WO2019201281A1 - 一种大型火电厂空冷机组乏汽余热回收供热系统 - Google Patents

一种大型火电厂空冷机组乏汽余热回收供热系统 Download PDF

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Publication number
WO2019201281A1
WO2019201281A1 PCT/CN2019/083081 CN2019083081W WO2019201281A1 WO 2019201281 A1 WO2019201281 A1 WO 2019201281A1 CN 2019083081 W CN2019083081 W CN 2019083081W WO 2019201281 A1 WO2019201281 A1 WO 2019201281A1
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steam
condenser
exhaust
heat
power plant
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PCT/CN2019/083081
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English (en)
French (fr)
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乌兰其其格
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联合瑞升(北京)科技有限公司
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Publication of WO2019201281A1 publication Critical patent/WO2019201281A1/zh
Priority to US16/742,926 priority Critical patent/US11085334B2/en

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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01KSTEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K7/00Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
    • F01K7/34Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being of extraction or non-condensing type; Use of steam for feed-water heating
    • F01K7/38Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being of extraction or non-condensing type; Use of steam for feed-water heating the engines being of turbine type
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24HEATING; RANGES; VENTILATING
    • F24DDOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D3/00Hot-water central heating systems
    • F24D3/10Feed-line arrangements, e.g. providing for heat-accumulator tanks, expansion tanks ; Hydraulic components of a central heating system
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01KSTEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K7/00Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
    • F01K7/34Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being of extraction or non-condensing type; Use of steam for feed-water heating
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01KSTEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K11/00Plants characterised by the engines being structurally combined with boilers or condensers
    • F01K11/02Plants characterised by the engines being structurally combined with boilers or condensers the engines being turbines
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01KSTEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K17/00Using steam or condensate extracted or exhausted from steam engine plant
    • F01K17/02Using steam or condensate extracted or exhausted from steam engine plant for heating purposes, e.g. industrial, domestic
    • F01K17/025Using steam or condensate extracted or exhausted from steam engine plant for heating purposes, e.g. industrial, domestic in combination with at least one gas turbine, e.g. a combustion gas turbine
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01KSTEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K21/00Steam engine plants not otherwise provided for
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01KSTEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K7/00Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
    • F01K7/34Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being of extraction or non-condensing type; Use of steam for feed-water heating
    • F01K7/42Use of desuperheaters for feed-water heating
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01KSTEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K7/00Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
    • F01K7/34Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being of extraction or non-condensing type; Use of steam for feed-water heating
    • F01K7/44Use of steam for feed-water heating and another purpose
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01KSTEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K9/00Plants characterised by condensers arranged or modified to co-operate with the engines
    • F01K9/003Plants characterised by condensers arranged or modified to co-operate with the engines condenser cooling circuits
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22STEAM GENERATION
    • F22DPREHEATING, OR ACCUMULATING PREHEATED, FEED-WATER FOR STEAM GENERATION; FEED-WATER SUPPLY FOR STEAM GENERATION; CONTROLLING WATER LEVEL FOR STEAM GENERATION; AUXILIARY DEVICES FOR PROMOTING WATER CIRCULATION WITHIN STEAM BOILERS
    • F22D11/00Feed-water supply not provided for in other main groups
    • F22D11/02Arrangements of feed-water pumps
    • F22D11/06Arrangements of feed-water pumps for returning condensate to boiler
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24HEATING; RANGES; VENTILATING
    • F24DDOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D2200/00Heat sources or energy sources
    • F24D2200/16Waste heat
    • YGENERAL 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
    • Y02TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02EREDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E20/00Combustion technologies with mitigation potential
    • Y02E20/14Combined heat and power generation [CHP]

Definitions

  • the invention belongs to the field of power saving of power plants, and particularly relates to a steam recovery and heat recovery system for air-cooling units of large thermal power plants.
  • the cold end loss of the Rankine cycle of thermal power plants accounts for more than 50% of the energy loss of the entire power plant. Therefore, recycling of steam turbine residual steam heat and reducing cold end loss is the most potential in the field of power plant energy conservation and emission reduction.
  • the steam-heat recovery system of steam turbines based on steam turbines has been initially applied. It is usually used to boost the exhaust steam from a single steam turbine in a dual-turbine of a thermal power plant by means of a steam booster.
  • the thermal system uses waste heat.
  • waste heat from a single steam turbine to exhaust the waste heat can not fully meet the external heating demand, and the exhaust steam heat of the dual steam turbine in the power plant is not fully utilized, and further research is needed.
  • a more reasonable heating and heating system will be constructed to further realize the spent steam recovery and heating system to receive the exhausted steam of the entire thermal power plant and improve the energy saving effect. This is the waste heat recovery of the spent steam.
  • the object of the present invention is to provide a steam-free waste heat recovery and heating system for an air-cooling unit of a large thermal power plant, especially when the external heating area is particularly large.
  • a spent steam waste heat recovery and heating system for a large-scale thermal power plant air-cooling unit wherein a large-scale thermal power plant air-cooling unit includes first and second steam turbines and corresponding condensing equipment, and the first and second steam turbines respectively have first and second steam turbines
  • the low-pressure cylinders are respectively connected to the corresponding condensing equipment through a steam exhaust pipe
  • the spent steam waste heat recovery heating system includes the first and second steam-extracting systems and their corresponding first and second steam-increasing machines, front-mounted condensers and Turbine condenser, wherein the steam exhaust system is taken out by the exhaust steam extraction system; the two steam turbines have independent steam extraction systems, and the steam exhaust system of each steam turbine is connected to the corresponding front condensation through a steam take-off pipe.
  • the steam turbine the front side of the front condenser is connected to the steam exhausted steam of the appropriate elevated back pressure, the water side is fed into the heat network back water, and the steam water heat exchange heating heat network return water;
  • the steam exhaust line of each steam turbine Also connected to the suction steam inlet of the corresponding steamifier, and a steam supply steam extraction pipe is connected to the steam steam inlet of the steam turbine, and the steam is sucked by the heat extraction steam pipe for pressurization; each steam increase
  • the exhaust port of the machine is connected to the condenser of the corresponding steam-increasing machine.
  • the side of the condenser of the steam-increasing machine is connected to the pressurized steam, and the water side is connected to the return water of the heat network to perform steam-water heat exchange heating to return the water.
  • the parameters of the entire thermal system are matched most optimally, the operation mode is optimal, the utilization of the spent steam is increased, the heating capacity is improved, the cold end loss is minimized, and the energy saving benefit is maximized.
  • Figure 1 is a first-line configuration of a steam-free waste heat recovery and heating system for an air-cooled unit of a large thermal power plant;
  • Figure 2 is a second configuration of the exhaust steam heat recovery system of the air-cooling unit of a large thermal power plant
  • the first and second steam turbines respectively have first and second steam turbine low-pressure cylinders
  • Each of the first and second direct air cooling units (or indirect air cooling unit condensers) is connected through a steam exhaust pipe; a spent steam waste heat recovery heating system is constructed, and the exhaust steam extraction system is used to exhaust the exhaust pipes from the two direct air cooling units (or The upper opening of the indirect air-cooling unit condenser throat leads out the exhaust steam; the two steam turbines have their own independent steam take-off systems, and each steam turbine's exhaust steam take-off system is connected to the corresponding one through a steam take-off line.
  • the front side of the condenser head is connected to the steam exhausted steam of the appropriate elevated back pressure, the water side is fed into the heat network backwater, and the steam-water heat exchange is used to heat the heat network backwater;
  • the steam take-off line of the steam turbine is also connected to the suction steam inlet of the corresponding steam-increasing machine, and the steam-heating extraction steam pipe is connected to the steam steam inlet of the steam-increasing machine, and the steam is sucked by the heat-supply extraction pipe to pressurize.
  • the steam exhaust port of each steam adding machine is connected to the corresponding steam booster condenser, the shell side is connected to the pressurized steam, the water side is connected to the heat network back water, and the steam and water heat exchange is used for heating the heat network back water;
  • the steam turbine heating and extraction pipe is also connected to the heat pipe heater.
  • the heating extraction is from two steam turbines, that is, the corresponding steam recovery turbine and the adjacent steam turbine.
  • the steam extraction can also be carried out in the middle of the steam extraction.
  • the exhaust steam extraction system includes a special steam-extracting component and a steam-extracting pipeline; the steam-extracting special component is installed in the opening portion of the direct air-cooling unit exhaust pipe (or the indirect air-cooling unit condenser throat);
  • the exhaust steam main pipe is arranged, and the spent steam main pipe is connected between the two steam turbine exhaust steam outlet pipes, and the regulating steam valve is provided with a regulating valve, and the regulating valve is opened or closed to realize the joint of the two steam exhausting pipes or Isolate different ways of working.
  • the multi-stage heating method is adopted for the return water of the heating network, and the multi-stage heating condenser is sequentially connected.
  • the heating condenser is a steam-water heat exchange structure, including multiple front condensers and multiple units. Steam booster and heat network heater, using low pressure steam, supercharged steam and heat extraction steam with different back pressures, reasonably adjust the connection sequence of multi-stage heating condensers, and realize the heat network backwater gradient Heating, making full use of the residual heat of the steam in the power plant.
  • the first steam turbine exhaust steam is connected to the first front condenser, and the first steam booster is connected to the first steam booster condenser, and the first steam booster exhaust pressure is higher than the first steam turbine exhaust steam pressure.
  • the second steam turbine exhaust steam is connected to the second front condenser, and the second steam booster is connected to the second steam booster condenser, and the second steam booster exhaust pressure is higher than the second steam turbine exhaust steam pressure.
  • the exhaust steam pressure of the second steam booster is greater than the exhaust steam pressure of the first steam booster.
  • the first steam turbine has the same or lower steam pressure than the second steam turbine; the booster ratio of the two steamifiers may be the same or different, and the steam booster adopts an adjustable structure or a fixed structure.
  • connection sequence of the multi-stage heating condenser may be adopted, the first front condenser, the second front condenser, and the first steam booster.
  • connection sequence of the multi-stage heating condenser may be adopted, the first front condenser, the first steam booster, and the second front Condenser, second steamer condenser, heat network heater.
  • valve regulating system for the flow switching control can be set.
  • the valve regulating system (not shown) includes, firstly, the first steamifier condenser and the second front condenser are sequentially connected; the two pipelines are led out at the water inlet end of the first steam booster condenser, respectively Connected to the water inlet of the first front condenser and the water inlet of the second steamifier; the water outlet of the second front condenser leads out two pipes, which are respectively connected to the first front The water side outlet of the condenser and the water side inlet of the condenser of the second steamer.
  • the regulating valve is respectively installed on the four-way pipeline, and the flow of the hot water flowing through the first steam-increasing machine condenser and the second front-mounted condenser is controlled by adjusting the opening and closing of the valve, and the mode is realized at one time (as shown in FIG. 1).
  • the hot mesh water flows from the second pre-condenser to the condenser from the first booster, or in the second mode (Fig. 2), the hot net water flows from the first booster condenser to the second precondensed condenser.
  • the steamer flows out. According to the adjustment of the parameters of the two steam turbines and the two steam-increasing machines, the pressure changes of the low-pressure steam and the supercharged steam can be flexibly configured, and the different operating modes of the system can be flexibly configured.
  • Adjusting valves are provided on each steam line and heating network circulating water pipe of the steam adding machine to realize the operation adjustment or shutdown of the system; the heating condensers of each level are provided with parallel bypass for independent operation at all levels. Or close.
  • Embodiment 1 As shown in FIG.
  • a power plant is installed with two 330MW class direct air cooling units.
  • the external heating area is 23 million m2, the return temperature of the hot network is 25-40 °C, the water supply temperature is 120 °C, and the heat network water is 10500 t/h.
  • the heating extraction parameters are 0.2-0.4 MPa.a and 233 °C. (The above parameters are merely examples for convenience of description. Other parameter configurations are also within the scope of the present application).
  • the actual situation of the power plant and the heating area is: the heating area of the heating network is particularly large, the return temperature of the heating network is 25-40 ° C, and the water supply temperature is 120 °C.
  • the thermal power plant is the heat source of urban heating.
  • the main sources of heat in the first station are: 1. Two 330MW-class direct air-cooled units of the power plant have no steam residual heat; 2. The two 330MW-class direct air-cooled units of the power plant provide steam extraction. .
  • the large-scale thermal power plant air-cooling unit spent steam waste heat recovery heating system including two steam turbines and two air-cooling units, a steam take-off system, a first front condenser, a second front condenser, a first steam-increasing machine, The second steam booster, the first steam booster condenser, and the second steam booster condenser; the exhaust steam extraction system is used to open the holes in the exhaust steam pipes of the two connected direct air cooling units, and the steam is taken out through the pipeline to Steam booster or pre-condenser; the operating back pressure of the two steam turbines is different; the hot network circulating water pipeline is sequentially connected to the first pre-condenser, the second pre-condenser, the first booster condenser, the first The second steam booster condenser and the heat net heater are heated.
  • the two steam turbines When heating in winter, the two steam turbines have different operating back pressures, which are high back pressure steam turbines and low back pressure steam turbines.
  • one of the turbines has a back pressure of 10.5 KPa.a (corresponding to a saturation temperature of 46.75 °C) and the other turbine has a back pressure of 15 KPa.a (corresponding to a saturation temperature of 54 °C).
  • 10.5 KPa.a and 15 KPa.a are merely examples for convenience of description. Other parameter configurations are also within the scope of this application).
  • the steam-utilizing turbine system of both units was recycled.
  • the exhaust steam extraction system uses the exhaust steam extraction system to take out from the 330MW first-stage steam turbine exhaust pipe and the 330MW second steam turbine exhaust pipe, respectively, and the two directly air-cooled exhaust steam are led out.
  • the exhaust steam extraction system includes a steam-extracting special-purpose part, a steam-extracting line, and a steam-steam tube.
  • the first exhaust steam outlet pipe connects the first front condenser steam side and the first steam booster suction steam inlet;
  • the second spent steam extraction pipe connects the second front condenser steam side and the second steam booster suction steam Entrance.
  • the steam turbine heating and exhausting pipeline is connected to the steam inlets of the two steamers; the exhaust steam outlet pipelines are respectively connected to the suction steam inlets of the corresponding steamers; the first steam turbine exhaust ports are connected to the first steamer condensers, The second steamer exhaust port is connected to the second steamer condenser.
  • the first steam-increasing machine steam pressure is 0.2--0.4MPa.a (temperature 233°C)
  • the first steam-increasing machine has a steam pressure of 10.5KPa.a (temperature 46.75°C)
  • the first steam-increasing machine exhaust pressure is 20KPa.a.
  • the second steam booster has a steam pressure of 0.2--0.4 MPa.a (temperature 233 °C), a second steam booster steam pressure of 15 KPa.a (temperature 54 °C), and a second steam-increasing engine exhaust pressure of 31 KPa.a.
  • the steam booster adopts an adjustable structure or a fixed structure.
  • the heat extraction steam is from the steam turbine of the corresponding spent steam recovery and the adjacent steam turbine.
  • Regulating valves are provided on the steam turbine steam line and the heating network circulating water pipe to realize the operation adjustment or shutdown of the system.
  • the return water temperature is 25-40 °C.
  • the hot network circulating water flows through the first pre-condenser, the second pre-condenser, the first steam-increasing condenser, the second steam-increasing condenser and the heat net heater. . After passing through the first pre-condenser, the temperature of the hot water reaches 45 ° C; after the second pre-condenser, the temperature of the hot water reaches 52.5 ° C; after the first steam booster, the temperature of the hot water It reaches 58.5 °C; after the second steamer condenser, the hot water temperature reaches 68.3 °C; after the heat network heater, the hot water temperature reaches 120 °C.
  • the hot network circulating water reaches 120 °C after multi-stage heating and is sent to the municipal pipe network.
  • Embodiment 2 as shown in FIG. 2
  • a power plant is installed with two 330MW class direct air cooling units.
  • the heating area is 23 million m2, the return temperature of the hot network is 25-40 °C, the water supply temperature is 120 °C, and the heat network water is 10500 t/h.
  • the heating extraction parameters are 0.2--0.4 MPa.a and 233 °C. (The above parameters are merely examples for convenience of description. Other parameter configurations are also within the scope of the present application).
  • the actual situation of the power plant and the heating area is: the heat supply area of the heat network is particularly large, and the heat network belongs to a large temperature difference heating.
  • the thermal power plant is the heat source of urban heating.
  • the main sources of heat in the first station are: 1. Two 330MW-class direct air-cooled units of the power plant have no steam residual heat; 2. The two 330MW-class direct air-cooled units of the power plant provide steam extraction. .
  • the large-scale thermal power plant air-cooling unit spent steam waste heat recovery heating system including two steam turbines and two air-cooling units, a steam take-off system, a first front condenser, a second front condenser, a first steam-increasing machine, The second steam booster, the first steam booster condenser, and the second steam booster condenser; the exhaust steam extraction system is used to open the holes in the exhaust steam pipes of the two connected direct air cooling units, and the steam is taken out through the pipeline to The steam booster or the newly added front condenser; the operating back pressure of the two steam turbines is different; the hot network circulating water pipeline is connected to the first front condenser, the first steam booster condenser, the second front condenser, The second steamifier condenser and the heat network heater are heated.
  • the two steam turbines When heating in winter, the two steam turbines have different operating back pressures, which are high back pressure steam turbines and low back pressure steam turbines.
  • one of the turbines has a back pressure of 10.5 KPa.a (corresponding to a saturation temperature of 46.75 ° C) and another turbine has a back pressure of 28 KPa.a (corresponding to a saturation temperature of 67.5 ° C).
  • 10.5 KPa.a and 28 KPa.a are merely examples for convenience of description. Other parameter configurations are also within the scope of the present application).
  • the spent steam of both units was recycled.
  • the exhaust steam extraction system uses the exhaust steam extraction system to take out from the exhaust pipe of the 330MW first steam turbine and the exhaust pipe of the 330MW second steam turbine, and the exhaust steam of the two direct air cooling units is led out.
  • the exhaust steam extraction system includes a steam-extracting special-purpose part, a steam-extracting line, and a steam-steam tube.
  • the first exhaust steam outlet pipe connects the front condenser steam side and the first steam booster suction steam inlet; the second spent steam outlet pipe connects the second front condenser steam side and the second steam booster suction steam inlet.
  • the first steam-increasing machine steam pressure is 0.2--0.4MPa.a (temperature 233°C)
  • the first steam-increasing machine has a steam pressure of 10.5KPa.a (temperature 46.75°C)
  • the first steam-increasing machine exhaust pressure is 20KPa.a.
  • the second steam booster has a steam pressure of 0.2--0.4 MPa.a (temperature 233 °C), a second steam booster steam pressure of 28 KPa.a (temperature 67.5 °C), and a second steam-increasing machine steam pressure of 48 KPa.a.
  • the steam booster adopts an adjustable structure or a fixed structure.
  • the heat extraction steam is from the steam turbine of the corresponding spent steam recovery and the adjacent steam turbine.
  • Regulating valves are provided on the steam turbine steam line and the heating network circulating water pipe to realize the operation adjustment or shutdown of the system.
  • the return water temperature is 25-40 °C
  • the hot network circulating water flows through the first pre-condenser, the first steam-increasing condenser, the second pre-condenser, the second steam-increasing condenser and the heat net heater. .
  • the temperature of the hot water reaches 45 ° C; after the first steam booster, the hot water temperature reaches 58.5 ° C; after the second pre-condenser, the hot water temperature The temperature reached 66 ° C; after the second steamer condenser, the hot water temperature reached 79 ° C; after the hot network heater, the hot water temperature reached 120 ° C.
  • the hot network circulating water reaches 120 °C after multi-stage heating and is sent to the municipal pipe network.
  • Embodiment 3 as shown in FIG.
  • a power plant is installed with two 600MW class indirect air cooling units.
  • the heating area is 35 million m2, the return temperature of the hot network is 25-40 °C, the water supply temperature is 125 °C, and the hot water is 15000 t/h.
  • the heating extraction parameters are 0.2--0.4 MPa.a and 233 °C. (The above parameters are merely examples for convenience of description. Other parameter configurations are also within the scope of the present application).
  • the two steam turbines When heating in winter, the two steam turbines have different operating back pressures, which are high back pressure steam turbines and low back pressure steam turbines.
  • one of the turbines has a back pressure of 10.5 KPa.a (corresponding to a saturation temperature of 46.75 °C) and the other turbine has a back pressure of 15 KPa.a (corresponding to a saturation temperature of 54 °C).
  • 10.5 KPa.a and 15 KPa.a are merely examples for convenience of description. Other parameter configurations are also within the scope of this application).
  • the spent steam of both units was recycled.
  • the first steam-increasing machine steam pressure is 0.2--0.4MPa.a (temperature 233°C)
  • the first steam-increasing machine has a steam pressure of 10.5KPa.a (temperature 46.75°C)
  • the first steam-increasing machine exhaust pressure is 20KPa.a.
  • the second steam booster has a steam pressure of 0.2--0.4 MPa.a (temperature 233 °C), a second steam booster steam pressure of 15 KPa.a (temperature 54 °C), and a second steam-increasing engine exhaust pressure of 31 KPa.a.
  • the return water temperature is 25-40 °C.
  • the hot network circulating water flows through the first pre-condenser, the second pre-condenser, the first steam-increasing condenser, the second steam-increasing condenser and the heat net heater. . After passing through the first pre-condenser, the temperature of the hot water reaches 45 ° C; after the second pre-condenser, the temperature of the hot water reaches 52.5 ° C; after the first steam booster, the temperature of the hot water It reaches 58.5 °C; after the second steamer condenser, the hot water temperature reaches 68.3 °C; after the heat network heater, the hot water temperature reaches 120 °C.
  • the hot network circulating water reaches 120 °C after multi-stage heating and is sent to the municipal pipe network.
  • Embodiment 4 as shown in FIG. 2
  • a power plant is installed with two 600MW class indirect air cooling units.
  • the heating area is 35 million m2, the return temperature of the hot network is 25-40 °C, the water supply temperature is 125 °C, and the hot water is 15000 t/h.
  • the heating extraction parameters are 0.2--0.4 MPa.a and 233 °C. (The above parameters are merely examples for convenience of description. Other parameter configurations are also within the scope of this application).
  • the two steam turbines When heating in winter, the two steam turbines have different operating back pressures, which are high back pressure steam turbines and low back pressure steam turbines.
  • one of the turbines has a back pressure of 10.5 KPa.a (corresponding to a saturation temperature of 46.75 ° C) and another turbine has a back pressure of 28 KPa.a (corresponding to a saturation temperature of 67.5 ° C).
  • 10.5 KPa.a and 28 KPa.a are merely examples for convenience of description. Other parameter configurations are also within the scope of the present application).
  • the spent steam of both units was recycled.
  • the first steam-increasing machine steam pressure is 0.2--0.4MPa.a (temperature 233°C)
  • the first steam-increasing machine has a steam pressure of 10.5KPa.a (temperature 46.75°C)
  • the first steam-increasing machine exhaust pressure is 20KPa.a.
  • the second steam booster has a steam pressure of 0.2--0.4 MPa.a (temperature 233 °C), a second steam booster steam pressure of 28 KPa.a (temperature 67.5 °C), and a second steam-increasing engine exhaust pressure of 48 KPa.a.
  • the return water temperature is 25-40 °C.
  • the hot network circulating water flows through the first pre-condenser, the second pre-condenser, the first steam-increasing condenser, the second steam-increasing condenser and the heat net heater. . After passing through the first pre-condenser, the temperature of the hot water reaches 45 ° C; after the second pre-condenser, the temperature of the hot water reaches 52.5 ° C; after the first steam booster, the temperature of the hot water It reaches 58.5 °C; after the second steamer condenser, the hot water temperature reaches 68.3 °C; after the heat network heater, the hot water temperature reaches 120 °C.
  • the hot network circulating water reaches 120 °C after multi-stage heating and is sent to the municipal pipe network.

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Abstract

一种用于大型火电厂空冷机组的乏汽余热回收供热系统,大型火电厂空冷机组包括第一、第二汽轮机和对应的凝汽设备,第一、第二汽轮机分别具有第一、二汽轮机低压缸(1、2),各自通过一排汽管道连接对应的凝汽设备。乏汽余热回收供热系统包括第一、二乏汽引出系统及各自对应的第一、二增汽机(7、8)、前置凝汽器(9、10)和增汽机凝汽器(11、12)。两汽轮机都有各自独立的乏汽引出系统,每个汽轮机的乏汽引出管路连接至对应前置凝汽器(9、10),前置凝汽器(9、10)壳侧通入适当抬高背压的汽轮机乏汽,水侧通入热网回水。每个汽轮机的乏汽引出管路还连接至对应增汽机(7、8)的抽吸蒸汽入口,并且汽轮机供热抽汽连接管路至增汽机(7、8)的动力蒸汽入口,利用供热抽汽抽吸乏汽进行增压。每个增汽机(7、8)的排汽口连接至对应增汽机凝汽器(11、12),增汽机凝汽器(11、12)壳侧通入增压乏汽,水侧通入热网回水。

Description

一种大型火电厂空冷机组乏汽余热回收供热系统 技术领域
本发明属于电厂节能领域,具体涉及一种大型火电厂空冷机组乏汽余热回收供热系统。
背景技术
众所周知,火力发电厂朗肯循环的冷端损失,占整个电厂能量损失的50%以上。因此回收利用汽轮机乏汽余热,降低冷端损失,在电厂节能减排领域是最有潜力的。
对于空冷机组,基于增汽机的汽轮机组乏汽余热回收供热系统已有初步应用,其通常是利用增汽机对火力发电厂双汽轮机中的单台汽轮机排出乏汽进行增压,接入对外供热系统进行余热利用。但是,在供热面积特别大的情况下,利用单台汽轮机排出乏汽增压后进行余热利用无法充分满足外部的供热需求,同时电厂中双汽轮机的乏汽余热也没有充分利用,需要进一步根据电厂及所对应供热区域实际状况,构建更加合理的供热热力系统,进一步实现乏汽余热回收供热系统接纳整个火力发电厂的乏汽量,提高节能效果,这是乏汽余热回收供热工程中必须解决的问题。
发明内容
本发明的目的在于提供一种大型火电厂空冷机组乏汽余热回收供热系统,尤其是对应外部供热面积特别大时。
一种用于大型火电厂空冷机组的乏汽余热回收供热系统,其中大型火电厂空冷机组,包括第一、二汽轮机和对应凝汽设备,第一、第二汽轮机分别具有第一、二汽轮机低压缸,各自通过一排汽管道连接对应的凝汽设备;乏汽余热回收供热系统包括第一、二乏汽引出系统及各自对应的第一、二增汽机、前置凝汽器和增汽机凝汽器,其中利用乏汽引出系统将汽轮机乏汽引出;两汽轮机都有各自独立的乏汽引出系统,每个汽轮机的乏汽引出系统通过一乏汽引出管路连接至对应前置凝汽器,前置凝汽器壳侧通入适当抬高背压的汽轮机乏汽,水侧通入热网回水,进行汽水换热加热热网回水;每个汽轮机的乏汽引出管路还连接至对应增汽机的抽吸蒸汽入口,并且一汽轮机供热抽汽管道连接至增汽机的动力蒸汽入口,利用供热抽汽管道抽吸乏汽进行增压;每个增汽机的排汽口连接至对应增汽机凝汽器,增汽机凝汽器壳侧通入增压乏汽,水侧通入热网回水,进行汽水换热加热热网回水。
通过上述技术方案,使得整个热力系统参数匹配最合理,运行方式最佳,提高乏汽利用量,提高供热能力,最大程度地降低冷端损失,实现节能效益最大化。
附图说明
图1是大型火电厂空冷机组乏汽余热回收供热系统构成方式一;
图2是大型火电厂空冷机组乏汽余热回收供热系统构成方式二;
其中1、第一汽轮机低压缸;2、第二汽轮机低压缸;3、第一直接空冷机组(或间接空冷机组凝汽器);4、第二空冷岛(或间接空冷 机组凝汽器);5、第一乏汽引出系统;6、第二乏汽引出系统;7、第一增汽机;8、第二增汽机;9、第一前置凝汽器;10、第二前置凝汽器;11、第一增汽机凝汽器;12、第二增汽机凝汽器;13、热网加热器;14、热网水系统;15、供热抽汽管道;16、排汽管道。
具体实施方式
下面结合附图对本发明作进一步描述,应当理解,此处所描述的内容仅用于说明和解释本发明,并不用于限定本发明。
对于大型火电厂空冷机组,包括第一、二汽轮机和对应的第一、二直接空冷机组(或间接空冷机组凝汽器),第一、第二汽轮机分别具有第一、二汽轮机低压缸,其各自通过一排汽管道连接第一、二直接空冷机组(或间接空冷机组凝汽器);构建乏汽余热回收供热系统,利用乏汽引出系统从两连接直接空冷机组的排汽管道(或间接空冷机组凝汽器喉部)上开孔将乏汽引出来;两汽轮机都有各自独立的乏汽引出系统,每个汽轮机的乏汽引出系统分别通过一乏汽引出管路连接至对应前置(乏汽)凝汽器,前置凝汽器壳侧通入适当抬高背压的汽轮机乏汽,水侧通入热网回水,进行汽水换热用于加热热网回水;每个汽轮机的乏汽引出管路还连接至对应增汽机的抽吸蒸汽入口,并且汽轮机供热抽汽管道连接至增汽机的动力蒸汽入口,利用供热抽汽管道抽吸乏汽进行增压。每个增汽机的排汽口连接至对应增汽机凝汽器,其壳侧通入增压乏汽,水侧通入热网回水,进行汽水换热用于加热热网回水;
汽轮机供热抽汽管道还连接管路至热网加热器。
供热抽汽来自于两汽轮机,即相应乏汽回收利用的汽轮机和相邻另一台汽轮机。供热抽汽也可采用中排蒸汽。
乏汽引出系统包括乏汽引出特制件、乏汽引出管路;乏汽引出特制件安装于直接空冷机组排汽管道(或间接空冷机组凝汽器喉部)上的开孔部位;还可以进一步设置乏汽母管,乏汽母管连接在两汽轮机乏汽引出管路之间,乏汽母管上设置有调节阀门,通过调节阀门开启或关闭,可实现两乏汽引出管路的联合或隔离不同工作方式。
针对供热热网系统,对热网回水采用多级加热方式,顺序连接多级加热式凝汽器,加热式凝汽器为汽水换热结构,包括多台前置凝汽器、多台增汽机凝汽器、热网加热器,利用不同背压的低压乏汽、增压乏汽和供热抽汽,合理调整布置多级加热式凝汽器的连接顺序,实现热网回水梯度加热,充分利用电厂乏汽余热。
第一汽轮机乏汽连接第一前置凝汽器,同时经第一增汽机连接第一增汽机凝汽器,第一增汽机排汽压力高于第一汽轮机乏汽压力。第二汽轮机乏汽连接第二前置凝汽器,同时经第二增汽机连接第二增汽机凝汽器,第二增汽机排汽压力高于第二汽轮机乏汽压力。
第二增汽机排汽压力大于第一增汽机排汽压力。其中,第一汽轮机乏汽压力相同或低于第二汽轮机乏汽压力;两增汽机的升压比可相同或不同,增汽机采用可调式结构,或采用固定式结构。
如第二汽轮机乏汽压力低于第一增汽机排汽压力,多级加热式凝汽器的连接顺序可采用,第一前置凝汽器、第二前置凝汽器、第一增汽机凝汽器、第二增汽机凝汽器、热网加热器。
如第二汽轮机乏汽压力高于第一增汽机排汽压力,多级加热式凝汽器的连接顺序可采用,第一前置凝汽器、第一增汽机凝汽器、第二前置凝汽器、第二增汽机凝汽器、热网加热器。
进一步可设置流向切换控制的阀门调节系统。
阀门调节系统(图中未示)包括,首先,第一增汽机凝汽器和第二前置凝汽器顺序连接;在第一增汽机凝汽器的水侧进口端引出两路管道,分别连接到第一前置凝汽器水侧出口和第二增汽机凝汽器水侧进口;第二前置凝汽器的水侧出口端引出两路管道,同样的分别连接到第一前置凝汽器水侧出口和第二增汽机凝汽器水侧进口。在四路管道上分别安装有调节阀门,通过调节阀门的开闭来控制通过第一增汽机凝汽器和第二前置凝汽器的热网水流向切换,方式一时(如图1)实现热网水从第二前置凝汽器流入从第一增汽机凝汽器流出,或者方式二时(如图2)实现热网水从第一增汽机凝汽器流入从第二前置凝汽器流出。可现场根据两汽轮机、两增汽机参数调整所导致低压乏汽、增压乏汽的压力变化,灵活配置系统不同运行方式。
增汽机各蒸汽管路和热网循环水管路上均设有调节阀门,用于实现系统的投运调节或关闭;各级加热式凝汽器设有并联旁路,用于实现各级独立投运或关闭。
实施例一:如图1所示
某电厂装机为2台330MW级直接空冷机组。
对外供热面积2300万㎡,热网回水温度25-40℃,供水温度120℃,热网水量10500t/h。供热抽汽参数0.2-0.4MPa.a、233℃。 (上述参数仅仅是为了叙述方便而举的例子。其他参数的配置方式也在本申请保护范围内)。
该电厂及供热区域实际状况是:热网供热面积特别大,热网回水温度25-40℃,供水温度120℃。该火电厂作为城市供热的热源点,其首站的热量主要来源为:1、该电厂两台330MW级直接空冷机组乏汽余热;2、该电厂两台330MW级直接空冷机组供热抽汽。
该大型火电厂空冷机组乏汽余热回收供热系统,包括两汽轮机和对应两空冷机组,乏汽引出系统、第一前置凝汽器、第二前置凝汽器、第一增汽机、第二增汽机、第一增汽机凝汽器、第二增汽机凝汽器;利用乏汽引出系统,分别在两连接直接空冷机组的排汽管道上开孔将乏汽引出来,通过管道输送到增汽机或前置凝汽器;两汽轮机的运行背压不同;热网循环水管路顺序接入第一前置凝汽器、第二前置凝汽器、第一增汽机凝汽器、第二增汽机凝汽器、热网加热器进行加热。
冬季供热时,两汽轮机具有不同运行背压,分别为高背压汽轮机、低背压汽轮机。比如,其中一台汽轮机背压为10.5KPa.a(对应的饱和温度46.75℃)运行,另一台汽轮机背压为15KPa.a(对应的饱和温度54℃)运行。(10.5KPa.a和15KPa.a,仅仅是为了叙述方便而举的例子。其他参数的配置方式也在本申请保护范围内)。两台机组的乏汽利用增汽机系统都被回收利用。
利用乏汽引出系统,分别从330MW的第一级汽轮机排汽管道上和330MW的第二汽轮机排汽管道上开孔将乏汽引出来,将两台直接 空冷的乏汽引出来。乏汽引出系统包括乏汽引出特制件、乏汽引出管路和乏汽母管。
第一乏汽引出管连接第一前置凝汽器汽侧和第一增汽机抽吸蒸汽入口;第二乏汽引出管连接第二前置凝汽器汽侧和第二增汽机抽吸蒸汽入口。
汽轮机供热抽汽管道连接至两个增汽机的动力蒸汽入口;乏汽引出管路分别连接对应增汽机的抽吸蒸汽入口;第一增汽机排汽口连接至第一增汽机凝汽器,第二增汽机排汽口连接至第二增汽机凝汽器。
第一增汽机动力蒸汽压力0.2--0.4MPa.a(温度233℃),第一增汽机引射蒸汽压力10.5KPa.a(温度46.75℃),第一增汽机排汽压力20KPa.a。
第二增汽机动力蒸汽压力0.2--0.4MPa.a(温度233℃),第二增汽机引射蒸汽压力15KPa.a(温度54℃),第二增汽机排汽压力31KPa.a。
增汽机采用可调式结构,或采用固定式结构。
供热抽汽来自于相应乏汽回收利用的汽轮机和相邻另一台汽轮机。
增汽机蒸汽管路和热网循环水管路上均设有调节阀门,用于实现系统的投运调节或关闭。
回水温度25-40℃热网循环水依次流过第一前置凝汽器、第二前置凝汽器、第一增汽机凝汽器、第二增汽机凝汽器和热网加热器。 经过第一前置凝汽器后,热网水温度达到45℃;经过第二前置凝汽器后,热网水温度达到52.5℃;经过第一增汽机凝汽器后,热网水温度达到58.5℃;经过第二增汽机凝汽器后,热网水温度达到68.3℃;经过热网加热器后,热网水温度达到120℃。热网循环水经过多级加热后达到120℃,送往市政管网。
实施例二:如图2所示
某电厂装机为2台330MW级直接空冷机组。
供热面积2300万㎡,热网回水温度25-40℃,供水温度120℃,热网水量10500t/h。供热抽汽参数0.2--0.4MPa.a、233℃。(上述参数仅仅是为了叙述方便而举的例子。其他参数的配置方式也在本申请保护范围内)。
该电厂及供热区域实际状况是:热网供热面积特别大,且该热网属于大温差供热。该火电厂作为城市供热的热源点,其首站的热量主要来源为:1、该电厂两台330MW级直接空冷机组乏汽余热;2、该电厂两台330MW级直接空冷机组供热抽汽。
该大型火电厂空冷机组乏汽余热回收供热系统,包括两汽轮机和对应两空冷机组,乏汽引出系统、第一前置凝汽器、第二前置凝汽器、第一增汽机、第二增汽机、第一增汽机凝汽器、第二增汽机凝汽器;利用乏汽引出系统,分别在两连接直接空冷机组的排汽管道上开孔将乏汽引出来,通过管道输送到增汽机或新增前置凝汽器;两汽轮机的运行背压不同;热网循环水管路接入第一前置凝汽器、第一增汽机凝汽器、第二前置凝汽器、第二增汽机凝汽器、热网加 热器进行加热。
冬季供热时,两汽轮机具有不同运行背压,分别为高背压汽轮机、低背压汽轮机。比如,其中一台汽轮机背压为10.5KPa.a(对应的饱和温度46.75℃)运行,另一台汽轮机背压为28KPa.a(对应的饱和温度67.5℃)运行。(10.5KPa.a和28KPa.a,仅仅是为了叙述方便而举的例子。其他参数的配置方式也在本申请保护范围内)。两台机组的乏汽都被回收利用。
利用乏汽引出系统,分别从330MW级第一汽轮机排汽管道上和330MW第二汽轮机排汽管道上开孔将乏汽引出来,将两台直接空冷机组的乏汽引出来。乏汽引出系统包括乏汽引出特制件、乏汽引出管路和乏汽母管。
第一乏汽引出管连接前置凝汽器汽侧和第一增汽机抽吸蒸汽入口;第二乏汽引出管连接第二前置凝汽器汽侧和第二增汽机抽吸蒸汽入口。
汽轮机供热抽汽连接管路至两个增汽机的动力蒸汽入口;乏汽引出管路分别连接对应增汽机的抽吸蒸汽入口;第一增汽机排汽口连接至第一增汽机凝汽器,第二增汽机排汽口连接至第二增汽机凝汽器。
第一增汽机动力蒸汽压力0.2--0.4MPa.a(温度233℃),第一增汽机引射蒸汽压力10.5KPa.a(温度46.75℃),第一增汽机排汽压力20KPa.a。
第二增汽机动力蒸汽压力0.2--0.4MPa.a(温度233℃),第二增 汽机引射蒸汽压力28KPa.a(温度67.5℃),第二增汽机排汽压力48KPa.a。
增汽机采用可调式结构,或采用固定式结构。
供热抽汽来自于相应乏汽回收利用的汽轮机和相邻另一台汽轮机。
增汽机蒸汽管路和热网循环水管路上均设有调节阀门,用于实现系统的投运调节或关闭。
回水温度25-40℃热网循环水依次流过第一前置凝汽器、第一增汽机凝汽器、第二前置凝汽器、第二增汽机凝汽器和热网加热器。经过第一前置凝汽器后,热网水温度达到45℃;经过第一增汽机凝汽器后,热网水温度达到58.5℃;经过第二前置凝汽器后,热网水温度达到66℃;经过第二增汽机凝汽器后,热网水温度达到79℃;经过热网加热器后,热网水温度达到120℃。热网循环水经过多级加热后达到120℃,送往市政管网。
实施例三:如图1所示
某电厂装机为2台600MW级间接空冷机组。
供热面积3500万㎡,热网回水温度25-40℃,供水温度125℃,热网水量15000t/h。供热抽汽参数0.2--0.4MPa.a、233℃。(上述参数仅仅是为了叙述方便而举的例子。其他参数的配置方式也在本申请保护范围内)。
冬季供热时,两汽轮机具有不同运行背压,分别为高背压汽轮机、低背压汽轮机。比如,其中一台汽轮机背压为10.5KPa.a(对应 的饱和温度46.75℃)运行,另一台汽轮机背压为15KPa.a(对应的饱和温度54℃)运行。(10.5KPa.a和15KPa.a,仅仅是为了叙述方便而举的例子。其他参数的配置方式也在本申请保护范围内)。两台机组的乏汽都被回收利用。
第一增汽机动力蒸汽压力0.2--0.4MPa.a(温度233℃),第一增汽机引射蒸汽压力10.5KPa.a(温度46.75℃),第一增汽机排汽压力20KPa.a。
第二增汽机动力蒸汽压力0.2--0.4MPa.a(温度233℃),第二增汽机引射蒸汽压力15KPa.a(温度54℃),第二增汽机排汽压力31KPa.a。
回水温度25-40℃热网循环水依次流过第一前置凝汽器、第二前置凝汽器、第一增汽机凝汽器、第二增汽机凝汽器和热网加热器。经过第一前置凝汽器后,热网水温度达到45℃;经过第二前置凝汽器后,热网水温度达到52.5℃;经过第一增汽机凝汽器后,热网水温度达到58.5℃;经过第二增汽机凝汽器后,热网水温度达到68.3℃;经过热网加热器后,热网水温度达到120℃。热网循环水经过多级加热后达到120℃,送往市政管网。
实施例四:如图2所示
某电厂装机为2台600MW级间接空冷机组。
供热面积3500万㎡,热网回水温度25-40℃,供水温度125℃,热网水量15000t/h。供热抽汽参数0.2--0.4MPa.a、233℃。(上述参数仅仅是为了叙述方便而举的例子。其他参数的配置方式也在本 申请保护范围内)。
冬季供热时,两汽轮机具有不同运行背压,分别为高背压汽轮机、低背压汽轮机。比如,其中一台汽轮机背压为10.5KPa.a(对应的饱和温度46.75℃)运行,另一台汽轮机背压为28KPa.a(对应的饱和温度67.5℃)运行。(10.5KPa.a和28KPa.a,仅仅是为了叙述方便而举的例子。其他参数的配置方式也在本申请保护范围内)。两台机组的乏汽都被回收利用。
第一增汽机动力蒸汽压力0.2--0.4MPa.a(温度233℃),第一增汽机引射蒸汽压力10.5KPa.a(温度46.75℃),第一增汽机排汽压力20KPa.a。
第二增汽机动力蒸汽压力0.2--0.4MPa.a(温度233℃),第二增汽机引射蒸汽压力28KPa.a(温度67.5℃),第二增汽机排汽压力48KPa.a。
回水温度25-40℃热网循环水依次流过第一前置凝汽器、第二前置凝汽器、第一增汽机凝汽器、第二增汽机凝汽器和热网加热器。经过第一前置凝汽器后,热网水温度达到45℃;经过第二前置凝汽器后,热网水温度达到52.5℃;经过第一增汽机凝汽器后,热网水温度达到58.5℃;经过第二增汽机凝汽器后,热网水温度达到68.3℃;经过热网加热器后,热网水温度达到120℃。热网循环水经过多级加热后达到120℃,送往市政管网。
最后应说明的是:以上所述仅为本发明的解释,并不用于限制本发明,尽管对本发明进行了详细的说明,对于本领域的技术人员 来说,其依然可以对前述所记载的技术方案进行修改,或者对其中部分技术特征进行等同替换。凡在本发明的精神和原则之内,所作的任何修改、等同替换、改进等,均应包含在本发明的保护范围之内。

Claims (10)

  1. 一种用于大型火电厂空冷机组的乏汽余热回收供热系统,其中大型火电厂空冷机组,包括第一、第二汽轮机和对应凝汽设备,第一、第二汽轮机分别具有第一、二汽轮机低压缸,各自通过一排汽管道连接对应的凝汽设备;其特征在于,乏汽余热回收供热系统包括第一、二乏汽引出系统及各自对应的第一、二增汽机、前置凝汽器和增汽机凝汽器,其中利用一乏汽引出系统将汽轮机乏汽引出;两汽轮机都有各自独立的乏汽引出系统,每个汽轮机的乏汽引出系统通过一乏汽引出管路连接至对应前置凝汽器,前置凝汽器壳侧通入汽轮机乏汽,水侧通入热网回水,进行汽水换热加热热网回水;每个汽轮机的乏汽引出管路还连接至对应增汽机的抽吸蒸汽入口,并且一汽轮机供热抽汽管道连接至增汽机的动力蒸汽入口,利用供热抽汽管道抽吸乏汽进行增压;每个增汽机的排汽口连接至对应增汽机凝汽器,增汽机凝汽器壳侧通入增压乏汽,水侧通入热网回水,进行汽水换热加热热网回水。
  2. 根据权利要求1所述的一种用于大型火电厂空冷机组的乏汽余热回收供热系统,其特征在于,多台前置凝汽器和多台增汽机凝汽器顺序串联,构成多级梯度热网回水加热系统。
  3. 根据权利要求1所述的一种用于大型火电厂空冷机组的乏汽余热回收供热系统,其特征在于,第一汽轮机乏汽引出系统连接第一前置凝汽器,同时经第一增汽机连接第一增汽机凝汽器,第一增汽机排汽压力高于第一汽轮机乏汽压力;第二汽轮机乏汽引出系统连接第二前置凝汽器,同时经第二增汽机连接第二增汽机凝汽器,第二增汽机排汽压力高于第二汽轮机乏汽压力。
  4. 根据权利要求3所述的一种用于大型火电厂空冷机组的乏汽余热回收供热系统,其特征在于,第二增汽机排汽压力大于第一增汽机排汽压力;其中,第一汽轮机乏汽压力相同于或低于第二汽轮机乏汽压力。
  5. 根据权利要求1所述的一种用于大型火电厂空冷机组的乏汽余热回收供热系统,其特征在于,两增汽机的升压比相同或不同,增汽机采用可调式结构,或采用固定式结构。
  6. 根据权利要求3所述的一种用于大型火电厂空冷机组的乏汽余热回收供热系统,其特征在于,第二汽轮机乏汽压力低于第一增汽机排汽压力,多级梯度热网回水加热系统的连接顺序为第一前置凝汽器、第二前置凝汽器、第一增汽机凝汽器、第二增汽机凝汽器。
  7. 根据权利要求3所述的一种用于大型火电厂空冷机组的乏汽余热回收供热系统,其特征在于,第二汽轮机乏汽压力高于第一增汽机排汽压力,多级梯度热网回水加热系统的连接顺序为第一前置凝汽器、第一增汽机凝汽器、第二前置凝汽器、第二增汽机凝汽器。
  8. 根据权利要求2所述的一种用于大型火电厂空冷机组的乏汽余热回收供热系统,其特征在于,多级梯度热网回水加热系统还包括热网加热器,汽轮机供热抽汽管道连接至热网加热器。
  9. 根据权利要求3所述的一种用于大型火电厂空冷机组的乏汽余热回收供热系统,其特征在于,多级梯度热网回水加热系统中设置流向切换控制的阀门调节系统,用于对第二前置凝汽器和第一增汽机凝汽器进行热网水流向切换。
  10. 根据权利要求9所述的一种用于大型火电厂空冷机组的乏汽余热回收供热系统,其特征在于,第一增汽机凝汽器和第二前置凝汽器顺序连接;在第一增汽机凝汽器的水侧进口端引出两路管道,分别连接到第一前置凝汽器水侧出口和第二增汽机凝汽器水侧进口;第二前置凝汽器的水侧出口端引出两路管道,同样的分别连接到第一前置凝汽器水侧出口和第二增汽机凝汽器水侧进口;在四路管道上分别安装有调节阀门,通过调节阀门的开闭来控制通过第一增汽机凝汽器和第二前置凝汽器的热网水流向切换。
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