EP2173972A1 - Rotor pour turbomachine à flux axial - Google Patents

Rotor pour turbomachine à flux axial

Info

Publication number
EP2173972A1
EP2173972A1 EP08787065A EP08787065A EP2173972A1 EP 2173972 A1 EP2173972 A1 EP 2173972A1 EP 08787065 A EP08787065 A EP 08787065A EP 08787065 A EP08787065 A EP 08787065A EP 2173972 A1 EP2173972 A1 EP 2173972A1
Authority
EP
European Patent Office
Prior art keywords
rotor
drum
discs
outer diameter
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
EP08787065A
Other languages
German (de)
English (en)
Other versions
EP2173972B1 (fr
Inventor
Douglas J. Arrell
David W. Hunt
Karsten Kolk
Harald Hoell
Harald Nimptsch
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
Application filed by Siemens AG filed Critical Siemens AG
Priority to PL08787065T priority Critical patent/PL2173972T3/pl
Priority to EP08787065A priority patent/EP2173972B1/fr
Publication of EP2173972A1 publication Critical patent/EP2173972A1/fr
Application granted granted Critical
Publication of EP2173972B1 publication Critical patent/EP2173972B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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
    • F01D5/02—Blade-carrying members, e.g. rotors
    • F01D5/06—Rotors for more than one axial stage, e.g. of drum or multiple disc type; Details thereof, e.g. shafts, shaft connections
    • 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
    • F01D5/28—Selecting particular materials; Particular measures relating thereto; Measures against erosion or corrosion
    • 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
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/053—Shafts
    • 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
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/32—Rotors specially for elastic fluids for axial flow pumps
    • F04D29/321—Rotors specially for elastic fluids for axial flow pumps for axial flow compressors
    • 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
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/582—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps
    • F04D29/584—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps cooling or heating the machine
    • 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
    • F05D2240/00—Components
    • F05D2240/20—Rotors
    • 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
    • F05D2300/00—Materials; Properties thereof
    • F05D2300/50—Intrinsic material properties or characteristics
    • F05D2300/502—Thermal properties

Definitions

  • the invention relates to a rotor for an axially flow-through flow machine, with a plurality of stacked rotor disks, which are clamped together axially by means of at least one tie rod and each having an outer diameter.
  • the rotor disks used in the rotor are known to carry on their outer sides in a ring arranged blades, by means of which a working medium compressible or by means of which the energy contained in a working medium can be converted into the rotational movement of the rotor.
  • the adjacent stacked rotor discs are braced together by at least one tie rod.
  • the tie rod extends through the rotor discs and is prestressed by nuts screwed on at the end. The tie rod ensures the fixed contact of the rotor discs.
  • a welded-together rotor can have an outer drum-shaped heat protection jacket for protecting the inner region of the rotor.
  • a cooled gas turbine engine is known. Its outer periphery is formed by annular blade carriers, which are provided to the axis with opposite recesses. In each of these recesses engages in each case a projecting edge of a rotor disk, so that the respective blade carrier is positively clamped between two rotor disks.
  • drum barrel for gas turbines from the patent CH 238 207
  • the drum barrel includes one out a plurality of rings axially assembled drum, which are welded together at the outer drum circumference at the joints.
  • the edge of a rotor disk is frictionally bordered in the region of the joints between two adjacent rings.
  • the object of the invention is therefore to provide a rotor for an axially flow-through turbomachine, preferably for a high-pressure compressor with a pressure ratio of greater than 1:16 and a comparatively large compressor mass flow, in which, while maintaining the concept with stacked contiguous rotor discs a cost-effective construction specified can be.
  • the rotor should have a particularly long life.
  • the efficiency of the compressor should be further improved.
  • a multi-part rotor as seen in its radial direction, is thus proposed, in which the inner rotor disks can be made of a different material than the drum provided on the outside.
  • the most suitable materials can thus be selected for the different loads on the drum and rotor discs.
  • both the drum and the encompassed rotor disks with a smaller diameter can each be made of a material with which a particularly long service life of the component can be achieved.
  • a device is specified, by means of which the drum can be connected in a rotationally fixed manner to the rotor disks of smaller diameter.
  • a slip-laden relative movement between the outside arranged drum and radially further inwardly arranged rotor discs is thus not possible, whereby a total of transmitted between the components to be transmitted torques and forces can be passed lossless.
  • the drum allows the sealing of gaps between the two rotor disks, so that at this point in the prior art possibly existing leakage current can be suppressed here. This increases the efficiency of the compressor.
  • the rotor disks can also be better examined for any material inclusions, imperfections and / or cracks which may be present by means of the known ultrasonic methods than the rotor disks with a larger diameter known from the prior art.
  • Advantageous embodiments are specified in the subclaims.
  • Rotor disc is arranged with the larger outer diameter immediately adjacent to the rotor disc with the smaller outer diameter.
  • the blades are hooked directly to the rotor disc with a larger diameter, whereas in the axial portion of the rotor, in which the
  • Rotor disc is arranged with a smaller diameter, the blades are hooked directly to the drum.
  • the rotor comprises a first section with a disk rotor and a second section with a drum rotor with internal rotor disks, which is preferably encompassed along its entire axial extent from the drum.
  • the web of the drum extends radially further inward than the rotor disk with a smaller outer diameter and has an axial width such that the web extends at least partially into a hub opening of the rotor disk with a smaller diameter.
  • the two - seen in the axial direction of the rotor - outer of the rotor disks gripped by the drum are hooked with the latter for receiving centrifugal force loads.
  • the drum thus encompasses at least two rotor disks, with the two outer rotor disks - seen in the axial direction - each providing an entanglement on their outer peripheries which can be brought into engagement with a corresponding hook or groove provided on the inside of the drum.
  • the direction of entanglement is selected so that the centrifugal force loads acting on the drum from the rotor disks at least partially can be included.
  • the centrifugal force occurring in this section of the rotor can be evenly distributed from the drum to the rotor discs arranged radially further inside. Due to the required mountability of the stackable construction with radially inwardly arranged rotor disks and radially outwardly arranged drum, it is necessary that at least the two outer rotor disks are hooked to the drum. In an arrangement in which the drum engages around only two rotor disks, thus both rotor disks are hooked to the drum.
  • the drum is formed of a heat-resistant material than the rotor disks.
  • this is a particularly inexpensive rotor can be specified because the heat-resistant and cost-intensive material is only to use for the drum.
  • the construction according to the invention is preferably used in the rear stages of an axial compressor in which particularly high temperatures in the range of greater than 400 ° C. occur during the compression process. With a more heat resistant drum, the life of the rotor can at least be maintained, if not extended even further. Since a lower temperature prevails in the interior of the rotor due to the temperature gradients in the drum material than in the air to be compressed, it may be sufficient that the rotor disks are made of a material which meets lower requirements in terms of temperature resistance.
  • the material of the rotor disks can be a cheaper than the material of the drum.
  • the drum may be made of a nickel-based alloy and the rotor disks encompassed by it may be made of a heat-resistant steel or alloy.
  • the web has two opposite flange-like end faces on, abut the flange-like end faces of adjacent rotor discs.
  • the end face of the rotor discs is positively against the end face of the web.
  • the positive connection can be produced by means of a Hirth toothing.
  • the drum has at least one groove for receiving at least one blade.
  • the groove is formed as a circumferential groove, so that in the circumferential groove all blades of a Laufschau- felkranzes can be used.
  • the use of circumferential grooves allows a particularly large number of blades per ring.
  • the circumferential grooves are cheaper to manufacture than axially extending slots for blades.
  • the number of circumferential grooves can be greater than the number of rotor disks encompassed by the drum.
  • Previously it was in the prior art so that each rotor blade stage a rotor disk was provided with a circumferential groove. This caused a comparatively large axial space for mounting the blades on the rotor.
  • the solution proposed can achieve a comparatively short axial installation space for the rotor and for the housing since, for example, when using two rotor disks, it is possible to provide three circumferential grooves on the outer circumference of the drum. can be used in the respective blades of different blade rings.
  • the outside of the drum for receiving arranged in wreath blades is formed, wherein the number of mountable blade rings can be greater than the number of rotor disks encompassed by the drum.
  • the invention is particularly useful when the rotor is used in a compressor with a pressure ratio greater than 1:16, wherein the compressor is preferably the compressor of a stationary gas turbine used for generating energy. Preferably, the rated power of the gas turbine is greater than 50 MW.
  • the invention can be used in principle in each section of a compressor.
  • the drum according to the invention preferably has an outer diameter of 1200 mm and larger.
  • the invention can also be used in the sections of the compressor, where - if only compressor discs without a drum would be used - this would have a smaller outer diameter than 1200 mm.
  • drum outer diameter smaller than 1200 mm are possible.
  • FIG. 1 shows a section through the longitudinal section through a rotor according to the invention
  • FIG 2 shows the same detail as FIG 1 with a modified drum.
  • FIG. 1 shows a section through the longitudinal section of a rotor 12 comprising a plurality of rotor disks 10 of a gas turbine (not shown).
  • the section of the rotor 12 is chosen so that this in the high pressure region of the
  • Axial compressor of the gas turbine is located.
  • the pumping direction of the axial compressor is from the left side of the drawing to the right side of the drawing.
  • the rotor disks 14, 16 are manufactured in a known configuration and have at their outer peripheries 18 each have a circumferential groove extending in the circumferential direction 20, which are provided for receiving blades of the compressor.
  • the rotor disks 14, 16 are flange-like against each other at a contact surface 22, wherein in this contact surface 22 a serration is provided for the positive connection.
  • Downstream and upstream refer to the direction of the compressed air flowing in the axial compressor.
  • the two rotor discs 24, 26 are encompassed by a longitudinally sectionally T-shaped, circular in cross-section drum 28.
  • the drum 28 has on its inner side 30 a radially inwardly directed endless circumferential ridge 32, which is provided with two opposite end surfaces 34.
  • the end faces 34 rest on the one hand on the rotor disk 24 and on the other hand on the rotor disk 26 on contact surfaces 36, 38 at.
  • the contact surfaces 36, 38 are structured such that in each case a positive connection in the form of a serration is provided.
  • Each of the rotor disks 24, 26 has in its outer region an axially extending circumferential hooks 40, 42.
  • the annular hooks 40, 42 each engage in an open towards the end face of the drum 28, arranged in this endless circumferential groove 44, 46 a.
  • the grooves 44, 46 thus each form a receptacle for the hooks 40, 42 arranged on the rotor disks 24, 26.
  • the drum 28 has on its outside also in the circumferential direction extending blade holding grooves 48, 50, 52, in each of which rotor blades are used in a blade ring.
  • the Laufschaufein have for this purpose to the blade retaining grooves 48, 50, 52 corresponding formed blade roots.
  • the guide shafts which can be inserted in the grooves 48, 50, 52 belong to the blade stages which carry out the last pressure increases in the medium to be compressed. Accordingly, the blade holding grooves 48, 50, 52 are arranged the last three compressor blade rings of the compressor. Due to the high temperatures occurring in the area of the drum 28 during the compression of the medium (air), it is made of a heat-resistant material than the rotor disks 24, 26 encompassed by the drum 28 and thus located radially further inward.
  • the rotor disks 24, 26 can thus are made of a less temperature-resistant material, since in their region lower temperatures than in the region of the drum 28.
  • the axial distance between the grooves 48 and 50 and between the grooves 50 and 52 in comparison is less than the distance in the use of three individual rotor discs instead of the drum 28, so that axial space can be saved in the compressor.
  • the saving of axial space overall allows the construction of a cheaper gas turbine or the construction of a cheaper compressor.
  • each of the rotor disks 24, 26 is hooked to the inside 30 of the drum 28. Even a slight placement of the two axially opposite ends 54, 56 of the drum 28 can thus be avoided.
  • the mechanical centrifugal force loads originating from the rotor can be transmitted from the drum 28 to the rotor disks 24, Be at least partially forwarded so that the mechanical stresses on the edge of the drum 28 remain within the allowable limits of the drum material.
  • tie rod 58 may of course also be provided a number of several, decentralized around the machine axis 60 concentrically arranged tie rods to press the rotor disks firmly together.
  • FIG 2 shows the same section of the gas turbine as FIG 1, wherein the same components are labeled with identical reference numerals.
  • the drum 28 shown in FIG. 2 has a modified web 32.
  • the web 32 according to the second embodiment of the drum 28 shown in FIG 2 extends not only up to those end surfaces 34 which abut against the contact surfaces 22 of the adjacent rotor disks 24, 26, but beyond this range.
  • the web 32 may also comprise a further hub region 62, the radial end of which lies substantially further inward than the contact surfaces 22 of the rotor disks 24, 26. In this way, a greater load capacity of the drum 28 can be achieved.
  • FIG 3 shows a further alternative embodiment of the invention is shown, wherein identical features are provided with identical reference numerals. Identical features also have the same function, so that the previous description for identical in Figure 3 design features also applies here. Subsequently, only the structural differences to FIG 2 will be explained in more detail.
  • the drum 28 according to FIG. 3 has a hub region 63 projecting even further radially inwards.
  • This hub portion 63 is also still in its axial Extent so wide that it lies radially within the hub areas 64 of the rotor disks 24, 26.
  • the boss portion 63 of the land 32 has an axial extent such that it extends partially into the hub opening 57 of the rotor disks 24, 26 of smaller diameter.
  • the invention thus relates to a rotor 12 for an axially flow-through turbomachine with a plurality of stacked rotor disks 10, 14, 16, 24, 26, which are braced by means of at least one tie rod 58 and each having an outer diameter.
  • a particularly inexpensive rotor 12 with a compact construction which is designed especially for particularly high pressure conditions with comparatively large compressor mass flows
  • at least one of the rotor disks 24, 26 of the rotor 12 have a smaller outer diameter than one of the adjacent rotor disks 16 and the existing difference in diameter is compensated by a rotor disk 24, 26 with a smaller outer diameter annularly encompassing drum 28.
  • only the drum 28 may be made of a more heat-resistant material.
  • the encompassed by her rotor discs 24, 26, however, can be made of a cheaper material, resulting in cost savings.
  • the drum 28 can carry at least one blade ring more than rotor disks 24, 26, which are encompassed by it.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Materials Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

L'invention concerne un rotor (12) pour une turbomachine à flux axial, avec plusieurs disques de rotor (10, 14, 16, 24, 26) disposés en pile qui sont interconnectés par contrainte au moyen d'au moins un tirant d'ancrage (58). L'invention vise à fournir un rotor (12) particulièrement économique, de construction compacte, qui soit notamment conçu pour des pressions particulièrement élevées avec des débits massiques de compresseur relativement élevés. A cet effet, au moins un des disques de rotor (24, 26) du rotor (12) présente un diamètre extérieur inférieur à celui d'un des disques de rotor voisins (16), et la différence de diamètre existante est compensée par un tambour (28) enserrant annulairement le disque de rotor (24, 26) de diamètre extérieur inférieur. A cet effet, seul le tambour (28) peut être réalisé dans un matériau plus résistant à la chaleur, tandis que les disques de rotor (24, 26) qu'il enserre peuvent être fabriqués en un matériau plus économique, ce qui réduit les coûts. De plus, le tambour (28) peut porter au moins une couronne d'aubes de plus que les disques de rotor (24, 26) qu'il enserre.
EP08787065A 2007-08-10 2008-08-08 Rotor pour turbomachine à flux axial Not-in-force EP2173972B1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
PL08787065T PL2173972T3 (pl) 2007-08-10 2008-08-08 Wirnik dla osiowej maszyny przepływowej
EP08787065A EP2173972B1 (fr) 2007-08-10 2008-08-08 Rotor pour turbomachine à flux axial

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP07015785A EP2025867A1 (fr) 2007-08-10 2007-08-10 Rotor pour une turbomachine
PCT/EP2008/060480 WO2009021927A1 (fr) 2007-08-10 2008-08-08 Rotor pour turbomachine à flux axial
EP08787065A EP2173972B1 (fr) 2007-08-10 2008-08-08 Rotor pour turbomachine à flux axial

Publications (2)

Publication Number Publication Date
EP2173972A1 true EP2173972A1 (fr) 2010-04-14
EP2173972B1 EP2173972B1 (fr) 2013-03-06

Family

ID=38871761

Family Applications (2)

Application Number Title Priority Date Filing Date
EP07015785A Withdrawn EP2025867A1 (fr) 2007-08-10 2007-08-10 Rotor pour une turbomachine
EP08787065A Not-in-force EP2173972B1 (fr) 2007-08-10 2008-08-08 Rotor pour turbomachine à flux axial

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP07015785A Withdrawn EP2025867A1 (fr) 2007-08-10 2007-08-10 Rotor pour une turbomachine

Country Status (8)

Country Link
US (1) US8459951B2 (fr)
EP (2) EP2025867A1 (fr)
JP (1) JP5235996B2 (fr)
CN (1) CN101779000B (fr)
ES (1) ES2404579T3 (fr)
PL (1) PL2173972T3 (fr)
RU (1) RU2479725C2 (fr)
WO (1) WO2009021927A1 (fr)

Families Citing this family (8)

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Publication number Priority date Publication date Assignee Title
US20130017092A1 (en) * 2011-07-11 2013-01-17 General Electric Company Rotor assembly for gas turbines
US20130264779A1 (en) * 2012-04-10 2013-10-10 General Electric Company Segmented interstage seal system
CN105275499B (zh) * 2015-06-26 2016-11-30 中航空天发动机研究院有限公司 一种具有离心增压和封严效果的双辐板涡轮盘盘心进气结构
US20240084708A1 (en) * 2016-02-05 2024-03-14 Siemens Energy Global GmbH & Co. KG Rotor comprising a rotor component arranged between two rotor discs
WO2021073786A1 (fr) * 2019-10-18 2021-04-22 Siemens Energy Global GmbH & Co. KG Rotor comprenant un composant de rotor disposé entre deux disques de rotor
KR101882132B1 (ko) * 2017-02-03 2018-07-25 두산중공업 주식회사 가스터빈 압축기 섹션의 디스크 조립체
KR101896436B1 (ko) * 2017-04-12 2018-09-10 두산중공업 주식회사 보강디스크를 포함하는 압축기 및 이를 포함하는 가스터빈
CN112534119B (zh) * 2018-08-02 2023-04-14 西门子能源全球有限两合公司 具有设置在两个转子盘之间的转子构件的转子

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CH238207A (de) * 1943-02-15 1945-06-30 Oerlikon Maschf Aus mehreren Teilen zusammengesetzter Trommelläufer für Dampf- und Gasturbinen.
CH242918A (de) * 1944-12-20 1946-06-15 Oerlikon Maschf Umlaufende Trommel für Turbomaschinen.
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GB755290A (en) * 1953-07-02 1956-08-22 Siemens Ag Improvements in or relating to gas turbine rotors
FR2272259B1 (fr) * 1974-05-21 1977-03-11 Alsthom Cgee
FR2566835B1 (fr) * 1984-06-27 1986-10-31 Snecma Dispositif de fixation de secteurs d'aubes sur un rotor de turbomachine
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Also Published As

Publication number Publication date
US20110318184A1 (en) 2011-12-29
RU2010108465A (ru) 2011-09-20
JP2010535973A (ja) 2010-11-25
EP2173972B1 (fr) 2013-03-06
CN101779000A (zh) 2010-07-14
ES2404579T3 (es) 2013-05-28
RU2479725C2 (ru) 2013-04-20
JP5235996B2 (ja) 2013-07-10
WO2009021927A1 (fr) 2009-02-19
PL2173972T3 (pl) 2013-08-30
US8459951B2 (en) 2013-06-11
EP2025867A1 (fr) 2009-02-18
CN101779000B (zh) 2013-04-17

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