EP3337958B1 - Rotor pour une turbomachine - Google Patents

Rotor pour une turbomachine Download PDF

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Publication number
EP3337958B1
EP3337958B1 EP16805333.8A EP16805333A EP3337958B1 EP 3337958 B1 EP3337958 B1 EP 3337958B1 EP 16805333 A EP16805333 A EP 16805333A EP 3337958 B1 EP3337958 B1 EP 3337958B1
Authority
EP
European Patent Office
Prior art keywords
tie rod
rotor
segments
rotor segment
adjacent
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
EP16805333.8A
Other languages
German (de)
English (en)
Other versions
EP3337958A1 (fr
Inventor
Steffen JAHRMARCHT
Kevin MINY
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 Energy Global GmbH and Co KG
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
Publication of EP3337958A1 publication Critical patent/EP3337958A1/fr
Application granted granted Critical
Publication of EP3337958B1 publication Critical patent/EP3337958B1/fr
Active 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
    • 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
    • F01D5/026—Shaft to 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
    • F01D5/02—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
    • F01D5/066—Connecting means for joining rotor-discs or rotor-elements together, e.g. by a central bolt, by clamps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/10—Centrifugal pumps for compressing or evacuating
    • F04D17/12—Multi-stage pumps
    • F04D17/122—Multi-stage pumps the individual rotor discs being, one for each stage, on a common shaft and axially spaced, e.g. conventional centrifugal multi- stage 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
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/053—Shafts
    • F04D29/054—Arrangements for joining or assembling 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
    • F04D29/60—Mounting; Assembling; Disassembling
    • F04D29/62—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps
    • F04D29/624—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • 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
    • F05D2230/00—Manufacture
    • F05D2230/50—Building or constructing in particular ways
    • F05D2230/51—Building or constructing in particular ways in a modular way, e.g. using several identical or complementary parts or features
    • 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
    • F05D2240/60—Shafts
    • 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
    • F05D2260/00—Function
    • F05D2260/30—Retaining components in desired mutual position
    • F05D2260/31—Retaining bolts or nuts
    • 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
    • F05D2260/00—Function
    • F05D2260/96—Preventing, counteracting or reducing vibration or noise

Definitions

  • the invention relates to a rotor for a fluid flow machine, comprising a plurality of rotor segments, each provided with a central opening and arranged axially adjacent to one another, a single tie rod extending through the openings of the rotor segments and two tensioning means, which are located at axially opposite ends of the tie rod are arranged and brace the rotor segments against each other.
  • Such rotors are known in the prior art in different configurations and are used in turbomachines to convert forms of energy into one another.
  • the flow energy and / or enthalpy of a working fluid in a steam / gas turbine can be converted into rotational energy of a rotor (turbine rotor).
  • a rotating driven rotor can be used to draw in any gas and compress it for further use within an industrial process (compressor rotor).
  • Known runners comprise a plurality of rotor segments, each of which is provided with a central opening and is arranged axially adjacent to one another. Some of the rotor segments are designed as so-called wheel disks, each of which carries a ring of radially extending blades (rotor blades). Furthermore, such a runner usually comprises a single central tie rod that extends through the openings of the runner segments. At the axially opposite ends of the tie rod, two clamping means are arranged, which brace the rotor segments against each other.
  • the tie rod is excited to vibrate during operation of a turbomachine. Vibration frequencies at or near the natural frequency of the tie rod are to be avoided, since such resonant vibrations of the tie rod are Impair the function of the turbomachine or lead to damage / destruction of the tie rod.
  • Turbine rotors are usually operated with a low rotation frequency, which essentially corresponds to the network frequency of the respective power network.
  • the natural frequencies of the tie rods installed in turbine rotors are accordingly regularly well above this rotation frequency, which is why harmful resonant vibrations of the tie rod can hardly occur in turbine stages.
  • the natural frequency of the tie rod in particular a compressor rotor, which is basically determined by the dimensions and material properties of the tie rod and by the tensile force exerted on the tie rod with the aid of the tensioning means.
  • the factors mentioned have different effects on the natural frequency of the tie rod.
  • the natural frequency of the tie rod is lower, the longer the free vibration length of the tie rod.
  • the length of the compressor rotor - and thus also of the tie rod passing through it - can result in a relatively low natural frequency of the tie rod, which severely limits the possible rotational frequencies of the compressor rotor.
  • the natural frequency of the tie rod is higher, the higher the tensile force exerted on the tie rod by the tensioning means.
  • the natural frequency of a tie rod can be increased by tightening the rotor segments against each other.
  • the tensile force of the tie rod cannot be increased arbitrarily, since a maximum permissible tensile force must not be exceeded for the tie rod due to the material and dimensions, in order to avoid damage or tearing of the tie rod.
  • the present invention provides a rotor of the type mentioned at the beginning, the rotor segments of which form at least two rotor segment groups, between which at least one further tensioning means is arranged.
  • the invention is therefore based on the idea of dividing the rotor segments into at least two rotor segment groups and to provide at least one further clamping means between them.
  • This at least one further tensioning means is used to brace the rotor segments of one of the two rotor segment groups against one another together with an end tensioning means.
  • the rotor segments of the second rotor segment group are then braced against the already braced rotor segment group by the opposite end clamping means.
  • the original vibration length of the tie rod between the two end tensioning means is divided into two shorter vibration lengths, whereby the original natural frequency of the tie rod is replaced by two higher natural frequencies of the shorter tie rod sections.
  • the maximum possible rotation frequency of the rotor is increased accordingly.
  • the tie rod comprises a plurality of tie rod sections which are arranged axially adjacent to one another and are each assigned to a rotor segment group.
  • a tie rod divided into several sections in this way can be optimally adapted with regard to the different rotor segment groups and can facilitate the arrangement and function of further tensioning means between the rotor segment groups.
  • the tie rod sections are cylindrical in shape, the cylinder diameters of the tie rod sections gradually decreasing from one end of the tie rod to form a stepped outer contour.
  • a graduated tie rod allows easy handling of the other clamping means when arranging and adjusting.
  • such a tie rod can easily be produced in one piece, but this embodiment does not fall within the scope of the claims.
  • the tensioning means comprise a plurality of stop elements and pressure elements adjustable for tensioning, with which the rotor segments of a rotor segment group are subjected to an axial force in the direction of the respective stop element.
  • Stop elements and pressure elements are common clamping devices for bracing rotor segments against each other. By adjusting the pressure element In the direction of the stop element, the rotor segments of the rotor segment group can be subjected to the axial tensile force of the tie rod.
  • At least one stop element is advantageously formed by a rotor element. This reduces the number of clamping devices required and consequently the components required for the rotor.
  • the at least one stop element is formed by a rotor segment which has an axially extending threaded bore into which an external thread formed at a free end of the tie rod is screwed.
  • This rotor segment then forms one end of the tie rod and can be used, for example, to mount the rotor in a housing of the turbomachine.
  • the at least one stop element can be formed by a rotor segment of an adjacent rotor segment group.
  • At least one pressure element is formed by a nut screwed onto an external thread of the tie rod, which is arranged in a receiving space defined by at least one rotor segment and presses against an adjacent rotor segment.
  • Nuts of this type are standardized, readily available components which, with a correspondingly small pitch of the external thread of the tie rod, permit precise adjustment of the force exerted on the rotor segments.
  • Adjacent tie rod sections are screwed together, one tie rod section having an axially extending threaded bore into which an external thread formed at a free end of the adjacent tie rod section is screwed.
  • a tie rod that can be dismantled offers advantages during transport and manufacture. Screw connections facilitate the assembly of the individual tie rod sections.
  • Figure 1 shows a rotor 1 for a turbomachine (not shown), which can be installed, for example, as a compressor rotor in a radial compressor.
  • the rotor 1 comprises a plurality of rotor segments 2, which are arranged axially adjacent to one another.
  • the rotor segments 2 have serration teeth and are each provided with a central opening through which a single tie rod 3 extends.
  • the tie rod 3 comprises a plurality of tie rod sections 4 which are arranged axially adjacent to one another.
  • the tie rod sections 4 are cylindrical, the cylinder diameters of the tie rod sections 4 gradually decreasing from one end of the tie rod 3 to form a stepped outer contour. Adjacent tie rod sections 4 are connected to one another by a screw connection.
  • Each tie rod section 4 has an axially extending threaded bore 5, into which an external thread 6 formed at a free end of the adjacent tie rod section 4 is screwed.
  • the tie rod sections can also be connected or screwed together in another way. One-piece training is also possible.
  • the rotor 1 comprises tensioning means 7, 8, which are arranged at axially opposite ends of the tie rod 3 and brace the rotor segments 2 against one another, and further tensioning means 7, 8, which are arranged between the rotor elements 2.
  • the clamping means 7, 8 comprise stop elements 7, which in the present case are each formed by a rotor segment 2.
  • a rotor segment 2 serving as a stop element 7 is arranged at a free end of the tie rod 3 and has an axially extending threaded bore 5, into which an external thread 6 formed at the free end of the tie rod 3 is screwed.
  • stop elements 7 can also be provided as separate components that do not form a rotor segment 2.
  • the tensioning means 7, 8 comprise a plurality of pressure elements 8 which can be axially adjusted for tensioning and with which the rotor segments 2 are subjected to an axial force in the direction of respectively corresponding stop elements 7.
  • each pressure element 8 is formed by a nut 8 screwed onto an external thread 6 of the tie rod 3, which is arranged in a receiving space 9 defined by a rotor segment 2 and presses against this rotor segment 2.
  • pressure elements can also be formed by rotor segments, the central opening of which is formed, for example, as a threaded bore.
  • the rotor segments 2 form three rotor segment groups 10, between each of which a stop element 7 and a pressure element 8 are arranged.
  • a runner segment group 10 can comprise a single runner segment 2 or a plurality of runner segments 2.
  • Each runner segment group 10 is assigned to a tie rod section 4.
  • the number of rotor segment groups 10 can vary depending on the structure of rotor 1.
  • the rotor 1 rotates about an axis of rotation X.
  • the rotation of the rotor 1 sets the tie rod 3 in vibration, the vibrations of the tie rod 3 taking place in isolation in each tie rod section 4.
  • the natural frequencies lie the tie rod sections 4 each clearly above the natural frequency of a tie rod of the same overall length that is not divided into several sections. This ensures that the oscillation frequencies of the tie rod 3 remain significantly below the respective natural frequencies during the operation of the turbomachine. In this way, the occurrence of harmful resonance vibrations of the tie rod 3 is reliably ruled out, but without giving up the advantages associated with a single central tie rod 3, such as, for example, simple manufacture and assembly.

Landscapes

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

Claims (4)

  1. Rotor (1) d'une turbomachine,
    comprenant
    - une pluralité de segments (2) de rotor, qui sont pourvus chacun d'une ouverture au milieu et qui sont disposés en étant voisins axialement les uns des autres,
    - un tirant (3) unique passant dans les ouvertures des segments (2) de rotor et deux moyens (7, 8) de serrage, qui sont disposés aux extrémités opposées axialement du tirant (3) et qui serrent les segments (2) de rotor les uns contre les autres,
    les segments (2) de rotor formant au moins deux groupes (10) de segments de rotor, entre lesquels est disposé au moins un autre moyen (7, 8) de serrage, et le tirant (3) comprenant une pluralité de tronçons (4) de tirant de forme cylindrique, qui sont disposés les uns à côté des autres axialement et qui sont associés chacun à un groupe (10) de segments de rotor,
    le diamètre de cylindre des tronçons (4) de tirant décroissant pas à pas à partir d'une extrémité du tirant (3), en formant un contour extérieur étagé,
    les moyens (7, 8) de serrage comprenant plusieurs éléments (8) d'application d'une pression réglables axialement pour le serrage, par lesquels les segments (2) de rotor sont soumis à une force axiale en direction d'éléments (7) de butée correspondants respectivement, chaque élément (8) d'application d'une pression étant formé d'un écrou (8), qui est vissé sur un filetage (6) extérieur du tirant (3), qui est disposé dans un espace (9) de réception défini par un segment (2) de rotor et qui pousse ce segment (2) de rotor,
    caractérisé en ce que
    des tronçons (4) voisins du tirant sont vissés les uns aux autres, un tronçon (4) de tirant ayant un taraudage (5) s'étendant axialement, dans lequel est vissé un filetage (6) extérieur constitué à une extrémité libre du tronçon (4) voisin du tirant.
  2. Rotor suivant la revendication 1,
    caractérisé en ce qu'au moins un élément (7) de butée est formé d'un segment (2) de rotor.
  3. Rotor suivant la revendication 2,
    caractérisé en ce que le au moins un élément (7) de butée est formé d'un élément (2) de rotor, qui a un taraudage (5) s'étendant axialement, dans lequel est vissé un filetage (6) extérieur constitué à une extrémité libre du tirant (3).
  4. Rotor suivant l'une des revendications 2 ou 3,
    caractérisé en ce qu'au moins un élément (7) de butée est formé d'un segment (2) de rotor d'un groupe (10) voisin de segments de rotor.
EP16805333.8A 2015-12-16 2016-11-21 Rotor pour une turbomachine Active EP3337958B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015225428.3A DE102015225428A1 (de) 2015-12-16 2015-12-16 Läufer für eine Strömungsmaschine
PCT/EP2016/078306 WO2017102254A1 (fr) 2015-12-16 2016-11-21 Rotor pour une turbomachine

Publications (2)

Publication Number Publication Date
EP3337958A1 EP3337958A1 (fr) 2018-06-27
EP3337958B1 true EP3337958B1 (fr) 2020-06-17

Family

ID=57471812

Family Applications (1)

Application Number Title Priority Date Filing Date
EP16805333.8A Active EP3337958B1 (fr) 2015-12-16 2016-11-21 Rotor pour une turbomachine

Country Status (6)

Country Link
US (1) US10718212B2 (fr)
EP (1) EP3337958B1 (fr)
CN (1) CN108368742B (fr)
DE (1) DE102015225428A1 (fr)
RU (1) RU2700846C1 (fr)
WO (1) WO2017102254A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11885340B2 (en) * 2020-05-14 2024-01-30 Siemens Energy Global GmbH & Co. KG Compressor rotor structure
US11959485B2 (en) * 2020-05-14 2024-04-16 Siemens Energy Global GmbH & Co. KG Compressor rotor structure and method for arranging said rotor structure
WO2023200454A1 (fr) * 2022-04-15 2023-10-19 Siemens Energy Global GmbH & Co. KG Structure de rotor et procédé d'assemblage ou de désassemblage d'une telle structure de rotor

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2365185A2 (fr) * 2010-03-10 2011-09-14 United Technologies Corporation Assemblage du section compresseur et turbine d'un moteur de turbine à gaz doté d'un système d'accouplement par adhérence de l'arbre de compresseur haute pression

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3715176A (en) * 1971-09-01 1973-02-06 Carrier Corp Turbo machine rotor structure
NL7809282A (nl) * 1977-10-17 1979-04-19 Gen Electric Koppelingsorganen voor de rotorschijven van een gas- turbine-compressor.
US4497612A (en) * 1983-11-25 1985-02-05 General Electric Company Steam turbine wheel antirotation means
JP3042095B2 (ja) * 1991-10-16 2000-05-15 石川島播磨重工業株式会社 ガスタービンの締結装置
JP4591047B2 (ja) * 2004-11-12 2010-12-01 株式会社日立製作所 タービンロータ及びガスタービン
IT1399904B1 (it) * 2010-04-21 2013-05-09 Nuovo Pignone Spa Rotore impilato con tirante e flangia imbullonata e metodo
CA2884133A1 (fr) 2012-09-07 2014-03-13 Siemens Aktiengesellschaft Procede permettant d'assembler ou de desassembler un rotor comportant une pluralite d'elements de rotor pour une turbomachine a ecoulement axial et rotor de ce type
ITCO20130071A1 (it) * 2013-12-18 2015-06-19 Nuovo Pignone Srl Metodo per assemblare un insieme di giranti mediante tiranti, girante e turbomacchina

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2365185A2 (fr) * 2010-03-10 2011-09-14 United Technologies Corporation Assemblage du section compresseur et turbine d'un moteur de turbine à gaz doté d'un système d'accouplement par adhérence de l'arbre de compresseur haute pression

Also Published As

Publication number Publication date
RU2700846C1 (ru) 2019-09-23
CN108368742A (zh) 2018-08-03
EP3337958A1 (fr) 2018-06-27
US10718212B2 (en) 2020-07-21
WO2017102254A1 (fr) 2017-06-22
DE102015225428A1 (de) 2017-07-06
CN108368742B (zh) 2020-08-18
US20180371916A1 (en) 2018-12-27

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