US20070110351A1 - Centering mechanisms for turbocharger bearings - Google Patents
Centering mechanisms for turbocharger bearings Download PDFInfo
- Publication number
- US20070110351A1 US20070110351A1 US11/281,735 US28173505A US2007110351A1 US 20070110351 A1 US20070110351 A1 US 20070110351A1 US 28173505 A US28173505 A US 28173505A US 2007110351 A1 US2007110351 A1 US 2007110351A1
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- United States
- Prior art keywords
- spring
- bearing
- housing
- free standing
- radial bias
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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
- 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
- F16C27/02—Sliding-contact bearings
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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
- F01D25/16—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
- F01D25/16—Arrangement of bearings; Supporting or mounting bearings in casings
- F01D25/166—Sliding contact 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
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/02—Parts of sliding-contact bearings
- F16C33/04—Brasses; Bushes; Linings
- F16C33/06—Sliding surface mainly made of metal
- F16C33/08—Attachment of brasses, bushes or linings to the bearing housing
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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
- 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
- F05D2230/00—Manufacture
- F05D2230/60—Assembly methods
- F05D2230/64—Assembly methods using positioning or alignment devices for aligning or centring, e.g. pins
-
- 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
- F05D2240/00—Components
- F05D2240/50—Bearings
- F05D2240/53—Hydrodynamic or hydrostatic bearings
-
- 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
- F05D2250/00—Geometry
- F05D2250/10—Two-dimensional
- F05D2250/18—Two-dimensional patterned
- F05D2250/184—Two-dimensional patterned sinusoidal
-
- 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
- F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
-
- 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
- F16C17/12—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load
- F16C17/18—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load with floating brasses or brushing, rotatable at a reduced speed
-
- 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
- F16C2226/00—Joining parts; Fastening; Assembling or mounting parts
- F16C2226/50—Positive connections
-
- 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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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T29/00—Metal working
- Y10T29/49—Method of mechanical manufacture
- Y10T29/49229—Prime mover or fluid pump making
- Y10T29/49236—Fluid pump or compressor making
Definitions
- Subject matter disclosed herein relates generally to turbomachinery for internal combustion engines and, in particular, bearings and components for use with bearings.
- Fully floating bearings rely on hydrodynamic films, in particular, an inner hydrodynamic film or films between the rotor shaft and the bearing and an outer hydrodynamic film or films between the bearing and the housing. Fully floating bearings can spin in the housing, typically, at between about 20 and about 40 percent of the rotor shaft speed. However, floating bearings can become unstable due to resonant frequencies in the shaft/bearing system driven by such rotation. To prevent such instabilities a semi-floating approach has been used.
- a bearing In a cylindrical coordinate system, a bearing may be defined with respect to radial, azimuthal and axial coordinates (e.g., r, ⁇ , z, respectively). See, e.g., Beyer, W. H., CRC Standard Mathematical Tables, 28th ed. Boca Raton, Fla.: CRC Press, p. 212, 1987.
- a semi-floating bearing Within a bearing housing, referred to as housing in subsequent text, a semi-floating bearing is normally located axially and azimuthally via one or more mechanisms. To prevent rotation (i.e., spinning in ⁇ ), a semi-floating bearing may employ a radial pin locating mechanism.
- Such a mechanism allows some movement in a radial direction along a radial line defined by the pin but prevents rotation of the bearing in the housing. While such a radial pin may provide for axial positioning as well, thrust forces can cause wear and misalignment issues; hence, other mechanisms are sometimes used for axial positioning (e.g., a pin oriented with its axis parallel to that of the bearing and fit into a notch in the end of the bearing).
- An exemplary spring for positioning a turbocharger bearing in a housing includes a free standing inner diameter, a free standing outer diameter and a substantially sinusoidal shape to provide an inward radial bias and to provide an outward radial bias wherein the spring balances the inward radial bias with the outward radial bias to thereby position a turbocharger bearing in a housing.
- Various exemplary springs, bearings, housings, assemblies, etc. are also disclosed.
- FIG. 1A is an end view of a prior art bearing for a turbocharger.
- FIG. 1B is a cross-sectional view of a prior art bearing in a prior art housing.
- FIG. 1C is a cross-sectional view of a prior art bearing in a prior art housing.
- FIG. 1D is an end view of a prior art bearing in a prior art housing.
- FIG. 2 is an end view of an exemplary assembly that includes a bearing positioned in a housing via an exemplary spring.
- FIG. 3 is a cross-sectional view of an exemplary assembly that includes a bearing positioned in a housing via two exemplary springs.
- FIG. 4 is a diagram of an exemplary spring, exemplary spring tangs and exemplary bearing features that cooperate with a spring.
- FIG. 5 is a diagram of an exemplary spring, exemplary spring tangs and exemplary bearing features that cooperate with a spring.
- FIG. 6 is an end view of an exemplary assembly that includes the exemplary spring of FIG. 4 .
- FIG. 7 is an end view of an exemplary assembly that includes the exemplary spring of FIG. 5 .
- FIG. 8A is a view of another exemplary spring.
- FIG. 8B is a view of yet another exemplary spring.
- FIG. 9 is an end view of an exemplary assembly that includes an exemplary spring mechanism and a side view of the exemplary spring mechanism.
- FIG. 10 is a cross-sectional view of an exemplary assembly that includes a bearing positioned in a housing via two exemplary cylindrical rings.
- FIG. 11A is a perspective view of an exemplary cylindrical ring of the assembly of FIG. 10 .
- FIG. 11B is a cross-sectional view of the exemplary cylindrical ring of FIG. 11A .
- FIG. 12 is a cross-sectional view of an exemplary assembly that includes a bearing positioned in a housing via two exemplary mesh rings.
- FIG. 13 is a cross-sectional view of an exemplary assembly that includes a bearing positioned in a housing via exemplary springs that aid in axial positioning of the bearing in the housing.
- FIG. 1A shows an end view of prior art bearing 100 , i.e., viewed in the r- ⁇ plane, where dashed lines represent various structural features.
- FIG. 1A also indicates a cross-section 1 B, which identifies the cross-section of the view of FIG. 1B .
- the bearing 100 includes a central bore 101 and various features that allow lubricant to flow to and from the bore 101 .
- the bearing 100 includes a pair of outer annular grooves or grind reliefs 104 , 104 ′ to promote lubricant flow.
- the grooves 104 , 104 ′ are referenced to define a center section 106 , a first outer section 110 and a second outer section 110 ′.
- the center section 106 of the bearing 100 includes a top opening 108 and a bottom opening 108 ′.
- the openings 108 , 108 ′ are disposed axially between the annular grooves 104 , 104 ′.
- Lubricant typically enters the bearing 100 from the top opening 108 and drains from the bottom opening 108 ′.
- Each of the outer sections 110 , 110 ′ includes a respective annular channel 116 , 116 ′.
- Each of the annular channels 116 , 116 ′ directs lubricant to a plurality of openings 118 , 118 ′.
- the openings 118 , 118 ′ allow lubricant to lubricate inner journals 120 , 120 ′, respectively.
- the openings 118 , 118 ′ are positioned at about 45°, 135°, 215° and 305°.
- the bearing 100 further includes an end notch 105 , which has a semi-circular section defined by a radius.
- the notch 105 is centered at an angle ⁇ N (e.g., about 112°) as measured from the bottom opening 108 ′.
- FIG. 1C shows a cross-sectional view of the prior art bearing 100 in a housing 160 .
- a radial pin 162 helps to position and prevent rotation of the bearing 100 . More specifically, the pin 162 acts to locate the bearing 100 axially and azimuthally while allowing freedom in the radial direction along the radial line of the pin 162 .
- Axial thrust load along the z-axis causes force to be transmitted from the bearing 100 to the housing 160 via the pin 162 .
- the pin allows for radial movement, some small amount of clearance exists between the outer diameter of the pin 162 and the inner diameter of the opening 108 . Consequently, during operation thrust may cause axial movement of the cartridge with respect to the housing. Such movement can contribute to wear and misalignment.
- lubricant may be oil such as an engine oil.
- the housing 160 includes lubricant inlets 163 , 163 ′ that direct lubricant toward the channels 116 , 116 ′ of the bearing 100 .
- the housing 160 includes an upper recess that, in conjunction with the bearing 100 , forms an upper chamber 164 that typically fills with lubricant during operation.
- the housing 160 also includes a lower recess that, in conjunction with the bearing 100 , forms a lower chamber 166 adjacent to a lubricant outlet 135 defined by the housing 160 .
- lubricant flows from the inlets 163 , 163 ′ to various regions (e.g., channels 116 , 116 ′, chambers 164 , 166 , etc.) and then to the outlet 165 .
- some small amount of lubricant may exits via small clearances between the ends of the bearing 100 and the housing 160 .
- the lower chamber 166 is substantially isolated from the upper chamber 164 to better direct lubricant to the inner journals 120 , 120 ′.
- the chambers 164 , 166 can have any of a variety of shapes, which are not explicitly shown in FIG. 1C or 1 D (see, e.g., conventional center housings).
- supplied lubricant flows from the inlets 163 , 163 ′ to the annular channels 116 , 116 ′ to the openings 118 , 118 ′ and to the journal surfaces 120 , 120 ′ of the bearing 100 .
- lubricant films are formed between the journal surfaces 120 , 120 ′ and the outer surface of the shaft where each lubricant film has a thickness determined by the diameter of a respective journal surface 120 , 120 ′ and an outer diameter of the shaft.
- Lubricant films are also formed between the bearing 100 and the housing 160 .
- films f, f′ are formed between the outer sections 110 , 110 ′ of the bearing 100 and the bore walls of the housing 160 .
- the films f, f′ act to dampen motion of the bearing 100 in the housing 160 .
- damping effectiveness of the films f, f′ varies as the bearing 100 moves in the bore of the housing 160 .
- the thickness of the films f, f′ varies as the bearing moves in the housing 160 .
- the thickness of such films is referred to as the squeeze film thickness.
- FIG. 1D is an end view of the prior art bearing 100 in the prior art housing 160 .
- the radial pin 162 cooperates with the opening 108 .
- a high degree of eccentricity may exist between the housing 160 and the bearing 100 . Consequently, lubricant films that form between the housing 160 and the bearing 100 may become uneven as the bearing nutates or rests in the housing.
- the weight of the rotor assembly causes the bearing to rest against the housing bore at essentially 100% eccentricity. Only upon dynamic motion does the bearing “pump up” (i.e., pressurize) the squeeze films that then move the bearing towards the center of the housing bore. If this action does not occur correctly, large motion or damage to the bearing can occur. This problem is particularly important for larger turbochargers owing to the manner in which rotor weight scales versus other parameters.
- various exemplary bearings or related components address primarily bearing/housing films (outer hydrodynamic films) as opposed to the aforementioned bearing/shaft films (inner hydrodynamic films).
- FIG. 2 shows an end view of a bearing 200 that relies on an exemplary spring 250 to locate the bearing 200 with respect to the housing 260 .
- a radial locating pin is not required, hence, the housing 260 does not require features associated with the pin of the housing 160 of FIG. 1B .
- the spring 250 allows for use of a housing having fewer features.
- the spring 250 balances an inward radial bias with an outward radial bias to position the bearing 200 in the housing 260 . More specifically, the arrows indicate directions of force exerted by the spring 250 to the bearing 200 and to the housing 260 . Such forces are sometimes referred to herein as radial support forces.
- the spring 250 e.g., spring constant, thickness, fixation mechanism, etc.
- it may be capable of substantially centering the bearing 200 in the housing 260 even when the turbocharger shaft is at rest.
- An exemplary spring optionally provides a low spring rate centering force to keep the bearing near the center of the bore of the housing under the weight of the rotor assembly.
- the spring rate may be purposely kept as low as possible to avoid increasing the overall rotor assembly support stiffness which can have a detrimental impact on shaft motion characteristics.
- dynamic forces can generate the hydrodynamic squeeze film to produce the desirable damping characteristics of a standard semi-floating bearing.
- the spring 250 acts to maintain a more even film thickness between the bearing 200 and the housing 260 (e.g., through radial support forces). Further, spring 250 provides resistance to flow of lubricant.
- spring 250 can help prevent undesirable levels of lubricant leakage at the ends of the bearing.
- the spring 250 can help prevent rotation of a bearing (e.g., via frictional forces between the spring(s) and the bearing and frictional forces between the spring(s) and the housing). Spring 250 is typically preloaded against the bearing and the housing bore and optionally preloaded with a force sufficient to avoid or reduce contact between the bearing 200 bearing and the housing 260 .
- FIG. 3 shows a cross-sectional view of an exemplary assembly whereby springs 250 , 250 ′ position bearing 200 , in a bore of a housing 260 .
- the bearing 250 has annular notches 205 , 205 ′ to seat the springs 250 , 250 ′, respectively.
- the springs 250 , 250 ′ may be oriented in any of a variety of manner with respect to the bearing 200 or the housing 260 , as indicated by open and shaded circles for the springs 250 , 250 ′.
- annular channels 216 , 216 ′ and the openings 218 , 218 ′ may differ, for example, as shown in other drawings.
- openings exist to allow lubricant to lubricate the journals 220 , 220 ′ and thereby form one or more bearing/shaft films.
- a specific example uses a spring 250 with a diameter of about 1 mm.
- a notch 205 of the bearing 200 has an axial length about twice that of the spring diameter (e.g., about 2 mm).
- These particular specifications may be used for a bearing having an axial length of about 30 mm and an outer diameter of about 14 mm.
- Such a bearing may have an inner diameter (e.g., central bore 201 ) of about 8.5 mm.
- FIG. 4 shows an exemplary spring 450 and various other features.
- Spring 450 is substantially planar, however, a spring may optionally includes at least part of a spiral (e.g., axial displacement or axial span).
- Spring 450 can be defined, in part, by a free inner diameter (D i ) and a free outer diameter (D o ).
- the exemplary spring 450 can be defined, in part, by one or more outer points 452 and one or more inner points 454 .
- the spring 450 has three inner points at the free standing inner diameter D i and three outer points at the free standing outer diameter D o .
- the spring 450 is sometimes referred to herein as a three-lobed spring that has a substantially smooth variation between inner and outer points (e.g., sinusoid).
- spring 450 when spring 450 is fitted to a bearing the one or more inner points contact the bearing. Positioned in a bore of a housing, the one or more outer points contact the housing. In such an assembly, spring 450 biases the bearing toward the axial center of the bore.
- Spring 450 optionally includes one or more tangs.
- Various exemplary tangs are shown. Tangs 462 , 462 ′ are oriented in substantially the same direction (e.g., perpendicular to a plane defined by the spring 450 , in the plane, etc.).
- a single tang 464 may be oriented in any of a variety of manners.
- Opposing tangs 462 , 466 are typically oriented perpendicular to a plane defined by the spring 450 and in opposite directions.
- Exemplary bearing features are also shown in FIG. 4 . These features cooperate with one or more of the aforementioned tangs.
- a groove 207 may include notches 282 , 282 ′ to accept one or more axially oriented tang.
- a bearing may include only one of the notches 282 , 282 ′.
- a groove 207 includes a radial notch 292 that may accept a radially directed tang.
- a bearing may include a combination of such notch features, which may be oriented axially, radially or at angles to thereby properly accommodate one or more tangs.
- a spring may have a circular, elliptical or rectangular cross section.
- the shape of the cross-section may be selected to provide a desired stiffness.
- a rectangular cross-section will have slightly higher stiffness than a circular cross-section given the same material of construction and approximately same cross-sectional area.
- a circular cross-section can provide for easier positioning on a bearing and/or positioning into the bore (e.g., consider that a circular cross-section may reduce sliding friction compared to a square cross-section).
- FIG. 5 shows an exemplary spring 550 and various other features.
- Spring 550 is substantially planar, however, a spring may optionally includes at least part of a spiral.
- Spring 550 can be defined, in part, by a free standing inner diameter (D i ) and a free standing outer diameter (D o ).
- spring 550 has four inner points at the free standing inner diameter D i and four outer points at the free standing outer diameter D o .
- Spring 550 is sometimes referred to herein as a four-lobed spring that has a substantially smooth variation between inner and outer points (e.g., sinusoid).
- springs with more lobes are possible (e.g., 5, 6, etc.).
- spring 550 when spring 550 is fitted to a bearing the one or more inner points contact the bearing and one or more outer points contact the housing. In such an assembly, the exemplary spring 550 biases the bearing toward the axial center of the housing.
- Spring 550 optionally includes one or more tangs, for example, similar to those described with respect to FIG. 4 .
- Exemplary bearing features are also shown in FIG. 5 , which are also similar to those described with reference to FIG. 4 .
- An exemplary spring may have a shape other than those shown in FIG. 4 and FIG. 5 while still retaining the general biasing concept. In general, the shape allows the spring to bias a bearing within a housing to thereby maintain a more even bearing/housing film thickness(es).
- FIG. 6 shows the exemplary spring 450 as part of an assembly that includes a bearing 200 and a housing 260 .
- the bearing 200 includes a notch diameter D N .
- the aforementioned free standing inner diameter D i is less than the notch diameter D N .
- the free standing outer diameter D o of the spring 450 may change once the spring 450 is fitted to the bearing 200 . Further, the outer diameter D o may exceed the bore diameter of the housing 260 .
- the spring 450 may be compressed to fit the bearing 200 and spring 450 into the bore of the housing 260 .
- the spring 450 includes a tang 464 that is seated in a notch 292 of the bearing 200 whereby the tang 464 and the notch 292 prevent the spring 450 from rotating about the bearing 200 .
- FIG. 7 shows the exemplary spring 550 as part of an exemplary assembly that includes an exemplary bearing 200 and an exemplary housing 260 .
- the features of FIG. 7 are similar to those of FIG. 6 except of course the number of lobes differs.
- FIG. 8A shows another exemplary spring 850 that has a free standing inner diameter D i .
- a gap exists in the spring 850 to facilitate installation.
- Such a spring optionally includes one or more tangs.
- the spring 850 includes several straight sections and several curved sections wherein the straight sections are tangent to D i and where the curved sections define a maximum diameter greater than D i .
- the gap exists along a curved section (e.g., approximately at the midpoint of a curved section).
- the three straight sections are tangent to the free standing inner diameter at approximately 0°, approximately 120°, and approximately 240°.
- FIG. 8B shows yet another exemplary spring 851 that has a free standing inner diameter D i .
- a larger gap exists in the spring 851 that in the spring 850 .
- Ends of the spring 851 are compressed toward the center during installation.
- characteristics of the ends e.g., angle and length
- the spring 851 also includes several straight sections and several curved sections. In this example, the straight sections are tangent to D i at approximately 0°, approximately 90° and approximately 180°.
- a spring may have any suitable spring rate, in one example, a spring has a static spring rate of approximately 2 lb/in (0.35 N/mm) to about 3 lb/in (0.53 N/mm). While a spring may have any suitable cross-section and associated dimension(s), in one example, a spring has a substantially circular cross-section and a diameter of about 0.036 in (1 mm). In one example, a spring with a static spring rate of about 2.8 lb/in (about 0.49 N/mm) and a diameter of about 0.036 in (about 1 mm) exerts a radial force of at least about 37 lb (about 165 N) to resist torque. Other examples are possible and may depend on features of a bearing, a housing, etc., and/or one or more operational conditions (e.g., steady-state operation, transient operation, rotational speed, etc.).
- An exemplary spring lies substantially in a plane (i.e., a substantially planar spring) and is suitable for positioning a turbocharger bearing in a housing.
- a spring may include a first end and a second end and a free standing inner diameter.
- FIGS. 8A and 8B such a spring may have a plurality of straight sections tangent to a free standing inner diameter and disposed between a first end and a second end wherein the straight sections provide an inward radial bias.
- a spring typically has one or more curved sections. For example, in FIGS.
- the springs include at least one curved section disposed between two of the straight sections to provide an outward radial bias. Regardless of the number of straight sections and/or curved sections, a spring typically balances an inward radial bias with an outward radial bias to thereby position a bearing in a housing. Where a free end exists, such an end may provide an outward radial bias.
- an exemplary spring may be seated in a annular groove or notch.
- partial grooves or notches are possible, for example, three separate grooves disposed at approximately 0°, approximately 120°, and approximately 240° may be used to seat the spring 850 of FIG. 8A .
- a groove has a diameter or radius that exceeds the free standing inner diameter or radius of a spring.
- An exemplary spring optionally includes one or more tangs. Such a tang or tangs may extend outward from a plane of a spring or lie in a plane of a spring.
- FIG. 9 shows an end view and a side view of another exemplary spring 950 where the end view shows the spring 950 as part of an assembly that includes a bearing 200 and a housing 260 .
- the spring 950 includes a ring member 952 that is machined or otherwise formed to create one or more tabs 956 , 956 ′, 956 ′′.
- the ring member 952 is optionally split to allow for installation on a bearing and/or to bias a bearing. With respect to machining, a rolling die is optionally used to cut slots into the ring member 952 to thereby form the tabs.
- the spring 950 is positioned in a groove or end notch 205 of the bearing 200 where the spring has five tabs 956 , 956 ′, 956 ′′, 956 ′′′, 956 ′′′′. These tabs bias the bearing 200 and the housing 260 as indicated by force arrows.
- material of construction is typically metal or alloy; however, other materials may suffice given constraints associated with operating conditions of a turbocharger.
- An exemplary spring includes a thin sheet metal ring with formed cantilever tangs to provide spring action.
- the spring is capable of operating correctly regardless of orientation.
- Such a spring can provide a “camming action” that resists bearing torque and thereby help frictional forces prevent rotation.
- FIG. 10 shows an exemplary assembly that includes a bearing 200 , a housing 260 and a pair of exemplary cylindrical rings 1050 , 1050 ′.
- the cylindrical rings 1050 provide for centering of the bearing 200 in the housing 260 .
- the pair of cylindrical rings 1050 , 1050 ′ sit in a pair of annular notches 207 , 207 ′ in the outer sections 210 , 210 ′ of the bearing 200 .
- Various features of the housing 260 are the same or similar to those described with respect to the housing 260 of FIG. 3 .
- the cylindrical rings 1050 , 1050 may be or include features of commercially available tolerance rings (e.g., tolerance rings marketed by Rencol Tolerance Rings, Bristol, UK). Such tolerance rings are often made from spring steel, stainless steel and other specialist spring materials.
- FIG. 11A shows a perspective view of the exemplary cylindrical ring 1050 .
- the exemplary cylindrical ring 1050 is split to allow for installation.
- the cylindrical ring 1050 may be manufactured by feeding a material to a rotating gear-like mechanism that deforms the material to form ridges and valleys.
- the material may be metal, alloy or other material.
- the cylindrical ring 1050 acts to position the bearing 200 in the housing 260 in a semi-floating manner.
- the cylindrical ring 1050 acts to resist lubricant flow axially toward the ends of the bearing 200 .
- the cylindrical rings 1050 , 1050 ′ have a diameter approximately equal to the diameter of the annular notches 207 , 207 ′. Overlap may occur whereby a peak sits in a valley; alternatively, a gap may exist once fitted to a bearing.
- FIG. 11B shows a cross-sectional view of the exemplary cylindrical ring 1050 along the line 11 B- 11 B of FIG. 11A .
- the cylindrical ring 1050 has a ring width W R , a height, a rise profile and a thickness.
- the dimensions may vary to provide a specific clearance between a bearing and a housing (i.e., a bearing/housing clearance).
- a specific example has a ring width W R of about 2 mm to about 3 mm.
- Such an exemplary ring may be fitted to a bearing having a notch width of about 2 mm to about 3 mm.
- An assembly may optionally include an exemplary mesh ring fitted to a bearing.
- a mesh ring may be formed of wire where the wire may be metal and/or other material.
- Commercially available knitted mesh materials such as the METEX® (Metex Corporation, N.J., USA) knitted mesh materials may be suitable for use as a mesh ring for a bearing as described herein.
- METEX® knitted mesh consists of wires of various metals or strands of other materials that have been knitted into a mesh structure. Structures of compressed knitted metal mesh yield to shock or vibration stresses but resume their original form when the force is relieved.
- a mesh ring may be resilient and capable of slight expansion for fitting to a bearing and compression for inserting such a bearing into the bore of a housing.
- FIG. 12 shows the assembly of FIG. 10 where the rings 1050 , 1050 ′ are replaced with mesh rings 1250 , 1250 ′.
- An exemplary mesh ring optionally has a rectangular cross-section similar to a piston ring suitable for use with a turbocharger center housing/bearing assembly. Other cross-sections are possible as well (e.g., circular, oval, etc.).
- a mesh ring can provide support to the bearing and shaft for centering without providing the majority of the stiffness and damping support. Further, such a ring can resist outward lubricant flow, which as described above, may cause leakage at the ends of a housing/bearing assembly.
- An exemplary assembly optionally includes one or more of the exemplary positioning mechanisms discussed herein (e.g., springs and cylindrical rings, a spring and a mesh ring, etc.).
- FIG. 13 shows an exemplary assembly that includes a bearing 1300 in the bore of a housing 1360 .
- the bearing 1300 includes various features as already discussed such as a bore 1301 , channels 1316 , 1316 ′, openings 1318 - 1318 ′′′′, etc.
- the housing 1360 includes various features as already discussed such as one or more lubricant inlets 1363 , 1363 ′, one or more lubricant outlets 1365 , etc. However, for purposes of axial position, the housing 1360 includes an annular notch 1365 and an associated annular plate 1395 or plate(s).
- the spring 1350 is at least partially seated in the notch 1365 and retaining mechanism 1395 to thereby limit axial movement of the bearing 1300 in the housing 1360 .
- Shear stress in such an example is acceptable for the spring 1350 .
- the characteristics of the spring 1350 ′ may differ from some of those of the spring 1350 .
- the spring 1350 may optionally have a larger outer diameter than that of the spring 1350 ′ or the spring 1350 may be thicker (e.g., a larger gauge) than the spring 1350 ′.
- the assembly optionally includes retaining mechanisms at both ends of the bearing and housing assembly.
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- Engineering & Computer Science (AREA)
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Abstract
An exemplary spring for positioning a turbocharger bearing in a housing includes a free standing inner diameter, a free standing outer diameter and a substantially sinusoidal shape to provide an inward radial bias and to provide an outward radial bias wherein the spring balances the inward radial bias with the outward radial bias to thereby position a turbocharger bearing in a housing. Various exemplary springs, bearings, housings, assemblies, etc., are also disclosed.
Description
- Subject matter disclosed herein relates generally to turbomachinery for internal combustion engines and, in particular, bearings and components for use with bearings.
- Advantages associated with low friction rotor bearings are well known in the field of turbomachinery where rotor speeds often exceed 100,000 RPM. Such high-speed applications, owing to the fact that rotor imbalance force increases as a square function of rotor speed, typically include a mechanism for radial damping of the rotor bearing. In addition, changes in operating conditions can generate significant axial thrust forces that act on a bearing; these forces should also be damped or absorbed.
- One type of low friction bearing is referred to as a fully floating bearing. Fully floating bearings rely on hydrodynamic films, in particular, an inner hydrodynamic film or films between the rotor shaft and the bearing and an outer hydrodynamic film or films between the bearing and the housing. Fully floating bearings can spin in the housing, typically, at between about 20 and about 40 percent of the rotor shaft speed. However, floating bearings can become unstable due to resonant frequencies in the shaft/bearing system driven by such rotation. To prevent such instabilities a semi-floating approach has been used.
- In a cylindrical coordinate system, a bearing may be defined with respect to radial, azimuthal and axial coordinates (e.g., r, Θ, z, respectively). See, e.g., Beyer, W. H., CRC Standard Mathematical Tables, 28th ed. Boca Raton, Fla.: CRC Press, p. 212, 1987. Within a bearing housing, referred to as housing in subsequent text, a semi-floating bearing is normally located axially and azimuthally via one or more mechanisms. To prevent rotation (i.e., spinning in Θ), a semi-floating bearing may employ a radial pin locating mechanism. Such a mechanism allows some movement in a radial direction along a radial line defined by the pin but prevents rotation of the bearing in the housing. While such a radial pin may provide for axial positioning as well, thrust forces can cause wear and misalignment issues; hence, other mechanisms are sometimes used for axial positioning (e.g., a pin oriented with its axis parallel to that of the bearing and fit into a notch in the end of the bearing).
- Overall, an industry need exists for bearing and bearing components housings that allow for better alignment and/or reduced wear. Various exemplary bearings, bearing components and housings presented herein address such issues.
- An exemplary spring for positioning a turbocharger bearing in a housing includes a free standing inner diameter, a free standing outer diameter and a substantially sinusoidal shape to provide an inward radial bias and to provide an outward radial bias wherein the spring balances the inward radial bias with the outward radial bias to thereby position a turbocharger bearing in a housing. Various exemplary springs, bearings, housings, assemblies, etc., are also disclosed.
- A more complete understanding of the various methods, devices, systems, arrangements, etc., described herein, and equivalents thereof, may be had by reference to the following detailed description when taken in conjunction with the accompanying drawings wherein:
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FIG. 1A is an end view of a prior art bearing for a turbocharger. -
FIG. 1B is a cross-sectional view of a prior art bearing in a prior art housing. -
FIG. 1C is a cross-sectional view of a prior art bearing in a prior art housing. -
FIG. 1D is an end view of a prior art bearing in a prior art housing. -
FIG. 2 is an end view of an exemplary assembly that includes a bearing positioned in a housing via an exemplary spring. -
FIG. 3 is a cross-sectional view of an exemplary assembly that includes a bearing positioned in a housing via two exemplary springs. -
FIG. 4 is a diagram of an exemplary spring, exemplary spring tangs and exemplary bearing features that cooperate with a spring. -
FIG. 5 is a diagram of an exemplary spring, exemplary spring tangs and exemplary bearing features that cooperate with a spring. -
FIG. 6 is an end view of an exemplary assembly that includes the exemplary spring ofFIG. 4 . -
FIG. 7 is an end view of an exemplary assembly that includes the exemplary spring ofFIG. 5 . -
FIG. 8A is a view of another exemplary spring. -
FIG. 8B is a view of yet another exemplary spring. -
FIG. 9 is an end view of an exemplary assembly that includes an exemplary spring mechanism and a side view of the exemplary spring mechanism. -
FIG. 10 is a cross-sectional view of an exemplary assembly that includes a bearing positioned in a housing via two exemplary cylindrical rings. -
FIG. 11A is a perspective view of an exemplary cylindrical ring of the assembly ofFIG. 10 . -
FIG. 11B is a cross-sectional view of the exemplary cylindrical ring ofFIG. 11A . -
FIG. 12 is a cross-sectional view of an exemplary assembly that includes a bearing positioned in a housing via two exemplary mesh rings. -
FIG. 13 is a cross-sectional view of an exemplary assembly that includes a bearing positioned in a housing via exemplary springs that aid in axial positioning of the bearing in the housing. - Various exemplary methods, devices, systems, arrangements, etc., disclosed herein address issues related to technology associated with turbochargers and are optionally suitable for use with electrically assisted turbochargers.
- For various drawings, a cylindrical coordinate system is used for reference that includes radial (r), axial (x) and azimuthal (Θ) dimensions.
FIG. 1A shows an end view of prior art bearing 100, i.e., viewed in the r-Θ plane, where dashed lines represent various structural features.FIG. 1A also indicates across-section 1B, which identifies the cross-section of the view ofFIG. 1B . - The
bearing 100 includes acentral bore 101 and various features that allow lubricant to flow to and from thebore 101. Thebearing 100 includes a pair of outer annular grooves orgrind reliefs grooves center section 106, a firstouter section 110 and a secondouter section 110′. - The
center section 106 of thebearing 100 includes a top opening 108 and a bottom opening 108′. Theopenings annular grooves top opening 108 and drains from thebottom opening 108′. - Each of the
outer sections annular channel annular channels openings openings inner journals bottom opening 108′ resides at about 0°, theopenings - The bearing 100 further includes an
end notch 105, which has a semi-circular section defined by a radius. Thenotch 105 is centered at an angle ΘN (e.g., about 112°) as measured from thebottom opening 108′. -
FIG. 1C shows a cross-sectional view of the prior art bearing 100 in ahousing 160. In this semi-floating bearing system, aradial pin 162 helps to position and prevent rotation of thebearing 100. More specifically, thepin 162 acts to locate thebearing 100 axially and azimuthally while allowing freedom in the radial direction along the radial line of thepin 162. Axial thrust load along the z-axis causes force to be transmitted from the bearing 100 to thehousing 160 via thepin 162. As the pin allows for radial movement, some small amount of clearance exists between the outer diameter of thepin 162 and the inner diameter of theopening 108. Consequently, during operation thrust may cause axial movement of the cartridge with respect to the housing. Such movement can contribute to wear and misalignment. - As described herein, lubricant may be oil such as an engine oil. With respect to lubricant flow, the
housing 160 includeslubricant inlets channels bearing 100. Thehousing 160 includes an upper recess that, in conjunction with thebearing 100, forms anupper chamber 164 that typically fills with lubricant during operation. Thehousing 160 also includes a lower recess that, in conjunction with thebearing 100, forms alower chamber 166 adjacent to a lubricant outlet 135 defined by thehousing 160. In such an arrangement, lubricant flows from theinlets channels chambers outlet 165. In addition, some small amount of lubricant may exits via small clearances between the ends of thebearing 100 and thehousing 160. In general, thelower chamber 166 is substantially isolated from theupper chamber 164 to better direct lubricant to theinner journals chambers FIG. 1C or 1D (see, e.g., conventional center housings). - Thus, in the arrangement of
FIG. 1C , supplied lubricant flows from theinlets annular channels openings bearing 100. When a shaft is presented, lubricant films are formed between the journal surfaces 120, 120′ and the outer surface of the shaft where each lubricant film has a thickness determined by the diameter of arespective journal surface - Lubricant films are also formed between the bearing 100 and the
housing 160. In particular, films f, f′ are formed between theouter sections bearing 100 and the bore walls of thehousing 160. The films f, f′ act to dampen motion of thebearing 100 in thehousing 160. However, damping effectiveness of the films f, f′ varies as the bearing 100 moves in the bore of thehousing 160. In particular, the thickness of the films f, f′ varies as the bearing moves in thehousing 160. Sometimes, the thickness of such films is referred to as the squeeze film thickness. -
FIG. 1D is an end view of the prior art bearing 100 in theprior art housing 160. As already explained, theradial pin 162 cooperates with theopening 108. However, given the nature of thepin 162 and theopening 108, a high degree of eccentricity may exist between thehousing 160 and thebearing 100. Consequently, lubricant films that form between thehousing 160 and thebearing 100 may become uneven as the bearing nutates or rests in the housing. - With respect to an at rest state, the weight of the rotor assembly (e.g., turbine, compressor wheel, shaft, etc.) causes the bearing to rest against the housing bore at essentially 100% eccentricity. Only upon dynamic motion does the bearing “pump up” (i.e., pressurize) the squeeze films that then move the bearing towards the center of the housing bore. If this action does not occur correctly, large motion or damage to the bearing can occur. This problem is particularly important for larger turbochargers owing to the manner in which rotor weight scales versus other parameters.
- As discussed herein, various exemplary bearings or related components (e.g., springs, housings, etc.) address primarily bearing/housing films (outer hydrodynamic films) as opposed to the aforementioned bearing/shaft films (inner hydrodynamic films).
- As mentioned in the Background, other prior art bearings include fully floating bearings where the bearing is allowed to spin in the housing bore. Such fully floating bearings can experience similar issues as the aforementioned semi-floating bearings (e.g., eccentric lubricant films). Various exemplary technologies discussed herein introduce one or more positioning mechanisms that can address various issues associated with prior art semi-floating and fully floating bearings.
- Various exemplary technologies presented herein allow for better centering of a bearing in a housing and, consequently, formation of a more even bearing/housing film or films.
FIG. 2 shows an end view of abearing 200 that relies on anexemplary spring 250 to locate thebearing 200 with respect to thehousing 260. In this example, a radial locating pin is not required, hence, thehousing 260 does not require features associated with the pin of thehousing 160 ofFIG. 1B . Thus, thespring 250 allows for use of a housing having fewer features. - As indicated by arrows, the
spring 250 balances an inward radial bias with an outward radial bias to position the bearing 200 in thehousing 260. More specifically, the arrows indicate directions of force exerted by thespring 250 to thebearing 200 and to thehousing 260. Such forces are sometimes referred to herein as radial support forces. Depending on the nature of the spring 250 (e.g., spring constant, thickness, fixation mechanism, etc.), when used in a turbocharger assembly, it may be capable of substantially centering thebearing 200 in thehousing 260 even when the turbocharger shaft is at rest. - An exemplary spring optionally provides a low spring rate centering force to keep the bearing near the center of the bore of the housing under the weight of the rotor assembly. Thus, the spring rate may be purposely kept as low as possible to avoid increasing the overall rotor assembly support stiffness which can have a detrimental impact on shaft motion characteristics. Further, in this example, dynamic forces can generate the hydrodynamic squeeze film to produce the desirable damping characteristics of a standard semi-floating bearing.
- In general, the
spring 250 acts to maintain a more even film thickness between the bearing 200 and the housing 260 (e.g., through radial support forces). Further,spring 250 provides resistance to flow of lubricant. Consider an example that includes twosprings 250 positioned near the ends of thebearing 200. In this example, thesprings 250 hinders axial flow of lubricant from the bearing/housing film. Such a mechanism can help prevent undesirable levels of lubricant leakage at the ends of the bearing. Yet further, thespring 250 can help prevent rotation of a bearing (e.g., via frictional forces between the spring(s) and the bearing and frictional forces between the spring(s) and the housing).Spring 250 is typically preloaded against the bearing and the housing bore and optionally preloaded with a force sufficient to avoid or reduce contact between the bearing 200 bearing and thehousing 260. -
FIG. 3 shows a cross-sectional view of an exemplary assembly whereby springs 250, 250′ position bearing 200, in a bore of ahousing 260. In this example, thebearing 250 hasannular notches springs springs bearing 200 or thehousing 260, as indicated by open and shaded circles for thesprings - As shown in
FIG. 3 ,lubricant inlets channels chamber 264 exists along a central section of thehousing 260; however, in this example, no pin is required and hence thehousing 260 does not include features to accommodate a locating pin. Alower chamber 266 exists along a central section of thehousing 260 and adjacent alubricant outlet 265. Thebearing 200 does not require a bottom opening such as theopening 108′ of thebearing 100. Thechambers housing 260 and thebearing 200. Further, theinlets outlet 265 may be located at positions other than those shown in the figures. A housing may have fewer or more inlets or outlets. - With respect to the
annular channels openings journals - With respect to dimensions, a specific example uses a
spring 250 with a diameter of about 1 mm. In this example, anotch 205 of thebearing 200 has an axial length about twice that of the spring diameter (e.g., about 2 mm). These particular specifications may be used for a bearing having an axial length of about 30 mm and an outer diameter of about 14 mm. Such a bearing may have an inner diameter (e.g., central bore 201) of about 8.5 mm. -
FIG. 4 shows anexemplary spring 450 and various other features.Spring 450 is substantially planar, however, a spring may optionally includes at least part of a spiral (e.g., axial displacement or axial span).Spring 450 can be defined, in part, by a free inner diameter (Di) and a free outer diameter (Do). Theexemplary spring 450 can be defined, in part, by one or moreouter points 452 and one or moreinner points 454. In the example ofFIG. 4 , thespring 450 has three inner points at the free standing inner diameter Di and three outer points at the free standing outer diameter Do. Thespring 450 is sometimes referred to herein as a three-lobed spring that has a substantially smooth variation between inner and outer points (e.g., sinusoid). - In general, when
spring 450 is fitted to a bearing the one or more inner points contact the bearing. Positioned in a bore of a housing, the one or more outer points contact the housing. In such an assembly,spring 450 biases the bearing toward the axial center of the bore. -
Spring 450 optionally includes one or more tangs. Various exemplary tangs are shown.Tangs spring 450, in the plane, etc.). Asingle tang 464 may be oriented in any of a variety of manners. Opposingtangs spring 450 and in opposite directions. - Exemplary bearing features are also shown in
FIG. 4 . These features cooperate with one or more of the aforementioned tangs. For example, agroove 207 may includenotches notches groove 207 includes aradial notch 292 that may accept a radially directed tang. A bearing may include a combination of such notch features, which may be oriented axially, radially or at angles to thereby properly accommodate one or more tangs. - A spring may have a circular, elliptical or rectangular cross section. Further, the shape of the cross-section may be selected to provide a desired stiffness. For example, a rectangular cross-section will have slightly higher stiffness than a circular cross-section given the same material of construction and approximately same cross-sectional area. However, in some instances, a circular cross-section can provide for easier positioning on a bearing and/or positioning into the bore (e.g., consider that a circular cross-section may reduce sliding friction compared to a square cross-section).
-
FIG. 5 shows anexemplary spring 550 and various other features.Spring 550 is substantially planar, however, a spring may optionally includes at least part of a spiral.Spring 550 can be defined, in part, by a free standing inner diameter (Di) and a free standing outer diameter (Do). In the example ofFIG. 5 ,spring 550 has four inner points at the free standing inner diameter Di and four outer points at the free standing outer diameter Do. Spring 550 is sometimes referred to herein as a four-lobed spring that has a substantially smooth variation between inner and outer points (e.g., sinusoid). Of course, springs with more lobes are possible (e.g., 5, 6, etc.). - In general, when
spring 550 is fitted to a bearing the one or more inner points contact the bearing and one or more outer points contact the housing. In such an assembly, theexemplary spring 550 biases the bearing toward the axial center of the housing.Spring 550 optionally includes one or more tangs, for example, similar to those described with respect toFIG. 4 . Exemplary bearing features are also shown inFIG. 5 , which are also similar to those described with reference toFIG. 4 . - An exemplary spring may have a shape other than those shown in
FIG. 4 andFIG. 5 while still retaining the general biasing concept. In general, the shape allows the spring to bias a bearing within a housing to thereby maintain a more even bearing/housing film thickness(es). -
FIG. 6 shows theexemplary spring 450 as part of an assembly that includes abearing 200 and ahousing 260. Thebearing 200 includes a notch diameter DN. In general, the aforementioned free standing inner diameter Di is less than the notch diameter DN. When thespring 450 is fitted to thebearing 200, preloading exists whereby thespring 450 biases thebearing 200 away from the walls of the housing. The free standing outer diameter Do of thespring 450 may change once thespring 450 is fitted to thebearing 200. Further, the outer diameter Do may exceed the bore diameter of thehousing 260. Thus, thespring 450 may be compressed to fit thebearing 200 andspring 450 into the bore of thehousing 260. - In this example, the
spring 450 includes atang 464 that is seated in anotch 292 of thebearing 200 whereby thetang 464 and thenotch 292 prevent thespring 450 from rotating about thebearing 200. -
FIG. 7 shows theexemplary spring 550 as part of an exemplary assembly that includes anexemplary bearing 200 and anexemplary housing 260. The features ofFIG. 7 are similar to those ofFIG. 6 except of course the number of lobes differs. -
FIG. 8A shows anotherexemplary spring 850 that has a free standing inner diameter Di. A gap exists in thespring 850 to facilitate installation. Such a spring optionally includes one or more tangs. Thespring 850 includes several straight sections and several curved sections wherein the straight sections are tangent to Di and where the curved sections define a maximum diameter greater than Di. In this example, the gap exists along a curved section (e.g., approximately at the midpoint of a curved section). Also, the three straight sections are tangent to the free standing inner diameter at approximately 0°, approximately 120°, and approximately 240°. -
FIG. 8B shows yet anotherexemplary spring 851 that has a free standing inner diameter Di. A larger gap exists in thespring 851 that in thespring 850. Ends of thespring 851 are compressed toward the center during installation. In this example, characteristics of the ends (e.g., angle and length) may be adjusted to provide proper biasing of a bearing in a housing. Thespring 851 also includes several straight sections and several curved sections. In this example, the straight sections are tangent to Di at approximately 0°, approximately 90° and approximately 180°. - While a spring may have any suitable spring rate, in one example, a spring has a static spring rate of approximately 2 lb/in (0.35 N/mm) to about 3 lb/in (0.53 N/mm). While a spring may have any suitable cross-section and associated dimension(s), in one example, a spring has a substantially circular cross-section and a diameter of about 0.036 in (1 mm). In one example, a spring with a static spring rate of about 2.8 lb/in (about 0.49 N/mm) and a diameter of about 0.036 in (about 1 mm) exerts a radial force of at least about 37 lb (about 165 N) to resist torque. Other examples are possible and may depend on features of a bearing, a housing, etc., and/or one or more operational conditions (e.g., steady-state operation, transient operation, rotational speed, etc.).
- An exemplary spring lies substantially in a plane (i.e., a substantially planar spring) and is suitable for positioning a turbocharger bearing in a housing. Such a spring may include a first end and a second end and a free standing inner diameter. As shown in
FIGS. 8A and 8B , such a spring may have a plurality of straight sections tangent to a free standing inner diameter and disposed between a first end and a second end wherein the straight sections provide an inward radial bias. As shown inFIGS. 2, 4 , 5, 6, 7, 8A and 8B, a spring typically has one or more curved sections. For example, inFIGS. 8A and 8B , the springs include at least one curved section disposed between two of the straight sections to provide an outward radial bias. Regardless of the number of straight sections and/or curved sections, a spring typically balances an inward radial bias with an outward radial bias to thereby position a bearing in a housing. Where a free end exists, such an end may provide an outward radial bias. - In an assembly, an exemplary spring may be seated in a annular groove or notch. Of course, partial grooves or notches are possible, for example, three separate grooves disposed at approximately 0°, approximately 120°, and approximately 240° may be used to seat the
spring 850 ofFIG. 8A . In general, a groove has a diameter or radius that exceeds the free standing inner diameter or radius of a spring. - An exemplary spring optionally includes one or more tangs. Such a tang or tangs may extend outward from a plane of a spring or lie in a plane of a spring.
-
FIG. 9 shows an end view and a side view of anotherexemplary spring 950 where the end view shows thespring 950 as part of an assembly that includes abearing 200 and ahousing 260. As shown in the side view, thespring 950 includes aring member 952 that is machined or otherwise formed to create one ormore tabs ring member 952 is optionally split to allow for installation on a bearing and/or to bias a bearing. With respect to machining, a rolling die is optionally used to cut slots into thering member 952 to thereby form the tabs. - As shown in the end view, the
spring 950 is positioned in a groove orend notch 205 of thebearing 200 where the spring has fivetabs bearing 200 and thehousing 260 as indicated by force arrows. As with other exemplary springs discussed herein, material of construction is typically metal or alloy; however, other materials may suffice given constraints associated with operating conditions of a turbocharger. - An exemplary spring includes a thin sheet metal ring with formed cantilever tangs to provide spring action. In such an example, where tangs are formed in alternating directions, the spring is capable of operating correctly regardless of orientation. Such a spring can provide a “camming action” that resists bearing torque and thereby help frictional forces prevent rotation.
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FIG. 10 shows an exemplary assembly that includes abearing 200, ahousing 260 and a pair of exemplarycylindrical rings bearing 200 in thehousing 260. In this example, the pair ofcylindrical rings annular notches outer sections bearing 200. Various features of thehousing 260 are the same or similar to those described with respect to thehousing 260 ofFIG. 3 . - The cylindrical rings 1050, 1050 may be or include features of commercially available tolerance rings (e.g., tolerance rings marketed by Rencol Tolerance Rings, Bristol, UK). Such tolerance rings are often made from spring steel, stainless steel and other specialist spring materials. A tolerance ring can be a frictional fastener capable of handling direct torque transfer, torque slip, axial retention, controlled collapse and radial loading between mating components. Peaks and valleys or waves act as radial springs and may be described by a spring formula: F=kΔr, where F is the force (e.g., N), k is the spring rate (e.g., Nm) and Δr is a radial distance by which a wave is compressed. Peak and valley shapes as well as material of construction and treatments can alter properties such as spring rate for a particular application.
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FIG. 11A shows a perspective view of the exemplarycylindrical ring 1050. The exemplarycylindrical ring 1050 is split to allow for installation. Thecylindrical ring 1050 may be manufactured by feeding a material to a rotating gear-like mechanism that deforms the material to form ridges and valleys. The material may be metal, alloy or other material. Thecylindrical ring 1050 acts to position the bearing 200 in thehousing 260 in a semi-floating manner. Thecylindrical ring 1050 acts to resist lubricant flow axially toward the ends of thebearing 200. - In the example of
FIG. 10 , thecylindrical rings annular notches -
FIG. 11B shows a cross-sectional view of the exemplarycylindrical ring 1050 along theline 11B-11B ofFIG. 11A . Thecylindrical ring 1050 has a ring width WR, a height, a rise profile and a thickness. The dimensions may vary to provide a specific clearance between a bearing and a housing (i.e., a bearing/housing clearance). A specific example has a ring width WR of about 2 mm to about 3 mm. Such an exemplary ring may be fitted to a bearing having a notch width of about 2 mm to about 3 mm. - An assembly may optionally include an exemplary mesh ring fitted to a bearing. A mesh ring may be formed of wire where the wire may be metal and/or other material. Commercially available knitted mesh materials such as the METEX® (Metex Corporation, N.J., USA) knitted mesh materials may be suitable for use as a mesh ring for a bearing as described herein. For example, METEX® knitted mesh consists of wires of various metals or strands of other materials that have been knitted into a mesh structure. Structures of compressed knitted metal mesh yield to shock or vibration stresses but resume their original form when the force is relieved. Thus, a mesh ring may be resilient and capable of slight expansion for fitting to a bearing and compression for inserting such a bearing into the bore of a housing.
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FIG. 12 shows the assembly ofFIG. 10 where therings mesh rings - An exemplary assembly optionally includes one or more of the exemplary positioning mechanisms discussed herein (e.g., springs and cylindrical rings, a spring and a mesh ring, etc.).
- Various exemplary positioning mechanisms optionally operate to position a bearing axially.
FIG. 13 shows an exemplary assembly that includes a bearing 1300 in the bore of ahousing 1360. The bearing 1300 includes various features as already discussed such as abore 1301,channels housing 1360 includes various features as already discussed such as one ormore lubricant inlets more lubricant outlets 1365, etc. However, for purposes of axial position, thehousing 1360 includes anannular notch 1365 and an associatedannular plate 1395 or plate(s). In this example, thespring 1350 is at least partially seated in thenotch 1365 andretaining mechanism 1395 to thereby limit axial movement of the bearing 1300 in thehousing 1360. Shear stress in such an example is acceptable for thespring 1350. Further, the characteristics of thespring 1350′ may differ from some of those of thespring 1350. For example, thespring 1350 may optionally have a larger outer diameter than that of thespring 1350′ or thespring 1350 may be thicker (e.g., a larger gauge) than thespring 1350′. The assembly optionally includes retaining mechanisms at both ends of the bearing and housing assembly. - Although some exemplary methods, devices, systems arrangements, etc., have been illustrated in the accompanying Drawings and described in the foregoing Detailed Description, it will be understood that the exemplary embodiments disclosed are not limiting, but are capable of numerous rearrangements, modifications and substitutions without departing from the spirit set forth and defined by the following claims.
Claims (20)
1. A substantially planar spring for positioning a turbocharger bearing in a housing, the spring comprising:
a first end and a second end;
a free standing inner diameter;
a plurality of straight sections tangent to the free standing inner diameter and disposed between the first end and the second end to provide an inward radial bias; and
a curved section disposed between two of the straight sections to provide an outward radial bias wherein the spring balances the inward radial bias with the outward radial bias to thereby position a turbocharger bearing in a housing.
2. The spring of claim 1 wherein the plurality of straight sections comprises three straight sections.
3. The spring of claim 2 further comprising another curved section disposed between two of the straight sections to provide an outward radial bias.
4. The spring of claim 1 wherein from the first end to the second end, the spring comprises a first curved section, a first straight section, a second curved section, a second straight section, a third curved section, a third straight section and a fourth curved section.
5. The spring of claim 4 wherein the straight sections comprise straight sections tangent to the free standing inner diameter to provide an inward radial bias.
6. The spring of claim 4 wherein the curved sections provide an outward radial bias.
7. The spring of claim 4 wherein the three straight sections are tangent to the free standing inner diameter at approximately 0°, approximately 120°, and approximately 240°.
8. The spring of claim 4 wherein the three straight sections are tangent to the free standing inner diameter at approximately 0°, approximately 90° and approximately 180°.
9. The spring of claim 1 wherein at least one of the first end and the second end provide an outward radial bias.
10. An assembly comprising the spring of claim 1 and a turbocharger bearing wherein the turbocharger bearing comprises an annular groove having a diameter that exceeds the free standing inner diameter of the spring.
11. The spring of claim 1 further comprising a tang.
12. The spring of claim 1 further comprising a free standing outer diameter.
13. The spring of claim 1 wherein the curved section defines in part a free standing outer diameter.
14. An assembly comprising:
a bearing that comprises an annular end notch; and
the spring of claim 1 seated in the annular end notch.
15. The assembly of claim 14 further comprising a housing wherein the housing comprises a bore and an annular end notch for seating the spring.
16. A substantially planar spring for positioning a turbocharger bearing in a housing, the spring comprising:
a free standing inner diameter;
a free standing outer diameter;
a substantially sinusoidal shape to provide an inward radial bias and to provide an outward radial bias wherein the spring balances the inward radial bias with the outward radial bias to thereby position a turbocharger bearing in a housing.
17. The spring of claim 16 further comprising one or more straight sections.
18. The spring of claim 16 wherein the sinusoidal shape comprises three or more lobes.
19. An assembly comprising:
a bearing;
a center housing of a turbocharger that comprises a bore;
one or more mesh rings fitted to the bearing to thereby center the bearing in the bore of the center housing.
20. The assembly of claim 19 wherein the one or more mesh rings comprise wire mesh.
Priority Applications (7)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US11/281,735 US20070110351A1 (en) | 2005-11-16 | 2005-11-16 | Centering mechanisms for turbocharger bearings |
EP06837447.9A EP1957758B1 (en) | 2005-11-16 | 2006-11-13 | Assembly comprising a turbocharger bearing housing and a semi-floating bearing |
PCT/US2006/043994 WO2007059036A2 (en) | 2005-11-16 | 2006-11-13 | Centering mechanisms for turbocharger bearings |
EP11159465.1A EP2392783B1 (en) | 2005-11-16 | 2006-11-13 | Turbocharger with squeeze film damper bearing and centering springs |
US12/536,710 US7766550B2 (en) | 2005-11-16 | 2009-08-06 | Centering mechanisms for turbocharger bearings |
US12/820,429 US8226296B2 (en) | 2005-11-16 | 2010-06-22 | Centering mechanisms for turbocharger bearings |
US13/555,133 US8449190B2 (en) | 2005-11-16 | 2012-07-21 | Centering mechanisms for turbocharger bearings |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US11/281,735 US20070110351A1 (en) | 2005-11-16 | 2005-11-16 | Centering mechanisms for turbocharger bearings |
Related Child Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US12/536,710 Division US7766550B2 (en) | 2005-11-16 | 2009-08-06 | Centering mechanisms for turbocharger bearings |
Publications (1)
Publication Number | Publication Date |
---|---|
US20070110351A1 true US20070110351A1 (en) | 2007-05-17 |
Family
ID=37831476
Family Applications (4)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US11/281,735 Abandoned US20070110351A1 (en) | 2005-11-16 | 2005-11-16 | Centering mechanisms for turbocharger bearings |
US12/536,710 Active US7766550B2 (en) | 2005-11-16 | 2009-08-06 | Centering mechanisms for turbocharger bearings |
US12/820,429 Active US8226296B2 (en) | 2005-11-16 | 2010-06-22 | Centering mechanisms for turbocharger bearings |
US13/555,133 Active US8449190B2 (en) | 2005-11-16 | 2012-07-21 | Centering mechanisms for turbocharger bearings |
Family Applications After (3)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US12/536,710 Active US7766550B2 (en) | 2005-11-16 | 2009-08-06 | Centering mechanisms for turbocharger bearings |
US12/820,429 Active US8226296B2 (en) | 2005-11-16 | 2010-06-22 | Centering mechanisms for turbocharger bearings |
US13/555,133 Active US8449190B2 (en) | 2005-11-16 | 2012-07-21 | Centering mechanisms for turbocharger bearings |
Country Status (3)
Country | Link |
---|---|
US (4) | US20070110351A1 (en) |
EP (2) | EP2392783B1 (en) |
WO (1) | WO2007059036A2 (en) |
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Citations (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2886354A (en) * | 1950-02-02 | 1959-05-12 | Bjorklund Gustaf Erik | Fasteners |
US2987349A (en) * | 1959-07-30 | 1961-06-06 | Gilbert Co A C | Self aligning bearing |
US3043636A (en) * | 1960-06-29 | 1962-07-10 | Thompson Ramo Wooldridge Inc | Bearing for high speed rotating shafts |
US3263907A (en) * | 1962-12-24 | 1966-08-02 | Garrett Corp | Gas turbine |
US3319484A (en) * | 1965-07-21 | 1967-05-16 | Clarostat Mfg Co Inc | Means for coupling shaft and bushing |
US3985458A (en) * | 1972-04-28 | 1976-10-12 | Roberts Industries, Inc. | Locking device |
US4415281A (en) * | 1981-11-23 | 1983-11-15 | United Technologies Corporation | Hydrodynamic fluid film bearing |
US4474484A (en) * | 1982-08-02 | 1984-10-02 | Roto-Master Inc. | Semi-floating bearing |
US4552466A (en) * | 1984-04-24 | 1985-11-12 | The United States Of America As Represented By The Administrator Of The National Aeronautics And Space Administration | Compliant hydrodynamic fluid journal bearing |
US4601590A (en) * | 1984-08-31 | 1986-07-22 | Ube Industries | Floating bush bearing |
US5230787A (en) * | 1991-12-30 | 1993-07-27 | Xerox Corporation | Spring and process for making a spring for a fluid bearing by electroforming |
US5634723A (en) * | 1995-06-15 | 1997-06-03 | R & D Dynamics Corporation | Hydrodynamic fluid film bearing |
US6449950B1 (en) * | 2000-09-12 | 2002-09-17 | Honeywell International Inc. | Rotor and bearing system for electrically assisted turbocharger |
US20030179961A1 (en) * | 2000-08-03 | 2003-09-25 | Horst Moshammer | Floating bearing |
US6964522B2 (en) * | 2004-01-22 | 2005-11-15 | Honeywell International Inc. | Hydrodynamic journal foil bearing system |
US20070047858A1 (en) * | 2005-08-31 | 2007-03-01 | Honeywell International, Inc. | Foil journal bearing with bilinear stiffness spring |
Family Cites Families (25)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3061386A (en) * | 1961-10-04 | 1962-10-30 | Star Kugelhalter Gmbh Dt | Tolerance rings |
US3122399A (en) * | 1962-04-11 | 1964-02-25 | David U Hunter | Self-balancing bearing construction |
GB1114568A (en) | 1964-07-16 | 1968-05-22 | Union Carbide Corp | Gas-bearing assembly |
GB1175470A (en) * | 1968-08-23 | 1969-12-23 | Ford Motor Co | Spring Loaded Bearing |
US3592517A (en) * | 1969-04-08 | 1971-07-13 | Rotron Inc | Bearing mounting arrangement |
US3980352A (en) * | 1973-05-11 | 1976-09-14 | Tribotech Incorporated | Spring bearing assembly |
FR2271443B2 (en) * | 1974-01-23 | 1977-06-10 | Pitner Alfred | |
DE2838768C3 (en) * | 1978-09-06 | 1981-02-19 | Dornier System Gmbh, 7990 Friedrichshafen | Multi-surface plain bearings |
CH658499A5 (en) * | 1982-05-26 | 1986-11-14 | Bbc Brown Boveri & Cie | Resilient supporting device for shaft bearings of high-speed rotors, in particular those of turbo machines |
US5055009A (en) * | 1989-12-12 | 1991-10-08 | Allied-Signal Inc. | Turbocharger with improved roller bearing shaft support |
DE4109481C2 (en) | 1991-03-22 | 1994-01-13 | Loehr & Bromkamp Gmbh | Snap ring |
US5890881A (en) * | 1996-11-27 | 1999-04-06 | Alliedsignal Inc. | Pressure balanced turbocharger rotating seal |
JPH112240A (en) * | 1997-06-10 | 1999-01-06 | Ishikawajima Harima Heavy Ind Co Ltd | Squeeze film damper bearing |
US5921683A (en) * | 1997-09-12 | 1999-07-13 | United Technologies Corporation | Bearing arrangement for air cycle machine |
JP4426049B2 (en) * | 1999-03-31 | 2010-03-03 | エドワーズ株式会社 | Magnetic bearing device and vacuum pump |
US6424066B1 (en) * | 1999-11-12 | 2002-07-23 | Camco International, Inc. | System for reducing wear and improving longevity of a electric submergible pumping system |
JP3536022B2 (en) * | 2000-10-04 | 2004-06-07 | ミネベア株式会社 | Pivot bearing device |
GB0025248D0 (en) * | 2000-10-13 | 2000-11-29 | Holset Engineering Co | A turbine |
US6811315B2 (en) * | 2002-12-18 | 2004-11-02 | Pratt & Whitney Canada Corp. | Compliant support for increased load capacity axial thrust bearing |
DE10314202B4 (en) * | 2003-03-28 | 2005-07-07 | Shaft-Form-Engineering Gmbh | circlip |
US7108488B2 (en) * | 2004-03-26 | 2006-09-19 | Honeywell International, Inc. | Turbocharger with hydrodynamic foil bearings |
US7214037B2 (en) * | 2004-06-28 | 2007-05-08 | Honeywell International, Inc. | Retention of ball bearing cartridge for turbomachinery |
US7104693B2 (en) * | 2004-06-28 | 2006-09-12 | Honeywell International, Inc. | Multi-thickness film layer bearing cartridge and housing |
US7753591B2 (en) * | 2005-06-30 | 2010-07-13 | Honeywell International Inc. | Turbocharger bearing and associated components |
US7648280B2 (en) * | 2007-04-12 | 2010-01-19 | Hamilton Sundstrand Corporation | Weight reduction for journal air bearing |
-
2005
- 2005-11-16 US US11/281,735 patent/US20070110351A1/en not_active Abandoned
-
2006
- 2006-11-13 EP EP11159465.1A patent/EP2392783B1/en active Active
- 2006-11-13 WO PCT/US2006/043994 patent/WO2007059036A2/en active Application Filing
- 2006-11-13 EP EP06837447.9A patent/EP1957758B1/en active Active
-
2009
- 2009-08-06 US US12/536,710 patent/US7766550B2/en active Active
-
2010
- 2010-06-22 US US12/820,429 patent/US8226296B2/en active Active
-
2012
- 2012-07-21 US US13/555,133 patent/US8449190B2/en active Active
Patent Citations (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2886354A (en) * | 1950-02-02 | 1959-05-12 | Bjorklund Gustaf Erik | Fasteners |
US2987349A (en) * | 1959-07-30 | 1961-06-06 | Gilbert Co A C | Self aligning bearing |
US3043636A (en) * | 1960-06-29 | 1962-07-10 | Thompson Ramo Wooldridge Inc | Bearing for high speed rotating shafts |
US3263907A (en) * | 1962-12-24 | 1966-08-02 | Garrett Corp | Gas turbine |
US3319484A (en) * | 1965-07-21 | 1967-05-16 | Clarostat Mfg Co Inc | Means for coupling shaft and bushing |
US3985458A (en) * | 1972-04-28 | 1976-10-12 | Roberts Industries, Inc. | Locking device |
US4415281A (en) * | 1981-11-23 | 1983-11-15 | United Technologies Corporation | Hydrodynamic fluid film bearing |
US4474484A (en) * | 1982-08-02 | 1984-10-02 | Roto-Master Inc. | Semi-floating bearing |
US4552466A (en) * | 1984-04-24 | 1985-11-12 | The United States Of America As Represented By The Administrator Of The National Aeronautics And Space Administration | Compliant hydrodynamic fluid journal bearing |
US4601590A (en) * | 1984-08-31 | 1986-07-22 | Ube Industries | Floating bush bearing |
US5230787A (en) * | 1991-12-30 | 1993-07-27 | Xerox Corporation | Spring and process for making a spring for a fluid bearing by electroforming |
US5634723A (en) * | 1995-06-15 | 1997-06-03 | R & D Dynamics Corporation | Hydrodynamic fluid film bearing |
US20030179961A1 (en) * | 2000-08-03 | 2003-09-25 | Horst Moshammer | Floating bearing |
US6449950B1 (en) * | 2000-09-12 | 2002-09-17 | Honeywell International Inc. | Rotor and bearing system for electrically assisted turbocharger |
US6964522B2 (en) * | 2004-01-22 | 2005-11-15 | Honeywell International Inc. | Hydrodynamic journal foil bearing system |
US20070047858A1 (en) * | 2005-08-31 | 2007-03-01 | Honeywell International, Inc. | Foil journal bearing with bilinear stiffness spring |
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US20080083397A1 (en) * | 2006-09-28 | 2008-04-10 | Jtekt Corporation | Supercharger |
US20100314959A1 (en) * | 2007-02-09 | 2010-12-16 | Jtekt Corporation | Rolling bearing device and electric generator |
EP2208903A3 (en) * | 2009-01-07 | 2012-11-21 | Honeywell International Inc. | Bearing and retention mechanisms |
CN102414421A (en) * | 2009-05-07 | 2012-04-11 | 博格华纳公司 | Spring clip method for anti-rotation and thrust constraint of rolling element bearing cartridge |
CN102414420A (en) * | 2009-05-07 | 2012-04-11 | 博格华纳公司 | Sliding clip method for anti-rotation and thrust constraint of a rolling element bearing cartridge |
US9068598B2 (en) | 2009-05-07 | 2015-06-30 | Borgwarner Inc. | Sliding clip method for anti-rotation and thrust constraint of a rolling element bearing cartridge |
KR101830817B1 (en) * | 2009-05-07 | 2018-02-21 | 보르그워너 인코퍼레이티드 | Spring clip method for anti-rotation and thrust constraint of a rolling element bearing cartridge |
US9068473B2 (en) | 2009-05-07 | 2015-06-30 | Borgwarner Inc. | Spring clip method for anti-rotation and thrust constraint of a rolling element bearing cartridge |
KR101838169B1 (en) * | 2009-05-07 | 2018-03-13 | 보르그워너 인코퍼레이티드 | Sliding clip method for anti-rotation and thrust constraint of a rolling element bearing cartridge |
US9140185B2 (en) * | 2009-11-24 | 2015-09-22 | Honeywell International Inc. | Locating mechanism for turbocharger bearing |
US20110120125A1 (en) * | 2009-11-24 | 2011-05-26 | Honeywell International | Locating Mechanism for Turbocharger Bearing |
WO2011138253A1 (en) * | 2010-05-06 | 2011-11-10 | Schaeffler Technologies Gmbh & Co. Kg | Rolling bearing device having a hydraulic damping device |
CN102884329A (en) * | 2010-05-06 | 2013-01-16 | 谢夫勒科技股份两合公司 | Rolling bearing device having a hydraulic damping device |
WO2012025531A1 (en) * | 2010-08-27 | 2012-03-01 | Schaeffler Technologies Gmbh & Co. Kg | Bearing |
KR101841239B1 (en) * | 2010-10-28 | 2018-05-04 | 보르그워너 인코퍼레이티드 | Rolling element bearing cartridge with axial thrust damping and anti-rotation assemblies |
WO2012079882A1 (en) * | 2010-12-17 | 2012-06-21 | Schaeffler Technologies AG & Co. KG | Bearing arrangement for a turbocharger |
CN103261721A (en) * | 2010-12-17 | 2013-08-21 | 谢夫勒科技股份两合公司 | Bearing unit for a turbocharger |
US9261105B2 (en) | 2010-12-17 | 2016-02-16 | Schaeffler Technologies AG & Co. KG | Bearing unit for a turbocharger |
WO2012079883A1 (en) * | 2010-12-17 | 2012-06-21 | Schaeffler Technologies AG & Co. KG | Bearing unit for a turbocharger |
EP2511543A1 (en) * | 2011-04-13 | 2012-10-17 | Kabushiki Kaisha Toyota Jidoshokki | Turbocharger |
US9400012B2 (en) | 2011-04-13 | 2016-07-26 | Kabushiki Kaisha Toyota Jidoshokki | Bearing structure of turbocharger |
CN104968896A (en) * | 2012-10-26 | 2015-10-07 | 博格华纳公司 | Fluid film hydrodynamic flexure pivot tilting pad semi-floating ring journal bearing with compliant dampers |
JP2015048756A (en) * | 2013-08-30 | 2015-03-16 | 株式会社Ihi | Rotor shaft support structure and supercharger |
US9797304B2 (en) | 2014-01-16 | 2017-10-24 | Bosch Mahle Turbo Systems Gmbh & Co. Kg | Exhaust gas turbocharger |
DE102014200743A1 (en) * | 2014-01-16 | 2015-07-16 | Bosch Mahle Turbo Systems Gmbh & Co. Kg | turbocharger |
US9004774B1 (en) * | 2014-04-08 | 2015-04-14 | Joseph S. Delgado | Ball bearing system for internal combustion engine turbochargers |
US10024361B2 (en) | 2014-07-09 | 2018-07-17 | Ihi Corporation | Bearing structure and turbocharger |
CN106662154A (en) * | 2014-07-09 | 2017-05-10 | 株式会社Ihi | Bearing structure and supercharger |
JPWO2016006459A1 (en) * | 2014-07-09 | 2017-04-27 | 株式会社Ihi | Bearing structure and turbocharger |
WO2016006459A1 (en) * | 2014-07-09 | 2016-01-14 | 株式会社Ihi | Bearing structure and supercharger |
US9488071B2 (en) | 2015-03-27 | 2016-11-08 | United Technologies Corporation | Piston ring anti-rotation |
EP3073136A1 (en) * | 2015-03-27 | 2016-09-28 | United Technologies Corporation | Squirrel cage and squeeze film damper bearing assembly with anti-rotation piston ring |
CN105937698A (en) * | 2016-06-28 | 2016-09-14 | 无锡市锡山区羊尖镇锦达商业设备厂 | Turbocharger floating bearing |
US11371388B2 (en) * | 2017-11-10 | 2022-06-28 | Mitsubishi Heavy Industries Marine Machinery & Equipment Co., Ltd. | Rotary machine and journal bearing |
CN109798156A (en) * | 2017-11-16 | 2019-05-24 | 曼恩能源方案有限公司 | Turbocharger |
US11280218B2 (en) | 2020-03-24 | 2022-03-22 | Borgwarner Inc. | Bearing housing assembly and turbocharger including the same |
Also Published As
Publication number | Publication date |
---|---|
US20120288224A1 (en) | 2012-11-15 |
EP1957758B1 (en) | 2016-01-13 |
EP1957758A2 (en) | 2008-08-20 |
US20100260450A1 (en) | 2010-10-14 |
US8226296B2 (en) | 2012-07-24 |
US7766550B2 (en) | 2010-08-03 |
EP2392783A3 (en) | 2012-04-25 |
US20090297082A1 (en) | 2009-12-03 |
WO2007059036A3 (en) | 2007-08-30 |
WO2007059036A2 (en) | 2007-05-24 |
US8449190B2 (en) | 2013-05-28 |
EP2392783A2 (en) | 2011-12-07 |
EP2392783B1 (en) | 2016-07-27 |
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