WO1982000865A1 - Assemblage autonome de roulement a billes amorti - Google Patents

Assemblage autonome de roulement a billes amorti Download PDF

Info

Publication number
WO1982000865A1
WO1982000865A1 PCT/US1980/001115 US8001115W WO8200865A1 WO 1982000865 A1 WO1982000865 A1 WO 1982000865A1 US 8001115 W US8001115 W US 8001115W WO 8200865 A1 WO8200865 A1 WO 8200865A1
Authority
WO
WIPO (PCT)
Prior art keywords
outer race
bearing assembly
rolling elements
outboard
fluid
Prior art date
Application number
PCT/US1980/001115
Other languages
English (en)
Inventor
F Keske
Original Assignee
F Keske
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by F Keske filed Critical F Keske
Priority to PCT/US1980/001115 priority Critical patent/WO1982000865A1/fr
Publication of WO1982000865A1 publication Critical patent/WO1982000865A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
    • F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
    • F16C19/183—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C25/00—Bearings for exclusively rotary movement adjustable for wear or play
    • F16C25/06—Ball or roller bearings
    • F16C25/08—Ball or roller bearings self-adjusting
    • F16C25/083—Ball or roller bearings self-adjusting with resilient means acting axially on a race ring to preload the bearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
    • F16C27/04—Ball or roller bearings, e.g. with resilient rolling bodies
    • F16C27/045—Ball or roller bearings, e.g. with resilient rolling bodies with a fluid film, e.g. squeeze film damping
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/60—Raceways; Race rings divided or split, e.g. comprising two juxtaposed rings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—Special parts or details in view of lubrication
    • F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
    • F16C33/6659—Details of supply of the liquid to the bearing, e.g. passages or nozzles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2360/00—Engines or pumps
    • F16C2360/23—Gas turbine engines
    • F16C2360/24—Turbochargers

Definitions

  • the present invention pertains to rolling element bearing assemblies, and in particular to ball and bearing assemblies for high speed equipment.
  • Bearing assemblies for gas turbines, turbochargers, and other high speed equipment are often required to withstand high rotational speeds as well as high temperatures. Such bearings are subjected to shaft whip, radial play, or sub-harmonic orbiting.
  • Prior art devices include sleeve bearings and associated oil film provided therebetween, which films can damp some of the shaft whip.
  • sleeve bearings introduce undesirable friction losses into the assembly.
  • Preloaded ball bearing assemblies have been used in the past in such high speed equipment in order to eliminate shaft whip or orbital wobbling and axial play and to increase the accuracy of the machine. An example of such a device is reported in an article published by the Society of Automotive Engineers, Inc.
  • a rotor suspension system includes two sets of preloaded ball bearings which provide for the damping of shaft whip and additionally allow for thermal expansion caused by high speeds and hot exhaust gases without affecting the accuracy of the system.
  • this rotor suspension system does not always ensure that damping fluid is properly located between the bearings and housing thereof.
  • this device does not contain a convenient means for ensuring that lubricating fluid is metered to the ball bearings. Further, the system is not self-contained, and thus parts must be assembled separately within the high speed equipment. Such on- the-site assembly always introduces the possibilities of mlsassembly and contamination from the surrounding environment.
  • the present invention is directed to overcoming one or more of the problems as set forth above.
  • the assembly further Includes a common inner race, a common inboard outer race, and first and second outboard outer races.
  • a first retainer associates the first outboard outer race with the common Inboard outer race and includes a device for biasing the first outboard outer race toward the inboard outer race.
  • Also included Is a second retainer for associating the second outboard outer race with said common inboard outer race and including a device for biasing the second outboard outer race toward the inboard outer race.
  • the assembly further Includes means for introducing fluid between the housing and the first and second retainers.
  • the ball bearing assembly is self-contained as the first and second sets of balls share a common inner race which can be used to accommodate the high speed shaft. Further, the assembly provides for proper damping as it allows for the introducing of fluid between the housing and the first and second retainers. The biasing device ensures that the accuracy of the assembly is not affected by thermal expansion.
  • a ball bearing assembly comprises an inner race having a pair of inner grooves and an outer race having a pair of outer grooves. Further, means are provided for biasing at least one of the pairs of grooves, i.e. axially preloading the balls in their grooves.
  • a housing is located about and spaced from the outer race and means are provided for introducing fluid into the space between the housing and the outer races. Further, means are provided for bleeding fluid from between the housing and said outer retainer, which means is spaced from the introducing means .
  • the above another aspect of the invention provides for the damping of shaft whip which can be associated with such devices. Further, the bleeding means ensures that a proper amount of fluid is always available between the housing and the spring retainer for purposes of damping and lubricating.
  • a check valve Is provided for metering fluid Into a space between the outer race and the inner race. Such a check valve is convenient and efficient.
  • the present invention solves the problems of the prior art devices by providing a self-contained bearing assembly which is preloaded to allow for thermal expansion, which is damped to reduce shaft whip associated with such high speed shafts, and which provides a convenient and efficient check valve for allowing proper lubrication of the ball.
  • FIG. 1 is a cross-sectional view of an embodiment of the self-contained ball bearing assembly of the invention.
  • FIG. 2 is an enlarged cross-sectional view of one of the balls of FIG. 1, including portions of the inner race, the outer outboard race, and the outer inboard race.
  • the self-contained ball bearing assembly 10 of the invention is depicted in FIG. 1.
  • the assembly includes a first plurality of balls 12 spaced from a second plurality of balls 14.
  • a common inner race 16 defines a bore 18 adapted for receiving a spindle 19 from, for example, a turbocharger, a gas turbine, a pump, or a compressor.
  • the common inner race 16 defines first and second annular grooves 20 and 22, which receive the first set of balls or roller elements 12 and the second set of balls or roller elements 14, respectively.
  • the cross-sectional diameter of the annular grooves 20 and 22 is larger than the diameter of balls 12 and 14, as will be described further hereinbelow and as can be seen, somewhat exaggerated, in Figure 2 for balls 14 and groove 22.
  • Assembly 10 further includes a common inboard outer race 24 and first and second outboard outer races 26 and 28, respectively.
  • Outboard outer races 26 and 28 are positioned adjacent the ends 27 and 29 of inboard outer race 24.
  • Outboard outer race 26 and common inboard outer race 24 define a first groove 30 which receives the first plurality of balls 12 and outboard outer race 28 and inboard outer race 24 define a second groove 32 which receives second plurality of balls 14.
  • the cross sectional diameters of grooves 30 and 32 are larger than the diameters of balls 12 and 14.
  • annular concave recesses 25, 31 and 33 (Fig. 2) of inner race 16, inboard outer race 24 and outboard outer race 28 are generated by revolving radii larger than the radius of ball 14.
  • the diameter of grooves as shown in Figure 2 is somewhat exaggerated.
  • a first annular spring retainer 34 Is positioned about outboard outer race 26 and inboard outer race 24 and crimped to inboard outer race 24 at point 36.
  • Spring retainer 34 holds a spring 33 against seat 35 thereof, which spring 38 biases outboard outer race 26 toward inboard outer race 24.
  • spring 36 is a horseshoe spring (U-shaped in cross-section). It is to be understood that other types of springs, such as helical coil springs, wave springs, and Belleville springs can also be used.
  • a second spring retainer 40 is positioned about inboard outer race 24 and second outboard outer race 28 and is crimped to inboard outer race 24 at point 42.
  • a second spring 44 is retained by spring retainer 40 against seat 41 thereof and urges second outboard outer race 28 toward Inboard outer race 24. Spring 44 is similar to spring 36.
  • Retainers 34 and 40 are received in a bore 46 defined by housing 48, which housing 48 is associated with the turbocharger or other such equipment.
  • Housing 48 includes first and second end covers 50 and 52.
  • Housing 48 also receives O-ring seals 54 and 56, which can be comprised of elastomeric materials or other materials well known in the art, and which are compressed against spring retainers 34 and 40, respectively, to form a sealing relationship between housing 48 and retainers 34 and 40.
  • Housing 48 defines an oil or lubricating and damping fluid feedline 58 which provides fluid from a high pressure source (not shown) .
  • Housing 48 also defines air and fluid bleed holes or conduits 60 and 62 which are located adjacent and inboard of 0- ring seals 54 and 56, respectively.
  • the high pressure fluid can form a damping film between the spring retainers 38 and 40 and the housing bore 46, and excess fluid and air can be bled through bleed holes 60 and 62 to ensure that the above clearance is completely filled with damping and lubricating fluid.
  • An annular cavity 64 is defined between spring retainers 34 and 40 and housing 48 and common inboard outer race 24.
  • This cavity 64 communicates with oil feedline 58 and also with a check valve means 66 which meters fluid to first and second plurality of balls 12 and 14, respectively.
  • Check valve means 66 includes an aperture or bore 68 which is defined by common inboard outer race 24 and a leaf spring 70.
  • Leaf spring 70 is essentially formed in the shape of a ring and can be inserted In groove 72 defined by inboard outer race 24.
  • Leaf spring 70 covers aperture 68 and maintains a certain predetermined fluid pressure in cavity 64 so that the above damping clearances are always filled with damping and lubricating fluid.
  • the arrows 74 in Figure 1 indicate that the pressure in cavity 46 is generally always great enough to cause the leaf spring 70 to flex, allowing oil to squirt or drop from check valve means 66 in order to lubricate the plurality of balls 12 and 14.
  • the valve also acts to meter a preselected supply of lubricating fluid to the balls 12 and 14.
  • the fluid after lubricating the balls 12 and 14, travels outboard thereof, where It is thrown by first and second annular slingers 76 and 78 into collector grooves 80 and 82, which are defined by end covers 50 and 52, respectively.
  • Oil sllngers 76 and 78 are L-shaped In cross-section and are mounted to the common inner race 16 outboard of the first and second plurality of balls 12 and 14, respectively. Sllngers 76 and 78 are held in place on common Inner race 16 by end retaining nuts 77 and 79, respectively.
  • Collector grooves 80 and 82 are annular and communicate with fluid drain channels 84 and 86, which are defined by housing 48 and which communicate with fluid drain 88. Bleed holes 60 and 62 also communicate with channels 84 and 86, respectively.
  • a line of contact can be established between the balls and the grooves under an axial or a thrust load.
  • the Inner race 16 can revolve at a very high speed. Accordingly, the temperature of the assembly 10 rises quite rapidly due to the rapid speed of revolution and also due to heat which flows from, for example, a hot turbine through the shaft or spindle 19.
  • the common inner race expands and forces the outboard outer races 26 and 28 to move axially away from the common inboard outer race 24. In so doing, the springs 38 and 44 are compressed.
  • the assembly 10 is not overstressed and the accuracy in positioning the center of rotation, clearance and efficiency necessary for high speed shaft operation is maintained as radial expansion is kept to a minimum.
  • the above assembly 10 keeps such shaft whip to a minimum by having a continuous damping film provided between retainers 34 and 40 and the housing 48.
  • the air bleejd holes 60 and 62 ensure that this film is continuous and completely fills the clearance.
  • the check valve means 66 of assembly 10 is efficient, convenient and only allows the required amount of lubricating fluid to flow to the first and second plurality of balls 12 and 14, while still maintaining sufficient pressure in cavity 64 to ensure that there is proper damping between the retainers 34 and 40 and the bore 46 of housing 48.
  • the assembly 10 is self-contained.
  • the assembly 10 can be Inserted into housing 48 by first removing one of the end covers 50, 52. Then assembly 10 is disposed into bore 46 and one of the end covers 50, 52 is replaced.
  • the shaft of the gas turbine or like can then be dlsposed through the bore 18 of the common inner race 16 to accomplish proper mounting thereof.
  • the assembly 10 can be preassembled under Ideal working conditions and incorporated in the appropriate machinery as needed without having to be assembled at the site of the machinery. Accordingly, errors due to Improper on-site assembly and contamination from the surrounding environment can be minimized.

Abstract

Assemblage de roulement a billes pour equipement a haute vitesse. Le probleme technique est d'eliminer le coup de fouet et le jeu axial de l'arbre tout en positionnant correctement le fluide d'amortissement. La solution consiste a monter des cages exterieures (26, 28) avec des dispositifs (34, 38, 40, 44) qui les poussent et les retiennent sans gener la lubrification.
PCT/US1980/001115 1980-08-28 1980-08-28 Assemblage autonome de roulement a billes amorti WO1982000865A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/US1980/001115 WO1982000865A1 (fr) 1980-08-28 1980-08-28 Assemblage autonome de roulement a billes amorti

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
PCT/US1980/001115 WO1982000865A1 (fr) 1980-08-28 1980-08-28 Assemblage autonome de roulement a billes amorti
WOUS80/01115800828 1980-08-28

Publications (1)

Publication Number Publication Date
WO1982000865A1 true WO1982000865A1 (fr) 1982-03-18

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WO (1) WO1982000865A1 (fr)

Cited By (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2600381A1 (fr) * 1986-06-18 1987-12-24 Rolls Royce Plc Dispositif pour retenir un corps dans un logement
GB2248278A (en) * 1990-07-04 1992-04-01 Mtu Friedrichshafen Gmbh Exhaust-driven turbocharger with a rotor mounted by a rolling bearing.
US5224095A (en) * 1990-01-30 1993-06-29 Johnson Service Company Network control system and method
US5237568A (en) * 1990-01-30 1993-08-17 Johnson Service Company Network control system with improved priority protocol
US5243595A (en) * 1990-01-30 1993-09-07 Johnson Service Company Combined connectionless and connection-oriented network control system
US5249184A (en) * 1990-01-30 1993-09-28 Johnson Service Company Network control system with improved reliability
US5253985A (en) * 1990-07-04 1993-10-19 Mtu Motoren- Und Turbinen-Union Friedrichshafen Gmbh Exhaust gas turbocharger having rotor runners disposed in roller bearings
WO2011138253A1 (fr) * 2010-05-06 2011-11-10 Schaeffler Technologies Gmbh & Co. Kg Dispositif de palier à roulement comportant un dispositif d'amortissement hydraulique
DE102011081419A1 (de) * 2011-08-23 2013-02-28 Schaeffler Technologies AG & Co. KG Quetschöldämpfer
US20140086731A1 (en) * 2011-04-13 2014-03-27 Schaeffler Technologies AG & Co. KG Bearing unit for a turbocharger
EP2975316A1 (fr) * 2014-05-24 2016-01-20 Honeywell International Inc. Turbocompresseur
EP2954220A4 (fr) * 2013-02-06 2016-06-29 United Technologies Corp Ensemble de roulement à billes duplex hybride
US9638138B2 (en) 2015-03-09 2017-05-02 Caterpillar Inc. Turbocharger and method
US9650913B2 (en) 2015-03-09 2017-05-16 Caterpillar Inc. Turbocharger turbine containment structure
US9683520B2 (en) 2015-03-09 2017-06-20 Caterpillar Inc. Turbocharger and method
US9732633B2 (en) 2015-03-09 2017-08-15 Caterpillar Inc. Turbocharger turbine assembly
US9739238B2 (en) 2015-03-09 2017-08-22 Caterpillar Inc. Turbocharger and method
US9752536B2 (en) 2015-03-09 2017-09-05 Caterpillar Inc. Turbocharger and method
US9822700B2 (en) 2015-03-09 2017-11-21 Caterpillar Inc. Turbocharger with oil containment arrangement
US9879594B2 (en) 2015-03-09 2018-01-30 Caterpillar Inc. Turbocharger turbine nozzle and containment structure
US9890788B2 (en) 2015-03-09 2018-02-13 Caterpillar Inc. Turbocharger and method
US9903225B2 (en) 2015-03-09 2018-02-27 Caterpillar Inc. Turbocharger with low carbon steel shaft
US9915172B2 (en) 2015-03-09 2018-03-13 Caterpillar Inc. Turbocharger with bearing piloted compressor wheel

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2986942A (en) * 1956-07-12 1961-06-06 Sperry Rand Corp Gyro verticals
US4141606A (en) * 1975-11-04 1979-02-27 Tokyo Shibaura Electric Co., Ltd. Rotating anode supporting structure for an x-ray tube

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2986942A (en) * 1956-07-12 1961-06-06 Sperry Rand Corp Gyro verticals
US4141606A (en) * 1975-11-04 1979-02-27 Tokyo Shibaura Electric Co., Ltd. Rotating anode supporting structure for an x-ray tube

Cited By (29)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2600381A1 (fr) * 1986-06-18 1987-12-24 Rolls Royce Plc Dispositif pour retenir un corps dans un logement
US5224095A (en) * 1990-01-30 1993-06-29 Johnson Service Company Network control system and method
US5237568A (en) * 1990-01-30 1993-08-17 Johnson Service Company Network control system with improved priority protocol
US5243595A (en) * 1990-01-30 1993-09-07 Johnson Service Company Combined connectionless and connection-oriented network control system
US5249184A (en) * 1990-01-30 1993-09-28 Johnson Service Company Network control system with improved reliability
GB2248278A (en) * 1990-07-04 1992-04-01 Mtu Friedrichshafen Gmbh Exhaust-driven turbocharger with a rotor mounted by a rolling bearing.
US5253985A (en) * 1990-07-04 1993-10-19 Mtu Motoren- Und Turbinen-Union Friedrichshafen Gmbh Exhaust gas turbocharger having rotor runners disposed in roller bearings
GB2248278B (en) * 1990-07-04 1994-02-02 Mtu Friedrichshafen Gmbh Exhaust-driven turbocharger with a rotor mounted by a rolling bearing
WO2011138253A1 (fr) * 2010-05-06 2011-11-10 Schaeffler Technologies Gmbh & Co. Kg Dispositif de palier à roulement comportant un dispositif d'amortissement hydraulique
CN102884329A (zh) * 2010-05-06 2013-01-16 谢夫勒科技股份两合公司 带有液压阻尼装置的滚动轴承设备
CN102884329B (zh) * 2010-05-06 2015-05-20 谢夫勒科技股份两合公司 带有液压阻尼装置的滚动轴承设备
US20140086731A1 (en) * 2011-04-13 2014-03-27 Schaeffler Technologies AG & Co. KG Bearing unit for a turbocharger
US8985857B2 (en) * 2011-04-13 2015-03-24 Schaeffler Technologies AG & Co. KG Bearing unit for a turbocharger
DE102011081419A1 (de) * 2011-08-23 2013-02-28 Schaeffler Technologies AG & Co. KG Quetschöldämpfer
US9897140B2 (en) 2013-02-06 2018-02-20 United Technologies Corporation Hybrid duplex ball bearing assembly
EP2954220A4 (fr) * 2013-02-06 2016-06-29 United Technologies Corp Ensemble de roulement à billes duplex hybride
EP2975316A1 (fr) * 2014-05-24 2016-01-20 Honeywell International Inc. Turbocompresseur
US9988976B2 (en) 2014-05-24 2018-06-05 Honeywell International Inc. Turbocharger
US9650913B2 (en) 2015-03-09 2017-05-16 Caterpillar Inc. Turbocharger turbine containment structure
US9683520B2 (en) 2015-03-09 2017-06-20 Caterpillar Inc. Turbocharger and method
US9732633B2 (en) 2015-03-09 2017-08-15 Caterpillar Inc. Turbocharger turbine assembly
US9739238B2 (en) 2015-03-09 2017-08-22 Caterpillar Inc. Turbocharger and method
US9752536B2 (en) 2015-03-09 2017-09-05 Caterpillar Inc. Turbocharger and method
US9822700B2 (en) 2015-03-09 2017-11-21 Caterpillar Inc. Turbocharger with oil containment arrangement
US9879594B2 (en) 2015-03-09 2018-01-30 Caterpillar Inc. Turbocharger turbine nozzle and containment structure
US9890788B2 (en) 2015-03-09 2018-02-13 Caterpillar Inc. Turbocharger and method
US9638138B2 (en) 2015-03-09 2017-05-02 Caterpillar Inc. Turbocharger and method
US9903225B2 (en) 2015-03-09 2018-02-27 Caterpillar Inc. Turbocharger with low carbon steel shaft
US9915172B2 (en) 2015-03-09 2018-03-13 Caterpillar Inc. Turbocharger with bearing piloted compressor wheel

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