JP2009281688A - Burner of combustion device, and combustion device equipped with the same - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a burner of a combustion device capable of realizing low NO<SB>x</SB>combustion using lean premixed air and fuel while simplifying the structure by only decreasing a flow velocity of a premixed air and fuel flow without using a swirler and without generating a backflow area for allowing formation of a flame holding area, and a combustion device equipped with the burner. <P>SOLUTION: The burner for injecting premixed air and fuel to a combustion chamber formed inside a combustion cylinder is equipped with a premixing tube part for introducing fuel and air to form the premixed air and fuel and a premixed air/fuel deriving part positioned on the downstream side of the premixing tube part for deriving the premixed air/fuel to the combustion chamber. In a premixed air/fuel flow passage formed of the premixing tube part and the premixed air/fuel deriving part, at least a part from a downstream end of the premixing tube part to a deriving port facing to the combustion chamber of the premixed air/fuel deriving part is formed as an enlarging passage in which a sectional area of the premixed air/fuel flow passage vertical to an axis of the burner gradually increases toward the downstream side. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a burner for a combustion apparatus used for a device that requires supply of high-temperature gas, such as a gas turbine engine and a boiler, and a combustion apparatus including the burner.

  Gas turbine engines have strict environmental standards regarding the composition of exhaust gas emitted by combustion, considering environmental conservation, and it is required to reduce harmful substances such as nitrogen oxides (hereinafter referred to as NOx). It has been. On the other hand, large-scale gas turbine engines for ground facilities and aircraft gas turbine engines tend to have a high pressure ratio due to demands for low fuel consumption and high output. The combustion temperature tends to increase as the inlet temperature of the combustion apparatus increases, and there is a concern that it may be a factor that rather increases NOx.

  Therefore, in recent years, a combustion method that adopts a lean premixed combustion method that effectively reduces the amount of NOx generated, for example, a combined combustion method that combines a lean premixed combustion method and a diffusion combustion method has been proposed (patents). References 1, 2). In the lean premix combustion method, air and fuel are premixed and burned as an air-fuel mixture with a uniform fuel concentration, so there is no combustion region where the flame temperature is locally high, and the fuel is diluted. As a result, the flame temperature can be lowered as a whole, so that there is an advantage that the amount of NOx generated can be effectively reduced, but blowout tends to occur during low load combustion. In addition, the diffusion combustion method burns fuel and air while diffusing and mixing them, so it is difficult to blow out even at low loads and has the advantage of excellent flame holding performance, while reducing the amount of NOx generated. There are challenges. Therefore, according to the combined combustion method, it is possible to reduce the amount of NOx generated by premixed combustion at high load while ensuring combustion stability by diffusion combustion at start-up and low load.

  By the way, in the conventional combined combustion type combustion apparatus, as shown in FIG. 6, for example, a swirler 83 is provided so as to surround the outside of a diffusion combustion burner (pilot burner) 82 disposed at the top 81a of the combustion cylinder 81 of the combustion apparatus 80. A premixed combustion burner (main burner) 84 having the above is disposed, and a burner unit 85 that injects the premixed gas P as a swirling flow into the combustion chamber is employed.

When the premixed fuel P is injected into the combustion chamber as a swirling flow using the premixed fuel burner 84 having the swirler 83, the premixed gas toward the top 81a of the combustion cylinder 81 is inside the swirling flow that has become negative pressure. A reverse flow region R of P is generated. In the conventional combustion apparatus 80, the backflow region R is formed in this way, and a high temperature combustion gas is circulated by the backflow and used as an ignition source to hold the flame.
JP-A-8-28871 Japanese Patent Application Laid-Open No. 8-210441

  However, in the flame holding mechanism that uses the swirler to generate the reverse flow region R and uses the high-temperature combustion gas as the ignition source, the combustion temperature decreases when the fuel concentration of the premixed gas is further diluted. If the combustion temperature decreases, the temperature of the circulated combustion gas decreases and it does not function as an ignition source, so flame holding becomes difficult. That is, the conventional burner that generates a swirling flow of the premixed gas using a swirler to hold the flame has a problem that it is difficult to further reduce NOx by diluting the fuel concentration of the premixed gas. . Furthermore, there is a problem that the structure of the burner is complicated by using a swirler.

  The present invention does not generate a backflow region by not using a swirling mechanism such as a swirler, and enables the formation of a flame holding region by only reducing the flow velocity of the premixed airflow, thereby simplifying the structure while simplifying the structure. It is an object of the present invention to provide a burner for a combustion apparatus capable of realizing low NOx combustion using a simple premixed gas and a combustion apparatus equipped with the burner.

  In order to achieve the above-described object, a burner of a combustion apparatus according to the present invention is a cylindrical burner that injects a premixed mixture of fuel and air into a combustion chamber formed inside a cylindrical combustion cylinder. A premixing tube portion that forms a premixed gas by introducing fuel and air, and a premixed gas deriving portion that is located downstream of the premixing tube portion and leads the premixed gas to the combustion chamber A premixed gas flow path formed by the premixed pipe section and the premixed gas outlet section, and at least a downstream end of the premixed pipe section that leads to the combustion chamber of the premixed gas outlet section. A portion up to the outlet is formed as an enlarged passage in which a cross-sectional area perpendicular to the axis of the burner of the premixed air channel gradually increases toward the downstream side.

  According to this configuration, the flow velocity of the premixed air flow ejected from the premixing tube portion is gradually reduced by passing through the enlarged passage having a cross-sectional area that gradually increases toward the downstream side. The premixed air flow that has been gradually decelerated by the expansion passage forms a flame holding region at a position where the flow velocity balances with the propagation speed of the flame. That is, according to the burner described above, the flame can be held by balancing the flow velocity of the premixed gas and the flame propagation speed, so that the flame is held even if the combustion temperature is lowered using a lean premixed gas. It becomes possible. In addition, since premixing is further promoted with a decrease in the flow velocity of the premixed air flow in the enlarged passage, a premixed gas having a uniform concentration distribution can be formed. Therefore, generation of NOx at the time of combustion can be significantly suppressed using a lean premixed gas. The flame holding region is formed in the combustion chamber or in the enlarged passage of the burner.

  In other words, the burner does not include a swirling mechanism that forms a swirling flow of the premixed gas, and injects the premixed gas into the combustion chamber without swirling. Therefore, an effect that a low NOx combustion can be realized by stably holding a flame even when a lean premixed gas as described above is used is obtained by a burner having a simple structure not provided with a swirling mechanism such as a swirler. Can do.

  In this invention, it is preferable that the said premixing pipe part is formed as a venturi mixer. According to this configuration, the premixing tube portion is formed into a Venturi tube shape having a minimum diameter portion located substantially at the center in the axial direction and a diameter expanding portion extending from the minimum diameter portion to the upstream side and the downstream side, respectively. Therefore, the diameter-enlarged portion downstream of the minimum diameter portion of the premixing tube portion functions as a part of the expansion passage. As a result, the effect of promoting premixing due to the deceleration of the premixed airflow becomes more prominent, and NOx generation can be effectively suppressed using a leaner premixed gas.

  Moreover, it is preferable that the fuel supply pipe for supplying fuel to the premixing pipe section is disposed concentrically with the premixing pipe section. By disposing the fuel supply pipe in this way, it becomes easy to obtain a premixed gas having a uniform fuel concentration in a location.

  The burner of the present invention may have a plurality of the premixing tube portions. By adopting such a configuration, even when a large amount of fuel is injected and high-load combustion is performed, a premixed gas with a uniform fuel concentration can be formed.

  The burner according to the present invention may include an ignition device that ignites in the enlarged passage. In this case, for example, an ignition device may be provided in the premixed gas outlet portion, or may be provided in a central portion in the radial direction of the premixed tube forming the premixed tube portion. Since the flow velocity of the premixed gas is decelerated in the premixed air flow passage formed as the enlarged passage, it is possible to prevent ignition and prevent ignition by igniting in the enlarged passage.

  A combustion apparatus according to the present invention includes the above-described burner, and a top portion of the combustion cylinder has a tapered shape that is smoothly connected to an inner peripheral wall of the lead-out portion of the burner, and forms a part of the enlarged passage. Yes.

  Generally, when the fuel concentration of the premixed gas is lowered, the position where the flow velocity of the premixed gas and the flame propagation speed are balanced shifts to the downstream side. In the combustion apparatus having the above configuration, the top portion of the combustion cylinder also forms a part of the enlarged passage, so that the flow rate of the premixed gas can be gradually reduced over a long distance. As a result, since the mixing is sufficiently performed, it becomes possible to form a flame holding region in the combustion chamber using a premixed gas having a lower concentration. That is, since a lower concentration premixed gas can be used, generation of NOx can be more effectively suppressed.

  As described above, according to the burner and the combustion device of the combustion device according to the present invention, the flame holding region can be formed only by reducing the flow velocity of the premixed air flow without causing a back flow region. Low NOx combustion using a lean premixed gas can be realized.

  Embodiments according to the present invention will be described below in detail with reference to the drawings. FIG. 1 is a simplified configuration diagram showing a gas turbine engine to which a combustion apparatus according to an embodiment of the present invention is applied. The gas turbine engine GT includes a compressor 1, a combustion device 2, and a turbine 3 as main components. The compressed air supplied from the compressor 1 is combusted by the combustion device 2, and high-pressure combustion gas generated thereby. Is supplied to the turbine 3. The compressor 1 is connected to the turbine 3 via the rotating shaft 5 and is driven by the turbine 3. The load 4 such as an aircraft rotor or generator is driven by the output of the gas turbine engine GT. The fuel F fed from the fuel supply device 9 is supplied to the combustion device 2 via the fuel control device 8.

  FIG. 2 is a cross-sectional view showing the combustion apparatus 2. This combustion apparatus 2 is a can type that is arranged in a ring shape around the engine rotation axis, and is attached to a combustion cylinder 12 that forms a combustion chamber 10 inside, and a tapered top portion 12 a of the combustion cylinder 12. The combustion chamber 10 is provided with a burner 14 for injecting a premixed mixture of fuel and air, and has a simple structure without a swirling mechanism such as a swirler that gives the premixed gas a swirl around an axis. The combustion cylinder 12 and the burner 14 are concentrically accommodated in a substantially cylindrical housing H that is an outer cylinder of the combustion apparatus 2. An end cover 18 is fixed to the front end of the housing H with bolts 20.

  An annular inner flange 24 is formed on the inner peripheral wall in the vicinity of the tip of the housing H, and a support cylinder 26 extending in a cylindrical shape from the combustion cylinder 12 is connected and fixed to the inner flange 24 with a bolt 28, so that combustion occurs. The top of the cylinder 12 is attached to the housing H. An air passage 30 is formed between the housing H and the combustion cylinder 12 to guide the compressed air A from the compressor 1 toward the top of the combustion cylinder 12 as indicated by an arrow. Furthermore, facing the air passage 30, a plurality of air introduction holes 32 are arranged in the circumferential direction on the peripheral wall of the support cylinder 28, and the compressed air A sent through the air passage 30 is The air is introduced into the air introduction space 34 formed by the housing H, the support cylinder 26, and the end cover 18 through the air introduction hole 32.

  FIG. 3 is a longitudinal sectional view showing a main part of the burner 14 of the combustion device 2 of FIG. The burner 14 has a cylindrical burner cylinder 40 having the same axis C1 as the combustion cylinder 12 and forming a peripheral wall of the burner 14, and a single premixing tube 42 fitted inside the burner cylinder 40. And a plurality of fuel supply pipes 44 for supplying the fuel F to the premixing pipe body 42. The premixing tube body 42 has a plurality of premixing tube portions 46 which are through-holes in the axial direction of the premixing tube body 42 for forming the premixed gas P, and each supply one fuel. The pipe 44 is arranged so as to face the inside of one premixing pipe portion 46 and inject the fuel F into the premixing pipe portion 46.

  The inner peripheral surface 40a in the vicinity of the downstream end of the burner tube 40 is a conical surface formed in a tapered shape with a diameter increasing toward the downstream side. At the upstream end of the tapered inner peripheral surface 40a, an annular flange surface 40b facing the upstream side in the axial direction is provided, and on the flange surface 40b, the downstream end face of the cylindrical premixing tube 42 is provided. 42a is in contact. On the other hand, the downstream end 40 c of the burner cylinder 40 is connected to the upstream end of the top portion 12 a of the combustion cylinder 12. That is, the portion having the tapered inner peripheral surface 40 a on the downstream side of the burner cylinder 40 functions as a premixed gas derivation section 48 that guides the premixed gas P from the premixing pipe section 46 into the combustion chamber 10. Note that the top 12a of the combustion cylinder 12 and the inner peripheral surface 40a of the premixed gas derivation section 48, both of which are tapered so as to increase in diameter toward the downstream side, are both tapered as in this embodiment. It is preferable that the shape is set so as to be smoothly connected.

  In the premixing pipe portion 46, together with the fuel F injected from the fuel supply pipe 44, compressed air A is introduced from the upstream end opening 40d of the burner cylinder 40, so that a premixed gas P of the fuel F and air A is formed. Is done. Each of the plurality of premixing tube portions 46 is formed as a venturi mixer having a venturi tube shape. That is, the minimum diameter portion 46a having the smallest passage diameter is provided near the center in the axial direction of the premixing pipe portion 46, and the downstream side and the upstream side thereof are the downstream side enlarged portion 46b and the upstream side enlarged portion 46c, respectively. It is formed as.

  As shown in FIG. 4, which is a rear view of the premixing tube body 42 of FIG. 3 as viewed from the downstream side, the premixing tube body 42 has one premixing tube portion 46 located at the center of the circular cross section. A total of seven premixing tube portions 46 are provided, including six premixing tube portions 46 arranged uniformly around the central premixing tube portion 46. The premixing tube portions 46 are arranged close to each other so that the openings 46d at the downstream ends thereof are substantially circumscribed. Further, the circumscribed circle Q of the six premixing pipe portions 46 indicated by the alternate long and short dash line in FIG. 4 is set so as to substantially match the shape of the upstream end of the inner peripheral surface 40a of the premixed gas outlet portion 48 shown in FIG. ing.

  Therefore, in the premixed gas flow path 52 formed by the premixed tube section 46 and the premixed gas outlet section 48, the downstream-side enlarged diameter section 46b of the premixed pipe section 46, the tapered premixed gas outlet section 48, and Is formed as an enlarged passage E in which the cross-sectional area perpendicular to the axis C1 of the burner 14 gradually increases toward the downstream side. From the vicinity of the downstream of the premixing pipe section 46 to the vicinity of the upstream of the premixed gas outlet section 48, the total cross sectional area of all the premixed gas pipe sections 46 and the cross sectional area of the premixed gas outlet section 48 as the passage area of the premixed gas flow path 52 Compared to the increase.

  As shown in FIG. 5, the premixing tube portion 46 includes a straight tube portion 46e having a cylindrical inner peripheral surface, a downstream tapered portion 46f and an upstream tapered portion 46g having tapered inner peripheral surfaces. It is good also as a venturi mixer structure which consists of. The downstream taper portion 46f and the upstream taper portion 46g are each formed in a tapered shape whose diameter increases from the downstream end and the upstream end of the straight pipe portion 46e. In this case, the downstream tapered portion 46 f of the premixing tube portion 46 and the premixed gas outlet portion 48 form an enlarged passage E.

  The fuel supply pipe 44 shown in FIG. 3 is preferably arranged on the axis C2 (only one representative is shown) of each premixing pipe section 46 in the radial direction. Further, in the axial direction, the tip end portion 44 a for injecting the fuel F is disposed so as to be positioned in the upstream side enlarged diameter portion 46 c upstream of the minimum diameter portion 46 a of the premixing tube portion 46.

  In the present embodiment, as shown in FIGS. 3 and 5, the spark plug 50, which is an ignition device for igniting the premixed gas P, is installed so as to face the inner peripheral surface 40 a of the premixed gas outlet 48. Thus, ignition is set in the enlarged passage E.

  Instead of installing the spark plug 50 in the premixed gas outlet 48 as in the present embodiment, for example, the spark plug 50 is connected to the premixing pipe 46 at the position of the premixing pipe 46 in the center of the premixed pipe 42. It may replace and may install in the combustion cylinder 12 like the past.

  By adjusting the concentration of the premixed gas P and the length and taper angle of each part constituting the enlarged passage E, the flame holding formed at a position where the flow velocity of the premixed gas P and the propagation speed of the flame are balanced. The position of the region B can be adjusted. In the present embodiment, the flame holding region B is set so as to extend from the premixed gas outlet 48 to the combustion chamber 10 of the combustion cylinder 12.

  Next, operations of the combustion device 2 and the burner 14 configured as described above will be described.

  As shown in FIG. 3, the fuel F injected from the fuel supply pipe 44 into the premixing pipe section 46 is mixed with the air A introduced into the premixing pipe section 46 from the upstream end opening 40 d of the burner cylinder 40. The premixed gas P passes through the minimum diameter portion 46a of the premixing tube portion 46, which is a venturi mixer. The premixed gas P that has passed through the minimum diameter portion 46a flows toward the combustion chamber 10 through a premixed gas flow path 52 formed by a premixed tube portion 46 and a premixed gas outlet portion 48 that are venturi mixers.

  In the premixed gas flow channel 52, a portion of the premixed gas flow channel 52 on the downstream side of the minimum diameter portion 46a has a cross-sectional area perpendicular to the axis C1 of the burner 14 of the premixed gas flow channel 52 toward the downstream side. That is, it is configured as an enlarged passage E that gradually increases along the flow of the premixed gas P. Therefore, as the premixed gas P flows through the enlarged passage E, the flow velocity of the premixed gas P gradually decreases. Due to the change in the flow rate of the premixed gas P, the flow of the premixed gas P is disturbed, and premixing is promoted. Further, the flame holding region B is formed at a position where the flow of the premixed gas P is gradually decelerated and reaches a speed that matches the propagation speed of the flame.

  In the combustion apparatus 2 of the present embodiment, the premixed gas P flows only in a direction substantially along the axis. That is, the burner 14 of the present embodiment does not have a mechanism such as a swirler that generates a swirling flow of the premixed gas P, so that the premixed gas P does not form a swirling flow in the combustion chamber 10. As a result, the backflow region of the premixed gas P is not formed in the combustion chamber 10. In other words, in the present embodiment, the flame holding region B has a flow velocity of the premixed gas P flowing substantially along the axial direction and a flame propagation velocity without using the combustion gas circulated by the reverse flow region. It is formed only by balancing.

  As described above, in the burner 14 of the present embodiment, the flame is held by balancing the flow velocity of the premixed gas P and the flame propagation velocity, so that the combustion temperature is lowered using the lean premixed gas P. Even so, it is possible to hold the flame. Further, since the premixing of the premixed gas P is further promoted in the expansion passage E by reducing the flow velocity of the premixed airflow, the premixed gas P having a uniform fuel concentration distribution can be formed. Therefore, generation of NOx during combustion can be significantly suppressed using the lean premixed gas P. Moreover, such an effect can be obtained by the burner 14 having a simple structure that does not require a swirling mechanism such as a swirler.

  In particular, in the embodiment of FIG. 3, the downstream side enlarged diameter portion 46 b downstream of the minimum diameter portion 46 a of the premixing tube portion 46 functions as a part of the enlarged passage E, so that the effect of promoting premixing is significant. is there.

  When the premixing pipe portion 46 is configured as a venturi mixer as shown in FIG. 3 or FIG. 5, the flow velocity of the premixed gas P injected from the premixing pipe portion 46 is sufficiently larger than the flame propagation speed. By setting, backfire into the premixing pipe portion 46 can be prevented.

  Further, since the fuel supply pipe 44 is arranged concentrically with the premixing pipe section 46, it becomes easy to obtain a premixed gas having a uniform fuel concentration in a location.

  Further, in the present embodiment, as shown in FIG. 4, an ignition plug 50 that is an ignition device for igniting the premixed gas P is installed so as to face the inner peripheral surface 40 a of the premixed gas derivation section 48. Ignite in expanded passage E. Therefore, it becomes possible to ignite the premixed gas P in a state where the flow velocity is sufficiently lowered, and it is possible to ignite easily and reliably.

  Furthermore, since the combustion apparatus 2 according to the present embodiment has the top portion 12a that is smoothly connected to the enlarged passage E formed in the burner 14, the top portion 12a also functions as a part of the enlarged passage E. Generally, when the fuel concentration of the premixed gas P is lowered, the position where the flow velocity of the premixed gas P and the flame propagation speed are balanced shifts to the downstream side. In this case, in the combustion apparatus 2 according to the present embodiment, the top portion 12a of the combustion cylinder 12 also forms a part of the enlarged passage E, so that the flow rate of the premixed gas P can be gradually reduced over a long distance. . As a result, the mixing is sufficiently performed, so that the flame holding region B can be formed in the combustion chamber 10 using the premixed gas P having a lower concentration. Therefore, it becomes possible to more effectively suppress the generation of NOx by using the premixed gas P having a lower concentration.

  A flame holding region B that mainly holds a flame is formed in a portion of the enlarged passage E formed in the combustion chamber 10. For this reason, it is preferable that the top part 12a of the combustion cylinder 12 which forms a part of the enlarged passage E in the combustion chamber 10 has a heat and fire resistant structure. On the other hand, the portion formed in the burner 14 in the enlarged passage E is a member that forms a part of the enlarged passage E in the burner 14 because it mainly forms a region where the flow rate of the premixed gas P is decelerated. The premixed tube body 42 and the premixed gas outlet 48 need not necessarily have a heat and fire resistant structure. However, by adjusting conditions such as the shape of the enlarged passage E and the flow rate of the fuel F, part or all of the flame holding region B can be formed in the premixed gas outlet portion 48 of the burner 14. In that case, it is desirable that the premixed tube body 42 and the premixed gas outlet 48 in the burner 14 have a heat-resistant and fireproof structure.

  Note that, in the burner 14 of the present embodiment, when the injection amount of the fuel F from the fuel supply pipe 44 is sufficiently large, the fuel rich state is also obtained in the premixed gas derivation unit 48. In this case, the burner 14 functions in the same manner as the diffusion combustion burner, and can cope with high-load operation.

  In the present embodiment, a plurality of premixing tube portions 46 are provided, but only one premixing tube portion 46 may be provided. When a plurality of premixing tube portions 46 are provided, the number and arrangement of the premixing tube portions 46 can be set as appropriate. In addition, the premixing pipe portion 46 is not limited to the above-described structure, and may employ any structure as long as it can premix fuel and air and does not generate a swirling flow in the combustion chamber 10. be able to.

  Moreover, in the said embodiment, although the example which applied the combustion apparatus 2 to gas turbine engine GT was demonstrated, the combustion apparatus which concerns on this invention requires supply of high temperature gas, such as a boiler, not only a gas turbine engine. It can be applied to other devices.

1 is a schematic view showing a gas turbine engine to which a combustion apparatus according to an embodiment of the present invention is applied. It is sectional drawing which shows the combustion apparatus of FIG. It is sectional drawing which expands and shows the principal part of the burner used for the combustion apparatus of FIG. It is the rear view which looked at the premixing pipe part of the burner of FIG. 3 from the downstream direction. It is sectional drawing which shows the modification of the premixing pipe part of the burner of FIG. It is sectional drawing which shows the conventional combustion apparatus.

Explanation of symbols

2 Combustion device 10 Combustion chamber 12 Combustion cylinder 12a Top 14 Burner 44 Fuel injection pipe 46 Premixing pipe section 48 Premixed gas outlet section 50 Spark plug 52 Premixed gas flow path F Fuel A Air P Premixed gas E Expanded path B Flame holding Region C1 Burner axis C2 Premix tube axis

Claims (10)

A burner for injecting a premixed mixture of fuel and air into a combustion chamber formed inside a combustion cylinder,
A premixing tube section in which fuel and air are introduced to form a premixed gas;
A premixed gas derivation section that is located downstream of the premixing pipe section and leads the premixed gas to the combustion chamber;
Of the premixed gas flow path formed by the premixed tube section and the premixed gas outlet section, at least a portion from the downstream end of the premixed pipe section to the outlet port facing the combustion chamber of the premixed gas outlet section However, the burner of the combustion apparatus in which the cross-sectional area perpendicular to the axis of the burner in the premixed air flow path is formed as an enlarged passage gradually increasing toward the downstream side.   2. The flame-holding region according to claim 1, wherein the expansion passage reduces the flow velocity of the premixed gas to the same speed as the propagation velocity of the flame so that the flow velocity of the premixed gas and the propagation velocity of the flame are balanced. A burner for a combustion apparatus for forming a gas in the expansion passage or in the combustion chamber.   The burner for a combustion apparatus according to claim 1 or 2, wherein the burner is not provided with a swirling mechanism for forming a swirling flow of the premixed gas.   The burner of a combustion apparatus according to any one of claims 1 to 3, wherein the premixing tube portion is formed as a venturi mixer.   The burner of a combustion apparatus according to any one of claims 1 to 4, wherein a fuel supply pipe that supplies fuel to the premixing pipe section is disposed concentrically with the premixing pipe section.   The burner of a combustion apparatus according to any one of claims 1 to 5, comprising a plurality of the premixing tube portions.   The burner of a combustion apparatus according to any one of claims 1 to 6, further comprising an ignition device that is provided in the premixed gas derivation portion and ignites in the expansion passage.   7. The burner of a combustion apparatus according to claim 1, wherein the burner is provided with an ignition device that is provided in a central portion in a radial direction of a premixing tube forming the premixing tube and ignites in the enlarged passage. A combustion apparatus comprising the burner according to any one of claims 1 to 8,
A combustion apparatus in which a top portion of the combustion cylinder has a tapered shape that is smoothly connected to an inner peripheral wall of a premixed gas outlet portion of the burner, and forms a part of the enlarged passage.   The flame holding region according to claim 9, wherein the enlarged passage reduces the flow rate of the premixed gas to the same speed as the propagation speed of the flame so that the flow velocity of the premixed gas and the propagation speed of the flame are balanced. Is formed in the enlarged passage or in the combustion chamber.

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