EP1764477B1 - Turbineschaufel mit kannelierter Spitze - Google Patents

Turbineschaufel mit kannelierter Spitze Download PDF

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Publication number
EP1764477B1
EP1764477B1 EP20050255625 EP05255625A EP1764477B1 EP 1764477 B1 EP1764477 B1 EP 1764477B1 EP 20050255625 EP20050255625 EP 20050255625 EP 05255625 A EP05255625 A EP 05255625A EP 1764477 B1 EP1764477 B1 EP 1764477B1
Authority
EP
European Patent Office
Prior art keywords
tip
flute
rib
airfoil according
airfoil
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.)
Expired - Fee Related
Application number
EP20050255625
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English (en)
French (fr)
Other versions
EP1764477A1 (de
Inventor
Ching-Pang Lee
Nicholas Charles Palmer
James Robert Bailey
Wenfeng Lu
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 Co
Original Assignee
General Electric Co
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 General Electric Co filed Critical General Electric Co
Priority to EP20050255625 priority Critical patent/EP1764477B1/de
Priority to DE200560007900 priority patent/DE602005007900D1/de
Publication of EP1764477A1 publication Critical patent/EP1764477A1/de
Application granted granted Critical
Publication of EP1764477B1 publication Critical patent/EP1764477B1/de
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
    • F01D5/12—Blades
    • F01D5/14—Form or construction
    • F01D5/20—Specially-shaped blade tips to seal space between tips and stator

Definitions

  • the present invention relates generally to gas turbine engines, and, more specifically, to turbine blade cooling.
  • air is pressurized in a compressor and mixed with fuel in a combustor for generating hot combustion gases.
  • Energy is extracted from the gases in several turbine stages which power the compressor and produce useful work such as powering an upstream fan in a turbofan aircraft engine application.
  • Each turbine stage includes a stationary turbine nozzle which directs the combustion gases through a corresponding row of turbine rotor blades extending radially outwardly from a supporting rotor disk.
  • the stator vanes and rotor blades include hollow airfoils with internal cooling circuits therein which use air bled from the compressor for cooling thereof during operation.
  • Each stage of vanes and blades is configured differently for maximizing energy extraction from the combustion gases as they flow downstream through the turbine during operation.
  • Each vane and blade also includes different cooling configurations specifically tailored to different heat loads from the combustion gases as they flow downstream over the pressure and suction sides thereof.
  • the typical turbine blade includes an airfoil having a radially outer tip spaced closely adjacent to a surrounding turbine shroud forming a small clearance or gap therebetween.
  • the combustion gases flow over the pressure and suction sides of the turbine blade, and a small portion of the combustion gases leaks past the blade tip through the small tip clearance.
  • the blade tip is particularly difficult to cool since it is exposed to the hot combustion gases on both the pressure and suction sides of the airfoil between the leading and trailing edges, as well as over the tip itself in the tip-shroud gap.
  • the tips typically include short height squealer ribs extending radially outwardly from a tip floor which defines an outwardly open tip cavity.
  • the tip floor defines the outer boundary for the internal cooling circuits of the airfoil, and positions the squealer ribs externally thereof which further increases the difficulty of tip cooling during operation.
  • turbine blade tips are subject to oxidation over extended use in the engine, and may require corresponding repair during maintenance outages of the engine. Oxidation damage to the blade tip commonly limits the useful life of the blade during operation, as well as decreases turbine efficiency as the blade tips oxidize and wear during operation and correspondingly increase the blade tip clearance.
  • the later patent discloses an inclined pressure side squealer rib at the tip shelf for protecting the cooling air film created thereat for enhancing tip performance.
  • the squealer ribs are subject to abrasion wear which affects both efficiency of blade tip performance, and effectiveness of the tip shelf cooling.
  • a turbine blade includes an airfoil having pressure and suction sidewalls extending between leading and trailing edges and root and tip.
  • the tip includes squealer ribs extending from a tip floor forming an open tip cavity.
  • the rib along the pressure sidewall has a squared external corner, and a flute extends along the base of the rib at the tip floor.
  • FIG. 1 Illustrated in Figure 1 is a turbine rotor blade 10 for a gas turbine engine.
  • the blade includes a hollow airfoil 12 integrally joined in turn to a radially inner platform 14 and dovetail 16.
  • the exemplary dovetail is an axial entry dovetail with multiple tangs or lobes supported in a complementary dovetail slot in the perimeter of a rotor disk (not shown).
  • a full row of the turbine blades 10 extends radially outwardly from the supporting rotor disk and receives combustion gases 18 from an upstream combustor (not shown) for extracting energy therefrom to power the engine compressor (not shown) during operation.
  • the hollow airfoil includes an internal cooling circuit 20 therein which receives through an inlet channel in the dovetail cooling air 22 bled from the compressor during operation.
  • the cooling circuit may have any conventional configuration, such as the three-pass serpentine cooling circuit illustrated which discharges the spent cooling air through various rows of film cooling holes through the airfoil between its leading and trailing edges in any conventional manner.
  • the airfoil 12 includes a generally concave pressure sidewall 24, and a laterally or circumferentially opposite, generally convex suction sidewall 26 extending chordally or axially in chord between opposite leading and trailing edges 28,30, and in longitudinal or radial span from a root 32 at the platform 14 to a radially outer tip 34 at the distal end of the airfoil.
  • the airfoil tip 34 includes a first squealer rib 36 along the pressure sidewall, and an opposite second squealer rib 38 along the suction sidewall which are integrally joined together at the leading and trailing edges 28,30 as additionally illustrated in Figure 1 .
  • the two ribs 36,38 extend radially outwardly from a common tip floor 40 which bridges the pressure and suction sidewalls of the airfoil and forms therebetween a tip cavity 42 open or exposed radially outwardly to face the radially surrounding turbine shroud (not shown) when mounted in the gas turbine engine.
  • the two squealer ribs 36,38 illustrated in Figure 2 provide radial extensions of the corresponding pressure and suction sidewalls 24,26 outwardly above the tip floor 40 and terminate in substantially squared internal corners around the tip cavity 42 and external corners aligned radially with the corresponding external pressure side or surface of the pressure sidewall 24 and suction side or external surface of the suction sidewall 26.
  • an elongate furrow or flute 44 is provided as a groove in the external surface of the pressure sidewall and extends chordally along the base of the first rib 36 at its junction with the tip floor 40.
  • the first rib 36 forms a radial extension of the common pressure sidewall 24 and therefore conforms in width A with the width of the pressure sidewall, and is generally equal thereto.
  • the second rib 38 forms an extension of the suction sidewall 26 and conforms in width thereto, which widths are substantially equal.
  • the second rib 38 thusly shares the common external surface of the suction sidewall 26 in a coplanar configuration along the full extent of the second rib between the leading and trailing edges.
  • the continuity of the first rib 36 with the external surface of the pressure sidewall 24 is interrupted radially by the flute 44 which offsets or recesses the base of the first rib 36 inwardly toward the tip cavity and away from the external pressure surface of the airfoil.
  • the exposed external corner of the first rib 36 above the flute 44 is radially aligned with or coplanar with the external pressure surface of the pressure sidewall below the flute 44, with the flute being in the form of a recess in the otherwise coextensive flat external surface of the pressure sidewall.
  • the first and second ribs 36,38 begin at the leading edge of the airfoil and join together in a common rib at the trailing edge of the airfoil.
  • the flute 44 commences in the pressure sidewall 24 immediately behind or near the airfoil leading edge and extends aft toward the trailing edge 30 at least along the extent of the tip cavity 42. As best illustrated in Figures 2 and 3 , the flute 44 preferably extends past the tip cavity 42 to the trailing edge 30 itself, and is spaced below the radially outer surface of the tip 34.
  • the flute 44 is preferably disposed solely in the lower portion of the first rib 36 along the tip floor 40 to the trailing edge of the blade, and not in the outer portion of the first rib 36 which maintains its generally square cross section conforming with the generally square cross section of the second rib 38.
  • the first rib 36 maintains a squared distal end of radial height B with a corresponding flat external surface of the corresponding height B which is generally coplanar with the flat external surface of the pressure sidewall 24 below the flute.
  • the height B of the squared end of the first rib 36 may be about 5-10 mils which represents a minor portion of the full depth C of the tip cavity, which is about 40-60 mils. In this way, the squared ends of both squealer ribs 36,38 are available for occasional tip rubbing with the surrounding turbine shroud and enjoy enhanced strength without compromising the configuration of the ribs or their performance following tip rubbing.
  • a row of inclined film cooling holes 46 is disposed along the length of the flute 44 as illustrated in the three figures, and extends from the internal cooling circuit 20 through the tip floor 40 and into the flute.
  • the film cooling holes may have any conventional configuration and size, and typically are inclined both radially and chordally aft with a compound inclination angle for introducing cooling air inside the flute for forming a continuous film of cooling air therein for discharge therefrom over the blade tip during operation.
  • the flute 44 is a local groove at the blade tip in the otherwise continuous external pressure surface thereof and terminates below the squared external corner of the first rib 36. In this way, the flute 44 permits the development of a continuous film of cooling air therein which then flows radially outwardly and around the external corner of the first rib 36 to protect the blade tip from the hot combustion gases 18 which migrate radially outwardly over the blade tip during operation.
  • the flute 44 provides enhanced cooling protection of the blade tip from where it commences near the leading edge of the airfoil to its termination at the thin trailing edge 30 of the airfoil. And, the squared corner configuration of the first rib 36 maintains its structural strength and integrity during tip rubbing, as well as maintains the original size of the flute 44 which is protected from tip rubbing by the height B of the additional material provided thereabove.
  • the exemplary flute 44 illustrated in Figure 3 is generally symmetrical in radial or vertical cross section, and includes a concave center fillet 48 as illustrated in Figure 3 which blends symmetrically radially outwardly and inwardly with corresponding outer and inner convex radii 50.
  • the two radii 50 introduce rounded corners or edges with the concave fillet 48 to blend with the external pressure surface of the airfoil both radially below and above the flute 44.
  • the flute 44 transitions smoothly with the external surface of the airfoil and enhances the formation of the film cooling layer discharged from the flute 44 during operation and its protective performance as the hot combustion gases migrate radially outwardly over the flute 44 during operation.
  • the relative sizes of the center fillet 48 and external radii 50 may be individually varied as desired to correspondingly change the profile and included angle inside the flute for maximizing performance of the flute during operation.
  • the outer radius 50 terminates below the external corner of the first rib 36 for maintaining the finite height B at the top of the rib coplanar with the external pressure surface below the rib.
  • the flute 44 may be disposed in lower part along the edge of the tip floor 40, and the film cooling holes 46 are inclined through the tip floor and into the center fillet of the flute 44.
  • the base of the first rib 36 is internally convection cooled by the row of film cooling holes 46 extending through the base thereof, while being further protected by the cooling film of air discharged from the flute 44 during operation.
  • the tip may be further cooled by introducing a plurality of tip holes 52 extending radially through the tip floor 40 as illustrated in Figures 1 and 2 in flow communication between the cooling circuit 20 and the tip cavity 42.
  • the radial tip holes 52 introduce cooling air inside the tip cavity for cooling the tip ribs on one side, while the opposite side of the first rib 36 is additionally cooled by the cooling air film discharged from the flute 44 in the predominant radial direction of the combustion gas flow over the blade tip from the pressure to suction sides of the blade.
  • the introduction of the flute 44 in the otherwise radially extending pressure side squealer rib 36 enjoys the benefits of the tip shelf and inclined squealer rib introduced in the above identified two previous patents, while also further enhancing the cooling tip design.
  • the pressure side rib 36 maintains squared corners above the flute for enhanced strength and resistance to tip rubbing.
  • the flute itself is protected from tip rubbing by the squared distal end of the pressure side squealer rib, and therefore maintains its original shape, performance, and cooling ability even following tip rubbing.
  • the flute 44 extends for most of the length of the blade tip cavity as well as aft therefrom to the trailing edge of the blade for ensuring effective tip cooling over the majority of the blade tip, and including in particular the relatively thin trailing edge region thereof.

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

Claims (10)

  1. Turbinenschaufel (12), die Folgendes aufweist:
    seitlich einander gegenüberliegende druck- und saugseitige Seitenwände (24,26), die sich in Sehnenrichtung zwischen einander gegenüberliegenden Anström- und Abströmkanten (28,30) und in Spannweitenrichtung zwischen einem Fuß (32) und einer Spitze (34) erstrecken und einen inneren Kühlkreis (20) aufweisen; wobei die Spitze (34) erste und zweite Versteifungsrippen (36,38) aufweist, die sich von einem Spitzenboden (40) nach außen zu dessen quadratischen Innen- und Außenecken erstrecken; und
    wobei die druckseitige Seitenwand (24) in ihrer Außenoberfläche eine Einkehlung (44) aufweist, die sich in Sehnenrichtung entlang dem Fuß der ersten Rippe (36) an dem Spitzenboden (40) erstreckt und unterhalb der quadratischen Außenecke der ersten Rippe (36) endet.
  2. Schaufel nach Anspruch 1, wobei die Einkehlung (44) eine konkave Mittelverrundung (48) umfasst, die in äußere und innere konvexe Radien (50) übergeht.
  3. Schaufel nach Anspruch 2, wobei die erste Rippe (36) hinsichtlich der Breite mit der druckseitigen Seitenwand (24) konform ist und an ihrem Fuß von der Außenoberfläche nach innen zu der Einkehlung (44) versetzt angeordnet ist, wobei die Außenecke der ersten Rippe (36) über der Einkehlung (44) koplanar zu der Außenoberfläche unter der Einkehlung ausgerichtet ist.
  4. Schaufel nach Anspruch 3, wobei die ersten und zweiten Rippen (36,38) an den Anström- und Abströmkanten (28,30) integral miteinander verbunden sind und einen nach außen offenen Spitzenhohlraum (42) bilden, und wobei die Einkehlung (44) in der druckseitigen Seitenwand (24) hinter der Anströmkante beginnt und sich entlang dem Spitzenhohlraum (42) zu der Abströmkante (30) erstreckt.
  5. Schaufel nach Anspruch 4, wobei die Einkehlung einzig in einem unteren Bereich der ersten Rippe (36) entlang dem Spitzenboden (40) und nicht in ihrem äußeren Bereich ausgebildet ist.
  6. Schaufel nach Anspruch 5, wobei die Einkehlung (44) teilweise in dem Spitzenboden (40) ausgebildet ist.
  7. Schaufel nach Anspruch 5, wobei die Einkehlung (44) an dem Spitzenhohlraum (42) vorbei zu der Abströmkante (30) und dort unterhalb der Spitze (34) verläuft.
  8. Schaufel nach Anspruch 5, ferner umfassend eine Reihe Filmkühlungslöcher (46), die sich von dem Kühlkreis durch den Spitzenboden (40) in die Einkehlung (44) erstrecken.
  9. Schaufel nach Anspruch 8, ferner umfassend mehrere Spitzenlöcher (52), die sich zwischen dem Kühlkreis (20) und dem Spitzenhohlraum (42) durch den Spitzenboden (40) erstrecken.
  10. Schaufel nach Anspruch 5, wobei die Außenoberfläche der druckseitigen Seitenwand (24) die Einkehlung (44) koplanar umschließt und unterhalb sowie oberhalb der Einkehlung (44) flache Bereiche aufweist.
EP20050255625 2005-09-14 2005-09-14 Turbineschaufel mit kannelierter Spitze Expired - Fee Related EP1764477B1 (de)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP20050255625 EP1764477B1 (de) 2005-09-14 2005-09-14 Turbineschaufel mit kannelierter Spitze
DE200560007900 DE602005007900D1 (de) 2005-09-14 2005-09-14 Turbineschaufel mit kannelierter Spitze

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP20050255625 EP1764477B1 (de) 2005-09-14 2005-09-14 Turbineschaufel mit kannelierter Spitze

Publications (2)

Publication Number Publication Date
EP1764477A1 EP1764477A1 (de) 2007-03-21
EP1764477B1 true EP1764477B1 (de) 2008-07-02

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DE (1) DE602005007900D1 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8092178B2 (en) 2008-11-28 2012-01-10 Pratt & Whitney Canada Corp. Turbine blade for a gas turbine engine

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10436039B2 (en) 2013-11-11 2019-10-08 United Technologies Corporation Gas turbine engine turbine blade tip cooling
US10436040B2 (en) 2017-01-13 2019-10-08 Rolls-Royce Corporation Airfoil with dual-wall cooling for a gas turbine engine
EP4234885A3 (de) 2021-02-04 2023-09-06 Doosan Enerbility Co., Ltd. Schaufelblatt mit einem system zur kühlung verjüngter schaufelspitzen für eine turbinenlaufschaufel, turbinenlaufschaufel, turbinenlaufschaufelanordnung, gasturbine und verfahren zur herstellung eines schaufelblatts

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1033678B (de) * 1954-12-21 1958-07-10 Maschf Augsburg Nuernberg Ag Deckband fuer Stroemungsmaschinen-Laufschaufeln
US5261789A (en) 1992-08-25 1993-11-16 General Electric Company Tip cooled blade
US6554575B2 (en) * 2001-09-27 2003-04-29 General Electric Company Ramped tip shelf blade
US6672829B1 (en) 2002-07-16 2004-01-06 General Electric Company Turbine blade having angled squealer tip
US6790005B2 (en) * 2002-12-30 2004-09-14 General Electric Company Compound tip notched blade

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8092178B2 (en) 2008-11-28 2012-01-10 Pratt & Whitney Canada Corp. Turbine blade for a gas turbine engine

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Publication number Publication date
DE602005007900D1 (de) 2008-08-14
EP1764477A1 (de) 2007-03-21

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