GB2175957A - Lubrication system for turbochargers - Google Patents

Lubrication system for turbochargers Download PDF

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Publication number
GB2175957A
GB2175957A GB08612165A GB8612165A GB2175957A GB 2175957 A GB2175957 A GB 2175957A GB 08612165 A GB08612165 A GB 08612165A GB 8612165 A GB8612165 A GB 8612165A GB 2175957 A GB2175957 A GB 2175957A
Authority
GB
United Kingdom
Prior art keywords
bearing
housing
annular chamber
bearing carrier
carrier
Prior art date
Legal status (The legal status 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 status listed.)
Withdrawn
Application number
GB08612165A
Other versions
GB8612165D0 (en
Inventor
Jr Joe Albert Mceachern
James William Brogdon
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
TDY Industries LLC
Original Assignee
Teledyne Industries Inc
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 Teledyne Industries Inc filed Critical Teledyne Industries Inc
Publication of GB8612165D0 publication Critical patent/GB8612165D0/en
Publication of GB2175957A publication Critical patent/GB2175957A/en
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/16—Arrangement of bearings; Supporting or mounting bearings in casings
    • F01D25/162—Bearing supports
    • F01D25/164—Flexible supports; Vibration damping means associated with the bearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/18—Lubricating arrangements
    • 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
    • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
    • F16C19/546—Systems with spaced apart rolling bearings including at least one angular contact bearing
    • F16C19/547—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling bearings
    • F16C19/548—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling bearings in O-arrangement
    • 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
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2220/00—Application
    • F05D2220/40—Application in turbochargers
    • 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
    • F16C19/16—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 a single row of balls
    • F16C19/163—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 a single row of balls with angular contact
    • 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

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Supercharger (AREA)
  • Support Of The Bearing (AREA)

Abstract

A turbocharger has a main housing (12) with a throughbore in which a tubular bearing carrier (40) is mounted. A main shaft (14) having a turbine (18) at one end and a compressor (16) at its other end extends through the bearing carrier (40) and is rotatably mounted to the housing by two spaced bearing assemblies (48, 50). A lubrication system (80, 82) supplies lubricant to an annular chamber (54) for hydrostatically damping the shaft vibrations and the discharge of the lubricant from the chamber is employed to lubricate the bearing assemblies (48, 50). <IMAGE>

Description

SPECIFICATION Improvements in or relating to turbochargers Field of the invention The present invention relates generally to turbochargers and, more particularly, to a turbocharger with an improved lubrication system.
Background of the invention There have been a number of previously known devices which hydrostatically damp a shaft rotatably mounted to a housing. Examples of such devices are shown in U.S. Patent No. 3,881,841 to Straniti, May 6, 1975 and U.S. Patent No. 3,158,413 to Shelley, November 1964.
In these previously known devices, a thin layer of lubricant, commonly known as a squeeze film damper, is entrapped between an outer race of the bearing assembly and the housing in which the shaft is rotatably mounted. This squeeze film damper hyrostatically damps shaft vibration by hydrostatic action.
There have, however, been a number of previously known disadvantages with such hydrostatically damped bearing assemblies. One such disadvantage is that, after a period of time, the lubricant which forms the squeeze film damper deteriorates. Unless new lubricant is supplied to the squeeze film damper, the dampening action of the squeeze film damper will be degraded. The same is also true when the lubricant leaks from the squeeze film damper.
The present invention aims to provide a turbocharger construction which overcomes or at least reduces at least some of the above mentioned disadvantages of the previously known devices.
Summary of the present invention According to the present invention there is provided a turbocharger comprising: a main housing having a throughbore, a tubular bearing carrier having an outer periphery and an inner periphery, said bearing carrier positioned within said housing throughbore, said bearing carrier dimensioned so that said bearing carrier is positioned radially inwardly from said housing, thus forming at least one annular chamber therebetween, a shaft extending through said bearing carrier said shaft having a turbine at one end and a compressor at its other end, at least one bearing assembly for rotatably connecting said shaft to the inner periphery of said bearing carrier, a source of pressurised lubricant, means forfluidly connecting said source to one end of said annular chamber, and fluid passage means formed through said bearing carrier for fluidly connecting the other end of said annular chamber to said bearing assembly, wherein said annular chamber is dimensioned so that lubricant in said annular chamber hydrostatically damps said bearing assembly.
In operation, lubricant flows first through the annular chamber and, upon exit from the annular chamber, lubricates the bearing assemblies.
Furthermore, the oil within the annular chamber forms a squeeze film damper for hydrostatically dampening the bearing assemblies and thus minimising vibration between the housing and the shaft.
Brief description of the drawings A better understanding of the present invention will be had upon reference to the following detailed description when read in conjunction with the accompanying drawings, wherein like reference characters refer to like parts throughout the several views, and in which: Figure lisa diagrammatic view illustrating schematically a preferred embodiment of the present invention; Figure 2 is a fragmentary longitudinal sectional view illustrating part of the embodiment of Figure 1 to an enlarged scale; and Figure 3 is a cross sectional view taken substantially along line 3-3 in Figure 2.
Detailed description of the drawings With reference first to Figure 1, a preferred embodiment of a turbocharger 10 in accordance with the present invention is thereshown and comprises a main housing 12 having a shaft 14 rotatably mounted to it in a fashion which will subsequently be described in greater detail. As is conventional with turbochargers, a compressor 16 is secured to one end ofthe shaft 14 and a turbine 18 is secured to the other end of the shaft 14.
Upon rotation of the compressor 16, the compressor 16 inducts air at its inlet 20 (illustrated diagrammatically) and supplies compressed air at its outlet 22 to the intake 24 of an internal combustion engine 26. The internal combustion engine 26 has its exhaust 28 secured to the inlet 30 of the turbine 18 and the exhaust 32 from the turbine 18 is open to the atmosphere. In the conventional fashion, the exhaust from the engine 26 rotatably drives the turbine 18 which in turn rotatably drives the compressor 16 through the shaft 14.
With reference now particularly to Figure 2, the housing 12 includes a throughbore 34 which is coaxial with the shaft 14. Atubular bearing housing 36 having an outwardly extending flange 38 at one end is press fit into the througbore 34 until the flanged end 38 of the bearing housing 36 abuts against the housing 12. Preferably the housing 12 is constructed of aluminium for lightweight construction while the bearing housing 36 is constructed of steel for durability.
Atubular bearing carrier 40 having an outwardly extending flange 42 at one end is then positioned coaxially within the bearing housing 36 so that the flanges 38 and 42 flatly abut against each other. A retaining ring assembly 44 secures the bearing housing 36 and bearing carrier 40 against axial movement with respect to each other.
A pair of axially spaced bearing assemblies 48 and 50 rotatably mount the turbocharged shaft 14 to the bearing carrier 40. Each bearing assembly 48, 50 preferably comprises a ball bearing assembly having its inner race secured for rotation with the shaft 14 and its outer race secured against radial movement to the inner periphery 52 of the bearing carrier 40. In addition the bearing assemblies 48 and 50 are mounted between the shaft 14 and bearing carrier 40 adjacent each end of the bearing carrier 40.
With reference now to Figures 2 and 3, the bearing carrier 40 is dimensioned so that each of its ends is spaced radially inwardly from the inner surface of the bearing housing 36 thus forming annular chambers 54 therebetween. Referring particularly to Figure 2, a resilient seal 56 is sandwiched in between the bearing housing 36 and bearing carrier 40 adjacent the outer end of each annular chamber 54 while, similarly, a resilient seal 58 is sandwiched between the bearing housing 36 and bearing carrier 40 adjacent the inner end of each annular chamber 54. In addition, the radial width of each annular chamber 54 is very small, typically only a few thousandths of an inch (tens of microns).
Still referring to Figure 2, a first annular spray nozzle 60 is contained within the interior of the bearing carrier 40 and has one axial end 62 which abuts against the outer race of the bearing assembly 48. Similarly,-a second annular spray nozzle 64 is contained within the interior of the bearing carrier 40 and has its outer axial end 66 in abutment with the outer race of the other bearing assembly 50. The inner axial end 70 of the spray nozzle 64 abuts against a radially inwardly extending portion 72 on the bearing carrier 40.
A compression spring 74 is sandwiched in a state of compression between the inner axial end 76 of the spray nozzle 60 and the radially inwardly extending portion 72 of the bearing carrier 40. This compression spring 74 thus acts to balance the load evenly between the outer races of the bearing assemblies 48 and 50 to minimise vibration caused by unevenly loaded bearings.
Referring now to Figure 1, a pressurised lubricant source 80 (illustrated only diagrammatically) is fluidly connected to a fluid coupling 82 formed in the housing 12. This coupling 82, in turn, is fluidly connected to two passageways 84 and 86 formed through the housing 12. Passageways 84 and 86 are represented schematically in Figure 1.
Referring again to Figure 2, the fluid passageway 84 is fluidly connected to a radially extending port 88 formed through the bearing housing 36 adjacent the outer end of one annular chamber 54. Similarly, the other fluid passageway 86 is fluidly connected to a radial port 90 formed through the bearing housing 36 adjacent the outer end of the other annular chamber 54.
Still referring to Figure 2, a passageway 91 is formed through registering bores in bearing carrier 40 and spray nozzle 60. One end of the passageway 91 is open closely adjacent the innermost end of one annular chamber 54 while the other end of the passageway 91 is opened to an inner side 92 of the bearing assembly 48. Furthermore, the passageway 91 is obliquely formed with respect to the shaft axis so that it extends from the annular chamber 54 towards the bearing assembly 48. Similarly, an oblique passageway 94 is formed through the bearing carirer 40 and spray nozzle 64 so that one end ofthe passageway 94 is open to the other annular chamber 54 adjacent its innermost end while the other end of the passageway 94 is open to an inner side 96 of the other bearing assembly 50.
A pair of slingers 100 are secured at axially spaced positions to the shaft 12 so that one slinger 100 is positioned closely adjacent an outer end of each bearing assembly 40 and 50. Each slinger 100 includes a radially extending portion 102, preferably with impellers, which registers with and is closely adjacent its associated bearing assembly 48 or 50.
Each slinger 100, furthermore, is opened to a lubricant collection chamber 104 (Figure 1) formed in the housing 12.
In operation, lubricant from the source 80 is supplied under pressure to the fluid coupling 82 in the housing 12 so that the lubricant flows from the source 80, through the passageways 84 and 86 and to the outer ends of the annular chambers 54. The lubricant then flows axially inwardly through the annular chambers 54, through the obliquely extending passageways 91 and 94 and to the bearing assemblies 48 and 50, respectively, in order to lubricate the bearing assemblies.
After passing through the bearing assemblies 48 and 50, the lubricant is expelled radially outwardly by the slingers 100 into the lubricant collection chamber 104 inthe housing 12. The lubricant is then evacuated from the chamber 104 through a port 106 (Figure 1) and recycled by the lubrication system in conventional fashion.
Because the annular chambers 54 are very small in radial width, they form a squeeze film damperfor hydrostatically mounting the bearing carrier 40, and thus the bearing assemblies 48 and 50, to the housing 12.
The primary advantage of the present invention is that oil flow through the squeeze film dampers or annular chambers 54 is also used to lubricate the bearing assemblies 48 and 50. This provision of the invention thus ensures that a constant and fresh supply of oil is supplied to the squeeze film damper, thereby obviating many of the previously known disadvantages ofthe prior art devices. Furthermore, byfluidly connecting the annular chambers 54 in series with the lubrication flow to the main bearings 48 and 50, a much simpler, inexpensive and yet totally effective construction is thereby obtained.

Claims (10)

1. A turbocharger comprising: a main housing having a throughbore, a tubular bearing carrier having an outer periphery and an inner periphery, said bearing carrier positioned within said housing throughbore, said bearing carrier dimensioned so that said bearing carrier is positioned radially inwardly from said housing, thus forming at least one annular chamber therebetween, a shaft extending through said bearing carrier said shaft having a turbine atone end and a compressor at its other end, at least one bearing assembly for rotatably connecting said shaft to the inner periphery of said bearing carrier, a source of pressurised lubricant, means for fluidly connecting said source to one end of said annular chamber, and fluid passage means formed through said bearing carrier for fluidly connecting the other end of said annular chamber to said bearing assembly, wherein said annular chamber is dimensioned so that lubricant in said annular chamber hydrostatically damps said bearing assembly.
2. A turbocharger according to claim 1, and comprising a respective fluid seal between each end of said bearing carrier and said housing.
3. A turbocharger according to claim 1 or 2, wherein each fluid seal comprises a resilient 0ring.
4. A turbocharger according to claim 1, 2 or 3, wherein said at least one bearing assembly comprises two bearing assemblies, said bearing assemblies being axially spaced from each other, and comprising fluid seals extending between said bearing carrier and said housing which separate said at least one annular chamber into two axially spaced annular chambers, said fluid connecting means extending between said source and one end of each annular chamber, said fluid passage means extending between the other end of one annular chamber and one bearing assembly and the other end of the other annular chamber the other bearing assembly.
5. A turbocharger according to any one of claims 1 to 4, wherein said fluid passage means is opened to one end of said bearing assembly, and comprising a disk-shaped slinger secured to said shaft so that said slinger extends outwardly from said shaft adjacent the other side of said bearing assembly.
6. A turbocharger according to claim 5, wherein said housing includes a lubrication collection chamber open to said slinger.
7. A turbocharger according to any one of the preceding claims, wherein the or each bearing assembly comprises a ball bearing assembly.
8. A turbocharger according to any one of the preceding claims, and comprising a bearing housing mounted through said housing throughbore, said bearing carrier being coaxially mounted within said bearing housing, and wherein said housing is constructed of aluminium and said bearing housing is constructed of steel.
Amendments to the claims have been filed, and having the following effect: (a) Claim 1 above has been deleted or textually amended.
(b) New or textually amended claims have been filed as follows:- (c) Claim 9 above has been re-numbered as 10.
1. A turbocharger comprising: a main housing having a throughbore, a tubular bearing carrier having an outer periphery and an inner periphery, and means for mounting said bearing carrier within said housing throughbore to permit limited radial movement of said bearing carrier with respect to said housing and to form at least one annular chamber between said bearing carrier and said housing, a shaft extending through said bearing carrier, said shaft having a turbine mounted at one end and a compressor mounted at its other end, at least one bearing assembly for rotatably connecting said shaft to the inner periphery of said bearing carrier, a source of pressurised lubricant, means for fluidly connecting said source to one end of said annular chamber, and fluid passage means formed through said bearing carrier for fluidly connecting the other end of said annular chamber to said bearing assembly, said annular chamber being dimensioned so that lubricant in said annular chamber hydrostatically damps said bearing carrier, whereby said lubricant being supplied to said annular chamber acts to hydrostatically damp said bearing carrier, and then passes from said annular chamber and through said bearing carrier to said at least one bearing assembly to provide lubrication thereto.
9. A turbocharger according to claim 8, wherein said means for fluidly connecting said source to said annular chamber includes fluid passageways extending through said bearing housing.
10. A turbocharger substantially as herein described with reference to, and as shown in, the accompanying drawings.
GB08612165A 1985-05-30 1986-05-19 Lubrication system for turbochargers Withdrawn GB2175957A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US73938585A 1985-05-30 1985-05-30

Publications (2)

Publication Number Publication Date
GB8612165D0 GB8612165D0 (en) 1986-06-25
GB2175957A true GB2175957A (en) 1986-12-10

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ID=24972041

Family Applications (1)

Application Number Title Priority Date Filing Date
GB08612165A Withdrawn GB2175957A (en) 1985-05-30 1986-05-19 Lubrication system for turbochargers

Country Status (9)

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JP (1) JPS627935A (en)
AU (1) AU5786386A (en)
BR (1) BR8602391A (en)
DE (1) DE3617403A1 (en)
FR (1) FR2582727A1 (en)
GB (1) GB2175957A (en)
IT (1) IT1190576B (en)
NZ (1) NZ216319A (en)
SE (1) SE8602121L (en)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2569771A1 (en) * 1984-09-03 1986-03-07 Ishikawajima Harima Heavy Ind SUPPORT DEVICE FOR TURBOCHARGER TO ENABLE STABLE ROTATION OF A TURBINE TREE
EP0437349A1 (en) * 1990-01-10 1991-07-17 Ngk Insulators, Ltd. Method of manufacturing ceramic turbo charger rotor
DE4019720A1 (en) * 1990-06-21 1992-01-09 Bmw Rolls Royce Gmbh Through-flow calibration for compressed oil damper - is used with turbine and has housing with roller bearing, outer rings, and seals
FR2664330A1 (en) * 1990-07-04 1992-01-10 Mtu Friedrichshafen Gmbh LUBRICATION OF EXHAUST GAS TURBOCHARGER WHOSE ROTOR IS MOUNTED ON BEARINGS.
FR2856737A1 (en) * 2003-06-30 2004-12-31 Renault Sa Internal combustion engine for vehicle, has turbocharger fixed on cylindrical block through collar that is connected to connecting flange of turbocharger and locked radially on maintenance shaft fixed on block
GB2467966A (en) * 2009-02-24 2010-08-25 Dyson Technology Ltd A rotor assembly including a bearing cartidge mounted to a shaft
WO2012025531A1 (en) * 2010-08-27 2012-03-01 Schaeffler Technologies Gmbh & Co. Kg Bearing
EP2562436A1 (en) * 2011-08-26 2013-02-27 Dyson Technology Limited Bearing Assembly
EP2730754A3 (en) * 2012-11-12 2016-08-03 Cummins Ltd Turbomachine bearing assembly preloading arrangement
US9624940B2 (en) 2009-02-24 2017-04-18 Dyson Technology Limited Rotor assembly

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US4798523A (en) * 1986-12-19 1989-01-17 Allied-Signal Inc. Turbocharger bearing and lubrication system
JPS63186934U (en) * 1987-05-22 1988-11-30
JP2530995Y2 (en) * 1991-07-29 1997-04-02 石川島播磨重工業株式会社 Ball bearing supercharger
DE4230037A1 (en) * 1991-09-09 1993-03-11 Aisin Seiki CENTRIFUGAL RECHARGE BLOWER
DE102007022811B3 (en) * 2007-05-15 2008-12-11 Voith Patent Gmbh Turbocharger for internal-combustion engine, has turbine, compressor and shaft, where turbine rotor at one end of shaft and compressor rotor at other end are torque proof mounted
RU2456463C1 (en) * 2011-04-05 2012-07-20 Открытое акционерное общество "Научно-производственное объединение "Сатурн" (ОАО "НПО "Сатурн") Gas turbine engine shaft support
RU2482303C1 (en) * 2011-12-22 2013-05-20 Открытое акционерное общество "Научно-производственное объединение "Сатурн" (ОАО "НПО "Сатурн") Front support of lp turbine rotor of two-shaft gas turbine engine
RU2529276C1 (en) * 2013-06-06 2014-09-27 Открытое акционерное общество "Уфимское моторостроительное производственное объединение" ОАО "УМПО" Российская федерация Республика Башкортостан Resilient support of turbomachine rotor
RU2563954C1 (en) * 2014-08-14 2015-09-27 Открытое акционерное общество "Уфимское моторостроительное производственное объединение" ОАО "УМПО" Turbomachine rotor support
CN108799399B (en) * 2017-05-03 2020-08-14 通用电气公司 Squeeze film damper assembly
JP7146353B2 (en) * 2018-12-25 2022-10-04 東芝三菱電機産業システム株式会社 bearing device
US10982730B2 (en) * 2019-03-04 2021-04-20 Saint- Augustin Canada Electric Inc. Flywheel systems and related methods

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GB1412124A (en) * 1972-02-07 1975-10-29 Normalair Garrett Ltd Rotating machines
GB2119015A (en) * 1982-04-21 1983-11-09 Household Mfg Inc Turbocharger ventilation system
EP0100761A2 (en) * 1982-08-02 1984-02-15 Union Carbide Corporation Integral bearing system

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US4329000A (en) * 1980-08-28 1982-05-11 Caterpillar Tractor Co. Self-contained, damped ball bearing assembly
JPS60128934A (en) * 1983-12-16 1985-07-10 Honda Motor Co Ltd Turbocharger
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Publication number Priority date Publication date Assignee Title
GB1412124A (en) * 1972-02-07 1975-10-29 Normalair Garrett Ltd Rotating machines
GB2119015A (en) * 1982-04-21 1983-11-09 Household Mfg Inc Turbocharger ventilation system
EP0100761A2 (en) * 1982-08-02 1984-02-15 Union Carbide Corporation Integral bearing system

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2569771A1 (en) * 1984-09-03 1986-03-07 Ishikawajima Harima Heavy Ind SUPPORT DEVICE FOR TURBOCHARGER TO ENABLE STABLE ROTATION OF A TURBINE TREE
EP0437349A1 (en) * 1990-01-10 1991-07-17 Ngk Insulators, Ltd. Method of manufacturing ceramic turbo charger rotor
US5133122A (en) * 1990-01-10 1992-07-28 Ngk Insulators, Ltd. Method of manufacturing ceramic turbo charger rotor
DE4019720A1 (en) * 1990-06-21 1992-01-09 Bmw Rolls Royce Gmbh Through-flow calibration for compressed oil damper - is used with turbine and has housing with roller bearing, outer rings, and seals
FR2664330A1 (en) * 1990-07-04 1992-01-10 Mtu Friedrichshafen Gmbh LUBRICATION OF EXHAUST GAS TURBOCHARGER WHOSE ROTOR IS MOUNTED ON BEARINGS.
FR2856737A1 (en) * 2003-06-30 2004-12-31 Renault Sa Internal combustion engine for vehicle, has turbocharger fixed on cylindrical block through collar that is connected to connecting flange of turbocharger and locked radially on maintenance shaft fixed on block
GB2467966A (en) * 2009-02-24 2010-08-25 Dyson Technology Ltd A rotor assembly including a bearing cartidge mounted to a shaft
GB2467966B (en) * 2009-02-24 2013-04-03 Dyson Technology Ltd Rotor assembly
US9624940B2 (en) 2009-02-24 2017-04-18 Dyson Technology Limited Rotor assembly
WO2012025531A1 (en) * 2010-08-27 2012-03-01 Schaeffler Technologies Gmbh & Co. Kg Bearing
EP2562436A1 (en) * 2011-08-26 2013-02-27 Dyson Technology Limited Bearing Assembly
US8864460B2 (en) 2011-08-26 2014-10-21 Dyson Technology Limited Bearing assembly
EP2730754A3 (en) * 2012-11-12 2016-08-03 Cummins Ltd Turbomachine bearing assembly preloading arrangement
US9759093B2 (en) 2012-11-12 2017-09-12 Cummins Ltd. Turbomachine bearing assembly preloading arrangement
US10655498B2 (en) 2012-11-12 2020-05-19 Cummins Ltd. Turbomachine bearing assembly preloading arrangement

Also Published As

Publication number Publication date
IT1190576B (en) 1988-02-16
SE8602121D0 (en) 1986-05-12
JPS627935A (en) 1987-01-14
SE8602121L (en) 1986-12-01
NZ216319A (en) 1988-02-29
GB8612165D0 (en) 1986-06-25
IT8667438A0 (en) 1986-05-27
BR8602391A (en) 1987-01-21
DE3617403A1 (en) 1986-12-04
AU5786386A (en) 1986-12-04
FR2582727A1 (en) 1986-12-05

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