JP2000074333A - Cooling structure - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve a cooling performance of a cylinder having a cooling structure. SOLUTION: A plurality of protrusions 38 are provided sprinkled at an interval in a circumferential direction 40 and an axial direction 41 on an outer periphery of a combustion cylinder body 25, and further the protrusions 38 are deviated in a zigzag manner in the directions 40 and 41 of the body 25 and disposed. Cooling gas passages 39 extended obliquely at the respective protrusions 38 so as to approach an axis of the body 25 to be extended along the direction 41 and directed toward a downstream side of a cooling gas flow. Since a surface area of the body 25 is increased by the protrusions 38, a cooling effect of cooling air is improved. Since the protrusions 38 are disposed in the zigzag manner and the passages 39 are respectively provided in the protrusions 38, the cooling air is smoothly introduced into the passage 39. The air passage through the passage 39 flows along an inner periphery of the body 25 to lower a temperature of combustion as brought into contact with the inner periphery.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a cooling structure that can be suitably applied to a cylinder to which a high-temperature gas flows in contact.

[0002]

2. Description of the Related Art A typical conventional cooling structure for a cylindrical body is shown in FIG.
2 and FIG. The cooling structure for a cylindrical body shown in FIG. 12 has a configuration in which a plurality of cooling gas passages 4 are formed on the peripheral wall 3 of the cylindrical body 1 at intervals in the circumferential direction 9 and the axial direction 10. The cooling gas passage 4 communicates one surface 5 of the peripheral wall 3 in contact with the cooling gas and the other surface 6 of the peripheral wall 3 in contact with the high-temperature gas, and is located downstream in the flow direction of the cooling gas flow 7 parallel to the axial direction. Side (hereinafter referred to as the downstream side), it is inclined and extends so as to approach the other surface 6. The cooling gas flows into the hot gas side through the cooling gas passage 4 and flows downstream along the other surface 6 of the peripheral wall 3. As a result, the peripheral wall 3 is forcibly cooled, the temperature of the flow near the other surface 6 is lowered, and the amount of convection heating to the peripheral wall 3 is reduced.

[0003] In the cooling structure for a cylindrical body shown in FIG. 13, a plurality of ring-shaped projections 8 extending in the circumferential direction 9 are formed on the peripheral wall 3 of the cylindrical body 1 at intervals in the flow direction of the cooling gas flow 7. The cooling gas passage 4 is formed on the surface of the projection 8 facing the upstream side of the cooling gas flow 7 in the same manner as in FIG. This allows the cooling gas passage 4 through which the cooling gas passes.
And the forced cooling of the peripheral wall 3 is strengthened.

[0004]

In the cooling structure of the cylindrical body shown in FIG. 12, the cooling gas passage 4 is formed directly on the surface of the cylindrical body 1 where no projection is formed, so that the cooling gas is cooled. It is difficult to flow into the gas passage 4, and the length of the cooling gas passage 4 is shorter than that in the case where the projection exists. Therefore, there is a problem that the cooling effect by the cooling gas is not sufficiently exhibited. In addition, it is difficult to form the cooling gas passage 4 directly inclined on the peripheral wall 3 by machining with a drill or the like, and it is necessary to perform the machining by electric discharge machining or electrolytic machining, and there is a problem that productivity is poor.

In the cylindrical cooling structure shown in FIG. 13, the flow of the cooling gas to the downstream side is blocked by the ring-shaped projections 8 of the cylindrical body 1 on the upstream side of the cooling gas flow 7, so that the cooling gas flow It becomes difficult for the cooling gas to flow into the cooling gas passage 4 formed in the ring-shaped projection 8 on the downstream side of 7.
Therefore, there is a problem that the cooling effect by the gas is not sufficiently exhibited. Further, there is a problem that the weight of the cylindrical body increases due to the formation of the ring-shaped projections 8. Further, there is a problem that a locally high temperature portion of the cylindrical body 1 cannot be sufficiently cooled.

An object of the present invention is to provide a cooling structure having good cooling performance, capable of locally enhancing cooling, and having good manufacturability.

[0007]

SUMMARY OF THE INVENTION According to the present invention, a high-temperature gas flows in contact with one of an inner peripheral surface and an outer peripheral surface of a cylindrical body, and a cooling gas flows along one of the other surfaces of the cylindrical body. In the cooling structure, a plurality of projections are provided on the other surface of the cylindrical body at intervals in the circumferential direction and the axial direction, and each projection is provided in the circumferential direction and the axial direction of the cylindrical body. In each projection, a cooling gas passage extending along the axial direction of the cylindrical body and extending obliquely so as to approach the axis of the cylindrical body toward the downstream side of the cooling gas flow is provided at each projection. A cooling structure characterized by being formed.

According to the present invention, since a plurality of projections are provided on the surface of the cylinder body to which the cooling gas is supplied at intervals in the circumferential direction and the axial direction, the surface area of the cylinder body is reduced. It can increase the cooling effect. In addition, since the protrusions are arranged so as to be shifted in the circumferential direction and the axial direction of the cylindrical body, the cooling gas flow flowing in the axial direction of the cylindrical body smoothly flows downstream in the flow direction, and flows toward the downstream protrusion. The flowing cooling gas flow is not obstructed by the upstream projection. Thereby, the cooling effect by the projections can be enhanced. In addition, a cooling gas passage extending along the axial direction of the cylindrical body and extending obliquely toward the axis of the cylindrical body toward the downstream side of the cooling gas flow is formed in each projection, so that cooling is performed. The length of the gas passage can be made longer than when there is no protrusion. by this,
The forced convection cooling effect of the cooling gas on the cylinder can be enhanced. Further, since the cooling gas is blown from the cooling gas passage obliquely to the surface of the cylindrical body that comes into contact with the high-temperature gas, the cooling gas flows along the high-temperature gas contact surface. As a result, the temperature of the high-temperature gas flow near the high-temperature gas contact surface decreases, and the amount of convection heating to the cylindrical body is reduced. As a result,
The cooling effect of the cooling gas on the cylindrical body can be enhanced.

The projection of the present invention faces the upstream side of the cooling gas flow, and is inclined radially outward toward the downstream side of the cooling gas flow. A second inclined surface connected to a downstream end of the cooling gas flow and inclined so as to be radially inward toward the downstream side of the cooling gas flow, wherein the cooling gas passage is formed on the first inclined surface; It is characterized by being provided facing.

According to the present invention, the first inclined surface of the projection faces the upstream side of the cooling gas flow, and is inclined so as to be radially outward toward the downstream side of the cooling gas flow. Since the gas passage is provided facing the first inclined surface,
After colliding with the first inclined surface, the cooling gas smoothly flows into the cooling gas passage. Thereby, the cooling effect of the cooling gas on the cylindrical body can be enhanced.

The first inclined surface 47 of the present invention is a flat surface, and the axis 39a of the cooling gas passage is the first inclined surface 47.
Characterized by being perpendicular to.

According to the present invention, since the first inclined surface is a plane and the axis of the cooling gas passage is perpendicular to the first inclined surface, the cooling gas passage can be easily formed by machining such as a drill. Can be. Thereby, the manufacturability of the cooling gas passage is improved.

[0013] Further, the present invention is characterized in that projections are provided at a higher temperature portion of the cylinder body at a higher distribution density per unit area than at the remaining lower temperature portions.

According to the present invention, since the projections are provided at a higher temperature portion of the cylinder body at a higher density than at the remaining portions, the temperature rise is effectively exerted even on a cylinder having a locally high heat portion. Can be suppressed. Thereby, the useful life of the cylindrical body can be extended.

Further, the cooling gas passage of the present invention is characterized in that the cooling gas passage has an axis crossing an imaginary plane including the axis of the cylindrical body.

According to the present invention, since the cooling gas passage has an axis that intersects with an imaginary plane including the axis of the cylindrical body, even if the high-temperature gas flowing through the cylindrical body is a swirl flow, If the axes are crossed along the turning direction,
The problem that the cooling gas flow blown from the cooling gas passage and flowing along the cylinder body is disturbed by the swirling flow can be prevented.

The present invention also provides a nozzle body having a main nozzle hole and a pilot nozzle hole for ejecting a fuel gas, and an inner cylinder body provided around the nozzle body and defining an internal flow path. An introduction flow path connected to the inner flow path is defined between the body and the inner cylinder, and a gas introduction hole is formed in the peripheral wall of the inner cylinder so as to face the main nozzle hole and sandwich the introduction flow path. Inner cylinder, and an outer cylinder that is provided at an interval radially outward of the inner cylinder and defines an outer flow path, and a combustion cylinder that is provided at an interval radially outward of the outer cylinder. A plurality of projections are provided on the outer peripheral surface of the combustion cylinder main body at intervals in the circumferential direction and the axial direction, and the projections are further displaced in the circumferential direction and the axial direction of the combustion cylinder main body. , Each protrusion extends in the axial direction of the combustion cylinder main body, and goes downstream of the cooling gas flow A burner apparatus which comprises a combustion tube that brought by extending obliquely so as to approach the axis of the combustion liner body cooling gas passage is formed.

According to the present invention, the burner device is provided with a combustion cylinder, and the combustion cylinder has a cooling structure including a plurality of projections arranged on the combustion cylinder main body and a cooling gas passage formed in the projection. Since it is provided, even if combustion is performed under a high load, it is possible to prevent thermal damage to the combustion cylinder, and it is possible to increase the useful life of the entire burner device.

[0019]

FIG. 1 is a perspective view showing a simplified structure of a main part of a combustion cylinder having a cooling structure according to an embodiment of the present invention. FIG. 2 is a perspective view showing the combustion cylinder shown in FIG. FIG. 3 is a cross-sectional view illustrating a simplified configuration of a main part of a burner device provided, and FIG. 3 is a cross-sectional view illustrating a simplified overall configuration of the burner device illustrated in FIG. 2. The burner device 11 includes a diffuser 12, and a cylindrical holding case 14 is attached to the diffuser 12 via a flange 15. A combustion case 16 is provided in the holding case 14,
A combustion cylinder 24 is provided in the combustion case 16. One end of the combustion case 16 is attached to the diffuser 12. An air passage 18 is formed in the diffuser 12,
Combustion air (hereinafter abbreviated as air) is supplied to one end of the combustion case 16 through the air passage 18.

A mounting support block 26 is mounted on the diffuser 12, and one end of an outer gas supply pipe 28 is mounted on the mounting support block 26. A nozzle body 30 is attached to the other end of the outer gas supply pipe 28. Nozzle body 3
0, a space 32 is formed inside, and a partition sleeve 34 is mounted through the inner space 32 in the axial direction. The inner space 32 is partitioned by a partition sleeve 34 into an inner first space 32a and an outer second space 32b. The other end of the outer gas supply pipe 28 communicates with the second space 32b of the nozzle body 30. An inner gas supply pipe 36 is provided inside the outer gas supply pipe 28, and one end of the inner gas supply pipe 36 is attached to the mounting support block 26, and the other end is attached to the nozzle body 30. The inner gas supply pipe 36 is
The nozzle body 30 communicates with the first space 32a. Gas supply means (not shown) for supplying fuel gas is connected to the inner gas supply pipe 36 and the outer gas supply pipe 28. As the fuel gas, for example, city gas can be suitably used.

The inner cylindrical body 20 is mounted outside the nozzle body 30. The inner cylindrical body 20 is a substantially cylindrical member made of stainless steel, and its internal space defines an inner flow path 55. At one end of the inner cylindrical body 20, an inner projection 44 that protrudes inward in the radial direction with an interval in the circumferential direction is integrally provided on the inner peripheral surface of the peripheral wall. The inner cylindrical body 20 is coaxially supported by the nozzle body 30 via a plurality of (eight in the present embodiment) inner projections 44.

The nozzle body 30 is mounted such that the tip is directed to the downstream side in the fuel gas flow direction (hereinafter referred to as the downstream side). An inner flow path 55 is provided between the inner cylinder 20 and the nozzle body 30.
An introduction flow path (not shown) is defined. The air from the air passage 18 passes through the introduction passage and passes through the inner cylinder 20.
To the inner flow path 55. An inner swirler 4 having swirling vanes is provided between the tip of the nozzle body 30 and the inner cylindrical body 20.
6 are provided. Therefore, the air flowing through the introduction flow path is swirled by the inner swirler 46 and flows downstream in the inner flow path 55 in a swirling flow state.

An outer cylindrical body 22 is mounted radially outward of the inner cylindrical body 20 at an interval. The outer cylinder 22 is a substantially cylindrical member made of stainless steel, and defines an outer channel 57 between the outer cylinder 22 and the inner cylinder 20. An outer swirler 50 is integrally provided on the inner peripheral surface at one end of the outer cylinder 22, and the outer cylinder 22 is coaxially mounted on the outer peripheral surface of the inner cylinder 20 via the outer swirler 50. The outer swirler 50 is composed of swirling blades like the inner swirler 46. Since the outer swirler 50 is provided in this manner, the outer channel 57
Is turned into a swirling flow by the action of the outer swirler 50, and flows downstream in the external flow path 57 in a swirling flow state. An annular flange 52 protruding outward in the radial direction is integrally provided at one end of the outer cylinder 22, and one end of the combustion cylinder main body 25 of the combustion cylinder 24 is attached to a tip of the annular flange 52. I have. The combustion cylinder main body 25 is disposed coaxially with the inner cylinder 20 and the outer cylinder 22, and a substantially annular space 61 exists between the combustion cylinder 16 and the combustion case 16.

A plurality of (eight in the present embodiment) pilot nozzle holes 56 are formed at the tip end of the nozzle body 30 at intervals in the circumferential direction.
Is communicated with the first space 32 a of the nozzle body 30. A plurality (eight in the present embodiment) of main nozzle holes 58 extending in a substantially radial direction are formed at an intermediate portion of the nozzle body 30 at intervals in a circumferential direction. These main nozzle holes 58
The nozzle body 30 communicates with the second space 32b. Further, corresponding to each of the main nozzle holes 58, a gas introduction hole 60 is formed in the inclined portion of the inner projection 44 of the inner cylinder body 20 so as to penetrate the peripheral wall of the inner cylinder body 20, and the main nozzle hole 58 and the gas introduction hole are formed. Hole 60
Are arranged so as to face each other with the introduction channel interposed therebetween.

The axes of the main nozzle hole 58 and the gas introduction hole 60 are present in a virtual plane including the axis of the inner cylinder 20, and are present on a common straight line in the virtual plane. It is desirable that the inner diameter of the gas introduction hole 60 is set substantially equal to or larger than the inner diameter of the main nozzle hole 58. This makes it easier for the fuel gas ejected from the main nozzle hole 58 to flow into the gas introduction hole 60.

With this configuration, the fuel gas supplied through the internal gas supply pipe 36 is supplied to the nozzle 30
Of the pilot nozzle hole 56
Is squirted through. The inner cylindrical body 20 defines an inner flow path 55, and one end of the inner flow path 55, that is, the upstream side, extends between the nozzle body 30 and the inner cylindrical body 20 to form the introduction flow path. Part of the air flowing through the air flow path 18 passes through the introduction flow path and flows into the downstream inner flow path 55. The fuel gas ejected from the pilot nozzle hole 56 is ejected by the inner swirler 46 toward an airflow forming a swirling flow, and is substantially uniformly mixed by the action of the swirling flow to become a lean mixed gas.

The fuel gas supplied through the external gas supply pipe 28 is supplied to the first space 32b of the nozzle body 30 and is ejected from the main nozzle hole 58. Part of the air flowing through the air flow path 18 flows into the outer flow path 57 via the outer swirler 50 and flows downstream. The fuel gas ejected from the main nozzle hole 58 is ejected into the inner passage 55 through the introduction passage as described later or into the outer passage 57 through the gas introduction hole 60 across the introduction passage. Is done. The fuel gas ejected to the outer flow path 57 is ejected by the outer swirler 50 toward the airflow forming the swirling flow, and is uniformly mixed by the action of the swirling flow to become a lean mixed gas.

The remainder of the air flowing through the air passage 18 flows through a space 61 between the combustion tube 24 and the combustion case 16. The combustion cylinder main body 25 of the combustion cylinder 24 has a structure shown in FIG.
As shown in FIG. 3, a plurality of projections 38 are provided at intervals in the circumferential direction 40 and the axial direction 41, and a cooling gas passage 39 is formed in each projection 38. The projection 38 and the cooling gas passage 39 constitute a first cooling structure 65. The air flowing through the space 61 passes through each cooling gas passage 39 and is introduced into the combustion cylinder main body 25. The combustion cylinder main body 25 is provided with a dilution hole 63, and the space 6
1 flows through the dilution hole 63 and is introduced into the combustion cylinder 24. The introduced air lowers the temperature of the combustion gas so as not to abnormally increase, and burns the unburned fuel gas. Therefore, the dilution hole 63 is also called a combustion air hole.

In this embodiment, the gas concentration of the mixed gas flowing through the inner passage 55 is set to be higher than the gas concentration of the mixed gas flowing through the outer passage 57. In connection with this, an ignition plug 68 for igniting the mixed gas is provided to protrude into the inner channel 55. The base of the spark plug 68 is attached to the holding case 14, and the tip of the spark plug 68 projects through the combustion case 16, the combustion cylinder 24, the outer cylinder 22, and the inner cylinder 20 into the inner channel 55. The tip ignition portion of the ignition plug 68 generates a spark toward the mixed gas flowing through the inner flow path 55, and the mixed gas in the inner flow path 55 is ignited and burned by the spark. Furthermore, the inner channel 5
The flame of the combustion gas generated in 5 is propagated to the mixed gas flowing through the outer flow path 57, and the mixed gas in the outer flow path 57 is burned by the propagation of the flame.

The gap between the nozzle body 30 and the inner cylinder 20 that defines the introduction flow path is set smaller than the gap between the inner cylinder 20 and the outer cylinder 22. Therefore, the air flowing into the inner passage 55 is restricted in the gap. However, since the cross-sectional area of the inner flow path has increased greatly on the downstream side, the flow velocity of the airflow flowing through the inner flow path 55 is relatively slow. On the other hand, the flow velocity of the airflow flowing through the outer flow path 57 is relatively high.

At the end of the combustion cylinder main body 25 of the combustion cylinder 24, a cylindrical lead-out cylinder 70 is further provided. The lead-out cylinder 70 extends to the downstream side, and its tip is tapered. The leading end of the lead-out cylinder 70 is supported by a support plate 74 attached to the leading end of the combustion case 16. The combustion gas guided from the combustion cylinder 24 to one end of the discharge cylinder 70 passes through the discharge cylinder 70, is collected at the tapered tip, and flows downstream. A gas turbine 72 is disposed on the tip end side of the lead-out tube 70, and the combustion gas burned in the combustion tube 24 is supplied to the gas turbine 72 through the lead-out tube 70. A plurality of, for example, six such burner devices 11 are arranged at intervals in the circumferential direction with respect to the blades of the gas turbine 72. The gas turbine 72 is driven to rotate by the combustion gas from each burner device 11.

In such a burner device 11, fuel is ejected from the pilot nozzle hole 56 at the time of ignition, mixed with air introduced from the introduction flow passage to generate a mixed gas in the inner flow passage 55, and is generated by the ignition plug 68. Ignite the gas mixture. After ignition, the fuel gas is ejected from the main nozzle hole 58 so as to flow into the outer flow path 57, mixed with the air flowing through the outer flow path 57 to generate a mixed gas, and the flame from the inner flow path 55 causes the outer flow path 57. Is burned. When the mixed gas starts burning in the outer passage 57, the supply of the fuel gas supplied to the pilot nozzle hole 56 is stopped.

In such a combustion state, if the supply amount of the fuel gas supplied to the main nozzle hole 58 is reduced, the ejection speed of the fuel gas ejected from the main nozzle hole 58 is reduced, and the air flow flowing through the introduction flow path is reduced. , The fuel gas flows toward the inner passage 55 together with the air flow. Thus, even when the fuel gas supply amount is small and the load is low, the mixed gas is stably burned in the inner flow passage 55 having a small air amount.

On the other hand, when the supply amount of the fuel gas supplied to the main nozzle hole 58 is increased, the ejection speed of the fuel gas ejected from the main nozzle hole 58 is increased, and the fuel gas is supplied to the air flowing through the introduction passage. It overcomes the action of the flow and is introduced into the gas introduction hole 60 across the introduction flow path. The fuel gas introduced into the gas introduction hole 60 is jetted into the outer flow path 57 and mixed with air flowing through the outer flow path to generate a mixed gas. Thus, when the load of the fuel gas is large and the load is high, the mixed gas is stably burned in the outer passage having a large amount of air.

As described above, the combustion cylinder main body 2 of the combustion cylinder 24
5, a first cooling structure 65 is formed, and
A plurality of projections 38 are provided at intervals in the 0 and axial directions 41, and a cooling gas passage 39 is formed in each projection 38. The projections 38 are arranged in a staggered manner in the circumferential direction 40 and the axial direction 41 of the combustion cylinder main body 25 as shown in a circumferential development view of FIG. Each projection 38 has a chevron shape as shown in FIGS.
It has first and second inclined surfaces 47 and 48 connected to the flow direction 43 of the cooling air flow as the cooling gas flow. The flow direction 43 of the cooling air flow is parallel to the axis 25 a of the combustion cylinder main body 25.

The first inclined surface 47 is a flat surface, faces the upstream side (hereinafter referred to as the upstream side) 43 in the cooling air flow direction, and becomes radially outward toward the downstream side of the cooling air flow. Incline. The second inclined surface 48 is a plane,
Connecting to the downstream end of the cooling airflow of the first inclined surface 47,
It inclines so that it may become radially inward toward the downstream of the cooling air flow. The cooling gas passage 39 is provided with each projection 38.
Of the combustion cylinder main body 25 extends from the first inclined plane 47 along the axis 25a of the combustion cylinder main body 25 and toward the downstream side of the cooling air flow.
It extends obliquely so as to approach 5a. The cooling gas passage 39 communicates the first inclined surface 47 of the projection 38 with the inner peripheral surface of the combustion cylinder main body 25. Furthermore, the axis 3 of the cooling gas passage 39
9a is an axis 25a of the combustion cylinder main body 25 as shown in FIG.
Are parallel to the virtual plane 49 including.

The dimensions of the projection 38 and the cooling gas passage 39 in FIGS. 5 and 6 are set according to the specifications of the burner device 11, for example, as shown in Table 1. Cooling gas passage 3
It is preferable that the angle β between the nine axis 39a and the first inclined surface 47 is set to approximately 90 degrees. The reason will be described later. The cooling air is supplied to the first
It collides with the inclined surface 47, flows into the cooling gas passage 39 opened on the first inclined surface 47, and is introduced into the combustion cylinder main body 25.

[0038]

[Table 1]

As described above, since the plurality of projections 38 are provided on the combustion cylinder main body 25 in a dotted manner, the surface area of the cooling surface of the combustion cylinder main body 25 increases, and the cooling effect by the cooling air can be enhanced. . Since the projections 38 are arranged in a staggered manner in the circumferential direction 40 and the axial direction 41 of the combustion cylinder main body 25, the cooling air flow smoothly flows from the upstream side to the downstream side, and the upstream side projections 38 The cooling air flow toward the downstream protrusion 38 is not hindered. Further, since the cooling gas passage 39 is opened on the first inclined surface 47 facing the upstream side of the cooling air flow, the cooling air flows through the cooling gas passage 3.
9 smoothly flows.

Further, since the cooling gas passages 39 which extend obliquely are formed in each projection 38, the length of the cooling gas passage can be made longer than when there is no projection. Thereby, the forced convection cooling effect of the cooling air on the combustion cylinder 24 can be enhanced. Since cooling air is blown from the cooling gas passage 39 inclined into the combustion cylinder main body 25, the introduced cooling air forms a layered air layer flowing along the inner peripheral surface of the combustion cylinder main body 25. Thereby, the temperature of the combustion gas near the inner peripheral surface of the combustion cylinder main body 25 decreases, and the amount of convection heating to the combustion cylinder main body 25 decreases. As a result, the cooling effect of the cooling air on the combustion cylinder 24 can be enhanced. As described above, since the first cooling structure 65 can uniformly cool the entire outer peripheral surface of the combustion cylinder main body 25, it is possible to prevent thermal damage to the combustion cylinder 24 even when combustion is performed under a high load. The useful life of the entire burner device 11 including the combustion tube 24 can be extended.

FIG. 8 is a perspective view for explaining a method of manufacturing the projection and the cooling gas passage. The projection 38 and the cooling gas passage 39 are manufactured as follows. (1) A ring-shaped projection 7 extending in the circumferential direction on the outer peripheral surface of the combustion cylinder main body 25
6 is welded. (2) The ring-shaped projection 76 is divided in the circumferential direction by cutting. The divided portion is a portion shown by oblique lines in FIG.
Are arranged so as to be staggered in the circumferential direction 40 and the axial direction 41. (3) The cooling gas passage 39 is formed in the first inclined surface 47 of each projection 38 by drilling.

Since the workability of the drilling process is best when the drill is set perpendicular to the processing surface, the cooling gas passage 39 is formed so that its axis 39a is substantially perpendicular to the first inclined surface 47. Is done. It is for this reason that the angle β is set to approximately 90 degrees.

Thus, the projections 38 and the cooling gas passages 39 can be efficiently formed with good dimensional accuracy. Further, since the ring-shaped projection 76 is cut to form the projection 38, the weight of the combustion cylinder 24 can be reduced. Therefore, the manufacturability of the first cooling structure 65 can be improved.

FIG. 9 is a simplified perspective view showing a cooling structure near the dilution hole of the combustion cylinder main body. As described above, the air introduced from the dilution hole 63 burns the unburned fuel gas when the fuel gas is present, so that the peripheral wall of the combustion cylinder main body 25 downstream of the dilution hole 63 has a higher temperature than other parts. It may be. For this reason, the cooling structure on the downstream side of the dilution hole 63 is configured such that the distribution density per unit area of the projection 38 is larger than that of the remaining low temperature portion. Such a high-density cooling structure is called a second cooling structure 66. Second cooling structure 66 provided downstream of dilution hole 63
, Each of the projections 38 is arranged in a fan shape so as to be tapered toward the downstream side corresponding to the high temperature region. Second
The manufacturing of the cooling structure 66 is performed in the same manner as the first cooling structure 65. As described above, since the second cooling structure 66 can enhance the cooling of the local high-temperature portion, it is possible to prevent local thermal damage to the combustion cylinder main body 25 even when combustion is performed under a high load. it can. Thereby, the useful life of the entire burner device 11 including the combustion tube 24 can be improved. Other high-temperature portions in the combustion cylinder main body 25 include the vicinity of the ignition plug 68 and the like.
Can be provided.

In this embodiment, the axis 39a of the cooling gas passage 39 is formed parallel to the virtual plane 49 including the axis 24a of the combustion cylinder main body 25 as described above. However, as shown in FIG. 10, the axis 39a of the cooling gas passage 39 is aligned with the virtual plane 4 including the axis 25a of the combustion cylinder main body 25.
9 may be formed so as to intersect. This crossing angle is preferably selected so that the cooling air blown from the cooling gas passage 39 follows the turning direction of the combustion gas in the combustion cylinder main body 25. Accordingly, it is possible to avoid a problem that the flow of the cooling air along the inner peripheral surface of the combustion cylinder main body 25 is disturbed by the swirling flow of the combustion gas.

In this embodiment, the projection 38 has first and second inclined surfaces 47 and 48, and the cooling gas passage 39 is provided with the first and second inclined surfaces 47 and 48.
Although it is configured to be provided facing the inclined surface 47, the present invention is not limited to this configuration, and the shape of the projection 38 may be formed in another shape according to the specification of the burner device 11. The position of the gas passage may be formed at another position. Further, the first inclined surface need not be a flat surface, and the axis of the cooling gas passage 39 may not be perpendicular to the first inclined surface 47. Further, when there is no local high-temperature portion in the combustion cylinder main body 25, the second cooling structure 66 in which the distribution density of the projections 38 is increased may not be provided.

FIG. 11 is a simplified perspective view showing the structure of a combustion cylinder having a cooling structure according to another embodiment of the present invention. The combustion cylinder 77 of the present embodiment includes a combustion cylinder main body 82.
A first cooling structure 80 provided downstream of the Bunsen burner 78, a plurality of combustion air holes 79 provided in an intermediate region of the first cooling structure 80, and a first cooling structure 80 provided downstream of each combustion air hole 79. 2 cooling structure 81. First cooling structure 8
0 is the projection 3 as in the first cooling structure 65 shown in FIG.
8 are arranged at intervals in the circumferential direction and axial direction, and are arranged in a staggered manner. Each projection 38 has
A cooling gas passage 39 is formed. For example, six combustion air holes 79 are formed at equal intervals in the circumferential direction. The second cooling structure 81 is configured by arranging the protrusions 38 in, for example, ten fan-shapes at high density. The combustion gas in the combustion cylinder main body 82 is guided to the gas turbine 72 via the outlet cylinder 70. Since the combustion cylinder 77 is configured as described above, even if the unburned gas burns downstream of the combustion air hole 79 and a local temperature rise occurs in the combustion cylinder main body 82, the second cooling structure 81
Can be cooled effectively. Further, the combustion cylinder main body 82 can be uniformly cooled by the first cooling structure 80. Thus, the useful life of the combustion cylinder 77 can be extended.

As described above, the cylinder provided with the cooling structure of the present invention can be suitably used as a combustion cylinder of a burner device. However, the application of the present invention is not limited to the combustion cylinder of the burner device, and all cylinders that come into contact with the high-temperature gas, for example, the cylinder in which the high-temperature gas flows in contact with either the inner peripheral surface or the outer peripheral surface. It can be suitably applied to the body.

(Example 1) In order to confirm the cooling performance of a cylinder having the first cooling structure of the present invention, FIG.
The combustion cylinder 24 having the first cooling structure 65 shown in FIG. 1 was attached to the burner device 11 shown in FIG. 3 to measure the temperature of the combustion cylinder main body 25 during combustion. Temperature measurement was performed at a plurality of locations. The dimensions of each member of the burner device 11 were as shown in Table 2, and the dimensions of the projection 38 and the cooling gas passage 39 were as shown in Table 1 above. Axis 39 of cooling gas passage 39
The angle β formed between a and the first inclined surface 47 was 90 degrees.
The details of 800 protrusions formed on the combustion cylinder main body 25 were 90 in the circumferential direction (however, the portion provided with the spark plug 68 was 80) and 9 in the axial direction.

On the other hand, as a comparative example, a combustion cylinder having a first cooling structure in which a cooling gas passage is directly formed without forming a projection on the combustion cylinder main body is mounted on the same burner device 11 as in the embodiment, and the combustion cylinder during combustion is operated. The temperature of the combustion cylinder body was measured. Other configurations such as the number and arrangement of the cooling gas passages were exactly the same as those of the embodiment. Combustion conditions are shown in Table 3 for both Examples and Comparative Examples.
It was as follows.

[0051]

[Table 2]

[0052]

[Table 3]

As a result, the average temperature of the combustion gas was 950 ° C.
The temperature of the combustion cylinder main body 25 in the embodiment is the maximum temperature: 6
28 ° C, average temperature: 520 ° C. On the contrary,
Under the same conditions, the temperature of the combustion cylinder body of the comparative example was the highest temperature: 73
6 ° C, average temperature: 625 ° C. Therefore, it can be seen that the cooling performance of the combustion cylinder provided with the first cooling structure 65 of the present invention is better than that of the comparative example.

(Embodiment 2) In order to confirm the local cooling performance of the cylindrical body having the second cooling structure of the present invention, the burner device 11 shown in Embodiment 1 is used as an embodiment and the second cooling structure 66 shown in FIG. The temperature of the combustion cylinder main body 25 during combustion was measured by mounting the combustion cylinder 24 having Temperature measurement was performed at a plurality of locations. The second cooling structure 66 is provided downstream of each dilution hole 63. The second cooling structure 66 is configured by arranging ten protrusions 38 in a fan shape at a high density. On the other hand, as a comparative example, a combustion cylinder having a second cooling structure in which a cooling gas passage is directly perforated without forming a projection is mounted on the burner device 11 shown in the first embodiment, and the temperature of the combustion cylinder body during combustion is increased. A measurement was made. Other configurations such as the number, arrangement and distribution density of the cooling gas passages were the same as those of the embodiment. The combustion conditions were as shown in Table 3 for both the example and the comparative example.

As a result, the average temperature of the combustion gas was 950 ° C.
In the embodiment, the temperature downstream of the dilution hole 63 is 5
68 ° C. On the other hand, the temperature downstream of the dilution hole 63 in the comparative example was 775 ° C. under the same conditions. Therefore, it can be seen that the local cooling performance of the combustion cylinder provided with the second cooling structure 66 of the present invention is superior to the comparative example.

[0056]

According to the first aspect of the present invention, a plurality of projections are provided on the surface of the cylindrical body to which the cooling gas is supplied at intervals in the circumferential direction and the axial direction. In addition, the surface area of the cylindrical body is increased, and the cooling effect can be enhanced. In addition, since the protrusions are arranged so as to be shifted in the circumferential direction and the axial direction of the cylindrical body, the cooling gas flow flowing in the axial direction of the cylindrical body smoothly flows downstream in the flow direction, and flows toward the downstream protrusion. The flowing cooling gas flow is not obstructed by the upstream projection. Thereby, the cooling effect by the projections can be enhanced. Also, on each projection,
Since the cooling gas passage extending along the axial direction of the cylindrical body and extending obliquely toward the axis of the cylindrical body toward the downstream side of the cooling gas flow is formed, the length of the cooling gas passage is reduced. It can be longer than when there is no projection. Thereby, the forced convection cooling effect of the cooling gas on the cylindrical body can be enhanced. Further, since the cooling gas is blown from the cooling gas passage obliquely to the surface of the cylindrical body that comes into contact with the high-temperature gas, the cooling gas flows along the high-temperature gas contact surface. As a result, the temperature of the high-temperature gas flow near the high-temperature gas contact surface decreases, and the amount of convection heating to the cylindrical body is reduced. As a result, the cooling effect of the cooling gas on the cylinder can be enhanced.

According to the second aspect of the present invention, the first inclined surface of the projection faces the upstream side of the cooling gas flow and is inclined so as to be radially outward toward the downstream side of the cooling gas flow. Further, since the cooling gas passage is provided facing the first inclined surface, the cooling gas smoothly flows into the cooling gas passage after colliding with the first inclined surface. Thereby, the cooling effect of the cooling gas on the cylindrical body can be enhanced.

According to the third aspect of the present invention, since the first inclined surface is a plane and the axis of the cooling gas passage is perpendicular to the first inclined surface, the cooling gas passage is formed by machining such as a drill. It can be easily formed. by this,
The productivity of the cooling gas passage is improved.

According to the fourth aspect of the present invention, since the projections are provided at a higher temperature portion of the cylinder main body at a higher density than the remaining portions, the projections are provided with respect to the cylinder having a locally high heat portion. Can also effectively suppress a rise in temperature. Thereby, the useful life of the cylindrical body can be extended.

According to the fifth aspect of the present invention, since the cooling gas passage has an axis that intersects with an imaginary plane including the axis of the cylindrical body, the high-temperature gas flowing through the cylindrical body has a swirling flow. However, if the axes intersect with each other along the swirling direction of the swirling flow, it is possible to prevent the cooling gas flow blown from the cooling gas passage and flowing along the cylindrical body from being disturbed by the swirling flow. .

According to the sixth aspect of the present invention, the burner device is provided with a combustion cylinder, and the combustion cylinder includes a plurality of projections disposed on the combustion cylinder main body, and a cooling gas passage formed in the projection. Therefore, even if combustion is performed under a high load, heat damage to the combustion cylinder can be prevented, and the useful life of the entire burner device can be increased.

[Brief description of the drawings]

FIG. 1 is a simplified perspective view showing a configuration of a main part of a combustion cylinder having a cooling structure according to an embodiment of the present invention.

FIG. 2 is a simplified cross-sectional view showing a configuration of a main part of a burner device including the combustion cylinder shown in FIG.

FIG. 3 is a simplified cross-sectional view showing the entire configuration of the burner device shown in FIG. 2;

FIG. 4 is a development in a circumferential direction as viewed from the outer periphery of a combustion cylinder.

FIG. 5 is a cross-sectional view taken along the line VV of FIG. 1;

FIG. 6 is a side view as viewed from VI-VI in FIG. 1;

FIG. 7 is a plan view showing a relationship between an axis of a cooling gas passage and an axis of a combustion cylinder main body.

FIG. 8 is a perspective view for explaining a method of manufacturing a projection and a cooling gas passage.

FIG. 9 is a simplified perspective view showing a cooling structure near a dilution hole of a combustion cylinder main body.

FIG. 10 is a plan view showing another relationship between the axis of the cooling gas passage and the axis of the combustion cylinder main body.

FIG. 11 is a simplified perspective view showing a configuration of a combustion cylinder having a cooling structure according to another embodiment of the present invention.

FIG. 12 is a simplified perspective view showing the configuration of a conventional typical cooling structure for a cylindrical body.

FIG. 13 is a simplified perspective view showing the configuration of another conventional cooling structure for a cylindrical body.

[Description of Signs] 11 Burner device 20 Inner cylinder 22 Outer cylinder 24 Combustion cylinder 25 Combustion cylinder main body 30 Nozzle body 38 Projection 39 Cooling gas passage 58 Main nozzle hole 60 Gas introduction hole 63 Dilution hole 65 First cooling structure 66 First 2 cooling structure 68 Spark plug 70 Outer cylinder

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Kazuo Shimohira 7-44-1 Jindaiji Higashicho, Chofu City, Tokyo Inside the Aerospace Research Institute of Science and Technology Agency (72) Inventor Tsutomu Wakabayashi 4-chome Hiranocho, Chuo-ku, Osaka-shi, Osaka No. 1-2 in Osaka Gas Co., Ltd. (72) Koji Moriya Inventor Koji Morino 4-1-2 in Hirano-cho, Chuo-ku, Osaka-shi, Osaka (72) Inventor Yuji Nakamura Hirano-cho, Chuo-ku, Osaka-shi, Osaka 4-chome 1-2 F-term in Osaka Gas Co., Ltd. (reference) 3K017 AA07 AA10 AB05 AB07 AD03 AD10 AD11 AD13 DF04 DF07

Claims (6)

[Claims] 1. A cooling structure in which a high-temperature gas flows in contact with one of an inner peripheral surface and an outer peripheral surface of a cylindrical main body, and a cooling gas is supplied along the other surface of the cylindrical main body. A plurality of projections are provided on the other surface of the cylindrical body at intervals in the circumferential direction and the axial direction, and the projections are further shifted in the circumferential direction and the axial direction of the cylindrical body. The projection is formed with a cooling gas passage extending along the axial direction of the cylindrical body and extending obliquely toward the axis of the cylindrical body toward the downstream side of the cooling gas flow. Cooling structure. 2. A first inclined surface facing the upstream side of the cooling gas flow and inclining so as to be radially outward toward the downstream side of the cooling gas flow, and a cooling gas on the first inclined surface. A second inclined surface connected to the downstream end of the flow and inclined so as to be radially inward toward the downstream side of the cooling gas flow, wherein the cooling gas passage faces the first inclined surface. The cooling structure according to claim 1, wherein the cooling structure is provided. 3. The cooling structure according to claim 1, wherein the first inclined surface is a flat surface, and the axis 39a of the cooling gas passage is perpendicular to the first inclined surface. 4. The high-temperature portion of the cylindrical body is provided with protrusions having a higher distribution density per unit area than the remaining low-temperature portion.
3. The cooling structure according to any one of 3. 5. The cooling structure according to claim 1, wherein the cooling gas passage has an axis that intersects an imaginary plane including an axis of the cylindrical body. 6. A nozzle body having a main nozzle hole and a pilot nozzle hole for ejecting a fuel gas, and an inner cylinder body provided surrounding the nozzle body and defining an inner flow path, wherein the nozzle body and An introduction flow path connected to the inner flow path is defined between the inner flow path and the cylindrical body, and further, a gas introduction hole is formed in the peripheral wall of the inner cylinder body so as to face the main nozzle hole and sandwich the introduction flow path. A cylindrical body, and an outer cylindrical body that is provided at an interval radially outward of the inner cylindrical body and that defines an outer flow path; and a combustion cylinder that is provided at an outer radial interval of the outer cylindrical body. A plurality of projections are provided on the outer peripheral surface of the combustion cylinder main body at intervals in the circumferential direction and the axial direction, and the projections are further displaced in the circumferential direction and the axial direction of the combustion cylinder main body; The combustion extends in the axial direction of the combustion cylinder body and goes downstream of the cooling gas flow. Burner apparatus which comprises a combustion cylinder cooling gas passage extending obliquely so as to approach the axis of the body is formed.