Patent Application
20110070078
The present invention relates to a rotor cover assembly in a gas turbine engine, and more particularly, to a rotor cover assembly that limits leakage between a hot gas path and one or more cooled areas proximate to the rotor cover assembly.
In gas turbine engines, compressed air discharged from a compressor section and fuel introduced from a source of fuel are mixed together and burned in a combustion section, creating combustion products defining hot working gases. The working gases are directed through a hot gas path in a turbine section, where they expand to provide rotation of a turbine rotor. The turbine rotor may be linked to an electric generator, wherein the rotation of the turbine rotor can be used to produce electricity in the generator.
In view of high pressure ratios and high engine firing temperatures implemented in modern engines, it is important to limit leakage between the working gases in the hot gas path and cooling fluid in cooled areas in the engine to maximize performance and efficiency of the engine.
In accordance with a first aspect of the present invention, a cover assembly disposed about a rotor in a gas turbine engine is provided. The cover assembly comprises a first cover, a second cover, and securing structure. The first cover is disposed about the rotor and comprises a forward end and an opposed aft end. The first cover is associated with a case mounting structure that is fixed to an engine casing. The second cover is disposed about the rotor and comprises a forward end and an opposed aft end. At least a portion of the first cover is disposed radially outwardly from the second cover. The securing structure couples the first cover to the second cover and permits relative radial movement between the first and second covers.
The cover assembly may further comprise a flow directing duct adapted to alter a direction of working gases flowing between a combustor section of the engine and a turbine section of the engine.
The flow directing duct may be coupled to the first and second covers, and the first cover may be movable radially independently of the second cover and the flow directing duct.
The first cover, second cover, and flow directing duct may be movable axially substantially together.
The flow directing duct may be mounted to a vane carrier structure such that the flow directing duct is movable radially independently of the vane carrier structure and is movable axially with the vane carrier structure, the vane carrier structure mounted to the engine casing.
The securing structure may comprise a plurality of bolts, wherein a plurality of apertures are formed in a radially extending section of the first cover that receive the bolts. The apertures may comprise radial openings that are larger than diameters of corresponding ones of the bolts such that the first cover is permitted to move radially with respect to the bolts.
A first gap may be formed between the first and second covers, the first gap receiving cooling air that cools the first and second covers.
The second cover may include at least one bore formed therein, at least a portion of the cooling air in the first gap passes through the bore into a second gap between the second cover and the rotor, the cooling air in the second gap cools the second cover and the rotor.
The cover assembly may further comprise at least one sealing structure between the first and second covers, the sealing structure limiting leakage between the first gap and a hot gas path associated with the turbine section of the engine.
In accordance with a second aspect of the present invention, a cover assembly disposed about a rotor in a gas turbine engine is provided. The cover assembly comprises a first cover disposed about the rotor and comprising a forward end and an opposed aft end. The first cover is associated with a case mounting structure that is mounted to an engine casing. The cover assembly further comprises coupling structure that couples the first cover to the case mounting structure such that the first cover can move axially independently from the case mounting structure and the engine casing.
In accordance with a third aspect of the present invention, a cover assembly associated with a rotor in a gas turbine engine is provided. The cover assembly comprises an outer cover, an inner cover, a flow directing duct, securing structure, and coupling structure. The outer cover is disposed about the rotor and comprises a forward end and an opposed aft end. The outer cover is associated with a case mounting structure that is mounted to an engine casing. The inner cover is disposed about the rotor and comprises a forward end and an opposed aft end, at least a portion of the outer cover disposed radially outwardly from the inner cover. The flow directing duct is adapted to alter a direction of working gases flowing between a combustion section of the engine and a turbine section of the engine. The securing structure couples the first cover, the second cover, and the flow directing duct together. The securing structure permits the outer cover to move radially independently of the inner cover and the flow directing duct. The coupling structure couples the outer cover to the case mounting structure such that the cover assembly can move axially relative to the case mounting structure and the engine casing.
While the specification concludes with claims particularly pointing out and distinctly claiming the present invention, it is believed that the present invention will be better understood from the following description in conjunction with the accompanying Drawing Figures, in which like reference numerals identify like elements, and wherein:
In the following detailed description of the preferred embodiments, reference is made to the accompanying drawings that form a part hereof, and in which is shown by way of illustration, and not by way of limitation, specific preferred embodiments in which the invention may be practiced. It is to be understood that other embodiments may be utilized and that changes may be made without departing from the spirit and scope of the present invention.
Referring now to
In the illustrated embodiment, the combustor section 110 comprises a plurality of combustion apparatuses 200 and a duct structure 300. Each combustion apparatus 200, see
The duct structure 300 receives the first combustion products and any remaining fuel and air from the tubes 230 of the combustion apparatuses 200, allows any remaining fuel and air to combust to generate second combustion products, accelerates the first and second combustion products and outputs the first and second combustion products to the first row blade assembly 132A to effect rotation of the rotor 132, see
As noted above, the duct structure 300 comprises the duct or flow directing duct 310. The flow directing duct 310 comprises the first annular inner cavity 312A and a second inner cavity 312B, which communicate with one another, see
A similar combustor section comprising a plurality of combustion apparatuses and a duct structure is described in commonly owned U.S. patent application Ser. No. 11/498,479, entitled “At Least One Combustion Apparatus and Duct Structure for a Gas Turbine Engine,” by Robert Bland and filed on Aug. 3, 2006, the entire disclosure of which is hereby incorporated by reference herein. In an alternate embodiment, the combustor section may comprise a plurality of combustion apparatuses and a duct structure, such as that described in commonly owned U.S. patent application Ser. No. 12/420,149, entitled “Modular Transvane Assembly,” by Jody W. Wilson et al. and filed on Apr. 8, 2009, the entire disclosure of which is hereby incorporated by reference herein.
Referring now to
The rotor cover assembly 20 comprises in the illustrated embodiment an outer cover 27 and an inner cover 28, both of which are formed from a heat tolerant material, such as, for example, carbon steel, and both of which comprise generally cylindrical members that surround the rotor 132. The outer cover 27 illustrated in
A forward end 34 of the outer cover first portion 30 is suspended radially outwardly from the rotor 132 and may include a seal assembly (not shown) to create a substantially fluid tight seal with the rotor 132. The seal assembly may include a rotating structure, such as a knife edge seal, coupled to the rotor 132 and/or a non-rotating seal structure, such as a honeycomb seal, coupled to the forward end 34 of the outer cover first portion 30. The first portion 30 and an engine casing 36 form a compressor section exit diffuser 38 that slows air that is compressed in the compressor section 120 to a desired speed before the compressed air reaches the combustion apparatuses 200, by providing an increased volume for the flow of air on its way to the combustion apparatuses 200. That is, as the compressed air flows axially from the compressor section 120 toward the combustion apparatuses 200, i.e., from the forward end 34 of the outer cover first portion 30 toward an aft end 40 of the outer cover first portion 30, a volume of the compressor section exit diffuser 38 increases, thus slowing the air down. Once through the exit diffuser 38, the air enters a combustor plenum 39 and thereafter enters each of the combustion apparatuses 200 through a respective annular opening 41 associated with each the combustion apparatus 200, although other suitable structure may be included for introducing the air into the combustion apparatuses 202, e.g., apertures formed in a flow sleeve (not shown) of each of the combustion apparatuses 200. It is noted that the compressed air flowing to the combustor section 110 may have a temperature of about 600° F.
The aft end 40 of the outer cover first portion 30 is fixed to a forward end 42 of the outer cover second portion 32, e.g., via bolts 44. The aft end 40 is also associated with a case mounting structure 46, which mounting structure 46 comprises a generally cylindrical base 46A and a plurality of arm members 45 integral with and extending radially outwardly from the generally cylindrical base 46A. The case mounting structure 46 is fixed to the engine casing 36 via the arm members 45. A plurality of coupling structures 48 are used to couple the outer cover first portion aft end 40 to the generally cylindrical base portion 46A of the case mounting structure 46. The coupling structures 48 permit an amount of relative axial movement between the outer cover 27 and the case mounting structure 46, yet prevent radial and circumferential movement between the outer cover 27 and the case mounting structure 46. For example, the coupling structures 48 may be codder pins that provide radial and circumferential support while allowing relative axial movement between the outer cover 27 and the case mounting structure 46. It is noted that other suitable coupling structures may be employed so long as the outer cover 27 is sufficiently supported about the rotor 132 while permitting an amount of axial movement between the outer cover 27 and the case mounting structure 46.
As shown in
As shown in
A plurality of cooling air feed tubes 55 (one shown in
As shown in
Referring to
A plurality of bores 69 formed in the inner cover 28 allow the cooling air located in the first gap G1, i.e., from the cooling air feed tubes 55, to flow into a second gap G2 formed between the inner cover 28 and the rotor 132. The cooling air in the second gap G2 effects cooling of the inner cover 28 and the rotor 132.
A first radially inwardly extending portion 70 of a forward end 71 of the inner cover axially extending section 65B comes into close proximity with the rotor 132. The close proximity between the first portion 70 and the rotor 132 defines a third gap G3, which gap G3 defines a first flow path FP1, an axially upstream flow path, having a reduced radial dimension. A small amount of cooling air in the second gap G2 is permitted to flow through the first flow path FP1 and into a fourth gap G4, which fourth gap G4 is formed between the outer cover first portion 30 and the rotor 132. The cooling air in the fourth gap G4 effects cooling of a radially inner side 75 of the outer cover first portion 30 and the rotor 132. However, a radially outer side 77 of the outer cover first portion 30 is exposed to the compressed air flowing through the exit diffuser 38 on its way to the combustion apparatuses 200, which compressed air is considerably hotter than the cooling air provided by the cooling air feed tubes 55, i.e., about 600° F. for the compressed air vs. between about 250-350° F. for the cooling air.
As shown in
Rotor cooling air inlet apertures 80 define inlets for cooling air from the second gap G2 to pass into one or more passageways 81 formed in the rotor 132, see
Referring to
As most clearly shown in
As shown in
Referring to
The arrangement of the bolts 64 within the respective apertures 62, 82, 113 formed in the radially extending section 60 of the outer cover second portion 32, the radially outwardly extending section 65A of the inner cover 28 and the flow directing duct support structure 68, respectively, permits relative radial movement of the outer cover 27 with respect to the bolts 64, the inner cover 28 and the flow directing duct support structure 68. That is, since the radial openings RO1 of the apertures 62 are oversized, the outer cover 27 is permitted to move radially inwardly and radially outwardly a small amount with respect to the bolts 64, the inner cover 28, and the flow directing duct support structure 68.
Referring to
A protuberance 124 extends axially downstream from the second aft surface 121, i.e., to an axial location between the axial locations of the first and second aft surfaces 118, 121. The protuberance 124 may extend to substantially the same axial location as that of the first aft surface 118, as shown in
The lip 111 of the flow directing duct 310 is positioned in the slot 122 between the vane carrier structure 112 and the second aft surface 121, such that notches 126, see
During operation of the engine, the hot working gases from the combustion apparatuses 200 are directed into and through the flow directing duct 310 and are released at the annular exit 318, i.e., between the inner and outer edges 68, 108, into the turbine section 130. The working gases flow through the hot gas path HG where the working gases are expanded and cause the first, second, third and fourth axially spaced apart row blade assemblies 132A-132D to effect rotation of the rotor 132. Due to temperature differentials between the compressor air, the hot working gases, the cooling air, etc., the temperatures of the components of the combustor section 110 can be quite different, thus creating different amounts of thermal expansion of the components.
For example, the radially outer surfaces 77, 50 of the first and second portions 30, 32 of the outer cover 27 are exposed to compressor air, which compressor air is substantially hotter than the cooling air from the cooling means, i.e., about 600° F. for the compressor air as opposed to between about 250-350° F. for the cooling air, as noted above. Thus, the outer cover 27 is substantially hotter than the inner cover 28, which is substantially surrounded by the cooling air in the first and second gaps G1, G2. The outer cover 27 therefore is believed to experience a larger amount of thermal expansion than the inner cover 28. Since the rotor 132 is maintained at relatively cooler temperatures, i.e., due to its exposure to the cooling air from the cooling air feed tubes 55 that flows from the first gap G1 into the second gap G2, the rotor 132 is believed to experience a reduced amount of thermal expansion, as compared to a situation wherein the rotor 132 is not exposed to cooling air but is exposed to the air exiting the compressor section 120. Thus, the inner cover 28 is a better thermal match with the rotor 132 than the outer cover 27, i.e., the temperature of the rotor 132 is closer to the temperature of the inner cover 28 than to the temperature of the outer cover 27 as a result of the rotor 132 and the inner cover 28 being exposed to the cooling air. The close thermal match between the inner cover 28 and the rotor 132 allows for close placement of the inner cover 28 to the rotor 132 with a low risk of contact therebetween, which contact is desired to be avoided. Thus, an amount of cooling air that flows through the second flow path FP2 into the cooling cavity 78 is reduced, therefore reducing the amount of cooling air that can leak into the hot gas path HG from the cooling cavity 78.
Additionally, since the inner cover 28 is substantially entirely surrounded by cooling air from the cooling air feed tubes 55, i.e., from the cooling air in the first and second gaps G1, G2, the inner cover 28 is permitted to be located in close proximity to the blade angel wings 101. Specifically, since thermal expansion of the inner cover 28 is reduced, radial thermal growth of the inner cover 28 relative the angel wings 101 is reduced, such that contact therebetween is substantially prevented even when the inner cover 28 is located close to the angel wings 101. The placement of the inner cover 28 close to the blade angel wings 101 reduces the distance therebetween, which reduces leakage between the hot gas path HG and the cooling cavity 78.
As mentioned above, the relatively larger size of the radial openings RO1 of the apertures 62 formed in the radially extending section 60 of the outer cover second portion 32 permit the outer cover 27 to move radially independently from the bolts 64, the inner cover 28, and the flow directing duct 310. Specifically, the outer cover 27 is permitted to move radially inwardly and outwardly relative to the bolts 64, the inner cover 28, and the flow directing duct 310, until the bolts 64 contact the respective lower or upper surfaces defining the apertures 62 in the outer cover second portion 32. Accordingly, the size of the radial openings RO1 of the apertures 62 dictates how far the outer cover 27 is permitted to move radially relative to the bolts 64, the inner cover 28, and the flow directing duct 310. This relative radial movement is believed to accommodate differences in radial thermal expansion between the outer and inner covers 27, 28, i.e., the outer cover 27 will expand radially a greater amount than the inner cover 28 due to the outer cover 27 being exposed to hot working gases, which will allow the inner cover 28 to be located more closely to the rotor 132 while reducing the risk of contact therebetween.
It is noted that, since the radially outwardly extending section 60 of the outer cover 27 is axially coupled to the radially outwardly extending section 65A of the inner cover 28, i.e., via the bolts 64, the radially outwardly extending sections 60, 65A of respective covers 27, 28 do not move axially with respect to one another. However, as noted above, the notch 47A defined by the outer cover first and second portions 30, 32 may be slightly oversized in the axial direction with respect to the radial rib 47 of the inner cover 27. Thus, the outer cover 27 may be permitted to move axially slightly with respect to the forward end 71 of the inner cover 28, i.e., to accommodate differences in thermal growth between the outer and inner covers 27, 28.
Additionally, the attachment of the rotor cover assembly 20 to the case mounting structure 46 permits the cover assembly 20 and the mounting structure 46 to move axially relative to one another a small amount. Specifically, the connection of the outer cover 27 to the case mounting structure using the coupling structures 48, in combination with the positioning of the casing mounting structure cylindrical base 46A within the recess 49 defined by the outer cover first and second portions 30 and 32, allows the cover assembly 20 to displace axially with respect to the case mounting structure 46, and thus move axially independently from the engine casing 36. However, the disposal of the case mounting structure support members 52 in the axially oversized apertures 54 in the outer cover second portion 32 permits the outer cover second portion 32 and the case mounting structure 46 to move axially relative to one another a small amount before the outer cover second portion 32 and the support members 52 engage one another and, hence, prevents the cover assembly 20 from axially sliding too far relative to the case mounting structure 46 and the engine casing 36 or vice versa. The ability of the cover assembly 20 and the engine casing 36 to move axially relative to one another allows the cover assembly 20, i.e., the inner cover 28, to be closely located to the angel wings 101 without a high risk of contact therebetween, which reduces leakage between the hot gas path HG and the cooling cavity 78. Specifically, since the engine casing 36 is free to move axially with respect to the cover assembly 20 a small amount and vice versa, thermal expansion of the engine casing 36 will not cause a corresponding axial movement of the cover assembly 20 toward the first row of blades 79.
Moreover, the attachment of the lip 111 of the flow directing duct 310 to the vane carrier structure 112 facilitated by the mounting structures 114 permits the cover assembly 20 to move axially and circumferentially with the vane carrier structure 112, while allowing the cover assembly 20 to move radially independently from the vane carrier structure 112. Specifically, the lip 111 may slide radially on the second aft surface 121, but is axially held in place by the second aft surface 121 and the vane carrier structure 112 within the slot 122, and circumferentially held by the insertion of the protuberances 124 into the lip notches 126. This relative radial movement is believed to accommodate differences in thermal expansion between the vane carrier structure/engine casing and the cover assembly 20, which will allow the inner cover 28 to be located more closely to the rotor 132 while reducing the risk of contact therebetween, as the cover assembly 20 is permitted to move radially a small amount relative to the vane carrier structure/engine casing at the connection of the flow directing duct 310 to the vane carrier structure 112.
It is understood that traditional transition ducts and separate first vane members can be used in the place of the flow directing duct 310 without departing from the spirit and scope of the invention. Specifically, if traditional transition ducts and separate first vane members are used in the place of the flow directing duct 310, the separate first vane members would be affixed to the outer and inner covers 27, 28, i.e., via the bolts 64, in the place of the flow directing duct 310. The separate first vane members would also be supported by the vane carrier 112, i.e., via the mounting structures 114, in the place of the flow directing duct 310. During operation, the transition ducts would discharge the working gases from the respective combustion apparatuses 200 substantially axially toward the separate first vane members, which separate first vane members would alter the direction of the working gases in a traditional manner. The remaining structures described herein remain the same.
While particular embodiments of the present invention have been illustrated and described, it would be obvious to those skilled in the art that various other changes and modifications can be made without departing from the spirit and scope of the invention. It is therefore intended to cover in the appended claims all such changes and modifications that are within the scope of this invention.
