WO2014183235A1 - 直接空冷汽轮机复合式凝汽换热系统 - Google Patents

直接空冷汽轮机复合式凝汽换热系统 Download PDF

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Publication number
WO2014183235A1
WO2014183235A1 PCT/CN2013/000985 CN2013000985W WO2014183235A1 WO 2014183235 A1 WO2014183235 A1 WO 2014183235A1 CN 2013000985 W CN2013000985 W CN 2013000985W WO 2014183235 A1 WO2014183235 A1 WO 2014183235A1
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Prior art keywords
valve
heat exchanger
condensation heat
disposed
peak
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/CN2013/000985
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English (en)
French (fr)
Inventor
李庆华
马庆中
王雪峰
石红晖
王进
卢家勇
白志刚
冯云鹏
李谦瑞
张玉虎
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Electric Power Research Institute of State Grid Shanxi Electric Power Co Ltd
State Grid Corp of China SGCC
Original Assignee
Electric Power Research Institute of State Grid Shanxi Electric Power Co Ltd
State Grid Corp of China SGCC
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Publication of WO2014183235A1 publication Critical patent/WO2014183235A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28B—STEAM OR VAPOUR CONDENSERS
    • F28B7/00—Combinations of two or more condensers, e.g. provision of reserve condenser
    • 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
    • F01K17/00—Using steam or condensate extracted or exhausted from steam engine plant
    • F01K17/02—Using steam or condensate extracted or exhausted from steam engine plant for heating purposes, e.g. industrial, domestic
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28B—STEAM OR VAPOUR CONDENSERS
    • F28B1/00—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser
    • F28B1/02—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser using water or other liquid as the cooling medium
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28B—STEAM OR VAPOUR CONDENSERS
    • F28B9/00—Auxiliary systems, arrangements, or devices
    • F28B9/04—Auxiliary systems, arrangements, or devices for feeding, collecting, and storing cooling water or other cooling liquid
    • F28B9/06—Auxiliary systems, arrangements, or devices for feeding, collecting, and storing cooling water or other cooling liquid with provision for re-cooling the cooling water or other cooling liquid
    • 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
    • Y02E20/14—Combined heat and power generation [CHP]

Definitions

  • the present invention generally relates to a heat exchange system, and more particularly to a direct air-cooled steam turbine steam heat exchange system.
  • Waste heat recovery technology is an energy saving and emission reduction technology.
  • the design of the direct air cooling unit of the large power station has higher back pressure and exhaust steam temperature than the traditional wet cooling unit. Therefore, there is a large back pressure adjustment space, which is beneficial to the recovery and utilization of waste heat.
  • the absorption heat pump or the addition of a high back pressure condenser is mainly used for waste heat recovery.
  • Existing direct air-cooling units, whether using absorption heat pumps for waste heat recovery or adding high back pressure condensers for waste heat recovery, are limited to how to effectively use the residual heat of the unit in winter. These waste heat recovery devices are basically used in summer. Being idle, resulting in low device utilization.
  • the existing waste heat recovery device does not overcome the disadvantages of high back pressure and poor economic performance of the direct air-cooled steam turbine in summer.
  • the present invention provides a direct air-cooled steam turbine composite condensing heat exchange system, which solves the problem of low utilization rate in the existing waste heat recovery device in summer, and solves the problem of high back pressure of the direct air cooling unit in summer.
  • a direct air-cooled steam turbine composite condensing heat exchange system including A condensing heat exchanger, B condensing heat exchanger, heat network circulating pump, A peak cooling tower, B
  • the peak cooling tower, the A-peak cooling water circulation pump and the B-peak cooling water circulation pump, the exhaust steam exhaust pipe of the A direct air-cooling unit communicates with the inlet port of the A condensing heat exchanger through the first valve, and passes through the heat exchange condensation
  • the second valve, the first three-way and the third valve disposed on the hydrophobic port of the condensation heat exchanger are in communication with the input port of the exhaust device of the direct air-cooling unit of the A; the outlet of the heat network circulation pump is condensed with the A by the fourth valve
  • the circulating water inlet of the device is connected, and the circulating water outlet of the A condensation heat exchanger is connected to the inlet of the A-peak cooling tower through the fifth valve.
  • the output port of the A-peak cooling tower passes through the A-peak cooling water circulation pump and the sixth valve and A in turn.
  • the circulating water inlet of the condensation heat exchanger is connected; the exhaust steam exhaust pipe of the B direct air cooling unit communicates with the steam inlet of the B condensation heat exchanger through the seventh valve, and is condensed by heat transfer and then sequentially passes through B condensation.
  • Eighth threshold gate provided on the heat hydrophobic port, the input port of the second three-way exhaust apparatus and a ninth gate width B with direct air cooling unit communication; heat circulation pump outlet through tenth valve and condensate B
  • the circulating water inlet of the junction heat exchanger is connected, and the circulating water outlet of the B condensation heat exchanger is connected to the inlet of the B-peak cooling tower through the eleventh valve, and the output of the B-peak cooling tower passes through the B-peak cooling water circulation pump and the first
  • the twelve wide door is connected to the circulating water inlet of the B condensation heat exchanger; a communication pipe is arranged between the inlet of the A condensation heat exchanger and the inlet of the B condensation heat exchanger, and the first pipe is provided with a communication pipe A fifteenth valve; a second communication tube is disposed between the first three-way and the second three-way, and a sixteenth wide door is disposed on the second communication tube.
  • the circulating water outlet of the A condensation heat exchanger is in communication with the first heating pipeline, and the thirteenth valve is disposed on the first heating pipeline; the circulating water outlet of the B condensation heat exchanger and the first The two heating pipelines are connected to the pipeline, and the fourteenth valve is arranged on the second heating pipeline.
  • an A vacuuming tube is arranged, and the 17th wide door, the third three-way and the eighteenth valve are sequentially arranged on the A vacuuming pipe; the vacuuming in the B condensation heat exchanger a B vacuum pump is arranged on the mouth, and a nineteenth valve, a fourth three-way and a twentieth valve are arranged in sequence on the B vacuum pumping tube; a third communicating tube is arranged between the third three-way and the fourth three-way, A twenty-first valve is disposed on the third communication pipe.
  • FIG. 1 is a schematic view showing the structure of a system of the present invention.
  • BEST MODE FOR CARRYING OUT THE INVENTION The present invention will be described below with reference to the accompanying drawings:
  • a direct air-cooled steam turbine composite condensing heat exchange system including A condensing heat exchanger 1, B condensing heat exchanger 2, heating network circulating pump 5, A peak cooling tower 3.
  • a direct air-cooling unit's exhaust steam exhaust pipe 29 is connected to the inlet port of the A condensation heat exchanger 1 through the first valve 8
  • the second door 24, the first three-way 36 and the third valve 25 disposed on the drain port of the A condensing heat exchanger 1 are in communication with the input port of the exhaust device 30 of the direct air-cooling unit of the A;
  • the outlet of the heat network circulation pump 5 is connected to the circulating water inlet of the A condensation heat exchanger 1 through the fourth valve 11, and the circulating water outlet of the condensation heat exchanger 1 of A is cooled by the fifth valve 14 and the A peak. While the inlet of the tower 3 is connected, the output port of the A-peak cooling tower 3 is in turn connected to the circulating water inlet of the A condensing heat exchanger 1 through the A-peak cooling water circulation pump 6 and the sixth valve 13.
  • the exhaust steam exhaust pipe 31 of the B direct air cooling unit communicates with the steam inlet of the B condensation heat exchanger 2 through the seventh valve 9, and passes through the heat exchange condensation, and sequentially passes through the eighth valve disposed on the drain port of the B condensation heat exchanger 2. 27.
  • the second three-way 37 and the ninth wide door 28 are in communication with the input port of the exhaust unit 32 of the direct air cooling unit of the B; the outlet of the heat network circulating pump 5 passes through the tenth valve 15 and the circulating water of the B condensation heat exchanger 2
  • the inlet port is connected, and the circulating water outlet of the B condensation heat exchanger 2 is connected to the inlet of the B peak cooling tower 4 through the eleventh valve 18, and the output port of the B peak cooling tower 4 sequentially passes through the B peak cooling water circulation pump 7 and the twelfth
  • the valve 17 is in communication with the circulating water inlet of the B condensation heat exchanger 2.
  • the circulating water outlet of the condensing heat exchanger 1 is in communication with the first heating pipe conveying pipe 33, and the thirteenth valve 12 is disposed on the first heating pipe conveying pipe 33;
  • the circulating water outlet of the B condensation heat exchanger 2 is in communication with the second heating pipe delivery pipe 34, and the fourteenth valve 16 is disposed on the second heating pipe conveying pipe 34.
  • a communication pipe 35 is disposed between the inlet of the A condensation heat exchanger 1 and the inlet of the B condensation heat exchanger 2, and the fifteenth valve 10 is disposed on the communication pipe 35;
  • a second communication tube 38 is disposed between the second three passages 37, and a sixteenth door 26 is disposed on the second communication tube 38.
  • an A vacuuming pipe 41 On the vacuuming port of the A condensing heat exchanger 1, an A vacuuming pipe 41 is disposed, and a seventeenth valve 20, a third three-way 39 and an eighteenth door 19 are sequentially disposed on the A vacuuming pipe 41;
  • a vacuum pumping tube 42 is disposed on the vacuuming port of the heat exchanger 2, and a nineteenth valve 23, a fourth three-way 40 and a second tenth door 22 are sequentially disposed on the B vacuuming pipe 42; in the third three-way 39
  • a third communication pipe 43 is disposed between the fourth tee 40 and a second eleventh door 21 is disposed on the third communication pipe 43.
  • the first valve 8 is opened, the seventh valve 9 and the fifteenth threshold door 10 are closed, so that the whole system works in a towed state, that is, Only the residual heat of the A direct air cooling unit is recovered; at the same time, the fourth valve 11, the thirteenth valve 12, the tenth door 15 and the fourteenth valve 16 are opened, and the heat network circulating pump 5 will be connected to the first heating pipe.
  • the conveying pipe 33 performs hot water supply, and the water pumped into the A condensing heat exchanger 1 absorbs heat and then supplies hot water to the first heating pipe conveying pipe 33 through the thirteenth valve 12; at the same time, the heating network circulates
  • the pump 5 will also supply hot water to the second heating pipe transfer pipe 34, and pump it through the tenth valve 15 to the B condensing heat exchanger 2
  • the water in the water supplies the hot water to the second heating pipe transfer pipe 34 through the fourteenth valve 16; the sixth door 13, the fifth door 14, the twelfth valve 17, and the eleventh valve 18 are closed to make the peak
  • the cooling water system does not work; the second valve 24, the third threshold door 25, the sixteenth valve 26 and the eighth valve 27 are opened, the ninth valve 28 is closed, and the A condensing heat exchanger 1 and the B condensing heat exchanger 2 pass the above
  • the valve is hydrophobic; the eighteenth valve 19, the seventeenth valve 20, the twenty-first wide door 21 and the nineteenth valve 23 are opened
  • the seventh valve 9 is opened, the first valve 8 and the fifteenth valve 10 are closed, so that the whole system works in one to two working state, that is, only The waste heat of the B direct air cooling unit is recovered; at the same time, the fourth valve 11, the thirteenth valve 12, the tenth valve 15 and the fourteenth valve 16 are opened, and the heat network circulation pump 5 will be connected to the first heating pipe 33.
  • the hot water supply is performed, and the water pumped into the A condensation heat exchanger 1 supplies hot water to the first heating pipe delivery pipe 33 through the thirteenth valve 12; at the same time, the heat network circulation pump 5 is also paired with the second The heating pipe conveying pipe 34) performs hot water supply, and the water pumped into the B condensing heat exchanger 2 through the tenth valve 15 absorbs heat and passes through the fourteenth wide door 16 to the second heating pipe conveying pipe 34.
  • the above valve is hydrophobic; the twentyth valve 22, the seventeenth valve 20, the twenty-first door 21 and the nineteenth door 23 are opened, the eighteenth valve 19 is closed, and the A condensation heat exchanger 1 and B are condensed
  • the heater 2 is evacuated through the above valve.
  • the fourth valve 11, the thirteenth valve 12, the tenth valve 15 and the fourteenth valve 16 of the hot water circulating water system are simultaneously closed, the sixth wide door 13, the fifth threshold door 14, the twelfth of the peak cooling water system
  • the wide door 17 and the eleventh valve 18 are simultaneously opened, the fifteenth valve 10 as a steam supply contact valve is closed, and the twenty-first valve 21 as a vacuum contact is closed; the sixteenth threshold door 26 as a hydrophobic communication threshold Closed, the system is in a one-to-one working state, that is, two air-cooling units respectively drive the respective condensing heat exchanger and the peak cooling tower to work, so that the problem of high back pressure of the direct air-cooling unit in summer is fundamentally solved.
  • the temperature rise of the hot network circulating water in the condensing heat exchanger is between 10 °C and 20 °C, and the circulation of the mechanical ventilation cooling tower Water cooling capacity is generally 18 Within °C, therefore, the flow design of the peak cooling water of the condensing heat exchanger and the circulating water of the heating network can be approximated.
  • the external heat supply of the unit is deteriorated.
  • the back pressure operation range is between 25 and 35 kPa, and the operating back pressure of the peak cooler is generally between 15 and 25 kPa, to meet the waste heat recovery system for heating system design.
  • the single-machine peak cooling system has a steam extraction capacity of only 50% of the waste heat recovery system to meet the heat recovery system design of the waste heat recovery system.
  • the present invention can meet the requirements of the peak cooling system.
  • the main equipment of the invention comprises two condensation heat exchangers, two peak coolers, 3-5 heat network circulation pumps, and two peak cooling water circulation pumps.
  • the condensing heat exchanger is the core equipment of the system. When it is used as the exhaust steam heat recovery device, the hot water circulating water back to the water is pressurized by the heat network pump and then enters the condensing heat exchanger to heat the recovered waste heat, and then continues to the conventional heat network. After the heating reaches the required temperature, external heat is supplied; the amount of waste heat recovery can be adjusted by changing the back pressure of the unit.
  • the condensing heat exchanger When used as a peak cooling device, the condensing heat exchanger and the mechanical ventilation cooling tower form a closed circulating cooling water system, and a part of the exhaust steam is extracted for cooling, and the air cooling is reduced by reducing the heat load of the air cooling radiator.
  • the purpose of the unit operating back pressure When the condensing heat exchanger is used as a peak cooling device, the condensing heat exchanger and the mechanical ventilation cooling tower form a closed circulating cooling water system, and a part of the exhaust steam is extracted for cooling, and the air cooling is reduced by reducing the heat load of the air cooling radiator.
  • the purpose of the unit operating back pressure When the condensing heat exchanger is used as a peak cooling device, the condensing heat exchanger and the mechanical ventilation cooling tower form a closed circulating cooling water system, and a part of the exhaust steam is extracted for cooling, and the air cooling is reduced by reducing the heat load of the air cooling radiator. The purpose of the unit operating back pressure.
  • the peak cooling system operates in a unit that allows the two units to control the operating back pressure requirements.
  • the steam supply system, the air extraction system and the drainage system of the two condensing heat exchangers are all set up with the switching master control mode, which can respectively meet the waste heat recovery of the two units' single-unit heating operation.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Other Air-Conditioning Systems (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)

Abstract

一种直接空冷汽轮机复合式凝汽换热系统，包括A凝结换热器（1）、B凝结换热器（2）、热网循环泵（5）、A尖峰冷却塔（3）、B尖峰冷却塔（4）、A尖峰冷却水循环泵（6）和B尖峰冷却水循环泵（7），热网循环水回水经热网循环泵（5）升压后进入凝结换热器（1、2）加热回收余热后，通往热网继续加热达到要求温度后对外供热；当其作为尖峰冷却设备时，凝结换热器（1、2）与尖峰冷却塔（3、4）组成闭式循环冷却水系统，抽取部分排汽进行冷却，两台凝结换热器（1、2）的供汽系统、抽空气系统、疏水系统均设置采用切换母管制方式，满足两台机组单机供热运行的余热回收。

Description

直接空冷汽轮机复合式凝汽换热系统 技术领域 本发明涉及一种换热系统， 特别涉及一种直接空冷汽轮机乏汽换热系统。
背景技术 余热回收技术属节能减排技术。 大型电站直接空冷机组的设计背压及排汽温度 相比于传统的湿冷机组要高， 因此， 存在较大的背压调整空间， 有利于余热的 回收利用。 目前， 对于大型电站直接空冷机组， 主要是采用吸收式热泵或增设 高背压凝结器来进行余热回收的。 现有的直接空冷机组不论是采用吸收式热泵 进行余热回收， 还是增设高背压凝结器来进行余热回收， 都是局限在冬季如何 有效利用机组的余热来进行的， 这些余热回收装置在夏季基本处于闲置状态， 造成了设备利用率低。 此外， 现有的余热回收装置并没有克服直接空冷汽轮机 组夏季运行背压高和经济性能差的缺陷。 发明内容 本发明提供了一种直接空冷汽轮机复合式凝汽换热系统， 解决了现有余热回收 装置存在的在夏季利用率低的问题， 并解决了直接空冷机组夏季运行背压高的 问题。 本发明是通过以下技术方案解决以上技术问题的： 一种直接空冷汽轮机复合式凝汽换热系统， 包括 A凝结换热器、 B凝结换热器、 热网循环泵、 A尖峰冷却塔、 B尖峰冷却塔、 A尖峰冷却水循环泵和 B尖峰冷却 水循环泵， A直接空冷机组的乏汽排汽管通过第一阀门与 A凝结换热器的进汽口 连通， 经换热冷凝后依次通过 A凝结换热器的疏水口上设置的第二阀门、 第一 三通和第三阀门与 A直接空冷机组的排汽装置的输入口连通； 热网循环泵的出 口通过第四阀门与 A凝结换热器的循环水接入口连通， A凝结换热器的循环水输 出口通过第五阀门与 A尖峰冷却塔入口连通， A尖峰冷却塔的输出口依次通过 A 尖峰冷却水循环泵和第六阀门与 A凝结换热器的循环水入口连通； B直接空冷机 组的乏汽排汽管通过第七阀门与 B凝结换热器的进汽口连通， 经换热冷凝后依 次通过 B凝结换热器的疏水口上设置的第八阈门、 第二三通和第九阔门与 B直 接空冷机组的排汽装置的输入口连通； 热网循环泵的出口通过第十阀门与 B凝 结换热器的循环水接入口连通， B凝结换热器的循环水输出口通过第十一阀门与 B尖峰冷却塔入口连通， B尖峰冷却塔的输出口依次通过 B尖峰冷却水循环泵和 第十二阔门与 B凝结换热器的循环水入口连通； 在 A凝结换热器的进汽口与 B 凝结换热器的进汽口之间设置有连通管， 在连通管上设置有第十五阀门； 在第 一三通与第二三通之间设置有第二连通管， 在第二连通管上设置有第十六阔门。
A凝结换热器的循环水输出口与第一供热管路输送管连通，在第一供热管路输送 管上设置有第十三阀门； B凝结换热器的循环水输出口与第二供热管路输送管连 通， 在第二供热管路输送管上设置有第十四阀门。
在 A凝结换热器的抽真空口上， 设置有 A抽真空管， 在 A抽真空管上依次设置 有第十七阔门、 第三三通和第十八阀门； 在 B凝结换热器的抽真空口上， 设置 有 B抽真空管， 在 B抽真空管上依次设置有第十九阀门、 第四三通和第二十阀 门； 在第三三通与第四三通之间设置有第三连通管， 在第三连通管上设置有第 二十一阀门。 本发明为一种直接空冷汽轮机排汽冬季余热进行回收及夏季进行尖峰冷却的复 合式凝汽换热系统， 可分别满足冬季余热回收和尖峰冷却需要的高效节能技术， 综合考虑两项功能进行系统设计， 可达到减少投资， 提高设备利用率的目的。 附图说明 图 1是本发明的系统结构示意图。 具体实施方式 下面结合附图对本发明进行说明： 一种直接空冷汽轮机复合式凝汽换热系统， 包括 A凝结换热器 1、 B凝结换热器 2、 热网循环泵 5、 A尖峰冷却塔 3、 B尖峰冷却塔 4、 A尖峰冷却水循环泵 6和 B 尖峰冷却水循环泵 7， A直接空冷机组的乏汽排汽管 29通过第一阀门 8与 A凝 结换热器 1的进汽口连通， 经换热冷凝后依次通过 A凝结换热器 1的疏水口上 设置的第二闽门 24、 第一三通 36和第三阀门 25与 A直接空冷机组的排汽装置 30的输入口连通；热网循环泵 5的出口通过第四阀门 11与 A凝结换热器 1的循 环水接入口连通， A凝结换热器 1的循环水输出口通过第五阀门 14与 A尖峰冷 却塔 3入口连通， A尖峰冷却塔 3的输出口依次通过 A尖峰冷却水循环泵 6和第 六阀门 13与 A凝结换热器 1的循环水入口连通。
B直接空冷机组的乏汽排汽管 31通过第七阀门 9与 B凝结换热器 2的进汽口连 通， 经换热冷凝后依次通过 B凝结换热器 2的疏水口上设置的第八阀门 27、 第 二三通 37和第九阔门 28与 B直接空冷机组的排汽装置 32的输入口连通； 热网 循环泵 5的出口通过第十阀门 15与 B凝结换热器 2的循环水接入口连通， B凝 结换热器 2的循环水输出口通过第十一阀门 18与 B尖峰冷却塔 4入口连通， B 尖峰冷却塔 4的输出口依次通过 B尖峰冷却水循环泵 7和第十二阀门 17与 B凝 结换热器 2的循环水入口连通。
A凝结换热器 1的循环水输出口与第一供热管路输送管 33连通， 在第一供热管 路输送管 33上设置有第十三阀门 12;
B凝结换热器 2的循环水输出口与第二供热管路输送管 34连通， 在第二供热管 路输送管 34上设置有第十四阀门 16。 在 A凝结换热器 1的进汽口与 B凝结换热器 2的进汽口之间设置有连通管 35， 在连通管 35上设置有第十五阀门 10;在第一三通 36与第二三通 37之间设置有 第二连通管 38， 在第二连通管 38上设置有第十六阓门 26。
在 A凝结换热器 1的抽真空口上，设置有 A抽真空管 41，在 A抽真空管 41上依 次设置有第十七阀门 20、 第三三通 39和第十八闽门 19; 在 B凝结换热器 2的 抽真空口上，设置有 B抽真空管 42，在 B抽真空管 42上依次设置有第十九阀门 23、第四三通 40和第二十阓门 22;在第三三通 39与第四三通 40之间设置有第 三连通管 43， 在第三连通管 43上设置有第二十一阖门 21。
在冬季供热期间， 当对 A直接空冷机组的余热进行回收时： 开启第一阀门 8， 关闭第七阀门 9和第十五阈门 10， 使整个系统工作在一拖二 的工作状态， 即只对 A直接空冷机组的余热进行回收； 同时， 开启第四阀门 11、 第十三阀门 12、 第十闽门 15和第十四阀门 16， 热网循环泵 5将对第一供热管 路输送管 33进行热水供应， 泵入 A凝结换热器 1中的水进行吸热后通过第十三 阀门 12对第一供热管路输送管 33供热水； 与此同时， 热网循环泵 5也将对第 二供热管路输送管 34进行热水供应， 通过第十阀门 15泵入到 B凝结换热器 2 中的水通过第十四阀门 16向第二供热管路输送管 34供热水；关闭第六闽门 13、 第五阓门 14、 第十二阀门 17和第十一阀门 18， 使尖峰冷却水系统不工作； 第 二阀门 24、 第三阈门 25、 第十六阀门 26和第八阀门 27开启， 第九阀门 28关 闭， A凝结换热器 1和 B凝结换热器 2通过以上阀门进行疏水； 第十八阀门 19、 第十七阀门 20、 第二十一阔门 21和第十九阀门 23开启， 第二十阀门 22关闭， A凝结换热器 1和 B凝结换热器 2通过以上阀门进行抽真空。 在冬季供热期间， 当对 B直接空冷机组的余热进行回收时- 开启第七阀门 9， 关闭第一阀门 8和第十五阀门 10， 使整个系统工作在一拖二 的工作状态， 即只对 B直接空冷机组的余热进行回收； 同时开启第四阀门 11、 第十三阀门 12、 第十阀门 15和第十四阀门 16， 热网循环泵 5将对第一供热管 路输送管 33进行热水供应， 泵入 A凝结换热器 1中的水通过第十三阀门 12对 第一供热管路输送管 33供热水； 与此同时， 热网循环泵 5也将对第二供热管路 输送管 34)进行热水供应， 通过第十阀门 15泵入到 B凝结换热器 2中的水吸热 后通过第十四阔门 16向第二供热管路输送管 34供热水； 关闭第六阀门 13、 第 五阀门 14、 第十二阀门 17和第十一阀门 18， 使尖峰冷却水系统不工作； 开启 第九阀门 28、 第三阀门 25、 第十六阀门 26和第八阀门 27， 第二阀门 24关闭， A凝结换热器 1和 B凝结换热器 2通过以上阀门进行疏水； 第二十阀门 22、 第 十七阀门 20、 第二十一阓门 21和第十九阓门 23开启， 第十八阀门 19关闭， A 凝结换热器 1和 B凝结换热器 2通过以上阀门进行抽真空。 在夏季高温时间段， 需进行尖峰冷却时：
热网循环水系统的第四阀门 11、 第十三阀门 12、 第十阀门 15和第十四阀门 16 同时关闭， 尖峰冷却水系统的第六阔门 13、 第五阈门 14、 第十二阔门 17和第 十一阀门 18同时开启， 作为供汽联络阀的第十五阀门 10关闭， 作为抽真空联 络阔的第二十一阀门 21关闭； 作为疏水联络阈的第十六阈门 26关闭， 此时系 统成一拖一工作状态， 即两台空冷机组分别带动各自的凝结换热器和尖峰冷却 塔工作， 使直接空冷机组夏季运行背压高的问题得到根本的解决。 在机组调峰运行负荷及热网循环水回水温度范围内， 热网循环水在凝汽换热器 内的温升幅度在 10°C- 20°C之间， 机力通风冷却塔的循环水冷却能力一般在 18 °C之内， 因此， 凝汽换热器的尖峰冷却水与热网循环水的流量设计可取接近的 数值。 机组对外供热是恶化背压运行范围在 25- 35kPa之间， 而尖峰冷却器投用 后的运行背压一般在 15-25 千帕之间，以满足余热回收系统进行供热系统设计， 由于单机尖峰冷却系统的抽汽能力仅为余热回收系统的 50%,以满足余热回收系 统进行供热系统设计， 本发明可满足尖峰冷却系统的要求。 本发明的主要设备包括两台凝结换热器， 两个尖峰冷却器， 3-5台热网循环泵， 两台尖峰冷却水循环泵。 凝结换热器是系统的核心设备， 当其作为乏汽供热回 收装置时， 热网循环水回水经热网泵升压后进入凝结换热器加热回收余热后， 通往常规热网继续加热达到要求温度后， 对外供热； 通过改变机组运行背压可 调整余热回收量。 当凝结换热器作为尖峰冷却设备时， 凝汽换热器与机力通风 冷却塔组成闭式循环冷却水系统， 抽取部分乏汽进行冷却， 通过减小空冷散热 器的热负荷， 达到降低空冷机组运行背压的目的。
在冬季供热期间， 采用一台机组恶化背压加热热网回水， 另一台机组加热常规 加热器的运行方式， 这种方式可充分会收单机的余热， 可整体提高两台机组的 运行经济性。 在夏季运行期间， 尖峰冷却系统单元制运行， 可实现两台机组分 别控制运行背压要求。 为实现上述功能， 两台凝结换热器的供汽系统、 抽空气 系统、 疏水系统均设置采用切换母管制方式， 可分别满足两台机组单机供热运 行的余热回收。

Claims

权利要求
1、 一种直接空冷汽轮机复合式凝汽换热系统， 包括 A凝结换热器 （1 )、 B凝结 换热器 （2)、 热网循环泵 （5)、 A尖峰冷却塔 （3)、 B尖峰冷却塔 （4)、 A尖峰 冷却水循环泵 （6)和 B尖峰冷却水循环泵 （7)， 其特征在于， A直接空冷机组 的乏汽排汽管 （29) 通过第一阀门 （8) 与 A凝结换热器 （1 ) 的进汽口连通， 经换热冷凝后依次通过 A凝结换热器 （1 ) 的疏水口上设置的第二阀门 （24)、 第一三通 （36) 和第三阀门 （25) 与 A直接空冷机组的排汽装置 （30) 的输入 口连通； 热网循环泵 （5) 的出口通过第四阀门 （11 ) 与 A凝结换热器 （1 ) 的 循环水接入口连通， A凝结换热器 （1 ) 的循环水输出口通过第五阀门 （14) 与 A尖峰冷却塔（3) 入口连通， A尖峰冷却塔 （3) 的输出口依次通过 A尖峰冷却 水循环泵 （6) 和第六阈门（13) 与 A凝结换热器 （1 ) 的循环水入口连通； B直 接空冷机组的乏汽排汽管 （31 ) 通过第七阖门 （9) 与 B凝结换热器 （2) 的进 汽口连通， 经换热冷凝后依次通过 B凝结换热器 （2) 的疏水口上设置的第八阀 门 （27)、 第二三通（37)和第九阀门 （28)与 B直接空冷机组的排汽装置（32) 的输入口连通； 热网循环泵（5)的出口通过第十阔门（15)与 B凝结换热器（2) 的循环水接入口连通， B凝结换热器（2) 的循环水输出口通过第十一阀门 （18) 与 B尖峰冷却塔（4)入口连通， B尖峰冷却塔（4) 的输出口依次通过 B尖峰冷 却水循环泵 （7)和第十二阀门（17) 与 B凝结换热器 （2) 的循环水入口连通； 在 A凝结换热器 （1 ) 的进汽口与 B凝结换热器 （2) 的进汽口之间设置有连通 管 （35)， 在连通管 （35) 上设置有第十五阓门 （10); 在第一三通 （36) 与第 二三通 （37)之间设置有第二连通管 （38)， 在第二连通管 （38)上设置有第十 六阔门 （26)。
2、 根据权利要求 1所述的一种直接空冷汽轮机复合式凝汽换热系统， 其特征在 于， A凝结换热器 （1 ) 的循环水输出口与第一供热管路输送管（33)连通， 在第 一供热管路输送管 (33)上设置有第十三阀门 （12); B凝结换热器（2) 的循环水 输出口与第二供热管路输送管 (34)连通， 在第二供热管路输送管 (34)上设置有 第十四阀门 （16)。 3、 根据权利要求 2所述的一种直接空冷汽轮机复合式凝汽换热系统， 其特征在 于， 在 A凝结换热器（1 ) 的抽真空口上， 设置有 A抽真空管 （41 )， 在 A抽真 空管（41 )上依次设置有第十七阀门（20)、第三三通（39)和第十八阀门（19); 在 B凝结换热器（2) 的抽真空口上， 设置有 B抽真空管（42)， 在 B抽真空管
(42 ) 上依次设置有第十九阈门 （23)、 第四三通（40)和第二十阀门 （22); 在第三三通（39)与第四三通（40)之间设置有第三连通管（43)， 在第三连通 管 (43)上设置有第二十一阀门 （21 )。
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