CN207526872U - Hydrodynamic bearing, fluid dynamic-pressure bearing device, motor and shaping dies - Google Patents

Hydrodynamic bearing, fluid dynamic-pressure bearing device, motor and shaping dies Download PDF

Info

Publication number
CN207526872U
CN207526872U CN201721063800.3U CN201721063800U CN207526872U CN 207526872 U CN207526872 U CN 207526872U CN 201721063800 U CN201721063800 U CN 201721063800U CN 207526872 U CN207526872 U CN 207526872U
Authority
CN
China
Prior art keywords
dynamic pressure
bearing
hydrodynamic bearing
face
pressure groove
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
CN201721063800.3U
Other languages
Chinese (zh)
Inventor
新井隆生
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
NTN Corp
Original Assignee
NTN Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by NTN Corp filed Critical NTN Corp
Application granted granted Critical
Publication of CN207526872U publication Critical patent/CN207526872U/en
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D17/00—Forming single grooves in sheet metal or tubular or hollow articles
    • B21D17/02—Forming single grooves in sheet metal or tubular or hollow articles by pressing
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D53/00—Making other particular articles
    • B21D53/10—Making other particular articles parts of bearings; sleeves; valve seats or the like
    • 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
    • F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial 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
    • F16C17/10—Sliding-contact bearings for exclusively rotary movement for both radial and axial load
    • 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
    • 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
    • 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
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K5/00—Casings; Enclosures; Supports
    • H02K5/04—Casings or enclosures characterised by the shape, form or construction thereof
    • H02K5/16—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields
    • H02K5/167—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields using sliding-contact or spherical cap bearings
    • 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
    • F16C2204/00—Metallic materials; Alloys
    • F16C2204/10—Alloys based on copper
    • 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
    • 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
    • F16C2220/40—Shaping by deformation without removing material
    • F16C2220/46—Shaping by deformation without removing material by forging
    • 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
    • F16C2220/40—Shaping by deformation without removing material
    • F16C2220/48—Shaping by deformation without removing material by extrusion, e.g. of metallic profiles
    • 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
    • F16C2324/00—Apparatus used in printing
    • F16C2324/16—Printing machines
    • 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
    • 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
    • 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

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Power Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Sliding-Contact Bearings (AREA)
  • Manufacture Of Motors, Generators (AREA)
  • Shaping Metal By Deep-Drawing, Or The Like (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)

Abstract

The utility model provides hydrodynamic bearing, fluid dynamic-pressure bearing device, motor and shaping dies.The utility model is related to hydrodynamic bearings, more particularly to there is the hydrodynamic bearing of dynamic pressure groove by die forming in end face.Its subject is to improve the pressure improvement effect that the dynamic pressure groove formed in the end face of hydrodynamic bearing is played.To solve the subject, the hydrodynamic bearing (8) of the utility model has at upside end face (8b) dynamic pressure groove (8b1) as obtained from die forming.The groove bottom of dynamic pressure groove (8b1) tilts downwards towards outside diameter.So as to ensure the groove depth in the end face of hydrodynamic bearing dynamic pressure groove as obtained from die forming in whole region, the pressure improvement effect of dynamic pressure groove generation can be improved.The hydrodynamic bearing and fluid dynamic-pressure bearing device of the utility model, which are not only fitted into the spindle drive motor of disk drive device, to be used, and can also be fitted into the fan motor of cooling fan, multi-panel scanning motor of laser beam printer etc. and be used.

Description

Hydrodynamic bearing, fluid dynamic-pressure bearing device, motor and shaping dies
Technical field
The utility model is related to hydrodynamic bearings, more particularly to there is the hydrodynamic bearing of dynamic pressure groove by die forming in end face.
Background technology
Hydrodynamic bearing is the Fluid pressure generated using the bearing clearance between the shaft component of relative rotation come to axis Component carries out the component of non-contact bearing.The profit for making to be filled in bearing clearance is formed in the inner peripheral surface of hydrodynamic bearing and end face Slip-stream body (such as lubricating oil) generates the dynamic pressure groove of dynamic pressure.Dynamic pressure groove edge intersects with circumferential direction (the relative rotation direction of shaft component) Direction extends, and the flow direction of the lubricating fluid of bearing clearance circumferentially flowed with the relative rotation of shaft component is by dynamic pressure Slot is corrected, so as to which lubricating fluid is concentrated and Fluid pressure raising.
Dynamic pressure groove is formed in most cases by pressing die forming to bearing blank.For example, it shows in patent document 1 In the method that the inner peripheral surface of cylindric sintered body and end face pass through die forming dynamic pressure groove.
Citation
Patent document
Patent document 1：No. 3607661 bulletins of Japanese Patent Publication No.
But in general, dynamic pressure groove and the circumferential size in the mound portion ratio formed between its circumferential direction are constant (such as 1: 1). For in the case of the dynamic pressure groove that is formed at the end face of hydrodynamic bearing (thrust bearing surface), if making the circumferential size of dynamic pressure groove and mound portion Than to be constant, then with towards outside diameter and the circumferential width in dynamic pressure groove and mound portion broadens (with reference to Fig. 4).If in bearing blank End face is by dynamic pressure groove as die forming, then deflection (the plastic deformation generated when having pressed shaping dies in mound portion Amount) can be different according to radial direction position, therefore, as shown in figure 15, easily the height in generation mound portion 101 is with towards outer diameter Side and be lower, i.e. so-called " turned-down edge ".In this case, since the groove depth of dynamic pressure groove 102 towards outside diameter with shoaling, Therefore, ability (i.e., the centralized lubrication fluid that the flow direction of lubricating fluid is nearby corrected in the outer diameter end of dynamic pressure groove 102 Ability) be lower, it may not be possible to give full play to the pressure improvement effect of dynamic pressure groove 102.
Utility model content
Therefore, the purpose of this utility model is that the pressure that the dynamic pressure groove that raising is formed in the end face of hydrodynamic bearing is played Improvement effect.
Means for solving the problems
In order to solve the above problems, the utility model is related to hydrodynamic bearing be characterized in that, at the end of an axial side side There is dynamic pressure groove in face by die forming, and the groove bottom of the dynamic pressure groove rolls tiltedly towards outside diameter to axial the opposing party.
In this way, in the hydrodynamic bearing of the utility model, make to obtain by die forming in the end face of an axial side side The groove bottom of dynamic pressure groove tilted towards outside diameter to axial the opposing party side the side of groove depth (deepen).It is generating as a result, The top surface in mound portion towards outside diameter and to axial the opposing party side it is inclined, in the case of so-called " turned-down edge ", also can be in dynamic pressure The whole region of slot ensures groove depth more than regulation.In this case, centralized lubrication can be played in the whole region of dynamic pressure groove The ability of fluid, therefore, it is possible to fully improve the Fluid pressure of bearing clearance.
Above-mentioned hydrodynamic bearing can be formed by such as sintered body.Pass through the situation of die forming dynamic pressure groove in sintered body Under, for example, on melting part by the situation of die forming dynamic pressure groove compared with, springback capacity becomes larger, therefore, easily mound portion produce Raw " turned-down edge ".Therefore, the groove bottom inclination for making dynamic pressure groove as described above is especially effective.
Also have in above-mentioned hydrodynamic bearing other as obtained from die forming in the end face of axial the opposing party side In the case of dynamic pressure groove, preferably, make the groove bottom of other dynamic pressure groove towards outside diameter and rolled to an axial side oblique.By This, in the whole region of other dynamic pressure groove, can play the ability of centralized lubrication fluid, therefore, it is possible to fully improve dynamic pressure The pressure of the lubricating fluid of other bearing clearance that the end face of axial the opposing party side of bearing is faced.
Above-mentioned hydrodynamic bearing can be packed into fluid dynamic-pressure bearing device.Specifically, fluid dynamic-pressure bearing device has： Above-mentioned hydrodynamic bearing；Shaft component has the axle portion for the inner circumferential for being inserted into the hydrodynamic bearing and from the axle portion to outer diameter The flange part that side protrudes, the shaft component carry out relative rotation relative to the hydrodynamic bearing；Radial bearing portion, using described The Fluid pressure that journal bearing gap between the inner peripheral surface of hydrodynamic bearing and the peripheral surface of the axle portion generates is in radial direction On opposite bearing is carried out to the shaft component；Thrust bearing division, using in the end face of an axial side side for the hydrodynamic bearing The Fluid pressure that thrust bearing gap between the end face of the flange part generates in thrust direction to the shaft component into The opposite bearing of row, in the fluid dynamic-pressure bearing device, the Fluid pressure in thrust bearing gap is higher, the bearing in thrust direction Rigidity is higher.
In addition, the utility model is related to the manufacturing method of hydrodynamic bearing be characterized in that, by lateral from an axial side The end face pressing shaping dies of bearing blank shapes dynamic pressure groove, in the shaping dies, for shaping the dynamic pressure groove The forming face of groove bottom rolls oblique towards outside diameter and to axial the opposing party.The manufacturing method can be used by from an axial side The end face of side bearing blank presses the shaping dies to shape dynamic pressure groove, in the shaping dies, for shaping the dynamic pressure The forming face of the groove bottom of slot rolls oblique towards outside diameter and to axial the opposing party.
By be used in like this forming dynamic pressure groove groove bottom forming face towards outside diameter and to axial the opposing party side It tilts, as described above, even if in the case of producing " turned-down edge " in mound portion, can also ensure that the groove depth of dynamic pressure groove.
At this time, it is preferable that in shaping dies, for shape set on dynamic pressure groove circumferential direction between mound portion recess portion depth Degree is deepened with towards outside diameter.Specifically, it is preferable that being, the bottom surface of recess portion is flat surface orthogonal to the axial direction.It is recessed by this The mound portion of portion's forming towards outside diameter with increasing, therefore, even if in the case of producing rebound in demoulding later, It can be ensured that the groove depth (i.e. mound portion height) of the dynamic pressure groove near outer diameter end.
Utility model effect
As previously discussed, according to the utility model, can ensure to pass through mold in the end face of hydrodynamic bearing in whole region The groove depth of dynamic pressure groove obtained from forming, therefore the pressure improvement effect of dynamic pressure groove generation can be improved.
Description of the drawings
Fig. 1 is the sectional view of the spindle drive motor of the disk drive device of HDD.
Fig. 2 is loaded into the sectional view of the fluid dynamic-pressure bearing device of above-mentioned spindle drive motor.
Fig. 3 is the sectional view of hydrodynamic bearing that an embodiment of the utility model is related to.
Fig. 4 is the vertical view of above-mentioned hydrodynamic bearing.
Fig. 5 is the enlarged cross-sectional view near the upside end face of above-mentioned hydrodynamic bearing.
Fig. 6 is the bottom view of above-mentioned hydrodynamic bearing.
Fig. 7 is the vertical view for the hydrodynamic bearing that another embodiment is related to.
Fig. 8 is to represent to pass through in the dynamic pressure groove formation process of die forming dynamic pressure groove, dynamic pressure groove in the end face of sintered body The sectional view of state before forming.
Fig. 9 is that the end face of the hydrodynamic bearing of Fig. 8 is nearby amplified to the sectional view represented.
Figure 10 is the sectional view of state when representing the dynamic pressure groove forming in above-mentioned dynamic pressure groove formation process.
Figure 11 is that the end face of the hydrodynamic bearing of Figure 10 is nearby amplified to the sectional view represented.
Figure 12 is the sectional view for representing situation in above-mentioned dynamic pressure groove formation process, from mold discharge sintered body.
Figure 13 is that the end face of the hydrodynamic bearing of Figure 12 is nearby amplified to the sectional view represented.
Figure 14 is the sectional view for the fluid dynamic-pressure bearing device that another embodiment is related to.
Figure 15 is that the end face of previous hydrodynamic bearing is nearby amplified to the sectional view represented.
Reference sign
1 fluid dynamic-pressure bearing device
2 axle portions
3 wheel hubs
7 housings
8 hydrodynamic bearings
8a1,8a2 (radial direction) dynamic pressure groove
8b1,8c1 (thrust) dynamic pressure groove
8b2,8c2 mound portion
9 flange parts
11 plugs
12nd, 13 punch
12a, 13a forming section
12a1,13a1 slot bottom forming face
12a2,13a2 recess portion
14 formers
18 sintered bodies
R1, R2 radial bearing portion
T1, T2 thrust bearing division
S sealing spaces
Specific embodiment
Hereinafter, the embodiment based on description of the drawings the utility model.
Fig. 1 shows spindle drive motors used in the disk drive device of HDD.The spindle drive motor has：With this practicality The fluid dynamic-pressure bearing device 1 for the hydrodynamic bearing 8 that a novel embodiment is related to；For installing fluid dynamic-pressure bearing device 1 Bracket 6；Across the opposed stator coil 4 in the gap of radial direction and rotor magnet 5.Stator coil 4 is installed on bracket 6, turns Sub- magnet 5 is installed on the wheel hub 3 of fluid dynamic-pressure bearing device 1.In disk (illustration omitted) of the wheel hub 3 equipped with regulation number.When When being powered to stator coil 4, under the action of the electromagnetic force between stator coil 4 and rotor magnet 5, rotor magnet 5 is revolved Turn, thus wheel hub 3 and disk are integrally formed and are rotated.
As shown in Fig. 2, fluid dynamic-pressure bearing device 1 has：Hydrodynamic bearing 8；There is bottom by what hydrodynamic bearing 8 was held in inner circumferential The housing 7 of tubular；The shaft component rotatably freely supported by hydrodynamic bearing 8.In the present embodiment, shaft component is dynamic by being inserted in It is another that last item holds the axle portion 2 of 8 inner circumferential, the conduct of the other end set on the flange part 9 of one end of axle portion 2 and set on axle portion 2 The wheel hub 3 of flange part is formed.It should be noted that hereinafter, for convenience of description, if the open side of the housing 7 in axial direction is upper Side, occlusion side are downside.
Axle portion 2 is formed by such as metal, has the peripheral surface 2a for not having irregular straight cylinder planar.Flange part 9 is by example It is prominent from the lower end of axle portion 2 to outer diameter side if metal is formed.End face 9a, 9b of the axial both sides of flange part 9 are without bumps Flat surface.
Wheel hub 3 is formed by such as metal, and from from the upper end of the axle portion 2 round plate 3a prominent to outer diameter side, from round plate The outer diameter end of 3a to the cylindrical portion 3b extended axially below, from the lower end of cylindrical portion 3b further out diameter extension eaves portion 3c And the cylindric cyclic lug 3d extended downwards from the radial direction substantially central portion of round plate 3a is formed.In eaves portion The upside end face of 3c is equipped with disk (not shown).It should be noted that in illustrated example, wheel hub 3 is integrally formed, but also may be used Wheel hub 3 to be made of multiple components, such as cyclic lug 3d formed by other component.
Hydrodynamic bearing 8 is formed as cylindric by metal, resin.In the present embodiment, hydrodynamic bearing 8 by sintering metal, Such as the sintering metal containing more copper (such as more than 20 mass %) is formed, and is specifically burnt by the copper system using copper as principal component Knot metal or the copper and iron system sintering metal using copper and iron as principal component are formed.
Dynamic pressure groove is formed in the inner peripheral surface 8a of hydrodynamic bearing 8.In the present embodiment, as shown in figure 3, in hydrodynamic bearing Separated two region in the axial direction of 8 inner peripheral surface 8a is respectively formed with dynamic pressure groove 8a1,8a2 of chevron shape, and (cross hatch is Mound portion).In illustrated example, the dynamic pressure groove 8a1 of upside is formed as axial asymmetric, specifically, the ring more central than approximately axially The axial dimension in the upper region in the mound portion of shape is more than the axial dimension in the region than cricoid mound portion on the lower.It moves downside Indent 8a2 is formed as axially symmetric.
As shown in figure 4, the upside end face 8b in hydrodynamic bearing 8 is formed with dynamic pressure groove 8b1.Specifically, in hydrodynamic bearing 8 Upside end face 8b, in the circumferential alternately be equipped with dynamic pressure groove 8b1 and mound portion 8b2 (being represented by cross hatch).Dynamic pressure groove 8b1 along with The direction extension circumferentially intersected, such as formed spiral-shaped.Dynamic pressure groove 8b1 is with the rotation of shaft component that lubricating oil is inside What diameter side pressure entered is pumped into type.In illustrated example, dynamic pressure groove 8b1 is formed towards the fluid flow direction (figure during rotation of shaft component Middle arrow direction) downstream side and rolled to internal diameter and oblique be pumped into the spiral-shaped of type.Dynamic pressure groove 8b1 and mound portion 8b2 are reached The inner-diameter end of the upside end face 8b of hydrodynamic bearing 8 and outer diameter end are (specifically for end face 8b on the upside of being set on and inner peripheral surface 8a and outside The chamfered section on the boundary of circumferential surface 8d).The circumferential size ratio of dynamic pressure groove 8b1 and mound portion 8b2 in radial direction whole region is perseverance It is fixed, it is 1: 1 in illustrated example.Therefore, dynamic pressure groove 8b1 and mound portion 8b2 respectively with towards outside diameter and circumferential width gradually expands It is wide.
As shown in figure 5, the upper surface of mound portion 8b2 tilts downwards towards outside diameter (right side in figure).In addition, dynamic pressure groove The groove bottom of 8b1 tilts downwards towards outside diameter.As a result, the groove depth t (upper surfaces of mound portion 8b2 of dynamic pressure groove 8b1 Axial distance between the groove bottom of dynamic pressure groove 8b1) in whole region to be more than specified value, for example, 10 μm or more.It needs Illustrate, in Figure 5, exaggeration represents the angle of inclination of dynamic pressure groove 8b1 and mound portion 8b2, in fact, the internal diameter of dynamic pressure groove 8b1 Axial distance d between end and outer diameter end is 1~5 μm or so.
The upside end face 8b of hydrodynamic bearing 8 includes dynamic pressure groove 8b1 and mound portion 8b2, be whole region by die forming and Obtained face.In addition, in the upside end face 8b of hydrodynamic bearing 8, not only implement the forming (forging) by mold before sintering, also Implement the sintered forming (pressure-sizing) by mold.On the other hand, set on the upside end face 8b of hydrodynamic bearing 8 and inner peripheral surface 8a And the chamfered section on the boundary of peripheral surface 8d only implements the forming by mold before sintering, does not implement sintered by mold Forming.Therefore, the surface opening rate of the upside end face 8b (dynamic pressure groove 8b1 and mound portion 8b2) of hydrodynamic bearing 8 is smaller than chamfered section.
As shown in fig. 6, it is formed with the dynamic pressure groove 8c1 as thrust dynamic pressure generating unit in the downside end face 8c of hydrodynamic bearing 8. Specific shape of dynamic pressure groove 8c1 and mound portion 8c2 of downside end face 8c etc. and the dynamic pressure groove 8b1 of upside end face 8b and mound portion 8b2 Identical, and the description is omitted.
It should be noted that the shape of dynamic pressure groove 8b1,8c1 be not limited to it is above-mentioned.For example, it in the example shown in Fig. 7, moves The mound portion 8b2 that last item holds 8 upside end face 8b has inclination mound portion between the circumferential direction of spiral-shaped dynamic pressure groove 8b1 The 8b21 and cricoid back 8b22 for linking the inner-diameter end for tilting mound portion 8b21.By like this in the inner-diameter end of mound portion 8b2 Back 8b22 is set, can expect the further raising of Fluid pressure.
In addition, dynamic pressure groove 8b1,8c1 are not limited to be pumped into type, or with shaft component rotation and by lubricating fluid to What outside diameter squeezed out pumps out type.In addition, dynamic pressure groove 8b1,8c1 be not limited to it is spiral-shaped, or chevron shape, stairstepping (radial).
Axial groove 8d1 is formed in the peripheral surface of hydrodynamic bearing 8.The item number of axial groove 8d1 is arbitrary, in illustrated example In, along the circumferential direction equally spaced it is configured with three axial groove 8d1 (with reference to Fig. 4 and Fig. 6).
As shown in Fig. 2, housing 7 has the bottomed cylindrical of side 7a and bottom 7b with being formed as one.Side 7a's is interior Circumferential surface 7a1 is formed as straight cylinder planar, by press-in after gap bonding, press-in, sandwiched bonding agent etc. by hydrodynamic bearing 8 Peripheral surface 8d fix.As shown in Fig. 2, the gradual expanding conical surface upward is formed in the upper end of the peripheral surface of side 7a 7a3.Be formed between the cylinder planar inner peripheral surface 3d1 of the conical surface 7a3 and cyclic lug 3d of wheel hub 3 upward and half The diminishing cricoid sealing space S of diameter direction size.Using the capillary force of sealing space S, to prevent from riddling shell The leakage of the lubricating oil of the inside of body 7.
After above structure is assembled, it is full of the space of the inside of the housing 7 of the internal porosity comprising hydrodynamic bearing 8 Lubricating oil, so as to complete fluid dynamic-pressure bearing device 1 shown in Fig. 2.In the hypothesis temperature in use of fluid dynamic-pressure bearing device 1 In the range of, pasta is always held in the inside of sealing space S.
When shaft component rotates, radial axle is formed between the inner peripheral surface 8a of hydrodynamic bearing 8 and the peripheral surface 2a of axle portion 2 Gap is held, also, under the action of dynamic pressure groove 8a1,8a2, improved in the pressure for the oil film that above-mentioned journal bearing gap generates.Profit With the pressure (dynamic pressure effect) of the oil film, composition rotatably freely carries out non-contact branch to axle portion 2 and wheel hub 3 in radial directions Radial bearing portion R1, R2 held.
At the same time, between the downside end face 3a1 of the round plate 3a of wheel hub 3 and the upside end face 8b of hydrodynamic bearing 8 with And thrust bearing gap is respectively formed between the upside end face 9a of flange part 9 and the downside end face 8c of hydrodynamic bearing 8, also, Under the action of dynamic pressure groove 8b1,8c1 of the both ends of the surface of hydrodynamic bearing 8, carried in the pressure for the oil film that each thrust bearing gap generates It is high.Using the pressure (dynamic pressure effect) of these oil films, be formed in two thrust directions rotatably freely to axle portion 2 and wheel hub 3 into First and second thrust bearing division T1, T2 of the non-contact bearing of row.
At this point, using the axial groove 8d1 of the peripheral surface 8d formation in hydrodynamic bearing 8, form what can be circulated for lubricating oil Access.Using the access, it can prevent from generating the situation of the negative pressure of part in the lubricating oil for being filled in the inside of housing 7. Particularly, in the present embodiment, as shown in figure 3, the dynamic pressure groove 8a1 shapes of upside formed in the inner peripheral surface 8a of hydrodynamic bearing 8 As axial asymmetrical shape, therefore, the lubricating oil in journal bearing gap is pressed into downwards with the rotation of axle portion 2, Lubricating oil is recycled via above-mentioned access, and thus, it is possible to be reliably prevented the generation of local negative pressure.
Then, illustrate the manufacturing method of hydrodynamic bearing 8.The manufacture of hydrodynamic bearing 8 is via mixed processes, compression molding (forging Make) process, sintering circuit, size correction (pressure-sizing) process and dynamic pressure groove formed (slot pressure-sizing) process and carry out.
In mixed processes, mix various metal powders and make the raw material powder of hydrodynamic bearing 8.As composition raw material powder Metal powder, such as iron powder, copper powder, glass putty etc. can be used, in the present embodiment, use iron powder and copper powder.In addition to this, The forming of kollag, the metallic soap of graphite etc. etc. can also be coordinated in raw material powder with lubricator.
In compression molding process, after above-mentioned raw material powder is supplied in shaping dies, compressed, from into The powder compact of shape cylindrical shape.
In sintering circuit, powder compact is sintered under defined sintering temperature, so as to obtain sintered body.Sintering temperature Degree is set as the fusing point (1085 DEG C) less than copper, for example, 850~900 DEG C.
In size correction process, sintered body is recompressed using coining die, so as to (interior to the size of sintered body Diameter size, outer diameter, axial dimension) it is corrected.It should be noted that in size correction process, unshaped, which is set on, to be burnt The both ends of the surface of knot body and the chamfered section (not contacted with coining die) between peripheral surface and inner peripheral surface.
In dynamic pressure groove formation process, using slot coining die, dynamic pressure groove shown in Fig. 3 is shaped in the inner peripheral surface of sintered body 8a1,8a2, also, it is formed separately Fig. 4 and dynamic pressure groove 8b1,8c1 shown in fig. 6 in the both ends of the surface of sintered body.Need what is illustrated It is that similary with above-mentioned size correction process in dynamic pressure groove formation process, the chamfered section of unshaped sintered body is not (smart with slot Compression mould contacts).
Hereinafter, dynamic pressure groove formation process is described in detail.As shown in figure 8, slot coining die is used as to shape sintered body 18 Each face finishing die and have plug 11, upper punch 12, low punch 13 and former 14.
Forming section 11a, 11b of shape corresponding with dynamic pressure groove 8a1,8a2 are equipped in the peripheral surface of plug 11.
In forming section 12a of the forming face (lower surface) of upper punch 12 equipped with shape corresponding with dynamic pressure groove 8b1.Such as Fig. 9 Shown, forming section 12a has slot bottom forming face 12a1 for shaping the groove bottom of dynamic pressure groove 8b1 and for shaping mound portion 8b2 Recess portion 12a2.Slot bottom forming face 12a1 is tilted downwards towards outside diameter.The bottom surface of recess portion 12a2 (is used to shape mound portion The forming face of the top surface of 8b2) be formed as substantially parallel with coaxial orthogonal face.As a result, depth (the slot bottom of recess portion 12a2 Axial distance between the bottom surface of forming face 12a1 and recess portion 12a2) it is deepened with towards outside diameter.
In forming section 13a of the forming face (upper surface) of low punch 13 equipped with shape corresponding with dynamic pressure groove 8c1.Such as Fig. 9 Shown, forming section 13a has slot bottom forming face 13a1 for shaping the groove bottom of dynamic pressure groove 8c1 and for shaping mound portion 8c2 Recess portion 13a2.Slot bottom forming face 13a1 is tilted upward towards outside diameter.The bottom surface of recess portion 13a2 (is used to shape mound portion The forming face of the top surface of 8c2) be formed as substantially parallel with coaxial orthogonal face.As a result, depth (the slot bottom of recess portion 13a2 Axial distance between the bottom surface of forming face 13a1 and recess portion 13a2) it is deepened with towards outside diameter.It should be noted that In Fig. 8~13, exaggeration represents the depth of forming section 11a, 11b, 12a, 13a.In addition, in Fig. 9,11,13, exaggeration represents slot bottom The angle of inclination of forming face 12a1,13a1.
In dynamic pressure groove formation process, first, as shown in figure 8, in the sintered body 18 supported from below by low punch 13 Inner circumferential is inserted into plug 11, and the dynamic pressure groove of forming section 11a, 11b of plug 11 and the inner peripheral surface of sintered body 18 is made to form presumptive area It is opposed.In the state of axial position relationship of the sintered body 18 with plug 11 is maintained, as shown in Figure 10, upper punch is utilized 12 are pressed into sintered body 18 inner circumferential of former 14, so as to by the inner peripheral surface of sintered body 18 press on plug 11 forming section 11a, 11b.The shape transfer of forming section 11a, 11b is in the inner peripheral surface of sintered body as a result, so as to form dynamic pressure groove 8a1,8a2.
At the same time, sintered body 18 is oppressed from axial both sides using upper punch 12 and low punch 13, thus will be each Forming section 12a, 13a of punch 12,13 press on the both ends of the surface of sintered body 18.As a result, the shape transfer of forming section 12a, 13a in The both ends of the surface of sintered body 18, so as to shape dynamic pressure groove 8b1,8c1.Specifically, as shown in figure 11, each punch 12,13 is utilized Slot bottom forming face 12a1,13a1 of forming section 12a, 13a the end face of sintered body 18 is oppressed and shape dynamic pressure groove 8b1, 8c1, also, near the end face of sintered body 18 material occur Plastic Flow and enter each forming section 12a, 13a recess portion 12a2, 13a2, so as to shape mound portion 8b2,8c2.At this point, the depth of recess portion 12a2,13a2 is towards outside diameter with deepening, so as to fill out The height filled in mound portion 8b2,8c2 in recess portion 12a2,13a2 is increased with towards outside diameter.
Then, as shown in figure 12, sintered body 18 is discharged from the inner circumferential of former 14.Make sintered body 18 as a result, to radial outside Rebound, and the inner peripheral surface of sintered body 18 is removed from forming section 11a, 11b of the peripheral surface of plug 11, so as to by plug from sintering The inner circumferential extraction of body.Also, detach low punch 12,13, by forming section 12a, 13a of each punch 12,13 from sintered body 18 Both ends of the surface stripping.
At this point, when the axial oppressive force for discharging each punch 12,13, the rebound in axial direction is generated in sintered body 18, because This, as shown in figure 13, the height of mound portion 8b2,8c2 are lower (with reference to dotted line) than the state before rebound.Mound portion 8b2,8c2 are with direction Outside diameter and broaden, therefore, the deflection (amount of plastic deformation) when having been shaped by forming section 12a, 13a of upper low punch 12,13 It is more gone to outside diameter smaller.Therefore, the springback capacity (i.e. the reduction width of the height of mound portion 8b2,8c2) of mound portion 8b2,8c2 more to Outside diameter goes more to become larger.
On the other hand, for dynamic pressure groove 8b1, the 8c1 formed in the end face of sintered body 18, due to upper low punch 12,13 Forming section 12a, 13a generate decrement it is bigger, therefore, compared with mound portion 8b2,8c2, deflection (amount of plastic deformation) compared with Greatly.Therefore, in the oppressive force that low punch on releasing 12,13 generates, in the springback capacity that dynamic pressure groove 8b1,8c1 are generated very It is small.Therefore, the groove bottom of dynamic pressure groove 8b1,8c1 almost keep intact transferred with upper low punch 12,13 forming section 12a, 13a Slot bottom forming face 12a1,13a1 shape.In the present embodiment, slot bottom forming face 12a1,13a1 is respectively facing outside diameter And tilted to axially inner side (18 side of sintered body), therefore, the groove bottom of dynamic pressure groove 8b1,8c1 become towards outside diameter and to sintering The inclined face of axial center side of body 18.
As previously discussed, the top surface of mound portion 8b2,8c2 due to rebound towards outside diameter and it is inclined to axial center side In the case of, it is tilted by making the groove bottom of dynamic pressure groove 8b1,8c1 towards outside diameter to axial center side, it also can be by mound portion The height of 8b2,8c2, the i.e. groove depth of dynamic pressure groove 8b1,8c1 are ensured to be more than regulation.As a result, in the rotation of shaft component, The outer diameter end of dynamic pressure groove 8b1,8c1 nearby also give full play to the ability for concentrating oil, can improve the oil film pressure in thrust bearing gap Power and improve bearing rigidity.
In addition, the springback capacity of mound portion 8b2,8c2 are not constant on stricti jurise according to product, and therefore, mound portion 8b2,8c2 Height (particularly outer diameter end near height) according to product and there are some deviations.If the at this point, height of mound portion 8b2,8c2 Excessively high, then the region may be contacted with across the opposed component in thrust bearing gap (flange part 9, wheel hub 3).In present embodiment In, it is tilted by the groove bottom for making dynamic pressure groove 8b1,8c1 as described above, so as to both can ensure that the groove depth of dynamic pressure groove 8b1,8c1 It spends to be more than regulation, and the outer diameter end of the top surface of mound portion 8b2,8c2 can be made nearby to be retreated to the axial center side of sintered body 18, because This, is reliably prevented from mound portion 8b2,8c2 and the contact with its opposed component.
Then, sintered body 18 is taken out from slot coining die, so as to which hydrodynamic bearing 8 is completed.
The utility model is not limited to above-mentioned embodiment.Hereinafter, illustrating another embodiment of the utility model, but close In the point identical with above-mentioned embodiment, omit the description.
For example, in the above-described embodiment, show that setting passes through mold in the end face of the axial both sides of hydrodynamic bearing 8 The situation of dynamic pressure groove obtained from forming, but not limited to this, it can also be only logical in the end face setting of an axial side for hydrodynamic bearing 8 Dynamic pressure groove obtained from crossing die forming.For example, in the fluid dynamic-pressure bearing device 21 shown in Figure 14, in hydrodynamic bearing 8 Downside end face 8c is formed with dynamic pressure groove 8c1 shown in fig. 6, and dynamic pressure groove is not formed in the upside end face 8b of hydrodynamic bearing 8, and is formed Endless groove 8b3, radial direction slot 8b4.The sealing 7c prominent to radially inner side is equipped in the upper end of housing 7.In sealing 7c The inner peripheral surface 7c1 of taper and the peripheral surface 2a of axle portion 2 between be formed with wedge-shaped sealing space S.The side 7a of housing 7 and bottom Portion 7b is formed as not androgynous.Dynamic pressure groove is formed in the upside end face 7b1 of the bottom 7b of housing 7.In the downside end face of flange part 9 The thrust bearing gap of the first thrust bearing division T1 is formed between the upside end face 7b1 of the bottom 7b of 9b and housing 7.
In addition, it in the above-described embodiment, shows and passes through die forming dynamic pressure groove in the inner peripheral surface 8a of hydrodynamic bearing 8 The situation of 8a1,8a2, but the inner peripheral surface 8a of hydrodynamic bearing 8 can also be formed as barrel surface.It alternatively, can also be by the shell of Figure 14 The bottom 7b of body 7 as the utility model is related to hydrodynamic bearing.In this case, pass through in the upside end face 7b1 of bottom 7b Die forming dynamic pressure groove, the groove bottom of the dynamic pressure groove tilt downwards towards outside diameter.
In addition, in the above-described embodiment, show that hydrodynamic bearing 8 is fixed and the shaft component with axle portion 2 carries out The situation of rotation, but shaft component can also be fixed in contrast to this and rotate 8 side of hydrodynamic bearing.
In addition, in the above-described embodiment, lubricating fluid is shown a case that as oil, but in addition to this can also use Lubricating grease, magnetic fluid, air etc. are used as lubricating fluid.
In addition, the utility model is related to hydrodynamic bearing and the fluid dynamic-pressure bearing device that has the hydrodynamic bearing not only fill Enter and used in the spindle drive motor of the disk drive device of HDD etc., fan motor, the laser of cooling fan can also be packed into It is used in multi-panel scanning motor of beam printer etc..

Claims (8)

1. a kind of hydrodynamic bearing has dynamic pressure groove in the end face of an axial side side by die forming,
The hydrodynamic bearing is characterized in that,
The groove bottom of the dynamic pressure groove rolls oblique towards outside diameter and to axial the opposing party.
2. hydrodynamic bearing according to claim 1, wherein,
The hydrodynamic bearing is made of sintered body.
3. hydrodynamic bearing according to claim 1 or 2, wherein,
There is other dynamic pressure groove by die forming in the end face of axial the opposing party side,
The groove bottom of the other dynamic pressure groove rolls oblique towards outside diameter and to an axial side.
4. a kind of fluid dynamic-pressure bearing device, has：
Hydrodynamic bearing according to any one of claims 1 to 3；
Shaft component has the axle portion for the inner circumferential for being inserted into the hydrodynamic bearing and from the axle portion flange prominent to outer diameter side Portion, the shaft component carry out relative rotation relative to the hydrodynamic bearing；
Radial bearing portion, using between the journal bearing between the inner peripheral surface of the hydrodynamic bearing and the peripheral surface of the axle portion The Fluid pressure that gap generates in radial directions carries out the shaft component opposite bearing；
Thrust bearing division, using between the axial end face of a side side of the hydrodynamic bearing and the end face of the flange part The Fluid pressure that thrust bearing gap generates carries out the shaft component in thrust direction opposite bearing.
5. a kind of motor, with the fluid dynamic-pressure bearing device described in claim 4.
6. a kind of shaping dies is for by pressing to shape dynamic pressure groove from the end face of axial side's side bearing blank Shaping dies,
The shaping dies is characterized in that,
It is rolled for shaping the forming face of the groove bottom of the dynamic pressure groove towards outside diameter to axial the opposing party oblique.
7. shaping dies according to claim 6, wherein,
For shaping the depth of the recess portion in the mound portion between the circumferential direction of the dynamic pressure groove with being deepened towards outside diameter.
8. shaping dies according to claim 7, wherein,
The bottom surface of the recess portion is flat surface orthogonal to the axial direction.
CN201721063800.3U 2016-08-26 2017-08-23 Hydrodynamic bearing, fluid dynamic-pressure bearing device, motor and shaping dies Expired - Fee Related CN207526872U (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2016165840A JP6858508B2 (en) 2016-08-26 2016-08-26 Dynamic pressure bearings and their manufacturing methods
JP2016-165840 2016-08-26

Publications (1)

Publication Number Publication Date
CN207526872U true CN207526872U (en) 2018-06-22

Family

ID=61244865

Family Applications (2)

Application Number Title Priority Date Filing Date
CN201710733075.4A Active CN107781293B (en) 2016-08-26 2017-08-23 Dynamic pressure bearing, method of manufacturing the same, fluid dynamic pressure bearing device, motor, and molding die
CN201721063800.3U Expired - Fee Related CN207526872U (en) 2016-08-26 2017-08-23 Hydrodynamic bearing, fluid dynamic-pressure bearing device, motor and shaping dies

Family Applications Before (1)

Application Number Title Priority Date Filing Date
CN201710733075.4A Active CN107781293B (en) 2016-08-26 2017-08-23 Dynamic pressure bearing, method of manufacturing the same, fluid dynamic pressure bearing device, motor, and molding die

Country Status (3)

Country Link
JP (1) JP6858508B2 (en)
CN (2) CN107781293B (en)
WO (1) WO2018037822A1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107781293A (en) * 2016-08-26 2018-03-09 Ntn株式会社 Hydrodynamic bearing and preparation method, fluid dynamic-pressure bearing device, motor and shaping dies

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP7253874B2 (en) * 2018-03-08 2023-04-07 Ntn株式会社 Hydrodynamic bearing and its manufacturing method
JP2020165471A (en) * 2019-03-29 2020-10-08 日本電産株式会社 Gas dynamic pressure bearing, motor and blower
JP2023144590A (en) * 2022-03-28 2023-10-11 Ntn株式会社 Sintered oil-containing bearing, and fluid dynamic bearing device comprising the same

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6018614A (en) * 1984-05-31 1985-01-30 Taiho Kogyo Co Ltd Tapered land thrust bearing
JP3620815B2 (en) * 1997-09-11 2005-02-16 日立粉末冶金株式会社 Porous bearing
JP4811186B2 (en) * 2006-08-07 2011-11-09 日本電産株式会社 Hydrodynamic bearing device
JP5863422B2 (en) * 2011-11-30 2016-02-16 三菱重工業株式会社 Thrust bearing and rotating machine
JP2013185658A (en) * 2012-03-08 2013-09-19 Samsung Electro-Mechanics Japan Advanced Technology Co Ltd Rotary device and method of producing the same
JP6466105B2 (en) * 2014-09-01 2019-02-06 Ntn株式会社 Fluid dynamic bearing device and bearing member and shaft member used therefor
JP6858508B2 (en) * 2016-08-26 2021-04-14 Ntn株式会社 Dynamic pressure bearings and their manufacturing methods

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107781293A (en) * 2016-08-26 2018-03-09 Ntn株式会社 Hydrodynamic bearing and preparation method, fluid dynamic-pressure bearing device, motor and shaping dies

Also Published As

Publication number Publication date
WO2018037822A1 (en) 2018-03-01
CN107781293A (en) 2018-03-09
JP2018031460A (en) 2018-03-01
JP6858508B2 (en) 2021-04-14
CN107781293B (en) 2021-09-24

Similar Documents

Publication Publication Date Title
CN207526872U (en) Hydrodynamic bearing, fluid dynamic-pressure bearing device, motor and shaping dies
JP5384014B2 (en) Sintered bearing
WO2015045813A1 (en) Sintered metal bearing and fluid-dynamic bearing device provided with said bearing
CN103339393A (en) Fluid dynamic pressure bearing device
CN1807908B (en) Fluid lubrication bearing apparatus
WO2015012055A1 (en) Sintered bearing and process for producing same
CN105579721B (en) Sintered-metal bearing and its manufacture method
JP6461483B2 (en) Sintered bearing, fluid dynamic pressure bearing device including the same, and method for manufacturing sintered bearing
CN100564913C (en) The device of sintering sliding bearing and manufacture method thereof and this method of enforcement
JP6812113B2 (en) Sintered oil-impregnated bearing and its manufacturing method
CN101529104A (en) Dynamic-pressure bearing device, and bearing member manufacturing method
WO2017159345A1 (en) Dynamic pressure bearing and method for manufacturing same
JP7076266B2 (en) Manufacturing method of sintered oil-impregnated bearing
WO2015137059A1 (en) Sintered bearing, fluid dynamic bearing device and motor comprising same, and sintered bearing manufacturing method
JP7094118B2 (en) Sintered metal dynamic pressure bearing
WO2023189389A1 (en) Oil-impregnated sintered bearing and fluid dynamic bearing device including same
JP5606831B2 (en) Bearing member and manufacturing method thereof
JP2016180496A (en) Bearing member and manufacturing method thereof
JP2001041244A (en) Manufacture of bearing
JP2000240639A (en) Oil-impregnated sintered bearing and manufacture thereof
JP2006162077A (en) Method of manufacturing dynamic pressure type sintered oil retaining bearing and housing of information equipment spindle motor

Legal Events

Date Code Title Description
GR01 Patent grant
GR01 Patent grant
CF01 Termination of patent right due to non-payment of annual fee

Granted publication date: 20180622

CF01 Termination of patent right due to non-payment of annual fee