CN112833378B - Reheating system capable of improving heat supply capacity - Google Patents
Reheating system capable of improving heat supply capacity Download PDFInfo
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- CN112833378B CN112833378B CN202011577270.0A CN202011577270A CN112833378B CN 112833378 B CN112833378 B CN 112833378B CN 202011577270 A CN202011577270 A CN 202011577270A CN 112833378 B CN112833378 B CN 112833378B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F22—STEAM GENERATION
- F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
- F22B33/00—Steam-generation plants, e.g. comprising steam boilers of different types in mutual association
- F22B33/18—Combinations of steam boilers with other apparatus
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D15/00—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby
- F01D15/10—Adaptations for driving, or combinations with, electric generators
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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
- F01K11/00—Plants characterised by the engines being structurally combined with boilers or condensers
- F01K11/02—Plants characterised by the engines being structurally combined with boilers or condensers the engines being turbines
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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
- F01K7/00—Steam 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steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
- F01K7/02—Steam 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 multiple-expansion type
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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
- F01K7/00—Steam 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
- F01K7/16—Steam 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 only of turbine type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F22—STEAM GENERATION
- F22D—PREHEATING, 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
- F22D1/00—Feed-water heaters, i.e. economisers or like preheaters
- F22D1/50—Feed-water heaters, i.e. economisers or like preheaters incorporating thermal de-aeration of feed-water
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F22—STEAM GENERATION
- F22G—SUPERHEATING OF STEAM
- F22G5/00—Controlling superheat temperature
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
- F24D3/00—Hot-water central heating systems
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- Thermal Sciences (AREA)
- Control Of Steam Boilers And Waste-Gas Boilers (AREA)
Abstract
本发明属于热电联产机组技术领域，具体涉及一种可提高供热能力的再热系统。其技术方案为：一种可提高供热能力的再热系统，包括锅炉，锅炉通过管道连接有再热机组，再热机组的转轴上连接有再热机组发电机，锅炉与再热机组之间还连接有给水管路；所述锅炉的主蒸汽出口通过管道连接有旁路背压机，旁路背压机的转轴上连接有旁路背压机发电机，旁路背压机的出口管道和锅炉的主蒸汽出口的支管汇合后连接到锅炉的再热蒸汽进口，锅炉的再热蒸汽出口通过管道连接有疏水扩容器，疏水扩容器与给水管路连接，锅炉的再热蒸汽出口还连接有减温减压管路，减温减压管路连接到供热管网。本发明提供了一种增设旁路背压机来提高采暖期机组循环效率的再热系统。
The invention belongs to the technical field of cogeneration units, in particular to a reheating system capable of improving heating capacity. The technical scheme is as follows: a reheating system capable of improving heating capacity, comprising a boiler; the boiler is connected with a reheating unit through pipes; A water supply pipeline is also connected; the main steam outlet of the boiler is connected with a bypass back pressure machine through the pipeline, the bypass back pressure machine generator is connected to the rotating shaft of the bypass back pressure machine, and the outlet pipe of the bypass back pressure machine is connected After joining with the branch pipe of the main steam outlet of the boiler, it is connected to the reheat steam inlet of the boiler. The reheat steam outlet of the boiler is connected with a drain expansion vessel through a pipeline, the drain expansion vessel is connected with the feed water pipeline, and the reheat steam outlet of the boiler is also connected. There is a temperature reduction and pressure reduction pipeline, and the temperature reduction and pressure reduction pipeline is connected to the heating pipe network. The invention provides a reheating system for increasing the circulation efficiency of the unit during the heating period by adding a bypass back pressure machine.
Description
Technical Field
The invention belongs to the technical field of cogeneration units, and particularly relates to a reheating system capable of improving heat supply capacity.
Background
Energy conservation and emission reduction are policy measures for realizing sustainable development of economy in China, and for historical reasons, urban heat supply in China mainly depends on equipment with high energy consumption, low efficiency and heavy pollution, such as small heat supply units, small boilers and the like, and various emissions have great influence on the environment, so that haze weather is increased, the health of people is influenced, and the contradiction can be relieved by a centralized heat supply mode of a large-scale thermal power plant.
The method for central heating of large-scale thermal power plant mainly comprises punching steam extraction, high back pressure heating, low-pressure cylinder zero output, 3S coupling, heat pump technology and the like. However, although the above measures can increase the heat supply capacity of the unit, the heat supply capacity of the steam turbine cannot be exerted to the maximum, and the ever-increasing heat supply requirement of the city cannot be met. The problem of insufficient heat supply needs to be solved by newly building a boiler and power generation equipment or further excavating the potential of deep heat supply on the basis of the original reheating unit. With the rapid development of the domestic power industry in the years, the domestic power industry is supersaturated. The electric load rate of a turbo generator set with high parameter, large capacity and high efficiency is reduced sharply, some newly built million units need to be changed into deep peak shaving units, the load rate of most power plants is reduced to below 70 percent for long time, and even some power plants face the risk of shutdown. If a boiler and power generation equipment are continuously built, although the requirement of insufficient heat supply load can be met, two adverse factors are brought at the same time, one is that the power supersaturation phenomenon is more and more serious, a high-parameter, large-capacity and high-efficiency generator set needs to be continuously operated under reduced load, and the load factor of a power plant can be reduced to about 50% for long time; two high-parameter, high-capacity and high-efficiency generator sets run under low load, emission is increased, air quality is further reduced, and the requirement for heat supply is met by sacrificing the environment, which is contrary to the national dominant energy-saving and emission-reducing policy. Therefore, the heat supply potential of the reheating unit is developed to be most consistent with the national conditions at the present stage.
For the reheated system which is put into operation, if the reheated system is directly used for temperature reduction and pressure reduction heat supply through a boiler, the heat supply capacity can be exerted to the maximum, but the reheater has no flow, the problem of dry burning of the reheater cannot be solved, and the boiler cannot normally operate. If the middle-low pressure rotor of the steam turbine is changed into an optical axis, the boiler steam passes through a high-pressure cylinder and a reheater, and then is subjected to temperature reduction and pressure reduction for heat supply, so that the heat supply capacity can be maximized, and the problem of dry burning of the reheater of the boiler can be solved, but the rotor needs to be replaced by opening the cylinder after the heat supply period is over, the rotor needs to be replaced by opening the cylinder twice every year for a power plant, and the normal operation and time and labor consumption of the power plant are seriously influenced; the heating capacity of the reheating unit cannot be exerted to the maximum by adopting high-back-pressure heating, a 3S coupling, a heat pump and other heating technologies.
The technology of the invention can give full play to the heat supply potential of the reheating unit; the problem of dry burning of the superheater can be solved; the rotor does not need to be replaced by opening the cylinder every year, and the normal operation of the original unit is not influenced. The invention has three main advantages: firstly, the deep adjustment of electric load and thermal load is realized by utilizing the existing unit, the heating capacity of the reheating unit can be exerted to the maximum, the power of the turbine bypass back pressure unit is reduced to about 30 percent in the heating period, the electric power is subjected to deep peak regulation, the efficiency is not lower than the full load efficiency of the original unit, and the peak regulation is realized without reducing the efficiency; in the non-heating period, the unit can meet the peak regulation requirement in summer, and the problem of insufficient electric quantity in summer is solved; secondly, a new boiler is not required, so that investment is saved, energy is saved, emission is reduced, and national policies are met; and thirdly, the reheating unit and the bypass back press machine are coupled and transformed into a cogeneration unit, the unit coal consumption is greatly reduced, the circulation efficiency is greatly improved, and a new profit growth point is provided for a power plant.
Disclosure of Invention
In order to solve the problems in the prior art, the invention aims to provide a reheating system which is additionally provided with a bypass back press to improve the cycle efficiency of a unit in a heating period.
The technical scheme adopted by the invention is as follows:
a reheating system capable of improving heat supply capacity comprises a boiler, wherein the boiler is connected with a reheating unit through a pipeline, a reheating unit generator is connected to a rotating shaft of the reheating unit, and a water supply pipeline is connected between the boiler and the reheating unit; the main steam outlet of boiler has bypass back pressure machine through the pipe connection, be connected with bypass back pressure machine generator in the pivot of bypass back pressure machine, the outlet pipeline of bypass back pressure machine and the branch pipe of the main steam outlet of boiler join the reheat steam inlet that the back is connected to the boiler, the reheat steam outlet of boiler has hydrophobic flash tank through the pipe connection, hydrophobic flash tank and water supply line are connected, the reheat steam outlet of boiler still is connected with the pressure reduction pipeline that reduces the temperature, the pressure reduction pipeline that reduces the temperature is connected to the heat supply pipe network.
During heating, the original reheating unit is stopped, and steam is switched to the bypass backpressure unit. The main steam of the boiler enters the bypass backpressure machine to do work, the exhaust steam of the bypass backpressure machine enters a reheat steam inlet of the boiler, and part of the main steam of the boiler also enters the reheat steam inlet. The steam at the reheat steam outlet of the boiler is discharged to the drainage flash tank for expansion and then enters the water supply pipeline, and the hot water is replenished into the boiler. The heat supply capacity of the bypass back pressure unit reaches the maximum, can be increased by more than 2 times compared with the maximum heat supply capacity of the original reheating unit, the power reaches about 30% of the power of the original reheating unit, the bypass back pressure unit can improve the efficiency by increasing the number of stages and adopting the latest through-flow technology and other measures, the deep peak regulation is realized, and the efficiency is not reduced. After the heating period is finished, the bypass backpressure unit stops running, the steam is switched to the original reheating system to run, and the peak regulation requirement in summer can be met.
In the starting and stopping stages, the furnace can be stopped without stopping, the reheating unit and the unbalanced steam of the bypass backpressure unit share a high bypass system and a low bypass system, and steam enters a newly-added drainage flash tank after the temperature of the low bypass is reduced.
When the system runs in a heating period, the original reheating unit stops running, the high-pressure main steam regulating valve and the reheating combined steam valve are closed, and the condenser stops running; main steam enters a bypass backpressure machine, steam inlet parameters and steam exhaust parameters of the bypass backpressure machine are the same as those of a reheating cold section of an original reheating unit, the steam exhaust is subjected to temperature reduction and pressure reduction to supply heat, and the heat supply pressure is about 0.3 MPa. The temperature of the heat supply backwater is about 120 ℃, the heat supply backwater enters a deaerator of an original reheating unit, passes through a water feeding pump, a high heating unit and then enters a boiler superheater, and the deaerator and the high heating steam source come from a bypass back pressure machine.
The bypass back press and the original reheating unit are arranged in a split-shaft mode, a generator needs to be added, and the power of the generator is about 30% of that of the original reheating unit. Because of the single-shaft design of the bypass back pressure unit, the efficiency is not limited by critical rotating speed, the latest through-flow technology and more turbine stages can be adopted to improve the efficiency, and compared with the original reheating unit, the efficiency of the bypass back pressure unit cylinder can be improved by 3% -5%. The real realization does not sacrifice efficiency and realizes the deep peak regulation.
And (4) when the heating period is finished and the non-heating period is operated, the bypass back pressure unit is stopped, and steam enters the original reheating unit to operate.
As a preferred scheme of the invention, the water supply pipeline comprises a condensate pump, a low-pressure heater, a deaerator, a water supply pump and a high-pressure heater which are sequentially arranged, the boiler is positioned on one side of the high-pressure heater far away from the water supply pump, an inlet of the drainage flash tank is connected with a reheat steam outlet of the boiler through a pipeline, and an outlet of the drainage flash tank is connected with the condensate pump. Unbalanced steam of the boiler and the steam turbine enters the drainage flash tank after temperature and pressure reduction by utilizing a high-pressure bypass and a low-pressure bypass of an original reheating unit. After the low-pressure heater, the deaerator and the high-pressure heater respectively heat the feed water, the feed water is ensured to have higher temperature, and the consumption of energy in the boiler can be correspondingly reduced.
As a preferable scheme of the invention, one end of the temperature and pressure reducing pipeline far away from the boiler is also connected to the deaerator through a pipeline. In the heating period, steam of the temperature and pressure reducing pipeline provides a heat source for the deaerator.
As a preferable scheme of the invention, the outlet of the bypass back press is also connected with the high-pressure heater through a pipeline. During heating, the bypass back press provides a heat source for the high-pressure heater, and ensures that the supplied water reaches a sufficient temperature.
As a preferable scheme of the invention, the temperature and pressure reducing pipeline comprises a bypass back pressure machine emptying valve, a bypass back pressure machine stop valve, a bypass back pressure machine secondary temperature and pressure reducing valve and a bypass back pressure machine tertiary temperature and pressure reducing valve which are arranged in sequence.
In a preferred embodiment of the present invention, the reheating unit includes a high pressure cylinder, an intermediate pressure cylinder and a low pressure cylinder, which are sequentially disposed, a main steam outlet of the boiler is connected to a steam inlet of the high pressure cylinder through a pipeline, an outlet of the high pressure cylinder is connected to a reheat steam inlet of the boiler through a pipeline, a reheat steam outlet of the boiler is connected to the intermediate pressure cylinder through a pipeline, an outlet of the intermediate pressure cylinder is connected to the low pressure cylinder through a pipeline, and an outlet of the low pressure cylinder is connected to a water supply pipeline through a pipeline. Main steam of the boiler enters a high-pressure cylinder to do work, and exhaust steam of the high-pressure cylinder enters a reheat steam inlet of the boiler, is heated and then enters a middle pressure cylinder to do work. The exhaust steam of the intermediate pressure cylinder does work by the low pressure cylinder, so that the steam is fully utilized.
As a preferred scheme of the invention, the water supply pipeline comprises a condenser, a condensate pump, a low-pressure heater, a deaerator, a water supply pump and a high-pressure heater which are arranged in sequence, wherein an inlet of the condenser is connected with an outlet of the low-pressure cylinder through a pipeline, and an outlet of the high-pressure heater is connected with an inlet of the boiler through a pipeline.
As a preferable scheme of the invention, the outlet of the high-pressure cylinder is also connected with the high-pressure heater through a pipeline, the middle outlet of the intermediate-pressure cylinder is connected with the deaerator through a pipeline, and the middle outlet of the low-pressure cylinder is connected with the low-pressure heater through a pipeline. During the non-heating period, the exhaust steam of the high-pressure cylinder supplies heat to the high-pressure heater, the middle exhaust steam of the middle-pressure cylinder supplies heat to the deaerator, and the middle exhaust steam of the low-pressure cylinder supplies heat to the low-pressure heater, so that the water can be heated gradually.
As a preferable scheme of the invention, a water return pipe of the heat supply pipe network is connected with a deaerator. During heating, the return water of the heat supply pipe network enters the deaerator, and the feed water is recycled.
The invention has the beneficial effects that:
during heating, the original reheating unit is stopped, and steam is switched to the bypass backpressure unit. The main steam of the boiler enters the bypass backpressure machine to do work, the exhaust steam of the bypass backpressure machine enters a reheat steam inlet of the boiler, and part of the main steam of the boiler also enters the reheat steam inlet. The steam at the reheat steam outlet of the boiler is discharged to the drainage flash tank for expansion and then enters the water supply pipeline, and the hot water is replenished into the boiler. The heat supply capacity of the bypass back pressure unit reaches the maximum, can be increased by more than 2 times compared with the maximum heat supply capacity of the original reheating unit, the power reaches about 30% of the power of the original reheating unit, the bypass back pressure unit can improve the efficiency by increasing the number of stages and adopting the latest through-flow technology and other measures, the deep peak regulation is realized, and the efficiency is not reduced. After the heating period is finished, the bypass backpressure unit is stopped, the steam is switched to the original reheating system to operate, and the peak regulation requirement in summer can be met
Drawings
FIG. 1 is a schematic diagram of a thermodynamic system of the present invention in which a bypass back press is coupled to a reheat train;
fig. 2 is a schematic thermodynamic system diagram of a reheating unit.
In the figure, 1-boiler; 2-a reheating unit; 3-a reheat unit generator; 4-water supply pipeline; 5-a bypass back press; 6-bypass backpressure machine generator; 7-a hydrophobic flash tank; 8-a temperature and pressure reducing pipeline; 11-a high pressure bypass valve; 21-a high pressure cylinder; 22-intermediate pressure cylinder; 23-low pressure cylinder; 41-a condensate pump; 42-a low pressure heater; 43-a deaerator; 44-a feed pump; 45-high pressure heater; 46-a condenser; 51-bypass backpressure main steam regulating valve; 71-a reheat train low pressure bypass valve; 81-bypass backpressure machine evacuation valve; 82-bypass backpressure machine stop valve; 83-bypass back pressure machine two-stage temperature and pressure reducing valve; 84-bypass back pressure machine three-stage temperature and pressure reducing valve; 211-high pressure main steam regulating valve; 221-reheat combined steam valve; 421-low pressure heater stop valve; 431-deaerator stop valve; 451-high pressure heater cut-off valve; a-heat supply pipe network; b, discharging steam through a temperature and pressure reducing pipeline; c-supplying heat and returning water.
Detailed Description
Reference will now be made in detail to embodiments of the present invention, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to the same or similar elements or elements having the same or similar function throughout. The embodiments described below with reference to the drawings are illustrative and intended to be illustrative of the invention and are not to be construed as limiting the invention.
As shown in fig. 1 and fig. 2, the reheating system capable of improving heat supply capacity of the present embodiment includes a boiler 1, the boiler 1 is connected to a reheating unit 2 through a pipeline, a reheating unit generator 3 is connected to a rotating shaft of the reheating unit 2, and a water supply pipeline 4 is connected between the boiler 1 and the reheating unit 2; boiler 1's main steam outlet has bypass back pressure machine 5 through the pipe connection, be connected with bypass back pressure machine generator 6 in bypass back pressure machine 5's the pivot, the outlet pipeline of bypass back pressure machine 5 and boiler 1's main steam outlet's branch pipe join the back and are connected to boiler 1's reheat steam inlet, boiler 1's reheat steam outlet has hydrophobic flash vessel 7 through the pipe connection, hydrophobic flash vessel 7 is connected with water supply line 4, boiler 1's reheat steam outlet still is connected with temperature and pressure reduction pipeline 8, temperature and pressure reduction pipeline 8 is connected to heat supply pipe network A.
Wherein, reheat unit 2 is including the high pressure cylinder 21, intermediate pressure cylinder 22 and the low pressure cylinder 23 that set gradually, and the main steam outlet of boiler 1 passes through the pipeline and is connected with the steam inlet of high pressure cylinder 21, and the export of high pressure cylinder 21 passes through the pipeline and is connected with the reheat steam inlet of boiler 1, and the reheat steam outlet of boiler 1 passes through the pipeline and is connected with intermediate pressure cylinder 22, and the export of intermediate pressure cylinder 22 passes through the pipeline and is connected with low pressure cylinder 23, and the export of low pressure cylinder 23 passes through the pipeline and is connected with water supply pipe 4. Main steam of the boiler 1 enters a high-pressure cylinder 21 to do work, and exhaust steam of the high-pressure cylinder 21 enters a reheat steam inlet of the boiler 1, is heated and then enters an intermediate-pressure cylinder 22 to do work. The exhaust steam of the intermediate pressure cylinder 22 performs work of the low pressure cylinder 23, so that the steam is fully utilized.
The temperature and pressure reducing pipeline 8 comprises a bypass back-pressure machine emptying valve 81, a bypass back-pressure machine stop valve 82, a bypass back-pressure machine secondary temperature and pressure reducing valve 83 and a bypass back-pressure machine tertiary temperature and pressure reducing valve 84 which are arranged in sequence.
During heating, the original reheating unit 2 is stopped, and steam is switched to the bypass back press 5 unit. The main steam of the boiler 1 enters the bypass back press 5 to do work, the exhaust steam of the bypass back press 5 enters the reheat steam inlet of the boiler 1, and part of the main steam of the boiler 1 also enters the reheat steam inlet. The steam at the outlet of the reheat steam of the boiler 1 is discharged to a drain flash tank 7 for expansion and then enters a water supply pipeline 4, and the hot water is supplemented into the boiler 1. The heat supply capacity of the bypass back press 5 group reaches the maximum, can be increased by more than 2 times compared with the maximum heat supply capacity of the original reheating unit 2, the power reaches about 30% of the power of the original reheating unit 2, the effect improvement of the bypass back press 5 group can be realized by increasing the number of stages and adopting the latest through-flow technology and other measures, the deep peak regulation is realized, and the efficiency is not reduced. After the heating period is finished, the bypass back press 5 groups are stopped, the steam is switched to the original reheating system to operate, and the peak regulation requirement in summer can be met.
In the starting and stopping stages, the furnace can be stopped without stopping, the reheating unit 2 and the bypass back press 5 groups of unbalanced steam share a high bypass system and a low bypass system, and steam enters a newly-added drain flash tank 7 after temperature reduction at the low side.
When the system runs in the heating period, the original reheating unit 2 stops running, the high-pressure main steam regulating valve 211 and the reheating combined steam valve 221 are closed, and the condenser 46 stops running; main steam enters a bypass back press 5, steam inlet parameters and steam exhaust parameters of the bypass back press 5 are the same as those of a reheating cold section of an original reheating unit 2, the steam exhaust is used for supplying heat through temperature and pressure reduction, and the heat supply pressure is about 0.3 MPa. The temperature of the heating backwater C is about 120 ℃, the heating backwater C enters a deaerator 43 of an original reheating unit 2, passes through a water feeding pump 44, is subjected to high pressure heating, and then enters a superheater of a boiler 1, and the deaerator 43 and a high pressure heating steam source come from a bypass back pressure machine 5.
The bypass back press 5 and the original reheating unit 2 are arranged in a split-shaft mode, a generator needs to be added, and the power of the generator is about 30% of that of the original reheating unit 2. Because of the single-shaft design of the 5 groups of the bypass back press, the limitation of critical rotating speed is avoided, the latest through-flow technology and more turbine stages can be adopted to improve the efficiency, and compared with the original reheating unit 2, the efficiency of the 5 groups of cylinders of the bypass back press can be improved by 3% -5%. The real realization does not sacrifice efficiency and realizes the deep peak regulation.
And (3) when the heating period is finished and the non-heating period is in operation, the bypass back press 5 set is stopped, and steam enters the original reheating unit 2 for operation.
The invention can give full play to the heat supply potential of the reheating unit 2; the problem of dry burning of the superheater can be solved; the rotor does not need to be replaced by opening the cylinder every year, and the normal operation of the original unit is not influenced. The invention utilizes the existing unit to realize the deep adjustment of the electric load and the heat load, during the heating period, the heat supply capacity of the reheating unit 2 can be exerted to the maximum, the power of the steam turbine bypass back press 5 unit is reduced to about 30 percent, the electric power is subjected to deep peak regulation, the efficiency is not lower than the full load efficiency of the original unit, and the peak regulation is realized without reducing the efficiency; in the non-heating period, the unit can meet the peak regulation requirement in summer, and the problem of insufficient electric quantity in summer is solved. The invention does not need to newly build a boiler 1, saves investment, saves energy, reduces emission and conforms to national policies. The reheating unit 2 and the bypass back press 5 are coupled and transformed into a cogeneration unit, so that the unit coal consumption is greatly reduced, the circulation efficiency is greatly improved, and a new profit growth point is provided for a power plant.
Specifically, the water supply pipeline 4 includes a condenser 46, a condensate pump 41, a low-pressure heater 42, a deaerator 43, a water supply pump 44 and a high-pressure heater 45 which are arranged in sequence, the boiler 1 is located on one side of the high-pressure heater 45 far away from the water supply pump 44, an inlet of the drainage flash tank 7 is connected with a reheat steam outlet of the boiler 1 through a pipeline, an outlet of the drainage flash tank 7 is connected with the condensate pump 41, and an inlet of the condenser 46 is connected with an outlet of the low-pressure cylinder 23 through a pipeline. Unbalanced steam of the boiler 1 and the steam turbine enters the drainage flash tank 7 after temperature and pressure reduction by utilizing a high-pressure bypass and a low-pressure bypass of the original reheating unit 2. After the low-pressure heater 42, the deaerator 43 and the high-pressure heater 45 respectively heat the feed water, the feed water is ensured to have higher temperature, and the consumption of energy in the boiler 1 can be correspondingly reduced.
Furthermore, the end of the temperature and pressure reducing pipeline 8 far from the boiler 1 is connected to a deaerator 43 through a pipeline. In the heating period, steam in the temperature and pressure reducing pipeline 8 provides a heat source for the deaerator 43. The outlet of the bypass back press 5 is also connected to a high pressure heater 45 via a pipe. During heating, the bypass back press 5 provides a heat source for the high-pressure heater 45, and ensures that the feed water reaches a sufficient temperature. The outlet of the high-pressure cylinder 21 is also connected with a high-pressure heater 45 through a pipeline, the middle outlet of the intermediate-pressure cylinder 22 is connected with a deaerator 43 through a pipeline, and the middle outlet of the low-pressure cylinder 23 is connected with a low-pressure heater 42 through a pipeline. In the non-heating period, the exhaust steam of the high pressure cylinder 21 supplies heat to the high pressure heater 45, the middle exhaust steam of the intermediate pressure cylinder 22 supplies heat to the deaerator 43, and the middle exhaust steam of the low pressure cylinder 23 supplies heat to the low pressure heater 42, so that the water supply can be heated gradually.
Furthermore, the water return pipe of the heat supply pipe network a is connected with the deaerator 43. During heating, the backwater of the heat supply pipe network A enters the deaerator 43, and the feed water is recycled.
A bypass back-pressing machine main steam regulating valve 51 is installed on a pipe between a main steam outlet of the boiler 1 and the bypass back-pressing machine 5, a reheating unit low-pressure side valve 71 is installed on a pipeline between a reheating steam outlet of the boiler 1 and the drainage flash tank 7, a high-pressure main steam regulating valve 211 is arranged on a pipeline between the main steam outlet of the boiler 1 and the high-pressure cylinder 21, a reheating combined steam valve 221 is arranged on a pipeline between the reheating steam outlet of the boiler 1 and the intermediate pressure cylinder 22, a high-pressure heater stop valve 451 is installed on a steam inlet pipeline of the high-pressure heater 45, a deaerator stop valve 431 is installed on a steam inlet pipeline of the deaerator 43, a low-pressure heater stop valve 421 is installed on a steam inlet pipeline of the low-pressure heater 42, a high-pressure bypass valve 11 is installed on a pipeline between the main steam outlet of the boiler 1 and the reheating steam inlet of the boiler 1, and one-way valves are arranged on an outlet pipeline of the bypass back-pressing machine 5 and an outlet pipeline of the high-pressure cylinder 21.
And (3) heating period: as shown in fig. 1, unbalanced steam of the boiler 1 and the steam turbine enters the drain flash tank 7 after being subjected to temperature and pressure reduction by using a pipeline where the high-pressure bypass valve 11 of the original reheating unit 2 is located and a pipeline where the low-pressure bypass valve 71 of the reheating unit is located, and the high-pressure main steam regulating valve 211 and the reheating combined steam valve 221 of the original reheating unit 2 are closed. After the warming cylinder of the bypass back press 5 group is finished, the high-pressure main steam regulating valve 211 of the bypass back press 5 group is gradually opened, the evacuation valve 81 of the bypass back press is opened, the high-pressure bypass valve 11 and the low-pressure bypass valve are gradually closed, when the exhaust steam pressure of the bypass back press 5 approaches the heating pressure, the evacuation valve 81 of the bypass back press is gradually closed, the stop valve 82 of the bypass back press is opened, and the secondary temperature-reducing and pressure-reducing valve 83 of the bypass back press and the tertiary temperature-reducing and pressure-reducing valve 84 of the bypass back press start heating. The heating backwater C enters the deaerator 43, passes through the high-pressure heater 45 and then enters the boiler 1 to form a closed loop.
In the non-heating period: as shown in fig. 2, the bypass back-pressure machine main steam regulating valve 51, the bypass back-pressure machine evacuation valve 81, the bypass back-pressure machine shutoff valve 82, the bypass back-pressure machine secondary temperature and pressure reducing valve 83, and the bypass back-pressure machine tertiary temperature and pressure reducing valve 84 are closed. The steam operates according to the normal starting mode of the original reheating unit 2.
The invention is not limited to the above alternative embodiments, and any other various forms of products can be obtained by anyone in the light of the present invention, but any changes in shape or structure thereof, which fall within the scope of the present invention as defined in the claims, fall within the scope of the present invention.
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| CN115853608A (en) * | 2022-12-12 | 2023-03-28 | 东方电气集团东方汽轮机有限公司 | Steam turbine middle-connection door parameter adjusting heat supply system and method for improving steam flow of steam turbine middle-connection door parameter adjusting heat supply system |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| AU4297078A (en) * | 1978-02-10 | 1979-08-16 | Monash University | Power generation system |
| RU2299376C1 (en) * | 2005-12-23 | 2007-05-20 | Государственное образовательное учреждение высшего профессионального образования "Ульяновский государственный технический университет" | Method of operation of boiler |
| US20110259014A1 (en) * | 2010-04-23 | 2011-10-27 | General Electric Company | Refinery residuals processing for integrated power, water, and chemical products |
| JP5558310B2 (en) * | 2010-10-22 | 2014-07-23 | 株式会社東芝 | Carbon dioxide recovery method and carbon dioxide recovery steam power generation system |
| CN103628937B (en) * | 2013-11-29 | 2015-06-24 | 东方电气集团东方汽轮机有限公司 | Methods of Improving Utilization of Remaining Steam in Steam Turbine Units |
| CN104791875B (en) * | 2014-04-14 | 2016-03-30 | 中北大学 | A Combined Heat and Power System for Calculating Heat Loss |
| EP2942496B1 (en) * | 2014-05-08 | 2018-10-10 | General Electric Technology GmbH | Oxy boiler power plant with a heat integrated air separation unit |
| CN204786684U (en) * | 2015-06-26 | 2015-11-18 | 中国能源建设集团广东省电力设计研究院有限公司 | Wide load of little steam turbine of backpressure formula drive water -feeding pump supplies heat energy -saving system |
| CN104976671B (en) * | 2015-06-26 | 2021-07-23 | 中国能源建设集团广东省电力设计研究院有限公司 | Wide-load heat supply energy-saving system of back pressure type small steam turbine driven water feeding pump |
| CN105464719A (en) * | 2015-11-27 | 2016-04-06 | 东方电气集团东方汽轮机有限公司 | Heating steam extraction steam turbine unit |
| CN206144613U (en) * | 2016-09-05 | 2017-05-03 | 华能国际电力股份有限公司 | A thermoelectric decoupling heating system that extracts steam from power plant boilers |
| CN206267893U (en) * | 2016-11-07 | 2017-06-20 | 上海电气电站设备有限公司 | Cogeneration turbine |
| CN106968733A (en) * | 2017-04-27 | 2017-07-21 | 江阴市尚时环境工程有限公司 | Power plant's superhigh-pressure high-temp reheating embrittlement |
| CN109855147B (en) * | 2019-02-02 | 2023-04-28 | 华电电力科学研究院有限公司 | Combined cycle device based on heat supply and power peak regulation coupling and operation method thereof |
| CN110953571A (en) * | 2019-10-16 | 2020-04-03 | 孙少强 | Heat supply steam residual pressure cascade utilization system applied to coal-fired heat supply unit |
| CN212154886U (en) * | 2020-03-31 | 2020-12-15 | 华能国际电力股份有限公司德州电厂 | A Cascade Utilization System of Industrial Steam Residual Pressure Applied in the Mode of Shutdown of Coal-fired Steam Supply Unit |
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