Source: http://patents.com/us-10001028.html
Timestamp: 2019-03-19 07:47:45
Document Index: 737084133

Matched Legal Cases: ['Application No. 201380021474', 'Application No. 201280065406', 'Application No. 2014540037', 'Application No. 2014540037', 'Application No. 2015507242', 'Application No. 2009', 'Application No. 2014', 'Application No. 2014', 'Application No. 2015']

US Patent # 1,000,1028. Dual spring bearing support housing - Patents.com
United States Patent 10,001,028
Ganiger , et al. June 19, 2018
A bearing support housing for a gas turbine engine includes: an annular mounting flange; a first bearing cage including: an annular first bearing support ring; and an annular array of axially-extending first spring arms interconnecting the first bearing support ring and the mounting flange; and a second bearing cage including: an annular second bearing support ring; and an annular array of axially-extending second spring arms interconnecting the second bearing support ring and the mounting flange, the second spring arms defining spaces therebetween. The first spring arms are received between the second spring arms, and the bearing cages are sized so as to permit independent flexing motion of the first and second spring arms.
Ganiger; Ravindra Shankar (Bangalore, IN), Drummond; Stephanie Frances (Cambridge, MA), Schneider; Daryl Scott (Cincinnati, OH)
Ganiger; Ravindra Shankar
Drummond; Stephanie Frances
Schneider; Daryl Scott
Family ID: 49380287
13/453,837
US 20130280063 A1 Oct 24, 2013
Current CPC Class: F16C 19/54 (20130101); F16C 35/042 (20130101); F01D 25/16 (20130101); F01D 25/164 (20130101); F02C 7/06 (20130101); F16C 27/04 (20130101); F05D 2250/37 (20130101); F05D 2230/64 (20130101); F05D 2250/312 (20130101); F05D 2250/36 (20130101); F16C 2360/23 (20130101)
Current International Class: F01D 25/16 (20060101); F16C 35/04 (20060101); F16C 19/54 (20060101); F16C 27/04 (20060101); F02C 7/06 (20060101)
Field of Search: ;415/229
2521638 September 1950 Magnus
3011840 December 1961 Littleford
3133693 May 1964 Matthew
3325088 June 1967 Storer et al.
3536369 October 1970 Ainsworth et al.
3703081 November 1972 Krebs et al.
3901557 August 1975 Daniels
4084861 April 1978 Greenberg et al.
4186975 February 1980 Frommlet et al.
4201426 May 1980 Brozenske et al.
4245951 January 1981 Minnick
4289360 September 1981 Zirin
4304522 December 1981 Newland
4322117 March 1982 Briggs
4451110 May 1984 Forestier et al.
4652219 March 1987 McEachern, Jr. et al.
4676667 June 1987 Komatsu et al.
4693616 September 1987 Rohra et al.
4981415 January 1991 Marmol et al.
5052828 October 1991 Ciokajlo et al.
5088840 February 1992 Radtke
5201844 April 1993 Greenwood et al.
5237817 August 1993 Bornemisza
5619850 April 1997 Palmer et al.
6240719 June 2001 Vondrell et al.
6338578 January 2002 Adde et al.
6402469 June 2002 Kastl et al.
6413046 July 2002 Penn et al.
6439772 August 2002 Ommundson et al.
6443698 September 2002 Corattiyil et al.
6447248 September 2002 Kastl et al.
6540483 April 2003 Allmon et al.
6679045 January 2004 Karafillis et al.
6698936 March 2004 Dardelet et al.
6821083 November 2004 Lathrop et al.
6846158 January 2005 Hull
7322181 January 2008 Lapergue et al.
7384199 June 2008 Allmon et al.
7634913 December 2009 Singh et al.
8182156 May 2012 Kinnaird et al.
2003/0210979 November 2003 Doerflein et al.
2004/0047731 March 2004 Hull
2005/0100258 May 2005 Brossier et al.
2006/0045404 March 2006 Allmon et al.
2006/0083449 April 2006 Laurant et al.
2006/0153483 July 2006 Bridges et al.
2007/0104403 May 2007 Kawamura et al.
2008/0063333 March 2008 Bruno et al.
2008/0131277 June 2008 Shatz et al.
2008/0152483 June 2008 Godleski
2009/0214147 August 2009 Duong
2010/0027930 February 2010 Kinnaird et al.
2010/0054650 March 2010 Endres et al.
2011/0150372 June 2011 Care et al.
2012/0189429 July 2012 Witlicki
2012/0213629 August 2012 Rouesne
2012/0263578 October 2012 Davis et al.
2012/0321447 December 2012 Dijoud et al.
1451077 Oct 2003 CN
101014753 Aug 2007 CN
102004040340 Feb 2006 DE
1626188 Feb 2006 EP
2149681 Feb 2010 EP
2951232 Apr 2011 FR
2326679 Dec 1998 GB
4919209 Feb 1974 JP
54151712 Nov 1979 JP
57186616 Nov 1982 JP
2002525519 Aug 2002 JP
2004263854 Sep 2004 JP
2005240799 Sep 2005 JP
2009270612 Nov 2009 JP
0169047 Sep 2001 WO
US. Appl. No. 13/286,792, filed Nov. 1, 2011. cited by applicant .
U.S. Appl. No. 13/453,796, filed Apr. 23, 2012. cited by applicant .
PCT Search Report and Written Opinion dated Mar. 6, 2014 issued in connection with corresponding PCT Patent Application No. PCT/US2013/037509. cited by applicant .
Unoffcial translation of JP Office Action dated Nov. 24, 2015 in relation to corresponding JP Application 2015-507242. cited by applicant .
Unofficial English translation of Office Action issued in connection with corresponding CN Application No. 201380021474.8 dated May 28, 2013. cited by applicant .
U.S. Non-Final Office Action issued in connection with Related U.S. Appl. No. 12/183,489 dated Sep. 14 2011. cited by applicant .
PCT Search Report and Written Opinion issued in connection with Related PCT Application No. PCT/US2012/062781 dated Feb. 14, 2013. cited by applicant .
U.S. Non-Final Office Action issued in connection with Related U.S. Appl. No. 13/286,792 dated May 23, 2013. cited by applicant .
Chinese Office Action issued in connection with Related CN Application No. 201280065406.7 dated Feb. 28, 2015. cited by applicant .
Unofficial English Translation of Japanese Office Action issued in connection with Related JP Application No. 2014540037 dated May 12, 2015. cited by applicant .
Unofficial English Translation of Japanese Notice of Allowance issued in connection with Related JP Application No. 2014540037 dated Oct. 13, 2015. cited by applicant .
Unofficial English Translation of Japanese Office Action issued in connection with corresponding JP Application No. 2015507242 dated Nov. 1, 2016. cited by applicant .
U.S. Appl. No. 13/286,792, filed Nov. 1, 2011, Kevin Michael Do et al. cited by applicant .
U.S. Appl. No. 12/1834,89, filed Jul. 31, 2008, Ray Harris Kinnaird et al. cited by applicant .
U.S. Appl. No. 12/183,489, filed Jul. 31, 2008, Kinnaird et al. cited by applicant .
U.S. Appl. No. 13/286,792, filed Nov. 1, 2011, Do et al. cited by applicant .
U.S. Appl. No. 13/453,796, filed Apr. 23, 2012, Do et al. cited by applicant .
Japanese Search Report issued in connection with related JP Application No. 2009-172611 dated Jul. 12, 2013. cited by applicant .
Non-Final Rejection towards related U.S. Appl. No. 13/453,796 dated Sep. 25, 2013. cited by applicant .
Notice of Allowance issued in connection with related JP Application No. 2014-540040 dated Nov. 4, 2015. cited by applicant .
Japanese Search Report issued in connection with related JP Application No. 2014-540040 dated May 15, 2015. cited by applicant .
Japanese Search Report issued in connection with related JP Application No. 2015-507242 dated Nov. 13, 2015. cited by applicant.
1. A monolithic bearing support housing for a gas turbine engine, comprising: a singular annular mounting flange; a first bearing cage comprising: an annular first bearing support ring; and an annular array of axially-extending first spring arms interconnecting the first bearing support ring and the mounting flange; and a second bearing cage comprising: an annular second bearing support ring; and an annular array of axially-extending second spring arms interconnecting the second bearing support ring and the mounting flange, the second spring arms defining spaces therebetween; wherein the first bearing support ring extends axially and is disposed parallel to the annular array of first spring arms and located radially inside the annular array of first spring arms, and wherein forward and aft axial ends of the first bearing support ring lie within forward and aft axial ends of the annular array of first spring arms, and the first spring arms are received between the second spring arms, and the bearing cages are sized so as to permit independent flexing motion of the first and second spring arms.
2. The bearing support housing of claim 1 wherein each of the first and second spring arms extends axially from an aft face of the mounting flange.
3. The bearing support housing of claim 1 wherein each of the first spring arms includes: an axially-extending portion joining the mounting flange; and a radially-inwardly-extending portion joining the first bearing support ring.
4. The bearing support housing of claim 3 wherein: each of the second spring arms includes: an axially-extending portion joining the mounting flange; and a radially-inwardly-extending portion joining the second bearing support ring; and wherein an axial gap is defined between the first bearing support ring and the radially-inwardly-extending portions of the second spring arms.
5. The bearing support housing of claim 4 wherein the second bearing support ring extends axially away from the second spring arms.
6. The bearing support housing of claim 1 wherein the mounting flange has a plurality of mounting holes formed therethrough.
7. The bearing support housing of claim 1 wherein at least one of the bearing support rings includes a cylindrical inner surface.
8. The bearing support housing of claim 1 wherein at least one of the bearing support rings includes a bearing stop lip.
9. The bearing support housing of claim 1 wherein the first and second spring arms are arranged such that a first gap between each first spring arm and the adjacent spring arm on one side is less than a second gap between the same one of the first spring arms and the adjacent spring arm on the other side.
10. A monolithic bearing assembly for a gas turbine engine, comprising: a singular annular mounting flange secured to a stationary member of the engine; a first bearing cage comprising: an annular first bearing support ring; and an annular array of axially-extending first spring arms interconnecting the first bearing support ring and the mounting flange; a rolling-element first bearing mounted in the first bearing support ring; a second bearing cage comprising: an annular second bearing support ring; and an annular array of axially-extending second spring arms interconnecting the second bearing support ring and the mounting flange, the second spring arms defining spaces therebetween; a rolling-element second bearing mounted in the second bearing support ring; and a shaft mounted in the first and second bearings; wherein the first bearing support ring extends axially and is disposed parallel to the annular array of first spring arms and located radially inside the annular array of first spring arms, and wherein forward and aft axial ends of the first bearing support ring lie within forward and aft axial ends of the annular array of first spring arms, and the bearing cages are sized so as to permit independent flexing motion of the first and second spring arms.
11. The bearing assembly housing of claim 10 wherein each of the first and second spring arms extends axially from an aft face of the mounting flange.
12. The bearing assembly of claim 10 wherein each of the first spring arms includes: an axially-extending portion joining the mounting flange; and a radially-inwardly-extending portion joining the first bearing support ring.
13. The bearing assembly of claim 12 wherein: each of the second spring arms includes: an axially-extending portion joining the mounting flange; and a radially-inwardly-extending portion joining the second bearing support ring; and wherein an axial gap is defined between the first bearing support ring and the radially-inwardly-extending portions of the second spring arms.
14. The bearing assembly of claim 13 wherein the second bearing support ring extends axially away from the second spring arms.
15. The bearing assembly of claim 13 wherein the generally axially-extending portion of the second bearing support ring includes a cylindrical outer surface.
16. The bearing assembly of claim 15 further comprising a stationary damper housing surrounding the second bearing support ring; wherein the damper housing and the second bearing support ring cooperatively define an oil film damper.
17. The bearing assembly of claim 10 wherein the mounting flange has a plurality of mounting holes formed therethrough.
18. The bearing assembly of claim 17 wherein the mounting flange is secured to the stationary structure by a plurality of fasteners passing through mounting holes formed in the mounting flange.
19. The bearing assembly of claim 10 wherein at least one of the bearing support rings includes a cylindrical inner surface.
20. The bearing assembly of claim 10 wherein at least one of the bearing support rings includes a bearing stop lip.
21. The bearing assembly of claim 10 wherein the first and second spring arms are arranged such that a first gap between each first spring arm and the adjacent spring arm on one side is less than a second gap between the same one of the first spring arms and the adjacent spring arm on the other side.
This invention relates generally to gas turbine engine bearings and more particularly to mounting arrangements for such bearings.
It is known to support bearings, such as the large rolling-element bearings used in gas turbine engines, using spring centering cages. The spring constant of such cages can be manipulated to provide a desired stiffness and consequently affect the dynamics and vibration modes of the engine. Particularly in large aircraft turbofan engines, it has been demonstrated that engine dynamics will suffer significantly if such cages are not used.
Many gas turbine engines have at least one sump that includes two or more rolling element bearings positioned in close proximity to each other. These sumps have limited axial and radial space available to be used for bearings, spring cages, intermediate gearbox mounting, damper housings, air and oil seals, air pressurization channels, and oil transport between parts of the sump. The axial and radial space needed for an individual spring centering cage for each bearing, which is greater than required for a conventional stiff bearing mounting, is inconsistent with the need to keep the engine as small and light as possible.
Accordingly, there is a need for a bearing support adapted to mount multiple rolling element bearings in a confined space.
This need is addressed by the present invention, which provides an integral component incorporating two spring cages that are nested within each other, so as to operate independently, while only occupying the space normally required for a single spring bearing cage.
According to one aspect of the invention, a bearing support housing for a gas turbine engine, includes: an annular mounting flange; a first bearing cage including: an annular first bearing support ring; an annular array of axially-extending first spring arms interconnecting the first bearing support ring and the mounting flange; and a second bearing cage including: an annular second bearing support ring; and an annular array of axially-extending second spring arms interconnecting the second bearing support ring and the mounting flange, the second spring arms defining spaces therebetween; wherein the first spring arms are received between the second spring arms, and the bearing cages are sized so as to permit independent flexing motion of the first and second spring arms
According to another aspect of the invention, a bearing assembly for a gas turbine engine includes: an annular mounting flange secured to a stationary member of the engine; a first bearing cage including: an annular first bearing support ring; and an annular array of axially-extending first spring arms interconnecting the first bearing support ring and the mounting flange; a rolling-element first bearing mounted in the first bearing support ring; a second bearing cage including: an annular second bearing support ring; and an annular array of axially-extending second spring arms interconnecting the second bearing support ring and the mounting flange, the second spring arms defining spaces therebetween; a rolling-element second bearing mounted in the second bearing support ring; and a shaft mounted in the first and second bearings; wherein the first spring arms are received between the second spring arms, and the bearing cages are sized so as to permit independent flexing motion of the first and second spring arms.
FIG. 1 is a half-cross-sectional view of a gas turbine engine incorporating nested bearing spring cages constructed according to an aspect of the present invention;
FIG. 2 is an enlarged view of a bearing compartment of the gas turbine engine of FIG. 1;
FIG. 3 is a perspective view of a bearing support housing shown in FIG. 2;
FIG. 4 is a sectional perspective view of a portion of the bearing support housing shown in FIG. 3;
FIG. 5 is an enlarged view of a bearing compartment, showing an alternative bearing support housing;
FIG. 6 is a sectional view of a portion of the bearing support housing shown in FIG. 5; and
FIG. 7 is a perspective view of the bearing support housing shown in FIG. 5.
Referring to the drawings wherein identical reference numerals denote the same elements throughout the various views, FIG. 1 depicts a gas turbine engine 10. The engine 10 has a longitudinal axis 11 and includes a fan 12, a low pressure compressor or "booster" 14 and a low pressure turbine ("LPT") 16 collectively referred to as a "low pressure system". The LPT 16 drives the fan 12 and booster 14 through an inner shaft 18, also referred to as an "LP shaft". The engine 10 also includes a high pressure compressor ("HPC") 20, a combustor 22, and a high pressure turbine ("HPT") 24, collectively referred to as a "gas generator" or "core". The HPT 24 drives the HPC 20 through an outer shaft 26, also referred to as an "HP shaft". Together, the high and low pressure systems are operable in a known manner to generate a primary or core flow as well as a fan flow or bypass flow. While the illustrated engine 10 is a high-bypass turbofan engine, the principles described herein are equally applicable to turboprop, turbojet, and turboshaft engines, as well as turbine engines used for other vehicles or in stationary applications.
The inner and outer shafts 18 and 26 are mounted for rotation in several rolling-element bearings. The bearings are located in enclosed portions of the engine 10 referred to as "sumps".
FIG. 2 shows a portion of a sump of the engine 10 in more detail. The forward end of the outer shaft 26 is carried by a ball-type first bearing 32 and a roller-type second bearing 34 which in common nomenclature are referred to as the "#3B bearing" and the "#3R bearing", respectively. A static annular frame member referred to as a fan hub frame 36 surrounds the first and second bearings 32 and 34. The first and second bearings 32 and 34 are connected to the fan hub frame 36 by a bearing support housing 35. A stationary damper housing 42 with a cylindrical inner surface 44 surrounds the second bearing 34.
As best seen in FIGS. 3 and 4, the bearing support housing 35 is a single monolithic component incorporating first and second bearing cages 38 and 40. The first bearing cage 38 supports the first bearing 32, and the second bearing cage 40 supports the second bearing 34. The bearing support housing 35 includes a single annular, radially-extending mounting flange 46 including a plurality of mounting holes 48 which receive fasteners 49 (FIG. 2). The first bearing cage 38 comprises an annular, generally axially-extending first bearing support ring 50, and a plurality of first spring arms 52 interconnecting the mounting flange 46 and the bearing support ring 50. In this example the inner surface of the first bearing support ring 50 includes a bearing stop lip 56 and a plurality of holes 58 for receiving bolts 60 (FIG. 2) used to secure the first bearing 32. Each first spring arm 52 comprises a radially-outwardly extending portion 62 joining the aft end of the first bearing support ring 50, and an axially-extending portion 64 joining the mounting flange 46. The first bearing support ring 50 extends generally parallel to the axially-extending portions 62 of the first spring arms 52 and thus lies radially inside the ring of first spring arms 52. The number, shape, and dimensions of the first spring arms 52 may be modified to suit a particular application, in particular to achieve a desired stiffness of the first bearing cage 38. It is noted that the first spring arms 52 extend axially aft from the aft face 47 of the mounting flange 46. Because the relatively large surface area of the aft face 47 serves as a base for the first spring arms 52, there is significant design freedom to alter the individual cross-sectional shape and dimensions of the first spring arms 52.
The second bearing cage 40 is similar in construction to the first bearing cage 38. It comprises an annular second bearing support ring 66 and a plurality of second spring arms 68 interconnecting the mounting flange 46 and the second bearing support ring 66. The second bearing support ring 66 includes a generally axially-extending body with a cylindrical inner surface. The outer surface 74 of the second bearing support ring 66, in cooperation with the damper housing 42, forms a portion of an oil film damper 76 of a known type. In this example the inner surface of the second bearing support ring 66 defines a bearing stop lip 78. Each of the second spring arms 68 comprises a radially-outwardly extending portion 82 joining the forward end of the bearing support ring 66, and an axially-extending portion 86 joining the mounting flange 46. The number, shape, and dimensions of the spring arms 80 may be modified to suit a particular application, in particular to achieve a desired stiffness of the second bearing cage 40.
The first and second bearing cages 38 and 40 are sized such that the first bearing support ring 50 fits inside of and axially overlaps or "nests" within the second bearing cage 40. More specifically, the outside diameter over the first bearing support ring 50 is less than the inside diameter of the second spring arms 68 of the second bearing cage 40. Furthermore, the spaces between adjacent second spring arms 68 of the second bearing cage 40 are selected so that the first spring arms 52 of the first bearing cage 38 will fit between them, resulting in an interdigitated configuration. The inner and/or outer radii of the first spring arms 52 may be equal to the inner and/or outer radii of the second spring arms 68.
The bearing cages 38 and 40 may be preferentially "clocked" or angularly offset from a symmetrical orientation relative to each other. As seen in FIG. 3, the bearing cages 38 and 40 are offset such that a first gap "G1" between each first spring arm 52 and the adjacent second spring arm 68 on one side is less than a second gap "G2" between the same first spring arm 52 and the adjacent second spring arm 68 on the other side. This clocking is useful to provide space for the passage of oil lines or other similar structures (not shown), where equal gaps might provide insufficient clearance.
In operation, the spring arms of the first and second bearing cages 38 and 40 are free to move independently of one another, as required by flight loads and the dynamics of the first and second bearings 32 and 34. This allows the harmonic response of the bearings 32 and 34 to be controlled independently.
FIG. 5 shows a portion of a sump of an engine, similar to the engine 10, including an outer shaft 126, and incorporating an alternative bearing mounting arrangement. The forward end of the outer shaft 126 is carried by a ball-type first bearing 132 and a roller-type second bearing 134 which in common nomenclature are referred to as the "#3B bearing" and the "#3R bearing", respectively. A static annular frame member referred to as a fan hub frame 136 surrounds the first and second bearings 132 and 134. The first and second bearings 132 and 134 are connected to the fan hub frame 136 by a bearing support housing 135. A stationary damper housing 142 with a cylindrical inner surface 144 surrounds the second bearing 134.
As seen in FIGS. 6 and 7, the bearing support housing 135 is a single monolithic component incorporating first and second bearing cages 138 and 140. The first bearing cage 138 supports the first bearing 132, and the second bearing cage 140 supports the second bearing 134. The bearing support housing 135 includes a single annular, radially-extending mounting flange 146 including a plurality of mounting holes 148 which receive fasteners 149 (FIG. 5). The first bearing cage 138 comprises an annular, generally axially-extending first bearing support ring 150, and a plurality of first spring arms 152 interconnecting the mounting flange 146 and the first bearing support ring 150. In this example the inner surface of the first bearing support ring 150 has a bearing stop lip 156 and a plurality of holes 158 for receiving bolts 159 (FIG. 5) used to secure the first bearing 132. Each of the first spring arms 152 comprises a radially-outwardly extending portion 156 joining the aft end of the bearing support ring 150, and an axially-extending portion 160 joining the mounting flange 146. The number, shape, and dimensions of the first spring arms 152 may be modified to suit a particular application, in particular to achieve a desired stiffness of the first bearing cage 138.
The second bearing cage 140 is similar in construction to the first bearing cage 138 and comprises an annular second bearing support ring 166, and a plurality of second spring arms 168 interconnecting the mounting flange 146 and the second bearing support ring 166. The second bearing support ring 166 includes a generally axially-extending body 170 with a cylindrical inner surface 172. The outer surface 174 of the second bearing support ring 166, in cooperation with the damper housing 142, forms a portion of an oil film damper 176 of a known type. In this example the inner surface of the second bearing support ring 166 defines a bearing stop lip 178. Each of the second spring arms 168 comprises a radially-outwardly extending portion 182 joining the forward end of the second bearing support ring 166, and an axially-extending portion 186 joining the mounting flange 146. The number, shape, and dimensions of the second spring arms 168 may be modified to suit a particular application, in particular to achieve a desired stiffness of the second bearing cage 140. As with the bearing support housing 35 described above, there is wide flexibility to change the specific shape and dimensions of the first and second spring fingers 152 and 168.
The first and second bearing cages 138 and 140 are sized such that the first bearing support ring 150 fits inside of and axially overlaps or "nests" within the second bearing cage 140. More specifically, the outside diameter over the first bearing support ring 150 is less than the inside diameter of the second spring arms 168 of the second bearing cage 140. Furthermore, the spaces between adjacent second spring arms 168 of the second bearing cage 140 are selected so that the first spring arms 152 of the first bearing cage 138 will fit between them, resulting in an interdigitated configuration. The inner and/or outer radii of the first spring arms 152 may be equal to the inner and/or outer radii of the second spring arms 168.
The bearing cages 138 and 140 may be preferentially "clocked" or angularly offset from a symmetrical position relative to each other, as described above. In the example illustrated in FIGS. 5-7, the bearing cages 138 and 140 are clocked symmetrically to each other. One or more release slots 180 are formed at the forward end of the second bearing support ring 166 to provide for the passage of an oil line or nozzle (not shown).
The operation of the bearing support housing 135 is substantially identical to the operation of the bearing support housing 35 described above.
The bearing support housing configurations described above significantly reduce the axial and radial space required to fit multiple spring bearing cages into a bearing sump by nesting the cages together so they occupy the axial and radial space of one bearing cage. Engines which previously would have been unable to accommodate multiple spring bearing cages and dampers in the available sump space can now be arranged to include these features. While the nested bearing cage concept has been described with respect to a particular bearing arrangement, the concept may be used in any sump or location in the engine where it is desirable to provide multiple spring cages in a limited space. In addition to the overall product benefits of reduced part count (e.g. simplified logistics, handling, assembly), the single-piece design described herein also allows for the elimination of a joint between bearing cages, thus simplifying the flange configuration and reducing the overall stack-up.
The foregoing has described a bearing support housing for a gas turbine engine. While specific embodiments of the present invention have been described, it will be apparent to those skilled in the art that various modifications thereto can be made without departing from the spirit and scope of the invention. Accordingly, the foregoing description of the preferred embodiment of the invention and the best mode for practicing the invention are provided for the purpose of illustration only and not for the purpose of limitation.
Previous Patent US 10,001,027 | Next Patent US 10,001,029