• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    A plug (30) for regulating a flow of a gas (80) through a stationary structure of a system is disclosed. The plug (30) includes a housing (32) disposed on the stationary structure defining a temperature limit (60) in the system. The housing (32) defines a passageway (34) to allow the gas (80) to flow therethrough through the stationary structure. The plug (30) further includes at least one pressure actuated valve (36) disposed in the passage (34). The at least one pressure-actuated valve (36) automatically moves from the open position to the closed position when the pressure of the gas (80) exceeds a predetermined value, and automatically moves from the closed position to the open position when the pressure of the gas is the predetermined value below. The stationary structure separates, for example, a compressor exit chamber of a gas turbine from a turbine wheel space and allows the cooling of the turbine runner if the compressor discharge pressure falls below a threshold value.
    公开号:CH703587B1
    申请号:CH01285/11
    申请日:2011-08-02
    公开日:2016-01-15
    发明作者:Manikandan Thiyagarajan；Anantha Ramesh Rangaswamy；Pugalenthi Nanda Gopal
    申请人:Gen Electric；
    IPC主号:
    专利说明:

    Field of the invention
    The subject matter disclosed herein relates generally to gas turbines, and more particularly to apparatus and methods for selectively cooling high temperature areas in gas turbines.
    Background to the invention
    Gas turbine systems are widely used in areas such as power generation. A conventional gas turbine system includes a compressor section, a combustor section and a turbine section. The compressor section supplies compressed air to the combustor section, wherein the compressed air is mixed with fuel and burned, thereby producing a hot gas. This hot gas is supplied to the turbine section, where energy is extracted from the hot gas to do work.
    During operation of the gas turbine system, various components and areas in the system are exposed to high temperature flows that can cause failure or failure of the components and areas. Since higher temperature flows generally result in increased power, efficiency, and higher power output of the gas turbine system, and thus are desirable in the gas turbine system, the components and regions exposed to high temperature flows must be cooled to allow the gas turbine system to flow to work at elevated temperatures.
    An example of an area that should be cooled is the impeller space of the turbine section. The impeller space is generally the area of the turbine section surrounding the turbine impellers. Because the temperature in the impeller space increases due to the increased temperature of the flow through the impeller space or due to elevated ambient temperatures outside the gas turbine system, components in the impeller space, such as components of the rotor and the blade assembly, may undergo thermal expansion. This thermal expansion may eventually cause various components to rub or rub against or otherwise contact each other, possibly resulting in catastrophic damage to the components and the gas turbine system.
    [0005] Various strategies are known in the art for cooling the impeller space to prevent damage to the impeller space components. For example, a solution uses a portion of the air exiting the compressor section of the gas turbine system to cool the impeller space. Holes are created in the compressor discharge housing defining and separating the compressor discharge chamber and the front portion of the impeller space. The holes are then plugged with hole plugs. As the temperature in the impeller space approaches an unacceptably high temperature, the bore plugs are removed and a portion of the air from the compressor section is delivered through the bores to the impeller space, thereby cooling the impeller space.
    However, this strategy for cooling the impeller space has disadvantages. For example, For example, once the hole plugs have been removed, they can not be reapplied until the gas turbine system has been completely shut down. Thus, air from the compressor section is continuously supplied to the impeller space after the bore plugs have been removed until the gas turbine is shut down. In many cases, however, the impeller space does not require permanent cooling. For example, In many cases, temperature fluctuations in the impeller space are caused by fluctuations in the ambient temperature outside the gas turbine system. If the ambient temperature is relatively high, such as during the afternoon or during the summer months, the impeller space may require cooling, but if the ambient temperature is relatively low, such as in the evening or during the winter months, the impeller space may not require cooling. Thus, after the well stoppers have been removed and when the ambient temperature is relatively cool, air is unnecessarily diverted from the compressor section to the impeller space. This unnecessary diversion of compressed air can result in losses in power generation and in the efficiency of the gas turbine system.
    Accordingly, an apparatus and method for delivering cooling air to high temperature gas turbine system areas and components is desired wherein the cooling air is supplied to the areas and components only when needed, for example, during relatively high temperature operating conditions.
    Brief description of the invention
    Aspects and advantages of the invention are set forth in part in the description which follows.
    According to the invention, a plug for regulating a flow of a gas through a stationary structure of a system is provided. The plug includes a housing disposed on the stationary structure defining a temperature limit in the system. The housing defines a passage to allow the gas to flow through the stationary structure. The plug further includes at least one pressure actuated valve disposed in the passage and movable between an open position and a closed position. The at least one pressure-actuated valve is configured to automatically move from the open position to the closed position when the pressure of the gas exceeds a predetermined value, and automatically moves from the closed position to the open position when the pressure of the gas is the predetermined value below.
    The invention further relates to the use of at least one plug according to the invention for regulating a flow of a gas through a stationary structure of a system defining a temperature limit in the system.
    These and other features, aspects, and advantages of the present invention will become better understood with reference to the following description and appended claims. The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate embodiments of the invention and, together with the description, serve to explain the principles of the invention.
    Brief description of the drawings
    A comprehensive and implementation enabling disclosure of the present invention, including the best mode thereof, which is directed to a person skilled in the art, is given in the description which refers to the accompanying figures, in which:<Tb> FIG. 1 <SEP> is a cross-sectional view of a portion of a gas turbine system according to the present invention;<Tb> FIG. FIG. 2 is a cross-sectional view of an embodiment of a temperature boundary with a plug disposed thereon according to the present invention; FIG.<Tb> FIG. 3 is a cross-sectional view of an embodiment of the plug according to the present invention in an open position;<Tb> FIG. FIG. 4 is a cross-sectional view of the plug of FIG. 3 in a closed position; FIG.<Tb> FIG. 5 is a cross-sectional view of another embodiment of the plug according to the present invention in an open position;<Tb> FIG. FIG. 6 is a cross-sectional view of the plug of FIG. 5 in a closed position; FIG.<Tb> FIG. Fig. 7 is a cross-sectional view of another embodiment of the plug according to the present invention in an open position;<Tb> FIG. 8 <SEP> is a cross-sectional view of the plug of FIG. 7 in a closed position;<Tb> FIG. 9 is a cross-sectional view of yet another embodiment of the plug according to the present invention in an open position; and<Tb> FIG. Fig. 10 is a cross-sectional view of the plug of Fig. 9 in a closed position.
    Detailed description of the invention
    [0013] Reference will now be made in detail to embodiments of the invention, one or more examples of which are illustrated in the drawings. Each example is provided to illustrate the invention, not for the purpose of limiting the invention.
    1 shows a cross-sectional view of a portion of a gas turbine system 10. The gas turbine system 10 includes a compressor section 12, a combustor section 14, and a turbine section 16. Further, the system 10 may include a plurality of compressor sections 12, combustor sections 14, and turbine sections 16. The compressor section 12 and the turbine section 16 may be coupled together via a shaft (not shown). The shaft may be a single shaft or may be formed by a plurality of shaft segments connected together to form a shaft.
    The compressor section 12 compresses in operation a gas 80 while the gas 80 flows through the compressor section 12. The gas 80 may e.g. Air or any other suitable gas. The compressor section 12 allows the gas 80 to flow to the combustor section 14, which is configured to receive the gas 80, as is well known in the art. For example, For example, the compressor section 12 may include a compressor exit chamber 20 that is at least partially defined by a compressor exit housing 22. Compressed gas 80 discharged from the compressor section 12 may flow through the compressor exit chamber and into the combustor section 14, which is generally characterized by a plurality of combustors 15 arranged in an annular arrangement (only a single one of which is shown in FIG. 1 is illustrated). The compressed gas 80, after flowing into the combustor section 14, is burned after being mixed with a fuel, thus producing a hot gas 90.
    The resulting hot gas 90 flows from the combustor section 14 into the turbine section 16, which is configured to receive the hot gas 90, as is generally known in the art, to drive the gas turbine system 10 and produce power. The turbine section 16 may include a plurality of impellers 17 disposed in a turbine impeller space 24. The impellers may be mounted in annular groups on the shaft to form turbine rotors (not shown) in this manner. The turbine section 16 may further include a plurality of annular segments 19 disposed in the turbine runner space 24. The impeller space may further include a front impeller space 26. The front impeller space 26 may be at least partially defined by the compressor exhaust housing 22.
    There are numerous temperature limits 60 within the various ranges of the gas turbine system 10. As used herein, the term "temperature limit" refers to any location where the temperature on one side of a stationary structure is greater than the temperature on the opposite side of one such structure. These temperature limits also usually define stationary structures where there are pressure differences. It is common to position passages or holes, such as dilution holes or bore holes, at such temperature limits to allow relatively cooler, higher pressure gases on one side of the temperature limits to flow through the temperature limits and the relatively hotter, lower pressure Quenching or cooling areas on the opposite side of the temperature limits.
    An example of a temperature limit 60 is illustrated in FIG. As illustrated, a relatively cooler gas 80 flowing within the compressor exit chamber 20 creates a temperature limit 60 defined by the compressor exit housing 22 between the compressor exit chamber 20 and the front impeller space 26. One or more bore holes (not illustrated). is often provided at this temperature limit 60 to allow a portion of the gas 80 flowing through the compressor discharge chamber 20 to enter the front impeller space 26 to reduce the high temperatures in the front impeller space 26 and the turbine wheel space 24 in general, including the wheels 17, the stator components 19 and various other components of the gas turbine system 10 to cool.
    The operating temperatures within the front impeller space 26 may vary significantly due to differing operating condition temperatures and expected machine-to-machine variations, such as stage 1 or stage hot gas suction. In particular, the operating temperatures within the front impeller space 26 may vary according to the ambient temperature outside the gas turbine system 10. If e.g. the ambient temperature is relatively high, such as in the afternoon or during the summer months, the front impeller space 26 may be relatively hotter and require cooling. However, when the ambient temperature is relatively cooler, such as in the evening or during the winter months, the front impeller space 26 may be relatively cooler and require no cooling. For example, For example, the temperature of the gas 80 may range from about 550 degrees Fahrenheit ("° F") to about 750 ° F, i. from about 288 ° C to about 399 ° C, and the temperature of the front impeller space 26 may range from about 650 ° F to about 850 ° F, i. from about 343 ° C to about 454 ° C while the ambient temperature ranges from about -20 ° F to about 120 ° F, i. from about -29 ° C to about 49 ° C. Since the ambient temperature varies within this range, the temperatures of the gas 80 and the front impeller space 26 may vary accordingly. Further, the front impeller space 26 may require cooling when the temperature reaches a certain threshold temperature, for example, about 800 ° F, i. reached about 427 ° C. It should be understood that the temperature of the gas 80, the front impeller space 26 and the ambient temperature are not limited to the temperatures disclosed herein.
    According to the invention plug 30 are used in the bore holes. The plugs 30 may be advantageously configured to provide sufficient cooling air to the front impeller space 26 only when required, for example, during relatively higher temperature operating conditions. It should be understood that the plug 30 according to the present invention is not limited to use in a compressor exit housing 22, but rather may be used at any suitable temperature limit 60 to provide a cooling flow through the temperature limit 60 as required. It should be further understood that the plug 30 according to the present invention is not limited to use at a temperature limit 60 in a gas turbine system 10, but rather may be used at any temperature limit 60 in any suitable system.
    As illustrated in FIG. 2, the plug 30 according to the present invention may be used to regulate the flow of the gas 80 through a temperature limit 60, such as through a temperature limit 60 in a gas turbine system 10. As illustrated in FIG. 2, the temperature limit 60 may be e.g. be defined by the compressor outlet housing 22 in one embodiment. Further, the temperature limit 60 may be located between the compressor exit chamber 20 and the front impeller space 26. The plug 30 of the present invention may allow the gas 80 to selectively flow through the temperature boundary 60 to cool a relatively higher temperature area, as described below.
    As illustrated in FIGS. 3 to 10, the plug 30 according to the present invention comprises a housing 32 and at least one pressure-operated valve 36. The housing 32 may be disposed generally at the temperature limit 60 in the gas turbine system 10, for example, at the relatively lower temperature side of the temperature limit 60. For example, For example, the plug 30 may be disposed in a bore hole provided in the stationary structure defining the temperature limit 60. In various embodiments, the plug 30 may include threads that mate with threads in the bore hole, or may be welded, screwed, or otherwise secured in the bore hole using any suitable attachment or securing methods.
    The housing 32 includes a passage 34 for passing the gas 80 therethrough. Generally, the passage 34 may allow the gas 80 to flow from a region of relatively cooler temperature through the temperature boundary 60 to a region having a relatively higher temperature. The passageway 34 may be substantially straight or may meander or serpentine or may have any other suitable shape. Further, the passage 34 may include a plurality of branches receiving a plurality of gas flows 80. The passage 34 may have a substantially circular or oval cross section, a substantially rectangular cross section, a substantially triangular cross section, or any other suitable polygonal cross section. The cross-sectional area of the passageway 34 may be constant over the entire length of the passageway 34, or may be tapered or may include sections of varying cross-sections.
    The at least one pressure-actuated valve 36 is arranged in the passage 34 and between an open position, as illustrated in FIGS. 2, 3, 5, 7 and 9, and a closed position, as shown in FIGS. 4, 6, 8 and 10 is movable. In the open position, the valve 36 allows the gas 80 to flow through the passage 34, as explained above. In the closed position, however, the valve 36 prevents the gas 80 from flowing through the passage 34.
    For example For example, in exemplary embodiments, valve 36 may include a valve bore 38 extending therethrough, as illustrated in FIGS. 2-6, 9, and 10, and described further below. In the open position (see Figures 2, 3, 5 and 9), the valve bore 38 may be aligned with the passage 34 so that the gas 80 may pass through the valve bore 38 as the gas 80 flows through the passage 34. However, in the closed position (see Figures 4, 6 and 10), the valve bore 38 may be aligned with the inner walls of the passage 34 so that the gas 80 in the passage 34 is prevented from passing through the outer walls of the valve 36 Valve bore 38 and thus to flow through the passage 34.
    However, in alternative exemplary embodiments, the valve 36 may be movable into and out of the flow path of the gas 80 through the passageway 34, such that a valve bore 38 is not required. For example, For example, as illustrated in Figures 7 and 8 and described further below, in the open position (see Figure 7), the valve 36 may be located substantially proximate an interior wall of the passageway 34 such that the valve 36 controls the flow of the valve Gas 80 through the passage 34 only minimally hindered. However, in the closed position (see Fig. 8), the valve 36 may be substantially disposed in the passage 34 such that the passage 34 is completely or substantially blocked, thereby preventing the gas 80 from passing therethrough.
    Generally, the valve 36 according to the present invention may be actuated by relative changes in the pressure of the gas 80. The valve 36 may move from the open position to the closed position as the pressure of the gas 80 increases and may move from the closed position to the open position as the pressure of the gas 80 decreases. For example, For example, in the context of a gas turbine system 10, the pressure of the gas 80 may vary with respect to the temperature of the gas 80 and the ambient temperature outside of the gas turbine system 10. As discussed, the ambient temperature outside of the gas turbine system 10 may vary between relatively higher temperatures, for example during the afternoon or during the summer months, and relatively low temperatures, for example during the evening or during the winter months. As the ambient temperature rises and falls, the temperature of the gas 80, as well as the temperature in the front impeller space 26, may be subject to corresponding temperature variations. Further, the pressure of the gas 80 may vary inversely with the variation in the temperature of the gas 80.
    Thus, as the ambient temperature increases, so that the temperature of the gas 80 and the front wheel space 26 increases and cooling of the front wheel space 26 is required, the pressure of the gas 80 may decrease. This decrease in the pressure of the gas 80 may move the valve 36 to the open position and allow relatively cooler gas 80 to flow through the passage 34. The gas 80 may, in exemplary embodiments, flow out of the compressor exit chamber 20 through the passage 34 into the front impeller space 26 while cooling the front impeller space 26.
    Further, when the ambient temperature drops, so that the temperature of the gas 80 and the front impeller space 26 decreases, so that cooling of the front impeller space 26 is no longer required, the pressure of the gas 80 increases. This increase in the pressure of the gas 80 can move the valve 36 to the closed position and prevent the gas 80 from flowing through the passage 34, thereby preventing a wasteful diversion of gas 80 from the compressor discharge chamber 20 and the power output and increase the efficiency of the gas turbine system 10 during the periods when cooling of the front impeller space 26 is not required.
    Thus, it should be understood that the plug 30 according to the present invention is an automatic dynamic plug that does not require manual intervention after installation during normal operating conditions.
    In exemplary embodiments, as illustrated in FIGS. 2-10 and described below, the valve 36 may be biased toward the open position. For example, For example, in some exemplary embodiments, the plug 30 may include a spring component 40 in communication with the valve 36. The spring component 40 may generally exert a spring force on the valve 36 such that the valve 36 is biased toward the open position. In alternative exemplary embodiments, the valve 36 may be biased toward the open position by the weight of the valve 36 or by any other suitable application of a force that causes a bias toward the open position. It should be further understood that in some alternative embodiments, the valve 36 may be biased toward the closed position.
    It should be understood that each plug 30 may include a single pressure actuated valve 36 or a plurality of pressure actuated valves 36. For example, For example, in various embodiments, the passage 34 defined in the housing 32 may include a number of branches, as discussed above, and a valve 36 may be disposed in each branch of the passage 34. Alternatively, the plug 30 may include more than a single passage 34, and a valve 36 may be disposed in each passage 34. Alternatively, the plug 30 may include a single passage 34, and a plurality of valves may be disposed in the passage 34.
    Furthermore, it should be understood that more than a single plug 30, for example a plurality of plugs 30, may be disposed at the temperature limit 60. In exemplary embodiments, e.g. a plurality of plugs 30 may be disposed in the compressor outlet housing 22.
    Figs. 2 to 4 show an embodiment of the plug 30 according to the present invention. As illustrated, the valve 36 of this embodiment is movable between the open position (see Figures 2 and 3) and the closed position (see Figure 4) along a substantially linear horizontal axis. Further, the plug 30 includes a spring component 40 which provides a spring force for biasing the plug 30 toward the open position. In addition, a plurality of stops 42 may be arranged in the plug 30. The stops 42 may be positioned to orient the valve 36 in the open position such that the passage 34 and the valve bore 38 are aligned and in fluid communication with each other. In addition, in some embodiments, the stops 42 may be positioned to orient the valve 36 in the closed position such that the valve 36 properly seals the passageway 34 to prevent the gas 80 from flowing therethrough. As discussed above, when the valve 36 is in the open position, the force 50 applied to the valve 36 by the pressure of the gas 80 may be relatively lower, for example, when the temperature of the gas 80 is relatively higher, as shown in FIGS. 2 and 3 illustrated. However, when the temperature of the gas 80 drops, the force 50 applied to the valve 36 by the pressure of the gas 80 may increase correspondingly, thereby causing the valve 36 to move from the open position to the closed position move, as shown in Fig. 4 is illustrated. As the temperature of the gas 80 increases, the force 50 applied to the valve 36 by the pressure of the gas 80 may correspondingly decrease, thus causing the valve 36 to move from the closed position back to the open position.
    Figs. 5 and 6 show another embodiment of the plug 30 according to the present invention. As illustrated, the valve 36 of this embodiment is movable between the open position (see Fig. 5) and the closed position (see Fig. 6) along a substantially linear vertical axis. Further, the plug 30 includes a spring component 40 which provides a spring force to bias the plug 30 toward the open position. In addition, stops 42 may be disposed in the plug 30. The stops 42 may be positioned to orient the valve 36 in the open position such that the passage 34 and the valve bore 38 are aligned and in fluid communication with each other. In addition, in some embodiments, stops 42 may be positioned to orient valve 36 in the closed position such that valve 36 closes passage 34 properly to prevent gas 80 from flowing therethrough. As discussed above, when the valve 36 is in the open position, the force 50 applied to the valve 36 by the pressure of the gas 80 may be relatively lower, for example, as the temperature of the gas 80 is relatively higher, as in FIG. 5 illustrated. However, when the temperature of the gas 80 drops, the force 50 applied to the valve 36 by the pressure of the gas 80 may increase accordingly, causing the valve 36 to move from the open position to the closed position, as shown in FIG. 6 is illustrated. As the temperature of the gas 80 increases, the force 50 applied to the valve 36 by the pressure of the gas 80 may correspondingly decrease, thereby causing the valve 36 to move from the closed position back to the open position.
    Figs. 7 and 8 show another embodiment of the plug 30 according to the present invention. As illustrated, the valve 36 of this embodiment can be pivoted about a pivot point 44 between the open position (see Fig. 7) and the closed position (see Fig. 8). Further, the plug 30 includes a spring component 40 which provides a spring force to bias the plug 30 toward the open position. In addition, stops 42 may be disposed in the plug 30. The stops 42 may be positioned to align the valve 36 in the closed position such that the valve 36 closes the passage 34 properly sealingly to prevent the gas 80 from flowing therethrough. In addition, in some embodiments, the stops 42 may be positioned to orient the valve 36 in the open position such that the passage 34 and the valve bore 38 are aligned and in fluid communication with each other. As explained above, when the valve 36 is in the open position, the force 50 exerted on the valve 36 by the pressure of the gas 80 may be relatively lower, for example when the temperature of the gas 80 is relatively higher, as in FIG illustrated. However, when the temperature of the gas 80 drops, the force 50 applied to the valve 36 by the pressure of the gas 80 may increase accordingly, causing the valve 36 to move from the open position to the closed position, as in FIG Fig. 8 illustrates. As the temperature of the gas 80 increases, the force 50 applied to the valve 36 by the pressure of the gas 80 may correspondingly fall, thus causing the valve 36 to move from the closed position back to the open position.
    Figs. 9 and 10 show another embodiment of the plug 30 according to the present invention. As illustrated, the valve 36 of this embodiment is movable between the open position (see Fig. 9) and the closed position (see Fig. 10) along a substantially linear vertical axis. In this embodiment, however, the plug 30 is biased by the weight of the valve 36 toward the open position. In addition, stops 42 may be disposed in the plug 30. Some of the stoppers 42 may be positioned to orient the valve 36 in the open position such that the passage 34 and the valve bore 38 are aligned and in fluid communication with each other. Other stops 42 may be positioned to orient the valve in the closed position such that the valve 36 properly seals the passageway 34 to prevent the gas 80 from flowing therethrough. As explained above, when the valve 36 is in the open position, the force 50 applied to the valve 36 by the pressure of the gas 80 may be relatively lower, for example, when the temperature of the gas 80 is relatively higher, as in FIG illustrated. However, when the temperature of the gas 80 drops, the force 50 applied to the valve 36 by the pressure of the gas 80 may increase correspondingly, causing the valve 36 to move from the open position to the closed position, as in FIG. 10 illustrated. As the temperature of the gas 80 increases, the force exerted on the valve 36 by the pressure of the gas 80 may correspondingly fall, causing the valve 36 to move from the closed position back to the open position.
    It should be understood that the stiffness of the spring component 40, the weight, size and pressure surfaces of the valves 36, the size and length of the passages 34 and the valve bores 38 and the orientation of the stops 42 can be calibrated such that the plug 30 is properly responsive to changes in the pressure of the gas 80, and such that the valves 36 transition from the open position to the closed position as the pressure of the gas 80 increases, and move from the closed position to the open position as the pressure of the Gases 80 reduced.
    By including the pressure actuated valves 36 which move between an open position and a closed position, the plug 30 according to the present invention thus provides the gas 80 through the temperature limit 60 therethrough only when cooling is required, for example, during operating conditions with a relatively higher temperature. Thereby, the plug 30 according to the present invention prevents the wasteful diversion of the gas 80 through the temperature limit 60 when cooling is not required, for example during relatively lower temperature operating conditions. Thus, in exemplary embodiments, the plug 30 of the present invention provides improved efficiency and power generation by the gas turbine system 10 of the present invention during relatively lower temperature operating conditions while cooling various components of the gas turbine system 10 during higher operating conditions Temperature ensures.
    The present invention further contemplates using at least one plug 30 to regulate flow of a gas 80 through a temperature limit 60 in a gas turbine system 10. The method includes providing at least one plug 30. The plug 30 includes a housing 32 disposed at a temperature limit in the gas turbine system 10, the housing 32 defining a passageway 34 for flowing gas 80 therethrough, as well is explained above. The housing 32 further includes at least one pressure actuated valve 36 disposed in the passageway 34 and automatically movable between an open position and a closed position, as discussed above.
    This specification uses examples to disclose the invention, including the best mode, and also to enable any person skilled in the art to practice the invention.
    There is disclosed a plug 30 for regulating a flow of a gas 80 through a stationary structure of a system. The plug 30 includes a housing 32 disposed on the stationary structure defining a temperature limit 60 in the system. The housing 32 defines a passageway 34 to allow the gas 80 to flow therethrough through the stationary structure. The plug 30 further includes at least one pressure actuated valve 36 disposed in the passageway 34. The at least one pressure-operated valve 36 moves automatically from the open position to the closed position when the pressure of the gas 80 exceeds a predetermined value, and moves automatically from the closed position to the open position when the pressure of the gas falls below the predetermined value.
    LIST OF REFERENCE NUMBERS
    [0043]<Tb> 10 <September> Gas Turbine System<Tb> 12 <September> compressor section<Tb> 14 <September> combustor section<Tb> 15 <September> compressor<Tb> 16 <September> turbine section<Tb> 17 <September> Wheels<Tb> 19 <September> stator<Tb> 20 <September> compressor outlet chamber<Tb> 22 <September> compressor outlet housing<T b> 24 <September> turbine impeller chamber<tb> 26 <SEP> front wheel space<Tb> 30 <September> Plug<Tb> 32 <September> Housing<Tb> 34 <September> Continuity<tb> 36 <SEP> pressure operated valve<Tb> 38 <September> valve bore<Tb> 40 <September> spring component<Tb> 42 <September> stop<Tb> 44 <September> pivot point<Tb> 50 <September> compressive force<Tb> 60 <September> Temperature Limit<Tb> 80 <September> Gas<Tb> 90 <September> hot gas
    权利要求:
    Claims (12)
    [1]
    A plug (30) for regulating a flow of a gas (80) through a stationary structure of a system (10), the plug (30) comprising:a housing (32) attachable to the stationary structure representing a temperature limit (60) in the system (10), the housing (32) defining a passage (34) for passing the gas (80) therethrough. to flow through the stationary structure; andat least one pressure actuated valve (36) disposed in the passage (34) and movable between an open position and a closed position,wherein the at least one pressure actuated valve (36) is adapted to automatically move from the open position to the closed position when the pressure of the gas (80) exceeds a predetermined value, and automatically moves from the closed position to the open position when the pressure of the gas (80) falls below the predetermined value.
    [2]
    2. A plug (30) according to claim 1, wherein the at least one pressure-actuated valve (36) is biased in the direction of the open position.
    [3]
    3. plug (30) according to claim 2, wherein the bias is effected by a spring force.
    [4]
    A plug (30) according to claim 2, wherein the bias is effected by the weight of the at least one pressure operated valve (36).
    [5]
    5. A plug (30) according to any one of claims 1-4, wherein the at least one pressure-actuated valve (36) in the installed state of the plug (30) along a substantially linear vertical axis is movable.
    [6]
    A plug (30) according to any one of claims 1-4, wherein the at least one pressure actuated valve (36) is movable along a generally linear horizontal axis when the plug (30) is installed.
    [7]
    7. Plug (30) according to any one of claims 1-4, wherein the at least one pressure-actuated valve (36) is pivotable between the open position and the closed position.
    [8]
    8. A plug (30) according to any one of claims 1-7, wherein the plug has a plurality of pressure-operated valves (36).
    [9]
    Use of at least one plug according to any one of claims 1 to 8 for regulating a flow of a gas (80) through a stationary structure of a system (10) defining a temperature limit (60) in the system (10).
    [10]
    10. Use according to claim 9, wherein the system (10) is a gas turbine and the stationary structure between a compressor exit chamber (20) of the gas turbine and a front impeller space (26) of the gas turbine is arranged.
    [11]
    11. Use according to claim 10, wherein the at least one pressure-actuated valve (36) of the at least one plug (30) in the open position allows the gas (80) from the compressor exit chamber (20) through the passage (34) and into the front Impeller space (26) to flow in cooling the front impeller space (26).
    [12]
    12. Use according to claim 10 or 11, wherein the stationary structure is a compressor outlet housing (22) of the gas turbine.
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    同族专利:
    公开号 | 公开日
    US20120031105A1|2012-02-09|
    US8549865B2|2013-10-08|
    CN102418604B|2015-07-08|
    CN102418604A|2012-04-18|
    DE102011052235A1|2012-02-09|
    JP5833368B2|2015-12-16|
    JP2012036890A|2012-02-23|
    CH703587A2|2012-02-15|
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    法律状态:
    2017-03-15| NV| New agent|Representative=s name: GENERAL ELECTRIC TECHNOLOGY GMBH GLOBAL PATENT, CH |
    2021-03-31| PL| Patent ceased|
    优先权:
    申请号 | 申请日 | 专利标题
    US12/849,184|US8549865B2|2010-08-03|2010-08-03|Pressure-actuated plug|
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