EP1707759B1 - Carter d'une turbomachine - Google Patents

Carter d'une turbomachine Download PDF

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Publication number
EP1707759B1
EP1707759B1 EP06111846.9A EP06111846A EP1707759B1 EP 1707759 B1 EP1707759 B1 EP 1707759B1 EP 06111846 A EP06111846 A EP 06111846A EP 1707759 B1 EP1707759 B1 EP 1707759B1
Authority
EP
European Patent Office
Prior art keywords
housing
bridge
separating plane
contact face
shells
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
Application number
EP06111846.9A
Other languages
German (de)
English (en)
Other versions
EP1707759A2 (fr
EP1707759A3 (fr
Inventor
Joachim Krautzig
Mladen Matan
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.)
Ansaldo Energia Switzerland AG
Original Assignee
Ansaldo Energia Switzerland AG
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 Ansaldo Energia Switzerland AG filed Critical Ansaldo Energia Switzerland AG
Publication of EP1707759A2 publication Critical patent/EP1707759A2/fr
Publication of EP1707759A3 publication Critical patent/EP1707759A3/fr
Application granted granted Critical
Publication of EP1707759B1 publication Critical patent/EP1707759B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F01D25/243—Flange connections; Bolting arrangements

Definitions

  • the invention relates to a housing for a turbomachine, with a first housing shell, which is connected to a second housing shell along a parting plane, which usually passes through the machine axis (s).
  • At least one flange is formed in the region of the parting plane, with which the two housing shells are fastened to one another.
  • this flange extends in the parting plane and forms there a broadening of the housing, which extends radially with respect to a longitudinal direction of the housing and usually extends over the entire axial length or circumference of the housing.
  • the two housing shells are screwed directly to each other in the region of the flange, wherein the respective screw penetrates the parting plane preferably vertically.
  • the housing shells thus have contact surfaces which extend in the parting plane, which lie along the parting plane and which are pressed against each other within the respective flange by the respective screwing.
  • such a housing at least in a turbomachine, such as in a turbine or a compressor, have a rotationally symmetric or nearly rotationally symmetrical shape.
  • the radially projecting flanges are a hindrance to such a housing in two respects: on the one hand, the stiffness of the flange area relative to a bending moment in the circumferential direction, for example a thermal moment due to a radial temperature gradient across the wall, locally significantly different from the rest of the circumference, second, the additional masses and the radial extent of the flanges lead to a change in the temperature behavior of the housing in the region of the flange. Both disturbances have a detrimental effect on the deformation behavior of the housing by locally different curvatures and bends occur even when circumferentially constant pressure and / or temperature load. This gives a rotationally symmetrical housing in operation a no longer circular cross-section.
  • the flanges In order to keep the circumferential stiffness constant, the flanges must have a width of about 2 - 3 times the wall thickness. This is contradicted by the fact that they should ideally not protrude over the (rotational) contour of the rest of the housing for reasons of uniform thermal behavior as possible as well as reduction of the size. For these conflicting requirements, on the one hand sufficient bending stiffness in the circumferential direction and on the other hand small radial extent, can be difficult to find a satisfactory compromise with previously known design principles.
  • US 2'276'603 also proposes brackets with a wedge mechanism for increasing the closing forces, similar to the aforementioned DE 853'451 , Due to the small remaining vertical contact surfaces between the clamp and the housing half, however, the circumferential stiffening is only slight. The goal is obviously only the larger closing forces, which generate the brackets in cooperation with wedge-shaped widening contact surfaces on the housing flanges.
  • asymmetric deformation of the housing is problematic, especially in turbomachinery, since the housing is typically used to support vanes and sealing zones for blades.
  • the flow through the turbomachine is disturbed.
  • radial gaps between the blades and the housing-side sealing zones and between the guide vanes and rotor-side sealing zones can form or increase, which leads to a flow around the blades at the tip.
  • the efficiency of a turbomachine however significantly reduced when the high-energy flow flows around the blades at the tip and thus does not transfer work to the respective blade.
  • the invention deals with the problem of providing an improved embodiment for a housing of the aforementioned type which significantly improves in particular the dimensional stability of the housing by the circumferential stiffness in the region of the parting plane almost constant equal to Rest of the housing periphery is, and wherein at the same time the radial extent in the region of the parting plane can be largely adapted to the rest of the rotational contour of the housing.
  • the invention is based on the general idea, instead of the respective particular horizontal flanges or connecting brackets to attach at least one bridge, which extends perpendicular to the parting plane and the both sides of the parting plane fixed respectively in a corresponding bridge portion with both a housing shell and with the other housing shell and bending moment rigid is connected in the circumferential direction, which is achieved by such a bridge is designed as a plate whose measured in the parting plane and in the longitudinal direction of the housing longitudinal dimension is greater than their transversely measured to the parting transverse dimension, that on both housing shells a recess is formed into which the bridge is inserted with their bridge sections, and at least one of the bridge sections is bolted to the associated housing shell.
  • Such a bridge forms transversely to the parting plane an anchor which connects the two housing halves in the parting plane adjacent to each other firmly together.
  • the local bending stiffness achievable with the aid of the bridge at the parting plane can be made almost ideally equal to the remainder of the circumference.
  • the tensile strength of the bridge by a corresponding dimensioning and / or additional structural elements be many times greater than in a conventional screw which penetrates the flange perpendicular to the parting plane.
  • the most important feature is the bending moment stiff connection in the circumferential direction while reducing the radial extent in the parting plane.
  • the bridge is screwed to one of the bridge sections or to both bridge sections with the respectively associated housing half.
  • the housing shells in the region of the parting plane and the respective bridge are designed so that there is an at least approximately constant mass distribution over the entire circumference of the housing.
  • At least one of the bridge sections may be connected via a form-locking connection with the associated housing shell.
  • Suitable form-fitting connections are, for example, a dovetail coupling, a hammerhead coupling or a clip coupling.
  • a housing 1 according to the invention comprises a first housing shell 2 and a second housing shell 3.
  • the two housing shells 2, 3 abut each other along a parting plane 4.
  • the housing 1 is the housing 1 of a machine, preferably a turbomachine, such as a turbine, a gas turbine, a steam turbine, a compressor or a compressor.
  • the housing 1 may be internally or externally loaded with an overpressure.
  • the housing 1 may be thermally loaded internally or externally. Accordingly, the housing shells 2, 3 exposed to strong deformation forces.
  • At least one bridge 6 is provided in the region of the parting plane 4. This bridge 6 is also exposed to particularly high loads due to the above-mentioned heavy loads of the housing 1.
  • the bridge 6 can basically extend in the axial direction over the entire length of the housing 1. It is also possible to arrange several such bridges 6 in the axial direction of the housing 1 one behind the other. Furthermore, it is clear that the housing 1 in the diametrically opposite parting plane 4 can also have at least one such bridge 6.
  • the bridge 6 does not lead to an asymmetrical deformation of the housing 1 due to the occurring loads, it should have substantially the same strength and stiffness values and in particular the same thermal properties (mass, wall thickness, radial extent) as the remaining area of the housing shells 2, 3 .
  • This bridge 6 extends perpendicular to the parting plane 4 and is arranged so that it penetrates the parting plane 4. Accordingly, the bridge 6 has a first bridge section 7, which is located on the same side of the parting plane 4 as the first housing shell 2. Furthermore, the bridge 6 has a second bridge section 8, which, like the second housing shell 3 on the other side of Parting level 4 is located.
  • the first bridge section 7 is firmly connected to the first housing shell 2.
  • the second bridge section 8 is firmly connected to the second housing shell 3.
  • both bridge sections 7 and 8 are screwed to the associated housing shell 2, 3.
  • Corresponding fittings 9 are in Fig. 1 indicated by dash-dotted lines. The number and / or positioning and / or dimensioning of the screw 9 is selected depending on the forces and moments to be transmitted.
  • an associated contact surface is provided on the respective bridge section 7, 8, namely a first contact surface 10 on the first bridge section 7 and a second contact surface 11 on the second bridge section 8.
  • the first housing shell 2 has a first mating contact surface 12, while the second housing shell 3 has a second mating contact surface 13.
  • the contact surfaces 10, 11 lie flat against the respective mating contact surface 12, 13.
  • the connection of the bridge 6 to the housing shells 2, 3 is expediently such that the respective contact surface 10, 11 is pressed against the respective mating contact surface 12, 13. This is achieved with the variant according to Fig.
  • the contact surfaces 10, 11 and the mating contact surfaces 12, 13 extend in a plane 14, which stands on the parting plane 4. In the embodiment shown here, this plane 14 is perpendicular to the parting plane 4.
  • the invention includes embodiments with slightly inclined contact surfaces, in particular with the plane of symmetry of the housing mirror-inverted contact surfaces similar to a Aushebeschräge, in particular simplify the assembly and disassembly process ( Fig. 1a ).
  • the bridge 6 can be particularly easily dimensioned so that the transferable tensile forces are significantly greater than tensile forces that can be transmitted by conventional glands. In addition, the moment stiffness is increased. At the same time, such a bridge 6 builds comparatively compact, whereby the outer contour of the housing 1 is not or only slightly disturbed in terms of its symmetry.
  • the bridge 6 is designed as a plate.
  • a plate-shaped bridge 6 is a longitudinal dimension of the bridge 6, which is measured in the parting plane 4 and in the longitudinal direction of the housing 1, larger than a transverse dimension of the bridge 6, which is measured transversely to the parting plane 4, ie along the plane 14.
  • a plate-shaped bridge 6 can be anchored by a corresponding number of screw 9 with sufficient strength to the housing shells 2, 3.
  • Fig. 1 the position of the plane 14 is chosen so that the bridge 6 is completely or almost completely within the rotationally symmetrical outer contour 16 of the housing 1.
  • a corresponding recess 20 is formed on the two housing shells 2, 3, in which the bridge 6 is inserted with their bridge sections 7, 8.
  • the contact or mating contact surfaces 10, 11 and 12, 13 are included Fig. 1 all in one plane, which may be advantageous for machining, but means relatively large bridges 6 for large housing radii.
  • the size of the bridge 6 can be reduced to the degree required for the torque and power transmission by, according to Fig. 1a the contact or mating contact surfaces 10, 11 and 12, 13 no longer be left in one plane.
  • the contact surfaces may indeed remain flat, but be arranged in the form of a blunt wedge or otherwise describe any mathematically continuous or discontinuous waveform, such as a circular arc.
  • the design of the bridge 6 takes place in such a way that a substantially constant mass distribution results in the cross section of the housing 1 in the circumferential direction of the housing 1 over the region of the parting plane 4.
  • the housing has a substantially constant bending stiffness and moreover, the same thermal properties over the entire circumference, which in the case of the loads occurring during operation of the machine, a symmetrical deformation of the housing 1 is achieved particularly easily.
  • Fig. 2 shows one of the Fig. 1 very similar embodiment, but in which the bridge 6 is not completely integrated into the outer contour 16 of the housing 1, but slightly protrudes in the radial direction over the housing contour 16.
  • Form-fit connections 17 are provided, by means of which the respective bridge sections 7, 8 are fixedly connected to the associated housing shells 2, 3.
  • these form-locking connections 17 are each designed so that they fix the two housing shells 2, 3 along the parting plane 4 adjacent to each other. That is, the form-locking connections 17 prevent a relative movement between the two housing shells 2, 3 transversely to the parting plane. 4
  • Such additional form-locking connections 17 are advantageous if, in addition to the circumferential torques, even high forces have to be transmitted. In particular, they allow to dimension the screw only according to the torque transmission - which usually only relatively small bolt requires because of the relatively large height of the contact surfaces and thus large screw distances - without having to consider surcharges because of additional shear stress of the screws.
  • Fig. 3 the in Fig. 3 variant shown by a positive connection 17, which represents a clamp coupling.
  • This clip coupling has the advantage that it is radially mountable with respect to the longitudinal direction of the housing 1.
  • end sections 18 of the bridge 6 engage over end sections 19 of the housing shells 2, 3.
  • Fig. 4 is the positive connection 17 designed in the manner of a hammer head coupling.
  • the end portions 19 of the housing shells 2, 3 form undercuts which engage behind the end portions 18 of the bridge 6.
  • the bridge 6 can be mounted axially.
  • the screw 9 could be omitted in this type of form-locking connection 17 in principle or be further reduced, if either the positive connection about in the middle of the respective contact surfaces sets so that the moment can be transmitted by the planar support to both sides, or by taking in their place each arranges a second row of such compounds closer to the parting plane 4, so that the pairs of forces can be transmitted from the circumferential moments by suitable form-locking connections in the radial direction over the contact surfaces ( Fig. 4a ).
  • FIG. 5 is the positive connection 17 formed by shear forces form-fitting contours on the contact surfaces 10, 11 and on the mating contact surfaces 12, 13.
  • a detail A shows a Variant in which these form-fitting contours form a kind of toothing, wherein the respective contact surface 10 is provided with axial rows of teeth which engage in complementary rows of teeth which are formed on the mating contact surface 12.
  • the detail B shows another embodiment in which the form-fitting contours are wavy.
  • the respective contact surface 11 has a multiplicity of shafts which extend essentially axially and which engage in shafts which are complementary thereto and which are formed on the associated countercontact surface 13.
  • the screw 9 are required to clamp the contact surfaces 10, 11 against the mating contact surfaces 12, 13.
  • FIG. 6 shows Fig. 6 an embodiment in which the contact surfaces 10, 11 and the mating contact surfaces 12, 13 have a curved course and accordingly extend along a curvature.
  • This curvature is concave toward the interior of the housing 1.
  • this curvature extends coaxially to a curvature of the housing shells 2, 3, ie coaxially to a curvature of the housing 1 in the region of the parting plane 4.
  • a recess 20 is provided, in which the bridge 6 is inserted.
  • bridge 6 and recess 20 are also coordinated so that the bridge 6 is recessed in the recess and in particular within the outer contour 16 of the housing 1 extends.

Landscapes

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

Claims (7)

  1. Carter pour un moteur turbo, avec une première coque de carter (2), qui s'appuie le long d'un plan de séparation (4) contre une deuxième coque de carter (3) et les deux coques de carter (2, 3) étant fixées au niveau du plan de séparation (4) entre elles, moyennant quoi, au niveau du plan de séparation (4) au moins un pont (6) étant disposé, qui s'étend transversalement par rapport au plan de séparation (4) et qui est relié fermement sur un côté du plan de séparation (4), dans une première portion de pont (7), avec la première coque de carter (2) et, sur l'autre côté du plan de séparation (4), dans une deuxième portion de pont (8), avec la deuxième coque de carter (3), et au moins une surface de contact (10, 11) étant réalisée sur au moins une des portions de pont (7, 8), avec laquelle la portion de pont (7, 8) s'appuie sur toute sa surface contre une contre-surface de contact (12, 13), qui est réalisée sur la coque de carter (2, 3) correspondante, le pont (6) étant conçu comme une plaque dont la dimension longitudinale mesurée dans le plan de séparation (4) et dans la direction longitudinale du carter (1) est supérieure à sa dimension transversale mesurée transversalement par rapport au plan de séparation (4), moyennant quoi, sur les deux coques de carter (7, 8), est réalisé un évidement (20) dans lequel le pont (6) est inséré avec ses portions de pont (7, 8) et au moins une des portions de pont (7, 8) est vissée avec la coque de carter (2, 3) correspondante,
    caractérisé en ce que
    l'évidement (20) est conçu de façon à ce que le pont (6) se trouve au moins partiellement à l'intérieur du contour externe à symétrie de rotation du carter (1).
  2. Carter selon la revendication 1,
    caractérisé en ce que
    les coques de carter (2, 3) sont conçues, au niveau du plan de séparation (4) et du pont (6) correspondant, de façon à ce qu'il en résulte une répartition des masses au moins approximativement constante sur toute la circonférence du carter.
  3. Carter selon la revendication 1,
    caractérisé en ce que
    au moins une des portions de pont (7, 8) est reliée avec la coque de carter (2, 3) par l'intermédiaire d'une liaison par complémentarité de forme (17).
  4. Carter selon la revendication 1,
    caractérisé en ce que
    au moins une des portions de pont (7, 8) s'étend à l'intérieur d'un contour externe cylindrique (16) du carter (1).
  5. Carter selon la revendication 1,
    caractérisé en ce que
    le pont (6) est relié avec les coques du carter (2, 3) de façon à ce que la surface de contact (10, 11) correspondante soit comprimée contre la contre-surface de contact (12, 13) correspondante et la surface de contact (10, 11) correspondante et/ou la contre-surface de contact (12, 13) correspondante présentent une surface avec un coefficient de frottement augmenté.
  6. Carter selon la revendication 1,
    caractérisé en ce que la surface de contact (10, 11) correspondante et la contre-surface de contact (12, 13) s'étendent le long d'une courbure concave en direction de l'intérieur du carter (1), qui s'étend de manière coaxiale à une courbure des coques de carter (2, 3) au niveau du plan de séparation (4).
  7. Carter selon l'une des revendications 1 à 6,
    caractérisé en ce que
    les deux coques de carter (2, 3) sont fixées entre elles au niveau du plan de séparation (4) exclusivement par l'intermédiaire du pont (6) correspondant.
EP06111846.9A 2005-03-31 2006-03-28 Carter d'une turbomachine Not-in-force EP1707759B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102005015150A DE102005015150A1 (de) 2005-03-31 2005-03-31 Maschinengehäuse

Publications (3)

Publication Number Publication Date
EP1707759A2 EP1707759A2 (fr) 2006-10-04
EP1707759A3 EP1707759A3 (fr) 2011-10-26
EP1707759B1 true EP1707759B1 (fr) 2018-09-26

Family

ID=36121305

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06111846.9A Not-in-force EP1707759B1 (fr) 2005-03-31 2006-03-28 Carter d'une turbomachine

Country Status (4)

Country Link
US (1) US20060269393A1 (fr)
EP (1) EP1707759B1 (fr)
CN (1) CN1840956B (fr)
DE (1) DE102005015150A1 (fr)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2096272A1 (fr) 2008-02-27 2009-09-02 Siemens Aktiengesellschaft Boîtier de turbomachine divisé et doté de brides de joint partiel optimisées
EP2096273A1 (fr) * 2008-02-28 2009-09-02 Siemens Aktiengesellschaft Boîtier tubulaire pour une section d'un boîtier de turbomachine
CH705190A1 (de) * 2011-06-21 2012-12-31 Alstom Technology Ltd Druckgehäuse.
JP5984618B2 (ja) * 2012-10-18 2016-09-06 三菱日立パワーシステムズ株式会社 タービンのケーシング、タービン及びケーシングの組立方法
JP6099474B2 (ja) * 2013-01-23 2017-03-22 三菱重工業株式会社 車室、回転機械、車室の組み立て方法
DE102015213257A1 (de) * 2015-07-15 2017-01-19 Siemens Aktiengesellschaft Abdampfgehäuse für eine Turbine, Turbinengestell, Turbinengehäuse und Montagesystem
DE102016107119A1 (de) * 2016-04-18 2017-10-19 Man Diesel & Turbo Se Strömungsmaschinengehäuse
DE102019214917A1 (de) * 2019-09-27 2021-04-01 Continental Teves Ag & Co. Ohg Herstelloptimiertes Gehäuse für ein hydraulisches Aggregat zum Erzeugen von Bremsdruck für eine hydraulische Bremsanlage

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US6506018B1 (en) * 1999-01-25 2003-01-14 Elliott Turbomachinery Co., Inc. Casing design for rotating machinery and method for manufacture thereof

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Also Published As

Publication number Publication date
EP1707759A2 (fr) 2006-10-04
EP1707759A3 (fr) 2011-10-26
US20060269393A1 (en) 2006-11-30
CN1840956A (zh) 2006-10-04
DE102005015150A1 (de) 2006-10-05
CN1840956B (zh) 2012-11-14

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