EP2375006A1 - Carter de turbopompe rigidifié - Google Patents

Carter de turbopompe rigidifié Download PDF

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Publication number
EP2375006A1
EP2375006A1 EP11160236A EP11160236A EP2375006A1 EP 2375006 A1 EP2375006 A1 EP 2375006A1 EP 11160236 A EP11160236 A EP 11160236A EP 11160236 A EP11160236 A EP 11160236A EP 2375006 A1 EP2375006 A1 EP 2375006A1
Authority
EP
European Patent Office
Prior art keywords
flange
housing
casing
wall
web
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
EP11160236A
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German (de)
English (en)
Other versions
EP2375006B1 (fr
Inventor
Vincent Langlois
Laurent Fabbri
Julien Kohler
François Danguy
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.)
Safran Aircraft Engines SAS
Original Assignee
SNECMA SAS
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Publication date
Application filed by SNECMA SAS filed Critical SNECMA SAS
Publication of EP2375006A1 publication Critical patent/EP2375006A1/fr
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Publication of EP2375006B1 publication Critical patent/EP2375006B1/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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/52—Casings; Connections of working fluid for axial pumps
    • F04D29/528—Casings; Connections of working fluid for axial pumps especially adapted for liquid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2250/00—Geometry
    • F05D2250/70—Shape
    • F05D2250/71—Shape curved
    • F05D2250/711—Shape curved convex

Definitions

  • the invention relates to a turbomachine casing inside which high fluid pressures are involved, such as a centrifugal pump casing or turbine.
  • the invention makes it possible at the same time to reduce the deformations and mechanical stresses on the housing and to improve the tightness, in use.
  • a casing of the type that the invention aims to improve, which comprises a body with axial symmetry in which is defined a cavity housing, in particular, the centrifugal stage of the rotor.
  • the casing body has two annular parts of different diameters.
  • the smaller diameter portion is provided to house a portion of the rotor.
  • the larger diameter portion houses a centrifugal wheel and is provided with an annular, external mounting flange for bolting to another complementary housing.
  • externally axial ribs that is to say stiffeners extending parallel to the axis
  • These axial ribs, coming from molding, may have a certain height in the radial direction, which gives the casing body a certain rigidity.
  • the flange allows the centering of the two housings and the insertion between them of a seal, ensures the seal.
  • the axial ribs make it possible to limit the deformations of the casing for a given wall thickness.
  • the flange undergoes the deformations of the housing. Under the effects of pressure, the swelling of the housing tends to rotate the flange relative to its joint plane. This can lead to an opening by "yawn” may cause leakage, loss of centering, or even a breakage of the bolting.
  • the presence of ribs requires expensive and complex manufacturing techniques, such as foundry or powder metallurgy. The stress levels remain high in the crankcase wall but also in the ribs. These stresses often require the choice of very resistant materials, so expensive and reduce the reliability and robustness of the whole.
  • the invention overcomes these difficulties through a structure tending to distribute the deformations both axially and radially in such a way that the pivoting of the flange is no longer to be feared.
  • the invention relates to a turbomachine casing with a generally annular wall, comprising two parts of different diameters, the part of larger diameter being provided with a fastening flange, characterized in that a portion of said wall is extending between said flange and the smaller diameter portion has an annularly curved shape with its convexity facing inwardly of said housing.
  • the casing further comprises an outer annular veil that in a way doubles the portion of curved shape of the wall.
  • the web extends away from this wall portion between the flange and said smaller diameter portion.
  • the casing defined above can optionally be obtained by a welded assembly or any other assembly principle excluding molding or metallurgy powders, which simplifies and reduces the cost of manufacture.
  • turbomachine 12 with a generally annular wall comprising two coaxial parts, of X axis, of different diameters.
  • the turbomachine is a turbopump comprising, in addition to the housing 11, a rotor 13 and a complementary housing 14.
  • the larger diameter part of the housing 11 comprises a fastening flange 16 having a plurality of holes 18 regularly distributed circumferentially.
  • This flange 16 is fixed to another flange 19 of the complementary casing 14 which defines with the casing 11 a cavity 21 inside which are installed the rotating elements, in this case the rotor 13 of a centrifugal pump.
  • the smaller diameter portion 23 has a generally tubular shape and houses a portion of the rotor.
  • a wall portion 25 extending between the flange 16 and the smaller diameter portion 23 has an annularly curved shape.
  • the convexity of this wall portion 25 is oriented towards the inside of the housing, as shown.
  • This characteristic allows an advantageous distribution of the thrust forces generated by the pressure prevailing inside the chamber and illustrated by the arrows F. These thrust forces are no longer oriented only parallel to the axis of rotation but are distributed in efforts axial and substantially radial forces illustrated by arrows F1. This new distribution of forces results in a straightening of the flange 16 and a less pivoting thereof around its outer edge.
  • the housing is provided with an outer annular web 29, substantially frustoconical, extending in parallel and at a distance from said portion of the wall 25 annularly curved. More particularly, this frustoconical web 29 extends between the flange 16 and said smaller diameter portion 23 of the housing. The web is attached to this smaller diameter portion at a distance d from the curved wall portion 25.
  • the presence of the web 29 further limits the pivoting of the flange under the effect of the internal pressure in the housing.
  • the web 29 has at least one opening and preferably, as shown, several openings 34 regularly distributed circumferentially. These openings make it possible to avoid the confinement of the cavity 36 created between the curved wall and the web, to possibly have access to an instrumentation and to allow access for checks, especially for aging.

Landscapes

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

Abstract

Perfectionnement à un carter de turbopompe permettant de réduire les déformations et sollicitations mécaniques s'exerçant sur celui-ci. Le carter à paroi globalement annulaire (11) comporte une partie de plus grand diamètre comprenant une bride de fixation (16) et la portion (25) de la paroi d'étendant entre la bride (16) et la partie de plus petit diamètre (23) a une forme incurvée annulairement avec sa convexité orientée vers l'intérieur.

Description

  • L'invention se rapporte à un carter de turbomachine à l'intérieur duquel des hautes pressions de fluide sont mises en jeu, comme par exemple un carter de pompe centrifuge ou de turbine. L'invention permet à la fois de réduire les déformations et sollicitations mécaniques sur le carter et d'améliorer l'étanchéité, en utilisation.
  • On connaît un carter du type que l'invention vise à perfectionner, qui comporte un corps à symétrie axiale dans lequel est définie une cavité abritant, notamment, l'étage centrifuge du rotor. Le corps du carter comporte deux parties annulaires de diamètres différents. La partie de plus petit diamètre est prévue pour abriter une partie du rotor. La partie de plus grand diamètre abrite une roue centrifuge et est pourvue d'une bride de fixation annulaire, extérieure, destinée à être boulonnée à un autre carter complémentaire. Pour rigidifier ce carter, il est classique de prévoir extérieurement des nervures axiales (c'est-à-dire des raidisseurs s'étendant parallèlement à l'axe) régulièrement réparties circonférentiellement, qui s'étendent entre la bride et la portion de plus faible diamètre. Ces nervures axiales, venues de moulage, peuvent avoir une certaine hauteur dans le sens radial, ce qui confère au corps de carter une certaine rigidité.
  • La bride permet le centrage des deux carters et l'insertion entre eux d'un joint, assure l'étanchéité. Les nervures axiales permettent de limiter les déformations du carter pour une épaisseur de paroi donnée.
  • Néanmoins, la bride subit les déformations du carter. Sous les effets de la pression, le gonflement du carter a tendance à faire pivoter la bride par rapport à son plan de joint. Ceci peut entraîner une ouverture par "bâillement" pouvant entraîner une fuite, une perte de centrage, voire une rupture de la boulonnerie. En outre, la présence des nervures impose des techniques de fabrication coûteuses et complexes, comme la fonderie ou la métallurgie des poudres. Les niveaux de contrainte restent élevés dans la paroi du carter mais aussi dans les nervures. Ces sollicitations nécessitent souvent le choix de matériaux très résistants, donc coûteux et diminuent la fiabilité et la robustesse de l'ensemble.
  • L'invention permet de surmonter ces difficultés grâce à une structure tendant à répartir les déformations à la fois axialement et radialement d'une façon telle que le pivotement de la bride n'est plus à craindre.
  • Plus particulièrement, l'invention concerne un carter de turbomachine à paroi globalement annulaire, comprenant deux parties de diamètres différents, la partie de plus grand diamètre étant munie d'une bride de fixation, caractérisé en ce qu'une portion de ladite paroi s'étendant entre ladite bride et la partie de plus petit diamètre a une forme incurvée annulairement avec sa convexité orientée vers l'intérieur dudit carter.
  • Selon une autre caractéristique avantageuse, le carter comporte en outre un voile annulaire extérieur venant en quelque sorte doubler la portion de forme incurvée de la paroi. Le voile s'étend à distance de cette portion de paroi entre la bride et ladite partie de plus petit diamètre.
  • De cette façon, la combinaison de déplacements axiaux et radiaux limite le pivotement de la bride. Celui-ci est encore limité par la présence du voile. Les déformations du carter, plus faibles, sont mieux réparties, radialement et axialement. Par conséquent, on obtient une diminution notable des contraintes et le carter devient plus fiable et plus robuste, toutes choses égales par ailleurs.
  • En outre, le carter défini ci-dessus peut éventuellement être obtenu par un assemblage soudé ou tout autre principe d'assemblage excluant notamment le moulage ou la métallurgie des poudres, ce qui permet de simplifier et réduire le coût de la fabrication.
  • Bien entendu, le concept qui vient d'être défini ci-dessus s'applique à tout type de carter à l'intérieur duquel règne une pression élevée en fonctionnement, notamment une turbopompe ou une turbine.
  • L'invention sera mieux comprise et d'autres avantages de celle-ci apparaitront plus clairement à la lumière de la description qui va suivre d'un carter conforme à son principe, donnée uniquement à titre d'exemple et faite en référence aux dessins annexés dans lesquels :
    • la figure 1 est une vue générale en perspective avec arrachement du carter conforme à l'invention; et
    • la figure 2 est une demi-coupe partielle passant par l'axe de rotation du rotor et illustrant le même carter et d'autres éléments d'une turbopompe.
  • En se reportant aux dessins, on a représenté un carter 11 de turbomachine 12 à paroi globalement annulaire comprenant deux parties coaxiales, d'axe X, de diamètres différents. Selon l'exemple, cette turbomachine est une turbopompe comprenant, outre le carter 11, un rotor 13 et un carter complémentaire 14. La partie de plus grand diamètre du carter 11 comporte une bride de fixation 16 comportant une pluralité de trous 18 régulièrement répartis circonférentiellement. Cette bride 16 est fixée à une autre bride 19 du carter complémentaire 14 qui définit avec le carter 11 une cavité 21 à l'intérieur de laquelle se trouvent installés les éléments tournants, en l'occurrence ici le rotor 13 d'une pompe centrifuge. La partie de plus petit diamètre 23 a une forme globalement tubulaire et abrite une partie du rotor.
  • Selon une caractéristique importante de l'invention, une portion de paroi 25 s'étendant entre la bride 16 et la partie de plus petit diamètre 23 a une forme incurvée annulairement. La convexité de cette portion de paroi 25 est orientée vers l'intérieur du carter, comme représenté.
  • Cette caractéristique permet une répartition avantageuse des efforts de poussée générés par la pression régnant à l'intérieur de la chambre et illustrés par les flèches F. Ces efforts de poussée ne sont plus uniquement orientés parallèlement à l'axe de rotation mais se répartissent en efforts axiaux et en efforts sensiblement radiaux illustrés par les flèches F1. Cette nouvelle répartition des efforts se traduit par un redressement de la bride 16 et un moindre pivotement de celle-ci autour de son bord extérieur.
  • De plus, selon une autre caractéristique avantageuse, le carter est pourvu d'un voile annulaire 29 extérieur, sensiblement tronconique, s'étendant en parallèle et à distance de ladite portion de la paroi 25 incurvée annulairement. Plus particulièrement, ce voile tronconique 29 s'étend entre la bride 16 et ladite partie de plus petit diamètre 23 du carter. Le voile se rattache à cette partie de plus petit diamètre à une certaine distance d de la portion de paroi incurvée 25.
  • La présence du voile 29 limite encore le pivotement de la bride sous l'effet de la pression interne qui règne dans le carter.
  • Le voile 29 comporte au moins une ouverture et de préférence, comme représenté, plusieurs ouvertures 34 régulièrement réparties circonférentiellement. Ces ouvertures permettent d'éviter le confinement de la cavité 36 créée entre la paroi incurvée et le voile, d'accéder éventuellement à une instrumentation et de permettre l'accès pour des contrôles, notamment de vieillissement.

Claims (4)

  1. Carter à paroi globalement annulaire constituant une partie de boîtier de turbopompe et comprenant deux parties de diamètres différents, la partie de plus grand diamètre étant munie d'une bride de fixation (16), caractérisé en ce qu'une portion (25) de ladite paroi s'étendant entre ladite bride (16) et la partie de plus petit diamètre (23) a une forme incurvée annulairement avec sa convexité orientée vers l'intérieur dudit carter.
  2. Carter selon la revendication 1, caractérisé en ce qu'il comprend en outre un voile annulaire (29) extérieur s'étendant en parallèle et à distance de ladite portion (25) de ladite paroi entre ladite bride (16) et ladite partie de plus petit diamètre (23).
  3. Carter selon l'une des revendications précédentes, caractérisé en ce que ledit voile (29) comporte au moins une ouverture (34).
  4. Carter selon la revendication 3, caractérisé en ce que ledit voile comporte plusieurs ouvertures (34) régulièrement réparties circonférentiellement.
EP11160236.3A 2010-03-30 2011-03-29 Carter de turbopompe rigidifié Active EP2375006B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR1052337A FR2958324B1 (fr) 2010-03-30 2010-03-30 Carter de turbomachine rigidifie

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EP2375006A1 true EP2375006A1 (fr) 2011-10-12
EP2375006B1 EP2375006B1 (fr) 2015-09-23

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Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB897907A (en) * 1959-02-27 1962-05-30 Sulzer Ag Hydraulic machines for hydraulic storage power stations
US4720242A (en) * 1987-03-23 1988-01-19 Lowara, S.P.A. Centrifugal pump impeller
US4775295A (en) * 1985-05-17 1988-10-04 Klein, Schanzlin & Becker Aktiengesellschaft Centrifugal pump casing
US4786238A (en) * 1984-12-20 1988-11-22 Allied-Signal Inc. Thermal isolation system for turbochargers and like machines
EP0379196A2 (fr) * 1989-01-19 1990-07-25 Ebara Corporation Carter de pompe
EP0406868A2 (fr) * 1989-07-05 1991-01-09 Ebara Corporation Corps de pompe centrifuge
EP0413176A2 (fr) * 1989-08-18 1991-02-20 Ebara Corporation Corps en tôle, notamment pour pompes centrifuges à roue radiale
EP0442070A1 (fr) * 1990-02-13 1991-08-21 Ebara Corporation Carter de pompe en tÀ´le
US5184945A (en) * 1991-12-27 1993-02-09 Assoma, Inc. Bushing structure for using in magnetically driving centrifugal pumps
FR2698661A1 (fr) * 1992-11-30 1994-06-03 Europ Propulsion Turbopompe compacte de forte puissance pour moteur-fusée.
WO2009065881A1 (fr) * 2007-11-20 2009-05-28 Mann+Hummel Gmbh Carter pour un compresseur centrifuge radial
FR2933150A1 (fr) * 2008-06-25 2010-01-01 Snecma Etage redresseur dans un compresseur de turbomachine

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB897907A (en) * 1959-02-27 1962-05-30 Sulzer Ag Hydraulic machines for hydraulic storage power stations
US4786238A (en) * 1984-12-20 1988-11-22 Allied-Signal Inc. Thermal isolation system for turbochargers and like machines
US4775295A (en) * 1985-05-17 1988-10-04 Klein, Schanzlin & Becker Aktiengesellschaft Centrifugal pump casing
US4720242A (en) * 1987-03-23 1988-01-19 Lowara, S.P.A. Centrifugal pump impeller
EP0379196A2 (fr) * 1989-01-19 1990-07-25 Ebara Corporation Carter de pompe
EP0406868A2 (fr) * 1989-07-05 1991-01-09 Ebara Corporation Corps de pompe centrifuge
EP0413176A2 (fr) * 1989-08-18 1991-02-20 Ebara Corporation Corps en tôle, notamment pour pompes centrifuges à roue radiale
EP0442070A1 (fr) * 1990-02-13 1991-08-21 Ebara Corporation Carter de pompe en tÀ´le
US5184945A (en) * 1991-12-27 1993-02-09 Assoma, Inc. Bushing structure for using in magnetically driving centrifugal pumps
FR2698661A1 (fr) * 1992-11-30 1994-06-03 Europ Propulsion Turbopompe compacte de forte puissance pour moteur-fusée.
WO2009065881A1 (fr) * 2007-11-20 2009-05-28 Mann+Hummel Gmbh Carter pour un compresseur centrifuge radial
FR2933150A1 (fr) * 2008-06-25 2010-01-01 Snecma Etage redresseur dans un compresseur de turbomachine

Also Published As

Publication number Publication date
FR2958324A1 (fr) 2011-10-07
EP2375006B1 (fr) 2015-09-23
FR2958324B1 (fr) 2015-12-25

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