CN1991187A - Hydrodynamic bearing device and a recording disk drive equipped with it - Google Patents
Hydrodynamic bearing device and a recording disk drive equipped with it Download PDFInfo
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- CN1991187A CN1991187A CN 200710007762 CN200710007762A CN1991187A CN 1991187 A CN1991187 A CN 1991187A CN 200710007762 CN200710007762 CN 200710007762 CN 200710007762 A CN200710007762 A CN 200710007762A CN 1991187 A CN1991187 A CN 1991187A
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- 230000001050 lubricating effect Effects 0.000 claims description 107
- 238000003860 storage Methods 0.000 claims description 49
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- 238000005461 lubrication Methods 0.000 abstract description 6
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- 230000000694 effects Effects 0.000 description 19
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- 239000003921 oil Substances 0.000 description 8
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- 238000006243 chemical reaction Methods 0.000 description 2
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- 238000012423 maintenance Methods 0.000 description 2
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- 229910000831 Steel Inorganic materials 0.000 description 1
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- Sliding-Contact Bearings (AREA)
- Sealing Of Bearings (AREA)
- Rotational Drive Of Disk (AREA)
- Motor Or Generator Frames (AREA)
- Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
Abstract
The present invention can miniaturize a conical dynamic pressure bearing device, and to excellently enhance the performance thereof at a low cost. In the conical dynamic pressure bearing device, a fluid pressurizing means 13e to pressurize a lubrication fluid in the pressing direction toward the inner side of an inclined bearing space BS is continuously provided on an opening part located on the outer circumferential side of the substantially conical inclined bearing space BS formed in a space between both inclined dynamic pressure surfaces of a bearing sleeve 13 and a shaft bush 21, the pressurized lubrication fluid is pressed into the inner side from the outer circumferential side of the inclined bearing space BS by the fluid pressurizing means 13e to excellently generate the dynamic pressure in the lubrication fluid in the inclined bearing space BS irrespective of the opening angle of the inclined dynamic pressure surfaces, and the lubrication fluid to flow outwardly from the opening part on the outer circumferential side of the inclined bearing space BS is stably held in the inclined bearing space BS by the rotational centrifugal force.
Description
This case is that to be " Hydrodynamic bearing apparatus and have the recording disc drive unit of this device ", the applying date be " on June 23rd, 2004 ", application number dividing an application for the patent application of " 200410061902.2 " to title.
Technical field
The present invention relates to make on the structure kinetic pressure of utilizing lubricating fluid and float the recording disc drive unit that the non-contacting mode swivel bearing of one side forms the Hydrodynamic bearing apparatus of roughly cone shape axle bush and axle sleeve and has this device relatively with one side.
The invention still further relates to the Hydrodynamic bearing apparatus and the disc drive appts of hydraulic bearing member with the dynamic pressure support running shaft that utilizes lubricating fluid.
Background technique
In recent years, carrying out can be in the exploitation of the Hydrodynamic bearing apparatus of the various solid of rotation of stable support under the high speed.The structure that conical Hydrodynamic bearing apparatus wherein forms is as follows.In axle sleeve, can insert axle bush with the relative rotation with the roughly cone shape inclination dynamic pressure face of identical formation with the roughly cone shape inclination dynamic pressure face of formation, while is in the opposed gap of these axle bush inclination dynamic pressure faces and axle sleeve inclination dynamic pressure face, form roughly cone shape inclination bearing space, and the lubricating fluid that the packing lubrication wet goods is formed in this inclination bearing space.
Then, at least one side of two inclination dynamic pressure faces of above-mentioned axle bush and axle sleeve the dynamic pressure generation device that the groove structure etc. of suitable shape constitutes is set.Above-mentioned axle bush is relative with axle sleeve when rotating, by above-mentioned dynamic pressure generation device lubricating fluid is pressurizeed, make lubricating fluid produce kinetic pressure, and the kinetic pressure of utilizing this lubricating fluid makes above-mentioned axle bush and axle sleeve float all relatively radial and axial, thereby form the structure (for example, referring to Patent Document 1～4) of non-contact swivel bearing.
[patent documentation 1]
The flat 7-7886 of patent disclosure
[patent documentation 2]
The flat 10-339318 of patent disclosure
[patent documentation 3]
Patent disclosure 2002-174226
[patent documentation 4]
Patent disclosure 2003-97547
Like this, in the conical Hydrodynamic bearing apparatus, two dynamic pressure faces formations that form respectively on axle sleeve and the axle bush are formed slopely roughly cone shape to running shaft, but in order to make the relative floatation volume between fixed component and the rotating member stable, reliable, be preferably made and set the angle of release of the above-mentioned inclination dynamic pressure face conical drift angle of inclination dynamic pressure face (promptly should) big as far as possible, thus, axial kinetic pressure is improved.
In recent years, in the various rotating driving devices,, make lubricating fluid produce dynamic pressure with the exploitation of the Hydrodynamic bearing apparatus of supporting rotating shaft non-contactly as the bearing means that is used to make solid of rotation high speed and highi degree of accuracy rotation.For this Hydrodynamic bearing apparatus, the present inventor is by seeking whole device purpose of thinness, and exploitation also proposes to adopt for example device of the SB of axial hydrodynamic bearing portion of structure shown in Figure 23.Promptly, among the SB of axial hydrodynamic bearing portion shown in this figure, rotating member (rotation hub) 303 is connected with the running shaft 302 that is supported freely by hydraulic bearing member (axle sleeve) 301 rotations, simultaneously the axial outer end face (upper-end surface of Figure 23) of the end face of the axial inboard of the centre area of this rotating member 303 (lower face side of Figure 23) and above-mentioned hydraulic bearing portion 301 is configured to closely opposedly mutually, and the part in this axial opposed district forms the above-mentioned axial hydrodynamic bearing SB of portion.
Private side at the bearing space of the SB of this axial hydrodynamic bearing portion injects suitable lubricating fluid (figure omits), descend simultaneously concavity that for example spirality dynamic pressure is set and produce groove, make it along the circumferential direction side by side, with dynamic pressure generation device as this lubricating fluid, and utilize this dynamic pressure to produce the pressurization of groove, above-mentioned lubricating fluid is produced dynamic pressure, thereby obtain desired axial buoyancy.
Again, the opposed diametrically contraposition of outer peripheral sidewall face district at the interior all side wall surfaces and the running shaft 302 of above-mentioned hydraulic bearing member 301, form 2 RB of place radial dynamic pressure bearing portion, RB vertically, inside one side of the bearing space of these radial dynamic pressure bearings RB of portion is injected lubricating fluid (figure omits) continuously from the above-mentioned axial hydrodynamic bearing SB of portion.And following concavity is provided with for example man type dynamic pressure and produces groove, makes it along the circumferential direction side by side, with dynamic pressure generation device as this lubricating fluid, utilize the pressurization of this dynamic pressure generation device, above-mentioned lubricating fluid is produced dynamic pressure, thereby obtain desired radially buoyancy.
Like this, the structure that forms in the above-mentioned Hydrodynamic bearing apparatus is: form the bearing space from the 2 radial dynamic pressure bearing RB of portion, RB to the SB of axial hydrodynamic bearing portion continuously, and inject lubricating fluid continuously in this continuous bearing space.
Yet, strengthen to set the structure of inclination dynamic pressure face angle of release, owing to cause whole device that it is radially maximized, but be subjected to the restriction of magnetic drive portion etc., so can not be used to seek the little device of diameter.And when inclination dynamic pressure face angle of release was too big, the radial dynamic pressure deficiency may cause bearing rigidity to reduce.
Have again, strengthen and set inclination dynamic pressure face angle of release, the rotary centrifugal force of the outer circumferential side part of inclination bearing space is increased, the active force that this rotary centrifugal force produces is sometimes greater than the fluid confining force of fluid-tight portion, even be provided with under the situation of fluid-tight portion, also often cause lubricating fluid to drain to the outside.
Again, the advantage that so conical Hydrodynamic bearing apparatus has is: utilize two inclination dynamic pressure faces that form respectively in axle sleeve and the axle bush to constitute the inclination bearing space, thereby can obtain radial dynamic pressure and axial hydrodynamic power simultaneously.But the trend that its reverse side exists is: the isostasy that is filled in the lubricating fluid in the inclination bearing space is destroyed because of the size error slightly of each member easily, and is big thereby the pressure difference at inclination bearing space two end part becomes.Therefore the problem that exists is, is difficult to reliablely and stablely to obtain the relative floatation volume between fixed component and the rotating member, is not easy to obtain suitable bearing rigidity.
Yet, have in the Hydrodynamic bearing apparatus of such structure, because the gap size of the above-mentioned radial dynamic pressure bearing RB of portion and dynamic pressure produce groove shape machining errors during fabrication such as (flute length) etc., axially can form unbalanced shape sometimes.Therefore, example is as shown in Figure among the radial dynamic pressure bearing RB of portion of downside, and as Figure 24 represented with arrow length, pumping action power P1, P2 were axially becoming imbalance (P1＞P2 or P1＜P2) sometimes.The imbalance of this radial dynamic pressure bearing RB of portion even be communicated with each hydraulic bearing portion or its neighbouring part with the pressure adjustment with circulation ports such as split channels, can not be eliminated fully.When the pressure that especially is arranged on the lubricating fluid in the fluid storage portion 304 of core of the bearing space that comprises above-mentioned radial dynamic pressure bearing RB of portion and the SB of axial hydrodynamic bearing portion became less than atmospheric negative pressure, lubricating fluid often produced bubble.When this bubble infiltrates the inside of each hydraulic bearing portion, can not get good dynamic pressure, its result makes bearing characteristics significantly impaired.
Therefore, purpose of the present invention is: even provide a kind of inclination dynamic pressure face angle of release that do not strengthen also can reliablely and stablely obtain good relatively floatation volume, can also finely prevent Hydrodynamic bearing apparatus that the lubricating fluid from the inclination bearing space leaks and the disc drive appts with this device simultaneously.
Again, purpose of the present invention is: thus provide a kind of easy structure of utilizing can suitably keep tilting the pressure difference between the bearing space two end part can be convenient and obtain the Hydrodynamic bearing apparatus of the suitable relative floatation volume between fixed component and the rotating member and disc drive appts reliably with this device.
Again, purpose of the present invention is: provide a kind of easy structure of utilizing can finely prevent that bubble from the Hydrodynamic bearing apparatus and the disc drive appts of the dynamic pressure characteristic of continuous long-term stability taking place, can get at.
Summary of the invention
In order to solve above-mentioned problem, in the Hydrodynamic bearing apparatus aspect the present invention the 1st, make on the structure: from leaving in the 2 radial dynamic pressure bearing portions that appropriate intervals is provided with and radial dynamic pressure bearing portion axial hydrodynamic bearing portion sides adjacent bearing space in the diametrically contraposition district vertically to described axial hydrodynamic bearing portion, and between the space of the axial foreign side side adjacent with the axial hydrodynamic bearing portion of opposite side, utilization separates the pressure adjustment that forms with described bearing space and is communicated with split channel, simultaneously at the bearing space that is equivalent to the part between the described 2 place radial dynamic pressure bearing portions, the fluid storage portion that setting is made up of the formed clearance space of bearing space that radially enlarges described radial dynamic pressure bearing portion, and the pressurization of the lubricating fluid in the described 2 place radial dynamic pressure bearing portions is made fluid in the described fluid storage portion is malleation more than the barometric pressure.
And, for example in the Hydrodynamic bearing apparatus of the present invention the 3rd aspect, the bearing space that constitutes at least one side in the 2 place radial dynamic pressure bearing portions in above-mentioned the 1st aspect forms like this, make the gap size of this bearing space enlarge continuously or keep identical, constitute taper space or parellel space towards described fluid storage portion.
Again, in the Hydrodynamic bearing apparatus of the present invention the 5th aspect, by forming to such an extent that constitute roughly that " the ring-type aggregate of the tortuous groove of the herringbone shape of＜" font forms the dynamic pressure generation device in above-mentioned the 1st aspect, and the dot location of the tortuous groove of herringbone shape that formation is configured in the dynamic pressure generation device of at least one side in the 2 place radial dynamic pressure bearing portions is configured in from the axial centre position of this radial dynamic pressure bearing portion the position of moving to described fluid storage portion lateral deviation.
Hydrodynamic bearing apparatus according to the present invention the 1st aspect, the 3rd aspect or the 5th aspect with this structure, in the fluid storage portion that the core of the bearing space that comprises 2 place radial dynamic pressure bearing portions and axial hydrodynamic bearing portion is provided with, the lubricating fluid pressurization of its inner utilization radial dynamic pressure bearing portion, and often keep greater than atmospheric barotropic state, thereby can prevent from well to produce bubble in the lubricating fluid, stably obtain suitable dynamic pressure.
Again, for example in the Hydrodynamic bearing apparatus of the present invention the 2nd aspect, make on the structure except that described 2 place radial dynamic pressure bearing portions, to the pressurization of the lubricating fluid in the described axial hydrodynamic bearing portion, making the lubricating fluid in the described fluid storage portion is the above malleation of barometric pressure.
Hydrodynamic bearing apparatus according to the 2nd aspect with this structure, owing to can prevent to produce in the lubricating fluid bubble well, stably obtain suitable dynamic pressure, thereby can the reliability of Hydrodynamic bearing apparatus be improved with the stable dynamic pressure characteristic of the long-term acquisition of easy structure.
At this moment, in the Hydrodynamic bearing apparatus of the present invention the 4th aspect, constitute the bearing space of axially going up long radial dynamic pressure bearing portion in the 2 place radial dynamic pressure bearing portions of above-mentioned the 1st aspect and form like this, make it constitute the taper space.
According to the Hydrodynamic bearing apparatus of the present invention the 4th aspect, can realize above-mentioned effect expeditiously by the big radial dynamic pressure bearing portion of pressurization with this structure.
Again, in the Hydrodynamic bearing apparatus of the present invention the 6th aspect, make on the structure: be separately positioned in the tortuous groove of herringbone shape of each dynamic pressure generation device of 2 place radial dynamic pressure bearing portions of above-mentioned the 5th aspect, be positioned at than dot location and more be respectively A and D by the axial length of the groove outside axial, be positioned at when more being respectively B and C by the axial length of axially inboard groove than dot location, following relation is set up: A+D 〉=B+C.
Hydrodynamic bearing apparatus according to the present invention the 6th aspect with this structure, because the pressurization role to lubricating fluid in the 2 place radial dynamic pressure bearing portions is the private side that lubricating fluid is pressed into fluid storage portion generally, thereby fluid storage portion often keeps reliably greater than atmospheric barotropic state.
The recording disc drive unit of the present invention the 7th aspect has the spindle drive motor that is equipped with the described Hydrodynamic bearing apparatus of either side in 6 aspects, above-mentioned the 1st aspect to the, the epitrochanterian information-recording disk sheet that is contained in this spindle drive motor and to the record head of this information-recording disk sheet record or playback information.
The 7th recording disc drive unit according to having this structure also can obtain above-mentioned good action in the recording disc drive unit.
Description of drawings
Fig. 1 illustrates the longitudinal section explanatory drawing of the shaft type HDD of the Hydrodynamic bearing apparatus with an embodiment of the present invention with the spindle drive motor outline.
Fig. 2 amplifies to illustrate to be used for the longitudinal section explanatory drawing of HDD shown in Figure 1 with the structure of the conical hydraulic bearing portion of spindle drive motor.
Fig. 3 amplifies to illustrate to be used for the side-looking explanatory drawing of HDD shown in Figure 1 with the axle sleeve of the conical hydraulic bearing portion of spindle drive motor.
Fig. 4 amplifies to illustrate to be used for the longitudinal section explanatory drawing of HDD shown in Figure 1 with another structure of the conical hydraulic bearing portion of spindle drive motor.
Fig. 5 illustrates the longitudinal section explanatory drawing of the shaft type HDD of the Hydrodynamic bearing apparatus with another embodiment of the present invention with the rotating member that comprises axle bush of spindle drive motor.
Fig. 6 be illustrate conical hydraulic bearing portion axle sleeve another mode of execution overlook explanatory drawing.
Fig. 7 illustrates the longitudinal section explanatory drawing of the shaft type HDD of the Hydrodynamic bearing apparatus with another embodiment of the present invention with the spindle drive motor outline.
Fig. 8 is to use the longitudinal section explanatory drawing of schematic configuration example of the recording disc drive unit of the spindle drive motor with Hydrodynamic bearing apparatus of the present invention.
Fig. 9 illustrates the longitudinal section explanatory drawing of the shaft type HDD of the Hydrodynamic bearing apparatus with an embodiment of the present invention with the spindle drive motor outline.
Figure 10 illustrates to be used for shaft type HDD shown in Figure 9 longitudinal section explanatory drawing with the lubricating fluid circulation example of the conical hydraulic bearing portion of spindle drive motor.
Figure 11 illustrates to be used for shaft type HDD shown in Figure 9 longitudinal section explanatory drawing with another circulation example of the lubricating fluid of the conical hydraulic bearing portion of spindle drive motor.
Figure 12 illustrates the longitudinal section explanatory drawing of the shaft type HDD of the Hydrodynamic bearing apparatus with another embodiment of the present invention with the spindle drive motor outline.
Figure 13 illustrates the longitudinal section explanatory drawing of the shaft type HDD of the Hydrodynamic bearing apparatus with another embodiment of the present invention with the spindle drive motor outline.
Figure 14 illustrates the longitudinal section explanatory drawing of the shaft type HDD of the Hydrodynamic bearing apparatus with another embodiment of the present invention with the spindle drive motor outline.
Figure 15 illustrates the longitudinal section explanatory drawing of the shaft type HDD of the Hydrodynamic bearing apparatus with another embodiment of the present invention with the spindle drive motor outline.
Figure 16 illustrates the longitudinal section explanatory drawing of the shaft type HDD of the Hydrodynamic bearing apparatus with another embodiment of the present invention with the spindle drive motor outline.
Figure 17 illustrates the longitudinal section explanatory drawing of the shaft type HDD of the Hydrodynamic bearing apparatus with an embodiment of the present invention with the spindle drive motor outline.
Figure 18 amplifies the longitudinal section explanatory drawing of HDD shown in Figure 17 with the hydraulic bearing portion in the spindle drive motor is shown.
Figure 19 is the outstanding longitudinal section explanatory drawing that the skewed body of axle sleeve inner circle wall face is shown, and (c) is this figure of existing device, the (a) and (b) except that (c) with (d) be depicted as the application the embodiments of the present invention to (i).
Figure 20 is the line chart that the lubricating fluid pressure distribution in the bearing space is shown.
Figure 21 is the schematic illustration that the dynamic pressure generation groove structure of another embodiment of the present invention is shown.
Figure 22 is the schematic illustration that the dynamic pressure generation groove structure of another embodiment of the present invention is shown.
Figure 23 is the longitudinal section explanatory drawing that the Hydrodynamic bearing apparatus that an example developed in the past is shown.
Figure 24 is the longitudinal section explanatory drawing that the imbalance in the Hydrodynamic bearing apparatus of an illustration 23 is shown.
Embodiment
Below, describe embodiments of the present invention with reference to the accompanying drawings in detail.Before this, explanation earlier has the outline that the hard disk drive (HDD) of using Hydrodynamic bearing apparatus of the present invention is used spindle drive motor.
The general structure of rotating shaft shown in Figure 1/external rotor type spindle drive motor comprise as the stator pack 10 of fixed side member and install with respect to this stator pack from the upside shown in the figure, as the rotor set 20 of rotary side member.
Use in the center hole 13a at the bearing of above-mentioned axle sleeve 13, insert axle bush 21, it is rotated freely around rotary middle spindle X as the shaft component of the above-mentioned rotor set 20 of component part.The axle bush 21 of present embodiment forms with the corresponding roughly cone shape stainless steel of center hole 13a by constituting with the bearing of above-mentioned axle sleeve 13.Then, the bearing in the above-mentioned axle sleeve 13 forms roughly cone shape inclination dynamic pressure face with the inner peripheral surface of center hole 13a, and the outer circumferential face of above-mentioned axle bush 21 also forms identical roughly cone shape inclination dynamic pressure face simultaneously.The ring-type pit as the oil storage part of concavity is set down on the inclination dynamic pressure face of above-mentioned axle sleeve 13, and it is banded that its substantial middle portion is constituted.
The opposed part of these two inclination dynamic pressure faces forms the inclination bearing space that is made of micro-gap, and in should the inclination bearing space, leaves appropriate intervals in axially (along dynamic pressure face direction) and forms the coniform hydraulic bearing CB of portion in 2 places, CB.Specifically, the inclination bearing space of forming across several microns gaps, the inclination dynamic pressure that constitutes the inclination dynamic pressure face of axle sleeve 13 sides of each coniform hydraulic bearing CB of portion and axle bush 21 sides in the face of putting configuration, and is filled for example lubricating fluid such as ester class or polyalphaolefin class lubricating oil continuously in the bearing space that comprises this inclination bearing space.
At this moment, the structure of formation is to utilize cover the opening portion that 13b seals the lower end shown in the figure that is arranged on above-mentioned axle sleeve 13, utilizes this lid 13b not allow the lubricating fluid in above-mentioned each coniform hydraulic bearing portion escape to the outside.
Again, the structure that forms is also at least one side of two inclination dynamic pressure faces of above-mentioned axle sleeve 13 and axle bush 21, following concavity is provided with the dynamic pressure generation device that abridged among the figure for example has herringbone shape groove structure, and make its vertically (along dynamic pressure face direction) be divided into 2 parts, when thereby rotation drives above-mentioned axle bush 21, utilize each dynamic pressure to produce and lubricating fluid is pressurizeed, make it produce kinetic pressure with the pumping action of groove.The kinetic pressure of this lubricating fluid makes above-mentioned axle bush 21 float relatively toward radial and axial from axle sleeve 13 sides, keeps this axle bush with contactless state, thus the rotation hub body 22 that rotation is supported above-mentioned axle bush 21 freely and formed one or be fixed as one with this axle bush 21.
Like this, being produced by dynamic pressure should be from the open-ended outside that flows out at the axial two end part of the inclination bearing space that comprises above-mentioned each coniform hydraulic bearing CB of portion with the lubricating fluid after the groove pressurization, but make this lubricating fluid that flows out toward the outside by run through the circulation port 13c that is provided with in the body of above-mentioned axle sleeve 13 with heeling condition on the structure, return in the above-mentioned former coniform hydraulic bearing CB of portion.Promptly, 13c disposes like this this circulation port, the opening of lower end side shown in its figure is out in the inner space of above-mentioned lid 13b, simultaneously the opening of its upper end side is opened between the upper-end surface shown in the figure of above-mentioned axle sleeve 13 (being above-mentioned inclination bearing space) and hereinafter described fluid pressurization device 13e.
On the other hand, make the rotation hub body 22 that constitutes rotor set 20 with above-mentioned axle bush 21 form cup-shapeds, so that various carrier discs such as disk can be installed, and the member that utilization and above-mentioned axle bush 21 are integrated forms this hub body.
Above-mentioned rotation hub body 22 has the annular body 22a that is used to constitute rotor part at its peripheral part, inner peripheral surface side at this annular body 22a installs and fixes the cylindric rotor magnet 22b that applies the NS alternating magnetization on the circumferencial direction at regular intervals simultaneously, thereby constitutes rotor part.Near the configuration of the outer circumferential face of said stator core part 15, make itself and this outer circumferential face ring-type opposed above-mentioned rotor magnet 22b.
The lower axial end face of above-mentioned rotor magnet 22b forms axially relative position relation with the magnetic sheet 16 that is contained in above-mentioned pedestal 11 sides, utilize the magnetic attraction between these two member 22b and 16, whole above-mentioned rotation hub body 22 is inhaled toward axial, thereby formed the structure that can obtain to stablize rotation status.
Again, as shown in Figure 2, the lower end surface of the above-mentioned rotation hub body 22 that the upper-end surface that disposes above-mentioned axle sleeve 13 and outer circumferential side in the big part of the basic side diameter of above-mentioned axle bush 21 extend, make it opposed with axially close state, and between the lower end surface of the upper-end surface of this axle sleeve 13 and rotation hub body 22, form from the axial opposed gap AS of the open-ended continuity of the upper end side (being outer circumferential side) of above-mentioned inclination bearing space, it is extended along the radial direction that is approximately perpendicular to above-mentioned running shaft X.And, curve approximate right angle toward below and at axially extended radial clearance RS in the open-ended continuous formation of the outer circumferential side of this axial opposed gap AS.
Make the anti-avulsion retaining edge 13d of portion of the outermost perimembranous that forms the flange shape upper end part that is arranged on above-mentioned axle sleeve 13 projectedly outer circumferential face, with allow above-mentioned rotation hub body 22 central side lower end surfaces toward lower side with the inner peripheral surface that covers this anti-avulsion retaining edge 13d of portion from outer circumferential side and become the stepped ring center base portion 22c of setting projectedly radially close, thereby form above-mentioned radial clearance RS.And the open-ended connection of the lower end side of this radial clearance RS utilizes the compound fluid sealed department CS of capillary force and these two kinds of power of rotary centrifugal force, and it is extended toward lower side.
Utilize above-mentioned axle sleeve 13 outer circumferential side surface and 13 opposed at foreign side's side radially and this axle sleeve, as interior all side wall surfaces of the ring bodies member 25 of drop-proof component, form interior all inclination skew wall faces and the outer circumferential side inclined wall of this compound fluid sealed department CS respectively.The annular component of ring-type forms above-mentioned ring bodies member 25 by forming roughly, utilizes the fixing tabular hub mounted portion 25a that forms the outer circumferential side position of this annular body 25 of the fixing part 22d that is located at above-mentioned rotation hub body 22.
As mentioned above, the upper end part of above-mentioned axle sleeve 13 is provided with toward foreign side's side radially and bloats and the anti-avulsion retaining edge 13d of portion that protrudes, but disposes the part of this anti-avulsion retaining edge 13d of portion, makes the upper surface side of main part 25b of itself and above-mentioned annular body 25 axially opposed.And, these two member 13d and 25b are configured to and can prevent that above-mentioned rotation hub body 22 is toward the structure that axially comes off thereby form in axial butt joint.That is to say, be located at the anti-avulsion retaining edge 13d of portion of above-mentioned axle sleeve 13, it is the hub mounted portion 25a of the above-mentioned ring bodies member 25 of configuration on foreign side's side radially, and it is relative to be configured to the periphery wall that the inner circle wall face of the hub mounted portion 25a of above-mentioned ring bodies member 25 keeps off the edge 13d of portion from foreign side's side radially and above-mentioned anti-avulsion.
Again, as mentioned above, be positioned on inclination bearing space outer circumferential side open-ended, across axially opposed radially AS and diametrically contraposition gap RS, form compound fluid sealed department CS continuously, and the lubricating fluid in the above-mentioned inclination bearing space is filled into continuously the inside of these continuous spaces.At this moment, as shown in Figure 3, form on the outer circumferential face of the anti-avulsion retaining edge 13d of portion of axle sleeve 13 of above-mentioned radial clearance RS and form fluid pressurization device 13e, the direction that the private side toward the inclination bearing space is pressed into above-mentioned lubricating fluid is pressurizeed.
The fluid pressurization device 13e of present embodiment is formed by a plurality of spiral grooves that are arranged in ring-type, and is configured in above-mentioned inclination bearing space and prevents that the interior lubricating fluid of this inclination bearing space from flowing out to the part between the outside CS of fluid-tight portion.This fluid pressurization device 13e pressurizes to lubricating fluid toward upper side shown in the arrow V among Fig. 2, thereby formed structure is carried out pressurization to above-mentioned inclination bearing space on suction lubrication flow side.
At this moment, in the present embodiment, the flow direction of the lubricating fluid in the above-mentioned inclination bearing space is set at the below shown in the figure, but also can be set at the top as shown in Figure 4.
Like this, in the present embodiment, be pressed into the lubricating fluid that utilizes after fluid pressurization device 13e pressurizes from the outer circumferential side of inclination bearing space toward private side, thereby no matter the angle of release of inclination dynamic pressure face how, makes the lubricating fluid in the inclination bearing space produce kinetic pressure well.
And shown in the arrow W among Fig. 2, the lubricating fluid of wanting to escape to foreign side from the outer circumferential side opening portion of above-mentioned inclination bearing space because of rotary centrifugal force is pressed into inclination bearing space side, obtains stable the maintenance.That is, in the present embodiment, fluid pressurization device 13e is configured between inclination bearing space and the CS of fluid-tight portion, thus this fluid pressurization device 13e well the lubricating fluid of auxiliary fluid sealed department CS keep function.
Again, the fluid pressurization device 13e of present embodiment is formed by a plurality of spiral grooves that are arranged in ring-type, thereby manufacturing structure is simple and easy and have a fluid pressurization device 13e of good pressurization function expeditiously.
Then, in the mode of execution of Fig. 5, on the inner peripheral surface of the ring center base portion 22c of the rotation hub body 22 that forms above-mentioned diametrically contraposition gap RS, fluid pressurization device 13f is set.This fluid pressurization device 13f is formed by a plurality of spiral grooves that are arranged in ring-type, be pressed at private side on the direction of lubricating fluid and pressurize toward the inclination bearing space, and lubricating fluid is pressurizeed toward upper side, thereby the pressurization that formed structure sucks described inclination bearing space.
In this mode of execution, also can obtain the action effect identical with above-mentioned mode of execution.
On the other hand, in the mode of execution shown in Figure 6, in the upper-end surface of the anti-avulsion of the axle sleeve 13 retaining edge 13d of portion, promptly the end face that forms aforesaid axial opposed gap AS forms fluid pressurization device 13g, on the direction of going into toward the side pressure of inclination bearing interior volume lubricating fluid is pressurizeed.The fluid pressurization device 13g of present embodiment is also formed by a plurality of spiral grooves that are arranged in ring-type, toward central side lubricating fluid pressurizeed, thus the pressurization that formed structure sucks above-mentioned inclination bearing space.
In this mode of execution, also can obtain the action effect identical, but above-mentioned fluid pressurization device 13g also can be formed on rotation hub body 22 sides that form axial opposed gap AS with above-mentioned mode of execution.
Then, in shown in Figure 7, the mode of execution, ring-type anti-avulsion circle 21a is fixed on the fore-end of the lower end side of axle bush 21 to the composition mark same-sign corresponding with the hard disk drive (HDD) of above-mentioned Fig. 1.This anti-avulsion circle 21a is configured in down concavity and is arranged in the receipts dress 13h of portion of lower end side central part of axle sleeve 13, utilizes this configuration relation, has the function that rotor set of preventing 20 breaks away from.In this mode of execution, also can adopt and above-mentioned fluid pressurization device 13e, 13f, the same structure of 13g, and can obtain the action effect identical with them.
Spindle drive motor in each mode of execution like this for example is installed in the inner use of hard disk drive shown in Figure 8 (HDD).Promptly, as shown in Figure 8, the spindle drive motor M that will have the conical Hydrodynamic bearing apparatus of the respective embodiments described above is fixed on the mainboard 100a that constitutes sealing shape housing 100 and goes up use, and utilization and the sealing cover 100b that above-mentioned mainboard 100a cooperates, make the inner space of the housing 100 that comprises this spindle drive motor M form better purifying space 100c.The rotation hub body (with reference to the symbol among the figure 1 22) of above-mentioned spindle drive motor M is gone up information-recording disk sheets 101 such as hard disk is installed, and utilizes simultaneously by the fixing clamping element 103 of 102 pairs of above-mentioned rotation hub bodies of screw, makes above-mentioned information-recording disk sheet 101 keep motionless state.
Then, detailed description can suitably keep tilting between the bearing space two end part pressure difference and can be convenient and obtain the Hydrodynamic bearing apparatus of the suitable relative floatation volume between fixed component and the rotating member and recording disc drive unit reliably with this device.
Below, describe embodiments of the present invention with reference to the accompanying drawings in detail.Before this, at first explanation has the outline that the hard disk drive (HDD) of using conical Hydrodynamic bearing apparatus of the present invention is used spindle drive motor.
Rotating shaft shown in Figure 9/formed general structure of external rotor type spindle drive motor comprise as the stator pack 10 of fixed side member and 10 that install from the upside shown in the figure with respect to this stator pack, as the rotor set 20 of rotary side member.
The spindle drive motor shown in Figure 9 pair composition identical with the mode of execution shown in above-mentioned Fig. 1 etc. omits explanation herein with identical symbolic representation.
Mode of execution shown in Figure 9 forms does not have fluid pressurization device 13e, the 13f shown in Fig. 1 etc., the structure of 13g.
Rotating shaft shown in Figure 9/external rotor type spindle drive motor, though wherein produce with open-ended the flow out to outside of the lubricating fluid after the groove pressurization from the axial two end part of the inclination bearing space that comprises above-mentioned each coniform hydraulic bearing CB of portion by above-mentioned dynamic pressure, but form and this to be flow through with the heeling condition straight line shape toward outside lubricating fluid that flows out run through in the body of above-mentioned axle sleeve 13 and the circulation port 13c of setting, and return the interior circulation path of for example above-mentioned former coniform hydraulic bearing CB of portion, thereby formed structure is eliminated the pressure difference that produces between the two end part of above-mentioned inclination bearing space.The structure of this circulation port 13c hereinafter will be described.
As indicated above, be configured to the upper surface side of the main part 25b of above-mentioned ring bodies member 25 part of the anti-avulsion of the above-mentioned axle sleeve 13 retaining edge 13d of portion axially opposed.And these two member 13d and 25b be configured to and can axially dock, and axially coming off thereby formed structure prevents above-mentioned rotation hub body 22.
On the other hand, the circulation port 13c that is located at above-mentioned axle sleeve 13 is arranged to extend along the true dip direction almost parallel ground of above-mentioned inclination bearing space, the lower end side opening portion of this circulation port 13c is configured at the lower end surface of above-mentioned axle sleeve 13 13i opening, and faces the inner space of above-mentioned lid 13b.In addition, the upper end side opening portion of above-mentioned circulation port 13c is configured at the upper-end surface of above-mentioned axle sleeve 13 opening, and faces the outer side space AS of above-mentioned inclination bearing space.So, by circulation port 13c is set like this, form the circulation path of the lubricating fluid between this circulation port 13c and the above-mentioned inclination bearing space, for example such shown in each arrow among Figure 10 or Figure 11, be lubricated the circulation of fluid.
At this moment, above-mentioned circulation port 13c is as indicated above, extend with the true dip direction almost parallel ground of inclination bearing space, and straight line shape runs through above-mentioned axle sleeve 13, on axial two end faces of this axle sleeve 13 pair of openings is arranged.And in the pair of openings of this circulation port 13c, the lower end surface 13i that makes the above-mentioned axle sleeve 13 that is provided with the lower end side opening is along extending and form with respect to the direction that runs through the direction approximate vertical of above-mentioned circulation port 13c.That is, the opening of the lower end side of above-mentioned circulation port 13c is set, with the lower end surface 13i of above-mentioned axle sleeve 13 as the vertical openings face.Constitute the lower end surface 13i of this axle sleeve 13 by the roughly mortar shape concave surface of the inclination dynamic pressure face that is approximately perpendicular to the inner peripheral surface that is formed on this axle sleeve 13, and above-mentioned circulation port 13c the direction of approximate vertical to this roughly the lower end surface 13i of the axle sleeve 13 formed of mortar shape concave surface intersect, form the circular opening at this cross section.
Like this, unbalanced in the present embodiment corresponding to the lubricating fluid pressure that the two end part of inclination bearing space produce, lubricating fluid is flow through comprise the circulation path of this inclination bearing space and circulation port 13c, thereby it is unbalanced to eliminate pressure.Therefore, the lubricating fluid pressure at above-mentioned inclination bearing space two end part is kept in balance, to keep suitable kinetic pressure.
When forming above-mentioned circulation port 13c, if instrument is pressed close to from the lower end surface 13i of the above-mentioned axle sleeve 13 of the perforation direction that is approximately perpendicular to this circulation port 13c, form above-mentioned circulation port, then the position of instrument does not have deviation, can highi degree of accuracy form circulation port 13c, simultaneously owing to making the instrument load stress even, so can prolong tool life.
In the present embodiment,, that is to say, this hole is located at axle sleeve 13 sides because above-mentioned circulation port 13c is fixed component, thus stable and lubricating fluid is flowed by the circulation path that comprises circulation port 13c.
In the present embodiment, also make circulation port 13c extend and form with respect to inclination dynamic pressure face almost parallel ground, thereby the radial thickness to the joining portion of pedestal 11 that the axle sleeve 13 of circulation port 13c is set produces surplus, and the external diameter at the joining portion of axle sleeve 13 is reduced, and can seek miniaturization.And, because this reduces to make the corresponding increasing of the installable volume of coil of above-mentioned motor part etc., can improve and rotate drive performance.
On the other hand, in the mode of execution shown in Figure 12 of composition that will be identical with identical symbolic representation with above-mentioned mode of execution, the circulation port 43c that forms lubricating fluid circulation path is set, runs through and extend but make this circulation port 43c form axially (above-below direction shown in the figure).And, not in the mode of execution, forms lower end surface 13j1 and upper-end surface 13j2 shown in the figure of axle sleeve 13 by the simple tabular surface that radially extends, and above-mentioned circulation port 43c is set, with lower end surface 13j1 shown in the figure of the axle sleeve 13 of this simple tabular surface formation and upper-end surface 13j2 as the vertical openings face.That is, on these lower end surface 13j1 and upper-end surface 13j2, on the direction of approximate vertical, form the opening of circular across respectively with above-mentioned circulation port 43c as the above-mentioned axle sleeve 13 of vertical openings face.In the present embodiment, also can obtain the action effect roughly the same with above-mentioned mode of execution.
Again, in the mode of execution shown in Figure 13 of composition that will be identical with identical symbolic representation, form long and short 2 kinds of circulation port 53c1,53c2, make its axial (above-below direction shown in the figure) run through axle sleeve 13 and extension with above-mentioned mode of execution.And, long circulation port 53c1 is set, its formation is axially run through, the both ends of the surface up and down of axle sleeve 13 are interconnected, and with the lower end surface 13j1 of above-mentioned axle sleeve 13 and upper-end surface 13j2 as the vertical openings face, make these vertical openings faces have opening respectively.Different therewith is, short circulation port 53c2 is set, and it is partly extended out from the oil storage between the 2 coniform hydraulic bearing CB of portion, the CB, and with the lower end surface 13j1 of above-mentioned axle sleeve 13 as the vertical openings face, make this vertical openings face 13j1 have opening.
In this mode of execution, basically also can obtain the action effect roughly the same with above-mentioned mode of execution, but in the present embodiment, respectively the coniform hydraulic bearing CB of portion in 2 places, CB are formed the circulation path, each the coniform hydraulic bearing CB of portion, CB keep the lubricating fluid isostasy well, thereby, can correspond respectively to the state of the coniform hydraulic bearing CB of portion in 2 places, CB, obtain the action effect in the above-mentioned mode of execution.
In the mode of execution shown in Figure 14 of composition that will be identical with identical symbolic representation, make circulation port 63c with respect to a coniform hydraulic bearing CB of portion form axially (above-below direction shown in the figure) and run through and extend with above-mentioned mode of execution again.That is, this circulation port 63c is set, make its from the oil storage between the 2 coniform hydraulic bearing CB of portion, CB part toward extending axially, and with the lower end surface 13j1 of above-mentioned axle sleeve 13 as the vertical openings face, make this vertical openings mask that opening be arranged.Thereby constitute the equilibrium that to keep-up pressure to the coniform hydraulic bearing CB of portion of downside shown in the figure among the coniform hydraulic bearing CB of portion in above-mentioned 2 places, the CB.In this mode of execution, the coniform hydraulic bearing CB of portion obtains and the roughly the same action effect of above-mentioned mode of execution to 1 place (downside shown in the figure).
On the other hand, in the mode of execution shown in Figure 15 of composition that will be identical with identical symbolic representation with above-mentioned mode of execution, to the coniform hydraulic bearing CB of portion in 2 places, CB are subsidiary respectively 2 kinds of circulation port 73c1,73c2 are set, to form the circulation path, the lubricating fluid of the coniform hydraulic bearing CB of portion in 2 places, CB is circulated independently of each other.
Promptly, circulation port 73c1 among the figure shown in the right side forms the circulation path to the coniform hydraulic bearing CB of portion of downside among the figure, this circulation path is from the oil storage part between the 2 coniform hydraulic bearing CB of portion, the CB, (above-below direction among the figure) runs through axle sleeve 13 inside toward the downside among the figure vertically, extend, and with the lower end surface 13j1 of above-mentioned axle sleeve 13 as the vertical openings face, make it have opening.Different therewith is, the circulation port 73c2 shown in the left side forms the circulation path to the coniform hydraulic bearing CB of portion of upside among the figure among the figure, it from the oil storage between the 2 coniform hydraulic bearing CB of portion, CB part toward figure in oblique upper run through axle sleeve 13 inside, extend.
At this moment, set the direction that runs through of above-mentioned circulation port 73c2, the inclination concave surface 13k that makes upper-end surface shown in the figure that is located at above-mentioned axle sleeve 13 is as the vertical openings face, and this inclination concave surface 13k that is located on the upper-end surface of axle sleeve 13 is approximately perpendicular to above-mentioned circulation port 73c, extends.Promptly, on the upper-end surface of above-mentioned axle sleeve 13, form the taper inclination concave surface 13k of the perforation direction that is approximately perpendicular to above-mentioned circulation port 73c, and above-mentioned circulation port 73c2 intersects with this taper inclination concave surface 13k in the direction of approximate vertical, forms the opening of circular at this cross section.
In this mode of execution, also can obtain the action effect roughly the same with above-mentioned mode of execution, but in the present embodiment, respectively the coniform hydraulic bearing CB of portion in 2 places, CB are formed the circulation path that comprises circulation port 73c1,73c2 in mode fully independently, thereby the fine independently respectively isostasy of keeping lubricating fluid of each the coniform hydraulic bearing CB of portion, CB, can very stably obtain the action effect of above-mentioned mode of execution corresponding to the coniform hydraulic bearing CB of portion in 2 places, CB state separately.
On the other hand, mode of execution shown in Figure 16 is that the present invention is used for fixing axle/external rotor type spindle drive motor.This stationary axle/formed general structure of external rotor type spindle drive motor comprise as the stator pack 80 of fixed side member and 80 that install from upside shown in the figure with respect to this stator pack, as the rotor set 90 of rotary side member.
In the above-mentioned axle bush 82, insert the axle sleeve 91 of the rotor set 90 that forms hollow shape, it is rotated freely around rotary middle spindle X.This axle sleeve 91 is made of copper class materials such as phosphor bronzes for easy to process, and forms the roughly coniform bearing center hole 91a of the open and axial the other end (upper end among the figure) sealing of an axial end (lower end among the figure).The bearing of this axle sleeve 91 rotatably inserts the axle bush 82 as above-mentioned shaft component with in the center hole 91a.The bearing of above-mentioned axle sleeve 91 forms roughly cone shape inclination dynamic pressure face with the inner peripheral surface of center hole 91a, and the outer circumferential face of above-mentioned axle bush 82 forms identical roughly cone shape inclination dynamic pressure face simultaneously.On the inclination dynamic pressure face of above-mentioned axle sleeve 91, the annular recess portion as the oil storage part of concavity is set down, make its substantial middle portion form band shape.
The opposed part of these two inclination dynamic pressure faces forms the inclination bearing space that is made of micro-gap, and in should the inclination bearing space, leaves appropriate intervals along inclination dynamic pressure face direction and form the coniform hydraulic bearing CB of portion in 2 places, CB.Specifically, the inclination bearing space of forming across several microns gaps, the inclination dynamic pressure that constitutes the inclination dynamic pressure face of axle sleeve 91 sides of each coniform hydraulic bearing CB of portion and axle bush 82 sides in the face of putting configuration, and is filled for example lubricating fluid such as ester class or polyalphaolefin class lubricating oil continuously in comprising the bearing space BS of this inclination bearing space.At this moment, the structure of formation makes upper end such sealing the as indicated above shown in the figure of above-mentioned axle sleeve 91, thereby the lubricating fluid in above-mentioned each the coniform hydraulic bearing CB of portion, CB does not escape to the outside.
Again, the structure that forms is also at least one side of two inclination dynamic pressure faces of above-mentioned axle sleeve 91 and axle bush 82, following concavity setting for example has the dynamic pressure generation device (omitting among the figure) of herringbone grooves structure, and make it be divided into 2 parts vertically, when thereby rotation drives above-mentioned axle bush 82, utilize each dynamic pressure to produce and lubricating fluid is pressurizeed, make it produce kinetic pressure with the pumping action of groove.Utilize the kinetic pressure of this lubricating fluid, above-mentioned axle sleeve 91 is floated toward radial and axial relatively from axle bush 82 sides, keep this axle sleeve with contactless state, thus the rotation hub body 92 that rotation is supported above-mentioned axle sleeve 91 freely and formed one or be fixed as one with this axle sleeve 91.
Like this, being produced by dynamic pressure should be from the open-ended outside that flows out at the axial two end part of the inclination bearing space that comprises above-mentioned each the coniform hydraulic bearing CB of portion, CB with the lubricating fluid after the groove pressurization, but make this run through the above-mentioned axle bush 82 inner circulation port 82c that are provided with by past true dip direction on the structure, return in the above-mentioned former coniform hydraulic bearing CB of portion toward the outside lubricating fluid that flows out.
Promptly, the end of interior all sides of the circulation port 82c of present embodiment is set, make its along the central passage 82a that forms vertically at the axle center of above-mentioned axle bush 82 axially midway part carry out opening, form the opening of the end of the outer circumferential side that is located at this circulation port 82c simultaneously, make the inclination dynamic pressure face that forms on its outer circumferential face as the vertical openings face, and it is configured in the face of above-mentioned inclination axle bush space above-mentioned axle bush 82.So, by circulation port 82c is set like this, form the lubricating fluid circulation path between this circulation port 82c and the above-mentioned inclination bearing space, be lubricated the circulation of fluid.
Moreover, the open end section of the axle sleeve 91 of lower end side shown in the above-mentioned central passage 82a Closed Graph.
At this moment, set the perforation direction of above-mentioned circulation port 82c, make the inclination dynamic pressure face that forms on the outer circumferential face of above-mentioned axle bush 82 as the vertical openings face, and the inclination dynamic pressure that above-mentioned circulation port 82c forms on the outer circumferential face of the direction of approximate vertical and this axle bush 82 hand-deliver fork forms the opening of circular at this cross section.
On the other hand, making the rotation hub body 92 that constitutes rotor set 90 with above-mentioned axle sleeve 91 form roughly cup-shaped, so that various carrier discs such as disk can be installed, and is one with being pressed into etc. that mechanical connecting device engages with above-mentioned axle sleeve 91.The structure of this rotation hub body 92 is identical with the mode of execution of above-mentioned shaft type of spindle motor, thereby omits explanation.In this stationary axle type spindle drive motor, also obtain the action effect identical with the mode of execution of relevant above-mentioned shaft type of spindle motor.
Fig. 9 uses to hard disk drive (HDD) inside that the spindle drive motor in each mode of execution shown in Figure 16 for example is contained in as shown in Figure 8.That is, as shown in Figure 8, the spindle drive motor M of the conical Hydrodynamic bearing apparatus by will having the respective embodiments described above is fixed on the mainboard 100a that constitutes sealing shape housing 100, uses this motor.Utilize the sealing cover 100b that cooperates with above-mentioned mainboard 100a, form the inner space of the housing 100 that comprises this spindle drive motor M at better purifying space 100d.Go up information recode discs 101 such as hard disk is installed at the rotation hub body (with reference to the symbol among the figure 9 22) of above-mentioned spindle drive motor M, utilize simultaneously by the fixing clamping element 103 of 102 pairs of above-mentioned rotation hub bodies of screw to make above-mentioned information-recording disk sheet 101 keep motionless state.
So far, understand the invention that the inventor finishes specifically according to mode of execution, but the invention is not restricted to above-mentioned mode of execution, can in the scope that does not break away from its main points, do various conversion certainly.
For example, in the respective embodiments described above, be the circulation port 13c that lubricating fluid is set at axle sleeve 13, but to there not being the device of this circulation port, the present invention can use too.
For example, in the respective embodiments described above, be that fixed component is provided with the lubricating fluid circulation port, but also can form circulation port in the rotating member side.
Again, the respective embodiments described above are that the spindle drive motor of hard disk drive (HDD) usefulness is used the present invention, but to other various conical Hydrodynamic bearing apparatus, the present invention is available too.
Then, detailed description can prevent to produce bubble well and can obtain the Hydrodynamic bearing apparatus and the disc drive appts of dynamic pressure characteristic steady in a long-term with easy structure.
Below, describe embodiments of the present invention with reference to the accompanying drawings in detail.Before this, explanation earlier has the outline that the hard disk drive (HDD) of using Hydrodynamic bearing apparatus of the present invention is used spindle drive motor.
Shaft type HDD drive unit shown in Figure 17 with the complete machine of spindle drive motor by forming as the stator pack 210 of fixed component and upside is installed with respect to this stator pack 210 from figure rotor set 220 as rotating member.Wherein stator pack 210 has with screw and adorns the fixed frame 211 of abridged fixed pedestal side in the drawings.For in light weight, this fixed frame 211 is made of the aluminium metalloid material, be arranged at this fixed frame 211 substantial middle part and the inner peripheral surface side of the annular bearings holder 212 that forms in setting, utilize be pressed into or hot jacket will form hollow cylindrical, engage with above-mentioned bearing holder 212 as the axle sleeve 213 of hydraulic bearing member.This axle sleeve 213 is formed by copper class materials such as phosphor bronzes in order to carry out the hole processing of small aperture easily.The periphery attachment face of above-mentioned bearing holder 212 embeds the stator core 214 that the electromagnetic steel sheet lamination is formed, and simultaneously drive coil 215 is wound on each the salient pole portion that is provided with in this stator core 214 respectively.
As shown in figure 18, in the center hole set as the axle sleeve 213 of above-mentioned hydraulic bearing member, the running shaft 221 that constitutes above-mentioned rotor set 220 is inserted in rotation freely.Promptly, the dynamic pressure face diameter that the dynamic pressure face that forms in the inner circle wall portion of above-mentioned axle sleeve 213 is configured to form on the outer circumferential face with above-mentioned running shaft 221 is to opposed, and in the bearing space part that its micro-gap is formed, axial sky is opened appropriate intervals and is constituted 2 RB of place radial dynamic pressure bearing portion, RB.Specifically, the dynamic pressure face of axle sleeve 213 sides of the above-mentioned radial dynamic pressure bearing RB of portion and the dynamic pressure face of running shaft 221 sides are configured to: across several microns micro-gaps and opposed circle-shapedly.In the bearing space that this micro-gap is formed, inject or have lubricating fluids such as lubricant oil and magnetic fluid, make it continuous at axial direction.
The structure that forms is also at least one side of two dynamic pressure faces of above-mentioned axle sleeve 213 and running shaft 221, the lowland setting has the radial dynamic pressure generation groove of appropriate configuration under the ring-type, and make this groove axially be divided into 2 parts, thereby during rotation, utilizing this radial dynamic pressure to produce with the pumping action of groove pressurizes to abridged lubricating fluid among the figure, to produce dynamic pressure, and make hereinafter described rotation hub body 222 with above-mentioned running shaft 221 by the dynamic pressure of this lubricating fluid, with respect to above-mentioned axle sleeve 13, radially be subjected to the axle supporting with contactless state.
At this moment, for example "＜" font and the ring-type aggregate of the tortuous groove of the herringbone shape that forms form the above-mentioned radial dynamic pressure that is located at each radial dynamic pressure bearing RB of portion and produce and use groove by shown in Figure 24 constituting roughly, but forming on the structure will " suitable position, the summit of the middle body of＜" font constitutes the groove shape of substantial axial symmetry as the center with this.The radial dynamic pressure that utilization has this symmetrical channels shape produces the pumping action of using groove, shown in the arrow among for example above-mentioned Figure 24, will form the axially equilibrium state of symmetry.
Therefore, in the design, balanced pumping action because of above-mentioned each radial dynamic pressure bearing RB of portion, can not be pressed into lubricating fluid toward an axial side, but when implementing to make, because the gap size of above-mentioned each radial dynamic pressure bearing RB of portion and dynamic pressure produce shape (flute length) with groove and wait and produce foozle etc., the axial unbalanced shape of formation often, this often makes the pumping action of each radial dynamic pressure bearing RB of portion become imbalance.Therefore, in the present embodiment, above-mentioned axle sleeve 213 is formed many pressure adjustment split channel BP, axially running through.Hereinafter will elaborate these pressure adjustment split channel BP.
On the other hand, the rotation hub body 222 that constitutes rotor set 220 with above-mentioned running shaft 221 is made of the member of the roughly cup-shaped that ferrite class stainless steel is formed, and be pressed into or hot jacket upper end portion shown in the figure of the conjugate foramen 222a that is located at these rotation hub body 222 cores and above-mentioned running shaft 221 is engaged is one.This rotation hub body 222 has the roughly cylindric body 222b of recording medium disc such as in peripheral part installation diagram abridged disk, also have simultaneously from this body 222b toward foreign side radially stretch out, with disc placement section 222c at axial direction record support medium disc, and utilize pressing force that above-mentioned recording medium disc is fixed by the clamping element (not shown) that the top covers from figure top from figure of being fixed by screw.
At the inner circle wall face of the body 222b of above-mentioned rotation hub body 222 ring-type drive magnet 222d is installed.Dispose this annular drive magnet 222d, make its internal surface and said stator iron core 214 each salient pole outer circumference side edge face near and spherical opposed, the lower axial end face of this annular drive magnet 222d constitutes axially relative position relation with the magnetic sheet 223 that is contained in said fixing framework 221 sides simultaneously, thereby the structure that forms is the magnetic attraction that utilizes between these two member 222d and 223, above-mentioned whole rotation hub body 222 is attracted vertically, can obtain to stablize rotation status.
The structure that forms is also utilized the opening portion that cover on the lower end side shown in the figure that the 213a sealing is located at above-mentioned axle sleeve 213, makes the interior lubricating fluid of above-mentioned each radial dynamic pressure bearing RB of portion not escape to the outside.
It is opposed also the lower end surface shown in the figure of the upper-end surface shown in the figure of above-mentioned axle sleeve 213 and above-mentioned rotation hub body 222 central sides part to be configured to close vertically state, and formation begins continuous bearing space from the above-mentioned radial dynamic pressure bearing RB of portion in the axial opposed district between the lower end surface of the upper-end surface that makes these axle sleeves 213 and rotation hub body 222.Then, begin continuous bearing space at this from the radial dynamic pressure bearing RB of portion the SB of axial hydrodynamic bearing portion is set.That is, at least one square spirality or lambdoid axial hydrodynamic in two opposed dynamic pressure faces 213 that constitute above-mentioned axial opposed district and 222 produce groove, become the SB of axial hydrodynamic bearing portion thereby comprise the axial opposed part that this axial hydrodynamic produces groove.
With constitute upper-end surface side shown in the figure of axle sleeve 213 of this axial hydrodynamic bearing SB of portion dynamic pressure face and with its near the micro-gap configuration of the dynamic pressure face of lower end surface side shown in figure of opposed rotation hub body 222 across several microns, opposed vertically, lubricating fluids such as oil and magnetic fluid are filled into continuously in the bearing space of this micro-gap formation from the described radial dynamic pressure bearing RB of portion simultaneously, thereby the structure that forms when rotated, utilize above-mentioned axial hydrodynamic to produce the pumping action of groove, to above-mentioned lubricating fluid pressurization, to produce dynamic pressure, and utilize the dynamic pressure of this lubricating fluid, with the contactless state that axially floats, make above-mentioned running shaft 221 and rotation hub body 222 be subjected to the axle supporting.
The above-mentioned axial hydrodynamic bearing SB of portion of present embodiment is configured in the part that is equivalent to the most peripheral side in the axial opposed district between the lower end surface of the upper-end surface of above-mentioned axle sleeve 213 and rotation hub body 222, thereby formed structure makes its double as aspirator, will comprise the lubricating fluid inwardly side's pressurization toward the footpath that exists in the whole axial opposed district of the above-mentioned axial hydrodynamic bearing SB of portion in the part of the most peripheral side in this axial opposed district.
Divide the fluid-tight portion that capillary seal portion 224 forms by most peripheral wall as the axle sleeve 213 of above-mentioned hydraulic bearing member again.Promptly, this capillary seal portion 224 as fluid-tight portion is set, make it connect the axial opposed district that comprises the above-mentioned axial hydrodynamic bearing SB of portion from foreign side's side radially, and with its periphery wall that is divided in above-mentioned axle sleeve 213 and formation diametrically contraposition between the inner circle wall face periphery wall of this axle sleeve 213, as the back-pressure plate 225 of drop-proof component.Above-mentioned back-pressure plate 225 is made up of the annular component that is fixed in the lip part 222e that is located at above-mentioned rotation hub body 222, and the gap between the periphery wall of the inner circle wall face of this back-pressure plate 225 and above-mentioned axle sleeve 213 is enlarged continuously toward below shown in the figure, thereby form above-mentioned capillary seal portion 224, make it constitute the taper space, the lubricating fluid in the above-mentioned axial hydrodynamic bearing SB of portion is filled into this capillary seal portion 224 continuously.
At this moment, the anti-avulsion retaining edge 213b of portion is set in upper end portion shown in the figure of above-mentioned axle sleeve 213, its radius vector is bloated to foreign side, and the part of this anti-avulsion retaining edge 213b of portion is configured to axially opposed with the part of above-mentioned back-pressure plate 225.So the structure of formation is to utilize these two member 213b and 225 to prevent that above-mentioned rotation hub body 222 from axially coming off.
Here, separate with the above-mentioned bearing space that comprises each radial dynamic pressure bearing RB of portion, form many pressure adjustment split channel BP that are located at above-mentioned axle sleeve 213 in addition, make it axially run through above-mentioned axle sleeve 213, and on axial two end faces of above-mentioned axle sleeve 213, have opening portion BP1, BP2 respectively.And, be configured to bearing space inside opening between the radial dynamic pressure bearing RB of portion of upside shown in the figure of above-mentioned axial hydrodynamic bearing SB of portion and the contiguous SB of this axial hydrodynamic bearing portion configuration with being configured in the opening portion BP2 on the upside end face shown in the figure of above-mentioned axle sleeve 213 in these opening portions.
That is, this pressure adjustment with the opening portion BP2 of upside shown in the figure of split channel BP than the above-mentioned axial hydrodynamic bearing SB of portion by form on the position of radially inner side axially spaced-apart greater than the expansion clearance portion LS opening of the above-mentioned axial hydrodynamic bearing SB of portion.Therefore, make above-mentioned pressure adjustment, can be lubricated flowing of fluid well with forming good connected state between split channel BP and the bearing space.
On the other hand, dispose the opening portion BP2 on the downside end face shown in the figure that is configured in axle sleeve 213 among two opening portion BP1, the BP2 of above-mentioned pressure adjustment with split channel BP, make its toward lower end surface shown in the figure of this axle sleeve 213 with and the space opening in the axial outside that is divided into of above-mentioned lid 213a.
Except that this pressure adjustment being set with the split channel BP, present embodiment also at the bearing space that is equivalent to the part between above-mentioned 2 RB of place radial dynamic pressure bearing portion, the RB, is provided with the OS of fluid storage portion.The OS of this fluid storage portion is formed by the clearance space that radially enlarges the bearing space gained that constitutes the above-mentioned radial dynamic pressure bearing RB of portion, stores the lubricating fluid in the injection bearing space in the above-mentioned fluid storage OS of portion.And formed structure is to the lubricating fluid pressurization of above-mentioned 2 RB of place radial dynamic pressure bearing portion, RB, and the plus-pressure that the lubricating fluid among the OS of this fluid storage portion is formed is the above malleation of barometric pressure.
Particularly, form to constitute the bearing space of at least one side among above-mentioned 2 RB of place radial dynamic pressure bearing portion, the RB, make its formation that the gap size of this bearing space is enlarged continuously or keeps identical taper space or parallel space continuously toward the above-mentioned fluid storage OS of portion.This bearing space structure, inner circle wall face that can be by making above-mentioned axle sleeve 213 are along central axes or extend obliquely and form, and periphery wall that also can be by making running shaft 21 is along central axes or extend obliquely and form.
For example, in the mode of execution shown in Figure 19 (a), form and constitute the bearing space of the radial dynamic pressure bearing RB of portion of top shown in the figure among 2 RB of place radial dynamic pressure bearing portion, the RB, the taper space that its formation is dwindled the past above-mentioned fluid storage OS of portion of the gap size of this bearing space continuously, but the bearing space of the radial dynamic pressure bearing RB of portion of below shown in the formation pie graph, the taper space that its formation is enlarged the past above-mentioned fluid storage OS of portion of the gap size of this bearing space continuously.
In the mode of execution shown in Figure 19 (b), form and constitute the bearing space of the radial dynamic pressure bearing RB of portion of top shown in the figure among 2 RB of place radial dynamic pressure bearing portion, the RB, the taper space that its formation is dwindled the past above-mentioned fluid storage OS of portion of the gap size of this bearing space continuously, but the bearing space of the radial dynamic pressure bearing RB of portion of below shown in the formation pie graph makes its formation that the gap size of this bearing space is kept roughly the same parallel space continuously toward the above-mentioned fluid storage OS of portion.
In the mode of execution shown in Figure 19 (d), form and constitute the bearing space of the radial dynamic pressure bearing RB of portion of top shown in the figure among 2 RB of place radial dynamic pressure bearing portion, the RB, make its formation that the gap size of this bearing space is kept roughly the same parallel space continuously toward the above-mentioned fluid storage OS of portion, but the bearing space of the radial dynamic pressure bearing RB of portion of below shown in the formation pie graph, the taper space that its formation is enlarged the past above-mentioned fluid storage OS of portion of the gap size of this bearing space continuously.
In the mode of execution shown in Figure 19 (e), form 2 RB of place radial dynamic pressure bearing portion, both bearing spaces of RB, make its gap size that all constitutes this bearing space keep roughly the same parallel space continuously toward the above-mentioned fluid storage OS of portion.
In the mode of execution shown in Figure 19 (f), form and constitute the bearing space of the radial dynamic pressure bearing RB of portion of below shown in the figure among 2 RB of place radial dynamic pressure bearing portion, the RB, the taper space that its formation is dwindled the past above-mentioned fluid storage OS of portion of the gap size of this bearing space continuously, but the bearing space of the radial dynamic pressure bearing RB of portion of top shown in the formation pie graph makes its formation that the gap size of this bearing space is kept roughly the same parallel space continuously toward the above-mentioned fluid storage OS of portion.
In the mode of execution shown in Figure 19 (g), form 2 RB of place radial dynamic pressure bearing portion, both bearing spaces of RB, make it all constitute the taper space that the past above-mentioned fluid storage OS of portion of the gap size of this bearing space is enlarged continuously.
In the mode of execution shown in Figure 19 (h), form and constitute the bearing space of the radial dynamic pressure bearing RB of portion of top shown in the figure among 2 RB of place radial dynamic pressure bearing portion, the RB, the taper space that its formation is enlarged the past above-mentioned fluid storage OS of portion of the gap size of this bearing space continuously, form the bearing space of the radial dynamic pressure bearing RB of portion of below shown in the pie graph simultaneously, make its formation that the gap size of this bearing space is kept roughly the same parallel space continuously toward the above-mentioned fluid storage OS of portion.
In the mode of execution shown in Figure 19 (i), form and constitute the bearing space of the radial dynamic pressure bearing RB of portion of below shown in the figure among 2 RB of place radial dynamic pressure bearing portion, the RB, the taper space that its formation is dwindled the past above-mentioned fluid storage OS of portion of the gap size of this bearing space continuously, but the bearing space of the radial dynamic pressure bearing RB of portion of top shown in the formation pie graph, the taper space that its formation is enlarged the past above-mentioned fluid storage OS of portion of the gap size of this bearing space continuously.
Each mode of execution according to Figure 19 with this structure, utilization often keeps greater than atmospheric barotropic state the inside of the OS of fluid storage portion that is located at the bearing space central part that comprises 2 RB of place radial dynamic pressure bearing portion, RB and the SB of axial hydrodynamic bearing portion to the plus-pressure of the lubricating fluid among the above-mentioned radial dynamic pressure bearing RB of portion.For example, in each mode of execution of above-mentioned Figure 19 (e) and Figure 19 (g), shown in dot and dash line among Figure 20 (e) and solid line (g), make in the whole bearing space that comprises the OS of fluid storage portion and keep barotropic state, thereby prevent from well to produce bubble in the lubricating fluid, and stably obtain suitable dynamic pressure.
In contrast, in the past in the device of Ti Chuing, shown in (c) among above-mentioned Figure 19, the situation of existence is: form 2 RB of place radial dynamic pressure bearing portion, both bearing spaces of RB, make it all constitute the taper space that the past above-mentioned fluid storage OS of portion of the gap size of this bearing space is dwindled continuously.Under this situation, shown in the dotted line among Figure 20 (c),, make in the bearing space to the plus-pressure of these two radial dynamic pressure bearing RB of portion, especially the inside of the OS of fluid storage portion becomes less than atmospheric negative pressure state, thereby make the inner bubble that produces of lubricating fluid.
At this moment, constitute among above-mentioned 2 RB of place radial dynamic pressure bearing portion, the RB vertically that the bearing space of long gap hydraulic bearing portion forms the taper space, then utilize to have bigger stressed radial dynamic pressure bearing portion and can high efficiency realize above-mentioned action effect if make.
As can be known from Fig. 20, in the present embodiment, make on the structure except that above-mentioned 2 except that the radial dynamic pressure bearing RB of portion, RB, it is the above malleation of barometric pressure that the plus-pressure that the lubricating fluid of the sealing export department side of the SB of axial hydrodynamic bearing portion is subjected to also makes the lubricating fluid among the above-mentioned fluid storage OS of portion, thereby obtains further stable dynamic pressure.
On the other hand, dynamic pressure generation device in the above-mentioned mode of execution, for example as shown in Figure 21, "＜" font and the ring-type aggregate of the tortuous groove DG of the herringbone shape that forms forms also can obtain the action effect identical with above-mentioned mode of execution but will be configured in the axial centre position DGC that the dot location DGO of man type complications groove of the dynamic pressure generation device of at least one side among above-mentioned 2 RB of place radial dynamic pressure bearing portion, the RB is configured in respect to this radial dynamic pressure bearing RB of portion to the position that the above-mentioned fluid storage OS of portion lateral deviation is moved suitable distance by constituting roughly.That is, mode of execution is in this case set the axial length A that is configured in the groove DG1 in the axial outside among the tortuous groove DG of above-mentioned man type for axial length B greater than the groove DG2 that is configured in axial inboard (A＞B).
Again, in the mode of execution shown in Figure 22, setting slot length, make among the tortuous groove DG of herringbone shape, the DG of the dynamic pressure generation device that is located at 2 RB of place radial dynamic pressure bearing portion, RB respectively, be positioned at than dot location DGO and more be respectively A and D, be positioned at when more being respectively B and C by the axial length of axially inboard groove than dot location DGO by the axial axial length of the groove in the outside, following relation is set up:
A+D≥B+C。
According to mode of execution with this structure, pressurization role to the lubricating fluid among 2 RB of place radial dynamic pressure bearing portion, the RB is pressed into lubricating fluid toward the private side of the OS of fluid storage portion generally, thereby the lubricating fluid of fluid storage portion OS inside is often kept reliably greater than atmospheric barotropic state.
Moreover use the inside that the spindle drive motor of so various mode of executions for example is contained in hard disk drive (HDD) as shown in Figure 8, also can obtain same action effect.
That is, as shown in Figure 8, the spindle drive motor M of the conical Hydrodynamic bearing apparatus by will having the respective embodiments described above is fixed on the mainboard 100a that constitutes sealing shape housing 100, uses this motor.Utilize the sealing cover 100b that cooperates with above-mentioned mainboard 100a, form the inner space of the housing 100 that comprises this spindle drive motor M at better purifying space 100c.Go up information recode discs 101 such as hard disk is installed at the rotation hub body (with reference to the symbol among Figure 17 222) of above-mentioned spindle drive motor M, utilize simultaneously by the fixing clamping element 103 of 102 pairs of above-mentioned rotation hub bodies of screw to make above-mentioned information-recording disk sheet 101 keep motionless state.
So far, understand the invention that the inventor finishes specifically according to mode of execution, but the invention is not restricted to above-mentioned mode of execution, can in the scope that does not break away from its main points, do various conversion certainly.
Again, the respective embodiments described above are that hard disk drive (HDD) is used the present invention, even but to other various Hydrodynamic bearing apparatus, the present invention can use too.
In sum, the Hydrodynamic bearing apparatus of the present invention the 1st aspect, since the conical shaped inclination bearing space that in the opposed gap of two inclination dynamic pressure faces of axle sleeve and axle bush, forms with prevent that lubricating fluid in this inclination bearing space from escaping to the fluid pressurization device that the direction that lubricating fluid is pressed into toward the inside of inclination bearing space is pressurizeed be set between the outside fluid-tight portion, be pressed into the lubricating fluid after the fluid pressurization device pressurization from the outer circumferential side of inclination bearing space toward private side, regardless of inclination dynamic pressure face angle of release how to form on the structure can be, make the lubricating fluid in the inclination bearing space produce kinetic pressure well, the lubricating fluid that will escape to foreign side from the outer circumferential side opening portion of above-mentioned inclination bearing space because of rotary centrifugal force is stably remained in the inclination bearing space, so do not strengthen the angle of release of inclination dynamic pressure face, just can reliablely and stablely obtain well relative floatation volume, and the lubricating fluid that can prevent from bearing space well leaks, the lubricating fluid of auxiliary fluid sealed department keeps function well, can seek the miniaturization of Hydrodynamic bearing apparatus, improve reliability simultaneously.
The Hydrodynamic bearing apparatus of the present invention the 2nd aspect, owing to form the fluid pressurization device of above-mentioned the 1st aspect by a plurality of grooves that are arranged in ring-type, energy high efficiency manufacturing structure is simple and easy and have the fluid pressurization device of good pressurization function, thereby except that above-mentioned effect, can also seek to boost productivity.
The Hydrodynamic bearing apparatus of the present invention the 3rd aspect, because at least one side in two opposed walls of the radial direction of axle sleeve and axle bush is provided with the fluid pressurization device aspect the above-mentioned the 1st, the Hydrodynamic bearing apparatus of the present invention the 4th aspect, because at least one side in two axial opposed walls of axle sleeve and axle bush is provided with the fluid pressurization device aspect the above-mentioned the 1st, forming on the structure to utilize the opposed wall of axle sleeve or axle bush to make the fluid pressurization device with good function easily, thereby except that above-mentioned effect, can also boost productivity.
The Hydrodynamic bearing apparatus of the present invention the 5th aspect, since on the axle sleeve aspect the above-mentioned the 1st, be provided with the guiding flow out to the inclination bearing space outer side lubricating fluid, make it return the circulation port of the private side of inclination bearing space, what make lubricating fluid that the pressurization of fluid pressurization device causes moves through that circulation port is smooth and easy to carry out, thereby can further improve above-mentioned effect.
The recording disc drive unit of the present invention the 6th aspect, utilize record head that the epitrochanterian information-recording disk sheet that is contained in the spindle drive motor with described Hydrodynamic bearing apparatus of either side in 5 aspects, above-mentioned the 1st aspect to the is write down or playback information owing to form on the structure, thereby also can obtain above-mentioned effect in the recording disc drive unit.
In sum, Hydrodynamic bearing apparatus of the present invention, since install can counterrotating axle bush or at least one side setting of axle sleeve run through the circulation port of this axle bush or axle sleeve, and and the inclination bearing space between form the circulation path of lubricating fluid, by at least one side in the pair of openings that forms described circulation port at the vertical openings face that is approximately perpendicular to upwardly extending described axle bush in circulation port perforation side or axle sleeve, utilization makes lubricating fluid comprise the circulation path flow of circulation port, eliminate the imbalance of pressure of the lubricating fluid of inclination bearing space two end part generation rapidly, instrument is pressed close to from the vertical openings face that is approximately perpendicular to circulation port perforation direction, to form circulation port, thereby elimination tool offset, but highi degree of accuracy forms circulation port, and the load stress of instrument is even, prolonged tool life, so can suitably keep tilting the pressure difference at bearing space two end part with easy structure, convenient and obtain suitably floatation volume relatively between fixed component and the rotating member reliably, can seek the raising of productivity and reliability simultaneously.
Recording disc drive unit of the present invention, utilize record head that the epitrochanterian information-recording disk sheet that is contained in the spindle drive motor with above-mentioned Hydrodynamic bearing apparatus is write down or playback information owing to form on the structure, thereby can obtain above-mentioned effect too in the recording disc drive unit.
In sum, Hydrodynamic bearing apparatus of the present invention, because the pressure adjustment of the isostasy in the maintenance bearing space is set is with the split channel, also adopt and have the structure that the lubricating fluid that makes in the fluid storage portion that is located at the part between the 2 place radial dynamic pressure bearing portions is the pressurization of the above malleation of barometric pressure, thereby prevent to produce bubble well, stably obtain suitable dynamic pressure, so can obtain stable dynamic pressure characteristic for a long time with easy structure, the reliability of Hydrodynamic bearing apparatus is improved.
Disc drive appts of the present invention, owing to form the spindle drive motor rotation activation bit recording disc record or the playback information of the Hydrodynamic bearing apparatus that utilizes record head utilization to be had the invention described above on the structure, thereby can obtain the remarkable result of above-mentioned Hydrodynamic bearing apparatus in the recording disc drive unit too.
Claims (7)
1, a kind of Hydrodynamic bearing apparatus, have utilization by the dynamic pressure generation device to lubricating fluid pressurization and the kinetic pressure that produces and with the hydraulic bearing member of contactless state supporting rotating shaft,
The part in the diametrically contraposition district between the periphery wall of inner circle wall that is formed at described hydraulic bearing member and described running shaft is left appropriate intervals vertically 2 place radial dynamic pressure bearing portions is set, simultaneously
Be formed at and be integrated the jointly part in the axial opposed district between the axial end of the axial end of rotating member of rotation and described hydraulic bearing member of above-mentioned running shaft, axial hydrodynamic bearing portion is set, and in the continuous bearing space that forms of described axial hydrodynamic bearing portion, injecting described lubricating fluid continuously from this 2 radial dynamic pressure bearing portion, it is characterized in that
Make on the structure: radial dynamic pressure bearing portion from described 2 radial dynamic pressure bearing portions and described axial hydrodynamic bearing portion sides adjacent to the bearing space of described axial hydrodynamic bearing portion, and the space of the axial foreign side side adjacent with the axial hydrodynamic bearing portion of opposite side, utilization separates the pressure adjustment that forms with described bearing space and is communicated with split channel, simultaneously
Bearing space being equivalent to the part between the described 2 place radial dynamic pressure bearing portions is provided with fluid storage portion, and this fluid storage portion forms by radially the bearing space of described radial dynamic pressure bearing portion being enlarged the clearance space that the back forms, and
It is malleation more than the barometric pressure that the pressurization of carrying out at the lubricating fluid in the described 2 place radial dynamic pressure bearing portions makes fluid in the described fluid storage portion.
2, Hydrodynamic bearing apparatus as claimed in claim 1 is characterized in that,
Make on the structure: except that described 2 place radial dynamic pressure bearing portions, it is malleation more than the barometric pressure that the pressurization of carrying out at the lubricating fluid in the described axial hydrodynamic bearing portion makes fluid in the described fluid storage portion.
3, Hydrodynamic bearing apparatus as claimed in claim 1 is characterized in that,
The bearing space that constitutes at least one side in the described 2 place radial dynamic pressure bearing portions forms like this: make the gap size of this bearing space enlarge continuously or identical towards described fluid storage portion, constitute taper space or parellel space.
4, Hydrodynamic bearing apparatus as claimed in claim 2 is characterized in that,
Constituting the bearing space of axially going up long radial dynamic pressure bearing portion in the described 2 place radial dynamic pressure bearing portions forms like this: constitute described taper space.
5, Hydrodynamic bearing apparatus as claimed in claim 1 is characterized in that,
" the ring-type aggregate of the tortuous groove of the herringbone shape of＜" font forms described dynamic pressure generation device, and the dot location that formation is configured in the tortuous groove of herringbone shape of at least one side's dynamic pressure generation device in the described 2 place radial dynamic pressure bearing portions is configured in from the axial centre position of this radial dynamic pressure bearing portion on the position that described fluid storage portion lateral deviation is moved by constituting roughly.
6, Hydrodynamic bearing apparatus as claimed in claim 4 is characterized in that,
In the tortuous groove of the herringbone shape of each the dynamic pressure generation device that is separately positioned on described 2 place radial dynamic pressure bearing portions, more be made as A and D respectively when being positioned at by the axial length of the groove outside axial than dot location, to be positioned at when more being made as B and C respectively by the axial length of axially inboard groove than dot location, following relation is set up:
A+D≥B+C。
7, a kind of recording disc drive unit is characterized in that,
Have the spindle drive motor that is equipped with each described Hydrodynamic bearing apparatus in the claim 1 to 6, the epitrochanterian information-recording disk sheet that is contained in this spindle drive motor and to the record head of this information-recording disk sheet record or playback information.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2003178368A JP2005016556A (en) | 2003-06-23 | 2003-06-23 | Conical dynamic pressure bearing device, and recording disk drive device having the same |
| JP2003178368 | 2003-06-23 | ||
| JP2003282497 | 2003-07-30 | ||
| JP2003340952 | 2003-09-30 |
Related Parent Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2004100619022A Division CN1303335C (en) | 2003-06-23 | 2004-06-23 | Hydrodynamic bearing device and a recording disk drive equipped with it |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1991187A true CN1991187A (en) | 2007-07-04 |
| CN100540923C CN100540923C (en) | 2009-09-16 |
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ID=34180019
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2007100077624A Expired - Fee Related CN100540923C (en) | 2003-06-23 | 2004-06-23 | Hydrodynamic bearing apparatus and recording disc drive unit with this device |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP2005016556A (en) |
| CN (1) | CN100540923C (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102454694A (en) * | 2010-10-19 | 2012-05-16 | 日本电产株式会社 | Fluid dynamic bearing mechanism including communicating channel, spindle motor, and disk drive apparatus |
| CN103378794A (en) * | 2012-04-18 | 2013-10-30 | 联想（新加坡）私人有限公司 | Rrotating mechanism, portable electric apparatus and service life extension method for fluid dynamic bearing |
Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4567476B2 (en) * | 2005-01-28 | 2010-10-20 | アルファナテクノロジー株式会社 | motor |
| KR20070035757A (en) | 2005-09-28 | 2007-04-02 | 삼성전기주식회사 | Fulid circulation typed hydrodynamics bearing |
| JP5401637B2 (en) * | 2008-05-26 | 2014-01-29 | 日本電産株式会社 | Fluid dynamic bearing device, spindle motor, and disk drive device |
| JP5233854B2 (en) | 2009-06-12 | 2013-07-10 | 日本電産株式会社 | Bearing device, spindle motor, and disk drive device |
| JP2011002024A (en) | 2009-06-18 | 2011-01-06 | Nippon Densan Corp | Bearing apparatus, spindle motor, and disk drive apparatus |
| JP2011133105A (en) | 2009-11-25 | 2011-07-07 | Nippon Densan Corp | Dynamic pressure bearing and spindle motor using the same |
| CN103322067A (en) * | 2013-06-21 | 2013-09-25 | 东南大学 | Conical dynamic pressure spiral groove bearing containing self-lubricating material |
-
2003
- 2003-06-23 JP JP2003178368A patent/JP2005016556A/en not_active Withdrawn
-
2004
- 2004-06-23 CN CNB2007100077624A patent/CN100540923C/en not_active Expired - Fee Related
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102454694A (en) * | 2010-10-19 | 2012-05-16 | 日本电产株式会社 | Fluid dynamic bearing mechanism including communicating channel, spindle motor, and disk drive apparatus |
| CN102454694B (en) * | 2010-10-19 | 2015-07-08 | 日本电产株式会社 | Fluid dynamic bearing mechanism including communicating channel, spindle motor, and disk drive apparatus |
| CN103378794A (en) * | 2012-04-18 | 2013-10-30 | 联想（新加坡）私人有限公司 | Rrotating mechanism, portable electric apparatus and service life extension method for fluid dynamic bearing |
Also Published As
| Publication number | Publication date |
|---|---|
| CN100540923C (en) | 2009-09-16 |
| JP2005016556A (en) | 2005-01-20 |
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