EP3724456B1 - Rotor à surfaces de contact optimisées au niveau de forces centrifuges - Google Patents

Rotor à surfaces de contact optimisées au niveau de forces centrifuges Download PDF

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Publication number
EP3724456B1
EP3724456B1 EP19720467.0A EP19720467A EP3724456B1 EP 3724456 B1 EP3724456 B1 EP 3724456B1 EP 19720467 A EP19720467 A EP 19720467A EP 3724456 B1 EP3724456 B1 EP 3724456B1
Authority
EP
European Patent Office
Prior art keywords
rotor
retaining
radius
width
component
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP19720467.0A
Other languages
German (de)
English (en)
Other versions
EP3724456A1 (fr
Inventor
Harald Hoell
Kevin KAMPKA
Peter Schröder
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 Energy Global GmbH and Co KG
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 Energy Global GmbH and Co KG filed Critical Siemens Energy Global GmbH and Co KG
Publication of EP3724456A1 publication Critical patent/EP3724456A1/fr
Application granted granted Critical
Publication of EP3724456B1 publication Critical patent/EP3724456B1/fr
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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
    • F01D11/00—Preventing or minimising internal leakage of working-fluid, e.g. between stages
    • F01D11/005—Sealing means between non relatively rotating elements
    • F01D11/006—Sealing the gap between rotor blades or blades and rotor
    • 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
    • F01D5/30—Fixing blades to rotors; Blade roots ; Blade spacers
    • F01D5/3007—Fixing blades to rotors; Blade roots ; Blade spacers of axial insertion type
    • F01D5/3015—Fixing blades to rotors; Blade roots ; Blade spacers of axial insertion type with side plates
    • 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
    • F01D5/08—Heating, heat-insulating or cooling means
    • F01D5/081—Cooling fluid being directed on the side of the rotor disc or at the roots of the blades
    • 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
    • F01D5/30—Fixing blades to rotors; Blade roots ; Blade spacers
    • F01D5/3007—Fixing blades to rotors; Blade roots ; Blade spacers of axial insertion type
    • 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
    • F01D5/30—Fixing blades to rotors; Blade roots ; Blade spacers
    • F01D5/32—Locking, e.g. by final locking blades or keys
    • F01D5/326—Locking of axial insertion type blades by other means
    • 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
    • F05D2220/00—Application
    • F05D2220/30—Application in turbines
    • F05D2220/32—Application in turbines in gas turbines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2240/00—Components
    • F05D2240/20—Rotors
    • F05D2240/24—Rotors for turbines
    • 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
    • F05D2250/00—Geometry
    • F05D2250/20—Three-dimensional
    • F05D2250/27—Three-dimensional hyperboloid
    • 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
    • F05D2250/00—Geometry
    • F05D2250/70—Shape
    • F05D2250/71—Shape curved
    • 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
    • F05D2250/00—Geometry
    • F05D2250/70—Shape
    • F05D2250/71—Shape curved
    • F05D2250/711—Shape curved convex
    • 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
    • F05D2250/00—Geometry
    • F05D2250/70—Shape
    • F05D2250/71—Shape curved
    • F05D2250/712—Shape curved concave

Definitions

  • the invention relates to a rotor with a rotor disk and a plurality of rotor components attached to the circumference of the rotor disk, the rotor disk having a support surface pointing towards the rotor axis and the respective rotor component having a holding surface complementary to the support surface.
  • the EP 1944471 B1 a rotor with a rotor disk on which a plurality of sealing elements are arranged on one end.
  • the rotor disk has a plurality of blade retaining grooves distributed around the circumference, which are intended for receiving rotor blades.
  • To cover the blade retaining grooves on one end face of the rotor disk there are sealing elements distributed around the circumference. Under the action of centrifugal force during rotation of the rotor, the sealing elements are supported directly on the rotor disk at the end of the sealing elements pointing towards the rotor axis.
  • the rotor disk has a circumferential projection which extends axially in front of the end face and on which a fastening shoulder which extends on the sealing element towards the rotor disk is supported.
  • a supporting surface pointing towards the rotor axis is almost necessarily formed on the projection of the rotor disk by a surface of revolution rotating around the rotor axis.
  • the holding surface of the fastening shoulder that rests against the support surface is basically designed to be complementary to the support surface with a matching radius.
  • the object of the present invention is therefore to realize a fastening of rotor components to a rotor disk in the event of large centrifugal forces occurring, with the aim being to achieve as uniform a pressure as possible in the support of the rotor component.
  • the generic rotor is used in particular for use in a gas turbine. However, the embodiment can also be applied to other types of rotors, for example steam turbines come into use. At least the rotor has at least one rotor disk on which a plurality of rotor components are arranged distributed around the circumference. In this case, the rotor defines a rotor axis and thus an axial direction.
  • the rotor disk has a peripheral, axially extending fastening shoulder.
  • the circumferential fastening shoulder forms a support surface on the side facing the rotor axis.
  • the support surface is a surface of revolution running around the rotor axis. Viewed in the axial direction, the support surface extends over that length over which the rotor component bears against the fastening shoulder.
  • the support surface has a specific support radius as a distance from the rotor axis at a respective axial position.
  • a mean support radius of the support surface can be defined as that radius which is given in the center of the support surface in the axial direction.
  • the rotor components each have a retaining shoulder which extends in the circumferential direction and axially to the rotor disk and which is arranged on the side facing the rotor axis below the fastening shoulder.
  • the holding shoulder has a holding surface that is complementary to the support surface.
  • the holding surface is also a section of a surface of revolution. Accordingly, the holding surface is defined as that surface of the holding shoulder which comes into contact with the fastening shoulder of the rotor disk.
  • the holding surface as a surface of revolution has a holding radius analogously at a respective axial position. Furthermore, an average holding radius of the holding surface can be determined, which is given in the center of the holding surface in the axial direction.
  • the centrifugal forces occurring in the rotor component can at least partially be transferred via the retaining shoulder in the system of the holding surface on the support surface are transferred to the attachment paragraph.
  • the holding radius and the supporting surface are usually formed by a matching surface of revolution and insofar as the holding radius and the supporting radius match
  • the holding radius is now smaller than the supporting radius.
  • a holding radius with at least 0.99 times the support radius and at the same time with a maximum of 0.9995 times the support radius is particularly advantageous compared to the known designs from the prior art. This means that a deviation of the smaller support radius from the larger support radius by a maximum of 1% is permissible, with the difference being at least 0.5 ⁇ .
  • the rotor component has an opening that extends axially through the rotor component.
  • the opening is to be arranged radially outside of the holding shoulder, ie also of the holding surface.
  • the opening extends in the circumferential direction over approximately half the width of the rotor component. This is considered to be the case when the width of the opening is at least 0.25 times the width of the rotor component in the circumferential direction, but the width of the opening is not selected to be greater than 0.75 times the width of the rotor component in the circumferential direction. The width at the same radial position is considered here.
  • the inventive design of the rotor component with a holding radius, which is selected slightly smaller than the support radius, with the introduction of the opening leads in combination to the particular advantage of the high load capacity of the connection between the holding shoulder and the fastening shoulder according to the invention.
  • the breakthrough allows for greater deformation of the rotor component and, on the other hand, the deformation is compensated for by the different radii of the holding surface and the supporting surface.
  • a more uniform contact of the support surface with the holding surface can be achieved with uniform compressive stresses compared to trying to determine a suitable geometry without breaking through.
  • the design of the holding shoulder of the rotor component is particularly advantageous if the holding radius is chosen to be at least 0.999 times the support radius. This leads to an advantageous design, in particular when used in a rotor of a gas turbine.
  • the width of the opening corresponding to approximately half the width of the rotor component is achieved particularly advantageously if the opening extends over at least 0.4 times the width of the rotor component in the circumferential direction. In this case, it is particularly advantageous if the opening extends over a maximum of 0.6 times the width of the rotor component.
  • An advantageous stress distribution is achieved when the breakdown increases with increasing radius.
  • the two sides lying opposite in the circumferential direction enclose an angle of approximately 45°.
  • the width should not increase too abruptly.
  • the support surface and the complementary holding surface can be designed differently when viewed in longitudinal section. In the simplest case, these are cylindrical surfaces. This simplifies production and ensures a defined position of the components relative to one another.
  • the disadvantage of this design is the distribution of stress in the fastening shoulder and the holding shoulder.
  • the supporting surface and the complementary holding surface can be crowned or curved (along the axial direction). In this case, however, the disadvantage is the production of the surfaces while maintaining the smallest tolerances. It has therefore turned out to be particularly advantageous if the supporting surface and the complementary holding surface are designed as a section of a conical surface, i.e. conically.
  • the opening angle of the defining cone is between 30° and 90°.
  • the angle between the support surface or the holding surface and the rotor axis is advantageously between 15° and 45°.
  • the design of the fastening shoulder with the support surface and the holding shoulder with is particularly advantageous of the holding surface if an opening angle of at least 45° is selected. Furthermore, it is particularly advantageous if the opening angle is a maximum of 75°.
  • the distance from the holding shoulder to the opening is not too large in relation to the width of the remaining web next to the opening. Based on a web width as the distance from the opening to the nearest side edge in the circumferential direction and a reference point in the center of the holding surface, it is therefore advantageous if the distance from the holding surface to the opening in the radial direction is not greater than the web width. It is particularly advantageous if the radial distance is between 0.25 and 0.75 times the web width.
  • the inventive design of the rotor component with a holding surface, which has a slightly smaller radius than the support surface, in combination with an opening can be used particularly advantageously when the rotor component has a substantially flat shape extending in the circumferential direction and radially.
  • the tensile stresses are at least twice as great as the bending stresses.
  • the retaining shoulder extends essentially in the axial direction.
  • the rotor component can be supported on the rotor opposite the holding shoulder with an inner edge section pointing towards the rotor axis.
  • the rotor disk optionally has a peripheral annular projection spaced apart from an end face of the rotor disk or from the fastening shoulder.
  • the corresponding annular projection is arranged on a second rotor disk adjacent to the rotor disk. At least the corresponding annular projection on the rotor disk or the second rotor disk forms a contact surface pointing towards the fastening shoulder, on which the inner edge section of the rotor components comes to rest and can be supported in the axial direction.
  • the embodiment according to the invention is suitable in a particularly advantageous manner in the case of a rotor disk on which a plurality of rotor blades arranged distributed over the circumference can be attached.
  • the rotor disk has a plurality of blade retaining grooves distributed over the circumference and axially penetrating the rotor disk.
  • the blade retaining grooves are covered at least in sections on an end face of the rotor disk by the rotor components which are distributed around the circumference.
  • the rotor disk 01 can be seen with a blade retaining groove 02 located on the radially outer circumference. This 02 is intended for receiving rotor blades (not shown here).
  • the rotor disk 01 has a fastening shoulder 04, which 04 extends in the circumferential direction and in the axial direction, and on the side facing the rotor axis, a support surface 05 having.
  • the supporting surface 05 is sketched slightly inclined and slightly crowned, purely as an example.
  • a conical shape of the support surface can be chosen as a simple suitable shape.
  • the rotor disk 01 has a circumferential, radially outwardly extending annular projection 07 at a distance from the fastening shoulder 04 .
  • a circumferential groove is formed below the fastening shoulder 04 and behind the annular projection 07 in this exemplary embodiment.
  • the rotor component 11 which is attached to the rotor disk 01 11 , can also be seen.
  • the rotor component 11 has a holding shoulder 14 which also extends in the circumferential direction and axially.
  • the holding shoulder 14 forms a holding surface 15 which is arranged on the side pointing radially outwards.
  • the holding surface 15 and the support surface 05 are listed as complementary to one another.
  • the retaining shoulder 14 is arranged near the end of the rotor component 11 facing the rotor axis, with an inner edge portion 17 being located at the end on the side facing the rotor axis. This 17 lies axially against the annular projection 07 of the rotor disk 01.
  • the geometries of the support surface 05 and the holding surface 15 are of essential importance, with these abutting one another over a bearing width 10 when viewed in the axial direction. That is to say, those surfaces of the fastening shoulder 04 or the holding shoulder 14 which abut one another over the bearing width 10 are regarded as the supporting surface 05 and the holding surface 15 .
  • the support surface 05 has a support radius 06 as a surface of rotation about the rotor axis.
  • the holding surface 15 of the rotor component 11 also designed as a section of a surface of revolution correspondingly has a holding radius 16 .
  • the support radius 06 and the holding radius 16 are determined at the same axial position. It is now of essential importance that the holding radius 16 is smaller than the support radius 06 and thus the axis of rotation of the holding surface 15 is positioned at a distance from the rotor axis.
  • the rotor component 11 has an opening 12 that penetrates the rotor component 11 in the axial direction, which is essential for the solution.
  • This 12 is arranged radially outside of the holding shoulder 14 .
  • the opening 12 is arranged at a specific mean distance 23 in the radial direction from the center of the holding surface 15 .
  • the 2 again the arrangement with the rotor disk 01 and the rotor component 11 in a section transverse to the rotor axis through the fastening shoulder 04 and the holding shoulder 14, viewed in the direction of the rotor disk 01 pointing away.
  • the rotor component 11 can be seen here with the inner edge section 17, which 17 rests axially on the annular projection 07.
  • This shape with the holding surface 15 not fully in contact with the support surface 05 initially viewed in the circumferential direction, leads to a uniform contact tension between the two surfaces 05, 15 in the event of high centrifugal forces due to a corresponding rotation of the rotor.
  • the opening 12 is located radially outside of the holding shoulder 14 , with two webs correspondingly remaining on the rotor component on both sides of the opening 12 .
  • the opening 12 in turn contributes to the uniform contact tension between the holding surface 15 and the support surface 05 .
  • the opening 12 has a width 22 in the circumferential direction, which corresponds approximately to half the width 21 of the rotor component 11 . Accordingly, webs with a web width of 24 remain on both sides.
  • the radial distance 23 from the center of the holding surface 15 to the opening 12 is not greater than the web width 24.
  • the opening 12 widens as the radius increases.
  • the angle between the side flank of the opening in the circumferential direction and the radial central axis is approximately 20°.
  • generous roundings are provided at the upper end of the side flank and at the lower end of the side flank.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
  • Centrifugal Separators (AREA)

Claims (16)

  1. Rotor comprenant un axe de rotor et un disque (01) de rotor, lequel (01) a un ressaut (04) de fixation faisant le tour et ayant une surface (05) d'appui, tournant autour d'un axe du rotor et tournée vers l'axe du rotor et comprenant plusieurs pièces (11) rotoriques réparties sur le pourtour, lesquelles (11) ont chacune un ressaut (14) de retenue ayant une surface (15) de retenue complémentaire de la surface (05) d'appui et formant une partie d'une surface de révolution, dans lequel, dans chaque section transversale, perpendiculairement à l'axe du rotor, la surface (05) d'appui a un rayon (06) d'appui et la surface (15) de retenue, un rayon (16) de retenue,
    caractérisé
    en ce que le rayon (16) de retenue représente au moins 0,99 fois et au plus 0,9995 fois le rayon (06) d'appui,
    dans lequel la pièce (11) rotorique a, radialement à l'extérieur de la surface (15) de retenue, une ouverture (12), laquelle (12) a une largeur (22) représentant au moins 0,25 fois et au plus 0,75 fois la largeur (21) de la pièce (11) rotorique dans la direction du pourtour.
  2. Rotor suivant la revendication 1,
    caractérisé
    en ce que le rayon (16) de retenue représente au moins 0,999 fois le rayon (06) d'appui.
  3. Rotor suivant la revendication 1 ou 2,
    caractérisé
    en ce que la largeur (22) de l'ouverture (12) représente au moins 0,4 fois et/ou au plus 0,6 fois la largeur (21) de la pièce (11) rotorique dans la direction du pourtour.
  4. Rotor suivant l'une des revendications 1 à 3,
    caractérisé
    en ce que l'ouverture (12) s'élargit en ayant un rayon croissant, la différence de la largeur, dans la direction du pourtour, représentant entre 0,75 fois et 1,25 fois la différence dans la direction radiale.
  5. Rotor suivant l'une des revendications 1 à 4,
    caractérisé
    en ce que la surface (05) d'appui et la surface (06) de retenue sont coniques, l'angle d'ouverture étant compris entre 30° et 90°.
  6. Rotor suivant l'une des revendications 1 à 5,
    caractérisé
    en ce que la distance (23) dans la direction radiale du milieu de la surface (15) de retenue à l'ouverture (12) correspond au plus à la distance (24) de l'ouverture (12) au bord dans la direction du pourtour de la pièce (11) rotorique.
  7. Rotor suivant l'une des revendications 1 à 6,
    caractérisé
    en ce que la pièce (11) rotorique a une forme s'étendant sensiblement dans la direction du pourtour et radialement, le ressaut (14) de retenue s'étendant dans la direction axiale.
  8. Rotor suivant l'une des revendications 1 à 7,
    caractérisé
    en ce que le disque (01) du rotor et/ou un deuxième disque du rotor voisin du disque (01) du rotor a une saillie annulaire faisant le tour à distance du côté frontal du disque (01) du rotor, et en ce que la pièce (11) rotorique a, du côté tourné vers l'axe du rotor, une partie (17) intérieure de bord, la partie (17) intérieure de bord s'appuyant axialement sur la saillie (07) annulaire en faisant face au ressaut (14) de retenue.
  9. Rotor suivant l'une des revendications 1 à 8,
    caractérisé
    en ce que le disque (01) du rotor a plusieurs rainures (02) de retenue d'aube traversantes axialement et réparties sur le pourtour, et les pièces (11) rotoriques recouvrent, au moins par endroits, les rainures (02) de retenue d'aube sur un côté frontal du disque du rotor.
  10. Pièce (11) rotorique à utiliser dans un rotor suivant l'une des revendications précédentes, comportant un ressaut (14) de retenue ayant une surface (15) de retenue formant une partie, complémentaire de la surface (05) d'appui du disque (01) de rotor, d'une surface de révolution, dans laquelle, dans chaque section transversale, perpendiculairement à l'axe du rotor, la surface (15) de retenue a un rayon (16) de retenue,
    caractérisée par,
    disposée radialement à l'extérieur de la surface (15) de retenue, une ouverture (12), laquelle (12) a une largeur (22) représentant au moins 0,25 fois et au plus 0,75 fois la largeur (21) de la pièce (11) rotorique dans la direction du pourtour,
    dans laquelle le rayon (16) de retenue représente au moins 0,99 fois et au plus 0,9995 fois le rayon (06) d'appui conforme aux prescriptions.
  11. Pièce (11) rotorique suivant la revendication 10,
    caractérisée
    en ce que le rayon (16) de retenue représente au moins 0,999 fois le rayon (06) d'appui.
  12. Pièce (11) rotorique suivant la revendication 10 ou 11,
    caractérisée
    en ce que la largeur (22) de l'ouverture (12) représente au moins 0,4 fois et/ou au plus 0,6 fois la largeur (21) dans la direction du pourtour.
  13. Pièce (11) rotorique suivant l'une des revendications 10 à 12,
    caractérisée
    en ce que l'ouverture (12) s'élargit en ayant un rayon croissant, la différence de la largeur, dans la direction du pourtour, représentant entre 0,75 fois et 1,25 fois la différence dans la direction radiale.
  14. Pièce (11) rotorique suivant l'une des revendications 10 à 13,
    caractérisée
    en ce que la surface (06) de retenue est conique, l'angle d'ouverture étant compris entre 30° et 90°.
  15. Pièce (11) rotorique suivant l'une des revendications 10 à 14,
    caractérisée
    en ce que la distance (23) dans la direction radiale du milieu de la surface (15) de retenue à l'ouverture (12) correspond au plus à la distance (24) de l'ouverture (12) au bord dans la direction du pourtour.
  16. Pièce (11) rotorique suivant l'une des revendications 10 à 15,
    caractérisée
    en ce que la pièce (11) rotorique a une forme s'étendant sensiblement dans la direction du pourtour et radialement, le ressaut (14) de retenue s'étendant dans la direction axiale.
EP19720467.0A 2018-05-03 2019-04-16 Rotor à surfaces de contact optimisées au niveau de forces centrifuges Active EP3724456B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP18170613.6A EP3564489A1 (fr) 2018-05-03 2018-05-03 Rotor à surfaces de contact optimisées au niveau de forces centrifuges
PCT/EP2019/059727 WO2019211091A1 (fr) 2018-05-03 2019-04-16 Rotor comportant des surfaces de contact optimisées pour la force centrifuge

Publications (2)

Publication Number Publication Date
EP3724456A1 EP3724456A1 (fr) 2020-10-21
EP3724456B1 true EP3724456B1 (fr) 2023-03-01

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EP18170613.6A Withdrawn EP3564489A1 (fr) 2018-05-03 2018-05-03 Rotor à surfaces de contact optimisées au niveau de forces centrifuges
EP19720467.0A Active EP3724456B1 (fr) 2018-05-03 2019-04-16 Rotor à surfaces de contact optimisées au niveau de forces centrifuges

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EP18170613.6A Withdrawn EP3564489A1 (fr) 2018-05-03 2018-05-03 Rotor à surfaces de contact optimisées au niveau de forces centrifuges

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US (1) US11319824B2 (fr)
EP (2) EP3564489A1 (fr)
JP (1) JP6995217B2 (fr)
KR (1) KR102498006B1 (fr)
CN (1) CN112119205B (fr)
WO (1) WO2019211091A1 (fr)

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US11415016B2 (en) * 2019-11-11 2022-08-16 Rolls-Royce Plc Turbine section assembly with ceramic matrix composite components and interstage sealing features

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WO2019211091A1 (fr) 2019-11-07
US11319824B2 (en) 2022-05-03
KR20210002683A (ko) 2021-01-08
JP2021517616A (ja) 2021-07-26
JP6995217B2 (ja) 2022-01-14
KR102498006B1 (ko) 2023-02-10
CN112119205A (zh) 2020-12-22
EP3564489A1 (fr) 2019-11-06
EP3724456A1 (fr) 2020-10-21
US20210095568A1 (en) 2021-04-01
CN112119205B (zh) 2022-11-11

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