Pulverized coal burner

Abstract: An oil gun (01) for stabilizing combustion is provided at the center portion, and an annular sectional oil primary air flow path (02) surrounding the oil gun (01) and an annular sectional pulverized coal and primary air mixture flow path (14) surrounding the oil primary air flow path (02) are provided. Around the mixture flow path (14), an annular sectional secondary air flow path (15) and an annular sectional tertiary air flow path (16) surrounding the secondary air flow path (15) are provided. A pulverized coal supply pipe is connected in the tangential direction to the mixture flow path (14). Further, an entering angle control means (28) of said mixture is provided within the pulverized coal supply pipe (11). Within the mixture flow path (14), a pulverized coal density dividing cylinder (25) is provided.

Description: BACKGROUND OF THE INVENTION: Field of the Invention: The present invention relates to a pulverized coal combustion burner as defined in the preamble portion of claim 1 to be applied to a pulverized coal firing boiler, a chemical industrial furnace, etc. for public power utilities and other industries. Description of the Prior Art: Fig. 11 is a longitudinal sectional view showing an example of a cylinder type pulverized coal burner in the prior art which is a basis of the present invention, Fig. 12 is a front view of the same, and Fig. 13 is a transverse sectional view taken on line VIII-VIII of Fig. 11. In this burner, there is provided an oil gun (01) for stabilizing combustion at the axis center portion of the burner, and an oil primary air flow path (13) surrounding the oil gun (01) and partitioned of the outer circumference by an oil primary air pipe (02), a pulverized coal and primary air mixture flow path (14) on the outer side of the oil primary air flow path (13), partitioned of the outer circumference by a primary air pipe (03), a secondary air flow path (15) further on the outer side of the pulverized coal and primary air mixture flow path (14), partitioned of the outer circumference by a secondary air pipe (04), and a tertiary air flow path (16) further on the outer side of the secondary air pipe (04), partitioned of the outer circumference by an outer cylinder are provided. At a terminal end portion of the oil primary air flow path (13), a swirl vane (05) is provided for maintaining stable flames of heavy oil. The oil primary air is supplied at a ratio of 5% to 10% of the entire air amount as an auxiliary air at the time of heavy oil firing or combustion stabilizing. A secondary air and a tertiary air for main combustion are divided to the secondary air and the tertiary air by an air wind box (09). The secondary air is given necessary swirl forces by a secondary swirl vane (07) and is supplied into a furnace through the secondary air flow path (15) and a secondary air nozzle (18). Likewise, the tertiary air also is given necessary swirl forces by a tertiary air swirl vane (08) and is supplied into the furnace through the tertiary air flow path (16) and a tertiary air nozzle (19). On the other hand, as shown in Fig. 13, a pulverized coal as a main fuel is supplied into the burner together with the primary air for carrying via a pulverized coal supply pipe (11) connected rectangularly to the primary air pipe (03) and further into the furnace through the mixture flow path (14) and a pulverized coal nozzle (17). The pulverized coal jetted from the pulverized coal nozzle (17) is ignited and burns as it is diffusing and mixing with the secondary air and the tertiary air, and further makes complete combustion by the air from an after-air port (not shown) provided downstream of the furnace. Incidentally, at a terminal end portion of the secondary air nozzle (18) which corresponds to the outer circumference of the primary air and pulverized coal mixture flow path (14), there is provided a flame stabilizing plate (06). In said axial symmetrical cylinder type burner in the prior art, there is such a shortcoming as mentioned below: As the pulverized coal supplied into the burner flows in rectangularly to the axis of the primary air pipe (03), there occur bias flows in the pulverized coal and primary air mixture flow path (14) and a pulverized coal density distribution in the circumferential direction at the outlet portion of the pulverized coal nozzle (17) becomes extremely ununiform. Accompanying therewith, the distance between the burner and the point of ignition of the pulverized coal becomes ununiform in the circumferential direction. That is, in the area where the pulverized coal density is high, the ignition point is near, and if it is low reversely, the ignition point becomes apart. If the ignition point becomes ununiform, there is a fear of the burner being damaged by heat in the area where the ignition point is near. Further, in the area where the ignition point is apart, as the secondary air has already partially diffused, the air ratio at the ignition point becomes high and an oxidation flame is generated, thus a generation of increased amount of NO x occurs. Following is a description of a burner in the prior art shown in Fig. 14 and Fig. 15: Fig. 14 is a longitudinal sectional view showing an example of a coal firing cylinder type burner in the prior art, and Fig. 15 is a transverse sectional view taken on line V-V of Fig. 14. In these figures, each numeral designates the respective component and part as follows: (201) a burner wind box, (202) a pulverized coal and primary air mixture cylinder, (203) a flame stabilizing plate, (204) a secondary air cylinder, (205) a tertiary air cylinder, (206) an oil burner gun guide pipe, (207) an oil burner gun, (208) a pulverized coal dense/thin separator, (209) a secondary air amount adjusting damper, (210) a secondary air swirl vane, (211) a tertiary air swirl vane, (212) a pulverized coal mixture throwing pipe, (213) a burner front wall, (214) a pulverized coal mixture compartment, (215) a secondary air compartment, (216) a tertiary air compartment, (217) a secondary air amount adjusting damper operation lever, (218) a secondary air swirl vane operation lever, (219) a tertiary air swirl vane operation lever, (220) a seal air, (221) a pulverized coal mixture, (222) a secondary air, (223) a tertiary air, (224) a liquid fuel and (225) a boiler furnace. A combustion air supplied from an air blowing equipment (not shown) is divided, while it is flowing, into the secondary air (222) and the tertiary air (223) within the burner wind box (201). The secondary air (222) is adjusted to a necessary amount by the secondary air amount adjusting damper (209) operated by an operation lever (217) and is supplied into the secondary air compartment (215) within the secondary air cylinder (204) via the secondary air swirl vane (210) operated by an operation lever (218) and then is blown into the boiler furnace (225). The remaining combustion air is supplied as the tertiary air (223) into the tertiary air compartment (216) within the tertiary air cylinder (205) via the tertiary air swirl vane (211) and then is blown into the boiler furnace (225). A coal as a fuel is pulverized by a coal pulverization equipment (not shown), is mixed with the primary air and is supplied as the pulverized coal mixture (221) to be blown into the pulverized coal mixture compartment (214) within the pulverized coal mixture cylinder (202) from the pulverized coal mixture throwing pipe (212). At the terminal end of the pulverized coal mixture cylinder (202), the flame stabilizing plate (203) is provided and, inside thereof, the oil burner gun guide pipe (206) passing through the pulverized coal mixture cylinder (202) is provided. On the outer circumference of the oil burner gun guide pipe (206), the cylindrical pulverized coal dense/thin separator (208), the front part and the rear part of which are reduced, is provided so as to be positioned near the outlet of the pulverized coal mixture compartment (214). Within the oil burner gun guide pipe (206), there is provided the oil burner gun (207) for atomized combustion of the liquid fuel (224). Combustion of the liquid fuel (224) by the oil burner gun (207) is made for a purpose of raising the temperature within the boiler furnace (225) before a pulverized coal combustion is commenced. Within the oil burner gun guide pipe (206), the seal air (220) is continuously supplied from an air blowing equipment (not shown) so that the oil burner gun guide pipe (206) may not be blocked by the pulverized coal after the pulverized coal combustion is commenced. The pulverized coal mixture (221) blown into the pulverized coal mixture compartment (214) is accelerated while it passes on the outer circumference of the pulverized coal dense/thin separator (208), and at the outlet portion of the pulverized coal mixture compartment (214) it suddenly expands and is decelerated. At this time, the pulverized coal within the pulverized coal mixture (221) flows for the most part biassedly by the inertia force on the outer circumferential side, or on the inner wall surface side of the pulverized coal mixture cylinder (202), and on the center portion side of the outlet of the pulverized coal mixture compartment (214), there flow the primary air within the pulverized coal mixture (221) and a small amount of the pulverized coal of fine particles mixed therewith. Accordingly, the jet flow of the pulverized coal mixture (221) blown into the boiler furnace (225) has such a density distribution wherein the pulverized coal density is high on the surface (outer side) and is low on the inner side. The flame stabilizing plate (203) provided at the terminal end of the pulverized coal mixture cylinder (202) generates swirl flows of the secondary air (222) flowing on the outer circumference of the pulverized coal mixture cylinder (202) on the back side surface of the flame stabilizing plate (203), thus the pulverized coal on the surface (outer side) of the jet flow of the pulverized coal mixture (221) is taken therein and ignited, and the pulverized coal flame at the ignition portion is stabilized. The pulverized coal mixture (221) blown into the boiler furnace (225) from the pulverized coal mixture cylinder (202) is ignited by an ignition source (not shown), while at around the jet portion the pulverized coal mixture (221) is ignited on the surface side of the jet flow of the pulverized coal mixture (221) and as it proceeds downstream of the jet flow of the pulverized coal mixture (221), ignition proceeds to the direction of the inner side, thus pulverized coal flames are generated. Fig. 16 is a schematic drawing showing a model of a pulverized coal flame. The nearer is the ignition point to the jet portion of the pulverized coal mixture (221), the more the pulverized coal flame tends to stabilize. At the ignition point of the pulverized coal flame, as shown in Fig. 16, the surface of the jet flow of the pulverized coal mixture (221) is heated by an ignition source, thereby a volatile content is generated and ignited. Accordingly, if the pulverized coal density on the surface side of the jet flow is high near the jet portion of the pulverized coal mixture (221), the ignition point of the pulverized coal flame comes nearer to the jet portion and stable pulverized coal flames are generated. The pulverized coal flames so generated continue combustion by the secondary air (222) and the tertiary air (223) blown from the circumference thereof. In the above described coal firing cylinder type burner in the prior art shown in Fig. 14 and Fig. 15, there are such shortcomings to be solved as follows: While the pulverized coal density distribution adjustment of the jet flow of the pulverized coal mixture (221) at the outlet of the pulverized coal mixture compartment (214) is made by the pulverized coal dense/thin separator (208), the pulverized coal density on the surface side of the jet flow does not become high enough, and in a combustion of low volatile content coals in which the fuel ratio (ratio of a solid carbon content and a volatile content) is high, the ignition point of the pulverized coal flame is parted far from the outlet of the pulverized coal mixture compartment (214), thus the ignition stability of flame is not good enough. Further, in case of a combustion amount within the boiler furnace (225) being decreased, the pulverized coal density of the pulverized coal mixture (221) supplied from a coal pulverizing equipment becomes lower and the ignition stability of the pulverized coal flame in a low load combustion becomes worse. Following is a description of a burner in the prior art shown in Fig. 17: Fig. 17 is a schematic longitudinal sectional view of a main part of a pulverized coal burner in the prior art, wherein there are provided an outer circumferential cylinder (307) on the inner side of a furnace wall port (309) via a tertiary air jet port (308) and a burner body (301') at the center on the inner side of the outer circumferential cylinder (307) via a secondary air jet port (306), and a pulverized coal and a primary air are supplied from the burner body (301'). A duct damper (not shown) is provided at an inlet on the left side of the figure and the air amount is increased or decreased unitarily not by each of the primary to the tertiary flow paths. The right side of Fig. 17 is a conceptual drawing of a combustion which shows that the combustion proceeds downstream with two stages: a reduction atmosphere where the air ratio is less than 1 and an oxidation atmosphere where the air ratio is more than 1, that is, the pulverized coal first makes a volatile content combustion in the reduction atmosphere and generates NO x , and then makes a combustion to convert to N 2 , or an oxidation combustion. Recently, as is known, since a low NO x is required for every kind of exhaust gases, in the above-mentioned combustion also, in order to convert immediately the NO x generated in the reduction atmosphere to N 2 , air (oxygen in fact) could be supplied quickly within the range where the temperature does not decrease, but there is such a problem that if, for example, the primary air amount is supplied too much, the ratio of a cooling heat becomes too high to a combustion heat so that the volatile content combustion does not develop, and even if the primary air amount is appropriately suppressed and the secondary and tertiary air are increased, due to the air flow line made by the terminal end (the right end of the figure) of the burner body (301') and the outer circumferential cylinder (307) being open like a funnel, as shown in figure, the air is not able to mix well into the combustion area unless it comes comparatively downstream. Needless to mention, the funnel-like opening at the terminal end of the burner body (301') and the outer circumferential cylinder (307) is indispensable for such requirement that air is to be uniformly mixed into so-called combustion flames of a generation gas (NO x etc.), air, etc. within the combustion area which makes a sudden expansion by combustion and that the current velocity of flames is to be appropriately suppressed so as to secure enough heat transmission to the furnace wall pipes, etc. The NO x generation amount in relation to the reduction atmosphere temperature taken at the portion where the pulverized coal finishes combustion after the reduction atmosphere and the oxidation atmosphere, or on the extreme right side of Fig. 17, is shown in a diagram of Fig. 18, which shows that the higher is the reduction atmosphere temperature, the lesser is the NO x amount. Fig. 19 is a diagram showing a relation between the secondary air amount and the coal volatile content amount in an example shown in Fig. 18. In the above-described pulverized coal combustion burner in the prior art shown in Fig. 17, there are such shortcomings to be solved as follows: In this pulverized coal combustion burner in the prior art, the jet ports of the primary air to carry the pulverized coal and of the secondary and tertiary air from the circumference are provided fixedly and the air amount cannot be adjusted at the jet ports to the kind of coal. Accordingly, the adjustment of the air amount is made by a usual duct damper provided at the inlet being adjusted. A low NO x combustion by the pulverized coal combustion burner depends on how quickly the coal volatile content combustion is made at the reduction are immediately after the jet ports and how quickly the generated NO x is converted to N 2 while the temperature does not decrease downstream. But, as the volatile content varies according to the kind of coal and yet many kinds of coal are used in a power station, there is such a problem in the pulverized coal combustion burner in the prior art which has funnel-like openings provided fixedly that the mixing area of the secondary air comes downstream and a low Nox combustion is not well attained to the kind of coal. A prior art pulverized coal combustion burner comprising the features of the preamble portion of claim 1 is described in EP-A-0 343 767. This burner has concentric passages for a primary air-fuel mixture and secondary and tertiary air flows respectively formed by coaxial tubes surrounding a central oil burner. A duct tangentially joins the inlet section of the mixture flow passage to introduce a swirling flow of primary combustion air in which pulverised fuel is suspended. Radial guide elements are provided at angularly spaced positions in the mixture flow passage. Another pulverized coal combustion burner is described in EP-A-0 571 704 which is similar in construction and has a radial inlet duct to the primary air-fuel mixture passage and which has spiral inlet ducts for the secondary and tertiary air flow passages, which are respectively provided with sprial guides. SUMMARY OF THE INVENTION: It is an object of the present invention to provide a pulverized coal combustion burner which is able to make a circumferential distribution of a pulverized coal density uniform at the outlet portion of a pulverized coal nozzle as well as to secure to generate a dense mixture at the outer circumference and a thin mixture on the inner side and to form pulverized coal flames which have stable ignition points. It is further an aspect of the present invention to provide a pulverized coal combustion burner which is able to decrease the NO x amount in the combustion. In order to attain these objects, the present invention provides a pulverized coal combustion burner as defined in claim 1. Such combustion burner comprising an oil gun for stabilizing combustion at the center portion, an annular sectional oil primary air flow path surrounding the oil gun, an annular sectional pulverized coal and primary air mixture flow path surrounding the oil primary air flow path, an annular sectional secondary air flow path surrounding the mixture flow path and an annular sectional tertiary air flow path surrounding the secondary air flow path, wherein a pulverized coal supply pipe is connected in the tangential direction to the mixture flow path. The pulverized coal combustion burner according to the present invention is so constructed as mentioned above and the pulverized coal supply pipe is connected in the tangential direction to the pulverized coal mixture flow path, thereby the pulverized coal mixture is given swirl forces and the pulverized coal density becomes high at the outer circumferential portion of the mixture flow path and thin on the inner side. By this swirling, the circumferential density distribution becomes uniform. In addition to said construction of the pulverized coal combustion burner according to the present invention, a construction is taken that a means to control the entering angle of said pulverized coal mixture is provided at the terminal end of the pulverized coal supply pipe, the swirling force of the pulverized coal mixture can be controlled. Accordingly, even if a combustion load decreases and the pulverized coal density in the mixture becomes lower, the pulverized coal is concentrated in the outer flow path, the pulverized coal density in that flow path is maintained at a certain level and the ignition can be stabilized. Further, in addition to said entering angle control means, if such a construction is taken that the front portion of the inside of said pulverized coal mixture cylinder is divided into an outer portion and an inner portion and a pulverized coal density separation cylinder which forms an annular sectional dense mixture path on the outer side and a thin mixture path on the inner side is provided, then said dense mixture and said thin mixture, respectively, flows into the annular sectional dense mixture path formed on the outer side and the thin mixture path formed on the inner side of the pulverized coal density separation cylinder, thus a pulverized coal combustion burner which can securely form a dense and thin mixture is obtained. Further, in a pulverized coal combustion burner according to the present invention in which a pulverized coal supply pipe is connected in the tangential direction to the mixture flow path, as mentioned above, if the mixture flow path is constructed so as to comprise an inner cylinder element having a flange which opens at the terminal end portion in a funnel shape and is intermittently cut-off portions along the circumference and an outer cylinder element surrounding the inner cylinder element, having a flange of same shape as that of said inner cylinder element at the terminal end portion and being rotatable around the axis relatively to the inner cylinder element, an NO x decrease can be efficiently attained. That is, by use of a construction in which the oil gun for stabilizing combustion and the oil primary air flow path are surrounded by the inner cylinder element and the outer cylinder element of said construction, at the time point that the oil gun is ignited, the pulverized coal combustion is commenced upon the pulverized coal and the pulverized coal carrying air being jetted from the outer circumference and enough reduction atmosphere and oxidation atmosphere are generated, if the outer cylinder element, for example, relatively to the inner cylinder element is rotated, then the cut-off portions of each flange (hereinafter the flange with the cut-off portions are referred to as "flange") are lapped (open), or rotatively separated (close), each other in the circumferential direction, and in case of lapping the outer circumferential secondary air comes straight in the flange area through the cut-off portions so that a quick secondary air supply is made, and a low NO x area (conversion to N 2 ) is made efficiently. And in case of rotative separation of the flanges, the cut-off portions proceed to the direction to close each other, the straight flow of the secondary air decreases and stops upon closing, and a funnel-like flange without cut-off portions equivalent to a conventional one is formed. If the opening of the cut-off portions of each flange is controlled appropriately, a straight flow of air which is best suited to the kind of coal can be obtained. Incidentally, the outer cylinder generates a secondary and a tertiary air, same as the conventional one. BRIEF DESCRIPTION OF THE DRAWINGS: In the accompanying drawings: Fig. 1 is a longitudinal sectional view showing a first preferred embodiment according to the present invention. Fig. 2 is a front view of Fig. 1. Fig. 3 is a transverse sectional view taken on line III-III of Fig. 1. Fig. 4 is a sectional view taken on line IV-IV in the direction of arrows of Fig. 1. Fig. 5 is a sectional view taken on line V-V in the direction of arrows of Fig. 1. Fig. 6 is a longitudinal sectional view showing a second preferred embodiment according to the present invention. Fig. 7 is a transverse sectional view taken on line II-II in the direction of arrows of Fig. 6. Fig. 8 is a transverse sectional view taken on line III-III in the direction of arrows of Fig. 6. Fig. 9 is a drawing of a main part of a third preferred embodiment according to the present invention, wherein Fig. 9(a) is a front view and Fig. 9(b) is a right side sectional view (longitudinal sectional view). Fig. 10 is a drawing showing a functional comparison between the third preferred embodiment and an example in the prior art, wherein Fig. 10(a) shows the third preferred embodiment and Fig. 10(b) shows a prior art. Fig. 11 is a longitudinal sectional view showing an example of a pulverized coal burner in the prior art. Fig. 12 is a front view of Fig. 11. Fig. 13 is a transverse sectional view taken on line VIII-VIII of Fig. 11. Fig. 14 is a longitudinal sectional view showing an example of a coal firing cylinder type burner in the prior art. Fig. 15 is a transverse sectional view taken on line V-V in the direction of arrows of Fig. 14. Fig. 16 is a schematic drawing showing a model of a pulverized coal flame. Fig. 17 is a schematic longitudinal sectional view of a main part of an example of a burner in the prior art. Fig. 18 is a diagram showing a relation between the final NO x generation and the reduction atmospheric temperature of an example in the prior art. Fig. 19 is a diagram showing a general relation between a secondary air amount and a coal volatile content amount. DESCRIPTION OF THE PREFERRED EMBODIMENTS: Following is a description in a concrete form on a pulverized coal combustion burner according to the present invention based on preferred embodiments shown in Fig. 1 to Fig. 10: (First Preferred Embodiment) A first preferred embodiment shown in Fig. 1 to Fig. 5 is described. In Fig. 1 to Fig. 5, same or similar component or part as those in the prior art described in Fig. 11 to Fig. 13 is given a same numeral for avoiding redundancy and a detailed description is omitted. In this first preferred embodiment, a pulverized coal supply pipe (11) is connected to a mixture flow path (14) in the tangential direction with a certain entering angle α (45° - 90°), and at the terminal end of the pulverized coal supply pipe (11) a block (28) is provided pivotally, right and left, on the burner transverse section around an axis on the inner end face of the pulverized coal supply pipe (11) for controlling the entering angle of said mixture. Also in this first preferred embodiment, a pulverized coal density dividing cylinder (25) to divide the mixture flow path (14) into an outer circumferential portion (26) and an inner circumferential portion (27) is provided. At the outer circumferential portion (26), that is, in a flow path (26) between said pulverized coal density dividing cylinder (25) and a primary air pipe (03), a plurality of block-like splitters (23) as shown in Fig. 4 are provided in the circumferential direction. At the inner circumferential portion (27), that is, in a flow path (27) between said pulverized coal density dividing cylinder (25) and an oil primary air pipe (02), a plurality of rectifying plates (24) as shown in Fig. 5 to rectify the flow parallel to the axis line are provided. Further in this first preferred embodiment, a secondary air nozzle (18) and a tertiary air nozzle (19) which form the terminal end of a secondary air flow path (15) and a tertiary air flow path (16) are provided both projectingly to the front of a pulverized coal nozzle (17) which forms the terminal end of the mixture flow path (14). On the outer side of the terminal end portion of the tertiary air nozzle (19), a dummy refractory (21) is provided so that the terminal end portion of the tertiary air flow path (16) opens to the direction to face to the outer side. In this first preferred embodiment as mentioned above, as the pulverized coal supply pipe (11) is connected in the tangential direction, the pulverized coal and primary air mixture is given swirl forces, a mixture of dense pulverized coal is formed on the outer circumferential portion and a mixture of thin pulverized coal is formed on the inner circumferential portion, each of which is flown into the outer circumferential flow path (26) and the inner circumferential flow path (27), respectively, divided by the pulverized coal density dividing cylinder (25). Further, the density distribution in the circumferential direction becomes uniform by the swirl force. Upon said mixture being jetted into a furnace while it is flowing with swirling, the pulverized coal flames diffuse in wide angles and not only the NO x increases by a sudden mixing with the tertiary air but also, by the combustion flames colliding with the furnace wall according to an arrangement of the burner, there occurs a problem of slagging or CO increase etc., hence the pulverized coal mixture is preferably a flow with a weak swirling or a straight flow in parallel with the burner axis. In this first preferred embodiment, the block-like splitters (23) provided in the flow path (26) on the outer side of the pulverized coal density dividing cylinder (25) at the terminal end portion of the burner serve to weaken the swirl flow of the dense mixture as well as to strengthen the flame stabilizing by the Karman vortex generated downstream of the splitters (25). On the other hand, the rectifying plates (24) provided in the flow path (27) on the inner side of the pulverized coal density dividing cylinder (25) rectify the thin mixture into a straight flow and the thin mixture is ignited to burn by the radiation heat from the dense mixture flames. The movable block (28) provided at the pulverized coal supply pipe (11) controls swirl forces of the pulverized coal by adjusting the entering angle of the primary air and pulverized coal mixture. Accompanying with lowering of a combustion load, the pulverized coal density in the pulverized coal mixture relatively lowers due to a limitation of a mill air flow and the ignition becomes unstable. Accompanying therewith, if the movable block (28) is moved to the direction in which the pivotal radius becomes larger, the pulverized coal concentrates by the centrifugal force in the flow path (26) on the outer side of the pulverized coal density dividing cylinder (25), and even if the combustion load lowers, the pulverized coal density on the outer side of the pulverized coal density dividing cylinder (25) is maintained at a certain level and a stable ignition is secured. Also in this first preferred embodiment, as the secondary air nozzle (18) and the tertiary air nozzle (19) are provided in the front of the pulverized coal nozzle (17), the contact of the secondary air jetted in parallel with the pulverized coal mixture with the flames is delayed and as a result an interference of the secondary air with the pulverized coal mixture before it is ignited can be prevented. Further in this first preferred embodiment, as the terminal end portion of the tertiary air flow path (16) opens to the direction to face to the outer side by the dummy refractory (21) on the outer face of the terminal end portion of the tertiary air nozzle (19), the tertiary air forms such a large circulation flow as to wrap the flames, a wide range of NO x reduction area is formed and NO x is decreased. The number of the splitters (23) provided on the circumference at the terminal end portion of the flow path (dense mixture flow path) (26) on the outer side of the pulverized coal density dividing cylinder (25) is preferably three or more. And the area ratio of the splitters (23) to the sectional area of the dense mixture flow path (26) is preferably in a range of 15% to 30%. The rectifying plates (24) provided in the flow path (thin mixture flow path) (27) on the inner side of the pulverized coal density dividing cylinder (25) are plane plates in the preferred embodiment and the length is preferably the pivotal pitch or more and the number is preferably three or more. As described above, in an axial symmetrical cylinder type pulverized coal burner according to the present invention, the pulverized coal is divided, dense and thin, by the swirl force, and a uniform ignition face and a stable ignition on the entire circumference of the burner can be obtained by a means to control the swirl force according to the load and by the splitters or the rectifying plates provided at the terminal end of the pulverized coal nozzle. Further, by the jetting position and direction of the secondary air nozzle and the tertiary air nozzle being optimized, a wide range of NO x reduction area is formed and NO x can be decreased. (Second Preferred Embodiment) A second preferred embodiment shown in Fig. 6 to Fig. 8 is described. In Fig. 6 to Fig. 8, same or similar component or part as those in the prior art described in Fig. 14 and Fig. 15 is given a numeral obtained by subtracting 100 from the numeral used in Fig. 14 or Fig. 15 and a detailed description is omitted. In Fig. 6 to Fig. 8, numeral (102) designates a cylindrical pulverized coal mixture cylinder, the front end of which is open to the direction to the inside of a boiler furnace (125), numeral (112) designates a pulverized coal mixture throwing pipe connected in the tangential direction to the rear end of said pulverized coal mixture cylinder (102), numeral (130) designates a pulverized coal mixture throwing velocity adjusting plate provided at the connecting portion of said pulverized coal mixture throwing pipe (112) and the pulverized coal mixture cylinder (102), and numeral (131) designates an operation lever thereof. Numeral (127) designates a pulverized coal density dividing cylinder, which divides the inside front portion of said pulverized coal mixture cylinder (102) into an outer portion and an inner portion, respectively, to form an annular sectional dense mixture path (133) on the outer side and an annular sectional thin mixture path (134) on the inner side. Numeral (128) designates a dense/thin mixture amount adjusting damper provided with a space at the rear portion of the pulverized coal density dividing cylinder (127), which is reciprocally movable within a pulverized coal mixture inner cylinder (126) by an operation lever (132). Numerals (129) and (137) designate a dense mixture swirl prevention plate provided in the dense mixture path (133) and a thin mixture swirl prevention plate provided in the thin mixture path (134), respectively. Numeral (108) designates a cylindrical pulverized coal dense/thin separator provided on the outer circumference of the pulverized coal density dividing cylinder (127) of the front portion of the dense mixture swirl prevention plate (129) and reduced of its front and rear portions. A pulverized coal mixture (121) supplied from a coal pulverizing equipment (not shown) is blown in the tangential direction into the pulverized coal mixture cylinder (102) from the pulverized coal mixture throwing pipe (112). At this time, the blowing velocity of the pulverized coal-mixture (121) is continuously maintained appropriately by the pulverized coal mixture throwing velocity adjusting plate (130) provided within the pulverized coal mixture throwing pipe (112). The pulverized coal mixture (121) blown into the pulverized coal mixture cylinder (102) receives an action of the centrifugal force and a dense mixture (135) in which the pulverized coal density is high is formed on the outer circumferential portion, or on the inner wall side of the pulverized coal mixture cylinder (102) and a thin mixture (136) is formed on the inner circumferential portion, or on the outer wall side of the pulverized coal mixture inner cylinder (126), respectively. The dense mixture (135) formed on the outer circumferential portion flows into the annular sectional dense mixture path (133) formed between the pulverized coal mixture cylinder (102) and the pulverized coal density dividing cylinder (127). The thin mixture (136) formed on the inner circumferential portion flows through an opening portion between the pulverized coal mixture inner cylinder (126) and the pulverized coal density dividing cylinder (127) into the annular sectional thin pulverized coal mixture path (134) formed between the pulverized coal density dividing cylinder (127) and a guide pipe (106) for an oil burner gun. The amount of the thin mixture (136) is adjusted by the dense/thin mixture amount adjusting damper (128) controlling the opening amount between the pulverized coal mixture inner cylinder (126) and the pulverized coal density dividing cylinder (127). If the jet flow of the dense mixture is a swirl flow, an expansion of the jet flow becomes large and a diffusion mixing with a secondary air (122) blown from the outer circumference is accelerated, hence the NO x generation amount increases and a diameter of the pulverized coal flame enlarges. But in this second preferred embodiment, the dense mixture (135) flown into the dense mixture path (133) is prevented from swirling by the dense mixture swirling prevention plate (129) to become a straight flow. The flow of the dense mixture (135) which is removed of the swirl flow component is accelerated while it passes on the outer circumference of the pulverized coal dense/thin separator (108), and suddenly expands and is decelerated at the outlet portion of the dense mixture path (133). At this time, as the pulverized coal within the dense mixture (135) flows for the most part biassedly on the inner wall face side of the outlet portion of the dense mixture path (133) by the inertia force, the jet flow of the dense mixture (135) immediately after it is blown into the boiler furnace (125) forms a pulverized coal mixture of further high density on its surface side. On the other hand, the thin mixture (136) is removed of its swirl flow component by the thin mixture swirl prevention plate (137) in the thin mixture path (134) and is blown into the boiler furnace (125) as a straight flow. As for the pulverized coal mixture so blown into the boiler furnace (125), the dense mixture (135) of a high pulverized coal density is formed on the outer circumferential side and the thin mixture (136) of a thin pulverized coal density is formed on the inner side, respectively securely, and the pulverized coal flame having a stable ignition point can be attained. Further, as the both dense/thin mixtures (135), (136) are blown as straight flows, there is no impediment of ignition caused by a dispersion of the dense mixture (135). If a combustion amount in the boiler furnace (125) decreases, the pulverized coal density (pulverized coal amount/primary air amount) of the pulverized coal mixture (121) supplied from a coal pulverizing equipment (not shown) decreases, but in this case the throwing velocity of the pulverized coal mixture (121) is accelerated by the pulverized coal mixture throwing velocity adjusting plate (130), the pulverized coal density of the dense pulverized coal mixture (135) is heightened by a separation efficiency of the pulverized coal being heightened and formation of a stable pulverized coal flame is attained. According to the burner of the present invention as mentioned above, as the pulverized coal density on the surface side of the pulverized coal mixture jet flow blown into the furnace can be maintained at a high density for a wide range of burner load, an always stable pulverized coal flame can be formed. And even with a low volatile content coal of a high fuel ratio, a stable combustion becomes possible. (Third Preferred Embodiment) A third preferred embodiment shown in Fig. 9 and Fig. 10 is described. In Fig. 9 and Fig. 10, same or similar component or part as those in the prior art described in Fig. 17 is given a same numeral and a description is omitted except where necessary. Fig. 9 and Fig. 10 show only the terminal end portions of the pulverized coal burner which are the feature portion of the third preferred embodiment, and the pulverized coal supply pipe is connected in the tangential direction to the pulverized coal and primary air mixture flow path, likewise as the pulverized coal burners of the first preferred embodiment and the second preferred embodiment. In Fig. 9, numeral (301) designates a burning oil tip which is an ignition means of the burner body provided at the center of a furnace wall port (309) along the port axis and numeral (302) designates an oil combustion air port which is a flame maintaining means. Incidentally, the burning oil tip (301) and the oil combustion air port (302) are hereinafter sometimes called collectively as "a burner body", which corresponds to the portion of a burner body (301') in the prior art shown in Fig. 17 removed of the outer cylinder having a funnel-like terminal end. Numeral (303) designates a pulverized coal and carrying air jet port surrounding the outer circumference of the burner body, numeral (304) designates a fixed cylinder (forming an inner cylinder and being fixed) surrounding the burner body via the pulverized coal and carrying air jet port (303) and having an inner flange (304a) which opens at the terminal end like a funnel and is intermittently cut off along the circumference, numeral (305) designates a movable cylinder (outer cylinder) surrounding fittedly the fixed cylinder (304), having an outer flange (305a) of a same shape as an inner flange (304a) of the fixed cylinder (304) at the terminal end and rotatable relatively to the fixed cylinder (304) around the cylinder axis, numeral (306) designates a secondary air jet port, numeral (307) designates an outer circumferential cylinder and numeral (308) designates a tertiary air jet port. Other construction is same as an example in the prior art. Following is a description on the function of the burner of the third preferred embodiment of the above-mentioned construction: Upon the movable cylinder (305) being rotated relatively to the fixed cylinder (304) around the axis nearly by a length of the width of the outer flange (305a) (or the inner flange (304a)), the cut-off portions of the inner flange (304a) are buried (closed) by the outer flange (305a) and the inner flange (304a) and the outer flange (305a) supplement so as to connect each other so that a funnel-like flange is formed around the fixed cylinder (304) (or movable cylinder (305)), that is, a same shape as the example in the prior art is obtained. In this state, the burner body is ignited and the pulverized coal is supplied together with air from the pulverized coal and carrying air jet port (303), and upon the combustion flame being formed enough, the movable cylinder (305) is rotated by an appropriate amount according to the kind of coal and is stopped at a point when a NO x sensor (not shown) shows a minimum NO x value. Needless to mention, a series of these operations may be constructed so as to be automatically done by a drive means via a computer, which is more preferable. As a result of the above, a part of the air passing the secondary air jet port (306) does not jet in a funnel shape but enters into the combustion area in a straight flow through the cut-off portions made by lapping of the inner flange (304a) and the outer flange (305a), thus the high temperature NO x just generated in the reduction atmosphere is supplied with O 2 and is urged to convert to N 2 , and a low NO x is attained efficiently. Fig. 10 is a drawing showing a functional 0 comparison of these functions with an example in the prior art, and a part of the secondary air flows in with straight lines in this third preferred embodiment as shown by arrows in Fig. 10(a), while the secondary air in the example in the prior art flows in with loop lines as shown in Fig. 10(b). 5 According to this third preferred embodiment as mentioned above, as the inner flange (304a) of the fixed cylinder (304) and the outer flange (305a) of the movable cylinder (305) connect or separate each other in the direction of circumference and a part of the flow path of the secondary air is formed straight with equal spaces in the direction of circumference, the secondary air is accelerated to mix in the combustion area, especially in the high temperature reduction atmosphere, and a conversion of NO x to N 2 is done enough, thus there is an advantage that a low NO x is attained efficiently. Further, there is an advantage that by the inner flange (304a) and the outer flange (305a) being connected or separated appropriately, application to various kinds of coal becomes possible. Thus, the burner so constructed as mentioned above has a following effect: As the flange of the inner cylinder and the flange of the outer cylinder are connected or separated by rotation in the direction of circumference and a part of the flow of the secondary air into the combustion faces can be made straight, the NO x can be converted to N 2 in close vicinity of the high temperature reduction atmosphere and a low NO x can be attained efficiently. Further, as the straight flow amount of the secondary air can be controlled by the connection or separation of flanges, application to various kinds of coal becomes possible. While the preferred form of the present invention has been described, variations thereto will occur to those skilled in the art within the scope of the present inventive concepts which are delineated by the following claims.

Claims: A pulverized coal combustion burner comprising an oil gun (01) for stabilizing combustion provided at the center portion; an annular sectional oil primary air flow path (13) surrounding said oil gun (01); an annular sectional pulverized coal and primary air mixture flow path (14) surrounding said oil primary air flow path (13); an annular sectional secondary air flow path (15) surrounding said mixture flow path (14); an annular sectional tertiary air flow path (16) surrounding said secondary air flow path (15); and a pulverized coal supply pipe (11) connected in the tangential direction to said mixture flow path (14); characterized in that means (28;130) for controlling an entering angle of said mixture is provided within said pulverized coal supply pipe (11). The pulverized coal combustion burner as claimed in claim 1, characterized in comprising a pulverized coal density dividing cylinder (25;127) which divides said mixture flow path (14) into an outer portion and an inner portion and forms an annular sectional dense mixture flow path (26;133) on the outer side and a thin mixture flow path (27;134) on the inner side, respectively. The pulverized coal combustion burner as claimed in claim 1 or 2, characterized in that said mixture flow path (14) is constructed by an inner cylindrical body (304) having a flange (304a) which opens at a terminal end in a funnel shape and is cut off intermittently along the circumference and an outer cylindrical body (305) surrounding said inner cylindrical body (304), having a flange (305a) which is of a same shape as said flange (304a) of the inner cylindrical body (304) at a terminal end and rotatable relatively to the inner cylindrical body (304) around the cylindrical body axis.

Inventors: ICHINOSE TOSHIMITSU, OOGURI MASAHARU, OOTA HIDEAKI, YAMADA HITOZI, ICHINOSE, TOSHIMITSU, OOGURI, MASAHARU, OOTA, HIDEAKI, YAMADA, HITOZI, Ichinose, Toshimitsu, c/o Nagasaki Res. &amp; Dev. Ctr, Ooguri, Masaharu, c/o Choryo Engineering Co.,Ltd., Oota, Hideaki, c/o Nag. Res. &amp; Dev. Ctr. Mitsubis., Yamada, Hitozi c/o Nagasaki Shipyard &amp; Mach.Works
Applicants: MITSUBISHI HEAVY IND LTD, MITSUBISHI JUKOGYO KABUSHIKI KAISHA
Application year: 1995
Main classification: F23D1
IPC codes: F23C6, F23D1, F23D17