CN101871486B - Bearing mechanism, spindle motor and disc driving device - Google Patents
Bearing mechanism, spindle motor and disc driving device Download PDFInfo
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- CN101871486B CN101871486B CN2010101619129A CN201010161912A CN101871486B CN 101871486 B CN101871486 B CN 101871486B CN 2010101619129 A CN2010101619129 A CN 2010101619129A CN 201010161912 A CN201010161912 A CN 201010161912A CN 101871486 B CN101871486 B CN 101871486B
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Abstract
A bearing mechanism comprises a shaft, a sleeve part, a thrusting part and a cover part. The lubricating oil is supplied in a communicated path in the sleeve part, a thrusting clearance between the sleeve part and the thrusting part and a conical clearance between the outer surface of the thrusting part and the cover part, wherein a lower opening on the communicated path is limited in the outer periphery on the lower surface of the sleeve part outside of the radial direction of the thrusting slot; an utmost outer radial part of the thrusting part is tangent with a wall surface of the communicated path or is closer to a center axis than the wall surface; the conical clearance is closer to a center axis than the utmost outer radial point; and a guiding clearance is limited between the outer periphery and the cover part.
Description
Technical field
The present invention relates to use gear mechanism, spindle motor and the disc driving equipment of hydrodynamic.
Background technique
Some known electrodynamic machines comprise the gear mechanism that uses hydrodynamic.The fluid dynamic pressure bearing device that in TOHKEMY JP-A 2007-16275 communique, uses in the disclosed spindle motor comprises axle and is inserted with the sleeve body of the tubulose of axle in it.Axle is fixed to the base plate of motor.Sleeve body is fixed to the rotor of motor.Axle be provided with lay respectively on the sleeve body with under two ring-type thrust flanges.Fluid dynamic pressure bearing device comprises radial bearing portion and thrust bearing portion, and radial bearing portion is set between axle and the sleeve body, and thrust bearing portion is set between each thrust flanges and sleeve body in two thrust flanges.Thereby sleeve body and rotor are respectively by to support with respect to the rotating mode of axle.Sleeve body has to be defined in makes two intercommunicating pores that the thrust gap communicates with each other in it.Near the open upper end of intercommunicating pore and lower ending opening, formed the interface of lubricant oil.
Disclosed hydrodynamic shaft bearing motor comprises axle that is fixed to pedestal and the sleeve that is set to sway in TOHKEMY JP-A 2000-245104 communique.The plate-like thrust plate of being processed by stainless steel is fixed to axle.Sleeve is provided with the ring-type thrust lining of being processed by dissimilar stainless steels.Thrust plate is set to along the direction parallel with axle against each other with the thrust lining.Thrust plate and thrust lining define the thrust gap together betwixt.Thrust lining in this hydrodynamic shaft bearing motor is processed by the stainless steel of high-durability, and this helps to prevent the damage of edges thrust lining of thrust plate.
Here, in having TOHKEMY JP-A 2007-162759 communique, under the situation of the gear mechanism of disclosed structure, during motor driving, be difficult to make the bubble that produces in the lubricant oil to be discharged through any interface of lubricant oil.
Summary of the invention
According to preferred implementation of the present invention; A kind of gear mechanism is provided, and this gear mechanism comprises along central axis with the stationary axle of vertical direction setting, the sleeve part, first push stopping part, cap and the lubricant oil that are inserted with said axle in it and are set to rotate with respect to said axle.First push stopping part is set to from the said diameter of axle to outside stretching, extension, and has the upper surface that the lower surface with sleeve part relatively is provided with.Cap is attached to sleeve part, and is set to relative with the outer surface of first push stopping part.The upper surface of the lower surface of sleeve part and first push stopping part defines the first thrust gap together betwixt.Axle and sleeve part define radial clearance together betwixt.
Sleeve part is limited with within it and extends upward the communication paths that is communicated with the top of radial clearance from the bottom of sleeve part.
The outer surface of first push stopping part and cap define tapered gaps together betwixt.Tapered gaps increases at the downward direction width gradually, and has the interface with lubricant oil.
Lubricant oil is arranged in radial clearance, communication paths, the first thrust gap and the tapered gaps.
Radial clearance comprises radial bearing portion, through the first dynamic pressure groove lubricant oil is produced radial dynamic pressure.The first thrust gap comprises the first thrust bearing portion, through the second dynamic pressure groove lubricant oil is produced the thrust dynamic pressure.
The lower surface of sleeve part has the peripheral part that is set at the first thrust gap radial outside.Peripheral part has the lower ending opening of the communication paths that limits within it.
The outer surface of first push stopping part is included in the surface of the conical shaped that the distance of downward direction and central axis reduces gradually or is parallel to the surface of the general cylindrical shape of extension of central axis.
The outermost radial outside of the outer surface of first push stopping part partly is set in planimetric map or is tangent with the wall surface of communication paths, perhaps than wall surface near central axis.
Tapered gaps is set to outermost radial outside point than wall surface near central axis.
Peripheral part and cap define guide clearance together betwixt, so that lubricant oil is guided in the direction of tapered gaps and towards the first thrust gap from lower ending opening.
Gear mechanism according to preferred implementation of the present invention allows lubricant oil to transport towards the first thrust gap from the lower ending opening of communication paths, makes that any bubble in the lubricant oil can both be discharged through tapered gaps.
Description of drawings
Fig. 1 is the sectional view of disc driving equipment according to the preferred embodiment of the present invention.
Fig. 2 is the sectional view according to the motor of preferred implementation of the present invention.
Fig. 3 is the sectional view according to the sleeve part of preferred implementation of the present invention.
Fig. 4 is the worm's eye view of sleeve part.
Fig. 5 A shows the figure of the internal surface of sleeve part.
Fig. 5 B and Fig. 5 C show the internal surface figure according to the sleeve part of other preferred implementation of the present invention.
Fig. 6 and Fig. 7 are the zoomed-in views according to the bottom of the gear mechanism of preferred implementation of the present invention.
Fig. 8 is the zoomed-in view according to the first thrust gap of preferred implementation of the present invention.
Fig. 9 is the zoomed-in view on the top of gear mechanism.
Figure 10 is the zoomed-in view according to second push stopping part of preferred implementation of the present invention.
Figure 11 is the zoomed-in view on the top of gear mechanism.
Figure 12 is the zoomed-in view according to the bottom of the gear mechanism of another preferred implementation of the present invention.
Figure 13 is the zoomed-in view according to the bottom of the gear mechanism of another preferred implementation of the present invention.
Figure 14 shows the figure according to first push stopping part of preferred implementation of the present invention.
Figure 15 shows the figure according to the communication paths of preferred implementation of the present invention.
Embodiment
Here supposition abbreviates the upside of accompanying drawing and downside as upside and downside respectively.Note; When in specification of the present invention, being used to describe relative position or the direction of different parts; Used the term that is called " making progress ", " downwards ", " left side ", " right side " etc. simply with reference to accompanying drawing, and these terms should not be considered to describe relative position or the direction of these parts when as installed is in device.
Fig. 1 is the vertical cross-section diagram of the disc driving equipment that comprises spindle motor 12 1 of exemplary preferred embodiment according to the present invention.Spindle motor will be called " motor " for short hereinafter.
Disc driving equipment 1 is so-called hard disk drive device.Disc driving equipment 1 for example comprises three dished wheels 11, motor 12, access portion 13 and the housing 14 that is used for recorded information.Motor 12 is set in holding tray 11, rotate.Access portion 13 is set to read information and/or information is write dish 11 from coiling 11.Notice that the quantity of dish is not limited to three.
Housing 14 comprises roughly first housing structure 141 and the second tabular housing structure 142 of cup-shaped.Motor 12 is contained in first housing structure 141 with access portion 13.In disc driving equipment 1, second housing structure 142 is connected to first housing structure 141 to define housing 14.The inner space of disc driving equipment 1 is clean, does not almost have dust or micronic dust.
Clamp holder 151 and interval body 152 are set to three dishes 11 are fixed to the rotor hub 31 of motor 12, make dish 11 separate equally spacedly each other along central axis J1 direction.Access portion 13 comprises six head 131, be set to six arms 132 and the head actuating mechanism 133 of supporting head part 131.Each head 131 be placed close to the dish 11 in a corresponding dish with magnetically from coil 11 read information and/or write information to the dish 11.Head actuating mechanism 133 is set to activate each arm 132 so that a relevant head moves with respect to a corresponding dish in the dish 11 in the head 131.According to said structure, each stature 131 is set in being retained as near the dish that is rotating 11, visit the desired locations on this dish 11 in the corresponding dish, to read information from this dish 11 and/or to write information on this dish 11.
Fig. 2 is the vertical cross-section diagram of motor 12.Motor 12 is external-rotor motors.Motor 12 comprises stationary part 2, rotation section 3 and fluid bearing mechanism 4.Fluid bearing mechanism 4 will be called " gear mechanism " 4 for short hereinafter.Rotation section 3 is supported via gear mechanism 4, makes rotation section 3 to rotate with respect to stationary part 2 around the central axis J1 of motor 12.
Hub main body 311 heart therein defines along the hole portion 313 that is parallel to or is roughly parallel to the direction extension of central axis J1.In the explanation hereinafter, near the part that comprises hole portion 313 the central axis J1 will be called as " sleeve part 5 " hereinafter.Bottom that defines sleeve part 5 in the sleeve part 5 and near the part 51 that is positioned at the center are outstanding downwards.This part 51 will abbreviate " bottom 51 " hereinafter as.Hub main body 311 has the recess 53 of central part qualification above that.The bottom of recess 53 defines the upper surface of sleeve part 5.Recess 53 comprises slightly to shoulder recessed and that be provided with around the recess 53.Axle 41 inserts in the hole portion 313 of sleeve part 5.Sleeve part 5 is limited with from sleeve part 5 bottoms along the upwardly extending communication paths 55 of direction that is parallel to or is roughly parallel to central axis J1 within it.Communication paths 55 perpendicular to or be approximately perpendicular to have in the cross section of central axis J1 round-shaped.Notice that the sectional shape of communication paths 51 is not limited to circle.
In motor 12, sleeve part 5 is defined as the part of gear mechanism 4 part that is supported by axle 41.That is, sleeve part 5 is not only as the part of rotation section 3 but also as the part of gear mechanism 4.Motor 12 is configured such that rotation section 3 is fixed to the sleeve part 5 of gear mechanism 4.
Fig. 3 is the partial cross section figure of sleeve part 5, only shows the bottom 51 and top 52 of sleeve part 5.The bottom 51 of sleeve part 5 comprises lower surface 61, the protuberance of giving prominence to 62, lid attachment 63, wide diameter portion 65 and shoulder 66 downwards.Lower surface 61 comprises lower end surface 611 and peripheral part 612.Being shaped as annular and being set to vertical of lower end surface 611 with central axis J1.Peripheral part 612 is positioned at the radial outside of lower end surface 611.Lower end surface 611 is located at respect to be parallel to or is roughly parallel to the low position, position of the lower end (being referred to as " lower ending opening " hereinafter) 551 of the direction ratio communication paths 55 of central axis J1.
The oblique cutting part 551a that extends in the communication paths 55 from peripheral part 612 is limited to lower ending opening 551.Stride the periphery zone that oblique cutting part 551a launches, promptly limit the periphery of communication paths 55 and in planimetric map, be circular surface, will be referred to as " wall surface 553 " of communication paths 55 hereinafter.The distance of border decentre axis J1 between oblique cutting part 551a and the lower end surface 611 is substantially equal to the radius of lower end surface 611, and the external diameter of lower end surface 611 is in the scope of about 7mm to about 8mm.The size of the lower end surface 611 of sleeve part 5 is less, thereby when making sleeve part 5, can be positioned at the hole portion 313 and the lower end surface 611 of center through using the processing of cutting tool one-time mechanical.
Fig. 4 illustrates the lower end surface 611 of sleeve part 5 and the worm's eye view of near zone thereof with the form of amplifying.Lower end surface 611 is limited with the dynamic pressure groove 611a of spiral pattern within it.Shown in Fig. 3 and 4, dynamic pressure groove 611a is set to be stretched over the interior week of ring-type plane of inclination 641.During motor 12 drove, dynamic pressure groove 611a was set to rotate to impel (i.e. suction) lubricant oil 46 to produce enough dynamic pressures and come drive motor 12 in dynamic pressure groove 611a, inwardly to advance.This is configured with and helps prevent the bubble that produces because lubricant oil 46 internal pressures reduce.
With reference to Fig. 3, the top 52 of sleeve part 5 have for annular and perpendicular to or be approximately perpendicular to the upper-end surface 521 of central axis J1.Upper-end surface 521 is limited with the roughly the same dynamic pressure groove of set-up mode with as shown in Figure 4 dynamic pressure groove 611a within it.More specifically, in planimetric map, the dynamic pressure groove of upper-end surface 521 is provided with respect to the mode of circumferential opposite direction (reverse orientation) to compare around central axis J1 with dynamic pressure groove 611a.The upper end 552 of communication paths 55 is positioned at the radial outside of upper-end surface 521.The upper end 552 of communication paths 55 will be called as " open upper end 552 " hereinafter.
With reference to Fig. 5 A, the internal surface 541 of sleeve part 5 is limited with respectively the dynamic pressure groove 71 and 72 at the herringbone pattern of the upper end portion of internal surface 541 and underpart above that.More specifically, dynamic pressure groove 71 and 72 makes each dynamic pressure groove 71 and 72 have the shape of horizontal " V " font along circumferentially being arranged on the internal surface 541.Each down dynamic pressure groove 72 have the following slot part 721 longer than slot part on it 722.This structure of dynamic pressure groove 72 helps to produce pressure makes lubricant oil 46 be described below in radial clearance upwards to flow that like this, lubricant oil 46 then will as shown in Figure 3ly be advanced through communication paths 55 and circulated to accomplish.
With reference to Fig. 5 B, in the modification of this preferred implementation, for following dynamic pressure groove 72, the length of following slot part 721 can with the length of last slot part 722 about equally.Under this situation, the tipper 73 that is parallel to slot part 721 extensions down can be arranged between every pair of adjacent following slot part 721.And with reference to Fig. 5 C, in the modification of this preferred implementation, the tipper 74 that is arranged essentially parallel to down slot part 721 extensions can be arranged under each following slot part 721.
In gear mechanism 4, between the outer surface of the internal surface 541 of the sleeve part shown in Fig. 5 A 5 and axle 41 as shown in Figure 2, be limited with small gap.This gap will be called as " radial clearance " hereinafter.During motor 12 drives; The dynamic pressure groove 71 and 72 of herringbone pattern is used for producing radial dynamic pressure for the lubricant oil 46 of radial clearance; Thereby form radial bearing portion, this radial bearing portion with respect to axle 41 perpendicular to or be approximately perpendicular to the direction stop sleeve portion 5 of central axis J1.Hereinafter, radial clearance and radial bearing portion will be represented by reference character 87 and 871 respectively.
Fig. 6 is the partial cross section figure that the bottom of gear mechanism 4 is shown with the form of amplifying.First push stopping part 42 is set to stretch to have annular shape from axle 41 radially outwards.First push stopping part 42 has upper surface 421 and conical surface 422, upper surface 421 perpendicular to or be approximately perpendicular to central axis J1, conical surface 422 is roughly taper shape and defines the outer surface of first push stopping part 42.Conical surface 422 is configured as along the distance of downward direction decentre axis J1 and reduces gradually.It is relative with the lower end surface 611 of sleeve part 5 that upper surface 421 is set to, between upper surface 421 and lower end surface 611, to limit small gap.This gap will be called as " the first thrust gap 81 " hereinafter.During motor 12 drove, the first thrust bearing portion 811 was formed in the first thrust gap 81, produced the thrust dynamic pressure with the dynamic pressure groove 611a through spirality pattern as shown in Figure 4 for the lubricant oil between first push stopping part 42 and sleeve part 5 46.
As shown in Figure 6, first cap 44 comprise along be parallel to or be roughly parallel to the upwardly extending cylindrical part of the direction of central axis J1 441, be the annulus 442 at center and the rake 443 adjacent with central axis J1 with annulus 442.Cylindrical part 441 be set to along perpendicular to or be approximately perpendicular to the lid attachment 63 of the direction contact sleeve portion 5 of central axis J1.
Fig. 7 is the figure that shows lower ending opening shown in Figure 6 551 and near zone thereof with the form of amplifying.Limit betwixt along the gap 671 that is parallel to or is roughly parallel to the direction of central axis J1 with the upper end of the adjacent shoulder 66 in the upper end of first diameter reducing part 631 with cylindrical part 441.Along be parallel to or be roughly parallel to central axis J1 direction gap 671 width preferably at about 0.3mm in the scope of about 0.6mm.Cylindrical part 441 is press fit into the outer surface of first diameter reducing part 631, is fixed to the upper through tackiness agent 9 simultaneously.Because the width in gap 671 falls in the aforementioned range, so first cap, 44 grades will can not cause cylindrical part 441 to contact with shoulder 66 if foozle occurs.
As shown in Figure 6, the upper surface 442a of annulus 442 for annular and perpendicular to or be approximately perpendicular to central axis J1.Upper surface 442a be set to along be parallel to or be roughly parallel to central axis J1 direction and communication paths 55 lower ending opening 551 a part relatively, be set to simultaneously along the protuberance 62 that is parallel to or is roughly parallel to the direction contact sleeve portion 5 of central axis J1.This structure prevents first cap, 44 closed lower openings 551.Upper surface 442a will be called as " ring-type surface of contact 442a " hereinafter.
Rake 443 comprises the first ring-type plane of inclination 443a and the second ring-type plane of inclination 443b.The first ring-type plane of inclination 443a is for annular and be set to be positioned at ring-type surface of contact 442a radially inner side and adjacent with ring-type surface of contact 442a.The second ring-type plane of inclination 443b is for annular and be set to be positioned at the first ring-type plane of inclination 443a radially inner side and adjacent with the first ring-type plane of inclination 443a.The first ring-type plane of inclination 443a is set to increase and extend upward gradually along with the radial distance from the upper surface 421 of the lower end surface 611 of sleeve part 5 and first push stopping part 42.The second ring-type plane of inclination 443b tilts along direction radially outward upwards, the second ring-type plane of inclination 443b with respect to the angle of inclination of central axis J1 less than the angle of inclination of the first ring-type plane of inclination 443a with respect to central axis J1.
The first ring-type plane of inclination 443a is set to relative with the ring-type plane of inclination 641 of sleeve part 5, makes the ring-type plane of inclination 443a that wins limit small gap 82 betwixt with ring-type plane of inclination 641.During motor 12 drove, this gap 82 was as guiding the lower ending opening 551 of lubricant oil 46 from communication paths 55 to the first thrust gap 81.This gap 82 will be called as " guide clearance 82 " hereinafter.The width of guide clearance 82 increases simultaneously along downward direction gradually, and the distance of guide clearance 82 decentre axis J1 reduces.The Extreme breadth of guide clearance 82 is preferably more than the 0.2mm, reducing the groove resistance of guide clearance 82, and is preferably below the 0.4mm, to reduce the amount of lubricant oil 46.Note, gap width be meant this gap with limit this gap both sides on the face that intersects with equal angular of surface on width.
The conical surface 422 of the second ring-type plane of inclination 443b and first push stopping part 42 limits gap 83 together betwixt.Gap 83 has the interface with lubricant oil 46 within it.Gap 83 is positioned at outermost radial outside point than the wall surface 553 of communication paths 55 more near central axis J1.Gap 83 is set to its width and increases gradually along downward direction.This gap 83 will be called as " first tapered gaps 83 " hereinafter.
The minimum width of first tapered gaps 83 is greater than the Extreme breadth of guide clearance 82.In addition, the Extreme breadth of the minimum width of first tapered gaps 83 and guide clearance 82 is all less than the width of communication paths 55.In gear mechanism 4, the guide clearance 82 and first tapered gaps 83 form the path that increases gradually along the downward direction width together.The first thrust gap 81 of stretching from central axis J1 is set at the boundary vicinity between the guide clearance 82 and first tapered gaps 83.The first thrust gap 81 along the width of direction that is parallel to or is roughly parallel to central axis J1 less than the minimum width of guide clearance 82.
Fig. 8 is the sectional view that shows the first thrust gap 81 and near zone thereof with the form of amplifying.More specifically, Fig. 8 shows the sectional view of a part of bottom 51 and first push stopping part 42 of sleeve part 5, wherein, the communication paths 55 shown in Fig. 6 is not set.The external diameter of first push stopping part 42; The i.e. radial dimension of the part 423 at the most peripheral place that is positioned at conical surface 422 of first push stopping part 42 in planimetric map; Less than the diameter of the lower end surface 611 of sleeve part 5, the i.e. diameter at the edge 681 of the boundary between lower end surface 611 and the ring-type plane of inclination 641.Part 423 will be called as first push stopping part 42 " outermost radial outside part 423 " hereinafter.And as shown in Figure 7, outermost radial outside part 423 is positioned at wall surface 553 than communication paths 55 more near central axis J1 in planimetric map.
Fig. 9 is the sectional view that the top of gear mechanism 4 is shown with the form of amplifying.Be set to upper-end surface 521 second relative push stopping part 43 with sleeve part 5 and be set to stretch roughly having the shape of annular, and be set in the recess 53 of hub main body 311 from axle 41 radially outwards.
Second push stopping part 43 have annular shape lower surface, outer ring-like face 432, be parallel to or be roughly parallel to outer surface 433 and the plane of inclination 434 of central axis J1.Lower surface 431 is set to outstanding slightly downwards.Outer ring-like face 432 is positioned at the radial outside of lower surface 431.Plane of inclination 434 extends upward from the upper end of outer surface 433, simultaneously gradually near central axis J1.The outer ring-like face 432 of second push stopping part 43 is set to along being parallel to or to be roughly parallel to the direction of central axis J1 relative with communication paths 55.
In the zone between the open upper end 552 of the top of radial clearance 87 and communication paths 55; It is relative with the upper-end surface 521 of sleeve part 5 that the lower surface 431 of second push stopping part 43 is set to, to limit the small gap 84 between upper-end surface 521 and lower surface 431.This gap 84 will be called as " the second thrust gap 84 " hereinafter.
In gear mechanism 4, the top of communication paths 55 and radial clearance 87 is each other through the second thrust gap, 84 indirect communication.It is relative with the sidewall 531 of recess 53 that the outer surface 433 of second push stopping part 43 is set to, and is limited with gap 85 therebetween.This gap 85 will be called as " side clearance 85 " hereinafter.Shown in figure 10, outer surface 433 is limited with a plurality of dynamic pressure groove 433a within it, and a plurality of dynamic pressure groove 433a tilt with the mode of pointing to towards single direction.
During motor 12 drove, the second thrust bearing portion 841 was formed in the second thrust gap 84 shown in Figure 9, with the dynamic pressure groove through spirality pattern lubricant oil 46 was produced the thrust dynamic pressure.In side clearance 85, dynamic pressure groove 433a be used for producing dynamic pressure so that lubricant oil 46 to dirty.This dynamic pressure helps to prevent that lubricant oil 46 is described below through 86 leakages of second tapered gaps.
Figure 11 shows at the open upper end 552 of the communication paths shown in Fig. 9 55 and the figure of near zone thereof with the form of amplifying.Open upper end 552 is positioned at the position lower than the position of upper-end surface 521.Sleeve part 5 is limited with from the upper-end surface 521 periphery above that towards plane of inclination 522 that open upper end 552 is extended obliquely.The diameter of the lower surface 431 of second push stopping part 43 is less than the diameter of the upper-end surface 521 of sleeve part 5, i.e. the diameter at the edge 523 of the boundary between upper-end surface 521 and the plane of inclination 522.
With reference to Fig. 9, second cap 45 comprises plectane portion 451 and sidepiece 452.Plectane portion 451 radially outward direction is downward-sloping slightly.Sidepiece 452 from the radial outer end of plectane portion 451 to extending below.The plane of inclination 434 of the sidepiece 452 and second push stopping part 43 limits second tapered gaps 86 together betwixt, makes second tapered gaps 86 increase gradually along the direction width that makes progress.Second tapered gaps 86 has the interface with lubricant oil 46 within it.
With reference to Fig. 6 and Fig. 9, lubricant oil 46 is set to fill uninterruptedly guide clearance 82, first tapered gaps 83, the first thrust gap 81, radial clearance 87, the second thrust gap 84, side clearance 85, second tapered gaps 86 and communication paths 55.
For motor 12; At sleeve part 5 during central axis J1 rotates with respect to axle 41; Sleeve part 5 is being supported by the first thrust bearing portion 811 and the second thrust bearing portion 841 along the direction of central axis J1, perpendicular to or the direction that is approximately perpendicular to central axis J1 support by radial bearing portion 871.
At this moment, make lubricant oil 46 communication paths 55 of flowing through downwards, and the guide clearance shown in Fig. 6 82 is used for lubricant oil 46 from the lower ending opening 551 of communication paths 55 along the direction of first tapered gaps 83 and towards 81 guiding of the first thrust gap.When lubricant oil 46 contains any bubble, make bubble advance finally to be discharged to the outside through interface with lubricant oil 46 through the guide clearance 82 and first tapered gaps 83.In addition, make lubricant oil 46 flow to the bottom of radial clearance 87, flow to its top through radial clearance 87, and flow back in the communication paths 55 through the second thrust gap 84 shown in Fig. 9 through the first thrust gap 81.That is, guide clearance 82 is limited between the peripheral part 612 and first cap 44 of sleeve part 5, to guide the direction of lubricant oil 46 first tapered gaps 83 from lower ending opening 551 edges and towards the first thrust gap 81.In other words, in the peripheral part 612 and the space between first cap 44 of sleeve part 5, guide clearance 82 is used for making the direction of lubricant oil 46 first tapered gaps 83 from lower ending opening 551 edges and flows towards the first thrust gap 81.
In gear mechanism 4, sleeve part 5 is not supported for and contacts with axle 41.Thereby rotation section 3 can be rotated with respect to stationary part 2 highi degree of accuracy and limited noise ground shown in figure 2.
As stated, because the external diameter of first push stopping part 42 is less than the diameter of the lower end surface 611 of sleeve part 5 in the gear mechanism 4, lubricant oil 46 is sent to the first thrust gap 81 from the lower ending opening 551 of communication paths 55.In gear mechanism 4, the lower ending opening 551 of communication paths 55 is positioned at the position higher than the position in the first thrust gap 81, simultaneously, guide clearance 82 be set to lower ending opening 551 relatively to tilt with respect to ring-type plane of inclination 641.This structure helps to make from flowing of the lubricant oil 46 in lower ending opening 551 to first thrust gaps 81 level and smooth, thereby prevents to produce whirlpool, and helps lubricant oil 46 is fed in the first thrust gap 81 smoothly.
And in the bottom of gear mechanism 4, any bubble in the lubricant oil 46 is discharged through first tapered gaps 83, and lubricant oil 46 is fed in the first thrust gap 81 simultaneously.The path that is combined to form by the guide clearance 82 and first tapered gaps 83 increases along the downward direction width gradually, so that bubble is discharged to the outside.The centrifugal force that in guide clearance 82, produces owing to the rotation of rotor hub 31 makes the pressure that acts on lubricant oil 46 become lower in the position near central axis J1 than the farther position of decentre axis J1.This pressure difference helps the proportion any bubble lower than the proportion of lubricant oil 46 to advance along the direction of central axis J1, makes bubble be discharged to easily in first tapered gaps 83.
Because guide clearance 82 is set to increase gradually along the downward direction width, foozle appears in institute will can not make guide clearance 82 local narrow, and this has guaranteed that any bubble advances through guide clearance 82 without restriction.
In gear mechanism 4; The diameter of the upper surface 421 of first push stopping part 42 is less than the diameter of the lower end surface 611 of sleeve part 5, and this helps to prevent that the lower end surface 611 of sleeve part 5 and the edge 681 of the boundary between the ring-type plane of inclination 641 from contacting with the upper surface 421 of first push stopping part 42.Therefore, even the hardness of first push stopping part 42 is lower than the hardness of sleeve part 5, also can be limited in the first thrust gap 81 and produces wear particle.Similarly, the diameter of the lower surface 431 of second push stopping part 43 is less than the diameter of the upper-end surface 521 of sleeve part 5, and this edge 523 that helps to prevent the upper-end surface 521 of sleeve part 5 contacts with the lower surface 431 of second push stopping part 43.Therefore, can be limited in the second thrust gap 84 and produce wear particle.This can prolong the life-span of gear mechanism 4.
As stated, about gear mechanism 4,, also can limit the wearing and tearing of first push stopping part 42 and second push stopping part 43 even first push stopping part 42 and second push stopping part 43 are not to be processed or do not carried out cover coat etc. by high abrasion resisting material.Much less, first push stopping part 42 and second push stopping part 43 can be processed or carried out cover coat etc. by high abrasion resisting material.
Above-mentionedly be used for being limited in the technology that the thrust gap produces wear particle and also be applicable in other fluid bearing mechanism except that gear mechanism 4.That is, under the situation of thrust gap by the component limit of two different hardness, the diameter of the thrust surface through making the member with low hardness may be limited in the thrust gap and produces wear particle less than the diameter of the thrust surface of another member with high hardness.Also be like this in radial clearance.That is, the width of the radial surface through making the member with low hardness may be limited to and produces wear particle in the radial clearance less than the width of the radial surface of the member with high hardness.
Now; Assembling for gear mechanism 4; When first cap 44 shown in Fig. 7 was attached to sleeve part 5, sleeve part 5 was placed to and faces down, and under this state; First cap 44 51 moves from sleeve part 5 tops towards the bottom, makes the cylindrical part 441 of the cap 44 of winning be press fit into bottom 51.Tackiness agent 9 is applied to second diameter reducing part 632 in advance.Thereby, make tackiness agent 9 on first diameter reducing part 631, expand thereby cylindrical part 441 mobile scatters tackiness agent 9.In this way, first cap 44 is press fit into to cover attachment 63 and be fixed to through tackiness agent 9 and covers attachment 63.The ring-type surface of contact 442a of first cap 44 contacts with protuberance 62, thereby confirms easily be parallel to or be roughly parallel to the position of direction first cap 44 of central axis J1 with respect to sleeve part 5.
Because first cap 44 is fixed to sleeve part 5 through press fit; So can more effectively prevent 44 distortion of first cap through the situation that swaged forging etc. is fixed to sleeve part 5 than first cap 44, this has improved the precision that limits the guide clearance 82 and first tapered gaps 83.Comprise that at lid second diameter reducing part 632 is convenient to be coupled to first cap 44 bottom 51 of sleeve part 5 in the attachment 63.And second diameter reducing part 632 is also as the mark of being convenient to tackiness agent 9 suitably is applied to desired locations.
In the situation of the outer surface of the bottom of sleeve part, tackiness agent can be forced out the space between cap and the sleeve part to the ring-type cap through adhesive in motor, to invade gear mechanism or to be attached near another member the gear mechanism.Yet with reference to Fig. 7, under motor 12 situations, gap 671 is set between the shoulder 66 of upper end and sleeve part 5 of cylindrical part 441, and gap 671 keeps the part that extrudes from the space between cylindrical part 441 and the lid attachment 63 in the tackiness agents 9.Thereby prevent that tackiness agent 9 from contacting with other member (for example stator 22 etc.).
And, because the small gap 672 that between second diameter reducing part 632 and cylindrical part 441, limits has kept tackiness agent 9, radially inwardly flow so prevent tackiness agent 9.Along perpendicular to or the width that is approximately perpendicular to the gap 672 that the direction of central axis J1 records be about 50 μ m.And protuberance 62 has guaranteed further to prevent that with contacting of ring-type surface of contact 442a tackiness agent 9 from radially inwardly flowing.
In gear mechanism 4, gap 672 is sealed by tackiness agent 9 at its whole circumference, thereby prevents that lubricant oil 46 from leaking through the space of covering between attachment 63 and the cylindrical part 441.Thereby, in the process of test bearing mechanism 4,, can save test bearing mechanism 4 through covering the leak-testing of the space gas leakage between attachment 63 and the cylindrical part 441 through gas (for example air or helium) is incorporated in the gear mechanism 4.
Figure 12 is the figure that illustrates according to the gear mechanism 4 of the exemplary variation of this preferred implementation.In this gear mechanism 4; Parallel or the almost parallel of the first ring-type plane of inclination 443a of the ring-type plane of inclination 641 of sleeve part 5 and first cap 44, and the guide clearance 82a that between the ring-type plane of inclination 641 and the first ring-type plane of inclination 443a, limits has the width of constant.Other structure characteristic of gear mechanism 4 identical with shown in Fig. 6.And in the gear mechanism 4 according to this exemplary variation, the downward-sloping so that lubricant oil 46 of guide clearance 82a is level and smooth from flowing of lower ending opening 551 to the first thrust gaps 81 of communication paths 55, thereby prevents to produce whirlpool.Owing to have a sleeve part 5 shown in Fig. 6, less according to the size of the lower end surface 611 of the sleeve part 5 of this exemplary variation, make when making sleeve part 5, can be through using cutting tool time processing hole portion as shown in Figure 3 313 and lower end surface 611.
Figure 13 is the figure that illustrates according to the guide clearance 82b of another exemplary variation of this preferred implementation.In first cap 44 according to this exemplary variation, perpendicular to or the circumferentia 442b that is approximately perpendicular to central axis J1 replace the first ring-type plane of inclination 443a shown in Fig. 6 to be set at the radially inner side of ring-type surface of contact 442a.Circumferentia 442b is positioned at the low position, position than ring-type surface of contact 442a.In addition, the lower surface 61 of sleeve part 5 perpendicular to or be approximately perpendicular to central axis J1.The part 611 near central axis J1 of lower end surface 61 is limited with dynamic pressure groove 611a within it, as lower end surface as shown in Figure 4 611.Part 611 is set to along being parallel to or to be roughly parallel to the upper surface 421 of direction and first push stopping part 42 of central axis J1 relative, between part 611 and upper surface 421, to limit the first thrust gap 81.The lower ending opening 551 of communication paths 55 is positioned at peripheral part 612 places of 81 radial outsides in the first thrust gap of lower surface 61.Other structure characteristic according to the gear mechanism 4 of this exemplary variation is identical with the structure characteristic of the gear mechanism 4 shown in Fig. 6.
In gear mechanism 4 according to this exemplary variation; The part that is positioned at lower ending opening 551 radial outsides of sleeve part 5 is set to contact with ring-type surface of contact 442a, make perpendicular to or be approximately perpendicular to the guide clearance 82b that central axis J1 extends and be defined between peripheral part 612 and the circumferentia 442b.The centrifugal force that during motor 12 drives, in guide clearance 82b, produces makes that the pressure that acts on lubricant oil 46 is lower in the farther position of decentre axis J1 at the position ratio near central axis J1.This pressure difference helps any bubble the advancing of the direction of central axis J1, and makes bubble be easy to be discharged in first tapered gaps 83.
Figure 14 shows the figure according to first push stopping part 42 of the exemplary variation of this preferred implementation.The outermost radial outside part 423 of first push stopping part 42 overlaps in the radially inner side portion of oblique cutting part 551a that is parallel to or be roughly parallel to direction and the lower ending opening 551 of central axis J1.In addition, in planimetric map, outermost radial outside part 423 is tangent with the wall surface 553 of communication paths 55.Under this situation, any bubble that allows to advance downwards from communication paths 55 advances under the situation of not disturbing first push stopping part 42 first tapered gaps 83.Notice that in planimetric map, outermost radial outside part 423 can be positioned at wall surface 553 radially inner sides, overlap with oblique cutting part 551a simultaneously.
Figure 15 is the figure that illustrates according to the communication paths 55a of the exemplary variation of this preferred implementation.Shown in figure 15, communication paths 55a reduces along the distance of the direction decentre axis J1 that makes progress gradually.The open upper end 552 of communication paths 55a is arranged in the second thrust gap 84, and communication paths 55a directly is communicated with the top of radial clearance 87.Notice that in other modification of this preferred implementation, the open upper end 552 of communication paths 55 can be arranged in radial clearance 87.
Although described exemplary preferred embodiment of the present invention above, should be appreciated that to the invention is not restricted to above-mentioned preferred implementation, but various other modification can also be arranged.For example, in other preferred implementation, the outer surface of first push stopping part 42 can be the surface roughly cylindraceous that is parallel to central axis J1.Under above-mentioned this situation, when the external diameter of first push stopping part 42 is set to the diameter less than the lower end surface 611 of sleeve part 5, allow lubricant oil 46 to flow into the first thrust gap 81 smoothly from the lower ending opening 551 of communication paths 55.
In above-mentioned preferred implementation, for the first thrust gap 81, the dynamic pressure groove is defined on the lower end surface that defines first thrust surface 611 of sleeve part 5.But, notice that in other preferred implementation, the dynamic pressure groove can be defined on the upper surface that defines second thrust surface 421 of first push stopping part 42.Notice that also in other preferred implementation, the dynamic pressure groove can be defined in the upper surface 421 of lower end surface 611 and first push stopping part 42 of sleeve part 5 on the two.Similarly, in above-mentioned preferred implementation, for the second thrust gap 84, the dynamic pressure groove is defined on the upper-end surface that defines the 3rd thrust surface 521 of sleeve part 5.But, notice that in other preferred implementation, the dynamic pressure groove can be defined on the lower surface that defines the 4th thrust surface 431 of second push stopping part 43.Notice that also in other preferred implementation, the dynamic pressure groove can be defined in the lower surface 431 of upper-end surface 521 and second push stopping part 43 of sleeve part 5 on the two.
In other preferred implementation; Sleeve part 5 can be limited with another communication paths that radially extends to communication paths 55 from the middle part of its internal surface 541 within it, with allow flow of lubricant through bottom, another communication paths and the communication paths 55 of the first thrust gap 81, radial clearance 87 to accomplish circulation.In Fig. 6 and gear mechanism 4 shown in Figure 7, the lower ending opening 551 of communication paths 55 is set on ring-type plane of inclination 641 and outer ring-like face 642, extend.Yet, notice that in other preferred implementation, lower ending opening 551 only can be set in ring-type plane of inclination 641 or only extend on the circumferentia 642 outside.Gear mechanism 4 shown in Figure 12 just so.Sleeve part 5 can have the barrel surface of alternative ring-type plane of inclination 641, and the edge 681 of barrel surface periphery of 611 from the lower end surface extends upward, and forms shoulder.And under this situation, allow lubricant oil 46 to flow into the first thrust gap 81 smoothly from the lower ending opening 551 of communication paths 55.
Notice that in other preferred implementation, sleeve part 5 can be by the component limit that separates with rotor hub 31.Under this situation, the sectional shape of communication paths 55 generally is not circular.Notice that also in other preferred implementation, motor 12 can be installed in the disc driving equipment of disc drive unit or other type.
Notice that also in other preferred implementation, first push stopping part and/or second push stopping part can be the integral parts of axle.
The present invention can be applicable to use in the gear mechanism of hydrodynamic.Comprise that the motor of gear mechanism according to the embodiment of the present invention can be used as the motor of disc driving equipment, and also can be as the motor of other type equipment.
Claims (20)
1. gear mechanism, this gear mechanism comprises:
Stationary axle, this stationary axle along central axis with the vertical direction setting;
Sleeve part, this sleeve part are inserted with said axle within it, and this sleeve part is set to rotate with respect to said axle, and said axle and said sleeve part define radial clearance together betwixt;
First push stopping part; This first push stopping part is set to from the said diameter of axle to outside stretching, extension; And this first push stopping part has the upper surface that the lower surface with said sleeve part relatively is provided with, and the said lower surface of said sleeve part and the said upper surface of said first push stopping part define the first thrust gap together betwixt;
Cap, this cap is attached to said sleeve part, and this cap is set to relative with the outer surface of said first push stopping part; And
Lubricant oil; Wherein,
Said sleeve part is limited with the communication paths that extends upward from the bottom of this sleeve part and be communicated with the top of said radial clearance within it;
The said outer surface of said first push stopping part and said cap define tapered gaps together betwixt, and said tapered gaps increases at the downward direction width gradually, and in said tapered gaps, have the interface of said lubricant oil;
Said lubricant oil is arranged in said radial clearance, said communication paths, the said first thrust gap and the said tapered gaps;
Said radial clearance comprises radial bearing portion, through the first dynamic pressure groove said lubricant oil is produced radial dynamic pressure;
The said first thrust gap comprises the first thrust bearing portion, through the second dynamic pressure groove said lubricant oil is produced the thrust dynamic pressure;
The said lower surface of said sleeve part has the peripheral part that is arranged on the said first thrust gap radial outside, and said peripheral part is limited with the lower ending opening of said communication paths within it;
The said outer surface of said first push stopping part comprises the surface of the conical shaped that reduces gradually along the distance of downward direction and said central axis or is parallel to the surface of the general cylindrical shape of said extension of central axis;
In planimetric map, the outermost radial outside of the said outer surface of said first push stopping part partly is set to or tangent with the wall surface of said communication paths, perhaps than said wall surface more near said central axis;
Said tapered gaps is set to outermost radial outside point than said wall surface more near said central axis; And
Said peripheral part and said cap define guide clearance together betwixt, to guide with the direction of said lubricant oil said tapered gaps from said lower ending opening edge and towards the said first thrust gap.
2. gear mechanism according to claim 1, wherein,
The said lower surface of said sleeve part comprises first thrust surface, in said first thrust surface, is limited with the said second dynamic pressure groove;
Said first push stopping part comprises second thrust surface that relatively is provided with said first thrust surface;
The said first thrust gap is defined between said first thrust surface and said second thrust surface;
Said peripheral part comprises the first ring-type plane of inclination, and this first ring-type plane of inclination and said cap relatively are provided with, along with increasing from the radial distance of said first thrust surface and extending upward gradually; And
Said guide clearance is defined between said first ring-type plane of inclination and the said cap.
3. gear mechanism according to claim 2, wherein, the external diameter of said first push stopping part is less than the diameter of said first thrust surface.
4. gear mechanism according to claim 3, wherein, the hardness of said first push stopping part is lower than the hardness of said sleeve part.
5. gear mechanism according to claim 2, wherein, the said second dynamic pressure groove also is defined in the said first ring-type plane of inclination.
6. gear mechanism according to claim 1, this gear mechanism also comprises second push stopping part, this second push stopping part is set to from the said diameter of axle to outside stretching, extension, and this second push stopping part be set to relative with the upper-end surface of said sleeve part, wherein,
Said communication paths has the open upper end in the said upper-end surface that is defined in said sleeve part;
The said upper-end surface of said sleeve part comprises the 3rd thrust surface;
Said second push stopping part comprises the 4th thrust surface that relatively is provided with said the 3rd thrust surface; And
Said the 3rd thrust surface and said the 4th thrust surface define the second thrust gap together betwixt and between the said open upper end of the said top of said radial clearance and said communication paths.
7. gear mechanism according to claim 6, wherein, the diameter of said the 4th thrust surface is less than the diameter of said the 3rd thrust surface.
8. gear mechanism according to claim 7, wherein, the hardness of said second push stopping part is lower than the hardness of said sleeve part.
9. gear mechanism according to claim 6, wherein, the said second thrust gap comprises the second thrust bearing portion, through the 3rd dynamic pressure groove said lubricant oil is produced the thrust dynamic pressure.
10. gear mechanism according to claim 6, wherein, said communication paths is communicated with via the said second thrust gap with the said top of said radial clearance indirectly.
11. gear mechanism according to claim 1, wherein, said communication paths directly is communicated with the said top of said radial clearance.
12. gear mechanism according to claim 2; Wherein, Said cap comprises the second ring-type plane of inclination, and it is relative with the said first ring-type plane of inclination that this second ring-type plane of inclination is set to, along with increasing from the radial distance of said first thrust surface and extending upward gradually.
13. gear mechanism according to claim 12, wherein, said guide clearance increases at the downward direction width gradually.
14. gear mechanism according to claim 13, wherein, the Extreme breadth of said guide clearance is in the scope of 0.2mm to 0.4mm.
15. gear mechanism according to claim 1, wherein,
Said sleeve part comprises outstanding protuberance downwards, and this protuberance is set at the radial outside of the said lower ending opening of said communication paths; And
Said cap comprises with said central axis being the ring-type surface of contact at center, and this ring-type surface of contact is set to contact said protuberance, and is set to along the direction that is parallel to or is roughly parallel to said central axis relative with the part of said lower ending opening.
16. gear mechanism according to claim 1, wherein,
Said sleeve part has oblique cutting part, and this oblique cutting part is set at the said wall surface of said communication paths and the boundary between the said peripheral part; And
The said outermost radial outside part of the said outer surface of said first push stopping part overlaps with said oblique cutting part in planimetric map.
17. gear mechanism according to claim 1, wherein,
Said cap is included in the cylindrical part that is parallel to or is roughly parallel to the direction extension of said central axis;
Said sleeve part has the attachment of lid and shoulder, and said lid attachment has the diameter that reduces and is set at the lower end of the outer surface of said sleeve part, and it is adjacent with the upper end of said lid attachment that said shoulder is set to;
Said cylindrical part arrives said lid attachment through adhesive; And
The upper end of said shoulder and said cylindrical part defines the gap along the direction that is parallel to or be roughly parallel to said central axis together betwixt.
18. gear mechanism according to claim 17, wherein, said lid attachment comprises first diameter reducing part and second diameter reducing part, and said second diameter reducing part is set under said first diameter reducing part and radially inner side.
19. a spindle motor, this spindle motor comprises:
Gear mechanism according to claim 1;
Stationary part, said axle is fixed on this stationary part; And
The rotation section, said sleeve part is attached on this rotation section.
20. a disc driving equipment, this disc driving equipment comprises:
Dish;
Motor according to claim 19, this motor is set to rotate said dish;
Access portion, this access portion are set to read information or information is write said dish from said dish; And
Housing, this housing hold said motor and said access portion.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2009105583 | 2009-04-23 | ||
| JP2009-105583 | 2009-04-23 | ||
| JP2009-290163 | 2009-12-22 | ||
| JP2009290163A JP2010270905A (en) | 2009-04-23 | 2009-12-22 | Bearing mechanism, motor, and disk drive device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101871486A CN101871486A (en) | 2010-10-27 |
| CN101871486B true CN101871486B (en) | 2012-07-04 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN2010101619129A Expired - Fee Related CN101871486B (en) | 2009-04-23 | 2010-04-15 | Bearing mechanism, spindle motor and disc driving device |
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Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5838734B2 (en) * | 2010-12-27 | 2016-01-06 | 日本電産株式会社 | Spindle motor, disk drive device, and spindle motor manufacturing method |
| JP2014059047A (en) * | 2012-09-14 | 2014-04-03 | Samsung Electro-Mechanics Co Ltd | Spindle motor |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1677795A (en) * | 2004-03-30 | 2005-10-05 | 日立环球储存科技荷兰有限公司 | Spindle motor and magnetic disk drive |
| CN1730957A (en) * | 2004-08-05 | 2006-02-08 | 松下电器产业株式会社 | Hydrodynamic bearing device |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP3718073B2 (en) * | 1999-02-19 | 2005-11-16 | 日本電産株式会社 | Hydrodynamic bearing motor |
| JP2007162759A (en) * | 2005-12-09 | 2007-06-28 | Matsushita Electric Ind Co Ltd | Dynamic-pressure fluid bearing device, motor, recording disk drive device, and assembling tool |
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Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1677795A (en) * | 2004-03-30 | 2005-10-05 | 日立环球储存科技荷兰有限公司 | Spindle motor and magnetic disk drive |
| CN1730957A (en) * | 2004-08-05 | 2006-02-08 | 松下电器产业株式会社 | Hydrodynamic bearing device |
Non-Patent Citations (2)
| Title |
|---|
| JP特开2000-245104A 2000.09.08 |
| JP特开2007-162759A 2007.06.28 |
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