JP5487917B2 - Multi-fuel burner device - Google Patents

Description

  The present invention relates to a multi-fuel burner apparatus capable of simultaneously burning different kinds of fuels or fuel gases having greatly different compositions.

  In recent years, in order to make effective use of resources, by-product gas discharged from various plants such as chemical plants or steelworks other than high-calorie fuels such as oil and coal has been used as fuel. . In addition, by-product gases differ greatly in composition due to differences in the production process, and the calorific values differ greatly from low to high calories, and burners for the combustion of these gases are also supplied to the fuel supplied. A suitable burner is required.

  Conventionally, it is difficult to burn fuels with greatly different compositions with one burner. Therefore, in a situation where fuels with different compositions are supplied, multiple types of burners suitable for the fuel are installed and supplied to the boiler. Different burners are used according to the fuel, or a plurality of boilers are installed for each different burner, and different boilers are used corresponding to the fuel.

  For this reason, the equipment becomes complicated and the equipment cost becomes high, and there are burners and boilers that are not used, which is uneconomical.

JP-A-9-119606 JP 2000-356307 A

  In view of such circumstances, the present invention provides a multi-fuel burner apparatus capable of simultaneously burning different types of fuel such as liquid and gas, or a plurality of fuel gases having greatly different compositions, with a single burner. .

  The present invention provides an outer cylinder nozzle that opens toward the throat, an inner cylinder nozzle that is provided concentrically with the outer cylinder nozzle and opens toward the throat, and between the inner cylinder nozzle and the outer cylinder nozzle. A plurality of rod-like gas burner nozzles disposed at predetermined intervals on a cylindrical surface parallel to the axis of the inner cylinder nozzle and centered on the axis of the inner cylinder; A rod-like oil burner disposed on the axial center of the cylinder nozzle, and an air adjusting unit for flowing a swirling flow from the periphery of the front end of the outer cylinder, and ejecting the second fuel gas from the gas burner nozzle, A third air is discharged from the inner cylinder nozzle, a first fuel gas having a lower calorie than the second fuel gas from the introduction flow path, and a secondary air is jetted concentrically from the air adjusting unit, and at least the first fuel gas and the Configured to burn the second fuel gas at the same time Those of the fuel burner system.

  Further, according to the present invention, the gas burner nozzle tip has a shape cut obliquely with respect to the shaft center, and a required number of jets are perforated on the slope of the tip, and the gas jetted from the jets The present invention relates to a multi-fuel burner apparatus whose direction intersects with the direction of gas ejected from adjacent gas burner nozzles.

  Further, according to the present invention, a concave groove that is inclined from the outer periphery toward the center is formed at the tip of the outer cylinder nozzle so as to divide the introduction flow path, and the flow of the first fuel gas is divided by the concave groove. In addition, the present invention relates to a multi-fuel burner device that causes secondary air to flow out so as to interrupt the flow of the first fuel gas.

  The present invention also relates to a multi-fuel burner device in which a swirler that imparts a swirling flow to the tertiary air is provided at the tip of the inner cylinder nozzle.

  The present invention also relates to a multi-fuel burner device in which the oil burner is movable back and forth in the axial direction of the oil burner, and also passes through a part of the tip of the outer cylinder nozzle from the outside of the outer cylinder nozzle. The invention relates to a multi-fuel burner device provided with an ignition torch extending toward the throat, and is inclined from the outer side of the outer cylinder nozzle to the axis of the outer cylinder nozzle, The present invention relates to a burner device for multiple fuels provided with a clinker monitoring window capable of monitoring at least a part of a throat portion, and further inclined from the outside of the outer cylinder nozzle to the axis of the outer cylinder nozzle. And a multi-fuel burner apparatus provided with a flame detector capable of monitoring at least one flame of the gas burner nozzle.

  According to the present invention, the outer cylinder nozzle that opens toward the throat, the inner cylinder nozzle that is provided concentrically with the outer cylinder nozzle and opens toward the throat, the inner cylinder nozzle and the outer cylinder nozzle A plurality of rod-like gas burner nozzles disposed at predetermined intervals on a cylindrical surface centered on the axis of the inner cylinder and parallel to the axis of the inner cylinder nozzle; A rod-shaped oil burner disposed on the axial center of the inner cylinder nozzle, and an air adjusting section for flowing a swirling flow from the periphery of the front end portion of the outer cylinder, and ejecting the second fuel gas from the gas burner nozzle , Tertiary air from the inner cylinder nozzle, first fuel gas having a lower calorie than the second fuel gas from the introduction flow path, and secondary air from the air adjusting portion are ejected concentrically, and at least the first fuel gas And the second fuel gas are burned simultaneously Therefore, the oil burner and the high calorie burner are arranged in the center, the influence of disturbance on the combustion of the oil burner and the high calorie burner is reduced, and a large opening area can be secured for a large volume of low calorie combustion gas. In addition, the ejection speed can be suppressed, and the low calorie gas is assisted by the combustion of the high calorie gas on the center side, so that the low calorie gas and the high calorie gas can be combusted simultaneously.

  According to the present invention, the gas burner nozzle tip has a shape cut obliquely with respect to the shaft center, and a required number of jets are perforated on the slope of the tip, and jetted from the jets. Since the gas direction intersects with the direction of the gas ejected from the adjacent gas burner nozzle, the flame by the gas burner nozzle is divided, the contact with the low calorie gas is promoted, the auxiliary combustion effect is increased and the flame is increased. By crossing, it has a flame holding action and combustion is stabilized.

  According to the present invention, a concave groove that is inclined from the outer periphery toward the center is formed at the tip of the outer cylinder nozzle so as to divide the introduction flow path, and the flow of the first fuel gas is caused by the concave groove. And the secondary air is caused to flow out so as to interrupt the flow of the first fuel gas thus diverted, so that mixing of the secondary air and the low calorie gas is promoted, and stable combustion of the low calorie gas can be achieved.

  Further, according to the present invention, since the swirler for providing the swirl flow to the tertiary air is provided at the tip of the inner cylinder nozzle, the mixing of the high calorie gas and the tertiary air is promoted and stable combustion of the high calorie gas can be achieved.

  According to the present invention, the oil burner can advance and retreat in the axial center direction of the oil burner, so that the oil burner can be prevented from being burned out when the oil burner is not used.

  Further, according to the present invention, the ignition torch extending toward the throat from the outside of the outer cylinder nozzle so as to pass through a part of the tip of the outer cylinder nozzle is provided. Ignition is performed reliably.

  Further, according to the present invention, the clinker monitoring window is provided which is inclined from the outside of the outer cylinder nozzle to the axis of the outer cylinder nozzle and can monitor at least a part of the throat portion. In addition, troubles such as burner burnout due to clinker adhesion can be prevented in advance, and the presence and status of a flame can be visually confirmed on site.

  According to the present invention, there is provided a flame detector that is provided so as to be inclined with respect to the axis of the outer cylinder nozzle from the outside of the outer cylinder nozzle and can monitor at least one flame of the gas burner nozzle. As a result, the combustion state can be monitored, and troubles such as misfire can be prevented.

It is the front view which fractured | ruptured a part of burner apparatus for multiple fuels based on the Example of this invention. It is the same front sectional view. FIG. FIG. It is sectional drawing of the 2nd gas burner nozzle front-end | tip part. It is explanatory drawing of the vane connection part of the 2nd air adjustment part of the said burner apparatus for multiple fuels. It is sectional drawing of the nozzle front-end part used for the said multi-fuel burner apparatus. It is a right view of the nozzle front end. It is a fragmentary figure of the rotation damper guide part of the said 2nd air adjustment part. FIG. 6 is a partial view of a rotary damper driving unit of the second air adjusting unit.

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

  1 to 4 show an example of a multi-fuel burner apparatus in which the present invention is implemented, and shows a multi-fuel burner apparatus 1 for burning two kinds of gases, low calorie gas and high calorie gas. In the figure, 2 is a boiler furnace wall, and 3 is a heat transfer tube provided on the boiler furnace wall. 1 to 3, the right side in the figure is the core side, and in the following description, the core side is the front end and the counter-core side is the rear end.

  The boiler furnace wall 2 is provided with a throat 4, and the multi-fuel burner device 1 is provided concentrically with the throat 4. The multi-fuel burner device 1 is mainly composed of a burner 5 and a combustion air adjusting device 6 provided so as to surround the tip of the burner 5.

  As will be described later, the combustion air adjusting device 6 includes a window box 7 concentric with the throat 4, a first air adjusting unit 8, and a second air adjusting unit 9, and is illustrated via a duct flange 10. Not connected to a combustion air supply. The combustion air adjusting device 6 can be connected to another combustion air adjusting device 6 through the duct flange 10, and the multi-fuel burner device 1 can be connected to the combustion air adjusting device 6 through the duct flange 10. Yes.

  The wind box 7 forms a duct space 11 around the burner 5, the first air adjusting portion 8 is provided concentrically at the tip of the burner 5, and the second air adjusting portion 9 is the first air adjusting portion 9. It is provided on the front end side of the air adjusting portion 8 so as to surround the periphery of the front end of the burner 5.

  The surface of the wind box 7 that faces the throat 4 is a front plate 12. The front plate 12 blocks the radiant heat from the throat 4 and is used for heat insulation from the hot air of the wind box 7. A heat insulating material 13 is provided. A cylindrical burner fixing flange 14 is provided at the center of the front plate 12, and the burner 5 is fixed to the burner fixing flange 14.

  First, the burner 5 will be described.

  The burner 5 has a double cylinder structure of an outer cylinder nozzle 15 opening toward the throat 4 and an inner cylinder nozzle 16 opening toward the throat 4. The outer cylinder nozzle 15 includes a nozzle front end 17 and an outer cylinder. The nozzle main body 18 has a two-part structure, and the nozzle front end 17 is made of a corrosion-resistant metal. Further, the nozzle front end portion 17 and the outer cylinder nozzle body 18 are fastened by a flange portion 19, and the front end portion of the outer cylinder nozzle body 18 has a tapered shape, and the outer diameter of the flange portion 19. Is smaller than the inner diameter of the burner fixing flange 14. The outer cylinder nozzle 15 and the inner cylinder nozzle 16 constitute a first gas burner nozzle 20.

An end plate 21 that closes the rear end of the outer cylinder nozzle body 18 is inclined with respect to the axial center, and the end plate 21 at the rear end portion of the outer cylinder nozzle body 18 is separated from the front plate 12. The first fuel gas inlet 22 is provided in the part. The first fuel gas inlet 22 is connected to a first gas supply source (not shown), and the first fuel gas 23 is supplied from the first fuel gas inlet 22. First fuel gas 23 has a low-calorie gas that can not be self-combustion of for example 500kcal / m ³ ~600kcal / m about ^3. The first fuel gas 23 can be injected with steam for stabilizing combustion. For example, a steam ejection nozzle (not shown) is provided at the first fuel gas inlet 22.

  A fixing flange 24 is provided in the middle of the outer cylinder nozzle 15, that is, at a position on the rear end side of the front plate 12. The fixing flange 24 is fastened to the burner fixing flange 14, and the outer cylinder nozzle body 18 and the The nozzle front end portion 17 is fixed integrally.

  The inner cylinder nozzle 16 is disposed concentrically with the outer cylinder nozzle 15 inside the outer cylinder nozzle 15, and a rear end portion is fixed to the end plate 21. The tip of the inner cylinder nozzle 16 is fitted into the nozzle front end portion 17 and the tip radial direction is positioned by the nozzle front end portion 17, but the tip can be displaced in the axial direction. A cylindrical space is formed between the inner cylinder nozzle 16 and the outer cylinder nozzle 15, and the space serves as an introduction flow path 25 for the first fuel gas 23.

  A tertiary air introduction duct 26 that is a cylindrical tube is provided between the inner cylinder nozzle 16 and the outer cylinder nozzle 15 in the radial direction. The tertiary air introduction duct 26 forms a tertiary air introduction port 30, and is provided at a position further divided by the circumference on the front end side than the front plate 12, and at a position divided into four parts in the drawing, The inside of the tube nozzle 16 communicates with the duct space 11.

  The portion of the inner cylinder nozzle 16 facing the tapered portion at the tip of the outer cylinder nozzle body 18 is similarly a tapered portion, and the inner cylinder front end portion 27 located on the front end side of the tapered portion is a straight portion. It has a cylindrical shape.

  The inner cylinder nozzle 16 is supported by the outer cylinder nozzle body 18 by the end plate 21 and the tertiary air introduction duct 26. An expansion / contraction expansion 28 is provided between the end plate 21 of the inner cylinder nozzle 16 and the tertiary air introduction duct 26, and the difference in thermal expansion between the outer cylinder nozzle 15 and the inner cylinder nozzle 16 is It is absorbed by the expansion 28.

  The rear end of the inner cylinder nozzle 16 is closed by a burner support portion 29 that also serves as an end plate. The burner support portion 29 has a three-layer structure along the axial direction, the front end layer being a heat insulating layer 31, the intermediate layer being an intermediate chamber 32, and the rear end layer being a rear end chamber 33. The rear end chamber 33 is hollow.

  Inside the inner cylinder nozzle 16, a plurality of, for example, four, rod-shaped second gas burner nozzles 34 parallel to the axis of the inner cylinder nozzle 16 are provided as a spat burner. The second gas burner nozzle 34 penetrates the burner support portion 29 in the horizontal direction and is arranged symmetrically on the same circumference, and is airtightly attached to the burner support portion 29 via a nozzle holder 35. Yes. A nozzle support 40 projects from the inner surface of the inner cylinder nozzle 16 toward the center, and the second gas burner nozzle 34 is removably inserted into the nozzle support 40 so that a middle portion of the second gas burner nozzle 34 is formed. It is supported by the nozzle support 40. Further, the nozzle support part of the nozzle support 40 is a cylindrical body, and has both ends enlarged.

  The second gas burner nozzle 34 has a double pipe structure, and the nozzle inner pipe 36 accommodated in the second gas burner nozzle 34 is connected to a ring header 38 via a connecting pipe 37. The connecting pipe 37 is bent in a U-shape and can be attached and detached from the rear end side and can be detached from the rear end side.

  Further, as shown in FIG. 5, the tip of the second gas burner nozzle 34 reaches the throat 4 and the tip is cut obliquely at the required angle θ, and the tip slope is required. A number of, for example, 5 to 8 gas ejection holes 56 are formed perpendicular to the slope. Further, the inclined surface at the tip is further inclined at a predetermined angle with respect to the radial line so as to be directed to the center of the throat 4, and as will be described later, the ejection direction of the ejected gas from the second gas burner nozzle 34, that is, the ejection For example, if there are four second gas burner nozzles 34 so that the flames formed by the gas intersect with each other, the direction of the inclined surface is set so that the flames have a cross-beam shape.

  Further, by adjusting the angle θ of the slope and the direction of the slope, the combustion vibration can be suppressed, and the angle of the slope and the direction of the slope where the combustion vibration does not occur are selected.

  The ring header 38 is provided on the burner support 29, and a second fuel gas supply pipe 39 communicates with the ring header 38 (see FIG. 4), and the ring header 38 connects the second fuel gas supply pipe 39. The second fuel gas source 41 is connected to a second fuel gas source (not shown) through which the second fuel gas 41 is supplied from the second fuel gas source to the ring header 38, and the second fuel gas source 41 is further supplied from the ring header 38 to the plurality of nozzle inner pipes 36. The fuel gas 41 is distributed and supplied. By supplying the second fuel gas 41 to the nozzle inner pipe 36 via the ring header 38, the second fuel gas 41 is evenly distributed to the plurality of nozzle inner pipes 36 without using a flow rate adjusting valve or the like. Is supplied.

Here, the second fuel gas 41 is, for example, high calorie gas capable of self-combustion of about 2500 kcal / m ³ or more.

  The second gas burner nozzle 34 has a structure in which a gap (not shown) is formed around the inner tube 36 of the nozzle and over the entire length, and the gap is communicated with the nozzle holder 35. The rear end chamber 33 communicates with the hole 42. The rear end chamber 33 is connected to a cooling air supply pipe 43, the cooling air supply pipe 43 is connected to a cooling air supply source (not shown), and the rear end chamber 33 is connected to the rear end chamber 33 via the cooling air supply pipe 43. Then, cooling air 44 is supplied. The cooling air 44 flows through the gaps in the second gas burner nozzle 34 through the communication hole 42, and flows out from the tip of the second gas burner nozzle 34 while cooling the second gas burner nozzle 34. Yes.

  A low calorie gas auxiliary burner (oil burner) 45 that extends through the center of the burner support 29 and extends along the axis of the inner cylinder nozzle 16 is provided. The oil burner 45 is attached to the burner support portion 29 via an oil burner support 46, and the oil burner 45 slidably penetrates the oil burner support 46, and the oil burner 45 and the oil burner. The support 46 is sealed and a gap is formed between the oil burner 45 and the oil burner support 46, and a seal gas 50 is supplied to the gap as described later.

  A sealing air supply pipe 47 communicates with the intermediate chamber 32, the sealing air supply pipe 47 is connected to a sealing gas supply source (not shown), and the intermediate chamber 32 and the oil burner support 46 communicate with each other. Connected by a tube 48. A gas shield is provided between the oil burner support 46 and the oil burner 45 by the seal gas 50 supplied from the intermediate chamber 32 to the oil burner support 46 through the communication pipe 48.

  A disc-shaped swirler 49 is fixed to the tip of the oil burner 45, and the swirler 49 is slidably fitted to the inner cylinder front end portion 27. Therefore, the oil burner 45 is supported by the oil burner support 46, and is supported by the inner cylinder front end portion 27 via the swirler 49. The swirler 49 has a required number of swirl vanes provided radially, and swirl flow is given to the gas passing through the swirler 49.

  The tip of the second gas burner nozzle 34 passes through the swirler 49 and protrudes to the throat 4, and the swirler 49 is formed with an escape portion 51 so as not to interfere with the second gas burner nozzle 34. Yes.

  The rear end portion of the oil burner 45 is connected to a linear motion actuator, for example, an air cylinder 53 via a connecting portion 52, and the oil burner 45 is guided by the oil burner support 46 by the extension of the air cylinder 53 and moves backward. The oil burner 45 moves forward by shortening the air cylinder 53. Further, the swirler 49 is guided by the inner cylinder front end portion 27 and advances and retracts integrally with the advance and retreat of the oil burner 45. Further, a position detector such as a limit switch 54 detects the position or installation state of the oil burner 45 through the movement of the connecting portion 52, and the oil burner 45 is set at the combustion operation position. At this time, a detection signal is generated by the limit switch 54. In the figure, a swirler 49 indicated by a two-dot chain line indicates a retracted position.

  At the rear end of the oil burner 45, a connector 55 for fluid connection that also serves as a switching valve is provided, and is connected to an oil supply source and a steam supply source (both not shown) via the connector 55, Oil or steam, or oil and steam can be selectively supplied to the oil burner 45 via the connector 55. The liquid fuel burned by the oil burner 45 may be heavy oil, light oil, pitch, or the like.

  In FIG. 1, reference numeral 58 denotes a clinker monitoring window, which is inclined from the outside of the outer cylinder nozzle 15 with respect to the axis of the outer cylinder nozzle 15 so that at least a part of the throat 4 can be monitored. It has become. By confirming whether the clinker has adhered to the throat 4 with the clinker monitoring window 58, troubles such as burner burnout due to clinker adhesion can be prevented. In addition, the presence and status of a flame can be visually confirmed on site.

  In FIG. 3, 59 is a flame detector which is directed in the flame direction and detects or monitors the state of the flame by infrared rays, and can monitor at least one flame of the oil burner 45 or the second gas burner nozzle 34. It has become. The flame detector 59 monitors one flame, but the flame formed by the ejected gas intersects each other and has a flame holding action between the mutual second gas burner nozzles 34. If one flame is monitored, it is possible to grasp the combustion state of the entire flame.

  Reference numeral 60 denotes an ignition torch for igniting fuel at start-up. The ignition torch 60 is supplied with an ignition fuel gas such as LPG or a liquid fuel such as oil and combustion air, and the ignition fuel is sparked. The ignition electrode which emits is provided, and a flame is ejected toward the throat 4 at the time of ignition.

  The combustion air adjusting device 6 will be described. The combustion air adjusting device 6 includes a first air adjusting unit 8 and a second air adjusting unit 9. First, the first air adjusting unit 8 will be described.

  As described above, the tertiary air introduction duct 26 is provided between the outer cylinder nozzle 15 and the inner cylinder nozzle 16, and the duct is formed by the tertiary air introduction port 30 formed by the tertiary air introduction duct 26. The space 11 communicates with the inside of the inner cylinder nozzle 16.

  A cylindrical slide damper 63 is slidably fitted on the tip of the outer cylinder nozzle body 18. The slide damper 63 has a larger axial dimension than the diameter of the tertiary air inlet 30, and the rear end of the slide damper 63 expands in a tapered shape. The slide damper 63 has a slide amount that can completely open the tertiary air inlet 30 and can be completely closed.

  An annular flange 64 is provided around the slide damper 63, and a plurality of, in this embodiment, two slide drive portions 65 are connected to the flange 64.

  The slide drive unit 65 penetrates the front plate 12 and the heat insulating material 13 in the axial direction. A rod support portion 66 is provided in a through portion of the front plate 12 and the heat insulating material 13, and a rod 67 is provided so as to be slidably penetrated by being supported by the rod support portion 66. A front end of the rod 67 is connected to the flange 64, and a handle 68 is provided at the rear end of the rod 67.

  The slide damper 63 moves in the axial direction by moving the slide drive unit 65 back and forth with the handle 68, and depending on the position of the slide damper 63, the slide damper 63 and the tertiary air introduction port 30 are moved. The overlapping amount, that is, the opening amount of the tertiary air inlet 30 is determined. Further, an opening amount confirmation meter 69 is provided in one of the slide drive portions 65 so that the position of the slide damper 63 can be confirmed. The opening confirmation meter 69 is provided on the rod support 66 and has an opening memory (not shown) engraved on the memory indicating needle 70 and the rod 67. The opening memory is located at the position of the slide damper 63. Or corresponding to the degree of opening of the tertiary air introduction port 30, and the memory indicating needle 70 indicates the scale so that the opening amount of the tertiary air introduction port 30 can be confirmed from the indicated scale. It has become. When the rod 67 is fixed, the nut 66a is tightened, the seal member is compressed, the rod 67 is fixed via the seal member, and / or a push bolt is pressed to fix the rod 67. .

  The rod 67 may be moved by an actuator such as a cylinder.

  Next, the second air adjusting unit 9 will be described with reference to FIGS.

  An internal wind box 73 is provided so as to form a donut-shaped secondary air introduction space 72 around the nozzle front end portion 17. The internal window box 73 has a circular outer shape, a donut-shaped recess formed in the center of a back plate 74 provided on the counter-core (rear side) side, and a donut shape surrounding the outer periphery of the recess The convex portion 75 is formed.

  A burner opening 76 concentric with the throat 4 and having the same diameter is formed on the front surface of the inner window box 73, and a throat guide portion 77 having a curved surface continuous with the throat 4 is provided around the burner opening 76. A vane shaft 78 is provided across the throat guide portion 77 and the peripheral edge of the concave portion of the back plate 74. The vane shaft 78 is parallel to the axis of the throat 4 and is provided at a required circumferential pitch. A vane 79 is rotatably provided on each vane shaft 78, and the vanes 79 are connected to each other by a link 81. ing.

  One vane shaft 78a of the vane shaft 78 is fixed to the vane 79a. By rotating the vane shaft 78a, the vane 79a rotates, and all the vanes 79 rotate integrally through the link 81. It is like.

  The front plate 12 is provided with a vane drive motor 82, and the output shaft of the vane drive motor 82 passes through the front plate 12 and the heat insulating material 13 in an airtight manner and is connected to the vane shaft 78 a through a rotary joint 83. Has been. The vane drive motor 82 is connected to a control unit (not shown), and the control unit drives the vane drive motor 82, rotates the vane shaft 78a, and changes the angle of the vane 79. . In FIG. 2, 84 is a handle for rotating the vane shaft 78a manually. The vane drive motor 82, the rotary joint 83, and the like constitute a vane rotation drive unit.

  As shown in FIGS. 7 and 8, the nozzle front end portion 17 is formed with a concave groove 85 inclined from the outer peripheral surface to the axial center side at a position corresponding to the second gas burner nozzle 34. A flow path 86 is formed between the throat guide portion 77 and the center of the throat 4. Further, a discharge port 87 through which the first fuel gas 23 is jetted is formed between the nozzle front end portion 17 and the inner cylinder front end portion 27. The discharge port 87 is divided in the circumferential direction by the concave groove 85. It will be in the state.

  In the figure, reference numeral 88 denotes a recess formed to avoid interference with the ignition torch 60.

  As shown in FIGS. 9 and 10, a ring-shaped rotary damper 89 is provided on the back surface 75 a of the convex portion 75 so as to be rotatable within a required angle range while being in sliding contact with the convex portion 75. The rotary damper 89 is attached to the back surface 75a with a bolt 90 via a washer, and a hole 91 through which the bolt 90 is inserted is a long hole in the circumferential direction. A guide roller 92 is rotatably provided on the outer peripheral surface of the convex portion 75 at a required position, at least at two locations, and the guide roller 92 is in contact with the outer peripheral surface of the rotary damper 89 so as to be able to roll. . Therefore, the rotary damper 89 is guided by the guide roller 92, and the rotary damper 89 can rotate within the range of the long hole 91.

  The back surface 75a is provided with substantially strip-shaped openings A93 at a predetermined angular pitch, and the rotary damper 89 is provided with openings B94 having the same shape and the same pitch as the openings A93. Within the rotation range of the damper 89, the opening A93 can be fully opened and fully closed. In the figure, the opening A93 is in a half-open state.

  A pair of brackets 95 projecting toward the center are erected on the inner peripheral surface of the rotary damper 89, and an eccentric cam 96 is fitted between the brackets 95. A rotating shaft 97 of the eccentric cam 96 is rotatably supported on the inner peripheral surface of the convex portion 75, and the rotating shaft 97 is connected to a rotating damper rotating shaft 99 via a rotating joint 98. The rotary damper rotating shaft 99 passes through the front plate 12 and the heat insulating material 13 in an airtight manner, and is connected to a rotary damper rotation input unit 101 supported by the front plate 12.

  The rotation input unit 101 is, for example, a worm speed reducer, and although not shown, the input shaft 102 is rotated by a handle to rotate the rotary damper rotary shaft 99 and the eccentric cam via the rotary joint 98. 96 is rotated, and further, the rotary damper 89 is rotated via the bracket 95. The rotation input unit 101, the rotary joint 98, the eccentric cam 96, and the like constitute a rotary damper drive unit.

  The rotation input unit 101 may include an actuator such as a motor, and the rotation damper 89 may be automatically rotated.

  Further, a rotary scale 103 is provided at the protruding position of the rotary damper rotating shaft 99 of the rotary input unit 101, an angle indicating needle 104 is provided at the protruding end of the rotary damper rotating shaft 99, and the rotating position of the rotary damper 89, that is, the You may make it show the opening degree of opening part A93.

  Furthermore, a perforated plate such as a punching metal is used for the outer peripheral surface and inner peripheral surface of the convex portion 75, and the secondary air introduction space 72 is separated from three surfaces of the rear surface, outer peripheral surface, and inner peripheral surface of the convex portion 75. You may make it take in combustion air. The perforated plate adjusts the balance between the pressure loss of the air passing through the rotary damper 89 and the pressure loss of the air passing through the outer peripheral surface and the inner peripheral surface of the convex portion 75 to adjust the flow rate by the rotary damper 89. Is to enable. It should be noted that the outer peripheral surface and the inner peripheral surface of the convex portion 75 may be closed by a separately provided closing plate (not shown).

  Hereinafter, the operation of the multi-fuel burner device 1 will be described.

  Corresponding to the fuel gas to be used, the slide drive unit 65 adjusts the position of the slide damper 63 to set the degree of opening of the tertiary air inlet 30, and the rotation through the rotation input unit 101. The rotation of the damper 89 is adjusted to set the opening degree of the opening A93, and the vane drive motor 82 is further driven to set the angle of the vane 79. Note that data on the degree of opening of the tertiary air inlet 30, the degree of opening of the opening A93, and the angle of the vane 79 are acquired in advance by a combustion test or the like.

  Combustion air is supplied from the duct flange 10 to the duct space 11.

  A part of the combustion air flowing into the duct space 11 is adjusted in flow rate by the slide damper 63 and flows into the inner cylinder nozzle 16 from the tertiary air introduction port 30, and flows in the axial direction. As a result, the swirler 49 is reached and passed through the swirler 49, so that swirl is given and the air is ejected from the periphery of the oil burner 45 and from the center of the second gas burner nozzle 34 as the tertiary air 107.

  The ignition torch 60 is ignited.

  The air cylinder 53 is shortened and the oil burner 45 is advanced to the ignition position. Whether or not the predetermined position has been reached is confirmed by a signal from the limit switch 54.

  When the oil burner 45 is set at a predetermined position, oil is ejected from the oil burner 45, the oil is ignited by the ignition torch 60, and the ignition torch 60 is extinguished.

  The low-calorie first fuel gas 23 is supplied from the first fuel gas inlet 22, and the high-calorie second fuel gas 41 is supplied from the second fuel gas supply pipe 39.

  By the ignition torch 60, the second fuel gas 41 ejected from the second gas burner nozzle 34 is ignited. Since the flame formed by the second gas burner nozzle 34 is set so as to intersect with each other, the second gas burner nozzle 34 is ignited and burned, so that The second gas burner nozzle 34 is also ignited and reaches a combustion state. Moreover, even if one of them misfires, the flame of the other 2nd gas burner nozzle 34 becomes a fire type, and it will be in a combustion state again.

  The first fuel gas 23 is supplied from the first fuel gas inlet 22, and the first fuel gas 23 flows in an axial direction along the end plate 21, and the inner cylinder nozzle 16 and the outer cylinder nozzle Through the introduction flow path 25 between 15, the flow is diverted by the concave groove 85 and ejected from the discharge port 87.

  The remainder of the combustion air flowing into the duct space 11 is adjusted in flow rate by the rotary damper 89, flows into the secondary air introduction space 72, and swirled by the vane 79, toward the throat 4. It flows out as secondary air 106. In the course of the outflow of the throat 4, since the concave groove 85 is formed in the nozzle front end portion 17, more combustion air flows out from the concave groove 85. Accordingly, the groove 85 has a shunting action, and the groove 85 is provided at a position corresponding to the second gas burner nozzle 34, so that the secondary air 106 is positively applied to the second gas burner nozzle 34. Supplied and promotes combustion of the second fuel gas 41.

  Further, since the secondary air 106 flowing out of the concave groove 85 flows out so as to interrupt the flow of the low-calorie first fuel gas 23 that has been diverted, the first fuel gas 23, the secondary air 106, Is promoted. Further, since the flames by the second gas burner nozzles 34 are formed adjacent to the flow of the divided first fuel gas 23, the auxiliary combustion action by the flames of the second gas burner nozzles 34 on the first fuel gas 23 is achieved. This increases and a good combustion state of the first fuel gas 23 is obtained.

  As described above, the secondary air 106 and the tertiary air 107 are supplied through the same wind box 7, and the flow rate of the secondary air 106 and the tertiary air 107 can be adjusted here. Optimal combustion air can be supplied by the single fuel burner device 1 without any disturbance to the air control system.

  By starting combustion, a temperature difference is generated between the outer cylinder nozzle 15 and the inner cylinder nozzle 16, and a thermal expansion difference based on the temperature difference is generated. The inner cylinder nozzle 16 is restrained by the outer cylinder nozzle 15 by the end plate 21 and the tertiary air introduction duct 26, and this thermal expansion difference is absorbed by expansion and contraction of the expansion 28.

  The combustion state is confirmed by the flame detector 59, and when the first fuel gas 23 is in a stable combustion state, the combustion by the oil burner 45 can be stopped. The air cylinder 53 is driven, and the oil burner 45 is retracted together with the swirler 49, and thermal damage to the swirler 49 and the oil burner 45 is prevented.

  The second gas burner nozzle 34 has a double-pipe structure as described above, and the cooling air 44 flows through the communication hole 42 toward the front end and then flows out from the front end. The cooling air 44 cools the second gas burner nozzle 34, particularly the tip, and prevents the second gas burner nozzle 34 from being burned out, thereby extending the life.

  Thus, it is possible to burn a low calorie fuel gas that cannot be self-combusted and to effectively use the by-product gas.

  It is effective to improve the combustion state and supply steam stably, and supply steam appropriately from the oil burner 45 according to the combustion state.

  In the above description, the second fuel gas 41 (high calorie gas) is burned by the second gas burner nozzle 34 as auxiliary combustion of the first fuel gas 23 (low calorie gas). Instead of combustion, oil may be burned by the oil burner 45.

  Next, maintenance of the multi-fuel burner device 1 will be described.

  First, when the maintenance of the second gas burner nozzle 34 is performed, the connecting pipe 37 connected to the target second gas burner nozzle 34 is removed. By removing the connecting pipe 37, there is no need to fix the second gas burner nozzle 34, and the second gas burner nozzle 34 can be pulled out in the rear end direction. The second gas burner nozzles 34 can be pulled out individually.

  When installing the second gas burner nozzle 34 for which maintenance has been completed, the above procedure may be reversed and the operation is extremely simple.

  Further, when performing large-scale maintenance, if the piping system connected to the multi-fuel burner device 1 is disconnected, the burner 5 is fixed only by the fixing flange 24 portion. Since the outer diameter of the outer cylinder nozzle 15 gradually decreases toward the front end side, the burner 5 can be pulled out to the rear end side by removing the fixing flange 24 from the burner fixing flange 14.

DESCRIPTION OF SYMBOLS 1 Burner apparatus for multiple fuels 2 Boiler furnace wall 3 Heat transfer tube 4 Throat 5 Burner 6 Combustion air adjustment device 7 Wind box 8 First air adjustment part 9 Second air adjustment part 12 Front plate 15 Outer cylinder nozzle 16 Inner cylinder nozzle 17 Nozzle Front end portion 18 Outer cylinder nozzle body 20 First gas burner nozzle 21 End plate 23 First fuel gas 25 Introduction flow path 26 Tertiary air introduction duct 27 Inner cylinder front end portion 28 Expansion 29 Burner support portion 30 Tertiary air introduction port 34 Second Gas burner nozzle 37 Connecting pipe 38 Ring header 41 Second fuel gas 42 Communication hole 44 Cooling air 45 Oil burner 48 Communication pipe 49 Swirler 50 Seal gas 53 Air cylinder 56 Gas ejection hole 63 Slide damper 65 Slide drive part 72 Secondary air introduction space 73 Internal wind box 75 Convex part 79 Vane 8 2 Vane drive motor 85 Concave groove 87 Discharge port 101 Rotation input unit 106 Secondary air 107 Tertiary air

Claims (7)

An outer cylinder nozzle that opens toward the throat, an inner cylinder nozzle that is provided concentrically with the outer cylinder nozzle and that opens toward the throat, and an introduction formed between the inner cylinder nozzle and the outer cylinder nozzle A plurality of rod-like gas burner nozzles disposed at predetermined intervals on a cylindrical surface parallel to the axis of the inner cylinder nozzle and centered on the axis of the inner cylinder; and a shaft of the inner cylinder nozzle A rod-shaped oil burner disposed on the center, and an air adjusting unit that flows a swirling flow from the periphery of the front end portion of the outer cylinder, and ejects a second fuel gas from the gas burner nozzle, and from the inner cylinder nozzle Tertiary air, the first fuel gas having a lower calorie than the second fuel gas from the introduction flow path, and the secondary air are ejected concentrically from the air adjusting unit, and the tip of the outer cylinder nozzle Inclined from the outer circumference to the center to divide the introduction channel A concave groove is formed at a position corresponding to the gas burner nozzle, and the flow of the first fuel gas is diverted by the concave groove and the secondary air flows out to interrupt the flow of the first fuel gas. is, to increase the auxiliaries retardant effect with respect to the first fuel gas from the combustion of the second fuel gas together to promote the combustion of the second fuel gas to co-fire and said second fuel gas and at least said first fuel gas A multi-fuel burner device characterized in that it is configured as described above.   The gas burner nozzle tip has a shape cut obliquely with respect to the axial center, and a required number of jet outlets are formed on the slope of the tip, and the direction of gas jetted from the jet outlet is adjacent to the gas burner. 2. The multi-fuel burner device according to claim 1, wherein the burner device intersects with the direction of gas ejected from the nozzle.   The burner apparatus for multiple fuels according to claim 1, wherein a swirler for providing a swirling flow to the tertiary air is provided at the tip of the inner cylinder nozzle.   The multi-fuel burner device according to claim 1, wherein the oil burner is movable back and forth in the axial direction of the oil burner.   The multi-fuel burner device according to claim 1, further comprising an ignition torch extending toward the throat so as to pass from a part of a tip portion of the outer cylinder nozzle from the outside of the outer cylinder nozzle.   The burner for multiple fuels according to claim 1, further comprising a clinker monitoring window provided at an inclination with respect to the axis of the outer cylinder nozzle from the outside of the outer cylinder nozzle and capable of monitoring at least a part of the throat portion. apparatus.   The multi-fuel use according to claim 1, further comprising a flame detector provided to be inclined with respect to an axis of the outer cylinder nozzle from the outside of the outer cylinder nozzle and capable of monitoring at least one flame of the gas burner nozzle. Burner device.

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