JP2014145486A - Cylindrical surface combustion burner and heater including the same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve a fire transfer property on the external surface of a side wall part 2s of a combustion cylinder 2, stabilize a combustion state at an early stage after ignition and reduce combustion sounds, in a cylindrical surface combustion burner 1 and a heater including the same.SOLUTION: A cylindrical surface combustion burner 1 includes a cylindrical combustion cylinder 2 in which a plurality of injection holes 3 jetting gaseous mixture M supplied inside to an external surface and combusting it are dispersedly formed, and a cylindrical ventilation cylinder 5 that is provided in a state of covering the external surface of the combustion cylinder 2 and comprises a porous material or fiber material. On the external surface of the combustion cylinder 2, a groove part 10 extending in the circumferential direction of the combustion cylinder 2 is formed.

Description

The present invention includes a cylindrical combustion cylinder in which a plurality of injection holes for spraying and burning an air-fuel mixture supplied inside is dispersedly formed,
The present invention relates to a cylindrical surface combustion burner including a cylindrical through cylinder made of a porous material or a fiber material provided so as to cover an outer surface of the combustion cylinder, and a heating device including the same.

As a conventional surface combustion burner for burning an air-fuel mixture ejected from a plurality of nozzle holes on a combustion surface in which a plurality of nozzle holes are dispersedly arranged, a cylindrical combustion cylinder having an outer surface of a side wall portion as a combustion surface is provided. So-called cylindrical surface combustion burners are known (see, for example, Patent Documents 1 and 2).
Such a cylindrical surface combustion burner is mainly used in such a form that it is inserted into a combustion gas passage leading to an exhaust opening in a heating device. In such a heating device, combustion is performed by combustion of an air-fuel mixture on the outer surface of the side wall portion of the combustion cylinder. A furnace tube or the like that forms a gas passage is heated, and a heating object existing outside the furnace tube is indirectly heated by the radiant heat of the furnace tube.
As such a cylindrical surface combustion burner, one having a cylindrical through cylinder made of a porous material or a fiber material provided so as to cover the outer surface of the side wall portion of the combustion cylinder is known. The one using a metal knit is sometimes called a metal knit burner.
And the cylindrical surface combustion burner provided with such a through-cylinder has a sufficient through-cylinder that continuously burns the air-fuel mixture on the outer surface of the side wall of the combustion cylinder and covers the outer surface of the side wall of the combustion cylinder. By burning red, stable combustion can be realized.

JP 2001-165408 A JP 2009-74703 A

However, the cylindrical surface combustion burner has a convex curvature in the circumferential direction on the outer surface of the side wall portion of the combustion cylinder that becomes the combustion surface, so that the combustion cylinder is compared with a surface combustion burner having a planar combustion surface. In particular, the fire transfer property in the circumferential direction of the combustion cylinder on the outer surface of the side wall portion of the cylinder becomes inferior. Therefore, from the time of ignition by the spark plug until the entire passing cylinder is sufficiently red-hot, so-called combustion vibrations occur in which the combustion location changes sequentially, and a relatively long time is required for stable combustion. There has been a problem that combustion sounds such as relatively loud ignition sounds and fire transfer sounds are generated.
In particular, in a heating apparatus in which such a cylindrical surface combustion burner is inserted into a combustion gas passage, if the combustion noise is amplified by resonance in the combustion gas passage, a very loud sound opens the combustion gas passage to the outside. Since it may occur from the exhaust opening, reduction of combustion noise was an important issue to be solved.

  The present invention has been made paying attention to such a point, and an object of the present invention is to improve the fire transfer property on the outer surface of the side wall portion of the combustion cylinder in the cylindrical surface combustion burner and the heating device including the same. In addition, the present invention is to provide a technique capable of stabilizing the combustion state at an early stage after ignition and further reducing combustion noise.

In order to achieve this object, a cylindrical surface combustion burner according to the present invention comprises:
A cylindrical combustion cylinder in which a plurality of injection holes for injecting and burning the air-fuel mixture supplied to the outside is burnt;
A cylindrical surface combustion burner provided with a cylindrical through cylinder made of a porous material or a fiber material provided so as to cover the outer surface of the combustion cylinder,
The first characteristic configuration is
A groove portion is formed on the outer surface of the combustion cylinder so as to extend in the circumferential direction of the combustion cylinder.

According to the first characteristic configuration, a part of the air-fuel mixture ejected from the plurality of nozzle holes on the outer surface of the side wall portion of the combustion cylinder (hereinafter sometimes simply referred to as “outer surface”) Before penetrating into the through cylinder that covers the outer surface of the cylinder, it flows into the groove formed on the outer surface of the combustion cylinder and is guided in the circumferential direction of the combustion cylinder. By forming such a flow of the air-fuel mixture in the circumferential direction along the groove portion, even if the entire through-cylinder is not sufficiently red-hot immediately after the ignition, it is sufficiently heated by flowing through the groove portion. Since the air-fuel mixture or the flame formed by igniting the air-fuel mixture flows well in the circumferential direction of the combustion cylinder, the fire transfer property on the outer surface of the combustion cylinder can be improved.
Therefore, according to the present invention, it is possible to realize a cylindrical surface combustion burner capable of stabilizing the combustion state at an early stage after ignition and further reducing combustion noise.

In addition to the first characteristic configuration described above, the second characteristic configuration of the cylindrical surface combustion burner according to the present invention includes:
The edge on the outer surface side of each of the plurality of nozzle holes is formed so as to expand toward the outside.

According to the second characteristic configuration, since the edges of the plurality of nozzle holes expand in the outer surface of the combustion cylinder, in other words, chamfered, the plurality of injection holes are formed. A part of the air-fuel mixture ejected from the hole diffuses along the edge and flows well into the groove.
Therefore, the amount of air-fuel mixture flowing in the circumferential direction along the groove formed on the outer surface of the combustion cylinder increases, and the fire transfer property on the outer surface of the combustion cylinder can be further improved, and the combustion state is stabilized. And combustion noise can be further reduced.

In addition to any of the first to second feature configurations described above, the third feature configuration of the cylindrical surface combustion burner according to the present invention includes:
The groove is formed so as to connect a plurality of the nozzle holes.

According to the third characteristic configuration, since the plurality of nozzle holes arranged in the circumferential direction are connected by the groove portion on the outer surface of the combustion cylinder, the air-fuel mixture ejected from the plurality of nozzle holes is further improved. It will flow into the groove.
Therefore, the amount of air-fuel mixture flowing in the circumferential direction along the groove formed on the outer surface of the combustion cylinder increases, and the fire transfer property on the outer surface of the combustion cylinder can be further improved, and the combustion state is stabilized. And combustion noise can be further reduced.

In addition to any of the first to third feature configurations described above, the fourth feature configuration of the cylindrical surface combustion burner according to the present invention is as follows:
The groove is a groove formed to extend in a direction perpendicular to the axial direction of the combustion cylinder,
The groove portions are distributed at a plurality of locations in the axial direction of the combustion cylinder.

  According to the fourth characteristic configuration, the single groove portion formed to extend perpendicularly to the axial direction of the combustion cylinder on the outer surface of the combustion cylinder is dispersedly arranged at a plurality of locations along the coaxial direction. A simple configuration can be adopted. Then, on the outer surface of the combustion cylinder, the air-fuel mixture ejected from the plurality of nozzle holes and flowing into the groove section is suppressed along the groove section in a state in which the air-fuel mixture is suppressed from flowing to the tip side along the axial direction of the combustion cylinder. It will flow well in the circumferential direction of the combustion cylinder. Therefore, the air-fuel mixture can be actively flowed in the circumferential direction of the combustion cylinder to further improve the fire transfer property on the outer surface of the combustion cylinder, further realizing stabilization of the combustion state and reduction of combustion noise. can do.

In addition to any of the first to fourth characteristic configurations described above, the fifth characteristic configuration of the cylindrical surface combustion burner according to the present invention includes:
An ignition unit for igniting an air-fuel mixture ejected to the outside of the combustion cylinder;
On the outer surface of the combustion cylinder, the occupation rate of the nozzle holes arranged in the ignition region near the ignition unit is larger than the occupation rate of the nozzle holes arranged in the non-ignition region other than the ignition region It is in.

  According to the fifth characteristic configuration, the occupancy rate of the injection holes in the ignition region is larger than the occupancy rate of the injection holes in the non-ignition region other than the ignition region on the outer surface of the combustion cylinder. More air-fuel mixture is ejected than in the non-ignition region. Therefore, in the ignition region, it is possible to stably ignite a large amount of air-fuel mixture in the ignition part and form a stable flame, thereby improving the fire transfer property on the outer surface of the through-cylinder and stabilizing the combustion state. And reduction of combustion noise can be realized.

The sixth feature configuration of the cylindrical surface combustion burner according to the present invention is in addition to any of the first to fifth feature configurations described above,
A band-shaped guide band is wound around the outer surface of the through-cylinder in the circumferential direction of the through-cylinder.

According to the sixth characteristic configuration, since the belt-shaped guide band is wound around the outer surface of the through-cylinder, it is formed by igniting the air-fuel mixture or the air-fuel mixture that has become hot by passing through the through-cylinder. A part of the flame is guided in the circumferential direction on the outer surface of the through-cylinder well along the guide band.
By forming a high-temperature air-fuel mixture or flame flow in the circumferential direction on the outer surface of the through-cylinder in this way, even if the entire through-cylinder is not sufficiently red hot immediately after the ignition point, the outer surface of the through-cylinder It is possible to improve the fire transfer property in the circumferential direction at, and to stabilize the combustion state and reduce the combustion noise.

Moreover, the heating device according to the present invention for achieving this object is as follows:
A heating device in which a combustion cylinder of a cylindrical surface combustion burner is inserted into one end side of a furnace cylinder in which a combustion gas passage leading to an exhaust opening is formed,
Its feature configuration is
The said cylindrical surface combustion burner exists in the point comprised as the cylindrical surface combustion burner which concerns on this invention.

  That is, according to the characteristic configuration of the heating device according to the present invention, the same effect as the above-described cylindrical surface combustion burner according to the present invention can be obtained, and the exhaust gas opening from the exhaust opening that opens the combustion gas passage to the outside can be obtained. Generation of combustion noise can be suppressed.

Side sectional view of metal knit burner of embodiment 1 is an exploded perspective view of the metal knit burner shown in FIG. The partial side view which shows the arrangement | positioning state of the nozzle hole and groove part in the combustion cylinder of the metal knit burner shown in FIG. Side sectional view of the steam generator of the embodiment Fig. 4 is a sectional view of the steam generator shown in Fig. 4 The perspective view of the steam generator shown in FIG. Schematic configuration diagram of an oven according to another embodiment

Embodiments of the present invention will be described with reference to the drawings.
The metal knit burner 1 shown in FIGS. 1 to 3 is configured as an embodiment of a cylindrical surface combustion burner according to the present invention, and the steam generator 20 shown in FIGS. It is comprised as a heating device concerning. Hereinafter, each detailed structure is demonstrated in order.

[Metal knit burner (tubular surface combustion burner)]
First, the metal knit burner 1 comprised as embodiment of the cylindrical surface combustion burner which concerns on this invention is demonstrated based on FIGS. 1-3.
1 is a side sectional view of the metal knit burner 1 according to the embodiment, FIG. 2 is an exploded perspective view of the metal knit burner 1 according to the embodiment, and FIG. 3 is a metal knit according to the embodiment. 2 is a partial side view showing an arrangement state of nozzle holes 3 in a combustion cylinder 2 of a burner 1. FIG.

As shown in FIGS. 1 and 2, the metal knit burner 1 includes a cylindrical combustion cylinder 2 in which a plurality of injection holes 3 for injecting and burning an air-fuel mixture M supplied to the inside is dispersed, It is configured as a cylindrical surface combustion burner provided with a cylindrical through cylinder 5 made of a fiber material provided so as to cover the outer surface of the combustion cylinder side wall 2 s of the combustion cylinder 2.
The combustion cylinder 2 is formed of a steel pipe made of a heat-resistant material (for example, made of stainless steel) with a distal end portion 2f sealed and a proximal end portion 2r opened, and a plurality of injection holes 3 are formed in the side wall portion.

The through-cylinder 5 is configured by a so-called metal knit made of a fiber material by knitting a wire made of a heat-resistant material (for example, stainless steel) into a knit shape. The through-cylinder 5 has an inner diameter that is substantially the same as the outer diameter of the combustion cylinder 2, and the entire circumference of the outer surface of the combustion cylinder side wall 2s is inserted by inserting the combustion cylinder 2 therein. Is in a state of covering.
The through-cylinder 5 is fixed to the combustion cylinder 2 by spot welding at a plurality of locations in the plane and brazing at the front end and the base end.

A mixer (not shown) that mixes natural gas city gas 13A and air to form an air-fuel mixture M is connected to the base end 2r of the combustion cylinder 2, and the pre-mixed air-fuel mixture M is used as a base. The gas is supplied into the combustion cylinder 2 through the end 2r.
Then, the air-fuel mixture M supplied to the inside of the combustion cylinder 2 is ejected to the outside of the combustion cylinder 2 through the plurality of injection holes 3 formed in the combustion cylinder 2. The air-fuel mixture M ejected to the outside of the combustion cylinder 2 on the outer surface of the combustion cylinder side wall portion 2s permeates through the through-cylinder 5 disposed outside the combustion cylinder 2 and burns while flowing out of the outer surface of the through-cylinder 5. However, due to this combustion, the through-cylinder 5 becomes hot and becomes red hot, and the mixture M that flows out next is heated by the red heat, so that the combustion is continued.

Moreover, the combustion cylinder 2 is being fixed in the state which penetrates the flange part 9 fixed to a furnace wall (illustration omitted). Further, the flange portion 9 has a posture extending toward the front end side, and generates an air-fuel mixture M which is ejected to the outside of the combustion cylinder 2 and further passes through the through cylinder 5 in an ignition gap 6g (an example of an ignition portion). A spark rod 6 that is ignited by a spark to be generated and a frame rod 7 that detects that a flame F is formed on the outer surface of the through-cylinder 5 are fixed.
As the spark rod 6, a known spark rod that applies a voltage to intermittently generate sparks at the ignition gap 6g at the tip is used. On the other hand, as the frame rod 7, an electric flame by the flame F is used. A known frame rod that detects a weak current generated through the flame F using a rectifying action is used.

Next, a detailed arrangement state of the plurality of nozzle holes 3 on the outer surface of the combustion cylinder side wall 2s will be described.
The arrangement state of the plurality of injection holes 3 is arranged in parallel at equal intervals along the circumferential direction of the combustion cylinder 2 (that is, the roll direction with respect to the axial direction X of the combustion cylinder 2, hereinafter referred to as “roll direction R”). The plurality of injection holes 3 are in a state of being distributed and arranged at equal intervals along the axial direction X of the combustion cylinder 2.

Further, as shown in FIG. 3, the occupancy rate of the injection hole 3 in the ignition region 2a (region surrounded by the one-dot chain line in FIG. 3) in the vicinity of the ignition gap 6g on the outer surface of the combustion cylinder side wall 2s is It is set to be larger than the occupation ratio of the nozzle holes 3 in the non-ignition region. In the present embodiment, the ignition region 2a is a region including the injection hole 3 at a distance approximately half of the circular cross section of the combustion cylinder 2, for example, centering on the injection hole 3 disposed at a position closest to the ignition gap 6g. It is said that.
Specifically, in the non-ignition region other than the ignition region 2a, four nozzle holes 3 having the same diameter in the roll direction R are arranged in parallel at equal intervals.
On the other hand, in the ignition region 2a, a plurality of nozzle holes 3 having the same diameter as the nozzle holes 3 arranged in the non-ignition region are arranged, but the arrangement interval in the roll direction R is half that of the non-ignition region. Therefore, the occupation ratio of the nozzle hole 3 is doubled with respect to the non-ignition region.

  And since the occupation rate of the injection hole 3 in the ignition region 2a is larger than the occupation rate of the injection hole 3 in the non-ignition region in this way, the ignition region 2a has a larger amount than the other non-ignition regions. The air-fuel mixture M is ejected. Therefore, immediately after the ignition time point when the supply of the air-fuel mixture M to the inside of the combustion cylinder 2 is started while applying a voltage to the spark rod 6 to generate a spark in the ignition gap 6g, a lot of the air-fuel mixture M Therefore, a stable flame F is formed because the sparks generated in the ignition gap 6g are stably ignited. In addition, by forming a stable flame F in the ignition region 2a in this way, the fire transfer property on the outer surface of the through-cylinder 5 is improved, and the combustion state is stabilized and the combustion noise is reduced. .

Further, a belt-shaped guide band 8 is wound around the outer surface of the through-cylinder 5 in the circumferential direction of the through-cylinder 5, specifically, in the spiral direction of the through-cylinder 5.
As the guide band 8, a coil spring in which a wire made of a heat resistant material (for example, stainless steel) is coiled is used.
Then, the air-fuel mixture M that has passed through the through-cylinder 5 and has reached a high temperature, or a part of the flame F that is formed by igniting the air-fuel mixture M, is satisfactorily along the guide band 8. Is guided in the circumferential direction. Therefore, the flow of the high-temperature air-fuel mixture M or the flame F in the circumferential direction on the outer surface of the through-cylinder 5 is formed in this way, so that the entire through-cylinder 5 is not sufficiently red-hot immediately after the ignition point. In this mode, the fire transfer from the ignition region 2a sequentially in the circumferential direction and the axial direction occurs stably, and the fire transfer property on the outer surface of the through-cylinder 5 is improved, and the combustion state is stabilized and the combustion noise is reduced. Will be.

In the metal knit burner 1 of the present embodiment, a groove 10 is formed on the outer surface of the combustion cylinder side wall 2s, and one of the air-fuel mixture M ejected from the plurality of injection holes 3 on the outer surface of the combustion cylinder side wall 2s. The portion flows into the groove 10 before being introduced into the through-cylinder 5 that covers the outer surface of the combustion cylinder side wall 2 s and is guided in the circumferential direction of the combustion cylinder 2. By forming such a flow of the air-fuel mixture M in the circumferential direction (roll direction R) along the groove portion 10, the groove portion 10 can be formed even if the entire through-cylinder 5 is not sufficiently red hot immediately after the ignition point. The air-fuel mixture M sufficiently heated by the flow or the flame F formed by igniting the air-fuel mixture M will flow well in the circumferential direction of the combustion cylinder 2, and as a result, the combustion cylinder side wall 2s. This will improve the transferability of fire on the outer surface.
And the fire transfer property in the outer surface of the combustion cylinder side wall part 2s is improved in this way, so that the combustion state is stabilized at an early stage after ignition and further the combustion noise is reduced.

Further, the groove 10 formed on the outer surface of the combustion cylinder side wall 2 s is a single groove 10 that extends in the circumferential direction of the combustion cylinder 2, specifically, the roll direction R with respect to the cylinder axis of the combustion cylinder 2. Are distributed at equal intervals at a plurality of locations along the axial direction X of the combustion cylinder 2.
The groove 10 is formed as a recess having a substantially square cross section, and the width thereof is substantially equal to the width of the nozzle hole 3. Then, each of the plurality of groove portions 10 dispersedly arranged along the axial direction X passes through the centers of the plurality of injection holes 3 arranged in parallel in the roll direction R, thereby connecting the plurality of injection holes 3 to each other. It is formed in a state to do.
Therefore, the air-fuel mixture M ejected from the plurality of nozzle holes 3 flows into the groove portion 10 more satisfactorily, and the fire transfer property on the outer surface of the combustion cylinder side wall portion 2s is further improved.

Furthermore, the edge 3a on the outer surface side of each of the plurality of nozzle holes 3 opened in the groove 10 is formed in a state of expanding in diameter toward the outside, specifically, in a state of being chamfered by 45 °. ing.
Therefore, on the outer surface of the combustion cylinder side wall portion 2s, a part of the air-fuel mixture M ejected from the plurality of nozzle holes 3 diffuses along the edge portion 3a and flows into the groove portion 10 favorably. The fire transfer property on the outer surface of the cylindrical side wall portion 2s is further improved.
The

[Steam generator (heating device)]
Next, the steam generator 20 configured as a heating device according to the present invention will be described with reference to FIGS.
4 is a side sectional view of the steam generator 20 according to the embodiment, and FIG. 5 is an elevational sectional view (VV section of FIG. 4) of the steam generator 20 according to the embodiment. 6 is a perspective view of the steam generator 20 according to the embodiment.

As shown in FIGS. 4-6, the steam generator 20 is comprised as a heating apparatus provided with the burner which burns the air-fuel mixture M in the combustion gas passage 50 which leads to the exhaust opening 25a, and as such a burner, A metal knit burner 1 having the same configuration as that shown in FIGS. 1 to 3 is provided.
Since this metal knit burner 1 has the same configuration as that shown in FIGS. 1 to 3 described above, a detailed description of the configuration is omitted, but the fire transfer property on the outer surface of the combustion cylinder side wall 2s. Is improved, the combustion state is stabilized early after ignition, and the combustion noise is further reduced. Therefore, at the start of operation of the steam generator 20, the ignition sound and combustion sound that flow out from the exhaust opening 25a are reduced.

Hereinafter, the overall configuration of the steam generator 20 will be described.
As shown in FIG. 4, the combustion gas passage 50 is configured by connecting a furnace tube 21, an intermediate header 22, and a smoke pipe 23. As indicated by solid line arrows in FIG. 4, the furnace tube 21 circulates the hot exhaust gas E generated by the combustion of the air-fuel mixture M by the metal knit burner 1 in the axial direction X of the main body tank 60 (left and right direction in FIG. 4). It is introduced into the main body tank 60 from one side (right side in FIG. 4, hereinafter referred to as “base end side”) and directed toward the other side in the axial direction X (left side in FIG. 4, hereinafter referred to as “tip side”). It is distributed. The intermediate header 22 guides and distributes the exhaust gas E that has passed through the furnace tube 21 to the smoke pipe 23 by turning its flow direction back. The smoke tube 23 circulates the exhaust gas E that has passed through the furnace tube 21 from the distal end side toward the proximal end side. An exhaust header 24 is provided outside the base end side in the axial direction X of the main body tank 60, and the exhaust gas E that has passed through the smoke pipe 23 is supplied to the exhaust header 24 and discharged to the outside of the main body tank 60. .
As described above, the combustion gas passage 50 is configured in a two-pass structure in which the exhaust gas E flows twice between the base end side and the tip end side in the axial direction X of the main body tank 60.

  A partition plate 66 that partitions the internal space of the main body tank 60 into an upper space and a lower space is provided. The lower space is configured as a water vapor generating section that heats the water W and generates the water vapor S. The partition plate 66 does not partition the upper side space and the lower side space in a sealed state, but a gap that communicates the lower side space and the upper side space on the proximal end side and the distal end side in the axial direction X of the main body tank 60. It has. The water vapor S generated in the water vapor generating section which is the lower space is supplied to the upper space of the partition plate 66 through the gap.

  Below the partition plate 66, water W is stored up to the reference water level T, and the furnace tube 21 and the smoke tube 23 are arranged in parallel with each other in a state where the furnace tube 21 and the smoke tube 23 are submerged below the reference water level T. Yes. Around the furnace tube 21 and the smoke tube 23 is a passage through which water W and water vapor S can freely flow. As shown in FIGS. 5 and 6, one furnace tube 21 is provided, and a plurality of smoke tubes 23 are provided at intervals in the circumferential direction of the furnace tube 21 so as to surround the periphery of the one furnace tube 21. It has been.

As shown in FIG. 1, the main body tank 60 has a horizontal cylindrical shape composed of a cylindrical outer peripheral wall and a pair of opposed outer walls that block both side surfaces of the cylindrical outer peripheral wall. Yes.
Above the outer peripheral wall of the main body tank 60, there is provided a water vapor outlet 61 for taking out the water vapor S generated in the main body tank 60. In addition, a pressure gauge attachment port 62 to which a pressure gauge (not shown) is attached, temperature A thermometer attachment port 63 to which a meter (not shown) is attached is provided. On the other hand, as shown in FIG. 5, a water supply port 64 for supplying water W for generating water vapor S in the main body tank 60 and a water level in the main body tank 60 are detected below the outer peripheral wall of the main body tank 60. A water level gauge connection port 65 to which a water level gauge (not shown) to be displayed is connected is provided. The water level gauge is provided in the main body tank 60 near the water vapor outlet 61 and is configured to detect the reference water level T. In addition, an opening / closing valve (not shown) is attached to the water vapor outlet 61.

Further, a flange-like burner fixing portion 60 a for inserting and fixing the metal knit burner 1 is provided on the outer wall on the base end side of the main body tank 60. And the flange part 9 of the metal knit burner 1 is fixed to the burner fixing | fixed part 60a in the state which inserted the combustion cylinder 2 in the inside of the furnace cylinder 21. FIG.
Then, exhaust gas E is generated by combustion on the outer surface of the through-cylinder 5 that covers the combustion cylinder 2 of the metal knit burner 1, and the exhaust gas E is introduced into the combustion gas passage 50. The metal knit burner 1 can be automatically ignited by the spark rod 6, and can be adjusted by a thermal power adjusting device after ignition.

As shown in FIG. 4, the combustion gas passage 50 is configured by connecting the inside of the furnace tube 21, the intermediate header 22, and the smoke pipe 23 in order in a communicating state. The base end side of the furnace tube 21 is connected to and supported by the base end side outer wall of the main body tank 60.
Similarly, the smoke pipe 23 is connected to and supported by the base side outer wall of the main body tank 60, and a base end side opening 23r that is an exhaust port for the exhaust gas E from the smoke pipe 23 is formed in the connection support. Further, the intermediate header 22 is supported on the tip side of the furnace tube 21 and the smoke tube 23.

  The furnace tube 21 is composed of a single circular tube, and the center axis of the furnace tube 21 is provided below the center axis of the main body tank 60 while providing the center axis of the furnace tube 21 along the axial direction X of the main body tank 60. It arrange | positions so that it may be located. The furnace tube 21 extends through the exhaust header 24 provided along the proximal end side outer wall of the main body tank 60 and extends to the distal end side, and is connected to the intermediate header 22.

The intermediate header 22 is provided on the distal end side inside the main body tank 60, and is disposed on the proximal end side of the intermediate header outer peripheral portion 22s and the intermediate header outer peripheral portion 22s that is a cylindrical outer peripheral portion along the inner surface of the outer peripheral wall of the main body tank 60. The intermediate header base end side surface 22r provided and the intermediate header front end side surface 22f provided on the front end side of the intermediate header outer peripheral portion 22s are formed in a hollow cylindrical shape.
A furnace tube 21 is connected to a lower portion of the intermediate header base end side surface 22r in a communicating state. On the other hand, six smoke tubes 23 along the inner surface of the outer peripheral wall of the main body tank 60 are connected to the upper portion of the intermediate header base end side surface 22r in a communicating state. In this way, the intermediate header 22 is configured to enable guide circulation in which the exhaust gas E flowing from the furnace tube 21 is branched into the six smoke pipes 23 and introduced.

  Further, the intermediate header front end side surface 22 f of the intermediate header 22 is disposed in a non-contact state with a space in the axial direction X of the main body tank 60 between the inner wall of the front end side outer wall of the main body tank 60. In this way, by providing a gap between the intermediate header front end side surface 22f and the front end side outer wall of the main body tank 60, and cooling the intermediate header front end side surface 22f with the water W existing in the gap, the intermediate header front end side surface 22f. The heat transfer from the main body tank 60 to the front end side outer wall can be suppressed, and the temperature rise of the front end side outer wall of the main body tank 60 can be suppressed. As a result, the water W in the main body tank 60 is heated, and the water vapor S can be generated more effectively. Further, the generation of thermal stress between the intermediate header 22 and the front end side outer wall of the main body tank 60 is eliminated, and the front end side outer wall of the main body tank 60 and the intermediate header 22 are distorted, cracked, damaged, etc. Can be prevented.

As shown in FIG. 5, above the furnace tube 21, six smoke pipes 23 are juxtaposed side by side along the upper inner surface of the outer peripheral wall of the main body tank 60. As shown in FIG. 4, these six smoke pipes 23 connect the proximal end side opening 23 r of the smoke pipe 23 and the front end side face 24 f of the exhaust header 24 in a communicating state. Thus, the exhaust gas E introduced from the intermediate header 22 into the smoke pipe 23 flows from the front end side to the base end side of the main body tank 60 and flows into the exhaust space 51 formed inside the exhaust header 24.
The exhaust gas E flowing into the exhaust space 51 is discharged to the outside through an exhaust opening 25a provided at the upper end of the exhaust header 24.
The exhaust opening 25a is provided, for example, as an opening in a top plate 70 of a housing of a system kitchen (not shown) or a device housing the steam generator 20, and is open to the outside. Placed in.

As shown in FIGS. 4 to 6, the furnace tube 21 and the smoke tube 23 are arranged in a state where the furnace tube 21 and the smoke tube 23 are submerged under the surface of the water W accommodated in the main body tank 60, and the water W is heated by the exhaust gas E to form water vapor. A water vapor generating part for generating S is configured.
Further, water W is consumed due to the generation of water vapor S, and the water level in the main body tank 60 is lowered. However, when the water level is detected by a water level gauge (not shown) and the water level falls below the reference water level T, the water level is increased. The water W pressurized by a pressure pump (not shown) is configured to be supplied into the main body tank 60 from a water supply port 64 provided below the outer peripheral wall.
A partition plate 66 that divides the inside of the main body tank 60 into a lower water vapor generating portion and an upper space thereof is connected and supported to the outer peripheral wall in the width direction Y of the main body tank 60.

  Next, the flow from when the water W is supplied from the water supply port 64 into the main body tank 60 until the water vapor S is taken out from the water vapor outlet 61 will be described. First, the water W is pressurized into a main body tank 60 so as to reach a reference water level T from a water supply port 64 provided at a lower portion of the main body tank 60 by being pressurized by a pressure pump (not shown). Then, it is heated by the furnace tube 21 and the smoke tube 23 to evaporate to become water vapor S and rises to the upper part of the main body tank 60, and after water droplets are separated, it flows into the upper space of the partition plate 66 through the gap, It is taken out from the water vapor outlet 61.

  The steam generator 20 configured as described above attenuates the combustion sound that propagates through the plurality of combustion gas passages 50 formed inside each of the plurality of smoke pipes 23 and merges in the exhaust space 51 as much as possible. It is comprised so that the noise which leaks from the opening part 25a can be reduced, The detail is demonstrated below.

  The exhaust header 24 is flattened with the plurality of smoke pipes 23 connected to the front end side surface 24f, with the axial direction X of the plurality of smoke pipes 23 in the transverse section as the short direction and the width direction Y perpendicular to the short direction as the long direction. Exhaust gas 51 configured to form an exhaust space 51 formed by extending a horizontal cross section in the height direction Z and flowing through the inside of the plurality of smoke pipes 23 toward the base end side in the axial direction X E rises after flowing into the exhaust space 51 from the front end side surface 24f of the exhaust header 24, and is discharged from the exhaust opening 25a provided at the upper end thereof.

Further, the exhaust header 24 is configured to extend toward the top plate 70 thereabove, and the ceiling 51t of the exhaust space 51 formed therein is an open air opening provided on the top plate 70. It is supposed to be located directly below 70a.
And the exhaust opening 25a is opened in the ceiling part 51t of the exhaust space 51 in a state where the cross section of the exhaust space 51 is narrowed in the width direction Y (the left-right direction in FIG. 5) which is the longitudinal direction.
Specifically, the exhaust space 51 has a flat rectangular parallelepiped shape that is translated upward without changing the flat cross section, and the ceiling portion 51t has a longitudinal direction. An opening is formed in the center portion in the width direction Y (left-right direction in FIG. 5). And the exhaust pipe 25 of predetermined height is connected to the opening formed in the center part of the ceiling part 51t, and the upper end opening part is made into the exhaust opening part 25a.
That is, the height of the exhaust header 24 is set as long as possible so that the ceiling portion of the exhaust space 51 formed inside the exhaust header 24 is located directly below the outside air release portion 70a provided above the exhaust header 24. Has been.

Therefore, even if the combustion sound generated on the outer surface of the combustion cylinder side wall 2 s of the metal knit burner 1 propagates through the combustion gas passage 50 and reaches the exhaust space 51, the combustion gas formed inside each smoke tube 23. Since the expansion ratio of the channel cross-sectional area in the flow direction of the exhaust gas E from the passage 50 to the exhaust space 51 becomes very large, the exhaust space 51 effectively acts as a so-called expansion silencer, and the energy of the combustion sound is reduced. Attenuating over a wide range is attenuated.
And the exhaust opening 25a opened to the ceiling 51t of the exhaust space 51 is in a state where the cross section of the exhaust space 51 is narrowed in the width direction Y which is the longitudinal direction of the flat cross section of the exhaust space 51. Since only the combustion sound in which the energy is dispersed can pass through the exhaust opening 25a due to being opened, it leaks as noise from the exhaust opening 25a. Leakage noise is reduced.

  Further, the exhaust pipe line 25 connected to the ceiling part 51t of the exhaust space 51 connects the ceiling part 51t of the exhaust space 51 very close to each other and the exhaust opening part 25a disposed in the outside air release part 70a. For this reason, it is formed as a very short conduit. Therefore, amplification due to combustion noise resonance in the exhaust pipe 25 is suitably suppressed.

Next, when the steam generator 20 configured as described above is used to gradually change the width w and height h of the cross section of the exhaust pipe 25 as shown in FIG. An experimental example of listening sound confirmation for confirming the magnitude of combustion sound leaking from 25a will be described.
The dimensions of the exhaust space 51 formed in the exhaust header 24 provided in the steam generator 20 used in this experiment are 140 mm in width (length in the left-right direction (width direction Y) in FIG. 5) and thick. The height (length in the left-right direction (axial direction X) in FIG. 4) is 20 mm, and the height (length in the vertical direction (height direction Z) in FIG. 4) is 400 mm. The width of the cross section of the exhaust pipe 25 in the thickness direction of the exhaust space 51 is 20 mm, which is the same as the thickness of the exhaust space 51.
The results of this experiment are shown in [Table 1] below.

As shown in the experimental results of Table 1 above, it was confirmed that the leakage of combustion noise from the exhaust opening 25a was reduced as the flow passage cross-sectional area of the exhaust opening 25a was reduced.
In addition, when the cross-sectional area of the exhaust opening 25a is small (width w is 10 to 11 mm), the height h of the exhaust pipe 25 is 15 mm or less to reduce combustion noise leakage. More preferably, it was confirmed that the leakage of combustion noise was further reduced if the height h was 10 mm or less. Further, when the exhaust pipe 25 is omitted (the height h of the exhaust pipe 25 is set to 0 mm) and the exhaust opening 25a is formed directly on the ceiling of the exhaust space 51, the leakage of combustion noise is most reduced. It was confirmed that
Note that if the cross-sectional areas of the exhaust pipe 25 and the exhaust opening 25a are too small, the exhaust of the exhaust gas E is hindered, the combustion state of the metal knit burner 1 becomes unstable, and the factors such as the discharge of CO It becomes. Therefore, it is necessary to maintain the flow path cross-sectional area at least the minimum cross-sectional area that can maintain the stable combustion state of the metal knit burner 1.

[Other Embodiments]
Finally, other embodiments of the present invention will be described. Note that the configuration of each embodiment described below is not limited to being applied independently, and can be applied in combination with the configuration of other embodiments as long as no contradiction arises.

(1) In the above embodiment, the example in which the heating device according to the present invention is applied to the steam generator 20 has been described. However, the heating device according to the present invention may be applied to another heating device such as an oven. . Hereinafter, the example which applied the heating apparatus which concerns on this invention to oven is demonstrated based on FIG.
The oven 100 shown in FIG. 7 includes the steam generator 20 shown in FIGS. 4 to 6 similar to that described in the above embodiment, and the steam S generated by the steam generator 20 is stored in the interior 110. Supplied.
In addition, a metal knit burner 1 ′ different from the metal knit burner 1 included in the steam generator 20 is built in, and the exhaust pipe E generated in the metal knit burner 1 ′ is provided in the inside 110 of the heating tube 102. The water vapor S stirred by the fan 103 in the interior 110 is heated to become superheated steam.
And the cooking target object in the store | warehouse | chamber 110 is heat-cooked with this overheated steam.
Further, the exhaust opening 25a of the steam generator 20 and the exhaust opening 102a formed at the tip of the heating tube 102 are arranged in a form to be inserted into the opening formed in the top plate 170, The exhaust gas E discharged from the exhaust openings 25a and 102a is discharged to the outdoors from a ventilation fan (not shown) provided in the sky.
And also about the oven 100 comprised in this way, the fire transfer property of the built-in metal knit burner 1, 1 'is improved, a combustion state is stabilized early after ignition, and also the combustion noise is reduced. For this reason, ignition noise and combustion noise are reduced at the start of operation.

(2) In the above embodiment, the cylindrical surface combustion burner according to the present invention is configured as the metal knit burners 1 and 1 ′ having the metal-knit through cylinder 5, but the cylinder 5 is made of metal knit such as porous ceramics. You may comprise by other porous materials or fiber materials.

(3) In the metal knit burner 1, 1 ′ of the above-described embodiment, the outer diameter of the combustion cylinder side wall 2 s is expanded toward the outer edge 3 a of each of the plurality of nozzle holes 3. However, the chamfering of 45 ° may be omitted.

(4) In the metal knit burner 1, 1 ′ of the above embodiment, the groove portion 10 is formed in the outer surface of the combustion cylinder side wall portion 2 s so as to connect a plurality of the injection holes 3. You may form as the groove part 10 which passes along the location in which the said nozzle hole 3 is not formed, without connecting 3.

(5) In the metal knit burner 1, 1 ′ of the above embodiment, the groove 10 formed to extend perpendicular to the axial direction X of the combustion cylinder 2 is formed on the outer surface of the combustion cylinder side wall 2 s. However, the grooves 10 may be formed in a spiral shape on the outer surface of the combustion cylinder side wall 2s.

(6) In the metal knit burner 1, 1 'of the above embodiment, the combustion cylinder 2 is formed in a cylindrical shape, but it may be formed in an elliptical cylinder or a rectangular cylinder.

  The present invention relates to a cylindrical combustion cylinder in which a plurality of injection holes for injecting and burning an air-fuel mixture supplied inside is dispersed, and a state in which the plurality of injection holes are covered from the outer surface of the combustion cylinder Can be suitably used as a cylindrical surface combustion burner provided with a cylindrical through-cylinder made of a porous material or a fiber material and a heating device provided with the same.

DESCRIPTION OF SYMBOLS 1, 1 ': Metal knit burner 2: Combustion cylinder 2a: Ignition area | region 2s: Side wall part 3: Injection hole 3a: Edge part 5: Through-cylinder 6: Spark rod 6g: Ignition gap (ignition part)
8: Guide band 10: Groove 20, 20 ': Steam generator (heating device)
21: Furnace 23: Smoke tube 24: Exhaust header 25: Exhaust pipe 25a: Exhaust opening 50: Combustion gas passage 51: Exhaust space 51t: Ceiling 70: Top plate 70a: Open air opening 100: Oven (heating device)
102a: exhaust opening 170: top plate E: exhaust gas M: mixture S: water vapor R: roll direction X: axial direction Y: width direction Z: height direction

Claims (7)

A cylindrical combustion cylinder in which a plurality of injection holes for injecting and burning the air-fuel mixture supplied to the outside is burnt;
A cylindrical surface combustion burner provided with a cylindrical through cylinder made of a porous material or a fiber material provided so as to cover the outer surface of the combustion cylinder,
A cylindrical surface combustion burner in which a groove portion extending in the circumferential direction of the combustion cylinder is formed on the outer surface of the combustion cylinder.   2. The cylindrical surface combustion burner according to claim 1, wherein each of the plurality of nozzle holes has an outer surface side edge portion formed in a state of increasing in diameter toward the outside.   The cylindrical surface combustion burner according to claim 1 or 2, wherein the groove is formed so as to connect a plurality of the nozzle holes. The groove is a groove formed to extend in a direction perpendicular to the axial direction of the combustion cylinder,
The cylindrical surface combustion burner according to any one of claims 1 to 3, wherein the grooves are dispersedly arranged at a plurality of locations in the axial direction of the combustion cylinder. An ignition unit for igniting an air-fuel mixture ejected to the outside of the combustion cylinder;
The occupancy rate of the nozzle holes arranged in the ignition region in the vicinity of the ignition part on the outer surface of the combustion cylinder is larger than the occupancy rate of the nozzle holes arranged in the non-ignition region other than the ignition region. Item 5. The cylindrical surface combustion burner according to any one of Items 1 to 4.   The cylindrical surface combustion burner according to any one of claims 1 to 5, wherein a belt-shaped guide band is wound around an outer surface of the through-cylinder in a circumferential direction of the through-cylinder. A heating device in which a combustion cylinder of a cylindrical surface combustion burner is inserted into one end side of a furnace cylinder in which a combustion gas passage leading to an exhaust opening is formed,
The said cylindrical surface combustion burner is a heating apparatus comprised as a cylindrical surface combustion burner of any one of Claims 1-6.

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