JPH0792214B2 - Fuel burning burner - Google Patents

Description

Description: TECHNICAL FIELD The present invention relates to a fuel combustion burner, and relates to a fuel such as a flame-retardant solid fuel, a liquid fuel, a slurry-like fuel, and particularly a slurry-like fuel such as a coal-water slurry. The present invention relates to a fuel combustion burner that is effective for high-efficiency and low-NOx generation combustion.

[Conventional technology]

One of the problems in using coal is that it is not easy to handle solids. Therefore, various fluid fuel technologies for coal have been developed. Among them, coal-water slurry (hereinafter referred to as a mixture of atomized coal and water)
CWM) is attracting worldwide attention due to its excellent economic efficiency.

CWM has low manufacturing and transportation costs and has great advantages in terms of handling, but since it contains a large amount of water in the fuel, it may have lower combustion efficiency than conventional pulverized coal. CWM is made into fine particles and sprayed into the combustion furnace. A two-fluid atomizer that causes a high-speed atomizing medium to collide with the atomizing medium is generally used for atomizing a relatively viscous fluid such as CWM. In the two-fluid atomizer, the higher the flow velocity of the atomizing medium is, the higher the atomization performance is, and the velocity of the CWM airflow ejected from the atomizer is about 5 times that in the case of pulverized coal by air transportation. In addition, sprayed CWM
Requires a water vaporization zone prior to its ignition. As a result of the high ejection speed and the time required for water evaporation, CW
It is known that the ignition position of M easily lifts from the burner surface to the wake side, and the flame temperature is as low as 100 ℃ ~ 200 ℃. Such retreat of the ignition position adversely affects combustion efficiency, flame stability, and nitrogen oxide (NOx) suppression.

CWM combustion requires NOx suppression, as with other fuels, and at least NOx emission suppression, which is at least as good as pulverized coal combustion, is required. Generally, NOx generated during combustion of various fuels including CWM is composed of heat-generated NOx generated by oxidation of nitrogen (N ₂ ) in combustion air under high temperature and nitrogen content (N) contained in fuel. It is roughly classified into fuel-derived NOx generated by oxidation during combustion.

Of these two types of NOx, the amount of heat-generated NOx generated strongly depends on the temperature of the combustion flame. When the flame temperature is low like CWM, the reaction between N ₂ and O ₂ is suppressed, and the amount generated is relatively small. On the other hand, the fuel-derived NOx does not change much with the flame temperature, but rather depends on the N content in the fuel. Coal, which is a combustible component of CWM, contains 0.5 to 2.5% by weight of N, depending on the type of coal. This value is extremely high compared to 0% by weight of LNG and 0.1% by weight of C heavy oil. Therefore, the amount of NOx generated from fuel is large and accounts for most of the total amount of NOx generated. In combustion of pulverized coal, the NO
It is known that it is indispensable to stably form the reduction region inside the flame in order to reduce x.

Under a combustion condition of low air (low air ratio combustion condition), coal releases a reducing gas such as H ₂ and CO to form a reduction region. Under such a reduction region, N content in coal is NH ₃ , H
Released as a compound such as CN. These nitrogen compounds are immediately oxidized to NOx in the presence of a high concentration of O _2, but have a function of reducing NOx to N ₂ when the O ₂ concentration is low. Therefore, by separating the combustion air into the low NOx burner of pulverized coal and gradually mixing this,
Some are configured to stably form a reduction region and a low O ₂ concentration region (denitration region).

[Problems to be solved by the invention]

On the other hand, in CWM, the time required for ignition is long by the evaporation time of water, and since it is ejected at high speed when atomized, the flame is easily separated from the burner surface. That is, since combustion proceeds in the downstream region where CWM and air are rapidly mixed, it is not easy to form a reduction region such as pulverized coal combustion, and it becomes difficult to suppress NOx emissions. In addition, the low ignitability is of course the direct cause of the decrease in the combustion rate, and further, when the flame is separated from the burner, it becomes an unstable combustion state that easily causes a misfire, which causes a problem in the reliability of the combustion device. .

In this way, in CWM combustion, the retreat of the ignition position adversely affects the combustion characteristics, improving the ignitability of the CWM, and drawing the ignition position as close to the burner as possible is the key point of the CWM burner development. As a method of drawing the ignition position, a method of introducing combustion air as a swirling flow is known. For example, there is a burner in which the position of the tertiary air nozzle is separated from the fuel nozzle and the tertiary air is injected as a strong swirl flow, such as the pulverized coal burner disclosed in Japanese Patent Laid-Open No. 59-208305. When fuel is ejected at a flow velocity of air such as pulverized coal, it is effective to inject the combustion air as a strong swirl flow. However, when fuel is ejected from the fuel nozzle at a high speed that is 3 to 5 times faster than the combustion air velocity like CWM, the optimum swirl strength range is extremely high when flame holding is performed only by the swirl force of air. It is very narrow, which makes it difficult to operate the burner. Further, in the two-fluid atomizer, if the flow velocity of the spray medium is reduced and the CWM ejection speed is reduced, atomization of CWM is hindered, and good combustion flame of CWM cannot be obtained. That is, when the spray fine diameter of CWM becomes large,
Since the heat transfer characteristics of the particles deteriorate, the ignitability decreases.

The object of the present invention is to solve the above-mentioned problems of the prior art,
An object of the present invention is to provide a fuel combustion burner which has good ignition and flame holding properties and at the same time can suppress generation of nitrogen oxides and unburned components.

[Means for solving problems]

The above-mentioned object is that the flame stabilizer is formed in a truncated cone shape, and the central axis of the truncated cone substantially corresponds to the axis of the fuel supply nozzle, and the fuel injection hole in the fuel supply nozzle is formed on the small diameter side of the truncated cone flame stabilizer. Is formed and a plurality of gaps through which air can flow are formed on the vertical side of the truncated cone, and the primary air jetted from these gaps extends along the inner wall surface of the flame stabilizer. This is achieved by allowing it to squirt.

[Action]

On the small diameter side of the cone-shaped flame stabilizer, the tip of the fuel supply nozzle,
That is, the atomizer is located. Therefore, the atomizer is located away from the fuel combustion flow area in the furnace or the like, and the evaporation deceleration time of water from the fuel can be secured. In addition, the air ejected from the gap formed on the vertical surface of the flame stabilizer flows along the inner wall surface of the flame stabilizer, does not directly hit the fuel jet from the atomizer, and has a negative pressure on the central axis of the burner. Such a gas region is formed. A circulating flow is generated in this gas region by the hot gas in the furnace.

Example of Invention

 Embodiments of the present invention will be described below with reference to the drawings.

FIG. 1 is a side sectional view showing an embodiment of a fuel combustion burner according to the present invention, FIG. 2 is a view taken along line AA of FIG. 1, and FIG.
It is a BB sectional view of the figure.

In FIG. 1, a main burner gun 1 for supplying a main fuel such as CWM is arranged at the center of the burner, and an atomizer 2 having a fuel ejection hole is provided at the tip of the CWM burner gun 1. A seal pipe 3 is concentrically arranged around the main burner gun 1 with a predetermined gap from the outer peripheral surface of the main burner gun 1, and an impeller (flame stabilizer) 4 is connected to one end of the seal pipe 3. It is set up. The flame stabilizer 4 is formed in a truncated cone shape, and its central axis corresponds to the axial center of the burner. Further, the atomizer 2 is located on the smaller diameter side of the cone-shaped flame stabilizer 4, and a radial seal ring 5 is fixed to the tip of the atomizer 2, and the peripheral edge of the tip of the seal ring 5 is the flame stabilizer. It is arranged at a predetermined interval from the inner wall surface of No. 4.

The flame stabilizer 4 is formed in a truncated cone shape, and a disk-shaped flame stabilizer ring 6 is installed at the tip (larger diameter side) thereof in a direction orthogonal to the axial direction of the burner. A cylindrical primary sleeve 7 is arranged outside the seal pipe 1 and the flame stabilizer 4, and a primary sleeve damper 10 for adjusting the flow rate of the primary air 9 from the wind box 8 is arranged on the primary sleeve 7. is set up. A cone ring 11 having a divergence angle substantially the same as the divergence angle of the cone-shaped flame stabilizer 4 is connected to the tip end of the primary sleeve 7 on the fuel injection side. A tertiary register 12 is arranged on the outer periphery of the primary sleeve 7 on the fuel injection direction side, a throat 13 is installed inside the furnace with respect to the tertiary register 12, and a caster 14 is installed from the throat 13 inside the furnace. . The casters 14 have substantially the same spread angle as the cone-shaped flame stabilizer 4. Inside the casters 14, furnace wall tubes 15 are embedded in parallel.

The flame stabilizer 4 is composed of a large number of flame stabilizer blades 4a having a truncated cone shape as shown in FIGS. Each flame stabilizer blade 4a is formed in a fan shape, and the side surface side of each blade forms the same curved inclined surface, and between the inclined surfaces of the flame stabilizer blades 4a adjacent to each other, As shown in detail in the drawing, they are arranged with a predetermined gap, and the primary air 9 flows through this gap. At this time, the primary air 9 is in the same direction as the swirling direction of the air in the tertiary register 12.

Next, the operation of the fuel combustion burner configured as described above will be described.

The main fuel 16 such as CWM passes through the inside of the main burner gun 1 and is ejected into the furnace through ejection holes formed in the atomizer 2. Since the atomizer 2 is located at the center (on the small diameter side) of the truncated cone-shaped flame stabilizer 4, and the throat 13 is located near the front end portion of the expanded truncated cone-shaped flame stabilizer 4, the atomizer 2 The fuel injected from is injected to a position away from the ejection hole without colliding with the inner wall surface of the flame stabilizer 4. At this time,
The seal air 17 passes through an annular gap formed between the main burner gun 1 and the seal pipe 3, and the seal gas is radially ejected from the gap between the seal pipe 3 and the seal ring 5 along the inner surface of the flame stabilizer 4. It Further, the primary air 9 whose flow rate is adjusted by the primary sleeve damper 10 from the wind box 8 is
It is radially ejected into the furnace through the space formed between the next sleeve 7 and the seal pipe 3 and from the gap formed between each flame stabilizer blade 4a forming the flame stabilizer 4. At the same time, the tertiary air 18 introduced through the tertiary register 9 is ejected from the gap between the cone ring 11 and the throat 13.

The fuel injected from the atomizer 2 can ensure the ignition retention time to the furnace 19 (inside the furnace) without colliding with the inner wall surface of the flame stabilizer 4. Especially when water needs to be evaporated before ignition as in CWM and high-speed injection is performed by a spray medium such as steam, the basin where the fuel is ignited is far from the ejection hole, so the fuel is decelerated and A basin is created for the evaporation of water, and the mixing and ignitability with the air from the throat 13 is greatly improved. Next, in the flame stabilizer 4, the primary air 9
Swirl while flowing along the inner wall surface of the flame stabilizer 4, and this air flow becomes a large swirl flow corresponding to the shape of the inner wall surface of the flame stabilizer 4, and the jet of fuel from the atomizer 2 and the atomizer 2
Does not hit directly. Therefore, a large negative pressure zone is formed at the center of the fuel jet flow, and the synergistic effect of the swirling flow swirling along the inner wall surface of the flame stabilizer 4 and the swirling flow of the tertiary air 18 from the throat 13 is produced. A fuel circulation area is efficiently formed, and the high temperature gas 20 in the furnace is pulled back to the tip end side of the atomizer 2 along the central axis of the burner. As a result, the fuel injected from the atomizer 2 is efficiently mixed with the high temperature gas in the furnace, and the moisture in the fuel is evaporated and the fuel is ignited. At this time, at the same time, a reducing gas for reducing NOx in the gas is easily generated, and the NOx can be reduced. Further, when this circulating flow is generated, the combustion ash in the furnace and the fine slurry in which the evaporation of water immediately after spraying is not completed adheres to the inner wall surface of the flame stabilizer 4, but along the inner wall surface of the flame stabilizer 4. Adhesion of combustion ash and fine slurry in the furnace is prevented by the sealing effect of the swirling air flow.

Further, the seal air 17 passes between the main burner gun 1 and the seal pipe 3, and a radial seal ring 5 is provided at the tip of the atomizer 2, so that the seal air 17 is radially emitted between the flame stabilizer 4 and the seal ring 5. Since it flows out along the inner wall surface of the flame stabilizer 4, adhesion of fine slurry or the like at the tip of the atomizer 2 is prevented. The seal air 17 has an effect of preventing adhesion of fine slurry and the like and an effect of preventing burnout of the metal portion of the burner due to flame radiation heat in the furnace.

Next, the flame holding ring 6 is provided in a direction orthogonal to the central axis of the burner and is connected to the primary sleeve 7, and a space portion having a triangular cross section is provided between the flame holding ring 6 and the primary sleeve 7. The air from the wind box 8 is not supplied to this space. Therefore, the primary air 17 that is ejected from the gap between the flame stabilizer blades 4a and swirls along the inner wall surface of the flame stabilizer 4;
A small vortex-like stagnant portion is formed in the space by the fine particles that are circulated along with the high-temperature combustion exhaust gas that is pulled back to the burner side by the circulating flow of the gas in the furnace, and the flame is held in this portion. As a result, the flame holding property is further improved by the flame holding mechanism and the fuel ignition improving mechanism described above, and a stable flame is formed. Further, since the fuel from the atomizer 2 immediately reaches the high temperature atmosphere immediately after spraying, the NOx reducing gas is actively generated in the flame holding section, and the NOx can be reduced.

Further, the cone ring 11 provided at the tip of the primary sleeve 7 has a function of radially ejecting the tertiary air 18 supplied through the tertiary register 12 along the throat 13 and the casters 14. The portion of the flame holding ring 6 is prevented from immediately mixing with the fuel from the atomizer 2. Then, the tertiary air 18 discharged from the throat 13 is mixed with the fuel on the downstream side of the fuel injection direction. Therefore, by adjusting the air distribution of each of the primary air 9 and the tertiary air 18, NO
It is possible to achieve complete combustion of the fuel after the low NOx reaction without inhibiting the reduction of NOx by the reducing gas.

Since the ignition and flame holding properties are improved as described above, the combustion efficiency can be improved and the unburned content in ash can be reduced, and at the same time NOx
Can be significantly reduced.

When burning oil or other fuel with good ignitability, move the main burner gun 1, atomizer 2, seal pipe 3, flame stabilizer 4 and flame holding ring 6 inside the furnace with respect to the burner center axis. As a result, the deceleration and the residence time of the fuel injected from the atomizer 2 can be adjusted to be small. In this case, since the flame can be moved and adjusted to the inside of the furnace so that the peak position of the flame temperature does not come closer to the flame stabilizer 4 side than necessary,
It is possible to suppress burnout and generation of heat (thermal) NOx due to abnormal temperature rise of the flame holding ring 6 and the throat 13.

In order to exert such an effect more reliably, the angle formed by the burner axis and the line connecting the large diameter side end of the flame stabilizer 4 and the ejection hole formed in the atomizer 2 is 90 ° or less, Desirably, the angle is 45 ° to 80 °.

FIG. 4 is a cross-sectional view showing another embodiment of the fuel combustion burner according to the present invention, FIG. 5 is a CC perspective view of FIG. 4, and FIG.
FIG. 7 is a sectional view of a main part showing the structure of the flame stabilizer in the burner shown in FIG. 7, and FIG. 7 is a sectional view of the main part showing another structure of the flame stabilizer in the burner shown in FIG.

In FIG. 4, an atomizer sleeve 42 is arranged around the main burner gun 41, and a flame stabilizer 43 having a frustoconical structure is installed at the tip of the atomizer sleeve 42. The flame stabilizer 43 is provided with a plurality of radiating rings 43a as shown in FIG. The radiating ring 43a is composed of a plurality of rings each having an inner diameter and an outer diameter different from each other, and a ring having a gradually increasing diameter is arranged from the tip portion of the atomizer 44 to the frustoconical tip portion (larger diameter side). The radiating ring 43a located on the smaller diameter side of the truncated cone-shaped flame stabilizer 43 is arranged so that the inner rim portion side of the outer radiating ring 43a is located with a predetermined annular gap on the outer peripheral edge side. In this way, a plurality of radiation rings 43a having a large diameter are sequentially arranged, and a plurality of annular gap portions having different diameters are formed.
An annular secondary sleeve caster 45 having a triangular cross-section having a side surface in a direction orthogonal to the wall surface of the flame stabilizer 43 is provided at the tip peripheral edge portion (large diameter side) of the flame stabilizer 43. An annular flame holding caster ring 46 having a wall surface in a direction orthogonal to the side surface of 45 is installed.

In FIG. 4, 47 is a primary air damper, 48 is a tertiary air register, 49 is a throat, 50 is a throat caster,
Reference numeral 51 is a water wall tube, 52 is a secondary sleeve, and the flame stabilizer 43 and flame caster ring 46 having a radial shape with the atomizer 44 as the apex.
Further, the throat caster 50 forms a triangular space portion having a burner axial cross-sectional shape.

Next, the operation of the fuel combustion burner configured as described above will be described.

The fuel injected from the main burner gun 41 is radially injected from the ejection holes formed in the atomizer 44. For this reason,
The jet 53 of fuel from the atomizer 44 has a spread and is decelerated before entering the furnace. Normally, with a two-fluid spray using steam or air, the initial velocity of 100 to 200 m / s or more is generated at the ejection hole, but due to this sufficient deceleration of fuel, the fuel is sufficiently mixed with combustion air and high temperature gas in the furnace, Stable combustion can be achieved. In this case, by increasing the angle (θ) formed by the burner axis and the surface connecting the ejection hole formed in the atomizer 44 and the inner wall surface of the flame stabilizer 43, the spread of the fuel jet 53 is also increased. The fuel does not adhere to the inner wall surface of the flame stabilizer 43 or the throat portion. If the spread angle (θ) is too small, the jet 53 of fuel collides with the inner wall surface of the flame stabilizer 43, and in fuels containing water such as CWM, coal particles before water evaporation / ignition and the water are flame stabilizers. It adheres and grows on the ring 43a. On the other hand, if the spread angle (θ) is too large, the distance between the atomizer 44 and the inside of the furnace cannot be sufficiently secured, so that the effect of decelerating the atomized fuel becomes weak. Therefore, it is important to set the deceleration distance of the fuel injected from the atomizer 44 as large as possible and to set the optimum spread angle (θ) so that the fuel jet does not contact the inner wall surface of the flame stabilizer 43. The total spread angle from one of the ejection holes formed on the atomizer 44 is about 20 °.
From this point, the spread angle (θ) is preferably about 30 ° or more in consideration of the margin. However, since the spread angle (θ) can be selected from the deceleration distance of the fuel due to the difference in the combustibility of the fuel, the maximum angle is preferably set to 80 °. That is, the spread angle (θ) is reduced in the case of fuel with poor ignitability, while the spread angle (θ) is reduced in the case of fuel with good ignitability.
Can be increased to set a shorter fuel deceleration distance. Thus, by selecting the optimum spread angle (θ), the effect of improving the ignitability can be obtained according to the degree of flame retardancy of the fuel.

Next, the primary air jetted from the gap between the flame stabilizer rings 43a is radially jetted at a spread angle close to the spread angle (θ) of the flame stabilizer 43. Therefore, as in the embodiment shown in FIG. 1, the vicinity of the tip of the atomizer 44 is in a negative pressure state with no air, and a high temperature gas 54 in the furnace is drawn in to form a circulating flow. Further, it is rapidly heated by the high temperature gas 54 and the ignitability is improved. Also, the primary air 9
Is a particle that does not sufficiently evaporate water in the spray flow such as CWM because it flows along the inner wall surface of the flame stabilizer 43 from each annular gap of the flame stabilizer ring 43a that constitutes the flame stabilizer 43. It is possible to prevent burnt ash and combustion ash from adhering to the inner wall surface of the flame stabilizer 43. Further, as in the burner shown in FIG. 1, a vortex is formed near the flame holding caster ring 46 as shown by the arrow in the figure, and at the same time, a high temperature stagnation zone that entrains a portion of the high temperature gas and atomized fuel in the circulating furnace. Is formed.

FIG. 5 shows the flow of the flame stabilizer ring 43a, the flame stabilizer caster ring 46, the primary air 9, and the tertiary air 18. Tertiary air
After being discharged from the throat 49 by the turning by the tertiary register 48, 18 diffuses in the furnace and forms a circulating flow of the furnace gas together with the primary air 9 from the flame stabilizer ring 43a. Further, since the flame holding caster rings 46 are radially installed, the tertiary air 18 is not mixed in the throat portion but mixed with the fuel on the downstream side of the furnace. The atomized fuel is first heated and ignited by the primary air 9 and the high temperature gas in the furnace under an air ratio condition insufficient for complete combustion to generate NOx and NOx reducing gas. Next, by mixing with the tertiary air 18, the NOx amount is reduced by the reducing gas and at the same time complete combustion is achieved. A high-temperature atmosphere is a necessary condition for generating such a reducing gas, but the flame stabilizer ring 43a, the secondary sleeve caster 45, and the flame stabilizer caster ring 46 viewed from the inside of the furnace have a shape that blocks the air flow path. As a result, the radiant heat in the furnace is absorbed and the effect of giving heat to the fuel spray flow is brought about. Therefore, the spray flow of the fuel exhibits a rapid temperature rise at the time of ignition, and low NO in this high temperature atmosphere.
x ・ Complete combustion is achieved. Also, the flame stabilizer rings 43a, 2
If the next sleeve caster 45 and flame holding caster ring 46 are made of a ceramic material, the durability of the burner can be improved due to its heat resistance.

6 and 7 are side sectional views showing another embodiment of the flame stabilizer according to the present invention.

In FIG. 6, the flame stabilizer 43 is configured with respect to an angle (θ) formed by the burner shaft center and a line connecting the ejection hole of the atomizer 44 and the tip portion (end portion on the large diameter side) of the flame stabilizer 43. The flame stabilizer ring 43a has a concave cross section. That is, the gap formed between each flame stabilizer ring 43a has a tapered shape at the tip of the gap (on the downstream side of the air flow). In this case, the primary air ejected from the gap between the flame stabilizer rings 43a efficiently ejects on the inner wall surface of the flame stabilizer 43 and has a large sealing effect on the flame stabilizer 43, so that particles in the fuel adhere It is effective in prevention.

In FIG. 7, with respect to the angle (θ) formed by the burner axis and the line connecting the ejection hole of the atomizer 44 and the tip of the flame stabilizer 43,
The cross section of the flame stabilizer ring 43a forming the flame stabilizer 43 is formed in a convex shape. In this case, with respect to the spread of the fuel spray flow at the time of diffusion, the distance to the inner wall surface of the flame stabilizer 43 becomes larger toward the downstream side of the fuel spray flow, so the flow due to the swirling of the fuel spray flow is large. Even if it becomes
There is no contact or interference with the inner surface of 43.

In the present invention, the member constituting the flame stabilizer is not limited to the ring as shown in FIGS. 5 to 7, but a plurality of slit-shaped grooves may be formed on a truncated cone-shaped radial plate material, or a large number of transparent members may be formed. A structure having holes may be used. When the flame stabilizer having such a structure is used, in addition to the effect of the structure of the flame stabilizer described above, the dimensional accuracy in manufacturing the flame stabilizer can be improved.

〔The invention's effect〕

As described above, according to the present invention, the ignition / flame holding properties of the fuel, especially the flame-retardant fuel such as CWM is improved, so that the unburned content is reduced and the combustion efficiency is improved. Further, since a high temperature atmosphere is achieved, the amount of NOx produced can be reduced at the same time.

[Brief description of drawings]

1 is a sectional view showing an embodiment of a fuel combustion burner according to the present invention, FIG. 2 is a view taken along the line AA of FIG. 1, FIG. 3 is a sectional view taken along the line BB of FIG. 2, and FIG. FIG. 5 is a cross-sectional view showing another embodiment of the fuel combustion burner according to the present invention, FIG. 5 is a CC perspective view of FIG. 4, and FIG. 6 is a main-part cross-sectional view showing another embodiment of the flame stabilizer in FIG. FIG. 7 is a sectional view of a main part showing still another embodiment of the flame stabilizer in FIG. 1,41 …… Main burner gun, 2,44 …… Atomizer, 3…
... Seal pipe, 4,43 ... Flame stabilizer, 5 ... Seal ring, 6 ... Flame ring, 7 ... Primary sleeve, 8 ... Wind box, 9 ... Primary air, 10, 47 ... … Primary air damper, 11…
… Flame holding ring, 12, 48 …… Tertiary register, 13, 49 …… Throat, 14, 50 …… Flame holding caster ring, 15, 51 …… Water wall pipe, 42 …… Atomizer sleeve, 45 …… 2 Next sleeve caster.

 ─────────────────────────────────────────────────── ─── Continuation of front page (72) Inventor Tadahisa Masai 6-9 Takaracho, Kure-shi, Hiroshima Babcock Hitachi Ltd. Kure Factory (72) Masakiyo Tanigawa 6-9 Takaracho, Kure-shi, Hiroshima Babcock Hitachi Kure Factory Co., Ltd. (72) Inventor Takashi Kawano 6-9 Takaracho, Kure City, Hiroshima Prefecture Babcock Hitachi Co., Ltd. Kure Factory (56) Reference JP 61-205711 (JP, A) JP 59-84008 (JP, A)

Claims (7)

[Claims] 1. A cylindrical air supply path provided in communication with a fuel combustion chamber, a fuel supply nozzle for injecting fuel toward the fuel combustion chamber, and a fuel injection side of the fuel supply nozzle. And a fuel combustion burner equipped with
The flame stabilizer is formed in a truncated cone shape, the central axis of the truncated cone substantially corresponds to the axis of the fuel supply nozzle, and the fuel injection hole in the fuel supply nozzle is formed on the small diameter side of the truncated cone flame stabilizer. A plurality of gaps through which air can flow are formed on the vertical surface side of the truncated cone and the primary air ejected from these gaps is ejected along the inner wall surface of the flame stabilizer. The fuel-burning burner is characterized in that 2. The flame stabilizer comprises a plurality of fan-shaped blades, and gaps through which air can flow are formed between the respective blades, and the primary air ejected from these gaps is the flame stabilizer. The fuel combustion burner according to claim (1), characterized in that the burner burns along the inner wall surface. 3. The flame stabilizer comprises a plurality of rings having different diameters, and gaps through which air can flow are formed between the respective rings, and the primary air ejected from these gaps is the flame stabilizer. The fuel combustion burner according to claim (1), characterized in that the fuel is burned along the inner wall surface of the. 4. A frustoconical ring is provided in an annular space formed by an inner peripheral edge of the flame stabilizer on the small diameter side and an outer peripheral surface of the tip of the fuel supply nozzle, and the small diameter side of the ring is formed by fuel. The fuel combustion according to claim (1), characterized in that it is fixed to the outer peripheral surface of the tip of the supply nozzle, and the large diameter side of the ring is separated from the inner wall surface of the flame stabilizer on the small diameter side. Burner. 5. The flow of air to the outside of the combustion chamber slightly on the vertical surface of the flame stabilizer or on the extended surface of the vertical surface close to the large diameter side end of the flame stabilizer. The fuel combustion burner according to claim (1), characterized in that a closed annular space having no passage is provided. 6. The angle formed by the line connecting the large-diameter side end of the vertical surface of the truncated cone-shaped flame stabilizer and the ejection hole formed at the tip of the fuel supply nozzle and the burner central axis line. And 30 ° to 80 °, the fuel combustion burner according to claim (1). 7. An angle formed by a line connecting a large-diameter side end portion of a vertical surface of the truncated cone-shaped flame stabilizer and an ejection hole formed at a tip end portion of the fuel supply nozzle and a burner central axis line. 45 ° to 80 °, the fuel combustion burner according to claim (1).