Fillet energized turbine stage

A turbine stage includes a row of airfoils and their platforms spaced laterally apart to define flow passages therebetween. Each airfoil is integrally joined to its platform at a corresponding arcuate fillet which is larger along the pressure side of the airfoil and smaller along the suction side as it varies in size around the leading edge. A film cooling root hole is disposed in the root fillet in flow communication with an internal cooling circuit in the airfoil for discharging cooling air along the fillet for energizing boundary layer flow of combustion gases flowing through the flow passages during operation.

BACKGROUND OF THE INVENTION

The present invention relates generally to gas turbine engines, and, more specifically, to turbines therein.

In a gas turbine engine air is pressurized in a compressor and mixed with fuel in a combustor for generating hot combustion gases. Turbine stages extract energy from the combustion gases to power the compressor, while also powering an upstream fan in a turbofan aircraft engine application, or powering an external drive shaft for marine and industrial applications.

A high pressure turbine (HPT) immediately follows the combustor and includes a stationary turbine nozzle which discharges combustion gases into a row of rotating first stage turbine rotor blades extending radially outwardly from a supporting rotor disk. The HPT may include one or more stages of rotor blades and corresponding turbine nozzles.

Following the HPT is a low pressure turbine (LPT) which typically includes multiple stages of rotor blades and corresponding turbine nozzles.

Each turbine nozzle includes a row of stator vanes having radially outer and inner endwalls in the form of arcuate bands which support the vanes. Correspondingly, the turbine rotor blades include airfoils integrally joined to radially inner endwalls or platforms supported in turn by corresponding dovetails which mount the individual blades in dovetail slots formed in the perimeter of the supporting rotor disk. An annular shroud surrounds the radially outer tips of the rotor airfoils in each turbine stage.

The stator vanes and rotor blades have corresponding airfoils including generally concave pressure sides and generally convex suction sides extending axially in chord between opposite leading and trailing edges. Adjacent vanes and adjacent blades form corresponding flow passages therebetween bound by the radially inner and outer endwalls.

During operation, the combustion gases are discharged from the combustor and flow axially downstream through the respective flow passages defined between the stator vanes and rotor blades. The aerodynamic contours of the vanes and blades, and corresponding flow passages therebetween, are precisely configured for maximizing energy extraction from the combustion gases which in turn rotate the rotor from which the blades extend.

The complex three-dimensional (3D) configuration of the vane and blade airfoils is tailored for maximizing efficiency of operation, and varies radially in span along the airfoils as well as axially along the chords of the airfoils between the leading and trailing edges. Accordingly, the velocity and pressure distributions of the combustion gases over the airfoil surfaces as well as within the corresponding flow passages also vary.

Undesirable pressure losses in the combustion gas flowpaths therefore correspond with undesirable reduction in overall turbine efficiency. For example, the combustion gases enter the corresponding rows of vanes and blades in the flow passages therebetween and are necessarily split at the respective leading edges of the airfoils.

The locus of stagnation points of the incident combustion gases extends along the leading edge of each airfoil, and corresponding boundary layers are formed along the pressure and suction sides of each airfoil, as well as along each radially outer and inner endwall which collectively bound the four sides of each flow passage. In the boundary layers, the local velocity of the combustion gases varies from zero along the endwalls and airfoil surfaces to the unrestrained velocity in the combustion gases where the boundary layers terminate.

One common source of turbine pressure losses is the formation of horseshoe vortices generated as the combustion gases are split in their travel around the airfoil leading edges. A total pressure gradient is effected in the boundary layer flow at the junction of the leading edge and endwalls of the airfoil. This pressure gradient at the airfoil leading edges forms a pair of counterrotating horseshoe vortices which travel downstream on the opposite sides of each airfoil near the endwall.

The two vortices travel aft along the opposite pressure and suction sides of each airfoil and behave differently due to the different pressure and velocity distributions therealong. For example, computational analysis indicates that the suction side vortex migrates away from the endwall toward the airfoil trailing edge and then interacts following the airfoil trailing edge with the pressure side vortex flowing aft thereto.

The interaction of the pressure and suction side vortices occurs near the midspan region of the airfoils and creates total pressure loss and a corresponding reduction in turbine efficiency. These vortices also create turbulence and increase undesirable heating of the endwalls.

Since the horseshoe vortices are formed at the junctions of turbine rotor blades and their integral root platforms, as well at the junctions of nozzle stator vanes and their outer and inner bands, corresponding losses in turbine efficiency are created, as well as additional heating of the corresponding endwall components.

Accordingly, it is desired to provide an improved turbine stage for reducing horseshoe vortex affects.

BRIEF DESCRIPTION OF THE INVENTION

A turbine stage includes a row of airfoils and their platforms spaced laterally apart to define flow passages therebetween. Each airfoil is integrally joined to its platform at a corresponding arcuate fillet which is larger along the pressure side of the airfoil and smaller along the suction side as it varies in size around the leading edge. A film cooling root hole is disposed in the root fillet in flow communication with an internal cooling circuit in the airfoil for discharging cooling air along the fillet for energizing boundary layer flow of combustion gases flowing through the flow passages during operation.

DETAILED DESCRIPTION OF THE INVENTION

Illustrated inFIG. 1are two exemplary first stage turbine rotor blades10which circumferentially adjoin each other in a full row thereof in a corresponding turbine stage of a gas turbine engine. As indicated above, combustion gases12are formed in a conventional combustor (not shown) and discharged in the axial downstream direction through the row of turbine blades10which extract energy therefrom for powering a supporting rotor disk (not shown) on which the blades are mounted.

The turbine stage includes a complete row of the blades, with each blade having a corresponding airfoil14integrally joined at a root end to a corresponding radially inner endwall or platform16. Each platform is in turn integrally joined to a corresponding axial-entry dovetail18conventionally configured for supporting the corresponding turbine blade in the perimeter of the rotor disk.

Each airfoil includes a generally concave pressure side20and a circumferentially or laterally opposite, generally convex suction side22extending axially in chord between opposite leading and trailing edges24,26. The two edges extend radially in span from root to tip of the airfoil.

As shown inFIGS. 1 and 2, each airfoil is hollow and includes an internal cooling circuit28bound by the opposite pressure and suction sides. The cooling circuit may have any conventional configuration and includes inlet channels extending through the platform and dovetail for receiving cooling air30bled from the compressor of the engine (not shown).

The cooling air is typically discharged from each airfoil through several rows of film cooling holes32located where desired on the pressure and suction sides of the airfoil, and typically concentrated near the leading edge thereof. Each airfoil typically also includes a row of trailing edge cooling holes34which emerge through the pressure side of the airfoil just before the thin trailing edge thereof.

The exemplary turbine blades illustrated inFIGS. 1 and 2may have any conventional configuration of the airfoil, platform, and dovetail for extracting energy from the combustion gases12during operation. As indicated above, the platform16is integrally joined to the root end of the airfoil and defines the radially inner flow boundary for the combustion gases12.

The blades are mounted in a row around the perimeter of the rotor disk, with the adjacent airfoils14being spaced circumferentially or laterally apart to define therebetween flow passages36for channeling the combustion gases12axially in the downstream direction during operation.

Each inter-airfoil flow passage36in the turbine stage illustrated inFIGS. 1 and 2is therefore defined and bounded by the pressure side20of one airfoil, the suction side22of the next adjacent airfoil, the corresponding pressure and suction side portions of the adjacent platforms16, and the radially outer turbine shroud (not shown) which surrounds the radially outer tip ends of the airfoils in the complete row of turbine blades.

As indicated above in the Background section, the combustion gases12flow through the corresponding flow passages36during operation and are necessarily split by the individual airfoils14. The high velocity combustion gases are circumferentially split at the corresponding airfoil leading edges24with a stagnation pressure threat, and with the formation of corresponding boundary layers along the opposite pressure and suction sides of the airfoil.

Furthermore, the combustion gases also form a boundary layer along the individual blade platforms16as the gases are split around the airfoil leading edge at its juncture with the platform.

Accordingly, the split combustion gas flow along the blade platforms results in a pair of counterrotating horseshoe vortices which flow axially downstream through the flow passages along the opposite pressure and suction sides of each airfoil. These horseshoe vortices create turbulence in the boundary layers, and migrate radially outwardly toward the mid-span regions of the airfoils and create losses of total pressure and reduce turbine efficiency.

In order to reduce these adverse affects of the horseshoe vortices, each platform16is integrally joined to the root end of each airfoil at a relatively large arcuate fillet38specifically configured to change the contour of the endwall or platform16to improve aerodynamic efficiency. Since the pressure and suction sides of the airfoil are differently configured for effecting the corresponding pressure and velocity distributions thereover, the fillet38preferably varies in size and configuration along the opposite sides of each airfoil. For example, the fillet38is larger along the airfoil pressure side20than along the suction side22around the leading edge24, and changes or blends smaller in size around the leading edge.

Furthermore, each of the fillets38includes a film cooling root or fillet hole40joined in flow communication with the internal cooling circuit28for discharging a portion of the spent cooling air30along the fillet during operation. The air discharged from the root hole40is used to energize the boundary layer flow of the combustion gases12at the initiation of the horseshoe vortices, and therefore weakens those vortices as they travel downstream through the corresponding flow passages36. The configuration of the root fillet38and placement of the root holes40may be tailored specifically to decrease the adverse affects of the horseshoe vortices beginning at their inception at the airfoil leading edges.

FIGS. 1–3illustrate several views of the root fillet38which preferentially varies in size from the leading edge24to the trailing edge26of the airfoil along the opposite pressure and suction sides20,22thereof. As best shown inFIG. 2, the fillet38extends from the platform16greater or higher in radial span or elevation (+) on the pressure side20than on the suction side22near the leading edge24.

The fillet38may be defined by its radius of curvature in the circumferential direction and smoothly blends the junction of the root end of the airfoil with the platform in an arcuate profile. The fillet38is substantially larger in size or extent on the airfoil pressure side than on the suction side to correspond with the different pressure and velocity profiles of the combustion gases on the opposite sides of the airfoil.

FIG. 2illustrates a circumferential section of the fillet38.FIG. 3illustrate the axial profile of the fillet38on the pressure side20of the airfoil. And,FIG. 4is a top view of the fillet38schematically showing its variation in size and surface area in the platform16on the opposite sides of the individual airfoils14.

A conventional blade platform is a symmetrical surface revolution around the axial centerline axis of the engine or turbine rotor forming circular arcs. In contrast, the root fillets38illustrated inFIGS. 2–4blend with the outer surface of the platforms16and vary the surface contour thereof both circumferentially and axially.

For example, each fillet38blends in depth (−) in a local depression42in the exposed or outer surface of the platform16which depression is substantially larger on the pressure side20of the airfoil than on the suction side. The local depression illustrated inFIGS. 2–4is relative to an otherwise conventional circumferentially circular platform having a reference or zero (θ) radial elevation.

Furthermore, since the introduction of the large fillets38and depressions42are local effects, the radial extent thereof may also be referenced from the forward and aft portions or edges of the flow platform which may remain axisymmetrical in the form of conventional circular arcs without local variation.

As shown inFIG. 2, for example, the fillet38increases preferably continuously in depth from the pressure side20of the airfoil to the platform16on the suction side of the next adjacent airfoil just aft of the leading edge of the airfoil near the maximum thickness or hump region thereof as best illustrated inFIG. 4.

As shown inFIGS. 3 and 4, the platform depression42is bounded by the isocline of zero depth (θ) and extends both axially in part and circumferentially in part, and terminates axially near the airfoil leading and trailing edges24,26corresponding with the forward and aft edges of the individual platform16. The local depression42has a maximum depth in the platform axially between the leading and trailing edges of the airfoil in the midchord region of the airfoil, and along the lateral or circumferential edges or splitlines of the individual platforms where they adjoin each other in the row of blades.

In the exemplary embodiment illustrated inFIG. 2, the local depressions42and bounding fillets38of adjacent airfoils14define a concave arcuate profile in the circumferential direction bounding the radially inner end of the common flow passage36defined circumferentially therebetween. Each turbine blade therefore has a fillet38and local depression42on its pressure side20which has a laterally concave arcuate profile, and a similar arcuate profile for the fillet and local depression on the opposite suction side22, which are different in extent or surface area due to the twist angle of the airfoil extending diagonally across each of the quadrilateral platforms illustrated inFIG. 4.

As best shown inFIGS. 2 and 4, the fillet38and depression42along the airfoil pressure side20are therefore circumferentially longer than the fillet38and depression along the suction side22of the adjacent airfoil. Correspondingly, the local depression42in the platform of each blade is larger in surface area on the pressure side20than on the opposite suction side22.

Since the horseshoe vortices are initiated at the forward end of the individual blade platforms at the junction with the leading edge24, the relatively large root fillets38and the cooperating local depressions42are specifically tailored in this region for weakening the vortices in conjunction with the introduction of the film cooling air from the root holes40.

FIGS. 1 and 4illustrate the varying size of the fillet38as it decreases in size around the leading edge24from the pressure side20to the suction side22.FIGS. 2 and 3illustrate the depth (−) of the local depression42as it blends with the fillet38. These figures also illustrate the increased elevation (+) of the fillet38as it blends with the root end of the airfoil.

FIG. 4illustrates the exemplary elevation (+) and depression (−) of the fillet38and the depressions42as they vary in surface area and radial span or elevation between the leading and trailing edges of each airfoil and each platform.

The fillet38as illustrated inFIGS. 1 and 4experiences a large change in size around the leading edge24and gradually blends to the trailing edge of each airfoil along the opposite sides of the platform. The platform, in turn, varies in surface depth to match the fillet38and blends with the forward and aft edges of the platform as illustrated inFIG. 3, with a maximum depth axially therebetween.

The relative size of the fillets38and local depressions42will vary in accordance with the specific design of the turbine stage, including the specific profile of the individual airfoils and their relative twist angle as mounted on the individual platform16. However, since the horseshoe vortices begin at the airfoil leading edge, the introduction of the large fillet38around the junction of the leading edge with the platform may be used to advantage with the root holes40for significantly weakening the horseshoe vortices during operation.

Although a single root hole40could be used in the fillet38on either or both sides of the leading edge24, in the preferred embodiment illustrated inFIG. 3a plurality of the root holes40border each of the leading edges24on the pressure and suction sides20,22for energizing the boundary layers at each of the horseshoe vortices. Each root hole may have a diameter in the exemplary range of 15–50 mils for injecting sufficient air into the fillet38to weaken in turn the horseshoe vortices.

For example,FIG. 3illustrates a preferred embodiment in which a pair of root holes40are located in each of the pressure and suction sides20,22of the airfoil on opposite sides of the leading edge24for injecting spent cooling air into the boundary layer of the combustion gas flow in the inter-blade flow passages.

Correspondingly, the fillets38are preferably devoid of any additional film cooling holes or apertures between the leading and trailing edges except near the leading edges24as indicated above. The fillets best cooperate with the introduction of air at the airfoil leading edges to weaken the horseshoe vortices at their inception since they increase in size and span as they travel downstream through the flow passages.

In the preferred embodiment illustrated in the several Figures, the root holes40are limited in axial position in chord aft from the leading edge24to within about five diameters of the root holes themselves to ensure the introduction of cooling air to energize the boundary layer at the inception of the horseshoe vortices.

The introduction of the large fillet around the airfoil leading edge blends the airfoil at its root with the platform and permits the introduction of the root holes40at this junction to preferentially inject spent cooling air to energize the boundary layer of the combustion gas flow at its inception along the blade platforms. The relatively large fillet38on the pressure side of the airfoil as illustrated inFIG. 2gradually slopes downwardly in the circumferential direction toward the suction side of the next adjacent blade along the flow streamline of the combustion gases.

Accordingly, the pressure side horseshoe vortex combines with the injected film cooling air at the fillet38and travels downwardly toward the suction side of the next adjacent blade in the circumferential direction as it also flows downstream through the flow passage. The pressure side horseshoe vortex therefore is biased closer to the blade platform and reduces its tendency to migrate radially outwardly toward the midspan of the airfoil as it flows downstream through the flow passage.

As illustrated inFIG. 4, the local depressions42between adjacent airfoils smoothly blend with the aft edges of the platforms to control flow of the corresponding horseshoe vortices as they exit the flow passage.

The root fillets38, local platform depressions42, and root holes40cooperate to create smaller horseshoe vortices from their inception which in turn will generate less flow turbulence. The vortices will remain closer to the blade platform and reduce their affect on the main passage flow. Total pressure losses will therefore be reduced for correspondingly increasing turbine efficiency. Furthermore, by reducing turbulence of the horseshoe vortices, the heat transfer coefficient with the platforms will also be reduced for decreasing undesirable heating of the platforms themselves.

Accordingly, weakening the horseshoe vortices can significantly reduce pressure losses and surface heating on the platform. And, film cooling from the root holes will also carry over to the platform surface for further insulating the platform from the hot combustion gases. The local depressions in the platforms on opposite sides of the airfoils lower the radially upward migration of the passage vortices and maintain the total pressure losses closer to the platforms to better protect the high velocity combustion gas main flow through the flow passages.

The introduction of the root fillets38, local depressions42, and root holes40provide benefits in both aerodynamics and heat transfer and may be applied to other turbine stages, including turbine nozzles as well. In a turbine nozzle, the vane airfoils are integrally formed with radially outer and inner bands which define similar endwalls. The fillets, local depressions, and root holes may be advantageously introduced at both endwalls of each vane for weakening the corresponding horseshoe vortices as they are created.