US20070278881A1 - Shaft Member For Hydrodynamic Bearing Apparatuses And A Method For Producing The Same - Google Patents

Shaft Member For Hydrodynamic Bearing Apparatuses And A Method For Producing The Same Download PDF

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Publication number
US20070278881A1
US20070278881A1 US11/629,910 US62991005A US2007278881A1 US 20070278881 A1 US20070278881 A1 US 20070278881A1 US 62991005 A US62991005 A US 62991005A US 2007278881 A1 US2007278881 A1 US 2007278881A1
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US
United States
Prior art keywords
hydrodynamic
shaft
bearing
face
radial
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Abandoned
Application number
US11/629,910
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English (en)
Inventor
Nobuyoshi Yamashita
Hideaki Kubota
Natsuhiko Mori
Keiji Nagasaki
Syoichi Kodera
Masato Utiumi
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
Fukui Byora Co Ltd
Original Assignee
NTN Corp
Fukui Byora Co Ltd
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
Priority claimed from JP2004261446A external-priority patent/JP4610973B2/ja
Priority claimed from JP2004261452A external-priority patent/JP4786157B2/ja
Application filed by NTN Corp, Fukui Byora Co Ltd filed Critical NTN Corp
Assigned to NTN CORPORATION, FUKUI BYORA CO., LTD. reassignment NTN CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: NAGASAKI, KEIJI, KODERA, SYOICHI, UTIUMI, MASATO, MAKINO, MASAHIRO, MORI, NATSUHIKO, KUBOTA, HIDEAKI, YAMASHITA, NOBUYOSHI
Publication of US20070278881A1 publication Critical patent/US20070278881A1/en
Abandoned legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B24—GRINDING; POLISHING
    • B24B—MACHINES, DEVICES, OR PROCESSES FOR GRINDING OR POLISHING; DRESSING OR CONDITIONING OF ABRADING SURFACES; FEEDING OF GRINDING, POLISHING, OR LAPPING AGENTS
    • B24B7/00—Machines or devices designed for grinding plane surfaces on work, including polishing plane glass surfaces; Accessories therefor
    • B24B7/10—Single-purpose machines or devices
    • B24B7/16—Single-purpose machines or devices for grinding end-faces, e.g. of gauges, rollers, nuts, piston rings
    • B24B7/162—Single-purpose machines or devices for grinding end-faces, e.g. of gauges, rollers, nuts, piston rings for mass articles
    • 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B24—GRINDING; POLISHING
    • B24B—MACHINES, DEVICES, OR PROCESSES FOR GRINDING OR POLISHING; DRESSING OR CONDITIONING OF ABRADING SURFACES; FEEDING OF GRINDING, POLISHING, OR LAPPING AGENTS
    • B24B5/00—Machines or devices designed for grinding surfaces of revolution on work, including those which also grind adjacent plane surfaces; Accessories therefor
    • B24B5/02—Machines or devices designed for grinding surfaces of revolution on work, including those which also grind adjacent plane surfaces; Accessories therefor involving centres or chucks for holding work
    • B24B5/04—Machines or devices designed for grinding surfaces of revolution on work, including those which also grind adjacent plane surfaces; Accessories therefor involving centres or chucks for holding work for grinding cylindrical surfaces externally
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B24—GRINDING; POLISHING
    • B24B—MACHINES, DEVICES, OR PROCESSES FOR GRINDING OR POLISHING; DRESSING OR CONDITIONING OF ABRADING SURFACES; FEEDING OF GRINDING, POLISHING, OR LAPPING AGENTS
    • B24B5/00—Machines or devices designed for grinding surfaces of revolution on work, including those which also grind adjacent plane surfaces; Accessories therefor
    • B24B5/18—Machines or devices designed for grinding surfaces of revolution on work, including those which also grind adjacent plane surfaces; Accessories therefor involving centreless means for supporting, guiding, floating or rotating work
    • 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
    • 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
    • F16C3/00—Shafts; Axles; Cranks; Eccentrics
    • F16C3/02—Shafts; Axles
    • 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
    • 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
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/08—Structural association with 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
    • F16C2370/00—Apparatus relating to physics, e.g. instruments
    • F16C2370/12—Hard disk drives or the like
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/49002—Electrical device making
    • Y10T29/4902—Electromagnet, transformer or inductor
    • Y10T29/49021—Magnetic recording reproducing transducer [e.g., tape head, core, etc.]
    • Y10T29/49025—Making disc drive
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/49544—Roller making
    • Y10T29/4956—Fabricating and shaping roller work contacting surface element
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/49544—Roller making
    • Y10T29/49565—One-piece roller making
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/49636—Process for making bearing or component thereof
    • Y10T29/49639—Fluid bearing

Definitions

  • the present invention relates to a shaft member for hydrodynamic bearing apparatuses which relatively rotatably supports the shaft member in the radial direction in a non-contact manner by the hydrodynamic effect which occurs in a radial bearing gap, and a method for producing the same.
  • a hydrodynamic bearing rotatably supports a shaft member by the hydrodynamic effect of lubricating oil which occurs in a bearing gap in a non-contact manner.
  • it is used in the spindle motor of disk-shaped recording medium drive units such as HDDs incorporated therein.
  • Hydrodynamic bearing apparatuses of this type are provided with a radial bearing portion which rotatably supports a shaft member in the radial direction in a non-contact manner, and a thrust bearing portion which rotatably supports the shaft member in the thrust direction in a non-contact manner.
  • Grooves for producing a hydrodynamic pressure are formed on the inner surface of a bearing sleeve or the outer surface of the shaft member, which constitutes the radial bearing portion.
  • hydrodynamic grooves are formed on both end faces of a flange portion of a shaft member which constitutes a thrust bearing portion, or on the face facing it (an end face of the bearing sleeve or an end face of a thrust member fixed on the housing, or the inner bottom face of the bottom of the housing, etc.) (for example, refer to patent document 1: Japanese Unexamined Patent Publication No. 2002-61641).
  • hydrodynamic grooves are formed, for example, on the outer surface of the shaft member in a herringbone arrangement or a spiral arrangement.
  • methods for forming the hydrodynamic grooves of this type include cutting (for example, refer to patent document 2: Japanese Unexamined Patent Publication No. H08-196056), etching (for example, refer to patent document 3: Japanese Unexamined Patent Publication No. H06-158357), among others.
  • a first object of the present invention is to provide a shaft member for hydrodynamic bearing apparatuses having higher dimensional accuracy at low costs and a method for producing the same.
  • a second object of the present invention is to provide a shaft member for hydrodynamic bearing apparatuses having hydrodynamic grooves processed with high accuracy without a large increase in the processing costs and a method for producing the same.
  • the present invention provides a shaft member for hydrodynamic bearing apparatuses which comprises a shaft portion and a flange portion both formed by forging, and a radial bearing face facing a radial bearing gap and formed on the outer periphery of the shaft portion, and the radial bearing face having a cylindricity of 3 ⁇ m or lower.
  • the cylindricity is defined as follows: when a cylindrical face (the target face of the cylindricity.
  • the radial bearing face of the shaft portion is placed between two geometrically correct coaxial cylindrical faces
  • the cylindricity is represented by the difference between the radii of the two coaxial cylindrical faces in the case where the interval between the two coaxial cylindrical faces (inscribed cylindrical face and circumscribed cylindrical face) is rendered minimum.
  • the radial bearing face can be any face facing the radial bearing gap which produces hydrodynamic effect, regardless of whether it has hydrodynamic grooves for producing hydrodynamic effect.
  • the cylindricity of the radial bearing face formed on the outer periphery of the shaft portion considerably affects the accuracy of particularly the radial bearing gap formed between the outer periphery of the shaft portion and the bearing component (bearing sleeve, housing, etc.) facing the outer periphery of the shaft portion. That is, if the value of the cylindricity becomes higher, the above radial bearing gap will not be constant in the circumferential direction or axial direction, making the difference between the widely gapped portions and narrowly gapped portions obvious.
  • the rotational torque of the shaft member at the narrowly gapped bearing portions becomes higher than at other portions, which leads to increased bearing loss, while the stiffness of the bearing becomes lower at the above widely gapped bearing portions than at other portions, which leads greater runout of the shaft.
  • the gap is not constant in the axial direction, an undesired flow of a lubricating fluid in the axial direction may occur and the appropriate circulation of the lubricating fluid may be adversely affected.
  • the cylindricity of the radial bearing face is defined to be 3 ⁇ m or lower. Accordingly, dimensional variation of the radial bearing gap in the circumferential direction or axial direction is suppressed, thereby suppressing the above bearing loss. This can also ensure the high stiffness of the bearing mentioned above. Therefore, the radial bearing gap between this shaft member and the bearing component facing the shaft member can be controlled with high accuracy to realize the high rotational accuracy of a bearing apparatus comprising the shaft member and bearing component.
  • the perpendicularity of both end faces of the flange portion and the perpendicularity of an end face of the shaft portion, relative to the radial bearing face formed on the outer periphery of the shaft portion are preferably 5 ⁇ m or lower, respectively.
  • the term “perpendicularity” is defined as follows: in the combination of a predetermined plane and a reference plane which should be perpendicular to each other, the perpendicularity is represented by the maximum value of the difference between the predetermined plane (an end face of the flange portion or an end face of the shaft portion herein) and a geometric plane which is geometrically perpendicular relative to the reference plane (the radial bearing face herein).
  • the value of the perpendicularity of the end face of the flange portion is higher than 5 ⁇ m, a variation is generated in a thrust bearing gap formed between the end face and that facing it, which may adversely affect the bearing performance including an increased bearing loss.
  • the value of the perpendicularity of the end face of the shaft portion is higher than 5 ⁇ m, it will be difficult to set the thrust bearing gap accurately, or when the end face of the shaft portion serves as the reference plane for grinding the outer surface of the shaft portion and the end face of the flange portion, the processing accuracy of these grinding surfaces may be lowered.
  • the above shaft member is formed of the shaft portion and flange portion respectively by forging.
  • both end faces of the shaft member an end face of the shaft portion and an end face of the flange portion located on both end faces of the shaft member
  • the shaft member having the radial bearing faces whose values of cylindricity and perpendicularity are suppressed can be obtained at low costs.
  • the shaft portion and flange portion of the above shaft member can be also integrally formed by forging for further cost reduction.
  • Forming a slanting recess portion at the corner of the shaft portion and flange portion can ensure the undercut of the grind stone in grinding both the outer surface of the shaft portion and the end face of the flange portion.
  • various methods can be usable as a method for forming this recess portion, forming by plastic processing is preferred from the perspective of inhibiting the production of burrs, impurities, etc., after processing.
  • the present invention provides a method for producing a shaft member for hydrodynamic bearing apparatuses which comprises a step of forming a shaft material having the shaft portion and flange portion integrally by forging; and a step of correcting the cylindricity of a part or the entire outer surface of the shaft portion. More preferably, the present invention provides a method for producing a shaft member for hydrodynamic bearing apparatuses, wherein a first grinding is performed on both end faces of the shaft material relative to the corrected face mentioned above, and a second grinding is then performed on at least the outer surface of the shaft material relative to the both end faces.
  • the cylindricity of the outer surface of the shaft portion is corrected after roughly forming of the shaft member (shaft material) having the shaft portion and flange portion integrally by forging. Therefore, highly accurate grinding (width grinding) can be performed relative to the corrected face in the first grinding step described later.
  • various plastic processing for example, rolling with round dies, flat dies, etc., can be used, as well as drawing compound, ironing, sizing by pressing (clipping) of split-cavity molds or the like.
  • both end faces located at both ends of the shaft material in the axial direction specifically an end face of the shaft portion and an end face of the flange portion are ground.
  • the end faces are ground relative to the outer circumferential surface of the shaft portion which has been subjected to the correcting process as mentioned above, these two end faces of the shaft material can be finished with highly accurate perpendicularity and flatness.
  • the second grinding is then performed on the outer surface of the shaft material relative to these two ground end faces of the shaft material.
  • Both end faces of the shaft material which are the reference planes, have been highly accurately finished in the first grinding step.
  • the target to be processed i.e., the outer circumferential surface of the shaft material can also be finished highly accurately.
  • the second grinding process is performed on at least a portion which will be the radial bearing face of the outer circumferential surface of the shaft material. Additionally, the process can also be performed on the outer circumferential surface of the flange portion. Furthermore, it can be performed on the other (on the shaft portion side) end face of the unground flange portion. In this second grinding step, these to-be-ground faces can be finished at a time by using grind stones (formed grind stone) having the outline shapes corresponding to these to-be-ground faces of the shaft material.
  • the shaft member in which the radial bearing face has the cylindricity of 3 ⁇ m or lower and both end faces of the flange portion and the end face of the shaft portion have the perpendicularity of 5 ⁇ m or lower, respectively, can be produced at low costs.
  • the above shaft member for hydrodynamic bearing apparatuses can be provided as a hydrodynamic bearing apparatus which comprises a bearing sleeve into which the shaft member is inserted at its inner surface; a radial bearing portion which produces pressure by the hydrodynamic effect which occurs in a radial bearing gap between the outer periphery of the shaft portion and the inner periphery of the bearing sleeve to support the shaft portion in the radial direction in a non-contact manner; a first thrust bearing portion which produces pressure by the hydrodynamic effect of a fluid which occurs in a thrust bearing gap on one end side of the flange portion to support the flange portion in the thrust direction in a non-contact manner; and a second thrust bearing portion which produces pressure by the hydrodynamic effect of the fluid occurring in the thrust bearing gap on the other end side of the flange portion to support the flange portion in the thrust direction in a non-contact manner.
  • hydrodynamic grooves for producing the hydrodynamic effect of the fluid can be formed asymmetrically in the axial direction on one of the outer circumferential surface of the shaft portion facing the radial bearing gap and the inner periphery face of the bearing sleeve opposing this outer circumferential surface.
  • the above hydrodynamic bearing apparatus can be provided as a motor which comprises a hydrodynamic bearing apparatus, a rotor magnet and a stator coil.
  • the present invention provides a shaft member for hydrodynamic bearing apparatuses which is a metallic shaft member for hydrodynamic bearing apparatuses which integrally comprises the shaft portion and the flange portion, in which a radial hydrodynamic groove region comprising the hydrodynamic grooves and demarcation portions demarcating each hydrodynamic groove is formed by plastic processing on the outer periphery of the shaft portion, and the outer circumferential surfaces of the demarcation portions in the radial hydrodynamic groove region are grinding surfaces.
  • the demarcation portions herein refer to the portions which demarcate the hydrodynamic grooves, including the so-called ridges between the hydrodynamic grooves.
  • so-called smooth portions which divide those slanting hydrodynamic grooves in the axial direction are also included in the demarcation portions.
  • the radial hydrodynamic groove region comprising the hydrodynamic grooves and demarcation portions demarcating each hydrodynamic groove is formed by plastic processing on the outer periphery of the shaft portion of the shaft member.
  • cutting powders are not produced unlike in cutting, thereby saving materials.
  • the trouble of performing masking preliminarily for preventing of corrosion can be dispensed with, and processing costs can be thus greatly reduced on the whole.
  • the present invention is characterized in that the outer circumferential surfaces of the demarcation portions in the radial hydrodynamic groove region are grinding surfaces.
  • These grinding surfaces are obtained by grinding the outer diameter portions of the demarcation portions (the top portions adjacent to the hydrodynamic grooves) demarcating the hydrodynamic grooves of the radial hydrodynamic groove regions formed by plastic processing. Accordingly, precise processing of the hydrodynamic groove region, which cannot be achieved only by plastic processing, is enabled, and the dimensional accuracy of the outer diameter and surface roughness can be accurately obtained. Therefore, according to the present invention, improved processing accuracy and reduced processing costs can be both achieved, such radial bearing gap in hydrodynamic bearing apparatuses can be controlled highly accurately.
  • Such a hydrodynamic groove region can be formed, for example, on both end faces of the flange portion formed integrally with the shaft portion by plastic processing.
  • the flange portion is so constructed that thrust hydrodynamic groove regions comprising the hydrodynamic grooves and demarcation portions demarcating each hydrodynamic groove are formed on its both end faces and the end face in axial direction of the demarcation portions in these thrust hydrodynamic groove regions are grinding surfaces.
  • the radial hydrodynamic groove region can be formed, for example, by a rolling process or a forging process.
  • both the radial hydrodynamic groove region and thrust hydrodynamic groove region can be formed by a forging process.
  • the shaft portion and flange portion, in which these hydrodynamic groove regions are formed, respectively can be formed, for example, integrally by forging.
  • the present invention also provides a method for producing a shaft member for hydrodynamic bearing apparatuses which comprises a shaft portion and a flange portion integrally, and a radial hydrodynamic groove region comprising hydrodynamic grooves and demarcation portions demarcating each hydrodynamic groove on the outer periphery of the shaft portion, the method comprising forming a radial hydrodynamic groove region by plastic processing on the outer periphery of the shaft portion of the shaft material, and then grinding a portion including an outer diameter portion of the demarcation portion in the radial hydrodynamic groove region.
  • both an improvement in the processing accuracy of the radial hydrodynamic groove region and reduction of the processing costs can be achieved.
  • forming the shaft material which integrally has the shaft portion and the flange portion by forging can realize further reduction of processing costs, or reduction of the cycle time per product.
  • Examples of the plastic processing of the radial hydrodynamic groove region employed include a forging process.
  • both the shaft material and radial hydrodynamic groove region can be formed by forging, and forging of them can be performed simultaneously. Accordingly, such a processing step can be simplified and the cycle time required for processing can be even reduced.
  • both the formation of the radial hydrodynamic groove region and the correction of the cylindricity of a portion including the radial hydrodynamic groove region of the shaft portion can be performed by rolling simultaneously so that such a processing step can be simplified and the cycle time can be shortened.
  • the mass productivity of the product can be dramatically improved.
  • the above shaft member for hydrodynamic bearing apparatuses can be presented, for example, as a hydrodynamic bearing apparatus which comprises a shaft member for hydrodynamic bearing apparatuses; and a sleeve member into which this shaft member is inserted at its inner surface and which forms a radial bearing gap between itself and the shaft member, which retains the shaft member and sleeve member in a non-contact manner by the hydrodynamic effect of a fluid occurring in the radial bearing gap.
  • the bearing sleeve can be formed, for example, from an oil-containing sintered metal, and a thrust hydrodynamic groove region can be formed on an end face in the axial direction of the sleeve instead of the end face of the flange portion.
  • the above hydrodynamic bearing apparatus can be provided as a motor comprising this hydrodynamic bearing apparatus, a rotor magnet and a stator coil.
  • the outer circumferential surface of the shaft portion and the end face of the flange portion of the shaft member involved in the formation of the radial bearing gap and thrust bearing gap can be processed highly accurately at low costs. Therefore, these bearing gaps of the hydrodynamic bearing apparatus incorporating the shaft member can be controlled highly accurately. As a result, high rotational accuracy can be imparted to the above hydrodynamic bearing apparatus.
  • the hydrodynamic grooves formed on the shaft member can be processed accurately without an increase in such processing costs.
  • the bearing performance of the hydrodynamic bearing apparatus integrating this shaft member can be exerted stably for a long term by controlling the bearing gap in the hydrodynamic bearing apparatus highly accurately.
  • FIG. 1 is a side elevational view of a shaft member for the hydrodynamic bearing apparatus according to the first embodiment of the present invention.
  • FIG. 2 is a cross-sectional view of a spindle motor for an information appliance integrating a hydrodynamic bearing apparatus comprising a shaft member.
  • FIG. 3 is a longitudinal sectional view of a hydrodynamic bearing apparatus.
  • FIG. 4 is a longitudinal sectional view of a bearing sleeve.
  • FIG. 5 is a side elevational view of a shaft material formed by a forging process.
  • FIG. 6 is a schematic illustration of a correcting process (rolling process) by round dies.
  • FIG. 7 is a schematic illustration of a correcting process (rolling process) by flat dies.
  • FIG. 8 is a schematic illustration showing an example a grinding apparatus according to the width grinding step of a shaft material.
  • FIG. 9 is a partial cross-sectional view showing an example of a grinding apparatus according to the width grinding step.
  • FIG. 10 is a schematic illustration showing an example of a grinding apparatus according to the full-face grinding step of a shaft material.
  • FIG. 11 is a schematic illustration showing an example of a grinding apparatus according to the grinding finishing step of a shaft material.
  • FIG. 12 is an expanded sectional view of the vicinity of the corner between the shaft portion and flange portion of a shaft member.
  • FIG. 13 is a side elevational view of a shaft member for a hydrodynamic bearing apparatus according to the second embodiment of the present invention.
  • FIG. 14 is a top view of the flange portion of a shaft member seen from the direction of arrow A.
  • FIG. 15 is a bottom view of the flange portion of a shaft member seen from the direction of arrow B.
  • FIG. 16 is a longitudinal sectional view of a hydrodynamic bearing apparatus comprising a shaft member.
  • FIG. 17 is a side elevational view of a shaft material formed by a forging process.
  • FIG. 18 is a top view of the flange portion of a shaft material seen from the direction of arrow A.
  • FIG. 19 is a bottom view of the flange portion of a shaft material seen from the direction of arrow B.
  • FIG. 20 is an expanded sectional view of a thrust hydrodynamic groove region formed on the end face of a flange portion on the side opposite to the shaft portion prior to grinding.
  • FIG. 21 is an expanded sectional view of a thrust hydrodynamic groove region after being ground.
  • FIGS. 1-12 A first embodiment of the present invention will be described below with reference to FIGS. 1-12 .
  • FIG. 2 conceptionally shows a constitutional example of a spindle motor for an information appliance incorporating a hydrodynamic bearing apparatus 1 according to the first embodiment of the present invention.
  • This spindle motor for an information appliance is used for disk drive units such as HDDs, and comprises the hydrodynamic bearing apparatus 1 which rotatably supports a shaft member 2 in a non-contact manner, a disk hub 3 which is mounted on the shaft member 2 , for example, a stator coil 4 and a rotor magnet 5 facing each other across a gap in the radial direction, and a bracket 6 .
  • the stator coil 4 is mounted on the outer periphery of the bracket 6
  • the rotor magnet 5 is mounted on the inner periphery of the disk hub 3 .
  • the bracket 6 has the hydrodynamic bearing apparatus 1 mounted on its inner periphery. Moreover, the disk hub 3 retains one or more disks D such as magnetic disks on its outer periphery.
  • the rotor magnet 5 is rotated by the excitation between the stator coil 4 and rotor magnet 5 , whereby the disk hub 3 and the disk D retained by the disk hub 3 is rotated unitarily with the shaft member 2 .
  • FIG. 3 shows the hydrodynamic bearing apparatus 1 .
  • This hydrodynamic bearing apparatus 1 is mainly constituted of a housing 7 having a bottom 7 b at its one end, a bearing sleeve 8 fixed on the housing 7 , and a shaft member 2 inserted at the inner periphery of the bearing sleeve 8 .
  • the bottom 7 b side of the housing 7 is referred to as the lower side, and the side opposite to the bottom 7 b is referred to as the upper side in the following description.
  • the housing 7 is constituted of, for example, a side portion 7 a formed of a resin material such as LCP, PPS and PEEK in the form of a cylinder, and a bottom 7 b located at one end side of the side portion 7 a and, for example, formed of a metallic material.
  • the bottom 7 b is formed separately from the side portion 7 a , is retrofitted on the lower inner periphery of the side portion 7 a .
  • hydrodynamic grooves are formed, for example, in the form of a spiral, as a portion for producing hydrodynamic pressure, although not shown in the Figs.
  • the bottom 7 b is formed separately from the side portion 7 a , and is fixed on the lower inner periphery of the side portion 7 a . It can be, however, formed integrally with the side portion 7 a , for example, from a resin material.
  • the hydrodynamic grooves provided on the upper end face 7 b 1 can be molded simultaneously with the injection molding of the housing 7 comprising the side portion 7 a and bottom 7 b , which can dispense with the trouble of forming the hydrodynamic grooves on the bottom 7 b.
  • the bearing sleeve 8 is formed of, for example, a porous body made of a sintered metal, especially a porous body of a sintered metal comprising copper as a main ingredient in the form of a cylinder, and is fixed at a predetermined position on an inner surface 7 c of the housing 7 .
  • a radial hydrodynamic pressure producing part is formed.
  • the upper hydrodynamic groove 8 a 1 is formed asymmetrically in the axial direction relative to the axial center m (the axial center of the region between the upper and lower slanted grooves), the axial dimension X 1 of the region above the center m in the axial direction is larger than the axial dimension X 2 of the region therebelow.
  • a region in which a plurality of hydrodynamic grooves are arranged spirally is formed throughout the lower end face 8 b of the bearing sleeve 8 or in a part of annular region, as a portion for producing thrust hydrodynamic pressure.
  • a sealing member 9 as a sealing means is formed of, for example, a soft metallic material such as brass and other metallic materials, or a resin material in a ring shape, as shown in FIG. 3 .
  • the sealing member 9 is press-fitted to the upper inner periphery of the side portion 7 a of the housing 7 , and is fixed by means of adhesion or the like.
  • the inner surface 9 a of the sealing member 9 is formed in the shape of a cylinder, and the lower end face 9 b of the sealing member 9 is in contact with the upper end face 8 C of the bearing sleeve 8 .
  • the shaft member 2 is formed of a metallic material such as stainless steel, and has a T-shaped cross section integrally comprising a shaft portion 21 and a flange portion 22 provided at the lower end of the shaft portion 21 .
  • radial bearing faces 23 a , 23 b facing the formation region of two hydrodynamic grooves 8 a 1 , 8 a 2 formed on the inner surface 8 a of the bearing sleeve 8 are formed at two axially separated positions.
  • the face 23 a and a tapered face 24 whose diameter gradually decreases toward the shaft tip are formed adjacently.
  • a cylinder face 25 which serves as a mounting portion of the disk hub 3 , is formed.
  • Annular recess portions 26 , 27 , 28 are formed between the two radial bearing faces 23 a , 23 b , between the other radial bearing face 23 b and flange portion 22 , and between the tapered face 24 and cylinder face 25 , respectively.
  • thrust bearing faces 22 a , 22 b facing the hydrodynamic groove regions formed on the lower end face 8 b of the bearing sleeve and the upper end face 7 b 1 of the bottom 7 b , respectively, are formed.
  • annular sealing space S whose radial dimension gradually increases upwardly from the bottom 7 b side of the housing 7 .
  • the oil level is within the range of the sealing space S.
  • the shaft member 2 is produced in mainly two steps: (A) forming step and (B) grinding step.
  • the (A) forming step includes a forging process (A- 1 ) and a correcting process (A- 2 )
  • the (B) grinding step includes width grinding (B- 1 ), full-face grinding (B- 2 ) and finish grinding (B- 3 ).
  • a bar material made of metal such as stainless steel which is a material of the shaft member 2 to be formed is cold-forged to form the shaft material 10 having a T-shaped cross section and integrally having the shaft portion 11 and flange portion 12 , as shown in FIG. 5 .
  • the cold-forging method used may be any of extrusion, upsetting, heading or the like, or combinations of them.
  • the outer circumferential surface 11 a of the shaft portion 11 after being subjected to the forging process has such a different diameter shape that the tapered face 14 is disposed therebetween, but may be formed to have a uniform diameter throughout its length by dispensing with the tapered face 14 .
  • forming the shaft material 10 by forging does not produce cutting allowance and can reduce wasted materials compared with forming the shaft material 10 having a similar shape by, for example, cutting or the like. Moreover, since it is a pressing operation, the cycle time per piece of the shaft material 10 can be improved, thereby improving the productivity.
  • the outer circumferential surface 11 a of the shaft portion of the shaft material 10 after being subjected to the forging process is subjected to a plastic processing for correcting the cylindricity.
  • This improves the cylindricity of the face 13 subjected to the correcting process, of the outer circumferential surface of the shaft portion 11 a of the shaft material 10 so that it falls within a required range (for example, 10 ⁇ m or lower).
  • the correcting process of the cylindricity employed may be, for example, a rolling process by using round dies 34 , flat dies 35 , etc., as shown in FIG. 6 or FIG. 7 .
  • the correcting process is conducted throughout the length of the outer circumferential surface of the shaft portion 11 , or can be conducted on a part thereof.
  • its processed region includes at least the region which will be the radial bearing faces 23 a , 23 b of the shaft member 2 .
  • a grinding apparatus 40 used in this grinding step comprises, for example, a carrier 41 which retains a plurality of the shaft material 10 as workpieces, and a pair of grind stones 42 , 42 which grinds the end face 11 b of the shaft portion of the shaft material 10 retained by the carrier 41 and the end face 12 b of the flange portion 12 on the side opposite to the shaft portion, as shown in FIG. 8 .
  • a plurality of notches 43 are provided on a part of the circumferential region of the outer circumferential edge of the carrier 41 at an equal pitch in the circumferential direction.
  • the shaft material 10 is contained in the notch 43 with its correcting process face 13 in angular contact with the inner face 43 a of the notch 43 .
  • the correcting process face 13 of the shaft material 10 protrudes slightly from the outer circumferential surface of the carrier 41 , and on the outer diameter side of the carrier, a belt 44 is provided in a tensioned state to bind the protruding portions of the shaft material 10 from the outer diameter side.
  • a pair of grind stones 42 , 42 are coaxially disposed with their end faces (grinding surfaces) facing each other at a predetermined interval.
  • the shaft material 10 is sequentially loaded into the notch 43 from a determined position.
  • the loaded material 10 traverses the end faces of the rotating grind stones 42 , 42 from their outer diameter edge toward the inside diameter edge, while being prevented from falling off from the notch 43 by binding of the belt 44 .
  • both end faces of the shaft material 10 i.e., the end face 11 b of the shaft portion and the end face 12 b of the flange portion 12 on the side opposite to the shaft portion are ground by the end faces of the grind stones 42 , 42 .
  • the corrected face 13 of the shaft material 10 is supported by the carrier 41 and this corrected face 13 has high cylindricity.
  • the perpendicularity of the rotation axis of the grind stone 42 and the grinding surface of the grind stone 42 and the parallelism of the rotation axis of the grind stone 42 and the rotation axis of the carrier 41 , etc. are controlled in advance with highly accuracy, relative to this corrected face 13 , the above-mentioned both end faces 11 b, 12 b of the shaft material 10 can be finished with high accuracy, enabling to suppress the value of the perpendicularity relative to the corrected face 13 .
  • the width of the shaft material 10 in the axial direction (the overall length including the flange portion 12 ) can be finished to have a predetermined size.
  • the outer circumferential surface 10 b of the shaft material 10 and the end face 12 a on the shaft portion side of the flange portion 12 are ground relative to both end faces 11 b , 12 b of the ground shaft material (second grinding step).
  • the grinding apparatus used in this grinding step is, for example, plunge-ground by the grind stone 53 with the back plate 54 and pressure plate 55 pressed against both end faces of the shaft material 10 , as shown in FIG. 10 .
  • the corrected face 13 of the shaft material 10 is rotatably supported by a shoe 52 .
  • the grind stone 53 is a formed grind stone which comprises a grinding surface 56 corresponding to the outer circumferential surface shape of the shaft member 2 as a finished product.
  • the grinding surface 56 comprises a cylinder grinding portion 56 a which grinds the outer circumferential surface 11 a throughout the axial length of the shaft portion 11 and the outer circumferential surface 12 c of the flange portion 12 ; and a plane grinding portion 56 b which grinds the end face 12 a on the shaft portion side of the flange portion 12 .
  • the grind stone 53 comprises, as the cylinder grinding portion 56 a , portions 56 a 1 , 56 a 2 , which grind the regions corresponding to the radial bearing faces 23 a , 23 b of the shaft member 2 , a portion 56 a 3 , which grinds the region corresponding to the tapered face 24 , a portion 56 a 4 , which grinds the region corresponding to the cylinder face 25 , portions 56 a 5 - 56 a 7 , which grind the recess portions 26 - 28 , respectively, and a portion 56 a 8 , which grinds the outer circumferential surface 12 c of the flange portion 12 .
  • the grind stone 53 is fed in a diagonal direction (the direction of arrow 1 in FIG. 10 ) with the shaft material 10 and grind stone 53 rotating, and the plane grinding portion 56 b of the grind stone 53 is pressed against the end face 12 a on the shaft portion side of the flange portion of the shaft material 10 , to mainly grind the end face 12 a on the shaft portion side. This causes the end face 12 a on the shaft portion side in the flange portion 22 of the shaft member 2 to be ground. Subsequently, the grind stone 53 is fed in the direction perpendicular to the rotation axis of the shaft material 10 (the direction of arrow 2 in FIG.
  • the cylinder grinding portion 56 a of the grind stone 53 is pressed against the outer circumferential surface 11 a of the shaft portion 11 of the shaft material 10 and the outer circumferential surface 12 c of the flange portion 12 to grind the faces 11 a, 12 c .
  • the regions 13 a , 13 b corresponding to the radial bearing faces 23 a , 23 b of the shaft material 10 are ground, and the recess portions 26 - 28 are formed.
  • the radial bearing faces 23 a , 23 b of the shaft member 2 and regions 13 s , 13 b , 15 corresponding to the cylinder face 25 are subjected to final finish grinding.
  • a grinding apparatus used in this grinding for example, performs plunge grinding by the grind stone 63 , while rotating the shaft material 10 held between the back plate 64 and pressure plate 65 by the cylinder grinder shown in FIG. 11 .
  • the shaft material 10 is rotatably supported by a shoe 62 .
  • a grinding surface 63 a of the grind stone 63 comprises the first cylinder grinding portion 63 a 1 , which grinds the regions 13 a , 13 b corresponding to the radial bearing faces 23 a , 23 b , and the second cylinder grinding portion 63 a 2 , which grinds the region 15 corresponding to the cylinder face 25 .
  • the rotating grind stone 63 is provided with the feed in the radial direction so that the radial bearing faces 23 a , 23 b and the regions 13 a , 13 b , 15 corresponding to the cylinder face 25 are ground respectively and these regions are finished with a final surface accuracy.
  • the regions corresponding to the radial bearing face 23 a , 23 b and the region corresponding to the cylinder face 25 are both subjected to finish grinding, the grinding of the region corresponding to the cylinder face 25 may be dispensed with.
  • the shaft member 2 as long as it is produced by the production method mentioned above, can be finished to have the cylindricity of the radial bearing faces 23 a , 23 b formed on the outer periphery of the shaft portion 21 of, for example, 3 ⁇ m or lower (desirably 1.5 ⁇ m or lower).
  • This allows, for example, variation in the radial bearing gap formed between itself and the inner periphery of the bearing sleeve 8 of in the hydrodynamic bearing apparatus 1 in the circumferential direction or axial direction to fall within a predetermined range, preventing bearing performance from being adversely affected by the variation of the above radial bearing gap.
  • the shaft member 2 in which the perpendicularity of both end faces of the flange portion 22 (thrust bearing faces) 22 a , 22 b and the perpendicularity of the end face 21 b of the shaft portion are both 5 ⁇ m or lower, relative to the radial bearing faces 23 a , 23 b formed on the outer periphery of the shaft portion 21 according to the above production method.
  • the thrust bearing faces 22 a , 22 b formed on both end faces of the flange portion 22 form the thrust bearing gap between the face opposing them (the lower end face 8 b of the bearing sleeve 8 and the upper end face 7 b 1 of the bottom 7 b of the housing 7 , etc.) and themselves.
  • the numerical value of such perpendicularity can be thus suppressed to a low level, whereby variation in of the above thrust bearing gap can be reduced.
  • the end face 21 b of the shaft portion serves not only as the reference plane for grinding the outer circumferential surface of the shaft portion 21 and the upper end face of the flange portion 22 (thrust bearing face 22 a side), but also as the reference plane for setting the above thrust bearing gap. Accordingly, by suppressing the numerical value of the perpendicularity of the end face 21 b of the shaft portion to a low level, and such a grinding face, as well as the thrust bearing gap, can be controlled highly accurately.
  • the cylinder grinding of the outer circumferential surface 10 b of the shaft material 10 and the plane grinding of the end face 12 a on the shaft portion side of the flange portion 12 are performed by the common grind stone 53 , but both grinding may be performed by different grind stones.
  • the recess portions 26 - 28 of the shaft member 2 are formed in the full-face grinding (B- 2 ) shown in FIG. 10 was exemplified.
  • these recess portions 26 - 28 may be subjected to the plastic processing (for example rolling) simultaneously in correcting process shown in FIGS. 6 and 7 .
  • the recess portion 27 of the corner between the shaft portion 21 and flange portion 22 is formed obliquely as shown in FIG. 12 .
  • the recess portion 27 to also serve as an undercut of the grind stone 53 for grinding the end face 12 a on the shaft portion side of the flange portion 12 and the outer circumferential surface of the shaft portion 11 a simultaneously in the full-face grinding (refer to FIG. 10 ).
  • the radial bearing faces 23 a , 23 b of the shaft member 2 and thrust bearing faces 22 a , 22 b are all smooth surfaces having no hydrodynamic grooves
  • hydrodynamic grooves may be formed on these bearing faces.
  • the radial hydrodynamic grooves can be formed by rolling or forging
  • the thrust hydrodynamic groove can be formed by pressing or forging, at the stage preceding the full-face grinding shown in FIG. 10 .
  • FIGS. 13-21 A second embodiment of the present invention will be described below with reference to FIGS. 13-21 . Note that the parts and components having the same constitution and action as the constitution (first embodiment) shown in FIGS. 1-12 are denoted by the identical reference numerals, and repeated explanations are omitted.
  • FIG. 16 shows a hydrodynamic bearing apparatus 101 according to the second embodiment of the present invention.
  • This hydrodynamic bearing apparatus 101 is also used in a spindle motor for disk drive units shown in FIG. 2 incorporated therein, and constitutes a motor together with, for example, a disk hub 3 , stator coil 4 , rotor magnet 5 and bracket 6 shown in the same Figs ( FIG. 2 ).
  • the hydrodynamic bearing apparatus 101 comprises a housing 7 having a bottom 7 b at its one end, a bearing sleeve 8 fixed on to the housing 7 , a shaft member 102 inserted at the inner periphery of the bearing sleeve 8 , and a sealing member 9 as its main components.
  • the side of the bottom 7 b of the housing 7 is referred to as the lower side
  • the side opposite to the bottom 7 b is referred to as the upper side in the description below.
  • the shaft member 102 is formed of, for example, a metallic material such as stainless steel, and has a T-shaped cross section integrally comprising a shaft portion 121 and a flange portion 122 provided at the lower end of the shaft portion 121 .
  • a cylinder region, radial hydrodynamic groove regions 123 a , 123 b are formed at two axially separated positions.
  • an inner surface 8 a of a bearing sleeve 8 facing the radial hydrodynamic groove regions 123 a , 123 b is a cylindrical face having no hydrodynamic grooves and having a circular cross section.
  • These two upper and lower hydrodynamic groove regions 123 a , 123 b comprise a plurality of hydrodynamic grooves 123 a 1 , 123 b 1 and demarcation portions 123 a 2 , 123 b 2 demarcating the hydrodynamic grooves 123 a 1 , 123 b 1 , respectively.
  • they are both in a herringbone shape.
  • the upper radial hydrodynamic groove region 123 a is formed asymmetrically in the axial direction relative to the axial center m (the center in the axial direction of the region between the upper and lower slanted grooves), and the axial dimension X 1 of the region above the axial center m is larger than the axial dimension X 2 of the region therebelow.
  • a thrust hydrodynamic groove region 122 a is formed.
  • a thrust hydrodynamic groove region 122 b is formed in a part of its annular region of the lower end face of the flange portion 122 .
  • These thrust hydrodynamic groove regions 122 a , 122 b comprise respectively a plurality of hydrodynamic grooves 122 a 1 , 122 b 1 and demarcation portions 122 a 2 , 122 b 2 demarcating the hydrodynamic groove 122 a 1 , 122 b 1 .
  • each of the region forms a spiral shape.
  • the thrust hydrodynamic groove regions 122 a , 122 b may be in the shape, for example, of a herringbone shape or the like, without being limited to the shape shown particularly.
  • each of the upper and lower faces may have different hydrodynamic groove shapes.
  • the radial hydrodynamic groove region 123 a a tapered face 124 , of which diameter gradually decreases toward the shaft tip, is formed adjacently, and a cylinder face 125 , which will be a mounting portion of the disk hub 3 , is formed further thereabove.
  • Annular recess portions 126 , 127 , 128 are formed between the two radial hydrodynamic groove regions 123 a , 123 b , between the other radial hydrodynamic groove region 123 b and the flange portion 122 , and between the tapered face 124 and the cylinder face 125 , respectively.
  • annular sealing space S whose size in the radial direction is gradually increased upwardly from the bottom 7 b side of the housing 7 is formed.
  • the oil level is maintained within the range of the sealing space S.
  • a first thrust bearing portion T 11 and a second thrust bearing portion T 12 which rotatably support the shaft member 102 in the thrust direction in a non-contact manner are formed by the pressure of these oil films.
  • the shaft member 102 is produced in mainly two steps: (C) forming step and (D) grinding step.
  • the (C) forming step comprises a shaft material forming process (C- 1 ), a thrust hydrodynamic groove region forming process (C- 2 ), a radial hydrodynamic groove region forming process (C- 3 ), and a shaft portion correcting process (C- 4 ).
  • the (D) grinding step comprises a width grinding process (D- 1 ), a full-face grinding process (D- 2 ), and a finish grinding process (D- 3 ).
  • a material of the shaft member 102 to be formed i.e., a metal material such as stainless steel is compression-formed (forging process) by using molds, for example, as shown in FIG. 17 , in a cold state, whereby the shaft material 110 integrally having the region 111 corresponding to the shaft portion (hereinafter referred to simply as a shaft portion) and the region 112 corresponding to the flange portion (hereinafter referred to simply as a flange portion) is formed (shaft material forming process (C- 1 )).
  • the molds used in the forge forming of this shaft material 110 also serves as the molds for forming thrust hydrodynamic groove regions 112 a , 112 b on the flange portion 112 in this embodiment.
  • plastic processing is performed in the positions corresponding to both end faces of the flange portion 112 .
  • thrust hydrodynamic groove regions 112 a (the shaft portion side), 112 b (opposite to the shaft portion side) comprising a plurality of hydrodynamic groove 112 a 1 , 112 b 1 and demarcation portions 112 a 2 , 112 b 2 demarcating these hydrodynamic grooves 112 a 1 , 112 b 1 are formed (thrust hydrodynamic groove region formation process (C- 2 )).
  • a method of cold-forging employed in the above forming step may be extrusion, upsetting, heading or the like, or combinations of them.
  • the outer circumferential surface lila of the shaft portion 111 after the forging process has a different diameter shape in which a tapered face 114 and a cylinder face 115 , which is upwardly continuous with the tapered face 114 and has a diameter smaller than other portions, are disposed therebetween, and the tapered face 114 may be dispensed with and formed to have a uniform dimer throughout its length.
  • Note that described in this embodiment is the case where the forming of the shaft material 110 and the forming of the thrust hydrodynamic groove regions 112 a , 112 b are conducted simultaneously by the forging process. However, both steps need not necessarily be performed simultaneously, and the thrust hydrodynamic groove regions 112 a , 112 b may be formed by plastic processing, for example, a forging process, pressing process or the like after forming the shaft material 110 by forging.
  • the shaft portion 111 of the shaft material 110 formed by forging in the previous step is pressurized a pair of rolling dies (for example, round dies, flat dies, etc.), for example, in the shape shown in FIGS. 6 or 7 and the pair of rolling dies are reciprocated in the directions opposite to each other so that a hydrodynamic groove transcription face previously formed on the holding face of either of the pair of rolling dies are transcribed (radial hydrodynamic groove region forming process (C- 3 )) on the outer circumferential surface 111 a of the shaft portion 111 .
  • a pair of rolling dies for example, round dies, flat dies, etc.
  • a rolling process for correcting cylindricity is conducted (shaft portion correcting process (C- 4 )) on the outer circumferential surface 111 a of the shaft portion 111 simultaneously with transcription of the above hydrodynamic grooves.
  • radial hydrodynamic groove regions 113 a , 113 b having the shape shown in FIG. 17 are formed at two axially separated positions on the outer circumferential surface 111 a of the shaft portion 111 , while out of the outer circumferential surface 111 a of the shaft portion, a face 113 including radial hydrodynamic groove regions 113 a , 113 b (for example, the bottom faces of hydrodynamic grooves 113 a 1 , 113 b 1 and the outer circumferential surfaces of demarcation portions 113 a 2 , 113 b 2 demarcating the hydrodynamic grooves 113 a 1 , 113 b 1 ) is corrected, and the cylindricity of the face 113 subjected to the correcting process is improved to be within a desired range (for example, 10 ⁇ m or lower). Simultaneously, the cylinder face 115 of the upper end of the shaft portion 111 is also subjected to a correcting process, and the c
  • forming of the radial hydrodynamic groove regions 113 a , 113 b and correction of the outer circumferential surface 111 a of the shaft portion can be both performed simultaneously by rolling.
  • a procedure to perform a rolling process of the radial hydrodynamic groove regions 113 a , 113 b on the face subjected to the correcting process can be also employed.
  • various processing methods including a rolling process, drawing, ironing, sizing by pressing split-cavity molds (clipping) and the like, can be employed in the correcting process of the cylindricity.
  • the correcting process is performed throughout the length of the outer circumferential surface 111 a of the shaft portion 111 , or can be conducted on a part of the outer circumferential surface 111 a as long as the part includes the radial hydrodynamic groove regions 113 a , 113 b.
  • the forming of the shaft material 110 integrally comprising the shaft portion 111 and flange portion 112 and the forming of the thrust hydrodynamic groove regions 112 a , 112 b on both end faces of the flange portion 112 are simultaneously performed both by forging, and in addition, the forming of the radial hydrodynamic groove regions 113 a , 113 b and the correcting process of the outer circumferential surface 111 a of the shaft portion are performed simultaneously both by rolling, whereby such processing steps can be simplified and machining time can be greatly shortened.
  • employing forging processes and rolling processes in which the cycle time per processed item is shorter can further shorten the machining time, enabling further cost reduction and improvement in mass productivity.
  • the height h 1 from the bottom face 112 b 3 of the hydrodynamic groove 112 b 1 to the axial end face 112 b 4 of the demarcation portion 112 b 2 in the thrust hydrodynamic groove region 112 b is set to a suitable value considering the forming accuracy in the above forging process and the grinding allowance in the width grinding (D- 1 ) of the shaft material 110 described later.
  • the height (not shown) from the bottom faces of the hydrodynamic grooves 113 a 1 , 113 b 1 in the radial hydrodynamic groove regions 113 a , 113 b to the outer circumferential surfaces of the demarcation portions 113 a 2 , 113 b 2 , and the height (not shown) from the bottom faces of the hydrodynamic groove 112 a 1 in the thrust hydrodynamic groove region 112 a on the shaft portion 111 side to the axial end faces of the demarcation portion 112 a 2 are set to suitable values considering the forming accuracy in the above forging process, and the full-face grinding (D- 2 ) of the shaft material 110 described later and the grinding allowance in the finish grinding (D- 3 ).
  • a grinding apparatus used in this grinding step comprises, as shown in FIGS.
  • a carrier 41 retaining a plurality of the shaft materials 110 as workpieces; and a pair of grind stones 42 , 42 which grind the end face opposite to the shaft portion side comprising the end face 111 b of the shaft portion of the shaft material 110 retained by the carrier 41 and the thrust hydrodynamic groove region 112 b of the flange portion 112 , as in the first embodiment.
  • the grinding apparatus 40 based on the first embodiment, and their explanations are thus omitted.
  • the shaft material 110 is sequentially loaded into the notch 43 from a fixed position.
  • the loaded shaft material 110 traverses the end faces of the rotating grind stones 42 , 42 from their outer diameter edge toward the inside diameter edge, while being prevented from falling off from the notch 43 by binding of the belt 44 .
  • both end faces of the shaft material 110 namely the end face 111 b of the shaft portion and the end face of the flange portion 112 on the side opposite to the shaft portion comprising the thrust hydrodynamic groove region 112 b are ground by the end faces of the grind stones 42 , 42 (refer to FIG. 9 ).
  • the width of the shaft material 110 in the axial direction (the entire length including the flange portion 112 ) is finished to have a predetermined size.
  • the thrust hydrodynamic groove region 112 b of the flange portion 112 is ground, for example, in such a manner that the demarcation portion 112 b 2 is ground by a predetermined grinding allowance (h 1 -h 2 in FIG. 21 ) from the height h 1 at the time of forging, as shown in FIG. 21 .
  • This renders the height of the demarcation portion 112 b 2 (the depth of the hydrodynamic groove 112 b 1 ) to be the same as the predetermined value h 2 (for example, 3 ⁇ m-15 ⁇ m). Therefore, the thrust bearing gap between the component facing it (in this embodiment, the bottom 7 b of the housing 7 ) and itself can be controlled highly accurately at the interval of a several micrometers to several ten micrometers.
  • the outer circumferential surface 110 a of the shaft material 110 and the end face of the flange portion 112 on the shaft portion side comprising the thrust hydrodynamic groove region 112 a are ground.
  • a grinding apparatus used in this grinding step conduct plunge-grinding by the grind stone 53 , with the back plate 54 and pressure plate 55 pressed against both end faces of the shaft material 110 , as in the first embodiment shown in FIG. 10 .
  • the corrected face 13 of the shaft material 110 is rotatably supported by a shoe 52 . Note that other constitutions of the grinding apparatus 50 than this is based on the first embodiment and their explanations are thus omitted.
  • the grind stone 53 is fed obliquely (the direction of arrow 1 in FIG. 10 ), the plane grinding portion 56 b of the grind stone 53 is pressed against the end face of the flange portion 112 on the shaft portion side of the shaft material 110 , the end face of the flange portion 112 on the shaft portion side (on the thrust hydrodynamic groove region 112 a side) comprising the thrust hydrodynamic groove region 112 a is ground.
  • the end face of the flange portion 122 of the shaft member 102 on the shaft portion side is formed, and grinding of the thrust hydrodynamic groove region 112 a is completed, and the thrust hydrodynamic groove region 122 a of the shaft member 102 is formed.
  • the grind stone 53 is fed in the direction perpendicularly intersecting the rotation axis of the shaft material 110 (the direction of arrow 2 in FIG. 10 ), the cylinder grinding portion 56 a of the grind stone 53 is pressed against the outer circumferential surface 111 a of the shaft portion 111 of the shaft material 110 and the outer circumferential surface 112 c of the flange portion 112 to grind the faces 111 a, 112 c .
  • the radial hydrodynamic groove region 123 a , 123 b and the region corresponding to the cylinder face 125 are ground, while the tapered face 124 , the outer circumferential surface 122 c of the flange portion 122 , and the recess portions 126 - 128 are further formed.
  • the demarcation portion 112 a 2 of the thrust hydrodynamic groove region 112 a formed on the end face of the flange portion 112 on the shaft portion side is ground, for example, by a predetermined grinding allowance from the height at the time of forging, similarly to the case of the thrust hydrodynamic groove region 112 b , although not shown in the Figs.
  • This renders the height of the demarcation portion 112 a 2 (the depth of the hydrodynamic groove 112 a 1 ) to have a predetermined value, whereby the thrust bearing gap between the component facing it (the lower end face 8 b of the bearing sleeve 8 in this embodiment) and itself is highly accurately controlled.
  • a grinding apparatus used in this grinding is a cylinder grinder shown in FIG. 11 . It performs plunge grinding by the grind stone 63 while rotating the shaft material 110 held between the back plate 64 and the pressure plate 65 . Note that other constitutions of the grinding apparatus 60 are based on the first embodiment, and their explanations are thus omitted.
  • the rotating grind stone 63 is provided with the feed in the radial direction so that the radial hydrodynamic groove regions 123 a , 123 b and the regions 113 a , 113 b and 115 corresponding to the cylinder face 125 are ground, and these regions are finished to have the final surface accuracy.
  • the demarcation portions 113 a 2 , 113 b 2 of the radial hydrodynamic groove regions 113 a , 113 b is ground, for example, by a predetermined grinding allowance from the height at the time of rolling, although not shown in the Figs.
  • the shaft member 102 shown in FIG. 13 is completed by performing, if necessary, heat treatment and cleaning process.
  • the shaft member 102 produced by the above production method has the radial hydrodynamic groove regions 123 a , 123 b formed at two separate upper and lower portions on the outer periphery of the shaft portion 121 by a rolling process, and has such a structure that the outer circumferential surfaces of the demarcation portions 123 a 2 , 123 b 2 of the radial hydrodynamic groove regions 123 a , 123 b are the grinding surfaces. It also has the thrust hydrodynamic groove regions 122 a , 122 b formed by a forging process on both end faces of the flange portion 122 , and has such a structure that the axial end faces of the thrust hydrodynamic groove regions 122 a , 122 b are the grinding surfaces.
  • the grinding surfaces of the demarcation portions 123 a 2 , 123 b 2 in the radial hydrodynamic groove regions 123 a , 123 b are formed in the (D- 2 ) full-face grinding process and (D- 3 ) finish grinding process. Moreover, the grinding surface of the demarcation portion 122 a 2 in the thrust hydrodynamic groove region 122 a is formed in the (D- 2 ) full-face grinding process, and the grinding surface is formed in the (D- 1 ) width grinding process of the demarcation portion 122 b 2 in the thrust hydrodynamic groove region 122 b.
  • the radial hydrodynamic groove regions 113 a , 113 b of the shaft material 110 are formed by a rolling process, and among the radial hydrodynamic groove regions 113 a , 113 b , the outer diameter portions of the demarcation portions 113 a 2 , 113 b 2 are ground, whereby the hydrodynamic grooves region 123 a , 123 b can be formed at reduced costs, while the dimensional accuracy of their outer diameters and surface roughness can be highly accurately finished.
  • the thrust hydrodynamic groove regions 122 a , 122 b low-cost forming and high-accuracy finish can be achieved at the same time for the same reason. This allows the radial bearing gap and thrust bearing gap in the hydrodynamic bearing apparatus 101 to be controlled highly accurately, enabling to produce stable bearing performance.
  • the cylindricity of the shaft portion 121 is corrected so that in particular the forming accuracy of the demarcation portions 123 a 2 , 123 b 2 in the radial hydrodynamic groove region 123 a , 123 b can be improved and the grinding allowance in grinding can be reduced. This enables to further shorten machining time and reduce processing costs.
  • the forming accuracy of the hydrodynamic groove region in forging or rolling is preliminarily increased, whereby the grinding allowance in grinding can be reduced.
  • hydrodynamic grooves need not be processed on the inner periphery of the bearing sleeve 8 .
  • the inner periphery of the bearing sleeve 8 can serve as the cylinder face 8 a , reducing such related costs.
  • hydrodynamic grooves need not be processed on the inner periphery of the bearing sleeve 8 , it is unnecessary to form the bearing sleeve 8 and the housing 7 as separate components. Therefore, these components can be unified (with a resin or the like), although not shown in the Figs. This can reduce the number of parts and related production costs.
  • the forging of the shaft material 110 and the thrust hydrodynamic groove regions 112 a , 112 b can be conducted simultaneously with the forming of the radial hydrodynamic groove regions 113 a , 113 b by forging.
  • the shape of the hydrodynamic grooves by forging is not particularly limited, and may be, for example, a herringbone shape, a spiral shape, or other various hydrodynamic groove shapes.
  • the thrust hydrodynamic groove regions 122 a , 122 b are formed on both end faces of the flange portion 122 .
  • the thrust hydrodynamic groove regions may be formed on the side of the lower end face 8 b of the bearing sleeve 8 and the upper end face 7 b 1 of the bottom 7 b facing the two end faces of the flange portion 122 , respectively.
  • bearings using hydrodynamic pressure producing parts comprising hydrodynamic grooves arranged in a herringbone shape and a spiral shape are shown as examples of the hydrodynamic bearing which constitutes the radial bearing portions R 1 , R 2 , R 11 , R 12 and the thrust bearing portions T 1 , T 2 , T 11 , T 12 .
  • the constitution of the hydrodynamic pressure producing parts is not limited to these.
  • the radial bearing portions R 1 , R 2 , R 11 , R 12 for example, multirobe bearing, step bearing, taper bearing, taper flat bearing or the like may be used.
  • the thrust bearing portions T 1 , T 2 , T 11 , T 12 step pocket bearing, taper pocket bearing, taper flat bearing and the like may be used.
  • a lubricating oil is mentioned as an example of a fluid which fills the inside of the hydrodynamic bearing apparatus 1 , 101 and produces hydrodynamic effect in the radial bearing gap between the bearing sleeve 8 and the shaft member 2 , 102 and the thrust bearing gap between the bearing sleeve 8 and housing 7 and the shaft member 2 , 102 .
  • a fluid which can produce hydrodynamic effect in the bearing gaps having hydrodynamic groove regions for example, a gas such as air and a lubricant having fluidity such as a magnetic fluid may be used.
  • the hydrodynamic bearing apparatus according to the present invention is suitable for spindle motors of information appliances, for example, magnetic disk apparatuses such as HDD, optical disk apparatuses such as CD-ROM, CD-R/RW, DVD-ROM/RAM, magneto-optic disk apparatuses such as MD and MO, etc., polygon scanner motors of laser beam printers (LBP), and other small motors.
  • magnetic disk apparatuses such as HDD
  • optical disk apparatuses such as CD-ROM, CD-R/RW, DVD-ROM/RAM
  • magneto-optic disk apparatuses such as MD and MO, etc.
  • LBP polygon scanner motors of laser beam printers

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Ocean & Marine Engineering (AREA)
  • Power Engineering (AREA)
  • Sliding-Contact Bearings (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
US11/629,910 2004-09-08 2005-08-31 Shaft Member For Hydrodynamic Bearing Apparatuses And A Method For Producing The Same Abandoned US20070278881A1 (en)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
JP2004-261446 2004-09-08
JP2004261446A JP4610973B2 (ja) 2004-09-08 2004-09-08 動圧軸受装置用軸部材の製造方法
JP2004-261452 2004-09-08
JP2004261452A JP4786157B2 (ja) 2004-09-08 2004-09-08 動圧軸受装置用軸部材およびその製造方法
PCT/JP2005/015952 WO2006027986A1 (ja) 2004-09-08 2005-08-31 動圧軸受装置用軸部材およびその製造方法

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US13/149,313 Division US9003664B2 (en) 2004-09-08 2011-05-31 Method for producing shaft member for hydrodynamic bearing apparatus

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US11/629,910 Abandoned US20070278881A1 (en) 2004-09-08 2005-08-31 Shaft Member For Hydrodynamic Bearing Apparatuses And A Method For Producing The Same
US13/149,313 Active 2025-11-29 US9003664B2 (en) 2004-09-08 2011-05-31 Method for producing shaft member for hydrodynamic bearing apparatus

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US (2) US20070278881A1 (ko)
KR (1) KR101164462B1 (ko)
WO (1) WO2006027986A1 (ko)

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US20100226601A1 (en) * 2006-09-12 2010-09-09 Ntn Corporation Fluid dynamic bearing device
US20110064342A1 (en) * 2002-03-13 2011-03-17 Seagate Technology Llc Single thrust bearing fluid dynamic bearing motor
US20120120525A1 (en) * 2010-11-15 2012-05-17 Samsung Electro-Mechanics, Co., Ltd. Motor and recording disk drive device
DE102011102113A1 (de) * 2011-05-20 2012-11-22 Schaudt Mikrosa Gmbh Mehrscheiben-Schleifmaschine mit zumindest zwei Spindelsätzen
FR2997741A1 (fr) * 2012-11-05 2014-05-09 Ningbo Zhenming Shaft Co Ltd Procede de fabrication d'un arbre d'entrainement de moteur antideflagrant
US8926183B2 (en) 2011-03-09 2015-01-06 Ntn Corporation Fluid dynamic bearing device

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JP6757219B2 (ja) * 2016-09-27 2020-09-16 Ntn株式会社 流体軸受装置用軸部材及びその製造方法、並びに流体軸受装置
CN108466114A (zh) * 2018-03-26 2018-08-31 宁波得晴电器科技有限公司 五金件打磨装置
CN111898242B (zh) * 2020-06-22 2023-12-15 东南大学 端面磨削电主轴柔性转子动力学建模与动态设计方法

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US6659647B2 (en) * 2001-03-08 2003-12-09 Ngk Spark Plug Co., Ltd. Ceramic dynamic pressure bearing, motor with bearing, hard disk device, and polygon scanner
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US20110064342A1 (en) * 2002-03-13 2011-03-17 Seagate Technology Llc Single thrust bearing fluid dynamic bearing motor
US8732954B2 (en) * 2002-03-13 2014-05-27 Seagate Technology Llc Single thrust bearing fluid dynamic bearing motor
US20100226601A1 (en) * 2006-09-12 2010-09-09 Ntn Corporation Fluid dynamic bearing device
US20120120525A1 (en) * 2010-11-15 2012-05-17 Samsung Electro-Mechanics, Co., Ltd. Motor and recording disk drive device
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US8926183B2 (en) 2011-03-09 2015-01-06 Ntn Corporation Fluid dynamic bearing device
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FR2997741A1 (fr) * 2012-11-05 2014-05-09 Ningbo Zhenming Shaft Co Ltd Procede de fabrication d'un arbre d'entrainement de moteur antideflagrant

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WO2006027986A1 (ja) 2006-03-16
KR101164462B1 (ko) 2012-07-18
KR20070062494A (ko) 2007-06-15
US9003664B2 (en) 2015-04-14
US20110232093A1 (en) 2011-09-29

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