WO2018036818A1 - Rotor muni d'une bague d'étanchéité segmentée - Google Patents

Rotor muni d'une bague d'étanchéité segmentée Download PDF

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Publication number
WO2018036818A1
WO2018036818A1 PCT/EP2017/070153 EP2017070153W WO2018036818A1 WO 2018036818 A1 WO2018036818 A1 WO 2018036818A1 EP 2017070153 W EP2017070153 W EP 2017070153W WO 2018036818 A1 WO2018036818 A1 WO 2018036818A1
Authority
WO
WIPO (PCT)
Prior art keywords
rotor
sealing
rotor according
support surface
segment
Prior art date
Application number
PCT/EP2017/070153
Other languages
German (de)
English (en)
Inventor
Peter Schröder
Fathi Ahmad
Karsten Kolk
Peter Kury
Mirko Milazar
Volker Vosberg
Vyacheslav Veitsman
Original Assignee
Siemens Aktiengesellschaft
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Siemens Aktiengesellschaft filed Critical Siemens Aktiengesellschaft
Publication of WO2018036818A1 publication Critical patent/WO2018036818A1/fr

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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
    • F01D11/00—Preventing or minimising internal leakage of working-fluid, e.g. between stages
    • F01D11/001—Preventing or minimising internal leakage of working-fluid, e.g. between stages for sealing space between stator blade and rotor
    • 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
    • F01D5/02—Blade-carrying members, e.g. rotors
    • F01D5/06—Rotors for more than one axial stage, e.g. of drum or multiple disc type; Details thereof, e.g. shafts, shaft connections

Definitions

  • the invention relates to a rotor of a gas turbine, wherein between the rotor blades of a first rotor disk and the rotor blades of a second rotor disk a plurality of sealing segments are arranged distributed in the circumference.
  • gas turbines there is fundamentally the problem that the rotor is best protected from the hot gas flowing through the gas turbine.
  • different sealing solutions are used between the individual rotor disks in the area of the intake of the rotor blades on the rotor disks.
  • sealing ring is formed by a plurality of individual distributed circumferentially arranged segments.
  • An exemplary embodiment is given for this purpose in EP 2 535 523 A2.
  • sealing segments are used, which are supported on both sides in a region lying radially below the rotor blades on a circumferential annular surface on the rotor disk.
  • the Ringflä ⁇ che on the rotor disk is in this case aligned facing the rotor axis, so that the centrifugal force leads to the sealing segment to a support on the annular surface of the rotor disk.
  • an axially opening receiving groove is present in an outer circumferential region of the sealing segment, into which a shoulder attached to the moving blade engages. This allows a mounting of the sealing segment with its positioning in its final position and subsequent approaching the adjoining blade with engagement of the paragraph in the receptacle ⁇ menut.
  • CA 2 921 257 AI discloses an embodiment in which the sealing segment is double-mounted on one side, wherein a shoulder on the sealing ⁇ segment engages in an axially opening annular groove in the rotor disk.
  • the sealing segment is supported inde ⁇ pendent of the position of the blade reliably to the rotor disk on this page.
  • a rotor according to the invention is used in particular for use in a gas turbine. Nevertheless, the solution according to the invention can be applied to a rotor of a steam turbine or other turbomachine. At least it requires a first rotor disk and a second rotor disk. It is provided that a plurality of first rotor blades are distributed in the circumference of the first rotor disk. Analog also includes the second rotor disk has a plurality of distributed in the circumference arrange ⁇ ter second blades. How the assembly of the fine guide takes place on the respective rotor disk is initially un ⁇ significant.
  • the rotor comprises a sealing ring formed from sealing segments, which extends between the first rotor disk and the second rotor disk.
  • Attachment of the sealing segments on the rotor discs is provided, that the first rotor disc a wei ⁇ send to the rotor axis first support surface and the second rotor disc analog Having a rotor axis facing second support surface.
  • first or second support surface is executed continuously or intermittently and it is also irrelevant whether the support surface has cylindrical, conical or other curved shape.
  • Essential in the orientation of the support surface is that a centrifugal force directed towards it, a secure position of the sealing segments is made possible with the inclusion of centrifugal force.
  • the sealing segments at the axially opposite sides have the sealing segments in a complementary to the first support surface and a first load surface komplemen ⁇ mentary to the second supporting surface second load surface. Accordingly, the load surfaces are arranged on the sealing segments on the radially outwardly facing side. This ensures at a centrifugal force in the sealing segments a system of load surfaces on the support surfaces.
  • the first rotor disc has an outwardly facing first Auflageflä ⁇ che, on which a first resting surface of the respective sealing segment for conditioning comes.
  • the invention provides that on the second rotor disk also pointing away from the rotor axis second bearing surface and on Sealing segment on the first resting surface axially opposite side, a second resting surface is arranged analogously to the investment of the first resting surface on the first bearing surface by abutment of the second resting surface on the second bearing surface on both sides a support of the sealing segment, so that a radial displacement can be prevented can.
  • the shape of support and resting surface is in this case to ⁇ next irrelevant as long as it is ensured that at ei ⁇ ner radially inwardly directed force on the sealing segment - axis at ⁇ play at standstill of the rotor with a horizontal rotor due to the force of gravity above at a position the rotor axis - a support of the sealing segment over the ⁇ sen resting surface on the support surface takes place.
  • a displacement of the sealing segment in the radial direction can be prevented directly by the rotor disk.
  • blade receiving grooves are advantageously present for receiving the rotor blades, which are in a particularly advantageous manner (parallel or inclined or bo ⁇ genförmig) along the rotor axis on both sides to an end face of the respective Rotor disc extend.
  • the shape of the support surface at Be Wegsichti ⁇ supply of absorbing the centrifugal forces and the support surface to the next ⁇ is arbitrary, it is advantageous if the contact surfaces are led off as a surface of revolution ⁇ support surfaces and / or. This can be either a pass ⁇ de surface of revolution as it is also acceptable even if the support surface and / or the bearing surface of the zueinan ⁇ spaced faces a surface of revolution are formed.
  • a Z-Y- is particularly preferably selected relieving surface or a conical surface with an angle to the Ro ⁇ gate axis of less than 15 ° as a surface of revolution. Furthermore, it is particularly advantageous to avoid an imbalance when a radiärsymmetrische embodiment ge ⁇ selected.
  • the support surfaces of the first rotor disk and the second rotor disk are either designed as a closed rotation surface or point
  • the bearing surfaces are also arranged radiärsymmetrisch with common consideration of all sealing segments advantageous.
  • a defined position of the sealing segments in the axial direction can be realized in different ways.
  • the first rotor ⁇ disc is numblerung mecanic transversely réellere ⁇ ADORABLE first end face and the second rotor disk has a one to numblerung mecanic transversely extending to the rotor disc second end face to the rotor axis, whereby in a particularly advantageous Way the first end face opposite the second end face is located.
  • one on the first end face substantially at the plant coming first collar surface and coming on the second end surface for abutment in the We ⁇ sentlichen second collar surface on the sealing segment.
  • the shape of the end face and the collar surface is irrelevant, provided that an axial centering of the sealing segment.
  • the end face can be formed at ⁇ play by bead-like, axially extending Erhe ⁇ environments.
  • the survey can be performed both annular and also a plurality of radially extending surveys can be used.
  • the Wennlie ⁇ ing end faces are made similar, as it just is not necessary that the axially ge ⁇ genübericide on the sealing collar segment surfaces are designed identically.
  • a minimum clearance is provided between the end surfaces and the flange surfaces, so that an un- problematic mounting of the seal segment between the end surfaces ⁇ is possible without causing jamming during assembly.
  • the arrangement of the support surface can be done in different position. Particularly advantageous is the Anord ⁇ drying the support surface axially extending on an approximately as (entspre ⁇ accordingly the shape of the supporting surface) forachelie ⁇ constricting rotor disc mounting projection. Thus, an edge of the fastening projection facing the rotor axis forms the support surface.
  • the facing the opposite rotor disk end of the support surface forms a free end of Befest Trentsvor ⁇ jump.
  • the free end of the fastening projection is arranged on an end face of the rotor disk forming the end of the blade retaining grooves.
  • the fastening projection extends beyond the front side.
  • the bearing surface can be formed by an edge of a mounting projection extending to the opposite rotor disk. With respect to the supporting surface and the bearing surface may be the same fastening ⁇ projection with a side facing to the rotor axis as the edge
  • Support surface and one of the rotor axis radially outwardly facing edge act as a support surface as well as the arrangement of two separate mounting projections is possible.
  • various possibilities are again available, wherein in a first particularly advantageous embodiment a first fastening projection of the first rotor disk is used to form the first rotor disk.
  • th support surface is closed ring-shaped.
  • the second fastening projection has at least two interruptions which separate the projection sections from one another.
  • the interruptions allow an advantageous installation of the sealing segments. It may be provided that a jump forward portion has an extension in the circumferential direction which is less than the length of the sealing segment in the circumferential direction, in contrast, the second cut Vorsprungab- be guided over the largely remaining circumference of the Fixed To ⁇ supply protrusion.
  • Projecting portions each with intermediate Unterbre ⁇ tions is used. It may be provided that the protrusion portions are each located between two blade retaining slots ⁇ .
  • the first fastening element can likewise be used.
  • gungsvorsprung alternatively to the annular embodiment also have a plurality of projection portions.
  • the first load surface can be formed in a particularly advantageous manner by a first attachment paragraph, which extends over at least 75% of the length of the sealing segment in the circumferential direction.
  • first attachment paragraph is carried out continuously or whether the first load surface is continuously present or whether the first load surface in this case has interruptions, ⁇ far whose faces together at least 75% of the length of the sealing segment.
  • the second load surface is formed flat ⁇ so advantageous from a second attachment shoulder analogous to the first load surface, which, however, extends in opposition to the advantageous embodiment of the first fixing heel at most over a length of 75% of the length of the sealing segment in the circumferential direction.
  • the length of the second fastening paragraph with the second load area is at least 25% of the length of the sealing segment in the circumferential direction.
  • Analogous to the first load surface or the first Befest Drab ⁇ rate may be provided that the second attachment paragraph extends continuously with the second load surface.
  • the second fastening shoulder is divided into at least two spaced-apart shoulder sections.
  • the interruption of the second attachment paragraph allows in a particularly advantageous manner, the assembly of the sealing segment on the rotor disk with equally un ⁇ broken second attachment projection.
  • the particularly advantageous embodiment of the rotor disks and the sealing segments leads to a possible mounting of the sealing segments with an obliquely axially radial insertion of the sealing segments on the first rotor disk, so that the first load surface comes to rest on the first support surface, wherein subsequently pivoting about the first load surface or the first support surface takes place, so that the heel portions on the sealing segment can pass through the interruptions in the fastening projection, with subsequent rotation of the sealing segments in the circumferential direction relative to the second rotor disk joining the heel portions under the projecting sections.
  • At least one blade is provided in a particularly advantageous manner with a blocking element which engages between two shoulder portions on the sealing segment.
  • a particularly advantageous embodiment of the sealing segments is given if they have on their radially outwardly facing side a sealing surface which extends substantially between the respective outer periphery of the rotor discs.
  • the shape of the sealing surface is here first irrelevant, wherein it is also advantageous if the sealing surface is shaped such that the flow through the gas turbine essentially takes place by the running and Leitschau ⁇ blades and a deviating flow along the sealing surface is prevented as far as possible.
  • the sealing surface may have a plurality of radial elevations.
  • the sealing segments have the inner shoulder at one end in the direction of contact and the outer shoulder in the circumferential direction at the other end.
  • a first sealing segment which has at both opposite ends an inner recessed from the outer peripheral surface paragraph, while a second sealing element on both sides against ⁇ lying in the circumferential direction has an outer shoulder.
  • a sealing strip extending in the axial direction over the width of the sealing segment is used. It can be provided on the one hand, that the sealing strip extends axially and in the circumferential direction and in this case engages in einan ⁇ the opposite end faces. It is advantageous, however, if in the inner shoulder a radially outwardly opening sealing receptacle is present, in which an axially and radially extending sealing strip is arranged. In this case, it is sufficient if the sealing strip rests against an underside facing the rotor axis of the outer shoulder. Alternatively, it is also possible to provide a corresponding receiving groove for the sealing strip in the outer shoulder as well.
  • sealing strips are arranged between the running ⁇ blades and the sealing segments.
  • the sealing strip is designed annularly, ie in the manner of a piston ring, over all the sealing segments.
  • the sealing strip is advantageously designed in each case in the length of the individual sealing segments.
  • the sealing strips engage in receiving grooves in the sealing element and come to rest on the running shoe.
  • the seal segment may be designed ver ⁇ different manner as viewed in a longitudinal section, in a first advanta- embodiment, the sealing segment is substantially performed kenförmig balsams. This is considered a right ⁇ eck, which surrounds the sealing segment in longitudinal section. Substituted ⁇ directs the rectangle is parallel to a connecting line between the load surfaces. In the bar-shaped sealing segment, the circumscribing rectangle has a height-to-width ratio of at most 1: 3. As a result, a large clearance is created below the sealing segment or only a very small radial height required.
  • the first support surface on the ers ⁇ th rotor disc and the second supporting surface to the second rotor disc is positioned with the same distance as possible to the rotor axis and with the same radial distance as possible to the outer periphery of the respective rotor disc. That is, with the same diameter of the rotor disks, the second support surface (possibly mirrored and) is positioned offset axially relative to the first support surface.
  • the first attachment projection on the first rotor disk and the second attachment projection to the second rotor disc cut each individual Vorsprungab- are formed in this embodiment, advantageously, which are respectively arranged between the Schaufelhal ⁇ tenuten to the rotor disks.
  • the sealing segment considered in a longitudinal section through the rotor axis in We ⁇ sentlichen L-shaped executed.
  • FIG. 1 is a schematic representation of a first exemplary embodiment of the arrangement of sealing segments between two rotor disks
  • Figure 2 is an exploded view of Figure 1;
  • Figure 3 shows another embodiment of the arrangement of sealing segments between rotor discs;
  • FIG. 4 is an exploded view of FIG. 3.
  • a first embodiment of a ⁇ inventive rotor is schematically outlined. Shown here is only essential for the invention range with the sealing segment 31 in arrangement between a first rotor disk 01 and a second rotor disk 02. On the first rotor disk 01 distributed in the periphery are a plurality of first blades 21 and on the second rotor disk 02 a plurality are attached distributed by second blades 22 in the circumference.
  • Figure 2 outlines the embodiment of Figure 1 as an exploded view. Visible is the Schaufelhaltenut 03 and associated with the holding profile 23 extending parallel to the rotor axis in the first rotor disk 01 is a Schaufelhaltenut 03 and a valve disposed in the show ⁇ felhaltenut 03 retaining profile 23 of the first running blade or vane 21.
  • the rotor disk 01 has the outer periphery of an axially he ⁇ stretching attachment projection 07, which is interrupted by the individual Schaufelhaltenuten 03 07th Insofar, a plurality of projection sections for realizing the fastening projection 07 are distributed in the circumference.
  • the fastening projection 07 forms, on the one hand, the support surface 11 facing the rotor axis.
  • the end face 17 facing the two ⁇ th rotor disk 02 serves to realize a contact of the sealing segment 31 in the axial direction.
  • this 13 is used with a radially outwardly facing support surface 15 for supporting the sealing segment 31, in particular when the rotor is at rest.
  • the second rotor disk 02 also has a blade retaining groove 04, in which the holding profile 24 of the blade 22 is added.
  • this exemplary embodiment of the second rotor disk 02 has a fastening projection 08 extending axially to the first rotor disk 01 adjacent to the outer circumference.
  • this attachment projection 08 analogously realizes a support surface 12 on the side facing the rotor axis and of the further ⁇ the fastening projection 08 on the radially outwardly facing side forms a support surface 16 for supporting the sealing segment 31.
  • the sealing segment 31 is substantially beam-like ⁇ out leads and has the radially outwardly facing side of the sealing surface 32. Although in this illustration, the sealing surface 32 is shown in a straight line, so this is in Re ⁇ ality to provide optimal flow seal with surveys.
  • this 31 has a fastening shoulder 37, 38 on the two axially opposite sides. These 37, 38 each form a load surface 41 or 42 with a radially outwardly pointing flank.
  • the sealing segment 31 is supported on the respective support surfaces 11, 12 via the load surface 41, 42.
  • a resting surface 45 which is formed by a flank facing the rotor axis of the first attachment paragraph 37 of the sealing segment 31, on the supporting surface 15 formed by the first rotor disk 01.
  • a support web 44 is arranged, which also has a resting surface 47 on the side facing the rotor axis 44, which in turn comes to rest on the bearing surface 16 of the second rotor disk 02.
  • a fixation in axial direction is achieved by a first collar surface 47 of the seal segment 31 is at the first end ⁇ surface 17 of the first rotor disk 01 for engaging and overall a second collar surface 48 of the sealing segment 31 abuts a second end face 18 of the second rotor disk 02 on the opposite side.
  • the sealing with respect to the rotor blades 21, 22 is advantageously realized by arranging on the rotor blades 21, 22 in each case a collar 25, 26 extending in sections over the sealing segment 31. In this case, the sealing segment 31 on both sides of a paragraph in which one of the circumferentially extending sealing strip 35,
  • the sealing strip 35, 36 is recorded a receiving groove.
  • the sealing strip 35, 36 can slightly emerge from the receiving groove in the sealing ⁇ segment 31, wherein a system on je ⁇ indigenous collar 25, 26 of the blade 21, 22 takes place.
  • first attachment paragraph 37 On the sealing segment 31 are two different ways of mounting mög ⁇ Lich.
  • first attachment ⁇ paragraph 37 at least one interruption, wherein the remaining paragraph sections of the attachment paragraph 37 of
  • Width of the blade retaining grooves 03 correspond between the respective projecting portions of the fastening projection 07.
  • the second fastening shoulder 38 is designed analogously to the first fastening shoulder 37 with at least one interruption, so that the sealing segment 31 can be mounted in a bayonet manner.
  • the sealing segment 31 is positi ⁇ oniert such that the heel portions of the first Befest Trentsab ⁇ rate 37 and the heel portions of the second fastening paragraph paragraph 38 between the projection portions of the first mounting projection 07 and the second mounting projection 08 can be passed through until a system of Resting surfaces 35 and 36 on the bearing surfaces 15 and 16 is given.
  • the arrangement of step portions of the respective Befest onlysab ⁇ set 37, 38 under the protrusion portions of the associated mounting projection 07, 08th is carried out essentially continuously, so that at least no bayonet-type mounting is possible on this side.
  • the sealing ⁇ segment 31 is inserted in an inclined orientation, first with the ers ⁇ th fastening shoulder 37 between the mounting projection 07 and the support ring 13.
  • the first rotor disk 51 in turn has blade retaining grooves 53, in which 53 the respective retaining profile 73 of the respective rotor blade 71 is arranged.
  • the term show ⁇ fel 71 a in sections over the sealing segment 81 extending collar 75 miles.
  • the sealing segment used for this purpose 81 is L-shaped out ⁇ leads and has an axially extending leg and a radially extending to the rotor axis leg.
  • the load surface 91 is arranged at the radially lower end of the second leg.
  • An edge of the first fastening shoulder 87 facing the rotor axis analogously forms the resting surface 95.
  • the first fastening shoulder 87 is implemented continuously over the length of the sealing segment 81.
  • the first rotor disk 51 the first rotor disk 51, the Consringnut 59 and the buildin ⁇ actuating projection 57 runs circumferentially. This allows a particularly stable connection of the sealing segment 81 to the first rotor disk 51.
  • the sealing segment 81 is pivoted in, as in the first exemplary embodiment in the second variant. For this purpose, first the sealing segment 81 is slid inclined with the first attachment paragraph 87 in the receiving groove 59. By the subsequent pivoting analogous to the previous example, the joining of the sealing segment 81 takes place on the second rotor disk 02.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)

Abstract

L'invention concerne un rotor de turbine à gaz comportant un premier disque de rotor (01) et un second disque de rotor (02) entre lesquels est agencée une bague d'étanchéité constituée de segments d'étanchéité (31). Pour la fixation, les segments d'étanchéité sont fixés directement aux disques de rotor (01, 02) sans appui de charge sur les aubes motrices (21, 22). On utilise à cette fin un assemblage de type à baïonnette.
PCT/EP2017/070153 2016-08-25 2017-08-09 Rotor muni d'une bague d'étanchéité segmentée WO2018036818A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP16185591.1A EP3287595A1 (fr) 2016-08-25 2016-08-25 Rotor dote d'un anneau d'etancheite segmente
EP16185591.1 2016-08-25

Publications (1)

Publication Number Publication Date
WO2018036818A1 true WO2018036818A1 (fr) 2018-03-01

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Application Number Title Priority Date Filing Date
PCT/EP2017/070153 WO2018036818A1 (fr) 2016-08-25 2017-08-09 Rotor muni d'une bague d'étanchéité segmentée

Country Status (2)

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EP (1) EP3287595A1 (fr)
WO (1) WO2018036818A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP7092938B2 (ja) * 2018-08-02 2022-06-28 シーメンス エナジー グローバル ゲゼルシャフト ミット ベシュレンクテル ハフツング ウント コンパニー コマンディートゲゼルシャフト ２つのロータディスクの間にロータ組立要素を配置したロータ
KR20220078706A (ko) * 2019-10-18 2022-06-10 지멘스 에너지 글로벌 게엠베하 운트 코. 카게 2개의 로터 디스크들 사이에 배열된 로터 구성 요소를 구비한 로터

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2256300A2 (fr) * 2009-05-15 2010-12-01 United Technologies Corporation Ensemble de joint à léchettes et étage rotorique associé
EP2535523A2 (fr) 2011-06-17 2012-12-19 General Electric Company Système d'étanchéité de turbine et procédé de son assemblage
DE102014115197A1 (de) * 2013-10-28 2015-04-30 General Electric Company Dichtungsbauteil zur Reduktion von sekundärer Luftströmung in einem Turbinensystem
CA2921257A1 (fr) 2015-02-20 2016-08-20 General Electric Company Joint d'etancheite inter etage de turbine multi etage a auget et methode d'assemblage

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2256300A2 (fr) * 2009-05-15 2010-12-01 United Technologies Corporation Ensemble de joint à léchettes et étage rotorique associé
EP2535523A2 (fr) 2011-06-17 2012-12-19 General Electric Company Système d'étanchéité de turbine et procédé de son assemblage
DE102014115197A1 (de) * 2013-10-28 2015-04-30 General Electric Company Dichtungsbauteil zur Reduktion von sekundärer Luftströmung in einem Turbinensystem
CA2921257A1 (fr) 2015-02-20 2016-08-20 General Electric Company Joint d'etancheite inter etage de turbine multi etage a auget et methode d'assemblage

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Publication number Publication date
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