JP2001182922A - Method of blowing secondary combustion air for application to garbage incinerator and apparatus therefor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a garbage incinerator which may be constructed with a simplified blowing port for blowing secondary combustion air, into the incinerator, and which, in the case where the volume of the secondary combustion air should be reduced, can keep the blowing pressure of the secondary combustion air at the blowing port into the incinerator in an optimum level, with a proper mixing of exhaust gas with the combustion air, allowing the generation of unburned gas such as dioxine or the like contained in the exhaust gas to be reduced. SOLUTION: The garbage incinerator system produces the exhaust gas resulted from combustion, wherein the unburned components of the exhaust gas are mixed with the secondary combustion air and burned. The secondary combustion air is blown through a plurality of tubing 1, 2, 3 with separated valves 13, 14, 15 respectively in such a fashion that one or more tubing selected from these tubing 1, 2, 3 supplies the secondary combustion air as required, while the total cross sectional area of an air passage may be controlled. Therefore, supplying the secondary combustion air through one or more selected tubing would be effective to vary the flow rate of air without decreasing outlet pressure.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a method for blowing air for secondary combustion in a refuse incinerator capable of maintaining a discharge pressure of a discharge port into a furnace even in a situation where the amount of air for secondary combustion is to be reduced. Related to the device.

[0002]

2. Description of the Related Art Conventionally, as a technique for removing dioxins in exhaust gas by combustion control, a method of measuring the temperature of exhaust gas in a furnace and adjusting the amount of secondary combustion air has been known.

For example, Japanese Unexamined Patent Publication No. 7-243630 (hereinafter referred to as the first
In the prior art, a plurality of secondary combustion air nozzles are provided so as to be asymmetrically arranged on the peripheral wall of the secondary combustion chamber in order to efficiently mix the combustible gas and the secondary combustion air. Have been.

For example, Japanese Patent Application Laid-Open No. 3-225106 (hereinafter referred to as "second conventional example") discloses a method for efficiently mixing a combustion gas and secondary combustion air with a peripheral wall of a secondary combustion chamber.
There is disclosed an apparatus in which two or more air supply nozzles are provided and secondary air is supplied from these nozzles toward a contact point of a horizontal virtual circle in a secondary combustion chamber.

In these first and second conventional examples, air is supplied from a fan of a secondary combustion air device to a pipe laid for secondary combustion air, and the flow rate is adjusted only by a damper opening. Have been.

[0006]

As described above, the first conventional example in which a plurality of secondary combustion air nozzles are provided asymmetrically in order to sufficiently promote the mixing of combustible gas and combustion air,
And in the second conventional example in which three or more air supply nozzles are provided on the peripheral wall of the secondary combustion chamber and secondary air is supplied toward the contact point of the horizontal imaginary circle in the chamber, Air is supplied from a combustion air fan to a pipe laid for secondary combustion air, and the flow rate is adjusted only by an opening degree of a damper provided in the middle of the pipe. That is, the cross section of the air path of the pipe remains constant. For this reason, when the secondary combustion air amount is large, the discharge pressure of the secondary combustion air into the furnace is high, and the exhaust gas and the air are sufficiently stirred.

However, the amount of exhaust gas generated may decrease depending on the nature of the waste in the furnace and the combustion state. In such a case, it is necessary to reduce the opening of the damper to reduce the amount of air for secondary combustion. However, as described above, since the cross-section of the air path of the pipe remains constant, the discharge pressure into the furnace becomes small, mixing of air and exhaust gas becomes insufficient, and unburned exhaust gas is generated. It will be easier. To avoid this, if the amount of secondary combustion air is increased even though the amount of generated exhaust gas is decreasing, the amount of secondary combustion air becomes excessive, and even if exhaust gas and air are mixed, the amount of exhaust gas There is a possibility that the temperature will decrease and the combustion of unburned gas will be suppressed.

Therefore, as shown in, for example, Japanese Patent Application Laid-Open No. 10-253046 (hereinafter referred to as a third conventional example), a front and rear movable plate and an opening / closing plate for axially connecting the swinging ends of these movable plates are formed. A pair of throttle members composed of a U-shaped parallel movement mechanism are arranged in the nozzle member to face each other, and the gap between the open / close plates is changed by an operating rod connected to these throttle members via a link, so that the jet flow is reduced. There has been proposed an apparatus in which the expansion range is kept small, and secondary air with high straightness can be blown without lowering the flow velocity of the air blown into the furnace.

However, in the third conventional example in which the shape of the cross section of the nozzle can be mechanically varied in order to sufficiently promote the mixing of the combustible gas and the air for secondary combustion as described above, Is a region that promotes the secondary combustion of exhaust gas, the ambient temperature is as high as 800 to 1000 ° C., and the exhaust gas contains a lot of dust. Expansion and the influence of dust pose problems. Therefore, it is necessary to take measures to protect the mechanism for changing the shape of the cross section of the nozzle, and the device becomes complicated, resulting in a new problem of increasing the cost.

[0010] The technical problem of the present invention is to simplify the structure of the secondary combustion air outlet into the furnace, and to reduce the amount of secondary combustion air in a refuse incinerator. An object of the present invention is to make it possible to maintain the discharge pressure of a discharge port into a furnace, secure the mixing property between exhaust gas and combustion air, and suppress the generation of unburned gas such as dioxins in exhaust gas.

[0011]

The method of blowing air for secondary combustion in a refuse incinerator according to the present invention comprises mixing unburned components contained in exhaust gas burned in the incinerator with air for secondary combustion. In a refuse incinerator system that burns, when blowing air for secondary combustion, a plurality of pipes are used, and the pipe to be used is selected from among the plurality of pipes according to the amount of air for secondary combustion. The method is characterized in that the flow rate is changed without lowering the discharge pressure by adjusting the road cross-sectional area and feeding the secondary combustion air from the selected pipe.

The apparatus used in this method is a refuse incineration system in which unburned components contained in exhaust gas burned in an incinerator are stirred and burned with secondary combustion air supplied from a secondary combustion air system. In the furnace system, the pipe for the secondary combustion air is composed of an aggregate of a plurality of pipes each having an independent valve, and the valve control device selects each of the valves according to a flow signal from the secondary combustion air device. Open / close control.

Further, the method for blowing air for secondary combustion in a refuse incinerator according to the present invention is characterized in that a plurality of pipes used for blowing air for secondary combustion have different cross-sectional areas.

In the apparatus used in this method, a plurality of pipes constituting the assembly have different cross-sectional areas, and are connected to each other.

In this apparatus, the plurality of tubes constituting the assembly are each formed of a rectangular tube having a rectangular cross section.

In this apparatus, a multi-tube is used as a plurality of tubes constituting the assembly.

Further, in the method of blowing air for secondary combustion in a refuse incinerator according to the present invention, the plurality of pipes used for blowing air for secondary combustion each have a nozzle,
It is characterized in that these nozzles have different opening areas at the tips.

In the apparatus used in this method, a plurality of tubes constituting the assembly are provided with nozzles each having a different opening area at the end, and are joined to each other.

Further, in this apparatus, the plurality of tubes constituting the assembly and the nozzles provided therein are each configured to have a rectangular cross section.

In this apparatus, the assembly of a plurality of pipes is composed of multiple pipes, and each nozzle is formed by a cylindrical body inserted at the tip of each pipe forming the multiple pipes. is there.

[0021]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiment 1 FIG. Hereinafter, the first of the present invention.
A method for blowing air for secondary combustion in a refuse incinerator according to the embodiment of the present invention and an apparatus used for this method will be described with reference to FIGS. FIG. 1 is a configuration diagram of a refuse incinerator system to which the secondary combustion air blowing device according to the first embodiment is applied, FIG. 2 is a configuration diagram of a piping system of the secondary combustion air blowing device, and FIG. It is a perspective view which shows the specific example of the piping shape of the air blowing apparatus for secondary combustion.

First, the system of the refuse incinerator according to the first embodiment will be described. In the refuse incinerator 20, refuse 22 introduced from a hopper 21 is sent into the furnace by a dust supply device 23, and a grate device is provided. It is driven by the amount of refuse sent from the refuse 24, the combustion air of the combustion air device 25 sent from below the refuse, and the secondary combustion air of the secondary combustion air device 12 supplied from the outlet 10 of the furnace wall. The exhaust gas burned in the furnace is stirred with the secondary combustion air at the furnace outlet 26,
Combustion is performed, and unburned components in the exhaust gas are burned, and boiler 2
The heat is exchanged at 7, the dust is removed by the exhaust gas treatment device 28, and the harmful substances are removed. The clean air is discharged from the chimney 29 to the atmosphere. Normally, the automatic combustion control device 30 stabilizes combustion fluctuations caused by changes in the supplied waste quality and waste properties.

The piping system for conveying the secondary combustion air from the secondary combustion air device 12 to the outlet 10 is shown in FIG.
And a set 31 of three rectangular tubes 1, 2 and 3 having different cross-sectional areas as shown in FIG. 1 and these rectangular tubes 1, 2 and 3 sandwich the rectangular tube 1 between the rectangular tubes 2 and 3 from both sides. It is joined in a sandwich shape. Then, as shown in FIG. 2, three sets of these assemblies 31 are respectively provided at the blowing ports 10 provided on the left and right walls of the furnace. Furthermore, in these assemblies 31, each set of rectangular tubes 1 is connected by a connecting tube 1A, and each set of rectangular tubes 2 is connected by a connecting tube 2A.
The rectangular pipes 3 of each set are connected to each other by a connecting pipe 3A, and the connecting pipes 1A, 2A, 3A are connected to the secondary combustion air device 12 via independent valves 13, 14, 15, respectively.
It is connected to the.

The valve control device 11 determines which of the rectangular tubes 1, 2 and 3 in each set will discharge the secondary combustion air. The valve control device 11 receives a flow rate signal from the secondary combustion air device 12 and selectively controls opening and closing of each of the valves 13, 14, 15 according to the flow rate.

Next, a method of blowing air for secondary combustion into the refuse incinerator 20 using the apparatus of the first embodiment will be described in further detail with reference to FIGS. 1 to 3.
According to Bernoulli's theorem, the pressure p
Is proportional to the square of the density ρ and the flow velocity v (m / h). here,
Assuming a constant density, the air volume F (m ³ / h) and the cross-sectional area S of the pipe
(m ² ), the relationship of the following equation (1) is as shown in the following equation (2). p∝ρv ² ‥‥‥‥‥‥‥‥‥‥‥‥ (1) p∝ρ (F / S) ² ‥‥‥‥‥‥‥‥‥‥ (2) From the relationship of equation (2), for example, When the air amount F is reduced by half, the pressure becomes 1/4. At this time, the same pressure can be maintained if the cross-sectional area becomes half the cross-sectional area according to the flow rate.
Therefore, when multiple pipes are combined and the flow rate decreases,
By reducing the number of pipes used and reducing the cross-sectional area of the pipes (air passages) as a whole, the flow rate can be changed without lowering the discharge pressure.

The secondary combustion air supplied into the furnace is supplied to each of the blowout ports 10 and 10 provided in the furnace wall through each assembly 31.
Supplied from At this time, when the amount of secondary combustion air is large, the secondary combustion air is supplied from all of the rectangular tubes 1, 2, and 3 of each assembly 31. When the amount of exhaust gas is reduced due to the nature of the refuse in the furnace and the combustion state, and the amount of secondary combustion air is reduced accordingly, for example, the rectangular pipe 2
The supply of air from is stopped, and the air is supplied from the rectangular tubes 1 and 3. Further, when the amount of air for secondary combustion is reduced, the supply of air from the rectangular tubes 2 and 3 is stopped, and the air is supplied only from the rectangular tube 1. In this way, by changing the number of rectangular tubes used in accordance with the increase or decrease in the amount of secondary combustion air, the discharge pressure of the amount of secondary combustion air into the furnace is always maintained constant (for example, a high pressure). While changing the flow rate, it is possible to suppress the generation of unburned gas such as dioxins in the exhaust gas.

If the cross-sectional areas of the rectangular tubes 1, 2, 3 are different from each other, and the ratio of these cross-sectional areas is, for example, 1: 2: 4, the secondary combustion from the rectangular tubes 1, 2, 3 can be performed. When air is supplied, combinations based on the cross-sectional area ratios of the rectangular tubes 1, 2, 3 are shown as 1, 2, (1 + 2), 4, as shown in Table 1 below.
(1 + 4), (2 + 4), (1 + 2 + 4) and valve 1
By making selections based on 3, 14, and 15, it is possible to correspond to a seven-step flow rate change. That is, as shown in the above equation (2), if the ratio between the amount of air and the sectional area is always kept constant, the discharge pressure can be kept constant. Therefore, when the flow rate decreases, the flow rate can be changed without lowering the discharge pressure by using a pipe having a small cross-sectional area as a whole.

[0028]

[Table 1]

By the way, when a plurality of rectangular tubes 1, 2, and 3 are selectively used, an unused tube which does not supply the secondary combustion air into the furnace is heated by gas or the like in the furnace. It may be overheated and adversely affect the upstream equipment such as burnout. Here, since the rectangular tubes 1, 2, and 3 are joined to form the aggregate 31, the unused tubes that do not supply the secondary combustion air into the furnace are used for heat transfer from gases and the like in the furnace. Even if the pipe is overheated, the heat of the unused pipe can be removed by the secondary combustion air flowing in the adjacent pipe in use, and the unused pipe can be cooled. For this reason, it is possible to avoid adversely affecting the equipment on the upstream side of the unused pipe. In addition, since the tubes constituting the assembly 31 are formed in a rectangular shape, the contact area between them when joining them can be increased, the heat transfer efficiency can be improved, and the cooling effect of the unused tubes can be enhanced.

Embodiment 2 FIG. 4 is a perspective view showing a specific example of a pipe shape of a secondary combustion air blowing device according to a second embodiment of the present invention, and other configurations of the refuse incinerator system are the same as those of the above-described first embodiment. It is the same as the one. Therefore, description will be made with reference to FIGS. 1 and 2 described above.

In the secondary combustion air blowing device according to the second embodiment, the piping system for transporting the secondary combustion air from the secondary combustion air device 12 to the outlet 10 has a cross-sectional area where materials are easily available. Of three circular tubes 4, 5, 6 with different diameters
1A, and these circular tubes 4, 5, 6 are joined together. Then, assemblage 31A is provided with blowing ports 10, 10 provided on both right and left walls of the furnace as shown in FIG.
Each of them has three sets. Further, in the assembly 31A, each set of circular pipes 4 is connected to each other by the connecting pipe 1A, each set of circular pipes 5 is connected to each other by the connecting pipe 2A, and each set of circular pipes 6 is connected to each other by the connecting pipe 3A. , Each connecting pipe 1A, 2A, 3A is an independent valve 1
It is connected to the secondary combustion air device 12 via 3, 14, and 15.

The valve control device 11 determines which of the circular pipes 4, 5 and 6 in each set discharges the secondary combustion air. The valve control device 11 receives a flow rate signal from the secondary combustion air device 12 and selectively controls opening and closing of each of the valves 13, 14, 15 according to the flow rate.

The secondary combustion air supplied into the furnace is supplied to each of the blowing ports 10 and 1 provided on the furnace wall through each assembly 31A.
Supply from 0. At this time, when the amount of the secondary combustion air is large, the secondary combustion air is supplied from all of the circular pipes 4, 5, and 6 of each assembly 31A. When the amount of exhaust gas generated by the nature and combustion state of the refuse in the furnace is reduced, and the amount of secondary combustion air is reduced accordingly, for example, the supply of air from the circular pipe 5 is stopped, and the circular pipe is stopped. Supplied from 4,6. Furthermore, when the amount of air for secondary combustion is reduced,
The supply of air from the circular tubes 5 and 6 is stopped, and air is supplied only from the circular tube 4. In this way, by changing the number of circular pipes to be used in accordance with the increase or decrease in the amount of secondary combustion air, the discharge pressure of the amount of secondary combustion air into the furnace is always kept constant (for example, high pressure). While changing the flow rate, it is possible to suppress the generation of unburned gas such as dioxins in the exhaust gas.

If the cross-sectional areas of the circular tubes 4, 5, and 6 are made different from each other and the ratio of these cross-sectional areas is set to, for example, 1: 2: 4 as in the first embodiment, each circular tube 4 , 5,6
When the secondary combustion air is supplied from the
The combinations based on the cross-sectional area ratios of 5, 6 are shown as 1, 2, (1 + 2), 4, (1 + 4), (2+
By selecting 4), (1 + 2 + 4) and the valves 13, 14, and 15, it is possible to cope with a seven-step flow rate change. That is, if the ratio between the amount of air and the cross-sectional area is always kept constant as shown in the above equation (2), the discharge pressure can be kept constant. Therefore, when the flow rate decreases, the flow rate can be changed without lowering the discharge pressure by using a pipe having a small cross-sectional area as a whole.

When the circular pipes 4, 5, and 6 are selectively used, the unused pipes to which the secondary combustion air is not supplied into the furnace are superheated by heat transfer from the gas in the furnace. Although there is a possibility that the upstream side equipment may have a bad influence such as burning, etc., since the circular pipes 4, 5, and 6 are joined to form the aggregate 31A, the air for secondary combustion is Even if unused pipes not supplied into the furnace are overheated by heat transfer from gas etc. in the furnace,
The heat of the unused pipes can be removed by the secondary combustion air flowing in the adjacent used pipes, and the unused pipes can be cooled. For this reason, it is possible to avoid adversely affecting the equipment on the upstream side of the unused pipe.

Embodiment 3 FIG. FIG. 5 is a perspective view showing a specific example of the pipe shape of the secondary combustion air blowing device according to the third embodiment of the present invention, and the other configuration of the refuse incinerator system is the same as that of the above-described first embodiment. It is the same as the one. Therefore, the description will be made with reference to FIGS. 1 and 2 described above.

The secondary combustion air blowing device according to the third embodiment uses a piping system for conveying the secondary combustion air from the secondary combustion air device 12 to the outlet 10 by three rectangular sections having different cross-sectional areas. It is formed from an aggregate 31B of tubes 7, 8, and 9, and two rectangular tubes 8, 9 among the rectangular tubes 7, 8, 9 are formed.
Are joined so as to be in contact with adjacent rectangular tubes on two surfaces. Then, assembling body 31B is provided with blowing ports 10, 10 provided on both right and left walls of the furnace as shown in FIG.
Each of them has three sets. Further, in the assembly 31B, the rectangular tubes 7 of each set are connected by a connecting tube 1A, the rectangular tubes 8 of each set are connected by a connecting tube 2A, and the rectangular tubes 9 of each set are connected by a connecting tube 3A. , Each connecting pipe 1A, 2A, 3A is an independent valve 1
It is connected to the secondary combustion air device 12 via 3, 14, and 15.

The valve control device 11 determines which of the rectangular tubes 7, 8 and 9 in each set discharges the secondary combustion air. The valve control device 11 receives a flow rate signal from the secondary combustion air device 12 and selectively controls opening and closing of each of the valves 13, 14, 15 according to the flow rate.

The secondary combustion air supplied into the furnace is supplied to each of the blowing ports 10, 1 provided in the furnace wall through each assembly 31B.
Supply from 0. At this time, when the amount of the secondary combustion air is large, the secondary combustion air is supplied from all of the rectangular tubes 7, 8, and 9 of the respective assemblies 31B. When the amount of exhaust gas is reduced due to the nature and combustion state of the refuse in the furnace, and the amount of secondary combustion air is reduced accordingly, for example, the supply of air from the rectangular pipe 8 is stopped, and the rectangular pipe is stopped. Supplied from 7,9. Furthermore, when the amount of air for secondary combustion is reduced,
The supply of air from the rectangular tubes 8 and 9 is stopped, and air is supplied only from the rectangular tube 7. In this way, by changing the number of rectangular tubes used in accordance with the increase or decrease in the amount of secondary combustion air, the discharge pressure of the amount of secondary combustion air into the furnace is always maintained constant (for example, a high pressure). While changing the flow rate, it is possible to suppress the generation of unburned gas such as dioxins in the exhaust gas.

If the cross-sectional areas of the rectangular tubes 7, 8, 9 are different from each other, and the ratio of these cross-sectional areas is, for example, 1: 2: 4 as in the first embodiment, the rectangular tubes 7 , 8,9
When the secondary combustion air is supplied from the
Combinations based on the sectional area ratios of 8, 9 are shown as 1, 2, (1 + 2), 4, (1 + 4), (2+
By selecting 4), (1 + 2 + 4) and the valves 13, 14, and 15, it is possible to cope with a seven-step flow rate change. That is, if the ratio between the amount of air and the cross-sectional area is always kept constant as shown in the above equation (2), the discharge pressure can be kept constant. Therefore, when the flow rate decreases, the flow rate can be changed without lowering the discharge pressure by using a pipe having a small cross-sectional area as a whole.

When a plurality of rectangular tubes 7, 8, and 9 are selectively used, the unused tubes to which the secondary combustion air is not supplied into the furnace are superheated by heat transfer from gas or the like in the furnace. However, there is a possibility that the upstream equipment may have a bad influence such as burnout, but here, two of the rectangular pipes 7, 8, 9 are in contact with the adjacent rectangular pipe on two sides. As a result, one rectangular tube surely comes into contact with the other two rectangular tubes, and the unused tube that does not supply the secondary combustion air into the furnace is placed inside the furnace. Even if it is overheated by the heat transfer from the gas or the like, the heat of the unused pipe can be efficiently removed by the secondary combustion air flowing in one or two adjacent pipes in use, and the unused pipe Can be efficiently cooled. For this reason, it is possible to avoid adversely affecting the equipment on the upstream side of the unused pipe.

Embodiment 4 FIG. FIG. 6 is a perspective view showing a specific example of the pipe shape of the secondary combustion air blowing device according to the fourth embodiment of the present invention, and other configurations of the refuse incinerator system are the same as those of the above-described first embodiment. It is the same as the one. Therefore, the description will be made with reference to FIGS. 1 and 2 described above.

The secondary combustion air blowing device according to the fourth embodiment includes a pipe system for conveying the secondary combustion air from the secondary combustion air device 12 to the outlet 10 by using a circular pipe 4 having a different diameter.
1, 42, and 43 are arranged concentrically, that is, a multi-tube (here, a triple tube) 50, and a first wind is provided between the innermost circular tube 41 and the intermediate circular tube 42. A passage 44 is formed, and the innermost circular tube 41 forms a second air passage 45. A third air passage 46 is formed between the outermost circular tube 43 and the intermediate circular tube 42. And, as shown in FIG. 2, three sets of these multiple pipes 50 are respectively provided at the blowing ports 10, 10 provided on both right and left walls of the furnace. Furthermore, these multiple tubes 50
Are connected to each other by the connecting pipe 1A.
Each of the second air passages 45 is connected to each other by the connecting pipe 2A, and each of the third air paths 46 is connected to each other by the connecting pipe 3A. 15 is connected to the secondary combustion air device 12.

Each of the air passages 44, 45,
Whether the secondary combustion air is discharged from 46 is determined by the valve control device 11. The valve control device 11 receives a flow rate signal from the secondary combustion air device 12 and selectively controls opening and closing of each of the valves 13, 14, 15 according to the flow rate.

The secondary combustion air to be supplied into the furnace is supplied from the respective blowing ports 10, 10 provided in the furnace wall via the air passages 44, 45, 46 of the respective multi-tubes 50. At this time, when the amount of the secondary combustion air is large, the secondary combustion air is supplied from all of the air passages 44, 45, and 46 of each of the multiple pipes 50. When the amount of exhaust gas is reduced due to the nature and combustion state of the refuse in the furnace, and the amount of secondary combustion air is reduced accordingly, for example, the supply of air from the second air passage 45 is stopped, The air is supplied from the first and third air paths 44 and 46. Furthermore, when the amount of air for secondary combustion is reduced, the supply of air from the second and third air passages 45 and 46 is stopped, and air is supplied only from the first air passage 44. In this way, by changing the number of air passages used according to the increase or decrease of the secondary combustion air amount,
The flow rate can be changed while maintaining the discharge pressure of the secondary combustion air amount into the furnace constantly (for example, high pressure), and the generation of unburned gas such as dioxins in exhaust gas can be suppressed. it can.

Further, the ratio of the cross-sectional area of each of the air passages 44, 45, 46 is set to, for example, 1: 2 as in the first embodiment.
When the diameter of each of the circular pipes 41, 42, 43 is selected so as to be 4, and the air for secondary combustion is supplied from each of the air paths 44, 45, 46, the cutoff of each of the air paths 44, 45, 46 is performed. The combinations based on the area ratios are 1, 2, (1+
2), 4, (1 + 4), (2 + 4), (1 + 2 + 4)
And by selecting the valves 13, 14, 15
It is possible to correspond to the flow rate change in seven stages. That is, if the ratio between the amount of air and the cross-sectional area is always kept constant as shown in the above equation (2), the discharge pressure can be kept constant. Therefore, when the flow rate decreases, the flow rate can be changed without lowering the discharge pressure by using a pipe having a small cross-sectional area as a whole.

When a plurality of air passages 44, 45, and 46 are selectively used, the unused pipes forming the air passage that does not supply the secondary combustion air into the furnace include gas in the furnace. Overheated by the heat transfer from the heat exchanger, there is a possibility of adversely affecting the upstream equipment such as burnout.
Are formed by circular pipes 41, 42 and circular pipes 42, 43 which directly overlap each other, and the outer peripheral surface of the circular pipe 41 which is the innermost pipe is the first pipe.
Since the inner wall of the air passage 44 is formed, the heat transfer efficiency is good, and even if an unused pipe that does not supply the secondary combustion air into the furnace is overheated by heat transfer from gas in the furnace, The heat of the unused pipe can be efficiently removed by the secondary combustion air flowing through the adjacent pipe in use, and the cooling effect of the unused pipe can be further enhanced. For this reason, it is possible to reliably prevent the device on the upstream side of the unused pipe from being adversely affected.

Here, circular pipes 41 and 42 of different diameters are used.
Although the description has been given by taking the multi-tube 50 by 43 as an example, the multi-tube may be configured by using a plurality of rectangular tubes of different diameters, and may be a multi-tube of three or more tubes. If the number of overlapping tubes is increased, the combination based on the cross-sectional area ratio can correspond to the flow rate change in more stages.

Also, here, circular pipes 41, 42,
The multi-tube 50 in which the concentric tubes 43 are arranged is described as an example. However, the multi-tubes in which the circular tubes 41, 42, and 43 are eccentrically arranged may be used.・ Effective.

Embodiment 5 FIG. FIG. 7 is a configuration diagram of a refuse incinerator system to which a secondary combustion air blowing device according to a fifth embodiment of the present invention is applied, and FIG. 8 shows a specific example of a pipe shape of the secondary combustion air blowing device. It is a perspective view, and the structure of the refuse incinerator system other than the piping shape of the air blowing apparatus for secondary combustion is the same as that of 1st Embodiment mentioned above. In the description, reference is made to FIG.

In the secondary combustion air blowing device of the fifth embodiment, the piping system for transporting the secondary combustion air from the secondary combustion air device 12 to the outlet 10 has three rectangular pipes 6.
1, 62, 63, and these rectangular tubes 61, 62, 63 are formed by replacing the rectangular tube 61 with the rectangular tubes 62, 63.
Nozzles having rectangular opening surfaces 64, 65, 66 of different sizes with their leading ends contracted in the left-right direction.
68 and 69 are formed. And these aggregates 6
0 is a blowing port 1 provided on both right and left walls of the furnace as shown in FIG.
Three sets are provided at 0 and 10, respectively. further,
These assemblies 60 are formed by connecting the rectangular tubes 61 of each set to each other.
A, each pair of rectangular tubes 62 is connected by the connecting tube 2A.
The rectangular pipes 63 of each set are connected to each other by a connecting pipe 3A, and the connecting pipes 1A, 2A, 3A are connected to the secondary combustion air device 1 through independent valves 13, 14, 15, respectively.
2 are connected.

The valve control device 11 determines which of the nozzles 67, 68, 69 of the rectangular tubes 61, 62, 63 in each set discharges the secondary combustion air. The valve control device 11 receives a flow rate signal from the secondary combustion air device 12 and controls each of the valves 13, 1 according to the flow rate.
4 and 15 are selectively opened and closed.

The secondary combustion air supplied into the furnace is supplied to each of the blowout ports 10 and 10 provided in the furnace wall through each assembly 60.
Supplied from At this time, when the amount of the secondary combustion air is large, the secondary combustion air is supplied from all of the nozzles 67, 68, and 69 of each assembly 60. When the amount of exhaust gas generated by the nature and combustion state of the refuse in the furnace is reduced, and the amount of air for secondary combustion is reduced accordingly, for example, the supply of air from the nozzle 68 is stopped, and the nozzles 67 and 67 are stopped. 69
Supplied from Further, when the amount of air for secondary combustion is reduced, the supply of air from the nozzles 68 and 69 is stopped,
It is supplied only from the nozzle 67. Thus, the rectangular tubes 61, 62, 63 used according to the increase or decrease of the secondary combustion air amount.
That is, by changing the number of nozzles 67, 68, and 69, the flow rate can be changed while constantly maintaining the discharge pressure of the amount of secondary combustion air into the furnace (for example, a high pressure). The generation of unburned gas such as dioxins can be suppressed. Further, since the secondary combustion air is discharged from the nozzles 67, 68, and 69, the spread range of the jet flow is suppressed to a small extent, and the flow rate of the air blown into the furnace is reduced without a strong linearity. The next air can be blown.

Further, the areas of the rectangular opening surfaces 64, 65, 66 of the nozzles 67, 68, 69 are made different from each other, and the ratio of these opening areas is set to, for example, 1: 1, as in the first embodiment.
If the ratio is 2: 4, when the secondary combustion air is supplied from each of the nozzles 67, 68, 69, each of the rectangular opening surfaces 64, 65,
66, the combinations based on the opening area ratio are 1, 2, (1 + 2), 4, (1 + 4), and (2+
By selecting 4), (1 + 2 + 4) and the valves 13, 14, and 15, it is possible to cope with a seven-step flow rate change. That is, if the ratio between the amount of air and the cross-sectional area is always kept constant as shown in the above equation (2), the discharge pressure can be kept constant. Therefore, when the flow rate decreases, the flow rate can be changed without lowering the discharge pressure by using a nozzle having a small opening area as a whole.

When the nozzles are selectively used from among the plurality of nozzles 67, 68, and 69, the unused nozzles that do not supply the secondary combustion air into the furnace are superheated by the heat transfer from the gas in the furnace. The heat is transmitted to the rectangular tubes that are continuous with this, and there is a possibility that the upstream devices may have a bad influence such as burnout. However, here, the rectangular tubes 61, 62, and 63 are joined to form the aggregate 60. Therefore, even if an unused nozzle that does not supply secondary combustion air into the furnace is overheated by heat transfer from gas etc. in the furnace, the secondary combustion air flowing through the adjacent used rectangular tube The heat of the non-use-side pipe (rectangular pipe and nozzle) can be taken away by air, and the non-use-side pipe can be cooled. For this reason, it is possible to avoid adversely affecting devices upstream of the unused pipe.

Embodiment 6 FIG. FIG. 9 is a perspective view showing a specific example of the pipe shape of the secondary combustion air blowing device according to the sixth embodiment of the present invention, and shows a waste incinerator system other than the piping shape of the secondary combustion air blowing device. The configuration is the first
And the fifth embodiment. Therefore, the description will be made with reference to FIGS. 2 and 7 described above.

In the secondary combustion air blowing device of the sixth embodiment, the piping system for transporting the secondary combustion air from the secondary combustion air device 12 to the outlet 10 has three pipes that are easily available. Of circular pipes 71, 72, and 73, and these circular pipes 71, 72, and 73 are joined to each other.
Nozzles 77, 78, 79 having 5, 76 are inserted. These nozzles 77, 78, 79 are each
1, 72, 73 are formed from circular cylinders of different thicknesses which are inserted and fixed from the respective ends thereof, have a predetermined length in the tube axis direction, and thereby provide a highly straight forward secondary combustion air. In addition to being capable of blowing, a plurality of types of cylinders having different wall thicknesses are prepared, so that the combination of the circular opening surfaces 74, 75, and 76 based on the opening area ratio can be easily changed. . Then, as shown in FIG. 2, three sets of these assemblies 70 are respectively provided at the blowing ports 10 provided on both right and left walls of the furnace. Further, in the assembly 70, each set of circular pipes 71 is connected by the connecting pipe 1A, each set of circular pipes 72 is connected by the connecting pipe 2A, and each set of circular pipes 73 is connected by the connecting pipe 3A. The connecting pipes 1A, 2A, 3A are connected to the secondary combustion air device 12 via independent valves 13, 14, 15, respectively.

The valve control device 11 determines which of the nozzles 77, 78, 79 of the circular pipes 71, 72, 73 of each set discharges the secondary combustion air. The valve control device 11 receives a flow rate signal from the secondary combustion air device 12 and controls each of the valves 13, 1 according to the flow rate.
4 and 15 are selectively opened and closed.

The secondary combustion air supplied into the furnace is supplied to each of the blowout ports 10 and 10 provided in the furnace wall through each assembly 70.
Supplied from At this time, when the amount of the secondary combustion air is large, the secondary combustion air is supplied from all of the nozzles 77, 78, and 79 of each assembly 70. When the amount of exhaust gas generated decreases due to the nature and combustion state of the refuse in the furnace, and the amount of air for secondary combustion is reduced accordingly, for example, the supply of air from the nozzle 78 is stopped and the nozzles 77 and 77 are stopped. 79
Supplied from Further, when the amount of air for secondary combustion is reduced, the supply of air from the nozzles 78 and 79 is stopped,
It is supplied only from the nozzle 77. Thus, the circular pipes 71, 72, 73 used according to the increase or decrease of the secondary combustion air amount.
That is, by changing the number of the nozzles 77, 78, 79, the flow rate can be changed while constantly maintaining the discharge pressure of the secondary combustion air amount into the furnace at a constant (for example, high pressure). The generation of unburned gas such as dioxins can be suppressed. Further, since the secondary combustion air is discharged from the nozzles 77, 78, and 79, the spread range of the jet is suppressed to be small, and the flow rate of the air blown into the furnace is not reduced, so that the air having a strong straightness can be obtained. The next air can be blown.

Further, the areas of the circular opening surfaces 74, 75, 76 of the nozzles 77, 78, 79 are different from each other, and the ratio of these opening areas is, for example, 1: 1, as in the first embodiment.
If the ratio is 2: 4, when the air for secondary combustion is supplied from each of the nozzles 77, 78, 79, each of the circular opening surfaces 74, 75,
76, the combinations based on the opening area ratio are 1, 2, (1 + 2), 4, (1 + 4), (2+
By selecting 4), (1 + 2 + 4) and the valves 13, 14, and 15, it is possible to cope with a seven-step flow rate change. That is, if the ratio between the amount of air and the cross-sectional area is always kept constant as shown in the above equation (2), the discharge pressure can be kept constant. Therefore, when the flow rate decreases, the flow rate can be changed without lowering the discharge pressure by using a nozzle having a small opening area as a whole.

When a plurality of nozzles 77, 78, and 79 are selectively used, the unused nozzles that do not supply the secondary combustion air into the furnace are superheated by heat transfer from the gas in the furnace. The heat is transmitted to the rectangular tube following this, and there is a possibility that the upstream device may have an adverse effect such as burnout. However, here, the circular tubes 71, 72, and 73 are joined to form an aggregate 70. Therefore, even if an unused nozzle that does not supply secondary combustion air into the furnace is overheated by heat transfer from gas in the furnace, the secondary combustion air that flows through the adjacent circular pipe in use is used. The heat of the non-use side pipe (circular pipe and nozzle) can be taken away by air, and the non-use side pipe can be cooled. For this reason, it is possible to avoid adversely affecting devices upstream of the unused pipe.

Embodiment 7 FIG. 10 is a perspective view showing a specific example of the pipe shape of the secondary combustion air blowing device according to the seventh embodiment of the present invention. The configuration is the same as that of the first and fifth embodiments. Therefore, the description will be made with reference to FIGS. 2 and 7 described above.

In the secondary combustion air blowing device of the seventh embodiment, the piping system for transporting the secondary combustion air from the secondary combustion air device 12 to the outlet 10 has three rectangular pipes 8.
1, 82, 83, and two rectangular tubes 82, 83 of these rectangular tubes 81, 82, 83 are joined so as to be in contact with the adjacent rectangular tubes on two sides, respectively, and the respective tips are formed. And rectangular opening surfaces 8 of different sizes
Nozzles 87, 88, 89 having 4, 85, 86 are inserted. These nozzles 87, 88, 89 are formed of rectangular cylinders having different thicknesses, which are inserted into the respective rectangular tubes 81, 82, 83 from their respective ends and fixed, have a predetermined length in the tube axis direction, This makes it possible to blow in the air for secondary combustion, which has strong straightness,
By preparing a plurality of cylinders having different wall thicknesses, it is possible to easily change the combination of the rectangular opening surfaces 84, 85, 86 based on the opening area ratio. Then, as shown in FIG. 2, three sets of these assemblies 80 are respectively provided at the blowing ports 10 provided on both right and left walls of the furnace. Further, in the assembly 80, each pair of rectangular tubes 81 is connected by the connecting tube 1A, each pair of rectangular tubes 82 is connected by the connecting tube 2A, and each pair of rectangular tubes 83 is connected by the connecting tube 3A. , Each connecting pipe 1A, 2A, 3A,
Each of them is connected to the secondary combustion air device 12 via an independent valve 13, 14, 15.

The valve control device 11 determines which of the nozzles 87, 88, 89 of the rectangular tubes 81, 82, 83 from each set discharges the secondary combustion air. The valve control device 11 receives a flow rate signal from the secondary combustion air device 12 and controls each of the valves 13, 1 according to the flow rate.
4 and 15 are selectively opened and closed.

The secondary combustion air supplied into the furnace is supplied to each of the blowout ports 10 and 10 provided in the furnace wall through each assembly 80.
Supplied from At this time, if the amount of the secondary combustion air is large, the secondary combustion air is supplied from all of the nozzles 87, 88, and 89 of each assembly 80. When the amount of exhaust gas is reduced due to the nature of the refuse in the furnace and the combustion state, and the amount of secondary combustion air is reduced accordingly, for example, the supply of air from the nozzle 88 is stopped, and the nozzles 87 and 87 are stopped. 89
Supplied from Further, when the amount of air for secondary combustion is reduced, the supply of air from the nozzles 88 and 89 is stopped,
It is supplied only from the nozzle 87. Thus, the rectangular tubes 81, 82, 83 used according to the increase or decrease of the secondary combustion air amount.
In other words, by changing the number of nozzles 87, 88, 89, the flow rate can be changed while constantly maintaining the discharge pressure of the secondary combustion air amount into the furnace at a constant (eg, high) pressure. The generation of unburned gas such as dioxins can be suppressed. Further, since the secondary combustion air is discharged from the nozzles 87, 88, 89, the spread range of the jet is suppressed to a small extent, and the flow rate of the air blown into the furnace is not reduced, and the air having a strong linearity can be obtained. The next air can be blown.

Further, the areas of the rectangular opening surfaces 84, 85, 86 of the nozzles 87, 88, 89 are different from each other, and the ratio of these opening areas is, for example, 1: 1, as in the first embodiment.
If the ratio is 2: 4, when the secondary combustion air is supplied from each of the nozzles 87, 88, 89, each of the rectangular opening surfaces 84, 85,
86 as shown in Table 1 above, 1, 2, (1 + 2), 4, (1 + 4), (2+
By selecting 4), (1 + 2 + 4) and the valves 13, 14, and 15, it is possible to cope with a seven-step flow rate change. That is, if the ratio between the amount of air and the cross-sectional area is always kept constant as shown in the above equation (2), the discharge pressure can be kept constant. Therefore, when the flow rate decreases, the flow rate can be changed without lowering the discharge pressure by using a nozzle having a small opening area as a whole.

When the nozzles 87, 88 and 89 are selectively used, the unused nozzles which do not supply the secondary combustion air into the furnace are superheated by the heat transfer from the gas in the furnace. Heat may be transmitted to a rectangular tube that is connected to the rectangular tube, which may have a bad influence such as burnout on the upstream device. In this case, two rectangular tubes 82, 82 out of the rectangular tubes 81, 82, 83 are used.
83 is formed in the aggregate 80 which is joined so that it contacts the adjacent rectangular tubes on two sides, so that one rectangular tube surely comes into contact with the other two rectangular tubes and removes the air for secondary combustion. Even if an unused nozzle that is not supplied into the furnace is overheated by heat transfer from gas or the like in the furnace, a non-use side pipe (rectangular pipe) is used by the secondary combustion air flowing in the adjacent used rectangular pipe. And the nozzle) can be deprived of heat, and the non-use side piping can be cooled. For this reason, it is possible to avoid adversely affecting devices upstream of the unused pipe.

Embodiment 8 FIG. FIG. 11 is a perspective view showing a specific example of the pipe shape of the secondary combustion air blowing device according to the eighth embodiment of the present invention, and shows a waste incinerator system other than the piping shape of the secondary combustion air blowing device. The configuration is the same as that of the first and fifth embodiments. Therefore, the description will be made with reference to FIGS. 2 and 7 described above.

The secondary combustion air blowing device according to the eighth embodiment has a pipe system for conveying the secondary combustion air from the secondary combustion air device 12 to the blowout port 10 with a circular pipe 9 having a different diameter.
Nozzles 97 and 98 which form air passage opening surfaces 94, 95 and 96 of different sizes at their ends, respectively, are composed of an assembly in which 1, 92 and 93 are arranged concentrically, that is, a multi-tube (here, a triple tube) 90. , 99 are inserted. These nozzles 97, 98, 99 are provided with respective circular tubes 91, 92, 93.
It is composed of circular cylinders of different diameters inserted and fixed from the respective ends into the inside, and has a predetermined length in the tube axis direction, so that it is possible to blow the secondary combustion air having a strong linearity. In addition, by preparing a plurality of types of cylinders having different wall thicknesses, the air passage opening surfaces 94, 95, 96
Can be easily changed depending on the opening area ratio. And, as shown in FIG. 2, three sets of these multiple pipes 90 are respectively provided at the blowing ports 10 provided on both right and left walls of the furnace. Furthermore, in the multiple tubes 90, the first air passages connected to the respective air passage opening surfaces 94 are connected to each other by the connecting tube 1A, and the second air passages connected to the respective air passage opening surfaces 95 are connected to the connecting tube 2A. The third air passages connected to the air passage opening surface 96 are connected to each other by the connecting pipe 3A.
The connection pipes 1A, 2A, and 3A are connected to the secondary combustion air device 12 via independent valves 13, 14, and 15, respectively.

Each of the nozzles 97 and 9 of each of the multiple pipes 90
Whether to discharge the secondary combustion air from 8, 99 is determined by the valve control device 11. The valve control device 11 receives a flow rate signal from the secondary combustion air device 12 and selectively controls opening and closing of each of the valves 13, 14, 15 according to the flow rate.

The secondary combustion air supplied into the furnace is supplied to each of the blowing ports 10, 10
Supplied from At this time, when the amount of air for secondary combustion is large, the nozzles 97, 98, 99
Supply air for secondary combustion from all of the above. When the amount of exhaust gas generated by the nature and combustion state of the refuse in the furnace is reduced, and the amount of secondary combustion air is reduced accordingly, for example, the supply of air from the nozzle 98 is stopped, and the nozzles 97 and 97 are stopped. 9
Supplied from 9. Further, when the amount of air for secondary combustion is reduced, the supply of air from the nozzles 98 and 99 is stopped, and the air is supplied only from the nozzle 97. As described above, the circular pipes 91 and 92 having different diameters used according to the increase and decrease of the secondary combustion air amount are used.
By changing the number of nozzles 92, 93, that is, the number of nozzles 97, 98, 99, the flow rate can be changed while the discharge pressure of the secondary combustion air amount into the furnace is always kept constant (for example, high pressure). In addition, generation of unburned gas such as dioxins in exhaust gas can be suppressed. Furthermore, since the secondary combustion air is discharged from the nozzles 97, 98, and 99, the spread range of the jet is suppressed to a small extent, and the flow rate of the air blown into the furnace is not reduced, and the air having a strong straightness can be obtained. The next air can be blown.

Further, if the area ratio of the air passage opening surfaces 94, 95, 96 of the nozzles 97, 98, 99 to each other is set to, for example, 1: 2: 4 as in the first embodiment, each nozzle 9
When supplying secondary combustion air from 7,98,99,
The combinations of the area ratios of the respective air passage opening surfaces 94, 95, and 96 are shown as 1, 2, (1 + 2), 4,
(1 + 4), (2 + 4), (1 + 2 + 4) and valve 1
By making selections based on 3, 14, and 15, it is possible to correspond to a seven-step flow rate change. That is, if the ratio between the amount of air and the cross-sectional area is always kept constant as shown in the above equation (2), the discharge pressure can be kept constant. Therefore, when the flow rate decreases, the flow rate can be changed without lowering the discharge pressure by using a nozzle having a small opening area as a whole.

When a plurality of nozzles 97, 98, and 99 are selectively used, the unused nozzles that do not supply the secondary combustion air into the furnace are superheated by heat transfer from the gas in the furnace. Heat may be transmitted to the circular pipe connected to the pipe, which may have adverse effects such as burnout on the upstream equipment. In this case, two of the air paths connected to the air path opening surfaces 94, 95, and 96 are used. However, the circular pipes 91 and 92 and the circular pipe 9
2 and 93, and a circular tube 91 which is the innermost tube has a first outer surface connected to an air passage opening surface 94.
Since the inner wall of the air passage is configured, heat transfer efficiency is good, and even if an unused pipe that does not supply secondary combustion air to the furnace is overheated by heat transfer from gas etc. The heat of the unused pipes can be efficiently removed by the secondary combustion air flowing through the used pipes, and the cooling effect of the unused pipes can be further enhanced. For this reason, it is possible to reliably avoid adverse effects on the equipment on the upstream side of the non-use-side pipe (circular pipe and nozzle).

Here, circular pipes 41, 42 of different diameters,
Circular pipe 9 of different diameter with 43 and nozzles 97, 98, 99
Although the description has been given by taking the multi-tubes 50 and 90 by 1, 92 and 93 as an example, a multi-tube may be configured using a plurality of different-diameter rectangular tubes or a plurality of different-diameter rectangular tubes with nozzles. Also, a multi-tube of three or more tubes may be used. If you increase the number of tubes to stack,
Combinations based on the cross-sectional area ratios of the circular tubes 41, 42, and 43 and combinations based on the area ratios of the opening surfaces of the nozzles 97, 98, and 99 can correspond to more stages of flow rate changes.

Here, circular pipes 41, 42 of different diameters,
Circular pipe 9 of different diameter with 43 and nozzles 97, 98, 99
A multi-tube 5 in which 1, 92 and 93 are all arranged concentrically
0 and 90 have been described as an example.
42, 43 and circular tubes 91 with nozzles 97, 98, 99,
The multiple tubes 92 and 93 may be eccentrically arranged. Even in such a case, the same operation and effect as described above can be obtained.

Furthermore, in each of the above-described embodiments, an example in which the air passage (the piping cross section and the nozzle opening surface) is formed in a rectangular, circular, ring-shaped, or circular shape has been described. It is not important that the air passage cross-sectional area ratio can be clearly defined, and any air passage shape may be adopted.

[0077]

As described above, according to the method for blowing air for secondary combustion in the refuse incinerator according to the first aspect of the present invention and the apparatus according to the fourth aspect used in this method, the combustion in the incinerator is performed. In a refuse incinerator system that stirs and burns unburned components contained in exhaust gas with air for secondary combustion, when blowing air for secondary combustion, using a plurality of pipes,
By selecting the pipe to be used from these multiple pipes according to the amount of secondary combustion air, the cross-sectional area of the air path is adjusted, and the secondary combustion air is sent from the selected pipe, thereby reducing the discharge pressure. Since the flow rate was changed without lowering,
Even when the amount of exhaust gas is reduced due to the nature of the refuse in the furnace and the combustion state, and the amount of secondary combustion air is reduced accordingly, the discharge pressure of the amount of secondary combustion air into the furnace is always constant. (For example, high pressure), the flow rate could be changed, and generation of unburned gas such as dioxins in exhaust gas could be suppressed. Further, such a flow rate adjusting function can be realized by a simplified secondary combustion air outlet.

According to the method for blowing air for secondary combustion in a refuse incinerator according to claim 2 of the present invention and the apparatus for claim 5 used in this method, the method is used for blowing air for secondary combustion. Since the pipes were made to have different cross-sectional areas and joined to each other, it was possible to cope with multi-step flow rate changes by combining the cross-sectional area ratios, and to supply secondary combustion air into the furnace. Even if unused pipes are not heated by heat transfer from gas etc. in the furnace,
The heat of the unused pipes could be removed by the secondary combustion air flowing in the adjacent used pipes, and the unused pipes could be cooled. For this reason, it was possible to avoid adversely affecting the equipment on the upstream side of the unused pipe.

According to the apparatus of claim 6 of the present invention,
Since the plurality of tubes constituting the assembly are each formed of a rectangular tube having a rectangular cross-sectional shape, the contact area when joining can be increased, and the heat transfer efficiency can be improved.
The cooling effect of unused pipes could be increased.

According to the device of claim 7 of the present invention,
Since multiple tubes were used as the plurality of tubes constituting the assembly, the heat transfer efficiency could be further improved, and the cooling effect of unused tubes could be further improved. For this reason, it was possible to reliably prevent the equipment on the upstream side of the unused pipe from being adversely affected.

According to the method for blowing secondary combustion air in a refuse incinerator according to claim 3 of the present invention and the apparatus according to claim 8 used in this method, it is used when blowing secondary combustion air. A plurality of pipes each have a nozzle, and these nozzles have different opening areas at the tip, and are configured to be joined to each other. If the unused nozzles that do not supply the secondary combustion air into the furnace are overheated by heat transfer from the gas in the furnace and heat is transferred to the pipes connected to the The heat of the unused pipes could be removed by the secondary combustion air flowing through the pipes in use, and the unused pipes (tubes and nozzles) could be cooled. For this reason, it was possible to avoid adversely affecting the equipment on the upstream side of the non-use side pipe. Further, the spread range of the jet flow can be suppressed to a small value, and it is possible to blow the secondary air having a high straightness without lowering the flow velocity of the air blown into the furnace.

According to the device of claim 9 of the present invention,
The multiple tubes that make up the assembly and the nozzles
Since the cross-sectional shape is configured to be rectangular, the contact area at the time of joining can be increased, the heat transfer efficiency can be improved, and the cooling effect of the non-use-side pipe (rectangular pipe and nozzle) can be enhanced. I was able to. Further, the spread range of the jet flow can be suppressed to a small value, and it is possible to blow the secondary air having a high straightness without lowering the flow velocity of the air blown into the furnace.

According to the apparatus of claim 10 of the present invention, an assembly of a plurality of pipes is formed from multiple pipes, and the cylindrical bodies inserted into the tips of the pipes forming the multiple pipes respectively. Since each nozzle was formed, the heat transfer efficiency could be further improved, and the cooling effect of the non-use side pipe (tube and nozzle) could be further improved. For this reason, it was possible to reliably avoid adverse effects on the equipment on the upstream side of the unused pipe. Further, the spread range of the jet flow can be suppressed to a small value, and it is possible to blow the secondary air having a high straightness without lowering the flow velocity of the air blown into the furnace.

[Brief description of the drawings]

FIG. 1 is a configuration diagram of a refuse incinerator system to which a secondary combustion air blowing device according to a first embodiment of the present invention is applied.

FIG. 2 is a configuration diagram of a piping system of the secondary combustion air blowing device according to the first embodiment.

FIG. 3 is a perspective view showing a specific example of a pipe shape of the secondary combustion air blowing device according to the first embodiment.

FIG. 4 is a perspective view showing a specific example of a pipe shape of a secondary combustion air blowing device according to a second embodiment of the present invention.

FIG. 5 is a perspective view showing a specific example of a pipe shape of a secondary combustion air blowing device according to a third embodiment of the present invention.

FIG. 6 is a perspective view showing a specific example of a pipe shape of a secondary combustion air blowing device according to a fourth embodiment of the present invention.

FIG. 7 is a configuration diagram of a refuse incinerator system to which a secondary combustion air blowing device according to a fifth embodiment of the present invention is applied.

FIG. 8 is a perspective view showing a specific example of a pipe shape of a secondary combustion air blowing device according to a fifth embodiment.

FIG. 9 is a perspective view showing a specific example of a pipe shape of a secondary combustion air blowing device according to a sixth embodiment of the present invention.

FIG. 10 is a perspective view showing a specific example of a pipe shape of a secondary combustion air blowing device according to a seventh embodiment of the present invention.

FIG. 11 is a perspective view showing a specific example of a pipe shape of a secondary combustion air blowing device according to an eighth embodiment of the present invention.

[Explanation of symbols]

1,2,3,7,8,9,61,62,63,81,8
2,83 Rectangular pipe (Pipe for secondary combustion air) 4,5,6,71,72,73 Circular pipe (Pipe for secondary combustion air) 10 Inlet 11 Valve control device 12 Secondary combustion air device 13 , 14, 15 valve 20 incinerator 31, 31A, 31B, 60, 70, 80 assembly 44, 45, 46 air path 50, 90 multiple pipe (collection of secondary combustion air piping) 64, 65, 66 , 74,75,76,84,85,8
6, 94, 95, 96 Nozzle opening surfaces 67, 68, 69, 77, 78, 79, 87, 88, 8
9,97,98,99 nozzles

Continued on the front page (72) Inventor Takuyuki Shimamoto 1-2-1, Marunouchi, Chiyoda-ku, Tokyo Nihon Kokan Co., Ltd. (72) Inventor Shigeyuki Doi 1-2-1, Marunouchi, Chiyoda-ku, Tokyo Nihon Kokan F term in the company (reference) 3K023 KA02 KB10 KC05 KD01 KD05 3K065 AA04 AB02 AC01 BA04 GA03 GA07 GA12 GA23 GA28 GA33 GA34 GA43 GA46 GA48 GA53 3K078 AA04 BA03 BA26 CA03 CA12 CA13 CA21

Claims (10)

[Claims] In a refuse incinerator system in which unburned components contained in exhaust gas burned in an incinerator are agitated and burned with secondary combustion air, a plurality of pipes are used when blowing secondary combustion air. By selecting a pipe to be used from among the plurality of pipes according to the amount of secondary combustion air, adjusting the cross-sectional area of the air passage, and sending secondary combustion air from the selected pipe, A method for blowing air for secondary combustion in a refuse incinerator, wherein the flow rate is changed without lowering the discharge pressure. 2. The method for blowing air for secondary combustion in a refuse incinerator according to claim 1, wherein a plurality of pipes used for blowing the air for secondary combustion have different cross-sectional areas. 3. A refuse incinerator according to claim 1, wherein the plurality of pipes used for blowing the secondary combustion air have nozzles, respectively, and the nozzles have different opening areas at the tips. Air blowing method for secondary combustion. 4. A refuse incinerator system for agitating an unburned component contained in exhaust gas burned in an incinerator with secondary combustion air supplied from a secondary combustion air device and burning the mixture. The air pipe is composed of an aggregate of a plurality of pipes, each of the plurality of pipes has an independent valve, and each of the valves is selected according to a flow signal from a secondary combustion air device. An air blowing device for secondary combustion in a refuse incinerator, comprising: a valve control device for controlling the opening and closing of the refuse. 5. The air blowing device for secondary combustion in a refuse incinerator according to claim 4, wherein the plurality of tubes constituting the assembly have different cross-sectional areas and are joined to each other. 6. The air blowing device for secondary combustion in a refuse incinerator according to claim 4, wherein each of the plurality of tubes constituting the assembly has a rectangular cross section. 7. The air blowing device for secondary combustion in a refuse incinerator according to claim 4, wherein the aggregate of the plurality of tubes is a multi-tube. 8. The secondary combustion air blower in a refuse incinerator according to claim 4, wherein the plurality of tubes constituting the assembly are provided with nozzles each having a different opening area at the tip end, and are joined to each other. apparatus. 9. The air blowing device for secondary combustion in a refuse incinerator according to claim 8, wherein each of the plurality of tubes constituting the assembly and the nozzles provided therein have a rectangular cross section. 10. The assembly of a plurality of tubes comprises a multi-tube,
9. The air blowing device for secondary combustion in a refuse incinerator according to claim 8, wherein each nozzle is formed by a plurality of cylinders respectively inserted into the tips of the tubes forming the multi-tube. .