JP2014137148A - Cyclone burner - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a cyclone burner that can stably burn the burning materials with variations in sizes and types of combustible materials.SOLUTION: A cyclone burner 1 comprises: a cylindrical part 11 of a burner casing 10 comprising an air fuel supply port 13 where a primary combustion air and burning materials are led, and first to third air inlets 141, 142, 143, and first to third thermometers 51, 52, 53; and a truncated cone shape part 12 of the burner casing comprising fourth and fifth air ducts 144, 145, and fourth and fifth thermometers 54, 55. A controller outputs control signals P1, P2, P3, P4, P5 to dampers 41-45 based on the temperature detected by the first to fifth thermometers 51-55, and adjusts opening degrees of the dampers 41-45. Further, the controller adjusts a volume of a secondary combustion air blowing to a first combustion chamber R1 from the first to fifth air inlets 141-145, and controls so that the detection temperature of the first to fifth thermometers 51-55 becomes a predetermined temperature.

Description

  The present invention relates to a cyclone burner capable of continuously burning a workpiece.

  Conventionally, a cyclone burner is known as a burner for burning pulverized coal. The cyclone burner for pulverized coal is formed of a cylindrical part to which combustion air and fuel are supplied in a tangential direction, and a truncated cone-shaped part that is connected to one end of the cylindrical part and decreases in diameter toward the tip side. There are some which have a hollow chamber, an exhaust tube which is arranged inside the cylindrical portion and opens into the hollow chamber, and a nozzle portion which is connected to the combustion furnace connected to the tip of the hollow chamber. In this type of cyclone burner, fuel pulverized coal is transported to the cylindrical part by combustion air, and pulverized coal is separated as the pulverized coal and combustion air swirl through the hollow chamber, while excess combustion air is discharged. The pulverized coal separated and discharged from the cylinder to the outside and the remaining combustion air are supplied to the combustion furnace and burned in the combustion furnace (see, for example, Patent Document 1).

  The cyclone burner described in Patent Document 1 has a sleeve formed so as to be able to advance and retreat from the hollow chamber toward the nozzle portion, and the sleeve is used when the ratio of combustion air supplied to the hollow chamber is large. It is formed so as to increase the resistance of the combustion air passing through the nozzle portion by being inserted into the portion. Thereby, the quantity of the combustion air supplied to a combustion furnace from a nozzle part is reduced, and it is comprised so that the air fuel ratio which is the ratio of the combustion air with respect to a fuel may be reduced.

JP 05-118511 A

  By the way, the cyclone burner has an application for burning granular substances other than pulverized coal. For example, when waste such as crushed municipal waste or dry powder of organic sludge is burned with a cyclone burner, the ignition temperature and calorific value of the combusted material will vary depending on the pulverized coal. There is a greater variation than. Therefore, when the cyclone burner of Patent Document 1 is used for fueling particulate matter other than pulverized coal, the combustion temperature is too low to cause incomplete combustion, or the combustion temperature is too high and the cyclone burner is damaged. There is an inconvenience and an inconvenience that the combustion temperature becomes unstable.

  Then, the subject of this invention is providing the cyclone burner which can burn a to-be-combusted object stably.

In order to solve the above-described problems, a cyclone burner according to the present invention has a cylindrical portion and a truncated cone-shaped portion that is continuous with the cylindrical portion and has a diameter that decreases toward the distal end side. A casing formed with,
An exhaust pipe having an opening communicating with the first combustion chamber at the tip and disposed coaxially with the casing;
An air / fuel supply unit that is provided in the cylindrical part of the casing and supplies a mixture of the combustible and the primary combustion air in a tangential direction of the cylindrical part;
An ignition part provided in the cylindrical part of the casing;
A thermometer that is provided on at least one side surface of the cylindrical portion of the casing and the truncated cone-shaped portion, and measures the temperature in the first combustion chamber;
At least one side surface of the cylindrical portion of the casing and the truncated cone-shaped portion is provided at the same axial position as the axial position where the thermometer is provided, and the secondary combustion air is supplied into the first combustion chamber. A secondary combustion air supply unit;
The secondary combustion air supply unit includes a combustion air control unit that controls the amount of secondary combustion air supplied into the first combustion chamber based on the temperature measured by the thermometer.

  According to the above configuration, the combustion object and the primary combustion air are supplied to the cylindrical portion of the casing in the tangential direction by the air / fuel supply portion, and thereby the turning toward the tip of the truncated cone shape portion from the cylindrical portion of the casing. A flow is formed in the first combustion chamber. When the temperature in the first combustion chamber rises to the ignition temperature by the ignition unit, the combustible supplied together with the primary combustion air burns in the first combustion chamber. The combustible is combusted in a process of swirling in the first combustion chamber from the cylindrical part of the casing toward the tip of the truncated cone part. Here, if there is variation in the type and size of the combusted material, the combustible material is easily combusted and the amount of generated heat varies, and as a result, the combustion temperature distribution in the first combustion chamber varies. Therefore, the temperature in the first combustion chamber is measured by a thermometer provided on at least one side surface of the cylindrical portion and the truncated cone shape portion of the casing, and the temperature in the first combustion chamber measured by the thermometer is measured. The amount of secondary combustion air supplied by the secondary combustion air supply unit provided at the same axial position as the thermometer is controlled by the combustion air control unit. For example, when the temperature measured by the thermometer is higher than a predetermined reference value, the amount of secondary combustion air is increased, and when the temperature measured by the thermometer is lower than the predetermined reference value, the secondary combustion air is increased. Reduce the amount of. Thereby, since the temperature in the first combustion chamber is stably maintained at a predetermined temperature, a cyclone burner that generates stable combustion heat can be obtained even if there are variations in the type and size of the combusted material. .

  In the cyclone burner according to an embodiment, a plurality of the thermometers are provided in the cylindrical part of the casing, and a plurality of the secondary combustion air supply parts are provided in the cylindrical part of the casing. .

  According to the above embodiment, the temperatures at the plurality of positions of the first combustion chamber corresponding to the cylindrical portion of the casing are measured with a plurality of thermometers, and a plurality of temperatures are measured based on the temperatures measured with these thermometers. The amount of secondary combustion air supplied to a plurality of positions of the cylindrical portion of the casing is controlled by the secondary combustion air supply unit. Therefore, the combustion temperature of the first combustion chamber corresponding to the cylindrical portion of the casing is stably maintained at a predetermined temperature.

  In the cyclone burner according to an embodiment, a plurality of the thermometers are provided in the truncated cone shape part of the casing, and a plurality of the secondary combustion air supply parts are provided in the truncated cone shape part of the casing. ing.

  According to the above embodiment, the temperature at the plurality of positions of the first combustion chamber corresponding to the truncated cone shape portion of the casing is measured with a plurality of thermometers, and a plurality of temperatures are measured based on the temperatures measured with these thermometers. The amount of secondary combustion air supplied to a plurality of positions of the truncated cone shape portion of the casing is controlled by the secondary combustion air supply portion. Therefore, the combustion temperature of the first combustion chamber corresponding to the truncated cone portion of the casing is stably maintained at a predetermined temperature.

  The cyclone burner according to an embodiment is connected to the first combustion chamber in the casing, separated by the swirl flow formed in the casing, and guided to the burned matter remaining without being burned in the first combustion chamber, A second combustion chamber for combusting the combustible is provided.

  According to the above-described embodiment, the combustion target that remains without being burned in the first combustion chamber is separated by the swirl flow formed in the casing, and is guided to the second combustion chamber for combustion. Therefore, it is possible to effectively burn the combustion object remaining without burning in the first combustion chamber, and to improve the combustion efficiency of the cyclone burner.

  A cyclone burner according to an embodiment includes a transport unit that is connected to a tip of a truncated cone-shaped portion of the casing and transports the remaining combusted material, and the second combustion chamber is formed inside the transport unit. Yes.

  According to the above embodiment, in addition to the remaining combustibles, the conveying means essential for the burner for discharging ash and incombustibles from the first combustion chamber is also used as the second combustion chamber. Thereby, the combustion efficiency of a to-be-combusted object can be improved, without making an apparatus structure large-scale. Therefore, a compact cyclone burner with high combustion efficiency can be obtained despite burning combustibles whose sizes and combustion substances vary. In addition, a screw conveyor, a closed chain conveyor, etc. are employable as a conveyance means.

In one embodiment, the cyclone burner is a screw conveyor having a conveying casing and a conveying screw rotatably accommodated in the conveying casing.
The second combustion chamber is formed in a transfer space formed between the transfer casing and the transfer screw of the screw conveyor.

  According to the above embodiment, the conveyance space between the conveyance casing and the conveyance screw of the screw conveyor can relatively easily partition the gas flow in the axial direction. The second combustion chamber can be formed easily sealed.

  In the cyclone burner according to an embodiment, the transport unit includes a tertiary combustion air supply unit that supplies tertiary combustion air to the second combustion chamber.

  According to the above embodiment, since the tertiary combustion air is supplied to the second combustion chamber of the transport means by the tertiary combustion air supply unit, the combusted material guided without being combusted in the first combustion chamber is transported. However, it can be burned effectively in the second combustion chamber.

In one embodiment of the cyclone burner, the conveying means is
A second combustion chamber thermometer for measuring the temperature in the second combustion chamber;
A tertiary combustion air control unit that controls the amount of tertiary combustion air supplied to the second combustion chamber by the tertiary combustion air supply unit based on the temperature measured by the second combustion chamber thermometer; .

  According to the above embodiment, the temperature of the second combustion chamber is measured by the second combustion chamber thermometer, and the tertiary combustion air supplied to the second combustion chamber by the tertiary combustion air supply unit based on the measured temperature. Since the amount of combustion air is controlled by the tertiary combustion air control unit, the temperature of the second combustion chamber is maintained at a predetermined temperature. Therefore, it is possible to stably burn the combustion object remaining without burning in the first combustion chamber.

  In one embodiment, the cyclone burner includes a cooling unit in which the transport unit is installed so as to surround the second combustion chamber and to which a cooling medium is supplied.

  According to the above embodiment, the temperature in the second combustion chamber is lowered by the cooling medium supplied to the cooling unit of the conveying means. Therefore, it is possible to prevent the inconvenience that the parts constituting the conveying means deteriorate at an excessive temperature.

The cyclone burner of one embodiment is
The temperature of the first combustion chamber is set to 750 ° C. or more and 850 ° C. or less by controlling the amount of the mixture supplied by the air / fuel supply unit and the amount of secondary combustion air supplied by the secondary combustion air supply unit. Control and
The tertiary combustion air control unit controls the amount of tertiary combustion air supplied to the second combustion chamber through the tertiary combustion air supply unit to control the temperature of the second combustion chamber to 500 ° C. or more and 600 ° C. or less. To do.

  According to the above embodiment, the temperature of the first combustion chamber is controlled to be 750 ° C. or higher and 850 ° C. or lower so that the chlorine component contained in the combusted material is completely burned to prevent generation of dioxins, and Can be efficiently burned. Further, by controlling the temperature of the second combustion chamber to 500 ° C. or more and 600 ° C. or less, it is possible to effectively burn a relatively small amount of the combusted material remaining without being burned in the first combustion chamber. Here, the combustion object led to the second combustion chamber has a temperature of 500 ° C. or higher and 600 ° C. or lower because it is substantially unnecessary to prevent the generation of dioxins because the chlorine component is completely burned in the first combustion chamber. Can be set to

  In the cyclone burner according to an embodiment, the combustible includes at least one of dry sludge powder and waste crushed pieces.

  According to the above embodiment, the sludge dry powder and waste fragments that are to be combusted contain various types of substances compared to pulverized coal, and there are variations in size and distribution of combustion substances. The cyclone burner according to the present invention can stably maintain the temperature of the first combustion chamber at a predetermined temperature in spite of the large variation in ignition temperature and calorific value compared to pulverized coal. The generated combustion heat can be generated. Here, organic sludge such as sewage sludge, septic tank sludge and activated sludge corresponds to the sludge. The above-mentioned waste includes all organic waste such as food residue, agricultural waste, waste plastic, paper waste and wood waste, livestock manure and the like.

It is a mimetic diagram showing the boiler device using the cyclone burner of an embodiment. It is a schematic cross section which shows the cyclone burner of embodiment. It is a schematic cross section which shows the cut surface of the axis orthogonal direction in the cylindrical part of a burner casing. It is a schematic cross section which shows the cut surface in the truncated cone shape part side rather than FIG. 3 of the cylindrical part of a burner casing.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the accompanying drawings.

  FIG. 1 is a schematic diagram showing a boiler apparatus using a cyclone burner according to an embodiment of the present invention. As shown in FIG. 1, this boiler apparatus stores a cyclone burner 1, a fixed quantity feeder 3 that stores the burned substance of the cyclone burner 1 and sends out a predetermined amount, and a burned substance discharged from the fixed quantity feeder 3. A first blower 5 that is transported to the cyclone burner 1 and supplies primary combustion air, a secondary combustion air that is supplied to the cyclone burner 1, and a tertiary combustion air that is supplied to the screw conveyor 2 of the cyclone burner 1 are generated. The second blower 6 and the heat exchanger 4 that generates the hot water or steam through the combustion gas of the cyclone burner 1 are generally configured.

  FIG. 2 is a schematic cross-sectional view showing the cyclone burner 1. As shown in FIG. 2, the cyclone burner 1 includes a burner casing 10 having a cylindrical portion 11, a truncated cone-shaped portion 12 that is continuous with the cylindrical portion 11 and has a diameter that decreases toward the distal end side, and the burner An exhaust pipe 19 arranged coaxially inside the cylindrical part 11 of the casing 10 and a screw conveyor 2 connected to the tip of the frustoconical part 12 of the burner casing 10 are provided.

  The burner casing 10 is formed by arranging a heat insulating material and a refractory material inside a heat resistant steel. As the heat insulating material, a heat insulating board formed of calcium silicate or the like can be used, and as the refractory material, a refractory brick or a castable refractory can be used. A first combustion chamber R <b> 1 is formed inside the cylindrical portion 11 and the truncated cone shape portion 12 of the burner casing 10.

  The cylindrical portion 11 of the burner casing 10 has an air / fuel supply port 13 as an air / fuel supply portion through which primary combustion air and an object to be burned are guided, and a first combustion chamber at the same axial position as the air / fuel supply port 13. A supply thermometer 50 for measuring the temperature of R1 is provided. The signal from the supply unit thermometer 50 is input to the controller 30 described later.

  Further, in the cylindrical portion 11 of the burner casing 10, first to third air supply ports 141 as secondary combustion air supply portions arranged at different positions in the axial direction in order from the side closer to the air fuel supply port 13. , 142, 143 are provided. Further, the cylindrical portion 11 of the burner casing 10 is disposed at the same axial position as the first to third air supply ports 141, 142, 143 and corresponds to the cylindrical portion 11 of the first combustion chamber R1. First to third thermometers 51, 52, and 53 for measuring the temperature are provided. Signals from the first to third thermometers 51, 52, and 53 are input to the controller 30. The first to third air supply ports 141, 142, and 143 are connected to pipes connected to the outlet of the second blower 6, and these pipes are connected to the first to third air supply ports 141, 142, and 143, respectively. Dampers 41, 42 and 43 are provided for adjusting the amount of secondary combustion air supplied. The dampers 41, 42 and 43 are operated by receiving control signals P 1, P 2 and P 3 from the controller 30, and the opening degree is controlled by the controller 30. The number of air supply ports and thermometers installed in the cylindrical portion 11 of the burner casing 10 may be other than three.

  Further, the cylindrical portion 11 of the burner casing 10 is provided with a flame port 15 on the opposite side of the air-fuel supply port 13 with respect to the central axis, and the flame burner 15 is provided with an activation burner 17 as an ignition unit. Yes. The outlet of the start burner 17 is provided with an opening / closing valve 18 that opens when the start burner 17 is activated and closes when the start burner 17 is stopped. An air supply port 16 through which the temperature adjustment air is guided from the second blower 6 is provided at the side of the flame port 15. A pipe for supplying temperature adjustment air to the air supply port 16 is provided with a damper 46 for adjusting the amount of the temperature adjustment air. The damper 46 operates in response to a drive signal P6 from the controller 30 and the opening degree is controlled by the controller 30. The start burner 17 has a blower blade that blows combustion air and a fuel injection nozzle provided on the downstream side of the blower blade. A motor that rotationally drives the blower blade includes an inverter 64 that is controlled by a controller 30. Power is supplied. The fuel injection nozzle is connected to a fuel tank 8 for storing kerosene, and a fuel valve 40 for adjusting the flow rate of kerosene is provided in a fuel pipe connecting the fuel tank 8 and the fuel injection nozzle. The fuel valve 40 operates by receiving a drive signal V from the controller 30, and the opening degree is controlled by the controller 30. The controller 30 outputs a control signal C4 to the inverter 64 to control the rotational speed of the blower blades, and outputs a drive signal V to the fuel valve 40 to control the flow rate of kerosene to be sent to the fuel injection nozzle. 17 is activated. Thereby, mist kerosene is mixed and burned with the combustion air blown out by the blower blades, and a flame caused by the burning of the kerosene is radiated to the first combustion chamber R1, and the cyclone burner 1 is started up in the first combustion chamber R1. Increase the temperature to the combustion temperature of the combustible.

  FIG. 3 is a schematic cross-sectional view showing a cut surface in a direction perpendicular to the axis of the cylindrical portion 11 of the burner casing 10. As shown in FIG. 3, the air / fuel supply port 13 provided in the tubular portion 11 faces the tangential direction of the tubular portion 11 having a circular cross section. As a result, the primary combustion air and the combusted material supplied from the air / fuel supply port 13 form a swirling flow in the cylindrical portion 11. This swirling flow flows from the cylindrical portion 11 toward the truncated cone shape portion 12, the flow velocity increases at the truncated cone shape portion 12, and solids such as unburned combustibles and incombustible materials are separated by centrifugal force. Moreover, the flame port 15 provided in the symmetrical position of the point which passes the axis | shaft and the air fuel supply port 13 of the cylindrical part 11 has faced the tangential direction of the cylindrical part 11 which has a circular cross section. Thereby, the flame supplied from the flame port 15 forms a swirling flow in the cylindrical portion 11.

  4 is a diagram showing a cut surface of the cylindrical portion 11 of the burner casing 10, and is a schematic cross-sectional view showing a cut surface on the truncated cone-shaped portion 12 side with respect to the cut surface of FIG. As shown in FIG. 4, the 1st air supply port 141 provided in the cylindrical part 11 has faced the tangential direction of the cylindrical part 11 which has a circular cross section. Thus, the secondary combustion air supplied from the first air supply port 141 is formed so as to easily join the swirl flow formed in the cylindrical portion 11 by the primary combustion air from the air fuel supply port 13. Yes. Similarly, the second and third air supply ports 142 and 143 are also provided so as to face the tangential direction of the tubular portion 11. Similarly, fourth and fifth air supply ports 144 and 145, which will be described later, are also installed facing the tangential direction of the truncated cone-shaped portion 12 having a circular cross section.

  The frustoconical portion 12 of the burner casing 10 is provided with fourth and fifth air supply pipes 144 and 145 as secondary combustion air supply parts arranged at different positions in the axial direction in order from the side closer to the supply pipe 13. It has been. Further, the frustoconical portion 12 of the burner casing 10 is disposed at the same axial position as the fourth and fifth supply pipes 144 and 145 and corresponds to the frustoconical portion 12 of the first combustion chamber R1. Fourth and fifth thermometers 54 and 55 for measuring the temperature are provided. Signals from the fourth and fifth thermometers 54 and 55 are input to the controller 30. The fourth and fifth air supply ports 144 and 145 are connected to a pipe connected to the outlet of the second blower 6, and this pipe is supplied to the fourth and fifth air supply ports 144 and 145 2. Dampers 44 and 45 for adjusting the amount of the next combustion air are provided. The dampers 44 and 45 operate by receiving drive signals P4 and P5 from the controller 30, and the opening degree is controlled by the controller 30. The number of air supply ports and thermometers installed in the truncated cone shape portion 12 of the burner casing 10 may be other than two.

  The flow rate of the combustion air supplied to the first to fifth air supply pipes 141, 142, 143, 144, 145 and the air supply port 16 may be adjusted by a flow rate adjusting valve other than the damper.

  The exhaust cylinder 19 is a tubular member made of heat-resistant steel, and is fixed through the ceiling surface of the cylindrical portion 11 of the burner casing 10. The lower end of the exhaust cylinder 19 is opened at a position slightly above the boundary between the cylindrical portion 11 and the truncated cone shape portion 12 in the axial direction. A first combustion gas pipe X1 that guides combustion gas to the heat exchanger 4 is connected to the upper end of the exhaust cylinder 19.

  The screw conveyor 2 includes a cylindrical conveyance casing 21, a jacket casing 22 that surrounds the outside of the conveyance casing 21, a conveyance screw 23 that is rotatably accommodated inside the conveyance casing 21, and a motor that rotationally drives the conveyance screw 23. It is roughly composed of M1. A communication hole that is continuous with the lower end of the first combustion chamber R1 is formed in the upper part on the one end side of the transfer casing 21, and from this communication hole, the combustion object that remains without being burned in the first combustion chamber R1, The ash of the combusted material and the incombustible material contained in the combusted material are put into the transport casing 21. These combustibles and the like are transported to the other end side by a transport space formed between the transport casing 21 and the transport screw 23, and are discharged from a discharge port 24 provided on the other end side of the transport casing 21. A rotary valve 25 is provided at the discharge port 24 of the screw conveyor 2 so as to hold the air pressure inside the burner casing 10 and the conveying casing 21. A cooling chamber 20 is formed between the transfer casing 21 and the jacket casing 22, and water as a cooling medium is supplied to the cooling chamber 20 from a water supply port 26 provided on one end side of the jacket casing 22 to cool the transfer space. A cooling jacket is formed. Water as a cooling medium is supplied to the cooling chamber 20 by a water supply pump 9 connected upstream of a water supply pipe connected to the water supply port 26. The water that has cooled the transfer space is discharged from a drain port 27 provided on the other end side of the jacket casing 22 as indicated by an arrow W.

  A conveyor air supply port 28 for supplying tertiary combustion air is provided at a position facing the communication hole with the first combustion chamber R <b> 1 of the transfer casing 21, and the conveyor air supply port 28 has the second air blower 6. A pipe connected to the outlet is connected. A pipe connected to the air supply port 28 is provided with a damper 47 that adjusts the amount of tertiary combustion air supplied to the conveyor air supply port 28. The damper 47 operates by receiving a drive signal P7 from the controller 30, and the opening degree is controlled by the controller 30. The flow rate of the combustion air supplied to the air supply port 28 may be adjusted by a flow rate adjusting valve other than the damper. The other end side of the communicating hole with the first combustion chamber R1 of the conveying casing 21 is on the same side as the side where the communicating hole is formed, and on the opposite side to the conveyor air inlet 28 with respect to the central axis of the conveying casing 2. A gas discharge port 29 for discharging the gas in the transport casing 2 is provided. A second combustion chamber R <b> 2 for burning the combusted material to be conveyed is formed in a portion between the conveyor air supply port 28 and the gas discharge port 29 in the conveyance space of the screw conveyor 2. The second combustion chamber R2 is provided with a sixth thermometer 56 for measuring the temperature in the second combustion chamber R2. The signal from the sixth thermometer 56 is input to the controller 30. A second combustion gas pipe X <b> 2 that guides the combustion gas to the heat exchanger 4 is connected to the gas discharge port 29.

  The fixed-quantity feeder 3 is loaded with a combusted material, a storage hopper 31 that stores the input combusted material, a screw conveyor 32 that discharges the combusted material from the lower end of the storage hopper 31, and a bottom surface of the storage hopper 31. It has the stirring blade 33 which is arrange | positioned and stirs a to-be-combusted material. The discharge port of the screw conveyor 32 is connected via a rotary valve 34 to a transport pipe F1 that transports the combusted material. The upstream end of the transport pipe F <b> 1 is connected to the outlet of the first blower 5. The conveying screw of the screw conveyor 32 is rotationally driven by a motor M2, and electric power to the motor M2 is supplied by an inverter 63 controlled by the controller 30.

  The storage hopper 31 of the quantitative feeder 3 is charged with a mixture of crushed waste obtained by crushing waste and dried sludge as combustibles. The crushing waste is obtained by crushing waste plastic, paper waste and wood waste as waste into a size of 1 mm to 20 mm square by a crusher. As waste, any one or more of waste plastic, paper waste, and wood waste may be used, or organic solids such as food residues and agricultural waste may be used. The dried sludge is obtained by drying sewage sludge, and may be organic sludge such as septic tank sludge and activated sludge, or inorganic sludge discharged from construction sludge, mines, quarries and the like.

  The first blower 5 is a pusher blower for supplying primary combustion air toward the air / fuel supply port 13 of the burner casing 10 and for transporting combustibles by the flow of the primary combustion air. The first blower 5 is a turbofan type blower in which the outlet angle of the blower blade is formed to be 90 ° or less, and the motor that rotationally drives the blower blade is supplied with electric power by the inverter 61 controlled by the controller 30. . The transport pipe F1 connected to the outlet of the first blower 5 is connected to the rotary valve 34 provided at the outlet of the screw conveyor 32 of the fixed quantity feeder 3 on the downstream side of the first blower 5, and is the most downstream end. Is connected to the air / fuel supply port 13 of the burner casing 10.

  The second blower 6 supplies secondary combustion air toward the first to fifth air supply ports 141, 142, 143, 144, and 145 of the cyclone burner 1, and supplies air to the flame port 15 of the cyclone burner 1 at startup. This is a forced air blower for supplying temperature-controlled air to the port 16 and supplying tertiary combustion air to the conveyor air supply port 28 of the screw conveyor 2 of the cyclone burner 1. The second blower 6 is a turbofan blower similar to the first blower, and the motor that rotationally drives the blower blades is supplied with electric power by the inverter 62 controlled by the controller 30. The blower pipe F2 connected to the outlet of the second blower 6 is connected to the blower branch pipe F21 on the burner casing 10 side of the cyclone burner 1 and the blower branch pipe F22 connected to the conveyor air inlet 28 of the screw conveyor 2. Divided. In the blower branch pipe F21 on the burner casing 10 side, the branch pipes connected to the first to fifth air supply ports 141, 142, 143, 144, and 145 branch off, and the pipe remaining in the most downstream is the flame outlet 15. The air supply port 16 is connected.

  The first and second blowers 5 and 6 may be other blowers such as a plate fan and an axial fan.

  The heat exchanger 4 is one in which the combustion gas and water of the cyclone burner 1 are guided, and hot water or steam is generated by exchanging heat between the high temperature combustion gas and low temperature water. As the heat exchanger 4, various types such as a multi-tube cylindrical heat exchanger, a double tube heat exchanger, a single tube heat exchanger, a plate heat exchanger, and a steam boiler may be adopted. it can.

  The controller 30 is an electronic device composed of a CPU, a memory, and the like, and controls the operation of the cyclone burner 1 by executing a program stored in advance in the memory.

  The boiler apparatus provided with the cyclone burner 1 having the above-described configuration operates as follows.

  First, an operation unit (not shown) connected to the controller 30 is operated, and an input for instructing activation of the boiler device is performed. Upon receiving an input of the start command, the controller 30 outputs the drive signal V to the fuel valve 40 to open the fuel valve 40, supply kerosene to the start burner 17, and control signal C4 to the inverter 64 of the start burner 17. Is output to start the blower blade, and the combustion operation of the start burner 17 is started. The start burner 17 radiates a flame into the first combustion chamber R1 through the flame port 15, and thereby the temperature in the first combustion chamber R1 rises. Here, the controller 30 controls the flow rate of the temperature adjustment air supplied to the flame opening 15 based on the temperature detected by the supply portion thermometer 50 of the tubular portion 11 of the first combustion chamber R1. That is, the controller 30 outputs the control signal C2 to the inverter 62 to operate the second blower 6, and supplies temperature-adjusted air toward the flame opening 15 through the blower branch pipe F21. Further, the controller 30 outputs a drive signal P6 to the damper 46 to adjust the opening degree of the damper 46, and to control the flow rate of the temperature adjustment air so that the temperature of the flame radiated from the flame port 15 is a predetermined set temperature. Control to be Here, the temperature of the flame discharged from the flame port 15 is preferably set to 550 ° C. or higher and 650 ° C. or lower, more preferably 600 ° C.

  When the controller 30 detects that the temperature in the first combustion chamber R1 has risen to a predetermined ignition temperature based on the temperature signal T0 output from the supply portion thermometer 50 of the cylindrical portion 11 of the first combustion chamber R1, Supply of the combusted material and the primary combustion air to the first combustion chamber R1 is started. That is, the controller 30 outputs a control signal C3 to the inverter 63 to operate the motor M2 of the screw conveyor 32 at a predetermined rotational speed, and the amount of combustibles in the storage hopper 31 of the quantitative feeder 3 is determined to a predetermined amount per time. Is supplied to the transport pipe F1. At the same time, the controller 30 outputs a control signal C1 to the inverter 61 to operate the blower blades of the first blower 5 at a predetermined rotational speed, and supplies a predetermined flow rate of air to the transport pipe F3. As a result, the combusted material is transported through the transport pipe F3, and a predetermined amount of combusted material and a predetermined flow rate of primary combustion air are supplied from the air / fuel supply port 13 into the first combustion chamber R1. Here, the amount of primary combustion air that conveys the combusted material to the air / fuel supply port 13 through the conveying pipe F3 is preferably set to 25% or more and 35% or less of the total air amount, and particularly preferably 30%. It is. The cyclone burner 1 according to the present embodiment maintains the first combustion chamber R1 at a combustion temperature of 750 ° C. or higher and 850 ° C. or lower to completely burn the burned object, and is 2.5 times the theoretical air amount of the burned object. It is preferable to supply the combustion air in an amount of 3.0 times or less as the entire air amount.

  The controller 30 starts the supply of the combusted material and the primary combustion air to the first combustion chamber R1, and to the first combustion chamber R1 through the first to fifth air supply ports 141, 142, 143, 144, and 145. The supply of secondary combustion air is started. That is, the controller 30 outputs the control signal C2 to the inverter 62 to increase the air flow rate of the second blower 6, and the first to fifth air supply ports 141, 142, 143, 144, via the air supply branch pipe F21. Combustion air is supplied toward 145. The controller 30 outputs control signals P1, P2, P3, P4, and P5 to the dampers 41, 42, 43, 44, and 45 to adjust the opening degree of the dampers 41, 42, 43, 44, and 45, and The flow rate of the secondary combustion air supplied to 1 combustion chamber R1 is controlled. Here, the amount of secondary combustion air supplied from the blower branch pipe F21 to the first combustion chamber R1 through the first to fifth air supply ports 141, 142, 143, 144, 145 is 65% or more of the total air amount. It is preferably set to 75% or less, particularly preferably 70%. The amount of the secondary combustion air is set to be 100% of the total air amount when the amount of the primary combustion air is summed up. As described above, when the cyclone burner 1 is started, the controller 30 first sets 25% to 35% of the total air amount as the primary combustion air with respect to the combusted material supplied from the air / fuel supply port 13. While supplying to combustion chamber R1, 65% or more and 75% or less of the whole air quantity is supplied to 1st combustion chamber R1 as secondary combustion air. When the cyclone burner 1 is started, the opening degree of the dampers 41, 42, 43, 44, and 45 that supply the secondary combustion air is set to a larger opening degree closer to the air / fuel supply port 13. As a result, the first to fifth secondary combustion air is supplied so that the damper 41 closest to the air fuel supply port 13 has the maximum flow rate, and the damper 45 farthest from the air fuel supply port 13 has the minimum flow rate. The air is supplied from the supply ports 141, 142, 143, 144, 145 to the first combustion chamber R1.

  When supply of the combusted material, the primary combustion air, and the secondary combustion air to the first combustion chamber R1 is started, the primary combustion air and the secondary combustion air form a swirling flow, and the first combustion chamber R1 It flows from the cylindrical part 11 side toward the truncated cone part 12 side. The combusted material supplied to the first combustion chamber R1 from the air / fuel supply port 13 together with the primary combustion air is combusted in the process of being conveyed in the swirling flow, and generates combustion gas. Most of the swirl flow that flows through the first combustion chamber R1 to the lower end of the truncated cone-shaped portion 12 becomes combustion gas, and flows up in a swirl manner on the central axis side of the first combustion chamber R1 and passes through the exhaust pipe 19. And is discharged from the burner casing 10. The combustion gas discharged from the burner casing 10 is guided to the heat exchanger 4 through the first combustion gas pipe X1. On the other hand, among the combustibles that have flowed through the first combustion chamber R1 to the lower end of the frustoconical portion 12 by the swirling flow, the combustibles and incombustibles that remain without being combusted act as a swirling flow It is separated from the swirl flow by force and falls to the lower end of the truncated cone portion 12 along the inner wall surface of the burner casing 10. The combustible or incombustible material that has reached the lower end of the truncated cone-shaped portion 12 is guided to the transport casing 21 of the screw conveyor 2.

  Since the combusted material supplied to the first combustion chamber R1 is a mixture of crushed waste and dried sludge, there are variations in the types and sizes of the combusted materials, and the combustible materials are easily combusted and heat is generated. There are variations in quantity. For this reason, variation occurs in the distribution of the combustion temperature in the first combustion chamber R1. In order to eliminate such variation in combustion temperature, the controller 30 detects, for example, that the detected temperature of any of the first to fifth thermometers 51, 52, 53, 54, and 55 is lower than the reference range. In this case, the opening degree of the dampers 41, 42, 43, 44, and 45 corresponding to the thermometers 51, 52, 53, 54, and 55 that have detected the decreased temperature is decreased, and the thermometers 51 and 52 that have detected the decreased temperature. , 53, 54, 55, the amount of secondary combustion air supplied from the supply ports 141, 142, 143, 144, 145 is decreased. On the other hand, when the detected temperature of any of the first to fifth thermometers 51, 52, 53, 54, and 55 has risen beyond the reference range, the controller 30 detects the increased temperature. , 52, 53, 54, 55 supply ports corresponding to the thermometers 51, 52, 53, 54, 55 detecting the increased temperature by increasing the opening degree of the dampers 41, 42, 43, 44, 45 The supply amount of the secondary combustion air from 141, 142, 143, 144, 145 is increased. In this way, the controller 30 functions as a combustion air control unit, and the dampers 41, 42, so that the detected temperatures of the first to fifth thermometers 51, 52, 53, 54, 55 are within a predetermined reference range. The opening degree of 43, 44, 45 is feedback controlled. As a result, even if there are variations in the particle size of the combusted material and the type and distribution of the combustible material, the combustion temperature in the first combustion chamber R1 can be stably maintained. Here, the reference range of the temperature detected by the first to fifth thermometers 51, 52, 53, 54, 55 can be set to a range of ± 30 ° C. of a predetermined reference value, and the reference value is It is preferable to set between 780 ° C. and 820 ° C. Thereby, the combustion temperature in 1st combustion chamber R1 can be stably hold | maintained at 750 degreeC or more and 850 degrees C or less. Thus, by setting the combustion temperature in the first combustion chamber R1 to 750 ° C. or higher, the chlorine component of the combusted material can be effectively oxidized, and generation of dioxins can be prevented. Further, by setting the combustion temperature in the first combustion chamber R1 to 850 ° C. or less, it is possible to prevent the burner casing 10 and the exhaust pipe 19 from being damaged due to high temperatures.

  The controller 30 activates the screw conveyor 2 when starting to supply combustibles and primary combustion air to the first combustion chamber R1. That is, power is supplied to the motor M1 to rotate the conveying screw 23, and a drive signal P7 is output to the damper 47 to open the damper 47, and the second combustion chamber R2 in the conveying casing 21 is opened from the conveyor air supply port 28. The third combustion air is blown out toward Further, the controller 30 operates the water supply pump 9 to supply water as a cooling medium to the cooling chamber 20 from the water supply port 26.

  The combustible material introduced into the second combustion chamber R2 of the screw conveyor 2 from the lower end of the frustoconical portion 12 is conveyed to the other end side of the conveying casing 21 by the conveying screw 23. It burns with the tertiary combustion air supplied from. Combustion gas generated by burning the combustibles is discharged from the second combustion chamber R2 through the gas discharge port 29, and is guided to the heat exchanger 4 through the second combustion gas pipe X2. Incombustibles and the like remaining without being burned in the second combustion chamber R2 are transported to the other end side by the transport screw 23, and are discharged as indicated by an arrow H through the discharge port 24 and the rotary valve 25.

  Based on the temperature of the second combustion chamber R2 measured by the sixth thermometer 56, the controller 30 controls the amount of tertiary combustion air supplied from the conveyor air inlet 28 to the second combustion chamber R2. When the detected temperature of the sixth thermometer 56 is lower than a predetermined reference value, the opening degree of the damper 47 is decreased and the supply amount of the tertiary combustion air is decreased. On the other hand, when the detected temperature of the sixth thermometer 56 exceeds a predetermined reference value, the opening degree of the damper 47 is increased and the supply amount of the tertiary combustion air is increased. Thereby, the combustion temperature of the second combustion chamber R2 is maintained at a predetermined temperature. The combustion temperature in the second combustion chamber R2 is preferably set to 500 ° C. or more and 600 ° C. or less. By setting the combustion temperature to 500 ° C. or higher, the combusted material remaining without being burned in the first combustion chamber R1 is efficiently burned. Further, by setting the combustion temperature to 600 ° C. or lower, it is possible to effectively prevent damage to the transport casing 21 and the transport screw 23 of the screw conveyor 2 that forms the second combustion chamber.

  As described above, the cyclone burner 1 of the present embodiment has the secondary combustion air supplied to the first combustion chamber R1 from the first to fifth air supply ports 141, 142, 143, 144, and 145 provided in the burner casing 10. Of the first to fifth thermometers 51, 52, 53, 54, 55 provided at substantially the same axial position as the first to fifth air supply ports 141, 142, 143, 144, 145. Since the control is based on the temperature, the combustion temperature in the first combustion chamber R1 can be made uniform despite burning the combusted material having a larger particle size and a larger variation in the distribution of combustion substances than pulverized coal. Stable combustion heat can be generated. Therefore, the temperature of the hot water generated by the heat exchanger 4 can be stabilized. Moreover, since the 2nd combustion chamber R2 connected to 1st combustion chamber R1 was formed in the conveyance space of the screw conveyor 2, the screw conveyor 2 essential in order to discharge | emit ash and an incombustible material from 1st combustion chamber R1 is secondary. By using the same as the combustion chamber R2, the combustor of the cyclone burner 1 can be used without combusting the apparatus configuration in spite of burning a combustible having a particle size larger than that of pulverized coal and a variation in the distribution of combustion substances. Combustion efficiency can be improved.

  In the above embodiment, the amount of secondary combustion air supplied from the first to fifth air supply ports 141, 142, 143, 144, 145 to the first combustion chamber R1 is controlled by the dampers 41, 42, 43, 44, 45. However, the first to fifth air supply ports 141, 142, 143, 144, and 145 are each connected to a blower, and the controller 30 controls the air flow rate of each of the blowers, so that the first to fifth air supply ports You may control the quantity of the secondary combustion air supplied to 1st combustion chamber R1 from 141,142,143,144,145.

DESCRIPTION OF SYMBOLS 1 Cyclone burner 2 Screw conveyor 3 Fixed quantity feeder 4 Heat exchanger 5 1st fan 6 2nd fan 8 Fuel tank 9 Water supply pump 10 Burner casing 11 Cylindrical part 12 Frustum shape part 13 Air fuel supply port 15 Flame outlet 16 Supply Air vent 17 Start burner 19 Exhaust tube 20 Cooling chamber 21 Transport casing 22 Jacket casing 23 Transport screw 25 Rotary valve 28 Conveyor air inlet 29 Gas exhaust port 30 Controller 40 Fuel valve 41, 42, 43, 44, 45 Damper 50 Supply section Thermometer 51 1st thermometer 52 2nd thermometer 53 3rd thermometer 54 4th thermometer 55 5th thermometer 141 1st air supply port 142 2nd air supply port 143 3rd air supply port 144 4th air supply Port 145 fifth air supply port R1 first combustion chamber R2 second combustion chamber

Claims (11)

A casing having a cylindrical portion and a frustoconical portion whose diameter decreases toward the distal end side of the cylindrical portion and in which the first combustion chamber is formed;
An exhaust pipe having an opening communicating with the first combustion chamber at the tip and disposed coaxially with the casing;
An air / fuel supply unit that is provided in the cylindrical part of the casing and supplies a mixture of the combustible and the primary combustion air in a tangential direction of the cylindrical part;
An ignition part provided in the cylindrical part of the casing;
A thermometer that is provided on at least one side surface of the cylindrical portion of the casing and the truncated cone-shaped portion, and measures the temperature in the first combustion chamber;
At least one side surface of the cylindrical portion of the casing and the truncated cone-shaped portion is provided at the same axial position as the axial position where the thermometer is provided, and the secondary combustion air is supplied into the first combustion chamber. A secondary combustion air supply unit;
A cyclone burner comprising: a combustion air control unit that controls the amount of secondary combustion air that the secondary combustion air supply unit supplies into the first combustion chamber based on the temperature measured by the thermometer. The cyclone burner according to claim 1,
A plurality of the thermometers are provided in the cylindrical part of the casing, and a plurality of the secondary combustion air supply parts are provided in the cylindrical part of the casing. The cyclone burner according to claim 1,
A plurality of the thermometers are provided in the truncated cone shape part of the casing, and a plurality of the secondary combustion air supply parts are provided in the truncated cone shape part of the casing. burner. The cyclone burner according to claim 1,
A first combustion chamber is connected to the first combustion chamber in the casing, separated by a swirl flow formed in the casing, and left to be burned without being burned in the first combustion chamber. A cyclone burner comprising two combustion chambers. The cyclone burner according to claim 4,
A cyclone burner comprising a conveying means connected to the tip of the frustoconical portion of the casing for conveying the remaining combusted material, wherein the second combustion chamber is formed inside the conveying means. . The cyclone burner according to claim 4,
The conveying means is a screw conveyor having a conveying casing and a conveying screw rotatably accommodated in the conveying casing,
The cyclone burner, wherein the second combustion chamber is formed in a transfer space formed between a transfer casing and a transfer screw of the screw conveyor. The cyclone burner according to claim 5,
The cyclone burner characterized in that the conveying means has a tertiary combustion air supply part for supplying tertiary combustion air to the second combustion chamber. The cyclone burner according to claim 5,
The conveying means is
A second combustion chamber thermometer for measuring the temperature in the second combustion chamber;
A tertiary combustion air control unit that controls the amount of tertiary combustion air supplied to the second combustion chamber by the tertiary combustion air supply unit based on the temperature measured by the second combustion chamber thermometer; Cyclone burner characterized by that. The cyclone burner according to claim 5,
The cyclone burner according to claim 1, wherein the conveying means includes a cooling unit which is installed so as to surround the second combustion chamber and to which a cooling medium is supplied. The cyclone burner according to claim 8,
The temperature of the first combustion chamber is set to 750 ° C. or more and 850 ° C. or less by controlling the amount of the mixture supplied by the air / fuel supply unit and the amount of secondary combustion air supplied by the secondary combustion air supply unit. Control and
The tertiary combustion air control unit controls the amount of tertiary combustion air supplied to the second combustion chamber through the tertiary combustion air supply unit to control the temperature of the second combustion chamber to 500 ° C. or more and 600 ° C. or less. Cyclone burner characterized by The cyclone burner according to claim 1,
The cyclone burner characterized in that the combustible includes at least one of dry sludge powder and waste fragments.

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