JP2011112344A - Burner device for multi-fuel - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a burner device for multi-fuel, capable of simultaneously burning a plurality of fuel gases having significantly different compositions, by a single burner. <P>SOLUTION: The burner includes an outer burner nozzle 15 and an inner burner nozzle 16, an introduction flow channel 25 formed between the inner burner nozzle and the outer burner nozzle, a plurality of rod-shaped gas burner nozzles 34 disposed inside of the inner burner nozzle, and a tertiary air introduction duct 26 disposed between the outer burner nozzle and the inner burner nozzle. A combustion air adjustment device has a first air adjustment section 8 and a second air adjustment section 9 received in a wind box 7, the first air adjustment section introduces the combustion air into the inner burner nozzle from the wind box through the tertiary air introduction duct, the second air adjustment section introduces the combustion air to a circumference of a tip section of the inner burner nozzle from the wind box, a second fuel gas 41 is supplied to the gas burner nozzles, and a first fuel gas 23 having calorie lower than that of the second fuel gas is supplied to the introduction flow channel. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a burner device for multiple fuels that enables simultaneous combustion of 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

  In view of such circumstances, the present invention provides a multi-fuel burner device capable of simultaneously burning a plurality of fuel gases having greatly different compositions with a single burner.

  The present invention comprises a burner and a combustion air adjusting device provided so as to surround the tip of the burner, the burner comprising an outer cylinder nozzle and an inner cylinder nozzle provided concentrically with the outer cylinder nozzle; An introduction flow path formed between the inner cylinder nozzle and the outer cylinder nozzle, a plurality of rod-shaped gas burner nozzles provided in parallel with the axis inside the inner cylinder nozzle, the outer cylinder nozzle, and the There is a tertiary air introduction duct that is provided between the inner cylinder nozzles in the radial direction and communicates the inside of the inner cylinder nozzle and the outside of the outer cylinder nozzle, and the combustion air adjusting device is housed in a wind box. An air adjusting unit and a second air adjusting unit, wherein the first air adjusting unit introduces combustion air from the wind box into the inner cylinder nozzle through the tertiary air introducing duct, and The air conditioning unit comes from the windbox Combustion air is introduced around the tip of the inner cylinder nozzle, a second fuel gas is supplied to the gas burner nozzle, and a first fuel gas having a lower calorie than the second fuel gas is supplied to the introduction flow path. The present invention relates to a multi-fuel burner device configured as described above.

  The present invention also relates to a multi-fuel burner device in which an oil burner is provided on the axial center of the inner cylinder nozzle, and the oil burner can advance and retreat in the axial direction of the oil burner.

  According to the present invention, the first air adjustment unit includes a slide damper that is slidably fitted to the outer cylinder nozzle, and the degree of opening of the tertiary air introduction duct is adjusted by sliding the slide damper. The present invention relates to a configured multi-fuel burner device.

  According to the present invention, the second air adjusting part has an internal window box that is housed in the window box and surrounds a tip portion of the outer cylinder nozzle, and a rear end surface of the internal window box extends along a circumference. The present invention relates to a multi-fuel burner apparatus configured such that openings are formed at predetermined intervals, and a rotary damper is rotatably provided on the rear end surface, and the degree of opening of the opening is adjusted by the rotation of the rotary damper. Is.

  According to the present invention, the first air adjustment unit includes a slide damper that is slidably fitted to the outer cylinder nozzle, and the degree of opening of the tertiary air introduction duct is adjusted by sliding the slide damper. The second air adjusting unit is housed in the window box and has an inner window box that surrounds a tip portion of the outer cylinder nozzle, and a rear end surface of the inner window box has a predetermined interval along a circumference. An opening is formed at the rear end surface, and a rotary damper is rotatably provided on the rear end face, and the opening degree of the opening is adjusted by the rotation of the rotary damper. It is.

  According to the present invention, the second air adjusting portion has a vane disposed at a predetermined interval around the tip of the outer cylinder nozzle. The secondary air is swirled by the vane, and the angle of the vane is adjusted. The present invention relates to a multi-fuel burner device configured to adjust the turning force.

  The present invention also relates to a multi-fuel burner device that is provided with a swirler having swirl vanes at the tip of the inner cylinder nozzle and configured to swirl the tertiary air.

  The present invention also relates to a multi-fuel burner device in which the swirler is attached to the oil burner, and the swirler can move forward and backward together with the oil burner.

  Furthermore, according to the present invention, the outer cylinder nozzle has a nozzle front end at the tip, and the nozzle front end has a plurality of concave grooves inclined toward the center at a position facing the gas burner nozzle. The present invention relates to a multi-fuel burner device in which the outlet of the introduction flow path is divided by a groove and a flow path for secondary air is formed.

  According to the present invention, a burner and a combustion air adjusting device provided so as to surround the tip of the burner are provided, and the burner is provided with an outer cylinder nozzle and an inner cylinder nozzle provided concentrically with the outer cylinder nozzle. An introduction flow path formed between the inner cylinder nozzle and the outer cylinder nozzle, a plurality of rod-shaped gas burner nozzles provided in the inner cylinder nozzle in parallel with the axis, and the outer cylinder nozzle And a tertiary air introduction duct provided in a radial direction between the inner cylinder nozzle and communicating the inside of the inner cylinder nozzle and the outside of the outer cylinder nozzle, and the combustion air adjusting device is accommodated in the wind box A first air adjusting unit and a second air adjusting unit, wherein the first air adjusting unit introduces combustion air into the inner cylinder nozzle from the wind box through the tertiary air introducing duct, The second air conditioning unit is the windbox Combustion air is introduced around the tip of the inner cylinder nozzle, a second fuel gas is supplied to the gas burner nozzle, and a first fuel gas lower in calorie than the second fuel gas is supplied to the introduction flow path. Therefore, the second fuel gas combusting in the center is less susceptible to disturbances, the auxiliary combustion action of the first fuel gas of the second fuel gas is stabilized, and the first fuel gas can be stably burned, Further, a plurality of fuel gases having different compositions can be burned by the same burner.

  According to the present invention, an oil burner is provided on the axial center of the inner cylinder nozzle, and the oil burner can advance and retreat in the axial center direction of the oil burner. The oil burner is prevented from being burned out by retreating.

  According to the present invention, the first air adjustment unit includes a slide damper that is slidably fitted to the outer cylinder nozzle, and an opening degree of the tertiary air introduction duct is adjusted by sliding of the slide damper. Therefore, it is possible to supply tertiary air optimal for combustion.

  According to the present invention, the second air adjusting part is housed in the window box and has an internal window box that surrounds a tip portion of the outer cylinder nozzle. The opening is formed at predetermined intervals along the rear end surface, and a rotary damper is rotatably provided on the rear end surface. The opening degree of the opening is adjusted by the rotation of the rotary damper. Secondary air can be supplied.

  According to the present invention, the first air adjustment unit includes a slide damper that is slidably fitted to the outer cylinder nozzle, and an opening degree of the tertiary air introduction duct is adjusted by sliding of the slide damper. The second air adjustment unit is housed in the wind box and has an internal window box that surrounds a tip portion of the outer cylinder nozzle. A rear end surface of the internal wind box extends along a circumference. Openings are formed at predetermined intervals, and a rotary damper is rotatably provided on the rear end surface, and the opening degree of the opening is adjusted by rotation of the rotary damper. The flow rate of the tertiary air can be adjusted independently, and a plurality of fuel gases having different compositions can be burned in an optimum state.

  Further, according to the present invention, the second air adjusting portion has vanes arranged at predetermined intervals around the outer cylinder nozzle tip, and the secondary air is swirled by the vanes and the angle of the vane Since the turning force is adjusted by the adjustment, mixing of the secondary air and the fuel gas is promoted, and combustion is promoted.

  According to the present invention, a swirler having a swirl vane is provided at the tip of the inner cylinder nozzle, and the swirl is provided to the tertiary air, so that mixing of the tertiary air and the fuel gas is promoted, Combustibility is improved.

  Further, according to the present invention, the swirler is attached to the oil burner, and the swirler can advance and retreat integrally with the oil burner. Therefore, the swirler is prevented from burning by retreating the swirler.

  According to the invention, the outer cylinder nozzle has a nozzle front end at the tip, and the nozzle front end has a plurality of concave grooves inclined toward the center at a position facing the gas burner nozzle, Since the outflow port of the introduction flow path is divided by the concave groove and the flow path of the secondary air is formed, the mixing of the secondary air and the first fuel gas is promoted, and the combustibility is improved. Show the effect.

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 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 facing the throat 4 is a front plate 12, which is insulated to block radiant heat from the throat 4 and to insulate the wind box 7 from high-temperature air. A 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 and an inner cylinder nozzle 16, and the outer cylinder nozzle 15 has a two-part structure of a nozzle front end portion 17 and an outer cylinder nozzle body 18, and the nozzle front end portion 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.

  The tip of the second gas burner nozzle 34 reaches the throat 4 and the tip has a shape cut obliquely. The slope of the tip has a required number, for example, 5 to 8 gas ejection holes (not shown). Are drilled 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 the flame is stabilized by intersecting the flames.

  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 to the ring header 38 from the second fuel gas source, and the second nozzle gas pipes 36 are secondly supplied from the ring header 38 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, 58 is a clinker monitoring window, 59 in FIG. 3 is a flame detector which is directed in the direction of the flame and detects or monitors the state of the flame by infrared rays, and 60 is a fuel detector at start-up. An ignition torch for igniting, and 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 is provided with an ignition electrode for emitting sparks or the like to the ignition fuel. When ignited, a flame is jetted toward the throat 4.

  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. 6 and 7, the nozzle front end portion 17 is formed with a concave groove 85 inclined from the outer peripheral surface toward the axial center side at a position corresponding to the second gas burner nozzle 34, and the concave groove 85 and the 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. 8 and 9, 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 the 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. Therefore, 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 Connection hole 44 Cooling air 45 Oil burner 48 Connection pipe 49 Swirler 50 Seal gas 53 Air cylinder 63 Slide damper 65 Slide drive part 72 Secondary air introduction space 73 Internal wind box 75 convex portion 79 vane 82 vane drive mode Motor 85 groove 87 discharge ports 101 rotary input unit 106 secondary air 107 tertiary air

Claims (9)

  A burner and a combustion air adjusting device provided so as to surround the tip of the burner, the burner comprising an outer cylinder nozzle, an inner cylinder nozzle provided concentrically with the outer cylinder nozzle, and the inner cylinder nozzle Between the outer cylinder nozzle and the inner cylinder nozzle, an introduction flow path formed between the outer cylinder nozzle and the inner cylinder nozzle, a plurality of rod-shaped gas burner nozzles provided in the inner cylinder nozzle in parallel with the axis, A tertiary air introduction duct that is provided in a radial direction and communicates the inside of the inner cylinder nozzle and the outside of the outer cylinder nozzle, and the combustion air adjustment device includes a first air adjustment unit housed in a wind box; A second air adjusting unit, wherein the first air adjusting unit introduces combustion air from the wind box through the tertiary air introduction duct into the inner cylinder nozzle, and the second air adjusting unit From the windbox to the inner cylinder Combustion air is introduced around the front end of the fuel gas, the second fuel gas is supplied to the gas burner nozzle, and the first fuel gas having a lower calorie than the second fuel gas is supplied to the introduction flow path. A burner device for multiple fuels.   2. The multi-fuel burner device according to claim 1, wherein an oil burner is provided on an axial center of the inner cylinder nozzle, and the oil burner can advance and retreat in an axial direction of the oil burner.   2. The first air adjustment unit includes a slide damper that is slidably fitted to the outer cylinder nozzle so that the opening degree of the tertiary air introduction duct is adjusted by sliding the slide damper. Multi-fuel burner device.   The second air adjusting unit is housed in the window box and has an internal window box surrounding a tip portion of the outer cylinder nozzle. Opening portions at predetermined intervals along the circumference of the rear end surface of the internal window box The multi-fuel burner device according to claim 1, wherein a rotary damper is rotatably provided on the rear end surface, and the degree of opening of the opening is adjusted by the rotation of the rotary damper.   The first air adjustment unit includes a slide damper that is slidably fitted to the outer cylinder nozzle, and is configured to adjust an opening degree of the tertiary air introduction duct by sliding of the slide damper. 2 The air adjustment part is housed in the window box and has an internal window box surrounding the tip portion of the outer cylinder nozzle, and openings are formed at predetermined intervals along the circumference on the rear end surface of the internal window box The multi-fuel burner apparatus according to claim 1, wherein a rotary damper is rotatably provided on the rear end surface, and the opening degree of the opening is adjusted by the rotation of the rotary damper.   The second air adjusting unit has vanes arranged at predetermined intervals around the outer nozzle end portion, and the secondary air is swirled by the vane and the turning force is adjusted by adjusting the angle of the vane. The multi-fuel burner device according to claim 1 configured as described above.   The multi-fuel burner device according to claim 1, wherein a swirler having swirl vanes is provided at a tip of the inner cylinder nozzle, and the swirl is provided to the tertiary air.   The multi-fuel burner device according to claim 7, wherein the swirler is attached to the oil burner, and the swirler can advance and retreat integrally with the oil burner.   The outer cylinder nozzle has a nozzle front end portion at a tip portion, and the nozzle front end portion has a plurality of concave grooves inclined toward the center at a position facing the gas burner nozzle, and the introduction flow path is formed by the concave grooves. The multi-fuel burner device according to claim 1, wherein the outlet of the fuel is divided and a flow path for secondary air is formed.

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