CN102486308A - Steam secondary reheating system - Google Patents
Steam secondary reheating system Download PDFInfo
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- CN102486308A CN102486308A CN2010105754859A CN201010575485A CN102486308A CN 102486308 A CN102486308 A CN 102486308A CN 2010105754859 A CN2010105754859 A CN 2010105754859A CN 201010575485 A CN201010575485 A CN 201010575485A CN 102486308 A CN102486308 A CN 102486308A
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Abstract
The invention provides a steam secondary heating system. The system comprises a steam turbine and a secondary reheater, wherein the steam turbine comprises a high-pressure cylinder, intermediate-pressure cylinders and a low-pressure cylinder which are connected in sequence; the secondary reheater is arranged on the exterior of a boiler, and is connected with the exhaust port of one intermediate-pressure cylinder of the steam turbine and the air inlet of the other intermediate-pressure cylinder or the low-pressure cylinder of the steam turbine; the secondary reheater produces high-temperature reheated steam, and introduces the high-temperature reheated steam into the other intermediate-pressure cylinder or the low-pressure cylinder. According to the steam secondary reheating system provided by the invention, the investment on the secondary reheating system is greatly reduced while the efficiency is improved, so that the steam secondary reheating system has the advantages of excellent investment income and technique economical efficiency.
Description
Technical field
The present invention relates to a kind of power equipment, relate in particular to a kind of secondary steam reheat system of novelty.
Background technology
In conventional thermal power plant, can adopt again heat to improve efficiency of thermal cycle.Wherein, heat is meant the steam of having done the part merit in the steam turbine drawn once more and heats again, draws the back-steam turbine then and continues acting.Hot again through reasonably, can reduce exhaust steam moisture, improve efficiency of thermal cycle.
Generally, hot again number of times efficiency of thermal cycle at most is high, but meanwhile cost is also high, so most of thermal power plant adopts boiler single reheat system, has only only a few thermal power plant to adopt boiler double reheat system.
The principal element that conventional boiler double reheat system cost is high is that the hot again pressure in flue gas-vapor heated second level is low, temperature is high, vapour density is little, volume flow is big; It is big that not only the hot again heating surface in the boiler second level is big, the steam turbine second level is pined for the through-flow volume of cylinder pressure again; The cost of equipment is high, and reheating pipe road, corresponding requirements second level specification is big, and the distance from the boiler to the steam turbine; The hot again pipeline back and forth in the second level is long between steam turbine and the boiler, the corresponding height of the cost of pipeline.In addition, pipeline is long back and forth, causes flow resistance big, has influenced efficiency of thermal cycle.These factors cause the investment return of conventional boiler double reheat system relatively poor, can't promote.
Summary of the invention
To the above-mentioned deficiency of prior art, inventor of the present invention has developed a kind of secondary steam reheat system of novel structure especially.The present invention is based on the thermodynamic cycle basic principle; To the high difficult problem of boiler double reheat system cost; Developed secondary steam reheat system of the present invention; Wherein the first order again heat be conventional boiler single reheat system, the hot more used reheater in the second level adopts carbonated drink-vapor heat exchanger, replaces boiler smoke-vapor heat exchanger.In addition, the present invention further adopts height, the intermediate pressure cylinder of the steam turbine heating second level reheated steam of drawing gas.
Particularly, the present invention proposes a kind of secondary steam reheat system, this system comprises:
Steam turbine, said steam turbine comprise high pressure cylinder, intermediate pressure cylinder and the low pressure (LP) cylinder that connects successively;
Secondary reheater is arranged at the boiler outside, and connect and connect with the steam drain of an intermediate pressure cylinder of said steam turbine with another intermediate pressure cylinder of said steam turbine or the air intake of low pressure (LP) cylinder,
Wherein, said secondary reheater produces high temperature reheated steam, and this high temperature reheated steam is introduced said another intermediate pressure cylinder or low pressure (LP) cylinder.
According to a preferred embodiment, in above-mentioned secondary steam reheat system, said secondary reheater adopts carbonated drink-vapor heated heat exchange mode.
According to a preferred embodiment, in above-mentioned secondary steam reheat system, said secondary reheater and high pressure cylinder, intermediate pressure cylinder or the two are connected wherein said high pressure cylinder, intermediate pressure cylinder or the two vapour source as said secondary reheater.
According to a preferred embodiment, in above-mentioned secondary steam reheat system, said secondary reheater draws gas from said high pressure cylinder, intermediate pressure cylinder or the two.
According to a preferred embodiment, in above-mentioned secondary steam reheat system, said high pressure cylinder, intermediate pressure cylinder or the two is to said secondary reheater steam discharge.
According to a preferred embodiment; In above-mentioned secondary steam reheat system; Said secondary reheater further with said secondary steam reheat system in one or more heaters be connected; The pressure of the heat regenerative system pressure of wherein said one or more heaters and the hydrophobic steam discharge after heat exchange of said secondary reheater is complementary (quite or low slightly), and wherein said secondary reheater enters said one or more heater with the hydrophobic steam discharge after heat exchange.
According to a preferred embodiment, in above-mentioned secondary steam reheat system, the high pressure cylinder of said steam turbine, intermediate pressure cylinder, low pressure (LP) cylinder be coaxial is with a generator.
According to a preferred embodiment, in above-mentioned secondary steam reheat system, the high pressure cylinder of said steam turbine, intermediate pressure cylinder, many generators of low pressure (LP) cylinder disalignment band.
Than prior art, secondary steam reheat system of the present invention has following advantage at least:
A. secondary steam reheat system of the present invention is high than the efficiency of thermal cycle of conventional boiler single reheat system;
B. compare with conventional boiler double reheat system, the carbonated drink of novel secondary steam reheat system-vapor heated second level reheater is positioned near the steam turbine, and reheating pipe road, the second level is short relatively a lot, and the pipeline flow resistance significantly reduces, and pipeline efficient is improved;
C. compare with conventional boiler double reheat system, carbonated drink-vapor heated second level reheater is positioned near the steam turbine, and reheating pipe road, the second level is short relatively a lot; And medium temperature is low; Low-temperature steel pipeline higher temperatures steel conduit unit price is low, and caliber is little, and pipeline cost significantly reduces;
D. the temperature of carbonated drink-vapor heated second level reheater is low, compares with the high-temperature boiler second level reheater of routine, and vapour density is big, and volume flow is little, and the heat transmission equipment cost of second level reheater is low;
E. the outlet reheat steam temperature of carbonated drink-vapor heated second level reheater is low, compares with the high-temperature boiler double reheat system steam turbine of routine, and second level reheat steam turbine equipment manufacturing cost is low;
F. the heating steam of carbonated drink-vapor heated second level reheater is drawn gas and steam discharge from steam turbine high-pressure cylinder, and the steam flow that gets into boiler single reheat device reduces, and the heat exchange area of boiler single reheat device reduces, and the cost of corresponding boiler single reheat device reduces.
To sum up;, conventional boiler double reheat system investment return poor problem low to conventional boiler single reheat system effectiveness; Secondary steam reheat system of the present invention significantly reduces the investment of double reheat system when raising the efficiency, have good investment return Technological Economy property.
Should be appreciated that the above generality of the present invention is described and following detailed description all is exemplary and illustrative, and be intended to further explanation is provided for as claimed in claim the present invention.
Description of drawings
Comprise that accompanying drawing is for providing the present invention further to be understood, they are included and are constituted the application's a part, and accompanying drawing shows embodiments of the invention, and play the effect of explaining the principle of the invention with this specification.In the accompanying drawing:
Fig. 1 schematically shows the conventional single reheat system of prior art.
Fig. 2 schematically shows the conventional double reheat system of prior art.
Fig. 3 shows the schematic structure according to an embodiment of secondary steam reheat system of the present invention.
Fig. 4-6 shows the schematic structure according to three preferred embodiments of the present invention.
The specific embodiment
Now with embodiments of the present invention will be described by referring to the drawings in detail.
Fig. 1 schematically shows the conventional single reheat system of prior art.Fig. 2 schematically shows the conventional double reheat system of prior art.The basic structure of reheat system illustrated in figures 1 and 2 and of the present invention similar, this partial content will be described in detail in following paragraph.
The main feature of shown in Figure 1 conventional single reheat system is: one-level boiler reheat machine 101 is only arranged.
The main feature of shown in Figure 2 conventional double reheat system is: (1) single reheat device 202 and secondary reheater 203 all are arranged at the inside of boiler 201.In addition, in double reheat system shown in Figure 2, this secondary reheater 203 is flue gas-vapor heat exchanger.As shown in Figure 2, this secondary reheater 203 joins through the double reheat pipeline with the steam discharge interface of the first order intermediate pressure cylinder 204 of steam turbine and the admission interface of second level intermediate pressure cylinder 205.Yet what from figure, can also see is that in the scheme of Fig. 2, because spacing is big between boiler and the steam turbine, so the double reheat pipeline must be longer.
In brief; The efficiency of thermal cycle of shown in Figure 1 conventional single reheat system is lower, and the efficient of shown in Figure 2 conventional double reheat system is higher, but the pressure of heat is low again, temperature is high, vapour density is little, volume flow is big in the second level; It is big that not only the hot again heating surface in the boiler second level is big, the steam turbine second level is pined for the through-flow volume of cylinder pressure again; The cost of equipment is high, and reheating pipe road, corresponding requirements second level specification is big, and the distance from the boiler to the steam turbine; The hot again pipeline back and forth in the second level is long between steam turbine and the boiler, the corresponding height of the cost of pipeline; Pipeline is long back and forth in addition, causes flow resistance big, has influenced efficiency of thermal cycle.Because boiler second level reheater, the steam turbine second level are pined for costs height such as cylinder pressure, reheating pipe road, the second level again, situation is more obvious in overcritical and above parameter unit, and this causes the investment return of conventional boiler double reheat system relatively poor, can't promote.
Fig. 3 shows the schematic structure according to an embodiment of secondary steam reheat system of the present invention.As shown in Figure 3, secondary steam reheat system 300 of the present invention mainly comprises boiler 301, steam turbine, secondary reheater 306, some heaters 307, condenser 308 and generator 309.Wherein, steam turbine comprises high pressure cylinder 302, first order intermediate pressure cylinder 303, second level intermediate pressure cylinder 304 and the low pressure (LP) cylinder 305 that connects successively.
One of characteristics of the present invention are: secondary reheater 306 is arranged at the outside of boiler 301.In fact, these secondary reheater 306 preferred arrangements are near steam turbine.In this embodiment, this secondary reheater 306 steam drain of being connected to the first order intermediate pressure cylinder 303 of steam turbine connects and connects with the air intake of the second level intermediate pressure cylinder 304 of steam turbine.This secondary reheater 306 can produce the reheated steam of high temperature, and the reheated steam of this high temperature is introduced in the second level intermediate pressure cylinder 304, to realize heat again.Be different from prior art, above-mentioned secondary reheater 306 adopts carbonated drink-vapor heated heat exchange mode.Therefore, owing to the spacing between carbonated drink-vapor heat exchanger (being secondary reheater 306) and the steam turbine is nearer in the present invention, so the double reheat pipeline is shorter.
In this embodiment, this secondary reheater 306 is connected to high pressure cylinder 302, and this high pressure cylinder 302 is as the vapour source of this secondary reheater 306.Particularly, can be this secondary reheater 306 from high pressure cylinder 302 draw gas or this high pressure cylinder 302 to the mode of these secondary reheater 306 steam discharges to secondary reheater 306 steam supplies.On the other hand; As shown in the figure; Secondary reheater 306 further is connected to a heater 307 (or the low one-level heater of pressure); The heat regenerative system pressure of this heater 307 (or pressure comparatively low one-level heater) need be complementary with the pressure of the hydrophobic steam discharge after heat exchange of secondary reheater 306 (quite or low slightly), so that this secondary reheater 306 can enter the hydrophobic steam discharge after heat exchange this heater 307 (or the low one-level heater of pressure).
In addition, the high pressure cylinder 302 of steam turbine, first order intermediate pressure cylinder 303, second level intermediate pressure cylinder 304 and low pressure (LP) cylinder 305 are coaxial in the embodiments of figure 3 is with a generator 309.But, being described below, these cylinders also can many generators of disalignment band.
According to the foregoing description, when work, the double reheat steam of low temperature will through reheating pipe road, the low temperature second level, get into carbonated drink-vapor heated secondary reheater 306 from first order intermediate pressure cylinder 303 outputs of steam turbine, become high temperature secondary reheated steam after being heated.The double reheat steam of this high temperature gets into steam turbine through reheating pipe road, the high temperature second level second level intermediate pressure cylinder 304 continues acting.
In addition, the heating steam of carbonated drink-vapor heated secondary reheater 306 can be from the steam discharge of the high pressure cylinder 302 of steam turbine, i.e. low temperature first order reheated steam; Perhaps also can heat respectively, optimize main steam turbine efficient with the steam discharge that draws gas with high pressure cylinder of the intermediate pressure cylinder of steam turbine.Heating steam is behind carbonated drink-vapor heated secondary reheater 306, and hydrophobic or steam discharge is got back to the heater 307 (or the low one-level heater of pressure) that heat regenerative system pressure is complementary.
For example, to 1 1000MW600 ℃ of ultra supercritical generating set, adopt the embodiment of Fig. 3; System compares with conventional boiler single reheat, and it is about 100,000,000 that investment increases, and efficiency of thermal cycle can improve about 1%; Can economize on coal every year 1.5 ten thousand tons; Reduce by 1,200 ten thousand yuan of operating costs, can recoup capital outlay in 8.3 years, have good returns of investment.
For example, to 1 1000MW600 ℃ of ultra supercritical generating set, adopt the embodiment of Fig. 3; System compares with the conventional boiler double reheat, and it is about 200,000,000 that equipment and pipeline cost reduce, though few about 6,000,000 yuan of operation income; But pay off period shortens half the, has better returns of investment.
To high temperature in future 700 ℃ of thermal power generating technologies of thermal recovery nickel-base alloy again; Because of the Unit Weight price of nickel-base alloy expensive more than 10 times than 600 ℃ of high-temperature steels; System compares with the conventional boiler double reheat, and secondary steam reheat system of the present invention has better technical and economic feasibility.
Below in conjunction with Fig. 4-6 other three preferred embodiments of the present invention are discussed further.
The basic structure of Fig. 4 and above embodiment shown in Figure 3 are similar.Therefore, ditto scheming identical or close structure will repeat no more.The main distinction point of the embodiment of Fig. 4 is: in the embodiment of Fig. 4, the vapour source of secondary reheater 406 further comprises high pressure cylinder, i.e. drawing gas further to heat up and raise the efficiency with the high pressure cylinder of steam turbine.
The basic structure of Fig. 5 and above embodiment shown in Figure 4 are similar.Therefore, ditto scheming identical or close structure will repeat no more.The main distinction point of the embodiment of Fig. 5 is: in the embodiment of Fig. 5; Has only an intermediate pressure cylinder to reduce the cylinder total quantity; Be that intermediate pressure cylinder among Fig. 5 is independent steam turbine cylinder, therefore secondary reheater connects with the air inlet of the low pressure (LP) cylinder of steam turbine in this embodiment.This secondary reheater can produce the reheated steam of high temperature, and the reheated steam of this high temperature is introduced in the low pressure (LP) cylinder, to realize heat again.
The basic structure of Fig. 6 and above embodiment shown in Figure 5 are similar.Therefore, ditto scheming identical or close structure will repeat no more.The main distinction point of the embodiment of Fig. 6 is: in the embodiment of Fig. 6, many generator 609-1 of high, medium and low cylinder pressure disalignment band of steam turbine, 609-2 improve unit efficiency and exert oneself.
To sum up, secondary steam reheat system of the present invention is based on the thermodynamic cycle basic principle, and system compares with single reheat, has improved efficiency of thermal cycle, reaches the comprehensive benefit of energy-saving and emission-reduction when improving economy.The novel secondary steam reheat system of the present invention adopts carbonated drink-vapor heated second level reheater; With second level reheater is that the conventional double reheat of flue gas-vapor heated system compares; Investment such as equipment, pipeline significantly reduces, and has better investment return Technological Economy property.
In addition, the heating steam of secondary steam reheat system of the present invention has plurality of optional vapour source, and hydrophobic steam discharge has multiple backheat whereabouts, is not limited to the accompanying drawing illustrated embodiment, and the different parameters unit is had broad applicability.
In addition, the high temperature reheated steam of the novel secondary steam reheat system of the present invention can cause another intermediate pressure cylinder or low pressure (LP) cylinder, has multiple mode, and the steam turbine of different manufacturers, different technologies is had broad applicability.
In addition, the high, medium and low cylinder pressure of steam turbine of the novel secondary steam reheat system of the present invention can coaxially be with a generator, also can many generators of disalignment band, have multiple mode, and the unit of all size capacity there is broad applicability.
Those skilled in the art can be obvious, can carry out various modifications and modification and without departing from the spirit and scope of the present invention to above-mentioned exemplary embodiment of the present invention.Therefore, be intended to that the present invention is covered and drop in appended claims and the come scope thereof to modification of the present invention and modification.
Claims (8)
1. secondary steam reheat system comprises:
Steam turbine, said steam turbine comprise high pressure cylinder, intermediate pressure cylinder and the low pressure (LP) cylinder that connects successively;
Secondary reheater is arranged at the boiler outside, and connect and connect with the steam drain of an intermediate pressure cylinder of said steam turbine with another intermediate pressure cylinder of said steam turbine or the air intake of low pressure (LP) cylinder,
Wherein, said secondary reheater produces high temperature reheated steam, and this high temperature reheated steam is introduced said another intermediate pressure cylinder or low pressure (LP) cylinder.
2. secondary steam reheat system as claimed in claim 1 is characterized in that, said secondary reheater adopts carbonated drink-vapor heated heat exchange mode.
3. secondary steam reheat system as claimed in claim 1 is characterized in that, said secondary reheater and high pressure cylinder, intermediate pressure cylinder or the two are connected wherein said high pressure cylinder, intermediate pressure cylinder or the two vapour source as said secondary reheater.
4. secondary steam reheat system as claimed in claim 3 is characterized in that, said secondary reheater draws gas from said high pressure cylinder, intermediate pressure cylinder or the two.
5. secondary steam reheat system as claimed in claim 3 is characterized in that, said high pressure cylinder, intermediate pressure cylinder or the two is to said secondary reheater steam discharge.
6. secondary steam reheat system as claimed in claim 1 is characterized in that, said secondary reheater further with said secondary steam reheat system in one or more heaters be connected,
The pressure of the heat regenerative system pressure of wherein said one or more heaters and the hydrophobic steam discharge after heat exchange of said secondary reheater is complementary,
Wherein said secondary reheater enters said one or more heater with the hydrophobic steam discharge after heat exchange.
7. secondary steam reheat system as claimed in claim 1 is characterized in that, the high pressure cylinder of said steam turbine, intermediate pressure cylinder, low pressure (LP) cylinder be coaxial is with a generator.
8. secondary steam reheat system as claimed in claim 1 is characterized in that, the high pressure cylinder of said steam turbine, intermediate pressure cylinder, many generators of low pressure (LP) cylinder disalignment band.
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Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104061028A (en) * | 2014-06-24 | 2014-09-24 | 华北电力大学 | Double-reheat combined cycle power generation system and method combining oxyhydrogen and pulverized coal combustion |
| CN104806308A (en) * | 2015-03-09 | 2015-07-29 | 章礼道 | Optimum scheme of ultra-supercritical secondary reheating unit |
| CN105352002A (en) * | 2015-11-12 | 2016-02-24 | 中国能源建设集团广东省电力设计研究院有限公司 | Steam exhausting heat supply system |
| CN107956524A (en) * | 2016-10-18 | 2018-04-24 | 神华集团有限责任公司 | Steam power system and coal-to-olefin chemical system |
| CN109519347A (en) * | 2018-11-26 | 2019-03-26 | 中国华能集团清洁能源技术研究院有限公司 | Point-line-focusing solar and coal fired power plant complementary power generation system and its energy distributing method |
| WO2019200976A1 (en) * | 2018-04-17 | 2019-10-24 | 章礼道 | Double reheating unit having ultra-high-pressure cylinder and high-pressure and intermediate-pressure cylinder each having additional heat regeneration stages |
| CN113137290A (en) * | 2021-05-28 | 2021-07-20 | 西安热工研究院有限公司 | High-parameter steam turbine steam reheating circulating system |
| CN114076004A (en) * | 2021-11-02 | 2022-02-22 | 神华国华寿光发电有限责任公司 | Medium-pressure heat supply system and medium-pressure heat supply method |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104061028A (en) * | 2014-06-24 | 2014-09-24 | 华北电力大学 | Double-reheat combined cycle power generation system and method combining oxyhydrogen and pulverized coal combustion |
| CN104061028B (en) * | 2014-06-24 | 2016-02-24 | 华北电力大学 | The double reheat association circulating power generation system that hydrogen-oxygen is combined with coal dust firing and method |
| CN104806308A (en) * | 2015-03-09 | 2015-07-29 | 章礼道 | Optimum scheme of ultra-supercritical secondary reheating unit |
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| US11066960B2 (en) | 2018-04-17 | 2021-07-20 | Lidao ZHANG | Double-reheat power generator with an ultra high pressure cylinder and a high-intermediate pressure cylinder each having additional heat recovery turbine stages |
| CN109519347A (en) * | 2018-11-26 | 2019-03-26 | 中国华能集团清洁能源技术研究院有限公司 | Point-line-focusing solar and coal fired power plant complementary power generation system and its energy distributing method |
| CN113137290A (en) * | 2021-05-28 | 2021-07-20 | 西安热工研究院有限公司 | High-parameter steam turbine steam reheating circulating system |
| CN114076004A (en) * | 2021-11-02 | 2022-02-22 | 神华国华寿光发电有限责任公司 | Medium-pressure heat supply system and medium-pressure heat supply method |
| CN114076004B (en) * | 2021-11-02 | 2023-08-25 | 国能寿光发电有限责任公司 | Medium-pressure heat supply system and medium-pressure heat supply method |
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Application publication date: 20120606 |