JPH10122552A - Regenerative burner - Google Patents

Abstract

PROBLEM TO BE SOLVED: To allow a regenerative burner to have a durability irrespective of honeycomb shape or a pellet shape, facilitate its maintenance work, and reduce NOx by a method wherein a storing chamber storing the regenerative body is arranged at an end part spaced apart from a wall of a combustion chamber at a passage section, and a changing-over means is fixed to the storing chamber. SOLUTION: A passage 12 has a suspending section 12b bent substantially orthogonally from the rear end of a cylindrical main body 12a. A storing chamber H having regenerative body 20 with aeration characteristic is arranged at its end, a position spaced apart from a side wall 1a of a combustion chamber 1. Discharged gas passed through the furnace through a passage T and combustion air blown from a blower means are alternatively flowed in the regenerative body 20 for every 5 to 60 seconds by a changing-over means 30 (a ratio of a total area of the passage T through which the combustion air flows to a total area of the passage T through which the discharged gas is sucked: 0.1 to 0.5) which can be removably fixed to the storing chamber H, heated by discharged gas (approximately 1100 deg.C) and the combustion air is heated with the regenerative body 20 at a high temperature.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a regenerative burner that heats combustion air using heat from exhaust gas, and more particularly to a regenerative burner that reduces NOx and facilitates dust treatment.

[0002]

2. Description of the Related Art In recent industrial furnaces, in order to save energy, a regenerative burner for heating combustion air by using heat of exhaust gas after combustion is used.

This regenerative burner is disclosed in, for example,
113,509 and JP-A-8-166,123.

[0004] These regenerative burners are generally made of a heat-resistant material and alternate between combustion air introduced into a combustion chamber of a furnace and exhaust gas burned in the combustion chamber of the furnace. By passing the gas through the combustion chamber, heated combustion air is introduced into the combustion chamber, and the exhaust gas is discharged by applying heat to the heat storage body.

In this case, when the heat storage body is provided near the furnace, and the heat storage body and the passage portion through which the combustion air and the exhaust gas flow are relatively rotated, the heated combustion air is continuously supplied into the furnace. Operation is possible, and the structure is simpler than that in which a heat exchanger for heat recovery is separately provided to heat the combustion air, and the combustion air is immediately heated by the heat storage material heated by the exhaust gas. Therefore, there is an advantage that the energy saving effect is high.

[0006]

However, in this regenerative burner, if the regenerator is provided at or near the wall of the combustion chamber of the furnace, the durability of the regenerator becomes a problem. When the heat of the exhaust gas is taken into the regenerator and the combustion air is heated by this heat, it is preferable to heat the regenerator using the exhaust gas immediately after being discharged from the combustion chamber, but when it is too close to the combustion chamber, In addition, there is a problem that the exhaust gas drifts and the heat storage body is easily damaged. In particular, when this heat storage body is divided into a number of independent small channels by a partition wall, and is configured by what is called a honeycomb shape, the thickness of the partition wall is excessively increased in order to increase heat exchange efficiency. Thinner,
Since the diameter of each small flow path is made as small as possible, the durability is further reduced.

[0007] Further, since exhaust gas after combustion contains dust and the like, dust and the like adhere to a honeycomb-shaped heat storage body having a large number of small holes when used for a long time. There is also a problem that it is difficult to perform maintenance for processing.

[0008] Furthermore, the honeycomb-shaped heat storage element has a disadvantage that it is more expensive than the so-called pellet-shaped heat storage element because of its complicated production.

SUMMARY OF THE INVENTION The present invention has been made to solve the above-mentioned problems associated with the prior art, and is durable regardless of whether the heat storage body is in the form of a honeycomb or pellets, is easy to perform maintenance, and is cost-effective. It is a first object to provide a regenerative burner which is also advantageous.

[0010] A second object of the present invention is to provide a regenerative burner for reducing NOx.

A third object of the present invention is to make sure that the switching means for circulating exhaust gas and combustion air through a plurality of passages has a reliable operation, has a simple structure, and has durability.

A fourth object of the present invention is to provide a regenerative burner that can easily treat dust.

[0015] A fifth object of the present invention is to provide a regenerative burner which has good flammability and easily enters exhaust gas.

[0014]

According to the first aspect of the present invention, there is provided a fuel cell system having a plurality of passages having a plurality of passages parallel to the combustion nozzle. The exhaust gas from the combustion chamber and the combustion air from the air supply means are alternately flown in a predetermined passage of the passage portion by switching the exhaust gas from the combustion chamber and the combustion air from the air supply means by the switching means. In a regenerative burner in which heated combustion air is heated by a heated air-permeable heat storage body to guide the combustion air to the combustion chamber, the heat storage body is housed at an end of the passage portion separated from a wall of the combustion chamber. A storage chamber is provided, and the switching means is attached to the storage chamber.

According to this configuration, since the heat storage body and the switching means are separated from the combustion chamber, the durability is improved.
Since the switching means is attached to the end of the passage, maintenance can be easily performed.

Here, "combustion air" is a general term for a gas containing oxygen atoms such as pure oxygen and nitrogen oxide or a mixed gas of oxygen gas such as air and oxygen-enriched air. It does not matter whether the “heat storage body” is a honeycomb-shaped one or a pellet-shaped one.

According to a second aspect of the present invention, the switching means is characterized in that, among the plurality of passages, the total area of the passage through which the combustion air flows is smaller than the total area of the passage through which the exhaust gas is sucked. I do.

With this arrangement, since the exhaust gas having a lower oxygen concentration than the combustion air becomes larger around the fuel ejected from the combustion nozzle, the fuel does not burn rapidly and the flame temperature is averaged. , Slow combustion, and the generation of NOx is suppressed.

According to a third aspect of the present invention, the switching means is arranged so that the ratio of the total area of the passage through which the combustion air flows to the total area of the passage through which the exhaust gas is sucked is 0.1 to 0.5. Features.

In this manner, the NOx reduction is achieved by the slow combustion, the pressure loss when the combustion air flows is small, and a highly practical regenerative burner can be obtained.

According to a fourth aspect of the present invention, the switching means has a switching chamber in the case, the exhaust chamber or the air chamber is provided inside the switching chamber, and the air chamber or the exhaust gas chamber is provided outside the switching chamber. The switching chamber is partitioned into small chambers, and the small chambers are communicated with the passages, and the small chambers are opened with side wall through holes so as to communicate with the air chambers and the exhaust gas chambers. And by rotating a switching member formed of a rotary plate having a through-hole opened so as to coincide with a predetermined position, the small chamber and the air chamber or the exhaust gas chamber are selectively connected to each other. Features.

In this way, when the number of the plurality of passages formed in the passage portion is relatively small, a switching means for easily switching and applying the exhaust gas and the combustion air to each passage can be formed, and the structure is simplified. Therefore, the switching operation is also reliable and has durability.

According to a fifth aspect of the present invention, the switching means rotates the switching member formed of the rotating plate by a single drive source.

According to this configuration, the structure of the switching means for switching between the exhaust gas and the combustion air is extremely simple, and the cost is also advantageous.

According to a sixth aspect of the present invention, the switching means is such that the switching members formed of rotating plates provided in each of the small chambers are rotated by independent driving sources.

In this way, when the number of the plurality of passages formed in the passage portion is relatively large, the formation of the switching means can be simplified.

In the invention described in claim 7, the switching means is provided so as to surround the lower part of the heat storage body provided at the end of the passage, and is provided so as to extend coaxially in the case. An air duct, which is communicated with a predetermined number of passages of the passages and is configured to introduce combustion air from an air supply means, and an air duct provided at an upper end of the air duct, and It has a closing plate that blocks communication between some of the passages and the air duct, and a rotation mechanism that rotates the air duct in the case. The air duct rotated by the rotation mechanism burns the heat storage body from the air duct. It is characterized in that air for use is guided, and exhaust gas after flowing through the heat storage body from a portion other than the air duct of the case is discharged to the outside.

In this way, even if the number of the plurality of passages formed in the passage portion increases, the size of the air duct is appropriately adjusted to easily switch the exhaust gas and the combustion air to each passage. Since the switching means to be applied can be formed and the structure is simple, the switching operation is reliable and has durability.

[0029] In the invention according to claim 8, the storage chamber has a heat storage body housed therein constituted by a pellet-shaped heat storage member, and has dust removing means for operating the heat storage member to remove dust and the like. It is characterized by the following.

In this way, when the pellet-shaped heat storage member is operated by rubbing while vibrating air, dust and the like can be easily removed during operation of the regenerative burner. If the pellet-shaped heat storage member is vibrated, the attached dust and the like can be dropped from the heat storage member and removed. In particular, when vibrating up and down, dust or the like adhering to the heat storage body can be dropped from the heat storage body and removed.

According to a ninth aspect of the present invention, in the storage chamber, the bottom plate is formed of a porous member.

[0032] In this manner, the broken fine pellet-shaped heat storage member or foreign matter adhering to the heat storage member is dropped from the bottom plate and removed, or is conveyed to the air flow and sent into the combustion chamber. The pellet-shaped heat storage member is always kept in a normal state, and can perform a combustion operation exhibiting a predetermined heat storage or heat exchange ability.

According to a tenth aspect of the present invention, the switching means is detachably attached to the accommodation chamber.

[0034] With this configuration, dust or the like adhering to the heat storage element can be dropped from the heat storage element only by rubbing the heat storage element in the storage chamber after removing the switching means from the storage chamber on the passage portion side. Therefore, the work of removing dust and the like can be performed easily and more completely, and the maintenance is easy.

According to the eleventh aspect, the passage portion is
The tip protrudes slightly from the wall of the combustion chamber, and a recess having a depth such that the tip of the combustion nozzle faces the bottom is formed in this protruding portion, and is cut off from the recess toward the outer circumference at a predetermined angle. The end opening of the passage is present on the slope formed by the step.

In this way, the flames are prevented from being blown off by the concave portions, and a stable flame can be obtained. Further, since the combustion air easily approaches the fuel, the combustion performance can be enhanced. Since the end opening of the passage is largely opened, the exhaust gas easily enters the passage.

In the twelfth aspect, the heat storage body is
It is characterized by comprising a short tubular heat storage member.

In this way, the short tubular heat storage member is
For example, the surface area is about twice as large as that of a ball-shaped heat storage member, the porosity at the time of filling is considerably large, and the heat absorption and heat radiation action is quick due to the small thickness, and the pressure loss when gas flows is small. Therefore, heat can be stored in a short time, the combustion air can be heated, and more excellent heat exchange ability can be exhibited.

According to a thirteenth aspect of the present invention, the switching means sets the time for switching between the exhaust gas from the combustion chamber and the combustion air from the air supply means to be 5 to 60 seconds. .

If the short tubular heat storage member is used, a predetermined heat storage or heat exchange ability can be exhibited in a short time, so that the time for switching between the exhaust gas from the combustion chamber and the combustion air from the air supply means is reduced. For a very short time of 5 to 60 seconds can exhibit a predetermined heat storage or heat exchange ability.

According to a fourteenth aspect of the present invention, the combustion nozzle is characterized in that a motive fluid composed of steam or high-speed air flows around or at the center.

This makes it possible to adjust the size, sharpness, and the like of the flame injected from the combustion nozzle, thereby increasing the flexibility of the flame and widening the range of controllability or versatility.

According to a fifteenth aspect of the present invention, there is provided a passage having an air passage for introducing combustion air from the air supply means into the combustion chamber and an exhaust gas passage for passing exhaust gas from the combustion chamber. Provide a heat storage body with ventilation,
A regenerative storage system in which the exhaust gas from the combustion chamber and the combustion air from the air supply unit are switched by a switching unit to flow alternately into the regenerator and the combustion air heated from the regenerator is introduced into the combustion chamber. In the burner, the heat storage body is constituted by a pellet-shaped heat storage member, and the heat storage member is provided with a conveyance unit that once carries the heat storage member out of the passage portion, removes dust, and then carries the dust storage member into the passage portion. .

In this way, even if the heat storage member in the form of a pellet is damaged, or if there is foreign matter that is often seen when the exhaust gas is contaminated, the damaged one is replaced or cleaned and then replaced. By carrying in again, the predetermined heat storage or heat exchange capability can be maintained continuously, and dust can be easily removed from the pellet-shaped heat storage member.

According to a sixteenth aspect of the present invention, the transfer means carries in a pellet-shaped heat storage member of substantially the same amount as the extracted pellet-shaped heat storage member.

In this way, the combustion operation can be continued while the pellet-shaped heat storage member exhibits a predetermined heat storage or heat exchange ability.

According to a seventeenth aspect of the present invention, in the transfer means, the bottom plate for supporting the pellet-shaped heat storage member is formed of a porous member.

In this way, the broken fine pellet-shaped heat storage member or foreign matter adhering to the heat storage member is dropped from the bottom plate and removed, or is conveyed to the air stream and sent into the combustion chamber, or the lower portion is removed. It is easy to fall and maintain a normal state all the time, and a combustion operation that exhibits a predetermined heat storage or heat exchange ability can be performed.

[0049] In the invention according to claim 18, the conveying means comprises a porous member in which the bottom plate is inclined at a predetermined angle, and the pellet-shaped heat storage member forms a layer having a substantially uniform thickness on the porous member. It is characterized by having such a configuration.

According to this structure, the heat storage member in the form of a pellet falls to the transfer means by its own weight and is carried in by the transfer means so as to have a predetermined thickness, thereby exhibiting a predetermined heat storage or heat exchange ability. Combustion operation can be performed continuously.

In the invention according to claim 19, the heat storage body is
It is characterized by comprising a short tubular heat storage member.

In this way, the short tubular heat storage member
For example, the surface area is about twice as large as that of a ball-shaped heat storage member, the porosity at the time of filling is considerably large, and the heat absorption and heat radiation action is quick due to the small thickness, and the pressure loss when gas flows is small. As it has the characteristic of becoming, it can store heat in a short time, heat the combustion air, show more excellent heat exchange capacity, and it is hard to fall, so make a layer of uniform thickness The heating can be carried out uniformly.

According to a twentieth aspect of the present invention, the switching means switches the exhaust gas from the combustion chamber and the combustion air from the air supply means for a period of 5 to 60 seconds. .

If the short tubular heat storage member is used, a predetermined heat storage or heat exchange capability can be exhibited in a short time, so that the time for switching between the exhaust gas from the combustion chamber and the combustion air from the air supply means is reduced. For a very short time of 5 to 60 seconds can exhibit a predetermined heat storage or heat exchange ability.

[0055]

Embodiments of the present invention will be described below in detail with reference to the drawings. FIG. 1 is a schematic longitudinal sectional view showing a state in which a regenerative burner according to a first embodiment of the present invention is attached to a combustion chamber wall of a heating furnace, and FIG.
3 is a sectional view taken along line 3-3 in FIG. 1, FIG. 4 is a sectional view taken along line 4-4 in FIG. 1, FIG.
FIG. 6 is a cross-sectional view taken along line 5-5 in FIG. 1, FIG. 6 is an explanatory view showing an operation state of the switching means of the embodiment, FIG. 7 is an explanatory view showing a gas flow state of the embodiment, FIG. Is a graph showing the state of NOx and combustion air pressure according to the embodiment.

(First Embodiment) First, the regenerative burner shown in FIG. 1 will be outlined. This regenerative burner 10
For example, the tip of a downwardly inclined passage portion 12 penetrates and attaches to a side wall 1a of a substantially sealed combustion chamber 1 made of a refractory material such as a refractory brick, and a combustion nozzle 11 provided in the passage portion 12 is provided. Fuel and primary air are sent into the furnace, and the combustion air (arrows in the figure) blown from blowing means (not shown) such as a blower is fed into the furnace through the heat storage unit 20, Exhaust gas (open arrow in the figure) after burning in the combustion chamber 1 is also discharged into the atmosphere through the heat storage unit 20.

In this case, the combustion air is heated by passing the combustion air through the regenerator 20 heated by the exhaust gas. The switching between the blowing of the combustion air into the furnace and the discharge of the exhaust gas is performed by switching means. 30 at predetermined time intervals (for example,
(Every 5 seconds to several minutes). It is desirable that the switching time is appropriately selected depending on the type of the heat storage body 20.

Further details will be described. This regenerative burner 10
A combustion nozzle 11 for injecting fuel and primary air into a furnace is provided at the center of a cylindrical main body 12a of a passage portion 12, and a combustion air passage for supplying combustion air around the combustion nozzle 11 and a combustion air passage are provided. 4 functioning as exhaust gas passage for exhaust
The two passages T are formed separately.

As shown in FIG. 2, the passage portion 12 has four passages T independent of each other by a partition wall 13.
Each of the passages T has an equal cross-sectional area, and serves as a combustion air passage or an exhaust gas passage for discharging exhaust gas by a switching unit 30 described later.

As shown in FIG. 3, a recess 14 having a depth such that the tip of the combustion nozzle 11 faces the bottom from the bottom of the combustion nozzle 11 is formed at the tip of the passage portion 12 as shown in FIG. Four passages T are opened around the place 14. By forming the recess 14 in this way, it is possible to eliminate the blow-out of the flame, and to obtain a stable flame.

The combustion nozzle 11 is configured such that a motive fluid composed of steam or high-speed air flows from the motive fluid supply unit 15 around or around the combustion nozzle 11. By flowing the motive fluid, the size or sharpness of the flame injected from the combustion nozzle 11 can be adjusted, the flexibility of the flame increases, and the range of controllability or versatility also increases. Such means are not necessarily required.

The cylindrical body 12 a of the passage portion 12 formed by partitioning the four passages T is provided on the side wall 1 a of the combustion chamber 1.
In this embodiment, the passage portion 12 has a substantially vertical bent portion 12b extending from a rear end portion of the tubular main body 12a. A housing chamber H in which a gas permeable heat storage body 20 is housed is provided at the portion, that is, at a position separated from the side wall 1 a of the combustion chamber 1.

The storage chamber H is formed by the inner side wall of the passage portion 12 and the bottom plate 21, and the heat storage body 20 stored therein does not matter whether it is a honeycomb or a pellet. However, considering maintenance such as dust removal work described later, the pellet-shaped heat storage member P
In the case of this pellet-shaped heat storage member P, the heat storage member P is divided into four parts by the partition wall 13 and is placed on a bottom plate 21 made of a porous member formed of a punching plate or a wire mesh. A predetermined amount is filled. In the case of a honeycomb-shaped heat storage member, the bottom plate 21 is not necessarily required.

However, regardless of whether it is in the form of a honeycomb or a pellet, the switching means 30 is connected to the accommodation chamber H as described later.
If it is detachable, there is an advantage that the switching means 30 can be removed and maintenance work of the heat storage body 20 can be performed.

The heat storage body 20 has a passage T
The exhaust gas that has passed through and the combustion air that has been blown from the blowing means are switched by the switching means 30 to flow alternately, and are heated by the exhaust gas to a high-temperature state.
0 heats the combustion air.

For example, the combustion air passing through the regenerator 20 is initially at room temperature (for example, about 20 ° C.), but is heated by the regenerator 20 to reach about 900 ° C. and is sent into the furnace. It is. On the other hand, the exhaust gas from the furnace is about 1100 ° C. when passing through the heat storage body 20, and is discharged at about 200 ° C. after applying heat to the heat storage body 20.

The pellet-shaped heat storage member P constituting the heat storage body 20 is not particularly limited. For example, the heat storage member P stores heat of a high-temperature gas of about 1100 ° C. like exhaust gas. Is used for heat-resistant oxidized ceramics such as alumina and mullite and nitride-based ceramics.
It is preferable to use a high-strength material, and MAS (cordierite) or LAS (lithium aluminum
(Silicate-based) low-expansion material or the like may be used. About 5
For a medium temperature gas of about 00 to 600 ° C., it is preferable to use a metal made of metal such as iron or copper which is cheaper than ceramics.

Here, the pellet shape means not only a spherical shape or a polygonal shape but also a short tubular shape such as a so-called Raschig ring, and also includes a short rod shape, a strip, a nugget shape and the like. I do.

The switching means 30 is provided in a case 31 detachably provided to the passage section 12. An exhaust gas chamber 32 is formed at the outermost periphery in the case 31, a switching chamber 33 is provided in the exhaust gas chamber 32, and an air chamber 34 is provided in the switching chamber 33. Small rooms A, B, C, so as to communicate with each other
D.

That is, the case 31 comprises an outer case H1, an intermediate case H2 and an inner case H3. The outer case H1, as shown in FIG.
The outer case H1 is a part for discharging exhaust gas, and an exhaust gas duct 36 is connected to the outer case H1 as shown in FIG. Has been established.

Further, the switching chamber 33 in the intermediate case H2 is provided.
Is a chamber through which the exhaust gas after passing through the heat storage unit 20 and the air toward the heat storage unit 20 flow, so that it is located immediately below the heat storage unit 20 and has substantially the same size as the heat storage unit 20. Is divided into four rooms A, B, C and D by a partition wall 13a similar to the partition wall 13.

Here, the inside of the switching room 33 is divided into four rooms by the four passages T of the passage portion 12 and the small chambers A to D.
This is for making the and the communication state. However, the passage T is another integer (for example, 3, 5, 6, 7, 8, 12, 16, etc.).
If the number of rooms is equal, the number of rooms may be equal.

However, as a practical matter, if the inside of the switching chamber 33 is partitioned by a number larger than four, the number of rotating plates R to be described later needs to be increased corresponding to this number, so that the configuration is considerably complicated. There is a risk of becoming. In such a case, it is preferable to configure as in a second embodiment described later.

Further, the inner case H3 is provided with an air chamber 34 into which the combustion air blown from the blowing means is introduced.
And is provided independently in the intermediate case H2.

In particular, a switching member R composed of first and second rotating plates R1 and R2 is provided in the inner case H3, and third and fourth rotating plates R3 are provided outside the intermediate case H2.
, R4, there is provided a switching member R. The through holes formed in these rotary plates R1 to R4 and the inner case H3 are provided.
Side walls S1, S2 of the intermediate case H2 and side walls S3, S4 of the intermediate case H2.
6 (a) to 6 (d) are opened. In FIG. 6,
To facilitate understanding of the state of the through holes, the fixed side through holes formed in the side walls S1 to S4 are indicated by thick lines, and the movable side through holes formed in the rotating plates R1 to R4 are indicated by thin lines.

The side walls S1 and S2 of the inner case H3 have
As shown in FIGS. 6A and 6C, the center angle is substantially 90 °.
The fixed-side through-holes O1, O2, O3, and O4 having a rotation angle of 0 ° to 90 ° and 180 ° to 270 ° are provided. The rotating plates R1 and R2 provided opposite the side walls S1 and S2 have a center angle of approximately 45 °.
Openings O5 and O6 on the movable side having
As shown in the figure, when the through hole O5 is at the position of the rotation angle of 0 ° to 45 °, the through hole O6 is at the position of 270 ° to 315 °.

As shown in FIGS. 6 (b) and 6 (d), radially outward sides (FIG. 7) of the side walls S3 and S4 of the intermediate case H2.
In the exhaust gas 1), through holes O7, O8, O9, and O10 having a central angle of approximately 90 ° are formed in a rotation angle range of 315 ° to 45 ° and a rotation angle of 135 ° to 225 °, and are formed in a radial direction. On the side (exhaust gas 2 in FIG. 7), through-holes O11, O12, O13, and O14 each having a center angle of approximately 90 ° have rotation angles of 0 ° to 90 °.
° and 180 ° to 270 °. Rotating plate R provided opposite side walls S3 and S4
3, R4 have through holes O15 and O16 having a center angle of approximately 45 ° on the radially outward side (exhaust gas 1 in FIG. 7), and a substantially central angle on the radially inward side (exhaust gas 2 in FIG. 7). The holes O17 and O18 each having 45 ° are, for example, as shown in FIG.
When the rotation angles of 17 and O15 are between 135 ° and 225 °, the openings O18 and O16 are located at positions of 45 ° and 135 °.

In this embodiment, since four passages T are formed in the passage portion 12, four passages T are formed in the intermediate case H2.
Partitions A to D are formed, and the side walls S1 to S4 and the rotary plates R1 to R4 have through holes O1 to O18 having the above-described positional relationship.
However, if three or another number of passages T are provided in the passage portion 12, the number of rooms in the intermediate case H2 and the angular relationship between the side wall and the through hole formed in the rotary plate will also be different. .

However, according to the experiments, no matter how many passages T are provided, the ratio of the combustion air to the exhaust gas is about 15% for the regenerative burner incorporated in the industrial furnace.
It is preferable that the combustion air pressure, which is 0 ppm or less and indicates the pressure loss of the combustion air, be in a range of about 500 mmAq or less.

That is, as shown in FIG. 8, it has been found that the value of (the passage area of the combustion air / the passage area of the exhaust gas) × 100 is preferably about 10 to 60.

The rotating plates R1 to R4 are attached to a rotating shaft 37 extending through the inside of the case 31, and are simultaneously rotated by rotating a motor M provided at the end. ing.

A spring 38 is provided between the rotating plates R1 and R2 in the air chamber 34, between the outer case H1 and the rotating plate R3, and between the rotating plate R4 and the outer case H1. Although the leakage between R and the side plate S of each case H is prevented, a lubricating member and a seal member 39 may be provided between them.

Next, the operation of the above embodiment will be described.
When the fuel and primary air are injected from the combustion nozzle 11 of the regenerative burner 10 and ignited by an ignition means (not shown), the combustion air blown from the blowing means toward the flame is sent into the furnace. In this regenerative burner 10,
The flame reaches the back of the furnace by the combustion air, and exhibits a good heating state.

The exhaust gas burned in the furnace is discharged into the atmosphere through the switching means 30 through the passage T and the regenerator 20, and the passage is switched while the continuous operation is performed by one-way rotation. Therefore, the supply of combustion air and the discharge of exhaust gas are continuously performed without stopping.

However, the switching means 30 of the present embodiment sets the number of revolutions of the motor M to a predetermined value so as to switch between blowing the combustion air into the furnace and discharging the exhaust gas at predetermined time intervals. The combustion air is heated at a predetermined ratio with respect to the exhaust gas and sent into the furnace. This state will be described below based on the rotation angle when the rotation is started from the position shown in FIG.

(0 ° to 45 °) Initially, the through holes O5 and O6 of the rotating plates R1 and R2 and the rotating plate R3 are located at positions as shown in FIG.
, R4, even if rotated by 45 ° from the position where the through holes O15, O17, O16, and O18 are located, the communication state between the through hole O5 and the through hole O1 continues. The hole O6 is discharged and is closed by the side wall S2.

Therefore, the air in the air chamber 34 is introduced into the chamber A from the through hole O1 in the side wall S1 through the through hole O5 in the rotary plate R1, but is not introduced into each of the chambers B, C and D. .

That is, the total air is for the A room, and the total opening is “1” (see the range of 0 ° to 45 ° in FIG. 7). Here, “1” means the total aperture.

On the other hand, as shown in FIGS. 6 (b) and 6 (d), the through hole O15 (exhaust gas 1) of the rotating plate R3 initially communicates with the through hole O8 of the side wall S3, and the exhaust gas is discharged from the chamber B as shown in FIGS. Room 3
2, the opening gradually decreases, the through hole O17 (exhaust gas 2) gradually starts to communicate with the through hole O12 in the side wall S3, the opening gradually increases, and the exhaust gas flows from the chamber B. It flows out into the exhaust gas chamber 32.

Further, in the rotary plate R4, the through hole O16 (exhaust gas 1) gradually starts to communicate with the through hole O10 in the side wall S4, the opening degree thereof gradually increases, and the exhaust gas flows out of the chamber D into the exhaust gas chamber 32. Initially, the exhaust gas from the C room was
The opening degree of the through hole O18 (exhaust gas 2) which has flowed out gradually decreases due to the side wall S4.

Therefore, in the range of the rotation angle, the exhaust gas from the chambers B, C and D flows out to the exhaust gas chamber 32, and the total opening amount is "2". here,
“2” means the total aperture.

(45 ° to 90 °) The rotating plates R1, R2
When the rotating plates R3 and R4 rotate more than 45 °, the through hole O5 of the rotating plate R1 starts to close, the combustion air from the chamber A decreases, and the through hole O6 starts to communicate with the through hole O3 of the side wall S2. , C combustion air increases. As a result, the amount of combustion air becomes A + C, but the amount of combustion air from the room A decreases and that from the room C increases, so that the total opening amount is “1” (45 in FIG. 7). ° -90 °).

On the other hand, the exhaust gas passes through the through hole O15 on the rotating plate R3 side.
(Exhaust gas 1) starts to close, and the through hole O17 (exhaust gas 2) communicates with the through hole O12 in the side wall S4. On the side of the rotary plate R4, the through hole O16 (exhaust gas 1) is in communication with the through hole O18.
Remain closed.

Therefore, as for the exhaust gas, the exhaust gas from the chambers B and D flows out to the exhaust gas chamber 32, and the total opening amount is as follows.
It becomes "2".

(90 ° to 135 °) The rotating plates R1, R
2 and the rotating plates R3 and R4 rotate by more than 90 DEG, the through hole O5 of the rotating plate R1 remains closed by the side wall S1, and the through hole O6 communicates with the through hole O3 of the side wall S2. . As a result, the combustion air becomes the amount of the C chamber, and the total opening amount is “1” (see the range of 90 ° to 135 ° in FIG. 7).

On the other hand, the exhaust gas passes through the through hole O15 on the rotating plate R3 side.
(Exhaust gas 1) starts to communicate with the through hole O7 in the side wall S3, and the through hole O17 (Exhaust gas 2) starts to close by the side wall S3. Further, the through hole O16 (exhaust gas 1) on the rotating plate R4 side starts to be closed by the side wall S4, and the through hole O18 (exhaust gas 2) starts to communicate with the through hole O14.

Therefore, the exhaust gas from the chamber A, the chamber B and the chamber D flows out to the exhaust gas chamber 32, and the total opening amount is “2”.

(135 ° to 180 °) The rotating plates R 1,
When R2 and rotating plates R3 and R4 rotate more than 135 °,
The through hole O5 of the rotating plate R1 starts to communicate with the through hole O2 of the side wall S1, and the through hole O6 of the rotating plate R2 starts closing the communication with the through hole O3 of the side wall S2. As a result, the combustion air becomes B + C
The total opening amount is “1” (see the range of 135 ° to 180 ° in FIG. 7).

On the other hand, the exhaust gas passes through the through hole O15 on the rotating plate R3 side.
(Exhaust gas 1) communicates with the through hole O7 in the side wall S3,
The gas is discharged from the chamber A, and the through hole O17 (exhaust gas 2) remains closed by the side wall S3. Further, the through hole O on the rotating plate R4 side is used.
16 (exhaust gas 1) remains closed by the side wall S4, and the through hole O18 (exhaust gas 2) is in communication with the through hole O14.
Discharge from room D.

Therefore, as for the exhaust gas, the exhaust gas from the chambers A and D flows out to the exhaust gas chamber 32, and the total opening amount is as follows.
It becomes "2".

Similarly, in the range of 180 ° to 225 °, the combustion air is introduced from the chamber B into the passage T communicating with the chamber B, and the exhaust gas flows through the chambers A, C and D. In the range of 225 ° to 270 °, the combustion air is introduced from the B and D chambers into the passage T communicating with the B and D chambers, and the exhaust gas is discharged to the A and C chambers. Are discharged to the exhaust gas chamber 32 through the respective chambers.

In the range of 270 ° to 315 °, the combustion air is supplied from the passage T communicating from the chamber D to the chamber D.
The exhaust gas is discharged to the exhaust gas chamber 32 through each of the chambers A, B, and C, and in the range of 315 ° to 360 °,
The combustion air is introduced from the chambers D and A to the passage T communicating with the chambers D and A, and the exhaust gas is discharged to the exhaust gas chamber 32 through the chambers B and C.

As described above, in the present embodiment, since the passage T is divided into four passages, the combustion air corresponding to the total opening amount “1” flows out to the passage T, and the exhaust gas corresponds to the total opening amount “2”. As a result, the passage T corresponding to the total opening "1" is always stopped based on the total opening.

As a result, the ratio of combustion air flow area / exhaust gas flow area = 1/2 = 0.5.

Further, for example, in the case where the air passage is divided into five passages T, the combustion air: exhaust gas: resting portion = 1: 3: 1. Distribution area / Exhaust gas distribution area = 1/3 = 0.33
Becomes

Similarly, considering the case where the passage T is divided into seven passages T, combustion air: exhaust gas: rest portion = 1:
5: 1. In this case, the ratio is such that combustion air distribution area / exhaust gas distribution area = 1/5 = 0.2.

As the number of divisions of the passage T is increased as described above, the area through which the combustion air flows becomes smaller.
The flow speed of the combustion air increases, and the pressure loss also increases. On the other hand, since the area where the fuel is jetted out comes into contact with the exhaust gas having a lower oxygen concentration than the part which comes into contact with the combustion air, the flame temperature is averaged and the combustion becomes slow, resulting in NOx emission. Generation is suppressed.

That is, as shown in FIG. 8, the horizontal axis represents the ratio of the area through which combustion air flows to the area through which exhaust gas flows, and the vertical axis represents the concentration of NOx and the pressure loss of air. As described above, the reason why the pressure loss is in the practical range with low NOx is that the ratio is in the range of 0.1 to 0.5.

Therefore, the practical division number is 1
It can be said that it is preferably two or less, and at least three or more.

Considering the case where the passage T is divided into twelve passages T, combustion air: exhaust gas: resting portion = 1: 1: 1
Although the ratio is 0: 1, the ratio in this case is such that combustion air circulation area / exhaust gas circulation area = 1/10 = 0.1.

(Second Embodiment) FIG. 9 shows a second embodiment of the present invention.
FIG. 10 is a sectional view showing the embodiment of FIG.
FIG. 11 is a sectional view taken along line -10, and FIG.
It is sectional drawing which follows the 1 line. As shown in FIG. 9, the regenerative burner 10 of the present embodiment is suitable for use as a switching means when the passage T is divided into four or more. Here, the passage T is divided into eight. The illustrated part shows the switching means and its vicinity.

The switching means 50 according to the present embodiment is the same as that shown in FIG.
As shown in FIG. 5, a partition plate 51 for equally dividing the passage portion 12 and the heat storage body 20 housed in the housing chamber H into eight regions, and a porous member slightly higher than the lower end of the partition plate 51 is provided. The bottom plate 21 is provided, and the bottom plate 21 supports a pellet-shaped heat storage member P filled with a predetermined amount. Note that the partition plate 51 may be formed using a heat-resistant material such as ceramics or fire-resistant bricks as in the partition wall 13 of the above-described embodiment, but a hollow shaft as in the present embodiment. It may be made of a relatively heat-resistant metal material that protrudes radially from 52. Note that a support shaft 53 is provided inside the hollow shaft 52.

The lower portion of the passage portion 12 is provided with a case 55 so as to surround the lower portion of the storage chamber H in which the heat storage body 20 is stored.
And an air duct 59 is provided in the case 55 so as to extend coaxially with the case 55.

That is, the air duct 59 is connected to the passage 1
2 and is configured to communicate with a predetermined number of passages T and to introduce the combustion air from the air supply means, and the other part of the case 55 is a part constituting the exhaust gas chamber 32 through which the exhaust gas flows. ing.

The lower end of the air duct 59 communicates with the passage 60 to which the combustion air is supplied, and the intermediate portion is cylindrical.
The sprocket 57 is fixed to the cylindrical portion 59a. The upper portion from the cylindrical portion 59a is a semi-cylindrical portion 59b having a semicircular cross section perpendicular to the axis, and occupies a half area of the passage portion 12, as shown in FIG.

However, the upper end of the air duct 59 is closed by a closing plate 54 so that a part of a predetermined number of communicating passages T does not communicate with the air duct 59. Here, the closing plate 54 is adapted to close two of the four passages T corresponding to the part of the air duct 59. Each of the closing plates 54, 54 for closing the two passages has an area slightly larger than the cross-sectional area of one of the eight passages T, so that each passage T can be reliably closed. Is configured.

Therefore, the combustion air is discharged from the air duct 59 between the two closing plates 54, 54 toward the heat storage unit 20 in the passage portion 12, and the exhaust gas after passing through the heat storage unit 20 is discharged. Flows into the case 55 from a portion where the air duct 59 does not exist. As in the first embodiment, the ratio of the total area of the passage through which the combustion air flows to the total area of the passage through which the exhaust gas is sucked is 0.1.
It is set to be 0.5.

That is, in this embodiment, as shown in FIG. 11, two closing plates 54 are provided, the total opening of combustion air is “2”, the total opening of exhaust gas is “4”, Since the total opening amount of the rest portion is set to “2”, the area of air flow for combustion / the area of exhaust gas circulation = 2/4 =
0.5.

However, the number of the closing plates 54 may be one, the total opening amount of the combustion air may be "1", the total opening amount of the exhaust gas may be "6", and the total opening amount of the rest portion may be "1". In this way, the area of air flow for combustion / the area of exhaust gas circulation = 1/6 = 0.1
7, which falls within the practical range described above.

Even with this configuration, as in the first embodiment, the exhaust gas has low NOx and the heat storage body 20
However, the heat storage type burner has durability, is easy to perform maintenance, and is advantageous in cost.

In the first and second embodiments, since the pellet-shaped heat storage member P is used, dust and the like accumulate here. In this case, it is preferable to remove dust and the like using the dust removing means 40 as shown in FIG.

As the dust removing means 40, for example, as shown in FIG. 12 (a), a vibrating block 41 is attached to the lower surface of the bottom plate 21, which is the porous member, and moves forward and backward in the axial direction on the vibrating block 41. The bottom plate 21 is vibrated by operating a drive source such as a motor M to drop dust and the like attached to the heat storage member P. In this case, as described above, the case 31 or 5
5 is provided so as to be detachable from the passage portion 12, so that the case 3
Remove 1 or 55 and a suitable dust collecting member (not shown)
Is disposed at the lower part of the heat storage body 20 and the work of removing dust and the like is performed, so that the cleaning work can be performed cleanly.

Further, when the pellet-shaped heat storage member P is vibrated while flowing air, dust and the like can be easily removed during operation of the regenerative burner, and the pellet-shaped heat storage member P can be vibrated without flowing air. Even if it is made to adhere, the attached dust etc. can be dropped and removed from the heat storage member P. In particular, when vibrating up and down, it is effective for removing dust and the like attached to the heat storage body 20.

FIG. 12B shows a configuration in which dust or the like can be removed without removing the case 31 or 55. This dust removing means 40
Opens a through-hole 43 in the passage portion 12, inserts a vibrating rod 42 with a projection 44 from the through-hole 43, rotates the vibrating rod 42 by a motor M, and vibrates the heat storage member P in the form of a pellet. It is intended to be added.

FIG. 12C shows the vibrating rod 4.
2 is bent into a wave shape. Such a vibrating rod 42
Is rotated by the motor M, vibration can be applied to the heat storage member P in the form of a pellet.

FIG. 12D shows the bottom plate 21.
Can be opened and closed, a horizontal bar 45 is inserted from this portion, and the horizontal bar 45 and the vertical bar 46 are connected to each other.
Is rotated by a motor M. Even in this case, vibration is applied to the pellet-shaped heat storage member P,
Dust and the like can be removed.

The dust removing means 40 shown in FIG.
Divides the bottom plate 21 into a plurality of parts, provides a partition 47 on the center line of each bottom plate 21, and attaches a shaft 48 to the lower surface of each bottom plate 21.
The arm 48 that rotates about the center a is attached to the drive member 4.
9 by moving the arm 48 forward and backward, FIG.
As shown in FIG. 3 (b), a state in which the outer periphery is uphill and a state as shown in FIG. 13 (c) are formed, and dust is removed by rubbing the entire pellet-shaped heat storage member P. It is like that.

The dust removing means 40 can sweep out the pellet-shaped heat storage member P to the outside by increasing the inclination of each bottom plate 21 to some extent, and further increase the amount of the pellet-shaped heat storage member by further increasing. P can be swept out to the outside, whereby the heat storage member P in the form of a pellet can be replaced.

Further, according to the present invention, the pellet-shaped heat storage member P accommodated in the accommodation room H may be once carried out of the passage portion 12, normalized, and then carried into the accommodation room H. .

For example, as shown in FIG. 14, the bottom plate 21 of the storage chamber H is inclined, and a transfer means 70 for transferring the auger-shaped pellet-shaped heat storage member P is provided at a lower end portion of the bottom plate 21. After the pellet-shaped heat storage member P is once carried out of the storage chamber H to the outside, the heat storage member P damaged or the heat storage member P to which the foreign matter adheres is removed or washed by the sorting unit 71, and the heat storage member P is normalized. The upper hopper 72 may be carried into the storage chamber H through the passage 73.

In this case, from the viewpoint of heat utilization, it is preferable that a constant amount of the heat storage member P is always present in the accommodation room H. Therefore, a new heat storage member having substantially the same amount as the extracted heat storage member P is used. It is preferable that the member P is carried into the accommodation room H.

The bottom plate 21 of the storage chamber H is formed of a porous member. In this case, the damaged fine heat storage member P and foreign matter adhering to the heat storage member P fall from the bottom plate. The heat storage member P in the storage chamber H is always kept in a normal state and can be operated to exhibit a predetermined heat storage or heat exchange ability. When the heat storage member P is carried into the bottom plate 21 by a predetermined angle and the heat storage member P is carried on the bottom plate 21 so as to form a layer having a substantially uniform thickness h, the heat storage member P falls to the transfer means 70 by its own weight. Will be exchanged.

The heat storage member P circulating while falling under its own weight is preferably constituted by a short tubular heat storage member such as a so-called Raschig ring as shown in FIG. The size, for example, the axial length l, the thickness t,
As the outer diameter d, various types can be considered depending on the material, and the outer diameter d itself may be porous.

[0134] Such a short tubular heat storage member P is easy to be stacked due to its shape, and is compared with a ball-shaped heat storage member.
The surface area per unit is about twice as large, and the porosity at the time of filling is 63%, compared to about 26% for ball-shaped ones.
Quite large with degree.

Further, the short tubular heat storage member has a problem that the heat capacity is small because the wall thickness is small and the porosity is large.
Moreover, since it has the characteristic that the pressure loss when the gas flows is also small, if this short tubular heat storage member is used, heat can be stored in a short time, and the heat can be stored in a short time. The air can be heated.

Therefore, if the switching time is made shorter, an excellent heat exchange ability can be exhibited. According to experiments, it has been found that a desired heat exchange ability can be exhibited without any problem even when the time for switching between the exhaust gas from the combustion chamber and the combustion air from the air supply means is set to 5 to 60 seconds. That is, for example, even in the case of switching every 5 seconds, in the case of 8 divisions, a slow rotation of 3 rpm may be used.

Further, since the short tubular heat storage member has the same effect as the ball-shaped heat storage member even if the volume is half, it is possible to design a compact heat storage type burner having a small pressure loss.

[0138] The present invention is not limited to the above-described embodiment, but can be variously modified within the scope of the claims. In the embodiment described above, the passage 12
At the end of the combustion chamber 1 on the side of the wall 1a, only the recess 14 is formed around the combustion nozzle 11, but it may be configured as shown in FIG.

FIG. 16 is a sectional view showing a combustion nozzle according to another embodiment of the present invention. The end of the passage portion 12 on the wall side of the combustion chamber 1 slightly protrudes from the wall 1a of the combustion chamber 1, and the protruding portion 12c has a concave portion having a depth at its center such that the tip of the combustion nozzle 11 faces the bottom. It is also possible to provide the end of the passage T on the slope 12d by cutting off the recess 14 so as to be inclined at a predetermined angle. In this case, the cut end of the passage T becomes oblique, and becomes a large opening.

In this way, the flame is prevented from being blown off due to the formation of the concave portion 14, and a stable flame can be obtained. Further, the combustion air easily approaches the fuel, and the combustion performance is improved. And the exhaust gas easily enters the passage T.

A passage T arranged around the combustion nozzle 11
In some cases, the combustion air is ejected, and in some cases, the exhaust gas is sucked. However, if the end of the passage portion 12 is formed in a substantially truncated cone shape as described above, the shape of the end of the passage T becomes When the combustion air is ejected from the passage T, the combustion air tends to approach the fuel jet due to the Coanda effect, and the combustion performance is enhanced. On the other hand, on the other hand, the exhaust gas that has passed through a path as far as possible from the fuel is sucked through the passage T having a large mouth, so that the exhaust gas easily enters the passage.

In particular, the above-mentioned pellet-shaped heat storage member P is once carried out of the storage chamber H to the outside, and after the heat storage member P is normalized by the sorting unit 71, it is again loaded into the storage chamber H. Not only a regenerative burner having a passage portion divided into a large number of passages, but also various regenerative burners as long as combustion air is heated using a regenerator heated by heat of exhaust gas. It can be applied to

[0143]

As described above, according to the present invention, the following effects can be obtained. According to the first aspect of the present invention, since the supply of combustion air and the exhaust gas are switched by switching the passage, continuous operation can be performed while continuing combustion,
Since the heat storage body is separated from the combustion chamber, the durability of the heat storage body is improved, and the switching means is attached to the end of the passage so that maintenance can be easily performed. Since the total area of the passage through which the combustion air flows is smaller than the total area of the passage through which the exhaust gas is sucked,
The flame temperature is averaged, the combustion becomes slow, and the generation of NOx is suppressed. Since the ratio of the total area of the passage through which the combustion air flows to the total area of the passage through which the exhaust gas is sucked is set to a predetermined value, the invention has a low NOx, a small pressure loss and a low practical use. High regenerative burner.

According to a fourth aspect of the present invention, an exhaust gas chamber, a switching chamber, and an air chamber are formed in a case, and the exhaust gas and the combustion air are switched by using a through hole formed in a side wall of each chamber. Therefore, when the number of the plurality of passages is relatively small, it is possible to easily switch between the exhaust gas and the combustion air, and since the structure is simple, the switching operation is reliable and has durability.

According to the fifth aspect of the present invention, since the switching member is rotated by a single drive source, the structure of the switching means is extremely simple, and the cost is advantageous.

According to the sixth aspect of the present invention, since the switching members are rotated by independent driving sources, when the number of the plurality of passages formed in the passage portion is relatively large, the formation of the switching means can be simplified. .

According to the seventh aspect of the present invention, the combustion air is guided to the heat storage body by closing a part of the air duct that rotates in the case below the heat storage body. Even if the number of passages increases, it is possible to easily form switching means for switching and applying exhaust gas and combustion air to each passage.

According to the eighth aspect of the present invention, since the heat storage body is formed in a pellet shape and rubbed against each other, dust and the like can be easily removed from the heat storage body.

According to the ninth aspect of the present invention, since the bottom plate is formed of a porous member, the pellet-shaped heat storage member is kept in a normal state all the time by removing foreign matters or the like, and a combustion operation for exhibiting a predetermined heat storage or heat exchange ability is performed. Can be.

According to the tenth aspect of the present invention, since the switching means is made detachable with respect to the accommodation chamber, the work of removing dust and the like can be performed easily and more completely, and the maintenance is easy.

According to the eleventh aspect, a stable flame can be obtained, the combustion performance can be improved, and the exhaust gas can easily enter the passage.

According to the twelfth aspect of the present invention, since the heat storage body is a short tube, heat absorbing and radiating actions are quick due to the characteristics of the short tube heat storage member, the pressure loss of the gas flow is small, and Heat can be stored and the combustion air can be heated, and more excellent heat exchange capacity can be exhibited.

According to the thirteenth aspect of the present invention, if a short tubular heat storage member is used, a predetermined heat storage or heat exchange capability can be exhibited in a short time, and the switching time of the combustion air can be reduced by 5 hours.
Even in an extremely short time of up to 60 seconds, a predetermined ability can be exhibited.

According to the fourteenth aspect of the present invention, when a motive fluid flows around the combustion nozzle, the flexibility of the flame is increased, and the range of controllability or versatility is increased.

According to a fifteenth aspect of the present invention, the heat storage body is formed in a pellet form, and the heat storage member is once carried out of the passage portion, dust is removed, and then the heat storage member is carried into the passage portion. Can be replaced and re-loaded, the predetermined force can be constantly maintained, and dust can be easily removed from the heat storage member.

According to the present invention, since the same amount of heat storage member as the extracted heat storage member is carried in, continuous operation can be performed while the heat storage member exhibits a predetermined capacity.

According to the seventeenth aspect of the present invention, since the bottom plate of the transporting means is formed of a porous member, it is easy to treat foreign substances, can maintain a normal state from beginning to end, and can operate at a predetermined capacity.

In the invention according to claim 18, the bottom plate is a porous member inclined at a predetermined angle, and the pellet-shaped heat storage member is placed on the porous member at a uniform thickness. It can be replaced with a new one, and can always operate with the required performance.

According to the nineteenth aspect of the present invention, since the heat storage element has a short tubular shape, heat can be stored in a short time, the combustion air can be heated, and more excellent heat exchange ability can be exhibited. Because it is difficult, it can be carried in a layer of uniform thickness,
Thereby, heating can be performed uniformly.

According to the twentieth aspect of the present invention, if a short tubular heat storage member is used, heat storage or heat exchange ability can be exhibited even in a very short time of 5 to 60 seconds.

[Brief description of the drawings]

FIG. 1 is a schematic longitudinal sectional view showing a first embodiment of the present invention.

FIG. 2 is a sectional view taken along line 2-2 in FIG.

FIG. 3 is a sectional view taken along line 3-3 in FIG.

FIG. 4 is a sectional view taken along line 4-4 in FIG.

FIG. 5 is a sectional view taken along line 5-5 in FIG.

FIG. 6 is an explanatory diagram showing an operation state of the switching means of the embodiment.

FIG. 7 is an explanatory diagram showing a gas flow state of the embodiment.

FIG. 8 is a graph showing the state of NOx and combustion air pressure according to the embodiment.

FIG. 9 is a cross-sectional view illustrating a second embodiment of the present invention.

FIG. 10 is a sectional view taken along line 10-10 in FIG. 9;

FIG. 11 is a sectional view taken along line 11-11 in FIG. 9;

FIG. 12 is a sectional view showing a dust removing unit of the embodiment.

FIG. 13 is a sectional view showing a dust removing unit of the embodiment.

FIG. 14 is a cross-sectional view of a main part showing still another embodiment of the present invention.

FIG. 15 is a perspective view showing a heat storage member used in the embodiment.

FIG. 16 is a sectional view showing still another embodiment of the present invention.

DESCRIPTION OF SYMBOLS 1 ... combustion chamber, 1a ... combustion chamber wall, 11 ... combustion nozzle, 12 ... passage, 12c ... projection, 12d ... slope, 14 ... recess, 20 ... heat storage element, 21 ... porous member, 30, 50 switching means, 31 case, 32 exhaust gas chamber, 33 switching chamber, 34 air chamber, 40 driving means, 51 partition plate, 54 closing plate, 55 case, 58 rotating mechanism, 59: air duct, 70: conveyance means, A, B, C, D: small chamber, h: thickness of heat storage member, H: accommodation chamber, M: drive source, O1 to O18: through hole, P: heat storage member, R: switching member, R1 to R4: rotating plate, S1 to S4: side wall, T: passage.

Claims (20)

[Claims] 1. Around a centrally extending combustion nozzle,
A tip of a passage having a plurality of passages parallel to the combustion nozzle is mounted so as to penetrate a wall of the combustion chamber, and exhaust gas from the combustion chamber and combustion air from an air supply means are provided in a predetermined passage of the passage. In the regenerative burner in which the air for combustion is heated by the air-permeable heat storage body heated by the heat of the exhaust gas and guided to the combustion chamber, A regenerative burner, wherein a storage chamber in which the heat storage body is stored is provided at an end portion separated from a wall of the combustion chamber, and the switching means is attached to the storage chamber. 2. The switching means according to claim 1, wherein, of the plurality of passages, a total area of a passage through which combustion air flows is smaller than a total area of a passage through which exhaust gas is sucked. The regenerative burner as described. 3. The switching means according to claim 1, wherein the ratio of the total area of the passage through which the combustion air flows to the total area of the passage through which the exhaust gas is sucked is 0.1 to 0.5. 2
The regenerative burner according to 1. 4. The switching means has a switching chamber in a case, and an exhaust gas chamber or an air chamber is provided inside the switching chamber, and the air chamber or the exhaust gas chamber is provided outside the switching chamber. Is divided into small chambers, and a through hole is opened in the side wall of the small chamber so as to communicate each small chamber with the passage and the air chamber and the exhaust gas chamber while communicating with each small chamber, and at a predetermined position with the through hole. The small chamber and the air chamber or the exhaust gas chamber are selectively connected to each other by rotating a switching member formed of a rotary plate having a through-hole opened so as to coincide with each other. The regenerative burner according to any one of 1 to 3. 5. The regenerative burner according to claim 4, wherein said switching means rotates a switching member comprising said rotating plate by a single drive source. 6. The switching device according to claim 4, wherein said switching means comprises a switching member provided in each of said small chambers and rotated by an independent drive source.
Or the regenerative burner according to 5. 7. A case provided so as to surround a lower part of a storage chamber in which a heat storage body provided at an end of the passage is stored, and a switching means extending coaxially into the case. An air duct provided to communicate with a predetermined number of passages of the passages and configured to introduce combustion air from the air supply means; and the predetermined number of passages provided at an upper end of the air duct. A closing plate that shuts off communication between some of the passages and the air duct, and a rotation mechanism that rotates the air duct in the case, and the heat storage is performed by the air duct that is rotated by the rotation mechanism. The combustion air is guided to the body, and the exhaust gas after flowing through the heat storage body from a portion other than the air duct of the case is discharged to the outside. Thermal storage burner . 8. The storage chamber according to claim 1, wherein the heat storage body housed inside the storage chamber is constituted by a pellet-shaped heat storage member, and has a dust removing means for operating the heat storage member to remove dust and the like. The regenerative burner according to any one of 1 to 7. 9. The regenerative burner according to claim 8, wherein the storage chamber has a bottom plate formed of a porous member. 10. The regenerative burner according to claim 1, wherein said switching means is detachably attached to said storage chamber. 11. The passage portion has a tip slightly projecting from a wall of the combustion chamber, and a recess having a depth such that a tip of the combustion nozzle faces a bottom is formed in the projection. 2. An end opening of the passage is provided on a slope formed by cutting off at a predetermined angle toward an outer periphery.
0. The regenerative burner according to any one of 0. 12. The regenerative burner according to claim 1, wherein the regenerator is constituted by a short tubular regenerative member. 13. The heat storage device according to claim 12, wherein the switching means sets a time for switching between the exhaust gas from the combustion chamber and the combustion air from the air supply means to 5 to 60 seconds. Expression burner. 14. The regenerative burner according to claim 1, wherein a motive fluid comprising steam or high-speed air flows around or at the center of the combustion nozzle. 15. A heat storage element having a passage portion having an air passage for introducing combustion air from an air supply means into a combustion chamber and an exhaust gas passage for passing exhaust gas from the combustion chamber, wherein the passage portion has air permeability. So that the exhaust gas from the combustion chamber and the combustion air from the air supply means are switched by switching means to flow alternately into the heat storage body and to guide the combustion air heated from the heat storage body into the combustion chamber. In the regenerative burner, the heat storage body is constituted by a pellet-shaped heat storage member, and the heat storage member is once carried out of the passage portion, and is provided with conveyance means for carrying dust into the passage portion after removing dust. Features a regenerative burner. 16. The regenerative burner according to claim 15, wherein said conveying means carries in a pellet-shaped heat storage member in substantially the same amount as the extracted pellet-shaped heat storage member. 17. The regenerative burner according to claim 15, wherein said transport means comprises a bottom plate for supporting said pellet-shaped thermal storage member made of a porous member. 18. The transfer means, wherein the bottom plate is constituted by a porous member inclined at a predetermined angle, and the pellet-shaped heat storage member is formed on the porous member so as to form a layer having a substantially uniform thickness. The regenerative burner according to any one of claims 15 to 17, wherein: 19. The regenerative burner according to claim 15, wherein said regenerator is constituted by a short tubular regenerative member. 20. The heat storage device according to claim 19, wherein the switching unit switches the exhaust gas from the combustion chamber and the combustion air from the air supply unit for a period of 5 to 60 seconds. Expression burner.