US20050278938A1 - Method of bonding metallic members by plastic-flow bonding and plastic-flow bonded body - Google Patents
Method of bonding metallic members by plastic-flow bonding and plastic-flow bonded body Download PDFInfo
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- US20050278938A1 US20050278938A1 US11/211,502 US21150205A US2005278938A1 US 20050278938 A1 US20050278938 A1 US 20050278938A1 US 21150205 A US21150205 A US 21150205A US 2005278938 A1 US2005278938 A1 US 2005278938A1
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- bonding
- bonded
- plastic
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21K—MAKING FORGED OR PRESSED METAL PRODUCTS, e.g. HORSE-SHOES, RIVETS, BOLTS OR WHEELS
- B21K25/00—Uniting components to form integral members, e.g. turbine wheels and shafts, caulks with inserts, with or without shaping of the components
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
- B23P—METAL-WORKING NOT OTHERWISE PROVIDED FOR; COMBINED OPERATIONS; UNIVERSAL MACHINE TOOLS
- B23P11/00—Connecting or disconnecting metal parts or objects by metal-working techniques not otherwise provided for
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
- F16D1/06—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end
- F16D1/064—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end non-disconnectable
- F16D1/072—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end non-disconnectable involving plastic deformation
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- G—PHYSICS
- G11—INFORMATION STORAGE
- G11B—INFORMATION STORAGE BASED ON RELATIVE MOVEMENT BETWEEN RECORD CARRIER AND TRANSDUCER
- G11B19/00—Driving, starting, stopping record carriers not specifically of filamentary or web form, or of supports therefor; Control thereof; Control of operating function ; Driving both disc and head
- G11B19/20—Driving; Starting; Stopping; Control thereof
- G11B19/2009—Turntables, hubs and motors for disk drives; Mounting of motors in the drive
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- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K15/00—Methods or apparatus specially adapted for manufacturing, assembling, maintaining or repairing of dynamo-electric machines
- H02K15/02—Methods or apparatus specially adapted for manufacturing, assembling, maintaining or repairing of dynamo-electric machines of stator or rotor bodies
- H02K15/03—Methods or apparatus specially adapted for manufacturing, assembling, maintaining or repairing of dynamo-electric machines of stator or rotor bodies having permanent magnets
-
- 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
- H02K7/003—Couplings; Details of shafts
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T29/00—Metal working
- Y10T29/49—Method of mechanical manufacture
- Y10T29/49002—Electrical device making
- Y10T29/49009—Dynamoelectric machine
- Y10T29/49012—Rotor
-
- 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
- Y10T29/49826—Assembling or joining
- Y10T29/49908—Joining by deforming
- Y10T29/49938—Radially expanding part in cavity, aperture, or hollow body
-
- 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
- Y10T403/00—Joints and connections
- Y10T403/49—Member deformed in situ
Definitions
- the present invention relates to a method of bonding metallic members by plastic-flow bonding, and a bonded body obtained by the method.
- Conventional methods for fitting metallic members to each other and subjecting them by plastic-flow bonding include a method for subjecting two members to plastic-flow bonding in a gap-fitting state (for example, refer to Japanese Patent Laid-open No. 11-120743, page 4 and FIGS. 3 and 4).
- another method for fitting two metallic members to each other includes a method of subjecting them to plastic-flow bonding in a press-fitting state (for example, refer to Japanese Patent Laid-open No. 2001-54268, page 2 and FIG. 1).
- An object of the present invention is to provide, at a low cost, a method for plastic-flow bonding with high bonding strength and high accuracy, which eliminates any occurrence of contamination.
- the present invention provides a method of bonding metallic members by a plastic flow bonding to produce a bonded body with an increased bonding strength and free from contamination.
- the present invention further provides a plastic flow bonded metallic body with a high bonding strength and free of contamination.
- the bonded body can be applied especially to an apparatus for rotating a rotating disc and a rotating shaft, the members being bonded to each other.
- the present invention provides a bonding method for bonding metallic members, which comprises the steps of: fitting a metallic members to another metallic member, followed by effecting preliminarily plastic bonding by means of a preliminarily bonding punch; and generating compression force in an axial direction of the members in the vicinity of the fitting portion of the bonding members after the preliminarily plastic bonding, and allowing part of the material of the bonding members to effect plastic-flow in such a manner as to fill a gap defined between the metallic members, so as to plastically bond the members; whereby the members are tightly integrated with each other.
- FIG. 1 is a general plane view of a hard disk drive to which the present invention is applied.
- FIG. 2 is a vertical cross-sectional view of the hard disk drive shown in FIG. 1 .
- FIG. 3 is an enlarged cross-sectional view of a dynamic pressure bearing spindle motor, using a bonded body of a hub and a shaft, in the hard disk drive shown in FIG. 2 .
- FIG. 4 is a vertical cross-sectional view of the bonded body of the hub and the shaft.
- FIG. 5 is a side view of the shaft.
- FIG. 6 is a vertical cross-sectional view of the hub.
- FIG. 7 is a vertical cross-sectional view of a molding die used in a process of preliminarily plastic bonding.
- FIG. 8 is an enlarged vertical cross-sectional view of a bonded portion of the shaft and the hub after completion of the preliminarily plastic bonding.
- FIG. 9 is a vertical cross-sectional view of a molding die used in a process of plastic-flow bonding.
- FIG. 10 is an enlarged vertical cross-sectional view of the bonded portion of the shaft and the hub after the completion of the plastic-flow bonding.
- FIG. 11 is an enlarged vertical cross-sectional view of a groove of the shaft.
- FIG. 12 is an enlarged vertical cross-sectional view of a round groove of the shaft.
- FIG. 13 is an enlarged view showing a groove having a knurl at the shaft.
- FIG. 14 is an enlarged vertical cross-sectional view of the bonded portion of the shaft and the hub, representing a stress after the completion of the preliminarily plastic bonding.
- FIG. 15 is an enlarged vertical cross-sectional view of the bonded portion of the shaft and the hub, representing a stress after the completion of the plastic bonding.
- the present invention is applied to a bonding method for bonding a bonding member to a member to be bonded, which are used for a device for rotating the bonding member serving as a rotary disk and the member to be bonded serving as a rotary shaft integrally connected to each other.
- the method comprises the steps of:
- the present invention is also applied to a bonded body comprising a bonding member and a member to be bonded, which are used in a device for rotating the bonding member on which rotary disks are stacked and the member to be bonding serving as a rotary shaft in integral bonding:
- portion, in the vicinity of the fitting portion of the member to be bonded, of the bonding member is pressurized at a load in excess of an elastic limit of the material of the bonding member;
- a compression force in an axial direction of the to-be-bonded member is generated at the portion in the vicinity of the fitting portion of the bonding member, and then, part of the material of the fitting portion in excess of the elastic limit is allowed to plastic-flow in such a manner as to fill a clearance defined between the member to be bonded and the bonding member;
- the present invention is further applied to a mechanical apparatus provided with a bonded body comprising a bonding member and a member to be bonded, which are used in a device for rotating the bonding member on which rotary disks are stacked and the to-be-bonded member serving as a rotary shaft in integral bonding:
- the technical fields to which the present invention is applied are a bonding method for subjecting, to plastic-flow bonding, metallic members such as a shaft and a hub in a spindle motor for use in a disk device, a DVD or a CD-ROM in a computer or the like, in particular, in a spindle motor having a dynamic pressure bearing structure, which is a thin-type hard disk drive motor to be loaded in a portable personal computer such as a notebook personal computer.
- a bonded body with reference to FIGS. 1 to 15 .
- FIGS. 1 to 15 For the convenience, there are set forth meanings of all reference numerals in the following table.
- the bonding method for subjecting the two members to the plastic-flow bonding and the bonded body according to the present invention are exemplified here in a dynamic pressure bearing spindle motor in a hard disk drive by the use of a bonded body including a hub and a shaft in a preferred embodiment.
- FIG. 1 is a general plane view of a hard disk drive
- FIG. 2 is a cross-sectional view of the hard disk drive shown in FIG. 1 .
- reference numeral 200 designates a hard disk of a hard disc drive (abbreviated as “an HDD”), in which a dynamic pressure bearing spindle motor 100 is disposed.
- a read-out device 300 reads out data from a hard disk rotationally driven by the dynamic pressure bearing spindle motor 100 .
- FIG. 3 shows a dynamic pressure-bearing spindle motor in the hard disk drive, in which a bonded body of a hub and a shaft is used, in a preferred embodiment according to the present invention.
- a shaft 1 is integrated with a hub 2 by a bonding method according to the present invention.
- a magnet 13 To the hub 2 is securely fixed a magnet 13 .
- a plurality of disks 3 serving as storage mediums are stacked on a flange 24 of the hub with disk spacers 4 held therebetween and are secured by a clamp 5 that is tightened to a female screw 32 of the shaft 1 with a screw 6 .
- the shaft 1 is rotatably fitted into the bore of a dynamic pressure bearing metal 8 secured to a housing 7 .
- a radial dynamic pressure bearing is constituted by the effect of a dynamic pressure generated by a magnetic fluid filled inside the housing according to rotation.
- the housing 7 is fixedly secured to a base 11 .
- a thrust receiving plate 10 is joined to the housing 7 while a stopper ring 12 is held between the dynamic pressure bearing metal 8 and the thrust receiving plate 10 , and thus, constitutes a thrust bearing in which a spherical edge portion 40 of the shaft 1 is supported at a thrust receiving face 41 .
- the shaft 1 is suppressed by the stopper ring 12 fitted into a stopper groove 42 from floating in a thrust direction.
- a wound stator core 14 is securely bonded to the base 11 with an adhesive, and therefore, the magnet 13 receives rotating force at the time of energization, thereby rotating the hub 2 .
- the hub 2 as a bonding member should be made of a material which is liable to plastically deform and has deformation resistance is smaller than that of the shaft 1 serving as a member to be bonded.
- the hub 2 is made of ferrite stainless steel, for example, SUS430 in consideration of corrosion resistance and magnetic characteristics in terms of a motor.
- the shaft 1 is formed into a columnar shape, and is made of martensitic stainless steel excellent in abrasion resistance or corrosion resistance such as SUS440 or SUS420 J2 in consideration of bearing performance, followed by hardening.
- an annular groove 31 At an outer diameter portion to be bonded in the vicinity of one end of the shaft 1 is formed an annular groove 31 . The details of the shape of the groove will be described later.
- FIG. 4 shows a bonded body of the hub and the shaft in a preferred embodiment according to the present invention.
- the shaft 1 is provided with the annular groove 31 formed in the outer diameter portion to be bonded in the vicinity of one end of the shaft 1 and is plastically bonded to a bonding hole 21 formed in the hub 2 having a diameter greater than the outer diameter of the shaft 1 by a method, described below, as shown in FIG. 6 .
- the shaft 1 and the hub 2 are bonded to each other through a first process in which the shaft 1 shown in FIG. 5 is freely fitted or gap-fitted to the hub 2 shown in FIG. 6 , followed by preliminarily plastic bonding, and a second process of plastic-flow bonding.
- a bottom face 23 of the hub 2 is held by a stand 63 , as shown in FIG. 7 .
- the hub 2 is held at an outer diameter 25 thereof by an inner diameter 62 of a guide ring 61 .
- an edge portion 34 on a side on which the annular groove 31 is formed at the outer diameter portion to be bonded of the shaft 1 is inserted into and fitted to the bonding hole 21 of the hub 2 .
- a clearance or gap at the fitting portion between the shaft 1 and the hub 2 when the edge portion 34 of the shaft 1 is inserted into the bonding hole 21 of the hub 2 that is, a clearance between the wall surface of the bonding hole 21 of the hub 2 and the outer peripheral surface of the shaft 1 should be set as small as 0 to 0.02 mm.
- the outer diameter of the shaft 1 is set to 3.00 mm while the inner diameter of the bonding hole 21 of the hub 2 is set to 3.01 mm.
- a preliminarily bonding punch 60 is fitted to the inner circumference 65 of the guide ring 61 and the shaft 1 is fitted into a guide hole 64 formed at substantially the center of the preliminarily bonding punch 60 , thereby holding the shaft 1 .
- the shaft 1 is held in the guide hole 64 of the preliminarily bonding punch 60 guided on the inner circumference 65 of the guide ring 61 , and then, the preliminarily bonding punch 60 is driven by a press ram, not shown into the bonding member.
- a ring-like projection 66 having a projection width K is formed at the tip of the preliminarily bonding punch 60 by which an edge portion 22 of the hub 2 is pressed down in the vicinity of the bonding hole 21 .
- the pressing force of the preliminarily bonding punch 60 is a load that generates stress large enough to plastic-deform the material forming the hub 2 , and force that plastically deforms a portion corresponding to such a depth as to fill the fitting clearance between the shaft 1 and the hub 2 vertically.
- the preliminarily bonding punch 60 is pressed down at the above-described load, and then, the material in the vicinity of the bonding hole 21 of the hub 2 is allowed to plastic-flow, followed by the preliminary bonding.
- the bonding portion after the preliminarily plastic bonding in the above-described manner is shown in FIG. 8 , which is an enlarged vertical cross-sectional view.
- a ring-like bonding projection 76 presses a portion of the bottom portion 72 of a preliminarily bonding mark 71 in the vicinity of the bonding hole 21 .
- the ring-like bonding projection 76 is disposed at the tip of the punch 70 and has a projection width W smaller than the projection width K of the preliminarily bonding projection 66 of the preliminarily bonding punch 60 .
- the pressing force of the punch 70 is a load large enough to generate a stress for effecting a plastic deformation of the material forming the hub 2 .
- the punch 70 is pressed down at the above-described load, and then, the material in the vicinity of the bonding hole 21 of the hub 2 is allowed to effect plastic-flow over the entire circumference of the groove 31 , followed by the bonding.
- the bonded portion after the plastic-flow bonding in the above-described manner is shown in FIG. 10 , which is an enlarged vertical cross-sectional view of the bonding.
- the projecting width W and pressing depth H due to the bonding projection 76 of the punch 70 are too great, the load for the plastic deformation becomes large, and therefore, the material more than that flowing in the groove is liable to be fluidized, thereby degrading the bonding accuracy.
- the projecting width W and the pressing depth H are set according to the shape of the groove.
- FIG. 11 shows one example of the portion of the groove 31 of the shaft 1 .
- Factors determining the cross-sectional shape of the groove 31 of the shaft 1 include the groove depth H, a groove width B, a groove angle ⁇ , the number n of grooves and the like.
- the depth H of the groove 31 of the shaft 1 is too small, a sufficient shearing strength cannot be achieved due to easy plastic deformation when external force is exerted in an axial direction.
- the depth H of the groove 31 of the shaft 1 is too large, the material insufficiently flows into the groove, thereby forming a gap, so as to degrade the strength.
- the screw hole 67 for screwing the clamp 5 is formed at the lower portion of the shaft 1 , and further, the female screw 32 is disposed at the inner wall surface of the screw hole 67 of the shaft 1 . Consequently, the thickness at a portion near the bonded portion of the hub 2 to the lower portion of the shaft 1 becomes small.
- the groove depth H of the groove 31 of the shaft 1 shown in FIG. 11 should desirably range from about 0.07 to about 0.13 mm.
- the width B of the groove 31 of the shaft 1 can be varied according to the shearing strength required at the bonded portion. However, if the width is set too largely, a distance from the tip of the punch 70 to the lower portion of the groove 31 of the shaft 1 becomes great in bonding to the hub 2 , thereby increasing a fluid frictional loss of the material in the vicinity of the bonding hole 21 of the hub 2 , which should flow into the groove 31 of the shaft 1 . Therefore, even if the large load is applied to the hub 2 by the punch 70 , the internal stress of the material in the vicinity of the bonding hole 21 of the hub 2 near the lower portion of the shaft 1 cannot be increased enough to achieve the plastic deformation.
- the material in the vicinity of the bonding hole 21 of the hub 2 near the lower portion of the shaft 1 is reduced in quantity of the plastic deformation, so that the material in the vicinity of the bonding hole 21 of the hub 2 insufficiently flows into the groove 31 of the shaft 1 .
- the depth H of the groove 31 of the shaft 1 shown in FIG. 11 should desirably range from about 0.07 to about 0.13 mm.
- the groove angle ⁇ representing an opening degree (i.e., an angle) of the groove 31 of the shaft 1
- the opening angle ⁇ of the groove 31 of the shaft 1 is small, the material in the vicinity of the bonding hole 21 of the hub 2 is less prone to flow into the groove 31 of the shaft 1 when the large load is applied to the hub 2 by the punch 70 .
- the opening angle ⁇ of the groove 31 of the shaft 1 is great, the material in the vicinity of the bonding hole 21 of the hub 2 shallowly bites when the large load is applied to the hub 2 by the punch 70 , so that drawing strength becomes small. In this manner, if the groove angle ⁇ of the groove 31 of the shaft 1 shown in FIG.
- the groove angle ⁇ of the groove 31 of the shaft 1 should desirably range from about 60° to about 120°.
- the contact area between the shaft 1 and the hub 2 becomes larger, thereby increasing the drawing strength.
- the number n of grooves 31 of the shaft 1 is great, the material in the vicinity of the bonding hole 21 of the hub 2 is less prone to flow into the groove 31 of the shaft 1 when the large load is applied to the hub 2 by the punch 70 .
- the number n of grooves 31 of the shaft 1 is too great, the drawing strength is much degraded.
- the drawing strength is highest.
- the cross-sectional shape of the groove 31 of the shaft 1 need not be a triangle as shown in FIG. 11 . It may be a round shape, as shown in FIG. 12 .
- a knurl 36 may be formed at a thread between the grooves 31 of the shaft 1 , as shown in FIG. 13 .
- the groove 31 of the shaft 1 is formed over the entire circumference of the shaft 1 , the material in the vicinity of the bonding hole 21 of the hub 2 plastically flows over the entire circumference in a uniform manner when the large load is applied to the hub 2 by the punch 70 , and further, strain also uniformly is exerted over the entire circumference, so that both of accuracy of a right angle and strength can be enhanced.
- the groove 31 of the shaft 1 can be molded by lathing, thus achieving high productivity.
- the position of the groove 31 of the shaft 1 should be set near a pressing surface 24 of the hub 2 as possible. If the position of the groove 31 of the shaft 1 is positioned apart from the pressing surface 24 of the hub 2 , a fluid frictional resistance becomes high, and therefore, the material in the vicinity of the bonding hole 21 of the hub 2 is prone to flow into the groove 31 of the shaft 1 .
- the outer circumferential portion of the shaft 1 having the annular groove 31 formed at the outer periphery of the shaft 1 is freely fitted into the bonding hole 21 of the hub 2 ; the large load is applied to the hub 2 by the punch 70 ; the vicinity of the hole formed at the end surface of the hub 2 is plastically deformed over the entire circumference; the shaft 1 and the bonding hole 21 of the hub 2 are subjected to the preliminarily plastic bonding in such a manner as to fill the gap; the material in the vicinity of the bonding hole 21 at the end surface is plastically deformed over the entire circumference after the preliminarily plastic bonding of the hub 2 in the state in which a stress a is exerted on the bonding hole 21 of the hub 2 ; a compression stress is exerted on the shaft 1 in such a manner as to fill the groove 31 of the shaft 1 ; and then, the material in the vicinity of the bonding hole 21 of the hub 2 is allowed to
- the shearing force and strain P of the material in the vicinity of the bonding hole 21 of the hub 2 and the stress ⁇ caused by the preliminarily plastic bonding are exerted on a portion remote from the pressing portion, on which the strain is hardly exerted, as shown in FIG. 15 .
- the connection strength between the hub 2 and the shaft 1 is high.
- the present invention is not limited to the above-described preferred embodiment, but it can be applied to bonding between other members of various kinds of metals, for example, a shaft, a cylinder or the like and a flat plate.
- the fitting accuracy before the bonding may be rough in comparison with the press-fitting, the high productivity can be achieved in inexpensive equipment, and further, the fabricating cost can be reduced.
Abstract
The disclosure is concerned with a bonding method for bonding metallic members, which comprises the steps of: fitting a metallic members to another metallic member, followed by effecting preliminarily plastic bonding by means of a preliminarily bonding punch; and generating compression force in an axial direction of the members in the vicinity of the fitting portion of the bonding members after the preliminarily plastic bonding, and allowing part of the material of the bonding member to effect plastic-flow in such a manner as to fill a gap defined between the metallic members, so as to plastically bond the members; whereby the members are tightly integrated with each other.
Description
- This application is a divisional application of Ser. No. 10/677,291 filed Oct. 3, 2003.
- 1. Technical Field to Which the Invention Pertains
- The present invention relates to a method of bonding metallic members by plastic-flow bonding, and a bonded body obtained by the method.
- 2. Related Art
- Conventional methods for fitting metallic members to each other and subjecting them by plastic-flow bonding include a method for subjecting two members to plastic-flow bonding in a gap-fitting state (for example, refer to Japanese Patent Laid-open No. 11-120743, page 4 and FIGS. 3 and 4).
- Furthermore, another method for fitting two metallic members to each other includes a method of subjecting them to plastic-flow bonding in a press-fitting state (for example, refer to Japanese Patent Laid-open No. 2001-54268,
page 2 and FIG. 1). - In a bonding method disclosed in Patent Laid-open No.11-120743, since plastic-flow bonding is performed after metallic members are free-fitted with a gap to each other, a portion other than the vicinity of a portion which is pressed to effect plastic-flow forms a gap, as a matter of fact, which leads to relatively weak bonding strength, especially, bending strength. In particular, a problem will arise in the case where thin metal plate members are pressed to effect plastic-flow for bonding.
- In a bonding method disclosed in Japanese Patent Laid-open No. 2001-54268, since plastic-flow bonding is performed after two members are press-fitted to each other, there is no gap at a portion other than the vicinity of a portion which is pressed to effect plastic-flow, and therefore, high bonding strength, in particular, high bending strength can be achieved. However, a scrape or a gall tends to occur in the two members at the time of the press-fitting, thereby bringing about occurrence of bending due to the press-fitting or contamination. Moreover, high precision in shape of the bonding members is needed to manage a press-fitting margin, thereby increasing a cost.
- An object of the present invention is to provide, at a low cost, a method for plastic-flow bonding with high bonding strength and high accuracy, which eliminates any occurrence of contamination.
- The present invention provides a method of bonding metallic members by a plastic flow bonding to produce a bonded body with an increased bonding strength and free from contamination.
- The present invention further provides a plastic flow bonded metallic body with a high bonding strength and free of contamination. The bonded body can be applied especially to an apparatus for rotating a rotating disc and a rotating shaft, the members being bonded to each other.
- The present invention provides a bonding method for bonding metallic members, which comprises the steps of: fitting a metallic members to another metallic member, followed by effecting preliminarily plastic bonding by means of a preliminarily bonding punch; and generating compression force in an axial direction of the members in the vicinity of the fitting portion of the bonding members after the preliminarily plastic bonding, and allowing part of the material of the bonding members to effect plastic-flow in such a manner as to fill a gap defined between the metallic members, so as to plastically bond the members; whereby the members are tightly integrated with each other.
-
FIG. 1 is a general plane view of a hard disk drive to which the present invention is applied. -
FIG. 2 is a vertical cross-sectional view of the hard disk drive shown inFIG. 1 . -
FIG. 3 is an enlarged cross-sectional view of a dynamic pressure bearing spindle motor, using a bonded body of a hub and a shaft, in the hard disk drive shown inFIG. 2 . -
FIG. 4 is a vertical cross-sectional view of the bonded body of the hub and the shaft. -
FIG. 5 is a side view of the shaft. -
FIG. 6 is a vertical cross-sectional view of the hub. -
FIG. 7 is a vertical cross-sectional view of a molding die used in a process of preliminarily plastic bonding. -
FIG. 8 is an enlarged vertical cross-sectional view of a bonded portion of the shaft and the hub after completion of the preliminarily plastic bonding. -
FIG. 9 is a vertical cross-sectional view of a molding die used in a process of plastic-flow bonding. -
FIG. 10 is an enlarged vertical cross-sectional view of the bonded portion of the shaft and the hub after the completion of the plastic-flow bonding. -
FIG. 11 is an enlarged vertical cross-sectional view of a groove of the shaft. -
FIG. 12 is an enlarged vertical cross-sectional view of a round groove of the shaft. -
FIG. 13 is an enlarged view showing a groove having a knurl at the shaft. -
FIG. 14 is an enlarged vertical cross-sectional view of the bonded portion of the shaft and the hub, representing a stress after the completion of the preliminarily plastic bonding. -
FIG. 15 is an enlarged vertical cross-sectional view of the bonded portion of the shaft and the hub, representing a stress after the completion of the plastic bonding. - The present invention is applied to a bonding method for bonding a bonding member to a member to be bonded, which are used for a device for rotating the bonding member serving as a rotary disk and the member to be bonded serving as a rotary shaft integrally connected to each other.
- The method comprises the steps of:
- inserting the member to be bonded into a fitting hole formed in the bonding member having an inner diameter greater than an outer diameter of the member to be bonded, followed by positioning the member to be bonded;
- pressurizing a portion, in the vicinity of the fitting portion of the member to be bonded, of the bonding member at a load for generating a stress enough to effect plastically deform the material of the bonding member, followed by preliminarily plastic bonding;
- further pressurizing the portion, in the vicinity of the fitting portion of the member to be bonded, of the bonding member at a load in excess of an elastic limit of the material of the bonding member; and
- generating compression force in an axial direction of the member to be bonded at the portion in the vicinity of the fitting portion of the bonding member, and then,
- allowing part of the material of the fitting portion in excess of the elastic limit to effect plastic-flow in such a manner as to fill a gap defined between the member to be bonded and the bonding member;
- whereby the bonding member and the member to be bonded are tightly integrated with each other.
- The present invention is also applied to a bonded body comprising a bonding member and a member to be bonded, which are used in a device for rotating the bonding member on which rotary disks are stacked and the member to be bonding serving as a rotary shaft in integral bonding:
- wherein a portion, in the vicinity of the fitting portion of the member to be bonded, of the bonding member is pressurized at a load for generating a stress enough to plastically deform the material of the bonding member, followed by preliminarily plastic bonding;
- further the portion, in the vicinity of the fitting portion of the member to be bonded, of the bonding member is pressurized at a load in excess of an elastic limit of the material of the bonding member; and
- a compression force in an axial direction of the to-be-bonded member is generated at the portion in the vicinity of the fitting portion of the bonding member, and then, part of the material of the fitting portion in excess of the elastic limit is allowed to plastic-flow in such a manner as to fill a clearance defined between the member to be bonded and the bonding member;
- whereby the bonding member and the member to be bonded are tightly integrated with each other.
- The present invention is further applied to a mechanical apparatus provided with a bonded body comprising a bonding member and a member to be bonded, which are used in a device for rotating the bonding member on which rotary disks are stacked and the to-be-bonded member serving as a rotary shaft in integral bonding:
- wherein a portion, in the vicinity of the fitting portion of the to-be-bonded member, of the bonding member is pressed to provide a plastically deformed part, which is in the vicinity of the fitting portion of the to-be-bonded member and is further pressed, followed by plastic-flow bonding.
- The technical fields to which the present invention is applied are a bonding method for subjecting, to plastic-flow bonding, metallic members such as a shaft and a hub in a spindle motor for use in a disk device, a DVD or a CD-ROM in a computer or the like, in particular, in a spindle motor having a dynamic pressure bearing structure, which is a thin-type hard disk drive motor to be loaded in a portable personal computer such as a notebook personal computer. In addition, it relates to a bonded body with reference to FIGS. 1 to 15. For the convenience, there are set forth meanings of all reference numerals in the following table.
TABLE 1 Shaft 2 Hub 3 Disc 4 Disc spacer 5 Clamp 6 Screw 7 Housing 8 Dynamic pressure bearing metal 10 Thrust receiving plate 11 Base 12 Stopper ring 13 Magnet 14 Stator core 21 Bonding hole 22 Edge portion 23 Bottom face 25 Outer diameter of hub 24 Flange 31 Annular groove 32 Female screw 34 Edge portion 40 Spherical edge portion 41 Thrust receiving face 42 Stopper groove 60 Preliminary bonding punch 61 Guide ring 62 Inner diameter 63 Stand 64 Guide hole 65 Inner diameter of guide ring 66 Preliminary bonding projection 67 Screw hole 70 Punch 71 Preliminary bonding mark 72 Bottom portion of preliminary mark 74 Guide hole 76 Bonding projection 80 Preliminary bonded body 100 Dynamic pressure bearing spindle motor 200 Hard disc 300 Read-out device - The bonding method for subjecting the two members to the plastic-flow bonding and the bonded body according to the present invention are exemplified here in a dynamic pressure bearing spindle motor in a hard disk drive by the use of a bonded body including a hub and a shaft in a preferred embodiment.
-
FIG. 1 is a general plane view of a hard disk drive, andFIG. 2 is a cross-sectional view of the hard disk drive shown inFIG. 1 . - In
FIGS. 1 and 2 ,reference numeral 200 designates a hard disk of a hard disc drive (abbreviated as “an HDD”), in which a dynamic pressure bearingspindle motor 100 is disposed. A read-outdevice 300 reads out data from a hard disk rotationally driven by the dynamic pressure bearingspindle motor 100. -
FIG. 3 shows a dynamic pressure-bearing spindle motor in the hard disk drive, in which a bonded body of a hub and a shaft is used, in a preferred embodiment according to the present invention. - In
FIG. 3 , ashaft 1 is integrated with ahub 2 by a bonding method according to the present invention. To thehub 2 is securely fixed amagnet 13. A plurality ofdisks 3 serving as storage mediums are stacked on aflange 24 of the hub with disk spacers 4 held therebetween and are secured by aclamp 5 that is tightened to afemale screw 32 of theshaft 1 with a screw 6. Theshaft 1 is rotatably fitted into the bore of a dynamicpressure bearing metal 8 secured to a housing 7. Thus, a radial dynamic pressure bearing is constituted by the effect of a dynamic pressure generated by a magnetic fluid filled inside the housing according to rotation. The housing 7 is fixedly secured to abase 11. Athrust receiving plate 10 is joined to the housing 7 while astopper ring 12 is held between the dynamicpressure bearing metal 8 and thethrust receiving plate 10, and thus, constitutes a thrust bearing in which aspherical edge portion 40 of theshaft 1 is supported at athrust receiving face 41. Theshaft 1 is suppressed by thestopper ring 12 fitted into astopper groove 42 from floating in a thrust direction. Awound stator core 14 is securely bonded to the base 11 with an adhesive, and therefore, themagnet 13 receives rotating force at the time of energization, thereby rotating thehub 2. - Next, an explanation will below be made of the
hub 2 and theshaft 1. It is desirable that thehub 2 as a bonding member should be made of a material which is liable to plastically deform and has deformation resistance is smaller than that of theshaft 1 serving as a member to be bonded. Thehub 2 is made of ferrite stainless steel, for example, SUS430 in consideration of corrosion resistance and magnetic characteristics in terms of a motor. Theshaft 1 is formed into a columnar shape, and is made of martensitic stainless steel excellent in abrasion resistance or corrosion resistance such as SUS440 or SUS420 J2 in consideration of bearing performance, followed by hardening. At an outer diameter portion to be bonded in the vicinity of one end of theshaft 1 is formed anannular groove 31. The details of the shape of the groove will be described later. -
FIG. 4 shows a bonded body of the hub and the shaft in a preferred embodiment according to the present invention. InFIG. 4 , theshaft 1 is provided with theannular groove 31 formed in the outer diameter portion to be bonded in the vicinity of one end of theshaft 1 and is plastically bonded to abonding hole 21 formed in thehub 2 having a diameter greater than the outer diameter of theshaft 1 by a method, described below, as shown inFIG. 6 . Theshaft 1 and thehub 2 are bonded to each other through a first process in which theshaft 1 shown inFIG. 5 is freely fitted or gap-fitted to thehub 2 shown inFIG. 6 , followed by preliminarily plastic bonding, and a second process of plastic-flow bonding. - First, a description of the first process of the preliminarily plastic bonding will be given below. A
bottom face 23 of thehub 2 is held by astand 63, as shown inFIG. 7 . Thehub 2 is held at anouter diameter 25 thereof by aninner diameter 62 of aguide ring 61. Thereafter, anedge portion 34 on a side on which theannular groove 31 is formed at the outer diameter portion to be bonded of theshaft 1 is inserted into and fitted to thebonding hole 21 of thehub 2. - It is desirable from the viewpoint of bonding accuracy that a clearance or gap at the fitting portion between the
shaft 1 and thehub 2 when theedge portion 34 of theshaft 1 is inserted into thebonding hole 21 of thehub 2, that is, a clearance between the wall surface of thebonding hole 21 of thehub 2 and the outer peripheral surface of theshaft 1 should be set as small as 0 to 0.02 mm. In the present preferred embodiment, the outer diameter of theshaft 1 is set to 3.00 mm while the inner diameter of thebonding hole 21 of thehub 2 is set to 3.01 mm. - In this manner, while the
bottom surface 23 of thehub 2 is held by thestand 63, theedge portion 34 of theshaft 1 is inserted into and fitted to thebonding hole 21 of thehub 2. Thus, a preliminarily bondingpunch 60 is fitted to theinner circumference 65 of theguide ring 61 and theshaft 1 is fitted into aguide hole 64 formed at substantially the center of the preliminarily bondingpunch 60, thereby holding theshaft 1. Theshaft 1 is held in theguide hole 64 of the preliminarily bondingpunch 60 guided on theinner circumference 65 of theguide ring 61, and then, the preliminarily bondingpunch 60 is driven by a press ram, not shown into the bonding member. When the preliminarily bondingpunch 60 is driven by the press ram, a ring-like projection 66 having a projection width K is formed at the tip of the preliminarily bondingpunch 60 by which anedge portion 22 of thehub 2 is pressed down in the vicinity of thebonding hole 21. - The pressing force of the preliminarily bonding
punch 60 is a load that generates stress large enough to plastic-deform the material forming thehub 2, and force that plastically deforms a portion corresponding to such a depth as to fill the fitting clearance between theshaft 1 and thehub 2 vertically. The preliminarily bondingpunch 60 is pressed down at the above-described load, and then, the material in the vicinity of thebonding hole 21 of thehub 2 is allowed to plastic-flow, followed by the preliminary bonding. The bonding portion after the preliminarily plastic bonding in the above-described manner is shown inFIG. 8 , which is an enlarged vertical cross-sectional view. - Subsequently, an explanation will below be made of the second process of the plastic-flow bonding. In the second process shown in
FIG. 9 , a preliminary bondedbody 80 of theshaft 1 and thehub 2 which have been subjected to the preliminarily plastic bonding is held by thestand 63 at thebottom face 23 of thehub 2, and theouter diameter 25 of thehub 2 is held by theinner diameter 62 of theguide ring 61. Then, theshaft 1 is held in aguide hole 74 formed in apunch 70 guided on theinner diameter 65 of theguide ring 61. In this state, a press ram, not shown, drives thepunch 70 into the bonding member. When thepunch 70 is driven into the bonding member, a ring-like bonding projection 76 presses a portion of thebottom portion 72 of a preliminarily bondingmark 71 in the vicinity of thebonding hole 21. The ring-like bonding projection 76 is disposed at the tip of thepunch 70 and has a projection width W smaller than the projection width K of the preliminarily bondingprojection 66 of the preliminarily bondingpunch 60. - The pressing force of the
punch 70 is a load large enough to generate a stress for effecting a plastic deformation of the material forming thehub 2. Thepunch 70 is pressed down at the above-described load, and then, the material in the vicinity of thebonding hole 21 of thehub 2 is allowed to effect plastic-flow over the entire circumference of thegroove 31, followed by the bonding. The bonded portion after the plastic-flow bonding in the above-described manner is shown inFIG. 10 , which is an enlarged vertical cross-sectional view of the bonding. - Furthermore, in order to achieve a high bonding accuracy, the smaller the gap between the
guide hole 64 of the preliminarily bondingpunch 60 or theguide hole 74 of thepunch 70 and the outer peripheral surface of theshaft 1, the higher the bonding accuracy is obtained. Moreover, if the projecting width K and pressing depth J due to the preliminarily bondingprojection 66 of the preliminarily bondingpunch 60 are too large, the load for effecting the plastic deformation becomes large, thereby degrading the accuracy of thehub 2. - Additionally, if the projecting width W and pressing depth H due to the
bonding projection 76 of thepunch 70 are too great, the load for the plastic deformation becomes large, and therefore, the material more than that flowing in the groove is liable to be fluidized, thereby degrading the bonding accuracy. Thus, the projecting width W and the pressing depth H are set according to the shape of the groove. - Next, a description will be given below of the shape of the
groove 31 of theshaft 1.FIG. 11 shows one example of the portion of thegroove 31 of theshaft 1. Factors determining the cross-sectional shape of thegroove 31 of theshaft 1 include the groove depth H, a groove width B, a groove angle θ, the number n of grooves and the like. - If the depth H of the
groove 31 of theshaft 1 is too small, a sufficient shearing strength cannot be achieved due to easy plastic deformation when external force is exerted in an axial direction. In contrast, if the depth H of thegroove 31 of theshaft 1 is too large, the material insufficiently flows into the groove, thereby forming a gap, so as to degrade the strength. As shown inFIG. 7 , thescrew hole 67 for screwing theclamp 5 is formed at the lower portion of theshaft 1, and further, thefemale screw 32 is disposed at the inner wall surface of thescrew hole 67 of theshaft 1. Consequently, the thickness at a portion near the bonded portion of thehub 2 to the lower portion of theshaft 1 becomes small. Therefore, if the depth H of thegroove 31 of theshaft 1 shown inFIG. 11 is increased, the strength of theshaft 1 is degraded. Thus, the groove depth H of thegroove 31 of theshaft 1 should desirably range from about 0.07 to about 0.13 mm. - The width B of the
groove 31 of theshaft 1 can be varied according to the shearing strength required at the bonded portion. However, if the width is set too largely, a distance from the tip of thepunch 70 to the lower portion of thegroove 31 of theshaft 1 becomes great in bonding to thehub 2, thereby increasing a fluid frictional loss of the material in the vicinity of thebonding hole 21 of thehub 2, which should flow into thegroove 31 of theshaft 1. Therefore, even if the large load is applied to thehub 2 by thepunch 70, the internal stress of the material in the vicinity of thebonding hole 21 of thehub 2 near the lower portion of theshaft 1 cannot be increased enough to achieve the plastic deformation. As a consequence, the material in the vicinity of thebonding hole 21 of thehub 2 near the lower portion of theshaft 1 is reduced in quantity of the plastic deformation, so that the material in the vicinity of thebonding hole 21 of thehub 2 insufficiently flows into thegroove 31 of theshaft 1. In this manner, if the depth H of thegroove 31 of theshaft 1 shown inFIG. 11 is increased, the strength of theshaft 1 is degraded. Thus, the depth H of thegroove 31 of theshaft 1 should desirably range from about 0.07 to about 0.13 mm. - Moreover, as shown in
FIG. 11 , as to the groove angle θ representing an opening degree (i.e., an angle) of thegroove 31 of theshaft 1, if the opening angle θ of thegroove 31 of theshaft 1 is small, the material in the vicinity of thebonding hole 21 of thehub 2 is less prone to flow into thegroove 31 of theshaft 1 when the large load is applied to thehub 2 by thepunch 70. In contrast, if the opening angle θ of thegroove 31 of theshaft 1 is great, the material in the vicinity of thebonding hole 21 of thehub 2 shallowly bites when the large load is applied to thehub 2 by thepunch 70, so that drawing strength becomes small. In this manner, if the groove angle θ of thegroove 31 of theshaft 1 shown inFIG. 11 is small, the material is less prone to flow into thegroove 31 of theshaft 1; in contrast, if the groove angle θ of thegroove 31 of theshaft 1 is large, the drawing strength becomes small. As a result, the groove angle θ of thegroove 31 of theshaft 1 should desirably range from about 60° to about 120°. - Furthermore, as the number n of
grooves 31 of theshaft 1 is greater, the contact area between theshaft 1 and thehub 2 becomes larger, thereby increasing the drawing strength. However, if the number n ofgrooves 31 of theshaft 1 is great, the material in the vicinity of thebonding hole 21 of thehub 2 is less prone to flow into thegroove 31 of theshaft 1 when the large load is applied to thehub 2 by thepunch 70. As a consequence, if the number n ofgrooves 31 of theshaft 1 is too great, the drawing strength is much degraded. Thus, when the number n ofgrooves 31 of theshaft 1 is 2, the drawing strength is highest. Upon comparison of the case of n=1 with the case of n=2 under the condition that the groove width B is the same, the contact area between the shaft and the hub is greater in the case of n=2, thereby increasing the drawing strength. - Incidentally, the cross-sectional shape of the
groove 31 of theshaft 1 need not be a triangle as shown inFIG. 11 . It may be a round shape, as shown inFIG. 12 . In the case where a high torque strength is needed at the bonded portion between the lower portion of theshaft 1 and thehub 2, aknurl 36 may be formed at a thread between thegrooves 31 of theshaft 1, as shown inFIG. 13 . - Additionally, if the
groove 31 of theshaft 1 is formed over the entire circumference of theshaft 1, the material in the vicinity of thebonding hole 21 of thehub 2 plastically flows over the entire circumference in a uniform manner when the large load is applied to thehub 2 by thepunch 70, and further, strain also uniformly is exerted over the entire circumference, so that both of accuracy of a right angle and strength can be enhanced. In addition, thegroove 31 of theshaft 1 can be molded by lathing, thus achieving high productivity. - Furthermore, it is preferable that the position of the
groove 31 of theshaft 1 should be set near apressing surface 24 of thehub 2 as possible. If the position of thegroove 31 of theshaft 1 is positioned apart from thepressing surface 24 of thehub 2, a fluid frictional resistance becomes high, and therefore, the material in the vicinity of thebonding hole 21 of thehub 2 is prone to flow into thegroove 31 of theshaft 1. - In view of this, in the present preferred embodiment, as shown in
FIG. 14 , the outer circumferential portion of theshaft 1 having theannular groove 31 formed at the outer periphery of theshaft 1 is freely fitted into thebonding hole 21 of thehub 2; the large load is applied to thehub 2 by thepunch 70; the vicinity of the hole formed at the end surface of thehub 2 is plastically deformed over the entire circumference; theshaft 1 and thebonding hole 21 of thehub 2 are subjected to the preliminarily plastic bonding in such a manner as to fill the gap; the material in the vicinity of thebonding hole 21 at the end surface is plastically deformed over the entire circumference after the preliminarily plastic bonding of thehub 2 in the state in which a stress a is exerted on thebonding hole 21 of thehub 2; a compression stress is exerted on theshaft 1 in such a manner as to fill thegroove 31 of theshaft 1; and then, the material in the vicinity of thebonding hole 21 of thehub 2 is allowed to plastic-flow. The shearing force and strain P of the material in the vicinity of thebonding hole 21 of thehub 2 and the stress σ caused by the preliminarily plastic bonding are exerted on a portion remote from the pressing portion, on which the strain is hardly exerted, as shown inFIG. 15 . Thus, the connection strength between thehub 2 and theshaft 1 is high. - Incidentally, the present invention is not limited to the above-described preferred embodiment, but it can be applied to bonding between other members of various kinds of metals, for example, a shaft, a cylinder or the like and a flat plate.
- According to the present invention, it is possible to achieve the sufficient strength and accuracy without any occurrence of bending or contamination even in the case of the bonding between the thin hub and the small-diameter shaft.
- Moreover, the fitting accuracy before the bonding may be rough in comparison with the press-fitting, the high productivity can be achieved in inexpensive equipment, and further, the fabricating cost can be reduced.
Claims (6)
1. A bonding method for bonding metallic members, which comprises the steps of: fitting a metallic members to another metallic member, followed by effecting preliminarily plastic bonding by means of a preliminarily bonding punch; and generating compression force in an axial direction of the members in the vicinity of the fitting portion of the bonding members after the preliminarily plastic bonding, and, allowing part of the material of the bonding member to effect plastic-flow in such a manner as to fill a gap defined between the metallic members, so as to plastically bond the members.
2. A bonding method for bonding a bonding member onto a member to be bonded, which are used in a device for rotating the bonding member serving as a rotary disk and the to-be-bonded member serving as a rotary shaft in integral bonding, the bonding method comprising:
a first step of fitting the bonding member to the member to be bonded, followed by preliminarily plastic bonding by a preliminarily bonding punch; and
a second step of generating compression force in an axial direction of the to-be-bonded member in the vicinity of the fitting portion of the bonding member after the preliminarily plastic bonding in the first step, and then, allowing part of the material of the bonding member to plastic-flow in such a manner as to fill a clearance defined between the bonding member and the member to be bonded, so as to plastically bond the bonding member onto the member to be bonded;
whereby the bonding member and the member to be bonded are tightly integrated with each other.
3. A bonding method for bonding a bonding member onto a member to be bonded as claimed in claim 2 , wherein the bonding member and the member to be bonded are freely fitted to each other.
4. A bonding method for bonding a bonding member onto a member to be bonded, which are used in a device for rotating the bonding member serving as a rotary disk and the to-be-bonded member serving as a rotary shaft in integral bonding, the bonding method comprising the steps of:
inserting the member to be bonded into a fitting hole formed at the bonding member having an inner diameter greater than an outer diameter of the member to be bonded, and positioning the member to be bonded thereat;
pressurizing a portion, in the vicinity of the fitting portion of the member to be bonded, of the bonding member at a load for generating a stress enough to plastically deform the material of the bonding member, followed by preliminarily plastic bonding;
further pressurizing the portion, in the vicinity of the fitting portion of the member to be bonded, of the bonding member at a load in excess of an elastic limit of the material of the bonding member; and
generating compression force in an axial direction of the to-be-bonded member at the portion in the vicinity of the fitting portion of the bonding member, and then, allowing part of the material of the fitting portion in excess of the elastic limit to plastic-flow in such a manner as to fill a clearance defined between the member to be bonded and the bonding member;
whereby the bonding member and the member to be bonded are tightly integrated with each other.
5. A bonding method for bonding a bonding member onto a member to be bonded as claimed in claim 1 , wherein an annular groove is formed at the fitting portion of the to-be-bonded member to the bonding member.
6. A bonding method for bonding a bonding member onto a member to be bonded as claimed in claim 5 , wherein a knurl is formed at the annular groove formed at the fitting portion of the to-be-bonded member to the bonded member.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
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US11/211,502 US20050278938A1 (en) | 2002-10-04 | 2005-08-26 | Method of bonding metallic members by plastic-flow bonding and plastic-flow bonded body |
Applications Claiming Priority (4)
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JP2002292794A JP3868361B2 (en) | 2002-10-04 | 2002-10-04 | Plastic flow joint and its joining method |
JP2002-292794 | 2002-10-04 | ||
US10/677,291 US7489056B2 (en) | 2002-10-04 | 2003-10-03 | Method of bonding metallic members by plastic-flow bonding and plastic-flow bonded body |
US11/211,502 US20050278938A1 (en) | 2002-10-04 | 2005-08-26 | Method of bonding metallic members by plastic-flow bonding and plastic-flow bonded body |
Related Parent Applications (1)
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US10/677,291 Division US7489056B2 (en) | 2002-10-04 | 2003-10-03 | Method of bonding metallic members by plastic-flow bonding and plastic-flow bonded body |
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US20050278938A1 true US20050278938A1 (en) | 2005-12-22 |
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US10/677,291 Expired - Fee Related US7489056B2 (en) | 2002-10-04 | 2003-10-03 | Method of bonding metallic members by plastic-flow bonding and plastic-flow bonded body |
US11/211,502 Abandoned US20050278938A1 (en) | 2002-10-04 | 2005-08-26 | Method of bonding metallic members by plastic-flow bonding and plastic-flow bonded body |
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US10/677,291 Expired - Fee Related US7489056B2 (en) | 2002-10-04 | 2003-10-03 | Method of bonding metallic members by plastic-flow bonding and plastic-flow bonded body |
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US (2) | US7489056B2 (en) |
EP (1) | EP1406027B1 (en) |
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DE (1) | DE60302966T2 (en) |
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Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20070236091A1 (en) * | 2006-04-06 | 2007-10-11 | Nidec Corporation | Rotor unit, bearing mechanism, motor, and data storage disk drive device |
US7667360B2 (en) | 2006-04-06 | 2010-02-23 | Nidec Corporation | Rotor unit, bearing mechanism, motor, and data storage disk drive device |
US20100232993A1 (en) * | 2009-03-12 | 2010-09-16 | Nidec Corporation | Motor |
US8253286B2 (en) * | 2009-03-12 | 2012-08-28 | Nidec Corporation | Motor with coming-off preventing portion |
US20150249368A1 (en) * | 2012-09-18 | 2015-09-03 | Meidensha Corporation | Stator fixing structure |
US10770933B2 (en) * | 2012-09-18 | 2020-09-08 | Meidensha Corporation | Stator fixing structure |
US20190097488A1 (en) * | 2017-09-26 | 2019-03-28 | Nidec Corporation | Motor |
US10910907B2 (en) * | 2017-09-26 | 2021-02-02 | Nidec Corporation | Motor |
Also Published As
Publication number | Publication date |
---|---|
CN1221966C (en) | 2005-10-05 |
JP3868361B2 (en) | 2007-01-17 |
CN1497574A (en) | 2004-05-19 |
DE60302966T2 (en) | 2006-08-03 |
EP1406027A1 (en) | 2004-04-07 |
JP2004122209A (en) | 2004-04-22 |
DE60302966D1 (en) | 2006-02-02 |
EP1406027B1 (en) | 2005-12-28 |
US20040071504A1 (en) | 2004-04-15 |
US7489056B2 (en) | 2009-02-10 |
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