Intermittent spigot joint for gas turbine engine casing connection

Abstract

A gas turbine engine casing apparatus includes annular first and second annular cases connected by a spigot joint. The spigot joint includes an annular projection of the first annular case fitted into an annular recess of the second annular case. A plurality of circumferentially spaced apart scallops are formed on one of surfaces of the annular projection or of the annular recess, and are located in selective circumferential locations adjacent respective enhanced stiff areas of the first and second annular cases.

Claims

1. A gas turbine engine casing assembly, comprising: a first annular case having a central axis and an annular seat at one of a front end and a rear end of the first annular case, the annular seat having an annular surface facing toward the central axis and a surface angled relative to the central axis; a second annular case connected coaxially to the first annular case and having an annular projection received in the annular seat, the annular projection having: a surface contacting the surface angled relative to the central axis of the annular seat, and an annular surface engaging the annular surface of the annular seat at a plurality of locations that are distributed circumferentially along the annular surface of the annular seat; and a plurality of scallops circumferentially spaced from one another and formed on at least one of the annular surface of the annular projection and the annular surface of the annular seat, a given scallop of the plurality of scallops being between a given pair of locations of the plurality of locations, wherein at least one of the scallops is located symmetrically about a radial central axis of a structural member projecting from the at least one of the annular surface of the annular projection and the annular surface of the annular seat.

2. The gas turbine engine casing assembly of claim 1, further comprising a plurality of fasteners extending through the annular seat and the annular projection at respective locations distributed circumferentially along the annular surface of the annular seat.

3. The gas turbine engine casing assembly of claim 2, wherein the annular surface of the annular seat and the annular surface of the annular projection are disposed radially outward of the plurality of fasteners.

4. The gas turbine engine casing assembly of claim 1, wherein the structural member is a strut.

5. The gas turbine engine casing assembly of claim 1, wherein at least one scallop of the plurality of scallops is arcuate.

6. The gas turbine engine casing assembly of claim 1, wherein the annular surface of the annular seat is disposed radially outward of the annular surface of the annular projection relative to the central axis.

7. The gas turbine engine casing assembly of claim 6, wherein the annular projection includes a second surface that faces toward the central axis and is disposed radially inward of the annular surface of the annular projection, and the annular seat includes a second surface that contacts the second surface of the annular projection.

Description

DESCRIPTION OF THE DRAWINGS

(1) Reference is now made to the accompanying figures in which:

(2) FIG. 1 is a partial schematic side cross-sectional view of a gas turbine engine as an example illustrating application of the described subject matter;

(3) FIG. 2 is an isometric view of an intermediate case which may be used in the gas turbine engine of FIG. 1;

(4) FIG. 3 is a partial isometric view of the intermediate case of FIG. 2, showing the block area 3 thereof in an enlarged scale;

(5) FIG. 4 is a partial cross-sectional view of the intermediate case taken along line 4-4 in FIG. 3, showing the circumferential dimension and location of a shallow groove in a spigot with respect to a radial central axis of a strut of the intermediate case; and

(6) FIG. 5 is a partial cross-sectional view of the intermediate case of FIG. 2 connected by a spigot joint to a compressor case.

(7) It will be noted that throughout the appended drawings, like features are identified by like reference numerals.

DETAILED DESCRIPTION

(8) FIG. 1 illustrates an exemplary turbofan gas turbine engine 10 which includes in serial flow communication about a longitudinal central axis 12, a fan assembly 13 having a plurality of circumferentially spaced fan blades 14, a high pressure compressor (HPC) assembly 16 having a plurality of circumferentially spaced compressor blades 50 and blades 51, a diffuser 18, a combustor 20, a high pressure turbine (HPT) 22 and a low pressure turbine (LPT) 24. LPT 24 is connected to the fan assembly 13 by a low pressure (LP) shaft 26, and HPT 22 is connected to the HPC assembly 16 by a high pressure (HP) shaft 28.

(9) It should be noted that the terms “axial”, “radial” and “circumferential” used for various components throughout the description and appended claims are defined with respect to the longitudinal central axis 12 of the engine.

(10) A generally cylindrical casing assembly 32 envelops the engine 10 and thereby defines a main flow path (indicated by arrows) 36 through a core of engine 10 and a bypass flow path (indicated by arrows) 37.

(11) Is should be noted that the terms “upstream”, “downstream”, “front” and “aft” are defined with respect to the direction of the air flow entering into and passing through the main flow path 36 of the engine 10.

(12) The casing assembly 32 according to one embodiment may include a generally cylindrical fan case 44, which houses the fan rotor assembly 13, a generally cylindrical intermediate case 46 downstream of the fan case 44 and a gas generator case 52 downstream of the intermediate case 46. The intermediate case 46 may include a bearing seat 58 for mounting an HP bearing 59 thereto. The cylindrical casing assembly 32 may further include a cylindrical bypass duct case 56 generally surrounding the gas generator case 52 and a cylindrical compressor shroud 48 which encircles blade tips of the HPC assembly 16. The cylindrical compressor shroud 48, gas generator case 52 and the bypass duct case 56 are located downstream of and are connected to the intermediate case 46.

(13) Referring to FIGS. 1 and 2, the intermediate case 46 according to one embodiment may include a number of cylindrical walls 41, 42, 43 and 45 which are co-axially positioned and radially spaced apart one from another. In a radially outward sequence the cylindrical wall 41 may be an inner hub of the intermediate case 46 to support the bearing seat 58, cylindrical walls 42 and 43 in combination may form at least part of an annular split configuration for dividing the bypass flow path 37 from the main flow path 36, and the cylindrical wall 45 may be an outer wall of the intermediate case 46 and may be connected to the bypass duct 56. The cylindrical walls 42 and 43 of the intermediate case 46 may be connected to the respective compressor shroud 48 and the gas generator case 52.

(14) The intermediate case 46 may further have a plurality of radially extending struts 40 which may each be configured as a hollow structure. The radially extending struts 40 may be circumferentially spaced apart one from another, each connecting or being integrated with the respective cylindrical walls 41, 42, 43, and 45 and thus in combination support all the cylindrical walls 41, 42, 43 and 45 in an integrated configuration to form the intermediate case 46.

(15) Referring to FIGS. 1-5, the cylindrical compressor shroud 48 may be connected to the cylindrical wall 42 of the intermediate case 46 for example by a spigot joint 60 (see FIG. 5). The spigot joint 60 according to one embodiment may include an annular projection 62 integrated with an aft end of the cylindrical wall 42 and may be tightly fitted in an annular recess 64 formed in a front end of the cylindrical compressor shroud 48. The annular projection 62 may have an outer-diameter surface 66 and an inner-diameter surface 68 facing away from each other and axially projecting from the aft end of the cylindrical wall 42. The annular recess 64 may have an outer-diameter surface 70 and an inner-diameter surface 72 which face each other and may axially extend into the front end of the cylindrical compressor shroud 48. It should be noted that outer-diameter surfaces 66 and 70 define a respective annular surface having a diameter greater than a diameter of a respective annular surface defined by inner-diameter surfaces 68, 72. The annular projection 62 may be received in the annular recess 64 such that the outer-diameter surfaces 66 and 70 mate with each other or the inner-diameter surfaces 68 and 72 mate with each other. A plurality of mounting holes 76 and 78 may be provided in the respective annular projection 62 on a radial end surface 77 and a front end (through a radial bottom surface 79 of the annular recess 64) of the cylindrical compressor shroud 48 to receive respective fasteners for securing a spigotted connection between the cylindrical compressor shroud 48 and the cylindrical wall 42 of the intermediate case 46, which forces the annular projection 62 to be fully inserted into the annular recess 64 until the radial end surface 77 of the annular projection 62 is in firm contact with the radial bottom surface 79 of the annular recess 64 in order to secure the spigotted connection between the cylindrical compressor shroud 48 and the intermediate case 46.

(16) A tight fit of the spigot joint 60 is required for concentricity control of the cylindrical wall 42 of the cylindrical intermediate case 46 and the cylindrical compressor shroud 48 for the purpose of blade tip clearance control of the HPC blades 50 with respect to the cylindrical compressor shroud 48. Nevertheless, during engine operation the spigot joint 60 may become excessively tight between the outer-diameter surfaces 66 and 70 due to different thermal expansion coefficients of the two mating parts. For example, the intermediate case 46 according to one embodiment may be made of magnesium and the compressor shroud 48 may be made of titanium which has a thermal expansion coefficient lower than the thermal expansion coefficient of magnesium. At a cold assembly condition according to this embodiment, the spigot joint 60 may be tight between the inner-diameter surfaces 68 and 72. However, under operating conditions such a thermal mismatch of the two mating parts of the spigot joint 60 may result in high compressive stresses developing in a plurality locally stiffer regions indicated by “A”, adjacent the respective struts 40. Such local high compressive stresses may cause an elevated risk of stress cracking.

(17) According to one embodiment, a plurality of circumferentially spaced intermittent scallops or shallow grooves 74 (see FIG. 3) may be machined or otherwise provided on, in this example, the outer diameter surface 66 of the annular projection 62 in locations circumferentially adjacent the respective struts 40 in order to reduce a local contact area between the annular projection 62 and the annular recess 64 in order to reduce the occurrence of an over-tight spigot fit during engine operation, potentially relieving some of the compressive stresses developed in the respective regions A.

(18) Alternatively, the scallops or shallow grooves 74 may be provided on the outer-diameter surface 70 of the annular recess 64. Alternatively, scallop the scallops or shallow grooves 74 may be provided on both surfaces 66 and 70.

(19) Optionally, the scallops or shallow grooves 74 may be circumferentially located symmetrically about a radial central axis 80 of the respective radially extending struts 40. Optionally, the scallops or shallow grooves 74 may be configured in an arc profile equal to or less than 20 degrees because the scallops or shallow grooves 74 are provided for locally reducing the presences of an over-tight spigot fit conditions in selected circumferential locations while maintaining concentricity control of the spigotted connection. As noted, the scallops or shallow grooves 74 are circumferentially intermittent, as the skilled reader will appreciate in light of this disclosure that a fully-annular groove may disadvantageously affect spigot fit, such as required for concentricity control of the spigotted connection. The scallops or shallow grooves 74 according to one embodiment may have a depth of 0.015 inches (0.37 mm) or less.

(20) The above-described subject matter may be applicable to spigotted connections between first and second annular engine cases of other types, not limited to the spigotted connection between an intermediate case and a compressor shroud. Furthermore, the plurality of circumferentially extending and spaced apart scallops or shallow grooves 74 may be formed on one of the outer-diameter surfaces 66, 70 or on one of the inner-diameter surfaces 68, 72, and may be located in selective circumferential locations adjacent respective enhanced stiff areas of two connected annular cases. Depending on the particular configuration of the cases, the enhanced stiff areas may be formed with bosses, discrete struts or supports, etc. wherein the local areas may be stiffer than surrounding areas.

(21) As a general example, the plurality of scallops or shallow grooves may be formed on the outer-diameter surface of the annular projection and/or of the annular recess when one of the connected cases which is integrated with the annular projection has a thermal expansion coefficient higher than a thermal expansion coefficient of the other of the connected case which defines the annular recess therein.

(22) As another general example, the plurality of scallops or shallow grooves may be formed on the inner-diameter face of the annular projection or of the annular recess when one of the annular cases which is integrated with the annular projection has a thermal expansion coefficient lower than a thermal expansion coefficient of the other of the connected cases which defines the annular recess.

(23) As a note, spigot connections also exist where there is not a second mating diameter (i.e. 68 and 72 do not exist) where the described subject matter could still apply.

(24) The above description is meant to be exemplary only, and one skilled in the art will recognize that changes may be made to the embodiments described without departing from the scope of the described subject matter. For example, in the above-described embodiments, it is a high pressure compressor (HPC) tip clearance control that is being preserved but the described subject matter is also applicable for low pressure compressor (LPC) tip clearance control. Modifications which fall within the scope of the described subject matter will be apparent to those skilled in the art, in light of a review of this disclosure, and such modifications are intended to fall within the appended claims.