EP0893576A2 - Connection of rotating elements - Google Patents

Connection of rotating elements Download PDF

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Publication number
EP0893576A2
EP0893576A2 EP98810441A EP98810441A EP0893576A2 EP 0893576 A2 EP0893576 A2 EP 0893576A2 EP 98810441 A EP98810441 A EP 98810441A EP 98810441 A EP98810441 A EP 98810441A EP 0893576 A2 EP0893576 A2 EP 0893576A2
Authority
EP
European Patent Office
Prior art keywords
centering
positive
insert ring
connection according
connection
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
EP98810441A
Other languages
German (de)
French (fr)
Other versions
EP0893576A3 (en
EP0893576B1 (en
Inventor
Harry Alkelin
Mikael Fryklund
Roland Nilsson
Per Thörnblad
Hans Dr. Wettstein
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.)
General Electric Technology GmbH
Original Assignee
ABB Alstom Power Switzerland Ltd
ABB Asea Brown Boveri Ltd
Asea Brown Boveri AB
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 ABB Alstom Power Switzerland Ltd, ABB Asea Brown Boveri Ltd, Asea Brown Boveri AB filed Critical ABB Alstom Power Switzerland Ltd
Publication of EP0893576A2 publication Critical patent/EP0893576A2/en
Publication of EP0893576A3 publication Critical patent/EP0893576A3/en
Application granted granted Critical
Publication of EP0893576B1 publication Critical patent/EP0893576B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F01D5/025—Fixing blade carrying members on shafts
    • 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
    • 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
    • F05D2230/60—Assembly methods
    • F05D2230/64—Assembly methods using positioning or alignment devices for aligning or centring, e.g. pins
    • F05D2230/642—Assembly methods using positioning or alignment devices for aligning or centring, e.g. pins using maintaining alignment while permitting differential dilatation
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T403/00—Joints and connections
    • Y10T403/21—Utilizing thermal characteristic, e.g., expansion or contraction, etc.
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T403/00—Joints and connections
    • Y10T403/21—Utilizing thermal characteristic, e.g., expansion or contraction, etc.
    • Y10T403/217—Members having different coefficients of expansion
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T403/00—Joints and connections
    • Y10T403/48—Shrunk fit

Definitions

  • the invention relates to a force-locking connection of rotating components according to the preamble of claim 1.
  • Such connections are found, for example, when assembling rotor disks of thermally highly loaded gas turbines.
  • the rotor of a turbomachine generally consists of several rotor disks, which are lined up axially and aligned concentrically. These rotor disks are clamped together by one or more tie rods and thus form a compact unit.
  • the rotors have a very high axial rigidity and centering Exhibit [concentricity], i.e. that in the different operating states no unstable conditions, vibrations or eccentric running through Changes in the center of gravity can result. This despite the inevitable different coefficients of thermal expansion of the applied different materials. About such displacements of the rotor parts against each other Hirth serrations can be avoided on the end faces of the rotor disks be arranged.
  • Other measures, such as short cones etc. could in practice offset rotor parts against each other and thus non-circular running, which can lead to the destruction of the rotor and stator prevent.
  • the invention tries to avoid these disadvantages. It is her job based on a non-positive and positive connection of rotating components create which is designed or can be retrofitted so that a operational misalignment [rotation or displacement] of components to each other is avoided.
  • the rotating components 1 and 2 as rotor disks 1 and 2nd designated.
  • the individual rotor disks are 1, 2 axially strung together and by at least one (not in the figures illustrated) tie rods clamped together concentrically.
  • the through the Tension forces caused by tie rods result in a non-positive connection of the Rotor disks.
  • these of the frictional forces resulting from the clamping forces are not sufficient to cause a misalignment to prevent the rotor disks against each other.
  • this can be the case when the rotor disks are different during rotation Have stretching behavior, partly because they are made of different materials consist.
  • This positive and non-positive connection is formed as a centering seat 3, which lies between two adjacent to each other Rotor disks are provided and biased by an insert ring 7.
  • the centering seat has the shape of a on the two adjacent rotor disks orbiting, concentric level with a positive, protruding Centering offset 4 on the rotor part 1 and a negative, drawn centering offset 5 on the rotor part 2.
  • the insert ring 7 is on the inner rotor disk relative to the centering seat 1 arranged, namely in a cavity 6. It is biased, which is the occasion assembly by thermal shrinking. On the occasion of the rotation Due to the centrifugal force due to mass, he presses the relative to the centering seat 3 internal rotor disc 1 against the external rotor disc 2 and creates a positive and non-positive connection.
  • the positive and negative Centering offsets 4, 5 of this centering seat have essentially one cylindrical contact surface 8, which is concentric with the rotor axis. Of course, there is also a slightly conical alignment of the contact surface 8 possible.
  • the centering seat prevents radial displacement and through that The contact pressure also increases the resistance to axial displacement of the rotor disks against each other. Such shifts can be caused by the thermal expansions and thermal stresses at the high operating temperatures of the gas turbines are caused.
  • the centering seat 3 is both in front of and behind the contact surface 8 provided with concave undercuts 10. Their facing the contact surface Fillets end within the contact area.
  • the internal mechanical stress curve can be changed so that the Zones of greatest mechanical stress, i.e. of the greatest voltage gradient be moved from the area of the contact surface 8.
  • both rotor parts achieved that among those mentioned certain Operating conditions in the contact area only crack-closing and thus Crack growth-preventing surface-parallel compressive stresses arise.
  • the mutual centering of the rotor disks via two conical seats via two conical seats.
  • a double conical is then useful Training of the centering seat 3 with a corresponding double conical extending contact surface 9.
  • the rotor part 2 which the has positive centering offset 4, while the rotor part 1 with the negative Centering offset 5 is provided.
  • the tolerances are chosen so that one of these conical surfaces is fully loaded during operation, while the offsets of the other conical surface are only partially in contact.
  • the insert ring 7 not all over, but only with part of its outer surface on the Rotor disc 1 is present. This can be achieved by using the ring a collar 11 is provided.
  • the federal government is in its diameter and its axial extent so that it is a small on both sides of the collar Gap 12 generated between ring 7 and rotor disk 1. The smaller one now The contact surface causes a favorable, reduced heat transfer from the rotor disc on the insert ring.
  • the rotor disk 1 - in the cavity 6 of the Insert ring 7 is housed - made of a ferritic steel with lower Expansion coefficient and the rotor disk 2 consists of an austenitic Steel with higher expansion coefficients is used as a material for the Insert ring 7 preferably also a material with higher coefficients of expansion chosen. In the case of gas turbines with high thermal loads are these material combinations for rotor disks 1 and 2 common.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
  • Pressure Welding/Diffusion-Bonding (AREA)
  • Mutual Connection Of Rods And Tubes (AREA)

Abstract

The positive engagement occurs via a staged centering seat (3) and the forced locking between the two parts takes place by means of axially pre-tensioned components. At least one of the component parts has an internal hollow space (6). In the hollow space an inlay ring (7) is arranged, which during operation exerts a radial force on the centering seat (3). The inlay ring (7) locates only with a part of its axial extent on the component part (1) working in conjunction with it. The inlay ring is pre-tensioned. The installation of the inlay ring occurs by thermal shrinkage. The centering part (4, 5) of the centering seat (3) is at least slightly cylindrical or conical.

Description

Technisches GebietTechnical field

Die Erfindung betrifft eine kraft- urrd formschlüssige Verbindung von rotierenden Bauteilen gemäss Oberbegriff des Patentanspruchs 1.
Solche Verbindungen finden sich beispielsweise beim Zusammenfügen von Rotorscheiben von thermisch hochbelasteten Gasturbinen.The invention relates to a force-locking connection of rotating components according to the preamble of claim 1.
Such connections are found, for example, when assembling rotor disks of thermally highly loaded gas turbines.

Stand der TechnikState of the art

Der Rotor einer Turbomaschine besteht im allgemeinen aus mehreren Rotorscheiben, welche axial aneinandergereiht und konzentrisch ausgerichtet sind. Diese Rotorscheiben sind durch einen oder mehrere, Zuganker miteinander verspannt und bilden so eine kompakte Einheit. Für den Betrieb einer Turbomaschine ist erforderlich, dass die Rotoren eine sehr hohe axiale Steifheit und Zentrierung [Rundlauf] aufweisen, d.h., dass sich in den verschiedenen Betriebszuständen keine instabilen Zustände, Vibrationen oder azentrischer Lauf durch Schwerpunktsverlagerungen ergeben können. Dies trotz der unvermeidlichen unterschiedlichen Temperaturausdehnungskoeffizienten der angewandten unterschiedlichen Materialien. Um solche Versetzungen der Rotorteile gegeneinander zu vermeiden kann an den Stirnflächen der Rotorscheiben eine Hirth-Verzahnung angeordnet sein. Die Herstellung derselben ist jedoch sehr teuer und erfordert hochgenaue Maschinen. Andere Massnahmen, wie kurze Zapfen etc. konnten in der Praxis eine Versetzung von Rotorteilen gegeneinander und somit unrunden Lauf, welcher zur Zerstörung von Rotor und Stator führen kann, nicht verhindern. The rotor of a turbomachine generally consists of several rotor disks, which are lined up axially and aligned concentrically. These rotor disks are clamped together by one or more tie rods and thus form a compact unit. For the operation of a turbo machine it is necessary that the rotors have a very high axial rigidity and centering Exhibit [concentricity], i.e. that in the different operating states no unstable conditions, vibrations or eccentric running through Changes in the center of gravity can result. This despite the inevitable different coefficients of thermal expansion of the applied different materials. About such displacements of the rotor parts against each other Hirth serrations can be avoided on the end faces of the rotor disks be arranged. However, the production of the same is very expensive and requires highly precise machines. Other measures, such as short cones etc. could in practice offset rotor parts against each other and thus non-circular running, which can lead to the destruction of the rotor and stator prevent.

Darstellung der ErfindungPresentation of the invention

Die Erfindung versucht, diese Nachteile zu vermeiden. Es liegt ihr die Aufgabe zugrunde, eine kraft- und formschlüssige Verbindung von rotierenden Bauteilen zu schaffen, welche so ausgebildet ist oder so nachgerüstet werden kann, dass eine betriebsbedingte Dejustierung [Verdrehung oder Verschiebung] von Bauteilen zueinander vermieden wird.The invention tries to avoid these disadvantages. It is her job based on a non-positive and positive connection of rotating components create which is designed or can be retrofitted so that a operational misalignment [rotation or displacement] of components to each other is avoided.

Bei einer Verbindung der eingangs genannten Art wird dies mit den kennzeichnenden Merkmalen des Patentanspruchs erreicht.
Weitere Merkmale und Vorteile ergeben sich aus den Unteransprüchen.In the case of a connection of the type mentioned at the outset, this is achieved with the characterizing features of the patent claim.
Further features and advantages result from the subclaims.

Kurze Beschreibung der ZeichnungBrief description of the drawing

In der Zeichnung sind zwei Ausführungsbeispiele der Erfindung anhand einer Anwendung bei Gasturbinen vereinfacht dargestellt.
Es zeigen:

Fig. 1
schematisch Ausschnitte von zwei benachbarten Rotorscheiben in einer ersten Ausführungsform;
Fig. 2
schematisch Ausschnitte von zwei benachbarten Rotorscheiben in einer zweiten Ausführungsform;
Fig. 3
den Zentriersitz aus Fig. 1 in vergrösserter Ansicht.
In the drawing, two exemplary embodiments of the invention are shown in simplified form on the basis of an application in gas turbines.
Show it:
Fig. 1
schematically sections of two adjacent rotor disks in a first embodiment;
Fig. 2
schematically sections of two adjacent rotor disks in a second embodiment;
Fig. 3
the centering seat of FIG. 1 in an enlarged view.

Es sind nur die für das Verständnis der Erfindung wesentlichen Elemente gezeigt; insbesondere ist nicht der an sich bekannte und unveränderte Teil des Rotors oder andere Rotoreinzelheiten etc. dargestellt. Funktionsgleiche Teile sind bei den verschiedenen Beispielen mit den gleichen Bezugszeichen bezeichnet. Only the elements essential for understanding the invention are shown; in particular is not the known and unchanged part of the rotor or other rotor details etc. shown. Functionally identical parts are in the different examples with the same reference numerals.

Weg zur Ausführung der ErfindungWay of carrying out the invention

Nachstehend sind die rotierenden Bauteile 1 und 2 als Rotorscheiben 1 resp. 2 bezeichnet. Bei einem Rotor für Turbomaschinen sind die einzelnen Rotorscheiben 1, 2 axial aneinandergereiht und durch wenigstens einen (in den Figuren nicht dargestellten) Zuganker konzentrisch miteinander verspannt. Die durch die Zuganker bedingten Spannkräfte ergeben eine kraftschlüssige Verbindung der Rotorscheiben. Es kann jedoch Betriebszustände geben, in welchen diese von den Spannkräften herrrührenden Reibkräfte nicht ausreichen, um eine Dejustierung der Rotorscheiben gegeneinander zu verhindern. Dies kann insbesondere der Fall sein, wenn die Rotorscheiben während der Rotation unterschiedliches Dehnungsverhalten aufweisen,unter anderem, weil sie aus verschiedenen Materialien bestehen.Below are the rotating components 1 and 2 as rotor disks 1 and 2nd designated. In the case of a rotor for turbomachinery, the individual rotor disks are 1, 2 axially strung together and by at least one (not in the figures illustrated) tie rods clamped together concentrically. The through the Tension forces caused by tie rods result in a non-positive connection of the Rotor disks. However, there may be operating conditions in which these of the frictional forces resulting from the clamping forces are not sufficient to cause a misalignment to prevent the rotor disks against each other. In particular, this can be the case when the rotor disks are different during rotation Have stretching behavior, partly because they are made of different materials consist.

Deshalb ist gemäss Fig. 1 bei einer ersten Ausführungsform eines Rotors zusätzlich zur kraftschlüssigen Verbindung der benachbarten Rotorscheiben eine radial wirksame form- und kraftschlüssige Verbindung als Sperre gegen radiale Achsversetzungen vorgesehen. Diese form- und kraftschlüssige Verbindung ist als Zentriersitz 3 ausgebildet, welcher zwischen je zwei aneinanderliegenden Rotorscheiben vorgesehen und durch einen Einlagering 7 vorgespannt ist. Dabei weist der Zentriersitz auf den beiden benachbarten Rotorscheiben die Form einer umlaufenden, konzentrischen Stufe auf mit einem positiven, hervorstehenden Zentrierversatz 4 am Rotorteil 1 und einem negativen, eingezogenen Zentrierversatz 5 am Rotorteil 2.1 is therefore in a first embodiment of a rotor in addition to the non-positive connection of the adjacent rotor disks Radially effective positive and non-positive connection as a lock against radial Axis offsets provided. This positive and non-positive connection is formed as a centering seat 3, which lies between two adjacent to each other Rotor disks are provided and biased by an insert ring 7. Here the centering seat has the shape of a on the two adjacent rotor disks orbiting, concentric level with a positive, protruding Centering offset 4 on the rotor part 1 and a negative, drawn centering offset 5 on the rotor part 2.

Der Einlagering 7 ist an der relativ zum Zentriersitz innenliegenden Rotorscheibe 1 angeordnet, und zwar in einem Hohlraum 6. Er ist vorgespannt, was anlässlich der Montage durch thermisches Schrumpfen erfolgen kann. Anlässlich der Rotation presst er infolge der massenbedigten Fliehkraft die relativ zum Zentriersitz 3 innenliegende Rotorscheibe 1 gegen die aussenliegende Rotorscheibe 2 und bewirkt damit eine form- und kraftschlüssige Verbindung. Die positiven und negativen Zentrierversatze 4, 5 dieses Zentriersitzes weisen im wesentlichen eine zylindrische Kontaktfläche 8 auf, welche konzentrisch zur Rotorache liegt. Selbstverständlich ist auch eine leicht konische Ausrichtung der Kontaktfläche 8 möglich. Der Zentriersitz verhindert eine radiale Verschiebung und durch die Anpresskraft wird zudem ein erhöhter Widerstand gegen axiale Verschiebungen der Rotorscheiben gegeneinander,erzielt. Solche Verschiebungen können durch die Wärmedehnungen und die Wärmespannungen bei den hohen Betriebstemperaturen der Gasturbinen verursacht werden.The insert ring 7 is on the inner rotor disk relative to the centering seat 1 arranged, namely in a cavity 6. It is biased, which is the occasion assembly by thermal shrinking. On the occasion of the rotation Due to the centrifugal force due to mass, he presses the relative to the centering seat 3 internal rotor disc 1 against the external rotor disc 2 and creates a positive and non-positive connection. The positive and negative Centering offsets 4, 5 of this centering seat have essentially one cylindrical contact surface 8, which is concentric with the rotor axis. Of course, there is also a slightly conical alignment of the contact surface 8 possible. The centering seat prevents radial displacement and through that The contact pressure also increases the resistance to axial displacement of the rotor disks against each other. Such shifts can be caused by the thermal expansions and thermal stresses at the high operating temperatures of the gas turbines are caused.

Der Zentriersitz 3 ist gemäss Fig. 3 sowohl vor als auch hinter der Kontaktfläche 8 mit konkaven Freistichen 10 versehen. Deren der Kontaktfläche zugewandten Ausrundungen enden innerhalb der Kontaktfläche. Mit dieser Massnahme kann der materialinterne mechanische Spannungsverlauf so geändert werden, dass die Zonen der grössten mechanischen Belastung, d.h. des grössten Spannungsgradienten aus dem Bereich der Kontaktfläche 8 verlagert werden. Gleichzeitig werden diejenigen Zonen der Rotorteile 1 oder 2, in denen unter bestimmten Betriebsbedingungen rissöffnende und damit risswachstumsfördernde oberflächenparallele Zugpannungen auftreten können, dem Berührungsbereich des jeweils andern Rotorteils 1 oder 2 .entzogen, damit dort keine Fretting-Risse entstehen können. Desweiteren wird durch die Überdeckung der Vorderkante des Freistich es des jeweils anderen Rotorteils durch eine die zu erwartende Relativbewegungen und Einbautoleranzen übersteigende Verlängerung der Kontaktflächen beider Rotorteile erreicht, dass unter den erwähnten bestimmten Betriebsbedingungen im Berührungsbereich nur noch riss-schliessende und damit risswachstums-verhindernde oberflächenparallele Druckspannungen entstehen. According to FIG. 3, the centering seat 3 is both in front of and behind the contact surface 8 provided with concave undercuts 10. Their facing the contact surface Fillets end within the contact area. With this measure the internal mechanical stress curve can be changed so that the Zones of greatest mechanical stress, i.e. of the greatest voltage gradient be moved from the area of the contact surface 8. Be at the same time those zones of the rotor parts 1 or 2 in which under certain Operating conditions crack-opening and thus crack growth-promoting surface parallel Tensile stresses can occur, the area of contact of each removed from other rotor parts 1 or 2, so that there are no fretting cracks can. Furthermore, by covering the front edge of the undercut it of the other rotor part by one of the relative movements to be expected extension of the contact surfaces exceeding installation tolerances both rotor parts achieved that among those mentioned certain Operating conditions in the contact area only crack-closing and thus Crack growth-preventing surface-parallel compressive stresses arise.

In einer weiteren Ausführungsform kann die gegenseitige Zentrierung der Rotorscheiben über zwei konische Sitze erfolgen. Sinnvoll ist dann eine doppelkonische Ausbildung des Zentriersitzes 3 mit einer entsprechenden doppelkonisch verlaufenden Kontaktfläche 9. In diesem Fall ist es der Rotorteil 2, welcher den positiven Zentrierversatz 4 aufweist, während der Rotorteil 1 mit dem negativen Zentrierversatz 5 versehen ist. Die Toleranzen werden dabei so gewählt, dass während des Betriebes jeweils eine dieser konischen Flächen voll belastet ist, während die Versatze der anderen,konischen Fläche nur teilweise in Kontakt sind.In a further embodiment, the mutual centering of the rotor disks via two conical seats. A double conical is then useful Training of the centering seat 3 with a corresponding double conical extending contact surface 9. In this case it is the rotor part 2 which the has positive centering offset 4, while the rotor part 1 with the negative Centering offset 5 is provided. The tolerances are chosen so that one of these conical surfaces is fully loaded during operation, while the offsets of the other conical surface are only partially in contact.

Bei einer bevorzugten Ausführungsform ist vorgesehen, dass der Einlagering 7 nicht vollflächig, sondern nur mit einem Teil seiner äusseren Oberfläche an der Rotorscheibe 1 anliegt. Dies kann dadurch erzielt werden, indem der Ring mit einem Bund 11 versehen wird. Der Bund ist in seinem Durchmesser und seiner axialen Erstreckung so bemessen, dass er beidseitig vom Bund einen kleinen Spalt 12 zwischen Ring 7 und Rotorscheibe 1 generiert. Die nunmehr kleinere Angriffsfläche bewirkt eine günstige, reduzierte Wärmeübertragung von der Rotorscheibe auf den Einlagering.In a preferred embodiment it is provided that the insert ring 7 not all over, but only with part of its outer surface on the Rotor disc 1 is present. This can be achieved by using the ring a collar 11 is provided. The federal government is in its diameter and its axial extent so that it is a small on both sides of the collar Gap 12 generated between ring 7 and rotor disk 1. The smaller one now The contact surface causes a favorable, reduced heat transfer from the rotor disc on the insert ring.

Wird davon ausgegangen, dass die Rotorscheibe 1 - in dessen Hohlraum 6 der Einlagering 7 untergebracht ist - aus einem ferritischem Stahl mit niedrigerem Ausdehnungskoeffizienten besteht und die Rotorscheibe 2 aus einem austenitischen Stahl mit höheren Ausdehnungskoeffizienten, so wird als Werkstoff für den Einlagering 7 vorzugsweise ebenfalls ein Werkstoff mit höheren Ausdehnungskoeffizienten gewählt. Im Falle von_thermisch hochbelasteten Gasturbinen sind diese Materialkombinationen für die Rotorscheiben 1 und 2 durchaus üblich. It is assumed that the rotor disk 1 - in the cavity 6 of the Insert ring 7 is housed - made of a ferritic steel with lower Expansion coefficient and the rotor disk 2 consists of an austenitic Steel with higher expansion coefficients is used as a material for the Insert ring 7 preferably also a material with higher coefficients of expansion chosen. In the case of gas turbines with high thermal loads are these material combinations for rotor disks 1 and 2 common.

BezugszeichenlisteReference list

11
rotierendes Bauteil, Rotorscheiberotating component, rotor disc
22nd
rotierendes Bauteil, Rotorscheiberotating component, rotor disc
33rd
ZentriersitzCentering seat
44th
positiver Zentrierversatzpositive centering offset
55
negativer Zentrierversatznegative centering offset
66
Hohlraum von 1Cavity of 1
77
EinlageringInsert ring
88th
zylindrische Kontaktflächecylindrical contact surface
99
doppelkonische Kontaktflächedouble conical contact surface
1010th
FreistichFreeway
1111
Bund auf 7Confederation on 7th
1212th
Spaltgap

Claims (9)

Kraft- und formschlüssige Verbindung von rotierenden Bauteilen (1, 2) , welche im Bereich der Verbindung während der Rotation unterschiedliches Dehnungsverhalten aufweisen, wobei der Formschluss über einen gestuften Zentriersitz (3) erfolgt und der Kraftschluss zwischen den beiden Bauteilen mittels axial vorgespannter Elemente erfolgt, und wobei zumindest eines der Bauteile einen Hohlraum (6) im Innern aufweist,
dadurch gekennzeichnet, dass im Hohlraum (6) ein Einlagering (7) angeordnet ist, welcher während des Betriebes eine radiale Kaft auf den Zentriersitz (3) ausübt.Non-positive and positive connection of rotating components (1, 2), which have different expansion behavior in the area of the connection during rotation, the positive connection taking place via a stepped centering seat (3) and the non-positive connection between the two components using axially preloaded elements, and wherein at least one of the components has a cavity (6) inside,
characterized in that an insert ring (7) is arranged in the cavity (6) and exerts a radial force on the centering seat (3) during operation. Verbindung nach Anspruch 1, dadurch gekennzeichnet, dass der Einlagering (7) nur mit einem Teil seiner axialen Erstreckung an dem mit ihm zusammenwirkenden Bauteil (1)anliegt.Connection according to claim 1, characterized in that the insert ring (7) only with part of its axial extension on that with it interacting component (1). Verbindung nach Anspruch 1, dadurch gekennzeichnet, dass der Einlagering (7) vorgespannt ist.Connection according to claim 1, characterized in that the insert ring (7) is biased. Verbindung nach Anspruch 3, dadurch gekennzeichnet, dass der Einbau des Einlageringes (7) in den Hohlraum (6) durch thermisches Schrumpfen erfolgt.Connection according to claim 3, characterized in that the installation of the insert ring (7) in the cavity (6) by thermal shrinking he follows. Verbindung nach Anspruch 1, dadurch gekennzeichnet, dass der Zentrierversatz (4, 5) des Zentriersitzes (3) zumindest annähernd zylindrisch oder leicht konisch ausgebildet ist. Connection according to claim 1, characterized in that the centering offset (4, 5) of the centering seat (3) at least approximately cylindrical or is slightly conical. Verbindung nach Anspruch 5, dadurch gekennzeichnet, dass der Zentriersitz (3) sowohl vor als auch hinter der Kontaktfläche (8) mit konkaven Freistichen (10) versehen ist, deren der Kontaktfläche zugewandte Ausrundungen innerhalb der Kontaktfläche enden.Connection according to claim 5, characterized in that the centering seat (3) both in front of and behind the contact surface (8) with concave undercuts (10) is provided, the fillets facing the contact surface end within the contact area. Verbindung nach Anspruch 5, dadurch gekennzeichnet, dass das Bauteil (2) mit dem negativen Zentrierversatz (5) und der Einlagering (7) aus einem Werkstoff bestehen, welcher einen höheren Ausdehnungskoeffizienten aufweist als der Werkstoff des Bauteiles (1) mit dem positiven Zentrierversatz (4), in dessen Hohlraum (6) der Einlagering (7) untergebracht ist.Connection according to claim 5, characterized in that the component (2) with the negative centering offset (5) and the insert ring (7) from one Material consist of a higher coefficient of expansion has as the material of the component (1) with the positive centering offset (4), in the cavity (6) of the insert ring (7) housed is. Verbindung nach Anspruch 1, dadurch gekennzeichnet, dass der Zentriersitz (3) eine doppelkonische Kontaktfläche (9) aufweist, und dass das Bauteil (2) mit dem positiven Zentrierversatz (4) und der Einlagering (3) aus einem Werkstoff bestehen, welcher einen höheren Ausdehnungskoeffizienten aufweist als der Werkstoff des Bauteiles (1) mit dem negativen Zentrierversatz (5), in dessen Hohlraum (6) der Einlagering (7) untergebracht ist.Connection according to claim 1, characterized in that the centering seat (3) has a double-conical contact surface (9), and that Component (2) with the positive centering offset (4) and the insert ring (3) consist of a material that has a higher coefficient of expansion has as the material of the component (1) with the negative Centering offset (5), in the cavity (6) of the insert ring (7) housed is. Verwendung der kraft- und formschlüssigen Verbindung nach einem der Ansprüche 1 bis 10 zum Zusammenfügen von Rotorscheiben von Turbomaschinen, insbesondere von thermisch hochbelasteten Gasturbinen, wobei einzelne, konzentrisch aneinanderangeordnete Rotorscheiben im Rotorinneren durch einen oder mehrere Bolzen miteinander verschraubt sind.Use of the non-positive and positive connection according to one of the Claims 1 to 10 for joining rotor disks of turbomachinery, especially of gas turbines subject to high thermal loads, whereby individual, concentrically arranged rotor disks in The rotor interior is screwed together by one or more bolts are.
EP98810441A 1997-07-03 1998-05-14 Connection of rotating elements Expired - Lifetime EP0893576B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19728345 1997-07-03
DE19728345A DE19728345A1 (en) 1997-07-03 1997-07-03 Non-positive and positive connection of rotating components

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EP0893576A2 true EP0893576A2 (en) 1999-01-27
EP0893576A3 EP0893576A3 (en) 1999-12-08
EP0893576B1 EP0893576B1 (en) 2003-12-03

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Also Published As

Publication number Publication date
DE19728345A1 (en) 1999-01-07
EP0893576A3 (en) 1999-12-08
US6276863B1 (en) 2001-08-21
US6126357A (en) 2000-10-03
JPH1172002A (en) 1999-03-16
DE59810313D1 (en) 2004-01-15
EP0893576B1 (en) 2003-12-03

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