WO2009125566A1 - 固体燃料バーナ、固体燃料バーナを用いた燃焼装置とその運転方法 - Google Patents
固体燃料バーナ、固体燃料バーナを用いた燃焼装置とその運転方法 Download PDFInfo
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- WO2009125566A1 WO2009125566A1 PCT/JP2009/001573 JP2009001573W WO2009125566A1 WO 2009125566 A1 WO2009125566 A1 WO 2009125566A1 JP 2009001573 W JP2009001573 W JP 2009001573W WO 2009125566 A1 WO2009125566 A1 WO 2009125566A1
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- Prior art keywords
- air
- nozzle
- furnace
- fuel
- solid fuel
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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
- F23C7/00—Combustion apparatus characterised by arrangements for air supply
- F23C7/008—Flow control devices
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23D—BURNERS
- F23D1/00—Burners for combustion of pulverulent fuel
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23D—BURNERS
- F23D2201/00—Burners adapted for particulate solid or pulverulent fuels
- F23D2201/10—Nozzle tips
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23D—BURNERS
- F23D2201/00—Burners adapted for particulate solid or pulverulent fuels
- F23D2201/20—Fuel flow guiding devices
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23D—BURNERS
- F23D2900/00—Special features of, or arrangements for burners using fluid fuels or solid fuels suspended in a carrier gas
- F23D2900/00003—Fuel or fuel-air mixtures flow distribution devices upstream of the outlet
Definitions
- the present invention relates to a solid fuel burner suitable for pulverizing a solid fuel, carrying it in an air current, and carrying out floating combustion, a combustion apparatus using the solid fuel burner, and an operating method thereof.
- Combustion devices use steam temperature and pressure rise and reheat cycle for higher efficiency.
- the water supplied to the boiler evaporates through a heat transfer pipe installed along the wall of the furnace, drives the steam turbine as main steam through the superheater, then passes through the reheater as reheated steam and reheats. Then, the steam turbine is driven again, passes through the condenser, becomes water, and is supplied to the furnace again.
- Patent Document 1 As a method for controlling the temperature and flow rate of the combustion gas, there is a method of controlling the temperature distribution in the furnace by changing the jet direction of fuel from the burner up and down (Patent Document 1). Also, in the downstream part of the furnace, the combustion gas flow paths are divided, and the amount of combustion gas flowing through each flow path is controlled using means such as a damper, so that the heat transfer section installed in each combustion gas flow path A method of adjusting the amount of heat transfer of is known.
- combustion gas flow path for supplying fuel to the fuel nozzle divides the gas flow path, and even when the amount of combustion gas flowing in each gas flow path is changed, it is sufficient for the adhesion of ash in the combustion gas. Consideration is necessary. Further, since the partition walls are provided, the individual flow paths are narrowed, and sufficient consideration is required for the installation of the heat transfer section.
- An object of the present invention is to control the direction of fuel jetted from a solid fuel burner to a furnace in a vertical direction or a horizontal direction by a flow rate of air flowing through the air nozzle with a relatively simple structure, thereby determining a flame formation position in the furnace.
- Changing the temperature of the combustion gas at the furnace outlet, the temperature of the heat transfer tube installed on the wall of the furnace and the heat transfer tube provided on the downstream side of the flue, the temperature of the fluid flowing through the heat transfer tube can be kept constant
- the present invention includes a fuel nozzle that ejects a mixed fluid of a solid fuel and its carrier gas, and at least one air that is disposed outside the fuel nozzle and ejects combustion air.
- the solid fuel burner having a nozzle at least one of the air nozzles is formed in an annular shape on the outer periphery of the fuel nozzle, and an internal air flow path is formed by an obstacle in a plurality of regions in the circumferential direction of the nozzle.
- a solid fuel burner that is divided and has a flow rate adjusting means for adjusting a flow rate flowing through at least one of the plurality of regions.
- a deviation in flow rate and momentum in the circumferential direction of the fuel nozzle may be generated with respect to the flow ejected from the air nozzle. it can.
- the flow rate of air flowing through the lower air nozzle of the fuel nozzle is increased, the flow rate and flow velocity of air at the nozzle outlet are increased to increase the momentum.
- a negative pressure is generated in the lower region of the fuel nozzle due to the surrounding air being entrained by surrounding air.
- the negative pressure is increased in the lower region of the fuel nozzle.
- the fuel ejected from the fuel nozzle into the furnace flows biased downward by the downward force due to the pressure distribution, and a flame is formed in the lower part of the furnace than usual.
- the temperature distribution in the furnace is biased downward, the amount of heat absorption in the furnace is increased, and the amount of heat absorption in the heat transfer tube provided in the flue portion on the downstream side of the furnace can be reduced.
- the flow rate of air flowing through the upper air nozzle of the fuel nozzle is increased, the flame in the furnace is formed above the normal, the temperature distribution in the furnace is biased upward, and the amount of heat absorbed in the furnace Decreases, and it becomes possible to increase the amount of heat absorbed by the heat transfer tube provided in the downstream portion of the furnace.
- a solid fuel burner is configured such that the outer peripheral partition wall of the outermost flow path is formed of a partition wall or a water wall of a furnace body constituting the furnace.
- the inner peripheral partition of the outermost flow path of the solid fuel burner is connected to the air nozzle to which the fuel nozzle and burner are connected.
- the partition wall or water wall of the furnace body constituting the furnace and the fuel nozzle and wind box have different temperatures during the operation of the combustion apparatus (boiler, etc.), and therefore there is a difference in the rate of thermal expansion.
- the partition wall or water wall of the furnace body on the outer peripheral side of the air nozzle or the partition wall (furnace body side partition wall) connected to it, and the partition wall (fuel nozzle side partition wall) connected to the inner peripheral fuel nozzle or wind box The relative position changes depending on the temperature. For this reason, it is difficult to divide the flow path in the circumferential direction by providing an obstacle in the radial direction connecting the inner peripheral partition wall and the outer peripheral partition wall constituting the air nozzle.
- the structure shown in any one of the following (A) to (C) is used as a method of dividing the inside of the air nozzle into a plurality of circumferential directions (directions crossing the gas flow).
- (A) It has the obstacle which divides the inside of the air nozzle constituted annularly into a plurality of fields in the peripheral direction, and the obstacle is connected to the inner peripheral side partition of the air nozzle and is not connected to the outer peripheral side partition. .
- Flow rate adjusting means for adjusting the flow rate flowing through at least one of the plurality of regions of the air nozzle is provided, and a flow rate deviation is given in the circumferential direction of the fuel nozzle to the flow ejected from the air nozzle.
- (B) It has the obstacle which divides the inside of the air nozzle constituted annularly into a plurality of fields in the peripheral direction, and the obstacle is connected to the outer peripheral side partition wall of the air nozzle and is not connected to the inner peripheral side partition wall. . And it has the flow volume adjustment means which adjusts the flow volume which flows through at least 1 area
- (C) It has an obstacle that divides the inside of the annularly configured air nozzle into a plurality of regions in the circumferential direction, and the obstacle is connected to the outer peripheral side partition of the air nozzle and is not connected to the inner peripheral side partition.
- An obstacle is connected to the inner peripheral partition wall of the air nozzle and is not connected to the outer peripheral partition wall.
- Flow rate adjusting means for adjusting a flow rate flowing through at least one of the plurality of regions of the air nozzle is provided, and a flow rate deviation is given in the circumferential direction of the fuel nozzle with respect to the flow ejected from the air nozzle.
- some of the air passes through the space between the obstacle and the inner or outer partition wall, but most of the air stays in the same region. For this reason, as in the methods (A) and (B), the fuel ejected from the fuel nozzle flows in a biased direction in the direction in which the amount of air ejected from the air nozzle is large.
- the obstacles that divide the interior of the air nozzle described in (A) to (C) into a plurality of regions in the circumferential direction are the combustion air shown in FIGS. 8 to 10 between the obstacle and the air nozzle wall surface.
- obstacles form a closed space in which only the inlet and outlet in the flow direction of the combustion air are opened, and the combustion air flows through the closed space from the burner upstream side to the furnace side ( (It may be called a split type air nozzle).
- the tertiary air nozzles 12 and 13 connecting and integrating two obstacles connected to the inner peripheral wall of the air nozzle shown in FIGS. 3 and 4 are specific examples, and the air nozzle described in (A) above. It is one embodiment.
- a split type air nozzle in which two obstacles connected to the outer peripheral wall of the air nozzle described in (B) are connected and integrated is also within the scope of the present invention.
- the fuel nozzle is adapted to the flow ejected from the split type air nozzle.
- the flow rate deviation can be given in the circumferential direction. For this reason, the fuel ejected from the fuel nozzle flows biased in the direction in which the amount of air ejected from the air nozzle is large.
- the split air nozzles arranged outside the fuel nozzles are arranged vertically with respect to the fuel nozzles, and the flow rate and the jet velocity of the air jetted from the upper and lower air nozzles into the furnace are adjusted.
- the momentum calculated by the product of the air flow rate and the jet flow velocity changes in the vertical direction of the burner outlet, and the air flow rate ejected from the air nozzles above and below the burner is individually controlled in the vertical direction in the furnace at the burner outlet. Can do.
- the temperature distribution in the furnace differs in the vertical direction of the burner outlet, and the heat absorption amount in the furnace and the heat absorption amount in the heat transfer tube provided in the flue portion on the downstream side of the furnace change.
- the controllability of the air flow rate in the burner is enhanced by the split type air nozzles provided above and below the fuel nozzle.
- an air nozzle is disposed outside the annular nozzle and an obstacle that is divided into a plurality of regions in the circumferential direction inside the annular air nozzle is disposed, You may make it the structure which has a flow volume adjustment means which adjusts the air quantity ejected from an air nozzle.
- the solid fuel burner of the present invention has a fuel nozzle outlet that is relatively short in one direction and relatively long in the opposite direction (the cross section in the direction crossing the flow path of the fuel nozzle is two orthogonal directions).
- the inner peripheral partition walls constituting at least one of the air nozzles are also perpendicular to each other.
- the outer peripheral partition walls may have the same length in two orthogonal directions.
- the fuel ejected from the fuel nozzle is easily dispersed in the long side direction.
- the long side direction is a direction orthogonal to the gas flow direction in the combustion apparatus (furnace)
- the fuel is dispersed in the furnace so that the space in the furnace is effectively utilized, and the fuel furnace
- the residence time inside can be increased as compared with the conventional case. For this reason, it is possible to reduce the emission amount of nitrogen oxides (NOx) and to reduce the unburned amount.
- NOx nitrogen oxides
- the outlet of the fuel nozzle has a wide nozzle shape.
- the inner peripheral partition wall constituting at least one air flow path has different lengths in the long side direction and the short side direction, and the outer peripheral partition wall is orthogonal.
- the cross section in the direction crossing the flow path of the air nozzle increases the thickness in one direction out of the two orthogonal directions. For this reason, when a deviation of the air flow rate is given to a portion having a large thickness, the air flow rate is large. Therefore, the deviation of the air flow rate ejected from the air nozzle into the furnace makes it easy to induce the fuel jet ejected from the fuel nozzle. .
- the outlet of the fuel nozzle of the solid fuel burner has a so-called wide nozzle shape with a long side in the horizontal direction, and the thickness of the air nozzle described above is increased and decreased.
- the direction of the fuel jet ejected from the solid fuel burner can be changed in the vertical direction by increasing the thickness in the direction and further giving the fuel flow rate deviation in the vertical direction.
- the solid fuel burner of the present invention flows through the mixed fluid flowing through the fuel nozzle or the air nozzle at the tip of the outer peripheral partition wall of the fuel nozzle or the inner peripheral partition wall tip of the air nozzle containing the fuel nozzle. It is desirable to provide a flame holding ring that is an obstacle that obstructs the flow of air.
- the negative pressure due to the pressure of the fluid flowing around the flame retaining ring is negative.
- a region of pressure is formed.
- a circulating flow is formed which is a flow in the opposite direction (downstream to upstream) with respect to the direction of ejection from each nozzle.
- the high-temperature gas generated by combustion returns from the downstream and stays in the circulating flow, accelerating the ignition of fuel particles flowing around.
- the fuel jet ignited by this circulating flow flows in an up-and-down direction due to the air flow difference in each region of the air nozzle, thereby changing the flame formation position.
- flame ignition is performed stably in the vicinity of the circulation flow at the outlet of the fuel nozzle, and only the ignition formation direction can be changed, so the temperature distribution in the furnace, the amount of heat absorbed in the furnace, and the flue section on the downstream side of the furnace It becomes easy to control the amount of heat absorption in the heat transfer tube provided in.
- the solid fuel burner of the present invention it is desirable to provide a guide member for deflecting the flow toward the outer peripheral side (direction away from the fuel nozzle) at the outermost peripheral air nozzle outlet.
- a guide member for deflecting the flow toward the outer peripheral side (direction away from the fuel nozzle) at the outermost peripheral air nozzle outlet As a method for suppressing nitrogen oxide (NOx) generated during combustion of solid fuel, there is a method in which mixing of fuel and air in the vicinity of the burner is suppressed, and the fuel is burned under the condition of air shortage near the burner. In the burner using this method, when the flow rate of air flowing through the air nozzle is decreased, the air is entrained by the fuel jet and flows toward the central axis, and the mixing with the fuel may be accelerated.
- NOx nitrogen oxide
- the direction of the air ejected from the air nozzle is fixed to the outer peripheral side by providing a guide member that guides the direction of the air ejection flow to the outer peripheral side at the tip of the air nozzle. For this reason, even when the air flow rate is decreased, it is possible to suppress the mixing of fuel and air in the vicinity of the burner.
- the guide member occupies a projected area of 90% or more with respect to a cross-sectional area in a direction crossing the flow path at the minimum portion (throat portion) of the air nozzle. .
- the projected area By setting the projected area to 90% or more, the flow direction is guided to the outer periphery by the guide member.
- a flow velocity component outward in the radial direction of the fuel nozzle is induced in the air ejected from the air nozzle by the guide member. Since the flow of air ejected from the air nozzle into the furnace makes it easier for the surrounding gas to be wound outward, the gas pressure in the region between the air nozzle and the fuel nozzle is higher than when the induction member is not provided. descend. For this reason, when the flow rate deviation is given to the air jetted from the air nozzle in the circumferential direction of the fuel nozzle, the bias of the fuel jetted from the fuel nozzle is strengthened.
- the flame formation position in the vertical or horizontal direction in the furnace at the outlet of the fuel nozzle by adjusting the flow rate of air flowing through the air nozzle.
- the solid fuel burner of the present invention it becomes possible to control the formation position of the flame in the furnace in the vertical direction or the horizontal direction of the solid fuel burner by the air flow rate flowing through the air nozzle, and in the combustion apparatus (furnace) Since the residence time of the combustion gas flowing through the cylinder changes, the amount of heat transfer in the combustion apparatus changes, and the temperature of the combustion gas at the outlet can be changed.
- the combustion apparatus provided with the solid fuel burner of the present invention and its operating method, the temperature of the combustion gas at the furnace outlet, the temperature of the heat transfer tube installed on the wall surface of the furnace, the temperature of the fluid flowing through the heat transfer tube Or, in order to maintain the temperature of the heat transfer tube provided in the furnace or in the flue portion on the downstream side thereof (see FIG. 14) and the temperature of the fluid flowing through the heat transfer tube, the flame formation position can be changed. Become.
- FIG. 2 is a cross-sectional view of the solid fuel burner of FIG.
- FIG. 2 is a cross-sectional view of the solid fuel burner of FIG. 1 taken along the line BB.
- FIG. 2 is a cross-sectional view of the solid fuel burner of FIG. It is a figure which shows the gas temperature behavior in the furnace exit in the combustion apparatus provided with the solid fuel burner of the 1st Embodiment of this invention.
- FIG. 8 is a cross-sectional view of the solid fuel burner of FIG.
- FIG. 8 is a cross-sectional view taken along the line CC of another example of the solid fuel burner of FIG. 7.
- FIG. 8 is a cross-sectional view taken along the line CC of another example of the solid fuel burner of FIG. 7.
- FIG. 12 is a cross-sectional view of the solid fuel burner of FIG. 11 taken along the line CC.
- FIG. 12 is a cross-sectional view taken along the line CC of another example of the solid fuel burner of FIG. 11. It is the schematic of the combustion apparatus which provided the solid fuel burner which shows embodiment of this invention in the furnace wall.
- FIG. 1 is a schematic view showing a cross section of a solid fuel burner showing a first embodiment of the present invention.
- FIG. 2 is a view for explaining the first embodiment of the present invention, in order to show the state of flame formation when a deviation is given to the air flow rate ejected from the air nozzle into the furnace with respect to the solid fuel burner of FIG.
- FIG. 3 is a cross-sectional view taken along the furnace partition wall of the solid fuel burner shown in FIG. 1 (a cross-sectional view taken along line AA in FIG. 1)
- FIG. 4 is a wind box portion of the solid fuel burner shown in FIG.
- FIG. 5 is a cross-sectional view taken along line BB in FIG. 1 (FIG. 1 is a cross-sectional view taken along line BB in FIG. 1)
- FIG. 5 is a cross-sectional view taken along the wind box of the solid fuel burner shown in FIG. FIG.
- a fuel nozzle 10 for supplying and transporting a mixed fluid of solid fuel together with primary air of the solid fuel burner 1 is connected to a transport pipe (not shown) on the upstream side.
- a secondary air nozzle 11 for ejecting secondary air is provided.
- Tertiary air nozzles 12 and 13 for ejecting tertiary air are provided on the outer periphery of the secondary air nozzle 11.
- quaternary air nozzles 14 to 17 for ejecting quaternary air are provided on the outer periphery of the tertiary air nozzles 12 and 13.
- the tertiary air nozzles 12 and 13 of the present embodiment are divided air nozzles provided in the vertical direction across the fuel nozzle 10.
- the quaternary air nozzles 14 to 17 are the outermost peripheral air nozzles that form a flow path on the outermost periphery in the solid fuel burner 1 of the present embodiment.
- the partition wall 18 constituting the fuel nozzle 10 also serves as an inner peripheral wall of the secondary air nozzle 11 provided in an annular shape on the outer periphery of the fuel nozzle 10.
- the outer peripheral wall 19 of the secondary air nozzle 11 also serves as the inner peripheral walls of the tertiary air nozzles 12 and 13 and the fourth air nozzles 16 and 17.
- An upper tertiary air nozzle 12 and a lower tertiary air nozzle 13 are arranged so as to sandwich the fuel nozzle 10, and the upper tertiary air nozzle 12 is formed by a cylindrical partition wall 19 and a bent plate-shaped peripheral wall obstacle 20.
- the lower tertiary air nozzle 13 is configured by the cylindrical partition wall 19 and the bent plate-shaped obstacle 21.
- the quaternary air nozzles 14 to 17 are divided into respective regions by the peripheral wall obstacles 20 and 21, the outer peripheral partition wall 29 and the inner peripheral partition wall 19 are separated.
- the quaternary air nozzle 14 is provided on the upper outer periphery of the tertiary air nozzle 12, the quaternary air nozzle 15 is provided on the lower outer periphery of the tertiary air nozzle 13, and the quaternary air nozzle 16 is on the left when viewed from the furnace side.
- the tertiary air nozzle partition 19 and the obstacles 20 and 21 are provided outside, and the quaternary air nozzle 17 is seen from the furnace side and the right tertiary air nozzle partition 19 and the peripheral wall obstacles 20 and 21 outside. Is provided.
- An oil gun 24 is provided through the center of the fuel (pulverized coal) nozzle 10 and is used for auxiliary combustion when the burner is started or when low-load combustion is performed.
- a throttle 25 is provided in the fuel nozzle 10 to prevent backfire of the solid fuel.
- a flame holding ring 26 is provided at the tip of the partition wall 18 separating the fuel nozzle 10 and the secondary air nozzle 11, and the flame holding ring 26 is a fuel in the furnace near the tip of the fuel (pulverized coal) nozzle 10.
- the opening for installing the burner 1 on the furnace wall 28 is a burner throat portion 29, and the burner throat portion 29 also serves as an outer peripheral partition wall of the quaternary air nozzles 14 to 17.
- a water pipe 30 is provided on the wall surface of the furnace wall 28 other than the burner throat portion 29.
- a guide member (guide sleeve) 32 for guiding the secondary air and the tertiary air in a direction away from the fuel nozzle 10 is provided at the tip of the partition wall 19 between the secondary air nozzle 11 and the tertiary air nozzles 12 and 13. Further, a guiding member for guiding the tertiary air and the quaternary air in the direction away from the fuel nozzle 10 at the tip of the peripheral wall obstacles 20 and 21 between the tertiary air nozzles 12 and 13 and the quaternary air nozzles 14 and 15 ( Guide sleeves 34 and 35 are provided. Air flowing through the combustion air nozzles 11 to 17 is supplied from an air box 39 surrounding the burner 1.
- a flow 37 of a mixed fluid of solid fuel and primary air flows, and in the secondary air nozzle 11, a flow of secondary air 41 flows.
- the upstream sides of the tertiary air nozzles 12 and 13 and the quaternary air nozzles 14 to 17 have the same air flow path, and the flow rate regulators (dampers) 38a, 38b, 43, and 44 are used to connect the tertiary air and the 4th.
- the air flow 42 used as the secondary air is adjusted.
- the flow rate of the secondary air flow 41 flowing through the secondary air nozzle 11 is adjusted by a flow rate regulator (damper) 40, and the total flow rate and the tertiary air are adjusted by a flow rate regulator (damper) 38.
- the air in the tertiary air nozzles 12 and 13 used as the tertiary air is adjusted by flow rate regulators (dampers) 43 and 44, respectively.
- the flow of the tertiary air and the quaternary air 49 and 50 ejected from the nozzles 12 and 13 and the quaternary air nozzles 14 to 17 into the furnace (FIG. 1 distinguishes the tertiary air and the quaternary air in the furnace. Without being shown as an upper stream 49 and a lower stream 50).
- the outer peripheral part (fuel jet) 51 of a flame is formed in a furnace.
- the fuel mixed fluid flow 46 and the secondary air flow 48 in the furnace are separated, and the circulating flow 33 expands. Since the high-temperature gas stays in the circulating flow 33, the ignition of the fuel particles proceeds and the stability of the flame is improved.
- a flame is formed in the vicinity of the outlet of the fuel nozzle 10 and oxygen consumption progresses, so that a reducing flame region having a low oxygen concentration is expanded in the flame.
- nitrogen contained in the solid fuel is released as a reducing substance such as ammonia or cyanide, and acts as a reducing agent that reduces nitrogen oxide (NOx) to nitrogen. For this reason, NOx generation amount can be reduced.
- unburned portion in the fuel ash
- guide members 32, 34, and 35 for guiding the air ejected from the air nozzles to the outer peripheral direction at the outlets of the tertiary air nozzles 12 and 13 and the quaternary air nozzles 14 to 17, in the furnace
- the mixing of the fuel, the tertiary air and the quaternary air in the vicinity of the burner is delayed because the fuel mixed fluid flow 46, the secondary air flow 48, the tertiary air and the quaternary air flows 49 and 50 flow away from each other.
- the reduction flame area expands.
- FIG. 1 illustrates a case where air is flowed from the tertiary air nozzles 12 and 13 so as to obtain an equal jet flow velocity
- FIG. 2 operates a flow rate adjustment damper 43 of the tertiary air nozzle 12 installed on the upper side of the burner 1. This is a case where a small amount of air is flowed in comparison with other nozzles.
- the fuel jet 51 is formed in the furnace as a downward flow due to the deviation of the air flow rate flowing through the tertiary air nozzles 12 and 13. Further, as the fuel flows downward, a flame formed from the circulating flow 33 downstream of the flame holding ring 26 is also formed downward. For this reason, the temperature distribution in the furnace is biased downward, the heat absorption amount in the furnace is increased, and the heat absorption amount in the heat transfer tube provided in the downstream portion of the furnace can be reduced.
- the formation position of the flame 51 can be controlled in the vertical direction by giving a deviation to the air flow rate flowing through the tertiary air nozzles 12 and 13. Therefore, the temperature of the combustion gas at the furnace outlet, the temperature of the heat transfer tube installed on the wall of the furnace, the temperature of the fluid flowing through the heat transfer tube, or the temperature of the heat transfer tube provided in the furnace or in the flue section downstream thereof, Based on the temperature of the fluid flowing through the heat transfer tube, the flow rate of air flowing through the tertiary air nozzles 12 and 13 of the solid fuel burner 1 can be individually controlled in the vertical direction of the burner 1.
- a flame retaining ring 26 that prevents the flow of the mixed fluid 37 flowing through the fuel nozzle 10 and the air flowing through the secondary air nozzle 11 at the tip of the outer peripheral partition 18 of the fuel nozzle 10.
- guide members 32, 34, and 35 are provided at the outlets of the tertiary air nozzles 12 and 13 and the 4 air nozzles 14 to 17, respectively, for deflecting the flow toward the outer peripheral side (direction away from the fuel nozzle 10).
- a circulation flow 33 is formed in the furnace, and high-temperature gas stays in the circulation flow 33, and by igniting the fuel, flame ignition is performed at the outlet of the fuel nozzle 10. It becomes possible to form stably in the downstream of 26. For this reason, the ignition position can be fixed regardless of the flow rate of the air ejected from the tertiary air nozzles 12 and 13. For this reason, even when an air flow rate deviation ejected from the tertiary air nozzles 12 and 13 is given, only the formation direction (angle) of the flame 51 can be changed.
- the guide members 32, 34, and 35 are provided, the direction of the air ejected from the air nozzles 11 to 17 can always be formed on the outer peripheral side of the burner 1. For this reason, even when the flow rate is reduced, it is possible to suppress the mixing of fuel and air in the furnace in the vicinity of the burner 1. Accordingly, mixing of fuel and air in the furnace near the burner 1 can be suppressed, and NOx can be reduced.
- the dampers 40, 43, and 44 corresponding to the secondary air nozzle 11 and the tertiary air nozzles 12 and 13 are shown as air flow rate adjustment dampers, but as shown in FIG.
- You may provide as flow regulation dampers 56a and 56b provided in 16,17.
- the flow rate adjustment dampers 38a, 38b, 56a, 56b can give a deviation to the flow rates of the air flowing through the tertiary air nozzles 12, 13 and the quaternary air nozzles 14-17.
- FIG. 6 shows a case where the flow rate adjustment dampers 38a and 38b for adjusting the air amount of the quaternary air nozzles 14 and 15 of the solid fuel burner 1 of the first embodiment are operated to give a deviation in the vertical flow rate of the burner 1.
- the gas temperature change at the furnace exit when the flow rate adjusting dampers 43 and 44 of the tertiary air nozzles 12 and 13 are operated to give a deviation to the flow rate in the vertical direction of the burner 1 is shown.
- the gas temperature at the furnace outlet changes due to the deviation of the air flow rate in the vertical direction of the air nozzle of the burner 1.
- a change in gas temperature at the furnace outlet indicates an increase or decrease in heat absorption in the furnace.
- a decrease in gas temperature means that heat absorption in the furnace has increased, and cooling of the combustion gas has progressed.
- the partition walls 19 and 29 and the peripheral wall obstacles 20 and 21 need to be provided.
- the outer peripheral partition wall 29 of the outermost channel is the furnace body partition wall 28 or the water wall 30 constituting the furnace.
- the inner peripheral partition wall 19 and the peripheral wall obstacles 20 and 21 are connected to a wind box 39 to which the fuel nozzle 10 and the burner 1 are connected.
- the fuel nozzle 10 and the wind box 39 have a difference in thermal expansion with the operation of the combustion apparatus (boiler) with respect to the furnace body partition wall 28 or the water wall 30.
- the quaternary air nozzles 14 to 17 are divided into four regions by the obstacles 20 and 21 connected only to the tertiary air nozzles 12 and 13, thereby providing an effect of adjusting the flow rate. Yes.
- FIG. 7 is a schematic view showing a cross section of a solid fuel burner showing a second embodiment of the present invention.
- FIG. 8 is a cross-sectional view of the solid fuel burner shown in FIG.
- the difference from the first embodiment shown in FIGS. 1 to 5 is that, in FIGS. 7 and 8, the split-type three air nozzles 12 and 13 of the first embodiment are not provided and the outermost peripheral nozzle regions 14 to 17 are not provided. Is divided in the circumferential direction.
- the outermost peripheral air nozzle is divided into regions 14 to 17 through which air corresponding to the tertiary air flows in the burner 1 by the obstacles 53 and 54.
- the regions 14 to 17 connected to the wind box 39 are composed of an upper region 14, a lower region 15, a left region 16 and a right region 17 when viewed from the furnace side, and flow control dampers 38 a provided in the upper and lower regions 14 and 15, respectively.
- 38b and the flow rate adjusting dampers 56a and 56b provided in the left and right regions 16 and 17, respectively, can individually adjust the air flow rate.
- the obstacles 53 and 54 are connected to the inner peripheral side partition wall 19 of the outermost peripheral air nozzle, and are not connected to the outer peripheral side partition wall 29 (burner throat portion which is an opening for installing the burner 1 of the furnace wall 28).
- the movement of the combustion air between the regions 14 to 17 is prevented.
- the damper 38a is throttled to flow through the upper region 14. Air flow rate and air jet velocity are reduced. For this reason, the air flow rate and the air jet velocity in the other regions 15 to 17 are increased.
- required by the product of an air flow rate and an air ejection flow velocity will increase the downward momentum with respect to the circumferential direction of the fuel nozzle 10.
- FIG. Due to the air jet ejected from the outermost peripheral air nozzle into the furnace, the surrounding gas is entrained in the jet at the outermost peripheral air nozzle outlet, and thus a negative pressure is generated. As the momentum at the outermost peripheral air nozzle increases downward, the negative pressure on the lower side increases at the outermost peripheral air nozzle outlet. For this reason, the flow 48 of the secondary air in the furnace that flows near the outermost peripheral air nozzle flows in a downwardly biased manner in the furnace. Further, since the negative pressure in the lower portion of the circulating flow 33 is increased by the flow 48 of the secondary air, the fuel jet 46 flowing near the circulating flow 33 is also biased downward.
- the fuel jet 46 is formed as a downward flow in the furnace due to the deviation of the air flow rate flowing through the regions 14 to 17 of the outermost peripheral air nozzle. Further, the fuel 51 flows downward, so that the flame 51 is also formed downward. For this reason, the temperature distribution in the furnace is biased downward, the heat absorption amount in the furnace is increased, and the heat absorption amount in the heat transfer tube provided in the downstream flue of the furnace can be reduced.
- the obstacles 53 and 54 for dividing the combustion air nozzle of the solid fuel burner 1 into a plurality of portions in the circumferential direction are provided.
- the outer peripheral partition wall 29 of the solid fuel burner 1 is constituted by the furnace body partition wall 28 or the water wall 35 constituting the furnace, and the inner peripheral partition wall 19 of the outermost air nozzle regions 14 to 17 is the fuel nozzle 10 or the burner 1.
- the outer peripheral partition wall 29 and the inner peripheral partition wall 19 have a difference in thermal expansion accompanying the operation of the combustion apparatus (boiler).
- the outermost peripheral air nozzle is divided into a plurality of regions, but the obstacles 53 and 54 are not connected to the outer peripheral partition wall 29. For this reason, it is possible to give a flow rate deviation in the circumferential direction of the fuel nozzle 10 without being affected by fluctuations in the relative positions of the outer peripheral partition wall 29 and the inner peripheral partition wall 19 due to thermal expansion differences.
- the flame formation direction in the vertical direction in the furnace is described. However, in order to form the flame in the horizontal direction in the furnace, a flow rate deviation of the combustion air flowing in the regions 16 and 17 is given. Thus, it is also possible to deflect the flame formation direction left and right.
- the obstacles 53 and 54 are connected from the inner peripheral partition wall 19, but the obstacles 53 and 54 are connected to the outer peripheral partition wall 29 as shown in FIG. It may be separated from the peripheral partition wall 19.
- the obstacles 53 and 54 are connected only to the inner peripheral partition wall 19, and the obstacles 60 and 61 are connected only to the outer peripheral partition wall 29 and connected to both the inner peripheral side and the outer peripheral side.
- Obstacles 53, 54, 60, 61 may be provided twice. By providing obstacles twice, the movement of air between the regions 14 to 17 is further reduced.
- the secondary air nozzle 11 is provided on the outer peripheral portion of the fuel nozzle 10, but the secondary air nozzle 11 is not provided and the fuel nozzle 10 and the outermost peripheral air nozzle regions 14 to 17 may contact each other. The effect of deflection of the flame formation position due to the air flow rate deviation is obtained in the same manner.
- FIG. 11 is a schematic view showing a cross section of a solid fuel burner showing a third embodiment of the present invention.
- 12 is a cross-sectional view taken along the line CC of FIG.
- the fuel nozzle 10 and the secondary air nozzle 11 have a relatively short vertical diameter, for example. This is a so-called wide nozzle having a relatively long left-right diameter.
- the fuel nozzle 10 and the secondary air nozzle 11 have shown the example by which the long side was formed in the horizontal direction.
- the outer peripheral partition walls 29 of the regions 14 to 17 of the outermost peripheral air nozzle have a circular shape having the same vertical and horizontal lengths.
- the thickness in the cross-sectional direction in the direction crossing the flow paths of the respective regions 14 to 17 of the outermost peripheral air nozzle is 1 out of the two orthogonal directions.
- the direction is thicker. For this reason, when a flow rate deviation is given to a portion having a large thickness, the flow rate is large. Therefore, a fuel jet jetted from the fuel nozzle 10 into the furnace due to a flow rate deviation ejected from the outermost peripheral air nozzle regions 14 to 17. It becomes easy to induce.
- the air nozzles are the secondary air nozzle 11 and the outermost peripheral air nozzle regions 14 to 17.
- the tertiary air nozzles 12 and 13 which are divided air nozzles may be provided inside the regions 14 to 17.
- the peripheral wall obstacles 20 and 21 of the divided type tertiary air nozzles 12 and 13 can be used as obstacles for dividing the outermost peripheral air nozzle regions 14 to 17. .
- FIG. 14 is a schematic view of a combustion apparatus in which a solid fuel burner showing a first embodiment of the present invention is provided on a furnace wall.
- the solid fuel burner 1 includes a fuel nozzle 10 and air nozzles 12 and 13.
- the air nozzles 12 and 13 are provided above and below in order to explain the air amount deviation in the vertical direction, but any of the burners 1 of the above-described first to third embodiments of the present invention can be applied.
- the fuel nozzle 10 is connected to a solid fuel pulverizer 66, a carrier air fan 67, and a fuel hopper 68 through a fuel carrier pipe 65 upstream of the fuel nozzle 10.
- the air nozzles 12 and 13 are connected to an air fan 70 via flow rate adjusting valves 71 and 72.
- a plurality of the solid fuel burners 1 are connected to the furnace 74.
- the partition wall 28 constituting the furnace 74 is constituted by a water pipe and absorbs combustion heat.
- a heat transfer surface 76 suspended from the ceiling portion in the furnace 74 and a heat transfer surface 76 disposed in the downstream flue of the furnace 74 are disposed.
- the temperature of water or steam or the temperature of the material constituting the water pipe 30 or the heat transfer pipe is measured.
- a plurality of thermometers (not shown) are installed at appropriate positions.
- FIG. 14 includes a control calculator 73 that controls the flow rate control valves 71 and 72 based on the steam temperature at the water tube outlet of the furnace 74 and the steam temperature at the outlet of the heat transfer surface 76.
- air is ejected from the air nozzles 12 and 13 configured to sandwich the fuel nozzle 10 in the vertical direction, inclining in the opposite direction to the fuel nozzle 10.
- the jet flow velocity is also increased.
- the momentum obtained by the product of the flow rate and the ejection flow velocity also increases the momentum in the axial direction, and the downward momentum increases in the furnace 74. Due to the jet of air, the surrounding gas is entrained in the jet at the outlet of the fuel nozzle 10, so that a negative pressure is generated, and the negative pressure causes the fuel jet flowing near the air jet to also flow downwardly.
- the fuel jet ejected from the fuel nozzle 10 is formed as a downward flow at the outlet of the furnace burner 1 due to the deviation of the air flow rate ejected from the air nozzles 12 and 13. Further, as the fuel flows downward, a flame formed in the furnace 74 from the solid fuel burner 1 is also formed downward. For this reason, the temperature distribution in the furnace 74 is biased downward, the heat absorption amount in the furnace 74 is increased, and the heat absorption amount in the heat transfer surface 76 provided in the downstream side flue of the furnace 74 can be decreased. It becomes.
- the air flow rate of the upper air nozzle 12 is increased, the flame formed at the outlet of the burner 1 is formed above the normal, the temperature distribution in the furnace 74 is biased upward, and heat absorption in the furnace 74 is performed. The amount is reduced, and the amount of heat absorbed by the heat transfer surface 76 provided on the downstream side flue of the furnace 74 can be increased.
- the change in the gas temperature at the furnace outlet when the burner structure shown in the first embodiment of the present invention is applied to the furnace 74 shown in FIG. 14 is as shown in FIG.
- the gas temperature at the outlet of the furnace 74 changes due to the deviation of the air flow rate in the vertical direction of the burner 1.
- a change in gas temperature at the outlet of the furnace 74 indicates an increase or decrease in heat absorption in the furnace 74.
- the lowering of the gas temperature means that the heat absorption in the furnace 74 is increased and the cooling of the combustion gas is advanced.
- the amount of heat absorbed by each heat transfer surface 76 can be changed by controlling the flow rate adjusting valves 71 and 72 via the control arithmetic unit 73 and changing the formation position of the flame.
- the temperature of the steam flowing through the wall of the furnace 74 and the heat transfer surface 76 has a predetermined design temperature to protect the turbine and the material of the heat transfer surface on the upstream side. The design temperature range can be protected by changing.
- the heat absorption amount may temporarily increase.
- the steam temperature fluctuates
- the fluctuation of the steam temperature can be suppressed by changing the formation position of the flame as described above.
- the present invention is a solid fuel burner capable of easily changing the heat absorption position in the combustion apparatus, and is highly applicable to a furnace such as a boiler having good combustion efficiency.
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Abstract
Description
このように複雑な流体経路を通る場合、各伝熱部において規定の伝熱量を得ることが重要となる。規定の伝熱量を得るため、各伝熱部に対しては燃焼ガスの温度、流量を制御する必要が生じる。
例えば、燃料ノズルの下側の空気ノズルを流れる空気流量を増加させると、ノズル出口での空気の流量と流速が上昇して運動量が増す。このとき、噴出する空気が周囲の気体を巻き込むことで燃料ノズルの下側の領域では負の圧力が生じる。このため、燃料ノズル周囲の周方向の圧力分布は、燃料ノズルの下側の領域で負の圧力が強まる。このため、燃料ノズルから火炉内に噴出する燃料は圧力分布により下向きの力が働くことで下向きに偏って流れ、火炎が通常よりも火炉内の下部に形成される。
また、反対に燃料ノズルの上側の空気ノズルを流れる空気流量を増加させると、火炉内での火炎が通常よりも上部に形成されて火炉内の温度分布が上側に偏り、火炉での熱吸収量が減少し、火炉の下流部に設けた伝熱管での熱吸収量を増加させることが可能となる。
(A)環状に構成された空気ノズルの内部を周方向に複数の領域に区分する障害物を有し、前記障害物は前記空気ノズルの内周側隔壁と接続し、外周側隔壁と接続しない。前記空気ノズルの複数の領域の少なくとも1つの領域を流れる流量を調整する流量調整手段を有し、前記空気ノズルから噴出する流れに対し、前記燃料ノズルの周方向に流量偏差を与える。
このとき、一部の空気は障害物と外周側隔壁との間隔を通り抜けるが、大部分の空気は同じ領域内に留まる。前記空気ノズルから火炉内に噴出する空気の流れが周囲の気体を巻込むことで生じる燃料ノズル周囲の周方向の圧力分布は、前記流量偏差に従って圧力分布に差が生じる。このため、燃料ノズルから噴出する燃料は前記空気ノズルから噴出する空気量の多い方向に偏って流れる。
この場合は、一部の空気は障害物と内周側隔壁との間隔を通りぬけるが、大部分の空気は同じ領域内に留まる。このため、(A)の方法と同様に燃料ノズルから噴出する燃料は前記空気ノズルから噴出する空気量の多い方向に偏って流れる。
この場合は、一部の空気は障害物と内周側または外周側隔壁との間隔を通りぬけるが、大部分の空気は同じ領域内に留まる。このため、(A)や(B)の方法と同様に燃料ノズルから噴出する燃料は前記空気ノズルから噴出する空気量の多い方向に偏って流れる。
このように燃料ノズルの上下に設けた分割型空気ノズルにより、バーナでの空気流量の制御性が高まる。
なお、前記環状の空気ノズルに加え、前記環状ノズルの外側に空気ノズルを配置して環状の空気ノズルの内部の周方向に複数の領域に区分する障害物を配置し、前記環状ノズルの外側の空気ノズルから噴出する空気量を調整する流量調整手段を有する構成にしてもよい。
固体燃料の燃焼時に発生する窒素酸化物(NOx)の抑制方法として、バーナ近傍での燃料と空気との混合を抑制し、燃料をバーナ近くでは空気不足の条件で燃焼させる方法がある。この方法を用いたバーナにおいて空気ノズルを流れる空気流量を減少させた場合には空気が燃料噴流に同伴されて中心軸側に向かって流れ、燃料との混合が早まる場合が考えられる。しかし空気ノズル先端に空気噴出流れの向きを外周側に誘導する誘導部材を設けることで、前記空気ノズルから噴出する空気の方向が外周側に固定される。このため、特に空気流量を減少させた場合にも燃料と空気とのバーナ近傍での混合を抑制することが可能となる。
図1は本発明の第1の実施形態を示す固体燃料バーナの断面を示す概略図である。また、図2は本発明の第1の実施形態を説明するため、図1の固体燃料バーナに対して空気ノズルから火炉内に噴出する空気流量に偏差を与えた場合の火炎形成状況を示すための概略図である。図3は図1に示す固体燃料バーナの火炉隔壁部分での断面矢視図(図1のA-A線断面矢視図)であり、図4は図1に示す固体燃料バーナの風箱部分での断面矢視図(図1のB-B線断面矢視図)であり、図5は図1に示す固体燃料バーナの風箱部分での断面矢視図(図1のC-C線断面矢視図)である。
燃料ノズル10を構成する隔壁18は、燃料ノズル10の外周に環状に設けられる2次空気ノズル11の内周壁を兼ねている。また、2次空気ノズル11の外周壁19は3次空気ノズル12、13や4次空気ノズル16、17の内周壁を兼ねている。燃料ノズル10を挟むように上側の3次空気ノズル12と下側の3次空気ノズル13が配置され、円筒状の隔壁19と折曲板状の周壁障害物20で上側の3次空気ノズル12が構成され、円筒状の隔壁19と折曲板状の障害物21で下側の3次空気ノズル13が構成される。4次空気ノズル14~17は周壁障害物20、21で各々の領域に区分されるものの、外周側の隔壁29と内周側の隔壁19は分離している。4次空気ノズル14は3次空気ノズル12の外周上側に設けられ、4次空気ノズル15は3次空気ノズル13の外周下側に設けられ、4次空気ノズル16は火炉側からに見て左側の3次空気ノズルの隔壁19と障害物20、21の外側に設けられ、4次空気ノズル17は火炉側からに見て右側の3次空気ノズルの隔壁19と周壁障害物20、21の外側に設けられている。
燃料(微粉炭)ノズル10の中央部を貫通してオイルガン24が設けられており、バーナ起動時や低負荷燃焼時に助燃のために使用される。固体燃料の逆火防止のために燃料ノズル10内に絞り部25が設けられている。また、燃料ノズル10と2次空気ノズル11を隔てる隔壁18の先端に保炎リング26が設けられており、該保炎リング26は燃料(微粉炭)ノズル10の先端部付近の火炉内で燃料と1次空気の混合流体と2次空気が混合して生じる循環流33を拡大する機能がある。
また火炉壁28のバーナ1を設置する開口部はバーナスロート部29であり、バーナスロート部29は4次空気ノズル14~17の外周隔壁を兼ねている。また、火炉壁28のバーナスロート部29以外の壁面には水管30が設けられている。
またこれら燃焼用空気ノズル11~17を流れる空気はバーナ1を取り囲む風箱39から供給される。
図1は、3次空気ノズル12、13から均等の噴出流速となるように空気を流した場合、図2はバーナ1の上側に設置した3次空気ノズル12の流量調整ダンパ43を操作し、他のノズルと比べて少量の空気を流した場合である。
図1~図5に示す第1の実施形態と異なる点は、図7、図8においては第1の実施形態の分割型の3空気ノズル12、13を持たず、最外周ノズル領域14~17を周方向に区分していることである。
具体的には、ダンパ38aを絞ることで上側の領域14を流れる空気流量と空気噴出流速が減る。このため、他の領域15~17の空気流量と空気噴出流速が増加する。このため、空気流量と空気噴出流速との積で求められる空気運動量は、燃料ノズル10の周方向に対して下向きの運動量が増すことになる。最外周空気ノズルから火炉内に噴出する空気噴流により、最外周空気ノズル出口では周囲のガスが噴流に巻き込まれるため、負圧が生じる。最外周空気ノズルでの運動量が下向きに強まることで、最外周空気ノズル出口では下側の負圧が強まる。このため、最外周空気ノズルのそばを流れる火炉内の2次空気の流れ48は火炉内で下向きに偏って流れる。さらに2次空気の流れ48により循環流33も下側の部分の負圧が強まるため、循環流33の傍を流れる燃料噴流46も下向きに偏る。
図11、図12に示す実施例と図7、図8に示す第2の実施形態と異なる点は、燃料ノズル10と2次空気ノズル11が、例えば上下方向の径は相対的に短く、これと直交する左右方向の径は相対的に長い、いわゆる幅広のノズルであることである。本実施形態では、燃料ノズル10と2次空気ノズル11は長辺側が水平方向に形成された例を示している。また、最外周空気ノズルの各領域14~17の外周隔壁29は上下方向と左右方向の長さが同一の円形形状となる。
固体燃料バーナ1は燃料ノズル10と空気ノズル12、13から構成される。本実施形態では、上下方向の空気量偏差について説明するため、空気ノズル12、13を上下に設けているが、前述の本発明の実施形態1から3の何れのバーナ1も適用できる。
火炉74を構成する隔壁28は水管で構成されており、燃焼熱を吸収する。さらに火炉74内の天井部から吊下げた伝熱面76と火炉74の下流側煙道に配置した伝熱面76が配置されている。また、火炉74の壁面の水管30(図1参照)や前記伝熱面76での熱吸収量を測定するため、水や蒸気の温度、又は水管30や伝熱管を構成する材料の温度を計測する温度計(図示せず)がそれぞれ適所に複数個設置される。
11 2次空気ノズル
12、13 3次空気ノズル
14~17 4次空気ノズル(最外周ノズル領域)
18、19 隔壁 20、21 周壁障害物
24 オイルガン 25 絞り部
26 障害物(保炎リング)
28 火炉壁(炉体隔壁)
29 バーナスロート部(最外周流路の外周側隔壁)
30 水壁(水管)
32、34、35 誘導部材(ガイドスリーブ)
33 循環流
37 固体燃料と1次空気の混合流体の流れ
38、40、43、44 流量調節器(ダンパ)
39 風箱 41 2次空気の流れ
42 3次空気と4次空気として用いられる空気の流れ
46 火炉内での混合流体(燃料噴流)の流れ
48 火炉内での2次空気の流れ
49、50 火炉内での3次空気と4次空気の流れ
51 火炉内での火炎外周部(燃料噴流)
53、54 障害物 56 流量調節ダンパ
65 燃料搬送管 66 固体燃料の粉砕機
67 搬送空気ファン 68 燃料ホッパ
70 空気ファン 71、72 流量調節弁
73 制御演算器 74 火炉
76 伝熱面
Claims (11)
- 固体燃料とその搬送気体の混合流体を噴出する燃料ノズルと、前記燃料ノズルの外側に配置され、燃焼用空気を噴出する少なくとも1つの空気ノズルを有する固体燃料バーナにおいて、
前記空気ノズルの内、少なくとも1つの空気ノズルは前記燃料ノズルの外周に環状に構成され、該環状空気ノズルの内部の空気流路が障害物により該環状空気ノズルの周方向に複数の領域に区分され、該区分された複数の領域のうち、少なくとも1つの領域を流れる空気流量を調整する流量調整手段を有することを特徴とする固体燃料バーナ。 - 前記環状空気ノズル内部の空気流路を、該空気ノズルの周方向に複数の領域に区分するための障害物は、(a)該空気ノズルを構成する内周側の隔壁とだけ接続した障害物、(b)該空気ノズルの外周側隔壁とだけ接続した障害物又は(c)内周側の隔壁とだけ接続した障害物と外周側の隔壁とだけ接続した障害物を組み合わせた二重障害物であることを特徴とする請求項1記載の固体燃料バーナ。
- 前記燃料ノズルの出口側の流路を横断する方向の断面形状が、該燃料ノズルの一方向の径方向の長さを相対的に短く、前記一方向の径方向に直交する径方向の長さを相対的に長くし、
前記空気ノズルの内、少なくとも1つの空気流路を構成する内周隔壁は、該空気流路を横断する方向の断面形状が、該空気ノズルの一方向の径方向の長さを相対的に短く、前記一方向の径方向に直交する径方向の長さを相対的に長くし、外周隔壁は一方向の径方向の長さと前記一方向の径方向に直交する径方向の長さが同一であることを特徴とする請求項1又は請求項2に記載の固体燃料バーナ。 - 前記燃料ノズル及び前記空気ノズルの一方向の径方向の長さが相対的に短い短辺側を鉛直方向に形成し、前記一方向の径方向に直交する径方向の長さが相対的に長い長辺側を水平方向に形成したことを特徴とする請求項3に記載の固体燃料バーナ。
- 前記環状の空気ノズルに加え、該環状の空気ノズルの外側に配置される空気ノズルを有し、前記環状の空気ノズルの外側に配置される空気ノズルから噴出する空気量を調整する流量調整手段を有することを特徴とする請求項1記載の固体燃料バーナ。
- 前記環状の空気ノズルの内部を前記空気ノズルの周方向に複数の領域に区分する障害物を、前記燃料ノズルの外側壁面に接続させたことを特徴とする請求項5に記載の固体燃料バーナ
- 前記燃料ノズルの外周に環状に構成された空気ノズルの外周に設けられる前記複数の領域に区分された空気ノズルの一部は前記燃料ノズルの上側と下側にだけ空気流路を有し、該空気流路は、該空気流路の内周側隔壁とだけ接続した障害物を備え、該障害物は燃焼用空気の流れ方向の入口と出口だけを開放した閉鎖空間を形成したことを特徴とする請求項5記載の固体燃料バーナ。
- 前記空気ノズルのうち少なくとも1つの空気ノズルの出口に空気の流れを燃料ノズルから離れた該空気ノズルの外周側方向に偏向させる誘導部材を設けたことを特徴とする請求項1記載の固体燃料バーナ。
- 前記燃料ノズルの出口に前記燃料ノズルを流れる燃料噴流又は前記燃料ノズルに近接する空気ノズルを流れる空気の流れを妨げる障害物を設けたことを特徴とする請求項1記載の固体燃料バーナ。
- 請求項1記載の固体燃料バーナを炉壁に設置した火炉を有した燃焼装置において、
前記火炉出口での燃焼ガス温度、火炉壁面に設置した伝熱管の温度、前記伝熱管を流れる流体の温度、火炉内やその下流側の煙道部に設けた伝熱管の温度又は前記伝熱管を流れる流体の温度に基づき、前記固体燃料バーナの前記空気ノズルのうち、内部が前記燃料ノズルの周方向に障害物で複数の領域に区分された前記複数の領域のうち、少なくとも1つの領域を流れる空気流量を変更する制御装置を有することを特徴とする燃焼装置。 - 請求項1記載の固体燃料バーナを炉壁に設置した火炉を有する燃焼装置の運転方法であって、
前記火炉出口での燃焼ガス温度、火炉壁面に設置した伝熱管の温度、前記伝熱管を流れる流体の温度、または火炉内やその下流側の煙道部に設けた伝熱管の温度や前記伝熱管を流れる流体の温度に基づき、前記固体燃料バーナの前記空気ノズルを流れる空気量に対し、前記燃料ノズルの周方向で偏差を与えることを特徴とする燃焼装置の運転方法。
Priority Applications (7)
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AU2009234947A AU2009234947B2 (en) | 2008-04-10 | 2009-04-03 | Solid fuel burner, combustion apparatus using solid fuel burner, and method of operating the combustion apparatus |
BRPI0911632A BRPI0911632A2 (pt) | 2008-04-10 | 2009-04-03 | queimador de combustível sólido, aparelho de combustão que usa queimador de combustível sólido e método para operar o aparelho de combustão |
EP09731364.7A EP2273193B1 (en) | 2008-04-10 | 2009-04-03 | Solid fuel burner, combustion apparatus using solid fuel burner |
KR1020107025076A KR101660051B1 (ko) | 2008-04-10 | 2009-04-03 | 고체 연료 버너, 고체 연료 버너를 이용한 연소장치와 그 운전방법 |
JP2010507142A JP5190509B2 (ja) | 2008-04-10 | 2009-04-03 | 固体燃料バーナ、固体燃料バーナを用いた燃焼装置とその運転方法 |
US12/934,158 US20110053102A1 (en) | 2008-04-10 | 2009-04-03 | Solid fuel burner, combustion apparatus using solid fuel burner, and method of operating the combustion apparatus |
CA2719040A CA2719040C (en) | 2008-04-10 | 2009-04-03 | Solid fuel burner, combustion apparatus using solid fuel burner and method of operating the combustion apparatus |
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WO2014027609A1 (ja) | 2012-08-14 | 2014-02-20 | バブコック日立株式会社 | 固体燃料バーナ |
WO2014027611A1 (ja) * | 2012-08-14 | 2014-02-20 | バブコック日立株式会社 | 固体燃料バーナと該固体燃料バーナを備えた燃焼装置の運転方法 |
JP2015072118A (ja) * | 2014-11-26 | 2015-04-16 | 三菱重工業株式会社 | 油焚きバーナ、固体燃料焚きバーナユニット及び固体燃料焚きボイラ |
US9702545B2 (en) | 2011-11-16 | 2017-07-11 | Mitsubishi Heavy Industries, Ltd. | Oil-fired burner, solid fuel-fired burner unit, and solid fuel-fired boiler |
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Publication number | Publication date |
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BRPI0911632A2 (pt) | 2015-10-13 |
KR20110000572A (ko) | 2011-01-03 |
US20110053102A1 (en) | 2011-03-03 |
AU2009234947B2 (en) | 2013-05-16 |
KR101660051B1 (ko) | 2016-09-26 |
EP2273193B1 (en) | 2016-03-16 |
JP5190509B2 (ja) | 2013-04-24 |
AU2009234947A1 (en) | 2009-10-15 |
CA2719040C (en) | 2016-01-05 |
EP2273193A4 (en) | 2014-05-21 |
JPWO2009125566A1 (ja) | 2011-07-28 |
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CA2719040A1 (en) | 2009-10-15 |
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