US20100260591A1 - Spanwise split variable guide vane and related method - Google Patents
Spanwise split variable guide vane and related method Download PDFInfo
- Publication number
- US20100260591A1 US20100260591A1 US11/808,314 US80831407A US2010260591A1 US 20100260591 A1 US20100260591 A1 US 20100260591A1 US 80831407 A US80831407 A US 80831407A US 2010260591 A1 US2010260591 A1 US 2010260591A1
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- Prior art keywords
- vane
- sections
- variable guide
- guide vane
- section
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D17/00—Regulating or controlling by varying flow
- F01D17/10—Final actuators
- F01D17/12—Final actuators arranged in stator parts
- F01D17/14—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits
- F01D17/16—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of nozzle vanes
- F01D17/162—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of nozzle vanes for axial flow, i.e. the vanes turning around axes which are essentially perpendicular to the rotor centre line
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
- F01D5/12—Blades
- F01D5/14—Form or construction
- F01D5/141—Shape, i.e. outer, aerodynamic form
- F01D5/146—Shape, i.e. outer, aerodynamic form of blades with tandem configuration, split blades or slotted blades
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/40—Casings; Connections of working fluid
- F04D29/52—Casings; Connections of working fluid for axial pumps
- F04D29/54—Fluid-guiding means, e.g. diffusers
- F04D29/56—Fluid-guiding means, e.g. diffusers adjustable
- F04D29/563—Fluid-guiding means, e.g. diffusers adjustable specially adapted for elastic fluid pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2250/00—Geometry
- F05D2250/30—Arrangement of components
- F05D2250/31—Arrangement of components according to the direction of their main axis or their axis of rotation
- F05D2250/311—Arrangement of components according to the direction of their main axis or their axis of rotation the axes being in line
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T50/00—Aeronautics or air transport
- Y02T50/60—Efficient propulsion technologies, e.g. for aircraft
Definitions
- This invention relates to gas turbine machines and, more specifically, to turbine compressor variable guide vane constructions.
- axial flow gas turbines are designed to optimally operate at a fixed rotational speed and output.
- axial flow gas turbine compressors have limited variable stage geometry and limited air extractions. These factors lead to significant off-design aerodynamic conditions, such as the rotating stall phenomenon, during startup and shutdown operations.
- Rotating stall manifests itself as local stall cells that rotate at about half the wheel or rotor speed. These cells provide coherent unsteady aerodynamic loads on both the rotor and stator blades. As the rotor changes speed, the stall cell count changes, thereby setting up different orders of excitation or nodal diameters. The vibratory response on the rotor and stator blades from the rotating stall aerodynamic loads may lead to increased sensitivity to normal blade damage and premature failures.
- the one-piece variable IGV stage manages the compressor flow uniformly from the ID to OD. Therefore it is not possible to separate the flow control to the ID zone from the remainder of the flow path.
- the IGVs are split and independently controllable to manage especially the ID flow path where rotating stall occurs.
- This spanwise split of the individual IGVs improves axial flow compressor rotor and stator blade durability by eliminating the aerodynamic excitation on axial flow compressor rotor and stator blades, thus also eliminating rotating stall, especially during start-up and shut-down operations.
- spanwise separation of the compressor flow management provides a method of preventing axial flow compressor rotating stall aerodynamics from forming coherent unsteady loads by separately managing the compressor flow in the ID and OD flow path zones.
- the ID and OD flow path zones can be merged by adjusting the inner and outer vane sections to establish a single airfoil profile, i.e., with no differential angle between the sections.
- the invention relates to a variable guide vane for an axial flow compressor comprising: a first radially outer vane section; and a second radially inner vane section; the first and second vane sections angularly adjustable relative to each other about a longitudinal radial axis of the vane.
- the invention in another aspect, relates to a variable guide vane for an axial flow compressor comprising: a first radially outer vane section; a second radially inner vane section; the first and second vane sections angularly adjustable relative to each other about a longitudinal radial axis of the vane; and wherein the first and second vane sections are secured to respective shafts lying on the radial axis, each of the shafts being independently rotatable.
- FIG. 1 is a schematic side elevation of a split IGV in accordance with an exemplary but non-limiting embodiment of the invention
- FIG. 2 is a schematic front elevation of the IGV shown in FIG. 1 ;
- FIG. 3 is a schematic plan view of the IGV shown in FIGS. 1 and 2 ;
- FIG. 4 is a schematic front view of an actuator mechanism for adjusting the IGVs of a compressor stator
- FIG. 5 is a schematic view similar to FIG. 1 but showing an alternative drive embodiment for split IGVs.
- a turbine compressor stator IGV 10 is spanwise split into two sections, a radially inner section 12 and a radially outer section 14 , each pivotable about a common radial axis 16 .
- FIG. 3 A radial view of the spanwise split is best seen in FIG. 3 . From this standpoint, it is clear that the IGV ID and OD sections 12 , 14 , respectively, are positioned at different angles relative to the incoming axial flow, referenced by flow arrow 18 .
- FIG. 3 also shows the radially-oriented axis of rotation 16 that extends through the IGV sections 12 , 14 and that is common to both.
- the OD IGV section 14 has a leading edge 20 and a trailing edge 22
- the ID IGV section 12 has a leading edge 24 and a trailing edge 26 .
- concentric shafts 28 , 30 are employed to rotate the IGV sections 12 , relative to each other about the axis 16 . More specifically, the radially outer end of shaft 28 is fixed to an ID IGV section first gear 32 .
- the shaft 28 extends through the OD IGV section 14 (and is rotatable relative thereto), and is fixed to the ID IGV section 12 .
- the gear 32 is engaged by a first sync gear 34 ( FIG. 2 ), rotation of the latter causing the ID IGV section 12 to pivot about the axis 16 on a stub or other suitable bearing 36 .
- the OD IGV section 14 is provided with a bushing 38 through which shaft 28 passes, and shaft 30 is telescoped over the shaft 28 and extends between OD IGV 14 and a second gear 40 .
- Gear 40 is engaged with a second sync ring gear 42 ( FIG. 2 ). Independent rotation of the sync ring gears 34 , 42 will cause differential rotation of IGV sections 12 , 14 , such that the IGV ID and OD sections become angularly offset as shown in FIG. 3 .
- FIG. 4 illustrates one exemplary but non-limiting manner in which the first and second sync ring gears 32 , can be rotated, as well as engagement of the rings with multiple IGVs 10 that surround a rotor shaft (not shown), the axis of which is shown at 44 .
- a first linear actuator 46 having a cylinder 48 and piston 50 may be arranged such that the remote end 52 of the piston 50 is pivotably attached to the second ring 34 , and the base 54 of the cylinder 48 is pivotably attached to a stationary support 56 (e.g., the compressor casing). Extension (or retraction) of the piston 50 causes rotational movement of the sync ring gear 34 and movement of the IGV ID section 12 of each IGV 10 .
- a second actuator 58 having a cylinder 60 and piston 62 is pivotally attached to the first ring 32 , and the base 64 of the cylinder 60 is pivotably attached to the casing 56 .
- Actuation of the linear actuators may be coordinated by, for example, computer program or other suitable control means, to achieve the desired movement of the ID and OD vane sections 12 , 14 .
- the ID and OD sections of the IGVs will be offset as shown in FIG. 3 .
- the ID and OD IGV sections 12 , 14 will be adjusted to eliminate the offset, i.e., reducing the differential angle between the ID and OD IGV sections substantially to zero.
- any suitable mechanical, pneumatic or hydraulic actuators may be employed to rotate the IGV ID and OD sections.
- ID and OD IGV spanwise lengths are variable, based upon either CFD predictions or measured data.
- the only requirement on blade span is that the sum of the ID and OD radial blade lengths together span the entire flow path.
- FIG. 5 illustrates another exemplary and non-limiting embodiment where each IGV section of the IGV 110 is actuated by its own sync ring. More specifically, the IGV 110 is split to include an ID IGV section 112 and an OD IGV section 114 , with a slight radial gap 58 at the interface.
- the ID IGV section 112 is provided with a shaft 60 secured to a gear 62 .
- the gear 62 is engaged by a first sync ring gear 64 , the rotation of which causes ID IGV section 112 to rotate about a radial axis of rotation 116 .
- the OD IGV section 114 likewise is provided with a shaft 66 to which is fixed a second gear 68 engaged by a second sync ring gear 70 .
- sync ring gears 64 and 70 may be rotated independently to fix the ID IGV and OD IGV sections at the desired angles relative to the incoming air flow vector.
- the ID and OD airfoil sections do not need to have the same configuration at the ID-OD interface location. Additionally, the interface section need not be parallel to the engine center line as displayed in the figures, but may have a generally defined section.
- this spanwise split IGV invention improves axial flow compressor rotor and stator blade durability by eliminating aerodynamic excitation.
- a method to reduce the axial flow compressor rotating stall aerodynamics is provided by preventing the formation of coherent unsteady loads.
- the spanwise split IGV also provides a method for separately managing the compressor flow in the ID and OD flow path zones. This reduces the ID stall zone and weakens the ability of the rotating stall to form a coherent unsteady vibratory force on the compressor airfoils.
Abstract
Accordingly, in one aspect, the invention relates to a variable guide vane for an axial flow compressor comprising: a first radially outer vane section; and a second radially inner vane section; the first and second vane sections angularly adjustable relative to each other about a longitudinal radial axis of the vane.
Description
- This invention relates to gas turbine machines and, more specifically, to turbine compressor variable guide vane constructions.
- Power generation axial flow gas turbines are designed to optimally operate at a fixed rotational speed and output. In addition, axial flow gas turbine compressors have limited variable stage geometry and limited air extractions. These factors lead to significant off-design aerodynamic conditions, such as the rotating stall phenomenon, during startup and shutdown operations.
- Rotating stall manifests itself as local stall cells that rotate at about half the wheel or rotor speed. These cells provide coherent unsteady aerodynamic loads on both the rotor and stator blades. As the rotor changes speed, the stall cell count changes, thereby setting up different orders of excitation or nodal diameters. The vibratory response on the rotor and stator blades from the rotating stall aerodynamic loads may lead to increased sensitivity to normal blade damage and premature failures.
- Recent investigations have revealed that during off-speed operation (such as at start-up and shut-down), fixed speed, multi-staged axial flow compressors with a single stage of variable geometry vanes, VSV, called Inlet Guide Vanes (IGVs), exhibit separated flow at the inner diameter (ID) flow path while the outer diameter (OD) flow path zone is more stable. This part-speed, ID-located stall effect is predicted in computational fluid dynamics (CFD) analysis of a typical fixed speed, multi-staged axial flow compressor.
- Traditionally, the one-piece variable IGV stage manages the compressor flow uniformly from the ID to OD. Therefore it is not possible to separate the flow control to the ID zone from the remainder of the flow path.
- In accordance with an exemplary but non-limiting embodiment of the invention, the IGVs are split and independently controllable to manage especially the ID flow path where rotating stall occurs. This spanwise split of the individual IGVs improves axial flow compressor rotor and stator blade durability by eliminating the aerodynamic excitation on axial flow compressor rotor and stator blades, thus also eliminating rotating stall, especially during start-up and shut-down operations. Stated differently, spanwise separation of the compressor flow management provides a method of preventing axial flow compressor rotating stall aerodynamics from forming coherent unsteady loads by separately managing the compressor flow in the ID and OD flow path zones. This reduces the ID stall strength and weakens the ability of the rotating stall to form a coherent unsteady vibratory force on the compressor airfoils. Under normal operating conditions, the ID and OD flow path zones can be merged by adjusting the inner and outer vane sections to establish a single airfoil profile, i.e., with no differential angle between the sections.
- Accordingly, in one aspect, the invention relates to a variable guide vane for an axial flow compressor comprising: a first radially outer vane section; and a second radially inner vane section; the first and second vane sections angularly adjustable relative to each other about a longitudinal radial axis of the vane.
- In another aspect, the invention relates to a variable guide vane for an axial flow compressor comprising: a first radially outer vane section; a second radially inner vane section; the first and second vane sections angularly adjustable relative to each other about a longitudinal radial axis of the vane; and wherein the first and second vane sections are secured to respective shafts lying on the radial axis, each of the shafts being independently rotatable.
-
FIG. 1 is a schematic side elevation of a split IGV in accordance with an exemplary but non-limiting embodiment of the invention; -
FIG. 2 is a schematic front elevation of the IGV shown inFIG. 1 ; -
FIG. 3 is a schematic plan view of the IGV shown inFIGS. 1 and 2 ; -
FIG. 4 is a schematic front view of an actuator mechanism for adjusting the IGVs of a compressor stator; and -
FIG. 5 is a schematic view similar toFIG. 1 but showing an alternative drive embodiment for split IGVs. - With reference now to
FIGS. 1-3 , a turbinecompressor stator IGV 10 is spanwise split into two sections, a radiallyinner section 12 and a radiallyouter section 14, each pivotable about a commonradial axis 16. - A radial view of the spanwise split is best seen in
FIG. 3 . From this standpoint, it is clear that the IGV ID andOD sections flow arrow 18.FIG. 3 also shows the radially-oriented axis ofrotation 16 that extends through theIGV sections FIG. 1 , theOD IGV section 14 has a leadingedge 20 and atrailing edge 22, while theID IGV section 12 has a leadingedge 24 and atrailing edge 26. - With reference again to
FIGS. 1 and 2 ,concentric shafts IGV sections 12, relative to each other about theaxis 16. More specifically, the radially outer end ofshaft 28 is fixed to an ID IGV sectionfirst gear 32. Theshaft 28 extends through the OD IGV section 14 (and is rotatable relative thereto), and is fixed to theID IGV section 12. Thegear 32 is engaged by a first sync gear 34 (FIG. 2 ), rotation of the latter causing theID IGV section 12 to pivot about theaxis 16 on a stub or other suitable bearing 36. - At the same time, the OD
IGV section 14 is provided with abushing 38 through whichshaft 28 passes, andshaft 30 is telescoped over theshaft 28 and extends betweenOD IGV 14 and asecond gear 40. Gear 40 is engaged with a second sync ring gear 42 (FIG. 2 ). Independent rotation of thesync ring gears IGV sections FIG. 3 . -
FIG. 4 illustrates one exemplary but non-limiting manner in which the first and secondsync ring gears 32, can be rotated, as well as engagement of the rings withmultiple IGVs 10 that surround a rotor shaft (not shown), the axis of which is shown at 44. In this example, a firstlinear actuator 46 having acylinder 48 andpiston 50 may be arranged such that the remote end 52 of thepiston 50 is pivotably attached to thesecond ring 34, and thebase 54 of thecylinder 48 is pivotably attached to a stationary support 56 (e.g., the compressor casing). Extension (or retraction) of thepiston 50 causes rotational movement of thesync ring gear 34 and movement of theIGV ID section 12 of eachIGV 10. Similarly, asecond actuator 58 having acylinder 60 andpiston 62 is pivotally attached to thefirst ring 32, and thebase 64 of thecylinder 60 is pivotably attached to thecasing 56. Actuation of the linear actuators may be coordinated by, for example, computer program or other suitable control means, to achieve the desired movement of the ID andOD vane sections FIG. 3 . When the turbine is operating under normal full-load conditions, the ID andOD IGV sections - It will be appreciated that any suitable mechanical, pneumatic or hydraulic actuators may be employed to rotate the IGV ID and OD sections.
- It will be understood that the ID and OD IGV spanwise lengths (i.e., radial lengths) are variable, based upon either CFD predictions or measured data. The only requirement on blade span is that the sum of the ID and OD radial blade lengths together span the entire flow path.
-
FIG. 5 illustrates another exemplary and non-limiting embodiment where each IGV section of theIGV 110 is actuated by its own sync ring. More specifically, theIGV 110 is split to include anID IGV section 112 and anOD IGV section 114, with a slightradial gap 58 at the interface. TheID IGV section 112 is provided with ashaft 60 secured to agear 62. Thegear 62 is engaged by a firstsync ring gear 64, the rotation of which causesID IGV section 112 to rotate about a radial axis ofrotation 116. - The
OD IGV section 114 likewise is provided with a shaft 66 to which is fixed a second gear 68 engaged by a second sync ring gear 70. - It will be appreciated that by using separate linear actuators similar to those shown in
FIG. 4 ,sync ring gears 64 and 70 may be rotated independently to fix the ID IGV and OD IGV sections at the desired angles relative to the incoming air flow vector. - In general application, the ID and OD airfoil sections do not need to have the same configuration at the ID-OD interface location. Additionally, the interface section need not be parallel to the engine center line as displayed in the figures, but may have a generally defined section.
- Splitting the IGVs into ID and OD sections as described above has a number of benefits and advantages. For example, this spanwise split IGV invention improves axial flow compressor rotor and stator blade durability by eliminating aerodynamic excitation. By spanwise separation of the compressor flow management, a method to reduce the axial flow compressor rotating stall aerodynamics is provided by preventing the formation of coherent unsteady loads. The spanwise split IGV also provides a method for separately managing the compressor flow in the ID and OD flow path zones. This reduces the ID stall zone and weakens the ability of the rotating stall to form a coherent unsteady vibratory force on the compressor airfoils.
- Another benefit of separate spanwise management of compressor flows is improved power turn-down capability. Fixed speed axial flow compressors provide power turn-down by reducing compressor flow. This flow reduction is provided by IGV closure. Optimal management of the split spanwise IGV improves turn-down performance and turn-down magnitude.
- While the invention has been described in connection with what is presently considered to be the most practical and preferred IGV embodiment, it is to be understood that the invention is not to be limited to the disclosed embodiment, but on the contrary, is intended to cover various VSV modifications and equivalent arrangements included within the spirit and scope of the appended claims.
Claims (17)
1. A variable guide vane for an axial flow compressor comprising:
a first radially outer vane section; and
a second radially inner vane section; said first and second vane sections angularly adjustable relative to each other about a longitudinal radial axis of said vane.
2. The variable guide vane of claim 1 wherein said first and second vane sections interface along a horizontal split line substantially perpendicular to said longitudinal axis.
3. The variable guide vane of claim 2 wherein said horizontal split line is located about mid-way along a radial length dimension of said vane.
4. The variable guide vane of claim 1 wherein said first and second vane sections are secured to respective shafts lying, on said radial axis, each of said shafts being independently rotatable.
5. The variable guide vane of claim 4 wherein each of said shafts has a gear secured at a respective end thereof, engageable with a respective sync ring gear.
6. The variable guide vane of claim 1 wherein said first and second vane sections are mounted on a common shaft lying on said longitudinal axis, one of said vane sections fixed to said shaft, and the other of said vane sections rotatable relative to said shaft.
7. The variable guide vane of claim 1 wherein said first and second vane sections are mounted to respective shafts, each fixed to a gear at respective opposite ends of the guide vane.
8. The variable guide vane of claim 5 wherein said respective sync gears are each rotatable by a hydraulic actuator.
9. A variable guide vane for an axial flow compressor comprising:
a first radially outer vane section;
a second radially inner vane section; said first and second vane sections angularly adjustable relative to each other about a longitudinal radial axis of said vane; and
wherein said first and second vane sections are secured to respective shafts lying on said radial axis, each of said shafts being independently rotatable.
10. The variable guide vane of claim 9 wherein said first and second vane sections interface along a horizontal split line substantially perpendicular to said longitudinal axis.
11. The variable guide vane of claim 9 wherein said horizontal split line is located about mid-way along a radial length dimension of said vane.
12. The variable guide vane of claim 9 wherein said first and second vane sections are secured to respective shafts lying on said radial axis, each of said shafts being independently rotatable.
13. A method of eliminating rotating stall aerodynamic excitation associated with axial flow turbine compressor inlet guide vanes comprising:
(a) splitting each variable guide vane in a row of such inlet guide vanes to form a radially inner section and a radially outer section; and
(b) adjusting relative angular positions of said radially inner and radially outer sections relative to a direction of flow of air across said guide vanes.
14. The method of claim 13 wherein said radially inner and radially outer sections are adjusted by separate ring gears.
15. The method of claim 13 including selecting a radial length for each section based on computational fluid dynamics predictions.
16. The method of claim 13 comprising angularly offsetting said radially inner and radially outer sections during start-up and shut-down.
17. The method of claim 16 comprising reducing the angular offset between said radially inner and radially outer sections substantially to zero during normal full load operation.
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US11/808,314 US20100260591A1 (en) | 2007-06-08 | 2007-06-08 | Spanwise split variable guide vane and related method |
CH00809/08A CH702692B1 (en) | 2007-06-08 | 2008-05-28 | Variable vane and method for removing an aerodynamic excitation. |
DE102008002867A DE102008002867A1 (en) | 2007-06-08 | 2008-05-28 | Split span adjustable vane and associated method |
CNA2008101100478A CN101319683A (en) | 2007-06-08 | 2008-05-29 | Rotatable guiding blade and related method |
JP2008148823A JP2008303877A (en) | 2007-06-08 | 2008-06-06 | Span divided variable guide vane and method related thereto |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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US11/808,314 US20100260591A1 (en) | 2007-06-08 | 2007-06-08 | Spanwise split variable guide vane and related method |
Publications (1)
Publication Number | Publication Date |
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US20100260591A1 true US20100260591A1 (en) | 2010-10-14 |
Family
ID=39942279
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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US11/808,314 Abandoned US20100260591A1 (en) | 2007-06-08 | 2007-06-08 | Spanwise split variable guide vane and related method |
Country Status (5)
Country | Link |
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US (1) | US20100260591A1 (en) |
JP (1) | JP2008303877A (en) |
CN (1) | CN101319683A (en) |
CH (1) | CH702692B1 (en) |
DE (1) | DE102008002867A1 (en) |
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-
2007
- 2007-06-08 US US11/808,314 patent/US20100260591A1/en not_active Abandoned
-
2008
- 2008-05-28 CH CH00809/08A patent/CH702692B1/en not_active IP Right Cessation
- 2008-05-28 DE DE102008002867A patent/DE102008002867A1/en not_active Withdrawn
- 2008-05-29 CN CNA2008101100478A patent/CN101319683A/en active Pending
- 2008-06-06 JP JP2008148823A patent/JP2008303877A/en not_active Withdrawn
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US20100068049A1 (en) * | 2008-09-12 | 2010-03-18 | General Electric Company | Features to properly orient inlet guide vanes |
US20130028716A1 (en) * | 2009-11-20 | 2013-01-31 | Snecma | Turbine engine having a stage of variable-pitch stator vanes with independent control |
US9429169B2 (en) * | 2009-11-20 | 2016-08-30 | Snecma | Turbine engine having a stage of variable-pitch stator vanes with independent control |
CN102536893A (en) * | 2010-12-21 | 2012-07-04 | 哈米尔顿森德斯特兰德公司 | Air cycle machine compressor rotor |
US9903389B2 (en) * | 2011-03-07 | 2018-02-27 | Mitsubishi Hitachi Power Systems, Ltd. | Axial-flow compressor and modification method |
US20120230813A1 (en) * | 2011-03-07 | 2012-09-13 | Hitachi, Ltd. | Axial-Flow Compressor and Modification Method |
US9103228B2 (en) | 2011-08-08 | 2015-08-11 | General Electric Company | Variable stator vane control system |
CN102588329A (en) * | 2012-03-13 | 2012-07-18 | 张仁田 | Axial-flow type water pump with blade-type adjustable line segment |
US10472978B2 (en) | 2015-12-07 | 2019-11-12 | Rolls-Royce Plc | Fan blade apparatus |
US10358934B2 (en) | 2016-04-11 | 2019-07-23 | United Technologies Corporation | Method and apparatus for adjusting variable vanes |
US10450889B2 (en) * | 2016-06-14 | 2019-10-22 | Rolls-Royce Plc | Compressor geometry control |
DE102016122696A1 (en) | 2016-11-24 | 2018-05-24 | Rolls-Royce Deutschland Ltd & Co Kg | Entry guide wheel for a turbomachine |
US10273976B2 (en) | 2017-02-03 | 2019-04-30 | General Electric Company | Actively morphable vane |
US10711797B2 (en) * | 2017-06-16 | 2020-07-14 | General Electric Company | Inlet pre-swirl gas turbine engine |
US10724435B2 (en) | 2017-06-16 | 2020-07-28 | General Electric Co. | Inlet pre-swirl gas turbine engine |
US10794396B2 (en) | 2017-06-16 | 2020-10-06 | General Electric Company | Inlet pre-swirl gas turbine engine |
US10815886B2 (en) | 2017-06-16 | 2020-10-27 | General Electric Company | High tip speed gas turbine engine |
US11280212B2 (en) * | 2019-01-24 | 2022-03-22 | MTU Aero Engines AG | Guide vane cascade for a turbomachine |
US11480111B2 (en) * | 2019-05-15 | 2022-10-25 | Honeywell International Inc. | Variable area turbine nozzle and method |
US11428160B2 (en) | 2020-12-31 | 2022-08-30 | General Electric Company | Gas turbine engine with interdigitated turbine and gear assembly |
FR3118652A1 (en) * | 2021-01-06 | 2022-07-08 | Safran Aircraft Engines | Actuating cylinder for turbomachine blade |
Also Published As
Publication number | Publication date |
---|---|
DE102008002867A1 (en) | 2008-12-11 |
CH702692B1 (en) | 2011-08-31 |
JP2008303877A (en) | 2008-12-18 |
CN101319683A (en) | 2008-12-10 |
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