WO2009125566A1 - Brûleur à combustible solide, appareil de combustion utilisant un brûleur à combustible solide, et procédé de fonctionnement de l'appareil de combustion - Google Patents

Brûleur à combustible solide, appareil de combustion utilisant un brûleur à combustible solide, et procédé de fonctionnement de l'appareil de combustion Download PDF

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Publication number
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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WO
WIPO (PCT)
Prior art keywords
air
nozzle
furnace
fuel
solid fuel
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Application number
PCT/JP2009/001573
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English (en)
Japanese (ja)
Inventor
岡▲崎▼洋文
木山研滋
越智佑介
倉増公治
Original Assignee
バブコック日立株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Publication date
Application filed by バブコック日立株式会社 filed Critical バブコック日立株式会社
Priority to US12/934,158 priority Critical patent/US20110053102A1/en
Priority to CA2719040A priority patent/CA2719040C/fr
Priority to KR1020107025076A priority patent/KR101660051B1/ko
Priority to JP2010507142A priority patent/JP5190509B2/ja
Priority to AU2009234947A priority patent/AU2009234947B2/en
Priority to EP09731364.7A priority patent/EP2273193B1/fr
Priority to BRPI0911632A priority patent/BRPI0911632A2/pt
Publication of WO2009125566A1 publication Critical patent/WO2009125566A1/fr

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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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D1/00—Burners for combustion of pulverulent fuel
    • 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
    • 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
    • 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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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Pre-Mixing And Non-Premixing Gas Burner (AREA)

Abstract

Selon l'invention, une buse à air formée sur le côté externe d'une buse de combustible (10) d'un brûleur à combustible solide (1) est divisée circonférentiellement en régions (12-17). La buse à air comprend des moyens (43, 44) pour réguler les débits d'écoulement d'écoulements d'air s'écoulant à travers les régions supérieure et inférieure divisées (12, 13). La buse (régions 12-17) est reliée uniquement à une paroi de buse (19) et comprend des obstacles (20, 21) pour diviser circonférentiellement l'intérieur de la buse en sections. Lorsque les débits des écoulements d'air s'écoulant à travers les régions dans la périphérie la plus à l'extérieur du brûleur sont modifiés, une différence de moment dans la direction haut-bas du brûleur (1) est produite et la position à laquelle une flamme est formée est modifiée. Grâce à cela, la température du gaz de combustion à la sortie d'un four, la température d'un tube de transfert de chaleur installé sur une surface de paroi de four, la température du fluide s'écoulant dans le tube de transfert de chaleur, les températures de tubes de transfert de chaleur installés dans le four et dans une conduite de gaz en aval du four, et les températures de fluides s'écoulant dans les tubes de transfert de chaleur sont régulées de façon à être constantes.
PCT/JP2009/001573 2008-04-10 2009-04-03 Brûleur à combustible solide, appareil de combustion utilisant un brûleur à combustible solide, et procédé de fonctionnement de l'appareil de combustion WO2009125566A1 (fr)

Priority Applications (7)

Application Number Priority Date Filing Date Title
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 (fr) 2008-04-10 2009-04-03 Bruleur a combustible solide, appareil de combustion utilisant un bruleur a combustible solide et procede de fonctionnement de l'appareil de combustion
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
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
EP09731364.7A EP2273193B1 (fr) 2008-04-10 2009-04-03 Brûleur à combustible solide, appareil de combustion utilisant un brûleur à combustible solide
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

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JP2008-102048 2008-04-10
JP2008102048 2008-04-10

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WO2009125566A1 true WO2009125566A1 (fr) 2009-10-15

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US (1) US20110053102A1 (fr)
EP (1) EP2273193B1 (fr)
JP (1) JP5190509B2 (fr)
KR (1) KR101660051B1 (fr)
AU (1) AU2009234947B2 (fr)
BR (1) BRPI0911632A2 (fr)
CA (1) CA2719040C (fr)
WO (1) WO2009125566A1 (fr)

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US20130340659A1 (en) * 2011-02-22 2013-12-26 Babcock-Hitachi Kabushiki Kaisha Combustion device
WO2014027609A1 (fr) 2012-08-14 2014-02-20 バブコック日立株式会社 Brûleur à combustible solide
WO2014027611A1 (fr) * 2012-08-14 2014-02-20 バブコック日立株式会社 Brûleur à combustible solide et procédé de fonctionnement d'un dispositif de combustion ayant un brûleur à combustible solide
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
KR20170134705A (ko) * 2015-06-12 2017-12-06 미츠비시 히타치 파워 시스템즈 가부시키가이샤 버너, 연소 장치, 보일러 및 버너의 제어 방법
US11306915B2 (en) 2018-09-26 2022-04-19 Taiheiyo Cement Corporation Cement kiln burner device and method for operating the same

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DE102011018697A1 (de) * 2011-04-26 2012-10-31 Babcock Borsig Steinmüller Gmbh Brenner für partikelförmigen Brennstoff
US9638413B2 (en) 2014-03-05 2017-05-02 Progreen Labs, Llc Treatment device of a heating system
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US9593857B2 (en) 2014-03-07 2017-03-14 ProGreen Labs, LLC. Heating system
CN104595890B (zh) * 2015-02-05 2017-01-25 湖南吉祥石化科技股份有限公司 附墙无缝扁平火焰低氮氧化物排放燃烧器
PL3130851T3 (pl) * 2015-08-13 2021-08-02 General Electric Technology Gmbh Instalacja i sposób zapewnienia spalania w kotle
JP2020030037A (ja) * 2018-08-20 2020-02-27 三菱日立パワーシステムズ株式会社 固体燃料バーナ
JP7223595B2 (ja) * 2019-02-19 2023-02-16 ポリプラスチックス株式会社 付着物除去装置及び方法

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US20130340659A1 (en) * 2011-02-22 2013-12-26 Babcock-Hitachi Kabushiki Kaisha Combustion device
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
JP5832653B2 (ja) * 2012-08-14 2015-12-16 三菱日立パワーシステムズ株式会社 固体燃料バーナ
US9599335B2 (en) 2012-08-14 2017-03-21 Mitsubishi Hitachi Power Systems, Ltd. Solid-fuel burner
JP2014055759A (ja) * 2012-08-14 2014-03-27 Babcock-Hitachi Co Ltd 固体燃料バーナを備えた燃焼装置
CN104508372A (zh) * 2012-08-14 2015-04-08 三菱日立电力系统株式会社 固体燃料燃烧器
WO2014027609A1 (fr) 2012-08-14 2014-02-20 バブコック日立株式会社 Brûleur à combustible solide
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WO2014027611A1 (fr) * 2012-08-14 2014-02-20 バブコック日立株式会社 Brûleur à combustible solide et procédé de fonctionnement d'un dispositif de combustion ayant un brûleur à combustible solide
JP5908091B2 (ja) * 2012-08-14 2016-04-26 三菱日立パワーシステムズ株式会社 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
CN104508372B (zh) * 2012-08-14 2016-06-08 三菱日立电力系统株式会社 固体燃料燃烧器
JPWO2014027609A1 (ja) * 2012-08-14 2016-07-25 三菱日立パワーシステムズ株式会社 固体燃料バーナ
WO2014027610A1 (fr) * 2012-08-14 2014-02-20 バブコック日立株式会社 Dispositif de combustion ayant un brûleur à combustible solide
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
KR20170134705A (ko) * 2015-06-12 2017-12-06 미츠비시 히타치 파워 시스템즈 가부시키가이샤 버너, 연소 장치, 보일러 및 버너의 제어 방법
KR102080380B1 (ko) 2015-06-12 2020-02-21 미츠비시 히타치 파워 시스템즈 가부시키가이샤 버너, 연소 장치, 보일러 및 버너의 제어 방법
US11306915B2 (en) 2018-09-26 2022-04-19 Taiheiyo Cement Corporation Cement kiln burner device and method for operating the same

Also Published As

Publication number Publication date
EP2273193A4 (fr) 2014-05-21
EP2273193B1 (fr) 2016-03-16
CA2719040A1 (fr) 2009-10-15
KR101660051B1 (ko) 2016-09-26
AU2009234947A1 (en) 2009-10-15
JPWO2009125566A1 (ja) 2011-07-28
JP5190509B2 (ja) 2013-04-24
AU2009234947B2 (en) 2013-05-16
US20110053102A1 (en) 2011-03-03
KR20110000572A (ko) 2011-01-03
CA2719040C (fr) 2016-01-05
BRPI0911632A2 (pt) 2015-10-13
EP2273193A1 (fr) 2011-01-12

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