EP2052133A2 - Ensemble destiné à optimiser le jeu fonctionnel pour des turbomachines - Google Patents

Ensemble destiné à optimiser le jeu fonctionnel pour des turbomachines

Info

Publication number
EP2052133A2
EP2052133A2 EP07817418A EP07817418A EP2052133A2 EP 2052133 A2 EP2052133 A2 EP 2052133A2 EP 07817418 A EP07817418 A EP 07817418A EP 07817418 A EP07817418 A EP 07817418A EP 2052133 A2 EP2052133 A2 EP 2052133A2
Authority
EP
European Patent Office
Prior art keywords
inner ring
outer ring
arrangement according
ring
arrangement
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
Application number
EP07817418A
Other languages
German (de)
English (en)
Other versions
EP2052133B1 (fr
Inventor
Alexander Böck
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
MTU Aero Engines AG
Original Assignee
MTU Aero Engines GmbH
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 MTU Aero Engines GmbH filed Critical MTU Aero Engines GmbH
Publication of EP2052133A2 publication Critical patent/EP2052133A2/fr
Application granted granted Critical
Publication of EP2052133B1 publication Critical patent/EP2052133B1/fr
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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
    • F01D11/00—Preventing or minimising internal leakage of working-fluid, e.g. between stages
    • F01D11/08—Preventing or minimising internal leakage of working-fluid, e.g. between stages for sealing space between rotor blade tips and stator
    • F01D11/14—Adjusting or regulating tip-clearance, i.e. distance between rotor-blade tips and stator casing
    • F01D11/20—Actively adjusting tip-clearance
    • F01D11/22—Actively adjusting tip-clearance by mechanically actuating the stator or rotor components, e.g. moving shroud sections relative to the rotor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2240/00—Components
    • F05D2240/10—Stators
    • F05D2240/11—Shroud seal segments
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2300/00—Materials; Properties thereof
    • F05D2300/50—Intrinsic material properties or characteristics
    • F05D2300/501—Elasticity

Definitions

  • the invention relates to an arrangement for optimizing the running gap for at least sections of axial-type turbomachinery by controlling or regulating the run-gap-relevant inner diameter of at least one stator blade surrounding a rotor blade ring.
  • active fission control or "Active Clearance Control CACC” is usually used by experts in this technology.
  • the known structural solutions are generally based on the principle that housing areas or stator elements defined with air lower temperature, d. H. With cooling air, are flown to influence by thermal contraction of these components, the running gap. A reduction or interruption of the cooling air flow causes the components to expand again. The effect is the more effective, the greater the temperature difference between the component and cooling air.
  • a hot turbine stator is charged with relatively cool compressor air.
  • Such an arrangement is protected, for example, in US Pat. No. 6,454,529 B1.
  • the development also goes with compressors to the active fission attitude control. A thermal influence of the housing or stator comes especially in the compressor due to low temperature differences to their limits. Thus, more responsive and more powerful systems are in demand.
  • the object of the invention is to propose an arrangement for running gap optimization for at least sections of axial design executed turbomachinery, which is particularly responsive and powerful and therefore preferably suitable for use in compressors.
  • the assembly comprises a novel stator structure having an inner ring, an outer ring concentric with and radially spaced therefrom, and a plurality of webs integrally connecting the rings on. All webs are inclined relative to the radial direction by the same angle in the circumferential direction. Furthermore, the arrangement comprises an adjusting device for rotating the inner ring relative to the outer ring with elastic change of the running gap-relevant inner diameter.
  • Figure 1 shows a partial cross section through an arrangement for running gap optimization
  • Figure 2 is a partial longitudinal section through a compressor with two arrangements for running gap optimization
  • FIG 3 shows a partial cross section through an arrangement for running gap optimization in the region of a sensor for running splitting.
  • the arrangement 1 for running gap optimization comprises two essential functional units, firstly an integral, elastically deformable stator structure 3 and secondly an adjusting device with at least one lever 10, at least one actuator 16 and at least one sensor 18 for running splitter detection.
  • the stator structure 3 consists essentially of a circular, self-contained inner ring 5, of a concentric to this radially spaced circular outer ring 7 and a plurality of distributed over the circumference of the stator 3, the inner ring 5 and the outer ring 7
  • the webs 8 are inclined at a defined angle ⁇ relative to the radial direction in the circumferential direction, so that a relative rotation of the inner ring 5 and the outer ring 7, a reversible compression or expansion of the inner ring 5 and thus a change of Laufspaltrelevan - Th inner diameter D has the result.
  • the inner ring 5 has in relation to the outer ring 7 has a thinner cross-section, is thus much more flexible. This ensures that the desired change in diameter essentially results from the deformation of the inner ring 5.
  • the radially inner and radially outer ends of the webs 8 are integrally connected to the inner ring 5 and the outer ring 7 and designed as elastic solid joints. It can be seen that the webs 8 are contoured over their radial length, wherein the radially central region 9 is thickened relative to the ends and thus stiffened. Thus, the webs 8 behave over the majority of their radial length rigid body-like, which amplifies the change in diameter of the inner ring 5 at a given Relatiwerpitung.
  • the webs 8 may also be contoured with respect to their axial extent. Their axial depth can be greater on the outer ring 7 than on the inner ring 5, with a conical taper between them. At high axial stiffness so the adjustment can be reduced. This contouring is not shown.
  • the outer ring 7 is rotationally held in a housing-like support 29, so that it forms the truly static element of the stator structure 3.
  • the possibly with - not shown in Figure 1 - blade tips coming into contact inner ring 5 is radially inside provided with a friction-tolerant Anstreifbelag 17, the inside of the clearance gap-relevant inner diameter D predetermines.
  • the Anstreifbelag 17 follows the elastic deformation (compression, expansion) of the inner ring. 5
  • FIG. 1 also shows essential elements of the adjusting device.
  • the relative rotation causing force transmission between the inner ring 5 and the outer ring 7 takes place mechanically.
  • a pivoting movements about an axis parallel to the axis of rotation of the turbomachine axis permitting storage 13 for a lever 10 is disposed on the outer ring 7 at least one point of its circumference.
  • the inner ring 5 is a corresponding recess, which together with a nose-like end of the lever 10 is a positive, play-free and low-friction Joint 15 forms.
  • the connecting line from the joint 15 to the bearing 13 (center to center) extends at an angle ß to the radial direction.
  • the adjusting kinematics including the angle ⁇ , are designed so that the local run-gap-relevant deformation of the inner ring 5 optimally corresponds to the deformation in the region of a web 8.
  • the angle ⁇ is generally different from the angle ⁇ .
  • the angles ⁇ and ⁇ are here - arbitrarily - set in such a way that the longitudinal center line of a web 8 and the connecting line from the bearing 13 to the joint
  • FIG. 16 is preferably designed as a double-acting, ie pressure and tensile forces generating, power cylinder whose power supply can be pneumatically, hydraulically or electrically / electronically. Due to the arrangement on the long lever arm 12, the Aktuator element and thus also its weight, etc. are reduced. Only the required Aktuatorhub thereby increases. In Figure 1, another gap without web 8 with a bearing and a yoke for another lever 10 (not shown) is right below recognizable. With uniform distribution over the circumference, four actuator / lever kinematics would be provided here. Theoretically, a kinematics for the stator structure would suffice. With a view to the most uniform possible deformation of the inner around 5 and on a redundant system you will probably install two or more kinematics.
  • FIG. 2 shows, as a concrete example of application, a multi-stage compressor 26 in an axial construction with two arrangements 1, 2 according to the invention for splitting optimization in partial longitudinal section.
  • the multi-part housing 27 of the compressor 26 with flange. 2 the flow channel of the compressor with a plurality of rotor and vane rings and a part of the rotor 34 is shown. The - not reproduced - rotation axis would run horizontally below the representation.
  • the flow through the compressor 26 is from left to right, see the white arrows.
  • the arrangements 1, 2 lie in the radial planes of the blade rings 30, 31, wherein the axial distance is such that there is still a vane ring with Leitschaufelkranz- segments 33 between the arrangements 1, 2 place.
  • a common carrier 29 for the two stator structures 3, 4 is present within the housing 27 and fastened to the housing 27 via a flange connection.
  • the inner ring 5 of the left, upstream stator structure 3 is kinematic on both sides with vane ring segments 32, 33 coupled.
  • the inner ring 6 of the right stator structure 4 is kinematically coupled on one side with the Leitschaufelkranzsegrnenten 33. In this way, the assemblies 1, 2 affect not only the running gaps of the blade rings 30, 31, d. H.
  • the vane ring segments 33 Due to the two-sided coupling with the inner rings 5 and 6, the vane ring segments 33 are optimally moved. The vane ring segments 32 coupled only on one side to the inner ring 5 are not moved to the same extent, but still advantageously.
  • FIG. 3 shows, in a partial cross-section, the region of such a sensor 18 within an arrangement for running-gap optimization.
  • the sensor 18 is fixed relative to the inner ring 5 immediately surrounding a blade ring.
  • a sleeve-like holder 20 is integrated into the inner ring 5, in which the sensor 18 is radially inserted from the outside against the stop and again pulled out.
  • the authoritative radially inner sensor end is approximately flush with the inner surface of the squealer pad 17.
  • a bellows 24 extends radially between the housing 27 of the compressor 26 and the outer ring 7 and forms an elastic, open channel for a flexible connection line 19 of the sensor 18.
  • the bellows 24 is also used to the sensor 18 by exerting a defined radial force in its Betri ebsposition to keep.
  • the bellows 24 is in turn connected to a cover 25 which is attached to a flange 28 of the housing 27 releasably and sealed, preferably screwed.
  • the connection line 19 leads to electrical or electronic components, which are attributable to the control or regulation system of the gap optimization ultimately exporting, at least one actuator 16.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)

Abstract

L'invention concerne un ensemble destiné à optimiser le jeu fonctionnel pour des turbomachines de construction axiale grâce à la commande et à la régulation du diamètre interne, qui correspond au jeu fonctionnel d'au moins une structure de stator entourant la couronne des aubes mobiles. La structure de stator comprend une aube interne fermée, une aube externe espacée de manière radiale et concentrique par rapport à l'aube interne, et plusieurs éléments de liaison qui sont inclinés par rapport au sens radial vers la périphérie, et qui permettent de relier intégralement l'aube interne et l'aube externe. Ledit ensemble comprend un dispositif de réglage permettant la rotation de l'aube interne par rapport à l'aube externe grâce à la modification élastique du diamètre interne correspondant au jeu fonctionnel.
EP07817418.2A 2006-08-17 2007-08-08 Ensemble destiné à optimiser le jeu fonctionnel pour des turbomachines Expired - Fee Related EP2052133B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006038753A DE102006038753A1 (de) 2006-08-17 2006-08-17 Anordnung zur Laufspaltoptimierung für Turbomaschinen
PCT/DE2007/001416 WO2008019657A2 (fr) 2006-08-17 2007-08-08 Ensemble destiné à optimiser le jeu fonctionnel pour des turbomachines

Publications (2)

Publication Number Publication Date
EP2052133A2 true EP2052133A2 (fr) 2009-04-29
EP2052133B1 EP2052133B1 (fr) 2014-01-15

Family

ID=39044234

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07817418.2A Expired - Fee Related EP2052133B1 (fr) 2006-08-17 2007-08-08 Ensemble destiné à optimiser le jeu fonctionnel pour des turbomachines

Country Status (5)

Country Link
US (1) US8608427B2 (fr)
EP (1) EP2052133B1 (fr)
CA (1) CA2660368A1 (fr)
DE (1) DE102006038753A1 (fr)
WO (1) WO2008019657A2 (fr)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009006029A1 (de) * 2009-01-24 2010-07-29 Mtu Aero Engines Gmbh Turbomaschine
US9228447B2 (en) 2012-02-14 2016-01-05 United Technologies Corporation Adjustable blade outer air seal apparatus
US9683453B2 (en) * 2013-09-11 2017-06-20 General Electric Company Turbine casing clearance management system
US9695705B2 (en) 2014-10-29 2017-07-04 General Electric Company Systems and methods for controlling rotor to stator clearances in a steam turbine
US10458429B2 (en) 2016-05-26 2019-10-29 Rolls-Royce Corporation Impeller shroud with slidable coupling for clearance control in a centrifugal compressor
US10851712B2 (en) 2017-06-27 2020-12-01 General Electric Company Clearance control device
IT201900005266A1 (it) * 2019-04-05 2020-10-05 Nuovo Pignone Tecnologie Srl Turbina a vapore con pale statoriche girevoli
CN110725722B (zh) * 2019-08-27 2022-04-19 中国科学院工程热物理研究所 一种适用于叶轮机械的动叶叶顶间隙动态连续可调结构
CN113107615B (zh) * 2021-04-08 2022-08-26 沈阳航空航天大学 基于偏心阻尼作用的主动间隙控制篦齿密封结构

Family Cites Families (8)

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Publication number Priority date Publication date Assignee Title
US3227418A (en) * 1963-11-04 1966-01-04 Gen Electric Variable clearance seal
DE2922835C2 (de) * 1979-06-06 1985-06-05 MTU Motoren- und Turbinen-Union München GmbH, 8000 München Umfangsspaltdichtung an Axialströmungsmaschinen
GB2108591A (en) * 1981-11-03 1983-05-18 Rolls Royce Casing of a gas turbine engine rotor
DE3509192A1 (de) * 1985-03-14 1986-09-25 MTU Motoren- und Turbinen-Union München GmbH, 8000 München Stroemungsmaschine mit mitteln zur kontrolle des radialspaltes
GB2313414B (en) * 1996-05-24 2000-05-17 Rolls Royce Plc Gas turbine engine blade tip clearance control
US6454529B1 (en) * 2001-03-23 2002-09-24 General Electric Company Methods and apparatus for maintaining rotor assembly tip clearances
DE10233881B4 (de) * 2002-07-25 2010-02-18 Rolls-Royce Deutschland Ltd & Co Kg Durch thermische Effekte radial veränderbares Ringelement
US7686569B2 (en) * 2006-12-04 2010-03-30 Siemens Energy, Inc. Blade clearance system for a turbine engine

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2008019657A3 *

Also Published As

Publication number Publication date
US8608427B2 (en) 2013-12-17
EP2052133B1 (fr) 2014-01-15
WO2008019657A2 (fr) 2008-02-21
US20100232942A1 (en) 2010-09-16
DE102006038753A1 (de) 2008-03-13
WO2008019657A3 (fr) 2008-04-17
CA2660368A1 (fr) 2008-02-21

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