CN103363516A - Circulating fluidized bed boiler with second reheaters - Google Patents
Circulating fluidized bed boiler with second reheaters Download PDFInfo
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- CN103363516A CN103363516A CN201310329406XA CN201310329406A CN103363516A CN 103363516 A CN103363516 A CN 103363516A CN 201310329406X A CN201310329406X A CN 201310329406XA CN 201310329406 A CN201310329406 A CN 201310329406A CN 103363516 A CN103363516 A CN 103363516A
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- temperature reheater
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
- F01K7/16—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type
- F01K7/22—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type the turbines having inter-stage steam heating
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F22—STEAM GENERATION
- F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
- F22B31/00—Modifications of boiler construction, or of tube systems, dependent on installation of combustion apparatus; Arrangements of dispositions of combustion apparatus
- F22B31/0007—Modifications of boiler construction, or of tube systems, dependent on installation of combustion apparatus; Arrangements of dispositions of combustion apparatus with combustion in a fluidized bed
- F22B31/0015—Modifications of boiler construction, or of tube systems, dependent on installation of combustion apparatus; Arrangements of dispositions of combustion apparatus with combustion in a fluidized bed for boilers of the water tube type
- F22B31/003—Modifications of boiler construction, or of tube systems, dependent on installation of combustion apparatus; Arrangements of dispositions of combustion apparatus with combustion in a fluidized bed for boilers of the water tube type with tubes surrounding the bed or with water tube wall partitions
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F22—STEAM GENERATION
- F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
- F22B31/00—Modifications of boiler construction, or of tube systems, dependent on installation of combustion apparatus; Arrangements of dispositions of combustion apparatus
- F22B31/0007—Modifications of boiler construction, or of tube systems, dependent on installation of combustion apparatus; Arrangements of dispositions of combustion apparatus with combustion in a fluidized bed
- F22B31/0084—Modifications of boiler construction, or of tube systems, dependent on installation of combustion apparatus; Arrangements of dispositions of combustion apparatus with combustion in a fluidized bed with recirculation of separated solids or with cooling of the bed particles outside the combustion bed
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23C—METHODS OR APPARATUS FOR COMBUSTION USING FLUID FUEL OR SOLID FUEL SUSPENDED IN A CARRIER GAS OR AIR
- F23C10/00—Fluidised bed combustion apparatus
- F23C10/02—Fluidised bed combustion apparatus with means specially adapted for achieving or promoting a circulating movement of particles within the bed or for a recirculation of particles entrained from the bed
- F23C10/04—Fluidised bed combustion apparatus with means specially adapted for achieving or promoting a circulating movement of particles within the bed or for a recirculation of particles entrained from the bed the particles being circulated to a section, e.g. a heat-exchange section or a return duct, at least partially shielded from the combustion zone, before being reintroduced into the combustion zone
- F23C10/08—Fluidised bed combustion apparatus with means specially adapted for achieving or promoting a circulating movement of particles within the bed or for a recirculation of particles entrained from the bed the particles being circulated to a section, e.g. a heat-exchange section or a return duct, at least partially shielded from the combustion zone, before being reintroduced into the combustion zone characterised by the arrangement of separation apparatus, e.g. cyclones, for separating particles from the flue gases
- F23C10/10—Fluidised bed combustion apparatus with means specially adapted for achieving or promoting a circulating movement of particles within the bed or for a recirculation of particles entrained from the bed the particles being circulated to a section, e.g. a heat-exchange section or a return duct, at least partially shielded from the combustion zone, before being reintroduced into the combustion zone characterised by the arrangement of separation apparatus, e.g. cyclones, for separating particles from the flue gases the separation apparatus being located outside the combustion chamber
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Fluidized-Bed Combustion And Resonant Combustion (AREA)
Abstract
The invention discloses a circulating fluidized bed boiler with second reheaters. The boiler comprises an air compartment, an air distributor, a combustion chamber, a primary air system, a second air system, a horizontal flue, a plurality of cyclone separators, a plurality of external heat exchangers and a back-end flue. The contraction ratio of the lower part of the combustion chamber is 0.2-0.49. A flue gas damper is arranged in the back-end flue. The back-end flue contains at least two parallel flues. A low-temperature superheater is arranged in one parallel flue. A primary low-temperature reheater is arranged in the other parallel flue. A medium-temperature superheater is arranged in at least one external heat exchanger. A primary high-temperature reheater is arranged in at least one external heat exchanger. A second low-temperature reheater and a second high-temperature reheater are arranged in at least one external heat exchanger. A high-temperature superheater is arranged at the upper part of the combustion chamber. The boiler can effectively raise the heat-transfer intensity inside the boiler, and cooperates with optimized heating surface arrangement modes to achieve effective combination of second reheaters and a circulating fluidized bed, and therefore the aims of raising power generating efficiency of coal power units and reducing pollutant discharge are achieved, and long and high-efficient running of the device can be guaranteed.
Description
Technical field
The present invention relates to a kind of CFBB, particularly with the CFBB of double reheat.
Background technology
China has now become world-class production of energy state and country of consumption, and nearly ten years coal proportion in energy resource structure and is estimated and will be continued to the middle of this century always about 70%.Yet, high-sulfur higher with colm proportion ash-rich in the coal resources in China, for this reason, improve unit generation efficient, reducing pollutant emission is the central task of power industry.
Combustion technology of circulating fluidized is that the low-grade fuel high-efficiency cleaning burning in unique realization commercialization of present stage and maximization that grew up in nearly 30 years utilizes technology, with its impayable low pollutant emission advantage, efficiently solve energy-conservation and problems environmental protection two aspects, represented a much progress of current combustion technology.
At present, improving steam parameter, increasing hot number of times again is the effective ways that improve unit generation efficient, but CFBB is running into larger difficulty aspect the further raising unit generation efficient.This be because, CFBB is under rated load, the normal combustion temperature is no more than 930 ℃ usually in the stove, with respect to other combustion system such as the boilers such as pulverized-coal fired boiler or cyclone-combustion stove, its ignition temperature is on the low side, the problem of high parameter heating surface metal material causes running into larger bottleneck aspect the further raising steam parameter in addition; If increase again hot number of times, then need consider the position of heating surface, pulverized-coal fired boiler has the double reheat heating surface is arranged in precedent in the higher furnace outlet horizontal flue of cigarette temperature, but because the difference on the Gas-solid Two-phase Flow, the furnace outlet place flue gas of CFBB carries a large amount of solid particles, and velocity of flue gas can be up to about 30m/s, if double reheat heating surface is arranged in this zone, its wearing and tearing are inevitable serious, so that boiler is difficult to safe operation; As secondary reheater is arranged in the back-end ductwork entirely, then owing to also arranging other heating surface in the back-end ductwork, the Heat absorption fraction of each heating surface is difficult to adjusted in concert, regulates at temperature to be difficult to arrange.In addition, what is more important, double reheat vapour pressure ratio single reheat steam pressure is lower, and is unlikely excessive for the double reheat steam pressure is lost, and needs to adopt lower steam flow rate, yet, lower steam speed also makes steam very limited to the cooling capacity of heating surface tube wall, and namely the heating surface pipe wall temperature is closer to the temperature of the outer medium of pipe, therefore for considering the hot bearing capacity of heating surface pipe, that steam flow rate can not be got again is excessively low, and the two is difficult to balance; Simultaneously, in the boiler startup process, be the unlikely overtemperature dry combustion method of protection reheater, tend to adopt as introducing the methods such as main steam cooling and protect reheater.The introducing of secondary reheater has increased hot heating surface area again, make the Heat absorption fraction of reheater surpass the Heat absorption fraction of superheater, when taking the main steam cooling, will need more quantity of steam, namely original quantity of steam is difficult to satisfied protect simultaneously single reheat device and secondary reheater; Below all limited the combination of double reheat and Combustion technology of circulating fluidized, made the further raising of Circulating Fluidized Bed Boilers efficient be difficult to realize.
Summary of the invention
The objective of the invention is for the prior art above shortcomings and overcome the difficult point that above-mentioned double reheat combines with CFBB, a kind of CFBB with double reheat is provided, it is not in the situation that significantly increase fuel energy Effective Raise furnace heat transfer intensity and heat utilization ratio, thereby realize effective combination of double reheat and CFBB, reach the purpose of further raising coal group of motors generating efficiency and low pollutant emission coexistence, and the long-term efficient operation of assurance equipment.
For achieving the above object, a kind of CFBB with double reheat of the present invention, comprise air compartment, comprise air-distribution device, burner hearth, primary air system, secondary air system, the horizontal flue of air distribution plate and blast cap, at least three cyclone separators, at least three outer heat exchangers, back-end ductwork, be provided with the water-cooling wall with upper and lower header in the burner hearth, it is characterized in that described lower furnace portion is 0.2-0.49 along the shrinkage ratio of depth direction; Described back-end ductwork adopts parallel Multi-flue structure, at least comprise two parallel flues, be provided with gas proportioning damper in the every flue, gas proportioning damper at least one parallel flue was provided with low temperature superheater before the flow of flue gas direction, gas proportioning damper in another parallel flue at least was provided with low-temperature reheater one time before the flow of flue gas direction, arrange economizer and air preheater in the back-end ductwork of all gas baffles after the flow of flue gas direction; In at least one outer heat exchanger, be provided with medium temperature overheater, in at least one outer heat exchanger, be provided with high temperature reheater one time, in at least one outer heat exchanger, be provided with the secondary low-temperature reheater, at least one outer heat exchanger, be provided with the secondary high-temperature reheater; In stove, be provided with high temperature superheater; The upper collecting chamber of water-cooling wall, low temperature superheater, medium temperature overheater and high temperature superheater are communicated with successively by pipeline, and a low-temperature reheater and a high temperature reheater are by pipeline connection, and secondary low-temperature reheater and secondary high-temperature reheater pass through pipeline connection.
Above-mentioned burner hearth can be single burner hearth, and its underpart is provided with an air distribution plate, and air distribution plate is provided with several blast caps.
Above-mentioned burner hearth also can adopt the two air distributor structures of single burner hearth, and its underpart is provided with two air distribution plates, and every air distribution plate is provided with several blast caps.
Above-mentioned burner hearth also can be annular furnace, and its underpart is provided with the air distribution plate of annular, and this air distribution plate is provided with several blast caps.
During use, the Boiler Steam of existing certain degree of superheat enters the steam turbine high-pressure cylinder acting from water-cooling wall flow through successively after out low temperature superheater, medium temperature overheater and high temperature superheater; After flowing through a low-temperature reheater and a high temperature reheater successively, steam turbine high-pressure cylinder steam out enters the acting of steam turbine the first intermediate pressure cylinder; From steam turbine the first intermediate pressure cylinder steam out flow through successively again secondary low-temperature reheater and secondary high-temperature reheater, enter successively afterwards the acting of steam turbine the second intermediate pressure cylinder and turbine low pressure cylinder;
For realizing effective combination of double reheat and Combustion technology of circulating fluidized, need the aspect factors such as Consideration of Heat Transfer intensity, heating surface position, steam temperature adjusting and heating surface protection:
Aspect furnace heat transfer, for CFBB, because the power of support fuel and bed material particle is from fan pressure head, for the increment that makes fan energy consumption can not surpass the energy consumption saving amount that double reheat system improves unit efficiency at least, therefore granule density need to be maintained reasonable level.Shrinkage ratio than present boiler hearth of circulating fluidized bed lower furnace depth direction is generally 0.5-0.7, the present invention is controlled to be 0.2-0.49 with lower furnace portion along the shrinkage ratio of depth direction, change under the little condition at primary air fan and overfire air fan pressure head, stronger to the endocorpuscular towing of stove and the ability of carrying secretly, can improve the granule density in upper furnace zone, thereby increase the convection heat transfer' heat-transfer by convection intensity of upper furnace zone Dual-Phrase Distribution of Gas olid, so that carbonated drink side draught heat is improved, satisfy the needs that the double reheat heating surface is introduced CFBB.And large shrinkage ratio structure so that primary air flow to account for the total blast volume share less, it is larger that secondary air flow accounts for the total blast volume share, regulating for the air quantity of Secondary Air provides well-to-do adjustable range.
Aspect the heating surface layout, low temperature superheater all is located at gas baffle along in the flow of flue gas direction parallel flue before with a low-temperature reheater, and with respect to burner hearth, granule density is low herein, therefore heat-transfer intensity and heating surface wear degree also are lower than in the stove, can reduce steel grade.Like this, both economical with materials costs is avoided again too much heating surface is set in stove and the situation that significantly drags down local flue-gas temperature in the stove occurs, and can prevent local cigarette temperature drop to fuel ignition point and is unfavorable for that the phenomenon of fuel after-flame occurs; Medium temperature overheater, high temperature reheater, secondary low-temperature reheater and a secondary high-temperature reheater all are arranged in the outer heat exchanger, external heat exchanger is owing to the high heat transfer strength characteristics of its inner bubbling fluidized bed makes the heating surface pipe temperature closer to particle temperature, and the high heat transfer strength characteristics of bubbling fluidized bed will satisfy the steam parameter needs that can realize double reheat in the high heat transfer intensity in the composite burner and the outer heat exchanger.
Aspect the steam temperature adjusting, by regulating the aperture of respectively organizing gas proportioning damper and the acting in conjunction that passes in and out outer heat exchanger different temperatures ash flow proportional, make the respectively independent adjusting of vapor (steam) temperature of superheater, single reheat device and secondary reheater, in the guaranteed whiles of heating surface steam parameter at different levels, do not reduce unit efficiency, guarantee again the normal operation of economizer and air preheater; In addition, secondary low-temperature reheater and secondary high-temperature reheater are arranged in the outer heat exchanger, the steam that can greatly facilitate secondary reheaters at different levels switches, in boiler at low load operation and shutdown process, can effectively protect the secondary reheater heating surface, avoid the dry combustion method of secondary reheater, guarantee the normal operation of equipment;
As a further improvement on the present invention, the ips of described secondary high-temperature reheater is at least than the large 1.7mm of ips of secondary low-temperature reheater; This is because double reheat vapour pressure ratio single reheat steam pressure is lower, and is unlikely excessive for the double reheat steam pressure is lost, and needs to adopt lower steam flow rate.Yet lower steam speed also makes steam very limited to the cooling capacity of heating surface tube wall, and namely the heating surface pipe wall temperature is closer to the temperature of the outer medium of pipe, and therefore for considering the hot bearing capacity of heating surface pipe, that steam flow rate can not be got again is excessively low.The pressure loss by adjusting the heating surface intraductal working medium and pipe environment temperature of living in and pipe can bear the many factors such as exchange capability of heat, the ips of secondary reheater is done as above requirement, so that the steam flow rate at two places has comparatively significant difference, can satisfy simultaneously the needs of two aspects.
The present invention can realize effective combination of double reheat and CFBB, can on the basis of existing large circulating fluidized bed boiler unit efficiency be improved 1.5%-2% again;
As a further improvement on the present invention, described high temperature superheater can be U-shaped pendant superheater; Be convenient to the flue gas heat exchange with the higher burner hearth central area of temperature, improve heat exchange efficiency;
In sum, the present invention is not in the situation that significantly increase fuel energy Effective Raise furnace heat transfer intensity, and cooperate preferred heating surface arrangement to realize double reheat and the effective combination of CFBB, thereby reach the purpose that improves coal group of motors generating efficiency and low pollutant emission coexistence, and the long-term efficient operation of assurance equipment.
Description of drawings
Fig. 1 is the structural representation of the embodiment of the invention one.
Fig. 2 is the structural representation of the embodiment of the invention two.
Fig. 3 is the left view of Fig. 2.
Fig. 4 is the plan structure schematic diagram of the embodiment of the invention three.
The specific embodiment
The present invention is further detailed explanation below in conjunction with accompanying drawing.
Embodiment one
As shown in Figure 1, this embodiment is the CFBB with double reheat, comprise air compartment 14, single burner hearth 11, be provided with the air-distribution device of single air distribution plate 15 and several blast cap (not shown), be provided with the primary air system of blower fan 16 and airduct, be provided with the secondary air system of blower fan 17 and airduct, horizontal flue 18, three cyclone separators 1, three outer heat exchangers 2, back-end ductwork 3, cyclone separator 1 connects horizontal flue 18, the bottom of back-end ductwork 3 and burner hearth 11, the two ends of three outer heat exchangers 2 link to each other with separately cyclone separator 1 and the bottom of burner hearth 11 respectively, reach furnace roof around the burner hearth 11 by on being with, the water-cooling wall 19 of lower header forms, and described burner hearth 11 bottoms are 0.3 along the shrinkage ratio (i.e. L1/L2 among the figure) of depth direction; Be provided with three groups of gas baffles 12 in the described back-end ductwork 3, gas baffle 12 comprises three parallel flues 20 along the back-end ductwork 3 before the flow of flue gas direction, in the back-end ductwork 3 of gas baffle 12 after the flow of flue gas direction, be provided with economizer 13 and air preheater 21, in a parallel flue 20, be provided with low temperature superheater 4, in another parallel flue 20, be provided with low-temperature reheater 7 one time, in last parallel flue 20, be provided with other heating surfaces; In an outer heat exchanger 2, be provided with medium temperature overheater 5, in another outer heat exchanger 2, be provided with one time high temperature reheater 8, in another outer heat exchanger 2, be provided with secondary low-temperature reheater 9 and secondary high-temperature reheater 10; In burner hearth 11, be provided with high temperature superheater 6; The upper collecting chamber of water-cooling wall 19, low temperature superheater 4, medium temperature overheater 5 and high temperature superheater 6 are communicated with successively by pipeline, a low-temperature reheater 7 and a high temperature reheater 8 pass through pipeline connection, secondary low-temperature reheater 9 passes through pipeline connection with secondary high-temperature reheater 10, the ips that secondary low-temperature reheater 9 adopts is 48mm, and the ips that secondary high-temperature reheater 10 adopts is 52.5mm.
During use, the Boiler Steam of existing certain degree of superheat enters the steam turbine high-pressure cylinder acting from water-cooling wall 19 flow through successively after out low temperature superheater 4, medium temperature overheater 5 and high temperature superheater 6; After flowing through a low-temperature reheater 7 and a high temperature reheater 8 successively, steam turbine high-pressure cylinder steam out enters the acting of steam turbine the first intermediate pressure cylinder; From steam turbine the first intermediate pressure cylinder steam out flow through successively again secondary low-temperature reheater 9 and secondary high-temperature reheater 10, enter successively afterwards the acting of steam turbine the second intermediate pressure cylinder and turbine low pressure cylinder;
The boiler hearth of circulating fluidized bed endoparticle is risen by the gas towing, theoretical and facts have proved according to fluidization, the required blast of burner hearth is approximately equal to stove endoparticle weight, i.e. stock on the unit are, the available pressure unit representation, and can calculate by this zone granule density.For CFBB, furnace heat transfer is mainly the convection heat transfer' heat-transfer by convection between Dual-Phrase Distribution of Gas olid body and heating surface, and this convection heat transfer' heat-transfer by convection is relevant with concentration of solid particles, and concentration of solid particles is higher, and heat-transfer effect is better, and heat-transfer intensity is higher.The present invention is owing to the adding of double reheat heating surface, and total heat output increases, and therefore needs to guarantee higher heat-transfer intensity in the stove, and namely need to there be higher granule density in the upper furnace zone; Simultaneously because the power of support material from fan pressure head, and is to make the increment of fan energy consumption can not surpass at least the energy consumption saving amount that double reheat system improves unit efficiency, therefore granule density need to be maintained reasonable level.
Shrinkage ratio than present boiler hearth of circulating fluidized bed bottom is 0.5-0.7, the present embodiment lower furnace portion is 0.3 along the shrinkage ratio of depth direction, can make two blower fans 16,17 under the little condition of pressure head variation, more obvious to burner hearth 11 endocorpuscular towing effects, when real work, can significantly improve the granule density in upper furnace zone, the ratio (usually between 0.2～0.5) of the pressure drop of furnace outlet area unit height and the average unit height pressure drop of burner hearth (ratio of bed pressure drop and furnace height) is improved approximately 0.1 again, thereby increased the heat-transfer intensity in the stove, can satisfy the needs that the double reheat heating surface is arranged.
Low temperature superheater 4 all is located at gas baffle 12 along in the flow of flue gas direction parallel flue 20 before with a low-temperature reheater 7, with respect to burner hearth 11, granule density is low herein, so heat-transfer intensity and heating surface wear degree also be lower than in the stove, can reduce steel grade.Like this, both economical with materials costs is avoided again too much heating surface is set in stove and the situation that significantly drags down local flue-gas temperature in the stove occurs, and can prevent local cigarette temperature drop to fuel ignition point and be unfavorable for that the phenomenon of fuel after-flame occurs; Medium temperature overheater 5, high temperature reheater 8, secondary low-temperature reheater 9 and a secondary high-temperature reheater 10 all are located in the outer heat exchanger 2, and the high heat transfer intensity in the composite burner and the high heat transfer strength characteristics of outer heat exchanger 2 interior bubbling fluidized beds will satisfy the steam parameter needs that can realize double reheat.
By regulating the aperture of respectively organizing gas baffle 12, can regulate the exhaust gas volumn of each parallel flue 20, thereby regulate the Heat absorption fraction of low temperature superheater 4, a low-temperature reheater 7, enter the vapor (steam) temperature that the solid particle flow of outer heat exchanger 2 interior different temperatures can be regulated secondary reheater by adjusting, thereby the steam temperature of different heating surfaces is all independently regulated, namely in the guaranteed whiles of heating surface steam parameter at different levels, do not reduce unit efficiency.Secondary low-temperature reheater 9 and secondary high-temperature reheater 10 are arranged in the outer heat exchanger 2, the steam that can greatly facilitate the secondary reheater system switches, in boiler at low load operation and shutdown process, effectively protect the secondary reheater heating surface, avoid the dry combustion method of secondary reheater, guarantee the normal operation of equipment; The less secondary low-temperature reheater 9 of internal diameter is so that steam flow rate is higher, but the temperature that effective cooling should the zone heating surface pipe, the secondary high-temperature reheater 10 interior steam flow rates that internal diameter is larger are slower, can make the steam pressure loss of secondary reheater maintain very low level, thus so that all to some extent assurances of the pressure and temperature of double reheat steam.Compare with the single reheat Circulating Fluidized Bed Boilers with steam parameter, the present invention introduces double reheat can improve 1.5%-2% again with unit efficiency;
Embodiment two
Such as Fig. 2, shown in Figure 3, this embodiment compares with embodiment one, its difference only is: its burner hearth 26 is the two air distributor structures of single burner hearth, the bottom is provided with two air distribution plates 22, respectively be provided with several blast cap (not shown) on two air distribution plates 22, described burner hearth 26 bottoms are 0.20 along the shrinkage ratio (i.e. L3/L4 among the figure) of depth direction, respectively be provided with three cyclone separators 1 and three outer heat exchangers 2 in burner hearth 26 both sides, be provided with medium temperature overheater 5 in two outer heat exchangers 2 therein, in other two outer heat exchangers 2, be provided with high temperature reheater 8 one time, in another outer heat exchanger 2, be provided with secondary low-temperature reheater 9, in another outer heat exchanger 2, be provided with secondary high-temperature reheater 10; The ips that secondary low-temperature reheater 9 adopts is 46mm, and the ips that secondary high-temperature reheater 10 adopts is 48mm.
The operation principle of the present embodiment and embodiment one are similar, burner hearth 26 bottoms are 0.2 along the shrinkage ratio of depth direction, the ratio (usually between 0.2～0.5) of the pressure drop of furnace outlet area unit height and the average unit height pressure drop of burner hearth (ratio of bed pressure drop and furnace height) is improved approximately 0.13 again, thereby the realization double reheat is planted the effective combination of CFBB of chamber structure therewith, reach the purpose that improves coal group of motors generating efficiency and low pollutant emission coexistence, and the long-term efficient operation of assurance equipment.
Embodiment three
As shown in Figure 4, this embodiment compares with embodiment two, and its difference only is: burner hearth 27 is annular furnace, and its underpart is provided with the air distribution plate of annular, and this air distribution plate is provided with several blast caps; Described burner hearth 27 bottoms are 0.49 along the shrinkage ratio (i.e. L5/L6 among the figure) of depth direction, the ratio (usually between 0.2～0.5) of the pressure drop of furnace outlet area unit height and the average unit height pressure drop of burner hearth (ratio of bed pressure drop and furnace height) is improved approximately 0.06 again, thereby increased the heat-transfer intensity in the stove, can satisfy the needs of double reheat heating surface.Be provided with six cyclone separators 1 and six outer heat exchangers 2 around burner hearth 27;
In sum, the present invention is by changing lower furnace portion along the shrinkage ratio of depth direction, improve the granule density in upper furnace zone to rational level, the ratio (usually between 0.2～0.5) of the pressure drop of furnace outlet area unit height and the average unit height pressure drop of burner hearth (ratio of bed pressure drop and furnace height) is improved approximately 0.05～0.15 again, in the situation that do not increase fuel energy Effective Raise furnace heat transfer intensity, and cooperate the relation of preferred heating surface arrangement and secondary reheater ips at different levels with effective combination of realization double reheat and CFBB, thereby reach the purpose that improves coal group of motors generating efficiency and low pollutant emission coexistence, and the long-term efficient operation of assurance equipment.
Claims (6)
1. CFBB with double reheat, comprise air compartment, comprise air-distribution device, burner hearth, primary air system, secondary air system, the horizontal flue of air distribution plate and blast cap, at least three cyclone separators, at least three outer heat exchangers, back-end ductwork, be provided with the water-cooling wall with upper and lower header in the burner hearth, it is characterized in that described lower furnace portion is 0.2-0.49 along the shrinkage ratio of depth direction; Described back-end ductwork adopts parallel Multi-flue structure, at least comprise two parallel flues, be provided with gas proportioning damper in the every flue, gas proportioning damper at least one parallel flue was provided with low temperature superheater before the flow of flue gas direction, gas proportioning damper in another parallel flue at least was provided with low-temperature reheater one time before the flow of flue gas direction, arrange economizer and air preheater in the back-end ductwork of all gas baffles after the flow of flue gas direction; In at least one outer heat exchanger, be provided with medium temperature overheater, in at least one outer heat exchanger, be provided with high temperature reheater one time, in at least one outer heat exchanger, be provided with the secondary low-temperature reheater, at least one outer heat exchanger, be provided with the secondary high-temperature reheater; In stove, be provided with high temperature superheater; The upper collecting chamber of water-cooling wall, low temperature superheater, medium temperature overheater and high temperature superheater are communicated with successively by pipeline, and a low-temperature reheater and a high temperature reheater are by pipeline connection, and secondary low-temperature reheater and secondary high-temperature reheater pass through pipeline connection.
2. a kind of CFBB with double reheat as claimed in claim 1 is characterized in that described burner hearth is single burner hearth list air distributor structure, and its underpart is provided with an air distribution plate, and air distribution plate is provided with several blast caps.
3. a kind of CFBB with double reheat as claimed in claim 1 is characterized in that described burner hearth adopts the two air distributor structures of single burner hearth, and its underpart is provided with two air distribution plates, and every air distribution plate is provided with several blast caps.
4. a kind of CFBB with double reheat as claimed in claim 1 is characterized in that described burner hearth is annular furnace, and its underpart is provided with the air distribution plate of annular, and this air distribution plate is provided with several blast caps.
5. such as the arbitrary described a kind of CFBB with double reheat of claim 1 to 4, the ips that it is characterized in that described secondary high-temperature reheater is at least greater than the ips 1.7mm of secondary low-temperature reheater.
6. a kind of CFBB with double reheat as claimed in claim 5 is characterized in that described high temperature superheater is U-shaped pendant superheater.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310329406.XA CN103363516B (en) | 2013-08-01 | 2013-08-01 | A kind of CFBB with double reheat |
| PCT/CN2014/082913 WO2015014233A1 (en) | 2013-08-01 | 2014-07-24 | Circulating fluidized bed boiler having secondary reheat |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201310329406.XA CN103363516B (en) | 2013-08-01 | 2013-08-01 | A kind of CFBB with double reheat |
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| CN103363516A true CN103363516A (en) | 2013-10-23 |
| CN103363516B CN103363516B (en) | 2015-10-28 |
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Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2015014233A1 (en) * | 2013-08-01 | 2015-02-05 | 东方电气集团东方锅炉股份有限公司 | Circulating fluidized bed boiler having secondary reheat |
| CN104501142A (en) * | 2014-12-23 | 2015-04-08 | 哈尔滨锅炉厂有限责任公司 | Secondary re-heating device and re-heating method for circulating fluidized bed boiler |
| CN104728823A (en) * | 2015-03-17 | 2015-06-24 | 西安热工研究院有限公司 | Novel supercritical carbon dioxide coal-fired boiler |
| WO2018036536A1 (en) * | 2016-08-24 | 2018-03-01 | 东方电气集团东方锅炉股份有限公司 | 1000 mw ultra-supercritical parameter circulating fluidized-bed boiler |
| CN108180470A (en) * | 2017-11-28 | 2018-06-19 | 东南大学 | The fire coal circulating fluid bed boiler of supercritical carbon dioxide and electricity generation system and electricity-generating method |
| CN111536496A (en) * | 2020-04-21 | 2020-08-14 | 东南大学 | Pressurized oxygen-enriched combustion circulating fluidized bed boiler and method thereof |
| US11333349B2 (en) * | 2018-07-19 | 2022-05-17 | Korea Institute Of Industrial Technology | Fluid sand falling type circulating fluidized bed boiler with a plurality of risers and method of operating the same |
| CN114688546A (en) * | 2021-12-29 | 2022-07-01 | 浙江大学 | Hot ash returning flow control device and method capable of achieving lateral air distribution and achieving double adjustment of bed temperature and steam temperature |
Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1120144A (en) * | 1994-12-23 | 1996-04-10 | 燃烧工程有限公司 | Reheater protection in a circulating fluidized bed steam generator |
| PL180643B1 (en) * | 1994-08-25 | 2001-03-30 | Ramesh D Khanna | System for and method of secondary feeding industrial or municipal circulating fluidised bed furnace boilers capable to reduce sox and nox emission form such boilers |
| PL180911B1 (en) * | 1995-01-05 | 2001-05-31 | Foster Wheeler Energia Oy | Fluidised bed unit with flow compensation |
| CN1427201A (en) * | 2001-11-12 | 2003-07-02 | 石川岛播磨重工业株式会社 | Circulation fluidized layer boiler |
| CN101438099A (en) * | 2006-05-10 | 2009-05-20 | 福斯特韦勒能源股份公司 | A fluidized bed heat exchanger for a circulating fluidized bed boiler and a circulating fluidized bed boiler with a fluidized bed heat exchanger |
| CN101986024A (en) * | 2010-11-18 | 2011-03-16 | 上海锅炉厂有限公司 | Arrangement structure of all levels of superheaters of circulating fluidized bed boiler |
| CN102353044A (en) * | 2011-09-09 | 2012-02-15 | 北京君达能源投资有限公司 | Gas combustion-supporting device of recirculating fluidized bed and combustion control device of recirculating fluidized bed |
| CN203431837U (en) * | 2013-08-01 | 2014-02-12 | 东方电气集团东方锅炉股份有限公司 | Circulating fluidized bed boiler with secondary reheat function |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5442919A (en) * | 1993-12-27 | 1995-08-22 | Combustion Engineering, Inc. | Reheater protection in a circulating fluidized bed steam generator |
| DE19834881B4 (en) * | 1998-05-18 | 2007-06-21 | Lentjes Gmbh | Fluidized bed combustion system with steam generation |
| JP3554518B2 (en) * | 2000-02-21 | 2004-08-18 | 株式会社タクマ | High temperature and high pressure circulating fluidized bed boiler using waste as fuel. |
| CN102374524B (en) * | 2011-10-28 | 2013-06-26 | 西安热工研究院有限公司 | Secondary reheating system for power-station boiler |
| CN202501442U (en) * | 2012-02-29 | 2012-10-24 | 东方电气集团东方锅炉股份有限公司 | Boiler with three flues arranged at tail part thereof |
| CN103363516B (en) * | 2013-08-01 | 2015-10-28 | 东方电气集团东方锅炉股份有限公司 | A kind of CFBB with double reheat |
-
2013
- 2013-08-01 CN CN201310329406.XA patent/CN103363516B/en active Active
-
2014
- 2014-07-24 WO PCT/CN2014/082913 patent/WO2015014233A1/en active Application Filing
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| PL180643B1 (en) * | 1994-08-25 | 2001-03-30 | Ramesh D Khanna | System for and method of secondary feeding industrial or municipal circulating fluidised bed furnace boilers capable to reduce sox and nox emission form such boilers |
| CN1120144A (en) * | 1994-12-23 | 1996-04-10 | 燃烧工程有限公司 | Reheater protection in a circulating fluidized bed steam generator |
| PL180911B1 (en) * | 1995-01-05 | 2001-05-31 | Foster Wheeler Energia Oy | Fluidised bed unit with flow compensation |
| CN1427201A (en) * | 2001-11-12 | 2003-07-02 | 石川岛播磨重工业株式会社 | Circulation fluidized layer boiler |
| CN101438099A (en) * | 2006-05-10 | 2009-05-20 | 福斯特韦勒能源股份公司 | A fluidized bed heat exchanger for a circulating fluidized bed boiler and a circulating fluidized bed boiler with a fluidized bed heat exchanger |
| CN101986024A (en) * | 2010-11-18 | 2011-03-16 | 上海锅炉厂有限公司 | Arrangement structure of all levels of superheaters of circulating fluidized bed boiler |
| CN102353044A (en) * | 2011-09-09 | 2012-02-15 | 北京君达能源投资有限公司 | Gas combustion-supporting device of recirculating fluidized bed and combustion control device of recirculating fluidized bed |
| CN203431837U (en) * | 2013-08-01 | 2014-02-12 | 东方电气集团东方锅炉股份有限公司 | Circulating fluidized bed boiler with secondary reheat function |
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2015014233A1 (en) * | 2013-08-01 | 2015-02-05 | 东方电气集团东方锅炉股份有限公司 | Circulating fluidized bed boiler having secondary reheat |
| CN104501142A (en) * | 2014-12-23 | 2015-04-08 | 哈尔滨锅炉厂有限责任公司 | Secondary re-heating device and re-heating method for circulating fluidized bed boiler |
| CN104728823A (en) * | 2015-03-17 | 2015-06-24 | 西安热工研究院有限公司 | Novel supercritical carbon dioxide coal-fired boiler |
| WO2018036536A1 (en) * | 2016-08-24 | 2018-03-01 | 东方电气集团东方锅炉股份有限公司 | 1000 mw ultra-supercritical parameter circulating fluidized-bed boiler |
| CN108180470A (en) * | 2017-11-28 | 2018-06-19 | 东南大学 | The fire coal circulating fluid bed boiler of supercritical carbon dioxide and electricity generation system and electricity-generating method |
| CN108180470B (en) * | 2017-11-28 | 2018-10-23 | 东南大学 | The fire coal circulating fluid bed boiler of supercritical carbon dioxide and electricity generation system and electricity-generating method |
| US11333349B2 (en) * | 2018-07-19 | 2022-05-17 | Korea Institute Of Industrial Technology | Fluid sand falling type circulating fluidized bed boiler with a plurality of risers and method of operating the same |
| CN111536496A (en) * | 2020-04-21 | 2020-08-14 | 东南大学 | Pressurized oxygen-enriched combustion circulating fluidized bed boiler and method thereof |
| CN114688546A (en) * | 2021-12-29 | 2022-07-01 | 浙江大学 | Hot ash returning flow control device and method capable of achieving lateral air distribution and achieving double adjustment of bed temperature and steam temperature |
| CN114688546B (en) * | 2021-12-29 | 2023-01-10 | 浙江大学 | Hot ash returning flow control device and method capable of achieving lateral air distribution and achieving double adjustment of bed temperature and steam temperature |
Also Published As
| Publication number | Publication date |
|---|---|
| CN103363516B (en) | 2015-10-28 |
| WO2015014233A1 (en) | 2015-02-05 |
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