JP3463117B2 - Burner device - Google Patents

Description

Detailed Description of the Invention

[0001]

TECHNICAL FIELD The present invention relates to a burner device for burning fuel gas.

[0002]

[Prior Art] In order to perform district power generation, district heating, etc.,
Various cogeneration systems have been proposed and put into practical use. One typical system of such a cogeneration system includes a burner device for burning fuel gas, and a gas turbine that is rotatably driven by the combustion gas burned by the burner device. It is used to generate electricity.

The burner device in such a cogeneration system has a primary nozzle means to which the fuel gas from the first gas supply means is supplied and a secondary nozzle means to which the fuel gas from the second gas supply means is supplied. Some have and. The primary nozzle means defines the first flow path, and the fuel gas from the first gas supply means is jetted into the air flow flowing through the first flow path, whereby a combustible mixed gas is generated.
Further, the secondary nozzle means defines the second flow path, and the fuel gas from the second gas supply means is ejected into the air flow flowing through the second flow path, whereby the combustible gas mixture of the primary nozzle means is discharged. Also, a combustible mixed gas having a low gas concentration is generated. In such a burner device, since the gas concentration of the mixed gas of the primary nozzle means is higher than the gas concentration of the mixed gas of the secondary nozzle means, the mixed gas of the primary nozzle means is combusted, and the combustion gas of this primary nozzle means is burned. Is used to combust the mixed gas in the secondary nozzle means. By burning the fuel gas in this way, lean combustion becomes possible, and the combustion temperature of the combustion gas can be lowered, which enables highly efficient combustion while suppressing the generation of nitric oxide (NOx). .

[0004]

In such a burner device, the combustion output of the burner device is controlled by controlling the injection amount of the fuel gas injected into the second flow path.
When the injection amount of fuel gas is reduced to reduce the combustion output, the combustion flame from the secondary nozzle means disappears, or the injection control of the fuel gas cannot keep up, and the combustion state of the secondary nozzle means becomes unstable. There is.

Further, if the combustion flame from the secondary nozzle means is extinguished or turned on while the fuel gas from the primary nozzle means is maintained in a combustion state, a temperature fluctuation is caused in the combustion gas, and this combustion gas is exhausted. In a gas turbine that is delivered as gas, it causes load fluctuations.

An object of the present invention is to provide a burner device which burns stably even when the injection amount of fuel gas is reduced and has an excellent flame holding ability.

[0007]

The present invention, as shown in FIGS. 1 to 4, includes: (a) a cylindrical first nozzle means 10 defining a first flow path 45; and (b) The injection nozzle body 20, the first nozzle means 1
0 is provided concentrically and forms a substantially annular gap 39 between the inner surface of the first nozzle means 10 and the outer surface of the injection nozzle body 20. This gap 39 is continuous with the first flow path 45, The ejection hole 4 that has a space 22b into which the fuel gas is supplied, extends substantially in the radial direction, and communicates with the space 22b and the gap 39.
8 are formed, and the ejection holes 48 are formed in the first nozzle means 1
0, and (c) a through hole 50 is formed in the first nozzle means 10 in the ejection hole 48 so as to face each other through the gap 39, and (d). The cylindrical second nozzle means 12 is provided concentrically outside the first nozzle means 10 and has the through hole 5
An annular second in which the fuel gas through 0 and the air are premixed
Second nozzle means 12 that defines the flow path 47 of (1), (e) gas supply means that supplies the fuel gas to the space 22b of the injection nozzle body 20 in a controllable manner, and (f) the gap 39 and the second The air flow path 8 to the second flow path 47.
A combustion space is formed downstream of the first and second flow paths 45, 47 including an air supply source that supplies air via (h) the air flow path 8 through the gap 39 and The flow velocity of the air flowing through the first flow passage 45 is relatively low, the flow velocity of the air flowing through the air flow passage 8 to the second flow passage 47 is relatively high, and (i) from the ejection holes 48 of the injection nozzle body 20. Of the fuel gas passes through the gap 39, the through hole 50, and the second fuel gas.
(J) When the amount of fuel gas supplied from the gas supply means is small, the jet speed of the fuel gas jetted from the jet holes 48 of the jet nozzle body 20 is low, and therefore, Spout 4
The fuel gas ejected from No. 8 flows into the first flow path 45 under the action of the air flow flowing through the gap 39. (k) When the supply amount of the fuel gas from the gas supply means increases, the injection nozzle body The jet speed of the fuel gas jetted from the jet holes 48 of 20 increases, whereby the fuel gas jetted from the jet holes 48 overcomes the air flow flowing through the gap 39 and the second flow path 47. To the second flow path 47 as the fuel gas supply increases.
The burner device is characterized in that the flow rate flowing to the inside also increases.

According to the present invention, the flow velocity of the air flowing through the first flow passage 45 defined by the cylindrical first nozzle means 10 is relatively low and defined by the cylindrical second nozzle means 12. The flow velocity of the air flowing through the second flow passage 47 is relatively high, and the fuel gas from the ejection holes 48 of the injection nozzle body 20 is ejected toward the second flow passage through the first flow passage.
Therefore, when the injection amount of the fuel gas is small, the ejection speed of the fuel gas is low, and the fuel gas ejected from the ejection holes 48 flows through the first flow path under the action of the air flow flowing through the first flow path. . When the ejection amount of the fuel gas increases, the ejection velocity of the fuel gas increases, whereby the fuel gas ejected from the ejection holes 48 overcomes the air flow flowing through the first passage and is directed toward the second passage. Flow, and the ejection amount ejected to the second flow path increases. As described above, when the injection amount of the fuel gas is small, a large amount of the fuel gas flows in the first flow passage having a small air flow rate, and therefore, the mixed gas having a relatively high gas concentration flows in the first flow passage. The generated fuel gas burns stably even though the amount of jet is small. Further, when the injection amount of the fuel gas increases, a part of the fuel gas flows to the first flow path, and the remaining part flows to the second flow path having a large air flow rate, and the flow rate of the second flow path increases. The amount increases as the amount of fuel gas ejected increases.
Therefore, the mixed gas having a relatively low gas concentration is generated in the second flow path, and the fuel gas is burned in the first and second nozzle means. First
The second nozzle means is concentrically arranged outside the nozzle means. The fuel gas ejected from the ejection holes 48 of the ejection nozzle body is ejected toward the second flow passage through the first flow passage. Therefore, when the ejection amount of the fuel gas ejected from the ejection hole 48 is small, the fuel gas ejected from the ejection hole 48 becomes the first due to the air flow flowing through the gap 39 between the injection nozzle body and the first nozzle means. Flowing into the flow path. Further, when the amount of fuel gas ejected from the ejection holes 48 increases, the fuel gas ejected from the ejection holes 48 and the injection nozzle body
A second nozzle defined between the first nozzle means and the second nozzle means through a portion of the first flow path between the second nozzle means and
Flowing into the channel 47 of the above and sufficiently premixed. Thus, the fuel gas ejected from the second ejection holes of the injection nozzle body can be fed to the first and second flow paths as required according to the ejection amount. The present invention also provides the first flow path 4
5 and the second flow passage 47 are provided with mixed gas introduction means 76, 82, 84 for guiding a part of the lean mixed gas of the second flow passage 47 to the first flow passage 45. It is characterized by According to the present invention, since the mixed gas introduction means is provided between the first flow path and the second flow path, a part of the mixed gas generated in the second flow path becomes a first gas. Introduced into the first flow path, the gas concentrations of the mixed gas in the first flow path and the mixed gas in the second flow path are made uniform, and deviation of the combustion state is reduced.

Further, the present invention is characterized in that the maximum ejection speed of the fuel gas ejected from the ejection holes 48 of the injection nozzle body 20 is 1 to 1000 m / s.

According to the present invention, since the maximum ejection speed of the fuel gas is 1 to 1000 m / s, when the ejection amount of the fuel gas increases, the air flow flowing through the first flow path can be overcome to a sufficient amount. Fuel gas is ejected to the second flow path, and the fuel gas from the second flow path is stably burned.

The present invention is also characterized in that the injection nozzle body 20 is provided with another ejection hole 46 for ejecting the fuel gas toward the first flow path 45.

According to the invention, the injection nozzle body ejects the fuel gas to the first flow path in addition to the ejection holes 48 for ejecting the fuel gas to the second flow path through the first flow path. It has another ejection hole 46 for Therefore, when the fuel gas ejection amount is small, the first and second channels are provided in the first flow path.
The fuel gas is supplied from the ejection holes of the above, so that the gas concentration of the mixed gas in the first flow path can be increased. The present invention is characterized in that the inner diameter of the through hole 50 is substantially equal to or larger than the inner diameter of the ejection hole 48 formed in the through hole 50 so as to face each other. According to the present invention, the inner diameter of the through hole 50 is substantially equal to or larger than the inner diameter of the ejection hole 48 formed to face the through hole 50, so that the fuel gas ejected from the ejection hole 48 is Can be reliably guided to the through hole 50 as required, and can be supplied to the second flow path 47 through the through hole 50.

The present invention, as shown in FIG.
(A) The injection nozzle body 102 has a space 104 to which the fuel gas is supplied, and has a tip inclined portion 106 inclined inward in the radial direction toward the tip side.
6, the injection nozzle body 102 in which the ejection holes 108 are formed
And (b) a cylindrical first nozzle means 110, which is provided on the downstream side of the injection nozzle body 102 and forms an introduction opening 126 with a narrowed opening area between the injection nozzle body 102 and
The first nozzle means 110 defining the first flow path 118, and (c) the injection nozzle body 102 and the first nozzle means 110 are covered, and the injection nozzle body 102 and the first nozzle means 110 are covered.
A cylindrical second defining the annular second flow path 120 between
Nozzle means 114, (d) gas supply means for supplying fuel gas to the space 104 of the injection nozzle body 102 in a flow path controllable manner, and (e) an air flow path upstream of the second flow path 120. An air supply source for supplying air from (f) the first nozzle means 110 and the second nozzle through the air flow path.
The flow velocity of the air flowing through the second flow path 120 between the first flow passage 120 and the nozzle means 114 is relatively high, and the flow velocity of the air flowing from the air flow passage through the introduction opening 102 to the first flow passage 118 is relatively high. (G) the fuel gas from the ejection holes 108 of the injection nozzle body 102 is ejected toward the first and second flow paths 118 and 120, and (h) the amount of fuel gas supplied from the gas supply means. Is small, the ejection speed of the fuel gas ejected from the ejection holes 108 of the injection nozzle body 102 is low, and therefore the fuel gas ejected from the ejection holes 108 is
When the flow rate of the fuel gas from the gas supply means increases, the injection nozzle body 102 is subjected to the action of the airflow flowing through the first flow path 118 through the flow path 26 and flows into the first flow path 118. The ejection speed of the fuel gas ejected from the ejection hole 108 is increased, and the fuel gas ejected from the ejection hole 108 is supplied to the first passage 118 through the second passage 120. It flows through the introduction opening 126 to the second flow path 120 without being affected by the flow, and thus the flow rate of the second flow path 120 increases as the supply amount of the fuel gas increases. The burner device is characterized in that

According to the present invention, when the amount of fuel gas supplied by the gas supply means whose flow rate is controllable is small, the injection nozzle body 10 is
The fuel gas from the second ejection hole 108 is introduced into the introduction opening 126.
Through the first flow path 118 of the first nozzle means 110,
When the fuel gas and the air flow together with the air and the fuel gas is premixed by the gas supply means, the fuel gas from the ejection holes 108 passes through the introduction opening 126. First and second nozzle means 110,1
It flows with the air into the second flow passage 120 formed between 18 and is sufficiently premixed in the second flow passage 120 and introduced into the combustion space. Therefore, the high concentration region of the fuel gas is not formed, and the NOx concentration can be kept low.

[0015]

[0016]

[0017]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of a burner device according to the present invention will be described below with reference to the accompanying drawings. Figure 1
FIG. 3 is a sectional view schematically showing an embodiment of the burner device according to the present invention, FIG. 2 is an enlarged sectional view showing a part of the burner device shown in FIG. 1, and FIG. It is sectional drawing which further expands and shows the injection nozzle body of 1 burner apparatus, and its vicinity.

Referring to FIG. 1, the illustrated burner device includes a diffuser portion of a burner test case indicated by reference numeral 2. A cylindrical test case 4 is attached to the diffuser portion 2, and the test case 4 is shown in FIG. 1 extends to the right. A combustion case 6 is arranged in the test case 4. The combustion case 6 has a hollow cylindrical shape. One end (the left end in FIG. 1) of the combustion case 6 is attached to the diffuser part 2, and the other end extends to the right in FIG. An air passage 8 is also formed in the diffuser portion 2, and combustion air is supplied to one end of the combustion case 6 through the air passage 8. This combustion air is sent in a state of being compressed by a compressor (not shown), for example.

In this embodiment, the first nozzle means 10, the second nozzle means 12 and the combustion cylinder 14 are arranged in one end of the combustion case 6. Referring also to FIG. 2, a mounting support block 16 is mounted on a part of the diffuser portion 2, and one end of an external gas supply pipe 18 is mounted on the mounting support block 16 and the external gas supply pipe 18 is attached. An injection nozzle body 20 is attached to the other end of the. A space 22 is formed inside the injection nozzle body 20, and a partition sleeve 24 is attached by penetrating the interior space 22 in the axial direction, and the partition sleeve 24 allows the interior space 22 to be located inside the first space 22a and the first space 22a. It is partitioned into a second space 22b outside the one space 22a (see FIG. 3). The other end of the outer gas supply pipe 18 communicates with the second space 22b of the injection nozzle body 20. An inner gas feed pipe 26 is concentrically arranged inside the outer gas feed pipe 18, one end of which is attached to the attachment support block 16 and the other end of which is attached to the injection nozzle body 20. There is. The inner gas supply pipe 26 communicates with the first space 22a of the injection nozzle body 20.

A first gas supply device for supplying fuel gas to the inner gas supply pipe 26 is connected to the inner gas supply pipe 26.
The first gas supply device is a gas supply source (not shown) in which fuel gas is stored, a gas supply pipe 28 that guides the fuel gas from the gas supply source, and a flow rate of gas supplied through the gas supply pipe 28. The gas supply pipe 28 includes a flow rate control means, for example, a flow rate control valve (not shown) for controlling the internal gas supply pipe 2.
It is connected to 6. A second gas supply device for supplying fuel gas to the external gas supply pipe 18 is connected to the external gas supply pipe 18. The second gas supply device is a gas supply source (not shown) in which fuel gas is stored, a gas supply pipe 30 for guiding the fuel gas from the gas supply source, and a flow rate of gas supplied through the gas supply pipe 30. The gas feed pipe 30 is connected to the outer gas feed pipe 18 by including a flow control means for controlling the above, for example, a flow control valve (not shown). Therefore, the first and second gas supply devices constitute gas supply means for supplying the fuel gas to the injection nozzle body 20. As the fuel gas, for example, city gas can be conveniently used.

The first nozzle means 10 is a jet nozzle body 2
It is mounted on the outside of 0. First nozzle means 1 shown
Reference numeral 0 denotes a first cylindrical member 32, and one end of the first cylindrical member 32 is integrally provided with inner protrusions 34 that are spaced in the circumferential direction and project radially inward. The first cylindrical member 32 is concentrically supported by the injection nozzle body 20 via the plurality of inner protrusions 34.

In this embodiment, as shown in FIG. 3, the injection nozzle body 20 includes a main body portion 31 having a large outer diameter, an intermediate taper portion 33 tapering radially inward, and a small diameter portion having a small outer diameter. 35 and a tip tapered portion 37, which are provided toward the tip side in the order described above. In connection with this, each inner protrusion 34 of the first cylindrical member 32 has a support portion 34a whose distal end surface extends in the axial direction (vertical direction in FIG. 3) and a radial direction from the inner support portion 34a. And an inclined portion 34b that extends obliquely inward,
The large diameter portion 31 of the injection nozzle body 20 is attached to the support portion 34a. In such a mounted state, the injection nozzle body 2
The inclined portion 3 of the inner protrusion 34 facing the intermediate tapered portion 33 of 0
4b are opposed to each other, and the intermediate taper portion 33 and the inner protrusion 34
A slight gap 39 exists between the inclined portion 34b and the inclined portion 34b.
With this configuration, the first cylindrical member 32
Between the injection nozzle body 20 and the injection nozzle body 20, there is a substantially annular gap in a predetermined range in the circumferential direction, in other words, in a region excluding the region where the support portion 34a of the inner protrusion 34 exists, Is introduced into the first cylindrical member 32 through the gap and the gap 39 between the intermediate tapered portion 35 and the inclined portion 34b. That is, the gap 39 is defined by the first nozzle means 10
Is formed between the inner surface of the nozzle and the outer surface of the injection nozzle body 20 in the substantially annular shape described above.

A first swirler 36 is disposed between the small diameter portion 35 of the injection nozzle body 20 and one end of the first cylindrical member 32. The first swirler 36 is composed of a plurality of fins arranged at intervals in the circumferential direction, and in this embodiment, the slanted portion 34 b of the inner projection 34 is followed by an inner portion of the first cylindrical member 32. It is provided integrally on the peripheral surface. Therefore, the air flowing through the gap between the injection nozzle body 20 and the first cylindrical member 32 is not swept by the first swirler 36.
Becomes a swirl flow, and flows in the first cylindrical member 32 to the right in FIGS. 1 and 2 in the swirl flow state. First
The swirler 36 may be formed separately from the first cylindrical member 32 and may be interposed therebetween.

Referring again to FIGS. 1 and 2, the second nozzle means 12 is mounted outside the first nozzle means 10. The illustrated second nozzle means 12 is composed of a second cylindrical member 38, and one end portion of the second cylindrical member 38 has a first swirler 40 and a first cylindrical member 32.
It is mounted concentrically on the outside of this. In this embodiment, the second swirler 40 is composed of a plurality of fins arranged at intervals in the circumferential direction and is integrally provided on the inner peripheral surface of the second cylindrical member 38. Cylindrical member 3 of 1
2 is supported by the second swirler 40. Since the second swirler 40 is provided in this manner, the air introduced between the first cylindrical member 32 and the second cylindrical member 38 becomes a swirling flow due to the action of the second swirler 40. 1 and 2 in the second cylindrical member 38 in a swirling flow state.
Flows to the right at. This second swirler 40 is
It may be formed separately from the cylindrical member 38, and may be interposed between the first and second cylindrical members 32 and 38.

An annular flange 42 protruding outward in the radial direction is integrally provided at one end of the second cylindrical member 38, and one end of the combustion cylinder 14 is attached to a tip end of the annular flange 42 by a mounting screw 44. Installed by. Combustion cylinder 1
A cylindrical member 4 is concentrically arranged on the first and second cylindrical members 32 and 38, and an annular outer space exists between the combustion cylinder 14 and the combustion case 6.

In this embodiment, a plurality of first tapered portions 37 of the injection nozzle body 20 are circumferentially spaced from each other.
Of the ejection holes 46 are formed, and these first ejection holes 46 communicate with the first space 22a of the ejection nozzle body 20. Further, a plurality of second ejection holes 48 extending substantially in the radial direction are formed at intervals in the circumferential direction in the intermediate tapered portion 33 of the ejection nozzle body 20, and these second ejection holes 48 are formed. Is communicated with the second space 22b. Furthermore, the first cylindrical member 32 is provided corresponding to each of the second ejection holes 48.
A through hole 50 is formed in the inclined portion 34b of the inner protrusion 34, and the second ejection hole 48 and the through hole 50 of the inclined portion 34b are arranged to face each other with a gap 39 therebetween. The inner diameter of the through hole 50 is preferably set to be substantially equal to or larger than the inner diameter of the second injection hole 48 of the injection nozzle body 20. With this structure, the fuel gas injected from the second injection hole 48 is surely guided to the second injection hole 48.

With this structure, the fuel gas supplied through the gas supply pipe 28 is supplied to the inner gas supply pipe 2
6 is fed to the first space 22a of the injection nozzle body 20 and is ejected through the first ejection hole 46. As shown in FIGS. 1 and 2, the first nozzle means 10 defines a first flow path 45 by means of a first cylindrical member 32.
One end portion of the flow passage 45, that is, the upstream side portion, extends between the jet nozzle body 20 and the first cylindrical member 32, and a part of the air flowing through the air flow passage 8 and the jet nozzle body 20 and the first nozzle member 20. Through the inner opening between the first flow path 4 and the first cylindrical member 32.
5 and flows downstream. The fuel gas ejected from the first ejection holes 46 is ejected toward the air flow flowing as a swirl flow by the first swirler 36, and is substantially uniformly mixed by the action of the swirl flow to be mixed gas (fuel gas And a combustible mixed gas of air). The air ratio of the mixed gas in the first flow path 45 is set to, for example, about 1.4 to 1.9. By operating the flow rate control means (not shown) of the first gas supply device, the ejection amount of the fuel gas ejected from the first ejection holes 46 can be controlled.
Further, the fuel gas supplied through the gas supply pipe 30 is
The gas is supplied to the second space 22b of the injection nozzle body 20 through the outer gas supply pipe 18 and ejected from the second ejection hole 48. The second nozzle means 12, as shown in FIGS. 1 and 2,
An annular second flow path 47 is defined outside the first cylindrical member 32 by the second cylindrical member 38, and the remaining part of the air flowing through the air flow path 8 is the first cylindrical member 32. Through the outer opening between the second flow path 4 and the second cylindrical member 38.
7 and flows downstream. The fuel gas ejected from the second ejection holes 46 is ejected to the first flow passage 45 through the gap 39 (FIG. 3) and to the second flow passage 47 after passing through the gap 39 and the through hole 50 as described later. To be done. The fuel gas ejected into the second flow path 47 is ejected toward the air flow which becomes a swirl flow by the second swirler 40, and is substantially uniformly mixed by the action of the swirl flow to be mixed gas (fuel It becomes a combustible mixed gas of gas and air). By operating the flow rate control means (not shown) of the second gas supply device, the ejection amount of the mixed gas for combustion ejected from the second ejection holes 48 can be controlled.

The rest of the air flowing through the air passage 8 flows through the space 51 between the combustion cylinder 14 and the combustion case 6. In this embodiment, a plurality of air holes 52 are formed in the combustion cylinder 14 at intervals in the circumferential direction and the axial direction, and the air flowing through the space 51 has these air holes 52.
Is introduced into the combustion cylinder 14 through. The air introduced through the air holes 52 creates an air layer that flows along the inner peripheral surface of the combustion cylinder 14, and the combustion cylinder 14 is cooled by the air layer. These air holes 52 can be formed by bending a part of the combustion cylinder 14 outward in the radial direction. If necessary, a dilution hole (not shown) may be provided in the combustion cylinder 14 so that the temperature of the combustion gas that combusts and flows in the combustion cylinder 14 does not rise abnormally as described below. When the dilution hole is provided in this way, the air flowing in the space 51 is introduced into the combustion cylinder 14 through the dilution hole, and the temperature of the combustion gas is lowered by the introduced air. If the combustion cylinder 14 does not rise to an abnormally high temperature, the air holes 5
2 can be omitted.

In this embodiment, as shown in FIG. 1, the tip portion of the first nozzle means 10, that is, the other end portion of the first cylindrical member 32, and the tip portion of the second nozzle means 12, that is, the first nozzle portion 12, The other end of the cylindrical member 38 of No. 2 extends to the substantially same position or substantially the same position, and the combustion cylinder 1
The tip of 4 extends beyond the first and second nozzle means 10, 12 and further to the right in FIG. Therefore, the combustion flame due to the mixed gas flowing through the first flow path 45 is generated rightward in FIG. 1 from the inside or the tip of the first cylindrical member 32, and due to the mixed gas flowing through the second flow path 47. The combustion flame is generated from the tip of the second cylindrical member 38 to the right in FIG. 1, and these combustion flames are burned in the combustion cylinder 14 as required.

In this embodiment, the gas concentration of the combustible mixed gas flowing through the first flow path 45 is set to be higher than the gas concentration of the combustible mixed gas flowing through the second flow path 47. In connection with this, the ignition part of the ignition means 56 for igniting the mixed gas projects into the first flow path 45. The ignition means 56 comprises an elongated ignition member 58,
The base portion is attached to the test case 4, and the tip end portion thereof penetrates the combustion case 6, the combustion cylinder 14, the second cylindrical member 38, and the first cylindrical member 32 and projects into the first flow path 45. There is. The tip ignition part of the ignition member 58 is the first flow path 4
A spark is generated toward the mixed gas flowing through the gas No. 5, and the mixed gas in the first flow path 45 is ignited and burned by the spark.
Then, the flame of the combustion gas generated in the first flow path 45 is propagated to the mixed gas flowing in the second flow path 47, and the mixed gas in the second flow path 47 is burned by the propagation of the flame.

Further, the gap between the injection nozzle body 20 and the first cylindrical member 32 is set smaller than the gap between the first cylindrical member 32 and the second cylindrical member 38. The air flowing into the first flow path 45 is supplied to the first flow path 4
Since the cross-sectional area of the first flow path is greatly increased in the downstream side after being narrowed at the inner opening of No. 5, the flow velocity of the air flow flowing through the first flow path 45 is relatively low, whereas Thus, the flow velocity of the airflow flowing through the second flow path 47 becomes relatively high.

At the tip of the combustion cylinder 14, a cylindrical lead-out cylinder 60 is further provided. The lead-out tube 60 extends to the right in FIG. 1, and the tip portion thereof is formed to be tapered. The combustion gas guided from the combustion tube 14 to one end of the lead-out tube 60 flows through the lead-out tube 60 and Collected at the tapered tip and flows downstream. A gas turbine 62 is disposed on the tip side of the lead-out pipe 60, and the combustion gas burned in the combustion pipe 14 is fed to the gas turbine 62 through the lead-out pipe 60, and the gas turbine 62 is driven by the combustion gas from the burner device. It is driven to rotate. The leading end of the lead-out tube 60 is supported by a support plate 64 attached to the leading end of the combustion case 6.

In this embodiment, a part of the combustible mixed gas in the second flow path 47 is mixed with the combustible mixed gas in the first flow path 45. The illustrated first cylindrical member 32 includes a cylindrical nozzle main body 72 and the nozzle main body 72.
The nozzle main body 72 has one end portion (the left end portion in FIGS. 1 and 2) attached to the injection nozzle body 20. The nozzle body 72 has substantially the same inner diameter from the vicinity of one end to the other end, and one end thereof is curved slightly outward in the radial direction,
As a result, the air flowing through the air flow path 8 is guided to the curved one end portion and guided to the gap between the injection nozzle body 20 and the nozzle body 72. The tip nozzle 74 includes a large diameter portion 76 having a large inner diameter, a small diameter portion 78 having a small inner diameter, and a taper portion 80 connecting the large diameter portion 76 and the small diameter portion 78,
The taper portion 80 extends inward in the radial direction in a tapered shape. In this embodiment, the inner diameter of the small diameter portion 78 is equal to that of the nozzle body 7.
2 is substantially equal to the inner diameter of 2, and the inner diameter of the large diameter portion 76 is
8 and the inner diameter of the nozzle body 72 are set larger.

In this embodiment, the large diameter portion 76 of the tip nozzle 74 is attached to the other end of the nozzle body 72. Also referring to FIG. 4, four pins 82 are fixed to the other end of the nozzle body 72 by welding at substantially equal intervals in the circumferential direction, and a tip nozzle 74 is welded to the tip of these pins 82 by welding. It is fixed. Since the tip nozzle 74 is mounted in this way, the second flow path 4 is provided between the outer peripheral surface of the other end portion of the nozzle body 72 and the inner peripheral surface of the large diameter portion 76 of the tip nozzle 74.
An annular introduction opening 84 for introducing the mixed gas flowing through 7 into the first flow path 45 is formed. Therefore, the diluted mixed gas flowing through the second flow passage 47 is introduced into the first flow passage 45 through the introduction opening 84 and mixed with the diluted mixed gas flowing through the first flow passage 45. The mixed gas introduced from the second flow path 47 dilutes the gas concentration of the mixed gas flowing through the first flow path 45 to make the gas concentration substantially uniform. In addition,
When it is not necessary to dilute the mixed gas flowing through the first flow path 45, the above-described introduction opening 84 can be omitted, and in this case, therefore, the first nozzle means 10 can be formed of a simple cylindrical member. .

In this embodiment, the ignition member 58 of the ignition means 56 is located near the other end of the nozzle body 72 of the first nozzle means 10, specifically, upstream of the introduction opening 84 when viewed in the flow direction of the mixed gas. It is arranged on the side. With this configuration, the mixed gas flowing through the first flow path 45, that is, the mixed gas having a relatively high gas concentration before the mixed gas from the second flow path 47 is introduced is sent to the ignition member 58. As a result, the deterioration of the ignition performance of the ignition means 56 can be avoided.

In such a burner device, at the time of ignition, the first
The fuel gas from the gas supply device is supplied to the first space 22a of the injection nozzle body 20 through the inner gas supply pipe 26, and the fuel gas is ejected from the first space 22a through the first ejection holes 46. Therefore, the fuel gas is ejected toward the air flow flowing through the first flow passage 45, and the mixed gas having a relatively high concentration flows through the first flow passage 45. Then, when a spark is generated from the ignition means 56 toward such a mixed gas flow, the mixed gas is burned by this spark, and the mixed gas flowing through the first flow path 45 is burned to become a combustion gas.

After the ignition by the ignition means 56, the fuel gas from the second gas supply device is fed to the second space 22b of the injection nozzle body 20 through the outer gas feed pipe 18, and the second space 2
Fuel gas is ejected from 2b through the second ejection hole 48. Then, the fuel gas thus ejected flows through the gap 39 between the intermediate tapered portion 33 of the injection nozzle body 20 and the inclined portion 34b of the first cylindrical member 32 into the through hole 50, and through the through hole 50. It is jetted into the second flow path 47.
Therefore, the fuel gas is ejected toward the air flow flowing through the second flow path 47, and the relatively thin mixed gas (concentration lower than the gas concentration of the mixed gas flowing through the first flow path 45) becomes the second mixed gas.
Flow through the second flow path 47 and the flame from the first flow path 45 propagates to the second flow path 47.
The mixed gas flowing through 7 burns to become combustion gas.

After the mixed gas flowing through the second flow path 47 is burned in this way, the supply of the fuel gas from the first gas supply device is stopped, and thereafter the fuel supplied from the second gas supply device is stopped. The gas is burned. In such a combustion state, if the supply amount of the fuel gas from the second gas supply device is reduced in order to reduce the combustion output of the burner device, the fuel gas ejected from the second ejection holes 48 of the ejection nozzle body 20. The amount of jetting is small and the jetting speed becomes slow. When the ejection speed is slowed in this way, as understood from FIG. 3, the fuel gas ejected from the second ejection holes 48 is discharged between the large diameter portion 31 of the injection nozzle body 20 and the first cylindrical member 32. Passing through the intermediate tapered portion 33 and the inclined portion 34b of the inner protrusion 34
The air flow flowing between the first and second flow paths 45 is greatly affected by the air flow. Therefore, most of the fuel gas ejected from the second ejection holes 48 flows through the first flow passage 45, and the amount ejected into the second flow passage 47 through the through holes 50 is small. Therefore, although the gas concentration of the mixed gas generated in the first flow path 45 in which the air flow is relatively slow becomes high, and the supply amount of the fuel gas supplied from the second supply device is small, The mixed gas from the first flow path 45 is stably burned.

On the other hand, when the supply amount of the fuel gas from the second gas supply device is increased in order to increase the combustion output of the burner device, the fuel gas ejected from the second ejection holes 48 of the ejection nozzle body 20 is ejected. The larger the amount, the faster the ejection speed. When the ejection speed is increased in this way, as can be understood from FIG. 3, the fuel gas ejected from the second ejection holes 48 has the intermediate tapered portion 33 and the inner protrusion 34 of the injection nozzle body 20.
Of the first cylindrical member 32 through the gap 39 to flow into the through hole 50 of the inclined portion 34b of the first cylindrical member 32 without being much affected by the air flow flowing between the inclined portion 34b and the inclined portion 34b. The amount of gas delivered through the chamber increases as the amount of gas delivered increases. Hence the second
Most of the fuel gas ejected from the ejection holes 48 is ejected into the second flow path 47 through the through holes 50 and flows through the second flow path 47 together with the air flow flowing through the second flow path 47. Therefore, a relatively thin mixed gas is generated in the second flow path 47 in which the air flow is relatively fast, and a large amount of fuel gas supplied from the second supply device is relatively thin in the second flow path 47. It becomes a gas and is burnt in a stable and lean manner.

In this way, the fuel gas ejected from the second ejection holes 48 of the injection nozzle body 20 is fed to the first and second flow paths 45 and 47 according to the ejection amount. Depends on the flow velocity of the air flow flowing through the first flow path 45, the size of the second ejection hole 48, and the like, but the intermediate tapered portion 33 of the injection nozzle body 20 and the inclined portion of the first cylindrical member 32. 34
The gap 39 with b can be set to, for example, about 0.1 to 1.0 mm. Further, in order to overcome the air flow flowing through the first flow passage and sufficiently discharge the fuel gas ejected from the second ejection holes 48 of the injection nozzle body 20 into the second flow passage 47, It is desirable to set the maximum ejection speed of the fuel gas from the ejection holes 48 in the range of 1 to 1000 m / s.

As described above, in this burner device, when the supply amount of the fuel gas is small, the mixture gas becomes a relatively rich mixed gas and is burned mainly from the first nozzle means 10, and the supply amount of the fuel gas is large. Sometimes, a relatively thin mixed gas is burned mainly from the second nozzle means, and the fuel gas can be stably burned even if the supply amount from the second gas supply device largely changes.

In the above-described embodiment, after the ignition, the supply of the fuel gas from the first gas supply device is stopped, and the fuel gas from the second gas supply device is supplied to the injection nozzle body for combustion. However, the present invention is not limited to this, and even after ignition, the fuel gas from the second gas supply device and the fuel gas from the first gas supply device are always supplied to the injection nozzle body and burned. Good.

[0043]

The jet nozzle body and the structure related thereto can be configured as shown in FIG. With reference to FIG. 5, in this modification, the injection nozzle body 102 has a space 104 into which fuel gas is fed, and fuel gas from a gas supply device (not shown) is fed into this space 104. It The tip end portion of the injection nozzle body 102 is provided with a tip end inclined portion 106 that inclines radially inward toward the tip end side,
A plurality of ejection holes 108 are provided in the tip inclined portion 106 at intervals in the circumferential direction.

On the downstream side of the jet nozzle body 102, there is a first
Nozzle means 110 is provided. The first nozzle means 110 is composed of a first cylindrical member 112, as shown in FIG.
In the direction of flow of the combustion air. Further, second nozzle means 114 is provided so as to cover the jet nozzle body 102 and the first nozzle means 110. The second nozzle means 114 is composed of the second cylindrical member 116, and extends upward in FIG. 5 from one end portion that covers the jet nozzle body 102.

In this variation, as can be seen from FIG. 5, the first cylindrical member 112 defines the first flow path 118 therein and the second cylindrical member 116 is the injection nozzle body 102. An annular second flow path 120 is defined between the second flow path 120 and the first cylindrical member 112. In connection with this,
Although not shown, the upstream side of the second flow path 120 is connected to an air flow path for supplying combustion air. Therefore, as will be readily understood, the combustion air from the air flow passage (not shown) passes through the second flow passage 120 through the arrow 122.
The flow velocity of the air flow becomes relatively high. Further, a part of the air flowing through the second flow passage 120 passes through the introduction opening 126 between the injection nozzle body 102 and the first cylindrical member 112, as shown by an arrow 124, and the first flow passage 118. To the downstream side through the first flow path 118. Since the opening area of the introduction opening 126 of the first flow path 118 is narrowed, the flow velocity of the air flow flowing through the first flow path 118 is relatively low.

By adopting such a configuration as well, the fuel gas ejected from the ejection holes 108 of the injection nozzle body 102 is fed to the first and second flow paths 118 and 120 according to the ejection amount. can do. That is, when the supply amount of the fuel gas from the gas supply device (not shown) is small, the injection amount of the fuel gas ejected from the ejection holes 108 of the injection nozzle body 102 is small and the ejection speed thereof is low. When the ejection speed becomes low in this way, the fuel gas is greatly affected by the air flow flowing from the second flow path 120 through the introduction opening 126 into the first flow path 118, and together with this air flow, the first It comes to flow through the flow path 118. Therefore, most of the fuel gas ejected from the ejection holes 108 flows through the first flow passage 118 and the second flow passage 1
The amount ejected to 20 decreases. On the other hand, when the amount of fuel gas supplied from the gas supply device increases, the injection nozzle body 1
02, the ejection amount of the fuel gas ejected from the ejection hole 108 increases and the ejection speed thereof increases. When the ejection speed increases in this way, the fuel gas ejected from the ejection holes 108 is not much affected by the air flow flowing from the second flow passage 120 into the first flow passage 118, and the introduction opening portion is not affected. It passes through 126 and is ejected into the second flow path 120. Therefore, most of the fuel gas ejected from the second ejection holes 48 does not flow into the first flow passage 118 and the second flow passage 12 does not flow.
0 is jetted out to the downstream side together with the airflow flowing through the second flow path 120. As described above, when the supply amount of the fuel gas is small, a mixed gas having a relatively high gas concentration is generated in the first flow path 118 having a low air flow rate,
When the supply amount of the fuel gas is large, a mixed gas having a relatively low gas concentration can be generated in the second flow path 120 having a high air flow rate, and the mixed gas can be stably generated even if the supply amount of the fuel gas is significantly changed. It can burn.

Examples and Comparative Examples In order to confirm the effects of the burner device of the present invention, FIGS.
A combustion gas combustion experiment was conducted using the burner device of the embodiment shown in FIG. The dimensions of each member in the burner device used were as follows. For the injection nozzle body,
Eight first jet holes having a diameter of 1.3 mm were provided at substantially equal intervals in the circumferential direction, and eight second jet holes having a diameter of 2.6 mm were provided at substantially equal intervals in the circumferential direction. The first nozzle means has an inner diameter of 36 mm and a length of 102 mm.
Nozzle main body, inner diameter 46 mm, length 11 mm large diameter portion, inner diameter 36 mm, length 16 mm small diameter portion, and a taper portion of 5 mm in length connecting these both, the taper angle of the taper portion is 45 degrees. A certain tip nozzle was used, and the large diameter portion of the tip nozzle was attached to the nozzle body to form a first cylindrical member. Eight inner protrusions extending over an angle range of 15 degrees were provided on the nozzle body at substantially equal intervals, and the gap between the inclined portion of the inner protrusion and the intermediate taper portion of the ejection nozzle was set to 0.5 mm. . Further, as the second nozzle means, a second cylindrical member having an inner diameter of 70 mm and a length of 100 mm was used. By using such first and second cylindrical members, the radial cross-sectional area of the first flow path is set to 1018 mm ² and the radial cross-sectional area of the ^second flow path is set in consideration of their wall thickness. to 2038mm ^2, also sets the radial cross-sectional area of the supply opening to 405mm ^2. Furthermore, as the combustion cylinder 14, a cylindrical member having an inner diameter of 143 mm and a length of 358 mm was used. This cylindrical member is provided with eight air holes having a diameter of 6 mm at the mouth portion (left end portion in FIGS. 1 and 2) at substantially equal intervals in the circumferential direction. 1.2m in diameter with substantially equal spacing in the direction
Eight air hole sets each having 36 m air holes were provided in the longitudinal direction.

In a combustion experiment using such a burner device, air having a temperature of 350.degree.
It was fed at a rate of 00 Nm ³ / H. The air sent is
About 4% of it goes through the first channel and about 55% of it goes through the second
And about 41% of it flowed through the outside of the combustion cylinder, and the air flowing outside the combustion cylinder flowed into the combustion cylinder through the air holes of the combustion cylinder. Using methane as the fuel gas, the first of the injection nozzle body is used at a rate of 1 Nm ³ / H.
In addition to being ejected from the ejection hole, it is ejected from the second ejection hole of the injection nozzle body at a rate of 24 Nm ³ / H, and the fed air and methane are mixed into a mixed gas and ignited by an ignition member to burn the mixed gas. To generate combustion gas. After this ignition, the ejection of methane from the first ejection hole was stopped,
The amount of methane emitted from the second outlet is 25 Nm.
³ / H, the feed amount was gradually reduced from the ratio of 25 Nm ³ / H, and the change in the combustion state was investigated.

In this combustion, the supply amount of methane is 95%
The combustion of the burner disappears when it is reduced to 5%, and the turndown ratio (a ratio that indicates how much the combustion gas feed rate can be reduced based on 100% feed rate)
Was 1:20. From this experimental result, it was confirmed that the burner apparatus of the embodiment burns stably even if the supply of methane is reduced, its flame holding ability is high, and more efficient operation of the system including the burner apparatus is possible. did it.

As a comparative example, the gap between the intermediate tapered portion of the ejection nozzle body and the inclined portion of the first cylindrical member is eliminated, in other words, all the fuel gas ejected from the second ejection hole is made to flow in the second flow. The above-described combustion experiment was conducted using a burner device having substantially the same configuration as that of the example except that the fuel was fed to the road, and the feeding conditions of air and combustion gas were the same as those of the example.

In the combustion experiment of the comparative example, when the feed amount of methane was reduced by 20% and reduced to 80%, the combustion of the burner device disappeared and the turndown ratio was 4: 5.

[0053]

According to the burner device of the present invention, the first flow passage 45 defined by the cylindrical first nozzle means 10 is provided.
The flow velocity of the air flowing through the nozzle is relatively low, the flow velocity of the air flowing through the second flow path 47 defined by the cylindrical second nozzle means 12 is relatively high, and the jet holes 48 of the jet nozzle body 20 are provided.
The fuel gas from is ejected toward the second flow path through the first flow path. Therefore, when the injection amount of the fuel gas is small, the ejection speed of the fuel gas is low, and the fuel gas ejected from the ejection holes 48 flows through the first flow path under the action of the air flow flowing through the first flow path. . When the ejection amount of the fuel gas increases, the ejection velocity of the fuel gas increases, whereby the fuel gas ejected from the ejection holes 48 overcomes the air flow flowing through the first passage and is directed toward the second passage. Flow, and the ejection amount ejected to the second flow path increases. As described above, when the injection amount of the fuel gas is small, a large amount of the fuel gas flows in the first flow passage having a small air flow rate, and therefore, the mixed gas having a relatively high gas concentration flows in the first flow passage. The generated fuel gas burns stably even though the amount of jet is small. Further, when the injection amount of the fuel gas increases, a part of the fuel gas flows into the first flow path, and the rest flows into the second flow path with a large air flow rate, and
The flow rate flowing in the flow path of No. 2 increases as the amount of fuel gas jetted increases. Therefore, the mixed gas having a relatively low gas concentration is generated in the second flow path, and the first mixed gas is generated.
And the fuel gas comes to burn in the second nozzle means. The second nozzle means is concentrically arranged outside the first nozzle means, and the ejection hole 48 of the ejection nozzle body has the first ejection port 48.
Is formed at one end of the nozzle means. The fuel gas ejected from the ejection holes 48 of the ejection nozzle body is ejected toward the second flow passage through the first flow passage. Therefore, when the ejection amount of the fuel gas ejected from the ejection hole 48 is small, the fuel gas ejected from the ejection hole 48 and the first nozzle
By the air flow flowing through the gap 39 with the nozzle means of
Flow into the channel. Further, when the amount of the fuel gas ejected from the ejection hole 48 increases, the fuel gas ejected from the ejection hole 48 flows through a part of the first flow path between the injection nozzle body and the first nozzle means. Through which it flows into a second flow path defined between the first nozzle means and the second nozzle means for premixing. Thus, the fuel gas ejected from the second ejection holes of the injection nozzle body can be fed to the first and second flow paths as required according to the ejection amount. Further, according to the present invention, since the mixed gas introduction unit is provided between the first flow path and the second flow path, a part of the mixed gas generated in the second flow path is The gas is introduced into the first flow path, whereby the gas concentrations of the mixed gas in the first flow path and the mixed gas in the second flow path are made uniform, and deviation of the combustion state is reduced.

Further, according to the present invention, since the maximum ejection speed of the fuel gas is 1 to 1000 m / s, when the ejection amount of the fuel gas increases, it is sufficient to overcome the air flow flowing through the first flow path. A certain amount of fuel gas is ejected to the second flow path, and the fuel gas from the second flow path is stably burned.

Further, according to the present invention, the injection nozzle body, in addition to the ejection holes 48 for ejecting the fuel gas toward the second flow path through the first flow path, supplies the fuel gas to the first flow path. It has another ejection hole 46 for ejecting. Therefore, when the injection amount of the fuel gas is small, the fuel gas from the first and second ejection holes is fed to the first flow path, and therefore the gas concentration of the mixed gas in the first flow path is increased. be able to.

[0056]

According to the present invention, the inner diameter of the through hole 50 is substantially equal to or larger than the inner diameter of the ejection hole 48 formed so as to face each other in the through hole 50. The fuel gas is surely guided to the through hole 50 as required, and can be supplied to the second flow path 47 through the through hole 50. Further according to the invention,
When the supply of the fuel gas by the gas supply means capable of controlling the flow rate is small, the fuel gas from the ejection hole 108 of the injection nozzle body 102 passes through the introduction opening 126 and the first nozzle means 110.
When the fuel gas and the air are premixed in the first flow path 118 of the fuel gas, and the fuel gas is supplied from the gas supply means in large quantities, the fuel gas from the ejection holes 108 is discharged. , Through the introduction opening 126 and the first and second
The second flow path 12 flows along with air into the second flow path 120 formed between the nozzle means 110 and 118.
At 0, it is sufficiently premixed and introduced into the combustion space. Therefore, the high concentration region of the fuel gas is not formed, and NO
The x concentration can be kept low.

[Brief description of drawings]

FIG. 1 is a sectional view schematically showing an embodiment of a burner device according to the present invention.

FIG. 2 is an enlarged sectional view schematically showing a main part of the burner device of FIG.

3 is a cross-sectional view showing the injection nozzle body and its vicinity in the burner device of FIG. 1 in a further enlarged manner.

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

FIG. 5 is an enlarged cross-sectional view showing a modification of the injection nozzle body and the configuration related thereto.

[Explanation of symbols]

2 Diffuser section 6 burner case 8 air flow paths 10,110 First nozzle means 12,114 Second nozzle means 20,102 injection nozzle body 32,112 first cylindrical member 38,116 Second cylindrical member 45,118 First channel 46 First ejection hole 47,120 Second channel 48 Second ejection hole 56 Ignition means 62 gas turbine 108 ejection hole

─────────────────────────────────────────────────── ─── Continuation of front page (72) Inventor Koji Morie 4-1-2, Hirano-cho, Chuo-ku, Osaka-shi, Osaka Within Osaka Gas Co., Ltd. (72) Inventor Tsutomu Wakabayashi 4-chome, Hirano-cho, Chuo-ku, Osaka-shi, Osaka 1-2 In Osaka Gas Co., Ltd. (72) Inventor Takahiro Sako 4-1-2, Hirano-cho, Chuo-ku, Osaka-shi, Osaka Prefecture In-house Gas Co., Ltd. (72) Yuji Nakamura Hirano-cho, Chuo-ku, Osaka-shi, Osaka chome No. 1 No. 2 Osaka Gas Co., Ltd. in the (56) reference Patent flat 10-89689 (JP, a) JP Akira 50-18810 (JP, a) (58 ) investigated the field (Int.Cl. ⁷ , DB name) F02C 7/00-9/26 F23R 3/28-3/32 F23D 14/02

Claims (6)

(57) [Claims] 1. A tubular first nozzle means (10) defining a first flow path (45), and (b) an injection nozzle body (20) provided concentrically with the first nozzle means (10). A substantially annular gap 39 is formed between the inner surface of the first nozzle means 10 and the outer surface of the injection nozzle body 20, and this gap 39 is connected to the first flow passage 45 and is supplied with fuel gas. A jet hole 48 is formed which has a space 22b and extends substantially in the radial direction and communicates with the space 22b and the gap 39. The jet hole 48 is provided with the jet nozzle body 20 provided in the first nozzle means 10. (C) Through holes 50 are formed in the first nozzle means 10 so as to face each other in the ejection holes 48 via the gap 39, and (d) the second nozzle means 12 having a cylindrical shape. And provided concentrically outside the first nozzle means 10, Second nozzle means and fuel gas and air through the holes 50 defines a second flow path 47 of the annular be premixed 1
2, (e) gas supply means for supplying the fuel gas to the space 22b of the injection nozzle body 20 in a controllable manner, and (f) the air passage 8 in the gap 39 and the second passage 47.
A combustion space is formed downstream of the first and second flow paths 45, 47, and (h) from the air flow path 8 through the gap 39. The flow velocity of the air flowing through the first flow passage 45 is relatively low, the flow velocity of the air flowing through the air flow passage 8 to the second flow passage 47 is relatively high, and (i) from the ejection holes 48 of the injection nozzle body 20. Of the fuel gas passes through the gap 39, the through hole 50, and the second fuel gas.
(J) When the amount of fuel gas supplied from the gas supply means is small, the jet speed of the fuel gas jetted from the jet holes 48 of the jet nozzle body 20 is low, and therefore, Spout 4
The fuel gas ejected from No. 8 flows into the first flow path 45 under the action of the air flow flowing through the gap 39. (k) When the supply amount of the fuel gas from the gas supply means increases, the injection nozzle body The jet speed of the fuel gas jetted from the jet holes 48 of 20 increases, whereby the fuel gas jetted from the jet holes 48 overcomes the air flow flowing through the gap 39 and the second flow path 47. To the second flow path 47 as the fuel gas supply increases.
A burner device characterized in that the flow rate flowing to the inside also increases. 2. A mixed gas for guiding a part of the lean mixed gas of the second flow passage 47 to the first flow passage 45 between the first flow passage 45 and the second flow passage 47. Introduction means 76, 82, 84
The burner device according to claim 1, wherein a burner device is provided. 3. The ejection hole 48 of the ejection nozzle body 20.
The maximum ejection velocity of fuel gas ejected from
The burner device according to claim 1 or 2, wherein m / s. 4. The injection nozzle body 20 is provided with another ejection hole 46 for ejecting the fuel gas toward the first flow path 45, as claimed in any one of claims 1 to 3. Burner device described in. 5. The inner diameter of the through hole 50 is substantially equal to or larger than the inner diameter of the ejection holes 48 formed in the through hole 50 so as to face each other.
Burner apparatus according to one of claims 1 to 4. 6. (a) An injection nozzle body (102) having a space (104) into which fuel gas is supplied, and a tip sloping portion (10) sloping radially inward toward a tip side.
6, the injection nozzle body 102 in which the ejection hole 108 is formed in the tip inclined portion 106, and (b) the cylindrical first nozzle means 110, which is provided on the downstream side of the injection nozzle body 102. A first nozzle means 110 that defines an introduction opening 126 having a narrowed opening area between the injection nozzle body 102 and defines a first flow path 118; and (c) the injection nozzle body 102 and the first nozzle means 110. The nozzle means 110 is covered and the jet nozzle body 102 and the first nozzle means 110 are covered.
A cylindrical second defining the annular second flow path 120 between
Nozzle means 114, (d) gas supply means for supplying fuel gas to the space 104 of the injection nozzle body 102 in a flow path controllable manner, and (e) an air flow path upstream of the second flow path 120. An air supply source for supplying air from (f) the first nozzle means 110 and the second nozzle through the air flow path.
The flow velocity of the air flowing through the second flow path 120 between the first flow passage 120 and the nozzle means 114 is relatively high, and the flow velocity of the air flowing from the air flow passage through the introduction opening 102 to the first flow passage 118 is relatively high. (G) the fuel gas from the ejection holes 108 of the injection nozzle body 102 is ejected toward the first and second flow paths 118 and 120, and (h) the amount of fuel gas supplied from the gas supply means. Is small, the ejection speed of the fuel gas ejected from the ejection holes 108 of the injection nozzle body 102 is low, and therefore the fuel gas ejected from the ejection holes 108 is
When the flow rate of the fuel gas from the gas supply means increases, the injection nozzle body 102 is subjected to the action of the airflow flowing through the first flow path 118 through the flow path 26 and flows into the first flow path 118. The ejection speed of the fuel gas ejected from the ejection hole 108 is increased, and the fuel gas ejected from the ejection hole 108 is supplied to the first passage 118 through the second passage 120. It flows through the introduction opening 126 to the second flow path 120 without being affected by the flow, and thus the flow rate of the second flow path 120 increases as the supply amount of the fuel gas increases. A burner device characterized by: