KR20210134356A - solid fuel burner - Google Patents

Abstract

In the fuel concentrator (34) provided on the central side of the fuel nozzle (21) to impart a velocity component in a direction away from the center of the fuel nozzle (21) to the mixed fluid, a plurality of blades (41a) for imparting rotation to the mixed fluid , 41b), and by configuring the turning angle of the blade 41a to be adjustable in the burner axial direction, it is possible to switch between coal and biomass fuel and use it while maintaining the risk of wear and ignitability.

Description

solid fuel burner

The present invention relates to a solid fuel burner that transports and burns a solid fuel, and particularly relates to a solid fuel burner suitable for fuel particles having a large particle size such as biomass particles.

As a method of improving the ignition property of a solid fuel burner used for boilers, such as a thermal power plant, and improving flame stability, there exists a method of raising a fuel concentration or raising the oxygen concentration of fuel carrier gas.

For example, in Patent Document 1 (Japanese Patent No. 5886031 Specification: JP 5886031 B2), by arranging the turning blade 16 in the flow path of the biomass fuel ejection nozzle 11 to form a swirling flow, fuel is concentrated on the outer periphery. is described. In Patent Document 1, the turning degree adjusting plate 17 is disposed on the downstream side of the turning blade 16 to adjust the turning of the fuel flow.

In Patent Document 2 (Japanese Patent No. 6231047 specification: JP 6231047 B2), in the center of the primary air nozzle 9, a first swirler 6 for imparting swirl to the mixed fluid, and a first swirler 6 ) and the technique of providing the 2nd turning machine 7 which gives turning in the reverse direction is described. In the technique described in Patent Document 2, a strong vortex is applied to the mixed fluid with the first vortex device 6 to move the solid fuel particles to the outer peripheral side of the primary air nozzle, and the second vortex device 7 is used for the first The swirl of the mixed fluid is weakened by giving the swirl in the opposite direction to the swirler 6 . Accordingly, while solid fuel particles are concentrated in the vicinity of the flame retarder 10 installed in the opening of the burner, the mixed fluid with less rotation is discharged from the opening to improve ignition performance.

In Patent Document 3 (US Patent Publication No. 2013/0305971 Publication: US 2013/0305971 A1), a spiral blade-shaped deflection means 17, 18, 19 is provided in a flow channel 5, and a flow path ( A technique for concentrating fuel on the outer periphery of flow channel 5) is described.

In Patent Document 4 (Chinese Patent Application Laid-Open No. 101832551 A: CN 101832551 A), a weight-shaped member 10 for moving the flow to the outer periphery is disposed on the upstream side of the member 11 for imparting a turning. In Patent Document 4, the weight-shaped member 10 and the member 11 for providing the turning are configured so that the position in the axial direction can be adjusted by the rod-shaped members 19 and 20 .

Specification of Japanese Patent No. 5886031 ([0030]-[0031], Figs. 1- Fig. 3, Fig. 21) Specification of Japanese Patent No. 6231047 ([0048]-[0061], Figs. 1- Fig. 3, Fig. 21) US Patent Publication No. 2013/0305971 ([0041]-[0043], FIG. 1) Chinese Patent Laid-Open No. 101832551 ([0036]-[0038], FIG. 1)

From social demands, such as a warming countermeasure, the solid fuel burner which uses biomass fuel like the technique of patent document 1 is calculated|required. However, in the present situation, the supply of biomass fuel is not stable. Therefore, it is preferable that coal and biomass can be switched and used according to the situation of procurement of a fuel.

In the burners described in Patent Documents 1 to 4, turning is applied to the mixed fluid to concentrate the fuel on the outer peripheral side. Here, compared with coal, biomass fuel has a low risk of abrasion at the time of the collision with respect to the member which provides turning. Compared with coal, the ignitability is low in the biomass fuel, and there is a difference that the risk to burnout is also low.

Therefore, when coal fuel is simply used for the burner for biomass fuels described in patent document 1, while the risk of abrasion is high, although ignitability is high, there exists a problem of being easy to burn. Conversely, when biomass fuel is used for the burner for pulverized coal described in Patent Documents 2 to 4, there is a problem of low ignitability although it is difficult to wear.

The present invention makes it a technical subject to switch between coal and biomass fuel and use it while maintaining the risk to wear and ignitability.

In order to solve the above technical problem, the solid fuel burner of the invention according to claim 1,

A fuel nozzle through which a mixed fluid of the solid fuel and its carrier gas flows and is opened toward the furnace;

a combustion gas nozzle disposed on the outer peripheral side of the fuel nozzle to eject combustion gas;

A fuel concentrator provided on the central side of the fuel nozzle to apply a velocity component in a direction away from the center of the fuel nozzle to the mixed fluid.

A solid fuel burner having a

The fuel concentrator has a plurality of blades for imparting rotation to the mixed fluid, and a rotation angle of the blades with respect to the burner axial direction is adjustable.

The invention according to claim 2 is the solid fuel burner according to claim 1,

It is characterized in that while installing at two places spaced apart from the burner axial direction, the turning direction of each of the plurality of blade structures is in the opposite direction, and the turning angle of the blade at least upstream with respect to the flow direction of the mixed fluid is adjustable. do it with

The invention according to claim 3 is the solid fuel burner according to claim 1,

The fuel concentrator is configured to be movable along the burner axial direction.

In order to solve the above technical problem, the solid fuel burner of the invention according to claim 4,

A fuel nozzle through which a mixed fluid of the solid fuel and its carrier gas flows and is opened toward the furnace;

a combustion gas nozzle disposed on the outer peripheral side of the fuel nozzle to eject combustion gas;

A fuel concentrator provided on the central side of the fuel nozzle to apply a velocity component in a direction away from the center of the fuel nozzle to the mixed fluid.

A solid fuel burner having a

The fuel concentrator has a plurality of blades for imparting rotation to the mixed fluid, and is installed in two places spaced apart from the burner axial direction, and the rotation direction of each of the plurality of blade structures is in the reverse direction,

The fuel concentrator is configured to be movable along the burner axial direction.

The invention according to claim 5 is the solid fuel burner according to claim 4,

The fuel concentrator may be configured such that a turning angle of at least an upstream blade with respect to the burner axial direction with respect to the flow direction of the mixed fluid is adjustable.

The invention according to claim 6 is the solid fuel burner according to any one of claims 1 to 5,

and a shaft for supporting the blade;

A spraying device for spraying cleaning gas toward the boundary between the blade and the shaft

It is characterized in that it is provided with.

The invention according to claim 7 is the solid fuel burner according to claim 6,

The injection device having a jet port for discharging gas in a radial direction from the shaft portion, and a gas guide member for guiding the gas from the jet port to a boundary portion between the blade and the shaft portion.

It is characterized in that it is provided with.

According to the invention described in claim 1, since the turning angle of the blade of the fuel concentrator can be adjusted, the turning angle can be adjusted according to the fuel used, and the coal and biomass fuel can be switched while maintaining the risk of wear and ignitability. can be made available.

According to the invention described in claim 2, in addition to the effects of the invention described in claim 1, at least the swing angle of the upstream blade can be adjusted, and the swing angle of the upstream blade can be adjusted according to the fuel used, The blades on the downstream side can dampen the swirl of the mixed fluid. Therefore, the expansion of the classification of the mixed fluid can be adjusted.

According to the invention described in claim 3, in addition to the effects of the invention described in claim 1, the position of the fuel concentrator along the burner axial direction can be adjusted according to the fuel to be used, and the risk of burnout can be dealt with.

According to the invention described in claim 4, since the fuel concentrator having blades opposite to each other can move in the axial direction, the position in the axial direction can be adjusted according to the fuel used, and the coal and coal can be separated while maintaining the risk of wear and ignitability. Biomass fuels can be converted and made available.

According to the invention described in claim 5, in addition to the effect of the invention described in claim 4, at least the swing angle of the upstream blade can be adjusted. , can respond to the risk of burnout.

According to the invention described in claim 6, in addition to the effects of the invention described in any of claims 1 to 5, it is possible to suppress the accumulation of fine particles of solid fuel at the boundary portion between the blade and the shaft. Accordingly, it is possible to suppress the inability to adjust the turning angle or move the fuel concentrator due to the deposition of fine particles.

According to the invention described in claim 7, in addition to the effects of the invention described in claim 6, the gas ejected from the jetting port is guided by the gas guide member, and deposition of fine particles can be suppressed with a simple configuration.

BRIEF DESCRIPTION OF THE DRAWINGS It is an overall explanatory drawing of the combustion system of Example 1 of invention.
It is explanatory drawing of the solid fuel burner of Example 1. FIG.
Fig. 3 is an explanatory view of the turning angle inclination mechanism of the blade of the fuel concentrator according to the embodiment, Fig. 3 (A) is a cross-sectional view of a main part, Fig. 3 (B) is an explanatory view of a high-angle position, and Fig. 3 (C) is It is explanatory drawing of a low-angle position.
It is explanatory drawing of the analysis result of the position and opening diameter of a downstream blade with respect to a coal fuel and a biomass fuel.
5 is an explanatory diagram of another embodiment 1 of the present invention.
Fig. 6 is an explanatory view of another embodiment 2 of the present invention, Fig. 6 (A) is a schematic view, and Fig. 6 (B) is a partial detailed view.
It is explanatory drawing of the gas guide member in the form shown in FIG.

Next, specific examples (hereinafter, referred to as examples) of the embodiments of the present invention will be described with reference to the drawings, but the present invention is not limited to the following examples. In addition, in the description using the following drawings, illustration other than the member necessary for description is abbreviate|omitted suitably for the ease of understanding.

Example 1

BRIEF DESCRIPTION OF THE DRAWINGS It is an overall explanatory drawing of the combustion system of Example 1 of this invention.

In FIG. 1 , in a combustion system (combustion device) 1 of Example 1 used in a thermal power plant or the like, biomass fuel (solid fuel) is accommodated in a bunker (fuel hopper) 4 . The biomass fuel of the bunker 4 is pulverized with a mill (pulverizer) 5 . The pulverized fuel is supplied to a solid fuel burner 7 of a boiler (furnace) 6 through a fuel pipe 8 and burned. In addition, a plurality of solid fuel burners 7 are provided in the boiler 6 .

The exhaust gas discharged from the boiler 6 is denitrified in the denitration device 9 . The denitrified exhaust gas passes through the air preheater 10 . In the air preheater 10 , heat exchange between the air sent from the blower 11 and the exhaust gas is performed. Accordingly, the air from the blower 11 is heated while the temperature of the exhaust gas is lowered. The air from the blower 11 is supplied as combustion air to the solid fuel burner 7 and the boiler 6 through the air pipe 12. As shown in FIG.

When the exhaust gas that has passed through the air preheater 10 passes through the gas gas heater (heat recovery unit) 13 , heat is recovered and the temperature is lowered.

As for the exhaust gas that has passed through the gas gas heater (heat recovery device) 13 , dust and the like in the exhaust gas are recovered and removed by the dry dust collector 14 .

The exhaust gas that has passed through the dry dust collector 14 is sent to the desulfurization device 15 for desulfurization.

As for the exhaust gas that has passed through the desulfurization device 15 , dust and the like in the exhaust gas are recovered and removed by the wet dust collector 16 .

The exhaust gas that has passed through the wet dust collector 16 is reheated by a gas gas heater (reheater) 17 .

The exhaust gas that has passed through the gas gas heater (reheater) 17 is exhausted from the chimney 18 to the atmosphere.

In addition, since the structure of the mill 5 itself can use various conventionally well-known structures, for example, since it describes in Unexamined-Japanese-Patent No. 2010-242999 etc., detailed description is abbreviate|omitted.

It is explanatory drawing of the solid fuel burner of Example 1. FIG.

Fig. 3 is an explanatory view of the turning angle inclination mechanism of the blade of the fuel concentrator of the embodiment, Fig. 3 (A) is a cross-sectional view of a main part, Fig. 3 (B) is an explanatory view of a high-angle position, and Fig. 3 (C) is It is explanatory drawing of a low-angle position.

In FIG. 2, the solid fuel burner 7 of Example 1 has the fuel nozzle 21 through which the carrier gas flows. The opening of the downstream end of the fuel nozzle 21 is provided in the wall surface (furnace wall, water pipe wall) 23 of the furnace 22 of the boiler 6 . As for the fuel nozzle 21, the fuel pipe 8 is connected to the upstream end. The fuel nozzle 21 is formed in the hollow cylindrical shape, and the flow path 24 through which solid fuel (pulverized biomass fuel and coal fuel) and carrier gas flow is formed in the inside of the fuel nozzle 21. As shown in FIG.

On the outer periphery of the fuel nozzle 21 , a gas nozzle for internal combustion (gas nozzle for secondary combustion) 26 which jets combustion air to the furnace 22 is provided. Moreover, on the outer peripheral side of the gas nozzle 26 for inner side combustion, the gas nozzle for outer side combustion (gas nozzle for tertiary combustion) 27 is provided. Each of the combustion gas nozzles 26 and 27 blows the air from the window box (wind box) 28 toward the inside of the furnace 22 . In the first embodiment, at the downstream end of the gas nozzle 26 for internal combustion, a guide vane 26a inclined outward in the radial direction with respect to the center of the fuel nozzle 21 (the diameter increases as it goes downstream) is formed. has been Moreover, the throat part 27a along the axial direction and the enlarged part 27b parallel to the guide vane 26a are formed in the downstream of the gas nozzle 27 for outer side combustion. Accordingly, the combustion air blown out from the respective combustion gas nozzles 26 and 27 is blown out so as to be diffused from the center of the axial direction.

In addition, the flame retainer 31 is supported by the opening at the downstream end of the fuel nozzle 21 . In Fig. 2, the flame retainer 31 is provided with an inner peripheral side projection 31a. The inner peripheral side projection 31a is formed to protrude toward the center side of the fuel nozzle 21, and the inner peripheral side projection 31a is periodically arranged at intervals along the circumferential direction.

In the central portion of the flow passage section of the fuel nozzle 21, a cylindrical or rod-shaped central shaft member is provided so as to penetrate the collision plate 32a supported by the collision plate flange 21a of the fuel nozzle 21, whereby As the fuel concentrator 34 , the upstream first swirler 41 and the downstream second swirler 42 are supported.

In the example shown in FIG.2, FIG.3, the oil starting burner (oil gun) 32 is penetratingly and arrange|positioned. The oil-started burner 32 is supported in a state penetrating through the collision plate 32a supported by the collision plate flange 21a of the fuel nozzle 21 .

A protective cylinder 32b for protecting the oil starting burner 32 is attached to the outer periphery of the oil starting burner 32 . A fuel concentrator 34 is supported on the outer periphery of the protective cylinder 32b. In the fuel concentrator 34 , an inner cylinder 35 disposed on the outer circumferential side of the protective cylinder 32b and an outer cylinder 36 disposed on the outer circumferential side of the inner cylinder 35 are disposed. The outer cylinder 36 is supported by the collision plate 32a via a support body (not shown). Therefore, the inner cylinder 35 is slidably supported in the axial direction with respect to the protective cylinder 32b and the outer cylinder 36 of the oil-started burner 32 . In addition, the outer cylinder 36 is not limited to the structure supported by the collision plate, A change, such as setting it as the structure fixed to the oil starting burner 32 at a position outside the movable range of the inner cylinder 35, is also possible.

In FIG. 2 , a positioning rod 37 as an example of a positioning member is supported by the inner cylinder 35 . The positioning rod 37 is formed in a rod shape, and extends toward the upstream side in the fluid flow direction in parallel with the oil starting burner 32 . The upstream part of the positioning rod 37 penetrates the collision plate 32a and extends to the outside of the flow path 24 .

In addition, the positioning rod 37 may be installed so that it may be built in the central shaft member of a cylindrical or rod shape, whereby abrasion damage due to collision of fuel particles can be avoided.

In FIG. 2 , the fuel concentrator 34 has an upstream first swirler 41 and a downstream second swirler 42 . In Figs. 2 and 3 , each of the turning machines 41 and 42 has a plurality of blades 41a and 42a that incline the oil-driven burner 32 with respect to the axis. In the first embodiment, in the downstream second revolving machine 42 , the blade 42a is fixedly supported on the outer peripheral surface of the outer cylinder 36 .

In FIG. 3 , in the first swing machine 41 on the upstream side, the blade 41a is supported by the rotation shaft 43 . The rotating shaft 43 is rotatably supported on the outer surface of the inner cylinder 35 . The rotating shaft 43 penetrates the shaft passage part 36a formed in the outer cylinder 36 and extending in the gas flow direction. A cam portion 44 protruding outward in the radial direction is supported by the rotating shaft 43 . A pin 44a extending parallel to the rotation shaft 43 is supported by the cam portion 44 (see Fig. 3A). The pin 44a penetrates the guide groove 36b (refer FIG.3(B), FIG.3(C)). The guide groove 36b is formed in the outer cylinder 36, and is formed in the elongate hole shape which can guide the pin 44a.

Accordingly, in the fuel concentrator 34 of the first embodiment, when the positioning rod 37 is inserted or drawn out in the axial direction, the inner cylinder 35 moves in the axial direction. Thereby, the pin 44a contacts the guide groove 36b, the cam part 44 rotates, and the rotating shaft 43 rotates. Accordingly, the blade 41a moves between the low-angle position shown in FIG. 3C and the high-angle position shown in FIG. 3B .

Moreover, in Example 1, the turning angle of the blade 42a of the 2nd turning machine 42 is set to the reverse direction and the same angle with respect to the turning angle of the blade 41a in a low-angle position.

In the solid fuel burner 7 of Example 1 provided with the said structure, when the fuel used is a biomass fuel, the positioning rod 37 is press-fitted. Accordingly, the inner cylinder 35 moves to the downstream side in the flow direction of the fluid. Accordingly, each of the turning machines 41 and 42 moves to the downstream side in the axial direction (the side approaching the furnace 22 ).

In addition, at this time, the blade 41a of the first swinging machine 41 on the upstream side moves to the high-angle position. Therefore, the turning angle of the blade (vane) 41a of the 1st turning machine 41 becomes large.

Here, biomass fuel has lower ignitability than coal, and intends to increase ignitability by concentrating fuel particles. Accordingly, in the first embodiment, the turning angle of the blade 41a is increased to increase the turning angle of the mixed fluid. Therefore, even if it uses a biomass fuel, the ignition property of a fuel can be improved.

Further, in the first embodiment, the fuel concentrator 34 is moved to the downstream side, so that the fuel that has once moved to the outer circumferential side is reflected from the inner surface of the fuel nozzle 21 and moves to the inner circumferential side, before moving to the inner circumferential side, an opening (the flame retainer 31) ) is easy to reach. Therefore, compared with the case where the fuel concentrator 34 is located on the upstream side, the ignitability and the enrichment effect of a fuel are improved.

In biomass fuel, compared with coal fuel, since an average particle diameter is large and ignitability is inferior, compared with the case where the radiant heat which a burner receives from the said flame is coal combustion, it is small compared with it.

Therefore, compared with the time of coal combustion, since the risk with respect to the burnout of the fuel concentrator 34 is low, even if the fuel concentrator 34 moves downstream, the risk of burnout is suppressed.

Moreover, since biomass fuel has a lower risk of wear than coal, even if it enlarges the turning angle of the blade 41a, the adverse effect on life is small.

In addition, biomass fuel is an oxygen-containing fuel, and after ignition, there is little amount of additional oxygen required. Therefore, the amount of air blown out from the secondary air nozzle (inside combustion gas nozzle 26) on the outer periphery is reduced compared with coal, and the amount of primary air that contributes to ignition by that much is set. Here, in the first embodiment, a guide vane 26a is provided at the downstream end so that the air jet from the secondary air nozzle (the gas nozzle 26 for internal combustion) is formed with a circulating flow having a large enlargement. However, when the amount of secondary air is reduced and the amount of primary air is set to be large, the expansion of the jet ejected from the solid fuel burner 7 becomes relatively small.

On the other hand, in Example 1, when using biomass fuel, it is set to (turning angle of the 1st turning machine 41)>(turning angle of the 2nd turning machine 42). Therefore, the swirl strongly imparted by the blade 41a on the upstream side is reduced on the downstream side, and it is blown out in a state where the swing remains. Therefore, the jet ejected from the solid fuel burner 7 is in a state with a spreading effect by turning. Accordingly, insufficient expansion of classification is also prevented.

In addition, in the solid fuel burner 7 of Example 1, when coal (pulverized coal) fuel is used, the positioning rod 37 is withdrawn in an axial direction. Accordingly, each of the turning machines 41 and 42 moves integrally to the upstream side in the axial direction (the direction away from the furnace 22 ). Therefore, the blade 41a of the first swing machine 41 moves to the low-angle position, and the swing angle becomes small.

Therefore, the wear of the blade 41a by coal fuel is suppressed compared with the case where a turning angle is large. Moreover, in coal fuel, since ignition property is higher than biomass fuel, even if the fuel concentrator 34 is an upstream side or turning is weak, ignition property is sufficiently securable. On the other hand, since the burnout risk is high in coal fuel, the burnout risk, especially the burnout risk of the 2nd swirler provided on the downstream furnace opening side, can be reduced by the fuel concentrator 34 being located upstream.

In addition, in Example 1, in the case of coal fuel, it is (turning angle of the 1st turning machine 41)=(turning angle of the 2nd turning machine 42). In the case of coal fuel, when a swirling component remains in a fraction, a fraction spreads and becomes too wide, and there exists a possibility that a circulating flow may not be formed. If the circulating flow is not formed, there is a problem in that the NOx reduction effect is reduced. On the other hand, in Example 1, in the coal fuel, the turning provided by the 1st turning machine 41 of an upstream is offset by the 2nd turning machine 42 of a downstream. Therefore, in Example 1, excessive expansion of the fractionation in the case of coal fuel can be suppressed, and the NOx reduction effect can be maintained.

It is explanatory drawing of the analysis result of the position and opening diameter of a downstream blade with respect to a coal fuel and a biomass fuel.

4 shows that the distance from the open end of the fuel nozzle 21 to the installation reference position of the downstream blade 42a is L with respect to coal and biomass, and the opening diameter of the fuel nozzle 21 is D. A furnace based on numerical analysis (CFD: Computational Fluid Dynamics) for a total of 9 L/Ds of the maximum, medium, and minimum 3, and the blade angle θ for each of the maximum, medium, and minimum 3 types. The effect of reducing NOx at the exit and UBC (unburned carbon in ash: Unburned Carbon) are obtained, and this is evaluated relative to “performance” and scored, and each risk of backfire, abrasion, and deposition is also scored, The most preferable combination of L/D and θ is obtained.

Coal has little effect of θ on performance when L/D is minimum and medium (sensitivity is small), but when L/D is maximum, the effect of θ is large, and when the angle is maximum, sufficient performance is obtained. However, as the angle decreases, the performance decreases. Therefore, it is preferable to set L/D to the middle and θ to the minimum in the case where each risk of backfire, wear, and deposition is the smallest.

On the other hand, biomass is preferably a combination of minimizing L/D and maximizing θ in order to make the performance in which the influence of θ appears larger (sensitivity is large) compared to coal at any L/D. And since each risk is suppressed small compared with coal also in the said combination, it is preferable to set in this combination.

In this way, according to the type of fuel, the preferable combination of L/D and θ, which is comprehensively evaluated in terms of performance and risk, differs, but according to the present invention, both can be set under appropriate conditions.

Therefore, in the solid fuel burner 7 of Example 1, while being able to switch between a biomass fuel and a coal fuel by operating the positioning rod 37, and being able to use it, at the time of use, the risk to abrasion and ignitability. , it is possible to suppress an increase in the risk of burnout.

In particular, in Example 1, both the adjustment of the turning angle and the adjustment of the position in the axial direction are possible by operation of the positioning rod 37. As shown in FIG. Therefore, compared with the case where the member which performs the position adjustment of a turning angle and an axial direction is respectively provided, while operation is easy, the number of parts is also reduced, and cost is also reduced.

In addition, it is preferable to provide a protective cover on the positioning rod 37 for abrasion countermeasures.

5 is an explanatory diagram of another embodiment 1 of the present invention.

In FIG. 5, while changing the position of the cam part 44' and the guide groove 36b' to the position shifted by 90 degrees, the outer cylinder 36 is rotatable in the circumferential direction with respect to the oil start burner 32. It is also possible to set it as the structure in which angle adjustment of the blade 41a is possible by doing this.

Fig. 6 is an explanatory view of another embodiment 2 of the present invention, Fig. 6 (A) is a schematic view, and Fig. 6 (B) is a partial detailed view.

In FIG. 6 , a gas supply pipe 101 is disposed between the outer periphery of the oil starting burner 32 and the inner cylinder 35 . The gas supply pipe 101 is supported in a state penetrating through the collision plate 32a. In the gas supply pipe 101, an oil starting burner 32 penetrates the inside, and the inner cylinder 35 is supported on the outer surface so as to be movable along the gas flow direction.

The gas supply pipe 101 is hollow inside, and is comprised so that the gas for cleaning can pass. In the gas supply pipe 101, corresponding to the range in which the inner cylinder 35 is movable, the gas outlet 102 is formed in multiple numbers on the outer surface.

The gas source 103 which supplies the gas for cleaning to the gas supply pipe 101 is arrange|positioned outside the collision plate 32a. As the cleaning gas, preferably the influence on the combustion of the solid fuel burner (7) for selecting a small gas species, and can be used for air or nitrogen (N ₂₎ gas or the like. In addition, it is preferable to set it as the flow volume with few influences with respect to combustion of the solid fuel burner 7, and, as for the flow volume of the gas for cleaning, according to the specification of the solid fuel burner 7, it can select suitably. Therefore, as the gas source 103, conventionally well-known arbitrary structures, such as a fan for ventilation, a compressor, a gas cylinder, and a valve, are employable.

It is explanatory drawing of the gas guide member in the form shown in FIG.

In FIG. 6 , the gas guide member 104 is supported on the upstream side of the inner cylinder 35 with respect to the gas flow direction. The gas guide member 104 is formed in the shape of a cone whose outer diameter becomes large as it goes downstream in the gas flow direction. In FIG. 7, in this form, let the outer diameter of the gas supply pipe 101 be D1, let the inner diameter of the upstream end of the gas guide member 104 be D2, and let the outer diameter of the downstream end of the gas guide member 104 be D3. And, when the outer diameter of the block (= outer cylinder 36) of the blade 41a is D4, it is configured so that the relationship of the following formula (1) is established.

D3>D4>D2>D1… Formula (1)

In addition, if D3 is too large, since the amount of fine particles, such as pulverized coal, colliding with the gas guide member 104 increases, it is preferable to make D3 into a value as close as possible to D4.

Accordingly, the gas ejected from the jet port 102 is guided from the inner surface of the gas guide member 104, and includes the base portion 106 of the rotation shaft 43, that is, the boundary between the rotation shaft 43 and the blade 41a. It is sprayed in the range 106 to Moreover, in this form, gas is also injected into the part 107 of the upstream end of the inner cylinder 35, the upstream end of the outer cylinder 36, and the part 108 of the corner of the inner cylinder 35. As shown in FIG.

In addition, on the outer surface of the gas guide member 104, pulverized coal or the like fed from upstream is guided outward in the radial direction.

The injection apparatuses 101-104 of this form are comprised by each member which attached|subjected each said code|symbol 101-104.

(Operation of other form 2)

In the form shown in FIG. 6, FIG. 7, by the injection devices 101-104, the base part 106 of the blade 41a whose turning angle is adjustable, and the upstream of the inner cylinder 35 movable in the gas flow direction. The gas is injected into the upstream end portion 108 of the outer cylinder 36 which is a boundary portion between the end portion 107 and the inner cylinder 35 .

In the configuration in which gas is not injected into the root portion 106 , fine particles such as pulverized coal may be deposited over time depending on the specifications of the solid fuel burner 7 . If the fine particles are deposited or adhered, since the fine particles are clogged at the base portion of the blade 41a, there is a fear that the turning angle of the blade 41a cannot be adjusted. In addition, if the particles are clogged in the respective portions 107 and 108, there is a possibility that the inner cylinder 35 cannot be moved in the gas flow direction.

On the other hand, in this form, gas is injected to each part 106-108 by the injection apparatus 101-104, and accumulation of microparticles|fine-particles is suppressed. Therefore, it becomes possible to perform the adjustment of the turning angle of the blade 41a and adjustment of the position of the gas flow direction stably over a long period of time.

In addition, in this form, the gas guide member 104 and the inner cylinder 35 are comprised so that movement is possible, and even if the inner cylinder 35 moves, the positional relationship with the gas guide member 104 does not change. Accordingly, it is possible to stably inject the gas to each of the parts 106 to 108 .

In addition, in this form, the jet port 102 is formed corresponding to the movement range of the inner cylinder 35. As shown in FIG. Therefore, even when the inner cylinder 35 moves, the gas can be stably fed to the inner surface side of the gas guide member 104 .

Moreover, in this form, with the simple structure of the gas guide member 104, gas can be injected, and accumulation of microparticles|fine-particles can be suppressed.

(Other changes)

As mentioned above, although the Example of this invention was described in detail, this invention is not limited to the said Example, It is possible to make various changes within the summary of this invention described in the claims.

For example, although the configuration in which only the upstream blade 41a is capable of adjusting the turning angle has been exemplified, it is also possible to make the turning angle of the downstream blade 42a adjustable.

Moreover, although the structure of the gas nozzle 26 and 27 for two stages|stages which has the gas nozzle 26 for secondary combustion and the gas nozzle 27 for tertiary combustion was illustrated, it is not limited to this, Combustion gas It is also possible to make a nozzle into one stage or three stages or more.

In addition, although the structure which performs the adjustment of the turning angle and the adjustment of the position in an axial direction with the one position adjustment rod 37 was illustrated, it is not limited to this. It is also possible to provide the member for adjustment of a turning angle and the member for position adjustment of an axial direction, respectively. For example, the rotation shaft of the blade (the pivot point for adjusting the turning angle) is provided on the inner cylinder of a double cylinder that can slide with each other, and the cam movable mechanism as shown in Fig. 5 is provided on the outer cylinder, the inner cylinder and the outer cylinder It is possible to adjust the deflection angle of the slewing blade by shifting the relative positional relationship of In addition, if the inner cylinder and the outer cylinder are integrally slid in the nozzle axial direction, position adjustment in the axial direction is also possible. Moreover, the relative rotation of an inner cylinder and an outer cylinder, and the movement to a nozzle axial direction are operable by providing a rod, respectively, for example. In addition, when adjustment of the turning angle is not necessary depending on the type of fuel used, design, specifications, etc., the fuel concentrator 34 may be configured to have only a function of moving in the nozzle axial direction. When movement is not required, it is also possible to set it as the structure which can only adjust a turning angle.

Moreover, as the fuel concentrator 34, although the structure which has the 1st turning machine 41 and the 2nd turning machine 42 is preferable, it is also possible to set it as the structure of only the 1st turning machine 41, and three or more turns is possible. It is also possible to set it as the structure provided with a group.

In the form shown in FIG.6, FIG.7, the structure of the injection apparatuses 101-104 is not limited to the structure illustrated, It can change arbitrarily. For example, the shape of the gas guide member is not limited to a conical shape, and can be any shape, such as a parabolic (parabolic) shape or a polygonal pyramid shape. In addition, although the structure of the cylindrical tube shape along the oil starting burner 32 was illustrated for the gas supply pipe|tube 101, it is not limited to this. For example, it is also possible to extend a pipe from the internal combustion gas nozzle 26 to cross the flow path 24 to supply air. In particular, in the configuration in which the oil starting burner 32 is not provided and the first swirling machine 41 and the second swirling machine 42 are connected by a spindle-shaped member extending in the gas flow direction, the gas for internal combustion A configuration that extends the tubing from the nozzle 26 is particularly suitable. In addition, the injection devices 101-104 can also be provided in both of the 1st swirling machine 41 of an upstream and the 2nd swirling machine 42 of a downstream, and the 1st swirling machine 41 of an upstream ), it is also possible to do it only on the side.

7: Solid fuel burner
21: fuel nozzle
22: brazier
26, 27: gas nozzle for combustion
34: fuel concentrator
41a: upstream blade
41a, 41b: blade
43: shaft
101 to 104: injection device
102: vent
104: gas guide member

Claims (7)

A fuel nozzle through which a mixed fluid of the solid fuel and its carrier gas flows and is opened toward the furnace;
a combustion gas nozzle disposed on the outer periphery of the fuel nozzle to eject combustion gas;
A fuel concentrator provided on the central side of the fuel nozzle to apply a velocity component in a direction away from the center of the fuel nozzle to the mixed fluid.
A solid fuel burner having a
The fuel concentrator has a plurality of blades for imparting rotation to the mixed fluid, and a rotation angle of the blades with respect to the burner axial direction is adjustable. The turning direction of each of the plurality of blade structures is in the reverse direction while installing at two places spaced apart from the burner axial direction, and the turning direction of the blade at least upstream with respect to the flow direction of the mixed fluid. A solid fuel burner characterized in that the angle is adjustable. The solid fuel burner according to claim 1, wherein the fuel concentrator is configured to be movable along the burner axial direction. A fuel nozzle through which a mixed fluid of the solid fuel and its carrier gas flows and is opened toward the furnace;
a combustion gas nozzle disposed on the outer periphery of the fuel nozzle to eject combustion gas;
A fuel concentrator provided on the central side of the fuel nozzle to apply a velocity component in a direction away from the center of the fuel nozzle to the mixed fluid.
A solid fuel burner having a
The fuel concentrator has a plurality of blades for imparting rotation to the mixed fluid, and is installed in two places spaced apart from the burner axial direction, and the rotation direction of each of the plurality of blade structures is in the reverse direction,
The fuel concentrator is a solid fuel burner, characterized in that it is configured to be movable along the burner axial direction. The solid fuel burner according to claim 4, wherein the fuel concentrator is configured such that a turning angle of at least an upstream blade with respect to the burner axial direction with respect to the flow direction of the mixed fluid is adjustable. According to any one of claims 1 to 5, wherein the shaft for supporting the blade;
A spraying device that sprays cleaning gas toward the boundary between the blade and the shaft.
A solid fuel burner comprising a. The injection device according to claim 6, further comprising: a jet port for discharging gas in a radial direction from the shaft portion; and a gas guide member for guiding the gas from the jet port to a boundary portion between the blade and the shaft section.
A solid fuel burner comprising a.

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