Abstract
A Helmholtz damper for a combustor of a gas turbine includes an enclosure defining a damping volume from which a neck portion extends and which has a flow path (F) for cooling and purging air with an inlet opening and an outlet opening to the enclosure. The outlet opening is formed in the neck portion. A seal is arranged at the neck portion adjacent to the outlet opening for cooling and purging air such that a cooling effect of the seal is provided.
Claims
1. A Helmholtz damper for a combustor of a gas turbine comprising; an enclosure defining a damping volume from which a neck portion extends in a longitudinal direction, said enclosure having an inlet opening and an outlet opening, wherein said damping volume has a flow path (F) from said inlet opening to said outlet opening of said enclosure for cooling and purging air, wherein said neck portion is defined by two annular surfaces having different longitudinal lengths with said outlet opening formed between said annular surfaces, and wherein a seal is arranged at said neck portion adjacent to said shorter annular surface of the outlet opening such that cooling and purging air establishes a cooling effect at an end of said seal.
2. The Helmholtz damper according to claim 1, further comprising a common supply of cooling and purging air for the damper and said seal.
3. The Helmholtz damper according to claim 1, wherein said seal is an integrated part of said neck portion.
4. The Helmholtz damper according to claim 1, wherein said neck portion has an extended length for the accommodation of said seal and/or fastening means.
5. The Helmholtz damper according to claim 1, wherein said neck portion is provided with fastening means to an interface of a combustor chamber.
6. The Helmholtz damper according to claim 1, wherein said seal is arranged on a radial outer side with regard to said enclosure of the damper.
7. The Helmholtz damper according to claim 1, wherein said seal is arranged on a radial inner side with regard to said enclosure of the damper.
8. The Helmholtz damper according to claim 1, wherein said seal is segmented along a sealing surface.
9. The Helmholtz damper according to claim 1, wherein said seal is a spring type seal.
10. The Helmholtz damper according to claim 1, wherein said enclosure is a single volume device.
11. The Helmholtz damper according to claim 1, wherein said enclosure is a segmented volume device.
12. The Helmholtz damper according to claim 11, wherein each segment within said segmented volume device has a different size and establishes a varying damper volume.
13. The Helmholtz damper according to claim 1, wherein the damper is designed as a retrofit part for mounting in existing burners or combustors of gas turbines.
14. The Helmholtz damper according to claim 9, wherein the spring-type seal is a hula-seal or an E-seal.
Description
BRIEF DESCRIPTION OF THE DRAWINGS
(1) In the following, the present invention will be described in more detail with regard to some embodiments or examples of realization of the invention, with reference to the attached drawings, in which:
(2) FIG. 1 is a schematic cross-section view of a first embodiment of a Helmholtz damper according to the invention and applied to a premix burner;
(3) FIG. 2 is a schematic cross-section view of a second embodiment of a Helmholtz damper according to the invention with an alternative form of a seal;
(4) FIG. 3 is a schematic perspective view of a third embodiment of a Helmholtz damper according to the invention, having a single damping volume;
(5) FIG. 4 is a schematic perspective view of a fourth embodiment of a Helmholtz damper according to the invention, having a segmented damping volume; and
(6) FIG. 5 is a schematic cross-section view of a fifth embodiment of a Helmholtz damper according to the invention with an alternative positioning of the seal.
DESCRIPTION
(7) In FIG. 1, a first embodiment of a Helmholtz damper 10 according to the invention is shown in a schematic cross-section view in application to a premix burner 8 of a combustion system of a gas turbine. The Helmholtz damper 10 is mounted to an interface between a premix burner 8 and a front panel 7 of a combustor of the gas turbine. For providing the required damping effect in view of thermoacoustic vibrations during the operation of the gas turbine, the Helmholtz damper 10 has an enclosure 1 defining a rectangular damper volume 11 at a lateral outer side of the premix burner 8 in respective indentations. The enclosure 1 of the damper 10 is furthermore provided with a neck portion 2 of an elongated form. With the elongated neck portion 2, the Helmholtz damper 10 is mounted at the interface between the premix burner 8 and the front panel 7. For this purpose, fastening means 5 are provided at the radial inner side of the neck portion 2 in the form of a rectilinear wall portion like a flange adapted for mounting to the outer side of the premix burner 8. A flow path F for cooling and purging air is provided, passing through the damper volume 11 and the neck portion 5 from an inlet opening 6 to an outlet opening 3. The latter is included in the neck portion 2 of the damper 10. In this embodiment, the outlet opening 3 is formed by the free end of the tube-like neck portion 2. With this flow path F of cooling and purging air, the Helmholtz damper 10 is cooled in order to maintain the required temperatures for a stable operation and for achieving the required damping effect even in case of varying pressure oscillations during the operation of the gas turbine. The airflow F of cooling and purging air is in particular required for cooling the neck portion 2 of the Helmholtz damper 10, which is arranged more closely to the hot gas of the combustion chamber.
(8) According to the present invention, the Helmholtz damper 10 has furthermore at the neck portion 2 a seal 4. The seal 4 in this example of realization is arranged at the radial outer side of the neck portion 2 and contacts the front panel 7 for providing the required sealing effect. The seal 4 at the neck portion 2 is in such a position that the cooling and purging air of the flow path F coming from the outlet opening 3 passes around or along the seal 4 and in particular the front end of the seal 4 facing to the inner side of the combustion system, i.e. to the hot gases of the combustor of the gas turbine. Through this specific arrangement and positioning of the seal 4 of the Helmholtz damper 10 with regard to the outlet opening 3 for the flow path F of the cooling and purging air, an efficient and simultaneous cooling of the seal 4 as well as the enclosure 1 of the Helmholtz damper 10 is achieved. The neck portion 2 is formed with a sufficient length in order to arrange the seal 4 at the radial outer side of the enclosure 1. The front end of the neck portion 2 forms the outlet opening 3 for the flow path F of the cooling and purging air, which is supplied from a common cooling air supply means for the damper 10 and the seal 4. By means of this arrangement and positioning of the seal 4 with regard to the outlet opening 3 of the enclosure 1, the same airflow F is used for the purpose of cooling the damper 10 and in particular the neck portion 2 of the damper 10 as well as the seal 4. According to the invention, it is therefore not required to provide separate cooling means for the purpose of the efficient sealing as well as the providing of a damping effect of the Helmholtz damper 10. The amount of required cooling air is therefore considerably reduced, i.e. up to half of the amount of cooling air necessary for such conventional damping and sealing means in gas turbines.
(9) Hereby, also the complexity of the construction and design of the sealing/damping means is reduced. With the invention, the overall costs of the sealing and damping means for such combustor systems of gas turbines are therefore also reduced. The seal 4 may be an integrated part of the neck portion 2 of the Helmholtz damper 10, or may be attached to the neck portion 2 by any appropriate means of attachment, e.g. welding, screw means, etc. The seal 4 in the form of realization shown in FIG. 1 is a spring-type seal, e.g. a so-called hula seal, for enabling sufficiently large displacements in an elastic range. Between the premix burner 8 and the front panel 7, the seal has several leaf springs formed in a semi-circle loop facing to the radial outer side of the Helmholtz damper 10. Other types of seals 4 may also be used for the sealing effect of the Helmholtz damper 10 according to the invention. Also, alternative positions of the arrangement of the seal 4 are possible, as long as the seal 4 is in such a position that the airflow F of cooling and purging air coming from the inside of the Helmholtz damper 10 passes over at least a portion of the seal 4, e.g. the seal front portion, in order to provide the necessary cooling effect of the seal in combination with the cooling of the enclosure 1 and neck portion 2 of the damper 10. With this specific design of the Helmholtz damper 10 according to the invention, an efficient sealing and damping function is guaranteed in one and the same device. Since the amount of required cooling air is considerably reduced, the operation stability of the gas turbine is also given. With the comparatively low amount of cooling airflow, which is mixed with the gas in the combustion chamber, also the NOx and CO emissions are lower as compared to conventional damping and sealing devices for gas turbines.
(10) Possible implementations for the Helmholtz damper 10 with a combined sealing and damping function are in particular the interfaces between burners and combustors and associated parts of a gas turbine. For example, the damper 10 according to the present invention can be applied to interfaces of EV burners (Environmental Vortex burners), AEV burners, BEV burners and SEV burners (Sequential Environmental Vortex burners). Nevertheless, it is to be noted that the application possibilities of the Helmholtz damper of the invention are not limited to these types of combustor or burner, and the invention can be applied to other interfaces in gas turbines, such as a liner-front-panel interface or a liner-carrier interface of a sequential combustion system of a gas turbine. In any of these implementations, a sealing as well as a damping of thermoacoustic vibrations is required, and by the Helmholtz damper 10 of the invention, these two functions are efficiently provided with a less complex form of design and with a considerably reduced amount of required cooling and purging air.
(11) A second example of realization is shown in a schematic cross-section view of FIG. 2. Also in case of this second example of realization, the Helmholtz damper 10 of the invention is provided with an essentially rectangular enclosure 1 forming a damping volume 11, through which an airflow F of purging and cooling air is guided. The cooling air enters at the inlet opening 6 provided at a lateral wall of the enclosure 1, passes through the interior of the damping volume 11 and flows out from an outlet opening 3, which is the front opening of a neck portion 2 of the Helmholtz damper 10. Cooling air coming from the outlet opening 3 passes around the front part of a seal 4, which is provided for the sealing of the combustor chamber, and prevents the increase in temperature due to a flow of hot gas H in the combustor. The neck portion 2 is provided with an elongated form such that fastening means 3 as well as a seal 4 may be incorporated into the Helmholtz damper 10 at this neck portion 2. Contrary to the first embodiment described with reference to FIG. 1, this second embodiment according to FIG. 2 has a seal 4 on the radial inner side of the damper 10 and the related combustor system or gas turbine. The attachment means 3 is formed at the radial outer side of the Helmholtz damper 10 in form of a rectilinear wall of the neck portion 2, by means of which the damper 10 is fixedly attached to a liner 9 of the gas turbine. On the radial inner side, the neck portion 2 is provided with a seal 4, which is in this example of realization an E-type seal. By interposing the seal 4 between the radial inner side of the neck portion and a burner front panel 7, a tight sealing of the interior of the combustor chamber, in which the hot combustor gases H flow, as schematically indicated by the arrow H in FIG. 2, is provided. Also here, the cooling airflow F coming from the inlet opening 6 and passing through the neck portion 2 in order to flow out of the outlet opening 3, passes along a lateral front surface of the seal 4 such that the seal 4 is cooled by one and the same cooling airflow F as compared to the cooling of the Helmholtz damper 10 itself.
(12) At the outlet opening 3, there may be provided flow guiding means (not shown in FIG. 2) for directing the flow F of cooling and purging air from the direction of the longitudinal axis of the neck portion 2 specifically to the seal 4, which is arranged in this embodiment laterally at a radial inner side of the neck portion 2. With this measure, the cooling effect is even more increased. Also in this form of realization of the Helmholtz damper 10 of the invention, the seal 4 and the enclosure 1 are provided with one and the same common cooling air supply. The supply of cooling air coming from the inlet opening 6 may be formed by any conventional airflow generation means, which is known to the person skilled in the art. For example, the cooling air can be bypass air coming from a compressor of the gas turbine, or can be separate cooling air coming from the outside of the gas turbine. With this design of a Helmholtz damper 10 according to the invention, the seal is shielded by the stream of cooling air coming from the outlet opening 3, without separate cooling means being required for the achievement of an efficient sealing effect.
(13) The Helmholtz damper 10 of the invention is so to speak a combination of both functions in a very efficient and compact manner, namely the damping effect as well as the cooling of the sealing means. Not only is the amount of required cooling and purging air reduced by the invention, but also the overall costs of the sealing and damping devices are less compared to conventional gas turbines due to the common parts and synergies achieved by this form of design of a Helmholtz damper 10. According to an advantageous aspect of the invention, the Helmholtz damper 10 is formed as an independent device, which can easily be maintained and, if necessary, replaced. However, the present invention is not limited to such a form of realization, and the Helmholtz damper 10 may also be an integrated part of other components of the gas turbine. Also with regard to the specific form of the enclosure 1 and the position of the seal 4 with relation to the enclosure 1, the invention is not limited to the shown forms of realization. For example, the neck portion 2 can be at a middle position of the enclosure 1 instead of a lateral position as shown in the embodiments of FIG. 1 and FIG. 2. Also the inlet opening 6 and the position of the outlet opening 3 may be modified within the scope of the present invention.
(14) FIG. 3 and FIG. 4 show in perspective schematic views two different further examples of realization of a Helmholtz damper 10 according to the present invention: it is to be noted that the damper 10 shown in FIG. 3 and FIG. 4 in only schematic views is usually not a rectilinear damper 10, but has an overall annular form for the mounting on a circumferential outer side of a circular component of a combustor system of a gas turbine. Also here, the damper 10 has an enclosure 1 forming a damping volume 11 in an essentially rectilinear or square cross-section form. The enclosure 1 is formed on a lateral upper side with a neck portion 2, in which several outlet openings 3 are provided for the airflow of cooling and purging air coming from an inlet opening (not shown in FIG. 3 and FIG. 4). In the neck portion 2, the radial outer side (upper side in FIG. 3 and FIG. 4) is formed as a flat wall portion, which serves as fastening means 5 for the secure mounting of the damper 10 within a combustor system of a gas turbine. On the opposite side of the neck portion 2, there is also provided a seal 4, which in this case is a spring-type seal, e.g. a hula seal as in the case of the first embodiment of FIG. 1. Contrary to the first embodiment of FIG. 1, the seal 4 in this embodiment of FIG. 3 and FIG. 4 is formed at a radial inner side of the neck portion 2. Depending on the specific flows of hot gases in the combustion systems, the seal 4 on the neck portion 2 of the damper 10 may be in a radial outer position or inner position, as it is required.
(15) According to the embodiment shown in a schematic view of FIG. 3, the enclosure 1 is a single volume forming a single damping volume 11. Such a form of realization is specifically adapted to a damping of low frequency pulsations. On the other hand, the example of realization according to FIG. 4 is formed with several inner partition walls within the damper volume 11, i.e. the interior of the enclosure 1, such that a segmented damping volume is created. Such a form of realization of the Helmholtz damper 10 of the invention is in particular adapted for vibrations of high frequency. By means of such a modification of the inner form of the enclosure 1, the Helmholtz damper 10 can be adapted to different types of applications and operation situations of gas turbines and combustor interfaces. Besides this example of a possible modification of the Helmholtz damper 10 in view of the range of frequencies, to which it is adapted for its damping effect, the damper 10 can also be modified by other means: for example, the damper volume itself, the neck length and the area of the outlet opening, and the form of the enclosure 1 can be modified in order to make the Helmholtz damper 10 suitable for different frequencies or to make it flexible for a damping of multiple frequencies. The Helmholtz damper 10 according to the invention is in particular designed as a retrofit part, which can also be installed into existing combustion systems of gas turbines. For the purpose of a mounting and the integration within the open spaces and areas of such combustion systems, the Helmholtz damper 10 of the invention can also be designed in a retractable form of construction.
(16) Finally, in FIG. 5, a fifth embodiment of a Helmholtz damper 10 for a combustor of a gas turbine according to the present invention is shown in a schematic cross-section view. Also in this example of realization, the Helmholtz damper 10 is applied to a premix burner 8 and is attached to a front panel 7 of a combustor chamber or burner by means of fastening means 5 in the form of an elongated rectilinear wall in a neck portion 2 of the enclosure 1 of the Helmholtz damper 10. The enclosure 1 forms a damping volume 11 in a rectilinear cross-section form, in which an inlet opening 6 as well as an outlet opening 3 for cooling and purging air are provided. The arrow F in FIG. 5 represents an airflow path for this cooling and purging air, which comes from a common supply of cooling air (not shown in FIG. 5) for the purpose of cooling the damper 10 as well as a seal 4. In this form of realization according to FIG. 5, the seal 4 is in a radial inner position with regard to the rotational axis of the gas turbine. Also in this form of realization, the seal 4 may be a spring-type seal, such as a hula seal or an E-seal, which is characterized by a large possibility of displacement between the respective turbine components, i.e. in this case the premix burner 8 and the front panel 7 of the burner. The seal 4 is cooled by the cooling and purging air coming from the outlet opening 3, so that the cooling airflow F forms a kind of shield for protecting the seal 4 from the high temperatures of hot gases within the adjacent combustion chamber of the gas turbine. This means also in this case of the form of realization according to FIG. 5 a common cooling airflow F is used for the cooling of in particular a neck portion 2 of the Helmholtz damper 10 as well as the seal 4, which is arranged in an area close to the outlet opening 3 of the neck portion 2. With this form of realization, the required mass flow of cooling air is considerably reduced, since both elements, i.e. the seal element and the damper element, are cooled by one and the same cooling airflow F. The two basic elements use the same device for supplying cooling air, so that the damper/sealing device is less complex in view of its construction. The overall costs are therefore also limited.
(17) The Helmholtz damper 10 according to the present invention may have a different form with regard to the enclosure 1, e.g. an elongated form or a more compressed form, depending on the respective designs of gas turbines. Also the type of seal used at the area of the neck portion of the Helmholtz damper 10 of the invention can be different from the examples shown in the above description. Also the position of the inlet opening 6 and the outlet opening 3 may be different as compared to the above-described examples of realization. Provided that one and the same cooling and purging airflow F is used for the cooling of both the damper 10 and the seal 4, the invention may be realized in a broad variety of possible designs without departing from the scope of protection of the attached claims.
