US20020141862A1 - Oil control device - Google Patents
Oil control device Download PDFInfo
- Publication number
- US20020141862A1 US20020141862A1 US10/109,430 US10943002A US2002141862A1 US 20020141862 A1 US20020141862 A1 US 20020141862A1 US 10943002 A US10943002 A US 10943002A US 2002141862 A1 US2002141862 A1 US 2002141862A1
- Authority
- US
- United States
- Prior art keywords
- control device
- oil control
- channels
- oil
- shaft
- 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.)
- Abandoned
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Classifications
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- 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
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/06—Lubrication
- F04D29/063—Lubrication specially adapted for elastic fluid pumps
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- 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
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- 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
- F01D25/183—Sealing means
- F01D25/186—Sealing means for sliding contact bearing
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas- turbine plants for special use
- F02C6/04—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output
- F02C6/10—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output supplying working fluid to a user, e.g. a chemical process, which returns working fluid to a turbine of the plant
- F02C6/12—Turbochargers, i.e. plants for augmenting mechanical power output of internal-combustion piston engines by increase of charge pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D25/00—Pumping installations or systems
- F04D25/02—Units comprising pumps and their driving means
- F04D25/04—Units comprising pumps and their driving means the pump being fluid-driven
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- 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
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- 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
- F16C17/00—Sliding-contact bearings for exclusively rotary movement
- F16C17/26—Systems consisting of a plurality of sliding-contact bearings
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- 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
Abstract
An oil control device for incorporation in a system for sealing the passage of a rotating shaft (3) through an opening. The oil control device comprises an annular member (10) for rotation with said shaft (3) and provided with a circumferentially spaced array of passages (24, 18) for centrifugally displacing fluid away from said shaft (3) as it rotates. The passages (24, 18) comprise channels which are open along their length.
Description
- TECHNICAL FIELD
- The present invention relates to an oil control device. The invention provides an oil control device particularly suitable for incorporation in a system for sealing the passage of a rotational shaft through a wall separating adjacent chambers subject to differential fluid pressures. Particularly, but not exclusively, the invention relates to an oil control device for incorporation in the thrust bearing sealing system of a compressor, such as a turbocharger compressor.
- Turbochargers are well known devices for supplying air to the intake of an internal combustion engine at pressures above atmospheric (boost pressures). A conventional turbocharger essentially comprises an exhaust gas driven turbine wheel mounted on a rotatable shaft within a turbine housing. Rotation of the turbine wheel rotates a compressor wheel mounted on the other end of the shaft within a compressor housing. The compressor wheel delivers compressed air to the intake manifold of the engine, thereby increasing engine power.
- The turbocharger shaft is conventionally supported by journal and thrust bearings, including appropriate lubricating systems, located within a central bearing housing connected between the turbine and compressor wheel housings. It is well known that providing an effective sealing system to prevent oil leakage from the central bearing housing into the compressor or turbine housing is problematical. This is particularly the case at the compressor end of the turbocharger since at low boost pressures there can be a significant drop in pressure from the bearing housing to the compressor housing which encourages oil leakage into the compressor housing.
- In a conventional turbocharger design, the shaft passes from the bearing housing to the compressor housing through an appropriate passage in a compressor housing back plate, or oil seal plate, with a thrust bearing assembly located adjacent the plate within the bearing housing. It is oil supplied to the thrust bearing assembly which can leak into the compressor housing. To combat this, it is conventional to incorporate in such thrust bearing assemblies a seal assembly including an oil control device (often referred to within the turbocharger industry as an “oil slinger”). An oil slinger is an annular component which rotates with the shaft and comprises a number of radially extending passages which effectively act as vanes for slinging oil away from the shaft and in particular away from the passage from the bearing housing into the compressor housing. An annular splash chamber located around the thrust bearing and sealing assembly collects the oil for re-circulation within the lubrication system. For instance the splash chamber may be provided with drainage channels to drain oil to a sump.
- Many such thrust bearing sealing systems are known, for instance an example of a typical system is disclosed in U.S. Pat. No. 4,157,834. In this particular system the oil slinger component is integral with a thrust collar component of the thrust bearing assembly. In other arrangements the oil slinger may be a discrete component suitably mounted for rotation with the shaft. The present invention relates to the configuration of an oil slinger which may be either a discrete component or an intregal part of another component such as a part of a thrust bearing and/or sealing assembly.
- It is an object of the present invention to provide an oil slinger which is simpler, and hence cheaper, to manufacture than conventional designs. A further object is to provide an oil slinger with improved pumping efficiency compared with conventional designs.
- According to a first aspect of the present invention there is provided an oil slinger for incorporation in a system for sealing the passage of a rotating shaft through an opening, the oil slinger comprising an annular member for rotation with said shaft and provided with a circumferentially spaced array of passages for centrifugally displacing fluid away from said shaft as it rotates, wherein said passages comprise channels which are open along their length.
- As is discussed further below, forming the oil slinging passages as open channels provides a number of benefits over conventional designs in which the oil slinging passages are radial holes drilled into the oil slinger. Manufacture of the oil slinger is simplified as a number of known techniques can be used, such as sintering or injection moulding, which are more efficient than the machining required to manufacture conventional oil slingers. In addition to reducing the cost of manufacture, the manufacturing ease enables the configuration of the passages to be varied so that the pumping characteristic of the oil slinger can be “tuned”. Open channels are also subject to lower stresses than drilled holes and accordingly durability of the oil slinger may be increased.
- Preferably the annular member defines at least one generally radially extending face in which a plurality of said channels are formed.
- In a preferred embodiment the annular member comprises a central cylindrical body portion and a surrounding annular portion, wherein said at least one face is defined by the annular portion, for instance at an axial end thereof.
- The annular portion preferably has an axially extending part which is radially spaced from said body portion defining an annular gap therebetween. In use the annular gap may receive a flange of an oil seal plate or the like which defines said openings. In this embodiment at least some of said channels in the or each face communicate with said annular gap.
- The channels may have a variety of configurations. For instance one or more of said channels may be substantially straight, and may be either radial or be swept backwards or forwards relative to the direction of rotation of the oil slinger.
- Alternatively at least some of said channels may be curvilinear with either a constant or varying radius of curvature.
- The channels may have a constant cross-sectional area or a cross-sectional area which increases or decreases along the length of the respective channel in a direction away from the axis rotation of the oil slinger, depending on the desired pumping characteristic. A varying cross-sectional area may for instance be provided by varying the width and/or depth of respective channels.
- According to a second aspect of the present invention there is provided a seal system for sealing the passage of a rotating shaft through an opening in a wall the system comprising an oil slinger in accordance with the first aspect of the present invention mounted for rotation with said shaft.
- For instance the invention provides a sealing system for sealing passage of a rotatable shaft through an opening in a wall from leakage of lubricant supplied to a thrust bearing assembly associated with said shaft, the system comprising an oil slinger according to the first aspect of the present invention mounted for rotation with said shaft between said wall and said thrust bearing assembly.
- Although oil slingers in accordance with the present invention may have many varied applications they are particularly suitable for incorporation in the sealing systems of turbochargers. Accordingly, a third aspect of the present invention provides a turbocharger comprising a compressor housing and a bearing housing separated by a wall, a rotating shaft mounted on bearing systems housed within said bearing housing, said shaft extending through said wall from the bearing housing into the compressor housing, and an oil slinger according to the first aspect of the invention mounted to said shaft on the bearing housing side of said wall to help prevent leakage of lubricant from the bearing housing into the compressor housing.
- The wall may be a compressor back plate, or separate oil seal plate, adapted for mating co-operation with the oil slinger. Preferably the oil slinger has a first generally radially extending axial end face which is in running engagement with said plate (at least some of said channels preferably being defined in said first end face), and/or a second generally radially extending axial end face which faces said thrust bearing assembly (at least some of said channels preferably being formed in said second end face).
- An embodiment of the present invention will now be described, by way of example only, with reference to the accompanying drawings, in which:
- FIG. 1 is an axial cross-section through a turbocharger bearing housing incorporating the present invention;
- FIG. 2 is an enlargement of the compressor end of the bearing housing of FIG. 1, showing detail of the location of an oil slinger in accordance with the present invention;
- FIGS. 3 and 4 are perspective views showing opposite sides of the oil slinger in isolation;
- FIG. 5 is a perspective view showing the oil slinger of FIGS. 3 and 4 together with an oil seal plate shown in FIGS. 1 and 2; and
- FIG. 6 is a radial cross-section of the oil slinger/oil seal plate combination of FIG. 5.
- Referring to the drawings, FIG. 1 is an axial cross-section through parts of a turbocharger incorporating the present invention. The illustrated turbocharger comprises a compressor wheel1 and turbine wheel 2 mounted to opposite ends of a
common shaft 3 which extends through a central bearinghousing 4. Much of the detail of the bearing housing and the bearing arrangements is not important to enable the understanding or implementation of the present invention and so will not be described in depth. Such details may be entirely conventional. - In general, the bearing
housing 4 has a central portion which housesjournal bearing assemblies assembly 7 and terminates in a radially extending diffuser section 8 which forms the diffuser portion of the compressor (a compressor cover (not shown) being bolted to the diffuser section around the compressor wheel 1). The chamber in which the compressor wheel rotates (referred to hereinafter as the compressor housing) is separated from the bearing housing by anoil seal plate 9 which sits within the diffuser section 8 of the bearinghousing 4. Theoil seal plate 9 is part of an oil seal system which further incorporates anoil slinger 10 in accordance with the present invention. Further details of these components will now be described with particular reference to FIGS. 2 to 6. - The oil seal system comprising the
oil seal plate 9 andoil slinger 10 separates the compressor housing from the bearing housing and sits between the compressor wheel 1 and thethrust bearing assembly 7. The oil seal system is provided to prevent oil which must be supplied to thethrust bearing assembly 7 from leaking into the compressor housing, particular at low compressor speeds at which there will be a pressure drop from the bearing housing to the compressor housing. - The oil seal plate is fixed in position within the housing whereas the
oil slinger 10 is mounted for rotation with theshaft 3, and thus rotates relative to theoil seal plate 9. Theoil slinger 10 andoil seal plate 9 mate together in a generally conventional configuration to provide a labyrinthine passage from the bearing housing to the compressor housing to protect against oil leakage. Details of theoil seal plate 9 andoil slinger 10, and the co-operation between the two, will now be described with additional reference to FIGS. 3 to 6. FIGS. 3 and 4 are perspective views of the oil slinger 10 (not to scale with FIG. 1 or FIG. 2) looking in opposite axial directions. FIGS. 5 and 6 show theoil slinger 10 andoil seal plate 9 mated together, FIG. 6 being a radial cross-section of the view shown in FIG. 5. - From the drawings it will be seen that the oil seal plate comprises an
annular disc 11 having acentral aperture 12 defined by an axially extendingannular flange 13 which extends into the bearinghousing 4. Theflange 13 surrounds theshaft 3 but with an annular gap therebetween. - The
oil seal plate 9 has a secondannular flange 14 extending axially into the bearinghousing 4 from adjacent its outer periphery. Thesecond flange 14 has both a greater axial and radial dimension than thefirst flange 13 and bears against thethrust bearing assembly 7. Anannular shoulder 15 is defined between theflange 14 and outer periphery of thedisc 11 and provides an annular seat for an O-ring 16 which provides a seal between the radially outer extent of theoil seal plate 9 and the bearinghousing 4. A thirdannular flange 17 extends radially from the compressor side of theoil seal plate 9 approximately midway between thecentral aperture 12 and the outer periphery of thedisc 11. - Turning now to the
oil slinger 10 in accordance with an embodiment of the present invention, this comprises a centralcylindrical body 18 and a radially stepped annular portion which essentially comprises a radially extendingflange portion 19 and a radially enlarged axially extendingportion 20. Theenlarged portion 20 surrounds part of thebody 18 adjacent theflange portion 19 thereby defining anannular slot 21 which receives theannular flange 12 of theoil seal plate 9 such that thebody 18 of theoil slinger 10 extends into thecentral aperture 12 of theoil seal plate 9. Theradial surface 22 of theenlarged portion 20 of theoil slinger 10 is radially stepped providing an axially raised portion which lies in running engagement with the surface of thedisc 11 of theoil seal plate 9 around theflange 12. Anannular groove 22 is provided in the external surface of thebody 18 of theoil slinger 10 within which sits an sealingring 23 which provides a seal between theoil slinger 10 and theflange 12 of theoil seal plate 9. - The oil slinging function is provided by two axially spaced circumferential arrays of oil slinging passages defined by open channels formed in opposing end faces of the annular portion of the
oil slinger 10. A first set ofoil slinging channels 24 is provided in the axial end face 22 of theenlarged portion 20 of the annular portion of theoil slinger 10, extending between respective openings in the radially inner and outer surfaces of theenlarged portion 20. In the illustrated embodiment there are tenchannels 24 circumferentially spaced around theenlarged portion 20. Thechannels 24 do not extend exactly radially, but in this case are swept forward at a slight angle. - The second set of oil slinging passages comprises
channels 25 formed in theflange portion 19 of theoil slinger 10, each extending between a respective opening in the outer surface of theflange portion 19 and an opening into theannular slot 21. Again in this embodiment there are tenchannels 25 which are swept forward at a slight angle. - In operation the
oil slinger 10 seals the passage of theshaft 3 from the bearinghousing 4 into the compressor housing. The centralcylindrical body 18 of the oil slinger extends between the compressor wheel 1 and athrust collar 7a which is a part of thethrust bearing assembly 7. As mentioned above, the raised portion of theface 22 of the enlarged portion of theoil slinger 10 is in running engagement with theoil seal plate 9. Thechannels 24 thus sweep across the surface of thedisc 11 of theoil seal plate 9. Similarly, thechannels 25 formed in the opposing face of theannular portion 19 of theoil slinger 10 sweep across a surface of thethrust bearing 7. Rotation of theoil slinger channels oil seal plate 9 andoil slinger 10 is centrifugal accelerated by the rotation of theoil slinger channels seal plate flange 14 and the outer surface of the oil slinger 10). The displaced oil then drains away for re-circulation in a conventional manner. - The basic operation of the
oil slinger 10 of the present invention is essentially the same as that of prior art oil slingers. The fundamental difference between the present invention and the prior art, however, is that the oil slinging passages are formed by open channels as opposed to the radial holes provided in conventional oil slingers. By adopting an open channel configuration manufacture of the oil slinger is greatly simplified. In particular, it is possible to vary the exact configuration of the channels without difficulty whereas with conventional oil slingers in which the oil slinging passages are formed by holes drilled into the oil slinger it would be extremely difficult to deviate from a simple arrangement of exactly radially extending passages (as are found in the prior art). In contrast, with the present invention a number of features of the characteristics of the channels can be readily altered to “tune” the pumping characteristics of the oil slinger. For instance the channels can be angled relative to radial lines extending from the centre of the oil slinger as shown in the embodiment described above. The channels can thus be swept either forwards or backwards relative to the intended direction of rotation of the oil slinger. Similarly, curved channels could be employed rather than simple straight channels as illustrated. - In the illustrated embodiment the channels have parallel sides. As a further modification the sides could taper or the depth of each channel could increase or decrease along its length. It will also be appreciated that two or more of the aforementioned features could be combined and that neighbouring channels could have different configurations.
- There are a number of existing manufacturing techniques that could be readily employed in the production of oil slingers in accordance with the present invention including sintering and injection moulding techniques. Such techniques are relatively low cost compared to the machining required to produce conventional oil slinger designs. Oil slingers in accordance with the present invention can therefore be manufactured more cheaply and efficiently than existing oil slinger designs.
- A further advantage is that the open oil slinger channels are not subject to the same degree of stressing as the simple drilled holes of conventional oil slingers and can therefore be made more durable than conventional oil slingers.
- It will be appreciated that a number of modifications can be made to the specific example described, in addition to the possible features mentioned above. For instance, channels may be provided in one rather than both of the opposing faces of the annular portion of the oil slinger, and the number of channels in the or each array may vary from the number illustrated. The oil slinger illustrated is a discrete component but could be integral with other parts of the oil seal or thrust bearing assembly. For instance, the oil slinger could be integral with the
thrust bearing collar 7 a. In addition, the detailed configuration of theoil slinger 10 may vary, for instance to match varying configurations ofoil seal plate 9. Furthermore, in different turbocharger arrangements theoil slinger 10 may co-operate with a backplate of the compressor housing rather than with a separate oil seal plate as in the illustrated embodiment. - Other possible modifications will be readily apparent to the appropriately skilled person.
Claims (20)
1. An oil control device for incorporation in a system for sealing the passage of a rotating shaft through an opening, the oil control device comprising an annular member for rotation with said shaft and provided with a circumferentially spaced array of passages for centrifugally displacing fluid away from said shaft as it rotates, wherein said passages comprise channels which are open along their length.
2. An oil control device according to claim 1 , wherein said annular member defines at least one generally radially extending face in which a plurality of said channels are formed.
3. An oil control device according to claim 2 , wherein the annular member comprises a central cylindrical body portion and a surrounding annular portion, and wherein said at least one face is defined by said annular portion.
4. An oil control device according to claim 3 , wherein said at least one face is defined at an axial end of said annular portion.
5. An oil control device according to claim 4 , wherein said annular portion defines first and second oppositely facing axial end faces each of which is provided with an array of said channels.
6. An oil control device according to claim 5 , wherein said annular portion has an axially extending part which is radially spaced from said body portion defining an annular gap therebetween.
7. An oil control device according to claim 6 , wherein at least some of said channels in the or each face communicate with said annular gap.
8. An oil control device according to claim 1 , wherein at least one of said channels is substantially straight.
9. An oil control device according to claim 8 , wherein said substantially straight channel extends radially from the axis of rotation of the shaft and oil control device.
10. An oil control device according to claim 8 , wherein said straight channel is angularly off-set relative to radial lines extending from the axis of rotation of the oil control device, such that said channel is swept relative to the direction of rotation.
11. An oil control device according to claim 1 , wherein at least some of said channels are curvilinear.
12. An oil control device according to claim 11 , wherein said curvilinear channels have a constant radius of curvature.
13. An oil control device according to claim 11 , wherein said curvilinear channels have a radius of curvature which varies along the length of said channels in a direction away from the centre of axis of rotation.
14. An oil control device according to claim 13 , wherein said channels have a constant cross-sectional area.
15. An oil control device according to claim 13 , wherein the cross-sectional area of at least some of said channels varies along the length of the respective channel in a direction away from the axis rotation of the oil control device.
16. An oil control device according to claim 15 , wherein the width of said channels varies to give said varied cross-sectional area.
17. An oil control device according to claim 15 , wherein the depth of said channels varies to give said varying cross-sectional area.
18. A seal system according to claim 1 further comprising a turbocharger comprising a compressor housing and a bearing housing separated by a wall, a rotating shaft mounted on bearing systems housed within said bearing housing, said shaft extending through said wall into from the bearing housing into the compressor housing, said oil control device being mounted to said shaft on the bearing housing side of said wall to help prevent leakage of lubricant from the bearing housing into the compressor housing.
19. A turbocharger according to claim 18 , wherein said wall is a compressor back plate, adapted for mating co-operation with the oil control device.
20. A turbocharger according to claim 19 , wherein said oil control device has a first generally radially extending axial end face which is in running engagement with said plate, at least some of said channels being defined in said first end face.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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GBGB0108119.9A GB0108119D0 (en) | 2001-03-30 | 2001-03-30 | Oil control device |
GB0108119.9 | 2001-03-30 |
Publications (1)
Publication Number | Publication Date |
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US20020141862A1 true US20020141862A1 (en) | 2002-10-03 |
Family
ID=9911995
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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US10/109,430 Abandoned US20020141862A1 (en) | 2001-03-30 | 2002-03-28 | Oil control device |
Country Status (6)
Country | Link |
---|---|
US (1) | US20020141862A1 (en) |
EP (1) | EP1245793A1 (en) |
JP (1) | JP2002357273A (en) |
KR (1) | KR20020077259A (en) |
CN (1) | CN1379184A (en) |
GB (1) | GB0108119D0 (en) |
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US6935849B2 (en) | 2003-10-16 | 2005-08-30 | Honeywell International, Inc. | Grooved shaft member and associated turbocharger and method |
US20050084396A1 (en) * | 2003-10-16 | 2005-04-21 | Gutknecht Daniel A. | Grooved shaft member and associated turbocharger and method |
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US20070292263A1 (en) * | 2005-08-19 | 2007-12-20 | Honeywell International, Inc. | Output shaft air/oil separator to redundantly protect against output shaft o-ring leakage |
US8096774B2 (en) * | 2005-10-24 | 2012-01-17 | Borgwarner Inc. | Turbocharger |
US20080317596A1 (en) * | 2005-10-24 | 2008-12-25 | Borg Warner Inc. | Turbocharger |
US20100316485A1 (en) * | 2008-04-08 | 2010-12-16 | Ihi Corporation | Turbocharger |
US8794905B2 (en) * | 2008-04-08 | 2014-08-05 | Ihi Corporation | Turbocharger |
US20100000498A1 (en) * | 2008-07-03 | 2010-01-07 | Vortech Engineering, Inc. | Supercharger |
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US20110146224A1 (en) * | 2009-12-21 | 2011-06-23 | Rolls-Royce Deutschland Ltd & Co Kg | Arrangement for the discharge of oil-venting air on a gas-turbine engine |
US8826637B2 (en) * | 2009-12-21 | 2014-09-09 | Rolls-Royce Deutschland Ltd & Co Kg | Arrangement for the discharge of oil-venting air on a gas-turbine engine |
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US20140233873A1 (en) * | 2011-12-27 | 2014-08-21 | Mitsubishi Heavy Industries, Ltd. | Thrust bearing device for supercharger |
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US9309775B2 (en) * | 2012-05-21 | 2016-04-12 | United Technologies Corporation | Rotational debris discourager for gas turbine engine bearing |
US20130305684A1 (en) * | 2012-05-21 | 2013-11-21 | Jacob Peter Mastro | Debris discourager |
US9103231B2 (en) | 2012-06-28 | 2015-08-11 | Electro-Motive Diesel, Inc. | Bearing support for a turbocharger |
US9127690B2 (en) | 2012-06-28 | 2015-09-08 | Electro-Motive Diesel, Inc. | Turbocharger support housing having alignment features |
US10598184B2 (en) | 2012-06-29 | 2020-03-24 | Ihi Corporation | Turbocharger |
US9790950B2 (en) * | 2012-06-29 | 2017-10-17 | Ihi Corporation | Turbocharger |
US20150078884A1 (en) * | 2012-06-29 | 2015-03-19 | Ihi Corporation | Turbocharger |
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US9540950B2 (en) * | 2012-11-06 | 2017-01-10 | GM Global Technology Operations LLC | Oil deflector |
US20140127012A1 (en) * | 2012-11-06 | 2014-05-08 | GM Global Technology Operations LLC | Oil deflector |
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US10138813B2 (en) | 2013-09-30 | 2018-11-27 | Siemens Aktiengesellschaft | Oil bearing with drain system, gas turbine comprising such an oil bearing |
US20150280522A1 (en) * | 2014-03-31 | 2015-10-01 | Caterpillar Inc. | Electric machine having rotor cooling assembly |
USRE49234E1 (en) * | 2014-08-13 | 2022-10-04 | Lg Electronics Inc. | Scroll compressor |
USRE49074E1 (en) | 2014-08-13 | 2022-05-17 | Lg Electronics Inc. | Scroll compressor |
US20160326959A1 (en) * | 2014-12-09 | 2016-11-10 | Rolls-Royce Corporation | Oil flow enhancer bearing assembly |
US11015526B2 (en) * | 2014-12-09 | 2021-05-25 | Rolls-Royce Corporation | Oil flow enhancer bearing assembly |
US20160201727A1 (en) * | 2014-12-23 | 2016-07-14 | Cummins Ltd | Bearing assembly support |
US11078962B2 (en) * | 2014-12-23 | 2021-08-03 | Cummins Ltd. | Bearing assembly support |
US9163558B1 (en) * | 2015-03-11 | 2015-10-20 | Borgwarner Inc. | Complex path design of the flinger and insert |
US10975877B2 (en) * | 2015-06-05 | 2021-04-13 | Nuovo Pignone Srl | Combined bearing and turbomachine including said bearing |
US20180172015A1 (en) * | 2015-06-05 | 2018-06-21 | Nuovo Pignone Tecnologie Srl | Combined bearing and turbomachine including said bearing |
US9638203B2 (en) * | 2015-09-15 | 2017-05-02 | Borgwarner Inc. | Bearing housing |
US20190003337A1 (en) * | 2016-02-23 | 2019-01-03 | Ihi Charging Systems International Gmbh | Rotor assembly for an exhaust gas turbocharger |
US10495097B2 (en) * | 2016-12-12 | 2019-12-03 | Garrett Transporation I Inc. | Turbocharger assembly |
US20180163737A1 (en) * | 2016-12-12 | 2018-06-14 | Honeywell International Inc. | Turbocharger assembly |
US20190203635A1 (en) * | 2017-01-27 | 2019-07-04 | Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. | Lubricating device for bearing, and exhaust turbosupercharger |
US11066983B2 (en) * | 2017-01-27 | 2021-07-20 | Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. | Lubricating device for bearing, and exhaust turbosupercharger |
US10428928B2 (en) * | 2017-03-24 | 2019-10-01 | Hamilton Sundstrand Corporation | Lubrication system for high speed gearbox operating in zero gravity |
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Also Published As
Publication number | Publication date |
---|---|
KR20020077259A (en) | 2002-10-11 |
EP1245793A1 (en) | 2002-10-02 |
CN1379184A (en) | 2002-11-13 |
JP2002357273A (en) | 2002-12-13 |
GB0108119D0 (en) | 2001-05-23 |
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Legal Events
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