JPH0989242A - Regenerative burner and heating furnace with regenerative burner - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a regenerative burner capable of setting a wide combustion reaction area and use the regenerative burner to set a temperature uniform in the heating furnace with a relatively small number of regenerative burners. SOLUTION: This regenerative burner comprises a fuel injection nozzle 2 provided on a burner body 8 and having branch nozzles 2a and 2b at its tip ends, flow passages 3a, 3b provided symmetrically relative to the fuel injection nozzle 2 and having combustion air jetting ports 3A, 3B at their tip ends, and heat accumulators 1a, 1b connected at one ends thereof to the flow passages 3a, 3b and provided at the other ends thereof with pipes 7a, 7b which are connected to a change-over valve 6, the flow passages 3a, 3b forming an inclination angle α relative to an axial direction of the fuel injection nozzle 2 to enlarge an area of combustion. In this case, the use of the regenerative burner enables reducing a number of regenerative burners installed in a heating furnace and sets a temperature distribution uniform in the heating furnace.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a regenerative burner and a heating furnace provided with the regenerative burner, and more particularly to a regenerative burner for recovering sensible heat of combustion exhaust gas with a regenerator and preheating combustion air and its regenerative type. A heating furnace equipped with a burner,
It is equipped with a combustion mechanism that can form a combustion region in which the flame injection direction injected from the heat storage burner is different from the flame injection direction of a normal heat storage burner, and the combustion mechanism can uniformly heat the furnace space. The present invention relates to a heat storage type burner that can be used and a heating furnace including the heat storage burner.

[0002]

2. Description of the Related Art Conventionally, as an example of a burner for preheating combustion air with sensible heat of combustion exhaust gas to save energy,
There is a regenerative burner as shown in FIGS. 8 (a) and 8 (b).
The figure (a) is sectional drawing of the heat storage type burner disclosed by Unexamined Utility Model Publication No. 6-46138, and the figure (b) is its front view. In the figure, the regenerative burner 10 is a combination of a burner body 22 and regenerators 99a and 99b. The burner body 22 has a nozzle insertion port 44 and a flow passage 55.
a, 55b and holes 66a, 66b are provided, the fuel injection nozzle 77 is inserted into the nozzle insertion port 44, and the flow passage 55
a and 55b are heat storage bodies 99 through connecting pipes 88a and 88b.
a and 99b, respectively.

Next, the piping system of the regenerative burner 10 will be described with reference to FIG. 9. The fuel injection nozzle 77 is connected to the fuel supply source 13 via the control valve 11 and the flow rate adjusting valve 12. The heat storage body 99a is connected to the switching valves 14a and 16a, is connected to the blower 15 which is a combustion air supply source via the switching valve 14a, and is connected to the fan 17 which is an exhaust gas suction source via the switching valve 16a. Similarly, the heat storage body 99b is connected to the switching valves 14b and 16b, and the switching valve 1
4b is connected to a blower 15 which is a combustion air supply source, and a fan 1 which is an exhaust gas suction source is connected via a switching valve 16b.
7 is connected.

Next, the combustion and exhaust of this heat storage type burner will be described. Fuel gas is continuously supplied from the fuel injection nozzle 77 into the heating furnace, and the combustion air is blower 1
5 through the switching valve 14a, the heat storage body 99a, the flow path 55a
And is injected into the furnace for combustion. Channel 5
The combustion exhaust gas from 5b is sucked by the fan 17 through the heat storage body 99b and the switching valve 16b, and the combustion exhaust gas is discharged to the outside of the furnace. At that time, the sensible heat of the combustion exhaust gas is absorbed by the heat storage body. This heat storage type burner is provided with flow passages on both sides of the fuel injection nozzle, and performs alternating combustion in which the jetting of combustion air and the suction of combustion exhaust gas are switched at regular intervals. Combustion air becomes hot preheated air when passing through the heated heat storage body and is supplied into the furnace.

In the heat storage type burner, as shown in FIG. 9, the combustion flame F is formed substantially parallel to the burner axis C, and the temperature of the burner axis C is almost the same as the combustion flame F as shown in FIG.
Is formed along. In addition, as for the flow of the combustion exhaust gas, a standing gas flow is formed as shown by the arrow. As described above, in the conventional regenerative burner, the sensible heat of the combustion exhaust gas is recovered by the regenerator and supplied to the heating furnace as high-temperature preheated air by the switching combustion, thereby providing a heating furnace with high thermal efficiency.

The heating furnace of FIGS. 10 and 11 shows a heating furnace equipped with the regenerative burner of FIG. The heating furnace of FIG. 10 is a heating furnace in which heat storage burners 10A and 10B are arranged diagonally, that is, so-called heat storage burners are arranged in a staggered manner. When the heat storage burner is arranged as described above, the combustion exhaust gas flow in the furnace is as shown in FIG.
The flame F of each regenerative burner is along the axis of the fuel injection nozzle, and the stationary combustion gas flow in the heating furnace
Occurs. Therefore, by arranging the regenerative burner in such a manner, it is a combustion method that realizes a uniform temperature distribution in the heating furnace and realizes efficient heating.

Further, in the heating furnace 20 shown in FIG. 11, the regenerative burners 10A and 10B are arranged on the same furnace wall,
A combustion method in which these regenerative burners are alternately burned to generate a non-stationary flow of combustion gas in the furnace to form a uniform temperature distribution in the heating furnace 20 and realize efficient heating. Is.

[0008]

In the conventional regenerative burner, since the combustion region is formed in the axial direction of the fuel injection nozzle, as shown in FIG. 10, the regenerative burners are arranged in a staggered manner in the heating furnace. The temperature distribution is uniform and the heating is performed.
When the temperature distribution in the heating furnace is made uniform, it is necessary to set the arrangement of the regenerative burner in consideration of the combustion area of the regenerative burner. Therefore, depending on the shape of the heating furnace, FIG.
As shown in No. 2 of the heating furnace, a regenerative burner is arranged on the same furnace wall for uniform temperature distribution in the heating furnace for heating.

As described above, the conventional regenerative burner has a relatively narrow combustion region, and therefore the regenerative burner must be mounted on the wall of the heating furnace in consideration of the combustion region. Therefore, the number of installed regenerative burners tends to increase, and efficient heating is realized by making the temperature distribution in the heating furnace uniform. As a result, in the conventional combustion method using the regenerative burner, it is necessary to form the combustor by using a large number of regenerative burners, which results in a high facility cost of the heating furnace.

Further, according to the conventional regenerative burner, a plurality of regenerative burners are installed in the heating furnace, which has a drawback that the number of switching valves for supplying combustion air and fuel increases. In other words, there is a drawback that the number of inspections of the switching valves that control combustion of the heating furnace increases, and because the number of installed switching valves increases, the probability that the switching valves will fail increases, the frequency of equipment failure increases, and maintenance of the heating furnace increases. It has the drawback of being expensive.

The present invention has been made in view of the above-mentioned problems, and provides a regenerative burner in which a combustion reaction region can be widely set, and a temperature in a heating furnace can be made uniform with a relatively small number of burners. An object of the present invention is to provide a heating furnace provided with a heat storage type burner that can be used.

[0012]

The present invention has been made in order to solve the above-mentioned problems, and the invention according to claim 1 is to provide a fuel injection nozzle in the center of the burner body, and to arrange the fuel injection nozzle shaft core in the fuel injection nozzle axis. On the other hand, heat storage characterized in that a flow path for ejecting combustion air into the heating furnace at an inclination angle α is provided in the burner body on both sides of the fuel injection nozzle, and a heat storage body is connected in series to the flow path. It is a formula burner.

In the invention according to claim 2, the burner main body provided on the side wall of the heating furnace, the fuel injection nozzle provided at the center of the burner main body, and the burner main body on both sides of the fuel injection nozzle are provided. A flow path is provided, through which the combustion air passes at an inclination angle α with respect to the fuel injection nozzle, and the combustion air is ejected from the combustion air ejection port at the tip thereof, and the flow path whose one end is the combustion air ejection port. A heat storage type burner characterized by comprising a heat storage body connected to the other end.

According to the first or second aspect of the present invention, the flow path is formed in the nozzle body so that the combustion air is injected at a predetermined inclination angle α with respect to the axis of the fuel injection nozzle. The combustion flame spreads in the heating furnace at a predetermined injection angle α according to α, so that the combustion region expands and the flow of the combustion gas is alternating combustion, so that the flow of the combustion gas flows in the opposite direction at a predetermined cycle. As a result, the combustion gas flow is made non-stationary, and the temperature in the heating furnace is made uniform so that the heating is performed.

The invention according to claim 3 is the same as claim 1
In the heat storage type burner according to [4], the inclination angle α is 30.
This is a heat storage type burner characterized by being in the range of 60 ° to 60 °. When the inclination angle α is 30 ° or less, the combustion range is reduced, which is not preferable. The range of 30 ° to 60 ° is optimal because it has a drawback that heating of the burned region is insufficient, and the burner body also includes a burning region to easily suffer heat damage.

According to the invention described in claim 4, a fuel injection nozzle is provided in the center of the burner body, and the flow of combustion air on both sides of the fuel injection nozzle which is inclined at an angle α outward from the axis of the fuel injection nozzle. Paths are respectively provided in the burner body, and a heat storage type burner, which is provided with a heat storage body respectively connected to the flow path, is installed in the heating furnace, and combustion air is supplied from one flow path of the heat storage type burner. Alternately performing jetting and suction of combustion exhaust gas from the other flow path to set the temperature distribution in the furnace as a non-stationary flow of the combustion reaction gas in the heating furnace. It is a heating furnace equipped with a burner. According to the present invention, the regenerative burner is provided with a fuel injection nozzle and a pair of flow passages, and these flow passages are inclined outward at a predetermined angle α with respect to the axis of the fuel injection nozzle, and the fuel is provided at the tip thereof. A jet port is provided, and a combustion region is formed at an angle α with respect to the furnace wall. The combustion area in one regenerative burner can be expanded, and even with one regenerative burner, the flow of the combustion reaction gas can be made non-stationary by alternating combustion, so that the combustion reaction gas The flow is periodically disturbed to form a heating furnace capable of heating while keeping the temperature inside the heating furnace uniform.

[0017]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 is a sectional view showing a regenerative burner according to the present invention and a heating furnace provided with the regenerative burner, and FIG. 2 is a front view of the regenerative burner. In FIG. 1, the regenerative burner 1 comprises a pair of regenerators 1 a and 1 b, a fuel injection nozzle 2 and a burner body 8. The tip of the fuel injection nozzle 2 is branched at a predetermined angle with respect to the nozzle axis C of the fuel injection nozzle.
a and 2b are formed. The tip of the fuel injection nozzle 2 including the branch nozzles 2a and 2b is formed in the burner body 8. The burner body 8 is further provided with flow paths 3a and 3b through which combustion air passes, symmetrically with respect to the fuel injection nozzle 2.
Combustion air ejection ports 3A and 3B are formed to eject combustion air into the furnace. The flow paths 3a and 3b have an angle α outside the nozzle axis C so that the combustion air ejected from the combustion air outlets 3A and 3B is directed toward the nozzle axis C at an angle α. The slope is given. Channel 3a,
Combustion air outlets 3A and 3B are formed at one end of 3b, and heat accumulators 1a and 1b are connected to the other ends thereof. The heat accumulators 1a and 1b are the heat storage body container 5
Heat storage bodies 4a and 4b are housed in a and 5b, respectively. One of the heat accumulators 1a and 1b is provided with the flow paths 3a and 3b, respectively.
To the pipes 7a and 7b, respectively. The ends of the pipes 7a and 7b are connected to the switching valve 6. The fuel injection nozzle 2 is provided with a shutoff valve 11. The regenerative burner has a burner body 8 mounted on the side wall of a heating furnace 9.

The heat storage bodies 4a and 4b are preferably made of a material having a large specific surface area, good air permeability and high heat resistance, and a ceramic honeycomb structure is most suitable. May be Further, the branch nozzles 2a and 2b and the flow paths 3a and 3b are cylindrical tubes, and the cross-sectional shape thereof is circular, but it is obvious that they may be elliptical or quadrangular. In FIG. 2, although the combustion air jets 3A and 3B are shown in an elliptical shape, the flow passages 3a and 3b are cylindrical, and the exposed shape of the combustion air jets 3A and 3B inside the furnace is the flow passage. It is shown in an elliptical shape because it is an oblique section of 3a and 3b.

Next, regarding the piping system of the regenerative burner 1,
This will be described with reference to FIGS. 1 and 3. In FIG. 1, the pipes 7 a and 7 b connected to the regenerative burner 1 are connected to the switching valve 6. The switching valve 6 for switching the supply of combustion air and the exhaust of combustion exhaust gas is provided with a valve 6C, the branch port 6A of which is connected to the fan and the branch port 6B of which is connected to the blower. The switching valve 6 is set so that combustion air is supplied to one heat storage burner 1a and combustion exhaust gas is discharged from the other heat storage burner 1b. The switching state of the switching valve 6 is represented by shutoff valves 6a to 6d in FIG.
Further, individual cutoff valves 6a to 6d may be used in place of the switching valve 6, and the piping system thereof will be described with reference to FIG. 3. The cutoff valves 6a and 6b are connected to the fan 17, and the cutoff valves 6c and 6c.
6d is connected to the blower 15. Further, the fuel injection nozzle 2 is connected to the fuel supply source 13 via the shutoff valve 11 and the flow rate control valve 12, and the same applies to the piping system in the case of FIG.

On the other hand, as shown in FIG. 1, the flow passages 3a and 3b through which the combustion air or combustion exhaust gas passes are inclined outward at an angle α with respect to the axis C of the fuel injection nozzle 2, and the nozzle body is inclined. On the furnace side of 8, the ends of the flow paths 3a and 3b are opened as combustion air jets 3A and 3B. Therefore,
Combustion air is injected into the furnace from the combustion air jet port 3A or 3B at an injection angle α with respect to the nozzle axis C. Similarly, the branch nozzles 2a and 2b of the fuel injection nozzle 2 are branched along the flow paths 3a and 3b at a predetermined angle with respect to the axis C, respectively. The inclination angle α of the flow paths 3a, 3b through which the combustion air or the combustion exhaust gas passes is set outside the axis C of the fuel injection nozzle in the range of 30 ° to 60 °. Generally, it is set in the range of 30 ° to 60 ° with respect to the side wall of the heating furnace 9. If the inclination angle α is 30 ° or less, the advantage over the conventional heat storage type burner is lost, so 30 ° or more is desirable. Further, if the inclination angle α is 60 ° or more, the combustion flame may directly heat the side wall of the burner body 8 or the heating furnace 9 to cause damage, and it is preferably 60 ° or less. Therefore, in this embodiment, the inclination angle α is 45 ° ±
The range of 15 ° is the allowable range.

Further, as shown in FIG. 2, the distance L between the fuel air jet port 3A and the branch nozzle 2a and the distance L between the fuel air jet port 3B and the branch nozzle 2b are equal to each other.
It is preferably 1.5 times or more and 3 times or less than the diameter D of A and 3B. NOx generated when the distance L is too small
As the amount increases, there arises a problem that the ejection angle α of the fuel air ejection port cannot be secured. On the other hand, if the distance L is too large, the reaction between the fuel and the fuel air is delayed and unburned gas (for example, CO gas) is generated, which causes a problem of being included in the combustion exhaust gas. Therefore, in the present embodiment, the above range is suitable.

Next, the combustion / exhaust of the heating furnace equipped with the regenerative burner according to the above embodiment will be described with reference to FIGS. In FIG. 1, the combustion air is supplied from the branch port 6B of the switching valve 6 to the heat storage body 4a via the pipe 7a, and the combustion air is preheated via the heated heat storage body 4a to become high-temperature preheated air for combustion. It is ejected from the air ejection port 3A into the furnace. On the other hand, fuel is continuously supplied from the fuel injection nozzle 2 into the furnace. The fuel reacts with the combustion air and burns. On the other hand, the combustion exhaust gas passes through the flow path 3b and the heat storage body 4b.
And is exhausted from the branch port 6A to the outside of the furnace via the switching valve 6. Further, in FIG. 3, the combustion air is shut off by the shutoff valve 6c.
Is supplied to the heat storage body 4a via the flow path 3a and is jetted into the furnace from the combustion air jet port 3A at a predetermined jet angle α via the flow path 3a. On the other hand, the fuel gas is continuously ejected from the fuel supply source 13 through the flow rate adjusting valve 12 and the shutoff valve 11 through the branch nozzles 2a and 2b. The combustion exhaust gas passes through the heat storage body 4b through the flow path 3b and is exhausted from the blower 17 to the outside of the furnace through the cutoff valve 6b.

As shown in FIG. 1, the combustion air is ejected along the flow path 3a from the combustion air ejection port 3A at an inclination angle α with respect to the burner axis direction, and the combustion air is ejected to the position of the region I in general. It The fuel gas is dragged by the ejector effect due to the flow of the combustion air, and a large amount of fuel gas is ejected to the fuel nozzle 2a side and flows to the position of region II in general. The combustion exhaust gas in the furnace is diffused and mixed with the combustion air while being entrained as shown by the arrow X, and burned, and the combustion reaction is generally located in the region III. The combustion exhaust gas is sucked from the combustion air jet port 3B, and the sensible heat of the combustion exhaust gas heats the heat storage body 4b,
The gas is exhausted outside the furnace via the switching valve 6.

When the combustion reaction at the position of the region III continues for a certain time, the combustion reaction is switched to the position of the region IV by the switching operation of the valve 6C of the switching valve 6. In this combustion state, the combustion air flows through the heat storage body 4b into the combustion air jet port 3B.
Squirted from. The fuel gas is continuously ejected from the fuel gas supply source through the branch nozzles 2a and 2b, and the fuel gas is dragged by the ejector effect due to the flow of the combustion air discharged from the combustion air ejection port 3B and is thus ejected on the fuel nozzle 2b side. More fuel is injected and the combustion exhaust gas in the furnace is entrained and diffusely mixed with the combustion air and burned. This combustion reaction generally takes place at the position of region IV. The combustion exhaust gas is sucked into the heat storage body 4a from the flow path 3a through the combustion air jet port 3A,
The sensible heat of the combustion exhaust gas heats the heat storage body 4 a, and the heat is discharged to the outside of the furnace via the switching valve 6.

In the heating furnace equipped with the regenerative burner of the above embodiment, the jetting direction of the combustion air changes at a predetermined cycle depending on the jetting angle, so that the combustion reaction occurs even if the combustion is performed by a single regenerative burner. The area will change in a predetermined cycle. At the same time, the direction in which the generated combustion exhaust gas flows also changes. Therefore, when one is in the combustion state, the flow is stationary in the heating furnace, but when the combustion reaction region is switched, the combustion gas is disturbed in the heating furnace, that is, the gas in the furnace is disturbed. The combustion gas flow in the furnace is non-stationary because the flow alternates its direction. As described above, the non-stationary flow in the heating furnace is effective in uniformly setting the temperature in the furnace. Further, the combustion gas is a combustion air ejection port 3 for ejecting combustion air and drawing in combustion exhaust gas.
A and 3B are provided in close proximity to each other, and the low N is used because the combustion exhaust gas in the furnace is entrained and diffusely mixed with air for combustion.
Ox combustion becomes possible, and the amount of NOx in exhaust gas can be reduced.

Next, another embodiment of the heat storage type burner according to the present invention will be described with reference to FIG. In the embodiment of FIG. 4, the same parts as those of the embodiment of FIG. 1 are designated by the same reference numerals. In FIG. 4A, the structure of the fuel injection nozzle 2 is different, and the tip of the fuel injection nozzle 2 is a straight pipe. The regenerators 1a and 1b have regenerators 5a and 5b respectively accommodating the regenerators 4a and 4b, and the flow channels 3a and 5b.
3b is inclined outwardly at an angle α with respect to the nozzle axis direction C, and the combustion air jet port 3A, 3A,
3B is opened. The burner body 8 is formed of a combustion tile or the like. Further, the fuel injection nozzle 2 is provided with a fuel cutoff valve 11, and its piping system is the same as that in FIG.

Further, as shown in FIG. 4 (b), the distance L between the combustion air jets 3A, 3B and the combustion air jet burner 2 is L.
Is set to be in a range of at least 1 time and not more than 3 times the diameter D of the combustion air ejection ports 3A, 3B. The reason why the distance L is set to be in the range of at least 1 time and not more than 3 times the diameter D of the combustion air jets 3A and 3B is that the distance L between the fuel injection nozzle 2 and the combustion air jets 3A or 3B is too small. There is a problem that the amount of nitrogen oxides (NOx) generated is increased, and the ejection angle α of the combustion air ejected from the combustion air ejection ports 3A and 3B.
This is because there arises a problem that cannot be sufficiently secured.

On the other hand, if the distance L is too large, the reaction between the fuel and the combustion air is delayed and unburned gas (for example, CO gas)
Therefore, the above range is preferable in the present embodiment because there is a problem that the above occurs and suction and exhaust are performed from the combustion air jet port.

Further, the inclination angle α of the flow path, that is, the range of the injection angle α of the combustion air jet is set to the range of 30 ° to 60 °. For the same reason as described above, when the injection angle α is too small, for example, when the injection angle α is 30 ° or less, the moving range of the combustion reaction region becomes narrow and the wide range can be heated uniformly. There is a drawback that you can not do it. Further, if the injection angle α is too large, for example, the injection angle α becomes 6
If it is 0 ° or more, the combustion region is formed in the vicinity of the furnace wall, the flame may directly collide with the furnace wall, and the burner tile or the furnace wall may be easily damaged by heat. The above range is preferable because it causes a problem that it is difficult to heat the place.

Next, the combustion / exhaust operation of the heat storage type burner of FIG. 4 is similar to the embodiment of FIG. The fuel is continuously injected from the combustion air injection nozzle 2 into the furnace, and the combustion air is ejected into the furnace from the combustion air ejection port 3A through the heat storage body 4a and burns. At that time, the combustion air is preheated to a high temperature by the heat storage body 4a, the combustion exhaust gas passes through the heat storage body 4b, and the sensible heat of the combustion exhaust gas is stored in the heat storage body 4b. The combustion region III has an angle α with respect to the axis of the fuel injection nozzle 2. When this combustion / exhaust state has passed for a certain time, the switching valve 6 is activated, and the combustion air is ejected from the combustion air ejection port 3B through the heat storage body 4b into the furnace for combustion. At that time, the combustion air is preheated to a high temperature by the heat storage body 4b and jetted into the furnace for combustion. It becomes the combustion area IV. The combustion exhaust gas is discharged from the combustion air jet port 3A to the outside of the furnace via the switching valve 6. The combustion regions III and IV are switched alternately, the gas flow becomes non-stationary, the gas flow in the heating furnace is periodically disturbed, and the temperature in the heating furnace becomes uniform.

Next, an embodiment in which the regenerative burner of the present invention is installed in a heating furnace will be described. FIG. 5 shows an embodiment used in a relatively small heating furnace, in which the regenerative burner 1 is provided on one side wall of the heating furnace 9. Fuel gas is continuously supplied from the fuel injection nozzle 2 into the furnace, and combustion air is about 3
The combustion air jet ports 3A and 3B are switched and injected at a cycle of 0 second, the combustion regions I and IV are switched, and the flow of combustion gas alternately occurs to become a non-stationary flow. Therefore, the temperature in the furnace can be easily and uniformly set. When the combustion regions I and IV are switched, the combustion gas flows collide with each other to disturb the gas flow, stirring the combustion atmosphere in the heating furnace and making the temperature inside the furnace uniform. In the heating furnace of FIG. 5, it was necessary to provide two heat storage burners in the conventional combustion method, but in this embodiment, one heat storage burner can be provided to uniformly control the temperature in the furnace. . Of course, the piping system can be simplified.

FIG. 6 illustrates another embodiment in which the regenerative burner of the present invention is installed in a heating furnace. The heating furnace shown in the figure is a heating furnace that is larger in the longitudinal direction than the embodiment of FIG. 5, and four units must be provided in the conventional regenerative burner.
In this embodiment, two regenerative burners 1A and 1B are arranged on both side walls of the heating furnace 9. Explaining the combustion / exhaust state of this embodiment, first, combustion is carried out in combustion regions B and C shown by solid lines to form a combustion gas flow, and about 30
After a lapse of seconds, combustion is carried out in combustion regions A and D shown by dotted lines to form a combustion gas flow. After about 30 seconds have passed, the combustion regions B and C are switched. The combustion gas flow is alternately repeated to uniformly control the temperature in the heating furnace. Further, when the combustion air is ejected from one of the combustion air jets of the regenerative burner 1A to be in a combustion state, the combustion exhaust gas is sucked into the heat accumulator from the other combustion air jet. As in the embodiment of FIG. 5, the combustion gas flow is also non-stationary, and the temperature inside the furnace can be easily made uniform by stirring the atmosphere inside the furnace. Of course, since the algebra of the heat storage type burner can be reduced, the piping system can be simplified.

FIG. 7 illustrates another embodiment in which the regenerative burner of the present invention is installed in a heating furnace. The figure shows a heating furnace 9
The regenerative burners 1A and 1C are respectively arranged on the side walls of the. The heat storage type burner 1A is of the above-mentioned embodiment, and the heat storage type burner 1C is of the conventional type. By combining the heat storage type burner in this way, the flow of the combustion gas and the combustion exhaust gas can be made non-stationary, so that the temperature inside the heating furnace 9 can be easily made uniform.

In this embodiment, first, combustion is performed in the combustion region A to form a combustion gas flow, and after about 30 seconds have elapsed, combustion is performed in the combustion region B to form a combustion gas flow. Further, after about 30 seconds have passed, a combustion gas flow is formed by the regenerative burner 1C. This burning time is
For example, the combustion time may be shorter than 30 seconds. The combustion gas flow becomes a non-stationary flow by alternately repeating, and the temperature in the heating furnace is easily controlled to be uniform. As described above, the heating furnace of FIG. 7 is a combustion control method in which a standing flow and a non-standing flow of combustion gas are alternately generated to uniformly control the temperature in the furnace, and the heat storage of the embodiment is performed. By using the formula burner, the temperature distribution in the heating furnace 9 can be made uniform with high accuracy.

As described above, the regenerative burner according to the present invention is provided with a pair of combustion air jets symmetrically with respect to the fuel injection nozzle, and the axial direction of the fuel injection nozzle is different from the conventional one. The combustion region is not formed in the fuel injection nozzle, but the combustion region is formed at a predetermined injection angle α with respect to the axial direction of the fuel injection nozzle. By alternating the combustion areas in the heating furnace by alternating combustion, a combustion field different from the conventional one is easily formed, and non-stationary combustion gas and flue gas flows are formed, and the temperature inside the furnace is changed. It can be set uniformly.

[0036]

As described above, according to the present invention, a combustion region can be formed in the heating furnace at a predetermined angle with respect to the nozzle axis direction. Therefore, unlike the conventional regenerative burner, There is an advantage that a combustion field can be formed at a predetermined angle with respect to the furnace wall, and there is an advantage that a regenerative burner capable of expanding the uniform heating space capacity in a single burner can be provided. Further, according to the heat storage type burner of the present invention, although it depends on the shape of the heating furnace and the inner volume of the furnace, even if the heating furnace has conventionally used two heat storage type burners, one heat storage type burner. Therefore, it is extremely effective in reducing the equipment cost of the combustion device.

Further, according to the regenerative burner of the present invention, the regenerative burner is provided with a pair of combustion air jets for ejecting combustion air in different directions. Since the flow of the combustion air in the opposite direction, that is, the non-stationary flow of the combustion gas can be easily formed in the furnace, it is extremely effective in uniformly designing the temperature distribution in the furnace.

Further, by using the heat storage type burner of the present invention or in combination with the heat storage type burner of the conventional method, it is possible to heat the heating furnace in a state in which the temperature distribution in the heating furnace is extremely uniform. There is an advantage that a relatively inexpensive heating furnace can be easily provided. Further, according to the heating furnace using the heat storage type burner of the present invention, since the combustion efficiency is improved, there is an advantage that a heating furnace capable of reducing the generation of harmful substances such as CO gas and NOx can be provided.

[Brief description of drawings]

FIG. 1 is a cross-sectional view showing an embodiment of a regenerative burner according to the present invention.

FIG. 2 is a front view of the regenerative burner of FIG.

FIG. 3 is a diagram showing a piping system of the heat storage burner of FIG.

FIG. 4 is a view showing another embodiment of the heat storage type burner according to the present invention.

FIG. 5 is a view showing a heating furnace provided with a regenerative burner according to the present invention.

FIG. 6 is a view showing another embodiment of the heating furnace provided with the heat storage burner according to the present invention.

FIG. 7 is a view showing another embodiment of the heating furnace provided with the heat storage burner according to the present invention.

FIG. 8 is a diagram showing an example of a conventional regenerative burner.

FIG. 9 is a diagram showing a piping system of a conventional heat storage burner.

FIG. 10 is a diagram showing an example of a heating furnace including a conventional regenerative burner.

FIG. 11 is a diagram showing an example of a heating furnace including a conventional regenerative burner.

[Explanation of symbols]

 1 Heat Storage Type Burner 2 Fuel Injection Nozzle 2a, 2b Fuel Injection Nozzle 3A, 3B Combustion Air Jet 3a, 3b Flow Path 4a, 4b Heat Storage Body 5a, 5b Heat Storage Housing Container 6 Switching Valve 7a, 7b Piping 8 Burner Main Body 9 Heating Furnace

Claims (4)

[Claims] 1. A fuel injection nozzle is provided at the center of a burner body, and a flow path for ejecting combustion air into a heating furnace at an inclination angle α with respect to the axis of the fuel injection nozzle is provided on both sides of the fuel injection nozzle. A regenerative burner, characterized in that it is provided in the main body, and a regenerator is connected to the flow path. 2. A burner main body provided on a side wall of a heating furnace, a fuel injection nozzle provided at the center of the burner main body, and burner main bodies provided on both sides of the fuel injection nozzle with respect to the fuel injection nozzle. And a flow passage through which combustion air passes at an inclination angle α and jets the combustion air from the combustion air jet at its tip, and a heat storage body connected to the other end of the flow passage whose one end is the combustion air jet. A heat storage type burner characterized by comprising: 3. The regenerative burner according to claim 1, wherein the inclination angle α is in the range of 30 ° to 60 °. 4. A fuel injection nozzle is provided in the center of the burner main body, and a flow passage through which combustion air inclined at an angle α from the axis of the fuel injection nozzle to the outside is provided on each side of the fuel injection nozzle. Further, a heat storage type burner, which is provided with a heat storage body respectively connected to the flow path, is installed in a heating furnace, and the combustion air is ejected from one flow path of the heat storage type burner and the combustion exhaust gas from the other flow path. The heating furnace having a regenerative burner is characterized in that the temperature distribution in the furnace is set by making the flow of the combustion reaction gas in the heating furnace non-stationary by alternately performing the suction of the above.