the working fluid after the completion of the power stroke, 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 all The Ministry is discharged to the environment in vain, so the efficiency will be in a lower state. The curve shown by 0-Α in Fig. 26 is the curve of the compression stroke of the conventional engine, and the straight line shown by Α-Β is the straight line of temperature and pressure change in the combustion explosion of the conventional engine, if we put the low-pressure gas source (including the The gas in the low-pressure oxygen-containing source and the low-pressure oxygen-free source (such as air) is compressed and then cooled or cooled during the compression process, so that the temperature of the working medium is lower or lower during the compression process. The temperature that should be reached during the adiabatic compression process, even reaches the constant temperature compression process, and even reaches the temperature reduction compression process, so that the gas working medium can be in a low temperature and high pressure state before the combustion explosion, so that the pressure after the combustion explosion is greater. The amplitude is increased (according to the gas equation ^ = ^Γ, the ratio of the pressure increase before and after combustion is determined by the ratio of the temperature increase before and after combustion. If the temperature rise before and after combustion is constant, the pressure before combustion is constant, then the temperature before combustion is lower. The higher the pressure after combustion, so as to reduce or eliminate the so-called "excess temperature" after the combustion explosion, and the temperature of the working temperature when the adiabatic expansion is completed. The degree is in a lower state to improve the efficiency of the engine. The curve shown by 0-D in Fig. 26 is a constant temperature compression curve, and the straight line shown by DE is a straight line of the pressure temperature change during the combustion explosion after the constant temperature compression process, and the curve shown by EF is shown from the point Ε The state begins with the adiabatic expansion work curve, it is not difficult to see that the value of ₂ is greatly reduced. It can be seen from the calculation that the efficiency of the expansion process from point Ε to point F is much higher than the efficiency of the expansion process from point Β to point C, while point 0 to point D The work consumed by the compression process is significantly lower than the work consumed by the compression process from point 0 to point A. The method of reducing the temperature of the working medium before combustion by cooling means to improve the efficiency to some extent, but in the process There is a cooling process, so waste heat is generated. If we can mix other working fluids (expansion agents, etc.) into the compressed working fluid, the temperature is lowered by mixing, and no residual heat is generated. This method will be simpler than cooling. The way is even better. As shown in Figure 26, if we can find a way to make the pressure temperature state point of the burned working fluid on the curve 0-A-H or to the left of the curve 0-AH, the working temperature after the expansion work It will reach a temperature equal to 0 or a temperature lower than 0, which will further improve the efficiency of the system, so that the pressure temperature state point of the burned working fluid is on the curve 0-AH or at The left side of the curve 0-A-H, the only feasible way is to use all or part of the heat released by the combustion chemical reaction to vaporize the liquid expansion agent or heat the high-pressure low-temperature gas expansion agent, and the pressure of the working medium after combustion is not lower than By the formula ^ = ( + )(177 )^ (where P is the working fluid pressure after combustion, P. is the working fluid pressure after the adiabatic compression is not burned and the expansion agent is not introduced, which is formed by the expansion agent after combustion. Partial pressure, Γ is the working temperature after combustion, Γ. It is the temperature of the working fluid which is not burned after adiabatic compression and is not introduced into the expansion agent. It is the adiabatic compression index, and the adiabatic compression index of air is 1. 4) The determined pressure value, ie the enthalpy value, will ensure that after combustion Pressure and temperature state of the working fluid at the point on the curve at the curve 0-AH 0- A- Η or left, so as to achieve higher efficiency and better environmental protection. In some cases, the heat released by the combustion chemical reaction can be used to vaporize the liquid expansion agent or heat the high-pressure low-temperature gas expansion agent to form a state in which the temperature does not change or does not change significantly before and after combustion, and the pressure is greatly increased (for example, In 26 cases, A-G); in another case, the compression force of the gas can be greatly increased, the temperature of the compressed gas reaches the environmental temperature limit or the material temperature limit, and the combustion chemical reaction is made. The released heat is all used to vaporize the liquid expansion agent or to heat the high-pressure low-temperature gas expansion agent to form a state in which the temperature does not change or does not change significantly before and after combustion, and the pressure is greatly increased (for example, as shown by Η-J in Fig. 26).

From the nature of the work process, no matter what kind of heat engine, there are only two working processes: one is the working preparation process, and it can be said to be the process of manufacturing the working medium. In this process, the temperature is important, but the most important is the working medium. The pressure; the other is the work process. In the traditional internal combustion engine, there is not only the interrelationship between the two processes, but also the timing or mechanical interconnection. Although there are separate circulation schemes announced, there is still a positive relationship between them. Time relationship, not mutual Two separate work units. The low-energy co-firing gas-filled blasting engine disclosed by the present invention, in the scheme provided with the blasting engine, is composed of two mutually independent working units to constitute a heat engine cycle, that is, the working fluid preparation process is performed by the compressor When the work process is completed by the explosion engine, there is no positive relationship between the two, and the working relationship between the two can be completely controlled, which can flexibly change the compression ratio and Displacement to meet the load response under various operating conditions.

In the actual thermodynamic cycle, the intrinsic correlation between the working conditions of the high temperature heat source and the low temperature heat source is neglected. Only one-sided attention to the temperature of the working medium under high temperature heat source and low temperature heat source L and

T ₂ , without paying attention to the state of the working medium under the high temperature heat source, can achieve the ideal working condition of the low temperature heat source. More attention should be paid to the matching of the working condition parameters under the high temperature heat source. Only when the state parameter pressure Ρ and temperature τ of the working medium match under the high temperature heat source, the working medium can efficiently reach the ideal low temperature heat source state from the high temperature heat source state.

In order to achieve high efficiency and low pollution, the working cycle mode of the traditional internal combustion engine should be changed from the traditional suction-compression-work-exhaustion cycle mode to the suction-compression-cooling-combustion-work-exhaust cycle mode, inhalation. a compression cooling-combustion work-exhaust cycle mode, inhalation-compression cooling-deep cooling-combustion work-exhaust cycle mode, inhalation-compression-enhancement-combustion work-exhaust cycle mode Or inhalation-compression cooling-enhancement-combustion work-exhaust cycle mode (so-called massification refers to the injection of expansion agent in the airflow channel of the system or in the hybrid desuperheater to increase the temperature and participate in the working fluid The method of moles), which will greatly improve the efficiency and environmental protection of the heat engine. Not only that, but also a suction-compression cooling-adiabatic compression-combustion adiabatic expansion work-exhaust cycle mode.

The structure disclosed in the present invention is a technical solution according to the above theory. In the low-entropy co-firing gas-filled blast engine disclosed in the present invention, when the compression is completed by the setting of the hybrid desuperheater and/or the heat exhaustor The working fluid (gas in the low-pressure gas source, including the low-pressure oxygen-containing gas source and the low-pressure oxygen-free gas source) is in the Ρ-Τ diagram shown in Figure 26 (the axis is the pressure Ρ and the X axis is the temperature Τ). Offset in the low temperature direction (as shown by 0-D in Fig. 26), thereby reducing the power consumption of the compression process, lowering the temperature of the low temperature heat source Γ ₂ , improving the efficiency of the engine and the environmental friendliness of the engine. Figure 27 is a comparison diagram of the cycle of the low-entropy co-firing gas-filled blast engine of the present invention and the cycle of the conventional internal combustion engine. The curve shown by abcda is the dynamometer diagram of the conventional internal combustion engine cycle, in which aefg- a The curve shown is the pressure of the low-energy co-firing gas-filled blast engine disclosed in the present invention at the end of compression of the compressor The dynamometer of the cycle when the force is the same as the pressure at the end of the compression of the conventional internal combustion engine, and the curve shown by ah-i-ga in the figure is the low-entropy co-firing blasting engine disclosed in the present invention at the compressor pressure The dynamometer of the cycle when the pressure at the end of the retraction is greater than the pressure at the end of the compression of the conventional internal combustion engine. It is not difficult to see that the low-entropy co-firing gas-filled blast engine system disclosed by the present invention has an essential improvement in efficiency compared with a conventional internal combustion engine.

According to the above theory, the low-energy co-firing gas-filled blasting engine disclosed by the present invention also discloses a more efficient and environmentally-friendly technical solution: when the compression stroke/process is completed, a certain proportion or all of the heat released by the combustion chemical reaction is used. The amount of heat released by a combustion chemical reaction for vaporizing a liquid expansion agent or heating a high-pressure low-temperature gas expansion agent, as shown in AG, AQ, and AN of FIG. 26, as shown in AG, AQ, and AN of the gasification liquid expansion agent In order to further improve efficiency and environmental protection, the low-entropy co-firing gas-filled blast engine disclosed in the present invention also discloses another technical solution: greatly improving the compression force of the gas , 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 used for all or nearly all of the gasification liquid expansion agent or the heating high pressure low temperature gas expansion agent to form the temperature before and after combustion. A state in which the pressure is greatly increased or not, and the pressure is greatly increased (for example, as shown by HJ in Fig. 26). Figure 27 is a comparison diagram of the cycle of the cycle of the low-energy co-firing gas-filled blast engine and the cycle of the conventional internal combustion engine disclosed in the present invention, wherein the curve shown by abcda is the dynamometer diagram of the cycle of the conventional internal combustion engine, and the abm-S in the figure The curve shown by a - is the low-entropy co-firing gas-filled blast engine disclosed in the present invention, when the pressure at the end of compression of the compressor is the same as the pressure at the end of the compression of the conventional internal combustion engine, but the heat released by the combustion chemical reaction a cycle diagram of all or nearly all used to vaporize a liquid expansion agent or to heat a high pressure low temperature gas expansion agent, the curve shown by aznta in the figure is a low entropy co-firing gas explosion engine disclosed in the present invention. The end of the compression of the compressor reaches the environmental temperature limit or the material temperature limit and all or nearly all of the heat released by the combustion chemical reaction is used for the circulation of the vaporized liquid expansion agent or the heating of the high pressure and low temperature gas expansion agent. Work map. It is not difficult to see that these two solutions in the low-energy co-firing gas-filled blast engine system disclosed by the present invention have higher efficiency and better environmental friendliness than conventional internal combustion engines.

In order to achieve the above object, the technical solution proposed by the present invention is as follows:

A low-entropy co-firing gas-filled blasting engine, comprising a compressor and an explosion-discharge engine, the compressor The gas inlet is set as a low pressure oxygen-containing gas inlet, and the compressed gas outlet of the compressor is in communication with a combustion chamber inflation port of the combustion chamber of the explosion-discharge engine, and the pressure-receiving capacity at the compressed gas outlet of the compressor is greater than 1 MPa, there is no timing relationship between the compressor and the blast engine.

A low-entropy co-firing gas-filled blast engine comprising a compressor, a blast engine and a high-pressure oxygen source, the gas inlet of the compressor being set as a low-pressure oxygen-free gas inlet, the compressed gas outlet of the compressor and the a combustion chamber inflation port of the combustion chamber of the explosion exhaust engine is connected, a pressure bearing capacity of the compressed gas outlet of the compressor is greater than 1 MPa, and there is no timing relationship between the compressor and the explosion exhaust engine. a high pressure oxidant introduction port at the outlet of the compressed gas of the compressor and/or on the combustion chamber and/or a communication passage between the compressed gas outlet of the compressor and the combustion chamber, A high pressure oxygen source is in communication with the high pressure oxidant inlet.

A low-entropy co-firing gas-filled blast engine comprising a compressor and a short-pressure gas-filled engine, wherein a gas inlet of the compressor is set as a low-pressure oxygen-containing gas inlet, and a compressed gas outlet of the compressor and the short-pressure The combustion chamber inlet of the combustion chamber of the gas-filled engine is in communication, and the pressure bearing capacity at the compressed gas outlet of the compressor is greater than 1 MPa, and there is no timing relationship between the compressor and the short-pressure inflatable engine.

A low-entropy co-firing gas-filled blast engine comprising a compressor, a short-pressure gas-filled engine and a high-pressure oxygen source, the gas inlet of the compressor being set as a low-pressure oxygen-free gas inlet, and the compressed gas outlet of the compressor The combustion chamber inflation port of the combustion chamber of the short-pressure pneumatic engine is in communication, and the pressure-receiving capacity at the compressed gas outlet of the compressor is greater than 1 MPa, and there is no between the compressor and the short-pressure inflatable engine a timing relationship between a compressed gas outlet of the compressor and/or a high pressure oxidant on the combustion chamber and/or a communication passage between the compressed gas outlet of the compressor and the combustion chamber The inlet, the high pressure oxygen source is in communication with the high pressure oxidant inlet.

The blast engine is a piston blast engine or an impeller blast engine. When the blast engine is set as a piston blast engine, the intake air volume flow of the gas inlet of the compressor is adjusted and the combustion chamber is inflated when the low-energy co-firing blasting engine is in a stable operating condition. The ratio of the intake air volume flow rate of the port is such that the ratio is greater than the compression ratio of the conventional piston internal combustion engine to achieve a gas pressure that is greater than the gas pressure of the combustion chamber of the piston type internal combustion engine when the compression stroke of the conventional piston internal combustion engine is completed. a state of pressure; when the blast engine is set as an impeller blast engine, and the intake of the gas inlet of the compressor is adjusted under a stable condition of the low-energy co-firing blasting engine The ratio of the volume flow rate to the intake volume flow rate of the combustion chamber inflation port is such that the ratio is greater than the compression ratio of the conventional impeller internal combustion engine to achieve a gas pressure greater than that of the conventional impeller type in the combustion chamber of the impeller type exhaust engine The state of the gas pressure at the end of the compression stroke of the internal combustion engine.

The low-entropy co-firing blasting engine further includes a switch that outputs power to the compressor via the damper.

a gas storage tank is disposed on the gas flow communication passage between the compressor and the blast engine, the blast engine is connected to the compressor via a first clutch, and the blast engine is coupled to the second clutch The vehicle is connected, the compressor is connected to the vehicle via a third clutch; the first clutch, the second clutch and the third clutch are coordinated by a control device. Wherein, the first clutch, the second clutch and the third clutch are coordinated by the control device to switch between eight working states to meet different working modes of the system, and the eight working states refer to The working mode of the three clutches and the three mechanisms is total, for example, the first working state is that the first clutch and the second clutch are in an engaged state, and the third clutch is in a disengaged state or a combined state, in which state The blast engine outputs power to the compressor and the vehicle; the second working state is that the first clutch is in an engaged state, and the third clutch and the second clutch are in a disengaged state, where In the state, the blast engine outputs power only to the compressor; the third working state is that the first clutch and the second clutch are in a disengaged state, and the third clutch is in an engaged state, in which state The vehicle uses its kinetic energy to output power to the compressor; a fourth operating state is the first clutch and The third clutch is in a disengaged state, and the second clutch is in an engaged state, in which the blast engine outputs power to the vehicle without outputting power to the compressor, the state utilizing the gas reservoir The compressed gas in the tank supplies compressed gas to the blast engine, and this state can instantaneously increase the net output power of the blast engine to meet the requirement of instantaneous load increase; the fifth working state is the a clutch, the second clutch and the third clutch are all in a disengaged state. In this working state, the blasting engine does not output power externally, and the remaining working states are that the three clutches are separated or The working mode of the arrangement and combination of the joint states will not be described herein.

A combustion chamber of the blast engine may be coupled to two or more work mechanisms.

The combustion chamber is set as a continuous combustion chamber, and the working mechanism of the blasting engine is set to work as a piston The mechanism is provided between the continuous combustion chamber and the piston working mechanism to introduce a working fluid in the continuous combustion chamber into the piston working mechanism in a positive relationship.

The compressor and the blast engine are simultaneously or individually set as adiabatic mechanisms.

The low-energy co-firing gas-filled blast engine further includes a non-condensable gas return pipe, a carbon dioxide liquefier and a low-pressure pure oxygen source, the carbon dioxide liquefier is disposed on an exhaust passage, and the low-pressure pure oxygen source is connected to the compressor The non-condensable gas return pipe communicates with the non-condensable gas outlet of the carbon dioxide liquefier and the gas inlet of the compressor, and the compressor, the combustion chamber and the carbon dioxide liquefier constitute a non-condensable gas circulation flow closure aisle.

The low-entropy co-firing blasting engine further includes a source of expansion agent on the compressor and/or at a compressed gas outlet of the compressor and/or on the combustion chamber and/or in the An expansion agent inlet is provided in the communication passage between the compressed gas outlet of the compressor and the combustion chamber, and the expansion agent source is in communication with the expansion agent inlet.

The low-entropy co-firing blasting engine further includes a heat eliminator disposed at a gas inlet of the compressor, and/or the heat eliminator is disposed on the compressor, and/or The heat exhauster is disposed at a compressed gas outlet of the compressor, and/or the heat exhaustor is disposed on a communication passage between the compressed gas outlet of the compressor and the combustion chamber, It is possible to perform heat removal and cooling on the gas to be compressed, the gas in the compressed process or the compressed gas.

The low-entropy co-firing blasting engine further includes a hybrid desuperheater, the compressed gas outlet of the compressor being in communication with the combustion chamber inflation port via the hybrid desuperheater; the hybrid desuperheater and expansion The source of the agent is connected.

Providing a fuel introduction port at a compressed gas outlet of the compressor and/or on a communication passage between the combustion chamber and/or a compressed gas outlet of the compressor and the combustion chamber, The fuel introduction port is in communication with the fuel source via a fuel control mechanism.

A gas storage tank is disposed on the gas flow between the compressed gas outlet of the compressor and the combustion chamber inflation port.

The low-entropy co-firing blasting engine further includes a thermally friction adjustable fuel storage tank on the compressor and/or at a compressed gas outlet of the compressor and/or on the combustion chamber and/or Or providing a thermal friction adjustable fuel inlet port on the communication passage between the compressed gas outlet of the compressor and the combustion chamber, The hot friction adjustable fuel inlet is connected to the hot friction adjustable fuel storage tank via a control mechanism. The thermally friction adjustable fuel in the thermal friction adjustable fuel storage tank is mixed with the gas compressed by the compressor via the hot friction adjustable fuel inlet.

The compressor can be a piston compressor or an impeller compressor.

The pressure capacity of the compressed gas outlet of the compressor is greater than 1 MPa, 1.5 MPa, 2 MPa, 2.5 MPa 3 MPa, 3.5 MPa, 4 MPa, 4.5 MPa, 5 MPa, 5.5 MPa, 6 MPa, 6.5 MPa, 7 MPa, 7.5 MPa, 8 MPa. 8.5MPa, 9MPa, 9.5MPa, 10MPa, 10.5MPa, 11MPa, 11.5MPa, 12MPa 12.5MPa 13MPa, 13.5MPa, 14MPa, 14.5MPa or more than 15MPa.

The pressure capacity of the combustion chamber is greater than 2.5 MPa.

The pressure capacity of the combustion chamber of the short-pressure pneumatic engine is greater than 2.5 WIPa, 3 MPa, 3.5 MPa, 4 MPa, 4.5 MPa, 5 MPa, 5.5 MPa, 6 MPa, 6.5 MPa, 7 MPa, 7.5 MPa, 8 MPa, 8.5 MPa, 9 MPa, 9.5 MPa, 10 MPa, 10.5 MPa, 11 MPa, 11.5 MPa, 12 MPa, 12.5 MPa, 13 MPa, 13.5 MPa, 14 MPa, 14.5 MPa or more than 15 MPa.

The ratio of the absolute amount of volume reduction in the compression stroke and the absolute volume increase in the expansion power stroke is less than 0.9, 0.8, 0.7, 0.6, 0.5, 0.4, 0.3, 0.2 or less than 0.1. .

The low-entropy co-firing blasting engine further includes a switch that outputs power to the compressor via the vent.

The ratio of the intake volume flow rate of the gas inlet of the impeller compressor to the intake volume flow rate of the combustion chamber inflation port is greater than 18, 20, 22, 24, 26, 28, 30, 32, 34, 36, 38 , 40, 42, 44, 46, 48 or 50 to achieve an operating mode in which the gas pressure charged into the combustion chamber is substantially higher than the gas pressure at the end of the conventional engine compression stroke; the gas inlet of the piston compressor The ratio of the intake air volume flow to the intake air volume flow of the combustion chamber inflation port is greater than 22, 24, 26, 28, 30, 32, 34, 36, 38, 40, 42, 44, 46, 48 or 50. The operating mode of the gas pressure that is charged into the combustion chamber is substantially higher than the gas pressure at the end of the conventional engine compression stroke.

The low-energy co-firing gas-filled blast engine further includes a non-condensable gas return pipe, a carbon dioxide liquefier and a non-condensable gas storage tank, the carbon dioxide liquefier is disposed on an exhaust passage, and the low pressure oxygen-free gas inlet of the compressor is a non-condensable gas storage tank is connected, and the non-condensable gas return pipe communicates with the non-condensable gas of the carbon dioxide liquefier The port and the non-condensable storage tank, the compressor, the combustion chamber, the carbon dioxide liquefier and the non-condensable gas storage tank constitute a non-condensable gas circulation flow closed passage.

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

The expander source is in communication with a liquid outlet of the expander liquefier, and the expander liquefier is disposed on the exhaust passage.

A low quality heat source heat exchanger is disposed between the hybrid desuperheater and the expansion agent source.

In order to make the low-energy co-firing gas-filled blast engine of the present invention more efficient and environmentally friendly, the present invention also discloses several methods for improving the efficiency and environmental protection of the low-energy co-firing gas-filled blast engine according to the present invention. The technical solutions are as follows:

A method for improving the efficiency and environmental protection of the low-energy co-firing gas-filled exhaust engine of the present invention, adjusting the pressure of the gas working fluid to be started to work above 15 MPa, adjusting the temperature of the gas working fluid to be started to work Below 2700K, the temperature and pressure of the gaseous working fluid that is about to start work are in line with the adiabatic relationship.

A method for improving the efficiency and environmental protection of the low-energy co-firing gas-filled exhaust engine of the present invention, controlling the expansion agent control mechanism to adjust the amount of expansion agent introduction and/or adjusting the amount of fuel introduced into the combustion chamber to achieve combustion The temperature of the gas in the afterburner does not exceed the temperature of the compressed gas at the gas outlet of the compressor.

A method for improving the efficiency and environmental protection of the low-energy co-firing gas-filled exhaust engine of the present invention, adjusting a ratio of an intake volume flow rate of a gas inlet of the compressor to an intake volume flow rate of the combustion chamber inflation port Realizing that the temperature of the compressed gas at the gas outlet of the compressor reaches an environmental temperature limit or a material temperature limit, adjusting the amount of expansion agent introduction and/or adjusting the introduction into the combustion chamber by controlling the expansion agent control mechanism The amount of fuel is such that the temperature in the combustion chamber after combustion does not exceed the limit reached by the temperature of the compressed gas at the gas outlet of the compressor in the environmental temperature limit and the material temperature limit.

A method for improving the efficiency and environmental protection of the low-energy co-firing gas-filled exhaust engine of the present invention, adjusting a ratio of an intake volume flow rate of a gas inlet of the compressor to an intake volume flow rate of the combustion chamber inflation port The pressure of the compressed gas at the gas outlet of the compressor is achieved to a limit of the pressure bearing capacity at the gas outlet of the compressor. a gas storage tank is disposed on the gas flow communication passage between the compressor and the short-pressure pneumatic engine, and a power output shaft of the short-pressure pneumatic engine passes through a first clutch and a power input shaft of the compressor Connected, the power output shaft of the short-pressure pneumatic engine is connected to the power shaft of the vehicle via a second clutch, and the power input shaft of the compressor is connected to the power shaft of the vehicle via a third clutch. Wherein, the first clutch, the second clutch and the third clutch are coordinated by a control device to switch between eight working states to meet different working modes of the system, and the eight working states refer to The working mode of the three clutches and the three mechanisms is total, for example, the first working state is that the first clutch and the second clutch are in an engaged state, and the third clutch is in a disengaged state or a combined state, in which state The short-pressure air-filled engine outputs power to the compressor and the vehicle; the second working state is that the first clutch is in an engaged state, and the third clutch and the second clutch are in a disengaged state, In this state, the short-pressure air-filled engine outputs power only to the compressor; the third working state is that the first clutch and the second clutch are in a disengaged state, and the third clutch is in an engaged state, In this state, the vehicle uses its kinetic energy to output power to the compressor; the fourth: E is the state is the first clutch And the third clutch is in a disengaged state, the second clutch is in an engaged state, in which the short-pressure air-fueled engine outputs power to the vehicle without outputting power to the compressor, the state is Using the compressed gas in the gas storage tank to supply compressed gas to the short-pressure gas-filled engine, this state can instantaneously increase the net output power of the short-pressure inflatable engine to meet the requirement of instantaneous load increase. The fifth working state is that the first clutch, the second clutch, and the third clutch are all in a separated state. In the working state, the short-pressure inflatable engine does not output power, and the remaining types The working state is also an operation mode in which the above three clutches are in a disengaged or engaged state, and will not be described herein.

The compressor and the short-pressure pneumatic engine are simultaneously or individually set as adiabatic mechanisms.

In the present invention, in the configuration in which the expander inlet is provided in the compressor, the expansion agent is made of a swelling agent other than water.

The so-called combustion chamber of the present invention may be a continuous combustion chamber or a batch combustion chamber.

In the low-energy co-firing gas-filled blast engine disclosed in the present invention, the so-called continuous combustion chamber refers to a combustion chamber in which fuel is continuously combusted in a combustion chamber, and the so-called intermittent combustion chamber refers to intermittent combustion of fuel in a combustion chamber. a combustion chamber including a batch type combustion chamber that burns in a positive relationship and an intermittent combustion chamber that does not burn in a positive relationship; in the structure in which the working mechanism is a piston working mechanism, the continuous combustion chamber The working fluid is introduced into the piston working mechanism by a control valve in a positive relationship.

All of the valves in the present invention may be control valves or timing control valves.

The so-called environmentally-friendly temperature limit in the present invention refers to the highest temperature at which no harmful pollutants are generated, and the environmental temperature limit for not generating nitrogen oxides is 1 800 K; the so-called material temperature limit refers to the temperature at which the material can withstand

In the present invention, "controlling the expansion agent control mechanism to adjust the amount of expansion agent introduction and/or adjusting the amount of fuel introduced into the combustion chamber to achieve a gas temperature in the combustion chamber after combustion does not exceed the gas outlet of the compressor "The temperature of the compressed gas" means that by controlling the expansion agent control mechanism to adjust the amount of the expansion agent introduced into the combustion chamber and/or adjusting the amount of fuel introduced into the combustion chamber, the heat generated by the fuel combustion chemical reaction is all or It is used for gasification of the expansion agent in a certain ratio, instead of heating and heating of the working medium in the combustion chamber, so that the temperature of the gas in the combustion chamber after the combustion of the fuel is not increased compared with the temperature before the introduction of the expansion agent. Or no significant increase.

In the present invention, the expansion agent and the fuel may be sufficiently mixed before entering the combustion chamber, and the expansion agent, the fuel and the oxidant (the oxidant means oxygen in the low-pressure oxygen-containing source and the high-pressure oxygen source, and the present invention) The so-called hydrogen peroxide is fully mixed before entering the combustion chamber.

In the low-energy co-firing gas-filled blast engine disclosed in the present invention, as described above, adjusting the amount of the expansion agent introduced into the combustion chamber and/or adjusting the amount of fuel introduced into the combustion chamber, the total amount of heat released by the combustion chemical reaction Or partially used to vaporize the liquid expansion agent or to heat the high-pressure low-temperature gas expansion agent, and the pressure of the working fluid after combustion is not lower than the formula ^(Ρ.+ Α)(77Γ.)^ (where the corpse is a post-combustion work) Mass pressure, P ₀ is the working pressure of unburned unexpanded agent after adiabatic compression, P _e is the partial pressure formed by the expanding agent after combustion, Γ is the working temperature after combustion, Γ is the adiabatic pressure The temperature of the working fluid which is not burned and not introduced into 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 value, so as to ensure the working fluid after burning. The pressure temperature status point is on curve 0-AH or on the left side of curve 0-AH, in order to achieve higher efficiency and better environmental protection. This way is more efficient and more practical in the implementation process. Good environmentally friendly technical solutions.

The fuel of the blast engine is set to diesel, and the combustion chamber temperature at the time of the impending combustion is set to Below the ignition point of the diesel, a spark plug is arranged in the combustion chamber of the blast engine; or the fuel of the blast engine is set to be gasoline, and the combustion chamber temperature at the time of the upcoming combustion is set higher than the ignition point of the gasoline. An injector is arranged in the combustion chamber of the blast engine.

The compressor is configured as a dual outlet compressor that outputs an intermediate pressure compressed gas and a high pressure compressed gas, and the high pressure compressed gas outlet of the dual outlet compressor is combusted by the hybrid desuperheater and the blast engine The chamber inflation port is connected, and an intermediate pressure combustion chamber inflation port is disposed on the explosion exhaust engine, and an intermediate pressure compressed gas outlet of the dual outlet compressor is in communication with the intermediate pressure combustion chamber inflation port.

The heat exchanger is configured as a temperature reducing heat exchanger, the compressor is configured as a dual outlet compressor that outputs an intermediate pressure compressed gas and a high pressure compressed gas, and the high pressure compressed gas outlet of the dual outlet compressor is a cooling heat exchanger is connected to the combustion chamber inflation port of the explosion exhaust engine, and an intermediate pressure combustion chamber inflation port is disposed on the explosion exhaust engine, and the medium pressure compressed gas outlet of the dual outlet compressor passes the cooling heat The exchanger is connected to the intermediate pressure combustion chamber inflation port after being heated by the temperature reducing heat exchanger and the low quality heat source heat exchanger.

Providing an expansion agent heat absorption high pressure passage on a combustion chamber wall of the explosion exhaust engine, wherein the expansion agent heat absorption high pressure passage communicates with the expansion agent inlet of the mixed 5t desuperheater, and the expansion agent absorbs the expansion agent After the heat is absorbed in the hot high pressure passage, the high temperature and high pressure gas is mixed in the hybrid type desuperheater to cool the high temperature and high pressure gas.

Providing an expansion agent heat absorption exhaust heat exchanger on an exhaust passage of the explosion exhaust engine, wherein the expansion agent heat absorption exhaust heat exchanger is in communication with the expansion agent inlet of the hybrid desuperheater, and the expansion agent is The heat sink in the heat-expanding exhaust heat exchanger of the expander is mixed with high-temperature and high-pressure gas in the hybrid type desuperheater to cool the high-temperature and high-pressure gas.

The compressor is provided with an expansion agent heat absorption compressor heat exchanger, the expansion agent heat absorption compressor heat exchanger is in communication with the expansion agent inlet of the hybrid desuperheater, and the expansion agent absorbs heat in the expansion agent After the heat is absorbed in the compressor heat exchanger, the high temperature and high pressure gas is mixed in the hybrid type desuperheater to lower the high temperature and high pressure gas and increase the number of moles of the working medium.

The principle of the scheme for providing the blast engine in the present invention is to compress air, low pressure oxygen, low pressure oxygen-containing gas or oxygen-free gas to a state larger than the gas pressure at the end of the compression stroke of the conventional internal combustion engine by using a compressor. , then fill this high-pressure gas into the combustion chamber of the explosion-discharge engine and ensure the explosion engine When the combustion chamber is inflated, the pressure is greater than the gas pressure at the end of the compression stroke of the conventional internal combustion engine. Under this high pressure, the combustion is performed without further compression, and the gas after the work is completed is discharged into the work mechanism.

The principle of the solution for providing the short-pressure air-filled engine in the present invention is to compress air, low-pressure oxygen, low-pressure oxygen-containing gas or oxygen-free gas into the pressure defined by the present invention by using the compressor, and then Filling a combustion chamber of the short-pressure gas-filled engine with a high-pressure gas to further compress the gas by using a compression stroke of the short-pressure gas-filled engine, and ensuring the combustion when the compression stroke of the short-pressure gas-filled engine is completed The gas pressure in the chamber is greater than the gas pressure at the end of the compression stroke of the conventional internal combustion engine. Under this high pressure, the combustion explosion is performed externally, and the gas after the work is completed is discharged into the working mechanism; Compression (or approximately constant temperature compression) An adiabatic compression-combustion adiabatic expansion work-exhaust cycle mode similar to the first half cycle of the Carnot cycle.

In order to further improve the efficiency and reduce the emission pollution, a hybrid desuperheater and/or a heat dissipator is also provided in the present invention, and in the solution provided with the blasting engine, the hybrid desuperheater and/or the radiator is used to The compressed gas is cooled during the compression process or cooled and cooled by the high temperature and high pressure gas from the compressor, and then charged into the combustion chamber of the blast engine, and the explosion is not performed in the combustion chamber to enter the explosion work. Stroke (or process) and exhaust stroke (or process), which allows the engine to operate at low temperatures and pressures; in the solution with the short-pressure inflatable engine, a hybrid desuperheater and/or a radiator pair The compressed gas is cooled during the compression process or cooled and cooled by the high temperature and high pressure gas from the compressor, and then charged into the combustion chamber of the short pressure range gas-filled engine, further compressed in the combustion chamber and then enters the explosion power stroke. (or process) and exhaust stroke (or process), which can improve engine efficiency. Moreover, in the low-energy co-firing blasting engine disclosed in the present invention, in the structure provided with the blasting engine, the compressor and the blasting engine do not have any phase relationship (without any timing relationship); In the disclosed low-energy co-firing gas-filled blast engine, in the structure provided with the short-pressure gas-filled engine, the compressor and the short-pressure air-fueled engine do not have any phase relationship (without any timing relationship), which is The power system offers a variety of combinations of options and is a revolutionary innovation that significantly reduces engine size, weight, and cost, and improves engine efficiency and environmental friendliness. The point of addition of the fuel may be in the combustion chamber or in the inflation passage outside the combustion chamber. In addition, the present invention also proposes to compress the gas original working medium to the environmental temperature limit and the material temperature limit by using the compressor. Value scheme, in which the heat released by fuel combustion is mainly used to heat the vaporized liquid expansion agent in the combustion chamber or to heat the high pressure low temperature gas expansion agent (ie, the heat released by the fuel combustion chemical reaction is fully or nearly fully expanded). The agent absorbs), thereby forming a gas state in a combustion chamber having a moderate pressure and a moderate temperature, achieving higher efficiency and better environmental friendliness.

In the low-energy co-firing gas-filled blast engine disclosed in the present invention, the so-called critical state includes a critical state, a supercritical state, and an ultra-supercritical state, and a state of higher temperature and higher pressure; the so-called vaporized liquid expansion agent refers to Vaporizing the expanding agent in a liquid state or heating the expanding agent in a critical state, the process may include heating the expanding agent that does not reach the vaporization temperature or heating the expanding agent that does not reach the critical temperature.

In the present invention, the so-called short-pressure pneumatic engine means that there is no independent suction stroke, and the exhaust process, the suction process and the compression process share one stroke, and the combustion explosion occurs after the exhaust, intake, and compression processes are completed. The engine of the stroke; the higher the gas pressure at the outlet of the compressor, the smaller the share of the compression process of the short-pressure gas-filled engine in the length of one stroke, and in a specific engine, according to the requirements of the working condition, The gas pressure at the gas outlet of the compressor and the compression force of the compression stroke of the short-pressure turbocharged engine are adjusted.

In the solution provided with the short-pressure air-filled engine, in order to improve the efficiency of the engine as much as possible, the compressor can be compressed under a constant temperature or approximately constant temperature, and the compressed gas is introduced. The short-pressure air-filled engine is adiabatically compressed in the short-pressure air-fueled engine, and is internally heated by fuel after adiabatic compression, and then subjected to adiabatic or near-adiabatic expansion work; FIG. 30 is a description A schematic diagram of the relationship between pressure P and temperature T in this process, in Fig. 30, the line segment indicated by 0-A (which may be a straight line or a curve) is a constant temperature or approximately constant temperature compression process in the compressor, AB The curve is an adiabatic or near adiabatic compression process in the short-pressure air-filled engine, and the line segment (which may be a straight line or a curve) indicated by BC is a constant volume or approximation in the short-pressure gas-filled engine. The constant-volume internal combustion combustion heating process, the curve indicated by C-0, is an adiabatic or near-adiabatic expansion work process in the short-pressure inflatable engine. In this figure, if the curve shown by C-0 coincides with the 0-H curve obtained by adiabatic or near adiabatic compression from the starting point 0 (for example, the atmospheric state point), it means that the temperature and pressure are returned after one cycle. In the initial state, this means that all or almost all of the heat released by the fuel in the combustion process is converted into work. In the present invention, the 0-A process, the AB process, and the BC can be adjusted in an integrated manner. The state point after the state point C is adiabatic or approximately adiabatic expansion work is on the curve indicated by 0-H or on the left side of the curve indicated by 0-H, or even on the right side of the 0-H curve, as far as possible Close to the curve shown by 0-H, this can effectively improve the efficiency of the engine. In the present invention, as described in this paragraph, the compression process is divided into two sections, the first section is constant temperature compression, and the second section is adiabatic compression, the purpose of which is to reduce the compression work as much as possible, As far as possible, the working temperature is kept at a certain temperature rise, so that under the premise of low power consumption in the compression process, the working medium has a certain temperature before combustion, thereby reducing the irreversible loss during the internal combustion heating process.

In a structure with a hybrid desuperheater and/or a heat exchanger, a lower exhaust gas temperature and higher thermal efficiency can be obtained. Moreover, the temperature of the high pressure gas before entering the blast engine can be lower than the ignition point of the fuel, so that the fuel can be thoroughly mixed with the oxygen-containing gas before inflating the blast engine, and this working mode can provide us with It takes a long enough time to mix the fuel with the oxygen-containing gas, which can greatly reduce engine pollution. Not only that, but we can also use a fuel injection system to provide a fuel mixture for multiple cylinders. Since there is no need for a positive relationship between the compressor and the blast engine, the compressor can be coaxial with the blast engine, or it can be non-coaxial, can be linked, or can be non-linked, interlocked via a clutch or a breaker, or via a transmission. Linkage. In the structure interlocked by the transmission, the load and the flow rate of the gas charged into the blast engine can be adjusted by adjusting the transmission ratio of the transmission to improve the load response of the system. Due to the setting of the tank, the compressor can be stopped when necessary and the engine is continuously operated, which can meet the instantaneous high power requirement of the load on the explosion engine.

The so-called co-firing cycle (or co-firing) of the present invention means that all of the heat released by the combustion of the fuel or nearly all of the heat or all of the heat released by the combustion of the fuel is involved in the cycle of the work cycle. In order to realize all the heat (or almost all heat) after the combustion of the fuel, all three modes can be used, one is to insulate the combustion chamber, and the other is to use the original working fluid to enter the combustion chamber wall before entering the combustion chamber. The heat absorption is brought back to the combustion chamber or directly involved in the work. The third is to use the original working fluid to return the exhausted tropical zone to the combustion chamber or directly participate in the work. For example, adiabatic engines, combined cycles, etc. are all in the form of a co-firing cycle.

The so-called low entropy co-firing cycle (or low entropy co-firing) of the present invention means that all the heat released by the combustion of the fuel or almost all the heat or more than the heat released by the combustion of the fuel are all involved in the work cycle, and the maximum pressure of the working medium is greatly high. The highest pressure of the working fluid in the traditional thermodynamic system and almost no excess temperature Loop. In order to further improve the environmental friendliness of the so-called low-entropy co-firing gas-filled exhaust engine, oxygen-containing gas which does not generate harmful compounds during heat-work conversion can be used as an oxidant for a low-entropy co-firing gas-filled engine.

The non-timing relationship between the so-called compressor and the blast engine in the low-entropy co-firing blasting engine disclosed in the present invention means that there is no need to determine the phase in accordance with the logical relationship of the engine working cycle. The blast engine can directly output power to the compressor, or it can not directly output power (for example, the compressor can be driven by a battery or the like). In the structure in which the exhaust engine directly outputs power to the compressor, there is no need to consider the phase between the two (that is, there is no need to consider the positive relationship), and if the explosion engine is disposed coaxially with the compressor, there is no need to consider The phase relationship, but only the dynamic balance of the two or the overall dynamic balance of the two connections. In some cases, in the structure in which the blast engine outputs power to the compressor, the power output shaft of the blast engine passes through a clutch, a breaker or a power input shaft through the transmission and the compressor connection.

The Miller cycle is defined as a cycle in which the suction stroke is less than the power stroke. For ease of understanding, in the present invention, a cycle in which the intake stroke is larger than the work stroke is defined as an anti-Miller cycle. Drawing on this logic and its nature, and because the solution disclosed in the present invention is not limited to the stroke, but also includes the process (such as using an impeller type compressor or an impeller type blast engine), here, we will have a smaller suction volume. The cycle of the work expansion volume is defined as a Miller-like cycle, and a cycle in which the suction volume is larger than the work expansion volume is defined as an inverse class Miller cycle. In the working state with efficiency as the main purpose, the Miller-like cycle can be used. In order to meet the requirements of the instantaneous output of the system and the high power output, the inverse Miller cycle can be used. The realization of the Miller-like cycle or the inverse Miller cycle can be achieved in the following ways: First, by the original design, the intake air amount of the compressor and the exhaust gas volume of the explosion-discharge engine are realized at a fixed speed ratio a Miller-like cycle or an inverse Miller cycle, that is, the intake air amount of the compressor is smaller than the exhaust gas volume of the blast engine to realize a Miller-like cycle, and the intake air amount of the compressor is greater than the blast engine The exhaust gas volume is used to realize the inverse Miller cycle; secondly, the Miller cycle or the inverse Miller cycle is realized by changing the rotational speed of the compressor and the explosion engine; Third, by setting a gas storage tank, The compressor and the blast engine are caused to perform a Miller-like cycle or an inverse Miller cycle without shifting.

In the present invention, Fig. 33 is a graph showing the relationship between the temperature T of the gas working medium and the pressure P, and the curve shown by 0-AH. It is the adiabatic relationship curve of the gas working through the zero point with the state parameters of 298K and 0.1 MPa; point B is the actual state point of the gas working medium, and the curve indicated by EBD is the adiabatic relationship curve passing point B, point A and B The pressure at the point is the same; the curve indicated by FG is the adiabatic relationship curve of the working medium passing through 2800K and 10MPa (that is, the current state of the gas working medium in the internal combustion engine).

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 33. 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. In the left side of the curve shown by 0-AH in Figure 33; 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. 33, but the temperature of the gas working fluid is not higher than the temperature calculated from the adiabatic relationship of the gas working fluid plus 1000 sum, 950K sum, and 900K And, add 850K, add 800K, add 750K, add 700K and add 650K, add 600K and add 550K, add 500K and add 450K and add 400K And, add 350K, add 300K and add 250K And, add 200K, and force 1 90Κ, force [Π 80Κ, plus 1 70K, force 1 60K, force 150K, force 140K and 130K and Add 1 20K sum, add 1 10K sum, force [1 100K sum, add 90K sum, add 80K sum, add 70K sum, add 60K sum, add 50K sum, add 40K sum, Adding 30K and/or not higher than the sum of 20K, that is, as shown in FIG. 33, the actual state point of the gas working medium is point B, and point A is the point on the same adiabatic relationship curve of pressure and point B, The temperature difference between point A and point B should be less than 1000Κ, 900Κ, 850Κ, 800Κ, 750Κ, 700Κ, 650Κ, 600Κ, 550Κ, 500Κ, 450Κ, 400Κ, 350Κ, 300Κ, 250Κ, 200Κ, 1 90Κ, 1 80Κ, 1 70Κ, 1 60Κ, 1 50Κ, 140Κ, 130Κ, 120Κ, 1 10Κ, 1 00Κ, 90Κ, 80Κ, 70Κ, 60Κ, 50Κ, 40Κ, 30Κ or less than 20.

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 (ie, the temperature and pressure of the gas working medium) is as shown in FIG. 33. The adiabatic process curve shown through the defect is in the left region of the EB-D.

In the present invention, the so-called gas working fluid to be started is the gas working fluid when the combustion in the combustion chamber is completed, and in the structure in which the expansion agent is introduced, the gas in the combustion reaction and the expansion agent introduction process are completed. Physical work.

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, in the structure in which the expansion agent source is provided, the state (i.e., temperature, pressure, and mass) of the gaseous working medium charged in the combustion chamber is adjusted, and the amount of fuel introduced into the combustion chamber and the amount of fuel are adjusted. The amount of expansion agent introduced into the system causes the temperature and pressure of the gaseous working fluid to be started to work in an adiabatic relationship.

In the present invention, in the structure provided with the heat exhaustor, the heat removal intensity of the heat exchanger is adjusted, and the state (ie, temperature, pressure, and mass) of the gas working medium charged in the combustion chamber is adjusted, and adjustment is made. The amount of fuel introduced into the combustion chamber is such that the temperature and pressure of the gaseous working fluid that is about to begin work are in an adiabatic relationship.

In the present invention, in the configuration in which the hybrid desuperheater is provided, the cooling intensity of the hybrid desuperheater is adjusted, and the state (ie, temperature, pressure, and mass) of the gaseous working medium charged in the combustion chamber is adjusted, Adjusting the amount of fuel introduced into the combustion chamber aligns the temperature and pressure of the gaseous working fluid that is about to begin work with an adiabatic relationship.

In the low-energy co-firing gas-filled blasting engine disclosed in the present invention, not only the timing relationship between the so-called compressor and the blasting engine is required, but the two can also be different types of mechanisms, and the two can be coaxial. It can also be non-coaxial, which completely changes the cycle mode of the suction-pressure-explosion-discharge of the traditional piston engine, and the cycle method of simply separating the cycle, but dividing the engine into two processes, namely, the work The quality preparation process and the working process of the working fluid. In particular, there is no timing relationship between the compressor and the blast engine, which will provide a new platform for the design, manufacture and use of the engine. For example, it can be compressed with a rotor compressor, a screw compressor, or an impeller compressor. After the combustion chamber is burned, the working fluid is provided for the cylinder piston type working mechanism, so that the superiority of the compression of the screw, the rotor and the impeller type mechanism and the temperature resistance and high pressure resistance of the cylinder piston type working mechanism can be exerted.

The low-entropy co-firing gas-filled blasting engine disclosed by the present invention can be closed by adjusting the inflation valve (the inflation valve can be a valve that inflates the combustion chamber or a valve that supplies the combustion chamber to the working mechanism) , different torque output can be obtained, especially when high torque output is required, the corresponding torque output can be obtained under the condition of satisfying good combustion, such as vehicle climbing, etc.; In the structure of the blast engine, by adjusting the inflation valve, the top dead center combustion or the deep top dead center combustion can be realized, thereby obtaining a large torque output, improving the efficiency and environmental protection of the blast engine (so-called upper The combustion at the end point refers to the combustion mode in which the piston is burned after passing the top dead center at a certain angle. The so-called depth after top dead center combustion refers to the combustion of the piston through the top dead center close to the top dead center of 45 degrees).

In the low-energy co-firing gas-filled blast engine disclosed in the present invention, one compressor can supply high-pressure gas to a multi-cylinder or a plurality of blast engines, or can provide high pressure to a single-cylinder or an blast engine by a plurality of compressors. gas.

The low-energy co-firing gas-filled blast engine disclosed in the present invention has a temperature of compressed air entering the blast engine due to the provision of a hybrid desuperheater and/or a heat eliminator between the compressor and the blast engine. The relationship between pressure and pressure has broken the relationship between the temperature and pressure formed in the compression stroke of a conventional engine, that is, the compressed gas compressed by a compressor and cooled by a hybrid desuperheater and/or a heat exchanger. The temperature is controllable and can be either below the fuel's ignition point or above the fuel's ignition point. This allows the engine to operate at high pressures and relatively low combustion temperatures, which not only reduces the engine's thermal load, but also greatly increases the efficiency of the engine. It also allows the engine's exhaust temperature to be significantly reduced to achieve exhaust. The self-liquefaction or the provision of a lower temperature exhaust for the subsequent liquefaction process is more conducive to the subsequent liquefaction process. In the present invention, a relatively low pressure gas source may be provided from a certain stage of the compressor, and the gas source is introduced into the combustion of the engine when the combustion chamber pressure is lower than the pressure of the gas source through the endothermic process or without the endothermic process. The pressure at which the chamber or the multi-stage turbine is introduced is lower than the level of the source pressure, thereby increasing the function of the engine or the turbine. In the low-energy co-firing gas-filled blasting engine disclosed by the invention, the setting of the expansion agent can adjust the relationship between the temperature and the pressure in the combustion chamber in a larger range, and get rid of the curing relationship between the pressure and the temperature of the conventional internal combustion engine, thereby achieving high efficiency. , environmental protection and high power.

The expansion agent filled in the system airflow channel or the hybrid desuperheater in the low-entropy co-firing gas explosion exhaust engine disclosed by the invention may be a liquid, a high-pressure low-temperature gas, and is in a critical state (including a critical state, a supercritical state, a super-super Fluids (such as gas liquefaction, etc.) in critical state and higher temperature and higher pressure state). The filling agent can act as a cooling agent or can not cool down, that is, the temperature of the expanding agent can be the same as or different from the temperature of the gas stream; the main function of charging the expanding agent is to increase the working fluid. The number of moles, in turn, results in lower combustion temperature rise at the same fuel level, reducing or avoiding the formation of nitrogen oxides, improving system efficiency and environmental friendliness. Can adjust the amount and fuel filled with expansion agent The amount of control achieves control of the explosion engine temperature, pressure and combustion rate. In the present invention, the blast engine can be set as an adiabatic blast engine to improve the efficiency of the system, and a heat storage zone can also be provided on the blast engine, which absorbs heat when the working temperature is high, in the working medium. After the expansion and cooling, the heat is supplied to the working medium, and the entire explosion-discharge engine is externally insulated. The solution of the expansion agent charged into the hybrid desuperheater in the present invention can make the expansion agent and the compressed gas have sufficient time for mixing, and is easy to prevent corrosion, antifreeze, etc., and is substantially superior to injecting liquid expansion into the cylinder. Or a solution of a gaseous expansion agent.

The term "insulation type mechanism" as used in the present invention means a mechanism having a heat insulating function.

In the low-energy co-firing gas-filled blasting engine disclosed in the present invention, a gas from a low-pressure gas source (including a low-pressure oxygen-containing source and a low-pressure oxygen-free source) can be cooled downstream by a expanding agent during the compression process ( The so-called co-current cooling is relative to convective cooling. In the process of downstream cooling, the expansion agent that absorbs the heat of the compressed gas in the process of compression and then heats up or vaporizes into the hybrid desuperheater and is compressed. The gas mixes and enters the combustion chamber together. The so-called compression process refers to the process in which the compressor compresses the gas from low pressure to high pressure. This process includes the compressor itself, the stages between the multistage compression processes, etc., which can be set to cool the compressed gas. The heat exchanger is in the order of the pressure of the compressed gas.

According to the Cobraon equation /^ = r, the molar number of the working fluid and the Kelvin temperature of the working fluid are equivalent from the perspective of the functional contribution. However, because the Kelvin temperature is based on 273.15, it is more difficult to multiply the Kelvin temperature if multiple work is to be obtained. It is relatively easy to multiply the number of moles, and it can be made more powerful. It is explained as follows: It is assumed that the temperature of the original working fluid before the combustion of the fuel is Γ. The working mole number is w. The heat released by the combustion of the fuel is β, and the temperature of the working fluid after the combustion of the fuel is η = Γ. ₊ ρ/θ3⁄4 (where, and ". are the molar heat capacity and the number of moles of the working fluid after combustion of the fuel, respectively, assuming that the combustion chemical reaction does not cause a change in the number of moles of the working medium), so the working force of the working medium after the combustion of the fuel For ^ = ^ = ?(Γ. ₊ ρ/θ _; if the mole number is c; the expansion agent is introduced into the combustion chamber before combustion, during combustion or after combustion, the temperature of the working fluid after combustion of the fuel is about τ Τ = τ ₊ (ρ- ^)/(ο3⁄4 ₊ ςχ) (where c is the molar specific heat capacity of the gas expansion agent, ₉ is the molar agent from the state before entering the combustion chamber to the temperature of r. The required heat), for this purpose, the expansion agent is introduced and the work of the working fluid formed after the combustion of the fuel is performed. The ability is P'V = (". + x, RT( = (". + x)R{T ₀ + (Q - xq) /(C". + C,x)). Therefore, before and after the introduction of the expansion agent, The difference in the working force of the working fluid is

P'V - PV = (". + x)R(T ₀ + (Q - xq)l(Cn ₀ + C _]X )) - n ₀ R{T ₀ + Q/Cn _Q ), in order to simplify the calculation, Assume". = 1 , c = , then after finishing,

Obviously, as long as we choose the right expansion agent and make (r.-g/c) positive, we can get more function. Not only that, because in this process, the temperature and pressure of the working fluid can be more matched, and the generation of excess temperature is reduced, thereby improving the efficiency of the thermodynamic system.

Diesel-fueled engines are almost all compression-ignition methods, which require high-pressure injection of fuel into the combustion chamber in a very short period of time, which not only makes the fuel injection system expensive, but also because of the short time, fuel and oxidant. (such as air) is difficult to mix thoroughly, which will deteriorate the engine's emissions. In order to avoid these problems, in the solution disclosed in the present invention, the diesel can be placed before the combustion chamber and the temperature is lower than the diesel ignition point. The high pressure and low temperature gas entering the combustion chamber is mixed, and the oil and gas mixture entering the combustion chamber is fully mixed. Since the temperature of the oil and gas mixture in the combustion chamber is lower than the ignition point of the diesel fuel, in this diesel fueled scheme, it is necessary to provide a spark plug in the combustion chamber. In order to ignite the oil and gas mixture, the efficiency and emissions of the diesel engine are better. The low-energy co-firing gas-filled blasting engine disclosed by the invention can also set the combustion chamber temperature to be higher than the ignition point of the diesel fuel when the diesel fuel is used, and the diesel fuel is directly injected into the combustion chamber, and the diesel fuel is burned in the combustion chamber. However, due to the high-pressure inflation of the combustion chamber, there is a strong flow, which can efficiently and fully mix the fuel and the gas to reduce the emission pollution.

Conventional gasoline-fueled engines are almost all ignition methods, and the pressure ratio cannot be high. Because the high pressure ratio is easy to cause deflagration, the technical solution disclosed in the present invention has temperature controllable due to high pressure ratio, and when the temperature reaches the ignition point of gasoline. It can make the gasoline engine save the ignition system like the traditional diesel engine, and directly inject the gasoline into the combustion chamber. However, since the concentration of oxygen in the combustion chamber can be adjusted by adjusting the amount of the expansion agent, it can be high pressure and high temperature. When the gasoline is burning, the gasoline is directly injected without detonating, so that the gasoline engine has better power and emissions. Therefore, in the gasoline-fueled technical solution of the present invention, only the fuel injector can be provided in the combustion chamber, and no spark plug can be provided.

The stable working condition of the present invention means that the compressor and the blast engine are in working state. Further, the mass flow rate of the compressor gas inlet is equal to the operating mass flow rate of the combustion chamber inflation port of the blast engine, and the gas in the low pressure gas source is not calculated under such operating conditions. A phase change of a partial component between the compressor and the blast engine causes a difference in mass flow rate, and does not calculate a mass flow rate due to the addition of fuel between the compressor and the blast engine. Variety. The low-enthalpy mixed-combustion blasting engine disclosed in the present invention can work independently according to the compressor and the blasting engine, so in some cases the compressor can work alone (such as at startup or need to be directed to the gas) When the storage tank is filled with compressed gas, in some cases the explosion-discharge engine can also work alone (for example, in a structure with a gas storage tank, when it is required to instantaneously output high power), the so-called stabilizer This does not include these conditions, and these conditions do not affect the setting of stable operating conditions.

As we all know, the compressor has no concept of compression ratio. The pressure of the gas generated by the compressor is also not directly related to the top dead center volume and the bottom dead center volume of the compressor. During the design and manufacture of the compressor, To minimize the top dead center volume, the ratio of the top dead center volume to the bottom dead center volume is called the clearance rate. It does not affect the output gas pressure, but it affects the efficiency of the compressor. The amount of pressure that can be generated by the compressor is determined by the ratio of the amount of suction of the compressor to the volumetric flow of the high pressure gas of the output gas downstream of the compressor. In the low-energy co-firing gas-filled blast engine disclosed in the present invention, the pressure at the end of the combustion of the blast engine combustion chamber is determined by the intake air volume of the compressor and the volumetric flow rate of the high-pressure gas charged into the blast engine (the so-called high-pressure gas volume flow is directed) The ratio of the volumetric flow rate in the high pressure state of the explosion-discharge engine to the high-pressure gas is determined. (In the structure in which the gaseous medium is introduced into the combustion chamber in an intermittent manner, the so-called explosion-discharge engine high-pressure gas volume flow is performed by each inflating. The volume of the high-pressure gas that can be charged and the number of times of inflation per unit time are determined. Therefore, in order to ensure that the gas pressure charged into the combustion chamber of the blast engine is greater than the gas pressure at the end of the compression stroke of the conventional internal combustion engine, the intake air amount of the compressor and the blast engine are required to be charged once. The volume under high pressure of the high pressure gas and the rotational speed of the blast engine are controlled, or the intake air amount of the compressor and the flow rate of the combustion chamber inflation port are controlled.

The so-called "intake volume flow of the gas inlet of the compressor in the steady-state condition of the low-energy co-firing gas-filled blast engine and the intake volume of the combustion chamber inlet of the blast engine" The ratio of the flow rate is a measure of the working state of the low-energy co-firing gas-filled exhaust engine disclosed in the present invention. The important parameter is equivalent to the compression ratio in a conventional engine. In the present invention, the purpose of setting the ratio to be larger than the compression ratio of the conventional engine is to form a gas working medium in the combustion chamber of the blast engine which is higher than the working fluid pressure of the conventional engine. In order to satisfy the gas pressure when the combustion gas in the combustion chamber of the explosion exhaust engine is greater than the compression pressure of the conventional internal combustion engine, the pressure of the compressed gas outlet of the compressor must reach a higher level to overcome the explosion. The gas acceleration loss, the flow loss and the pipe resistance when the engine combustion chamber is inflated, that is, in the low-entropy co-firing gas explosion exhaust engine disclosed in the present invention, the intake air amount and the compression capacity of the compressor are appropriately increased to meet need.

The so-called gas pressure charged into the combustion chamber of the blast engine is greater than the gas pressure at the end of the compression stroke of the conventional engine means that the fuel of the low-energy co-firing blasting engine disclosed in the present invention is charged as diesel. The gas pressure of the combustion chamber of the blast engine is greater than the pressure in the combustion chamber after the compression stroke of the conventional diesel engine is completed; if the fuel of the low-energy co-firing blasting engine disclosed in the present invention is set to be gasoline, the engine is charged The gas pressure of the combustion chamber is greater than the pressure in the combustion chamber when the compression stroke of the conventional gasoline engine is completed; if the compressor or the blast engine in the low-energy co-firing blasting engine disclosed in the present invention or both are set as the turbine The gas pressure into the combustion chamber of the blast engine is greater than the pressure in the combustion chamber when the compression stroke of the conventional turbine is completed; if the low-energy co-firing blasting engine disclosed in the present invention is set as the rotor engine, the explosion is charged The gas pressure in the combustion chamber of the engine is greater than the pressure in the combustion chamber when the compression stroke of the conventional rotary engine is completed; Forth. In the low-energy co-firing gas-filled blasting engine disclosed in the present invention, the gas pressure charged into the combustion chamber of the blast engine can be operated lower than the gas pressure at the end of the compression stroke of the conventional engine, but the working efficiency is correspondingly Impact.

In the low-energy co-firing blasting engine disclosed in the present invention, in the structure in which the blasting engine is set as a piston blasting engine, the gas pressure charged into the combustion chamber of the blast engine is greater than 3 MPa, 3.5 MPa> 4MPa, 4.5MPa, 5MPa, 5.5MPa, 6MPa, 6.5MPa, 7MPa, 7.5MPa, 8MPa, 8.5MPa, 9MPa, 9.5MPa, 诵Pa, 10.5MPa, 11MPa, 11.5MPa, 12MPa, 12.5MPa, 13MPa, 13.5MPa 14MPa, 14.5MPa, 15MPa, 15.5MPa, 16MPa, 16.5MPa, 17MPa, 17.5MPa, 18MPa, 18.5MPa, 19MPa, 19.5MPa, 20MPa, 25MPa, 30MPa, 35MPa, 40MPa, 45MPa, 50MPa, 55MPa or 60MPa. In order to achieve this pressure, the intake volume flow rate of the gas inlet of the compressor is adjusted with the inlet gas of the combustion chamber inlet of the blast engine. a ratio of the accumulated flow rate to achieve a set value of the gas pressure charged into the combustion chamber of the blast engine when the low-entropy co-firing gas-filled blast engine is in a stable working condition; the adjusting manner includes adjusting the row of the compressor The amount and the rotational speed as well as the displacement and rotational speed of the blast engine (the displacement of the blast engine refers to the volumetric flow rate of the charged gas at the charging pressure per revolution). In the structure in which the compressor is a piston type compressor, the gas pressure at the compressed gas outlet of the compressor is 3.5 MPa, 4 MPa, 4.5 MPa, 5 MPa, 5.5 MPa, 6 MPa, 6.5 MPa, 7 MPa > 7.5. MPa, 8MPa, 8.5MPa, 9MPa, 9.5MPa, 10MPa, 10.5MPa, 11MPa, 11.5MPa 12MPa 12.5MPa, 13MPa, 13.5MPa, 14MPa 14.5MPa, 15MPa, 15.5MPa, 16MPa, 16.5MPa, 17MPa, 17.5MPa, 18MPa, 18.5MPa, 19MPa, 19.5MPa, 20MPa, 25MPa, 30MPa, 35MPa, 40MPa, 45MPa, 50MPa, 55MPa or 60MPa.

In the low-energy co-firing gas-filled blast engine disclosed in the present invention, in the structure in which the blast engine is an impeller-type blast engine, the gas pressure charged into the combustion chamber of the blast engine is greater than 2 MPa, 2.5 MPa, 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, 11.5MPa, 12MPa 12.5 Pa 13MPa 13.5MPa, 14MPa, 14.5MPa, 15MPa, 15.5 Pa 16MPa, 16. 5MPa, 17MPa, 17.5MPa, 18MPa, 18.5MPa, 19MPa, 19.5MPa, 20MPa, 25MPa, 30MPa, 35MPa, 40MPa, 45MPa, 50MPa, 55MPa or 60MPa. In order to achieve this pressure, a ratio of an intake volume flow rate of the gas inlet of the compressor to an intake volume flow of the combustion chamber inflation port of the blast engine is adjusted to achieve the low entropy co-firing charge The gas pressure of the explosion-discharge engine charged in the combustion chamber of the explosion-discharge engine reaches a set value; the adjustment manner includes adjusting the displacement and the rotation speed of the compressor and the displacement and the rotation speed of the explosion-discharge engine ( The displacement of the blast engine refers to the volumetric flow rate of the charged gas at the charging pressure per revolution. In the structure in which the compressor is an impeller type compressor, the gas pressure at the compressed gas outlet of the compressor is greater than 2.5 Pa, 3 Pa> 3.5 MPa, 4 MPa, 4.5 MPa, 5 MPa, 5.5 MPa, 6 MPa. 6.5MPa, 7MPa, 7.5MPa> 8MPa, 8.5MPa, 9 Pa> 9.5MPa 10MPa, 10.5MPa, 11MPa, 11.5MPa. 12MPa, 12.5MPa, 13MPa, 13.5MPa, 14MPa, 14.5MPa 15MPa, 15.5 Pa. 16MPa, 16. 5MPa, 17MPa, 17.5MPa 18MPa, 18.5MPa, 19MPa, 19.5MPa, 20MPa, 25MPa, 30MPa, 35MPa 40MPa, 45MPa, 50MPa, 55MPa or 60MPa. In the low-entropy co-firing blasting engine disclosed in the present invention, in the structure provided with the impeller-type compressor, the intake volume flow rate of the gas inlet of the impeller-type compressor and the inflation port of the combustion chamber The ratio of intake air volume flow is greater than 18, 20, 22, 24, 26, 28, 30, 32, 34, 36, 38, 40, 42, 44, 46, 48, 50, 52, 54, 56, 58, 60 , 62, 64, 66, 68 or 70 to achieve an operating mode in which the gas pressure charged into the combustion chamber is substantially higher than the gas pressure at the end of the conventional engine compression stroke; the structure in which the piston compressor is provided The ratio of the intake volume flow rate of the gas inlet of the piston compressor to the intake volume flow rate of the combustion chamber inflation port is greater than 22, 24, 26, 28, 30, 32, 34, 36, 38, 40 , 42, 44, 46, 48, 50, 52, 54, 56, 58, 60, 62, 64, 66, 68 or 70 to achieve a gas pressure that is substantially higher than the conventional engine compression stroke The working mode of the gas pressure is completed.

The so-called explosion-discharge engine of the present invention is composed of a combustion chamber and an expansion working mechanism (ie, a work mechanism), and only performs a combustion and explosion work process (including a combustion explosion work stroke) and an exhaust process, and does not include suction. Process and compression process of a thermodynamic system (a system that is successfully converted to heat), in which the original working fluid enters the combustion chamber in a charging mode rather than inhalation; the combustion chamber and the expansion working mechanism ( That is, the work mechanism can be directly connected, or the combustion chamber can be placed in the expansion work mechanism (such as the structure in which the combustion chamber is disposed in the cylinder of the cylinder piston mechanism), and the combustion chamber can be operated by the control valve and the expansion. In the structure that connects the combustion chamber through the control valve and the expansion work mechanism, in order to fully and efficiently burn, the combustion chamber may be in a continuous combustion state, or the combustion chamber may be in an intermittent combustion state; one combustion chamber may correspond to one Expansion work mechanism, a combustion chamber can also correspond to two or more expansion work mechanisms; work mechanism can The piston type expansion working mechanism (including the rotor type expansion working mechanism) may also be a turbo type expansion working mechanism (ie, an impeller type working mechanism), and the so-called expansion working mechanism refers to the expansion of the working medium by the combustion chamber. A mechanism for externally outputting power; in order for such an engine to operate normally, it is necessary to add fuel to the intake air or to inject fuel in the combustion chamber, and depending on the fuel, an ignition or compression ignition form may be employed.

In the present invention, the short-pressure pneumatic engine outputs power to the compressor via the switch, or the short-pressure inflatable engine outputs power to the compressor.

The so-called low-pressure oxygen-containing source of the present invention refers to a gas source capable of providing a lower pressure containing oxygen or containing other oxidants, such as atmospheric, low-pressure oxygen, low-pressure oxygen-containing gas, etc.; The gas source refers to a gas source that can provide no or no other oxidant, such as a low-pressure carbon dioxide storage tank, a tail gas of a thermodynamic system, and a source of non-condensable gas; the so-called high-temperature and high-pressure gas refers to the temperature increase and pressure of the compressor. Gas; the so-called compressor refers to all the mechanisms that can compress the gas, such as cylinder piston type, impeller type, screw type, gear type, rotor type compressor, etc.; the so-called non-piston type compressor refers to the piston type compression. Compressor other than the machine, including impeller type compressor, screw type compressor, etc.; the so-called non-piston type blasting engine refers to the blasting engine other than the piston type blasting engine, including the impeller type blasting engine, the screw type Explosive exhaust engine, etc.; the so-called desuperheater refers to the device that cools the gas; the so-called hybrid desuperheater is a device that points to the working medium in the system to mix a substance to cool the working medium in the system; the so-called desuperheater refers to the ability to heat a device for discharging the system, such as a radiator, a heat exchanger, etc.; a so-called gas flow between the compressor and the blast engine Accumulator means connected to said gas reservoir is provided on the discharge passage of the compressor and the engine explosion, a so-called gas reservoir storage means is part of the compressed gas from the compressor is used.

In the present invention, the expansion agent refers to a working substance that does not participate in the combustion chemical reaction to raise or lower the temperature and adjust the number of moles of the working medium, and participates in the expansion work, such as water, carbon dioxide, helium, liquid nitrogen, liquid carbon dioxide. Wait.

In the present invention, the expansion agent refers to a working substance other than water which does not participate in the combustion chemical reaction to raise or lower the temperature and adjust the number of moles of the working medium and participate in the expansion work, such as carbon dioxide, helium, liquid nitrogen, Liquid carbon dioxide, etc.

In the present invention, the so-called low-quality heat source refers to the waste heat generated by the low-energy co-firing gas-filled blast engine disclosed in the present invention, such as the waste heat generated by the combustion chamber wall of the blast engine, and the waste heat in the exhaust gas of the blast engine. And the heat generated by the compressor and the heat that the environment can provide; the so-called low-quality heat source heat exchanger refers to a heat exchanger that heats the expansion agent by absorbing heat in the low-quality heat source, that is, a combustor heat exchanger on the combustion chamber wall of the blast engine (such as an expansion agent heat absorbing high pressure passage, etc.), an exhaust heat exchanger (such as an expansion agent heat absorbing row) disposed on an exhaust passage of the blast engine a gas heat exchanger or the like) and a compressor heat exchanger (such as a heat exchanger heat exchanger heat exchanger, etc.) provided on the compressor; the so-called high pressure oxygen source means a system that can directly supply an oxidant to the combustion chamber. Such as high-pressure gaseous oxygen, high-pressure gaseous oxygen produced by pressurized gasification of liquid oxygen, high-pressure hydrogen peroxide, etc.; so-called thermal friction adjustable fuel refers to a mixture of fuel and expansion agent, by adjusting the fuel in the mixture It was in proportion to Adjusting the calorific value and the number of moles of the thermomotive adjustable fuel, which may be an aqueous solution of an alcohol (such as an aqueous solution of ethanol, an aqueous solution of methanol, etc.), or a mixed solution of an alcohol, a hydrocarbon, and water (such as ethanol, a mixed solution of water and diesel, a mixed solution of ethanol, water and gasoline, etc.), it may also be a mixture of several different alcohols, hydrocarbons and expansion agents, such as ethanol, methanol, diesel, gasoline and water or A mixture of liquid carbon dioxide; not only that, the fuel in the thermomotive adjustable fuel may be composed of a plurality of fuels, and the expansion agent may also be composed of a plurality of expansion agents. The function of the thermal friction adjustable fuel is to reduce the number of system storage tanks, and to prevent the system with water as the expansion agent from freezing and anti-corrosion, and to make the structure simple and reduce the volume and cost of the system; the so-called "power axis of the vehicle""It is both the power input shaft and the power output shaft. The so-called original working fluid refers to the working medium that is not heated by internal combustion combustion, that is, the oxidant, reducing agent and expansion agent that enter the combustion chamber, and various phase change substances thereof, so-called phase change. The substance refers to the original working medium in different states, that is, gaseous, liquid or solid; the so-called gas liquefaction refers to the liquefied gas, such as liquid nitrogen, liquid helium, liquid carbon dioxide or liquefied air.

The so-called "heat-dissipator is disposed on the gas flow passage" means that all or part of the heat-dissipator is disposed on the passage through which the gas flows, and the heat-dissipator may be disposed on the pipeline, and may be disposed on the compressor, Anything that can be placed in the multi-stage compression process can cool the compressed gas.

The term "non-condensable gas" as used in the present invention means a gas which does not condense in the carbon dioxide liquefier and a gas carbon dioxide which is not condensed in the carbon dioxide liquefier, so-called non-condensable gas including helium gas or the like does not occur during combustion. a gas that does not condense by reacting with oxygen; a so-called carbon dioxide liquefier refers to a device that can liquefy carbon dioxide, and a condensate outlet can be provided between the carbon dioxide liquefiator or between the carbon dioxide liquefier and the blast engine The so-called expander liquefier refers to any device capable of liquefying the expansion agent. The cold source of the carbon dioxide liquefier and the expander liquefier may be a low temperature expander such as liquid nitrogen; it may also be a low temperature liquid oxygen or the like.

The high-pressure oxygen source in the present invention may be a hydrogen peroxide storage tank (i.e., a hydrogen peroxide storage tank), or may be a source of a high-pressure oxygen-containing gas such as a high-pressure air source.

The introduction port referred to in the present invention means a passage through which a working medium can be introduced, and includes a nozzle for ejecting means, and the like, which can introduce a fluid.

In the low-energy co-firing gas-filled blasting engine disclosed in the present invention, control valves, pumps, sensors, control units, fuel injectors, spark plugs, and rows can be disposed at appropriate places according to well-known techniques and principles. Gas control valve (door), etc.; so-called communication refers to direct communication, indirect communication through several processes (including mixing with other substances, etc.) or controlled connection through pumps, control valves, etc.

In the low-entropy co-firing blasting engine disclosed in the present invention, in the configuration in which the blasting engine is an impeller blasting engine according to a known technique, the combustion chamber is set as a continuous combustion chamber.

The so-called switch of the present invention refers to a device having a function of turning on and off the power transmission, the switch may be a mechanical connection or a separating device for gear meshing through a sliding gear, or may be spring-loaded, hydraulic or Electromagnetic clutches.

The control of engine speed and output power in the low-entropy co-firing blasting engine disclosed in the present invention can be controlled by controlling the amount of fuel, or by controlling the amount of gas mixture entering the blast engine.

The low-energy co-firing gas-filled blasting engine disclosed in the present invention, when the gas in the low-pressure gas source (including the low-pressure oxygen-containing source and the low-pressure oxygen-free source) does not contain nitrogen, even if there is no hybrid desuperheater In the mechanism of the heat exchanger, the compression force of the compressor can be greatly increased, and the pressure and temperature of the gas charged into the combustion chamber can be greatly increased at the same time. In order to avoid knocking, diesel or other non-detonation can be used. The fuel can also be controlled by introducing a bulking agent. In this configuration, a high pressure oxygen source can be provided in the system, the high pressure oxygen source being in communication with or in communication with the combustion chamber.

According to the disclosed technical solution, an explosion-discharge engine in which the exhaust gas temperature is close to the ambient temperature, lower than the ambient temperature, or substantially lower than the ambient temperature can be manufactured. In the structure in which the blast engine is set as a piston blast engine, in order to further improve efficiency, the combustion chamber and/or the work mechanism of the blast engine may be set to be thermally insulated or self-insulated. If the exhaust temperature is low to a certain extent, the self-insulation of the piston type exhaust engine can be achieved. The so-called self-insulation means that the heat of the high-temperature working medium after combustion will be transmitted to the cylinder wall, the piston top and the cylinder head at the beginning of the combustion explosion work. In the process of work, the temperature of the working medium will decrease rapidly, The heat that has been transmitted to the cylinder wall, the piston crown and the cylinder head at the beginning of the work is reabsorbed back into the working fluid, reducing the loss of heat and achieving the function equivalent to "insulation". In the self-insulated system, the contact with the working medium The outside of all the pressure-bearing walls (cylinder wall, piston top and cylinder head) can be insulated without heat transfer, and a small amount of heat transfer can be generated according to the temperature requirements of the pressure-bearing wall to reduce the temperature of the pressure-bearing wall; In the self-insulation system, a liquid passage or a liquid chamber may be provided in or outside the pressure-receiving wall contacting the working medium, and the liquid passage or the liquid chamber is filled with liquid to ensure The heat receiving uniformity of the pressure-receiving wall contacting the working medium and the heat storage property of the liquid optimize the change of the temperature of the gas in the cylinder, and a heat insulating layer may be disposed outside the liquid passage or the liquid chamber to reduce heat transfer to the environment.

The low-energy co-firing gas-filled blasting engine disclosed in the present invention can use hydrocarbon or carbon oxyhydroxide as fuel, for example, alcohol, and use an aqueous alcohol solution instead of the original fuel and expansion agent, not only can be antifreeze, but also can be used only An aqueous alcohol storage tank is used to replace the original fuel storage tank and expansion agent storage tank, and the ratio of the fuel and the expansion agent is adjusted by adjusting the concentration of the aqueous alcohol solution. In the low-energy co-firing gas-filled blasting engine disclosed in the present invention, an aqueous solution of hydrogen peroxide can be used instead of the oxidizing agent and the expanding agent, and the ratio of the oxidizing agent and the expanding agent can be adjusted by adjusting the concentration of the aqueous hydrogen peroxide solution, and a peroxidation can be used. The aqueous hydrogen storage tank replaces the oxidant storage tank (ie, the high pressure oxygen source) and the expander storage tank (ie, the expander source).

The low-energy co-firing gas-filled blasting engine disclosed by the invention can realize the non-differentiation of the fuel, because the gas charged in the combustion chamber of the blast engine is in a state of high pressure and low temperature, if it is charged into the blast engine The temperature of the gas is lower than the ignition point of the fuel. Any fuel injected into the combustion chamber or mixed with the high-pressure low-temperature gas in the combustion chamber can be ignited, which breaks the selectivity of the traditional engine and reduces the fuel. The fuel production cost can realize the diesel ignition type combustion mode, and even if the high pressure is high, the gasoline is not knocked due to the low temperature; not only that, even in the case of high temperature, the combustion speed can be adjusted by the expansion agent. Prevent knocking. In this form, it is possible to eliminate the classified production process of gasoline, diesel, and kerosene, and to produce only combustible hydrocarbons whose fluidity can meet the requirements.

The beneficial effects of the present invention are as follows:

The low-enthalpy mixed-combustion blasting engine disclosed by the invention achieves the purpose of high efficiency and low emission, has the characteristics of good load response, and greatly improves the environmental protection and energy saving of the engine.

DRAWINGS

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

2, 3 and 4 are schematic structural views of Embodiment 2 of the present invention;

Figure 5 is a schematic structural view of Embodiment 3 of the present invention;

Figure 6 is a schematic structural view of Embodiment 4 of the present invention;

Figure 7 is a schematic structural view of Embodiment 5 of the present invention; Figure 8 is a schematic structural view of Embodiment 6 of the present invention;

Figure 9 is a schematic structural view of Embodiment 7 of the present invention;

Figure 10 is a schematic structural view of Embodiment 8 of the present invention;

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

FIG. 13 is a schematic structural diagram of Embodiment 10 of the present invention; FIG.

Figure 14 is a schematic structural view of Embodiment 1 of the present invention;

Figure 15 is a schematic structural view of Embodiment 12 of the present invention;

Figure 16 is a schematic structural view of Embodiment 13 of the present invention;

Figure 17 is a schematic structural view of Embodiment 14 of the present invention;

18 is a schematic structural diagram of Embodiment 15 of the present invention;

FIG. 19 is a schematic structural diagram of Embodiment 16 of the present invention; FIG.

Figure 20 is a schematic structural view of Embodiment 17 of the present invention;

Figure 21 is a schematic structural view of Embodiment 18 of the present invention;

Figure 22 is a schematic structural view of Embodiment 196 of the present invention;

Figure 23 is a schematic structural view of Embodiment 20 of the present invention;

Figure 24 is a schematic structural view of Embodiment 21 of the present invention;

Figure 25 is a schematic structural view of Embodiment 22 of the present invention;

Figure 26 is a comparative explanatory diagram of the cycle of the disclosed and conventional internal combustion engine in the pressure and temperature coordinate system;

Figure 27 is a schematic view showing the comparison of the gongs of the disclosed circulating and conventional internal combustion engines;

Figure 28 is an explanatory diagram of a conventional external combustion cycle heated fluid;

Figure 29 is an explanatory view of a conventional internal combustion cycle heated fluid;

Figure 30 is a schematic view showing the relationship between the pressure P and the temperature T of the short-pressure air-filled engine scheme of the present invention; Figure 31 is a schematic structural view of Embodiment 23 of the present invention;

Figure 32 is a schematic structural view of Embodiment 24 of the present invention;

Figure 33 is a graph showing the relationship between the temperature T of the gas working fluid and the pressure P.

In the picture:

1 low pressure oxygen source, 2 compressor, 3 explosion engine, 4 hybrid desuperheater, 9 vehicles, 31 Short-pressure pneumatic engine, 300 combustion chamber, 23 gas storage tank, 32-way breaker, 30 continuous combustion chamber, 35-piston working mechanism, 38 control valve, 68 control mechanism, 66 hot-rolling adjustable fuel storage tank, 67 Thermal friction adjustable fuel inlet, 301 combustion chamber inflation port, 302 exhaust passage, 201 impeller compressor, 202 piston compressor, 1 16 high pressure oxygen source, 101 low pressure oxygen free source, 1 10 high pressure oxidant inlet , 1 15 oxygen control valve, 333 expansion agent source, 401 radiator, 402 cooling heat exchanger, 405 fuel inlet, 408 fuel control mechanism, 123 non-condensing return pipe, 335 carbon dioxide liquefier, 1 1 1 low pressure pure oxygen Source, 1 1 9 non-condensable gas storage tank, 3302 expansion agent heat absorption exhaust heat exchanger, 3303 spark plug, 3304 fuel injector, 4031 expansion agent inlet, 8000 power shaft, 4444 heat exchanger, 222333 first clutch, 222444 Second clutch, 3331 expansion agent control mechanism, 333444 third clutch, 3333 expansion agent liquefier. detailed description

Example 1

A low-energy co-firing gas-filled blasting engine as shown in FIG. 1 includes a compressor 2 and an explosion-discharge engine 3, the gas inlet of the compressor 2 is set as a low-pressure oxygen-containing gas inlet, and the low-pressure oxygen-containing gas inlet and low pressure The oxygen-containing source 1 is in communication, and the compressed gas outlet of the compressor 2 is in communication with the combustion chamber inflation port 301 of the combustion chamber 300 of the blast engine 3, and an exhaust passage 302 is provided on the combustion chamber 300. There is no timing relationship between the machine 2 and the blast engine 3, and the blast engine 3 outputs power to the compressor 2, and the pressure capacity at the compressed gas outlet of the compressor 2 is 10 MPa, wherein The blast engine 3 can be set as a piston blast engine or an impeller blast engine.

In specific implementation, in order to make the low-energy co-firing gas-filled blasting engine more efficient and environmentally friendly, adjust the pressure of the gas working fluid that is about to start work to above 15 MPa, and adjust the temperature of the gas working fluid that is about to start work to 2700K. Hereinafter, for example, the pressure of the gaseous working fluid to be started to work is 15 MPa, and the temperature is 1 200 K, so that the temperature and pressure of the gaseous working fluid to be started to work are in an adiabatic relationship; and/or in the low entropy mixing The gas-filled blast engine is in a steady state, adjusting a ratio of an intake volume flow rate of the gas inlet of the compressor 2 to an intake volume flow rate of the combustion chamber inflation port 301 to achieve a gas outlet of the compressor The pressure of the compressed gas reaches its pressure capacity limit of 10 MPa.

5MPa, 3MPa, 3. 5MPa 4 Pa, 4. 5MPa 5MPa, 5. 5MPa, 6MPa, 6. In addition to this embodiment, the pressure capacity at the outlet of the compressed gas of the compressor 2 can be set to 2. 5MPa, 3MPa, 3. 5MPa 4 Pa, 4. 5MPa 5MPa, 5. 5MPa, 6MPa, 6. 5MPa, 7MPa, 7. 5MPa, 8MPa, 8. 5MPa, 9MPa, 9. 5MPa, 10. 5MPa, 1 1 Pa, 1 1 . 5MPa, 1 2MPa, 1 2. 5MPa, 13MPa, 1 3. 5MPa, 14MPa, 14. 5MPa, 1 5MPa, 1 5. 5MPa, 1 6MPa, 1 6. 5MPa, 1 7MPa, 1 7. 5MPa, 18MPa, 1 8. 5MPa, 1 9MPa, 9.5 MPa, 20 MPa, 25 MPa, 30 MPa, 35 MPa, 40 MPa, 45 MPa, 50 MPa, 55 MPa or 60 MPa, by adjusting the intake volume flow rate of the gas inlet of the compressor 2 and the inlet of the combustion chamber inflation port 301 The ratio of gas volume flow is greater than 18, 20, 22, 24, 26, 28, 30, 32, 34, 36, 38, 40, 42, 44, 46, 48 or 50 to achieve the gas pressure at the outlet of the compressed gas, respectively The above pressure capacity limit is reached.

Example 2

The low-energy co-firing gas-filled blasting engine shown in FIG. 2, FIG. 3 and FIG. 4 includes a compressor 2, an explosion-discharge engine 3, and a high-pressure oxygen source 116. The gas inlet of the compressor 2 is set to a low pressure. An oxygen gas inlet, the low pressure oxygen-free gas inlet is in communication with the low pressure oxygen-free source 101, and the compressed gas outlet of the compressor 2 is in communication with the combustion chamber inflation port 301 of the combustion chamber 300 of the blast engine 3, An exhaust passage 302 is disposed on the combustion chamber 300, and there is no timing relationship between the compressor 2 and the blast engine 3, and the blast engine 3 outputs power to the compressor 2 at the compressor A high pressure oxidant inlet 1 10 is provided at the outlet of the compressed gas and/or on the combustion chamber 300 and/or on the communication passage between the compressed gas outlet of the compressor 2 and the combustion chamber 300. The high-pressure oxygen source 164 is connected to the high-pressure oxidant inlet 1 10 via an oxygen control valve 1 15 , and the pressure-receiving capacity at the compressed gas outlet of the compressor 2 is 15 MPa, wherein the explosion row Engine 3 can be set as a piston blast engine or blade Blowing row engine. Wherein, the high-pressure oxidant introduction port 1 10 in FIG. 2 is disposed at the compressed gas outlet of the compressor 2, and the high-pressure oxidant introduction port 1 10 in FIG. 3 is disposed on the combustion chamber 300, The high-pressure oxidant introduction port 1 in 4 is provided on a communication passage between the compressed gas outlet of the compressor 2 and the combustion chamber 300.

In specific implementation, in order to make the low-energy co-firing gas-filled blasting engine more efficient and environmentally friendly, adjust the pressure of the gas working fluid that is about to start work to above 15 MPa, and adjust the temperature of the gas working fluid that is about to start work to 2700K. Hereinafter, for example, the pressure of the gaseous working fluid to be started to work is 20 MPa, and the temperature is 1 500 K, so that the temperature and pressure of the gaseous working fluid to be started to work are in an adiabatic relationship, and/or the compressor 2 is adjusted. The ratio of the intake volume flow rate of the gas inlet to the intake volume flow rate of the combustion chamber inflation port 301 is such that the pressure of the compressed gas at the gas outlet of the compressor reaches its pressure capacity limit. 5MPa, 3MPa, 3. 5MPa, 4MPa, 4. 5MPa, 5MPa, 5. 5MPa, 6MPa, 6, in addition to this embodiment, the pressure capacity of the compressed gas outlet of the compressor 2 can be set to 2. 5MPa, 3MPa, 3. 5MPa, 4MPa, 4. 5MPa, 5MPa, 5. 5MPa, 6MPa, 6 · 5MPa, 7MPa, 7. 5MPa, 8MPa, 8. 5MPa, 9MPa, 9. 5MPa, 1 0MPa, 10. 5MPa, 1 1 MPa, 1 1 . 5MPa, 1 2MPa, 1 2. 5MPa, 13MPa, 13. 5MPa , 14MPa, 14. 5MPa, 15.5MPa, 1 6MPa, 1 6. 5MPa, 1 7MPa, 1 7. 5MPa, 18MPa, 1 8. 5MPa 1 9MPa, 1 9. 5MPa 20MPa, 25MPa, 30MPa, 35MPa, 40MPa 45MPa, 50MPa, 55MPa or 60 Pa, by adjusting the ratio of the intake volume flow rate of the gas inlet of the compressor 2 to the intake volume flow rate of the combustion chamber inflation port 301 is greater than 18, 20, 22, 24, 26, 28, 30, 32, 34, 36, 38, 40, 42, 44, 46, 48 or 50 to achieve the gas pressure at the outlet of the compressed gas respectively to reach the above pressure capacity limit.

Example 3

A low-entropy co-firing gas-filled blasting engine as shown in FIG. 5 differs from the first embodiment in that: the low-entropy co-firing blasting engine further includes an expansion agent source 333, and the combustion chamber 300 is provided with an expansion. The agent inlet 4031 is in communication with the expansion agent inlet 4031 via the expansion agent control mechanism 3331. The purpose of adding the expansion agent is to control (for example, reduce) the temperature of the working medium before the combustion of the fuel entering the combustion chamber, and also increase the number of working fluids and the working medium pressure after the fuel is burned, thereby improving the system. Thermal efficiency.

In a specific implementation, the expansion agent inlet 4031 may also be provided on the compressor 2 and/or at the compressed gas outlet of the compressor 2 and/or on the combustion chamber 300 and/or in the a compressed gas outlet of the compressor 2 and a communication passage between the combustion chambers 300; the blast engine 3 may be a piston blast engine or an impeller blast engine; for the low entropy co-firing The pneumatic blast engine is more efficient and environmentally friendly. Adjust the pressure of the gas working fluid that is about to start work to 15 MPa or more, and adjust the temperature of the gas working fluid that is about to start work to below 2700K. For example, adjust the gas working fluid that is about to start work. The pressure is 25 MPa, and the temperature is 1 700 K, so that the temperature and pressure of the gaseous working fluid to be started work conform to the adiabatic relationship, and/or the expansion agent control mechanism 3331 is controlled to adjust the amount of the expansion agent to be introduced and/or to adjust the introduction. The amount of fuel in the combustion chamber 300 is such that the temperature of the gas in the combustion chamber after combustion does not exceed the temperature of the compressed gas at the gas outlet of the compressor 2.

Example 4

A low-entropy co-firing gas-filled blast engine as shown in FIG. 6 differs from Embodiment 2 in that: The low enthalpy co-firing gas blasting engine further includes a swell agent source 333, on which a swell agent inlet 4031 is provided, the swell agent source 333 being in communication with the expansion agent inlet 4031 via an expansion agent control mechanism 3331. '

In a specific implementation, the expansion agent inlet 4031 may also be provided at the compressed gas outlet of the compressor 2 and/or on the combustion chamber 300 and/or at the compressed gas outlet of the compressor 2 In the communication channel between the combustion chambers 300; in order to make the low-energy co-firing gas-filled blasting engine more efficient and environmentally friendly, adjust the pressure of the gas working fluid that is about to start work to 15 MPa or more, and adjust the gas that is about to start work. The temperature of the working fluid is below 2700K. For example, the pressure of the gas working fluid to be started to work is 25 MPa, and the temperature is 1 700 K, so that the temperature and pressure of the gaseous working fluid to be started to work are in adiabatic relationship, and/or adjusted. a ratio of an intake volume flow rate of the gas inlet of the compressor 2 to an intake volume flow rate of the combustion chamber inflation port 301 to achieve a temperature of the compressed gas at a gas outlet of the compressor 2 to a material temperature limit Controlling the amount of expansion agent introduction by controlling the expansion agent control mechanism 3331 and/or adjusting the amount of fuel introduced into the combustion chamber 300 to achieve combustion in the combustion chamber The temperature does not exceed the limit at which the temperature of the compressed gas at the gas outlet of the compressor 2 reaches.

Example 5

A low-entropy co-firing gas-filled blasting engine as shown in FIG. 7 differs from the first embodiment in that: the low-entropy co-firing gas-filled blasting engine further includes a heat eliminator 4444, and the heat eliminator 4444 is disposed at Said on the compressor 2. The purpose of the heat extractor 4444 is to reduce the work consumed in the gas compression process, and also to increase the density of the gas, increase the oxygen content entering the combustion chamber, and increase the power of the engine.

In a specific implementation, the heat exhauster 4444 may also be disposed at the gas inlet of the compressor 2, and/or the heat exhauster 4444 is disposed on the compressor 2, and/or the heat exhauster 4444 is provided at the compressed gas outlet of the compressor 2, and/or the heat exhauster 4444 is provided on a communication passage between the compressed gas outlet of the compressor 2 and the combustion chamber 300.

Example 6

A low-entropy co-firing gas-filled blasting engine as shown in FIG. 8 differs from the first embodiment in that: the low-entropy co-firing blasting engine further includes a radiator 401 (ie, a heat extractor), the compressor 2 is set as the piston type compressor 202, and the pressure capacity of the compressed gas outlet of the piston type compressor 202 is 30 MPa, which is greater than the pressure of the compressed gas when the compression stroke of the conventional piston engine is completed (6-1 5 MPa). ), The compressed gas outlet of the piston compressor 202 is in communication with the combustion chamber inflation port 301 via the radiator 401, and the fuel of the explosion engine 3 is set to be gasoline, and is disposed in the combustion chamber of the explosion engine 3 The injector and the spark plug.

In addition to this embodiment, the pressure bearing capacity at the outlet of the compressed gas of the piston compressor 202 can be set to 2.5 MPa, 3 MPa, 3.5 MPa, 4 MPa, 4.5 MPa, 5 MPa, 5. 5 MPa, 6 MPa. , 6. 5MPa, 7MPa, 7. 5MPa, 8MPa 8. 5MPa, 9MPa, 9. 5MPa, 1 0MPa, 10. 5MPa, 1 1 MPa, 1 1 . 5MPa, 12MPa, 1 2. 5MPa, 13MPa, 1 3. 5MPa 1 4MPa, 14. 5MPa, 15MPa, 1 5. 5 Pa 1 6MPa, 1 6. 5MPa, 1 7MPa, 1 7. 5MPa, 1 8MPa, 1 8. 5MPa, 1 9MPa, 1 9. 5MPa, 20MPa, 25MPa 35MPa, 40MPa, 45MPa, 50MPa, 55MPa or 60MPa, by adjusting the ratio of the intake volume flow rate of the gas inlet of the piston type compressor 202 to the intake volume flow rate of the combustion chamber inflation port 301 is greater than 22, 24, 26 28, 30, 32, 34, 36, 38, 40, 42, 44, 46, 48 or 50 to achieve the gas pressure at the outlet of the compressed gas respectively to reach the above pressure capacity limit.

The heat sink of this embodiment has the same purpose and function as the heat extractor of the fifth embodiment.

Example 7

The low entropy co-firing blasting engine shown in Fig. 9 differs from the embodiment 6 in that the radiator 401 is provided as a temperature reducing heat exchanger 402.

Example 8

The low-energy co-firing gas-filled blasting engine shown in FIG. 10 is different from the embodiment 6 in that: the radiator 401 is replaced by a hybrid desuperheater 4, and the hybrid desuperheater 4 is provided with an expansion agent inlet 4031. The expansion agent source 333 is in communication with the expansion agent inlet 4031 via the expansion agent control mechanism 3331 and communicates with the combustion chamber inflation port 30.1 via the hybrid desuperheater 4, the temperature and pressure of the gaseous working fluid that is about to start work. Meet the class of adiabatic relationship. Since the compressed air compressed by the compressor has a large pressure and a high temperature, after the lower temperature expansion agent is added, the temperature of the compressed gas is lowered, the pressure is increased, and the excess temperature is reduced, but the system is The external heat rejection is not increased, and the thermal efficiency of the system is improved. Therefore, the hybrid desuperheater of this embodiment is substantially different from the heat exchanger of the fifth embodiment.

Example 9

The low-energy co-firing gas-filled blast engine shown in FIGS. 1 1 and 12 is different from the embodiment 8 in that the expansion agent source 333 is connected to the expansion agent inlet 4031 via a low-quality heat source heat exchanger. and The hybrid desuperheater 4 is further connected to the combustion chamber inflation port 301.

Wherein, in FIG. 11 , an expansion agent heat absorption high pressure passage 331 is disposed on the combustion chamber wall of the explosion exhaust engine 3, and the low quality heat source heat exchanger is set as the expansion agent heat absorption high pressure passage 331, and the expansion agent is The heat sinking heat in the expansion agent heat absorption passage 331 is mixed with the high temperature and high pressure gas in the hybrid type temperature reducer 4 to cool the high temperature and high pressure gas. The fuel of the blast engine 3 is set to diesel fuel, and the temperature of the gas in the combustion chamber immediately after the combustion is set to be lower than the ignition point of the diesel fuel, and the spark plug 3303 is provided in the combustion chamber of the blast engine 3.

In the specific implementation, the spark plug may not be provided, and the temperature of the gas in the combustion chamber is set to be higher than the ignition point of the diesel fuel, and the compression ignition mode of the conventional diesel engine is adopted.

In the exhaust passage 302 of the blast engine 3, an expansion agent heat absorption exhaust heat exchanger 3302 is provided in FIG. 12, and the low-quality heat source heat exchanger is set as the expansion agent heat absorption exhaust heat. In the exchanger 3302, the expansion agent absorbs heat in the expansion agent endothermic exhaust heat exchanger 3302, and then mixes with the high temperature and high pressure gas in the hybrid desuperheater 4 to cool the high temperature and high pressure gas. The fuel of the blast engine 3 is set to be gasoline, and the temperature of the gas in the combustion chamber at the time of combustion is set to be higher than the ignition point of the gasoline, and the fuel injector 3304 is provided in the combustion chamber of the blast engine 3 to The injector 3304 directly injects gasoline combustion expansion work in the combustion chamber, and realizes the compression ignition method like the conventional diesel engine, thereby eliminating the ignition system of the conventional gasoline engine.

Example 10

A low-entropy co-firing gas-filled blasting engine as shown in FIG. 13 differs from the embodiment 6 in that a fuel introduction is provided on a communication passage between the compressed gas outlet of the compressor 2 and the combustion chamber 300. Port 405, the fuel introduction port 405 is in communication with a fuel source via a fuel control mechanism 408.

In a specific implementation, it may also be at the compressed gas outlet of the compressor 2 and/or on the combustion chamber 300 and/or between the compressed gas outlet of the compressor 2 and the combustion chamber 300. A fuel introduction port 405 is provided in the communication passage. Due to the early introduction of the fuel, the fuel and the compressed gas (oxidant) are mixed for a sufficient period of time, so that the purpose of uniform mixing, sufficient combustion, power and emissions is easily achieved.

Example 1 1

The low entropy co-firing gas explosion exhaust engine shown in FIG. 14 differs from the embodiment 9 in that: The low-entropy co-firing gas-filled blast engine further includes a switch 32, and a gas storage tank 23 is disposed on the gas flow between the compressor 2 and the blast engine 3, and the blast engine 3 is The switch 32 outputs power to the compressor 2, and the expander source 333 communicates with the expander inlet 4031 via a low-quality heat source heat exchanger provided on the compressor 2 and is cooled by the hybrid The device 4 is in communication with the combustion chamber inflation port 301.

The purpose of providing the switch 32 is to cut off the power output of the blast engine 3 to the compressor 2 by means of the switch 32 when the output of the blast engine 3 is required to be increased in an instant, using gas storage. The compressed gas in tank 23 provides oxidant to blast engine 3, increasing the net power output of the blast engine.

Example 1 2

The low-energy co-firing gas-filled blasting engine shown in FIG. 15 is different from the embodiment 6 in that: the radiator 401 is replaced by a hybrid desuperheater 4, and the low-entropy co-firing blasting engine further includes a condensate return pipe 1 23 and a carbon dioxide liquefier 335, the carbon dioxide liquefier 335 is disposed on the exhaust passage 302 of the blast engine 3, and the low-pressure oxygen-containing source 1 is set as a low-pressure pure oxygen source 1 1 1 The low pressure pure oxygen source 111 is in communication with a low pressure oxygen-containing gas inlet of the compressor 2, and the non-condensable gas return pipe 1 23 communicates with the non-condensable gas outlet of the carbon dioxide liquefier 335 and the compressor 2 a gas inlet, the compressor 2, the hybrid desuperheater 4, the combustion chamber 300, and the carbon dioxide liquefier 335 constitute a non-condensable circulation flow closed passage, in the compressor 2, a hybrid desuperheater 4. The circulating closed passage formed by the combustion chamber 300 of the blast engine 3 and the carbon dioxide liquefier 335 is filled with non-condensable gas, and the non-condensable gas is in the compressor 2, the hybrid desuperheater 4, Explosive engine Circulating between the combustion chamber 300 of 3 and the carbon dioxide liquefier 335, the communication passage between the blast engine 3 and the carbon dioxide liquefier 335 is provided with a condensed water outlet 1 9 and the condensed water outlet 1 9 The road is in communication with the condensate storage tank 20 such that water vapor generated by combustion of the fuel is prevented from being frozen into ice in the carbon dioxide liquefier 335, causing clogging of the piping and affecting the purity of the recovered liquid carbon dioxide. The recovered carbon dioxide can be used in agricultural cultivation, industry, food industry, medical and cultural entertainment.

Alternatively, in a specific implementation process, the hybrid desuperheater 4 may not be provided for compactness. Example 13 A low-entropy co-firing gas-filled blasting engine as shown in FIG. 16 differs from the second embodiment in that: the low-entropy co-firing gas blasting engine further includes a non-condensing gas return pipe 1 23 and a carbon dioxide liquefier 335. The carbon dioxide liquefier 335 is disposed on the exhaust passage 302 of the blast engine 3, and the low pressure oxygen-free source 101 is set as a non-condensable storage tank 1 1 9 , and the non-condensable storage tank 1 1 9 The low pressure oxygen-free gas inlet of the compressor 2 is in communication, and the non-condensable gas return pipe 123 communicates with the non-condensable gas outlet of the carbon dioxide liquefier 335 and the non-condensable gas storage tank 1 1 9 , the compressor 2 The combustion chamber 300 of the blast engine 3, the carbon dioxide liquefied gas 335 and the non-condensable gas storage tank 1 19 constitute a non-condensable gas circulation flow closed passage, in the compressor 2, the blast engine 3 The combustion chamber 300, the carbon dioxide liquefier 335 and the non-condensable gas storage tank 1 9 are filled with a non-condensable gas in the circulation closed passage, and the non-condensable gas is in the compressor 2, the explosion a combustion chamber 300 of the exhaust engine 3, the carbon dioxide liquefier 335, and the non-condensable gas storage tank 1 1 9 Between cycles.

Example 14

A low-entropy co-firing gas-filled blasting engine as shown in FIG. 17 differs from the first embodiment in that: a gas storage tank is disposed on a gas flow communication passage between the compressor 2 and the blast engine 3 23, the power output shaft of the blast engine 3 is connected to the power input shaft of the compressor 2 via a first clutch 222333, and the power output shaft of the blast engine 3 passes through the second clutch 222444 and the power shaft of the vehicle 9. 8000 is connected, the power input shaft of the compressor 2 is connected to the power shaft 8000 of the vehicle 9 via a third clutch 333444; the first clutch 222333, the second clutch 222444 and the third clutch 333444 are controlled The device coordination work enables switching between various operating states to meet the requirements of different operating modes of the system. For example, the first working state is that the first clutch 222333 and the second clutch 222444 are in an engaged state, the third clutch 333444 In a separated state or a combined state, in which the blast engine 3 outputs power to the compressor 2 and the vehicle 9; the second working state is the first clutch The 222333 is in an engaged state, and the third clutch 333444 and the second clutch 222444 are in a disengaged state, in which the blast engine 3 outputs power only to the compressor 2; the third working state is The first clutch 222333 and the second clutch 222444 are in a disengaged state, and the third clutch 333444 is in an engaged state, in which the vehicle 9 uses its kinetic energy to output power to the compressor 2; The state is that the first clutch 222333 and the third clutch 333444 are in a separated state. The second clutch 222444 is in an engaged state, in which state the blast engine 3 outputs power to the vehicle 9 without outputting power to the compressor 2, in a state in which the gas storage tank is utilized The compressed gas in 23 supplies compressed gas to the blast engine 3, and this state can instantaneously increase the net output power of the blast engine 3 to meet the requirement of instantaneous load increase; the fifth working state is The first clutch 222333, the second clutch 222444, and the third clutch 333444 are all in a separated state. In this working state, the blast engine 3 does not output power, and other working states are not described again.

Example 15

A low-entropy co-firing blasting engine as shown in FIG. 18 differs from Embodiment 6 in that: the low-entropy co-firing blasting engine further includes a thermally friction-adjustable fuel storage tank 66, in the combustion chamber The hot friction adjustable fuel inlet 67 is connected to the hot friction adjustable fuel inlet 66 via the control mechanism 68, and the hot friction adjustable fuel storage tank 66 is provided. The thermomotive adjustable fuel is mixed with the gas compressed by the compressor 2 via the thermomotive adjustable fuel introduction port 67. The purpose of setting the thermo-motor adjustable fuel is to replace the original fuel and expansion agent with the thermo-motor adjustable fuel, not only to prevent freezing, but also to replace the original fuel storage tank and expansion with only one thermal-motor adjustable fuel storage tank. The tank is used, and the amount of the fuel and the expander required is changed by adjusting the concentration of the heat-adjustable fuel, and the structure is simple and the cost is low. The thermomotive adjustable fuel may be an aqueous solution of an alcohol such as an aqueous solution of ethanol, an aqueous solution of methanol, or the like, or a mixed solution of an alcohol, a hydrocarbon and water such as a mixed solution of ethanol, water and diesel, and a mixture of ethanol, water and gasoline. a solution, etc., which may be a mixture of several different alcohols, hydrocarbons, and expansion agents, such as ethanol, methanol, diesel, gasoline, water, and liquid carbon dioxide; It may be composed of a plurality of fuels, and the expansion agent may also be composed of a plurality of expansion agents.

Optionally, the thermo-motor adjustable fuel inlet 67 may also be disposed on the compressor 2 and/or at the compressed gas outlet of the compressor 2 and/or at the pressure of the compressor 2 The gas passage is connected to the communication passage between the combustion chamber 300.

Example 1 6

A low-entropy co-firing gas-filled blasting engine as shown in FIG. 19 differs from the first embodiment in that a expansion agent is provided on a communication passage between the compressed gas outlet of the compressor 2 and the combustion chamber 300. Enter a port 4031, the expansion agent source 333 is in communication with the expansion agent inlet 4031 via an expansion agent control mechanism 3331, and adjusts an intake volume flow rate of the gas inlet of the compressor 2 and an intake volume of the combustion chamber inflation port 301. The ratio of the flow rate is such that the temperature of the compressed gas at the gas outlet of the compressor 2 reaches the environmental protection temperature limit or the material temperature limit, and the amount of the expansion agent introduced is adjusted by the expansion agent control mechanism 3331 to realize the combustion in the combustion chamber. The temperature does not rise or does not increase significantly. The expansion agent in the expansion agent source 333 is set to a gas liquefaction.

Alternatively, the expander inlet 4301 may also be provided at the compressed gas outlet of the compressor 2 and/or on the combustion chamber 300.

Example 1 7

The low-entropy co-firing blasting engine shown in FIG. 20 differs from the first embodiment in that: a combustion chamber of the blasting engine 3 is connected to four working mechanisms, and the blasting engine 3 is combusted. The chamber is set as a continuous combustion chamber 30, the working mechanism of the blast engine 3 is set as a piston type working mechanism 35, and a control valve 38 is provided between the continuous combustion chamber 30 and the piston type working mechanism 35. The working fluid in the continuous combustion chamber 30 is intermittently introduced into the piston type working mechanism 35.

In a specific implementation, the compressor 2 and the blast engine 3 may be simultaneously or individually set as an adiabatic mechanism; the work mechanism may be set to one or more; in a structure in which a plurality of work mechanisms are provided The work mechanism can be set to the same type of mechanism, or can be set to different types of mechanisms, such as a piston work structure and an impeller work mechanism.

Example 18

The low-entropy co-firing gas-filled blasting engine shown in FIG. 21 differs from the embodiment 6 in that: the compressor 2 is set as a dual-outlet compressor 2000 that outputs an intermediate-pressure compressed gas and a high-pressure compressed gas, the double The high pressure compressed gas outlet 2001 of the outlet compressor 2000 is connected to the combustion chamber inflation port 301 of the blast engine 3 via the hybrid desuperheater 4, and the intermediate pressure combustion chamber inflation port 3301 is provided on the blast engine 3, and the double outlet compressor 2000 The medium-pressure compressed gas outlet 2002 communicates with the intermediate-pressure combustion chamber inflation port 3301, and the high-pressure compressed gas charged into the combustion chamber 300 through the high-pressure compressed gas outlet 2001 undergoes a combustion chemical reaction with the fuel to perform external expansion work. During the expansion work, when the working fluid pressure in the cylinder is less than the pressure of the medium pressure compressed gas, the medium pressure compressed gas is charged into the cylinder through the intermediate pressure combustion chamber inflation port 3301, and then Increasing the pressure of the working fluid in the cylinder at one time, thereby improving the operation of the blast engine 3 Functionality.

Example 1 9

The low-entropy co-firing gas-filled blasting engine shown in FIG. 22 differs from the embodiment 18 in that: the compressor 2 is configured as a dual-outlet compressor 2000 that outputs an intermediate-pressure compressed gas and a high-pressure compressed gas. The high pressure compressed gas outlet 2001 of the dual outlet compressor 2000 is connected to the combustion chamber inflation port 301 of the blast engine 3 via the temperature reducing heat exchanger 402, and the medium pressure combustion chamber inflation port 3301 is provided on the blast engine 3, and the double outlet The medium-pressure compressed gas outlet 2002 of the compressor 2000 is heated by the cooling heat exchanger 402 to communicate with the intermediate-pressure combustion chamber inflation port 3301, and the medium-pressure compressed gas having a lower temperature and a lower density is cooled to a higher temperature and a higher density. The high high pressure compressed gas has no loss of heat within the system, but the amount of total gas entering the blast engine 3 is increased, improving the functionality and efficiency of the low entropy co-firing blast engine.

Example 20

The low-energy co-firing gas-filled blasting engine shown in FIG. 23 differs from the embodiment 18 in that: the compressor 2 is configured as a dual-outlet compressor 2000 that outputs an intermediate-pressure compressed gas and a high-pressure compressed gas. The medium-pressure compressed gas outlet 2002 of the dual-outlet compressor 2000 is heated by a low-quality heat source heat exchanger to communicate with the intermediate-pressure combustion chamber inflation port 3301, and the low-quality heat source heat exchanger is set to be a combustion of the explosion-discharge engine 3. An intermediate pressure compressed gas heat absorption passage 332 on the chamber wall, and an intermediate pressure compressed gas heat absorption passage 332 on the combustion chamber wall of the explosion exhaust engine 3 serves as a heat source to supply heat to the medium pressure compressed gas to improve the low entropy The thermal efficiency of the co-firing blast engine, which outputs power to the dual outlet compressor 2000 via the damper 32.

Example 21

The low-entropy co-firing gas-filled blasting engine shown in FIG. 24 differs from the embodiment 6 in that: the piston-type compressor 202 is set as the impeller-type compressor 201, and the impeller-type compressor 201 is compressed. The pressure capacity at the gas outlet is 10 MPa, which is greater than the gas pressure at the outlet of the compressed gas of the conventional impeller compressor; the radiator 401 is set as the hybrid desuperheater 4; the detonation engine 3 is set to be a turbine type The blast engine, the blast engine 3 outputs power to the impeller compressor 201, and adjusts an intake volume flow rate of the gas inlet of the impeller compressor 201 and an intake volume flow rate of the combustion chamber inflation port 301. The ratio is such that the gas pressure at the outlet of the compressed gas reaches 10 MPa. In addition to this embodiment, the pressure-receiving capacity at the compressed gas outlet of the impeller-type compressor 201 may be set to 2.5 MPa, 3 MPa, 3.5 MPa, 4 MPa, 4.5 MPa, 5 MPa, 5.5 MPa, 6 MPa, 6.5 MPa, 7MPa, 7.5MPa, 8MPa, 8.5MPa, 9MPa, 9.5MPa, 10.5MPa, 11MPa, 11.5MPa, 12MPa, 12.5MPa, 13MPa, 13.5MPa, 14MPa, 14.5MPa, 15MPa, 15.5MPa, 16MPa, 16. 5MPa, 17MPa , 17.5 MPa, 18 MPa, 18.5 MPa, 19 MPa, 19.5 MPa, 20 MPa, 25 MPa, 30 MPa, 35 MPa, shed Pa, 45 MPa, 50 MPa, 55 MPa or 60 MPa, by adjusting the volume flow of the intake gas of the gas inlet of the impeller-type compressor 201 The ratio of the volumetric flow of the intake air to the combustion chamber inflation port 301 is greater than 18, 20, 22, 24, 26, 28, 30, 32, 34, 36, 38, 40, 42, 44, 46, 48 or 50. The gas pressure at the outlet of the compressed gas is achieved to reach the above pressure capacity limit.

Example 22

The low entropy co-firing blasting engine shown in FIG. 25 differs from the embodiment 8 in that an expansion liquefier 3333 is provided on the exhaust passage 302 of the blast engine 3, and the expansion liquefier The liquid outlet of 3333 is in communication with the expander source 333 to effect recycling of the expander.

Example 23

A low-energy co-firing gas-filled blasting engine as shown in FIG. 31, comprising a compressor 2 and a short-pressure gas-filled engine 31, the gas inlet of the compressor 2 being set as a low-pressure oxygen-containing gas inlet, and the low-pressure oxygen-containing gas inlet Connected to the low pressure oxygen-containing source 1 , the compressed gas outlet of the compressor 2 is in communication with the combustion chamber inflation port 301 of the combustion chamber 300 of the short-pressure inflatable engine 31, and an exhaust passage is provided in the combustion chamber 300 302, there is no timing relationship between the compressor 2 and the short-pressure pneumatic engine 31, and the short-pressure inflatable engine 31 outputs power to the compressor 2, and the compressed gas outlet of the compressor 2 The pressure bearing capacity is 1 MPa, the pressure capacity of the combustion chamber 300 is 2.5 MPa, and the absolute amount of volume reduction of the short-pressure pneumatic engine 31 during the compression stroke is smaller than the absolute volume increase of the expansion power stroke. Preferably, the compressor 2 can be configured as an impeller compressor 201 or a piston compressor 202.

In addition to this embodiment, the pressure bearing capacity at the compressed gas outlet of the compressor 2 can also be set to

I. 5MPa, 2MPa, 2.5MPa, 3MPa, 3.5MPa, 4MPa, 4, 5MPa, 5MPa, 5.5MPa, 6MPa, 6.5MPa, 7MPa, 7.5 Pa 8MPa, 8.5MPa, 9MPa, 9.5MPa, 10MIPa, 10.5 Pa 11MPa,

II. 5MPa, 12MPa, 12.5MPa, 13MPa, 13.5MPa, 14MPa, 14.5MPa or 15MPa; The pressure bearing capacity of the combustion chamber 300 can be set to 3 MPa, 3.5 MPa, 4 MPa, 4.5 MPa, 5 MPa, 5.5 MPa, 6 MPa, 6.5 MPa, 7 MPa, 7.5 MPa, 8 Pa 8.5 MPa, 9 MPa, 9.5 MPa, 10 MPa, 10.5 MPa, 11 MPa, 11.5 Pa, 12 MPa, 12.5 MPa, 13 MPa, 13.5 MPa, 14 MPa, 14.5 MPa or 15 MPa.

In specific implementation, in order to make the low-energy co-firing gas-filled blasting engine more efficient and environmentally friendly, adjust the pressure of the gas working fluid that is about to start work to 15 MPa or more, and adjust the temperature of the gas working fluid that is about to start work to below 2700K. For example, the gas pressure of the gas working medium to be started to work is 20 MPa, and the temperature is 1500 K, so that the temperature and pressure of the gas working fluid to be started to work are in an adiabatic relationship, and/or in the low entropy co-firing gas explosion. The exhaust engine is under stable conditions, and the ratio of the intake volume flow rate of the gas inlet of the compressor 2 to the intake volume flow rate of the combustion chamber inflation port 301 is adjusted to achieve compression at the gas outlet of the compressor. The pressure of the gas reaches its pressure capacity limit, which is greater than the compression ratio of the conventional engine, and the gas pressure of the combustion chamber charged into the short pressure range gas engine 31 is greater than that of the conventional engine compression stroke. The state of stress.

Example 24

The low-energy co-firing gas-filled blasting engine shown in FIG. 32 includes a low-pressure oxygen-free source 101, a compressor 2, a short-pressure gas-filled engine 31, and a high-pressure oxygen source 116, and the gas inlet of the compressor 2 is set to a low pressure. An oxygen gas inlet, the low pressure oxygen-free gas inlet is in communication with the low pressure oxygen-free source 101, and the compressed gas outlet of the compressor 2 is in communication with the combustion chamber inflation port 301 of the combustion chamber 300 of the short-pressure pneumatic engine 31, An exhaust passage 302 is provided in the combustion chamber 300, and there is no timing relationship between the compressor 2 and the short-pressure pneumatic engine 31, and the short-pressure inflatable engine 31 outputs power to the compressor 2. a high-pressure oxidant introduction port 110 is disposed at a compressed gas outlet of the compressor 2, and the high-pressure oxygen source 116 is in communication with the high-pressure oxidant introduction port 110 via an oxidant control valve 115; the compressed gas of the compressor 2 The pressure capacity at the outlet is 1 MPa, the pressure capacity of the combustion chamber 300 is 2.5 MPa, and the absolute amount of volume reduction of the short-pressure pneumatic engine 31 during the compression stroke is smaller than that of the expansion stroke One of the absolute increase in the amount of two.

Alternatively, the compressor 2 may be provided as an impeller compressor 201 or a piston compressor 202. In addition to this embodiment, the pressure bearing capacity at the compressed gas outlet of the compressor 2 may be set to 1.5 MPa, 2 MPa, 2.5 MPa, 3 MPa, 3.5 MPa, 4 MPa, 4.5 MPa, 5 MPa, 5.5 MPa, 6 MPa, 6.5MPa, 7MPa, 7.5MPa, 8MPa, 8.5MPa, 9MPa, 9.5MPa, 10MPa, 10.5MPa, 11MPa, 11.5MPa, 12MPa, 12.5MPa 13MPa, 13.5MPa, 14MPa, 14.5MPa or 15MPa; The pressure-receiving capacity of the chamber 300 is set to 3 MPa, 3.5 MPa, 4 MPa, 4.5 MPa, 5 MPa, 5.5 MPa, 6 MPa, 6.5 MPa, 7 MPa, 7.5 MPa, 8 MPa, 8.5 MPa, 9 MPa, 9.5 MPa, 10 MPa, 10.5 MPa, 11 MPa, 11.5 MPa, 12 MPa, 12.5 MPa, 13 MPa, 13.5 MPa, 14 MPa, 14.5 MPa or 15 MPa.

In specific implementation, in order to make the low-energy co-firing gas-filled blasting engine more efficient and environmentally friendly, adjust the pressure of the gas working fluid that is about to start work to 15 MPa or more, and adjust the temperature of the gas working fluid that is about to start work to below 2700K. For example, adjusting the gas working fluid to be started to work is 15 MPa, and the temperature is 1200 K, so that the temperature and pressure of the gaseous working fluid to be started to work are in an adiabatic relationship; and/or in the low-entropy co-firing gas explosion The exhaust engine is under stable conditions, and the ratio of the intake volume flow rate of the gas inlet of the compressor 2 to the intake volume flow rate of the combustion chamber inflation port 301 is adjusted to achieve compression at the gas outlet of the compressor. The pressure of the gas reaches its pressure capacity limit, which is greater than the compression ratio of the conventional engine, and the gas pressure of the combustion chamber charged into the short pressure range gas engine 31 is greater than that of the conventional engine compression stroke. a state of pressure; also at the compressed gas outlet of the compressor 2 and/or on the combustion chamber 300 and/or at the pressure 2 and the compressed gas outlet of the upper combustion chamber communicating passage 300 is provided between the high pressure oxidizer inlet 110, to effect thorough mixing of the oxidant with the fuel to improve combustion efficiency, thereby increasing the efficiency of the engine.

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

Claims

Rights request

A low-energy co-firing gas-filled blast engine comprising a compressor (2) and a blast engine (3), characterized in that: the gas inlet of the compressor (2) is set as a low-pressure oxygen-containing gas inlet, The compressed gas outlet of the compressor (2) is in communication with a combustion chamber inflation port (301) of the combustion chamber (300) of the blast engine (3), at the compressed gas outlet of the compressor (2) The pressure bearing capacity is greater than 1 MPa, and there is no timing relationship between the compressor (2) and the blast engine (3).

2. A low-entropy co-firing gas-filled blast engine comprising a compressor (2), an blast engine (3) and a high-pressure oxygen source (116), wherein: the gas inlet of the compressor (2) is set a low pressure oxygen-free gas inlet, the compressed gas outlet of the compressor (2) is in communication with a combustion chamber inflation port (301) of the combustion chamber (300) of the blast engine (3), the compressor (2) The pressure capacity at the outlet of the compressed gas is greater than 1 MPa, and there is no timing relationship between the compressor (2) and the blast engine (3) at the compressed gas outlet of the compressor (2) And/or providing a high pressure oxidant inlet (110) on the combustion chamber (300) and/or in a communication passage between the compressed gas outlet of the compressor (2) and the combustion chamber (300) The high pressure oxygen source (116) is in communication with the high pressure oxidant inlet (110).

3. A low-entropy co-firing gas-filled blast engine comprising a compressor (2) and a short-pressure gas-filled engine (31), characterized in that: the gas inlet of the compressor (2) is set as a low-pressure oxygen-containing gas inlet The compressed gas outlet of the compressor (2) is in communication with a combustion chamber inflation port (301) of the combustion chamber (300) of the short-pressure pneumatic engine (31), and the compression of the compressor (2) The pressure bearing capacity at the gas outlet is greater than 1 MPa, and there is no timing relationship between the compressor (2) and the short pressure range gas engine (31).

4. A low-entropy co-firing gas-filled blast engine comprising a compressor (2), a short-pressure gas-filled engine (31), and a high-pressure oxygen source (116), characterized by: a gas inlet of the compressor (2) a low pressure oxygen-free gas inlet, the compressed gas outlet of the compressor (2) being in communication with a combustion chamber inflation port (301) of the combustion chamber (300) of the short-pressure pneumatic engine (31), the pressure gas The pressure capacity at the outlet of the compressed gas of the machine (2) is greater than 1 MPa, and there is no timing relationship between the compressor (2) and the short-pressure inflatable engine (31), in the compressor (2) a high pressure oxidant at the outlet of the compressed gas and/or on the combustion chamber (300) and/or on the communication passage between the compressed gas outlet of the compressor (2) and the combustion chamber (300) The inlet (110), the high pressure oxygen source (116) is in communication with the high pressure oxidant inlet (110).

The low-entropy co-firing blasting engine according to claim 1 or 2, characterized in that: the blasting engine (3) is set as a piston blasting engine or an impeller blasting engine.

6. The low-entropy co-firing blasting engine according to claim 1 or 2, wherein: the low-entropy co-firing blasting engine further comprises a switch (32), the blasting engine (3) The compressor (2) outputs power via the switch (32).

7. The low-entropy co-firing gas-filled blasting engine according to claim 1 or 2, wherein: a gas is disposed on the gas flow communication passage between the compressor (2) and the blast engine (3) Storage tank

(23), the blast engine (3) is connected to the compressor (2) via a first clutch (222333), and the blast engine (3) is connected to the vehicle (9) via a second clutch (222444) The compressor (2) is coupled to the vehicle (9) via a third clutch (333444); the first clutch

(222333), the second clutch (222444) and the third clutch (333444) are coordinated by a control device.

A low-entropy co-firing blasting engine according to claim 1 or 2, wherein: said combustion chamber (300) is connected to two or more working mechanisms.

9. The low-entropy co-firing blasting engine according to claim 1 or 2, wherein: said combustion chamber (300) is set as a continuous combustion chamber (30), and said blasting engine (3) performs work The mechanism is set as a piston type working mechanism (35), and a control valve (38) is disposed between the continuous combustion chamber (30) and the piston type working mechanism (35) to be in the continuous combustion chamber (30) The working fluid is introduced into the piston working mechanism (35) in a positive relationship.

10. A low-entropy co-firing blasting engine according to claim 1 or 2, characterized in that said compressor (2) and said blast engine (3) are simultaneously or individually provided as adiabatic mechanisms.

The low-energy co-firing gas-filled blasting engine according to claim 1 or 3, wherein: the low-entropy co-firing gas blasting engine further comprises a non-condensing gas return pipe (123) and a carbon dioxide liquefier (335) And a low pressure pure oxygen source (111), the carbon dioxide liquefier (335) is disposed on the exhaust passage (302), and the low pressure pure oxygen source (111) is in communication with the compressor (2), the non-condensing a gas return pipe (123) communicating with a non-condensable gas outlet of the carbon dioxide liquefier (335) and a gas inlet of the compressor (2), the compressor (2), the combustion chamber (300), and the The carbon dioxide liquefier (335) constitutes a non-condensable circulation flow closed channel.

12. The low-entropy co-firing blasting engine according to claim 1, 2, 3 or 4, wherein: said low-entropy co-firing blasting engine further comprises a swell agent source (333), said squeezing gas And/or at the compressed gas outlet of the compressor (2) and/or on the combustion chamber (300) and/or at the compressed gas outlet of the compressor (2) An expansion agent inlet (4031) is provided in the communication passage with the combustion chamber (300), and the expansion agent source (333) is in communication with the expansion agent inlet (4031).

13. The low-entropy co-firing blasting engine according to claim 1, 2, 3 or 4, wherein: said low-entropy co-firing blasting engine further comprises a heat eliminator (4444), said heat rejection a device (4444) is provided at the gas inlet of the compressor (2), and/or the heat exchanger (4444) is provided on the compressor (2), and/or the heat radiator (4444) Provided at a compressed gas outlet of the compressor (2), and/or the heat exchanger (4444) is provided at a compressed gas outlet of the compressor (2) and the combustion chamber (300) On the communication channel between.

14. The low-entropy co-firing blasting engine according to claim 1, 2, 3 or 4, characterized in that - said low-entropy co-firing blasting engine further comprises a hybrid desuperheater (4), said plenum The compressed gas outlet of the machine (2) is in communication with the combustion chamber inflation port (301) via the hybrid desuperheater (4); the hybrid desuperheater (4) is in communication with the expansion agent source (333).

15. A low-entropy co-firing blasting engine according to claim 1, 2, 3 or 4, characterized by: at the compressed gas outlet of said compressor (2) and/or in said combustion chamber (300) Providing a fuel introduction port (405) on and/or in a communication passage between the compressed gas outlet of the compressor (2) and the combustion chamber (300), the fuel introduction port (405) being fueled The control mechanism (408) is in communication with the fuel source.

16. The low entropy co-firing blasting engine according to claim 1, 2, 3 or 4, characterized by: a compressed gas outlet of said compressor (2) and said combustion chamber inflation port (301) A gas storage tank (23) is disposed between the gas streams.

17. The low-entropy co-firing blasting engine according to claim 1, 2, 3 or 4, wherein: said low-entropy co-firing blasting engine further comprises a thermally friction adjustable fuel storage tank (66), The connection between the pressurization and/or the compressed gas outlet of the compressor (2) and the combustion chamber (300) A hot friction adjustable fuel inlet (67) is disposed on the passage, and the hot friction adjustable fuel inlet (67) is in communication with the hot friction adjustable fuel storage tank (66) via a control mechanism (68).

18. The low-entropy co-firing gas-filled blasting engine according to claim 1, 2, 3 or 4, wherein: said compressor (2) is set as a piston compressor (202) or an impeller type compressor (201) ).

19. A low-entropy co-firing blasting engine according to claim 3 or 4, wherein: said combustion chamber (300) has a pressure bearing capacity greater than 2.5 MPa.

20. A low-entropy co-firing blasting engine according to claim 3 or 4, wherein: said short-pressure pneumatic engine (31) has an absolute amount of volume reduction during compression stroke and an expansion power stroke The ratio of the absolute increase in volume is less than 0.9.

21. The low-entropy co-firing blasting engine according to claim 3 or 4, wherein: said low-entropy co-firing blasting engine further comprises a switch (32), said short-pressure inflatable engine ( 31) The compressor (2) is powered by the switch (32).

22. The low-entropy co-firing gas-filled blasting engine according to claim 18, wherein: the intake air volume flow of the gas inlet of the impeller-type compressor (201) and the inlet of the combustion chamber inflation port (301) The ratio of the gas volume flow rate is greater than 18; the ratio of the intake volume flow rate of the gas inlet of the piston compressor (202) to the intake volume flow rate of the combustion chamber inflation port (301) is greater than 22.

23. The low-entropy co-firing blasting engine according to claim 2 or 4, wherein: the low-entropy co-firing blasting engine further comprises a non-condensing gas return pipe (123) and a carbon dioxide liquefier (335). And a non-condensable storage tank (119), the carbon dioxide liquefier (335) is disposed on the exhaust passage (302), the low pressure oxygen-free gas inlet and the non-condensable gas storage tank (119) of the compressor (2) Connected, the non-condensable gas return pipe (123) communicates with the non-condensable gas outlet of the carbon dioxide liquefier (335) and the non-condensable gas storage tank

(119), the compressor (2), the combustion chamber (300), the carbon dioxide liquefier (335), and the non-condensable gas storage tank (119) constitute a non-condensable gas circulation flow closed passage.

24. The low-entropy co-firing gas-filled blasting engine according to claim 12, wherein: the expansion agent in the expansion agent source (333) is a gas liquefaction.

25. The low-entropy co-firing gas-filled blasting engine according to claim 12, wherein: said expansion agent source (333) is in communication with a liquid outlet of an expansion agent liquefier (3333), said expansion agent liquefier (3333) ) is located on the exhaust passage (302).

26. The low-entropy co-firing blasting engine according to claim 14, wherein a low-quality heat source heat exchanger is disposed between the hybrid desuperheater (4) and the expansion agent source (333).

27. A method for improving the efficiency and environmental friendliness of a low-entropy co-firing gas-filled blast engine according to claim 1, 2, 3 or 4, characterized in that: the pressure of the gas working medium to be started to work is adjusted to 15 MPa or more, Adjust the temperature of the gas working fluid that is about to start work to below 2700K, so that the temperature and pressure of the gas working fluid that is about to start work conform to the adiabatic relationship.

28. A method of improving the efficiency and environmental friendliness of a low-entropy co-firing gas-filled blast engine according to claim 12, wherein: controlling said expansion agent control mechanism (3331) to adjust an amount of expansion agent introduction and/or adjustment introduction The amount of fuel in the combustion chamber (300) is such that the temperature of the gas in the combustion chamber after combustion does not exceed the temperature of the compressed gas at the gas outlet of the compressor (2).

29. A method of improving the efficiency and environmental friendliness of a low-entropy co-firing gas-filled blast engine according to claim 12, characterized by: adjusting an intake volume flow rate of said gas inlet of said compressor (2) with said combustion chamber The ratio of the intake volume flow rate of the inflation port (301) to achieve the environmental temperature limit or the material temperature limit by the temperature of the compressed gas at the gas outlet of the compressor (2), by controlling the expansion agent control mechanism (3331) adjusting the amount of the expansion agent introduced and/or adjusting the amount of fuel introduced into the combustion chamber (300) to achieve the compressor in the combustion chamber after the temperature does not exceed the environmental temperature limit and the material temperature limit ( 2) The temperature at which the temperature of the compressed gas at the gas outlet reaches the limit.

30. A method for improving the efficiency and environmental friendliness of a low-entropy co-firing gas-filled blast engine according to claim 1, 2, 3 or 4, characterized in that: adjusting an intake volume of a gas inlet of said compressor (2) a ratio of the flow rate to the intake volume flow rate of the combustion chamber inflation port (301) to achieve a pressure of the compressed gas at the gas outlet of the compressor (2) to reach the gas outlet of the compressor (2) Limit of pressure capability.