CN102588986B - Optimized boiler designing method based on air cooling dry slagging technology - Google Patents
Optimized boiler designing method based on air cooling dry slagging technology Download PDFInfo
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Abstract
The invention discloses an optimized boiler designing method based on air cooling dry slagging technology. The optimized boiler designing method includes computing heat absorption capacity of an air side of an air preheater and flue exhausting temperature of a flue gas side of the air preheater during actual running according to disorganized leaked air generated by a dry slagging system when a boiler runs normally, further determining heat loss of a boiler system and obtaining reduction of heat efficiency of the boiler finally; and guiding selection of an air feeder according to the counted disorganized leaked air. The designing method can be used for designing the boiler, heat efficiency of the boiler can be guaranteed, simultaneously, air quantity of the air feeder of the boiler can be more reasonably determined, and accordingly purposes of improving running economical efficiency, reducing parameters of equipment, lowering manufacturing cost, reducing energy consumption, saving energy and reducing emission are achieved.
Description
Technical field
The present invention relates to the boiler design method in thermal power plant, particularly a kind of method for designing that adopts air cooling way to carry out dry slag-discharging boiler system.
Background technology
The important technical of energy-saving and emission-reduction when the boiler optimization in thermal power plant designs, its target is necessarily to meet under the condition of operation satisfied, obtains the running status of high efficiency, low pollution emission by adjusting the operational factors such as boiler wind speed adjustment, coal supply.The matching design of the operational factor such as air distribution, coal supply of boiler has direct impact to boiler combustion status, different air distribution, coal supply parameter the situation such as discharge capacity and high temperature corrosion that can directly cause different boiler efficiencies, dusty gas is set.
For different steam generator systems, the configuration of its parameter also has greatly difference.Air cooling dry dreg removing system is in the eighties in 20th century, is developed by Italian MAGALDI company.The Hebei state 2 × 350MW of Hua Sanhe power plant unit is China's project of Introduced From Abroad air-cooled dry type slag removal equipment and system first, put into operation in December, 1999, after this, Some Domestic research manufacturer independent research and development air cooling dry dreg removing system, and acquire large-scale application within the extremely short time, at the beginning of 2011, more than 360 platform coal-burning boiler generating sets of domestic about You130Duo Zuo power plant have adopted air-cooled dry-type slag discharging device systems, the nearly 57GW of total installation of generating capacity.
Air cooling dry dreg removing system utilizes natural air (hereinafter referred to as cooling air) as cooling medium, the equipment that the temperature of boiler bottom slag is reduced.The process that its heat is transmitted mainly completes by convection heat transfer' heat-transfer by convection and radiant heat transfer, high temperature bottom slag and cooling air reverse movement, high temperature bottom slag discharges amount of heat and is cooled, and the cooling air absorbing after heat enters in the boiler furnace of higher temperature, plays combustion-supporting wind action in boiler furnace.
In order to guarantee under all operating modes (boiler load variation, boiler purging, ature of coal variation etc.), the deslagging temperature of dry-type slag extractor is no more than design load, and meets the service requirement of follow-up equipment, and cooling air total amount should meet the requirement of maximum boiler slag removal amount.But when actual motion, operations staff's more attention is whether dry dreg removing system outlet slag temperature transfinites, and how to guarantee the safe operation of follow-up equipment.Therefore, in the time of the intake of the dry dreg removing system of design, be to be all greater than the needed cooling air quantity of boiler slag removal amount substantially, this must cause too much (being designated hereinafter simply as " inorganization " leaks out) of combustion air that enters burner hearth.
In pnenmatic slag handling system surfaces, see by cooling air recovery boiler deslagging heat, play positive role to promoting boiler efficiency, in fact really not so, under the impact of leaking out in this " inorganization ", pnenmatic slag handling system is to boiler performance and move disadvantageous aspect and mainly contain: larger " inorganization " leaked out and will on the flame kernel causing in boiler furnace, be moved, cause burning of coal degree in boiler to reduce, and may cause curtain wall coking; Also can exert an influence to air stage feeding system simultaneously; Most importantly the increase of leaking out of this " inorganization ", by " in a organized way " wind by air preheater is reduced, causes the cooling air deficiency of air preheater, affects air preheater heat exchange and causes exhaust gas temperature to improve, and has reduced on the contrary boiler efficiency.In conjunction with the practical operation situation of domestic Dry Slag Removal System, theory is calculated and is shown, the existence that this " inorganization " of dry dreg removing system leaked out, has caused exhaust gas temperature rising, when actual motion, reduce approximately 0.2～0.5 percentage point of boiler efficiency, even more.Designing unit, carrying out not counting when boiler smoke wind system calculates the inleakage of dry dreg removing system, does not consider leaking out of dry dreg removing system yet while causing pressure fan type selecting, make pressure fan type selecting bigger than normal, and energy consumption increases.
Summary of the invention
The technical issues that need to address of the present invention are to provide one can effectively improve boiler operating efficiency, reduces the boiler optimization method for designing of steam generator system energy consumption.
For solving the problems of the technologies described above, the technical solution adopted in the present invention is:
Boiler optimization method for designing based on air cooling dry deslagging technique, leak out according to the boiler inorganization that dry dreg removing system produces in normal course of operation, caloric receptivity and the air preheater fume side exhaust gas temperature of air preheater air side while calculating actual motion, the thermal loss of further determining steam generator system, finally draws boiler thermal output; The concrete grammar of boiler optimization design operates according to the following steps:
A. the caloric receptivity of air side while first calculating air preheater actual motion; The cold blast rate of setting air preheater air side is reduced to △ D, and unit is kg/s, and the inorganization air leakage coefficient of dry dreg removing system is α
gPZ;
A1. calculate Theory of Boiler Combustion air capacity, the computing formula of theoretical air requirement is
V
n°=0.0889(C
ar+0.375S
ar)+0.265H
ar-0.0333O
ar
V in formula
n°----theoretical air requirement, Nm
3/ kg
C
ar----coal-fired As-received carbon content, %
S
ar----coal-fired As-received sulfur content, %
H
ar----coal-fired As-received hydrogen content, %
O
ar----coal-fired As-received oxygen content, %
A2. calculate boiler combustion amount of actual air for combustion, the computing formula of amount of actual air for combustion is
V
n°'=V
n°（1+0.0016d)
V in formula
n° '----boiler amount of actual air for combustion, Nm
3/ kg
D----theoretical air water capacity, g/kg
A3. the cold wind reduction of air preheater air side while calculating steam generator system actual motion, computing formula is
△D＝αGPZρV
n°'B
j/3.6
V in formula
n° '---boiler amount of actual air for combustion, Nm
3/ kg
ρ---atmospheric density under-standard state, 1.293kg/m
3
B
j----boiler fired coal consumption, t/h
A4. the cold wind of air preheater air side caloric receptivity while calculating actual motion, computing formula is
Q
1=D
k1*C
1*△T
1+(D
k2-△D)*C
2*△T
2
D in formula
k1---wind mass flow of-air preheater side, kg/s
D
k2----air preheater side secondary air mass flow, kg/s
C
1wind mean specific heat of----cold, kj/ (kg ℃)
C
2----cold Secondary Air mean specific heat, kj/ (kg ℃)
△ T
1---wind of air preheater is imported and exported the temperature difference, ℃
△ T
2---air preheater Secondary Air is imported and exported the temperature difference, ℃
B. calculate the exhaust gas temperature of air preheater fume side;
The thermal discharge of air preheater fume side is the caloric receptivity of air preheater air side, and air preheater fume side thermal discharge is
Q
y=Q
1
The exhaust gas temperature that calculates air preheater fume side, the computing formula of air preheater flue gas fume side exhaust gas temperature is
T
yo=T
yi-Q
y/(D
yC
y)
D in formula
y----air preheater flue gas mass flow, kg/s
C
y----flue gas mean specific heat, kj/ (kg ℃)
T
yi---air preheater gas approach temperature, ℃
C. the thermal loss of steam generator system while calculating actual motion, and according to the rise of the heat Calculation air preheater fume side exhaust gas temperature of loss;
Air preheater gas approach temperature T when actual motion
yiremain unchanged, according to air preheater exhanst gas outlet temperature T
yocalculate air preheater fume side loses heat, computing formula is
△Q=△D*C
2*△T
2
According to the heat of air preheater fume side loss, calculate the rise of exhaust gas temperature, computing formula is
△T
yo=△Q/(D
yC
y)
D. calculate boiler efficiency according to above-mentioned result of calculation
The thermal loss calculating according to step C calculates the flue gas loss rate of steam generator system, and computing formula is
△q
2=3.6△Q/(1000B
jQ
r)
Formula Q
r---beyond-boiler, input the heat of boiler, by coal-fired low heat valve, Mj/kg
The thermal efficiency of steam generator system while finally calculating actual motion, computing formula is
η
gl=100-(q
2+△q
2+q
3+q
4+q
5+q
6)-0.3
Q in formula
2-boiler exhaust gas heat loss
Q
3-fuel gas heat loss due to incomplete combustion
Q
4-heat loss of imperfect solid combustion
Q
5-radiation loss
Q
6-other heat loss
E. leak out pressure fan is carried out to accurate type selecting according to the boiler inorganization that dry dreg removing system produces in normal course of operation, concrete type selection calculation process is as described below:
E1. the excess air factor that first calculates pressure fan inlet scoop in steam generator system, computing formula is
α in formula
1----furnace outlet excess air coefficient
α
f----burner hearth air leakage coefficient
α
pULV----pulverized coal preparation system air leakage coefficient
R
pA----primary air ratio
α
aH2----rotary regenerative air heater Secondary Air side air leak rate of air curtain
E2. according to the excess air factor of pressure fan inlet scoop, calculate the import air quantity of pressure fan, computing formula is
B in formula
j----boiler fired coal consumption, t/h
T----EAT, ℃
E3. according to the type selecting air quantity of the import Wind Coverage Calculation pressure fan of pressure fan, computing formula is
Q
X=K×K
q×V
xf2
K----height above sea level correction factor in formula
K
q----flow reserve factor
E4. set pressure fan type selecting blast in type selecting process constant, according to the type selecting air quantity of pressure fan, calculate pressure fan power demand P, computing formula is:
P=Q
x*p’/（3600*1000*η）
Q in formula
x----type selecting air quantity, m
3/ h;
The blast of p '----blower fan, Pa;
The internal efficiency of η----blower fan, gets 0.85,
Improvement of the present invention is: in described dry dreg removing system, each air intake point of dry slag extractor is provided with the flow measurement device for the dry dreg removing system inleakage of Real-Time Monitoring.
Further improvement of the present invention is: described flow measurement device is arranged on respectively dry slag extractor side cooling air air door import department and afterbody cooling air air door import department.
Owing to having adopted technique scheme, the technological progress that the present invention obtains is:
The invention solves and in the coal-fired boiler in thermal power plant air and gas system computational process based on air cooling dry deslagging technique, do not consider the dry dreg removing system defect that boiler efficiency and the impact of pressure fan type selecting are produced of leaking out, by leaking out of " inorganization " is converted into " in a organized way ", count in advance leaking out of dry dreg removing system, improve combustion system computational process, instruct pressure fan type selecting, both can guarantee boiler efficiency, can reduce again the type selecting air quantity of pressure fan, guarantee boiler efficiency, can reduce the device parameter of pressure fan simultaneously, reduce cost, improve performance driving economy, reduce energy consumption, energy-saving and emission-reduction.
The present invention is by installing flow measurement device, inleakage that can the dry slag extractor of Real-Time Monitoring, the original slag temperature measurement device of bonded boiler, can Measurement accuracy to the maximum cooling air quantity of dry deslagging of the unit of same size, for later engineering provides Data support, reach the benign cycle of engineering; Can also refer on the other hand the operation of delivery blower fan, regulate exerting oneself of pressure fan according to actual motion inleakage, reduce power consumption.
Accompanying drawing explanation
Fig. 1: be the structural representation of dry slag-discharging boiler system of the present invention.
Fig. 2: be the flow measurement device scheme of installation of dry dreg removing system.
Wherein: 1. dry slag extractor, the cinder notch that 2. falls, 3. side flow measurement device, 4. afterbody flow measurement device.
The specific embodiment
Below in conjunction with the drawings and specific embodiments, the present invention is described in further details.
Boiler optimization method for designing based on air cooling dry deslagging technique, is applied to certain the first phase 2x660MW of power plant ultra supercritical unit engineering, for designing the steam generator system based on air cooling dry deslagging technique.
The bottom slag of this project boiler adopts dry bottom ash handling system, the high temperature furnace slag that boiler is discharged drains into dry slag extractor by slag well and hydraulic shutoff door, in course of conveying warm sludge cooling by the air of reverse movement after, enter slag crusher, after slag crusher fragmentation, being promoted to slag warehousing by bucket elevator deposits, slag leaves the automobile passage of mucking haulage under storehouse, and automobile in-built slag between slag storehouse is transported to storage ash field outward and rolls storage or supply comprehensive utilization.Every a set of dry deslagging slag removing system of boiler configuration, it is exerted oneself and guarantees that being not less than boiler uses the maximum bed drain purge under design coal B-MCR operating mode, and leaves the surplus that is not less than 250%.Guarantee that at normal output be operation continuously under 8t/h, the EIAJ state that is 32t/h.
This engineering boiler is ultra supercritical direct current, single burner hearth, single reheat, balanced draft, totally-enclosed, dry ash extraction, Π type boiler, air preheater is three points of storehouse swingings, combustion system is opposed firing, sparking mode is plasma ignition, requiring the design load of exhaust gas temperature is 121 ℃, and boiler thermal output is 94.19%.Adopt the described method of invention to design, the maximum inorganization inleakage of dry dreg removing system is counted to boiler calculation and pressure fan type selecting, make exhaust gas temperature be stabilized in design load, the impact of dry dreg removing system inorganization inleakage was considered in the design phase, and while making actual motion, boiler thermal output still can maintain 94.19%.
The concrete grammar of boiler optimization design operates according to the following steps:
First calculate boiler thermal output.
Leak out according to the boiler inorganization that dry dreg removing system produces in normal course of operation, caloric receptivity and the air preheater fume side exhaust gas temperature of air preheater air side while calculating actual motion, the thermal loss of further determining steam generator system, finally draws boiler thermal output.
Basic data involved in design process is as table 1 and table 2
Table 1 ature of coal
The master data that table 2 designs
| Sequence number | Title | Symbol | Data | Unit |
| 1 | Air humidity content | d | 10 | g/kg |
| 2 | Boiler fired coal consumption | Bj | 255.5 | t/h |
| 3 | Fresh air inlet (FAI temperature | t | 20 | ℃ |
| 4 | Pressure fan total head | P’ | 4054 | Pa |
| 5 | The former shaft power of pressure fan | P | 2583 | kW |
| 6 | Height above sea level correction factor | K | 1.167 | ? |
| 7 | Flow reserve factor | Kq | 1.08 | ? |
| 8 | Furnace outlet excess air coefficient | α1 | 1.16 | ? |
| 9 | Burner hearth air leakage coefficient | αF | 0.01 | ? |
| 10 | Rotary regenerative air heater Secondary Air side air leak rate of air curtain | αAH2 | 0.02 | ? |
| 11 | Pulverized coal preparation system air leakage coefficient | αPULV | 0 | ? |
| 12 | Primary air ratio | RPA | 0.22 | ? |
| 13 | Dry dreg removing system " inorganization " air leakage coefficient | αGPZ | 0.05 | ? |
| 14 | Air specific weight under wind-warm syndrome of air preheater entrance | ? | 1.116 | kg/m 3 |
| 15 | Air specific weight under air preheater entrance secondary air temperature | ? | 1.135 | kg/m 3 |
| 16 | Wind air quantity of design air preheater entrance | ? | 452022 | m 3/h |
| 17 | Design air preheater entrance Secondary Air air quantity | ? | 1808495 | m 3/h |
| 18 | Flue gas flow | Dy | 742.5 | kg/s |
| 19 | Wind of air preheater is imported and exported the temperature difference | △T1 | 295 | ℃ |
| 20 | Air preheater Secondary Air is imported and exported the temperature difference | △T2 | 323 | ℃ |
| 21 | A wind mean specific heat | C1 | 1.01 | kj/(kg·℃) |
| 22 | Secondary Air mean specific heat | C2 | 1.01 | kj/(kg·℃) |
| 23 | Flue gas mean specific heat | Cy | 1.0759 | kj/(kg·℃) |
| 24 | Air preheater gas approach temperature | Tyi | 376 | ℃ |
| 25 | Boiler exhaust gas heat loss | q2 | 4.21 | % |
| 26 | Combustion gas incomplete combustion heat loss | q3 | 0.4 | % |
| 27 | Heat loss of imperfect solid combustion | q4 | 0.64 | % |
| 28 | Radiation loss | q5 | 0.17 | % |
| 29 | Other heat loss | q6 | 0.09 | % |
| 30 | Standard air state lower density | ρ | 1.015 | kg/m 3 |
A. first calculate the caloric receptivity of air preheater air side;
When actual motion, the total blast volume that enters steam generator system is the summation that pressure fan air quantity and dry dreg removing system inorganization are leaked out, because guaranteeing the total blast volume entering in boiler, needs remain unchanged, when the inorganization of dry dreg removing system is leaked out while entering in a large number in boiler, the air quantity that pressure fan is sent into boiler will reduce, the inorganization inleakage that its decrease is dry dreg removing system; Because the air output of pressure fan reduces, the cold blast rate of the air side by air preheater also will reduce; The cold blast rate of setting air preheater air side is reduced to △ D, and unit is kg/s, and the inorganization air leakage coefficient of dry dreg removing system is α
gPZvalue 0.05 in the present embodiment;
A1. calculate Theory of Boiler Combustion air capacity, the computing formula of Theory of Boiler Combustion air capacity is
V
n°=0.0889(C
ar+0.375S
ar)+0.265H
ar-0.0333O
ar
=0.0889×(60+0.375X0.8)+0.265×3.58-0.0333X8.15=6.04Nm
3/kg
The theoretical air requirement that calculates pressure fan is 6.04Nm
3/ kg.
A2. calculate boiler combustion amount of actual air for combustion, the computing formula of boiler combustion amount of actual air for combustion is
V
n°'=V
n°（1+0.0016d)
=6.04×(1+0.0016×10)=6.136Nm
3/kg
The amount of actual air for combustion of pressure fan is 6.136Nm
3/ kg.
A3. the cold wind reduction of air preheater air side when steam generator system moves while calculating actual motion, computing formula is
△D＝α
GPZρV
n°'B
j/3.6
=0.05×1.015×6.136×255.5/3.6=22.1kg/s
The cold wind reduction of air preheater air side is 28.15kg/s.
A4. the cold wind of air preheater air side caloric receptivity while calculating actual motion, computing formula is
Q
1=D
k1*C
1*△T
1+(D
k2-△D)*C
2*△T
2
=（0.999×452022/3600）×1.01×295+
（1.015×1808495/3600-28.15）×1.01×323
=196507KW
D in formula
k1---wind mass flow of-air preheater side, kg/s
D
k2----air preheater side secondary air mass flow, kg/s
C
1----wind mean specific heat, kj/ (kg ℃)
C
2----Secondary Air mean specific heat, kj/ (kg ℃)
△ T
1---wind of air preheater is imported and exported the temperature difference, ℃
△ T
2---air preheater Secondary Air is imported and exported the temperature difference, ℃
B. calculate the exhaust gas temperature of air preheater fume side
The heat exchange amount of air preheater fume side is the caloric receptivity of air preheater air side,
Q
y=Q
1=196507KW
Calculate thus the exhaust gas temperature of air preheater fume side,
T
yo=T
yi-Q
y/(D
yC
y)
=376-196507/(742.5×1.0759)
=130℃
D in formula
y----air preheater flue gas mass flow, kg/s
C
y----flue gas mean specific heat, kj/ (kg ℃)
T
yi---air preheater gas approach temperature, ℃
T
yo---air preheater exhanst gas outlet temperature (exhaust gas temperature), ℃
C. calculate the thermal loss of steam generator system, and according to the rise of the heat Calculation checking air preheater fume side exhaust gas temperature of thermal loss;
Set air preheater gas approach temperature T
yiremain unchanged, " inorganization " of dry dreg removing system leaked out to increase and will be caused air preheater exhanst gas outlet temperature T
yoraise, air preheater heat exchange amount reduces, and this part heat will be discharged with flue gas, increases heat loss due to exhaust gas, and the loses heat △ Q of air preheater fume side is
△Q=△D*C
2*△T
2
=22.1×1.01×(346-23)=7210kW
The minimizing of air preheater air side caloric receptivity, causes the minimizing of air preheater fume side heat exchange amount, further makes the exhaust gas temperature of air preheater fume side raise, and the rise of exhaust gas temperature is
△T
yo=△Q/(D
yC
y)
=9183/(742.5×1.0759)=9℃
△ T
yo---the rise (exhaust gas temperature) of air preheater exhanst gas outlet temperature, ℃
Compared with 121 ℃ of design loads, if do not considered that in the design phase dry dreg removing system leaks out, when actual motion, exhaust gas temperature will reach 130 ℃, and exhaust gas temperature increases by 9 ℃.
D. calculate boiler efficiency according to above-mentioned result of calculation
The thermal loss calculating according to step C calculates the flue gas loss rate △ q of steam generator system
2, computing formula is
△q
2=3.6△Q/(1000B
jQ
r)
=3.6×7210/(1000×255.5×22.7)=0.0058=0.45%
The thermal efficiency of last steam generator system calculates according to following formula
η
gl=100-(q
2+△q
2+q
3+q
4+q
5+q
6)-0.3
=100-(4.21+0.4+0.45+0.64+0.17+0.09)-0.3
=93.74
Q in formula
3, q
4, q
5, q
6all irrelevant with the inorganization inleakage of dry dreg removing system, only have boiler exhaust gas heat loss system and the inorganization of dry dreg removing system to leak out relevant, the inorganization of dry dreg removing system is leaked out and is directly made the exhaust gas temperature of boiler increase, thereby makes q
2increase.Also the thermal efficiency that is boiler reduces by 0.45 percentage point.
In the time that boiler design is calculated, according to the method described in the present invention dry dreg removing system inorganization is not leaked out and count pressure fan type selecting and boiler heat balance calculating, boiler efficiency in the time of actual motion will reduce by 0.45%, boiler thermal output for the engineering described in the present embodiment when the actual motion will be 93.74%, cannot be according to design 94.19% operating mode operation, unit economy reduces, the actual coal consumption of unit will increase to 258.4t/h by design load 257.2t/h, and coal consumption increases 1.2t/h.
Count dry dreg removing system inorganization inleakage when the boiler design by method for designing of the present invention, to make boiler operating efficiency still remain on 94.19%, identical with former design load, boiler annual utilization hours is pressed 5500h and is calculated, and every unit 6600t that economizes on coal every year, by 500 yuan per ton, 3,300,000 yuan of annual saving, and boiler can be moved according to design conditions, and be conducive to the prolonged boiler life-span, reduce fault rate.
Again pressure fan is carried out to type selecting
E. leak out pressure fan is carried out to accurate type selecting according to the boiler inorganization that dry dreg removing system produces in normal course of operation, concrete type selection calculation process is as described below:
E1. the excess air factor that first calculates the heavy pressure fan of steam generator system inlet scoop, computing formula is
=（1.16-0.01-0.05-0-1.16×0.22）/（1-0.02）
=0.865
E2. according to the air excess system of pressure fan inlet scoop, calculate the import air quantity of pressure fan, computing formula is
=0.865×255.5×6.136×1000×（273+20）/273
=1453768Nm
3/h
E3. according to the type selecting air quantity of the import Wind Coverage Calculation pressure fan of pressure fan, computing formula is
Q
X=K×K
q，V
xf2
=1.167×1.88×1453768
=183227m
3/h
E4. set pressure fan type selecting blast in type selecting process constant, according to the type selecting air quantity of pressure fan, calculate pressure fan power demand P, computing formula is:
P=Q
x*p’/（3600*1000*η）
=1832271×4054/3600/1000/0.85=2427.5kW
Reduce 146kW by pressure fan shaft power after method type selecting of the present invention compared with former type selecting motor shaft power, within 5500 hours, calculate by annual utilization hours, the 797500kWh that can economize on electricity in every unit year, by 0.5 yuan of every degree electricity, 39.875 ten thousand yuan of annual saving.
In engineering described in the present embodiment, dry slag extractor is made up of 18 unit altogether, and both sides, each unit all arrange cooling air air door, at slag drying machine afterbody, an electronic afterbody cooling air air door is set, and these air doors are for controlling the cooling air that enters slag drying machine.In the cold-air flap import of the both sides of 18Ge unit, slag drying machine unit, 2 × 18 flow measurement devices are set altogether, in the import of afterbody cold-air flap, 1 flow measurement device are set, layout drawing as shown in Figure 2.In the time of operation, be design air flow by cooling air debugging, in the time of operation, if air quantity off-design value, by regulating the electronic cold-air flap of afterbody to revise air quantity, guarantees that air quantity is in design load.
The perfect adaptation of the real-time monitoring to inleakage in the improvement by method for designing in advance and actual motion, can guarantee that boiler moves under design efficiency, avoid occurring the actual operating efficiency that occurs in the engineering in the past phenomenon lower than design efficiency, play the coal-fired effect of saving.
Claims (3)
1. the boiler optimization method for designing based on air cooling dry deslagging technique, it is characterized in that: leak out according to the boiler inorganization that dry dreg removing system produces in normal course of operation, caloric receptivity and the air preheater fume side exhaust gas temperature of air preheater air side while calculating actual motion, the thermal loss of further determining steam generator system, finally draws boiler thermal output; The concrete grammar of boiler optimization design operates according to the following steps:
A. the caloric receptivity of air side while first calculating air preheater actual motion; The cold blast rate of setting air preheater air side is reduced to △ D, and unit is kg/s, and the inorganization air leakage coefficient of dry dreg removing system is α
gPZ;
A1. calculate Theory of Boiler Combustion air capacity, the computing formula of theoretical air requirement is
V
n°=0.0889(C
ar+0.375S
ar)+0.265H
ar-0.0333O
ar
V in formula
n° be theoretical air requirement, the Nm of unit
3/ kg; C
arfor coal-fired As-received carbon content, S
arfor coal-fired As-received sulfur content, H
arfor coal-fired As-received hydrogen content, O
arfor coal-fired As-received oxygen content, C
ar, S
ar, H
ar, O
arunit all adopts percentage composition;
A2. calculate boiler combustion amount of actual air for combustion, the computing formula of amount of actual air for combustion is
V
n°'=V
n°（1+0.0016d）
V in formula
n° ' be boiler amount of actual air for combustion, the Nm of unit
3/ kg; D is theoretical air water capacity, the g/kg of unit;
A3. the cold wind reduction of air preheater air side while calculating steam generator system actual motion, computing formula is
△D＝α
GPZρV
n°'B
j/3.6
V in formula
n° ' be boiler amount of actual air for combustion, the Nm of unit
3/ kg; ρ is atmospheric density under standard state, units/kg/m
3; B
jfor boiler fired coal consumption, the t/h of unit;
A4. the cold wind of air preheater air side caloric receptivity while calculating actual motion, computing formula is
Q
1=D
k1*C
1*△T
1+(D
k2-△D)*C
2*△T
2
D in formula
k1for wind mass flow of air preheater side, units/kg/s; D
k2for air preheater side secondary air mass flow, units/kg/s; C
1for a cold wind mean specific heat, the kj/ of unit (kg ℃); C
2for cold Secondary Air mean specific heat, the kj/ of unit (kg ℃); △ T
1for wind of air preheater is imported and exported the temperature difference, unit ℃; △ T
2for air preheater Secondary Air is imported and exported the temperature difference, unit ℃;
B. calculate the exhaust gas temperature of air preheater fume side;
The thermal discharge of air preheater fume side is the caloric receptivity of air preheater air side, and air preheater fume side thermal discharge is
Q
y=Q
1
The exhaust gas temperature that calculates air preheater fume side, the computing formula of air preheater flue gas fume side exhaust gas temperature is
T
yo=T
yi-Q
y/(D
yC
y)
D in formula
yfor air preheater flue gas mass flow, units/kg/s; C
yfor flue gas mean specific heat, the kj/ of unit (kg ℃); T
yifor air preheater gas approach temperature, unit ℃;
C. the thermal loss of steam generator system while calculating actual motion, and according to the rise of the heat Calculation air preheater fume side exhaust gas temperature of loss;
Air preheater gas approach temperature T when actual motion
yiremain unchanged, according to air preheater exhanst gas outlet temperature T
yocalculate air preheater fume side loses heat, computing formula is
△Q=△D*C
2*△T
2
According to the heat of air preheater fume side loss, calculate the rise of exhaust gas temperature, computing formula is
△T
yo=△Q/(D
yC
y)
D. calculate boiler efficiency according to above-mentioned result of calculation
The thermal loss calculating according to step C calculates the flue gas loss rate of steam generator system, and computing formula is
△q
2=3.6△Q/(1000B
jQ
r)
Q in formula
rfor inputting the heat of boiler beyond boiler, by coal-fired low heat valve, the Mj/kg of unit;
The thermal efficiency of steam generator system while finally calculating actual motion, computing formula is
η
gl=100-(q
2+△q
2+q
3+q
4+q
5+q
6)-0.3
Q in formula
2for boiler exhaust gas heat loss; q
3for fuel gas heat loss due to incomplete combustion; q
4for heat loss of imperfect solid combustion; q
5for radiation loss; q
6for other heat loss, q
2to q
6heat loss all adopt percentage to represent, thereby the thermal efficiency while calculating steam generator system actual motion further draws the reduction value of the thermal efficiency;
E. leak out pressure fan is carried out to accurate type selecting according to the boiler inorganization that dry dreg removing system produces in normal course of operation, concrete type selection calculation process is as described below:
E1. the excess air factor that first calculates pressure fan inlet scoop in steam generator system, computing formula is
α in formula
1for furnace outlet excess air coefficient; α
ffor burner hearth air leakage coefficient; α
pULVfor pulverized coal preparation system air leakage coefficient; R
pAfor primary air ratio; α
aH2for rotary regenerative air heater Secondary Air side air leak rate of air curtain;
E2. according to the excess air factor of pressure fan inlet scoop, calculate the import air quantity of pressure fan, computing formula is
B in formula
jfor boiler fired coal consumption, the t/h of unit; T is EAT, unit ℃;
E3. according to the type selecting air quantity of the import Wind Coverage Calculation pressure fan of pressure fan, computing formula is
Q
X=K×K
q×V
xf2
In formula, K is height above sea level correction factor; K
qfor flow reserve factor;
E4. set pressure fan type selecting blast in type selecting process constant, according to the type selecting air quantity of pressure fan, calculate pressure fan power demand P, computing formula is:
P=Q
x*p’/（3600*1000*η）
Q in formula
xfor type selecting air quantity, the m of unit
3/ h; P ' is the blast of blower fan, the Pa of unit; η is the internal efficiency of blower fan.
2. the boiler optimization method for designing based on air cooling dry deslagging technique according to claim 1, is characterized in that: in described dry dreg removing system, each air intake point of dry slag extractor is provided with the flow measurement device for the dry dreg removing system inleakage of Real-Time Monitoring.
3. the boiler optimization method for designing based on air cooling dry deslagging technique according to claim 2, is characterized in that: described flow measurement device is arranged on respectively dry slag extractor side cooling air air door import department and afterbody cooling air air door import department.
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| CN108595723B (en) * | 2017-12-27 | 2021-10-08 | 华北电力科学研究院有限责任公司 | Method and device for calculating heat regeneration quantity of boiler air heater |
| CN111346471B (en) * | 2020-03-09 | 2021-01-05 | 山东大学 | Control method and system for industrial process waste gas treatment and cyclic utilization |
| CN111610044B (en) * | 2020-04-27 | 2022-06-24 | 国网河北省电力有限公司电力科学研究院 | Method for measuring, evaluating and calculating cooling air volume of dry-type slag extractor |
| CN114048635B (en) * | 2022-01-11 | 2022-05-03 | 天津国能津能滨海热电有限公司 | Performance detection method and device of air preheater and electronic equipment |
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Address after: 050031 No. 6 Jianhua Street, Shijiazhuang City, Hebei Province Patentee after: China Electric Power Construction Group Hebei electric survey and Design Research Institute Co., Ltd. Address before: 050031 No. 6 Jianhua Street, Shijiazhuang City, Hebei Province Patentee before: Hebei Province Power Surveying Design & Research Institute |