EP1707759A2 - Carter d'une turbomachine - Google Patents

Carter d'une turbomachine Download PDF

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Publication number
EP1707759A2
EP1707759A2 EP06111846A EP06111846A EP1707759A2 EP 1707759 A2 EP1707759 A2 EP 1707759A2 EP 06111846 A EP06111846 A EP 06111846A EP 06111846 A EP06111846 A EP 06111846A EP 1707759 A2 EP1707759 A2 EP 1707759A2
Authority
EP
European Patent Office
Prior art keywords
housing
bridge
parting plane
contact surface
plane
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
EP06111846A
Other languages
German (de)
English (en)
Other versions
EP1707759B1 (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
Alstom Technology 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 Alstom Technology AG filed Critical Alstom Technology 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 machine, in particular almost rotationally symmetrical housing, for example for a turbomachine, with a first housing shell, which is connected to a second housing shell along a parting plane, which usually goes 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 beyond the (rotational) contour of the rest of the housing for reasons of uniform thermal behavior as possible and 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 to increase the searing 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 greater closing forces.
  • US 2,169,092 Finally, the use of double T-shaped shrunken tie rods instead of bolts suggests.
  • 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 is significantly reduced when the high-energy flow flows around the blades at the tip and thereby does not transfer any work to the respective blade.
  • the invention deals with the problem of providing an improved embodiment for a housing of the type mentioned, in particular significantly improves the dimensional stability of the housing by the circumferential stiffness in the region of the parting plane almost constant equal to the Remainder of the housing periphery is, and at the same time the radial extent in the area 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 to attach at least one bridge, which extends perpendicular to the parting plane and the both sides of the parting plane in each case in a corresponding bridge portion both with one housing shell and with the other housing shell firmly and bending moment stiff in Circumferential direction is connected.
  • 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 can be screwed or otherwise connected to the respectively associated housing half at one of the bridge sections or at both bridge sections.
  • a particularly high flexural rigidity and, if necessary, can be achieved also strength for the respective connection between the respective housing shell and the respective bridge section are produced.
  • the bridge it is basically possible to integrate one of the two bridge sections in the associated housing shell, that is, the bridge then forms an integral part of the respective housing shell.
  • a fixed connection between the housing shell and the bridge formed integrally thereon or integrally or in one piece is particularly simple, and only one side of the bridge is detachably connected to the other housing shell.
  • 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 bear against 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 is rotationally symmetrical in the embodiments shown here. This is not obligatory.
  • 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 indicated by dash-dotted lines in Fig. 1. 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 against the respective mating contact surface 12, 13 is pressed. This is achieved in the variant of 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.
  • this plane 14 is perpendicular to the parting plane 4.
  • the invention are embodiments with slightly inclined contact surfaces, in particular with the symmetry plane of the housing mirror-inverted contact surfaces similar to a Aushebeschräge, in particular simplify the assembly and disassembly process (Fig. 2a and 4a).
  • the housing shells 2, 3 in the region of the parting plane 4 are also directly connected to one another with a further screw connection, which can offer advantages in machining, assembly and operation, in particular with regard to the tightness of the housing connection.
  • This gland is indicated by dotted lines and designated 15.
  • this screw 15 is arranged in a conventional manner so that it penetrates the parting plane 4, preferably vertically.
  • conventional screws and the bridges can alternate locally one behind the other in the axial direction.
  • Fig. 1 thus shows an embodiment in which the bridge 6 can be grown with comparatively little effort to a basically conventionally designed flange to improve in this way the rigidity of the flange 5 considerably.
  • Such an embodiment is in particular retrofittable.
  • 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 may for example be designed as a plate. It is also possible to design the bridge 6 as a rod.
  • a plate-shaped bridge 6 a longitudinal dimension of the bridge 6, which is measured in the parting plane 4 and in the longitudinal direction of the housing 1, greater 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.
  • the longitudinal dimension of the bridge 6 is in any case smaller than the transverse dimension of the bridge 6.
  • the longitudinal dimension of the bridge 6 is preferably one bar-shaped bridge 6 in the region of a thickness which is measured in the parting plane 4 and transversely to the longitudinal direction of the housing 1.
  • FIG. 2 another advantageous embodiment is obtained when the position of the plane 14 is selected 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 in Fig. 2 all in one plane, which may be advantageous for processing, however, means relatively large bridges 6 in large housing radii.
  • the size of the bridge 6 can be reduced to the required for the moment and power transmission Mass by according to Fig. 2a, the contact or mating contact surfaces 10, 11 and 12, 13 are no longer left in a plane. Either 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 preferably 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 substantially the same thermal properties over the entire circumference, whereby a symmetrical deformation of the housing 1 is achieved particularly easily at the loads occurring during operation of the machine.
  • FIG. 1 shows such an embodiment of the invention, in which the bridge 6 can be attached to a housing with a basically conventionally designed flange 5, the variants of FIG. 2 and Fig. 2a and all subsequent variants according to the invention, of common Constructions according to the prior art very different housing designs.
  • FIG. 3 shows a very similar embodiment to FIG. 2, in which, however, the bridge 6 is not completely integrated into the outer contour 16 of the housing 1, but projects slightly beyond the housing contour 16 in the radial direction.
  • the second bridge section 8 of the bridge 6 forms an integral part of the second housing shell 3. That is to say, the bridge 6 does not form a separate component in this embodiment but is in one piece or in one piece on one of the housing shells 2 or 3. here on the second housing shell 3, formed. Similar to FIG. 2 a, the contact surface according to FIG. 4 a can also be oblique or curved in the case of the bridge 6 integrated in one of the housing shells 2 or 3.
  • form-fitting connections 17 are provided, with the aid 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.
  • the means that the positive-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 bolts 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. 5 the variant shown in FIG. 5 is a form-locking 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.
  • the form-locking connection 17 is designed in the manner of a dovetail coupling, with the end sections 18 of the bridge 6 also engaging behind the end sections 19 of the housing shells 2, 3.
  • the bridge 6 shown in Fig. 6 must be mounted axially with respect to the longitudinal direction of the housing 1.
  • the positive connection 17 is designed in the manner of a hammer head coupling.
  • the end portions 19 of the housing shells 2, 3 as in the variant of FIG. 6 undercuts which engage behind the end portions 18 of the bridge 6.
  • the bridge 6 is axially mountable.
  • the screw 9 could basically account for this type of positive connection 17 or be further reduced, if you put either the positive connection about in the middle of the respective contact surfaces, so that the moment can be transmitted by the planar support to both sides, or by placing a second row of such compounds closer to the parting plane 4 in their place, so that the pairs of forces transmitted from the circumferential torques by suitable AusBanken in the radial direction over the contact surfaces can be (Fig. 7a).
  • the form-locking connection 17 is formed by form-locking contours transmitting shear forces 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 type 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 in this case has a multiplicity of waves which extend essentially axially and which engage in complementary waves 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. 9 shows an embodiment in which the contact surfaces 10, 11 and the mating contact surfaces 12, 13 a curved Have course and accordingly extend along a curve.
  • This curvature is concave toward the interior of the housing 1.
  • this curvature extends Coaxial with a curvature of the housing shells 2, 3, that is coaxial with a curvature of the housing 1 in the region of Trennebebe 4.
  • a recess 20 is also in the embodiment of FIG. 9 on the housing shells 2, 3 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.
  • one bridge section 7, 8 may be provided with a first form-locking connection 17, while the other bridge section 8 or 7 is fastened to the respective housing shell 2, 3 with a second form-locking connection 17 or only with screw connections 9.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
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 true EP1707759A2 (fr) 2006-10-04
EP1707759A3 EP1707759A3 (fr) 2011-10-26
EP1707759B1 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)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2096273A1 (fr) * 2008-02-28 2009-09-02 Siemens Aktiengesellschaft Boîtier tubulaire pour une section d'un boîtier de turbomachine
EP2096272A1 (fr) * 2008-02-27 2009-09-02 Siemens Aktiengesellschaft Boîtier de turbomachine divisé et doté de brides de joint partiel optimisées
CH705190A1 (de) * 2011-06-21 2012-12-31 Alstom Technology Ltd Druckgehäuse.

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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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US2276603A (en) 1938-11-04 1942-03-17 Parsons C A & Co Ltd Butt-jointing device
US2457073A (en) 1946-11-07 1948-12-21 Westinghouse Electric Corp Turbine cylinder joint
DE853451C (de) 1950-05-28 1952-10-23 Brown Flanschverbindung an Druckgefaessen, insbesondere an Gehaeusen von Dampf- und Gasturbinen
CH319355A (de) 1952-05-08 1957-02-15 Parsons & Marine Eng Turbine Flanschverbindung für Turbinengehäuse
US3914741A (en) 1973-11-01 1975-10-21 Bell Telephone Labor Inc Fault detection arrangement for digital transmission system

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US1957699A (en) * 1930-04-25 1934-05-08 Allis Chalmers Mfg Co Flange connection
US2169092A (en) * 1937-09-11 1939-08-08 Gen Electric Turbine-casing joint
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DE1056624B (de) * 1958-07-11 1959-05-06 Licentia Gmbh In einer oder in mehreren Achsebenen geteiltes Axialturbinengehaeuse
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US4208774A (en) * 1978-11-27 1980-06-24 United Technologies Corporation Process for welding flanges to a cylindrical engine casing having a plurality of spaced rails and ribs
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WO1999017000A1 (fr) * 1997-09-26 1999-04-08 Siemens Aktiengesellschaft Carter pour turbomachine
DE59909395D1 (de) * 1999-01-20 2004-06-09 Alstom Technology Ltd Baden Gehäuse für eine Dampf- oder eine Gasturbine
BR0008359A (pt) * 1999-01-25 2001-11-27 Elliott Turbo Alojamento para máquinas rotativas , método paraa fabricação de uma porção de alojamento ealojamento de alta pressão
JP2001107922A (ja) * 1999-10-08 2001-04-17 Mitsubishi Heavy Ind Ltd フランジレスケーシングの締結構造
GB0117550D0 (en) * 2001-07-19 2001-09-12 Rolls Royce Plc Joint arrangement

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2276603A (en) 1938-11-04 1942-03-17 Parsons C A & Co Ltd Butt-jointing device
US2457073A (en) 1946-11-07 1948-12-21 Westinghouse Electric Corp Turbine cylinder joint
DE853451C (de) 1950-05-28 1952-10-23 Brown Flanschverbindung an Druckgefaessen, insbesondere an Gehaeusen von Dampf- und Gasturbinen
CH319355A (de) 1952-05-08 1957-02-15 Parsons & Marine Eng Turbine Flanschverbindung für Turbinengehäuse
US3914741A (en) 1973-11-01 1975-10-21 Bell Telephone Labor Inc Fault detection arrangement for digital transmission system

Cited By (5)

* 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
WO2009106377A1 (fr) * 2008-02-27 2009-09-03 Siemens Aktiengesellschaft Boîtier divisé de turbomachine avec brides de joint optimisées
US8511985B2 (en) 2008-02-27 2013-08-20 Siemens Aktiengesellschaft Divided turbomachine housing having optimized parting line flanges
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.

Also Published As

Publication number Publication date
EP1707759B1 (fr) 2018-09-26
EP1707759A3 (fr) 2011-10-26
DE102005015150A1 (de) 2006-10-05
CN1840956A (zh) 2006-10-04
US20060269393A1 (en) 2006-11-30
CN1840956B (zh) 2012-11-14

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