Patent Application
20150184524
This invention is directed generally to turbine airfoils, and more particularly to hollow turbine airfoils having cooling channels for passing fluids, such as air, to cool the airfoils
Typically, gas turbine engines include a compressor for compressing air, a combustor for mixing the compressed air with fuel and igniting the mixture, and a turbine blade assembly for producing power. Combustors often operate at high temperatures that may exceed 2,500 degrees Fahrenheit Typical turbine combustor configurations expose turbine vane and blade assemblies to these high temperatures. As a result, turbine vanes and blades must be made of materials capable of withstanding such high temperatures. In addition, turbine vanes and blades often contain cooling systems for prolonging the life of the vanes and blades and reducing the likelihood of failure as a result of excessive temperatures
Typically, turbine blades are formed from an elongated portion forming a blade having one end configured to be coupled to a turbine blade carrier and an opposite end configured to form a blade tip. The blade is ordinarily composed of a leading edge, a trailing edge, a suction side, and a pressure side. The inner aspects of most turbine blades typically contain an intricate maze of cooling circuits forming a cooling system. The cooling circuits in the blades receive air from the compressor of the turbine engine and pass the air through the ends of the blade adapted to be coupled to the blade carrier. The cooling circuits often include multiple flow paths that are designed to maintain all aspects of the turbine blade at a relatively uniform temperature. At least some of the air passing through these cooling circuits is exhausted through orifices in the leading edge, trailing edge, suction side, and pressure side of the blade Cooling fluids pass over trip strips, which increase the heat transfer of the cooling system Most trip strips are formed from generally square or rectangular cross-sections, as shown in
A turbine airfoil usable in a turbine engine and having at least one cooling system with an efficient trip strip is disclosed. At least a portion of the cooling system may include one or more cooling channels having one or more trip strips protruding from an inner surface forming the cooling channel. The trip strip may have improved operating characteristics including enhanced heat transfer capabilities and a substantial reduction in pressure drop typically associated with conventional trip strips. In at least one embodiment, the trip strip may have a cross-sectional area with a first section of an upstream surface of the trip strip being positioned nonparallel and nonorthogonal to a surface forming the cooling system channel extending upstream from the at least one trip strip and a concave shaped downstream surface of the at least one trip strip that enables separated flow to reattach to the cooling fluid flow.
In at least one embodiment, a turbine airfoil may be formed from a generally elongated hollow airfoil formed from an outer wall, and having a leading edge, a trailing edge, a pressure side, a suction side, a root at a first end of the airfoil and a tip at a second end opposite to the first end, and a cooling system positioned within interior aspects of the generally elongated hollow airfoil. The cooling system may include one or more trip strips protruding from an inner surface defining a channel of the cooling system. The trip strip may be formed from a generally elongated body and the trip strip may have a cross-sectional area with at least a first section of an upstream surface of the trip strip being positioned nonparallel and nonorthogonal to a surface forming the cooling system channel extending upstream from the trip strip and a concave shaped downstream surface of the trip strip
A downstream surface of the trip strip may be formed from a concave surface forming generally a quarter circle. An upstreammost point of the downstream surface of the trip strip may be positioned upstream from an intersection of the downstream surface at a top surface of the trip strip An upstreammost point of the downstream surface of the trip strip may be positioned upstream from an intersection of the downstream surface and the inner surface defining the channel of the cooling system. The trip strip include a nonlinear top surface. In at least one embodiment, the nonlinear top surface has a convex shaped outer surface The nonlinear top surface have a leading edge that is positioned closer to the inner surface defining the channel of the cooling system than a trailing edge of the nonlinear top surface
The upstream surface of the trip strip may include a second section that is nonparallel and nonothogonal with the first section. The second section of the upstream surface may be positioned generally orthogonal to the surface forming the cooling system channel extending upstream from the trip strip. The second section of the upstream surface may be positioned generally orthogonal to a longitudinal axis of the channel of the cooling system in which the trip strip resides. The trip strip may have a consistent cross-sectional area throughout an entire length of the at least one trip strip
During use, cooling fluid is passed into the cooling system, including the cooling channel At least a portion of the cooling fluid contacts the trip strip In particular, at least a portion of the cooling fluid contacts the first section of the upstream surface, where the cooling fluid is directed upwardly at an angle that is nonparallel and nonorthogonal to the inner surface forming the cooling channel. The cooling fluid then strikes the second section of the upstream surface, which causes the cooling fluid to be directed at an even steeper angle away from the inner surface. The cooling fluid then flows past the second section and along the top surface. While passing the first section, the second section and the top surface, heat is being passed from the trip strip to the cooling fluid via convection The cooling fluid flows past the top surface and then a portion of the cooling fluids forms a circular flow of cooling fluids that flow against the concave downstream surface The formation of eddies on the downstream surface is mitigated by accommodating the primary vortex or eddie and ensuring higher velocity and thus higher heat transfer on the downstream surface as compared to the low velocity recirculation in conventional square or rectangle cross section trip strips. This uniquely shaped trip strip cross-sectional area creates higher internal convective cooling potential for the turbine blade cooling channel, thus generating a high rate of internal convective heat transfer and efficient overall cooling system performance. This performance equates to a reduction in cooling demand and better turbine engine performance. An advantage of the turbine airfoil cooling system is that the system is configured to cool cooling channels and because of its configuration is particularly well suited to cool cooling channels in industrial gas turbine engines.
Another advantage of the cooling system is that the configuration of the cross-sectional area of the trip strip reduces the amount of pressure drop typically associated with trip strips
These and other embodiments are described in more detail below
The accompanying drawings, which are incorporated in and form a part of the specification, illustrate embodiments of the presently disclosed invention and, together with the description, disclose the principles of the invention
As shown in
In at least one embodiment, as shown in
The cooling system 14 may include one or more trip strips 16 protruding from an inner surface 20 defining a channel 18 of the cooling system 14 The trip strip 16 may be formed from a generally elongated body 50. The trip strip 16, as shown in
In at least one embodiment, the trip strip 16 may include a nonlinear top surface 56. The nonlinear top surface 56 may have a convex shaped outer surface
The nonlinear top surface 56 may have a leading edge 60 that is positioned closer to the inner surface 20 defining the channel 18 of the cooling system 14 than a trailing edge 62 of the nonlinear top surface 56.
The upstream surface 26 of the trip strip 16 may include a second section 64 that is nonparallel and nonothogonal with the first section 24. The second section 64 of the upstream surface 26 may be positioned generally orthogonal to the surface 20 forming the cooling system channel 18 extending upstream from the trip strip 16 The second section 64 of the upstream surface 26 may be positioned generally orthogonal to a longitudinal axis 66 of the channel 18 of the cooling system 14 in which the trip strip 16 resides.
In at least one embodiment, the trip strip 16 may have a consistent cross-sectional area throughout an entire length of the trip strip 16. In another embodiment, the shape of the cross-sectional area of the trip strip 16 may vary throughout its length, especially when the trip strip 16 is nonorthogonal to the flow of cooling fluids over the trip strip 16, such as when the trip strip 16 is nonorthogonal to a longitudinal axis of the cooling channel 18 The trip strip 16 may extend from a first sidewall 68 to a second sidewall 70 forming the cooling channel 18. In another embodiment, the trip strip 16 may extend between the first and second sidewalls 68, 70 but only contact one of the sidewalls 68, 70 or stop short of contacting either sidewalls 68, 70. In yet another embodiment, the trip strip 16 may be positioned generally orthogonal to the longitudinal axis 66 of the cooling channel 18 The trip strip 16 may also be positioned nonparallel and nonorthogonal to the longitudinal axis 66 of the cooling channel 18 The height, e, of the trip strip 16 can change as a function of the relative distance between upstream and downstream trip strips 16, the pitch p. A consistent p/e ratio may be maintained for a cooling channel 18 or the p/e ratio may be varied along a portion of or along an entire length of the cooling channel 18.
During use, cooling fluid is passed into the cooling system 14, including the cooling channel 18. At least a portion of the cooling fluid contacts the trip strip 16. In particular, at least a portion of the cooling fluid contacts the first section 24 of the upstream surface 26, where the cooling fluid is directed upwardly at an angle that is nonparallel and nonorthogonal to the inner surface 26 forming the cooling channel 18. The cooling fluid then strikes the second section 64 of the upstream surface 26, which causes the cooling fluid to be directed at an even steeper angle away from the inner surface 26 The cooling fluid then flows past the second section 64 and along the top surface 56. While passing the first section 24, the second section 64 and the top surface 56, heat is being passed from the trip strip 16 to the cooling fluid via convection. The cooling fluid flows past the top surface 56 and then a portion of the cooling fluids forms a circular flow of cooling fluids that flow against the concave downstream surface 28 The flow of cooling fluids flows against the concave downstream surface 28 without formation of any eddies which would reduce the heat transfer and therefore negatively affect the heat transfer efficiency of the trip strip 16.
This uniquely shaped trip strip cross-sectional area creates higher internal convective cooling potential for the turbine blade cooling channel 18, thus generating a high rate of internal convective heat transfer and efficient overall cooling system performance. This performance equates to a reduction in cooling demand and better turbine engine performance.
The foregoing is provided for purposes of illustrating, explaining, and describing embodiments of this invention. Modifications and adaptations to these embodiments will be apparent to those skilled in the art and may be made without departing from the scope or spirit of this invention.
