CN115030816B - Indirect cooling heat exchange type zero carbon emission gas turbine cycle system and cycle method - Google Patents
Indirect cooling heat exchange type zero carbon emission gas turbine cycle system and cycle method Download PDFInfo
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- CN115030816B CN115030816B CN202210679753.4A CN202210679753A CN115030816B CN 115030816 B CN115030816 B CN 115030816B CN 202210679753 A CN202210679753 A CN 202210679753A CN 115030816 B CN115030816 B CN 115030816B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C3/00—Gas-turbine plants characterised by the use of combustion products as the working fluid
- F02C3/20—Gas-turbine plants characterised by the use of combustion products as the working fluid using a special fuel, oxidant, or dilution fluid to generate the combustion products
- F02C3/22—Gas-turbine plants characterised by the use of combustion products as the working fluid using a special fuel, oxidant, or dilution fluid to generate the combustion products the fuel or oxidant being gaseous at standard temperature and pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C3/00—Gas-turbine plants characterised by the use of combustion products as the working fluid
- F02C3/04—Gas-turbine plants characterised by the use of combustion products as the working fluid having a turbine driving a compressor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C7/00—Features, components parts, details or accessories, not provided for in, or of interest apart form groups F02C1/00 - F02C6/00; Air intakes for jet-propulsion plants
- F02C7/12—Cooling of plants
- F02C7/14—Cooling of plants of fluids in the plant, e.g. lubricant or fuel
- F02C7/141—Cooling of plants of fluids in the plant, e.g. lubricant or fuel of working fluid
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C7/00—Features, components parts, details or accessories, not provided for in, or of interest apart form groups F02C1/00 - F02C6/00; Air intakes for jet-propulsion plants
- F02C7/12—Cooling of plants
- F02C7/16—Cooling of plants characterised by cooling medium
- F02C7/18—Cooling of plants characterised by cooling medium the medium being gaseous, e.g. air
- F02C7/185—Cooling means for reducing the temperature of the cooling air or gas
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C7/00—Features, components parts, details or accessories, not provided for in, or of interest apart form groups F02C1/00 - F02C6/00; Air intakes for jet-propulsion plants
- F02C7/22—Fuel supply systems
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
- Y02E60/30—Hydrogen technology
- Y02E60/36—Hydrogen production from non-carbon containing sources, e.g. by water electrolysis
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- General Engineering & Computer Science (AREA)
- Engine Equipment That Uses Special Cycles (AREA)
Abstract
The invention provides an indirect cooling heat exchange type zero-carbon emission gas turbine circulating system and a circulating method, and belongs to the field of gas turbines. The method solves the problem that cascade utilization of energy in the turbine cooling air consumption control and system cannot be realized. The integrated indirect cooling heat exchanger comprises a low-temperature heat exchanger, a medium-temperature heat exchanger and a high-temperature heat exchanger which are sequentially connected in series, an air inlet of the low-pressure compressor is communicated with outside air, an air outlet of the low-pressure compressor is communicated with an air inlet of an air distributor through a pipeline, a first air outlet of the air distributor is communicated with a hot end inlet of the low-temperature heat exchanger, a hot end outlet of the low-temperature heat exchanger is communicated with a heat exchange pipeline of the turbine, and an outlet of the heat exchange pipeline is communicated with the outside atmosphere. The invention is suitable for clean combustion of gas turbines or aeroengines.
Description
Technical Field
The invention belongs to the field of gas turbines, and particularly relates to an indirect cooling heat exchange type zero-carbon emission gas turbine circulating system and a circulating method.
Background
Under the background of double carbon in the energy field of China, zero carbon emission of a gas turbine faces important technical requirements. Ammonia is a fuel with zero carbon properties, and combustion of ammonia fuel by gas turbines is one of the important technological paths for gas turbines to achieve zero carbon emissions. Ammonia is composed of two elements, hydrogen and nitrogen, and is a highly efficient hydrogen carrier. Compared with hydrogen, ammonia is easy to liquefy, and low-cost transportation and storage can be realized. The ammonia yield in China is the first world, and the preparation and transportation technology and the infrastructure are mature. The new energy is used for generating electricity to prepare green hydrogen, the green hydrogen is converted into ammonia for storage and transportation, and then the ammonia fuel or the mixed fuel mainly comprising ammonia is used for generating electricity, so that the method is one of the practical technical approaches for solving the problems of the future renewable energy volatility, the intermittence and the randomness of China.
Ammonia is difficult to burn, flame propagation speed is low, and flammability boundary is narrow, which is one of the key problems faced by ammonia gas turbine applications. Hydrogen has combustion characteristics opposite to those of ammonia, and the hydrogen and the ammonia have good complementarity and can form mixed fuel for combustion. Ammonia is cracked into hydrogen and nitrogen by ammonia cracking technology, and then the hydrogen and the nitrogen are mixed with ammonia, so that the hydrogen-ammonia mixed fuel can be formed under the condition of no external hydrogen source.
One of the main ways modern gas turbines have been to increase the pressure and temperature ratios. The pressure ratio increase presents a greater difficulty for gas turbine compressor design because as air is progressively compressed, the air temperature and volumetric flow increases, which results in a higher pressure ratio compression being more difficult and also requires a larger compressor size to achieve compression. The air after being pressurized is cooled by the inter-cooling heat exchange technology of the gas turbine compressor, so that the problem of pressurization under high pressure ratio is solved, but the inter-cooling heat exchange technology requires cold working medium input, and the efficiency of a gas turbine circulation system is indirectly influenced. In addition, when the turbine of the gas turbine faces the gas with higher temperature under the requirement of high temperature ratio, work needs to be done at the higher temperature, and the turbine needs more cooling air for cooling protection. Cooling air is commonly extracted from a compressor, the higher the temperature ratio of the gas turbine, the greater the cooling air demand, and the more complex the turbine blade cooling technology, which results in reduced gas turbine efficiency, and the turbine blade cooling technology also limits the temperature ratio improvement. Therefore, how to control the cooling air consumption is a critical issue.
Disclosure of Invention
In view of the above, the invention aims to provide an indirect cooling heat exchange type zero-carbon emission gas turbine circulating system and a circulating method, so as to solve the problems that the cooling air consumption of turbine cooling is controlled and the energy in the system cannot be utilized in a cascade manner.
In order to achieve the above purpose, the technical scheme of the invention is realized as follows:
The indirect cooling heat exchange type zero-carbon emission gas turbine circulation system comprises a gas turbine, an ammonia fuel system and an integrated indirect cooling heat exchanger, wherein the gas turbine comprises a low-pressure compressor, a high-pressure compressor, a combustion chamber and a turbine, the low-pressure compressor, the high-pressure compressor and the turbine are coaxially arranged and are connected through a rotating shaft, the ammonia fuel system comprises a liquid ammonia component and an ammonia cracking reactor, and the integrated indirect cooling heat exchanger comprises a low-temperature heat exchanger, a medium-temperature heat exchanger and a high-temperature heat exchanger which are sequentially connected in series;
The cold end inlet of the low-temperature heat exchanger is communicated with the liquid outlet of the liquid ammonia component, the cold end outlet of the low-temperature heat exchanger is communicated with the cold end inlet of the medium-temperature heat exchanger, the cold end outlet of the medium-temperature heat exchanger is communicated with the cold end inlet of the high-temperature heat exchanger, the cold end outlet of the high-temperature heat exchanger is communicated with the ammonia distributor, the first output port of the ammonia distributor is connected with the reactant inlet of the ammonia cracking reactor through a pipeline, the second output port of the ammonia distributor is communicated with the fuel inlet of the combustion chamber through a pipeline, and the mixed gas outlet of the ammonia cracking reactor is communicated with the fuel inlet of the combustion chamber through a pipeline;
The air inlet of the low-pressure air compressor is communicated with the outside air, the air outlet of the low-pressure air compressor is communicated with the air inlet of the air distributor through a pipeline, the first air outlet of the air distributor is communicated with the hot end inlet of the low-temperature heat exchanger, the hot end outlet of the low-temperature heat exchanger is communicated with the heat exchange pipeline of the turbine, the heat exchange pipeline outlet is communicated with the outside air, the second air outlet of the air distributor is communicated with the hot end inlet of the medium-temperature heat exchanger, the hot end outlet of the medium-temperature heat exchanger is communicated with the air inlet of the high-pressure air compressor, the air outlet of the high-pressure air compressor is communicated with the air inlet of the combustion chamber, the gas outlet of the combustion chamber is communicated with the air inlet of the turbine, the air outlet of the turbine is communicated with the hot end inlet of the high-temperature heat exchanger, and the hot end outlet of the high-temperature heat exchanger is communicated with the outside air.
Still further, the liquid ammonia subassembly includes liquid ammonia storage tank, liquid ammonia pipeline and liquid ammonia booster pump, and the inlet and the liquid ammonia storage tank intercommunication of liquid ammonia pipeline, the liquid outlet and the cold junction entry intercommunication of cryogenic heat exchanger of liquid ammonia pipeline install the liquid ammonia booster pump on the liquid ammonia pipeline.
Furthermore, a mixer is arranged on a pipeline communicated with the fuel inlet of the combustion chamber, a second output port of the ammonia distributor is communicated with the mixer through a pipeline, a mixed gas outlet of the ammonia cracking reactor is communicated with the mixer, and an output port of the mixer is communicated with the fuel inlet of the combustion chamber.
Furthermore, the heat exchange pipeline and the gas pipeline of the turbine are mutually separated and are not communicated, and the turbine adopts a closed cooling mode, namely cooling air does not enter the turbine to be mixed with the gas.
Furthermore, the external air is pressurized by the low-pressure compressor and then is divided into cooling air and working air by the air distributor, and the cooling air accounts for 5% -15% of the total air.
Further, in the low-temperature heat exchanger, the liquid ammonia is maintained in a liquid state, in the medium-temperature heat exchanger, the liquid ammonia is changed into ammonia, and in the high-temperature heat exchanger, the temperature of the ammonia is increased to a catalytic cracking working temperature range.
Further, the ammonia passing through the high-temperature heat exchanger is distributed into cracked ammonia and original ammonia through an ammonia distributor, the cracked ammonia accounts for 30-90% of the total ammonia amount, the cracked ammonia is used for providing raw materials for an ammonia cracking reactor, and the original ammonia is used for providing fuel for a combustion chamber.
Furthermore, the pressure loss of the low-temperature heat exchanger hot working medium is 1% -2%, the pressure loss of the medium-temperature heat exchanger hot working medium is 2% -4%, the pressure loss of the high-temperature heat exchanger hot working medium is 2% -4%, the pressure loss of the integrated indirect cooling heat exchanger cold working medium is 4% -6%, and the pressure loss of the ammonia cracking reactor is 4% -6%.
Further, the ammonia cracking reactor is a tubular reactor or a tower reactor.
The application further provides a circulating method of the indirect cooling heat exchange type zero-carbon emission gas turbine circulating system, which specifically comprises the following steps:
S1, after being pressurized by a liquid ammonia booster pump, liquid ammonia in a liquid ammonia storage tank sequentially enters a low-temperature heat exchanger, a medium-temperature heat exchanger and a high-temperature heat exchanger of an integrated indirect cooling heat exchanger, and in the low-temperature heat exchanger, the liquid ammonia cools cooling air and maintains a liquid state; in the high-temperature heat exchanger, the ammonia gas is cooled, the temperature of the ammonia gas is increased to a catalytic cracking working temperature range, the ammonia gas flowing out of the integrated indirect cooling heat exchanger is divided into two parts, namely cracked ammonia gas and original ammonia gas, the cracked ammonia gas enters an ammonia cracking reactor for reaction and cracking under the action of a catalyst, cracking products are nitrogen and hydrogen, and ammonia cracking gas produced by the ammonia cracking reactor is mixed with the original ammonia gas to form hydrogen/ammonia/nitrogen mixed fuel, and the hydrogen/ammonia/nitrogen mixed fuel enters a combustion chamber for combustion;
S2, after being pressurized by a low-pressure compressor, the air is divided into cooling air and working air, the cooling air enters a low-temperature heat exchanger of the integrated indirect cooling heat exchanger, is cooled after being subjected to heat exchange with liquid ammonia to form low-temperature cooling air, and is input into a turbine to cool the turbine, the cooling air does not enter the turbine to be mixed with fuel gas, and the turbine is cooled and then is discharged into the atmosphere;
s3, the working air enters a medium-temperature heat exchanger of the integrated indirect cooling heat exchanger, is cooled after heat exchange with liquid ammonia, forms low-temperature working air, enters a high-pressure compressor, is pressurized by the high-pressure compressor, and then chemically reacts with fuel in a combustion chamber to generate high-temperature and high-pressure fuel gas, and the fuel gas enters the high-temperature heat exchanger of the integrated indirect cooling heat exchanger after turbine expansion working, is cooled and discharged after heat exchange with ammonia.
Compared with the prior art, the indirect cooling heat exchange type zero-carbon emission gas turbine circulation system has the beneficial effects that:
(1) The invention creates the indirect cooling heat exchange type zero-carbon emission gas turbine circulating system, and realizes the efficient cascade utilization of energy sources in the gas turbine circulating system.
(2) According to the indirect cooling heat exchange type zero-carbon emission gas turbine circulating system, ammonia is the only fuel source, ammonia cracking reaction is realized under the condition of no extra heat source, and the fuel is finally hydrogen/ammonia/nitrogen mixed fuel, so that zero-carbon emission is realized. The presence of nitrogen in the fuel serves as a diluent to reduce NOx emissions.
(3) In modern gas turbines, with the gradual increase of the initial temperature of the gas before the turbine, the consumption of cooling air is increased, the cooling air generally accounts for about 20% or more of the total air, and the cooling air must be mixed with the gas after cooling the components so as to increase the flow of working medium in the turbine to improve the output work. However, the disadvantage of this design is that the cooling system is complex, the heat and mass transfer process of the cooling air needs to be considered, the back pressure of the cooling air is high (for cooling the high-pressure end of the turbine, the air extraction pressure is generally greater than 20bar, the air extraction temperature is about 450-550 ℃, and for cooling the low-pressure end of the turbine, the air extraction pressure is generally 10-15bar, the air extraction temperature is about 300-400 ℃), the pressure and the temperature of the extraction point of the cooling air are increased, and the cooling effect is poor. In addition, after the cooling air is mixed with the fuel gas, the temperature of the fuel gas is lowered, resulting in a decrease in turbine efficiency.
According to the invention, under the condition of no additional cold source, the low-temperature liquid ammonia is utilized, so that the cooling air temperature and consumption of the gas turbine are greatly reduced, the cooling air amount accounts for 5% -15% of the total air amount, and the cooling air temperature range is 60-100 ℃. The gas turbine adopts a closed cooling system, reduces the design difficulty of the cooling system, only considers the heat transfer process of cooling air, and directly discharges the cooled air into the atmosphere after cooling the components, so that the back pressure of the cooling air is low, the pressure of the cooling air can be lower than 10bar, and the cooling air can be extracted under the condition that the outlet pressure of a low-pressure compressor is lower. In addition, by utilizing the characteristic that a large amount of heat is required for liquid ammonia vaporization, the working air is cooled, the efficiency of the high-pressure compressor under the high pressure ratio can be improved, the high-pressure compressor has smaller size and the structure is more compact.
Drawings
The accompanying drawings, which are included to provide a further understanding of the invention and are incorporated in and constitute a part of this specification, illustrate embodiments of the invention and together with the description serve to explain the invention and do not constitute an undue limitation on the invention. In the drawings:
FIG. 1 is a schematic diagram of an indirect cooling heat exchange zero carbon emission gas turbine cycle system according to an embodiment of the present invention.
Reference numerals illustrate:
1. A low pressure compressor; 2, a high-pressure compressor, 3, a combustion chamber, 4, a turbine, 5, a rotating shaft, 6, a liquid ammonia storage tank, 7, a liquid ammonia booster pump, 8, an ammonia cracking reactor, 9, an integrated indirect cooling heat exchanger, 10, a low-temperature heat exchanger, 11, a medium-temperature heat exchanger, 12, a high-temperature heat exchanger, 13, an air distributor, 14, an ammonia distributor, 15 and a mixer.
Detailed Description
The present invention now will be described more fully hereinafter with reference to the accompanying drawings, in which some, but not all embodiments of the invention are shown. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention disclosed herein without departing from the scope of the invention.
In the description of the present invention, it should be noted that, directions or positional relationships indicated by terms such as "center", "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer", etc., are based on those shown in the drawings, are merely for convenience in describing the present invention and simplifying the description, and do not indicate or imply that the apparatus or elements referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus should not be construed as limiting the present invention. Furthermore, the terms "first," "second," and "third" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance.
In the description of the present invention, unless explicitly specified and limited otherwise, the terms "mounted," "connected," and "connected" are to be construed broadly, and may be, for example, fixedly connected, detachably connected, or integrally connected, mechanically connected, electrically connected, directly connected, indirectly connected via an intervening medium, or in communication between two elements. The specific meaning of the above terms in the creation of the present invention will be understood in a specific case by those skilled in the art.
In addition, the technical features which are described below and which are involved in the various embodiments of the invention can be combined with one another as long as they do not conflict with one another.
As shown in fig. 1, an indirect cooling heat exchange type zero-carbon emission gas turbine circulation system comprises a gas turbine, an ammonia fuel system and an integrated indirect cooling heat exchanger 9, wherein the gas turbine comprises a low-pressure gas compressor 1, a high-pressure gas compressor 2, a combustion chamber 3 and a turbine 4, the low-pressure gas compressor 1, the high-pressure gas compressor 2 and the turbine 4 are coaxially arranged and are connected through a rotating shaft 5, the ammonia fuel system comprises a liquid ammonia component and an ammonia cracking reactor 8, and the integrated indirect cooling heat exchanger 9 comprises a low-temperature heat exchanger 10, a medium-temperature heat exchanger 11 and a high-temperature heat exchanger 12 which are sequentially connected in series;
The cold end inlet of the low-temperature heat exchanger 10 is communicated with the liquid outlet of the liquid ammonia component, the cold end outlet of the low-temperature heat exchanger 10 is communicated with the cold end inlet of the medium-temperature heat exchanger 11, the cold end outlet of the medium-temperature heat exchanger 11 is communicated with the cold end inlet of the high-temperature heat exchanger 12, the cold end outlet of the high-temperature heat exchanger 12 is communicated with the ammonia distributor 14, a first output port of the ammonia distributor 14 is connected with the reactant inlet of the ammonia cracking reactor 8 through a pipeline, a second output port of the ammonia distributor 14 is communicated with the fuel inlet of the combustion chamber 3 through a pipeline, and a mixed gas outlet of the ammonia cracking reactor 8 is communicated with the fuel inlet of the combustion chamber 3 through a pipeline;
The air inlet of the low-pressure compressor 1 is communicated with the outside air, the air outlet of the low-pressure compressor 1 is communicated with the air inlet of the air distributor 13 through a pipeline, the first air outlet of the air distributor 13 is communicated with the hot end inlet of the low-temperature heat exchanger 10, the hot end outlet of the low-temperature heat exchanger 10 is communicated with the heat exchange pipeline of the turbine 4, the heat exchange pipeline outlet is communicated with the outside air, the second air outlet of the air distributor 13 is communicated with the hot end inlet of the medium-temperature heat exchanger 11, the hot end outlet of the medium-temperature heat exchanger 11 is communicated with the air inlet of the high-pressure compressor 2, the air outlet of the high-pressure compressor 2 is communicated with the air inlet of the combustion chamber 3, the gas outlet of the combustion chamber 3 is communicated with the air inlet of the turbine 4, the air outlet of the turbine 4 is communicated with the hot end inlet of the high-temperature heat exchanger 12, and the hot end outlet of the high-temperature heat exchanger 12 is communicated with the outside air.
According to the indirect cooling heat exchange type zero-carbon emission gas turbine circulating system, the cooling air consumption is reduced by reducing the temperature of cooling air as an effective means, in the circulating system, a large amount of heat is required to be absorbed in the liquid ammonia vaporization process, the cooling air and working air are greatly cooled by utilizing the liquid ammonia vaporization process, the cooling air cooling effect can be improved, the cooling air consumption can be reduced, and in addition, the improvement of the gas turbine efficiency is very beneficial because an external cold source is not required.
The application innovatively provides an indirect cooling heat exchange type zero-carbon emission gas turbine circulation system by utilizing an energy cascade utilization principle, wherein liquid ammonia is the only fuel source, cooling air and working air are cooled respectively through a liquid ammonia vaporization process, cooling air consumption reduction and compressor efficiency improvement are realized, partial ammonia is heated by utilizing gas exhaust to heat the ammonia to a catalytic cracking working temperature, cracking efficiency is improved, and the proportion of hydrogen/ammonia/nitrogen mixed fuel components is adjusted by changing the proportion of ammonia for cracking to the total ammonia amount. The fuel contains nitrogen, so that the fuel is diluted and combusted, and the NOx emission is reduced.
The liquid ammonia subassembly includes liquid ammonia storage tank 6, liquid ammonia pipeline and liquid ammonia booster pump 7, and the inlet and the liquid ammonia storage tank 6 intercommunication of liquid ammonia pipeline, the liquid outlet and the cold junction entry intercommunication of cryogenic heat exchanger 10 of liquid ammonia pipeline install liquid ammonia booster pump 7 on the liquid ammonia pipeline, in inputting the cold junction entry of cryogenic heat exchanger 10 with the liquid ammonia in the liquid ammonia storage tank 6 through liquid ammonia booster pump 7.
Be equipped with blender 15 on the pipeline of the fuel entry of intercommunication combustion chamber 3, the second delivery outlet of ammonia distributor 14 passes through pipeline and blender 15 intercommunication, and the gas mixture export and the blender 15 intercommunication of ammonia pyrolysis reactor 8, the delivery outlet of blender 15 communicates with the fuel entry of combustion chamber 3, makes the fuel carry out better mixing before getting into combustion chamber 3 through setting up blender 15 for the burning in the combustion chamber 3 is more abundant.
The heat exchange pipeline and the gas pipeline of the turbine 4 are mutually separated and are not communicated, the turbine 4 adopts a closed cooling mode, namely cooling air does not enter the turbine 4 to be mixed with gas, the design difficulty of a cooling system is reduced, only the heat transfer process of the cooling air is considered, and the cooling air is directly discharged into the atmosphere after cooling the components, so that the back pressure of the cooling air is low.
The outside air is pressurized by the low-pressure compressor 1 and then is separated into cooling air and working air by the air distributor 13, and the cooling air accounts for 5% -15% of the total air. In the low-temperature heat exchanger 10, liquid ammonia is kept in a liquid state, in the medium-temperature heat exchanger 11, the liquid ammonia is changed into ammonia, in the high-temperature heat exchanger 12, the temperature of the ammonia is increased to a catalytic cracking working temperature range (500-600 ℃), the ammonia passing through the high-temperature heat exchanger 12 is distributed into cracked ammonia and original ammonia through an ammonia distributor 14, the cracked ammonia accounts for 30-90% of the total ammonia amount, the cracked ammonia is used for providing raw materials for the ammonia cracking reactor 8, the original ammonia is used for providing fuel for the combustion chamber 3, the pressure loss of a hot working medium of the low-temperature heat exchanger 10 is 1% -2%, the pressure loss of the hot working medium of the medium-temperature heat exchanger 11 is 2% -4%, the pressure loss of the hot working medium of the high-temperature heat exchanger 12 is 2% -4%, the pressure loss of a cold working medium of the integrated inter-cooling heat exchanger 9 is 4% -6%, and the pressure loss of the ammonia cracking reactor 8 is 4% -6%.
The ammonia cracking reactor 8 is a tubular reactor or a tower reactor, and may be any other type of cracking reactor structure in the prior art, and is not limited to the specific embodiments disclosed in the present application, and those skilled in the art may specifically select according to specific requirements.
The circulating method of the indirect cooling heat exchange type zero-carbon emission gas turbine circulating system specifically comprises the following steps:
S1, pressurizing liquid ammonia in a liquid ammonia storage tank 6 through a liquid ammonia booster pump 7, sequentially entering a low-temperature heat exchanger 10, a medium-temperature heat exchanger 11 and a high-temperature heat exchanger 12 of an integrated indirect cooling heat exchanger 9, cooling air by the liquid ammonia in the low-temperature heat exchanger 10, maintaining the liquid ammonia in a liquid state, cooling working air by the liquid ammonia in the medium-temperature heat exchanger 11, vaporizing the working air and changing the working air into ammonia gas, cooling fuel gas by the ammonia gas in the high-temperature heat exchanger 12, increasing the temperature of the ammonia gas to a catalytic cracking working temperature range (500-600 ℃), dividing the ammonia gas flowing out of the integrated indirect cooling heat exchanger 9 into two parts, namely cracked ammonia gas and original ammonia gas, enabling the cracked ammonia gas to enter an ammonia cracking reactor 8 for reaction and cracking under the action of a catalyst, wherein the cracking product is nitrogen gas and hydrogen gas, the cracking rate is 30% -100%, and the ammonia cracking gas generated by the ammonia cracking reactor 8 is mixed with the original ammonia gas to form hydrogen/ammonia/nitrogen mixed fuel, and the hydrogen/nitrogen mixed fuel enters a combustion chamber 3 for combustion;
S2, after being pressurized by the low-pressure compressor 1, the air is divided into cooling air and working air, the cooling air enters a low-temperature heat exchanger 10 of the integrated indirect cooling heat exchanger 9, is cooled after heat exchange with liquid ammonia to form low-temperature cooling air, the temperature of the low-temperature cooling air is 60-100 ℃, the low-temperature cooling air is input into the turbine 4, the turbine 4 is cooled, the cooling air does not enter the turbine 4 to be mixed with fuel gas, and the turbine 4 is cooled and then discharged into the atmosphere;
S3, the working air enters a medium-temperature heat exchanger 11 of the integrated indirect cooling heat exchanger 9, is cooled after heat exchange with liquid ammonia to form low-temperature working air, enters a high-pressure compressor 2, is pressurized by the high-pressure compressor 2, and then is subjected to chemical reaction with fuel in a combustion chamber 3 to generate high-temperature and high-pressure fuel gas, and the fuel gas is expanded by a turbine 4 to do work and then enters a high-temperature heat exchanger 12 of the integrated indirect cooling heat exchanger 9, is cooled after heat exchange with ammonia and is discharged.
Specific examples of a circulation method of an indirect cooling heat exchange type zero carbon emission gas turbine circulation system are given below:
the heat medium pressure loss of the low-temperature heat exchanger is 1%, the heat medium pressure loss of the medium-temperature heat exchanger is 2%, the heat medium pressure loss of the high-temperature heat exchanger is 2%, the cold medium pressure loss of the integrated indirect-cooling heat exchanger is 5%, and the pressure loss of the ammonia cracking reactor is 4%;
the circulating method of the indirect cooling heat exchange type zero-carbon emission gas turbine circulating system specifically comprises the following steps:
S1, the pressure and the temperature in a liquid ammonia storage tank 6 are respectively 20bar and 15 ℃, the flow rate of the liquid ammonia is 60kg/S, after the liquid ammonia in the liquid ammonia storage tank 6 is pressurized by a liquid ammonia booster pump 7, the pressure of the liquid ammonia is 30bar, the liquid ammonia sequentially enters a low-temperature heat exchanger 10, a medium-temperature heat exchanger 11 and a high-temperature heat exchanger 12 of an integrated indirect cooling heat exchanger 9, the liquid ammonia cools cooling air in the low-temperature heat exchanger 10, the liquid ammonia is maintained in a liquid state, and the pressure and the temperature of the liquid ammonia are respectively 29.7bar and 65.4 ℃; in the high-temperature heat exchanger 12, the ammonia gas is cooled to the fuel gas, the pressure and the temperature of the ammonia gas are 28.52bar and 550 ℃, the ammonia gas flowing out of the integrated indirect cooling heat exchanger 9 is divided into two parts, namely cracked ammonia and original ammonia, the cracked ammonia accounts for 50% of the total ammonia amount, the cracked ammonia enters an ammonia cracking reactor for reaction and cracking under the action of a catalyst, the cracking products are nitrogen and hydrogen, the cracking rate is 100%, the pressure and the temperature of the ammonia cracking gas are 27.38bar and 100 ℃, the ammonia cracking gas produced by the ammonia cracking reactor is mixed with the original ammonia gas to form hydrogen/ammonia/nitrogen mixed fuel, the temperature is 302.8 ℃, and the volume fractions of the three components are 50%, 33.3% and 16.7%, and the three components enter the combustion chamber 3 for combustion;
S2, the air flow is 860kg/S, after being pressurized by a low-pressure compressor 1, the air pressure and the temperature are respectively 10bar and 363.3 ℃, the air is divided into cooling air and working air, the cooling air quantity is 86kg/S and accounts for 10% of the total air quantity, the cooling air enters a low-temperature heat exchanger 10 of an integrated inter-cooling heat exchanger 9, after heat exchange with liquid ammonia, the temperature is reduced, low-temperature cooling air is formed, the pressure and the temperature of the low-temperature cooling air are respectively 9.9bar and 80 ℃, the low-temperature cooling air is input into a turbine 4, the turbine 4 is cooled, and because the turbine 4 adopts a closed cooling method, the cooling air does not enter the turbine 4 to be mixed with fuel gas, and the turbine 4 is cooled and then discharged into the atmosphere;
S3, the working air quantity is 774kg/S, the working air enters a medium-temperature heat exchanger 11 of an integrated indirect cooling heat exchanger 9, the temperature is reduced after heat exchange with liquid ammonia, low-temperature working air is formed, the pressure and the temperature of the low-temperature working air are respectively 9.8bar and 255.2 ℃, the low-temperature working air enters a high-pressure compressor 2, after the working air is pressurized by the high-pressure compressor 2, the pressure and the temperature of the working air are respectively 23bar and 438.8 ℃, the working air and fuel react in a combustion chamber 3 to generate high-temperature high-pressure fuel gas, the pressure loss of the combustion chamber 3 is 5%, the pressure and the temperature of outlet fuel gas of the combustion chamber 3 are respectively 21.85bar and 1500 ℃, the pressure and the temperature of the outlet fuel gas of the turbine 4 are respectively 1.07bar and 626.8 ℃ after expansion working of the fuel gas enters a high-temperature heat exchanger 12 of the integrated indirect cooling heat exchanger 9, the cooled fuel gas is discharged after heat exchange with ammonia, and the cooled fuel gas pressure and the cooled fuel gas is respectively 1.05bar and 585.1 ℃, and the fuel gas is discharged out of a system.
The heat load of the gas turbine is 1116.6MW, the output power is 496.23MW, the generator efficiency is 98%, the power generation power of the indirect cooling heat exchange type zero-carbon emission gas turbine circulation system is 486.31MW, and the power generation efficiency is 43.55%.
The inventive embodiments disclosed above are merely intended to help illustrate the inventive embodiments. The examples are not intended to be exhaustive or to limit the invention to the precise form disclosed. Many modifications and variations are possible in light of the above teaching. The embodiments were chosen and described in order to best explain the principles of the invention and the practical application, to thereby enable others skilled in the art to best understand and utilize the invention.
Claims (9)
1. The indirect cooling heat exchange type zero-carbon emission gas turbine circulation system is characterized by comprising a gas turbine, an ammonia fuel system and an integrated indirect cooling heat exchanger (9), wherein the gas turbine comprises a low-pressure gas compressor (1), a high-pressure gas compressor (2), a combustion chamber (3) and a turbine (4), the low-pressure gas compressor (1), the high-pressure gas compressor (2) and the turbine (4) are coaxially arranged and are connected through a rotating shaft (5), the ammonia fuel system comprises a liquid ammonia component and an ammonia cracking reactor (8), and the integrated indirect cooling heat exchanger (9) comprises a low-temperature heat exchanger (10), a medium-temperature heat exchanger (11) and a high-temperature heat exchanger (12) which are sequentially connected in series;
the cold end inlet of the low-temperature heat exchanger (10) is communicated with the liquid outlet of the liquid ammonia component, the cold end outlet of the low-temperature heat exchanger (10) is communicated with the cold end inlet of the medium-temperature heat exchanger (11), the cold end outlet of the medium-temperature heat exchanger (11) is communicated with the cold end inlet of the high-temperature heat exchanger (12), the cold end outlet of the high-temperature heat exchanger (12) is communicated with the ammonia distributor (14), the first output port of the ammonia distributor (14) is connected with the reactant inlet of the ammonia cracking reactor (8) through a pipeline, the second output port of the ammonia distributor (14) is communicated with the fuel inlet of the combustion chamber (3) through a pipeline, and the mixed gas outlet of the ammonia cracking reactor (8) is communicated with the fuel inlet of the combustion chamber (3) through a pipeline;
The air inlet of the low-pressure air compressor (1) is communicated with the outside air, the air outlet of the low-pressure air compressor (1) is communicated with the air inlet of the air distributor (13) through a pipeline, the first air outlet of the air distributor (13) is communicated with the hot end inlet of the low-temperature heat exchanger (10), the hot end outlet of the low-temperature heat exchanger (10) is communicated with the heat exchange pipeline of the turbine (4), the heat exchange pipeline outlet is communicated with the outside air, the second air outlet of the air distributor (13) is communicated with the hot end inlet of the medium-temperature heat exchanger (11), the hot end outlet of the medium-temperature heat exchanger (11) is communicated with the air inlet of the high-pressure air compressor (2), the air outlet of the high-pressure air compressor (2) is communicated with the air inlet of the combustion chamber (3), the gas outlet of the combustion chamber (3) is communicated with the air inlet of the turbine (4), the air outlet of the turbine (4) is communicated with the hot end inlet of the high-temperature heat exchanger (12), and the hot end outlet of the high-temperature heat exchanger (12) is communicated with the outside air;
The liquid ammonia assembly comprises a liquid ammonia storage tank (6), a liquid ammonia pipeline and a liquid ammonia booster pump (7), wherein a liquid inlet of the liquid ammonia pipeline is communicated with the liquid ammonia storage tank (6), a liquid outlet of the liquid ammonia pipeline is communicated with a cold end inlet of a low-temperature heat exchanger (10), and the liquid ammonia booster pump (7) is installed on the liquid ammonia pipeline.
2. The indirect cooling heat exchange type zero carbon emission gas turbine circulation system according to claim 1, wherein a mixer (15) is arranged on a pipeline communicated with a fuel inlet of the combustion chamber (3), a second output port of the ammonia distributor (14) is communicated with the mixer (15) through a pipeline, a mixed gas outlet of the ammonia cracking reactor (8) is communicated with the mixer (15), and an output port of the mixer (15) is communicated with the fuel inlet of the combustion chamber (3).
3. The indirect cooling heat exchange type zero-carbon emission gas turbine circulation system according to claim 1, wherein the heat exchange pipeline and the gas pipeline of the turbine (4) are separated from each other and are not communicated, and the turbine (4) adopts a closed cooling mode.
4. The indirect-cooling heat exchange type zero-carbon emission gas turbine circulation system of claim 1, wherein the outside air is divided into cooling air and working air through an air distributor (13) after being pressurized by the low-pressure compressor (1), and the cooling air amount accounts for 5% -15% of the total air amount.
5. An indirect-cooling heat exchange type zero-carbon emission gas turbine circulation system according to claim 1, wherein in the low-temperature heat exchanger (10), liquid ammonia is maintained in a liquid state, in the medium-temperature heat exchanger (11), liquid ammonia is changed into ammonia, and in the high-temperature heat exchanger (12), the temperature of the ammonia is increased to a catalytic cracking operation temperature range.
6. The indirect cooling heat exchange type zero-carbon emission gas turbine circulation system according to claim 1, wherein the ammonia passing through the high-temperature heat exchanger (12) is distributed into cracked ammonia and original ammonia through an ammonia distributor (14), the cracked ammonia accounts for 30-90% of the total ammonia amount, the cracked ammonia is used for providing raw materials for an ammonia cracking reactor (8), and the original ammonia is used for providing fuel for a combustion chamber (3).
7. The indirect cooling heat exchange type zero-carbon emission gas turbine circulation system of claim 1, wherein the low-temperature heat exchanger (10) is 1% -2% in hot working medium pressure loss, the medium-temperature heat exchanger (11) is 2% -4% in hot working medium pressure loss, the high-temperature heat exchanger (12) is 2% -4% in hot working medium pressure loss, the integrated indirect cooling heat exchanger (9) is 4% -6% in cold working medium pressure loss, and the ammonia cracking reactor (8) is 4% -6% in pressure loss.
8. The indirect-cooling heat exchange type zero-carbon emission gas turbine circulation system according to claim 1, wherein the ammonia cracking reactor (8) is a tubular reactor or a tower reactor.
9. The circulation method of the indirect-cooling heat exchange type zero-carbon emission gas turbine circulation system according to any one of claims 1 to 8, characterized by comprising the following steps:
S1, pressurizing liquid ammonia in a liquid ammonia storage tank (6) through a liquid ammonia booster pump (7), sequentially entering a low-temperature heat exchanger (10), a medium-temperature heat exchanger (11) and a high-temperature heat exchanger (12) of an integrated indirect cooling heat exchanger (9), cooling air by the liquid ammonia in the low-temperature heat exchanger (10), maintaining the liquid ammonia in a liquid state, cooling working air by the liquid ammonia in the medium-temperature heat exchanger (11), vaporizing the working air to form ammonia, cooling fuel gas by the ammonia in the high-temperature heat exchanger (12), raising the temperature of the ammonia to a catalytic cracking working temperature range, dividing the ammonia flowing out of the integrated indirect cooling heat exchanger (9) into two parts, namely cracked ammonia and original ammonia, enabling the cracked ammonia to enter an ammonia cracking reactor (8), reacting and cracking under the action of a catalyst, enabling a cracked product to be nitrogen and hydrogen, mixing ammonia cracked gas produced by the ammonia cracking reactor (8) with the original ammonia to form hydrogen/ammonia/nitrogen mixed fuel, and enabling the ammonia to enter a combustion chamber (3) for combustion;
s2, after being pressurized by the low-pressure compressor (1), the air is divided into cooling air and working air, the cooling air enters a low-temperature heat exchanger (10) of the integrated indirect cooling heat exchanger (9), is cooled after being subjected to heat exchange with liquid ammonia to form low-temperature cooling air, and is input into the turbine (4), the turbine (4) is cooled, the cooling air does not enter the turbine (4) to be mixed with fuel gas, and the turbine (4) is cooled and then is discharged into the atmosphere;
S3, the working air enters a medium-temperature heat exchanger (11) of the integrated indirect cooling heat exchanger (9), is cooled after heat exchange with liquid ammonia to form low-temperature working air, enters a high-pressure air compressor (2), is pressurized by the high-pressure air compressor (2), and then chemically reacts with fuel in a combustion chamber (3) to generate high-temperature and high-pressure fuel gas, and the fuel gas enters a high-temperature heat exchanger (12) of the integrated indirect cooling heat exchanger (9) after expansion work of a turbine (4) and is cooled and discharged after heat exchange with ammonia.
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| CN116181484A (en) * | 2023-03-10 | 2023-05-30 | 广西大学 | A New Closed Gas Turbine Device Based on Heat Runaway Effect |
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| Publication number | Priority date | Publication date | Assignee | Title |
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