CN104633647A - Emission reduction and energy saving system capable of omitting GGH - Google Patents
Emission reduction and energy saving system capable of omitting GGH Download PDFInfo
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- CN104633647A CN104633647A CN201410826086.3A CN201410826086A CN104633647A CN 104633647 A CN104633647 A CN 104633647A CN 201410826086 A CN201410826086 A CN 201410826086A CN 104633647 A CN104633647 A CN 104633647A
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Abstract
The invention discloses an emission reduction and energy saving system capable of canceling a GGH. The emission reduction and energy saving system capable of canceling the GGH comprises an air pre-heater, a high temperature heat exchanger, a first segment of a low temperature heat exchanger, a dry type electrostatic dust collector, a draught fan, a booster fan, a second segment of the low temperature heat exchanger, a desulfurization tower, a wet type electric dust collector, a third segment of the low temperature heat exchanger and a chimney which are sequentially connected with a rear smoke channel of a furnace in series; the system also comprises an air heat exchanger and a secondary air fan which are sequentially connected with a secondary cold air channel in series, wherein the output end of the secondary air fan is connected with the side air input end of the air pre-heater through the air heat exchanger; the system also comprises a low pressure heater, a first water pump, a second water pump and a third water pump. By the adoption of the structure of the emission reduction and energy saving system capable of canceling the GGH, the dust collection efficiency of the dry type electrostatic dust collector can be improved, and the new devices are adopted for replacing the using function of the GGH; meanwhile, by the adoption of the novel heat exchange structures, the purpose of furthest recycling the waste heat of discharged smoke is achieved.
Description
Technical field
The present invention relates to the technical field of boiler power plant, particularly relate to a kind of reduction of discharging energy conserving system cancelling GGH.
Background technology
Along with developing rapidly of global economy, people are also faced with severe environmental problem when enjoying its achievement, and the pollutant produced by coal-burning power plant and Industrial Boiler is the main source of air environmental pollution.Reduce dust in air content and become state key concern content.The thermal power plant of 47 key cities' main city zone of Chinese Ministry of Environmental Protection's No. 14 bulletin requirements in 2013, need meet special emission limit 20mg/m in the soot emissions of chimney entrance after dust removal installation and desulphurization system transformation
3.
In China's active service fired power generating unit, the exhaust gas temperature of boiler, about 130 DEG C ~ 160 DEG C, substantially all exceedes intrinsic economic exhaust gas temperature 110 DEG C.By the impact of thermal power plant's ature of coal condition, when use coal poor or exhaust gas temperature is higher time, flue dust ratio resistance is higher, the efficiency of dust collection of dry electrostatic cleaner is caused to reduce, dust emission level does not often reach the requirement of national standard, and when not arranging GGH, because behind absorption tower, flue-gas temperature is lower, and carry gypsum particle, chimney easily occurs " gypsum rain " and emit " white cigarette " problem, and after GGH is set, " gypsum rain " problem can be controlled, but GGH invests and operating cost is higher, from current ruuning situation, it is high that GGH also also exists resistance, corrosion is serious with blocking, the shortcomings such as equipment investment is high.
Meanwhile, because demand for energy increases, coal shortage brings series of problems to power industry.To adopt an effective measure raising energy utilization rate, reduce the common recognition that cost of electricity-generating has become electricity power enterprise.
Therefore, design one and can make full use of smoke discharging residual heat; Can reduce dust discharge amount again, the new system simultaneously GGH can replaced is most important.
Summary of the invention
Technical problem underlying to be solved by this invention is to provide a kind of reduction of discharging energy conserving system cancelling GGH, be intended to overcome prior art and think that exhaust gas temperature need be arranged on the technology prejudice of more than flue gas acid dew point, dry electrostatic cleaner inlet flue gas temperature is down near flue gas acid dew point, dry electrostatic cleaner dust specific resistance is declined, to improve dry electrostatic cleaner efficiency of dust collection; And adopt new equipment to replace the using function of GGH, meanwhile, realize the object reclaiming smoke discharging residual heat to greatest extent.
For solving the problems of the technologies described above, the invention provides a kind of reduction of discharging energy conserving system cancelling GGH, comprise the air preheater, high-temperature heat-exchanging, cryogenic heat exchanger one section, dry electrostatic cleaner, air-introduced machine, booster fan, cryogenic heat exchanger two sections, desulfurizing tower, wet electrical dust precipitator, cryogenic heat exchanger three sections and the chimney that are serially connected with boiler back end ductwork successively; And comprising the air heat exchanger and overfire air fan that are serially connected with cold secondary air duct successively, described overfire air fan output connects the air side input of described air preheater through described air heat exchanger; Native system also comprises low-pressure heater, the first water pump, the second water pump and the 3rd water pump;
Described low-pressure heater is serially connected with in the main condensate pipeline of steam turbine, the input of described low-pressure heater connects the heat transferring medium input of described high-temperature heat-exchanging through described first water pump, the heat transferring medium output of described high-temperature heat-exchanging connects the output of described low-pressure heater;
The heat transferring medium output of described cryogenic heat exchanger three sections connects the heat transferring medium input of described cryogenic heat exchanger one section through described second water pump, the heat transferring medium output of described cryogenic heat exchanger one section connects the heat transferring medium input of described cryogenic heat exchanger three sections;
The heat transferring medium output of described air heat exchanger connects the heat transferring medium input of described cryogenic heat exchanger two sections through described 3rd water pump, the heat transferring medium output of described cryogenic heat exchanger two sections connects the heat transferring medium input of described air heat exchanger.
Further, the outlet temperature of described cryogenic heat exchanger one section is 90-95 DEG C.
Further, the outlet temperature of described cryogenic heat exchanger two sections is 80-85 DEG C.
Further, the outlet temperature of described cryogenic heat exchanger three sections is 70-75 DEG C.
Further, native system also comprises two expansion tanks, and the output of two described expansion tanks connects the input of described second water pump and described 3rd water pump respectively.
Further, described low-pressure heater comprises the primary heater, secondary heater, the 3rd heater and the 4th heater that are connected in series successively.
Further, native system also comprises recirculation control valve, first valve, second valve, 3rd valve and the 4th valve, described recirculation control valve is serially connected with between the heat transferring medium output of described high-temperature heat-exchanging and the input of the first water pump, described first valve is connected between described primary heater output and the heat transferring medium output of high-temperature heat-exchanging, described second valve is connected between described primary heater input and the heat transferring medium output of high-temperature heat-exchanging, described 3rd valve is connected between described secondary heater input and the first water pump input, described 4th valve is connected between described 4th heater input and the first water pump input.
Further, described cryogenic heat exchanger one section adopts Novel heat exchange pipe, described Novel heat exchange pipe comprises heat exchanger tube and heat exchange fin, described in two, heat exchanger tube be arranged in parallel, some peripheries described heat exchange fin being separately positioned on to heat exchanger tube described in two, described heat exchange fin is respectively equipped with concavo-convex alternate arc-shaped protrusions, described arc-shaped protrusions presents bellows-shaped in heat exchange fin plane.
Further, often pair of described heat exchange fin comprises fin and lower fin, and described upper fin and lower fin are symmetricly set on the both sides up and down of heat exchanger tube described in two respectively.
Further, the gap of 5-10mm is provided with between described upper fin and described lower fin.
Further, described cryogenic heat exchanger two sections is membrane heat exchanger, comprises heat exchange fin and fluid hose; Described fluid hose is located at the both sides of described heat exchange fin, and described heat exchange fin comprises base plate, top board and two pipes; Described two pipes are arranged in parallel and have elongated slot vertically, and described base plate is positioned opposite with top board and be connected base and the top margin of described two pipe elongated slots respectively in both sides; The diameter of two pipes of described heat exchange fin is greater than the diameter of described fluid hose; Described base plate and top board are arranged in parallel or arrange in splayed configuration.
After present invention employs technique scheme, by exhaust gas temperature is dropped to below flue gas acid dew point, namely by reducing below dry electrostatic cleaner inlet flue gas temperature to flue gas acid dew point, reduce dry electrostatic cleaner dust specific resistance, effectively improve the efficiency of dust collection of dry electrostatic cleaner, make chimney breast dust emission concentration be reduced to 15 ~ 18mg/Nm
3, reach discharging standards; Meanwhile, under the prerequisite not affecting using function, the parts of this highly energy-consuming of GGH, high fault rate can be cancelled, under about 80 DEG C of lower exhaust gas temperatures, achieve the object reclaiming smoke discharging residual heat to greatest extent.
Accompanying drawing explanation
Fig. 1 is structural representation of the present invention;
Fig. 2 is the structural representation of cryogenic heat exchanger of the present invention a section;
Fig. 3 is the structural representation of cryogenic heat exchanger of the present invention two sections;
Fig. 4 is cryogenic heat exchanger of the present invention two sections of heat exchange fins is the schematic diagram of parallel construction;
The schematic diagram of Fig. 5 to be the heat exchange fin of cryogenic heat exchanger of the present invention two sections be splayed structure.
Detailed description of the invention
As shown in Figure 1, the invention discloses a kind of reduction of discharging energy conserving system cancelling GGH, comprise the air preheater 1, high-temperature heat-exchanging 2, cryogenic heat exchanger one section 3, dry electrostatic cleaner 13, air-introduced machine 14, booster fan 15, cryogenic heat exchanger two section 4, desulfurizing tower 16, wet electrical dust precipitator 17, cryogenic heat exchanger three section 32 and the chimney 18 that are serially connected with boiler back end ductwork 11 successively; And comprising the air heat exchanger 42 and overfire air fan 19 that are serially connected with the cold secondary air duct 12 of boiler successively, described overfire air fan 19 output connects the air side input of described air preheater 1 through described air heat exchanger 42; Native system also comprises low-pressure heater 5, first water pump 7, second water pump 8 and the 3rd water pump 9;
Described low-pressure heater 5 is serially connected with in the main condensate pipeline of steam turbine, the input of described low-pressure heater connects the heat transferring medium input of described high-temperature heat-exchanging 2 through described first water pump 7, the heat transferring medium output of described high-temperature heat-exchanging 2 connects the output of described low-pressure heater 5;
The heat transferring medium output that described cryogenic heat exchanger is three section 32 connects the heat transferring medium input of described cryogenic heat exchanger one section 3 through described second water pump 8, and the heat transferring medium output that described cryogenic heat exchanger is a section 3 connects the heat transferring medium input of described cryogenic heat exchanger three section 32;
The heat transferring medium output of described air heat exchanger 42 connects the heat transferring medium input of described cryogenic heat exchanger two section 4 through described 3rd water pump 9, and the heat transferring medium output that described cryogenic heat exchanger is two section 4 connects the heat transferring medium input of described air heat exchanger 42.
Further, described cryogenic heat exchanger one section of 3 outlet temperature is 90-95 DEG C; Preferably, described cryogenic heat exchanger one section of 3 outlet temperature is 90 DEG C.
Further, the outlet temperature of described cryogenic heat exchanger two section 4 is 80-85 DEG C; Preferably, described cryogenic heat exchanger two section of 4 outlet temperature is 80 DEG C.
Further, the outlet temperature of described cryogenic heat exchanger three section 32 is 70-75 DEG C; Preferably, described cryogenic heat exchanger three section of 32 flue gas that wet electrical dust precipitator can be exported about 50-60 DEG C is promoted to about 75 DEG C.
Further, native system also comprises two expansion tanks (31,41), and the output of two described expansion tanks connects the input of described second water pump 8 and described 3rd water pump 9 respectively.
Further, described low-pressure heater 5 comprises the primary heater 51, secondary heater 52, the 3rd heater 53 and the 4th heater 54 that are connected in series successively.
Further, native system also comprises recirculation control valve 21, first valve 61, second valve 62, 3rd valve 63 and the 4th valve 64, described recirculation control valve 21 is serially connected with between the heat transferring medium output of described high-temperature heat-exchanging 2 and the input of the first water pump 7, described first valve 61 is connected between described primary heater 51 output and the heat transferring medium output of high-temperature heat-exchanging 2, described second valve 62 is connected between described primary heater 51 input and the heat transferring medium output of high-temperature heat-exchanging 2, described 3rd valve 63 is connected between described secondary heater 52 input and the first water pump 7 input, described 4th valve 64 is connected between described 4th heater 54 input and the first water pump 7 input.
This method is through practical application, owing to being connected in series thermal source in air preheater front end, the air themperature entering air preheater is made to be increased to 50 DEG C by room temperature, the air themperature entering boiler after air preheater heating is 315 DEG C, boiler exhaust gas carries out after heat exchange through air preheater, the flue-gas temperature of discharging air preheater can rise to 148 DEG C by original 131 DEG C, there is the difference variation of 17 DEG C, the quality of residual heat from boiler fume has greatly improved, value also just improves greatly, therefore can be used for the boiler feedwater of heating boiler heat regenerative system, the steam further reducing steam turbine draws gas, the generating efficiency of effective raising steam turbine, the heat of the low-temperature flue gas that cryogenic heat exchanger one section absorbs can be used to heat the flue gas after wet electrical dust precipitator, the flue-gas temperature entering chimney is made to be raised to 75 DEG C from original 50 DEG C, improve exhaust gas temperature, the raising of exhaust gas temperature, improve the exhaustion smoke height of chimney, while reduction flue gas is to chimney corrosion, decrease the pollution of smoke evacuation to environment.
Further, as shown in Figure 2, described cryogenic heat exchanger one section 3 is finned heat exchanger, comprise heat exchanger tube 31 and heat exchange fin 32, described in two, heat exchanger tube 31 be arranged in parallel, some peripheries described heat exchange fin 32 being separately positioned on to heat exchanger tube 31 described in two, described heat exchange fin 32 is respectively equipped with concavo-convex alternate arc-shaped protrusions 35, described arc-shaped protrusions 35 presents bellows-shaped in heat exchange fin 32 plane.Often pair of described heat exchange fin 32 comprises fin 33 and lower fin 34, and described upper fin 33 and lower fin 34 are symmetricly set on the both sides up and down of heat exchanger tube 31 described in two respectively.The gap of 5-10mm is provided with between described upper fin 33 and described lower fin 34.
The novel in structural design of this heat exchanger tube, effectively heat exchange area can be increased on the basis not increasing shared heat transfer space, about 10% can be increased compared with the common two-tube H type fin heat exchange pipe heat exchange area of same size, and be conducive to flue gas around heat exchanger tube, produce stronger streaming, increase the time of contact of flue gas and heat exchange fin, enhanced heat exchange effect, substantially increases the heat transfer efficiency of heat exchanger.This heat exchanger tube can realize batch production by die apparatus, reduces cost of manufacture.
Further, as shown in Figures 3 to 5, described cryogenic heat exchanger two section 4 is membrane heat exchanger, comprises heat exchange fin 41 and fluid hose 42, described heat exchange fin and fluid hose surface coating inorganic nonmetallic materials, and through high-temperature process, temperature: 800-1000 DEG C; Or be coated with acidproof polymeric coating layer again.Described fluid hose 42 is located at the both sides of described heat exchange fin 41.Described heat exchange fin 41 comprises base plate 411, top board 412 and two pipes 413; Described two pipes 413 are arranged in parallel and have elongated slot vertically, described base plate 411 and both sides positioned opposite with top board 412 are connected base and the top margin of described two pipe 413 elongated slots respectively, the diameter of two pipes 413 of described heat exchange fin is greater than the diameter of described fluid hose 42, described base plate 411 and top board 412 is arranged in parallel or in splayed configuration arrange.The above-mentioned design of heat exchange fin of the present invention and layout, not only have larger area of dissipation, Stability Analysis of Structures, and level and smooth streamline, is conducive to reducing washing away of flue dust, life-extending.
The base plate 411 of the heat exchange fin 41 in this cryogenic heat exchanger 4, top board 412 and two pipes 413 form the special pipe that cross section is dumb-bell shape, band steel structure is added compared to the light pipe of traditional membrane type heat exchanger plates, add heat exchange area, enhance flue gas 41 stream between fluid hose 42 and heat exchange fin, reach the object of enhanced heat exchange; The dumbbell-shaped section of described heat exchange fin 41 has good flexibility simultaneously, carries out, in high-temperature heat treatment process, effectively to reduce high temperature deformation at heat exchange fin 41, improves the quality of heat exchange fin 41; Described heat exchange fin 41 can realize batch production by mould, reduces cost of manufacture; The membrane type heat exchanger plates of described temperature heat exchanger 4 adopts some above-mentioned heat exchange fins 41 to form, and some fluid hoses 42 are located between some heat exchange fins 41 and are also communicated with according to this, thus improve the heat transfer efficiency of whole cryogenic heat exchanger 4.The diameter of the pipe 413 of described heat exchange fin 41 both sides is greater than the diameter of fluid hose 42, avoids directly washing away of high ash-laden gas fluid pipe 42, effectively can prevent dust stratification.Simultaneously, the surface of described fluid hose 42 and heat exchange fin 41 is coated with Inorganic and Nonmetallic Coating and acidproof polymeric coating layer, the acid resistance of cryogenic heat exchanger 4 is strengthened greatly, can overcome cold end corrosion well, making flue-gas temperature be down to below acid dew point becomes possibility.Dumbbell shape structure heat exchange fin is adopted to be because in later stage nonmetallic materials coating, in high-temperature process, not yielding (relatively existing band steel heat exchange fin) and can heat exchange area be increased.
Native system installs wet cottrell additional, wet cottrell can effectively reduce pollutant emission in flue gas, especially to gypsum drop, acid mist, toxic heavy metal and PM10, especially the fine dust of PM2.5 has good removal effect, to the power plant's ubiquitous desulfuration absorbing tower demister poor effect put into operation at present, the tools such as gypsum rain pollution improve significantly effect.
After present invention employs technique scheme, by exhaust gas temperature is dropped to below flue gas acid dew point, namely by reducing below dry electrostatic cleaner inlet flue gas temperature to flue gas acid dew point, reduce dry electrostatic cleaner dust specific resistance, effectively improve the efficiency of dust collection of dry electrostatic cleaner, make chimney breast dust emission concentration be reduced to 15 ~ 18mg/Nm
3, reach discharging standards; Meanwhile, under the prerequisite not affecting using function, the parts of this highly energy-consuming of GGH, high fault rate can be cancelled, under about 80 DEG C of lower exhaust gas temperatures, achieve the object reclaiming smoke discharging residual heat to greatest extent.
All distortion that those of ordinary skill in the art can directly derive from the disclosure of invention or associate, all should think protection scope of the present invention.
Claims (9)
1. can cancel a reduction of discharging energy conserving system of GGH, it is characterized in that: comprise the air preheater, high-temperature heat-exchanging, cryogenic heat exchanger one section, dry electrostatic cleaner, air-introduced machine, booster fan, cryogenic heat exchanger two sections, desulfurizing tower, wet electrical dust precipitator, cryogenic heat exchanger three sections and the chimney that are serially connected with boiler back end ductwork successively; And comprising the air heat exchanger and overfire air fan that are serially connected with cold secondary air duct successively, described overfire air fan output connects the air side input of described air preheater through described air heat exchanger; Native system also comprises low-pressure heater, the first water pump, the second water pump and the 3rd water pump;
Described low-pressure heater is serially connected with in the main condensate pipeline of steam turbine, the input of described low-pressure heater connects the heat transferring medium input of described high-temperature heat-exchanging through described first water pump, the heat transferring medium output of described high-temperature heat-exchanging connects the output of described low-pressure heater;
The heat transferring medium output of described cryogenic heat exchanger three sections connects the heat transferring medium input of described cryogenic heat exchanger one section through described second water pump, the heat transferring medium output of described cryogenic heat exchanger one section connects the heat transferring medium input of described cryogenic heat exchanger three sections.
The heat transferring medium output of described air heat exchanger connects the heat transferring medium input of described cryogenic heat exchanger two sections through described 3rd water pump, the heat transferring medium output of described cryogenic heat exchanger two sections connects the heat transferring medium input of described air heat exchanger.
2. a kind of reduction of discharging energy conserving system cancelling GGH as claimed in claim 1, is characterized in that: the outlet temperature of described cryogenic heat exchanger one section is 90-95 DEG C.
3. a kind of reduction of discharging energy conserving system cancelling GGH as claimed in claim 1, is characterized in that: the outlet temperature of described cryogenic heat exchanger two sections is 80-85 DEG C.
4. a kind of reduction of discharging energy conserving system cancelling GGH as claimed in claim 1, is characterized in that: the outlet temperature of described cryogenic heat exchanger three sections is 70-75 DEG C.
5. a kind of reduction of discharging energy conserving system cancelling GGH as claimed in claim 1, it is characterized in that: native system also comprises two expansion tanks, the output of two described expansion tanks connects the input of described second water pump and described 3rd water pump respectively.
6. a kind of reduction of discharging energy conserving system cancelling GGH as claimed in claim 1, is characterized in that: described low-pressure heater comprises the primary heater, secondary heater, the 3rd heater and the 4th heater that are connected in series successively.
7. a kind of reduction of discharging energy conserving system cancelling GGH as claimed in claim 6, it is characterized in that: native system also comprises recirculation control valve, first valve, second valve, 3rd valve and the 4th valve, described recirculation control valve is serially connected with between the heat transferring medium output of described high-temperature heat-exchanging and the input of the first water pump, described first valve is connected between described primary heater output and the heat transferring medium output of high-temperature heat-exchanging, described second valve is connected between described primary heater input and the heat transferring medium output of high-temperature heat-exchanging, described 3rd valve is connected between described secondary heater input and the first water pump input, described 4th valve is connected between described 4th heater input and the first water pump input.
8. a kind of reduction of discharging energy conserving system cancelling GGH as claimed in claim 1, it is characterized in that: described cryogenic heat exchanger one section adopts Novel heat exchange pipe, described Novel heat exchange pipe comprises heat exchanger tube and heat exchange fin, described in two, heat exchanger tube be arranged in parallel, some peripheries described heat exchange fin being separately positioned on to heat exchanger tube described in two, described heat exchange fin is respectively equipped with concavo-convex alternate arc-shaped protrusions, described arc-shaped protrusions presents bellows-shaped in heat exchange fin plane.
9. a kind of reduction of discharging energy conserving system cancelling GGH as claimed in claim 1, is characterized in that: described cryogenic heat exchanger two sections is membrane heat exchanger, comprises heat exchange fin and fluid hose; Described fluid hose is located at the both sides of described heat exchange fin, and described heat exchange fin comprises base plate, top board and two pipes; Described two pipes are arranged in parallel and have elongated slot vertically, and described base plate is positioned opposite with top board and be connected base and the top margin of described two pipe elongated slots respectively in both sides; The diameter of two pipes of described heat exchange fin is greater than the diameter of described fluid hose; Described base plate and top board are arranged in parallel or arrange in splayed configuration.
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| CN201410826086.3A CN104633647A (en) | 2014-08-21 | 2014-12-25 | Emission reduction and energy saving system capable of omitting GGH |
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| CN201410414407.9A CN104165351A (en) | 2014-08-21 | 2014-08-21 | Emission reduction and energy conservation system without GGH |
| CN2014104144079 | 2014-08-21 | ||
| CN201410826086.3A CN104633647A (en) | 2014-08-21 | 2014-12-25 | Emission reduction and energy saving system capable of omitting GGH |
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Cited By (2)
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| CN104990096A (en) * | 2015-07-17 | 2015-10-21 | 福建德兴节能科技有限公司 | Low-energy-consumption management method for chimney white smoke |
| CN111981501A (en) * | 2020-07-30 | 2020-11-24 | 中国大唐集团科学技术研究院有限公司西北电力试验研究院 | Anti-blocking heat exchange device of air preheater of pulverized coal boiler |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN104165351A (en) * | 2014-08-21 | 2014-11-26 | 成信绿集成股份有限公司 | Emission reduction and energy conservation system without GGH |
| CN104266210A (en) * | 2014-10-13 | 2015-01-07 | 成信绿集成股份有限公司 | Energy saving system for deeply reducing emission and capable of replacing GGH (Gas-Gas Heater) |
| CN105020737A (en) * | 2015-07-22 | 2015-11-04 | 成信绿集成股份有限公司 | System for improving safety of air pre-heater by utilizing spiral-fin type heat exchanger |
| CN105371291A (en) * | 2015-11-09 | 2016-03-02 | 华电电力科学研究院 | System capable of utilizing smoke waste heat in gradient mode for assisting in removing SO3 and improving dust removing efficiency |
| CN106123001B (en) * | 2016-06-24 | 2019-03-29 | 福建龙净环保股份有限公司 | A kind of smoke waste heat utilization system and method |
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| Publication number | Publication date |
|---|---|
| CN104165351A (en) | 2014-11-26 |
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Application publication date: 20150520 |