JP4754987B2 - Damping device, combustor and gas turbine - Google Patents

Description

  The present invention relates to a damping device, a combustor, and a gas turbine. In particular, the present invention relates to an attenuation device that can be made compact without deteriorating acoustic performance, a combustor including the attenuation device, and a gas turbine.

  The gas turbine has a compressor, a combustor, and a turbine. The compressor takes in air, compresses it to a high pressure, and sends the high-pressure air to the combustor. In the combustor, the fuel is blown out to the high pressure air to burn the fuel. High-temperature combustion gas generated by the combustion of fuel is sent to the turbine, and this high-temperature combustion gas drives the turbine. Since the rotating shaft of the turbine and the rotating shaft of the compressor rotate together, the turbine is driven in this manner, so that the compressor is also driven, and air is taken in and compressed as described above.

  The gas turbine that operates in this way may generate combustion vibration when the fuel burns as described above, and this combustion vibration causes noise and vibration during the operation of the gas turbine. In particular, in recent gas turbines, the NOx (nitrogen oxide) of exhaust gas is reduced in consideration of the influence on the environment during operation. However, in order to reduce NOx, lean combustion of fuel is required. Often used. However, lean combustion tends to cause instability of combustion, and combustion vibration is likely to occur. Therefore, in the conventional gas turbine, combustion vibration is suppressed by providing a vibration damping device in each part of the combustor. For example, in Patent Document 1, an acoustic liner is attached to the tail cylinder. Moreover, in patent document 2, the acoustic damper is provided in the bypass duct. These damping devices have a resonance space, and each attenuates and suppresses combustion vibration by resonating vibration in a specific frequency region in the resonance space.

JP 2002-174427 A JP 2004-183943 A

  However, each of the damping devices such as the acoustic liner and the acoustic damper provided in the gas turbine has an effect of suppressing vibrations in a specific frequency region, but each has a limited frequency region having an effect of suppressing vibrations. . On the other hand, there is a possibility that combustion vibrations in a plurality of frequency regions may occur during operation of the gas turbine. However, if a plurality of attenuation devices that are effective in suppressing vibrations in each frequency region are provided, the space occupied by the attenuation device There was a risk of becoming larger. Thus, when the space occupied by the reduction gear is increased, there is a possibility that the maintainability is deteriorated.

  This invention is made | formed in view of the above, Comprising: It aims at providing the damping device, the combustor, and gas turbine which can aim at coexistence with the improvement of damping performance and the improvement of maintenance property.

In order to solve the above-described problems and achieve the object, an attenuation device according to the present invention includes a perforated plate and a housing, and an acoustic liner having an acoustic liner resonance space composed of the perforated plate and the housing. An acoustic damper having an acoustic part connected to the housing and having an acoustic damper resonance space communicating with the acoustic liner resonance space on the inside; and a circular pipe part formed by a circular pipe having the acoustic part And the acoustic part has two connection parts and the flow area gradually changes from one connection part to the other connection part, and the flow area of the connection part is small. A circular pipe connection part which is a side connection part is connected to the circular pipe part, and an acoustic liner connection part which is a connection part having a larger flow area in the connection part is connected to the housing A tapered portion which is continued, and the fluid resistance member provided on said acoustic damper resonance space is disposed in the vicinity of both end portions of at least the fluid resistance member with included in said acoustic damper, dividing the sound portion into a plurality And a removable part.

  In this invention, the acoustic damper resonance space is communicated with the acoustic liner resonance space by connecting the acoustic part of the acoustic damper to the housing having the acoustic liner resonance space between the perforated plate. As a result, the vibration in the frequency domain that resonates with the acoustic liner is attenuated by the acoustic liner, and the vibration in the frequency domain that resonates with the acoustic damper is transmitted to the acoustic damper resonance space via the acoustic liner resonance space. Is done. Accordingly, it is possible to attenuate the vibration in the frequency domain that can be attenuated by the acoustic liner and the vibration in the frequency domain that can be attenuated by the acoustic damper. Further, by connecting the acoustic damper to the acoustic liner, the entire attenuation device such as the acoustic liner and the acoustic damper can be made compact, and the space occupied by the attenuation device can be reduced. As a result, it is possible to achieve both the improvement of the damping performance and the improvement of the maintainability.

  In the damping device according to the present invention, the acoustic damper is provided with an attaching / detaching portion, and the acoustic portion is formed in a divided structure that can be divided into at least two by the attaching / detaching portion. .

  In this invention, by forming the acoustic part of the acoustic damper with a divided structure, it is possible to perform inspection or replacement for each part by disassembling at the time of inspection or replacement of parts. As a result, the maintainability can be further improved. In addition, by adjusting the frequency region of vibration to be resonated by dividing the acoustic part, the volume of the acoustic damper resonance space can be easily changed by replacing or adding the acoustic part. it can. As a result, the attenuation performance can be improved more reliably.

  In the attenuation device according to the present invention, the acoustic part has a branching part, and the acoustic part is branched into at least two by the branching part.

  According to the present invention, by dividing the acoustic part, the acoustic part can be branched into a plurality of portions that are effective in damping vibrations in different frequency regions. Thereby, vibrations in a plurality of frequency regions can be attenuated. As a result, the attenuation performance can be improved more reliably.

  The attenuation device according to the present invention is characterized in that the acoustic part has a curved part.

  In the present invention, the acoustic damper can be made flexible by providing a curved portion in the acoustic portion. As a result, even when a device equipped with the attenuation device expands or contracts due to heat or a movement due to vibration or the like occurs, the acoustic part can be bent by the curved part. Can be relaxed. As a result, damage to the attenuation device can be suppressed and durability can be improved.

  In the damping device according to the present invention, the acoustic damper includes a fluid resistance member, and the fluid resistance member is provided in the acoustic damper resonance space.

  In the present invention, by providing a fluid resistance member in the acoustic damper resonance space, the fluid resistance member can also be attenuated. In addition, when adjusting the frequency region of the vibration to be attenuated, it can be adjusted not only by changing the volume of the acoustic damper resonance space but also by changing the resistance value by the fluid resistance member. As a result, the attenuation performance can be improved more reliably.

  In the damping device according to the present invention, a plurality of the fluid resistance members are provided, and the plurality of fluid resistance members are separated from each other.

  In the present invention, by providing a plurality of fluid resistance members and separating them from each other, vibrations in a plurality of frequency regions can be attenuated. As a result, the attenuation performance can be improved more reliably.

  Moreover, the attenuation device according to the present invention is characterized in that the acoustic part has a circular pipe part formed by a circular pipe.

  In this invention, a commercially available piping member can be used by forming an acoustic part with circular piping. Thereby, an acoustic part can be manufactured easily. As a result, the manufacturing cost can be reduced.

  Further, in the attenuation device according to the present invention, the acoustic part has two connection parts and has a taper part in which a flow path area gradually changes from one connection part to the other connection part. The circular pipe connection portion, which is the connection portion on the side of the taper portion having the smaller flow path area, is connected to the circular pipe portion, and the connection portion of the taper portion on the side of the larger flow passage area is connected. An acoustic liner connecting portion which is a connecting portion is connected to the housing.

  In this invention, the opening area of the acoustic damper resonance space with respect to the acoustic liner resonance space can be widened by providing a tapered portion between the housing of the acoustic liner and the circular pipe portion. Thereby, even when the diameter of a circular piping part is thin, more vibration can be attenuated with an acoustic damper. As a result, the attenuation performance can be improved more reliably.

  In the damping device according to the present invention, the acoustic part has a resonance chamber, and the resonance chamber is connected to the circular pipe part.

  In this invention, by providing a resonance chamber in the acoustic part, it is possible to suppress vibrations in the low frequency region in the resonance chamber. Thereby, the frequency region which can be attenuated can be expanded in the low frequency direction. As a result, the attenuation performance is further improved.

  Moreover, the attenuation device according to the present invention is characterized in that the acoustic liner is formed in an annular shape.

  In this invention, since the acoustic liner is formed in an annular shape, vibrations generated inside the acoustic liner can be received all around the acoustic liner. Therefore, vibration transmitted from the inside of the acoustic liner in all directions can be damped more reliably. As a result, the attenuation performance can be improved more reliably.

  In the damping device according to the present invention, the acoustic damper is connected to an outer peripheral surface of the housing.

  In this invention, since the acoustic damper is connected to the outer peripheral surface of the housing, the acoustic damper having a large cross-sectional area can be easily provided. That is, by making the width of the acoustic damper in the width direction of the housing approximately the same as the width of the housing in the same direction, the cross-sectional area of the acoustic damper can be easily secured. Thereby, it is possible to more reliably receive a wide range of vibrations with the acoustic damper. As a result, the attenuation performance can be improved more reliably.

  Moreover, the damping device according to the present invention is characterized in that a plurality of the acoustic dampers are connected to one housing.

  In the present invention, by connecting a plurality of acoustic dampers to one housing, the vibrations can be damped by the plurality of acoustic dampers, so that the damping can be performed more reliably. As a result, the attenuation performance can be improved more reliably.

  In the damping device according to the present invention, the plurality of acoustic dampers connected to one housing have different volumes of the acoustic damper resonance space.

  In the present invention, since the volume of the acoustic damper resonance space of the plurality of acoustic dampers provided is different from each other, vibrations in different frequency regions can be attenuated by the respective acoustic dampers. As a result, the attenuation performance can be improved more reliably.

  In the damping device according to the present invention, one or more partition plates are disposed in the acoustic liner resonance space, and the acoustic liner resonance space is partitioned into a plurality of spaces by the partition plate. It is characterized by being.

  In this invention, since the acoustic liner resonance space is partitioned into a plurality of spaces by the partition plate, the frequency region to be attenuated can be clearly divided for each partitioned space, and the vibration in the frequency region is more reliably damped. can do. As a result, the attenuation performance can be improved more reliably.

  Moreover, the combustor which concerns on this invention is equipped with a vehicle interior and a tail cylinder, and is provided with the damping device mentioned above by attaching the said acoustic liner to the said tail cylinder.

  In the present invention, by providing the above-described damping device in the combustor, vibrations in a plurality of frequency regions can be attenuated among the combustion vibrations at the time of fuel combustion by the combustor. Moreover, by mounting the acoustic liner to which the acoustic damper is connected to the tail cylinder of the combustor, the combustion vibration near the flame of the combustor can be attenuated by the acoustic liner and the acoustic damper. Thereby, combustion vibration can be attenuated more effectively. Furthermore, by equipping the above-described attenuation device as the attenuation device equipped in the combustor, the space occupied by the attenuation device around the combustor can be reduced. As a result, it is possible to achieve both the improvement of the damping performance and the improvement of the maintainability.

  The combustor according to the present invention is characterized in that a part of the acoustic part is located outside the vehicle compartment.

  In the present invention, by exposing a part of the acoustic part to the outside of the passenger compartment, maintenance of the exposed portion can be performed from outside the passenger compartment. As a result, the maintainability can be further improved.

  Further, the combustor according to the present invention is characterized in that a plurality of purge holes are formed in a portion of the acoustic part located in the vehicle interior.

  According to the present invention, the acoustic damper resonance space can be purged by forming a purge hole in a portion of the acoustic unit located in the vehicle interior. That is, when the internal pressure of the combustion chamber of the combustor and the internal pressure of the vehicle compartment are compared, the internal pressure of the vehicle interior is higher, so the internal pressure of the acoustic liner resonance space and the acoustic damper resonance space communicating with the combustion chamber is Lower than the internal pressure. For this reason, by forming a purge hole in the acoustic part, air in the vehicle compartment flows into the acoustic damper resonance space of the acoustic part from the purge hole, and the acoustic damper resonance space can be purged. Thereby, high-temperature air and unburned fuel that have entered the acoustic damper resonance space and the acoustic liner resonance space from the combustion chamber can be pushed back toward the combustion chamber. Therefore, the acoustic damper resonance space and the acoustic liner resonance space can be maintained in a clean state. As a result, combustion vibration during fuel combustion can be stably damped.

  The gas turbine according to the present invention includes the combustor.

  In the present invention, by providing the above-described combustor in the gas turbine, vibrations in a plurality of frequency regions can be attenuated among the combustion vibrations during the operation of the gas turbine. Moreover, since the entire acoustic device can be made compact, it is possible to improve the maintainability of both the acoustic device and the devices located in the vicinity thereof. As a result, it is possible to achieve both improvement in damping performance and improvement in maintainability, and a high quality gas turbine can be obtained.

  The damping device, the combustor, and the gas turbine according to the present invention have an effect that it is possible to achieve both improvement in damping performance and improvement in maintenance performance.

  Embodiments of an attenuation device according to the present invention will be described below in detail with reference to the drawings. Note that the present invention is not limited to the embodiments. In addition, constituent elements in the following embodiments include those that can be easily replaced by those skilled in the art or those that are substantially the same.

  1 is a cross-sectional view of a gas turbine including a damping device according to Embodiment 1 of the present invention. The gas turbine 1 shown in the figure is provided with an air intake 2, a compressor 3, a combustor 10, and a turbine 4 from the upstream side to the downstream side of the air flow. The air taken in from the air intake 2 is compressed by the compressor 3 and is sent to the combustor 10 as high-temperature and high-pressure compressed air. In the combustor 10, gas fuel such as natural gas or liquid fuel such as light oil or light heavy oil is supplied to the compressed air to burn the fuel, thereby generating high-temperature and high-pressure combustion gas. This high-temperature and high-pressure combustion gas passes through a tail cylinder 15 described later and is then injected into the turbine 4.

  FIG. 2 is a detailed view of the combustor shown in FIG. The combustor 10 is provided with an inner cylinder 13, a tail cylinder 15, and the like inside an outer cylinder 11 and a casing housing 12. An inner cylinder 13 is provided inside the outer cylinder 11, and a pilot nozzle 16 and a main nozzle 17 are provided on the inner cylinder 13 from one of axial end portions of the inner cylinder 13 formed in a substantially cylindrical shape. It is arranged. Further, a tail cylinder 15 is connected to an end portion on the opposite side of the end portion on the side where the main nozzle 17 or the like is provided among the end portions in the axial direction of the inner cylinder 13. The tail cylinder 15 is formed in a cylindrical shape, and the inside is formed as a combustion chamber 19 described later. Further, the tail cylinder 15 is curved while its cross-sectional area becomes smaller toward the end on the side opposite to the side connected to the inner cylinder 13. The tail cylinder 15 has a larger cross-sectional area, that is, the inner cylinder 13 side is an upstream side of the air flow sent from the compressor 3 as described above, and is curved while the cross-sectional area is reduced. Is on the downstream side. Further, the inside of the casing housing 12 is formed as a casing 18, and the tail cylinder 15 is provided in the casing 18.

  FIG. 3 is a cross-sectional view taken along the line AA of FIG. The tail cylinder 15 is provided with an attenuation device 20. The damping device 20 includes an acoustic liner 21 and an acoustic damper 30, and the acoustic liner 21 is mounted around the inner cylinder 13 in the vicinity of the tail cylinder 15. The acoustic liner 21 includes a plurality of sound absorbing holes 23 and a perforated plate 22 formed in a cylindrical shape and a housing 24 formed around the perforated plate 22. In addition, it is preferable that the aperture ratio of the sound absorption hole 23 with respect to the porous plate 22 is 10% or less. Further, the inside of the perforated plate 22 or the inside of the acoustic liner 21 is a part of the space inside the tail cylinder 15, and the space inside the tail cylinder 15 is formed as a combustion chamber 19. The porous plate 22 is blocked from the outside by a housing 24, and the space between the porous plate 22 and the housing 24 is formed as an acoustic liner resonance space 25.

  The acoustic damper 30 is connected to the housing 24 of the acoustic liner 21. The direction in which the acoustic damper 30 is connected is connected to the acoustic liner 21 in a direction in which the acoustic damper 30 is located on the downstream side of the transition piece 15. The acoustic damper 30 includes an acoustic part 31 having a space inside, and the space inside the acoustic part 31 is formed as an acoustic damper resonance space 32. The acoustic damper resonance space 32 communicates with the acoustic liner resonance space 25 by connecting the acoustic damper 30 to the housing 24 of the acoustic liner 21 as described above.

  FIG. 4 is a BB arrow view of FIG. The acoustic part 31 of the acoustic damper 30 is formed by a circular pipe part 33 and a taper part 40 each having an acoustic damper resonance space 32 inside. The circular piping part 33 is formed in a cylindrical shape. The tapered portion 40 is located between the circular pipe portion 33 and the housing 24, and the acoustic damper 30 is connected to the housing 24 by connecting the tapered portion 40 to the housing 24. In the taper portion 40, both end portions in the flow direction of the air flowing through the acoustic damper resonance space 32 are connection portions 41, one of which is connected to the housing 24 and the other is connected to the circular piping portion 33.

  Of the connecting portions 41, the connecting portion 41 on the side connected to the housing 24 is formed as an acoustic liner connecting portion 42. When the acoustic liner connecting portion 42 is connected to the housing 24, the acoustic damper 30 is acoustically connected. Connected to the liner 21. The position where the taper portion 40 is connected is connected to the surface of the housing 24 facing the downstream side of the transition piece 15. Further, the connecting portion 41 on the side connected to the circular piping portion 33 is formed as a circular piping connecting portion 43, and this circular piping connecting portion 43 has the same shape as the cross-sectional shape of the circular piping portion 33, that is, a circular shape. It is formed in a shape. The circular pipe connection portion 43 is located in the downstream direction of the transition piece 15 with respect to the acoustic liner connection portion 42.

  The shape of the tapered portion 40 connected to both the acoustic liner 21 and the circular pipe portion 33 in these states is the length in the direction orthogonal to the flow direction of the air flowing through the acoustic damper resonance space 32, that is, the tapered portion 40. Is narrower from the acoustic liner connection portion 42 toward the circular pipe connection portion 43. For this reason, the cross-sectional area of the acoustic damper resonance space 32 inside the tapered portion 40, that is, the flow path area gradually changes, and the flow path area becomes smaller from the acoustic liner connection portion 42 toward the circular pipe connection portion 43. ing. Thereby, the acoustic damper 30 opens with respect to the acoustic liner 21 with a flow path area larger than the flow path area of the circular pipe portion 33.

  The circular pipe portion 33 is formed in a cylindrical shape as described above, and for example, a commercially available pipe member or the like is used. Since the circular pipe connecting portion 43 is located on the downstream side of the tail tube 15 with respect to the acoustic liner connecting portion 42, the circular pipe portion 33 connected to the circular pipe connecting portion 43 is connected to the tapered portion 40. 15 is formed in the downstream direction. Further, the circular piping part 33 is curved in the middle, and the direction in which the circular piping part 33 is formed is changed. The curved portion is a curved portion 34, and the curved portion 34 is formed by bending the circular piping portion 33 so as to be convex in the direction of the transition piece 15. Due to the curved portion 34, the circular piping portion 33 formed along the tail tube 15 is bent in a direction away from the tail tube 15. Moreover, the front-end | tip part 35 of the circular piping part 33 formed in this way is obstruct | occluded by hemispherical shape.

  FIG. 5 is a detailed view of part C in FIG. The circular piping part 33 is formed so as to be divided into a plurality of parts, and an attachment / detachment flange 36 that is a part of the attachment / detachment part is formed at a connection portion of each of the divided circular piping parts 33. The detachable flange 36 is formed in a flange shape at the end of each circular pipe portion 33. Each of the divided circular pipe sections 33 can be attached / detached by aligning the attachment / detachment flanges 36, sandwiching both attachment / detachment flanges 36 together, and sandwiching the attachment / detachment flanges 36 by an attachment / detachment coupling 37 which is a part of the attachment / detachment part. Fixed to. The circular piping part 33 divided into a plurality of parts can be attached and detached by the attaching / detaching flange 36 and the attaching / detaching coupling 37, and the circular piping part 33 is formed in a divided structure that can be divided into a plurality of parts. Further, the circular pipe portion 33 is fixed in the passenger compartment 18 by a support portion 38, and the damping device 20 is fixed in the passenger compartment 18 by the acoustic liner 21 that is mounted on the tail cylinder 15 and the support portion 38. The sound damper 30 is fixed and provided in the passenger compartment 18 (FIG. 2).

  The damping device according to the first embodiment is configured as described above, and the operation thereof will be described below. When the gas turbine 1 is operated, high-temperature and high-pressure air compressed by the operation of the compressor 3 is sent to the combustor 10, and fuel is supplied from the pilot nozzle 16 and the main nozzle 17 to the compressed air. By injecting, fuel burns in the combustion chamber 19. When fuel burns in the combustion chamber 19, combustion vibration may occur due to the combustion. In particular, when the fuel is lean burned in order to reduce the NOx emission, the combustion tends to become unstable and combustion vibrations are likely to occur.

  When combustion vibrations are generated in this way, air vibrations (pressure waves) due to the combustion vibrations enter the sound absorption holes 23 of the porous plate 22 of the acoustic liner 21. The acoustic liner 21 has an acoustic liner resonance space 25, and a perforated plate 22 having a plurality of sound absorbing holes 23 is provided between the acoustic liner resonance space 25 and the combustion chamber 19. The air in the space 25 and the air in the sound absorption hole 23 constitute a resonance system by the air in the acoustic liner resonance space 25 functioning as a spring. For this reason, among the air vibrations or sounds caused by the combustion vibrations generated inside the perforated plate 22, the sound in the sound absorbing holes 23 with respect to the sound in the frequency domain corresponding to the volume of the acoustic liner resonance space 25 and the total length of the sound absorbing holes 23. Since the air vibrates vigorously and resonates, the sound at this resonance frequency is absorbed by the friction at that time. Thereby, the amplitude of the combustion vibration is attenuated, and the sound due to the combustion vibration is reduced.

  Further, the acoustic damper 30 is connected to the acoustic liner 21, and the acoustic liner resonance space 25 and the acoustic damper resonance space 32 are connected. For this reason, the combustion vibration generated in the combustion chamber 19 is transmitted to the acoustic damper resonance space 32 via the acoustic liner resonance space 25. Since the acoustic damper 30 extends in the downstream direction of the tail cylinder 15, the acoustic damper resonance space 32 has a larger volume than the acoustic liner resonance space 25. For this reason, in the acoustic damper resonance space 32, vibrations having a longer wavelength than that of the vibrations attenuated in the acoustic liner resonance space 25, that is, frequency regions lower than the frequency range of vibrations that can be attenuated in the acoustic liner resonance space 25. Can be damped.

  In the above damping device, the acoustic damper 30 is connected to the acoustic liner 21, and the acoustic damper resonance space 32 is communicated with the acoustic liner resonance space 25. Both the acoustic liner 21 and the acoustic damper 30 have a function of attenuating vibration, but the acoustic liner 21 attenuates vibration in a relatively high frequency region, and the acoustic damper 30 attenuates vibration in a relatively low frequency region. . For this reason, by making the acoustic liner resonance space 25 and the acoustic damper resonance space 32 communicate with each other, it is possible to attenuate the vibrations in the frequency domain that can be attenuated. That is, by connecting the acoustic liner 21 and the acoustic damper 30, vibrations in a plurality of frequency regions can be attenuated, or vibrations in a wide frequency region can be attenuated. Further, by connecting the acoustic damper 30 to the acoustic liner 21, the space occupied by the attenuation device 20 can be reduced as compared with the case where the acoustic damper 30 and the acoustic liner 21 are provided separately. As a result, the space around the damping device 20 is increased, and workability such as maintenance can be improved. As a result, it is possible to achieve both the improvement of the damping performance and the improvement of the maintainability.

  The acoustic part 31 of the acoustic damper 30 has a circular pipe part 33 formed in a cylindrical shape. Thereby, when manufacturing the acoustic damper 30, a commercially available piping member can be used, and the acoustic part 31 of the acoustic damper 30 can be manufactured easily. As a result, it is possible to reduce the manufacturing cost when manufacturing the attenuation device 20.

  Moreover, the circular piping part 33, that is, the acoustic part 31, is divided, the attachment / detachment flange 36 is provided at the joint portion, and the attachment / detachment coupling 37 is used, whereby the circular piping part 33 can be easily disassembled and assembled. . Thereby, when inspecting the damping device 20 or exchanging parts, it is possible to perform inspection or the like for each part by disassembling at the part of the detachable flange 36. As a result, the maintainability can be further improved. Further, by making the acoustic part 31 into a divided structure, when adjusting the frequency region of the vibration to be resonated in the acoustic damper resonance space 32, the member of the acoustic part 31 is added or exchanged to change the acoustic damper resonance space 32. The volume of the can be easily changed. As a result, the attenuation performance can be improved more reliably.

  Further, a taper portion 40 is provided between the housing 24 of the acoustic liner 21 and the circular pipe portion 33. The taper portion 40 has a flow passage area that narrows from the acoustic liner connection portion 42 toward the circular pipe connection portion 43, and therefore, for the acoustic liner 21, the flow passage area of the circular pipe portion 33 is smaller than the flow passage area. It opens with a large channel area. Thereby, more vibrations can be attenuated by the acoustic damper 30. In addition, although the circular pipe portion 33 has a larger diameter, it is easier to attenuate the vibration. However, even if the diameter of the circular pipe portion 33 is reduced in order to make the damping device 20 compact, the acoustic liner connecting portion 42 of the taper portion 40 is reduced. Since the acoustic liner 21 is opened with a large flow path area, many vibrations can be attenuated by the acoustic damper 30. As a result, the attenuation performance can be improved more reliably.

  Further, by forming the curved portion 34 in the circular piping portion 33, the acoustic damper 30 can be made flexible. For this reason, even when the damping device 20 is provided in the combustor 10 and the combustor 10 expands and contracts due to heat during operation, the acoustic damper 30 can be bent by the curved portion 34, and thus the combustor 10 expands and contracts. The stress on the acoustic unit 31 can be relaxed. As a result, damage to the attenuation device 20 can be suppressed and durability can be improved.

  Further, the damping device 20 is configured by connecting the acoustic damper 30 to the acoustic liner 21, and the damping device 20 is combusted by mounting the acoustic liner 21 of the damping device 20 on the tail cylinder 15 of the combustor 10. The vessel 10 is provided. Thereby, vibrations in a plurality of frequency regions can be damped by the damping device 20 among the combustion vibrations generated during the combustion of the fuel in the combustor 10. Further, when the acoustic liner 21 is mounted on the tail cylinder 15, it is mounted near the inner cylinder 13 of the tail cylinder 15. Thereby, the combustion vibration near the flame during the combustion of the fuel is transmitted to the acoustic liner 21 and further transmitted to the acoustic damper 30, whereby the combustion vibration near the flame can be attenuated. Thereby, combustion vibration can be attenuated more effectively. Further, by installing the attenuation device 20 as the attenuation device equipped in the combustor 10, the space occupied by the attenuation device 20 around the combustor 10 is compared with the case where the acoustic liner and the acoustic damper are separately provided. Can be reduced. As a result, it is possible to achieve both the improvement of the damping performance and the improvement of the maintainability.

  In addition, by providing the gas turbine 1 with the damping device 20, vibrations in a plurality of frequency regions can be attenuated among combustion vibrations during operation of the gas turbine 1. In addition, since the space occupied by the attenuation device 20 can be reduced, the work space of the passenger compartment 18 is increased, and workability such as inspection can be improved. As a result, it is possible to achieve both the improvement of the damping performance during the operation of the gas turbine 1 and the improvement of the maintainability in the vicinity of the combustor 10. In addition, by providing the gas turbine 1 with the combustor 10 including the damping device 20, it is possible to obtain a high-quality gas turbine 1 having excellent damping performance and good maintainability.

  This attenuation device has substantially the same configuration as that of the attenuation device according to the first embodiment, but is characterized in that a fluid resistance member is provided in the acoustic damper resonance space. Since other configurations are the same as those of the first embodiment, the description thereof is omitted and the same reference numerals are given. FIG. 6 is a cross-sectional view of the main part of the acoustic section of the attenuation device according to Embodiment 2 of the present invention. A porous metal 51 serving as a fluid resistance member is provided inside the circular pipe portion 33 of the attenuation device 50 shown in the figure, that is, in the acoustic damper resonance space 32. The porous metal 51 is composed of a porous metal, that is, a metal in which a large number of small holes are formed. The porous metal 51 is formed in a part of the circular pipe portion 33 and in the internal space of the circular pipe portion 33. Is provided in the acoustic damper resonance space 32.

  In addition, the circular pipe portion 33 in the portion where the porous metal 51 is formed has detachable flanges 36 in the vicinity of both ends of the porous metal 51 in the direction of formation of the central axis of the circular pipe portion 33. Thereby, the circular piping part 33 of the part in which the porous metal 51 is formed is formed as a short piping part 52 in which the detachable flanges 36 are formed at both ends. Also, since the detachable flange 36 is formed in the short piping portion 52 in this way, the short piping portion 52 can be attached to and detached from the circular piping portion 33 located at both ends of the short piping portion 52 by the detachable coupling 37. It is fixed.

  The attenuating device 50 according to the second embodiment is configured as described above, and the operation thereof will be described below. Since the porous metal 51 is formed in the acoustic damper resonance space 32, and the countless small holes are formed in the porous metal 51, the acoustic damper resonance is performed through the same path as that of the damping device 20 of the first embodiment. The combustion vibration transmitted to the space 32 during the operation of the gas turbine 1 passes through the holes of the porous metal 51. At that time, the vibration is converted into heat and attenuated by the friction between the air transmitting the combustion vibration and the wall surface of the hole of the porous metal 51.

  In the above damping device 50, the porous metal 51 is provided in the acoustic damper resonance space 32, so that the combustion vibration during the operation of the gas turbine 1 is caused not only by the volume of the acoustic damper resonance space 32 but also by the porous metal 51. Can also be attenuated. As a result, the attenuation performance can be further improved.

  Further, when changing the frequency region of the vibration to be attenuated, not only the volume of the acoustic damper resonance space 32 is changed, but also the size of the porous metal 51, the size of the holes formed in the porous metal 51, the density, etc. It can also be adjusted by changing. That is, by changing the resistance value of the porous metal 51, it is possible to adjust the frequency range of vibration attenuated by the acoustic damper 30. As a result, the attenuation performance can be improved more reliably.

  Further, by providing the porous metal 51 in the short pipe portion 52, when the resistance value of the porous metal 51 is changed, the short pipe portion 52 is replaced with the short pipe in which the porous metal 51 having a different resistance value is formed. By exchanging with the portion 52, the resistance value of the porous metal 51 can be easily changed. Moreover, by connecting the short piping part 52 between the pair of attachment / detachment flanges 36 of the circular piping part 33 of the acoustic damper 30 in which the porous metal 51 is not formed, and fixing with the attachment / detachment coupling 37, it is easy. A porous metal 51 can be newly provided. As a result, the attenuation performance can be easily improved.

  This attenuating device has substantially the same configuration as the attenuating device according to the first embodiment, but is characterized in that the circular pipe portion is branched. Since other configurations are the same as those of the first embodiment, the description thereof is omitted and the same reference numerals are given. FIG. 7 is a plan view of an attenuation device according to Embodiment 3 of the present invention. In the attenuation device 60 shown in the figure, the acoustic part 31 has a branch part 61, and the branch part 61 branches the circular pipe part 33 in two directions. The branch portion 61 is formed such that another circular piping portion 33 intersects or is connected to the circular piping portion 33 formed in a straight line. The circular piping portion 33 where the other circular piping portion 33 intersects with the branch portion 61 is formed as a first circular piping portion 62, and the circular piping intersecting with the first circular piping portion 62 by the branching portion 61. The part 33 is formed as a second circular pipe part 63. The first circular piping portion 62 and the second circular piping portion 63 have different lengths from the branch portion 61, and the first circular piping portion 62 is longer than the second circular piping portion 63. .

  In addition, the circular pipe part 33 in the part where the branch part 61 is formed is provided with a detachable flange 36 in the vicinity of both ends of the branch part 61 in the formation direction of the central axis of the circular pipe part 33. Thereby, the circular piping part 33 of the part in which the branch part 61 is formed is formed as the short piping part 64 by which the attachment / detachment flange 36 was formed in both ends. For this reason, the short piping part 64 in which the branch part 61 is formed is detachably fixed to the circular piping part 33 located at both ends of the short piping part 64 by the detachable coupling 37.

  The attenuator 60 according to the third embodiment is configured as described above, and the operation thereof will be described below. A branch part 61 is formed in the acoustic part 31, and the circular pipe part 33 is branched by the branch part 61. Further, the branched circular piping part 33 is formed with a first circular piping part 62 and a second circular piping part 63 having different lengths. The acoustic damper 30 of the damping device 60 has a different frequency range of vibration that can be damped depending on the volume of the acoustic damper resonance space 32. Specifically, the frequency region of vibration that can be attenuated decreases as the volume of the acoustic damper resonance space 32 increases, and the frequency region of vibration that can be attenuated increases as the volume of the acoustic damper resonance space 32 decreases.

  The acoustic damper 30 has such characteristics, but the first circular piping portion 62 and the second circular piping portion 63 are different in length, and the length of the first circular piping portion 62 is the same. Since the length is longer than the length of the second circular piping portion 63, the volume of the acoustic damper resonance space 32 of the second circular piping portion 63 is larger than that of the acoustic damper resonance space 32 of the first circular piping portion 62. . For this reason, the frequency region of the vibration that can be damped is different between the first circular piping portion 62 and the second circular piping portion 63, and the first circular piping portion 62 has a lower frequency range than the second circular piping portion 63. Can be damped.

  In the above damping device, by providing the branch portion 61 in the acoustic section 31, it is possible to provide a plurality of circular piping sections 33 that are effective in damping vibrations in different frequency regions. Further, the circular pipe part 33 is branched at the branch part 61 into the first circular pipe part 62 and the second circular pipe part 63, and the lengths of the first circular pipe part 62 and the second circular pipe part 63 are made different. Thus, vibrations in different frequency regions can be attenuated, or vibrations in a wide frequency region can be attenuated. As a result, the attenuation performance can be improved more reliably.

  Further, the branch portion 61 is provided in the short piping portion 64, and the short piping portion 64 and the second circular piping portion 63 are integrally formed, so that the short piping portion 52 of the attenuation device 50 of the second embodiment is short. The length of the second circular piping portion 63 can be easily changed by replacing the piping portion 64 with another short piping portion 64 in which the second circular piping portion 63 having a different length is formed. Further, by connecting the short pipe portion 64 between the pair of attachment / detachment flanges 36 of the circular pipe portion 33 of the acoustic damper 30 where the circular pipe portion 33 is not branched, it is easily fixed by the attachment / detachment coupling 37. The circular piping part 33 can be branched. As a result, the attenuation performance can be easily improved.

  The circular pipe section 33 is only branched in two directions by the branch section 61, ie, the first circular pipe section 62 and the second circular pipe section 63, but the circular pipe section 33 is branched in three directions. May be. The frequency region that can be attenuated can be further increased by branching in a plurality of directions of three or more directions and making the lengths of the branched circular pipe portions 33 different from each other. As a result, the attenuation performance can be further improved.

  This attenuation device has substantially the same configuration as the attenuation device according to the first embodiment, but is characterized in that a resonance chamber is formed in the acoustic part. Since other configurations are the same as those of the first embodiment, the description thereof is omitted and the same reference numerals are given. FIG. 8 is a plan view of an attenuation device according to Embodiment 4 of the present invention. In the attenuation device 70 shown in the figure, a resonance chamber 71 is provided at the end of the circular pipe portion 33. The resonance chamber 71 is formed of a rectangular parallelepiped whose length, width, and height are larger than the outer diameter of the circular pipe portion 33, and has a space inside. Since the resonance chamber 71 is connected to the end of the circular piping portion 33 so that the inner spaces of both the resonance chamber 71 and the circular piping portion 33 communicate with each other, the inner space of the resonance chamber 71 is also acoustically connected. It is formed as a part of the damper resonance space 32.

  The attenuator 70 according to the fourth embodiment is configured as described above, and the operation thereof will be described below. A resonance chamber 71 formed with a size larger than the outer diameter of the circular piping portion 33 is connected to the tip of the circular piping portion 33, and the space inside the circular piping portion 33 and the space inside the resonance chamber are It is connected and formed integrally. As a result, the acoustic damper resonance space 32 is formed with a significantly large volume. When the volume of the acoustic damper resonance space 32 is large, the acoustic damper 30 can dampen vibrations having a low frequency range. Therefore, the resonance chamber 71 is connected to the circular pipe portion 33 to dramatically increase the volume of the acoustic damper resonance space 32. Increasing the frequency significantly reduces the frequency region that can be attenuated.

  The attenuation device 70 described above increases the volume of the acoustic damper resonance space 32 by providing the resonance chamber 71 in the circular pipe portion 33. Thereby, the vibration of a low frequency area | region can be attenuated among the vibrations transmitted to the acoustic damper resonance space 32. Thereby, the frequency region which can be attenuated can be expanded in the low frequency direction. As a result, the attenuation performance is further improved.

  This attenuating device has substantially the same configuration as that of the attenuating device according to the fourth embodiment, but is characterized in that a part of the acoustic unit is disposed outside the passenger compartment. Since other configurations are the same as those of the fourth embodiment, the description thereof is omitted and the same reference numerals are given. FIG. 9 is a detailed view of a combustor including a damping device according to Embodiment 5 of the present invention. In the attenuation device 80 shown in the figure, a part of the acoustic unit 31 is formed outside the passenger compartment 18. The acoustic unit 31 included in each attenuation device of the first to fourth embodiments is formed from the upstream side of the tail cylinder 15 toward the downstream direction, but the acoustic unit 31 formed in the fifth embodiment is an acoustic liner. 21 is formed in the direction of the vehicle housing 81 from the connecting portion with the vehicle 21. A through hole 82 having a diameter substantially the same as the outer diameter of the circular pipe portion 33 is formed in the casing housing 81, and the circular pipe portion 33 protrudes outside the vehicle compartment 18 from the through hole 82. That is, the circular pipe portion 33 is formed in a state of penetrating the vehicle compartment housing 81. A resonance chamber 71 is provided at the end of the circular piping portion 33 that penetrates the vehicle casing housing 81, and this resonance chamber 71 is configured so that the circular piping portion 33 passes through the vehicle casing housing 81. 18 is arranged outside. Further, the gap between the through hole 82 and the circular pipe portion 33 located in the through hole 82 is sealed with a sealing material or the like.

  The attenuating device 80 according to the fifth embodiment is configured as described above, and the operation thereof will be described below. A through hole 82 is formed in the casing housing 81, and the resonance chamber 71 is visually recognized from the outside by arranging the resonance chamber 71 outside the casing 18 by passing the circular piping portion 33 through the through hole 82. Can do.

  The above-described attenuation device 80 exposes a part of the acoustic part 31, that is, a part of the resonance chamber 71 and the circular pipe part 33 to the outside of the vehicle compartment 18, thereby removing the exposed resonance chamber 71 and the like from the vehicle compartment 18. Can be done from outside. Maintenance such as inspection of the attenuation device 80 is performed in the vehicle interior 18 in the conventional attenuation device, but by arranging a part of the acoustic unit 31 outside the vehicle interior 18, this portion of the maintenance is performed in the vehicle. This can be done easily from outside the chamber 18. As a result, the maintainability can be further improved.

  This attenuation device has substantially the same configuration as the attenuation device according to the first embodiment, but is characterized in that an acoustic damper is connected to the outer peripheral surface of the housing. Since other configurations are the same as those of the first embodiment, the description thereof is omitted and the same reference numerals are given. FIG. 10 is a detailed view of a combustor including a damping device according to Embodiment 6 of the present invention. In the attenuation device 100 shown in the figure, an acoustic damper 101 is connected to the outer peripheral surface 113 of the housing 111 of the acoustic liner 110. In other words, the acoustic dampers included in each of the attenuation devices according to the first to fifth embodiments are connected to the acoustic liner 21 in a direction positioned on the downstream side of the tail cylinder 15, but the attenuation device 100 according to the sixth embodiment includes the acoustic damper. The acoustic damper 101 is provided in a direction perpendicular to the flow direction of the air flowing in the tail cylinder 15 with respect to the acoustic liner 110. Further, the acoustic damper 101 is not provided with the tapered portion 40 (see FIG. 4), and is formed by a member having a cylindrical shape.

  Specifically, the acoustic damper 101 includes an acoustic damper base portion 102 that is a portion connected to the housing 111 of the acoustic liner 110, and a circular piping portion 33, both of which are piping members having a circular cross-sectional shape. Is formed by. The acoustic damper base portion 102 and the circular piping portion 33 are connected by a detachable coupling 37, and an end portion of the circular piping portion 33 opposite to the end portion on the acoustic damper base portion 102 side is closed. . Further, the diameter of the circular piping member forming the acoustic damper 101 is approximately the same as the width in the flow direction of the air flowing in the tail cylinder 15.

  Further, since the acoustic damper 101 is provided in a direction orthogonal to the flow direction of the air flowing in the tail cylinder 15 with respect to the acoustic liner 110, the acoustic damper 101 is directed from the acoustic liner 110 to the vehicle compartment housing 12. It is provided for. In addition, the acoustic damper 101 provided in this direction is bent along the inner shape of the passenger compartment housing 12 in the vicinity of the passenger compartment housing 12, and more specifically, the acoustic damper base portion 102 is disposed on the passenger compartment housing 12. It is bent along the inner shape. Further, the circular piping portion 33 connected to the acoustic damper base portion 102 formed in this way is fixed to the inner surface of the vehicle compartment housing 12 by the support portion 118.

  11 is a cross-sectional view taken along the line DD of FIG. The acoustic liner 110 has an annular shape and is formed over the entire circumference. That is, the porous plate 22 in which the plurality of sound absorbing holes 23 are formed is formed in a cylindrical shape, and the housing 111 is formed around the porous plate 22. The porous plate 22 is blocked from the outside by the housing 111, and the space between the porous plate 22 and the housing 111 is formed as an acoustic liner resonance space 115. Further, since the housing 111 is formed around the perforated plate 22 in this way, at the outer end in the radial direction of the perforated plate 22 formed in a cylindrical shape in the housing 111, a cylindrical shape is provided. The outer wall portion 112 is formed. The acoustic damper 101 is connected to the outer peripheral surface 113 which is the outer surface of the outer wall portion 112, that is, the acoustic damper base portion 102 is connected to the outer peripheral surface 113 of the housing 111. In addition, the outer wall 112 of the housing 111 is formed with an opening hole 114 having a diameter equal to the inner diameter of the acoustic damper 101 at a portion to which the acoustic damper 101 is connected, and the acoustic damper 101 is formed by the opening hole 114. The acoustic damper resonance space 103 which is the space of the inner portion communicates with the acoustic liner resonance space 115.

  The attenuating device 100 according to the sixth embodiment is configured as described above, and the operation thereof will be described below. Since the acoustic liner 110 is formed in an annular shape, the combustion vibration generated in the combustion chamber 19 of the tail cylinder 15 is transmitted to the acoustic liner resonance space 115 from the sound absorbing hole 23 of the porous plate 22 formed in a cylindrical shape. The combustion vibration transmitted to the acoustic liner resonance space 115 is evenly damped by the acoustic liner 110 being formed in an annular shape.

  Since the above-described attenuation device 100 has the acoustic liner 110 formed in an annular shape, combustion vibration generated inside the acoustic liner 110 can be received all around the acoustic liner 110. Therefore, the combustion vibration transmitted from the inside of the acoustic liner 110 in all directions can be more reliably damped. That is, the combustion vibration generated inside the acoustic liner 110 and transmitted in all directions radially outward of the acoustic liner 110 can be received by the acoustic liner resonance space 115, and the combustion vibration can be attenuated. it can. As a result, the attenuation performance can be improved more reliably.

  In addition, since the acoustic damper 101 is connected to the outer peripheral surface 113 of the housing 111, the acoustic damper 101 having a large cross-sectional area can be easily provided. That is, by making the width of the acoustic damper 101 in the width direction of the housing 111 approximately the same as the width of the housing 111 in the same direction, the cross-sectional area of the acoustic damper 101 can be easily secured. As a result, the acoustic damper 101 can more reliably receive a wide range of vibrations. As a result, the attenuation performance can be improved more reliably.

  Moreover, the acoustic damper 101 can be provided more easily by forming the acoustic damper 101 from the acoustic damper base portion 102 and the circular piping portion 33, both of which are made of piping members. As a result, the manufacturing cost can be reduced.

  In addition, since the acoustic damper 101 is connected to the outer peripheral surface 113 of the housing 111 of the acoustic liner 110, the degree of freedom when providing the acoustic damper 101 can be improved. That is, since the direction in which the acoustic damper 101 is provided with respect to the acoustic liner 110 is not determined, a layout when the acoustic damper 101 is provided by bending the acoustic damper 101 according to the surrounding shape in which the attenuation device 100 is disposed. The degree of freedom can be improved. As a result, the attenuation device 100 can be provided more easily.

  This attenuator has substantially the same configuration as that of the attenuator according to the sixth embodiment, but is characterized in that a plurality of acoustic dampers are provided. Since other configurations are the same as those of the sixth embodiment, the description thereof is omitted and the same reference numerals are given. FIG. 12 is a cross-sectional view of the main part of the acoustic section of the attenuation device according to Embodiment 7 of the present invention. In the attenuation device 120 shown in the figure, an acoustic liner 110 is formed in an annular shape, and two acoustic dampers are connected to the outer peripheral surface 113 of the housing 111 of the acoustic liner 110. Specifically, a first acoustic damper 121 that is an acoustic damper formed in the same shape as the acoustic damper 101 included in the attenuation device 100 according to the sixth embodiment is connected to the outer peripheral surface 113 of one housing 111. A second acoustic damper 125, which is an acoustic damper different from the first acoustic damper 121, is connected to the outer peripheral surface 113. The second acoustic damper 125 is formed of a cylindrical member, that is, a pipe member having a circular cross section, like the first acoustic damper 121, and is connected to the outer peripheral surface 113 of the housing 111. The end opposite to the end is closed. The second acoustic damper 125 has a shorter overall length than the first acoustic damper 121. Therefore, a first acoustic damper resonance space 122 that is an acoustic damper resonance space located inside the first acoustic damper 121 and a second acoustic damper resonance space that is an acoustic damper resonance space located inside the second acoustic damper 125. The volume is different from that of the first acoustic damper resonance space 126, and the volume of the second acoustic damper resonance space 126 is smaller than that of the first acoustic damper resonance space 122.

  The attenuating device 120 according to the seventh embodiment is configured as described above, and the operation thereof will be described below. A first acoustic damper 121 and a second acoustic damper 125 are connected to the outer peripheral surface 113 of one housing 111, and a first acoustic damper resonance space 122 and a second acoustic damper resonance space 126, which are spaces inside these, are provided. The volume of the second acoustic damper resonance space 126 is smaller than the volume of the first acoustic damper resonance space 122. For this reason, the first acoustic damper resonance space 122 and the second acoustic damper resonance space 126 have different frequencies of vibration that can be damped, and the second acoustic damper resonance space 126 is more than the first acoustic damper resonance space 122. The frequency range of vibration that can be damped is high.

  Since the above-described damping device 120 can dampen vibration by two acoustic dampers by connecting the first acoustic damper 121 and the second acoustic damper 125 to one housing 111, it can more reliably attenuate combustion vibration. Can do. As a result, the attenuation performance can be improved more reliably.

  Moreover, since the volume of the 1st acoustic damper resonance space 122 which the 1st acoustic damper 121 has and the volume of the 2nd acoustic damper resonance space 126 which the 2nd acoustic damper 125 has are mutually different, it differs by each acoustic damper. Frequency domain vibration can be attenuated. Specifically, since the volume of the second acoustic damper resonance space 126 is smaller than the volume of the first acoustic damper resonance space 122, when the two are compared, the first acoustic damper resonance space 122 is relatively Therefore, the vibration in the lower frequency region can be attenuated, and the second acoustic damper resonance space 126 can attenuate the vibration in the higher frequency region. As a result, the attenuation performance can be improved more reliably.

  This attenuator has substantially the same configuration as that of the attenuator according to Example 6, but is characterized in that a partition plate is provided in the acoustic liner resonance space. Since other configurations are the same as those of the sixth embodiment, the description thereof is omitted and the same reference numerals are given. FIG. 13: is principal part sectional drawing of the acoustic part of the attenuation apparatus which concerns on Example 8 of this invention. In the attenuation device 130 shown in the figure, an acoustic liner 110 is formed in an annular shape, and the acoustic liner resonance space 115 that is a space located inside the acoustic liner 110 is divided into a plurality of spaces. A partition plate 135 is provided for partitioning. The two partition plates 135 are disposed in the acoustic liner resonance space 115, and the positions thereof are substantially equal from the position where the acoustic damper 101 is connected in the annular acoustic liner 110. Thus, they are arranged at such distributed positions.

  The partition plate 135 disposed in this way is formed in a plate shape connected to the housing 111 and the porous plate 22 of the acoustic liner 110. For this reason, the acoustic liner resonance space 115 is closed at the position where the partition plate 135 is provided. Therefore, the acoustic liner resonance space 115 is partitioned by the partition plate 135, and the acoustic liner resonance space is partitioned into two spaces by the two partition plates 135. The acoustic damper resonance space 103 included in the acoustic damper 101 connected to the housing 111 communicates with one of the two spaces, and the side of the two spaces with which the acoustic damper resonance space 103 communicates. The communication space is a communication-side acoustic liner resonance space 131, and the other space is a non-communication-side acoustic liner resonance space 132. In addition, in the communication-side acoustic liner resonance space 131 and the non-communication-side acoustic liner resonance space 132, the non-communication-side acoustic liner resonance space 132 has a larger volume than the communication-side acoustic liner resonance space 131. .

  The attenuator 130 according to the eighth embodiment is configured as described above, and the operation thereof will be described below. The acoustic liner resonance space 115 is divided into a communication side acoustic liner resonance space 131 and a non-communication side acoustic liner resonance space 132 by two partition plates 135. Therefore, in the acoustic liner resonance space 115, the combustion vibration can be attenuated independently in the communication side acoustic liner resonance space 131 and the non-communication side acoustic liner resonance space 132. The acoustic damper resonance space 103 communicates with the communication side acoustic liner resonance space 131 of the communication side acoustic liner resonance space 131 and the non-communication side acoustic liner resonance space 132. As a result, the communication side acoustic liner resonance space 131 alone is smaller than the volume of the non-communication side acoustic liner resonance space 132, but the combined volume of the communication side acoustic liner resonance space 131 and the acoustic damper resonance space 103 is the non-communication side. The volume of the acoustic liner resonance space 132 is larger. For this reason, the frequency of vibration that can be damped is different between the communication-side acoustic liner resonance space 131 and the non-communication-side acoustic liner resonance space 132, and the communication-side acoustic liner resonance space 131 is more than the non-connection-side acoustic liner resonance space 132. However, the frequency range of vibration that can be damped is low.

  Since the above-described attenuation device 130 divides the acoustic liner resonance space 115 into two spaces by the two partition plates 135, the frequency region to be attenuated can be clearly divided for each divided space. That is, since the acoustic liner resonance space 115 is partitioned into the communication side acoustic liner resonance space 131 and the non-communication side acoustic liner resonance space 132 by the two partition plates 135, the communication side acoustic liner resonance space 131 and the non-communication side acoustics are separated. Combustion vibrations can be damped independently from each other by the liner resonance space 132. As a result, the frequency region to be attenuated can be clearly divided between the communication-side acoustic liner resonance space 131 and the non-communication-side acoustic liner resonance space 132, and vibrations in the frequency region can be more reliably damped. As a result, the attenuation performance can be improved more reliably.

  Further, since the acoustic damper resonance space 103 communicates only with the communication side acoustic liner resonance space 131, the volume of the communication side acoustic liner resonance space 131 and the acoustic damper resonance space 103 is set as a non-communication side acoustic liner resonance space. It can be clearly larger than the volume of 132. Accordingly, the communication-side acoustic liner resonance space 131 can attenuate vibrations in a relatively low frequency region, and the non-communication-side acoustic liner resonance space 132 attenuates vibrations in a relatively high frequency region. be able to. As a result, vibrations in a plurality of frequency regions can be damped more reliably.

  Further, a partition plate 135 is provided in the acoustic liner resonance space 115, and vibrations in different frequency regions are attenuated in the communication side acoustic liner resonance space 131 and the non-communication side acoustic liner resonance space 132. And the non-communication side acoustic liner resonance space 132 can be made into a shape suitable for attenuation of the vibration of the frequency domain attenuate | damped in each space. As a result, when designing the acoustic liner 110, the communication-side acoustic liner resonance space 131 and the non-communication-side acoustic liner resonance space 132 can be designed independently, which facilitates the design. As a result, the manufacturing cost can be reduced.

  FIG. 14 is a detail view of a main part of an acoustic part of an attenuation measure according to a modification of the first embodiment. The acoustic part 31 of the acoustic damper 30 included in the attenuation device 20 according to the first embodiment is formed only in the acoustic liner 21 and the other part is sealed, but the acoustic part 31 has a purge hole. 90 may be formed. For example, as shown in FIG. 14, a plurality of purge holes 90 may be formed in the circular pipe portion 33. By thus forming the purge hole 90 in the circular pipe portion 33, the acoustic damper resonance space 32 can be purged. Specifically, since the compressed air from the compressor 3 is sent to the vehicle compartment 18 and flows from the vehicle compartment 18 toward the combustion chamber 19, the internal pressure of the vehicle compartment 18 is higher than the internal pressure of the combustion chamber 19. Therefore, the internal pressure of the acoustic liner resonance space 25 and the acoustic damper resonance space 32 communicating with the combustion chamber 19 is lower than the internal pressure of the vehicle compartment 18. Thereby, by forming the purge hole 90 in the circular pipe portion 33, the air in the passenger compartment 18 flows into the acoustic damper resonance space 32 from the purge hole 90, and the acoustic damper resonance space 32 can be purged.

  In some cases, high-temperature air or unburned fuel enters the acoustic damper resonance space 32 or the acoustic liner resonance space 25 from the combustion chamber 19, but even in this case, by purging the acoustic damper resonance space 32, Can be pushed back in the direction of the combustion chamber 19. Therefore, the acoustic damper resonance space 32 and the acoustic liner resonance space 25 can be maintained in a clean state. As a result, combustion vibration during fuel combustion can be stably damped. The purge hole 90 may be formed in a portion other than the circular pipe portion 33. For example, as long as it is a part located in the vehicle interior 18 among the acoustic parts 31, such as the said taper part 40 and the resonance chamber 71 formed in the attenuation device 70 which concerns on Example 4, it may be formed anywhere. Further, since the purge hole 90 can purge the acoustic damper resonance space 32 by causing the air in the passenger compartment 18 to flow into the acoustic damper resonance space 32, the acoustic unit 31 as in the attenuation device 80 according to the fifth embodiment. When a part of the purge hole 90 is disposed outside the vehicle compartment 18, the purge hole 90 must be formed in the acoustic part 31 located in the vehicle compartment 18.

  FIG. 15 is a plan view of an attenuation device according to a modification of the first embodiment. Moreover, although the curved part 34 formed in the circular piping part 33 which the attenuation apparatus 20 which concerns on Example 1 has is formed only in one place, the curved part may be formed in multiple numbers. For example, as shown in FIG. 15, a plurality of bending portions 95 are provided, the bending directions of these bending portions 95 are curved so as to protrude in the opposite directions, and the circular pipe portion 33 meanders. You may form so that it may do. Accordingly, since a plurality of flexible curved portions 95 can be formed, the circular pipe portion 33 is more easily expanded and contracted, and even when the expansion and contraction due to heat during operation of the combustor 10 is large, the combustor 10. It is possible to more reliably relieve the stress on the acoustic part 31 due to the expansion and contraction of the. As a result, damage to the attenuation device 20 can be suppressed and durability can be further improved.

  Further, by providing a plurality of curved portions 95 so as to meander the circular piping portion 33, the overall length of the circular piping portion 33 can be increased. Thereby, the volume of the acoustic damper resonance space 32 can be increased. For this reason, the frequency region that can be attenuated by the acoustic damper 30 can be expanded in the low frequency direction. Further, by making the circular pipe portion 33 meander, the entire damping device 20 can be made compact while increasing the volume of the acoustic damper resonance space 32. As a result, it is possible to achieve both the improvement of the damping performance and the improvement of the maintainability.

  FIG. 16 is a cross-sectional view of a main part of an attenuation device according to a modification of the second embodiment. Further, in the acoustic damper resonance space 32 of the attenuation device 50 according to the second embodiment, only one porous metal 51 serving as a fluid resistance member is provided, but a plurality of porous metals 51 are provided. May be. For example, as shown in FIG. 16, two short piping parts 52 provided with porous metal 51 may be connected to circular piping part 33, and two porous metals 51 may be provided so as to be separated from each other. . The above-described combustion vibration of the fuel by the combustor 10 includes vibrations in a plurality of frequency regions. By providing a plurality of porous metals 51 and separating them in this manner, the vibrations in the plurality of frequency regions are damped. can do. Alternatively, the frequency range of vibration that can be damped can be expanded. As a result, the attenuation performance can be improved more reliably. Note that the number of porous metals 51 provided in the acoustic damper resonance space 32 is not two, but may be three or more. By providing a plurality of porous metals 51, vibrations in the frequency region corresponding to the number of porous metals 51 provided can be damped, so that the damping performance can be improved more reliably.

  FIG. 17 is a detailed view of a combustor including a damping device according to a modification of the first embodiment. In addition, although the damping device 20 according to the first embodiment includes one damping device 20 for one combustor 10, a plurality of damping devices 20 may be provided in one combustor 10. For example, as shown in FIG. 17, two attenuation devices 20 may be provided for one tail cylinder 15. In this case, if one of the attenuation devices 20 is provided in the tail cylinder 15, and the acoustic liner 21 of the other attenuation device 20 cannot be attached to the tail cylinder 15 over one turn, this acoustic The liner 21 does not have to be wrapped around the tail tube over one turn. Further, the acoustic liner resonance spaces 25 included in these acoustic liners 21 may have different volumes. Moreover, you may form the length of the circular piping part 33 which each acoustic damper 30 of the two damping devices 20 has different length, respectively. Accordingly, the total volume of the acoustic liner resonance space 25 and the acoustic damper resonance space 32 of each of the two attenuation devices 20 is the total volume of the acoustic liner resonance space 25 and the acoustic damper resonance space 32 of one attenuation device 20. Therefore, more vibration can be damped.

  Moreover, since the volumes of the acoustic liner resonance space 25 and the acoustic damper resonance space 32 of the two attenuation devices 20 are formed in different sizes, vibrations in different frequency regions can be attenuated. Thereby, the frequency region which can be attenuated can be expanded. As a result, the attenuation performance can be improved more reliably. When a plurality of attenuation devices 20 are provided in one combustor 10 as described above, three or more attenuation devices 20 may be provided instead of two. By providing a plurality of damping devices 20 in one combustor 10, the combined volume of the acoustic liner resonance space 25 and the acoustic damper resonance space 32 is increased, and the volume of the acoustic liner resonance space 25 and the acoustic damper resonance space are increased. Since a plurality of 32 volumes having different sizes can be formed, vibrations in a plurality of frequency regions can be attenuated. As a result, the attenuation performance can be dramatically improved.

  FIG. 18 is a cross-sectional view of main parts of an attenuation device according to a modification of the sixth embodiment. In addition, the acoustic liner 110 included in the attenuation device 100 according to the sixth embodiment is formed in an annular shape over the entire circumference, but the acoustic liner may not be formed over the entire circumference. For example, as shown in FIG. 18, the acoustic liner 140 may be formed in a predetermined range in the annular circumferential direction. That is, the porous plate 142 is formed in a shape in which the cross-sectional shape is an arc shape, and is connected to the tail tube main body plate 148 forming the tail tube 15. Further, the housing 141 of the acoustic liner 140 is formed so that the range provided in the annular circumferential direction is the same as the range in which the perforated plate 142 formed in an arc shape is provided, It connects to the perforated plate 142 or the tail tube main body plate 148. Accordingly, the acoustic liner resonance space 145 provided by the housing 141 and the porous plate 142 also has the same range in the circumferential direction as the porous plate 142 or the housing 141.

  When the frequency region of vibration attenuated by the acoustic liner 140 is a frequency region that can be attenuated without forming the acoustic liner 140 over the entire circumference, the acoustic liner 140 is not necessarily formed over the entire circumference. Alternatively, the acoustic liner 140 may be provided in a range suitable for the frequency range of the vibration to be damped. As a result, the vibration in the frequency region that needs to be damped can be damped more reliably, and the range in which the acoustic liner 140 is provided is reduced, so that the manufacturing cost can be reduced. As a result, it is possible to achieve both improvement in attenuation performance and reduction in manufacturing cost.

  FIG. 19 is a cross-sectional view of main parts of an attenuation device according to a modification of the seventh embodiment. In the attenuation device 120 according to the seventh embodiment, the first acoustic damper 121 and the second acoustic damper 125 are connected to one acoustic liner 110 as acoustic dampers. A partition plate 135 may be provided on the acoustic liner 110 to which the second acoustic damper 125 is connected, similarly to the attenuation device 130 according to the eighth embodiment. For example, as shown in FIG. 19, three partition plates 135 may be provided in an acoustic liner resonance space 115 included in the acoustic liner 110, and the acoustic liner resonance space 115 may be partitioned into three spaces. Among these three spaces, the space where the first acoustic damper resonance space 122 communicates is the first acoustic liner resonance space 151, and the space where the second acoustic damper resonance space 126 communicates is the second acoustic liner resonance space 151. A space in which the first acoustic damper resonance space 122 and the second acoustic damper resonance space 126 are not in communication with each other is a third acoustic liner resonance space 153.

  For this reason, when comparing the volume of the three acoustic liner resonance spaces 115 and the acoustic damper, the volume of the first acoustic damper resonance space 122 and the first acoustic liner resonance space 151 is the largest. The volume of the second acoustic damper resonance space 126 and the second acoustic liner resonance space 152 is the next largest, and the first acoustic damper resonance space 122 and the second acoustic damper resonance space 126 communicate with each other. The third acoustic liner resonance space 153 that is not present has the smallest volume. For this reason, the first acoustic liner resonance space 151, the second acoustic liner resonance space 152, and the third acoustic liner resonance space 153 have different vibration frequencies that can be damped. The resonance space 151 is the lowest, and the frequency region of vibration that can be damped is higher in the order of the second acoustic liner resonance space 152 and the third acoustic liner resonance space 153.

  Even when the first acoustic damper 121 and the second acoustic damper 125 having different internal volumes are connected to the acoustic liner 110, a partition plate 135 is provided in the acoustic liner resonance space 115 so that three acoustic liner resonance spaces 115 are provided. By dividing into spaces, vibrations in an arbitrary frequency region can be attenuated more reliably. That is, the acoustic liner resonance space 115 has a higher frequency range of vibration that can be attenuated in the order of the first acoustic liner resonance space 151, the second acoustic liner resonance space 152, and the third acoustic liner resonance space 153. Since it is partitioned by the partition plate 135, the frequency region of the vibration to be damped can be clearly divided. Thereby, the vibration of the frequency region can be attenuated more reliably, and the attenuation performance can be improved more reliably.

  FIG. 20 is a cross-sectional view of main parts of an attenuation device according to a modification of the sixth embodiment. Further, in the damping device 100 according to the sixth embodiment, the acoustic damper 101 made of a pipe member having a circular cross section is connected to the outer peripheral surface 113 of the acoustic liner 110. The acoustic damper 101 is further connected to the pipe member. Other than the above may be connected. For example, as shown in FIG. 20, the resonance chamber 160 may be connected to the acoustic damper 101 connected to the outer peripheral surface 113 of the housing 111 of the acoustic liner 110 in the same manner as the attenuation device 70 according to the fourth embodiment. That is, a rectangular parallelepiped whose length, width, and height are all greater than the outer diameter of the acoustic damper 101 at the end of the acoustic damper 101 opposite to the end connected to the acoustic liner 110. A resonance chamber 160 formed and having a space inside may be connected. The space inside the resonance chamber 160 is connected to the space inside the acoustic damper 101 similarly to the damping device 70 according to the fourth embodiment, and is formed as a part of the acoustic damper resonance space 103. As a result, the volume of the acoustic damper resonance space 103 increases dramatically, and the frequency region that can be attenuated dramatically decreases. Therefore, among the vibrations transmitted to the acoustic damper resonance space 103, the vibration in the low frequency region can be attenuated, and the frequency region that can be attenuated can be expanded in the low frequency direction. As a result, the attenuation performance is further improved.

  21 and 22 are cross-sectional views of main parts of an attenuation device according to a modification of the sixth embodiment. Further, even when the acoustic damper 101 is connected to the outer peripheral surface 113 of the housing 111 of the acoustic liner 110, the porous metal 51 may be provided in the same manner as the attenuation device 50 according to the second embodiment. For example, as shown in FIG. 21, a porous metal 51 may be provided in an acoustic damper resonance space 103 included in the acoustic damper 101 connected to the outer peripheral surface 113 of the housing 111 of the acoustic liner 110. Further, as shown in FIG. 22, the porous metal 51 may be provided in the acoustic damper resonance space 103 even when the resonance chamber 160 is connected to the acoustic damper 101.

  As described above, by providing the porous metal 51 in the acoustic damper resonance space 103, the combustion vibration transmitted to the acoustic damper resonance space 103 passes through the holes of the porous metal 51. That is, since many small holes are formed in the porous metal 51, the combustion vibration transmitted to the acoustic damper resonance space 103 passes through the small holes. At that time, the vibration is converted into heat and attenuated by the friction between the air transmitting the combustion vibration and the wall surface of the hole of the porous metal 51. Thereby, the combustion vibration can be damped not only by the volume of the acoustic damper resonance space 103 but also by the porous metal 51, and the damping performance can be improved. Further, by disposing the porous metal 51, it is possible to more reliably attenuate the vibration in the frequency region that needs to be damped, and to improve the robustness with respect to the frequency of the vibration. As a result, the attenuation performance can be improved more reliably.

  The attachment / detachment portion for connecting the circular pipe portions 33 to each other is provided so that the circular pipe portions 33 divided into a plurality of parts can be reliably connected to each other and can be easily attached / detached. Other than the ring 37, the detachable portion may have a structure other than the detachable flange 36 and the detachable coupling 37.

  Further, in the attenuation device 120 according to the seventh embodiment, the two acoustic dampers of the first acoustic damper 121 and the second acoustic damper 125 are connected to the housing 111 of the acoustic liner 110, but are connected to the single housing 111. There may be three or more acoustic dampers. By connecting a plurality of acoustic dampers to one housing and making the acoustic damper resonance spaces of the respective acoustic dampers have different volumes, vibrations in different frequency regions can be attenuated by each acoustic damper. For this reason, by providing acoustic dampers according to the number of frequency regions of vibrations that need to be damped, vibrations can be damped more reliably. As a result, the attenuation performance can be improved more reliably.

  In the attenuation device 130 according to the eighth embodiment, two partition plates 135 are disposed in the acoustic liner resonance space 115, and three partition plates 135 are disposed in the modified example. May be other than these. The partition plate 135 preferably divides the acoustic liner resonance space 115 in accordance with the number of frequency regions of vibrations that need to be damped by the damping device 130, and is therefore preferably set according to the usage state of the damping device 130. . For this reason, the number of the partition plates 130 may be other than two or three.

  In the above-described attenuation device, the sound absorption holes 23 formed in the porous plate 22 of the acoustic liner have an opening ratio of 10% or less with respect to the porous plate 22, but the opening ratio of the sound absorption holes 23 with respect to the porous plate 22. May be greater than 10%. The sound absorption by the sound absorbing holes 23 is more likely to be absorbed when the diameter of the sound absorbing holes 23 is smaller, and becomes less likely to be absorbed as the diameter increases. For this reason, when the diameter of the sound absorbing hole 23 is increased, the effect of sound absorption by the sound absorbing hole 23 is reduced. Specifically, when the opening ratio of the sound absorbing hole 23 with respect to the porous plate 22 is 30% or more, the sound absorbing hole 23 The hole 23 does not absorb much sound, and the vibration attenuation by the acoustic liner is mainly due to the acoustic liner resonance space. Therefore, since the acoustic liner attenuates vibrations in consideration of the diameter of the sound absorbing hole 23 or the aperture ratio of the sound absorbing hole 23 with respect to the porous plate 22 and the volume of the acoustic liner resonance space, by adjusting both, The vibration in the desired frequency region can be damped more reliably. As a result, the attenuation performance can be improved more reliably.

  Moreover, Examples 1-8 and each modification mentioned above may be combined not only independently but respectively. For example, the damping device 50 of the second embodiment and the damping device 70 of the fourth embodiment are combined to connect the resonance chamber 71 to the circular pipe portion 33 provided with the porous metal 51, or the damping device 60 of the third embodiment. In addition, the purge hole 90 may be formed in both the first circular piping portion 62 and the second circular piping portion 63 by combining the damping device of the above modification. By combining the above-described attenuation devices, the attenuation performance can be improved more reliably and the maintainability can be improved.

  As described above, the damping device, the combustor, and the gas turbine according to the present invention are useful for a gas turbine having a combustor, and are particularly suitable for a case where vibration during combustion of fuel in the combustor is attenuated. .

It is sectional drawing of a gas turbine provided with the damping device which concerns on Example 1 of this invention. It is detail drawing of the combustor shown in FIG. It is AA sectional drawing of FIG. It is a BB arrow line view of FIG. FIG. 5 is a detailed view of part C in FIG. 4. It is principal part sectional drawing of the acoustic part of the attenuation apparatus which concerns on Example 2 of this invention. It is a top view of the damping device concerning Example 3 of the present invention. It is a top view of the damping device concerning Example 4 of the present invention. It is detail drawing of a combustor provided with the damping device concerning Example 5 of the present invention. It is detail drawing of a combustor provided with the damping device concerning Example 6 of the present invention. It is DD sectional drawing of FIG. It is principal part sectional drawing of the acoustic part of the attenuation apparatus which concerns on Example 7 of this invention. It is principal part sectional drawing of the acoustic part of the attenuation apparatus which concerns on Example 8 of this invention. FIG. 6 is a detail view of a main part of an acoustic part of an attenuation measure according to a modification of Example 1; FIG. 6 is a plan view of an attenuation device according to a modified example of the first embodiment. FIG. 10 is a cross-sectional view of a main part of an attenuation device according to a modification of the second embodiment. It is detail drawing of a combustor provided with the damping device which concerns on the modification of Example 1. FIG. FIG. 10 is a cross-sectional view of a main part of an attenuation device according to a modification example of Example 6. FIG. 10 is a cross-sectional view of a main part of an attenuation device according to a modification example of Example 7. FIG. 10 is a cross-sectional view of a main part of an attenuation device according to a modification example of Example 6. FIG. 10 is a cross-sectional view of a main part of an attenuation device according to a modification example of Example 6. FIG. 10 is a cross-sectional view of a main part of an attenuation device according to a modification example of Example 6.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Gas turbine 2 Air intake 3 Compressor 4 Turbine 10 Combustor 11 Outer cylinder 12, 81 Cascade housing 13 Inner cylinder 15 Tail cylinder 16 Pilot nozzle 17 Main nozzle 18 Car compartment 19 Combustion chamber 20, 50, 60, 70, 80, 100, 120, 130 Attenuator 21, 110, 140 Acoustic liner 22, 142 Perforated plate 23 Sound absorption hole 24 Housing 25, 115, 145 Acoustic liner resonance space 30, 101 Acoustic damper 31 Acoustic part 32, 103 Acoustic damper resonance space 33 Circular piping portion 34, 95 Curved portion 35 Tip portion 36 Detachable flange 37 Detachable coupling 38, 118 Support portion 40 Taper portion 41 Connection portion 42 Acoustic liner connection portion 43 Circular piping connection portion 51 Porous metal 52, 64 Short piping portion 61 Branching portion 62 First circular piping portion 63 Second circular piping Part 71, 160 Resonance chamber 82 Through hole 90 Purge hole 102 Acoustic damper base part 111, 141 Housing 112 Outer wall part 113 Outer peripheral surface 114 Opening hole 121 First acoustic damper 122 First acoustic damper resonance space 125 Second acoustic damper 126 Second Acoustic damper resonance space 131 communication side acoustic liner resonance space 132 non-communication side acoustic liner resonance space 135 partition plate 148 tail cylinder main body plate 151 first acoustic liner resonance space 152 second acoustic liner resonance space 153 third acoustic liner resonance space

Claims (15)

An acoustic liner comprising a perforated plate and a housing, and having an acoustic liner resonance space constituted by the perforated plate and the housing;
An acoustic damper having an acoustic part connected to the housing and having an acoustic damper resonance space communicating with the acoustic liner resonance space inside;
The acoustic part has a circular pipe part formed by a circular pipe,
The acoustic part has two connection parts, and the flow area gradually changes from one connection part to the other connection part, and the connection part has a smaller flow area. A circular pipe connecting part which is a connecting part is connected to the circular pipe part, and an acoustic liner connecting part which is a connecting part on the side having a larger flow area in the connecting part is a tapered part connected to the housing;
A fluid resistance member provided in the acoustic damper resonance space;
An attachment / detachment portion provided in the acoustic damper and disposed at least in the vicinity of both ends of the fluid resistance member, and capable of dividing the acoustic portion into a plurality of parts,
An attenuation device comprising: The acoustic part has a branch part,
The attenuation device according to claim 1, wherein the acoustic unit is branched into at least two or more by the branching unit.   The attenuation device according to claim 1, wherein the acoustic part has a curved part. A plurality of the fluid resistance members are provided,
The damping device according to claim 1, wherein the plurality of fluid resistance members are separated from each other. The detachable portion disposed in the vicinity of both ends of the fluid resistance member is disposed in the vicinity of both ends of the fluid resistance member in the formation direction of the central axis of the circular pipe portion, and the fluid resistance member The attenuation device according to claim 1 , wherein the circular pipe portion in a portion where the is formed is formed as a short pipe portion in which the detachable portion is formed at both ends. The acoustic part has a resonance chamber,
The resonance chamber, the attenuation device according to any one of claims 1 to 5, characterized in that connected to the circular pipe portion. The acoustic liner, damping device according to any one of claims 1 to 6, characterized in that it is formed in an annular shape. The acoustic damper, the damping device according to any one of claims 1 to 7, characterized in that connected to the outer peripheral surface of the housing. The acoustic damper, the damping device according to any one of claims 1-8, characterized in that it is more connected to one of said housing. The attenuation device according to claim 9 , wherein a plurality of the acoustic dampers connected to one housing have different volumes of the acoustic damper resonance space. One or more partition plates are disposed in the acoustic liner resonance space,
The acoustic liner resonant space, the attenuation device according to any one of claims 1 to 10, characterized in that it is divided into a plurality of spaces by the partition plate. It has a passenger compartment and a tail tube,
A combustor comprising the damping device according to any one of claims 1 to 11 , wherein the acoustic liner is mounted on the tail cylinder. The combustor according to claim 12 , wherein a part of the acoustic part is located outside the vehicle compartment. The combustor according to claim 12 or 13 , wherein a plurality of purge holes are formed in a portion of the acoustic unit located in the vehicle interior. Gas turbine, comprising a combustor according to any one of claims 12-14.

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