WO2015096414A1 - 一种高压再热燃气-蒸汽联合循环发电系统及发电方法 - Google Patents

一种高压再热燃气-蒸汽联合循环发电系统及发电方法 Download PDF

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WO2015096414A1
WO2015096414A1 PCT/CN2014/080217 CN2014080217W WO2015096414A1 WO 2015096414 A1 WO2015096414 A1 WO 2015096414A1 CN 2014080217 W CN2014080217 W CN 2014080217W WO 2015096414 A1 WO2015096414 A1 WO 2015096414A1
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pressure
power generation
gas turbine
medium
steam
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PCT/CN2014/080217
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English (en)
French (fr)
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郭桦
付忠广
杨天亮
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贾金祥
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国电新能源技术研究院
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K5/00—Plants characterised by use of means for storing steam in an alkali to increase steam pressure, e.g. of Honigmann or Koenemann type
    • F01K5/02—Plants characterised by use of means for storing steam in an alkali to increase steam pressure, e.g. of Honigmann or Koenemann type used in regenerative installation
    • 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
    • Y02E20/00—Combustion technologies with mitigation potential
    • Y02E20/16—Combined cycle power plant [CCPP], or combined cycle gas turbine [CCGT]

Definitions

  • the invention relates to a gas-steam combined cycle power generation device, in particular to a high pressure reheat gas-steam combined cycle Ring power system.
  • the invention also relates to a power generation method in which the power generation system can be used.
  • the most common steam cycle for conventional thermal power generation is the Rankine Cycle, but based on the Rankine cycle.
  • Power generation technology has problems such as low power generation efficiency, large consumption of coal, and serious pollution.
  • the traditional steam cycle power generation method has no Law to meet the needs of sustainable social and economic development, as fossil energy, non-renewableness of coal and petroleum resources and environmental issues The growing severity has led researchers to focus more and more on energy-efficient, clean power generation technologies.
  • Gas turbine is a kind of mining Brayton Cycle, thermal power equipment with air and gas as working fluid, gas turbine and its combined cycle With low pollution, high power supply efficiency and wide load adjustment range, natural gas can be directly applied to gas turbine installations. There is no need for a separate working fluid generating device.
  • the world's natural gas resources are abundant and low-cost, in the national economic development strategy and country Driven by the demand for competition, many countries have advanced gas turbine technology as their priority for science and technology development and key The focus of technical research and development.
  • the combined cycle efficiency is still greatly improved. Space.
  • GT26 sequential Combustion Systems
  • Reheat cycle achieving a higher pressure ratio
  • a set of 22 high-efficiency subsonic compressors to double the air to the conventional engine pressure ratio
  • the high pressure is pressed into the circular environmentally friendly combustion chamber, and the process requirements for the gas turbine equipment are extremely high and the cost is high.
  • the invention develops an existing gas-steam combined cycle power generation method for the existing 9FA-class gas turbine combined cycle
  • the system represents a modified combined cycle power generation system, adding high pressure reheat and intermediate cooling processes to the gas cycle, and The use of intercooling heat is improved in the steam cycle mode, so that the combined cycle efficiency ratio of the power generation system is F
  • the gas turbine-based combined cycle is increased by 3 to 5 percentage points, and the single-machine output power is increased by more than 70% to 800 MW.
  • the invention also provides a modified high pressure reheat gas-steam combined cycle power generation method.
  • the present invention modifies the existing 9FA gas turbine combined cycle, the original simple cloth in the gas turbine
  • the high-pressure reheat and intermediate cooling processes are added to the Layton cycle to form a gas turbine system for performing complex Brayton cycles;
  • the steam cycle part of the steam water system is improved, and the intercooler cooling water heat energy is recycled in the steam cycle; the heat of the invention
  • the comparison between the force cycle and the existing 9FA and GT26 combined cycle system is shown in Figure 2.
  • the present invention has obvious advantages. Increase, the overall cycle efficiency can also be improved.
  • the method of the present invention is that the steps include:
  • Gas cycle Based on the Brayton cycle, the compressed air is mixed with the fuel to produce a high-temperature gas turbine. Work to promote generator power generation, exhaust gas is introduced into the steam cycle to recover waste heat; the air is excess air, and the compression process is two-stage. Pressing with a primary compressor to the first stage pressure, and using a secondary compressor to press the secondary pressure, which is the highest pressure after air compression; At least one inter-stage cooling process is passed between the two-stage compression of the air; a reheating process is added to the gas cycle, and the gas is in one cycle After two turbines work, the gas with reduced pressure after the high pressure gas turbine is reheated, and then passed through the medium pressure gas turbine.
  • a power generation system based on the power generation method consisting of a gas turbine subsystem and a steam turbine subsystem, a gas turbine
  • the subsystem includes a medium pressure system and a high pressure system
  • the medium pressure system includes a primary compressor, a medium pressure combustion chamber, and a medium pressure gas turbine.
  • the high pressure system includes a secondary compressor, a high pressure combustion chamber and a high pressure gas turbine, and at least one is provided between the primary and secondary compressors. Interstage cooler; the air is sequentially compressed by the first and second compressors, and then enters the high pressure combustion chamber for combustion and heating.
  • the medium-pressure turbine works after reheating; the exhaust port of the medium-pressure system is connected to the steam turbine subsystem The exhaust gas recovers heat in the steam turbine subsystem.
  • the power generation system and method according to any one of (1) to (3) in order to further improve the efficiency of the combined cycle,
  • the cooling water of the intercooling process is introduced into the steam cycle, and when cooling water is used to cool the compressed air in the steam cycle Exchange of heat.
  • the cooling water of the intercooler is connected to the steam turbine subsystem.
  • the turbine subsystem uses waste heat boiler type, including waste heat boiler and steam turbine; waste heat boiler is used for recovery, conversion and utilization of combustion
  • waste heat boiler is used for recovery, conversion and utilization of combustion
  • the exhaust heat of the gas turbine is usually a group of heat exchanger tubes and vessels such as steam drums, economizers, evaporators, superheaters, and headers. Into.
  • the high pressure system and the medium voltage system can all be coaxially arranged to make high voltage
  • the medium pressure gas turbine and the two-stage compressor are all coaxial; they can also be arranged in a split shaft, and the first-stage compressor and the two-stage compressor are distributed in the same
  • the coaxial they are respectively coaxial with the medium pressure gas turbine and the high pressure gas turbine to form an independent high pressure system and medium voltage system.
  • the exhaust temperature is lower than At 538 °C, a single-pressure or multi-pressure non-reheated steam-water system is used; when the gas turbine exhaust temperature is higher than 538 °C, To use a steam-water system with reheat cycle; when the gas turbine exhaust temperature is higher than 593 °C, three-pressure reheating can be used.
  • the invention uses a 9FA-class gas turbine as a reference, and the exhaust gas temperature is 650 ° C, so three pressures are selected. Reheat steam cycle system.
  • the present invention is directed to a high pressure reheat gas-steam combined cycle
  • the loop performs parameter optimization to find optimized parameters based on the operation of the system of the present invention to achieve optimal combined cycle efficiency.
  • the invention uses aspen plus software to the current 9FA gas-fired combined cycle unit, GT26 unit and the invention
  • the power generation system is modeled, and the parameters of the power generation system of the present invention are optimized by calculation and analysis to determine the optimal working condition.
  • the system is simulated under ISO conditions, with an ambient temperature of 15 ° C, an atmospheric pressure of 0.10135 MPa, and an atmospheric relative humidity of 60%.
  • Refer to the operating parameters published by the 9FA system to determine the inlet air parameter is 0.1 MPa / 15 ° C / 678.5 kg / s, after the compressor is compressed
  • the gas parameter is 1.54MPa/404.5°C/678.5kg/s
  • the inlet gas parameter is 1.54MPa/15°C/16.8kg/s
  • the temperature parameter of the gas is 1.54MPa/1325°C/695.3kg/s
  • the exhaust gas parameter after the gas turbine is 0.105MPa/650°C/695.3kg.
  • the gas turbine works at 314 MW.
  • the steam part is a three-pressure reheat type, and the pressure levels are 9.63 MPa, 2.16 MPa, and 0.367 MPa, respectively.
  • the steam inlet parameters of the high pressure cylinder are 9.63MPa/540°C/90.8kg/s; the steam exhaust parameters of the high pressure cylinder are 2.16MPa/321°C/90.8kg/s; medium pressure
  • the steam inlet parameter of the cylinder is 2.16MPa/540°C/104.2kg/s;
  • the steam inlet parameter of the low pressure cylinder is 0.367MPa/300.3°C/121.5kg/s;
  • the number is 0.00484 MPa / 35.5 ° C / 121.5 kg / s.
  • the total output of the steam turbine is 160.7 MW.
  • parameter setting is performed with reference to the reference system, and the simulation results are compared with the existing GT26 system, such as Table 2. Shown.
  • the system of the present invention when operating in this parameter interval, the combined cycle efficiency is higher than 60.36%, which is better than the GT26 system using the benchmark system parameters of the present invention. 60.03% efficiency value;
  • the gas turbine efficiency of the system of the present invention can be Up to 42.96%, the combined cycle efficiency reached the highest 61.22%.
  • variable condition analysis is performed.
  • the system of the invention has a two-stage system of high pressure and medium pressure, and thus respectively By adjusting the intake air temperature of the high and medium pressure gas turbines, the efficiency of the system under different working conditions can be obtained. By summarizing the data, It is merged into Table 4.
  • the gas is reheated and burned to return to the first time.
  • the flat intake air temperature, and the control temperature is 1325 ° C, the relatively highest cycle efficiency can be obtained, at this time the combined cycle system
  • the total output power is 817MW, the gas turbine efficiency is 42.96%, and the combined cycle efficiency is 61.22%.
  • increasing the high pressure temperature to 1500 °C can achieve higher efficiency, but this temperature has exceeded the F class of the benchmark of the present invention.
  • the range of gas turbines, and the increased temperature have more stringent requirements on the system process, resulting in additional costs, so the temperature is increased Higher efficiency is not the invention direction of the system, so the 1500 °C data is not used as the best working condition parameter.
  • the first stage compressor and the first stage compressor Medium-pressure turbine coaxial, medium-pressure system constitutes a common Class-F gas turbine unit, and the high-pressure system can be regarded as an additional high-pressure part. low
  • the medium pressure system can be operated separately during the load.
  • the system of the present invention is similar to the conventional 9FA combined cycle unit.
  • the system of the present invention has the following main features:
  • the invention uses a reheat structure, which is different from the ordinary reheat unit, and the system of the present invention is optimally operated.
  • the high pressure of air is as high as 14 MPa, which is much higher than that of ordinary Class F gas turbines (1.5-2 MPa) and reheat units (about 3 MPa).
  • the invention sets the compressed air pressure of the first-stage compressor to the pressure level of the common gas turbine, and the secondary air compressor compresses the air to the invention. High voltage level
  • Intercooler heat recovery Since the present invention employs a high pressure of 14 MPa, the heat in the air compression process is greatly increased. Loss of quantity. Therefore, the system is equipped with an intercooler to reduce the inlet air temperature of the secondary compressor and reduce the power consumption of the compressor. In addition, In order to utilize this part of heat, the system is provided with a heat recovery part of the intercooler, and the cooling water of the intercooler is introduced into the waste heat boiler. Use it to make the cycle more efficient;
  • the invention can optionally arrange the high pressure system and the medium voltage system in a split shaft.
  • High pressure systems and medium voltage systems Structural separation makes the starting method more flexible, and the high-pressure system can be started according to the load; at the same time, the two compressors are distributed On different shafts, the gas turbine can not be dragged when it is distributed on the same shaft, which reduces the difficulty of starting the gas system.
  • the invention is compared with a conventional F-stage combined cycle unit.
  • the invention adds reheat and intercooling circulation device, running air
  • the highest pressure of compression is much higher than that of ordinary F-class units.
  • the efficiency of optimal efficiency is 3 percentage points higher than that of ordinary F-class units.
  • the stand-alone power is 73% higher, reaching 817MW.
  • the invention is compared to the GT26 unit.
  • the GT26 uses a subsonic compressor to compress the air once to twice the normal gas turbine pressure ratio (3 MPa), which requires high equipment and high cost.
  • the invention uses two-stage compression with intermediate cooling to compress the air by 14 MPa to achieve more
  • the high pressure ratio is structurally easy to implement and low in cost.
  • the GT26 is pressed into a circular environmentally friendly combustion chamber by a group of 22-stage high-efficiency subsonic compressors with a high pressure twice that of a conventional gas turbine. There is no intermediate cooling and it is expensive. Meanwhile, the combustion chamber is designed to reduce environmental emissions of NO x.
  • the invention adds a reheat cycle and an intermediate cooling cycle to the simple gas cycle of the existing 9FA gas turbine.
  • the system adopts a "command group" composed of multi-axis multi-combustion engine units, which is technically easier to implement and has a lower cost. .
  • the efficiency of the system of the present invention is 1.2 percentage points higher, and the efficiency is improved more than that of the actual running GT26 system.
  • the invention improves the efficiency of the combined cycle when operating in the vicinity of the optimal parameters, and the natural gas is emitted when the same amount of electricity is emitted.
  • the consumption is lower than that of the ordinary F-class gas combined cycle unit, so the power generation cost will be lower than that of the ordinary unit.
  • Table 5 compares the new high-pressure reheat system with the ordinary F-class gas turbine system through relevant calculations. Some data in the table are collected. Use an approximation.
  • the system of the present invention is widely used in place of the ordinary gas turbine, which can effectively reduce the fuel consumption and thus reduce Low greenhouse gas emissions.
  • FIG. 1 is a schematic structural view of a power generation system for a high-pressure and medium-voltage system of the present invention
  • FIG. 2 is a schematic structural view of a coaxial power generation system of a high voltage and medium voltage system according to the present invention
  • the structure of the power generation system of this embodiment is as shown in FIG.
  • the medium pressure gas turbine 13 is coaxial with the primary compressor 11, the high pressure gas turbine 23 and the secondary pressure
  • the gas machine 21 is coaxial, the gas turbine is coupled with the generators 10 and 20; the high pressure system and the medium voltage system are arranged in a split shaft;
  • a three-pressure reheat waste heat recovery boiler and a steam turbine are provided in the steam turbine subsystem.
  • the specific structure is: the water supply structure is divided into The high, medium and low pressure water paths are provided with a high pressure cylinder 69, an intermediate pressure cylinder 59 and a low pressure cylinder 49. Condenser 71 connected low
  • the pressure water pump 41 is divided into two paths after being pressurized, and the cold water pump 31, the intercooler 30, the high pressure steam drum 64 are sequentially connected in one way, and finally the connection is high.
  • the superheater 65 is pressed; the other is connected to the low-pressure economizer 42 in the waste heat boiler, and then connected to the high, medium and low pressure three paths respectively.
  • the pressure road is connected to the front high pressure economizer 62 and the rear high pressure economizer 63 through the high pressure water pump 61 in sequence, and finally merges with the intercooled water passage.
  • the high pressure steam drum 64 is connected, and then the high pressure superheater 65 is connected to the steam turbine high pressure cylinder 69, and the high pressure cylinder 69 is connected to the reheater.
  • the exhaust gas merges, the intermediate pressure cylinder 59 is connected through the reheater 55, and the intermediate pressure cylinder 59 is exhausted to the air inlet of the low pressure cylinder 49; the low pressure road
  • the low pressure steam drum 43 and the low pressure superheater 44 are connected in sequence, and are connected to the low pressure cylinder 49 together with the exhaust steam of the intermediate pressure cylinder 59.
  • the low pressure cylinder 49 The exhaust gas enters the condenser 71.
  • the steam turbine drives the generator 40 to output electrical energy to the outside.
  • air with a large excess coefficient enters through the air inlet A1, passes through the primary compressor 11 and two.
  • the two-stage compression of the stage compressor 21 is also intermediately cooled by compressed air through an intercooler 30.
  • Excessive high pressure The air enters the high pressure combustion chamber 22 and the natural gas injected through the high pressure system gas inlet B2 is ignited under a high pressure environment of 14 MPa.
  • the burning and burning flue gas includes a large amount of unreacted air, and these 1325 ° C high temperature flue gas pushes the high pressure gas turbine 23 And drive the high-voltage generator 20 to output electrical energy.
  • the smoke after the work enters the medium pressure combustion chamber 12, at a medium pressure ring of 1.54 MPa.
  • the hot boiler exhaust port C2 is discharged.
  • the operating parameter of the power generation system is set to: a first stage pressure of 1.54 MPa, a secondary pressure of 14 MPa, and an intercooling temperature of 100 ° C.
  • the medium pressure gas turbine intake air temperature and the high pressure gas turbine inlet air temperature are both 1325 ° C; the high, medium, and The low cylinder intake pressure is set to 9.63 MPa, 2.16 MPa and 0.367 MPa, respectively, and the corresponding intake air temperature is set to 565.5 ° C, 565.5 ° C and 305 ° C. See Table 6 for other parameter selection.
  • Embodiment 2 This embodiment is different from Embodiment 1 in that the intake air inlet temperatures of the high, medium and low cylinders in the steam power generation subsystem are respectively set.
  • the parameters were: 540 ° C, 540 ° C and 305 ° C; the remaining structure and parameters were basically consistent with Example 1.
  • the structure of the power generation system of this embodiment is as shown in FIG. 2.
  • This embodiment differs from Embodiment 1 in that a high voltage system and a medium voltage system The coaxial arrangement is adopted; the remaining structure and parameters are consistent with Embodiment 1.
  • first”, “second” or similar words do not mean any order, quality or importance, just Used to distinguish between different technical features.
  • the modifier "about” used in conjunction with the quantity contains the value and content context specified Meaning (for example: it contains errors when measuring a specific number).

Abstract

本发明涉及一种高压再热燃气-蒸汽联合循环发电系统及发电方法。该系统由燃气轮机子系统和蒸汽轮机子系统组成，燃气轮机子系统包含用于两级空气压缩、两次燃烧及高压、中压两次透平做功的装置；高温燃气初次做功后，进入中压燃烧室再热后二次做功，提高了整体循环的平均吸热温度；两级压气机中间设置至少一级间冷器，间冷器热流和两级压气机相连。蒸汽轮机子系统采用三压再热式的锅炉和蒸汽轮机，间冷器冷却水和高压水相连，高中低压水和间冷器冷却水多次分级吸热，高效利用了热能。本发明在最佳参数下运行时，联合循环效率较F级燃气轮机为主的联合循环系统提高3至5个百分点，单机输出功率提高70％以上，达到800MW级。

Description

一种高压再热燃气-蒸汽联合循环发电系统及发电方法 技术领域
本发明涉及一种燃气-蒸汽联合循环发电装置，特别涉及一种高压再热燃气-蒸汽联合循 环发电系统。本发明还涉及可使用该发电系统的发电方法。
背景技术
传统的火力发电最常用的蒸汽循环方式是朗肯循环(Rankine Cycle)，但是基于朗肯循环的 发电技术存在发电效率低，燃煤消耗量大，污染严重等问题。传统的蒸汽循环发电方式已无 法满足社会经济持续发展需要，作为化石能源，煤炭和石油资源的不可再生性以及环境问题 的日益严峻使研究人员将越来越多的目光投向节能、清洁的发电技术上。燃气轮机是一种采 用布雷顿循环(Brayton Cycle)，以空气和燃气为工质的热动力设备，燃气轮机及其联合循环具 有污染低、供电效率高和负荷调整范围宽等特点，天然气可以直接应用在燃气轮机装置上， 而不需要单独的工质发生设备。世界天然气资源充足、价格低廉，在国家经济发展战略和国 际竞争的需求推动下，许多国家都把先进的燃气轮机技术作为本国科技优先发展领域和关键 技术研究开发的重点。
世界上著名的一些燃气轮机制造商已研制成功一系列性能先进的机组。如GE公司9FA， ABB公司的GT26等。这些机组单机功率在200MW以上，燃气初温达到1260-1300℃以上， 压比10-30，简单循环效率为40％左右。为了进一步提高发电设备的效率，使用一种新的发 电技术——燃气-蒸汽联合循环(GTCC：Gas Turbine Combined Cycle)，将蒸汽轮机朗肯循环与 燃气轮机的布雷顿循环循环结合起来，同时利用了燃气轮机循环平均吸热温度高和蒸汽轮机 循环平均放热温度低的优点，又克服了两者的缺点，所以循环效率大大高于单独的燃气轮机 或蒸汽轮机发电机组。目前，燃气轮机组成联合循环后效率超过55％，如9FA组成的联合循 环系统效率可达56.7％，而GT26组成的KA26联合循环系统效率超过58％。
在F级燃气轮机为代表的燃气-蒸汽联合循环的基础上，联合循环效率还有较大幅度提升 的空间。而对于GT26系统，其采用了顺序燃烧装置(Sequential Combustion Systems)，利用了 再热循环，实现了较高压比，由一组22级高效亚音速压气机将空气以两倍于常规燃机压比的 高压压入环形环保燃烧室，对燃机设备的工艺要求极高，造价昂贵。
发明内容
本发明发展了现有的燃气-蒸汽联合循环的发电方法，针对现有的以9FA级燃机联合循环 系统为代表的联合循环发电系统进行改进，在燃气循环中加入高压再热和中间冷却过程，并 针对间冷热量的利用在蒸汽循环方式上进行了改进，使得该发电系统联合循环效率比以F级 燃气轮机为主的联合循环提高3到5个百分点，单机输出功率提高70％以上，达到800MW 级；本发明同时提供了改造后的高压再热燃气-蒸汽联合循环发电方法。
为实现以上发明目的，本发明改造现有的9FA燃机联合循环，在燃气轮机原有的简单布 雷顿循环中加入高压再热和中间冷却两项过程，形成进行复杂布雷顿循环的燃气轮机系统； 将蒸汽循环部分汽水系统进行改进，将间冷器冷却水热能在蒸汽循环中回收利用；本发明热 力循环和现有的9FA和GT26联合循环系统对比见图2，相比现有的系统，本发明比功明显 增加，整体循环效率也可获得一定提升。
本发明的技术方案具体为：
(1)本发明方法为，步骤包括：
燃气循环。以布雷顿循环为基础，通入压缩空气与燃料混合燃烧，产生的高温燃气透平 做功推动发电机发电，排气导入蒸汽循环回收余热；所述空气为过量空气，压缩过程为两级， 用一级压气机压至一级压力，用二级压气机压至二级压力，此压力即空气压缩后的最高压力； 空气两级压缩之间经过至少一级间冷过程；所述燃气循环中加入再热过程，一次循环中燃气 两次透平做功，将通过高压燃气透平后压力降低的燃气再热，再通过中压燃气透平。
蒸汽循环。以朗肯循环为基础，将燃气循环排气余热作为热源，由蒸汽做功推动发电机 发电。
基于该发电方法的一种发电系统，由燃气轮机子系统和蒸汽轮机子系统组成，燃气轮机 子系统包括中压系统和高压系统，中压系统包括一级压气机、中压燃烧室和中压燃气透平， 高压系统包括二级压气机、高压燃烧室和高压燃气透平，一级和二级压气机之间设有至少一 级间冷器；空气顺序通过所述一、二级压气机两级压缩后，进入高压燃烧室燃烧加热，高温 燃气高压透平后进入中压燃烧室，再热后中压透平做功；中压系统排气口连通蒸汽轮机子系 统，排气在蒸汽轮机子系统回收热量。
(2)根据(1)所述的发电系统和方法，运行系统时设置空气一级压力为1.5-2.4MPa， 二级压力为6-20MPa；设置一级间冷过程，间冷温度为100-200℃。
(3)根据(2)所述的发电系统和方法，运行系统时，参数进一步设置为，所述高压燃 气透平进气温度为1000-1500℃，中压燃气透平进气温度为1200-1500℃。
(4)根据(1)至(3)任一项所述的发电系统和方法，为进一步提高联合循环效率，将 所述间冷过程的冷却水引入所述蒸汽循环中，在蒸汽循环中回收利用冷却水冷却压缩空气时 交换的热量。对应的发电系统中，间冷器的冷却水连通蒸汽轮机子系统。
(5)根据(1)至(4)任一项所述的发电系统和方法，发电过程中进行蒸汽循环的蒸汽 轮机子系统使用余热锅炉型，包括余热锅炉和蒸汽轮机；余热锅炉用来回收、转换和利用燃 气轮机的排气余热，通常是汽包、省煤器、蒸发器、过热器以及集箱等换热管簇和容器等组 成的。
(6)根据(1)至(5)任一项所述的发电系统和方法，发电过程中进一步使用三压再热 式余热锅炉和蒸汽轮机；三压式给水结构分为高、中、低压水三路，给水在余热锅炉中分级 吸热，经过了水的加热、饱和水蒸发和饱和汽的过热三个阶段；蒸汽轮机设置有高、中、低 压三个缸，高压缸排气口与中压缸进气口之间连接余热锅炉中的再热器，高压缸排汽经再热 器再热后，进入中压缸做功。
(7)根据(6)所述的发电系统和方法，将间冷过程中的冷却水接入三压再热式蒸汽循 环的高压水路。对应的发电系统中，间冷器冷却水流可选择与余热锅炉中的高压气包连通， 冷却水经间冷器吸热后变为部分汽化的高压给水进入高压汽包，与另一部分直接来自蒸汽轮 机子系统的高压给水混合汽化，进入高压汽水流程。由于间冷水的加入，三压给水中的高压 给水量有很大的提高，高压给水所占比重较一般三压再热给水系统高。
(8)根据根据(6)至(7)任一项所述的发电系统和方法，所述蒸气循环中高、中、低 三路压力分别设置为9.63MPa、2.16MPa和0.367MPa。
(9)根据(8)所述的发电系统和方法，设置一级压力1.54MPa，二级压力14MPa，间 冷温度100℃，高压燃气透平进气温度和中压燃气透平进气温度均为1325℃。此时，所述发 电系统的联合循环效率最高。
(10)根据(1)至(9)任一项所述的发电系统和方法，将属于中压系统的中压燃气透 平与一级压气机同轴布置，属于高压系统的高压燃气透平与二级压气机同轴布置，燃气透平 与发电机采用离合器或其它常用方式连轴。高压系统和中压系统可全部同轴设置，使高压、 中压燃气透平和两级压气机全部同轴；也可以分轴设置，一级压气机与二机压气机分布在不 同轴上，各自分别与中压燃气透平和高压燃气透平同轴，形成独立的高压系统和中压系统， 分轴设置时，系统运行时可按负荷灵活选择是否启动高压系统，同时可避免压气机放到同一 根轴上导致燃气轮机无法拖动的状况，减少启动难度。
对于所述蒸汽循环子系统的具体选择，一般的，当燃气轮机在额定功率下排气温度低于 538℃时，则多采用单压或多压无再热的汽水系统；当燃气轮机排气温度高于538℃时，则可 以采用有再热循环的汽水系统；当燃气轮机排气温度高于593℃时，则可以采用三压再热循 环的汽水系统。本发明使用9FA级燃气轮机作为基准，排气温度为650℃，因此选用了三压 再热式蒸汽循环系统。
对于本发明所述的发电系统和方法中的运行参数，本发明针对高压再热燃气-蒸汽联合循 环进行参数寻优，找到基于本发明系统运行的优化的参数，达成最佳的联合循环效率。
本发明使用aspen plus软件对目前的9FA级燃气蒸汽联合循环机组、GT26机组和本发明 发电系统进行建模，通过计算分析对本发明发电系统进行参数寻优，确定最佳的工况。
对本发明系统模拟计算之前，先对现有的9FA级燃气蒸汽联合循环机组、GT26机组进 行建模。
系统模拟时采用ISO工况，环境温度15℃、大气压力0.10135MPa、大气相对湿度60％。 参照9FA系统公布的运行参数，确定进口空气参数为0.1MPa/15℃/678.5kg/s，压缩机压缩后 燃气参数是1.54MPa/404.5℃/678.5kg/s，入口燃气参数为1.54MPa/15℃/16.8kg/s；燃烧生成高 温燃气参数是1.54MPa/1325℃/695.3kg/s，燃气透平后的尾气参数是0.105MPa/650℃/695.3kg。 燃机做功为314MW。蒸汽部分为三压再热式，压力级别分别是9.63MPa、2.16MPa、0.367MPa。 高压缸进汽参数为9.63MPa/540℃/90.8kg/s；高压缸排汽参数2.16MPa/321℃/90.8kg/s；中压 缸进汽参数2.16MPa/540℃/104.2kg/s；低压缸进汽参数0.367MPa/300.3℃/121.5kg/s；排汽参 数0.00484MPa/35.5℃/121.5kg/s。蒸汽轮机总输出功为160.7MW。
将模拟结果汇总并与现有9FA级联合系统参数进行对比，如表1所示。
表1：现有9FA系统与aspen模拟参数对比
项目 现有9FA型联合循环系统 aspen模拟基准系统
空气流量 638.5kg/s 678.5kg/s
天然气流量 16.8kg/s 16.8kg/s
压比 15.4 15.4
燃气透平进气温度 1325℃ 1325℃
排气温度 609℃ 658℃
排烟温度 83℃ 82℃
燃机出力 304MW 307MW
总输出功 472MW 468MW
燃机效率 37.23％ 37.56％
联合循环效率 57.74％ 57.20％
由表1可知，aspen模拟系统效率与实际9FA系统效率相差不大，各项参数比较接近， 模拟较为符合现有9FA系统，因此本发明选择aspen模拟的9FA系统作为基准系统。
对于GT26系统，参照基准系统进行参数设置，模拟结果与现有GT26系统对比如表2 所示。
表2：现有GT26系统与aspen模拟参数对比
项目 现有GT26系统 aspen模拟系统
空气流量 545.6kg/s 540kg/s
天然气流量 16.4kg/s 12.99kg/s
压比 30 30
燃气透平进气温度 1255℃ 1235℃
再热温度 1255℃ 1235℃
排气温度 630℃ 605℃
燃机出力 262MW 267MW
总输出功 398MW 380MW
KA-26联合循环效率 57.0％ 60.03％
对于模拟结果，需要说明的是，GT26公布的工作参数与本发明基准设定不同，采用和本 发明系统相同的容量、流量和大致结构后，GT26在aspen模拟中效率也有了上升，达到 60.03％。
总体上，考察aspen模拟和实际系统结果，可以认为吻合度达到了参数分析要求。
在模拟计算过程中，有三个参数对本发明系统的整体联合循环效率有重大影响：一级压 力、二级压力以及间冷后空气温度。通过变参数实验进行参数寻优，从而找出使效率最高的 最佳值。表3所示为效率最高的相关参数。
表3：效率最高的相关参数表
Figure PCTCN2014080217-appb-000001
Figure PCTCN2014080217-appb-000002
由表3中数据可知，在空气一级压力1.5-2.4MPa，二级压力为6-20MPa，间冷温度为 100-200℃时，运行本发明系统均有较佳的联合循环效率。
优选的，当一级压力为1.5-2MPa，二级压力为9-18MPa，间冷温度100℃，本发明系统 在此参数区间运行时，联合循环效率高于60.36％，优于使用本发明基准系统参数的GT26系 统的60.03％效率值；
进一步优选的，当一级压力为1.54MPa，二级压力为14MPa时，本发明系统燃机效率可 达42.96％，联合循环效率达到最高的61.22％。
在最佳参数分析后，进行变工况分析。本发明系统存在高压和中压两级系统，因而分别 调整高、中压燃气透平进气温度，可以得到不同工况下系统的效率。通过对数据的汇总，将 其汇成表4。
表4：不同高中压温度下的效率
Figure PCTCN2014080217-appb-000003
Figure PCTCN2014080217-appb-000004
由表4中数据可知，高压燃气透平进气温度为1000-1500℃，中压燃气透平进气温度为 1200-1500℃时，本发明系统有较佳的联合循环效率。
优选的，当选择高压和中压燃气透平进气温度相同，即将燃气再热燃烧使之回复初次透 平的进气温度，并且控制温度为1325℃时，可获得相对最高的循环效率，此时联合循环系统 的总输出功817MW，燃机效率42.96％，联合循环效率达到61.22％。需要说明的是，虽然表 4所示，将高压温度提高至1500℃可获得更高的效率，但此温度已超出了本发明基准的F级 燃机范围，且提高温度对系统工艺有更加严苛的要求，带来额外的成本，因此提高温度以获 得更高效率不是本系统的发明方向，故不选用1500℃数据为最佳工况参数。
另外，基于本发明可选择的燃气轮机高压系统和中压系统分轴设置方式，一级压气机与 中压透平同轴，中压系统构成普通F级燃机机组，高压系统可视为额外增加的高压部分。低 负荷时可单独运行中压系统，此时，本发明系统类似于普通的9FA级联合循环机组。
综上所述，本发明系统具有如下主要特点：
1.高压再热。本发明使用了再热结构，与普通再热机组不同，本发明系统最佳运行时的 空气高压压力高达14MPa，远高于普通F级燃机(1.5-2MPa)以及再热机组(3MPa左右)。 本发明设置一级压气机压缩空气压力至普通燃机压力级别，二级压气机压缩空气到本发明要 求的高压级别；
2.间冷器热量回收。由于本发明采用了14MPa的高压力，大大增加空气压缩过程中的热 量损失。因而本系统设置了间冷器，降低二级压气机进口空气温度，减少压缩机耗功。此外， 为了利用这部分热量，本系统设置了间冷器热量回收部分，将间冷器的冷却水引入余热锅炉 加以利用，使循环效率更高；
3.分轴布置。本发明可选择将高压系统与中压系统分轴布置。通过高压系统和中压系统 结构上分离，使启动方式更加灵活，可根据负荷选择启动高压系统；同时两个压气机分布在 不同轴上，可避免放分布于同一轴上时燃气轮机无法拖动的状况，减少燃气系统启动难度。
本发明与普通F级联合循环机组相比。本发明增加了再热和间冷循环装置，运行时空气 压缩的最高压力远高于普通F级机组，最佳效率运行时效率比普通F级机组高出3个百分点 以上，单机功率高出73％，达到817MW。
本发明与GT26机组相比。GT26使用亚音速压气机将空气一次压缩至两倍常规燃机压比 (3MPa)，对设备工艺要求很高，造价昂贵；本发明采用带中间冷却的两级压缩，将空气压缩 14MPa，实现更高压比，结构上却易于实现且造价较低。GT26由一组22级高效亚音速压气 机将空气以两倍于常规燃机压比的高压压入环形环保燃烧室，无中间冷却，造价昂贵。同时， 环保燃烧室的设计可降低NOx的排放量。本发明是在现有9FA燃气轮机的简单燃气循环基础 上增加了再热循环及中间冷却循环，系统采用的是多轴多燃机单元组成的“机组群”，技术上 更易实现，并且造价更低。与GT26参照本发明基准条件下运行时的效率60.03％相比，本发 明系统效率高了1.2个百分点，与实际运行的GT26系统相比，效率提高的更多。
本发明由于在最佳参数附近运行时，提高了联合循环效率，在发出相同电量时天然气消 耗量较普通F级燃气联合循环机组有一定的减少，因而发电成本较普通机组也会有一定的降 低，表5通过相关计算对新型高压再热系统和普通F级燃机系统进行对比，表中部分数据采 用近似值。
表5：本发明经济性分析
  单位 F级燃机系统 高压再热系统
系统总输出功 MW 471.5 825.127
燃机效率 ％ 38.36 42.96
联合循环效率 ％ 57.62 61.40
标准煤耗率b＝123/h g/kWh 213.468 200.326
装机设备年利用小时数 h 4500 5000
年发电量 亿kWh 21.2 41.3
年节省标煤数量(与F级燃机联合循环机组相比) 吨标煤 0 54218.3
标准天然气消耗率 Nm3/kWh 0.36 0.33
年节省天然气数量(与F级燃机联合循环机组相比) 亿立方米 0 7.08
天然气节省费用 万元 0 20.1
年减排CO2(与F级燃机联合循环机组相比) 万吨 0 4.68
如表5所示，大范围使用本发明系统代替普通燃机，可以有效减少燃料消耗量，从而降 低温室气体的排放。
附图说明
图1为本发明所述高压、中压系统分轴的发电系统结构示意图；
图2为本发明所述高压、中压系统同轴的发电系统结构示意图；
图3为GT26、9FA系统和本发明所述再热发电系统的循环温熵对比图；
图中标号：11-一级压气机；12-中压燃烧室；13-中压燃气透平；21-二级压气机；22-高压 燃烧室；23-高压燃气透平；10、20-发电机；30-间冷器；31-间冷水泵；40-蒸汽轮机发电机； 41-低压水泵；42-低压省煤器；43-低压汽包；44-低压过热器；49-蒸汽轮机低压缸；51-中压 水泵；52-中压省煤器；53-中压汽包；54-中压过器；55-再热器；59-蒸汽轮机中压缸；61- 高压水泵；62-前高压省煤器；63-后高压省煤器；64-高压汽包；65-高压过热器；69-蒸汽轮 机高压缸；71-凝汽器；A1-空气入口；B1-中压系统燃气入口；B2-高压系统燃气入口；C1- 余热锅炉烟气入口；C2-余热锅炉排烟口。
具体实施方式
实施例1：
本实施例发电系统结构如图1所示。
燃气轮机子系统中，中压燃气透平13与一级压气机11同轴，高压燃气透平23与二级压 气机21同轴，燃气透平与发电机10和20连轴；高压系统和中压系统采用分轴布置；
蒸气轮机子系统中，设置三压再热式余热锅炉和蒸汽轮机。具体结构为：给水结构分为 高、中、低压水三路，蒸汽轮机设置有高压缸69、中压缸59和低压缸49。凝汽器71连接低 压水泵41，加压后分两路，一路依次连接冷水泵31、间冷器30、高压汽包64，最后连通高 压过热器65；另一路连接余热锅炉中的低压省煤器42，之后分别连接高、中、低压三路。高 压路经高压水泵61依次连接前高压省煤器62、后高压省煤器63，最后和间冷水路汇合一同 接入高压汽包64，再经过高压过热器65连接蒸汽轮机高压缸69，高压缸69排气连接再热器 55；中压路经中压水泵51依次连接中压省煤器52、中压汽包53、中压过热器54，与高压缸 的排气汇合，经过再热器55连接中压缸59，中压缸59排气连接低压缸49进气口；低压路 依次连接低压汽包43、低压过热器44，与中压缸59排汽汇合一同接入低压缸49，低压缸49 排汽进入冷凝器71。蒸汽轮机带动发电机40向外输出电能。
该发电系统工作时，过量系数很大的空气由空气入口A1进入，经过一级压气机11和二 级压气机21的两级压缩，其间还经过一个间冷器30对压缩空气进行中间冷却。过量的高压 空气进入高压燃烧室22和经高压系统燃气入口B2喷入的天然气在14MPa的高压环境下燃 烧，燃烧的烟气中包括大量未发生反应的空气，这些1325℃的高温烟气推动高压燃气透平23 并带动高压级发电机20输出电能。做功后的烟气进入中压燃烧室12，在1.54MPa的中压环 境中和经中压系统燃气入口B1喷入的天然气混合，燃烧再热至1325℃高温，推动中压燃气 透平13带动中压级发电机10输出电能，排气经余热锅炉烟气入口C1进入余热锅炉依次加 热高压过热器65、再热器55、高压汽包64、中压过热器54、后高压省煤器63、中压汽包53、 低压过热器44、前高压省煤器62、中压省煤器52，低压汽包43和低压省煤器42后，经余 热锅炉排烟口C2排出。
该发电系统运行参数设置为：一级压力1.54MPa，二级压力为14MPa，间冷温度为100℃， 中压燃气透平进气温度和高压燃气透平进气温度均为1325℃；将蒸汽发电子系统中的高、中、 低缸进气压力分别设定为9.63MPa、2.16MPa和0.367MPa，相应进气温度分别设定为：565.5℃、 565.5℃和305℃。其他参数选择详见表6。
实施例2：
该实施例与实施例1区别为，将蒸汽发电子系统中的高、中、低缸进气进气温度分别设 定为：540℃、540℃和305℃；其余结构与参数与实施例1基本保持一致。
实施例3：
本实施例发电系统结构如图2所示。该实施例与实施例1区别为，高压系统和中压系统 采用同轴布置；其余结构与参数与实施例1保持一致。
对比例1：
该对比例使用普通9FA联合循环系统，参照实施例1参数设置运行，作为本发明基准系 统。具体参数设置和运行结果见表6。
对比例2：
该对比例使用现有的GT26联合循环系统，参照实施例2参数设置运行。具体参数设置 和运行结果见表6。
表6实施例与对比例运行数据对比：
Figure PCTCN2014080217-appb-000005
Figure PCTCN2014080217-appb-000006
上述实施例并非具体实施方式的穷举，还可有其他的实施例，上述实施例目的在于说明 本发明，而非限制本发明的保护范围，所有由本发明简单变化而来的应用均落在本发明的保 护范围内。
此专利说明书使用实例去展示本发明，其中包括最佳模式，并且使熟悉本领域的技术人 员制造和使用此项发明。此发明可授权的范围包括权利要求书的内容和说明书内的具体实施 方式和其它实施例的内容。这些其它实例也应该属于本发明专利权要求的范围，只要它们含 有权利要求相同书面语言所描述的技术特征，或者它们包含有与权利要求无实质差异的类似 字面语言所描述的技术特征。
所有专利，专利申请和其它参考文献的全部内容应通过引用并入本申请文件。但是如果 本申请中的一个术语和已纳入参考文献的术语相冲突，以本申请的术语优先。
本文中公开的所有范围都包括端点，并且端点之间是彼此独立地组合。
需要注意的是，“第一”，“第二”或者类似词汇并不表示任何顺序，质量或重要性，只是 用来区分不同的技术特征。结合数量使用的修饰词“大约”包含所述值和内容上下文指定的 含义(例如：它包含有测量特定数量时的误差)。

Claims (23)

  1. 一种高压再热燃气-蒸汽联合循环发电系统，由燃气轮机子系统和蒸汽轮机子系统组 成，其特征在于：燃气轮机子系统包括中压系统和高压系统，中压系统包括一级压气机、中 压燃烧室和中压燃气透平，高压系统包括二级压气机、高压燃烧室和高压燃气透平，一级和 二级压气机之间设有至少一级间冷器；运行时过量空气通过所述一、二级压气机两级压缩后， 进入高压燃烧室燃烧加热，产生的高温燃气经高压燃气透平后进入中压燃烧室，再热后经中 压燃气透平做功；中压系统排气口连通蒸汽轮机子系统，排气在蒸汽轮机子系统回收热量。
  2. 根据权利要求1所述的发电系统，其特征在于：所述发电系统参数设置为，中压系统 中，一级压缩后的空气一级压力为1.5-2.4MPa；高压系统中，二级压缩后的空气二级压力为 6-20MPa；设置一级间冷器，空气的间冷温度为100-200℃。
  3. 根据权利要求1或2所述的发电系统，其特征在于：高压燃气透平进气温度为 1000-1500℃，中压燃气透平进气温度为1200-1500℃。
  4. 根据权利要求1至3任一项所述的发电系统，其特征在于：所述间冷器的冷却水连通 所述蒸汽轮机子系统，回收冷却水的热量。
  5. 根据权利要求1至4任一项所述的发电系统，其特征在于：所述蒸汽轮机子系统包括 余热锅炉和蒸汽轮机，所述中压系统排气口连接余热锅炉烟气入口。
  6. 根据权利要求1至5任一项所述的发电系统，其特征在于：所述余热锅炉和蒸汽轮机 为三压再热式；给水结构分为高、中、低压三路，给水可在余热锅炉中多次分级吸热；所述 蒸汽轮机设置有高、中、低压缸，高压缸与中压缸之间连接再热器，高压缸排汽进入再热器 再热后，进入中压缸做功。
  7. 根据权利要求1至6任一项所述的发电系统，其特征在于：所述间冷器的冷却水流接 入所述蒸汽轮机子系统的高压水路。
  8. 根据权利要求1至7任一项所述的发电系统，其特征在于：所述蒸气轮机子系统高、 中、低三路压力分别为9.63MPa、2.16MPa和0.367MPa。
  9. 根据权利要求1至8任一项所述的发电系统，其特征在于：所述发电系统参数设置为， 一级压力1.54MPa，二级压力14MPa，间冷温度100℃，高压燃气透平进气温度和中压燃气 透平进气温度均为1325℃。
  10. 根据权利要求1至9任一项所述的发电系统，其特征在于：所述中压燃气透平与一 级压气机同轴，所述高压燃气透平与二级压气机同轴，燃气透平与发电机连轴。
  11. 根据权利要求1至10任一项所述的发电系统，其特征在于：所述高压系统和中压系 统采用同轴布置或分轴布置，分轴时，一级压气机与二级压气机分布在不同轴上。
  12. 一种高压再热燃气-蒸汽联合循环发电方法，步骤包括：
    燃气循环，压缩空气与燃料混合燃烧，产生的高温燃气透平做功推动发电机发电，排气 导入蒸汽循环回收余热；
    蒸汽循环，将燃气循环排气余热作为热源，由蒸汽做功推动发电机发电；
    其特征在于：
    所述空气为过量空气，压缩过程为两级，空气经一级压气机压至一级压力，经二级压气 机压至二级压力；
    所述空气两级压缩之间经过至少一级间冷过程；
    所述燃气循环中加入再热过程，一次循环中燃气两次透平做功，将通过高压燃气透平后 压力降低的燃气再热，再通过中压燃气透平。
  13. 根据权利要求12所述的发电方法，其特征在于：所述空气一级压力为1.5-2.4MPa， 二级压力为6-20MPa；设置一级间冷过程，间冷温度为100-200℃。
  14. 根据权利要求12或13所述的发电方法，其特征在于：所述高压燃气透平进气温度 为1000-1500℃，中压燃气透平进气温度为1200-1500℃。
  15. 根据权利要求12至14任一项所述的发电方法，其特征在于：将所述间冷过程的冷 却水引入所述蒸汽循环中，回收间冷却水的热量。
  16. 根据权利要求12至15任一项所述的发电方法，其特征在于：所述蒸汽循环中使用 余热锅炉和蒸汽轮机，将所述燃气循环中的排气导入余热锅炉回收余热。
  17. 根据权利要求12至16任一项所述的发电方法，其特征在于：所述蒸汽循环为三压 再热式；高、中、低压三路给水通过余热锅炉分级吸热；蒸汽分别在所述蒸汽轮机的高、中、 低压缸内做功，高压路的蒸汽在高压缸做功后排出，再热后进入中压缸再次做功。
  18. 根据权利要求12至17任一项所述的发电方法，其特征在于：将所述间冷过程的冷 却水流接入所述蒸汽循环的高压水路。
  19. 根据权利要求12至18任一项所述的发电方法，其特征在于：所述蒸气循环高、中、 低三路压力分别为9.63MPa、2.16MPa和0.367MPa。
  20. 根据权利要求12至19任一项所述的发电方法，其特征在于：一级压力1.54MPa， 二级压力14MPa，间冷温度100℃，高压燃气透平进气温度和中压燃气透平进气温度均为 1325℃。
  21. 根据权利要求12至20任一项所述的发电方法，其特征在于：布置所述一级压气机、 二级压气机、中压燃气透平和高压燃气透平全部同轴运行。
  22. 根据权利要求12至21任一项所述的发电方法，其特征在于：布置所述一级压气机 和中压燃气透平同轴运行，二级压气机和高压燃气透平在另一轴上同轴运行。
  23. 根据权利要求12至22任一项所述的发电方法，其特征在于：将一级压气机和中压 燃气透平单独运行，或者与二级压气机和高压燃气透平联合运行。
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