JPH07113509A - Heat accumulation type low nox burner - Google Patents

Abstract

PURPOSE:To permit the securing of stabilized combustion by a method wherein combustion air and combustion waste gas are passed through a heat accumulating body alternately and continuously to preheat combustion air by the heat of combustion waste gas and supply it to a burner. CONSTITUTION:A switching means 3 is turned continuously or intermittently to communicate sequentially the exhaust gas chamber 6a and the feed air chamber 6b of an outlet and inlet means 6 with either one of the chamber of a heat accumulating body 1, partitioned equally into N chambers circumferentially. Then, fuel F is injected continuously from a fuel nozzle 31, penetrating the center of the heat accumulating body 1, into a furnace 35 while high-temperature combustion air A is injected from the heat accumulating body 1 into the furnace 35 continuously through places around the circumference of the heat accumulating body. Accordingly, an effect, same as alternate combustion, can be obtained by only switching the combustion air A while continuing the injection of the fuel F. Thus, the combustion air is preheated by passing the combustion air A and the combustion exhaust gas E through the heat accumulating body 1 alternately and continuously and, thereafter, the preheated combustion air is supplied to a burner. According to this method, stabilized combustion can be secured.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a regenerative burner which recovers waste heat from exhaust gas and uses it for preheating combustion air. More specifically, the present invention relates to a regenerative burner that preheats and supplies combustion air with the heat of combustion exhaust gas by alternately passing combustion air and combustion exhaust gas through a relatively rotating heat storage body. .

[0002]

2. Description of the Related Art In a conventional heat storage type burner, for example, as shown in FIG. 15, a burner gun (fuel nozzle) 102 is installed in a wind box 101 so as to penetrate the wind box 101, and a heat storage body 103 is passed through. The combustion air and the fuel supplied are mixed in a burner and then injected into the furnace. That is, the conventional burner 10
Reference numeral 4 is a pair of a fuel nozzle 102 and a combustion air injection nozzle (in this case, the wind box 101). The two burners 104 form a pair, and the combustion gas is discharged from the other burner 104 while one of the burners 104 is burning.
The combustion gas is provided so that exhaust heat is recovered by the heat storage body 103 when exhausted through the wind box 101 of the other burner. Therefore, the conventional heat storage type burner alternately supplies the combustion air and the fuel to one set of burners, and therefore, means for selectively connecting the combustion air supply system and the exhaust system to the burner, and the fuel. And means for supplying the burner to either one of the burners. Then, for such switching of the flow paths of the combustion gas and the combustion air, it is considered to use a combination of electromagnetic valves, a four-way valve, a three-way valve, or the like. In the figure, reference numeral 105 is a four-way valve, 106 is an electromagnetic valve, 107 is a pushing fan, and 108 is an induction fan.

[0003]

However, in the conventional burner structure in which the air nozzle and the fuel nozzle are paired,
On the burner side at rest, there are problems that the high temperature combustion exhaust gas exhausted burns the fuel nozzle or causes coking of residual fuel. In order to avoid the burnout of the fuel nozzle, the arrangement and structure of the fuel nozzle are disclosed in JP-A-2-100.
The burner of No. 02 must be complicated, and there is a problem that the burner becomes large.

Further, when a solenoid valve is combined to switch the flow paths of the combustion gas and the combustion air, the solenoid valve that can be used in a high temperature atmosphere is expensive and the equipment cost is significantly increased.
Moreover, since the solenoid valves for gas pipes are quite large, it is desirable to reduce the number of uses because the space is taken up if the number increases. In addition, in this case, the supply of the combustion air and the exhaust of the combustion gas are momentarily reduced or delayed at the time of switching, the flame becomes unstable, and the generation of CO increases. When a four-way valve is used, the exhaust system and the air supply system cause a short path in the four-way valve at the moment of switching, and the amount of combustion air supplied to the burner momentarily decreases, resulting in a flame. May destabilize.

Further, in the heat storage type burner of the type in which the burners are burned alternately, it is necessary to take a lead time for injecting the combustion air so that the fuel is injected with a slight delay from the combustion air for ignition. Since it is preferable, complicated control such that fuel is supplied after a lapse of a certain time after the flow of combustion air is switched is generally required. Therefore, a heat storage type low NOx burner that does not require switching of fuel is desired.

It is an object of the present invention to provide a heat storage type low NOx burner which does not require fuel switching only by switching combustion air continuously without interruption.

[0007]

In order to achieve such an object, the heat storage type low NOx burner of the present invention has N (N
= N + 1, where n is a positive even number of 2 or more and is the number of chambers through which the fluid always flows. ) A heat storage body that is evenly divided into chambers and allows fluid to pass through each chamber in the axial direction, a fuel nozzle that directly penetrates the heat storage body to inject fuel into the furnace, and a combustion air supply system. A double tubular inlet / outlet means partitioned by an annular partition into an air supply chamber connected to the exhaust gas and an exhaust chamber connected to the combustion gas exhaust system, and a heat storage body and an inlet / outlet interposed between the heat storage body and the inlet / outlet means. While disconnecting from the means, the air supply communication holes for communicating the air supply chamber and the heat storage body and the exhaust communication holes for communicating the exhaust chamber and the heat storage body are alternately arranged n / 2 each, And a switching means for continuously or intermittently rotating to sequentially communicate the exhaust chamber and the air supply chamber of the inlet / outlet means with any of the heat storage chambers divided into N chambers, and the exhaust communication of the switching means. The hole and the communication hole for supply of air are arranged at an interval of an angle α represented by Formula 7,

[Equation 7] In addition, the size of the communication hole for supply air and the size of the communication hole for exhaust should be expressed by the formula 8.

[Equation 8] Satisfactory, fuel is continuously injected into the furnace, and high temperature combustion air is injected around the fuel directly from the heat storage body into the furnace. In the present specification, the term “a room in which a heat storage body is partitioned” refers not only to a case where the heat storage body itself is partitioned into a plurality of chambers but also a case where the heat storage body is substantially partitioned into a plurality of chambers by a distribution chamber. Both are included.

Further, the heat storage type low NOx burner of the present invention is
N (where N = n + 1, n is a positive even number of 2 or more, and indicates the number of chambers in which the fluid always flows). One chamber is defined as the total number of chambers Z (where Z = a · N, a Represents a number of units and is a positive integer excluding 0), and a plurality of divided chambers are formed in the heat storage body, and a total of Z chambers is formed of 1 a-vacant chamber in which no fluid constantly flows. Formed between the N chamber and the N chamber of another unit, and the arrangement angle α between the exhaust communication hole and the air supply communication hole has the relationship of Expression 9.

[Equation 9] In addition, the size of the exhaust communication hole and the supply air communication hole is expressed by the mathematical formula 10.
The relationship indicated by

[Equation 10] I am satisfied.

Further, the heat storage type low NOx burner of the present invention is
Heat storage that is evenly divided into N (N = n + 2, where n is a positive integer greater than or equal to 2 and is the number of chambers in which fluid always flows) circumferentially, and allows fluid to pass axially through each chamber A body, a fuel nozzle that directly injects fuel into the furnace through the center of the heat storage body, an air supply chamber connected to the combustion air supply system, and an exhaust chamber connected to the combustion gas exhaust system A double tubular inlet / outlet means partitioned by a partition wall and a heat storage body interposed between the heat storage body and the inlet / outlet means to shut off the heat storage body and the inlet / outlet means, and to supply communication between the air supply chamber and the heat storage body. A gas communication hole, an exhaust chamber, and an exhaust communication hole that communicates the heat storage body with each other are arranged at an interval of an angle C represented by Formula 11.

[Equation 11] And continuous or intermittently rotating to sequentially connect the exhaust chamber and the air supply chamber of the inlet / outlet means to any of the heat storage chambers divided into N chambers, and to continuously feed the fuel into the furnace. And the high temperature combustion air is directly injected from the heat storage body into the furnace.

Further, the heat storage type low NOx burner of the present invention is
N (where N = n + 2, n is a positive integer of 2 or more and indicates the number of chambers through which the fluid always flows). One chamber is the total number of chambers Z (where Z = a · N, a Is a positive integer excluding 0, which indicates the number of units, and is formed in the heat storage body with a plurality of partitioned chambers, and the formula 12 is provided between the exhaust communication hole and the air supply communication hole.

[Equation 12] The interval of the angle C represented by is set.

Further, the heat storage type low NOx burner of the present invention is
The fuel jetted from the fuel nozzle and the combustion air jetted from the heat storage body are jetted substantially in parallel, or the fuel nozzle rotates at the same time as the switching means and is directed toward the combustion air flow jetted from the heat storage body. The fuel is always injected from the side.

Further, the heat storage type low NOx burner of the present invention is
At the outlet of the heat storage body inside the furnace, nozzles that are independent of each other and communicate with each compartment of the heat storage body are arranged.

Further, the heat storage type low NOx burner of the present invention is
A burner throat is provided in front of the heat accumulator and the fuel nozzle, the cross-sectional area of which is narrowed toward the tip side, and a plurality of exhaust holes are provided around the burner throat.

[0014]

Therefore, the air supply chamber and the exhaust chamber of the inlet / outlet means are communicated with different chambers / compartments of the heat storage body through the air supply communication hole and the exhaust communication hole of the switching means, respectively, and do not intersect with each other. The combustion air and the combustion exhaust gas are flown to the. At this time, in the case of the inventions of claims 1 and 2, the combustion gas is sucked and flowed from the furnace into the a.n / 2 chamber of the heat storage body partitioned into the a.N chamber, and the other a. Combustion air is pushed into the n / 2 chamber to flow, and the remaining a chamber is not connected to any of the flow paths and becomes a vacant chamber in which the fluid does not flow. Therefore, if the chamber / compartment communicating with the air supply chamber of the inlet / outlet means and the chamber / compartment communicating with the exhaust chamber are sequentially changed by the operation of the switching means, the discharged fluid and the supplied fluid accumulate heat. It will flow through the same room / compartment of the body at different times.
For example, the combustion air flows through the heat storage body after flowing the combustion exhaust gas, and the heat of the heat storage body heated by the passage of the combustion exhaust gas is taken by the combustion air to complete the heat exchange.

The flow of the fluid is switched such that the air supply communication hole and the exhaust communication hole do not exist in the same chamber / compartment at the same time, and the front communication chambers are sequentially operated one by one from the front communication hole. Since the exhaust communication hole is moved to a compartment, the chamber / compartment in front of the heat storage body, for example, even if the exhaust communication hole is exposed to air, the supply communication hole and other exhaust and air supply communication holes behind it are still in the same chamber / compartment. It exists inside, and switching does not start. Then, after the exhaust communication hole in the front row is completely switched to the front compartment that was empty, the room / compartment that has been communicating with the exhaust communication hole in the front row until now becomes an empty room. The next communication hole for air supply is approaching. At this time, the air supply communication hole can be switched over while simultaneously straddling the two compartments of the existing room / compartment and the new compartment / compartment (vacant room) while supplying the fluid to the two compartments / compartment at the same time. , The flow of fluid is not interrupted. In addition, the exhaust communication hole in the front row is the room that is one before the room / compartment where the air supply communication hole is approaching.
Since it is located in the section, the exhaust gas for exhaust and the combustion air supplied are not mixed in the same section.

Further, in switching the flow of the fluid in the case of the third and fourth aspects of the invention, both the exhaust communication hole and the air supply communication hole are simultaneously moved to the respective front empty chambers. When the exhaust communication hole and the air supply communication hole completely occupy the front chamber / compartment, the room / compartment that has been communicating with the exhaust communication hole and the air supply communication hole is empty. Becomes Here, when the exhaust communication hole and the air supply communication hole communicate with a plurality of chambers / compartments at one time, the rearmost chamber / compartment in the rotation direction becomes an empty room. At this time, the exhaust communication hole and the air supply communication hole can be switched over while simultaneously straddling the two compartments of the existing room / compartment and the new room / compartment while supplying the fluid to the two compartments at the same time. Fluid flow is never interrupted. Moreover, since the exhaust communication hole in the front is occupied in the section one before the section where the supply communication hole is approaching, the exhaust combustion exhaust gas and the supplied combustion air are mixed in the same section. It doesn't fit.

Therefore, high-temperature combustion air close to the temperature of the combustion exhaust gas is stably supplied from around the combustion nozzle directly into the furnace without causing a momentary decrease or delay. In the case of the invention of claim 5, the combustion air and the fuel which are directly injected into the furnace separately are spread out without being mixed immediately after being injected into the furnace, and are spread in various places in the furnace apart from the combustion nozzle and the air nozzle. Mix with. However, combustion air is extremely hot (eg 1
Since it is close to 000 ° C or higher), stable combustion occurs when mixed. Further, when the heat of the heat storage body decreases, the combustion air is supplied by using the heat storage body of the combustion air supply means that has exhausted the combustion gas until now by switching only the combustion air without switching the fuel. To do. Therefore, the same result as the alternating combustion is obtained only by switching the supply of the combustion air.

Further, in the case of the invention of claim 6, the fuel jet merges with the straight-flowing combustion air jet as a cross wind jet. At this time, in the combustion air jet, a pair of circulation flows which are mutually opposite vortex regions are generated by the crosswind jet and the fuel jet, and the fuel jet is taken into the inside of the jet of the combustion air. After that, the high-concentration region of the combustion air jet is complicatedly diffused in the cross section by the large and small vortex clusters generated inside each of the two vortex regions, and at the same time, the fuel jet taken in the center of the jet is also dispersed. Diffused. That is, after the fuel jet is taken into the combustion air jet, the fuel jet gradually spreads throughout the inside of the jet, and is mixed with the high temperature combustion air and burned in the combustion air jet. During that time, combustion occurs on the surface of the fuel jet mixed with the combustion air to generate NOx.
The x is taken into the fuel jet by the circulation flow and rapidly reduced.

Further, in the case of the invention of claim 7, when the section of the heat storage body through which the combustion exhaust gas and the combustion air flows is switched by the rotation of the switching means, the nozzles for injecting the combustion air are successively circumferentially arranged. Be transferred. Therefore, when the combustion air is directly injected from the nozzle into the furnace, the flame position rotates in the circumferential direction in the furnace to form a non-stationary flame. Moreover, the momentum of the combustion air is controlled by the nozzle,
A flame having a predetermined shape and property is formed.

Furthermore, in the present invention, a burner throat may be installed in front of the heat storage body and the combustion nozzle, the flow passage cross-sectional area being narrowed toward the tip end side, and a plurality of discharge holes around which the combustion gas can pass and be discharged. For example, the injection energy of the fuel air injected from the heat storage causes exhaust gas recirculation in which part of the high temperature combustion exhaust gas is sucked into the burner throat.

[0021]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The structure of the present invention will be described in detail below with reference to the embodiments shown in the drawings.

FIG. 1 is a principle view showing an embodiment of a heat storage type low NOx burner of the present invention. This heat storage type low NOx burner
Combustion air A and fuel F at a much higher temperature (for example, about 800 ° C. or higher, preferably about 1000 ° C. to 1100 ° C.) than the combustion air of about 300 ° C. to 400 ° C. used in conventional diffusion combustion. In this case, they are separately injected into the furnace 35 for combustion. More specifically, in the heat storage type low NOx burner of the present embodiment, the fuel nozzle 31 for injecting the fuel F into the furnace 35 is passed through the center of the heat storage body 1,
The combustion air A, which has been heated to a high temperature, is injected substantially in parallel from around the fuel jet. Where combustion air A
Is passed through a portion of the heat storage body 1 where the combustion gas has been exhausted, and is heated to high temperature. Further, the amount of the combustion air A injected into the furnace 35 through the heat storage body 1 is almost the entire amount, and a part (usually about several%) of the combustion air A remains at room temperature to cool the fuel nozzle 31. As the fuel nozzle 31 and the heat storage body 1 around it
In some cases, it may be injected into the furnace 35 through the gap 24 between. However, it can be said that the combustion air A, which is substantially the entire amount, is injected into the furnace 35 after being heated to a high temperature through the heat storage body 1.

Here, the system for supplying the combustion air A and exhausting the combustion exhaust gas E through the heat storage body 1 is basically N in the circumferential direction (N = n + 1, where n is 2). The above-mentioned positive even number is the number of chambers through which the fluid always flows.) The heat storage body 1 that is evenly divided into the chambers and allows the fluid to pass through each chamber in the axial direction, and the supply air connected to the combustion air supply system 33. An inlet / outlet means 6 having an air chamber 6a and an exhaust chamber 6b connected to the combustion gas exhaust system 34, and between the inlet / outlet means 6 and the heat storage body 1 are arranged between the heat storage body 1 and the inlet / outlet means 6. While switching off, switching means 3 that rotates continuously or intermittently to sequentially connect the exhaust chamber 6b and the air supply chamber 6a of the inlet / outlet means 6 to any of the chambers of the heat storage body 1 partitioned into N chambers. It consists of The heat storage body 1 is divided into at least three or more chambers by itself or by a distribution means arranged on the upstream side thereof.

The heat storage body 1 is not limited to a particular shape or material, but is 1000
For heat exchange between a high-temperature fluid of around 0 ° C. and a low-temperature fluid of around 20 ° C. such as combustion air, it is preferable to use a honeycomb-shaped one produced by extrusion molding using a ceramic such as cordierite or mullite as a material. Also,
The honeycomb-shaped heat storage body 1 may be made of a material other than ceramics, for example, a metal such as heat-resistant steel. Also, from 500
At medium and high temperatures around 600 ° C., it is preferable to use a metal such as aluminum, iron, or copper, which is relatively cheaper than ceramics. The honeycomb shape originally means hexagonal cells (holes), but in the present specification, not only the original hexagonal cells but also quadrangular or triangular cells are opened innumerably. Further, as described above, the honeycomb-shaped heat storage body 1 may be obtained by bundling tubes or the like without integrally molding.
In the case of the present embodiment, the heat storage body 1 is divided into a total number of chambers Z (a · N) in the circumferential direction by the distribution chamber 2 arranged in front of it. For example, in the case of the embodiment shown in FIG. 1, the distribution chamber 2 divided into three chambers 9a, 9b, 9c by the partition 8 causes combustion in the heat storage body 1 as shown in FIG. It is divided into three chambers, a chamber 11 for flowing exhaust gas and a chamber 12 for flowing combustion air. That is, since the heat storage body 1 itself has a honeycomb shape composed of a set of cells each of which constitutes an independent flow path, the range partitioned by the distribution chamber 2 is defined as one partitioned chamber. Will be formed. When the distribution chamber 2 is provided, the fluid flowing in through the communication holes 4 and 5 can be dispersed and uniformly distributed over the entire area of the heat storage body 1. Further, the shape of the heat storage body 1 is not particularly limited to the honeycomb shape shown in the drawing, and as shown in FIGS. 10A and 10B, the heat storage material 2 having a flat plate shape or a corrugated plate shape.
7 are arranged radially in a cylindrical casing 28, or as shown in FIG. 10C, a pipe-shaped heat storage material 27.
The cylindrical casing 28 so that the fluid may pass through in the axial direction.
It may be filled inside. Further, in the present embodiment, the single heat storage body 1 is substantially divided into the Z chamber by the distribution chamber 2, but the present invention is not particularly limited to this.
The heat storage body 1 itself may be partitioned and formed in the aN chamber. For example, as shown in FIG. 10 (D), a cylindrical casing 28, which is partitioned and formed in the circumferential direction by partition walls 29 into which the fluid can pass in the axial direction, is prepared. It may be configured by filling a lump of the heat storage material 27 having a spherical shape, a short tube, a short rod, a strip, a nugget shape, a net shape, or the like. When using a heat storage material 27 such as SiN that can be used at a much higher temperature than cordierite or mullite, it is not easy to form a complicated honeycomb shape, but a simple pipe shape, rod, ball, etc. It is easy to mold into. Therefore, it is preferable to employ a heat storage structure as shown in (C) and (D) of FIG.

Here, the number of chambers divided into the heat storage body 1 is a chamber for flowing combustion air (hereinafter referred to as an air supply chamber) 12 and a chamber for flowing combustion exhaust gas (hereinafter referred to as an exhaust chamber) 11. At least one vacant room (a room in which fluid does not flow) 10 as a set
When n = 2, that is, N = n +
The minimum number of rooms is 1 to 3. Then, the exhaust chamber 11 and the air supply chamber 12 are paired, and for example, two sets of the exhaust chambers 11 _-1 , 11 _-2 and the air supply chambers 12 _-1 , 12 are shown in FIG. _Although an example is shown in which _-2 is combined, any number of combinations can be combined in this way. It is also possible to form a plurality of units by setting N chambers as one unit. That is, the total number Z of rooms is represented by Z = a · N (where a is
Is a positive integer excluding 0 indicating the number of units). In this case, the positions of the communication holes 4 and 5 are set so that the vacant chamber is located between the units. In this way
It is also possible to form a plurality of units of the total number Z of chambers in the heat storage body 1 with the N chambers as one unit. This relationship is shown in Figure 5.
For example. In FIG. 5, for convenience of drawing, the positional relationship and size of the exhaust communication hole 4 and the air supply communication hole 5 are not shown accurately.

The inlet / outlet means 6 is divided by an annular partition wall, for example, a cylindrical partition wall 7, into an air supply chamber 6a connected to the combustion air supply system 33 and an exhaust chamber 6b connected to the exhaust system 34. There is. In the case of the present embodiment, the supply chamber 6a is formed inside the partition wall 7, and the exhaust chamber 6b is formed outside. In the case of the present embodiment, the switching means 3 is provided between the inlet / outlet means 6 and the distribution chamber 2 so as to rotate independently with the switching means 3. For example, as shown in FIG. 2, the inlet / outlet means 6 holds the switching means 3 rotatably with the bearing member 15 interposed between the outer cylinder portion 13a and the support ring 23 of the switching means 3. Then, seal members 16 and 17 are provided between the inlet / outlet means 6 and the switching means 3 so as to prevent fluid from leaking.

The switching means 3 for connecting the supply chamber 6a and the exhaust chamber 6b of the inlet / outlet means 6 to only the corresponding chambers / compartments 12 and 11 of the heat storage body 1 is composed of a disc orthogonal to the flow path. The air supply communication hole 5 for communicating one compartment with 1 and the supply chamber 6a and the exhaust communication hole 4 for communicating one compartment with the exhaust chamber 6b are provided by a · n / 2 each. There is. For example, in the case of FIG. 1, since n is 2 and a is 1, it has one air supply communication hole 5 and one exhaust communication hole 4. The exhaust communication hole 4 and the supply communication hole 5 must be such that the supply communication hole 5 and the exhaust communication hole 4 cannot exist in the same chamber / compartment at the same time. The front-row communication holes located in the chambers / compartments are sequentially moved one by one to the front chambers / compartments, and the sizes of the air supply communication holes and the exhaust communication holes 4 are set so that they do not overlap each other in the radial direction. It is necessary to satisfy the three conditions that all of them are placed in one room at the same time when they are placed.
That is, the exhaust chamber 6b communicates with the exhaust chamber 11 of the heat storage body 1, and the exhaust communication hole 4 communicates with the air supply chamber 6a and the air supply chamber 12 of the heat storage body 1 communicates with each other. Alternating with n /
Two of them are arranged, and the exhaust communication hole 4 and the supply air communication hole 5 are arranged at an interval of an angle α represented by Formula 13.

[Equation 13] Further, the sizes of the air supply communication hole 5 and the exhaust communication hole 4 have the relationship of Expression 14.

[Equation 14] It is necessary to be satisfied. Here, the angle α is α = 3
It is preferably set to 60 ° / n. At this time, since the exhaust communication holes 4 and the air supply communication holes 5 are arranged at equal intervals, the position design of the communication holes and the drilling work are facilitated.

In the case where a plurality of units are provided, a number of empty chambers 10 in which the fluid does not always flow out of the total number Z of chambers are formed between the units, and the relationship of Expression 15 is satisfied.

[Equation 15] The exhaust communication hole 4 and the air supply communication hole 5 are arranged at an angle α, and the size of the exhaust communication hole 4 and the air supply communication hole 5 is defined by Equation 16

[Equation 16] It is provided so as to satisfy the relationship shown by.

For example, when n = 4 and a = 1, as shown in FIG. 6A, the exhaust communication holes _4-1 , _4-2 and the air supply communication holes _5-1 , _{5-2 are provided.} Two and are arranged alternately.
The Check 10 without communicating hole between the rotation direction front row of exhaust communicating hole 4 _-1 and the air supply communicating hole _5-2 is formed. In this case, it is assumed that, as shown in FIG. 6B, all the air supply communication holes _5-1 , _5-2 and the exhaust communication holes _4-1 , _4-2 are gathered in one chamber. , All are housed in one room without overlapping in the radial direction. At this time, the air supply communication holes 5 _-1 , _5-2 and the exhaust communication holes 4 _-1 , _4-2 are set to have substantially the same size and shape, but the invention is not particularly limited to this. However, the size and shape may be changed between air supply and exhaust, and if necessary, the size and shape may be changed for each communication hole.

Further, exhaust communicating hole 4,4 _-1, 4 _-2, ...,
4 _-n and the air supply communicating hole _{5,5 -1, 5 -2, ...,} 5 -n hole shape, particularly limited not triangles and rectangles in a circle shown in FIG. 3,
Not only the elliptical shape and the rectangular shape but also the asymmetrical shape shown in FIG. 4 can be implemented. Generally, the amount of combustion air and the amount of combustion exhaust gas are set in a substantially balanced relationship, but in some cases, one communication hole may be set larger than the other communication hole. Alternatively, when the exhaust communication hole 4 and the air supply communication hole 5 have substantially the same size, the combustion gas expanded by combustion is discharged to the outside of the furnace without passing through the heat storage body 1, and other It is preferable to supply it to a heat treatment facility, a convection heat exchanger, an economizer, a heating facility or the like so that it can be used as a heat source. It should be noted that, even if the communication holes have a shape other than a circular shape, the relationships of the above-mentioned formulas 13 to 16 are established. β ₁ is a central angle circumscribing from the rotation center O of the switching means 3 to the exhaust communication hole 4, and β ₂ is a central angle circumscribing from the rotation center O of the switching means 3 to the intake communication hole 5.

Further, the angle α between the exhaust communication hole, for example, 4 _-1 and the air supply communication hole 5 _-1 , which are in a front-rear relationship, is set so that they do not communicate with the same chamber / compartment of the heat storage body 1 at the same time. It is set. Therefore, when based on the exhaust communicating hole 4 _-1 of the front row, when the front row of the exhaust communicating hole 4 _-1 is approaching the partition 8, the air supply communicating hole 5 _-1 adjacent room partition 8 at least present in the amount corresponding to a position separated in the exhaust communicating hole 4 _-1, further exhaust communicating hole 4 _-2 next chambers sharing of the partition 8
For at least the exhaust from at least the exhaust communicating hole 4 _-1 present in distant positions by communicating holes 5 _-1 minute for air supply, further a fourth air supply communicating hole of the chamber 5 _-2 sharing of the partition 8 from Communication hole 4
_-1 , the air supply communication hole _5-1 and the exhaust communication hole _4-2 are present at positions separated by three holes. That is, as shown in FIG. 6 (A), exhaust communicating hole 4 _-1 front row ahead of Check 10
When approaching inside, the room next to the same room 11 _-1 (one room after)
The air supply communication hole 5 _-1 does not reach the partition 8 with 12 _-1, and only the exhaust communication hole 4 _-1 in the front row extends over the front empty chamber 10 so that the two chambers communicate at the same time. . Then, the chamber exhaust communicating hole of the front row 4 _-1 when it is completely switched to the front of the chamber was empty chamber 10, was present exhaust communicating hole 4 _-1 front row ever 11 _-1 becomes an empty room, and the air supply communication hole 5 _-1 of the adjacent room 12 _{-2 at} the rear side comes into contact therewith, and only the second-row air supply communication hole 5 _-1 has two rooms 11 _-1 , 11 _-2 It moves to the vacant room 11 _-1 so as to straddle the room. In this way, the third column exhaust communicating hole 4 _-2, 4 column air supply communicating hole _5-2 is transferred to successively forward the chamber is switched fluid flow. That is, the vacant chamber 1 is rotated in the direction opposite to the rotation direction of the switching means 3.
The exhaust communication holes 4 _-1 , _4-2 and the supply air communication holes 5 _-1 , _5-2 are arranged in a positional relationship in which exhaust gas and supply air are switched so that 0 relatively rotates. ing.

In this embodiment, the switching means 3 is rotatably supported by the entrance / exit means 6 and the bearing means 15. The drive mechanism is provided so as to be rotatable continuously or intermittently. Although the drive mechanism is not particularly limited, for example, in the case of the present embodiment, a gear 22 is formed on the peripheral edge of the disc-shaped switching means 3 and a motor 21 having a drive gear 20 meshing with the gear 22 is provided in the switching means 3. It is arranged around and is driven by a motor. Of course, the present invention is not limited to this, and it may be rotationally driven by a friction wheel that is pressed against the peripheral edge of the switching means 3. Sealing materials 18 and 19 are interposed and sealed between the casing 13b housing the heat storage body 1 and the distribution chamber 2 and the switching means 3 and between the switching means 3 and the distribution chamber 2.

Although not shown, the exhaust system 34 and the air supply system 33 are connected to a push-in fan and an induction fan. Further, an ignition burner 37 for starting up is installed as needed.

The fuel nozzle 31 is arranged so as to penetrate the heat storage body 1 and be directly exposed or projected into the furnace interior 35. There is a slight gap 2 between the fuel nozzle 31 and the heat storage body 1.
4 is provided, and a part of the combustion air is made to flow as a cooling fluid. Of course, this cooling air is not flowed in some cases. More specifically, the fuel nozzle 31 penetrates through the center of the inlet / outlet means 6, the center of the switching means 3, the center of the distribution chamber 2 and the center of the heat storage body 1 and has an injection port (not shown) inside the furnace 35 or It is installed so as to project into the burner throat 32 and is supported by the casing 13a or the like. Here, the injection port is opened in the axial direction at the center of the tip.

Further, in front of the heat storage body 1 and the fuel nozzle 31, the burner is provided with bypass holes 25 as a plurality of exhaust holes through which the flow passage cross-sectional area is narrowed toward the tip side and the combustion exhaust gas can pass therethrough and be discharged. A throat 32 is installed. The burner throat 32 is not necessarily installed, but the existence of the burner throat 32 prevents the combustion air A injected from the heat storage body 1 from being diffused, and the injection energy of the combustion air causes the burner throat 32 to pass through the bypass hole 25. NOx can be reduced by sucking the combustion exhaust gas to cause exhaust gas recirculation around the fuel jet flow and reducing hydrocarbon radicals generated in the fuel jet flow. Further, a part of the combustion exhaust gas sucked into the burner throat 32 through the bypass hole 25 is accompanied by the combustion air to increase the capacity of the combustion gas. Therefore, the combustion gas can be forced to reach farther.

According to the burner configured as described above, low NOx combustion can be realized as follows.

The switching operation between the air in the fuel and the exhaust gas will be described in detail with reference to FIGS. 1 and 3 as follows. First, when the combustion air A is introduced into the air supply chamber 6a of the inlet / outlet means 6, the combustion air A flows into the second chamber 9b of the distribution chamber 2 through the air supply communication hole 5 and is further applicable. Flows into the chamber / compartment 12 of the heat storage body 1. At this time, since the corresponding compartment / chamber of the heat storage body 1 is heated by the heat of the high-temperature gas / combustion exhaust gas E that had passed before the switching, the passing combustion air A takes away the heat of the heat storage body 1. The temperature is set to a high temperature, that is, a high temperature near the temperature of the combustion gas that has heated the heat storage body 1. Then, from around the fuel nozzle 31 arranged in the center of the heat storage body 1, the combustion air A having a high temperature of about 1000 ° C. is directly injected into the furnace 35 in parallel with the fuel F. On the other hand, the combustion exhaust gas F in the furnace 35 is introduced into the corresponding compartment 11 of the heat storage body 1 communicated with the exhaust chamber 6b of the inlet / outlet means 6 through the exhaust communication hole 4 by the action of the induction fan of the exhaust system 34. To be done. Then, the combustion exhaust gas whose temperature is lowered by heating the section 11 of the heat storage body 1 flows into the first chamber 9a of the distribution chamber 2 and is then discharged to the exhaust chamber 6b through the exhaust communication hole 4. .

Next, when the switching means 3 is continuously or intermittently rotated counterclockwise from the state shown in FIG.
First, the exhaust communication hole 4 extends over the third chamber 9c of the left adjacent distribution chamber, and the first chamber 9a and the third chamber 9c simultaneously communicate with the exhaust chamber 6b. Therefore, the combustion exhaust gas E in the furnace passes through the first compartment and the third compartment (the portion indicated by reference numeral 10 in FIG. 3) of the heat storage body 1 before the first chamber 9a of the distribution chamber 2.
And the third chamber 9c, and flows out to the exhaust chamber 6b which is connected to these chambers 9a and 9c through the exhaust communication hole 4. And it is exhausted. After that, the exhaust communication hole 4 is completely switched to the third chamber 9c (the part that was the empty chamber indicated by reference numeral 10 in FIG. 3), and then the second chamber 9b.
The air supply communication hole 5 that was occupied by the space is switched to the first chamber 9a (the chamber portion indicated by the reference numeral 11 in FIG. 3), and the second chamber 9b (the chamber indicated by the reference numeral 12 in FIG. 3). The area partitioned by is an empty room. In other words, the combustion exhaust gas E is flown into the vacant chamber 10 where the fluid has not been flown until now,
The combustion air A is made to flow into the chamber 11 in which the combustion exhaust gas E has been made to flow, and the fluid is not made to flow in the chamber 12 in which the combustion air A has been made to flow. Therefore, the heat storage body 1 is heated by the heat of the combustion exhaust gas E, and the combustion air A passing through the heated heat storage body 1 is warmed by the heat of the heat storage body 1. At this time, the fluid flow is switched while communicating with the two chambers even when the two chambers are occupying the vacant chamber 10, so that the fluid flow is not interrupted. Then, the combustion exhaust gas E is sequentially switched to the combustion air A next to the combustion exhaust gas E without interruption. Therefore, the combustion air A passes through the heated heat storage body 1 and has a high temperature close to the exhaust gas temperature, for example, 10
The hot air of about 00 ° C. is supplied to the furnace 35.

The high temperature combustion air A, which corresponds to almost the entire amount of combustion air, and the fuel F injected from the fuel nozzle 31 are separately injected into the furnace 35 and burned while spreading in the furnace 35. At this time, since the combustion air A and the fuel F rapidly reduce their flow velocities and widen the mixing region, it is a condition that is originally difficult to burn. However, since the combustion air A itself has a high temperature of about 1000 ° C., it easily burns even under such conditions. That is, it burns slowly. This slow combustion produces less NOx. The combustion gas generated by the slow combustion is used in the inside of the furnace 35 as described above, then passes through a part of the heat storage body 1 and is discharged to the outside of the furnace. Here, the switching of the heat storage body 1 is, for example, 20 seconds to 90 seconds.
Second, preferably about 10 seconds, or when the combustion gas discharged through the heat storage body 1 reaches a predetermined temperature, for example, about 200 ° C.

The above embodiment is one example of the preferred embodiment of the present invention, but the present invention is not limited to this, and various modifications can be made without departing from the gist of the present invention. For example, the switching means 3 may form each communication hole in almost all regions except a portion for forming a vacant chamber.

7 to 9 show another embodiment of the switching means 3. In the switching means 3 of this embodiment, the exhaust communication hole 4 and the air supply communication hole 5 are holes of a size occupying substantially the entire area of each chamber of the heat storage body 1 divided into N chambers, and the combustion exhaust gas E is discharged. The arrangement relationship is such that at least one or more empty chambers can be partitioned between the flowing chamber and the chamber for flowing the combustion air A.
That is, the heat storage body 1 has N (N = n + 2, where n is a positive integer of 2 or more) in the circumferential direction and is always a fluid because of the division by the distribution chamber 2 or the division of the heat storage body itself as in the above-described embodiment. The number of chambers in which the fluid flows is equal to the number of chambers in which the fluid flows. here,
The number of chambers divided into the heat storage body 1 is at least two vacant chambers (fluid does not flow) with one set of a supply chamber 12 for flowing combustion air and one exhaust chamber 11 for flowing combustion exhaust gas. Room) 10,
It is a combination of 10 and 4 rooms / compartment is the minimum number of rooms / compartment. The number of exhaust chambers 11 and the number of supply chambers 12 do not have to be the same, and in some cases, as shown in FIG. 9, the number of supply chambers 12 is larger than the number of exhaust chambers 11. It is also possible to do so or vice versa. In this case, when the ratio between the exhaust gas amount and the air amount is different, there is an advantage that the heat transfer surface area of the heat storage body used can be changed for each ratio and an appropriate heat balance can be maintained. Further, a plurality of chambers / compartments may be made to flow the fluid simultaneously by one communication hole. For example, in FIG.
Alternatively, as shown in FIG. 8, two or three or more chambers / compartments may be simultaneously connected to one communication hole. In this case, the size of the vacant room required for switching is reduced, and the switching time can be shortened. Further, it is also possible to form a plurality of units with N chambers as one unit. That is, the total number Z of rooms is Z =
It is represented by a · N (where a is a positive integer excluding 0 indicating the number of units). In this case, the positions of the communication holes 4 and 5 are set such that one group of exhaust chambers 11 and one group of air supply chambers 12 are alternately arranged with one vacant chamber 10 interposed. This relationship is illustrated in FIGS. 8 and 9. 8 and 9, the fuel nozzle 31 is not shown for convenience of drawing.

The switching means 3 includes one or more chambers / compartments 12, 12 _-1 , 12 _-2 , ..., Of the heat storage body 1.
12 _-n and the supply chamber 6a for communicating the air supply communication hole 5,
One or more rooms / compartments 11, 11 _-1 , 1,
1 _-2, ..., and a 11 _-n and the exhaust communicating hole for communicating the exhaust chamber 6b 4 only the number of units a. For example, in FIG.
In this case, the number of units a is 1, so that each unit has one air supply communication hole 5 and one exhaust communication hole 4. It is necessary that the exhaust communication hole 4 and the air supply communication hole 5 satisfy a positional relationship such that at least one or more empty chambers 10 can be defined between them. That is, in the case of one unit, the air supply communication hole 5 and the exhaust communication hole 4 are represented by the formula 17

[Equation 17] Are arranged at intervals of an angle C represented by. Here, the angle C is an angle corresponding to the vacant space, that is, (360 ° / (n
It is preferable to set it slightly larger than +2)).
In this case, it is possible to completely prevent the supply air and the exhaust gas from being mixed with each other, and to minimize the pressure loss. Further, when a plurality of units are provided, the exhaust communication hole 4 and the air supply communication hole 5 are provided.
Between and

[Equation 18] The intervals of the angle C represented by are set, and the exhaust communication holes 4 and the air supply communication holes 5 for the number of units are alternately arranged.

The switching of the fluid flow in the switching means configured as described above is performed by simultaneously moving both the exhaust communication hole 4 and the air supply communication hole 5 to the respective front empty chambers 10, 10. Be seen. When the exhaust communication hole 4 and the air supply communication hole 5 completely occupy the front chamber / compartment that was an empty room, the exhaust communication hole 4 and the air supply communication hole 5 communicate with each other until now. The room / compartment that was open will be vacant. For example, taking the case of one unit and eight chambers shown in FIG. 7 as an example, the rearmost chambers / compartments 11 _-3 and 12 _{-3 in} the rotation direction are empty. At this time, the exhaust communication hole 4 and the air supply communication hole 5 are provided in the chamber / compartment 11 _-1 ,
11 _-2 , 11 _-3 and 12 _-1 , 12 _-2 , 12 _-3 and new chambers / compartments 10 and 10 are simultaneously crossed over four compartments, but can be switched while simultaneously supplying fluid to a plurality of compartments. Since the vacant chamber 10 is also used, the flow of fluid is not interrupted, and the exhaust communication hole 4 on the front side is one position before the section where the communication hole 5 for air supply is approaching. Since the exhaust gas is exhausted and the combustion air supplied is not mixed with each other in the same section.

As shown in FIG. 11, the switching means 3 and the fuel nozzle 31 are integrally rotated by welding or the like, while the fuel injection hole 23 of the fuel nozzle 31 is switched.
Provided in the radial direction of the air supply communication hole 5 of the switching means 3
It is also possible to simultaneously rotate the fuel nozzle 31 and the fuel nozzle 31 to inject the fuel F into the air flow A at all times. In this case, the fuel jet merges with the jet air for combustion that travels straight as a cross-wind jet. At this time, in the combustion air jet, a pair of circulation flows which are mutually opposite vortex regions are generated by the crosswind jet and the fuel jet, and the fuel jet is taken into the inside of the jet of the combustion air. After that, the high-concentration region of the combustion air jet is complicatedly diffused in the cross section by the large and small vortex clusters generated inside each of the two vortex regions, and at the same time, the fuel jet taken in the center of the jet is also dispersed. Diffused. That is, after the fuel jet is taken into the combustion air jet, the fuel jet gradually spreads throughout the inside of the jet, and is mixed with the high temperature combustion air and burned in the combustion air jet. During that time, combustion occurs on the surface of the fuel jet mixed with the combustion air to generate NOx, and the NOx is taken into the fuel jet by the circulation flow and rapidly reduced.

FIG. 12 shows another embodiment. The heat storage type low NOx burner of this embodiment is the heat storage body 1 of the burner shown in FIG.
Number N of compartments of the heat storage body 1 on the outlet side (inside the furnace 35) of the
The same number of independent nozzles 38, ..., 38 are installed. The nozzles 38, ..., 38 are opened in the burner throat 32, respectively. In this embodiment, the nozzle 3
8, 38 are formed integrally with the burner throat 32. However, the present invention is not limited to this, and the nozzles 38, ...
And may be formed. The burner throat 32 has 3 inside the furnace
5. A plurality of bypass holes 25 for discharging the combustion exhaust gas of No. 5
Is provided. The bypass hole 25 is preferably provided for each nozzle 38. The nozzle 38,
..., 38, the rear end side is the chamber / compartment 10, 1 of the heat storage body 1.
It is widened to the size occupied by the regions 1 and 12, and the tip side is narrowed to a desired size. This nozzle 38, ..., 3
By changing the size of the opening of 8, the injection speed (momentum) of the combustion air can be freely controlled, and the shape and properties of the flame can be changed. For example, it can be a strong flame or a weak flame with no momentum.

FIG. 13 shows another embodiment. In the heat storage type low NOx burner of this embodiment, except for the burner throat 32 portion of the burner of the embodiment of FIG. 12, the nozzles 38, ..., 38 connected to each compartment / chamber of the heat storage body 1 are directly placed in the furnace 35. , 38, the combustion air is directly injected into the furnace 35, while the combustion exhaust gas is sucked into the heat storage body 1 from the nozzle 38.

According to the burner thus constructed, the combustion air is injected from any one of the independent nozzles 38 by the continuous or intermittent rotation of the switching means 3, while the one of the nozzles is operated. After that, the combustion exhaust gas is sucked to the heat storage body 1 side. Since the switching of the flow of the combustion air and the combustion exhaust gas to the heat storage body 1 is performed by the rotation of the switching unit 3, the flow sequentially moves to the adjacent nozzle 38. Therefore, as shown in (A) to (C) of FIG. 14, the position at which the combustion air is injected sequentially changes in the circumferential direction, and a flame position in the furnace 35 forms a non-stationary flame in which the flame position always rotates in the circumferential direction. To do. Such a non-stationary flame can avoid overheating of the tube even with a very high temperature flame when installing an object to be heated around the burner, for example, when using it for a water tube boiler.

Further, in this embodiment, the inlet / outlet means 6 is formed by a cylindrical member, but it is not particularly limited to this, and may be formed by a double cylindrical body such as a hexagon, a quadrangle or a triangle. Further, the above-mentioned embodiment shows the minimum unit of the burner system, and two or more burner systems may be arranged in the furnace body.

[0049]

As is apparent from the above description, the heat storage type low NOx burner of the present invention is arranged such that the exhaust system and the air supply system are sequentially arranged in any one of the chambers of the heat storage body which are divided into N chambers in the circumferential direction. Fuel is continuously injected into the furnace from a fuel nozzle that penetrates through the center of the heat storage body, and fuel is continuously injected into the furnace by moving the area around it to continuously inject hot combustion air from the heat storage body into the furnace. Therefore, the effect similar to the alternating combustion can be obtained only by switching the combustion air while continuously injecting the fuel, and the equipment for switching the fuel and the control device for adjusting the injection timing are not required. Further, since the chamber through which the combustion air and the combustion exhaust gas pass is switched using the vacant chamber, stable combustion can be secured without the combustion air being reduced or stagnant at the time of switching. In addition, since the fuel nozzle is continuously cooled by the injected fuel, there is no risk of burning and fuel coking, and the arrangement position and structure are not complicated.

Further, in the present invention, when the fuel and the combustion air are injected substantially parallel to each other and separately injected, the high temperature combustion air and the fuel cause slow combustion everywhere in the furnace to accumulate heat. The generation of NOx can be significantly reduced as compared with the conventional heat storage type burner without losing the characteristics of the type burner.

Further, in the present invention, when the fuel nozzle is rotated together with the switching means to join the fuel jet with the combustion air jet from the side, the fuel jet is taken into the high temperature combustion air jet and the inside of the combustion air jet is taken. Since the NOx is diffused and burned by the NOx, the generated NOx is further taken into the fuel jet flow and reduced, and NOx is significantly reduced.

Further, in the present invention, the switching of the hot air is continuously performed, so even if the excess air ratio is set to the necessary minimum, stable combustion is maintained without oxygen shortage in the furnace, It is possible to minimize the amount of CO generated.

Further, in the case of the invention of claim 7, the combustion air is directly injected into the furnace from each independent nozzle, and the location is changed so that the combustion air is rotated in the circumferential direction around the combustion nozzle. It is possible to form a non-stationary flame in which the flame formed therein rotates in the circumferential direction. Therefore, even in the case of a very high temperature flame, it is possible to avoid overheating of the object to be heated arranged around the burner, for example, the tube of the water tube boiler. Moreover, by changing the size of the nozzle opening, the injection speed (momentum) of the combustion air into the furnace can be freely controlled, and the shape and properties of the flame can be changed.

Further, when a burner throat is provided in front of the heat storage body and the combustion nozzle, the flow passage cross-sectional area is narrowed toward the tip side and a plurality of exhaust holes are provided around it, the combustion air injected from the heat storage body Since a part of high-temperature combustion gas is accompanied by the combustion air by the injection energy, exhaust gas recirculation can be performed to reduce NOx and increase the capacity of the combustion gas to reach the interior of the furnace.

[Brief description of drawings]

FIG. 1 is a perspective view showing a basic configuration of a heat storage type low NOx burner of the present invention.

FIG. 2 is a sectional view showing an embodiment of a heat storage type low NOx burner of the present invention.

FIG. 3 is an explanatory diagram showing a relationship between an exhaust communication hole and an air supply communication hole.

FIG. 4 is an explanatory diagram showing another example of an exhaust communication hole and an air supply communication hole.

FIG. 5 is a list showing the number N of chambers in relation to the number n of chambers through which a fluid flows and the number a of units.

FIG. 6 is a diagram showing a relationship between an exhaust communication hole and an air supply communication hole when n = 4 and a = 1, (A) is a layout view of all communication holes, and (B) is one chamber. It is explanatory drawing of the state which gathered all the holes in.

FIG. 7 is a principle view showing another embodiment of the switching means.

FIG. 8 is a list showing the arrangement of chambers in relation to the number of chambers in which a fluid flows and the number of units a.

FIG. 9 is a list diagram showing the arrangement of chambers in the relationship between the number of chambers in which a fluid flows and the number of units a in an example in which the numbers of communication holes for exhaust and supply holes are different.

FIG. 10 is an explanatory view showing another embodiment of the heat storage body, (A)
Is a type in which plates are radially arranged, (B) is a type in which corrugated plates are radially arranged, (C) is a type in which pipes are bundled,
(D) shows a type in which a heat storage material is filled in a casing divided into N chambers.

FIG. 11 is a longitudinal sectional view showing another embodiment of the heat storage type low NOx burner of the present invention.

FIG. 12 is a longitudinal sectional view showing another embodiment of the heat storage type low NOx burner of the present invention.

FIG. 13 is a longitudinal sectional view showing another embodiment of the heat storage type low NOx burner of the present invention.

FIG. 14 is an explanatory diagram of operations (A) to (C) in which the flame rotates in the circumferential direction in the heat storage type low NOx burner used in the embodiment of FIG. 13.

FIG. 15 is a principle diagram of a conventional heat storage type burner.

[Explanation of symbols]

 1 Heat Storage Body 2 Distribution Chamber 3 Switching Means 4 Exhaust Communication Hole 5 Air Supply Communication Hole 6 Entry / Exit Means 6a Air Supply Chamber 6b Exhaust Chamber 7 Partition Walls 9a, 9b, 9c Distribution Chamber 10 Heat Storage Vacancy 11 Heat Storage Chamber for exhausting body 12 Chamber for supplying air to heat storage body 13a, 13b Casing F Fuel A High temperature combustion air E Combustion exhaust gas 31 Fuel nozzle 32 Burner throat 35 In furnace

Claims (13)

[Claims] 1. N (N = n + 1, where n is a positive even number equal to or greater than 2 is the number of chambers through which fluid always flows) circumferentially is evenly divided into chambers, and fluid is axially distributed in each chamber. A heat storage body that can pass through, a fuel nozzle that penetrates the center of this heat storage body to inject fuel directly into the furnace, and is connected to an air supply chamber connected to the combustion air supply system and a combustion gas exhaust system. A double tubular inlet / outlet means partitioned from the exhaust chamber by an annular partition wall and the heat storage body and the inlet / outlet means are interposed to shut off the heat storage body and the inlet / outlet means, while the air supply is provided. A supply air communication hole that communicates the chamber and the heat storage body and an exhaust communication hole that communicates the exhaust chamber and the heat storage body are alternately arranged by n / 2 each, and rotate continuously or intermittently. The exhaust chamber and the air supply chamber of the inlet / outlet means are arranged in any one of the heat storage chambers divided into N chambers. It consists of switching means to communicate next,
Further, the exhaust communication hole and the air supply communication hole of the switching means are arranged at an interval of an angle α represented by Formula 1, and Further, the relationship between the size of the air supply communication hole and the size of the exhaust communication hole is expressed by Equation 2 as follows: A heat storage type low NOx burner which is satisfied and which continuously injects fuel into the furnace and directly injects high temperature combustion air around the fuel from the heat storage body into the furnace. 2. A total number of chambers Z (where Z = a, where N = n + 1, n is a positive even number of 2 or more and indicates the number of chambers in which the fluid always flows).・ N, a is a positive integer excluding 0 indicating the number of units) A plurality of unit chambers are formed in the heat storage body, and a total of Z chambers is a unit of a vacant chamber in which fluid does not always flow. Configuring N
Formed between the chamber and the N chamber of the other unit, and the arrangement angle α between the exhaust communication hole and the air supply communication hole has the relationship of Equation 3, Moreover, the relationship between the size of the exhaust communication hole and the supply air communication hole is expressed by the following equation (4). The heat storage type low NO according to claim 1, characterized in that
x burner. 3. N (N = n + 2, where n is a positive integer greater than or equal to 2 is the number of chambers in which fluid always flows) circumferentially is evenly divided into chambers, and fluid is axially distributed in each chamber. A heat storage body that can pass through, a fuel nozzle that penetrates the center of this heat storage body to inject fuel directly into the furnace, and is connected to an air supply chamber connected to the combustion air supply system and a combustion gas exhaust system. A double tubular inlet / outlet means partitioned from the exhaust chamber by an annular partition wall and the heat storage body and the inlet / outlet means are interposed to shut off the heat storage body and the inlet / outlet means, while the air supply is provided. An air supply communication hole that communicates the chamber and the heat storage body and an exhaust communication hole that communicates the exhaust chamber and the heat storage body are arranged at an interval of an angle C represented by Formula 5, and ] And switching means for continuously or intermittently rotating to sequentially communicate the exhaust chamber and the air supply chamber of the inlet / outlet means with any of the chambers of the heat storage body divided into N chambers. A heat storage type low NOx burner characterized by continuously injecting fuel and injecting high temperature combustion air around the fuel directly into the furnace from the heat storage body. 4. A total number of chambers Z (where Z = a, where N = n + 2, n is a positive integer of 2 or more and indicates the number of chambers in which the fluid always flows) is defined as one unit. · N, a is a positive integer excluding 0, which indicates the number of units, is defined in the heat storage body as a compartmentalized chamber of a plurality of units, and Equation 6 is provided between the exhaust communication hole and the air supply communication hole. Number 6] The heat storage type low NOx burner according to claim 3, wherein an interval of an angle C represented by is set. 5. The heat storage type according to claim 1, wherein the fuel injected from the fuel nozzle and the combustion air injected from the heat storage body are injected substantially in parallel. Low NOx burner. 6. The fuel nozzle is rotated simultaneously with the switching means so that fuel is always injected from a side toward a combustion air flow injected from the heat storage body. The heat storage type low NOx burner according to any one of 1. 7. The outlet of the heat storage body inside the furnace is provided with a nozzle that is independent of each other and communicates with each chamber in which the heat storage body is partitioned. The heat storage type low NOx burner described. 8. A burner throat having a flow passage cross-sectional area narrowed toward the tip side in front of the heat storage body and the fuel nozzle, and a burner throat having a plurality of exhaust holes in the periphery thereof is installed.
8. A heat storage type low NOx burner according to any one of 1 to 7. 9. The heat storage body is partitioned into an aN (where a is the number of units) chambers in the circumferential direction between the heat storage body and the switching means, and fluid can pass in the axial direction. The heat storage type low NOx burner according to any one of claims 1 to 8, wherein the heat storage type low NOx burner is divided into an aN chamber by providing the distribution chamber. 10. The heat storage type low NOx burner according to claim 1, wherein the heat storage body has a honeycomb shape having a large number of cell holes communicating in the axial direction. 11. The heat storage body is formed by arranging a large number of pipe-shaped heat storage materials in a radial direction so that a fluid passes through in an axial direction. Heat storage type low NOx burner. 12. The heat storage type low NOx burner according to claim 1, wherein the heat storage body is formed by arranging a large number of flat or corrugated heat storage materials in a radial pattern. 13. The heat storage bodies are independent of each other and are aN
The heat storage type low NOx burner according to any one of claims 1 to 8, wherein a block or a small piece of heat storage material is filled in a casing which is partitioned into a chamber and through which a fluid can pass in the axial direction.