EP2084368A1 - Turbinenschaufel - Google Patents
TurbinenschaufelInfo
- Publication number
- EP2084368A1 EP2084368A1 EP07820422A EP07820422A EP2084368A1 EP 2084368 A1 EP2084368 A1 EP 2084368A1 EP 07820422 A EP07820422 A EP 07820422A EP 07820422 A EP07820422 A EP 07820422A EP 2084368 A1 EP2084368 A1 EP 2084368A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- blade
- heat protection
- protection element
- turbine
- cooling
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
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
- 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
- F01D5/18—Hollow blades, i.e. blades with cooling or heating channels or cavities; Heating, heat-insulating or cooling means on blades
- F01D5/186—Film cooling
Definitions
- the invention relates to a turbine blade according to the preamble of claim 1.
- Turbomachines in particular gas turbines, are used in many areas to drive generators or work machines.
- a gas turbine usually has a rotatably mounted rotor surrounded by a stationary housing.
- the fixed assemblies of a gas turbine are collectively referred to as a stator.
- the energy content of a fuel is used to generate a rotational movement of the rotor component.
- the fuel is burned in a combustion chamber, compressed air being supplied by an air compressor.
- the working medium produced in the combustion chamber by the combustion of the fuel which is under high pressure and at high temperature, is guided via a turbine unit connected downstream of the combustion chamber, where it relaxes to perform work.
- a number of rotor blades which are usually combined into blade groups or rows of blades, are arranged thereon and drive the rotor components by impulse transmission of the flow medium.
- To guide the flow medium in the turbine unit also commonly associated guide blade rows are arranged between adjacent blade rows with the turbine housing.
- the turbine blades in particular the guide vanes, usually have an airfoil extending along a blade axis for suitable guidance of the working medium, to which a platform extending transversely to the blade axis can be integrally formed on the end side for fastening the turbine blade to the respective support body.
- a particularly high efficiency is a design target.
- an increase in the degree of efficiency can basically be achieved by increasing the outlet temperature at which the working medium leaves the combustion chamber and flows into the turbine unit. The temperatures reached during the operation of such a gas turbine are up to 1300 0 C.
- the exposed to these high temperatures of the working fluid components and components of the gas turbine are thus subject to high thermal stress.
- the affected components in particular the rotor blades and / or guide vanes of the turbine unit, are cooled.
- the turbine blades are usually provided with cooling channels, in particular, an effective and reliable cooling of the particular thermally loaded front edge of the respective turbine blade should be ensured.
- Coolant is usually used as coolant. This can be supplied to the respective turbine blade via a number of integrated into the blade or the blade profile coolant channels. Starting from these, the cooling air flows through the respectively provided regions of the turbine blades in exit channels branching off from them, as a result of which convective cooling of the blade inner and the blade wall is achieved. On the exit side, these channels are left open, so that the cooling air, after flowing through the turbine blade, flows out of the outlet openings, also referred to as film cooling holes, and forms a cooling film on the surface of the airfoil. As a result of this cooling-air film, the blade base body is largely protected on the surface from direct and intensive contact with the hot working medium flowing past at high speed.
- the outlet openings in this region are usually arranged uniformly along at least two rows aligned parallel to the front edge.
- the outlet channels are also generally aligned obliquely to the longitudinal direction of the turbine blade, which supports the formation of the protective, flowing on the surface cooling air film.
- the front edge of the blade can also be provided with a heat protection layer.
- This heat protection layer is expediently made of a more temperature-resistant material than that of the blade main body.
- the heat protection layer is characterized by a low coefficient of thermal conduction, whereby the temperature load of the base material of the bluff body is reduced.
- Turbine blade through such a heat protection layer in conjunction with a cooling of the leading edge region of the blade increases.
- this heat protection has the disadvantage that cracks in the heat protection layer occur after a certain time. These cracks reduce the protection of the blade body from the hot exhaust gas of the gas turbine, so that cracking may also occur due to the increased thermal load in the base body of the turbine blade. Such cracks in the blade body endanger the reliability and can lead to failure of the gas turbine.
- a modular turbine blade of the aforementioned type is known.
- the turbine blade comprises a cast base body with an airfoil profile on which there are provided on the inflow edge side a plurality of cooling air blowout slots, which are provided by a blade airfoil on the airfoil. fil laterally mounted fender are covered at a distance.
- the cooling air emerging from the slots cools the torn leading edge in the manner of impingement cooling and, following the impingement cooling, is deflected by the sheet in such a way that it can leave the modular turbine blade in the area of the pressure side face and suction side face.
- the invention is therefore based on the object to provide a turbine blade of the type mentioned above, which ensures a particularly high reliability of the gas turbine with simple means even when used in high flow temperatures.
- the invention is based on the consideration that, especially with regard to the reliability and economy of a gas turbine, the turbine blades should have as long as possible by a suitably selected heat protection.
- the fact should be taken into account that just the leading edge of the turbine blade is thermally heavily loaded. This should therefore be specially protected
- the heat protection element is mounted at a distance to the blade body in the leading edge region, whereby a direct contact of the heat protection element is avoided with the blade body.
- its outer surface in the leading edge region is provided with a number of secondary cooling channels, these running from the main cooling channel to the blade main body outer surface.
- These auxiliary cooling channels are arranged homogeneously distributed behind the heat protection element for effective cooling in the leading edge region of the blade body.
- stresses and resulting cracks can be avoided.
- this has a number of its outer surface extending in the direction of the blade main body outlet channels. This trained to guide a cooling flow channel also serves as a connecting element between the heat protection element and the blade body.
- the outlet channel protrudes at one end into a main cooling channel formed in the blade inside, wherein the medium flowing in the main cooling channel medium can flow to cool the heat protection element on the outer surface.
- the particularly critical region namely the leading edge region of the turbine blade
- the particularly critical region is particularly effectively protected from the high temperatures of the working medium of the turbine.
- the cooling takes place in such a way that a cooling flow from the main cooling channel is partly conducted through the outlet channels of the heat protection element onto its outer surface and flows partly from the main cooling channel, via the auxiliary cooling channels of the blade base body, through the intermediate space formed by the heat protection element and the blade base body.
- a protective film is formed on the outer surface of the heat protection element.
- This cooling film prevents direct contact of the hot working medium of the turbine with the heat protection element, whereby the temperature load of the impinged outer surface is reduced.
- the still occurring increase in the temperature of the heat protection element does not affect directly on the temperature of the blade body in the leading edge region, since the heat protection element is arranged at a distance from the blade body.
- the heat transfer between the heat protection element and the blade body is also by the flowing between the inner surface of the heat protection member and the blade body outer surface Cooling medium significantly reduced by the heat in the leading edge area is removed by the internal cooling flow.
- the heat protection element has a shape adapted to the profile of the blade body in the leading edge region. This ensures that the turbine blade has a flow-optimized shape in the leading edge region even after the attachment of the heat protection element.
- the form of the heat protection element corresponding to the blade body leads to a uniform expansion of the gap in the leading edge region.
- the cooling medium flows at a predominantly constant speed along the blade body outer surface and the inner surface of the heat protection element, whereby the cooling in the leading edge region of the turbine blade is particularly uniform.
- the heat protection element is made of a material which is more temperature-resistant than the blade body. Since the heat protection element is directly impinged by the hot working medium during operation of the turbine, it is precisely this component that is exposed to a high temperature load. Therefore, the heat protection element should be made of a particularly temperature-resistant material to ensure above all the reliability and minimize the downtime of the turbine.
- the heat protection element is designed for an impingement cooling for a particularly effective cooling, this is achieved by keeping the distance of the heat protection element to the blade main body sufficiently low.
- the heat protection element is preferably attached at a distance of 1 mm to 3 mm from the blade base body. assigns. Just a heat protection element attached to this distance in the leading edge region of the turbine blade ensures a sufficiently high impact velocity of the cooling medium on the inner surface of the heat protection element, whereby a particularly effective cooling is achieved by impingement cooling. Since the static pressure in the main cooling channel of the blade base body is predetermined, the impact velocity of the cooling flow is determined, for example, in addition to, for example, the diameter of the auxiliary cooling channels, above all by the distance between the heat protection element and the blade main body.
- a sufficiently high velocity of the cooling medium immediately before impinging on the inner surface of the heat protection element is necessary because this intimate contact between the cooling medium and the inner surface of the heat protection element is achieved.
- the auxiliary cooling channels are arranged substantially perpendicular to the inner surface of the heat protection element.
- the cooling flow from the main cooling channel is perpendicular to the inner surface of the heat protection element, whereby a large part of the kinetic energy of the cooling medium is used for a particularly intimate contact between the particles in the cooling flow and the inner surface of the heat protection element.
- the heat of the heat protection element is transferred to the inner cooling stream in a particularly effective manner and transported away.
- the heat protection element in the edge regions of the turbine blade is connected to the blade main body.
- the heat protection element can advantageously be used at the points of the turbomachine where components and assemblies of the thermal turbomachine are charged with the hot working medium.
- the use of the heat protection element for protecting the leading edge region of the turbine blade is particularly preferred since the temperature load of the blade main body in this region is particularly high.
- such a heat protection system minimizes the downtime of the gas turbine, since the life is increased by the heat protection element.
- the advantages achieved by the invention are, in particular, that an effective protection of the leading edge region of the turbine blade against the high temperatures of the working medium of the turbines is provided by the heat protection element arranged upstream of the blade main body of the turbine blade.
- the heat protection element allows the use of an impingement cooling, whereby the heat protection element can be cooled particularly effectively.
- the heat protection element prevents any cracks that may arise from the outer surface of the heat protection element from spreading into the blade base body.
- FIG. 5 shows a cross section through a turbine blade provided with a heat protection element
- FIG. 6 shows, in an alternative embodiment, a turbine blade with a heat protection element integrated in the leading edge region of the blade base body.
- the gas turbine 1 has a compressor 2 for combustion air, a combustion chamber 4 and a turbine unit 6 for driving the compressor 2 and a generator, not shown, or a working machine.
- the turbine unit 6 and the compressor 2 are arranged on a common, also called turbine rotor turbine shaft 8, with which the generator or the working machine is connected, and which is rotatably mounted about its central axis 9.
- the combustion chamber 4 designed in the manner of an annular combustion chamber is equipped with a number of burners 10 for the combustion of a liquid or gaseous fuel.
- the turbine unit 6 has a number of rotatable blades 12 connected to the turbine shaft 8.
- the blades 12 are arranged in a ring on the turbine shaft 8 and thus form a number of blade rows.
- the turbine unit 6 comprises a number of fixed vanes 14, which are also fixed in a ring shape with the formation of rows of vanes on an inner casing 16 of the turbine unit 6.
- the blades 12 serve to drive the turbine shaft 8 by impulse transfer from the turbine unit 6 flowing through the working medium M.
- the vanes 14, however, serve to guide the flow of the working medium M between two seen in the flow direction of the working medium M consecutive blade rows or blade rings.
- a successive pair of a ring of vanes 14 or a row of vanes and a ring of blades 12 or a blade row is also referred to as a turbine stage.
- Each vane 14 has a platform 18, which is arranged to fix the respective vane on the inner housing 16 of the turbine unit 6 as a wall element.
- the platform 18 is - as well as the turbine blade 12, 14 - while a comparatively thermally heavily loaded component.
- Each blade 12 is in an analogous manner via a also as
- a guide ring 21 is arranged on the inner housing 16 of the turbine unit 6 between the spaced-apart platforms 18 of the guide vanes 14 of two adjacent guide blade rows. The outer surface of each guide ring 21 is also exposed to the hot, the turbine unit 6 flowing through the working medium M and spaced in the radial direction from the outer end of the opposite blades 12 by a gap.
- the guide rings 21 arranged between adjacent guide blade rows serve in particular as cover elements, which protect the inner housing 16 or other housing-built-in components against overstressing of the working medium M flowing through the turbine 6.
- the combustion chamber 4 is designed in the embodiment as a so-called annular combustion chamber, in which a plurality of circumferentially around the turbine shaft 8 arranged around burners 10 opens into a common combustion chamber.
- the combustion chamber 4 in its entirety is designed as an annular structure that is positioned around the turbine shaft 8.
- the combustion chamber 4 is designed for a comparatively high temperature of the working medium M of about 1000 0 C to 1600 0 C.
- the rotor blades 12 -as shown in FIG. 2 - have a heat protection element 22 mounted in the leading edge region.
- Each of the heat shield elements 22 attached to the rotor blades 12 is equipped on the working medium side with a particularly heat-resistant protective layer such as, for example, ceramic or made of a high-temperature-resistant material.
- the turbine blade 12, 14 is provided with a number of secondary cooling channels 24 in the leading edge region.
- the likewise in the leading edge region of the turbine blade 12, 14 mounted and projecting into a main cooling channel 26 outlet channels 28 are used in addition to the leadership of the cooling medium K as fastening elements for the heat protection element 22.
- the preferably used as cooling medium K cooling air K flows, due to the main cooling channel 26 of the blade body 30 prevailing higher pressure relative to the ambient pressure in the turbine unit 6, via the subcooling channels 24 in the space formed between the outer surface 32 of the blade body 30 and the inner surface 34 of the heat protection member 22 and through the Exit channels 28 of the heat protection element 22, wherein the effluent from the outlet channels 28 cooling air K forms a protective film between the working medium M and the outer surface 36 of the heat protection member 22.
- the cooling air K escaping from the secondary cooling channels 24 of the blade main body 30 flows against the inner surface 34 of the heat protection element 22 and cools them by the resulting impact cooling effect.
- FIG. 3 and 4 show the heat protection element 22 in two different sectional views, it being apparent from the longitudinal section of the heat protection element 22 shown in FIG. 3 that the outlet channels 28 are arranged one behind the other viewed in the longitudinal direction of the heat protection element 22 and wherein each outlet channel 28 extends from the outer surface 36 of the heat protection member 22 extends to the inner surface 34 toward. As shown in FIG. 4, the exit channels 28 can be arranged centrally in the longitudinal direction of the heat protection element 22.
- the heat protection element 22 has a shape adapted to the profile of the blade body 30 in the leading edge region. This achieves, inter alia, that the turbine window 12, 14 also has a flow-optimized shape even after the heat protection element 22 has been attached to the blade main body 30.
- a bent heat protection element 22 causes a constant distance between the inner surface 34 of the heat protection member 22 and the outer surface 32 of the blade body 30, whereby a particularly effective cooling in this area is made possible.
- the cooling air K required for cooling flows from the main cooling channel 26 of the turbine blade 12, 14 through the auxiliary cooling channels 24 and the outlet channels 28, resulting in a cooling film on the Outer surface 36 of the heat protection element 22 forms.
- the cooling of the inner surface 34 of the heat protection element 22 and the Outer surface 32 of the blade body 30 in the leading edge region of the turbine blade 12, 14 takes place by the outflow of the cooling air K from the secondary cooling channels 24, wherein the inner surface 34 of the heat protection element 22 is cooled particularly effectively by the impact cooling effect occurring.
- the auxiliary cooling channels 24 are preferably arranged in such a way that the cooling air K flowing out of the auxiliary cooling channels 24 impinges perpendicular to the inner surface 34 of the heat protection element 22 .
- the distance of the heat protection element 22 to the blade body 30 is preferably to be chosen so that an intimate contact between the cooling air K and the baffle is effected by a sufficiently high flow rate of the cooling medium K when hitting the inner surface 34 of the heat protection element 22 and thus the impact cooling effect established.
- FIG. 1 A particularly expedient embodiment of the turbine blade 12, 14 with the heat protection element 22 according to the invention is shown in FIG.
- the heat protection element 22 has been integrated into the leading edge region of the blade body 30, whereby the original outer shape of the turbine blade 12, 14 is maintained in an advantageous manner.
- the aerodynamic design of the turbomachine is thus not changed, whereby a reduction in the efficiency of the gas turbine, for example, due to vortex formations on the outer edges in a externally attached to the blade body 30 heat protection element 22 is prevented.
- the gap between the heat protection element 22 and the blade main body 30 required for producing impingement cooling is achieved in this special embodiment of the turbine blade 12, 14 by placing the heat protection element 22 on a recess 38 present in the blade base body 30. This is the extending into the flow channel of the gas turbine outer surface of the turbine blade 12, 14th partially formed by the outer surface of the heat protection element 22.
- the free ends of the heat protection element 22 according to FIG. 5 are integrally formed flush with the blade walls formed by the base body 30 in order to achieve an offset-free surface of the turbine blade 12, 14.
- the part of the main body 30, which is opposite to the heat protection element 22, is set back to the blade interior, so that the edge regions of the heat protection element 22 are connected to the blade body.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Turbine Rotor Nozzle Sealing (AREA)
Description
Claims
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP07820422A EP2084368B1 (de) | 2006-10-30 | 2007-09-20 | Turbinenschaufel |
PL07820422T PL2084368T3 (pl) | 2006-10-30 | 2007-09-20 | Łopatka turbiny |
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP06022622A EP1930544A1 (de) | 2006-10-30 | 2006-10-30 | Turbinenschaufel |
EP07820422A EP2084368B1 (de) | 2006-10-30 | 2007-09-20 | Turbinenschaufel |
PCT/EP2007/059989 WO2008052846A1 (de) | 2006-10-30 | 2007-09-20 | Turbinenschaufel |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2084368A1 true EP2084368A1 (de) | 2009-08-05 |
EP2084368B1 EP2084368B1 (de) | 2010-03-03 |
Family
ID=37945313
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP06022622A Withdrawn EP1930544A1 (de) | 2006-10-30 | 2006-10-30 | Turbinenschaufel |
EP07820422A Not-in-force EP2084368B1 (de) | 2006-10-30 | 2007-09-20 | Turbinenschaufel |
Family Applications Before (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP06022622A Withdrawn EP1930544A1 (de) | 2006-10-30 | 2006-10-30 | Turbinenschaufel |
Country Status (10)
Country | Link |
---|---|
US (1) | US20100068069A1 (de) |
EP (2) | EP1930544A1 (de) |
JP (1) | JP2010508461A (de) |
CN (1) | CN101535601A (de) |
AT (1) | ATE459784T1 (de) |
DE (1) | DE502007003043D1 (de) |
ES (1) | ES2341384T3 (de) |
PL (1) | PL2084368T3 (de) |
RU (1) | RU2405940C1 (de) |
WO (1) | WO2008052846A1 (de) |
Families Citing this family (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CH700687A1 (de) * | 2009-03-30 | 2010-09-30 | Alstom Technology Ltd | Gekühltes bauteil für eine gasturbine. |
US9399271B2 (en) * | 2010-12-28 | 2016-07-26 | Rolls-Royce Corporation | Heat treating and brazing of an object |
EP3105425B1 (de) * | 2014-02-13 | 2019-03-20 | United Technologies Corporation | Gasturbinenmotorkomponentenkühlkreislauf mit lüftungssockel |
US10301945B2 (en) * | 2015-12-18 | 2019-05-28 | General Electric Company | Interior cooling configurations in turbine rotor blades |
CN105422188A (zh) * | 2016-01-13 | 2016-03-23 | 北京航空航天大学 | 一种带隔热罩式复合冷却结构的涡轮叶片 |
US10577942B2 (en) * | 2016-11-17 | 2020-03-03 | General Electric Company | Double impingement slot cap assembly |
US20190024513A1 (en) * | 2017-07-19 | 2019-01-24 | General Electric Company | Shield for a turbine engine airfoil |
KR102028803B1 (ko) * | 2017-09-29 | 2019-10-04 | 두산중공업 주식회사 | 가스 터빈 |
US11286783B2 (en) * | 2020-04-27 | 2022-03-29 | Raytheon Technologies Corporation | Airfoil with CMC liner and multi-piece monolithic ceramic shell |
Family Cites Families (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB841117A (en) * | 1957-08-02 | 1960-07-13 | Rolls Royce | Improvements in or relating to stator blades of fluid machines |
GB995182A (en) * | 1963-06-20 | 1965-06-16 | Rolls Royce | Improvements in or relating to gas turbine engine combustion equipment |
US3269700A (en) * | 1964-12-07 | 1966-08-30 | United Aircraft Corp | Heat shield for turbine strut |
US3423069A (en) * | 1967-09-29 | 1969-01-21 | Trw Inc | Airfoil |
JPS527482B2 (de) * | 1972-05-08 | 1977-03-02 | ||
US4026659A (en) * | 1975-10-16 | 1977-05-31 | Avco Corporation | Cooled composite vanes for turbine nozzles |
JPS5390509A (en) * | 1977-01-20 | 1978-08-09 | Koukuu Uchiyuu Gijiyutsu Kenki | Structure of air cooled turbine blade |
JP4027430B2 (ja) * | 1996-12-02 | 2007-12-26 | シーメンス アクチエンゲゼルシヤフト | タービン翼並びにガスタービン設備におけるその使用 |
DE19848104A1 (de) * | 1998-10-19 | 2000-04-20 | Asea Brown Boveri | Turbinenschaufel |
US6709230B2 (en) * | 2002-05-31 | 2004-03-23 | Siemens Westinghouse Power Corporation | Ceramic matrix composite gas turbine vane |
US7011502B2 (en) * | 2004-04-15 | 2006-03-14 | General Electric Company | Thermal shield turbine airfoil |
US7871246B2 (en) * | 2007-02-15 | 2011-01-18 | Siemens Energy, Inc. | Airfoil for a gas turbine |
-
2006
- 2006-10-30 EP EP06022622A patent/EP1930544A1/de not_active Withdrawn
-
2007
- 2007-09-20 EP EP07820422A patent/EP2084368B1/de not_active Not-in-force
- 2007-09-20 WO PCT/EP2007/059989 patent/WO2008052846A1/de active Application Filing
- 2007-09-20 ES ES07820422T patent/ES2341384T3/es active Active
- 2007-09-20 DE DE502007003043T patent/DE502007003043D1/de active Active
- 2007-09-20 US US12/447,972 patent/US20100068069A1/en not_active Abandoned
- 2007-09-20 JP JP2009533769A patent/JP2010508461A/ja active Pending
- 2007-09-20 CN CNA2007800407001A patent/CN101535601A/zh active Pending
- 2007-09-20 PL PL07820422T patent/PL2084368T3/pl unknown
- 2007-09-20 RU RU2009120554/06A patent/RU2405940C1/ru not_active IP Right Cessation
- 2007-09-20 AT AT07820422T patent/ATE459784T1/de active
Non-Patent Citations (1)
Title |
---|
See references of WO2008052846A1 * |
Also Published As
Publication number | Publication date |
---|---|
ATE459784T1 (de) | 2010-03-15 |
CN101535601A (zh) | 2009-09-16 |
DE502007003043D1 (de) | 2010-04-15 |
EP1930544A1 (de) | 2008-06-11 |
JP2010508461A (ja) | 2010-03-18 |
EP2084368B1 (de) | 2010-03-03 |
PL2084368T3 (pl) | 2010-07-30 |
RU2405940C1 (ru) | 2010-12-10 |
ES2341384T3 (es) | 2010-06-18 |
WO2008052846A1 (de) | 2008-05-08 |
US20100068069A1 (en) | 2010-03-18 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP2084368B1 (de) | Turbinenschaufel | |
DE60027390T2 (de) | Gekühlte Gasturbinenschaufel und deren Herstellungsmethode | |
DE60224339T2 (de) | Kühleinsatz mit tangentialer Ausströmung | |
DE60018817T2 (de) | Gekühlte Gasturbinenschaufel | |
DE102009043866B4 (de) | Turbinenlaufschaufel für eine Turbomaschine und Verfahren zur Reduktion von Bugwelleneffekten | |
DE102011053930B4 (de) | Vorrichtung und Verfahren zur Kühlung von Plattformabschnitten von Turbinenrotorschaufeln | |
EP1947293B1 (de) | Leitschaufel für eine Gasturbine | |
DE2943464A1 (de) | Dichtungsvorrichtung fuer ein gasturbinentriebwerk | |
DE102008002890A1 (de) | Wechselseitig gekühltes Turbinenleitrad | |
DE102010060280A1 (de) | Schaufelblatthitzeschild | |
EP1659262A1 (de) | Turbinenschaufel für eine Gasturbine, Verwendung einer Turbinenschaufel sowie Verfahren zum Kühlen einer Turbinenschaufel | |
EP3121371B1 (de) | Turbine mit gekühlten turbinenleitschaufeln | |
EP1245806B1 (de) | Gekühlte Gasturbinenschaufel | |
EP1614859A1 (de) | Filmgekühlte Turbinenschaufel | |
EP1656497B1 (de) | Diffusor zwischen verdichter und brennkammer einer gasturbine angeordnet | |
EP1409926A1 (de) | Prallkühlvorrichtung | |
EP3336313A1 (de) | Turbinen-laufschaufelanordnung für eine gasturbine und verfahren zum bereitstellen von dichtluft in einer turbinen-laufschaufelanordnung | |
EP1249578B1 (de) | Kühlung einer Gasturbine | |
DE102019104814B4 (de) | Mit einem Einsatzträger ausgestattete Turbinenschaufel | |
EP1510653B1 (de) | Gekühlte Turbinenschaufel | |
EP1731715A1 (de) | Übergangsbereich zwischen einer Brennkammer und einer Turbineneinheit | |
WO2004090423A1 (de) | Hitzeschildelement | |
WO2000060219A1 (de) | Strömungsmaschine mit einer kühlbaren anordnung von wandelementen und verfahren zur kühlung einer anordnung von wandelementen | |
DE102016124147A1 (de) | Innenkühlkonfigurationen in Turbinenrotorschaufeln | |
DE102009044584A1 (de) | Einrichtung in Zusammenhang mit Turbinenschaufelkühlöffnungen |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
17P | Request for examination filed |
Effective date: 20090409 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC MT NL PL PT RO SE SI SK TR |
|
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
DAX | Request for extension of the european patent (deleted) | ||
GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC MT NL PL PT RO SE SI SK TR |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: FG4D Free format text: NOT ENGLISH |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: NV Representative=s name: SIEMENS SCHWEIZ AG Ref country code: CH Ref legal event code: EP |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: FG4D |
|
REF | Corresponds to: |
Ref document number: 502007003043 Country of ref document: DE Date of ref document: 20100415 Kind code of ref document: P |
|
REG | Reference to a national code |
Ref country code: SE Ref legal event code: TRGR |
|
REG | Reference to a national code |
Ref country code: ES Ref legal event code: FG2A Ref document number: 2341384 Country of ref document: ES Kind code of ref document: T3 |
|
REG | Reference to a national code |
Ref country code: NL Ref legal event code: VDEP Effective date: 20100303 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20100303 |
|
REG | Reference to a national code |
Ref country code: PL Ref legal event code: T3 |
|
LTIE | Lt: invalidation of european patent or patent extension |
Effective date: 20100303 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20100303 Ref country code: FI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20100303 Ref country code: LV Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20100303 |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: FD4D |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: CY Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20100303 Ref country code: EE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20100303 Ref country code: GR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20100604 Ref country code: IE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20100303 Ref country code: NL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20100303 Ref country code: RO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20100303 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20100303 Ref country code: IS Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20100703 Ref country code: CZ Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20100303 Ref country code: BG Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20100603 |
|
PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: PT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20100705 Ref country code: DK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20100303 |
|
26N | No opposition filed |
Effective date: 20101206 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20101119 Year of fee payment: 4 |
|
BERE | Be: lapsed |
Owner name: SIEMENS A.G. Effective date: 20100930 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MC Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20100930 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: BE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20100930 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: GB Payment date: 20110915 Year of fee payment: 5 Ref country code: SE Payment date: 20110908 Year of fee payment: 5 Ref country code: PL Payment date: 20110824 Year of fee payment: 5 Ref country code: FR Payment date: 20111005 Year of fee payment: 5 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20100303 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: IT Payment date: 20100930 Year of fee payment: 4 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: ES Payment date: 20111013 Year of fee payment: 5 |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: PL |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R119 Ref document number: 502007003043 Country of ref document: DE Effective date: 20120403 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LI Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20110930 Ref country code: DE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20120403 Ref country code: CH Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20110930 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: HU Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20100904 Ref country code: LU Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20100920 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: TR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20100303 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20120921 |
|
REG | Reference to a national code |
Ref country code: SE Ref legal event code: EUG |
|
GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20120920 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: ST Effective date: 20130531 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: GB Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20120920 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: FR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20121001 Ref country code: IT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20120920 |
|
REG | Reference to a national code |
Ref country code: ES Ref legal event code: FD2A Effective date: 20131022 |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: MM01 Ref document number: 459784 Country of ref document: AT Kind code of ref document: T Effective date: 20120920 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: PL Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20120920 |
|
REG | Reference to a national code |
Ref country code: PL Ref legal event code: LAPE |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: AT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20120920 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: ES Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20120921 |