EP1012445A1 - Aube pour une turbomachine, et turbine a vapeur - Google Patents

Aube pour une turbomachine, et turbine a vapeur

Info

Publication number
EP1012445A1
EP1012445A1 EP98951240A EP98951240A EP1012445A1 EP 1012445 A1 EP1012445 A1 EP 1012445A1 EP 98951240 A EP98951240 A EP 98951240A EP 98951240 A EP98951240 A EP 98951240A EP 1012445 A1 EP1012445 A1 EP 1012445A1
Authority
EP
European Patent Office
Prior art keywords
blade
cross
region
axis
steam turbine
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
EP98951240A
Other languages
German (de)
English (en)
Other versions
EP1012445B2 (fr
EP1012445B1 (fr
Inventor
Mathias Deckers
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.)
Siemens AG
Original Assignee
Siemens 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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=7841609&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP1012445(A1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Siemens AG filed Critical Siemens AG
Publication of EP1012445A1 publication Critical patent/EP1012445A1/fr
Application granted granted Critical
Publication of EP1012445B1 publication Critical patent/EP1012445B1/fr
Publication of EP1012445B2 publication Critical patent/EP1012445B2/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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
    • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
    • F01D5/12—Blades
    • F01D5/14—Form or construction
    • F01D5/141—Shape, i.e. outer, aerodynamic form
    • 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
    • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
    • F01D5/12—Blades
    • F01D5/14—Form or construction
    • 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
    • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
    • F01D5/12—Blades
    • F01D5/14—Form or construction
    • F01D5/141—Shape, i.e. outer, aerodynamic form
    • F01D5/145—Means for influencing boundary layers or secondary circulations

Definitions

  • the invention relates to a blade for a turbomachine, the blade being directed along a blade axis and having a foot end region, a head end region and a central region and a cross-sectional region arranged perpendicularly to the blade axis along this blade axis.
  • the invention further relates to a steam turbine, in particular a high-pressure or medium-pressure steam turbine.
  • an inclination of the turbine blade in the circumferential direction is specified.
  • An inclination of the turbine blade in the area of the blade tip and the hub area of the turbine blade leads to a curved blade, such a bend being applicable only to guide blades due to the mechanical properties.
  • the article states in general that a rotation of the blade also has an influence on the inclination of the blade, so that with a three-dimensional design in the end regions of the blade, both the blade inclination, the blade rotation and the blade profile are at disposition.
  • Inlet guide vanes are arranged in the axial compressor along the gas flow path in front of the rotor and guide vanes. These inlet or inlet guide vanes have a curved cross section, except in the area of the walls.
  • the middle vane part with the arched cross section merges into a smooth and continuously curved surface in each wall region in the non-arched cross-sectional profile in the wall regions.
  • the cross-sectional profiles of the airfoil thus change continuously over the height of the outlet guide vane.
  • the inlet angle remains constant over the entire height of the inlet guide vane.
  • German Auslegeschrift 28 41 616 describes a guide vane ring for an axial turbine with guide vanes, the guide vanes being arranged between an inner and an outer ring and the profile thickness of the airfoil changing in proportion to the blade pitch. The change in the blade profile takes place via the
  • the guide vanes taper, so that their cross section changes accordingly, the blade profile remaining essentially unchanged over the blade height.
  • a twisting of the blade is also carried out over the length of the blade of the guide blade in order to take into account the change in the peripheral speed of the blades following the guide blade above the channel height. The blade is therefore adjusted by deflecting the center of gravity of the profile cuts perpendicular to the
  • Profile chord (curvature or bend), ie an axial and circumferential deflection at the same time, combined with a chord length variation.
  • Inclined turbine blades for a steam turbine are also described in the article "Development of three-dimensional stage viscous time marching method for optimization of short height stages" by G. Singh, P.J. Walker, B.R. Haller, in: “VDI Reports No. 1185, 1995, pp. 157-179.
  • the object of the invention is to provide a blade with low flow losses for a flow machine.
  • Another object of the invention is to provide a steam turbine with low flow losses.
  • the object directed to a blade for a flow machine is achieved by such a blade which is directed along a blade axis and has a foot end region, a foot axis, along this blade axis
  • the axially spaced cross-sectional areas in the foot end area and in the head end area are preferably rotated in the same direction towards the central area. As a result, the rotation is reduced again over the entire height of the blade from the head end region to the foot end region.
  • the blade is preferably designed to be arranged in a blade ring which has a circumferential direction, the cross-sectional direction coinciding locally with the circumferential direction.
  • This results in a bending in the peripheral zones of the blade in the circumferential direction with a simultaneous rotation (angle adjustment) in the end regions of the blade, whereby a reduction in flow losses and thus an increase in the efficiency of a flow machine can be achieved.
  • this results on the one hand in an increase in the mechanical exit energy with the same thermal energy input, and on the other hand in a reduction in the thermal energy use and thus the environmental impact due to pollutant emissions with the same exit energy compared to purely cylindrical or purely inclined or purely curved blades.
  • the cross-sectional profiles are preferably rotated with respect to their center of gravity or with respect to the blade axis (if different, e.g. due to inhomogeneous mass distribution).
  • the angle of rotation that occurs is referred to below as the stagger angle and performing the rotation as the stagger angle change.
  • the cross sectional profile along the blade axis is preferably the same everywhere.
  • the cross-sectional profile therefore does not change over the height of the blade.
  • the cross-sectional area of the cross-sectional profiles is preferably also constant.
  • the blade preferably has a combination of a circumferential deflection of the center of gravity of the cross-sectional profiles (bending in the circumferential direction) and a staggering of the cross-sectional profiles (without changing the profile) in the top and bottom end area (hub and housing area).
  • the blade in the middle region is preferably cylindrical.
  • the sides (pressure side, suction side) of the blade therefore run parallel to the blade axis.
  • the blade is preferably designed as a guide blade or rotor blade of a steam turbine, in particular a high-pressure or medium-pressure steam turbine.
  • the blade preferably has a small length to width ratio, as is the case in particular for blades for a high-pressure steam turbine.
  • the object directed to a steam turbine is achieved for a steam turbine which is directed along a turbine axis and has an inflow region, an outflow region and a blading region arranged in terms of flow technology between the fact that in the blading region a blade directed along a blade axis is arranged, which over the Blade axis has an inclination and a twist, which each increase from a foot end region to a central region and decrease from the central region to a head end region.
  • the blade with increasing and decreasing inclination and rotation is preferably assigned to the inflow area. It is therefore preferably arranged in the first stage and / or the subsequent stages. This applies both to steps comprising a blade ring made of moving blades or guide blades. Since the proportion of so-called secondary losses (edge losses) in the hub and housing area is particularly high in the first stages of a high-pressure or medium-pressure steam turbine (for example up to 30% of the total losses) and is reduced by the specified blade shape, this can result in a noticeable The increase in efficiency can be achieved.
  • a twisted blade ie a blade with twisting and changing the cross-sectional profile and / or the cross-sectional area increasing over its length, is preferably arranged in the outflow region.
  • a purely cylindrical blade that is to say with side walls parallel to the blade axis, is provided axially between the steps, comprising the twisted blade and the blade with increasing and decreasing inclination as well as change in the angle of the blade.
  • Such an arrangement of blades of different geometries provides a steam turbine with low flow losses and high efficiency.
  • FIG. 3 shows a spatial representation of the blade area of a blade
  • FIG. 4 shows a cross section through the blade area of the blade according to FIG. 3 and
  • FIG. 5 shows a further cross section through the blade according to FIG. 3 axially spaced from the cross section according to FIG. 4 in the direction of the blade axis.
  • FIG. 1 shows a flow machine, a high-pressure steam turbine 11, in a longitudinal section, which is directed along a turbine axis 17.
  • the steam turbine 11 has a turbine shaft 20 which is directed along the turbine axis 17 and is surrounded by a turbine housing 18.
  • the steam turbine 11 has an inflow region 12 for action fluid, superheated steam, and an outflow region 13 for the superheated steam.
  • a blading area 14 is provided axially between the inflow area 12 and the outflow area 13.
  • a central region 10 Arranged in between in the direction of the blade axis 2 is a central region 10.
  • a moving blade 8 borders on the turbine shaft 20 and a guide blade 9 on the turbine housing.
  • the rotor blades 8 and / or guide blades 9 closest to the inflow region 12 are each designed as a blade 1 which is inclined and rotated in the foot end region 3 and in the head end region 4.
  • Rotary vanes 8 and guide vanes 9 located downstream of the outflow region 13 are each designed as twisted vanes 19 with twisting increasing over the blade axis 2 and changing cross-sectional profile.
  • Purely cylindrical blades 16 are arranged in the blading area 14 axially between the inclined and twisted blades 1 and the twisted blades 19, the suction and pressure sides of which are each parallel to the blade axis 2.
  • FIG. 2 shows a section of a blade ring 21 in which blades 1 are arranged next to one another in the circumferential direction 6a.
  • the blade ring 21 is unwound along the circumferential direction 6a and is shown with only two blades 1.
  • the circumferential direction 6a corresponds to the circumference of the turbine shaft 20 in a section perpendicular to the turbine axis 17.
  • the main flow direction 22 of the steam flowing in the steam turbine 11 is perpendicular to the circumferential direction 6a of the blade ring 21.
  • FIG. 3 shows a spatial representation of the blade area 23 of a blade 1 directed along a blade axis 2.
  • the airfoil area 23 has a foot end area 3, a head end area 4 and in between a central area 10.
  • a fastening region adjoining the foot end region 3 and with which the turbine blade 1 is fastened in the turbine shaft 20 or the turbine housing 18 is not shown.
  • a shroud possibly adjoining the head end area 4 is also not shown.
  • the turbine blade 1 is inclined in a cross-sectional direction 6, which preferably corresponds to the circumferential direction 6a of the blade ring 21, and is rotated in the axial direction by a difference angle ⁇ (see FIGS. 4 and 5).
  • the increasing in the foot end region 3 towards the central region 10 and increasing circumferential bend corresponds to the same rotation and circumferential bend as in the head end region 4.
  • the degree of displacement and twisting remains constant over the height of the central region 10.
  • the size of the turning back and shifting back over the head end area 4 is preferably the same as the shifting and twisting in the foot end area 3.
  • the circumferential bend here means a displacement of the cross-sectional profile 5, 5a in the direction of a cross-sectional direction 6, which preferably corresponds to the circumferential direction 6a of a blade ring 21.
  • a rotation of the blade 1 takes place by changing the stagger angle, ie changing the angle ⁇ according to FIG. 4 and FIG. 5 by rotating the cross-sectional profile 5 about the blade axis 2, which preferably coincides with the gravity axis of the blade 1.
  • this also corresponds to a rotation about the center of gravity 7 (center of gravity 7) of the cross-section profile 5, 5a.
  • the cross-sectional profile 5, 5a, 5b is the same for each cross-section over the entire height of the airfoil region 23, ie in particular that the cross-sectional shape and cross-section are constant.
  • the cross-sectional profile 5b shown in FIG. 5 is rotated relative to the cross-sectional profile 5a shown in FIG. 4 by the difference angle ⁇ and shifted by the displacement value ⁇ U. This corresponds to a change in the stagger angle ß to the value of the stagger angle ß '(FIG. 5).
  • the edge losses i.e. The flow mechanical losses in the vicinity of the turbine shaft and the turbine housing, which can be up to about 30% of the total losses, a reduction of these edge losses due to the twisting and circumferential bending of the blade in a steam turbine leads to an increase in efficiency.
  • the degree of twisting and circumferential bending can be adapted to the flow conditions in a steam turbine, whereby the twisting and circumferential bending can also extend over the entire central region. It is also possible that the central area is purely cylindrical, i.e. the suction side and the pressure side of the blade are directed parallel to the blade axis.

Abstract

L'invention concerne une aube (1) destinée à une turbomachine (11), qui est orientée selon son axe (2). Des profils de section (5), placés, dans le sens axial, à une certaine distance les uns des autres et perpendiculairement par rapport à l'axe d'aube (2), sont décalés, les uns par rapport aux autres en gardant la même orientation, dans la zone d'extrémité de tête (4) et dans la zone d'extrémité de base (3) de l'aube (1), en direction de la zone centrale (10), de sorte que l'aube (1) est déplacée le long de son axe (2) de façon convexe. En outre, des profils de section (5a, 5b; 15a, 15b) situés, dans le sens axial, à une certaine distance les uns des autres, sont soumis à une torsion, les uns par rapport aux autres, dans la zone d'extrémité de base (3) et/ou dans la zone d'extrémité de base (4). L'invention concerne également une turbine à vapeur (11).
EP98951240A 1997-09-08 1998-08-31 Aube pour une turbomachine Expired - Lifetime EP1012445B2 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19739318 1997-09-08
DE19739318 1997-09-08
PCT/DE1998/002556 WO1999013199A1 (fr) 1997-09-08 1998-08-31 Aube pour une turbomachine, et turbine a vapeur

Publications (3)

Publication Number Publication Date
EP1012445A1 true EP1012445A1 (fr) 2000-06-28
EP1012445B1 EP1012445B1 (fr) 2002-10-02
EP1012445B2 EP1012445B2 (fr) 2008-01-16

Family

ID=7841609

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98951240A Expired - Lifetime EP1012445B2 (fr) 1997-09-08 1998-08-31 Aube pour une turbomachine

Country Status (8)

Country Link
US (1) US6354798B1 (fr)
EP (1) EP1012445B2 (fr)
JP (1) JP4217000B2 (fr)
KR (1) KR20010023783A (fr)
CN (1) CN1100195C (fr)
AT (1) ATE225460T1 (fr)
DE (1) DE59805843D1 (fr)
WO (1) WO1999013199A1 (fr)

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DE10027084C2 (de) * 2000-05-31 2002-07-18 Honda Motor Co Ltd Leitschaufel und Leitschaufelkaskade für einen Axialverdichter
US6682301B2 (en) * 2001-10-05 2004-01-27 General Electric Company Reduced shock transonic airfoil
EP1314859B1 (fr) * 2001-11-22 2006-08-02 Siemens Aktiengesellschaft Procédé de fabrication de turbines à vapeur
PL372916A1 (en) 2002-04-11 2005-08-08 Richard A. Haase Water combustion technology-methods, processes, systems and apparatus for the combustion of hydrogen and oxygen
CA2426892C (fr) 2002-08-16 2011-10-25 The Fuel Genie Corporation Dispositif et methode changeant la vitesse angulaire d'un ecoulement d'air
US7262550B2 (en) * 2003-04-15 2007-08-28 Luminus Devices, Inc. Light emitting diode utilizing a physical pattern
EP1710397B1 (fr) * 2005-03-31 2014-06-11 Kabushiki Kaisha Toshiba Aube de guidage courbée
FR2903138B1 (fr) * 2006-06-28 2017-10-06 Snecma Aube mobile et disque de rotor de turbomachine, et dispositif d'attache d'une telle aube sur un tel disque
US8545170B2 (en) * 2009-10-27 2013-10-01 General Electric Company Turbo machine efficiency equalizer system
US8342009B2 (en) 2011-05-10 2013-01-01 General Electric Company Method for determining steampath efficiency of a steam turbine section with internal leakage
ITTO20111009A1 (it) * 2011-11-03 2013-05-04 Avio Spa Profilo aerodinamico di una turbina
US9032733B2 (en) 2013-04-04 2015-05-19 General Electric Company Turbomachine system with direct header steam injection, related control system and program product
CN107489461A (zh) * 2017-09-15 2017-12-19 哈尔滨汽轮机厂有限责任公司 一种用于汽轮机叶片的高效宽负荷叶型
RU191926U1 (ru) * 2019-02-28 2019-08-28 Публичное Акционерное Общество "Одк-Сатурн" Сопловой аппарат турбины
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Also Published As

Publication number Publication date
WO1999013199A1 (fr) 1999-03-18
EP1012445B2 (fr) 2008-01-16
ATE225460T1 (de) 2002-10-15
JP2001515983A (ja) 2001-09-25
EP1012445B1 (fr) 2002-10-02
DE59805843D1 (de) 2002-11-07
JP4217000B2 (ja) 2009-01-28
CN1100195C (zh) 2003-01-29
US6354798B1 (en) 2002-03-12
KR20010023783A (ko) 2001-03-26
CN1269865A (zh) 2000-10-11

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