JP4139794B2 - Bright flame burner - Google Patents

Description

  The present invention provides an annular primary air discharge port and an annular secondary air on an outer peripheral portion of a gas supply cylinder having a gas ejection part on the tip side, as viewed in the axial direction along the axial direction of the gas supply cylinder. A discharge port is provided in a state where the primary air discharge port is located inside, and a secondary swirling means for swirling the secondary combustion air discharged from the secondary air discharge port is provided, from the gas ejection part The present invention relates to a luminous flame burner configured to burn ejected gas fuel in a state where a luminous flame is formed.

Such a luminous flame burner is used for secondary combustion in which gas fuel ejected from a gas ejection section is swung from a primary combustion air discharged from an annular primary air outlet and swirled from an annular secondary air outlet. It burns in a state where a bright flame is formed with air, and is used as a heat source for various heating furnaces such as a glass melting furnace.
That is, from an annular primary air discharge port located at the outer peripheral portion of the gas supply cylinder in an axial direction view (hereinafter sometimes referred to as a gas supply cylinder axial direction view) along the axial direction of the gas supply cylinder. By discharging the primary combustion air and discharging the secondary combustion air in a state of swirling from the annular secondary air discharge port located outside the primary air discharge port as viewed in the axial direction of the gas supply cylinder, While suppressing the flow of the secondary combustion air to the swirl center side, the gas fuel jetted from the gas jetting part and the combustion air are gently mixed to generate carbon particles. A bright flame is formed by burning.

  In such a luminous flame burner, conventionally, as shown in FIG. 8, a cylindrical inner cylindrical body 41 and a cylindrical outer cylindrical body 42 are provided concentrically with their tips aligned with each other. The distal end portion of the cylindrical gas supply cylinder 5 is concentrically positioned at the proximal end portion of the body 41, the gas ejection portion N is provided at the distal end of the gas supply cylinder 5, and the peripheral edge of the distal end of the gas supply cylinder 5 The annular primary air discharge port 9 is formed by the inner peripheral surface of the inner cylinder 41, and the annular secondary air discharge port 11 is formed by the tip of the inner cylinder 41 and the tip of the outer cylinder 42. The secondary combustion air A flowing in the secondary combustion air flow path 43 is swirled in the secondary combustion air flow path 43 between the inner cylinder 41 and the outer cylinder 42 so that the secondary combustion air A is swirled. A secondary swirl blade 44 was provided as a swivel means.

  That is, the gas fuel G is ejected from the gas ejection part N, and the primary combustion air A is linearly discharged from the annular primary air discharge port 9 along the axial direction, and the gas fuel G and the primary combustion are discharged. The inside air cylinder 41 is caused to flow toward the cylinder tip side while being mixed with the working air A, and is allowed to flow out from the front end opening of the inner cylinder body 41 in a mixed state. As such, the gas fuel G and the primary combustion air A The secondary combustion air A is discharged in a swirling state from the annular secondary air discharge port 11 located at the outer peripheral portion of the portion that is mixed and flows out from the inner cylindrical body 41.

  The gas fuel G ejected from the gas ejection part N is burned while generating carbon particles in the oxygen shortage state in the primary combustion air A while flowing in the inner cylindrical body 41. It is made to flow out from the tip, and further, the secondary combustion air A from the secondary air discharge port is mixed and burned at the outflow portion, and burned by a so-called two-stage combustion type so as to form a luminous flame. (For example, refer nonpatent literature 1.).

Japan Burner Study Group, “Practical gas combustion equipment handling” (first edition), Nikkan Kogyo Shimbun, March 25, 1985, P65, lines 2-8, Fig. 5.18 (b)

However, conventionally, the primary combustion air discharged in a straight line from the primary air discharge port is prevented from being diffused by the cylinder wall while flowing in the inner cylinder, and thus easily flows to the cylinder center side. Since the gas fuel and the primary combustion air are easy to mix while flowing in the inner cylinder and the gas fuel is easy to burn, carbon particles are hardly generated.
Therefore, conventionally, since it is difficult to generate carbon particles, the generation rate of luminous flame is low, and there is room for improvement.

  This invention is made | formed in view of this situation, The objective is to provide the luminous flame burner which can improve the incidence rate of luminous flame.

The luminous flame burner according to the present invention has an annular primary air discharge port and an annular shape on the outer peripheral portion of a gas supply cylinder provided with a gas ejection part on the tip side, as viewed in the axial direction along the axial direction of the gas supply cylinder. Secondary air discharge port is provided in a state where the primary air discharge port is located on the inside, and a secondary swirling means for swirling secondary combustion air discharged from the secondary air discharge port is provided, The gas fuel ejected from the gas ejection part is configured to burn in a state of forming a luminous flame,
The first characteristic configuration includes a plurality of blade bodies dispersed along a circumferential direction of the primary air discharge port, and primary swirl vanes that swirl the primary combustion air discharged from the primary air discharge port are provided.
The inclination angle at which each of the blade bodies of the primary swirl blade is inclined to one side in the circumferential direction with respect to the axial center of the primary air discharge port as viewed in the radial direction of the primary air discharge port is in the range of 20 to 40 °. is set to,
The gas jetting part is located on the outer peripheral side of the straight-going gas jetting part jetting gas fuel along the flow direction of the primary combustion air discharged from the primary air discharge port, and the straight-going gas jetting part And it is characterized by the point comprised with the radial gas ejection part which ejects gas fuel radially .

  That is, the inventors of the present invention have made intensive studies to improve the incidence of luminous flame, provided primary swirling blades that swirl the primary combustion air discharged from the primary air discharge port, and Inclination angle at which each blade body is inclined to one side in the circumferential direction with respect to the axial center of the primary air discharge port when viewed in the radial direction of the primary air discharge port (hereinafter, sometimes simply referred to as the inclination angle of the blade body) ) Was set in the range of 20 to 40 °, it was found that the generation amount of carbon particles can be increased and the generation rate of luminous flame can be improved.

  That is, the primary air is discharged from the annular primary air discharge port located on the outer periphery of the gas supply cylinder as viewed in the axial direction of the gas supply cylinder while being swung by the primary swirl vane. When both the primary combustion air and the secondary combustion air are discharged in a swirling state from the discharge port and the annular secondary air discharge port on the outer side, both the primary combustion air and the secondary combustion air are on the swivel center side. The flow to the outside is suppressed, and the gas fuel flow jetted from the gas jetting part is swirled in a state of covering the outer peripheral part of the gas fuel flow, so that it flows outside the gas fuel flow jetted from the gas jetting part. It is possible to gradually mix the gas fuel with the primary combustion air and the secondary combustion air in the form of mixing with the primary combustion air or the secondary combustion air.

  As such, the gas fuel, the primary combustion air, and the secondary combustion air are mixed with the primary combustion air or the secondary combustion air from the gas fuel flow from the gas ejection portion that flows outside. When mixing with each of the combustion airs is performed gradually, the outside of the gas fuel stream is mixed with the primary combustion air or the secondary combustion air and burned by the combustion heat. Since the inner one is heated and thermally decomposed to generate carbon particles, it is possible to burn while generating carbon particles efficiently.

However, even if the primary swirl vane is provided, the smaller the inclination angle of the blade body of the primary swirl vane, the weaker the swirl force of the primary combustion air and the easier the primary combustion air flows to the swirl center side. As a result, the amount of carbon particles generated tends to decrease.
Then, the inventors of the present invention have found that the lower limit of the inclination angle of the blade body, which can increase the generation amount of carbon grains and improve the generation rate of bright flames, is 20 °.

In addition, the larger the tilt angle of the blade of the primary swirl vane, the more gently the gas fuel and primary combustion air are mixed to increase the amount of carbon particles generated. Then, the mixing of the gas fuel and the primary combustion air becomes too slow and tends to lift easily.
Then, the inventors of the present invention are able to sufficiently suppress the lift and maintain the stable combustion, while increasing the generation amount of carbon particles and improving the generation rate of the luminous flame, which can improve the luminous flame generation rate. It was found that the upper limit of was 40 °.
In short, when a primary swirl vane for swirling the primary combustion air discharged from the primary air discharge port is provided and the inclination angle of the blade body of the primary swirl vane is set in a range of 20 to 40 °, carbon is stably burned. The amount of generated particles can be increased, and a bright flame burner that can improve the generation rate of bright flames can be provided.

Further, according to the first feature configuration, although the gas fuel radially ejected from the radial gas ejection section is gently mixed with the primary combustion air and the secondary combustion air flowing in the swirl state, the straight gas ejection Combusted faster by mixing with the primary combustion air or secondary combustion air faster than the gas fuel ejected from the section, while the gas fuel ejected from the straight gas ejection section is discharged from the primary air discharge port The amount of carbon particles generated from the gas fuel ejected from the straight gas ejection part is gradually mixed with the primary combustion air or the secondary combustion air flowing along the flow direction of the primary combustion air. Since it increases further, the gas fuel ejected from the straight gas ejection part is stably burned while efficiently generating carbon particles in a state where the gas fuel is held by the flame of the gas fuel combustion from the radial gas ejection part .
In other words, it is possible to improve the stability of combustion while efficiently generating carbon particles, so it is possible to widen the adjustment range of combustion conditions, such as adjustment of the air ratio, and improve usability. be able to.

By the way, if the gas jetting part is composed only of a straight gas jetting part that jets gas fuel along the flow direction of the primary combustion air discharged from the primary air discharge port, the amount of carbon particles generated will increase. However, since the mixing of the gas fuel with the primary combustion air and the secondary combustion air tends to be slower, the adjustment range of the combustion conditions while maintaining stable combustion is somewhat narrowed, which is convenient. This is somewhat disadvantageous in terms of improvement.
In addition, if the gas jetting part is constituted only by the radial gas jetting part that jets the gas fuel radially, the mixing of the gas fuel, the primary combustion air, and the secondary combustion air can be accelerated to stabilize the combustion. However, since mixing with the primary combustion air and the secondary combustion air becomes faster, the amount of carbon particles generated is reduced, which is somewhat disadvantageous for improving the luminous flame generation rate.
Accordingly, it is possible to improve the usability while sufficiently improving the generation rate of the luminous flame.

In addition to the first feature configuration, the second feature configuration is
The ratio of the amount of gaseous fuel ejected from the straight gas ejecting portion and the amount of gaseous fuel ejected from the radial gas ejecting portion is set in a range of 1: 9 to 5: 5. .

That is, the inventors of the present invention have intensively studied to improve the generation rate of luminous flames, and in the case of having the above first characteristic configuration, the amount of gas fuel ejected from the straight gas ejection portion and the radial gas ejection If the ratio of the amount of gas fuel ejected from the section (hereinafter sometimes referred to as a straight-to-radiant gas ejection ratio) is set in the range of 1: 9 to 5: 5, the luminous flame generation rate is further improved. It was found that this is preferable.

  That is, when the ratio of the amount of jet from the straight gas jet portion is smaller than 1: 9, the ratio of the straight gas jet to the radiant gas jet ratio from the straight gas jet portion that is more likely to generate carbon particles than the radial gas jet portion. Since the amount of gas fuel injection is reduced, the generation rate of luminous flame cannot be improved by reducing the generation amount of carbon particles. On the other hand, the straight gas emission ratio is more than 5: 5. If the ratio of the amount of ejection from the section is large, more carbon particles can be generated, but combustion tends to be unstable, and the straight-to-radiant gas ejection ratio is in the range of 1: 9 to 5: 5. It has been found that the setting is preferable in order to further improve the generation rate of the luminous flame.

And the range of the flame which is formed becomes wide, so that the ratio of the amount of jets from the straight gas jet part is set to a small ratio in the range of 1: 9 to 5: 5. If the ratio of the amount of ejection from the straight gas ejection portion is set to a larger ratio, the width of the formed flame becomes narrower (in other words, the length becomes longer). Become).
Therefore, the flame can be formed in a predetermined shape while further improving the generation rate of the bright flame by setting the straight gas-to-radiant gas ejection ratio in the range of 1: 9 to 5: 5. .

In addition to either the first or second feature configuration, the third feature configuration is
The ratio of the discharge amount of primary combustion air from the primary air discharge port and the discharge amount of secondary combustion air from the secondary air discharge port is set in a range of 5:95 to 20:80. Features a point.

  That is, the inventors of the present invention have intensively studied to improve the generation rate of luminous flames, and in the one having the first or second characteristic configuration, the discharge amount of primary combustion air from the primary air discharge port And the ratio of the amount of secondary combustion air discharged from the secondary air discharge port (hereinafter sometimes referred to as primary to secondary air discharge ratio) in the range of 5:95 to 20:80 The present inventors have found that it is preferable to further improve the generation rate of luminous flame.

In other words, if the primary to secondary air discharge ratio is set to a ratio in which the ratio of the discharge amount from the primary air discharge port is smaller than 5:95, it flows in the vicinity of the flow region of the gas fuel ejected from the straight gas ejection portion. The primary combustion air that tends to be mixed with it becomes too small and the combustion tends to become unstable. On the other hand, the ratio of the discharge amount from the primary air discharge port is larger than the primary to secondary air discharge ratio of 20:80. If the ratio is set, the amount of primary combustion air that tends to flow near the flow region of the gas fuel jetted from the straight gas jet part and easily mix with it increases, and the generation amount of carbon particles decreases, resulting in a bright flame. It has been found that when the primary to secondary air discharge ratio is set in the range of 5:95 to 20:80, it is preferable to further improve the luminous flame generation rate. It was.
Therefore, by setting the primary to secondary air discharge ratio in the range of 5:95 to 20:80, the generation rate of the bright flame can be further improved.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
For example, as shown in FIGS. 6 and 7, the bright flame burner B is used for heating a glass melting furnace 30 for melting water glass. Since the melting temperature of the water glass is 1000 to 1300 ° C., the luminous glass burner B is heated to about 1000 to 1300 ° C. so that the water glass to be melted can be melted.

The glass melting furnace 30 is provided with a melting tank 32 in the lower part of the furnace body 31, and a rectangular furnace space 35 is defined in a plan view by four side walls 33 and a ceiling wall 34 at the upper part of the melting tank 32. It is configured.
The bright flame burner B is provided to be held in the burner installation opening 1 formed in the one side wall 33 so that the gas fuel and the combustion air are ejected laterally with respect to the upper side of the dissolution tank 32, and the ceiling wall 34. An exhaust port 36 is provided at the end opposite to the bright flame burner B side, and an exhaust passage 37 is connected to the exhaust port 36 so that a bright flame is generated above the dissolution tank 32 by the bright flame burner B. A flame F having a high rate is formed sideways, and the combustion exhaust gas is discharged from the exhaust port 36 through the exhaust passage 37.

A glass raw material inlet 38 is provided at each of the side walls 33 of the both side walls 33 connected to both ends of the burner installation side wall 33 provided with the bright flame burner B, and a bright flame at the bottom of the melting tank 32 is provided. A takeout port 39 is provided at the end opposite to the burner B side.
That is, the glass raw material is introduced into the melting tank 32 from the inlets 38 on both sides, and the glass raw material is melted while flowing toward the outlet 39, and clean molten glass is taken out through the outlet 39. It is configured.

As shown in FIGS. 1 and 2, the luminous flame burner B comprises a burner tile 2 that forms a part of the furnace wall and forms the circular burner installation opening 1, and a burner body that is attached to the burner tile 2. M, the blower 3 that supplies the combustion air A to the burner body M, and the combustion air A that is supplied to the burner body M by the blower 3 exchanges heat with the combustion exhaust gas flowing through the exhaust passage 37. An exhaust heat recovery heat exchanger 4 for preheating the combustion air A is provided.
The burner body M has a cylindrical gas supply cylinder 5 provided with a gas ejection part N on the tip side, a cylindrical inner combustion cylinder 6 through which the primary combustion air A flows, and a secondary combustion air A. A cylindrical outer combustion cylinder 7 to be flowed is integrally assembled in a state in which the gas supply cylinder 5, the inner combustion cylinder 6, and the outer combustion cylinder 7 are arranged in order from the inner side and arranged concentrically.

A description will be given of each part of the burner body M.
The gas supply cylinder 5 is provided with a tapered portion 5t having a smaller diameter on the distal end side and closed at the distal end and the rear end.
The inner combustion cylinder 6 is formed to have a smaller diameter than the burner installation opening 1 of the burner tile 2, and the outer combustion cylinder 7 has an outer diameter of the burner installation opening 1 of the burner tile 2. They are formed to have substantially the same diameter.
Then, the gas supply cylinder 5, the inner combustion cylinder 6 and the outer combustion cylinder 7 are aligned with each other, the rear end of the inner combustion cylinder 6 is retracted from the rear end of the gas supply cylinder 5, and the outer combustion cylinder 7. The rear end is provided concentrically with the rear end retracted from the rear end of the inner combustion cylinder 6, and the rear ends of the inner combustion cylinder 6 and the outer combustion cylinder 7 are closed.

  A primary air flow path 8 through which primary combustion air A flows is formed between the gas supply cylinder 5 and the inner combustion cylinder 6, and the front end of the gas supply cylinder 5 and the front end of the inner combustion cylinder 6 are formed. An annular primary air discharge port 9 is formed by the portion, and a secondary air flow passage 10 is formed between the inner combustion cylinder 6 and the outer combustion cylinder 7 to allow the secondary combustion air to flow, and the inner combustion An annular secondary air discharge port 11 is formed by the tip of the cylinder 6 and the tip of the outer combustion cylinder 7.

  That is, the annular primary air discharge port 9 and the annular secondary air discharge port 11 are provided at the outer peripheral portion of the gas supply tube 5 as viewed in the axial direction along the axial direction of the gas supply tube 5. 9 is located inside, and the primary air discharge port 9 and the secondary air discharge port 11 are provided at the same position or substantially the same position in the axial direction of the gas supply cylinder.

Further, the primary air discharge port 9 is provided with a plurality of blade bodies 12w dispersed along the circumferential direction of the primary air discharge port 9, and swirls the primary combustion air A discharged from the primary air discharge port 9. A primary swirl vane 12 is provided.
As shown also in FIG. 3, each blade body 12 w of the primary swirl vane 12 is in relation to the axial center of the primary air outlet 9, that is, the gas supply cylinder axis P in the radial direction of the primary air outlet 9. The inclination angle α inclined to one side in the circumferential direction is set in the range of 20 to 40 °.

Furthermore, the primary air flow path 8 is provided with an orifice 13 that can change and adjust the flow rate of the primary combustion air A discharged from the primary air discharge port 9.
As shown in FIG. 4, the orifice 13 has two annular plates 13a and 13b each having a plurality of openings in the circumferential direction, one of which is fixed and the other is rotatable around a gas supply cylinder axis. In this state, the operation piece 13c is disposed between the gas supply cylinder 5 and the inner combustion cylinder 6 so as to rotate the rotatable rotation plate 13a. It protrudes outward.

  Then, by rotating the rotation plate 13a from the outside using the operation piece 13c, the phase in the circumferential direction of the opening portion of the rotation plate 13a is changed and adjusted, and the primary combustion air A is passed. By changing the opening area of the window 13d, the flow rate of the primary combustion air A passing through the orifice 13 is changed and adjusted, and the flow rate of the primary combustion air A discharged from the primary air discharge port 9 is changed and adjusted. It is configured.

The secondary air discharge port 11 is provided with secondary swirl vanes 14 as secondary swirl means for swirling the secondary combustion air A discharged from the secondary air discharge port 11.
The secondary swirl blade 14 includes a plurality of blade bodies 14w that are dispersed along the circumferential direction of the secondary air discharge port 11, and swirls the secondary combustion air A discharged from the secondary air discharge port 11. Although not shown, the inclination angle α of each of the blade bodies 14w of the secondary swirl blade 14 is, for example, in the range of 20 to 40 °, and is greater than the inclination angle α of the primary swirl blade 12. A large angle is set.

  Then, the primary combustion air A is discharged from the annular primary air discharge port 9 along the axial direction of the primary air discharge port 9, that is, along the gas supply cylinder axis direction in a state of swirling, and the gas supply cylinder axis direction The state in which the secondary combustion air A swirls around the outer peripheral portion of the primary combustion air flow A discharged from the primary air discharge port 9 from the annular secondary air discharge port 11 outside the primary air discharge port 9 as viewed. Thus, the air is discharged along the axial direction of the secondary air discharge port 11, that is, along the axial direction of the gas supply cylinder.

  The gas ejection part N is a single straight gas ejection hole as a straight gas ejection part that ejects the gas fuel G along the flow direction of the primary combustion air A discharged from the primary air discharge port 9. 15 and a plurality of (8 in this embodiment) radiating gas ejection holes 16 as radial gas ejection portions which are located on the outer peripheral side of the straight gas ejection holes 15 and radially eject gas fuel G. And is configured.

  The straight gas ejection holes 15 are provided in the center of the distal end wall that closes the distal end of the gas supply cylinder 5 with the hole axis aligned in the direction of the gas supply cylinder axis. The radiating gas ejection hole 16 has a forward inclined shape in which the hole axis is inclined toward the distal end side of the gas supply cylinder with respect to the radial direction of the gas supply cylinder 5, and surrounds the peripheral wall of the tapered portion 5 t of the gas supply cylinder 5. The holes are formed by being distributed at equal intervals in the direction.

  That is, the gas fuel G is jetted in a straight line along the flow direction of the primary combustion air A discharged from the annular primary air discharge port 9 through the straight gas jet holes 15, and is used for eight radiations. By the gas ejection holes 16, the gas fuel G is ejected radially outwardly from the outside of the straight traveling gas ejection holes 15 in the flow direction of the primary combustion air A.

  The ratio of straight-to-radiant gas ejection, which is the ratio of the amount of gas fuel ejected from the straight gas ejection portion and the amount of gas fuel ejection from the radial gas ejection portion, is set in the range of 1: 9 to 5: 5. To do. In this embodiment, the ratio of the straight-to-radiant gas ejection ratio is the diameter and number of the straight-going gas ejection holes 15 as the straight-advancing gas ejection part, the diameter of the radiation gas ejection hole 16 as the radial-gas ejection part, and Set based on the number of glass melting furnaces to be installed, based on the number.

  That is, in the range of the straight-to-radiant gas jet ratio in the range of 1: 9 to 5: 5, the smaller the ratio of the jet amount from the straight-going gas jet portion, the wider the width of the flame formed. On the contrary, the width of the flame formed becomes narrower as the ratio of the ejection amount from the straight gas ejection portion is set to be larger.

  And the burner main body M constructed by integrally assembling the gas supply cylinder 5, the inner combustion cylinder 6, the outer combustion cylinder 7 and the like in the arrangement form as described above, the tip portion of the outer combustion cylinder 7 as the tip portion. The burner tile 2 is held in a state of being fitted in the burner installation opening 1.

As shown in FIG. 1, a gas supply path 17 through which gas fuel G such as city gas is supplied is connected to the rear end of the gas supply cylinder 5.
The gas fuel G is supplied to the gas supply cylinder 5 through the gas supply path 17 and is ejected from the straight gas ejection holes 15 and the eight radiation gas ejection holes 16.

  The gas supply path 17 is provided with an on-off valve 18 for intermittently supplying the gas fuel G and a gas supply amount adjusting valve 19 for adjusting the supply amount of the gas fuel G.

  A main air supply path 20 that guides combustion air A from the blower 3 is branched into a primary air supply path 21 and a secondary air supply path 22, and the primary air supply path 21 is connected to the peripheral wall at the rear end of the inner combustion cylinder 6. The secondary air supply path 22 is connected to the peripheral wall at the rear end of the outer combustion cylinder 7. That is, the primary combustion air A is supplied into the inner combustion cylinder 6 through the primary air supply passage 21, discharged from the primary air discharge port 9, and the secondary combustion air A is burned outside through the secondary air supply passage 22. The gas is supplied into the cylinder 7 and discharged from the secondary air discharge port 11.

  The primary air supply path 21 is provided with a primary air adjustment damper 23, and the secondary air supply path 22 is provided with a secondary air adjustment damper 24, and the primary air adjustment damper 23 and the secondary air adjustment damper 24 are provided. By the respective adjustments, the ratio of the diversion from the main air supply path 20 to the primary air supply path 21 and the secondary air supply path 22 of the combustion air A, that is, the discharge of the primary combustion air A from the primary air discharge port 9 is achieved. The primary to secondary air discharge ratio, which is the ratio of the amount and the discharge amount of the secondary combustion air A from the secondary air discharge port 11, is adjusted.

  The total gas fuel ejection amount, which is the sum of the ejection amount of the gas fuel G from the straight gas ejection holes 15 and the ejection amount of the gas fuel G from the eight radiation gas ejection holes 16, is determined by the gas supply amount adjusting valve 19. And the total combustion air discharge amount that combines the discharge amount of the primary combustion air A from the primary air discharge port 9 and the discharge amount of the secondary combustion air A from the secondary air discharge port 11 is By adjusting the rotational speed of the blower 3, it is adjusted so as to have a predetermined set air ratio with respect to the total gas fuel ejection amount.

  Further, the primary-secondary air discharge ratio is adjusted by the primary air adjustment damper 23 and the secondary air adjustment damper 24 in a state where the total combustion air discharge amount is adjusted by the blower 3. . Incidentally, the primary to secondary air discharge ratio is adjusted to a range of 5:95 to 20:80.

  The control of the gas supply amount adjusting valve 19 for adjusting the total gas fuel injection amount and the control of the blower 3 for adjusting the total combustion air discharge amount are performed by a control unit (not shown) of the luminous flame burner B. It is configured to do it automatically. The primary to secondary air discharge ratio is adjusted by manually operating the primary air adjustment damper 23 and the secondary air adjustment damper 24.

  In this embodiment, the flow rates of the gas fuel G ejected from the straight gas ejection holes 15 and the gas fuel G ejected from the radiation gas ejection holes 16 are set in a range of 30 to 40 m / sec, The flow rates of the primary combustion air A discharged from the air discharge port 9 and the secondary combustion air A discharged from the secondary air discharge port 11 are 10 under the condition that the flow rate of the primary combustion air A is higher. It is set in the range of ~ 20 m / sec.

Hereinafter, based on FIG. 1, the combustion form of the luminous flame burner comprised as mentioned above is demonstrated.
The gas fuel G is jetted in a straight line along the axial direction of the gas supply cylinder by the straight gas jet holes 15, and is used for straight running from the outside of the straight gas jet holes 15 by the eight radiation gas jet holes 16. The gas fuel G is jetted radially in the direction of jetting of the gas fuel G from the gas jet holes 15, and is primary from the outside of the eight radiation gas jet holes 16 by the annular primary air discharge ports 9. The combustion air A is discharged along the axial direction of the gas supply cylinder while swirling, and the secondary combustion air A is discharged from the outside of the primary air discharge opening 9 by the annular secondary air discharge opening 11. It is discharged along the heart direction.
Then, both the primary combustion air A and the secondary combustion air A that are discharged in a swirl state are restrained from flowing toward the swirl center, and therefore, the straight-travel gas ejection holes 15 and the eight radiation gas ejection holes. Gas fuel G, primary combustion air A, and secondary combustion air A are mixed with the primary combustion air A or the secondary combustion air A from the gas fuel G ejected from 16 that flows outside. Mixing with the air A is performed gently.
And the form which mixes with the primary combustion air A or the secondary combustion air A from what flows outside the gas fuel flow G from the straight gas ejection hole 15 and the eight radiation gas ejection holes 16 When the gas fuel G, the primary combustion air A, and the secondary combustion air A are gently mixed, the outside of the gas fuel flow G is the primary combustion air A or the secondary combustion air. The combustion heat combusted by mixing with A heats the inner part of the gas fuel stream G, which is pyrolyzed to generate carbon particles. Therefore, the straight gas ejection holes 15 and the eight radiation gas ejections are generated. The gas fuel G ejected from the holes 16 is burned while carbon particles are efficiently generated, and a flame F having a high generation rate of luminous flame is formed.

  Moreover, although the gas fuel G ejected radially from the eight radiation gas ejection holes 16 is gently mixed with the combustion air A flowing in the swirl state, the gas fuel ejected from the straight gas ejection holes 15 Gas fuel G mixed with the primary combustion air A or the secondary combustion air A faster than G and combusted faster and ejected from the straight gas ejection holes 15 is primary combustion discharged from the primary air discharge ports 9. Of carbon particles from the gas fuel G ejected from the straight gas ejection holes 15 by flowing along the flow direction of the combustion air A and gently mixing with the primary combustion air A or the secondary combustion air A Since the amount is further increased, the gas fuel G ejected from the straight gas ejection holes 15 is retained in the flame by the combustion of the gas fuel G from the eight radiation gas ejection holes 16, and carbon Stable combustion with efficient generation of grains Will be the incidence of luminous flame is of even higher.

  Next, primary swirl vanes 12 for swirling the primary combustion air A discharged from the primary air discharge port 9 are provided, and the inclination angles of the blade bodies 12w of the primary swirl vanes 12 are set in the range of 20 to 40 °. The result of having verified the point which can improve the incidence rate of a luminous flame is demonstrated.

When such a luminous flame burner B is used as a heat source for the glass melting furnace 30 described above, it is preferable to quickly melt the glass raw material introduced from the inlet 38, so that the front side of the furnace space 35 (installation of the luminous flame burner B). Side) (for example, a range of about 1/3 of the depth) is required to increase the heating temperature, and by increasing the generation rate of the flame F of the flame F formed by the luminous flame burner B, It becomes possible to raise the heating temperature of the front side portion of the furnace space 35.
Therefore, in this verification test, the glass melting furnace 30 is operated while changing the plurality of primary swirling blades 12 having different inclination angles of the blade bodies 12w, and at each position in the direction along the front-rear direction in the furnace space 35, The relationship between the inclination angle of the blade body 12w and the temperature of the furnace space 35 (hereinafter sometimes referred to as the furnace temperature) was examined.

Incidentally, the depth and width of the inner space 35 of the glass melting furnace 30 used in the verification test are 6970 mm and 1700 mm, respectively, and the height from the bottom of the melting tank 32 to the ceiling wall 34 is 1700 mm, and the luminous flame burner B is provided at a substantially intermediate height between the bottom surface of the dissolution tank 32 and the ceiling wall 3.
And the furnace temperature of the position of 600 mm height from the bottom face of the dissolution tank 32 was measured.
The combustion amount of the bright flame burner B used for the verification test is 2600 kW, and the preheating temperature of the combustion air A by the exhaust heat recovery heat exchanger 4 is 90 ° C.

The result of the verification test is shown in FIG.
FIG. 5 shows that the distance from the tip of the bright flame burner B is 500 mm (P _{500 in} FIG. 5), 1250 mm (P _{1250 in} FIG. 5), 3000 mm (P _{3000 in} FIG. 5), and 6000 mm. position shows the relationship between the inclination angle and the furnace temperature Metropolitan of sail body 12w in each of (P ₆₀₀₀ in FIG. 5).
In the verification test, if the inclination angle of the blade body 12w is larger than 40 °, the mixing of the gas fuel G and the primary combustion air A becomes too slow, and the flame is easily lifted, and the combustion stability is improved. In FIG. 5, the range in which the inclination angle of the blade body 12 w is 0 to 40 ° is illustrated in FIG. 5, and the range in which the inclination angle of the blade body 12 w is greater than 40 ° is not illustrated in FIG. 5. Yes.

At a position where the distance from the tip of the bright flame burner B is 500 mm and a position of 1250 mm, the furnace temperature decreases as the inclination angle of the blade body 12w decreases from 40 °, and the furnace temperature decreases as the inclination angle decreases. The decreasing rate is larger in the range where the inclination angle of the blade body 12w is smaller than 20 ° compared to the range of 20-40 °.
That is, if the inclination angle of the blade body 12w of the primary swirl blade 12 is set in the range of 20 to 40 °, the luminous flame generation rate can be remarkably improved, and the front side portion of the furnace space 35 is heated. The temperature can be significantly increased.

[Another embodiment]
Next, another embodiment will be described.
(A) The number of the gas jet holes 15 for rectilinear advance as the straight gas jet part is not limited to the one exemplified in the above embodiment, but may be plural.
Further, the number of the radiation gas ejection holes 16 as the radial gas ejection portions is not limited to the eight illustrated in the above embodiment, but in order to eject the gas fuel G radially. At least 3 or more are preferable.

(B) The straight gas jet part is configured by forming a straight gas jet hole 15 in the gas supply cylinder 5 as in the above embodiment, and replacing the gas supply pipe 5 with a cylindrical gas nozzle. It may be configured to be provided in a state protruding from the tip wall.
Further, the radial gas jetting portion is provided with a plurality of radiating gas jetting holes 16 dispersed in the circumferential direction of the gas supply cylinder 5 in the circumferential direction as in the above embodiment. These cylindrical gas nozzles may be provided on the peripheral wall of the gas supply cylinder 5 while being distributed in the circumferential direction so as to protrude from the peripheral wall.

(C) In the above-described embodiment, an example is shown in which gas fuel is supplied to the rectilinear gas ejection portion and the radial gas ejection portion through a common supply system called the gas supply cylinder 5. However, the gas fuel may be supplied by a separate supply system.
In this case, a gas jet ratio adjusting means capable of adjusting the ratio of gas fuel supplied to the straight gas jet section and the radial gas jet section through each supply system is provided, and the straight-to-radiant gas jet ratio can be changed and adjusted. You may comprise as follows.
In this case, for example, by changing and adjusting the straight-to-radiant gas ejection ratio using the gas ejection ratio adjusting means, the flame shape is arbitrarily changed, for example, to match the shape of the heating furnace to which the luminous flame burner is installed. can do.

( D ) In the above embodiment, the primary air adjusting damper 23 and the secondary air adjusting damper 24 are provided to configure the primary to secondary air discharge ratio to be adjustable. The air conditioning damper 23 and the secondary air conditioning damper 24 may be omitted, and the primary to secondary air discharge ratio may be fixedly set. In this case, it is preferable to set the primary to secondary air discharge ratio in the range of 5:95 to 20:80 in order to improve the generation rate of the luminous flame.

( E ) As the relationship between the inclination angle of the blade body 12w of the primary swirl blade 12 and the inclination angle of the blade body 14w of the secondary swirl blade 14, in the above embodiment, the blade body 14w of the secondary swirl blade 14 However, the inclination angle of the blade body 12w of the primary swirl blade 12 may be increased or the both may be the same.

( F ) Flow rates of the gas fuel G ejected from the straight gas ejection section and the gas fuel G ejected from the radial gas ejection section, the primary combustion air A and the secondary air discharged from the primary air discharge port 9 The relationship between the flow rates of the secondary combustion air A discharged from the discharge port 11 is the relationship in which the flow rate of the gas fuel G is faster in the above embodiment. In any case, it is preferable to make the flow rate of the gas fuel G different from the flow rate of the combustion air A in terms of stabilization of combustion.

  The flow speed of the gas fuel G ejected from the straight gas ejection section may be different from the flow speed of the gas fuel G ejected from the radial gas ejection section.

  The relationship between the flow rate of the primary combustion air A discharged from the primary air discharge port 9 and the flow rate of the secondary combustion air A discharged from the secondary air discharge port 11 is the primary combustion in the above embodiment. Although the flow rate of the working air A is increased, the flow rate of the secondary combustion air A may be increased, or both may be the same.

( G ) The specific configuration of the secondary swirl means is not limited to the secondary swirl blade 14 illustrated in the above embodiment. For example, the secondary combustion air is introduced into the outer combustion cylinder 7 in the tangential direction so that the blower 3 causes the secondary combustion air to flow in a swirl state in the cylindrical outer combustion cylinder 7, and the secondary air discharge port 11. Alternatively, the secondary combustion air may be discharged in a swirling state.

( H ) The primary swirl vane 12 is configured to be detachable from the primary air discharge port 9, and the primary swirl vane 12 provided in the primary air discharge port 9 can be changed to one having a different inclination angle of the blade body 12w. You may comprise as follows.

The luminous flame burner according to (i) the present invention application is not limited to a glass melting furnace, it can be used in various heating furnaces and boilers, etc. of the aluminum melting furnace or the like.

Longitudinal side view of luminous flame burner according to an embodiment Front view of luminous flame burner according to an embodiment The development view of the principal part showing the primary swirl vane of the luminous flame burner according to the embodiment A longitudinal front view showing an orifice of a luminous flame burner according to an embodiment The figure which shows the relationship between the inclination angle of the blade body of the primary swirl blade and the furnace temperature Vertical side view of a glass melting furnace provided with a luminous flame burner according to an embodiment Transverse plan view of a glass melting furnace provided with a luminous flame burner according to an embodiment Longitudinal side view of conventional luminous flame burner

Explanation of symbols

5 Gas supply tube 9 Primary air discharge port 11 Secondary air discharge port 12 Primary swirl vane 12w Blade body 14 Secondary swirl means 15 Straight gas jet part 16 Radial gas jet part N Gas jet part

Claims (3)

An annular primary air discharge port and an annular secondary air discharge port are formed on the outer peripheral portion of the gas supply cylinder having a gas ejection portion on the front end side in the axial direction along the axial direction of the gas supply cylinder. Gas ejected from the gas ejection section, provided with a primary air discharge port located inside, and provided with secondary swirling means for swirling secondary combustion air discharged from the secondary air discharge port A luminous flame burner configured to burn fuel in a luminous flame-forming state,
Provided with a plurality of blade bodies dispersed along the circumferential direction of the primary air discharge port, and provided with primary swirl vanes for swirling the primary combustion air discharged from the primary air discharge port,
The inclination angle at which each of the blade bodies of the primary swirl blade is inclined to one side in the circumferential direction with respect to the axial center of the primary air discharge port as viewed in the radial direction of the primary air discharge port is in the range of 20 to 40 °. is set to,
The gas jetting part is located on the outer peripheral side of the straight-going gas jetting part jetting gas fuel along the flow direction of the primary combustion air discharged from the primary air discharge port, and the straight-going gas jetting part And the luminous flame burner comprised including the radial gas ejection part which ejects gas fuel radially . 2. The ratio of the amount of gas fuel ejected from the straight gas ejection portion and the amount of gas fuel ejection from the radial gas ejection portion is set in a range of 1: 9 to 5: 5 . Bright flame burner. The ratio of the discharge amount of primary combustion air from the primary air discharge port and the discharge amount of secondary combustion air from the secondary air discharge port is set in a range of 5:95 to 20:80. The luminous flame burner according to claim 1 or 2 .

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