• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    COMBUSTION BURNER, AND, BOILER. A combustion burner (1) with a combustion nozzle (2) is described for injecting combustible gas obtained by combining solid fuel and primary air, secondary air nozzles (3, 4) for injecting secondary air from the outer periphery of the nozzle fuel (2) and a flame stabilizer (5) arranged in the opening of the fuel nozzle (2). In the combustion burner (1) the flame stabilizer (5) has a divided shape that expands in the direction of the flow of the combustible gas. In addition, in the section seen in the direction in which the flame stabilizer (5) extends, between the combustion nozzle sections (20 including the central geometry axis, the maximum distance (h) between the central geometry axis of the fuel nozzle (2) and the enlarged end of the flame stabilizer, and the internal diameter (r) of the opening (21) of the combustion nozzle (2) satisfy the ratio of h / (r / 2) 0.6).
    公开号:BR112012002169B1
    申请号:R112012002169-9
    申请日:2010-03-11
    公开日:2020-11-03
    发明作者:Keigo Matsumoto；Koutaro Fujimura；Kazuhiro Domoto；Toshimitsu Ichinose；Naofumi Abe；Jun Kasai
    申请人:Mitsubishi Heavy Industries, Ltd；
    IPC主号:
    专利说明:

    TECHNICAL FIELD
    The present invention relates to a combustion burner and a boiler including the combustion burner and, more particularly, to a combustion burner capable of reducing the amount of nitrogen oxide (NOx) emission and a boiler including the burner of combustion. BACKGROUND OF THE INVENTION
    Conventional combustion burners typically employ a configuration to stabilize the external flame of the combustion flame. In this configuration, an area of high temperature and high oxygen is formed in a part of the outer periphery of the combustion flame, resulting in an increase in the amount of NOx emission. As an example of such conventional combustion burners 15 employing this configuration, a technology described in Patent Document 1 is known.
    [Patent Document 1] Japanese Patent No. 2781740 DESCRIPTION OF THE INVENTION PROBLEM TO BE SOLVED BY THE INVENTION
    The present invention aims to provide a combustion burner capable of reducing the amount of NOx emission and a boiler including the combustion burner. MEANS TO SOLVE THE PROBLEM
    According to one aspect of the present invention, a combustion burner includes: a fuel nozzle that injects prepared combustible gas by mixing solid fuel and primary air; a secondary air nozzle that injects secondary air from the outer periphery of the fuel nozzle; and a flame carrier that is arranged in a fuel nozzle opening. The flame carrier has a divider shape that extends in the direction of the flow of the combustible gas and, when viewed in cross section along the direction in which the flame carrier expands, the cross section passing through a central geometric axis of the nozzle of fuel, a maximum distance h from the central axis of the fuel nozzle to an extended end of the flame carrier and an internal diameter r of the fuel nozzle opening satisfy h / (r / 2) <0.6. EFFECT OF THE INVENTION
    Because the combustion burner according to the present invention achieves stabilization of the internal flame of the combustion flame (stabilization of the flame in a central area of the opening of the fuel nozzle), an external peripheral part of the combustion flame is kept in low temperature compared to the settings for stabilizing the external flame of the combustion flame (stabilizing the flame at the outer periphery of the fuel nozzle or stabilizing the flame 15 in an area close to the inner wall surface of the fuel nozzle opening). Therefore, with secondary air, the temperature of the outer peripheral part of the combustion flame in a high oxygen atmosphere can be lowered. This is advantageous in that the amount of NOx emission in the outer peripheral part of the combustion flame is reduced. BRIEF DESCRIPTION OF THE DRAWINGS
    Fig. 1 is a diagram of a combustion burner configuration according to an embodiment of the present invention.
    Fig. 2 is a front view of a combustion burner opening illustrated in Fig. 1.
    Fig. 3 is a schematic to explain a combustion burner flame carrier illustrated in Figure 1.
    Fig. 4 is a schematic to explain the effects of the combustion burner illustrated in Fig. 1.
    Fig. 5 is a graph of the results of the combustion burner performance test illustrated in Fig. 1.
    Fig. 6 is a schematic to explain the effects of the flame carrier illustrated in Fig. 3.
    Fig. 7 is a graph of the results of the combustion burner performance test.
    Fig. 8 is a schematic to explain a combustion burner flow rectifier structure illustrated in Fig. 1.
    Fig. 9 is a schematic to explain a flow rectifying ring of the rectifier structure illustrated in Fig. 8.
    Fig. 10 is a schematic to explain a modification of the combustion burner illustrated in Fig. 1.
    Fig. 11 is a schematic to explain a modification of the combustion burner illustrated in Fig- 1 •
    Fig. 12 is a schematic to explain a modification of the combustion burner illustrated in Fig. 1-
    Fig. 13 is a graph of the results of the combustion burner performance test.
    Fig- 14 is a schematic to explain a modification of the combustion burner illustrated in Fig. 1-
    Fig- 15 is a schematic to explain a modification of the combustion burner illustrated in Fig- 1-
    Fig- 16 is a schematic to explain a modification of the combustion burner illustrated in Fig- 1-
    Fig- 17 is a schematic to explain a modification of the combustion burner illustrated in Fig- 1 •
    Fig- 18 is a schematic to explain a modification of the combustion burner illustrated in Fig- 1 •
    Fig- 19 is a schematic to explain a modification of the combustion burner illustrated in Fig- 1 •
    Fig. 20 is a schematic to explain the amount of NOx emission when the combustion burner illustrated in Fig-1 is applied to a boiler using an additional air system.
    Fig. 21 is a schematic to explain the amount of NOx emission when the combustion burner of Fig. 1 is applied to the boiler using the additional air system.
    Fig- 22 is a configuration diagram for a typical pulverized coal combustion boiler. BEST MODE (S) FOR CARRYING OUT THE INVENTION
    The present invention will now be described in detail with reference to the accompanying drawings. This embodiment is not intended to limit the present invention. The components of the embodiment include components that are replaceable and obviously replaceable while maintaining the unit of the invention. A plurality of modifications described in the embodiment can be combined in any way within the scope obvious to those skilled in the art. [Pulverized Coal Combustion Boiler]
    Fig. 22 is a configuration diagram for a typical pulverized coal combustion boiler. This pulverized coal combustion boiler 100 is a boiler that burns pulverized coal to produce thermal energy and is used for power generation or industrial applications, for example.
    The pulverized coal combustion boiler 100 includes an oven 110, a combustion apparatus 120 and a steam generating apparatus 130 (see Fig. 22). Furnace 110 is a furnace for burning pulverized coal and includes a combustion chamber and a flue gas duct 112 connected above the combustion chamber 111.0 combustion apparatus 120 is an apparatus that burns pulverized coal and includes combustion burners 121, systems pulverized coal supply 122 supplying pulverized coal to the respective combustion burners 121, and a supply system 123 supplying secondary air to the combustion burners 121. The combustion apparatus 120 is arranged so that the combustion burners 121 are connected to the combustion chamber 111 5 of the oven 110. In the combustion apparatus 120, the air supply system 123 supplies additional air to complete the oxidation and combustion of the pulverized coal to the combustion chamber 111.0 steam generating apparatus 130 is an apparatus which heats fed water to the boiler through heat exchange with combustible gas to generate steam and includes a 131 economizer, a re heater 132 a superheater 133 and a steam drum (not shown). The steam generating apparatus 130 is configured so that the economizer 131, the reheater 132 and the superheater 133 are arranged stepwise in the flue gas duct 112 of the oven 110.
    In the pulverized coal combustion chamber 100, first, in the combustion apparatus 120, the pulverized coal supply system 122 supplies pulverized coal and primary air to the combustion burner 121, and the air supply system 123 supplies secondary air to combustion of the combustion burner 121 (see Fig. 22). Subsequently, combustion burner 121 ignites combustion gas containing pulverized coal, primary air and secondary air and injects the combustible gas into the combustion chamber 111. Consequently, the combustible gas burns in the combustion chamber 111, whereby the gas fuel is produced. The combustible gas is then discharged from the combustion chamber 111 through the flue gas duct. In this process, the steam generating apparatus 130 causes the heat exchanged between the fuel gas and the water fed to the boiler to generate steam. The steam is to be supplied to an external plant (a steam turbine, for example).
    In the pulverized coal combustion boiler 100, the sum of the quantity of primary air supply and the quantity of secondary air supply is established to be less than a theoretical volume of air with respect to the quantity of pulverized coal supply, by means of than the combustion chamber 111 is maintained in a reducing atmosphere. The NOx 5 emitted as a result of the combustion of the pulverized coal is reduced in the combustion chamber 111, and additional air (AA) is then further supplied, whereby the oxidation and combustion of the pulverized coal is completed (additional air system ). Thus, the amount of NOx emission due to the combustion of the pulverized coal is reduced. [Combustion Burner]
    Fig. 1 is a diagram of a combustion burner configuration according to an embodiment of the present invention and is a sectional view of the combustion burner in the direction of its height along its central geometric axis. Fig. 2 is a front view of a combustion burner opening illustrated in Fig. 1.
    This combustion burner 1 is a solid fuel combustion burner and is used as the combustion burner 121 in the pulverized coal combustion boiler 100 shown in Fig. 22, for example. An example will now be given where the pulverized coal is used 20 as solid fuel and the combustion burner 1 is applied to the pulverized coal combustion boiler 100. The combustion burner 1 includes a fuel nozzle 2, a secondary air nozzle main 3, a secondary air nozzle 4 and a flame carrier 5 (see Figs. 1 and 2). Fuel nozzle 2 is a nozzle 25 that injects fuel gas (primary air containing solid fuel) prepared by mixing pulverized coal (solid fuel) and primary air. The main secondary air nozzle 3 is a nozzle that injects primary secondary air (coal secondary air) into the outer periphery of the fuel gas injected by the fuel nozzle 2. The secondary air nozzle 4 is a nozzle that injects secondary air into the fuel nozzle. external periphery of the main secondary air injected by the main secondary air nozzle 3. The flame carrier 5 is a device used to ignite the combustible gas and stabilize the flame and is arranged in an opening 21 of the fuel nozzle 2.
    For example, in the present embodiment, the fuel nozzle 2 and the main secondary air nozzle 3 each have an elongated tubular structure and have rectangular openings 21 and 31, respectively (see Figs. 1 and 2). With the fuel nozzle 2 in the center, the main secondary air nozzle 3 is arranged on the outside, whereby 10 a double tube is formed. The secondary air nozzle 4 has a double tube structure and has an opening shaped like a ring 41. In the inner ring of the secondary air nozzle 4, the fuel nozzle 2 and the main secondary air nozzle 3 are inserted and arranged. Therefore, with the opening 21 of the fuel nozzle 2 in the center, the opening 31 of the main secondary air nozzle 3 is arranged on the outside of the opening 21 and the opening 41 of the secondary air nozzle 4 is arranged on the outside of the opening. 31. The openings 21 to 41 of these nozzles 2 to 4 are aligned and arranged coplanarly. The flame carrier 5 is supported by a plate member (not shown) on the upstream side of the fuel gas, and is arranged in the opening 21 of the fuel nozzle 2. The 20 downstream ends (extended end) of the flame carrier 5 and of the openings 21 to 41 of these nozzles 2 to 4 are aligned coplanarly.
    In the combustion burner 1, the fuel gas prepared by mixing pulverized coal and primary air is injected through the opening 21 of the fuel nozzle 2 (see Fig. 1). In this process, the combustible gas 25 is branched in the flame carrier 5 at the opening 21 of the fuel nozzle 2 and then ignited and burned to be combustible gas. At the outer periphery of the combustible gas, the primary secondary air is injected through the opening 31 of the primary secondary air nozzle 3, whereby combustion of the combustible gas is facilitated. At the external periphery of the combustion flame the secondary air is supplied through the opening 41 of the secondary air nozzle 4, whereby the external peripheral part of the combustion flame is cooled. [Flame Bearer Arrangement]
    In the combustion burner 1, to reduce the amount of NOx emission as a result of the combustion of the pulverized coal, the arrangement of the flame carrier 5 relative to the opening 21 of the fuel nozzle 2 is optimized, which will be described below.
    First, when viewed in cross section along a direction in which the flame carrier 5 extends, the cross section passing through the central geometric axis of the fuel nozzle 2, the flame carrier 5 has a widening split shape in the direction of the flow of the fuel gas (mixed gas of pulverized coal and primary air) (see Figs. 1 and 3). In addition, a maximum distance h from the central geometrical axis of the fuel nozzle 2 to the enlarged end (the downstream end of the split shape) of the flame carrier 5 and an internal diameter r of the opening 21 of the fuel nozzle 2 satisfy h / (r / 2) <0.6.
    For example, in the first embodiment, the fuel nozzle 2 has a rectangular opening 21 and is thus arranged in which its height direction is aligned with the vertical direction and its width direction is aligned with the horizontal direction (see Figs. 1 and 2). At the opening 21 of the fuel nozzle 2, the flame carrier 5 is arranged. The flame carrier 5 has a split shape that extends in the direction of the fuel gas flow and has an elongated shape in the direction perpendicular to the direction of widening. The flame carrier 5 has its longitudinal direction aligned with the width direction of the fuel nozzle 2 and substantially 1 crosses the opening 21 of the fuel nozzle 2 in the direction of the width of the opening 21. In addition, the flame carrier 5 it is arranged in the center line of the opening 21 of the fuel nozzle 2, thereby bisecting the opening 21 of the fuel nozzle 2 in the direction of the height of the opening 21. The flame carrier 5 has a substantially isosceles triangular cross section and a substantially elongated shape prismatic (see Figs. 1 and 3). When viewed in cross section along the axial direction of the fuel nozzle 2, the flame carrier 5 is arranged on the central geometric axis of the fuel nozzle 2. Specifically, the flame carrier 5 has its apex directed towards the upstream side of the combustible gas and its base arranged in alignment with the opening 21 of the fuel nozzle 2. In this way, the flame carrier 5 has a split shape that extends in the direction of the flow of the combustible gas. In addition, the flame carrier 5 has a division angle (the apex angle of the isosceles triangle) θ and a division width (the base length of the isosceles triangle) L placed in predetermined respective sizes. The flame carrier 5 having such a split shape is arranged in a central area of the opening 21 of the fuel nozzle 2 (see Figs. 1 and 2). The "central area" of opening 21 here means an area where, with the flame carrier 5 having a split shape that widens in the direction of the flow of the combustible gas, when viewed in cross section along the direction in which the carrier of flame 5 widens, the cross section passing through the central geometric axis of the fuel nozzle 2, the maximum distance h from the central geometric axis of the fuel nozzle 2 to the widened end (the end downstream of the split shape) of flame 5 and the internal diameter r of the opening 21 of the fuel nozzle 2 satisfy h / (r / 2) <0.6. In the present embodiment, because the flame carrier 5 is arranged on the central geometric axis of the fuel nozzle 2, the maximum distance h from the central geometric axis of the fuel nozzle 2 to the extended end of the flame carrier 5 is a half Vi of the split width of the flame carrier 5.
    In the combustion burner 1, because the flame carrier 5 has a split shape, the combustible gas is branched in the flame carrier 5 at the opening 21 of the fuel nozzle 2 (see Fig. 1). In this configuration, the flame carrier 5 is arranged in the central area of the opening 21 of the fuel nozzle 2 and the combustible gas is ignited and the flame is stabilized in this central area. Thus, stabilization of the internal flame of the combustion flame (stabilization of the flame in the central area of the opening 21 of the fuel nozzle 2) is achieved.
    In this configuration, compared to the settings (not shown) for stabilizing the external flame of the combustion flame (stabilizing the flame at the outer periphery of the fuel nozzle or stabilizing the flame in an area close to the inner wall surface of the nozzle opening fuel), an external peripheral part Y of the combustion flame is kept at low temperature (see Fig. 4). Therefore, with secondary air, the temperature of the outer peripheral part Y of the combustion flame in an atmosphere of high oxygen can be lowered. Thus, the amount of NOx emission in the outer peripheral part Y of the combustion flame is reduced.
    Fig. 5 is a graph of the results of the combustion burner performance test illustrated in Fig. 1, representing test results of the relationship between a position h / (r / 2) of the flame carrier 5 of the nozzle opening 20 21 of fuel 2 and the amount of NOx emission.
    This performance test measured in the combustion burner 1 illustrated in Fig. 1, the amount of NOx emission, with the distance h from the flame carrier 5 varied. The internal diameter r of the fuel nozzle 2, the division angle θ and the division width L of the flame carrier 5, for example, have been established constants. The amount of NOx emission is represented in values related to a configuration that stabilizes the external flame of the combustion flame (a configuration in which a flame carrier is disposed on the outer periphery of a fuel nozzle, see Patent Document 1) ( that is, h / (r / 2) = 1).
    As the test results represent, it can be seen that the amount of NOx emission decreases when the position of the flame carrier 5 approaches the center of the opening 21 of the fuel nozzle 2 (see Fig. 5). Specifically, with the position of the flame carrier 5 5 satisfying h / (r / 2) <0.6, the amount of NOx emission decreases equal to or more than 10%, exhibiting advantageous properties.
    In the combustion burner 1, it is preferable that the ends of the flame carrier 5 in the longitudinal direction and the inner wall surface of the opening 21 of the fuel nozzle 2 come into contact 10 with each other. In the typical design, however, a small gap d of a few millimeters is defined between the ends of the flame carrier 5 and the internal wall surface of the fuel nozzle 2, in consideration of the thermal expansion of the members (see Fig. 2). Thus, in the configuration in which the ends of the flame carrier 5 and the inner wall surface of the fuel nozzle 15 are arranged close together, the ends of the flame carrier 5 are exposed to radiation from the combustion flame. As a result, flame propagation proceeds from the ends of the flame carrier 5 to the inside, which is preferable. [Split Angle and Split Width of the Flame Bearer]
    In combustion burner 1, to suppress the amount of NOx emission as a result of combustion of solid fuel, it is preferable that the shape of the flame carrier division 5 is optimized, which will be described below.
    As mentioned earlier, in the combustion burner 25 1, the flame carrier 5 has the division format to branch the combustible gas (see Fig. 3). In this configuration, it is preferable that the flame carrier 5 has a division shape with a triangular cross section with its apex directed towards the upstream side of the flow direction of the combustible gas (see Fig. 6 (a)). With the flame carrier 5 having such a triangular cross section, the branched combustible gas flows along the side surfaces of the flame carrier 5 and is pulled into the base 1 side due to the differential pressure. This makes it difficult for the combustible gas to diffuse outwardly in the radial direction of the flame carrier 5 and, therefore, the stabilization of the internal flame of the combustion flame is properly ensured (or increased). Consequently, the outer peripheral part Y of the combustion flame (see Fig. 4) is kept at a low temperature, whereby the amount of NOx emission due to mixing with secondary air is reduced.
    In a configuration in which a flame carrier has a plate-like split shape (see Fig. 6 (b)), the branched fuel gas flows towards the inner wall surface of a flame carrier fuel nozzle. This is a typical configuration of conventional combustion burners in which the combustible gas is branched in the flame carrier and guided along the surface of the inner wall of the fuel nozzle. In this configuration, an area close to the internal wall surface of the fuel nozzle becomes rich in fuel gas, compared to a central area of the fuel nozzle, and the outer peripheral part Y of the combustion flame has a higher temperature than a inner part X (see Fig. 4). As a result, in the outer peripheral part Y of the combustion flame, the amount of NOx emission, due to mixing with secondary air, may increase.
    In the configuration described above, it is preferable that the division angle 0 of the flame carrier 5, having a triangular cross section, is 0 <90 (degrees) (see Fig. 3). It is still preferable that the split angle 0 of the flame carrier 5 is 0 <60 (degrees). Under such conditions, the branched fuel gas is prevented from diffusing towards the sides of the wall surface without the fuel nozzle, whereby stabilization of the internal flame of the combustion flame is more appropriately ensured.
    For example, in the present embodiment, the flame carrier 5 has a division shape with an isosceles triangular cross section, and the division angle θ is fixed as θ <90 (degrees) (see 5 Figure 3). In addition, because the flame carrier 5 is arranged symmetrically with respect to the direction of flow of the combustible gas, each lateral inclined angle (0/2) is determined below 30 (degrees).
    In addition, in the configuration described above, it is preferable that the split width L of the flame carrier 5 with a triangular cross section 10 and the internal diameter r of the opening 21 of the fuel nozzle 2 satisfy 0.06 <T, / r is more preferable to satisfy 0.10 <L / r. Under such conditions, an L / r ratio of the split width L of the flame carrier 5 to the inner diameter r of the fuel nozzle 2 is optimized, whereby the amount of NOx emission is reduced.
    Fig. 7 is a graph of the results of the combustion burner performance test, representing the test results of the relationship between the L / r ratio of the split width L of the flame carrier 5 to the inner diameter r of the opening 21 of the fuel nozzle 2 and the amount of NOx emission.
    This performance test measured, in the combustion burner 1 shown in Fig. 1, the amount of NOx emission, with the width of division L of the flame carrier 5 varied. The internal diameter r of the fuel nozzle 2, the distance h and the angle of division θ of the flame carrier 5, for example, were kept constant. The amount of NOx emission is represented in relative values for an example where the width of division L for the combustion flame is L = 0.
    As the test results represent, it can be seen that the amount of NOx emission decreases when the width of division L of the flame carrier 5 increases. Specifically, it can be observed that the amount of NOx emission decreases by 20% with 0.06 <L / r and the amount of NOx emission decreases equal to or more than 30% with 0.10 <L / r. However, with 0.13 <L / r, a decrease in the amount of NOx emission tends to the bottom. The upper limit of the split width L is defined by the relation to the position h / (r / 2) of the flame carrier 5 at the opening 21 of the fuel nozzle 2. In other words, if the split width L becomes too wide , the position of the flame carrier approaches the internal flame stabilizing the effect for the combustion flame to be lowered, which is not preferable (see Fig. 5). Therefore, it is preferable that the split width L of the flame carrier 5 is optimized based on the relationship (L / r ratio) with the internal diameter r of the opening 21 of the fuel nozzle 2 and the relationship with the position h / (r / 2) of the flame carrier 5.
    Although the flame carrier 5 has a triangular cross section in the present embodiment, this is not limiting. The flame carrier 5 may have a V-shaped cross section (not shown). This setting also provides similar effects. However, it is preferable that the flame carrier 5 has a triangular cross section, instead of a V shaped cross section. For example, a V shaped cross section can cause the flame bearer to deform due to the heat of irradiation during combustion with oil fuel (1). In addition, ash can be retained, adhered to and deposited within the flame carrier. With the flame carrier 5 having a triangular cross section and the oven made of ceramic, the adhesion 25 of the ash is relieved. [Fuel Nozzle Rectifying Structure]
    Fig. 8 is a schematic for explaining a combustion burner flow rectifying structure illustrated in Fig. 1. Fig. 9 is a schematic for explaining a rectifying structure flow rectifying ring illustrated in Fig. 8.
    In conventional combustion burners with a configuration that stabilizes the external flame of the combustion flame, the combustible gas or secondary air is supplied in swirling flows or flows with steep angles. In this way, a recirculation area is formed on the outer periphery of a fuel nozzle, whereby external ignition and external flame stabilization are carried out efficiently (not shown).
    Conversely, because the combustion burner 110 employs the configuration that stabilizes the internal flame of the combustion flame as described above, it is preferable that the combustible gas and the secondary air (primary secondary air and secondary air) are supplied in straight flows (see Fig. 1). In other words, it is preferable that the fuel nozzle 2, the main secondary air nozzle 3 and the secondary air nozzle 4 have a structure for supplying combustible gas, the secondary air was straight flows without swirling them.
    For example, it is preferable that the fuel nozzle 2, the main secondary air nozzle 3 and the secondary air nozzle 4 have an unimpeded structure that prevent straight flows of fuel gas or secondary air in their internal gas passages (see Fig. 1). Such obstacles include, for example, eddy blades to produce eddy flows and a structure to guide gas flows towards an area close to the inner wall surface.
    In this configuration, because the combustible gas and secondary air 25 are injected in straight flows to form a combustion flame, in a configuration that stabilizes the internal flame of the combustion flame, the gas circulation in the combustion flame is suppressed. Consequently, the outer peripheral part Y of the combustion flame (see Fig. 4) is kept at a low temperature, whereby the amount of NOx emission due to mixing with secondary air is reduced.
    In addition, in the combustion burner 1 it is preferable that the fuel nozzle 2 has a flow rectification mechanism 6 (see Figs. 8 and 9). The flow rectification mechanism 6 is a mechanism that 5 rectifies the fuel gas flows to be supplied to the fuel nozzle 2 and has the function of causing the pressure drop in the fuel gas passing through the fuel nozzle 2 and suppressing the diversion fuel gas flow, for example. In this configuration, the flow rectification mechanism 6 produces straight flows of combustible gas in the fuel nozzle 2. 10 With the flame carrier 5 being arranged in the central area of the opening 21 of the fuel nozzle 2, the stabilization of the internal fuel of the flame combustion is carried out (see Fig. 1). The stabilization of the internal flame is thus properly ensured, whereby the amount of NOx emission in the outer peripheral part Y of the combustion flame (see Fig. 4) is reduced.
    For example, in the present embodiment, the fuel nozzle 2 has a circular tube structure on the upstream side of the combustible gas (at the base of the combustion burner 1) and its cross section is gradually changed to be a rectangular cross section on the opening 20 21 (see Figs. 2, 8 and 9). The flow rectification mechanism 6 of an annular orifice is arranged in an upstream part of the fuel nozzle 2. The fuel nozzle 2 has a linear (straight shape) passage of the combustible gas from a position where the rectification mechanism of flow 6 is disposed through the opening 21. Within the fuel nozzle 2, in a range of the flow rectification mechanism 6 to the opening 21 (the flame carrier 5) no obstacle that prevents the straight flows is placed. In this way, a structure (flow rectification structure for fuel gas) is formed in which the flow rectification mechanism 6 rectifies the fuel gas flows and the straight flows of the fuel gas are directly supplied to the opening 21 of the fuel nozzle 2 .
    It is preferable that the distance between the flow rectifying mechanism 6 and the opening 21 of the fuel nozzle 2 is equal to or greater than twice (2H) a height H of the combustion burner 1 and it is more preferable that the distance be ten times (10H) height H. In this way, adverse effects of placing the flow rectification mechanism 6 for fuel gas flows are reduced, whereby preferable straight flows are formed. [First Flame Bearer Modification]
    In the present embodiment, in a front view of the fuel nozzle 2, the fuel nozzle 2 has the rectangular opening 21 and the flame carrier 5 is arranged to substantially cross-section the central area of the opening 21 of the fuel nozzle 2 ( see Fig. 2). In addition, a single elongated flame carrier 5 is disposed.
    This is not, however, limiting and in the combustion burner 1 a pair of flame carriers 5, 5 can be arranged in parallel in the central area of the opening 21 of the fuel nozzle 2 (see Fig. 10). In this configuration, an area interspersed between the pair of flame carriers 5, 5 is formed at the opening 21 of the fuel nozzle 2 (see figure 11). In the interspersed area, shortage of air occurs. As a result, a reducing atmosphere due to scarcity of air is formed in the central area of the opening 21 of the fuel nozzle. Thus, the amount of NOx emission in the internal part X of the combustion flame (see Fig. 4) is reduced.
    For example, in the present embodiment, the pair of elongated flame carriers 5, 5 is arranged in parallel, with their longitudinal directions aligned with the direction of the width of the opening 21 of the fuel nozzle 2 (see Fig. 10). With these flame carriers 5, 5 substantially cross-sectioning the opening 21 of the fuel nozzle 2, the opening 21 of the fuel nozzle 2 is divided into three areas in the height direction. When viewed in cross section along the direction in which the flame carrier 5 extends, the cross section passing through the central geometric axis of the fuel nozzle 2, each of the flame carriers 5, 5 has a split shape with a triangular cross section with its direction widening in line with the flow direction of the fuel gas (see Fig. 11). The pair of flame carriers 5, 5 is configured so that both are in the central area of the opening 21 of the fuel nozzle 2. Specifically, they are configured so that a maximum distance h from the central geometric axis of the fuel nozzle 2 for the respective enlarged ends of the flame carrier pair 5, 5 and the inner diameter r of the opening 21 of the fuel nozzle 2 satisfy h / (r / 2) <0.6. In this way, the internal flame stabilization of the combustion flame is carried out.
    In the configuration described above, the pair of flame carriers 5, 5 is arranged (see Figs. 10 and 11). This is not, however, limiting and three or more flame carriers 5 can be arranged in parallel in the central area of the opening 21 of the fuel nozzle 2 (not shown). In such a configuration also a reducing atmosphere, due to the scarcity of air, is formed in areas interspersed between the adjacent flame carriers 5, 5. Thus, the amount of NOx emission in the internal part X of the combustion flame (see Fig 4) is reduced. [Second Modification of Flame Bearer Format] Alternatively, in combustion burner 1, the pair of flame bearers 5, 5 can be arranged so that they intersect and be connected, and their intersection is placed in the central area of the opening 21 of the fuel nozzle 2 (see Fig. 12). In this configuration, with the pair of flame carriers 5, 5 crossing and being connected, a strong surface of strong ignition is formed at its intersection. With this intersection placed in the central area of the opening 21 of the fuel nozzle 2, the stabilization of the internal flame of the combustion flame is carried out properly. Thus, the amount of NOx emission in the internal part X of the combustion flame (see Fig. 4) is reduced. For example, in the present embodiment, the pair of 5 elongated flame carriers 5, 5 is arranged with their longitudinal directions aligned with the direction of the width and the height of the opening 21 of the fuel nozzle 2 (see Fig. 12 ). These flame carriers 5, 5 substantially cross-section aperture 21 in the direction of width and in the direction of height, respectively. These 10 flame 5, 5 carriers are arranged in the central area of the fuel nozzle opening 2. In this way, the intersection of the flame carriers 5, 5 is placed in the central area of the fuel nozzle opening 2. In addition , the flame carriers 5 are configured so that the maximum distance h (h ') from the central geometric axis of the fuel nozzle to the respective 15 extended ends of the flame carriers 5 and the internal diameter r (r') of the opening 21 of the fuel nozzle 2 satisfy h / (r / 2) <0.6 (h7 (r '/ 2) <0.6). Thus, stabilization of the internal flame of the combustion flame is achieved.
    In the configuration described above, the pair of carriers 5, 5 is arranged 20 (see Fig. 12). This is not, however, limiting and three or more flame carriers 5 can cross and be connected with their intersection placed in the central area of the fuel nozzle opening (not shown). In such a configuration also, the intersection of the flame bearers 5, 5 is formed in the central area of the opening 21 of the fuel nozzle 2. 25 Thus, the stabilization of the internal flame of the combustion flame is carried out properly and the amount of emission of NOx in the internal part X of the combustion flame (see Fig. 4) is reduced.
    Fig. 13 is a graph of combustion burner performance test results representing comparative test results of combustion burner 1 shown in Fig. 10 and combustion burner 1 shown in Fig. 12. Combustion burners 1 are common in that both have the pair of flame carriers 5, 5 arranged in the central area of the opening 21 of the fuel nozzle 2. However, both differ from each other in that the combustion burner 1 shown in Fig. 10 has a structure (parallel division structure) in which the pair of flame carriers 5, 5 is arranged in parallel, while the combustion burner 1 shown in Figure 12 has a structure (cross division structure) in which the pair of flame carriers flame 5, 5 is arranged in an intersecting manner. Numeric values 10 of unburned carbon are relative values for combustion burner 1 (1.00) illustrated in Fig. 10.
    As the test results represent, it can be seen that, in combustion burner 1 illustrated in Figure 12, unburned carbon decreases relatively. [Third Modification of Flame Bearer Format]
    Alternatively, in the combustion burner 1, a plurality of flame carriers 5 can be arranged in a number sign pattern (#) and the area surrounded by these flame carriers 5 can be placed in the central area of the fuel nozzle opening 21 2 (see Fig. 14). In other words, the configuration of Fig. 10 and the configuration of Fig. 12 can be combined. In this configuration, a surface of strong ignition is formed over the area surrounded by the flame bearers 5. With the area surrounded by the flame bearers 5 placed in the central area of the opening 21 of the fuel nozzle 2, the stabilization of the internal flame of the flame of combustion is carried out properly. Thus, the amount of NOx emission in the internal part X of the combustion flame (see Fig. 4) is reduced.
    For example, in the present embodiment, four elongated flame carriers 5 are arranged in a number sign pattern and are configured so that their longitudinal directions are aligned with the width direction or the height direction of the fuel nozzle 2 ( see Fig. 14). Each flame carrier 5 substantially cuts the opening 21 of the fuel nozzle 2 in the direction of the width or in the direction of the height. Each of the four flame carriers 5 is arranged in the central area of the opening 21 of the fuel nozzle 2. Thus, the area surrounded by the flame carriers 5 is arranged in the central area of the opening 21 of the fuel nozzle 2. In addition, the flame carriers 5 are configured so that the maximum distance h from the central geometric axis 10 of the fuel nozzle 1 to the respective extended ends of the flame carriers 5 and the internal diameter r of the opening 21 of the fuel nozzle 2 satisfy h / ( r / 2) <0.06. Thus, the stabilization of the internal flame of the combustion flame is carried out properly.
    In the configuration described above, it is preferable that the spans of arrangement between the flame carriers 5 are small (see Fig. 14). In this configuration, a free area in the area surrounded by flame carriers 5 is small. Consequently, a pressure drop in the area surrounding the flame carrier 5 becomes relatively large due to the shape of the flame carrier division 5, whereby the flow rate of the combustible gas in the area surrounded by the flame carrier 5 in the fuel nozzle 2 decreases. Therefore, the ignition of the fuel nozzle 2 decreases. Therefore, the ignition of the fuel gas is carried out quickly.
    In the configuration described above, four flame carriers 5 25 are arranged in a number sign pattern (see Fig. 14). This is not, however, limiting and any number of (for example, two in the direction of height and three in the direction of width) flame carriers 5 can be connected to form an area surrounded by flame carriers 5 (not shown). With the area surrounded by the flame carriers 5 placed in the central area of the opening 21 of the fuel nozzle 2, stabilization of the internal flame of the combustion flame is carried out properly. [Example of Application with Fuel Nozzle Having Circular Opening]
    In the present embodiment, in a front view of the fuel nozzle 2, the fuel nozzle 2 has the rectangular opening 21 in which the flame carriers 5 are arranged (see Figs. 2, 10, 12 and 14). This is not, however, limiting and the fuel nozzle 2 can have a circular opening 21, in which the flame carriers 5 are arranged (see Figs. 15 and 16).
    For example, in the combustion burner 1 shown in Fig. 15, in the circular opening 21, flame carriers 5, having a cross-split structure (see Fig. 12), are arranged. In the combustion burner 1 shown in Fig. 16, in the circular opening 21, the flame carriers 5, connected in a numerical signal pattern (see Fig. 14), are arranged.
    In these configurations, with the intersection of flame bearers 5 (see Fig. 12) or the area surrounded by flame bearers 5 (see Fig. 14) disposed in the central area of the opening 21 of the fuel nozzle 2, the stabilization of the internal flame of the combustion flame is carried out properly.
    For example, with circular opening 21, secondary air is supplied uniformly through multiple supplies of secondary air through concentric circles. This suppresses the formation of a local area of high oxygen, which is preferable. [Secondary Air Nozzle Damping Structure]
    In general, the outer peripheral part Y of the combustion flame 25 tends to be a local area of high temperature and high oxygen, due to the supply of secondary air (see Fig. 4). It is therefore preferable that the amount of secondary air supply is adjusted to alleviate this state of high temperature and high oxygen. On the other hand, when a large amount of unburned combustible gas remains, it is preferable that this is relieved.
    Therefore, in the combustion burner 1, a plurality of (three, in this example) secondary air nozzles 4 is arranged on the outer periphery of the main secondary air nozzle 3 (see Fig. 17). In addition, the main secondary air nozzle 3 and each secondary air nozzle 4 have a damping structure, thereby adjusting the supply quantities of the main secondary air and the secondary air. In this configuration, it is preferred that each secondary air nozzle 4 is able to adjust the injection direction of the secondary air within a range of ± 30 (degrees).
    In this configuration, when a secondary air nozzle 4 arranged on the external side injects more secondary air than a secondary air nozzle 4 arranged on the internal side, the diffusion of the secondary air is relieved. Consequently, a state of high temperature and high oxygen in the outer peripheral part Y of the combustion flame is relieved. On the other hand, in this configuration, when a secondary air nozzle 4, disposed on the internal side, injects more secondary air than a secondary air nozzle 4 arranged on the internal side, the diffusion of the secondary air is promoted. Consequently, an increase in unburned combustible gas is suppressed. In this way, by adjusting the amount of secondary air injection from each secondary air nozzle 4, the state of the combustion flame is appropriately controlled.
    The configuration described above is useful when solid fuels with different fuel ratios are selectively used. For example, when coal with a high volatile content is used as a solid fuel, adjusting to cause secondary air diffusion at an early stage, the state of the combustion flame is properly controlled.
    In the configuration described above, it is preferable that all primary secondary air nozzles 4 are constantly operated. In this configuration, in comparison with a configuration in which some nozzle (s) is / are not operated, the burning of the secondary air nozzles, caused by the irradiation of flame from the oven, is suppressed. For example, all secondary air nozzles 4 are constantly operated. In addition, secondary air is injected at a minimum flow rate to an extent that a specific secondary air nozzle 4 will not be burned. The other secondary air nozzles 4 supply secondary air over wide ranges of flow rate and flow rate. In this way, the secondary air supply can be carried out properly, depending on changes in the operating conditions of the boiler. For example, during low load operation of the boiler, secondary air is injected at a minimum flow rate to an extent that a portion of the secondary air nozzles 4 will not be burned. The amount of secondary air supply to the other secondary air nozzles 4 is adjusted as well. The flow rate of the secondary air can thus be maintained, whereby the state of the combustion flame is properly maintained.
    In the configuration described above, a part of the secondary air nozzles 4 can also serve as an oil orifice (see Fig. 18). In this configuration, for example, when combustion burner 1 is applied to the pulverized coal combustion boiler 100, a part of the secondary air nozzles 4 is used as an oil orifice. Through the secondary air nozzle (s) 4, the oil necessary to start the boiler operation is supplied. This configuration eliminates the need for additional oil holes or additional secondary air nozzles, thereby reducing the height of the boiler.
    In the configuration described above, it is preferable that the primary secondary air supplied to the primary secondary air nozzles 3 and the secondary air supplied to the secondary air nozzle 4 are supplied through different supply systems (see Fig. 19). In this configuration, even when a large number of secondary air nozzles (the main secondary air nozzle 3 and a plurality of such secondary air nozzles 4) are provided, they are readily operated and adjusted. [Application in Flamed Boiler on Wall]
    It is preferable that combustion burner 1 is applied to a Flamed Wall boiler (not shown). In this configuration, because the secondary air is gradually supplied, the amount of air supply can be readily controlled. Thus, the amount of NOx emission is reduced. [Adoption of Additional Air Supply System] It is preferable that combustion burner 1 is applied to the pulverized coal combustion boiler 100, which employs the additional air system (see Fig. 22).
    In other words, this combustion burner 1 employs a configuration that stabilizes the internal flame of the combustion flame (see Fig. 11). Therefore, uniform combustion of the internal part X of the combustion flame is promoted, whereby the temperature of the outer peripheral part Y of the combustion flame is reduced and the amount of NOx emission from the combustion burner 1 is reduced (see Figs. 4 and 5). Consequently, the air supply ratio by the combustion burner 1 is increased, whereby the additional air supply ratio is decreased. Thus, the amount of NOx emission caused by the additional air is reduced and the amount of NOx emission from the entire boiler is reduced.
    Figs. 20 and 21 are schematic to explain the amount of NOx emission when this combustion burner 1 is applied to a boiler using an additional air system.
    Conventional combustion burners employ a configuration that stabilizes the external flame of the combustion flame (see Patent Document 1). This configuration causes an area where oxygen remains in the internal part X of the combustion flame (see Fig. 4). Therefore, in order to sufficiently reduce NOx, in general, the rate of additional air supply needs to be adjusted to about 30% to 40% and the excess air ratio of a combustion burner to an additional air supply area needs to be adjusted. at about 0.8 (see the left side of Fig.20). This in turn causes a problem with a large amount of NOxI emitted in the additional air supply area.
    In contrast, combustion burner 1 employs a configuration that stabilizes the internal flame of the combustion flame (see 10 Fig. 1). In this configuration, because uniform combustion in the internal part X of the combustion flame (see Fig. 4) is promoted, a reducing atmosphere is formed in the internal part X of the combustion flame. Therefore, the excess air ratio from combustion burner 1 to the additional air supply area can be increased (see Fig. 21). Therefore, although the ratio of excess air from combustion burner 1 to the additional air supply area is increased to about 0.9, the rate of additional air supply can be decreased to about 0% to 20% (see the right side of fig. 20). In this way, the amount of NOx emission in the additional air supply area is reduced and the amount of NOx emission by the entire boiler is reduced.
    In combustion burner 1, by stabilizing the internal flame of the combustion flame, the excess air ratio of the entire boiler can be reduced to 1.0 to 1.1 (typically, the excess air ratio is about 1.15). The boiler efficiency thus increases. [Effects] As described above, on combustion burner 1, when viewed in cross section along the direction in which the flame carrier 5 expands, the cross section passing through the central geometric axis of the fuel nozzle 2, the fuel carrier flame 5 has a split shape that expands in the direction of flow of the combustible gas (see Figs. 1 and 3). The maximum distance h (h ') from the central geometric axis of the fuel nozzle 2 to the respective extended ends of the flame carriers 5 and the internal diameter r (r') of the opening 21 of the fuel nozzle 2 satisfy h / 5 (r / 2) <0.6 (see Figs. 1, 2, 10 to 12 and 14 to 16). Because this configuration achieves internal flame stabilization of the combustion flame (flame stabilization in a central area of the fuel nozzle opening), the outer peripheral part Y of the combustion flame is kept at a low temperature compared to the settings (no illustrated) for stabilization of the external flame of the combustion flame (stabilization of the flame on the outer periphery of the fuel nozzle or stabilization of the flame in an area close to the internal wall surface of the fuel nozzle opening) (see Fig. 4). Therefore, with secondary air, the temperature of the outer peripheral part Y of the combustion flame and an atmosphere of high oxygen can be lowered. This is advantageous in that the amount of NOx emission in the outer periphery Y part of the combustion flame (see Fig. 4) is reduced.
    In the combustion burner 1, the "central area" of the opening 21 of the fuel nozzle 2 means an area where, with the 20 flame carrier 5 having a split shape that widens in the direction of the flow of the combustible gas, when viewed in cross section along the direction in which the flame carrier 5 extends, the cross section passing through the central geometric axis of the fuel nozzle 2, the maximum distance h (h1) from the central geometric axis of the fuel nozzle 2 to the the enlarged ends 25 (the downstream end of the split formation) of the flame carriers 5 and the inner diameter r (r ') of the opening 21 of the fuel nozzle 2 satisfy h / (r / 2 <0.6 (h' / r '/ 2)> 0.6) (see Figs. 1.2, 10 to 12 and 14 to 16). The maximum distance h (h ') means the maximum distance h (h') of a plurality of wide ends of the flame carriers 5. The internal diameter of the fuel nozzle 2 refers to when the opening 21 of the fuel nozzle 2 it is rectangular, an internal size r, r 'in its width and height directions (see Figs. 2, 10, 12 and 14); refers to, when the opening 21 of the fuel nozzle 2 is circular, its diameter r 5 (see Figs. 15 and 16); and refers to, when the opening 21 of the fuel nozzle 2 is elliptical, its long diameter and short diameter (not shown).
    In the combustion burner 1, the split width L of the split format of the flame carrier 5 and the internal diameter r of the opening 10 21 of the fuel nozzle 2 satisfy 0.06 <L / r (see Figs. 1 and 3) . In this configuration, because the L / r ratio of the split width L of the flame carrier 5 to the internal diameter r of the fuel nozzle 2 is optimized, the stabilization of the internal flame is adequately ensured. This is advantageous in that the amount of NOx emission in the outer peripheral part Y of the combustion flame (see Fig. 4) is reduced.
    In the combustion burner 1, the fuel nozzle 2 and the secondary air nozzles 3, 4 have a structure that injects fuel gas or secondary air in direct flow (see figs. 1, 8 and 11). In this configuration, the combustible gas and the secondary air are injected in straight flows to form a combustion flame, whereby, in a configuration that stabilizes the internal flame of the combustion flame, the gas circulation in the combustion flame is suppressed. . Consequently, the outer peripheral part of the combustion flame is kept at a low temperature, whereby the amount of NOx emission due to mixing with secondary air is reduced.
    In the combustion burner 1, the flame carriers 5 are arranged in parallel in the central area of the opening 21 of the fuel nozzle 2 (see Figs. 10, 11, 14 and 16). In this configuration, in an area interspersed between the adjacent flame bearers 5, 5, a reducing atmosphere, due to the scarcity of air, is formed. This is advantageous in that the amount of NOx emission in the internal part X of the combustion flame (see Fig. 4) is reduced.
    In the combustion burner 1, the pair of flame carriers 5, 5, 5 are arranged so that they cross and are connected and their intersection is placed in the central area of the opening 21 of the fuel nozzle 2 (see Figs. 12, and 14 to 16). In this configuration, with the pair of flame carriers 5, 5 intersecting and connected, a surface of strong ignition is formed at their intersection. With the intersection arranged in the central area of the opening 21 of the fuel nozzle 2, stabilization of the internal flame of the combustion flame is carried out properly. Thus, the amount of NOx emission in the internal part X of the combustion flame (see Fig. 4) is reduced.
    In the combustion burner 1, a plurality of secondary air nozzles 15 (the secondary air nozzle 4) are arranged and these secondary air nozzles are able to adjust the amount of secondary air supply in a relative manner to each other (see Fig. . 17). In this configuration, by adjusting the amount of secondary air injection from each secondary air nozzle 4, the state of the combustion flame is adequately controlled 20, which is advantageous.
    In the combustion burner 1 with the configuration described above, all secondary air nozzles (secondary air nozzles 4) are constantly operated. This configuration is advantageous in that, compared to a configuration in which some secondary air nozzle (s) is / are not operated, the burning of the secondary air nozzles caused by the irradiation of oven flame is suppressed.
    In the combustion burner 1 with the configuration described above, a part of the secondary air nozzles 4 also serves as an oil orifice or a gas orifice (see Fig. 18). In this configuration, for example, when the combustion burner 1 is applied to the pulverized coal combustion boiler 100, through the secondary air nozzle (s) 4 also serving as an oil orifice or an orifice. gas, the oil required to start the boiler operation can be supplied. This is advantageous in that this configuration eliminates the need for additional oil holes or additional secondary air holes and the boiler height can be reduced. INDUSTRIAL APPLICABILITY
    As described above, the combustion burner and the boiler including the combustion burner according to the present invention are useful in terms of reducing the amount of NOx emission.
    LETTERS OR NUMBER EXPLANATIONS 1 combustion burner 2 fuel nozzle 21 opening 3 main secondary air nozzle 31 opening 4 secondary air nozzle 41 opening 5 flame carrier 6 flow rectifying mechanism 100 boiler 110. oven 111. combustion chamber 112. fuel gas duct 120. combustion appliance 121. combustion burner 122. pulverized coal supply system 123. air supply system 130 steam generating apparatus 131 economizer 132 reheater 133 superheater
    权利要求:
    Claims (11)
    [0001]
    1. Combustion burner (1), comprising: a fuel nozzle (2) that is configured to inject fuel gas prepared by mixing solid fuel and primary air; a secondary carbon air nozzle (3) disposed on an external side of the fuel nozzle (2) and configured to inject secondary coal air from an external periphery of the fuel nozzle (2); a secondary air nozzle (4) arranged on an external side of the fuel nozzle (2) and the secondary coal air nozzle (3) and configured to inject secondary coal air from the external periphery of the fuel nozzle (2 ); and a plurality of flame carriers (5) which are arranged in an opening (21) of the fuel nozzle (2), characterized by the fact that: the flame carriers (5) have a split format that expands in one direction of flow of the fuel gas and has a vertex directed upstream of the flow direction to branch / divide the fuel gas in a direction of flow of the fuel gas when viewed in cross section along a direction in which the carriers of flame (5) widen; and the fuel nozzle (2), the secondary coal air nozzle (3) and the secondary air nozzle (4) are respectively configured to inject fuel gas, the secondary coal air and the secondary air in a straight flow without swirl them.
    [0002]
    2. Combustion burner (1), according to claim 1, characterized by the fact that, when seen in cross section along a direction in which the flame carrier (5) widens, the cross section passing through a central axis of the fuel nozzle (2), a maximum distance h from the central axis of the fuel nozzle (2) to an enlarged end of the flame carrier (5) and an internal diameter r of the opening (21) of the fuel nozzle fuel (2) satisfy h / (r / 2) <0.6.
    [0003]
    3. Combustion burner (1) according to claim 1 or 2, characterized by the fact that the division width L of the flame carrier division format (5) and the internal diameter r of the opening (21) of the fuel nozzle (2) satisfy 0.06 <L / r.
    [0004]
    Combustion burner (1) according to any one of claims 1 to 3, characterized in that a plurality of such flame carriers (5) is arranged in parallel in a central area of the opening (21) of the nozzle fuel (2).
    [0005]
    Combustion burner (1) according to any one of claims 1 to 4, characterized in that a plurality of flame carriers (5) are connected.
    [0006]
    Combustion burner (1) according to any one of claims 1 to 5, characterized in that the fuel nozzle (2) has a rectangular or elliptical opening and the flame carrier (5) substantially cross-section an area center of the fuel nozzle opening (21) (2).
    [0007]
    Combustion burner (1) according to any one of claims 1 to 5, characterized in that the fuel nozzle (2) has a circular opening and the flame carrier (5) substantially crosses a central area of the opening (21) of the fuel nozzle (2).
    [0008]
    Combustion burner (1) according to any one of claims 1 to 7, characterized in that a plurality of such secondary air nozzles (4) are arranged, and the secondary air nozzles (4) are capable of adjust a quantity of secondary air supply in a relative manner to each other.
    [0009]
    9. Combustion burner (1), according to claim 8, characterized in that all secondary air nozzles (4) are constantly operated.
    [0010]
    10. Combustion burner (1) according to claim 8 or 9, characterized in that a part of the secondary air nozzles (4) also serves as an oil opening or gas opening.
    [0011]
    11. Boiler, characterized by the fact that it comprises the combustion burner (1) as defined in any one of claims 1 to 10.
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    同族专利:
    公开号 | 公开日
    JP2011149676A|2011-08-04|
    CN103644565B|2017-03-01|
    KR20120034769A|2012-04-12|
    US20160010853A1|2016-01-14|
    EP2518404A1|2012-10-31|
    CL2012000251A1|2012-08-31|
    BR112012002169A2|2016-05-31|
    KR101436777B1|2014-09-03|
    EP2518404A4|2015-06-03|
    US9127836B2|2015-09-08|
    CN102414512A|2012-04-11|
    CN103644565A|2014-03-19|
    US9869469B2|2018-01-16|
    JP5374404B2|2013-12-25|
    MY154695A|2015-07-15|
    MX2012001169A|2012-02-13|
    US20120247376A1|2012-10-04|
    KR20130133089A|2013-12-05|
    TW201122373A|2011-07-01|
    EP2518404B1|2017-07-12|
    TWI519739B|2016-02-01|
    PL2518404T3|2017-12-29|
    WO2011077762A1|2011-06-30|
    ES2638306T3|2017-10-19|
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    法律状态:
    2019-01-15| B06F| Objections, documents and/or translations needed after an examination request according [chapter 6.6 patent gazette]|
    2019-09-03| B06U| Preliminary requirement: requests with searches performed by other patent offices: procedure suspended [chapter 6.21 patent gazette]|
    2020-06-02| B09A| Decision: intention to grant [chapter 9.1 patent gazette]|
    2020-11-03| B16A| Patent or certificate of addition of invention granted [chapter 16.1 patent gazette]|Free format text: PRAZO DE VALIDADE: 10 (DEZ) ANOS CONTADOS A PARTIR DE 03/11/2020, OBSERVADAS AS CONDICOES LEGAIS. |
    优先权:
    申请号 | 申请日 | 专利标题
    JP2009-290899|2009-12-22|
    JP2009290899|2009-12-22|
    JP2010-026882|2010-02-09|
    JP2010026882A|JP5374404B2|2009-12-22|2010-02-09|Combustion burner and boiler equipped with this combustion burner|
    PCT/JP2010/054091|WO2011077762A1|2009-12-22|2010-03-11|Combustion burner and boiler provided with combustion burner|
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