CN105627283A - Steam system suitable for power station boiler with steam parameter of 700 ℃ grade and above - Google Patents
Steam system suitable for power station boiler with steam parameter of 700 ℃ grade and above Download PDFInfo
- Publication number
- CN105627283A CN105627283A CN201610037186.7A CN201610037186A CN105627283A CN 105627283 A CN105627283 A CN 105627283A CN 201610037186 A CN201610037186 A CN 201610037186A CN 105627283 A CN105627283 A CN 105627283A
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- superheater
- steam
- wall
- reheater
- low
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- UGFAIRIUMAVXCW-UHFFFAOYSA-N Carbon monoxide Chemical compound [O+]#[C-] UGFAIRIUMAVXCW-UHFFFAOYSA-N 0.000 claims abstract description 20
- 239000003546 flue gas Substances 0.000 claims abstract description 20
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 25
- 238000010521 absorption reaction Methods 0.000 abstract description 11
- 238000010438 heat treatment Methods 0.000 abstract description 6
- 238000009835 boiling Methods 0.000 abstract description 4
- 238000001816 cooling Methods 0.000 description 10
- 238000000034 method Methods 0.000 description 7
- 239000003245 coal Substances 0.000 description 4
- 230000006866 deterioration Effects 0.000 description 2
- 238000001704 evaporation Methods 0.000 description 2
- 230000008020 evaporation Effects 0.000 description 2
- 239000007789 gas Substances 0.000 description 2
- 239000000779 smoke Substances 0.000 description 2
- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical compound [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 description 1
- 229910052799 carbon Inorganic materials 0.000 description 1
- 238000002485 combustion reaction Methods 0.000 description 1
- 238000007796 conventional method Methods 0.000 description 1
- 230000005611 electricity Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 238000010248 power generation Methods 0.000 description 1
- 238000003303 reheating Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F22—STEAM GENERATION
- F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
- F22B31/00—Modifications of boiler construction, or of tube systems, dependent on installation of combustion apparatus; Arrangements of dispositions of combustion apparatus
- F22B31/08—Installation of heat-exchange apparatus or of means in boilers for heating air supplied for combustion
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Control Of Steam Boilers And Waste-Gas Boilers (AREA)
Abstract
The invention discloses a steam system suitable for a power station boiler with steam parameters of 700 ℃ grade and above, which comprises a hearth, a horizontal flue and a tail flue which are sequentially communicated along the flow direction of flue gas, wherein a spiral water-cooled wall, a wall type reheater and a screen type superheater are arranged in the hearth, a high-temperature superheater and a high-temperature reheater are arranged in the horizontal flue, and a low-temperature reheater, a low-temperature superheater and an economizer are arranged in the tail flue. The invention can effectively solve the problem that the boiler flue gas side heat release proportion and the steam side heat absorption proportion of the heating surface are difficult to match, and reduce the possibility of film-like boiling of working media in the water-cooled wall.
Description
Technical field
The invention belongs to field of thermal power, relate to a kind of suitable in the vapour system that steam parameter is 700 DEG C of grades and above station boiler.
Background technology
In recent years, becoming increasingly conspicuous of the environmental problem such as domestic haze, international community's censure to China's carbon emission in addition, promote the Chinese government carry out consumption of coal overall control and optimize coal occupation mode. The coal that China consumes every year there are about half for combustion power generation. For electricity power enterprise, only it is improved system cycle efficieny, when low coal consumption and low stain thing are discharged, the electric power of equivalent could be produced. Improving steam parameter is realize system cycle efficieny to improve one of most efficient method.
The steam parameter of state-of-the-art generating set has exceeded 600 DEG C in the world at present, and pressure has exceeded 30MPa, and system cycle efficieny is up to 44%. When vapor (steam) temperature brings up to 700 DEG C of levels, pressure reaches about 38MPa, and the cycle efficieny of system can bring up to about 50%. Being that for 26.15MPa/605 DEG C/603 DEG C level units, the heat absorption ratio of economizer is 8.4% for a 600MWe steam parameter, water-cooling wall heat absorption ratio is about 50%, and the heat absorption ratio of superheated steam and reheated steam is about 41.6%. When steam parameter brings up to 35MPa/702 DEG C/720 DEG C, the heat absorption ratio of economizer is 5.1%, and water-cooling wall heat absorption ratio is about 44.4%, and superheater and reheater heat absorption ratio are about 50.5%. Compared with 600 DEG C of level units, the water-cooling wall heat absorption ratio of 700 DEG C of level units reduces 5.6%, and the heat absorption ratio of superheater and reheater improves 8.9%.
If arranging heating surface by a conventional method, first, back-end ductwork needs to arrange the convection heating surface of superheater and reheater, owing in back-end ductwork, the thermal discharge of flue gas is certain and steam needs to absorb more heat to reach higher parameter, this may result in final steam parameter and is unable to reach design load or need to arrange that very big heating surface makes up the heat output reduced by heat transfer temperature difference and reduce; Secondly, assume that the steam parameter of outlet reaches 38.5MPa/702 DEG C/720 DEG C levels, so the temperature of the steam of water-cooling wall outlet must exceed the pseudo-critical temperature under this pressure, namely Temperature of Working be in big than heat rating time water screen tube section be positioned at inside the stronger burner hearth that is heated, possibly even it is in the strongest burner region that is heated, this may result in this section water-cooling wall generation class film boiling, causes heat transfer deterioration.
Summary of the invention
It is an object of the invention to the shortcoming overcoming above-mentioned prior art, provide a kind of suitable in the vapour system that steam parameter is 700 DEG C of grades and above station boiler, this system can effectively solve the problem that the boiler smoke of heating surface is sidelong the problem that ratio of specific heat example is difficult to mate with steam side heat absorption ratio, and reduces the probability of working medium generation class film boiling in water-cooling wall.
For reaching above-mentioned purpose, of the present invention include being sequentially connected logical burner hearth, horizontal flue and back-end ductwork along the direction of flow of flue gas suitable in the vapour system that steam parameter is 700 DEG C of grades and above station boiler, helical water-cooled wall, wall reheater and pendant superheater it is provided with in burner hearth, it is provided with high temperature superheater and high temperature reheater in horizontal flue, in back-end ductwork, is provided with low-temperature reheater, low temperature superheater and economizer;
Wall reheater is positioned on the outer wall of upper furnace, and pendant superheater is positioned at the direction that the top of burner hearth, high temperature superheater and high temperature reheater circulate along flue gas and is sequentially distributed;
Low-temperature reheater and low temperature superheater are positioned at the top of economizer, and the outer wall of back-end ductwork is coated with wall enclosed superheater, and the outlet of wall enclosed superheater is connected to steam-water separator.
Boiler feedwater is connected with the high pressure cylinder of steam turbine through economizer, helical water-cooled wall, low temperature superheater, wall enclosed superheater, steam-water separator, pendant superheater and high temperature superheater successively, and reheated steam is connected with the intermediate pressure cylinder of steam turbine through low-temperature reheater, wall reheater and high temperature reheater successively.
The top of back-end ductwork is divided into front flue and rear pass by dividing wall, and wherein, low-temperature reheater is arranged in front flue, and low temperature superheater is arranged in rear pass, and economizer is positioned at the bottom of dividing wall.
Also including water tank, the outlet of steam-water separator is connected with the water inlet of water tank.
In wall enclosed superheater, the flow direction of working medium is contrary with the flow direction of flue gas in back-end ductwork.
The method have the advantages that
Of the present invention is helical water-cooled wall for lower furnace portion in vapour system that steam parameter is 700 DEG C of grades and above station boiler, can effectively reduce furnace side flue gas and be released to the heat of water-cooling wall, thus effectively solving the boiler smoke of heating surface under 700 DEG C of grades and above steam parameter to be sidelong the problem that ratio of specific heat example is difficult to mate with steam side heat absorption ratio, reduce the probability of working medium generation class film boiling in water-cooling wall. The working medium of helical water-cooled wall output enters and is arranged in the low temperature superheater of back-end ductwork, make the Temperature of Working that helical water-cooled wall export be in greatly than heat rating time avoid being heated inside stronger burner hearth. Additionally, the wall reheater being arranged in upper furnace can not only be effectively improved the caloric receptivity of reheated steam, but also the flue gas convection heat transfer' heat-transfer by convection amount to reheated steam can be reduced, thus improve the flue gas convection heat transfer' heat-transfer by convection amount to superheated steam, it is ensured that final superheated steam and reheated steam reach design load. The main endothermic process of reheated steam completes in wall reheater, the heat that in back-end ductwork, flue gas is released to reheated steam by the mode of heat convection is less, thus ensure that low-temperature reheater, low temperature superheater and low-level (stack-gas) economizer have bigger heat transfer temperature difference in heat transfer process, it is thus possible to reduce the heat transfer area of heat exchanger.
Accompanying drawing explanation
Fig. 1 is the structural representation of the present invention.
Wherein, 1 be helical water-cooled wall, 2 be water tank, 3 be pendant superheater, 4 be high temperature superheater, 5 be steam-water separator, 6 be wall reheater, 7 be high temperature reheater, 8 be wall enclosed superheater, 9 be low-temperature reheater, 10 be low temperature superheater, 11 for economizer.
Detailed description of the invention
Below in conjunction with accompanying drawing, the present invention is described in further detail:
With reference to Fig. 1, of the present invention include being sequentially connected logical burner hearth, horizontal flue and back-end ductwork along the direction of flow of flue gas suitable in the vapour system that steam parameter is 700 DEG C of grades and above station boiler, helical water-cooled wall 1, wall reheater 6 and pendant superheater 3 it is provided with in burner hearth, it is provided with high temperature superheater 4 and high temperature reheater 7 in horizontal flue, in back-end ductwork, is provided with low-temperature reheater 9, low temperature superheater 10 and economizer 11; Wall reheater 6 is located on the outer wall of upper furnace, and pendant superheater 3 is positioned at the direction that the top of burner hearth, high temperature superheater 4 and high temperature reheater 7 circulate along flue gas and is sequentially distributed; Low-temperature reheater 9 and low temperature superheater 10 are positioned at the top of economizer 11, and the outer wall of back-end ductwork is coated with wall enclosed superheater 8, and the outlet of wall enclosed superheater 8 is connected to steam-water separator 5; Boiler feedwater is connected with the high pressure cylinder of steam turbine through economizer 11, helical water-cooled wall 1, low temperature superheater 10, wall enclosed superheater 8, steam-water separator 5, pendant superheater 3 and high temperature superheater 4 successively, and reheated steam is connected with Steam Turbine Through IP Admission through low-temperature reheater 9, wall reheater 6 and high temperature reheater 7 successively.
It should be noted that the top of back-end ductwork is divided into front flue and rear pass by dividing wall, wherein, low-temperature reheater 9 is arranged in front flue, and low temperature superheater 10 is arranged in rear pass, and economizer 11 is positioned at the bottom of dividing wall. Present invention additionally comprises water tank 2, the outlet of steam-water separator 5 is connected with the water inlet of water tank 2; In wall enclosed superheater 8, the flow direction of working medium is contrary with the flow direction of flue gas in back-end ductwork.
The specific works process of the present invention is as follows:
Flue gas is discharged through burner hearth, horizontal flue and back-end ductwork successively, boiler feedwater forms main steam through economizer 11, helical water-cooled wall 1, low temperature superheater 10, wall enclosed superheater 8, steam-water separator 5, pendant superheater 3 and high temperature superheater 4 successively, and enter in the high pressure cylinder of steam turbine, in start-up course, the water that steam-water separator 5 is separated enters in water tank 2; Reheated steam enters in the intermediate pressure cylinder of steam turbine successively after low-temperature reheater 9, wall reheater 6 and high temperature reheater 7 reheating.
The design principle of the present invention is as follows:
In lower furnace portion, the present invention only arranges that water-cooling wall is the evaporation endothermic amount in order to reduce working medium, the evaporation endothermic amount ratio that when bringing up to 700 DEG C with steam parameter and be above, working medium is less matches, the temperature of the working medium exported by helical water-cooled wall controls below the pseudo-critical temperature under relevant pressure, and the working medium of helical water-cooled wall output is introduced the low temperature superheater 10 being positioned at back-end ductwork, the Temperature of Working that its purpose is to make helical water-cooled wall export be in big than heat rating time avoid being heated inside stronger burner hearth, thus reducing the probability of water-cooling wall heat transfer deterioration. Arrange that wall reheater 6 can be effectively improved the caloric receptivity of reheated steam in upper furnace, but also the flue gas convection heat transfer' heat-transfer by convection amount to reheated steam can be reduced, thus improving the flue gas convection heat transfer' heat-transfer by convection amount to superheated steam, it is ensured that final superheated steam and reheated steam reach design load. The main endothermic process of reheated steam completes in wall reheater 6, the heat that in back-end ductwork, flue gas is released to reheated steam by the mode of heat convection is less, thus ensure that low-temperature reheater 9, low temperature superheater 10 and low-level (stack-gas) economizer 1 have bigger heat transfer temperature difference in heat transfer process, it is thus possible to reduce the heat transfer area of heat exchanger.
Claims (4)
1. one kind is applicable to the vapour system that steam parameter is 700 DEG C of grades and above station boiler, it is characterized in that, it is sequentially connected logical burner hearth, horizontal flue and back-end ductwork including the direction along flow of flue gas, helical water-cooled wall (1), wall reheater (6) and pendant superheater (3) it is provided with in burner hearth, it is provided with high temperature superheater (4) and high temperature reheater (7) in horizontal flue, in back-end ductwork, is provided with low-temperature reheater (9), low temperature superheater (10) and economizer (11);
Wall reheater (6) is positioned on the outer wall of upper furnace, and pendant superheater (3) is positioned at the direction that the top of burner hearth, high temperature superheater (4) and high temperature reheater (7) circulate along flue gas and is sequentially distributed;
Low-temperature reheater (9) and low temperature superheater (10) are positioned at the top of economizer (11), being coated with wall enclosed superheater (8) on the outer wall of back-end ductwork, the outlet of wall enclosed superheater (8) is connected to steam-water separator (5);
Boiler feedwater is connected with the high pressure cylinder of steam turbine through economizer (11), helical water-cooled wall (1), low temperature superheater (10), wall enclosed superheater (8), steam-water separator (5), pendant superheater (3) and high temperature superheater (4) successively, and reheated steam is connected with Steam Turbine Through IP Admission through low-temperature reheater (9), wall reheater (6) and high temperature reheater (7) successively.
2. according to claim 1 suitable in the vapour system that steam parameter is 700 DEG C of grades and above station boiler, it is characterized in that, the top of back-end ductwork is divided into front flue and rear pass by dividing wall, wherein, low-temperature reheater (9) is arranged in front flue, low temperature superheater (10) is arranged in rear pass, and economizer (11) is positioned at the bottom of dividing wall.
3. according to claim 1 suitable in the vapour system that steam parameter is 700 DEG C of grades and above station boiler, it is characterized in that, also including water tank (2), the outlet of steam-water separator (5) is connected with the water inlet of water tank (2).
4. according to claim 1 suitable in the vapour system that steam parameter is 700 DEG C of grades and above station boiler, it is characterised in that in wall enclosed superheater (8), the flow direction of working medium is contrary with the flow direction of flue gas in back-end ductwork.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610037186.7A CN105627283B (en) | 2016-01-20 | 2016-01-20 | Steam system suitable for power station boiler with steam parameter of 700 ℃ grade and above |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610037186.7A CN105627283B (en) | 2016-01-20 | 2016-01-20 | Steam system suitable for power station boiler with steam parameter of 700 ℃ grade and above |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105627283A true CN105627283A (en) | 2016-06-01 |
| CN105627283B CN105627283B (en) | 2017-12-05 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201610037186.7A Active CN105627283B (en) | 2016-01-20 | 2016-01-20 | Steam system suitable for power station boiler with steam parameter of 700 ℃ grade and above |
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| Country | Link |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106765013A (en) * | 2016-11-29 | 2017-05-31 | 北京巴布科克·威尔科克斯有限公司 | Ultra-high parameter ultra-supercritical boiler three-stage burner hearth |
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| JP2007107788A (en) * | 2005-10-12 | 2007-04-26 | Babcock Hitachi Kk | Installation method of boiler facility |
| CN203642147U (en) * | 2013-12-29 | 2014-06-11 | 哈尔滨锅炉厂有限责任公司 | Automatic 660 MW-class ultra-supercritical boiler |
| CN104061565A (en) * | 2014-06-30 | 2014-09-24 | 章礼道 | Zhundong coal-burning ultra-supercritical power station boiler |
| CN203869022U (en) * | 2014-05-30 | 2014-10-08 | 内蒙古瑞特科技有限公司 | Boiler system and temperature adjusting device thereof |
| CN104676573A (en) * | 2015-03-09 | 2015-06-03 | 章礼道 | 720-DEG C efficient ultra-supercritical secondary reheating power plant boiler |
| CN205316287U (en) * | 2016-01-20 | 2016-06-15 | 华能国际电力股份有限公司 | Steam system suitable for power station boiler with steam parameter of 700 ℃ grade and above |
-
2016
- 2016-01-20 CN CN201610037186.7A patent/CN105627283B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007107788A (en) * | 2005-10-12 | 2007-04-26 | Babcock Hitachi Kk | Installation method of boiler facility |
| CN203642147U (en) * | 2013-12-29 | 2014-06-11 | 哈尔滨锅炉厂有限责任公司 | Automatic 660 MW-class ultra-supercritical boiler |
| CN203869022U (en) * | 2014-05-30 | 2014-10-08 | 内蒙古瑞特科技有限公司 | Boiler system and temperature adjusting device thereof |
| CN104061565A (en) * | 2014-06-30 | 2014-09-24 | 章礼道 | Zhundong coal-burning ultra-supercritical power station boiler |
| CN104676573A (en) * | 2015-03-09 | 2015-06-03 | 章礼道 | 720-DEG C efficient ultra-supercritical secondary reheating power plant boiler |
| CN205316287U (en) * | 2016-01-20 | 2016-06-15 | 华能国际电力股份有限公司 | Steam system suitable for power station boiler with steam parameter of 700 ℃ grade and above |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106765013A (en) * | 2016-11-29 | 2017-05-31 | 北京巴布科克·威尔科克斯有限公司 | Ultra-high parameter ultra-supercritical boiler three-stage burner hearth |
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| Publication number | Publication date |
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| CN105627283B (en) | 2017-12-05 |
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