CN110836365A - Waste heat utilization system and method for circulating fluidized bed boiler of thermal power plant - Google Patents
Waste heat utilization system and method for circulating fluidized bed boiler of thermal power plant Download PDFInfo
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- CN110836365A CN110836365A CN201911267822.5A CN201911267822A CN110836365A CN 110836365 A CN110836365 A CN 110836365A CN 201911267822 A CN201911267822 A CN 201911267822A CN 110836365 A CN110836365 A CN 110836365A
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- 239000002918 waste heat Substances 0.000 title claims abstract description 24
- 238000000034 method Methods 0.000 title claims abstract description 15
- 239000002893 slag Substances 0.000 claims abstract description 94
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 67
- 230000001105 regulatory effect Effects 0.000 claims abstract description 46
- 238000000605 extraction Methods 0.000 claims description 12
- UGFAIRIUMAVXCW-UHFFFAOYSA-N Carbon monoxide Chemical compound [O+]#[C-] UGFAIRIUMAVXCW-UHFFFAOYSA-N 0.000 claims description 10
- 239000003546 flue gas Substances 0.000 claims description 10
- 238000005259 measurement Methods 0.000 claims description 10
- 230000001172 regenerating effect Effects 0.000 claims description 6
- 239000000779 smoke Substances 0.000 abstract description 6
- 238000007599 discharging Methods 0.000 abstract description 4
- 239000000446 fuel Substances 0.000 abstract description 4
- 239000011148 porous material Substances 0.000 description 8
- 238000010521 absorption reaction Methods 0.000 description 2
- 239000010884 boiler slag Substances 0.000 description 2
- 238000006477 desulfuration reaction Methods 0.000 description 2
- 230000023556 desulfurization Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 239000000428 dust Substances 0.000 description 2
- 238000004134 energy conservation Methods 0.000 description 2
- 238000004880 explosion Methods 0.000 description 2
- 239000007789 gas Substances 0.000 description 2
- 238000010438 heat treatment Methods 0.000 description 2
- 239000002956 ash Substances 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 239000003245 coal Substances 0.000 description 1
- 238000002485 combustion reaction Methods 0.000 description 1
- 238000012544 monitoring process Methods 0.000 description 1
- 238000010992 reflux Methods 0.000 description 1
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23C—METHODS OR APPARATUS FOR COMBUSTION USING FLUID FUEL OR SOLID FUEL SUSPENDED IN A CARRIER GAS OR AIR
- F23C10/00—Fluidised bed combustion apparatus
- F23C10/18—Details; Accessories
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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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23C—METHODS OR APPARATUS FOR COMBUSTION USING FLUID FUEL OR SOLID FUEL SUSPENDED IN A CARRIER GAS OR AIR
- F23C10/00—Fluidised bed combustion apparatus
- F23C10/18—Details; Accessories
- F23C10/24—Devices for removal of material from the bed
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23J—REMOVAL OR TREATMENT OF COMBUSTION PRODUCTS OR COMBUSTION RESIDUES; FLUES
- F23J15/00—Arrangements of devices for treating smoke or fumes
- F23J15/06—Arrangements of devices for treating smoke or fumes of coolers
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- 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
- Y02E20/30—Technologies for a more efficient combustion or heat usage
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Fluidized-Bed Combustion And Resonant Combustion (AREA)
- Engine Equipment That Uses Special Cycles (AREA)
Abstract
The invention discloses a waste heat utilization system and a waste heat utilization method for a circulating fluidized bed boiler of a thermal power plant, wherein the waste heat utilization system comprises a slag cooler, a low-temperature economizer, a shaft seal heater, a first low-pressure heater and a second low-pressure heater; the water side outlet of the shaft seal heater is respectively communicated with the water side inlet of the slag cooler and the water side inlet of the low-temperature economizer; a first regulating valve group is arranged on a pipeline between the shaft seal heater and the slag cooler, a second regulating valve group and a first low-pressure heater are sequentially arranged from an outlet of the first regulating valve group to a pipeline of the low-temperature economizer, and electric gate valves are arranged at a water side inlet and an outlet of the first low-pressure heater; the water side outlets of the slag cooler and the low-temperature economizer are both connected with a second low-pressure heater; one branch of condensed water at the outlet of the shaft seal heater enters the slag cooler to heat and recover the slag discharging heat of the boiler, and the other branch of condensed water passes through the first low-pressure heater and the low-temperature economizer to heat and recover the smoke discharging heat of the boiler, so that the utilization rate of the fuel heat of the boiler and the heat economy of a thermal power plant can be improved.
Description
Technical Field
The invention relates to an ash residue system of a circulating fluidized bed boiler, in particular to a waste heat utilization system and method of a circulating fluidized bed boiler of a thermal power plant.
Background
According to the analysis of a calorimetric method, only 35-42% of the fuel combustion heat quantity of a thermal power plant is converted into electric energy, the deslagging temperature of a circulating fluidized bed boiler is usually 850-950 ℃, the exhaust gas temperature is usually 130-150 ℃, and the heat loss of exhaust gas and deslagging is two maximum heat losses in various heat losses of the boiler, which is equivalent to 5-12% of the fuel heat quantity. If the heat discharged by the two parts can be efficiently recycled, the method makes a great contribution to energy conservation and emission reduction of the thermal power plant.
Disclosure of Invention
The invention aims to solve the problems and provides a system and a method for utilizing residual heat of discharged slag and discharged smoke of a circulating fluidized bed boiler of a thermal power plant, which adopt the following two modes to operate in parallel: 1) a boiler slag cooler is adopted to heat condensed water, and the heat of boiler slag discharge is recovered to a turbine thermodynamic system; 2) the low-temperature economizer is adopted to heat the condensed water, and the heat of the exhaust smoke of the boiler is recovered to a turbine thermodynamic system, so that the heat efficiency of the thermal power plant unit is improved.
In order to achieve the purpose, the invention adopts the technical scheme that: a waste heat utilization system of a circulating fluidized bed boiler of a thermal power plant comprises a slag cooler, a low-temperature economizer, a shaft seal heater, a first low-pressure heater and a second low-pressure heater;
the water side outlet of the shaft seal heater is respectively communicated with the water side inlet of the slag cooler and the water side inlet of the low-temperature economizer; a first regulating valve group is arranged on a pipeline between the shaft seal heater and the slag cooler, a second regulating valve group and a first low-pressure heater are sequentially arranged from an outlet of the first regulating valve group to a pipeline of the low-temperature economizer, and electric gate valves are arranged at a water side inlet and an outlet of the first low-pressure heater; a plurality of groups of slag coolers are connected in parallel, and the water side outlets of the slag coolers and the low-temperature economizer are connected with a second low-pressure heater;
the first low-pressure heater is the low-pressure heater with the lowest steam extraction parameter of the turbine regenerative system, and the steam extraction parameter of the second low-pressure heater is higher than the first heater by one grade.
First regulating valve group includes first manual gate valve, first pneumatic control valve, the manual gate valve of second and first electric gate valve, and first manual gate valve, first pneumatic control valve and the manual gate valve of second connect gradually, and the entry and the manual gate valve exit linkage first bypass pipeline of first manual gate valve, first electric gate valve set up on first bypass pipeline.
And a first flow measurement pore plate is arranged on a pipeline from the outlet of the first regulating valve group to the slag cooler.
And a second flow measuring pore plate and a second electric gate valve are arranged on a pipeline between the first flow measuring pore plate and the inlet of the slag cooler, and a third electric gate valve is arranged on an outlet pipeline of the slag cooler.
And a safety valve is also arranged between the inlet of the slag cooler and the second electric gate valve.
The second regulating valve group comprises a third manual gate valve, a second pneumatic regulating valve, a fourth manual gate valve and a fourth electric gate valve, the third manual gate valve, the second pneumatic regulating valve and the fourth manual gate valve are sequentially connected, an inlet of the second manual gate valve and an outlet of the fourth manual gate valve are connected with a second bypass pipeline, and the fourth electric gate valve is arranged on the second bypass pipeline.
And a seventh electric gate valve is arranged between the low-temperature economizer and the second low-pressure heater.
A waste heat utilization method of a circulating fluidized bed boiler of a thermal power plant comprises the following steps:
the slag cooler and the low-temperature economizer are connected in parallel for operation;
condensed water at the outlet of the shaft seal heater passes through the slag cooler and the first low-pressure heater respectively, and the condensed water heated by the first low-pressure heater enters the low-temperature economizer to be heated and then is mixed with the condensed water heated by the slag cooler to enter the second low-pressure heater;
the first low-pressure heater is the low-pressure heater with the lowest steam extraction parameter of the turbine regenerative system, and the steam extraction parameter of the second low-pressure heater is higher than that of the first low-pressure heater by one grade.
The slag inlet temperature of the slag cooler is 900 +/-50 ℃, the slag outlet temperature is 150 +/-5 ℃, and the condensed water at 47-68 ℃ of the shaft seal heater outlet is heated to 90 +/-5 ℃ by the slag cooler.
The temperature of inlet flue gas of the low-temperature economizer is 130-150 ℃, the temperature of outlet flue gas is 95-115 ℃, condensed water at the outlet of the shaft seal heater, which is 47-68 ℃, is heated to 82-85 ℃ through the first low-pressure heater and then heated to 90 +/-5 ℃ through the low-temperature economizer.
Compared with the prior art, the invention has at least the following beneficial effects: a first regulating valve group is arranged on a water side outlet pipeline of the shaft seal heater, so that the flow of condensed water can be regulated, and a first waste heat utilization branch is formed from an outlet of the first regulating valve group to the slag cooler; the outlet of the first regulating valve group is connected with the second regulating valve group, then connected with the first low-pressure heater and finally connected with the low-temperature economizer to form a second waste heat utilization branch, the condensed water is subjected to primary heating by the first low-pressure heater and then enters the low-temperature economizer for heating, the condensed water is mixed with the water discharged from the slag cooler after being discharged from the low-temperature economizer and then enters the second low-pressure heater, and the two branches are connected in parallel and operate to heat the condensed water at the same time. By adopting the system, one branch of condensed water at the outlet of the shaft seal heater enters the slag cooler to heat and recover the slag discharging heat of the boiler, and the other branch of condensed water passes through the first low-pressure heater and then passes through the low-temperature economizer to heat and recover the smoke discharging heat of the boiler, so that the utilization rate of the fuel heat of the boiler and the heat economy of the thermal power plant are improved, and great contribution is made to energy conservation and emission reduction of the thermal power plant.
Furthermore, set up pneumatic control valve in the first regulating valve group, can conveniently adjust medium flow to set up manual gate valve respectively at pneumatic control valve's both ends, can be used for maintaining pneumatic control valve and prevent the reflux, the both ends of first regulating valve group set up the second passageway that bypass pipeline can regard as the export of bearing seal heater to realize the medium transport.
Furthermore, a first flow measuring orifice plate is arranged on a pipeline from an outlet of the first regulating valve group to the slag cooler, so that the total flow of the condensed water flowing to the slag cooler can be monitored in real time.
Furthermore, a second flow measurement pore plate and a second electric gate valve are arranged on a pipeline between the first flow measurement pore plate and the inlet of the slag cooler, the second flow measurement pore plate can be used for monitoring the water flow entering each slag cooler, the second electric gate valve can close the water flow entering the fault slag cooler at any time, and the third electric gate valve can prevent backflow.
Furthermore, a safety valve is arranged between the inlet of the slag cooler and the second electric gate valve, when a single slag cooler breaks down, the second electric gate valve and the third electric gate valve at the inlet and the outlet of the slag cooler are closed, condensed water in the pipe side of the slag cooler absorbs heat and evaporates, and the safety valve is opened and bounced after the pressure exceeds a set value of the safety valve, so that pipe explosion of the slag cooler is prevented.
By adopting the method, the slag cooler and the low-temperature economizer are connected in parallel to operate to heat the condensed water, one branch of the condensed water at the outlet of the shaft seal heater enters the slag cooler to heat and recover the heat of discharged slag of the boiler, the other branch passes through the first low-pressure heater and then the low-temperature economizer to heat and recover the heat of discharged smoke of the boiler, and the slag cooler and the low-temperature economizer are connected in parallel to operate; the condensed water at the outlet of the shaft seal heater respectively passes through the slag cooler and the first low-pressure heater, the condensed water heated by the first low-pressure heater enters the low-temperature economizer to be heated, then is mixed with the condensed water heated by the slag cooler and enters the second low-pressure heater, the total flow of the water in the system and the flow of the two pipelines can be respectively adjusted, the water flow entering the two branches is controlled, and simultaneously, the slag discharge and smoke discharge heat of the boiler is recovered to a turbine thermodynamic system, so that the heat efficiency of a thermal power plant unit is improved.
Drawings
FIG. 1 is a schematic diagram of a system and method for utilizing waste heat of a circulating fluidized bed boiler according to the present invention;
FIG. 2 is a schematic diagram of a system and method for utilizing waste heat of a circulating fluidized bed boiler according to the present invention;
in the drawings, 1-shaft seal heater; 2-first manual gate valve; 3-a first pneumatic regulating valve; 4-a second manual gate valve; 5-a first electric gate valve; 6-a first flow measurement orifice plate; 7-a second flow measurement orifice plate; 8-a second electric gate valve; 9-safety valve; 10-a slag cooler; 11-a third electric gate valve; 12-a third manual gate valve; 13-a second pneumatic regulating valve; 14-a fourth manual gate valve; 15-a fourth electric gate valve; 16-a fifth electric gate valve; 17-a first low pressure heater; 18-a sixth electric gate valve; 19-a low-temperature economizer; 20-seventh electric gate valve; 21-a second low pressure heater; 22-a boiler; 23-an air preheater; 24-a dust remover; 25-a draught fan; 26-a desulfurization absorption tower; 27-chimney.
Detailed Description
The present invention will be described in further detail with reference to the accompanying drawings.
A waste heat utilization system of a circulating fluidized bed boiler of a thermal power plant comprises a slag cooler 10, a low-temperature economizer 19, a shaft seal heater 1, a first low-pressure heater and a second low-pressure heater; wherein, the water side outlet of the shaft seal heater 1 is respectively communicated with the water side inlet of the slag cooler 10 and the water side inlet of the low-temperature economizer 19; the pipeline between the shaft seal heater 1 and the slag cooler 10 is provided with a first regulating valve group, the outlet of the first regulating valve group is sequentially provided with a second regulating valve group and a first low-pressure heater on the pipeline from the low-temperature economizer 19, the inlet and the outlet of the water side of the first low-pressure heater are respectively provided with a fifth electric gate valve 16 and a sixth electric gate valve 18, the multiple groups of slag coolers 10 are connected in parallel, and the outlets of the slag coolers 10 and the low-temperature economizer 19 are connected with the second low-pressure heater.
First regulating valve group includes first manual gate valve 2, first pneumatic control valve 3, the manual gate valve 4 of second and first electric gate valve 5, and first manual gate valve 2, first pneumatic control valve 3 and the manual gate valve 4 of second connect gradually, and first bypass pipeline is connected to the entry of first manual gate valve 2 and the manual gate valve 4 exit linkage of second, and first electric gate valve 5 sets up on first bypass pipeline.
A first flow measurement orifice plate 6 is arranged on a pipeline from an outlet of the first regulating valve group to the slag cooler 10.
A second flow measuring pore plate 7 and a second electric gate valve 8 are arranged on a pipeline between the first flow measuring pore plate 6 and the inlet of the slag cooler 10, and a third electric gate valve 11 is arranged on an outlet pipeline of the slag cooler 10.
The second regulating valve group comprises a third manual gate valve 12, a second pneumatic regulating valve 13, a fourth manual gate valve 14 and a fourth electric gate valve 15, the third manual gate valve 12, the second pneumatic regulating valve 13 and the fourth manual gate valve 14 are sequentially connected, an inlet of the third manual gate valve 12 and an outlet of the fourth manual gate valve 14 are connected with a second bypass pipeline, and the fourth electric gate valve 15 is arranged on the second bypass pipeline.
A seventh electric gate valve 20 is provided between the low-temperature economizer and the second low-pressure heater.
The waste heat utilization method of the circulating fluidized bed boiler of the thermal power plant, the slag cooler 10 and low-temperature coal economizer 19 run in parallel;
condensed water at the outlet of the shaft seal heater 1 passes through the slag cooler 10 and the first low-pressure heater respectively, and the condensed water heated by the first low-pressure heater enters the low-temperature economizer 19 to be heated and then is mixed with the condensed water heated by the slag cooler 10 to enter the second low-pressure heater;
the first low-pressure heater is the low-pressure heater with the lowest steam extraction parameter of the turbine regenerative system, and the steam extraction parameter of the second low-pressure heater is higher than the first low-pressure heater by one grade;
the slag inlet temperature of the slag cooler 10 is 900 +/-50 ℃, the slag outlet temperature is 150 +/-5 ℃, and the condensed water at 47-68 ℃ of the outlet of the shaft seal heater 1 is heated to 90 +/-5 ℃ by the slag cooler 10.
The temperature of the inlet flue gas of the low-temperature economizer 19 is 130-150 ℃, the temperature of the outlet flue gas is 95-115 ℃, and the condensed water at the outlet of the shaft seal heater 1 at 47-68 ℃ is heated to 82-85 ℃ through the first low-pressure heater 17 and then heated to 90 +/-5 ℃ through the low-temperature economizer 19.
The system provided by the invention aims at a 300 MW-level unit, a steam turbine regenerative system of the system is provided with seven levels of heaters, and the seven levels of heaters comprise a three-level high-pressure heater, a one-level deaerator and a three-level low-pressure heater, wherein the first low-pressure heater is a No. 7 low-pressure heater 17 and is a low-pressure heater with the lowest steam extraction parameter, the second low-pressure heater is a No. 6 low-pressure heater 21, and the steam extraction parameter is one level higher than that of the No. 7 low-pressure heater.
Condensed water at the outlet of the shaft seal heater 1 passes through the slag cooler 10 and the No. 7 low-pressure heater 17 respectively, and the condensed water heated by the No. 7 low-pressure heater 17 enters the low-temperature economizer 19 to be heated and then is mixed with the condensed water heated by the slag cooler 10 to enter the No. 6 low-pressure heater 21.
Referring to fig. 1, the waste heat utilization system of the circulating fluidized bed boiler of the present invention comprises a slag cooler arranged at the lower part of the boiler and a low temperature economizer arranged at the outlet of a draught fan at the rear part of the boiler, wherein the slag cooler and the low temperature economizer are operated in parallel;
the slag cooler 10 arranged at the lower part of the boiler has the slag inlet temperature of 900 +/-50 ℃, the slag outlet temperature of 150 +/-5 ℃, the condensed water at 47-68 ℃ at the outlet of the shaft seal heater 1 passes through a first regulating valve group consisting of a first manual gate valve 2, a first pneumatic regulating valve 3, a second manual gate valve 4 and a first electric gate valve 5, a first flow measuring orifice plate 6, a plurality of slag coolers 10 running in parallel, a second flow measuring orifice plate 7, a second electric gate valve 8 and a safety valve 9 are all arranged on an inlet pipeline of the slag coolers 10 along the medium flow direction, the condensed water enters the slag coolers 10 to exchange heat with slag, the absorbed heat temperature rises to 90 +/-5 ℃, the total output of the slag coolers 10 is designed to be 200%, when one of the slag coolers fails, the second electric gate valve 8 at the inlet and the third electric gate valve 11 at the outlet of the slag cooler are closed, the condensed water in the pipe side of the failed slag cooler absorbs heat and evaporates, the pressure exceeds the set value of the safety valve and jumps, preventing the slag cooler 10 from tube explosion.
The inlet flue gas temperature of the low-temperature economizer 19 is 130-150 ℃, the outlet flue gas temperature is 95-115 ℃, the low-temperature economizer 19 is arranged on the other branch of the condensed water at the outlet of the first regulating valve group, the condensed water is heated to 82-85 ℃ through a second regulating valve group, a fifth electric gate valve 16 and a No. 7 low-pressure heater 17 which are composed of a third manual gate valve 12, a second pneumatic regulating valve 13, a fourth manual gate valve 14 and a fourth electric gate valve 15, the heat is absorbed after the heat exchange between the heat and the flue gas in the low-temperature economizer through a sixth electric gate valve 18, the heat and the condensed water at the outlet of the third electric gate valve 11 are combined and enter a No. 6 low-pressure heater 21, and the amount of the condensed water entering the low-temperature economizer 19 is regulated by the second regulating valve group.
Referring to fig. 2, high temperature slag at 900 ± 50 ℃ generated during the operation of the circulating fluidized bed boiler 22 of the thermal power plant is discharged into the slag cooler 10; the flue gas at the tail part of the boiler is exhausted into the atmosphere through an air preheater 23, a dust remover 24, an induced draft fan 25, a low-temperature economizer 19, a desulfurization absorption tower 26 and a chimney 27.
The foregoing is only a preferred embodiment of the invention and is not intended to be limiting in any way, as it will be appreciated by those skilled in the art that changes may be made in this invention without departing from the principles and spirit of the invention, which is defined in the appended claims.
Claims (10)
1. The waste heat utilization system of the circulating fluidized bed boiler of the thermal power plant is characterized by comprising a slag cooler (10), a low-temperature economizer (19), a shaft seal heater (1), a first low-pressure heater and a second low-pressure heater;
a water side outlet of the shaft seal heater (1) is respectively communicated with a water side inlet of the slag cooler (10) and a water side inlet of the low-temperature economizer (19); a first regulating valve group is arranged on a pipeline between the shaft seal heater (1) and the slag cooler (10), a second regulating valve group and a first low-pressure heater are sequentially arranged on a pipeline from an outlet of the first regulating valve group to the low-temperature economizer (19), and an electric gate valve is arranged at an inlet and an outlet of the water side of the first low-pressure heater; a plurality of slag coolers (10) are connected in parallel, and water side outlets of the slag coolers (10) and the low-temperature economizer (19) are connected with a second low-pressure heater;
the first low-pressure heater is the low-pressure heater with the lowest steam extraction parameter of the turbine regenerative system, and the steam extraction parameter of the second low-pressure heater is higher than that of the first low-pressure heater by one grade.
2. The waste heat utilization system of the circulating fluidized bed boiler of the thermal power plant as claimed in claim 1, wherein the first regulating valve group comprises a first manual gate valve (2), a first pneumatic regulating valve (3), a second manual gate valve (4) and a first electric gate valve (5), the first manual gate valve (2), the first pneumatic regulating valve (3) and the second manual gate valve (4) are sequentially connected, an inlet of the first manual gate valve (2) and an outlet of the second manual gate valve (4) are connected with a first bypass pipeline, and the first electric gate valve (5) is arranged on the first bypass pipeline.
3. The waste heat utilization system of the circulating fluidized bed boiler of the thermal power plant as claimed in claim 1, characterized in that a first flow measurement orifice plate (6) is arranged on a pipeline from an outlet of the first regulating valve group to the slag cooler (10).
4. The waste heat utilization system of the circulating fluidized bed boiler of the thermal power plant as claimed in claim 3, characterized in that a second flow measurement orifice plate (7) and a second electric gate valve (8) are arranged on a pipeline between the first flow measurement orifice plate (6) and the inlet of the slag cooler (10), and a third electric gate valve (11) is arranged on an outlet pipeline of the slag cooler (10).
5. The waste heat utilization system of the circulating fluidized bed boiler of the thermal power plant as claimed in claim 1, characterized in that a safety valve (9) is further arranged between the inlet of the slag cooler (10) and the second electric gate valve (8).
6. The waste heat utilization system of the circulating fluidized bed boiler of the thermal power plant as claimed in claim 1, wherein the second regulating valve group comprises a third manual gate valve (12), a second pneumatic regulating valve (13), a fourth manual gate valve (14) and a fourth electric gate valve (15), the third manual gate valve (12), the second pneumatic regulating valve (13) and the fourth manual gate valve (14) are sequentially connected, an inlet of the second manual gate valve (12) and an outlet of the fourth manual gate valve (14) are connected with a second bypass pipeline, and the fourth electric gate valve (15) is arranged on the second bypass pipeline.
7. The waste heat utilization system of a circulating fluidized bed boiler of a thermal power plant according to claim 1, characterized in that a seventh electric gate valve (20) is provided between the low-temperature economizer (19) and the second low-pressure heater.
8. A method for utilizing the afterheat of the circulating fluidized-bed boiler in thermal power plant,
the slag cooler (10) and the low-temperature economizer (19) are connected in parallel for operation;
condensed water at the outlet of the shaft seal heater (1) passes through the slag cooler (10) and the first low-pressure heater respectively, and the condensed water heated by the first low-pressure heater enters the low-temperature economizer (19) to be heated and then is mixed with the condensed water heated by the slag cooler (10) to enter the second low-pressure heater;
the first low-pressure heater is the low-pressure heater with the lowest steam extraction parameter of the turbine regenerative system, and the steam extraction parameter of the second low-pressure heater is higher than that of the first low-pressure heater by one grade.
9. The method for utilizing the waste heat of the circulating fluidized bed boiler in the thermal power plant according to the claim 8, characterized in that the slag cooler (10) has the slag inlet temperature of 900 ± 50 ℃, the slag outlet temperature of 150 ± 5 ℃, and the condensed water at the outlet of the shaft seal heater (1) with the temperature of 47 ℃ to 68 ℃ is heated to 90 ± 5 ℃ through the slag cooler (10).
10. The method for utilizing the waste heat of the circulating fluidized bed boiler in the thermal power plant according to claim 8, wherein the temperature of the inlet flue gas of the low-temperature economizer (19) is 130-150 ℃, the temperature of the outlet flue gas is 95-115 ℃, and the condensed water at the outlet of the shaft seal heater (1) with the temperature of 47-68 ℃ is heated to 82-85 ℃ through the first low-pressure heater and then heated to 90 +/-5 ℃ through the low-temperature economizer (19).
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| CN201911267822.5A CN110836365A (en) | 2019-12-11 | 2019-12-11 | Waste heat utilization system and method for circulating fluidized bed boiler of thermal power plant |
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| CN201911267822.5A CN110836365A (en) | 2019-12-11 | 2019-12-11 | Waste heat utilization system and method for circulating fluidized bed boiler of thermal power plant |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112283584A (en) * | 2020-10-15 | 2021-01-29 | 中国能源建设集团广东省电力设计研究院有限公司 | Exchange system |
| CN114001348A (en) * | 2021-11-24 | 2022-02-01 | 三河发电有限责任公司 | Thermodynamic system |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN106895390A (en) * | 2017-04-19 | 2017-06-27 | 山东大学 | A kind of station boiler multi-element heterogeneous afterheat utilizing system |
| CN106989382A (en) * | 2017-05-24 | 2017-07-28 | 中国能源建设集团湖南省电力设计院有限公司 | A kind of thermal power plant Slag Cooler for Circulation Fluidized Bed Boiler cooling water system |
| CN108826269A (en) * | 2018-07-23 | 2018-11-16 | 中国能源建设集团山西省电力勘测设计院有限公司 | The utilization system of fume afterheat and deslagging waste heat based on CFB boiler |
| CN211290024U (en) * | 2019-12-11 | 2020-08-18 | 中国电力工程顾问集团西北电力设计院有限公司 | Waste heat utilization system of circulating fluidized bed boiler of thermal power plant |
-
2019
- 2019-12-11 CN CN201911267822.5A patent/CN110836365A/en active Pending
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106895390A (en) * | 2017-04-19 | 2017-06-27 | 山东大学 | A kind of station boiler multi-element heterogeneous afterheat utilizing system |
| CN106989382A (en) * | 2017-05-24 | 2017-07-28 | 中国能源建设集团湖南省电力设计院有限公司 | A kind of thermal power plant Slag Cooler for Circulation Fluidized Bed Boiler cooling water system |
| CN108826269A (en) * | 2018-07-23 | 2018-11-16 | 中国能源建设集团山西省电力勘测设计院有限公司 | The utilization system of fume afterheat and deslagging waste heat based on CFB boiler |
| CN211290024U (en) * | 2019-12-11 | 2020-08-18 | 中国电力工程顾问集团西北电力设计院有限公司 | Waste heat utilization system of circulating fluidized bed boiler of thermal power plant |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112283584A (en) * | 2020-10-15 | 2021-01-29 | 中国能源建设集团广东省电力设计研究院有限公司 | Exchange system |
| CN114001348A (en) * | 2021-11-24 | 2022-02-01 | 三河发电有限责任公司 | Thermodynamic system |
| CN114001348B (en) * | 2021-11-24 | 2023-08-25 | 三河发电有限责任公司 | Thermodynamic system |
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