EP2157283A1 - Fixation d'aube avec élément d'amortissement pour une turbomachine - Google Patents

Fixation d'aube avec élément d'amortissement pour une turbomachine Download PDF

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Publication number
EP2157283A1
EP2157283A1 EP08014644A EP08014644A EP2157283A1 EP 2157283 A1 EP2157283 A1 EP 2157283A1 EP 08014644 A EP08014644 A EP 08014644A EP 08014644 A EP08014644 A EP 08014644A EP 2157283 A1 EP2157283 A1 EP 2157283A1
Authority
EP
European Patent Office
Prior art keywords
blade
friction means
mounting according
recess
foot mounting
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.)
Withdrawn
Application number
EP08014644A
Other languages
German (de)
English (en)
Inventor
Christoph Dr. Richter
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Siemens AG
Original Assignee
Siemens AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Siemens AG filed Critical Siemens AG
Priority to EP08014644A priority Critical patent/EP2157283A1/fr
Priority to PCT/EP2009/060423 priority patent/WO2010020568A1/fr
Publication of EP2157283A1 publication Critical patent/EP2157283A1/fr
Withdrawn legal-status Critical Current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
    • F01D5/12—Blades
    • F01D5/26—Antivibration means not restricted to blade form or construction or to blade-to-blade connections or to the use of particular materials
    • 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
    • F05D2240/80—Platforms for stationary or moving blades
    • 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 blade attachment comprising a rotor provided with Schaufelfußnuten and at least one blade comprising a blade root and a Schaufelfußplatte, wherein the blade is designed for installation in the Schaufelfußnut.
  • a steam turbine as an exemplary embodiment of a turbomachine essentially comprises a rotor which is rotatably mounted and a housing arranged around the rotor.
  • the turbine blades are placed in so-called grooves in the rotor.
  • grooves there are various Nutenformen known, such as the so-called T-shape or the Christmas tree groove.
  • the blade roots are inserted into these grooves and, in use, are urged radially outwards by the centrifugal force, creating contact surfaces between the grooves and the blade roots.
  • the turbine blades may oscillate during operation. On the one hand, such vibrations lead to flow losses and, on the other hand, also lead to material fatigue. It would be desirable to have an improved turbine blade attachment where blade vibration is minimized.
  • the invention begins, whose task is to provide a blade attachment, are reduced in the vibrations.
  • a blade attachment comprising a rotor provided with Schaufelfußnuten and at least one blade comprising a blade root and a Schaufelfußplatte, wherein the blade is designed for installation in the Schaufelfußnut, wherein the rotor has a recess, in which a friction means is arranged is pressed by a centrifugal force occurring during operation against the blade root plate.
  • the friction means is arranged in the recess before the blade is installed in the blade root groove.
  • the recess is in this case a little larger than the size of the friction means, whereby it is possible to insert the blade root in the Schaufelfußnut.
  • the recess is designed as a bore.
  • a bore is a comparatively quick and inexpensive way to make a recess.
  • the friction means is formed as a pin, wherein the pin has a slightly smaller diameter than the bore.
  • the friction means can be moved freely in the bore.
  • there is then the possibility that the friction means is pressed against the blade base plate as a result of a centrifugal force acting in operation in the bore.
  • the recess is made oblique with respect to the radial direction. Due to the oblique arrangement of the friction means in the obliquely arranged recess prevail frictional forces with which the vibration of a blade can be effectively damped.
  • the friction means clamps in the recess against the blade root plate.
  • the system of friction means, recess and blade root plate forms a rigid system. Disturbing vibrations are reduced by the rigid system.
  • the recess is designed at an angle of 45 °.
  • the recess may advantageously also be between 35 ° and 55 °, between 30 ° and 60 °, between 40 ° and 50 ° and between 25 ° and 75 °.
  • the choice of angle depends on the coefficients of friction of the material of the rotor and the material of the friction means and the material of the blade root.
  • the recess is arranged on a Schaufelfußplattenende. If vibrations occur during operation, these vibrations are strongest at the outer end of the footplate. Therefore, it is advantageous to arrange the friction means just at this outer point. Vibrations are thereby further reduced.
  • the friction means has a lower coefficient of friction than the material of the rotor and the blade root.
  • a bronze-like alloy has proven to be a material for the friction agent.
  • the pin has a round-shaped end, which has contact with the blade root plate during operation.
  • the rounded end has a suitable radius, which depends on the angle of the recess to the radial direction, on the thickness of the friction means. Due to the round tip of the friction means ensures that at a vibration of the blade root plate always a sufficiently large contact surface between the friction means and the blade root plate prevails.
  • the blade root plate end has a bevel on which the friction means rests during operation.
  • the friction means is here seen in cross-section substantially triangular.
  • FIG. 1 shows a section of a blade root 1, which is arranged in a arranged in the rotor 3 Schaufelfußnut 2.
  • the rotor 3 rotates in operation about a rotation axis, not shown.
  • Presentation shows the situation during operation.
  • a centrifugal force in the radial direction 4 acts on the blade root 1.
  • a recess 6 is arranged in the rotor 3.
  • a friction means 7 is arranged movably.
  • the friction means 7 also experiences a centrifugal force in operation in the radial direction 4 and exerts a force on a Schaufelfußplattenende 8.
  • a movement of the Schaufelfußplattenendes 8 in the radial direction 4 is thereby effectively avoided, whereby blade vibrations are prevented.
  • FIG. 2 shows a plan view of the blade root 1 from above.
  • the blade root 1 is executed here curved.
  • the axis of rotation 9 is symbolized by the dotted line.
  • On a first side of the blade root 1 a plurality of recesses 6 are arranged with friction means 7.
  • the recesses 6 can in this case be arranged at equidistant intervals on the first side 10.
  • On the second side 11 a plurality of recesses 6 are arranged with friction means 7 as well.
  • the recesses 6 can be arranged at equidistant intervals on the second side 11. Preferably, at the ends of the second side 11, the number of recesses 6 heaped.
  • FIG. 3 is an enlarged view of the friction means 7 with the recess 6 can be seen.
  • the recess 6 is in this case designed as a bore, wherein the diameter of the bore is larger than the diameter of the running as a pin friction means 7.
  • the recess 6 and the friction means 7 are inclined at an angle ⁇ relative to the axis of rotation 9.
  • the angle ⁇ is preferably 45 °.
  • the angle ⁇ is between 35 ° and 55 °.
  • the angle is between 30 ° and 60 °.
  • the angle is between 25 ° and 65 °.
  • FIG. 4 is a representation of the blade vibrations of the blade symbolized.
  • the blade root 1 has a contact with the Schaufelfußnut 2 at different support edges 5.
  • the friction means 7 exerts a force on the Schaufelfußplattenende 8 under centrifugal force.
  • a friction occurs between the friction means 7 and the blade root plate end 8, whereby a vibration is reduced.
  • a friction between the friction means 7 and the rotor 3 is present at the second friction point 15. This friction counteracts the centrifugal force.
  • the friction means 7 is shown symbolized.
  • the friction means 7 is cylindrical in shape with a radius R. At the contact point 16 between the friction means 7 and the blade root 1, the friction means 7 is formed pointed under a radius R '.
  • FIG. 7 An alternative embodiment of the friction means 7 can be seen.
  • the friction means 7 is in this case elongated and is seen in cross-section triangular.
  • the Schaufelfußplattenende 8 is hereby bevelled.
  • the recess 6 has a total of three straight walls 17. Under centrifugal force is the friction agent 7 moves in the radial direction 4, whereby the friction means 7 rests against the wall 17 and the chamfered surface 18.
  • FIG. 8 is a plan view of a curved blade root 1 with a total of four according to FIG. 7 trained friction means 7 to see.
  • the friction means 7 are elongate and arranged at the ends of the blade root 1.
  • the friction means 7 should have a low coefficient of friction, z.
  • bronze-type alloys can be used. These alloys have a reasonably high density, which is comparable to steel, which makes it possible to generate sufficient contact forces.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
EP08014644A 2008-08-18 2008-08-18 Fixation d'aube avec élément d'amortissement pour une turbomachine Withdrawn EP2157283A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP08014644A EP2157283A1 (fr) 2008-08-18 2008-08-18 Fixation d'aube avec élément d'amortissement pour une turbomachine
PCT/EP2009/060423 WO2010020568A1 (fr) 2008-08-18 2009-08-12 Fixation d'aube avec élément d'amortissement pour une turbomachine

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP08014644A EP2157283A1 (fr) 2008-08-18 2008-08-18 Fixation d'aube avec élément d'amortissement pour une turbomachine

Publications (1)

Publication Number Publication Date
EP2157283A1 true EP2157283A1 (fr) 2010-02-24

Family

ID=41226936

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08014644A Withdrawn EP2157283A1 (fr) 2008-08-18 2008-08-18 Fixation d'aube avec élément d'amortissement pour une turbomachine

Country Status (2)

Country Link
EP (1) EP2157283A1 (fr)
WO (1) WO2010020568A1 (fr)

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2997274A (en) * 1953-04-13 1961-08-22 Morgan P Hanson Turbo-machine blade vibration damper
US3037741A (en) * 1958-12-29 1962-06-05 Gen Electric Damping turbine buckets
US4936749A (en) * 1988-12-21 1990-06-26 General Electric Company Blade-to-blade vibration damper
EP0437977A1 (fr) * 1990-01-18 1991-07-24 United Technologies Corporation Configuration de jante de disque de turbine
EP0509838A1 (fr) * 1991-04-19 1992-10-21 General Electric Company Amortissement des vibrations des aubes de turbines à gaz
US5226784A (en) * 1991-02-11 1993-07-13 General Electric Company Blade damper
US5242270A (en) * 1992-01-31 1993-09-07 Westinghouse Electric Corp. Platform motion restraints for freestanding turbine blades
WO2000070193A1 (fr) * 1999-05-14 2000-11-23 Siemens Aktiengesellschaft Turbomachine comportant un systeme d'etancheite pour un rotor
EP1124038A1 (fr) * 2000-02-09 2001-08-16 Siemens Aktiengesellschaft Aubage de turbine
US20070183894A1 (en) * 2006-02-08 2007-08-09 Snecma Turbomachine rotor wheel

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2997274A (en) * 1953-04-13 1961-08-22 Morgan P Hanson Turbo-machine blade vibration damper
US3037741A (en) * 1958-12-29 1962-06-05 Gen Electric Damping turbine buckets
US4936749A (en) * 1988-12-21 1990-06-26 General Electric Company Blade-to-blade vibration damper
EP0437977A1 (fr) * 1990-01-18 1991-07-24 United Technologies Corporation Configuration de jante de disque de turbine
US5226784A (en) * 1991-02-11 1993-07-13 General Electric Company Blade damper
EP0509838A1 (fr) * 1991-04-19 1992-10-21 General Electric Company Amortissement des vibrations des aubes de turbines à gaz
US5242270A (en) * 1992-01-31 1993-09-07 Westinghouse Electric Corp. Platform motion restraints for freestanding turbine blades
WO2000070193A1 (fr) * 1999-05-14 2000-11-23 Siemens Aktiengesellschaft Turbomachine comportant un systeme d'etancheite pour un rotor
EP1124038A1 (fr) * 2000-02-09 2001-08-16 Siemens Aktiengesellschaft Aubage de turbine
US20070183894A1 (en) * 2006-02-08 2007-08-09 Snecma Turbomachine rotor wheel

Also Published As

Publication number Publication date
WO2010020568A1 (fr) 2010-02-25

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