Gas turbine engine component having wavy cooling channels with pedestals

Gas turbine engines operate by passing a volume of high energy gases through a plurality of stages of vanes and blades, each having an airfoil, in order to drive turbines to produce rotational shaft power. The shaft power is used to drive a compressor to provide compressed air to a combustion process to generate the high energy gases. Additionally, the shaft power is used to drive a generator for producing electricity, or to produce high momentum gases for producing thrust. In order to produce gases having sufficient energy to drive the compressor or generator, it is necessary to combust the fuel at elevated temperatures and to compress the air to elevated pressures, which again increases the temperature. Thus, the vanes and blades are subjected to extremely high temperatures, often times exceeding the melting point of the alloys comprising the airfoils.

In order to maintain gas turbine engine components, such as the airfoils and outer air seals disposed about the tips of the airfoils, at temperatures below their melting point, it is necessary to, among other things, cool the components with a supply of relatively cooler air, typically bleed from the compressor. The cooling air is directed into the component to provide impingement and film cooling. For example, cooling air is passed into the interior of the airfoil to remove heat from the alloy, and subsequently discharged through cooling holes to pass over the outer surface of the airfoil to prevent the hot gases from contacting the vane or blade directly. Various cooling air patterns and systems have been developed to ensure sufficient cooling of various portions of the components.

Typically, each airfoil includes a plurality of interior cooling channels that extend through the airfoil and receive the cooling air. The cooling channels typically extend straight through the airfoil from the inner diameter end to the outer diameter end such that the air passes out of the airfoil. The cooling channels are typically formed by dividers or partitions that extend between the pressure side and suction side. In other embodiments, a serpentine cooling channel extends axially through the airfoil while winding radially back and forth. Cooling holes are placed along the leading edge, trailing edge, pressure side and suction side of the airfoil to direct the interior cooling air out to the exterior surface of the airfoil for film cooling. In blade outer air seals, a similar cooling channel extends between an inner circumferential surface that seals against the blade tips and an outer circumferential surface that contains the cooling air. Holes are typically provided in the inner circumferential surface to bleed cooling air to the tips of the blades.

In order to improve cooling effectiveness, the cooling channels are typically provided with trip strips and pedestals to improve heat transfer from the component to the cooling air. Trip strips, which typically comprise small surface undulations on the airfoil walls, are used to promote local turbulence and increase cooling. Pedestals, which typically comprise cylindrical bodies extending between the channel walls, are used to provide partial blocking of the passageway to control flow. Various shapes, configurations and combinations of partitions, trip strips and pedestals have been used in an effort to increase turbulence and heat transfer from the component to the cooling air.

Sometimes, it is desirable to obtain different heat transfer characteristics at different radial or circumferential positions along the component, particularly in microcircuits comprising narrower channels located between more centrally located channels and the pressure side or suction side of an airfoil. The microcircuits can be further formed by the use of ribs that subdivide the channel into individual circuits. Trip strips can be positioned within the cooling channels to vary the heat transfer, but trip strips are difficult to position within microcircuits. Microcircuits are typically manufactured using a constant thickness sheet of refractory metal, thus fixing the width of the cooling channel. It has been proposed to use microcircuits having cooling channels of constant width that are tapered (decreasing in length between the leading and trailing edges) in the radial direction to decrease cross-sectional area and increase heat transfer properties at the tip of the blade, as is described in U.S. Publication No. 2010/0003142 to Piggush et al., which is assigned to United Technologies Corporation. However, large differences in the heat transfer coefficient are difficult to achieve without the ability to change the Mach number of the coolant fluid, which is typically done with some type of augmentation feature such as trip strips or pedestals. There is a continuing need to improve cooling of turbine components at different radial or circumferential positions of the cooling channels to increase the temperature to which the components can be exposed thereby increasing the overall efficiency of the gas turbine engine.

The present invention is directed toward a gas turbine engine component having an internal cooling channel for receiving cooling air. The gas turbine engine component comprises a plurality of walls, a cooling channel, a plurality of ribs and a plurality of pedestals. The plurality of walls has a pair of major surfaces opposed to define an interior chamber. The cooling channel extends through the interior chamber of the plurality of walls between the major surfaces. The plurality of ribs extends through the cooling channel to form a plurality of wavy passages having bowed-out sections. The plurality of pedestals is positioned between adjacent ribs, each pedestal being positioned in a bowed-out section.

FIG. 1 shows a gas turbine engine including a turbine section in which blades having the cooling channels of the present invention are used.

FIG. 2 is a perspective view of a blade used in the turbine section of FIG. 1 having an airfoil through which wavy cooling channels of the present invention extend.

FIG. 3 is a top cross-sectional view of the blade taken at section 3 - 3 of FIG. 2 showing a suction side microcircuit in which the wavy cooling channels are disposed.

FIG. 4 is a side cross-sectional view of the microcircuit taken at section 4 - 4 of FIG. 3 showing an arrangement of wavy ribs and pedestals that form the wavy cooling channels.

FIG. 5 is a close-up view of the arrangement of FIG. 4 showing pedestals of varying diameter interposed between offset adjacent ribs of varying waviness.

FIG. 6 is a broken away cross-sectional view of the high pressure turbine of FIG. 1 showing a blade outer air seal which incorporates wavy cooling channels of the present invention.

FIG. 7 is a broken away perspective view of the blade outer air seal of FIG. 6 showing pedestals of varying diameter interposed between the wavy cooling channels.

FIG. 8 is a close-up view of another embodiment of the microcircuit taken at section 4 - 4 of FIG. 3 showing an arrangement of wavy ribs having teardrop shaped pedestals.

FIG. 1 shows gas turbine engine 10 , in which the wavy cooling channels having pedestals of the present invention may be used. Gas turbine engine 10 comprises a dual-spool turbofan engine having fan 12 , low pressure compressor (LPC) 14 , high pressure compressor (HPC) 16 , combustor section 18 , high pressure turbine (HPT) 20 and low pressure turbine (LPT) 22 , which are each concentrically disposed around longitudinal engine centerline CL. Fan 12 is enclosed at its outer diameter within fan case 23 A. Likewise, the other engine components are correspondingly enclosed at their outer diameters within various engine casings, including LPC case 23 B, HPC case 23 C, HPT case 23 D and LPT case 23 E such that an air flow path is formed around centerline CL.

Inlet air A enters engine 10 and it is divided into streams of primary air A P and secondary air A S after it passes through fan 12 . Fan 12 is rotated by low pressure turbine 22 through shaft 24 to accelerate secondary air A S (also known as bypass air) through exit guide vanes 26 , thereby producing a major portion of the thrust output of engine 10 . Shaft 24 is supported within engine 10 at ball bearing 25 A, roller bearing 25 B and roller bearing 25 C. primary air A P (also known as gas path air) is directed first into low pressure compressor (LPC) 14 and then into high pressure compressor (HPC) 16 . LPC 14 and HPC 16 work together to incrementally step up the pressure of primary air A P . HPC 16 is rotated by HPT 20 through shaft 28 to provide compressed air to combustor section 18 . Shaft 28 is supported within engine 10 at ball bearing 25 D and roller bearing 25 E. The compressed air is delivered to combustors 18 A and 18 B, along with fuel through injectors 30 A and 30 B, such that a combustion process can be carried out to produce the high energy gases necessary to turn turbines 20 and 22 , as is known in the art. Primary air A P continues through gas turbine engine 10 whereby it is typically passed through an exhaust nozzle to further produce thrust.

HPT 20 and LPT 22 each include a circumferential array of blades extending radially from discs 31 A and 31 B connected to shafts 28 and 24 , respectively. Similarly, HPT 20 and LPT 22 each include a circumferential array of vanes extending radially from HPT case 23 D and LPT case 23 E, respectively. Specifically, HPT 20 includes blades 32 A and 32 B and vane 34 . Blades 32 A and 32 B include internal channels or passages into which compressed cooling air A C air from, for example, HPC 16 is directed to provide cooling relative to the hot combustion gasses. Cooling passages of the present invention include microcircuits having opposing wavy ribs that increase the cross-sectional area of the passages and pedestals positioned between the ribs that produce a net reduction in the cross-sectional area of the passage, thereby improving heat transfer from blades 32 A and 32 B to the cooling air.

FIG. 2 is a perspective view of blade 32 A of FIG. 1 . Blade 32 A includes root 36 , platform 38 and airfoil 40 . Span S of airfoil 40 extends radially from platform 28 along axis A to tip 41 . Airfoil 40 extends generally axially along platform 38 from leading edge 42 to trailing edge 44 across chord length C. Root 36 comprises a dovetail or fir tree configuration for engaging disc 31 A ( FIG. 1 ). Platform 38 shrouds the outer radial extent of root 36 to separate the gas path of HPT 20 from the interior of engine 10 ( FIG. 1 ). Airfoil 40 extends from platform 38 to engage the gas path. Airfoil 40 includes leading edge cooling holes 46 , trailing edge cooling slots 47 , pressure side cooling holes 48 , pressure side 50 and suction side 52 . Although not shown, airfoil 40 may also include various cooling holes along suction side 52 . As shown, airfoil 40 includes cooling passages 54 that extend from tip 41 radially down to root 36 . Typically, cooling air is directed into the radially inner surface of root 36 from, for example, HPC 16 ( FIG. 1 ). The cooling air is guided out of cooling holes 46 , cooling slots 47 and the other cooling holes. As shown in FIG. 4 , cooling passages 54 include wavy cooling channels having pedestals of the present invention, which are placed at different radial positions along airfoil 40 to provide different cooling characteristics of cooling air A C ( FIG. 1 ). As discussed with reference to FIG. 5 , the size of the wavy ribs and pedestals can be increased to increase the Mach number and heat transfer coefficient of cooling air A C ( FIG. 1 ) at the local radial position.

FIG. 3 is a top cross-sectional view of blade 32 A taken at section 3 - 3 of FIG. 2 showing cooling passages 54 extending through airfoil 40 . In particular, airfoil 40 comprises a thin-walled structure having a plurality of hollow cavities that form cooling channels 54 A- 54 D. The depiction of cooling holes in airfoil 40 is omitted in FIG. 3 . Cooling air A C ( FIG. 1 ) flows through cooling channels 54 A- 54 D and out the cooling holes to provide cooling to airfoil 40 . Cooling channels 54 B, 54 C and 54 D comprise conventional internal cooling channels formed using partitions 55 A- 55 C. Cooling channel 54 A comprises a microcircuit cooling channel formed of opposing internal major surfaces 56 A and 56 B positioned between suction side 50 and internal cooling channels 54 B and 54 C. Cooling channel 54 A is, in one embodiment, manufactured using a constant thickness sheet of refractory metal such that channel 54 A has a near constant width between internal surfaces 56 A and 56 B. As such, the width of cooling channel 54 A is in the general circumferential direction extending between suction side 50 and pressure side 52 , while its length is in the general axial direction extending between leading edge 42 and trailing edge 44 . Cooling channel 54 A provides cooling specifically configured for positions along suction side 50 . Cooling channel 54 A includes wavy ribs disposed between internal surfaces 56 A and 56 B to form radially extending microcircuits, as shown in FIG. 4 .

FIG. 4 is a side cross-sectional view of microcircuit cooling channel 54 A taken at section 4 - 4 of FIG. 3 showing an arrangement of wavy ribs 58 A- 58 F and pedestal groups 60 A and 60 B in cooling channel 54 A. Ribs 58 A- 58 F extend generally radially between an inner diameter portion of airfoil 40 and tip 41 such that cooling air A C is guided radially through blade 32 A. Ribs 58 A- 58 F connect suction side 50 to partition 55 A ( FIG. 3 ). Ribs 58 A- 58 F are of the same width in the general circumferential direction, each being uniformly thick across their radial extent such that passage 54 A is uniformly thick between surfaces 56 A and 56 B. Likewise, ribs 58 A- 58 F are of the same length in the general axial direction, each being nearly uniformly thick across their radial extent. Every other rib is identical, with the remaining ribs being mirror images. For example, ribs 58 A, 58 C and 58 E are the same as each other, and ribs 58 B, 58 D and 58 F are the same as each other and are mirror images of ribs 58 A, 58 C and 58 E. Ribs 58 A- 58 F include lower segments that extend generally straight in the radial direction. The straight segments define a nominal cross-sectional area for channels 65 A- 65 E. Ribs 58 A- 58 F include upper segments that extend in the radial direction in an undulating or wavy pattern, as will be discussed in greater detail with respect to FIG. 5 .

First pedestal grouping 60 A is positioned radially outward of ribs 58 A- 58 F, between the tips of the ribs and blade tip 41 . First pedestal grouping 60 A includes pedestals 62 , which are all of equal shape. In the disclosed embodiment, pedestals 62 are circular and have the same diameter. Pedestals 62 are distributed in a staggered pattern such that cooling air A C is diffused through grouping 60 A to remove heat. Specifically, pedestals 62 connect suction side 50 with partition 55 A to pull heat away from suction side 50 . Second pedestal grouping 60 B includes pedestals 64 , and is interposed with the wavy upper segments of ribs 58 A- 58 F. Pedestals 64 also connect suction side 50 with partition 55 A to pull heat away from suction side 50 . The wavy upper segments of ribs 58 A- 58 F and pedestals 64 are configured to increase the Mach number and the heat transfer coefficient of cooling air A C as it passes through channels 65 A- 65 E formed between ribs 58 A- 58 F. In other embodiments of the invention, pedestals 62 and 64 need not be round, but can be of other shapes that reduce the net cross-sectional area of channels 65 A- 65 E.

The shape of wavy channels 65 A- 65 E and the size of pedestals 64 are selected to achieve desired Mach numbers and heat transfer coefficients at selected local regions along airfoil 40 . For example, a relatively low heat transfer coefficient is desired near where cooling air A C enters channels 65 A- 65 E. Here, channels 65 A- 65 E are configured as a straight passage with no augmentation features, such as pedestals or trip strips. However, a higher heat transfer coefficient is desired at positions further radial outward of the straight segments. There, a single pedestal 64 is positioned in the center of each channel at a position where ribs 58 A- 58 F form a bowed-out or expanded portion. In alternative embodiments, multiple pedestals are positioned where ribs 58 A- 58 F form bowed-out or expanded portions.

FIG. 5 is a close-up view of the microcircuit cooling channel arrangement of FIG. 4 showing pedestals 64 A- 64 F of varying diameter interposed between offset adjacent ribs 58 C- 58 E of varying wavyness. Ribs 58 C- 58 E form cooling channels 65 D and 65 E. Ribs 58 C- 58 E include bowed-in sections 66 A and 66 B and bowed-out sections 68 A and 68 B. Bowed-out sections 68 A and 68 B provide an area in which to place pedestals 64 D and 64 A, respectively. Ribs 58 A- 58 C extend in a radial direction and are spaced from each other in an axial direction, with respect to radial axes 70 A and 70 B. The lengths of the bowed-out portions of channel 65 D and 65 E produce bowed-in portions in adjacent channels, in the axial direction. As such, channel 65 D includes bowed-in portion 66 A and channel 65 E includes bowed-in portion 66 B. Bowed-in portion 66 A is positioned axially upstream of bowed-out portion 68 B, while bowed-in portion 66 B is positioned axially downstream of bowed-out portion 68 A. Thus, bowed-out portions and bowed-in portions give rise to the wavy shape of ribs 58 A- 58 F and channels 65 A- 65 E. Bowed-in sections 66 A and 66 B comprise constrictions or contractions of channels 65 A- 65 E. Bowed-out sections 68 A and 68 B comprise expansions of channels 65 A- 65 E. The bowed-out and bowed-in portions also give rise to a staggered distribution of pedestals 64 : pedestals in every other column are radially offset from those in axially adjacent columns.

Ribs 58 C- 58 E are bowed so that the addition of pedestals 64 A- 64 F creates only a moderate reduction in the cross section area of the channels, rather than a sudden reduction such as from a pedestal in a straight channel. Ribs 58 C- 58 E curve around pedestals 64 A- 64 F so that the shape of ribs 58 C- 58 F approximate the shape of pedestals 64 A- 64 F. For example, channel 65 D includes bowed-out portion 68 A having a specific length, while channel 65 E includes bowed-out portion 68 B having a specific length. Pedestal 64 D is positioned centrally within bowed-out portion 68 A, and pedestal 64 A is positioned centrally within bowed-out portion 68 B. Bowed-out portion 68 B and pedestal 64 A are larger than bowed-out portion 68 A and pedestal 64 D, respectively. Thus, putting aside the presence of pedestals 64 A and 64 D, the cross-sectional area of channel 65 E is larger than the cross-sectional area of channel 65 D at bowed-out portions 68 B and 68 A. However, because pedestal 64 A is larger than pedestal 64 D, the net cross-sectional area at bowed-out portion 65 A is smaller than at bowed-out portion 68 A. In other words, the distance between rib 58 D and pedestal 64 A at bowed-out portion 68 B is less than the distance between rib 58 D and pedestal 64 D at bowed-out portion 68 A. As such, pedestal 64 A and bowed-out portion 68 B result in a larger Mach number and larger heat transfer coefficient within channel 65 E as compared to pedestal 64 D and bowed-out portion 68 A in channel 65 D. In other embodiments, multiple pedestals can be used in place of each of pedestals 64 A and 64 D. The multiple pedestals can be configured to have the same blockage effect within each of channels 68 B and 68 A. For example, two smaller pedestals having half the width of pedestal 64 A can be positioned in channel 68 B. As shown in FIG. 5 , the lengths of the bowed-out portions 68 A and 68 B increase as channels 65 D and 65 E extend radially outwardly such that additional cooling is provided.

Ribs 58 A- 58 F form an axially extending series of ribs having a radially extending series of bowed-out sections interposed with an array of pedestals that decrease the overall cross-sectional area of channels 65 A- 65 E. This configuration creates flow paths within channels 65 A- 65 E that have cross-sectional areas that decrease relatively uniformly. Specifically, successive bowed-out sections and successive pedestals increase in length and diameter, respectively, in uniform stepped increments in the radial streamwise direction such that cross-sectional areas of the channels are reduced at a constant rate. For comparison, if pedestals are introduced into straight walled channels, there would be significant local reduction in cross section area followed directly by an equal increase in the cross section area, which would result in a non-constant reduction of the Mach number and heat transfer coefficient. Additionally, if only pedestals and no ribs were used to change the desired heat transfer coefficient, sparsely spaced pedestals where low heat transfer is desirable would result in little thermal communication between opposing walls of the channel. Wavy ribs 58 A- 58 F of the present invention allow a significant amount of conduction between surfaces 56 A and 56 B, thereby reducing thermal gradients between the surfaces. Wavy ribs 58 A- 58 F also produce a strong structural tie between surfaces 56 A and 56 B that reduces thermally induced stresses. Wavy ribs 58 A- 58 F additionally permit placement of pedestals 64 A- 64 F such that changes in heat transfer coefficient can be achieved while simultaneously changing the Mach number, thereby allowing uniform changes.

The present invention has been described with respect to gas turbine engine airfoils, such as blades and vanes. The invention, however, may also be incorporated into other types of gas turbine engine components that utilize flow or pressurized cooling air A C . For example, air seals located at outer diameter ends of turbine blades utilize cooling air to cool the outer diameter extend of the gas path. These air seals are often referred to as a blade outer air seal (BOAS). As described with reference to FIGS. 6 and 7 , wavy cooling channels having pedestals of differing diameters, as configured for the present invention, may be incorporated into blade outer air seals.

FIG. 6 is a broken away cross-sectional view of high pressure turbine (HPT) 20 of FIG. 1 showing blade outer air seal 82 which incorporates wavy cooling channels of the present invention. HPT 20 is axially positioned between combustor section 18 and vane 34 . Disk 31 A ( FIG. 1 ) includes rotor blade 32 A, which extends radially toward HPT case 23 D. Blade 32 A includes root portion 72 , airfoil portion 74 having tip 76 , and platform 78 . Root portion 72 retains blade 32 A to disk 31 A during rotation of rotor HPT 20 . Airfoil portion 74 extends radially outwardly through flow path 80 and provides a flow surface that is acted upon by primary air A P ( FIG. 1 ). Platform 78 extends laterally from airfoil portion 74 and mates with similar platforms (not shown) of circumferentially adjacent blades to define a radially inner boundary to the flow of combustion gases through HPT 20 . HPT case 23 D extends circumferentially about and radially outwardly of HPT 20 and includes a plurality of blade outer air seals (BOAS) 82 , which comprise a radially outer boundary for the flow of combustion gases through the turbine. Each blade outer air seal 82 includes baffle 84 . Each pair of BOAS 82 and baffle 84 comprises a pair of opposing major surfaces that form cooling chamber 92 . Cooling air A C ( FIG. 1 ) is directed between BOAS 82 and baffle 84 to cool the interior surface of HPT case 23 D. Wavy cooling channels including pedestals are disposed within cooling chamber 92 , as shown in FIG. 7 .

FIG. 7 is a broken away perspective view of blade outer air seal 82 of FIG. 6 showing pedestals 64 A- 64 C of varying diameter interposed between wavy ribs 58 D and 58 E. Wavy ribs 58 D and 58 E form cooling channel 65 E. Cooling air A C flows within cooling channel 65 E. Configured as such, cooling channel 65 E functions similarly to cooling channel 65 E of FIGS. 4 and 5 , with similar features labeled alike. BOAS 82 includes base 86 and hook portions 88 A and 88 B. Baffle 84 is positioned over BOAS 82 to form cooling chamber 92 .

Base 86 extends circumferentially over tips 76 of airfoil portions 74 ( FIG. 6 ) and may include appropriate abradable material as is known in the art. Hook portions 88 A and 88 B extend radially from base 86 and include axial projections to engage with mating mounting hardware on HPT case 23 D ( FIG. 6 ). Base 86 and hook portions 88 A and 88 B may include seal slots (not shown) for receiving feather seals to seal between an adjacent BOAS. Base 86 also includes cooling chamber 92 , which may be embedded radially inward into base 86 . Baffle 84 covers BOAS 82 to retain cooling air A C within chamber 92 . In FIG. 7 , baffle 84 is partially broken away to shown ribs 58 D and 58 E and pedestals 64 A- 64 C.

Ribs 58 D and 58 E extend radially outwardly from base 86 toward baffle 84 . Likewise, pedestals 64 A- 64 C extend radially outwardly from base 86 toward baffle 84 . Ribs 58 D and 58 E are spaced from each other in the axial direction. As shown, cooling air A C enters cooling channel 65 E between ribs 58 D and 58 E. Ribs 58 D and 58 E and pedestals 64 A- 64 C need not contact baffle 84 , but may do so in various embodiments. In other embodiments, ribs 58 D and 58 E may extend radially inwardly from baffle 84 toward base 86 . In yet another embodiment, baffle 84 may be integrally formed with base 86 , such as by a casting process, and ribs 58 D and 58 E and pedestals 64 A- 64 C may extend from both baffle 84 and base 86 . In any embodiment, baffle 84 comprises a cover having a surface that forms the outer radial extent of cooling chamber 92 .

The configuration of ribs 58 D and 58 E and pedestals 64 A- 64 C are selected to achieve desired Mach numbers and heat transfer coefficients at selected regions along base 86 . For example, in the embodiment shown, cooling air A C flows from a first, wider end of channel 65 E to a second, narrower end of channel 65 E. A low heat transfer coefficient may be desirable where cooling air A C enters channel 65 E. Thus, ribs 58 D and 58 E are positioned further apart from each other with a small diameter pedestal positioned between. A higher heat transfer coefficient may be desirable where cooling air A C leaves channel 65 E. Thus, ribs 58 D and 58 E are positioned closer toward each other with a large diameter pedestal positioned between. In another embodiment, cooling air A C flows from the second, narrower end of channel 65 E to the first, wider end of channel 65 E, opposite from what is shown in FIG. 7 .

FIG. 8 is a close-up view of another embodiment of the microcircuit taken at section 4 - 4 of FIG. 3 showing an arrangement of wavy ribs 94 A- 94 C having teardrop shaped pedestals 96 A- 96 F. Ribs 94 A- 94 C have varying wavyness to accommodate the shape of teardrop shaped pedestals 96 A- 96 F. Ribs 94 A- 94 C form cooling channels 98 A and 98 B. Ribs 94 A- 94 C include bowed-in sections 100 A and 100 B and bowed-out sections 102 A and 102 B. Bowed-out sections 102 A and 102 B provide an area in which to place pedestals 96 D and 96 A, respectively. Ribs 94 A- 94 C extend in a radial direction and are spaced from each other in an axial direction, with respect to radial axes 104 A and 104 B. Bowed-in sections 100 A and 100 B and bowed-out sections 102 A and 102 B give rise to the wavy shape of ribs 94 A- 94 C and channels 98 A and 98 B. The bowed-out and bowed-in portions also give rise to a staggered distribution of pedestals 96 A- 96 D.

Pedestals 96 A- 96 D are teardrop shaped to assist in eliminating or reducing stagnation zones behind each pedestal within channels 98 A and 98 B. Stagnation zones detrimentally reduce thermal transfer effectiveness. As depicted in FIG. 8 , pedestal 96 A includes leading edge wall 106 , trailing edge wall 108 and side walls 110 A and 110 B. Leading edge wall 106 has a first radius of curvature R 1 so as to produce a rounded leading edge. Trailing edge wall 108 has a second radius of curvature R 2 so as to produce a rounded trailing edge. Radius of curvature R 2 is less than the first radius of curvature R 1 . Side walls 110 A and 110 B are longer than the distance between side walls 110 A and 110 B at all points such that pedestal 96 A has an elongate shape. Side walls 110 A and 110 B extend straight between rounded leading edge wall 106 and rounded trailing edge wall 108 . In the depicted embodiments pedestal 96 A is tapered along the entire length between the leading and trailing edges, but need not be in every embodiment. Side walls 110 A and 110 B are tangent with the circles of leading edge wall 106 and trailing edge wall 108 . As such, side walls 110 A and 110 B converge toward each other as they extend from leading edge wall 106 to trailing edge wall 108 . Pedestal 96 A is thus provided with a decreasing height as it extends from its leading edge to its trailing edge. In other words, the distance between side walls 110 A and 110 B near leading edge 106 is larger than the distance between side walls 110 A and 110 B near trailing edge 108 . In one embodiment, radius of curvature R 2 is smaller than radius of curvature R 1 such that diffusion angle α is about 5 to about 10 degrees. This diffusion angle α reduces the wake behind pedestal 96 , maintaining straight channel flow of the cooling air between ribs 94 B and 94 C. Diffusion angles α above 10 degrees tend to result in detachment of the cooling air flow as it wraps around the pedestal, similar to that of a round pedestal, thereby resulting in undesirable turbulence dead zones.

As with the embodiment of FIG. 5 , ribs 94 A- 94 C are shaped to correspond to the shape of pedestals 96 A- 96 F. Ribs 94 A- 94 C include straightened portions that correspond to the straight sidewalls of each pedestal. For example, ribs 94 B and 94 C include straight portions 112 A and 112 B that correspond to sidewalls 110 A and 110 B of pedestal 96 A. Ribs 94 A- 94 C are bowed so that the addition of pedestals 96 A- 96 F creates only a moderate reduction in the cross section area of the channels, rather than a sudden reduction such as from a pedestal in a straight channel. As described above, putting aside the presence of pedestals 96 A and 96 D, the cross-sectional area of channel 98 B is larger than the cross-sectional area of channel 98 A at bowed-out portions 102 B and 102 A. However, because pedestal 96 A is larger than pedestal 96 D, the net cross-sectional area at bowed-out portion 65 A is smaller than at bowed-out portion 68 A. In other words, the distance between rib 94 B and pedestal 96 A at bowed-out portion 102 B is less than the distance between rib 94 B and pedestal 96 D at bowed-out portion 102 A. As such, pedestal 96 A and bowed-out portion 102 B result in a larger Mach number and larger heat transfer coefficient within channel 98 B as compared to pedestal 96 D and bowed-out portion 102 A in channel 98 A.

Ribs 94 A- 94 C form an axially extending series of ribs having a radially (as depicted) or circumferentially (such as within a BOAS) extending series of bowed-out sections interposed with an array of pedestals that decrease the overall cross-sectional area of channels 98 A- 98 B. This configuration creates flow paths within channels 98 A- 98 B that have cross-sectional areas that decrease relatively uniformly. Specifically, successive bowed-out sections and successive pedestals increase in length and width, respectively, in uniform stepped increments in the radial or circumferential streamwise direction such that cross-sectional areas of the channels are reduced at a constant rate. Further, in the embodiment of FIG. 8 , each pedestal and bowed-out section itself tapers in length and width, respectively, in the radial or circumferential streamwise direction along the axis of the teardrop shaped pedestal. The teardrop shape reduces stagnation zones behind each pedestal.

The present invention permits the local Mach number and heat transfer coefficient to be manipulated to produce moderate or large increases wherever desirable in the airfoil component. For example, in some configurations it is desired to have a quite low heat transfer coefficient in one region of the component and a much higher heat transfer coefficient in another portion of the component. The diameter of the pedestals and the lengths of the bowed-out portions can be varied to adjust these parameters. The wavy ribs and pedestals of the present invention are easily stamped, such is in embodiments where refractory sheet metal of constant width is used to produce microcircuits. As such, the Mach number and heat transfer coefficient can be readily changed within a constant thickness channel.

While the invention has been described with reference to an exemplary embodiment(s), it will be understood by those skilled in the art that various changes may be made and equivalents may be substituted for elements thereof without departing from the scope of the invention. In addition, many modifications may be made to adapt a particular situation or material to the teachings of the invention without departing from the essential scope thereof. Therefore, it is intended that the invention not be limited to the particular embodiment(s) disclosed, but that the invention will include all embodiments falling within the scope of the appended claims.