CN202675925U - Drive turbine steam exhaust cooling system and thermal power generating unit of thermal power plant - Google Patents
Drive turbine steam exhaust cooling system and thermal power generating unit of thermal power plant Download PDFInfo
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- CN202675925U CN202675925U CN201220350161XU CN201220350161U CN202675925U CN 202675925 U CN202675925 U CN 202675925U CN 201220350161X U CN201220350161X U CN 201220350161XU CN 201220350161 U CN201220350161 U CN 201220350161U CN 202675925 U CN202675925 U CN 202675925U
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- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E20/00—Combustion technologies with mitigation potential
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Abstract
The utility model discloses a drive turbine steam exhaust cooling system and a thermal power generating unit of a thermal power plant. The drive turbine steam exhaust cooling system comprises a drive turbine, an air preheater and a draught fan, wherein the steam exhaust cooling system further comprises an air cooler, the air cooler enables steam exhaust of the drive turbine to be cooled by inlet air coming from the draught fan, and in addition, a steam exhaust inlet of the air cooler is connected with a steam exhaust outlet of the drive turbine, an air inlet of the air cooler is connected with the draught fan, and an air outlet of the air cooler is connected with the air inlet of the air preheater. The drive turbine steam exhaust cooling system and the thermal power generating unit of the thermal power plant effectively utilizes steam exhaust energy of the drive turbine, improves efficiency of the thermal power plant, and at the same time, reduces coal consumption and pollutant emissions.
Description
Technical field
The utility model relates to the thermal power generation field, is specifically related to the exhaust steam cooling system of driving steam turbine in the thermal power generation.
Background technology
Along with the development of national economy, society constantly improves the demand of electric power.For the new developing country that carries out industrialization and rapid economic development, such as China, the consumption of electric power and the installed capacity in power plant increase rapidly.For China, owing to being subjected to the maintenance variety of its primary energy and storing quantitative limitation, the fuel in power plant is about more than 70% take coal as main in recent decades, and this trend does not in a foreseeable future have basic change.Although coal fired thermal power plant has the advantages such as cost is lower, fuel source is extensive for China, there are the shortcomings such as efficient is lower, pollutant emission is more in coal fired thermal power plant.Owing to being discharged into the burning that pollutant in the atmosphere derives from coal basically, thus relevant between the coal consumption amount of the discharge capacity of pollutant and thermal power plant.Also reduced the discharge capacity of thermal power plant's pollutant in the atmosphere when reducing the thermal power plant coal consumption.
Some rotating machinerys of thermal power plant are often driven by driving steam turbine (also claiming small turbine) by such as feed pump, blower fan etc.In present power plant, the exhaust steam of driving steam turbine (steam discharge) enters condenser by circulating water, is referred to as clammy.Also have the driving steam turbine exhaust steam of indivedual power plant to be cooled off by air cooling condenser, the employing cooling blower in atmosphere, is called the air cooling with the exhaust steam thermal release.
The existing driving steam turbine exhaust steam type of cooling, the energy in the exhaust steam is not reclaimed in clammy or air cooling.And contain a large amount of energy in the exhaust steam, and mainly be vaporization potential, if because utilizing the driving steam turbine exhaust steam energy that energy saving for power plants is brought very large benefit, improve the efficient of thermal power plant, can reduce coal consumption, reduce simultaneously the discharge capacity of pollutant.
The utility model content
The purpose of this utility model provides a kind of system and fired power generating unit of utilizing the exhaust steam energy of driving steam turbine.
For achieving the above object, the utility model provides a kind of thermal power plant driving steam turbine exhaust steam cooling system, comprises driving steam turbine, air preheater and blower fan, it is characterized in that:
Described exhaust steam cooling system also comprises aerial cooler, and described aerial cooler cools off the exhaust steam of described driving steam turbine by the air intake from described blower fan; And
The exhaust steam entrance of described aerial cooler is connected with the exhaust steam of described driving steam turbine outlet, and the air inlet of described aerial cooler is connected with described blower fan, and the air outlet of described aerial cooler is connected with the air inlet of described air preheater.
In one preferred embodiment, described driving steam turbine can drive feed pump, air-introduced machine, water circulating pump, primary air fan, pressure fan or condensate pump, also can drive the generator generating.
Preferably, exhaust steam enters electric turbine after supercooling condenses into water condenser to be reclaiming working medium, or the heater of getting back to heat regenerative system according to condensing water temperature is to reclaim working medium and heat.
Preferably, described blower fan comprises boiler fan and/or primary air fan.
The utility model also provides a kind of fired power generating unit, and described fired power generating unit comprises generator, electric turbine, boiler, deduster, high-pressure heater, low-pressure heater, flue gas-to water-to-water heat exchanger and above-mentioned driving steam turbine exhaust steam cooling system;
Wherein, the outlet of described boiler and described flue gas-is connected for the water-to-water heat exchanger fume side, described flue gas-be connected with described high-pressure heater to water-to-water heat exchanger water side;
A part of high-temperature flue gas of the outlet of described boiler is by described flue gas-give water-to-water heat exchanger, heated feed water.
In another preferred embodiment, described fired power generating unit also comprises:
Flue gas-condensate water heat exchanger;
Wherein, described flue gas-be connected for the outlet of water-to-water heat exchanger fume side with described flue gas-condensate water heat exchanger fume side;
The outlet of described flue gas-condensate water heat exchanger fume side is connected with the outlet of described air preheater; And
The water side of described flue gas-condensate water heat exchanger is connected with low-pressure heater, heat-setting water.
In another preferred embodiment, from flue gas flow, described flue gas-in parallel with described air preheater to water-to-water heat exchanger and flue gas-condensate water heat exchanger.
In another preferred embodiment, on the feedwater flow process, described flue gas-connect for water-to-water heat exchanger with described high-pressure heater.
In another preferred embodiment, on the feedwater flow process, described flue gas-give water-to-water heat exchanger in parallel with described high-pressure heater, a part of feedwater with after the feedwater main road separates by described flue gas-be heated to water-to-water heat exchanger, converge with the feedwater main road again, burble point and point be respectively the upstream, downstream of all high-pressure heaters or arbitrarily the two-stage high-pressure heater between.
In another preferred embodiment, on the feedwater flow process, described flue gas-give water-to-water heat exchanger with simultaneously parallel connection of high-pressure heater and connecting.
In another preferred embodiment, described flue gas-be arranged in the upstream of all high-pressure heaters or be arranged in the downstream of all high-pressure heaters or be arranged between the described high-pressure heater of any two-stage to water-to-water heat exchanger.
In another preferred embodiment, on the condensate water flow process, described flue gas-condensate water heat exchanger is connected with described low-pressure heater.
In another preferred embodiment, on the condensate water flow process, described flue gas-condensate water heat exchanger is in parallel with described low-pressure heater, after separating with the condensate water main road, part condensate water is heated by described flue gas-condensate water heat exchanger, converge with the condensate water main road again, burble point and point be respectively the upstream, downstream of all low-pressure heaters or arbitrarily the two-stage low-pressure heater between.
In another preferred embodiment, described flue gas-condensate water heat exchanger and described low-pressure heater are in parallel and connect simultaneously.
In another preferred embodiment, described flue gas-condensate water heat exchanger is arranged in the upstream of all low-pressure heaters or is arranged in the downstream of all low-pressure heaters or is arranged between any two described low-pressure heaters.
In another preferred embodiment, described fired power generating unit also is included in the storage heater of arranging on the hot Secondary Air of described air preheater outlet, wherein, described storage heater adopts drawing gas for adding hot vapour source, with the hot Secondary Air of heating air preheater outlet of steam turbine.
In another preferred embodiment, on the flue that enters described flue gas-give water-to-water heat exchanger and described flue gas-condensate water heat exchanger the controllable register door is set also, described condition baffle plate is used for regulating exhaust gas volumn.
In another preferred embodiment, described fired power generating unit also can be provided with feed water booster pump, and described feed water booster pump is used for overcoming described flue gas-to the resistance of water-to-water heat exchanger.
In another preferred embodiment, described fired power generating unit also can be provided with condensate booster pump, and described condensate booster pump is used for overcoming the resistance of described flue gas-condensate water heat exchanger.
Preferably, 1 the above flue gas-give water-to-water heat exchanger is set in the fired power generating unit of the present utility model.
Preferably, 1 the above flue gas-condensate water heat exchanger is set in the fired power generating unit of the present utility model.
In the utility model, described feedwater and condensate water can derive from the steam turbine of this fired power generating unit, maybe can derive from the steam turbine of other fired power generating unit.
Preferably, the fuel of described fired power generating unit is coal, combustion gas body or oil.Fired power generating unit of the present utility model is the single reheat fired power generating unit, or the double reheat fired power generating unit.Driving steam turbine exhaust steam cooling system of the present utility model and generating set utilize boiler fan and primary air fan to driving steam turbine exhaust steam cool off, wind and the Secondary Air of sending into boiler are heated, and be gas energy and cascade utilization with this energy replacement, be that inferior exhaust steam energy becomes high-quality energy after replacing, with heated feed water and condensate water.That is, (1) adopts primary air fan and/or pressure fan by the exhaust steam cooling of aerial cooler to driving steam turbine, wind of simultaneously heating blower outlet and/or Secondary Air.(2) the part high-temperature flue gas of boiler economizer outlet is without air preheater, and successively by flue gas-give water-to-water heat exchanger and flue gas-condensate water heat exchanger, heated feed water and condensate water, reduced the required electric turbine amount of drawing gas of high-pressure heater, improved feed temperature, simultaneously, also reduced the electric turbine amount of drawing gas that low-pressure heater draws gas required.Therefore, reduce the electric turbine hear rate, reduced the coal consumption amount of fired power generating unit, the discharge capacity of minimizing fired power generating unit pollutant.
To sum up, the utlity model has following advantage:
(1) takes full advantage of the latent heat of vaporization in energy, the especially exhaust steam of driving steam turbine exhaust steam.
(2) the driving steam turbine exhaust steam adopts the cooling air mode system simple.
(3) by exhaust steam energy is replaced into gas energy, by having realized the cascade utilization of energy, improved the utilization rate of energy.
(4) improved and entered air preheater cold wind temperature, avoided the cold junction heated surface corrosion of air preheater.Compare with the scheme of the employing steam warming machine of commonly using at present or hot blast recirculation, the utility model is less to the negative effect of unit whole efficiency.
(5) adopt flue gas and condensate water, flue gas and to the mode of water direct heat-exchange, system is simple, cost is low.
(6) extracted steam from turbine heating air preheater exports hot Secondary Air, improves boiler inlet temperature.
Description of drawings
Fig. 1 is the system layout schematic diagram of an embodiment of driving steam turbine exhaust steam cooling system of the present utility model;
Fig. 2 is the system schematic of an embodiment of fired power generating unit of the present utility model;
Fig. 3 is the block diagram of an embodiment of the position of flue gas of the present utility model-give water-to-water heat exchanger;
Fig. 4 is the block diagram of another embodiment of the position of flue gas of the present utility model-give water-to-water heat exchanger;
Fig. 5 is the block diagram of another embodiment of the position of flue gas of the present utility model-give water-to-water heat exchanger;
Fig. 6 is the block diagram of another embodiment of the position of flue gas of the present utility model-give water-to-water heat exchanger;
Fig. 7 is the block diagram of another embodiment of the position of flue gas of the present utility model-give water-to-water heat exchanger;
Fig. 8 is the block diagram of another embodiment of the position of flue gas of the present utility model-give water-to-water heat exchanger;
Fig. 9 is the block diagram of an embodiment of the position of flue gas of the present utility model-condensate water heat exchanger;
Figure 10 is the block diagram of another embodiment of the position of flue gas of the present utility model-condensate water heat exchanger;
Figure 11 is the block diagram of another embodiment of the position of flue gas of the present utility model-condensate water heat exchanger; And
Figure 12 is the block diagram that an embodiment of storage heater is set on the basis of Fig. 2.
The specific embodiment
Below with reference to accompanying drawing preferred embodiment of the present utility model is elaborated, in order to clearlyer understand the purpose of this utility model, characteristics and advantage.It should be understood that embodiment shown in the drawings is not the restriction to the utility model scope, and just for the connotation of technical solutions of the utility model is described.Same or analogous part uses the same reference numerals to represent among the figure.
Below, major technique term of the present utility model is described.
Herein, described boiler main will comprise boiler plant.Described boiler plant is not specifically limited, and only otherwise utility model purpose of the present utility model is produced restriction to be got final product, is well known by persons skilled in the art.Can adopt π type boiler (or claiming to send the type boiler), tower boiler, inverted U boiler etc., can be coal-burning boiler, oil burning boiler etc., can be natural circulation boiler, forced circulation boiler, direct current cooker etc., all in protection domain of the present utility model.
Herein, described air preheater is not specifically limited, and only otherwise utility model purpose of the present utility model is produced restriction to be got final product, is well known by persons skilled in the art.Can adopt tubular preheater, rotary preheater etc., all in protection domain of the present utility model.
Herein, described deduster refers to catch the equipment of dust in the flue gas.Only otherwise utility model purpose of the present utility model is produced restriction to be got final product, be well known by persons skilled in the art.Can adopt electrostatic precipitator, cloth bag flue gas ash removal unit, electricity bag flue gas ash removal unit, moisture film flue gas ash removal unit etc., all in protection domain of the present utility model.
Herein, described aerial cooler is a heat exchanger, perhaps is parallel connection, series connection, series-parallel several heat exchangers.
Herein, described flue gas-to water-to-water heat exchanger is a heat exchanger, perhaps is parallel connection, series connection, series-parallel several heat exchangers.
Herein, described flue gas-condensate water heat exchanger is a heat exchanger, perhaps is parallel connection, series connection, series-parallel several heat exchangers.
Herein, described blower fan is not specifically limited, and only otherwise utility model purpose of the present utility model is produced restriction to be got final product, is well known by persons skilled in the art.Can adopt centrifugal fan, axial fan etc., all in protection domain of the present utility model.
Herein, described flue gas-comprise pipe heat exchanger, plate type heat exchanger, surface-type heat exchanger, indirect-heating heat exchanger etc. to water-to-water heat exchanger, all in protection domain of the present utility model.
Herein, described flue gas-condensate water heat exchanger comprises pipe heat exchanger, plate type heat exchanger, surface-type heat exchanger, indirect-heating heat exchanger etc., all in protection domain of the present utility model.
Herein, described aerial cooler comprises pipe heat exchanger, plate type heat exchanger, surface-type heat exchanger, indirect-heating heat exchanger etc., all in protection domain of the present utility model.
Herein, described high-pressure heater refers to the heater with the heated feed water that draws gas of steam turbine.
Herein, low-pressure heater refers to the heater with the heat-setting water that draws gas of steam turbine.
Herein, driving steam turbine refers to for the driving feed pump, or air-introduced machine, or water circulating pump, or primary air fan, or pressure fan, or condensate pump, or other rotating machinery, or drives the steam turbine of generator.
Herein, the driving steam turbine exhaust steam refers to the steam discharge after steam enters the driving steam turbine acting.
Below describe embodiment of the present utility model in detail.Fig. 1 is the system layout schematic diagram of an embodiment of driving steam turbine exhaust steam cooling system of the present utility model.As shown in Figure 1, in the driving steam turbine exhaust steam cooling system, at first pass through aerial cooler 102 by driving steam turbine 101 exhaust steam out that is used for driving such as the driven equipments such as pump 105, this aerial cooler 102 is similar with the air cooling condenser of Air-cooled Unit.The exhaust steam entrance of aerial cooler 102 is connected with the exhaust steam of driving steam turbine 101 outlet, and the exhaust steam outlet of aerial cooler 102 is connected with electric turbine condenser 103.The air inlet of aerial cooler 102 is connected with pressure fan and/or primary air fan 104, and the wind outlet of aerial cooler 102 is connected with the air inlet of air preheater 2.
After the exhaust steam of driving steam turbine 101 enters aerial cooler 102, by the cold wind cooling from pressure fan and/or primary air fan 104, exhaust steam enters the condenser 103 of electric turbine to reclaim working medium (as shown in Figure 1) after supercooling condenses into water, also can get back to the heater of heat regenerative system to reclaim working medium and heat according to condensing water temperature.Simultaneously, from pressure fan/or the cold wind of primary air fan 104 enter air preheater 2 after being heated.
In other words, heated wind and the Secondary Air of air preheater 2 imports from the exhaust steam of driving steam turbine 101, to keep or to keep burner air intake (instant heating Secondary Air) temperature and coal pulverizer air intake (being heat primary air) temperature as far as possible.Thus, the energy of exhaust steam (the especially latent heat of vaporization) is converted to the heat primary air of air preheater 2 outlets and the energy of hot Secondary Air.And in the existing thermal power plant, the normal flue gas that adopts from boiler export of wind of air preheater import and Secondary Air needs to consume the gas energy of a part.Yet, since the flue-gas temperature of boiler export up to 350～400 ℃ about, therefore it also can be used to heat feedwater and the condensate water of higher temperature, therefore wishes to reduce wind being used for heating the air preheater import in the flue gas of boiler export and the exhaust gas volumn of Secondary Air as far as possible.
In the utility model, because the cold wind of air preheater import can be by driving steam turbine exhaust steam heating, therefore greatly reduced the amount of the boiler export high-temperature flue gas that is used for heating in the air preheater wind and Secondary Air in the prior art.The high-temperature flue gas that displaces is used for heating feedwater and the condensate water in the fired power generating unit.
Fig. 2-12 illustrates the structural plan that the boiler export flue gas that displaces is used for the embodiment of the feedwater of heating fired power generating unit and condensate water.Referring to Fig. 2, in the present embodiment, fired power generating unit comprises: boiler 1, air preheater 2, deduster 3, pressure fan/primary air fan 104, flue gas-give water-to-water heat exchanger 11, flue gas-condensate water heat exchanger 12, high-pressure heater 13, oxygen-eliminating device 14, low-pressure heater 15, generator 16, electric turbine (high pressure cylinder, intermediate pressure cylinder, low pressure (LP) cylinder) 17 and driving steam turbine 101.
As shown in Figure 2, the outlet of boiler 1 is connected with flue gas with air preheater 2 simultaneously and is connected to water-to-water heat exchanger 11.Flue gas-give water-to-water heat exchanger 11 is connected connection with high-pressure heater.The outlet of flue gas-condensate water heat exchanger 12 and flue gas-give water-to-water heat exchanger 11 is connected with low-pressure heater and is connected.
The outlet of flue gas-be connected to boiler 1 for water-to-water heat exchanger 11, the part in the flue gas that boiler 1 burning produces is by flue gas-to water-to-water heat exchanger 11 heated feed waters.In the present embodiment, from flue gas flow, flue gas-give water-to-water heat exchanger 11 in parallel with air preheater 2.On the feedwater flow process, flue gas-give water-to-water heat exchanger 11 in parallel with high-pressure heater 13, i.e. part feedwater with after the feedwater main road separates by flue gas-be heated to water-to-water heat exchanger 11, converge with the main road that feeds water again.Burble point and point can be respectively the upstream, downstream of all high-pressure heaters or arbitrarily the two-stage high-pressure heater between.Flue gas-to water-to-water heat exchanger is one-level, but also can be multistage.
Flue gas is through behind the flue gas-give water-to-water heat exchanger 11, and by flue gas-condensate water heat exchanger 12 heat-setting water, flue gas-condensate water 12 is connected with low-pressure heater 15 from the flue gas of flue gas-give water-to-water heat exchanger 11 outlets.In the present embodiment, on the condensate water flow process, flue gas-condensate water heat exchanger 12 is in parallel with low-pressure heater 15, is heated by flue gas-condensate water heat exchanger after namely a part of condensate water is separated with the condensate water main road, converges with the condensate water main road again.Burble point and point can be respectively the upstream, downstream of all low-pressure heaters or arbitrarily the two-stage low-pressure heater between.Flue gas-condensate water heat exchanger is one-level, but also can be multistage.
Flue gas mixes with the flue gas of air preheater 2 outlets from the flue gas that flue gas-condensate water heat exchanger 12 exports through behind flue gas-condensate water heat exchanger 12.After two strands of above-mentioned flue gases mix, through deduster 3, then enter desulfuration absorbing tower.
In the above-described embodiments, also be provided with aerial cooler 102, the exhaust steam entrance of aerial cooler 102 is connected with the exhaust steam of driving steam turbine 101 outlet, and the exhaust steam outlet is connected with electric turbine condenser 103.The air inlet of aerial cooler 102 is connected with pressure fan and/or primary air fan 104, and the outlet of aerial cooler 102 is connected with the air inlet of air preheater 2.Thus, formed driving steam turbine exhaust steam cooling system.
After the exhaust steam of driving steam turbine 101 entered aerial cooler 102, by the cold wind cooling from pressure fan and/or primary air fan 104, exhaust steam entered the condenser 103 of electric turbine 16 to reclaim working medium after supercooling condenses into water.Simultaneously, from pressure fan/or the cold wind of primary air fan 104 enter air preheater 2 after being heated.
In above-described embodiment, inferior gas energy becomes high-quality energy after replacing, and has heated simultaneously electric turbine feedwater and condensate water.Namely, the part high-temperature flue gas of boiler export is successively by flue gas-give water-to-water heat exchanger and flue gas-condensate water heat exchanger, the feedwater of heating electric turbine and condensate water, the high-pressure heater that has reduced the high-energy quality of original heated feed water draws gas and/or has improved feed temperature, simultaneously, the low-pressure heater that has reduced the low-yield quality of original heat-setting water draws gas, and has reduced the electric turbine hear rate.
In addition, utilize the exhaust steam of driving steam turbine, improved by driving steam turbine exhaust steam cooling system and enter air preheater cold wind temperature, avoid the cold junction heated surface corrosion of air preheater.Compare with the scheme of the employing steam warming machine of commonly using at present or hot blast recirculation, the utility model is less to the negative effect of unit whole efficiency.
It is pointed out that flue gas of the present utility model-various modification can be arranged and do not break away from spirit of the present utility model for position and the arrangement of water-to-water heat exchanger.Referring to Fig. 3-8, on the feedwater flow process, flue gas-can connect with high-pressure heater for water-to-water heat exchanger, it is flue gas-be arranged in to the water-to-water heat exchanger downstream (referring to Fig. 3) of all high-pressure heaters, perhaps flue gas-be arranged in to the water-to-water heat exchanger upstream (referring to Fig. 4) of all high-pressure heaters, perhaps flue gas-to water-to-water heat exchanger be arranged in any two-stage high-pressure heater between (referring to Fig. 5), several flue gases-be arranged in simultaneously in the above-mentioned position to water-to-water heat exchanger perhaps are set.
In addition, on the feedwater flow process, flue gas-give water-to-water heat exchanger also can be in parallel with high-pressure heater, i.e. part feedwater with after the feedwater main road separates by flue gas-be heated to water-to-water heat exchanger, converge (referring to Fig. 6) with the main road that feeds water again.Burble point and point can be respectively the upstream, downstream of all high-pressure heaters or arbitrarily the two-stage high-pressure heater between.Flue gas-give water-to-water heat exchanger can be one-level, also can be some levels.In addition, on the feedwater flow process, flue gas-give water-to-water heat exchanger also can be in parallel and connect (referring to Fig. 7, Fig. 8) simultaneously with high-pressure heater, and flue gas-give water-to-water heat exchanger can be one-level, also can be some grades.Flue gas-when connecting for water-to-water heat exchanger with high-pressure heater, the resistance of heat exchanger 11 can be overcome by the electric turbine feed pump, also can feed water booster pump be set in addition and overcome.
The position of flue gas of the present utility model-condensate water heat exchanger and arrangement also can have various modification and not break away from spirit of the present utility model.Referring to Fig. 9-11, on the condensate water flow process, flue gas-condensate water heat exchanger can be connected with low-pressure heater, be that flue gas-condensate water heat exchanger can be arranged in the downstream of all low-pressure heaters, perhaps be arranged in the upstream of all low-pressure heaters, perhaps be arranged in any two-stage low-pressure heater between (referring to Fig. 9), several flue gases-condensate water heat exchanger perhaps is set is arranged in simultaneously in the above-mentioned position.
In addition, on the condensate water flow process, flue gas-condensate water heat exchanger also can be in parallel with low-pressure heater, is heated by flue gas-condensate water heat exchanger after namely a part of condensate water is separated with the condensate water main road, converges (referring to Figure 10) with the condensate water main road again.Burble point and point can be respectively the upstream, downstream of all low-pressure heaters or arbitrarily the two-stage low-pressure heater between.Flue gas-condensate water heat exchanger can be one-level, also can be some levels.In addition, on the condensate water flow process, flue gas-condensate water heat exchanger also can and be connected with simultaneously parallel connection of low-pressure heater, and flue gas-condensate water heat exchanger can be one-level (referring to Figure 11), also can be some levels.Flue gas-when the condensate water heat exchanger was connected with low-pressure heater, the resistance of heat exchanger can be overcome by the electric turbine condensate pump, also can condensate booster pump be set in addition and overcome.
And above-mentioned feedwater and condensate water can be come the steam turbine in this generating set, maybe can derive from other steam turbine.
In addition, on the basis of the above, can also storage heater 18 be set at the hot Secondary Air of air preheater outlet, referring to Figure 12.Adopt the electric turbine one-level to draw gas as adding hot vapour source, usually adopt larger the drawing gas of the degree of superheat, with the hot Secondary Air of heating air preheater outlet, its effect is further to improve boiler inlet temperature.
In addition, also can in the flue that enters flue gas-give water-to-water heat exchanger and flue gas-condensate water heat exchanger, the controllable register door be set and regulate exhaust gas volumn.
In addition, above-mentioned flue gas-can mutually make up for the various arrangements of water-to-water heat exchanger, flue gas-condensate water heat exchanger, aerial cooler (embodiment illustrated in fig. 2 is one of combination) and do not break away from spirit of the present utility model.Driving steam turbine exhaust steam cooling system of the present utility model and generating set utilize boiler fan and primary air fan to driving steam turbine exhaust steam cool off, wind and the Secondary Air of sending into boiler are heated, and be gas energy and cascade utilization with this energy replacement, be that inferior exhaust steam energy becomes high-quality energy after replacing, with heated feed water and condensate water.That is, (1) adopts primary air fan and/or pressure fan by the exhaust steam cooling of aerial cooler to driving steam turbine, wind of simultaneously heating blower outlet and/or Secondary Air.(2) the part high-temperature flue gas of boiler economizer outlet is without air preheater, and successively by flue gas-give water-to-water heat exchanger and flue gas-condensate water heat exchanger, heated feed water and condensate water, reduced the required electric turbine amount of drawing gas of high-pressure heater, improved feed temperature, simultaneously, also reduced the electric turbine amount of drawing gas that low-pressure heater draws gas required.Therefore, reduce the electric turbine hear rate, reduced the coal consumption amount of fired power generating unit, the discharge capacity of minimizing fired power generating unit pollutant.
To sum up, the utlity model has following advantage:
(1) takes full advantage of the latent heat of vaporization in energy, the especially exhaust steam of driving steam turbine exhaust steam.
(2) the driving steam turbine exhaust steam adopts the cooling air mode system simple.
(3) by exhaust steam energy is replaced into gas energy, by having realized the cascade utilization of energy, improved the utilization rate of energy.
(4) improved and entered air preheater cold wind temperature, avoided the cold junction heated surface corrosion of air preheater.Compare with the scheme of the employing steam warming machine of commonly using at present or hot blast recirculation, the utility model is less to the negative effect of unit whole efficiency.
(5) adopt flue gas and condensate water, flue gas and to the mode of water direct heat-exchange, system is simple, cost is low.
(6) the electric turbine heating air preheater that draws gas exports hot Secondary Air, improves boiler inlet temperature.
Below described preferred embodiment of the present utility model in detail, but it will be appreciated that, after having read above-mentioned instruction content of the present utility model, those skilled in the art can make various changes or modifications the utility model.These equivalent form of values fall within the application's appended claims limited range equally.
Claims (10)
1. thermal power plant's driving steam turbine exhaust steam cooling system comprises driving steam turbine, air preheater and blower fan, it is characterized in that:
Described exhaust steam cooling system also comprises aerial cooler, and described aerial cooler cools off the exhaust steam of described driving steam turbine by the air intake from described blower fan; And
The exhaust steam entrance of described aerial cooler is connected with the exhaust steam of described driving steam turbine outlet, and the air inlet of described aerial cooler is connected with described blower fan, and the air outlet of described aerial cooler is connected with the air inlet of described air preheater.
2. fired power generating unit, comprise generator, electric turbine, boiler and deduster, it is characterized in that, also comprise: high-pressure heater, low-pressure heater, flue gas-to water-to-water heat exchanger and driving steam turbine exhaust steam cooling system as claimed in claim 1;
Wherein, the outlet of described boiler and described flue gas-is connected for the water-to-water heat exchanger fume side, described flue gas-be connected with described high-pressure heater to water-to-water heat exchanger water side; And
A part of high-temperature flue gas of the outlet of described boiler is by described flue gas-give water-to-water heat exchanger, heated feed water.
3. fired power generating unit as claimed in claim 2 is characterized in that, also comprises:
Flue gas-condensate water heat exchanger;
Wherein, described flue gas-be connected for the outlet of water-to-water heat exchanger fume side with described flue gas-condensate water heat exchanger fume side;
The outlet of described flue gas-condensate water heat exchanger fume side is connected with the outlet of described air preheater; And
The water side of described flue gas-condensate water heat exchanger is connected with low-pressure heater, heat-setting water.
4. fired power generating unit as claimed in claim 2, it is characterized in that, on the feedwater flow process, described flue gas-give water-to-water heat exchanger in parallel with described high-pressure heater, a part of feedwater with after the feedwater main road separates by described flue gas-be heated to water-to-water heat exchanger, converge with the feedwater main road again, burble point and point be respectively the upstream, downstream of all high-pressure heaters or arbitrarily the two-stage high-pressure heater between.
5. fired power generating unit as claimed in claim 2, it is characterized in that, described flue gas-connect for water-to-water heat exchanger with described high-pressure heater is arranged in the upstream of all high-pressure heaters or is arranged in the downstream of all high-pressure heaters or is arranged between the described high-pressure heater of any two-stage.
6. fired power generating unit as claimed in claim 3, it is characterized in that, on the condensate water flow process, described flue gas-condensate water heat exchanger is in parallel with described low-pressure heater, after separating with the condensate water main road, part condensate water is heated by described flue gas-condensate water heat exchanger, converge with the condensate water main road again, burble point and point be respectively the upstream, downstream of all low-pressure heaters or arbitrarily the two-stage low-pressure heater between.
7. fired power generating unit as claimed in claim 3, it is characterized in that, described flue gas-condensate water heat exchanger is connected with described low-pressure heater, is arranged in the upstream of all low-pressure heaters or is arranged in the downstream of all low-pressure heaters or is arranged between any two described low-pressure heaters.
8. fired power generating unit as claimed in claim 2 or claim 3, it is characterized in that, also be included in the storage heater of arranging on the hot Secondary Air of described air preheater outlet, wherein, described storage heater adopts drawing gas for adding hot vapour source, with the hot Secondary Air of heating air preheater outlet of steam turbine.
9. fired power generating unit as claimed in claim 3 is characterized in that, on the flue that enters described flue gas-give water-to-water heat exchanger and described flue gas-condensate water heat exchanger the controllable register door is set also, and described condition baffle plate is used for regulating exhaust gas volumn.
10. fired power generating unit as claimed in claim 7 is characterized in that, also is provided with condensate booster pump, and described condensate booster pump is used for overcoming the resistance of described flue gas-condensate water heat exchanger.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201220350161XU CN202675925U (en) | 2012-07-19 | 2012-07-19 | Drive turbine steam exhaust cooling system and thermal power generating unit of thermal power plant |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201220350161XU CN202675925U (en) | 2012-07-19 | 2012-07-19 | Drive turbine steam exhaust cooling system and thermal power generating unit of thermal power plant |
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| CN202675925U true CN202675925U (en) | 2013-01-16 |
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| CN201220350161XU Expired - Lifetime CN202675925U (en) | 2012-07-19 | 2012-07-19 | Drive turbine steam exhaust cooling system and thermal power generating unit of thermal power plant |
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Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103114881A (en) * | 2013-02-25 | 2013-05-22 | 山东岱荣热能环保设备有限公司 | Multi-working-medium backheating type Rankine cycle system |
| CN103134043A (en) * | 2013-01-29 | 2013-06-05 | 北京源深节能技术有限责任公司 | Boiler system with U-shaped flue and boiler water charging system |
| CN103742936A (en) * | 2013-12-30 | 2014-04-23 | 哈尔滨空调股份有限公司 | Steam turbine waste heat exchange system for thermal power plant |
| CN104653241A (en) * | 2013-11-18 | 2015-05-27 | 舒少辛 | Waste heat recovery device for indirect air-cooling unit |
| CN105626171A (en) * | 2016-03-28 | 2016-06-01 | 西安热工研究院有限公司 | Waste heat utilization system for indirect air-cooling unit |
| CN107152316A (en) * | 2017-07-13 | 2017-09-12 | 中国能源建设集团湖南省电力设计院有限公司 | A kind of gradient utilization system of steam energy |
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2012
- 2012-07-19 CN CN201220350161XU patent/CN202675925U/en not_active Expired - Lifetime
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103134043A (en) * | 2013-01-29 | 2013-06-05 | 北京源深节能技术有限责任公司 | Boiler system with U-shaped flue and boiler water charging system |
| CN103134043B (en) * | 2013-01-29 | 2015-04-08 | 北京源深节能技术有限责任公司 | Boiler system with U-shaped flue and boiler water charging system |
| CN103114881A (en) * | 2013-02-25 | 2013-05-22 | 山东岱荣热能环保设备有限公司 | Multi-working-medium backheating type Rankine cycle system |
| CN103114881B (en) * | 2013-02-25 | 2015-11-18 | 山东岱荣热能环保设备有限公司 | Multiple working medium backheating type Rankine cycle system |
| CN104653241A (en) * | 2013-11-18 | 2015-05-27 | 舒少辛 | Waste heat recovery device for indirect air-cooling unit |
| CN103742936A (en) * | 2013-12-30 | 2014-04-23 | 哈尔滨空调股份有限公司 | Steam turbine waste heat exchange system for thermal power plant |
| CN103742936B (en) * | 2013-12-30 | 2016-02-03 | 哈尔滨空调股份有限公司 | Steam turbine waste heat exchange system for thermal power plant |
| CN105626171A (en) * | 2016-03-28 | 2016-06-01 | 西安热工研究院有限公司 | Waste heat utilization system for indirect air-cooling unit |
| CN107152316A (en) * | 2017-07-13 | 2017-09-12 | 中国能源建设集团湖南省电力设计院有限公司 | A kind of gradient utilization system of steam energy |
| CN107152316B (en) * | 2017-07-13 | 2023-08-22 | 中国能源建设集团湖南省电力设计院有限公司 | Cascade utilization system of steam energy |
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