CN110287561B - Low-temperature flue gas cooling system of standby combustor and parameter design method thereof - Google Patents
Low-temperature flue gas cooling system of standby combustor and parameter design method thereof Download PDFInfo
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- 238000001816 cooling Methods 0.000 title claims abstract description 198
- UGFAIRIUMAVXCW-UHFFFAOYSA-N Carbon monoxide Chemical compound [O+]#[C-] UGFAIRIUMAVXCW-UHFFFAOYSA-N 0.000 title claims abstract description 103
- 239000003546 flue gas Substances 0.000 title claims abstract description 103
- 238000000034 method Methods 0.000 title claims abstract description 15
- 239000000779 smoke Substances 0.000 claims description 46
- 238000002955 isolation Methods 0.000 claims description 22
- 238000010304 firing Methods 0.000 claims description 14
- 230000001105 regulatory effect Effects 0.000 claims description 12
- 239000002956 ash Substances 0.000 claims description 10
- 238000002485 combustion reaction Methods 0.000 claims description 9
- 230000002093 peripheral effect Effects 0.000 claims description 7
- 235000002918 Fraxinus excelsior Nutrition 0.000 claims description 5
- 238000004519 manufacturing process Methods 0.000 description 7
- 239000003245 coal Substances 0.000 description 5
- QVGXLLKOCUKJST-UHFFFAOYSA-N atomic oxygen Chemical compound [O] QVGXLLKOCUKJST-UHFFFAOYSA-N 0.000 description 4
- 229910052760 oxygen Inorganic materials 0.000 description 4
- 239000001301 oxygen Substances 0.000 description 4
- 239000002893 slag Substances 0.000 description 3
- QGZKDVFQNNGYKY-UHFFFAOYSA-N Ammonia Chemical compound N QGZKDVFQNNGYKY-UHFFFAOYSA-N 0.000 description 2
- 229910000975 Carbon steel Inorganic materials 0.000 description 2
- 238000010521 absorption reaction Methods 0.000 description 2
- 239000010962 carbon steel Substances 0.000 description 2
- 239000002817 coal dust Substances 0.000 description 2
- 230000008602 contraction Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 239000007789 gas Substances 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 239000000725 suspension Substances 0.000 description 2
- 208000034699 Vitreous floaters Diseases 0.000 description 1
- 229910021529 ammonia Inorganic materials 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000004364 calculation method Methods 0.000 description 1
- 238000004939 coking Methods 0.000 description 1
- 230000001276 controlling effect Effects 0.000 description 1
- 230000009977 dual effect Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 238000002347 injection Methods 0.000 description 1
- 239000007924 injection Substances 0.000 description 1
- 238000005259 measurement Methods 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
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- 239000000126 substance Substances 0.000 description 1
- 230000009466 transformation Effects 0.000 description 1
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23L—SUPPLYING AIR OR NON-COMBUSTIBLE LIQUIDS OR GASES TO COMBUSTION APPARATUS IN GENERAL ; VALVES OR DAMPERS SPECIALLY ADAPTED FOR CONTROLLING AIR SUPPLY OR DRAUGHT IN COMBUSTION APPARATUS; INDUCING DRAUGHT IN COMBUSTION APPARATUS; TOPS FOR CHIMNEYS OR VENTILATING SHAFTS; TERMINALS FOR FLUES
- F23L9/00—Passages or apertures for delivering secondary air for completing combustion of fuel
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- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F30/00—Computer-aided design [CAD]
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Abstract
The invention discloses a low-temperature flue gas cooling system of a standby combustor and a parameter design method thereof, wherein low-temperature flue gas is led out from an outlet of a boiler induced draft fan and is respectively cooled by a primary air nozzle and a secondary air nozzle of the standby combustor through a main pipe, a branch pipe and a branch pipe.
Description
Technical field:
the invention relates to a low-temperature flue gas cooling system of a standby combustor and a parameter design method thereof.
The background technology is as follows:
the number and the layer number of the large-scale power station boiler burners are designed according to BMCR working conditions, and the actual operation load is much lower than the evaporation capacity of the BMCR working conditions, so that if coal types are designed by combustion, part of the burners are always in a stop and standby state in actual operation. In recent years, due to industrial structure adjustment and large-scale building of new energy engineering for power generation, the annual utilization hours of thermal power generating units are greatly reduced, and the load rate of partial units is less than 60% and the depth peak regulation is even less than 30% even for partial units which are even less than 2000 hours. The number of off-stream burners of the boiler is greatly increased. To prevent burnout of the standby burner, the primary and secondary air nozzles must be ventilated and cooled. The design cooling mode of the existing boiler standby burner is as follows: the secondary air nozzle (comprising peripheral air, central air and ashed air) is cooled by using the hot air of the secondary air box, and the primary air nozzle is cooled by using the primary air pipe big air valve before the burner or the inlet cold air of the coal mill. In order to prevent the burnout of the standby burner, in terms of design, the manufacturer requires that the secondary air valve full Guan Xianwei have a flow area of about 5%, the peripheral air cooling air volume of the standby burner is about 5% of the design air volume, and the other secondary air cooling air volumes are about 10% of the design air volume. On-site observation, the opening of the secondary air valve of the standby burner of each plant is more in the range of 15-25%. The control of the cooling air quantity is regulated according to the wall temperature of the standby burner, different burner materials and different control wall temperatures, and the wall temperature set value is provided by a burner manufacturing plant.
The existing standby burner adopts air cooling for the primary air nozzle and the secondary air nozzle, because the air quantity (wind speed) is low and the momentum is insufficient, the cooling air is difficult to penetrate the flue gas of the hearth to enter the middle part of the hearth and fully mix with coal dust for combustion, in addition, the cooling air is far away from the operating burner and is difficult to participate in the initial combustion of the coal dust, the cooling air has the property of unstructured air quantity to a certain extent, if the operating oxygen quantity of the boiler is not increased, the combustible matters of boiler ash and slag can be increased, if the combustible matters of ash and slag are prevented from being increased, the operating oxygen quantity must be increased, and the concentration of NOx in the flue gas at the outlet of the hearth can be increased. In addition, the cooling air of the standby burner in the main combustion area occupies a certain proportion of the total air quantity, which inevitably leads to the decrease of the proportion of the burnt air and the increase of the concentration of the NOx in the flue gas at the outlet of the hearth. The NOx concentration increase value is related to the boiler type, the coal type and the number of the standby burners, and is in the range of 15mg/Nm 3 ～85mg/Nm 3 。
The secondary air nozzle of the existing standby burner adopts secondary air box hot air cooling, the air temperature is more 290-360 ℃, compared with low-temperature medium cooling, the cooling effect is poor, in order to ensure that the wall temperature of the standby burner does not exceed the standard, the input cooling air quantity is increased, the concentration of ash combustible materials and the NOx concentration of the flue gas at the outlet of a hearth are further increased, and in addition, the power consumption of a fan is also increased.
The primary air nozzle of the existing standby burner is cooled by using the primary air pipe big air valve of the burner or the cold air at the inlet of the coal mill, and the part of cold air quantity directly enters the hearth without passing through the air preheater, so that the cooling effect of the air preheater is reduced, the exhaust gas temperature is increased, and the increasing range is determined by the number of the standby burners and the cooling air quantity, and is mostly 2-4 ℃.
The existing cooling mode of the primary air pipe big air valve of the burner is that the inlet of the air door is provided with a finer filter screen, the filter screen is easy to be blocked by air floaters, the filter screen is not monitored by differential pressure, and if the burner is not provided with a wall temperature measuring point, the burner is easy to burn.
The invention comprises the following steps:
in order to solve the technical problems, the invention provides a low-temperature flue gas cooling system of a standby combustor and a parameter design method thereof, and the technical scheme adopted by the invention is as follows:
a low-temperature flue gas cooling system for a standby burner is characterized in that low-temperature flue gas is led out from an outlet of a boiler induced draft fan and sequentially passes through a main pipe, a branch pipe and a branch pipe to cool a primary air nozzle and a secondary air nozzle of the standby burner respectively.
Preferably, the low-temperature flue gas is connected to a cooling air pipeline behind an air cooling air door of the primary air nozzle or a primary air pipe in front of the primary air burner through a part of branch pipes for cooling the primary air nozzle; and the other part of branch pipes pass through the hot air box and are connected to the air chambers behind the secondary air baffles of the burner to cool the secondary air nozzles.
Preferably, the low-temperature flue gas is led out from the outlets of two boiler induced draft fans respectively, and is converged into one main pipe through two main pipes which are parallel, and the main pipes have the same pipe diameter; wherein, two parallel main pipes are provided with electric isolation gates for system isolation; the branch main pipe is provided with two paths, the opposite-flow combustion boilers are distributed in the front and the back of the boiler, the tangential combustion boilers are distributed in the left and the right of the boiler, and the branch main pipe is connected with the main pipe and the branch pipe; each standby burner is provided with a branch pipe which is connected with a branch main pipe and branch pipes, and each branch pipe is connected with each cooling channel of each burner.
Preferably, each branch pipe is provided with an electric isolation door for system isolation; and each branch pipe is also respectively provided with an electric regulating door for regulating the cooling smoke quantity.
Preferably, for the opposed firing boiler, the branch pipes for cooling the primary air cyclone burner are provided with four paths at most, and are respectively connected to the air pipes behind the central air isolation door, the air cooling air door rear pipeline or the primary air pipe in front of the primary air cyclone burner, and the air chambers behind the inner secondary air sleeve air door and the outer secondary air sleeve air door; the branch pipe of the cooling ashes wind burner is provided with a path which is connected to the wind chamber behind the ashes wind door; wherein expansion joints are respectively arranged on branch sections of the air chambers connected with the inner secondary air sleeve air door and the outer secondary air sleeve air door; for tangential firing boilers, the branch pipes for cooling the primary air burner are provided with two paths at most, and are respectively connected to a pipeline behind an atmospheric cooling air door or a primary air pipe in front of the primary air burner and an air chamber behind a peripheral air door, the cooling secondary air burner and the ashed air burner are respectively provided with a branch pipe, are respectively connected to the air chambers behind the secondary air and the ashed air door, and are respectively provided with expansion joints on the branch sections connected with the air chambers.
The parameter design method of the low-temperature flue gas cooling system of the standby combustor comprises the following specific steps:
1) The cooling smoke amount in the main pipe, the branch pipes and the branch pipes is calculated according to the following steps:
1.1 The amount of cooling smoke in each cooling passage is calculated according to the following formula:
wherein: q (Q) i zgy For the cooling smoke volume of the ith cooling channel, i epsilon [1, N]The method comprises the steps of carrying out a first treatment on the surface of the N is the total number of cooling channels in the standby burner;
Q i rk cooling the hot air quantity for the ith cooling channel, kg/h;
Q i Lk cooling the air quantity of the atmosphere for the ith cooling channel, kg/h;
t i" rk cooling the temperature of the hot air as it exits the combustor for an ith cooling channel;
t i′ rk cooling the hot air temperature, DEG C, for an ith cooling channel;
t i" Lk is the temperature of the ith cooling channel atmospheric air as it exits the burner, c;
t Lk the temperature is the atmospheric air temperature of the ith cooling channel;
C i rk is (t) i" rk +t i′ rk ) Average air specific heat capacity at temperature/2, kJ/kg. ℃;
C i Lk is (t) i" Lk +t Lk ) Average air specific heat capacity at temperature/2, kJ/kg. ℃;
t i" y is the temperature of the i-th cooling channel low-temperature flue gas when leaving the burner, and is at the temperature of DEG C;
t y the temperature of the low-temperature flue gas of the ith cooling channel is DEG C;
C i y is (t) i" y +t y ) Average specific heat capacity of flue gas at temperature/2, kJ/kg. ℃;
1.2 Calculating the cooling smoke amount in each branch pipe according to the following formula:
Q j fgy ＝∑Q i zgy (2)
wherein: q (Q) j fgy For cooling smoke quantity in the j-th branch pipe, kg/h, j is E [1, M]M is the total number of branch pipes;
1.3 The cooling smoke amount in each branch main pipe is calculated according to the following formula:
Q k fzmgy ＝∑Q j fgy (3)
wherein: q (Q) k fzmgy For cooling smoke quantity in kth branch main pipe, kg/h, K is E [1,2 ]]；
1.4 Calculating the cooling smoke amount in the main pipe according to the following formula:
Q mgy ＝∑Q k fzmgy (4)
wherein: q (Q) mgy Cooling smoke amount in the main pipe, kg/h;
2) The conveying pressure difference of each series flue gas cooling channel, namely the conveying pressure difference of each branch pipe series piping system is calculated according to the following formula:
ΔP i ss ＝P y -ΔP i rs -P rc (5)
wherein: ΔP i ss The pressure difference is the delivery pressure difference of the i branch pipe series pipe system, kPa; p (P) y The pressure value of a flue gas meter at the outlet of the induced draft fan is kPa; ΔP i rs Designing resistance for the i-th branch pipe serial pipe system burner, and kPa; p (P) rc Is burnt byThe pressure value of the burner outlet gauge is kPa; the i branch pipe serial pipe system is an i branch pipe, and a branch pipe, a branch main pipe and a main pipe which are communicated with the i branch pipe;
3) The diameters of the main pipe, the branch main pipes, the branch pipes and the branch pipes are calculated according to the following steps:
3.1 The diameter of each branch pipe is calculated according to the following formula:
d i zgy ＝18.8*[Q i zgy /(W y *ρ y )] 0.5 (6)
wherein: d, d i zgy The diameter of the branch pipe is the diameter of the ith branch pipe, mm; q (Q) i zgy The mass flow of the smoke of the ith branch pipe; ρ y For cooling the average flue gas density of the flue gas system, kg/m 3 ；W y The flue gas flow rate of the flue gas cooling system is m/s;
3.2 Calculating the diameters of the branched pipes according to the following formula:
d j fgy ＝18.8*[Q j fgy /(W y *ρ y )] 0.5 (7)
wherein: d, d j fgy The diameter of the jth branch pipe is mm; q (Q) j fgy The smoke mass flow is divided into a j-th path;
3.3 Calculating the diameter of each branch main pipe according to the following formula:
d k fzmgy ＝18.8*[Q k fzmgy /(W y *ρ y )] 0.5 (8)
wherein: d, d k fzmgy The diameter of the branch main pipe of the kth path is mm; q (Q) k fzmgy The mass flow of the smoke is the k branch main pipe;
3.4 The parent tube diameter is calculated according to the following formula:
d mgy ＝18.8*[Q mgy /(W y *ρ y )] 0.5 (9)
wherein: d, d mgy The diameter of the main pipe is mm; q (Q) mgy Is the mass flow of the main pipe;
4) The cooling flue gas duct resistance and were calculated as follows:
wherein: ΔP i y The resistance sum of the branch pipe series pipe system of the ith path is kPa;
λ mg 、
the coefficients of resistance along the way are respectively a main pipe, a kth branch main pipe, a jth branch pipe and an ith branch pipe;
L mg 、
the lengths of the main pipe, the kth branch main pipe, the jth branch pipe and the ith branch pipe are m respectively;
d mg 、
the diameters m of the main pipe, the kth branch main pipe, the jth branch pipe and the ith branch pipe are respectively;
ζ mg 、
the local resistance coefficients of the main pipe, the kth branch main pipe, the jth branch pipe and the ith branch pipe are respectively determined; />
5) Taking the resistance and the middle maximum value delta P of the ith branch pipe series pipe system calculated in the step 4 i y(max) If DeltaP i y(max) >ΔP i ss Then the flue gas flow rate W of each pipeline needs to be reselected y Bringing the step 3 and the step 4 again, and recalculating the diameters and delta P of the pipelines i y Up to DeltaP i y(max) <ΔP i ss At this time, the flue gas flow rate is the optimal flue gas flow rate, and a cooling system is designed according to the diameters of all pipelines under the optimal flue gas flow rate.
Compared with the prior art, the invention has the following beneficial effects:
the low-temperature flue gas cooling system of the standby combustor provided by the invention adopts low-temperature flue gas to replace air for cooling, the specific heat capacity of the low-temperature flue gas is not greatly different from the specific heat capacity of the air, and the temperature of the low-temperature flue gas is much lower than that of the air, so that the flue gas cooling is more advantageous.
The low-temperature flue gas cooling system of the standby combustor provided by the invention can reduce the influence of cooling air on the rise of boiler ash and slag combustibles under the condition that the excess air coefficient (the operating oxygen amount of the boiler) of the boiler is unchanged.
The low-temperature flue gas cooling system of the standby combustor can avoid the increase of the concentration of NOx at the outlet of the hearth caused by increasing the cooling air quantity, and reduce the denitration ammonia injection quantity and the denitration pressure.
The low-temperature flue gas cooling system of the standby combustor provided by the invention can be used for relieving the problem of the rise of the boiler exhaust gas temperature caused by the fact that primary tuyere cooling wind does not pass through an air preheater, and improving the boiler operation efficiency.
The low-temperature flue gas cooling system of the standby burner can avoid the possible burning loss of the burner caused by the blockage of the filter screen at the inlet of the primary air nozzle cooling large air valve.
The low-temperature flue gas cooling system of the standby burner provided by the invention can improve the main and reheat steam temperatures of the boiler under the condition that the excess air coefficient (the running oxygen amount of the boiler) of the boiler is unchanged. The design of the boiler generally ensures that the main steam temperature rated value is 35% -100% BMCR, the reheat steam temperature rated value ensures that the reheat steam temperature is 50% -100% BMCR, according to the actual running condition, more than 70% of the boilers have unit load lower than 60%, the main reheat steam temperature starts to be lower, and some boilers have lower main reheat steam temperature due to the design and coal type problems even though the rated load is. Especially in recent years, the unit load rate is increasingly reduced, the unit load rate in partial areas is less than 60 percent and even is close to 30 percent, the steam temperature is difficult to ensure, and the safe and economic operation of the unit is seriously affected. The low-temperature flue gas cooling system of the standby burner is exactly used under a low-load working condition, the temperature of the hearth is reduced due to the fact that low-temperature flue gas enters the hearth, radiation heat absorption of the hearth is reduced, the low-temperature flue gas circulates in the furnace, the flue gas quantity is increased, the convection heat absorption proportion is increased, and therefore the main and reheat steam temperatures can be obviously improved, and if required, even the low-temperature flue gas quantity (exceeding the cooling requirement) can be increased to improve the steam temperature. The low-temperature flue gas cooling system of the standby burner can be used for the ultra-low load flexible transformation of a unit, and the dual functions of cooling the standby burner and raising the temperature of main and reheat steam are realized.
According to the low-temperature flue gas cooling system of the standby burner, the adopted low-temperature flue gas enters the hearth, so that the temperature of the hearth is reduced, and boiler coking and screen wall temperature overtemperature are prevented to a certain extent.
Description of the drawings:
FIG. 1 is a schematic diagram of a opposed firing boiler cooling system in an embodiment;
FIG. 2 is a schematic diagram of a tangential firing boiler cooling system in an embodiment;
in the figure: 1 is a A, B boiler induced draft fan; 2 is a main pipe; 3 is a main pipe electric isolation door; 4 is a branch main pipe; 5 is a branch pipe; 6 is a branch pipe; 7 is a branch pipe electric isolation door; 8 is a branch pipe electric regulating door; 9 is a central wind isolation door; 10 primary air nozzle cooling big air valve; 11 is a primary air cyclone burner of the opposed firing boiler; 12 is a burn-out wind burner of the opposed firing boiler; 13 is an inner overgrate air sleeve air door; 14 is an outer overgrate air sleeve damper; 15 is a burn-out damper of the opposed firing boiler; 16 is a branch pipe expansion joint; 17 is a primary air burner of a tangential firing boiler; 18 is the secondary air and the ashes air burner of the tangential boiler; 19 is secondary air and burn-out air door; 20 are perimeter wind dampers.
Detailed Description
The invention is further illustrated by the following examples in conjunction with the accompanying drawings:
embodiment one:
the embodiment adopts the low-temperature flue gas cooling system of the standby combustor to cool the primary air nozzle and the secondary air nozzle of the standby combustor of the opposed firing boiler, and as shown in figure 1, the cooling system comprises a A, B boiler induced draft fan 1, a main pipe 2, a branch main pipe 4, a branch pipe 5 and a branch pipe 6;
the low-temperature flue gas is respectively led out from the open holes of the outlet flue of the A, B boiler induced draft fan, the nominal diameter of the open holes is equal to the inner diameter of the main pipe 2, two parallel main pipes are welded, and then one main pipe 2 is led in, and each main pipe 2 is a pipeline with the same inner diameter; wherein, two parallel main pipes are provided with a main pipe electric isolation door 3 for system isolation. A. The boiler induced draft fan 1 supplies air at the same time, so that the condition that the system cannot normally operate due to the failure of a single boiler induced draft fan is avoided, and the design provides enough flue gas for a cooling system; the other end of the main pipe 2 is divided into two paths of branch main pipes 4 to the front and the back of the opposite burning boiler; each branch pipe 5 (if one burner has only one cooling channel, the branch pipe is a branch pipe, such as a burn-out wind burner 12) is led out from the branch main pipe 4 and is arranged in front of each standby burner; each standby burner branch pipe 6 is led out from each corresponding branch pipe 5. One branch pipe 6 of each standby primary air cyclone burner 11 is connected to a rear air pipe of a central air isolation door 9 and used for cooling a central air secondary air nozzle, one branch pipe 6 is connected to a rear air pipe of a primary air nozzle air cooling air door 10 or a front primary air pipe of the primary air cyclone burner 11 and used for cooling the primary air nozzle, and the other two branch pipes 6 are respectively connected to air chambers behind an inner secondary air sleeve air door 13 and an outer secondary air sleeve air door 14 and used for cooling the secondary air nozzle; each branch pipe (branch pipe 5 is a branch pipe 6) of each standby burning wind combustor 12 is connected to the wind chamber behind the burning wind door 15 for cooling the burning wind nozzle.
Each branch pipe 6 is provided with a branch pipe electric isolation door 7 for system isolation; and each branch pipe 6 is also provided with a branch pipe electric regulating valve 8 for regulating the cooling smoke amount. The specific regulation mode is to carry out closed-loop regulation according to the highest allowable wall temperature range of the burner provided by the manufacturing plant, and the wall temperature is controlled within the allowable wall temperature range by regulating the cooling low-temperature flue gas quantity. Because the temperature in the secondary air box is higher, in order to avoid deformation and displacement caused by expansion or contraction acting force of the bellows and the burner, each branch pipe 6 penetrates through the secondary air box, namely, the branch pipe expansion joint 16 is respectively arranged on the branch sections of the air box after connecting the inner secondary air sleeve air door with the outer secondary air sleeve air door and the air chamber after burning out the air door.
All the pipelines of the embodiment can adopt carbon steel pipes, and the surface temperature of the cooling flue gas pipeline is generally higher than 100 ℃, so that all the cooling flue gas pipelines are insulated. Depending on the site situation, the necessary pipe support and suspension is considered.
The low-temperature flue gas for cooling is led out from the outlet of the induced draft fan of the boiler through the main pipe 2, is sent into the cooling channels of the primary air nozzle and the secondary air nozzle of the standby burner through the branch main pipe 4, the branch pipe 5 and the branch pipe 6, and realizes the cooling of all the nozzles of the standby burner. The low-temperature flue gas for cooling is provided by a boiler induced draft fan, the gauge pressure of an air outlet of the boiler induced draft fan is generally 1.5 kPa-3.5 kPa, and the negative pressure of an outlet of a combustor is generally-50 Pa, so that the pressure difference meets the conveying requirement of the cooled flue gas, and a booster fan is not required to be added.
After the low-temperature flue gas cooling system of the standby combustor provided by the invention is used, the original cooling system of the standby combustor can not be dismantled, and only the operation is stopped for standby.
Embodiment two:
the embodiment adopts the low-temperature flue gas cooling system of the standby combustor to cool the primary air nozzle and the secondary air nozzle of the standby combustor of the tangential circular combustion boiler, as shown in fig. 2, the cooling system comprises a A, B boiler induced draft fan 1, a main pipe 2, a branch main pipe 4, a branch pipe 5 and a branch pipe 6;
the low-temperature flue gas is respectively led out from the open holes of the outlet flue of the A, B boiler induced draft fan, the nominal diameter of the open holes is equal to the inner diameter of the main pipe 2, two parallel main pipes 2 are welded, and then one main pipe 2 is converged, and each main pipe 2 is a pipeline with the same inner diameter; wherein, two parallel main pipes 2 are provided with main pipe electric isolation doors 3 for system isolation. A. The boiler induced draft fan 1 supplies air at the same time, so that the condition that the system cannot normally operate due to the failure of a single boiler induced draft fan is avoided, and the design provides enough flue gas for a cooling system; the other end of the main pipe 2 is divided into two branches of main pipes 4 to the left and right sides of the tangential firing boiler; each branch pipe 5 (if one burner has only one cooling channel, the branch pipe is a branch pipe, such as a secondary air burner 18 and a burn-out air burner 18) is led out from the branch main pipe 4 and is arranged in front of each standby burner; each standby burner branch pipe 6 is led out from each corresponding branch pipe 5. One branch pipe 6 of each standby primary air burner 17 is connected to the air chamber behind the peripheral air door 20 for cooling the peripheral air nozzle. One branch pipe 6 is connected to the back air pipe of the primary air nozzle air cooling air door 10 or the front primary air pipe of the primary air burner 17 for cooling the primary air nozzle. Each branch pipe 6 (branch pipe 5 is a branch pipe 6) of each standby secondary air and burn-out air burner 18 is connected to the air chamber behind the secondary air door and the burn-out air door 19 for cooling the secondary air nozzle and the burn-out air nozzle.
Each branch pipe 6 is provided with a branch pipe electric isolation door 7 for system isolation; and each branch pipe 6 is also provided with a branch pipe electric regulating valve 8 for regulating the cooling smoke amount. The specific regulation mode is to carry out closed-loop regulation according to the highest allowable wall temperature range of the burner provided by the manufacturing plant, and the wall temperature is controlled within the allowable wall temperature range by regulating the cooling low-temperature flue gas quantity. Because the temperature in the secondary air box is higher, in order to avoid deformation and displacement caused by expansion or contraction acting force of the bellows and the burner, each branch pipe 6 penetrates through the secondary air box, namely, the branch sections of the air chamber connected with the peripheral air door, the secondary air and the air chamber connected with the ashed air door are all provided with branch pipe expansion joints 16.
All the pipelines of the embodiment can adopt carbon steel pipes, and the surface temperature of the cooling flue gas pipeline is generally higher than 100 ℃, so that all the cooling flue gas pipelines are insulated. Depending on the site situation, the necessary pipe support and suspension is considered.
The low-temperature flue gas for cooling is led out from the outlet of the induced draft fan of the boiler through the main pipe 2, is sent into the cooling channels of the primary air nozzle and the secondary air nozzle of the standby burner through the branch main pipe 4, the branch pipe 5 and the branch pipe 6, and realizes the cooling of all the nozzles of the standby burner. The low-temperature flue gas for cooling is provided by a boiler induced draft fan, the gauge pressure of an air outlet of the boiler induced draft fan is generally 1.5 kPa-3.5 kPa, and the negative pressure of an outlet of a combustor is generally-50 Pa, so that the pressure difference meets the conveying requirement of the cooled flue gas, and a booster fan is not required to be added.
After the low-temperature flue gas cooling system of the standby combustor provided by the invention is used, the original cooling system of the standby combustor can be not dismantled, and only the operation is stopped to be used as a standby
Embodiment III:
the embodiment adopts the low-temperature flue gas cooling system of the standby burner in the first embodiment or the second embodiment, and the parameter design method comprises the following specific steps:
1) The cooling smoke amount in the main pipe, the branch pipes and the branch pipes is calculated according to the following steps:
1.1 The amount of cooling smoke in each cooling passage is calculated according to the following formula:
wherein: q (Q) i zgy The cooling smoke quantity is calculated for the ith cooling channel, kg/h, i E [1, N]The method comprises the steps of carrying out a first treatment on the surface of the N is the total cooling channel number in the standby burner, (the cooling smoke quantity of the ith cooling channel is the cooling smoke quantity in the ith branch pipe connected with the ith cooling channel), wherein,
for the opposed firing boiler, the number of cooling channels of each primary air cyclone burner is at most 4, and the number of cooling channels of each ember air burner is 1; the number of cooling channels of the primary air burner of the tangential firing boiler is at most 2, and the number of cooling channels of the secondary air burner and the burnout air burner is 1.
Q i rk Cooling hot air quantity for the ith cooling channel, kg/h, provided by a manufacturing plant;
Q i Lk cooling the air quantity of the atmosphere for the ith cooling channel, kg/h, provided by a manufacturing plant;
t i" rk cooling the temperature of the hot air as it exits the combustor for an ith cooling channel, c, provided by the manufacturer;
t i′ rk cooling the hot air temperature, DEG C, for an ith cooling channel, provided by a manufacturing plant;
t i" Lk providing for the temperature, DEG C, of the ith cooling channel atmospheric air as it exits the burner, at the manufacturer;
t Lk providing the air temperature, DEG C and the temperature of the air in the ith cooling channel for a manufacturing plant;
C i rk is (t) i" rk +t i′ rk ) Average air specific heat capacity at temperature/2, kJ/kg. ℃;
C i Lk is (t) i" Lk +t Lk ) Average air specific heat capacity at temperature/2, kJ/kg. ℃;
t i" y is the firsti, cooling the temperature of the low-temperature flue gas leaving the burner in the channel, and controlling the temperature;
t y taking the annual actual measurement highest value of the temperature of the low-temperature flue gas of the cooling channel at the ith temperature;
C i y is (t) i" y +t y ) Average specific heat capacity of flue gas at temperature/2, kJ/kg. ℃;
1.2 Calculating the cooling smoke amount in each branch pipe according to the following formula:
Q j fgy ＝∑Q i zgy (2)
wherein: q (Q) j fgy For cooling smoke quantity in the j-th branch pipe, kg/h, j is E [1, M]M is the total number of branch pipes; each standby burner corresponds to 1 branch pipe, and the number of branch pipes depends on the number of standby burners;
1.3 The cooling smoke amount in each branch main pipe is calculated according to the following formula:
Q k fzmgy ＝∑Q j fgy (3)
wherein: q (Q) k fzmgy For cooling smoke quantity in kth branch main pipe, kg/h, K is E [1,2 ]]；
1.4 Calculating the cooling smoke amount in the main pipe according to the following formula:
Q mgy ＝∑Q k fzmgy (4)
wherein: q (Q) mgy Cooling smoke amount in the main pipe, kg/h;
2) The delivery pressure difference of each series flue gas cooling channel is calculated according to the following formula:
ΔP i ss ＝P y -ΔP i rs -P rc (5)
wherein: ΔP i ss The pressure difference is the delivery pressure difference of the i branch pipe series pipe system, kPa; p (P) y The pressure of a flue gas meter at the outlet of the induced draft fan is kPa; ΔP i rs Designing resistance for the ith series cooling flue gas channel burner, kPa, provided by the manufacturer; p (P) rc For burner outlet gauge pressure, kPa, P in this example rc Taking 0; wherein the ith branch pipe series pipe system is the ith branchThe branch pipe, the branch main pipe and the main pipe are communicated with the pipe; p (P) y The method comprises the steps of calculating the corresponding pressure of the lowest possible load of a unit in relation to the load of the unit;
3) The diameters (inner diameters) of the main pipe, the branch main pipes, the branch pipes and the branch pipes are calculated as follows:
3.1 The diameter of each branch pipe is calculated according to the following formula:
d i zgy ＝18.8*[Q i zgy /(W y *ρ y )] 0.5 (6)
wherein: d, d i zgy The diameter of the branch pipe is the diameter of the ith branch pipe, mm; q (Q) i zgy The mass flow of the smoke of the ith branch pipe is kg/h; ρ y For cooling the average flue gas density of the flue gas system, kg/m 3 ；W y For cooling the flue gas flow rate of the flue gas system, m/s is selected according to DL/T5121, and each pipeline can take the same flow rate; wherein ρ is y ＝(P y +2P dq )*273*ρ 0 /[2*P 0 *(t y +273)]。P dq For local average atmospheric pressure, kPa. ρ 0 Is the standard state density of smoke, kg/m 3 。P 0 Is the standard atmospheric pressure, kPa.
3.2 Calculating the diameters of the branched pipes according to the following formula:
d j fgy ＝18.8*[Q j fgy /(W y *ρ y )] 0.5 (7)
wherein: d, d j fgy The diameter of the jth branch pipe is mm; q (Q) j fgy The mass flow of the smoke is kg/h for the j-th branch pipe;
3.3 Calculating the diameter of each branch main pipe according to the following formula:
d k fzmgy ＝18.8*[Q k fzmgy /(W y *ρ y )] 0.5 (8)
wherein: d, d k fzmgy The diameter of the branch main pipe of the kth path is mm; q (Q) k fzmgy The mass flow of the smoke of the kth branch main pipe is kg/h;
3.4 The parent tube diameter is calculated according to the following formula:
d mgy ＝18.8*[Q mgy /(W y *ρ y )] 0.5 (9)
wherein: d, d mgy The diameter of the main pipe is mm; q (Q) mgy The mass flow rate of the main pipe is kg/h;
4) The cooling flue gas duct resistance and were calculated as follows:
wherein: ΔP i y The resistance sum of the branch pipe series pipe system of the ith path is kPa;
λ mg 、
the coefficients of resistance along the way are respectively a main pipe, a kth branch main pipe, a jth branch pipe and an ith branch pipe;
L mg 、
the lengths of the main pipe, the kth branch main pipe, the jth branch pipe and the ith branch pipe are m respectively;
d mg 、
the diameters m of the main pipe, the kth branch main pipe, the jth branch pipe and the ith branch pipe are respectively;
ζ mg 、
the local resistance coefficients of the main pipe, the kth branch main pipe, the jth branch pipe and the ith branch pipe are respectively (the local resistance coefficient is the resistance coefficient of each pipeline caused by valve, elbow, expansion joint, tee joint, section change and the like).
5) Taking the resistance and the middle maximum value delta P of the ith branch pipe series pipe system calculated in the step 4 i y(max) If DeltaP i y(max) >ΔP i ss ThenThe flue gas flow rate W of each pipeline needs to be selected again y Bringing the step 3 and the step 4 again, and recalculating the diameters and delta P of the pipelines i y Up to DeltaP i y(max) <ΔP i ss And taking the flue gas flow rate at the moment as the optimal flue gas flow rate, and designing a cooling system. (if there is low load to increase the main and reheat steam temperature, the additional cooling smoke volume can be determined by thermal calculation according to the temperature increasing range requirement)
The low-temperature flue gas cooling system for the standby combustor provided by the invention adopts the low-temperature flue gas at the outlet of the induced draft fan of the boiler to cool the standby combustor, so that the problems of large cooling air quantity requirement, high combustible substances of boiler ash, high NOx concentration at the outlet of a hearth, high smoke discharge temperature, high power consumption of the fan, easiness in burning loss of a primary tuyere and the like caused by air cooling can be solved.
Claims (3)
1. A parameter design method of a low-temperature flue gas cooling system of a standby combustor is characterized by comprising the following steps of: the low-temperature flue gas in the low-temperature flue gas cooling system of the standby burner is led out from an outlet of a boiler induced draft fan, and is respectively cooled by a primary air nozzle and a secondary air nozzle of the standby burner through a main pipe, a branch pipe and a branch pipe in sequence, wherein the low-temperature flue gas is connected to a cooling air pipeline behind an air cooling air door of the primary air nozzle or a primary air pipe in front of the primary air burner through part of branch pipes for cooling the primary air nozzle; the other part of branch pipes pass through the hot air box and are connected to the air chambers behind the secondary air baffles of the burner to cool the secondary air nozzles;
the low-temperature flue gas is led out from the outlets of two boiler induced draft fans respectively, and is converged into one main pipe through two main pipes in parallel, and all the main pipes have the same pipe diameter; wherein, two parallel main pipes are provided with electric isolation gates for system isolation; the branch main pipe is provided with two paths, the opposite-flow combustion boilers are distributed in the front and the back of the boiler, the tangential combustion boilers are distributed in the left and the right of the boiler, and the branch main pipe is connected with the main pipe and the branch pipe; each standby burner is provided with a branch pipe which is connected with a branch main pipe and branch pipes, and each branch pipe is connected with each cooling channel of each burner; the parameter design method comprises the following specific steps:
1) The cooling smoke amount in the main pipe, the branch pipes and the branch pipes is calculated according to the following steps:
1.1 Calculating the cooling smoke amount in each branch pipe according to the following formula:
wherein: q (Q) i zgy Cooling smoke volume for the ith branch pipe, i epsilon [1, N]The method comprises the steps of carrying out a first treatment on the surface of the N is the total number of branch pipes in the standby burner;
Q i rk cooling the hot air quantity for the ith branch pipe, and kg/h;
Q i Lk cooling the air quantity of the atmosphere for the ith branch pipe, wherein kg/h is the air quantity of the atmosphere;
t i " rk cooling the temperature of the hot air leaving the burner for the ith branch pipe, c;
t i ′ rk cooling the temperature of the hot air for the ith branch pipe;
t i " Lk is the temperature of the atmospheric air of the ith branch pipe when leaving the burner;
t Lk the temperature of the atmospheric air of the ith branch pipe is DEG C;
C i rk is (t) i " rk +t i ′ rk ) Average air specific heat capacity at temperature/2, kJ/kg. ℃;
C i Lk is (t) i " Lk +t Lk ) Average air specific heat capacity at temperature/2, kJ/kg. ℃;
t i " y the temperature of the low-temperature flue gas of the ith branch pipe when leaving the burner is set at DEG C;
t y the temperature of the low-temperature flue gas of the ith branch pipe is DEG C;
C i y is (t) i " y +t y ) Average specific heat capacity of flue gas at temperature/2, kJ/kg. ℃;
1.2 Calculating the cooling smoke amount in each branch pipe according to the following formula:
Q j fgy ＝∑Q i zgy (2)
wherein: q (Q) j fgy For cooling smoke quantity in the j-th branch pipe, kg/h, j is E [1, M]M is the total number of branch pipes;
1.3 The cooling smoke amount in each branch main pipe is calculated according to the following formula:
Q k fzmgy ＝∑Q j fgy (3)
wherein: q (Q) k fzmgy For cooling smoke quantity in kth branch main pipe, kg/h, K is E [1,2 ]]；
1.4 Calculating the cooling smoke amount in the main pipe according to the following formula:
Q mgy ＝∑Q k fzmgy (4)
wherein: q (Q) mgy Cooling smoke amount in the main pipe, kg/h;
2) The conveying pressure difference of each series flue gas cooling channel, namely the conveying pressure difference of each branch pipe series piping system is calculated according to the following formula:
ΔP i ss ＝ P y -ΔP i rs - P rc (5)
wherein: ΔP i ss The pressure difference is the delivery pressure difference of the i branch pipe series pipe system, kPa; p (P) y The pressure value of a flue gas meter at the outlet of the induced draft fan is kPa; ΔP i rs Designing resistance for the i-th branch pipe serial pipe system burner, and kPa; p (P) rc The pressure value is the pressure value of the outlet of the burner, and is kPa; the i branch pipe serial pipe system is an i branch pipe, and a branch pipe, a branch main pipe and a main pipe which are communicated with the i branch pipe;
3) The diameters of the main pipe, the branch main pipes, the branch pipes and the branch pipes are calculated according to the following steps:
3.1 The diameter of each branch pipe is calculated according to the following formula:
d i zgy ＝18.8*[Q i zgy /( W y *ρ y )] 0.5 (6)
wherein: d, d i zgy The diameter of the branch pipe is the diameter of the ith branch pipe, mm; q (Q) i zgy Cooling smoke quantity for the ith branch pipe; ρ y For cooling the average flue gas density of the flue gas system kg-m 3 ；W y The flue gas flow rate of the flue gas cooling system is m/s;
3.2 Calculating the diameters of the branched pipes according to the following formula:
d j fgy ＝18.8*[Q j fgy /( W y *ρ y )] 0.5 (7)
wherein: d, d j fgy The diameter of the jth branch pipe is mm; q (Q) j fgy Cooling smoke quantity for the jth branch pipe;
3.3 Calculating the diameter of each branch main pipe according to the following formula:
d k fzmgy ＝18.8*[Q k fzmgy /( W y *ρ y )] 0.5 (8)
wherein: d, d k fzmgy The diameter of the branch main pipe of the kth path is mm; q (Q) k fzmgy Cooling smoke quantity for the kth branch main pipe;
3.4 The parent tube diameter is calculated according to the following formula:
d mgy ＝18.8*[Q mgy /(W y *ρ y )] 0.5 (9)
wherein: d, d mgy The diameter of the main pipe is mm; q (Q) mgy Cooling smoke volume for the main pipe;
4) The cooling flue gas duct resistance and were calculated as follows:
wherein: ΔP i y The resistance sum of the branch pipe series pipe system of the ith path is kPa;
λ mg 、λ k fzmg 、λ j fg 、λ i zg the coefficients of resistance along the way are respectively a main pipe, a kth branch main pipe, a jth branch pipe and an ith branch pipe;
L mg 、L k fzmg 、L j fg 、L i zg the lengths of the main pipe, the kth branch main pipe, the jth branch pipe and the ith branch pipe are respectively,m；
d mg 、d k fzmg 、d j fg 、d i zg the diameters m of the main pipe, the kth branch main pipe, the jth branch pipe and the ith branch pipe are respectively;
ζ mg 、ζ k fzmg 、ζ j fg 、ζ i zg the local resistance coefficients of the main pipe, the kth branch main pipe, the jth branch pipe and the ith branch pipe are respectively determined;
5) Taking the resistance and the middle maximum value delta P of the ith branch pipe series pipe system calculated in the step 4 i y(max) If DeltaP i y(max) >ΔP i ss Then the flue gas flow rate W of each pipeline needs to be reselected y Bringing the step 3 and the step 4 again, and recalculating the diameters and delta P of the pipelines i y Up to DeltaP i y(max) <ΔP i ss At this time, the flue gas flow rate is the optimal flue gas flow rate, and a cooling system is designed according to the diameters of all pipelines under the optimal flue gas flow rate.
2. The parameter design method according to claim 1, wherein: each branch pipe is provided with an electric isolation door for system isolation; and each branch pipe is also respectively provided with an electric regulating door for regulating the cooling smoke quantity.
3. The parameter design method according to any one of claims 1-2, wherein:
for the opposed firing boiler, the branch pipes for cooling the primary air cyclone burner are provided with four paths at most, and are respectively connected to the air pipes behind the central air isolation door, the air pipes behind the air cooling air door or the primary air pipes in front of the primary air cyclone burner, and the air chambers behind the air doors of the inner and outer secondary air sleeves; the branch pipe of the cooling ashes wind burner is provided with a path which is connected to the wind chamber behind the ashes wind door; wherein expansion joints are respectively arranged on branch sections of the air chambers connected with the inner secondary air sleeve air door and the outer secondary air sleeve air door;
for tangential firing boilers, the branch pipes for cooling the primary air burner are provided with two paths at most, and are respectively connected to a pipeline behind an atmospheric cooling air door or a primary air pipe in front of the primary air burner and an air chamber behind a peripheral air door, the cooling secondary air burner and the ashed air burner are respectively provided with a branch pipe, are respectively connected to the air chambers behind the secondary air and the ashed air door, and are respectively provided with expansion joints on the branch sections connected with the air chambers.
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