TW201631283A - Damping device, burner and gas turbine - Google Patents

Abstract

A damping device (60) comprises: a silencing lining (61), which may form a silencing lining resonance space (75) along the outer periphery of a combustion chamber (35) flowing with combustion gas, and a silencing damper (62) disposed on the outer periphery of the silencing lining (61) and forming a silencing damper resonance space (85) communicated with the silencing lining resonance space (75). The silencing lining (61) is formed with a damping opening (82) for communicating the silencing lining resonance space (75) and the silencing damper resonance space (85) and is connected to the silencing damper (62), and comprises: an interrupted portion (87), which is a portion interrupted by the damping opening (82) in the circumferential direction of the combustion chamber (35), and a continuous portion (88), which is a portion appearing to be continuous in the circumferential direction of the combustion chamber (35).

Description

Damping device, burner and gas turbine

The present invention relates to a vibration damping device, a burner, and a gas turbine for dampening combustion vibrations generated during combustion.

In the conventionally known burner, a vibration damping device including a sound absorbing liner and a sound absorbing damping is provided (for example, refer to Patent Document 1). In the damper device, the damper has a tubular plate portion and a lining provided on an outer peripheral side of the plate portion, and the damper damper includes a damper cover provided on an outer peripheral side of the lining and a lining. The opening of the cover. The space formed between the plate portion and the lining is separated by the first zone partition and the second zone partition, wherein a space of one third of the entire circumference of the upper portion is the first silencing damper The resonance space, and the two-thirds of the space in the lower part of the whole period is the sound lining resonance space. Moreover, the space formed between the lining and the damper cover is the second silencing damping resonance space. Further, the second silencing-damping resonance space communicates with the first silencing-damping resonance space via the opening portion, thereby achieving integral damping noise and exerting its function.

[Previous Technical Literature] [Patent Document]

[Patent Document 1] International Patent Publication No. 2010/097982

However, in the burner of Patent Document 1, the opening portion is a silencing damping for integrating the first silencing damping resonance space and the second silencing damping resonance space. The silencing lining resonance space is interrupted by the first silencing damping resonance space in the circumferential direction. When the silencing lining resonance space is interrupted in the circumferential direction, it is difficult to suppress the combustion vibration by the silencing lining in the interrupted portion. Therefore, in the case of the muffling damping, vibration can be suppressed, but on the other hand, in the case of the muffing lining, the vibration-damping performance is reduced depending on the size of the portion to be interrupted.

Accordingly, the present invention provides a vibration damping device, a burner, and a gas turbine that can maintain the performance of suppressing vibration generated by the noise reduction damping while improving the performance of vibration suppression by the sound absorbing liner. .

A vibration damping device and a vibration damping device according to the present invention are characterized in that: a sound absorbing liner is provided which forms a sound absorbing lining resonance space and a sound absorbing damping along an outer circumference of an internal flow path through which a fluid flows, and is provided in the sound absorbing sound lining a sound-absorbing damping resonance space communicating with the sound-absorbing lining resonance space; the sound-absorbing lining is formed with: damping for connecting the sound-absorbing lining resonance space to the noise-damping resonance resonance space and connecting the noise-damping damping The opening has an interruption portion which is a portion interrupted by the damping opening in a direction along the outer circumference of the internal flow path, and a continuous portion which is attached to the outer circumference of the internal flow path A continuous area in the direction.

According to this configuration, the continuous portion can be provided on the sound absorbing liner while forming the damper opening. Therefore, in the interruption portion of the silencing lining, since the silencing lining resonance space can be communicated with the silencing damping resonance space by the damper opening, the combustion vibration generated by the fluid flowing through the internal flow path can be attenuated by the damped damping. Vibration. Moreover, by the continuous portion of the silencing lining, since the silencing lining is not interrupted in the direction along the outer circumference of the internal flow path, the continuous portion of the silencing lining can be along the outer circumference of the internal flow path. A silencing lining resonance space is formed in the direction. Therefore, by the portion where the silencing lining is not interrupted, the combustion vibration generated by the fluid flowing through the internal flow path can be appropriately attenuated by the silencing lining to be damped. Due to the above characteristics, it is possible to maintain the vibration suppressing performance by the muffler damping, and at the same time, it is possible to improve the performance of suppressing vibration generated by the silencing lining. Further, the damper opening may be any shape such as a rectangle, a circle, or an ellipse, and is not particularly limited.

Further, the silencing lining is formed in a cylindrical shape in a circumferential direction along the outer circumference of the internal flow path, and is perpendicular to the circumferential direction. The intersecting axial direction is the width direction, and the above-described damping opening is preferably formed on one side in the width direction.

According to this configuration, the damping opening can be formed by being placed on one side in the width direction of the sound absorbing liner. Therefore, the interruption portion can be provided on one side in the width direction of the sound absorbing liner, and the continuous portion can be provided on the other side in the width direction of the sound absorbing liner.

Further, the silencing lining has a cylindrical shape in which a direction along the outer circumference of the internal flow path is a circumferential direction, and an axial direction perpendicular to the circumferential direction is a width direction, and the damper opening is formed in the width direction. The center is better.

According to this configuration, the damper opening can be formed at the center in the width direction of the silencing lining. Therefore, it is possible to provide an interruption portion in the center of the width direction of the sound absorbing liner, and to provide a continuous portion on both sides in the width direction of the sound absorbing liner.

Further, it is preferable that the damper opening is an opening that forms a rectangular shape.

According to this configuration, the damping opening can be easily formed by setting the damping opening to a rectangular shape.

The burner of the present invention is characterized in that it includes the above-described vibration damping device and a transition piece in which the internal flow path is formed inside.

According to this configuration, it is possible to appropriately dampen (attenuate) the combustion vibration generated by the combustion gas which is a fluid flowing inside the cylinder of the burner by the vibration damping device. That is, by connecting the silencer The damped silencing lining is arranged along the outer circumference of the burner's tail cylinder, and the combustion vibration near the flame of the burner can be damped by the sound absorbing liner and the muffling damping, and the combustion vibration can be more effectively damped (attenuated). .

A gas turbine according to the present invention includes the above-described burner and a turbine that is rotated by combustion gas generated in the burner.

According to this configuration, by using a burner that suppresses combustion vibration, the load caused by the combustion vibration can be suppressed, so that durability can be improved.

1‧‧‧ gas turbine

11‧‧‧Compressor

12‧‧‧ burner

13‧‧‧ turbine

24‧‧‧Rotor

30‧‧‧ burner housing

31‧‧‧Outer tube

32‧‧‧Inner tube

33‧‧‧Tail cylinder

34‧‧‧Engine chamber

35‧‧‧ combustion chamber

60‧‧‧Vibration device

61‧‧‧Sound lining

62‧‧‧Damping damping

71‧‧‧Porous plate

72‧‧‧ lining

72a‧‧‧Cylinder

72b‧‧‧Side plate department

73‧‧‧ Sound absorbing holes

75‧‧‧Sound lining resonance space

81‧‧‧ hood

81a‧‧‧Cylinder

81b‧‧‧Side plate department

82‧‧‧damped opening

85‧‧‧Dampening Damping Resonance Space

87‧‧‧Interrupted parts

88‧‧‧Continuous parts

Central axis of the S‧‧‧ burner

A-A‧‧‧ cut line

B-B‧‧‧ cut line

Fig. 1 is a schematic configuration diagram of a gas turbine in the first embodiment.

Fig. 2 is an enlarged view of the burner in the gas turbine of Fig. 1.

Fig. 3 is a cross-sectional view showing the vibration damping device of the first embodiment taken along the axial direction.

Fig. 4 is a cross-sectional view taken along line A-A of Fig. 3.

Fig. 5 is a cross-sectional view taken along line B-B of Fig. 3.

Fig. 6 is a developed view showing the development of the silencing lining of the first embodiment in the circumferential direction.

Fig. 7 is a graph showing the performance of the sound absorbing ability of the sound absorbing liner of the first embodiment.

Figure 8 is a development of the sound absorbing lining of the second embodiment in the circumferential direction. Figure.

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. Further, the invention is not limited by the embodiments. Further, the constituent elements in the examples to be described later include those that can be replaced by the person skilled in the art, and which can be easily substituted or substantially equivalent. In addition, the components described below can be combined as appropriate, and when the examples are plural, the embodiments can be combined.

[Example 1]

Fig. 1 is a schematic configuration diagram of a gas turbine in the first embodiment. Fig. 2 is an enlarged view of the burner in the gas turbine of Fig. 1. Fig. 3 is a cross-sectional view showing the vibration damping device of the first embodiment taken along the axial direction. Fig. 4 is a cross-sectional view taken along line A-A of Fig. 3. Fig. 5 is a cross-sectional view taken along line B-B of Fig. 3. Fig. 6 is a developed view showing the development of the silencing lining of the first embodiment in the circumferential direction. Fig. 7 is a graph showing the performance of the sound absorbing ability of the sound absorbing liner of the first embodiment.

As shown in Fig. 1, the gas turbine 1 includes a compressor 11, a combustor 12, a turbine 13, and an exhaust chamber 14, and a generator (not shown) is connected to the compressor 11 side.

The compressor 11 has an air intake port 15 for taking in air, and a plurality of stationary vanes 17 and a plurality of rotor blades 18 are alternately disposed in the compressor turbine chamber 16. The burner 12 is pressed against the compressor 11 The compressed compressed air is supplied to the fuel and ignited by the burner to be combusted. The turbine 13 is provided with a plurality of stationary vanes 21 and a plurality of rotor blades 22 alternately disposed in the turbine turbine chamber 20. The exhaust chamber 14 has an exhaust diffuser 23 that is continuous with the turbine 13 . Further, the rotor 24 is located at a central portion penetrating the compressor 11, the combustor 12, the turbine 13, and the exhaust chamber 14, and the end portion on the compressor 11 side is rotatably supported by the bearing portion 25, and The end of the one side of the exhaust chamber 14 is rotatably supported by the bearing portion 26. Further, a plurality of rotating plates are fixed to the rotor 24, and the moving blades 18 and 22 are coupled to each other, and a drive shaft of the generator (not shown) is coupled to an end portion of the compressor 11 side.

Therefore, the air taken in from the air intake port 15 of the compressor 11 is compressed by the plurality of stationary blades 21 and the plurality of moving blades 22, thereby becoming high-temperature and high-pressure compressed air, and in the burner 12, The compressed air is supplied with a predetermined fuel for combustion. Then, the high-temperature high-pressure combustion gas which is generated as the working fluid in the burner 12 is driven to rotate by the plurality of stationary blades 21 and the plurality of moving blades 22 constituting the turbine 13, and is driven to be connected. The generator of the rotor 24. On the other hand, the exhaust gas as the combustion gas after the rotation of the drive rotor 24 is released into the atmosphere by the exhaust gas diffusion pipe 23 of the exhaust chamber 14 after being converted into a static pressure.

Fig. 2 is an enlarged view of the burner of Fig. 1. The burner 12 has a burner housing 30. The combustor casing 30 includes an inner cylinder 32 disposed inside the outer cylinder 31 and a tail cylinder 33 coupled to the front end portion of the inner cylinder 32, and is inclined along the rotation axis I with respect to the rotor 24. It extends obliquely to the central axis S.

The outer cylinder 31 is locked to the turbine chamber casing 27, and the turbine casing casing 27 is formed with a turbine chamber 34 through which compressed air from the compressor 11 flows. The inner tube 32 has a base end portion supported by the outer tube 31 and disposed inside the outer tube 31 at a predetermined interval from the outer tube 31. A pilot burner 40 is disposed along the central axis S at a central portion of the inner cylinder 32. A plurality of main burners 50 are disposed around the pilot burner 40 at equal intervals around the pilot burner 40 and in parallel with the pilot burner 40. The base end of the transition piece 33 is connected to a front end of the cylindrical inner tube 32. The transition piece 33 is formed such that the smaller the sectional area of the transition piece is formed and curved, and the stationary blade 21 that faces the first stage of the turbine 13 is opened. The transition piece 33 is internally formed with a combustion chamber 35. The quake 33 is provided with a vibration damping device 60 for attenuating the combustion vibration generated in the transition piece 33.

As shown in FIGS. 3 to 5, the damper device 60 has a silencing lining 61 provided on the inner peripheral side and a silencing damper 62 provided on the outer peripheral side. The silencing lining 61 is provided to absorb the higher frequency vibrations generated by the combustion vibrations; the damper damping 62 is provided to absorb the lower frequency vibrations generated by the combustion vibrations.

The silencing lining 61 is provided along the outer circumference of the cylindrical tail cylinder 33, and the ring and the entire circumference in the circumferential direction. The silencing lining 61 includes a perforated plate 71 in which a plurality of sound absorbing holes 73 are formed, and a lining 72 provided around the perforated plate 71. The perforated plate 71 is also a part of the transition piece 33 and is formed in a cylindrical shape, and the inside thereof is the above-described combustion chamber (internal flow path) 35. The lining cover 72 is provided on the outer peripheral side of the perforated plate 71. The cylindrical cylindrical portion 72a and the pair of side plate portions 72b provided on both sides in the axial direction of the central axis S of the cylindrical portion 72a are provided so as to cover the porous plate 71. Thereby, the silencing lining resonance space 75 is formed between the perforated plate 71 and the lining cover 72 over the entire circumference, and the silencing lining resonance space 75 is blocked from the external space by the lining cover 72.

The muffler damping 62 is provided along the outer circumference of the silencing lining 61, the ring and the entire circumference in the circumferential direction. The noise reduction damper 62 includes a damper cover 81 provided around the silencing lining 61 and a damper opening 82 formed in the cylindrical portion 72a of the lining cover 72.

The damper cover 81 has a cylindrical cylindrical portion 81a provided on the outer peripheral side of the silencing lining 61, and a pair of side plate portions 81b provided on both axial sides of the central axis S of the cylindrical portion 81a. It is provided so as to cover the cylindrical portion 72a of the sound absorbing liner 61. Thereby, the muffling damping resonance space 85 is formed between the cylindrical portion 72a of the silencing lining 61 and the damper cover 81 over the entire circumference, and the muffling damping resonance space 85 is blocked from the external space by the damper cover 81.

The damper opening 82 is an opening that communicates the silencing lining resonance space 75 of the silencing lining 61 with the silencing damping resonance space 85 of the silencing damper 62. As shown in Fig. 6, the damper opening 82 is formed on one side in the width direction when the axial direction of the central axis S is the width direction with respect to the cylindrical portion 72a of the lining 72 that is developed in the circumferential direction. It has a rectangular opening.

In the silencing lining 61 in which the damper opening 82 is formed, the cylindrical portion 72a of the lining 72 is formed by opening a damping The opening 82 of the opening 82 interrupted in the circumferential direction and the continuous portion 88 continuous in the circumferential direction. Therefore, the silencing lining resonance space 75, as shown in Fig. 4, is formed over the entire circumference in the continuous portion 88, and on the other hand, as shown in Fig. 5, in the interruption portion 87, it is the circumference. The direction is interrupted. Further, the continuous portion 88 is provided on one side in the width direction of the lining cover 72, and the interruption portion 87 is provided on the other side in the width direction of the lining cover 72.

In the vibration damping device 60 formed as described above, when combustion vibration is generated in the combustion chamber 35 due to combustion of the fuel, the combustion vibration is transmitted from the combustion chamber 35 to the sound absorbing resonance space via the sound absorbing hole 73 of the perforated plate 71. 75. It is transmitted to the combustion vibration in the silencing lining resonance space 75, and becomes a combustion vibration of a higher frequency, and is damped (attenuated) in the silencing lining resonance space 75.

Further, the silencing lining resonance space 75 is connected to the silencing damping resonance space 85 via the damper opening 82. Therefore, the combustion vibration generated in the combustion chamber 35 is transmitted to the silencing damping resonance space 85 via the silencing lining resonance space 75. It is transmitted to the combustion vibration in the muffler damping resonance space 85, and becomes a combustion vibration of a lower frequency, and is attenuated (attenuated) in the muffler damping resonance space 85.

Next, the vibration damping performance (sound absorbing ability) provided in the silencing lining 61 of the first embodiment will be described with reference to Fig. 7. In the graph of Fig. 7, the vertical axis is the conventional ratio (old ratio) of the sound absorbing ability of the sound absorbing liner 61, and the horizontal axis thereof is the aspect ratio (L/θ) of the damper opening 82. The sound absorbing ability of the silencer lining 61 is achieved by using the established calculation hand. The method is parsed and exported. Here, the conventional (old) silencing lining has a damping opening 82 formed in the entire width of the cylindrical portion 72a of the lining cover 72. At this time, the damper opening 82 of the first embodiment has the same area as the opening area of the conventional damper opening. Further, the aspect ratio of the damper opening 82 is represented by L/θ when the length in the width direction of the damper opening 82 is L and the length in the circumferential direction of the damper opening 82 is θ.

Here, the sound absorbing ability of the sound absorbing liner 61 is analyzed through a plurality of sound patterns. The acoustic mode is expressed by the Nodal Diameter (ND), and the number of pitch diameters indicates the number of sine waves generated in the circumferential direction of the combustion chamber 35. In other words, 1ND is an acoustic mode when one sine wave is generated in the circumferential direction of the combustion chamber 35, and similarly, 2 to 8 ND is when the sine wave is generated in the circumferential direction of the combustion chamber 35 by 2 to 8 Sound mode. Further, the sound absorbing ability of the silencing lining 61 is a sinusoidal wave generated along the circumferential direction of the combustion chamber 35, and the phase difference is set to a predetermined phase amount, and is analyzed while spanning 360 degrees.

As shown in Fig. 7, the above analysis results confirmed that the sound absorbing ability of the silencing lining 61 was in the forward side as compared with the conventional one. That is to say, since the opening area of the damper opening 82 is the same as the opening area of the conventional damper opening, it can be confirmed that the vibration damping performance by the damper damping 62 is maintained one side while being lifted The vibration damping performance of the sound absorbing liner 61.

As described above, according to Embodiment 1, the continuous portion 88 can be disposed on the sound absorbing liner 61 while forming the damper opening 82. Therefore, at the interruption portion 87 of the sound absorbing liner 61, since the damping opening 82 can be used Since the silencing lining resonance space 75 is connected to the muffling damping resonance space 85, the combustion vibration generated by the combustion chamber 35 can be attenuated by the muffling damping 62 to be damped. Further, by the continuous portion 88 of the silencing lining 61, since the silencing lining resonance space 75 of the silencing lining 61 is not interrupted in the circumferential direction, the continuous portion 88 of the silencing lining 61 can be formed in the circumferential direction. Silence lining resonance space 75. Therefore, the combustion vibration in the combustion chamber 35 can be appropriately attenuated by the silencing lining 61 to be damped by the portion of the sound absorbing liner 75 in which the sound absorbing liner 75 is not interrupted. As described above, it is possible to maintain the performance of suppressing vibration formed by the noise damper 62 while improving the vibration-suppressing performance formed by the silencing lining 61.

Further, according to the first embodiment, the damper opening 82 can be formed by being placed on one side in the width direction of the sound absorbing liner 61. Therefore, the interruption portion 87 can be provided on one side in the width direction of the sound absorbing liner 61, and the continuous portion 88 can be provided on the other side in the width direction of the sound absorbing liner 61.

Further, according to the first embodiment, by making the damper opening 82 into a rectangular shape, the damper opening 82 can be easily formed by machining.

Further, according to the first embodiment, it is possible to appropriately attenuate the combustion vibration generated by the combustion gas (fluid) flowing inside the tail cylinder 33 of the burner 12 by the vibration damping device 60. That is, by arranging the sound absorbing liner 61 connected to the noise damper 62 along the outer circumference of the tail cylinder 33 of the burner 12, the combustion vibration near the flame of the burner 12 can be reduced by the sound absorbing liner 61 and the noise absorbing damping 62. Vibration, which can more effectively dampen (attenuate) combustion vibration.

Further, according to the first embodiment, by using the burner 12 for suppressing the combustion vibration, the load caused by the combustion vibration can be suppressed, so that the durability of the gas turbine 1 can be improved.

Further, in the first embodiment, the damper opening 82 has a rectangular shape. However, the shape is not limited. For example, any shape such as a circular shape or an elliptical shape may be used.

[Example 2]

Next, the vibration damping device 100 of the second embodiment will be described with reference to Fig. 8. Fig. 8 is a development view showing the development of the sound absorbing liner of the second embodiment in the circumferential direction. In the second embodiment, in order to avoid redundancy, only the differences from the first embodiment will be described, and the same components as those in the first embodiment will be described with the same reference numerals. In the damper device 60 of the first embodiment, the damping portion 82 is formed on one side of the width direction with respect to the cylindrical portion 72a of the lining cover 72, and the damper device 100 of the second embodiment is formed. With respect to the cylindrical portion 72a of the hood 72, the damper opening 82 is formed at the center in the width direction thereof.

As shown in Fig. 8, in the damper device 100 of the second embodiment, since the damper opening 82 is formed at the center in the width direction of the cylindrical portion 72a of the lining cover 72, the interruption portion 87 is formed in the width direction. Central. Further, the continuous portion 88 is a pair of interrupted portions 87 and is provided on both sides in the width direction.

As described above, according to Embodiment 2, the damper opening 82 can be formed at the center in the width direction of the silencing lining 61. Therefore, it can be eliminated The interruption portion 87 is provided at the center in the width direction of the lining 61, and a pair of continuous portions 88 are provided on both sides in the width direction of the damper 61.

35‧‧‧ combustion chamber

60‧‧‧Vibration device

61‧‧‧Sound lining

62‧‧‧Damping damping

71‧‧‧Porous plate

72‧‧‧ lining

72a‧‧‧Cylinder

72b‧‧‧Side plate department

73‧‧‧ Sound absorbing holes

75‧‧‧Sound lining resonance space

81‧‧‧ hood

81a‧‧‧Cylinder

81b‧‧‧Side plate department

82‧‧‧damped opening

85‧‧‧Dampening Damping Resonance Space

87‧‧‧Interrupted parts

88‧‧‧Continuous parts

Central axis of the S‧‧‧ burner

A-A‧‧‧ cut line

B-B‧‧‧ cut line

Claims (6)

A vibration damping device comprising: a sound absorbing lining, wherein a sound absorbing lining resonance space and a sound absorbing damping are formed on an outer circumference of an internal flow path through which a fluid flows, and is provided on an outer peripheral side of the sound absorbing lining, And forming a silencing damping resonance space communicating with the sound absorbing lining space; the silencing lining has: an interruption portion, wherein the sound absorbing lining resonance space is communicated with the silencing damping resonance space and the silencing damping a connected damper opening which becomes a portion interrupted by the damper opening in a direction along the outer circumference of the internal flow path, and a continuous portion which is continuous in a direction along the outer circumference of the internal flow path The part. The vibration damping device according to the first aspect of the invention, wherein the sound absorbing liner is formed in a cylindrical shape in a circumferential direction along a circumference of the internal flow path, and an axial direction perpendicular to the circumferential direction. In the width direction, the damper opening is formed on one side in the width direction. The vibration damping device according to the first aspect of the invention, wherein the sound absorbing liner is formed in a cylindrical shape in a circumferential direction along a circumference of the internal flow path, and an axial direction perpendicular to the circumferential direction. In the width direction, the above-mentioned damper opening is formed at the center in the width direction. The damper device according to any one of claims 1 to 3, wherein the damper opening is an opening formed in a rectangular shape. A damper according to any one of claims 1 to 4, and a tail cylinder in which the internal flow path is formed inside. A gas turbine comprising: the burner according to claim 5; and a turbine that is rotated by the combustion gas generated in the burner.