EP3337958A1 - Rotor for a turbomachine - Google Patents

Rotor for a turbomachine

Info

Publication number
EP3337958A1
EP3337958A1 EP16805333.8A EP16805333A EP3337958A1 EP 3337958 A1 EP3337958 A1 EP 3337958A1 EP 16805333 A EP16805333 A EP 16805333A EP 3337958 A1 EP3337958 A1 EP 3337958A1
Authority
EP
European Patent Office
Prior art keywords
rotor
tie rod
adjacent
segments
segment
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
EP16805333.8A
Other languages
German (de)
French (fr)
Other versions
EP3337958B1 (en
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/en
Application granted granted Critical
Publication of EP3337958B1 publication Critical patent/EP3337958B1/en
Active 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
    • F01D5/026—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 turbomachine, comprising a plurality of rotor segments, each provided with a central opening and arranged axially adjacent to each other, a single extending through the openings of the rotor segments tie rods and two clamping means, the axial opposite ends of the tie rod are arranged and brace the rotor segments against each other.
  • Such runners are known in the prior art in different embodiments and are used in turbomachines to convert energy forms into each other. For example, the flow energy and / or enthalpy of a
  • Working fluids are converted in a steam / gas turbine into rotational energy of a rotor (turbine rotor).
  • a rotatably driven rotor may be used to aspirate any gas and compress it for further use within an industrial process
  • Known runners comprise a plurality of runner segments, each provided with a central opening and axially adjacent to each other.
  • Some of the Läufersegmen ⁇ te are designed as so-called wheel disc, each ⁇ wells a ring of radially extending blades wear (blades).
  • such a traveler usually comprises a single central tie rod which extends through the openings of the rotor segments. At axially opposite ends of the tie rod two clamping means are arranged, which clamp the rotor segments against each other.
  • Turbine rotors are usually operated at a low rotational frequency, which essentially corresponds to the grid frequency of the respective power grid.
  • the natural frequencies of the installed in turbine rotors tie rods are accordingly regularly well above this rotational frequency, which is why an occurrence of harmful resonant vibrations of the tie rod in turbine stages can hardly occur.
  • the Eigenfre acid sequence of the tie rod in particular a compression rotor, which generally ca- pacity by the dimensions and material of the tie rod, and is determined by the force exerted by means of tensioning means to tension the tie rod.
  • the factors mentioned have a different effect on the natural frequency of the tie rod.
  • the natural frequency of the tie rod is the lower, the longer the free oscillation length of the tie rod.
  • the plurality of wheel discs and other rotor segments may be for the compressor rotor - and thus also for him passing through tie rods - quite a length result, which is associated with a relatively low natural frequency of the tie rod, what the possible rotational frequencies of
  • Compressor rotor severely limits.
  • the natural frequency of the tie rod is the higher, the higher is the force exerted on the tie rods on the tension means.
  • the natural frequency of a tie rod can be increased by straining the rotor segments more strongly against each other.
  • the tensile ⁇ force of the tie rod can not be increased arbitrarily, as for the tie rod material and dimensions due to a maximum to ⁇ casual tensile force may not be exceeded in order to avoid a Be ⁇ damage or tearing of the tie rod.
  • the present invention provides a rotor of the type mentioned, whose rotor segments form at least two rotor segment groups, between which at least one further clamping means is arranged.
  • the invention is thus based on the idea to divide the Läuferseg ⁇ elements in at least two rotor segment groups and hen between these at least one further clamping means vorzuse-.
  • This at least one further clamping means is verwen ⁇ det to clamp together with an end-side clamping means the rotor segments of one of the two rotor segment groups against each other.
  • the runner segments of the second runner ment group are then clamped by the opposite end clamping means against the already strained runner segment group.
  • the original vibra ⁇ tion length of the tie rod between the two end clamping means is divided into two shorter oscillation lengths, whereby the original natural frequency of the tie rod is replaced by two higher natural frequencies of the shorter Switzerlandankerabroughe. Accordingly, the maximum possible Rotati ⁇ onsfrequenz of the rotor is increased.
  • the clamping means comprise a stop element and a verspan ⁇ nen adjustable pressure element, with which the rotor segments of a rotor segment group are subjected to an axial force in the direction of the stop element.
  • Stop elements and pressure elements are common clamping means to clamp Läuferseg ⁇ elements against each other.
  • Pressure element in the direction of the stop element can be applied to the rotor segments of the rotor segment group with the axial tensile force of the tie rod.
  • At least one stop element is advantageously formed by a runner element. This reduces the number of required clamping devices and consequently the components required for the rotor.
  • the at least one stop element is gebil ⁇ det of a rotor segment, which has an axially extending threaded hole ⁇ , into which a ⁇ out at a free end of the tie rod ⁇ formed external thread is screwed.
  • This rotor segment then forms one end of the tie rod and can serve, for example, the bearing of the rotor in a housing of the Strömungsma ⁇ machine.
  • the at least one stop element may be formed by a rotor segment of an adjacent rotor segment group.
  • at least one pressure element is formed by a screwed onto an external thread of the tie rod nut which is arranged at a defined by at least one rotor segment up receiving space and pushes against an adjacent rotor ⁇ segment.
  • Such nuts represent standardized, readily available components, the precise A ⁇ position the force exerted on the rotor segments ben Erlau at correspondingly low pitch of the external thread of the tension rod.
  • the tie rod comprises a plurality of tie rod sections, which are arranged axially adjacent to each other and are advantageously assigned to a respective rotor segment group.
  • Such a tie rod divided into several sections can be optimally adapted with regard to the different rotor segment groups and facilitate the arrangement and function of further tensioning means between the rotor segment groups.
  • the tie rod sections are cylin ⁇ derförmig, wherein the cylinder diameter of the Wernere starting from one end of the tie rod gradually decrease to form a stepped outer contour.
  • a stepped tie rods permits a simple handle lo ⁇ bung of the further tensioning means for placing and adjusting.
  • such a tie rod can be easily manufactured in one piece.
  • Buchankerabête adjacent to each other can also be ver ⁇ screwed, wherein a Werankerabrough having an axially extending threaded bore, into which a hole formed at a free end of the adjacent Switzerlandankerabitess external thread is screwed.
  • a collapsible tie rod offers advantages during transport and production. Screw connections facilitate the assembly of the individual tie rod sections. Further features and advantages of the present invention will become apparent from the following description of an embodiment of the rotor according to the invention with reference to the accompanying drawings. That's it
  • Figure 1 is a cross-sectional view of a rotor according to a
  • Figure 1 shows a rotor 1 for a turbomachine (not shown), which may be installed, for example, as a compressor rotor in ei ⁇ nem radial compressor.
  • the rotor 1 comprises a plurality of rotor segments 2, which are arranged axially adjacent to each other.
  • the rotor segments 2 point
  • the tie rod 3 comprises a plurality of tie rod portions 4, which are arranged axially adjacent to each other.
  • the tie rod sections 4 are cylindrically thoroughly manufactured ⁇ det, wherein the cylinder diameter of the tie rod sections 4, starting from one end of the tie rod 3 gradually decrease to form a stepped outer contour.
  • Adjacent tie rod sections 4 are connected to each other by a screw connection.
  • a 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 rotor 1 comprises tightening means 7,8, which are arranged at axial ends of the tie rod ge ⁇ genüberificat 3 and the rotor segments 2 braced against each other, as well as further clamping 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 are.
  • serving as a stop element 7 runner ⁇ segment 2 is arranged at a free end of the tie rod 3 and has an axially extending threaded bore 5, into which a male formed on the free end of the tie rod 3 .gewinde 6 is screwed.
  • stop elements 7 can also be provided as separate components which do not form a rotor segment 2.
  • the tensioning means 7, 8 comprise a plurality of pressure elements 8 which are axially adjustable for clamping and with which the runner segments 2 are acted upon by an axial force in the direction of respectively corresponding stop elements 7.
  • ⁇ of the pressure member 8 is formed in the present case of a bolted on a réellege ⁇ thread 6 of the tie rod 3 nut 8, which is arranged in a space defined by a runner segment 2 receiving space 9, and presses against this race segment.
  • 2 Al ternatively ⁇ pressure elements can however also be formed by rotor segments whose central opening is formed for example as Ge ⁇ threaded bore.
  • the rotor segments 2 form in the illustrated embodiment, three rotor segment groups 10, between each of which a stop element 7 and a pressure element 8 are arranged.
  • a rotor segment group 10 may comprise a single rotor segment 2 or a plurality of rotor segments 2.
  • Each rotor segment group 10 is a Switzerlandankerab ⁇ section 4 assigned.
  • the number of rotor segment groups 10 may vary depending on the structure of the rotor 1.
  • the rotor 1 rotates about a rotation axis X.
  • the rotation of the rotor 1 causes the tie rod 3 to oscillate, whereby the vibrations of the tie rod 3 in each tie rod section 4 take place in isolation.

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)

Abstract

The invention relates to a rotor for a turbomachine, comprising a plurality of axially adjacently arranged rotor segments which are each provided with a central opening, an individual tie rod extending through the openings of the rotor segments, and two holding means which are arranged on axially opposing ends of the tie rod and hold the rotor segments together, the rotor segments forming at least two rotor segment groups between which at least one other holding means is arranged.

Description

Beschreibung description
Läufer für eine Strömungsmaschine Die Erfindung betrifft einen Läufer für eine Strömungsmaschine, umfassend eine Mehrzahl von Läufersegmenten, die jeweils mit einer mittigen Öffnung versehen und axial benachbart zueinander angeordnet sind, einen einzelnen sich durch die Öffnungen der Läufersegmente erstreckenden Zuganker und zwei Spannmittel, die an axial gegenüberliegenden Enden des Zugankers angeordnet sind und die Läufersegmente gegeneinander verspannen . The invention relates to a rotor for a turbomachine, comprising a plurality of rotor segments, each provided with a central opening and arranged axially adjacent to each other, a single extending through the openings of the rotor segments tie rods and two clamping means, the axial opposite ends of the tie rod are arranged and brace the rotor segments against each other.
Derartige Läufer sind im Stand der Technik in unterschiedli- chen Ausgestaltungen bekannt und dienen in Strömungsmaschinen dazu, Energieformen ineinander umzuwandeln. Beispielsweise kann die Strömungsenergie und/oder Enthalpie eines Such runners are known in the prior art in different embodiments and are used in turbomachines to convert energy forms into each other. For example, the flow energy and / or enthalpy of a
Arbeitsfluids in einer Dampf-/Gasturbine in Rotationsenergie eines Läufers umgewandelt werden (Turbinenläufer) . Alternativ kann ein rotierend angetriebener Läufer verwendet werden, um ein beliebiges Gas anzusaugen und zur weiteren Verwendung innerhalb eines industriellen Prozesses zu verdichten Working fluids are converted in a steam / gas turbine into rotational energy of a rotor (turbine rotor). Alternatively, a rotatably driven rotor may be used to aspirate any gas and compress it for further use within an industrial process
(Verdichterläufer) . Bekannte Läufer umfassen eine Mehrzahl von Läufersegmenten, die jeweils mit einer mittigen Öffnung versehen und axial benachbart zueinander angeordnet sind. Einige der Läufersegmen¬ te sind dabei als sogenannte Radscheiben ausgebildet, die je¬ weils einen Kranz sich radial erstreckender Schaufeln tragen (Laufschaufeln) . Ferner umfasst ein solcher Läufer zumeist einen einzelnen sich durch die Öffnungen der Läufersegmente ersteckenden zentralen Zuganker. An axial gegenüberliegenden Enden des Zugankers sind zwei Spannmittel angeordnet, welche die Läufersegmente gegeneinander verspannen. (Compressor rotor). Known runners comprise a plurality of runner segments, each provided with a central opening and axially adjacent to each other. Some of the Läufersegmen ¬ te are designed as so-called wheel disc, each ¬ weils a ring of radially extending blades wear (blades). Furthermore, such a traveler usually comprises a single central tie rod which extends through the openings of the rotor segments. At axially opposite ends of the tie rod two clamping means are arranged, which clamp the rotor segments against each other.
Während des Betriebs einer Strömungsmaschine wird der During operation of a turbomachine is the
Zuganker zu Schwingungen angeregt. Dabei sind Schwingungsfre¬ quenzen in Höhe oder nahe bei der Eigenfrequenz des Zugankers zu vermeiden, da solche Resonanzschwingungen des Zugankers die Funktion der Strömungsmaschine beeinträchtigen oder zu einer Schädigung/Zerstörung des Zugankers führen können. Turbinenläufer werden üblicherweise mit einer niedrigen Rotationsfrequenz betrieben, die im Wesentlichen der Netzfrequenz des jeweiligen Stromnetzes entspricht. Die Eigenfrequenzen der in Turbinenläufern verbauten Zuganker liegen entsprechend regelmäßig deutlich oberhalb dieser Rotationfrequenz, weshalb ein Auftreten schädlicher Resonanzschwingungen des Zugankers in Turbinenstufen kaum auftreten kann. Tie rod excited to vibrate. Here, Schwingungsfre ¬ frequencies at or near the natural frequency of the tension rod to avoid such resonance oscillations of the tie rod affect the function of the turbomachine or can lead to damage / destruction of the tie rod. Turbine rotors are usually operated at a low rotational frequency, which essentially corresponds to the grid frequency of the respective power grid. The natural frequencies of the installed in turbine rotors tie rods are accordingly regularly well above this rotational frequency, which is why an occurrence of harmful resonant vibrations of the tie rod in turbine stages can hardly occur.
Anders stellt sich die Situation für Verdichterläufer dar, da diese mit möglichst hohen Rotationsfrequenzen betrieben wer- den. Denn je höher die Rotationsfrequenz ist, desto größer ist die erzielbare Verdichterleistung. Sofern die Eigenfre¬ quenz des Zugankers eines Verdichterläufers nicht unterhalb der Rotationsfrequenz des Verdichterläufers liegen darf, stellt diese daher einen leistungsbegrenzenden Faktor für die Verdichterleistung dar. The situation is different for compressor rotors, since they are operated with the highest possible rotational frequencies. Because the higher the rotation frequency, the greater the achievable compressor performance. If the Eigenfre ¬ frequency of the tie rod of a compressor rotor may not be below the rotational frequency of the compressor rotor, this therefore represents a power limiting factor for the compressor performance.
Vor diesem Hintergrund ist es wünschenswert, die Eigenfre¬ quenz des Zugankers insbesondere eines Verdichtungsläufers zu erhöhen, die grundsätzlich durch die Abmessungen und Materi- aleigenschaften des Zugankers sowie durch die mit Hilfe der Spannmittel auf den Zuganker ausgeübte Zugkraft bestimmt wird. Dabei wirken sich die genannten Faktoren unterschiedlich auf die Eigenfrequenz des Zugankers aus. Die Eigenfrequenz des Zugankers liegt desto tiefer, je länger die freie Schwingungslänge des Zugankers ist. Infolge der Mehrzahl von Radscheiben und weiterer Läufersegmente kann sich für den Verdichterläufer - und damit auch für den ihn durchsetzenden Zuganker - durchaus eine Länge ergeben, die mit einer relativ niedrigen Eigenfrequenz des Zugankers einhergeht, was die möglichen Rotationsfrequenzen des Against this background, it is desirable to increase the Eigenfre acid sequence of the tie rod, in particular a compression rotor, which generally ca- pacity by the dimensions and material of the tie rod, and is determined by the force exerted by means of tensioning means to tension the tie rod. The factors mentioned have a different effect on the natural frequency of the tie rod. The natural frequency of the tie rod is the lower, the longer the free oscillation length of the tie rod. As a result of the plurality of wheel discs and other rotor segments may be for the compressor rotor - and thus also for him passing through tie rods - quite a length result, which is associated with a relatively low natural frequency of the tie rod, what the possible rotational frequencies of
Verdichterläufers stark einschränkt. Dagegen liegt die Eigenfrequenz des Zugankers desto höher, je höher die über die Spannmittel auf den Zuganker ausgeübte Zugkraft ist. Infolgedessen lässt sich die Eigenfrequenz eines Zugankers dadurch erhöhen, dass die Läufersegmente stär- ker gegeneinander verspannt werden. Allerdings kann die Zug¬ kraft des Zugankers nicht beliebig gesteigert werden, da für den Zuganker material- und abmessungsbedingt eine maximal zu¬ lässige Zugkraft nicht überschritten werden darf, um eine Be¬ schädigung bzw. ein Reißen des Zugankers zu vermeiden. Compressor rotor severely limits. In contrast, the natural frequency of the tie rod is the higher, the higher is the force exerted on the tie rods on the tension means. As a result, the natural frequency of a tie rod can be increased by straining the rotor segments more strongly against each other. However, the tensile ¬ force of the tie rod can not be increased arbitrarily, as for the tie rod material and dimensions due to a maximum to ¬ casual tensile force may not be exceeded in order to avoid a Be ¬ damage or tearing of the tie rod.
In der Praxis ist es daher nicht immer möglich, eine genügend hohe Eigenfrequenz des Zugankers konstruktiv einzustellen, um eine gewünschte Verdichterleistung zu erreichen. Diesem Problem wurde bislang entgegengetreten, indem abweichende Zugankeranordnungen verwendet wurden, die in der Regel aus mehreren kürzeren, dezentral angeordneten Zugankern bestehen. Ein Nachteil dieser Lösung ist jedoch, dass mit einem einzelnen zentralen Zuganker verbundene Vorteile, wie bei- spielsweise eine einfache Herstellung und Montage, nicht mehr realisierbar sind. In practice, it is therefore not always possible to constructively set a sufficiently high natural frequency of the tie rod in order to achieve a desired compressor performance. This problem has been counteracted so far by using deviating tie rod arrangements, which usually consist of several shorter, decentralized tie rods. A disadvantage of this solution, however, is that advantages associated with a single central tie rod, such as, for example, simple manufacture and assembly, can no longer be realized.
Es ist daher eine Aufgabe der vorliegenden Erfindung, einen verbesserten Läufer zu schaffen, der die genannten Nachteile überwindet und höhere Rotationsfrequenzen erlaubt. It is therefore an object of the present invention to provide an improved rotor that overcomes the aforementioned disadvantages and allows higher rotational frequencies.
Zur Lösung dieser Aufgabe schafft die vorliegende Erfindung einen Läufer der eingangs genannten Art, dessen Läufersegmente wenigstens zwei Läufersegmentgruppen bilden, zwischen de- nen wenigstens ein weiteres Spannmittel angeordnet ist. To achieve this object, the present invention provides a rotor of the type mentioned, whose rotor segments form at least two rotor segment groups, between which at least one further clamping means is arranged.
Der Erfindung liegt somit die Idee zugrunde, die Läuferseg¬ mente in wenigstens zwei Läufersegmentgruppen aufzuteilen und zwischen diesen wenigstens ein weiteres Spannmittel vorzuse- hen. Dieses wenigstens eine weitere Spannmittel wird verwen¬ det, um zusammen mit einem endseitigen Spannmittel die Läufersegmente einer der beiden Läufersegmentgruppen gegeneinander zu verspannen. Die Läufersegmente der zweiten Läuferseg- mentgruppe werden dann durch das gegenüberliegende endseitige Spannmittel gegen die bereits verspannte Läufersegmentgruppe verspannt. Auf diese Weise wird die ursprüngliche Schwin¬ gungslänge des Zugankers zwischen den beiden endseitigen Spannmitteln in zwei kürzere Schwingungslängen unterteilt, wodurch die ursprüngliche Eigenfrequenz des Zugankers durch zwei höhere Eigenfrequenzen der kürzeren Zugankerabschnitte ersetzt wird. Entsprechend wird die maximal mögliche Rotati¬ onsfrequenz des Läufers erhöht. The invention is thus based on the idea to divide the Läuferseg ¬ elements in at least two rotor segment groups and hen between these at least one further clamping means vorzuse-. This at least one further clamping means is verwen ¬ det to clamp together with an end-side clamping means the rotor segments of one of the two rotor segment groups against each other. The runner segments of the second runner ment group are then clamped by the opposite end clamping means against the already strained runner segment group. In this way, the original vibra ¬ tion length of the tie rod between the two end clamping means is divided into two shorter oscillation lengths, whereby the original natural frequency of the tie rod is replaced by two higher natural frequencies of the shorter Zugankerabschnitte. Accordingly, the maximum possible Rotati ¬ onsfrequenz of the rotor is increased.
Gemäß einer Ausführungsform der vorliegenden Erfindung umfassen die Spannmittel ein Anschlagelement und ein zum Verspan¬ nen verstellbares Druckelement, mit dem die Läufersegmente einer Läufersegmentgruppe mit einer Axialkraft in Richtung des Anschlagelements beaufschlagt sind. Anschlagelemente und Druckelemente stellen gängige Spannmittel dar, um Läuferseg¬ mente gegeneinander zu verspannen. Durch Verstellen des According to one embodiment of the present invention, the clamping means comprise a stop element and a verspan ¬ nen adjustable pressure element, with which the rotor segments of a rotor segment group are subjected to an axial force in the direction of the stop element. Stop elements and pressure elements are common clamping means to clamp Läuferseg ¬ elements against each other. By adjusting the
Druckelements in Richtung des Anschlagelements lassen sich die Läufersegmente der Läufersegmentgruppe mit der axialen Zugkraft des Zugankers beaufschlagen. Pressure element in the direction of the stop element can be applied to the rotor segments of the rotor segment group with the axial tensile force of the tie rod.
Vorteilhaft ist wenigstens ein Anschlagelement von einem Läu- ferelement gebildet. Dies verringert die Zahl der erforderli- chen Spannmittel und infolgedessen der für den Läufer benö- tigten Komponenten. At least one stop element is advantageously formed by a runner element. This reduces the number of required clamping devices and consequently the components required for the rotor.
Gemäß einer Variante der vorliegenden Erfindung ist das wenigstens eine Anschlagelement von einem Läufersegment gebil¬ det, das eine sich axial erstreckende Gewindebohrung auf¬ weist, in die ein an einem freien Ende des Zugankers ausge¬ bildetes Außengewinde geschraubt ist. Dieses Läufersegment bildet dann ein Ende des Zugankers und kann beispielsweise der Lagerung des Läufers in einem Gehäuse der Strömungsma¬ schine dienen. According to a variant of the present invention, the at least one stop element is gebil ¬ det of a rotor segment, which has an axially extending threaded hole ¬ , into which a ¬ out at a free end of the tie rod ¬ formed external thread is screwed. This rotor segment then forms one end of the tie rod and can serve, for example, the bearing of the rotor in a housing of the Strömungsma ¬ machine.
Gemäß einer weiteren Variante der vorliegenden Erfindung kann das wenigstens eine Anschlagelement von einem Läufersegment einer benachbarten Läufersegmentgruppe gebildet sein. Bevorzugt ist wenigstens ein Druckelement von einer auf ein Außengewinde des Zugankers geschraubten Mutter gebildet, die in einem wenigstens durch ein Läufersegment definierten Auf- nahmeraum angeordnet ist und gegen ein benachbartes Läufer¬ segment drückt. Derartige Muttern stellen standardisierte, leicht verfügbare Bauteile dar, die bei entsprechend geringer Steigung des Außengewindes des Zugankers eine präzise Ein¬ stellung der auf die Läufersegmente ausgeübten Kraft erlau- ben. According to a further variant of the present invention, the at least one stop element may be formed by a rotor segment of an adjacent rotor segment group. Preferably, at least one pressure element is formed by a screwed onto an external thread of the tie rod nut which is arranged at a defined by at least one rotor segment up receiving space and pushes against an adjacent rotor ¬ segment. Such nuts represent standardized, readily available components, the precise A ¬ position the force exerted on the rotor segments ben Erlau at correspondingly low pitch of the external thread of the tension rod.
Vorteilhaft umfasst der Zuganker eine Mehrzahl von Zugankerabschnitten, die axial benachbart zueinander angeordnet sind und vorteilhaft jeweils einer Läufersegmentgruppe zugeordnet sind. Ein derart in mehrere Abschnitte unterteilter Zuganker kann im Hinblick auf die unterschiedlichen Läufersegmentgruppen optimal angepasst sein und die Anordnung und Funktion weiterer Spannmittel zwischen den Läufersegmentgruppen erleichtern . Advantageously, the tie rod comprises a plurality of tie rod sections, which are arranged axially adjacent to each other and are advantageously assigned to a respective rotor segment group. Such a tie rod divided into several sections can be optimally adapted with regard to the different rotor segment groups and facilitate the arrangement and function of further tensioning means between the rotor segment groups.
Gemäß einer Ausgestaltung sind die Zugankerabschnitte zylin¬ derförmig ausgebildet, wobei die Zylinderdurchmesser der Zugankerabschnitte ausgehend von einem Ende des Zugankers unter Bildung einer abgestuften Außenkontur schrittweise abnehmen. Ein derart abgestufter Zuganker erlaubt eine einfache Handha¬ bung der weiteren Spannmittel bei dem Anordnen und Verstellen. Ferner kann ein solcher Zuganker problemlos einteilig hergestellt werden. Benachbarte Zugankerabschnitte können auch miteinander ver¬ schraubt sein, wobei ein Zugankerabschnitt eine sich axial erstreckende Gewindebohrung aufweist, in die ein an einem freien Ende des benachbarten Zugankerabschnitts ausgebildetes Außengewinde geschraubt ist. Ein zerlegbarer Zuganker bietet Vorteile beim Transport und bei der Herstellung. Schraubverbindungen erleichtern das Zusammenfügen der einzelnen Zugankerabschnitte . Weitere Merkmale und Vorteile der vorliegenden Erfindung werden anhand der nachfolgenden Beschreibung einer Ausführungsform des erfindungsgemäßen Läufers unter Bezugnahme auf die beiliegende Zeichnung deutlich. Darin ist According to one embodiment, the tie rod sections are cylin ¬ derförmig, wherein the cylinder diameter of the Zugankerabschnitte starting from one end of the tie rod gradually decrease to form a stepped outer contour. Such a stepped tie rods permits a simple handle lo ¬ bung of the further tensioning means for placing and adjusting. Furthermore, such a tie rod can be easily manufactured in one piece. Zugankerabschnitte adjacent to each other can also be ver ¬ screwed, wherein a Zugankerabschnitt having an axially extending threaded bore, into which a hole formed at a free end of the adjacent Zugankerabschnitts external thread is screwed. A collapsible tie rod offers advantages during transport and production. Screw connections facilitate the assembly of the individual tie rod sections. Further features and advantages of the present invention will become apparent from the following description of an embodiment of the rotor according to the invention with reference to the accompanying drawings. That's it
Figur 1 eine Querschnittsansicht eine Läufers gemäß einer Figure 1 is a cross-sectional view of a rotor according to a
Ausführungsform der vorliegenden Erfindung.  Embodiment of the present invention.
Figur 1 zeigt einen Läufer 1 für eine Strömungsmaschine (nicht dargestellt) , der beispielsweise als Verdichterläufer in ei¬ nem Radialverdichter verbaut sein kann. Der Läufer 1 umfasst eine Mehrzahl von Läufersegmenten 2, die axial benachbart zueinander angeordnet sind. Die Läufersegmente 2 weisen Figure 1 shows a rotor 1 for a turbomachine (not shown), which may be installed, for example, as a compressor rotor in ei ¬ nem radial compressor. The rotor 1 comprises a plurality of rotor segments 2, which are arranged axially adjacent to each other. The rotor segments 2 point
Hirthverzahnungen auf und sind jeweils mit einer mittigen Öffnung versehen, durch welche sich ein einzelner Zuganker 3 erstreckt. Der Zuganker 3 umfasst eine Mehrzahl von Zugankerabschnitten 4, die axial benachbart zueinander angeordnet sind. Die Zugankerabschnitte 4 sind zylinderförmig ausgebil¬ det, wobei die Zylinderdurchmesser der Zugankerabschnitte 4 ausgehend von einem Ende des Zugankers 3 unter Bildung einer abgestuften Außenkontur schrittweise abnehmen. Benachbarte Zugankerabschnitte 4 sind miteinander durch eine Schraubverbindung verbunden. Dabei weist jeweils ein Zugankerabschnitt 4 eine sich axial erstreckende Gewindebohrung 5 auf, in die ein an einem freien Ende des benachbarten Zugankerabschnitts 4 ausgebildetes Außengewinde 6 geschraubt ist. Selbstver¬ ständlich können die Zugankerabschnitte auch auf andere Weise miteinander verbunden oder verschraubt sein. Auch eine einteilige Ausbildung ist möglich. Hirth teeth on 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 portions 4, which are arranged axially adjacent to each other. The tie rod sections 4 are cylindrically ausgebil ¬ det, wherein the cylinder diameter of the tie rod sections 4, starting from one end of the tie rod 3 gradually decrease to form a stepped outer contour. Adjacent tie rod sections 4 are connected to each other by a screw connection. In this case, in each case a 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. Selbstver ¬ Naturally, the Zugankerabschnitte may be linked in other ways or bolted together. Even a one-piece education is possible.
Ferner umfasst der Läufer 1 Spannmittel 7,8, die an axial ge¬ genüberliegenden Enden des Zugankers 3 angeordnet sind und die Läufersegmente 2 gegeneinander verspannen, sowie weitere Spannmittel 7,8, die zwischen den Läuferelementen 2 angeord- net sind. Further, the rotor 1 comprises tightening means 7,8, which are arranged at axial ends of the tie rod ge ¬ genüberliegenden 3 and the rotor segments 2 braced against each other, as well as further clamping means 7,8 which are arranged between the rotor elements. 2
Die Spannmittel 7,8 umfassen einerseits Anschlagelemente 7, die vorliegend jeweils von einem Läufersegment 2 gebildet sind. Dabei ist ein als Anschlagelement 7 dienendes Läufer¬ segment 2 an einem freien Ende des Zugankers 3 angeordnet und weist eine sich axial erstreckende Gewindebohrung 5 auf, in die ein an dem freien Ende des Zugankers 3 ausgebildetes Au- ßengewinde 6 geschraubt ist. Anschlagelemente 7 können aber auch als separate Bauteile vorgesehen sein, die kein Läufersegment 2 bilden. On the one hand, the clamping means 7, 8 comprise stop elements 7, which in the present case are each formed by a rotor segment 2 are. In this case, serving as a stop element 7 runner ¬ segment 2 is arranged at a free end of the tie rod 3 and has an axially extending threaded bore 5, into which a male formed on the free end of the tie rod 3 ßengewinde 6 is screwed. However, stop elements 7 can also be provided as separate components which do not form a rotor segment 2.
Andererseits umfassen die Spannmittel 7,8 mehrere zum Ver- spannen axial verstellbare Druckelemente 8, mit denen die Läufersegmente 2 mit einer Axialkraft in Richtung jeweils korrespondierender Anschlagelemente 7 beaufschlagt sind. Je¬ des Druckelement 8 wird vorliegend von einer auf ein Außenge¬ winde 6 des Zugankers 3 geschraubten Mutter 8 gebildet, die in einem durch ein Läufersegment 2 definierten Aufnahmeraum 9 angeordnet ist und gegen dieses Läufersegment 2 drückt. Al¬ ternativ können Druckelemente aber auch durch Läufersegmente gebildet sein, deren mittige Öffnung beispielsweise als Ge¬ windebohrung ausgeformt ist. On the other hand, the tensioning means 7, 8 comprise a plurality of pressure elements 8 which are axially adjustable for clamping and with which the runner segments 2 are acted upon by an axial force in the direction of respectively corresponding stop elements 7. Depending ¬ of the pressure member 8 is formed in the present case of a bolted on a Außenge ¬ thread 6 of the tie rod 3 nut 8, which is arranged in a space defined by a runner segment 2 receiving space 9, and presses against this race segment. 2 Al ternatively ¬ pressure elements can however also be formed by rotor segments whose central opening is formed for example as Ge ¬ threaded bore.
Die Läufersegmente 2 bilden bei der dargestellten Ausführungsform drei Läufersegmentgruppen 10, zwischen denen jeweils ein Anschlagelement 7 und ein Druckelement 8 angeordnet sind. Dabei kann eine Läufersegmentgruppe 10 ein einzelnes Läufersegment 2 oder eine Mehrzahl von Läufersegmenten 2 umfassen. Jede Läufersegmentgruppe 10 ist einem Zugankerab¬ schnitt 4 zugeordnet. Die Zahl der Läufersegmentgruppen 10 kann aber je nach Aufbau des Läufers 1 variieren. Während des Betriebs der Strömungsmaschine rotiert der Läufer 1 um eine Drehachse X. Die Rotation des Läufers 1 versetzt den Zuganker 3 in Schwingungen, wobei die Schwingungen des Zugankers 3 in jedem Zugankerabschnitt 4 isoliert erfolgen. Da die Längen der einzelnen Zugankerabschnitte 4 kürzer als die Länge des gesamten Zugankers 3 sind, liegen die Eigenfre¬ quenzen der Zugankerabschnitte 4 jeweils deutlich oberhalb der Eigenfrequenz eines nicht in mehrere Abschnitte unter¬ teilten Zugankers gleicher Gesamtlänge. Dies stellt sicher, dass die Schwingungsfrequenzen des Zugankers 3 während des Betriebs der Strömungsmaschine deutlich unterhalb der jewei¬ ligen Eigenfrequenzen bleiben. Auf diese Weise wird das Auftreten schädlicher Resonanzschwingungen des Zugankers 3 ver- lässlich ausgeschlossen, ohne allerdings die mit einem einzelnen zentralen Zuganker 3 verbundenen Vorteile aufzugeben, wie beispielsweise eine einfache Herstellung und Montage. The rotor segments 2 form in the illustrated embodiment, three rotor segment groups 10, between each of which a stop element 7 and a pressure element 8 are arranged. In this case, a rotor segment group 10 may comprise a single rotor segment 2 or a plurality of rotor segments 2. Each rotor segment group 10 is a Zugankerab ¬ section 4 assigned. However, the number of rotor segment groups 10 may vary depending on the structure of the rotor 1. During operation of the turbomachine, the rotor 1 rotates about a rotation axis X. The rotation of the rotor 1 causes the tie rod 3 to oscillate, whereby the vibrations of the tie rod 3 in each tie rod section 4 take place in isolation. Since the lengths of the individual tie rod sections 4 are shorter than the length of the entire tie rod 3, the Eigenfre ¬ frequencies of Zugankerabschnitte 4 are each well above the natural frequency of a not divided into several sections under ¬ tie rod of the same overall length. This ensures that the vibration frequencies of the tie rod 3 during operation of the turbomachine remain well below jewei ¬ ligen natural frequencies. In this way, the occurrence of harmful resonance vibrations of the tie rod 3 is reliably excluded, without, however, giving up the advantages associated with a single central tie rod 3, such as ease of manufacture and assembly.
Obwohl die Erfindung im Detail durch das bevorzugte Ausfüh- rungsbeispiel näher illustriert und beschrieben wurde, so ist die Erfindung nicht durch die offenbarten Beispiele einge¬ schränkt und andere Variationen können vom Fachmann hieraus abgeleitet werden, ohne den Schutzumfang der Erfindung zu verlassen . Although the invention in detail has been illustrated approximately example in more detail by the preferred execution and described, the invention is not ¬ limited by the disclosed examples and other variations can be derived by those skilled thereof, without departing from the scope of the invention.

Claims

Patentansprüche claims
1. Läufer (1) für eine Strömungsmaschine, 1. rotor (1) for a turbomachine,
umfassend eine Mehrzahl von Läufersegmenten (2), die jeweils mit einer mittigen Öffnung versehen und axial benachbart zueinander angeordnet sind, einen einzelnen sich durch die Öffnungen der Läufersegmente (2) erstreckenden Zuganker (3) und zwei Spannmittel (7, 8), die an axial gegenüberlie¬ genden Enden des Zugankers (3) angeordnet sind und die Läu¬ fersegmente (2) gegeneinander verspannen, dadurch gekennzeichnet, dass die Läufersegmente (2) wenigstens zwei Läu¬ fersegmentgruppen (10) bilden, zwischen denen wenigstens ein weiteres Spannmittel (7, 8) angeordnet ist. comprising a plurality of rotor segments (2), each provided with a central opening and arranged axially adjacent to each other, a single tie rod (3) extending through the openings of the rotor segments (2) and two tensioning means (7, 8) attached to axial gegenüberlie ¬ ing ends of the tie rod (3) are arranged and the Läu ¬ fersegmente (2) braced against each other, characterized in that the rotor segments (2) at least two Läu ¬ fersegmentgruppen (10) form, between which at least one further clamping means (7 , 8) is arranged.
2. Läufer nach Anspruch 1, 2. runner according to claim 1,
dadurch gekennzeichnet, dass die Spannmittel (7, 8) ein An¬ schlagelement (7) und ein zum Verspannen verstellbares Druckelement (8) umfassen, mit dem die Läufersegmente (2) einer Läufersegmentgruppe (10) mit einer Axialkraft in Richtung des Anschlagelements (7) beaufschlagt sind. characterized in that the clamping means (7, 8) comprise an on ¬ impact element (7) and for clamping adjustable pressure element (8) with which the rotor segments (2) of a rotor segment group (10) with an axial force in the direction of the stop element (7 ) are acted upon.
3. Läufer nach Anspruch 2, 3. runner according to claim 2,
dadurch gekennzeichnet, dass wenigstens ein Anschlagelement (7) von einem Läufersegment (2) gebildet ist.  characterized in that at least one stop element (7) is formed by a rotor segment (2).
4. Läufer nach Anspruch 3, 4. rotor according to claim 3,
dadurch gekennzeichnet, dass das wenigstens eine Anschlag¬ element (7) von einem Läufersegment (2) gebildet ist, das eine sich axial erstreckende Gewindebohrung (5) aufweist, in die ein an einem freien Ende des Zugankers (3) ausgebil¬ detes Außengewinde (6) geschraubt ist. characterized in that the at least one abutment ¬ element (7) by a rotor segment (2) is formed, which has an axially extending threaded bore (5) into which at a free end of the tie rod (3) ausgebil ¬ detes external thread ( 6) is screwed.
5. Läufer nach einem der Ansprüche 3 oder 4, 5. runner according to one of claims 3 or 4,
dadurch gekennzeichnet, dass das wenigstens eine Anschlag¬ element (7) von einem Läufersegment (2) einer benachbarten Läufersegmentgruppe (10) gebildet ist. characterized in that the at least one stop ¬ element (7) by a rotor segment (2) of an adjacent rotor segment group (10) is formed.
6. Läufer nach einem der Ansprüche 2 bis 5, 6. rotor according to one of claims 2 to 5,
dadurch gekennzeichnet, dass wenigstens ein Druckelement characterized in that at least one pressure element
(8) von einer auf ein Außengewinde (6) des Zugankers (3) geschraubten Mutter (8) gebildet ist, die in einem durch wenigstens ein Läufersegment (2) definierten Aufnahmeraum(8) is formed by a screwed onto an external thread (6) of the tie rod (3) nut (8) in a by at least one rotor segment (2) defined receiving space
(9) angeordnet ist und gegen ein benachbartes Läufersegment (2) drückt. (9) is arranged and presses against an adjacent runner segment (2).
7. Läufer nach einem der vorhergehenden Ansprüche, 7. runner according to one of the preceding claims,
dadurch gekennzeichnet, dass der Zuganker (3) eine Mehrzahl von Zugankerabschnitten (4) umfasst, die axial benachbart zueinander angeordnet sind und vorteilhaft jeweils einer Läufersegmentgruppe (10) zugeordnet sind.  characterized in that the tie rod (3) comprises a plurality of Zugankerabschnitten (4), which are arranged axially adjacent to each other and are advantageously associated with a respective rotor segment group (10).
8. Läufer nach Anspruch 7, 8. runner according to claim 7,
dadurch gekennzeichnet, dass die Zugankerabschnitte (4) zy¬ linderförmig ausgebildet sind, wobei die Zylinderdurchmes¬ ser der Zugankerabschnitte (4) ausgehend von einem Ende des Zugankers (3) unter Bildung einer abgestuften Außenkontur schrittweise abnehmen. characterized in that the tie rod sections (4) are formed zy ¬ linderförmig, the Zylinderdurchmes ¬ ser the tie rod sections (4), starting from one end of the tie rod (3) gradually decrease to form a stepped outer contour.
9. Läufer nach einem der Ansprüche 7 oder 8, 9. runner according to one of claims 7 or 8,
dadurch gekennzeichnet, dass benachbarte Zugankerabschnitte characterized in that adjacent tie rod sections
(4) miteinander verschraubt sind, wobei ein Zugankerab- schnitt (4) eine sich axial erstreckende Gewindebohrung(4) are screwed together, wherein a Zugankerab- section (4) has an axially extending threaded bore
(5) aufweist, in die ein an einem freien Ende des benachbarten Zugankerabschnitts (4) ausgebildetes Außengewinde (6) geschraubt ist. (5) into which a male thread (6) formed at a free end of the adjacent tie rod portion (4) is screwed.
EP16805333.8A 2015-12-16 2016-11-21 Rotor for a turbomachine Active EP3337958B1 (en)

Applications Claiming Priority (2)

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DE102015225428.3A DE102015225428A1 (en) 2015-12-16 2015-12-16 Runner for a turbomachine
PCT/EP2016/078306 WO2017102254A1 (en) 2015-12-16 2016-11-21 Rotor for a turbomachine

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EP3337958A1 true EP3337958A1 (en) 2018-06-27
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WO (1) WO2017102254A1 (en)

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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 (en) * 2022-04-15 2023-10-19 Siemens Energy Global GmbH & Co. KG Rotor structure and method for assembly or disassembly of such rotor structure

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Publication number Priority date Publication date Assignee Title
US3715176A (en) * 1971-09-01 1973-02-06 Carrier Corp Turbo machine rotor structure
NL7809282A (en) * 1977-10-17 1979-04-19 Gen Electric CLUTCH ELEMENTS FOR THE ROTOR DISCS OF A GAS TURBINE COMPRESSOR.
US4497612A (en) * 1983-11-25 1985-02-05 General Electric Company Steam turbine wheel antirotation means
JP3042095B2 (en) * 1991-10-16 2000-05-15 石川島播磨重工業株式会社 Gas turbine fastening device
JP4591047B2 (en) * 2004-11-12 2010-12-01 株式会社日立製作所 Turbine rotor and gas turbine
US8517687B2 (en) 2010-03-10 2013-08-27 United Technologies Corporation Gas turbine engine compressor and turbine section assembly utilizing tie shaft
IT1399904B1 (en) * 2010-04-21 2013-05-09 Nuovo Pignone Spa STACKED ROTOR WITH TIE AND BOLTED FLANGE AND METHOD
KR20150047509A (en) 2012-09-07 2015-05-04 지멘스 악티엔게젤샤프트 Method for assembling and disassembling a rotor having a number of rotor components of an axial flow turbomachine and such a rotor
ITCO20130071A1 (en) * 2013-12-18 2015-06-19 Nuovo Pignone Srl METHOD TO ASSEMBLE A SET OF IMPELLERS THROUGH TIE RODS, IMPELLER AND TURBOMACHINE

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US10718212B2 (en) 2020-07-21
US20180371916A1 (en) 2018-12-27
CN108368742B (en) 2020-08-18
DE102015225428A1 (en) 2017-07-06
WO2017102254A1 (en) 2017-06-22
EP3337958B1 (en) 2020-06-17
RU2700846C1 (en) 2019-09-23

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