CN116838480A - Method for changing regenerative cycle of gas turbine into humidification cycle - Google Patents
Method for changing regenerative cycle of gas turbine into humidification cycle Download PDFInfo
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- CN116838480A CN116838480A CN202310828696.6A CN202310828696A CN116838480A CN 116838480 A CN116838480 A CN 116838480A CN 202310828696 A CN202310828696 A CN 202310828696A CN 116838480 A CN116838480 A CN 116838480A
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- 238000000034 method Methods 0.000 title claims abstract description 27
- 230000001172 regenerating effect Effects 0.000 title claims abstract description 15
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 153
- 239000007789 gas Substances 0.000 claims abstract description 129
- 238000002485 combustion reaction Methods 0.000 claims abstract description 29
- 239000000779 smoke Substances 0.000 claims abstract description 27
- VNWKTOKETHGBQD-UHFFFAOYSA-N methane Chemical compound C VNWKTOKETHGBQD-UHFFFAOYSA-N 0.000 claims abstract description 22
- 230000001105 regulatory effect Effects 0.000 claims abstract description 12
- 239000003345 natural gas Substances 0.000 claims abstract description 11
- 238000001816 cooling Methods 0.000 claims description 34
- 239000002918 waste heat Substances 0.000 claims description 20
- 239000000446 fuel Substances 0.000 claims description 10
- 239000000498 cooling water Substances 0.000 claims description 9
- 238000006243 chemical reaction Methods 0.000 claims description 7
- 230000009466 transformation Effects 0.000 abstract description 7
- 239000008358 core component Substances 0.000 abstract description 4
- 239000000306 component Substances 0.000 abstract description 2
- 238000007599 discharging Methods 0.000 abstract description 2
- 230000008569 process Effects 0.000 description 7
- 238000010248 power generation Methods 0.000 description 6
- 230000008901 benefit Effects 0.000 description 3
- 238000002407 reforming Methods 0.000 description 3
- 238000010793 Steam injection (oil industry) Methods 0.000 description 2
- 238000010438 heat treatment Methods 0.000 description 2
- 238000004064 recycling Methods 0.000 description 2
- UGFAIRIUMAVXCW-UHFFFAOYSA-N Carbon monoxide Chemical compound [O+]#[C-] UGFAIRIUMAVXCW-UHFFFAOYSA-N 0.000 description 1
- UZHDGDDPOPDJGM-UHFFFAOYSA-N Stigmatellin A Natural products COC1=CC(OC)=C2C(=O)C(C)=C(CCC(C)C(OC)C(C)C(C=CC=CC(C)=CC)OC)OC2=C1O UZHDGDDPOPDJGM-UHFFFAOYSA-N 0.000 description 1
- 238000004378 air conditioning Methods 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 239000002826 coolant Substances 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 239000003344 environmental pollutant Substances 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 239000003546 flue gas Substances 0.000 description 1
- 238000002347 injection Methods 0.000 description 1
- 239000007924 injection Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 231100000719 pollutant Toxicity 0.000 description 1
- 238000011084 recovery Methods 0.000 description 1
- 239000007921 spray Substances 0.000 description 1
- 238000005507 spraying Methods 0.000 description 1
- 230000001502 supplementing effect Effects 0.000 description 1
- 230000001131 transforming effect Effects 0.000 description 1
Classifications
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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
- F02C7/143—Cooling of plants of fluids in the plant, e.g. lubricant or fuel of working fluid before or between the compressor stages
- F02C7/1435—Cooling of plants of fluids in the plant, e.g. lubricant or fuel of working fluid before or between the compressor stages by water injection
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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
- F02C3/30—Adding water, steam or other fluids for influencing combustion, e.g. to obtain cleaner exhaust gases
- F02C3/305—Increasing the power, speed, torque or efficiency of a gas turbine or the thrust of a turbojet engine by injecting or adding water, steam or other fluids
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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
- F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use
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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
- F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use
- F02C6/18—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use using the waste heat of gas-turbine plants outside the plants themselves, e.g. gas-turbine power heat plants
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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
- F02C7/08—Heating air supply before combustion, e.g. by exhaust gases
- F02C7/10—Heating air supply before combustion, e.g. by exhaust gases by means of regenerative heat-exchangers
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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
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Engine Equipment That Uses Special Cycles (AREA)
Abstract
The invention discloses a method for changing the regenerative cycle of a gas turbine into the humidification cycle, wherein a gas compressor sucks air, pressurizes the air, then discharges the air and sends the air into a aftercooler, and the air exchanges heat with cold water to cool the air; an air placing path is arranged on an air pipeline between the aftercooler and the humidifier, and the air discharging amount is regulated according to different humidifying circulation working conditions, so that the outlet pressure of the air compressor is kept unchanged basically; the air in the humidifier is in countercurrent contact with the hot water; the wet air from the humidifier enters the combustion chamber after heat exchange with the exhaust smoke of the gas turbine in the heat regenerator; natural gas and wet air are mixed and combusted and then enter a turbine to apply work, the turbine drives a compressor and a generator to rotate, and the generator generates electric energy; the turbine exhaust gas is discharged into the atmosphere after being subjected to heat exchange with wet air and water respectively through a heat regenerator and an economizer, through-flow matching of the two components is realized without changing core components (a gas compressor and a turbine) of the gas turbine, the transformation difficulty of changing the existing gas turbine unit into humidification circulation is greatly reduced, and the higher energy utilization rate of the system is maintained.
Description
Technical Field
The invention relates to the field of gas turbines, in particular to a method for changing the regenerative cycle of a gas turbine into a humidification cycle.
Background
The gas turbine is a fossil energy large-scale power generation heat-power conversion device with highest efficiency at present. With the development of economy and society and the expansion of the application of gas turbines, the performance requirements on the gas turbines are higher and higher, the higher efficiency and the stricter pollutant emission are required, and the higher requirements on the flexibility of the circulation load adjustment of the gas turbines, the partial load performance, the influence of the environmental state and the like are also provided. The current gas turbine for power generation mainly adopts the combined cycle of the Brabender and the Rankine, on one hand, the potential of improving the cycle performance only by increasing the temperature and the pressure ratio is smaller and smaller, and on the other hand, the gas turbine is limited by the cycle type, and is difficult to meet the requirements of various types of users.
The recuperator cycle is a thermodynamic cycle of a gas turbine, and as shown in fig. 1, C represents a compressor, CB represents a combustion chamber, T represents a turbine, RE represents a recuperator, and G represents a generator. The air compressor C sucks air from the atmosphere, pressurizes the air and then discharges the air to the regenerator RE; the air enters a combustion chamber CB after heat exchange with the exhaust smoke of the gas turbine in a heat regenerator RE; natural gas (or other fuels) and hot air are mixed and combusted and then enter a turbine T to do work, the turbine T drives a compressor C and a generator G to rotate through a shaft, and the generator G generates electric energy; the turbine T discharges smoke to the atmosphere through the regenerator RE to recover heat.
In order to better achieve the goals of high efficiency, low emission, low cost, high flexibility and the like, and meet diversified demands, various novel thermodynamic cycles based on gas turbines are continuously proposed and developed. The wet gas turbine cycle is one of the most representative. The circulation adopts mixed working medium (wet air) and carries out heat recovery and air humidification at different positions according to the requirement. Depending on the technical route, the air humidification cycle can be broadly divided into three specific forms: circulation of the spray at different locations (compressor front/interstage/rear etc.) in the gas circuit; a vapor injection cycle (SteamInjectedGasTurbine, STIG or Cheng cycle); and a wet air turbine cycle (HumidAirTurbine, HAT cycle) for recovering low-grade waste heat and humidifying air through the humidifier. Compared with other novel power cycles, the common characteristics of the wet gas turbine cycle are that: (1) the power consumption of the gas compressor is reduced, or (and) the internal waste heat of the gas turbine cycle is fully utilized by means of spraying, steam injection and humidification processes, so that the efficiency is improved; (2) air humidification, increased working medium flow and improved circulation specific work; (3) the wet air is combusted, so that the NOx emission of the system is effectively reduced; (4) the steam bottom circulation component is omitted, the structure is more compact, and the cost is reduced; (5) the air humidification increases the adjustable quantity and improves the operation flexibility of the system.
The humidification cycle (HAT cycle) is a representative and main part of an air humidification cycle with a water circuit, and the flow is shown in fig. 2, C represents a compressor, CB represents a combustion chamber, T represents a turbine, RE represents a regenerator, G represents a generator, AC represents an aftercooler, EC represents an economizer, H represents a humidifier, and P1 and P2 represent a water pump. The air compressor C sucks air from the atmosphere, pressurizes the air and discharges the air to the aftercooler AC; the air in the aftercooler AC exchanges heat with water from the bottom of the humidifier H, and the air is sent into the humidifier H after being cooled; the air in the humidifier H is in countercurrent contact with hot water, the temperature of the air is raised and humidified, and the water temperature is reduced; the wet air from the humidifier H enters a combustion chamber CB after heat exchange with the exhaust smoke of the gas turbine in a heat regenerator RE; natural gas (or other fuels) and wet air are mixed and combusted and then enter a turbine T to do work, the turbine T drives a compressor C and a generator G to rotate through a shaft, and the generator G generates electric energy; the turbine T discharges smoke through a heat regenerator RE and an economizer EC, exchanges heat with wet air and water respectively, recovers waste heat and discharges the waste heat into the atmosphere; the cold water from the humidifier H exchanges heat with the flue gas in the economizer, and the water after heating is mixed with the water discharged from the aftercooler and then is sent to the upper part of the humidifier. The bottom of the humidifier H is connected to the economizer EC via a water pump P1. The water pump P2 is connected to the underside of the humidifier H.
In addition to having the common features of an air humidification cycle, HAT cycle has the following unique advantages: (1) the water is subjected to variable-temperature evaporation in the humidifier, low-grade waste heat in the system can be more fully utilized, and the system is superior to steam injection circulation and combined circulation from the thermodynamic aspect, so that the system has the potential of highest power generation efficiency; (2) turbine blade cooling with humid air can increase cycle efficiency compared to using air as a cooling medium; (3) high efficiency can be achieved over a wide pressure ratio range.
Disclosure of Invention
The volume flow of the outlet gas of the compressor in the humidification cycle can be increased by more than 20% in the humidification process, and the turbine through-flow capacity is designed according to the matching of the flow of the compressor in the existing installed regenerative cycle gas turbine unit, so that the humidification working condition is not considered, and if the humidification cycle is changed directly, the exhaust pressure of the compressor is obviously increased, and surging is caused.
In order to balance the throughflow of the compressor and the turbine, the transformation of the existing regenerative cycle gas turbine into a humidification cycle gas turbine can be realized by adopting a method of transforming a core component (the compressor or the turbine) of the gas turbine or arranging an exhaust gas emptying bypass in an exhaust pipeline of the compressor. The difficulty of directly reforming the core component of the gas turbine is great, the overall performance of the reformed gas turbine is difficult to ensure, the method is equivalent to the through-flow matching of redesigning a gas turbine, and the uncertainty of system reforming is extremely large. An exhaust vent bypass is arranged on an exhaust pipeline of the air compressor, and no exhaust residue Wen Yuya is recycled, so that the system efficiency can be directly and obviously reduced, and no benefit is caused after transformation. Based on the reasons, the feasibility technology of changing the existing installed gas turbine into the humidification circulation is lack and has large uncertainty, so that the user transformation will is reduced, and the popularization of the humidification circulation gas turbine is influenced.
From the aspect of difficulty in transformation, the method for arranging the exhaust vent bypass on the exhaust pipeline of the compressor is a feasible scheme, but recycling of the residual temperature and the residual pressure of the exhaust is considered, otherwise, the aim of improving the system efficiency by humidification circulation is difficult to realize. From the aspect of energy cascade utilization, the expander power generation is the first choice for recycling the exhaust residual temperature and residual pressure. But the gas turbine has the advantages of compact structure, small power generation scale, economy, transformation complexity, low power generation efficiency and the like, and can combine the characteristics of distributed energy supply by utilizing the exhaust residual temperature and residual pressure, and the utilization of residual temperature and residual pressure in a step and multiple purposes, so that the overall energy utilization rate is higher.
The invention provides a method for changing the regenerative cycle of an existing gas turbine into the humidification cycle, which is a humidification gas turbine cycle process for utilizing the residual temperature and the residual pressure of the exhaust gas of a compressor, and is used for reforming the regenerative cycle unit of the existing installed gas turbine into the humidification gas turbine cycle and improving the energy utilization rate of a system. Based on the energy cascade utilization thought, a process of exhausting the residual Wen Yuya of the exhaust gas by the gas compressor is set, and the high-grade waste heat of the exhaust gas is recovered first and is used for heating the circulating humidifying water of the humidifying gas turbine, so that the humidifying circulating efficiency is improved; the residual pressure process is divided into three operation modes of summer, winter and spring and autumn, the winter mode is used for recovering exhaust low-grade waste heat for heat supply, and the residual pressure is used for driving a pneumatic water pump and pressurizing circulating humidifying water of the gas turbine; in the summer mode, the low-grade waste heat of the exhaust gas is directly radiated to the atmosphere, the cooled compressed air is subjected to work in the adiabatic expansion machine, the air is rapidly cooled after the work expansion, and the cold air is directly used for fresh air cooling of a building; in the spring and autumn mode, the low-grade waste heat of the exhaust is directly radiated to the atmosphere, and the exhaust residual pressure is directly utilized to drive the pneumatic water pump.
The invention adopts the following technical scheme:
a method for changing the regenerative cycle of a gas turbine into a humidification cycle includes that a gas compressor C sucks air from the atmosphere, pressurizes the air and then discharges the air to an aftercooler AC; in the aftercooler AC, the air exchanges heat with cold water, and the air is cooled; an air discharge path is arranged on an air pipeline between the aftercooler AC and the humidifier H, part of air is led out from the air discharge path, and the air discharge quantity is regulated through a valve according to different humidifying circulation working conditions, so that the numerical variation of the outlet pressure of the compressor C is maintained to be not more than 3%; the air in the humidifier H is in countercurrent contact with hot water, the temperature of the air is raised and humidified, and the water temperature is reduced; the wet air from the humidifier H enters a combustion chamber CB after heat exchange with the exhaust smoke of the gas turbine in a heat regenerator RE; natural gas or other fuels are mixed with wet air and then enter a turbine to do work, the turbine T drives a compressor C and a generator G to rotate through a shaft, and the generator G generates electric energy; the turbine exhaust gas passes through a heat regenerator RE and an economizer EC, exchanges heat with wet air and water respectively, recovers waste heat and is discharged into the atmosphere;
the outlet water of the humidifier H is divided into two paths after passing through the heat supply network heat exchanger WC, and enters the aftercooler AC and the economizer EC respectively, and the water is mixed and returned to the humidifier H after being heated.
In the invention, maintaining the numerical variation of the outlet pressure of the compressor C not to exceed 3% means maintaining the numerical variation of the outlet pressure of the compressor C within the range of-3%.
Further, the method for changing the regenerative cycle of the gas turbine into the humidification cycle uses a humidification gas turbine circulation system with residual temperature and residual pressure utilization of the exhaust gas discharged by a gas compressor, wherein the circulation system comprises a gas compressor C, a combustion chamber CB, a turbine T, a regenerator RE, a generator G, an aftercooler AC, an economizer EC, a humidifier H, a heat supply network heat exchanger WC, a cooling heat exchanger CT, an adiabatic expander EP, a first electric water pump P1, a pneumatic water pump P3, a first valve V1 and a second valve V2;
the gas inlet of the gas compressor C is communicated with the atmosphere, the gas outlet of the gas compressor C is communicated with the AC gas inlet of the aftercooler, the AC gas outlet of the aftercooler is divided into two paths, one path is communicated with the CT gas inlet of the cooling heat exchanger, and the other path is connected with the gas inlet of the humidifier H; the gas outlet of the humidifier H is communicated with the air inlet of the regenerator RE, the air outlet of the regenerator RE is communicated with the air inlet of the combustion chamber CB, the fuel inlet of the combustion chamber CB is communicated with a natural gas source, the gas outlet of the combustion chamber CB is communicated with the gas inlet of the turbine T, the smoke outlet of the turbine T is communicated with the smoke inlet of the regenerator RE, the smoke outlet of the regenerator RE is communicated with the smoke inlet of the economizer EC, and the smoke outlet of the economizer EC is communicated with the atmosphere; the CT gas outlet of the cooling heat exchanger is divided into two paths: one path is sequentially connected with a first valve V1 and a driving air source inlet of a pneumatic water pump P3, and a driving air source outlet of the pneumatic water pump P3 is communicated with the atmosphere; the other path is sequentially connected with a second valve V2 and a gas inlet of an adiabatic expander EP, and a gas outlet of the adiabatic expander EP is communicated with a building air conditioner air duct;
the waterway at the bottom of the humidifier H is divided into two paths: one path is communicated with an inlet of a first electric water pump P1, the other path is communicated with an inlet of a pneumatic water pump P3, and an outlet of the first electric water pump P1 is communicated with a humidifying water inlet of a heat supply network heat exchanger WC after being converged with an outlet pipeline of the pneumatic water pump P3; the humidifying water outlet of the heat supply network heat exchanger WC is divided into two paths: one path is communicated with a water inlet of the aftercooler AC, and the other path is communicated with a water inlet of the economizer EC; the water outlet of the aftercooler AC is communicated with the humidifying water inlet of the humidifier H after being converged with the water outlet pipeline of the economizer EC;
the generator G is connected with the compressor C and the turbine T through the same shaft.
Further, the method includes a summer mode, a winter mode, and a spring and autumn mode.
Further, summer mode: the first valve V1 is closed, the second valve V2 regulates the air quantity of the emptying path, the air exchanges heat with cooling water (usually from a cooling tower) in the cooling heat exchanger CT for cooling, the air residual pressure is utilized to do work in the adiabatic expander EP for further cooling to become cold air, and the cold air is directly connected into an air duct of a building air conditioner to serve as cold fresh air; and stopping the water circulation of the heat supply network at the WC position of the heat supply network heat exchanger.
Further, winter mode: the second valve V2 is closed and the first valve V1 regulates the amount of the vent path air; at the WC position of the heat supply network regenerator, the outlet water of the humidifier exchanges heat with heat supply network water (building air conditioner heat supply network backwater), so that the inlet water temperature of the aftercooler and the economizer is reduced, the air temperature of an emptying path and the final exhaust gas temperature are further reduced, and the waste heat of the air of the emptying path is recovered; the electric water pump and the pneumatic water pump work simultaneously, air drives the pneumatic water pump to work under full load by utilizing residual pressure, and the electric water pump is regulated through frequency conversion, so that the water flow entering the aftercooler AC and the economizer EC is kept constant; and cooling the position of the heat exchanger CT, and stopping cooling water circulation.
Further, spring and autumn mode: the second valve V2 is closed and the first valve V1 regulates the amount of the vent path air; the air exchanges heat with cooling water (usually from a cooling tower) in a cooling heat exchanger CT, the cooled air residual pressure is utilized to drive a pneumatic water pump to work under full load, and the electric water pump is regulated through frequency conversion to maintain constant water flow entering an aftercooler AC and an economizer EC; and stopping the water circulation of the heat supply network at the WC position of the heat supply network heat exchanger.
The beneficial effects are that:
the invention provides a method for changing the regenerative cycle of a gas turbine into the humidification cycle, which adopts the technical scheme of the invention, and can realize the through-flow matching of the two without changing the core components (a gas compressor and a turbine) of the gas turbine, thereby greatly reducing the transformation difficulty of changing the existing gas turbine unit into the humidification cycle and keeping higher system energy utilization rate. An effective technical path is provided for changing the existing installed gas turbine regenerative cycle unit into humidification cycle.
Drawings
FIG. 1 gas turbine recuperated cycle; in the figure, C represents a compressor, CB represents a combustion chamber, T represents a turbine, RE represents a regenerator, and G represents a generator;
FIG. 2HAT cycle typical flow; in the figure, C represents a compressor, CB represents a combustion chamber, T represents a turbine, RE represents a regenerator, G represents a generator, AC represents an aftercooler, EC represents an economizer, H represents a humidifier, and P11 and P12 represent water pumps;
FIG. 3 illustrates a wet gas turbine cycle with residual temperature and pressure utilization for compressor bleed air of the present invention; in the figure, C denotes a compressor, CB denotes a combustion chamber, T denotes a turbine, RE denotes a regenerator, G denotes a generator, AC denotes an aftercooler, EC denotes an economizer, H denotes a humidifier, WC denotes a heat-supply-network heat exchanger, CT denotes a cooling heat exchanger, EP denotes an adiabatic expander, P1 denotes a first electric water pump, P2 denotes a second electric water pump, P3 denotes a pneumatic water pump, V1 denotes a first valve, and V2 denotes a second valve.
Detailed Description
The invention will now be described in detail with reference to the accompanying drawings and specific embodiments thereof. The following examples are intended to be illustrative only and the scope of the invention is to be construed as including the full breadth of the claims and by the recitation of the following examples, the full breadth of the claims can be fully set forth by those skilled in the art.
The circulation flow of the humidifying gas turbine with the residual temperature and residual pressure utilization of the air compressor discharging and exhausting is shown in fig. 3, wherein C represents the air compressor, CB represents a combustion chamber, T represents a turbine, RE represents a heat regenerator, G represents a generator, AC represents an aftercooler, EC represents an economizer, H represents the humidifier, WC represents a heat network heat exchanger, CT represents a cooling heat exchanger, EP represents an adiabatic expander, P1 represents a first electric water pump, P2 represents a second electric water pump, P3 represents a pneumatic water pump, V1 represents a first valve, and V2 represents a second valve. As shown in fig. 3, the humidification gas turbine circulation system for utilizing the residual temperature and the residual pressure of the air compressor discharge exhaust gas comprises an air compressor C, a combustion chamber CB, a turbine T, a heat regenerator RE, a generator G, an aftercooler AC, an economizer EC, a humidifier H, a heat supply network heat exchanger WC, a cooling heat exchanger CT, an adiabatic expander EP, a first electric water pump P1, a second electric water pump P2, a pneumatic water pump P3, a first valve V1 and a second valve V2. In the aspect of the gas circuit, a gas inlet of the gas compressor C is communicated with the atmosphere, a gas outlet of the gas compressor C is communicated with an AC gas inlet of the aftercooler, the AC gas outlet of the aftercooler is divided into two paths, one path is communicated with a CT gas inlet of the cooling heat exchanger, and the other path is connected with a gas inlet of the humidifier H. The gas outlet of the humidifier H is communicated with the air inlet of the regenerator RE, the air outlet of the regenerator RE is communicated with the air inlet of the combustion chamber CB, the fuel inlet of the combustion chamber CB is communicated with a natural gas source, the gas outlet of the combustion chamber CB is communicated with the gas inlet of the turbine T, the smoke outlet of the turbine T is communicated with the smoke inlet of the regenerator RE, the smoke outlet of the regenerator RE is communicated with the smoke inlet of the economizer EC, and the smoke outlet of the economizer EC is communicated with the atmosphere. The CT gas outlet of the cooling heat exchanger is divided into two paths: one path is communicated with a driving air source inlet of the pneumatic water pump P3 (a first valve V1 is arranged in the middle pipeline), and a driving air source outlet of the pneumatic water pump P3 is communicated with the atmosphere; the other path is communicated with the gas inlet of the adiabatic expander EP (the middle pipeline is provided with a second valve V2), and the gas outlet of the adiabatic expander EP is communicated with the air duct of the building air conditioner. In the aspect of waterways, the waterway at the bottom of the humidifier H is divided into two paths: one path is communicated with an inlet of a first electric water pump P1, the other path is communicated with an inlet of a pneumatic water pump P3, and an outlet of the first electric water pump P1 is communicated with a humidifying water inlet of a heat supply network heat exchanger WC after being converged with an outlet pipeline of the pneumatic water pump P3; the heat supply network water inlet and outlet of the heat supply network heat exchanger WC are respectively communicated with the heat supply network, and the humidifying water outlet of the heat supply network heat exchanger WC is divided into two paths: one path is communicated with the water inlet of the aftercooler AC, and the other path is communicated with the water inlet of the economizer EC. The water outlet of the aftercooler AC is communicated with the humidifying water inlet of the humidifier H after being converged with the water outlet pipeline of the economizer EC. The water inlet of the second electric water pump P2 is communicated with a water source, and the water outlet of the second electric water pump P2 is communicated with a water supplementing port of the humidifier H. In mechanical aspect, the generator G is connected with the compressor C and the turbine T through the same shaft.
A process for changing the regenerative cycle of a gas turbine into the humidification cycle comprises the steps of using the humidification gas turbine circulation system with the residual temperature and the residual pressure of the exhaust gas of the compressor, and dividing the process flow into a summer mode, a winter mode and a spring and autumn mode.
Summer mode:
the gas circuit flow is as follows: the air compressor C sucks air from the atmosphere, pressurizes the air and discharges the air to the aftercooler AC; in the aftercooler AC, the air exchanges heat with cold water, and the air is cooled; an air discharge path is arranged on an air pipeline between the aftercooler AC and the humidifier H, part of air is led out from the air discharge path, the air quantity of the air discharge path is regulated through a second valve V2 according to different humidification circulation working conditions, the variation of the pressure at the outlet of the compressor C is maintained to be not more than 3%, the air discharge path exchanges heat with cooling water (usually from a cooling tower) in a cooling heat exchanger CT for cooling, the air is further cooled by acting in an adiabatic expander EP by utilizing the residual air pressure to become cold air, and the cold air is directly connected into a building air conditioning duct to serve as cold fresh air. The air in the humidifier H is in countercurrent contact with hot water, the temperature of the air is raised and humidified, and the water temperature is reduced; the wet air from the humidifier H enters a combustion chamber CB after heat exchange with the exhaust smoke of the gas turbine in a heat regenerator RE; in the combustion chamber CB, natural gas (or other fuels) and wet air are mixed and combusted and then enter a turbine T to do work, the turbine T drives a compressor C and a generator G to rotate through a shaft, and the generator G generates electric energy; the turbine T discharges smoke through a heat regenerator RE and an economizer EC, exchanges heat with wet air and water respectively, recovers waste heat and discharges the waste heat into the atmosphere; the first valve V1 is closed and the pneumatic water pump P3 is not operated.
The waterway flow is as follows: the outlet water of the humidifier H is divided into two paths after passing through the heat supply network heat exchanger WC, and enters the aftercooler AC and the economizer EC respectively, and the water is mixed and returned to the humidifier H after being heated; and stopping the water circulation of the heat supply network at the WC position of the heat supply network heat exchanger.
Winter mode:
the gas circuit flow is as follows: the air compressor C sucks air from the atmosphere, pressurizes the air and discharges the air to the aftercooler AC; in the aftercooler AC, the air exchanges heat with cold water, and the air is cooled; an air discharge path is arranged on an air pipeline between the aftercooler AC and the humidifier H, part of air is led out from the air discharge path, the air discharge quantity is regulated through a first valve V1 according to different humidification circulation working conditions, the pressure variation of an outlet of the compressor C is maintained to be not more than 3%, and the air drives a pneumatic water pump P3 to work under full load by residual pressure. The air in the humidifier H is in countercurrent contact with hot water, the temperature of the air is raised and humidified, and the water temperature is reduced; the wet air from the humidifier H enters a combustion chamber CB after heat exchange with the exhaust smoke of the gas turbine in a heat regenerator RE; in the combustion chamber CB, natural gas (or other fuels) and wet air are mixed and combusted and then enter a turbine T to do work, the turbine T drives a compressor C and a generator G to rotate through a shaft, and the generator G generates electric energy; the turbine T discharges smoke through a heat regenerator RE and an economizer EC, exchanges heat with wet air and water respectively, recovers waste heat and discharges the waste heat into the atmosphere; the second valve V2 is closed and the adiabatic expander EP is not operated.
The waterway flow is as follows: the outlet water of the humidifier H is divided into two paths after passing through the heat supply network heat exchanger WC, and enters the aftercooler AC and the economizer EC respectively, and the water is mixed and returned to the humidifier H after being heated; at the WC position of the heat supply network regenerator, the outlet water of the humidifier exchanges heat with heat supply network water (building air conditioner heat supply network backwater), so that the inlet water temperature of the aftercooler AC and the economizer EC is reduced, the air temperature of an emptying path and the final exhaust gas temperature are further reduced, and the air waste heat of the emptying path is recovered; the electric water pump P1 is regulated through frequency conversion, so that the total water quantity of the electric water pump P1 and the pneumatic water pump P3 is basically kept unchanged (the flow numerical deviation is controlled to be +/-10 percent), and the water flow entering the aftercooler AC and the economizer EC is maintained; and cooling the position of the heat exchanger CT, and stopping cooling water circulation.
Spring and autumn mode:
the gas circuit flow is as follows: the air compressor C sucks air from the atmosphere, pressurizes the air and discharges the air to the aftercooler AC; in the aftercooler AC, the air exchanges heat with cold water, and the air is cooled; an air discharge path is arranged on an air pipeline between the aftercooler AC and the humidifier H, part of air is led out from the air discharge path, the air discharge quantity is regulated through a first valve V1 according to different humidification circulation working conditions, the pressure change quantity of an outlet of the air compressor C is maintained to be not more than 3%, the air exchanges heat with cooling water (usually from a cooling tower) in a cooling heat exchanger CT for cooling, and the cooled air residual pressure is utilized for driving a pneumatic water pump P3 to work under full load. The air in the humidifier H is in countercurrent contact with hot water, the temperature of the air is raised and humidified, and the water temperature is reduced; the wet air from the humidifier H enters a combustion chamber CB after heat exchange with the exhaust smoke of the gas turbine in a heat regenerator RE; in the combustion chamber CB, natural gas (or other fuels) and wet air are mixed and combusted and then enter a turbine T to do work, the turbine T drives a compressor C and a generator G to rotate through a shaft, and the generator G generates electric energy; the turbine T discharges smoke through a heat regenerator RE and an economizer EC, exchanges heat with wet air and water respectively, recovers waste heat and discharges the waste heat into the atmosphere; the second valve V2 is closed and the adiabatic expander EP is not operated.
The waterway flow is as follows: the outlet water of the humidifier H is divided into two paths after passing through the heat supply network heat exchanger WC, and enters the aftercooler AC and the economizer EC respectively, and the water is mixed and returned to the humidifier H after being heated; the electric water pump P1 is regulated through frequency conversion, so that the total water quantity of the electric water pump P1 and the pneumatic water pump P3 is basically kept unchanged (the flow numerical deviation is controlled to be +/-10 percent), and the water flow entering the aftercooler AC and the economizer EC is maintained; and stopping the water circulation of the heat supply network at the WC position of the heat supply network heat exchanger.
The present invention is not described in detail in part as being well known to those skilled in the art. The above examples are merely illustrative of preferred embodiments of the invention, which are not exhaustive of all details, nor are they intended to limit the invention to the particular embodiments disclosed. Various modifications and improvements of the technical scheme of the present invention will fall within the protection scope of the present invention as defined in the claims without departing from the design spirit of the present invention.
Claims (6)
1. A method for changing the regenerative cycle of a gas turbine into a humidification cycle, characterized in that a compressor (C) sucks air from the atmosphere, pressurizes the air and then discharges the air to an Aftercooler (AC); in an Aftercooler (AC), air exchanges heat with cold water, and the air is cooled; an air discharge path is arranged on an air pipeline between a Aftercooler (AC) and a humidifier (H), part of air is led out from the air discharge path, and the air discharge quantity is regulated through a valve according to different humidifying circulation working conditions, so that the numerical variation of the outlet pressure of the compressor (C) is maintained to be no more than 3%; the air in the humidifier (H) is in countercurrent contact with hot water, the temperature of the air is raised and humidified, and the water temperature is reduced; the wet air from the humidifier (H) enters a combustion Chamber (CB) after heat exchange with the exhaust gas of the gas turbine in a heat Regenerator (RE); natural gas (or other fuels) and wet air are mixed and combusted and then enter a turbine to apply work, the turbine (T) drives a gas compressor (C) and a generator (G) to rotate through a shaft, and the generator (G) generates electric energy; the turbine exhaust gas passes through a heat Regenerator (RE) and an Economizer (EC), exchanges heat with wet air and water respectively, recovers waste heat and is discharged into the atmosphere;
the outlet water of the humidifier (H) is divided into two paths after passing through a heat supply network heat exchanger (WC) and respectively enters a Aftercooler (AC) and an Economizer (EC), and the water is mixed and returned to the humidifier (H) after being heated.
2. The method according to claim 1, characterized in that the method of changing the gas turbine regenerative cycle to a humidification cycle uses a humidification gas turbine cycle system with a compressor bleed air with a utilization of the residual temperature and pressure, the cycle system comprising a compressor (C), a combustion Chamber (CB), a turbine (T), a Regenerator (RE), a generator (G), a Aftercooler (AC), an Economizer (EC), a humidifier (H), a heat network heat exchanger (WC), a cooling heat exchanger (CT), an adiabatic Expander (EP), a first electric water pump (P1), a pneumatic water pump (P3), a first valve (V1) and a second valve (V2);
the gas inlet of the gas compressor (C) is communicated with the atmosphere, the gas outlet of the gas compressor (C) is communicated with the gas inlet of the Aftercooler (AC), the gas outlet of the Aftercooler (AC) is divided into two paths, one path is communicated with the gas inlet of the cooling heat exchanger (CT), and the other path is connected with the gas inlet of the humidifier (H); the gas outlet of the humidifier (H) is communicated with the air inlet of the heat Regenerator (RE), the air outlet of the heat Regenerator (RE) is communicated with the air inlet of the combustion Chamber (CB), the fuel inlet of the combustion Chamber (CB) is communicated with a natural gas source, the gas outlet of the combustion Chamber (CB) is communicated with the gas inlet of the turbine (T), the smoke outlet of the turbine (T) is communicated with the smoke inlet of the heat Regenerator (RE), the smoke outlet of the heat Regenerator (RE) is communicated with the smoke inlet of the Economizer (EC), and the smoke outlet of the Economizer (EC) is communicated with the atmosphere; the gas outlet of the cooling heat exchanger (CT) is divided into two paths: one path is sequentially connected with a driving air source inlet of a first valve (V1) and a pneumatic water pump (P3), and a driving air source outlet of the pneumatic water pump (P3) is communicated with the atmosphere; the other path is sequentially connected with a second valve (V2) and a gas inlet of an adiabatic Expander (EP), and a gas outlet of the adiabatic Expander (EP) is communicated with an air duct of the building air conditioner;
the waterway at the bottom of the humidifier (H) is divided into two paths: one path is communicated with an inlet of a first electric water pump (P1), the other path is communicated with an inlet of a pneumatic water pump (P3), and an outlet of the first electric water pump (P1) is communicated with a humidifying water inlet of a heat supply network heat exchanger (WC) after being converged with an outlet pipeline of the pneumatic water pump (P3); the humidifying water outlet of the heat supply network heat exchanger (WC) is divided into two paths: one path is communicated with a water inlet of an Aftercooler (AC), and the other path is communicated with a water inlet of an Economizer (EC); the water outlet of the Aftercooler (AC) is communicated with the humidifying water inlet of the humidifier (H) after being converged with the water outlet pipeline of the Economizer (EC);
the generator (G) is connected with the compressor (C) and the turbine (T) through the same shaft.
3. The method of claim 1, wherein the method comprises a summer mode, a winter mode, and a spring and autumn mode.
4. A method according to claim 3, characterized in that in summer mode: the first valve (V1) is closed, the second valve (V2) regulates the air quantity of the emptying path, the air exchanges heat with cooling water (from a cooling tower) in the cooling heat exchanger (CT) for cooling, the air residual pressure is utilized to apply work in the adiabatic Expander (EP) for further cooling to become cold air, and the cold air is directly connected into an air duct of a building air conditioner to serve as cold fresh air; and stopping the circulation of the water of the heat supply network at the position of the heat supply network heat exchanger (WC).
5. A method according to claim 3, characterized in that in winter mode: the second valve (V2) is closed, and the first valve (V1) regulates the air quantity of the emptying path; at the heat network regenerator (WC), the outlet water of the humidifier exchanges heat with heat network water (building air conditioner heat network backwater), so that the inlet water temperature of the aftercooler and the economizer is reduced, the air temperature of an emptying path and the final exhaust gas temperature are further reduced, and the waste heat of the air of the emptying path is recovered; the electric water pump and the pneumatic water pump work simultaneously, air drives the pneumatic water pump to work under full load by utilizing residual pressure, and the electric water pump is regulated through frequency conversion, so that the water flow entering the Aftercooler (AC) and the Economizer (EC) is kept constant; at the cooling heat exchanger (CT), the cooling water circulation is stopped.
6. A method according to claim 3, characterized in that the spring and autumn mode: the second valve (V2) is closed, and the first valve (V1) regulates the air quantity of the emptying path; the air exchanges heat with cooling water (from a cooling tower) in a cooling heat exchanger (CT), the cooled air residual pressure is utilized to drive a pneumatic water pump to work under full load, and the electric water pump is regulated through frequency conversion to maintain constant water flow entering a Aftercooler (AC) and an Economizer (EC); and stopping the circulation of the water of the heat supply network at the position of the heat supply network heat exchanger (WC).
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