WO2015045813A1 - 焼結金属軸受、及びこの軸受を備えた流体動圧軸受装置 - Google Patents
焼結金属軸受、及びこの軸受を備えた流体動圧軸受装置 Download PDFInfo
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- WO2015045813A1 WO2015045813A1 PCT/JP2014/073554 JP2014073554W WO2015045813A1 WO 2015045813 A1 WO2015045813 A1 WO 2015045813A1 JP 2014073554 W JP2014073554 W JP 2014073554W WO 2015045813 A1 WO2015045813 A1 WO 2015045813A1
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- dynamic pressure
- bearing
- sintered metal
- metal bearing
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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
- F04D25/08—Units comprising pumps and their driving means the working fluid being air, e.g. for ventilation
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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
- F04D25/06—Units comprising pumps and their driving means the pump being electrically driven
- F04D25/0606—Units comprising pumps and their driving means the pump being electrically driven the electric motor being specially adapted for integration in the pump
- F04D25/0613—Units comprising pumps and their driving means the pump being electrically driven the electric motor being specially adapted for integration in the pump the electric motor being of the inside-out type, i.e. the rotor is arranged radially outside a central stator
- F04D25/062—Details of the bearings
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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
- F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
- F04D29/056—Bearings
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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
- F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
- F04D29/056—Bearings
- F04D29/057—Bearings hydrostatic; hydrodynamic
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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
- F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
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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
- F16C17/10—Sliding-contact bearings for exclusively rotary movement for both radial and axial load
- F16C17/102—Sliding-contact bearings for exclusively rotary movement for both radial and axial load with grooves in the bearing surface to generate hydrodynamic pressure
- F16C17/107—Sliding-contact bearings for exclusively rotary movement for both radial and axial load with grooves in the bearing surface to generate hydrodynamic pressure with at least one surface for radial load and at least one surface for axial load
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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
- 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
- F16C33/10—Construction relative to lubrication
- F16C33/1005—Construction relative to lubrication with gas, e.g. air, as lubricant
- F16C33/101—Details of the bearing surface, e.g. means to generate pressure such as lobes or wedges
- F16C33/1015—Pressure generating grooves
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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
- 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
- F16C33/10—Construction relative to lubrication
- F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
- F16C33/103—Construction relative to lubrication with liquid, e.g. oil, as lubricant retained in or near the bearing
- F16C33/104—Construction relative to lubrication with liquid, e.g. oil, as lubricant retained in or near the bearing in a porous body, e.g. oil impregnated sintered sleeve
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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
- 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
- F16C33/10—Construction relative to lubrication
- F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
- F16C33/109—Lubricant compositions or properties, e.g. viscosity
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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
- 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
- F16C33/12—Structural composition; Use of special materials or surface treatments, e.g. for rust-proofing
- F16C33/128—Porous bearings, e.g. bushes of sintered alloy
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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
- 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
- F16C33/14—Special methods of manufacture; Running-in
- F16C33/145—Special methods of manufacture; Running-in of sintered porous bearings
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- G—PHYSICS
- G11—INFORMATION STORAGE
- G11B—INFORMATION STORAGE BASED ON RELATIVE MOVEMENT BETWEEN RECORD CARRIER AND TRANSDUCER
- G11B19/00—Driving, starting, stopping record carriers not specifically of filamentary or web form, or of supports therefor; Control thereof; Control of operating function ; Driving both disc and head
- G11B19/20—Driving; Starting; Stopping; Control thereof
- G11B19/2009—Turntables, hubs and motors for disk drives; Mounting of motors in the drive
- G11B19/2036—Motors characterized by fluid-dynamic bearings
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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
- F05D2230/20—Manufacture essentially without removing material
- F05D2230/22—Manufacture essentially without removing material by sintering
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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
- F16C2202/00—Solid materials defined by their properties
- F16C2202/02—Mechanical properties
- F16C2202/10—Porosity
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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
- F16C2220/00—Shaping
- F16C2220/20—Shaping by sintering pulverised material, e.g. powder metallurgy
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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
- F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
- F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
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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
- F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
- F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
- F16C2240/70—Diameters; Radii
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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
- F16C2360/46—Fans, e.g. ventilators
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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
- F16C2361/00—Apparatus or articles in engineering in general
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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
- F16C2370/00—Apparatus relating to physics, e.g. instruments
- F16C2370/12—Hard disk drives or the like
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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
- F16C2380/00—Electrical apparatus
- F16C2380/26—Dynamo-electric machines or combinations therewith, e.g. electro-motors and generators
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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
- 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
- F16C33/10—Construction relative to lubrication
- F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
- F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
- F16C33/107—Grooves for generating pressure
Definitions
- the present invention relates to a sintered metal bearing and a fluid dynamic bearing device provided with the bearing.
- Sintered metal bearings are used by impregnating the internal pores with lubricating oil, and the lubricating oil impregnated inside with the relative rotation of the shaft inserted in the inner circumference is applied to the sliding portion with the shaft. It oozes out to form an oil film, and the shaft is rotated and supported through this oil film.
- Such sintered metal bearings are more specifically used as bearing devices for motors mounted on various electric equipments including information equipment because of their excellent rotational accuracy and quietness. More specifically, HDDs, CDs, and DVDs are used. It is suitably used as a bearing for a spindle motor in a disk drive device for a Blu-ray disc, or as a bearing for a polygon scanner motor, a fan motor or the like of a laser beam printer (LBP).
- LBP laser beam printer
- dynamic pressure grooves as dynamic pressure generating portions are arranged in a predetermined manner on the inner peripheral surface and / or the end surface of the bearing with the aim of further improving quietness and extending the service life. Things are known.
- so-called dynamic pressure groove sizing has been proposed as a method of forming the dynamic pressure grooves. This sizing is performed by, for example, pressing the sintered body into the inner periphery of the die and pressing it in the axial direction with the upper and lower punches, thereby firing the mold on the outer periphery of the sizing pin previously inserted into the inner periphery of the sintered body. Encroach the body.
- the shape of the molding die that is, the shape corresponding to the dynamic pressure groove is transferred to the inner peripheral surface of the sintered body, and the dynamic pressure groove is formed into a predetermined shape (see, for example, Patent Document 1).
- bubbles are generated by generating a negative pressure in the region, and there is a concern that the bearing performance may be deteriorated due to intrusion into the bearing gap and the buffer volume of the lubricating oil may be decreased due to the expansion of the bubbles.
- this bearing is a porous body formed by sintering a compression-molded raw material powder, and in the sintered metal bearing provided with the dynamic pressure generating portion on the inner peripheral surface, the dynamic pressure generating portion
- the dynamic pressure groove array region formed by arranging a plurality of dynamic pressure grooves inclined with respect to the circumferential direction is formed continuously in the axial direction, the axial dimension is 6 mm or less, and the entire bearing It is characterized by having a density ratio of 80% or more and 95% or less.
- the “density ratio” means a value (percentage) obtained by dividing the density of the porous body forming the sintered metal bearing by the density assuming that the porous body has no pores. .
- the density ratio of the entire bearing is set to a range of 80% or more and 95% or less
- the density ratio becomes uniform compared to the conventional case. It is made in view of the point to be done. That is, in the compacting process of this type of bearing, the raw material powder filled in the mold is pressed along the axial direction of the compact to be molded into a predetermined shape (usually cylindrical). It is common to do.
- the direct pressure side for example, the upper side in the axial direction
- the surface layer part in contact with the direct mold tends to become dense
- the pressure side or mold The side farther from for example, the lower side in the axial direction or the core of the green compact
- the axial dimension is reduced to 6 mm or less, and the density ratio is set to 80% or more and 95% or less (for example, the amount of compression of the raw material powder in the axial direction is adjusted) ),
- the difference in density ratio between the surface layer side and the core side and between the one side in the axial direction and the other side was found to be very small.
- the dynamic pressure groove array region is formed continuously in the axial direction and the recesses described in Patent Document 2, for example, are omitted, the bearing interior and the bearing clearance are provided via the bearing surface (dynamic pressure groove array region). Therefore, an appropriate lubricating fluid can be circulated.
- the dynamic pressure groove can be made longer than the conventional one because the region between the dynamic pressure groove arrangement regions is omitted, so that the dynamic pressure action can be further improved. it can.
- the sintered metal bearing according to the present invention may have a density ratio variation within the bearing of 3% or less. While setting the density ratio of the entire bearing in the above-mentioned range and keeping the variation in the density ratio inside the bearing within the above-mentioned range, the density ratio of the surface layer portion is prevented while preventing the escape of dynamic pressure from the bearing surface. It can be set to such an extent that the lubricating oil or the like can exude properly into the bearing gap. In addition, the density ratio of the region excluding the surface layer portion (region inside the surface layer portion) can be set so that the amount of the lubricating oil or the like impregnated by the inner region becomes an appropriate amount.
- the dynamic pressure groove array regions continuous in the axial direction have a herringbone shape, and the dynamic pressure grooves constituting each dynamic pressure groove array region are at the center side in the axial direction. It may be continuous.
- the sintered metal bearing according to the present invention may have an inner diameter of 3 mm or less and an outer diameter of 6 mm or less.
- the bearing rigidity measures can be taken with the axial dimension and its density ratio, the dimension in the radial direction can be maintained at the same level as the conventional one. Specifically, if the inner diameter dimension and the outer diameter dimension are within the above ranges, a corresponding springback amount in the radial direction can be obtained. Therefore, a dynamic pressure groove having a predetermined depth (several ⁇ m level) can be formed, and a required dynamic pressure effect can be expected.
- the sintered metal bearing according to the above description includes, for example, this sintered metal bearing, a shaft portion inserted through the inner periphery of the sintered metal bearing, a fixed side including the sintered metal bearing, and a rotating side including the shaft portion. It is also possible to suitably provide a fluid dynamic pressure bearing device including a seal space formed between the two and a lubricating oil filled in a bearing inner space including the inside of the sintered metal bearing.
- the lubricating oil has a kinematic viscosity at 40 ° C. of 20 cSt or more and 170 cSt or less, and a kinematic viscosity at 100 ° C. of 2 cSt or more and 50 cSt or less. It may be shown.
- the density ratio of the sintered metal bearing is adjusted to optimize its internal structure, and the lubricating oil is used with a relatively high viscosity depending on the application, thereby further improving the bearing performance. It contributes to improvement and can suppress the deterioration of the lubricating oil. Therefore, even when the thickness is reduced, it is possible to provide a high-performance and highly reliable fluid dynamic pressure bearing device.
- the fluid dynamic pressure bearing device can exhibit appropriate and stable bearing rigidity over a long period of time even when the weight of the rotating body is increased. Therefore, the fluid dynamic pressure bearing device is attached to the fluid dynamic pressure bearing device and the shaft portion. It can also be preferably provided as a fan motor including a fan.
- a sintered metal bearing can be provided.
- FIG. 3 It is a conceptual diagram of the fan motor which concerns on one Embodiment of this invention. It is sectional drawing of the fluid dynamic pressure bearing apparatus which comprises the motor of FIG. It is sectional drawing of the sintered metal bearing which concerns on one Embodiment of this invention. It is the figure which looked at the upper end surface of the sintered metal bearing shown in FIG. 3 from the axial direction upper side. It is the figure which looked at the lower end surface of the sintered metal bearing shown in FIG. 3 from the axial lower side. It is sectional drawing of the sintered metal bearing which concerns on other embodiment of this invention.
- the disk portion side of the hub portion is treated as “upper side” and the lid member side as “lower side” as viewed from the sintered metal bearing.
- this vertical direction does not limit the actual installation mode and usage mode of the product.
- FIG. 1 shows a schematic cross-sectional view of a fan motor 2 provided with a fluid dynamic pressure bearing device 1 according to the present invention and an information device 3 on which the fan motor 2 is mounted.
- the fan motor 2 is a so-called centrifugal type fan motor 2 and is attached to a base 4 of a component (information device 3) to be cooled.
- the fan motor 2 includes a fluid dynamic pressure bearing device 1, a plurality of fans 5 provided on the rotating member 9 of the fluid dynamic pressure bearing device 1, and a drive for rotating the fans 5 integrally with the rotating member 9.
- Part 6 The drive unit 6 includes, for example, a coil 6a and a magnet 6b that are opposed to each other via a gap in the radial direction.
- the coil 6a is on the fixed side (base 4)
- the magnet 6b is on the rotation side (the rotation member 9). It is fixed to the hub part 10) which comprises.
- each fan 5 When the coil 6a is energized, the magnet 6b is rotated by the exciting force between the coil 6a and the magnet 6b, thereby a plurality of sheets standing on the outer peripheral edge of the rotating member 9 (the hub portion 10 in this embodiment).
- the fan 5 rotates integrally with the rotating member 9. By this rotation, each fan 5 generates an air flow outward in the outer diameter direction, and is drawn into the air flow, so that the intake air flows downward in the axial direction from the hole 4a of the base 4 provided on the upper side in the axial direction of the fan motor 2. Arises towards. By generating an air flow inside the information device 3 in this way, the heat generated inside the information device 3 can be released (cooled) to the outside.
- FIG. 2 shows a cross-sectional view of the fluid dynamic bearing device 1 incorporated in the fan motor 2.
- the fluid dynamic pressure bearing device 1 mainly includes a housing 7, a sintered metal bearing 8 fixed to the inner periphery of the housing 7, and a rotating member 9 that rotates relative to the sintered metal bearing 8. Yes.
- the rotating member 9 has a hub portion 10 disposed on the upper end opening side of the housing 7 and a shaft portion 11 inserted into the inner periphery of the sintered metal bearing 8.
- the hub portion 10 is located on the outer diameter side of the disc portion 10a that covers the upper end opening side of the housing 7, the first tubular portion 10b that extends downward from the disc portion 10a in the axial direction, and the first tubular portion 10b.
- the second cylindrical portion 10c extends downward from the disk portion 10a in the axial direction, and the flange portion 10d extends further from the lower end in the axial direction of the second cylindrical portion 10c to the outer diameter side.
- the disk portion 10 a faces one end surface (upper end surface 8 b) of the sintered metal bearing 8 fixed to the inner periphery of the housing 7.
- the plurality of fans 5 are provided integrally with the hub portion 10 so as to stand up from the outer peripheral edge of the flange portion 10d.
- the shaft portion 11 is formed integrally with the hub portion 10 in this embodiment, and has a flange portion 12 at the lower end thereof.
- the upper end surface 12 a of the flange portion 12 faces the other end surface (lower end surface 8 c) of the sintered metal bearing 8.
- the shaft portion 11 can be formed separately from the hub portion 10, and in this case, the upper end of the shaft portion 11 is fixed to a hole provided in the center of the hub portion 10 by means such as press fitting or adhesion. Is also possible.
- one of the shaft portion 11 and the hub portion 10 formed of different materials can be formed as an insert part, and the other can be formed by injection molding of metal or resin. *
- the housing 7 has a cylindrical shape with both axial ends open, and the lower end opening side is sealed with a lid member 13.
- the inner peripheral surface 7 a of the housing 7 is fixed to the sintered metal bearing 8, and the outer peripheral surface 7 b is fixed to the base 4 of the information device 3.
- the axial spacing between the upper end surface 7c of the housing 7 and the lower end surface 10a1 of the disc portion 10a of the hub portion 10 is greater than the facing interval between the upper end surface 8b of the sintered metal bearing 8 and the lower end surface 10a1 of the disc portion 10a.
- it is set to such a size that it can be regarded as substantially not affecting the increase in loss torque during rotational driving.
- a tapered seal surface 7d having an outer diameter that increases upward is formed on the upper outer periphery of the housing 7.
- the tapered seal surface 7d is gradually reduced in size in the radial direction from the closed side (downward) to the open side (upward) of the housing 7 between the inner peripheral surface 10b1 of the first cylindrical portion 10b.
- An annular seal space S is formed. This seal space S communicates with the outer diameter side of the thrust bearing gap of the first thrust bearing portion T1 described later when the shaft portion 11 and the hub portion 10 are rotated, and is between the bearing inner space including each bearing gap. This makes it possible to distribute lubricating oil.
- the filling amount of the lubricating oil is adjusted so that the oil surface (gas-liquid interface) of the lubricating oil is always maintained in the seal space S (see FIG. 2). reference).
- the sintered metal bearing 8 is formed by compressing a raw material powder mainly composed of a metal such as copper (including not only pure copper but also a copper alloy) and iron (including not only pure iron but also an iron alloy such as stainless steel). It is a porous body of sintered metal obtained by sintering, and generally has a cylindrical shape. A region where a plurality of dynamic pressure grooves 8a1 are arranged as a dynamic pressure generating portion is formed on the whole or a part of the inner peripheral surface 8a of the sintered metal bearing 8. In the present embodiment, as shown in FIG.
- the dynamic pressure groove array region includes a plurality of dynamic pressure grooves 8a1 inclined at a predetermined angle with respect to the circumferential direction, and the dynamic pressure grooves 8a1 are partitioned in the circumferential direction.
- Herring the inclined hill portion 8a2 that extends and the belt portion 8a3 that extends in the circumferential direction and divides each dynamic pressure groove 8a1 in the axial direction both the inclined hill portion 8a2 and the belt portion 8a3 are cross-hatched in FIG. 3). It is arranged in a bone shape and is formed at two locations in the axial direction.
- the upper dynamic pressure groove array region A1 and the lower dynamic pressure groove array region A2 are both axial with respect to the axial center line (the imaginary line connecting the axial center of the belt portion 8a3 in the circumferential direction). They are formed symmetrically, and their axial dimensions are equal to each other.
- a region where a plurality of dynamic pressure grooves 8b1 as dynamic pressure generating portions are arranged is formed on the entire upper surface 8b of the sintered metal bearing 8 or a part thereof.
- a region in which a plurality of dynamic pressure grooves 8b1 extending in a spiral shape are arranged in the circumferential direction is formed.
- the direction of the spiral of the dynamic pressure groove 8b1 is set to the direction corresponding to the rotation direction of the rotating member 9.
- the dynamic pressure groove arrangement region having the above-described configuration is a first thrust described later between the lower end surface 10a1 of the disk portion 10a of the opposing hub portion 10.
- a thrust bearing gap of the bearing portion T1 is formed.
- a region where a plurality of dynamic pressure grooves 8c1 as dynamic pressure generating portions are arranged is formed on the whole or a part of the lower end surface 8c of the sintered metal bearing 8.
- a region in which a plurality of dynamic pressure grooves 8c1 extending in a spiral shape are arranged in the circumferential direction is formed.
- the direction of the spiral of the dynamic pressure groove 8 c 1 is set to the direction corresponding to the rotation direction of the rotating member 9. That is, in the installation mode illustrated in FIG. 2, the orientation corresponds to the rotational direction of the flange portion 12 of the rotating member 9 (the direction in which dynamic pressure can be generated between the flange portion 12).
- the dynamic pressure groove arrangement region having the above-described configuration is a second thrust bearing portion described later between the upper end surface 12a of the opposing flange portion 12.
- a thrust bearing gap of T2 is formed (see FIG. 2).
- the thrust bearing gap is automatically set when the fluid dynamic bearing device 1 is assembled. That is, in the state where the fluid dynamic bearing device 1 is assembled as shown in FIG. 2, the flange portion 12 and the disk portion 10 a of the hub portion 10 are arranged at positions where the sintered metal bearing 8 fixed to the housing 7 is sandwiched in the axial direction. Is done. Therefore, the value obtained by subtracting the axial dimension of the sintered metal bearing 8 from the facing distance between the lower end surface 10a1 of the hub portion 10 and the upper end surface 12a of the flange portion 12 is set as the total sum of the thrust bearing clearances.
- One or a plurality (three in the present embodiment) of axial grooves 8d1 are formed on the outer peripheral surface 8d of the sintered metal bearing 8.
- the axial groove 8d1 forms a lubricating oil passage between the housing 7 and the inner peripheral surface 7a of the housing 7 when the sintered metal bearing 8 is fixed to the housing 7 (see FIG. 2).
- the axial dimension L (the axial distance between the end faces 8b and 8c) is set to 6 mm or less.
- the inner diameter dimension D1 (more precisely, the inner diameter dimension of the band 8a3 which becomes the smallest diameter portion together with the inclined hill portion 8a2 of the inner peripheral surface 8a) is set to 3 mm or less, and the outer diameter dimension D2 is set to 6 mm or less.
- the sintered metal bearing 8 has a density ratio of the entire bearing (density of the porous body forming the sintered metal bearing 8 / density assuming that the porous body has no pores) of 80% or more and It is set to be 95%. Moreover, in this sintered metal bearing 8, the variation in the density ratio inside the bearing is smaller (uniformized) than in the prior art. Specifically, it is preferable that variation in density ratio in the bearing is suppressed to 3% or less. In addition, the variation in density ratio at this time can be evaluated by using the porosity that allows the density ratio and a constant phase to be recognized.
- the pore ratio is expressed by the volume ratio (percentage) of the pores per unit volume of the bearing, and as a rule of thumb, the density ratio indicates an almost negative phase (-1 correlation coefficient). .
- the surface open area ratio of the inner peripheral surface 8a, particularly the inner peripheral surfaces of the inclined hill portion 8a2 and the belt portion 8a3 which are the radial bearing surfaces is adjusted to, for example, 2% or more and 15% or less.
- the sintered metal bearing 8 having the above-described configuration is manufactured through the following steps, for example.
- the sintered metal bearing 8 having the above-described structure includes a compacting step (S1) for compressing raw material powder to obtain a compacted body, and sintering to obtain a sintered body by sintering the compacted body.
- the step (S2) and the dynamic pressure groove sizing step (S3) for sizing the sintered body and forming the dynamic pressure groove 8a1 as the dynamic pressure generating portion on at least the inner peripheral surface 8a of the sintered body are mainly performed.
- a size sizing step (S031) for applying size sizing to the sintered body, and the inner peripheral surface 8a of the sintered body.
- a rotational sizing step (S032) for performing rotational sizing.
- the steps (S1) to (S3) will be described focusing on the dynamic pressure groove sizing step (S3).
- raw material powder used as the material of the sintered metal bearing 8 used as a final product is prepared, and this is compression-molded into a predetermined shape by die press molding.
- a die, a core pin inserted and disposed in the hole of the die, a lower punch disposed between the die and the core pin and configured to be movable up and down with respect to the die is compression-molded using a molding die composed of an upper punch configured to be capable of relative displacement (lifting) with respect to both the die and the lower punch.
- the raw powder is filled in the space defined by the inner peripheral surface of the die, the outer peripheral surface of the core pin, and the upper end surface of the lower punch, and then the upper punch is lowered with the lower punch fixed.
- the raw material powder in a filled state is pressurized in the axial direction.
- a compacting body is shape
- the axial dimension of the green compact is the distance between the lower end surface of the upper punch and the upper end surface of the lower punch, more specifically, the axial dimension that should target the bottom dead center of the upper punch ( It becomes possible to set within an appropriate range by controlling according to the subsequent setting and taking into account dimensional changes due to various sizing.
- (S3) Dynamic Pressure Groove Sizing Step By applying a predetermined dynamic pressure groove sizing to the sintered body obtained through the above series of steps, the dynamic pressure groove array region A1, on the inner peripheral surface 8a of the sintered body. A2 is molded.
- the forming apparatus used here is disposed between a die having a press-fitting hole of a sintered body, a sizing pin that can be inserted into the press-fitting hole of the die, and the die and the sizing pin.
- a lower punch configured to be movable up and down relative to the die, and an upper punch configured to be movable up and down with respect to both the die and the lower punch.
- the inner diameter dimension of the press-fitting hole of the die is appropriately set according to the press-fitting allowance of the sintered body to be sized.
- the outer peripheral surface of the sizing pin is provided with a molding die having a shape corresponding to the dynamic pressure groove array regions A1 and A2 (FIG. 3) of the inner peripheral surface 8a to be molded, and the lower end surface of the upper punch and the lower Formed on the upper end surface of the punch are molding dies having shapes corresponding to the dynamic pressure groove 8b1 arrangement region of the upper end surface 8b to be molded and the dynamic pressure groove 8c1 arrangement region (FIGS. 4A and 4B) of the lower end surface 8c, respectively. .
- the sintered body is pushed into the press-fitting hole of the die, the outer peripheral surface of the sintered body is pressed, and the inner peripheral surface of the sintered body bites against the mold of the sizing pin inserted in the inner periphery in advance.
- the upper punch is further lowered, the sintered body is sandwiched between the upper punch and the lower punch, and the sintered body in a state where the deformation in the outer diameter direction is constrained by the die is pressed in the axial direction.
- the inner peripheral surface bites into the mold. In this way, the shape of the mold is transferred to the inner peripheral surface of the sintered body, and the dynamic pressure groove array regions A1 and A2 are formed on the inner peripheral surface.
- the molds provided on the lower end surface of the upper punch and the upper end surface of the lower punch bite into the upper end surface and the lower end surface of the sintered body, respectively, so that the shapes of the respective molds are formed on the upper end surface and the lower end surface. Is transferred and the corresponding arrangement region of the dynamic pressure grooves 8b1 and 8c1 is formed.
- the die After forming the predetermined dynamic pressure groove array regions A1 and A2 and the dynamic pressure groove 8b1 and 8c1 array regions on the inner peripheral surface and both end surfaces of the sintered body in this way, the die is moved relative to the lower punch. Lowering and releasing the restraint state of the sintered body by the die. As a result, the sintered body is spring-backed in the outer diameter direction, and the sintered body can be removed from the sizing pin. At this time, the required amount of springback is such that the mold provided on the sizing pin does not get caught in the axial direction in the sintered body peripheral surface (especially the dynamic pressure groove array region) after sizing.
- the thickness of the sintered body that is, the thickness of the sintered metal bearing 8 as a finished product (outer diameter D2 ⁇ inner diameter D1) ) Is set.
- the sizing pin used for molding is sintered after sizing while forming the dynamic pressure groove 8a1 having a required depth by setting the inner diameter dimension D1 to 3 mm or less and the outer diameter dimension D2 to 6 mm or less. Can be pulled out from the body without getting caught.
- the inside of the fluid dynamic bearing device 1 having the above configuration is filled with lubricating oil as a lubricating fluid.
- lubricating oil can be used.
- a lubricating oil or the like is preferably used.
- a lubricating oil having a kinematic viscosity at 40 ° C. of 20 cSt or more and 170 cSt or less and a kinematic viscosity at 100 ° C. of 2 cSt or more and 50 cSt or less is preferably used.
- the first radial bearing portion R1 and the second radial bearing portion R2 that support the shaft portion 11 in a non-contact manner so as to be rotatable in the radial direction are separated from each other in the axial direction. Is done.
- the dynamic pressure action of the dynamic pressure groove 8b1 is between the thrust bearing gap between the upper end surface 8b of the sintered metal bearing 8 (region where the dynamic pressure grooves 8b1 are arranged) and the lower end surface 10a1 of the hub portion 10 facing the upper end surface 8b.
- an oil film of lubricating oil is formed.
- the dynamic pressure action of the dynamic pressure groove 8c1 is between the thrust bearing gap between the lower end surface 8c of the sintered metal bearing 8 (the region where the dynamic pressure grooves 8c1 are arranged) and the upper end surface 12a of the flange portion 12 facing this.
- an oil film of lubricating oil is formed.
- the pressure of these oil films constitutes a first thrust bearing portion T1 and a second thrust bearing portion T2 that support the rotating member 9 in a thrust non-contact manner.
- the axial dimension of the sintered metal bearing 8 is set to 6 mm or less, and the density ratio of the entire bearing is set to a range of 80% or more and 95% or less.
- the difference in density ratio can be made very small on the part side, on the upper and lower sides in the axial direction. Accordingly, even when the dynamic pressure groove array regions A1 and A2 are configured to be continuous in the axial direction, the sintered metal bearing is interposed via the dynamic pressure groove array regions A1 and A2 (particularly the bottom surface of the dynamic pressure groove 8a1). Therefore, an appropriate amount of lubricating oil can be circulated between the interior of 8 and the bearing clearance.
- the density ratio of the surface layer portion of the sintered metal bearing 8 is adjusted by adjusting the size and molding conditions so that the variation of the density ratio in the sintered metal bearing 8 is 3% or less. While preventing the escape of dynamic pressure from the surface, it can be set to such an extent that the lubricating oil or the like can exude properly into the bearing gap. In addition, the density ratio of the region excluding the surface layer portion (the inner region closer to the core than the surface layer portion) can be set so that the amount of the lubricating oil or the like impregnated by the inner region becomes an appropriate amount. Thereby, the design of the seal space S in consideration of the buffer performance due to the temperature change is established.
- the lubricating oil impregnated in the bearing internal space including the internal pores of the sintered metal bearing 8 has a kinematic viscosity at 40 ° C. of 20 cSt or more and 170 cSt or less, and the kinematic viscosity at 100 ° C. What showed 2 cSt or more and 50 cSt or less was used.
- the density ratio of the sintered metal bearing 8 is adjusted to optimize the internal structure, and the lubricating oil is used with a relatively high viscosity depending on the application, thereby improving the bearing performance. It is possible to contribute to the improvement and to suppress the deterioration of the lubricating oil. Therefore, even when the thickness is reduced, it is possible to provide the fluid dynamic bearing device 1 with high performance and high reliability.
- the sintered metal bearing 8 and the manufacturing method thereof according to the present invention are not limited to the above-described embodiments, and various modifications and changes can be made within the scope of the present invention. Of course.
- the sintered body in the dynamic pressure groove sizing step, the sintered body is pressed into the die, and the sintered body is compressed in the axial direction by the upper punch and the lower punch so that the dynamic pressure is applied to the peripheral surface of the sintered body.
- the case where the groove array regions A1 and A2 are formed has been illustrated, but if possible, the dynamic pressure groove array regions A1 and A2 are formed on the inner peripheral surface of the sintered body only by pressing in the axial direction without pressing into the die. May be formed.
- the movement mode of the upper punch and the lower punch at the time of axial compression is not limited to the above example.
- other pressing modes such as lowering the upper punch and further compressing the sintered body by raising the lower punch from a state where the sintered body is compressed to some extent in the axial direction between the upper punch and the lower punch may be employed. Is possible.
- the dynamic pressure groove array regions A1 and A2 having the herringbone shape are formed as the dynamic pressure generating portion of the inner peripheral surface 8a is illustrated.
- the dynamic pressure grooves having other shapes are also formed.
- each of the dynamic pressure groove array regions A1 and A2 may or may not necessarily have a symmetrical shape with the axial center position as a boundary. Further, the dynamic pressure groove array regions A1 and A2 that are continuous in the axial direction may or may not have a symmetrical shape with respect to the boundary.
- the shape thereof is arbitrary. More specifically, any form can be adopted as long as the lubricating oil is drawn in the direction away from the boundary positions of the dynamic pressure groove array regions A1 and A2 toward the end faces 8b and 8c, respectively.
- the dynamic pressure grooves 8b1 and 8c1 are formed on the upper end surface 8b and the lower end surface 8c, respectively.
- the dynamic pressure groove is formed only on one of the upper end surface 8b and the lower end surface 8c.
- a configuration may be adopted in which no dynamic pressure groove is provided in any of the end faces 8b and 8c.
- the lubricating oil is applied to the bearing internal space including the internal pores of the sintered metal bearing 8.
- the sintered metal bearing 8 may be impregnated with lubricating oil at the time of completion of the bearing (before incorporation).
- the sintered metal bearing 8 according to the above description is not limited to the fluid dynamic bearing device 1 of the thin type as illustrated above (the seal space S is arranged on the outer diameter side of the radial bearing portions R1 and R2).
- the present invention can be applied to other types of fluid dynamic bearing devices.
- the fluid dynamic pressure bearing device 1 is applicable not only to the centrifugal type fan motor 2 as illustrated above but also to other types of fan motors 2 such as an axial flow type.
- a small motor for information equipment 3 used under high-speed rotation such as a spindle motor used in a disk drive device such as an HDD, a spindle motor for driving a magneto-optical disk of an optical disk, It can be suitably used as a bearing device for driving various motors such as a polygon scanner motor of a laser beam printer.
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Abstract
Description
まず、最終的な製品となる焼結金属軸受8の材料となる原料粉末を用意し、これを金型プレス成形により所定の形状に圧縮成形する。具体的には、図示は省略するが、ダイと、ダイの孔内に挿入配置されるコアピンと、ダイとコアピンとの間に配設され、ダイに対して昇降可能に構成された下パンチ、および、ダイと下パンチの何れに対しても相対変位(昇降)可能に構成された上パンチとで構成される成形金型を用いて原料粉末の圧縮成形を行う。この場合、ダイの内周面とコアピンの外周面、および、下パンチの上端面とで区画形成される空間に原料粉末を充填し、然る後、下パンチを固定した状態で上パンチを下降させ、充填状態の原料粉末を軸方向に加圧する。そして、加圧しながら所定の位置まで上パンチを下降させ、原料粉末を所定の軸方向寸法にまで圧縮することで、圧粉成形体が成形される。この際、圧粉成形体の軸方向寸法は、上パンチの下端面と、下パンチの上端面との距離、より具体的には上パンチの下死点を、目標とすべき軸方向寸法(この後の焼結、各種サイジングによる寸法変化を考慮して設定)に応じて制御することで、適切な範囲に設定可能となる。
上述のようにして、圧粉成形体を得た後、この圧粉成形体を原料粉末に応じた温度で焼結することにより、焼結体を得る。
そして、焼結体に対して寸法サイジングを施して、焼結体の外径寸法や内径寸法、及び軸方向寸法を最終製品に準じた寸法に矯正すると共に、内周面8aの表面開孔率を、動圧軸受として好適な割合に調整する。この段階では、焼結体の内周面8aに所定の動圧溝配列領域A1,A2は未だ形成されてない。同様に、図示は省略するが、焼結体の両端面8b,8cに所定の動圧溝8b1,8c1配列領域は未だ形成されていない。
上記一連の工程を経て得られた焼結体に対して所定の動圧溝サイジングを施すことで、焼結体の内周面8aに動圧溝配列領域A1,A2を成形する。ここで使用する成形装置は、図示は省略するが、焼結体の圧入穴を有するダイと、ダイの圧入穴に挿入可能に配置されるサイジングピンと、ダイとサイジングピンとの間に配設され、ダイに対して相対的に昇降可能に構成された下パンチ、および、ダイと下パンチの何れに対しても昇降可能に構成された上パンチとを有する。この場合、ダイの圧入穴の内径寸法は、サイジングすべき焼結体の圧入代に応じて適宜設定される。また、サイジングピンの外周面には、成形すべき内周面8aの動圧溝配列領域A1,A2(図3)に対応する形状の成形型が設けられると共に、上パンチの下端面、及び下パンチの上端面にはそれぞれ、成形すべき上端面8bの動圧溝8b1配列領域、下端面8cの動圧溝8c1配列領域(図4A、図4B)に対応する形状の成形型がそれぞれ設けられる。
2 ファンモータ
3 情報機器
4 ベース
5 ファン
6 駆動部
7 ハウジング
7a 内周面
8 焼結金属軸受
8a 内周面
8a1 動圧溝(内周面)
8a2 傾斜丘部
8a3 帯部
8b 上端面
8b1 動圧溝(上端面)
8c 下端面
8c1 動圧溝(下端面)
9 回転部材
10 ハブ部
10a 円盤部
10a1 下端面
12 フランジ部
13 蓋部材
A1,A2 動圧溝配列領域
R1,R2 ラジアル軸受部
T1,T2 スラスト軸受部
S シール空間
Claims (7)
- 原料粉末を圧縮成形したものを焼結することで形成された多孔質体であって、内周面に動圧発生部を設けた焼結金属軸受において、
動圧発生部として、円周方向に対して傾斜させた複数の動圧溝を配列してなる動圧溝配列領域が軸方向に連続して形成され、軸方向寸法が6mm以下とされると共に、密度比が80%以上でかつ95%以下となることを特徴とする焼結金属軸受。 - 軸受内部における密度比のばらつきが3%以下に抑えられている請求項1に記載の焼結金属軸受。
- 軸方向で連続する動圧溝配列領域は何れもヘリングボーン形状をなし、各動圧溝配列領域を構成する動圧溝がその軸方向中央側で連続している請求項1に記載の焼結金属軸受。
- 内径寸法が3mm以下で、かつ外径寸法が6mm以下とされる請求項1に記載の焼結金属軸受。
- 請求項1~4の何れかに記載の焼結金属軸受と、焼結金属軸受の内周に挿通される軸部と、焼結金属軸受を含む固定側と軸部を含む回転側との間に形成されるシール空間と、焼結金属軸受の内部を含む軸受内部空間に充填される潤滑油とを備えた流体動圧軸受装置。
- 潤滑油は、40℃での動粘度が20cSt以上でかつ170cSt以下を示し、100℃での動粘度が2cSt以上でかつ50cSt以下を示すものである請求項5に記載の流体動圧軸受装置。
- 請求項5又は6に記載の流体動圧軸受装置と、軸部に取付けられるファンとを備えたファンモータ。
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EP14849434.7A EP3051156B1 (en) | 2013-09-24 | 2014-09-05 | Sintered metal bearing, fluid-dynamic bearing device provided with said bearing, and fan motor provided with said bearing device |
US15/021,771 US10415573B2 (en) | 2013-09-24 | 2014-09-05 | Fluid-dynamic bearing device provided with a sintered metal bearing and a fan motor provided with the fluid-dynamic bearing device |
KR1020167005646A KR102206759B1 (ko) | 2013-09-24 | 2014-09-05 | 소결 금속 베어링, 및 이 베어링을 구비한 유체 동압 베어링 장치 |
CN201480052728.7A CN105579720B (zh) | 2013-09-24 | 2014-09-05 | 烧结金属含油轴承、具备其的流体动压轴承装置及风扇电动机 |
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JP2013196973A JP6199675B2 (ja) | 2013-09-24 | 2013-09-24 | 焼結金属軸受、及びこの軸受を備えた流体動圧軸受装置 |
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JP2018061408A (ja) * | 2016-10-07 | 2018-04-12 | 日本電産株式会社 | ファンモータ |
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CN108869541B (zh) * | 2018-01-12 | 2024-04-02 | 刘慕华 | 一种径向轴承、转子系统及径向轴承的控制方法 |
US20190353177A1 (en) * | 2018-05-21 | 2019-11-21 | Asia Vital Components Co., Ltd. | Fan frame seat and fan thereof |
JP7320365B2 (ja) * | 2019-03-28 | 2023-08-03 | Ntn株式会社 | 焼結金属製コンロッド、及びその製造方法 |
US11873903B2 (en) | 2019-12-19 | 2024-01-16 | Eaton Intelligent Power Limited | Self-correcting hydrodynamic seal |
US11209047B1 (en) * | 2020-07-14 | 2021-12-28 | John Wun-Chang Shih | Liquid guiding structure for fluid dynamic pressure bearing |
JP2023047578A (ja) * | 2021-09-27 | 2023-04-06 | Ntn株式会社 | 動圧軸受及びこれを備えた流体動圧軸受装置 |
WO2023243496A1 (ja) * | 2022-06-14 | 2023-12-21 | Ntn株式会社 | 流体動圧軸受用潤滑油組成物、流体動圧軸受、及び流体動圧軸受装置 |
JP2024043207A (ja) * | 2022-09-16 | 2024-03-29 | Ntn株式会社 | 動圧軸受、動圧軸受装置及びモータ |
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JP3607492B2 (ja) | 1997-03-06 | 2005-01-05 | Ntn株式会社 | 動圧型多孔質含油軸受およびその製造方法 |
JP2002097503A (ja) * | 2000-07-17 | 2002-04-02 | Hitachi Powdered Metals Co Ltd | 動圧溝付き焼結軸受の製造方法 |
JP2006118594A (ja) * | 2004-10-21 | 2006-05-11 | Hitachi Powdered Metals Co Ltd | 動圧軸受およびその製造方法 |
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EP3051156A1 (en) | 2016-08-03 |
US20160230769A1 (en) | 2016-08-11 |
EP3051156B1 (en) | 2020-04-22 |
KR20160058765A (ko) | 2016-05-25 |
US10415573B2 (en) | 2019-09-17 |
EP3051156A4 (en) | 2017-07-05 |
JP6199675B2 (ja) | 2017-09-20 |
JP2015064019A (ja) | 2015-04-09 |
CN105579720A (zh) | 2016-05-11 |
CN105579720B (zh) | 2019-01-22 |
KR102206759B1 (ko) | 2021-01-25 |
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