EP2347101B1 - Turbine à gaz et moteur à turbine à gaz associé - Google Patents
Turbine à gaz et moteur à turbine à gaz associé Download PDFInfo
- Publication number
- EP2347101B1 EP2347101B1 EP09827201.6A EP09827201A EP2347101B1 EP 2347101 B1 EP2347101 B1 EP 2347101B1 EP 09827201 A EP09827201 A EP 09827201A EP 2347101 B1 EP2347101 B1 EP 2347101B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- turbine
- gas turbine
- gas
- wall
- hollow
- 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.)
- Not-in-force
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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
- F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
- F01D25/24—Casings; Casing parts, e.g. diaphragms, casing fastenings
- F01D25/246—Fastening of diaphragms or stator-rings
-
- 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
- F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
- F01D25/24—Casings; Casing parts, e.g. diaphragms, casing fastenings
- F01D25/26—Double casings; Measures against temperature strain in casings
Definitions
- the invention relates to a gas turbine having a substantially hollow conical or hollow cylindrical, extending along a machine axis vane carrier and a segmented in the circumferential and / or axial direction in ring segments, substantially hollow cone-shaped or hollow cylindrical outer wall of an annular hot gas path whose ring segments by means of a number are fastened by hooking elements on the inside of the guide blade carrier.
- Gas turbines are used in many areas to drive generators or work machines.
- the energy content of a fuel is used to generate a rotational movement of a turbine shaft.
- 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, under high pressure and at high temperature, is guided via a turbine unit arranged 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 turbine shaft via a momentum transfer from the working medium.
- guide vanes are also usually arranged between adjacent rotor blade rows and connected to the turbine housing, which are combined into rows of guide blades. These are attached to a usually hollow cylindrical or hollow cone-shaped vane carrier.
- the hot gas channel is usually lined by so-called ring segments which form axial sections of the outer wall of the hot gas channel. These are usually fastened via hooking elements on the guide blade carrier, so that the entirety of the ring segments in the circumferential direction as well as the guide blade carrier form a hollow conical or hollow cylindrical structure.
- the components of the gas turbine can deform by different thermal expansion in different operating conditions, which has a direct influence on the size of the radial gap between the blades and the outer wall of the hot gas channel.
- These radial gaps are differently dimensioned when starting and stopping the turbine than in regular operation.
- the gas turbine components such as guide vane or outer wall are always to be dimensioned so that the radial gaps are kept sufficiently large to cause any damage to the gas turbine in any operating condition.
- a correspondingly comparatively generous design of the radial gaps leads to considerable losses in the efficiency.
- the invention is therefore based on the object to provide a gas turbine, which allows a particularly high efficiency while maintaining the greatest possible operational safety and life.
- interlocking elements of at least one of the ring segments of the input gas turbine engine are geometrically adjusted such that in the non-operating state the outer wall delimiting the hot gas path has a substantially elliptical cross-sectional contour in a section perpendicular to the machine axis.
- the invention is based on the consideration that a particularly high efficiency would be possible by reducing the radial gaps in regular operation, ie, for example, full load operation of the gas turbine.
- a comparatively large dimension of the radial gaps was required in particular because the turbine deforms differently in different operating states.
- an ovalization of the cylindrical or conically shaped components of the gas turbine occurs, which must be taken into account in the design of the radial gaps.
- the ovalization in the operation of the gas turbine should be kept as low as possible.
- This cross-sectional contour should be designed in such a way that the cross-sectional contour present at room temperature after installation of the gas turbine is then circular due to thermal deformations occurring in the operating state
- the thermal expansions should therefore not, as in the prior art JP 2005-042612 and JP 54-081409 to be suppressed.
- the ring segments described at the beginning with which the hot gas path is lined outside the rotor blades, correspondingly.
- the ring segments form in the axial section of the blades in the circumferential direction of the outer wall of the hot gas path, which thus together form the rotor blades the closest lying hollow cone-shaped or hollow cylindrical component of the gas turbine. Therefore, the cross-section perpendicular to the machine axis of the ring segments forming the outer wall of the hot gas path has the elliptical cross-sectional contour described in the inoperative state.
- the ring segments forming the outer wall of the hot gas path in the axial section of the rotor blades are usually hooked in the guide blade carrier via hooking elements. Since the vane support is a relatively solid component which has a comparatively large deformation during operation, the cross-sectional contour formed by all ring segments in the operating state is often determined by the attachment or clamping of the ring segments in the vane support and its deformation during operation. It is therefore not absolutely necessary to manufacture the cold contour of the external wall consisting of ring segments in elliptical form, since the deformation induced by the contact points on the interlocking elements is established anyway.
- the compensation of the ovalization of the guide vane carrier can therefore be achieved by advantageously only the individual hooking elements of the ring segments are adapted so that the outer wall of a substantially elliptical Has cross-sectional contour. Since these ring segments are exchangeable service parts, this makes it possible on the one hand to retrofit existing gas turbines, on the other hand to compensate for manufacturing errors in guide vanes and also a particularly simple adaptation to changing driving styles including other modified measures to reduce the radial gap.
- the length of the main and minor axes of the elliptical cross-sectional contour in each case selected such that the respective component has a substantially circular cross-sectional contour by its thermal deformation in the operating state in the production of the hollow cone-shaped or hollow cylindrical components of the gas turbine.
- This can be done, for example, by introducing an expected in operation by 90 degrees offset ovalization.
- the elliptical shape of these components is thus chosen so that the deformations are compensated in the operating state just so that the operation produces a circular cross-section and thus over the entire circumference of the gas turbine same radial gaps are present, d. h.,
- the radial gaps have no variance over the circumference. As a result, even in the construction of the radial gaps can be sized accordingly narrow, which has a higher efficiency of the gas turbine result.
- the interlocking elements are adapted in their radial length and / or arranged to change the radial position of the interlocking elements in a corresponding retaining groove of the guide blade carrier inserts. These then lie between the hooks of the hooking elements and the retaining groove and thus lead along the circumference to different radial positions of ring segments.
- De Facto can thus be provided either distributed along the circumference ring segments with different lengths radial entanglements in the vane support, or the Verhakungsetti the ring segments along a circumference are identical, in which case to change the radial Position of the ring segments along the circumference of different thickness supplements are used for the corresponding entanglements.
- the turbine shaft in the cold operating state, can be displaced in the direction of the hot gas flow, so that an enlargement of the radial gap occurs in the case of a hollow conical shape of the outer wall with enlargement of the radius in the direction of the hot gas flow in the cold inoperative state, and thus in the cold state (eg when starting the combustion process) Gas turbine), the remaining counter-ovalization represents no restriction for the achievable radial gap in the warm state. As a result, an even greater efficiency of the gas turbine can be achieved.
- such a gas turbine is used in a gas and steam turbine plant.
- the advantages achieved by the invention are, in particular, that a particularly high efficiency of the gas turbine is achieved by a reduction of the radial gaps by a targeted design of the hollow cone-shaped or hollow cylindrical components of a gas turbine such that they have a substantially elliptical cross-sectional contour in the inoperative state.
- a particularly high efficiency of the gas turbine is achieved by a reduction of the radial gaps by a targeted design of the hollow cone-shaped or hollow cylindrical components of a gas turbine such that they have a substantially elliptical cross-sectional contour in the inoperative state.
- 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 referred to as a turbine rotor turbine shaft 8, with which the generator or the working machine is connected, and which is rotatably mounted about its turbine axis 9.
- the running in the manner of an annular combustion chamber 4 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 stationary vanes 14, which are also attached in a donut-like manner to a vane support 16 of the turbine unit 6 to form rows of vanes.
- the blades 12 serve to drive the turbine shaft 8 by momentum 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 14 to a vane support 16 of the turbine unit 6 as a wall element.
- the platform 18 is a thermally comparatively heavily loaded component which forms the outer boundary of a hot gas channel for the working medium M flowing through the turbine unit 6.
- Each blade 12 is attached to the turbine shaft 8 in an analogous manner via a platform 19, also referred to as a blade root.
- each ring segment 21 is arranged on a guide blade carrier 16 of the turbine unit 6 respectively.
- the inner surface of each ring segment 21 is also exposed to the hot, the turbine unit 6 flowing through the working medium M and therefore limits the outside of the annular hot gas path as the outer wall.
- In the radial direction is the outer wall from the outer end of the opposite blades 12 spaced by a radial gap.
- the ring segments 21 arranged between adjacent guide blade rows serve in particular as cover elements which protect the guide blade carrier 16 or other housing built-in components against thermal overstress by the hot 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 open into a common combustion chamber space.
- the combustion chamber 4 is configured in its entirety as an annular structure which is positioned around the turbine shaft 8 around.
- FIG. 2 and FIG. 3 now schematically show the guide vane 16 of the gas turbine 1 in a cross section perpendicular to the turbine axis 9 once left in the inoperative state, ie at cold gas turbine 1, and right in the operating state, ie at operating temperature.
- the guide vane carrier 16 has a material temperature corresponding to the ambient temperature of the gas turbine.
- the operating temperature is much higher; beyond 100 ° C.
- the guide blade carrier 16 is composed of an upper segment 24 and a lower segment 26.
- the two segments 24, 26 are connected to one another via flanges 28 and each form a connecting joint 30 at their connection point.
- FIG. 2 4 illustrates a deformation of the prior art vane support 16 such that the distance between the peaks 32 of the respective upper and lower portions 24, 26 increases.
- the cross section of the guide blade carrier 16 thereby deforms into a vertical ellipse.
- a circular contour is shown for comparison in dashed line style.
- the turbine shaft 8 is displaceable along the turbine axis 9.
- the turbine shaft 8 In the cold state, that is, if there is an elliptical shape of the hot gas channel, then the turbine shaft 8 can be moved in the direction of the hot gas flow direction. As a result of the conical shape of the hot gas channel, this causes an enlargement of the radial gaps. Then, when in operation, a circular cross-section sets by thermal deformation, the turbine shaft 8 is displaced in the reverse direction to optimize the radial gap.
- the ring segments 21 can be configured by a correspondingly introduced ovalization so that the hot gas channel receives a circular cross-section during operation.
- the Verhakungs institute for fixing the ring segments 21 on the guide blade carrier 16 may be different lengths, ie be different lengths for different circumferential positions, or inserts between the hook and holding the guide vane 16 are introduced, which influence the radial position of the respective ring segments 21 with the same length Verhakungs instituten.
- the perpendicular to the machine axis cross-sectional contour of the Ring segments 21 formed radially outer outer wall of the annular hot gas channel is namely largely determined by the passed through the Verhakungs institute the ring segments deformation of the vane support 16. Accordingly, in 2 and FIG. 3 Instead of guide vanes 16 also be understood - then flangeless - the outer wall of the hot gas path of a gas turbine.
- the ovalization can be avoided in the operating state.
- the radial gaps can be designed correspondingly smaller, resulting in a significantly higher overall efficiency of the gas turbine 1 without sacrificing operational safety.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Turbine Rotor Nozzle Sealing (AREA)
Claims (5)
- Turbine ( 1 ) à gaz ayant un support ( 16 ) d' aubes directrices sensiblement en forme de cône creux ou de cylindre creux et s' étendant le long d'un axe de machine et une paroi extérieure d' un trajet annulaire pour du gaz chaud segmentée, dans la direction périphérique et/ou axiale, en segments ( 21 ) annulaires et sensiblement en forme de cône creux et/ou de cylindre creux, dont les segments ( 21 ) annulaires sont fixés au moyen d'un certains nombres d'éléments d' accrochage au côté intérieur du support ( 16 ) d' aubes directrices,
caractérisée en ce que
les éléments d' accrochage d' au moins l'un des segments ( 21 ) annulaires sont adaptés géométriquement de manière à ce que, dans l'état hors de fonctionnement suivant une coupe perpendiculaire à l'axe de la machine, la paroi extérieure délimitant le trajet pour du gaz chaud ait un contour de section transversale sensiblement en forme d' ellipse. - Turbine ( 1 ) à gaz suivant la revendication 1,
dans laquelle les longueurs du grand axe et du petit axe du contour de section transversale en forme d' ellipse sont choisies respectivement de manière à ce que la paroi extérieure ait, après la déformation thermique se produisant dans l'état de fonctionnement, un contour de section transversale sensiblement circulaire. - Turbine ( 1 ) à gaz suivant la revendication 1 ou 2,
dans laquelle les éléments d'accrochage sont adaptés dans leur longueur radiale et/ou pour des positions radiales différentes des éléments d' accrochage des cales sont disposées dans une rainure de maintien du support ( 16 ) d' aubes directrices. - Turbine ( 1 ) à gaz suivant les revendications 1 à 3,
qui comprend un arbre ( 8 ) de turbine ayant un certain nombre d' aubes ( 12 ) mobiles regroupées en rangées d' aubes mobiles et disposées tout autour d' un dispositif de palier de l' arbre ( 8 ) de la turbine, qui est conçu de manière à ce que l'arbre ( 8 ) de la turbine puisse coulisser le long de l' axe ( 9 ) de la turbine. - Installation de turbine à gaz et de turbine à vapeur ayant une turbine ( 1 ) à gaz suivant l'une des revendications 1 à 4.
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP09827201.6A EP2347101B1 (fr) | 2008-11-19 | 2009-09-15 | Turbine à gaz et moteur à turbine à gaz associé |
PL09827201T PL2347101T3 (pl) | 2008-11-19 | 2009-09-15 | Turbina gazowa i odpowiednia przemysłowa instalacja turbiny gazowej lub parowej |
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP08020190A EP2189630A1 (fr) | 2008-11-19 | 2008-11-19 | Turbine à gaz, support d'aube directrice pour une telle turbine à gaz, et moteur à turbine à gaz avec une telle turbine à gaz |
EP09827201.6A EP2347101B1 (fr) | 2008-11-19 | 2009-09-15 | Turbine à gaz et moteur à turbine à gaz associé |
PCT/EP2009/061936 WO2010057698A1 (fr) | 2008-11-19 | 2009-09-15 | Turbine à gaz |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2347101A1 EP2347101A1 (fr) | 2011-07-27 |
EP2347101B1 true EP2347101B1 (fr) | 2013-07-03 |
Family
ID=40532518
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP08020190A Withdrawn EP2189630A1 (fr) | 2008-11-19 | 2008-11-19 | Turbine à gaz, support d'aube directrice pour une telle turbine à gaz, et moteur à turbine à gaz avec une telle turbine à gaz |
EP09827201.6A Not-in-force EP2347101B1 (fr) | 2008-11-19 | 2009-09-15 | Turbine à gaz et moteur à turbine à gaz associé |
Family Applications Before (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP08020190A Withdrawn EP2189630A1 (fr) | 2008-11-19 | 2008-11-19 | Turbine à gaz, support d'aube directrice pour une telle turbine à gaz, et moteur à turbine à gaz avec une telle turbine à gaz |
Country Status (7)
Country | Link |
---|---|
US (1) | US9074490B2 (fr) |
EP (2) | EP2189630A1 (fr) |
JP (1) | JP5281167B2 (fr) |
CN (1) | CN102216570B (fr) |
ES (1) | ES2426099T3 (fr) |
PL (1) | PL2347101T3 (fr) |
WO (1) | WO2010057698A1 (fr) |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US8506245B2 (en) * | 2010-07-08 | 2013-08-13 | General Electric Company | Steam turbine shell |
JP5738127B2 (ja) * | 2011-09-01 | 2015-06-17 | 三菱日立パワーシステムズ株式会社 | 蒸気タービン |
EP3078448B1 (fr) * | 2015-04-10 | 2018-07-11 | Rolls-Royce Deutschland Ltd & Co KG | Procédé d'usinage d'un carter pour une turbomachine. |
ES2865387T3 (es) * | 2017-08-04 | 2021-10-15 | MTU Aero Engines AG | Segmento de paletas guía para una turbina |
KR102062594B1 (ko) * | 2018-05-11 | 2020-01-06 | 두산중공업 주식회사 | 베인 캐리어, 이를 포함하는 압축기 및 가스 터빈 |
Family Cites Families (23)
Publication number | Priority date | Publication date | Assignee | Title |
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US3169748A (en) * | 1962-12-06 | 1965-02-16 | Westinghouse Electric Corp | Turbine apparatus |
JPS5481409A (en) * | 1977-12-12 | 1979-06-28 | Hitachi Ltd | Turbine casing |
US4426191A (en) * | 1980-05-16 | 1984-01-17 | United Technologies Corporation | Flow directing assembly for a gas turbine engine |
JPS58160502A (ja) | 1982-03-19 | 1983-09-24 | Toshiba Corp | コンバインドサイクルプラントの起動方法 |
JPS62126225A (ja) * | 1985-11-25 | 1987-06-08 | Hitachi Ltd | タ−ビン過給機のタ−ビンケ−ス |
US5063661A (en) * | 1990-07-05 | 1991-11-12 | The United States Of America As Represented By The Secretary Of The Air Force | Method of fabricating a split compressor case |
US5605438A (en) * | 1995-12-29 | 1997-02-25 | General Electric Co. | Casing distortion control for rotating machinery |
CN1212323A (zh) * | 1998-05-13 | 1999-03-31 | 韩凤琳 | 热流涡轮机 |
EP1131537B1 (fr) | 1998-11-11 | 2004-10-06 | Siemens Aktiengesellschaft | Procede de fonctionnement d'une turbomachine |
EP1022439B1 (fr) * | 1999-01-20 | 2004-05-06 | ALSTOM Technology Ltd | Carter de turbine à vapeur ou à gaz |
US6409471B1 (en) * | 2001-02-16 | 2002-06-25 | General Electric Company | Shroud assembly and method of machining same |
ATE353416T1 (de) * | 2001-07-06 | 2007-02-15 | R & D Dynamics Corp | Hydrodynamische folien-gleitringdichtung |
GB2383380B (en) * | 2001-12-19 | 2005-05-25 | Rolls Royce Plc | Rotor assemblies for gas turbine engines |
US6691019B2 (en) * | 2001-12-21 | 2004-02-10 | General Electric Company | Method and system for controlling distortion of turbine case due to thermal variations |
US6715297B1 (en) * | 2002-09-20 | 2004-04-06 | General Electric Company | Methods and apparatus for supporting high temperature ducting |
US6811315B2 (en) * | 2002-12-18 | 2004-11-02 | Pratt & Whitney Canada Corp. | Compliant support for increased load capacity axial thrust bearing |
JP2005042612A (ja) * | 2003-07-22 | 2005-02-17 | Ishikawajima Harima Heavy Ind Co Ltd | ケーシング及びケーシングの変形防止システム並びにその方法 |
US7255929B2 (en) * | 2003-12-12 | 2007-08-14 | General Electric Company | Use of spray coatings to achieve non-uniform seal clearances in turbomachinery |
DE102004058487A1 (de) * | 2004-12-04 | 2006-06-14 | Mtu Aero Engines Gmbh | Gasturbine |
US7374396B2 (en) * | 2005-02-28 | 2008-05-20 | General Electric Company | Bolt-on radial bleed manifold |
US7681601B2 (en) * | 2005-08-24 | 2010-03-23 | Alstom Technology Ltd. | Inner casing of a rotating thermal machine |
US8801370B2 (en) * | 2006-10-12 | 2014-08-12 | General Electric Company | Turbine case impingement cooling for heavy duty gas turbines |
US8128353B2 (en) * | 2008-09-30 | 2012-03-06 | General Electric Company | Method and apparatus for matching the thermal mass and stiffness of bolted split rings |
-
2008
- 2008-11-19 EP EP08020190A patent/EP2189630A1/fr not_active Withdrawn
-
2009
- 2009-09-15 EP EP09827201.6A patent/EP2347101B1/fr not_active Not-in-force
- 2009-09-15 US US13/129,633 patent/US9074490B2/en not_active Expired - Fee Related
- 2009-09-15 PL PL09827201T patent/PL2347101T3/pl unknown
- 2009-09-15 CN CN200980146179.9A patent/CN102216570B/zh not_active Expired - Fee Related
- 2009-09-15 JP JP2011535935A patent/JP5281167B2/ja not_active Expired - Fee Related
- 2009-09-15 ES ES09827201T patent/ES2426099T3/es active Active
- 2009-09-15 WO PCT/EP2009/061936 patent/WO2010057698A1/fr active Application Filing
Also Published As
Publication number | Publication date |
---|---|
EP2347101A1 (fr) | 2011-07-27 |
CN102216570A (zh) | 2011-10-12 |
CN102216570B (zh) | 2014-03-05 |
US20110280721A1 (en) | 2011-11-17 |
JP5281167B2 (ja) | 2013-09-04 |
JP2012508843A (ja) | 2012-04-12 |
US9074490B2 (en) | 2015-07-07 |
ES2426099T3 (es) | 2013-10-21 |
WO2010057698A1 (fr) | 2010-05-27 |
EP2189630A1 (fr) | 2010-05-26 |
PL2347101T3 (pl) | 2013-12-31 |
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