EP3445953B1 - Strömungsmaschinengehäuse - Google Patents

Strömungsmaschinengehäuse Download PDF

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Publication number
EP3445953B1
EP3445953B1 EP16787365.2A EP16787365A EP3445953B1 EP 3445953 B1 EP3445953 B1 EP 3445953B1 EP 16787365 A EP16787365 A EP 16787365A EP 3445953 B1 EP3445953 B1 EP 3445953B1
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EP
European Patent Office
Prior art keywords
curved
force
housing
curvature radius
screw connections
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.)
Active
Application number
EP16787365.2A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP3445953A1 (de
Inventor
Claus Michael Fost
Jochen Homann
Florian Brahm
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.)
MAN Energy Solutions SE
Original Assignee
MAN Energy Solutions SE
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Application filed by MAN Energy Solutions SE filed Critical MAN Energy Solutions SE
Publication of EP3445953A1 publication Critical patent/EP3445953A1/de
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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
    • F01D25/26—Double casings; Measures against temperature strain in casings
    • F01D25/265—Vertically split casings; Clamping arrangements therefor
    • 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
    • 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
    • F01D25/246—Fastening of diaphragms or stator-rings

Definitions

  • the invention relates to a turbomachine housing.
  • a turbomachine housing such as a steam turbine housing, is typically composed of a plurality of housing parts, in particular a first, lower-part housing part and a second, cover-like housing part, which are connected to one another by means of screw connections on opposite or adjacent flanges.
  • Fig. 1 shows a section of a section through a turbomachine housing 1 known from the prior art, namely steam turbine housing, in the area of a cover-like housing part 2.
  • the cover-like housing part 2 has a wall 3 with a curved cross section with a curved inside 4 and a curved outside 5.
  • a flange 6 is formed at the edge region of the cover-like housing part 2, which flange flange 7 connects to an adjacent flange, not shown, of an adjacent housing part.
  • lid-like housing part 2 of the turbomachine housing 1 is connected to the adjacent housing part, not shown, via screw connections 8, each screw connection 8 in FIG Fig.
  • FIG. 1 The embodiment shown includes a screw 9, a nut 10 cooperating with the screw 9 and an expansion sleeve 11.
  • the screw connections 8 are tightened
  • Fig. 1 shows a force vector 12, which symbolizes the screw force of the screw connection 8.
  • the force vector 12 of the screw force of the screw connection extends through an axis 13 of the respective screw connection 8.
  • turbomachine housing in which the tightness of the flange connection between adjacent housing parts can be better guaranteed than is possible with turbomachine housings known from the prior art.
  • the present invention is based on the object of creating a novel turbomachine housing.
  • the curved inside is contoured in a first area facing away from the screw connections over a first curvature radius R1 and in a second R2, the area facing the screw connections over a second curvature radius R2 deviating from the first curvature radius R1, in such a way that in the area of the screw connections a force vector the force, which is dependent on a pressure inside the turbomachine housing, but approximately coaxially opposite to a force vector of the screw force of the screw connections, which extends through the axis of the screw connections, namely in such a way that an offset between the force vector of the force that of is dependent on the pressure inside the turbomachine housing, and the force vector of the screw force is ⁇ 0.15 of the flange width B.
  • the curved outside is contoured over a third radius of curvature, the third radius of curvature R3 and the first radius of curvature R1 differing from one another.
  • an offset between the force vector of the force, which is dependent on the pressure inside the turbomachine housing, and the force vector of the screw force of the screw connections is ⁇ 0.05 of the flange width B.
  • the first radius of curvature R1 of the curved inside is larger than the second radius of curvature R2 of the curved inside, the centers of these two radius of curvature being offset from one another both in the vertical direction and in the horizontal direction. This is particularly preferred for setting favorable lever ratios in the area of the screw connections and thus for ensuring a good tightness of the turbomachine housing.
  • the third radius of curvature R3 of the curved outside is larger than the first radius of curvature R1 of the curved inside, and furthermore the centers of these two radiuses of curvature cannot be offset from one another in the vertical direction in the horizontal direction.
  • This further development of the invention also serves to set favorable leverage ratios in the area of the flange connection or screw connections and thus to ensure good tightness of the turbomachine housing.
  • a contour that extends through the curved wall of the second housing part intersects at least at one point of the curved wall, in particular at the upper vertex of the curved one Wall, from the curved outside and the curved inside has the same distance, the opposite or delimiting flange surfaces in the area of the screw connections at an intersection that lies approximately on the axis of the screw connections.
  • a distance between this point of intersection and the axis of the screw connections is ⁇ 0.15, preferably ⁇ 0.05, of the flange width B.
  • the second region of the arched inner side facing the screw connections and contoured with the second radius of curvature R2 merges into an evenly contoured region of the inner side on a side facing away from the first region.
  • the invention relates to a turbomachine housing, in particular a steam turbine housing.
  • Fig. 2 shows a preferred embodiment of a turbomachine housing 21 according to the invention in the region of a second, cover-like housing part 22, which is connected to a first, lower-part housing part of the turbomachine housing 21, not shown.
  • a curved wall 23 is shown, which comprises an inside 24 that is curved in cross section and a curved outside 25.
  • the shown, lid-like housing part 22 of the turbomachine housing 21 has a flange 26 with a flange surface 27, with the lower part-like housing part of the turbomachine housing 21 with a corresponding flange surface adjoining this flange surface 27 of the flange 26 of the lid-like housing part 22, and then then these housing parts are connected to one another via screw connections 28.
  • Each of the screw connections 28 in turn has a screw 29, a nut 30 and an expansion sleeve 31.
  • the curved inside 21 in a first area facing away from the screw connections 28 over a first radius of curvature R1 and in a second area facing the screw connections 28 over a second area from first curvature radius R1 deviating curvature radius R2 is contoured in such a way that in the area of the screw connections 28 a force vector 32 of the screw force of the respective screw connection runs approximately coaxially, but opposite to a force vector 34 of the force which is dependent on the pressure inside the turbomachine housing.
  • the offset ⁇ x between the force vector 32 of the force of the respective screw connection 28 and the force vector 34 of the force dependent on the internal pressure is ⁇ 0.15, preferably ⁇ 0.05, of the flange width B.
  • the first curvature radius R1 is the curvature radius with which the curved inner side 24 of the curved wall 23 of the cover-like housing part 22 of the turbomachine housing 21 is curved in the area that faces away from the screw connections 28.
  • the area in which the curved wall 23 is contoured in the area of its inside 24 with the first radius of curvature R1 extends to the upper apex 35 of the curved wall 23.
  • the first radius of curvature R1 of the curved inside 24 is larger than the second radius of curvature R2 of the curved inside 24, center points 36, 37 of these radius of curvature R1, R2 being offset from one another both in the vertical direction and in the horizontal direction.
  • the curved outer side 25 of the curved wall 23 of the housing part 21 is contoured via a third radius of curvature R3, the third radius of curvature R3 and the first radius of curvature R1 differing from one another.
  • the third radius of curvature R1 of the curved outside 25 of the wall 23 is larger than the first radius of curvature R1 of the curved inside 24 of the wall 23, the center points of these radius of curvature R1 and R3 also being offset from one another, preferably in such a way that the radius of curvature R1 and R3 are offset from each other in the vertical direction, but not in the horizontal direction.
  • the area of the curved inside 24 of the housing part 22 contoured with the second radius of curvature R2 continuously merges on a first side with the first area of the curved inside 24 contoured with the first radius of curvature R1.
  • the area of the curved inner side 24 contoured with the second radius of curvature R2 continuously merges on a side facing away from the first area into an evenly contoured area of the inner side 24, in which the curved inner side 24 is then no longer curved, but rather is level.
  • This just contoured area of the curved inner surface 24 of the curved wall 23 runs adjacent to the flange surface 27 of the flange 26 and in particular ensures that the housing part 22 of the turbomachine housing 21 on the inside thereof in the area of the screw connections 28 has a greater material thickness than if the curvature of the inside 24 would extend to the flange surface 27. As a result, the strength of the turbomachine housing 21, in particular the housing part 22, can be increased.
  • the above-described contouring of the inside 24 of the curved wall 23 via the radii R1 and R2, in particular in combination with the corresponding contouring of the curved outside 25 via the radius R3, can ensure that an offset between the force vectors 32, 34 is minimal, in particular that they run approximately coaxially, as a result of which favorable lever ratios can be set in the area of the screw connections 28 in such a way that good tightness of the turbomachine housing can be provided.
  • the force vectors 32, 34 run in opposite directions, but on one axis.
  • Fig. 2 also shows a contour 39 of the curved wall 23 of the cover-like housing part 22, which extends through the wall 23 between the curved inside 24 and the curved outside 25 and which extends at least at one point of the curved wall 23, in Fig. 2 at the apex 35 thereof, the same distance from the curved outside 25 and the curved inside 24.
  • this contour 39 is a circular section contour which, as already stated, is at the same distance from the inside 24 and the outside 25 in the region of the upper vertex 35 of the curved wall 23.
  • An intersection 40 of this contour 39 with the flange surface 27 in the region of the screw connections 28 is preferably approximately on the axis 33 of the screw connections 28 through which the force vector 32 of the screw force extends.
  • a distance between this intersection 40 and the axis 33 of the screw connections 28 is ⁇ 0.15, preferably ⁇ 0.05 of the flange width B.
  • the present invention proposes a defined contouring of the turbomachine housing, in particular a steam turbine housing, and preferably in the area of the curved wall 23 of the cover-like housing part 22 of the turbomachine housing 21.
  • This defined contouring ensures that an offset ⁇ x between the force vectors 32 and 34 the screw forces and the force dependent on the internal pressure in the turbomachine housing and extending perpendicular to the force vectors is in a defined range, preferably zero. This allows good tightness of the fluid machine housing 21 to be ensured.
  • the screwing force required to ensure the tightness in the flange area between the adjacent flanges of the turbomachine housing can also be reduced.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Supercharger (AREA)
EP16787365.2A 2016-04-18 2016-10-19 Strömungsmaschinengehäuse Active EP3445953B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016107119.6A DE102016107119A1 (de) 2016-04-18 2016-04-18 Strömungsmaschinengehäuse
PCT/EP2016/075002 WO2017182106A1 (de) 2016-04-18 2016-10-19 Strömungsmaschinengehäuse

Publications (2)

Publication Number Publication Date
EP3445953A1 EP3445953A1 (de) 2019-02-27
EP3445953B1 true EP3445953B1 (de) 2020-04-01

Family

ID=57206220

Family Applications (1)

Application Number Title Priority Date Filing Date
EP16787365.2A Active EP3445953B1 (de) 2016-04-18 2016-10-19 Strömungsmaschinengehäuse

Country Status (6)

Country Link
EP (1) EP3445953B1 (zh)
JP (1) JP6700476B2 (zh)
CN (1) CN109154207B (zh)
BR (1) BR112018069249B1 (zh)
DE (1) DE102016107119A1 (zh)
WO (1) WO2017182106A1 (zh)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20200248589A1 (en) * 2019-01-31 2020-08-06 Elliott Company Oval Steam Turbine Casing
USD941360S1 (en) 2019-01-31 2022-01-18 Elliott Company Oval steam turbine casing

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2278304A (en) 1940-07-30 1942-03-31 Westinghouse Electric & Mfg Co Joint construction
DE3542073A1 (de) 1985-11-28 1987-06-04 Bbc Brown Boveri & Cie Flanschverbindung an einem mehrteiligen, innendruckbeanspruchten gehaeuse, insbesondere von dampfturbinen
EP2405105A2 (en) 2010-07-08 2012-01-11 General Electric Company Steam turbine shell

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0674003A (ja) * 1991-07-12 1994-03-15 Mitsubishi Heavy Ind Ltd 圧力容器
US6752589B2 (en) * 2002-10-15 2004-06-22 General Electric Company Method and apparatus for retrofitting a steam turbine and a retrofitted steam turbine
JP2004150357A (ja) * 2002-10-30 2004-05-27 Toshiba Corp 蒸気タービン
JP4559781B2 (ja) * 2004-06-30 2010-10-13 株式会社東芝 蒸気タービンケーシングおよび蒸気タービン
DE102005015150A1 (de) * 2005-03-31 2006-10-05 Alstom Technology Ltd. Maschinengehäuse
EP2096273A1 (de) * 2008-02-28 2009-09-02 Siemens Aktiengesellschaft Rohrförmiges Gehäuse für einen Abschnitt eines Druckgehäuses einer Turbomaschine
US8128353B2 (en) * 2008-09-30 2012-03-06 General Electric Company Method and apparatus for matching the thermal mass and stiffness of bolted split rings
CH705191A1 (de) * 2011-06-21 2012-12-31 Alstom Technology Ltd Druckgehäuse.
CN105134800A (zh) * 2015-08-11 2015-12-09 哈尔滨汽轮机厂有限责任公司 汽轮机可顷瓦轴承的装配方法

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2278304A (en) 1940-07-30 1942-03-31 Westinghouse Electric & Mfg Co Joint construction
DE3542073A1 (de) 1985-11-28 1987-06-04 Bbc Brown Boveri & Cie Flanschverbindung an einem mehrteiligen, innendruckbeanspruchten gehaeuse, insbesondere von dampfturbinen
EP2405105A2 (en) 2010-07-08 2012-01-11 General Electric Company Steam turbine shell

Also Published As

Publication number Publication date
WO2017182106A1 (de) 2017-10-26
CN109154207A (zh) 2019-01-04
EP3445953A1 (de) 2019-02-27
BR112018069249B1 (pt) 2023-02-14
JP2019513944A (ja) 2019-05-30
DE102016107119A1 (de) 2017-10-19
JP6700476B2 (ja) 2020-05-27
BR112018069249A2 (pt) 2019-01-22
CN109154207B (zh) 2021-08-31

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